JP2020016274A - Automatic transmission - Google Patents

Abstract

To accurately move a position to a contact previous position from a release position by first and second springs, and to accurately move the piston by only the second springs when moving the piston to a fastening direction from the contact previous position.SOLUTION: In an automatic transmission 10 having a friction fastening element BR2 in which first and second springs 92, 93 for making energization forces act on a piston 60 from a release position up to a contact previous position and a zero clearance position are arranged while being overlapped on each other in a radial direction, the first springs 92 are arranged in a plurality of pieces in a peripheral direction, and a stopper member 37 is attached to a vertical wall part 32 connected to a transmission case 11. The stopper member 37 comprises a plurality of regulation portions 37b extending to a peripheral direction along a circumference in which center axes of the first springs 92 are arranged, and receiving only the energization forces of the first springs 92.SELECTED DRAWING: Figure 3

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.

  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, a plurality of planetary gear sets (planetary gear mechanisms) connected to the fluid transmission device, and clutches and brakes. A transmission mechanism having a plurality of frictional engagement elements, and a plurality of frictional engagement elements are selectively engaged by hydraulic control to achieve a plurality of speeds with different reduction ratios. ing.

  2. Description of the Related Art In recent years, fluid transmission devices have tended to be abolished in response to demands for increasing the number of stages and reducing the weight of automatic transmissions. In this case, it is conceivable to realize a smooth start while avoiding engine stall by performing slip control of at least one frictional engagement element that is engaged at the first speed when starting.

  When performing slip control of a frictional engagement element that is engaged at the first speed when starting, a brake that does not rotate the hydraulic chamber has better controllability at engagement than a clutch that rotates the hydraulic chamber. It is conceivable to perform slip control on a brake that is engaged at the first speed.

  In the automatic transmission configured as described above, for the brakes to be engaged at the first speed at the start, the piston for engaging the friction plate is urged by a spring to improve the responsiveness at the start, and the engagement direction is increased. What is moved to is known.

  For example, in Patent Document 1, a piston for fastening a plurality of friction plates is biased by a first spring and a second spring from a release position to a first position moved a predetermined distance in a fastening direction, and a plurality of friction plates are moved from the first position. A brake is disclosed in which a plate is urged by a second spring only to a second position where the plate is in a zero clearance state, and is urged by a fastening hydraulic pressure from the second position to a fastening position to fasten a plurality of friction plates. I have.

  FIG. 21 is a sectional view showing a brake of a conventional automatic transmission. As shown in FIG. 21, the brake 200 includes a plurality of friction plates 203 disposed between a hub member 201 and a drum member 202, an outer cylindrical portion 204a of a housing 204 that is a part of a transmission case, and a flange. And a piston 206 fitted to a cylinder 205 formed by the portion 204b and the inner cylindrical portion 204c.

  The brake 200 is also provided with a fastening hydraulic chamber 207 to which a hydraulic fluid for fastening that urges the piston 206 in the fastening direction is supplied. It has a release hydraulic chamber 208 to which release hydraulic oil biased in the release direction is supplied.

  In the fastening hydraulic chamber 207, a first spring 209 and a second spring 210 for biasing the piston 206 in the fastening direction are arranged. The first spring 209 is partially disposed in a groove portion 204d formed in the outer cylindrical portion 204a of the housing 204, and the second spring 210 is disposed radially inside the first spring 209.

  When the brake 200 is engaged, the engagement hydraulic pressure is discharged from the engagement hydraulic pressure chamber 207 and the release hydraulic pressure is supplied to the release hydraulic pressure chamber 208 so that the piston 206 causes the first spring 209 and the second spring 210 to operate. When the release hydraulic pressure is discharged from the compressed release position, the piston 206 is urged by the first spring 209 and the second spring 210, and is moved from the release position to the first position moved a predetermined distance in the fastening direction. You.

  When the piston 206 reaches the first position, the piston 206 is urged only by the second spring 210, and is moved from the first position to the second position where the plurality of friction plates 203 enter the zero clearance state. When the fastening hydraulic pressure is supplied after the piston 206 reaches the second position, the piston 206 is urged by the fastening hydraulic pressure, and is moved to a fastening position where the plurality of friction plates 203 are fastened.

  On the other hand, when the brake 200 is released, the release hydraulic pressure is discharged from the release hydraulic pressure chamber 208, and the engagement hydraulic pressure is supplied to the engagement hydraulic pressure chamber 207. Is discharged to supply the release hydraulic pressure, the piston 206 is urged in the release direction, and the piston 206 is moved to the release position where the first spring 209 and the second spring 210 are compressed.

  In the brake 200, the urging force of the first spring 209 is set to be larger than the urging force of the second spring 210, so that the piston 206 is moved from the release position to the first position by the first spring 209 and the second spring 210 with good responsiveness. As a result, the second spring 210 can accurately move from the first position to the second position.

JP-A-2017-150533

  As described in Patent Document 1, in an automatic transmission provided with a brake in which a plurality of friction plates are arranged between a hub member and a drum member, a piston for fastening the plurality of friction plates is attached in a fastening direction. When the first and second springs that act on the force are arranged at different positions in the radial direction, the configuration is such that the radial dimension is large.

  On the other hand, by arranging the first and second springs at positions overlapping in the radial direction, it is considered that the radial dimension can be reduced, and the configuration can be made compact in the radial direction.

  Thus, in the automatic transmission having the friction fastening element such as the brake disposed at the position where the first and second springs overlap in the radial direction, the piston is moved from the release position immediately before the piston comes into contact with the plurality of friction plates from the release position. A first spring is formed so as to apply a biasing force in the fastening direction to a position immediately before contact, and a biasing force is applied to the piston in the fastening direction from the release position to a zero clearance position where the plurality of friction plates are in a zero clearance state. When the second spring is formed as described above, the piston is accurately moved by the first and second springs from the release position to the position immediately before the contact by the first and second springs, and is precisely moved by the second spring only when the piston is moved from the position immediately before the contact to the fastening direction. It is desired to make it.

  However, in a case where the first and second springs arranged at positions overlapping in the radial direction are spaced apart from the outer peripheral wall of the transmission case and arranged radially inward, for example, how the piston comes into contact from the release position The problem is whether the first and second springs can be moved to the immediately preceding position with high accuracy, and if the movement from the position immediately before contact is made in the fastening direction, the movement can be made with only the second spring with high accuracy.

  In view of the above, the present invention provides an automatic transmission having a friction fastening element in which first and second springs for applying a biasing force to a piston are radially overlapped with each other. Another object of the present invention is to accurately move only the second spring when moving in the fastening direction from the position immediately before contact with the first and second springs.

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

  First, an invention according to claim 1 of the present application is directed to a plurality of friction plates arranged in a transmission case, a piston for fastening the plurality of friction plates, and a fastening direction from a release position to a position immediately before contact with the piston. An automatic transmission including a first spring for applying an urging force to the piston, and a second spring for applying an urging force to the piston in a fastening direction from the release position to the zero clearance position. The first spring and the second spring are arranged at positions overlapping in the radial direction and at different positions in the circumferential direction, and the first spring has a center axis of the first spring different in the circumferential direction on the same circumference. A plurality of pistons are provided in the circumferential direction so as to be arranged at positions, and the piston is connected to the transmission case at a vertical wall portion extending in the radial direction. A stopper member that restricts the urging force of the first spring from acting on the piston when the piston is moved in the fastening direction and allows the urging force of the second spring to act on the piston; A first mounting portion attached to the vertical wall portion; and a first portion provided on a side opposite to the vertical wall portion side and extending in a circumferential direction along a circumference on which a center axis of the first spring is disposed. And a plurality of regulating portions for receiving only the urging force of the spring.

  According to a second aspect of the present invention, in the first aspect of the invention, the friction fastening element includes a hub member connected to the transmission case, and a drum member connected to a predetermined rotating member. Wherein the plurality of friction plates are brakes disposed between the hub member and the drum member.

  According to a third aspect of the present invention, in the second aspect of the present invention, the hub member includes a cylindrical portion with which the friction plate is spline-engaged and is spline-engaged with the transmission case. A first hub member, and a second hub member disposed adjacent to the first hub member and fitted to the transmission case, wherein the vertical wall portion is provided on the second hub member. It is characterized by having.

