JP2008038977A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enhance the mountability of an automatic transmission to a vehicle body by keeping the end cover of the transmission from extending. <P>SOLUTION: An end cover 4 is provided for closing an opening in the end of a transmission case 3 opposite to a torque converter, and a clutch 33 is disposed adjacent thereto. A piston 140, a hydraulic chamber 160 and the like which make up the hydraulic servo device of the clutch 33 are provided at the clutch hub 120 of the clutch 33 on the end cover 4 side of the clutch 33, whereby extension of the end cover 4 to the side opposite to the torque converter is kept within an area with a small diameter. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a structure of an automatic transmission, particularly a mechanical power transmission mechanism thereof, and belongs to the technical field of automobiles.

  An automatic transmission for an automobile is a combination of a torque converter and a transmission gear mechanism, and the power transmission path of the transmission gear mechanism is switched by selective operation of frictional engagement elements such as a plurality of clutches and brakes to obtain a predetermined gear stage. Although it is configured to shift automatically, the number of the frictional engagement elements and the number of planetary gear sets constituting the transmission gear mechanism tend to increase as the number of shift stages increases, and the overall size tends to increase. The problem is how to deal with this.

  In response to this problem, for example, Patent Literature 1 and Patent Literature 2 include a reduction planetary gear set in which a sun gear is fixed, a ring gear is an input element, and a carrier is an output element, and a carrier and an output member that are output elements. In an automatic transmission having a clutch that connects and disconnects, a configuration is disclosed in which the clutch is arranged on the outer periphery of a planetary gear set to reduce the axial dimension.

  In this case, the automatic transmission of Patent Document 1 is configured such that a carrier, which is an output element of a planetary gear set, and a clutch drum that constitutes a clutch are connected. In the automatic transmission of Patent Document 2, the carrier and the clutch In both cases, a hydraulic servo device for fastening the clutch and a balance chamber provided on the opposite side of the hydraulic chamber across the piston of the servo device are connected. The clutch drum is housed in a clutch drum.

JP 2004-36717 A JP 2002-349647 A

  By the way, when the hydraulic servo device and the balance chamber are housed in the clutch drum constituting the clutch as in the automatic transmissions described in Patent Document 1 and Patent Document 2, the clutch drum having a large diameter is disposed on one side in the axial direction. Will bulge out. In particular, when the diameter of the clutch is originally large, such as when the clutch is arranged on the outer periphery of the speed reduction planetary gear set, the clutch drum swells with a larger diameter.

  Therefore, when this clutch is disposed at the end of the transmission on the side opposite to the torque converter, the end cover that closes the opening of the end of the transmission case bulges toward the side opposite the torque converter with a large diameter. Thus, for example, in the engine room in which the automatic transmission is accommodated, it becomes difficult to avoid interference with the vehicle body constituent members and the like, which causes a problem of mounting on the vehicle body.

  Therefore, the present invention suppresses the end cover from bulging to the counter-torque converter side with a large diameter when a clutch is disposed at the end cover side end portion of the automatic transmission. It is an object to improve the mounting property of the vehicle to the vehicle body.

  In order to solve the above problems, the present invention is configured as follows.

  First, an invention according to claim 1 of the present application includes an end cover that closes an opening of an end portion of a transmission case on the counter-torque converter side, a first rotating member that is disposed adjacent to the end cover, An automatic transmission having a clutch that connects and disconnects the second rotating member, wherein the clutch includes an inner peripheral clutch hub, an outer peripheral clutch drum, and a plurality of friction members disposed therebetween. And a hydraulic servo device that controls the fastening of the friction plate, and the hydraulic servo device is provided on the clutch hub portion or a member connected to the clutch hub on the end cover side of the clutch. It is characterized by being.

  According to a second aspect of the present invention, in the automatic transmission according to the first aspect of the present invention, the end cover has an axial center portion that bulges toward the anti-torque converter, and the hydraulic servo device is disposed in the bulged portion. The hydraulic chamber which comprises is accommodated.

