JP2001221254A - Clutch structure for automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce an overall axial direction length of a clutch and to prevent oil leakage from a cylinder housing a piston for pressing a friction plate. SOLUTION: A clutch drum 80 comprises a second member 81 having a hub part 82, an outer cylinder 84, and a disc part 83, a first member 85 having a drum part 87 and a vertical wall 86 welded to a corner from the disc part 83 to the outer cylinder, and a third member 100 having a cylinder part 102 folded back inside the hub part. The piston 96 is arranged in the cylinder 95 formed by the first member 85. An extended part 112 of the piston is offsetted toward the vertical wall 86 side, so the friction plate 93 and a clutch hub 90 can also be gathered to the vertical wall side for reducing a length of the drum part 87. Oil leakage also does not occur because the cylinder is formed by the first member. The clutch drum is sandwiched and supported from inside and outside by the cylinder part 102 and the hub part 82 at a protruding part 22 of an intermediate bulkhead so tilting also does not occur.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch structure for a transmission mechanism of an automatic transmission.

[0002]

2. Description of the Related Art In an automatic transmission mounted on a vehicle or the like, a plurality of gears are realized by combining a planetary gear mechanism and a plurality of clutches or the like as fastening elements, and combining these fastening and releasing. In the clutch, a plurality of friction plates are arranged between a clutch drum connected to one rotation member and a hub connected to another connection member, and the clutch drum and the hub are fastened / released by pressing / releasing the friction plates.

[0003] In an automatic transmission, a plurality of such clutches are generally provided. If the required transmission torque is large, a friction plate corresponding to this is provided near the outer wall of the transmission case. And ensure a large distance from the rotation axis. Therefore, the outer diameter of the clutch drum accommodating the friction plate inside also increases.
The clutch drum is manufactured by molding from a plate material to reduce its weight. A large-sized clutch drum is manufactured by being divided, for example, as disclosed in Japanese Patent Publication No. 6-19191.

In the device disclosed in this publication, as shown in FIG. 5, a clutch drum 150 is formed by a vertical wall 151 and a drum portion 1.
52 and an inner cylinder 153. The vertical wall 151 has a flange portion 154 extending in the axial direction on the outer periphery, and a hole 15
5 In addition, the end of the drum section 152 has a vertical wall 151.
And extends cylindrically in the axial direction. The inner cylinder 153 has one end coupled to the edge of the hole 155 in the vertical wall, and extends in the same direction as the drum 152.
And a second cylindrical portion 158 connected to the other end of the first cylindrical portion via a vertical wall 157 and having a smaller diameter than the first cylindrical portion 156 and further extending in the axial direction.

The vertical wall 151 and the drum portion 152 are welded to each other from the outside at the base of a flange portion 154 of the vertical wall, and the inner cylinder 15 is formed.
Reference numeral 3 denotes one end of the first cylindrical portion 156 inserted into the hole 155 of the vertical wall 151, and is welded from the outside along the periphery of the hole 155. The first cylindrical portion 156 is rotatably supported on a fixed side member 161 projecting in the axial direction of the transmission case 160, and the second cylindrical portion 158 is spline-coupled to the rotating shaft 164.

In a space defined by the vertical wall 151 and the inner cylinder 153, a cylinder 159 having an inner peripheral surface of the flange portion 154 and an outer peripheral surface of the first cylindrical portion 156 as a sliding surface of the piston 165 is formed. 165 presses the friction plate 166. The first cylinder 156 has a cylinder 159.
Oil hole 1 opening to the hydraulic chamber formed by piston and piston 165
67 is provided, and a ring groove 168 is formed in the fixed member 161 so as to communicate with the oil hole 167 so that oil is supplied. Seal rings 169 are provided on both axial sides of the ring groove 168.

[0007]

However, in the conventional clutch drum as described above, the flange 154 on which the drum 152 overlaps serves as a sliding surface of the piston 165, so that the stroke length of the piston 165 is reduced. In order to ensure this, the flange portion 154 needs a predetermined axial length, and as a result, there is a limit in moving the friction plate 166 closer to the vertical wall 151 side. Therefore, there is a problem that it is difficult to reduce the axial length of the entire clutch.

Further, the inner cylinder 153 of the clutch drum 150 is attached to the first cylindrical portion 15
6 is merely fitted on the outer periphery of the fixed side member 161, there is a possibility that the vertical wall 151 and the drum part 152 connected to the vertical wall 151 may fall due to the force acting on the first cylindrical part 156 from the seal ring 169, We must allow for this. Furthermore, the vertical wall 151 and the inner cylinder 1
Since 53 is welded and joined at the periphery of the hole 155 of the vertical wall, which is a part forming the hydraulic chamber of the cylinder 159, oil leakage from the joint may occur depending on the welding quality.

