JP2020169681A - Clutch structure of automatic transmission - Google Patents

Abstract

To suppress backlash in a peripheral direction between hub members of both clutches and a power transmission member as much as possible, and to shorten lengths of the power transmission member, a first clutch and a second clutch as whole in an axial direction as much as possible when constituting both the hub members of the first clutch and the second clutch which are arranged in parallel with each other in the axial direction of an automatic transmission so as to be connected to the power transmission member.SOLUTION: An axial extension member 51 which is spline-fit to an internal peripheral side end part of a power transmission member 45, and extends along the axial direction is arranged, a first hub member 35 of a first clutch (front-side clutch 40) is formed at the power transmission member 45 integrally therewith, and a second hub member 34 of a second clutch (intermediate clutch 30) is formed at the axial extension member 51 integrally therewith, or rotates integrally with a member which is formed at the axial extension member 51 integrally therewith.SELECTED DRAWING: Figure 3

Description

The present invention belongs to the technical field relating to the clutch structure of an automatic transmission.

In general, an automatic transmission mounted on a vehicle includes a plurality of planetary gear sets (planetary gear mechanisms) and a plurality of friction fastening elements (particularly hydraulic friction fastening elements) including a clutch. The plurality of planetary gear sets and the plurality of friction fastening elements are arranged coaxially. Then, in the automatic transmission, the plurality of friction fastening elements are selectively fastened by hydraulic control or the like to switch the power transmission path via the planetary gear set, and the plurality of forward gears and reverse gears (reverse gears). Usually, 1st speed) is achieved.

The clutch has a clutch drum member and a hub member provided on the inner peripheral side of the clutch drum member via a plurality of friction plates arranged in the axial direction of the automatic transmission. The clutch drum member and the hub member are connected to other rotating members (input shaft, output shaft, rotating element of the planetary gear set, power transmission member, clutch drum member or hub member of another clutch), respectively. The clutch drum member and the hub member may be connected to another rotating member by spline fitting (see, for example, Patent Document 1).

In Patent Document 1, the automatic transmission is a first clutch (referred to as a third clutch CL3 in Patent Document 1) and a second clutch (in Patent Document 1) arranged side by side in the axial direction of the automatic transmission. , The second clutch (called CL2), and the hub members of the first clutch and the second clutch are both provided with power provided on the opposite side of the first clutch from the second clutch in the axial direction. It is connected to a transmission member (referred to as a clutch 11 in Patent Document 1). Specifically, an axial extension member extending in the axial direction of the automatic transmission and integrally coupled with the hub member of the second clutch is provided on the inner peripheral side of the hub members of the first clutch and the second clutch. , The axial extension member and the power transmission member are spline-fitted, and the axial extension member and the hub member of the first clutch are spline-fitted.

JP-A-2018-115741

In Patent Document 1, the axial extension member and the power transmission member are spline-fitted, and the axial extension member and the hub member of the first clutch are spline-fitted, so that the power transmission member and the first Since two spline fittings are interposed between the hub member of the clutch, there is a problem that the play in the circumferential direction between the two splines is considerably increased. Further, in Patent Document 1, the hub member of the first clutch passes between the engagement hydraulic chamber of the first clutch and the engagement hydraulic chamber of the second clutch, and extends inward to the axial extension member. Therefore, the lengths of the power transmission member, the first clutch, and the second clutch as a whole in the axial direction become long.

The present invention has been made in view of these points, and an object of the present invention is to use a power transmission member for both the hub members of the first clutch and the second clutch arranged side by side in the axial direction of the automatic transmission. In the case of being configured to be connected to the above, the play in the circumferential direction between the hub member and the power transmission member of the first clutch and between the hub member and the power transmission member of the second clutch should be minimized. The purpose is to shorten the axial length of the entire power transmission member, the first clutch, and the second clutch as much as possible.

In order to achieve the above object, in the present invention, the first clutch is intended for a clutch structure of an automatic transmission including a first clutch and a second clutch arranged side by side in the axial direction of the automatic transmission. The second clutch has a first clutch drum member and a first hub member provided on the inner peripheral side of the first clutch drum member via a plurality of friction plates arranged in the axial direction. A second clutch drum member provided on the inner peripheral side of the first clutch drum member and a second clutch drum member provided on the inner peripheral side of the second clutch drum member via a plurality of friction plates arranged in the axial direction. A power transmission member having a hub member and provided on the side opposite to the second clutch of the first clutch in the axial direction and a power transmission member provided on the outer peripheral side of the first clutch drum member. Further includes a power transmission drum member connected to the outer peripheral side end portion of the above, and an axial extension member spline-fitted with the inner peripheral side end portion of the power transmission member and extending along the axial direction. The first hub member is integrally formed with the power transmission member, and the second hub member is integrally formed with the axial extension member or integrally with the axial extension member. The configuration is such that it is fixed so that it rotates integrally.

With the above configuration, the first hub member is integrally formed with the power transmission member, and the second hub member is integrally formed with the axial extension member spline-fitted with the first hub member, or the shaft. Since it is fixed to the member integrally formed with the directional extension member so as to rotate integrally, there is no play in the circumferential direction between the first hub member and the power transmission member, and the power transmission is performed with the second hub member. Since only one spline fitting is interposed between the members, the play in the circumferential direction between the second hub member and the power transmission member can be suppressed to be small. Further, since the first hub member is integrally formed with the power transmission member, the first hub member does not need to extend to the inner peripheral side, and may extend in the axial direction of the automatic transmission. Therefore, the axial lengths of the power transmission member, the first clutch, and the second clutch as a whole can be shortened as much as possible.

In the clutch structure of the automatic transmission, the first clutch includes a first engaging piston that advances in the axial direction so as to engage a plurality of friction plates of the first clutch, and the first engaging piston. It further has a first fastening hydraulic chamber to which hydraulic oil for advancing in the axial direction is supplied, and the second clutch is in the axial direction so as to engage a plurality of friction plates of the second clutch. It further has a second fastening hydraulic chamber to advance and a second fastening hydraulic chamber to which hydraulic oil for advancing the second fastening piston in the axial direction is supplied, and the first fastening hydraulic chamber and the second fastening It is preferable that the hydraulic chamber is arranged inside the first hub member in the radial direction.

As a result, since the first hub member only extends in the axial direction of the automatic transmission, the first fastening hydraulic chamber and the second fastening hydraulic chamber are compactly arranged inside the first hub member in the radial direction. be able to.

As described above, when the first fastening hydraulic chamber and the second fastening hydraulic chamber are arranged radially inside the first hub member, the first clutch is said to the first fastening piston. The first centrifugal balance chamber provided on the power transmission member side opposite to the first fastening hydraulic chamber and a part of the wall portion of the first centrifugal balance chamber are in contact with the power transmission member. It further has a first centrifugal balance chamber forming member, and the hydraulic oil of the first centrifugal balance chamber is used as a lubricating oil between the power transmission member and the first centrifugal balance chamber forming member of the first clutch. It is preferable that an oil passage for leading to the friction plate is provided.

