JP2008082345A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To positively rigidly connect an input shaft to a seal plate in an automatic transmission, and to easily carry out assembly of a hydraulic servo mechanism by axially compacting the hydraulic servo mechanism, that is to say, the automatic transmission. <P>SOLUTION: The hydraulic servo mechanism is provided with a piston 44 provided slidably in an axial direction in a hub member 32h connected to a turbine shaft 17, and the seal plate 46 connected to the turbine shaft 17, forming a clutch oil pressure chamber 33a in cooperation with one part of the piston 44, and capable of receiving the piston 44 at a retreat position. An inner circumference female screw part 50b formed on an inner circumference part of the seal plate 46 is screwed on an outer circumference male screw part 50a formed on an outer circumference part of a connection portion of the turbine shaft 17 with the seal plate 46 via rotation around an axis of the seal plate 46, and the seal plate 46 is connected to a turbine shaft 17. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an automatic transmission, and more particularly to an improved structure for connecting a seal plate of a hydraulic servo mechanism for fastening a multi-plate fastening mechanism to an input shaft in a clutch or the like.

  Conventionally, an automatic transmission mounted on an automobile is provided with a plurality of clutches and brakes. As a clutch, a hub member having an inner peripheral hub portion connected to an input shaft is provided on an outer peripheral side of the inner peripheral hub portion. A drum member having an outer peripheral drum portion arranged, a multi-plate fastening mechanism provided between the inner peripheral hub portion and the outer peripheral drum portion, a hydraulic servo mechanism for fastening the multi-plate fastening mechanism, and this hydraulic servo mechanism, A piston member that presses the multi-plate fastening mechanism, a hydraulic chamber for driving the piston member, and a return spring that returns the piston member to the retracted position are well known.

  In the automatic transmission of Patent Document 1, in the hydraulic servo mechanism of the clutch shown in FIG. 17, the piston member is provided on the cylindrical power transmission member connected to the drum member and the drum member so as to be slidable in the axial direction. A hydraulic chamber is formed in a portion surrounded by the drum member and the cylindrical power transmission member, a spring retainer is provided on the opposite side of the piston member in the axial direction with respect to the hydraulic chamber, and the spring retainer is attached to the cylindrical power transmission member. The stopper spring, which is fitted in a fitting shape and engaged with the cylindrical power transmission member in an outer fitting shape, is locked so as not to move in the opposite axial direction, and a return spring is provided between the spring retainer and the piston member. It is intervened.

  Here, in the clutch hydraulic servomechanism, the applicant of the present application has a piston member slidably provided in the axial direction on a hub member connected to the input shaft, and a return spring is interposed between the piston member and the hub member. In place of the spring retainer, a seal plate is provided which is connected to the input shaft and forms a hydraulic chamber for driving the piston member in cooperation with a part of the piston member and can receive the piston member in the retracted position. Things are being put into practical use.

JP 2000-220703 A

  As described above, in the clutch hydraulic servomechanism, the piston member is slidably provided in the axial direction on the hub member connected to the input shaft, and the seal plate is connected to the input shaft to cooperate with a part of the piston member. In an automatic transmission that works to form a hydraulic chamber for driving a piston member, the seal plate receives a very large hydraulic pressure, and thus it is necessary to securely connect the seal plate to the input shaft securely.

  Therefore, as in Patent Document 1 in which the spring retainer is locked to the cylindrical power transmission member with a stopper ring, the seal plate is connected to the piston member with respect to the piston member by a stopper ring that is externally engaged with the input shaft. It is conceivable to lock in the axially opposite side so as not to move. However, since the seal plate and the stopper ring must be provided in parallel in the axial direction, the axial width of the stopper ring is required to ensure that the seal plate that receives a large hydraulic pressure can be securely locked. Therefore, the clutch equipped with the hydraulic servo mechanism, that is, the automatic transmission cannot be made compact in the axial width.

  Therefore, it is conceivable to omit the stopper ring and weld the seal plate to the input shaft. However, when assembling this hydraulic servo mechanism, welding the seal plate to the input shaft after assembling the return spring is a welding operation with this seal plate biased by the return spring. Assembling becomes difficult. When a predetermined rotating member that rotates relative to the seal plate is provided adjacently and a thrust bearing is mounted between the rotating member and the seal plate, the stopper ring becomes an obstacle and the thrust ring There is also a possibility that the bearing cannot be easily and securely mounted.

  On the other hand, when releasing the drive hydraulic pressure of the piston member, the piston member biased by the return spring is received by the seal plate, but at this time, it is necessary to properly adjust the clearance between the plates of the multi-plate fastening mechanism, By doing so, an appropriate open state of the multi-plate fastening mechanism can be created, and the responsiveness can be improved by making the piston member an appropriate stroke. However, as described above, when the seal plate is locked by the stopper ring, when the clearance between the plates of the multi-plate fastening mechanism is adjusted appropriately, the plate, hub member, stopper ring of the multi-plate fastening mechanism For example, the thickness in the axial direction needs to be finely adjusted, and this clearance adjustment operation becomes very complicated.

  An object of the present invention is to reliably and firmly connect a seal plate to an input shaft in an automatic transmission, to make the hydraulic servo mechanism, that is, the automatic transmission compact in the axial direction, and to assemble the hydraulic servo mechanism. And so on.

