WO2005108812A1 - 自動変速機のクラッチ装置 - Google Patents
自動変速機のクラッチ装置 Download PDFInfo
- Publication number
- WO2005108812A1 WO2005108812A1 PCT/JP2005/008742 JP2005008742W WO2005108812A1 WO 2005108812 A1 WO2005108812 A1 WO 2005108812A1 JP 2005008742 W JP2005008742 W JP 2005008742W WO 2005108812 A1 WO2005108812 A1 WO 2005108812A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- drum
- clutch
- piston
- engagement element
- biston
- Prior art date
Links
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
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- 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
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- 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 more particularly to a technology capable of miniaturizing the clutch device.
- a clutch device in which two sets of friction engagement elements are supported on one clutch drum is known.
- a biston for engaging one friction engagement element is disposed inside the clutch drum, and a piston for engaging the other friction engagement element is provided outside the clutch drum.
- one of the pistons is a so-called pull piston.
- the clutch device of the automatic transmission described in Patent Document 1 Japanese Patent Application Laid-Open No. 2003-16034 1 is that.
- the biston on the outer peripheral side is used as a pull piston, and when the biston is moved in a direction away from the clutch drum, one friction engagement element is It is engaged.
- the clutch device of the above-mentioned patent document 1 rotates integrally with the clutch drum on the rotating shaft, and connects an axial member, which can be considered as a inner drum portion of the clutch drum, by splines.
- the piston is made slidable. Therefore, the axial member needs to have a length capable of sliding the two pistons, and the axial length becomes relatively long, which in turn causes a problem that the entire clutch device becomes large.
- the present invention has been made against the background described above, and an object of the present invention is to provide a clutch device which can be miniaturized. Disclosure of the invention
- the first invention for achieving the first object comprises: (a) a clutch drum; (b) first and second friction engagement elements supported by the clutch drum; (c) an outer periphery of the clutch drum A first piston, axially displaceable on one side, for engaging said first frictional engagement element, and (d) axially displaceable on the inner circumferential side of the clutch drum, A clutch device for an automatic transmission comprising a second screw for engaging a second frictional engagement element, wherein (e) the clutch drum comprises an inner drum portion welded to the rotation shaft; An outer drum portion welded to the inner drum portion to support the first frictional engagement element and the second frictional engagement element, and ⁇ the first biston is axially slidable with respect to the inner drum portion (G) said second Tons, characterized in that it is slidable in the axial direction with respect to the rotation axis.
- the first piston can slide on the inner drum portion and the second piston can slide on the rotary shaft, so both screws can be slid on the inner drum portion.
- the inner drum portion can be made shorter than the movable structure, and the inner drum portion and the rotating shaft are connected by welding, as in the case of Patent Document 1, when connecting by splines As compared with this, the axial dimension of the joint portion is shortened, which also makes it possible to shorten the inner drum portion. Therefore, the entire clutch device can be miniaturized.
- a second aspect of the present invention is the clutch apparatus according to the first aspect, wherein a welded portion between the rotating shaft and the inner drum portion and a welded portion between the inner drum portion and the outer drum portion extend in a radial direction. It is characterized by being juxtaposed.
- an inner circumferential end to be welded to the inner drum portion is formed in a depth direction of the welding portion.
- the radial outer end of the inner peripheral end of the feeder drum is It is possible to detect flaws in the welds between the auta drum and the inner drum and between the inner drum and the shaft.
- a fourth aspect of the present invention is the clutch apparatus according to the third aspect, wherein the water drum portion has an annular convex curved portion or an annular bent portion which is further recessed in the depth direction of the welding portion than the inner circumferential end. It is characterized by
- the tip of the flaw detection probe for flaw detection of the weld between the outer drum and the inner drum and the weld between the inner drum and the rotating shaft is ultrasonic wave. Even if the tip projects beyond the output section, the tip can be accommodated in the annular convexly curved section, so that the tip is disposed radially outward of the inner circumferential end of the water drum section. In comparison, the inner circumferential end of the footer drum can be shortened.
