Patent Publication Number: US-2022212384-A1

Title: Injection Molding Apparatus with Insulated Integrated Actuator Electronic Drive

Description:
RELATED APPLICATIONS 
     This application is a continuation in part of and claims the benefit of priority to U.S. application Ser. No. 17/408,562 filed Aug. 23, 2021 (7185US2) which in turn is a continutation of and claims and is entitled to the benefit of priority to international application PCT/US2020/019669 (7185WO0) filed Feb. 25, 2020 which in turn claims and is entitled to the benefit of priority of U.S. Provisional Application Ser. No. 62/810,204 filed Feb. 25, 2019 and U.S. Provisional Application Ser. No. 62/862,277 filed Jun. 17, 2019 the disclosures of all of which are incorporated by reference as if fully set forth herein. 
     This application further claims the benefit of priority to U.S. provisional application 63/226,779 filed Jul. 29, 2021, the disclosure of which is incorporated by reference as if fully set forth herein. 
     This application is also a continuation in part of and claims the benefit of priority to U.S. application Ser. No. 17/181,292 filed Feb. 22, 2021 (7187US1) which is in turn a continuation of international application PCT/US2020/046736 (7187WO0) filed Aug. 18, 2020 which in turn claims and is entitled to the benefit of priority of U.S. provisional application No. 62/889,385 (7187US) filed Aug. 20, 2019, the disclosures of all of which are incorporated by reference as if fully set forth herein. 
     The disclosures of all of the following are incorporated by reference in their entirety as if fully set forth herein: U.S. Pat. Nos. 5,894,025, 6,062,840, 6,294,122 (7018), U.S. Pat. Nos. 6,309,208, 6,287,107, 6,343,921, 6,343,922, 6,254,377, 6,261,075, 6,361,300 (7006), U.S. Pat. Nos. 6,419,870, 6,464,909 (7031), U.S. Pat. No. 6,062,840 (7052), U.S. Pat. No. 6,261,075 (7052US1), U.S. Pat. Nos. 6,599,116, 7,234,929 (7075US1), U.S. Pat. No. 7,419,625 (7075US2), U.S. Pat. No. 7,569,169 (7075US3), U.S. Pat. No. 8,297,836 (7087) U.S. patent application Ser. No. 10/214,118, filed Aug. 8, 2002 (7006), U.S. Pat. No. 7,029,268 (7077US1), U.S. Pat. No. 7,270,537 (7077US2), U.S. Pat. No. 7,597,828 (7077US3), U.S. patent application Ser. No. 09/699,856 filed Oct. 30, 2000 (7056), U.S. patent application Ser. No. 10/269,927 filed Oct. 11, 2002 (7031), U.S. application Ser. No. 09/503,832 filed Feb. 15, 2000 (7053), U.S. application Ser. No. 09/656,846 filed Sep. 7, 2000 (7060), U.S. application Ser. No. 10/006,504 filed Dec. 3, 2001, (7068), International Application WO2011119791 filed Mar. 24, 2011 (7094), U.S. application Ser. No. 10/101,278 filed Mar. 19, 2002 (7070) and PCT Application No. PCT/US11/062099 (7100WO0) and PCT Application No. PCT/US11/062096 (7100WO1), U.S. Pat. Nos. 8,562,336, 8,091,202 (7097US1) and U.S. Pat. No. 8,282,388 (7097US2), U.S. Pat. No. 9,205,587 (7117U50), U.S. application Ser. No. 15/432,175 (7117US2) filed Feb. 14, 2017, U.S. Pat. No. 9,144,929 (7118US0), U.S. Publication No. 20170341283 (7118US3), U.S. Pat. No. 9,724,861 (7129US4), U.S. Pat. No. 9,662,820 (7129US3), international application WO2014172100 (7131WO0), Publication No. WO2014209857 (7134WO0), international application WO2015066004 (7140WO0), Publication No. WO2015006261 (7135WO0), International application Publication No. WO2016153632 (7149WO2), International application publication no. WO2016153704 (7149WO4), U.S. Pat. No. 9,937,648 (7135US2), U.S. Pat. No. 10,569,458 (7162US1), International Application WO2017214387 (7163WO0), International Application PCT/US17/043029 (7165WO0) filed Jul. 20, 2017, International Application PCT/US17/043100 (7165WO1), filed Jul. 20, 2017 and International Application PCT/US17/036542 (7163WO0) filed Jun. 8, 2017 and International Application WO2018129015 (7169WO0), International application WO2018148407 (7170WO0), International application WO2018148407 (7171WO0), international application WO2018175362 (7172WO0), international application WO2018194961 (7174WO0), international application WO2018200660 (7176WO0), international application WO2019013868 (7177WO0), international application WO2019100085 (7178WO0), international application WO2020176479 (7185WO0), international application WO2021/034793 (7187WO0), international application WO2021080767 (7188WO0). 
    
    
     BACKGROUND OF THE INVENTION 
     Injection molding systems have been developed for performing injection molding cycles controlled by an electric motor actuator mounted for protection from overheating. The electrical drive systems are typically contained within a master electronic controller device. Such electrical drive systems when incorporated into the circuitry, boards or housing of the master controller can suffer loss of speed of communication and loss of integrity of digital and analog signal communication between the processors of the master controller and the driver components of the electric actuator. Separating the electric drive element from the master controller and mounting the electric drive element on or to or within the housing of the electric actuator can provide improved operation of the master controller as well as improved communication of electronic signals back and forth between the master controller and the driver components of the electric actuator. 
     SUMMARY OF THE INVENTION 
     In accordance with the invention there is provided An injection molding apparatus, comprising: 
     a heatable manifold arranged to receive molten injection fluid from an injection molding machine and substantially maintain the molten injection fluid at a selected temperature; 
     one or more nozzles; 
     a flow channel formed through the manifold and at least one of the one or more nozzles, the flow channel arranged to pass the molten injection fluid received by the manifold and deliver the molten injection fluid to a gate of a mold cavity; 
     an electrical drive having an interface arranged to receive and distribute electrical energy in controllably varied amounts during an injection cycle; 
     a valve pin; 
     an actuator coupled to the valve pin and arranged to control a flow of molten injection fluid toward the mold cavity by controllably moving the valve pin, the actuator having: 
     a driver arranged to receive the controllably varied electrical energy from the electrical drive and drive the actuator in response to the controllably varied electrical energy from the electrical drive; and 
     an actuator housing that houses the driver, wherein the electrical drive is housed within or by the actuator housing or mounted on or to the actuator housing via a drive mount; 
     a source of heat absorptive fluid; and 
     at least one channel formed in or proximate one or the other or both of the actuator housing and the drive mount and sealably interconnected to the source, wherein concurrent the injection cycle, the heat absorptive fluid is routed through the at least one channel in a flow that absorbs heat from one or the other or both of the actuator housing and the drive mount. 
     Such an apparatus can further comprise: 
     a linear travel converter interconnected to the actuator in an arrangement that allows the valve pin to be driven along a linear axis (X)that is either non coaxial or coaxial relative to a drive axis (Y) of the actuator. 
     In such an apparatus the at least one channel is typically disposed within a heat conductive mount mounted in heat conductive communication with the heatable manifold, and the linear travel converter is mounted in heat conductive communication with the heat conductive mount. 
     The linear travel converter typically further comprises: 
     a converter housing mounted in direct or indirect heat conductive communication to or with the heatable manifold and the actuator housing. 
     The drive mount is typically mounted in heat communication with the actuator housing. 
     One or the other or both of the actuator housing and the electrical drive are preferably in substantial heat communication with the heatable manifold. 
     The at least one channel is typically disposed within a heat conductive housing body mountable in heat communication with the actuator housing. 
     The at least one channel is typically disposed within a heat conductive mount mounted in heat conductive communication with the heatable manifold, and wherein one or more of the actuator housing and the electrical drive is mounted in heat conductive communication with the heat conductive mount. 
     The actuator can further comprise: 
     a drive member; and 
     a drive mechanism, the drive mechanism being either a transmission that permits the driver to rotatably drive the drive member linearly via a rotor or a linear drive mechanism that permits the driver to directly drive the drive member linearly. 
     One or the other or both of the actuator housing and the drive mount are comprised, at least in part, of a metal material and mounted in substantially direct metal to metal heat conductive communication with the heatable manifold. 
     The electrical drive typically includes a pulse-width modulator (PWM) that converts received electrical energy into a reciprocating voltage waveform signal, the reciprocating voltage waveform signal being adapted to drive a corresponding phase-coil of the actuator driver. 
     Such an apparatus can further comprise: 
     one or more sensors arranged to generate one or more sensor signals indicative of one or more of:
         a rotational position of the actuator;   a linear position of the actuator;   a position of a valve pin associated with the actuator;   a pressure of the molten injection fluid within the flow channel;   a temperature of the molten injection fluid within the flow channel of the heatable manifold;   a pressure of the molten injection fluid within a nozzle channel;   a temperature of the molten injection fluid within the nozzle channel;   a pressure of the molten injection fluid within the mold cavity;   a temperature of the molten injection fluid within the mold cavity;   a pressure of the molten injection fluid within a barrel of the injection molding machine; and   a temperature of the molten injection fluid within the barrel of the injection molding machine; and,       

     an actuator controller arranged, in response to at least one of the one or more sensor signals, to direct at least one operation of the actuator or its associated valve pin, the at least one operation including to: 
     travel during the injection cycle to positions that correspond to a predetermined profile, wherein the predetermined profile is associated with a set of injection fluid pressures, linear or rotational pin positions, linear actuator or valve pin positions, barrel screw positions, barrel pressures or actuator drive fluid pressures corresponding to the at least one of the one or more sensor signals; 
     withdraw from a closed gate position upstream at a reduced velocity over a selected path of upstream travel; 
     travel downstream at a reduced velocity over a selected path of downstream travel where a distal tip end of the valve pin travels to a gate closed position; or
         travel upstream or downstream to an intermediate position between a gate closed position and a fully upstream position, wherein the valve pin is maintained in the intermediate position for a selected period of time during the injection cycle, and wherein, in the intermediate position, the distal tip end of the valve pin restricts flow of the molten injection fluid to less than a maximum flow.       

     In another aspect of the invention there is provided an injection molding method, comprising: 
     providing an actuator housing adapted to support an electrical drive, wherein supporting the electrical drive includes housing the electrical drive within the actuator housing or mounting the electrical drive on or to the actuator housing via a drive mount; 
     heating a manifold; 
     receiving at the manifold a molten injection fluid from an injection molding machine; 
     substantially maintaining the molten injection fluid at a selected temperature; 
     receiving the molten injection fluid from the manifold in a flow channel formed through the manifold and at least one nozzle; 
     delivering the molten injection fluid to a gate of a mold cavity; 
     distributing, with the electrical drive, electrical energy in controllably varied amounts during the course of an injection cycle to a driver; 
     driving an actuator in response to the controllably varied electrical energy; 
     moving a valve pin with the actuator and thereby controlling a flow of molten injection fluid toward the mold cavity; 
     concurrent the injection cycle, routing a heat absorptive fluid through at least one channel formed in or proximate one or the other or both of the actuator housing and the drive mount; and 
     absorbing heat from one or the other or both of the actuator housing and the drive mount into the heat absorptive fluid. 
     In such a method driving the actuator typically includes: 
     driving a drive member along a linear drive axis (Y); and 
     driving the valve pin along a non-coaxial pin axis (X). 
     In such a method driving the actuator can include: 
     driving a drive member along a linear drive axis (X); and 
     driving the valve pin along a coaxial pin axis (X). 
     In another aspect of the invention there in provided an injection molding apparatus, comprising: 
     an injection molding machine; 
     a heated manifold arranged to receive a flow of injection fluid injected by the injection molding machine; 
     a flow channel arranged to receive at least some of the injection fluid distributed by the heated manifold, the flow channel further arranged to deliver the injection fluid to a gate of a mold cavity; 
     an electrical drive having an interface arranged to receive and controllably distribute electrical energy in controllably varied amounts during an injection cycle; 
     an actuator having a driver and rotor assembly, the driver adapted to controllably drive the rotor rotatably around a drive axis (Y) in response to at least some of the electrical energy from the electrical drive; and 
     an actuator housing arranged to house the actuator and at least part of the driver and rotor assembly, wherein the actuator housing and the electrical drive are disposed remote from the heated manifold in substantial isolation from heat of the heated manifold during the injection cycle. 
     Such an apparatus typically further comprises: 
     a source of heat absorptive fluid; and 
     at least one channel formed in or proximate the actuator housing and sealably interconnected to the source, wherein concurrent the injection cycle, the heat absorptive fluid is routed through the at least one channel in a flow that absorbs heat from the actuator housing. 
     Such an apparatus can further comprise: 
     a drive mount within or coupled to the actuator housing, the drive mount arranged to support the electrical drive; 
     a source of heat absorptive fluid; and 
     at least one channel formed in or proximate the drive mount and sealably interconnected to the source, wherein concurrent the injection cycle, the heat absorptive fluid is routed through the at least one channel in a flow that absorbs heat from the drive mount. 
     Such an apparatus can futher comprise: 
     a cooling device disposed between the heated manifold and the actuator housing, the cooling device adapted to substantially isolate the electrical drive from heat of the heated manifold during the injection cycle. 
     In such an apparatus the cooling device typically has a body of highly heat conductive material containing one or more channels arranged to pass a flow of heat absorptive fluid is routed. 
     In another aspect of the invention there is provided an injection molding apparatus, comprising: 
     a heatable manifold ( 40 ) arranged to receive molten injection fluid ( 18 ) from an injection molding machine ( 13 ) and substantially maintain the molten injection fluid at a selected temperature; 
     one or more nozzles ( 20 ,  22 ,  24 ); 
     a flow channel ( 19 ,  42 ,  44 ,  46 ) formed through the manifold and at least one of the one or more nozzles, the flow channel arranged to pass the molten injection fluid received by the manifold and deliver the molten injection fluid to a gate ( 32 ,  34 ,  36 ) of a mold cavity ( 30 ); 
     an electrical drive ( 940   d ,  941   d ,  942   d ) having an interface arranged to receive and distribute electrical energy in controllably varied amounts during an injection cycle; 
     a valve pin ( 1040 ,  1041 ,  1042 )); an actuator ( 940 ,  941 ,  942 ) coupled to the valve pin and arranged to control a flow of molten injection fluid toward the mold cavity ( 30 ) by controllably moving the valve pin, the actuator having:
         a driver ( 940   dr ,  941   dr ,  942   dr ), arranged to receive the controllably varied electrical energy from the electrical drive ( 940   d ,  941   d ,  942   d ) and drive the actuator ( 940 ,  941 ,  942 ) in response to the controllably varied electrical energy from the electrical drive; and   an actuator housing ( 940   h ,  941   h ,  942   h ) that houses the driver ( 940   dr ,  941   dr ,  942   dr ), wherein the electrical drive ( 940   d ,  941   d ,  942   d ) is housed within or by the actuator housing ( 940   h ,  941   h ,  942   h ) or mounted on or to the actuator housing via a drive mount ( 20 ,  940   ds ,  941   ds ),       

     a source of heat absorptive fluid ( 260 ,  125   f ); and 
     at least one channel ( 25 ,  33 ,  125 ) formed in or proximate one or the other or both of the actuator housing ( 940   h ,  941   h ,  942   h ) and the drive mount ( 940   ds ,  941   ds ) and sealably interconnected to the source, wherein concurrent the injection cycle, the heat absorptive fluid is routed through the at least one channel ( 25 ,  33 ,  125 ) in a flow that absorbs heat from one or the other or both of the actuator housing and the drive mount. 
     In such an apparatus the drive mount ( 940   ds ,  941   ds ) is typically mounted in heat communication or contact with the actuator housing ( 940   h ,  941   h ,  942   h ). 
     One or the other or both of the actuator housing ( 20 ,  940   h ,  941   h ,  942   h ) and the electrical drive ( 940   d ,  941   d ,  942   d ) are typically in substantial heat communication with the heatable manifold ( 40 ). 
     The at least one channel ( 25 ,  33 ,  125 ) can be disposed within a heat conductive housing body ( 20 ,  940   ds ,  941   ds ) mountable in heat communication or contact with the actuator housing ( 940   h ,  941   h ,  942   h ). 
     The heat conductive housing body ( 20 ,  940   ds ,  941   ds ) can be adapted to be readily attachable to and detachable from the actuator housing ( 940   h ,  941   h ,  942   h ). 
     The at least one channel ( 25 ,  33 ,  125 ) can be disposed within a heat conductive mount ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) mounted in heat conductive communication or contact with the heatable manifold ( 40 ). 
     The heat conductive mount ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) can be adapted to be readily attachable to and detachable from the heatable manifold ( 40 ) 
     One or more of the actuator housing ( 20 ,  940   h ,  941   h ,  942   h ) and the electrical drive ( 940   d ,  941   d ,  942   d ) can be mounted in heat conductive communication or contact with the heat conductive mount ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     One or more of the actuator housing ( 20 ,  940   h ,  941   h ,  942   h ) and the electrical drive ( 940   d ,  941   d ,  942   d ) can be adapted to be readily attachable to and detachable from the heat conductive mount ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     Such an apparatus as above can further comprise a linear travel converter ( 15 ) interconnected to the actuator ( 940 ,  941 ,  942 ) in an arrangement that allows the valve pin ( 1040 ,  1041 ,  1042 ) to be driven along a linear axis (X) that is either non coaxial or coaxial relative to a drive axis (Y) of the actuator. 
     In such an apparatus the at least one channel ( 25 ,  33 ,  125 ) can be disposed within a heat conductive mount ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) mounted in heat conductive communication or contact with the heatable manifold ( 40 ) wherein the linear travel converter ( 15 ) is adapted to be mounted in heat conductive communication with the heat conductive mount ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     In such an embodiment, the linear travel converter ( 15 ) is typically adapted to be readily attachable to and detachable from the heat conductive mount ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     In such an apparatus the actuator typically further comprises: 
     a drive member ( 150 ,  940   l ,  9401   d ); and 
     a drive mechanism, the drive mechanism being either a transmission ( 190 ,  191 ) that permits the driver ( 100 ,  200 ,  940   dr ,  941   dr ,  942   dr ) to rotatably drive the drive member ( 150 ) linearly via a rotor ( 250 ,  940   r ,  941   r ,  942   r ) or a linear drive mechanism ( 940   dr ,  9401   d ) that permits the driver to directly drive the drive member ( 9401   d ) linearly. 
     One or the other or both of the actuator housing ( 20 ,  940   h ,  941   h ,  942   h ) and the drive mount ( 940   ds ,  941   ds ) are typically comprised, at least in part, of a metal material and can be mounted in substantially direct metal to metal heat conductive communication or contact with the heatable manifold ( 40 ). 
     One or the other or both of the actuator housing ( 20 ,  940   h ,  941   h ,  942   h ) and the drive mount ( 940   ds ,  941   ds ) can be mounted in substantially direct metal to metal heat conductive communication or contact with the heatable manifold ( 40 ) via a mount ( 60 ,  60   s ) that is comprised of either a heat insulative material or a heat conductive material. 
     The electrical drive ( 940   d ,  941   d ,  942   d ) typically includes a pulse-width modulator (PWM) that converts received electrical energy into a reciprocating voltage waveform signal, the reciprocating voltage waveform signal being adapted to drive a corresponding phase-coil of the actuator driver ( 940   dr ,  941   dr ,  942   dr ). 
     The linear travel converter typically further comprises: 
     a converter housing ( 120 ,  9401   h ) mounted in direct or indirect heat conductive communication or contact with the heatable manifold ( 40 ) and the actuator housing ( 20 ,  940   h ,  941   h ,  942   h ). 
     Such an apparatus as described above can further comprise: 
     one or more sensors ( 950 ,  951 ,  952 ) arranged to generate one or more sensor signals indicative of one or more of: 
     a rotational position of the actuator ( 940 ,  941 ,  942 ); 
     a linear position of the actuator ( 940 ,  941 ,  942 ); 
     a position of a valve pin ( 1040 ,  1041 ,  1042 ) associated with the actuator ( 940 ,  941 ,  942 ); 
     a pressure of the molten injection fluid ( 18 ) within the flow channel ( 19 ); 
     a temperature of the molten injection fluid ( 18 ) within the flow channel ( 19 ) of the heatable manifold ( 40 ); 
     a pressure of the molten injection fluid ( 18 ) within a nozzle channel ( 42 ,  44 ,  46 ); 
     a temperature of the molten injection fluid ( 18 ) within the nozzle channel ( 42 ,  44 ,  46 ; 
     a pressure of the molten injection fluid ( 18 ) within the mold cavity ( 30 ); 
     a temperature of the molten injection fluid ( 18 ) within the mold cavity ( 30 ); 
     a pressure of the molten injection fluid ( 18 ) within a barrel of the injection molding machine ( 13 );and 
     a temperature of the molten injection fluid ( 18 ) within the barrel of the injection molding machine ( 13 ); and 
     an actuator controller ( 16 ) arranged, in response to at least one of the one or more sensor signals, to direct at least one operation of the actuator ( 5 ,  940 ,  941 ,  942 ) or its associated valve pin ( 1040 ,  1041 ,  1042 ), the at least one operation including to: 
     travel during the injection cycle to positions that correspond to a predetermined profile, wherein the predetermined profile is associated with a set of injection fluid pressures, linear or rotational pin positions, linear actuator or valve pin positions, barrel screw positions, barrel pressures or actuator drive fluid pressures corresponding to the at least one of the one or more sensor signals; or, withdraw from a closed gate position upstream at a reduced velocity over a selected path of upstream travel and subsequently at a selected higher velocity than the reduced velocity; or, 
     travel downstream at a reduced velocity over a selected path of downstream travel where a distal tip end of the valve pin travels to a gate closed position; or, 
     travel upstream or downstream to an intermediate position between a gate closed position and a fully upstream position, wherein the valve pin is maintained in the intermediate position for a selected period of time during the injection cycle, and wherein, in the intermediate position, the distal tip end of the valve pin restricts flow of the molten injection fluid to less than a maximum flow. 
     In another aspect of the invention there is provided an injection molding method, comprising: 
     providing an actuator housing ( 940   h ,  941   h ,  942   h ) adapted to support an electrical drive ( 940   d ,  941   d ,  942   d ), wherein supporting the electrical drive includes housing the electrical drive within the actuator housing or mounting the electrical drive on or to the actuator housing via a drive mount ( 941   ds ,  942   ds ), heating a manifold ( 40 ); 
     receiving at the manifold a molten injection fluid ( 18 ) from an injection molding machine ( 13 ); 
     substantially maintaining the molten injection fluid at a selected temperature; 
     receiving the molten injection fluid from the manifold in a flow channel ( 19 ,  42 ,  44 ,  46 ) formed through the manifold ( 40 ) and at least one nozzle  20 ,  22 ,  24 ); 
     delivering the molten injection fluid to a gate ( 32 ,  34 ,  36 ) of a mold cavity ( 30 ); 
     distributing, with the electrical drive ( 940   d ,  941   d ,  942   d ), electrical energy in controllably varied amounts during the course of an injection cycle to a driver ( 940   dr ,  941   dr ,  942   dr ); 
     driving an actuator in response to the controllably varied electrical energy; 
     moving a valve pin ( 1040 ,  1041 ,  1042 ) with the actuator and thereby controlling a flow of molten injection fluid ( 18 ) toward the mold cavity ( 30 ); 
     concurrent the injection cycle, routing a heat absorptive fluid ( 260 ) through at least one channel ( 25 ,  33 ,  125 ) formed in or proximate one or the other or both of the actuator housing ( 940   h ,  941   h ,  942   h ) and the drive mount ( 940   ds ,  941   ds ), and 
     absorbing heat from one or the other or both of the actuator housing and the drive mount into the heat absorptive fluid ( 260 ). 
