JP2020190301A - Automatic transmission - Google Patents

Abstract

To arrange an oil passage extending radially inside in an axial direction efficiently, in an automatic transmission which includes a brake in which a hydraulic chamber is arranged radially inside of a hub member.SOLUTION: An automatic transmission includes a brake which includes: a piston 80 for fastening a plurality of friction plates 70 arranged between a hub member 20 and a drum member 60; and a hydraulic chamber 90 provided radially inside of the hub member 20. At a side part on the opposite side from the piston 80 side of the hub member 20, a hub support member 31 is contacted. On the radially inside of the hub member 20, a hydraulic chamber component member 41 for forming the hydraulic chamber 90 is arranged. An extension part 32b of the hub support member 31 and the hydraulic chamber component member 41 are joined on a mating surface F in an axial direction. On the mating surface F, a communication oil passage 114 is provided for communicating a radial oil passage 111 provided at the hub support member 31, extending radially and opened to the mating surface F, and an axial oil passage 113 provided at the hydraulic chamber component member 41, communicating with the hydraulic chamber, and opened to the mating surface F.SELECTED DRAWING: Figure 5

Description

The present invention relates to an automatic transmission mounted on a vehicle and belongs to the technical field of an automatic transmission for a vehicle.

Conventionally, as an automatic transmission mounted on a vehicle, a fluid transmission device such as a torque converter connected to a drive source such as an engine, and a plurality of planetary gear sets (planetary gear mechanism) and a clutch connected to the fluid transmission device. Generally, a transmission mechanism having a plurality of friction fastening elements such as a brake is provided, and a plurality of friction fastening elements are selectively fastened by hydraulic control to achieve a plurality of gears having different reduction ratios. Are known.

In recent years, there has been a tendency to abolish fluid transmission devices in response to demands for avoidance of large size and weight reduction due to the increase in the number of stages of automatic transmissions. In this case, it is conceivable to realize a smooth start while avoiding an engine stall by slip-controlling at least one friction fastening element that is fastened at the first speed shift stage at the time of starting.

When slip-controlling the friction fastening element that is fastened at the 1st speed shift stage at the time of starting, the brake that does not rotate the hydraulic chamber has better controllability at the time of fastening than the clutch that rotates the hydraulic chamber. It is conceivable to slip control the brake (hereinafter referred to as "starting brake") that is engaged in the 1st speed shift stage.

In an automatic transmission configured in this way, the start brake frequently performs slip control, so it is necessary to effectively suppress heat generation of the friction plate due to slip control in order to maintain the required durability. There is.

In order to suppress the heat generation of the friction plate, it is conceivable to increase the amount of lubricating oil supplied to the friction plate to improve the cooling performance, but it is stored in the inner peripheral surface of the transmission case and in the transmission case. In a brake in which a plurality of friction plates are arranged between the outer peripheral surface of a predetermined rotating member, lubricating hydraulic oil stays near the inner peripheral surface of the transmission case and drag resistance due to viscosity between the friction plates. May increase the rotational resistance.

As a response to this, for example, in Patent Document 1, in a brake fastened at a first-speed shift stage that is slip-controlled at the time of starting, the brake is coupled to an outer peripheral surface of a hub member coupled to a transmission case and a predetermined rotating member. A plurality of friction plates are arranged between the drum member and the inner peripheral surface of the drum member.

FIG. 14 is a cross-sectional view showing a brake of a conventional automatic transmission. As shown in FIG. 14, the brake 200 is provided between the hub member 202 coupled to the transmission case 201, the drum member 204 coupled to the predetermined rotating member 203, and between the hub member 202 and the drum member 204. It has a plurality of arranged friction plates 205 and a piston 206 for fastening the plurality of friction plates 205. The hub member 202 is coupled to the transmission case 201 via a hub support member 209 that is coupled to the transmission case 201.

In the brake 200, the lubrication supply oil passage 207 extends radially inward from the transmission case 201 through the inside of the hub support member 209 and through the spline portion 210 formed on the outer peripheral surface of the hub member 202, as shown by the arrow 208. It extends from one side in the axial direction to the other side in the axial direction to supply hydraulic oil for lubrication to a plurality of friction plates 205.

The hydraulic oil for lubrication receives the centrifugal force of the friction plate 205 spline-engaged with the drum member 204, moves outward in the radial direction as shown by the arrow 211, and is supplied between the friction plates 205 for slip control. It is designed to cool the heat generated by the friction plate 205. The lubricating hydraulic oil that has moved to the inner peripheral surface of the drum member 204 is prevented from moving outward in the axial direction and staying as shown by the arrow 212 due to the rotation of the drum member 204. ..

Japanese Unexamined Patent Publication No. 2016-90048

By the way, in order to suppress the expansion of the axial dimension due to the increase in the number of stages of the automatic transmission, by arranging the fastening hydraulic chamber and the releasing hydraulic chamber inside the hub member in the radial direction, in particular, the outer circumference inside the transmission case It is considered to shorten the peripheral axial dimension to shorten the large diameter range of the transmission case.

In this case, the oil passage for supplying hydraulic oil to the fastening hydraulic chamber and the releasing hydraulic chamber arranged inside the hub member in the radial direction is such that the above-mentioned connecting member shown in FIG. 14 is radially inside the hub member. It is considered effective to form an oil channel by extending it to.

However, in order to arrange the hub support member provided with the oil passage inside the transmission case in the radial direction, a space is required in the axial direction, and the axial dimension may be expanded in order to avoid interference with peripheral parts. There is.

Therefore, according to the present invention, in an automatic transmission having a brake in which a plurality of friction plates are arranged between a hub member and a drum member and a hydraulic chamber is arranged inside the hub member in the radial direction, the automatic transmission extends inward in the radial direction. The challenge is to efficiently arrange the oil passages in the axial direction.

In order to solve the above problems, the present invention is characterized in that it is configured as follows.

First, the invention according to claim 1 of the present application
A non-rotatable hub member coupled to a transmission case, a rotatable drum member coupled to a rotating element, a plurality of friction plates arranged between the hub member and the drum member, and the plurality of friction plates. An automatic transmission having a brake having a piston for fastening a friction plate and a hydraulic chamber to which hydraulic oil for urging the piston is supplied.
The hydraulic chamber is arranged inside the hub member in the radial direction.
A hub support member that is fixed to the transmission case and supports the hub member is in contact with the side portion of the hub member on the anti-piston side.
A hydraulic chamber constituent member forming the hydraulic chamber is arranged inside the hub member in the radial direction.
The hub support member includes an extension portion that extends radially inward from the hub member.
The extension portion of the hub support member and the hydraulic chamber constituent member are connected by a mating surface in the axial direction.
The hub support member is provided with a radial oil passage that extends in the radial direction and is open to the mating surface.
The hydraulic chamber constituent member is provided with an axial oil passage that communicates with the hydraulic chamber and is open to the mating surface.
The mating surface is characterized in that it extends in the radial direction along the mating surface and is provided with a communicating oil passage for communicating the radial oil passage and the axial oil passage.

