JP2016023762A - Transmission clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make it possible to reduce an axial dimension of a clutch drum and configure the clutch drum axially compact if a hydraulic fluid introduction portion introducing a hydraulic fluid into a plurality of hydraulic fluid supply portions is provided in the clutch drum.SOLUTION: A clutch drum 11 of one clutch 10 out of a plurality of clutches disposed concentrically includes a cylindrical portion 63 provided radially inward thereof and fitted into an outer circumferential side of a boss portion 2c extending from a longitudinal wall portion 2b of a transmission case 2 along an axial center, the cylindrical portion 63 includes a plurality of hydraulic fluid introduction portions 81d introducing a hydraulic fluid to be supplied to a plurality of hydraulic fluid supply portions 15, 25, and 35 from a transmission case 2, and the hydraulic fluid introduction portion 81d is provided on each of an inner circumference and an outer circumference of the cylindrical portion 63.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a clutch device for a transmission mounted on a vehicle, and belongs to the technical field of a vehicle transmission.

  A transmission mounted on a vehicle such as an automatic transmission switches a power transmission path composed of a planetary gear set or the like by selectively engaging a plurality of frictional engagement elements composed of clutches, brakes, or the like, according to the driving state of the vehicle. It is configured to achieve a predetermined gear position.

  A clutch used in such a transmission generally has a plurality of friction plates arranged between a clutch drum as an outer rotating member and a clutch hub as an inner rotating member, and a plurality of friction plates are applied by a piston when hydraulic pressure is supplied. The plate is pressed and fastened to couple the clutch drum and the clutch hub.

  For example, Patent Document 1 discloses an automatic transmission having such a clutch. As shown in FIG. 12, in the automatic transmission 201, first, second, and third clutches 210, 220, and 230 are arranged on the same axis in the transmission case, and the first, second, and third clutches are arranged. The clutches 210, 220, and 230 include a plurality of friction plates 213, 223, and 233 and a plurality of friction plates 213, 223, and 233 disposed between the clutch drums 211, 221, and 231 and the clutch hubs 212, 222, and 232, respectively. Pistons 214, 224, and 234 to be pressed, and hydraulic chambers 215, 225, and 235 to which hydraulic oil that biases the pistons 214, 224, and 234 toward the friction plate is supplied.

  Then, hydraulic fluid (hydraulic pressure) is supplied from the axial center side of the first, second, and third clutches 210, 220, and 230 to the hydraulic chambers 215, 225, and 235, whereby the pistons 214, 224, and 234 cause friction plates. The clutch drums 211, 221, 231 and the clutch hubs 212, 222, 232 are coupled to each other by being pressed and fastened.

JP 2002-242953 A

  In recent years, multi-stage automatic transmissions have been promoted for the purpose of improving the fuel efficiency of vehicles, etc., and the number of planetary gear sets tends to increase along with this, but if the number of planetary gear sets increases, the entire transmission As a result, the dimension in the axial direction increases, resulting in a problem of in-vehicle performance. In particular, in a horizontal automatic transmission in which the shaft center extends in the vehicle body width direction, interference with a frame member or the like is likely to be a problem, and the in-vehicle problem may become more prominent.

  As shown in FIG. 12, the one described in Patent Document 1 includes first, second, and third clutches 210 and 220 on the inner peripheral side of the clutch drum 211 of the first clutch 210 formed in a bottomed cylindrical shape. 230, friction plates 213, 223, 233 are arranged, and the clutch drum 211 is fitted to the outer peripheral side of the boss portion 202 extending along the axial center from the vertical wall portion of the transmission case on the radially inner side thereof. And a cylindrical portion 217 connected to the input shaft 203.

  The cylinder portion 217 of the clutch drum 211 is provided with hydraulic oil introduction portions 217a and 217b for introducing hydraulic oil to be supplied to the hydraulic chambers 215 and 225 of the first and second clutches 210 and 220, respectively. A hydraulic oil introduction portion 217 c for introducing hydraulic oil to be supplied to the centrifugal balance chamber 226 of the two clutch 220 is provided.

  The cylindrical portion 217 of the clutch drum 211 is provided with a plurality of hydraulic oil introduction portions 217a, 217b, and 217c that introduce hydraulic oil to the hydraulic chambers 215 and 225 and the centrifugal balance chamber 226 in the axial direction. The hydraulic oil is introduced into the portions 217a, 217b, and 217c from the inner peripheral side of the cylindrical portion 217.

  It is conceivable that a planetary gear set or a further clutch is arranged on the inner peripheral side of the second clutch 220 or the third clutch 230 in order to reduce the axial dimension along with the multi-stage automatic transmission. When hydraulic oil introduction parts that introduce hydraulic oil into a plurality of hydraulic oil supply parts such as a balance chamber are arranged in the axial direction in the cylindrical part 217 of the clutch drum 211, the axial dimension can be effectively shortened. It is difficult and it becomes a problem how to arrange the hydraulic oil supply oil passage in order to ensure good in-vehicle performance.

  Therefore, the present invention is capable of reducing the axial dimension when the hydraulic oil introduction section for introducing the hydraulic oil to the plurality of hydraulic oil supply sections is provided in the clutch drum, and is configured to be compact in the axial direction. It is an object of the present invention to provide a clutch device for a transmission that can achieve the above.

  In order to solve the above-described problems, a transmission clutch device according to the present invention is configured as follows.

  First, the invention according to claim 1 of the present application includes a plurality of clutches arranged on the same axis in a transmission case, and each of the plurality of clutches includes a clutch drum, a clutch hub, and the clutch drum. And a clutch of a transmission having a plurality of friction plates disposed between the clutch hub, a piston that presses the plurality of friction plates, and a hydraulic chamber that is supplied with hydraulic oil that urges the pistons toward the friction plate. The clutch drum of one of the plurality of clutches includes a cylindrical portion extending in an axial direction on a radially inward side thereof, and the cylindrical portion is pivoted from a vertical wall portion of the transmission case. The hydraulic oil that is fitted to the outer peripheral side of the boss portion extending along the center and is supplied to a plurality of hydraulic oil supply portions including the hydraulic chambers of the clutch and other clutches is introduced from the transmission case. Duplicate Comprising a hydraulic oil introduction section, the hydraulic oil introduction section, characterized in that provided on the inner peripheral side and outer peripheral side of the cylindrical portion.

  According to a second aspect of the present invention, in the clutch device for a transmission according to the first aspect, the hydraulic oil introduction portion is also provided on the vertical wall portion side of the transmission case in the cylindrical portion. It is characterized by being.