  According to a third aspect of the present invention, in the automatic transmission according to the first or second aspect, at least a part of a piston constituting the hydraulic servo device is adjacent to the end cover, and an adjacent portion thereof. The end cover is characterized in that it has a shape along the piston with a predetermined clearance.

  According to a fourth aspect of the present invention, in the automatic transmission according to any one of the first to third aspects of the present invention, a boss portion that extends toward the torque converter is provided at the axial center portion of the end cover. And a sleeve rotatably supported on the boss portion, a disk portion connecting the sleeve and the clutch hub, and the hydraulic servo device is formed on the outer periphery of the sleeve. The inner peripheral part of the piston is slidably fitted, and a seal plate that is prevented from moving toward the cover side is locked to the end cover side, and the outer peripheral part of the seal plate and the piston are A sliding contact portion is provided between the intermediate portion in the radial direction, and a hydraulic chamber constituting the hydraulic servo device is formed by the seal plate, the inner peripheral portion of the piston, and the sleeve. The features.

  According to a fifth aspect of the present invention, in the automatic transmission according to any one of the first to fourth aspects, a cylindrical portion that extends the clutch hub toward the end cover is provided. A sliding contact portion is provided between the cylindrical portion and the piston, and a balance chamber is formed by the cylindrical portion, the piston, the disc portion, and the sleeve.

  With the configuration described above, the following effects can be obtained according to the inventions of the present application.

  First, according to the first aspect of the present invention, in the configuration in which the clutch is disposed adjacent to the end cover on the side opposite to the torque converter of the transmission case, the hydraulic servo device for the clutch is Since it is provided on the clutch end cover side on the clutch hub constituting the clutch or a member connected to the clutch hub, when the hydraulic servo device is disposed on the end cover side, this is a clutch drum having a large diameter. Compared with the case where the end cover is housed, the end cover can be prevented from bulging in the axial direction in a small-diameter region.

  In particular, when the clutch is disposed on the outer periphery of the planetary gear set, for example, when the diameter is originally large, the end cover is effectively prevented from bulging out in a region having a large diameter. This makes it possible to improve the mountability of the automatic transmission on the vehicle body, such as avoiding interference with other vehicle body components.

  According to the second aspect of the present invention, the end cover has an axial center portion that bulges toward the anti-torque converter, and the hydraulic chamber that constitutes the hydraulic servo device is housed in the bulged portion. Thus, the effect of the invention of claim 1 can be achieved reliably.

  According to the third aspect of the present invention, when at least a part of the piston constituting the hydraulic servo apparatus is adjacent to the end cover, the end cover is provided with a predetermined clearance so as to follow the piston. Thus, it is possible to minimize the bulging of the end cover to the anti-torque converter, and the mountability of the automatic transmission on the vehicle body is further improved.

  Further, according to the invention of claim 4, the piston is slidably fitted to the outer periphery of the sleeve supported on the boss portion extending from the axial center portion of the end cover to the torque converter side, and The seal plate is locked to the end cover side, and a hydraulic chamber is formed by the seal plate, the inner peripheral portion of the piston, and the sleeve, so that the hydraulic chamber is accommodated in a relatively small diameter area around the boss portion. Therefore, this also suppresses the end cover from bulging out to the anti-torque converter with a large diameter.

  According to the fifth aspect of the present invention, since the balance chamber for removing the influence of the residual hydraulic pressure in the hydraulic chamber when the clutch is not engaged is also provided on the clutch hub side, the balance chamber is placed in the clutch drum having a large diameter. As compared with the case where the balance chamber is provided, the bulging of the end cover due to the provision of the balance chamber is suppressed in a small-diameter region, and the mountability of the automatic transmission is further improved.

  Embodiments of the present invention will be described below.

  First, the overall mechanical configuration of the automatic transmission 1 according to the present embodiment will be described with reference to FIG. 1. The automatic transmission 1 is applied to a horizontal engine, and the main component is an engine. It has a driven torque converter 10 and a transmission mechanism 20 to which the 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. It is like that.

