Abstract:
A transmission is provided having an input member, an output member, at least four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices include clutches and brakes actuatable in combinations of two to establish a plurality of forward gear ratios and one reverse gear ratio.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims the benefit of U.S. Provisional Application No. 61/588,837 filed Jan. 20, 2012. The disclosure of the above application is incorporated herein by reference. 
     FIELD 
     The invention relates generally to a multiple speed transmission having a plurality of planetary gear sets and a plurality of torque transmitting devices and more particularly to a transmission having ten or more speeds, at least four planetary gear sets and a plurality of torque transmitting devices. 
     BACKGROUND 
     The statements in this section merely provide background information related to the present disclosure and may or may not constitute prior art. 
     A typical multiple speed transmission uses a combination of friction clutches, planetary gear arrangements and fixed interconnections to achieve a plurality of gear ratios. The number and physical arrangement of the planetary gear sets, generally, are dictated by packaging, cost and desired speed ratios. 
     While current transmissions achieve their intended purpose, the need for new and improved transmission configurations which exhibit improved performance, especially from the standpoints of efficiency, responsiveness and smoothness and improved packaging, primarily reduced size and weight, is essentially constant. Accordingly, there is a need for an improved, cost-effective, compact multiple speed transmission. 
     SUMMARY 
     A transmission is provided having an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices are for example clutches and brakes. 
     In an embodiment of the present invention, the first, second, third and fourth planetary gear sets each having a sun gear, a carrier member and a ring gear, wherein the input member is continuously connected for common rotation with the sun gear of the second planetary gear set, and wherein the output member is continuously connected for common rotation with the carrier member of the first planetary gear set. 
     In another embodiment of the present invention, a first interconnecting member continuously interconnects the carrier member of the first planetary gear set with the ring gear of the third planetary gear set. 
     In still another embodiment of the present invention, a second interconnecting member continuously interconnects the ring gear of the first planetary gear set with the carrier member of the second planetary gear set. 
     In still another embodiment of the present invention, a third interconnecting member continuously interconnects the ring gear of the second planetary gear set with the carrier member of the third planetary gear set. 
     In still another embodiment of the present invention, a fourth interconnecting member continuously interconnects the carrier member of the third planetary gear set with the ring gear of the fourth planetary gear set. 
     In still another embodiment of the present invention, a fifth interconnecting member continuously interconnects the sun gear of the third planetary gear set with the carrier member of the fourth planetary gear set. 
     In yet another embodiment of the present invention, a first torque transmitting mechanism is selectively engageable to interconnect the sun gear of the third planetary gear set and the carrier member of the fourth planetary gear set with the input member and the sun gear of the second planetary gear set. 
     In yet another embodiment of the present invention, a second torque transmitting mechanism is selectively engageable to interconnect the ring gear of the second planetary gear set, the carrier member of the third planetary gear set and the ring gear of the fourth planetary gear set with the input member and the sun gear of the second planetary gear set. 
     In yet another embodiment of the present invention, a third torque transmitting mechanism is selectively engageable to interconnect the carrier member of the first planetary gear set and the ring gear of the third planetary gear set with the carrier member of the third planetary gear set and the ring gear of the fourth planetary gear set. 
     In yet another embodiment of the present invention, a fourth torque transmitting mechanism is selectively engageable to interconnect the sun gear of the fourth planetary gear set with the stationary member. 
     In yet another embodiment of the present invention, a fifth torque transmitting mechanism is selectively engageable to interconnect the carrier member of the fourth planetary gear set and the sun gear of the third planetary gear set with the stationary member. 
     In yet another embodiment of the present invention, a sixth torque transmitting mechanism is selectively engageable to interconnect the ring gear of the fourth planetary gear set, carrier member of the third planetary gear set and the ring gear of the second planetary gear set with the stationary member. 
     In yet another embodiment of the present invention, a seventh torque transmitting mechanisms is selectively engageable to interconnect the sun gear of the first planetary gear set with the stationary member. 
