JP2001221288A - Coil spring assembly and damper mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a difference of a stress generated at a radial side portion of a coil and a stress generated at a radial outer side potion less in a coil spring assembly in which an intermediate sheet is provided on a coil spring extended in a rotation direction. SOLUTION: In a first coil spring assembly 24, a coil spring 33 comprises a plurality of coils extending in a rotation direction. The coil spring 33 has a V-shaped portion opened to a radial inner side. The V-shaped portion comprises a first portion 63 approximately straightly extending, a second portion 64 and a bent portion 65 formed therebetween. The intermediate sheet 33 is disposed at a bent portion 65 of the coil spring 30 and has a receiving portion for receiving at least radial outer side portion of an end surface of the first portion 63 and an end surface of the second portion 64. It is restricted that a plurality of radial inner side portions at the bent portion 65 are approached each other in the rotation direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a coil spring assembly, and more particularly to a coil spring assembly including a coil spring extending in a circumferential direction.

[0002]

2. Description of the Related Art A damper mechanism is used in, for example, a power transmission system and is a mechanism for transmitting torque and absorbing / damping torsional vibration. The damper mechanism is the first
The rotating member includes a rotating member, a second rotating member, and a spring member or an elastic body that is disposed between the rotating members and that is compressed in a rotating direction between the rotating members when the members rotate relative to each other. The spring member includes, for example, a coil spring assembly.

The coil spring assembly used for the damper mechanism needs to have a low rigidity and a wide torsion angle in order to improve the vibration absorbing performance.
A damper mechanism that extends long in an arc in the rotation direction of the damper mechanism is used. However, in such an arc-type coil spring assembly, the intermediate portion of the coil spring moves radially outward due to a component force radially outward when the spring is compressed, and slides against other members. Problems are easy to occur. In such a case, the frictional resistance increases, and the vibration damping function of the damper mechanism decreases.

In order to solve such a problem, there is known a technique in which an intermediate sheet is provided at an intermediate portion of an arc type coil spring. The intermediate sheet has a wedge shape inserted from the outer peripheral side into the intermediate portion of the coil spring, and further has a portion that supports the outer peripheral side of the intermediate portion. Further, the intermediate sheet has a smooth outer peripheral surface in the rotational direction, and can smoothly slide in the rotational direction with respect to a member arranged on the outer peripheral side. As a result, even if the coil spring is long in the circumferential direction, sliding with other members on the outer peripheral side is reduced.

[0005]

Generally, when a spring such as a coil spring is compressed in the rotating direction, the amount of deflection on the outer peripheral side becomes larger than the amount of deflection on the inner peripheral side. This is because the amount of movement in the rotation direction of the outer peripheral portion of the spring support that pushes the coil spring in the rotation direction is larger than the amount of movement of the inner peripheral portion in the rotation direction. As a result, the amount of torsion of the inner peripheral side portion of the coil strand becomes larger than the amount of torsion of the outer peripheral side portion, so that the stress at each inner peripheral side portion of the coil strand becomes greater than the stress at each outer peripheral side portion. As described above, since the generated stress is biased between the outer peripheral portion and the inner peripheral portion of the coil in one spring, a problem arises in manufacturing and using the spring.

[0006] Considering the above problem with respect to the above-mentioned damper mechanism, the above prior art is disclosed in, for example, Japanese Patent Laid-Open No.
In each of these cases, two of the outer peripheral portions of the coils corresponding to the intermediate sheet become inaccessible to each other with the intermediate sheet interposed therebetween. I have. Therefore, no twist occurs in the inner peripheral portion extending between the two outer peripheral portions. That is, in these prior arts, the effective number of turns on the inner peripheral side of the coil is one less than the effective number of turns on the outer peripheral side as compared with the damper mechanism without the intermediate sheet. For this reason, the difference between the stress generated in each inner peripheral side portion of the coil and the stress generated in each outer peripheral side portion is further increased.

SUMMARY OF THE INVENTION An object of the present invention is to provide a coil spring assembly in which an intermediate sheet is provided on a coil spring extending long in the rotation direction, and a difference between a stress generated at each inner peripheral portion of the coil and a stress generated at each outer peripheral portion of the coil. Is to make it smaller.

[0008]

According to a first aspect of the present invention, there is provided a coil spring assembly for compressing in a rotational direction when relative rotation occurs in a damper mechanism.
It has a coil spring. The coil spring includes a plurality of coils extending in the rotation direction. The coil spring is arranged to be compressed in the rotation direction when the first rotating member and the second rotating member rotate relatively. The coil spring includes a first portion and a second portion, and a boundary disposed between the first and second portions. A plurality of radially inner portions of the coil at the boundary are restricted from rotationally approaching each other.

