JP5844601B2 - Vibration damping device - Google Patents

Vibration damping device Download PDF

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Publication number
JP5844601B2
JP5844601B2 JP2011229285A JP2011229285A JP5844601B2 JP 5844601 B2 JP5844601 B2 JP 5844601B2 JP 2011229285 A JP2011229285 A JP 2011229285A JP 2011229285 A JP2011229285 A JP 2011229285A JP 5844601 B2 JP5844601 B2 JP 5844601B2
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portion
diameter side
hole
inner diameter
central axis
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JP2013087871A (en
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靖浩 石川
靖浩 石川
義則 兵藤
義則 兵藤
大輔 中原
大輔 中原
竜也 西中
竜也 西中
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ジヤトコ株式会社
ユニプレス株式会社
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Description

  The present invention relates to a vibration damping device for a torque converter.

  Patent Document 1 discloses a vibration damping device for attenuating vibrations of power generated by an engine.

JP 2010-007717 A

  As shown in FIG. 8, the vibration damping device 200 of Patent Document 1 includes a hold plate 202 that is fixed to a lock-up piston 201 and receives the rotational driving force of an engine, and a driven plate 203 that is connected to a turbine of a torque converter. And a spring (an outer diameter side spring 204 and an inner diameter side spring 205) that elastically couples the hold plate 202 and the driven plate 203 in the rotational direction and is disposed along the circumferential direction of the rotation.

  In this vibration damping device 200, when the lock-up piston 201 is fastened to the cover converter 206 and brought into the lock-up state, the rotational driving force of the engine is directly input to the hold plate 202 connected to the lock-up piston 201. The rotational driving force input to the hold plate 202 is transmitted to the driven plate 203 side via springs (outer diameter side spring 204, inner diameter side spring 205) provided on the outer diameter side and inner diameter side of the hold plate 202. It has become so.

  Here, since the hold plate 202 is connected to the lock-up piston 201 by the rivet R on the inner diameter side, when the engine is in the lock-up state and the rotational driving force of the engine is directly input to the hold plate 202, the hold plate 202 Torsional stress acts on the connecting portion of the plate 202 by the rivet R. Therefore, the hold plate 202 needs to have circumferential rigidity that can withstand torsional stress.

Further, the lock-up piston 201 is fastened to the cover converter 206 by displacing (curving) the lock-up piston 201 to the cover converter side by the hydraulic pressure (apply pressure) applied to the lock-up piston 201 (see FIG. Middle, see arrow).
However, if the rigidity strength of the hold plate 202 is high, the curvature of the lockup piston 201 is hindered, and it is difficult to fasten the lockup piston 201 to the cover converter 206 quickly. Therefore, it is preferable that the hold plate 202 has low rigidity in the bending direction (axial direction) of the lockup piston 201.

  As described above, in order to perform smooth lockup in the vibration damping device 200, it is necessary to suppress the axial rigidity while maintaining the circumferential rigidity of the hold plate 202 high.

  In the case of Patent Document 1, as shown in FIG. 8B, a pierce hole 208 is provided on the outer diameter side of the support hole 207 of the hold plate 202 that supports the inner diameter side spring 205, and the axial direction of the hold plate 202 is changed. Decreasing stiffness is disclosed.

  However, as in Patent Document 1, just by providing the piercing hole 208 on the outer diameter side of the support hole 207, the rigidity on both sides of the support hole 207 does not decrease, so the axial rigidity of the hold plate 202 is sufficiently increased. I couldn't lower it.

  Accordingly, it is required to suppress the rigidity in the axial direction while maintaining the rigidity in the circumferential direction of the hold plate high so that the lockup piston can be quickly fastened to the cover converter.

The present invention includes a hold plate that is fixed to a lockup piston of a torque converter and rotates about a central axis integrally with the lockup piston;
A driven plate connected to the turbine of the torque converter and rotating about the central axis;
A vibration provided on the outer diameter side and the inner diameter side in the radial direction of the central axis and arranged along the circumferential direction around the central axis and elastically connecting the hold plate and the driven plate in the rotational direction. In the damping device,
A spring holding portion that protrudes from the fixing portion of the hold plate to the lock-up piston to the inner diameter side and that has a holding hole that holds the spring on the inner diameter side;
A through hole formed in the grip portion on both sides of the holding hole in the direction along the central axis of the inner diameter side spring ,
The through hole is a long hole formed along the circumferential direction, and communicates with the holding hole from both sides of the holding hole.
Wherein the through-hole, and the vibration damping device having the configuration narrowing the circumferential direction of the width of the connection portion between the inner diameter side and outer diameter side sandwiching the through hole 40.

In part the spring holding portion is formed in the hole plates, it is possible to weaken the rigidity and strength of the shaft Direction, hold plate, easily bent in the axial direction, an excellent member flexible.

It is a figure explaining a torque converter provided with a vibration damping device concerning an embodiment. It is a figure explaining the vibration damping device concerning an embodiment. It is a figure explaining the hold plate concerning an embodiment. It is the enlarged view to which a part of hold plate concerning an embodiment was expanded. It is a figure explaining the driven plate concerning an embodiment. It is a figure explaining the equalizer concerning embodiment. It is an enlarged view of the spring holding part of the hold plate concerning an embodiment. It is a figure explaining the vibration damping device concerning a prior art example.

