WO2005108811A1 - Clutch device for automatic speed changer - Google Patents

Clutch device for automatic speed changer Download PDF

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Publication number
WO2005108811A1
WO2005108811A1 PCT/JP2005/008741 JP2005008741W WO2005108811A1 WO 2005108811 A1 WO2005108811 A1 WO 2005108811A1 JP 2005008741 W JP2005008741 W JP 2005008741W WO 2005108811 A1 WO2005108811 A1 WO 2005108811A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
wall
balancer
drum
oil
Prior art date
Application number
PCT/JP2005/008741
Other languages
French (fr)
Japanese (ja)
Inventor
Hirofumi Onishi
Yuji Yasuda
Original Assignee
Toyota Jidosha Kabushiki Kaisha
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyota Jidosha Kabushiki Kaisha filed Critical Toyota Jidosha Kabushiki Kaisha
Publication of WO2005108811A1 publication Critical patent/WO2005108811A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types

Definitions

  • 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.
  • a clutch device provided with a wall to cancel the centrifugal hydraulic pressure in the hydraulic chamber.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2003-106341
  • 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
  • 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.
  • a balancer wall forming a cancel oil chamber together with the piston on the back side of the clutch device.
  • the balancer wall is attached to an inner peripheral portion of the clutch drum.
  • 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.
  • the axial dimension of the clutch device that is, the automatic transmission provided with the clutch device, is further reduced.
  • 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.
  • the gap between the piston and the balancer wall is sealed by the lip seal provided on the piston.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 ⁇ 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.
  • 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.
  • 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 ⁇ 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 ⁇ 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.
  • the first piston 18 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.
  • 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.
  • the A return spring 62 is provided for urging in a direction in which the spring is separated.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second piston 20 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the lip seal 50 provided on the outer drum section 30 seals the space between the first piston 18 and the outer drum ⁇ 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.
  • 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.
  • 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
  • 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.
  • 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.
  • 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.
  • the gap between the first piston 18 and the balancer wall 60 is sealed by the lip seal 66.
  • the lip seal 66 is replaced with the lip seal 66.
  • another seal member such as an oil seal may be used.
  • the seals of the first, third and fourth hydraulic chambers 54, 78 and 92 may be other seal members such as oil seals.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

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

自動変速機のクラッチ装置 技術分野  Automatic transmission clutch device
本発明は、 自動変速機に備えられるクラッチ装置に関し、 特に、 ピストンとク ラッチドラムとにより形成される油圧室の遠心油圧をキャンセルするキャンセル 油室が、 ビストンとその背面に設けられたバランサ壁とにより形成されているク ラッチ装置に関する。 背景技術  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
摩擦係合要素を支持するクラッチドラムの外側に、 そのクラッチドラムととも に油圧室を形成するビストンが設けられ、 ビストンの油圧室とは反対の背面側に 、 ビストンとともにキヤンセル油室を形成するバランサ壁が設けられ、 上記油圧 室の遠心油圧をキャンセルするようにしたクラッチ装置が知られている。  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.
たとえば、特開 2 0 0 3— 1 0 6 3 4 1号公報 （特許文献 1 ) に記載されたク ラッチ装置がそれである。  For example, the clutch device described in Japanese Patent Application Laid-Open No. 2003-106341 (Patent Document 1) is such a device.
ところで、上記特許文献 1のように、 キャンセル油室がピストンとその背面側 に設けられたバランサ壁とにより形成されている場合において、 キャンセル油室 への作動油の供給を入力軸側から行うようにした場合、 そのキヤンセル油室に供 給された作動油を排出する油排出穴を内周側に設けなければならない。 そこで、 バランサ壁の内周縁を切り欠いて油排出穴とすることが考えられるが、 バランサ 壁の内周縁を切り欠いてしまうと、 バランサ壁自体の強度確保が困難になるとい う問題があった。  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. .