Further, the invention according to claim 2 is the invention according to claim 1.
A sealing member extending in the radial direction is mounted on the mating surface so as to surround the outer peripheral side of the communication oil passage.

Further, the invention according to claim 3 is the invention according to claim 2 or claim 3.
The hub support member is provided with an inclined oil passage that connects the radial oil passage and the communication oil passage.
The inclined oil passage is formed so as to be inclined toward the mating surface so as to be connected to the communication oil passage while facing inward in the radial direction.

The invention according to claim 4 is the invention according to claim 4.
The hydraulic chamber has a fastening hydraulic chamber to which hydraulic oil for urging the piston in the fastening direction is supplied, and a releasing hydraulic chamber to which hydraulic oil is supplied so as to urge the piston in the releasing direction. And
The hub support member is provided with a fastening hydraulic chamber, a fastening supply oil passage connected to the release hydraulic chamber, and a release supply oil passage, respectively.
The fastening supply oil passage includes the radial oil passage, the axial oil passage, the communication oil passage, and the inclined oil passage.
The release supply oil passage includes the radial oil passage, the axial oil passage, the communication oil passage, the second radial oil passage having the same configuration as the inclined oil passage, and the second Axial oil passage and the second
It is equipped with a communication oil passage and a second inclined oil passage.
The fastening supply oil passage and the release supply oil passage are characterized in that they are arranged at different positions in the circumferential direction.

The invention according to claim 5 is the invention according to claim 4.
The hydraulic chamber component member has an outer peripheral side cylindrical portion fitted to the hub member, and has a cylindrical portion.
A circumferential oil passage extending in the circumferential direction for supplying lubricating oil to the friction plate is formed in the fitting portion between the outer peripheral side cylindrical portion and the hub member.
The hub support member includes a third radial oil passage extending in the radial direction and a third axial oil passage extending in the axial direction and connecting the third radial oil passage and the circumferential oil passage. Is provided,
The third radial oil passage is characterized in that it is arranged at a different circumferential position from the first and second radial oil passages.

According to the invention according to claim 1 of the present application, a radial oil passage for supplying hydraulic oil to a hydraulic chamber arranged radially inside the hub member and an axial oil passage communicating with the hydraulic chamber are connected. By providing the communication oil passage along the mating surface between the extension portion of the hub support member and the hydraulic chamber component member, the hub support member provided with the radial oil passage is extended to the inside in the radial direction and the shaft. Compared with the case of connecting to the directional oil passage, the axial dimension inside the transmission case in the radial direction can be configured more compactly.

Specifically, for example, the communication oil passage provided in the extension portion of the hub support member is opened toward the mating surface side of the extension portion of the hub support member and the hydraulic chamber constituent member, and is a released portion. Is formed by being covered with the hydraulic chamber constituent members, so that the wall on the hydraulic chamber constituent member side of the communicating oil passage is omitted as compared with the case where the communicating oil passage is provided only in the extension portion of the hub support member. Therefore, the axial dimension of the communication oil passage can be compactly configured.

Further, according to the second aspect of the present invention, the mating surface is provided with a seal member extending in the radial direction so as to surround the outer peripheral side of the communication oil passage, thereby forming an extension portion of the hub support member and a hydraulic chamber configuration. The hydraulic oil flowing through the communication oil passage provided along the mating surface with the member can be reliably supplied to the hydraulic chamber. Therefore, the axial dimension can be effectively compacted with a simple structure.

Further, according to the invention of claim 3, the first inclined oil passage is inclined so as to connect the first radial oil passage and the first communicating oil passage while facing inward in the radial direction. Therefore, for example, when the first radial oil passage and the first communication oil passage are offset in the axial direction, the first inclined oil passage is not inclined as compared with the case where the first inclined oil passage is not inclined. Axial space efficiency can be improved.

Further, according to the invention of claim 4, the fastening supply oil passage and the release supply oil passage are the radial oil passage and the second radial oil passage, and the axial oil passage and the second shaft. It is provided with a directional oil passage, a communication passage, a second communication oil passage, an inclined oil passage and a second inclined oil passage, and the fastening supply passage and the release supply oil passage are located at different positions in the circumferential direction. Due to the arrangement, the axial dimension can be made compact even in a configuration including a fastening supply oil passage and a release supply oil passage.

Further, according to the invention of claim 5, the third radial oil passage constituting the lubrication supply oil passage for friction plate lubrication is circumferential to the fastening supply oil passage and the release supply oil passage. Since the hub support members are arranged at different positions, the axial dimensions can be made compact even in a configuration in which the hub support member is provided with a supply oil passage for fastening, a supply oil passage for release, and a supply oil passage for lubrication. ..

It is a skeleton diagram of the automatic transmission which concerns on embodiment of this invention. It is a fastening table of friction fastening elements of an automatic transmission. It is sectional drawing of the brake of an automatic transmission and its periphery. It is another cross-sectional view of the brake of an automatic transmission and its periphery. It is still another sectional view of the brake of an automatic transmission and its periphery. It is still another sectional view of the brake of an automatic transmission and its periphery. It is a perspective view which shows the assembled state of a hub member of a brake and a piston. It is a perspective view which shows the assembled state of the hub member of the brake, the hub support member, and the 1st hydraulic chamber constituent member. It is a perspective view which shows the assembled state of the hub member and the hub support member of a brake. It is a perspective view which shows the hub member. It is a perspective view which shows the hub support member. It is another perspective view which shows the assembled state of a hub member of a brake and a piston. It is a perspective view which shows the 1st hydraulic chamber component. It is sectional drawing which shows the brake of the conventional automatic transmission.

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

FIG. 1 is an outline diagram of an automatic transmission according to an embodiment of the present invention. The automatic transmission 10 is connected to a drive source such as an engine without a fluid transmission device such as a torque converter. The automatic transmission 10 is arranged in a transmission case 11 with an input shaft 12 connected to a drive source and arranged on the drive source side (left side in the figure) and on the opposite drive source side (right side in the figure). It has an output shaft 13. The automatic transmission 10 is a vertically installed type for front engine / rear drive vehicles, etc., in which the input shaft 12 and the output shaft 13 are arranged on the same axis.

On the axis of the input shaft 12 and the output shaft 13, from the drive source side, the first, second, third, and fourth planetary gear sets (hereinafter, simply "first, second, third, and fourth gear sets"". PG1, PG2, PG3, PG4 are arranged.

