JP2018003921A - Oil supply structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil supply structure which can supply oil to a canceler chamber from an oil flow-in space even if a clutch piston is arranged between the oil flow-in space at the outside of a clutch drum and the canceler chamber.SOLUTION: An external fitting part 71 which is externally fit to an input shaft 41 is formed at a clutch drum 61. An oil flow-in space 123 into which oil flows is arranged at a position adjacent to the external fitting part 71 of the clutch drum 61 around the input shaft 41. The oil flow-in space 123 and a canceler chamber 97 communicate with each other via an oil passage composed of an outer groove 131 formed at the clutch drum 61 and an internal peripheral groove 132 formed between the input shaft 41 and the external fitting part 71.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an oil supply structure for supplying oil to a clutch.

  In a vehicle equipped with an automatic transmission, the torque generated by the engine is input to the automatic transmission via a torque converter, and the driving force changed by the automatic transmission is transmitted to the drive wheels. For example, a continuously variable transmission (CVT) or a stepped automatic transmission (AT) is widely used as the automatic transmission.

  In an automatic transmission, a clutch (brake) for braking a rotating element or connecting a rotating element and another rotating element is often used. The clutch needs to be supplied with oil for its operation. Further, the clutch must absorb the differential rotation between the rotating elements, and requires oil supply for lubrication in order to prevent seizure due to the absorption of the differential rotation. Therefore, in the automatic transmission, the hydraulic pressure generated by the oil pump is regulated by the valve body, and the regulated hydraulic pressure is supplied from the valve body to each part such as a clutch that requires oil supply through the oil passage. .

  For example, FIG. 4 shows a clutch 203 that directly connects / disconnects the rotary shaft 201 and the gear 202. In FIG. 4, the hatching indicating the cross section is omitted.

  The rotating shaft 201 is inserted through a substantially cylindrical stator shaft 204. A retainer 206 is installed between the stator shaft 204 and the unit case 205 that forms the outer shell of the automatic transmission. The stator shaft 204 is fixedly held to the unit case 205 by the retainer 206. Yes.

  A needle roller bearing 211 is interposed between the rotating shaft 201 and the stator shaft 204. Further, an inner race (inner ring) of a ball bearing 212 is externally fitted to the rotating shaft 201 at a position away from the needle roller bearing 211 in the rotating axis direction. An outer race (outer ring) of the ball bearing 212 is fixed to the unit case 205. Thereby, the rotating shaft 201 is rotatably held by the unit case 205 via the needle roller bearing 211 and the ball bearing 212.

  Further, an inner race of a ball bearing 213 is fitted on the rotating shaft 201 adjacent to the ball bearing 212 on the stator shaft 204 side. The gear 202 is fixed to the outer race of the ball bearing 213.

  The clutch 203 is provided on the stator shaft 204 side with respect to the ball bearing 213. The clutch 203 includes a clutch drum 221, a clutch hub 222, a clutch piston 223, and a canceller 224.

  The clutch drum 221 is provided at a position adjacent to the stator shaft 204 side with respect to a portion where the ball bearing 213 is externally fitted. The clutch drum 221 includes a substantially cylindrical fitting portion 231 that is spline-fitted with the spline 231, a substantially annular plate-like first intermediate portion 232 that extends outward from the fitting portion 231 in the rotational radial direction, and a first A substantially cylindrical second intermediate portion 233 extending from the intermediate portion 232 to the outer peripheral surface of the stator shaft 204; a substantially annular plate-shaped third intermediate portion 234 extending outward from the second intermediate portion 233 in the rotational radial direction; A substantially cylindrical plate holding portion 235 extending from the third intermediate portion 234 to the gear 202 side in the rotation axis direction is formed continuously in this order. A plurality of clutch plates 236 are held in the plate holding portion 235 so as to extend from the plate holding portion 235 to the inside in the rotation radial direction with an interval in the rotation axis direction.

  The clutch hub 222 is formed integrally with the gear 202 and has a substantially cylindrical shape extending from the gear 202 to a plurality of clutch plates 236 from the inside in the rotational radial direction to a position facing the clutch plate 236. A plurality of clutch disks 237 are held on the clutch hub 222 at intervals in the rotation axis direction. The clutch plates 236 and the clutch disks 237 are arranged so as to be alternately arranged in the rotation axis direction.