The oil is introduced from the oil passage 170 to the space inside the inner cylinder 153. However, since the connection between the second cylinder 158 and the rotary shaft 164 is spline-coupled, the spline portion is connected to the spline. Since the diameter is adjusted to be large or the tooth surface is aligned, there is a gap in either the tooth surface or the diameter, and there is also a problem that oil easily leaks from the space through the spline portion in the axial direction. Therefore, in view of the above problems, the present invention can reduce the axial length of the entire clutch, eliminate the possibility of oil leakage, and easily define an oil passage around the clutch drum. The purpose is to provide.

[0010]

According to a first aspect of the present invention, there is provided a clutch in which a friction plate provided between a clutch drum and a clutch hub is pressed by a piston to connect the clutch drum to the clutch hub. A first member, a second member of which a clutch drum is sequentially connected from the outside to the inside;
The first member is formed integrally with a drum portion having a spline meshing with the friction plate and a vertical wall extending from one end of the drum portion in the inner diameter direction, and the second member is an outer peripheral portion of the piston. A first cylindrical portion forming a sliding surface of the first cylindrical portion, a second cylindrical portion forming a sliding surface of the inner peripheral portion of the piston,
And a first disk portion connecting the first cylindrical portion and the second cylindrical portion is integrally formed to form a hydraulic chamber of the piston, and the third member has a coaxial smaller diameter than the second cylindrical portion of the second member. The clutch drum has three cylindrical portions, and the clutch drum is supported by sandwiching a cylindrical support shaft between the second cylindrical portion and the third cylindrical portion.

First, the cylinder in which the piston is housed is
Since the first cylindrical portion, the first disk portion, and the second cylindrical portion are formed by the second member integrally formed, even if the clutch drum is composed of a plurality of members, oil leakage may occur on the cylinder side. Absent. Also, the second cylindrical portion of the clutch drum and the third
Since the cylindrical part sandwiches the support shaft from both the outer diameter side and the inner diameter side,
Prevents the clutch drum from falling down and improves the accuracy of holding the posture.

According to a second aspect of the present invention, in particular, the vertical wall of the first member of the clutch drum is welded at a bending angle from the first disk portion to the first cylindrical portion of the second member, and the first disk portion and the first disk portion are vertically welded. The wall extends substantially straight in the radial direction. When integrally forming the first disk portion and the drum portion including the first cylindrical portion forming the sliding surface of the piston, the drum portion starts from the tip of the first cylindrical portion. hand,
Since the drum portion starts from the position of the first disk portion in the axial direction, the overall length of the clutch drum can be reduced.

According to a third aspect of the present invention, there is provided the clutch drum of the second aspect.
The length of the first cylindrical portion of the member was set to a limit corresponding to the required stroke of the piston, and the piston was provided with an extension extending radially across the vicinity of the distal end of the first cylindrical portion. By disposing the friction plate on the outer diameter side that can be pressed by the extension portion, a cancel pressure chamber can be provided on the back side of the piston.

According to a fourth aspect of the present invention, a pressing portion extending in the direction of the friction plate is provided at the outer diameter end of the extension portion of the piston after offsetting toward the vertical wall side of the first member after crossing the vicinity of the tip of the first cylindrical portion. It had it. By offsetting the extension toward the vertical wall, the friction plate and the clutch hub meshing with the friction plate can be moved toward the vertical wall, and the axial size of the clutch is reduced.

According to a fifth aspect of the present invention, a flange is formed on an opposite side of the vertical wall of the piston to extend in an axial direction, and a spring receiver for supporting a return spring for biasing the piston has an inner peripheral surface of the flange and the second member. The inner peripheral surface of the first cylindrical portion of the second member and the inner peripheral surface of the flange of the piston have substantially the same diameter, and the pressure receiving area on both surfaces of the piston is reduced. It is assumed that they are substantially equal. Since the respective pressure receiving areas in the pressure chamber sandwiching the piston and the cancel pressure chamber are substantially equal, a cancel effect with good responsiveness can be obtained.

According to a sixth aspect of the present invention, a bush is provided between the support shaft and the third cylindrical portion of the third member of the clutch drum.
The bush defines an oil passage in a space between the support shaft and the clutch drum. Due to the presence of the bush,
Since the flow of the oil in the axial direction beyond the bush is prevented, the oil is efficiently supplied to the lubrication-required portion communicating with the oil passage.

According to a seventh aspect of the present invention, there is provided the clutch drum of the second aspect.
The member has a second disk portion extending in the radial direction from the end of the second cylindrical portion, and the third member has a third disk portion extending in the radial direction from the end of the third cylindrical portion. The member and the third member are joined by welding the second disk portion and the third disk portion, particularly at a radially intermediate portion between the second cylindrical portion and the third cylindrical portion. Since the welding portion is located outside the vicinity of the second cylindrical portion and the third cylindrical portion, there is no possibility that the roundness of the second cylindrical portion or the third cylindrical portion is impaired by thermal distortion.

