JP4594513B2 - Lock-up damper device - Google Patents

Description

[0001]
[Industrial application fields]
The present invention relates to a lockup damper device used for a lockup clutch of an automatic transmission for an automobile, for example, and more particularly to a lockup damper device provided with a seat member between a hold plate and a clutch plate.
[0002]
[Prior art]
As a conventional lock-up damper device, for example, there is one described in JP-A-10-61747.
[0003]
If the outline is explained based on FIG. 9, this apparatus is arranged slidably in the axial direction between the front cover 1 which is an input side member and the turbine housing 2 which is an output side member, and is provided on the outer surface. A plurality of clutch plates (pistons) 3 having an annular friction facing 4 in pressure contact with the inner peripheral surface of the front cover 1, and a plurality of clutch plates 3 along the circumferential direction of the clutch plates 3, Are provided between the clutch plate 3 and the hold plate 6. The torsion spring 5 is elastically connected to the clutch plate 3. The hold plate 6 is rivet fixed to the outer peripheral side of the clutch plate 3. And a guide plate 7 with which the outer peripheral surface of the torsion spring 5 on the clutch plate 3 side abuts.
[0004]
The hold plate 6 is formed with a spring accommodating portion 8 for accommodating and holding the torsion springs 5 at an outer peripheral portion bent in an approximately L shape, and one end portion of the spring accommodating portion 8 in the circumferential direction. In addition, a first support portion 9 that is bent in a substantially U shape and receives one end portion of the torsion spring 5 is integrally provided. On the other hand, the turbine housing 2 is provided with a projecting second support 10 that receives the other end of the torsion spring 5.
[0005]
Further, on the upper surface and the back surface of the first support portion 9, there are provided protrusions 9a and 9b that are formed together when the hold plate 6 is press-formed.
[0006]
The guide plate 7 is formed to be relatively thin as a whole because it is necessary to increase the outer diameter of the torsion spring 5, and the main body 7 a is bent substantially in an L shape along the inner surface of the clutch plate 3. At the same time, L-shaped locking pieces 7b, 7b provided at both ends of the main body 7a are provided with locking holes 7c, 7d for locking the projections 9a, 9b.
[0007]
Accordingly, the rotational torque of the crankshaft of the engine is output from the front cover 1 to the hold plate 6 via the clutch plate 3 and further to the turbine housing 2 via the first and second support portions 9 and 10 and each torsion spring 5. At this time, the torque deformation and torsional vibration torque from the engine are absorbed by the compression deformation of the torsion spring 5, and the transmission to the turbine 2 is sufficiently blocked.
[0008]
Further, when each of the torsion springs 5 is compressed and expanded in diameter, the outer peripheral surface of the torsion spring 5 is brought into sliding contact with the inner surface of the guide plate 7 to avoid sliding with the clutch plate 3, and the clutch Generation | occurrence | production of abrasion of the board 3 is prevented.
[0009]
[Problems to be solved by the invention]
However, in the conventional lock-up damper device, as described above, the guide plate 7 can prevent the clutch plate 3 from being worn by the guide plate 7 when the torsion springs 5 are compressed and deformed. Since the locking holes 7c and 7d are locked to the projections 9a and 9b with respect to the plate 6 to be positioned and fixed, the circumferences of the locking holes 7c and 7d and the protrusions 9a and 9b High positional accuracy in the direction and radial direction is required. Therefore, for example, if the positional accuracy is low and a positional deviation occurs, not only can both be locked, but even if it can be locked, it is fixed at this locking portion and free movement is possible. Therefore, partial waviness deformation occurs in the main body 7a of the thin guide plate 7 as a whole. As a result, the contact surface pressure at the swell deformation portion between the inner surface of the main body 7a and the outer peripheral surface of the torsion spring 5 increases, and excessive hysteresis and wear at the contact portion are promoted, resulting in a decrease in durability. Yes.