  According to a third aspect of the present invention, there is provided the transmission clutch device according to the first or second aspect, wherein the transmission case has a facing portion facing the boss portion on an outer peripheral side of the boss portion. Provided with a communication path for supplying hydraulic oil from the transmission case to the hydraulic oil introduction portion provided on the inner peripheral side of the cylindrical portion between the cylindrical portion and the boss portion. A communication path for supplying hydraulic oil from the transmission case to the hydraulic oil introduction portion provided on the outer peripheral side of the cylindrical portion between the cylindrical portion and the facing portion, the first sleeve being disposed The second sleeve provided with the above is disposed, and the first sleeve and the second sleeve are integrated.

  According to a fourth aspect of the present invention, in the clutch device for a transmission according to the second or third aspect, the hydraulic fluid supply unit is configured to supply hydraulic fluid that urges the piston in the anti-friction plate direction. A centrifugal balance chamber to be supplied is included, and the hydraulic oil introducing portion for the centrifugal balance chamber is provided on a vertical wall portion side of the transmission case in the cylindrical portion.

  With the above configuration, according to the first aspect of the present invention, the clutch drum of one clutch among the plurality of clutches arranged on the same axis is arranged on the radially inner side of the transmission case. A cylindrical portion fitted to the outer peripheral side of the boss portion extending along the axial center from the vertical wall portion is provided, and hydraulic oil to be supplied to the plurality of hydraulic oil supply portions is introduced into the cylindrical portion from the transmission case. A plurality of hydraulic oil introduction portions are provided, and the hydraulic oil introduction portions are provided on the inner peripheral side and the outer peripheral side of the cylindrical portion. As a result, the axial dimension can be shortened by shortening the axial dimension as compared with the case where the hydraulic oil introduction part is provided only on the inner peripheral side of the cylindrical part, and the axial dimension can be made compact. it can.

  According to the invention described in claim 2, the hydraulic oil introduction portion is also provided on the vertical wall portion side of the transmission case in the cylindrical portion, thereby further reducing the axial dimension of the cylindrical portion of the clutch drum. Thus, the axial dimension can be shortened, and the above-described effects can be more effectively achieved.

  According to a third aspect of the present invention, the first sleeve having a communication path for supplying hydraulic oil from the transmission case to the hydraulic oil introducing portion is disposed between the cylindrical portion and the boss portion. A second sleeve provided with a communication path for supplying hydraulic oil from the transmission case to the hydraulic oil introducing portion is disposed between the cylindrical portion and the opposing portion, and the first sleeve and the second sleeve are As a result of the integration, the number of parts can be reduced and variation in the position of the first sleeve and the second sleeve can be suppressed as compared with the case where the first sleeve and the second sleeve are formed separately. can do.

  According to the invention described in claim 4, the hydraulic oil supply section includes a centrifugal balance chamber, and the hydraulic oil introduction section for the centrifugal balance chamber is provided on the vertical wall portion side of the transmission case in the cylindrical portion. . Since the centrifugal balance chamber is supplied with lower hydraulic pressure than the hydraulic chamber, the hydraulic oil is used as a clutch drum by the hydraulic oil as compared to the case where the hydraulic oil introduction portion for the hydraulic chamber is provided on the vertical wall portion side of the transmission case in the cylindrical portion. The urging force that urges the cylindrical portion in the axial direction can be reduced, and the rotational resistance of the clutch drum can be suppressed.

It is sectional drawing of the rear part of the automatic transmission which concerns on 1st Embodiment of this invention. It is sectional drawing cut | disconnected in the other cross section of the rear part of the said automatic transmission. It is sectional drawing cut | disconnected by the other cross section of the rear part of the said automatic transmission. It is sectional drawing cut | disconnected by the other cross section of the rear part of the said automatic transmission. It is sectional drawing of the rear part of the said automatic transmission which expanded the principal part of FIG. It is sectional drawing of the automatic transmission along the Y6-Y6 line in FIG. It is the schematic of the automatic transmission seen from the Y7 direction in FIG. It is sectional drawing of the rear part of the automatic transmission which concerns on 2nd Embodiment of this invention. It is sectional drawing cut | disconnected in the other cross section of the rear part of the said automatic transmission. It is sectional drawing cut | disconnected by the other cross section of the rear part of the said automatic transmission. It is sectional drawing of the rear part of the said automatic transmission which expanded the principal part of FIG. It is sectional drawing which shows the conventional automatic transmission.

  Hereinafter, an embodiment in which the present invention is applied to an automatic transmission will be described.

  FIG. 1 is a cross-sectional view of the rear portion of the automatic transmission according to the first embodiment of the present invention, FIG. 2 is a cross-sectional view taken along another cross-section of the rear portion of the automatic transmission, and FIGS. FIG. 6 is a cross-sectional view taken along another cross section of the rear portion of the automatic transmission.

  As shown in FIGS. 1 to 4, the automatic transmission 1 according to this embodiment includes a plurality of planetary gears on an axis 3 a of an input shaft 3 connected to a drive source such as an engine in a transmission case 2. A transmission mechanism 4 having a set and a plurality of frictional engagement elements such as a clutch and a brake is provided.

  The automatic transmission 1 switches the power transmission path through the plurality of planetary gear sets by combining the engagement states of the plurality of friction engagement elements to change the gear ratio of the transmission mechanism 4 to obtain a predetermined gear stage. It is configured. For example, the automatic transmission 1 includes four planetary gear sets and five frictional engagement elements. By selectively engaging three of these frictional engagement elements, eight forward speeds and reverse speeds are formed. It is comprised so that.

  In the present embodiment, on the input shaft 3 extending from the drive source side at the rear portion of the transmission case 2 (hereinafter, the counter drive source side is the rear and the drive source side is the front), the drive source side The first and second clutches 10 and 20 are arranged in the axial direction on the side opposite to the driving source, the third clutch 30 is arranged on the inner peripheral side of the second clutch 20, and the inner periphery of the first clutch 10. A first planetary gear set 40 disposed on the side and a second planetary gear set 50 disposed on the inner peripheral side of the third clutch 30 are provided.

  In the automatic transmission 1, the second planetary gear set 50 is disposed on the inner peripheral side of the third clutch 30, so that the planetary gear set 50, the third clutch 30, and the second clutch 20 can be disposed to overlap each other in the radial direction. In comparison with the case where these are arranged in the axial direction, the axial dimension is shortened. Further, by arranging the first planetary gear set 40 on the inner peripheral side of the first clutch 10, the axial direction is shortened.

  The first, second, and third clutches 10, 20, and 30 are all clutch drums 11, 21, and 31 that are outer rotating members, clutch hubs 12, 22, and 32 that are inner rotating members, clutch drums 11, A plurality of friction plates 13 which are arranged side by side in the axial direction between 21 and 31 and the clutch hubs 12, 22 and 32 and are alternately engaged with the clutch drums 11, 21 and 31 and the clutch hubs 12, 22 and 32. , 23, 33, pistons 14, 24, 34 that are arranged on the side opposite to the driving source of the plurality of friction plates 13, 23, 33 and press the plurality of friction plates 13, 23, 33, and pistons 14, 24, 34 The hydraulic chambers 15, 25, and 35 are provided on the side opposite to the driving source and supplied with hydraulic oil (hydraulic pressure) that urges the pistons 14, 24, and 34 in the friction plate direction.