In this coil spring assembly, since the radial inner portions of the plurality of coils at the boundary portion are restricted from approaching each other in the rotational direction, the radius formed between the radial inner portions is restricted. The outer portion in the direction is less likely to be twisted when the spring is compressed. That is, in the above structure, the effective number of turns on the radially outer side of the coil spring is reduced as compared with the related art. As a result, the difference between the stress generated at each radially inner portion and the stress generated at each radially outer portion during spring compression is reduced. Note that "restricted to approach in the rotational direction" means that the space that can be approached to each other in the rotational direction is smaller than that of the conventional or other coil parts, except when it is immovable. In some cases, it is impossible to move at the initial stage.

[0010] In the coil spring assembly according to the second aspect, in the first aspect, the radially inner portions of the plurality of coils at the boundary portion are in close contact with each other in the rotational direction. In this coil spring assembly, the radially inner portions of the plurality of coils at the boundary portion are in close contact with each other, so that further approach in the rotational direction is restricted. The term "close contact" as used herein includes, besides the state of complete contact, the state of having a slight gap in the rotational direction and immediately contacting each other when the spring is compressed.

According to a third aspect of the present invention, there is provided a coil spring assembly according to the first or second aspect, which is disposed at a boundary of the coil spring and receives at least a radially outer portion of the end face of the first portion and the end face of the second portion. And an intermediate sheet having a receiving portion for receiving the intermediate sheet. In the coil spring assembly according to a fourth aspect, in the third aspect, the receiving portion entirely receives the end surface of the first portion and the end surface of the second portion.

In this coil spring assembly, the receiving portion supports the end faces of the first portion and the second portion not only in the radially outward direction but also in the radially outward direction. At the time of compression, the posture is stable and both are easily compressed in parallel. In the coil spring assembly according to claim 5, according to claim 3 or 4, the plurality of coil radially inner portions at the boundary portion have a first radius between two radially outer portions supported by the intermediate sheet. And a second radially inner portion on at least one side in the rotational direction.

In this coil spring assembly, the first radially inner portion and the second radially inner portion are restricted from approaching each other in the rotational direction. As a result, the twisting operation does not occur in the radially outer portion extending between the first radially inner portion and the second radially inner portion, and the effective number of turns in the radially outer portion is reduced. In the coil spring assembly according to the sixth aspect, in the third or fourth aspect, a radially inner portion of the plurality of coils at the boundary portion is located between the two radially outer portions supported by the intermediate sheet. It comprises a radially inner portion and second and third radially inner portions on both sides in the rotational direction.

In this coil spring assembly, the first radially inner portion and the second radially inner portion are restricted from approaching each other in the rotational direction. As a result, the twisting operation does not occur in the radially outer portion extending between the first radially inner portion and the second radially inner portion, and the effective number of turns in the radially outer portion is reduced. Furthermore, the first
The radially inner portion and the third radially inner portion are restricted from rotationally approaching each other. As a result, the first
No twisting action occurs on the radially outer portion extending between the radially inner portion and the third radially inner portion, and the effective number of turns in the radially outer portion is reduced.

According to a seventh aspect of the present invention, in the coil spring assembly according to any one of the third to sixth aspects, the coil spring has a plurality of boundaries, and the intermediate sheet is provided for each boundary. The coil spring assembly according to claim 8 further comprises a pair of spring seats according to any one of claims 1 to 7. The pair of spring seats support both ends of the coil spring, and are supported by the first rotating member and the second rotating member. Each spring seat supports the coil spring so that it cannot rotate around the spring center axis.

In this coil spring assembly, since both ends of the coil spring are supported by the spring seat, the coil spring cannot rotate around the spring center axis. Accordingly, if the coil spring is arranged so that the effective number of turns in the radially inner portion of the coil can be sufficiently secured, that state can be maintained. Claim 9
The coil spring assembly according to any one of claims 1 to 8, wherein the effective number of turns inside the first portion in the radial direction is larger than the number of effective turns outside in the radial direction, and the effective number of turns inside the second portion in the radial direction. The number of turns is greater than the effective number of turns on the radially outer side. The expression “the number of turns is large” means that the number of turns is at most one, and also includes the case where the number of turns is 0.1 to 1.0 depending on the position of the end.

In this coil spring assembly, in both the first portion and the second portion, the number of effective turns on the radially inner side is larger than the number of effective turns on the radially outer side. The difference in stress between the radially inner side and the radially outer side is reduced. In the coil spring assembly according to the tenth aspect, in any one of the first to ninth aspects, the first portion and the second portion extend substantially linearly, bend at the boundary, and toward the rotation center of the damper mechanism. An open V-shaped portion is formed.