This makes it possible to easily guide the hydraulic oil from the first centrifugal balance chamber to the friction plate of the first clutch as lubricating oil. Further, when the lubricating oil is supplied to the friction plate through the inside of the power transmission member and the first hub member from the oil passage provided inside the input shaft or the output shaft arranged on the inner peripheral side of the axial extension member. In comparison, the length of the power transmission member in the axial direction can be shortened.

In one embodiment in the case where the first fastening hydraulic chamber and the second fastening hydraulic chamber are arranged radially inside the first hub member, the first clutch drum member is provided on the inner peripheral side of the second clutch drum member. The three clutch drum members are provided on the inner peripheral side of the third clutch drum member and on the opposite side of the second hub member from the first hub member via a plurality of friction plates arranged in the axial direction. A third clutch having a third hub member is further provided, the second hub member is integrally formed with the axial extension member, and the third clutch drum member is integrally formed with the second hub member. It is fixed so that it rotates to.

As a result, in addition to the first clutch and the second clutch, the third clutch is arranged side by side in the axial direction of the automatic transmission, and the third clutch drum member of the third clutch also rotates integrally with the power transmission member. In this case, the third clutch drum member is fixed to the second hub member adjacent thereto so as to rotate integrally with the third clutch drum member, so that the circumference between the third clutch drum member and the power transmission member is The backlash in the direction can be suppressed to be small, and the length of the entire power transmission member, the first clutch, the second clutch, and the third clutch in the axial direction can be shortened as much as possible.

In the above embodiment, the second clutch includes a second centrifugal balance chamber provided on the second hub member side, which is opposite to the second fastening hydraulic chamber with respect to the second fastening piston. It further has a second centrifugal balance chamber forming member that constitutes a part of the wall portion of the second centrifugal balance chamber and abuts on the second hub member, and the second hub member and the second centrifugal balance chamber forming member. It is preferable that an oil passage for guiding the hydraulic oil of the second centrifugal balance chamber to the friction plate of the second clutch as lubricating oil is provided between the two.

This makes it possible to easily guide the hydraulic oil from the second centrifugal balance chamber to the friction plate of the second clutch as lubricating oil. Further, lubricating oil is supplied to the friction plate through the inside of the axial extension member and the second hub member from the oil passage provided inside the input shaft or the output shaft arranged on the inner peripheral side of the axial extension member. Compared with the case, the length of the second hub member in the axial direction can be shortened. Therefore, the axial length of the entire power transmission member, the first clutch, the second clutch, and the third clutch can be shortened as much as possible.

In another embodiment in which the first fastening hydraulic chamber and the second fastening hydraulic chamber are arranged radially inside the first hub member, the first fastening hydraulic chamber and the second fastening hydraulic chamber are provided on the inner peripheral side of the second clutch drum member. The third clutch drum member is provided on the inner peripheral side of the third clutch drum member and on the side opposite to the first hub member of the second hub member via a plurality of friction plates arranged in the axial direction. A third clutch having a third hub member is further provided, the third clutch drum member is integrally formed with the axial extension member, and the second hub member is integrally formed with the axial extension member. It is fixed to the third clutch drum member, which is an integrally formed member, so as to rotate integrally.

As a result, as in the configuration of the above-described embodiment, the play in the circumferential direction between the third clutch drum member and the power transmission member can be suppressed to be small, and the power transmission member, the first clutch, and the second clutch can be suppressed. And the length of the entire third clutch in the axial direction can be shortened as much as possible.

In another embodiment, the second clutch has a second centrifugal balance chamber provided on the second hub member side, which is opposite to the second fastening hydraulic chamber with respect to the second fastening piston. It further has a second centrifugal balance chamber forming member that constitutes a part of the wall portion of the second centrifugal balance chamber and is in contact with the third clutch drum member, and the third clutch drum member and the second centrifugal balance. It is preferable that an oil passage for guiding the hydraulic oil of the second centrifugal balance chamber to the friction plate of the second clutch as lubricating oil is provided between the chamber forming member.

This makes it possible to easily guide the hydraulic oil from the second centrifugal balance chamber to the friction plate of the second clutch as lubricating oil. Further, from the oil passage provided inside the input shaft or the output shaft arranged on the inner peripheral side of the axial extension member, the lubricating oil is supplied from the axial extension member, the third clutch drum member and the second hub member. The axial lengths of the third clutch drum member and the second hub member can be shortened as compared with the case where the second clutch is supplied to the friction plate through the inside. Therefore, the axial length of the entire power transmission member, the first clutch, the second clutch, and the third clutch can be shortened as much as possible.

As described above, according to the clutch structure of the automatic transmission of the present invention, the circumferential direction between the hub member and the power transmission member of the first clutch and between the hub member and the power transmission member of the second clutch. The backlash of the automatic transmission can be reduced as much as possible, and the axial length of the automatic transmission of the power transmission member, the first clutch and the second clutch as a whole can be shortened as much as possible.

It is a skeleton diagram which shows the automatic transmission to which the clutch structure which concerns on embodiment of this invention is applied. It is a fastening table which shows the fastening state of the friction fastening element at each shift stage of the automatic transmission. It is an enlarged sectional view of the part provided with three clutches in the said automatic transmission. It is a figure corresponding to FIG. 3 which shows the modification of the said embodiment.

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

FIG. 1 shows, as an example, an automatic transmission 1 to which the clutch structure according to the embodiment of the present invention is applied. The automatic transmission 1 is a vertical type automatic transmission mounted on an FR type vehicle.

The automatic transmission 1 includes a transmission case 11, an input shaft 12 inserted into the transmission case 11 and to which power from a drive source (engine, motor, etc.) of the vehicle is input, and inside the transmission case 11. A transmission mechanism 14 accommodated in the transmission and transmitting power from the drive source via the input shaft 12, and an output shaft 13 inserted in the transmission case 11 and outputting power from the transmission mechanism 14 to the propeller shaft. have.

The input shaft 12 and the output shaft 13 are coaxially arranged along the vehicle front-rear direction, and the input shaft 12 is located on the front side of the vehicle and the output shaft 13 is mounted on the vehicle with the automatic transmission 1 mounted on the vehicle. Is located on the rear side of the vehicle. In the following description, the drive source side (left side in FIG. 1) in the axial direction of the input shaft 12 (axial direction of the output shaft 13) is referred to as a front side, and the side opposite to the drive source in the axial direction of the input shaft 12 ( The right side of FIG. 1) is called the rear side. Further, the axial direction of the input shaft 12 (the axial direction of the output shaft 13) is also referred to as the axial direction of the automatic transmission 1, and hereinafter, the axial direction of the automatic transmission 1 is simply referred to as the axial direction. The radial direction of the automatic transmission 1, which is the direction perpendicular to the axial direction, is simply called the radial direction.