  When hydraulic pressure is supplied to the hydraulic chambers 15, 25, 35, the pistons 14, 24, 34 press the friction plates 13, 23, 33 from the counter drive source side, and the clutch drums 11, 21, 31 and the clutch By coupling the hubs 12, 22, and 32, the clutches 10, 20, and 30 are fastened.

  The first, second and third clutches 10, 20, 30 also have pistons 14, 24, 34 on the opposite side of the hydraulic chambers 15, 25, 35 across the pistons 14, 24, 34 in the anti-friction plate direction. Centrifugal balance chambers 16, 26, 36 are provided to which hydraulic oil to be energized is supplied.

  The centrifugal balance chambers 16, 26, and 36 are such that when the clutches 10, 20, and 30 are released, the pistons 14, 24, and 34 are pressed in the direction of the friction plate by the centrifugal force acting on the hydraulic pressure in the hydraulic chambers 15, 25, and 35. The friction plates 13, 23, 33 are prevented from being dragged by the above, and the urging force that urges the pistons 14, 24, 34 in the anti-friction plate direction is generated by the centrifugal force acting on the supplied hydraulic oil, This pressing force cancels the pressing force in the direction of the friction plate.

  In the automatic transmission 1, the hydraulic chambers 15, 25, 35 of the first, second, and third clutches 10, 20, 30 and the centrifugal balance chambers 16, 26, 36 use the clutch drum 11 of the first clutch 10. Next, the configuration of the hydraulic chambers 15, 25, 35 and the centrifugal balance chambers 16, 26, 36 will be described.

  FIG. 5 is a cross-sectional view of the rear part of the automatic transmission, in which the main part of FIG. 1 is enlarged. As shown in FIG. 5, a boss portion 2c extending from the vertical wall portion 2b extending in the radial direction to the drive source side along the axis 3a is provided at the rear portion of the transmission case 2 on the counter drive source side of the outer peripheral portion 2a. A cylindrical first sleeve 5 is fitted and fixed to the outer peripheral side of the boss portion 2c. The rear portion of the transmission case 2 is also provided with an opposing portion 2d extending in the axial direction facing the boss portion 2c on the outer peripheral side of the boss portion 2c, and a cylindrical second on the inner peripheral side of the opposing portion 2d. The sleeve 6 is fitted and fixed.

  As shown in FIG. 1, the clutch drum 11 of the first clutch 10 includes an outer cylindrical portion 61 that extends in the axial direction with which the friction plate 13 is engaged, and a bottom portion that extends in the radial direction on the counter drive source side of the outer cylindrical portion 61. 62 and an inner cylindrical portion 63 that extends in the axial direction on the inner side of the bottom portion 62, and is formed in a bottomed cylindrical shape, and the inner cylindrical portion 63 is formed on the outer peripheral side of the first sleeve 5 and the inner peripheral periphery of the second sleeve 6. And is rotatably supported by the transmission case 2 via the first sleeve 5 and the second sleeve 6.

  The clutch drum 11 extends from a central portion in the axial direction of the inner cylindrical portion 63 to a bottom portion 62 that extends in the radial direction along the front surface of the vertical wall portion 2b of the transmission case 2, respectively. A cylindrical first cylinder portion 65 and a second cylinder portion 66 extending forward are provided.

  The piston 34 of the third clutch 30 is fitted between the front outer peripheral surface of the inner cylindrical portion 63 of the clutch drum 11 and the inner peripheral surface of the first cylinder portion 65, and the outer peripheral surface of the first cylinder portion 65 and the clutch drum 11, the piston 24 of the second clutch 20 is fitted between the outer peripheral surface of the outer cylindrical portion 61 and the outer peripheral surface of the outer cylindrical portion 61 of the clutch drum 11 and the inner peripheral surface of the second cylinder portion 66. The piston 14 of the 1st clutch 10 is fitted by this.

  The hydraulic chamber 35 of the third clutch 30 is made oil-tight by the front outer peripheral surface of the inner cylindrical portion 63, the front surface of the bottom portion 62, the inner peripheral surface of the first cylinder portion 65, and the rear surface of the piston 34. The hydraulic chamber 25 of the second clutch 20 is formed in an oil-tight manner by the outer peripheral surface of the first cylinder portion 65, the front surface of the bottom portion 62, the inner peripheral surface of the outer cylindrical portion 61, and the rear surface of the piston 24. The hydraulic chamber 15 of the first clutch 10 is formed in an oil-tight manner by the outer peripheral surface of the outer cylindrical portion 61, the inner peripheral surface of the second cylinder portion 66, and the back surface of the piston 14.

  The piston 14 of the first clutch 10 is spline-engaged with the first member 71 extending in the axial direction from the hydraulic chamber 15 of the first clutch 10 on the outer peripheral side of the clutch drum 11 of the first clutch 10 and the first member 71. The second member 72 is connected and extends in the radial direction through the outer cylindrical portion 61 of the clutch drum 11 of the first clutch 10 and presses the friction plate 13 of the first clutch 10 from the counter drive source side. Yes.

  The back surface of the piston 14 constituting the hydraulic chamber 15 of the first clutch 10 is formed by the rear surface of the vertical wall portion 71 a provided at the rear portion of the first member 71. The hydraulic chamber 15 of the first clutch 10 is provided on the outer peripheral side of the clutch drum 11 and can be configured using the outer peripheral side of the clutch drum 11.

  The centrifugal balance chamber 16 of the first clutch 10 is formed in an oil-tight manner by the outer surface of the outer cylindrical portion 61 of the clutch drum 11, the inner peripheral surface of the first member 71, and the front surface of the vertical wall portion 71a. The centrifugal balance chamber 26 of the second clutch 20 is formed by the outer peripheral surface of the one cylinder portion 65, the rear surface of the vertical wall portion 65a extending outwardly provided at the front end portion thereof, and the front surface and front inner peripheral surface of the piston 24. A rear surface of the seal plate 75 that is formed in an oil-tight manner and extends in the radial direction attached to the front outer peripheral surface of the inner cylindrical portion 63 of the clutch drum 11, the front outer peripheral surface of the inner cylindrical portion 63 and the front surface of the piston 34. The centrifugal balance chamber 36 of the third clutch 30 is formed in an oil-tight manner by the front inner peripheral surface.