     In yet another embodiment of the present invention, the torque transmitting mechanisms are selectively engageable in combinations of at least two to establish a plurality of forward speed ratios and at least one reverse speed ratio between the input member and the output member. 
     Further features, aspects and advantages of the present invention will become apparent by reference to the following description and appended drawings wherein like reference numbers refer to the same component, element or feature. 
    
    
     
       DRAWINGS 
       The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way. 
         FIG. 1  is a lever diagram of an embodiment of a ten speed transmission according to the present invention; 
         FIG. 2  is a diagrammatic illustration of an embodiment of a ten speed transmission according to the present invention; and 
         FIG. 3  is a truth table presenting the state of engagement of the various torque transmitting elements in each of the available forward and reverse speeds or gear ratios of the transmissions illustrated in  FIGS. 1 ,  2  and  3 . 
     
    
    
     DETAILED DESCRIPTION 
     The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. 
     At the outset, it should be appreciated that the embodiments of the multi-speed automatic transmissions of the present invention have an arrangement of permanent mechanical connections between the elements of the four planetary gear sets. A second component or element of a first planetary gear set is permanently coupled to a third component or element of the third planetary gear set. A third component or element of the first planetary gear set is permanently coupled a second component or element of the second planetary gear set. A third component or element of the second planetary gear set is permanently coupled to a second component or element of the third planetary gear set and a third component or element of the fourth planetary gear set. A first component or element of the third planetary gear set is permanently coupled to a second component or element of the fourth planetary gear set. 
     Referring now to  FIG. 1 , an embodiment of a ten speed transmission  10  is illustrated in a lever diagram format. A lever diagram is a schematic representation of the components of a mechanical device such as an automatic transmission. Each individual lever represents a planetary gear set wherein the three basic mechanical components of the planetary gear are each represented by a node. Therefore, a single lever contains three nodes: one for the sun gear, one for the planet gear carrier, and one for the ring gear. The relative length between the nodes of each lever can be used to represent the ring-to-sun ratio of each respective gear set. These lever ratios, in turn, are used to vary the gear ratios of the transmission in order to achieve an appropriate ratios and ratio progression. Mechanical couplings or interconnections between the nodes of the various planetary gear sets are illustrated by thin, horizontal lines and torque transmitting devices such as clutches and brakes are presented as interleaved fingers. Further explanation of the format, purpose and use of lever diagrams can be found in SAE Paper 810102, “The Lever Analogy: A New Tool in Transmission Analysis” by Benford and Leising which is hereby fully incorporated by reference. 
     The transmission  10  includes an input shaft or member  12 , a first planetary gear set  14 , a second planetary gear set  16 , a third planetary gear set  18  and a fourth planetary gear set  20  and an output shaft or member  22 . In the lever diagram of  FIG. 1 , the first planetary gear set  14  has three nodes: a first node  14 A, a second node  14 B and a third node  14 C. The second planetary gear set  16  has three nodes: a first node  16 A, a second node  16 B and a third node  16 C. The third planetary gear set  18  has three nodes: a first node  18 A, a second node  18 B and a third node  18 C. The fourth planetary gear set  20  has three nodes: a first node  20 A, a second node  20 B and a third node  20 C. 
     The input member  12  is continuously coupled to the first node  16 A of the second planetary gear set  16 . The output member  22  is coupled to the second node  14 B of the first planetary gear set  14  and the third node  18 C of the third planetary gear set  18 . The second node  14 B of the first planetary gear set  14  is coupled to the third node  18 C of the third planetary gear set  18 . The third node  14 C of the first planetary gear set  14  is coupled to the second node  16 B of the second planetary gear set  16 . The third node  16 C of the second planetary gear set  16  is coupled to the second node  18 B of the third planetary gear set  18 . The first node  18 A of the third planetary gear set  18  is coupled to second node  20 B of the fourth planetary gear set  20 . The second node  18 B of the third planetary gear set  18  is coupled to the third node  20 C of the fourth planetary gear set  20 . 