The transmission mechanism 14 has a first planetary gear set PG1 (hereinafter referred to as a first gear set PG1), a second planetary gear set PG2 (hereinafter referred to as a second gear set PG2), and a third planetary gear set PG3 (hereinafter referred to as a third gear set PG2) arranged in the axial direction. It has a gear set PG3) and a fourth planetary gear set PG4 (hereinafter referred to as a fourth gear set PG4). The first gear set PG1, the second gear set PG2, the third gear set PG3, and the fourth gear set PG4 are arranged in this order from the front side to form a plurality of power transmission paths from the input shaft 12 to the output shaft 13. The first to fourth gear sets PG1 to PG4 are arranged coaxially with the input shaft 12 and the output shaft 13.

The first gear set PG1 has a first sun gear S1, a first ring gear R1 and a first carrier C1 as rotating elements. The first gear set PG1 is a single pinion type, and a plurality of pinions P1 supported by the first carrier C1 and arranged at intervals in the circumferential direction of the first gear set PG1 are the first sun gear S1 and the first ring gear. It is meshed with both R1.

The second gear set PG2 has a second sun gear S2, a second ring gear R2, and a second carrier C2 as rotating elements. The second gear set PG2 is also a single pinion type, and a plurality of pinions P2 supported by the second carrier C2 and arranged at intervals in the circumferential direction of the second gear set PG2 are the second sun gear S2 and the second ring gear. It is meshed with both R2.

The third gear set PG3 has a third sun gear S3, a third ring gear R3, and a third carrier C3 as rotating elements. The third gear set PG3 is also a single pinion type, and a plurality of pinions P3 supported by the third carrier C3 and arranged at intervals in the circumferential direction of the third gear set PG3 are the third sun gear S3 and the third ring gear. It is meshed with both R3.

The fourth gear set PG4 has a fourth sun gear S4, a fourth ring gear R4, and a fourth carrier C4 as rotating elements. The fourth gear set PG4 is also a single pinion type, and a plurality of pinions P4 supported by the fourth carrier C4 and arranged at intervals in the circumferential direction of the fourth gear set PG4 are the fourth sun gear S4 and the fourth ring gear. It is meshed with both R4.

The first sun gear S1 of the first gear set PG1 is divided into two in the axial direction of the input shaft 12, and is arranged on the rear side relative to the front side first sun gear S1a arranged on the relatively front side. It has one sun gear S1b. That is, the first gear set PG1 is a double sun gear type gear set. Since the front and rear first sun gears S1a and S1b have the same number of teeth and mesh with the pinion P1 supported by the first carrier C1, these front and rear first sun gears S1a and S1b The number of revolutions of is always equal. That is, the front and rear first sun gears S1a and S1b always rotate at the same rotation speed, and when the rotation of one gear is stopped, the rotation of the other gear is also stopped.

The first sun gear S1 (strictly speaking, the rear first sun gear S1b) and the fourth sun gear S4 are always connected, the first ring gear R1 and the second sun gear S2 are always connected, and the second carrier C2 and the fourth carrier are always connected. C4 is always connected, and the third carrier C3 and the fourth ring gear R4 are always connected. Further, the input shaft 12 is always connected to the first carrier C1, and the output shaft 13 is always connected to the fourth carrier C4. Specifically, the input shaft 12 is connected to the first carrier C1 via a power transmission member 18 passing between the front and rear first sun gears S1a and S1b. The rear first sun gear S1b and the fourth sun gear S4 are connected to each other via a power transmission shaft 15. The second carrier C2 and the fourth carrier C4 are connected via a power transmission member 16.

The speed change mechanism 14 has five friction fastening elements (three clutches 20) for selecting one from the plurality of power transmission paths formed by the first to fourth gear sets PG1 to PG4 and switching the power transmission path. , 30, 40 and two brakes 50, 60).

The three clutches 20, 30, and 40 are arranged in front of the first gear set PG1 and are arranged side by side in the axial direction. These three clutches 20, 30 and 40 are arranged in the order of the clutch 20, the clutch 30 and the clutch 40 from the rear side (the side closer to the first gear set PG1). Hereinafter, the clutch 20 is referred to as a rear clutch 20, the clutch 30 is referred to as an intermediate clutch 30, and the clutch 40 is referred to as a front clutch 40.

In the axial direction, the brake 50 is arranged on the front side of the front clutch 40, and the brake 60 is arranged on the rear side of the brake 50 and in the vicinity of the third gear set PG3. Hereinafter, the brake 50 is referred to as a front brake 50, and the brake 60 is referred to as a rear brake 60.

The rear clutch 20 is configured to connect and disconnect the input shaft 12 and the first carrier C1 and the third sun gear S3. The rear clutch 20 is arranged immediately in front of the first gear set PG1.

The intermediate clutch 30 is configured to connect and disconnect the first ring gear R1 and the second sun gear S2 and the third sun gear S3. The intermediate clutch 30 is arranged immediately on the front side of the rear clutch 20.

The front clutch 40 is configured to engage and disengage between the second ring gear R2 and the third sun gear S3. The front clutch 40 is arranged immediately on the front side of the intermediate clutch 30.

The front brake 50 is configured to connect and disconnect the first sun gear S1 (strictly speaking, the front first sun gear S1a) and the transmission case 11. When the front brake 50 is fastened, the first sun gear S1 is fixed to the transmission case 11. The front brake 50 and the front first sun gear S1a are connected to each other by a connecting member 8.

The rear brake 60 is configured to connect and disconnect the third ring gear R3 and the transmission case 11. When the rear brake 60 is fastened, the third ring gear R3 is fixed to the transmission case 11.

Each of the friction fastening elements is fastened by supplying hydraulic oil to the fastening hydraulic chamber of each friction fastening element. As shown in the fastening table of FIG. 2, by selectively fastening three friction fastening elements from the five friction fastening elements, forward speeds 1 to 8 and backward speeds are formed. In the fastening table of FIG. 2, the circles indicate that the friction fastening elements are fastened, and the blanks indicate that the friction fastening elements are released (released).