Embodiments of the present invention will be described below.
FIG. 1 is a diagram illustrating a vibration damping device 1 in the torque converter 100.
2A and 2B are diagrams for explaining the vibration damping device 1, wherein FIG. 2A is a plan view, FIG. 2B is a cross-sectional view taken along line AA in FIG. 2A, and FIG. It is BB sectional drawing in.
In FIG. 2A, approximately 1/3 in the lower right is a plan view in a state where the driven plate 4 exists, and approximately 1/3 in the lower left is a plan view in which the driven plate 4 is not shown. And approximately 1/3 on the upper side is a cross-sectional view of the vibration damping device 1 cut along a plane orthogonal to the central axis X.

  As shown in FIGS. 1 and 2, the vibration damping device 1 is provided inside the torque converter 100, and includes a hold plate 3, a driven plate 4, and springs (an outer diameter side spring 5 and an inner diameter side spring 6). And an equalizer 7.

  When the torque converter 100 is brought into a lock-up state in which the lock-up piston 2 is fastened to the cover converter 101 and the rotational driving force of the engine is directly input to the transmission mechanism unit side. This is provided in order to prevent the vibration of the engine from directly propagating to the speed change mechanism portion side.

Hereinafter, each component of the vibration damping device 1 will be described.
3A and 3B are diagrams for explaining the hold plate 3, wherein FIG. 3A is a plan view and FIG. 3B is a cross-sectional view taken along line AA in FIG. 4A is an enlarged view of a part of the hold plate 3, and FIG. 4B is a cross-sectional view taken along line AA in FIG.

[Hold plate]
As shown in FIG. 2, the hold plate 3 is fixed to the surface of the lockup piston 2 opposite to the cover converter 101, and is provided so as to rotate integrally with the lockup piston 2.

As shown in FIG. 3, the hold plate 3 is a molded body of a ring-shaped plate member as viewed from the axial direction, and a ring-shaped fixing portion 31 is provided on the inner diameter side thereof.
The fixing portion 31 is provided with a rivet hole 31a passing through the fixing portion 31 in the thickness direction. The hold plate 3 is fixed to the lock-up piston 2 by a rivet R through which the rivet hole 31a is inserted. Yes.
In the embodiment, a total of nine rivet holes 31a are provided at predetermined intervals in the circumferential direction around the central axis X, and these are imaginary circles Im1 centered on the central axis X (FIG. 4A). Refer to the above).

On the outer periphery of the fixed portion 31, abutting portions 34 extending outward in the radial direction are provided at a total of three locations at predetermined intervals in the circumferential direction around the central axis X.
In plan view, the abutment portion 34 has a shape in which the circumferential width increases as the distance from the central axis X increases, and the outer peripheral edge of each abutment portion 34 is a flange located on the radially outer side of the fixed portion 31. Connected to the unit 33.

An outer diameter side spring 5 to be described later contacts the contact portion 34 from the circumferential direction (see FIG. 2). The contact portion 34 has a curved shape in a cross-sectional view in order to secure a contact surface with the outer diameter side spring 5.
Specifically, as shown in FIGS. 3B and 4B, the contact portion 34 is curved so as to bulge in the direction away from the lockup piston 2 in order from the inner diameter side. An inner diameter side curved portion 34a, an outer diameter side curved portion 34b curved so as to swell in a direction approaching the lockup piston 2, and a linear portion extending in a direction away from the lockup piston 2 parallel to the central axis X 34c, and has a shape along the periphery of the outer diameter side spring 5 on the lockup piston 2 side.

The distal end side of the linear portion 34 c extending in the direction away from the lockup piston 2 is curved outward in the radial direction, and the distal end thereof is integrally connected to the inner periphery of the flange portion 33.
The flange portion 33 is located on the transmission mechanism portion side (the side away from the lock-up piston 2) from the fixed portion 31, and extends along a direction substantially orthogonal to the central axis X (see FIG. 3B). ).

  The flange portion 33 has a ring shape when viewed from the axial direction, and extends in parallel to a flange portion 71 of an equalizer 7 described later, and has a range in which the equalizer 7 can move in a direction away from the lockup piston 2. It prescribes.

  A peripheral wall portion 33 a extending in a direction away from the lockup piston 2 is formed on the outer peripheral edge of the flange portion 33 by bending the outer diameter side of the flange portion 33 in a direction away from the lockup piston 2. The peripheral wall portion 33a is provided over the entire circumference of the outer peripheral edge of the flange portion 33 in the circumferential direction around the central axis X (see FIG. 3A), and a flange portion with which an equalizer 7 to be described later contacts. 33 and the outer diameter side of the hold plate 3 including the abutting portion 34 described above are provided to ensure the strength. And this surrounding wall part 33a is formed by the substantially same outer diameter as the cylindrical part 2c (refer FIG.4 (b)) provided in the outer periphery of the lockup piston 2. As shown in FIG.

  On the inner peripheral edge of the flange portion 33, an outer regulating portion 33b extending inward in the radial direction is provided. As shown in FIG. 4B, the outer restricting portion 33 b extends in the direction away from the lockup piston 2 along the outer periphery viewed from the axial direction of the outer diameter side spring 5, and the outer diameter side spring 5. Is provided in order to restrict movement in a direction away from the lockup piston 2.