- a fifth aspect of the invention is the clutch apparatus according to any one of the first to fourth aspects of the invention.
- the lip seal provided on the drum of the sun drum seals between the first piston and the water drum portion.
- the accommodating portion is made thick.
- the shaft dimensions of the part can be shortened, and hence the clutch device can be further miniaturized.
- the sixth invention is the clutch apparatus according to any one of the first invention to the fifth invention, wherein the second biston includes a lip seal for sealing between the water drum portion and the lip shaft, and a seal between the lip shaft and the rotary shaft. It is important to note that a lip seal is To be a reward.
- the lip seal seals between the avatar drum portion and the second biston and between the rotation shaft and the second biston, the axial dimension of the second piston is obtained.
- the clutch device can be further miniaturized.
- the seventh invention is the clutch apparatus of the fourth invention, wherein the first piston is slidably fitted on the outer peripheral surface of the annular convex curved portion of the water drum portion, and the second screw is the water drum. It is slidably fitted on the inner circumferential surface of the annular convex curved part of the part.
- the clutch device since the first piston and the first biston are slidably fitted directly on both surfaces of the clutch drum, the clutch device becomes compact.
- the first frictional engagement element and the first frictional engagement element are separated by a predetermined distance in the axial direction in the clutch drum.
- the first screw when driven in a direction away from the second biston in the axial direction, pressing the second engagement element;
- the first engaging element is pressed when driven in a direction away from the first biston in the axial direction.
- the eighth aspect of the invention configured as described above, by using the first piston and the second piston provided on both sides of the clutch drum, that is, on both sides in the axial direction, the axial direction can be obtained in the clutch drum.
- the first friction engagement element and the second friction engagement element arranged at a predetermined distance apart from each other can be engaged and operated.
- FIG. 1 is a cross-sectional view showing a part of an automatic transmission including a clutch device to which the present invention is applied.
- FIG. 2 is a view showing a state in which a flaw detection probe is disposed on the outer peripheral side of the inner peripheral side cylindrical portion of the water drum portion in order to perform the flaw detection inspection of the first welded portion and the second welded portion.
- FIG. 3 is a cross-sectional view in which the inner drum portion is cut in the radial direction so as to include the grooves.
- FIG. 1 is represented by a part of an automatic transmission including a clutch device 10 to which the present invention is applied, that is, an alternate long and short dash line.
- FIG. 6 is a cross-sectional view showing the upper half of the shaft center.
- the clutch device 10 has a cylindrical clutch drum 1 with a bottom, which supports the first friction engagement element 12 and the second friction engagement element 14 so as to be spaced apart by a predetermined distance in the axial direction.
- the first piston 18 is disposed so as to cover the clutch drum 16 according to the M rule of T, and the second biston 10 is disposed inside the clutch drum 16.
- the clutch drum 16 has an inner drum portion 26 welded to each other at the first welding portion 24 at the input shaft 22 which is a rotating shaft, and the inner drum portion 26 and the second welding portion 28 mutually It consists of an arc-shaped drum ⁇ 30 which is welded.
- the input shaft 22 is a torque-compact turbine shaft that is rotationally driven by a traveling drive source such as an engine.
- the inner drum portion 6 is a cylindrical member, and is disposed on the inner peripheral side of the first piston 18, and an end face on the second piston 20 side protrudes radially outward on the input shaft 22 2 2 2 It is made to coincide with the surface on the second Biston 20 side of a.
- the first welded portion 24 is formed on the outer peripheral edge of the surface on the second biston 20 side of the ridge portion 22a and the inner peripheral edge of the surface on the second biston 20 side of the inner drum rod P 26. ing.
- 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 in one of the axial directions. 0a, an annular bottom portion 30b whose inner peripheral edge is connected to the inner peripheral side cylindrical portion 30a, and an outer peripheral side tubular portion 30c connected to the outer peripheral edge of the bottom portion 30b It is done.