Specifically, the first speed is formed by engaging the rear clutch 20, the front brake 50, and the rear brake 60. The second speed is formed by engaging the intermediate clutch 30, the front brake 50 and the rear brake 60. The third speed is formed by engaging the rear clutch 20, the intermediate clutch 30, and the rear brake 60. The fourth speed is formed by engaging the intermediate clutch 30, the front clutch 40 and the rear brake 60. The fifth speed is formed by engaging the rear clutch 20, the front clutch 40, and the rear brake 60. The sixth speed is formed by engaging the rear clutch 20, the intermediate clutch 30, and the front clutch 40. The 7th speed is formed by engaging the rear clutch 20, the front clutch 40 and the front brake 50. The eighth speed is formed by engaging the intermediate clutch 30, the front clutch 40 and the front brake 50. A retreat speed is formed by engaging the front clutch 40, the front brake 50, and the rear brake 60. At the 6th speed, the rotation speed of the input shaft 12 and the rotation speed of the output shaft 13 are the same.

Next, the configurations of the rear clutch 20, the intermediate clutch 30, and the front clutch 40 will be described in detail with reference to FIG. The front clutch 40 corresponds to the first clutch of the present invention, the intermediate clutch 30 corresponds to the second clutch of the present invention, and the rear clutch 20 corresponds to the third clutch of the present invention. In FIG. 3, C is the central axis of the input shaft 12 (the central axis of the output shaft 13).

As shown in FIG. 3, the front clutch 40 is provided on the inner peripheral side of the first clutch drum member 6 and the first clutch drum member 6 via a plurality of friction plates 41 arranged in the axial direction. It has a hub member 35. The first clutch drum member 6 and the first hub member 35 are arranged coaxially with the input shaft 12 and the output shaft 13. The first clutch drum member 6 has a bottomed tubular shape that opens to the front side. The rear end (bottom) of the first clutch drum member 6 is connected to the second ring gear R2. The first hub member 35 is provided on the side of the front clutch 40 opposite to the intermediate clutch 30 (that is, the front side of the front clutch 40) and is integrally formed with an annular power transmission member 45 that is rotatable around the input shaft 12. It is formed so as to project rearward from the power transmission member 45. The power transmission member 45 is connected to the third sun gear S3 via the power transmission drum member 5. By such a connection, the front clutch 40 can be engaged in and disengaged between the second ring gear R2 and the third sun gear S3.

The power transmission member 45 and the power transmission drum member 5 are arranged coaxially with the input shaft 12 and the output shaft 13. The power transmission drum member 5 has a bottomed tubular shape that opens to the front side, and is provided on the outer peripheral side of the first clutch drum member 6. The front end portion (open side end portion) of the power transmission drum member 5 is connected to the outer peripheral side end portion of the power transmission member 45. The rear end (bottom) of the power transmission drum member 5 is connected to the third sun gear S3.

The power transmission member 45 has a tubular boss portion 45a projecting rearward at the inner peripheral side end portion thereof, and extends along the axial direction on the inner peripheral side of the boss portion 45a at the boss portion 45a. It is spline-fitted with the axial extension member 51. The axial extension member 51 is provided with a snap ring 71 that regulates the axial movement of the power transmission member 45 with respect to the axial extension member 51.

The plurality of friction plates 41 of the front clutch 40 are a drum side friction plate 41a movably attached to the inside of the front end portion (opening side end portion) of the first clutch drum member 6 and a first first. The hub member 35 includes a hub-side friction plate 41b that is movable in the axial direction and is attached so as to alternate with the drum-side friction plate 41a.

The front clutch 40 includes a first fastening piston 42 that advances in the axial direction (in the present embodiment, the front side) so as to engage a plurality of friction plates 41 (drum side friction plate 41a and hub side friction plate 41b). It further has a first fastening hydraulic chamber 43 to which hydraulic oil for advancing the first fastening piston 42 in the axial direction (front side) is supplied.

The first fastening hydraulic chamber 43 is arranged inside the first hub member 35 in the radial direction, and is formed by the first fastening piston 42 and the first fastening hydraulic chamber forming member 52. The first fastening hydraulic chamber forming member 52 is spline-fitted with the axial extension member 51. The axial extension member 51 is provided with a snap ring 72 that regulates the axial movement of the first fastening hydraulic chamber forming member 52 with respect to the axial extension member 51.

The first fastening hydraulic chamber forming member 52 is provided with a first oil passage 52a for supplying hydraulic oil to the first fastening hydraulic chamber 43 from the inside in the radial direction so as to extend in the radial direction. Further, the axial extension member 51 is provided with an oil passage 51a for a first fastening hydraulic chamber extending in the radial direction for supplying hydraulic oil to the first fastening hydraulic chamber 43 via the first oil passage 52a. Has been done.

The first fastening piston 42 has a pressure receiving portion 42a that receives the pressure of the hydraulic oil supplied to the first fastening hydraulic chamber 43. The pressure receiving portion 42a is located on the front side of the first fastening hydraulic chamber 43, and moves to the front side under the pressure of the hydraulic oil. The pressure receiving portion 42a is a plurality of first return springs 47 (1st return springs 47) provided side by side in the circumferential direction in the first centrifugal balance chamber 48 located on the opposite side (front side) of the first fastening hydraulic chamber 43 with respect to the pressure receiving portion 42a. In FIG. 3, only one is shown), which is urged to the rear side. In the present embodiment, each first return spring 47 is composed of a compression coil spring. It is also possible to configure the first return spring 47 with a leaf spring (the same applies to the second return spring 37 and the third return spring 27 described later).

The first fastening piston 42 is formed in a bottomed tubular shape that opens to the rear side, and the bottom portion located on the front side corresponds to the pressure receiving portion 42a. The opening-side end (rear-side end) of the first fastening piston 42 extends radially outward, and the radially outer end of the expanded portion is located on the rear side of the friction plate 41. A pressing portion 42b that presses the friction plate 41 forward is provided.

Here, between the input shaft 12 and the axial extension member 51 in the radial direction, the connecting member 8 that connects the front brake 50 and the front first sun gear S1a and the axial extension member 51 can be rotated. A rotation support member 9 for supporting is provided. The rotation support member 9 also performs rotation support for the connecting member 8 located on the inner peripheral side of the rotation support member 9.

The input shaft 12 is provided with an oil passage 12a extending along the center of the input shaft 12 and a plurality of oil passages 12b extending radially outward from the oil passage 12a. An oil passage 8a extending in the radial direction is provided in a portion of the connecting member 8 corresponding to each oil passage 12b. Hydraulic oil is supplied to the rotary support member 9 through the oil passages 12a, 12b, 8a. The hydraulic oil supplied to the rotary support member 9 is supplied from the oil passage 9a provided in the portion of the rotary support member 9 corresponding to the oil passage 51a for the first fastening hydraulic chamber to the oil passage 51a for the first fastening hydraulic chamber and the oil passage 51a. It is supplied to the first fastening hydraulic chamber 43 via the first oil passage 52a. The hydraulic oil supplied to the first fastening hydraulic chamber 43 moves the pressure receiving portion 42a of the first fastening piston 42 to the front side against the urging force of the first return spring 47, and the pressing portion 42b moves the friction plate 41. Is pressed forward, whereby the drum-side friction plate 41a and the hub-side friction plate 41b are engaged with each other, and the front-side clutch 40 is engaged. The front side of the friction plate 41 is provided with a retaining portion 45b composed of a power transmission member 45 that receives the pressing force of the pressing portion 42b.