  The clutch piston 223 is provided between the clutch drum 221 and the clutch hub 222 so as to be movable in the rotational axis direction. The clutch piston 223 has an annular shape when viewed in the rotational axis direction, and an inner peripheral end thereof faces the second intermediate portion 233 of the clutch drum 221 from the outside in the rotational radial direction. A seal 238 is attached to the clutch piston 223. A part of the seal 238 is in liquid-tight contact with the plate holding part 235 of the clutch drum 221, and another part is in liquid-tight contact with the second intermediate part 233 of the clutch drum 221. Thus, a piston chamber 241 to which hydraulic pressure acting on the clutch piston 223 is supplied is formed between the clutch drum 221 and the clutch piston 223 around the rotation shaft 201.

  The canceller 224 is provided between the clutch hub 222 and the clutch piston 223. The shape seen in the direction of the rotation axis is an annular shape, and the inner peripheral end thereof is externally fitted to the fitting portion 231 of the clutch drum 221. A seal 242 is attached to the outer peripheral end of the canceller 224. The seal 242 is in liquid-tight contact with the clutch piston 223. As a result, a canceller chamber 243 is formed between the clutch piston 223 and the canceller 224. The canceller chamber 243 is provided with a return spring 244, and the clutch piston 223 and the canceller 224 are elastically biased in a direction away from each other by the biasing force of the return spring 244.

  The clutch piston 223 moves to the clutch plate 236 side by the hydraulic pressure supplied to the piston chamber 241 and presses the clutch plate 236. By this pressing, the clutch plate 236 and the clutch disc 237 are pressed against each other, and the clutch 203 is engaged. When the hydraulic pressure is released from the engaged state of the clutch 203, the clutch piston 223 is separated from the clutch plate 236 by the urging force of the return spring 244 interposed between the clutch piston 223 and the canceller 126. As a result, the pressure contact between the clutch disk 237 and the clutch plate 236 is released, and the clutch 203 is released.

  The stator shaft 204 is formed with an oil passage 251 through which oil is supplied from the valve body. The oil passage 251 is opened at the end surface of the stator shaft 204 on the clutch drum 221 side. An oil supply hole 252 is formed through the first intermediate portion 232 of the clutch drum 221. As a result, the oil supplied to the oil passage 251 flows into the space 253 between the stator shaft 204 and the first intermediate portion 232, and flows into the canceller chamber 243 from the space 253 through the oil supply hole 252.

  In a state where the clutch drum 221 is rotating, centrifugal force acts on the oil in the canceller chamber 243, and centrifugal hydraulic pressure is generated in the canceller chamber 243. The centrifugal hydraulic pressure in the piston chamber 241 can be canceled (cancelled) by this centrifugal hydraulic pressure. Therefore, when the hydraulic pressure in the piston chamber 241 is released from the engaged state, the clutch piston 223 smoothly moves to the clutch drum 221 side by the urging force of the return spring 244.

Japanese Patent Laying-Open No. 2015-145682

  In the configuration shown in FIG. 4, the inner diameter of the clutch piston 223 is larger than the size of the clutch drum 221, and the pressure receiving area of the clutch piston 223 is smaller. For example, if the inner diameter of the clutch piston 223 is reduced so that the inner peripheral end of the clutch piston 223 faces the fitting portion 231 of the clutch drum 221 from the outside in the rotational radial direction, the pressure receiving area of the clutch piston 223 is increased. be able to. And the transmission torque capacity of the clutch 203 can be increased by expanding the pressure receiving area.

  However, if the inner peripheral end of the clutch piston 223 faces the fitting portion 231 of the clutch drum 221 from the outside in the rotational radial direction, the space between the oil passage 251 and the canceller chamber 243 between the oil passage 251 Since the clutch piston 223 is disposed, oil cannot be supplied from the space 253 to the canceller chamber 243.

  An object of the present invention is to provide an oil supply structure capable of supplying oil from an oil inflow space to a canceller chamber even when a clutch piston is disposed between the oil inflow space outside the clutch drum and the canceller chamber. is there.

  In order to achieve the above object, an oil supply structure according to the present invention includes a clutch drum, a clutch piston, and a canceller, and an outer fitting portion that is fitted on a rotating shaft is formed on the clutch drum. Provided inside, a piston chamber is formed between the clutch drum and the clutch piston, the inner peripheral end of the clutch piston faces the outer fitting portion in the rotational radial direction, and the canceller is a piston with respect to the clutch piston. In the clutch having the configuration provided on the opposite side of the chamber, the hydraulic pressure is supplied to the canceller chamber formed between the clutch piston and the canceller. In this structure, the outer fitting portion is provided around the rotating shaft. An oil inflow space into which oil flows is provided at an adjacent position, and the oil inflow space and the cancel box are disposed between the rotating shaft and the outer fitting portion. An oil passage for communicating is provided a chamber.