     In such a method driving the actuator ( 940 ,  941 ,  942 ) can include: 
     driving a drive member ( 150 ) along a linear drive axis (Y); and driving the valve pin ( 1040 ,  1041 ,  1042 ) along a non-coaxial pin axis (X). 
     In such a method driving the actuator ( 940 ,  941 ,  942 ) can include: 
     driving a drive member ( 9401 ,  9401   d ) along a linear drive axis (X); and 
     driving the valve pin ( 1040 ,  1041 ,  1042 ) along a coaxial pin axis (X). 
     In another aspect of the invention there is provided an injection molding apparatus ( 10 ) comprising an injection molding machine ( 13 ) that injects a flow of injection fluid ( 18 ) to a heated manifold ( 40 ) that distributes the injection fluid ( 18 ) to a flow channel that delivers the injection fluid to a gate ( 32 ,  34 ,  36 ) of a mold cavity ( 30 ), the injection molding apparatus ( 10 ) comprising: 
     an actuator ( 940 ,  941 ,  942 ) comprised of a rotor ( 940   r ,  941   r ,  942   r ) having a drive axis (Y) and a driver ( 940   dr ,  941   dr ,  942   dr ) interconnected to the rotor ( 940   r ,  941   r ,  942   r ) adapted to controllably drive the rotor rotatably around the drive axis Y, the driver ( 940   dr ,  941   dr ,  942   dr ) receiving electrical energy or power from an electrical drive ( 940   d ,  941   d ,  942   d ), 
     the electrical drive ( 940   d ,  941   d ,  942   d ) comprising an interface that receives and controllably distributes electrical energy or power in controllably varied amounts during the course of an injection cycle to the driver ( 940   dr ,  941   dr ,  942   dr ), the actuator having a housing ( 940   h ,  941   h ,  942   h ) that houses the rotor ( 940   r ,  941   r ,  942   r ) and the driver ( 940   dr ,  941   dr ,  942   dr ), the housing being adapted to support the rotor ( 940   r ,  941   r ,  942   r ), 
     the electrical drive ( 940   d ,  941   d ,  942   d ) being housed within or by the housing ( 940   h ,  941   h ,  942   h ) or being mounted on or to the housing ( 940   h ,  941   h ,  942   h ), the housing ( 940   h ,  941   h ,  942   h ) and the electrical drive ( 940   d ,  941   d ,  942   d ) being mounted on, to or in close proximity to the heated manifold ( 40 ), 
     the apparatus including a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) disposed between the heated manifold ( 40 ) and the housing ( 940   h ,  941   h ,  942   h ), 
     the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from communication with heat emanating from the heated manifold ( 40 ) or to heat sink or absorb heat communicated or communicable to the electrical drive ( 940   d ,  941   d ,  942   d ) from the heated manifold ( 40 ) or both. 
     The cooling device (( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) is typically adapted to substantially isolate or insulate the housing ( 940   h ,  941   h ,  942   h ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
     The electrical drive ( 940   d ,  941   d ,  942   d ) is typically mounted on or to the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     The electrical drive ( 940   d ,  941   d ,  942   d ) can be housed within or by the actuator housing ( 940   h ,  941   h ,  942   h ) or physically mounted on or to the housing ( 940   h ,  941   h ,  942   h ) in thermally conductive communication or contact therewith. 
     The housing is typically mounted on or to the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     The housing ( 940   h ,  941   h ,  942   h ) can be mounted in direct heat communicative contact with the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     The housing ( 940   h ,  941   h ,  942   h ) can be mounted on or to the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) via a mount ( 60 ) comprised of a heat insulative material. 
     In such an embodiment the mount ( 60 ) can be adapted to form a gap (G′) between the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) and one or the other or both of the housing ( 940   h ) and the electric drive ( 940   d ). 
     In such an embodiment the mount ( 60 ) can be adapted to form a gap (G) between the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) and the manifold ( 40 ). 
     The housing ( 940   h ,  941   h ,  942   h ) can be interconnected to a rotary to linear converter device ( 9401 ,  9411 ,  9421 ) in an arrangement wherein the valve pin ( 1040 ,  1041 ,  1042 ) is driven along a linear axis (X) that is non coaxial relative to a drive axis (Y) of the actuator, the rotary to linear converter device being mounted to the cooling device in direct heat communicative contact therewith. 
     The housing ( 940   h ,  941   h ,  942   h ) can be interconnected to a rotary to linear converter device ( 9401 ,  9411 ,  9421 ) in an arrangement wherein the valve pin ( 1040 ,  1041 ,  1042 ) is driven along a linear axis (X) that is non coaxial relative to a drive axis (Y) of the actuator, the rotary to linear converter device being mounted on or to the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) via a mount ( 60 ) comprised of a heat insulative material. 
     In such an embodiment the mount ( 60 ) can be adapted to form a gap (G′) between the cooling device and one or the other or both of the linear converter device ( 940   l ), the actuator housing ( 940   h ) and the electric ( 940   d ). 
     In such an embodiment the mount ( 60 ) can be adapted to form a gap (G) between the cooling device and the manifold ( 40 ). 
     The housing ( 940   h ,  941   h ,  942   h ) can be interconnected to a rotational speed control device ( 46 ) that is interconnected to a rotary to linear converter device ( 9401 ,  9411 ,  9421 ) in an arrangement wherein the valve pin ( 1040 ,  1041 ,  1042 ) is driven along a linear axis (X) that is non coaxial relative to a drive axis (Y) of the actuator, the rotary to linear converter device being mounted in direct heat communicative contact with the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     The housing ( 940   h ,  941   h ,  942   h ) can be interconnected to a rotational speed control device ( 46 ) that is interconnected to a rotary to linear converter device ( 9401 ,  9411 ,  9421 ) in an arrangement wherein the valve pin ( 1040 ,  1041 ,  1042 ) is driven along a linear axis (X) that is non coaxial relative to a drive axis (Y) of the actuator, the rotary to linear converter device being mounted on or to the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) via a mount ( 60 ) comprised of a heat insulative material. 
     In such an embodiment the mount ( 60 ) can be adapted to form a gap (G′) between the cooling device and one or the other or both of the linear converter device ( 9401 ,  9401   h ), the actuator housing ( 940   h ), the rotational speed control device ( 46 ) and the electric drive ( 940   d ). 
     In such an embodiment the mount ( 60 ) can be adapted to form a gap (G) between the cooling device ( 940   mc ) and the manifold ( 40 ). 
     The cooling device ( 940   mc ,  941   mc ,  942   mc ) can be mounted in direct or indirect thermal contact or communication with the heated manifold ( 40 ). 
     The cooling device can comprise a body of highly heat conductive material that can contain one or more channels through which a flow of a selected cool or cooling fluid is routed. 
     The cooling device can comprises a body of selected heat conductive material that can be actively cooled via application through, on or to the body of selected material cool or cooling fluid. 
     The cooling device can comprise a Peltier effect device. 
     The electric actuator ( 940 ,  941 ,  942 ) typically comprises a driver ( 940   dr ,  941   dr ,  942   dr ) comprised of one or more of a stator and armature that are interconnected to a rotatably mounted rotor or shaft ( 940   r ,  941   r ,  942   r ) such that when the drivers ( 940   dr ,  941   dr ,  942   dr ) rotate on application and receipt of electrical energy or power, the shafts ( 940   r ,  941   r ,  942   r ) are rotated. 
     The rotor ( 940   r ,  941   r ,  942   r ) can have a drive axis (Y), the driver ( 940   dr ,  941   dr ,  942   dr ) being interconnected to the rotor ( 940   r ,  941   r ,  942   r ) and adapted to controllably drive the rotor ( 940   r ,  941   r ,  942   r ) rotatably around the drive axis Y. 
     The driver ( 940   dr ,  941   dr ,  942   dr ) typically receives electrical energy or power from the electrical drive ( 940   d ,  941   d ,  942   d ). 
     The electrical drive ( 940   d ,  941   d ,  942   d ) is typically interconnected to a controller ( 16 ) that includes a processor that communicates instruction signals to the electric actuator, the controller ( 16 ) being mounted remote from the electrc drive ( 940   d ,  941   d ,  942   d ) that typically receives electrical energy or power from a power source (PS) and controllably distributes the received electrical energy or power in controllably varied amounts during the course of an injection cycle to the drivers ( 940   dr ,  941   dr ,  942   dr ). 
     The housing ( 940   h ,  941   h ,  942   h ) typically houses the rotor ( 940   r ,  941   r ,  942   r ) and the driver ( 940   dr ,  941   dr ,  942   dr ) and is adapted to support the rotor ( 940   r ,  941   r ,  942   r ) such that the rotor is drivably rotatable ( 940   rt ,  941   rt ,  942   rt ). 
     The cooling device ( 940   mc ,  941   mc ,  942   mc ) can be mounted on or to an intermediate mount ( 940   m ) comprised of a metal material, the intermediate mount ( 940   m ) being mounted in direct metal to metal contact or communication with the heated manifold ( 40 ). 
     In such an embodiment, the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) can be disposed between the heated manifold ( 40 ) and the rotary to linear converter device ( 9401 ,  9411 ,  9421 ), the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being adapted to substantially isolate or insulate the linear converter device ( 9401 ,  9411 ,  9421 ) from substantial communication of heat emanating or emitted from the heated manifold ( 40 ). 
     The electrical drive ( 940   d ,  941   d ,  942   d ) is typically housed within or by the housing ( 940   h ,  941   h ,  942   h ) or is physically mounted on or to the housing ( 940   h ,  941   h ,  942   h ) in thermally conductive communication or contact therewith. 
     The electrical drive ( 940   d ,  941   d ,  942   d ) typically includes a pulse-width modulator (PWM) that converts received electrical energy or power into sinusoidal voltage waveforms, each sinusoidal voltage waveform being adapted to drive a corresponding phase-coil of the actuator driver ( 940   dr ,  941   dr ,  942   dr ). 
     The pulse-width modulator (PWM) typically comprises an inverter or a comparator. 
     The pulse width modulator (PWM) typically comprises a three-phase inverter that converts electrical energy or power received from the interface into three sinusoidal voltage waveforms, each one of the three sinusoidal voltage waveforms being adapted to drive a corresponding one of three phase-coils of the actuator driver. 
     The electrical energy or power received at or by the pulse width modulator (PWM) typically comprises a DC bus voltage. 
     The interface is typically adapted to receive one or more control signals from a controller ( 16 ) of the injection molding apparatus ( 10 ) and to convert electrical energy or power received the power source (PS) into sinusoidal waveforms based on the one or more control signals. 
     The interface is typically comprised of the pulse width modulator (PWM) which converts electrical energy or power received from the power source into sinusoidal waveforms based on the one or more control signals. 
     The one or more control signals received by the interface can contain control information causing the pulse width modulator (PWM) to convert the received electrical energy or power into sinusoidal waveforms adapted to drive the corresponding phase-coils of the actuator driver to adjust one or more of a position, a velocity or torque of the actuator rotor ( 940   r ,  941   r ,  942   r ). 
     The one or more control signals can comprise analog electrical signals received at the electrical drive from the controller ( 16 ). 
     The electrical drive ( 940   d ,  941   d ,  942   d ) typically comprises one or the other or both of a digital signal receiving ( 16   r ) and transmitting ( 16   s ) device, wherein: the digital signal receiving and transmitting device is adapted to receive ( 16   r ) and transmit ( 16   s ) digital signals between the electrical drive ( 940   d ,  941   d ,  942   d ) and the controller ( 16 ) of the injection molding apparatus ( 10 ); and wherein, the digital signals include the one or more control signals, where the one or more control signals are digital control signals received from the controller. 
     The digital control signals can include one or more of differential position commands, differential current commands, and differential velocity commands. 
     The digital signal receiving and transmitting device ( 16   r ,  16   s ) can be adapted to receive digital signals from the actuator, wherein the digital signals received from the actuator include one or more feedback signals corresponding to operation of one or more of the actuator and the actuator rotor. 
     The pulse width modulator (PWM) can convert the electrical energy or power received from the interface into sinusoidal waveforms adapted to drive the corresponding phase-coils of the actuator driver based at least in part on the one or more feedback signals. 
     The one or more feedback signals received from the actuator typically include one or more of an incremental feedback signal and an absolute feedback signal. 
     The apparatus can include a passive cooler ( 10 ,  14 ,  100 ,  502 ,  507 ,  2000 ,  2002 ) having a first thermally conductive surface ( 502   b ,  103 ,  104   i ,  2000   is ,  2002   us ) engaged with a housing surface ( 121   s ,  41 ,  43 ,  140 ,  9401   s ) of the actuator housing ( 43 ,  45 ,  940   h ,  941   h ,  942   h ) and a second thermally conductive surface ( 11 ,  130 ,  502   a ,  2000   ms ) engaged with a plate surface ( 21 ,  80   a ,  80   ms ,  140 ) of a cool or cooled clamp plate ( 80 ,  507 ) in an arrangement such that heat is conducted from the actuator housing to the cool or cooled clamp plate. 
     The passive cooler is typically comprised of a selected highly heat conductive material. 
     The apparatus can further comprise a signal converter ( 1500 ) for converting signals generated by an injection molding apparatus ( 10 ) that is comprised of an injection molding machine (IMM) having a drivably rotatable barrel screw (BS) that generates an injection fluid ( 18 ), a heated manifold ( 40 ) that receives an injection fluid ( 18 ) from the injection molding machine (IMM) and distributes the injection fluid ( 18 ) to one or more gates ( 32 ,  34 ,  36 ), a mold ( 42 ) having a cavity ( 30 ) communicating with the gates to receive the injection fluid ( 18 ), wherein the injection molding machine (IMM) includes a machine controller (MC) or a control unit (HPU) that generates one or more directional control valve compatible signals (VPS), wherein the direction control valve compatible signals (VPS) are compatible for use by a signal receptor, interface or driver of a standard fluid directional control valve ( 12 ) to instruct the fluid directional control valve ( 12 ) to move to a position that routes a source of drive fluid to flow in a direction that drives an interconnected fluid drivable actuator ( 940   f ,  941   f ,  942   f ) to move in a direction that operates to begin an injection cycle and to move in a direction that operates to end an injection cycle, wherein the signal converter ( 1500 ) is interconnected to the machine controller (MC) or control unit (HPU), the signal converter ( 1500 ) receiving and converting the directional control valve compatible signals (VPS) to a command signal (MOPCS, PDCVS) that is compatible with a signal receptor or interface of an electrically powered actuator ( 940   e ,  941   e ,  942   e ) or a signal receptor or interface of a proportional directional control valve (V, V 1 , V 2 ) that drives a fluid driven actuator ( 940   p ,  941   p ,  942   p ), 
     wherein the signal converter ( 1500 ) includes a processor that converts the command signals (MOPCS, PDCVS) into a form, frequency, power or format that is usable by the signal receptor or interface of the electrically powered actuator ( 940   e ,  941   e ,  942   e ) or by the signal receptor or interface of the proportional directional control valve (V, V 1 , V 2 ) to respectively cause the electrically powered actuator ( 940   e ,  941   e ,  942   e ) or the proportional directional control valve (V, V 1 , V 2 ) to be driven in a direction that operates to either begin an injection cycle or to end an injection cycle. 
     The directional control valve compatible signals (VPS) can comprise a voltage signal of predetermined voltage or magnitude indicative of a predetermined rotational position of the barrel screw (BS) of the injection molding machine (IMM) that generates pressurized injection fluid ( 18 ) within the apparatus. 
     The apparatus ( 10 ) can further comprise one or more sensors ( 950 ,  951 ,  952 , SN, SC, SPSR, BPSR) that detect and generate one or more sensor signals indicative of one or more of rotational or linear position of an actuator ( 940   e ,  941   e ,  942   e ,  940   p ,  941   p ,  942   p ) or its associated valve pin ( 1040 ,  1041 ,  1042 ), pressure or temperature of the injection fluid ( 18 ) within a fluid channel ( 19 ) of the manifold ( 40 ) or within a nozzle channel ( 42 ,  44 ,  46 ) or within the cavity ( 30 ) of the mold ( 33 ) or within a barrel of the injection molding machine (IMM), the apparatus ( 10 ) including an actuator controller ( 16 ) that receives and uses the one or more sensor signals in a program that: 
     instructs the actuator ( 940   e ,  941   e ,  942   e ,  940   p ,  941   p ,  942   p ) or its associated valve pin ( 1040 ,  1041 ,  1042 ) to travel during the course of the injection cycle to positions that correspond to a predetermined profile of injection fluid pressures, linear or rotational pin positions, linear actuator or valve pin positions, barrel screw positions, barrel pressures or actuator drive fluid pressures or that, 
     instructs the actuator ( 940   e ,  941   e ,  942   e ,  940   p ,  941   p ,  942   p ) or its associated valve pin ( 1040 ,  1041 ,  1042 ) such that the valve pin is withdrawn from a closed gate position upstream at a reduced velocity over a selected path of upstream travel, or that, 
     instructs the actuator ( 940   e ,  941   e ,  942   e ,  940   p ,  941   p ,  942   p ) or its associated valve pin ( 1040 ,  1041 ,  1042 ) to travel such that the valve pin is driven downstream at a reduced velocity over a selected path of travel where a distal tip end of the pin travel from upstream of the gate to a gate closed position, or that, 
     instructs the actuator ( 940   e ,  941   e ,  942   e ,  940   p ,  941   p ,  942   p ) or its associated valve pin ( 1040 ,  1041 ,  1042 ) to travel such that the valve pin is driven upstream or downstream to an intermediate position between a gate closed position and a fully upstream position where the valve pin is maintained in the intermediate position for a selected period of time during the course of the injection cycle wherein, in the intermediate position, the distal tip end of the valve pin restricts flow of injection of the injection to less than a maximum flow. 
     In another aspect of the invention there is provided a method of performing an injection molding cycle comprising operating the apparatuses described above. 
     In another aspect of the invention there is provided an injection molding apparatus ( 10 ) comprising an injection molding machine ( 13 ) that injects a flow of injection fluid ( 18 ) to a heated manifold ( 40 ) that distributes the injection fluid ( 18 ) to a flow channel that delivers the injection fluid to a gate ( 32 ,  34 ,  36 ) of a mold cavity ( 30 ), the injection molding apparatus ( 10 ) comprising: 
     an actuator ( 940 ,  941 ,  942 ) comprised of a rotor ( 940   r ,  941   r ,  942   r ) having a drive axis (Y) and a driver ( 940   dr ,  941   dr ,  942   dr ) interconnected to the rotor ( 940   r ,  941   r ,  942   r ) adapted to controllably drive the rotor rotatably around the drive axis Y, the driver ( 940   dr ,  941   dr ,  942   dr ) receiving electrical energy or power from an electrical drive ( 940   d ,  941   d ,  942   d ), 
     the electrical drive ( 940   d ,  941   d ,  942   d ) comprising a pulse-width modulator (PWM) that converts received electrical energy or power into sinusoidal voltage waveforms, each sinusoidal voltage waveform being adapted to drive a corresponding phase-coil of the actuator driver ( 940   dr ,  941   dr ,  942   dr ), the actuator having a housing ( 940   h ,  941   h ,  942   h ) that houses the rotor ( 940   r ,  941   r ,  942   r ) and the driver ( 940   dr ,  941   dr ,  942   dr ), the housing being adapted to support the rotor ( 940   r ,  941   r ,  942   r ), 
     the electrical drive ( 940   d ,  941   d ,  942   d ) being housed within or by the housing ( 940   h ,  941   h ,  942   h ) or being mounted on or to the housing ( 940   h ,  941   h ,  942   h ), 
     the housing ( 940   h ,  941   h ,  942   h ) and the electrical drive ( 940   d ,  941   d ,  942   d ) being mounted on, to or in close proximity to the heated manifold ( 40 ), 
     the apparatus including a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) disposed between the heated manifold ( 40 ) and the housing ( 940   h ,  941   h ,  942   h ), 
     the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from communication with heat emanating from the heated manifold ( 40 ) or to heat sink or absorb heat communicated or communicable to the electrical drive ( 940   d ,  941   d ,  942   d ) from the heated manifold ( 40 ) or both. 
     In another aspect of the invention there is provided a method of performing an injection molding cycle comprising operating the apparatus described above. 
     In another aspect of the invention there is provided an injection molding apparatus ( 10 ) comprising an injection molding machine ( 13 ) that injects a flow of injection fluid ( 18 ) to a heated manifold ( 40 ) that distributes the injection fluid ( 18 ) to a flow channel that delivers the injection fluid to a gate ( 32 ,  34 ,  36 ) of a mold cavity ( 30 ), the injection molding apparatus ( 10 ) comprising: 
     an actuator ( 940 ,  941 ,  942 ) comprised of a rotor ( 940   r ,  941   r ,  942   r ) having a drive axis (Y) and a driver ( 940   dr ,  941   dr ,  942   dr ) interconnected to the rotor ( 940   r ,  941   r ,  942   r ) adapted to controllably drive the rotor rotatably around the drive axis Y, the driver ( 940   dr ,  941   dr ,  942   dr ) receiving electrical energy or power from an electrical drive ( 940   d ,  941   d ,  942   d ), the electrical drive ( 940   d ,  941   d ,  942   d ) comprising an interface that receives and controllably distributes electrical energy or power in controllably varied amounts during the course of an injection cycle to the driver ( 940   dr ,  941   dr ,  942   dr ), 
     the actuator having a housing ( 940   h ,  941   h ,  942   h ) that houses the rotor ( 940   r ,  941   r ,  942   r ) and the driver ( 940   dr ,  941   dr ,  942   dr ), the housing being adapted to support the rotor ( 940   r ,  941   r ,  942   r ), 
     the apparatus including a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) mounted on or to the heated manifold ( 40 ), 
     the electrical drive ( 940   d ,  941   d ,  942   d ) being mounted on or to the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) in close proximity to the heated manifold ( 40 ) in an arrangement such that at least the electrical drive ( 940   d ,  941   d ,  942   d ) is isolated or insulated from substantial communication with heat emanating or emitted from the heated manifold ( 40 ) or such that the cooling device acts as a heat sink or absorbs heat communicated or communicable to the electrical drive ( 940   d ,  941   d ,  942   d ) from the heated manifold ( 40 ) or both. 
     In such an embodiment, the electrical drive ( 940   d ,  941   d ,  942   d ) is typically housed within or by the housing ( 940   h ,  941   h ,  942   h ) or is physically mounted on or to the housing ( 940   h ,  941   h ,  942   h ) in thermally conductive communication or contact therewith and the housing is mounted on or to the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     In such an embodiment the housing ( 940   h ,  941   h ,  942   h ) is typically mounted in direct heat communicative contact with the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). 
     Such an embodiment can further comprise a controller ( 16 ) mounted or disposed in a location remote from the electric drive ( 940   d ,  941   d ,  942   d ) and the heated manifold ( 40 ), the electric drive and the controller ( 16 ) being interconnected and adapted to exchange signals that control operation of the actuator ( 940 ,  941 ,  942 ). 
