JP2004346966A - Multi-disk frictional engagement device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a multi-disk frictional engagement device simplified in structure, reduced in size, and expected to reduce the number of components and production cost. <P>SOLUTION: A plurality of driven plates 11 to 16 spline-fitted to a spline groove 2 formed in the inner periphery of a transmission case 1 and drive plates 21 to 26 spline-fitted to a spline groove 7 formed in the outer periphery of a rotating body 5 are arranged alternately each other. A piston 41 is arranged on one side thereof and a retaining plate 17 spline-fitted to the spline groove 2 is arranged on the other side. Also, a snap ring 30 having the function of a dish plate in which the outer peripheral edge 32 thereof is locked to the ring groove and the inner peripheral edge 31 abuts on the side face 17a of the retaining plate 17 is installed. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a multi-disc friction engagement device such as a multi-disc clutch and a multi-disc brake used in, for example, an automatic transmission.
[0002]
[Prior art]
2. Description of the Related Art An automatic transmission for a vehicle shifts using a plurality of multi-plate friction engagement devices such as a high clutch, a reverse clutch, a 2 & 4 brake, a low clutch, and a low & reverse brake.
[0003]
A multi-disc friction engagement device such as a multi-disc clutch and a multi-disc brake used in these automatic transmissions will be described.
[0004]
FIG. 7 is a sectional view of a main part of an automatic transmission having a multi-plate brake, and 101 is a transmission case. A plurality of spline grooves 102 extending in the axial direction are formed on the inner surface of the transmission case 101, and spline teeth formed on the outer periphery of the plurality of driven plates 111 to 116 and the retaining plate 117 move in the spline groove 102 in the axial direction. Spline fitting is possible. Further, a snap ring 118 for retaining the retaining plate 117 and receiving a thrust load is engaged with an annular ring groove 102a formed at an end of the spline groove 102.
[0005]
On the other hand, a plurality of spline grooves 105 extending in the axial direction are also formed on the outer periphery of the hub 104 of the rotating body 103, and are formed on the inner periphery of the plurality of drive plates 121 to 126 alternately arranged with the driven plates 111 to 116. The spline teeth are spline-fitted movably in the axial direction.
[0006]
Further, a piston 106 is provided on the rear end side of the transmission case 101 so as to be movable in the axial direction, a dish plate 119 is interposed between the piston 106 and the driven plate 111, and provided on the piston 106 and the transmission case 101. A return spring 109 is provided between the retainer 108 and the retainer 108.
[0007]
When hydraulic oil is supplied to the hydraulic chamber 110 formed between the rear surface of the piston 106 and the transmission case 101, the piston 106 moves forward against the spring force of the return spring 109, and moves through the dish plate 119. The driven plates 111 to 116 and the drive plates 121 to 126 are pressed against the retaining plate 117 supported by the snap ring 118. By this pressing, the friction surfaces of the driven plates 111 to 116 and the drive plates 121 to 126 alternately arranged are surface-engaged, that is, fastened to brake the rotation of the rotating body 103. Here, the dish plate 119 interposed between the piston 106 and the driven plate 111 is elastically deformed, and the press-contact force between the alternately arranged driven plates 111 to 116 and the drive plates 121 to 126 gradually increases, and the fastening is performed. Reduces shock during operation.
[0008]
On the other hand, by discharging the hydraulic oil supplied to the hydraulic chamber 110, the piston 106 is pushed back by the spring force of the return spring 109, and the pressure contact force between the alternately arranged driven plates 111 to 116 and the drive plates 121 to 126 is reduced. The connection is released and the fastening is released, and the shape of the dish plate 119 returns to the no-load state.
[0009]
Similarly, in a multi-plate clutch, a plurality of driven plates whose outer circumferences are spline-fitted to spline grooves formed on the inner circumference of the clutch drum, and inner faces are spline-fitted to spline grooves formed on the outer circumference of the clutch hub. The drive plate and the drive plate are alternately arranged, and when the piston advances, the driven plate and the drive plate are pushed through the dish plate to the retaining plate supported by the snap ring by spline fitting into the spline groove of the clutch drum. In some cases, the clutch drum and the clutch hub are fastened so as to transmit power (see, for example, Patent Document 1).