- the inner circumferential side tubular portion 3 0 a and the outer circumferential side tubular portion 3 0 c have a cylindrical shape with the axis as the center line.
- the inner cylindrical portion 30a is disposed so as to fit on the outer periphery of the inner drum portion 26, and the end face on the second piston 20 side is on the second piston 20 side of the inner drum portion 26.
- the second welding portion 28 is formed on the inner peripheral edge of the end face, which is aligned with the end face. Therefore, the first welding portion 24 and the second welding portion 28 are juxtaposed so as to overlap in the radial direction.
- the first welding portion 24 and the second welding portion 28 are formed, for example, by laser beam welding so that the welding depth is in a direction parallel to the axial center. It is made.
- the axial length of the inner cylindrical portion 3 0 a is longer than the welding depth of the first welded portion 24 and the second welded portion 28.
- the bottom 30 b is provided substantially perpendicularly to the radial direction of the input shaft 22, and is connected to the end on the first piston 18 side of the inner circumferential side tubular portion 3 0 a. In addition, the bottom 30 b is located at a position slightly closer to the outer periphery than the midpoint in the radial direction, and the first piston 18 further than the end on the first piston 18 side of the inner cylindrical portion 30 a.
- An annular convex curved portion 30 d having a U-shaped cross section 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.
- FIG. 2 shows the flaw detection probe 100 in order to conduct flaw detection inspection of the first welding portion 24 and the second welding portion 28.
- the inner circumferential side cylindrical portion 30a of the welding drum portion 30 is shown in FIG. It is a figure which shows the state arrange
- the tip end portion 104 on the tip side of the ultrasonic wave output P 102 is formed on the bottom portion 30 b of the water drum portion 30. It is arranged so as to be accommodated in the annular convex curved portion 30 d, and in that state, the ultrasonic wave is irradiated from the ultrasonic wave output portion 102 to the welded portions 24 and 28. , Welds 4.2 8 are flawed.
- the outer peripheral side cylindrical portion 30 c of the sun drum portion 30 extends from the bottom portion 30 b to the second piston 20 side, and the inner peripheral surface in the vicinity of the opening portion
- a plurality of inward friction plates 32 of the friction engagement element 1 2 are spline fitted so as not to be relatively rotatable.
- the first friction engagement element 12 is composed of a plurality of inward friction plates 32 and a plurality of outward friction plates 34 interposed between the plurality of inward friction plates 32.
- the plurality of outwardly directed friction plates 34 are spline-fit relative to each other on the outer peripheral surface of the ring gear 36 functioning as a clutch hub.
- the second friction engagement element is further provided on the inner circumferential surface of the outer circumferential side cylindrical portion 30 c of the faucet drum portion 30 on the bottom 30 b side than the portion supporting the first friction engagement element 1.
- 1 4 inward friction plates 3 8 are spline fitted non-rotatably.
- the second friction engagement element 14 is composed of a 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 4 0 are not relatively rotatable on the outer peripheral surface of the clutch hub 4 2 substantially perpendicular to the input shaft 2 2.
- the spline is fitted to the Noh. Since the inner peripheral edge of the clutch hub 42 is fixed to the sun gear 4 4, the clutch hub 4 2 is integrally rotated with the sun gear 4 4.
- the first piston 18 is a press-formed product press-formed from a steel plate, and is connected to the outer peripheral edge of the annular bottom portion 18 a and the bottom portion 8 a thereof, and the outer periphery of the oven drum ⁇ 0 And a cylindrical projecting portion 18 c connected to the cylindrical portion 18 b and protruding in the axial direction beyond the base drum portion 30.
- the projecting portion 18 c has a spline shape over the entire circumference, and is configured such that the tips of the splines of the inner circumferential surface coincide with the inner circumferential surface of the cylindrical portion 18 c.
- An outer peripheral surface of an annular plate-like pressing member 46 is spline-fitted to the projecting portion 18 c of the first piston 18.