     In another aspect of the inventionve there is provided a method of performing an injection molding cycle comprising operating an apparatus as described immediately above. 
     In another aspect of the invention there is provided an injection molding apparatus ( 10 ) comprising an injection molding machine ( 13 ) that injects a flow of injection fluid ( 18 ) to a heated manifold ( 40 ) that distributes the injection fluid ( 18 ) to a flow channel that delivers the injection fluid to a gate ( 32 ,  34 ,  36 ) of a mold cavity ( 30 ), the injection molding apparatus ( 10 ) comprising: 
     an actuator ( 940 ,  941 ,  942 ) comprised of a rotor ( 940   r ,  941   r ,  942   r ) having a drive axis (Y) and a driver ( 940   dr ,  941   dr ,  942   dr ) interconnected to the rotor ( 940   r ,  941   r ,  942   r ) adapted to controllably drive the rotor rotatably around the drive axis Y, the driver ( 940   dr ,  941   dr ,  942   dr ) receiving electrical energy or power from an electrical drive ( 940   d ,  941   d ,  942   d ), 
     the electrical drive ( 940   d ,  941   d ,  942   d ) comprising an interface that receives and controllably distributes electrical energy or power in controllably varied amounts during the course of an injection cycle to the driver ( 940   dr ,  941   dr ,  942   dr ), 
     the actuator having a housing ( 940   h ,  941   h ,  942   h ) that houses the rotor ( 940   r ,  941   r ,  942   r ) and the driver ( 940   dr ,  941   dr ,  942   dr ), the housing being adapted to support the rotor ( 940   r ,  941   r ,  942   r ), 
     the electrical drive ( 940   d ,  941   d ,  942   d ) being housed within or by the housing ( 940   h ,  941   h ,  942   h ) or being mounted on or to the housing ( 940   h ,  941   h ,  942   h ), 
     the housing ( 940   h ,  941   h ,  942   h ) and the electrical drive ( 940   d ,  941   d ,  942   d ) being mounted or disposed in a location spaced or remote from the heated manifold ( 40 ) that substantially isolates or insulates at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
     In another aspect of the invention there is provided a method of performing an injection molding cycle comprising operating the apparatus described above. 
     In each of the apparatuses described herein, the apparatus preferably further comprises a controller ( 16 ) mounted or disposed in a location remote from the electric drive ( 940   d ,  941   d ,  942   d ) and the heated manifold ( 40 ), the electric drive and the controller ( 16 ) being interconnected and adapted to exchange signals that control operation of the actuator ( 940 ,  941 ,  942 ). 
     In each of the embodiments described herein where a gap (G, G′) is formed via use of a mount ( 60 ), the gap (G, G′) typically serves as a heat insulator or heat insulative gap (G, G′) where air that is disposed in the gap (G, G′) separating the surface of the mount from heat conductive contact with a surface of the manifold ( 40 ) or cooling device ( 940   mc ) is non heat conductive relative to metal materials and thus the air typically functions as a heat insulator. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The accompanying drawings contain numbering of components and devices that correspond to the numbering appearing in the following Summary. 
         FIG. 1  is a side schematic view of an injection molding apparatus having a center valve with associated actuator ( 940 ) and two downstream valves with associated actuators ( 941 ,  942 ) that are opened to a mold cavity in a predetermined sequence after the center valve is first opened, the actuators ( 940 ,  941 ,  942 ) each comprising an electric motor having an electric drive ( 940   d ,  941   d ,  942   d ) that is incorporated into or physically onto the housing ( 940   h ,  941   h ,  942   h ) of the actuator such that the electric drive ( 940   d ,  941   d ,  942   d ) is in direct thermal communication with the housing ( 940   h ,  941   h ,  942   h ) of the actuator, the housings of each of the actuators ( 940 ,  941 ,  942 ) being mounted on or to or in close physical proximity to a heated manifold with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the housing ( 940   h ,  941   h ,  942   h ) that is adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
         FIG. 1A  is a side schematic view of an electric actuator ( 941 ) comprised of a housing ( 941   h ) and an electric drive ( 941   d ) that is readily attachable to and detachable from the housing ( 941   h ) of the actuator via a conventional attachment and detachment mechanism such as bolts ( 941   b ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
         FIG. 1B  is a view similar to  FIG. 1A  showing the actuator housing ( 941   h ) and electric drive being mounted in a spaced relationship on or to the cooling device via mounts ( 60 ) that are typically comprised of a heat insulative material such as titanium, bismuth, stainless steel. lead, chromium or the like. 
         FIG. 2  is a side sectional schematic view of an electric actuator in a apparatus similar to the  FIG. 1  apparatus where the actuator ( 940 ) has a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) and the electric drive ( 940   d ) being mounted on, to or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator housing ( 940   h ) to a rotary to linear travel converter ( 9401 ,  940   h ) which is in turn mounted on, to or in close physical proximity to a heated manifold with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the linear travel converter ( 9401 ,  940   h ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ,  941   d ,  942   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
         FIG. 2A  is a top front perspective view of an embodiment of comprised of an electric actuator ( 940 ) having a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) and the electric drive ( 940   d ) being mounted to or on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a rotational speed reducing device ( 46 ) that is in turn mounted to a rotary to linear travel converter ( 9401 ,  940   h ) which is in turn mounted on or to or in close physical proximity to a heated manifold ( 40 ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the linear travel converter ( 9401 ,  940   h ), the rotational speed reducing device ( 46 ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ) the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
         FIG. 2B  is a side sectional view of the  FIG. 2A  apparatus taken along lines  2 B- 2 B. 
         FIG. 2BB  is a closeup sectional view of the standoffs or mounts by which the rotary to linear converter  15  and its housing  9401   h  (together with the speed reducing device  46  and actuator  940  to which the converter  15 ) is subassembled) is mounted to the heated manifold ( 40 ). 
         FIG. 2C  is a top front partial sectional perspective view of the  FIGS. 2B, 2BB  subassembly. 
         FIG. 2D  is a side sectional view of the subassembled rotational speed reducing device  46 , a harmonic, and rotary to linear converter device  9401  components of the subassembly shown in  FIGS. 2A, 2B, 2BB, 2C . 
         FIG. 2E  is a top rear exploded perspective view of the rotational speed reducing device  46  shown in  FIGS. 2A, 2B, 2BB, 2C, 2D . 
         FIG. 2F  is a top front perspective view of another embodiment comprised of an actuator having a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a rotary to linear travel converter ( 9401 ,  9401   h ) which is in turn mounted on, to or in close physical proximity to a heated manifold ( 40 ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the linear travel converter ( 9401 ,  940   h ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
         FIG. 2G  is a sectional view of the apparatus of  FIG. 2F  along lines  2 G- 2 G. 
         FIG. 2H  is a top front perspective view of another embodiment comprised of an actuator having a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a linear travel converter ( 9401 ,  940   h ) which is in turn mounted on or to or in close physical proximity to a heated manifold ( 40 ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the linear travel converter ( 9401 ,  940   h ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ) the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
         FIG. 2I  is a sectional view of the  FIG. 2H  apparatus taken along lines  21 - 21 . 
         FIG. 3A  is a side sectional schematic view of an electric actuator in an apparatus similar to the  FIG. 1  apparatus where the actuator ( 940 ) has a drive axis Y that is coaxial with the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to or on or in close physical proximity to the heated manifold ( 40 ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ) the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
         FIG. 3B  is a side sectional schematic view of an electric actuator in a apparatus similar to the  FIG. 1  apparatus where the actuator ( 940 ) has a drive axis Y that is coaxial with the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to or on or in direct thermal communication with the heated manifold ( 40 ) via mounts ( 940   s ) mounted on or to or in direct thermal communication or contact with the heated manifold ( 40 ). 
         FIG. 4  is a side sectional schematic view of another electric actuator in a apparatus similar to the  FIGS. 1, 2  apparatus where the actuator ( 940 ) has a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted in one iteration ( 940 ) both to a top clamp plate ( 80 ) and to or on or in direct thermal communication with the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a linear travel converter ( 9401 ,  940   h ) which is in turn mounted on or to or in direct thermal communication or contact with the heated manifold ( 40 ). In another iteration ( 940   a ) the housing of the actuator may or may not be mounted also to the top clamp plate  80 . 
         FIG. 4A  is an alternative embodiment where a rotary to linear travel converter  120  is interconnected to an actuator for converting rotary motion to linear motion along a non coaxial axial axis relative to the axis of the rotor, and where a cooling channel  125  is disposed within a housing body  120   ro  that is readily attachable to and detachable from a main linear converter housing body  120   ri.    
         FIG. 5  is a side sectional schematic view of another electric actuator in a apparatus similar to the  FIGS. 1, 2  apparatus where the actuator ( 940 ) has a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to or on or in direct thermal communication with the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a linear travel converter ( 9401 ,  940   h ) which is in turn mounted on or to a top clamping plate ( 80 ), the linear travel converter being disposed in direct thermal communication with the heated manifold ( 40 ). 
         FIG. 6  is a top rear left perspective view of an injection molding system similar to the  FIG. 1  system showing a specific configuration of a distal end housing cooling component with a specific configuration of actively cooled channels incorporated into the body of the component. 
         FIG. 6A  is a sectional end view of the  FIG. 6  system along lines  6 A- 6 A showing details of the distal end cooling housing component or drive mount  940   ds.    
         FIG. 6B  is a side sectional view of the  FIG. 6  injection molding system showing details of the rotor and driver, stator and armature, components and the manner in which they are mounted within the actuator housing. 
         FIG. 7  is a top left rear perspective view of an injection molding system with the housing cooling component disposed and extending along a bottom radial wall of the housing with actively cooled cooling channels disposed within the radial wall. 
         FIG. 7A  is a side sectional view of the  FIG. 7  system along lines  7 A- 7 A of  FIG. 7 . 
         FIG. 8  is a top left rear perspective view of an injection molding system with the housing cooling components disposed and extending along a pair of opposing side radial walls of the actuator housing with actively cooled cooling channels disposed within the side radial walls. 
         FIG. 8A  is a sectional view along lines  8 A- 8 A of  FIG. 8 . 
         FIG. 9  is a top rear perspective view of an injection molding system having an actuator housing wall comprised of a top radial plate member that is not actively cooled and a unitary housing member comprised of axial and side radial walls that are actively cooled. 
         FIG. 10  is an end view of the  FIG. 9  apparatus. 
         FIG. 11  is an exploded perspective view of the  FIG. 9  system. 
         FIG. 12  is a front right perspective view of an injection molding system showing an electric motor actuator mounted to a linear to linear converter  15  having a converter housing  120  having opposing left and right radial side walls that contain actively cooled cooling channels, the side walls being assemblable together with top and bottom axial wall plates that are not actively cooled. 
         FIG. 12A  is a sectional view taken along lines  12 A of  FIG. 12   
         FIG. 12B  is a top rear partially sectional perspective view of another electric actuator in an apparatus similar to the  FIGS. 1, 2  apparatus where the actuator ( 940 ) has a drive axis Y that is arranged non-coaxially relative to the travel axis X of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a linear travel converter ( 9401 ,  940   h ) which is in turn mounted on or to or in close physical proximity to a heated manifold ( 40 ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the linear travel converter ( 9401 ,  940   h ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
         FIG. 12C  is a sectional view taken along lines  12 C- 12 C of  FIG. 12B . 
         FIG. 12D  is a sectional view taken along lines  8 - 8  of  FIG. 12B . 
         FIG. 12E  is a side sectional view of another embodiment having an actuator with the motor rotor  940   r ,  940   dr  coaxial with the valve pin axis X, the actuator being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) with the cooling device being disposed between the heated manifold ( 40 ) and the the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ), the actuator being further mounted in a passive cooling engagement and arrangement with the top clamp plate  20  via a highly heat conductive plate  10  having wings  14  with engagement surfaces  11  for engaging the top clamp plate which itself is cool relative to the manifold  40 . 
         FIG. 12F  is a closeup perspective view of the passive cooling device and cooling device  940   mc  shown in  FIG. 12E . 
         FIG. 12G  is a side sectional view of another embodiment having an actuator with the motor rotor  940   r ,  940   dr  coaxial with the valve pin axis X, the actuator housing being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) with the cooling device being disposed between the heated manifold ( 40 ) and the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ), the actuator being further mounted in a passive cooling engagement and arrangement with the top clamp plate  20  via a highly heat conductive flanged metal plate or device  100  having side and end engagement surfaces  104   i ,  130  for engaging a surface  43  of the actuator housing and also engaging a surface  140  of the top clamp plate  20  which itself is cool relative to the manifold  40 . 
         FIG. 12H  is a front perspective view of the assembly shown in  FIG. 12G . 
         FIG. 13A  is a side partial sectional view of another embodiment having an actuator  10  with the motor rotor  940   r ,  940   dr  coaxial with the valve pin axis X, the actuator housing being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) with the cooling device being disposed between the heated manifold ( 40 ) and the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ), the actuator being further mounted in a passive cooling engagement and arrangement with the top clamp plate  20  via a highly heat conductive metal device  502  having an engagement surface  502   b  for engagement with an outside surface  121   s  of the actuator  12  and another surface  502   a  for engagement with a surface  80   a  of the cool top clamp plate  80 . The actuator of this embodiment is further mounted in a spaced relationship to the cooling device via mounts  60  comprised of a heat insulative material such as titanium, bismuth, stainless steel, lead, chromium or the like. 
         FIG. 13B  is a view of an apparatus similar to  FIG. 13A  where the actuator  12  is mounted directly on or to the cooling device without being spaced as in the  FIG. 13A  embodiment. 
         FIG. 14A  is a top front perspective view of another embodiment having an actuator with the motor rotor  940   r ,  940   dr  coaxial with the valve pin axis X, the actuator housing being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) with the cooling device being disposed between the heated manifold ( 40 ) and the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ), the actuator being further mounted in a passive cooling engagement and arrangement with the top clamp plate  20  via metal device  500  having heat conductive members  502 ,  507  having an engagement surfaces  502   b ,  507   u  for heat conductive communication and engagement with an outside surface  121   s  of the actuator  12  and another surface  502   a ,  507   a  for engagement with a surface  80   a  of the cool top clamp plate  80 . The actuator of this embodiment is further mounted in a spaced relationship to the cooling device  940   mc  via mounts  60  comprised of a heat insulative material such as titanium, bismuth, stainless steel, lead, chromium or the like. 
         FIG. 14B  is a view of an apparatus or assembly similar to  FIG. 14A  where the actuator  12  is mounted directly on or to the cooling device without being spaced as in the  FIG. 13A  embodiment. 
       All of the embodiments shown in  FIGS. 12B to 14B  include a passive cooling device that, in addition to an active cooling channel  33 ,  25 ,  125  disposed in a mount  940   ds ,  940   mc  or the like, conducts heat or thermal energy from the actuator housing  940   h  to another heat conductive component of the system such as the top clamp plate  80  that is inherently cool or is actively cooled. Such a passive cooling devices as described herein include a heat conducting member such as a metal containing body  502   100 ,  2002  that is arranged when the system is assembled to make heat conductive contact with both the actuator housing  940   h  and the other heat conductive component such as top clamp plate  80  of the system such that heat is sinked or transmitted or conducted to the other heat conductive component  80  from the actuator housing  940   h . Such other heat conductive component  80  can be actively cooled via a cooling fluid that is routed in a flow through a channel  25  in the other heat conductive component. Alternatively such other heat conductive component can comprise a non actively cooled metal containing that is inherently cool relative to the manifold  40  when heated during the course of an injection cycle. 
         FIG. 15  is a side sectional schematic view of an injection molding system showing electric actuators with electric drive  940   d  mounted on or to the actuator housing, the actuators and electric drive  940   d  being mounted in an extended spaced apart relationship relative to the heated manifold such that the actuator and electric drive  940   d  are isolated or insulated from significant heat communication with the heated manifold  40 . In the embodiment shown the actuator and electric drive are mounted to a cool or cooled top clamp plate and are interconnected to a rotary to linear drive converter device, the linear drive converter device also being mounted to the top clamp plate. 
         FIG. 16  is a side sectional schematic view of another embodiment of an injection molding system having electric actuators with electric drive  940   d  mounted on or to the actuator housing, the actuators and electric drive  940   d  being mounted in an extended spaced apart relationship relative to the heated manifold such that the actuator and electric drive  940   d  are isolated or insulated from substantial or significant heat communication with the heated manifold  40 . In the embodiment shown the actuator and electric drive are mounted to a cool or cooled top clamp plate  140  and are interconnected to a rotary to linear drive converter device, the linear drive converter device also being mounted to the top clamp plate. 
         FIG. 17  is a side schematic view of a prior art injection molding apparatus in which an injection molding machine (IMM) includes a stock or standard IMM controller or signal generator that sends a standard IMM controller signal to the solenoid of a directional flow control valve that directs the position of the valve to move between a valve gate closed and valve gate open position. 
         FIG. 18  is a side schematic view of one embodiment of an injection molding apparatus according to the invention where the valve gates include an electrically powered or electric motor containing actuator, the apparatus including a machine signal converter that receives a standard signal generated by an injection machine controller converts the signal to a control signal compatible with the signal receptor of the electrically powered actuators used in the apparatus, the converter routing the converted signal to the actuator processor. 
         FIG. 19  is a generic schematic diagram of an arrangement of signal communications between an injection molding machine controller, sensors, a signal converter and electric actuators or the interface of a proportional directional control valve. 
         FIG. 20  is a schematic diagram of an arrangement of signal communications between an injection molding machine controller, position sensors, a signal converter and electric actuators. 
         FIGS. 21A-21  E are schematic cross-sectional close-up views of the center and one of the lateral gates  34  of the  FIG. 1  apparatus showing various stages of the progress of sequential injection; 
         FIGS. 22A-22B  show tapered end valve pin positions at various times and positions between a starting closed position as in  FIG. 22A  and various upstream opened positions, RP representing a selectable path length over which the velocity of withdrawal of the pin upstream from the gate closed position to an open position is reduced relative to the velocity of upstream movement that the valve pin would normally have over the uncontrolled velocity path FOV when pin velocity is at its maximum; 
         FIGS. 21A-21E  show an apparatus having a valve pin that has a cylindrically configured tip end, the tips ends of the pins being positioned at various times and positions between a starting closed position as in  FIG. 23A  and various upstream opened positions, RP wherein RP represents a path of selectable length over which the velocity of withdrawal of the pin upstream from the gate closed position to an open position is reduced relative to the velocity of upstream movement that the valve pin would normally have over the uncontrolled velocity path FOV when the pin velocity is at its maximum. 
         FIGS. 22A-22B  show tapered tip end valve pin positions at various times and positions between a starting closed position as in  FIG. 22A  and various upstream opened positions as in  FIG. 22B . 
         FIGS. 23A-23B  show valve pins with cylindrically configured tip ends at axial positions at various times and positions between a starting closed position as in  FIG. 23A  and various upstream opened positions as in  FIG. 23B . 
         FIG. 24  is a schematic side sectional view of the armature and drive rod components of a linear drive proportional solenoid that can be substituted for the assembly of rotary motion enabling components of the rotary electric actuators described herein to enable direct linear actuation movement of the drive rod by the armature when energized with electricity. 
         FIG. 25  is a schematic side sectional view of the armature and drive rod components of a linear motor that can be substituted for the assembly of rotary motion enabling components of the rotary electric actuators described herein to enable direct linear actuation movement of the drive rod by the armature when energized with electricity. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The embodiments of  FIGS. 1A through 14  utilize an electric actuator housing ( 940   h ,  941   h ,  941   h ) that is mounted on or to a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) that comprises an actively cooled device comprised of a body of highly heat conductive material such as steel, copper or the like. The highly heat conductive body of the cooling device typically contains fluid flow channels ( 33 ) through which a cool or cooled fluid such as water, oil, air, brine ( 260 ) is routed or pumped to proactively cool the thermally conductive body of the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ). The cooling device can be alternatively actively cooled by routing or applying a cool or cooled substance (such as air, gas or liquid) over the exterior surface of the cooling mechanism. The cooling device can also comprise a thermoelectric cooler or solid-state Peltier effect device that is typically comprised of an array of alternating n- and p-type semiconductor plates that with application of electric current exploit the Peltier effect. Solid solutions of bismuth telluride, antimony telluride, and bismuth selenide are preferred materials for Peltier effect devices because they provide the best performance from 180 to 400 K and can be made both n-type and p-type. 
     In an alternative embodiments such as disclosed in  FIGS. 15, 16 , the electric drive ( 940 ,  941   d ,  942   d ) can be insulated or isolated from substantial communication of heat generated by or emanating from the heated manifold ( 40 ) by disposing or mounting the electric drive together with the electric actuator ( 940 ,  941 ,  942 ) on which the electric drive is mounted or housed in location that is spaced apart or remote from the heated manifold ( 40 ) such that heat generated by the heated manifold ( 40 ) cannot substantially transmit to the electric drive ( 940   d ,  941   d ,  942   d ). 
     As shown in  FIG. 1  a typical injection molding apparatus has a center valve with an associated actuator ( 940 ) and two downstream valves with associated actuators ( 941 ,  942 ) that are opened to a mold cavity  30  in a predetermined sequence as described herein after the center valve is first opened, the actuators ( 940 ,  941 ,  942 ) each comprising an electric motor having an electric drive ( 940   d ,  941   d ,  942   d ). 
       FIG. 1  shows an injection molding apparatus having a center valve with associated actuator ( 940 ) and two downstream valves with associated actuators ( 941 ,  942 ) that are opened to a mold cavity  30  in a predetermined sequence as described herein after the center valve is first opened, the actuators ( 940 ,  941 ,  942 ) each comprising an electric motor having an electric drive ( 940   d ,  941   d ,  942   d ). The electric drive ( 940   d ,  941   d ,  942   d ) can be housed within the same housing ( 940   h ,  941   h ,  942   h ) as the driver components of the electric actuator ( 940 ,  941 ,  941 ), or the electric drive ( 940   d ,  941   d ,  942   d ) can be housed within a physically separate thermally conductive housing ( 941   ds ) such as shown in  FIG. 1A  that is readily attachable to and detachable from the housing ( 941   h ) that houses the driver components (stator, armature) and rotor component of the electric actuator via conventional device such as bolts, screws, clamps, magnets or the like ( 941   b ). As shown in  FIG. 1A , the thermally conductive housing ( 941   ds ) is disposed in substantial thermally conductive communication or contact with the heated manifold ( 40 ) via the thermally conductive mounting of the thermally conductive housing ( 941   ds ) to the actuator housing ( 940   h ) which is in turn mounted via mount device ( 940   mm ) in substantial heat or thermally conductive communication or contact with the heated manifold ( 40 ). 
     As shown in  FIG. 1 , the housing of the actuators ( 940   h ,  941   h ,  942   h ) can be provided with cooling channels  25  embedded within the body  940   h ,  941   h  of the housing similar to the embodiment of  FIGS. 8, 8A  or as described herein, a readily detachable and attachable housing body component such as component  20   ao  containing active cooling channels  25  as described herein can be attached to the housing body  940   h ,  941   h ,  942   h . Such active cooling channels are typically interconnected to a source  260  of cooling fluid  25   f  that is pumped through the channels  25  thus cooling the actuator housing  940   h ,  941   h ,  942   h  and its associated mounted or embedded components including the electric drive  940   d ,  941   d ,  942   d  and the drivers  100 ,  200 . 
