JP6428201B2 - Transmission - Google Patents

Description

  The present invention relates to a transmission including a first clutch and a second clutch disposed around the first clutch.

  Conventionally, this type of transmission includes a clutch C4 configured as a multi-plate friction type hydraulic clutch and a clutch C3 configured as a multi-plate friction type hydraulic clutch and disposed around the clutch C4. (For example, refer to Patent Document 1). The clutches C3 and C4 of this transmission share a drum member including an inner drum and an outer drum having a base end portion welded to the outer periphery of the side wall portion of the inner drum. The drum member defines an inner cylinder portion that supports the piston of the clutch C4, an engagement oil chamber of the clutch C4 together with the piston, and an engagement oil chamber of the clutch C3 together with the piston of the clutch C3. And an annular wall portion defined radially outward from the oil synthesizing chamber. A plurality of engagement oil chamber oil holes communicating with the engagement oil chamber of the clutch C4 are formed in the inner cylinder portion of the drum member, and the engagement oil chamber of the clutch C3 is communicated with the annular wall portion. In this way, a plurality of oil passages for engagement oil chambers are formed radially. Furthermore, a plurality of first engagement oil chamber recesses communicating with the engagement oil chamber oil holes and a plurality of second engagements communicating with the engagement oil chamber oil passages are formed on the inner peripheral surface of the inner cylinder portion. An oil chamber recess is formed. Further, a sleeve is fitted (press-fitted) into the inner cylindrical portion of the drum member, and the drum member is rotatably supported by a fixed shaft portion (cylindrical portion) of the front support fixed to the case via the sleeve. Is done. The first engagement oil chamber recess corresponding to the clutch C4 communicates with the first engagement hydraulic pressure supply oil passage of the fixed shaft portion via the first oil hole formed in the sleeve, and corresponds to the clutch C3. The concave portion for the two engagement oil chambers communicates with the second engagement hydraulic pressure supply oil passage of the fixed shaft portion via the second oil hole formed in the sleeve. And between the sleeve and the fixed shaft portion, a plurality of seal rings for restricting the leakage of hydraulic oil so as to be located on both sides of the first and second engaging oil chamber recesses in the axial direction of the fixed shaft portion. And each seal ring is in sliding contact with the inner peripheral surface of the sleeve.

JP 2013-155849 A

  Here, in the transmission as described above, the drum member and the sleeve are rotated together, and the inner cylinder of the drum member is prevented from leaking the hydraulic oil supplied to the engagement oil chambers of the clutches C3 and C4. It is necessary to tightly fit the sleeve into the portion by, for example, press fitting. However, when the sleeve is tightly fitted in the inner cylinder portion of the drum member, the sleeve is partially inserted into the first engagement oil chamber recess or the second engagement oil chamber recess formed in the inner cylinder portion of the drum member. And the inner peripheral surface of the sleeve may be deformed (wavy). When such deformation of the inner peripheral surface of the sleeve occurs, it becomes necessary to perform cutting so that the inner peripheral surface becomes a perfect circle with respect to the sleeve that is in sliding contact with the seal ring, which increases the manufacturing cost of the transmission. Resulting in. Furthermore, in the cutting process, it is necessary to prevent chips from entering the first engagement oil chamber recess and the second engagement oil chamber recess, which further increases the processing cost.

  Therefore, the present invention suppresses the deformation of the sleeve fitted to the inner cylinder portion of the drum member shared by the first clutch and the second clutch disposed around the first clutch, thereby reducing the manufacturing cost of the transmission. The main purpose is to reduce this.

A transmission according to the present invention includes:
In a transmission including a first clutch having a first piston and a first engagement oil chamber, and a second clutch having a second piston and a second engagement oil chamber and disposed around the first clutch,
An inner cylinder portion that supports the first piston, the first engagement oil chamber together with the first piston, and the second piston and the first engagement oil chamber radially outward from the first engagement oil chamber. A drum member having an annular wall portion extending from the inner cylinder portion so as to define two engagement oil chambers;
A cylindrical sleeve fitted to the inner cylinder portion of the drum member,
The drum member communicates with the plurality of engagement oil chamber oil holes formed in the inner cylinder portion so as to communicate with the first engagement oil chamber, respectively, and the second engagement oil chamber. A plurality of engagement oil chamber oil passages formed in the annular wall portion and a plurality of first engagement members formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the engagement oil chamber oil holes, respectively. An oil chamber recess, and a plurality of second engagement oil chamber recesses formed on the inner peripheral surface of the inner cylinder so as to communicate with the oil passage for the engagement oil chamber,
The sleeve includes a first oil hole that allows communication between the first engagement oil chamber recess and a first engagement hydraulic pressure oil passage provided inside the sleeve; the second engagement oil chamber recess; A second oil hole that communicates with a second engagement hydraulic pressure oil passage provided inside the sleeve;
The second engagement oil chamber recess is formed deeper than the first engagement oil chamber recess so as to be closer to the annular wall portion than the first engagement oil chamber recess. The number of recesses for oil chambers is greater than the number of recesses for second engagement oil chambers.

  Thus, the 2nd engagement oil chamber recessed part corresponding to an outer 2nd clutch can be made deep by making the annular wall part of a drum member adjoin. Therefore, it is possible to reduce the width of the second engagement oil chamber recess in the circumferential direction of the inner cylinder portion (drum member) without increasing the oil passage resistance in the second engagement oil chamber recess. Further, by increasing the number of first engagement oil chamber recesses corresponding to the inner first clutch than the number of second engagement oil chamber recesses, the circumferential direction of each first engagement oil chamber recess The width at can be reduced. As a result, when the sleeve is tightly fitted to the inner cylinder portion of the drum member, the sleeve is prevented from entering the concave portions of the first and second engagement oil chambers, and the inner sleeve of the sleeve fitted to the inner cylinder portion is prevented. The peripheral surface can be maintained in a perfect circle. Therefore, in this transmission, it is not necessary to perform a cutting process for making the inner peripheral surface into a perfect circle shape with respect to the sleeve fitted in the inner cylinder portion. As a result, deformation of the sleeve fitted to the inner cylinder portion of the drum member shared by the first and second clutches can be suppressed, and the manufacturing cost of the transmission can be reduced.

It is a schematic block diagram of the power transmission device containing the automatic transmission which is a transmission by this invention. 2 is an operation table showing a relationship between each shift stage of the automatic transmission included in the power transmission device of FIG. 1 and operation states of clutches and brakes. It is a principal part expanded sectional view which shows the transmission by this invention. It is a principal part expanded sectional view which shows the transmission by this invention. It is a schematic diagram which shows the oil-path structure of the clutch of the transmission by this invention.

  Next, the form for implementing this invention is demonstrated, referring drawings.

  FIG. 1 is a schematic configuration diagram showing a power transmission device 20 including an automatic transmission 25 which is a transmission according to the present invention. A power transmission device 20 shown in the figure is connected to a crankshaft of an engine (not shown) mounted on a front wheel drive vehicle and can transmit power from the engine to left and right drive wheels (front wheels) (not shown). As shown in the figure, the power transmission device 20 includes, for example, a transmission case 22 made of aluminum alloy, a starting device (fluid transmission device) 23 housed in the transmission case 22, an oil pump 24, an automatic transmission 25, a gear. A mechanism (gear train) 40, a differential gear (differential mechanism) 50, a hydraulic control device 60 attached to the transmission case 22, and the like are included.

  The starting device 23 included in the power transmission device 20 includes an input-side pump impeller 23p connected to an engine crankshaft and an output-side turbine runner 23t connected to an input shaft (input member) 26 of an automatic transmission 25. , A stator 23s disposed inside the pump impeller 23p and the turbine runner 23t to rectify the flow of hydraulic oil from the turbine runner 23t to the pump impeller 23p, a one-way clutch 23o that restricts the rotational direction of the stator 23s in one direction, and lock-up The torque converter includes a clutch 23c, a damper mechanism 23d, and the like. However, the starting device 23 may be configured as a fluid coupling that does not include the stator 23s.

  The oil pump 24 is a gear pump having a pump assembly including a pump body and a pump cover, an external gear connected to the pump impeller 23p of the starting device 23 via a hub, an internal gear that meshes with the external gear, and the like. It is configured. The oil pump 24 is driven by power from the engine, and sucks hydraulic oil (ATF) stored in an oil pan (not shown) to generate a hydraulic pressure required by the starter 23 and the automatic transmission 25. Pump to 60.

  The automatic transmission 25 is configured as an 8-speed transmission, and as shown in FIG. 1, in addition to the input shaft 26, a double pinion type first planetary gear mechanism 30 and a Ravigneaux type second planetary gear. The gear mechanism 35 includes four clutches C1, C2, C3 and C4 for changing the power transmission path from the input side to the output side, two brakes B1 and B2, and a one-way clutch F1.

  The first planetary gear mechanism 30 of the automatic transmission 25 is engaged with a sun gear 31 that is an external gear and a ring gear 32 that is an internal gear disposed concentrically with the sun gear 31 and one of the first gear mechanism 30 and the sun gear 31. The other has a planetary carrier 34 that holds a plurality of sets of two pinion gears 33a and 33b meshing with the ring gear 32 so as to be rotatable (rotatable) and revolved. As illustrated, the sun gear 31 of the first planetary gear mechanism 30 is fixed to the transmission case 22, and the planetary carrier 34 of the first planetary gear mechanism 30 is coupled to the input shaft 26 so as to be integrally rotatable. The first planetary gear mechanism 30 is configured as a so-called reduction gear, and decelerates the power transmitted to the planetary carrier 34 as an input element and outputs it from a ring gear 32 as an output element.