本発明は、 以上の事情を背景として為されたものであり、 その目的とするとこ ろは、 キャンセル油室からの作動油の排油抵抗を低くしつつ、 キャンセル油室を 形成するバランサ壁の強度を確保することができるクラッチ装置を提供すること しある o 発明の開示 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
前記目的を達成するための第 1発明は、 （a) 摩擦係合要素を支持するクラッチ ドラムの外側に該クラッチドラムとともに油圧室を形成するピストンと、 該ピス トンの前記油圧室側とは反対の背面側に該ピストンとともにキャンセル油室を形 成するバランサ壁とが設けられた自動変速機のクラッチ装置であって、 （b) 前記 バランサ壁が前記クラッチドラムの内周部に取り付けられており、 （c) 該クラッ チドラムの前記バランサ壁が取り付けられた部分に形成され、 軸心方向に延びる 複数の溝と、 （d) 前記キャンセル油室に作動油を供給する供給油孔とを、 含むこ とを特徴とする。  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.
このように構成された第 1発明によれば、 クラッチドラムのバランサ壁取り付 け部に軸心方向に延びる溝が形成されており、 その溝からキャンセル油室の作動 油が排出されるので、 バランサ壁にキャンセル油室の作動油を排出するための切 り欠きを設ける必要がなくなる。 従って、 キャンセル油室からの作動油の排油抵 抗を低く しつつ、 バランサ壁の強度を確保することができる。  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.
また、 第 2発明は、 第 1発明のクラッチ装置において、 前記供給油孔は、 クラ ツチドラムの内周部に形成されて、 前記溝内に開口するものである。  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.
このように構成された第 1発明によれば、 クラッチ装置すなわちそれが備えら れた自動変速機の軸方向寸法が一層小型となる。  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.
また、 第 3発明は、 第 1発明または第 2発明のクラッチ装置において、 前記ピ ストンには、 そのビストンと前記バランサ壁の外周部との間をシールするリップ シールが設けられていることを特徴とする。  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
このように構成された第 3発明によれば、 ビストンに設けられたリップシール によりピストンとバランサ壁との間がシールされている。 これに対して、 前記特 許文献 1のように、 ビストンとバランサ壁 （特許文献 1ではキャンセルプレート ) との間を 0リングによりシールする場合には、 〇リングを収容するためにその 収容部分を肉厚にする必要があり、 その肉厚とされた部分のために軸方向寸法が 長くなつてしまうが、 第 1 1発明の場合には、 そのような肉厚な部分が必要なく なるのでピストンの軸寸法を短くでき、 ひいては、 クラッチ装置を小型化するこ とができる。 図面の簡単な説明 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
図 1は、 本発明が適用されたクラッチ装置を含む自動変速機の一部を示す断面 図である。  FIG. 1 is a sectional view showing a part of an automatic transmission including a clutch device to which the present invention is applied.
図 2は、 ィンナドラム部を溝を含むように径方向に切断した断面図である。 符号の説明  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 : クラッチ装置  1 0: Clutch device
1 2 ：第 1摩擦係合要素  1 2: First friction engagement element
1 4 ：第 2摩擦係合要素  1 4: Second friction engagement element
1 6 ： クラッチドラム  16: Clutch drum
1 8 ：第 1 ピストン  1 8: 1st piston
5 4 ：第 1油圧室  5 4: 1st hydraulic chamber
6 0 ：バランサ壁  60: Balancer wall
6 6 ： リツフシ一ル  6 6: Refills
7 4 ： リップシール  7 4: Lip seal
6 8 ：第 2油圧室 （キャンセル油室）  6 8: 2nd hydraulic chamber (canceled oil chamber)
7 2 ：油孔 （供給油孔）  7 2: Oil hole (Supply oil hole)
7 6 ： リップシール 発明を実施するための最良の形態  7 6: Lip seal best mode for carrying out the invention
以下、本発明の実施例を図面を参照しつつ詳細に説明する。 図 1は、 本発明が' 適用されたクラッチ装置 1 0を含む自動変速機の一部すなわち 1点鎖線で表され る軸心の上半分を示す断面図である。  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.