     As shown in  FIG. 1A  active cooling channels  25  can alternatively be provided or disposed within the body of a drive mount  940   ds ,  941   ds ,  942   ds  that houses an electric drive  940   d ,  941   d ,  942   d . Such a drive mount can be readily attachable to and detachable from the housing  940   h ,  941   h ,  942   h  of the actuator housing  940   h ,  941   h ,  942   h . Such active cooling channels  25  are typically interconnected to a source  260  of cooling fluid  25   f  that is pumped through the channels  25  thus cooling the actuator housing  940   h ,  941   h ,  942   h  and its associated mounted or embedded components including the electric drive  940   d ,  941   d ,  942   d  and the drivers  100 ,  200 . 
     Similarly where a rotary to linear travel converter  15  with linear drive member  9401 ,  FIGS. 4, 12  is interconnected to an actuator housing  20 ,  940 , the housing  9401   h ,  120   ro  of the linear travel converter can contain cooling channels  25  that are interconnected to a source  260  of cooling fluid  25   f  that is pumped through the channels  25  thus cooling the actuator housing  940   h ,  941   h ,  942   h  and its associated mounted or embedded components including the electric drive  940   d ,  941   d ,  942   d  and the drivers  100 ,  200 . 
     In an alternative embodiment as shown in  FIG. 4A , the cooling channels  125  can be disposed within a housing component  120   ro  that is readily attachable to and detachable from the main linear travel converter housing  9401   h ,  120   ri . In such an embodiment cooling fluid  125   f  can be pumped through the channels  125  thus cooling the rotary to linear converter housing  120   ro ,  120   ri  and the actuator housing  940   h ,  941   h ,  942   h  and its associated mounted or embedded components including the electric drive  940   d ,  941   d ,  942   d  and the drivers  100 ,  200 . 
     As shown in all of the embodiments of  FIGS. 1, 1A, 2, 3, 4, 5  the electric drive ( 940   d ,  941   d ,  942   d ) is mounted on or to the actuator housing ( 940   h ,  941   h ,  942   h ) in some manner such that the drive components such as a Pulse Width Modulator (PWM) and associated electrical components are disposed in substantial heat communication or contact with the actuator housing ( 940   h ,  941   h ,  942   h ) or the heated manifold ( 40 ). 
     As shown in  FIGS. 1, 21A-21E  the injection cycle can be a cascade process where injection is effected in a sequence from the center nozzle  22  first and at a later predetermined time from the lateral nozzles  20 ,  24 . As shown in  FIG. 21A  the injection cycle is started by first opening the pin  1040  of the center nozzle  22  and allowing the fluid material  100  (typically polymer or plastic material) to flow up to a position  100   a  in the cavity just before  100   b  the distally disposed entrance into the cavity  34 ,  36  of the gates of the lateral nozzles  24 ,  20  as shown in  FIG. 1 . After an injection cycle is begun, the gate of the center injection nozzle  22  and pin  1040  is typically left open only for so long as to allow the fluid material  100   b  to travel to a position  100   p  just past the positions  34 ,  36 . Once the fluid material has travelled just past  100   p  of the lateral gate positions  34 ,  36 , the center gate  32  of the center nozzle  22  is typically closed by pin  1040  as shown in  FIGS. 21B, 21C, 21D and 21E . The lateral gates  34 ,  36  are then opened by upstream withdrawal of lateral nozzle pins  1041 ,  1042  as shown in  FIGS. 21B-21E . As described below, the rate of upstream withdrawal or travel velocity of lateral pins  1041 ,  1042  can be controlled as described below. 
     In alternative embodiments, the center gate  32  and associated actuator  940  and valve pin  1040  can remain open at, during and subsequent to the times that the lateral gates  34 ,  36  are opened such that fluid material flows into cavity  30  through both the center gate  32  and one or both of the lateral gates  34 ,  36  simultaneously. 
     When the lateral gates  34 ,  36  are opened and fluid material NM is allowed to first enter the mold cavity into the stream  102   p  that has been injected from center nozzle  22  past gates  34 ,  36 , the two streams NM and  102   p  mix with each other. If the velocity of the fluid material NM is too high, such as often occurs when the flow velocity of injection fluid material through gates  34 ,  36  is at maximum, a visible line or defect in the mixing of the two streams  102   p  and NM will appear in the final cooled molded product at the areas where gates  34 ,  36  inject into the mold cavity. By injecting NM at a reduced flow rate for a relatively short period of time at the beginning when the gate  34 ,  36  is first opened and following the time when NM first enters the flow stream  102   p , the appearance of a visible line or defect in the final molded product can be reduced or eliminated. 
     The rate or velocity of upstream withdrawal of pins  1041 ,  1042  starting from the closed position is controlled via controller  16  which controls the rate and direction of drive of the electric actuators  940 ,  941 ,  942 . 
     The user programs controller  16  via data inputs on a user interface to instruct the electric actuators to drive pins  1041 ,  1042  at an upstream velocity of travel that is reduced relative to a maximum velocity that the actuators can drive the pins  1041 ,  1042  to travel. Such reduced pin withdrawal rate or velocity is executed until a position sensor such as  951 ,  952  detects that an actuator  941 ,  952  or an associated valve pin (or another component), has reached a certain position such as the end point COP, COP 2 ,  FIGS. 22B, 23B  of a restricted flow path RP, RP 2 . A typical amount of time over which the pins are withdrawn at a reduced velocity is between about 0.01 and 0.10 second, the entire injection cycle time typically being between about 0.3 seconds and about 3 seconds, more typically between about 0.5 seconds and about 1.5 seconds. 
       FIG. 1  shows position sensors  950 ,  951 ,  952  for sensing the position of the motors  940 ,  941 ,  942  and their associated valve pins (such as  1040 ,  1041 ,  1042 ) and feed such position information to controller  16  for monitoring purposes. As shown, fluid material  18  is injected from an injection machine into a manifold runner  19  and further downstream into the bores  44 ,  46  of the lateral nozzles  24 ,  22  and ultimately downstream through the gates  32 ,  34 ,  36 . When the pins  1041 ,  1042  are withdrawn upstream to a position where the tip end of the pins  1041  are in a fully upstream open position such as shown in  FIG. 21D , the rate of flow of fluid material through the gates  34 ,  36  is at a maximum. However when the pins  1041 ,  1042  are initially withdrawn beginning from the closed gate position,  FIG. 21A , to intermediate upstream positions,  FIGS. 21B, 21C , a gap  1154 ,  1156  that restricts the velocity of fluid material flow is formed between the outer surfaces  1155  of the tip end of the pins  44 ,  46  and the inner surfaces  1254 ,  1256  of the gate areas of the nozzles  24 ,  20 . The restricted flow gap  1154 ,  1156  remains small enough to restrict and reduce the rate of flow of fluid material  1153  through gates  34 ,  36  to a rate that is less than maximum flow velocity over a travel distance RP of the tip end of the pins  1041 ,  1042  going from closed to upstream as shown in  FIGS. 1, 21B, 21C, 21E and 22B, 23B . 
     The pins  1041  can be controllably withdrawn at one or more reduced velocities (less than maximum) for one or more periods of time over the entirety of the length of the path RP over which flow of mold material  1153  is restricted. Preferably the pins are withdrawn at a reduced velocity over more than about 50% of RP and most preferably over more than about 75% of the length RP. As described below with reference to  FIGS. 22B, 23B , the pins  1041  can be withdrawn at a higher or maximum velocity at the end COP 2  of a less than complete restricted mold material flow path RP 2 . 
     The trace or visible lines that appear in the body of a part that is ultimately formed within the cavity of the mold on cooling above can be reduced or eliminated by reducing or controlling the velocity of the pin  1041 ,  1042  opening or upstream withdrawal from the gate closed position to a selected intermediate upstream gate open position that is preferably 75% or more of the length of RP. 
     RP can be about 1-8 mm in length and more typically about 2-6 mm, more typically 2-4 mm and even more typically 1-5 mm in length. According to the invention, the position of the electric actuators are adjusted in response to sensing of position of a suitable component such as the rotor of an actuator  941 ,  942  or associated valve pin to less than 100% open. Adjustment of the drive of an actuator  931 ,  942  thus reduces the velocity of upstream travel of the pins  1041 ,  1042  for the selected period of time. At the end of the travel or length of path RP, RP 2 , a position sensor signals the controller  16 , the controller  16  determines that the end COP, COP 2  has been reached and the valve pin is driven at higher velocity, typically to its end of stroke (EOS) or its 100% open position to allow the actuator pistons and the valve pins  1041 ,  1042  to be driven at maximum upstream velocity FOV in order to reduce the cycle time of the injection cycle. 
     Typically the user selects one or more reduced velocities that are less than about 90% of the maximum velocity (namely velocity when the valve  600  is fully open), more typically less than about 75% of the maximum velocity and even more typically less than about 50% of the maximum velocity at which the pins  1041 ,  1042  are drivable by the electric actuator apparatus. The actual maximum velocity at which the actuators  941 ,  942  and their associated pins  1041 ,  1042  are driven is predetermined by selection of the size and configuration of the actuators  941 ,  942 . The maximum drive rate of the electric actuator apparatus is predetermined by the manufacturer and the user of the apparatus and is typically selected according to the application, size and nature of the mold and the injection molded part to be fabricated. 
     Preferably, the valve pin and the gate are configured or adapted to cooperate with each other to restrict and vary the rate of flow of fluid material  1153 ,  FIGS. 22A-22B, 23A-23B  over the course of travel of the tip end of the valve pin through the restricted velocity path RP. Most typically as shown in  FIGS. 22A, 22B  the radial tip end surface  1155  of the end  1142  of pin  1041 ,  1042  is conical or tapered and the surface of the gate  1254  with which pin surface  1155  is intended to mate to close the gate  34  is complementary in conical or taper configuration. Alternatively as shown in  FIGS. 23A, 23B , the radial surface  1155  of the tip end  1142  of the pin  1041 ,  1042  can be cylindrical in configuration and the gate can have a complementary cylindrical surface  1254  with which the tip end surface  1155  mates to close the gate  34  when the pin  1041  is in the downstream gate closed position. In any embodiment, the outside radial surface  1155  of the tip end  1142  of the pin  1041  creates restricted a restricted flow channel  1154  over the length of travel of the tip end  1142  through and along restricted flow path RP that restricts or reduces the volume or rate of flow of fluid material  1153  relative to the rate of flow when the pin  1041 ,  1042  is at a full gate open position, namely when the tip end  1142  of the pin  1041  has travelled to or beyond the length of the restricted flow path RP. 
     In one embodiment, as the tip end  1142  of the pin  1041  continues to travel upstream from the gate closed GC position (as shown for example in  FIGS. 22A, 23A ) through the length of the RP path (namely the path travelled for the predetermined amount of time), the rate of material fluid flow  1153  through restriction gap  1154  through the gate  34  into the cavity  30  continues to increase from  0  at gate closed GC position to a maximum flow rate when the tip end  1142  of the pin reaches a position FOP (full open position), where the pin is no longer restricting flow of injection mold material through the gate. In such an embodiment, at the expiration of the predetermined amount of time when the pin tip  1142  reaches the FOP (full open) position the pin  1041  is immediately driven by at maximum velocity FOV (full open velocity). In alternative embodiments, when the predetermined time for driving the pin at reduced velocity has expired and the tip  1142  has reached the end of restricted flow path RP 2 , the tip  1142  may not necessarily be in a position where the fluid flow  1153  is not still being restricted. In such alternative embodiments, the fluid flow  1153  can still be restricted to less than maximum flow when the pin has reached the changeover position COP 2  where the pin  1041  is driven at a higher, typically maximum, upstream velocity FOV. 
     In the alternative examples shown in the  FIGS. 22B, 23B  examples, when the pin has travelled the predetermined path length at reduced velocity and the tip end  1142  has reached the changeover point COP, the tip end  1142  of the pin  1041  (and its radial surface  1155 ) no longer restricts the rate of flow of fluid material  1153  through the gap  1154  because the gap  1154  has increased to a size that no longer restricts fluid flow  1153  below the maximum flow rate of material  1153 . Thus in one of the examples shown in  FIG. 22B  the maximum fluid flow rate for injection material  1153  is reached at the upstream position COP of the tip end  1142 . In another example shown in  FIGS. 22B, 23B , the pin  1041  can be driven at a reduced velocity over a shorter path RP 2  that is less than the entire length of the restricted mold material flow path RP and switched over at the end COP 2  of the shorter restricted path RP 2  to a higher or maximum velocity FOV. In another alternative embodiment, the pin  1041  can be driven and instructed to be driven at reduced or less than maximum velocity over a longer path length RP 3  having an upstream portion UR where the flow of injection fluid mold material is not restricted but flows at a maximum rate through the gate  34  for the given injection molding apparatus. In this example the velocity or drive rate of the pin  1041  is not changed over until the tip end of the pin  1041  or actuator  941  has reached the changeover position COP 3 . As in other embodiments, a position sensor senses either that the valve pin  1041  or an associated component has travelled the path length RP 3  or reached the end COP 3  of the selected path length and the controller receives and processes such information and instructs the drive apparatus to drive the pin  1041  at a higher, typically maximum velocity upstream. In another alternative embodiment, the pin  1041  can be driven at reduced or less than maximum velocity throughout the entirety of the travel path of the pin during an injection cycle from the gate closed position GC up to the end-of-stroke EOS position, the controller  16  being programmed to instruct the drive system for the actuator to be driven at one or more reduced velocities for the time or path length of an entire closed GC to fully open EOS cycle. 
     Typically, when the time period for driving the pin  1041  at reduced velocity has expired and the pin tip  1142  has reached the position COP, COP 2 , the pins  1041 ,  1042  are driven at the maximum velocity or rate of travel that the actuator system is capable of driving the valve pins  1041 ,  1042 . Alternatively, the pins  1041 ,  1042  can be driven at a preselected FOV velocity that is less than the maximum velocity at which the pin is capable of being driven when the restriction valve  600  is fully open but is still greater than the selected reduced velocities that the pin is driven over the course of the RP, RP 2  path to the COP, COP 2  position. 
     At the expiration of the predetermined reduced velocity drive time, the pins  1041 ,  1042  are typically driven further upstream past the COP, COP 2  position to a maximum end-of-stroke EOS position. The end-of-stroke position EOS is an upstream position selected by the user that can be the maximum upstream position that the pin can be withdrawn to or the EOS position can be a less than maximum upstream position to which the valve pin can be withdrawn. The upstream COP, COP 2  position is downstream of the maximum upstream end-of-stroke EOS open position of the tip end  1142  of the pin. The length of the path RP or RP 2  is typically between about 2 and about 8 mm, more typically between about 2 and about 6 mm and most typically between about 2 and about 4 mm. In practice the maximum upstream (end of stroke) open position EOS of the pin  1041 ,  1042  ranges from about 8 mm to about 18 inches upstream from the closed gate position GC. 
     The electric drive ( 940   d ,  941   d ,  942   d ) can be housed within the same housing ( 940   h ,  941   h ,  942   h ) as the driver components of the electric actuator ( 940 ,  941 ,  941 ), or the electric drive ( 940   d ,  941   d ,  942   d ) can be housed within a physically separate thermally conductive housing ( 941   ds ) such as shown in  FIG. 1A  that is readily attachable to and detachable from the housing ( 941   h ) that houses the driver components (stator, armature) and rotor component of the electric actuator via conventional device such as bolts, screws, clamps, magnets or the like ( 941   b ). As shown in  FIG. 1A , the thermally conductive housing ( 941   ds ) mounted on the actuator housing is disposed in substantial thermally conductive communication or contact with the actuator housing ( 941   h ) which is in turn mounted via the actively cooled device ( 940   mc ) and the mount device ( 940   mm ) to the heated manifold ( 40 ). As shown the cooling device ( 940   mc ) with fluid receiving and cooling channels ( 33 ) is disposed between the electric drive ( 941   d ), the housing ( 941   h ) and the heated manifold ( 40 ) in an arrangement such that at least the electric drive ( 941   d ) and typically also the housing ( 941   h ) are isolated or insulated from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
     In all embodiments, the electric drive ( 940   d ,  941   d ,  942   d ) is mounted on, to or within the actuator housing ( 940   h ,  941   h ,  942   h ). The actuator housing ( 940   h ,  941   h ,  942   h  is mounted on or to the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) in some manner such that at least the drive components such as a Pulse Width Modulator (PWM) and associated electrical components are isolated or insulated from substantial communication with heat emanating or emitted from the heated manifold ( 40 ) or such that the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) acts to heat sink or absorb heat communicated or communicable to the electrical drive ( 940   d ,  941   d ,  942   d ) from the heated manifold ( 40 ) or both. 
     As shown in  FIGS. 1, 21A-21E  the injection cycle is a cascade process where injection is effected in a sequence from the center nozzle  22  first and at a later predetermined time from the lateral nozzles  20 ,  24 . As shown in  FIGS. 21A, 22A  the injection cycle is started by first opening the pin  1040  of the center nozzle  22  and allowing the fluid material  100  (typically polymer or plastic material) to flow up to a position  100   a  in the cavity just before  100   b  the distally disposed entrance into the cavity  34 ,  36  of the gates of the lateral nozzles  24 ,  20  as shown in  FIG. 1 . After an injection cycle is begun, the gate of the center injection nozzle  22  and pin  1040  is typically left open only for so long as to allow the fluid material  100   b  to travel to a position  100   p  just past the positions  34 ,  36 . Once the fluid material has travelled just past  100   p  of the lateral gate positions  34 ,  36 , the center gate  32  of the center nozzle  22  is typically closed by pin  1040  as shown in  FIGS. 21B, 21C, 21D and 21E . The lateral gates  34 ,  36  are then opened by upstream withdrawal of lateral nozzle pins  1041 ,  1042  as shown in  FIGS. 21B-21E . As described below, the rate of upstream withdrawal or travel velocity of lateral pins  1041 ,  1042  can be controlled as described below. 
     In alternative embodiments, the center gate  32  and associated actuator  940  and valve pin  1040  can remain open at, during and subsequent to the times that the lateral gates  34 ,  36  are opened such that fluid material flows into cavity  30  through both the center gate  32  and one or both of the lateral gates  34 ,  36  simultaneously. 
     When the lateral gates  34 ,  36  are opened and fluid material NM is allowed to first enter the mold cavity into the stream  102   p  that has been injected from center nozzle  22  past gates  34 ,  36 , the two streams NM and  102   p  mix with each other. If the velocity of the fluid material NM is too high, such as often occurs when the flow velocity of injection fluid material through gates  34 ,  36  is at maximum, a visible line or defect in the mixing of the two streams  102   p  and NM will appear in the final cooled molded product at the areas where gates  34 ,  36  inject into the mold cavity. 
     By injecting NM at a reduced flow rate for a relatively short period of time at the beginning when the gate  34 ,  36  is first opened and following the time when NM first enters the flow stream  102   p , the appearance of a visible line or defect in the final molded product can be reduced or eliminated. 
     The rate or velocity of upstream withdrawal of pins  1041 ,  1042  starting from the closed position is controlled via controller  16  which controls the rate and direction of drive of the electric actuators  940 ,  941 ,  942 . 
     The user programs controller  16  via data inputs on a user interface to instruct the electric actuators to drive pins  1041 ,  1042  at an upstream velocity of travel that is reduced relative to a maximum velocity that the actuators can drive the pins  1041 ,  1042  to travel. Such reduced pin withdrawal rate or velocity is executed until a position sensor such as  951 ,  952  detects that an actuator  941 ,  952  or an associated valve pin (or another component), has reached a certain position such as the end point COP, COP 2 ,  FIGS. 22B, 23B  of a restricted flow path RP, RP 2 . A typical amount of time over which the pins are withdrawn at a reduced velocity is between about 0.01 and 0.10 second, the entire injection cycle time typically being between about 0.3 seconds and about 3 seconds, more typically between about 0.5 seconds and about 1.5 seconds. 
       FIG. 1  shows position sensors  950 ,  951 ,  952  for sensing the position of the motors  940 ,  941 ,  942  and their associated valve pins (such as  1040 ,  1041 ,  1042 ) and feed such position information to controller  16  for monitoring purposes. As shown, fluid material  18  is injected from an injection machine into a manifold runner  19  and further downstream into the bores  44 ,  46  of the lateral nozzles  24 ,  22  and ultimately downstream through the gates  32 ,  34 ,  36 . When the pins  1041 ,  1042  are withdrawn upstream to a position where the tip end of the pins  1041  are in a fully upstream open position such as shown in  FIG. 21D , the rate of flow of fluid material through the gates  34 ,  36  is at a maximum. However when the pins  1041 ,  1042  are initially withdrawn beginning from the closed gate position,  FIG. 21A , to intermediate upstream positions,  FIGS. 21B, 21C , a gap  1154 ,  1156  that restricts the velocity of fluid material flow is formed between the outer surfaces  1155  of the tip end of the pins  44 ,  46  and the inner surfaces  1254 ,  1256  of the gate areas of the nozzles  24 ,  20 . The restricted flow gap  1154 ,  1156  remains small enough to restrict and reduce the rate of flow of fluid material  1153  through gates  34 ,  36  to a rate that is less than maximum flow velocity over a travel distance RP of the tip end of the pins  1041 ,  1042  going from closed to upstream as shown in  FIGS. 1, 21B, 21C, 21E and 22B, 23B . 
     The pins  1041  can be controllably withdrawn at one or more reduced velocities (less than maximum) for one or more periods of time over the entirety of the length of the path RP over which flow of mold material  1153  is restricted. Preferably the pins are withdrawn at a reduced velocity over more than about 50% of RP and most preferably over more than about 75% of the length RP. As described below with reference to  FIGS. 22B, 23B , the pins  1041  can be withdrawn at a higher or maximum velocity at the end COP 2  of a less than complete restricted mold material flow path RP 2 . 
     The trace or visible lines that appear in the body of a part that is ultimately formed within the cavity of the mold on cooling above can be reduced or eliminated by reducing or controlling the velocity of the pin  1041 ,  1042  opening or upstream withdrawal from the gate closed position to a selected intermediate upstream gate open position that is preferably 75% or more of the length of RP. 
     RP can be about 1-8 mm in length and more typically about 2-6 mm, more typically 2-4 mm and even more typically 1-3 mm in length. According to the invention, the position of the electric actuators are adjusted in response to sensing of position of a suitable component such as the rotor of an actuator  941 ,  942  or associated valve pin to less than 100% open. Adjustment of the drive of an actuator  931 ,  942  thus reduces the velocity of upstream travel of the pins  1041 ,  1042  for the selected period of time. At the end of the travel or length of path RP, RP 2 , a position sensor signals the controller  16 , the controller  16  determines that the end COP, COP 2  has been reached and the valve pin is driven at higher velocity, typically to its end of stroke (EOS) or its 100% open position to allow the actuator pistons and the valve pins  1041 ,  1042  to be driven at maximum upstream velocity FOV in order to reduce the cycle time of the injection cycle. 
     Typically the user selects one or more reduced velocities that are less than about 90% of the maximum velocity (namely velocity when the valve  600  is fully open), more typically less than about 75% of the maximum velocity and even more typically less than about 50% of the maximum velocity at which the pins  1041 ,  1042  are drivable by the electric actuator apparatus. The actual maximum velocity at which the actuators  941 ,  942  and their associated pins  1041 ,  1042  are driven is predetermined by selection of the size and configuration of the actuators  941 ,  942 . The maximum drive rate of the electric actuator apparatus is predetermined by the manufacturer and the user of the apparatus and is typically selected according to the application, size and nature of the mold and the injection molded part to be fabricated. 