As shown in FIG. 3, an opening 32 surrounded by the fixing portion 31, the contact portion 34, and the flange portion 33 is located on the outer diameter side of the fixing portion 31 in plan view.
In the opening 32, an outer diameter side spring 5 is located, which is disposed in a housing space S (see FIG. 3B) formed between the hold plate 3 and the lockup piston 2.

The openings 32 are formed with a predetermined length in the circumferential direction around the central axis X. In the embodiment, a total of three openings 32 are provided at equal intervals.
The opening 32 is formed over an angular range W that can accommodate two outer-diameter-side springs 5 (5a, 5b) arranged in the circumferential direction when viewed from the central axis X ((a in FIG. 2). ), See FIG.

On the inner diameter side of the opening 32, an inner regulating portion 31b is provided by cutting and bending. The inner regulating portion 31b is bent toward the front side in the drawing (in the direction away from the lock-up piston) in FIG. 3A, and the outer diameter side spring 5 disposed in the opening 32 moves in the inner diameter direction. It is provided to regulate
The inner restricting portion 31b is formed in two portions in the circumferential direction, avoiding a position overlapping the radially outer side of the rivet hole 31a when viewed from the central axis X. As shown in FIG. The inner side regulation part 31b is formed in the arc shape along the virtual circle Im2 centering on the central axis X. As shown in FIG.

As shown in FIG. 2, the outer diameter side spring 5 positioned in the opening 32 in plan view is composed of a pair of split springs 5a and 5b, and a contact portion 34 in the longitudinal direction of the split springs 5a and 5b. A retainer 8 is inserted and attached to the end portion on the side.
One end of each of the split springs 5a and 5b is in contact with the contact portion 34 of the hold plate 3 through the retainer 8 in the circumferential direction, and the other end is in contact with a support portion 72 of the equalizer 7 described later in the circumferential direction.
Therefore, both ends of the outer diameter side spring 5 are held in a state of being gripped by the adjacent contact portions 34, 34 in the circumferential direction around the central axis X, and along the circumferential direction around the central axis X. Has been placed.

As shown in FIG. 3, a spring holding portion 35 for holding the inner diameter side spring 6 is formed on the inner diameter side of the fixed portion 31 so as to bulge toward the central axis X side.
The spring holding portions 35 are formed so as to overlap with the contact portions 34 when viewed from the central axis X, and are provided at three positions in the circumferential direction around the central axis X in the embodiment.

  As shown in FIG. 4A, the spring holding portion 35 is formed with a holding hole 36 for holding the inner diameter side spring 6. The holding hole 36 has a circumferential width W1 that is substantially the same as the axial length of the inner diameter side spring 6. The inner diameter side spring 6 disposed in the holding hole 36 has both ends in the axial direction at the holding hole. It is provided in a state of being gripped by 36 edges 36a, 36a.

On the inner diameter side and outer diameter side edges of the holding hole 36, restriction portions 37 and 38 are provided by cutting and bending.
The restricting portion 37 is bent in a direction away from the lockup piston 2, and the restricting portion 38 is bent toward the lockup piston 2. In the embodiment, the restricting portions 37 and 38 restrict the movement of the inner diameter side spring 6 in the inner diameter direction and the outer diameter direction.

The width W2 of the restricting portions 37 and 38 in the circumferential direction around the central axis X is shorter than the width W1 of the holding hole 36.
In the embodiment, the inner diameter side spring 6 is compressed in the axial direction of the inner diameter side spring 6 by an opening 43 (see FIG. 5) of the driven plate 4 described later. Therefore, only the central portion in the longitudinal direction of the inner diameter side spring 6 is in contact with the restriction portions 37 and 38 so that the expansion and contraction in the axial direction of the inner diameter side spring 6 is not greatly hindered by the restriction portion 37. Has been.

Both sides of the holding hole 36 in the spring holding portion 35 are gripping portions 39 for gripping both ends of the inner diameter side spring 6. The grip portion 39 has a curved shape in a cross-sectional view in order to secure a contact surface with the inner diameter side spring 6.
As shown in FIG. 4B, the grip portion 39 is curved so as to swell in a direction approaching the lock-up piston 2 in a cross-sectional view, and is closest to the lock-up piston 2 in the curved portion. The apex 39a located at the center of the holding hole 36 is positioned substantially at the center in the radial width W3.

[Driven plate]
5A and 5B are views for explaining the driven plate 4. FIG. 5A is a plan view, FIG. 5B is a cross-sectional view taken along the line AA in FIG. 5A, and FIG. It is an enlarged view.

  As shown in FIG. 2, the driven plate 4 is located on the opposite side of the hold plate 3 from the lock-up piston 2, and the driven plate 4 and the hold plate 3 are in contact with the spring receiving portion 45 on the outer peripheral side. 34 are provided so as to overlap each other when viewed in the axial direction.

