JP3601522B2 - Damper device - Google Patents

Description

[0001]
[Industrial applications]
The present invention relates to a damper device.
[0002]
[Prior art]
Conventionally, an automatic transmission includes a torque converter as a fluid transmission device, and has a structure in which rotation of an engine taken out by a crankshaft is transmitted to an input shaft of a transmission mechanism via the torque converter.
[0003]
The torque converter includes a pump impeller, a turbine runner, a stator, a lock-up clutch device, and a damper device. The rotation from the engine is transmitted to the pump impeller via the front cover, and the turbine runner is rotated by the flow of oil generated with the rotation of the pump impeller, and the rotation of the turbine runner is transmitted to the input shaft. It has become.
[0004]
Further, the lock-up clutch device includes a clutch plate movably disposed in the axial direction, and a friction material is stuck to the clutch plate. Then, when a preset vehicle speed is obtained after the vehicle starts, the clutch plate and the front cover are brought into contact, and the lock-up clutch device is engaged. As a result, the rotation of the engine is transmitted to the input shaft without passing through the torque converter.
[0005]
By the way, when the lock-up clutch device is engaged, if a sudden change in the output torque of the engine is directly transmitted to the input shaft, vibration, noise, and the like are generated.
[0006]
Therefore, a damper device is provided between the lock-up clutch device and the turbine hub. The damper device includes a plurality of springs disposed at a plurality of positions in a circumferential direction of the clutch plate, a plurality of holding plates for holding the respective springs, and a plurality of drives fixed to the clutch plate and brought into contact with one ends of the respective springs. And a driven plate fixed to the turbine hub and brought into contact with the other end of the spring.
[0007]
When the transmission torque is transmitted to the clutch plate in association with the engagement of the lock-up clutch device, the spring bends (deflects), and transmits the transmission torque in a bent state via the turbine hub to the input shaft. And absorbs a sudden change in transmission torque (see Japanese Patent Application Laid-Open No. 2-26319).
[0008]
[Problems to be solved by the invention]
However, in the conventional damper device, since the holding plate and the drive plate are not positioned radially inside the spring, they may move when assembled to the clutch plate. Becomes difficult.
[0009]
Therefore, in order to facilitate the assembling work, the holding plate and the drive plate are fixed to the clutch plate by rivets.
[0010]
However, when the holding plate and the drive plate are to be assembled to the clutch plate by rivets, not only the number of parts is increased, but also it is necessary to attach rivets to the clutch plate in advance, so that the man-hour is increased and the damper device is required. The cost increases.
[0011]
Further, two rivets are used for each holding plate and each drive plate in order to prevent the rivet from moving at the time of assembling. Therefore, the holding plate and the drive plate are matched with each rivet. Therefore, the assemblability of the damper device is reduced correspondingly.
[0012]
SUMMARY OF THE INVENTION It is an object of the present invention to provide a damper device capable of solving the problems of the conventional damper device, reducing the cost and improving the assemblability.
[0013]
[Means for Solving the Problems]
For this purpose, in the damper device of the present invention, the damper device is disposed between the clutch plate and the output member engaged with the front cover of the fluid transmission device, and is disposed at a plurality of positions in the circumferential direction of the clutch plate. The provided spring is held at the outermost peripheral portion of the clutch plate.
[0014]
And it has a plurality of drive plates fixed to the clutch plate and pressing the spring when the clutch plate and the front cover are engaged.
[0015]
The clutch plate includes a flat plate portion extending in a radial direction, and a rising portion extending in an axial direction from an outer peripheral edge of the flat plate portion and having a plurality of locking grooves corresponding to the drive plates. . Each of the drive plates includes a curved portion that forms a recess toward the side opposite to the clutch plate in the axial direction, and a locking portion that is locked in each of the locking grooves to position the drive plate.
Further, another engaging portion for receiving the spring when the clutch plate and the front cover are engaged with each other in connection with the output member is provided in the curved portion.
[0016]
In another damper device of the present invention, the locking portion of each drive plate and the locking groove position the drive plate in the circumferential direction and the radial direction.
[0017]
In still another damper device according to the present invention, the locking portion of each of the drive plates has a shape in which the width becomes wider toward the outside in the radial direction. The locking groove has a shape corresponding to the locking portion. Further, a dovetail engagement is performed by the locking portion and the locking groove of each drive plate.
[0018]
In still another damper device of the present invention, the drive plate and the clutch plate are further fixed by tox caulking.