  The outer cylindrical portion 61 of the clutch drum 11 is connected to the first cylindrical portion 61a formed on the driving source side in a comb-like shape and engaged with the friction plate 13, and the counter driving source side is connected to the bottom portion 62, and the piston 24 is connected to the inner periphery. A second cylindrical portion 61b that is fitted to the surface and the piston 14 is fitted to the outer peripheral surface, and a vertical wall portion 61c that extends in the radial direction by connecting the first cylindrical portion 61a and the second cylindrical portion 61b. I have. The outer surface of the outer cylindrical portion 61 of the clutch drum 11 constituting the centrifugal balance chamber 16 is formed by the outer peripheral surface of the second cylindrical portion 61a and the rear surface of the vertical wall portion 61c.

  A disc spring 37 that functions as a return spring for returning the piston 34 in the clutch releasing direction is attached between the seal plate 75 and the piston 34 in the centrifugal balance chamber 36, and the outer cylindrical portion 61 is provided in the centrifugal balance chamber 16. A coil spring 17 that functions as a return spring for returning the piston 14 in the clutch releasing direction is mounted between the rear surface of the vertical wall portion 61 c and the vertical wall portion 71 a of the first member 71.

  As for the centrifugal balance chamber 26, as shown in FIG. 4, a leaf spring 27 that functions as a return spring for returning the piston 24 in the clutch release direction is attached to the counter drive source side of the piston 24. The piston 24 includes a protrusion 24a that extends through the bottom 62 of the clutch drum 11 and extends to the side opposite to the driving source, and a leaf spring 27 is connected and fixed to the protrusion 24a.

  FIG. 6 is a cross-sectional view of the automatic transmission along the line Y6-Y6 in FIG. 1, 2, 3, and 4 correspond to cross sections taken along lines Y1-Y1, Y2-Y2, Y3-Y3, and Y4-Y4 in FIG. 6, respectively.

  As shown in FIGS. 4 and 6, the leaf spring 27 includes a flat plate portion 27a extending in the radial direction orthogonal to the axial direction, and a drive source from the radially inner end of the flat plate portion 27a to the radially inner side. Two inclined portions 27b extending obliquely to the side, the flat plate portion 27a is fixed to the protrusion 24a of the piston 24, and the radially inner end of the inclined portion 27b contacts the bottom 62 of the clutch drum 11. The piston 24 is urged toward the counter drive source side. Three leaf springs 27 are provided at equal intervals in the circumferential direction.

  Thus, in the automatic transmission 1, the hydraulic chamber 15 of the first clutch 10 is provided on the outer peripheral side of the hydraulic chamber 25 of the second clutch 20, and the hydraulic chamber 35 of the third clutch 30 is connected to the second clutch 20. It is provided on the inner peripheral side of the hydraulic chamber 25. The centrifugal balance chamber 16 of the first clutch 10 is provided on the outer peripheral side of the centrifugal balance chamber 26 of the second clutch 20, and the centrifugal balance chamber 36 of the third clutch 30 is the same as that of the centrifugal balance chamber 26 of the second clutch 20. It is provided on the inner circumference side.

  In the automatic transmission 1, hydraulic chamber hydraulic oil supply oil passages 81 and 82 that supply hydraulic oil to supply hydraulic pressure to the hydraulic chambers 15, 25, and 35, respectively, using the clutch drum 11 of the first clutch 10. 83, and a centrifugal balance chamber hydraulic oil supply oil passage 84 for supplying hydraulic oil to the centrifugal balance chambers 16, 26, 36.

  As shown in FIG. 1, the hydraulic oil supply passage 81 for the hydraulic chamber for the first clutch includes an axial oil passage 81 a provided in the boss 2 c of the transmission case 2 and extending in the axial direction, and a first sleeve. 5 and is provided to extend in the axial direction into the communication path 81c communicating with the axial oil path 81a via the communication path 81b on the transmission case 2 side, and the inner cylindrical portion 63 of the clutch drum 11. The axial oil passage 81f communicated with the communication passage 81c of the first sleeve 5 through the communication hole 81d, the bottom 62 of the clutch drum 11, and the outer cylindrical portion 61 are provided so as to extend in the radial direction. Is constituted by a radial oil passage 81g communicated with the axial oil passage 81f and an opening 81h opening in the hydraulic chamber 15 of the first clutch 10.

  As shown in FIG. 2, the hydraulic oil supply fluid passage 82 for the second clutch hydraulic chamber includes an axial oil passage 82 a provided in the boss portion 2 c of the transmission case 2 and extending in the axial direction, and a first sleeve. 5 is provided to extend in the axial direction into the communication passage 82c communicated with the axial oil passage 82a via the communication passage 82b on the transmission case 2 side, and the inner cylindrical portion 63 of the clutch drum 11. An axial oil passage 82f communicated with the communication passage 82c of the first sleeve 5 through the communication hole 82d and a bottom portion 62 of the clutch drum 11 are provided so as to extend in the radial direction, and an inner end portion is provided in the axial oil passage. A radial oil passage 82g communicated with 82f and an opening 82h that opens to the hydraulic chamber 25 of the second clutch 20 are configured.

  As shown in FIG. 3, the hydraulic oil supply fluid passage 83 for the hydraulic chamber for the third clutch includes a radial oil passage 83 a provided in the facing portion 2 d of the transmission case 2 and extending in the radial direction, and the second sleeve 6. The communication path 83c communicated with the radial oil path 83a and the communication path of the second sleeve 6 via the communication hole 83d provided to extend in the inner cylindrical portion 63 of the clutch drum 11 in the axial direction. An axial oil passage 83f communicated with 83c, a radial oil passage 83g provided in the bottom 62 of the clutch drum 11 so as to extend in the radial direction, and an inner end portion thereof communicated with the axial oil passage 83f; The three-clutch 30 includes an opening 83h that opens into the hydraulic chamber 35.

  As shown in FIG. 5, the communication passage 81c provided in the first sleeve 5 constituting the hydraulic oil supply oil passage 81 for the first clutch is specifically connected to the communication hole 81b on the transmission case 2 side. Communication hole 81c1 and a circumferential groove 81c2 communicated with the communication hole 81d of the inner cylindrical portion 63 of the clutch drum 11. Similarly, the communication holes 82c of the first sleeve 5 and the communication holes 83c of the second sleeve 6 constituting the hydraulic oil supply oil passages 82 and 83 for the second and third clutches are similarly formed on the transmission case 2 side. , 83b and a circumferential groove communicated with the communication holes 82d, 83d of the inner cylindrical portion 63 of the clutch drum 11.

  The automatic transmission 1 is provided with a control valve unit (not shown), and the first, second, and third clutches 10, 10 through the hydraulic chamber hydraulic oil supply oil passages 81, 82, 83 are provided from the control valve unit. The hydraulic oil is supplied to the hydraulic chambers 15, 25, and 35 of the 20 and 30 to supply the fastening hydraulic pressure.