     A first clutch  26  selectively connects the input member or shaft  12  and the first node  16 A of the second planetary gear set  16  with the first node  18 A of the third planetary gear set  18  and the second node  20 B of the fourth planetary gear set  20 . A second clutch  28  selectively connects the input member or shaft  12  and the first node  16 A of the second planetary gear set  16  with the third node  16 C of the second planetary gear set  16 , the second node  18 B of the third planetary gear set  18  and the third node  20 C of the fourth planetary gear set  20 . A third clutch  30  selectively connects the third node  20 C of the fourth planetary gear set  20  with the third node  18 C of the third planetary gear set  18 , the second node  14 B of the first planetary gear set  14  and the output member  22 . A first brake  32  selectively connects the first node  20 A of the fourth planetary gear set  20  with a stationary member or transmission housing  50 . A second brake  34  selectively connects the first node  18 A of the third planetary gear set  18  and the second node  20 B of the fourth planetary gear set  20  with the stationary member or transmission housing  50 . A third brake  36  selectively connects the third node  16 C of the second planetary gear set  16 , the second node  18 B of the third planetary gear set  18  and the third node  20 C of the fourth planetary gear set  20  with the stationary member or transmission housing  50 . 
     Referring now to  FIG. 2 , a stick diagram presents a schematic layout of an embodiment of the ten speed transmission  10  according to the present invention. In  FIG. 2 , the numbering from the lever diagram of  FIG. 1  is carried over. The clutches and couplings are correspondingly presented whereas the nodes of the planetary gear sets now appear as components of planetary gear sets such as sun gears, ring gears, planet gears and planet gear carriers. 
     For example, the planetary gear set  14  includes a sun gear member  14 A, a ring gear member  14 C and a planet gear carrier member  14 B that rotatably supports a set of planet gears  14 D (only one of which is shown). The sun gear member  14 A is connected for common rotation with a first shaft or interconnecting member  42 . The ring gear member  14 C is connected for common rotation with a second shaft or interconnecting member  44 . The planet carrier member  14 B is connected for common rotation with the output shaft or member  22 . The planet gears  14 D are each configured to intermesh with both the sun gear member  14 A and the ring gear member  14 C. 
     The planetary gear set  16  includes a sun gear member  16 A, a ring gear member  16 C and a planet gear carrier member  16 B that rotatably supports a set of planet gears  16 D (only one of which is shown). The sun gear member  16 A is connected for common rotation with the input shaft or member  12 . The ring gear member  16 C is connected for common rotation with a third shaft or interconnecting member  46 . The planet carrier member  16 B is connected for common rotation with the second shaft or interconnecting member  44 . The planet gears  16 D are each configured to intermesh with both the sun gear member  16 A and the ring gear member  16 C. 
     The planetary gear set  18  includes a sun gear member  18 A, a ring gear member  18 C and a planet gear carrier member  18 B that rotatably supports a set of planet gears  18 D (only one of which is shown). The sun gear member  18 A is connected for common rotation with a fourth shaft or interconnecting member  48  and a fifth shaft or interconnecting member  52 . The ring gear member  18 C is connected for common rotation with the output shaft or member  22 . The planet carrier member  18 B is connected for common rotation with the third shaft or interconnecting member  46  and with a sixth shaft or interconnecting member  54 . The planet gears  18 D are each configured to intermesh with both the sun gear member  18 A and the ring gear member  18 C. 
     The planetary gear set  20  includes a sun gear member  20 A, a ring gear member  20 C and a planet gear carrier member  20 B that rotatably supports a set of planet gears  20 D (only one of which is shown). The sun gear member  20 A is connected for common rotation with a seventh shaft or interconnecting member  56 . The ring gear member  20 C is connected for common rotation with an eighth shaft or interconnecting member  58  and with the sixth shaft or interconnecting member  54 . The planet carrier member  20 B is connected for common rotation with the fifth shaft or interconnecting member  52  and with a ninth shaft or interconnecting member  60 . The planet gears  20 D are each configured to intermesh with both the sun gear member  20 A and the ring gear member  20 C. 