[0019]
[Action and effect of the invention]
According to the present invention, in the damper device as described above, the damper device is disposed between the clutch plate and the output member engaged with the front cover of the fluid transmission device, and includes a plurality of clutch plates in the circumferential direction. The springs respectively arranged at the positions are held at the outermost peripheral portion of the clutch plate.
[0020]
And it has a plurality of drive plates fixed to the clutch plate and pressing the spring when the clutch plate and the front cover are engaged.
[0021]
The clutch plate includes a flat plate portion extending in a radial direction, and a rising portion extending in an axial direction from an outer peripheral edge of the flat plate portion and having a plurality of locking grooves corresponding to the drive plates. . Each of the drive plates includes a curved portion that forms a recess toward the side opposite to the clutch plate in the axial direction, and a locking portion that is locked in each of the locking grooves to position the drive plate.
Further, another engaging portion for receiving the spring when the clutch plate and the front cover are engaged with each other in connection with the output member is provided in the curved portion.
[0022]
In this case, when assembling each of the drive plates to the clutch plate, the mounting load of the spring is generated in the circumferential direction of the drive plate, but by locking the locking portion of each of the drive plates to the locking groove. Each drive plate is positioned in the circumferential direction of the clutch plate.
[0023]
Therefore, even if the mounting load is applied to the drive plate, the operation of assembling the drive plate to the clutch plate does not become difficult. As a result, the assemblability of the damper device can be improved.
[0024]
In another damper device of the present invention, the locking portion of each drive plate and the locking groove position the drive plate in the circumferential direction and the radial direction.
[0025]
In this case, when positioning each drive plate in the circumferential direction and the radial direction of the clutch plate, it is only necessary to lock the locking portion of each drive plate in the locking groove, so that the drive plate is aligned with the rivet. No need.
[0026]
Also, since the drive plate is positioned radially outward from the spring, the drive plate does not move when assembled to the clutch plate. Therefore, the assemblability of the damper device can be improved.
[0027]
In still another damper device according to the present invention, the locking portion of each of the drive plates has a shape in which the width becomes wider toward the outside in the radial direction. The locking groove has a shape corresponding to the locking portion. Further, a dovetail engagement is performed by the locking portion and the locking groove of each drive plate.
[0028]
In this case, the movement of the drive plate with respect to the clutch plate is circumferentially and radially restricted by the splicing engagement, so that the drive plate does not move when assembled to the clutch plate. Therefore, the assemblability of the damper device can be improved.
[0029]
In still another damper device of the present invention, the drive plate and the clutch plate are further fixed by tox caulking.
[0030]
In this case, since it is not necessary to use rivets or the like, the number of parts can be reduced. Further, since it is not necessary to attach a rivet to the clutch plate in advance, the number of steps can be reduced and the cost of the damper device can be reduced.
[0031]
【Example】
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
[0032]
FIG. 1 is a longitudinal sectional view of a torque converter according to an embodiment of the present invention, and FIG. 2 is a plan view of the torque converter according to the embodiment of the present invention.
[0033]
In the figure, the torque converter includes a pump impeller 11, a turbine runner 12, a stator 13, a lock-up clutch device 14, and a damper device 15 that together form a torus with the pump impeller 11.
[0034]
The rotation of the engine (not shown) transmitted via a crankshaft (not shown) is transmitted to the front cover 16 and transmitted to the pump impeller 11 fixed to the front cover 16. In this case, when the pump impeller 11 rotates, the oil in the torus rotates around the shaft, and centrifugal force is applied to circulate between the pump impeller 11, the turbine runner 12, and the stator 13.
[0035]
In this case, when the pump impeller 11 has just started to rotate and the rotation speed difference between the turbine runner 12 and the turbine runner 12 is large, such as when the vehicle starts, oil flowing out of the turbine runner 12 moves in a direction that hinders the rotation of the pump impeller 11. Flows. Therefore, a stator 13 is provided between the pump impeller 11 and the turbine runner 12, and when a difference in rotation speed between the two is large, the stator 13 converts the oil flow in a direction that assists the rotation of the pump impeller 11. .
[0036]
When the rotation speed of the turbine runner 12 increases and the rotation speed difference between the turbine runner 12 and the pump impeller 11 decreases, the oil that has hit the front side of the blade 31 of the stator 13 hits the back side, and the oil Obstruct flow.
[0037]
Therefore, a one-way clutch 17 that allows the stator 13 to rotate only in a certain direction is provided on the inner peripheral side of the stator 13. Therefore, when the oil hits the back side of the blade 31, the stator 13 rotates spontaneously, and the oil can circulate smoothly. The outer race 18 of the one-way clutch 17 is fixed to the stator 13, and the inner race 19 is fixed to a case of an automatic transmission (not shown).