In the transmission case 11, the first clutch CL1 is arranged on the drive source side of the first gear set PG1, the second clutch CL2 is arranged on the drive source side of the first clutch CL1, and the drive source of the second clutch CL2. A third clutch CL3 is arranged on the side. Further, the first brake BR1 is arranged on the drive source side of the third clutch CL3, and the second brake BR2 is arranged on the drive source side of the third gear set PG3 and on the anti-drive source side of the second gear set PG2.

The first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 are all single pinion types in which the pinion supported by the carrier directly meshes with the sun gear and the ring gear. The first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 have sun gears S1, S2, S3, S4, ring gears R1, R2, R3, R4, and carriers C1, C2, respectively, as rotating elements. , C3, and C4.

The first gear set PG1 is a double sun gear type in which the sun gear S1 is divided into two in the axial direction. The sun gear S1 has a first sun gear S1a arranged on the drive source side and a second sun gear S1b arranged on the opposite drive source side. The first and second sun gears S1a and S1b have the same number of teeth and mesh with the same pinion supported by the carrier C1. As a result, the first and second sun gears S1a and S1b always rotate in the same rotation.

In the automatic transmission 10, the sun gear S1 of the first gear set PG1, specifically, the second sun gear S1b and the sun gear S4 of the fourth gear set PG4 are always connected, and the ring gear R1 of the first gear set PG1 and the sun gear of the second gear set PG2 are always connected. S2 is always connected, the carrier C2 of the second gear set PG2 and the carrier C4 of the fourth gear set PG4 are always connected, and the carrier C3 of the third gear set PG3 and the ring gear R4 of the fourth gear set PG4 are always connected. ..

The input shaft 12 is always connected to the carrier C1 of the first gear set PG1 through between the first sun gear S1a and the second sun gear S1b, and the output shaft 13 is always connected to the carrier C4 of the fourth gear set PG4.

The first clutch CL1 is disposed between the input shaft 12 and the carrier C1 of the first gear set PG1 and the sun gear S3 of the third gear set PG3 so as to connect and disconnect the first clutch CL1. It is arranged between the ring gear R1 of the first gear set PG1 and the sun gear S2 of the second gear set PG2 and the sun gear S3 of the third gear set PG3 so as to connect and disconnect them. The third clutch CL3 is the second gear set. It is arranged between the ring gear R2 of the PG2 and the sun gear S3 of the third gear set PG3 so as to connect and disconnect them.

The first brake BR1 is disposed between the transmission case 11 and the sun gear S1 of the first gear set PG1, specifically, the first sun gear S1a so as to connect and disconnect the first brake BR1. Is disposed between the transmission case 11 and the ring gear R3 of the third gear set PG3 so as to connect and disconnect them.

With the above configuration, the automatic transmission 10 has D as shown in FIG. 2 by combining the engaged states of the first clutch CL1, the second clutch CL2, the third clutch CL3, the first brake BR1, and the second brake BR2. The 1st to 8th speeds in the range and the backward speeds in the R range are formed.

In the automatic transmission 10, the second brake BR2, which is fastened at the first speed shift stage at the time of starting, is slip-controlled, and the second brake BR2 corresponds to the friction fastening element of the automatic transmission according to the present invention. Hereinafter, the brake BR2 will be described.

3 is a cross-sectional view of the automatic transmission brake and its surroundings, FIG. 4 is another cross-sectional view of the automatic transmission brake and its surroundings, and FIGS. 5 and 6 are the automatic transmission brake and its surroundings, respectively. It is still another sectional view of. FIG. 3 shows a cross section of the automatic transmission brake and its surroundings corresponding to a cross section along the Y3-Y3 line of FIG. 7, and FIGS. 4, 5, and 6 show the Y4-Y4 line of FIG. 12, respectively. The cross section of the brake of the automatic transmission corresponding to the cross section along the Y5-Y5 line and the Y6-Y6 line and its surroundings is shown.

As shown in FIGS. 3 to 6, the brake BR2 is housed in a transmission case 11 formed in a substantially cylindrical shape, and is connected to the sun gear S3 of the third gear set PG3 to form the first, second, and third clutches. One of a pair of internal and external rotating members of CL1, CL2, and CL3 is arranged on the outer peripheral side of the integrated power transmission member 14.

The power transmission member 14 is arranged on the outer peripheral side of the power transmission member 15 that connects the carrier C2 of the second gear set PG2 and the carrier C4 of the fourth gear set PG4, and the power transmission member 15 is the sun gear S1 of the first gear set PG1. Specifically, it is arranged on the outer peripheral side of the power transmission member 16 that connects the second sun gear S1b and the sun gear S4 of the fourth gear set PG4.

The brake BR2 includes a hub member 20 coupled to the transmission case 11, a drum member 60 arranged on the opposite drive source side of the hub member 20 and coupled to the ring gear R3 of the third gear set PG3, and the hub member 20 and the drum. It has a plurality of friction plates 70 arranged side by side in the axial direction with the member 60, and a piston 80 arranged on the anti-drive source side of the plurality of friction plates 70 to fasten the plurality of friction plates 70. ..

The brake BR2 has a hydraulic chamber 90 to which hydraulic oil for urging the piston 80 is supplied inside the hub member 20 in the radial direction. The hydraulic chamber 90 includes a fastening hydraulic chamber 91 to which the fastening hydraulic oil for urging the piston 80 in the fastening direction is supplied and a releasing hydraulic chamber to which the releasing hydraulic oil for urging the piston 80 in the releasing direction is supplied. It is equipped with 92.

As shown in FIG. 3, the brake BR2 also includes a spring 101 that applies an urging force to the piston 80 in the fastening direction as an urging member that urges the piston 80 inside the hub member 20 in the radial direction.

The hub member 20 has a vertical wall portion 22 extending in a direction orthogonal to the axial direction of the transmission case 11 and formed in a substantially disk shape, and a vertical wall portion 22 inside the vertical wall portion 22 in the direction opposite to the drive source side. It is provided with a cylindrical portion 23 extending substantially in a cylindrical shape.

The hub member 20 has a spline portion 24 having a spline formed on the outer peripheral surface of the vertical wall portion 22, and the spline portion 24 engages with the spline portion 11a having a spline formed on the inner peripheral surface of the transmission case 11. It is coupled to the transmission case 11.

The cylindrical portion 23 of the hub member 20 has a spline portion 25 having a spline formed on the outer peripheral surface thereof, and the fixed side friction plate 71 constituting the friction plate 70 is spline-engaged with the spline portion 25.