In this coil spring assembly, since the first portion and the second portion extend substantially linearly, they are easily compressed in parallel. In the coil spring assembly according to claim 11, in claim 10, the coil spring is
In a free state before being mounted on the damper mechanism, a V-shaped portion is formed in advance.

In this coil spring assembly, it becomes easy to mount the coil spring assembly on the damper mechanism. The damper mechanism according to claim 12, wherein the first rotating member, the second rotating member arranged to be rotatable relative to the first rotating member, and the damper mechanism according to claim 1. And a coil spring assembly. A plurality of coil spring assemblies are provided. The damper mechanism further includes a connecting member that connects the plurality of intermediate sheets to each other.

In this damper mechanism, the connecting members can balance the radially outward forces acting on the plurality of intermediate sheets from the coil spring.
As a result, it is possible to prevent the intermediate sheet from sliding with respect to other members.

[0021]

1 to 3 show the structure of a damper mechanism 1 according to an embodiment of the present invention. The damper mechanism 1 can be used for a clutch disk assembly, a flywheel assembly, a lock-up device of a torque converter, and other power transmission systems of a vehicle.

The damper mechanism 1 mainly includes a first rotating member 2
And a second rotating member 3 arranged to be rotatable relative to the first rotating member 2, and a coil spring assembly 4 arranged between the rotating members 2, 3 in the rotating direction. Here, any of the first rotating member 2 and the second rotating member 3 may be an input side or an output side member, but in this embodiment, the first rotating member 2 is an input side member and the second rotating member Member 3
Is an output side member. In addition, since the main purpose of the present embodiment is to explain the structure of the damper mechanism, the description of the specific structure of input and output for transmitting torque with other members is omitted.

In FIG. 2 and FIG. 3, OO is the rotation axis of the damper mechanism 1. Further, the arrow R1 side in FIG. 1 is the driving side (rotation direction positive side) of the damper mechanism 1, and the arrow R2
The side is the opposite side (the negative side in the rotation direction). In the following description, the “rotational (circumferential) direction”, “axial direction”, and “radial direction” refer to each direction of the damper mechanism 1 as a rotating body, unless otherwise specified.

The first rotating member 2 is a substantially disk-shaped member as shown in FIG. The first rotating member 2 has a pair of window holes 19 extending substantially in an arc shape in the circumferential direction. Each window hole 19
Has an inner peripheral edge 21, an outer peripheral edge 22, and both edges 23 in the rotational direction. The inner peripheral edge 21 is composed of two generally linear portions forming a V-shape that opens radially inward. The outer peripheral edge 22 is formed in a substantially arc shape. Further, on the outer peripheral edge of the first rotating member 2, a total of three substantially semicircular protrusions 20 protruding outward in the radial direction are formed at equal intervals in the circumferential direction. A hole 20a is provided at a portion corresponding to the protrusion 20.
Are formed.

In other words, the first rotating member 2 includes an annular portion 34 on the outer peripheral side of the window hole 19, a central portion 35 on the inner peripheral side of the pair of window holes 19, Window hole 19
, And a pair of connecting portions 36 connecting the annular portion 34 and the central portion 35. Second
The rotating member 3 mainly includes a first plate 6, a second plate 7, and a plurality of pins 8 for fixing the plates 6 and 7 to each other. First plate 6 and second plate
The plate 7 is a member having substantially the same shape, and is arranged symmetrically on both axial sides of the first rotating member 2. The plates 6 and 7 are substantially disk-shaped members as shown in FIG. Further, a circular center hole 17 is formed at the center of each of the plates 6 and 7. Further, window holes 9 having the same shape are formed in the plates 6 and 7 at positions corresponding to the window holes 19. That is, each window hole 9 has an inner peripheral edge 11, an outer peripheral edge 12 and both edges 13 in the rotation direction. Further, on the outer peripheral edges of the plates 6 and 7, a protruding portion 10 protruding outward in the radial direction is formed. The protrusions 10 are formed at three places, and are equally spaced in the circumferential direction. The protruding portion 10 is located between the protruding portions 20 of the first rotating member 2 in the circumferential direction. Further, the protrusion 10 of the plate 6 and the protrusion 1 of the plate 7
0 are fixed to each other by pins 8. Thus, the axial distance between the plates 6 and 7 is determined, and the plates 6 and 7 rotate integrally.