     Preferably, the valve pin and the gate are configured or adapted to cooperate with each other to restrict and vary the rate of flow of fluid material  1153 ,  FIGS. 22A-22B, 23A-23B  over the course of travel of the tip end of the valve pin through the restricted velocity path RP. Most typically as shown in  FIGS. 22A, 22B  the radial tip end surface  1155  of the end  1142  of pin  1041 ,  1042  is conical or tapered and the surface of the gate  1254  with which pin surface  1155  is intended to mate to close the gate  34  is complementary in conical or taper configuration. Alternatively as shown in  FIGS. 23A, 23B , the radial surface  1155  of the tip end  1142  of the pin  1041 ,  1042  can be cylindrical in configuration and the gate can have a complementary cylindrical surface  1254  with which the tip end surface  1155  mates to close the gate  34  when the pin  1041  is in the downstream gate closed position. In any embodiment, the outside radial surface  1155  of the tip end  1142  of the pin  1041  creates restricted a restricted flow channel  1154  over the length of travel of the tip end  1142  through and along restricted flow path RP that restricts or reduces the volume or rate of flow of fluid material  1153  relative to the rate of flow when the pin  1041 ,  1042  is at a full gate open position, namely when the tip end  1142  of the pin  1041  has travelled to or beyond the length of the restricted flow path RP. 
     In one embodiment, as the tip end  1142  of the pin  1041  continues to travel upstream from the gate closed GC position (as shown for example in  FIGS. 22A, 23A ) through the length of the RP path (namely the path travelled for the predetermined amount of time), the rate of material fluid flow  1153  through restriction gap  1154  through the gate  34  into the cavity  30  continues to increase from  0  at gate closed GC position to a maximum flow rate when the tip end  1142  of the pin reaches a position FOP (full open position), where the pin is no longer restricting flow of injection mold material through the gate. In such an embodiment, at the expiration of the predetermined amount of time when the pin tip  1142  reaches the FOP (full open) position the pin  1041  is immediately driven by at maximum velocity FOV (full open velocity). In alternative embodiments, when the predetermined time for driving the pin at reduced velocity has expired and the tip  1142  has reached the end of restricted flow path RP 2 , the tip  1142  may not necessarily be in a position where the fluid flow  1153  is not still being restricted. In such alternative embodiments, the fluid flow  1153  can still be restricted to less than maximum flow when the pin has reached the changeover position COP 2  where the pin  1041  is driven at a higher, typically maximum, upstream velocity FOV. 
     In the alternative examples shown in the  FIGS. 22B, 23B  examples, when the pin has travelled the predetermined path length at reduced velocity and the tip end  1142  has reached the changeover point COP, the tip end  1142  of the pin  1041  (and its radial surface  1155 ) no longer restricts the rate of flow of fluid material  1153  through the gap  1154  because the gap  1154  has increased to a size that no longer restricts fluid flow  1153  below the maximum flow rate of material  1153 . Thus in one of the examples shown in  FIG. 22B  the maximum fluid flow rate for injection material  1153  is reached at the upstream position COP of the tip end  1142 . In another example shown in  FIGS. 22B, 23B , the pin  1041  can be driven at a reduced velocity over a shorter path RP 2  that is less than the entire length of the restricted mold material flow path RP and switched over at the end COP 2  of the shorter restricted path RP 2  to a higher or maximum velocity FOV. In another alternative embodiment, shown in  FIG. 4B , the pin  1041  can be driven and instructed to be driven at reduced or less than maximum velocity over a longer path length RP 3  having an upstream portion UR where the flow of injection fluid mold material is not restricted but flows at a maximum rate through the gate  34  for the given injection molding apparatus. In this  FIG. 4B  example the velocity or drive rate of the pin  1041  is not changed over until the tip end of the pin  1041  or actuator  941  has reached the changeover position COP 3 . As in other embodiments, a position sensor senses either that the valve pin  1041  or an associated component has travelled the path length RP 3  or reached the end COP 3  of the selected path length and the controller receives and processes such information and instructs the drive apparatus to drive the pin  1041  at a higher, typically maximum velocity upstream. In another alternative embodiment, the pin  1041  can be driven at reduced or less than maximum velocity throughout the entirety of the travel path of the pin during an injection cycle from the gate closed position GC up to the end-of-stroke EOS position, the controller  16  being programmed to instruct the drive system for the actuator to be driven at one or more reduced velocities for the time or path length of an entire closed GC to fully open EOS cycle. 
     Typically, when the time period for driving the pin  1041  at reduced velocity has expired and the pin tip  1142  has reached the position COP, COP 2 , the pins  1041 ,  1042  are driven at the maximum velocity or rate of travel that the actuator system is capable of driving the valve pins  1041 ,  1042 . Alternatively, the pins  1041 ,  1042  can be driven at a preselected FOV velocity that is less than the maximum velocity at which the pin is capable of being driven when the restriction valve  600  is fully open but is still greater than the selected reduced velocities that the pin is driven over the course of the RP, RP 2  path to the COP, COP 2  position. 
     At the expiration of the predetermined reduced velocity drive time, the pins  1041 ,  1042  are typically driven further upstream past the COP, COP 2  position to a maximum end-of-stroke EOS position. The end-of-stroke position EOS is an upstream position selected by the user that can be the maximum upstream position that the pin can be withdrawn to or the EOS position can be a less than maximum upstream position to which the valve pin can be withdrawn. The upstream COP, COP 2  position is downstream of the maximum upstream end-of-stroke EOS open position of the tip end  1142  of the pin. The length of the path RP or RP 2  is typically between about 2 and about 8 mm, more typically between about 2 and about 6 mm and most typically between about 2 and about 4 mm. In practice the maximum upstream (end of stroke) open position EOS of the pin  1041 ,  1042  ranges from about 8 mm to about 18 inches upstream from the closed gate position GC. 
     As shown in each of the embodiments shown in the Figures the electrical drive ( 940   d ,  941   d ,  942   d ) is incorporated into, housed within, or physically mounted onto or in direct heat communication with the actuator housing ( 940   h ,  941   h ,  942   h ) of the actuator such that the electric drive ( 940   d ,  941   d ,  942   d ) is in direct or indirect thermal communication or contact with the thermally conductive housing ( 940   h ,  941   h ,  942   h ) of the actuator. 
     The electrical drive ( 940   d ,  941   d ,  942   d ) can be housed or mounted in a thermally conductive housing body ( 940   ds ) that is readily attachable to and detachable from the actuator housing ( 940   h ,  941   h ,  942   h ) as shown in  FIGS. 1A, 1B  such a readily attachable and detachable housing body ( 940   ds ) being attachable or mountable to the actuator housing ( 940   h ,  941   h ,  942   h ) in an arrangement such that the electrical drive ( 940   d ,  941   d ,  942   d ) is in direct or indirect thermally conductive contact or communication with the actuator housing ( 940   h ,  941   h ,  942   h ). 
     As shown, the housings ( 940   h ,  941   h ,  942   h ) of each of the actuators ( 940 ,  941 ,  942 ) is mounted on, to or in close physical proximity to a heated manifold ( 40 ). 
     The electric actuators  940 ,  941 ,  942  typically comprise a driver  940   dr ,  941   dr ,  942   dr  typically comprised of a stator and armature that are interconnected to a rotatably mounted rotor or shaft  940   r ,  941   r ,  942   r  such that when the drivers  940   dr ,  941   dr ,  942   dr  rotate on application and receipt of electrical energy or power, the shafts  940   r ,  941   r ,  942   r  are simultaneously rotatably moved and driven. 
     The rotor ( 940   r ,  941   r ,  942   r ) has a drive axis (Y). The driver ( 940   dr ,  941   dr ,  942   dr ) is interconnected to the rotor ( 940   r ,  941   r ,  942   r ) and adapted to controllably drive the rotor rotatably around the drive axis Y. 
     The drivers ( 940   dr ,  941   dr ,  942   dr ) receive electrical energy or power from an electrical drive ( 940   d ,  941   d ,  942   d ). The electrical drive ( 940   d ,  941   d ,  942   d ) typically comprises an interface that receives electrical energy or power from a power source PS and controllably distributes the received electrical energy or power in controllably varied amounts during the course of an injection cycle to the drivers ( 940   dr ,  941   dr ,  942   dr ). 
     The actuator includes a housing ( 940   h ,  941   h ,  942   h ) that houses the rotor ( 940   r ,  941   r ,  942   r ) and the driver ( 940   dr ,  941   dr ,  942   dr ) and is adapted to support the rotor ( 940   r ,  941   r ,  942   r ) such that the rotor is drivably rotatable  940   rt ,  941   rt ,  942   rt . The housing ( 940   h ,  941   h ,  942   h ) is typically thermally or heat conductive such that the housing can deliver heat to a cooler body such as the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) described herein or a cooler body such as the top clamp plate with which the actuator housing may be passively cooled. The thermally conductive actuator housing body ( 940   h ,  941   h ,  942   h ) can receive heat or thermal energy from devices such as the manifold ( 40 ) with which the housing ( 940   h ,  941   h ,  942   h ) could be in thermally conductive communication or contact but for provision and arrangement of the cooling device disclosed herein that prevents or retards such thermal transmission of heat from the manifold ( 40 ). 
     The electrical drive ( 940   d ,  941   d ,  942   d ) is typically housed within or by the housing ( 940   h ,  941   h ,  942   h ) or is physically mounted on or to the housing ( 940   h ,  941   h ,  942   h ) in thermally conductive communication or contact therewith. 
     The electrical drive ( 940   d ,  941   d ,  942   d ) typically includes a PWM or pulse-width modulator that converts received electrical energy or power into sinusoidal voltage waveforms, each sinusoidal voltage waveform being adapted to drive a corresponding phase-coil of the actuator driver ( 940   dr ,  941   dr ,  942   dr ). 
     The PWM or pulse-width modulator typically comprises an inverter or comparator. 
     The PWM modulator typically comprises a three-phase PWM inverter that converts electrical energy or power received from the interface into three sinusoidal voltage waveforms, each one of the three sinusoidal voltage waveforms being adapted to drive a corresponding one of three phase-coils of the actuator driver. 
     The electrical energy or power received at or by the PWM modulator can be a DC bus voltage. 
     The interface of the electrical drive  940   d ,  941   d ,  942   d  is adapted to receive one or more control signals from a controller  16  of the injection molding apparatus and to convert electrical energy or power received the power source PS into sinusoidal waveforms based on the one or more control signals. The interface is comprised of the PWM or pulse width modulator which converts electrical energy or power received from the power source into sinusoidal waveforms based on the one or more control signals. 
     The one or more control signals received by the interface of the electrical drive contain control information causing the pulse width modulator to convert the received electrical energy or power into sinusoidal waveforms adapted to drive the corresponding phase-coils of the actuator driver to adjust one or more of a position, a velocity or torque of the actuator rotor  940   r ,  941   r ,  942   r.    
     The one or more control signals can comprise analog electrical signals received at the electrical drive from the controller  16 . 
     The electrical drive  940   d ,  941   d ,  942   d  can further comprise one or the other or both of a digital signal receiving ( 16   r ) and transmitting ( 16   s ) device,  FIG. 1A . The controller ( 16 ) includes a digital command or signal generating mechanism such as a computer drive, microcontroller, microcircuit, chipset or the like interconnected to a digital data storage medium to and from which the digital command or signal generating mechanism exchanges digital signals, data or commands. The controller ( 16 ) is adapted to send and received digital signals, commands, data to and from a digital signal receiving device ( 16   r ) contained within the electrical drive ( 940   d ,  941   d ,  942   d ). The digital commands that are received ( 16   s ) by the electrical drive ( 940   d ,  941   d ,  942   d ) are used by the drive ( 940   d ,  941   d ,  942   d ) to control distribution of electrical energy or power to the driver ( 940   dr ,  941   dr ,  942   dr ) thus controlling the speed of rotation of the rotor of the actuator ( 940 ,  941 ,  942 ) during the course of the injection cycle. 
     The electrical drive ( 940   d ,  941   d ,  942   d ) can also include a digital signal, data or command sending device ( 16   s ) that is typically comprised of a microcontroller, microcircuit, chipset or the like and adapted to communicate or send digital signals back to a digital signal receiving device contained within the controller ( 16 ). 
     The digital control signals can include one or more of differential position commands, differential current commands, and differential velocity commands. 
     The digital signal receiving and transmitting device ( 16   r ,  16   s ) further can receive digital signals from the actuator, wherein the digital signals received from the actuator include one or more feedback signals corresponding to operation of one or more of the actuator and the actuator rotor. 
     The one or more feedback signals received by the electrical drive ( 940   d ,  941   d ,  942   d ) from the actuator can include one or more of an incremental feedback signal and an absolute feedback signal. Such incremental feedback signal or absolute feedback signal sent by the actuator to the electrical drive can be communicated or sent back to the controller ( 16 ) by the digital signal sending device ( 16   s ). 
     The apparatus shown in  FIG. 1A  comprises an electric actuator ( 941 ) having a housing ( 941   h ) and an electric drive ( 941   d ) that is readily attachable to and detachable from the housing ( 941   h ) of the actuator via a conventional attachment and detachment mechanism such as bolts ( 941   b ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ), the cooling device being adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
     As shown in  FIG. 1B , the actuator housing ( 941   h ) and electric drive can alternatively be mounted in a spaced relationship on or to the cooling device via mounts ( 60 ) that are typically comprised of a heat insulative material such as titanium, bismuth, stainless steel, lead, chromium or the like. 
     An example of direct metal to metal contact is as shown in the  FIG. 2B  embodiment where actuator housing  940   h  is mounted in direct metal to metal contact with the heated manifold  40  via mounts  60  that are typically comprised of a heat insulative material. The actuator housing  940   h  is mounted in direct metal to metal contact with mounts  60   s  that are typically comprised of a heat conductive material mounted in direct metal to metal contact with the actively cooled mount  940   mc  such that heat is conducted from the actuator housing  940   h  to the actively cooled mount  940   mc  that acts as a heat sink for heat contained in the actuator housing  940   h . The actively cooled mount  940   mc  is itself is mounted to the heated manifold  40  via direct metal to metal contact or communication with mounts  60  which are in turn mounted in direct metal to metal contact with the heated manifold  40 . Thus the direct metal to metal contact of mounts  60 ,  60   s  as described substantially accomplishes a direct metal to metal communication or contact of the actuator housing  940   h  and the electric drive  940   d  with the heated manifold  40 . 
       FIGS. 2A to 2E  show an embodiment where the actuator ( 940 ) has a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) and the electric drive ( 940   d ) being mounted on, to or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator housing ( 940   h ) to a rotary to linear travel converter ( 9401 ,  940   h ) which is in turn mounted on, to or in close physical proximity to a heated manifold with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the linear travel converter ( 9401 ,  940   h ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ,  941   d ,  942   d ). The cooling device is adapted and arranged relative to the electric drive to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). The cooling device is also typically adapted and arranged to isolate or insulate the actuator housing ( 940   h ) and the rotary to linear converter ( 940   l ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). In the  FIGS. 2A to 2E  embodiment the conversion of motor movement is conversion of rotary motion of the rotor directly to non coaxial linear motion of the drive member  9401  along axis X of the valve pin. 
       FIG. 2A  shows an embodiment where the electric actuator ( 940 ) has a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) and the electric drive ( 940   d ) being mounted to or on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a rotational speed reducing device ( 46 ) that is in turn mounted to a rotary to linear travel converter ( 9401 ,  940   h ) which is in turn mounted on or to or in close physical proximity to a heated manifold ( 40 ) with the cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) disposed between the heated manifold ( 40 ) and the rotary to linear travel converter ( 9401 ,  940   h ), the rotational speed reducing device ( 46 ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ). The cooling device is adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). The cooling device is also typically adapted and arranged to isolate or insulate the actuator housing ( 940   h ) and the rotary to linear converter ( 940   l ) and the rotational speed reducing device ( 46 ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
     In this embodiment the rotary to linear converter  15  and its housing  9401   h  together with the speed reducing device  46  and actuator  940  to which the converter  15  is subassembled are mounted to the heated manifold ( 40 ) via standoffs or mounts  60  that are preferably comprised of a heat insulative material such as titanium, bismuth. stainless steel, lead, chromium or the like. 
     As shown in  FIG. 2D  the rotational speed reducing device  46  comprises a harmonic device and the rotary to linear converter device  9401  comprises a wheel or disc that uses an eccentric or eccentrically disposed pin or projection to drive the valve pin along pin axis X. 
       FIGS. 2F, 2G  show another embodiment comprised of an actuator having a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ). The actuator housing ( 940   h ) is mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a rotary to linear travel converter ( 9401 ,  9401   h ) which is in turn mounted on, to or in close physical proximity to a heated manifold ( 40 ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) disposed between the heated manifold ( 40 ), the linear travel converter ( 9401 ,  940   h ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ). The cooling device is adapted and arranged to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). As shown the  FIGS. 2F, 2G  cooling device ( 940   mc ) comprises a single unitary elongated plate on which both the actuator housing ( 940   h ), electric drive ( 940   d ), converter ( 940   l ) and converter housing ( 9401   h ) are mounted with the cooling device being adapted and arranged to isolate or insulate all of the electric drive ( 940   d ), the actuator housing ( 940   h ) and the rotary to linear converter ( 940   l ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
     In an alternative embodiment, the mounts  60  such as mount  60   s ,  FIG. 2B , can be comprised of a highly heat conductive material such as copper such that heat is more readily conducted from the actuator housing  940   h  to the actively cooled mount  940   mc.    
       FIGS. 2H, 2I  shows another embodiment comprised of an actuator having a drive axis Y that is arranged non-coaxially relative to the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a linear travel converter ( 9401 ,  940   h ) which is in turn mounted on or to or in close physical proximity to a heated manifold ( 40 ) with a separate unitary body cooling device such as a plate ( 940   mc   1 ) being disposed and arranged between the heated manifold ( 40 ) and the rotary to linear travel converter ( 9401 ,  940   h ). The actuator housing ( 940   h ) is separately mounted on or to a separate unitary body cooling device ( 940   mc   2 ). The cooling devices ( 940   mc   1 ,  940   mc   2 ) are each separately adapted and arranged to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). As shown the rotary to linear converter ( 940   l ) is mounted to the separate cooling device ( 940   mc   1 ) in an arrangement such that the rotary to linear converter ( 940   l ) and electric drive ( 940   d ) are substantially isolated or insulated from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). And, as shown the actuator housing ( 940   h ) is mounted to the separate cooling device ( 940   mc   2 ) in an arrangement such that the actuator housing ( 940   h ) and the electric drive ( 940   d ) are substantially isolated or insulated from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). As shown each of the separate cooling devices or plates ( 940   mc   1 ,  940   mc   2 ) separately contain fluid channels ( 33 ) for receiving cool or cooled fluid that cools the cooling devices. As shown the linear to linear converter ( 940   l ) is mounted to the separate cooling device ( 940   mc   1 ) in an arrangement such that the linear to linear converter ( 940   l ) and electric drive ( 940   d ) are substantially isolated or insulated from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). And, as shown the actuator housing ( 940   h ) is mounted to the separate cooling device ( 940   mc   2 ) in an arrangement such that the actuator housing ( 940   h ) and the electric drive ( 940   d ) are substantially isolated or insulated from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). As shown each of the separate cooling devices or plates ( 940   mc   1 ,  940   mc   2 ) separately contain fluid channels ( 33 ) for receiving cool or cooled fluid that cools the cooling devices. 
     In the  FIGS. 2F, 2G, 2H, 2I  embodiment, the linear to linear converter  15  comprises a travel converter that is comprised of a sliding body  507  fixedly interconnected a linear drive shaft  150  of the actuator. An undersurface of the sliding body  507  is slidably mounted on a mounting surface of a bottom wall of a subassembled body housing such that the sliding body  507  is controllably drivable along the first linear drive axis (Y) by controlled drive of the actuator with the controller  16 . As shown in the specific embodiment, the sliding body  507  is formed to include an aperture or slot within the body  507  that is configured and adapted to cause the valve pin  1040  to be driven at one or more selected speeds along axis X in relation to the rotational speed of drive of the actuator  940 . The upstream end of the valve pin is fixedly connected to a follower pin around which is typically mounted one or more wheels that are typically rotatably mounted on the follower pin as disclosed in WO2018/194961 the disclosure of which is incorporate herein by reference in its entirety as if fully set forth. The housing, follower pin, valve pin and manifold are assembled such that the guide slot receives the follower pin and wheels in an arrangement where the outside surfaces of the wheels engage against the guide surface of the slot. As the sliding body  507  is moved along axis Y the slot moves along axis X and the follower pin is forced by engagement against the moving slot surface to move along the non coaxial axis X, the valve pin thus moving along the axis X together with movement of the sliding body  507  along axis Y. The speed of movement of the valve pin  1040  depends both on the contour or profile of the surface of guide slot and on the speed of movement of the linear drive member  150  of actuator  940 . Typically the linear drive member  150  of the  FIGS. 2F, 2G, 2H  embodiment is driven linearly along axis Y in the same fashion as the linear drive member  9401  of the  FIGS. 3A, 3B  embodiment is driven along a coaxial pin axis X via a rotor nut  940  having threads  940   rt  that are screwably engaged with the male threads  9401   t  of the drive member  9401 . In a similar manner, the linear drive member  150  of the  FIGS. 2F, 2G  embodiments can include a nut (not shown) that is fixedly disposed on the distal end of the linear drive member  150  the nut being screwably engaged with a complementary male thread  940   rt  disposed on the distal end of the motor&#39;s rotor  940   r  in an arrangement that causes the drive member  150  to be driven reciprocally along a linear axis Y that is non coaxial relative to the linear pin axis X. In all cases the linear drive member  150 ,  940 ,  9401   d  is driven linearly along a selected axis X, Y and is interconnected to the valve pin  1040 ,  1041  in an arrangement adapted to drive the valve pin reciprocally along the valve pin axis X. In the embodiment of  FIGS. 2F to 2I , the slot has a linear or straight configuration such that the speed of movement of valve pin  1040  varies directly or linearly with the speed of movement of linear drive member  150 . Alternatively, theslot  509  can have a stepped or curved surface configuration comprised of two separate straight steps of differing slopes or degrees of angle relative to linear movement axis X which results in the velocity of valve pin  1040  increasing when the valve pin is withdrawn upstream and reaches higher upstream positions. Thus the velocity of movement of the valve pin  1040  along the X axis can be changed relative to a constant linear drive member  150  velocity via a stepped or curved slot profile. 
     In the  FIGS. 2F, 2G, 2H, 2I  embodiment, the rotary to linear converter  15  comprises a travel converter that is comprised of a sliding body  507  fixedly interconnected a linear drive shaft  150  of the actuator. An undersurface of the sliding body  507  is slidably mounted on a mounting surface of a bottom wall of a subassembled body housing such that the sliding body  507  is controllably drivable along the first linear drive axis (Y) by controlled drive of the actuator with the controller  16 . As shown in the specific embodiment, the sliding body  507  is formed to include an aperture or slot within the body  507  that is configured and adapted to cause the valve pin  1040  to be driven at one or more selected speeds along axis X in relation to the rotational speed of drive of the actuator  940 . The upstream end of the valve pin is fixedly connected to a follower pin around which is typically mounted one or more wheels that are typically rotatably mounted on the follower pin as disclosed in WO2018/194961 the disclosure of which is incorporate herein by reference in its entirety as if fully set forth. The housing, follower pin, valve pin and manifold are assembled such that the guide slot receives the follower pin and wheels in an arrangement where the outside surfaces of the wheels engage against the guide surface of the slot. As the sliding body  507  is moved along axis Y the slot moves along axis X and the follower pin is forced by engagement against the moving slot surface to move along the non coaxial axis X, the valve pin thus moving along the axis X together with movement of the sliding body  507  along axis Y. The speed of movement of the valve pin  1040  depends both on the contour or profile of the surface of guide slot and on the speed of movement of the linear drive member  150  of actuator  940 . 