As shown in FIG. 5A, the driven plate 4 is a molded body of a ring-shaped plate member as viewed from the axial direction, and a ring-shaped attachment portion 41 is provided on the inner diameter side thereof.
In the vibration damping device 1, the attachment portion 41 is provided in a direction orthogonal to the central axis X, and the attachment portion 41 is provided with an attachment hole 41 a. The attachment holes 41a are provided through the attachment portion 41 in the thickness direction, and a plurality of attachment holes 41a are provided at predetermined intervals in the circumferential direction around the central axis X.

  In the embodiment, a total of six mounting holes 41a are provided, and the driven plate 4 is connected to the turbine of the torque converter by rivets (not shown) inserted through the mounting holes 41a. .

The outer diameter side of the mounting portion 41 is a curved portion 42 that curves so as to bulge toward the lockup piston 2, and the curved portion 42 penetrates the curved portion 42 in the thickness direction and has an opening 43. Is formed.
In the embodiment, the apex portion 42a that is located closest to the lockup piston 2 side of the curved portion 42 is formed so as to be located approximately in the middle in the radial width W4 of the opening 43, and the opening 43 is centered. Three are provided at predetermined intervals in the circumferential direction around the axis X.

  In the embodiment, in the state where the driven plate 4 is incorporated in the vibration damping device 1, the shape of the curved portion 42 is set so that the apex portion 42 a crosses the central portion viewed from the axial direction of the inner diameter side spring 6. (See (c) of FIG. 5).

On the outer periphery of the driven plate 4, spring receiving portions 45 extending radially outward are provided in a total of three locations at predetermined intervals in the circumferential direction around the central axis X.
In plan view, the spring receiving portion 45 has a shape in which the width in the circumferential direction increases as the distance from the central axis X increases, and the outer diameter side spring 5 abuts from the circumferential direction.
The spring receiving portion 45 is curved in a cross-sectional view in order to secure the contact surface with the outer diameter side spring 5 while avoiding interference with the contact portion 34 of the hold plate 3 located on the lockup piston 2 side. It has a shape.

  Specifically, as shown in FIGS. 5B and 5C, the spring receiving portion 45 is curved from the inner diameter side so as to bulge in the direction away from the lockup piston 2 in order from the inner diameter side. 45a and a linear portion 45b extending in a direction orthogonal to the central axis X, and the spring receiving portion so that the linear portion 45b crosses the central portion viewed from the axial direction of the outer diameter side spring 5. 45 shapes are set.

[equalizer]
6A and 6B are diagrams for explaining the equalizer 7, wherein FIG. 6A is a plan view seen from the axial direction, FIG. 6B is a cross-sectional view taken along line AA in FIG. 6A, and FIG. (B) is an enlarged view of the region C in (b), (d) is a BB cross-sectional view in (a).

  As shown in FIG. 2 (b), the equalizer 7 is positioned between the lock-up piston 2 and the hold plate 3 in the axial direction of the central axis X, with respect to the lock-up piston 2 and the hold plate 3. Are provided so as to be relatively rotatable.

  The equalizer 7 includes a ring-shaped main body portion 70 as viewed from the axial direction, a flange portion 71, and a support portion 72 extending from the main body portion 70 toward the inner diameter side.

A side of the main body portion 70 opposite to the lock-up piston 2 is bent radially outward, and a flange portion 71 extending in a direction orthogonal to the central axis X is formed.
In the embodiment, the outer diameter side spring 5 moved radially outward by centrifugal force comes into contact with the inner peripheral surface 70 a of the main body portion 70, and the stress that the main body portion 70 receives from the outer diameter side spring 5. In order to prevent the deformation, the flange portion 71 is provided in the main body portion 70 to ensure the strength.

The support portion 72 supports the other ends of the split springs 5a and 5b described above, and is formed to extend radially inward from the end portion of the main body portion 70 on the lockup piston 2 side.
In the embodiment, three support portions 72 are formed at equal intervals in the circumferential direction around the central axis X, and are provided to connect the pair of split springs 5a and 5b in the circumferential direction around the central axis X. It has been.

  As shown in FIG. 6 (c), the support portion 72 extends radially inward from the end on the lock-up piston 2 side, and is then bent in a direction away from the lock-up piston 2. It is bent to the inner diameter side. Therefore, the support part 72 is made into the shape curved so that the center part seen from the axial direction of the outer diameter side spring 5 may be crossed from the lockup piston 2 side.

In the embodiment, the movement of the equalizer 7 to the transmission side is restricted by the flange portion 33 of the hold plate 3, and the movement to the engine side is restricted by the lockup piston 2.
The movement of the equalizer 7 in the inner diameter direction (center axis X) side is basically restricted by the outer diameter side spring 5, and the movement in the outer diameter direction is restricted by the cylindrical portion 2 c of the lockup piston 2. It is like that.

In the vibration damping device 1 having such a configuration, as shown in FIG. 1, when the engine speed reaches a predetermined speed, the lockup piston 2 is pushed to the engine side by hydraulic pressure, and the torque converter 100 includes the lockup piston 2. The friction lining 2b is locked up with the cover converter 101.
In the lock-up state, the rotational driving force of the engine is directly input to the hold plate 3 via the lock-up piston 2, so that the hold plate 3 rotates about the central axis X relative to the driven plate 4. .
At this time, since the contact surface 45c (see FIG. 5A) of the spring receiving portion 45 of the driven plate 4 is in contact with the outer diameter side spring 5 from the axial direction, the hold plate 3 is provided with the spring receiving portion. While rotating the outer diameter side spring 5 in the circumferential direction at 45, it rotates relative to the driven plate 4.