  The automatic transmission according to claim 1 includes an input shaft, a hub member having an inner peripheral hub portion connected to the input shaft, and a drum member having an outer peripheral drum portion disposed on the outer peripheral side of the inner peripheral hub portion. In the automatic transmission comprising a multi-plate fastening mechanism provided between the inner peripheral hub portion and the outer peripheral drum portion and a hydraulic servo mechanism having a piston member for fastening the multi-plate fastening mechanism, the hydraulic servo A piston member of the mechanism is provided on the hub member so as to be slidable in the axial direction, and the hydraulic servo mechanism is coupled to the input shaft and cooperates with a part of the piston member to drive a hydraulic pressure for driving the piston member. A seal plate that can form a chamber and can receive the piston member at the retracted position is provided, and is formed on the inner peripheral female screw portion formed on the inner peripheral portion of the seal plate and on the outer peripheral portion of the seal plate connecting portion of the input shaft. Is A seal plate having an outer peripheral male screw, and an inner peripheral female screw portion screwed onto the outer peripheral male screw in an outer fitting manner through rotation around the axis of the seal plate, and the seal plate is connected to the input shaft A connection structure is provided.

  In this automatic transmission, the hub member, the drum member, and the multi-plate fastening mechanism are mainly applied to a clutch, but application to a brake is also conceivable. In this automatic transmission, when hydraulic pressure is supplied to the hydraulic chamber in the hydraulic servo mechanism, the piston member is driven by this hydraulic pressure to press the multi-plate fastening mechanism, the multi-plate fastening mechanism is fastened, and the input shaft The driving force can be transmitted from the hub member to the drum member via the multi-plate fastening mechanism.

  In the hydraulic servo mechanism, a return spring that is interposed between the hub member and the piston member and biases the piston member to the retracted position can be provided. When the hydraulic pressure is released from the hydraulic chamber, the return spring biases The piston member thus received is received at the retracted position by the seal plate, the multi-plate fastening mechanism is released, and the driving force of the input shaft cannot be transmitted from the hub member to the drum member via the multi-plate fastening mechanism.

  In particular, due to the seal plate connection structure, an inner peripheral female screw portion is formed on the inner peripheral portion of the seal plate, and an outer peripheral male screw is formed on the outer peripheral portion of the seal plate connection portion of the input shaft. The screw portion is screwed into an outer fitting shape through rotation around the axis of the seal plate, and the seal plate is connected to the input shaft. Therefore, the seal plate receives very large oil pressure, but the seal plate can be securely and firmly connected to the input shaft, and the conventional stopper ring is not required, so the hydraulic servo mechanism is compact in the axial direction. In addition, after the return spring is assembled, the seal plate in a state of being urged by the return spring can be easily assembled, so that the hydraulic servo mechanism can be easily assembled.

The following configuration can be adopted as a dependent claim of claim 1.
The seal plate connecting portion of the input shaft has a small diameter portion in which the outer peripheral male screw portion is formed, and a large diameter portion having a stepped portion as a boundary in the small diameter portion. A washer member interposed between the attachment portion and the seal plate is provided, and the seal plate is fastened to the stepped portion via the washer member in a pressed state (Claim 2). A plurality of tool insertion concave holes into which a tool for rotating the seal plate can be inserted are formed in the disc portion of the seal plate. A predetermined rotating member is provided adjacent to the seal plate on the opposite side of the hydraulic chamber in the axial direction, and a thrust bearing is mounted between the rotating member and the seal plate.

  According to the automatic transmission of the first aspect, the hydraulic servo mechanism includes a piston member that is slidable in the axial direction on a hub member that is connected to the input shaft, and a part of the piston member that is connected to the input shaft. A hydraulic pressure chamber for driving the piston member and a seal plate capable of receiving the piston member at the retracted position in cooperation with the inner peripheral female screw portion formed on the inner peripheral portion of the seal plate, and the input shaft The outer peripheral male screw formed on the outer peripheral portion of the seal plate coupling portion, and the inner peripheral female screw portion is screwed to the outer peripheral male screw in an outer fitting manner through rotation around the axis of the seal plate, Since the seal plate is connected to the input shaft, the seal plate is subjected to very large hydraulic pressure, but the seal plate can be securely and firmly connected to the input shaft. The hydraulic servo mechanism, that is, the automatic transmission can be made compact in the axial direction, and the seal plate in the state of being biased by the return spring can be easily assembled after the return spring is assembled. Therefore, the hydraulic servomechanism can be easily assembled.

  According to the automatic transmission of claim 2, the seal plate coupling portion of the input shaft has a small diameter portion in which an outer peripheral male screw portion is formed, and a large diameter portion having a stepped portion as a boundary in the small diameter portion, The seal plate connection structure includes a washer member interposed between the stepped portion and the seal plate, and the seal plate is fastened to the stepped portion via this washer member so that the seal plate is input. It can be reliably positioned and connected to the seal plate connecting part of the shaft.Here, by preparing a plurality of washer members having different axial thicknesses as washer members, when assembling the hydraulic servo mechanism, By adopting a washer member with an appropriate thickness, the clearance between the plates of the multi-plate fastening mechanism is properly adjusted while the piston member is received by the seal plate and positioned at the retracted position. It can be. By simply changing the thickness of the washer member, the thickness can be changed by preparing a plurality of washer members having different thicknesses in advance, so that the clearance adjustment operation can be greatly simplified.