  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 disposed facing 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, and the case 11 The lockup clutch 16 is provided between the turbine 13 and 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 a 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 set 21 disposed on the torque converter 10 side, a second planetary gear set 22 disposed on the anti-torque converter 10 side, and third and third planets disposed between them. The first planetary gear sets 23 and 24 are 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 paths of the planetary gear sets 21 to 24. ~ The third clutches 31 to 33 and the first and second brakes 41 and 42 arranged in order from the torque converter 10 side as well, so that forward 1st to 6th speed and reverse speed can be obtained. Yes.

  Each of the first to fourth planetary gear sets 21 to 24 includes a sun gear 21a to 24a, a plurality of pinions 21b to 24b respectively meshed with the sun gears 21a to 24a, and a carrier that supports the pinions 21b to 24b. 21c to 24c and ring gears 21d to 24d meshed with the pinions 21b to 24b.

  In the first planetary gear set 21, the sun gear 21a is fixed to the transmission case 3, the carrier 21c is connected to the drum side of the first clutch 31, and the ring gear 21d is connected to the turbine shaft 17 and the drum side of the second clutch. Yes.

  In the second planetary gear set 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 side of the third clutch 33.

  In the third planetary gear set 23, the sun gear 23a is connected to the drum side of the third clutch 33 and the second brake 42, and the carrier 23c is connected to the hub side of the second clutch 32 and the first brake 41, The ring gear 23 d is connected to the carrier 24 c of the fourth planetary gear set 24.

  Further, in the fourth planetary gear set 24, the sun gear 24a is connected to the hub side of the first clutch 31, the ring gear 24d is connected to the carrier 23c of the third planetary gear set 23, and is connected to the first brake 41, and the carrier 24c. Is coupled to the ring gear 23d of the third planetary gear set 23 and 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 to drive the left and right axles 61 and 62.

  Here, the relationship between the operating states of the clutches 31 to 33 and the brakes 41 and 42 and the shift speed is shown in Table 1.

Next, the configuration of the third clutch 33 disposed at the end of the transmission gear mechanism 20 on the side opposite to the engine, which is a characteristic part of the present invention, and its surroundings will be described in detail.

  As shown in FIG. 2, the opening of the transmission case 3 on the side opposite to the torque converter (hereinafter referred to as “rear side”) is closed by an end cover 4. The end cover 4 has a shaft center portion that bulges rearward, and a boss portion 4b that extends to the torque converter side (hereinafter referred to as “front side”) along the axis on the inner side of the bulge portion 4a. The sleeve member 5 for forming an oil passage is fitted and fixed to the base of the boss 4b. The sun gear 22a of the second planetary gear set 22 is spline-fitted and fixed to the front end of the boss portion 4b.

  A disc-shaped first connecting member 22e extending to the inner peripheral side is joined to the front end side of the ring gear 22d of the second planetary gear set 22, and a second connecting member 22f is connected to the inner peripheral portion of the first connecting member 22e. Are joined, and the inner peripheral portion of the second connecting member 22f is spline-fitted to the turbine shaft 17, whereby the rotation of the turbine shaft 17 is input to the ring gear 22d.

  Further, a sleeve 22c ″ extending rearward is integrally formed on the inner peripheral portion of the disc portion 22c ′ on the rear side of the carrier 22c that supports the pinion 22b of the second planetary gear set 22, and the sleeve 22c ″ is integrally formed. The carrier 22c is rotatably supported by being rotatably fitted on the sleeve member 5.

  Thereby, the rotation input from the turbine shaft 17 to the ring gear 22d is decelerated by the second planetary gear set 22 and output from the carrier 22c.

  The third clutch 33 is disposed on the outer periphery of the ring gear 22d of the second planetary gear set 20.

  The third clutch 33 includes a bottomed cylindrical clutch drum 110 that is open at one end, and a cylindrical clutch hub 120 that is disposed inside the drum 110 so as to be relatively rotatable concentrically with the drum 110. And have. The inner peripheral surface of the outer peripheral portion of the drum 110 and the outer peripheral surface of the hub 120 facing the drum 110 are respectively formed with splines of internal teeth and external teeth, and a plurality of frictional teeth having teeth on the outer peripheral side are formed on these splines. The plates 131... 131 and the plurality of friction plates 132... 132 having teeth on the inner peripheral side are alternately engaged.