A first centrifugal balance chamber forming member 49 forming a part of a wall portion of the first centrifugal balance chamber 48 is provided between the first fastening piston 42 and the power transmission member 45. The wall portion of the first centrifugal balance chamber 48 is composed of a first fastening hydraulic chamber forming member 52, an axial extension member 51, a first fastening piston 42, and a first centrifugal balance chamber forming member 49.

The first centrifugal balance chamber forming member 49 is pressed forward by the reaction force of the urging force that urges the pressure receiving portion 42a to the rear side of the first return spring 47, and the front end of the first centrifugal balance chamber forming member 49. Is in contact with the power transmission member 45. The rear end of the inner peripheral end of the first centrifugal balance chamber forming member 49 is in contact with the outer peripheral surface of the boss portion 45a of the power transmission member 45.

The first centrifugal balance chamber forming member 49 is formed so that a portion other than the portion with which the first return spring 47 abuts protrudes rearward from the portion with which the first return spring 47 abuts. This is to make the volume of the first centrifugal balance chamber 48 an appropriate value while ensuring the length of the first return spring 47.

The axial extension member 51 is provided with a first centrifugal balance chamber oil passage 51b extending in the radial direction in the same manner as the first fastening hydraulic chamber oil passage 51a. The oil passage 51b for the first centrifugal balance chamber is provided at a portion of the axially extending member 51 that is different from the oil passage 51a for the first fastening hydraulic chamber in the circumferential direction. The hydraulic oil supplied to the rotation support member 9 by the oil passages 12a, 12b, 8a is supplied to the first centrifugal balance chamber 48 via the oil passage 51b for the first centrifugal balance chamber.

An oil passage is provided between the power transmission member 45 and the first centrifugal balance chamber forming member 49 to guide the hydraulic oil of the first centrifugal balance chamber 48 to the friction plate 41 of the front clutch 40 as lubricating oil. There is. Specifically, the hydraulic oil of the first centrifugal balance chamber 48 is applied to a part of the first centrifugal balance chamber forming member 49 in the circumferential direction of the portion (inner peripheral side end and front side end) that comes into contact with the power transmission member 45. A groove 49a is formed so as to flow along the surface of the power transmission member 45. The hydraulic oil that has passed through the groove 49a formed at the inner peripheral side end and the front side end of the first centrifugal balance chamber forming member 49 in order is the first along the surface (rear side surface) of the power transmission member 45 by centrifugal force. After flowing to the 1 hub member 35, it reaches the friction plate 41 through a through hole (not shown) provided in the first hub member 35 so as to extend in the radial direction.

By providing such an oil passage (groove 49a), the hydraulic oil from the first centrifugal balance chamber 48 can be easily guided to the friction plate 41 as a lubricating oil. Further, the axial length of the power transmission member 45 is shortened as compared with the case where the lubricating oil is supplied from the oil passage 12a provided inside the input shaft 12 to the friction plate 41 through the inside of the power transmission member 45. Can be done.

The intermediate clutch 30 is provided via a second clutch drum member 7 provided on the inner peripheral side of the first clutch drum member 6 and a plurality of friction plates 31 arranged in the axial direction on the inner peripheral side of the second clutch drum member 7. It has a second hub member 34 provided in the above. The second clutch drum member 7 and the second hub member 34 are arranged coaxially with the input shaft 12 and the output shaft 13. The second clutch drum member 7 has a bottomed tubular shape that opens to the front side. The rear end (bottom) of the second clutch drum member 7 is connected to the first ring gear R1 and the second sun gear S2. The second hub member 34 is fixed to the third clutch drum member 4 (which is integrally formed with the axial extension member 51 as described later) in the rear clutch 20 and is the third clutch. It is connected to the third sun gear S3 via the drum member 4, the axial extension member 51, the power transmission member 45, and the power transmission drum member 5. By such a connection, the intermediate clutch 30 can connect and disconnect the first ring gear R1 and the second sun gear S2 and the third sun gear S3.

The plurality of friction plates 31 of the intermediate clutch 30 are a drum-side friction plate 31a and a second friction plate 31a movably attached to the inside of the front end (opening-side end) of the second clutch drum member 7. A hub-side friction plate 31b that is movable in the axial direction and is attached so as to alternate with the drum-side friction plate 31a is included in the outer peripheral portion (friction plate attachment portion 34b described later) of the hub member 34.

The intermediate clutch 30 and the second fastening piston 32 that advance in the axial direction (rear side in this embodiment) so as to engage the plurality of friction plates 31 (drum side friction plate 31a and hub side friction plate 31b) with each other. Further, it has a second fastening hydraulic chamber 33 to which hydraulic oil for advancing the second fastening piston 32 in the axial direction (rear side) is supplied.

The second fastening hydraulic chamber 33 is arranged radially inside the first hub member 35 and behind the first fastening hydraulic chamber 43, and is provided by the second fastening piston 32 and the second fastening hydraulic chamber forming member 53. It is formed. The second fastening hydraulic chamber forming member 53 is spline-fitted with the axial extension member 51 in the same manner as the first fastening hydraulic chamber forming member 52. The axial extension member 51 is provided with a snap ring 73 that regulates the axial movement of the second fastening hydraulic chamber forming member 53 with respect to the axial extension member 51.

The second fastening hydraulic chamber forming member 53 is provided with a second oil passage 53a for supplying hydraulic oil to the second fastening hydraulic chamber 33 from the inside in the radial direction so as to extend in the radial direction. Further, the axial extension member 51 is provided with an oil passage 51c for a second fastening hydraulic chamber extending in the radial direction for supplying hydraulic oil to the second fastening hydraulic chamber 33 via the second oil passage 53a. Has been done.

The second fastening piston 32 has a pressure receiving portion 32a that receives the pressure of the hydraulic oil supplied to the second fastening hydraulic chamber 33. The pressure receiving portion 32a is located on the rear side of the second fastening hydraulic chamber 33, and moves to the rear side by receiving the pressure of the hydraulic oil. The pressure receiving portion 32a is a plurality of second return springs 37 provided side by side in the circumferential direction in the second centrifugal balance chamber 38 located on the opposite side (rear side) of the second fastening hydraulic chamber 33 with respect to the pressure receiving portion 32a. It is urged to the front side by the urging force (only one is shown in FIG. 3). In this embodiment, each second return spring 37 is composed of a compression coil spring.