[0010]
[Patent Document 1]
JP-A-3-9119
[Problems to be solved by the invention]
According to the multi-disc brake shown in FIG. 7 and the multi-disc clutch described in Patent Document 1, the dish plate is arranged between the piston and the driven plate, so that the shock is gently tightened and the shock at the time of the fastening operation is reduced. You.
[0012]
However, since the snap ring, the alternately arranged driven plate and drive plate, and the dish plate are continuously arranged in the axial direction, the multi-plate frictional engagement device such as a multi-plate brake or a multi-plate clutch is axially arranged. There is a concern that it is long, requires a large installation space, and causes an increase in weight. In particular, in an automatic transmission in which various multi-plate frictional engagement devices are arranged in the transmission case in the axial direction, the total length of the automatic transmission is increased and the weight is greatly increased.
[0013]
In addition, the number of components of the multi-plate friction engagement device is large, the configuration is complicated, and a large number of man-hours are required for the assembling operation.
[0014]
SUMMARY OF THE INVENTION Accordingly, an object of the present invention, which has been made in view of the above points, is to provide a multi-plate friction engagement device which can achieve simplification and downsizing of the configuration and can be expected to reduce the number of components and the manufacturing cost.
[0015]
[Means for Solving the Problems]
The multi-plate frictional engagement device according to claim 1, which achieves the above object, is formed on a plurality of frictional engagement plates that are spline-fitted into spline grooves formed on an inner periphery of the fixing member, and is formed on an outer periphery of the rotating body. And a friction engagement plate that is spline-fitted to the spline groove, a piston is arranged on one side of the alternately arranged friction engagement plate, and a spline formed on the fixing member on the other side. A friction engagement plate that is spline-fitted into the groove and is supported by a snap ring that is engaged with a ring groove formed in an annular shape on the inner periphery of the fixed member, and that is alternately arranged by the piston. In the multi-plate friction engagement device for fastening by pressing the snap ring to the retaining plate, the snap ring is shaped like an annular disk and moves from the inner peripheral edge to the outer peripheral edge. Te be conical away from the retaining plate, the outer peripheral edge, characterized in that the peripheral edge in the locked to the ring groove formed in the fixed member is disposed in contact with the retaining plate.
[0016]
According to a first aspect of the present invention, when the multi-plate friction engagement device is a multi-plate brake, and the friction engagement plates alternately arranged by the piston are pressed against the retaining plate, the multi-plate friction engagement device is disposed between the ring groove and the retaining plate. The arranged snap rings are elastically deformed to receive the retaining plates, and the pressing force between the alternately arranged friction engagement plates is gradually increased to perform the fastening, thereby alleviating the shock at the time of the fastening operation.
[0017]
Accordingly, since the snap ring also functions as a dish plate, the conventional dish plate can be omitted, and the compact and lightweight multi-plate friction engagement device can be obtained. In addition, with the reduction in the number of components, simplification of the configuration and simplification of the assembling work become possible, and a reduction in manufacturing cost can be expected.
[0018]
According to a second aspect of the present invention, in the multiple disc friction engagement device of the first aspect, the fixing member is a transmission case of an automatic transmission.
[0019]
According to the second aspect of the present invention, the fixing member is a transmission case of an automatic transmission, and by using a multiple disc friction engagement device for the automatic transmission, the entire automatic transmission can be reduced in size and weight. In other words, the multi-plate friction engagement device can be easily disposed in the transmission case having a limited storage volume.