The pin 8 is disposed between the protrusions 20 in the circumferential direction and shifted from the center in the circumferential direction toward the rotation direction R1. Further, when the pin 8 is twisted with respect to the rotation direction R2, the pin 8 can move by 60 degrees as a positive side torsion angle,
When twisted with respect to the rotation direction R1 side, it is possible to move by 30 degrees as a negative side torsion angle. The pin 8 can be used as a stopper for stopping the relative rotation of the damper mechanism 1 by contacting the projection 20.

In other words, the plates 6 and 7 include an outer annular portion 14, an inner annular portion 15 formed between the center hole 17 and the pair of window holes 9, It is a portion between the pair of window holes 9 in the circumferential direction, and includes a pair of connecting portions 16 for connecting the annular portions 14 and 15 to each other. As shown in FIG. 3, the annular portions 14 of the plates 6 and 7 are arranged apart from the first rotating member 2 in the axial direction, respectively, but the pair of connecting portions 16 are closer to each other in the inner circumferential direction. It is an inclined part, so the annular part 15
Is close to the first rotating member 2.

Next, the coil spring assembly 4 will be described. The coil spring assembly 4 includes a pair of first and second coil spring assemblies 24 and 25, and ring-shaped connecting members 26 and 27. A pair of first and second coil spring assemblies 24,25 are located in a pair of window holes 9,19, respectively. Each of the first and second coil spring assemblies 24 and 25 includes one coil spring 30, first and second spring seats 31 and 32 disposed at both ends thereof, and an intermediate sheet 33 provided therebetween. It is composed of

The coil spring 30 extends long to approximately both ends in the window holes 9 and 19. The coil spring 30 has a large ratio of the length in the circumferential direction to the coil diameter of 7 or more, and has a shape elongated in the rotation direction. This ratio is at least 4 or more, preferably in the range of 6-8. With the coil spring 3 mounted in the damper mechanism 1,
0 is divided into a first portion 63 on the rotation direction R1 side, a second portion 64 on the rotation direction R2 side, and a bent portion 65 corresponding to an intermediate boundary therebetween. The first portion 63 and the second portion 64 extend in a substantially straight line, so that the V-
It forms a character-shaped part. For this reason, the first portion 63 and the second portion 64 are compressed in parallel during compression, and the coils are likely to adhere to each other. As in the present embodiment, two damper mechanisms 1 are used.
In the type in which the present coil spring is used, the angle formed by the first portion and the second portion is approximately 90 degrees, and
It is preferably in the range of 00 degrees. The circumferential angle of the coil spring is about 145 degrees, at least 60 degrees or more, preferably 90 degrees or more, and most preferably 1 degree or more.
It is in the range of 20 degrees to 150 degrees.

Since the first portion 63 and the second portion 64 have the same length, the bent portion 65 and the intermediate sheet 33 are arranged at the center of the coil spring 30 in the rotation direction.
However, as shown in the modification of FIG.
The position of the intermediate sheet 33 may be shifted in the rotation direction from the rotation center of the coil spring 30 by making the length of the second portion 64 different from that of the coil spring 30. In FIG. 18, the first portion 63 is shorter than the second portion 64, that is, the bent portion 65 and the intermediate sheet 33 are shifted from the rotation direction center position of the coil spring 30 by the illustrated θ in the rotation direction R1 side. I have. The magnitude of the displacement angle θ is not limited to this modification.

The coil spring 30 may be in the above-mentioned V-shaped portion in a free state, or may be linear in a free state and only when incorporated into the damper mechanism 1
You may make it a character-shaped part. However, when the coil spring 30 is in the above-described V-shaped portion in a free state, it is easy to mount the coil spring 30 to the damper mechanism. The axial dimension (coil diameter) of the coil spring 30 is
7, which is longer than the axial distance between them. As a result, both sides of the coil spring 30 in the axial direction protrude from the window hole 9 in the axial direction.

Although the first portion 63 and the second portion 64 are integrally formed in one coil spring 30, the first portion 63 and the second portion 64 are divided by the intermediate sheet 33 at the bent portion 65, so that the first portion 63 and the second portion 64 are connected in series in the rotational direction. It is another working spring part. The first and second spring seats 31 and 32 and the intermediate seat 33 are connected to the coil spring 30.
And is made of, for example, resin or the like. The first and second spring seats 31 and 32 and the intermediate seat 33 have substantially the same axial dimension as the coil spring 30. That is, the first and second spring seats 31 and 32 and the intermediate seat 33 protrude from the window holes 9 of the plates 6 and 7 in the axial direction.

