WO2005108811A1

WO2005108811A1 - Clutch device for automatic speed changer

Info

Publication number: WO2005108811A1
Application number: PCT/JP2005/008741
Authority: WO
Inventors: Hirofumi Onishi; Yuji Yasuda
Original assignee: Toyota Jidosha Kabushiki Kaisha
Priority date: 2004-05-06
Filing date: 2005-05-06
Publication date: 2005-11-17
Also published as: JP2005320991A

Abstract

A clutch device (10) for an automatic speed changer has a first piston (18) provided outside the clutch drum (30) supporting friction engagement elements (12, 14), where the first piston (18) forms, together with a clutch drum (30), a first hydraulic pressure chamber (54), and has a balancer wall (60) provided on the rear surface side opposite the first hydraulic pressure chamber (54) side of the first piston (18), where the balancer wall (60) forms, together with the first piston (18), a cancel oil chamber (68). Axially extending grooves (70) are formed at an installation section of the balancer wall (60). The above structure eliminates the need of providing in the balancer wall (60) a cutout for discharging hydraulic oil in the cancel oil chamber (68), and therefore discharge resistance of hydraulic oil from the cancel oil chamber (second hydraulic pressure chamber)(68) is reduced and the strength of the balance wall (60) can be secured.

Description

Automatic transmission clutch device

The present invention relates to a clutch device provided in an automatic transmission, and in particular, a cancel oil chamber for canceling centrifugal oil pressure of a hydraulic chamber formed by a piston and a clutch drum is provided with a piston and a balancer wall provided on a back surface thereof. The present invention relates to a clutch device formed by: Background art

A piston that forms a hydraulic chamber with the clutch drum is provided outside the clutch drum that supports the friction engagement element, and a balancer that forms a canceller oil chamber together with the piston on the back side opposite to the hydraulic chamber of the piston. There is known a clutch device provided with a wall to cancel the centrifugal hydraulic pressure in the hydraulic chamber.

For example, the clutch device described in Japanese Patent Application Laid-Open No. 2003-106341 (Patent Document 1) is such a device.

By the way, in the case where the cancel oil chamber is formed by the piston and the balancer wall provided on the back side thereof as in Patent Document 1, supply of the hydraulic oil to the cancel oil chamber is performed from the input shaft side. In this case, an oil discharge hole for discharging the hydraulic oil supplied to the cancel oil chamber must be provided on the inner peripheral side. Therefore, it is conceivable that the inner peripheral edge of the balancer wall is cut out to form an oil discharge hole.However, if the inner peripheral edge of the balancer wall is cut out, it is difficult to secure the strength of the balancer wall itself. .

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to reduce the drainage resistance of hydraulic oil from the cancel oil chamber and reduce the resistance of the balancer wall forming the cancel oil chamber. Occasionally provide a clutch device that can ensure strength o Disclosure of the invention

According to a first aspect of the present invention, there is provided: (a) a piston forming a hydraulic chamber together with the clutch drum outside a clutch drum supporting a friction engagement element; and a piston opposite to the hydraulic chamber side of the piston. And a balancer wall forming a cancel oil chamber together with the piston on the back side of the clutch device. (B) The balancer wall is attached to an inner peripheral portion of the clutch drum. (C) a plurality of grooves formed in a portion of the clutch drum to which the balancer wall is attached and extending in the axial direction, and (d) a supply oil hole for supplying hydraulic oil to the cancel oil chamber. This is the feature.

According to the first aspect of the present invention, a groove extending in the axial direction is formed in the balancer wall mounting portion of the clutch drum, and the hydraulic oil in the cancel oil chamber is discharged from the groove. It is not necessary to provide a notch on the balancer wall for discharging the hydraulic oil in the cancel oil chamber. Therefore, the strength of the balancer wall can be secured while lowering the drainage resistance of the hydraulic oil from the cancel oil chamber.

A second invention is the clutch device according to the first invention, wherein the supply oil hole is formed in an inner peripheral portion of the clutch drum, and opens into the groove.

According to the first invention configured as described above, the axial dimension of the clutch device, that is, the automatic transmission provided with the clutch device, is further reduced.