  According to the automatic transmission of the third aspect, since the plurality of tool insertion concave holes into which the tool for rotating the seal plate can be inserted are formed in the disc portion of the seal plate, when the seal plate is assembled, Insert a tool into a plurality of tool insertion concave holes in the disc part, rotate the seal plate with the tool, and screw the inner peripheral female screw part into the outer peripheral male screw easily and securely into the outer fitting shape, The seal plate can be connected to the input shaft.

  According to the automatic transmission of the fourth aspect, the predetermined rotation member is provided adjacent to the seal plate on the opposite side in the axial direction from the hydraulic chamber, and a thrust bearing is mounted between the rotation member and the seal plate. Therefore, the rotational resistance that interacts with the rotating member and the seal plate can be eliminated, but the conventional stopper ring can be omitted, so that the thrust bearing can be easily and securely mounted between the rotating member and the seal plate. Can do.

  In particular, the automatic transmission according to the present invention includes a piston member in which a hydraulic servo mechanism is slidably provided in an axial direction on a hub member connected to an input shaft, and a part of the piston member connected to the input shaft. A seal plate that cooperates to form a hydraulic chamber for driving the piston member and can receive the piston member in the retracted position is provided on the outer peripheral male screw formed on the outer peripheral portion of the seal plate connecting portion of the input shaft. A seal plate coupling structure in which an inner circumferential female screw portion formed on the inner circumferential portion of the seal plate is screwed into an outer fitting shape through rotation around the axis of the seal plate, and the seal plate is coupled to the input shaft. It is a thing.

  The automatic transmission 1 is applied to a horizontal engine, and has, as main components, a torque converter 10 driven by the engine and a transmission mechanism 20 to which an output rotation of the torque converter 10 is input. The output rotation of the transmission mechanism 20 is input to the differential device 60 via the intermediate transmission mechanism 50. In the following description, the torque converter 10 side will be described as the front, and the anti-torque converter 10 side will be described as the rear.

  The torque converter 10 includes a case 11 connected to the engine output shaft 2, a pump 12 fixed in the case 11, and a pump 12 that is disposed opposite to the pump 12 via hydraulic oil. A turbine 13 to be driven, a stator 15 interposed between the pump 12 and the turbine 13 and supported by the transmission case 3 via a one-way clutch 14 to increase torque, the case 11 and the turbine 13 and a lock-up clutch 16 that directly connects the engine output shaft 2 and the turbine 13 via the case 11. The rotation of the turbine 13 is output to the transmission mechanism 20 via the turbine shaft 17.

An oil pump 18 that is driven by the engine output shaft 2 via the case 11 of the torque converter 10 is disposed on the opposite side of the torque converter 10 from the engine.
The transmission mechanism 20 includes a first planetary gear mechanism 21 disposed on the torque converter 10 side, a second planetary gear mechanism 22 disposed on the anti-torque converter 10 side, and third and third planets disposed between them. 4 planetary gear mechanisms 23, 24, and further arranged in order from the torque converter 10 side as a plurality of frictional engagement elements such as clutches and brakes for switching the power transmission path composed of these planetary gear mechanisms 21-24. The first to third clutches 31 to 33 and the first and second brakes 41 and 42 that are sequentially arranged on the counter-torque converter 10 side as well, so that the forward 1st to 6th speeds and the reverse speed can be obtained. It has become.

  The first to fourth planetary gear mechanisms 21 to 24 all have sun gears 21a to 24a, a plurality of pinions 21b to 24b meshed with these sun gears 21a to 24a, and carriers that support these pinions 21b to 24b. 21c to 24c and ring gears 21d to 24d engaged with the pinions 21b to 24b.

  In the first planetary gear mechanism 21, the sun gear 21 a is fixed to the transmission case 3, the carrier 21 c is connected to the hub portion of the first clutch 31, and the ring gear 21 d is connected to the turbine shaft 17 and the hub portion of the second clutch 32. ing. In the second planetary gear mechanism 22, the sun gear 22 a is fixed to the transmission case 3, the ring gear 22 d is connected to the turbine shaft 17, and the carrier 22 c is connected to the hub portion of the third clutch 33.

  In the third planetary gear mechanism 23, the sun gear 23a is connected to the drum portion of the third clutch 33 and the second brake 42, the carrier 3c is connected to the hub portion of the second clutch 32 and the first brake 41, and the ring gear 23d is The four planetary gear mechanism 4 is connected to the carrier 4c. In the fourth planetary gear mechanism 24, the sun gear 24a is coupled to the drum portion of the first clutch 31, the ring gear 24d is coupled to the carrier 3c of the third planetary gear mechanism 23 and coupled to the first brake 41, and the carrier 24c is The ring gear 23 d of the three planetary gear mechanism 23 is coupled to the output gear 25 to the intermediate transmission mechanism 50. The rotation of the output gear 25 is input to the differential device 60 via the intermediate transmission mechanism 50 and drives the left and right axles 61 and 62. Table 1 shows the relationship between the operating states of the clutches 31 to 33 and the brakes 41 and 42 and the gear positions. However, ○ mark indicates fastening.

Next, the first planetary gear mechanism 21 and the first and second clutches 31 and 32 will be described.
As shown in FIGS. 2 and 3, a pump case 18 a for the pump 18 is disposed on the rear side of the case member 11 of the torque converter 10, and the outer periphery of the case member 11 and the pump case 18 a is the transmission case 3. The sleeve member 4 is externally fitted to the turbine shaft 17 so as to be relatively rotatable in the vicinity of the rear side of the torque converter 10 and fixed to the front end by a plurality of bolts 3a and 3b.