As shown in FIG. 10, the spline portion 25 has a first tooth portion 26 having a predetermined axial length in which the spline portion 25 splines engages with the plurality of friction plates 70 even when the plurality of friction plates 70 are released. The tooth portion 27 is formed to have a shorter axial length than the first tooth portion 26 and is spline-engaged with the plurality of friction plates 70. A plurality of, specifically, three first tooth portions 26 are arranged on the hub member 20 at substantially equal intervals in the circumferential direction.

The hub support member 31 includes a vertical wall portion 32 extending in a direction orthogonal to the axial direction of the transmission case 11 and formed in a substantially disk shape. As shown in FIG. 4, a lubrication supply oil passage L1 for supplying lubricating hydraulic oil to the friction plate 70 is formed in the vertical wall portion 32 of the hub support member 31.

In the hub support member 31, the outer peripheral surface of the vertical wall portion 32 is fitted to the inner peripheral surface 11b of the transmission case 11 on the drive source side of the spline portion 24 of the hub member 20. The hub support member 31 is prevented from coming off to the drive source side by the snap ring 17, is fixed to the transmission case 11 by using the detent pin 18, and is coupled to the transmission case 11. The hub support member 31 may be fitted and fixed to the inner peripheral surface 11b of the transmission case 11 by press fitting, and may be coupled to the transmission case 11.

As shown in FIG. 4, a valve body 5 for supplying hydraulic oil to the hydraulic chamber 90 and the friction plate 70 of the brake BR2 is arranged below the transmission case 11. The valve body 5 is housed in an oil pan (not shown) attached below the transmission case 11 and fixed to the transmission case 11. The hub support member 31 has a valve body connecting portion 34 for connecting to the valve body 5, and the lubrication supply oil passage L1 is connected to the valve body 5 through the case opening 11c formed in the transmission case 11. It is formed like this.

As shown in FIG. 5, a fastening supply oil passage L2 for supplying the fastening hydraulic oil to the fastening hydraulic chamber 91 is formed in the vertical wall portion 32 of the hub support member 31, and as shown in FIG. , A release supply oil passage L3 for supplying release hydraulic oil to the release hydraulic chamber 92 is formed.

As shown in FIG. 11, the lubrication supply oil passage L1, the release supply oil passage L3, and the fastening supply oil passage L2 are arranged side by side in the circumferential direction on the lower side of the transmission case 11, and the hub support member 31 , Lubrication supply oil passage L1, release supply oil passage L3, and fastening supply oil passage L2 are formed so as to be connected to the valve body 5, respectively.

As shown in FIG. 3, the vertical wall portion 32 of the hub support member 31 is formed with a stepped portion 32a recessed on the drive source side on the anti-drive source side. The stepped portion 32a of the hub support member 31 engages with the inner peripheral side of the vertical wall portion 22 of the hub member 20 when the vertical wall portion 22 of the hub member 20 comes into contact with the vertical wall portion 32 of the hub support member 31. It is formed like this.

The vertical wall portion 32 of the hub support member 31 is provided with an extension portion 32b extending to the inside in the radial direction of the hub member 20. The vertical wall portion 32 (extension portion 32b) of the hub support member 31 is formed with a plurality of boss portions 35 extending substantially in a columnar shape on the anti-drive source side on the inner peripheral side. As shown in FIGS. 9 and 11, the plurality of boss portions 35 are dispersedly arranged in the circumferential direction, and each of the boss portions 35 is formed with screw holes 35a on the counter-drive source side. By screwing the fastening bolt B1 into the screw hole 35a of the boss portion 35 from the anti-drive source side of the second hydraulic chamber component 51, the first hydraulic chamber component 41 and the second hydraulic chamber component 41 and the second are on the anti-drive source side of the hub support member 31. The hydraulic chamber component 51 is connected.

As shown in FIG. 3, the first hydraulic chamber component 41 has a vertical wall portion 42 extending in a direction orthogonal to the axial direction of the transmission case 11 and formed in a substantially disk shape, and a radial direction of the vertical wall portion 42. A first cylindrical portion 43 as an outer peripheral side cylindrical portion extending substantially cylindrically from the outside to the anti-drive source side, and a second cylindrical portion 44 extending substantially cylindrically from the radial inside of the vertical wall portion 42 toward the anti-drive source side. The first cylindrical portion 43 and the second cylindrical portion 44 are formed so as to have substantially equal axial lengths.

The surface of the vertical wall portion 42 of the first hydraulic chamber constituent member 41 on the drive source side is in contact with the surface of the extension portion 32b of the hub support member 31 on the opposite drive source side with an axial mating surface F.

The first cylindrical portion 43 of the first hydraulic chamber constituent member 41 is provided inside the cylindrical portion 23 of the hub member 20 in the radial direction. The first cylindrical portion 43 of the first hydraulic chamber component 41 includes a flange portion 43a extending radially outward so as to fit on the inner peripheral surface of the cylindrical portion 23 of the hub member 20 on the anti-drive source side, and the hub member. It is provided so as to form a lubrication supply oil passage L1 with the cylindrical portion 23 of 20.

The second cylindrical portion 44 of the first hydraulic chamber component 41 has an outer peripheral surface 44a on the drive source side and an outer peripheral surface 44b on the anti-drive source side, and the outer peripheral surface 44b on the anti-drive source side is a release hydraulic chamber. The radial dimension is smaller than the outer peripheral surface 44a on the drive source side so as to form 92.

As shown in FIGS. 3, 8 and 13, the second cylindrical portion 44 of the first hydraulic chamber component 41 is also recessed from the drive source side to the anti-drive source side in a substantially rectangular shape, and the hub support member 31 A plurality of boss portion accommodating portions 45 for accommodating the plurality of boss portions 35, and a bolt insertion hole 44c for inserting the fastening bolt B1 are formed.

The second hydraulic chamber constituent member 51 extends in a direction orthogonal to the axial direction of the transmission case 11 and is formed in a substantially disk shape, and is arranged on the opposite drive source side of the first hydraulic chamber constituent member 41. A bolt insertion hole 52 through which the fastening bolt B1 is inserted is formed inside the second hydraulic chamber component 51 in the radial direction.

As described above, the fastening bolt B1 is supported by the hub from the anti-drive source side of the second hydraulic chamber component 51 through the bolt insertion hole 52 of the second hydraulic chamber component 51 and the bolt insertion hole 44c of the first hydraulic chamber component 41. By screwing into the screw hole 35a of the member 31, the first hydraulic chamber component 41 is coupled to the anti-drive source side of the hub support member 31, and the second hydraulic chamber component 41 is connected to the anti-drive source side of the first hydraulic chamber component 41. The hydraulic chamber component 51 is connected.

The second hydraulic chamber component 51 is formed so as to extend radially outward from the second cylindrical portion 44 of the first hydraulic chamber component 41, and the outer peripheral surface of the second hydraulic chamber component 51 passes through the seal member 53. It is fitted to the piston 80.