[0038]
Thus, the torque converter is operated as a torque converter to amplify torque when the rotation speed difference between the pump impeller 11 and the turbine runner 12 is large, and is operated as a fluid coupling when the rotation speed difference is small. Can be
[0039]
Next, the lock-up clutch device 14 will be described.
[0040]
In this case, when a preset vehicle speed is obtained after the vehicle starts, the lock-up clutch device 14 is engaged. Therefore, since the rotation of the engine is transmitted to the input shaft of the transmission (not shown) without passing through the torque converter, fuel efficiency can be improved. The lock-up clutch device 14 is operated by switching the supply of oil by a lock-up relay valve (not shown), and the clutch plate 21 moves in the axial direction. It can be moved away.
[0041]
For this purpose, a release-side oil chamber R1 is formed between the clutch plate 21 and the front cover 16, and an engagement-side oil chamber R2 is formed between the clutch plate 21 and the turbine runner 12. Accordingly, when oil is supplied to the release-side oil chamber R1, the lock-up clutch device 14 is released, and when oil is supplied to the engagement-side oil chamber R2, the lock-up clutch device 14 is engaged. .
[0042]
When the lock-up clutch device 14 is engaged, the rotation of the crankshaft is directly transmitted to the input shaft via the front cover 16, the clutch plate 21, the damper device 15, and the turbine hub 23 as an output member. Is transmitted. For this purpose, a spline groove 23a is formed on the inner periphery of the turbine hub 23, and the turbine hub 23 and the input shaft are spline-fitted by the spline groove 23a.
[0043]
Reference numeral 61 denotes a thrust bearing disposed between the turbine hub 23 and the front cover 16; 65, a thrust bearing disposed between the stator 13 and the turbine hub 23; And a thrust bearing disposed between the bearing and the bearing.
[0044]
The damper device 15 is for absorbing a change in transmission torque generated when the clutch plate 21 and the front cover 16 are disengaged. The damper device 15 is fixed to the clutch plate 21 by a tox caulking 58 and is integrated with the clutch plate 21. The drive plate 57 includes a driven plate 32 and springs 33 and 34 which are disposed opposite to the drive plate 57 and are rotated integrally with the turbine runner 12.
[0045]
The springs 33 are for the first stage disposed at eight positions in the circumferential direction of the clutch plate 21, while the springs 34 are disposed at four positions in the circumferential direction of the clutch plate 21. It is for the second stage, and is disposed every other in the spring 33. The spring 34 is smaller in diameter and shorter than the spring 33, and starts to bend after the transmission torque reaches the bending point torque when the torsion angle of the spring 33 reaches a set value.
[0046]
Therefore, the rotation transmitted from the front cover 16 via the friction material 20 is transmitted to the turbine hub 23 via the damper device 15, but in this case, the springs 33 and 34 contract and the rotation is transmitted. To absorb fluctuations in transmission torque during transmission. Further, it is possible to prevent generation of vibration, noise, and the like due to transmission of a sudden change in the output torque of the engine to the transmission.
[0047]
The pump impeller 11 and the turbine runner 12 are respectively constituted by blades 41 and 42, outer shells 43 and 44 and inner cores 45 and 46 disposed on both sides of the blades 41 and 42, respectively. The outer shell 44 of the turbine runner 12 is connected to the turbine hub 23 by rivets 47 together with the driven plate 32.
[0048]
Incidentally, the clutch plate 21 extends in the axial direction, and slides in the axial direction along the sliding (sliding) moving surface formed on the turbine hub 23. A first flat plate portion 52 extending radially outward from the rising portion 51, a curved portion 53 extending radially outward from the first flat plate portion 52, a first flat portion 52 extending radially outward from the curved portion 53. The second flat plate portion 54 includes a cylindrical second rising portion 55 extending in the axial direction from the second flat plate portion 54.
[0049]
The curved portion 53 is protruded from the first and second flat plate portions 52 and 54 toward the engine, and the outside of the spring 33 is held between the second flat plate portion 54 and the second rising portion 55. A part is formed.
[0050]
In this case, since the spring 33 is disposed on the outermost peripheral portion of the clutch plate 21, the space formed between the front cover 16 and the torus can be sufficiently utilized, and the spring 33 The diameter can be set large. Therefore, the spring constant of the spring 33 can be reduced, and as a result, the natural frequency can be reduced.
[0051]
A drive plate 57 is provided to surround and hold the springs 33 and 34 together with the clutch plate 21 and transmit the rotation of the clutch plate 21 to the springs 33 and 34.