  According to this structure, the clutch drum is formed with an external fitting portion that is externally fitted to the rotating shaft. An oil inflow space into which oil flows is provided at a position adjacent to the outer fitting portion around the rotation shaft. The oil inflow space and the canceller chamber are communicated with each other through an oil passage provided between the rotating shaft and the outer fitting portion. Therefore, even if the inner peripheral end of the clutch piston faces the outer fitting portion in the rotational radial direction, and the clutch piston is arranged between the oil inflow space and the canceller chamber, the oil path from the oil inflow space Oil can be supplied to the canceller chamber through.

  Also, in the configuration in which the inner peripheral end of the clutch piston faces the outer fitting portion in the rotational radial direction, the inner peripheral end is brought close to the outer fitting portion so that a gap is formed between the outer fitting portion and the outer fitting portion. As a result, the pressure receiving area of the clutch piston can be increased. By increasing the pressure receiving area, it is possible to increase the transmission torque capacity of the clutch without increasing the number of clutches (the number of clutch plates and clutch disks) or increasing the hydraulic pressure supplied to the piston chamber. Therefore, it is possible to increase the transmission torque capacity of the clutch while avoiding the problems of cost increase due to an increase in the number of clutches and insufficient strength of the clutch drum and clutch piston due to an increase in the hydraulic pressure supplied to the piston chamber.

  The oil path may include an inner circumferential groove formed on the inner circumferential surface of the outer fitting portion over the entire length in the rotation axis direction.

  In the configuration in which the spline is formed on the outer peripheral surface of the rotating shaft and the inner peripheral surface of the outer fitting portion, and the rotating shaft and the outer fitting portion are spline-fitted, a part of the spline formed on the inner peripheral surface of the outer fitting portion An inner circumferential groove may be formed by missing (missing teeth).

  In the configuration in which another member (such as a lock nut) is in contact with the outer surface of the outer fitting portion, the oil passage is formed on the inner circumferential surface of the outer fitting portion over the entire length in the rotation axis direction, and the clutch drum And an outer groove formed on the outer surface and extending in the rotational radial direction and connected to the inner circumferential groove.

  Instead of the inner peripheral groove, an outer peripheral groove extending in the direction of the rotation axis may be formed on the peripheral surface of the rotation shaft. However, in the configuration in which the outer groove is formed on the outer surface of the clutch drum, the rotational shaft and the outer fitting portion must be aligned in the rotational direction so that the outer groove is connected to the outer peripheral groove. Since it takes time to assemble the clutch drum, it is preferable that an inner peripheral groove is formed on the inner peripheral surface of the outer fitting portion.

  According to the present invention, even if the clutch piston is disposed between the oil inflow space outside the clutch drum and the canceller chamber, oil can be supplied from the oil inflow space to the canceller chamber. For this reason, the pressure receiving area of the clutch piston can be increased, and the increase in the pressure receiving area causes problems such as an increase in cost due to an increase in the number of clutches and insufficient strength of the clutch drum and clutch piston due to an increase in hydraulic pressure supplied to the piston chamber. While avoiding, the transmission torque capacity of the clutch can be increased.

It is sectional drawing which shows the structure of a part of transmission unit to which the oil supply structure which concerns on one Embodiment of this invention was applied. It is sectional drawing which shows the structure of the vicinity of a clutch. It is the side view which looked at the external fitting part and 1st intermediate part of the clutch drum from the right side. It is sectional drawing which shows the structure of a part of conventional transmission unit.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

<Transmission unit>
FIG. 1 is a cross-sectional view illustrating a partial configuration of a transmission unit 1 to which an oil supply structure according to an embodiment of the present invention is applied. In FIG. 1, the hatching indicating the cross section is omitted.

  The transmission unit 1 is a unit that is mounted on a vehicle, changes the torque generated by an engine (not shown), and transmits the torque to drive wheels (not shown), and includes a torque converter 2 and an automatic transmission 3. The torque converter 2 and the automatic transmission 3 are accommodated in a unit case 4 that forms an outer shell of the transmission unit 1.