The facing surface (plane on the drive source side) 54 of the second hydraulic chamber component 51 facing the hydraulic chamber forming portion 82 of the piston 80, which will be described later, is provided with a step portion recessed on the opposite drive source side. A shim member 55 is arranged on the facing surface 54 of the second hydraulic chamber component 51 facing the piston 80, and a radial inner end portion of the shim member 55 is arranged in a step portion.

The shim member 55 is brought into contact with a plurality of springs 101 and a plurality of stoppers 86 of the piston 80, which will be described later. The shim member 55 regulates the piston 80 to a predetermined release position when the stopper portion 86 of the piston 80 comes into contact with the side surface of the shim member 55 on the drive source side. In this way, the shim member 55 that constitutes the regulation member that regulates the piston 80 to the release position is attached to the second hydraulic chamber component 51.

The hub support member 31, the hub member 20, the first hydraulic chamber constituent member 41, and the second hydraulic chamber constituent member 51 are each formed of an aluminum-based material and are made of the same material.

The drum member 60 includes a cylindrical portion 61 which is arranged so as to face the outer peripheral side of the cylindrical portion 23 of the hub member 20 and extends in the axial direction in a substantially cylindrical shape, and a transmission case 11 radially inward from the anti-drive source side of the cylindrical portion 61. It is provided with a vertical wall portion 62 extending in a direction orthogonal to the axial direction of the above and formed in a substantially disk shape.

The vertical wall portion 62 of the drum member 60 is coupled to the ring gear R3 as a rotating member. The cylindrical portion 61 of the drum member 60 has a spline portion 61a having a spline formed on its inner peripheral surface, and the rotating side friction plate 72 constituting the friction plate 70 is spline-engaged with the spline portion 61a. The fixed side friction plate 71 and the rotating side friction plate 72 are alternately arranged in the axial direction.

The piston 80 is arranged between the hub member 20 and the drum member 60, specifically between the cylindrical portion 23 of the hub member 20 and the cylindrical portion 61 of the drum member 60, and is arranged in the first hydraulic chamber constituent member 41. It is slidably fitted to the outer peripheral surface of the second cylindrical portion 44. The piston 80 is prevented from coming off toward the anti-drive source side by the second hydraulic chamber component 51.

The piston 80 is formed in an annular shape, and as shown in FIG. 4, a pressing portion 81 provided on the outer peripheral side to press the friction plate 70 and a hydraulic chamber forming portion provided on the inner peripheral side to form the hydraulic chamber 90. It includes a connecting portion 83 that connects the pressing portion 81 and the hydraulic chamber forming portion 82, and a plurality of stopper portions 86 ... 86 that regulate the release position of the piston 80.

The pressing portion 81 of the piston 80 is arranged on the opposite drive source side of the friction plate 70, the hydraulic chamber forming portion 82 is arranged inside the hub member 20 in the radial direction, and the connecting portion 83 forms the pressing portion 81 and the hydraulic chamber. It extends inward in the radial direction of the friction plate 70 from the anti-drive source side of the friction plate 70 so as to connect with the portion 82.

The hydraulic chamber forming portion 82 of the piston 80 is formed by one of the fastening hydraulic chambers 91 by means of a counter-drive source side surface (a surface on the second hydraulic chamber component 51 side) 84 extending in the radial direction inside the hub member 20 in the radial direction. It constitutes a part. A step portion 85 that is recessed from the inner diameter side to the outer diameter side is provided on the inner peripheral portion of the hydraulic chamber forming portion 82, and the step portion 85 and the inner cylindrical portion 44 of the first hydraulic chamber constituent member 41 are provided. The release hydraulic chamber 92 is partitioned by.

The piston 80 extends radially inward from the anti-drive source side of the friction plate 70 and is fitted to the outer peripheral surface of the second hydraulic chamber component 51, and the drive source side of the second hydraulic chamber component 51 is radially inward. It extends inward and is fitted to the outer peripheral surfaces 44a and 44b of the second cylindrical portion 44 of the first hydraulic chamber component 41. A seal member 87 that seals between the hydraulic chamber forming portion 82 and the first hydraulic chamber constituent member 41 is mounted on the end portion of the piston 80 on the opposite drive source side in the radial direction of the hydraulic chamber forming portion 82. .. A seal member 88 that seals between the hydraulic chamber forming portion 82 and the first hydraulic chamber constituent member 41 is mounted on the end portion of the piston 80 on the drive source side in the radial direction of the hydraulic chamber forming portion 82. ..

In this way, the fastening hydraulic chamber 91 is a space portion defined by the surface 84 on the opposite drive source side of the hydraulic chamber forming portion 82 of the piston 80, the first hydraulic chamber constituent member 41, and the second hydraulic chamber constituent member 51. Is formed by. The release hydraulic chamber 92 is formed by a step portion 85 of the hydraulic chamber forming portion 82 of the piston 80 and a space portion partitioned by the first hydraulic chamber constituent member 41.

As shown in FIG. 3, the plurality of stopper portions 86 are arranged in the fastening hydraulic chamber 91. Each stopper portion 86 is formed in a columnar shape. The stopper portion 86 is formed so as to extend from the surface of the hydraulic chamber forming portion 82 of the piston 80 on the opposite drive source side to the piston facing surface side of the second hydraulic chamber constituent member 51. Each stopper portion 86 is configured to regulate the release position of the piston 80 by abutting with the shim member 55 of the second hydraulic chamber component 51 in the released state of the piston 80.

As shown in FIG. 5, the spring 101 is arranged in the fastening hydraulic chamber 91. In the hydraulic chamber forming portion 82 of the piston 80 forming the fastening hydraulic chamber 91, the surface 84 on the anti-drive source side receives the urging force by the spring 101. The end portion of the spring 101 on the opposite side of the piston is arranged so as to abut the shim member 55 arranged on the surface 54 of the second hydraulic chamber component 51 facing the piston 80. The spring 101, the fastening hydraulic chamber 91, and the releasing hydraulic chamber 92 are arranged at positions that overlap in the radial direction inside the hub member 20 in the radial direction.

A plurality of springs 101 composed of coil springs extending in the axial direction are held at ends on the drive source side by a holding plate 102 formed in an annular shape. The holding plate 102 is provided with a plurality of spring guide portions 103 that project cylindrically toward the anti-drive source side and on which a plurality of springs 101 are mounted, respectively, at a position where the plurality of springs 101 overlap in the radial direction and in the circumferential direction. Are placed in different positions. Each stopper portion 86 of the piston 80 is inserted into each spring 101 from the drive source side.