  The second planetary gear mechanism 35 of the automatic transmission 25 is an internal gear disposed concentrically with the first sun gear 36a and the second sun gear 36b, which are external gears, and the first and second sun gears 36a and 36b. Ring gear 37, a plurality of short pinion gears 38a meshing with first sun gear 36a, a plurality of long pinion gears 38b meshing with second sun gear 36b and a plurality of short pinion gears 38a and meshing with ring gear 37, a plurality of short pinion gears 38a, It has a planetary carrier 39 for holding a plurality of long pinion gears 38b so as to be rotatable (rotatable) and revolved. The ring gear 37 of the second planetary gear mechanism 35 functions as an output member of the automatic transmission 25, and the power transmitted from the input shaft 26 to the ring gear 37 is transmitted to the left and right via the gear mechanism 40, the differential gear 50 and the drive shaft 51. Is transmitted to the driving wheel. The planetary carrier 39 is supported by the transmission case 22 via the one-way clutch F1, and the rotation direction of the planetary carrier 39 is limited to one direction by the one-way clutch F1.

  The clutch C1 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The ring gear 32 of the first planetary gear mechanism 30 and the second planetary gear mechanism 35 This is a multi-plate friction type hydraulic clutch (friction engagement element) capable of connecting the first sun gear 36a to each other and releasing the connection therebetween. The clutch C2 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The input shaft 26 and the planetary carrier 39 of the second planetary gear mechanism 35 are connected to each other. It is a multi-plate friction type hydraulic clutch that can be connected and released from both.

  The clutch C3 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The ring gear 32 of the first planetary gear mechanism 30 and the second planetary gear mechanism 35 This is a multi-plate friction hydraulic clutch capable of connecting the second sun gear 36b to each other and releasing the connection therebetween. The clutch C4 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The planetary carrier 34 and the second planetary gear mechanism 35 of the first planetary gear mechanism 30 are provided. This is a multi-plate friction hydraulic clutch that can connect the second sun gear 36b to each other and release the connection therebetween.

  The brake B1 has a hydraulic servo including a plurality of friction plates, separator plates, an oil chamber to which hydraulic oil is supplied, and the like, so that the second sun gear 36b of the second planetary gear mechanism 35 cannot be rotated to the transmission case 22. This is a multi-plate friction type hydraulic brake that can be fixed and can release the fixing of the second sun gear 36b to the transmission case 22. The brake B2 has a hydraulic servo including a plurality of friction plates, separator plates, an oil chamber to which hydraulic oil is supplied, and the planetary carrier 39 of the second planetary gear mechanism 35 is fixed to the transmission case 22 so as not to rotate. This is a multi-plate friction type hydraulic brake that can release the fixation of the planetary carrier 39 to the transmission case 22.

  The one-way clutch F1 includes an inner race coupled to (fixed to) the planetary carrier 39 of the second planetary gear mechanism 35, an outer race, a plurality of sprags, a plurality of springs (plate springs), a cage, and the like. When the outer race rotates in one direction with respect to the race, torque is transmitted through each sprag, and when the outer race rotates in the other direction with respect to the inner race, both are rotated relative to each other. However, the one-way clutch F1 may have a configuration other than a sprag type such as a roller type.

  The clutches C1 to C4 and the brakes B1 and B2 operate by receiving hydraulic oil supplied and discharged by the hydraulic control device 60. FIG. 2 shows an operation table showing the relationship between the respective shift stages of the automatic transmission 25 and the operating states of the clutches C1 to C4, the brakes B1 and B2, and the one-way clutch F1. The automatic transmission 25 provides the forward 1st to 8th gears and the reverse 1st and 2nd gears by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG. . Note that at least one of the clutches C1 to C4 excluding the brake B1 and the brake B2 may be a meshing engagement element such as a dog clutch.

  The gear mechanism 40 is fixed to a counter drive gear 41 connected to the ring gear 37 of the second planetary gear mechanism 35 of the automatic transmission 25 and a counter shaft 42 extending in parallel with the input shaft 26 of the automatic transmission 25. A counter driven gear 43 that meshes with the counter drive gear 41, a drive pinion gear (final drive gear) 44 that is integrally formed (or fixed) on the counter shaft 42 so as to be spaced apart from the counter driven gear 43 in the axial direction, and a drive pinion gear 44 and a differential ring gear (final driven gear) 45 coupled to the differential gear 50.

  FIG. 3 is an enlarged cross-sectional view of a main part showing the automatic transmission 25 of the power transmission device 20. FIG. 2 shows the configuration around the clutches C3 and C4 included in the automatic transmission 25. As shown in the drawing, a clutch C3 (second clutch) that fastens the ring gear 32 of the first planetary gear mechanism 30 and the second sun gear 36b of the second planetary gear mechanism 35 is connected to the planetary carrier 34 of the first planetary gear mechanism 30. It arrange | positions around the clutch C4 (1st clutch) which fastens the 2nd sun gear 36b of the 2nd planetary gear mechanism 35. As shown in FIG.

  The clutch C3 includes a clutch hub (second clutch hub) 3, a plurality of friction plates (second friction engagement plates) 304f whose inner peripheral portions are fitted to the clutch hub 3, and a clutch drum (second clutch drum). 300, a plurality of separator plates (second friction engagement plates) 304s whose outer peripheral portions are fitted to the clutch drum 300, and a piston (second piston) that presses the friction plates 304f and the separator plates 304s into friction engagement. ) 305. The clutch hub 3 is integrated (connected) to the ring gear 32 of the first planetary gear mechanism 30 as a power input member, and rotates integrally with the ring gear 32. The clutch drum 300 is connected to the second sun gear 36b of the second planetary gear mechanism 35 as a power output member (power transmission target), and rotates integrally with the second sun gear 36b. The friction plate 304f fitted to the clutch hub 3 is an annular member having a friction material stuck on both sides, and the separator plate 304s fitted to the clutch drum 300 is an annular member formed on both sides smoothly. is there.

  As shown in FIGS. 3 and 4, the clutch drum 300 of the clutch C3 extends in the axial direction of the clutch drum 300 (automatic transmission 25) and is connected to the second planetary gear mechanism 35 via a connecting member (not shown). A substantially cylindrical outer cylinder part 301 (second outer cylinder part) connected to the second sun gear 36b and a base end part (the right end in FIGS. 3 and 4) of the outer cylinder part 301 extend inward. A substantially annular annular wall portion (second annular wall portion) 302 extends from the inner peripheral portion of the annular wall portion 302 in the same direction (coaxially) as the outer tubular portion 301 so as to be located inside the outer tubular portion 301. A substantially cylindrical inner cylinder portion 303 (second inner cylinder portion) that is taken out and extends in the axial direction of the clutch drum 300. The outer cylindrical portion 301, the annular wall portion 302, and the inner cylindrical portion 303 are integrally formed by casting, for example, an aluminum alloy, and the annular wall portion 302 is formed between the proximal end portion of the outer cylindrical portion 301 and the inner cylindrical portion 303. It extends radially from the proximal end. In the clutch drum 300 configured as described above, the outer cylinder portion 301 on the outer side and the inner cylinder portion 303 on the inner side function as ribs, respectively, so that the strength can be improved satisfactorily.

  Splines 301 s that can be engaged with the concavo-convex portions formed on the outer peripheral portion of each separator plate 304 s are formed on the inner peripheral surface of the outer cylindrical portion 301 of the clutch drum 300. A plurality of separator plates 304 s are fitted to the splines 301 s of the outer cylinder portion 301 so as to be alternately arranged with a plurality of friction plates 304 f fitted to the clutch hub 3. Further, a backing plate is fitted to the spline 301s of the outer cylinder portion 301 so as to be able to come into contact with the friction plate 304f arranged on the first and second planetary gear mechanisms 30, 35 side (left side in FIG. 3). Combined. The backing plate is supported in the axial direction by a snap ring attached to the outer cylinder portion 301.

  The inner cylinder portion 303 is formed to be shorter than the outer cylinder portion 301, and has a cylindrical outer peripheral surface and a concave cylindrical inner peripheral surface 303i each having the axis of the clutch drum 300 as a central axis. The piston 305 is supported by the outer peripheral surface of the inner cylindrical portion 303 and the inner peripheral surface of the outer cylindrical portion 301 surrounding the inner cylindrical portion 303 so as to be movable in the axial direction. In the present embodiment, an uneven portion that can be engaged with the spline 301 s of the outer cylinder portion 301 is formed on the outer peripheral portion of the pressing portion of the piston 305 that contacts the separator plate 304 s located closest to the engine side (right side in FIG. 3). The piston 305 is prevented from rotating by the spline 301s.

  Further, a seal member is disposed between the piston 305 and the outer peripheral surface of the inner cylinder portion 303 and between the piston 305 and the inner peripheral surface of the outer cylinder portion 301, and the annular wall portion 302 of the clutch drum 300 and the piston 305 are disposed. An engagement oil chamber (second engagement oil chamber) 306 to which hydraulic oil (engagement hydraulic pressure) for engaging the clutch C3 is supplied is defined between the rear surface and the rear surface. That is, in the clutch C <b> 3, the engagement oil chamber 306 is defined by the clutch drum 300 (the annular wall portion 302) and the piston 305. Further, as shown in FIGS. 3 and 4, a plurality (four in the present embodiment) of oil holes (through holes) 303 x communicating with the engagement oil chamber 306 are provided in the inner cylinder portion 303 in the circumferential direction. It is formed at intervals.