[0010]
[Means for Solving the Problems]
The present invention has been devised in view of the technical problems of the conventional lock-up damper device, and the invention according to claim 1 is provided between the front cover and the turbine so as to be slidable in the axial direction. A clutch plate having a friction facing that press-contacts the front cover, an output member connected to the turbine and arranged to be rotatable relative to the clutch plate, and the clutch plate and the output member in a circumferential direction. A plurality of torsion springs that are elastically connected to each other, a hold plate that is fixed to the clutch plate and has a spring accommodating portion that accommodates the torsion spring, and is interposed between the clutch plate and the hold plate, A lock-up damper device comprising a seat member that is in contact with an outer peripheral surface of the torsion spring on the clutch plate side on an inner surface; The inner and outer peripheral portions of the serial sheet member, while supporting the clamping state between the inner surface of the clutch plate opposite to the back and the back surface of the holding plate, the clamping support region with respect to the seat member, the seat It is characterized in that it is set in the inner and outer peripheral areas of the member .
[0011]
Therefore, according to the present invention, the thin sheet member is basically supported in a sandwiched state between the clutch plate and the hold plate, so that the conventional positioning accuracy between the locking hole and the protrusion is high. As a matter of course, since the fixing point is eliminated, the occurrence of undulation deformation during the clamping operation is prevented.
[0013]
The invention according to claim 2 is characterized in that an axial gap is formed between the inner and outer peripheral portions of the sheet member that are clamped and the clutch plate.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, each embodiment of the lockup damper device according to the present invention will be described with reference to the drawings.
[0015]
That is, FIGS. 2 and 3 show a first embodiment of the present invention. This device includes an unillustrated front cover connected to an engine crankshaft and an output side member of a torque converter. A disc-shaped clutch plate 21 is disposed between a turbine housing and a clutch hub (not shown) at the center of the turbine housing so as to be slidable in the axial direction. A plurality of torsion springs 22 are arranged at equal intervals in the circumferential direction on the outer peripheral side of 21. A hold plate 23 that holds the torsion springs 22 on the outer peripheral side is fixed to the outer peripheral side of the clutch plate 21 by caulking a plurality of rivets 20, while the front cover has an outer surface on the clutch plate 21 side. A driven plate 24 that transmits the rotational force from the input side to the turbine housing via the torsion spring 22 is fixed. Further, a seat member 25 is provided between the clutch plate 21 and the hold plate 23, with which the outer peripheral surface of the torsion spring 22 on the clutch plate 21 side abuts.
[0016]
As shown in FIG. 2, the clutch plate 21 integrally has a holding portion 21a whose outer peripheral portion is bent in a substantially U-shaped cross section, and has an annular shape on the outer surface of the holding portion 21a. A friction facing 26 is provided.
[0017]
As shown in FIGS. 2 to 6, the hold plate 23 has an annular shape, and an inner peripheral base portion is fixed to the clutch plate 21 by a rivet 20, while an outer peripheral portion bent in a substantially L shape. In part, eight spring accommodating portions 27 for accommodating the respective torsion springs 22 are formed inside, and a first support portion 28 for receiving one end portion of each torsion spring 22 is formed on a side portion of the spring accommodating portion 27. It is integrally formed.
The clutch plate 21, a portion of the inner circumferential side of the rivet 20, longitudinal section substantially semicircular reinforcing ribs 23a are formed bent.
[0018]
Each of the spring accommodating portions 27 is bent in a substantially U shape from the outer peripheral edge of the hold plate 23 so as to cover the outer peripheral surface of each of the torsion springs 22, and the front end edge 27a is predetermined in the axial direction. It is extended to the position. In addition, the spring accommodating portion 27 has a tongue piece 27b that is cut and raised inward from the base portion in a substantially square shape to support the inner peripheral side outer peripheral surface of each torsion spring 22.
[0019]
The first support portion 28 is formed in a substantially U-shape that is smaller than the spring accommodating portion 27, and the front end edge 28 a is disposed at a position having the same diameter as the front end edge 27 a of the spring accommodating portion 27. ing.