  The clutch hub 120 of the third clutch 33 is connected to the outer periphery of the disc portion 22c ′ of the carrier 22c constituting the second planetary gear set 22, and is formed integrally with the disc portion 22c ′. The hub 120 is provided with an extended cylindrical portion 121 extending rearward from the connecting portion with the disk portion 22c ′.

  Further, the piston 140 constituting the hydraulic servo device of the third clutch 33 includes an inner pressure receiving portion 141 located immediately after the disc portion 22c ′ of the carrier 22c, and a tip portion of the piston 140 which is the friction plate 131, The outer peripheral friction plate pressing portion 142 is located immediately after the 132 row, and the cylindrical portion 143 is provided between them and extends from the outer peripheral end of the pressure receiving portion 141 to the rear side.

  In addition, a disc-shaped seal plate 150 is disposed immediately after the piston 140, and the rear end portion of the sleeve 22c ″ of the carrier 22c is prevented from coming out rearward by a snap ring 151. It is locked with.

  A seal member 152 formed of a lip seal attached to the outer peripheral portion of the seal plate 150 is in sliding contact with the inner peripheral surface of the cylindrical portion 143 of the piston 140, whereby the seal plate 150 and the sleeve of the carrier 22c. 22c ″ and the pressure receiving portion 141 and the cylindrical portion 143 of the piston 140 define a hydraulic chamber 160 constituting a hydraulic servo device, and an oil passage 161 provided in the end cover 4 is formed in the hydraulic chamber 160. Oil pressure is supplied through an oil passage 162 provided in the sleeve member 5 and an oil passage 163 provided in the sleeve 22c ″.

  Further, between the pressure receiving portion 141 of the piston 140 and the disc portion 22c ′ of the carrier 22c, the piston is operated in the direction opposite to the direction in which the hydraulic pressure supplied to the hydraulic chamber 160 is applied (clutch engagement direction) (clutch release direction). A return spring 170 that biases 140 is attached.

  Further, an inner peripheral side sealing member 144 formed of a lip seal that is in sliding contact with the outer peripheral surface of the sleeve 22c ″ of the carrier 22c is mounted on the inner peripheral portion of the pressure receiving portion 141 of the piston 140, and the outer periphery of the pressure receiving portion 141 is also provided. The outer peripheral side sealing member 145 made of the same lip seal that is slidably in contact with the inner peripheral surface of the extension cylindrical portion 121 of the hub 120 is attached to the portion, whereby the pressure receiving portion 141 of the piston 140 and the disc portion of the carrier 22c. The balance chamber 180 is defined by 22c ′ and the sleeve 22c ″ and the extended cylindrical portion 121 of the hub 120.

  Then, hydraulic oil is supplied to the balance chamber 180 through the oil passage 181 provided in the end cover 4, the oil passage 182 provided in the sleeve member 5, the oil passage 183 provided in the sleeve 22c ″ of the carrier 22c, and the like. When a hydraulic pressure is not supplied to the hydraulic chamber 160, a force in the clutch fastening direction that acts on the piston 140 due to the centrifugal force that acts on the hydraulic oil remaining in the hydraulic chamber 160 is introduced into the balance chamber 180. It cancels out by the force in the clutch release direction due to the centrifugal force of the working oil.

  Further, a disc portion 111 extending inwardly is integrally formed at the front end portion of the clutch drum 110 of the third clutch 33, and the inner peripheral portion of the disc portion 111 is connected to the power transmission member 112. It is connected. The power transmission member 112 extends forward and is connected to the sun gear 23a of the third planetary gear set 23 shown in FIG. 1, and the transmission gear mechanism 20 is connected via the third planetary gear set 23 and the fourth planetary gear set 24. It is led to the output gear 25 which takes out power from the.

  Further, in this embodiment, the second brake 42 is disposed on the outer periphery of the third clutch 33.