  The clutch C4 includes a clutch hub (first clutch hub) 4, a plurality of friction plates (first friction engagement plates) 404f whose inner peripheral portions are fitted to the clutch hub 4, and a clutch drum (first clutch drum). 400, a plurality of separator plates (first friction engagement plates) 404s whose outer peripheral portions are fitted to the clutch drum 400, and a piston (first piston) that presses the friction plates 404f and the separator plates 404s into friction engagement. 405. The clutch hub 4 is integrated (connected) with the planetary carrier 34 of the first planetary gear mechanism 30 as a power input member, and rotates integrally with the planetary carrier 34. The clutch drum 400 is connected to the second sun gear 36b of the second planetary gear mechanism 35 as a power output member (power transmission target), and rotates integrally with the second sun gear 36b. The friction plate 404f fitted to the clutch hub 4 is an annular member with friction material stuck on both sides, and the separator plate 404s fitted to the clutch drum 400 is an annular member formed on both sides smoothly. is there.

  As shown in FIGS. 3 and 4, the clutch drum 400 of the clutch C4 includes a substantially cylindrical outer cylinder portion 401 (first outer cylinder portion) extending in the axial direction of the clutch drum 400 (automatic transmission 25). A substantially annular annular wall portion (first annular wall portion) 402 extending inwardly from one end of the outer cylindrical portion 401, and an inner peripheral portion of the annular wall portion 402 positioned inside the outer cylindrical portion 401. And a substantially cylindrical inner cylinder 403 (first inner cylinder or inner cylinder) extending in the same direction (coaxial) as the outer cylinder 401 and extending in the axial direction of the clutch drum 400. Including. The outer tubular portion 401, the annular wall portion 402, and the inner tubular portion 403 are integrally formed by casting, for example, an aluminum alloy, and the annular wall portion 402 is formed from the proximal end portion of the outer tubular portion 401 and the inner tubular portion 403. It extends radially inward from the base end.

  In the inner cylinder portion 403 of the clutch drum 400, a sleeve 500 formed in a cylindrical shape with steel (iron) is tightly fitted (integrated) by, for example, press-fitting so as to rotate integrally with the clutch drum 400. . Further, in the sleeve 500, an annular front support (front support portion) made of, for example, an aluminum alloy that is fixed (integrated) to the transmission case 22 that accommodates the clutches C3 and C4 and constitutes a part of the transmission case 22. A 22 f cylindrical portion 220 is inserted. Further, a bush 92 (see FIG. 3) is interposed between the free end portion of the inner cylindrical portion 403 and the cylindrical portion 220. Accordingly, the clutch drum 400, that is, the inner cylinder portion 403 is rotatably supported by the front support 22f, that is, the transmission case 22, via the sleeve 500 and the like. A stator shaft 230 connected to the stator 23s of the starting device 23 (torque converter) via a one-way clutch 23o is non-rotatably connected (fixed) to the cylindrical portion 220 of the front support 22f.

  A spline 401 s that can be engaged with an uneven portion formed on the outer peripheral portion of each separator plate 404 s is formed on the inner peripheral surface of the outer cylindrical portion 401 of the clutch drum 400. A plurality of separator plates 404s are fitted to the splines 401s of the outer cylinder portion 401 so as to be alternately arranged with a plurality of friction plates 404f fitted to the clutch hub 4. In addition, a backing plate is fitted to the spline 401s of the outer cylinder portion 401 so as to be able to come into contact with the friction plate 404f arranged on the most first and second planetary gear mechanisms 30, 35 side (left side in FIG. 3). Combined. The backing plate is supported in the axial direction by a snap ring attached to the outer cylinder portion 401.

  The annular wall 402 of the clutch drum 400 includes an annular outer wall 402 a extending radially inward (inner cylinder 403 side) from the base end of the outer cylinder 401, and a radially outer side from the inner cylinder 403. And an annular inner wall portion 402b that extends in the axial direction, and a reduced diameter portion 402n that extends in the axial direction between the inner peripheral portion of the outer wall portion 402a and the outer peripheral portion of the inner wall portion 402b. The inner wall portion 402b is offset in the direction away from the outer tube portion 401 with respect to the outer wall portion 402a, and is closer to the engine side than the outer wall portion 402a (the opposite side to the free end portion of the clutch drum 400, that is, FIG. 3 and FIG. 4 on the right). Further, the reduced diameter portion 402 n has an outer peripheral surface 402 o that is located on the opposite side of the outer cylindrical portion 401 with respect to the outer wall portion 402 a and is reduced in diameter from the outer peripheral surface of the outer cylindrical portion 401. The outer peripheral surface 402o of the reduced diameter portion 402n is formed in a cylindrical surface shape having the axis of the clutch drum 400 as the center axis, and the radius of curvature of the outer peripheral surface 402o is larger than the radius of curvature of the inner peripheral surface 303i of the inner cylindrical portion 303. It is determined to be extremely small.

  Further, the annular wall portion 402 (inner wall portion 402b) of the clutch drum 400 faces the piston 405 between the outer tube portion 401 and the inner tube portion 403 in the radial direction (toward the left side in FIGS. 3 and 4). ) The intermediate cylindrical portion 420 formed so as to extend, and the intermediate cylindrical portion 420 is surrounded between the outer peripheral surface 402o of the reduced diameter portion 402n and the intermediate cylindrical portion 420 in the radial direction, and the inner wall portion 402b And an annular recess 402c formed to be recessed from the inner surface toward the outside (the right side in FIGS. 3 and 4). The inner cylinder 403 of the clutch drum 400 is formed to be longer than the outer cylinder 401, and the piston 405 is supported by the outer peripheral surface of the inner cylinder 403 so as to be movable in the axial direction.

  The piston 405 of the clutch C4 includes a pressure receiving portion 405a that is movably supported by the outer peripheral surface of the inner cylinder portion 403, and extends from the outer peripheral portion of the pressure receiving portion 405a to the most engine side (right side in FIGS. 3 and 4). A pressing portion 405b that is in contact with the separator plate 404s, a cylindrical extending portion 405c that extends from the outer peripheral portion of the pressure receiving portion 405a to the opposite side of the pressing portion 405b, and an inner peripheral surface of the extending portion 405c. And a concave cylindrical surface 405d extending on the outer side in the radial direction and opposite to the extending portion 405c. On the outer peripheral portion of the pressing portion 405b, an uneven portion that can be engaged with the spline 401s of the outer cylinder portion 401 of the clutch drum 400 is formed. As a result, the piston 405 is prevented from rotating by the spline 401s. Further, the extending portion 405c of the piston 405 is inserted (fitted) into an annular recess 402c formed in the annular wall portion 402 of the clutch drum 400, and the inner peripheral surface of the extending portion 405c defines the annular recess 402c. Slidably contacts the outer peripheral surface (cylindrical surface) 421 of the intermediate cylindrical portion 420 to be performed.

  A seal member such as a D ring or an O ring is disposed between the pressure receiving portion 405a of the piston 405 and the outer peripheral surface of the inner cylindrical portion 403, and the inner peripheral surface of the extending portion 405c of the piston 405 and the intermediate cylindrical portion. Between the outer peripheral surface 421 of 420, a seal member 90 such as a D ring or an O ring is disposed. Accordingly, the clutch C4 is engaged between the annular wall portion 402 (inner wall portion 402b) of the clutch drum 400 and the back surface of the pressure receiving portion 405a of the piston 405 and radially inward from the outer peripheral surface of the extending portion 405c. An engagement oil chamber (first engagement oil chamber) 406 to which hydraulic oil (engagement hydraulic pressure) is supplied is defined. That is, in the automatic transmission 25, the engagement oil chamber 406 is defined radially inward of the engagement oil chamber 306 of the clutch C3 by the clutch drum 400 (the annular wall portion 402) and the piston 405.

  Further, the inner cylinder 403 of the clutch drum 400 integrally rotates the cancel plate 407 so as to be positioned on the first and second planetary gear mechanisms 30 and 35 side (left side in FIGS. 3 and 4) with respect to the piston 405. To support. The inner peripheral portion of the cancel plate 407 is supported in the axial direction by a snap ring attached to the inner cylinder portion 403. A lip seal (seal member) 91 is attached to the outer periphery of the cancel plate 407, and the seal member 91 is in sliding contact with a concave cylindrical surface 405d formed on the piston 405. As a result, the cancel plate 407 defines a centrifugal oil pressure cancel chamber (first centrifugal oil pressure cancel chamber) 408 for canceling the centrifugal oil pressure generated in the engagement oil chamber 406 together with the piston 405. Further, a plurality of return springs 409 are disposed between the piston 405 and the cancel plate 407.