  On the other hand, as shown in FIG. 4, the centrifugal balance chamber hydraulic oil supply oil passage 84 communicates with an oil storage portion 85 provided in the outer peripheral portion 2 a of the transmission case 2 and extends in the axial direction. A radial oil passage 84b that communicates with the axial oil passage 84a and extends in the radial direction, a recess 2e formed between the boss portion 2c of the transmission case 2 and the opposing portion 2d, the first sleeve 5, 2 An oil reservoir 84d formed by the sleeve 6 and the inner cylindrical portion 63 of the clutch drum 11 and communicated with the radial oil passage 84b through the communication passage 84c, and a transmission case 2 in the inner cylindrical portion 63 of the clutch drum 11. An axial oil passage 84f in the inner cylindrical portion 63 communicated with the oil reservoir portion 84d through a communication hole 84e provided on the vertical wall portion 2b side, and a radial direction at the front portion of the inner cylindrical portion 63. Provided in The end portion is constituted by a radial oil passage 84g communicated with the axial oil passage 84f, and the opening portion on the radially outer side of the radial oil passage 84g faces the centrifugal balance chamber 36 of the third clutch 30. .

  The first centrifugal balance chamber is formed by a communication hole on the piston 34 side and a communication hole on the first cylinder part 65 side at a fitting part between the outer peripheral part of the piston 34 and the first cylinder part 65 of the third clutch 30. A communication passage 84j is provided, and a communication hole on the piston 24 side and an outer cylinder are formed in a fitting portion between the outer peripheral portion of the piston 24 of the second clutch 20 and the second cylindrical portion 61b of the outer cylindrical portion 61 of the clutch drum 11. A communication path 84k between the second centrifugal balance chambers is provided, which is a communication hole on the part 61 side.

  The hydraulic oil supplied to the centrifugal balance chamber 36 of the third clutch 30 by the hydraulic oil supply oil passage 84 for the centrifugal balance chamber is located on the outer peripheral side via the first and second centrifugal balance chamber communication paths 84j and 84k. The centrifugal balance chamber 26 of the second clutch 20 and the centrifugal balance chamber 16 of the first clutch 10 are sequentially supplied.

  FIG. 7 is a schematic view of the automatic transmission viewed from the Y7 direction in FIG. As shown in FIG. 7, the oil reservoir 85 is formed in a box shape with the upper part opened in the outer peripheral part 2 a of the transmission case 2, and the lower part has substantially the same height as the axis 3 a of the input shaft 3. Is provided. A cover 7 is disposed above the oil reservoir 85.

  The oil reservoir 85 is provided above the opening of the radial oil passage 84g on the centrifugal balance chamber 36 side of the hydraulic oil supply oil passage 84 for the centrifugal balance chamber that communicates the oil reservoir 85 and the centrifugal balance chamber 36. The hydraulic oil in the oil reservoir 85 is supplied to the centrifugal balance chamber 36 by gravity. In this way, the oil reservoir 85 supplies the hydraulic oil to the centrifugal balance chambers 16, 26, 36 via the centrifugal balance chamber hydraulic oil supply oil passage 84 or discharges it from the centrifugal balance chambers 16, 26, 36. Can be done.

  As shown in FIG. 6, the hydraulic chamber hydraulic oil supply oil passages 81, 82, 83 for the first, second, and third clutches are arranged at different positions at equal intervals in the circumferential direction. Two hydraulic chamber hydraulic oil supply oil paths 81, 82, 83 for the first, second, and third clutches are provided at intervals of 180 degrees, and six hydraulic chamber hydraulic oil supply oil paths 81, 82, 83 are 60 degrees. It is provided at intervals. As for the hydraulic oil supply oil passage 84 for the centrifugal balance chamber, two hydraulic oil supply oil passages 84 for the centrifugal balance chamber are provided at intervals of 180 degrees, and hydraulic oil supply for the hydraulic chambers for the first and second clutches in the circumferential direction is provided. It is provided between the oil passages 81 and 82.

  As described above, in the automatic transmission 1, the clutches 10, 20, and 30 are provided with the hydraulic chambers 15, 25, and 35 and the centrifugal balance chambers 16, 26, and 36 as hydraulic oil supply units to which hydraulic oil is supplied. , Hydraulic chamber hydraulic oil supply passages 81, 82 for supplying hydraulic fluid to the hydraulic chambers 15, 25, 35 and the centrifugal balance chambers 16, 26, 36 to the clutch drum 11 of the transmission case 2 and the first clutch 10, 83 and a hydraulic oil supply oil passage 84 for the centrifugal balance chamber are provided.

  The inner cylindrical portion 63 of the clutch drum 11 is provided with communication holes 81d, 82d, 83d as hydraulic oil introduction portions for introducing hydraulic oil from the transmission case 2 to the hydraulic oil supply portions 15, 25, 35. The communication holes 81d, 82d, and 83d are provided on the inner peripheral side and the outer peripheral side of the inner cylindrical portion 63. The communication holes 81 d and 82 d are provided side by side in the axial direction on the inner peripheral side of the inner cylindrical portion 63, and the communication hole 83 d is provided on the outer peripheral side of the inner cylindrical portion 63. The communication hole 81d on the inner peripheral side and the communication hole 83d on the outer peripheral side of the inner cylindrical portion 63 are provided adjacent to each other in the axial direction, but may be provided so as to overlap in the axial direction.

  Further, the communication holes 81d and 82d formed on the inner peripheral side of the inner cylindrical portion 63 of the clutch drum 11 and the communication passages 81c and 82c constituting the hydraulic oil supply oil passages 81 and 82, respectively, are axially connected to the first sleeve 5. In the outer peripheral surface of the first sleeve 5, seal member groove portions 5 a are formed on both axial sides of the communication passages 81 c and 82 c, and the seal member 8 is mounted.

  A communication hole 83 d formed on the outer peripheral side of the inner cylindrical portion 63 of the clutch drum 11 and a communication path 83 c constituting the hydraulic oil supply oil path 83 are provided in the second sleeve 6, and are formed on the inner peripheral surface of the second sleeve 6. Also, groove portions 6a for the seal member are formed on both sides in the axial direction of the communication passage 83c, and the seal member 8 is mounted.

  On the other hand, first and second planetary gear sets (hereinafter referred to as “first and second gear sets”) 40 and 50 arranged on the inner peripheral side of the first clutch 10 and the third clutch 30 are arranged side by side in the axial direction. As shown in FIG. 2, the first and second gear sets 40 and 50 are single-pinion type planetary gear sets, which are sun gears 41 and 51, ring gears 42 and 52, sun gears 41 and 51, and ring gear 42, respectively. , 52, and a plurality of pinions 43, 53 that mesh with the pinions 43, 53, and carriers 44, 54 that support the pinions 43, 53.