First and second spring seats 31, 32
As shown in FIG. 7 to FIG. 9, the head includes a receiving portion 41, an outer peripheral side supporting portion 42, an inner peripheral side supporting portion 43, and a projecting portion 44. The receiving portion 41 is a substantially rectangular plate-like portion as shown in FIG. The outer peripheral side supporting portion 42 includes a receiving portion 41
And has a peripheral surface 42a along the shape of the coil spring 30 on the inner peripheral side thereof. The inner peripheral side support portion 43 has a shape protruding inward in the rotation direction from the receiving portion 41, and has a peripheral surface 43a on the outer peripheral side that is a smooth curved surface that matches the shape of the coil. The protruding portion 44 is a substantially columnar portion protruding inward in the rotation direction from the center portion of the receiving portion 41. Projection 44
Has a cylindrical portion and a frustoconical portion further extending from the cylindrical portion. The tip of the truncated cone is a flat stopper surface.

With the above configuration, the receiving surface 46 inside the receiving portion 41 in the rotational direction has a substantially ring shape following the shape of the coil. Furthermore, the receiving surface 46 is configured to conform to the shape of both ends in the circumferential direction of the coil spring 30. Here, both ends of the coil spring 30 are not ground, and maintain a round or oval cross section of the element wire. Therefore, the receiving surface 46 is also a coil spring 3
It has a curved cross section along the shape of 0. Further, the receiving surface 46 gradually increases from a part thereof in the counterclockwise direction in FIG. As a result, an end face 47 facing counterclockwise is formed at the boundary between the lowest part and the highest part. The tip cross section of the coil spring 30 is in contact with the end face 47, and therefore, the coil spring 30 cannot be rotated clockwise in FIG. 7 with respect to the spring seats 31, 32. As described above, the end turn of the coil spring 30 is non-grinded,
Breakage and the like hardly occur, and the manufacturing cost is also reduced.

A flat contact surface 48 is formed on the side of the receiving portion 41 opposite to the receiving surface 46. The contact surface 48 is the window hole 19
And the rotating edge 13 of the window hole 9. In this state, the radially outer surface of the outer peripheral side support portion 42 contacts the outer peripheral edges 12 and 22, and the inner peripheral side support portion 43.
Radially inward faces of the inner peripheral edges 11 and 21.
In this state, the spring seats 31 and 32 are connected to the window holes 9 and 1.
9 cannot rotate around the spring center axis of the coil spring 30.

Next, the intermediate sheet 33 will be described.
FIGS. 10 to 12 show the structure of the intermediate sheet 33, and FIGS. 13 and 14 show the engagement state between the intermediate sheet and the coil spring 30. The intermediate sheet 33 is a member inserted into the bent portion 65 of the coil spring 30 from the outer peripheral side. The intermediate sheet 33 includes a receiving portion 50, an outer peripheral side supporting portion 51, and a projecting portion 52. The receiving portion 50 has a generally wedge shape in plan view, in other words, a shape in which the circumferential width decreases toward the inner peripheral side. The receiving part 50 is the bent part 6
5 is a portion for supporting the end of the first portion 63 and the end of the second portion 64 in the rotation direction.

The outer peripheral side supporting portion 51 extends from the outer peripheral side portion of the receiving portion 50 to both sides in the circumferential direction. Peripheral support 51
Has an outer peripheral surface 56 that is straight in the axial direction but is smoothly curved along the rotational direction. Further, the outer peripheral side support portion 51 has an inner peripheral surface 60 that is curved in the axial direction so as to conform to the shape of the coil of the coil spring. The protruding portions 52 are columnar portions formed on both sides of the receiving portion 50 in the rotation direction. As a result, a substantially ring-shaped receiving surface 5 conforming to the shape of the coil is provided on both circumferential sides of the receiving portion 50.
5 are formed. Further, a concave portion 58 is formed on the outer peripheral side portion of the receiving portion 50 on both sides in the axial direction. The shape of the concave portion 58 in a plan view is a shape in which the width in the rotation direction gradually decreases from the outer peripheral side to the inner peripheral side.

As shown in FIG. 13, the coil spring 3
0, the end portion of the first portion 63 and the second portion 6
4 are in contact with and supported by the receiving surfaces 55, respectively. The protrusion 52 extends into the end of the first portion 63 and the end of the second portion 64. As shown in FIG. 14, the radially outer portion 71 at the circumferential end of the first portion 63 abuts against the receiving surface 55 from the rotating direction, and the radially outer portion 72 at the circumferential end of the second portion 64 is It is in contact with the receiving surface 55 from the rotation direction. The first radially inner portion 73 of the coil formed between the radially outer portions 71 and 72 of the two coils is located near the inner peripheral end of the receiving portion 50. Note that the first radially inner portion 73 is not twisted when the spring is compressed because the radially outer portions 71 and 72 are inaccessible by the intermediate sheet 33.

