Patent Abstract:
A transmission is provided having an input member, an output member, four planetary gear sets, a four coupling members and a six torque-transmitting mechanisms. Further, a hydraulic fluid control circuit is provided for controlling the operation of the plurality of torque-transmitting devices. The hydraulic fluid control circuit receives pressurized hydraulic fluid from an off-axis hydraulic fluid pump and has a plurality of fluid passages disposed in the transmission house, input member and other coupling members.

Full Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This nonprovisional application claims the benefit of U.S. Provisional Application No. 61/659,787, filed on Jun. 14, 2012, which is hereby incorporated in its entirety herein by reference. 
    
    
     FIELD 
     The present invention relates generally to multiple speed transmissions having a plurality of planetary gear sets and a plurality of torque-transmitting devices and more particularly to a hydraulic control circuit for controlling the operation of the 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 control systems is essentially constant. More efficient hydraulic controls require less energy and provide improved performance, weight efficiency and driver satisfaction. Accordingly, there is a need for an improved, cost-effective, compact multiple speed transmission. 
     SUMMARY 
     A transmission is provided having a transmission housing, a first, a second, a third, and a fourth planetary gear sets each having a first, a second, and a third members, an input and output members rotatably supported by the transmission housing, four interconnecting members each continuously interconnecting one of the first, second, and third members of the planetary gear sets with another of the first, second, and third members of the planetary gear sets, an intermediate member rotatably supported by the one of the four interconnecting members, and six torque transmitting mechanisms each selectively interconnecting at least one of the first, second, and third members of the planetary gear sets with at least another of the first members, second members, third members of the planetary gear sets, the intermediate member, or the transmission housing. The input member continuously interconnected with the second member of the second planetary gear set. The output member continuously interconnected to the second member of the fourth planetary gear set. The torque transmitting mechanisms are selectively engageable in combinations of at least three to establish ten forward speed ratios and at least one reverse speed ratio between the input member and the output member. 
     In one example of the present invention, a first of the four interconnecting members continuously interconnects the first member of the first planetary gear set with the first member of the second planetary gear set. A second of the four interconnecting members continuously interconnects the second member of the first planetary gear set with the third member of the fourth planetary gear set. A third of the four interconnecting members continuously interconnects the third member of the second planetary gear set with the first member of the third planetary gear set. A fourth of the four interconnecting members continuously interconnects the third member of the third planetary gear set with the first member of the fourth planetary gear set. 
     In another example of the present invention, a first of the six torque transmitting mechanisms is selectively engageable to interconnect at least one of the first member of the first planetary gear set and the first member of the second planetary gear set with the transmission housing. A second of the six torque transmitting mechanisms is selectively engageable to interconnect the third member of the first planetary gear set with the transmission housing. A third of the six torque transmitting mechanisms is selectively engageable to interconnect at least one of the second member of the second planetary gear set and the input member with the first member of the fourth planetary gear set. A fourth of the six torque transmitting mechanisms is selectively engageable to interconnect at least one of the third member of the second planetary gear set and the first member of the third planetary gear set with the intermediate member. A fifth of the six torque transmitting mechanisms is selectively engageable to interconnect the second member of the third planetary gear set with the intermediate member. A sixth of the six torque transmitting mechanisms is selectively engageable to interconnect at least one of the second member of the first planetary gear set and the third member of the fourth planetary gear set with the intermediate member. 
     In yet another example of the present invention, each of the six torque transmitting mechanisms include a clutch pack and an actuating assembly. The actuating assembly of the first of the six torque transmitting mechanisms includes a piston, an apply chamber, and a dam spring. The actuating assembly of the second of the six torque transmitting mechanisms includes a piston, a first apply chamber, a second apply chamber, and a dam chamber. The actuating assemblies of the third, fourth, fifth, and sixth of the six torque transmitting mechanisms each include a piston, an apply chamber, and a dam chamber. 
     In yet another example of the present invention, the transmission housing includes a front portion, a center portion, and a rear portion. The actuating assembly of the first of the six torque transmitting mechanisms is supported by the center portion. The actuating assembly of the second of the six torque transmitting mechanisms is supported by the rear portion. 