  The clutch drum 300 of the clutch C3 disposed around the clutch C4 is fixed to the outer peripheral surface of the clutch drum 400 of the clutch C4 so as to surround at least a part of the outer cylinder portion 401. That is, the inner cylinder portion 303 of the clutch drum 300 is fitted to the reduced diameter portion 402n of the clutch drum 400 so that the front end thereof is in contact with the back surface of the outer wall portion 402a of the clutch drum 400 (annular wall portion 402). The inner peripheral surface 303i of the cylindrical portion 303 is joined to the outer peripheral surface 402o of the reduced diameter portion 402n by welding such as electron beam welding or laser welding. Thus, the clutch drums 300 and 400 are integrated coaxially and constitute a single drum member shared by the clutches C3 and C4. Further, the inner cylinder portion 303 of the clutch drum 300 constitutes an inner cylinder portion in the one drum member. Further, the annular wall 302 of the clutch drum 300 and the inner wall 402 b of the annular wall 402 of the clutch drum 400 define an engagement oil chamber 306 together with the piston 305 and an engagement oil chamber 406 together with the piston 405. An annular wall portion of the one drum member that defines

  In the automatic transmission 25, an annular cancellation chamber defining portion 410 is integrally formed with the clutch drum 400 (outer cylinder portion 401) of the clutch C4. The cancel chamber defining section 410 defines a centrifugal oil pressure cancel chamber 308 for canceling the centrifugal oil pressure generated in the engagement oil chamber 306 of the outer clutch C3 together with the clutch drum 300 and the piston 305. In the present embodiment, as shown in FIGS. 3 and 4, the cancel chamber defining portion 410 has an inner portion of the outer cylinder portion 301 of the clutch drum 300 that is outward from the outer tube portion 401, that is, radially outward from the annular recess 402 c. It extends toward the circumferential surface.

  Further, the outer peripheral surface of the cancel chamber defining portion 410 is in sliding contact with the inner peripheral surface of the piston 305 of the clutch C3, and a D ring or O ring is provided between the cancel chamber defining portion 410 and the inner peripheral surface of the piston 305. Such a sealing member is arranged. As a result, a centrifugal hydraulic pressure cancel chamber 308 is defined between the back surface of the cancel chamber defining portion 410 and the outer wall portion 402a (the right side surface in FIGS. 3 and 4) and the piston 305. Further, a plurality of return springs 309 are disposed between the back surface of the cancel chamber defining unit 410 and the piston 305. In the present embodiment, a plurality of protrusions that protrude toward the piston 305 and engage with one end of the corresponding return spring 309 are formed at equal intervals on the back surface of the cancel chamber defining unit 410.

  Thus, by integrally forming the cancel chamber defining portion 410 for the clutch C3 on the clutch drum 400 of the clutch C4 including the outer cylinder portion 401, the annular wall portion 402 and the inner cylinder portion 403, the clutches C3 and C4 The number of parts and the number of assembling steps can be reduced, and the accuracy of each part in the clutch drum 400, that is, the positional accuracy of the outer cylinder 401, the annular wall 402, the inner cylinder 403, and the cancel chamber defining part 410 can be easily improved. Can do. Since the cancel chamber defining portion 410 is integrally formed with the clutch drum 400, the piston 405, the return spring 409, the seal member, and the like are attached to the outer peripheral surface 402o of the clutch drum 400 (the reduced diameter portion 402n). Prior to welding, the clutch drum 300 is assembled in advance.

  Further, by integrally forming the outer tube portion 401, the annular wall portion 402, the inner tube portion 403, and the cancel chamber defining portion 410, the outer tube portion 401 and the inner tube portion 403 function as ribs and the cancel chamber is defined. The thickness of the portion 410 can be ensured and the strength of the clutch drum 400 can be ensured satisfactorily. Thereby, the clutch drum 400 can be made of a lightweight material such as an aluminum alloy to reduce the weight. Further, in the present embodiment, the cancel chamber defining portion 410 is located on the outer side so as to be located on the first and second planetary gear mechanisms 30 and 35 side (left side in FIG. 4) with respect to the outer wall portion 402a of the clutch drum 400. It is offset from the wall 402a in the axial direction of the outer cylinder 401. In this way, by offsetting the cancel chamber defining portion 410 in the axial direction of the outer cylinder portion 401 from the outer wall portion 402a, stress concentration around the proximal end portion of the outer cylinder portion 401 is suppressed, and the clutch drum 400 The strength can be further improved. However, instead of integrally forming the cancel chamber defining portion 410 on the clutch drum 400, a separate cancel chamber defining member may be welded or fastened to the clutch drum 400.

  3 to 5, the oil for supplying hydraulic oil to the engagement oil chamber 306 and the centrifugal oil pressure cancellation chamber 308 of the clutch C3 and the engagement oil chamber 406 and the centrifugal oil pressure cancellation chamber 408 of the clutch C4. The road structure will be described. FIG. 5 is a schematic view showing a state in which the inner surface of the inner cylindrical portion 403 is viewed from the axial center side of the clutch drum 400. The broken line in FIG. 5 shows the elements of the sleeve 500, and the two-dot chain line in FIG. Indicates elements of the front support 22f.

  As shown in FIGS. 3 and 4, in the automatic transmission 25, hydraulic oil is supplied to the engagement oil chamber 306 and the centrifugal oil pressure cancellation chamber 308 of the clutch C <b> 3 defined around the inner cylinder portion 303 of the clutch drum 300. In order to allow exhaustion, a plurality (the same number as the oil holes 303x, four in the present embodiment) of the oil passages 402x for engagement oil chambers and a plurality (in the present embodiment, in the inner wall portion 402b of the clutch drum 400) are provided. 4) cancellation chamber oil passages 402y are formed. The plurality of engagement oil chamber oil passages 402x extend radially and radially, and communicate with corresponding oil holes 303x of the inner cylinder portion 303 of the clutch drum 300, respectively. The plurality of cancellation chamber oil passages 402y alternately extend radially and radially so as not to overlap the plurality of engagement oil chamber oil passages 402x when viewed from the axial direction, and are formed in the clutch drum 400, respectively. It communicates with a corresponding one of the plurality of recesses 402r (see FIGS. 3 and 4). The recess 402r is formed to extend in a substantially L shape across the back surface of the outer wall 402a of the clutch drum 400 and the outer peripheral surface 402o of the reduced diameter portion 402n and communicate with the centrifugal hydraulic pressure cancel chamber 308.

  In this way, the engagement oil chamber oil passage 402x and the cancellation chamber oil passage 402y are formed on substantially the same plane in the inner wall portion 402b of the clutch drum 400, so that the clutch drum 400 and the clutches C3 and C4 can be connected. An increase in axial length can be suppressed. Furthermore, the engaging oil chamber oil passage 402x and the canceling chamber oil passage 402y are alternately formed as viewed from the axial direction, so that they operate substantially equally with respect to the annular engaging oil chamber 306 and the centrifugal oil pressure canceling chamber 308. It becomes possible to supply oil.

  As shown in FIGS. 4 and 5, the inner cylinder portion 403 of the clutch drum 400 has a plurality (eight in this embodiment) of C4 engagement oils respectively communicating with the engagement oil chambers 406 of the clutch C4. A chamber oil hole 403x and a plurality (four in this embodiment) of C4 cancel chamber oil holes 403y each communicating with the centrifugal hydraulic pressure cancel chamber 408 of the clutch C4 are formed. The plurality of oil holes 403x for C4 engagement oil chambers are formed in the inner cylinder portion 403 so as to be arranged in pairs in the circumferential direction and in close proximity to each other. The plurality of C4 cancellation chamber oil holes 403y are separated from the annular wall portion 402 (inner wall portion 402b) of the clutch drum 400 and spaced apart in the circumferential direction (such as the C4 engagement oil chamber oil holes 403x). It is formed in the inner cylinder part 403 so that it may line up.

  Further, a plurality (four in this embodiment) of C3 engagement oil chamber recesses (second engagement oil chambers) communicated with the engagement oil chamber oil passage 402x, respectively, on the inner peripheral surface of the inner cylinder portion 403. Recesses 403a and a plurality of (four in this embodiment) C4 engagement oil chamber recesses (first engagement oil chamber recesses) 403b communicating with the C4 engagement oil chamber oil holes 403x, respectively. Is formed. That is, in this embodiment, the number of C4 engagement oil chamber recesses 403b is the same as the number of C4 engagement oil chamber oil holes 403x, and is larger than the number of C3 engagement oil chamber recesses 403a. In addition, a plurality (four in this embodiment) of C3 cancel chamber recesses (second cancel chamber recesses) 403c communicating with the cancel chamber oil passage 402y are respectively provided on the inner peripheral surface of the inner cylinder portion 403. A plurality (four in this embodiment) of C4 cancel chamber recesses (first cancel chamber recesses) 403d communicating with the C4 cancel chamber oil holes 403y are formed.

  As can be seen from FIGS. 4 and 5, the plurality of C3 engagement oil chamber recesses 403a overlap with the annular wall 402 (inner wall 402b) of the clutch drum 400 when viewed from the radial direction of the clutch drums 300 and 400, It is formed on the inner peripheral surface of the inner cylinder portion 403 so as to be arranged at intervals (equal intervals) in the circumferential direction. The plurality of C4 engagement oil chamber recesses 403b are separated from the annular wall portion 402 (inner wall portion 402b) of the clutch drum 400 and spaced apart in the circumferential direction from the C3 engagement oil chamber recesses 403a ( It is formed on the inner peripheral surface of the inner cylinder portion 403 so as to be lined up at equal intervals. That is, the C4 engagement oil chamber recess 403 b is formed closer to the free end portion of the inner cylinder portion 403 than the annular wall portion 402. Furthermore, like the C4 engagement oil chamber oil holes 403x, the plurality of C4 engagement oil chamber recesses 403b are formed so as to be close to each other in pairs.