In the invention according to claim 8, a brake band constituting a brake is arranged on the outer periphery of the drum portion of the first member. Since the first member has the drum portion and the vertical wall integrally formed and has no welded portion, the brake band can be disposed over the entire width of the drum portion, and the outer peripheral surface of the drum portion is effectively used.

[0019]

Embodiments of the present invention will be described below with reference to examples. First, FIG. 1 is a skeleton diagram showing a transmission mechanism in an embodiment to which the present invention is applied. A first planetary gear mechanism G1 and a second planetary gear mechanism G2 are provided in this order from the input side connected to the torque converter T along the axis of the input shaft IN supported by the transmission case. In the drawings, since each member is configured symmetrically with respect to the axis, the lower half of the axis is not shown.

The first planetary gear mechanism G1 is a single pinion type, and the second planetary gear mechanism G2 is a Ravigneaux type. The first planetary gear mechanism G1 has a first
A sun gear S1, a first pinion P1, a first carrier D1, and a first ring gear R1. The first pinion P1 rotatably supported by the first carrier D1 is located between the first sun gear S1 and the first ring gear R1. Are engaged with each other.

The second planetary gear mechanism G2 includes a second sun gear S2 and a third sun gear S3, a second pinion P2 and a third pinion P3, a second carrier D2 and a second ring gear R2.
Consists of The second pinion P2 and the third pinion P3 are the second
The second pinion P2 is rotatably supported by the carrier D2 and meshes with each other. The second pinion P2 is further positioned between the second sun gear S2 and the second ring gear R2 and meshes with each other. Further, the third pinion P3 is a third sun gear S3.
And are engaged.

The input shaft IN is integrally connected to a first ring gear R1 of the first planetary gear mechanism G1 by a first rotating member M1, and a second planetary gear is connected by a second rotating member M2 via a third clutch C3. Second carrier D of gear mechanism G2
2 can be connected. The first sun gear S1 of the first planetary gear mechanism G1 is fixed to the transmission case by a fourth member M4. The first carrier D1 is
In order from the third rotating member M3, the first clutch C1, the fifth clutch
The third planetary gear mechanism G2 has a third
It can be connected to the sun gear S3.

The second sun gear S of the second planetary gear mechanism G2
The second rotation member 2 can be connected to the third rotation member M3 by the sixth rotation member M6 via the second clutch C2. Sixth
The rotating member M6 can also be fixed to the transmission case by the second brake B2. A seventh rotating member M7 is integrally connected to the second carrier D2 of the second planetary gear mechanism G2, and the seventh rotating member M7 is fixed to the transmission case by a first brake B1 and a one-way clutch provided in parallel. It is possible. The one-way clutch is engaged with the rotation input in the direction opposite to the rotation of the input shaft IN, that is, fixes the seventh rotation member M7. The output gear OUT is integrally connected to the second ring gear R2 of the second planetary gear mechanism G2 via the eighth rotating member M8.

In the above configuration, the first as a fastening element
To the third clutch C1 to C3, the first and second brakes B1,
By engaging two of B2 and the one-way clutch, six forward speeds and one reverse speed are obtained as shown in FIG. In the figure, a circle indicates a fastening element to be fastened. The details of the rotation transmission path at each gear are described in Japanese Patent Application No. 11-29
No. 7574 is cited and omitted here.

FIG. 3 is a sectional view showing a specific structure around the first planetary gear mechanism G1 and the first and second clutches C1 and C2 in the transmission mechanism. A protruding cylinder 6 extends from a pump cover 4 on the torque converter side (not shown) of the transmission case 1, and a stator shaft 7 is fixed through the protruding cylinder 6. The input shaft 10 (IN) is supported on the stator shaft 7. Further, an intermediate partition 2 extends from the transmission case 1, and is provided at its central portion with protrusions 21 and 22 extending to both sides in the axial direction and through which the input shaft 10 and others penetrate.

A first planetary gear mechanism G1 is disposed at a position corresponding to the end of the stator shaft 7 in the axial direction from the pump cover 4 toward the intermediate partition 2, and the first sun gear S
1 is spline-coupled to the tip of the stator shaft 7. In a space defined by the pump cover 4 and the intermediate partition 2, a first clutch C1 is disposed between the first planetary gear mechanism G1 and the pump cover 4, and the first planetary gear mechanism G1 is sandwiched therebetween. And the second clutch on the side opposite to the first clutch C1.
The clutch C2 is arranged.