The second fastening piston 32 is formed in a bottomed tubular shape that opens to the rear side, and the bottom portion located on the front side corresponds to the pressure receiving portion 32a. The opening-side end (rear-side end) of the second fastening piston 32 extends radially outward, and the radially outer end of the expanded portion is located on the front side of the friction plate 31. A pressing portion 32b for pressing the friction plate 31 to the rear side is provided. The pressing portion 32b is located immediately behind the pressing portion 32b of the first fastening piston 42.

The hydraulic oil supplied to the rotary support member 9 by the oil passages 12a, 12b, 8a as described above is from the oil passage 9b provided in the portion of the rotary support member 9 corresponding to the oil passage 51c for the second fastening hydraulic chamber. , Is supplied to the second fastening hydraulic chamber 33 via the second fastening hydraulic chamber oil passage 51c and the second oil passage 53a. The hydraulic oil supplied to the second fastening hydraulic chamber 33 causes the pressure receiving portion 32a of the second fastening piston 32 to move to the rear side against the urging force of the second return spring 37, and the pressing portion 32b is a friction plate. The 31 is pressed to the rear side, whereby the drum side friction plate 31a and the hub side friction plate 31b are engaged with each other, and the intermediate clutch 30 is in the engaged state. A retaining portion 34a composed of a second hub member 34 is provided on the rear side of the friction plate 31 to receive the pressing force of the pressing portion 32b.

The rear clutch 20 has a third clutch drum member 4 provided on the inner peripheral side of the second clutch drum member 7, and a plurality of friction plates 21 arranged in the axial direction on the inner peripheral side of the third clutch drum member 4. It has a third hub member 24 provided therethrough. The third clutch drum member 4 and the third hub member 24 are arranged coaxially with the input shaft 12 and the output shaft 13. The third clutch drum member 4 is formed of, for example, an aluminum alloy integrally with the axially extending member 51. The third clutch drum member 4 has a bottomed tubular shape that opens to the rear side, and the bottom portion 4a of the third clutch drum member 4 is connected to the axially extending member 51. As a result, the third clutch drum member 4 is connected to the third sun gear S3 in the same manner as the first hub member 35 and the second hub member 34. The third hub member 24 is arranged on the side of the second hub member 34 opposite to the first hub member 35 (rear side of the second hub member 34), and is the front end of the rotating shaft 81 of the first carrier C1. It is connected to the disk-shaped member 82 connected to the portion. As described above, the first carrier C1 (rotary shaft 81) is connected to the input shaft 12 via the power transmission member 18. By such a connection, the rear clutch 20 can connect and disconnect the input shaft 12 and the first carrier C1 and the third sun gear S3.

The second hub member 34 of the intermediate clutch 30 has a friction plate mounting portion 34b to which the hub side friction plate 31b is mounted, and a radial extending portion 34c extending radially inward from the friction plate mounting portion 34b. The above-mentioned retaining portion 34a is provided at the rear end portion of the friction plate mounting portion 34b. The second hub member 34 is fixed to the bottom portion 4a of the third clutch drum member 4 so as to rotate integrally with the radial extension portion 34c via the rivet 80. Instead of the retaining portion 34a provided on the second hub member 34, it is also possible to provide a retaining portion on the bottom portion 4a of the third clutch drum member 4 to receive the pressing force by the pressing portion 32b.

A second centrifugal balance chamber forming member 39 forming a part of the wall portion of the second centrifugal balance chamber 38 is provided between the second fastening piston 32 and the bottom portion 4a of the third clutch drum member 4. The wall portion of the second centrifugal balance chamber 38 is composed of a second fastening hydraulic chamber forming member 53, an axial extension member 51, a second fastening piston 32, and a second centrifugal balance chamber forming member 39.

The second centrifugal balance chamber forming member 39 is pressed rearward by the reaction force of the urging force that urges the pressure receiving portion 32a to the front side of the second return spring 37, and is pushed to the rear side of the second centrifugal balance chamber forming member 39. The end is in contact with the bottom portion 4a of the third clutch drum member 4. The front end of the inner peripheral end of the second centrifugal balance chamber forming member 39 is in contact with the outer peripheral surface of the axial extension member 51.

The second centrifugal balance chamber forming member 39 is formed so that a portion other than the portion with which the second return spring 37 abuts protrudes forward from the portion with which the second return spring 37 abuts. This is to make the volume of the second centrifugal balance chamber 38 an appropriate value while ensuring the length of the second return spring 37.

The axial extension member 51 is provided with a second centrifugal balance chamber oil passage 51d extending in the radial direction. The oil passage 51d for the second centrifugal balance chamber is provided at a portion of the axially extending member 51 that is different from the oil passage 51c for the second fastening hydraulic chamber in the circumferential direction. The hydraulic oil supplied to the rotation support member 9 by the oil passages 12a, 12b, and 8a is supplied to the second centrifugal balance chamber 38 via the oil passage 51d for the second centrifugal balance chamber.

Between the second centrifugal balance chamber forming member 39 and the bottom 4a of the third clutch drum member 4, there is an oil passage that guides the hydraulic oil of the second centrifugal balance chamber 38 to the friction plate 31 of the intermediate clutch 30 as lubricating oil. It is provided. Specifically, the operation of the second centrifugal balance chamber 38 is performed on a part of the second centrifugal balance chamber forming member 39 in the circumferential direction of the portion (inner peripheral end and rear end) that comes into contact with the third clutch drum member 4. A groove 39a is formed to allow oil to flow along the surface of the third clutch drum member 4. The hydraulic oil that has passed through the groove 39a formed at the inner peripheral side end and the rear side end of the second centrifugal balance chamber forming member 39 in order is subjected to centrifugal force to the bottom portion 4a of the third clutch drum member 4 and the second hub member 34. After flowing to the friction plate mounting portion 34b along the surface of the radial extension portion 34c, the friction plate 31 is reached through a through hole (not shown) provided in the friction plate mounting portion 34b so as to extend in the radial direction.

By providing such an oil passage (groove 39a), the hydraulic oil from the second centrifugal balance chamber 38 can be easily guided to the friction plate 31 as lubricating oil. Further, as compared with the case where the lubricating oil is supplied from the oil passage 12a provided inside the input shaft 12 to the friction plate 31 through the inside of the third clutch drum member 4 and the second hub member 34, the third clutch drum member 4 In particular, the axial length of the second hub member 34, particularly the radial extension 34c, can be shortened.

The plurality of friction plates 21 of the rear clutch 20 are attached to the inside of the third clutch drum member 4 so as to be movable in the axial direction, and to the outer peripheral portion of the third hub member 24 in the axial direction. Includes a hub-side friction plate 21b that is movable and mounted so as to alternate with the drum-side friction plate 21a.