  The sleeve member 4 is integrally formed with an annular pump cover member 4a. The pump cover member 4a is connected to the transmission case 3 through a pump case 18a and is rotationally restrained. The pump cover member 4a includes a pump cover member 4a. A hydraulic oil passage 4b to which pressurized hydraulic oil supplied from 18 (hydraulic hydraulic oil) is supplied is formed.

Next, the first planetary gear mechanism 21 will be described.
The first planetary gear mechanism 21 is a constant reduction type planetary gear mechanism in which the sun gear 21a does not rotate, the rotation of the turbine shaft 17 is input to the ring gear 21d, the carrier 21c is decelerated and rotated, and power is output from the carrier 21c. is there. The sun gear 21 a of the first planetary gear mechanism 21 is externally fitted to the rear part of the sleeve member 4 by spline fitting and is rotationally restrained. The carrier 21 c that supports the plurality of pinions 21 b is connected to the sleeve via the ball bearing 5. The member 4 is rotatably supported. On the rear side of the first planetary gear mechanism 21, the annular member 6 is fitted and fixed to the flange-like portion 17 a of the turbine shaft 17, and the annular plate 7 is externally attached to the step on the front surface of the annular member 6 near the inner periphery. The rear end portion of the ring gear 21 d of the first planetary gear mechanism 21 is joined to the outer peripheral portion of the annular plate 7.

Next, the first clutch 31 will be described.
The first clutch 31 is an annular one having a multi-plate clutch portion 31 a disposed on the outer peripheral side of the first planetary gear mechanism 21. The rotation of the carrier 21c of the first planetary gear mechanism 21 is switched between a fastening state where the rotation is transmitted to the sun gear 24a of the fourth planetary gear mechanism 24 and an open state where the rotation is not transmitted. The first clutch 31 includes a hub member 31h, a drum member 31d, a plurality of friction plates 30a whose inner peripheral portion is spline-engaged with an outer peripheral spline of the hub portion 31b of the hub member 31h, and a drum portion of the drum member 31d. A plurality of friction plates 30b whose outer peripheral portion is spline-engaged with the inner peripheral side spline of 31e and arranged alternately with the plurality of friction plates 30a, and the multi-plate clutch portion 31a are engaged (connected state) and released (divided) For example, a hydraulic servo mechanism 33 for switching to a state).

  A friction lining material is provided on both front and rear surfaces of the friction plate 30a, and a plurality of radial oil grooves are formed in the friction lining material. The hydraulic oil (lubricating oil) that has flowed into the outer peripheral side spline of the hub portion 31b of the hub member 31h flows into the lubricating oil groove and lubricates and cools the plurality of friction plates 30a, 30b.

  The hub member 31h includes a cylindrical portion 21e integrally formed on the outer peripheral end portion of the carrier 21c, a hub portion 31b externally fitted to the cylindrical portion 21e by spline fitting, and an integral formation with the hub portion 31b. An annular member having an L-shaped cross section is formed from the annular locking portion 31c. The locking portion 31c receives the plurality of friction plates 30a, 30b when the multi-plate clutch portion 31a is fastened by the piston 34 of the hydraulic servo mechanism 33, and the friction plates 30a at both ends in the front-rear direction are only on one side. Friction lining material is provided.

  The drum member 31d is a bottomed cylindrical annular member that covers the outer peripheral side of the first and second clutches 31 and 32 and the rear side of the second clutch 32, and a drum portion 31e is provided at a front end side portion of the drum member 31d. The inner peripheral end portion of the drum member 31d formed is joined to the outer peripheral end portion of the flange-shaped portion of the first power transmission member 35 coupled to the sun gear 24a of the fourth planetary gear mechanism 24, and the hub portion 31b from the carrier 21c. Rotational driving force transmitted to the drum portion 31e via is transmitted to the sun gear 24a of the fourth planetary gear mechanism 24.

Next, the hydraulic servo mechanism 33 will be described.
The hydraulic servo mechanism 33 includes a piston 34, a clutch hydraulic chamber 33a, a balance hydraulic chamber 33b, a plurality of return springs 33c, and the like. The clutch hydraulic chamber 33a and the balance hydraulic chamber 33b are disposed between the first planetary gear mechanism 21 and the pump cover member 4a and on the inner peripheral side of the first clutch 31.

  The piston 34 has a piston portion 34a on the inner peripheral side, a cylindrical portion 34b connected to the outer peripheral portion of the piston portion 34a, and a pressing that extends outward from the outer peripheral portion of the cylindrical portion 34b and approaches the front side of the friction plates 30a and 30b. The part 34c is integrally formed. At the front end of the hub portion 31b, a plurality of arc portions 31f having a circular arc cross section are formed at appropriate intervals in the circumferential direction, and these arc portions 31f are axially directed to a plurality of arc holes formed in the pressing portions 34c of the piston 34. Is inserted in such a way as to be relatively movable.

  The cylindrical portion 37 with which the inner peripheral portion of the piston 34 is in sliding contact is formed of a thin cylindrical member having a thickness of several millimeters, and the latter half portion of the cylindrical portion 37 is externally fixed to the inner peripheral cylindrical portion 38 of the carrier 21c. The space between the inner peripheral portion and the cylindrical portion 37 is sealed by a seal member made of a lip seal fixed to the inner peripheral portion of the piston 34. A predetermined (several mm) radial clearance 37a is formed over the entire circumference between the inner peripheral surface of the front half portion of the cylindrical portion 37 and the outer peripheral surface of the inner peripheral cylindrical portion 38. It always communicates with the clutch hydraulic chamber 33a.