The first ring gear R1 of the first planetary gear mechanism G1 is welded to the outer peripheral edge of the disk member 30 having the cylindrical portion 31 at the center, and the cylindrical portion 31 is spline-connected to the input shaft 10. Further, the first pinion P1 is the first carrier D
1 are supported by a first carrier plate 41 and a second carrier plate 42. Thrust bearings 13 and 14 are provided between the disc member 30 and the first carrier plate 41 and between the first carrier plate 41 and the first sun gear S1, respectively. Furthermore, the first
A thrust washer 12 is provided between the sun gear S1 and the end surface of the protruding cylindrical portion 6 of the pump cover 4.

The clutch drum 50 of the first clutch C1
Is composed of a first member 55 and a second member 51.
The second member 51 includes a hub portion 52 of an inner cylinder, a disk portion 53 extending outward from the hub portion 52, and an outer cylinder 5 connected to the disk portion 53.
Consists of four. The first member 55 is formed by the disk portion 5 of the second member 51.
The vertical wall 56 is joined to the outer cylinder 54 at a turning angle and extends further outward. The drum wall 57 is connected to the vertical wall 56.

The hub 52 is supported by the protruding cylinder 6 of the pump cover 4 via a bush 58. The end of the hub 52 of the clutch drum 50 is connected to the first planetary gear mechanism G1.
And the second carrier plate 42 is connected by a spline connection. A thrust bearing 15 is provided between the disk part 53 and the pump cover 4.

A step 59 is formed at the corner of the second member from the disk portion 53 to the outer cylinder 54, and the first step is formed on the step.
The inner peripheral edge of the vertical wall 56 of the member 55 is butt-welded. Thereby, the vertical wall 56 of the first member looks like the disk portion 53 of the second member 51 is extended outward, and both are substantially straight.

The drum portion 57 extends toward the first planetary gear mechanism G1. A clutch hub 60 is provided facing the inside of the drum portion 57, and a plurality of friction plates 63 alternately mesh with splines 61 and 62 formed on the inner periphery of the drum portion 57 and the outer periphery of the clutch hub 60. Clutch hub 60
Has an inner diameter substantially equal to the outer diameter of the outer cylinder 54 of the second member.

The second member 51 of the clutch drum 50 includes
A ring-shaped cylinder 64 is formed between the outer peripheral surface of the hub 52 and the inner peripheral surface of the outer cylinder 54, and a piston 65 is slidably disposed in the cylinder 64. Cylinder 64 and piston 6
By supplying oil to the hydraulic chamber formed between the pistons 5, the piston 65 can stroke in the axial direction to press the friction plate 63. A spring receiver 66 is attached to the outer periphery of the hub 52 by a snap ring 67, and a return spring 68 is provided between the piston 65 and the spring receiver 66.

A flange 69 extends on the spring receiver 66 side of the piston 65 and serves as a sliding surface for the spring receiver 66. A cancel pressure chamber is formed between the piston 65 and the spring receiver 66. The inner peripheral surface of the outer cylinder 54 and the inner peripheral surface of the flange 69 have substantially the same diameter, and the pressure receiving areas of the piston 65 in the hydraulic chamber and the cancel pressure chamber are equal.

The piston 65 further includes an extension 74 extending radially outward from a portion immediately near the distal end of the outer cylinder 54 while sitting on the disk portion 53 of the second member 51. The extending portion 74 is offset toward the vertical wall 56 side of the first member after traversing the distal end portion of the outer cylinder 54 to form a predetermined axial gap with the end portion of the clutch hub 60. And
The pressing portion 75 extends from the outer diameter end of the extension portion 74 to be folded back to the friction plate 63. The top end of the outer cylinder 54 is notched in the figure to avoid interference with the offset extension 74. The inner peripheral surface of the outer cylinder 54 is a sliding surface of a piston 65 as a cylinder 64 up to its tip, and the lower corner of the tip is chamfered to a minimum.

The clutch hub 60 of the first clutch C1 extends outside the first planetary gear mechanism G1 and is connected to the disk 71 of the rotating member 70. The rotating member 70 has its cylindrical portion 7
The second planetary gear 2 extends through the intermediate partition 2 in the axial direction on the input shaft 10, and the distal end of the cylindrical portion 72 protrudes from a cylindrical portion (third cylindrical portion) 102 of a third member 100 described later. The mechanism G2 is spline-coupled to a third sun gear S3 (not shown). The rotating member 70 constitutes a fifth rotating member.

The clutch drum 80 of the second clutch C2
The first member 85, the second member 81, and the third member 100
It is composed of The second member 81 includes an inner cylinder hub portion (second cylindrical portion) 82, a disk portion 83 extending outward from one end of the hub portion 82, and an outer cylinder (first cylindrical portion) 84 connected to the disk portion 83. , An inner disk portion 89 extending inward from the other end of the hub portion 82.

The first member 85 is formed by the disk portion 8 of the second member 81.
3 and a vertical wall 86 extending further outward.
And a drum part 87 connected to The third member 100 has a disk portion 101 joined to the inner disk portion 89 of the second member 81.
And a cylindrical portion 102 extending in the axial direction.