     In yet another example of the present invention, the center portion of the transmission housing includes an apply passage in communication with the apply chamber of the first of the six torque transmitting mechanisms. The rear portion of the transmission housing includes a first apply passage in communication with the first apply chamber of the second of the six torque transmitting mechanisms, a second apply passage in communication with the second apply chamber of the second of the six torque transmitting mechanisms, and a dam passage in communication with the dam chamber of the second of the six torque transmitting mechanisms. 
     In yet another example of the present invention, the front portion of the transmission housing includes a first, second, third, and fourth apply passages and a dam passage. The fourth apply passage is in communication with the apply chamber of the third of the six torque transmitting mechanisms. The dam passage is in communication with the dam chamber of the third of the six torque transmitting mechanisms. 
     In yet another example of the present invention, the input member includes a first, second, and third apply passages and a dam passage. The first apply passage of the input member is in communication with each of the first apply passage of the front portion of the transmission housing and the apply chamber of the fourth of the six torque transmitting mechanisms. The second apply passage of the input member is in communication with each of the second apply passage of the front portion of the transmission housing and the apply chamber of the fifth of the six torque transmitting mechanisms. The third apply passage of the input member is in communication with each of the third apply passage of the front portion of the transmission housing and the apply chamber of the sixth of the six torque transmitting mechanisms. The dam passage of the input member is in communication with each of the dam passage of the front portion of the transmission housing and the dam chambers of each of the fourth, fifth, and sixth of the six torque transmitting mechanisms. 
     In yet another example of the present invention, the input member includes a first, a second, a third, and a fourth bores disposed parallel to a longitudinal axis of the input member, a first clutch port in communication with the apply chamber of the fourth of the six torque-transmitting mechanisms and the first bore of the input member, a second clutch port in communication with the apply chamber of the fifth of the six torque-transmitting mechanisms and the second bore of the input member, a third clutch port in communication with the apply chamber of the sixth of the six torque-transmitting mechanisms and the third bore of the input member, and a first, second, and third dam ports in communication with the dam chambers of the fourth, fifth, and sixth of the six torque-transmitting mechanisms, respectively, and the fourth bore of the input member. 
     In yet another example of the present invention, the multi-speed transmission further includes a sleeve shaft supported by the front portion of the transmission housing, a plurality of input member seals, a first annular channel, a second annular channel, a third annular channel, and a fourth annular channel. The annular channels are defined by the inner surface of the sleeve shaft, the outer surface of the input member, and the plurality of input member seals. The first annular channel communicates with the first bore of the input member through a first port. The second annular channel communicates with the second bore of the input member through a second port. The third annular channel communicates with the third bore of the input member through a third port. The fourth annular channel communicates with the fourth bore of the input member through a fourth port. 
     In yet another example of the present invention, the multi-speed transmission further includes a hydraulic fluid pump fixed to the transmission housing and drivingly connected to a torque converter pump. 
     In yet another example of the present invention, the multi-speed transmission further includes a first, second, and third speed sensor assembly each having a sensor and a ring, the sensor of the first speed sensor assembly is disposed on the transmission housing and the ring of the first speed sensor assembly is fixed to the input member, the sensor of the second speed sensor assembly is disposed on the center portion of the transmission housing and the ring of the second speed sensor assembly is fixed to the first of the four interconnecting members, and the sensor of the third speed sensor assembly is disposed on the rear portion of the transmission housing and the ring of the third speed sensor assembly is fixed to the output member. 
     Further features 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. 1A  is a schematic cross-sectional view of a front portion of an embodiment of a ten speed transmission according to the present invention; 
         FIG. 1B  is a schematic cross-sectional view of a rear portion of an embodiment of a ten speed transmission according to the present invention; 
         FIG. 2A  is a schematic cross-sectional view of a portion of an embodiment of a ten speed transmission according to the present invention; 
         FIG. 2B  is a schematic cross-sectional view of a shaft of a ten speed transmission according to the present invention; 
         FIG. 3A  is a schematic cross-sectional view of a portion of an embodiment of a ten speed transmission according to the present invention; 
         FIG. 3B  is a schematic cross-sectional view of a shaft of a ten speed transmission according to the present invention; 
         FIG. 4A  is a schematic cross-sectional view of a front portion of an embodiment of a ten speed transmission according to the present invention; and 
         FIG. 4B  is a schematic cross-sectional view of a rear portion of an embodiment of a ten speed transmission according to the present invention. 