  The connection relationship between the rotating members of the first, second, and third clutches 10, 20, and 30 and other power transmission members will be described.

  The clutch drum 11 of the first clutch 10 is connected to another rotating element or the like disposed on the drive source side of the first gear set 40 by the spline engagement of the power transmission member 91 extending in the radial direction at the front end portion of the outer cylindrical portion 61. It is connected to the clutch hub 22 of the second clutch 20 and the clutch drum 31 of the third clutch 30 via a first cylinder portion 65 connected to the bottom portion 62.

  The clutch hub 22 of the second clutch 20 and the clutch drum 31 of the third clutch 30 are integrally formed of a common cylindrical part and coupled to the first cylinder part 65, and the second outer part of the cylindrical part is connected to the outer peripheral surface of the cylindrical part. The friction plate 23 of the second clutch 20 is engaged, and the friction plate 33 of the third clutch 30 is engaged with the inner peripheral surface of the cylindrical part.

  By integrating the clutch hub 22 of the second clutch 20 and the clutch drum 31 of the third clutch 30, the clutch hub 22 of the second clutch 20 and the clutch drum 31 of the third clutch 30 are formed separately. Compared to the case, the radial dimension is shortened.

  The clutch hub 12 of the first clutch 10 has a flange portion 12a extending radially inward from the front end portion of the spline portion with which the friction plate 13 is engaged, and the inner peripheral end portion of the flange portion 12a is the first end portion. It is connected to a ring gear 42 of one gear set 40.

  The clutch drum 21 of the second clutch 20 has a flange portion 21a extending inward in the radial direction from the front end portion of the spline portion with which the friction plate 23 is engaged through the front side of the cylindrical part. The portion 21 a is connected to the sun gear 41 of the first gear set 40 and the ring gear 52 of the second gear set 50.

  The clutch hub 32 of the third clutch 30 has a flange portion 32a extending radially inward from the rear end portion of the spline portion with which the friction plate 33 is engaged, and the inner peripheral end portion of the flange portion 32a is the first end portion. The two gear sets 50 are connected to the carrier 54 and connected to the input shaft 3 through the carrier 54 so as to rotate integrally with the input shaft 3.

  The sun gear 51 of the second gear set 50 is spline-fitted and connected to the non-drive source side of the power transmission member 92 that extends in the axial direction on the outer peripheral side of the input shaft 3, and the drive source side of the power transmission member 92 is It is connected to other rotating elements and the like arranged on the drive source side of the gear set 40. The carrier 44 of the first gear set 40 is spline-fitted and connected to the non-drive source side of the power transmission member 93 that extends in the axial direction on the outer peripheral side of the power transmission member 92. The first gear set 40 is connected to another rotating element or the like disposed on the drive source side.

  In the automatic transmission 1, an oil passage 3 b extending in the axial direction is provided on the input shaft 3, and the friction plates 13, 23, 33 of the first, second, and third clutches 10, 20, 30 are provided from the oil passage 3 b. In addition, the lubricating oil is supplied to the bearings between the pinions 43 and 53 of the first and second gear sets 40 and 50 and the carriers 44 and 54.

  The operation of the automatic transmission 1 according to this embodiment will be described. When hydraulic oil is supplied to the hydraulic chamber 15 of the first clutch 10 via the hydraulic chamber hydraulic oil supply oil passage 81 and the fastening hydraulic pressure is supplied. The first clutch 10 is engaged, the clutch drum 11 and the clutch hub 12 are coupled, and the hydraulic oil is supplied to the hydraulic chamber 25 of the second clutch 20 via the hydraulic oil supply oil passage 82 for the hydraulic chamber. When the hydraulic pressure is supplied, the second clutch 20 is engaged, the clutch drum 21 and the clutch hub 22 are coupled, and the hydraulic oil is supplied to the hydraulic chamber 35 of the third clutch 30 via the hydraulic chamber hydraulic oil supply oil passage 83. Is supplied and the engagement hydraulic pressure is supplied, the third clutch 30 is engaged and the clutch drum 31 and the clutch hub 32 are coupled.

  Further, the centrifugal balance chambers 16, 26, 36 of the first, second, and third clutches 10, 20, and 30 have a hydraulic fluid supply oil passage 84 for the centrifugal balance chamber and a communication path between the first and second centrifugal balance chambers. The hydraulic oil is supplied by 84j, 84k, and the hydraulic chambers 15, 25, 25 of the clutches 10, 20, 30 in the released state by the pressing force that presses the pistons 14, 24, 34 based on the centrifugal force acting on the hydraulic oil. The pressing force that presses the pistons 14, 24, and 34 in the fastening direction by the hydraulic oil in the cylinder 35 is cancelled.

  In the present embodiment, the clutch drum 11 of the first clutch 10 is rotatably supported by the transmission case 2 via the first sleeve 5 and the second sleeve 6, but the first sleeve 5 and the second sleeve 6 are supported. It is also possible to directly and freely support the transmission case 2 without using the.

  As described above, in the automatic transmission 1 according to the present embodiment, the clutch drum 11 of one clutch 10 among the plurality of clutches arranged on the same axis is located on the radially inner side of the transmission case 2. A cylindrical portion 63 fitted to the outer peripheral side of the boss portion 2c extending along the axial center from the vertical wall portion 2b is provided, and hydraulic oil to be supplied to the plurality of hydraulic oil supply portions is transmitted to the cylindrical portion 63. A plurality of hydraulic oil introduction portions 81d, 82d, 83d, 84e introduced from the case 2 are provided, and the hydraulic oil introduction portions 81d, 82d, 83d are provided on the inner peripheral side and the outer peripheral side of the cylindrical portion 63. As a result, the axial dimension can be shortened by shortening the axial dimension as compared with the case where the hydraulic oil introduction part is provided only on the inner peripheral side of the cylindrical part, and the axial dimension can be made compact. it can.

  Further, the hydraulic oil introducing portion 84e is also provided on the cylindrical wall 63 on the side of the vertical wall 2b of the transmission case 2, thereby further reducing the axial size of the cylindrical portion 63 of the clutch drum 11 and reducing the axial size. Shortening can be achieved.

  The hydraulic oil supply unit includes the centrifugal balance chambers 16, 26, and 36, and the hydraulic oil introduction unit 84 e for the centrifugal balance chamber is provided on the vertical wall 2 b side of the transmission case 2 in the cylindrical unit 63. Since the centrifugal balance chambers 16, 26, and 36 are supplied with lower pressure than the hydraulic chambers 15, 25, and 35, a hydraulic oil introduction portion for the hydraulic chamber is provided on the vertical wall portion side of the transmission case in the cylindrical portion. As compared with the case, the urging force that urges the cylindrical portion of the clutch drum in the axial direction by the hydraulic oil can be reduced, and the rotational resistance of the clutch drum can be suppressed.