By adjusting the thickness of the shim member 55, the piston 80 can maintain the gap between the pressing surface of the pressing portion 81 of the piston 80 and the friction plate 70 at the release position at a predetermined value. At this time, since the stopper portion 86 and the spring 101 are provided in parallel between the piston 80 and the shim member 55, changing the thickness of the shim member 55 affects the compressed state of the spring 101 in the released state. Giving can be suppressed.

The spring 101 is supported by the anti-drive source side of the hydraulic chamber forming portion 82 of the piston 80 via the holding plate 102, and the anti-drive source side of the spring 101 is a shim member on the drive source side of the second hydraulic chamber constituent member 51. It is supported via 55. The spring 101 is set so that the piston 80 is in the zero clearance position when the spring 101 has a free length.

In this way, the spring 101 exerts an urging force on the piston 80 from the release position to the zero clearance position in the fastening direction. Then, when the fastening hydraulic pressure is supplied to the fastening hydraulic chamber 91 when the piston 80 is in the zero clearance position, the piston 80 presses the plurality of friction plates 70, and the plurality of friction plates 70 form the vertical wall portion of the hub member 20. It is sandwiched between the 22 and the piston 80, and is in a fastening state in which relative rotation becomes impossible.

On the other hand, when the piston 80 is in the fastening position, when the fastening hydraulic pressure is discharged from the fastening hydraulic chamber 91 and the releasing hydraulic pressure is supplied to the releasing hydraulic chamber 92, the piston 80 is urged and moved in the releasing direction. , The piston 80 is moved to the zero clearance position. The piston 80 is further urged and moved in the release direction against the spring 101 and moved to the release position.

In the automatic transmission 10, as shown in FIG. 3, a cutout portion 83b for the hub member is formed in the connecting portion 83 of the piston 80 so as to correspond to the spline portion 25 of the cylindrical portion 23 of the hub member 20. .. The anti-drive source side of the spline portion 25 of the cylindrical portion 23 of the hub member 20 is fitted into the notch portion 83b for the hub member of the piston 80, and the hub member 20 and the piston 80 are arranged so as to overlap in the axial direction. ing.

As shown in FIG. 7, the piston 80 is formed with notches 83b for hub members at substantially equal intervals in the circumferential direction corresponding to a plurality of hub members 20, specifically, three first spline teeth 26. Has been done.

In the hub member 20, when the piston 80 rotates in the circumferential direction, the side surface 83c of the notch portion 83b for the hub member comes into contact with the side surface of the first spline tooth 26 of the hub member 20, and the piston 80 reaches a predetermined amount or more, for example, the piston. The rotation of the 80 is restricted from rotating by a predetermined amount or more so that the rotation angle is 1 degree.

As shown in FIG. 11, the hub support member 31 is formed with two bolt insertion holes 32c in the vicinity of the fastening supply oil passage L2 and the release supply oil passage L3. As shown in FIG. 13, a screw hole 41a is formed in the first hydraulic chamber component 41 corresponding to the bolt insertion hole 32c of the hub support member 31.

As shown in FIG. 12, the first hydraulic chamber component 41 has a screw hole 41a of the first hydraulic chamber component 41 through a fastening bolt B2 from the drive source side of the hub support member 31 through a bolt insertion hole 32c of the hub support member 31. It is connected to the hub support member 31 by being screwed into. As shown in FIG. 13, the first hydraulic chamber constituent member 41 has a fastening supply oil passage L2 and a release supply oil passage L3 between the hub support member 31 and the first hydraulic chamber constituent member 41 on the drive source side. A seal member 47 that seals the periphery of the vehicle is attached.

Next, a supply oil passage for supplying hydraulic oil to the brake BR2 will be described.
The lubrication supply oil passage L1 for supplying the lubricating hydraulic oil to the friction plate 70 is formed in the hub member 20, the hub support member 31, and the first hydraulic chamber constituent member 41. The fastening supply oil passage L2 for supplying the fastening hydraulic oil to the fastening hydraulic chamber 91 is formed in the hub support member 31, the first hydraulic chamber constituent member 41, and the second hydraulic chamber constituent member 51. The release supply oil passage L3 for supplying the release hydraulic oil to the release hydraulic chamber 92 is formed in the hub support member 31 and the first hydraulic chamber constituent member 41.

As shown in FIGS. 3 and 4, the lubrication supply oil passage L1 includes a radial oil passage 131 provided in the vertical wall portion 32 of the hub support member 31 and extending in the radial direction, and the radial oil of the hub support member 31. A circumferential oil passage 132 connected to the passage 131 and provided in an annular shape in the circumferential direction at a fitting portion X between the cylindrical portion 23 of the hub member 20 and the cylindrical portion 43 of the first hydraulic chamber component 41, and a radial oil passage. The 131 and the circumferential oil passage 132 are connected, and the axial oil passage 133 as a third axial oil passage extending in the axial direction and the circumferential oil passage 132 provided in the cylindrical portion 23 of the hub member 20 are provided. It is configured to be connected and provided with a supply port 134 that opens to the outer peripheral surface of the cylindrical portion 23 of the hub member 20 to supply lubricating oil to the friction plate 70.

In the present embodiment, the circumferential oil passage 132 is a fitting portion X between the outer peripheral surface of the cylindrical portion 43 of the first hydraulic chamber component 41 and the inner peripheral surface of the cylindrical portion 23 of the hub member 20. In the first hydraulic chamber component 41, the outer peripheral surface of the cylindrical portion 43 is recessed inward in the radial direction, but the inner peripheral surface of the cylindrical portion 23 of the hub member 20 is recessed in the radial direction. It may be formed by recessing both the outer peripheral surface of the cylindrical portion 43 of the first hydraulic chamber constituent member 41 and the inner peripheral surface of the cylindrical portion 23 of the hub member 20.

As shown in FIG. 10, a plurality of supply ports 134 are provided side by side in the axial direction of the cylindrical portion 23 of the hub member 20, and a plurality of supply ports 134 are provided apart from each other in the circumferential direction of the cylindrical portion 23 of the hub member 20. The supply port 134 is provided so as to open to the tip of each first spline tooth 26 of the spline portion 25 of the cylindrical portion 23 of the hub member 20.

A groove extending in the axial direction is formed at the tip of the first spline tooth 26 provided with the supply port 134 at the center position in the circumferential direction, and the supply port 134 is formed on the bottom surface of the groove of the groove. .. As a result, the distance between each friction plate 70 engaged with the spline portion 25 and the supply port 134 is increased as compared with the case where the groove portion is not provided at the tip of the first spline tooth 26. Unintended movement of the friction plate due to the supply of oil can be suppressed.