<Torque converter>
The torque converter 2 includes a front cover 11, a pump impeller 12, a turbine hub 13, a turbine runner 14, a lockup mechanism 15, and a stator 16.

  The front cover 11 extends in a substantially disk shape around the rotation axis, and has an outer peripheral end bent toward the automatic transmission 3 (left side in FIG. 1; hereinafter referred to as “left side”). The center portion of the front cover 11 bulges to the engine side (the right side in FIG. 1, hereinafter referred to as “the right side”). The generated torque (engine torque) of the engine is input to the bulged portion.

  The pump impeller 12 is disposed on the left side of the front cover 11. The outer peripheral end of the pump impeller 12 is connected to the outer peripheral end of the front cover 11 and is provided so as to be able to rotate integrally with the front cover 11 around the rotation axis. A plurality of blades 21 are arranged radially on the inner surface of the pump impeller 12.

  The turbine hub 13 is disposed between the front cover 11 and the pump impeller 12. The turbine hub 13 integrally includes a substantially cylindrical boss portion 22 and a flange portion 23 extending from the boss portion 22 to the outside in the rotational radial direction.

  The turbine runner 14 is fixed to the surface of the flange 23 of the turbine hub 13 on the pump impeller 12 side. A plurality of blades 24 are arranged radially on the surface of the turbine runner 14 facing the pump impeller 12.

  The lockup mechanism 15 includes a lockup piston 25 and a damper mechanism 26.

  The lock-up piston 25 has a substantially annular plate shape, and an inner peripheral end portion thereof is fitted on the flange portion 23 of the turbine hub 13 and is positioned between the front cover 11 and the turbine runner 14. If the hydraulic pressure of the engagement side oil chamber 27 on the turbine runner 14 side is higher than the hydraulic pressure of the release side oil chamber 28 on the front cover 11 side with respect to the lockup piston 25, the differential pressure causes the lockup piston 25 to move to the front cover. Move to the 11 side. Conversely, if the hydraulic pressure in the release side oil chamber 28 is higher than the hydraulic pressure in the engagement side oil chamber 27, the lockup piston 25 moves to the turbine runner 14 side due to the differential pressure.

  A friction material 29 is stuck to the outer peripheral end of the surface of the lockup piston 25 on the front cover 11 side. When the lock-up piston 25 moves to the front cover 11 side due to the differential pressure and the friction material 29 is pressed against the front cover 11, the pump impeller 12 and the turbine runner 14 are directly connected (lock-up on). From this state, when the lockup piston 25 moves to the turbine runner 14 side due to the differential pressure, the friction material 29 is separated from the front cover 11 and the direct connection between the pump impeller 12 and the turbine runner 14 is released (lockup off). The

  The damper mechanism 26 is a mechanism for dampening vibrations from the engine when the pump impeller 12 and the turbine runner 14 are directly connected. Specifically, the damper mechanism 26 includes a retaining plate 31 supported by the lock-up piston 25, a spring 32 supported by the retaining plate 31, and the retaining plate 31 elastically in the rotational direction via the spring 32. And a driven plate 33 connected to each other and an outer peripheral member 34 surrounding the outer periphery of the spring 32. The vibration input to the front cover 11 is damped as the spring 32 repeatedly compresses and restores between the retaining plate 31 and the driven plate 33.

  The stator 16 is disposed between the pump impeller 12 and the turbine runner 14.

  When the pump impeller 12 is rotated by the engine torque in the lock-up off state, an oil flow from the pump impeller 12 toward the turbine runner 14 is generated. The oil flow is received by the blade 24 of the turbine runner 14 and the turbine runner 14 rotates. At this time, the amplifying action of the torque converter 2 occurs, and the turbine runner 14 generates torque larger than the engine torque.

<Automatic transmission>
The automatic transmission 3 includes an input shaft 41, a gear 42, and a clutch 43.

  The input shaft 41 is formed as a hollow shaft. The input shaft 41 extends on the rotational axis of the torque converter 2 and is inserted through the torque converter 2. A boss portion 22 of the turbine hub 13 is externally fitted to the right end portion of the input shaft 41, and the boss portion 22 is spline-fitted. As a result, the input shaft 41 rotates integrally with the turbine hub 13, and further rotates together with the turbine runner 14 and the lockup mechanism 15 (the lockup piston 25 and the damper mechanism 26) fixed to the turbine hub 13. To do.

