VARIABLE DISPLACEMENT HYDRAULIC SERVOMOTOR SYSTEM

Abstract: A bidirectional hydraulic servomotor system (10) includes a variable-displacement motor (12) which may impel or brake movement of a load member that either resists or assists movement by the servomotor. Controlled load move­ ment is achieved with minimal consumption of hydraulic fluid. The hydraulic servo apparatus (10) comprises a: pressure fluid source means (34); a bidirectional variable-displacement hydraulic motor (12) having a pair of fluid inlet/return ports (30, 32); a double acting fluid pressure responsive actuator (22) for changing the displacement of said motor means in response to a fluid pressure differential applied through plungers (84, 86); a directional control valve (46) for directing said flow of pressurized fluid to either of motor ports (30, 32) and for directing returned fluid from the other port to fluid source (34); flow control means (66, 70; 68, 72) for throttling said returned fluid only at and above a predetermined flow rate, said throttling increasing with fluid flow rate have said predetermined flow rate; a pressure responsive bistable valve (100) commun­ icating with said motor ports (30, 32) for shifting between one position providing communication between the motor port having the lower fluid pressure and the plunger (84) ef­ fecting a decrease of motor displacement, and the other position providing communication between the motor port having the higher fluid pressure and the plunger (86) effecting an increase of motor displacement, and a pressure differential responsive metering valve (122) closing said communication between said bistable valve (100) and said double-acting actuator (22) in response to a selected pressure differential between said pair of motor ports (30,32) to direct higher fluid pressure to actuator means (22) and proportionately metering said higher fluid pressure to said actuator means (22) at pressure differ­ entials above said selected level to increase displacement of the motor (12).

Description: The present invention is in the field of hydraulic servo apparatus. More particularly, the present invention relates to a variable displacement hydraulic servo apparatus. Conventional hydraulic servomotors are known wherein a rotational cylinder defines a circumferentially arrayed plurality of axial bores each reciprocally receiving one of a like plurality of plunger members. The plunger members are driven to reciprocate in the bores as the cylinder rotates by their cooperation with a variably angulated swash plate. By variation of the angular position of the swash plate, the displacement of the hydraulic servomotor may be varied. In the aerospace field it is conventional to effect movement of aerodynamic control surfaces by use of fixed displacement hydraulic servomotors. The displacement of these motors is selected to meet stall torque requirements under maximum aerodynamic, or peak load, conditions. During operation under less than peak loads the flow demand of the fixed displacement motor is in excess of that required by the aerodynamic load. Thus, an unnecessary burden to supply pressurized fluid volume is placed on the aircraft hydraulic system. Heretofore, while it has been recognized that variable-displacement hydraulic servomotors offer advantages of reduced consumption of pressurized hydraulic fluid during periods of off-peak operation, their use has been ruled out by deficiencies in conventional servomotor control teachings when considered for application in the aerospace environment. In other words, the aerospace application environment requires a hydraulic servomotor and system which is substantially unaffected by the variable pressure to which an aircraft hydraulic reservoir is subject. Also, certain of the aerodynamic control surfaces of an aircraft present a uniquely challenging problem to the designer of a variable displacement hydraulic servo system. That is, the aircraft control surface, or load member for the servo system, may present a uniform resisting load, or a varying resisting load. The load may change from resisting to assisting, or vice versa, during some control movements, or under certain maneuvering conditions of aircraft flight. Under all of these varying conditions, the displacement of the servomotor must be controlled to effect movement of resisting loads at a desired rate with minimal fluid consumption. The servomotor displacement must be controlled to meet stall torque requirements of the variable resisting load without consumption of fluid volume in excess of that required to move the load. Also, assisting load conditions must not be allowed to cause runaway motion of the control surface. Under these assisting load conditions the servomotor must function as a pump to act like a brake controlling movement of the control surface. But, the braking effect must not be excessive or uncontrolled in its action. The transition from driving a resisting load to braking an assisting load must not be so slow as to allow runaway movement of the control surface, or so sudden as to result in impact-like braking. All of the above considerations have heretofore militated against application of variable displacement hydraulic servomotors to effect movement of the flight control surfaces of aircraft. GB-A-2117932 discloses a drive unit, which is suitable, for instance, for operating a thrust reverser of an aircraft engine. A rotary hydraulic motor has a number of pistons and is controlled by a wobbler which itself is connected to a