  According to a fourth aspect of the present invention, in the third aspect of the invention, the second hub member has a lubricating oil supply passage for supplying lubricating oil to the friction plate. A plurality of lubrication supply portions extending in the axial direction from the vertical wall portion are provided, and the first spring and the second spring are radially overlapped with the plurality of lubrication supply portions and at different positions in the circumferential direction. It is characterized by being arranged.

  According to a fifth aspect of the present invention, in the invention according to any one of the first to fourth aspects, the stopper member is formed in a substantially annular shape, and the stopper member is formed on the vertical wall portion. A mounting groove depressed from the side to the side opposite to the stopper member side is provided, and the stopper member is fitted to the mounting groove and mounted to the vertical wall portion.

  According to the invention described in claim 1 of the present application, the first and second springs that apply the urging force to the piston from the release position to the position immediately before contact and the zero clearance position are disposed at positions overlapping in the radial direction. In an automatic transmission having a friction fastening element, a plurality of first springs are provided in a circumferential direction, and a stopper member is attached to a vertical wall portion connected to a transmission case.

  The stopper member includes a plurality of restricting portions that extend in the circumferential direction along the circumference where the center axis of the first spring is disposed on the side opposite to the vertical wall portion side and receive only the urging force of the first spring. Can be Thereby, the plurality of regulating portions provided on the single stopper member can be machined with high precision by the same machining, and the piston is accurately moved from the release position to the position immediately before contact by the first and second springs. be able to.

  When the stopper member is integrally formed on the vertical wall portion connected to the transmission case, a plurality of lubrication lubrication members are provided on the vertical wall portion at positions overlapping the stopper member in the radial direction and different positions in the circumferential direction. When the supply portion and the like are integrally formed, the end surfaces of the plurality of regulating portions of the stopper member may not be machined by the same machining by the lubrication supply portion and the like, but are coupled to the transmission case. By attaching a separate stopper member to the vertical wall, the end faces of the plurality of restricting portions of the stopper member can be processed by the same machining to improve the positional accuracy of the end surfaces of the plurality of restricting portions, and the piston is released. The first and second springs can accurately move from the position to the position immediately before the contact.

  Further, the restricting portion provided on the stopper member extends in the circumferential direction along the circumference on which the central axis of the first spring is disposed, so that the central side of the first spring can be restricted, and the diameter of the first spring can be reduced. It is possible to accurately receive the urging force of the first spring as compared with the case where only the outer side or the inner side in the radial direction is regulated, and to move the piston with accuracy only by the second spring when moving the piston from the position immediately before touching in the fastening direction. it can.

  Therefore, in an automatic transmission having a frictional fastening element in which the first and second springs for applying a biasing force to the piston are radially overlapped with each other, the first and second springs are moved from the release position to the position immediately before the contact. When moving in the fastening direction from the position immediately before contact with the second spring, it is possible to move with high accuracy only by the second spring.

  According to the second aspect of the invention, in the friction fastening element, a plurality of friction plates are arranged between the hub member connected to the transmission case and the drum member connected to the predetermined rotating member. By being a brake, in an automatic transmission with a brake, the lubricating hydraulic oil supplied to the friction plate of the brake is suppressed from staying due to the rotation of the drum member, and the friction oil between the friction plates due to the lubricating hydraulic oil is suppressed. Drag resistance can be suppressed.

  According to the third aspect of the invention, the hub member of the brake includes the first hub member spline-engaged with the transmission case, and the second hub member fitted with the transmission case. The vertical wall portion to which the stopper member is attached is provided on the second hub member. Thereby, the second hub member can be fitted and fixed to the transmission case, the vertical wall portion to which the stopper member is attached is fixed to the transmission case, and the first and second pistons are moved from the release position to the position immediately before the contact. The second spring can be moved more precisely.

  According to the invention described in claim 4, the second hub member includes a plurality of lubrication supply portions, and the first and second springs overlap the plurality of lubrication supply portions in the radial direction. , The first and second springs can be made more compact in the radial direction than when they do not overlap the lubrication supply part in the radial direction.

  According to the invention described in claim 5, the stopper member is formed in a substantially annular shape, is fitted in the mounting groove provided in the vertical wall portion, and is mounted on the vertical wall portion. The stopper member can be relatively easily attached to the connected vertical wall portion.

1 is a skeleton diagram of an automatic transmission according to an embodiment of the present invention. 4 is a table of engagement of friction engagement elements of the automatic transmission. It is sectional drawing of the brake of an automatic transmission, and its periphery. FIG. 4 is an enlarged view of a main part of the brake shown in FIG. It is another sectional view of the brake of an automatic transmission and its circumference. FIG. 5 is a further sectional view of a brake of the automatic transmission and its periphery. FIG. 5 is a further sectional view of a brake of the automatic transmission and its periphery. FIG. 5 is a further sectional view of a brake of the automatic transmission and its periphery. FIG. 4 is a perspective view showing an assembled state of a brake hub member, an oil passage forming member, and a piston. FIG. 3 is a perspective view showing an assembled state of a brake hub member and an oil passage forming member. It is a perspective view showing a hub member of a brake. FIG. 4 is a perspective view showing a first hub member. It is a perspective view showing a 2nd hub member. It is another perspective view which shows the hub member of a brake. FIG. 5 is a perspective view showing a stopper member and a piston to which an urging receiving member is attached. It is a perspective view which shows an urging unit. FIG. 17 is a cross-sectional view of the urging unit taken along line Y17-Y17 in FIG. 16. FIG. 5 is an explanatory diagram for explaining an arrangement of a stopper member and an urging unit. It is sectional drawing which shows the brake in a release state and a state just before a contact. It is sectional drawing which shows the brake in a zero clearance state and a fastening state. It is a sectional view showing a brake of a conventional automatic transmission.

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

  FIG. 1 is a skeleton 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 provided in a transmission case 11 on an input shaft 12 connected to a drive source and disposed on a drive source side (left side in the figure) and on an opposite drive source side (right side in the figure). Output shaft 13. The automatic transmission 10 is of a vertical type such as for a front engine / rear drive vehicle in which an input shaft 12 and an output shaft 13 are arranged on the same axis.

  First, second, third, and fourth planetary gear sets (hereinafter simply referred to as “first, second, third, and fourth gear sets”) are provided on the axis of the input shaft 12 and the output shaft 13 from the drive source side. PG1, PG2, PG3, PG4).

  In the transmission case 11, a first clutch CL1 is provided on the drive source side of the first gear set PG1, a second clutch CL2 is provided on the drive source side of the first clutch CL1, and a drive source of the second clutch CL2 is provided. The third clutch CL3 is disposed on the side. Further, a first brake BR1 is provided on the drive source side of the third clutch CL3, and a second brake BR2 is provided on the drive source side of the third gear set PG3 and on the opposite drive source side of the second gear set PG2.

  Each of the first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 is a single pinion type in which a pinion supported by a carrier directly meshes with a sun gear and a ring gear. The first, second, third, and fourth gear sets PG1, PG2, PG3, and PG4 each include, as rotating elements, sun gears S1, S2, S3, and S4, ring gears R1, R2, R3, and R4, and carriers C1 and C2. , 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. Thus, the first and second sun gears S1a and S1b always rotate in the same manner.

  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. 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 the space 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 to connect and disconnect them. 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 are arranged to be connected and disconnected, and the third clutch CL3 is connected to the second gear set. It is arranged between the ring gear R2 of PG2 and the sun gear S3 of the third gear set PG3, and connects and disconnects 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, and connects and disconnects them. Is disposed between the transmission case 11 and the ring gear R3 of the third gear set PG3 to connect and disconnect them.

  With the above-described configuration, the automatic transmission 10 is configured such that the combination of the engagement states of the first clutch CL1, the second clutch CL2, the third clutch CL3, the first brake BR1, and the second brake BR2, as shown in FIG. The first to eighth speeds in the range and the reverse speed in the R range are formed.

  In the automatic transmission 10, the second brake BR2, which is engaged at the first gear when starting, is subjected to slip control, and the second brake BR2 corresponds to a friction engagement element of the automatic transmission according to the present invention. Hereinafter, the brake BR2 will be described.