  A seal plate 39 that partitions the front end of the clutch hydraulic chamber 33a is provided on the front side of the piston portion 34a of the piston 34. An inner peripheral cylindrical portion of the seal plate 39 is formed integrally with the carrier 21c and is rotatable relative to the sleeve member 4. It is externally fitted to a cylindrical body 38a that extends forward from the inner circumferential cylindrical portion 38 that is externally fitted, and is restricted from moving forward by a snap ring.

  The space between the inner peripheral cylindrical portion of the seal plate 39 and the cylindrical body 38a is sealed with an O-ring, and the outer peripheral portion of the seal plate 39 is fitted into the cylindrical portion 34c of the piston 34 so as to be relatively movable in the axial direction. A seal member fixed to the outer peripheral portion seals between the outer peripheral portion of the seal plate 39 and the cylindrical portion 34c. Thus, the clutch hydraulic chamber 33a is partitioned by the piston portion 34a, the seal plate 39, the cylindrical portion 37, the inner peripheral cylindrical portion 38, and the cylindrical body 38a. The clutch hydraulic chamber 33a is provided with a hydraulic oil supply oil path for supplying hydraulic oil from the oil path 4c in the sleeve member 4.

  The hydraulic oil supply oil passage is connected to a plurality of radial oil passages 40a formed in the sleeve member 4 so as to communicate with the oil passage 4c of the sleeve member 4, and to the outer peripheral ends of the radial oil passages 40a. An annular groove formed in the member 4 and a plurality of inclined oil passages 40b in the radial direction inclined so as to move rearward as it communicates with the annular groove.

  The outer ends of the plurality of inclined oil passages 40b are hydraulic oil supply ports 40c through which hydraulic oil is directly supplied to the clutch hydraulic chamber 33a. The hydraulic oil supply ports 40c are inner peripheral surfaces of the front half of the cylindrical portion 37. Is opened on the outer peripheral surface of the cylindrical body 38a. In this manner, the plurality of hydraulic oil supply ports 40c completely overlaps the cylindrical portion 37 with which the inner peripheral portion of the piston portion 34a is in sliding contact in the axial direction. However, if necessary, the plurality of hydraulic oil supply ports 40c may be formed so as to partially overlap the cylindrical portion 37 in the axial direction.

  When the first clutch 31 is in an open (separated) state, the balance hydraulic chamber 33b generates a force in the clutch fastening direction that acts on the piston 34 by centrifugal force that acts on the hydraulic oil in the clutch hydraulic chamber 33a. This is for canceling with the force in the clutch opening direction due to the centrifugal force acting on the hydraulic oil. A cylindrical portion 34b of the piston 34 is fitted into the cylindrical portion 21e of the hub member 31h so as to be slidable in the axial direction. The space between 34a and the cylindrical portion 21e is sealed. Thus, the piston 34 is supported by a member that rotates integrally with the hub portion 31b, and the balance hydraulic chamber 33b includes the carrier 21c, the cylindrical portion 21e and the inner peripheral cylindrical portion 38, the cylindrical portion 37, the piston portion 34a, The cylinder 34b is partitioned on the rear side of the clutch hydraulic chamber 33a.

  The balance hydraulic chamber 33b includes a shaft hole and an oil passage 21f formed in the pinion shaft that supports the pinion 21b, a clearance between the needle bearing 21g on the inner peripheral side of the pinion 21b, and an oil passage 21h formed in the sleeve member 4. The hydraulic fluid is communicated with the oil passage 4c in the sleeve member 4 through the hydraulic oil, and the hydraulic oil is introduced into the balance hydraulic chamber 33b. A plurality of return springs 33c for elastically urging the piston 34 in the clutch release direction are mounted in the balance hydraulic chamber 33b. When pressurized hydraulic fluid is supplied to the clutch hydraulic chamber 33a of the first clutch 31 described above, the piston 34 moves rearward, and the pressing portion 34c presses the plurality of friction plates 30a, 30b rearward, and the multi-plate clutch portion. 31a will be in a fastening state. On the other hand, when the hydraulic oil pressure in the clutch hydraulic chamber 33a is switched to the drain pressure, the first clutch 31 is released.

  A detected member 26 having a large number of teeth is arranged on the outer peripheral side of the drum portion 31e. This detected member 26 is fixed to the pressing portion 34c of the piston 34, and the teeth of the detected member 26 are detected to detect the teeth of the carrier 21c. A rotation speed sensor 27 for detecting the rotation speed is fixed to the transmission case 3. A rotational speed sensor 28 for detecting the rotational speed of the drum member 31d is provided in the transmission case 3 on the outer peripheral side of the drum member 31d, and the drum member 31d includes a number of rotational speed sensors 28 so as to face the rotational speed sensor 28. Slits (not shown) are formed.

Next, the second clutch 32 will be described.
The second clutch 32 has an annular multi-plate clutch portion 32 a corresponding to a multi-plate fastening mechanism, and is disposed on the rear side of the first clutch 31 and the first planetary gear mechanism 21. The second clutch 32 can be switched between an engaged state in which the rotational driving force of the turbine shaft 17 is transmitted to the carrier 23c of the third planetary gear mechanism 23 and an opened state in which the second clutch 32 is divided. The second clutch 32 includes a hub member 32h, a drum member 32d, a plurality of friction plates 30c whose inner peripheral portion is spline-engaged with an outer peripheral spline of the inner peripheral hub portion 32b of the hub member 32h, and a drum member 32d. A plurality of friction plates 30d, the outer periphery of which is spline-engaged with the inner periphery side spline of the outer peripheral drum portion 32e and alternately arranged with the plurality of friction plates 30c, and the multi-plate clutch portion 32a in the engaged state and the released state A hydraulic servo mechanism 43 for switching is provided.