Further, a third invention is the clutch device according to the first invention or the second invention, wherein the piston is provided with a lip seal for sealing between the piston and an outer peripheral portion of the balancer wall. And

According to the third aspect of the present invention, the gap between the piston and the balancer wall is sealed by the lip seal provided on the piston. On the other hand, when the gap between the piston and the balancer wall (cancellation plate in Patent Document 1) is sealed by a zero ring as in Patent Document 1, a housing portion for housing the ring is required. It is necessary to increase the wall thickness, and the axial dimension becomes longer due to the thicker portion. In the case of the eleventh invention, however, such a thick portion is not necessary. Therefore, the shaft dimension of the piston can be shortened, and the size of the clutch device can be reduced. Brief Description of Drawings

FIG. 1 is a sectional view showing a part of an automatic transmission including a clutch device to which the present invention is applied.

FIG. 2 is a cross-sectional view of the inner drum portion cut in a radial direction so as to include a groove. Explanation of symbols

1 0: Clutch device

1 2: First friction engagement element

1 4: Second friction engagement element

16: Clutch drum

1 8: 1st piston

5 4: 1st hydraulic chamber

60: Balancer wall

6 6: Refills

7 4: Lip seal

6 8: 2nd hydraulic chamber (canceled oil chamber)

7 2: Oil hole (Supply oil hole)

7 6: Lip seal best mode for carrying out the invention

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a cross-sectional view showing a part of an automatic transmission including a clutch device 10 to which the present invention is applied, that is, an upper half of an axis represented by a chain line.

The clutch device 10 includes a bottomed cylindrical clutch that supports the first friction engagement element 12 and the second friction engagement element 14 at a predetermined distance from each other in the axial direction. A first piston 18 is arranged outside the drum 16 to cover the clutch drum 16, and a second piston 20 is arranged inside the clutch drum 16.

The clutch drum 16 has an inner drum part 26 that is mutually welded to the input shaft 22 that is a rotating shaft at a first welding part 24, and the inner drum part 26 and the second welding part 28 that are mutually welded. It consists of a key drum section 30 to be welded. The input shaft 22 is a turbine shaft of a torque converter that is rotationally driven by a driving source such as an engine.

The inner drum part 26 is a cylindrical member, and is disposed on the inner peripheral side of the first piston 18, and has a flange 2 whose end face on the second biston 20 side projects radially outward on the input shaft 22. The second piston 20a is aligned with the surface of the second piston 20 on the side of 2a. The first welded portion 24 is formed on the outer periphery of the surface of the flange portion 22 a on the second piston 20 side and on the inner peripheral edge of the surface of the inner drum portion 26 on the second piston 20 side. I have.

On the other hand, the outer drum portion 30 is a bottomed cylindrical member concentric with the shaft center, which is press-formed from a steel plate so as to open at one side in the axial direction. 30a, an annular bottom portion 30b having an inner peripheral edge connected to the inner peripheral side tubular portion 30a, and an outer peripheral side tubular portion 30c connected to the outer peripheral edge of the bottom portion 30b. It is configured. The inner peripheral side tube portion 30a and the outer peripheral side tube portion 30c have a cylindrical shape with the axis as the center line.

The inner cylindrical portion 30a is arranged so as to be fitted to the outer periphery of the inner drum portion 26, and the end face of the second piston 20 side is formed on the second piston 20 side of the inner drum portion 26. The second welded portion 28 is formed on the inner peripheral edge of the end face. Therefore, the first welded portion 24 and the second welded portion 28 are juxtaposed so as to overlap in the radial direction. The first welded portion 24 and the second welded portion 28 are formed by, for example, laser beam welding so that the welding depth is in a direction parallel to the axis. The axial length of the inner cylindrical portion 30a is longer than the welding depth of the first welded portion 24 and the second welded portion 28.

The bottom 3 O b is provided substantially perpendicular to the radial direction of the input shaft 22, and It is connected to the end of the first piston 18. In addition, the bottom 3 Ob is located at a position slightly more than the radially outermost point than the radially intermediate point, and the first piston 18 more than the end of the inner peripheral side cylinder portion 30 a on the first piston 18 side. A U-shaped annular convex curved portion 30d, which is convex in the axial direction on the side and concave in the axial direction on the second piston 20 side, is locally formed.