  A substantially cylindrical stator shaft 44 is fitted on the input shaft 41. The right end portion of the stator shaft 44 is located between the pump impeller 12 and the turbine runner 14 in the rotational axis direction, and a space is provided between the end portion and the boss portion 22 of the turbine hub 13. Yes. The stator 16 of the torque converter 2 is fixed to the right end portion of the stator shaft 44, and the stator shaft 44 supports the stator 16 so as not to rotate. The stator shaft 44 extends from the torque converter 2 to the left side. A substantially annular plate-like retainer 45 is fitted on the stator shaft 44 by press-fitting in a portion extending from the torque converter 2. The retainer 45 is fastened to the unit case 4 with bolts. Thereby, the stator shaft 44 is fixedly held by the unit case 4 via the retainer 45.

  A gap 46 is provided between the input shaft 41 and the stator shaft 44, and a needle roller bearing 47 is disposed in the gap 46 at a position facing the retainer 45 in the rotational radial direction. The input shaft 41 is rotatably held on the stator shaft 44 via a needle roller bearing 47. Further, an inner race (inner ring) of a ball bearing 48 is fitted on the left end portion of the input shaft 41. An outer race (outer ring) of the ball bearing 48 is fixed to the unit case 4. Thus, the left end of the input shaft 41 is rotatably held by the unit case 4 via the ball bearing 48.

  A ball bearing 51 is fitted on the input shaft 41 adjacent to the right side of the ball bearing 48.

  The gear 42 is fixed to the outer race of the ball bearing 51. Specifically, the gear 42 is connected to a substantially cylindrical boss 52, a substantially annular plate-like web 53 extending from the boss 52 to the outside in the rotational radial direction, and an outer peripheral end portion of the web 53, and is connected to the outer peripheral surface. A substantially cylindrical rim 54 having a large number of gear teeth is integrally provided. The boss 52 is externally fitted and fixed to the outer race of the ball bearing 51, so that the gear 42 is provided to be rotatable relative to the input shaft 41.

  FIG. 2 is a cross-sectional view showing a configuration in the vicinity of the clutch 43.

  The clutch 43 is provided between the retainer 45 and the ball bearing 51. The clutch 43 includes a clutch drum 61, a clutch hub 62, a clutch piston 63, and a canceller 64.

  The clutch drum 61 includes a substantially cylindrical outer fitting portion 71 fitted on the input shaft 41, a substantially annular plate-shaped first intermediate portion 72 extending outward from the outer fitting portion 71 in the rotational radial direction, A substantially cylindrical second intermediate portion 73 extending from the first intermediate portion 72 to the outer peripheral surface of the stator shaft 44; and a substantially annular plate-shaped third intermediate portion 74 extending outward from the second intermediate portion 73 in the rotational radial direction; A substantially cylindrical plate holding portion 75 extending from the third intermediate portion 74 to the gear 42 side in the rotational axis direction is formed continuously in this order. A plurality of clutch plates 76 are held in the plate holding portion 75 in a state extending from the plate holding portion 75 to the inside in the rotation radial direction at intervals in the rotation axis direction.

  A spline 81 is formed on the outer peripheral surface of the input shaft 41 at a portion adjacent to the right side of the portion where the ball bearing 51 is fitted. Correspondingly, a spline 82 is formed on the inner peripheral surface of the outer fitting portion 71. The external fitting portion 71 is externally fitted to a portion of the input shaft 41 where the spline 81 is formed, and the spline 82 is engaged with the spline 81 so that the input shaft 41 is spline-fitted.

  Further, a screw 83 is cut on the outer peripheral surface of the input shaft 41 at a portion adjacent to the right side of the portion where the spline 81 is formed. A lock nut 84 is screwed into a portion where the screw 83 is cut. When the lock nut 84 is tightened, the inner race of the ball bearing 48, the inner race of the ball bearing 51, and the outer fitting portion 71 of the clutch drum 61 are formed on the input shaft 41 with a pressing surface 85 (see FIG. 1) and the lock nut 84. The inner race of the ball bearing 48, the inner race of the ball bearing 51, and the clutch drum 61 are fixed to the input shaft 41.

  The clutch hub 62 is formed integrally with the gear 42 and has a substantially cylindrical shape extending from the web 53 of the gear 42 to a position facing the plurality of clutch plates 76 from the inside in the rotational radial direction. A plurality of clutch disks 91 are held on the clutch hub 62 at intervals in the rotation axis direction. The clutch plates 76 and the clutch disks 91 are arranged so as to be alternately arranged in the rotation axis direction.