  The second brake 42 extends from the outer periphery of the end cover 4 to the front side and is housed inside a cylindrical fitting portion 4b fitted inside the rear end opening of the transmission case 3. A plurality of friction plates 42a... 42a having teeth on the outer peripheral side in splines respectively formed on the inner peripheral surface of the fitting portion 4b and the outer peripheral surface of the clutch drum 33a of the third clutch 33 opposed thereto. The plurality of friction plates 42b... 42b having teeth on the inner peripheral side are alternately engaged.

  A piston 42c is disposed on the front surface of the outer peripheral portion of the end cover 4, and two internal and external hydraulic chambers 42d and 42e are supplied with hydraulic pressure from an oil passage (not shown) between the piston 42c and the front surface of the end cover 4. Is provided. Further, the cylindrical fitting portion 4b is provided with notches at a plurality of locations in the circumferential direction, and the return spring 42f of the piston 42c is accommodated.

  Here, as described above, the member to be braked of the second brake 42 also serves as the drum 110 of the third clutch 33. Therefore, the drum 110 of the third clutch 33 is fixed when the brake 42 is operated. Accordingly, the sun gear 23a of the third planetary gear set 23 shown in FIG. 1 is fixed.

  Next, the operation of this embodiment will be described.

  As described above, the rotation of the turbine shaft 17 that extracts the output of the torque converter 10 is input to the ring gear 22d of the second planetary gear set 22 via the second connecting member 22f and the first connecting member 22e. Since the sun gear 22a of the planetary gear set 22 is fixed to the boss portion 4b of the end cover 4, the rotation input to the ring gear 22d is decelerated and output to the carrier 22c.

  Then, if the third clutch 33 is engaged and the second brake 42 is released, the rotation output to the carrier 22c is transmitted from the hub 120 of the third clutch 33 to the drum 110 and the power transmission member 112. Is transmitted to the sun gear 23a of the third planetary gear set 23, and according to the state of the other friction elements, as shown in Table 1, the third speed, the fifth speed, and the reverse speed are realized, and the difference from the output gear 25 is achieved. It is output to the moving device 60 side.

  In that case, according to the above configuration, the rotation of the turbine shaft 17 is input from the front side of the second planetary gear set 22 to the ring gear 22d and output from the rear side via the carrier 22c, and this output rotation is also transmitted to the planetary gear. This is input to the clutch hub 120 of the third clutch 33 arranged on the outer periphery of the set 22. That is, the rotation of the third clutch 33 is input from the rear side to the clutch hub 120 and output from the clutch drum 110 to the front side.

  Then, on the rear side of the second planetary gear set 22, that is, on the end cover 4 side, the disk portion 22 c ′ and the sleeve 22 c ″ of the carrier 22 c are integrated with the clutch hub 120. A hydraulic chamber 160 is configured by the sleeve 22c ″, the seal plate 150 locked to the sleeve 22c ″, and the pressure receiving portion 141 on the inner periphery of the piston 140 slidably fitted to the sleeve 22c ″. Therefore, the hydraulic servo device is provided on the clutch hub 120 on the end cover 4 side of the clutch 3.

  Therefore, compared to the case where the piston is housed in the clutch drum having a large diameter or the hydraulic chamber is provided, the end cover 4 on the side opposite to the torque converter when the hydraulic servo device is provided on the end cover 4 side of the clutch 33. Since the balance chamber 180 is formed inside the extended cylindrical portion 121 in which the clutch hub 120 is extended to the rear side, the balance chamber is reduced in diameter. Therefore, the bulge of the end cover 4 toward the anti-torque converter can be suppressed in a small-diameter region.

  Therefore, as shown in the figure, the end cover 4 protrudes rearward in the axial direction at the shaft center portion, but is shaped toward the torque converter side at a portion away from the shaft center. For example, the automatic transmission 1 When the vehicle is placed horizontally in the engine room, it is possible to avoid interference with the side frame X disposed in the front-rear direction in the engine room. improves.

  In addition, the end cover 4 is shaped so as to be along the piston 140 with a predetermined clearance on the outer peripheral side thereof so as to be along the seal plate 150 positioned on the immediately preceding side at the inner peripheral portion. As a result, the bulging of the end cover 4 toward the anti-torque converter is suppressed to a minimum, which contributes to an improvement in the mounting property to the vehicle body.