[0020]
Further, both the front end edges 27 a and 28 a are integrally connected by a connecting member 29. That is, as shown in FIGS. 2 to 6, the connecting member 29 is formed in an endless annular shape and continuously connects all the front end edges 27 a and 28 a along the circumferential direction. The front end portion 29a extends substantially horizontally and slightly protrudes from the front end edge of the holding portion 21a of the clutch plate 21.
[0021]
As shown in FIG. 3, eight of the torsion springs 22 are arranged at equal intervals in the circumferential direction of the hold plate 23, and both end portions thereof are the first support portion 28 and a driven plate 24 described later. The clutch plate 21 and the turbine housing are elastically connected to each other through the two support portions 24a and 28.
[0022]
The driven plate 24 has an inner peripheral base fixed to a turbine hub of the turbine housing by a rivet, and a part of the outer peripheral portion is bent inward in a substantially L shape as shown in FIG. The bent portion is configured as the second support portion 24a.
[0023]
As shown in FIGS. 1A and 1B, the seat member 25 is formed to be relatively thin in order to ensure a large outer diameter of the torsion spring 22 in the spring accommodating portion 27, and the ring of the clutch plate 21. It is formed in a substantially arc shape along the shape, and its circumferential length L is slightly larger than the length of the adjacent two torsion springs 22, 22 in the series direction.
Further, the width dimension W is formed to be a length from a slightly inner peripheral side to the vicinity of the outer peripheral end of the hold plate 23 from the rivet 20. Further, insertion holes 30 and 30 through which the two rivets 20 are inserted are formed in the inner peripheral portion 25 a of the sheet member 25.
[0024]
The sheet member 25 is supported in a sandwiched state between the inner side surface of the holding portion 21 a of the clutch plate 21 and the rear surface of the outer peripheral portion of the hold plate 23.
[0025]
That is, the seat member 25 is configured such that when the hold plate 23 is fixed to the clutch plate 21 with the rivet 20, the insertion holes 30 and 30 of the rivet 20 are aligned with the rivet holes 31 and 31 on the clutch plate 21 side in advance. The holding plate 23 is overlapped while being positioned through the rivet hole, and then each rivet 20 is inserted and crimped. As a result, the hold plate 23 is firmly attached to the clutch plate 21, and the sheet member 25 is sandwiched and supported between the both plates 21 and 23.
[0026]
As shown by the shaded area in FIG. 1A, this clamping pressure range includes a band-shaped inner peripheral area 32 that is a fixed area of the rivet 20, and a trapezoidal central area on the back side where the first support portion 28 of the hold plate 23 is located. 33, the outer peripheral region 34 on the outer peripheral side of the spring accommodating portion 27, and the outer end regions 35, 35 on the outer end sides of the spring accommodating portions 27 on both sides. Further, there is a gap between the step-shaped inner peripheral region 32, the trapezoidal central region 33, and the narrow strip-shaped outer peripheral regions 34, 34, and the step portion of the clutch plate 21 facing the step portion, as shown in FIG. A gap C is formed as shown in FIG.
[0027]
The rivet insertion holes 30 and 30 formed in the sheet member 25 have an inner diameter set relatively larger than an outer diameter of the shaft portion of the rivet 20, and an inner peripheral edge of the shaft portion of the rivet 20 at the time of the caulking. There is no strong pressure contact with the outer peripheral surface.
[0028]
Therefore, according to this embodiment, when the engine reaches a predetermined rotation or more, the friction facing 26 is pressed against the front cover due to the pressure difference between the front and back of the clutch plate 21, and the front cover is directly connected to the turbine via the torsion springs 22. Is done.
[0029]
Torque fluctuations and torsional vibrations that are input from the engine side to the converter side in this directly connected state can be effectively reduced by the vibration absorbing action by the expansion and contraction of each torsion spring 22.
[0030]
Further, since the inner and outer circumferences of the respective torsion springs 22 are held in the spring accommodating portions 27 of the hold plate 23, the outer circumferential surfaces of the respective torsion springs 22 are extended during the expansion and contraction operations of the respective torsion springs 22. It slides on the outer peripheral side inner surface of the spring accommodating portion 27 and the inner surface of the sheet member 25 in a substantially line contact state. For this reason, sliding with the inner peripheral surface of the holding part 21a of the clutch plate 21 is avoided, and the occurrence of wear on the inner peripheral surface of the holding part 21a is prevented. As a result, the durability of the clutch plate 21 is improved.