クラッチ装置 1 0は、 第 1摩擦係合要素 1 2および第 2摩擦係合要素 1 4を軸 心方向に所定距離離隔して位置する状態でそれぞれ支持する有底円筒状のクラッ チドラム 1 6の外側にそのクラッチドラム 1 6を覆うように第 1 ピストン 1 8が 配置され、 そのクラッチドラム 1 6の内側に第 2ピストン 2 0が配置された構造 を有している。 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.
クラッチドラム 1 6は、 回転軸である入力軸 2 2に第 1溶接部 2 4において互 いに溶接されるインナドラム部 2 6と、 そのインナドラム部 2 6と第 2溶接部 2 8において互いに溶接されるァゥ夕ドラム部 3 0とからなる。 なお、 上記入力軸 2 2は、 エンジン等の走行用駆動源によって回転駆動されるトルクコンパ一夕の タービン軸である。  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.
上記ィンナドラム部 2 6は円筒状部材であり、 第 1 ピストン 1 8の内周側に配 置され、 第 2ビストン 2 0側の端面が、 入力軸 2 2において径方向外側に突き出 す鍔部 2 2 aの第 2ピストン 2 0側の面と一致させられている。 そして、 その鍔 部 2 2 aの第 2ピストン 2 0側の面の外周緣とィンナドラム部 2 6の第 2ピスト ン 2 0側の面の内周縁に前記第 1溶接部 2 4が形成されている。  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.
一方、 ァウタドラム部 3 0は、 軸方向の一方に開口するように鋼板からプレス 成形された前記軸心と同心の有底円筒状部材であり、 内周側端部となる内周側筒 咅 P 3 0 aと、 その内周側筒部 3 0 aに内周縁が連結される環状の底部 3 0 bと、 その底部 3 0 bの外周縁に連結される外周側筒部 3 0 cとから構成されている。 上記内周側筒部 3 0 aおよび外周側筒部 3 0 cは軸心を中心線とする円筒状を成 している。  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.
上記内周側筒部 3 0 aは、 インナドラム部 2 6の外周に嵌合するように配置さ れ、 第 2ピストン 2 0側の端面が前記ィンナドラム部 2 6の第 2ピストン 2 0側 の端面と一致させられており、 その端面の内周縁に前記第 2溶接部 2 8が形成さ れている。 従って、 第 1溶接部 2 4および第 2溶接部 2 8は、 径方向において重 なるように並設されている。 なお、 第 1溶接部 2 4および第 2溶接部 2 8は、 た とえばレーザビーム溶接によりその溶接深さが軸心と平行な方向となるように形 成されている。 内周側筒部 3 0 aの軸方向長さは、 第 1溶接部 2 4および第 2溶 接部 2 8の溶接深さよりも長くされている。  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.
底部 3 O bは、 入力軸 2 2の径方向に略垂直に設けられ、 内周側筒部 3 0 aの 第 1 ピストン 1 8側の端部に連結されている。 また、 その底部 3 O bには、 径方 向中間点よりもやや外周よりの位置に、 内周側筒部 3 0 aの第 1 ピストン 1 8側 の端部よりもさらに第 1 ピストン 1 8側で軸心方向の凸となり第 2ピストン 2 0 側で軸心方向の凹となる断面 U字状の環状凸曲部 3 0 dが局部的に形成されてい る。 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.
ァゥ夕ドラム咅 (5 3 0の外周側筒部 3 0 cは、 底部 3 0 b力、ら第 2ピストン 2 0 側に延びており、 開口部付近の内周面に、 第 1摩擦係合要素 1 2の複数の内向摩 擦板 3 2が相対回転不能にスプライン嵌合されている。 第 1摩擦係合要素 1 2は 、 上記複数の内向摩擦板 3 2およびその複数の内向摩擦板 3 2の間に介在させら れる複数の外向摩擦板 3 4から構成される。 この複数の外向摩擦板 3 4は、 クラ ツチハブとして機能するリングギヤ 3 6の外周面に相対回転不能にスプライン嵌 合している。  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.