control arm ad moved through a ball joint by a piston. The piston is subject to hydraulic pressure from a solenoid-operated servo valve, and is controlled by a signal summing network. Signals indicative of input command, the position of the output shaft of the motor, the velocity of the output shaft, and the position of the wobbler are summed up by the signal summing network so that the motor displacement matches the load applied to the drive unit. The present invention provides variable displacement hydraulic servo apparatus wherein the displacement control member of the motor is resiliently biased to a minimum displacement position. A pair of oppositely acting pistons are affective upon the displacement control member. The pistons are, under control of a differential pressure responsive shuttle valve and a differential pressure responsive metering valve, communicated with the motor ports so that the differential fluid pressure across the motor results in a corresponding control pressure which is effective to urge the displacement control member toward the maximum displacement position. This is true whether the motor is driving a resisting load, or being driven as a pump by an assisting load. The direction of motor operation is exclusively under control of a direction control valve. The pair of pistons are also balanced because both are exposed to the internal case pressure of the motor so that variations in case pressure do not cause a change in the displacement control function of the motor. Variations in motor case pressure may result from changes in the hydraulic system reservoir pressure as the aircraft altitude changes. The servo system includes a flow control device effective on the return conduit from the motor to throttle the return fluid flow dependent upon the volume level flow rate of this flow. Return fluid flow from the motor is gradually throttled so long as the volume flow rate thereof is below a selected level. Upon the volume flow rate of returned fluid reaching the selected level, which is indicative of the servomotor being driven by an assisting load, the flow is throttled at a rapidly increasing function of fluid flow volume. Thus, a very effective load-braking function is effective upon the return volume of fluid reaching the selected level. During operation of the servo system with an assisting load, the servomotor functions as a pump pressurizing the fluid return conduit which is throttled by the flow control device. The displacement control function of the servomotor remains biased toward a minimum displacement position for the displacement control member. However, in the event that sufficient braking torque is not provided by the servomotor, the displacement control function is effective to increase motor displacement, to thereby increase braking torque. According to a particularly preferred embodiment of the invention, the servomotor is of the axial piston swash plate type having a pair of fluid flow ports. The swash plate, or displacement control member, is yieldably biased to a minimum displacement position. A first plunger member is exposed on one side to internal motor case pressure and on the other side is exposed to a higher, metered control pressure from a metering valve. The first plunger urges the swash plate toward an increased or maximum displacement position in opposition to the yieldable bias thereon. A second plunger is also effective to move the swash plate, and is exposed to internal motor case pressure and to the lower or return fluid pressure from the motor. The second plunger is arranged to assist the yieldable bias in urging the swash plate to the minimum displacement position. A differential pressure responsive spool valve provides communication of the higher or supply and of the lower or return fluid pressures to the metering valve and second plunger, respectively, as described above. The pressure differential responsive metering valve controls flow of inlet pressure fluid to the first plunger so that a pair of displacement control dead bands are created on both sides of a proportional control band. In the proportional control band motor displacement transitions progressively between minimum and maximum values. A directional control valve is provided to select motor rotational direction by supplying pressure fluid to one motor port and receiving return fluid from the other motor port. A flow control device is provided in the return fluid conduit to provide a motor-braking function during operation of the servomotor system with an assisting load. An advantage of the present invention is the provision of a hydraulic servomotor system which during off peak-load operation consumes considerably less pressurized hydraulic fluid than would a fixed displacement servomotor having the same stall torque. An additional advantage is the provision of a hydraulic servomotor which during peak-load operation is able to provide a stall torque favorably comparable to that of a fixed displacement servomotor. Another advantage of this invention is the provision of a hydraulic servo system wherein load movement is accomplished with automatic transition between load driving and load braking by the servomotor as required to control load velocity. Yet another advantage of the present invention is the provision of a hydraulic servomotor system wherein direction of operation of the servomotor is under the exclusive control of a simple directional control valve with displacement control and functional transition between load driving and load