  Thereby, since the rotational driving force input to the hold plate 3 is input to the driven plate 4 via the outer diameter side spring 5, the input rotational driving force is transmitted to a turbine hub and a transmission (not shown). Will be communicated.

Here, as shown in FIG. 2A, the edge 43 a of the opening 43 of the driven plate 4 and the edge 36 a of the holding hole 36 of the spring holding portion 35 of the hold plate 3 are arranged around the central axis X. It is arranged with a phase difference of angle θ in the direction.
Therefore, immediately after the transmission of the rotational driving force from the hold plate 3 to the driven plate 4 is started, only the outer diameter side spring 5 is compressed.
When the transmitted rotational driving force (torque) increases and the hold plate 3 rotates relative to the driven plate 4 by θ, compression by the edge 43a of the opening 43 of the inner diameter side spring 6 is started. The
Therefore, the rotational driving force is finally input to the driven plate 4 via the outer diameter side spring 5 and the inner diameter side spring 6.

Hereinafter, the main part of the hold plate 3 in the vibration damping device 1 will be described.
FIG. 7 is an enlarged view showing the periphery of the spring holding portion 35 of the hold plate 3 in an enlarged manner.
As shown in FIG. 7, the spring holding portion 35 of the hold plate 3 is formed to extend from the ring-shaped fixing portion 31 of the hold plate 3 toward the inner diameter side (center axis X side).

  In the fixing portion 31, rivet holes 31a are formed at predetermined intervals in the circumferential direction around the central axis X, and the spring holding portion 35 is located between the rivet holes 31a, 31a adjacent in the circumferential direction when viewed from the central axis X side. Extends radially inward.

In plan view, the spring holding portion 35 has a shape in which the circumferential width W5 becomes narrower toward the inner diameter side (center axis X), and the holding hole 36 of the inner diameter side spring 6 is formed at the center thereof. Is formed.
The holding hole 36 is provided so as to penetrate the spring holding portion 35 in the thickness direction, and both ends in the longitudinal direction (axial direction) of the inner diameter side spring 6 are supported by peripheral edges 36 a of the holding hole 36. Has been.

On the inner diameter side and the outer diameter side of the holding hole 36, there are a restriction portion 37 bent in a direction away from the lockup piston 2 by cutting and bending and a restriction portion 38 bent in a direction approaching the lockup piston 2. Is provided.
In plan view, the connecting portion 36b between the base end of the restricting portion 37 and the holding hole 36 is formed in an arc shape to alleviate stress concentration.

A through portion 40 is formed on the outer diameter side of the holding hole 36 in a target shape with a virtual line Im3 connecting the central axis X and the middle in the circumferential direction of the holding hole 36 interposed therebetween.
The through portion 40 is formed with a predetermined length W6 along the circumferential direction around the central axis X. The end of the through portion 40 on the imaginary line Im3 side extends to the outside of the holding hole 36 in the radial direction, and the through portion 40 communicates with the holding hole 36 from the outside of the holding hole 36 in the radial direction.

  The outer peripheral edge 40b of the penetrating portion 40 is formed along a virtual circle Im5 centered on the central axis X. The virtual circle Im5 is a virtual circle having a smaller diameter than the virtual circle Im6 passing through the inner diameter side edge of the rivet hole 31a.

  In the embodiment, the hold plate 3 is connected and fixed to the lockup piston 2 by a rivet R through which the rivet hole 31a is inserted (see FIG. 2B). Therefore, when the torque converter 100 is in the lock-up state and the rotational driving force of the engine is input from the lock-up piston 2 to the hold plate 3, the torsion is caused between the lock-up piston 2 and the hold plate 3. Stress acts.

This stress acts in the circumferential direction of the rivet R (rivet hole 31a) that connects the lockup piston 2 and the hold plate 3.
In the case of FIG. 7, torsional stress acts in the circumferential direction around the central axis X in a region between a virtual circle Im6 passing through the inner diameter side edge of the rivet hole 31a and a virtual circle Im7 passing through the outer diameter side edge.
Therefore, if the through portion 40 is formed in the circumferential direction of the rivet hole 31a and reaching the region sandwiched between the virtual circle Im6 and the virtual circle Im7, the rigidity of the hold plate 3 against torsional stress is reduced.
Therefore, in the embodiment, the position of the outer peripheral edge 40b is set so that the penetration part 40 is formed on the inner diameter side of the virtual circle Im6 (rivet hole 31a).

The inner peripheral edge 40a of the penetrating portion 40 is formed along a virtual circle Im4 centered on the central axis X.
The virtual circle Im4 is a virtual circle that passes radially outside the contact point P on the outer diameter side between the inner diameter side spring 6 and the edge 36a of the holding hole 36, and the holding hole when the through portion 40 is not formed. This is a virtual circle having a smaller diameter than a virtual circle Im8 passing through an outer edge 36c (indicated by a virtual line in the drawing) of 36.