  Further, as shown in FIG. 5, each C3 cancel chamber recess 403c is closer to the annular wall 402 than the C4 cancel chamber recess 403d, and two C4 engagement oil chamber recesses 403b paired with each other. And the C4 cancellation chamber recess 403d in the circumferential direction. Furthermore, each C3 engagement oil chamber recess 403a is closer to the annular wall 402 than the two C4 engagement oil chamber recesses 403b that are paired with each other, and the two C4 engagement oil chamber recesses 403a. It is formed in the inner cylinder part 403 so that one side of 403b and the inner cylinder part 403 may be arranged in the axial direction. In this embodiment, as shown in FIG. 5, each C3 engagement oil chamber recess 403a includes a C3 in the circumferential direction of the inner cylinder portion 403 of the two C4 engagement oil chamber recesses 403b that are paired with each other. It is arranged in the axial direction with one side away from the cancellation chamber recess 403c. The central axis of the one C4 engagement oil chamber recess 403b and the central axis of the C3 engagement oil chamber recess 403a aligned therewith extend coaxially. In addition, as shown in FIG. 4, each C3 engagement oil chamber recess 403a is formed deeper than each C4 engagement oil chamber recess 403b.

  On the other hand, on the outer peripheral surface of the cylindrical portion 220 of the front support 22f that rotatably supports the clutch drum 400, as shown in FIGS. 3 and 5, C3 engagement hydraulic pressure supply, which is an annular recess (groove), is provided. An oil passage (second engagement hydraulic supply oil passage) 223, a C4 engagement hydraulic supply oil passage (first combined hydraulic supply oil passage) 224, and a cancel chamber supply oil passage (cancellation oil supply oil passage) 234 are formed. Yes. The base end of the cylindrical portion 220 is positioned so that the C3 engagement hydraulic pressure supply oil passage 223 is positioned inside the C3 engagement oil chamber recess 403a of the inner cylindrical portion 403 supported by the cylindrical portion 220 of the front support 22f. It is formed on the side (the right end side in FIG. 3). Further, the C3 engagement hydraulic pressure supply oil passage 223 corresponds to one of the plurality of radial oil passages 221 formed in the front support 22f, one of the plurality corresponding to the plurality of axial oil passages 222, and a plurality of oil holes. 225 is connected to the hydraulic control device 60 via one of the corresponding ones.

  The free end of the cylindrical portion 220 is positioned so that the C4 engagement hydraulic pressure oil passage 224 is positioned inside the C4 engagement oil chamber recess 403b of the inner cylindrical portion 403 supported by the cylindrical portion 220 of the front support 22f. It is formed on the side (left end side in FIG. 3). Further, the C4 engagement hydraulic pressure supply oil passage 224 corresponds to any one of the plurality of radial oil passages 221 formed in the front support 22f, one corresponding to the plurality of axial oil passages 222, and a plurality of oil holes. 225 is connected to the hydraulic control device 60 via one of the corresponding ones. The cancellation chamber supply oil passage 234 is located between the C3 engagement hydraulic supply oil passage 223 and the C4 engagement hydraulic supply oil passage 224 in the axial direction of the cylindrical portion 220 of the front support 22f. 220. Further, the cancel chamber supply oil passage 234 corresponds to one of the plurality of radial oil passages 221 formed in the front support 22f, one of the plurality of axial oil passages 222, and the plurality of oil holes 225. Is connected to the hydraulic control device 60 (drain oil passage) through any one of the above.

  Furthermore, as shown in FIG. 5, the sleeve 500 fitted into the inner cylinder portion 403 of the clutch drum 400 has a plurality (four in this embodiment) of C3 engagement oil supply holes (second oil holes). 503, a plurality (eight in this embodiment) C4 engagement oil supply holes (first oil holes) 504, and a plurality (four in this embodiment) C3 cancel oil supply holes (fourth oil holes). 534c and a plurality (four in this embodiment) of C4 cancel oil supply holes (third oil holes) 534d.

  The C3 engagement oil supply hole 503 is formed in the sleeve 500 so that the inner C3 engagement oil supply oil passage 223 communicates with the outer C3 engagement oil chamber recess 403a. The C4 engagement oil supply hole 504 is formed in the sleeve 500 so that the inner C4 engagement oil supply oil passage 224 communicates with the outer C4 engagement oil chamber recess 403b. The C3 cancel oil supply hole 534c is formed in the sleeve 500 so as to communicate the inner cancel chamber supply oil passage 234 and the outer C3 cancel chamber recess 403c. The C4 cancel oil supply hole 534d is formed in the sleeve 500 so as to communicate the inner cancel chamber supply oil passage 234 with the outer C4 cancel chamber recess 403d. In the present embodiment, each of the plurality of C3 cancel oil supply holes 534c and C4 cancel oil supply holes 534d includes a C3 engagement oil supply hole 503 and a C4 engagement oil supply hole in the axial direction of the sleeve 500, as shown in FIG. The sleeve 500 is arranged on the sleeve 500 so as to be aligned in a row in the circumferential direction.

  As shown in FIG. 3, a C3 engagement hydraulic pressure supply oil passage 223, a C4 engagement hydraulic supply oil passage 224, and a cancel chamber are provided between the cylindrical portion 220 and the sleeve 500 in the axial direction of the cylindrical portion 220. A plurality (four in this embodiment) of seal members (seal rings) 95 are disposed so as to be located on both sides of the supply oil passage 234. In other words, the plurality of seal members 95 are disposed so as to be positioned on both sides of the C3 engagement oil supply hole 503 and on both sides of the C4 engagement oil supply hole 504 in the axial direction of the cylindrical portion 220. Each seal member 95 is in sliding contact with the inner peripheral surface of the sleeve 500 and regulates leakage of hydraulic oil from the C3 engagement hydraulic supply oil passage 223, the C4 engagement hydraulic supply oil passage 224, and the cancel chamber supply oil passage 234. .

  Thereby, hydraulic oil (engagement hydraulic pressure) for engaging the clutch C3 is supplied from the hydraulic control device 60 to the oil passages 221 and 222 of the front support 22f and the C3 engagement hydraulic pressure supply oil passage 223 of the cylindrical portion 220. , The C3 engagement oil supply hole 503 of the sleeve 500, the C3 engagement oil chamber recess 403 a of the inner cylinder portion 403, the engagement oil chamber oil passage 402 x of the inner wall portion 402 b, and the inner cylinder portion 303 of the clutch drum 300. The oil is supplied to the engagement oil chamber 306 of the clutch C3 through the oil hole 303x. Further, hydraulic oil (engagement hydraulic pressure) for engaging the clutch C4 is supplied from the hydraulic control device 60, such as the oil paths 221 and 222 of the front support 22f, the C4 engagement hydraulic pressure supply oil path 224 of the cylindrical portion 220, The oil is supplied to the engagement oil chamber 406 of the clutch C4 via the C4 engagement oil supply hole 504 of the sleeve 500, the C4 engagement oil chamber recess 403b of the inner cylinder 403, and the C4 engagement oil chamber oil hole 403x.

  Further, in the centrifugal hydraulic pressure cancellation chamber 308 of the clutch C3, the oil passages 221 and 222 of the front support 22f, the cancellation chamber supply oil passage 234 of the cylindrical portion 220, the C3 cancellation oil supply hole 534c of the sleeve 500, the inner cylinder portion, etc. Hydraulic oil (cancellation oil, that is, drain oil) is supplied from the hydraulic control device 60 via the C3 cancel chamber recess 403c 403, the cancel chamber oil passage 402y of the inner wall 402b, and the recess 402r. The centrifugal hydraulic pressure cancellation chamber 408 of the clutch C4 includes oil passages 221 and 222 of the front support 22f, a cancellation chamber supply oil passage 234 of the cylindrical portion 220, a C4 cancellation oil supply hole 534d of the sleeve 500, an inner cylinder portion, and the like. Hydraulic oil (cancellation oil, that is, drain oil) is supplied from the hydraulic control device 60 via the C4 cancellation chamber recess 403d and the C4 cancellation chamber oil hole 403y.

  In the automatic transmission 25 configured as described above, the C3 engagement oil chamber recess 403a corresponding to the outer clutch C3 is formed so as to be close to the annular wall 402 (inner wall 402b) of the clutch drum 400. Therefore, the C3 engagement oil chamber recess 403a can be deepened. Accordingly, the width of the C3 engagement oil chamber recess 403a in the circumferential direction of the inner cylinder 403 (clutch drum 400) can be reduced without increasing the oil flow resistance in the C3 engagement oil chamber recess 403a. Become. Further, by increasing the number of C4 engagement oil chamber recesses 403b corresponding to the inner clutch C4 as compared with the number of C3 engagement oil chamber recesses 403a, the circumferential direction of each C4 engagement oil chamber recess 403b is increased. The width can be reduced.

  This suppresses the sleeve 500 from entering the C3 engagement oil chamber recess 403a and the C4 engagement oil chamber recess 403b when the sleeve is tightly fitted to the inner cylinder 403 of the clutch drum 400 by press fitting, The inner peripheral surface of the sleeve 500 that is fitted (press-fitted) into the inner cylinder portion 403 and is in sliding contact with the plurality of seal members 95 can be maintained in a perfect circle. Therefore, in the automatic transmission 25, it is not necessary to perform a cutting process for making the inner peripheral surface into a perfect circle shape with respect to the sleeve 500 fitted to the inner cylindrical portion 403. As a result, it is possible to suppress the deformation of the sleeve 500 fitted to the inner cylinder portion 403 of the clutch drum 400 that constitutes one drum member together with the clutch drum 300, and to reduce the manufacturing cost of the automatic transmission 25. . Further, the inner peripheral surface of the sleeve 500 is maintained in a perfect circle, so that the hydraulic oil leaks from the C3 engagement hydraulic supply oil passage 223, the C4 engagement hydraulic supply oil passage 224, and the cancel chamber supply oil passage 234. Can be regulated very well.