  3 is a sectional view of the brake of the automatic transmission and its periphery, FIG. 4 is an enlarged view of a main part of the brake and its periphery shown in FIG. 3, and FIG. 5 is another sectional view of the brake of the automatic transmission and its periphery. FIGS. 6, 6, 7 and 8 are further sectional views of the brake of the automatic transmission and the periphery thereof. FIGS. 3, 5, 6, 7, and 8 respectively correspond to the cross-sections along the lines Y3-Y3, Y5-Y5, Y6-Y6, Y7-Y7, and Y8-Y8 of FIG. 1 shows a cross-section of a brake of an automatic transmission according to the present invention and its periphery.

  As shown in FIGS. 3 to 8, 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 be connected to the first, second, and third clutches. One of a pair of inner and outer rotating members CL1, CL2, and CL3 is disposed on the outer peripheral side of the power transmission member 14 in which the pair is integrated.

  The power transmission member 14 is disposed on the outer peripheral side of a 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 connected to 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 (inside fixed member) 20 connected to the transmission case 11, and a drum member (outside rotation) disposed on the side opposite to the drive source of the hub member 20 and connected to the ring gear R3 of the third gear set PG3. Member) 40, a plurality of friction plates 50 arranged in the axial direction between the hub member 20 and the drum member 40, and a plurality of friction plates 50 arranged on the side of the plurality of friction plates 50 opposite to the driving source. And a piston 60 to be fastened.

  The brake BR2 has a hydraulic chamber 70 to which hydraulic oil for urging the piston 60 is supplied. The hydraulic chamber 70 is a hydraulic chamber for engagement 71 to which hydraulic oil for urging the piston 60 in the direction of engagement is supplied. And a release hydraulic chamber 72 that is arranged on the opposite side of the fastening hydraulic chamber 71 with the piston 60 interposed therebetween and is supplied with release hydraulic oil that urges the piston 60 in the release direction.

  As shown in FIG. 7, the brake BR2 has an oil passage forming member 80 that forms a fastening supply oil passage L2 that supplies fastening hydraulic oil to the fastening hydraulic chamber 71. The oil passage forming member 80 includes a piston. 60 is disposed on the side opposite to the driving source and at the side opposite to the driving source of the hub member 20 and is coupled to the hub member 20.

  As shown in FIG. 5, the brake BR2 also has a plate member 85 that forms a lubricating oil supply passage L1 that supplies the lubricating hydraulic oil to the plurality of friction plates 50 together with the hub member 20. It is arranged on the drive source side of the hub member 20 and is coupled to the hub member 20.

  The brake BR2 also has an urging unit 90 for urging the piston 60, as shown in FIG. The urging unit 90 includes an urging member 91 that urges the piston 60. As the urging member 91, a first urging member that applies an urging force to the piston 60 in a fastening direction and a second urging member that acts as a second urging member. A first spring 92 and a second spring 93 are provided.

  FIG. 9 is a perspective view showing an assembled state of a brake hub member, an oil passage forming member and a piston, FIG. 10 is a perspective view showing an assembled state of a brake hub member and an oil passage forming member, and FIG. FIG. 12 is a perspective view showing a first hub member, FIG. 13 is a perspective view showing a second hub member, FIG. 14 is another perspective view showing a brake hub member, 15 is a perspective view showing a stopper member and a piston to which an urging receiving member is attached, FIG. 16 is a perspective view showing an urging unit, and FIG. 17 is an urging force along a line Y17-Y17 in FIG. It is sectional drawing of a unit.

  As shown in FIGS. 3 to 15, the hub member 20 includes a first hub member 21 with which the friction plate 50 is spline-engaged, and a second hub member 31 that supplies lubricating hydraulic oil to the friction plate 50. , The second hub member 31 is disposed adjacent to the drive source side of the first hub member 21.

  As shown in FIG. 3, the first hub member 21 extends in a radial direction perpendicular to the axial direction of the transmission case 11 and has a substantially disk-shaped vertical wall portion 22, and a radially inner side of the vertical wall portion 22. And an inner cylindrical portion 23 extending in a substantially cylindrical shape on the side opposite to the drive source.

  The first hub member 21 has a spline portion 24 in which a spline is formed on the outer peripheral surface of the vertical wall portion 22. The spline portion 24 is splined to a spline portion 11 a in which a spline is formed on the inner peripheral surface of the transmission case 11. It is engaged and connected to the transmission case 11.

  The inner cylindrical portion 23 of the first hub member 21 has a plurality of, specifically, six, spline portions 25 having splines formed on the outer peripheral surface in the circumferential direction. The side friction plate 51 is in spline engagement.

  The inner cylindrical portion 23 of the first hub member 21 has a predetermined axial length in which the spline portion 25 is spline-engaged with the plurality of friction plates 50 even when the plurality of friction plates 50 are released. Excluding portions are formed shorter in the axial direction than the spline portions 25.

  As shown in FIG. 6, the second hub member 31 extends in a radial direction orthogonal to the axial direction of the transmission case 11 and has a substantially disk-shaped vertical wall portion 32. A lubrication boss 33 as a lubrication supply unit that extends in a substantially cylindrical shape to the side and supplies lubrication hydraulic oil to the friction plate 50 is provided.

  As shown in FIG. 3, the outer peripheral surface of the vertical wall portion 32 of the second hub member 31 is fitted to the inner peripheral surface 11 b of the transmission case 11 on the drive source side of the spline portion 24 of the first hub member 21. I have. The second hub member 31 is fixed to the transmission case 11 in the circumferential direction using the detent pin 18 and is coupled to the transmission case 11.

  The second hub member 31 is also fixed in the axial direction from the drive source side by a snap ring 17, as shown in FIG. On the inner peripheral surface 11b of the transmission case 11, a peripheral groove 3 into which the snap ring 17 is fitted is provided over the entire circumference. The circumferential groove 3 is formed so as to be depressed radially outward from the inner peripheral surface 11b of the transmission case 11 in a substantially rectangular cross section, and is inclined at a predetermined angle toward the drive source side and toward the opposite drive source side toward the drive source side. A groove-side inclined surface 3a is provided.

  When not mounted, the snap ring 17 has a larger diameter when mounted, is formed in a substantially annular shape with a substantially rectangular cross section, and is provided with a snap ring-side inclined surface 17a that contacts the circumferential groove-side inclined surface 3a on the drive source side. I have. The snap ring-side inclined surface 17a is formed so as to be inclined at a predetermined angle toward the non-drive source side toward the outside in the radial direction.

  The second hub member 31 is fitted by the snap ring 17 in a state where the snap ring 17 is biased in the radially expanding direction in the circumferential groove 3 and the snap ring side inclined surface 17a comes into contact with the circumferential groove side inclined surface 3a. It is fixed in the axial direction from the drive source side. The second hub member 31 is pressed from the drive source side by the snap ring 17, and the vertical wall portion 32 of the second hub member 31 presses the vertical wall portion 22 of the first hub member 21 from the drive source side, so that the first hub member 31 is pressed. The anti-drive source side of the spline portion 24 of the hub member 21 is fixed in the axial direction by abutting on a step portion 11c formed on the inner peripheral surface of the transmission case 11.

  As shown in FIG. 13, the second hub member 31 is provided with a plurality of lubrication bosses 33, specifically, five lubrication bosses 33. The five lubricating bosses 33 are arranged at different positions in the circumferential direction on substantially the same circumference around the axis of the input shaft 12 and the output shaft 13. Each of the lubrication boss portions 33 includes a lubrication supply oil passage L1 for supplying a lubricating hydraulic oil to the friction plate 50.

  As shown in FIG. 5, a valve body 5 that supplies hydraulic oil to the hydraulic chamber 70 of the brake BR2, the friction plate 50, and the like is disposed below the transmission case 11. The valve body 5 is housed in an oil pan (not shown) mounted below the transmission case 11 and is fixed to the transmission case 11. The second hub member 31 has a valve body connecting portion 34 for connecting to the valve body 5, and a lubricating oil supply passage L 1 is connected to the valve body 5 through a case opening 11 d formed in the transmission case 11. It is formed so that.