braking being performed automatically by the servo system. Additional objects and advantages of the present invention will be apparent from a reading of the following detailed description of a single preferred embodiment, taken in conjunction with the appended drawing figures, in which: FIG. 1 schematically depicts a servo system embodying the present invention, and having component parts thereof shown partially in cross section or in symbolic form for ease of understanding; FIG. 2 provides a longitudinal cross sectional view of a servomotor portion of the servo system of FIG. 1, with parts thereof also shown schematically for ease of understanding; FIG. 3 provides a fragmentary cross sectional view taken along line 3-3 of FIG. 2; and FIG. 4 presents a graphical representation of a flow-versus-pressure-drop characteristic of a component of the servo system depicted in FIG. 1. FIG. 1 depicts schematically a variable displacement hydraulic servomotor system (10) embodying the present invention. The system (10) includes a variable displacement bidirectional hydraulic motor (12) which is of the swash plate type. The motor (12) includes a rotary shaft (14) by which the motor's output and braking torque may be connected to a movable load member (not shown). It is important to understand that the load member to which the shaft (14) is connected may either resist or assist movement thereof by the hydraulic servomotor system (10). Carried upon the shaft (14) and drivingly connected thereto is a cylinder member (16). The cylinder member (16) defines a plurality of circumferentially arrayed and axially extending bores (18) (not visible viewing FIG. 1). A plurality of plunger members (20) are sealingly and reciprocally received in the plurality of bores (18) of the cylinder member (16). The plunger members (20) extend from the cylinder member (16) to movably engage a variably angularly disposed swash plate member (22). As a result of the angular disposition of the swash plate member (22), the plunger members are driven to reciprocate in the bores (18) in response to rotation of the shaft (14) and cylinder member (16). The swash plate member (22) is pivotally carried by the motor (12) for movement about a pivot axis generally referenced with the numeral (24). It will be appreciated that by pivotally readjusting the angular position of the swash plate member (22) the length of reciprocation of the plurality of plunger members (20) with rotation of the cylinder member (16) and the displacement of the motor (10) is selectively variable. Further it will be understood that the plurality of bores (18) at their end opposite the swash plate member (22) open to a conventional fluid flow commutation device (not shown) such that fluid flow to and from the plurality of bores (18) in a pair of conduits (26) and (28) is unidirectional in each conduit and is dependent upon the direction of rotation of shaft (14) and cylinder (16). The conduits (26) and (28) open in ports (30) and (32) respectively on the pump (12). In order to provide fluid flow to the motor (12) and to receive return fluid therefrom, the servo system (10) includes a source (34) having a pump (36) receiving fluid from a reservoir (38) and delivering this fluid pressurized via a conduit (40). The source (34) is also able to receive returned fluid, as by conduits (42) and (44) opening into the reservoir (38). The reservoir (38) is maintained at a relatively small positive pressure with respect to ambient. This reservoir pressure is considerably below the system pressure provided by pump (36). The servo system (10) also includes a directional control valve generally referenced with a numeral (46). The control valve (46) includes a housing (48) defining a bore (50) wherein is slidably and sealingly received a spool valve member (52). The conduit (40) communicates with an annular chamber (54) circumscribing the spool valve (52) at a central land (56) thereof. Spaced from the annular chamber (54) and land (56) on opposite sides thereof are a pair of annular chambers (58) and (60) respectively communicating with the ports (30) and (32) and conduits (26) and (28) via a respective pair of check valves (62) and (64) and a pair of flow control devices (66) and (68). Each of the flow control devices (66) and (68) also includes a respective check valve (70) and (72). Further spaced apart from the center land (56), the flow control valve (52) includes a pair of end lands (74) and (76) respectively aligning with a pair of annular chambers (78) and (80). Each of the annular chambers (78) and (80) communicates with the return conduit (44) opening into the reservoir (38). In order to provide pressurized fluid from the source (34) via the conduit (40) to either one of the conduits (26) and (28) of the motor (12) the spool valve (52) of the directional control valve (46) is movable either rightwardly or leftwardly from the centered position illustrated via a lever (82). By way of example, if the spool valve (52) is moved rightwardly from its centered position as depicted, the conduit (40) is communicated with the conduit (28) via chambers (54) and (60) and the check valve (64). Consequently, fluid returned from the motor (12) via conduit (26) must flow past the check valve (70) and through the flow control device (66) on its way to chamber (58). As a result of the land (74) also being moved rightwardly, the chamber (58) is communicated with chamber (78), and fluid may flow therefrom to the return conduit (44) and thence to reservoir (38). It