- One surface of the outer peripheral edge of the pressing member 46 is in contact with the end surface of the cylindrical portion 18 b of the first piston 18, and the other surface is a snap fixed to the inside of the projecting portion 18 c Since the ring 48 is in contact with the pressing member 46, the pressing member 46 can not move in the circumferential and axial directions relative to the first biston 18.
- the bottom portion 8a is formed with an annular concave portion 18d which is slidably fitted to the outer peripheral surface of the annular convex portion 30d of the utter drum 30, and which can be accommodated therein. Then, on the outer peripheral surface of the outer peripheral side corner portion 30 e of the annular convex curved portion 30 d of the data drum portion 30, the annular concave portion 18 d of the first piston 18 and the outer drum sound P 3 0 A rubber lip seal 50 is fixed by vulcanization to seal between it and the annular convex curved portion 30 d. In addition, the inner peripheral edge of the first piston 18 is slidable with respect to the outer peripheral surface of the inner drum portion 26.
- the space between the inner peripheral edge of the first piston 18 and the inner drum portion 26 is also 1 Sealed by a rubber lip seal 52 fixed to the inner peripheral edge of Biston 18
- a first hydraulic chamber 54 is formed therebetween.
- the pressing member 46 fixed to the projection 18 c of the first piston 18 is moved in a direction away from the bottom 30 b of the drum unit 30, so that the first frictional engagement element 12 is moved. Press.
- the first friction engagement element 11 The first frictional engagement element 11 is fixed to the outer peripheral side cylindrical portion 30 c of the evening drum portion 30 on the side opposite to the pressing member 46, and the first frictional engagement element 1 in the axial direction is formed. Since the snap ring 58 is provided to prevent movement to the four side, the first friction engagement element 12 is pressed by the pressing member 46 so that the first friction engagement element 1 1 The plurality of inward friction plates 32 and the outward friction plates 34 constituting the two are engaged with each other.
- a disc-shaped balancer wall 60 is fitted on the outer periphery of the inner drum portion 26.
- the balancer wall 60 is connected to an annular plate portion 60 a substantially perpendicular to the axial center of the inner drum portion 26 and to the outer peripheral edge of the annular plate portion 60 a to form the first piston 1. Consists of a tubular portion 6 O b facing the 8 side.
- a return spring 62 is provided between the annular plate portion 60 a and the bottom 18 a of the first piston 18 so as to bias them in the direction away from each other.
- the surface on the opposite side of the first piston 18 of the inner peripheral edge of the balancer wall 60 is in contact with the snap ring 64 fixed to the outer peripheral surface of the inner drum portion 26.
- the wall 60 is prohibited from moving away from the first biston 18.
- the radius of the inner peripheral surface of the cylindrical portion 60 b is set to be slightly larger than the radius of the radial outer surface of the annular recess 18 d of the first piston 18, and the annular recess 1
- the rubber lip seal 6 6 provided on the outer peripheral surface of the outer peripheral side corner portion 18 d of 8 d makes the cylindrical portion 6 0 d of the balancer wall 60 and the annular recess 1 8 d of the first piston 18 8
- a second hydraulic pressure chamber 68 is formed between the balancer wall 60 and the bottom 18a of the first screw hole 18.
- FIG. 3 is a sectional view in which the inner drum portion 26 is cut in the radial direction so as to include the grooves 70. As shown in FIG. 3, the grooves 70 are equally spaced in the circumferential direction in the present embodiment. A place is provided.
- the side of the groove 70 communicating with the second hydraulic chamber 68 is provided.
- An oil hole 72 is formed at one end of which is open.
- the oil holes 72 are not provided for all the grooves 70, but are provided in a part (four in FIG. 3).
- the oil hole 72 functions as an supply oil hole for supplying the hydraulic oil to the second hydraulic chamber 68, and when centrifugal force acts on the hydraulic oil, the hydraulic oil becomes the oil hole 72 and the groove 70. It is supplied to the second hydraulic chamber 68 from the input shaft 22 side via the input shaft 22.