The rear clutch 20 advances in the axial direction (rear side in this embodiment) so as to engage the plurality of friction plates 21 (drum side friction plate 21a and hub side friction plate 21b) with each other. And a third fastening hydraulic chamber 23 to which hydraulic oil for advancing the third fastening piston 22 in the axial direction (rear side) is further provided.

The third fastening hydraulic chamber 23 is arranged behind the bottom portion 4a of the third clutch drum member 4, and is formed by the bottom portion 4a of the third clutch drum member 4, the axial extension member 51, and the third fastening piston 22. Has been done. The axial extension member 51 is provided with an oil passage 51e for a third fastening hydraulic chamber extending in the radial direction for supplying hydraulic oil to the third fastening hydraulic chamber 43 from the inside in the radial direction.

A pressure receiving portion 22a of the third fastening piston 22 is arranged behind the bottom portion 4a of the third clutch drum member 4. The pressure receiving portion 22a is a plurality of third return springs 27 (in FIG. 3) provided side by side in the circumferential direction in the third centrifugal balance chamber 28 located on the side opposite to the third fastening hydraulic chamber 23 with respect to the pressure receiving portion 22a. It is urged to the front side by the urging force (only one is shown). In this embodiment, each third return spring 27 is composed of a compression coil spring.

The third fastening piston 22 is formed in a bottomed tubular shape that opens to the rear side, and the bottom portion 4a located on the front side corresponds to the pressure receiving portion 22a. The opening-side end (rear-side end) of the third fastening piston 22 extends radially outward, and the radially outer end of the expanded portion is located on the front side of the friction plate 21. A pressing portion 22b that presses the friction plate 21 to the rear side is provided.

The hydraulic oil supplied to the rotary support member 9 is supplied from the oil passage 9c provided in the portion of the rotary support member 9 corresponding to the oil passage 51e for the third fastening hydraulic chamber through the oil passage 51e for the third fastening hydraulic chamber. Is supplied to the third fastening hydraulic chamber 23. The hydraulic oil supplied to the third fastening hydraulic chamber 23 moves the pressure receiving portion 22a of the third fastening piston 22 to the rear side against the urging force of the third return spring 27, and the pressing portion 22b is a friction plate. 21 is pressed to the rear side, whereby the drum side friction plate 21a and the hub side friction plate 21b are engaged with each other, and the rear side clutch 20 is in the engaged state. A retaining member 76 (consisting of a snap ring similar to the snap ring 77 described later) is provided on the rear side of the friction plate 21 to receive the pressing force of the pressing portion 22b.

The third centrifugal balance chamber 28 is composed of an axial extension member 51, a third fastening piston 22, and a third centrifugal balance chamber forming member 29. The third centrifugal balance chamber forming member 29 is fitted to the axial extension member 51. A C-shaped snap ring 77, which is partially cut off in the circumferential direction, is fitted in the rear side portion (groove portion) of the third centrifugal balance chamber forming member 29 in the axial extension member 51. The movement of the third centrifugal balance chamber forming member 29 to the rear side is restricted by 77. As a result, the third centrifugal balance chamber forming member 29 can receive the reaction force of the urging force that urges the pressure receiving portion 22a of the third return spring 27 to the front side.

The axial extension member 51 is provided with a third centrifugal balance chamber oil passage 51f extending in the radial direction. The third centrifugal balance chamber oil passage 51f is provided in a portion of the axial extension member 51 that is different from the third fastening hydraulic chamber oil passage 51e in the circumferential direction. The hydraulic oil supplied to the rotation support member 9 by the oil passages 12a, 12b, 8a is supplied to the third centrifugal balance chamber 28 via the oil passage 51f for the third centrifugal balance chamber.

Here, for example, the first hub member 35 of the front clutch 40 extends radially inward to the axial extension member 51 and is spline-fitted with the axial extension member 51 in the same manner as the power transmission member 45. To do. In this case, since the two spline fittings are interposed between the power transmission member 45 and the first hub member 35, there is a problem that the backlash in the circumferential direction between the two splines is considerably increased.

On the other hand, in the present embodiment, since the first hub member 35 is integrally formed with the power transmission member 45, there is no play in the circumferential direction between the first hub member 35 and the power transmission member 45. Further, since the second hub member 34 is fixed to the bottom portion 4a of the third clutch drum member 4 integrally formed with the axial extension member 51, the second hub member 34 is between the second hub member 34 and the power transmission member 45. Since only one spline fitting is interposed, the play in the circumferential direction between the second hub member 34 and the power transmission member 45 can be suppressed to be small. Similarly, the play in the circumferential direction between the third clutch drum member 4 and the power transmission member 45 can be suppressed to be small.

Further, since the first hub member 35 only extends in the axial direction and does not need to extend to the inner peripheral side, the first fastening hydraulic chamber 43 and the second fastening hydraulic chamber 43 are radially inside the first hub member 35. The 33 can be arranged compactly. Further, since the second hub member 34 is fixed to the bottom portion 4a of the third clutch drum member 4, both the second hub member 34 and the bottom portion 4a of the third clutch drum member 4 are extended in the axial direction. There is no need to extend inward in the radial direction. Therefore, the axial length of the power transmission member 45, the front clutch 40, the intermediate clutch 30, and the rear clutch 20 can be shortened as much as possible.

The present invention is not limited to the above embodiment, and can be substituted within a range that does not deviate from the gist of the claims.

For example, in the above embodiment, the second hub member 34 is fixed to the bottom portion 4a of the third clutch drum member 4 integrally formed with the axial extension member 51, but as shown in FIG. 4 for example (FIG. 4). In No. 4, the same parts as those in FIG. 3 are designated by the same reference numerals, and detailed description thereof will be omitted.) The second hub member 34 is integrally formed with the axial extension member 51 with, for example, an aluminum alloy, and the third The bottom portion 4a of the clutch drum member 4 may be fixed to the second hub member 34 (radial extension portion 34c) so as to rotate integrally via the rivet 80. In this case, the third clutch drum member 4 can be manufactured by press-molding, for example, a steel plate, and in this way, the third clutch drum member 4 can be manufactured with higher accuracy than that of the above embodiment. You will be able to.

In the example of FIG. 4, the radial extension portion 34c of the second hub member 34 extends radially inward from the friction plate mounting portion 34b and is connected to the axial extension member 51. As a result, the rear end of the second centrifugal balance chamber forming member 39 comes into contact with the radial extension portion 34c of the second hub member 34. Further, the hydraulic oil of the second centrifugal balance chamber 38 is used as lubricating oil between the second centrifugal balance chamber forming member 39 and the radial extension portion 34c of the second hub member 34 to the friction plate 31 of the intermediate clutch 30. An oil passage (groove 39a) for guiding is provided. The hydraulic oil that has passed through the groove 39a flows radially to the friction plate mounting portion 34b along the surface of the radial extension portion 34c of the second hub member 34 by centrifugal force, and then extends radially to the friction plate mounting portion 34b. It reaches the friction plate 31 through the through hole provided as described above.