     
    
    
     DETAILED DESCRIPTION 
     The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. 
     Referring to the drawings, wherein like reference numbers refer to like components, in  FIGS. 1A and 1B  a multi-speed transmission  10  is illustrated. The transmission  10  includes an input shaft or member  12  and an output shaft or member  14 . The input shaft or member  12  is connected to an engine (not shown) through a torque converter and locking clutch assembly  15 . The output shaft  14  is continuously connected with the final drive unit or transfer case (not shown). 
     In a preferred embodiment of the present invention, the transmission  10  includes four planetary gear sets  16 ,  18 ,  20  and  22 . The planetary gear sets  16 ,  18 ,  20  and  22  are connected between the input shaft or member  12  and the output shaft  14 . 
     The first planetary gear set  16  includes a sun gear member  24 , a ring gear member  26  and a carrier member  28  that rotatably supports a set of planet gears  30 . Sun gear member  24  is connected for common rotation with a first shaft or interconnecting member  32 . Ring gear member  26  is connected for common rotation with a second shaft or interconnecting member  34 . Carrier member  28  is connected for common rotation with a third shaft or member  36 . Planet gears  30  are each configured to intermesh with both the sun gear member  24  and the ring gear member  26 . 
     The second planetary gear set  18  includes a sun gear member  42 , a ring gear member  44  and a carrier member  46  that rotatably supports a set of planet gears  48 . Sun gear member  42  is connected for common rotation with the first shaft or interconnecting member  32 . Ring gear member  44  is connected for common rotation with a fourth shaft or interconnecting member  50 . Carrier member  46  is connected for common rotation with the input shaft or member  12 . Planet gears  48  are each configured to intermesh with both the sun gear member  42  and the ring gear member  44 . 
     The third planetary gear set  20  includes a sun gear member  52 , a ring gear member  54  and a carrier member  56  that rotatably supports a set of planet gears  58 . Sun gear member  52  is connected for common rotation with the fourth shaft or interconnecting member  50 . Ring gear member  54  is connected for common rotation with a fifth shaft or interconnecting member  60 . Carrier member  56  is connected for common rotation with a sixth shaft or interconnecting member  62 . Planet gears  58  are each configured to intermesh with both the sun gear member  52  and the ring gear member  54 . 
     The fourth planetary gear set  22  includes a sun gear member  72 , a ring gear member  74  and a carrier member  76  that rotatably supports a set of planet gears  78 . Sun gear member  72  is connected for common rotation with the fifth shaft or interconnecting member  60 . Ring gear member  74  is connected for common rotation with the third shaft or interconnecting member  36 . Carrier member  76  is connected for common rotation with the output shaft  14 . Planet gears  78  are each configured to intermesh with both the sun gear member  72  and the ring gear member  74 . 
     The transmission  10  includes a variety of torque-transmitting mechanisms or devices allowing for selective coupling of shafts or interconnecting members, members of the planetary gear sets and the transmission housing  100 . More specifically, transmission  10  includes a first clutch  80 , a second clutch  82 , a third clutch  84 , a fourth clutch  86 , a first brake  90 , and a second brake  92 . For example, first clutch  80  is selectively engageable to connect the fifth shaft or interconnecting member  60  to the input shaft or member  12 . Second clutch  82  is selectively engagable to connect the seventh shaft or interconnecting member  64  to the sixth shaft or interconnecting member  62 . Third clutch  84  is selectively engagable to connect the fourth shaft or interconnecting member  50  to the seventh shaft or interconnecting member  64 . Fourth clutch  86  is selectively engageable to connect the third shaft or interconnecting member  36  to the seventh shaft or interconnecting member  64 . First brake  90  is selectively engagable to connect the second shaft or interconnecting member  34  to the transmission housing  100  to restrict rotation of the second shaft or interconnecting member  34  relative to the transmission housing  100 . Second brake  92  is selectively engagable to connect the first shaft or interconnecting member  32  to a transmission housing  100  to restrict rotation of the first shaft or interconnecting member  32  relative to the transmission housing  100 . 