- the second hydraulic pressure chamber 68 functions as a cancellation oil chamber for canceling the centrifugal hydraulic pressure of the first hydraulic pressure chamber 54.
- the oil hole 72 also functions as a discharge hole for hydraulic oil, and in a state where hydraulic oil is being supplied to the first hydraulic chamber 54, the hydraulic oil in the second hydraulic chamber 68 is an oil hole. Although it is discharged from 7 2, groove 70 also functions as a discharge path for hydraulic oil, and the hydraulic oil in second hydraulic chamber 6 8 is also discharged to the back side of balancer wall 60 via groove 70. As a result, the resistance to discharge of hydraulic fluid from the second hydraulic pressure chamber 68 is reduced.
- the second piston 20 is a press-formed product, and an inner circumferential portion 20 a that is stepwise separated from the second frictional engagement element 14 as the position in the axial direction is on the outer circumferential side, and its inner circumferential portion 20 a And the outer periphery 20 0 b of which the outermost periphery faces the second friction engagement element 14, and the outer periphery 20 b is connected to the outer periphery of the outer circumferential side in a stepwise manner toward the outer periphery.
- a section U-shaped connecting section 20 c connecting between the section 20 a and the outer peripheral section 2 O b is provided.
- a connecting portion 20 c which is a connection portion between the inner peripheral portion 0 a and the outer peripheral portion 20 b is slidably fitted in the annular convex curved portion 30 d, and the outer periphery of the connecting portion 20 c
- a rubber lip seal 74 is fixed to the face (the face on the bottom 30 b side of the drum portion 30), and the lip seal 7 4 There is a seal between bottom ridge 0 b and second screw 20.
- a third oil pressure chamber 7 8 is sealed between the second piston 20 and the bottom 3 O b of the water drum portion 30, sealed by a rubber seal 7 6 fixed to the inner peripheral edge of the piston 20. Is formed.
- the second piston 20 When the hydraulic oil is supplied to the third hydraulic chamber 78 via the oil hole 80 formed in the input shaft 12, the second piston 20 is the bottom portion 3 O of the reaction drum portion 30. It is moved in the direction away from b to press the second frictional engagement element 14. Also, the second friction engagement The second friction engagement element 14 is fixed to the outer peripheral side cylindrical portion 30c of the support drum portion 30 on the opposite side of the second piston 20 of the element 14 to the first friction engagement element in the axial direction. Since a snap ring 82 is provided to prevent movement to the 1 1 side, the second frictional engagement element 14 is pressed by the second piston 20 so that the second frictional engagement element The plurality of inward friction plates 38 and the outward friction plates 40 that constitute 14 are engaged with each other.
- a balance wall 84 is fitted to the outer periphery of the input shaft 22 on the opposite side of the bottom 30b of the outer drum 30 of the second piston 20.
- the balancer wall 84 is an annular plate-like member provided substantially perpendicular to the axial center of the input shaft 22, and between the balancer wall 84 and the second biston 20, A return spring 86 is provided to bias in the direction away from each other.
- the surface opposite to the second piston 20 of the inner peripheral edge of the balancer wall 86 is in contact with the snap ring 8 8 fixed to the outer peripheral surface of the input shaft 22. The wall 84 is prohibited from moving away from the second piston 20.
- a rubber-made lip seal 90 is provided on the outer peripheral edge of the balancer wall 84 so as to seal between the second piston 20 and the balancer wall 84, and between the balancer wall 84 and the second biston 20
- the fourth hydraulic chamber 92 is formed to function as a cancel oil chamber for canceling the centrifugal hydraulic pressure of the third hydraulic chamber 78.
- the first piston 18 can slide on the inner drum portion 26 and the second piston 20 can slide on the input shaft 22.
- the inner drum portion 26 can be made shorter than that in which both bistons 18 and 22 can slide on the inner drum rod 26 and between the inner drum portion 26 and the input shaft 22
- the input shaft 2 and the inner drum portion 26 and the inner drum portion 26 can be used.
- the welding cost can be reduced because the part 26 and the water drum part 30 can be welded at the same time.