will be seen that the motor (12) also includes a pair of oppositely acting plunger members (84) and (86) which are sealingly and reciprocally received in respective bores (88) and (90) defined by the housing (92) of the motor (12). A coil compression spring (94) extends between the housing of the pump (12) and a spring stop (96) carried upon the plunger (84) in order to yieldably bias the swash plate member (22) toward a minimum displacement position. Each of the plungers (84) and (86) is fluid pressure responsive by its exposure at its rightward end to a respective chamber wherein is receivable fluid pressure and by its exposure at its left end within a cavity (98) within the motor (12). The conduit (42) communicates cavity (98) to the reservoir (38). The servomotor system (10) also includes a bistable valve device generally referenced with the numeral (100). The valve device (100) includes a housing (102) defining an elongate bore (104) therein. Slidably and sealingly received within the bore (104) is an elongate spool valve member (106). The spool valve cooperates with the housing (102) to define a pair of variable volume chambers (108) and (110) at opposite ends of the spool valve member. A branch passage (112) from conduit (26) connects with the chamber (108) while a branch passage (114) from conduit (28) connects with the chamber (110). Thus it will be appreciated that the spool valve member (106) is movable between either one of two possible positions at opposite ends of the bore (104) depending upon the sense of fluid pressure differential existing between the conduits (26) and (28) of the motor (12). By way of example, the spool valve member (106) is depicted at its leftward position wherein the conduit (26) has a lower fluid pressure than the conduit (28). Consequently, the flow path means generally referenced with the numeral (116) communicates the conduit (26) via passage (112) with a conduit (118) communicating with the plunger member (84). On the other hand, the higher pressure conduit (28) is communicated via passage (114) and the flow path (116) of the bistable valve (100) with a passage (120) leading to a differential pressure responsive metering valve (122) and subsequently to the plunger (86) of the motor member (12). If the sense of pressure differential between conduits (26) and (28) is reversed, the valve member (106) will shift rightwardly so that the lower pressure is still communicated to plunger (84), while the higher pressure is communicated to metering valve (122) and plunger (86). Interposed in the passage (120) between the bistable valve (100) and the plunger (86) of motor (12), the metering valve (122) includes a housing (124) defining a stepped bore (126) therein in which is received a stepped valve member (128). A spring (130) urges the valve member (128) to a first position wherein communication between the upstream portion of passage (120) leading from the bistable valve (100) and the downstream portion of passage (120) leading to the plunger member (86) is closed. The differential pressure responsive metering valve (122) also has connection with the passage (118) via a passage (132) so that the larger diameter portion (134) of the stepped bore (126) is communicated with the lower of the fluid pressures existing at the conduits (26) and (28). Having observed the structure of servo system (10) in overview, attention may now be given to its operation. During operation of the servo system (10) the pump (36) draws fluid from the reservoir (38) and provides this fluid pressurized to the conduit (40). The direction of operation of the servomotor (12) is selectable by movement of lever (82) to shift the spool valve (52) either rightwardly or leftwardly from its centered position as depicted in FIG. 1. By way of example, the spool valve (52) may be shifted rightwardly from its centered position as depicted so that the conduit (40) is communicated with the port (32) and conduit (28) of servomotor (12) to supply pressure fluid thereby to the bores (18) within cylinder member (16). This supply of pressure fluid will result in rotation of cylinder member (16) and shaft (14) in a selected direction of rotation and in the return of relatively lower pressure fluid via the conduit (26) to the directional control valve (46). The returned flow of fluid will pass through check valve (70) and flow control device (66) on its way to the reservoir (38) via conduit (44). If the servomotor (12) is driving a resisting load, the supplied fluid from pump (36) and conduit (28) will have a higher pressure than the returned fluid in conduit (26). That is, a differential pressure will exist across the servomotor (12). Consequently, the shuttle valve (100) will be in its leftward position as depicted in FIG. 1. It will be seen that in the position depicted of the shuttle valve (100), the conduit (26) is communicated with the passage (118) and the plunger member (84). Consequently, the relatively lower return fluid pressure acting upon plunger member (84) assists the spring (94) in biasing the swash plate member (22) to the lower displacement position thereof. So long as the resisting torque required to drive the load member is below a certain valve, the pressure differential between conduits (26) and (28) will remain below a selected level. However, in the event the resisting torque exceeds the certain value, the pressure differential across the servomotor (12) as appearing at conduits (26) and (28) will reach and perhaps exceed the certain value. This