  When the penetrating portion 40 is provided on the radially outer side of the holding hole 36, it is necessary to secure a radial width for forming the holding hole 36 in the hold plate 3. As described above, the rigidity of the rivet in the circumferential direction needs to be ensured. In this case, the holding hole 36 (spring holding portion 35) is moved radially inward to form the holding hole 36. Space will be secured. Then, the working diameter of the inner diameter side spring 6 (the diameter from the central axis X) is limited, and the capacity for torque input is reduced.

In the embodiment, the inner peripheral edge 40a of the penetrating portion 40 is positioned radially inward from the outer diameter side edge 36c (indicated by a phantom line in the drawing) of the holding hole 36 when the penetrating portion 40 is not formed. ing. The imaginary line Im3 side of the through portion 40 is held so that the through portion 40 is connected to the holding hole 36 at a radially outer side than the contact point P on the outer diameter side between the inner diameter side spring 6 and the edge 36a. The holding hole 36 communicates with the holding hole 36 from an oblique direction outside the hole 36 in the radial direction.
This is because when the penetrating portion 40 communicates with the holding hole 36 on the inner diameter side of the contact point P, the gripping of the inner diameter side spring 6 in the gripping portion 39 is hindered.

  Thereby, since the holding hole 36 is not moved to the inner diameter side of the hold plate 3 in order to form the through portion 40, the working diameter of the inner diameter side spring 6 is limited, and the capacity for torque input is reduced. Is prevented.

  The penetrating portion 40 is a long hole whose basic shape extends along the circumferential direction around the central axis X, and the distal end 40 c in the direction away from the holding hole 36 is a gripping portion 39 on both sides of the holding hole 36 in the spring holding portion 35. It is formed to the range which extends to the approximate center.

In the hold plate 3, a continuous portion (continuous portion) extending continuously outward in the radial direction when viewed from the central axis X is a portion that increases the rigidity of the hold plate 3 against bending in the axial direction.
In the case of the hold plate 3 shown in FIG. 7, the abutting portion 34 is located on the radially outer side opposite to the spring holding portion 35 with the fixed portion 31 in between when viewed from the central axis X.
Therefore, for example, when the through portion 40 is not formed, the range of the width W7 from the grip portion 39 to the contact portion 34 is a continuous portion extending continuously outward in the radial direction when viewed from the central axis X.

  In this case, the rigidity of the hold plate 3 against bending in the axial direction is enhanced by the range of the width W7. As a result, the axial direction (thrust direction) of the central axis X of the lockup piston 2 to which the hold plate 3 is fixed. ) Is also more rigid against bending.

In the embodiment, by providing the penetrating portion 40 having a circumferential width W6, the continuous portion extending continuously from the grip portion 39 to the abutting portion 34 in the radial direction is narrowed to the range of the width W8. It has been.
Therefore, as compared with the case where the through portion 40 is not provided, the rigidity of the hold plate 3 with respect to the bending in the axial direction is weakened by the width of the continuous portion.

Furthermore, since the penetration part 40 is located in the middle of the continuous part, the connection part 31c between the inner diameter side (gripping part 39) and the outer diameter side (contact part 34) is narrowed across the penetration part 40. The inner diameter side (gripping part 39) and the outer diameter side (contact part 34) are each easily bent in the axial direction with the connection part 31c as a boundary.
Therefore, this also weakens the rigidity of the lockup piston 2 to which the hold plate 3 is fixed against bending in the axial direction.

In the embodiment, the hold plate 3 has an inner diameter side (gripping portion 39) and an outer diameter side (contact portion 34) that are curved in the axial direction with the connection portion 31c as a boundary. The through portion 40 is a range from the edge 36a on both sides of the holding hole 36 to both side ends 35a in the circumferential direction of the spring holding portion 35, and withstands bending stress repeatedly input to the connecting portion 31c. It is formed within a range where strength can be maintained.
For example, since the rigidity of the hold plate increases as the plate thickness of the hold plate 3 increases, in the embodiment, the hold plate can be increased by increasing the circumferential width W6 of the through portion 40 as the plate thickness increases. The rigidity is adjusted appropriately.

  In the embodiment, the circumferential width W6 of the penetrating portion 40 is the maximum within a range in which the strength of the connecting portion 31c can be ensured, and the distal end 40c of the penetrating portion 40 is the It can be extended in the circumferential direction to the vicinity.

As described above, the hold plate 3 fixed to the lock-up piston 2 of the torque converter 100 and rotating around the central axis X integrally with the lock-up piston 2 and the turbine of the torque converter 100 are connected around the central axis X. The rotating driven plate 4, the hold plate 3 and the driven plate 4 are elastically coupled in the rotation direction, and the inner diameter side spring 6 and the outer diameter side spring 5 disposed in the circumferential direction around the central axis X, In the vibration damping device 1, the rotational driving force of the engine input to the hold plate 3 is transmitted to the driven plate 4 via the inner diameter side spring 6 and the outer diameter side spring 5.
In the hold plate 3, the spring holding portion 35 in which the holding hole 36 of the inner diameter side spring 6 is formed extends (projects) from the ring-shaped fixing portion 31 to the lockup piston 2 to the inner diameter side. In the spring holding portion 35, through portions 40 are provided in contact with the holding holes 36 in the holding portions 39 on both sides of the holding holes 36 in the circumferential direction around the central axis X. The holding holes 36 are provided on the inner diameter side. The structure is formed along the central axis of the spring 6.