  A friction lining material is provided on both front and rear surfaces of the friction plate 30c, and a plurality of radial lubricating oil grooves are formed in the friction lining material. The hydraulic oil (lubricating oil) that has flowed into the outer peripheral side spline of the inner peripheral hub portion 32b of the hub member 32h flows through the lubricating oil groove and lubricates and cools the plurality of friction plates 30c and 30d. Note that the friction lining material is provided only on one side of the friction plates 30c at both ends in the front-rear direction. The hub member 32h includes an inner peripheral hub portion 32b, a locking portion 32c that receives the plurality of friction plates 30c and 30d, and an annular joint portion 32f that protrudes from the inner peripheral portion of the front portion of the inner peripheral hub portion 32b to the inner peripheral side. Are integrally formed, and the annular joint portion 32 f is joined to the front surface of the outer peripheral portion of the annular member 6.

  The drum member 32d is a bottomed cylindrical annular member that covers the outer peripheral side and the rear side of the second clutch 32. The drum member 32d is disposed on the inner side and in the vicinity of the front side of the drum member 31d. An outer peripheral drum portion 32e is formed in the portion. The inner peripheral end portion of the drum member 32d is joined to the outer peripheral portion of the bowl-shaped portion of the second power transmission member 36 that is externally fitted to the turbine shaft 17 so as to be rotatable relative to the turbine shaft 17, and the drum member 32d is connected to the drum member via the multi-plate clutch portion 32a. The rotational driving force transmitted to the member 32d is transmitted to the carrier 23c of the third planetary gear mechanism 23 via the second power transmission member 36.

Next, the hydraulic servo mechanism 43 will be described.
2 to 4, the hydraulic servo mechanism 43 includes a piston 44 (piston member 44), a clutch hydraulic chamber 43a, a balance hydraulic chamber 43b, a plurality of return springs 43c, and the like. The piston 44 is integrally formed with an annular piston portion 44a, a cylindrical portion 44b connected to the outer peripheral portion of the piston portion 44a, and a pressing portion 44c extending from the cylindrical portion 44b to the outer peripheral side and facing the friction plates 30c and 30d. It is.

  A plurality of arc portions 32f having an arc cross section are formed at the rear end portion of the inner peripheral hub portion 32b of the hub member 32h, and these arc portions 32f are axially relative to the arc holes of the pressing portion 44c of the piston 44. It is inserted freely. The cylindrical portion 45 with which the inner peripheral portion of the piston portion 44a is slidably contacted is formed integrally with the inner peripheral portion of the annular member 6, and the inner peripheral portion and the cylinder are sealed by a seal member made of a lip seal fixed to the inner peripheral portion of the piston portion 44a. The space between the portions 45 is sealed. Here, the annular member 6 is included in the hub member 32h, and a piston 44 is slidably provided in the axial direction in the hub member 32h.

  An annular seal plate 46 that divides the rear end of the clutch hydraulic chamber 43a is provided, and a cylindrical portion 44b of the piston 44 is fitted on the seal plate 46 so as to be slidable in the axial direction, and is fixed to the outer peripheral portion of the seal plate 46. The space between the cylindrical portion 44b and the outer peripheral portion of the seal plate 46 is sealed by a sealing member made of a lip seal. The seal plate 46 is externally connected to the turbine shaft 17 corresponding to the input shaft, forms a clutch hydraulic chamber 43a in cooperation with a part of the piston 44, and can receive the piston 44 in the retracted position.

  The turbine shaft 17 includes a large-diameter portion 17b connected to the rear side of the flange-shaped portion 17a, a small-diameter portion 17c connected to the rear side of the large-diameter portion 17b, and a large-diameter portion 17b. A stepped portion 17d at the boundary of the small diameter portion 17c is formed. An outer peripheral male screw portion 50 a is formed on the outer peripheral portion of the small diameter portion 17 c, and an inner peripheral female screw portion 50 b is formed on the inner peripheral portion of the seal plate 46. A seal plate coupling structure 50 that couples the seal plate 46 to the turbine shaft 17 includes the outer peripheral male screw portion 50 a and the inner peripheral female screw portion 50 b, and the inner peripheral female screw portion 50 b is connected to the seal plate 46. Are screwed into an outer fitting shape through rotation around the axis of the shaft.

  Further, the seal plate coupling structure 50 includes a washer member 47 interposed between the inner peripheral portion of the seal plate 46 and the stepped portion 17d. The washer member 47 functions as a spacer for adjusting the clearance between the plurality of friction plates 30c, 30d of the multi-plate clutch portion 32a, and the seal plate 46 is pressed against the stepped portion 17d via the washer member 47. It is concluded with the state.

  The inner peripheral portion of the seal plate 46 faces the inner peripheral portion of the second power transmission member 36 as a predetermined rotating member from the front, and an annular thrust bearing 48 is mounted between the inner peripheral portions, An annular bearing receiving surface 48 e for supporting the thrust bearing 48 is formed on the rear surface of the inner peripheral portion of the seal plate 46.