  The clutch piston 63 is provided between the clutch drum 61 and the clutch hub 62 so as to be movable in the rotational axis direction. The clutch piston 63 has an annular shape when viewed in the rotational axis direction, and an inner peripheral portion thereof faces the outer fitting portion 71 of the clutch drum 61 from the outer side in the rotational radial direction. A seal 92 is attached to the clutch piston 63. The outer peripheral end portion 93 of the seal 92 is in liquid-tight contact with the plate holding portion 75 of the clutch drum 61, and the inner peripheral end portion 94 is in liquid-tight contact with the outer fitting portion 71 of the clutch drum 61. As a result, a piston chamber 95 to which hydraulic pressure acting on the clutch piston 63 is supplied is formed between the clutch drum 61 and the clutch piston 63 around the input shaft 41.

  The canceller 64 is provided between the clutch hub 62 and the clutch piston 63. The shape viewed in the direction of the rotation axis is an annular shape, and the inner peripheral end portion thereof is externally fitted to the external fitting portion 71 of the clutch drum 61. A seal 96 is attached to the outer peripheral end of the canceller 64. The seal 96 is in liquid-tight contact with the clutch piston 63. Thereby, a canceller chamber 97 is formed between the clutch piston 63 and the canceller 64. The canceller chamber 97 is provided with a return spring 98, and the clutch piston 63 and the canceller 64 are elastically biased in a direction away from each other by the biasing force of the return spring 98. By this urging, the canceller 64 abuts on a snap ring 99 attached to the outer fitting portion 71 of the clutch drum 61, and movement in the rotation axis direction is restricted.

  The clutch piston 63 moves toward the clutch plate 76 by the hydraulic pressure supplied to the piston chamber 95 and presses the clutch plate 76. By this pressing, the clutch plate 76 and the clutch disc 91 are pressed against each other, and the clutch 43 is engaged. When the hydraulic pressure is released from the engaged state of the clutch 43, the clutch piston 63 is separated from the clutch plate 76 by the urging force of the return spring 98 interposed between the clutch piston 63 and the canceller 64. As a result, the pressure contact between the clutch disk 91 and the clutch plate 76 is released, and the clutch 43 is released.

<Oil supply structure>
As shown in FIG. 1, the oil pump 5 is disposed on the left side of the input shaft 41. The oil pump 5 includes a pump drive shaft 101 and a pump gear 102.

  The pump drive shaft 101 extends along the rotation axis and is inserted into the input shaft 41. The right end of the pump drive shaft 101 is directly connected to the front cover 11 of the torque converter 2. A gap is provided between the input shaft 41 and the pump drive shaft 101, and an inter-shaft oil passage 111 is provided by the gap. The left end of the inter-shaft oil passage 111 is sealed with a seal 112. The inter-shaft oil passage 111 is opened at the right end face of the input shaft 41 and communicates with the release-side oil chamber 28 between the front cover 11 and the lockup piston 25.

  An axial oil passage 113 is formed at the left end of the pump drive shaft 101. Further, the pump drive shaft 101 is formed with a communication oil passage 114 that connects the inter-shaft oil passage 111 and the shaft center oil passage 113.

  The pump gear 102 is provided so as to be able to rotate integrally with the pump drive shaft 101. When the front cover 11 of the torque converter 2 rotates, the pump drive shaft 101 rotates and the pump gear 102 rotates integrally with the pump drive shaft 101. As the pump gear 102 rotates, oil pressure is generated in the oil pump 5, and the oil pressure is supplied to a valve body (not shown).

  A plurality of supply oil passages 115 are formed inside the retainer 45. Each supply oil passage 115 is opened on the inner peripheral surface of the retainer 45.

  A communication oil passage 116, a clutch oil passage 117, and a canceller oil passage 118 are formed in the stator shaft 44.

  The communication oil passage 116 communicates with one of the supply oil passages 115 (hereinafter referred to as “first supply oil passage 115” when it is necessary to distinguish this supply oil passage 115 from other supply oil passages 115). doing. Further, the communication oil passage 116 is opened to the gap 46 between the input shaft 41 and the stator shaft 44 on the right side of the needle roller bearing 47 and communicates with the gap 46.