     In the embodiment of  FIGS. 2F to 2I , the slot has a linear or straight configuration such that the speed of movement of valve pin  1040  varies directly or linearly with the speed of movement of linear drive member  150 . Alternatively, the slot  509  can have a stepped or curved surface configuration comprised of two separate straight steps of differing slopes or degrees of angle relative to linear movement axis X which results in the velocity of valve pin  1040  increasing when the valve pin is withdrawn upstream and reaches higher upstream positions. Thus the velocity of movement of the valve pin  1040  along the X axis can be changed relative to a constant linear drive member  150  velocity via a stepped or curved slot profile. 
     As can be readily imagined, the contour or profile of the slot included in member  507  can be selected to be of any stepped, curved or other non linear configuration such that the velocity V of movement of the valve pin  80  along the linear axis X has any selected or predetermined non linear or varying correlation to the velocity of movement of the linear drive member  150 , in particular such that the velocity along axis X changes to one or more greater or less preselected velocities over the course of travel of the valve pin  1040  between gate closed and gate full open positions where the velocity of the linear drive member  150  is constant over the same course of travel of the valve pin  1040 . 
     Other configurations of linear converters that cause the pin to be driven as varying velocities over the course of an injection cycle can be used such as disclosed in WO2018/194961. 
       FIG. 3A  shows another embodiment of an electric actuator where the actuator ( 940 ) has a drive axis Y that is coaxial with the travel axis X of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to or on or in close physical proximity to the heated manifold ( 40 ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ). In this embodiment, the cooling device is adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). The cooling device is also typically adapted and arranged to isolate or insulate the actuator housing ( 940   h ) and the rotary to linear converter ( 940   l ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). The cooling device is also typically adapted to heat sink heat from the actuator housing ( 940   h ) and the rotary to linear converter ( 940   l ) to the cooling device. 
       FIG. 3B  shows an embodiment where the actuator ( 940 ) has a drive axis Y that is coaxial with the travel axis of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to or on or in direct thermal communication with the heated manifold ( 40 ) via mounts ( 940   s ) mounted on or to or in direct thermal communication or contact with the heated manifold ( 40 ). The cooling device is also typically adapted to heat sink heat from the actuator housing ( 940   h ) and the rotary to linear converter ( 940   l ) to the cooling device. The mounts  940   s  can be comprised of highly heat conductive material such as copper or alternatively comprised of heat insulative material such as titanium. 
       FIG. 5  shows an apparatus similar to the  FIG. 2  apparatus where the actuator ( 940 ) has a drive axis Y that is arranged non-coaxially relative to the travel axis X of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to or on or in direct thermal communication with the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a linear travel converter ( 940   l ) having a housing ( 9401   h ) which is in turn mounted on or to a top clamping plate ( 80 ) via a flange ( 9401   f ), the linear travel converter ( 940   l ) being disposed in direct thermal communication with the heated manifold ( 40 ). 
     In all embodiments where the electric actuator  940  drives a linear drive member such as drive members  150 ,  940   l ,  940   ld , the drive member can be driven directly by electromagnetic force  940   ef  generated by the driver  940   r  as described herein with reference to the solenoid and linear motor devices of  FIGS. 24, 25 . The selected axis A of drive of the drive member  150 ,  9401 ,  9401   d  can be coaxial or non coaxial relative to the pin axis X. 
       FIG. 12B  shows another embodiment where the actuator ( 940 ) has a drive axis Y that is arranged non-coaxially relative to the travel axis X of the valve pin ( 1040 ), the actuator housing ( 940   h ) being mounted to, on or in close physical proximity to the heated manifold ( 40 ) via mounting of the actuator ( 940 ) to a linear travel converter ( 9401 ,  940   h ) which is in turn mounted on or to or in close physical proximity to a heated manifold ( 40 ) with a cooling device ( 940   mc ,  940   mc   1 ,  940   mc   2 ,  941   mc ,  942   mc ) being disposed between the heated manifold ( 40 ) and the linear travel converter ( 9401 ,  940   h ), the actuator housing ( 940   h ,  941   h ,  942   h ) and the electric drive ( 940   d ). The cooling device is adapted to substantially isolate or insulate at least the electrical drive ( 940   d ,  941   d ,  942   d ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). The cooling device is also typically adapted and arranged to isolate or insulate the actuator housing ( 940   h ) and the rotary to linear converter ( 940   l ) from substantial communication with heat emanating or emitted from the heated manifold ( 40 ). 
     The  FIG. 12B  embodiment includes a passive cooling device comprised of a mount ( 2000 ) as shown in  FIGS. 12C, 12D . The mount ( 2000 ) is preferably comprised of a thermally conductive material having first ( 2000   is ) and second ( 2000   ms ) heat conductive surfaces that are disposed between the clamping plate ( 80 ) and the actuator housing ( 940   h ). A surface ( 9401   s ) of the actuator housing ( 940   h ) is mounted in thermal communication or contact with the first heat conductive surface ( 2000   is ) and a surface ( 80   ms ) of the clamping plate ( 80 ) is mounted in thermal communication or contact with the second conductive surface ( 2000   ms ). The second conductive surface ( 2000   ms ) of the mount ( 20000 ) is adapted to be urged into compressed (dsf) thermally conductive contact or communication with the surface ( 80   ms ) of the clamping plate ( 80 ). 
     The mount ( 2000 ),  FIGS. 612B, 12C, 12D  includes a resiliently compressible spring ( 2002 ) disposed between the actuator housing ( 940   h ) and the clamping plate ( 80 ) that is adapted to urge (dsf) the surface ( 2000   ms ) of the mount ( 2000 ) into compressed thermally conductive contact or communication with the surface ( 80   ms ) of the clamping plate ( 80 ). 
     The spring ( 2002 ),  FIGS. 12B, 12C, 12D  comprises one or more resiliently compressible arms ( 2002   a ) that are resiliently bendable  2002   j  and have an actuator engagement surface ( 2002   us ) adapted to engage a complementary surface ( 940   us ) of the actuator housing ( 940   h ). The spring ( 2002 ), the mount ( 2000 ) and the clamping plate are arranged such that the resiliently compressible arms ( 2002   a ) bend when the actuator housing ( 940   h ), mount ( 2000 ) and clamping plate ( 80 ) are assembled together with the manifold ( 40 ) to cause the actuator engagement surface ( 2002   us ) to compressibly engage (USF) the complementary surface ( 940   us ) and to urge the surface ( 2000   ms ) of the mount ( 2000 ) into compressed (dsf) thermally conductive contact or communication with the surface ( 80   ms ) of the clamping plate ( 80 ) when the heated manifold ( 80 ) is brought to operating temperature. 
     In the  FIGS. 12E, 12F  embodiment a bottom surface  41  of the body  45  of the actuator  40  is mounted in thermally conductive contact with a top surface  12  of the highly thermally conductive cooling or mounting plate  10 . The bottom or downstream surface  13  of the cooling or mount plate  10  is in turn mounted in compressed contact with the top or upstream facing surface  31  of highly thermally conductive metal cooling block  30 . The cooling block  940   mc  is proactively cooled with water pumped through cooling channels  33  during active operation of the entire apparatus. As shown the cooling block is mounted on a mount  60  the bottom surfaces  63  of which are mounted in direct contact with the top surface  57  of the heated hotrunner  40 . During operation of the apparatus, the cooled cooling block  940   mc  serves to maintain the actuator  40  cool and/or relatively insulated from the heated manifold  40 . In the embodiment shown in the Figures, the cooling block  30  is mounted on the intermediate mount  60  which itself is mounted in engagement contact with the body or top surface  57  of the heated manifold  50  via bolts  62 . Heat from the heated manifold  50  is thus thermally conducted or transferred through the bolts  62  and through the mount  60 , block  30  and mount  10  to the actuator  40 . 
     As shown in  FIGS. 12E, 12F  the highly thermally conductive cooling mount  10  has lateral extensions or wings  14  that are configured and arranged to have an upper or upstream facing surface(s)  11  that make compressed contact with a lower surface  21  of the cooled clamp plate  20  thus enabling heat that may otherwise flow from the manifold  50  to/through the cooling block  30  and the plate  10  and the actuator  40  to be conductively transferred to the cooled clamp plate  20 . Once the actuator  40  together with winged cooling plate  10  and in the position shown in  FIGS. 1-9  on cooling device  30  and mount  60  onto surface  57 , the rest of the system is assembled and arranged such that the clamp plate  20  is mounted a spaced distance S upstream of the heated manifold  50 . The actuator  40  and its associated components plate  30  and mount  60  collectively have a mounting height AH extending upstream from the surface  57  of the heated manifold  50 . The receiving cavity  20  of the clamp plate  20  has a receiving depth CH of sufficient size together with space S to accommodate receipt of the mounting height AH of the assembly of the actuator  40 , plates  100 , and cooling device  30 . 
     Thus in the  FIGS. 12E, 12F  embodiment, some portion of the heat that is conducted to the body of the actuator  40  from the heated manifold  40  is re-routed or conducted to the wings  14  via heat conductive engagement of the surfaces  13  and  31 . Such heat that is conducted to the wings  14  is in turn conducted to the clamp plate surface  21  via engagement with the spring-loaded heat conductive surface  11 , the clamp plate  20  acting as a heat sink to help lower the temperature of the body  45  of the actuator  40 . 
     As shown the system is adapted and arranged so that when assembled, the clamp plate  20  is thermally isolated from the heated manifold by an insulating air space S by which the clamp plate  20  is spaced apart from the upstream surface  57  of the manifold  50 . Typically, the clamp plate  20  is maintained in such a thermally isolated position relative to the manifold  50 , the clamp plate having little to no direct thermally conductive contact with the manifold  50  other than incidentally through a less than about 2 inch square area of contact that may exist between a spacer  48  and the clamp plate  20  and between the spacer  48  and the manifold  50 , the spacer  48  being disposed between the clamp plate  20  and the manifold for purposes of ensuring proper positioning of the manifold  50  relative to the clamp plate  20 . The clamp plate  20  is typically cooled with a cooling fluid pumped and flowing through cooling channels  25  in the body of the clamp plate  20 . Thus, thermally conductive direct contact between the surfaces  11  and the clamp plate surface  21  enable heat to transfer from the body  45  of the actuator  40  to the clamp plate  20 , the heat being readily dissipated by the cooled clamp plate  20 . 
     The winged cooling plate  10  is comprised of a highly thermally conductive material. The cooling plate assembly  10 ,  30 ,  60  has an assembled height ASH when mounted to the manifold surface  57  that extends from the downstream-most mounting surface  63  of the mount  60  to the upstream facing engagement surface  11  of the wings  14  of the cooling plate  10 ,  FIGS. 4-6 . The length of the spacing distance S is predetermined relative to the assembled height ASH such that when the components of the system including the clamp plate  20  and manifold  50  are assembled and connected together with the mold  500 , the upstream facing surfaces  11  of the wings  14  engage the downstream facing surface  21  of the clamp plate  20  under a selected amount of compression created by the downstream bending of wings  14  resulting in upward spring force SF being exerted by wings  14  urging surfaces  11  in an upstream direction into compressed engagement with surface  21  of cooled clamp plate  20 . Thus the system is adapted to have an assembled configuration where on assembly together of the clamp plate  20 , mold  500 , manifold  50 , actuator  40  and mount  10 , the spring force in the wings  14  is loaded thus urging the surfaces  11  into thermally conductive compressed engagement with the surface  21 . 
     The compressed contact between thermally conductive metal surfaces  11  and  21  enables heat flow between the bodies  10 ,  20  having the metal surfaces. The cooling device  30  is typically cooled to less than about 100 degrees Fahrenheit and is actively cooled by water injection flow during an injection cycle. When the injection molding machine  70  is shut down, all of the other components of the apparatus including the cooling device are also typically shut down causing the actuator  40  to be more prone and subject to being heated up by the manifold  50 . The manifold  50  is very large in size and mass and thus takes a longer time to cool down on shutting the apparatus down. Thus immediately after shut down of the apparatus, the cooling block  30  is not proactively working to maintain the actuator  40  cool while the manifold  50  simultaneously remains at a very high temperature thus causing elevated heat transfer from the manifold  50  through the mount  60  and the block  30  to the actuator  40 . The thermally conductive plate-mount  10  serves to divert the manifold heat via the wings  14  to the relatively cool clamp plate  20  which is itself a very large mass of material which is not easily heated up by the hot manifold on shut down. The thermally conductive mount  10  thus essentially cools the actuator  40  or at least works to minimize or lessen the amount of heat transfer from the manifold  50  to the actuator  40  without active cooling by the cooling device  30 . 
     In the embodiment shown in  FIGS. 12E, 12F , a spacer  80  is compressibly connected to selected position on the downstream facing surface  21  of the clamp plate  20  such that the upstream facing surface  11  of the wings  14  engage a downstream facing surface  83  of the spacers  80  rather than directly to the clamp plate surface  21 . The spacers  80  are comprised of a highly thermally conductive material so that heat conducts readily from the wings  14  to the spacers  80  and in turn from the spacers to the clamp plate body  20 . The spacers  80  can be employed to increase the size of the insulating air space S 1  or for otherwise accommodating thickness, height or other size variations in the components  10 ,  30 ,  60  or other components that may be employed to assemble and mount the cooling plate  10 . As in other embodiments, the size, depth and height of the various components of the system shown in  FIGS. 12D, 12E  are preselected such that when the components of the system are all assembled, in particular when the clamp plate  20  and manifold are mounted to the mold  500  and the spacers  48  and  80  are assembled and connected to the clamp plate  20 , the upstream facing surfaces  11  of the wings  14  engage the downstream facing surface  83  of the spacers  80  under a selected amount of compression created by the downstream bending of wings  14  resulting in upward spring force SF being exerted by wings  14  urging surfaces  11  in an upstream direction into compressed engagement with surfaces  83  of spacers  80 . As in other embodiments, the clamp plate  20  is preferably thermally isolated from the heated manifold  50 . 
     In an alternative embodiment shown in  FIGS. 12G, 12H  the actuator  940  is mounted to the manifold  40 , separated from direct contact with the manifold  40  by the cooling device  30  and the mount  60  for the cooling device. The  FIGS. 11, 12  apparatus has cooling or heat deflector plates  100  which are flanged as shown. The plates  100  have one or more slots  150  that slidably receive projections  160  from a sidewall  43  of the actuator  40  such that the plates  150  can be slid or moved in an upstream or downstream direction  180  relative to the actuator  40 . The projections  160  comprise a bolt  160   b  that extends laterally through the slots  150 , the bolts having a diameter that is complementary to the width W of the slots  150  so that the plate  100  is prevented from travelling in front to back direction T and is slidable in an up and down direction UD. The projections  160  preferably have a head portion  160   h  having a diameter that is wider than the width W of the slot  150 , the head portion  160   h  having an inwardly facing surface  160   a  that engages the outwardly facing edge surfaces  150   a  of the slots  150  thus preventing the plates  100  from moving in a lateral direction L away from the outside lateral surface  43  of the body of the actuator  40 . As shown, the bolts  160   b  are screwed and secured a selected distance into the depth of the body of the actuator  40  as shown in  FIG. 10  so as to stably position the projections  160  and the head  160   h  and inwardly facing surface  160   a  relative to the the side edges  150   a  of the slots  150  such the inside surfaces  104   i  of the sides  104  of the plates  100  are held in engaged contact with the outside surface  43  of the actuator  40 . 
     The inside surfaces  104   i  that are engaged with the outside surface  43  of the actuator are thus in heat conductive contact with the sidewall  43  or other outside surface of the actuator  40  as may alternatively be selected for engagement of the plates  100  therewith. As shown, the plates  100  have a top flanged portion  106  that extends and is disposed between a top end surface  47  of the actuator  40  and a downstream facing surface  140  of the top clamp plate  20 . The top flanged portion  106  of the cooling or deflector plates  100  have a top or upstream facing surface  130  that is urged by spring force  128  of spring  120  into engagement and heat conductive contact with the downstream facing surface  140  of the top clamp plate. A plate or leaf spring  120  is disposed in engagement with the top surface  47  of the actuator  40 . The leaf spring  120  is configured and arranged having a pair of laterally extending arms  120  having terminal ends  122  that engage with a pair of receiving or bearing surfaces  102  of the plate(s)  100 . 
     As shown in  FIGS. 12G, 12H  the ends  122  of the spring  120  engage with the plates at about the area of the bend in the plates  100  that forms the flange. When the arms  120  of the springs are compressed, the ends  122  of the arms exert an upstream directed spring force  128  against the plates  100  that urges the upstream facing surfaces  130  of the plates  100  into heat conductive engagement with the downstream facing surface  140  of the top clamp plate. 
     In such an alternative embodiment, heat that is conducted to the body of the actuator  940  from the heated manifold  40  is re-routed or conducted to the side portions  104  of the plates  100  via heat conductive engagement of the inside surfaces  104   i  of the sides  104  with the outside surfaces  43  of the actuator  940 . Such heat that is conducted to the side portions  104  is in turn conducted to the top portions  106  which is in turn conducted to the body of the clamp plate  20  via the spring-loaded  128  heat conductive contact between the top surface  130  of the top portions  106  with the surface  140  of the top clamp plate  20 . 
     As shown in  FIGS. 12G, 12H  the body of the actuator  940  is mounted directly on and in heat conductive engagement or contact with the cooling block  940   mc . The actuator  940  in combination with the cooling plates  100  and cooling device is mounted and secured via bolts  62  onto the upstream facing surface  57  of the heated manifold  40 . As shown the actuator  940  and associated components have a certain height AH that they extend upstream from the surface  57 . Once the actuator  40  together with its accompanying plates  100  and spring  120  has been mounted in the position shown in  FIGS. 12F, 12G  on cooling device  30  and surface  57 , the rest of the system is assembled such that the clamp plate  20  is mounted a spaced distance S upstream of the heated manifold  50 . The mounting height AH of the assembly of the actuator  40 , plates  100 , and cooling device  30  and the depth CH of the receiving aperture CA in the clamp plate  20  are preselected so that when the components of the system including the clamp plate  20  and manifold  50  are assembled and connected together with the mold  500 , the upstream facing surface  130  of the plates  100  engage the downstream facing surface  140  of the clamp plate  20  under compression created by compression of springs  120  resulting in the spring force  128  urging surface  130  in an upstream direction into compressed engagement with surface  140 . 
     When the system is assembled as described with the upstream surface  130  of the plates engaging the downstream surface  140  of the clamp plate under compression  128 , the inside surfaces  104   i  of the plates  100  are free to slide upstream and downstream UD against the outside surface  43  of the actuator  40 , the plates themselves being free to slide upstream and downstream UD to accommodate any changes in the distance AH that can or may occur as a result of expansion or contraction of the length, width or depth of the manifold  50 , plates  30 ,  60  or  20  or the actuator body  40  or other components of the system when the assembled system is raised to elevated operating temperature or lowered from operating temperature to room temperature. 
     As shown in  FIGS. 12G, 12H  the system is adapted and arranged so that when assembled, the clamp plate  20  is thermally isolated from the heated manifold by an insulating space S by which the clamp plate is spaced apart from the manifold  40 . The insulating space S results from the pre-selection of the actuator height AH relative to the cavity height CH where the spring force  128  occurs on assembly of the clamp plate  20  together with the mold  500  and manifold  50 . Typically, the clamp plate  20  is isolated from and mounted to either or both the mold  500  and manifold  50  such that the clamp plate  20  is maintained in a thermally isolated position relative to the manifold  50  spaced by S, the clamp plate having little to no direct thermally conductive contact with the manifold  50  other than incidentally through a less than about 2 inch square area of contact that may exist between a spacer  48  or other component and the clamp plate  20 , the spacer  48  being in similar conductive contact with the manifold  50 . The spacer  48  is disposed between the clamp plate  20  and the manifold  50  for purposes of ensuring the proper positioning of the manifold  50  relative to the clamp plate  20 . The clamp plate  20  may alternatively be mounted to the mold  500  without conductive contact with the manifold  50  such that insulating space S is maintained. 
     The clamp plate  20  is typically cooled with a cooling fluid disposed and flowing through cooling channels  25  in the body of the clamp plate  20 . Thus, thermally conductive direct contact between the slidable plates  100  and the clamp plate  20  enable heat to transfer from the body of the actuator  40  to the clamp plate, the heat being readily dissipated by the cooled clamp plate  20 . 
     As shown in  FIGS. 12G, 12H  the downstream facing surfaces  60   a  of a downstream mount  60  for the cooling device  940   mc  are mounted in compressed metal to metal contact with the top surface  57  of the manifold  40  when the system is fully assembled. The cooling block  940   mc  is proactively cooled with water pumped through cooling channels  33  during active operation of the entire apparatus. During operation of the apparatus, the cooled cooling block  940   mc  serves to maintain the actuator  40  cool and/or relatively insulated from the heated manifold  40 . In the embodiment shown, the cooling block  940   mc  is mounted on an intermediate mount  60  which itself is mounted in engagement contact with the body or upstream facing surface  57  of the heated manifold  50  via bolts  62 . Heat from the heated manifold  50  is thus thermally conducted or transferred to the actuator  40  through the bolts  62 , mount  60  and block  30 . 
     In all embodiments of the invention, the mold  500  is preferably also thermally isolated from the manifold, there being on incidental contact between certain components such as an injection nozzle with both the manifold and the mold. 
       FIG. 15  shows an embodiment where electric actuators with electric drive  940   d  are mounted in an extended spaced apart relationship relative to the heated manifold such that the actuator and electric drive  940   d  are isolated or insulated from significant heat communication with the heated manifold  40 . In the embodiment shown the actuator and electric drive are mounted to a cool or cooled top clamp plate and are interconnected to a rotary to linear drive converter device, the linear drive converter device also being mounted to the top clamp plate. 
       FIG. 16  shows another embodiment where electric actuators  200  with electric drive  940   d  are mounted in an extended spaced apart relationship relative to the heated manifold such that the actuator and electric drive  940   d  are isolated or insulated from substantial or significant heat communication with the heated manifold  40 . In the embodiment shown the actuator and electric drive are mounted to a cool or cooled top clamp plate  80  and are interconnected to a rotary to linear drive converter device, the linear drive converter device also being mounted to the top clamp plate. As shown in  FIG. 16 , the electrically powered actuator  200  is mounted on side surface  140   ss  of the top clamp plate  140  and the elongated shaft  20  and converter  15  are mounted within apertures or channels  140   us ,  140   uc  formed on the interior or underside of the top clamp plate. Again, the top clamp plate  80  is typically cooled via water that flows through cooling channels  145  bored within the top clamp plate  80 . In the  FIG. 16  embodiment, the converter  15  is mounted to the heated manifold  40  via bolts  58  and springs  56 . The bolts  58  cause the converter housing  9401   h  and its interconnected valve pin  100   to  travel radially R together with radial expansion or travel of the heated manifold thus minimizing the necessity for prevention of pin decoupling or pin deformation due to radial expansion of the heated manifold  40 . The springs  56  are resiliently compressibly engaged between an upstream surface  60   u  of the manifold  60  and a downstream surface  40   hd  of the housing  9401   h  to cause an upstream facing heat conductive surface  40   s  of the housing  40  to compressibly engage with a downstream facing heat conductive surface  140   s  of the cooled top clamp plate  80  thus working to cause heat from the manifold  40  that is transmitted to housing  9401   h  to be transmitted from housing  9401   h  to the cooled top clamp plate  80  thus cooling the converter housing  940   h  and the converter components  40   c  generally. 