The outer cylindrical portion 30c of the drum 350 extends to the second piston 20 side with the bottom portion 30b force, and the inner peripheral surface near the opening portion has a first frictional engagement member. The plurality of inward friction plates 32 of the mating element 1 2 are spline-fitted so as to be relatively non-rotatable.The first friction engagement element 12 includes the plurality of inward friction plates 32 and the plurality of inward friction plates. It is composed of a plurality of outward friction plates 34 interposed between 32. The plurality of outward friction plates 34 are spline-fitted to the outer peripheral surface of a ring gear 36 functioning as a clutch hub so as to be relatively non-rotatable. are doing.

The inner peripheral surface of the outer cylindrical portion 30 c of the outer drum portion 30 further has a second frictional engagement on the bottom portion 30 b side of the portion supporting the first frictional engagement element 12. The inward friction plate 38 of the element 14 is spline-fitted so as not to rotate relatively. The second friction engagement element 14 includes the plurality of inward friction plates 38 and a plurality of outward friction plates 40 interposed between the plurality of inward friction plates 38. The plurality of outward friction plates 40 are spline-fitted to the outer peripheral surface of the clutch hub 42 which is substantially perpendicular to the input shaft 22 so as not to rotate relatively. Since the inner peripheral edge of the clutch hub 42 is fixed to the sun gear 44, the clutch hub 42 is rotated integrally with the sun gear 44.

The first piston 18 is a press-formed product press-formed from a steel plate, and has an annular bottom portion 18 a and an outer periphery of the fan drum 0 connected to an outer peripheral edge of the bottom portion 18 a. And a cylindrical projection 18c, which is connected to the cylindrical portion 18b and projects in the axial direction from the noise drum sound 30, and a force. The protruding portion 18c has a spline shape over the entire circumference, and is configured such that the tip of the spline on the inner peripheral surface coincides with the inner peripheral surface of the cylindrical portion 18c.

The projecting portion 18 c of the first piston 18 has an outer peripheral edge of an annular plate-shaped pressing member 46. Are spline-fitted. One surface of the outer peripheral edge of the pressing member 46 is in contact with the ί surface of the cylindrical portion 18 b of the first piston 18, and the other surface is fixed inside the projecting portion 18 c Since the pressing member 46 is in contact with the snap ring 48, the pressing member 46 cannot move relative to the first piston 18 in the circumferential direction and the axial direction.

Further, the bottom portion 18a is formed with an annular concave portion 18d which is slidably fitted on the outer peripheral surface of the annular convex curved portion 30d of the outer drum portion 30 and is capable of accommodating it. The outer peripheral surface of the outer peripheral corner portion 30 e of the annular convex curved portion 30 d of the auta drum 3P 30 has an annular concave portion 18 d of the first piston 18 and the annular convex portion of the auta drum portion 30. A rubber lip seal 50 sealing between the curved portion 30d is fixed by vulcanization. Further, the inner peripheral edge of the first piston 18 is slidable with respect to the outer peripheral surface of the inner drum portion 26, and the inner peripheral edge of the first piston 18 and the inner drum 咅 P 26 are also provided. Sealed by a rubber lip seal 52 fixed to the inner peripheral edge of the first piston 18, the bottom 咅 P 18 a of the first piston 18 and the bottom 3 O b of the outer drum 30 A first hydraulic chamber 54 is formed therebetween. When hydraulic oil is supplied to the first hydraulic chamber 54 via an oil hole 56 formed in the inner drum portion 26, the first piston 18 has a bottom portion 18a in which the oil is supplied. Since it is moved in a direction away from the bottom 30 b of the drum 30, the pressing member 46 fixed to the projection 18 c of the first piston 18 engages the first frictional engagement element 12. Press. Also, on the side of the first frictional engagement element 12 opposite to the pressing member 46, the first frictional engagement element 12 is fixed to the outer cylindrical part 30 c of the outer drum part 30 so that the first frictional engagement element 12 is in the axial direction. Since the snap ring 58 for preventing the first frictional engagement element 14 from moving toward the first frictional engagement element 14 is provided, the first frictional engagement element 12 is pressed by the pressing The plurality of inward friction plates 32 and outward friction plates 34 constituting the first friction engagement element 12 are engaged with each other.