[0031]
In addition, during the operation, each torsion spring 22 is compressed and deformed and a centrifugal force acts, and a large load in the diameter increasing direction acts on the outer peripheral side of the spring accommodating portion 27 to expand the spring accommodating portion 27. Although it tries to be deformed in the radial direction, since the front end edge 27a of the spring accommodating portion 27 and the front end edge 28a of the first support portion 28 are connected by the connecting member 29, the load in the diameter increasing direction is increased by the connecting member 29. Are distributed in the circumferential direction, and the generation of concentrated load on the connecting portion between the spring accommodating portion 27 and the first support portion 28 can be suppressed. As a result, the occurrence of cracks or the like at the connecting portion is prevented, and the durability of the hold plate 23 can be prevented from being lowered.
[0032]
Further, the connecting member 29 is not simply connected between the two adjacent front end edges 27a, 28a, but is formed in an endless annular shape so as to connect all of the front end edges 27a, 28a, and horizontally forward. Since it protrudes in the direction, the support rigidity of the load in the diameter-expanding direction is increased, and stable support of the torsion spring 22 by the spring accommodating portion 27 is also obtained.
[0033]
Further, as described above, since the supporting rigidity by the spring accommodating portion 27 is increased by the connecting member 29, the thickness of the entire hold plate 23 can be set sufficiently small. As a result, the weight and layout of the apparatus can be reduced. The degree of freedom can be improved.
[0034]
Further, since the front end edge 27a of the spring accommodating portion 27 extends in the axial direction, the edge contact between the front end edge 27a and the outer peripheral edge of the torsion spring 22 can be prevented, so that the occurrence of wear of the torsion spring 22 can be prevented.
[0035]
According to this embodiment, the attachment of the sheet member 25 to the hold plate 23 is not positioned and fixed by locking the protrusion and the locking hole as in the prior art, but the clutch plate 21 and the hold plate 23 Therefore, the sheet member 25 can be moved relatively freely in the circumferential direction, the radial direction, and the like (planar direction). As a result, the sheet member 25 can be attached in its original shape while preventing the sheet member 25 from waviness.
[0036]
Therefore, a partial increase in sliding frictional resistance during expansion / contraction deformation of the torsion spring 22 is prevented, and excessive hysteresis is prevented. In addition, the occurrence of wear is prevented, and a decrease in durability can be suppressed.
[0037]
Further, the clamping range for the sheet member 25 is not the entire surface, but a band-shaped inner peripheral region 32, a trapezoidal central region 33, a narrow strip-shaped outer peripheral region 34, and both outer end regions 35, 35. Since the intermediate region does not become a pinched state, the sheet member 25 can be moved in the plane direction, so that the occurrence of waviness deformation is also prevented in this respect.
[0038]
Further, since a gap C is formed between the stepped portion of the clutch plate 21 and the stepped portion of the seat portion, movement of the seat member 25 in the planar direction is allowed within this range. Further, it can be prevented.
[0039]
7 and 8 show a second embodiment of the present invention, in which the front end portion of the holding portion 21a of the clutch plate 21 extends horizontally in the axial direction, and the front end edge of the front end portion has a rectangular shape. The locking groove 40 is formed. As shown in FIG. 8, each of the locking grooves 40 is formed at a substantially central position in the circumferential direction of the spring accommodating portion 27 and the first support portion 28.
[0040]
The connecting member 29 is formed with a plurality of locking portions 41 at positions corresponding to the locking grooves 40 at the tip. Each of the locking portions 41 is formed by cutting and raising a part of the front end portion of the connecting member 29 and raising it vertically, and its width W1 is larger than the circumferential width of the locking groove 40. Are set to be slightly smaller, and these engage with the respective locking grooves 40 from the radial direction.