  Further, in the automatic transmission 25, a plurality of C4 engagement oil chamber recesses 403b are arranged at intervals in the circumferential direction of the inner cylinder part 403 and are closely adjacent to each other to form a pair. It is arranged. The C3 engagement oil chamber recess 403a is formed in the inner cylinder 403 so as to be aligned with one of the two C4 engagement oil chamber recesses 403b paired with each other in the axial direction of the inner cylinder 403. . This makes it possible to continuously form one of the two C4 engagement oil chamber recesses 403b and the C3 engagement oil chamber recess 403a that are paired with each other with the same tool. It is possible to suppress the increase in

  Further, in the automatic transmission 25, the C3 cancel chamber recess 403c is closer to the annular wall portion 402 (inner wall portion 402b) of the clutch drum 400 than the C4 cancel chamber recess 403d, and is paired with each other. It is formed between the C4 engagement oil chamber recess 403b and the C4 cancel chamber recess 403d in the circumferential direction. Further, the C3 engagement oil chamber recess 403a is aligned in the axial direction with one of the two C4 engagement oil chamber recesses 403b paired with each other and spaced apart from the C3 cancellation chamber recess 403c in the circumferential direction. It is formed in the inner cylinder part 403. As a result, the sealing performance between the C3 engagement oil chamber recess 403a and the C3 cancellation chamber recess 403c corresponding to the clutch C3 is ensured, and the hydraulic oil is more and less transferred between the two. It becomes possible to suppress.

  The piston 405 extends radially outward from the inner peripheral surface of the extension portion 405c and on the opposite side of the extension portion 405c, and slides on the seal member 91 mounted on the outer periphery of the cancel plate 407 of the clutch C4. It has a concave cylindrical surface 405d in contact therewith. Thereby, as shown in FIG. 4, the chamber diameter (outer diameter) of the centrifugal hydraulic pressure cancel chamber 408 of the clutch C <b> 4 can be made larger than the chamber diameter (outer diameter) of the engagement oil chamber 406. Accordingly, it is possible to satisfactorily ensure the centrifugal oil pressure canceling performance in the centrifugal oil pressure canceling chamber 408 and reduce the rigidity (spring constant) of the return spring 409. As a result, the hydraulic pressure (engagement hydraulic pressure of the clutch C4) to be supplied to the engagement oil chamber 406 when the clutch C4 is engaged can be reduced to further improve the fuel consumption of the vehicle on which the automatic transmission 25 is mounted. it can.

  As described above, in the automatic transmission 25, it is possible to ensure a sufficiently high canceling performance of the centrifugal oil pressure in the centrifugal oil pressure canceling chamber 408 of the clutch C4. Therefore, in the clutch C4, as shown in FIG. 4, at least one oil hole 407h is formed in the inner peripheral portion of the cancel plate 407, and the zero base point B0 of the centrifugal oil pressure in the centrifugal oil pressure cancellation chamber 408 is set to the maximum of the oil hole 407h. The outer peripheral point can be shifted radially outward. Thereby, a part of the hydraulic oil (cancellation oil) that has flowed into the centrifugal hydraulic pressure cancellation chamber 408 from the oil hole 407h of the cancel plate 407 flows out, and the meshing portion between the sun gear 31 and the pinion gear 33a of the first planetary gear mechanism 30, It is possible to provide lubrication for the meshing portion between the pinion gear 33b and the pinion gear 33a, the meshing portion between the pinion gear 33b and the ring gear 32, and the like.

  Further, in the automatic transmission 25, the C3 cancel that communicates with the cancel chamber oil passage 402y and the cancel chamber supply oil passage 234 on the inner peripheral surface of the inner cylinder portion 403 of the clutch drum 400 that constitutes a drum member together with the clutch drum 300. A chamber recess 403c and a C4 cancel chamber recess 403d communicating with the C4 cancel chamber oil hole 403y and the cancel chamber supply oil passage 234 are formed at intervals in the circumferential direction. Thus, the zero base point B0 of the centrifugal hydraulic pressure in the centrifugal hydraulic pressure cancellation chamber 408 of the clutch C4 can be moved radially outward as described above without changing the zero base point of the centrifugal hydraulic pressure in the centrifugal hydraulic pressure cancellation chamber 308 of the clutch C3. it can. Therefore, in the automatic transmission 25, it is possible to satisfactorily ensure the centrifugal oil pressure cancellation performance in both the centrifugal oil pressure cancel chambers 308 and 408.

  In other words, the C3 cancel chamber recess 403c for supplying hydraulic oil to the cancel chamber oil passage 402y and the C4 for supplying hydraulic oil to the C4 cancel chamber oil hole 403y are provided on the inner peripheral surface of the inner cylinder portion 403 of the clutch drum 400. By providing the cancel chamber recess 403d independently, the centrifugal oil pressure cancel chambers 308 and 408 can independently set the zero base point of the centrifugal oil pressure. As a result, the automatic transmission 25 can improve the degree of freedom of adjustment between the cancellation performance of the inner clutch C4 in the centrifugal hydraulic pressure cancellation chamber 408 and the cancellation performance of the outer clutch C3 in the centrifugal hydraulic pressure cancellation chamber 308.

  In addition, in the automatic transmission 25, for the C3 cancel oil supply hole 534c and the C4 cancel oil supply hole 534d of the sleeve 500, a common (single) cancel chamber is formed in the cylindrical portion 220 of the front support 22f. Hydraulic oil (cancellation oil) can be supplied from the supply oil passage 234. Accordingly, it is possible to suppress an increase in the axial length of the inner cylinder portion 403 of the clutch drum 400, that is, the clutches C3 and C4. Further, in the above-described embodiment, the plurality of C3 cancel oil supply holes 534c and C4 cancel oil supply holes 534d are respectively formed as C3 engagement oil supply holes 503 and C4 engagement oil in the axial direction of the sleeve 500 as shown in FIG. The sleeve 500 is arranged in the circumferential direction so as to be aligned with the supply hole 504. Thereby, the axial length of clutch C3, C4 can be shortened more. However, the C3 cancel oil supply hole 534c and the C4 cancel oil supply hole 534d may be disposed slightly shifted in the axial direction.

  As described above, the transmission according to the present invention includes the first clutch having the first piston and the first engagement oil chamber, the second piston and the second engagement oil chamber, and around the first clutch. In the transmission including the second clutch arranged, the inner cylinder portion that supports the first piston, the first engagement oil chamber together with the first piston, and the first piston together with the second piston. A drum member having an annular wall portion extending from the inner cylinder portion so as to define the second engagement oil chamber radially outward from the first engagement oil chamber; and the inner cylinder of the drum member A plurality of engagement oil chamber oil holes formed in the inner cylinder portion so as to communicate with the first engagement oil chamber, respectively. The annular wall portions so as to communicate with the second engagement oil chambers, respectively. A plurality of first engagement oil chamber recesses formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the plurality of engagement oil chamber oil passages formed, and the engagement oil chamber oil holes, respectively. And a plurality of second engagement oil chamber recesses formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the engagement oil chamber oil passage, respectively, and the sleeve includes the first sleeve A first oil hole for communicating between the engagement oil chamber recess and a first engagement hydraulic pressure supply oil passage provided on the inner side of the sleeve; and a second oil hole provided on the inner side of the second engagement oil chamber recess and the sleeve. A second oil hole communicating with the two-engagement hydraulic pressure supply oil passage, wherein the second engagement oil chamber recess is closer to the annular wall than the first engagement oil chamber recess. The first engagement oil chamber recesses are formed deeper than the first engagement oil chamber recesses, and the number of the first engagement oil chamber recesses is larger than the number of the second engagement oil chamber recesses.

  In this transmission, a plurality of oil holes for engagement oil chambers are formed in the inner cylinder portion of the drum member shared by the first and second clutches so as to communicate with the first engagement oil chamber of the first clutch. Is done. A plurality of oil passages for engagement oil chambers are formed in the annular wall portion of the drum member so as to communicate with the second engagement oil chamber, respectively. Further, on the inner peripheral surface of the inner cylinder portion, a plurality of first engagement oil chamber recesses respectively communicating with the engagement oil chamber oil holes, and a plurality of second engagement holes respectively communicating with the engagement oil chamber oil passages. An engagement oil chamber recess is formed. Further, the sleeve fitted to the inner cylinder portion of the drum member has a first oil hole for communicating the first engagement oil chamber recess and the first engagement hydraulic pressure oil passage provided inside the sleeve; A second oil hole that communicates between the second engagement oil chamber recess and a second engagement hydraulic pressure supply oil passage provided inside the sleeve; The second engagement oil chamber recess is formed deeper than the first engagement oil chamber recess so as to be closer to the annular wall than the first engagement oil chamber recess. The number of chamber recesses is greater than the number of second engagement oil chamber recesses.

  Thus, the 2nd engagement oil chamber recessed part corresponding to an outer 2nd clutch can be made deep by making the annular wall part of a drum member adjoin. Therefore, it is possible to reduce the width of the second engagement oil chamber recess in the circumferential direction of the inner cylinder portion (drum member) without increasing the oil passage resistance in the second engagement oil chamber recess. Further, by increasing the number of first engagement oil chamber recesses corresponding to the inner first clutch than the number of second engagement oil chamber recesses, the circumferential direction of each first engagement oil chamber recess The width at can be reduced. As a result, when the sleeve is tightly fitted to the inner cylinder portion of the drum member, the sleeve is prevented from entering the concave portions of the first and second engagement oil chambers, and the inner sleeve of the sleeve fitted to the inner cylinder portion is prevented. The peripheral surface can be maintained in a perfect circle. Therefore, in this transmission, it is not necessary to perform a cutting process for making the inner peripheral surface into a perfect circle shape with respect to the sleeve fitted in the inner cylinder portion. As a result, deformation of the sleeve fitted to the inner cylinder portion of the drum member shared by the first and second clutches can be suppressed, and the manufacturing cost of the transmission can be reduced.