The hub support member 31 is formed so that the lubrication supply oil passage L1 is connected to the valve body 5. The radial oil passage 131 of the hub support member 31 is provided on the vertical wall portion 32 of the hub support member 31 and opens on the lower surface of the valve body connection portion 34 to be connected to the valve body 5. The valve body 5 is capable of supplying lubricating hydraulic oil to a plurality of friction plates 70 through the lubricating supply oil passage L1.

As shown in FIG. 5, the fastening supply oil passage L2 is provided on the vertical wall portion 32 of the hub support member 31, and is provided on the mating surface F between the extension portion 32b of the hub support member 31 and the first hydraulic chamber constituent member 41. The radial oil passage 111 which is opened and extends in the radial direction and the second cylindrical portion 44 of the first hydraulic chamber constituent member 41 are provided and opened to the mating surface F and extend in the axial direction, and the second hydraulic chamber constituent member. It is configured to include an axial oil passage 113 provided in 51 and opened and connected to the fastening hydraulic chamber 91 via a radial oil passage 112 extending in the radial direction.

The fastening supply oil passage L2 is provided on the mating surface F and extends in the radial direction along the mating surface F, and the communicating oil passage 114 for communicating the radial oil passage 111 and the axial oil passage 113. And an inclined oil passage 115 provided in the hub support member 31 and connecting the radial oil passage 111 and the communicating oil passage 114. The inclined oil passage 115 is formed so as to be inclined toward the mating surface F so as to be connected to the communication oil passage 114 while facing inward in the radial direction.

As described above, the communication oil passage 114 and the inclined oil passage 115 are formed on the mating surface F between the surface of the extension portion 32b of the hub support member 31 on the anti-drive source side and the vertical wall portion 42 of the first hydraulic chamber component 41. A seal member 47 extending in the radial direction is attached so as to surround the outer peripheral side of the.

In the present embodiment, the communication oil passage 114 is a hub at a mating surface F between the surface of the extension portion 32b of the hub support member 31 on the anti-drive source side and the vertical wall portion 42 of the first hydraulic chamber constituent member 41. The surface of the extension portion 32b of the support member 31 on the anti-drive source side is recessed on the drive source side, but the vertical wall portion 42 of the first hydraulic chamber component 41 is recessed on the anti-drive source side. It may be formed by recessing both the surface of the extension portion 32b of the hub support member 31 on the anti-drive source side and the vertical wall portion 42 of the first hydraulic chamber constituent member 41.

The opposite drive source side of the communication oil passage 114 and the inclined oil passage 115 of the hub support member 31 is formed by being covered with the first hydraulic chamber constituent member 41, and the radial oil passage 112 of the second hydraulic chamber constituent member 51 is formed. It is formed by being covered with a first hydraulic chamber component 41.

The hub support member 31 is formed so that the fastening supply oil passage L2 is connected to the valve body 5. The radial oil passage 111 of the hub support member 31 is provided in the vertical wall portion 32 of the hub support member 31 and opens on the lower surface of the valve body connection portion 34 to be connected to the valve body 5. The valve body 5 is capable of supplying the fastening hydraulic oil to the fastening hydraulic chamber 91 through the fastening supply oil passage L2 to supply a predetermined fastening hydraulic pressure.

As shown in FIG. 6, the release supply oil passage L3 is provided on the vertical wall portion 32 of the hub support member 31, and is provided on the mating surface F between the extension portion 32b of the hub support member 31 and the first hydraulic chamber constituent member 41. A radial oil passage 111 that is opened and extends in the radial direction, and a radial oil passage 111 that is provided in the second cylindrical portion 44 of the first hydraulic chamber component 41 and is opened to the mating surface F to extend in the axial direction and open to the release hydraulic chamber 92. It is configured to include an axial oil passage 122 connected to the engine.

The release supply oil passage L3 is provided on the mating surface F, extends in the radial direction along the mating surface F, and is a communication oil passage 123 for communicating the radial oil passage 121 and the axial oil passage 122. And an inclined oil passage 124 provided in the hub support member 31 and connecting the radial oil passage 121 and the communicating oil passage 123. The inclined oil passage 124 is formed so as to be inclined toward the mating surface F so as to be connected to the communication oil passage 123 while facing inward in the radial direction.

As described above, the communication oil passage 123 and the inclined oil passage 124 are provided on the mating surface F between the surface of the extension portion 32b of the hub support member 31 on the anti-drive source side and the vertical wall portion 42 of the first hydraulic chamber component 41. A seal member 47 extending in the radial direction is attached so as to surround the outer peripheral side of the.

In the present embodiment, the communication oil passage 123 is a hub at a mating surface F between the surface of the extension portion 32b of the hub support member 31 on the anti-drive source side and the vertical wall portion 42 of the first hydraulic chamber constituent member 41. The surface of the extension portion 32b of the support member 31 on the anti-drive source side is recessed on the drive source side, but the vertical wall portion 42 of the first hydraulic chamber component 41 is recessed on the anti-drive source side. It may be formed by recessing both the surface of the extension portion 32b of the hub support member 31 on the anti-drive source side and the vertical wall portion 42 of the first hydraulic chamber constituent member 41.

The opposite drive source side of the communication oil passage 123 and the inclined oil passage 124 of the hub support member 31 is covered with the first hydraulic chamber constituent member 41.

The hub support member 31 is formed so that the release supply oil passage L3 is connected to the valve body 5. The radial oil passage 121 of the hub support member 31 is provided in the vertical wall portion 32 of the hub support member 310 and opens on the lower surface of the valve body connection portion 34 to be connected to the valve body 5. The valve body 5 is capable of supplying the release hydraulic oil to the release hydraulic chamber 92 through the release supply oil passage L3 to supply a predetermined release hydraulic pressure.

In the automatic transmission 10, as shown in FIG. 11, the radial oil passages 111, 121, and 131 constituting the fastening supply oil passage L2, the release supply oil passage L3, and the lubrication supply oil passage L1, respectively, are arranged in the circumferential direction. They are arranged side by side. As shown in FIG. 12, the circumferential oil passage 132 constituting the lubrication supply oil passage L1 is connected to the radial oil passage 131 and extends in the circumferential direction in an annular shape.

According to the brake BR2 configured in this way, the radial oil passages 111 and 121 for supplying hydraulic oil to the hydraulic chamber 90 arranged inside the hub member 20 in the radial direction communicate with the hydraulic chamber 90. The communication oil passages 114 and 123 connecting the axial oil passages 113 and 122 are provided along the mating surface F between the extension portion 32b of the hub support member 31 and the first hydraulic chamber constituent member 41. The axial dimension of the transmission case 11 on the inner side of the transmission case 11 as compared with the case where the hub support member 31 provided with the radial oil passages 111 and 121 is extended to the inner side in the radial direction and connected to the axial oil passages 113 and 122. Can be configured compactly.