[0041]
Therefore, according to this embodiment, when the torsion spring 22 is compressed and deformed and a relative load acts on the first support portion 28 and the second support portion 24a in the circumferential direction, the circumferential load is applied to each engagement. Since it can be received by the inner end edge of the locking groove 40 via the stopper 41, that is, by the clutch plate 21, the circumferential support rigidity of the torsion spring 22 is also increased, and each torsion spring 22 is Thus, it is possible to obtain a good expansion / contraction deformation and to secure a stable transmission torque.
[0042]
The present invention is not limited to the configuration of each of the above embodiments, and for example, the shape and size of the sheet member 25 can be freely changed according to the specifications of the apparatus.
[0043]
【The invention's effect】
As is apparent from the above description, according to the invention described in claim 1, the mounting of the sheet member to the hold plate is not positioned and fixed by locking the protrusion and the locking hole as in the prior art, Since the sheet member is attached by being sandwiched between the clutch plate and the hold plate, when the sheet member is attached, the sheet member is prevented from being swelled and can be attached in the original shape.
[0044]
Accordingly, an increase in sliding frictional resistance during expansion / contraction deformation of the torsion spring is prevented, and excessive hysteresis is prevented. In addition, the occurrence of wear is prevented, and a decrease in durability can be suppressed.
[0045]
Further, since the occurrence of undulation deformation can be prevented, the sheet member can be set to be thinner, and as a result, the outer diameter of the torsion spring can be made sufficiently large, and the heat treatment after the sheet member molding is performed. It can also be abolished.
[0046]
According to the second aspect of the present invention, the clamping range for the sheet member is not the entire surface, but a part of the inner and outer peripheral sides, and these intermediate regions do not become a clamping state. This also makes it possible to prevent the occurrence of undulation deformation.
[0047]
According to the third aspect of the present invention, since the axial gap is formed between the inner and outer peripheral portions of the sheet member that are clamped and the clutch plate, the movement of the sheet member in the planar direction is within this range. Is allowed, and the occurrence of undulation deformation can be further prevented.
[Brief description of the drawings]
FIG. 1A is a front view of a seat member used in a first embodiment of a lockup damper device according to the present invention, and B is a cross-sectional view taken along line AA in FIG.
2 is a cross-sectional view taken along the line BB of FIG. 3 showing a first embodiment of the lock-up damper device according to the present invention.
FIG. 3 is a front view showing a part of the embodiment in cross section.
FIG. 4 is a perspective view of a hold plate used in the present embodiment.
5 is a cross-sectional view taken along the line CC of FIG. 6 showing a hold plate used in the present embodiment.
FIG. 6 is a front view of the hold plate.
7 is a cross-sectional view taken along line DD of FIG. 8 showing a second embodiment of the present invention.
FIG. 8 is a front view of the embodiment.
FIG. 9 is a cross-sectional view showing a conventional lock-up damper device.
[Explanation of symbols]
21 ... Clutch plate 22 ... Torsion spring 23 ... Hold plate 24 ... Driven plate 25 ... Sheet member 27 ... Spring accommodating portion

Claims (2)

A clutch plate is provided between the front cover and the turbine so as to be slidable in the axial direction, and has a friction facing that press-contacts the front cover. The clutch plate is connected to the turbine so as to be rotatable relative to the clutch plate. An output member, a plurality of torsion springs that elastically connect the clutch plate and the output member from the circumferential direction, and a hold plate that is fixed to the clutch plate and has a spring accommodating portion that accommodates the torsion spring. the is interposed between the clutch plate and the hold plate, a lock-up damper device including a seat member outer peripheral surface of the torsion spring of the clutch plate side abuts the inside surface,
While supporting the inner and outer peripheral parts of the sheet member between the back surface of the hold plate and the inner surface of the clutch plate facing the back surface ,
The lockup damper device according to claim 1, wherein a nipping support area for the sheet member is set in an inner and outer peripheral area of the sheet member. The lockup damper device according to claim 1, wherein an axial gap is formed between the inner and outer peripheral portions of the seat member that are clamped and the clutch plate .

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