  In the above-described embodiment, the clutch hub 120, the disk portion 22c ′ and the sleeve 22c ″ of the carrier 22c are integrated, but this may be a separate integrated structure.

  Next, another embodiment of the seal structure of the hydraulic chamber and balance chamber of the present invention will be described.

  First, in the embodiment shown in FIG. 3, an O-ring 251 is attached as a seal member to the outer peripheral end of the seal plate 250, and this O-ring 251 is a cylindrical portion provided at the radial intermediate portion of the piston 240. By sliding contact with the outer peripheral surface of 241, the outer peripheral portion of the hydraulic chamber 260 is sealed.

  In the embodiment shown in FIG. 4, a lip seal 341 is attached as a sealing member to the intermediate portion in the radial direction of the piston 340, and the lip seal 341 is a cylindrical portion 351 provided at the outer peripheral end of the seal plate 350. The outer peripheral portion of the hydraulic chamber 360 is sealed by being in sliding contact with the inner peripheral surface.

  Further, in the embodiment shown in FIG. 5, an O-ring 441 is mounted as a seal member at the intermediate portion in the radial direction of the piston 440, and this O-ring 441 is a cylindrical portion 451 provided at the outer peripheral end of the seal plate 450. The outer peripheral portion of the hydraulic chamber 460 is sealed by being in sliding contact with the outer peripheral surface.

  On the other hand, regarding the seal structure of the balance chamber, in the embodiment shown in FIG. 6, an O-ring 542 as a seal member is attached to the inner peripheral portion of the friction plate pressing portion 541 in the piston 540, and this is the clutch hub 520. The outer peripheral portion of the balance chamber 580 is sealed by being in sliding contact with the outer peripheral surface of the extended cylindrical portion 521.

  Further, in the embodiment shown in FIG. 7, an O-ring 622 as a seal member is mounted on the inner peripheral surface of the extension cylindrical portion 621 of the clutch hub 620, and this is used for sealing the hydraulic chamber at the radial intermediate portion of the piston 640. The outer peripheral portion of the balance chamber 680 is sealed by sliding contact with the outer peripheral surface of the cylindrical portion 641.

  Further, in the embodiment shown in FIG. 8, an O-ring 722 as a seal member is mounted on the outer peripheral surface of the extended cylindrical portion 721 of the clutch hub 720, and this is the directly inner peripheral side of the friction plate pressing portion 741 in the piston 740. The outer peripheral portion of the balance chamber 780 is sealed by being in sliding contact with the inner peripheral surface of the cylindrical portion 742 provided on the outer periphery.

  In each of the embodiments shown in FIGS. 3 to 8, the hydraulic servo device including the piston and the hydraulic chamber and the balance chamber are provided on the clutch hub 120 side between the end cover 4 and the clutch 33. Compared with the case where these are provided on the side of the clutch drum having a large diameter, the bulging portion 4a of the end cover 4 toward the counter-torque converter is suppressed in a small-diameter region. Although it protrudes to the rear side, it has a shape brought close to the torque converter side at a part away from the axial center. Therefore, the mountability of the transmission 1 on the vehicle body is improved as in the embodiment shown in FIG.

  Further, the end cover 4 has a shape set along the piston with a predetermined clearance on the outer peripheral side so as to follow the seal plate located on the immediately preceding side at the inner peripheral part. Thus, the bulging of the end cover 4 toward the anti-torque converter side is suppressed to the minimum as in the embodiment shown in FIG.

  In the above embodiment, as shown in an enlarged view in FIG. 9, teeth are provided on the outer periphery of the friction plates 131 and 132 of the third clutch 33, and the splines on the inner peripheral surface of the clutch drum 110 are engaged. The plurality of combined friction plates 131 are all formed of a metal plate, whereas the plurality of friction plates are provided with teeth on the inner periphery and engaged with splines on the outer peripheral surface of the clutch hub 120. Reference numeral 132 denotes a configuration in which a facing member 132b is attached to the surface of the mandrel 132a.