  Here, as shown in FIG. 4, the thrust bearing 48 is provided between the annular first and second race members 48b and 48b and the first and second race members 48b and 48b facing each other in the axial direction. An annular roller holding member 48c and a plurality of rollers 48d rotatably held at appropriate intervals by the roller holding member 48c are provided, and the first and second race members 48b and 48b are relatively rotatable via these rollers 48d. The first race member 48a is disposed in contact with the smooth front surface near the inner end of the second power transmission member 36, and the second race member 48b is the smooth bearing receiving surface 48e of the seal plate 46. Are arranged in contact with each other. Note that at least one of the first and second race members 48b and 48b can be omitted.

  When the seal plate 46 is screwed into the small diameter portion 17c, a plurality of tool insertion concave holes 46a for inserting a rotation tool are formed in the seal plate 46 at equal intervals in the circumferential direction. A thrust bearing 49 is also mounted between the flange portion of the first power transmission member 35 and the flange portion of the second power transmission member 36.

  The cylindrical portion 45 of the annular member 6 is formed in a cylindrical shape having a thickness of several millimeters, and a predetermined number (several) is provided between the inner peripheral surface of the rear portion of the cylindrical portion 45 and the outer peripheral surface of the large-diameter portion 17b of the turbine shaft 17. mm) radial clearance 45a is formed over the entire circumference. The clutch hydraulic chamber 43a is partitioned by a piston 44, a seal plate 46, and a large diameter portion 17b. A plurality of radial oil passages 17f communicating with an oil passage 17e inside the turbine shaft 17 is formed in the large diameter portion 17b, and pressurized hydraulic fluid is supplied from these oil passages 17e, 17f to the clutch hydraulic chamber 43a. The hydraulic oil supply port 17g in which the plurality of oil passages 17f open to the clutch hydraulic chamber 43a overlaps the inner peripheral surface of the cylindrical portion 45 in the axial direction. However, you may comprise so that it may overlap partially as needed.

  The balance hydraulic chamber 43b is formed on the front side of the clutch hydraulic chamber 43a. The balance hydraulic chamber 43b is defined by the annular member 6 and the piston 44. The balance hydraulic chamber 43b is connected to the oil passage 17e inside the turbine shaft 17. The hydraulic fluid is introduced into the balance hydraulic chamber 43b. In the balance hydraulic chamber 43b, a plurality of return springs 43c are provided between the piston 44 and the annular member 6 at regular intervals in the circumferential direction. The balance hydraulic chamber 43b is for obtaining the same function as the balance hydraulic chamber 33b of the first clutch 31. Also in the second clutch 32, when pressurized hydraulic oil is supplied to the clutch hydraulic chamber 43a, the second clutch 32 is engaged, and when the hydraulic oil pressure in the clutch hydraulic chamber 43a is switched to the drain pressure, the second clutch 32 is opened.

Next, the effect of the automatic transmission 1 described above will be described.
A hydraulic servo mechanism 43 is connected to the hub member 32 h connected to the turbine shaft 17 so as to be slidable in the axial direction, and is coupled to the turbine shaft 17 and cooperates with a part of the piston 44 to clutch hydraulic pressure. A seal plate 46 that forms the chamber 43a and can receive the piston 44 in the retracted position is provided, and the inner peripheral female screw portion 50b formed on the inner peripheral portion of the seal plate 46 is connected to the seal plate 46 of the turbine shaft 17 The outer peripheral male screw 50a is formed on the outer peripheral portion of the portion, and the inner peripheral female screw portion 50b is screwed into the outer peripheral male screw 50a in an outer fitting manner through rotation around the axis of the seal plate 46. The seal plate 46 includes a seal plate coupling structure 50 in which the seal plate 46 is coupled to the turbine shaft 17.

  Therefore, the seal plate 46 receives a very large hydraulic pressure, but the seal plate 46 can be securely and firmly connected to the turbine shaft 17, and the conventional stopper ring is not required. The transmission 1 can be made compact in the axial direction. Further, after the return spring 43c is assembled, the seal plate 46 in a state of being biased by the return spring 43c can be easily assembled. 43 can be easily assembled.

  The connecting portion of the turbine shaft 17 with the seal plate 46 includes a small diameter portion 17c in which an outer peripheral male screw portion 50a is formed, and a large diameter portion 17b with the stepped portion 17d as a boundary in the small diameter portion 17c. The seal plate coupling structure 50 includes a washer member 47 interposed between the stepped portion 17d and the seal plate 46, and is fastened with the seal plate 46 pressed against the stepped portion 17d via the washer member 47. Therefore, the seal plate 46 can be surely positioned and connected to the connecting portion of the turbine shaft 17 with the seal plate 46.

  Then, by preparing a plurality of washer members 47 having different axial thicknesses as the washer member 47, when the hydraulic servo mechanism 43 is assembled, the washer member 47 having an appropriate thickness is adopted, so that the piston 44 The clearance between the plurality of friction plates 30c and 30d of the multi-plate clutch portion 32a can be appropriately adjusted while being received by the seal plate 46 and positioned at the retracted position. By only changing the thickness of the washer member 47, the thickness change can be prepared by preparing a plurality of washer members 47 having different thicknesses in advance, so that the clearance adjustment operation can be greatly simplified.