A disc-shaped balancer wall 60 is fitted on the outer periphery of the inner drum portion 26 on the back side of the first piston 18 opposite to the first hydraulic chamber 54 side. The balancer wall 60 is connected to an annular plate portion 60 a substantially perpendicular to the axis of the inner drum portion 26 and an outer peripheral edge of the annular plate portion 60 a, and the first piston 1 It consists of a cylindrical portion 6 Ob directed toward the 8 side. Between the annular plate portion 60a and the bottom portion 18a of the first piston 18, the A return spring 62 is provided for urging in a direction in which the spring is separated. On the other hand, the surface of the inner peripheral edge of the balancer wall 60 opposite to the first piston 18 is brought into contact with a snap ring 64 fixed on the outer peripheral surface of the inner drum portion 26, so that the balancer The movement of the wall 60 in a direction away from the first biston 18 is prohibited. The radius of the inner peripheral surface of the cylindrical portion 60 b is set to be slightly larger than the radius of the radially outer surface of the annular recess 18 d of the first piston 18. An outer peripheral corner of 8 d 18 A rubber lip seal 66 provided on the outer peripheral surface of e provides a cylindrical portion 60 d of the balancer wall 60 and an annular recess 18 of the first piston 18. The second hydraulic chamber 68 is formed between the balancer wall 60 and the bottom 18 a of the first biston 18 by being sealed between the second hydraulic chamber 68 and d.

The above-mentioned second hydraulic chamber 68 and the rear side of the balancer wall 60 are provided at the portion where the balancer wall 60 of the inner drum portion 26 is attached (the second hydraulic chamber 68 of the balancer wall 60 is different from the second hydraulic chamber 68). A groove 70 extending in the axial direction for communicating with the space on the opposite side) is provided at a plurality of positions in the circumferential direction. FIG. 2 is a cross-sectional view of the inner drum portion 26 cut radially so as to include the groove 70. As shown in FIG. 2, the grooves 70 are formed at equal intervals in the circumferential direction in this embodiment. It is provided in places.

Further, the inner drum portion 26 is formed with an oil hole 72 having one end opening on a side of the groove 70 communicating with the second hydraulic chamber 68. However, as shown in FIG. 2, the oil ginseng 72 is not provided for all the ditches 70, but is provided for a part (four in FIG. 2). The oil hole 72 functions as a supply oil hole for supplying hydraulic oil to the second hydraulic chamber 68. When centrifugal force acts on the hydraulic oil, the hydraulic oil passes through the oil hole 72 and the groove 70. It is supplied to the second hydraulic chamber 68 from the input shaft 22 through the input shaft 22. Thereby, the second hydraulic chamber 68 functions as a cancel oil chamber that cancels the centrifugal hydraulic pressure of the first hydraulic chamber 54. The oil hole 72 also functions as a hydraulic oil discharge hole, and when the hydraulic oil is being supplied to the first hydraulic chamber 54, the hydraulic oil in the second hydraulic chamber 68 is filled with the oil hole. Although it is discharged from 72, the groove 70 also functions as a discharge path for hydraulic oil, and the hydraulic oil in the second hydraulic chamber 68 also flows to the back side of the balancer wall 60 via the groove 70. Since the oil is discharged, the drainage resistance of the hydraulic oil from the second hydraulic chamber 68 is reduced. The second piston 20 is a press-formed product, and has an inner peripheral portion 20 a that is gradually separated from the second frictional engagement element 14 as the position in the axial direction is closer to the outer peripheral side, and an inner peripheral portion 20 a thereof. And an outer peripheral portion 20 b whose outermost peripheral portion faces the second frictional engaging element 14 in a stepwise manner toward the second frictional engaging element 14, and A connecting portion 20c having a U-shaped cross section for connecting between the peripheral portion 20a and the outer peripheral portion 2Ob is provided. A connecting portion 20c, which is a connecting portion between the inner peripheral portion 20a and the outer peripheral portion 20b, is slidably fitted in the annular convex curved portion 30d. A rubber lip seal 74 is fixed to the outer peripheral surface (the bottom surface of the outer drum portion 30 on the P30b side), and the lip seal 74 allows the outer drum portion 30 to be fixed. There is a seal between the bottom 30b and the second biston 20. Further, the inner peripheral edge of the second piston 20 is slidable with respect to the input shaft 22, and the inner peripheral edge of the second piston 20 and the input shaft 22 are also slidable. It is sealed by a rubber lip seal 76 fixed to the inner peripheral edge of the piston 20, and a third lip is formed between the second piston 20 and the bottom of the drum D P30. A hydraulic chamber 78 is formed.