       FIG. 17  shows a conventional prior art pneumatically (or hydraulically) driven apparatus  10  with a central nozzle  22  feeding molten material  18  from an injection molding machine IMM through a main inlet  18   a  to a distribution channel  19  of a manifold  40 . The IMM typically comprises a barrel (not shown) and a controllably rotatably drivable or driven screw BS that initiates and ends an injection cycle at selected points in time when the screw BS is rotatably driven to generate flow of injection fluid  18 . The beginning of an injection cycle is typically defined at a selected point in time when the screw BS is initially rotated from a standstill position or at a time that occurs shortly after the time when the screw BS is initially begun rotating. The end of the cycle is typically defined by a time at which the screw BS is stopped from rotating following and after the selected time that defines the beginning of the cycle when the screw BS is drivably rotated. The distribution channel  19  commonly feeds three separate nozzles  20 ,  22 ,  24  which all commonly feed into a common cavity  30  of a mold  33 . One of the nozzles  22  is controlled by fluid driven actuator  940   f  and arranged so as to feed into cavity  30  at an entrance point or gate that is disposed at about the center  32  of the cavity. As shown, a pair of lateral nozzles  20 ,  24  feed into the cavity  30  at gate locations that are distal  34 ,  36  to the center gate feed position  32 . 
     As shown in  FIGS. 17 and 18  the injection cycle using apparatuses according to the present invention are most preferably a cascade process as described in U.S. Pat. No. 1,056,945, the disclosure of which is incorporated by reference as if fully set forth herein, where injection is effected or initiated in a sequence from the center nozzle  22  first and at a later predetermined time from the lateral nozzles  20 ,  24 . 
     As described for example in U.S. Pat. No. 1,056,945, the injection cycle is started by first opening the pin  1040  of the center nozzle  22  and allowing the fluid material  100  (typically polymer or plastic material) to flow up to a position the cavity just before the distally disposed entrance into the cavity  34 ,  36  of the gates of the lateral nozzles  24 . After an injection cycle is begun, the gate of the center injection nozzle  22  and pin  1040  is typically left open only for so long as to allow the fluid material to travel to a position just past the positions at which the downstream gates  34 ,  36  are located. Once the fluid material has travelled just past the lateral or downstream gate positions  34 ,  36 , the center gate  32  of the center nozzle  22  is typically closed by pin  1040 . The lateral or downstream gates  34 ,  36  are then opened by upstream withdrawal of lateral nozzle pins  1041 ,  1042 . The rate of upstream withdrawal or travel velocity of lateral pins  1041 ,  1042  is typically carried out such that one or both of the downstream pins  1041 ,  1042  are first withdrawn upstream over some portion of the full upstream withdrawal path of the pins  1041 ,  1042  at a first relatively slow speed or velocity and subsequently at a higher speed as described in detail in U.S. Pat. No. 9,011,736, the disclosure of which is incorporated by reference as if fully set forth herein. The center gate  32  and associated actuator  940   f  and valve pin  1040  can remain open at, during and subsequent to the times that the lateral or downstream gates  34 ,  36  are opened such that fluid material flows into cavity  30  through both the center gate  32  and one or both of the lateral gates  34 ,  36  simultaneously. When the lateral or downstream gates  34 ,  36  are opened and fluid material is allowed to first enter the mold cavity into the stream that has been injected from center nozzle  22  past gates  34 ,  36 , the two streams mix with each other. If the velocity of the fluid material is too high, such as often occurs when the flow velocity of injection fluid material through gates  34 ,  36  is at maximum, a visible line or defect in the mixing of the two streams will appear in the final cooled molded product at the areas where gates  34 ,  36  inject into the mold cavity. By injecting fluid at a reduced flow rate for a relatively short period of time at the beginning when a downstream gate  34 ,  36  is first opened and following the time when fluid first enters the first downstream flowing stream, the appearance of a visible line or defect in the final molded product can be reduced or eliminated. 
     The rate or velocity of upstream and downstream travel of pins  1041 ,  1042  starting from either the gate closed position or the fully open upstream position is controlled via an actuator controller  16  which controls the rate and direction of flow of pneumatic or hydraulic fluid from the drive system  14  to the actuators  940   f ,  941   f ,  942   f . A predetermined profile of valve pin or actuator positions versus elapsed time can be input into the actuator controller  16  as the basis for controlling upstream and downstream travel of the valve pin(s)  1041  et al. at one or more selected velocities over the course of travel of the valve pin through the stroke length either upstream or downstream. For example the actuator controller  16  can include instructions that instruct the actuators to move at a reduced velocity relative to one or more selected higher velocities of withdrawal. The higher velocity is typically selected to be the highest velocity at which the system is capable of driving the actuators. Typically, the instructions instruct the actuators to move the valve pins upstream from the gate closed position at a reduced velocity over the course of travel where the tip end of the valve pin restricts the flow of injection fluid  18  to less than the flow would otherwise be if the valve pin were disposed fully upstream, the restriction occurring as a result of the tip end of the valve pin restricting the size of the flow path or opening at or near the gate  32 ,  34 ,  36  to a size that is less than the size of the opening or flow path would otherwise be if the valve pin were disposed fully upstream of the gate  32 ,  34 ,  36 . 
     In the  FIG. 17  prior system, the actuator controller  16  typically receives a signal in real time from a pressure sensor  603  (or  605 ,  607 ) disposed in the drive fluid line communicating with the exit of the metering valve  600 , the signal being indicative of the reduced drive fluid pressure in line  703  (or  705 ,  707 ). In a system where an electric motor apparatus is used in conjunction with an apparatus according to the invention, the actuator controller  16  typically receives a signal in real time indicative of the position of the actuator or the valve pin  1041 ,  1042 . The actuator controller  16  instructs the valve  600  or the electric actuator  941   e ,  942   e  to move according to a predetermined profile of drive pressures or electric actuator or valve pin positions that effect the initial slow and subsequent fast moving valve pin velocity protocols described herein. 
     As shown in the apparatus of  FIG. 17  the injection molding machine IMM includes its own internal manufacturer supplied machine controller that generates standardized beginning of cycle gate closed and end of cycle gate open and gate closed machine voltage signals VS typically 0 volts for gate open and 24 volts for gate open (or 0 volts and 120 volts respectively). The standardized machine voltage signals VS are typically sent either directly to the solenoids of a master directional control valve  12  (that controls the direction of flow of actuator drive fluid into or out of the drive chambers of all of the plurality of fluid driven actuators  940   f ,  941   f ,  942   f ) to cause the directional control valve  12  (DCV) to move to a gate closed or gate open actuator drive fluid flow position. Or, the same standardized voltage signals VSC can be sent to the directional control valve  12  via the actuator controller  16  which generates the same standardized voltage signals VSC as the VS signals in response to receipt from a screw position sensor SPSR of a machine screw position signal SPS sent by the injection molding machine IMM to the actuator controller  16 , the actuator controller  16  thus generating the same beginning of cycle and end of cycle control voltage signals VSC as the machine IMM can otherwise generate and send VS directly to the directional control valve  12 . Thus, where conventional standardized directional control valves  12  are used, the sending of start of cycle and end of cycle signals can be simplified via electrical or electronic signal connections directly to the internal signal generator or controller contained within the injection molding machine. 
     Electrically powered actuators or electric motors and proportional directional control valves cannot directly receive and utilize a standardized 0 volt (gate closed), 24 volt (gate open) or 0 volt (gate closed) 120 volt (gate open) signals generated by the start and stop cycle controller or signal generator that is typically included in a conventional injection molding machine. 
     As shown in a generic schematic form in  FIG. 19 , an apparatus  10  according to the invention incorporates a signal converter  1500  that can receives standardized injection machine generated start of cycle and end of cycle signals VS (such as 0 volts, 24 volts or 120 volts) and converts the received standardized signal VS to an output power signal MOCPS or PDCVS that is compatible for receipt and use by an electric motor or a proportional direction control valve power signal. The two different actuator based systems, namely electric motor and proportional directional control valve, are shown together in the generic  FIG. 11  for illustration purposes only. More typically, a practical implementation of a system as shown in  FIG. 11  would be such that the converter  1500  would contain a single microcontroller and an interconnected driver that is configured to work with one or the other of an electric actuator based system or a proportional directional control valve system. 
       FIG. 18  shows an electric actuator based apparatus in simplified schematic form. As shown in  FIG. 1 , electric actuators  940   e ,  941   e ,  942   e  each have a rotating rotor  940   r ,  941   r ,  942   r  that is driven by electrical power (typically delivered via the converter  1500 ) one or more of the precise polarity, amplitude, voltage and strength of which is controlled for input to the motors by actuator controller  16  and the program contained in the actuator controller  16 . The rotating rotors  940   r ,  941   r ,  942   r  are interconnected to a translationally movable shaft or other suitable connecting devices  940   c ,  941   c ,  942   c  that interconnect the valve pins  1040 ,  1041 ,  1042  to the driven rotors  940   r ,  941   r ,  942   r . A typical interconnection between a shaft driven by a rotor and the head of a valve pin is shown in U.S. Reexamination Certificate 6,294,122 C1 and U.S. Pat. No. 9,492,960 the disclosures of which are incorporated herein by reference in their entirety as if fully set forth herein. 
       FIG. 18  illustrates an example of an apparatus  10  according to the invention having a plurality of electric power driven actuators  940   e ,  941   e ,  942   e , with a central nozzle  22  feeding molten material  18  from an injection molding machine IMM through a main inlet  18   a  from a barrel of the injection molding machine IMM to a distribution channel  19  of a manifold  40 . As in the conventional apparatus of  FIG. 1  in the  FIGS. 2, 3  apparatuss the IMM typically comprises a barrel (not shown) and a controllably rotatably drivable or driven screw BS disposed within the barrel to generate a pressurized supply of injection fluid  18  the pressure of which can be detected by a barrel pressure sensor BPSR which can send a signal indicative of barrel pressure to a controller  16  for use in controlling positioning and velocity of the valve pin  1040 ,  1041 ,  1042 . The screw BS of the IMM initiates and ends an injection cycle at selected points in time when rotation of the screw BS is started and stopped. The beginning of an injection cycle is typically defined at a first selected point in time when the screw BS is initially rotated from a standstill position or at a time that occurs shortly after the time when the screw is initially rotated. The end of the cycle is typically defined by a selected second time following and after the first selected time at which second time the screw is stopped from rotating and injection fluid  18  is stopped from being injected into the heated manifold  40 . 
     The distribution channel  19  commonly feeds three separate nozzles  20 ,  22 ,  24  which all commonly feed into a common cavity  30  of a mold  33 . One of the nozzles  22  is controlled by an electric motor actuator  940   e  and arranged so as to feed into cavity  30  at an entrance point or gate that is disposed at about the center  32  of the cavity. As shown, a pair of lateral nozzles  20 ,  24  feed into the cavity  30  at gate locations that are distal  34 ,  36  to the center gate feed position  32 . 
     As with the apparatus of  FIG. 17 , an injection cycle using the apparatuses of  FIGS. 18, 19  typically are used to carry out a cascade or sequential valve gate process where injection is effected in a sequence from the center nozzle  22  first and at later predetermined times from the lateral nozzles  20 ,  24 . The cascade process is discussed in detail as an example only, the invention encompassing configurations and protocols where a single valve pin and valve gate inject into a single cavity. 
     Also as with the  FIG. 17  apparatus, the  FIGS. 18,19  apparatuses  10  include an actuator controller  16  that typically includes a program that converts a standard voltage signal (such as 0V, 24V, 120V) received from an injection machine controller MC into an instruction signal IS that is compatible with, receivable and interpretable by a motor driver MD to cause the motor driver MD to generate a motor operating control power signal MOCPS that signals the start of an injection cycle and the end of injection cycle, the start typically being a power signal that drives the motor to withdraw the valve pin  1040 ,  1041 ,  1042  from a gate closed position and the end being a power signal that drives the motor to drive the valve pin from an upstream position to a gate closed position. The controller  16  can include a program with instructions that can move and drive the valve pin to and along any predetermined position or velocity profile including at reduced velocities as described above. Reduced velocity in the case of the  FIG. 2  apparatus means a velocity that is less than the maximum velocity at which the electric actuator is capable of driving the pin, typically less than about 75% of maximum and more typically less than about 50% of maximum velocity whether upstream or downstream. 
     The actuator controller  16  typically includes additional instructions that can instruct a valve pin  1041 ,  1042 ,  1040  to be driven either upstream or downstream starting from either a fully closed downstream or a fully upstream, gate open position at one or more reduced upstream or reduced downstream velocities over at least the beginning portion of the upstream path of travel of the valve pins  1040 ,  1041 ,  1042  or the latter portion of the downstream path of travel of the valve pins toward the gates  32 ,  34 ,  36  where the tip end  1142  of the pin  1041  restricts flow of the injection fluid through the gate such as shown and described in U.S. Pat. No. 10,569,458. 
     In one embodiment, an electric actuator  940   e ,  941   e ,  942   e  is drivably interconnected to a valve pin  1040 ,  1041 ,  1042  in an arrangement wherein the electric motor drives the valve pin along the axis A of the valve pin and drives the tip end of the valve pin between a first position where the tip end of the valve pin obstructs the gate  34  to prevent the injection fluid from flowing into the cavity, a second position upstream of the first position wherein the tip end of the valve pin restricts flow  1153  of the injection fluid along at least a portion of the length of the drive path extending between the first position and the second position, and a third maximum upstream position where the injection fluid material flows freely without restriction from the tip end of the pin. 
     The electric motor  940   e ,  941   e ,  942   e  can be configured and arranged relative to its associated valve pin  1040 ,  1041 ,  1042  such as shown in  FIG. 3  such that the driven rotor  940   r ,  941   r ,  942   r  and shaft components of the motor are axially aligned with the axis A of the valve pin  1040 ,  1041 . Alternatively, a motor configuration can be used such as in U.S. Pat. No. 9,492,960 and  FIGS. 2, 4, 5, 6  where the driven rotor and shaft components are arranged at an angle to the axis A, X  FIGS. 2, 4, 5, 6  of the valve pin  1040 ,  1041 ,  1042 . 
     In an embodiment such as shown in  FIG. 18  an injection cycle can be started by first opening the pin  1040  of the center nozzle  22 , and allowing the fluid material  100   a  (typically polymer or plastic material) to flow up to a position the cavity just before  100   b  the distally disposed entrance into the cavity  34 ,  36  of the gates of the lateral nozzles  24 ,  20 . After an injection cycle is begun, the gate of the center injection nozzle  22  and pin  1040  is typically left open only for so long as to allow the fluid material  100   b  to travel to a position just past  100   p  the positions  34 ,  36 . Once the fluid material has travelled just past  100   p  the lateral gate positions  34 ,  36 , the center gate  32  of the center nozzle  22  is typically closed by pin  1040  at some predetermined time during the injection cycle. The lateral gates  34 ,  36  are then opened by upstream withdrawal of lateral nozzle pins  1041 ,  1042 . 
     In alternative embodiments, the center gate  32  and associated actuator  940   e , and valve pin  1040  can remain open at, during and subsequent to the times that the lateral gates  34 ,  36  are opened such that fluid material flows into cavity  30  through both the center gate  32  and one or both of the lateral gates  34 ,  36  simultaneously. When the lateral gates  34 ,  36  are opened and fluid material  100   a  is allowed to first enter the mold cavity into the stream that has been injected from center nozzle  22  past gates  34 ,  36 , the two streams mix with each other. If the velocity of the fluid material is too high, such as often occurs when the flow velocity of injection fluid material through gates  34 ,  36  is at maximum, a visible line or defect in the mixing of the two streams will appear in the final cooled molded product at the areas where gates  34 ,  36  inject into the mold cavity. By injecting from a downstream gate  34 ,  36  at a reduced flow rate for a relatively short period of time at the beginning when the gate  34 ,  36  is first opened and following the time when fluid first enters the flow stream  100   a , the appearance of a visible line or defect in the final molded product can be reduced or eliminated. 
     A signal converter  1500 ,  FIGS. 18, 19  is provided that enables a user to connect the standardized voltage signal output (VS, VSC) of a conventional IMM controller to the input of the electric motors  940   e ,  941   e ,  942   e ,  FIGS. 2, 3, 4, 5, 6, 10, 11, 12  in the same manner that the user interconnected an IMM controller in a conventional apparatus as in  FIG. 1  to DCVs. The signal converter  1500  receives and converts received IMM voltage signals (such as 0 volts, 24 volts, 120 volts) to control signals (MOCPS or PDCVS that operate to begin cycle and end cycle). As shown in  FIGS. 10, 11, 12  the standardized voltage signals VS can be alternatively generated by an HPU (hydraulic power unit) that is physically separate but interconnected to the machine controller MC, the HPU unit,  FIGS. 10, 11, 12  receiving a barrel screw position signal SPS from the machine controller and generating therefrom a corresponding standardized VS signal that is in turn sent to the controller  16  for conversion to an instruction signal IS usable by either a motor driver MD, or by a proportional directional valve driver HVD, PVD, to drive either a motor or a proportional directional valve to initiate and end an injection cycle. 
     Thus the standard start and stop control signals generated by an IMM (VS, VSC) can operate in conjunction with the converter  1500  to instruct either the electric actuators,  940   e ,  941   e ,  942   e  or the fluid driven actuators  940   p ,  941   p ,  942   p , to at least initiate or begin an injection cycle (such as by instructing the actuators  940   e ,  941   e ,  942   e ,  940   p ,  941   p ,  942   p  to drive a valve pin upstream from a gate closed position) and to end or stop an injection cycle (such as by instructing the actuators  940   e ,  941   e ,  942   e ,  940   p ,  941   p ,  942   p  to drive a valve pin downstream from a gate open position into a gate closed position). 
     Most preferably the physical or mechanical electric signal connectors that are typically used to connect a wire or cable from the IMM (or machine controller MC) to the signal conversion device  1500 , are the same physical or mechanical connectors that are used in conventional apparatuses to connect the IMM (or machine controller MC) to the DCVs of a conventional apparatus as described with reference to  FIG. 10 . 
     As shown in  FIGS. 18, 19, 20  the signal output VS of the IMM can be connected directly to signal converter  1500  which converts the VS signal into a motor open close power signal MOPCS or a proportional directional control valve signal PDCVS that is compatible with and processable by the motors  940   e ,  941   e ,  942   e  or the proportional directional control valves V, V 1 , V 2 . Alternatively, the signal output of the IMM of the machine controller MC of the  FIGS. 10, 11, 12  embodiment can comprise a barrel screw position signal SPS that is sent to an intermediate HPU unit by a screw position sensor SPSR. 
     The MOCPS and PDCVS signals include signals that correspond to the VS signals that operate to affect the beginning and end of an injection cycle. 
     Typically the  FIG. 18  apparatus  10  includes one or more position sensors,  950 ,  951 ,  952  or other sensors, SN, SC that detect a selected condition of the injection fluid  18  in one or more of the manifold fluid flow channel  19 , a nozzle flow channel  42 ,  44 ,  46  or in the cavity  30  of the mold  33 . 
     The actuator controller  16  can include a program that receives and processes a real time signal indicative of a condition of the injection fluid  18  or a component of the apparatus ( 10 ) such as rotational position of a rotor  940   r ,  941   r ,  942   r  or axial linear position of a valve pin  1040 ,  1041 ,  1042 . The real time signals sent to and received by the actuator controller  16  are generated by one or more of position sensors  950 ,  951 ,  952  or fluid condition sensors SN, SC. The sensors detect and send a signal to the actuator controller that is typically indicative of one or more of rotational position (sensors  950 ,  951 ,  952 ) of a rotor  940   r ,  941   r ,  942   r  or of linear axial position of a valve pin  1040 ,  1041 ,  1042 . The fluid condition sensors typically comprise one or more of a pressure or temperature sensor SN that senses injection fluid  18  within a manifold channel  19  or a nozzle channel  42 ,  44 ,  46  or senses pressure or temperature of the injection fluid SC within the cavity  30  of the mold  33 . 
     The actuator controller  16  can include a program that processes the received signal(s) from one or more of the sensors  950 ,  951 ,  952 , SN, SC according to a set of instructions that use the received signals as a variable input or other basis for controlling one or more of the position or velocity of the actuators  940   e ,  941   e ,  942   e  or their associated valve pins  1040 ,  1041 ,  1042  throughout all or selected portion of the duration of an injection cycle or all or a portion of the length of the upstream or downstream stroke of the actuators  940   e ,  941   e ,  942   e.    
     As shown the controller  16  can be included within and comprise a component of the converter  1500 ,  FIGS. 10, 11, 12 . Where the converter  1500  includes a controller  16  that includes position and velocity control instructions, the converter  1500  can thus send its machine open close power signals MOCPS (or valve open close signals PDCVS) together with position velocity signals (PVS) to either the electric actuators  940   e ,  941   e ,  942   e  or proportional directional control valves V, V 1 , V 2 . The control signals MOCPS and PDCVS thus include a signal that has been converted from and corresponds to one or the other of the converted VS signals received by the converter  1500  from the IMM controller MC or the HPU. The position or velocity control signals PVS can control the position or velocity of the valve pin according to any predetermined profile of pin position or velocity versus time of injection cycle. The form, format, intensity and frequency of the MOCPS, PDCVS and PVS signals are compatible with the signal receiving interface of the electric actuators  940   e ,  941   e ,  942   e  or valves V, V 1 , V 2 . 
     In the embodiment shown in  FIGS. 2A, 2B, 2BB, 2C, 2D, 2E , the controllably rotatable shaft of the electric actuator  940  is interconnected downstream to a rotational speed reducing device  46 . In the specific embodiment shown, the speed reducing device  46  comprises a strain wave gear that is in turn interconnected to an eccentric pin drive mechanism  9401  that converts rotational motion to linear motion of the valve pin  1040 . In such an embodiment, the valve pin  1040  can be interconnected to or interengaged with a cam member  600  that is driven eccentrically around an output rotation axis such as the axis  12   a  of the motor rotor or the axis R 3  of the speed reducing, torque increasing device  46 . The eccentricity of the cam member  600  enables variable speed and higher torque control over the linear drive movement of the pin  1040  along linear axis A. 
     In the embodiments of  FIGS. 1B, 21A, 14A , the motor rotor axis is coaxial with the valve pin axis and thus the actuator housing ( 940   h ,  941   h ,  942   h ) is mounted on, to and in direct heat communicative contact with the cooling device ( 940   mc ) via heat insulative mounts ( 60 ). The mounts ( 60 ) can be adapted to form a heat insulative gap (G′) between the cooling device and one or the other or both of the housing ( 940   h ) and the electric drive ( 940   d ). 