[0052]
In the present embodiment, the drive plate 57 is formed into a piece and has a substantially fan-like shape. The drive plate 57 is disposed adjacent to each other at eight positions in the circumferential direction of the clutch plate 21 and has a ring shape as a whole. Each drive plate 57 is fixed to the clutch plate 21 by the tox caulking 58 at two locations in the circumferential direction. Further, at both ends of each drive plate 57, a curved portion Q1 formed by being raised so as to face the second rising portion 55 is formed, and the curved portion Q1 forms an inner holding portion of the spring 33. . Therefore, when the drive plates 57 are fixed to the clutch plate 21 adjacent to each other, the curved portions Q1 of the drive plates 57 are also adjacent to each other.
[0053]
Further, when the lock-up clutch device 14 is engaged with the center of the drive plate 57 and the clutch plate 21 rotates in the forward direction (counterclockwise direction in FIG. 2) (hereinafter referred to as “at the time of forward drive”). ), And when the clutch plate 21 rotates in the reverse direction (clockwise direction in FIG. 2) during engine braking or the like (hereinafter, referred to as “during reverse driving”), the spring pressing portion M that presses the spring 33 is provided. It is formed. In the spring pressing portion M, the pressing surface Ma contacts the end surface of the spring 33 during the forward driving and the pressing surface Mb during the reverse driving.
[0054]
As described above, both ends of the springs 33 and 34 are sandwiched by the spring pressing portions M of the two drive plates 57 adjacent to each other, and the outside is held by the outside holding portion and the inside is held by the inside holding portion. You.
[0055]
The spring pressing portion M includes a curved portion M1 extending along the end surface of the spring 33, a rising portion M2 rising along the second rising portion 55, and a lock formed on the second rising portion 55. The locking portion M3 is locked with the groove 55a. The locking grooves 55a are formed at eight locations in the circumferential direction corresponding to the respective drive plates 57.
[0056]
Therefore, by locking the locking portion M3 in the locking groove 55a, the drive plates 57 and the springs 33 can be positioned in the circumferential direction of the clutch plate 21.
[0057]
Further, the width of the spring pressing portion M is made wider toward the outside in the radial direction, and a taper corresponding to the shape of the locking portion M3 is formed in the locking groove 55a, so that the locking portion M3 and the locking groove 55a are formed. Thus, the seam engagement is performed. Therefore, by locking the locking portion M3 in the locking groove 55a, each drive plate 57 can be positioned in the radial direction of the clutch plate 21.
[0058]
Further, when assembling the drive plates 57 to the clutch plate 21, the mounting load of the spring 33 is generated in the circumferential direction. By engaging the engaging portion M3 in the engaging groove 55a, the clutch plate Since each drive plate 57 is positioned in the circumferential direction of the motor 21, even if the mounting load is applied to the drive plate 57, the operation of assembling the drive plate 57 to the clutch plate 21 does not become difficult. Further, since the drive plate 57 is positioned in the radial direction with respect to the spring 33, the drive plate 57 does not move when assembled to the clutch plate 21. Therefore, the assemblability of the damper device 15 can be improved.
[0059]
The drive plates 57 can be positioned in the circumferential direction and the radial direction of the clutch plate 21 only by locking the locking portions M3 in the locking grooves 55a. 58 allows the clutch plate 21 to be fixed. Therefore, since it is not necessary to use rivets or the like, the number of parts can be reduced. Further, since it is not necessary to attach rivets to the clutch plate 21 in advance, the number of steps can be reduced and the cost of the damper device 15 can be reduced.
[0060]
In positioning the drive plates 57 in the circumferential direction and the radial direction of the clutch plate 21, there is no need to align the drive plates 57 with the rivets, just by locking the locking portions M3 in the locking grooves 55 a. Therefore, the assemblability of the damper device 15 can be improved.
[0061]
Further, since each drive plate 57 is formed into a piece and the spring 33 is pressed by two drive plates 57 adjacent to each other, not only can the free length of the spring 33 be increased, but also the spring 33 The width of the pressing portion M can be made relatively large. Therefore, the strength of the drive plate 57 can be increased, and it is not necessary to perform heat treatment or the like, so that the cost of the damper device 15 can be reduced.
[0062]
On the other hand, the driven plate 32 extends in the radial direction along the turbine runner 12 and forms a locking portion T corresponding to the spring 33. The locking portion T receives the spring 33 when the clutch plate 21 is driven forward and when it is driven reversely. In the locking portion T, the pressing surface Ta contacts the end surface of the spring 33 during the forward drive, and the pressing surface Tb contacts the reverse surface during the reverse drive.