In the hold plate 3, a range from the holding portions 39 on both sides of the holding hole 36 in the spring holding portion 35 to the radially outer fixed portion 31 is a continuous portion extending continuously outward in the radial direction when viewed from the central axis X. The continuous portion increases the rigidity strength (bending strength) in the axial direction of the central axis X of the hold plate 3.
If comprised as mentioned above, since the width | variety of the circumferential direction of the continuous part extended continuously in the radial direction seeing from the central axis X is narrowed, the rigidity strength of the axial direction of the hold plate 3 can be weakened. Thereby, since the hold plate 3 becomes a member excellent in flexibility that is easily bent in the axial direction, the rigidity against the bending in the axial direction of the fixed lockup piston 2 to which the hold plate 3 is fixed can be weakened. .

  In particular, a contact portion 34 extending radially outward is provided on the opposite side of the spring holding portion 35 with the fixed portion 31 in between, and a continuous portion extending continuously outward in the radial direction when viewed from the central axis is a spring holding portion. When the range from the grip portion 39 of the portion 35 to the contact portion 34 through the fixing portion 31 is reached, the rigidity strength (bending strength) in the axial direction of the central axis X of the hold plate 3 is further increased. Even in such a case, since the rigidity strength in the axial direction of the hold plate 3 can be weakened, the rigidity of the lock-up piston 2 against bending in the axial direction is lowered.

  Further, in the grip portion 39, the penetrating portion 40 is within a range in which the holding of the inner diameter side spring 6 by the grip portion 39 from both sides of the holding hole 36 to the vicinity of both side ends 35 a in the circumferential direction of the spring holding portion 35 is not impaired. It was set as the structure provided.

  With this configuration, as viewed from the central axis X, a space portion by the through portion 40 is intermittently formed in the middle of a continuous portion that is continuous radially outward from the grip portions 39 on both sides of the holding hole 36. Therefore, the rigidity strength with respect to the bending of the hold plate 3 in the axial direction can be reduced. Thereby, since the rigidity of the hold plate 3 in the axial direction is suppressed, the lock-up piston 2 can be quickly fastened to the cover converter.

  A plurality of rivet holes 31 a through which rivets R (fastening members) for fastening the hold plate 3 to the lock-up piston 2 are inserted are provided at predetermined intervals in the circumferential direction around the central axis X. In addition, the penetrating portion 40 is provided on the inner diameter side of the rivet hole 31a.

When the rotational driving force of the engine is input from the lockup piston 2 to the hold plate 3, a torsional stress acts between the lockup piston 2 and the hold plate 3, and this torsional stress is applied to the lockup piston. 2 and the hold plate 3, that is, acts in the circumferential direction of the rivet R. In the case of the hold plate 3, a torsional stress acts in the circumferential direction of the rivet hole 31a of the rivet R. Therefore, if the through-hole 40 is formed extending in the circumferential direction of the rivet hole 31a, the rigidity of the hold plate 3 against the torsional stress is reduced. End up.
By configuring as described above and providing the penetrating portion 40 on the inner diameter side of the rivet hole 31a, the rigidity in the axial direction can be suppressed while maintaining the rigidity in the circumferential direction of the hold plate 3 high.

  In particular, the through portion 40 is formed to extend from both edges 36 a of the holding hole 36 toward both side ends 35 a of the holding hole 36 when viewed from the central axis X. The through portion 40 is formed of the holding hole 36. The outer diameter side contact point P of the inner diameter side spring 6 is radially outer than the contact point P of the inner diameter side spring 6 and in the inner diameter side of the rivet hole 31a.

  If comprised in this way, in order to provide the penetration part 40, since it is not necessary to move the holding hole 36 to radial inside, the inner diameter side spring 6 can be arrange | positioned to the outer diameter side as much as possible. That is, since it is not necessary to reduce the working diameter of the inner diameter side spring 205 in order to provide the through portion 40, the capacity of the inner diameter side spring with respect to torque input does not decrease. Therefore, in the conventional case, it has been necessary to provide a higher-performance spring in order to compensate for a decrease in the capacity of torque input. However, in the case of the vibration damping device 1 according to the embodiment, there is no such need. A cheaper spring can be used.

  The through portion 40 is a long hole formed along the circumferential direction around the central axis X, and the circumferential and radial widths of the long hole are set according to the thickness of the hold plate. The configuration.

  With this configuration, the rigidity of the hold plate changes according to the plate thickness. Therefore, by setting the circumferential direction and radial width of the long hole according to the plate thickness, the rigidity of the hold plate 3 in the circumferential direction is set. It is possible to make the hold plate 3 bend easily in the axial direction by reducing the rigidity in the axial direction while suppressing the decrease in the axial direction.

  In the above-described embodiment, the case where the penetrating portion 40 is provided in communication with the holding hole 36 of the spring holding portion 35 has been illustrated. However, when viewed from the central axis X, the portion extending from the grip portion 39 to the radially outer side If it is possible to weaken the rigidity strength, a notch communicating with the holding hole 36 or a piercing hole may be provided instead of the through portion.

  Furthermore, although the case where the inner peripheral edge 40a and the outer peripheral edge 40b of the penetration part 40 are formed so as to be along the virtual circle Im4 and the virtual circle Im5, respectively is illustrated, good.