fluid pressure differential across the servomotor (12) is also applied to the differential pressure responsive metering valve (122) by its connection in the passage (120) and connection of the larger diameter bore portion (134) with the conduit (118) via the branch passage (132). Consequently, when the differential pressure across the servomotor (12) reaches the certain value, the stepped valve member (128) of the differential pressure responsive metering valve (122) is urged downwardly to open communication through the passage (120) to the plunger member (86). Communication of the relatively higher fluid pressure to the plunger member (86) causes this plunger to drive the swash plate member toward a position of greater angulation with respect to the shaft (14) and cylinder (16) to thereby increase the displacement per rotation of the servomotor (12). This angular repositioning of the swash plate member (22) takes place in opposition to the bias provided by spring (94) and the urging provided by plunger member (84) in response to the relatively lower fluid pressure communicated thereto. The increased displacement of the servomotor (12) caused it to generate an increased driving torque for delivery to the load. The displacement of the servomotor (12) is progressively increased as described above in response to increasing differential pressure thereacross until a maximum displacement position is reached for the swash plate member (22). On the other hand, in the event that the load connected with shaft (14) becomes an assisting load, this assisting load will drive the servomotor (12) as a pump and result in the fluid pressure level at the return conduit (26) reaching and then exceeding the fluid pressure level supplied to the conduit (28) by the source (34). As a reminder to the reader that the servomotor (12) may function also as a pump, it will be hereinafter occasionally referred to as a motor pump unit. As a result, the fluid flowing in conduit (26) through the motor pump unit (12) and back to the source (34) via conduit (26) will be impelled in this circulation now by both pump (36) and the motor pump unit (12) operating as a pump. The result is a larger flow of fluid than would result with the motor pump unit (12) operating as a motor. This increase in fluid flow volume is sensed by the flow control device (66). In the event that the fluid flow through device (66) reaches a determined level, this device provides a sharply increased throttling of the fluid flow which is progressive with increasing fluid flow rate. Attention given now to FIG. 4 will graphically illustrate this progressive throttling of the return fluid flow by flow control device (66). FIG. 4 illustrates that as flow rate increases from zero at the left of the margin (line A) of the graphical depiction in FIG. 4 there is a gradually increasing inherent throttling of the return fluid flow. This inherent throttling of return fluid flow is the result of natural pipe line friction with increasing fluid flow volume and velocity. Upon the achievement of a flow rate, which is represented at line B of the graphical depiction of FIG. 4, a flow dependent throttling function begins to take effect so that as flow rate increases the pressure drop which is permitted to take place across the motor pump unit (12) increases. In the event that the fluid flow rate continues to increase (which is indicative of an assisting load continuing to accelerate and drive the motor pump unit (12) as a pump) so that a flow rate above that indicated at line B is achieved, a sharply increasing throttling function is provided. At flow rates at and above the level indicated by line B on the graph of FIG. 4 the pressure drop allowed across the motor pump unit (12) is greatly increased. This throttling of the return fluid flow causes the motor pump unit (12) to act as a hydraulic brake on the load and to control the acceleration and load velocity of the assisting load. In the event it is desired to operate the motor pump unit in the direction opposite to that described above, it is apparent that the spool valve member (52) may be shifted leftwardly in the bore (50) in response to movement of lever (82). The motor pump unit (12) will thus operate as described above but with an opposite direction of rotation and opposite direction of load movement. Attention now to FIGS. 2 and 3 in conjunction will reveal the particular structure of the motor pump unit (12). Reference numerals used on FIG. 1 are carried over to FIGS. 2 and 3. It will be observed viewing FIGS. 2 and 3 that the housing (92) of the servomotor (12) in fact includes portions (102) and (124) thereof which receive the bistable spool valve (106) and the differential pressure responsive metering valve (122). The servomotor (12) includes a plate member (136) which is sealingly associated with the cylinder (16), and provides fluid flow communication between the bores (18) of the latter and the passages (26) and (28). Also, the motor (12) includes a plug member (138) outwardly closing the bore (134) and sealingly receiving a relatively movable spring seat (140). The spring seat (140) supports spring (130) and is adjustably movable by rotation of an adjusting member (142) threadably engaging the plug member (138). Adjustment of the preload of spring (130) by rotation of adjusting member (142) allows external adjustment of the threshold differential pressure across motor (12) whereat displacement increase is initiated. It will be recalled that this displacement increase is effected