Further, in the bent portion 65, the second and third radially inner portions 74, 75 provided on both sides of the first radially inner portion 73 are both formed with respect to the first radially inner portion 73. It is inaccessible during spring compression.
Specifically, the second and third radially inner portions 74, 75
Are in close contact with the first radially inner portion 73 in the rotational direction. As a result, both the radially outer portion 71 at the end of the first portion 63 and the radially outer portion 72 at the circumferential end of the second portion 64 are not twisted during spring compression. That is, by making the radially inner portions inaccessible to each other in the bent portion 65, the effective number of turns in the radially outer portion is reduced.

As a result, the first and second portions 63, 64
, The effective number of turns on the radially outer side is 11, but the effective number of turns on the radially inner side is 12. In other words, in each of the portions 63 and 64, the effective number of turns on the inner side in the radial direction is one more than the effective number of turns on the outer side in the radial direction. Regarding the feature of the present invention in which the effective number of turns can be set as described above, further, paragraphs (1) to (1)
This will be described in detail according to (4).

(1) First, the effective number of turns in the radially outer portion of the coil of the coil spring 30 is set to 24, and the effective number of turns in the radially inner portion is set to 25. Do one more for each part. Further, by stopping the coil spring 30 from rotating with respect to the first and second spring seats 31, 32, the above-mentioned state can be maintained.

(2) Next, since the radially outer portions 71 and 72 of the bent portion 65 are in contact with the intermediate sheet 33, the first radially inner portion 73 is not twisted in the rotational direction. The number of effective turns on the inner side in the radial direction is reduced as compared with the case where no coil is provided. (3) However, by bringing the first radially inner portion 73 and the second radially inner portion 74 into close contact in the rotational direction, the first
The radially outer portion 71 of the portion 63 is not twisted in the rotational direction. That is, the number of effective turns on the radially outer side of the first portion 63 is reduced.

(4) Further, the first radially inner portion 73
The radially outer portion 72 of the second portion 64 is prevented from being twisted in the rotational direction by bringing the radially outer portion 72 of the second portion 64 into close contact with the third radially inner portion 75 in the rotational direction. That is, the number of effective turns on the radially outer side of the second portion 64 is reduced. Connecting members 26, 2
7 is between the first plate 6 and the first rotating member 2 in the axial direction,
And an annular plate member disposed axially between the second plate 7 and the second rotating member 3. Connecting members 26, 2
7 includes an annular portion 37 and a pair of engaging claws 38 extending radially inward from the inner peripheral edge of the annular portion 37. Annular part 3
7 is located between the annular portion 14 and the annular portion 34 in the axial direction. The pair of engaging claws 38 are provided at positions facing each other in the radial direction. The engaging claw portions 38 are press-fitted into the concave portions 58 of the intermediate sheet 33 from both axial sides.
As a result, the intermediate sheet 33 rotates integrally with the connecting members 26 and 27. In addition, the intermediate sheet 33 and the connecting members 26 and 27 may be one member integrally formed. Further, the pair of intermediate sheets 33 is connected to the connecting member 2.
By being connected to each other by 6, 27, a radially outward force acting from the coil spring 30 is balanced with each other. Therefore, the intermediate sheet 33 is formed on the outer peripheral edge 12 of the window hole 9 and the outer peripheral edge
It is possible to maintain a state where a gap is provided in the radial direction with respect to 2, that is, it is difficult to slide.

Further, since the connecting members 26 and 27 are arranged between the plates 6 and 7 in the axial direction, the axial size of the damper mechanism 1 can be shortened without increasing the radial size. In addition, the pair of coil spring assemblies 24 and 25 includes a first rotating member 2 and a second rotating member 3.
, Are positioned in the axial direction via connecting members 26 and 27. Specifically, the connecting members 26 and 27 are disposed between the first rotating member 2 and the plate 6 in the axial direction and between the first rotating member 2 and the plate 7 in the axial direction. Abut on both sides in the axial direction. As described above, since the pair of coil spring assemblies 24 and 25 are axially supported inside the plates 6 and 7 in the axial direction, the pair of coil spring assemblies 2 and 25 are supported.
There is no need to dispose a supporting member outside the axial direction of the coil springs 4 and 25, and the pair of coil spring assemblies 24 and 25 are exposed in the damper mechanism 1 in the axial direction. As a result, the axial dimensions of the coil spring assemblies 24 and 25 and thus the coil diameter of the coil spring 30 can be made sufficiently large within the limited axial space. This means that the torsional vibration damping function is improved by lowering the rigidity of the coil spring 30. Further, the plates 6 and 7 can be arranged on the innermost side in the axial direction so that the axial distance between them can be reduced.
And second spring seats 31, 32 and intermediate seat 3
3 is located further axially inward than the axially outer edge portion.