ァウタドラム部 3 0の外周側筒部 3 0 cの内周面には、 さらに、 上記第 1摩擦 係合要素 1 2を支持している部分よりも底部 3 0 b側に、 第 2摩擦係合要素 1 4 の内向摩擦板 3 8が相対回転不能にスプライン嵌合されている。 第 2摩擦係合要 素 1 4は、 上記複数の内向摩擦板 3 8およびその複数の内向摩擦板 3 8の間に介 在させられる複数の外向摩擦板 4 0から構成される。 この複数の外向摩擦板 4 0 は、 入力軸 2 2に対して略垂直とされたクラッチハブ 4 2の外周面に相対回転不 能にスプライン嵌合されている。 このクラッチハブ 4 2の内周縁はサンギヤ 4 4 に固定されているので、 クラッチハブ 4 2は、 サンギヤ 4 4と一体回転させられ る。  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.
前記第 1 ピストン 1 8は、 鋼板からプレス成形されたプレス成形品であって、 円環状の底部 1 8 aと、 その底部 1 8 aの外周縁に連結されてァゥ夕ドラム咅 0の外周を覆う円筒部 1 8 bと、 その円筒部 1 8 bに連結され、 ァゥ夕ドラム音 3 0よりも軸方向に突き出す筒状の突出部 1 8 cと力、らなる。 この突出部 1 8 c は、 全周にわたりスプライン形状とされており、 内周面のスプラインの歯先が円 筒部 1 8 cの内周面と一致するように構成されている。  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.
上記第 1 ピストン 1 8の突出部 1 8 cには、 円環板状の押圧部材 4 6の外周縁 がスプライン嵌合されている。 その押圧部材 4 6の外周縁の一方の面は、 第 1ピ ストン 1 8の円筒部 1 8 bの ί 面に当接され、 他方の面は、 突出部 1 8 cの内側 に固定されたスナップリング 4 8に当接されているので、 押圧部材 4 6は、 第 1 ビストン 1 8に対して周方向および軸方向に相対移動不能となっている。 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.
また、 上記底部 1 8 aには、 ァウタドラム部 3 0の環状凸曲部 3 0 dの外周面 に摺動可能に嵌合し且つそれを収容可能な環状凹部 1 8 dが形成されている。 そ して、 ァウタドラム咅 P 3 0の環状凸曲部 3 0 dの外周側角部 3 0 eの外周面には 、 第 1ピストン 1 8の環状凹部 1 8 dとァウタドラム部 3 0の環状凸曲部 3 0 d との間をシールするゴム製のリップシール 5 0が加硫により固着されている。 また、 第 1 ピストン 1 8の内周縁はィンナドラム部 2 6の外周面に対して摺動 可能とされており、 また、 その第 1ビストン 1 8の内周縁とィンナドラム咅 P 2 6 との間も第 1 ピストン 1 8の内周縁に固着されたゴム製のリップシール 5 2によ りシールされており、 第 1ピストン 1 8の底咅 P 1 8 aとァウタドラム部 3 0の底 部 3 O bとの間に第 1油圧室 5 4が形成されている。 この第 1油圧室 5 4に、 ィ ンナドラム部 2 6に形成された油孔 5 6を経由して作動油が供給されると、 第 1 ビストン 1 8は、 その底部 1 8 aがァゥ夕ドラム部 3 0の底部 3 0 bから離隔す る方向に移動させられるので、 第 1 ピストン 1 8の突出部 1 8 cに固定された押 圧部材 4 6が第 1摩擦係合要素 1 2を押圧する。 また、 第 1摩擦係合要素 1 2の 押圧部材 4 6とは反対側には、 ァウタドラム部 3 0の外周側筒部 3 0 cに固定さ れて第 1摩擦係合要素 1 2が軸方向の第 1摩擦係合要素 1 4側へ移動することを 阻止するスナップリング 5 8が設けられているので、 押圧部材 4 6により第 1摩 擦係合要素 1 2が押圧されることにより、 その第 1摩擦係合要素 1 2を構成する 複数の内向摩擦板 3 2および外向摩擦板 3 4は互いに係合させられる。  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.