  As shown in FIG. 7, the second hub member 31 further includes a fastening supply oil passage L <b> 2 that extends from the vertical wall portion 32 to the opposite driving source side in a substantially columnar shape and supplies hydraulic oil to the fastening hydraulic chamber 71. As shown in FIG. 8, a release oil supply passage L <b> 3 that extends substantially vertically from the vertical wall 32 to the non-drive source side and supplies hydraulic oil to the release hydraulic chamber 72, as shown in FIG. 8. And a release boss portion 36 having

  As shown in FIG. 13, the fastening boss 35 and the release boss 36 are arranged at different positions on the substantially same circumference around the axis of the input shaft 12 and the output shaft 13 together with the lubrication boss 33. It is arranged between two lubricating bosses 33 arranged below the transmission case 11.

  In the automatic transmission 10, the fastening supply oil passage L2, the release supply oil passage L3, and the lubrication supply oil passage L1 are arranged circumferentially below the transmission case 11, and the second hub member 31 The fastening supply oil passage L2, the release supply oil passage L3, and the lubrication supply oil passage L1 are formed so as to be connected to the valve body 5, respectively.

  The lubricating oil supply passage L <b> 1 is formed in the hub member 20, specifically, in the second hub member 31. As shown in FIGS. 5 and 6, the second hub member 31 is provided with a lubrication recess 32 a that is recessed on the drive source side and is formed on the opposite drive source side to form a lubrication supply oil passage L <b> 1. A plate member 85 formed in a substantially annular shape is disposed on the drive source side so as to cover.

  The lubricating concave portion 32a of the second hub member 31 has a radial concave portion 32b that is concave in a substantially rectangular cross section and extends in the radial direction, and a radial concave portion 32b that is connected to the radial concave portion 32b and is concave in a substantially rectangular cross section and has a circular arc shape in the circumferential direction. It has a circumferential recess 32c that extends and a plurality of axial recesses 32d that are connected to the circumferential recess 32c at different positions in the circumferential direction and that are recessed in a circular cross section and extend in the axial direction. The axial recess 32d is provided in the lubrication boss 33 so as to extend in the axial direction to the non-drive source side in correspondence with the lubrication boss 33.

  In the automatic transmission 10, the second hub member 31 of the hub member 20 is provided with a fastening bolt 4 as a fastening member for connecting the oil passage forming member 80 and the plate member 85, and the fastening bolt 4 is connected to the second hub member 31. The oil passage forming member 80 and the plate member 85 are connected to each other, and the lubrication supply oil passage L1 is formed by the second hub member 31 and the plate member 85.

  The plate member 85 is provided with a bolt insertion hole 85a through which the fastening bolt 4 is inserted. The plate member 85 sandwiches the second hub member 31 by screwing the fastening bolt 4 into the screw hole 80a provided in the oil passage forming member 80 through the bolt insertion hole 85a and the lubrication recess 32a of the second hub member 31. Are connected to the oil passage forming member 80 and to the second hub member 31.

  As shown in FIGS. 5 and 6, the lubrication supply oil passage L1 formed by covering the lubrication recess 32a of the second hub member 31 with the plate member 85 includes a radial oil passage 131 extending in the radial direction. A circumferential oil passage 132 extending in an arc shape in the circumferential direction and connected to the radial oil passage 131, and an axial oil provided on the lubrication boss 33 and extending in the axial direction and connected to the circumferential oil passage 132. A road 133 is provided.

  The axial oil passage 133 is provided on the lubricating boss 33, extends in the radial direction, is connected to the axial oil passage 133, and opens to the outer peripheral surface of the lubricating boss 33 to lubricate the friction plate 50. A supply port 134 for supplying hydraulic oil is provided. The fastening bolt 4 extends in the axial direction through the axial oil passage 133 of the lubricating oil supply passage L1.

  As shown in FIG. 8, the second hub member 31 of the hub member 20 is provided with a fastening bolt 6 as a fastening member for connecting the oil passage forming member 80 and the plate member 85. The plate member 85 is provided with a bolt insertion hole 85b for inserting the fastening bolt 6, and the bolt insertion hole 85b is provided corresponding to the release boss portion.

  The release supply oil passage L3 is provided in the vertical wall portion 32 of the second hub member 31, extends in the radial direction, and opens in the release hydraulic chamber 72, and is provided in the release boss portion 36. And an axial oil passage 122 extending in the axial direction and connected to the radial oil passage 121, and the fastening bolt 6 extends in the axial direction through the axial oil passage 122 of the release supply oil passage L3.

  The plate member 85 also connects the fastening bolt 6 to the screw hole 80b provided in the oil passage forming member 80 through the bolt insertion hole 85b and the axial oil passage 122 of the release supply oil passage L3 provided in the second hub member 31. By being screwed together, the second hub member 31 is connected to the oil passage forming member 80 with the second hub member 31 interposed therebetween, and is connected to the second hub member 31. On the drive source side of the second hub member 31, a seal material is applied to a portion where the plate member 85 contacts.

  As shown in FIG. 3, the second hub member 31 also has a first cylindrical portion extending substantially in a cylindrical shape from the vertical wall portion 32 to the non-drive source side radially inside the inner cylindrical portion 23 of the first hub member 21. 38 and a second cylindrical portion 39. The second cylindrical portion 39 is formed to be longer in the axial direction than the first cylindrical portion 38 radially inside the first cylindrical portion 38. The first cylindrical portion 38 and the second cylindrical portion 39 together with the vertical wall portion 32 constitute a cylinder 72 a of the release hydraulic chamber 72.

  The vertical wall portion 32 of the second hub member 31 restricts the urging force of the first spring 92 from acting on the piston 60 when the piston 60 is moved in the fastening direction from the position immediately before the contact, and the second spring 93 A stopper member 37 that allows the urging force of the actuator to act is attached.

  As shown in FIG. 15, the stopper member 37 is formed in a substantially annular shape, and is provided with an attachment portion 37 a attached to the vertical wall portion 32 and a central axis of the first spring 92 provided on the side opposite to the vertical wall portion 32 side. And a plurality of restricting portions 37b that extend in the circumferential direction along the circumference where is disposed and receive only the urging force of the first spring 92.

  Each of the regulating portions 37b extends in the axial direction while the driving source side contacts the vertical wall portion 32 and extends in the circumferential direction in an arc shape along the circumference where the center axis of the first spring 92 is arranged. Is provided so that the end surface thereof contacts the second holding plate 95 of the urging unit 90. The circumferential end of the restricting portion 37b of the stopper member 37 extends radially inward and is connected to the mounting portion 37a.

  The mounting portion 37a is formed in a substantially rectangular cross section so as to connect the plurality of regulating portions 37b in the circumferential direction, and is formed in a circular arc shape in the circumferential direction inside the second spring 93 in the radial direction. As shown in FIG. 3, the vertical wall portion 32 of the second hub member 31 has a mounting recessed concavely from the stopper member side to the opposite side to the stopper member side corresponding to the shape of the mounting portion 37 a of the stopper member 37. A stopper groove 37 is provided, and the stopper member 37 is fitted to the mounting groove 32e and attached to the vertical wall portion 32.

  FIG. 18 is an explanatory diagram for explaining the arrangement of the stopper member and the urging unit. As shown in FIG. 18, the restricting portions 37 b of the stopper members 37 each have a first spring 92 in an arc shape along the circumference where the center axis of the first spring 92 is arranged at the portion where the first spring 92 is arranged. Is provided so as to extend in the circumferential direction including a portion where the second spring plate 93 is disposed, and abut on the second holding plate 95 of the urging unit 90. In a portion where the second spring 93 is disposed, the second holding plate of the urging unit 90 is provided. 95 is provided so as not to abut.

  In the automatic transmission 10, the stopper member 37 is formed separately from the second hub member 31 and attached to the second hub member 31. In the stopper member 37, the end faces of the plurality of restricting portions 37b projecting from the mounting portion 37a to the side opposite to the driving source are formed by the same machining, and the positional accuracy of the end surfaces of the plurality of restricting portions 37b is enhanced.

  As shown in FIG. 3, the drum member 40 is disposed opposite to the outer peripheral side of the inner cylindrical portion 23 of the first hub member 21, and extends substantially axially in a cylindrical shape in the axial direction. A vertical wall portion 42 extending from the drive source side to the radially inner side perpendicular to the axial direction of the transmission case 11 from the inner cylindrical portion 23 and formed in a substantially disk shape is provided.