Next, a plan view of FIG. 1 and FIG.
The torsional operation of the damper mechanism 1 will be described using the torsional characteristic diagram of FIG. The second rotating member 3 is twisted in the rotation direction R2 with respect to the first rotating member 2 fixed from the neutral state in FIG. First and second coil spring assemblies 2
The coil springs 30 at 4 and 25 are compressed in the rotation direction between the rotation direction edge 13 of the window hole 9 on the rotation direction R1 side and the rotation direction edge 23 of the window hole 19 on the R2 side. At this time, since the effective number of turns on the radially outer side is smaller than the effective number of turns on the radially inner side in each of the first portion 63 and the second portion 64, the stress generated in one turn in the radially inner portion and the one turn in the radially outer portion are generated. The difference between the stress and the applied stress.
Thus, the bias in the stress generated in each radially outer portion and each radially outer portion of the coil of the coil spring 30 is reduced.

When the torsion angle reaches 60 degrees, as shown in FIG. 15, the coils of the coil spring 30 come into close contact with each other, and the relative rotation stops. At this time, both the first portion 63 and the second portion 64 of the coil spring 30 are in a parallel compressed state in which the inner peripheral portion and the outer peripheral portion are uniformly compressed, and all the coils are in close contact with each other. That is, bending stress is less likely to act on the portions 63 and 64 of the coil spring 30, and the life of the coil spring 30 is extended. Further, the coil spring 30 can generate a sufficiently large load by the parallel compression.

It should be noted that the pin 8 and the projection 20 are not used as the stopper mechanism without using the coil spring assemblies 24 and 25.
May be used, or both may be combined. Such parallel compression is made possible by (1) each part 63, 6
4 extend substantially linearly, and (2) the intermediate sheet 33 fully supports the ends of the portions 63 and 64 not only radially outward but also radially outward.
That is, the posture of the 3, 64 during compression is stable. [Other Embodiments] A coil spring assembly 81 shown in FIG. 17 includes a coil spring 82, two spring seats 83, and two intermediate seats 84 and 85. The coil spring 82 has three generally linear portions, a first portion 87, a second portion 88, and a third portion 89. The first portion 87 and the second portion 88 have a first
A bent portion 91 is formed, and a V-shaped portion opened on the inner peripheral side is formed. The first bent sheet 91 has a first intermediate sheet 84.
Is arranged. Further, the second portion 88 and the third portion 89
A second bent portion 92 is formed between the two, and a V-shaped portion opened to the inner peripheral side is formed. The second bent portion 92 has a second
An intermediate sheet 85 is arranged. Also, the first portion 87
A spring seat 83 is provided at an end of the spring seat 83. Further, a spring seat 83 is disposed at an end of the third portion 89.

The relationship between the coil spring 82, the two spring seats 83, and the two intermediate seats 84, 85 is the same as in the above embodiment. Therefore, each bent portion 9
In Nos. 1 and 92, the radially inner portions of the plurality of coils are in close contact with each other in the rotational direction, and the same effects as in the above embodiment can be obtained. In the first coil spring assembly 24 shown in FIG. 18, the first portion 63 of the coil spring 30 is shorter than the second portion 64. That is, the bent portion 65
Are formed at an angle θ shifted from the center position in the rotation direction of the coil spring 30 toward the rotation direction R1. As a result, the first portion 63 (the portion of the damper mechanism 1 on the rotation direction side) is
The spring constant is larger than the portion 64 (the portion on the opposite side of the rotation direction of the damper mechanism 1). The point where the intermediate sheet 33 is provided in the bent portion 65 and the state of the coil in the bent portion 65 are the same as those in the above-described embodiment.

As described above, in the coil spring 30 of the present embodiment, by providing a portion having higher rigidity than the coil spring of the above embodiment, the intermediate sheet 3 is provided.
Even when a problem occurs in which the intermediate sheet 3 comes into close contact with another member, the close contact of the intermediate sheet 33 can be released by the urging force of the highly rigid spring portion.