  In this case, with respect to the friction plate 132 that contacts both sides of the friction plate 131 engaged with the clutch drum, the facing member 132b is attached to both surfaces, but one surface contacts the pressing portion 142 of the piston 140. A friction plate 132 ′ disposed at one end and a friction plate 132 ″ disposed at the other end where one surface is in contact with the receiving portion 122 of the clutch hub 120 are engaged with the clutch drum. The facing member 132b is attached only to the other surface in contact with the friction plate 131.

  In other words, the facing member 132b is provided on the friction plate 132 that is always engaged with the clutch hub 120 connected to the carrier 22c, which is the output element of the second planetary gear set 22, and thus rotates. Through an oil groove (not shown) provided on the surface of 132b, the lubricating oil always flows from the inside to the outside in the radial direction by centrifugal force. As a result, so-called dragging of the friction plate when the clutch 33 is not engaged is suppressed, and torque loss due to this dragging is reduced.

  As described above, in the automatic transmission according to the present invention, the bulge of the end cover to the counter-torque converter side is suppressed in a region having a small diameter, so that the mountability to the vehicle body is improved. There is a possibility of being suitably used in the field of manufacturing industries of automobile automatic transmissions.

1 is a skeleton diagram showing an overall mechanical configuration of an automatic transmission according to an embodiment of the present invention. It is sectional drawing of the principal part of the embodiment. It is sectional drawing of other embodiment of the seal structure of a hydraulic chamber. It is sectional drawing of other embodiment of the seal structure of a hydraulic chamber. It is sectional drawing of other embodiment of the seal structure of a hydraulic chamber. It is sectional drawing of other embodiment of the seal structure of a balance chamber. It is sectional drawing of other embodiment of the seal structure of a balance chamber. It is sectional drawing of other embodiment of the seal structure of a balance chamber. It is an expanded sectional view which shows the structure of the friction plate of a clutch.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Automatic transmission 3 Transmission case 4 End cover 4a Expansion part 33 3rd clutch 22c 'Disk part 22c "Sleeve 110 Clutch drum 120 Clutch hub 140 Piston 150 Seal plate 160 Hydraulic chamber 180 Balance chamber

Claims (5)

An end cover that closes an opening at the end of the transmission case on the side opposite to the torque converter, and a clutch that is disposed adjacent to the end cover and connects and disconnects the first rotating member and the second rotating member. An automatic transmission,
The clutch includes an inner peripheral side clutch hub, an outer peripheral side clutch drum, a plurality of friction plates disposed therebetween, and a hydraulic servo device that controls fastening of the friction plates,
The automatic transmission is provided on the end cover side of the clutch, on the clutch hub portion or on a member connected to the clutch hub. The automatic transmission according to claim 1,
The automatic transmission according to claim 1, wherein the end cover has a shaft portion that bulges toward the anti-torque converter, and a hydraulic chamber that constitutes the hydraulic servo device is accommodated in the bulge portion. In the automatic transmission according to claim 1 or 2,
An automatic transmission characterized in that at least a part of a piston constituting the hydraulic servo device is adjacent to the end cover, and in the adjacent portion, the end cover has a shape along the piston with a predetermined clearance. Machine. In the automatic transmission according to any one of claims 1 to 3,
A boss portion extending toward the torque converter is provided at the shaft center portion of the end cover, a sleeve rotatably supported on the boss portion, and a disc portion for connecting the sleeve and the clutch hub And
A seal plate in which an inner peripheral portion of a piston constituting the hydraulic servo device is slidably fitted on the outer periphery of the sleeve, and movement to the cover side is prevented on the end cover side Are engaged, and a sliding contact portion between the outer peripheral portion of the seal plate and the intermediate portion in the radial direction of the piston is provided,
An automatic transmission characterized in that a hydraulic chamber constituting the hydraulic servo device is formed by the seal plate, an inner peripheral portion of a piston, and the sleeve. In the automatic transmission according to any one of claims 1 to 4,
A cylindrical portion that extends the clutch hub toward the end cover is provided, and a sliding contact portion is provided between the cylindrical portion and the piston.
An automatic transmission characterized in that a balance chamber is formed by the cylindrical portion, the piston, the disc portion, and the sleeve.

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