  The vertical wall portion 42 of the drum member 40 has the anti-drive source side coupled to the ring gear R3. The outer cylindrical portion 41 of the drum member 40 has a spline portion 41a in which a spline is formed on the inner peripheral surface, and a rotation-side friction plate 52 constituting the friction plate 50 is spline-engaged with the spline portion 41a. . The fixed-side friction plates 51 and the rotation-side friction plates 52 are arranged alternately in the axial direction.

  The vertical wall portion 42 of the drum member 40 is also provided with an extended portion 43 that extends cylindrically in the axial direction toward the drive source radially inside the inner cylindrical portion 23 of the first hub member 21. The hub member 20, specifically, the second hub member 31 is provided with a support portion 80 c that supports the drum member 40 on the outer peripheral side of the extending portion 43.

  An oil passage forming member 80 is connected to the second hub member 31 of the hub member 20 on the side opposite to the driving source, and the cylindrical member is recessed toward the driving source on the side opposite to the driving source of the oil path forming member 80 so as to extend the drum member 40. An extension portion accommodation hole 80d for accommodating the installation portion 43 is formed. The outer peripheral surface 80c of the extended portion accommodation hole 80d functions as a support portion 80c that is arranged on the outer peripheral side of the extended portion 43 and supports the drum member 40. The drum member 40 is supported by the support portion 80c via a bearing member 45 disposed between the extending portion 43 and the support portion 80c. As the bearing member 45, a radial bearing such as a radial roller bearing or a radial ball bearing is used.

  The piston 60 is disposed between the hub member 20 and the drum member 40, specifically, between the inner cylindrical portion 23 of the first hub member 21 and the outer cylindrical portion 41 of the drum member 40, and 31 is slidably fitted to the outer peripheral side of the second cylindrical portion 39. The snap ring 19 prevents the piston 60 from coming off to the side opposite to the drive source.

  The piston 60 is formed in an annular shape and is provided on the outer peripheral side and presses the friction plate 50. The piston 60 is provided on the inner peripheral side and forms a fastening hydraulic chamber 71 that forms a fastening hydraulic chamber 71. A connecting portion 63 that connects the pressing portion 61 and the fastening hydraulic chamber forming portion 62 and extends in the radial direction is provided.

  The pressing portion 61 is disposed on the anti-drive source side of the friction plate 50, the fastening hydraulic chamber forming portion 62 is disposed radially inside the inner cylindrical portion 23 of the first hub member 21, and the connecting portion 63 is pressed. It is provided so as to be connected from the portion 61 to the fastening hydraulic chamber forming portion 62. The fastening hydraulic chamber forming portion 62 is provided so as to protrude from the connecting portion 63 toward the drive source.

  The oil passage forming member 80 is disposed on the side opposite to the drive source of the piston 60, as shown in FIGS. The oil passage forming member 80 is fitted on the outer peripheral side of the second cylindrical portion 39 of the second hub member 31, and the boss portions 33 and 36 of the second hub member 31, specifically, the lubricating boss portion 33 and the release The boss portion 36 is disposed and coupled to the drive source side.

  The oil passage forming member 80 is provided on the outer peripheral side and is arranged and coupled to the boss portions 33 and 36 of the second hub member 31 on the side opposite to the driving source, and the piston 60 provided on the inner peripheral side and A coupling hydraulic chamber forming portion 82 disposed on the side opposite to the drive source to form the hydraulic hydraulic chamber 71, a connecting portion 83 connecting the coupling portion 81 and the hydraulic hydraulic chamber forming portion 82 and extending in the radial direction. It has.

  The fastening hydraulic chamber forming portion 82 is formed in a ring shape having a predetermined thickness, and as shown in FIG. 3, the fastening hydraulic chamber forming portion 62 between the second cylindrical portion 39 of the second hub member 31 and the piston 60. Is fitted to the outer peripheral side. The fastening hydraulic chamber 71 includes a fastening hydraulic chamber forming portion 62 of the piston 60, a fastening hydraulic chamber forming portion 82 of the oil passage forming member 80, and the second cylindrical portion 39 of the second hub member 31.

  The connecting portion 81 is formed to be thinner than the fastening hydraulic chamber forming portion 82, and is formed in an arc shape as shown in FIGS. The oil passage forming member 80 is provided with a plurality of connecting portions 81 in the circumferential direction, and in the present embodiment, five connecting portions 81, which are arranged apart from each other in the circumferential direction.

  The coupling portion 81 is provided with the screw holes 80a and 80b as described above. In the oil passage forming member 80, the fastening bolts 4 and 6 for fastening the oil passage forming member 80 and the plate member 85 with the second hub member 31 interposed therebetween are screwed into screw holes 80 a and 80 b provided in the coupling portion 81. Thus, the hub member 20 is coupled to the boss portions 33 and 36 on the side opposite to the driving source.

  The connecting portion 83 of the oil passage forming member 80 has substantially the same thickness as the connecting portion 81, and extends radially inward from the center in the circumferential direction of the connecting portion 81 as shown in FIGS. It is provided so as to be connected to the hydraulic chamber forming portion 82.

  As shown in FIG. 10, the oil passage forming member 80 includes a connecting portion 81 that is connected to the boss portions 33 and 36 of the second hub member 31 using two fastening bolts 4 and 6 on both sides in the circumferential direction. A coupling portion 81 is provided in which the center in the direction is coupled to the boss portion 33 of the second hub member 31 using one fastening bolt 4.

  The connecting portion 63 of the piston 60 has a cut-out portion 63a for an oil passage forming member cut out in substantially the same shape as the connecting portion 81 and the connecting portion 83 corresponding to the connecting portion 81 and the connecting portion 83 of the oil passage forming member 80. Are formed. The oil passage forming member 80 is disposed within a radial range of the piston 60, and the coupling portion 81 and the connecting portion 83 of the oil passage forming member 80 are fitted into the oil passage forming member cut-out portions 63 a of the connecting portion 63 of the piston 60. It is arranged at a position that overlaps the connecting portion 63 of the piston 60 in the axial direction.

  The connecting portion 63 of the piston 60 is also formed with a notch 63b for a spline portion which is cut out in substantially the same shape as the spline portion 25 corresponding to the spline portion 25 of the inner cylindrical portion 23 of the first hub member 21. I have. The opposite drive source side of the spline part 25 of the inner cylindrical part 23 of the first hub member 21 is fitted into the spline notch 63b of the connecting part 63 of the piston 60, and the inner cylindrical part 23 of the first hub member 21 The piston 60 is disposed so as to overlap in the axial direction.

  As shown in FIG. 3, the fastening hydraulic chamber forming portion 62 of the piston 60 is fitted on the outer peripheral side of the fastening hydraulic chamber forming portion 82 of the oil passage forming member 80 to extend in the axial direction, and an outer cylindrical portion 62 a is provided. A fastening hydraulic receiving portion 62b extending radially inward from the driving source side of the cylindrical portion 62a, and a second cylindrical portion 39 of the second hub member 31 extending from the radially inner side of the fastening hydraulic receiving portion 62b to the opposite driving source side. And an inner cylindrical portion 62c that extends in the axial direction by fitting into the inner cylindrical portion 62c.

  In the automatic transmission 10, the engagement hydraulic chamber 71 and the release hydraulic chamber 72 are arranged radially inside the inner cylindrical portion 23 of the first hub member 21 and the boss portions 33, 35, 36 of the second hub member 31, respectively. Have been.

  As described above, the fastening hydraulic chamber 71 is formed by the fastening hydraulic chamber forming portion 62 of the piston 60, the fastening hydraulic chamber forming portion 82 of the oil passage forming member 80, and the second cylindrical portion 39 of the second hub member 31. Is formed. The inner cylindrical portion 62c of the piston 60 is prevented from coming off to the opposite side of the drive source by the snap ring 19.

  As shown in FIG. 3, the release hydraulic chamber 72 has a swelling portion 62 d in which a radially inner side of the fastening hydraulic receiving portion 62 b of the piston 60 swells in a substantially U-shaped cross section toward the drive source side. , 74 are slidably fitted in the cylinder 72a of the second hub member 31 and are formed by the bulging portion 62d of the piston 60 and the cylinder 72a of the second hub member 31.