第 1ピストン 1 8の第 1油圧室 5 4側とは反対の背面側には、 円板状のバラン サ壁 6 0がインナドラム部 2 6の外周に嵌合している。 このバランサ壁 6 0は、 インナドラム部 2 6の軸心に対して略垂直な円環板部 6 0 aと、 その円環板部 6 0 aの外周縁に連結されて、 第 1 ピストン 1 8側に向かう筒部 6 O bとからなる 。 上記円環板部 6 0 aと第 1 ピストン 1 8の底部 1 8 aとの間には、 それらを互 いに離隔する方向に付勢するリターンスプリング 6 2が設けられている。 一方、 バランサ壁 6 0の内周縁の第 1 ピストン 1 8とは反対側の面は、 ィンナドラム部 2 6の外周面に固設されたスナップリング 6 4に当接させられているので、 バラ ンサ壁 6 0は、 第 1ビストン 1 8から離隔する方向への移動が禁止されている。 また、 上記筒部 6 0 bの内周面の半径は、 第 1 ピストン 1 8の環状凹部 1 8 d の径方向外側面の半径よりも僅かに大きくなるように設定されており、 環状凹部 1 8 dの外周側角部 1 8 eの外周面に設けられたゴム製のリップシ一ル 6 6によ り、 バランサ壁 6 0の筒部 6 0 dと第 1 ピストン 1 8の環状凹部 1 8 dとの間が シールされて、 バランサ壁 6 0と第 1ビストン 1 8の底部 1 8 aとの間に第 2油 圧室 6 8が形成されている。 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.
インナドラム部 2 6の前記バランサ壁 6 0が取り付けられている部分には、 上 記第 2油圧室 6 8とバランサ壁 6 0の背面側 （バランサ壁 6 0の第 2油圧室 6 8 とは反対側） の空間とを連通させる軸方向に延びる溝 7 0が周方向の複数箇所に 設けられている。 図 2は、 インナドラム部 2 6を溝 7 0を含むように径方向に切 断した断面図であり、 図 2に示すように、 溝 7 0は本実施例では周方向に等間隔 に 8箇所設けられている。  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.
さらに、 インナドラム部 2 6には、 上記溝 7 0の第 2油圧室 6 8と連通する側 に一端が開口する油孔 7 2が形成されている。 ただし、 この油孑し 7 2は、 図 2に 示すように、全ての溝 7 0に対して設けられているのではなく、 その一部 （図 2 では 4つ） に設けられている。 この油孔 7 2は、 第 2油圧室 6 8に対して作動油 を供給する供給油孔として機能し、 作動油に遠心力が作用すると、 作動油は、 油 孔 7 2および溝 7 0を介して入力軸 2 2側から第 2油圧室 6 8に供給される。 こ れにより、 第 2油圧室 6 8は、 第 1油圧室 5 4の遠心油圧をキャンセルするキヤ ンセル油室として機能する。 また、上記油孔 7 2は、 作動油の排出孔としても機 能し、 第 1油圧室 5 4に作動油が供給されつつある状態では、 第 2油圧室 6 8内 の作動油が油孔 7 2から排出されていくが、 溝 7 0も作動油の排出路として機能 し、 第 2油圧室 6 8内の作動油は溝 7 0を経由してバランサ壁 6 0の背面側へも 排出されるので、 第 2油圧室 6 8からの作動油の排油抵抗が低減されている。 第 2ピストン 2 0は、 プレス成形品であり、軸方向における位置が外周側ほど 第 2摩擦係合要素 1 4から段階的に離隔する内周部 2 0 aと、 その内周部 2 0 a の外周縁に連結されてタト周側ほど段階的に第 2摩擦係合要素 1 4側に向かい、 最 外周部が第 2摩擦係合要素 1 4と対向する外周部 2 0 bと、 それら内周部 2 0 a および外周部 2 O bの間を接続する断面 U字状の接続部 2 0 cとを備えている。 上記内周部 2 0 aと外周部 2 0 bとの連結部分である接続部 2 0 cは環状凸曲部 3 0 dに摺動可能に嵌め入れられており、 その接続部 2 0 cの外周面 （ァゥ夕ド ラム部 3 0の底咅 P 3 0 b側の面） にはゴム製のリップシール 7 4が固着されてお り、 そのリップシール 7 4により、 ァウタドラム部 3 0の底部 3 0 bと第 2ビス トン 2 0との間がシールされている。 また、 第 2ピストン 2 0の内周縁は入力軸 2 2に対して摺動可能とされており、 また、 その第 2ピストン 2 0の内周縁と入 力軸 2 2との間も、 第 2ピストン 2 0の内周縁に固着されたゴム製のリップシ一 ル 7 6によりシールされており、 第 2ピストン 2 0とァゥ夕ドラム咅 P 3 0の底咅 3 O bとの間に第 3油圧室 7 8が形成されている。 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.