by metering of pressurized fluid to plunger (86) via the valve (122). Viewing FIG. 3 it will also be seen that the housing (92) defines a stepped bore (144) to which the passages (112), (114), (120), and (132) open. A sleeve member (146) is sealingly received in the bore (144) and defines chambers (148), (150), (152) and (154) which are sealingly separated from one another except for their communication via sleeve member (146). The chambers (148-154) communicate with passages (112), (132), (120), and (114), respectively. Sleeve member (146) defines the bore (104) wherein is slidably received the spool valve member (106). It will be seen that a washer (156) and plug member (158) sealingly retain the sleeve member (146) and spool valve member (106) within bore (144). The washer member (156) defines radially extending slots (160) communicating the chambers (148) and (108) with one another. The spool valve member (106) includes four axially extending land portions (162-168) which sealingly cooperate with the sleeve member (146). Between the land portions, the sleeve member defines three groove portions (170-174). The flow path (116) comprises a first passage (176) defined by the spool valve member (106) and communicating the chamber (110) with the grooves (170) and (172). The spool valve member (106) also defines a second passage (178) communicating chamber (108) with the groove (172). In view of the above, it will be appreciated that in one of the two stable positions for spool valve member (106), as depicted, wherein the chamber (108) has the higher fluid pressure, this pressure is communicated to the passage (120) via passage (178), groove (172), and a port (180) in sleeve member (146) which opens to chamber (152). Similarly, the lower fluid pressure from chamber (110) is communicated via passage (176), groove (170) and a port (182) in sleeve member (146) to chamber (150) and passage (132). On the other hand, should the chamber (110) have the higher fluid pressure, the spool valve member (106) is shiftable leftwardly in bore (104) to a position at the opposite end thereof. In this second position of the spool valve member chamber (110) is communicated to passage (120) via passage (176), groove (174), port (180), and chamber (152). Similarly, the chamber (108) communicates with passage (132) via passage (178), groove (172), port (182), and chamber (150).

Claims: Hydraulic servo apparatus (10) which comprises: pressure fluid source means (34) for supplying a flow of pressurized fluid and for receiving returned fluid; bidirectional variable-displacement hydraulic motor means (12) having a pair of fluid inlet/return ports (30,32); double acting fluid pressure responsive actuator means (22) for changing the displacement of said motor means in response to a fluid pressure differential applied to a pair of oppositely disposed fluid pressure responsive faces thereof; directional control means (46) for directing said flow of pressurized fluid to either of said pair of motor ports (30,32) and for directing fluid from the other of said pair of ports to said fluid source means (34); flow control means (66,70; 68,72) interposing between the other of said pair of ports and said source means (34) for throttling said returned fluid only at and above a predetermined flow rate thereof, said throttling of said returned fluid increasing with fluid flow rate of above said predetermined flow rate; pressure responsive bistable valve means (100), communicating with said pair of motor ports (30,32) for shifting between two alternative positions, one position providing communication between the one of said motor ports having the lower fluid pressure and the one of said pair of oppositely disposed faces of said actuator means (22) effecting a decrease of motor displacement, and the other position providing communication between the one of said pair of motor ports having the higher fluid pressure and the other of said pair of oppositely disposed faces of said actuator means effecting the increase of motor displacement, and pressure differential responsive metering valve means (122) closing said communication between said bistable valve means (100) and said double-acting actuator means (22), said metering valve means being responsive to a selected pressure differential between said pair of motor ports (30,32) to open said communication of said higher fluid pressure to said other pressure responsive face of said actuator means to effect a fluid pressure differential thereat, and said metering valve proportionately metering said higher fluid pressure to said actuator means proportionately at pressure differentials above said selected level to increase displacement of said motor means. Apparatus according to Claim 1 characterized in that the said hydraulic motor means (12) includes a displacement control member (22) movable between a first position and a second position to respectively decrease and increase fluid displacement of said motor means per rotation of an output shaft (24) thereof, said motor means include a housing (92) defining an internal cavity (98), means providing communication between said internal cavity and said pressure fluid source (34) to maintain a chosen relatively low pressure in said cavity (98), oppositely disposed faces provided by a pair of plunger members (84,86) reciprocable in said motor housing and each being exposed at one end thereof to said internal cavity (98) and at the other end thereof defining a respective one of said pair of oppositely disposed