  In the automatic transmission 10, the release hydraulic chamber 72 is formed to have a smaller outer diameter than the fastening hydraulic chamber 71, and is coupled to the piston 60 on the outer peripheral side of the release hydraulic chamber 72 and biased by the biasing unit 90. An urging receiving member 100 that receives the urging force of the member 91 is arranged.

  The urging receiving member 100 is formed in an annular shape, and has a diameter extending in the radial direction between the inner cylindrical portion 23 of the first hub member 21 and the first cylindrical portion 38 of the second hub member 31, as shown in FIG. A radially extending portion 101 and an axially extending portion 102 extending in the axial direction from the radially inner side of the radially extending portion 101 toward the non-drive source side are provided.

  The biasing receiving member 100 is coupled to the piston 60 such that the opposite drive source side of the axially extending portion 102 is radially outwardly of the bulging portion 62d of the fastening hydraulic receiving portion 62b of the piston 60. An urging unit 90 is mounted between the urging receiving member 100, specifically, between the radially extending portion 101 and the oil passage forming member 80.

  As shown in FIGS. 16 and 17, the biasing unit 90 includes a first spring 92 and a second spring 93 extending in the axial direction, and ends of the first spring 92 and the second spring 93 on the opposite side to the driving source. There is provided a first holding plate 94 for holding, and a second holding plate 95 that is arranged to be spaced apart from the first holding plate 94 in the axial direction and holds an end of the first spring 92 on the drive source side.

  The first holding plate 94 is formed in a ring shape, and includes a first spring guide portion 94a and a second spring guide portion 94b which protrude in a cylindrical shape toward the drive source side and to which the first spring 92 and the second spring 93 are respectively mounted. ing. The first springs 92 and the second springs 93 are dispersedly arranged at positions overlapping in the radial direction and different positions in the circumferential direction.

  The second holding plate 95 is formed substantially symmetrically with respect to the first holding plate 94 in the axial direction. The second holding plate 95 has a first spring guide portion 95a to which a first spring 92 is mounted so as to protrude in a cylindrical shape on the side opposite to the drive source. The second holding plate 95 also has an insertion hole 95b through which the second spring 93 is inserted so that the end on the drive source side of the second spring 93 can protrude toward the side opposite to the first holding plate.

  The urging force of the first spring 92 is set larger than that of the second spring 93. The first spring 92 and the second spring 93 are coil springs. The first spring 92 is a large coil spring having a larger coil diameter than the second spring 93. The second spring 93 is formed to have a longer free length than the first spring 92, and the other end of the second spring 93 is provided on the first holding plate 94 so as to protrude from the second holding plate 95 on the side opposite to the first holding plate. Is held.

  In the automatic transmission 10, a plurality of first springs 92 and a plurality of second springs 93 are provided in the circumferential direction such that the central axes are arranged at different positions in the circumferential direction on the same circumference. 92 and six second springs 93 are dispersedly arranged at different positions in the circumferential direction.

  In the urging unit 90, the first holding plate 94 is supported on both circumferential sides of the connecting portion 81 of the oil passage forming member 80 and on the drive source side of the connecting portion 83, and the second holding plate 95 is provided on the urging receiving member 100. It is supported by the radially extending portion 101 on the side opposite to the drive source, and is attached to the transmission case 11.

  The radially extending portion 101 of the urging receiving member 100 is formed to support the second holding plate 95 and to support the other end of the second spring 93 inserted through the insertion hole 95b of the second holding plate 95. The second holding plate 95 is formed to have a radial dimension substantially equal to the outer diameter of the second holding plate 95.

  The radially extending portion 101 of the urging receiving member 100 is also provided with a notch 101a for a stopper member which is cut out in substantially the same shape as the regulating portion 37b corresponding to the regulating portion 37b of the stopper member 37. . The restricting portion 37b of the stopper member 37 attached to the vertical wall portion 32 of the second hub member 31 is inserted into the notch portion 101a for the stopper member of the radially extending portion 101 so that the piston 60 moves from the position immediately before contact to the fastening direction. When it is moved, it receives the second holding plate 95 of the urging unit 90 and regulates the urging force of the first spring 92.

  The inner peripheral surface of the inner cylindrical portion 23 of the first hub member 21 is formed radially larger than the first holding plate 94 and the second holding plate 95, and the urging unit 90 is disposed on the inner circumferential side of the inner cylindrical portion 23. Have been. The urging unit 90 has boss cutouts 94c and 95c formed on the first holding plate 94 and the second holding plate 95, respectively, corresponding to the bosses 33, 35 and 36 of the second hub member 31. Also in the radially extending portion 101 of the urging receiving member 100, a boss notch 101 b is formed corresponding to the bosses 33, 35, 36 of the second hub member 31.

  In the automatic transmission 10, the first spring 92 and the second spring 93 of the urging unit 90 radially overlap the lubrication boss 33, the fastening boss 35, and the release boss 36 of the second hub member 31. It is arranged at a wrapping position and a different position in the circumferential direction. Note that the fastening boss 35 and the release boss 36 are disposed radially outside of the lubrication boss 33, and the first spring 92 and the second spring 93 are radially overlapped with the lubrication boss 33. It is also possible to arrange them at different positions in the circumferential direction.

  The stopper member 37 attached to the vertical wall portion 32 of the second hub member 31 receives the urging force of the urging member 91 by the end surface of the regulating portion 37b on the side opposite to the driving source, and the second holding plate 95 moves toward the driving source. When being moved, the second holding plate 95 is received.

  When the second holding plate 95 supported by the urging receiving member 100 comes into contact with the end surface of the restricting portion 37 b on the side opposite to the driving source, the stopper 60 moves immediately before the piston 60 comes into contact with the plurality of friction plates 50. Is set to the position immediately before the contact. The position immediately before the contact of the piston 60 is appropriately set between the release position where the plurality of friction plates 50 are released and the zero clearance position where the friction plates 50 are in the zero clearance state.

  When the second holding plate 95 comes into contact with the stopper member 37, the urging receiving member 100 receives the urging force in the fastening direction by only the second spring 93. When the second spring 93 has a free length, the piston 60 is set to the zero clearance position.

  In this way, the urging unit 90 allows the first spring 92 to apply an urging force to the piston 60 via the urging receiving member 100 from the release position to the position immediately before the contact in the fastening direction, and the second spring 93 applies the urging force. An urging force is applied in the fastening direction from the release position to the zero clearance position via the receiving member 100.

  The stopper member 37 restricts the urging force of the first spring 92 from acting on the piston 60 when the piston 60 is moved in the fastening direction from the position immediately before the contact, and prevents the urging force of the second spring 93 from acting on the piston 60. It is tolerated.

  When the fastening hydraulic pressure is supplied to the fastening hydraulic chamber 71 when the piston 60 is at the zero clearance position, the piston 60 presses the plurality of friction plates 50, and the plurality of friction plates 50 move vertically of the first hub member 21. The holding member 26 protruding from the wall portion 22 on the side opposite to the driving source is sandwiched between the piston 60 and the holding member 26 and is moved to a fastening position where a fastening state where relative rotation is impossible is achieved.

  On the other hand, when the engagement hydraulic pressure is discharged from the engagement hydraulic chamber 71 and the release hydraulic pressure is supplied to the release hydraulic chamber 72 when the piston 60 is at the engagement position, the piston 60 is urged in the release direction and moved. , The piston 60 is moved to the zero clearance position.

  The piston 60 is further urged and moved in the release direction against the second spring 93, and is moved to a position immediately before contact. Next, the piston 60 is urged and moved in the release direction against the first spring 92 and the second spring 93, and is moved to the release position.

Next, a supply oil passage for supplying hydraulic oil to the brake BR2 will be described.
A fastening supply oil passage L2 for supplying fastening hydraulic oil to the fastening hydraulic chamber 71 of the brake BR2 is formed in the second hub member 31 and the oil passage forming member 80. The release supply oil path L3 for supplying the release hydraulic oil to the release hydraulic chamber 72 of the brake BR2 and the lubrication supply oil path L1 for supplying the lubrication hydraulic oil to the friction plate 50 are located within the second hub member 31. Is formed.