The vertical wall 86 of the first member 85 is
The disk portion 83 and the vertical wall 86 are welded to the corners of the outer cylinder 84 from the disk portion 83 so that the disk portion 83 and the vertical wall 86 extend substantially straight in the radial direction in cross section. The second member 81 and the third member 100 are formed by welding the inner peripheral edge of the inner disk portion 89 and the outer peripheral edge of the disk portion 101,
The inner disk portion 89 and the disk portion 101 also extend substantially linearly in the radial direction.

The hub portion 82 of the second member 81 has a sleeve 88
And is supported by the protruding portion 22 of the intermediate partition 2. Further, the third member 100 is disposed so as to penetrate the protruding portion 22 of the intermediate partition 2, and the bush 11 is provided between the cylindrical portion 102 and the protruding portion 22.

A clutch hub 90 is provided facing the inside of the drum portion 87, and a plurality of friction plates 93 are alternately meshed with splines 91 and 92 formed on the inner periphery of the drum portion 87 and the outer periphery of the clutch hub 90. . The clutch hub 90 extends outside the clutch hub 60 of the first clutch C1,
An end has a rising portion 94 extending outward. The rising portion 94 is engaged with the end of the drum portion 57 of the clutch drum 50 of the first clutch C1, and the second clutch C
The second clutch hub 90 rotates integrally with the clutch drum 50. The brake band 8 constituting the second brake B2 is disposed on the outer peripheral surface of the drum portion 87 of the clutch drum 80 so as to be engageable.

The third member 100 is supported on a rotating member 70 extending along the input shaft 10 and has a cylindrical portion 1 extending in the axial direction.
02 is connected to the second sun gear S of the second planetary gear mechanism G2.
Connect with 2. The third member 100 constitutes a sixth rotating member.

The second member 81 of the clutch drum 80 includes:
A ring-shaped cylinder 95 is formed between the outer peripheral surface of the hub portion 82 and the inner peripheral surface of the outer cylinder 84, and a piston 96 is slidably disposed in the cylinder 95. Cylinder 95 and piston 9
By supplying oil to the hydraulic chamber formed between the pistons 6, the piston 96 can stroke in the axial direction to press the friction plate 93. A spring receiver 98 is attached to the outer periphery of the hub 82 by a snap ring 99 (see FIG. 4), and a return spring 97 is provided between the piston 96 and the spring receiver 98.

A flange 110 extends on the spring receiver 98 side of the piston 96, and serves as a sliding surface of a seal lip on the outer peripheral edge of the spring receiver 98. A cancel pressure chamber is formed between the piston 96 and the spring receiver 98. Is done. The inner peripheral surface of the outer cylinder 84 and the inner peripheral surface of the flange 110 have substantially the same diameter, and the pressure receiving areas of the piston 96 in the hydraulic chamber and the cancel pressure chamber are equal.

The piston 96 further includes an extension 112 extending radially outward from a portion immediately near the distal end of the outer cylinder 84 while sitting on the disk portion 83 of the second member 81.
After the extension 112 crosses the distal end of the outer cylinder 84, the first
The clutch hub 90 is offset to the vertical wall 86 side of the member.
A predetermined gap in the axial direction is formed between the end portion and the end portion. A pressing portion 113 extends from the outer diameter end of the extension portion 112 toward the friction plate 93. The top end of the outer cylinder 84 is notched in the figure to avoid interference with the offset extending portion 112. The inner peripheral surface of the outer cylinder 84 extends to the tip of the cylinder 9
5 is a sliding surface of the piston 96, and the lower corner of the tip is chamfered to a minimum.

The thrust bearing 16 is provided between the end face of the projecting portion 22 of the intermediate partition 2 and the disk portion 101 of the third member 100.
Further, thrust bearings 17 and 18 are provided between the disk portion 101 and the disk portion 71 of the rotating member 70 and between the disk portion 71 and the disk member 30, respectively.

A plurality of rows of ball bearings 117 for supporting the output gear 115 are provided on the outer periphery of the projection 21 of the intermediate partition 2. A nut 118 having a threaded portion screwed into the inner diameter side of the protruding portion 21 presses the inner race of the ball bearing 117 against the wall surface of the intermediate partition 2 via a washer at the flange portion 119.

The second ring gear R2 of the second planetary gear mechanism G2 extends toward the output gear 115 and is welded to the annular member 120. The output gear 115 has a projection 116 extending toward the second planetary gear mechanism G2. Have. Then, the outer periphery of the protrusion 116 and the inner periphery of the annular member 120 are spline-coupled,
The second ring gear R2 and the output gear 115 are connected. Here, the annular member 120 constitutes an eighth rotating member.