DESCRIPTION OF SYMBOLS 1 Vibration damping device 2 Lock-up piston 3 Hold plate 4 Driven plate 5 Outer diameter side spring 6 Inner diameter side spring 7 Equalizer 8 Retainer 31 Fixed part 31a Rivet hole (insertion hole)
31b Inner restriction part 31c Connection part 32 Opening part 33 Flange part 33a Peripheral wall part 33b Outer restriction part 34 Abutting part 35 Spring holding part 36 Holding hole 37 Restriction part 38 Restriction part 39 Holding part 40 Through part 41 Attachment part 41a Attachment hole 42 Curved portion 43 Opening portion 45 Spring receiving portion 70 Body portion 71 Flange portion 72 Support portion 100 Torque converter 101 Cover converter P Contact point R Rivet (fastening member)
S Storage space X Center axis (Rotation center axis)

Claims (4)

  1. A hold plate fixed to the lock-up piston of the torque converter and rotating around the central axis integrally with the lock-up piston;
    A driven plate connected to the turbine of the torque converter and rotating about the central axis;
    A vibration provided on the outer diameter side and the inner diameter side in the radial direction of the central axis and arranged along the circumferential direction around the central axis and elastically connecting the hold plate and the driven plate in the rotational direction. In the damping device,
    A spring holding portion that protrudes from the fixing portion of the hold plate to the lock-up piston to the inner diameter side and that has a holding hole that holds the spring on the inner diameter side;
    A through hole formed in the grip portion on both sides of the holding hole in the direction along the central axis of the inner diameter side spring ,
    The through hole is a long hole formed along the circumferential direction, and communicates with the holding hole from both sides of the holding hole.
    A vibration damping device characterized in that the circumferential width of the connecting portion between the inner diameter side and the outer diameter side sandwiching the through hole is narrowed by the through hole .
  2. In the hold plate, a contact portion is provided on the outer side in the radial direction opposite to the spring holding portion across the fixed portion so that the spring on the outer diameter side contacts from the circumferential direction. A continuous portion extending in a radial direction from the grip portion to the contact portion is formed with a predetermined width in the circumferential direction,
    2. The vibration damping device according to claim 1, wherein the through hole is formed with a width in the circumferential direction extending to the continuous portion, and the connection portion is located in the continuous portion .
  3. The fixing portion of the hold plate is provided with a plurality of insertion holes through which a fastening member for fastening the hold plate to the lock-up piston is inserted at a predetermined interval in the circumferential direction.
    3. The vibration damping device according to claim 1, wherein the through hole is provided on an inner diameter side of the insertion hole.
  4. Before SL through hole, the outer circumferential edge of the retaining hole in the radial direction of the central axis, one of claims 1 to 3, characterized in that provided in the radial direction of the width across the radially The vibration damping device according to claim 1.
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KR20120115406A KR101494946B1 (en) 2011-10-18 2012-10-17 Vibration damping apparatus
CN201210397294.7A CN103062358B (en) 2011-10-18 2012-10-18 Arrangement for damping oscillations

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MX368828B (en) * 2013-09-13 2019-10-18 Nissan Motor Damper device.
JP6538729B2 (en) * 2014-03-13 2019-07-03 シェフラー テクノロジーズ アー・ゲー ウント コー. カー・ゲーSchaeffler Technologies AG & Co. KG Spring holding plate with cut and bent stopper
CN106461048B (en) * 2014-05-30 2019-03-19 有能沛思株式会社 The locking device of torque-converters
US10480615B2 (en) * 2016-03-16 2019-11-19 Aisin Aw Co., Ltd. Vibration damping device and method of designing the same

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JPH034830Y2 (en) * 1988-11-12 1991-02-07
JP2000002313A (en) * 1998-06-16 2000-01-07 Unisia Jecs Corp Torsional damper
JP2006037977A (en) * 2004-07-22 2006-02-09 Aisin Aw Industries Co Ltd End cap for damper spring of lockup damper
KR100660567B1 (en) 2005-08-30 2006-12-22 한국파워트레인 주식회사 Torque converter
KR100794265B1 (en) * 2006-01-06 2008-02-25 한국파워트레인 주식회사 Torque converter for hybrid electric vehicle
DE102008034557A1 (en) * 2007-08-02 2009-02-05 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Device for damping vibrations, in particular multistage torsional vibration dampers
JP5078535B2 (en) * 2007-10-10 2012-11-21 株式会社エクセディ Lock-up device and fluid torque transmission device including the same
JP5205068B2 (en) * 2008-01-18 2013-06-05 株式会社エクセディ Lock-up device
JP2010007717A (en) * 2008-06-25 2010-01-14 Valeo Unisia Transmission Kk Torsional vibration damping device
JP4934114B2 (en) * 2008-08-04 2012-05-16 ヴァレオユニシアトランスミッション株式会社 Torsional vibration reduction device
JP4773553B2 (en) 2009-08-26 2011-09-14 株式会社エクセディ Lock-up device for torque converter

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CN103062358B (en) 2016-09-07
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JP2013087871A (en) 2013-05-13
KR101494946B1 (en) 2015-02-23

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