     Similarly as shown for example in the embodiments of  FIGS. 2A through 2F  where the motor rotor axis (Y) is arranged non coaxial relative to the axis (X) of travel of the valve pin ( 1040 ), the mounts ( 60 ) can be adapted to form a gap (G′) between the cooling device ( 940   mc ) and the rotary to linear converter ( 9401 ,  9411 ,  940   h ,  9411   h ). In these embodiments, by virtue of the intermediate interconnection of the rotary to linear converter ( 9401 ,  9411 ,  940   h ,  9411   h ) between the actuator housing ( 940   h ) and mounting of the actuator housing ( 940   h ) and electric drive ( 940   d ) on or to the cooling device ( 940   mc ) via mounting of the rotary to linear converter ( 940   l ,  9401   h ) on or to the cooling device ( 940   mc ), the mounts ( 60 ) also effectively form a heat insulative gap (G′),  FIG. 2BB , between the cooling device ( 940   mc ) and one or the other or both of the housing ( 940   h ) and the electric drive ( 940   d ) as well as the rotary to linear converter ( 940   l ,  940   lh ,  9411 ,  941   lh ). 
     The specific strain wave gear and downstream eccentric rotary to linear drive mechanism of  FIG. 2A  et seq. is described in detail in U.S. international application publication WO2019/100085 A1, the disclosure of which is incorporated by reference in its entirety as if fully set forth herein. 
     As shown in  FIG. 2D , the converter  15  can comprise a mount or alignment support  40   a  and a sled or slide  43  to which is interconnected a valve pin  100 . The alignment support  40   a  has a guide surface  40   as  against which a complementary surface  43   s  of the sled or slide  43  slides as the sled  43  is driven reciprocally along a linear path A by the eccentric drive components that include the cam member  47 . The sled  43  has freely rotatably wheels  43   r  that facilitate upstream downstream sliding of the sled along surface  40   as . In an alternative embodiment, wheels  43   r  are not necessary and the lateral surface  43   s  can be adapted to slide directly against surface  40   as  without wheels. The alignment support  40   a  is attached to a rotation speed reducer  46 . The converter  15  is mounted as shown to the heated manifold  60 . 
     The converter  15  includes a drive or mounting wheel or disc  500  having a rotational center  500   c  to which is axially attached or interconnected the rotatable drive shaft  12  of the actuator  940  either directly or indirectly via rotatably interconnected elongated shaft  20 ,  20   f  or a connector shaft such as a splined shaft  42   s . The electrically powered rotatably driven rotor or drive shaft  12  of the motor is rotatably interconnected to the center  500   c  of the drive wheel or disc  500  of the rotary to linear converter  15  mechanism. An eccentrically mounted cam member  600 , typically a freely rotatable disc or wheel, is mounted to the rotatably driven disc or wheel  500  a selected eccentric off center distance ED from the rotational center  500   c  of the driven wheel or disc  500 . 
     The electrically powered drive of the motor rotor  12  drivably rotates R 3  the drive wheel  500  at a controllably selectable speed and direction. As shown, the drive wheel  500  of the converter  15  is rotatably driven, the eccentrically mounted cam member  600  rotates R 3  around the center  500   c  of the drive wheel  500 . As shown, the converter  15  includes a slide or sled  43  that is provided with a cam slot  43   sl  that is attached to the support  40   a  in an arrangement such that an outside circumferential surface  600   cs , of the cam member  600  engages a complementary interior cam surface  43   ss  of the slide or sled  43  member. The cam surface  43   ss  of the slide  43  is configured and adapted relative to the diameter D of the cam member  600  and the eccentric distance ED to enable the outside surface  600   cs  of the cam member  600  to forcibly engage the interior surface  43   ss  of the slide  43  and thus cause the slide  43  to be forcibly driven in a linear direction up and down or back and forth in or along a linear direction or axis A,  FIGS. 5-9  as the cam member  600  is eccentrically drivably rotated R 3  around the center of driven disc or wheel member  500 . As shown, valve pin  100  is fixedly attached to the driven slide or sled member  43  in an arrangement such that the valve pin  100  is linearly driven together with the linear movement A of the slide  43 . 
     Because of the eccentric mounting of the cam member  600 , the linear or axial speed, A 31 , A 32 , A 33  of the valve pin  1040  and sled  43  along the linear path A varies A 31 , A 32 , A 33  according to the rotational or angular position of the cam member  600  during the course of a constant rotational speed R 3 . The linear or axial speed A 32  is at a maximum when the cam member  600  is at the ninety degree rotational position and at a lesser speed when the cam member  600  is at the  45  degree position and the 135 degree rotational position. 
     Conversely because of the eccentric mounting of the cam member  600 , the torque force, exerted by the eccentric cam  600  on the valve pin  1040  and sled  43  along the linear path A varies according to the rotational or angular position of the cam member  600  the rotational speed R 3  is constant. The torque force is at a minimum when the cam member  600  is disposed at the ninety degree rotational position and at a higher torque when the cam member  600  is at the 45 degree position and the 135 degree rotational position. 
     The absolute highest torque position is a position where the cam is disposed in the absolute maximum moment position which is typically the 0 degree position, or the 180 degree position. 
     Rotation of the cam member  600  can be limited to travelling through an arc segment that is something less than the full 360 degrees that the shaft or output device would otherwise rotate, such as between 70 degrees above and below the 90 and 270 degree positions, most preferably between 40 degrees above and below the 90 and 270 degree positions. 
     The cam device ( 600 ) is eccentrically disposed or mounted off center a selected distance (ED, R) from the output rotation axis ( 12   a , R 3   a ) in an arrangement such that when the shaft ( 12 ) or rotation device ( 16 ,  430 ,  500 ) is rotatably driven, the cam member ( 600 ) is eccentrically rotatably drivable around the output rotation axis ( 12   a , R 3   a ) to selectable angular positions above and below either a 270 degree position or a 90 degree position,  FIGS. 6A, 6B, 6C . 
     In such a preferred embodiment, a controller ( 1000 ),  FIGS. 1, 6A, 11  is interconnected to the shaft ( 12 ) or output rotation device ( 16 ,  430 ,  500 ), the controller ( 1000 ) can include an algorithm that controllably limits rotation of the shaft ( 12 ) or output rotation device ( 16 ,  430 ,  500 ) during the course of an entire injection cycle to angular positions between about 70 degrees above and 70 degrees below the 270 degree position, or between about 70 degrees above and 70 degrees below the 90 degree position. A preselected angular position between the 270 or 90 degree position and 70 degrees above defines a fully open valve pin position (PFO) and a preselected angular position between the 270 or 90 degree position and 70 degrees below defines a valve pin position where the gate is closed (PFC). 
     As shown a slide, sled or linear travel device ( 43 ,  40 ,) is adapted to guide the valve pin along a linear path of travel (A, AS). The rotary to linear converter device ( 40 ,  43 ) can include stops or linear travel limiters (not shown) that are fixed to the alignment supports  40   a  of the rotary to linear converter  15  or otherwise fixedly attached relative to the sled  43 . The stops are typically mounted and adapted to limit linear travel of the slide or sled  43  such that when the cam member  600  is rotated to a preselected maximum angular position 70 degrees or less above or below the 270 (or 90) degree position, travel of the cam  600  and the valve pin is stopped. Typically, such preselected maximum angular positions above and below the 270 or 90 degree positions are selected so as to define a corresponding preselected valve fully open position (PFO) and a corresponding valve fully closed position (PFC). 
     The algorithm can controllably limit rotation of the shaft ( 12 ) or output rotation device ( 16 ,  430 ,  500 ) during the course of an entire injection cycle to angular positions between about 40 degrees above and 40 degrees below the 270 degree position or between about 40 degrees above and 40 degrees below the 90 degree position wherein a preselected angular position between 40 degrees above the 270 or 90 degree position defines the fully open valve pin position (PFO) and a preselected angular position  40  below the 270 or 90 degree position defines the valve pin position where the gate is closed (PFC). 
     An alternative manner of describing how rotation of the cam  600  is limited is that the algorithm of the controller  16 , 1000 limits rotation of the shaft ( 12 ) or output rotation device ( 16 ,  430 ,  500 ) to selectable angular positions that create a moment arm M that extends between a selected minimum moment arm M 2 , and a selected maximum moment arm, M 1 , the selectable angular positions being between 70 degrees above and 70 degrees below the preselected angular position (270 degrees) that corresponds to the selected maximum moment arm M 1 . Typically the absolute maximum moment arm M 1  exists when the rotational or angular position of the cam  600  is disposed at 270 degrees or 90 degrees, although other angular positions could be preselected to define or correspond to the absolute maximum moment arm position. 
     As shown the driven wheel or disc component  500  is typically mounted on the forward face  500   m  of the driven rotating disc or wheel component  700  of a speed reducing device  46  which is reduced in rotational speed relative to the rotational speed of the rotor or drive shaft  12  of the actuator  200 . 
     The rotational speed reducing device  46  can comprise a strain wave gear that includes a rotatable elliptical or other non circular shaped such as a three node containing shaped disk or ring that generates a reduction in rotation speed output relative to the rotation speed of the input rotor. The strain wave gear is typically comprised of three basic components: a wave generator, a flex spline and a circular spline. The wave generator is typically made up of an elliptical or other non circular shaped such as a three node containing shaped disk called a wave generator plug and an outer ball bearing, the outer bearing having an elliptical or other non circular shaped such as a three node containing shape as well. The flex spline is typically shaped like a shallow cup. The circumferential side walls of the spline are very thin, but the bottom is relatively rigid. This results in significant flexibility of the walls at the open end due to the thin wall, and in the closed side being quite rigid and able to be tightly secured to an output shaft. Teeth are positioned radially around the outside of the flex spline. The flex spline fits tightly over the wave generator, so that when the wave generator plug is rotated, the flex spline deforms to the shape of a rotating ellipse or other non circular shape such as a three node containing shape and does not slip over the outer elliptical or other non circular shaped such as a three node containing shaped ring of the ball bearing. The ball bearing lets the flex spline rotate independently to the wave generator&#39;s shaft. The circular spline is a rigid circular ring with teeth on the inside. The flex spline and wave generator are placed inside the circular spline, meshing the teeth of the flex spline and the circular spline. Because the flex spline is deformed into an elliptical or other non circular shaped such as a three node containing shape, its teeth only actually mesh with the teeth of the circular spline in two regions on opposite sides of the flex spline (located on the major axis of the ellipse or other non circular shaped such as a three node containing shape). 
     As the wave generator plug rotates, the flex spline teeth which are meshed with those of the circular spline change position. The major axis of the flex spline&#39;s ellipse or other non circular shaped such as a three node containing shape rotates with wave generator, so the points where the teeth mesh revolve around the center point at the same rate as the wave generator&#39;s shaft. The key to the design of the strain wave gear is that there are fewer teeth (often for example two fewer) on the flex spline than there are on the circular spline. This means that for every full rotation of the wave generator, the flex spline would be required to rotate a slight amount (two teeth in this example) backward relative to the circular spline. Thus the rotation action of the wave generator results in a much slower rotation of the flex spline in the opposite direction. For a strain wave gearing mechanism, the gearing reduction ratio can be calculated from the number of teeth on each gear. 
     The apparatus most preferably includes a position sensor  950 ,  951 ,  952  that senses a rotational position of the rotor  12  of the electric actuator or motor  200  or a position sensor that senses the linear position of the valve pin  1040  or a linearly moving member such as sled  43  that moves together with linear movement of the valve pin  1040 . In the  FIGS. 1, 2  embodiment, the position sensor typically comprises an encoder that senses the rotational position of the rotor  12  or a rotating element of the strain wave gear  400  such as the flexible spline  430  which in turn corresponds to the linear position of the pin  1040 . The linear position sensor PS can comprise a Hall Effect sensor (HES or H.E.S.) that senses a change in a magnetic field generated by a magnet that is mounted to and linearly moves together with linear movement of the pin  1040 , the sensor converting change in magnetic field to position of the valve pin  1040 . 
     In the embodiments shown, the strain wave gear  400 ,  FIGS. 10, 11, 12A, 12B, 12C, 12D  is comprised of the wave generator or thin walled bearing  460  that is mounted within and against the inner circumferential wall of the flex spline  430  that is in turn mounted within the inner splined circumference of a rigid circular spline  448  as shown for example in  FIGS. 2C, 2D, 2E . An inner bearing race  464  pressed on the elliptical or other non circular shaped such as a three node containing surface of the hub  472  either having or taking a shape complementary to the cam or elliptical or other non circular shaped such as a three node containing surfaces of the hub  472  and imparting forces  470  through the ball bearings  466  to the complementarily shaped outer race  462  that is also generally elliptical or other non circular shaped such as a three node containing shape and to the flex spline teeth  444 , forcing them to mesh with the ring gear teeth  446  as the cam turns on shaft  12 . 
     The input shaft comprises the motor shaft  12  that rotates around the shaft axis  12   a , the outer surface of which is compressibly mated with the inner circumferential surface  480  of the shaft receiving bore  474  of the hub of the gear. In the embodiment shown, output shaft or disc being the inner race  414  of an output bearing  410 , the interface surface  420  of the inner race  414  being attached to a complementary end surface  432  of the flexspline  430 . The strain wave gear as shown is comprised of a housing  400  on which a slewing ring bearing is mounted at the front end. The outer race  412  of the bearing is bolted to the housing and the inner race  414  is part of an armature  418  which is supported by rollers  416 . The slewing ring bearing provides superior stability against any forward to backward movement of the armature as it turns in the housing. The forward end or face  422  of the armature has a bolt pattern  424  on which the drive disc  500  is fastened by screws  428  which pass through bolt pattern  502 . The cam member  600  is bolted to armature  418  through one of the holes in bolt pattern  502  of the drive disc  500  and is rotated eccentrically a distance ED around output rotation axis R 3   a . The shoulder bolt  602  clamps a boss  604  to the disc  500  that is drivably rotated around the gear reducer rotation axis. The boss forms an inner race for roller bearings  606 . The outer race  608  has an outer surface  600   cs  that drives the sled  43  up and down. At the rearward end  420  of the armature there is a bolt pattern  426  to which the flex spline  430  is bolted. The flex spline is cup shaped. The forward end  432  is closed and has a bolt pattern  436  for securing the end of the flex spline to the armature by means of clamping plate  436  and bolts  438 . The sidewall  440  of the flex spline is thin for flexibility but retains good torsional strength. The rearward end of the cup shape  442  is open to receive the wave generator  460 . The exterior surface of the rim has gear teeth  444  which selectively engage teeth  446  on the ring gear  448  as the wave generator rotates. The wave generator is mounted on the motor drive shaft  12  by hub  472 . Hub  472  has an aperture  474  lined with compressible wedge shaped sleeves  480 . When screws  478  are tightened, they force the clamping ring  476  rearward compressing the sleeves and self-centering and clamping the hub to the shaft  12  without the use of Allen set screws or keyways for smoother operation. The wave generator  460  is composed of an oval shaped cam formed on hub  472  on which is mounted by force fit, a ball bearing assembly with a flexible inner race that is force fit on the cam portion of hub  472 . Lobes  482  on the hub form the inner race  464  into a cam with two lobes  468  formed 180 degrees apart in an oval shape. The outer race  462  can be rigid in the form an ellipse or other non circular shaped such as a three node containing shape complementary to the elliptical shape or other non circular shaped such as a three node containing shape of the hub  472  and the inner race  464  or can be thin and flexible so it can conform to the shape of the cam such that it projects outward (arrows  470 ,  FIGS. 12A &amp; 12B ) together with ball bearings  466  as the shaft  12  rotates, to force the gear teeth  444 ,  446  to mesh at locations  450 . The teeth  444  at locations  452  flex inward after the lobes have passed to allow clearance for one or more of the teeth  444  to skip the ring gear teeth  446  and allow the flex spline  430  to rotate in relation to the ring gear  448  as dictated by the gear ratio and number of teeth. 
     The nature of the arrangement of the operative components (wave generator, flex spline, circular spline) of the strain wave gear  46 ,  400  in a nested fashion provide a physical device depth GD, diameter DIA or physical size that is adapted to be compact and space efficient enough or sufficient to enable the device to be mounted to the housing of the rotary to linear converter  40 , and to be readily mountable to and dismountable from, alone or together with the rotary to linear converter, either one or the other of the top clamping plate and the heated manifold. 
     Alternatively the speed reducing, torque increasing device can comprise an assembly such as a worm gear assembly, a spur gear assembly), a planetary gear assembly where the rotor  12  of the motor is connected to and rotates the highest speed rotating gear or gear tooth containing component of the assembly and the intermediate shaft is connected to and rotated by the highest rotating gear or gear tooth containing component of the assembly to effectively reduce the rotational speed and increase the torque output of the rotor  12  that is transmitted to the output shaft that is driven at a reduced speed and higher torque. Other assemblies such as helical gear assemblies, or belts and pulley arrangements and assemblies can be used to affect such speed changing and torque changing. 
     A linear actuator that effects direct linear drive movement of the drive element such as a rod  940   l  or plunger  940   ld ,  FIGS. 24, 25 , can be used as an alternative to use of a rotary motion or rotor based actuator  940  as described with reference to the embodiments of  FIGS. 1 to 12 . 
     One example of a linear actuator is a proportional solenoid as shown in  FIG. 24  that effects analog positioning of a solenoid plunger or rod  940   ld  as a function of coil current contained in the armature or driver  940   dr . As shown a solenoid,  FIG. 24 , or linear motor,  FIG. 25 , employs a flux carrying geometry that can produce a high starting force on the plunger or rod  940   ld  to cause the plunger or rod  940   ld  to be controllably driven along the linear drive axis Y. The resulting force (torque) profile as the solenoid progresses through its operational stroke is nearly flat or descends from a high to a lower value. The solenoid can be useful for positioning, stopping mid-stroke, or for low velocity linear actuation movement of the plunger or rod  9401   d , especially in a dosed loop control system. The proportional concept is more fully described in SAE publication 860759 (1986) the disclosure of which is incorporated by reference in its entirety as if full set forth herein. Another example of a linear actuator is a linear motor,  FIG. 24 , that instead of producing torque (rotation) produces a linear force along its drive axis Y. A typical mode of operation is as a Lorentz-type actuator, in which applied force is linearly proportional to applied current and magnetic field. Thus a linear actuator  940  that effects direct linear driven movement of a rod  9401 , plunger or equivalent element  940   ld  can be employed as an alternative to a rotor based actuator for interconnection to a valve pin  1040  to effect controllable driven linear movement of the valve pin  1040  along its axis X of reciprocal movement as described hereinabove. 
     A linear actuator is particularly suited for use in a configuration where the drive axis Y of the actuator and the pin movement axis X are coaxially arranged such as in the embodiments described with reference to  FIGS. 3A, 3B, 12E, 12G, 12H, 13A, 13B, 14A  and the like. A linear actuator as described can be used to drive any drive member  940   l  as an alternative to the rotor based actuators described herein. 
     As used in this application with regard to various monitoring and control systems, the terms “controller,” “component,” “computer” and the like are intended to refer to a computer-related entity, either hardware, a combination of hardware and software, software, or software in execution. For example, a component or controller may be, but is not limited to being, a process running on a processor, a processor, an object, an executable, a thread of execution, a program, and/or a computer. By way of illustration, both an application running on a server and the server can be a component. One or more components may reside within a process and/or thread of execution and a component may be localized on one computer and/or distributed between two or more computers. 
     Claimed methods of the present invention may also be illustrated as a flow chart of a process of the invention. While, for the purposes of simplicity of explanation, the one or more methodologies shown in the form of a flow chart are described as a series of acts, it is to be understood and appreciated that the present invention is not limited by the order of acts, as some acts may, in accordance with the present invention, occur in a different order and/or concurrent with other acts from that shown and described herein. For example, those skilled in the art will understand and appreciate that a methodology could alternatively be represented as a series of interrelated states or events, such as in a state diagram. Moreover, not all illustrated acts may be required to implement a methodology in accordance with the present invention. 
     In various embodiments of the invention disclosed herein, the term “data” or the like means any sequence of symbols (typically denoted “0” and “1”) that can be input into a computer, stored and processed there, or transmitted to another computer. As used herein, data includes metadata, a description of other data. Data written to storage may be data elements of the same size, or data elements of variable sizes. Some examples of data include information, program code, program state, program data, other data, and the like. 
     As used herein, computer storage media or the like includes both volatile and non-volatile, removable and non-removable media for storage of information such as computer-readable instructions, data structures, program modules, or other data. Computer storage media includes RAM, ROM, EEPROM, FLASH memory or other memory technology, CD-ROM, digital versatile disc (DVDs) or other optical disk storage, magnetic cassettes, magnetic tape, magnetic disk storage or other magnetic storage devices, or any other medium which can be used to store desired information and which can be accessed by the computer. 
     The methods described herein may be implemented in a suitable computing and storage environment, e.g., in the context of computer-executable instructions that may run on one or more processors, microcontrollers or other computers. In a distributed computing environment (for example) certain tasks are performed by remote processing devices that are linked through a communications network and program modules may be located in both local and remote memory storage devices. The communications network may include a global area network, e.g., the Internet, a local area network, a wide area network or other computer network. It will be appreciated that the network connections described herein are exemplary and other means of establishing communications between the computers may be used. 
     A computer may include one or more processors and memory, e.g., a processing unit, a system memory, and system bus, wherein the system bus couples the system components including, but not limited to, the system memory and the processing unit. A computer may further include disk drives and interfaces to external components. A variety of computer-readable media can be accessed by the computer and includes both volatile and nonvolatile media, removable and nonremovable media. A computer may include various user interface devices including a display screen, touch screen, keyboard or mouse. 
     A “controller,” as used herein also refers to electrical and electronic control apparatus that comprise a single box or multiple boxes (typically interconnected and communicating with each other) that contain(s) all of the separate electronic processing, memory and electrical signal generating components that are necessary or desirable for carrying out and constructing the methods, functions and apparatuses described herein. Such electronic and electrical components include programs, microprocessors, computers, PID controllers, voltage regulators, current regulators, circuit boards, motors, batteries and instructions for controlling any variable element discussed herein such as length of time, degree of electrical signal output and the like. For example a component of a controller, as that term is used herein, includes programs, controllers and the like that perform functions such as monitoring, alerting and initiating an injection molding cycle including a control device that is used as a standalone device for performing conventional functions such as signaling and instructing an individual injection valve or a series of interdependent valves to start an injection, namely move an actuator and associated valve pin from a gate closed to a gate open position. In addition, although fluid driven actuators are employed in typical or preferred embodiments of the invention, actuators powered by an electric or electronic motor or drive source can alternatively be used as the actuator component. 
     In the absence of any specific clarification related to its express use in a particular context, where the terms “substantial” or “about” in any grammatical form are used as modifiers in the present disclosure and any appended claims (e.g., to modify a structure, a dimension, a measurement, or some other characteristic), it is understood that the characteristic may vary by up to 30 percent. For example, an element may be described as being substantially insulated or isolated from heat or thermal communication with another element such as a heated manifold. Or an element may be described as being in substantial heat or thermal communication with another element such as a heated manifold. In these cases the element that is described as being in substantial heat communication would be disposed relative to the heated or heat emitting component such as a heated manifold such that heat is readily conducted to the subject element. Similarly, a length or velocity or time may be described as being about a certain specified length or velocity or time. In these cases, the use of “about” to modify the characteristic permits a variance of the characteristic by up to 30 percent. Accordingly, a path length that is described as being between about 1 and about 8 mm includes a path that is between 0.7 or 1.3 mm and 5.6 or 10.4 mm.