The communication oil passages 114 and 123 provided in the extension portion 32b of the hub support member 31 are opened and extended toward the mating surface F side of the extension portion 32b of the hub support member 31 and the first hydraulic chamber constituent member 41. Since the surface of the portion 32b on the opposite drive source side is covered with the first hydraulic chamber constituent member 41, the communication oil passages 114 and 123 are provided only in the extension portion 32b of the hub support member 31. Therefore, the wall of the communication oil passages 114 and 123 on the first hydraulic chamber component 41 side can be omitted, and the axial dimensions of the communication oil passages 114 and 123 can be compactly configured.

Further, seal members 47, 47 extending in the radial direction so as to surround the outer peripheral side of the communication oil passages 114, 123 are mounted on the mating surface F of the extension portion 32b of the hub support member 31 and the first hydraulic chamber constituent member 41. Therefore, the hydraulic oil in the communication oil passages 114 and 123 provided along the mating surface F between the extension portion 32b of the hub support member 31 and the first hydraulic chamber component 41 is reliably supplied to the hydraulic chamber 90. can do. Therefore, the axial dimension can be effectively compacted with a simple structure.

Further, the inclined oil passages 115 and 124 are formed so as to be inclined so as to connect the radial oil passages 111 and 121 and the communicating oil passages 114 and 123 while facing inward in the radial direction. When the directional oil passages 111 and 121 and the communicating oil passages 114 and 123 are offset in the axial direction, the space efficiency in the axial direction can be improved as compared with the case where the inclined oil passages 115 and 124 are not inclined. ..

Further, the radial oil passages 111 and 121 provided in the fastening supply oil passage L2 and the release supply oil passage L3, the axial oil passages 113 and 122, the communication oil passages 114 and 123, and the inclined oil passage 115. Since the 124s are arranged at different positions in the circumferential direction, the axial dimensions can be made compact even in a configuration including the fastening supply oil passage L2 and the release supply oil passage L3.

Further, since the radial oil passage 131 constituting the lubrication supply oil passage L1 for friction plate lubrication is arranged at a different circumferential position from the fastening supply oil passage L2 and the release supply oil passage L3. Even in a configuration in which the hub support member 31 is provided with the lubrication supply oil passage L1 in addition to the fastening supply oil passage L2 and the release supply oil passage L3, the axial dimension can be made compact.

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

As described above, according to the present invention, in an automatic transmission having a brake in which a plurality of friction plates are arranged between a hub member and a drum member and a hydraulic chamber is arranged inside the hub member in the radial direction. Since it is possible to efficiently arrange the oil passage extending inward in the radial direction in the axial direction, it may be suitably used in the field of manufacturing technology of this type of automatic transmission or a vehicle equipped with the automatic transmission.

10 Automatic transmission 11 Transmission case 20 Hub member 31 Hub support member 32b Extension 41 First hydraulic chamber component (hydraulic chamber component)
43 First cylindrical part (outer peripheral side cylindrical part)
47 Seal member 60 Drum member 70 Friction plate 80 Piston 90 Hydraulic chamber 91 Fastening hydraulic chamber 92 Release hydraulic chamber 101 Spring 111 Axial oil passage 113 Axial oil passage 114 Communication oil passage 115 Inclined oil passage 121 Radial oil passage ( Second radial oil channel)
122 Axial oil passage (second axial oil passage)
123 Communication oil passage (second communication oil passage)
124 Inclined oil passage (second inclined oil passage)
131 Radial oil passage (third radial oil passage)
132 Circumferential oil passage 133 Axial oil passage (third axial oil passage)
BR2 2nd brake F mating surface L1 Lubrication supply oil passage L2 Fastening supply oil passage L3 Release supply oil passage X Fitting part

Claims (5)

A non-rotatable hub member coupled to a transmission case, a rotatable drum member coupled to a rotating element, a plurality of friction plates arranged between the hub member and the drum member, and the plurality of friction plates. An automatic transmission having a brake having a piston for fastening a friction plate and a hydraulic chamber to which hydraulic oil for urging the piston is supplied.
The hydraulic chamber is arranged inside the hub member in the radial direction.
A hub support member that is fixed to the transmission case and supports the hub member is in contact with the side portion of the hub member on the anti-piston side.
A hydraulic chamber constituent member forming the hydraulic chamber is arranged inside the hub member in the radial direction.
The hub support member includes an extension portion that extends radially inward from the hub member.
The extension portion of the hub support member and the hydraulic chamber constituent member are connected by a mating surface in the axial direction.
The hub support member is provided with a radial oil passage that extends in the radial direction and is open to the mating surface.
The hydraulic chamber constituent member is provided with an axial oil passage that communicates with the hydraulic chamber and is open to the mating surface.
The automatic transmission is characterized in that the mating surface extends in the radial direction along the mating surface and is provided with a communicating oil passage for communicating the radial oil passage and the axial oil passage. Machine. The automatic transmission according to claim 1, wherein a sealing member extending in the radial direction is mounted on the mating surface so as to surround the outer peripheral side of the communication oil passage. The hub support member is provided with an inclined oil passage that connects the radial oil passage and the communication oil passage.
The automatic according to claim 1 or 2, wherein the inclined oil passage is formed so as to be inclined toward the mating surface so as to connect to the communication oil passage while facing inward in the radial direction. transmission. The hydraulic chamber has a fastening hydraulic chamber to which hydraulic oil for urging the piston in the fastening direction is supplied, and a releasing hydraulic chamber to which hydraulic oil is supplied so as to urge the piston in the releasing direction. And
The hub support member is provided with a fastening hydraulic chamber, a fastening supply oil passage connected to the release hydraulic chamber, and a release supply oil passage, respectively.
The fastening supply oil passage includes the radial oil passage, the axial oil passage, the communication oil passage, and the inclined oil passage.
The release supply oil passage includes the radial oil passage, the axial oil passage, the communication oil passage, the second radial oil passage having the same configuration as the inclined oil passage, and the second It has an axial oil passage, a second communication oil passage, and a second inclined oil passage.
The automatic transmission according to claim 3, wherein the fastening supply oil passage and the release supply oil passage are arranged at different positions in the circumferential direction. The hydraulic chamber component member has an outer peripheral side cylindrical portion fitted to the hub member, and has a cylindrical portion.
A circumferential oil passage extending in the circumferential direction for supplying lubricating oil to the friction plate is formed in the fitting portion between the outer peripheral side cylindrical portion and the hub member.
The hub support member includes a third radial oil passage extending in the radial direction and a third axial oil passage extending in the axial direction and connecting the third radial oil passage and the circumferential oil passage. Is provided,
The automatic transmission according to claim 4, wherein the third radial oil passage is arranged at a different circumferential position from the radial oil passage and the second radial oil passage.

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