     The transmission  10  is capable of transmitting torque from the input shaft or member  12  to the output shaft  14  in at least ten forward torque ratios and one reverse torque ratio. Each of the forward torque ratios and the reverse torque ratios are attained by engagement of one or more of the torque-transmitting mechanisms (i.e. first clutch  80 , second clutch  82 , third clutch  84 , fourth clutch  86 , first brake  90  and second brake  92 ). Those skilled in the art will readily understand that a different speed ratio is associated with each torque ratio. Thus, at least ten forward speed ratios and at least one reverse speed ratio may be attained by the transmission  10 . 
     With continuing reference to  FIGS. 1A and 1B , the location of the brakes  90 ,  92  and clutches  80 ,  82 ,  84 ,  86  along the input shaft or member  12 , the fifth interconnecting member  60 , the output shaft  14 , and relative to the planetary gear sets  16 ,  18 ,  20 ,  22  will now be described. The first and second brakes  90 ,  92  are arranged coaxially with the fifth interconnecting member  60  and the first brake  90  is disposed axially rearward of the second brake  92 . The torque converter  15  is disposed at a front end  10 A of the transmission  10 . The first brake  90  is supported by both a center support assembly  102  and a rear cover  104  of the transmission housing  100 . The second brake  92  is supported by the center support assembly  102  of the transmission housing  100 . The first brake  90  includes an actuating assembly  90 A and a clutch pack  90 B. The actuating assembly  90 A of the first brake  90  includes a brake piston  106 , a first apply chamber  108 , a second apply chamber  110 , and a dam chamber  112 . The clutch pack  90 B of the first brake  90  includes a plurality of clutch plates  114  secured to the center support  102 . Upon pressurization of the apply chambers  108 ,  110 , the brake piston  106  is forced to compress the clutch plates  114  with a plurality of clutch plates  116  secured to the second shaft or interconnecting member  34 . The second brake  92  includes an actuating assembly  92 A and a clutch pack  92 B. The actuating assembly  92 A of the second brake  92  includes a brake piston  118 , an apply chamber  120 , and a spring  122 . The clutch pack  92 B of the second brake  92  includes a plurality of clutch plates  124  secured to the center support  102 . Upon pressurization of the apply chamber  120 , the brake piston  118  is forced to engage the clutch plates  124  with a plurality of clutch plates  126  secured to the first shaft or interconnecting member  32 . 
     The rear cover  104  of the transmission housing  100  further includes a first apply fluid passage  108 A and a second apply fluid passage  110 A. The first apply fluid passage  108 A is in communication with the first apply chamber  108  of the first brake  90 . The second apply fluid passage  110 A is in communication with the second apply chamber  110  of the first brake  90 . 
     The center support  102  of the transmission housing  100  further includes a first apply fluid passage  120 A in communication with the first apply chamber  120  of the second brake  92 . 
     The first, second, third, and fourth clutches  80 ,  82 ,  84 ,  86  are arranged coaxially with the input shaft or member  12 . The first clutch  80 , second clutch  82 , third clutch  84 , and fourth clutch  86  are disposed between a front wall  103  of the transmission housing  100  and the third planetary gear set  20 . More specifically, the first clutch  80  is adjacent the front wall  103 , the fourth clutch  86  is adjacent the third planetary gear set  20 , and the second clutch  82  is disposed adjacent the first clutch  80 . The third clutch  84  is disposed between the second and fourth clutches  82 ,  86 . 
     The first clutch  80  includes an actuating assembly  80 A and a clutch pack  80 B. The actuating assembly  80 A of the first clutch  80  includes an apply chamber  130 , a dam chamber  132  and a piston  134 . The actuating assembly  80 A is supported by the input shaft or member  12 . The clutch pack  80 B includes a plurality of clutch plates  135  fixed for common rotation with the input shaft or member  12  interweaved with a plurality of clutch plates  137  fixed for common rotation with the fifth shaft or interconnecting member  60 . The piston  134  of the actuating assembly  80 A engages the clutch pack  80 B to force the plurality of alternating friction disks together to interconnect the input shaft or member  12  with the ring gear  54  of the third planetary gear set  20 . 
     The second clutch  82  includes an actuating assembly  82 A and a clutch pack  82 B. The actuating assembly  82 A of the first clutch  82  includes an apply chamber  140 , a dam chamber  142  and a piston  144 . The actuating assembly  82 A is supported by the seventh shaft or interconnecting member  64 . The clutch pack  82 B includes a plurality of clutch plates  145  fixed for common rotation with the seventh shaft or interconnecting member  64  interweaved with a plurality of clutch plates  147  fixed for common rotation with e sixth shaft or interconnecting member  62 . The piston  144  of the actuating assembly  82 A engages the clutch pack  82 B to interconnect the seventh shaft or interconnecting member  64  with the carrier member  56  of the third planetary gear set  20 . 