faces, said pair of plunger means (84,86) operatively associating with said displacement control member (22) to move the latter between said first and said second position thereof. Apparatus according to Claim 2 characterized in that the said variable-displacement motor (12) is of the axial piston swash plate type having a swash plate defining said displacement control member (22), and said hydraulic motor having a housing (92) defining an internal cavity (98) containing said swash plate, a pair of bores (88, 90) opening into said cavity, a pair of functionally opposed plunger members (84, 86), each being reciprocable in a respective bore, one plunger member (84) being disposed and operatively associated with said swash plate (22) to urge the latter toward its lower-displacement position, the other plunger member (86) being disposed and operatively associated with said swash plate (22) to urge the latter toward its higher-displacement position, and said fluid source (34) including a reservoir (38) maintained at a comparatively low pressure, and conduit means (42) providing communication between said cavity (98) and said reservoir (38). Apparatus according to any one of Claims 1 to 3 characterized in that the bistable valve means (100) includes an elongate spool valve member (106) reciprocably received in a housing bore (104), means (26, 112, 108; 28, 114, 110) providing communication between said pair of motor ports with respective opposite ends of said spool valve member, said spool member (106) being freely movable between a first position at one end of said bore and a second position at the opposite end of said bore in dependence upon fluid pressure differential between said pair of motor ports, and defining three circumferential grooves (170, 172, 174) uniformly spaced apart along the length thereof, a pair of ports (180, 182) opening to said bore in spaced apart relation matching the spacing of adjacent grooves on said spool valve member, each one of said pair of ports communicating with a respective one of said oppositely disposed faces of said actuator means, and said spool valve member defining a first longitudinally extending passage (178) communicating the central grooves (172) with one end (180) of said spool valve member and a second longitudinally extending passage (176) communicating the opposite end (106) of said spool valve member with the outer two grooves (170, 174), whereby said central groove (172) is in registry with a respective one of said pair of ports (180, 182) in each of said first and second positions of said spool valve member while one of said outer two grooves (170, 172) is in registry with the other of said pair of ports. Apparatus according to any one of Claims 1 to 4 characterized in that the pressure differential responsive metering valve means (122) comprises a stepped bore (126) in a motorhousing (92) around said hydraulic motor means (12) a smaller diameter end of said bore (126) communicating with said other motor port and at a larger diameter portion thereof communicating with said one motor port, a passage (120) opening on said smaller diameter bore portion and communicating with said other pressure responsive face of said actuator means, and a stepped valve member (128) sealingly and reciprocably received in said smaller diameter and said larger diameter portions of said stepped bore (126) resilient means (130) yieldably urging said stepped valve member to a first position overlapping said passage (120) to close communication between said other motor port and said one pressure responsive face of said actuator means, and said stepped valve member moving toward said larger diameter bore portion in response to said selected fluid pressure differential between said motor ports in opposition to said resilient means, to open fluid metering communication between said other motor port and said other pressure responsive face of said actuator means. Apparatus according to any one of Claims 1 to 5 characterized in that the said directional control valve (46) includes a housing (48) defining an elongate bore (50) therein, an elongate spool valve member (52) reciprocably received in said bore between a first closed-center position and a pair of axially opposite motor operating positions, said spool valve member (52) defining a center land (56) and a pair of spaced end lands (74, 76), and a pair of circumferential grooves each one being between said center land and a respective end land, a fluid supply port (54) opening to said bore in registry with said center land in said closed-center position, and communicating with pressure fluid from said source (34), and a pair of return ports (78, 80) opening to said bore respectively in registry with said pair of end lands in said closed-center position and communicating with said source (34) for returning fluid thereto, a pair of ports (58, 60) opening to said bore each in registry with a respective one of said circumferential grooves and communicating with respective ones of said pair of motor ports (30, 32) whereby said spool valve member (52) is movable axially in either direction from said closed-center position of one of said motor operating positions to communicate pressure fluid to one of said pair of motor ports, and to communicate the other of said pair of motor ports to said source for the return of fluid thereto.

Inventors: BARKER, BRIAN P. C/O ALLIED-SIGNAL INC.
Applicants: ALLIED-SIGNAL INC. (A DELAWARE CORPORATION)
Application year: 1989
Main classification: F04B1
IPC codes: F04B1