Further, in the example of FIG. 4, the third fastening hydraulic chamber 23 is arranged behind the radial extension portion 34c of the second hub member 34, and the radial extension portion 34c and the axial extension member 51 are arranged. And will be formed by the third fastening piston 22.

Further, in the example of FIG. 4, the third fastening piston 22 and the third clutch drum member 4 have a portion that overlaps in the axial direction. Therefore, through holes 22c for avoiding interference with the third clutch drum member 4 are formed at a plurality of locations in the circumferential direction of the third fastening piston 22, and between the plurality of through holes 22a in the third clutch drum member 4. Through holes (not shown) for avoiding interference with the third fastening piston 22 are formed at a plurality of locations corresponding to the above.

Further, all of the second hub member 34, the third clutch drum member 4, and the axial extension member 51 can be integrally formed of, for example, an aluminum alloy.

The above embodiments are merely examples, and the scope of the present invention should not be construed in a limited manner. The scope of the present invention is defined by the scope of claims, and all modifications and modifications belonging to the equivalent scope of the claims are within the scope of the present invention.

The present invention is useful for a clutch structure of an automatic transmission, which includes a first clutch and a second clutch arranged side by side in the axial direction of the automatic transmission.

1 Automatic transmission 4 3rd clutch drum member 5 Power transmission drum member 6 1st clutch drum member 7 2nd clutch drum member 20 Rear clutch (3rd clutch)
21 Friction plate 24 Third hub member 30 Intermediate clutch (second clutch)
31 Friction plate 32 2nd fastening piston 33 2nd fastening hydraulic chamber 34 2nd hub member 35 1st hub member 38 2nd centrifugal balance chamber 39 2nd centrifugal balance chamber forming member 39a Groove (oil passage)
40 Front clutch (1st clutch)
41 Friction plate 42 1st fastening piston 43 1st fastening hydraulic chamber 45 Power transmission member 48 1st centrifugal balance chamber 49 1st centrifugal balance chamber forming member 49a Groove (oil passage)
51 Axial extension member

Claims (7)

It is a clutch structure of an automatic transmission provided with a first clutch and a second clutch arranged side by side in the axial direction of the automatic transmission.
The first clutch has a first clutch drum member and a first hub member provided on the inner peripheral side of the first clutch drum member via a plurality of friction plates arranged in the axial direction.
The second clutch is provided via a second clutch drum member provided on the inner peripheral side of the first clutch drum member and a plurality of friction plates arranged in the axial direction on the inner peripheral side of the second clutch drum member. Has a second hub member provided in the above
An annular power transmission member provided on the opposite side of the first clutch to the second clutch in the axial direction, and
A power transmission drum member provided on the outer peripheral side of the first clutch drum member and connected to the outer peripheral side end of the power transmission member.
An axial extension member that is spline-fitted with the inner peripheral end of the power transmission member and extends along the axial direction is further provided.
The first hub member is integrally formed with the power transmission member.
The second hub member is characterized in that it is integrally formed with the axial extension member or is fixed so as to rotate integrally with the member integrally formed with the axial extension member. The clutch structure of the automatic transmission. In the clutch structure of the automatic transmission according to claim 1,
The first clutch includes a first fastening piston that advances in the axial direction so as to engage a plurality of friction plates of the first clutch, and hydraulic oil for advancing the first engaging piston in the axial direction. Further has a first fastening hydraulic chamber to which
The second clutch includes a second fastening piston that advances in the axial direction so as to engage a plurality of friction plates of the second clutch, and hydraulic oil for advancing the second engaging piston in the axial direction. Further has a second fastening hydraulic chamber to which
A clutch structure of an automatic transmission, wherein the first fastening hydraulic chamber and the second fastening hydraulic chamber are arranged radially inside the first hub member. In the clutch structure of the automatic transmission according to claim 2,
The first clutch has a first centrifugal balance chamber provided on the power transmission member side, which is opposite to the first fastening hydraulic chamber with respect to the first fastening piston, and a wall of the first centrifugal balance chamber. It further has a first centrifugal balance chamber forming member that constitutes a part of the portion and is in contact with the power transmission member.
An oil passage is provided between the power transmission member and the first centrifugal balance chamber forming member to guide the hydraulic oil of the first centrifugal balance chamber to the friction plate of the first clutch as lubricating oil. The clutch structure of the automatic transmission is characterized by this. In the clutch structure of the automatic transmission according to claim 2 or 3,
The third clutch drum member provided on the inner peripheral side of the second clutch drum member and the inner peripheral side of the third clutch drum member and on the side opposite to the first hub member of the second hub member. A third clutch having a third hub member provided via a plurality of friction plates arranged in the axial direction is further provided.
The second hub member is integrally formed with the axial extension member.
The clutch structure of an automatic transmission is characterized in that the third clutch drum member is fixed to the second hub member so as to rotate integrally. In the clutch structure of the automatic transmission according to claim 4,
The second clutch is a second centrifugal balance chamber provided on the second hub member side, which is opposite to the second fastening hydraulic chamber with respect to the second fastening piston, and the second centrifugal balance chamber. It further has a second centrifugal balance chamber forming member that constitutes a part of the wall portion and abuts on the second hub member.
An oil passage for guiding the hydraulic oil of the second centrifugal balance chamber to the friction plate of the second clutch as lubricating oil is provided between the second hub member and the second centrifugal balance chamber forming member. The clutch structure of the automatic transmission is characterized by being In the clutch structure of the automatic transmission according to claim 2 or 3,
The third clutch drum member provided on the inner peripheral side of the second clutch drum member and the inner peripheral side of the third clutch drum member and on the side opposite to the first hub member of the second hub member. A third clutch having a third hub member provided via a plurality of friction plates arranged in the axial direction is further provided.
The third clutch drum member is integrally formed with the axial extension member.
The clutch structure of an automatic transmission is characterized in that the second hub member is fixed to the third clutch drum member, which is a member integrally formed with the axial extension member, so as to rotate integrally. .. In the clutch structure of the automatic transmission according to claim 6,
The second clutch is a second centrifugal balance chamber provided on the second hub member side, which is opposite to the second fastening hydraulic chamber with respect to the second fastening piston, and the second centrifugal balance chamber. It further has a second centrifugal balance chamber forming member that constitutes a part of the wall portion and abuts on the third clutch drum member.
An oil passage is provided between the third clutch drum member and the second centrifugal balance chamber forming member to guide the hydraulic oil of the second centrifugal balance chamber to the friction plate of the second clutch as lubricating oil. The clutch structure of the automatic transmission is characterized by being

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