  The first engagement oil chamber recess may be formed closer to the free end of the inner cylinder than the annular wall, and the second engagement oil chamber recess may be formed on the drum member. You may form so that it may overlap with the said annular wall part seeing from radial direction.

  Further, the plurality of first engaging oil chamber recesses may be arranged in the inner cylinder part so as to be arranged in pairs in the circumferential direction of the inner cylinder part and in close proximity to each other. Preferably, the second engagement oil chamber recess is formed in the inner cylinder portion so as to be aligned with one of the two first engagement oil chamber recesses paired with each other in the axial direction of the inner cylinder portion. May be. This makes it possible to continuously form one of the two first engagement oil chamber recesses and the second engagement oil chamber recess that are paired with each other, thereby suppressing an increase in processing cost. It becomes possible to do.

  The transmission is canceled by the inner cylinder portion so as to define a first centrifugal oil pressure cancel chamber for canceling the centrifugal oil pressure generated in the first engagement oil chamber together with the first piston. A chamber defining member may be further provided, and the drum member has a second centrifugal oil pressure canceling chamber for canceling the centrifugal oil pressure generated in the second engagement oil chamber having a diameter larger than that of the first centrifugal oil pressure canceling chamber. A cancel chamber defining portion defined together with the second piston on the outer side in the direction, a plurality of cancel chamber oil holes formed in the inner cylinder portion so as to communicate with the first centrifugal hydraulic pressure cancel chamber, respectively, A plurality of cancellation chamber oil passages formed in the annular wall portion so as to communicate with the second centrifugal hydraulic pressure cancellation chamber, and the inner portion so as to communicate with the cancellation chamber oil hole, respectively. A plurality of first cancel chamber recesses formed on the inner peripheral surface of the part, and a plurality of twenty-second cancel chambers formed on the inner peripheral surface of the inner cylinder part so as to communicate with the cancel chamber oil passage, respectively. The sleeve may include a third oil hole that communicates the first cancel chamber recess and a cancel oil supply oil passage provided inside the sleeve, and the second cancel chamber recess. And a fourth oil hole for communicating the cancel oil supply oil passage, the second cancel chamber recess is closer to the annular wall than the first cancel chamber recess, and The two engagement oil chamber recesses and the first cancellation chamber recess that form a pair may be formed in the circumferential direction, and the second engagement oil chamber recesses may be paired with each other. Of the two recesses for the first engagement oil chamber forming Chi, may be formed in the inner cylinder part so as to be aligned in the axial direction and one spaced from the second cancel chamber recess in the circumferential direction. As a result, the sealing performance between the second engagement oil chamber recess and the second cancel chamber recess corresponding to the second clutch is ensured, and the hydraulic oil is more favorable to flow back and forth between the two. Can be suppressed. In addition, in this transmission, since the cancel oil can be supplied from the common cancel oil supply oil passage to the third and fourth oil holes of the sleeve, the inner cylinder portion of the clutch drum, that is, the first and second oil holes can be supplied. It is possible to suppress an increase in the shaft length of the two clutches.

  The transmission may further include a case that accommodates the first and second clutches, and a cylindrical portion that is inserted into the sleeve may be integrated with the case. The first engagement hydraulic pressure supply oil path, the second engagement hydraulic pressure supply oil path, and the cancel oil supply oil path may be formed in the cylindrical portion, and the third oil hole and the fourth oil hole are The sleeve may be provided so as to be aligned in the circumferential direction of the sleeve between the first oil hole and the second oil hole in the axial direction of the sleeve, and between the cylindrical portion and the sleeve, A plurality of seal members may be arranged so as to be located on both sides of the first oil hole and on both sides of the second oil hole in the axial direction of the cylindrical portion. That is, also in this transmission, since the inner peripheral surface of the sleeve fitted to the inner cylinder portion can be maintained in a perfect circle shape, the gap between the cylindrical portion and the sleeve is sealed by a plurality of seal members. Thus, it is possible to very well regulate the leakage of oil from the first engagement hydraulic supply oil passage, the second engagement hydraulic supply oil passage, and the cancel oil supply oil passage. In addition, by providing the third and fourth oil holes so as to be aligned in the circumferential direction of the sleeve between the first oil hole and the second oil hole in the axial direction of the sleeve, the shafts of the first and second clutches The length can be further shortened.

  Further, the drum member includes a first clutch drum that defines the first engagement oil chamber together with the first piston, and the first engagement oil chamber joined to the first clutch drum and the second piston. A second clutch drum that defines the second engagement oil chamber on a radially outer side than the inner cylinder portion and the outer side of the inner cylinder portion in the axial direction. A first outer tube portion that is extended and fitted with an outer peripheral portion of the first friction engagement plate; and the inner tube portion extends radially between the inner tube portion and the first outer tube portion. A first annular wall portion formed integrally with the cylindrical portion and the first outer cylindrical portion, and the second clutch drum includes a second inner cylindrical portion that supports the second piston, The second inner cylinder portion extends in the axial direction and is fitted with the outer peripheral portion of the second friction engagement plate. A first molded integrally with the second inner cylindrical portion and the second outer cylindrical portion so as to extend in the radial direction between the outer cylindrical portion, the second inner cylindrical portion and the second outer cylindrical portion. You may have two annular walls.

  And this invention is not limited to the said embodiment at all, and it cannot be overemphasized that a various change can be made within the range of the extension of this invention. Furthermore, the mode for carrying out the invention described above is merely a specific embodiment of the invention described in the column for solving the problem, and is described in the column for means for solving the problem. It is not intended to limit the elements of the invention.

  The present invention can be used in the manufacturing industry of a transmission and a power transmission device including the transmission.

  3, 4 Clutch hub, 20 Power transmission device, 22 Transmission case, 22f Front support, 23 Starting device, 23c Lock-up clutch, 23d Damper mechanism, 23o One-way clutch, 23p Pump impeller, 23s Stator, 23t Turbine runner, 24 Oil pump , 25 automatic transmission, 26 input shaft, 30 first planetary gear mechanism, 31 sun gear, 32 ring gear, 33a, 33b pinion gear, 34 planetary carrier, 35 second planetary gear mechanism, 36a first sun gear, 36b second sun gear, 37 Ring gear, 38a Short pinion gear, 38b Long pinion gear, 39 Planetary carrier, 40 Gear mechanism, 41 Counter drive gear, 42 Counter shaft, 43 Counter driven , 44 drive pinion gear, 45 differential ring gear, 50 differential gear, 51 drive shaft, 60 hydraulic control device, 90, 91, 95 seal member, 92 bush, 220 cylindrical portion, 221 radial oil passage, 222 axial oil passage 223 C3 engagement hydraulic supply oil passage, 224 C4 engagement hydraulic supply oil passage, 225 oil hole, 230 stator shaft, 234 cancellation chamber supply oil passage, 300 clutch drum, 301 outer cylinder, 301 s spline, 302 annular wall Part, 303 inner cylinder part, 303i inner peripheral surface, 303x oil hole, 304f friction plate, 304s separator plate, 305 piston, 306 engagement oil chamber, 308 centrifugal oil pressure cancellation chamber, 309 return spring, 400 clutch drum, 401 outer cylinder Part 401 Spline, 402 annular wall portion, 402a outer wall portion, 402b inner wall portion, 402c annular recess, 402n reduced diameter portion, 402o outer peripheral surface, 402r recess, 402x oil passage for engagement oil chamber, 402y oil passage for cancellation chamber, 403 Inner cylinder, 403a C3 engagement oil chamber recess, 403b C4 engagement oil chamber recess, 403c C3 cancellation chamber recess, 403d C4 cancellation chamber recess, 403x C4 engagement oil chamber oil hole, 403y C4 cancellation chamber Oil hole, 404f Friction plate, 404s Separator plate, 405 Piston, 405a Pressure receiving part, 405b Pressing part, 405c Extension part, 405d Concave cylinder surface, 406 Engaging oil chamber, 407 Cancel plate, 407h Oil hole, 408 Centrifugal hydraulic pressure Cancellation chamber, 409 return spring, 410 carriage Cancellation chamber defining part, 420 intermediate cylindrical part, 421 outer peripheral surface, 500 sleeve, 503 C3 engagement oil supply hole, 504 C4 engagement oil supply hole, 534c C3 cancel oil supply hole, 534d C4 cancel oil supply hole, B1 , B2 brake, C1, C2, C3, C4 clutch, F1 one-way clutch.