[0050]

In the coil spring assembly according to the present invention, since the radial inner portions of the plurality of coils in the bent portion are restricted from approaching each other in the rotational direction with respect to each other, the coil spring assembly is located between the radial inner portions. The torsion is less likely to occur in the radially outer portion formed when the spring is compressed. That is, in the above structure, the effective number of turns on the radially outer side of the coil spring is reduced as compared with the related art. As a result, the difference between the stress generated at each radially inner portion and the stress generated at each radially outer portion during spring compression is reduced.

[Brief description of the drawings]

FIG. 1 is a plan view of a damper mechanism as one embodiment of the present invention.

FIG. 2 is a sectional view taken along line II-II of FIG.

FIG. 3 is a sectional view taken along line O-III of FIG. 1;

FIG. 4 is a plan view of a plate.

FIG. 5 is a plan view of a first rotating member.

FIG. 6 is a plan view of an intermediate connecting member.

FIG. 7 is a front view of a spring seat.

FIG. 8 is a sectional view of a spring seat.

FIG. 9 is a perspective view of a spring seat.

FIG. 10 is a side view of the intermediate sheet.

FIG. 11 is a plan view in which a cross section is partially formed in the intermediate sheet.

FIG. 12 is a perspective view of an intermediate sheet.

FIG. 13 is a partial plan view showing an engaged state between the intermediate seat and the coil spring.

FIG. 14 is a cross-sectional view showing an engaged state between the intermediate seat and the coil spring.

FIG. 15 is a plan view for explaining a twisting operation of the damper mechanism.

FIG. 16 is a positive-side torsional characteristic diagram of the damper mechanism.

FIG. 17 is a plan view of a spring assembly according to another embodiment.

FIG. 18 is a plan view of a damper mechanism according to another embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Damper mechanism 2 1st rotating member 3 2nd rotating member 4 Coil spring assembly 24 1st coil spring assembly 25 2nd coil spring assembly 30 Coil spring 33 Intermediate sheet 63 1st part 64 2nd part 65 Bending part

Claims (12)

[Claims] 1. A coil spring assembly for compressing in a rotational direction when relative rotation occurs in a damper mechanism, the coil spring assembly comprising a plurality of coils extending in a rotational direction, the first rotating member and the second rotating member. A coil spring including a first portion, a second portion, and a boundary portion formed between the first portion and the second portion and a boundary portion formed between the two portions. A coil spring assembly wherein the radially inner portions are restricted in rotational access to each other. 2. The coil spring assembly according to claim 1, wherein radially inner portions of the plurality of coils at the boundary portion are in close rotational contact with each other. 3. An intermediate sheet disposed at the boundary of the coil spring and having a receiving portion for receiving at least a radially outer portion of the end surface of the first portion and the end surface of the second portion. The coil spring assembly according to claim 1. 4. The coil spring assembly according to claim 3, wherein said receiving portion entirely receives an end surface of said first portion and an end surface of said second portion. 5. The radial inner portion of the plurality of coils at the boundary portion includes a first radial inner portion between two radial outer portions supported by the intermediate sheet, and a radial inner portion of the radial inner portion. The coil spring assembly according to claim 3 or 4, comprising at least one second radially inner portion in the rotation direction. 6. A radially inner portion of the plurality of coils at the boundary portion includes a first radially inner portion between two radially outer portions supported by the intermediate sheet, and a radially inner portion of the radially inner portion. The coil spring assembly according to claim 3 or 4, comprising a second and a third radially inner portion on both sides in the rotational direction. 7. The coil spring assembly according to claim 3, wherein said coil spring has a plurality of boundaries, and said intermediate sheet is provided for each of said boundaries. And a pair of spring seats supporting both ends of the coil spring and supported by the first rotating member and the second rotating member, wherein each of the spring seats rotates the coil spring about a spring center axis. The coil spring assembly according to claim 1, wherein the coil spring assembly is non-rotatably supported. 9. The effective number of turns on the radially inner side of the first portion is greater than the effective number of turns on the radially outer side, and the effective number of turns on the radially inner side of the second portion is greater than the effective number of turns on the radially outer side. The coil spring assembly according to any one of claims 1 to 8. 10. The first portion and the second portion extend substantially linearly and bend at the boundary to form a V-shaped portion that opens toward the center of rotation of the damper mechanism.
10. The coil spring assembly according to any one of claims 9 to 9. 11. The coil spring assembly according to claim 10, wherein the coil spring forms the V-shaped portion in a free state before being mounted on the damper mechanism. 12. A first rotating member, a second rotating member disposed so as to be rotatable relative to the first rotating member, and the coil spring assembly according to claim 1. A damper mechanism, comprising: a plurality of the coil spring assemblies; and a connecting member that connects the plurality of intermediate sheets to each other.