- the inner cylindrical portion 30a of the outer drum portion 30 is formed in the depth direction of the welded portions 24 and 28, the upper drum portion is formed.
- the first welded portion 24 and the second welded portion 28 can be subjected to flaw detection from the radially outer side of the inner peripheral side cylindrical portion 30a of the 30.
- the distal end portion 104 on the tip end side of the ultrasonic wave output portion 102 is an annular convex curved portion 3 0 d formed on the bottom portion 30b.
- the outer drum portion 30 can be accommodated.
- the inner cylindrical portion 3 0 a can be shortened.
- the lip seal 50 provided on the sun drum portion 30 seals the gap between the first piston 18 and the sun drum portion 30 so that the first biston 20 is formed.
- the provided lip seals 7 4 and 7 6 respectively seal between the outer drum 0 and the second piston 20 and between the input shaft 22 and the second piston 20.
- the axial dimensions of the tubular drum portion 30 and the second biston 10 can be shortened, and hence the clutch device 10 can be further miniaturized.
- the first piston 18 is slidably fitted on the outer peripheral surface of the annular convex curved portion 30 d of the outer drum portion 30, and the second piston 20 is mounted on the outer drum portion 3.
- the first piston 18 and the second piston 20 slide directly on both sides of the clutch drum 30 because the first piston 18 and the second piston 20 are slidably fitted on the inner peripheral surface of the annular convex curved portion 30 d of 0. Since the movable engagement is achieved, the clutch device 10 is compact.
- the first frictional engagement element 12 and the second frictional engagement element 14 are disposed at a predetermined distance in the axial direction in the clutch drum 30, and the first screw 1 8 pushes the first engagement element 12 when driven in the direction away from the second piston 20 in the axial direction, and the second piston 20 receives the first engagement element in the axial direction. Since it presses the first engagement element 14 when driven in a direction away from the piston 18, both sides of the clutch drum 30, ie, both in the axial direction, are pressed.
- the groove 70 extending in the axial direction is formed in the balancer wall 60 mounting portion of the clutch drum 30, and the hydraulic oil in the second hydraulic chamber 68 is discharged from the groove 70. Therefore, it is not necessary to provide the balancer wall 60 with a cutout for discharging the hydraulic fluid of the second hydraulic chamber 68. Therefore, the strength of the balancer wall 60 can be secured while reducing the resistance to the discharge of hydraulic fluid from the second hydraulic pressure chamber 68.
- the clutch device 10 can be further miniaturized.
- 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 dimensions can be shortened, and in turn, the clutch device 10 can be further miniaturized.
- the rotation axis is the input shaft 22.
- the output shaft or the counter axis may be the rotation axis.
- the annular convex curved portion 30d is formed on the bottom portion 30b of the autaa drum portion 30. Or the inner circumference of the drum portion 30.
- the length of the tip end portion 104 ie, the length of the tip end side of the ultrasonic wave output portion 102 is sufficiently short
- the length of the inner end 30a is not so long even if the flaw detection is performed by arranging the test piece on the outer side in the radial direction of the side cylindrical portion 30a, an annular convex curved portion 30d is formed. You do not have to.
- the seals of the first to fourth hydraulic chambers 54, 68, 78, 92 are lip seals 50, 52, 66, 74, 76, 90, respectively.
- the lip seals 50, 52, 66 have been used.