Claims (8)

In a transmission including a first clutch having a first piston and a first engagement oil chamber, and a second clutch having a second piston and a second engagement oil chamber and disposed around the first clutch,
An inner cylinder portion that supports the first piston, the first engagement oil chamber together with the first piston, and the second piston and the first engagement oil chamber radially outward from the first engagement oil chamber. A drum member having an annular wall portion extending from the inner cylinder portion so as to define two engagement oil chambers;
A cylindrical sleeve fitted to the inner cylinder portion of the drum member,
The drum member communicates with the plurality of engagement oil chamber oil holes formed in the inner cylinder portion so as to communicate with the first engagement oil chamber, respectively, and the second engagement oil chamber. A plurality of engagement oil chamber oil passages formed in the annular wall portion and a plurality of first engagement members formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the engagement oil chamber oil holes, respectively. An oil chamber recess, and a plurality of second engagement oil chamber recesses formed on the inner peripheral surface of the inner cylinder so as to communicate with the oil passage for the engagement oil chamber,
The sleeve includes a first oil hole that allows communication between the first engagement oil chamber recess and a first engagement hydraulic pressure oil passage provided inside the sleeve; the second engagement oil chamber recess; A second oil hole that communicates with a second engagement hydraulic pressure oil passage provided inside the sleeve;
The recess for the second engagement oil chamber is disposed closer to the annular wall portion than the recess for the first engagement oil chamber , and the width in the circumferential direction of the inner cylinder portion is reduced. is formed deeper than the first engagement oil chamber recess, wherein the number of first recesses for engagement oil chamber, than the number of the circumferential the so that the width in the direction becomes narrower second recess for engagement oil chamber transmission apparatus characterized by being Many established. The transmission according to claim 1, wherein
The concave portion for the first engagement oil chamber is formed on the free end side of the inner cylinder portion with respect to the annular wall portion,
The second engagement oil chamber recess is formed so as to overlap the annular wall portion when viewed from the radial direction of the drum member. The transmission according to claim 1 or 2,
The plurality of first engagement oil chamber recesses are arranged in the inner cylinder part so as to be arranged in pairs in the circumferential direction of the inner cylinder part and in close proximity to each other.
The recess for the second engagement oil chamber is formed in the inner cylinder portion so as to be aligned with one of the two recesses for the first engagement oil chamber paired with each other in the axial direction of the inner cylinder portion. A transmission characterized by. The transmission according to claim 3,
A cancel chamber defining member supported by the inner cylinder portion so as to define a first centrifugal oil pressure cancel chamber for canceling the centrifugal oil pressure generated in the first engagement oil chamber together with the first piston; ,
The drum member defines a second centrifugal hydraulic pressure cancel chamber for canceling centrifugal hydraulic pressure generated in the second engagement oil chamber, together with the second piston, radially outward from the first centrifugal hydraulic pressure cancel chamber. A cancel chamber defining portion, a plurality of cancel chamber oil holes formed in the inner cylinder portion so as to communicate with the first centrifugal hydraulic pressure cancel chamber, and a second centrifugal hydraulic pressure cancel chamber, respectively. A plurality of cancellation chamber oil passages formed in the annular wall, and a plurality of first cancellation chamber recesses formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the cancellation chamber oil holes, respectively. And a plurality of second cancellation chamber recesses formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the cancellation chamber oil passage,
The sleeve includes a third oil hole for communicating the first cancel chamber recess and a cancel oil supply oil passage provided inside the sleeve, the second cancel chamber recess and the cancel oil supply oil passage. Having a fourth oil hole for communication;
The concave portion for the second cancel chamber is closer to the annular wall portion than the concave portion for the first cancel chamber, and the two concave portions for the first engagement oil chamber and the first cancel chamber are paired with each other. The second engagement oil chamber recess is formed between the second engagement oil chamber recess and the second cancel oil chamber recess in the circumferential direction. The transmission according to claim 1, wherein the transmission is formed in the inner cylinder portion so as to be aligned with the one spaced apart from the chamber recess. The transmission according to claim 4,
A case for accommodating the first and second clutches;
The case is integrated with a cylindrical portion inserted into the sleeve,
The first engagement hydraulic pressure supply oil path, the second engagement hydraulic pressure supply oil path, and the cancel oil supply oil path are formed in the cylindrical portion,
The third oil hole and the fourth oil hole are provided so as to be arranged in the circumferential direction of the sleeve between the first oil hole and the second oil hole in the axial direction of the sleeve,
Between the cylindrical part and the sleeve, a plurality of seal members are disposed so as to be positioned on both sides of the first oil hole and on both sides of the second oil hole in the axial direction of the cylindrical part. A transmission characterized by. The transmission according to any one of claims 1 to 5,
The drum member includes a first clutch drum that defines the first engagement oil chamber together with the first piston, and is joined to the first clutch drum and together with the second piston than the first engagement oil chamber. A second clutch drum defining the second engagement oil chamber radially outward,
The first clutch drum includes the inner cylinder part, a first outer cylinder part that extends in an axial direction outside the inner cylinder part and is fitted with an outer peripheral part of a first friction engagement plate; A first annular wall portion formed integrally with the inner cylindrical portion and the first outer cylindrical portion so as to extend in a radial direction between the cylindrical portion and the first outer cylindrical portion;
The second clutch drum extends in the axial direction on the outer side of the second inner cylinder part and the second inner cylinder part that supports the second piston, and the outer peripheral part of the second friction engagement plate is fitted to the second clutch drum. The second outer cylinder part and the second inner cylinder part and the second outer cylinder part are integrally molded so as to extend in the radial direction between the second inner cylinder part and the second outer cylinder part. And a second annular wall portion. In a transmission including a first clutch having a first piston and a first engagement oil chamber, and a second clutch having a second piston and a second engagement oil chamber and disposed around the first clutch,
An inner cylinder portion that supports the first piston, the first engagement oil chamber together with the first piston, and the second piston and the first engagement oil chamber radially outward from the first engagement oil chamber. A drum member having an annular wall portion extending from the inner cylinder portion so as to define two engagement oil chambers;
A cylindrical sleeve fitted to the inner cylinder portion of the drum member,
The drum member communicates with the plurality of engagement oil chamber oil holes formed in the inner cylinder portion so as to communicate with the first engagement oil chamber, respectively, and the second engagement oil chamber. A plurality of engagement oil chamber oil passages formed in the annular wall portion and a plurality of first engagement members formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the engagement oil chamber oil holes, respectively. An oil chamber recess, and a plurality of second engagement oil chamber recesses formed on the inner peripheral surface of the inner cylinder so as to communicate with the oil passage for the engagement oil chamber,
The sleeve includes a first oil hole that allows communication between the first engagement oil chamber recess and a first engagement hydraulic pressure oil passage provided inside the sleeve; the second engagement oil chamber recess; A second oil hole that communicates with a second engagement hydraulic pressure oil passage provided inside the sleeve;
The recess for the second engagement oil chamber is disposed closer to the annular wall portion than the recess for the first engagement oil chamber, and the width in the circumferential direction of the inner cylinder portion is reduced. The first engagement oil chamber recesses are formed deeper than the first engagement oil chamber recesses, and the number of the first engagement oil chamber recesses is smaller than the number of the second engagement oil chamber recesses so that the width in the circumferential direction is narrower. Many established, transmission apparatus characterized by cutting the inner peripheral surface of the sleeve is not subjected. In a transmission including a first clutch having a first piston and a first engagement oil chamber, and a second clutch having a second piston and a second engagement oil chamber and disposed around the first clutch,
An inner cylinder portion that supports the first piston, the first engagement oil chamber together with the first piston, and the second piston and the first engagement oil chamber radially outward from the first engagement oil chamber. A drum member having an annular wall portion extending from the inner cylinder portion so as to define two engagement oil chambers;
A cylindrical sleeve fitted to the inner cylinder portion of the drum member,
The drum member communicates with the plurality of engagement oil chamber oil holes formed in the inner cylinder portion so as to communicate with the first engagement oil chamber, respectively, and the second engagement oil chamber. A plurality of engagement oil chamber oil passages formed in the annular wall portion and a plurality of first engagement members formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the engagement oil chamber oil holes, respectively. An oil chamber recess, and a plurality of second engagement oil chamber recesses formed on the inner peripheral surface of the inner cylinder so as to communicate with the oil passage for the engagement oil chamber,
The sleeve includes a first oil hole that allows communication between the first engagement oil chamber recess and a first engagement hydraulic pressure oil passage provided inside the sleeve; the second engagement oil chamber recess; A second oil hole that communicates with a second engagement hydraulic pressure oil passage provided inside the sleeve;
The recess for the second engagement oil chamber is disposed closer to the annular wall portion than the recess for the first engagement oil chamber, and the width in the circumferential direction of the inner cylinder portion is reduced. The first engagement oil chamber recesses are formed deeper than the first engagement oil chamber recesses, and the number of the first engagement oil chamber recesses is smaller than the number of the second engagement oil chamber recesses so that the width in the circumferential direction is narrower. Many defined,
The first clutch includes a first centrifugal hydraulic pressure cancellation chamber for canceling centrifugal hydraulic pressure generated in the first engagement oil chamber;
The second clutch includes a second centrifugal hydraulic pressure cancellation chamber for canceling centrifugal hydraulic pressure generated in the second engagement oil chamber,
The drum member has a plurality of cancel chamber oil holes formed in the inner cylinder portion so as to communicate with the first centrifugal hydraulic pressure cancel chamber, and the annular member so as to communicate with the second centrifugal hydraulic pressure cancel chamber, respectively. A plurality of cancellation chamber oil passages formed in the wall, and a plurality of first cancellation chamber recesses formed on the inner peripheral surface of the inner cylinder portion so as to communicate with the cancellation chamber oil holes, respectively. A plurality of second recesses for the cancel chamber formed on the inner peripheral surface of the inner cylinder so as to communicate with the oil passage for the cancel chamber;
The sleeve includes a third oil hole for communicating the first cancel chamber recess and a cancel oil supply oil passage provided inside the sleeve, the second cancel chamber recess and the cancel oil supply oil passage. Having a fourth oil hole for communication;
The plurality of first engagement oil chamber recesses, the plurality of first cancel chamber recesses, and the plurality of second cancel chamber recesses are arranged at intervals in the circumferential direction of the inner cylinder portion. The transmission is arranged in the inner cylinder portion.

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