     The third clutch  84  includes an actuating assembly  84 A and a clutch pack  84 B. The actuating assembly  84 A of the first clutch  84  includes an apply chamber  150 , a dam chamber  152  and a piston  154 . The actuating assembly  84 A is supported by the seventh shaft or interconnecting member  64 . The clutch pack  84 B includes a plurality of clutch plates  155  fixed for common rotation with the seventh shaft or interconnecting member  64  interweaved with a plurality of clutch plates  157  fixed for common rotation with the fourth shaft or interconnecting member  50 . The piston  154  of the actuating assembly  84 A engages the clutch pack  84 B to interconnect the seventh shaft or interconnecting member  64  with the sun gear  52  of the third planetary gear set  20  and the ring gear  44  of the second planetary gear set  18 . 
     The fourth clutch  86  includes an actuating assembly  86 A and a clutch pack  86 B. The actuating assembly  86 A of the first clutch  86  includes an apply chamber  160 , a dam chamber  162  and a piston  164 . The actuating assembly  86 A is supported by the seventh shaft or interconnecting member  64 . The clutch pack  86 B includes a plurality of clutch plates  165  fixed for common rotation with the seventh shaft or interconnecting member  64  interweaved with a plurality of clutch plates  167  fixed for common rotation with the third shaft or interconnecting member  36 . The piston  164  of the actuating assembly  86 A engages the clutch pack  86 B to interconnect the seventh shaft or interconnecting member  64  with the carrier member  28  of the first planetary gear set  16  and the ring gear  74  of the fourth planetary gear set  22 . 
     Referring now to  FIGS. 2A and 2B  with continuing reference to  FIGS. 1A and 1B , a portion of the transmission  10  is illustrated including the input shaft or member  12 , the fifth shaft or interconnecting member  60 , and the seventh shaft or interconnecting member  64  and further includes a hydraulic control circuit  200  in accordance with an embodiment of the present invention. The hydraulic control circuit  200  contains hydraulic fluid that is pressurized by a hydraulic fluid pump (not shown) and generates hydraulic control signals to actuate the first, second, third, and fourth clutches  80 ,  82 ,  84 ,  86  and first and second brakes  90 ,  92 . The hydraulic control circuit  200  includes four bores disposed in the input shaft or member  12 : a first bore  210 , a second bore  212 , a third bore  214 , and a fourth bore  216 . More specifically, the first, second, third, and fourth bores  210 ,  212 ,  214 ,  216  are disposed longitudinally in the input shaft or member  12 . Each bore  210 ,  212 ,  214 ,  216  is disposed 90° from the adjacent bore  210 ,  212 ,  214 ,  216  as shown in  FIG. 2B . The hydraulic control circuit  200  also includes four annular channels  218 ,  220 ,  222 ,  224  formed by a sleeve shaft  226 , the input shaft or member  12 , and a plurality of input shaft or member seals  228 A-E. The sleeve shaft  226  is fixedly attached to the front support  105  of the transmission housing  100 . The first annular channel  218  is defined by the outer surface of the input shaft or member  12 , the inner surface of the sleeve shaft  226  and the side surfaces of a first input shaft or member seal  228 A and a second input shaft or member seal  228 B. The second annular channel  220  is defined by the outer surface of the input shaft or member  12 , the inner surface of a sleeve shaft  226  and the side surfaces of the second input shaft or member seal  228 B and a third input shaft or member seal  228 C. The third annular channel  222  is defined by the outer surface of the input shaft or member  12 , the inner surface of a sleeve shaft  226  and the side surfaces of the third input shaft or member seal  228 C and the fourth input shaft or member seal  228 D. The fourth annular channel  224  is defined by the outer surface of the input shaft or member  12 , the inner surface of a sleeve shaft  226  and the side surfaces of the fourth input shaft or member seal  228 D and the fifth input shaft or member seal  228 E. 