An oil passage 122 is formed in the input shaft 10 at the axis thereof, and an oil hole for supplying lubricating oil from the oil passage 122 to each of the bearings and the engagement portion is provided. The oil from the oil hole 123 passes through the oil hole 124 provided in the cylindrical portion 72 of the rotating member 70 and the oil hole 125 provided in the cylindrical portion 102 of the clutch drum 80, and the thrust between the second sun gear S2 and the nut 118 Lubricate the bearing 19.

The oil from the oil hole 126 is supplied to the rotating member 70
The thrust bearing 18 between the (disk portion 71) and the disk member 30 is lubricated. Further, the third member 100 (disc portion 101) and the rotating member 70 (disc portion 7) of the clutch drum 80 pass through an oil hole 127 provided in the cylindrical portion 72 of the rotating member 70.
Lubricate the thrust bearing 17 between 1). Third
The bush 11 is lubricated through an oil hole 128 provided in the cylindrical portion 102 of the member 100, and the third member 100
Lubricating the thrust bearing 16 between the disc 101 and the end face of the projection 22. The oil from the oil hole 129 lubricates the thrust bearing 13 and the first pinion P1 and the first sun gear S via the thrust bearing 14.
1. Lubricate the meshing part.

The oil hole 130 is provided between the first pinion P1 and the first sun gear S1 via the thrust washer 12 between the first sun gear S1 and the protruding cylinder 6 from the oil hole 130 provided in the stator shaft 7, In addition, the space between the hub portion 52 and the sleeve 58 of the clutch drum is lubricated. The oil that has lubricated the above-described thrust bearings, meshing portions, and the like further flows outward, and lubricates necessary portions.

FIG. 4 is an enlarged view showing a supporting portion of the clutch drum 80 and a bearing lubrication structure of the output gear 115. The intermediate partition 2 has an oil hole 14 at a radial position corresponding to the ball bearing 117 supporting the output gear 115.
0 is provided through. Projection 22 of intermediate partition 2
Are formed with oil grooves 141 and 142 communicating from the end surface to the outer peripheral surface supporting the sleeve 88, and the oil groove 141 on the end surface is directed toward the radial center.

The oil groove 142 is formed on the wall of the intermediate partition 2 by the oil hole 14.
It is connected to an oil groove 143 extending to zero. Oil grooves 141 and 14 extending from the end face of the protruding portion 22 to the oil hole 140
2 and 143 can be formed by casting when the transmission case 1 is manufactured. The oil groove 142 on the outer peripheral surface of the protruding portion 22 is covered by the bush 88 to form an oil passage having a closed cross section.

As a result, the oil guided from the oil passage 122 of the input shaft 10 through the oil holes 126, 127, 128 to the space between the protruding portion 22 and the cylindrical portion 102 of the rotating member clutch drum 80 is transferred to the oil groove. The oil passes through 141, 142, 143 to reach the oil hole 140 of the intermediate partition wall 2, from which it is guided to the protruding portion 21 side to lubricate the ball bearing 117 supporting the output gear 115. At this time, the oil also lubricates the bush 11 provided between the cylindrical portion 102 and the protruding portion 22,
The flow to the left in the figure is substantially prevented by the bush 11, and the oil guided from the oil hole 128 to the outer peripheral side of the cylindrical portion 102 receives the thrust bearing 16 and the oil groove 141,
142, 143 and is efficiently supplied to the ball bearing 117 of the output gear 115.

The present embodiment is constructed as described above, and the clutch drums 50 and 80 are formed of the first outer drum including the drum portion and the vertical wall.
Cylinders 64 and 95 for pistons 65 and 96 which press the friction plate with only the second member, comprising at least two members 55 and 85 and inner second members 51 and 81 including a hub portion and a disk portion. Is formed, and the vertical wall 5 of the first member is formed.
Since the sixth and 86 and the disk portions 53 and 83 of the second member are welded together so as to be substantially straight, oil leakage from the hydraulic chamber due to poor welding or the like does not occur.

Then, the friction plate 63 meshing with the drum portion,
At the radial position 93, there is no cylinder that requires a sliding surface of a predetermined length due to the piston stroke.
6, 86 side. Then, the extension portions 74 and 11 of the piston extended in the radial direction to the radial position of the friction plate.
No. 2 engages with the friction plates because it crosses over the distal end portions of the outer cylinders 54 and 84 forming the cylinder, is once offset toward the vertical walls 56 and 86 of the first member, and is then turned back toward the friction plates 63 and 93. Opponent clutch hub 60, 90
Can also be moved to the vertical wall side. Thereby, the axial length of the drum portions 57 and 87 can be reduced.