  As shown in FIG. 7, the fastening supply oil passage L2 is provided on the vertical wall portion 32 of the second hub member 31 and extends in the radial direction. An axial oil passage 112 extending in the direction and connected to the radial oil passage 111, and an axial oil provided in the coupling portion 81 of the oil passage forming member 80 and extending in the axial direction and connected to the axial oil passage 112. A passage 113 and a radial oil passage 114 provided in the coupling portion 81, the connecting portion 83 and the fastening hydraulic chamber forming portion 82 of the oil passage forming member 80, extending in the radial direction and connected to the axial oil passage 113; The oil passage forming member 80 is provided in the fastening hydraulic chamber forming portion 82, and is formed by an axial oil passage 115 extending in the axial direction, connected to the radial oil passage 114, and opening to the fastening hydraulic chamber 71. I have.

  The radial oil passage 111 in the second hub member 31 is provided on the vertical wall portion 32 of the second hub member 31, opens on the lower surface of the valve body connection portion 34, and is connected to the valve body 5. The valve body 5 can supply a predetermined hydraulic pressure for fastening by supplying hydraulic fluid for fastening to the hydraulic chamber 71 for fastening through a supply oil passage L2 for fastening.

  The radial oil passage 114 of the oil passage forming member 80 is formed so as to extend radially inward from the outer peripheral surface of the coupling portion 81 of the oil passage forming member 80, and an opening of the radial oil passage 114 is formed on the outer peripheral surface of the coupling portion 81. A closing member 86 for closing the portion is attached.

  As described above, the release oil supply passage L3 is provided in the vertical wall portion 32 of the second hub member 31, extends radially, and opens in the release hydraulic chamber 72, as shown in FIG. It is constituted by a passage 121 and an axial oil passage 122 provided on the release boss portion 36 and extending in the axial direction and connected to the radial oil passage 121.

  The radial oil passage 121 in the second hub member 31 is provided on the vertical wall portion 32 of the second hub member 31, opens on the lower surface of the valve body connection portion 34, and is connected to the valve body 5. The valve body 5 can supply a release hydraulic oil to the release hydraulic chamber 72 through the release supply oil path L3 to supply a predetermined release hydraulic pressure.

  The axial oil passage 122 in the second hub member 31 is formed so as to extend in the axial direction from the end surface of the release boss portion 36 on the side opposite to the drive source to the drive source side. It is closed by screwing the bolt 6 into the screw hole 80b of the oil passage forming member 80.

  As described above, as shown in FIGS. 5 and 6, the lubricating supply oil passage L1 is provided on the vertical wall portion 32 of the second hub member 31 and extends in the radial direction. A circumferential oil passage 132 is provided on the vertical wall portion 32 of the hub member 31 and extends in an arc shape in the circumferential direction and is connected to the radial oil passage 131. The lubrication boss portion 33 is provided with a circumferential oil passage 132 extending in the axial direction. An axial oil passage 133 connected to the circumferential oil passage 132 is provided. The axial oil passage 133 is provided on the lubrication boss 33 and extends in the radial direction to be connected to the axial oil passage 133. A supply port 134 is provided on the outer peripheral surface of the fastening boss 35.

  In the automatic transmission 10, as shown in FIG. 13, 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 formed of a transmission case. 11 are arranged side by side in the circumferential direction below. The circumferential oil passage 132 constituting the lubricating supply oil passage L3 is connected to the radial oil passage 131 and extends along the circumferential direction in an arc shape on the side opposite to the radial oil passage 121 to form the radial oil passage 111. It extends to the non-radial oil passage 121 side.

  The five lubricating bosses 33 are respectively connected to the circumferential oil passage 132 and extend in the axial direction, and an axial oil passage 133 extending radially outward from the axial oil passage 133 to the outer peripheral surface of the lubricating boss 33. A supply port 134 that extends and supplies the lubricating hydraulic oil to the friction plate 50 is provided, and a plurality of supply ports 134 are provided side by side in the axial direction.

  The radial oil passage 131 of the second hub member 31 is provided on the vertical wall portion 32 of the second hub member 31, opens on the lower surface of the valve body connection portion 34, and is connected to the valve body 5. The valve body 5 can supply lubricating hydraulic oil to the plurality of friction plates 50 through the lubrication supply oil passage L1.

  In the brake BR2, the lubricating oil is supplied to the friction plate 50 from the outer peripheral surface of the lubrication boss 33 of the second hub member 31, and the heat generated by the friction plate 50 is cooled. The lubricating hydraulic oil supplied to the friction plate 50 moves to the inner peripheral surface of the outer cylindrical portion 41 of the drum member 40, and is prevented from moving and staying in the axial direction due to the rotation of the outer cylindrical portion 41 of the drum member 40. Have been.

  The five axial oil passages 133 in the second hub member 31 are formed so as to extend in the axial direction from the end face of the lubrication boss 33 on the side opposite to the drive source to the drive source side. The screw is closed by screwing the fastening bolt 4 into the screw hole 81a of the oil passage forming member 80.

  As shown in FIG. 11, a lubricating notch 27 is formed in the inner cylindrical portion 23 of the first hub member 21 in a circumferential direction corresponding to the lubricating boss 33 of the second hub member 31. ing. The lubricating boss 33 of the second hub member 31 is arranged corresponding to the lubricating notch 27 of the inner cylindrical portion 23 of the first hub member 21, and is supplied from the supply port 134 to the friction plate 50 through the lubricating notch 27. Hydraulic oil can be supplied.

Next, the operation of the brake BR2 will be described.
FIG. 19 is a sectional view showing the brake in the released state and the state immediately before contact, and FIG. 20 is a sectional view showing the brake in the zero clearance state and the engaged state. FIGS. 19 (a), 19 (b), 20 (a), and 20 (b) show the brake in the released state, the state immediately before contact, the zero clearance state, and the engaged state, respectively. 19 and 20 show an enlarged view of a main part of the brake BR2 shown in FIG.

  In FIG. 19A, the fastening hydraulic pressure is discharged from the fastening hydraulic pressure chamber 71, and the release hydraulic pressure is supplied to the release hydraulic pressure chamber 72. 93 shows a released state of the brake BR2 in a release position where the piston 60 is moved in the release direction on the side opposite to the driving source by compressing the piston 93 and the plurality of friction plates 50 are released.

  When the brake BR2 is engaged, the release hydraulic pressure is discharged from the release hydraulic chamber 72 in the release state shown in FIG. 19A, and the piston 60 is moved through the urging receiving member 100 as shown in FIG. Under the urging force of the first spring 92 and the second spring 93, the second holding plate 95 is moved in the fastening direction on the drive source side until the second holding plate 95 contacts the stopper member 37, and the position of the piston 60 is moved to the plurality of friction plates 50. The position just before the contact, which is immediately before the contact, is set, and the brake BR2 is in the state immediately before the contact.

  When the second holding plate 95 comes into contact with the stopper member 37 in the state immediately before the contact shown in FIG. 19B, the piston 60 is moved by the second spring 93 via the urging receiving member 100 as shown in FIG. Is moved in the fastening direction to the free length of the second spring 93 only by the urging force of the second spring 93, and the position of the piston 60 is in a state of contacting or almost in contact with the friction plates 50 without pressing the plurality of friction plates 50. The brake BR2 enters the zero clearance state where the zero clearance state is set to the zero clearance state.

  When the fastening hydraulic pressure is supplied to the fastening hydraulic chamber 71 in the zero clearance state shown in FIG. 20A, the piston 60 is supplied to the fastening hydraulic chamber 71 as shown in FIG. The piston 60 is moved by being urged in the fastening direction by the fastening hydraulic pressure, the piston 60 presses the plurality of friction plates 50, and the position of the piston 60 becomes the fastening position where the plurality of friction plates 50 cannot be relatively rotated, and the brake BR2 is engaged. State.

  On the other hand, when the brake BR2 is released, in the engagement state shown in FIG. 20B, the engagement hydraulic pressure is discharged from the engagement hydraulic pressure chamber 71 and the release hydraulic pressure is supplied to the release hydraulic pressure chamber 72, and the piston 60 is released. Due to the release hydraulic pressure supplied to the hydraulic chamber 72, the hydraulic chamber 72 is urged and moved in the release direction on the side opposite to the drive source, and passes through the zero clearance state shown in FIG. 20A and the state immediately before contact shown in FIG. 19 (a).