     The four input shaft or member seals  228 A-E are disposed coaxially with the input shaft or member  12  between the sleeve shaft  226  and the input shaft or member  12  and seals a first end  12 A of the input shaft or member  12 . The second and fourth annular channels  220 ,  224  communicate, respectively, with the first and third bores  210 ,  214  through first and third ports  230 ,  232  formed in the first end  12 A of the input shaft or member  12 . 
     The first bore  210  contains a first plug  234  fixedly disposed at a second end  12 B of the input shaft or member  12  to seal the first bore  210 . The first bore  210  communicates with the apply chamber  140  of the second clutch  82  (see  FIGS. 1A and 1B ) through a first apply port  236  of the input shaft or member  12 , a fifth annular channel  238 , a first apply side port  240  of the fifth shaft or interconnecting member  60 , and a first apply side port  242  of the seventh shaft or interconnecting member  64 . The fifth annular channel  238  is formed by the outer surface of the input shaft or member  12 , the inner surface of the fifth shaft or interconnecting member  60  and the side surfaces of a first and a second intermediate seal  244 A,  244 B. 
     The third bore  214  contains a second plug  246  fixedly disposed at the second end  12 B of the input shaft or member  12  to seal the third bore  214 . The third bore  214  communicates with the apply chamber  160  of the fourth clutch  86  (see  FIGS. 1A and 1B ) through a second apply port  248  of the input shaft or member  12 , a sixth annular channel  250 , a second apply side port  252  of the fifth shaft or interconnecting member  60 , and a second apply side port  254  of the seventh shaft or interconnecting member  64 . The sixth annular channel  250  is formed by the outer surface of the input shaft or member  12 , the inner surface of the fifth shaft or interconnecting member  60  and the side surfaces of a third and a fourth intermediate seal  244 C,  244 D. 
     The front support  105  of the transmission housing  100  includes a first, second, third, and fourth apply fluid passages  256 ,  258 ,  260 ,  262 , and a dam fluid passage  264 . The first apply fluid passage  256  communicates with the apply chamber  130  of the first clutch  80  (see  FIGS. 1A and 1B ) through a seventh annular channel  266  and a third apply port  268  of the input shaft or member  12 . The seventh annular channel  266  is formed by the outer surface of the front support  105 , the inner surface of the input shaft or member  12 , and the side surfaces of a fifth and sixth intermediate seal  244 E,  244 F. The second apply fluid passage  258  communicates with the first annular channel  218 . The third apply fluid passage  258  communicates with the second annular channel  220 . The fourth apply fluid passage  262  communicates with the fourth annular channel  224 . The dam fluid passage  264  communicates with the dam chamber  132  of the first clutch  80  (see  FIGS. 1A and 1B ) through an eighth annular channel  270  and a fourth apply port  272  of the input shaft or member  12 . The eighth annular channel  270  is defined by the outer surface of the front support  105 , the inner surface of the input shaft or member  12 , and the side surfaces of the sixth and a seventh intermediate seal  244 F,  244 G. 
     Referring now to  FIGS. 3A and 3B  with continuing reference to  FIGS. 1A and 1B , a portion of the transmission  10  is illustrated including the input shaft or member  12  turned 90° from the position shown in  FIG. 2A , the fifth shaft or interconnecting member  60 , and the seventh shaft or interconnecting member  64  and further includes a hydraulic control circuit  200  in accordance with an embodiment of the present invention. 
     The second bore  212  contains a third plug  273  fixedly disposed at the second end  12 B of the input shaft or member  12  to seal the second bore  212 . The second bore  220  communicates with the dam fluid passage  264  of the front support  105  through a first dam port  272  and the third annular channel  220 . The second bore  220  also communicates with the dam chamber  142  of the second clutch  82  (see  FIGS. 1A and 1B ) through the second dam port  274 , a ninth annular channel  276 , a first dam side port  278  of the fifth shaft or interconnecting member  60 , and a first dam side port  280  of the seventh shaft or interconnecting member  64 . The ninth annular channel  276  is formed by the outer surface of the input shaft or member  12 , the inner surface of the fifth shaft or interconnecting member  60  and the side surfaces of the second and a ninth intermediate seal  244 B,  244 H. The second bore  220  also communicates with the dam chamber  152  of the third clutch  84  (see  FIGS. 1A and 1B ) through the third dam port  282 , a tenth annular channel  284 , a second dam side port  286  of the fifth shaft or interconnecting member  60 , and a second dam side port  288  of the seventh shaft or interconnecting member  64 . The tenth annular channel  284  is formed by the outer surface of the input shaft or member  12 , the inner surface of the fifth shaft or interconnecting member  60  and the side surfaces of a tenth and the third intermediate seal  244 I,  244 C. The second bore  220  also communicates with the dam chamber  162  of the fourth clutch  86  (see  FIGS. 1A and 1B ) through the third dam port  290 , an eleventh annular channel  292 , a third dam side port  294  of the fifth shaft or interconnecting member  60 , and a third dam side port  296  of the seventh shaft or interconnecting member  64 . The eleventh annular channel  292  is formed by the outer surface of the input shaft or member  12 , the inner surface of the fifth shaft or interconnecting member  60  and the side surfaces of the fourth and an eleventh intermediate seal  244 D,  244 J. 