Also, since the friction plate pressing portions of the pistons 65 and 96 do not extend in the axial direction from the sliding surface of the cylinder but extend in the outer diameter direction, the outer diameters of the spring receivers 66 and 98 of the return springs are increased. As a result, the pressure receiving area of the cancel pressure chamber of the piston can be made equal to the pressure receiving area of the hydraulic chamber, and a well-balanced and highly responsive piston control can be performed. That is, the spring receivers 66, 9
Numeral 8 functions as a centrifugal cancel piston, in other words, it can be matched with the diameter of the centrifugal cancel piston only by changing the diameter of the first cylindrical portion of the second member, and a well-balanced piston control can be obtained. Further, the first member 5
5, 85 and the second members 51, 81 are welded at a radially intermediate position between the drum portion and the hub portion, so that the heat distortion is smaller than that of the conventional example in which the outermost diameter portion is welded. Is prevented from lowering the roundness.

In particular, in the clutch drum 80, the third member 100 further inside is joined to the second member 81, the cylindrical portion 102 is folded back to the same side as the hub portion 82, and the hub portion is interposed through the sleeve 88. Since it is supported on the outer periphery of the protrusion 22 of the partition wall and the cylindrical portion is supported on the inner periphery of the protrusion 22 which is a cylindrical support shaft via the bush 11,
The direction in which the reaction force of the sleeve acts on the hub portion and the direction in which the reaction force of the bush acts on the cylinder portion are balanced, so that the clutch drum does not fall.

Since the bush 11 is provided between the protruding portion 22 and the cylindrical portion 102, the flow of oil over the bush is prevented, and the oil hole 128 is provided between the protruding portion end face and the disk portion 101. An oil path to the space is defined, and the oil is appropriately guided to the thrust bearing 16, the sleeve 88, and the like.

[0059]

As described above, according to the present invention, the clutch drum includes the first member having the drum portion and the vertical wall extending in the inner diameter direction, the first cylindrical portion, the first disk portion, and the second cylindrical portion. A piston which presses a friction plate is disposed on a cylinder which is formed of a molded second member and has a sliding surface formed by the inner peripheral surface of the first cylindrical portion and the outer peripheral surface of the second cylindrical portion. Therefore, the cylinder is formed of a second member integrally molded,
Even if the clutch drum is composed of a plurality of members, there is an effect that oil leakage does not occur on the cylinder side.

The clutch drum comprises, in addition to the first member and the second member, a third member having a third cylindrical portion smaller in diameter and coaxial than the second cylindrical portion of the second member, and the clutch drum has a cylindrical shape. Since the support shaft is supported by being sandwiched between the second cylindrical portion and the third cylindrical portion, the clutch drum is prevented from falling down,
The posture holding accuracy is improved.

The vertical wall of the first member of the clutch drum is particularly welded at a bend from the first disk portion to the first cylindrical portion of the second member, so that the first disk portion and the vertical wall extend in the radial direction. By extending substantially in a straight line, the total length of the clutch drum can be reduced.

Further, the first member of the second member of the clutch drum
The length of the cylindrical portion is set to a limit corresponding to the required stroke of the piston, and the piston is provided with an extending portion extending in the outer radial direction across the vicinity of the tip of the first cylindrical portion, so that the friction plate is provided. Can be arranged on the outer diameter side that can be pressed by the extension portion, and a cancel pressure chamber can be provided on the back side of the piston. Then, after the extended portion of the piston crosses the vicinity of the tip of the first cylindrical portion, it is offset toward the vertical wall of the first member, and the outer diameter end has a pressing portion extending in the direction of the friction plate. The plate and the clutch hub can be moved toward the vertical wall, and the axial size of the clutch is reduced.

An axially extending flange is formed on the side of the piston opposite to the vertical wall, and a spring receiver for supporting a return spring for biasing the piston is provided on the inner peripheral surface of the flange and the second cylindrical portion of the second member. And the inner peripheral surface of the first cylindrical portion of the second member and the inner peripheral surface of the flange of the piston have substantially the same diameter, so that the pressure receiving areas on both surfaces of the piston are substantially equal. Thus, a cancellation effect with good responsiveness can be obtained.

Further, a bush is provided between the support shaft supporting the second cylindrical portion of the clutch drum and the third cylindrical portion of the third member, and the bush forms an oil passage in a space between the support shaft and the clutch drum. By this, the flow of the oil in the axial direction beyond the bush is prevented, so that the oil is efficiently supplied to the lubrication-required portion communicating with the oil passage.

The second member of the clutch drum has a second disk portion extending in the radial direction from the end of the second cylindrical portion, and the third member extends in the radial direction from the end of the third cylindrical portion. The second disk portion and the third disk portion are welded to each other, particularly at a radially intermediate portion between the second cylindrical portion and the third cylindrical portion. There is no possibility that the roundness of the third cylindrical portion is impaired.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram showing a power transmission mechanism of an automatic transmission according to an embodiment of the present invention.

FIG. 2 is a view showing an operation combination of a fastening element for shifting.

FIG. 3 is a sectional view showing a specific structure of the embodiment.