[0020]
According to a third aspect of the present invention, there is provided a multi-disc friction engagement device, comprising: a plurality of friction engagement plates that are spline-fitted into spline grooves formed on an inner periphery of a clutch drum; Friction engagement plates for spline fitting are alternately arranged in the formed spline grooves, a piston is arranged on one side of the alternately arranged friction engagement plates, and formed on the clutch drum on the other side. A retaining plate supported by a snap ring engaged with a ring groove formed annularly on the inner periphery of the clutch drum, the frictional members being alternately arranged by the piston. In the multi-plate friction engagement device for pressing and fastening the mating plate to the retaining plate, the snap ring has an annular disk shape and A conical shape that is separated from the retaining plate as it transitions from the peripheral edge to the outer peripheral edge, the outer peripheral edge is locked by a ring groove formed in the clutch drum, and the inner peripheral edge is disposed in contact with the retaining plate. It is characterized by having.
[0021]
According to a third aspect of the present invention, when the multi-plate friction engagement device is a multi-plate clutch, and the friction engagement plates alternately arranged are pressed against the retaining plate by the piston, the snap ring is elastically deformed to retain the snap ring. The plates are received, and the press-contact force between the alternately arranged friction engagement plates is gradually increased to perform the fastening, thereby alleviating the impact during the fastening operation.
[0022]
Therefore, since the snap ring also functions as a dish plate, the conventional dish plate can be omitted, and the compact and lightweight multi-plate friction engagement device can be obtained. In addition, with the reduction in the number of components, simplification of the configuration and simplification of the assembling work become possible, and a reduction in manufacturing cost can be expected.
[0023]
According to a fourth aspect of the present invention, in the multi-plate friction engagement device according to any one of the first to third aspects, the snap ring has a slit extending from the inner peripheral edge to the outer peripheral edge to partially separate the snap ring. It is characterized by.
[0024]
According to the fourth aspect of the present invention, since a part of the snap ring is divided by the slit, the diameter of the snap ring can be easily reduced, the work of mounting the snap ring in the ring groove becomes easy, and the assembling workability is improved.
[0025]
BEST MODE FOR CARRYING OUT THE INVENTION
(1st Embodiment)
Next, a first embodiment of a multiple disc friction engagement device according to the present invention will be described with reference to FIGS. 1 to 5 by taking an example of a multiple disc brake in which the multiple disc friction engagement device is used in an automatic transmission. explain. FIG. 1 is a sectional view of a main part of an automatic transmission having a multi-plate brake, and FIG. 2 is an enlarged view of a portion A in FIG.
[0026]
In the figure, reference numeral 1 denotes a transmission case which is a fixed member. A plurality of spline grooves 2 extending in the axial direction are formed on the inner periphery of the transmission case 1 which is formed in a substantially hollow cylindrical shape. The spline teeth 11a to 17a formed on the outer periphery of the driven plates 11 to 16 and the retaining plate 17, which are engagement plates, are spline-fitted movably in the axial direction. Further, a snap ring 30 for retaining the retaining plate 17 and receiving a thrust load is attached to a ring groove 3 formed annularly at the end of the spline groove 2 along the inner periphery of the transmission case 1.
[0027]
On the other hand, a plurality of spline grooves 7 extending in the axial direction are also formed on the outer periphery of the hub 6 of the rotating body 5, and the drive plates 21 to 21 which are a plurality of friction engagement plates alternately arranged with the driven plates 11 to 16. The spline teeth 21a to 26a formed on the inner periphery of 26 are spline-fitted movably in the axial direction.
[0028]
Further, a piston 41 is provided on the rear end side of the transmission case 1, which is one side of the alternately arranged driven plates 11 to 16 and the drive plates 21 to 26, so as to be movable in the axial direction. The piston 41 has a top end 42 facing the driven plate 11 and forms a hydraulic chamber 43 between the rear surface of the piston 41 and the transmission case 1. A return spring 46 is provided between the piston 41 and a retainer 45 provided on the transmission case 1.