上記第 3油圧室 7 8に、 入力軸 2 2に形成された油孔 8 0を経由して作動油が 供給されると、 第 2ピストン 2 0はァゥ夕ドラム部 3 0の底部 3 0 bから離隔す る方向に移動させられて第 2摩擦係合要素 1 4を押圧する。 また、 第 2摩擦係合 要素 1 4の第 2ピストン 2 0とは反対側には、 ァウタドラム部 3 0の外周側筒部 3 0 cに固定されて第 2摩擦係合要素 1 4が軸方向の第 1摩擦係合要素 1 側へ 移動することを阻止するスナップリング 8 2が設けられているので、 第 2ビスト ン 2 0により第 2摩擦係合要素 1 4が押圧されることにより、 その第 2摩擦係合 要素 1 4を構成する複数の内向摩擦板 3 8および外向摩擦板 4 0は互いに係合さ せられる。  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.
第 2ピストン 2 0のァウタドラム部 3 0の底咅 P 3 0 bとは反対側には、 バラン サ壁 8 4が入力軸 2 2の外周に嵌合させられている。 このバランサ壁 8 4は、 入 力軸 2 2の軸心に対して略垂直に設けられた円環板状部材であり、 バランサ壁 8 4と第 2ピストン 2 0との間には、 それらを互いに離隔する方向に付勢するリ夕 ーンスプリング 8 6が設けられている。 一方、 バランサ壁 8 6の内周縁の第 2ピ ストン 2 0とは反対側の面は、 入力軸 2 2の外周面に固設されたスナツプリング 8 8に当接させられているので、 バランサ壁 8 4は、 第 2ピストン 2 0から離隔 する方向への移動が禁止されている。 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.
また、 バランサ壁 8 4の外周縁には、 第 2ピストン 2 0との間をシールするゴ ム製のリップシール 9 0が設けられており、 バランサ壁 8 4と第 2ピストン 2 0 との間には、 第 3油圧室 7 8の遠心油圧をキャンセルするためのキャンセル油室 として機能する第 4油圧室 9 2が形成されている。  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.
以上、説明したように、 本実施例によれば、 クラッチドラム 3 0のバランサ壁 6 0の取り付け部に軸方向に延びる溝 7 0が形成されており、 その溝 7 0から第 2油圧室 6 8の作動油が排出されるので、 バランサ壁 6 0に第 2油圧室 6 8の作 動油を排出するための切り欠きを設ける必要がなくなる。 従って、 第 2油圧室 6 8からの作動油の排油抵抗を低くしつつ、 バランサ壁 6 0の強度を確保すること ができる。  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.
また、本実施例によれば、 油孔 7 2が溝 7 0に開口しているので、 油孔 7 2の 開口を、 直接、 第 2油圧室 6 8に設ける場合よりもインナドラム部 2 6の軸方向 寸法が短くでき、 ひいては、 クラッチ装置 1 0を一層小型化することができる。 また、本実施例によれば、 第 1ピストン 1 8に設けられたリップシール 6 6に より第 1ピストン 1 8とバランサ壁 6 0との間がシールされるので、 第 1 ピスト ン 1 8の軸寸法を短くでき、 ひいては、 クラッチ装置 1 0をより小型化すること ができる。  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.