  In the automatic transmission 1 according to the first embodiment, as shown in FIGS. 8 to 11, the inner cylindrical portion 63 of the clutch drum 11 is changed through a sleeve member in which the first sleeve and the second sleeve are integrated. It is also possible to support the machine case 2 so as to be rotatable between the boss part 2c and the opposing part 2d.

  FIG. 8 is a cross-sectional view of the rear portion of the automatic transmission according to the second embodiment of the present invention, FIG. 9 is a cross-sectional view taken along another cross-section of the rear portion of the automatic transmission, and FIG. FIG. 11 is a cross-sectional view of the rear portion of the automatic transmission in which the main portion of FIG. 8 is enlarged. 8, 9, 10, and 11 show the automatic transmission according to the second embodiment in FIGS. 1, 3, 4, and 5, respectively, of the automatic transmission according to the first embodiment. A cross section corresponding to the cross section is shown.

  Also in the automatic transmission 101 according to the second embodiment shown in FIGS. 8 to 11, the clutch drum 11 of the first clutch 10 is located on the inner side in the radial direction from the vertical wall portion 2 b of the transmission case 2 to the axial center. An inner cylindrical portion 63 fitted to the outer peripheral side of the boss portion 2c extending along the hydraulic cylinders 15, 25, 35 of the first, second, and third clutches 10, 20, and 30; Communication holes 81d, 82d, 83d, and 84e for introducing hydraulic oil to be supplied to the centrifugal balance chambers 16, 26, and 36 from the transmission case 2 are provided.

  In the inner cylindrical portion 63 of the clutch drum 11, communication holes 81 d and 82 d are provided on the inner peripheral side of the inner cylindrical portion 63 in the axial direction, and a communication hole 83 d is provided on the outer peripheral side of the inner cylindrical portion 63. A communication hole 84 e is provided on the vertical wall 2 b side of the transmission case 2 at 63.

  In the automatic transmission 101, the first sleeve 105 disposed between the inner cylindrical portion 63 of the clutch drum 10 and the boss portion 2 c of the transmission case 2, the inner cylindrical portion 63 of the clutch drum 10, and the transmission case 2. The second sleeve 106 disposed between the two opposing portions 2 d is formed integrally with the sleeve member 104.

  The sleeve member 104 connects the outer first sleeve 105 formed in a cylindrical shape, the inner second sleeve 106 formed in a cylindrical shape, and the counter driving source side of the first and second sleeves 105 and 106. The first sleeve 105 is fitted and fixed to the outer peripheral side of the boss 2c of the transmission case 2 and fixed to the transmission case 2, and the second sleeve 106 is connected to the transmission case 2. The two opposing portions 2d are disposed apart from the inner peripheral side.

  The inner cylindrical portion 63 of the clutch drum 11 is rotatably fitted to the outer peripheral side of the first sleeve 105 and the inner peripheral side of the second sleeve 106 of the sleeve member 104, and the clutch drum 11 is connected to the transmission via the sleeve member 104. The case 2 is rotatably supported.

  Also for the sleeve member 104, the first sleeve 105 is provided with communication passages 81c and 82c that respectively constitute the hydraulic chamber hydraulic oil supply passages 81 and 82 for the first and second clutches. A communication passage 83c constituting the hydraulic oil supply passage 83 for the hydraulic chamber for the third clutch is provided.

  As shown in FIG. 11, the communication path 81 c provided in the first sleeve 105 includes a communication hole 81 c 1 communicating with the communication hole 81 b on the transmission case 2 side and a communication hole 81 d of the inner cylindrical portion 63 of the clutch drum 11. And a circumferential groove 81c2 communicated with each other. The communication hole 82c of the first sleeve 105 and the communication hole 83c of the second sleeve 106 are also connected to the communication holes 82b and 83b on the transmission case side and the communication hole 82d of the inner cylindrical portion 63 of the clutch drum 11. , 83d and a circumferential groove communicated with 83d.

  Further, the seal member 8 is mounted on the outer peripheral surface of the first sleeve 105 in seal member grooves 105a formed on both axial sides of the communication passages 81c and 82c, and the communication passage 83c is provided on the inner peripheral surface of the second sleeve 106. The seal member 8 is attached to the seal member groove portions 106a formed on both sides in the axial direction.

  In the automatic transmission 101, as shown in FIG. 9, a concave portion 2f that is recessed in a circular shape is formed in the facing portion 2d of the transmission case 2, and a sealing member 108 that is formed in a substantially cylindrical shape is attached to the concave portion 2f. Has been. The seal member 108 is in contact with the inner cylindrical portion 63 of the clutch drum 11 so as to communicate the radial oil passage 83 a of the transmission case 2 and the communication passage 83 c of the sleeve member 104.

  In the automatic transmission 101, the hydraulic oil supply fluid passage 81 for the hydraulic chamber for the first clutch is connected to an axial oil passage 81a provided in the boss portion 2c of the transmission case 2 as shown in FIG. The clutch drum 11 communicated with the communication passage 81c of the sleeve member 104 communicated with the axial oil passage 81a via the communication passage 81b on the machine case 2 side and the communication passage 81c of the sleeve member 104 communicated with the communication hole 81d. An axial oil passage 81f, a radial oil passage 81g of the clutch drum 11 communicated with the axial oil passage 81f, and an opening 81h of the clutch drum 11 opening in the hydraulic chamber 15 of the first clutch 10 are configured. Yes.

  Regarding the hydraulic oil supply fluid passage for the hydraulic chamber for the second clutch, instead of the communication passage 81c of the first sleeve 5 constituting the hydraulic oil supply fluid passage 82 for the second clutch in the automatic transmission 1, The sleeve member 104 is configured in the same manner except that it is configured using the communication passage 81c of the first sleeve 5 of the sleeve member 104.

  As shown in FIG. 9, the hydraulic oil supply fluid passage 83 for the hydraulic chamber for the third clutch is arranged in the radial direction via the radial oil passage 83 a provided in the facing portion 2 d of the transmission case 2 and the seal member 108. The communication passage 83c of the sleeve member 104 communicated with the oil passage 83a, the axial oil passage 83f of the clutch drum 11 communicated with the communication passage 83c of the sleeve member 104 via the communication hole 83d, and the axial oil passage 83f. A radial oil passage 83g of the clutch drum 11 communicated with the opening 83h of the clutch drum 11 that opens to the hydraulic chamber 35 of the third clutch 30 is configured.