     The fourth bore  216  contains a fourth plug  298  fixedly disposed at the second end  12 B of the input shaft or member  12  to seal the fourth bore  216 . The fourth bore  214  communicates with the apply chamber  150  of the third clutch  84  (see  FIGS. 1A and 1B ) through a third apply port  300  of the input shaft or member  12 , a twelfth annular channel  302 , a third apply side port  304  of the fifth shaft or interconnecting member  60 , and a third apply side port  306  of the seventh shaft or interconnecting member  64 . The twelfth annular channel  302  is formed by the outer surface of the input shaft or member  12 , the inner surface of the fifth shaft or interconnecting member  60  and the side surfaces of the ninth and tenth intermediate seal  244 H,  244 I. 
     Referring now to  FIGS. 4A and 4B , another example of a transmission  310  of the present invention is illustrated and will now be described. In  FIGS. 4A and 4B , the reference numbers from  FIGS. 1A and 1B  are carried over where appropriate. The first, second, third, and fourth clutches  380 ,  382 ,  384 ,  386  are arranged coaxially with the input shaft or member  12 . The first clutch  380 , second clutch  382 , third clutch  384 , and fourth clutch  386  are disposed between the front wall  103  of the transmission housing  100  and the third planetary gear set  20 . More specifically, the first clutch  380  is adjacent the front wall  103 , the fourth clutch  386  is adjacent the third planetary gear set  20 , and the second clutch  382  is disposed adjacent the first clutch  380 . The third clutch  384  is disposed between the second and fourth clutches  382 ,  386 . 
     The first clutch  380  includes an actuating assembly  380 A and a clutch pack  380 B. The actuating assembly  380 A of the first clutch  380  includes an apply chamber  430 , a dam chamber  432  and a piston  434 . The actuating assembly  380 A is supported by the input shaft or member  12 . The clutch pack  380 B includes a plurality of alternating friction disks or rings fixed for common rotation with either the input shaft or member  12  or the fifth shaft or interconnecting member  60 . The piston  434  of the actuating assembly  380 A engages the clutch pack  380 B to force the plurality of alternating friction disks together to interconnect the input shaft or member  12  with the ring gear  54  of the third planetary gear set  20 . 
     The second clutch  382  includes an actuating assembly  382 A and a clutch pack  382 B. The actuating assembly  382 A of the first clutch  382  includes an apply chamber  440 , a dam chamber  442  and a piston  444 . The actuating assembly  382 A is supported by the seventh shaft or interconnecting member  64 . The clutch pack  382 B includes a plurality of alternating friction disks or rings fixed for common rotation with either the seventh shaft or interconnecting member  64  or the fourth shaft or interconnecting member  50 . The piston  444  of the actuating assembly  382 A engages the clutch pack  382 B to interconnect the seventh shaft or interconnecting member  64  with the sun gear  52  of the third planetary gear set  20  and the ring gear  44  of the second planetary gear set  18 . 
     The third clutch  384  includes an actuating assembly  384 A and a clutch pack  384 B. The actuating assembly  384 A of the first clutch  384  includes an apply chamber  450 , a dam chamber  452  and a piston  454 . The actuating assembly  384 A is supported by the seventh shaft or interconnecting member  64 . The clutch pack  384 B includes a plurality of alternating friction disks or rings fixed for common rotation with either the seventh shaft or interconnecting member  64  or the sixth shaft or interconnecting member  62 . The piston  454  of the actuating assembly  384 A engages the clutch pack  384 B to interconnect the seventh shaft or interconnecting member  64  with the carrier member  56  of the third planetary gear set. The clutch pack  384 A is disposed such that the piston  444  of the actuating assembly  382 A of the second clutch  382  passes through the clutch pack  384 A. 