また、本実施例によれば、 第 1ピストン 1 8をィンナドラム部 2 6に摺動可能 とし、 第 2ピストン 2 0を入力軸 2 2に摺動可能としているので、 両方のビスト ン 1 8、 2 2をインナドラム部 2 6に摺動可能に構成するよりもインナドラム部 2 6を短くすることができ、 また、 インナドラム部 2 6と入力軸 2 2との間は溶 接により結合されているので、 前記特許文献 1のように、 スプラインにより結合 する場合に比較して結合部分の軸方向寸法が短くなるので、 このことによつても インナドラム部 2 6を短くすることができる。 従って、 クラッチ装置 1 0全体を 小型化することができる。 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.
また、 本実施例によれば、 第 1溶接部 2 4および第 2溶接部 2 8が径方向に並 設されていることから、 入力軸 2 2とィンナドラム部 2 6、 およびィンナドラム 部 2 6とァウタドラム部 3 0を、 同時に溶接することが可能となるので、 溶接コ ストを削減することができる。  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.
また、 本実施例によれば、 ァゥ夕ドラム音 P 3 0の内周側筒部 3 0 aが溶接部 2 4、 2 8の深さ方向に形成されていることから、 ァゥ夕ドラム部 3 0の内周側筒 部 3 0 aの径方向外側から、 第 1溶接部 2 4および第 2溶接部 2 8の探傷を行う ことができる。  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.
また、 本実施例によれば、 探傷用プローブ 1 0 0において超音波出力部 1 0 よりも先端側の先端部 1 0 4を、 底部 3 0 bに形成された環状凸曲部 3 0 dに収 容することができるので、 先端部 1 0 4がァウタドラム部 3 0の内周側筒部 3 0 aの径方向外側に配置される場合に比較して、 ァウタドラム部 3 0の内周側筒部 3 0 aを短くすることができる。  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.
また、 本実施例によれば、 ァウタドラム部 3 0に設けられたリップシール 5 0 により第 1ピストン 1 8とァウタドラム咅 3 0との間がシールされ第 2ピストン 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
2 0に設けられたリップシール 7 4、 7 6により、 ァゥ夕ドラム部 3 0と第 2ピ ストン 2 0との間、 および入力軸 2 2と第 2ピストン 2 0との間がそれぞれシー ルされるので、 ァウタドラム部 3 0および第 2ピストン 2 0の軸寸法を短くでき 、 ひいては、 クラッチ装置 1 0をより小型化することができる。 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.
また、 本実施例によれば、 第 1 ピストン 1 8は、 ァゥ夕ドラム部 3 0の環状凸 曲咅 P 3 0 dの外周面に摺動可能に嵌合し、 第 2ピストン 2 0は、 ァウタドラム部 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
3 0の環状凸曲部 3 0 dの内周面に摺動可能に嵌合するものであることから、 第 1 ピストン 1 8および第 2ピストン 2 0はクラッチドラム 3 0の両面に直接的に 摺動可能に嵌合するので、 クラッチ装置 1 0が小型となる。 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.
また、 本実施例によれば、 第 1摩擦係合要素 1 2および第 2摩擦係合要素 1 4 は、 クラッチドラム 3 0内において軸心方向に所定距離を隔てて配置され、 第 1 ビストン 1 8は、 軸心方向において第 2ピストン 2 0から離隔する方向に駆動さ れたときに第 1係合要素 1 2を押圧し、 第 2ピストン 2 0は、前記軸心方向にお いて第 1 ビストン 1 8から離隔する方向に駆動されたときに第係合要素 1 4を押 圧するものであることから、 クラッチドラム 3 0の両面にすなわち軸心方向の両 側に設けられた第 1 ピストン 1 8および第 2ピストン 2 0を用いて、 クラッチド ラム 3 0内において軸心方向に所定距離を隔てて配置された第 1摩擦係合要素 1 2および第 2摩擦係合要素 1 4をそれぞれ係合作動させることが可能となる。 以上、 本発明の実施例を図面に基づいて詳細に説明したが、 本発明はその他の 態様においても適用される。 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.