When hydraulic oil is supplied to the third hydraulic chamber 78 via an oil hole 80 formed in the input shaft 22, the second piston 20 is moved to the bottom 30 of the gas drum 30. It is moved in a direction away from b and presses the second frictional engagement element 14. Also, on the opposite side of the second friction engagement element 14 from the second piston 20, the second friction engagement element 14 is fixed to the outer cylindrical portion 30 c of the outer drum portion 30 so that the second friction engagement element 14 is in the axial direction. Since the snap ring 82 is provided to prevent the second frictional engagement element 14 from moving toward the first frictional engagement element 1, the second frictional engagement element 14 is pressed by the second The plurality of inward friction plates 38 and outward friction plates 40 constituting the second friction engagement element 14 are engaged with each other.

A balancer wall 84 is fitted on the outer periphery of the input shaft 22 on the opposite side of the bottom surface P 30 b of the outer drum portion 30 of the second piston 20. The balancer wall 84 is an annular plate-like member provided substantially perpendicularly to the axis of the input shaft 22, and is located between the balancer wall 84 and the second piston 20. Urge to move away from each other Springs 86 are provided. On the other hand, the surface of the inner peripheral edge of the balancer wall 86 opposite to the second piston 20 is in contact with a snap ring 88 fixed to the outer peripheral surface of the input shaft 22. No. 84 is prohibited from moving in a direction away from the second piston 20.

Further, a rubber lip seal 90 for sealing between the balancer wall 84 and the second piston 20 is provided on the outer peripheral edge of the balancer wall 84, and a gap between the balancer wall 84 and the second piston 20 is provided. A fourth hydraulic chamber 92 functioning as a cancel oil chamber for canceling the centrifugal hydraulic pressure of the third hydraulic chamber 78 is formed in the third hydraulic chamber 78.

As described above, according to the present embodiment, the groove 70 extending in the axial direction is formed in the mounting portion of the balancer wall 60 of the clutch drum 30, and the second hydraulic chamber 6 extends from the groove 70. Since the hydraulic oil of FIG. 8 is discharged, it is not necessary to provide a cutout in the balancer wall 60 for discharging the hydraulic oil of the second hydraulic chamber 68. Therefore, the strength of the balancer wall 60 can be secured while lowering the drainage resistance of the hydraulic oil from the second hydraulic chamber 68.

In addition, according to the present embodiment, since the oil hole 72 is opened in the groove 70, the opening of the oil hole 72 is more easily provided in the inner drum portion 26 than in the case where the oil hole 72 is directly provided in the second hydraulic chamber 68. Therefore, the axial dimension of the clutch device 10 can be reduced, and the clutch device 10 can be further reduced in size. Further, according to the present embodiment, the lip seal 66 provided on the first piston 18 seals the space between the first piston 18 and the balancer wall 60. The shaft dimension can be shortened, and the clutch device 10 can be further reduced in size.

According to the present embodiment, the first piston 18 is slidable on the inner drum 26 and the second piston 20 is slidable on the input shaft 22. The inner drum part 26 can be made shorter than the structure in which the inner drum part 26 is slidable on the inner drum part 26, and the inner drum part 26 and the input shaft 22 are joined by welding. Therefore, as in Patent Document 1, the axial dimension of the connecting portion is shorter than that in the case of connecting by a spline, so that the inner drum portion 26 can also be shortened. Therefore, the entire clutch device 10 The size can be reduced.

Further, according to the present embodiment, since the first welded portion 24 and the second welded portion 28 are arranged in parallel in the radial direction, the input shaft 22 and the inner drum portion 26 and the inner drum portion 26 Since the auta drum 30 can be welded simultaneously, the welding cost can be reduced.