     The fourth clutch  386  includes an actuating assembly  386 A and a clutch pack  386 B. The actuating assembly  386 A of the first clutch  386  includes an apply chamber  460 , a dam chamber  462  and a piston  464 . The actuating assembly  386 A is supported by the seventh shaft or interconnecting member  64 . The clutch pack  386 B includes a plurality of alternating friction disks or rings fixed for common rotation with either the seventh shaft or interconnecting member  64  or the third shaft or interconnecting member  36 . The piston  464  of the actuating assembly  386 A engages the clutch pack  386 B to interconnect the seventh shaft or interconnecting member  64  with the carrier member  28  of the first planetary gear set  16  and the ring gear  74  of the fourth planetary gear set  22 . 
     With continuing reference to  FIGS. 4A and 4B , the locations for three speed sensor assemblies  510 ,  520 ,  530  in the transmission  310  will now be described. The speed sensor assemblies  510 ,  520 ,  530  each include a speed sensor  512 ,  522 ,  532  and a speed sensor ring  514 ,  524 ,  534 . The speed sensors  512 ,  522 ,  532  are fixedly attached to the transmission housing  100 . The speed sensors  512 ,  522 ,  532  are conventional speed sensors such as Hall Effect sensors or variable reluctance sensors and the like. The speed sensor rings  514 ,  524 ,  534  are in close proximity to the speed sensors  512 ,  522 ,  532  and are fixedly attached to one of the rotatable shafts or members of transmission  310 . The speed sensors  512 ,  522 ,  532  detect the presence of the respective speed sensor ring  514 ,  523 ,  534  to count the revolutions of the shaft or interconnecting member to which the speed sensor ring  514 ,  524 ,  534  is attached. Alternatively, the speed sensor rings  514 ,  524 ,  534  are magnetic strips or toothed portions of shafts having magnetic material formed in the rotatable shafts or members of transmission  310 . 
     For example, the first speed sensor  512  is fixedly attached to the transmission housing  100  and the first speed sensor ring  514  is fixedly disposed on the input shaft or member  12 . The second speed sensor  522  is fixedly disposed on center support  102  of the transmission housing  100  and the second speed ring  524  is fixedly disposed on the first shaft or interconnecting member  32 . The third speed sensor  532  is fixedly disposed on the rear cover  104  transmission housing  100  and the third speed sensor ring  534  is fixedly disposed on the output shaft  14 . Alternatively, the third speed sensor  532  is mounted to the inside surface of the piston  106  of the first brake  90   
     With continuing reference to  FIGS. 4A and 4B , the transmission  310  includes an off-axis oil pump  600 . The off-axis fluid pump assembly  600  includes a transmission fluid pump  602 , a drive gear or pulley member  604 , a driven gear or pulley member  606 , a pump shaft  608  and a chain or belt  610 . The transmission fluid pump  602  is fixedly attached to the transmission housing  100  or a similar stationary member along an axis “I” that is offset a predefined radial distance “d” from the axis “i” of the input shaft or member  12 . The drive gear or pulley member  604  is fixedly attached for common rotation with the torque converter  15 . The driven gear or pulley member  606  is fixedly connected for common rotation with the pump shaft  608 . The chain or belt  610  engages both the drive gear or pulley member  604  and the driven gear or pulley member  606  to transfer driving torque from the input shaft or member  12  to the pump shaft  608 . The pump shaft  608  transfers the driving torque produced in the chain or belt  610  to fluid pump  602 . A stepped ratio may be used between the drive gear or pulley member  604  and the driven gear or pulley member  606  to reduce the amount of energy transferred to the transmission fluid pump  602  thus resulting in a more efficient transmission  10 . The fluid pump assembly  600  provides fluid pressure and flow for transmission  10  function. Driving the fluid pump assembly  600  by a ratio connection allows the transmission  10  to more efficiently provide fluid pressure and flow. 
     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.

Technology Classification (CPC): 5