[0029]
The snap ring 30 mounted in the ring groove 3 of the transmission case 1 is made of spring steel, and FIG. 3A shows a perspective view in a no-load state, and FIG. As shown in the view of the arrow B and the sectional view taken along the line II in FIG. 13B, the retaining member 17 is formed in an annular disk shape, and gradually retains from the inner peripheral edge 31 to the outer peripheral edge 32 side. It is formed in a conical shape separated from the side, and a part thereof is divided by a slit 33 extending in a radial direction from an inner peripheral edge 31 to an outer peripheral edge 32. The outer diameter of the snap ring 30 is slightly smaller than the inner diameter of the bottom surface 3 a of the ring groove 3, the inner diameter is larger than the inner diameter of the retaining plate 17, and the inner peripheral edge 31 contacts the side surface 17 b of the retaining plate 17. It is formed to be accessible.
[0030]
The snap ring 30 thus formed has a cross-sectional shape shown in FIG. 4 (a), and is deformed by applying a load from the outer peripheral direction as shown by an arrow, and is deformed as shown in FIG. 4 (b). The diameter of the case 1 is reduced slightly to a smaller diameter. In the reduced diameter state, the snap ring 30 is inserted to the position of the ring groove 3, and the load is released to allow the snap ring 30 to be expanded and restored, so that the snap ring 30 can be easily mounted in the ring groove 3 as shown in FIG. Excellent in mounting workability. It is preferable that the width t of the slit 33 is set to the minimum dimension necessary for the diameter reduction.
[0031]
When hydraulic oil is supplied to the hydraulic chamber 43 formed between the rear surface of the piston 41 and the transmission case 1, the piston 41 moves forward against the spring force of the return spring 46, and the top end of the moving piston 41 The driven plates 11 to 16 and the drive plates 21 to 26 alternately arranged by 42 are pressed against the retaining plate 17. 5A, the pressing force P acts on the inner peripheral edge 31 of the snap ring 30, and the pressing force P acts on the inner peripheral edge 31 by the retaining plate 17 as the piston 41 advances. The outer peripheral edge 32 is pushed and expanded along the side surface 3b of the ring groove 3 and elastically deforms in a flat shape as shown in FIG. 2B, the retaining ring 17 is received by the snap ring 30, and the driven ring is alternately arranged. The friction surfaces of the plates 11 to 16 and the drive plates 21 to 26 are surface-engaged, that is, fastened to brake the rotation of the rotating body 5.
[0032]
At this time, due to the elastic deformation of the snap ring 30, the driven plates 11 to 16 and the drive plates 21 to 26, which are alternately arranged, gradually increase the pressure contact force and fasten, and the loose fastening reduces the shock at the time of fastening operation. You.
[0033]
On the other hand, when the hydraulic oil supplied into the hydraulic chamber 43 is discharged, the piston 41 is pushed back by the spring force of the return spring 46, and the pressure contact between the alternately arranged driven plates 11 to 16 and the drive plates 21 to 26 is released. To release the connection. Further, the pressing force on the snap ring 30 is also released, and the shape of the snap ring 30 returns to the no-load state.
[0034]
When the transmission case 1 is made of an aluminum alloy, it is preferable to perform a wear-resistant treatment such as forming a wear-resistant coating on the surface of the ring groove 3 by spraying a cast iron powder or the like.
[0035]
Therefore, according to the present embodiment configured as described above, since the snap ring 30 also has a function as a dish plate, the conventional dish plate can be omitted, and the axial length of the multi-plate brake is reduced. This makes it possible to reduce the size and weight of the multi-plate brake. With the compactness and weight reduction of the multi-plate brake, the mountability in the transmission case 1 is excellent, and the compactness and weight reduction of the automatic transmission can be obtained. In other words, the multiple disc brake can be easily arranged in the transmission case 1 having a limited storage volume.
[0036]
In addition, simplification of the configuration can be obtained with a reduction in the number of components, and simplification of the assembling work enables a reduction in the number of assembling steps, and a reduction in manufacturing costs can be expected.
[0037]
(2nd Embodiment)
Next, a second embodiment of the multi-plate friction engagement device according to the present invention will be described with reference to FIG. 6, taking as an example a case where the multi-plate friction engagement device is a multi-plate clutch used in an automatic transmission. For convenience of explanation, the same reference numerals are given to the portions corresponding to FIGS. 1 to 5, and the detailed description of the portions will be omitted.