  On the other hand, as shown in FIG. 10, the centrifugal balance chamber hydraulic oil supply oil passage 84 communicates with the oil reservoir 85 and is provided in the outer peripheral portion 2 a and the vertical wall portion 2 b of the transmission case 2. 84a, the radial oil passage 84b, the axial oil passage 84c that is communicated with the radial oil passage 84b and provided in the boss portion 2c of the transmission case 2, the inner cylindrical portion 63 of the clutch drum 11, and the sleeve member 104. An oil reservoir 84d formed by the communication case 84m on the transmission case 2 side and the communication passage 84n on the sleeve member 104 side and communicated with the axial oil passage 84c, and an oil reservoir 84d via the communication hole 84e. The axial oil passage 84f and the radial oil passage 84g of the clutch drum 11 communicated with each other, and the opening on the radially outer peripheral side of the radial oil passage 84g is inside the centrifugal balance chamber 36 of the third clutch 30. I face.

  The hydraulic oil supplied to the centrifugal balance chamber 36 of the third clutch 30 by the hydraulic oil supply oil passage 84 for the centrifugal balance chamber also passes through the first and second centrifugal balance chamber communication passages 84j and 84k. 20 centrifugal balance chambers 26 and the centrifugal balance chamber 16 of the first clutch 10 are sequentially supplied.

  Thus, also in the automatic transmission 101 according to the second embodiment, the clutch drum 11 of one clutch 10 out of the plurality of clutches arranged on the same axis is the transmission case on the radially inner side. 2 is provided with a cylindrical portion 63 fitted to the outer peripheral side of the boss portion 2c extending along the axis from the vertical wall portion 2b, and the hydraulic oil for supplying the cylindrical portion 63 to a plurality of hydraulic oil supply portions is provided. A plurality of hydraulic oil introduction portions 81d, 82d, 83d, and 84e introduced from the transmission case 2 are provided, and the hydraulic oil introduction portions 81d, 82d, and 83d are provided on the inner peripheral side and the outer peripheral side of the cylindrical portion 63.

  Further, the automatic transmission 101 includes first communication passages 81c and 83c for supplying hydraulic oil from the transmission case 2 to the hydraulic oil introduction portions 81d and 82d between the cylindrical portion 63 and the boss portion 2c. A sleeve 105 is disposed, and a second sleeve 106 having a communication passage 83c for supplying hydraulic oil from the transmission case 2 to the hydraulic oil introducing portion 83d is disposed between the cylindrical portion 63 and the facing portion 2d. By integrating the first sleeve 105 and the second sleeve 106, the number of parts can be reduced and the number of parts can be reduced as compared with the case where the first sleeve and the second sleeve are formed separately. Variations in the positions of the first sleeve and the second sleeve can be suppressed.

  In the present embodiment, the inner cylindrical portion 63 of the clutch drum 11 is provided with communication holes 81d, 82d, 83d for the hydraulic chamber on the inner peripheral side and outer peripheral side, and the centrifugal balance chamber on the vertical wall portion 2b side of the transmission case 2. Although a communication hole 83e for the centrifugal balance chamber may be provided on the inner peripheral side or the outer peripheral side of the inner cylindrical portion 63 of the clutch drum 11, the communication hole 83e for the clutch drum 11 may be provided. In the inner cylindrical portion 63, communication holes 81d, 82d, and 83d for the hydraulic chamber may be provided on the vertical wall portion 2b side of the transmission case 2.

  The inner cylindrical portion 63 of the clutch drum 11 is provided with two communication holes 81d and 82d on the inner peripheral side as the hydraulic oil introducing portion, and one hydraulic oil introducing portion is provided on the outer peripheral side of the inner cylindrical portion 63 of the clutch drum 11. As a communication hole 83e, at least one hydraulic oil introduction portion is provided on the outer peripheral side and the inner peripheral side of the inner cylindrical portion 63, respectively.

  The present invention is not limited to the illustrated embodiments, and various improvements and design changes can be made without departing from the scope of the present invention.

  As described above, according to the present invention, the axial dimension can be shortened, and a compact configuration in the axial direction can be achieved. Therefore, the hydraulic oil is introduced into the plurality of hydraulic oil supply portions in the clutch drum. There is a possibility that the present invention is suitably used in the technical field of manufacturing a transmission including a clutch provided with a hydraulic oil introduction portion or a vehicle equipped with the clutch.

DESCRIPTION OF SYMBOLS 1,101 Automatic transmission 2 Transmission case 2b Vertical wall part 2c Boss part 2c Opposite surface part 5, 105 First sleeve 6, 106 Second sleeve 10, 20, 30 Clutch 11, 21, 31 Clutch drum 12, 22, 32 Clutch hubs 13, 23, 33 Friction plates 14, 24, 34 Pistons 15, 25, 35 Hydraulic chambers 16, 26, 36 Centrifugal balance chamber 61 Outer cylindrical portion 62 Bottom 63 Inner cylindrical portions 81, 82, 83, 84 Hydraulic oil supply Oil passage 81d, 82d, 83d, 84e Communication hole 104 Sleeve member

Claims (4)

A plurality of clutches disposed on the same axis in the transmission case, each of the plurality of clutches including a clutch drum, a clutch hub, and a plurality of friction plates disposed between the clutch drum and the clutch hub; A clutch device for a transmission comprising: a piston that presses the plurality of friction plates; and a hydraulic chamber that is supplied with hydraulic oil that urges the pistons toward the friction plates.
The clutch drum of one of the plurality of clutches includes a cylindrical portion extending in the axial direction on the radially inner side thereof,
The cylindrical portion is fitted to the outer peripheral side of a boss portion extending along the axis from the vertical wall portion of the transmission case, and a plurality of hydraulic oil supply portions including the hydraulic chambers of the clutch and other clutches A plurality of hydraulic oil introduction portions for introducing hydraulic oil to be supplied to the transmission case from the transmission case;
The hydraulic oil introduction part is provided on the inner peripheral side and the outer peripheral side in the cylindrical part,
A clutch device for a transmission. The hydraulic oil introduction part is also provided on the vertical wall part side of the transmission case in the cylindrical part,
The clutch device for a transmission according to claim 1. The transmission case is provided with a facing portion facing the boss portion on the outer peripheral side of the boss portion,
A first sleeve provided with a communication path for supplying hydraulic oil from the transmission case to the hydraulic oil introduction portion provided on the inner peripheral side of the cylindrical portion between the cylindrical portion and the boss portion. Arranged,
A second sleeve having a communication path for supplying hydraulic oil from the transmission case to the hydraulic oil introduction portion provided on the outer peripheral side of the cylindrical portion is disposed between the cylindrical portion and the facing portion. Established,
The first sleeve and the second sleeve are integrated;
The clutch device for a transmission according to claim 1 or 2, wherein the clutch device is a transmission. The hydraulic oil supply unit includes a centrifugal balance chamber to which hydraulic oil for urging the piston in the anti-friction plate direction is supplied.
The hydraulic oil introduction portion for the centrifugal balance chamber is provided on the vertical wall portion side of the transmission case in the cylindrical portion,
The clutch device for a transmission according to claim 2 or claim 3, wherein

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