  As described above, the brake BR2 is slip-controlled when the vehicle starts moving. When the brake BR2 is engaged, a hydraulic pressure lower than the hydraulic pressure for engagement is supplied to the hydraulic pressure chamber 71 for engagement, and after the plurality of friction plates 50 are brought into a slip state, the hydraulic pressure for engagement is supplied to the hydraulic pressure chamber 71 for engagement to provide a plurality of hydraulic pressures. The friction plate 50 is fastened. On the other hand, when the brake BR2 is released, a hydraulic pressure lower than the release hydraulic pressure is supplied to the release hydraulic chamber 72, and after the plurality of friction plates 50 are brought into the slip state, the release hydraulic pressure is supplied to the release hydraulic chamber 72. The fastening of the plurality of friction plates 50 is released.

  When the brake BR2 is engaged and released, the lubricating oil is supplied to the plurality of friction plates 50 through the lubrication supply oil passage L1, and when the brake BR2 is slip-controlled, the plurality of friction plates are supplied through the lubrication supply oil passage L1. The lubricating hydraulic oil is supplied to 50.

  As described above, in the automatic transmission 10 according to the present embodiment, the first and second springs 92 and 93 that apply the urging force to the piston 60 from the release position to the position immediately before contact and the zero clearance position respectively overlap in the radial direction. A plurality of first springs 92 are provided in the circumferential direction, and a stopper member 37 is attached to the vertical wall portion 32 connected to the transmission case 11.

  A plurality of stopper members 37 extend in the circumferential direction along the circumference on which the center axis of the first spring 92 is disposed on the side opposite to the vertical wall portion 32 side, and receive only the urging force of the first spring 92. A regulating portion 37b is provided. Thereby, the plurality of regulating portions 37b provided on the single stopper member 37 can be machined with high precision by the same machining, and the first and second springs 92 are moved from the release position to the position immediately before the contact. 93 can be moved with high accuracy.

  When the stopper member 37 is formed integrally with the vertical wall portion 32 coupled to the transmission case 11, the vertical wall portion 32 is provided at a position radially overlapping with the stopper member 37 and at a position different in the circumferential direction. When the plurality of lubrication supply portions 33 and the like are integrally formed, the end surfaces of the plurality of restriction portions 37b of the stopper member 37 may not be able to be processed by the same machining by the lubrication supply portions 33 and the like. By attaching a separate stopper member 37 to the vertical wall portion 32 coupled to the transmission case 11, the end faces of the plurality of restricting portions 37b of the stopper member 37 are machined by the same machining to form the plurality of restricting portions 37b. The position accuracy of the end surface of the piston 60 can be improved, and the piston 60 is accurately moved from the release position to the position immediately before the contact by the first and second springs 92 and 93. Door can be.

  Further, since the regulating portion 37b provided on the stopper member 37 extends in the circumferential direction along the circumference where the center axis of the first spring 92 is arranged, it is possible to regulate the radially central side of the first spring 92. The urging force of the first spring 92 is more accurately received than when only the radially outer side or the radially inner side of the first spring 92 is regulated. It can be moved with high accuracy only by the spring 93.

  Accordingly, in the automatic transmission 10 including the friction fastening element BR2 in which the first and second springs 92 and 93 for applying the urging force to the piston 60 are arranged at the positions where they are radially overlapped, the piston 60 is moved from the release position. The first and second springs 92 and 93 can accurately move to the position immediately before the contact, and can be accurately moved only by the second spring 93 when moving from the position immediately before the contact in the fastening direction.

  Further, the friction fastening element BR2 is a brake BR2 in which a plurality of friction plates 50 are arranged between the hub member 20 connected to the transmission case 11 and the drum member 40 connected to the predetermined rotating member R3. As a result, in the automatic transmission 10 provided with the brake BR2, the lubricating hydraulic oil supplied to the friction plate 50 of the brake BR2 is prevented from staying due to the rotation of the drum member 40, and the friction oil between the friction plates Can be suppressed.

  The hub member 20 of the brake BR2 includes a first hub member 21 that is spline-engaged with the transmission case 11, and a second hub member 31 that is fitted with the transmission case 11, and a stopper member 37 is attached. The vertical wall portion 32 is provided on the second hub member 31. Thereby, the second hub member 31 can be fitted and fixed to the transmission case 11, the vertical wall portion 32 to which the stopper member 37 is attached is fixed to the transmission case 11, and the piston 60 contacts from the release position. The first and second springs 92 and 93 can be moved to the immediately preceding position with higher accuracy.

  Further, the second hub member 31 includes a plurality of lubrication supply portions 33, and the first and second springs 92 and 93 are disposed at positions overlapping the plurality of lubrication supply portions 33 in the radial direction. Accordingly, the first and second springs 92 and 93 can be made more compact in the radial direction than when they do not overlap the lubrication supply unit 33 in the radial direction.

  Further, the stopper member 37 is formed in a substantially annular shape, and is fitted to the mounting groove 32 e provided in the vertical wall portion 32 and attached to the vertical wall portion 32, so that the vertical wall portion coupled to the transmission case 11 is formed. The stopper member 37 can be attached to the 32 relatively easily.

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

  As described above, according to the present invention, the piston is released in the automatic transmission including the frictional fastening element in which the first and second springs for applying the urging force to the piston are arranged at the positions overlapping in the radial direction. Since the first and second springs can accurately move from the position to the position immediately before the contact by the first and second springs and can be precisely moved by the second spring only when moving from the position immediately before the contact to the fastening direction, this kind of automatic transmission It may be suitably used in the field of manufacturing technology of a machine or a vehicle on which it is mounted.

Reference Signs List 10 automatic transmission 11 transmission case 20 hub member 21 first hub member 23 inner cylindrical portion 31 second hub member 32 vertical wall portion 32e of second hub member mounting groove 33 lubrication boss 37 stopper member 37a mounting portion 37b Regulating portion 40 drum member 41 outer cylindrical portion 50 friction plate 60 piston 92 first spring 93 second spring BR2 second brake L1 lubrication supply oil passage

Claims (5)

A plurality of friction plates disposed in a transmission case; a piston for fastening the plurality of friction plates; a first spring for applying a biasing force to the piston in a fastening direction from a release position to a position immediately before contact; An automatic transmission having a frictional fastening element having a second spring for applying a biasing force in a fastening direction from the release position to the zero clearance position,
The first spring and the second spring are arranged at positions overlapping in a radial direction and different positions in a circumferential direction,
A plurality of the first springs are provided in the circumferential direction such that a center axis of the first spring is arranged at different positions in the circumferential direction on the same circumference,
When the piston is moved from the position immediately before the contact in the fastening direction to the vertical wall portion that is connected to the transmission case and extends in the radial direction, the urging force of the first spring is prevented from acting on the piston. A stopper member that allows the urging force of the second spring to act is attached,
The stopper member is provided on an attachment portion attached to the vertical wall portion, and is provided on a side opposite to the vertical wall portion side, and extends in a circumferential direction along a circumference on which a center axis of the first spring is arranged. An automatic transmission, comprising: a plurality of restricting portions that receive only the urging force of the first spring. The friction fastening element has a hub member coupled to the transmission case, and a drum member coupled to a predetermined rotating member, and the plurality of friction plates are disposed between the hub member and the drum member. The automatic transmission according to claim 1, wherein the automatic transmission is a brake disposed. The hub member includes a first hub member that includes a cylindrical portion with which the friction plate is spline-engaged and is spline-engaged with the transmission case. A second hub member fitted to the machine case,
The automatic transmission according to claim 2, wherein the vertical wall portion is provided on the second hub member. The second hub member includes a plurality of lubrication supply portions that have a lubrication supply oil passage that supplies hydraulic oil for lubrication to the friction plate and extend in the axial direction from the vertical wall portion,
4. The automatic transmission according to claim 3, wherein the first spring and the second spring are arranged at positions overlapping radially with the plurality of lubrication supply units and at positions different in the circumferential direction. 5. Machine. The stopper member is formed in a substantially annular shape,
The vertical wall portion is provided with a mounting groove recessed from the stopper member side to the opposite side to the stopper member side,
The automatic transmission according to any one of claims 1 to 4, wherein the stopper member is fitted to the mounting groove portion and attached to the vertical wall portion.

Images