Further, according to the present embodiment, since the inner peripheral side cylindrical portion 30a of the aerial drum sound P30 is formed in the depth direction of the welded portions 24, 28, the aerial drum sound P30 is formed. Flaw detection of the first welded portion 24 and the second welded portion 28 can be performed from the radially outer side of the inner cylindrical portion 30a of the portion 30.

Further, according to the present embodiment, in the flaw detection probe 100, the distal end portion 104 closer to the distal end side than the ultrasonic wave output portion 10 is formed into the annular convex curved portion 30d formed in the bottom portion 30b. The inner cylinder of the outer drum section 30 can be accommodated, as compared with the case where the tip section 104 is arranged radially outside the inner cylinder section 30a of the outer drum section 30. Part 30a can be shortened.

Further, according to the present embodiment, the lip seal 50 provided on the outer drum section 30 seals the space between the first piston 18 and the outer drum 咅 30, and the second piston

The lip seals 74 and 76 provided on the cylinder 20 seal the gap between the air drum 30 and the second piston 20 and the gap between the input shaft 22 and the second piston 20 respectively. As a result, the axial dimensions of the outer drum portion 30 and the second piston 20 can be reduced, and the clutch device 10 can be further reduced in size.

Further, according to the present embodiment, the first piston 18 is slidably fitted to the outer peripheral surface of the annular convex curve P 30 d of the gas drum section 30, and the second piston 20 is , Auta drum section

Since the first piston 18 and the second piston 20 are slidably fitted to the inner peripheral surface of the annular convex curved portion 30 d of 30, the first piston 18 and the second piston 20 are directly attached to both surfaces of the clutch drum 30. Since the clutch device 10 is slidably fitted, the size of the clutch device 10 is reduced.

Further, according to the present embodiment, the first friction engagement element 12 and the second friction engagement element 14 are arranged at a predetermined distance in the axial direction in the clutch drum 30, and 8 is driven in a direction away from the second piston 20 in the axial direction. Presses the first engagement element 12 when the second piston 20 is driven in a direction away from the first piston 18 in the axial direction. Therefore, the first piston 18 and the second piston 20 provided on both surfaces of the clutch drum 30, that is, on both sides in the axial direction, are used to press the shaft center in the clutch drum 30. The first frictional engagement element 12 and the second frictional engagement element 14 arranged at a predetermined distance in the direction can be engaged. Although the embodiments of the present invention have been described in detail with reference to the drawings, the present invention is applicable to other embodiments.

For example, in the above-described embodiment, the oil holes 72 are provided in half of the plurality of grooves 70, but the oil holes 72 may be provided in all of the plurality of grooves 70. Further, the number of the grooves 70 is not limited to that of the above-described embodiment, and is appropriately set according to the required oil drainage resistance.

Further, in the above-described embodiment, the gap between the first piston 18 and the balancer wall 60 is sealed by the lip seal 66. However, in a case other than the embodiment of the second invention, the lip seal 66 is replaced with the lip seal 66. Alternatively, another seal member such as an oil seal may be used. Further, the seals of the first, third and fourth hydraulic chambers 54, 78 and 92 may be other seal members such as oil seals.

The above is merely an embodiment, and the present invention can be embodied in various modified and improved forms based on the knowledge of those skilled in the art.

Claims

The scope of the claims

1. A piston that forms a hydraulic chamber together with the clutch drum outside the clutch drum that supports the friction engagement element, and a balancer that forms a cancel oil chamber together with the piston on the back side of the piston opposite to the hydraulic chamber side. A clutch device for an automatic transmission provided with a wall,

A plurality of grooves formed in a portion of the clutch drum to which the non-lancer wall is attached, the plurality of grooves extending in the axial direction;

A supply oil hole for supplying hydraulic oil to the cancel oil chamber;

A clutch device for an automatic transmission, comprising:

2. The clutch device for an automatic transmission according to claim 1, wherein the supply oil hole is formed in an inner peripheral portion of a clutch drum and opens into the groove.

3. The clutch device for an automatic transmission according to claim 1, wherein the piston is provided with a lip seal that seals between the piston and an outer peripheral portion of the balancer wall. .