FIG. 4 is an enlarged view showing a supporting portion of a clutch drum and a bearing lubrication structure of an output gear.

FIG. 5 is a view showing an example of a conventional clutch drum structure.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Transmission case 2 Intermediate partition wall 4 Pump cover 6 Projecting cylinder part 7 Stator shaft 8 Brake band 10 Input shaft 11 Bush 12 Thrust washer 13, 14, 15, 16, 17, 18, 19 Thrust bearing 21 Projecting part 22 Projecting part (Cylinder) Support member) 30 disk member 31 cylindrical part 41 first carrier plate 42 second carrier plate 50 clutch drum 51 second member 52 hub 53 disk part 54 outer cylinder 55 first member 56 vertical wall 57 drum part 58 bush 59 Stepped 60 Hub 61, 62 Spline 63 Friction plate 64 Cylinder 65 Piston 66 Spring receiver 67 Snap ring 68 Return spring 70 Rotating member 71 Disk part 72 Tube part 74 Extension part 75 Pressing part 80 Clutch drum 81 Second member 8 2 Hub part (second cylindrical part) 83 Disk part 84 Outer cylinder (first cylindrical part) 85 First member 86 Vertical wall 87 Drum part 88 Sleeve 89 Inner disk part 90 Hub 91, 92 Spline 93 Friction plate 94 Rising part 95 Cylinder 96 Piston 97 Return spring 98 Spring receiver 99 Snap ring 100 Third member 101 Disk part 102 Tube part (third cylindrical part) 110 Flange 112 Extension part 113 Pressing part 115 Output gear 116 Projecting part 117 Ball bearing 118 Nut 119 Flange part 120 annular member 122 oil passage 123, 124, 125, 126, 127, 128, 1
29, 130 Oil hole 140 Oil hole 141, 142, 143 Oil groove

Claims (8)

[Claims] 1. A clutch in which a friction plate provided between a clutch drum and a clutch hub is pressed by a piston to fasten the clutch drum and the clutch hub, wherein the clutch drums are sequentially connected from the outside to the inside. The first
A first member, a second member, and a third member.
The member is formed integrally with a drum portion having a spline meshing with the friction plate and a vertical wall extending from one end of the drum portion in the inner diameter direction, and the second member is a first member forming a sliding surface of an outer peripheral portion of the piston. The cylindrical portion, the second cylindrical portion forming the sliding surface of the inner peripheral portion of the piston, and the first disk portion connecting the first cylindrical portion and the second cylindrical portion are integrally formed to form a hydraulic chamber for the piston. The third member has a third cylindrical portion which is smaller in diameter and coaxial than the second cylindrical portion of the second member, and the clutch drum sandwiches a cylindrical support shaft between the second cylindrical portion and the third cylindrical portion. A clutch structure for an automatic transmission characterized by being supported by a clutch. 2. A vertical wall of the first member is welded at a bend from a first disk portion to a first cylindrical portion of a second member to form a first wall.
2. The clutch structure for an automatic transmission according to claim 1, wherein the disk portion and the vertical wall of the vehicle extend substantially linearly in the radial direction. 3. The length of the first cylindrical portion of the second member is set to a limit corresponding to a required stroke of the piston,
3. The clutch structure for an automatic transmission according to claim 2, wherein the piston has an extension extending in the outer radial direction across the vicinity of the tip of the first cylindrical portion. 4. The extension portion has a pressing portion that crosses the vicinity of the tip of the first cylindrical portion, is offset toward the vertical wall of the first member, and extends at an outer diameter end in the direction of the friction plate. The clutch structure for an automatic transmission according to claim 3, wherein: 5. An axially extending flange is formed on a side of the piston opposite to the vertical wall, and a spring receiver for supporting a return spring for biasing the piston is provided between an inner peripheral surface of the flange and the second member. The inner peripheral surface of the first cylindrical portion of the second member and the inner peripheral surface of the flange of the piston have substantially the same diameter. 5. The clutch structure for an automatic transmission according to claim 3, wherein said clutch structure is substantially equal. 6. A bush is provided between the support shaft and a third cylindrical portion of the third member, and the bush defines an oil passage in a space between the support shaft and the clutch drum. The clutch structure for an automatic transmission according to claim 1. 7. The second member has a second disk portion extending in an inner diameter direction from an end of a second cylindrical portion, and the third member is a third disk member.
A third disk portion extending in an outer radial direction from an end of the cylindrical portion, wherein the second member and the third member include a second disk portion and a third disk portion, and the second cylindrical portion and the third cylindrical portion; 7. A welded connection at a radially intermediate portion therebetween.
The clutch structure of the automatic transmission according to the above. 8. The clutch structure for an automatic transmission according to claim 1, wherein a brake band constituting a brake is disposed on an outer periphery of the drum portion of the first member.