  The clutch oil passage 117 is one of the supply oil passages 115 other than the first supply oil passage 115 (hereinafter referred to as “second supply oil when it is necessary to distinguish this supply oil passage 115 from the other supply oil passages 115. A path 115 ”), a position facing the radial direction of the rotation, and the left end surface of the stator shaft 44, extending in the direction of the rotational axis. The left end of the clutch oil passage 117 is sealed by press-fitting a ball 119. The clutch oil passage 117 communicates with the second supply oil passage 115 via a connection oil passage 120 formed in the stator shaft 44. An oil supply hole 121 is formed through the second intermediate portion 73 of the clutch drum 61, and the clutch oil passage 117 is connected to the oil supply hole 122 via a branch oil passage 122 formed in the stator shaft 44. 121 is in communication.

  The canceller oil passage 118 is different from the first supply oil passage 115 and the second supply oil passage 115 (hereinafter, when the supply oil passage 115 needs to be distinguished from the other supply oil passages 115). (Referred to as “third supply oil passage 115”) and a position facing the rotational radial direction and the left end face of the stator shaft 44 in the rotational axis direction. The canceller oil passage 118 is open at the left end face of the stator shaft 44 and communicates with an oil inflow space 123 provided between the left end face of the stator shaft 44 and the first intermediate portion 72 of the clutch drum 61. doing. The canceller oil passage 118 communicates with the third supply oil passage 115 via a connection oil passage 124 formed in the stator shaft 44.

  The hydraulic pressure supplied from the oil pump 5 to the valve body is regulated by the valve body. Then, oil is supplied from the valve body to the shaft center oil passage 113 and each supply oil passage 115 by the hydraulic pressure.

  The oil supplied to the shaft center oil passage 113 is supplied to the inter-shaft oil passage 111 through the communication oil passage 114, flows through the inter-shaft oil passage 111, and is supplied to the release side oil chamber 28 of the torque converter 2.

  The oil supplied to the first supply oil passage 115 is supplied to the gap 46 between the input shaft 41 and the stator shaft 44 through the communication oil passage 116, flows through the gap 46, and the right end of the stator shaft 44. And the boss 22 of the turbine hub 13 is supplied to the engagement side oil chamber 27 of the torque converter 2.

  The oil supplied to the second supply oil passage 115 is supplied to the clutch oil passage 117 through the connection oil passage 120, and is supplied from the clutch oil passage 117 to the piston chamber 95 of the clutch 43 through the branch oil passage 122 and the oil supply hole 121. The

  The oil supplied to the third supply oil passage 115 flows out to the canceller oil passage 118 through the connection oil passage 124, flows through the canceller oil passage 118, and the left end face of the stator shaft 44 and the clutch drum from the canceller oil passage 118. The oil flows out into the oil inflow space 123 between the first intermediate portion 72 of 61.

  FIG. 3 is a side view of the outer fitting portion 71 and the first intermediate portion 72 of the clutch drum 61 as viewed from the right side.

  For example, three outer grooves 131 are formed at equiangular intervals on the outer surfaces (right surfaces) of the outer fitting portion 71 and the first intermediate portion 72 of the clutch drum 61. Each outer groove 131 extends from the middle portion of the first intermediate portion 72 in the rotational radial direction to the inner side in the rotational radial direction, and is opened at the inner peripheral surface of the outer fitting portion 71.

  Then, on the inner peripheral surface of the outer fitting portion 71, a part of the spline 82 is missing (missing teeth) over the entire length in the rotation axis direction at the same position in the rotation direction as each outer groove 131, thereby forming the inner peripheral groove 132. Is formed.

  An oil supply hole 133 is formed through the outer fitting portion 71 at a position facing the canceller chamber 97.

  As a result, the oil flowing out from the canceller oil passage 118 into the oil inflow space 123 between the left end surface of the stator shaft 44 and the first intermediate portion 72 of the clutch drum 61 flows into the outer grooves 131, and the outer grooves 131. From the inner circumferential groove 132 to the canceller chamber 97 through the oil supply hole 133.