[0038]
FIG. 6 is a sectional view of an essential part of the multi-plate clutch, and reference numeral 51 denotes a clutch drum. A plurality of spline grooves 2 extending in the axial direction are formed on the inner periphery of the clutch drum 51, and a plurality of driven plates 11 to 16 and spline teeth 11 a to 17 a formed on the outer periphery of the retaining plate 17 are formed in the spline groove 2. Spline-fitted movably in the axial direction. Further, a snap ring 30 is mounted on a ring groove 3 formed annularly at the end of the spline groove 2 along the inner periphery of the clutch drum 51.
[0039]
On the other hand, a plurality of spline grooves 7 extending in the axial direction are also formed on the outer periphery of the hub 53 of the clutch hub 52, and are formed on the inner periphery of the plurality of drive plates 21 to 26 alternately arranged with the driven plates 11 to 16. The spline teeth 21a to 26a are spline-fitted movably in the axial direction.
[0040]
Further, a piston 41 is provided on the rear end side of the clutch drum 51, which is one side of the alternately arranged driven plates 11 to 16 and the drive plates 21 to 26, so as to be movable in the axial direction. The piston 41 has a top end 42 facing the driven plate 11 and forms a hydraulic chamber 43 between the rear surface of the piston 41 and the clutch drum 51. A return spring 46 is provided between the piston 41 and a retainer 45 provided on the clutch drum 51.
[0041]
When hydraulic oil is supplied to the hydraulic chamber 43, the piston 41 moves forward against the spring force of the return spring 46, and the driven plate 11 to 16 and the drive plate 21 to 26 are retained by the top end 42 of the moving piston 41. It is pressed against the lining plate 17. A pressing force acts on the inner peripheral edge 31 of the snap ring 30 from the retaining plate 17, and as the piston 41 advances, the pressing force applied from the retaining plate 17 to the inner peripheral edge 31 increases the outer peripheral edge 32 to the ring groove 3. Is gradually expanded along the side surface 3b of the disk drive and elastically deforms into a flat shape. The snap ring 30 receives the retaining plate 17, and the frictional surfaces of the alternately arranged driven plates 11 to 16 and the drive plates 21 to 26 are The clutch drum 51 and the clutch hub 52 are engaged so that power can be transmitted.
[0042]
Due to the elastic deformation of the snap ring 30 at this time, the press-contact forces of the alternately arranged driven plates 11 to 16 and the drive plates 21 to 26 are gradually increased and fastened, and the loose fastening reduces the shock at the time of fastening operation. Is done.
[0043]
On the other hand, when the hydraulic oil supplied into the hydraulic chamber 43 is discharged, the piston 41 is pushed back by the spring force of the return spring 46, and the pressure contact between the alternately arranged driven plates 11 to 16 and the drive plates 21 to 26 is released. To release the connection. Further, the pressing force on the snap ring 30 is also released, and the shape of the snap ring 30 returns to the no-load state.
[0044]
When the clutch drum 51 is made of an aluminum alloy, it is preferable to apply a wear-resistant treatment such as forming a wear-resistant coating on the surface of the ring groove 3 by spraying a cast iron powder or the like.
[0045]
Therefore, according to the present embodiment configured as described above, since the snap ring 30 also functions as a dish plate, the conventional dish plate can be omitted, and the axial length of the multi-plate clutch is reduced. And the weight of the multi-plate clutch can be reduced. Along with the miniaturization and weight reduction of the multi-plate clutch, the miniaturization and weight reduction of the automatic transmission can be obtained. In other words, a multi-plate clutch can be easily arranged in a transmission case having a limited storage volume.
[0046]
In addition, the configuration can be simplified with the reduction in the number of components, and the number of assembly steps can be reduced by simplifying the assembly work, and a reduction in manufacturing cost can be expected.
[0047]
It should be noted that the present invention is not limited to the above-described embodiment, and can be variously modified without departing from the spirit of the invention. For example, in the first and second embodiments, the multi-plate brake of the automatic transmission and the multi-plate friction engagement device of the multi-plate clutch have been described. However, the present invention may be applied to other devices such as a differential device. You can also.