     The input shaft or member  12  is continuously connected to an engine (not shown) or to a turbine of a torque converter (not shown). The output shaft or member  22  is continuously connected with the final drive unit or transfer case (not shown). 
     The torque-transmitting mechanisms or clutches  26 ,  28 ,  30  and brakes  32 ,  34 ,  36  and  38  allow for selective interconnection of the shafts or interconnecting members, members of the planetary gear sets and the housing. For example, the first clutch  26  is selectively engageable to connect the input shaft or member  12  with the fourth shaft or interconnecting member  48 . The second clutch  28  is selectively engageable to connect the input shaft or member  12  with the third shaft or interconnecting member  46 . The third clutch  30  is selectively engageable to connect the output shaft or member  22  with the sixth shaft or interconnecting member  54 . The first brake  32  is selectively engageable to connect the seventh shaft or interconnecting member  56  with the stationary element or the transmission housing  50  in order to restrict the member  56  from rotating relative to the transmission housing  50 . The second brake  34  is selectively engageable to connect the ninth shaft or interconnecting member  60  with the stationary element or the transmission housing  50  in order to restrict the member  60  from rotating relative to the transmission housing  50 . The third brake  36  is selectively engageable to connect the eighth shaft or interconnecting member  58  with the stationary element or the transmission housing  50  in order to restrict the member  58  from rotating relative to the transmission housing  50 . The fourth brake  38  is selectively engageable to connect the first shaft or interconnecting member  42  with the stationary element or the transmission housing  50  in order to restrict the member  42  from rotating relative to the transmission housing  50 . 
     Referring now to  FIG. 2  and  FIG. 3 , the operation of the ten speed transmission  10  will be described. It will be appreciated that transmission  10  is capable of transmitting torque from the input shaft or member  12  to the output shaft or member  22  in at least ten forward speed or torque ratios and at least one reverse speed or torque ratio. Each forward and reverse speed or torque ratio is attained by engagement of one or more of the torque-transmitting mechanisms (i.e. first clutch  26 , second clutch  28 , third clutch  30 , first brake  32 , second brake  34 , third brake  36  and fourth brake  36 ), as will be explained below.  FIG. 3  is a truth table presenting the various combinations of torque-transmitting mechanisms that are activated or engaged to achieve the various gear states. An “X” in the box means that the particular clutch or brake is engaged to achieve the desired gear state. An “O” represents that the particular torque transmitting device (i.e. a brake or clutch) is on or active, but not carrying torque. Actual numerical gear ratios of the various gear states are also presented although it should be appreciated that these numerical values are exemplary only and that they may be adjusted over significant ranges to accommodate various applications and operational criteria of the transmission  10 . Of course, other gear ratios are achievable depending on the gear diameter, gear teeth count and gear configuration selected. 
     For example to establish a reverse gear, first clutch  26  and third brake  36  are engaged or activated. The first clutch  26  connects the input shaft or member  12  with the fourth shaft or interconnecting member  48 . The third brake  36  connects the eighth shaft or interconnecting member  58  with the stationary element or the transmission housing  50  in order to restrict the member  58  from rotating relative to the transmission housing  50 . Likewise, the ten forward ratios are achieved through different combinations of clutch and brake engagement, as shown in  FIG. 3 . 
     It will be appreciated that the foregoing explanation of operation and gear states of the ten speed transmission  10  assumes, first of all, that all the clutches not specifically referenced in a given gear state are inactive or disengaged and, second of all, that during gear shifts, i.e., changes of gear state, between at least adjacent gear states, a clutch engaged or activated in both gear states will remain engaged or activated. 
     The description of the invention is merely exemplary in nature and variations that do not depart from the gist of the invention are intended to be within the scope of the invention. Such variations are not to be regarded as a departure from the spirit and scope of the invention.