  Since a plurality of tool insertion concave holes 46a into which a tool for rotating the seal plate 46 can be inserted are formed in the disc portion of the seal plate 46, when the seal plate 46 is assembled, a plurality of tools in the disc portion are assembled. A tool is inserted into the insertion concave hole 46a, the seal plate 46 is rotated by using the tool, and the inner peripheral female screw portion 50b is easily and reliably screwed into the outer peripheral male screw 50a. Can be coupled to the turbine shaft 17.

  A second power transmission member 36 is provided adjacent to the seal plate 46 on the opposite side of the clutch hydraulic chamber 43a in the axial direction, and a thrust bearing 48 is mounted between the second power transmission member 36 and the seal plate 46. Therefore, the rotational resistance that interacts with the second power transmission member 36 and the seal plate 46 can be eliminated. However, since the conventional stopper ring can be omitted, the second power transmission member 36 and the seal plate 46 can be omitted. The thrust bearing 48 can be easily and securely mounted.

  In the first clutch 21, a cylindrical portion 37 in which the inner peripheral portion of the piston 34 pressing the multi-plate clutch portion 31a is in sliding contact, and a hydraulic oil supply port through which hydraulic oil is directly supplied to the clutch hydraulic chamber 33a from the inner peripheral side. A predetermined radial clearance 37a is formed between the hydraulic oil supply port 40c and the hydraulic oil supply port 40c is not closed even if the piston 34 moves. When the hydraulic oil is supplied to the cylinder 34, the hydraulic oil can be reliably supplied from the hydraulic oil supply port 40c. Even if the inner peripheral surface of the cylindrical portion 37 and the hydraulic oil supply port 40c overlap in the axial direction, the piston 34 The sealing member is not damaged by the hydraulic oil supply port 40c.

  Since the radial clearance 37a is formed over the entire circumference, the clearance in the radial direction may be small. Therefore, the clutch hydraulic chamber 33a is hardly enlarged in the radial direction. Moreover, since the inner peripheral surface of the cylindrical portion 37 and the hydraulic oil supply port 40c overlap in the axial direction, the axial length of the clutch hydraulic chamber 33a and the hydraulic oil supply port 40c should be shortened by about 5 mm or more. The automatic transmission 1 can be made compact in the axial direction. In addition, since the cylindrical portion 37 is formed of an independent cylindrical member, the structure of the carrier 21c is simplified. Since the second clutch 32 has the same configuration as described above, the same operation and effect as described above can be obtained.

  Moreover, since the plurality of arc portions 31f of the hub portion 31b are inserted into the plurality of arc holes of the pressing portion 34c of the piston 34 so as to be relatively movable in the axial direction, the carrier 21c and the piston 34 are rotated together. The first clutch 31 can be made compact in the axial direction. Since the second clutch 32 has the same configuration as described above, the same operation and effect as described above can be obtained.

  It should be noted that various changes other than those disclosed above can be added without departing from the spirit of the present invention. The main part of the present invention can be applied to various automatic transmission clutches, or can be expected to be applied to various automatic transmission brakes.

It is a skeleton figure of the automatic transmission of the present invention. It is a longitudinal cross-sectional view of the principal part of an automatic transmission. It is an enlarged view of the principal part of FIG. It is an enlarged view of the principal part of FIG.

Explanation of symbols

1 automatic transmission 17 turbine shaft 17b large diameter portion 17c small diameter portion 17d stepped portion 32a multi-plate clutch portion 32b inner peripheral hub portion 32d drum member 32e outer peripheral drum portion 32h hub member 36 second power transmission member 43 hydraulic servo mechanism 43a clutch Hydraulic chamber 44 Piston 46 Seal plate 46a Tool insertion recessed hole 47 Washer member 48 Thrust bearing 50 Seal plate connection structure 50a Outer peripheral male screw part 50b Inner peripheral female screw part

Claims (4)

An input shaft, a hub member having an inner peripheral hub portion connected to the input shaft, a drum member having an outer peripheral drum portion disposed on the outer peripheral side of the inner peripheral hub portion, and the inner peripheral hub portion and the outer peripheral drum In an automatic transmission provided with a multi-plate fastening mechanism provided between the two parts and a hydraulic servo mechanism having a piston member for fastening the multi-plate fastening mechanism,
The piston member of the hydraulic servo mechanism is provided on the hub member so as to be slidable in the axial direction,
The hydraulic servo mechanism includes a seal plate coupled to the input shaft and forming a hydraulic chamber for driving the piston member in cooperation with a part of the piston member and capable of receiving the piston member in the retracted position;
An inner peripheral female screw portion formed on the inner peripheral portion of the seal plate and an outer peripheral male screw formed on the outer peripheral portion of the seal plate connecting portion of the input shaft. An automatic transmission comprising a seal plate coupling structure in which a portion is screwed into an outer fitting shape through rotation around a shaft center of a seal plate, and the seal plate is coupled to an input shaft. The seal plate coupling portion of the input shaft has a small diameter portion in which the outer peripheral male screw portion is formed, and a large diameter portion having a stepped portion as a boundary in the small diameter portion,
The seal plate coupling structure includes a washer member interposed between the stepped portion and the seal plate, and the seal plate is fastened to the stepped portion via the washer member in a pressed state. The automatic transmission according to claim 1.   3. The automatic transmission according to claim 2, wherein a plurality of tool insertion concave holes into which a tool for rotating the seal plate can be inserted are formed in a disc portion of the seal plate.   3. A predetermined rotating member is provided adjacent to the seal plate on the opposite side to the hydraulic chamber in the axial direction, and a thrust bearing is mounted between the rotating member and the seal plate. The automatic transmission described in 1.

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