<Effect>
As described above, the clutch drum 61 is formed with the external fitting portion 71 that is externally fitted to the input shaft 41. An oil inflow space 123 into which oil flows is provided at a position adjacent to the outer fitting portion 71 of the clutch drum 61 around the input shaft 41. The oil inflow space 123 and the canceller chamber 97 are communicated with each other via an oil path including an outer groove 131 formed in the clutch drum 61 and an inner circumferential groove 132 provided between the input shaft 41 and the outer fitting portion 71. ing. Therefore, even if the inner peripheral end portion of the clutch piston 63 faces the outer fitting portion 71 in the rotational radial direction, and the clutch piston 63 is disposed between the oil inflow space 123 and the canceller chamber 97, the oil Oil can be supplied from the inflow space 123 to the canceller chamber 97 through the oil passage (the outer groove 131 and the inner circumferential groove 132).

  Further, in the configuration in which the inner peripheral end portion of the clutch piston 63 is opposed to the outer fitting portion 71 in the rotational radial direction, the outer fitting portion 71 is formed so that a gap is generated between the inner peripheral end portion and the outer fitting portion 71. The pressure receiving area of the clutch piston 63 can be increased by bringing the clutch piston 63 close to each other. By increasing the pressure receiving area, the transmission torque capacity of the clutch 43 is increased without increasing the number of clutches (the number of clutch plates 76 and clutch disks 91) or increasing the hydraulic pressure supplied to the piston chamber 95. Can do. Accordingly, it is possible to increase the transmission torque capacity of the clutch 43 while avoiding the problem of insufficient strength of the clutch drum 61 and the clutch piston 63 due to an increase in cost due to an increase in the number of clutches and an increase in hydraulic pressure supplied to the piston chamber 95. .

<Modification>
As mentioned above, although one Embodiment of this invention was described, this invention can also be implemented with another form.

  For example, in the above-described embodiment, the configuration in which the inner peripheral groove 132 is formed on the inner peripheral surface of the outer fitting portion 71 of the clutch drum 61 is taken up. Not limited to this, instead of the inner circumferential groove 132, an outer circumferential groove may be formed by missing (missing teeth) a part of the spline 81 of the input shaft 41 in the rotational axis direction. However, in the configuration in which the outer groove 131 is formed on the outer surface of the clutch drum 61, it is necessary to align the rotational direction positions of the input shaft 41 and the outer fitting portion 71 so that the outer groove 131 is connected to the outer peripheral groove. In addition, since it takes time to assemble the clutch drum 61 to the input shaft 41, it is preferable that the inner peripheral groove 132 is formed on the inner peripheral surface of the outer fitting portion 71.

  In addition, although three oil passages including the outer groove 131 and the inner peripheral groove 132 connected to the outer groove 131 are formed, the number of oil passages including the outer groove 131 and the inner peripheral groove 132 can be reduced to the canceller chamber 97. It may be changed as appropriate according to the flow rate of oil that needs to be supplied. Further, the width (cross-sectional area) of the oil passage formed of the outer groove 131 and the inner peripheral groove 132 may be adjusted according to the flow rate of oil that needs to be supplied to the canceller chamber 97.

  Further, in the configuration in which the clutch drum 61 is fixed to the input shaft 41 without using the lock nut 84, the outer groove 131 is omitted, and the outer circumferential groove formed in the inner circumferential groove 132 or the input shaft 41 is oiled. A path may be configured.

  In addition, the oil supply to the clutch 43 provided in the automatic transmission 3 is taken as an example, but the present invention supplies oil to a clutch (brake) provided in a power transmission mechanism other than the automatic transmission 3. It is also applicable to the structure.

  In addition, various design changes can be made to the above-described configuration within the scope of the matters described in the claims.

43 Clutch 61 Clutch drum 63 Clutch piston 64 Canceller 71 External fitting portion 95 Piston chamber 97 Canceller chamber 123 Oil inflow space 132 Inner circumferential groove (oil passage)
223 Clutch hub 271 Clutch drum

Claims (1)

The clutch drum includes a clutch drum, a clutch piston, and a canceller, and an outer fitting portion is formed on the clutch drum. The clutch piston is provided inside the clutch drum, and the clutch drum, the clutch piston, A piston chamber is formed, an inner peripheral end portion of the clutch piston is opposed to the outer fitting portion in a rotational radial direction, and the canceller is provided on a side opposite to the piston chamber with respect to the clutch piston. In the clutch having the structure described above, the structure supplies hydraulic pressure to a canceller chamber formed between the clutch piston and the canceller,
An oil inflow space into which oil flows is provided at a position adjacent to the outer fitting portion around the rotating shaft,
An oil supply structure in which an oil passage is provided between the rotating shaft and the outer fitting portion to communicate the oil inflow space with the canceller chamber.

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