[0048]
【The invention's effect】
According to the multi-plate friction engagement device of the present invention described above, when the friction engagement plates alternately arranged by the piston are pressed against the retaining plate, the snap ring arranged between the ring groove and the retaining plate is pressed. The retaining plate is elastically deformed to receive the retaining plate, and the pressing force of the alternately arranged friction engagement plates is gradually increased, so that the impact during the fastening operation is reduced. In addition, since the snap ring also functions as a dish plate, the conventional dish plate can be omitted, the compact and lightweight multi-plate friction engagement device can be obtained, and the configuration can be simplified with the reduction in the number of components. It is possible to simplify the assembly and assembly work, and it can be expected that the manufacturing cost will be reduced.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a main part of an automatic transmission having a multi-plate brake showing an outline of a first embodiment of a multi-plate friction engagement device according to the present invention.
FIG. 2 is an enlarged view of a portion A in FIG.
FIG. 3 is an explanatory diagram of a snap ring.
FIG. 4 is a diagram illustrating a snap ring mounting operation.
FIG. 5 is an explanatory diagram of an operation of a snap ring.
FIG. 6 is a sectional view of a main part of a multi-plate clutch showing an outline of a second embodiment of the multi-plate friction engagement device according to the present invention.
FIG. 7 is a sectional view of a main part of an automatic transmission having a conventional multi-plate brake.
[Explanation of symbols]
1 Transmission case (fixing member)
2 Spline groove 3 Ring groove 5 Rotating body 7 Spline groove 11-16 Driven plate (friction engagement plate)
17 Retaining plate 21-26 Drive plate (friction engagement plate)
Reference Signs List 30 snap ring 31 inner peripheral edge 32 outer peripheral edge 33 slit 41 piston 43 hydraulic chamber 51 clutch drum 52 clutch hub

Claims (4)

A plurality of friction engagement plates that spline fit into spline grooves formed on the inner periphery of the fixing member, and friction engagement plates that spline fit into spline grooves formed on the outer periphery of the rotating body are alternately arranged, A piston is arranged on one side of the alternately arranged friction engagement plates, and a ring formed on the other side of the fixed member by spline fitting into a spline groove and formed annularly on the inner periphery of the fixed member. A multi-plate friction engagement device comprising a retaining plate supported by a snap ring locked in a groove, and pressing and fastening the alternately arranged friction engagement plates to the retaining plate by the piston,
The above snap ring,
An annular disk-like shape having a conical shape separated from the retaining plate as it transitions from the inner peripheral edge to the outer peripheral edge, wherein the outer peripheral edge is locked in a ring groove formed in the fixing member, and the inner peripheral edge is A multi-plate friction engagement device characterized by being arranged in contact with a ning plate. The multi-plate friction engagement device according to claim 1, wherein the fixing member is a transmission case of an automatic transmission. A plurality of friction engagement plates that spline fit into spline grooves formed on the inner periphery of the clutch drum and friction engagement plates that spline fit into spline grooves formed on the outer periphery of the clutch hub are alternately arranged, A ring is formed on one side of the alternately arranged friction engagement plates, and a piston is arranged on the other side, and spline-fitted on a spline groove formed on the clutch drum on the other side, and is formed annularly on the inner periphery of the clutch drum. A multi-plate friction engagement device comprising a retaining plate supported by a snap ring locked in a groove, and pressing and fastening the alternately arranged friction engagement plates to the retaining plate by the piston,
The above snap ring,
An annular disk-like shape having a conical shape separated from the retaining plate as it transitions from the inner peripheral edge to the outer peripheral edge, wherein the outer peripheral edge is locked in a ring groove formed in the clutch drum, and the inner peripheral edge is A multi-plate friction engagement device characterized by being arranged in contact with a ning plate. The above snap ring,
The multi-plate friction engagement device according to any one of claims 1 to 3, further comprising a slit extending from the inner peripheral edge to the outer peripheral edge and dividing a part thereof.

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