- Other seal members such as oil seals may be used in place of all or part of 74, 76, and 90.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/579,506 US7637363B2 (en) | 2004-05-06 | 2005-05-06 | Clutch device for automatic speed changer |
EP05738746.6A EP1744073B1 (en) | 2004-05-06 | 2005-05-06 | Clutch device for automatic speed changer |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-137421 | 2004-05-06 | ||
JP2004137421A JP4333469B2 (ja) | 2004-05-06 | 2004-05-06 | 自動変速機のクラッチ装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005108812A1 true WO2005108812A1 (ja) | 2005-11-17 |
Family
ID=35320294
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/008742 WO2005108812A1 (ja) | 2004-05-06 | 2005-05-06 | 自動変速機のクラッチ装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US7637363B2 (ja) |
EP (1) | EP1744073B1 (ja) |
JP (1) | JP4333469B2 (ja) |
CN (1) | CN100494720C (ja) |
WO (1) | WO2005108812A1 (ja) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100811611B1 (ko) | 2006-08-17 | 2008-03-11 | 현대자동차주식회사 | 자동변속기의 클러치 동력 전달장치 |
DE102007027120B4 (de) * | 2007-06-13 | 2015-10-22 | Volkswagen Ag | Kupplung mit Stützelement für ein Lamellenpaket |
JP2010133544A (ja) | 2008-12-08 | 2010-06-17 | Toyota Motor Corp | 自動変速機のピストン装置 |
KR101648984B1 (ko) * | 2009-03-31 | 2016-08-17 | 쟈트코 가부시키가이샤 | 다판 마찰 요소 |
DE102012013873B4 (de) * | 2012-07-12 | 2019-03-28 | GETRAG B.V. & Co. KG | Lamellenträger-Lageranordnung und Kupplungsanordnung für einen Kraftfahrzeugantriebsstrang |
JP6277610B2 (ja) * | 2013-06-24 | 2018-02-14 | 日産自動車株式会社 | 多板摩擦係合装置 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS6177455U (ja) * | 1984-10-29 | 1986-05-24 | ||
JPS63246541A (ja) * | 1987-03-31 | 1988-10-13 | Nissan Motor Co Ltd | 自動変速機用摩擦要素のドラム |
JP2003106341A (ja) | 2001-09-28 | 2003-04-09 | Aisin Aw Co Ltd | 自動変速機のクラッチ装置 |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4237749A (en) * | 1979-05-11 | 1980-12-09 | General Motors Corporation | Multi-speed power transmission |
JP3618699B2 (ja) * | 2001-07-26 | 2005-02-09 | アイシン・エィ・ダブリュ株式会社 | 自動変速機のクラッチ装置 |
JP3618710B2 (ja) | 2001-10-23 | 2005-02-09 | アイシン・エィ・ダブリュ株式会社 | 自動変速機のクラッチ装置 |
JP2004019830A (ja) | 2002-06-18 | 2004-01-22 | Toyota Motor Corp | 動力伝達断続装置 |
EP1568906B1 (de) * | 2004-02-27 | 2008-06-18 | BorgWarner Inc. | Doppelkupplung |
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2004
- 2004-05-06 JP JP2004137421A patent/JP4333469B2/ja not_active Expired - Fee Related
-
2005
- 2005-05-06 EP EP05738746.6A patent/EP1744073B1/en not_active Expired - Fee Related
- 2005-05-06 US US11/579,506 patent/US7637363B2/en not_active Expired - Fee Related
- 2005-05-06 WO PCT/JP2005/008742 patent/WO2005108812A1/ja not_active Application Discontinuation
- 2005-05-06 CN CNB2005800144651A patent/CN100494720C/zh not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6177455U (ja) * | 1984-10-29 | 1986-05-24 | ||
JPS63246541A (ja) * | 1987-03-31 | 1988-10-13 | Nissan Motor Co Ltd | 自動変速機用摩擦要素のドラム |
JP2003106341A (ja) | 2001-09-28 | 2003-04-09 | Aisin Aw Co Ltd | 自動変速機のクラッチ装置 |
Also Published As
Publication number | Publication date |
---|---|
US20070215432A1 (en) | 2007-09-20 |
EP1744073A1 (en) | 2007-01-17 |
CN100494720C (zh) | 2009-06-03 |
JP2005320990A (ja) | 2005-11-17 |
EP1744073A4 (en) | 2012-07-04 |
EP1744073B1 (en) | 2013-06-26 |
US7637363B2 (en) | 2009-12-29 |
JP4333469B2 (ja) | 2009-09-16 |
CN1950622A (zh) | 2007-04-18 |
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