[0063]
The locking portion T is disposed substantially parallel to the spring pressing portion M, and extends along the curved portion T1 extending substantially parallel to the curved portion M1 along the end surface of the spring 33, and the second rising portion 55. And a rising portion T2 rising substantially parallel to the rising portion M2.
[0064]
Since both end surfaces of the springs 33 and 34 are pressed by the spring pressing portion M and the locking portion T, they are easily worn. Therefore, spring seats 71 and 72 are provided on both end surfaces of the springs 33 and 34, respectively. Further, a curved portion M1 is formed in the spring pressing portion M and a curved portion T1 is formed in the locking portion T, so that the contact area with the spring seats 71 and 72 is increased. Therefore, the wear resistance of the spring pressing portion M, the locking portion T, and the spring seats 71 and 72 can be improved.
[0065]
When the clutch plate 21 is driven forward, the spring 33 is pressed by the spring pressing portion M and received by the locking portion T. Then, as the spring 33 is compressed, the distance between the spring pressing portion M and the locking portion T decreases, and when the pressing surface Ta of the locking portion T hits the curved portion Q1, the compression of the spring 33 is reduced. Stopped. Thus, the curved portion Q1 functions as a stopper for the locking portion T.
[0066]
Next, the Tox caulking 58 will be described.
[0067]
FIG. 3 is a perspective view of a portion where the tox caulking is performed in the embodiment of the present invention, and FIG. 4 is a diagram illustrating a working state of the tox caulking in the embodiment of the present invention.
[0068]
In the figure, 21 is a clutch plate, 57 is a drive plate, and 58 is a tox caulking. The tox caulking 58 can be applied by advancing a punch 81 disposed on the clutch plate 21 side toward a die 82 disposed on the drive plate 57 side.
[0069]
The die 82 has a bottom surface 83 and a groove 84 formed around the bottom surface 83. Therefore, when the punch 81 is advanced toward the die 82, the material of the drive plate 57 enters the groove 84, and the material of the clutch plate 21 spreads radially outward. As a result, the clutch plate 21 and the drive plate 57 can be joined.
[0070]
In this case, it is not necessary to perform drilling on the clutch plate 21 and the drive plate 57, and the number of steps is small, so that the cost of the damper device 15 (FIG. 1) can be reduced.
[0071]
It should be noted that the present invention is not limited to the above-described embodiment, but can be variously modified based on the gist of the present invention, and they are not excluded from the scope of the present invention.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a torque converter according to an embodiment of the present invention.
FIG. 2 is a plan view of the torque converter according to the embodiment of the present invention.
FIG. 3 is a perspective view of a portion where tox caulking is performed in the embodiment of the present invention.
FIG. 4 is a diagram showing a work state of tox caulking in the embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 11 Pump impeller 12 Turbine runner 13 Stator 14 Lock-up clutch device 15 Damper device 16 Front cover 21 Clutch plate 23 Turbine hub 33, 34 Spring 51, 55 First, second rising portion 52, 54 First, second flat plate Part 57 drive plate 58 tox caulking 55a locking groove M3, T locking part

Claims (4)

The springs disposed between the clutch plate and the output member, which are engaged with the front cover of the fluid transmission, and provided at a plurality of locations in the circumferential direction of the clutch plate, respectively, In a damper device held by an outer peripheral portion, the clutch plate has a plurality of drive plates fixed to the clutch plate and pressing a spring when the clutch plate and the front cover are engaged with each other. flat portion extending in a direction, and extends in the axial direction from the outer peripheral edge of the plate portion, and wherein in correspondence with each drive plate includes a rising portion in which a plurality of locking grooves are formed, each drive plate shaft curved portion which forms a recess towards the opposite side of the clutch plate in the direction, and the each engaging groove Provided with a locking portion for positioning the sealed was provided by the drive plate, the ligated with the output member, when said clutch plate and the front cover has been engaged, the other engagement for receiving the spring A damper device, wherein a stop portion is provided on the curved portion . The damper device according to claim 1, wherein the locking portion of each of the drive plates and the locking groove position the drive plate in a circumferential direction and a radial direction. Said locking portion of each drive plate has a width increasing shape becomes radially outward, the engaging groove together with having a shape corresponding to the engaging portion, the engaging portion of the drive plate The damper device according to claim 1, wherein the dovetail engagement is performed by the and the locking groove. The damper device according to claim 3, wherein the drive plate and the clutch plate are fixed by a tox caulking.

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