たとえば、前述の実施例では、 油孔 7 2は、 複数の溝 7 0の半数に設けられて いたが、 複数の溝 7 0の全部に対して油孔 7 2が設けられてもよい。 また、 溝 7 0の数は前述の実施例のものに限定されず、 要求される排油抵抗に応じて適宜設 定される。  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.
また、前述の実施例では、 第 1 ピストン 1 8とバランサ壁 6 0との間はリップ シール 6 6によりシールされていたが、 第 2発明の実施以外の場合には、 リップ シール 6 6に代えて、 オイルシール等、 他のシール部材を用いても良い。 また、 第 1、 第 3 第 4油圧室 5 4、 7 8、 9 2のシールも、 オイルシール等、 他のシ —ル部材を用いても良い。  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.
なお、 上述したのはあくまでも一実施形態であり、 本発明は当業者の知識に基 づいて種々の変更、 改良を加えた態様で実施することができる。  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

請求の範囲 The scope of the claims
1 . 摩擦係合要素を支持するクラッチドラムの外側に該クラッチドラムとともに 油圧室を形成するビストンと、 該ピストンの前記油圧室側とは反対の背面側に該 ビストンとともにキャンセル油室を形成するバランサ壁とが設けられた自動変速 機のクラッチ装置であって、 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,
前記バ^ンサ壁が前記クラッチドラムの内周部に取り付けられており、 該クラッチドラムの前記ノ ランサ壁が取り付けられた部分に形成され、 軸心方 向に延びる複数の溝と、  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;
前記キャンセル油室に作動油を供給する供給油孔と  A supply oil hole for supplying hydraulic oil to the cancel oil chamber;
を、 含むことを特徴とする自動変速機のクラッチ装置。  A clutch device for an automatic transmission, comprising:
2 . 前記供給油孔は、 クラッチドラムの内周部に形成されて、 前記該溝内に開口 するものである請求項 1の自動変速機のクラッチ装置。  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 . 前記ピストンには、 該ピストンと前記バランサ壁の外周部との間をシールす るリップシールが設けられていることを特徴とする請求項 1または 2に記載の自 動変速機のクラッチ装置。  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. .
PCT/JP2005/008741 2004-05-06 2005-05-06 Clutch device for automatic speed changer WO2005108811A1 (en)

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JP2004137422A JP2005320991A (en) 2004-05-06 2004-05-06 Clutch device for automatic transmission
JP2004-137422 2004-05-06

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1764523A2 (en) * 2005-09-16 2007-03-21 Zf Friedrichshafen Ag Multi-disc clutch device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101106747B1 (en) * 2011-04-05 2012-01-18 씨스톤 테크놀로지스(주) Clutch

Citations (3)

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Publication number Priority date Publication date Assignee Title
JPH0921430A (en) * 1995-07-07 1997-01-21 Jatco Corp Hydraulic clutch device and sealing structure for hydraulic circuit
JP2001041261A (en) * 1999-07-29 2001-02-13 Aisin Aw Co Ltd Clutch device
JP2003106341A (en) * 2001-09-28 2003-04-09 Aisin Aw Co Ltd Clutch device of automatic speed change gear

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0921430A (en) * 1995-07-07 1997-01-21 Jatco Corp Hydraulic clutch device and sealing structure for hydraulic circuit
JP2001041261A (en) * 1999-07-29 2001-02-13 Aisin Aw Co Ltd Clutch device
JP2003106341A (en) * 2001-09-28 2003-04-09 Aisin Aw Co Ltd Clutch device of automatic speed change gear

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1764523A2 (en) * 2005-09-16 2007-03-21 Zf Friedrichshafen Ag Multi-disc clutch device
EP1764523A3 (en) * 2005-09-16 2009-08-05 Zf Friedrichshafen Ag Multi-disc clutch device

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