JP2005048875A - Spring assembly - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide spring assembly capable of reducing wear of a coil spring and providing stable performance of the coil spring. <P>SOLUTION: This spring assembly 5 has a first coil spring 51, a second coil spring 52, a pair of spring seats 53, and a support member 54. Free length of the second coil spring 52 is set to be shorter than that of the first coil spring 51, and the second coil spring 52 is arranged in an inner peripheral part of the first coil spring 51. The pair of spring seats 53 are arranged by opposing to both ends of the first coil spring 51. The pair of spring seats 53 has a support part 53a, an engaging part 53b, and a through hole 53c. The support member 54 is inserted into an inner peripheral part of the second coil spring 52 and its both end parts are slidably engaged with a pair of through holes 53c. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a spring assembly, and more particularly to a spring assembly that is compressed in a rotational direction when at least two members of a torsional vibration damper rotate relative to each other.

  A damper assembly such as a clutch disk assembly of a vehicle, a flywheel assembly, or a lock-up clutch of a torque converter is provided with a spring assembly for absorbing torsional vibration. The spring assembly is arranged to elastically connect the input side rotating member and the output side rotating member in the circumferential direction. The spring assembly is compressed in the rotational direction between the two members when the input-side rotating member and the output-side rotating member rotate relative to each other. By using such a spring assembly and a frictional resistance generating part that generates a frictional resistance at the time of relative rotation, the torsional vibration input to the input side rotating member is absorbed and damped.

  The spring assembly includes, for example, a first coil spring, a second coil spring, and a pair of spring seats. The second coil spring is disposed on the inner periphery of the first coil spring. In this second coil spring, the free length may be set shorter than the first coil spring. At this time, in a state where the input side rotating member and the output side rotating member are not rotating relative to each other, the second coil spring is movable in the rotation direction on the inner peripheral portion of the first coil spring. The pair of spring seats are disposed opposite to both ends of the first coil spring. The pair of spring seats has a support portion and an engagement portion. The support part can support both ends of the first coil spring. The engaging portion is provided on the support portion, and can be engaged with the inner peripheral portion of the first coil spring and can be brought into contact with both ends of the second coil spring.

  In such a spring assembly, when the input side rotation member and the output side rotation member start relative rotation, the first coil spring is compressed by the support portion of the spring seat. When the relative rotation between the input side rotation member and the output side rotation member is further increased, the second coil spring is also compressed by the engagement portion of the spring seat while the first coil spring is compressed by the support portion.

  In the conventional spring assembly, when the input-side rotating member and the output-side rotating member start relative rotation, the second coil spring disposed on the inner peripheral portion of the first coil spring is moved by the centrifugal force of the first coil spring. Repeat contact or slide on the inner and outer sides. Then, depending on the situation, the second coil spring may enter between the strands of the first coil spring, or the inner periphery of the first coil spring or the outer periphery of the second coil spring may be worn. In addition, when the relative rotation between the input side rotation member and the output side rotation member is further increased and the second coil spring is compressed, the second coil spring is in contact with the inner periphery of the first coil spring. Since the second coil spring expands and contracts, the wear of the first and second coil springs may be further promoted. In particular, when the second coil spring is compressed while the second coil spring repeats contact outside the inner periphery of the first coil spring, the track on which the second coil spring operates is not stable. There may be variations in the performance of the coil spring. As described above, when the performance of the second coil spring varies, it becomes difficult to stably exhibit the performance of not only the second coil spring but also the entire first and second coil springs.

  SUMMARY OF THE INVENTION An object of the present invention is to reduce the wear of a coil spring and to stably exhibit the performance of the coil spring in a spring assembly.

  The spring assembly according to claim 1 is a spring assembly that is compressed in the rotational direction when at least two members of the torsional vibration damper rotate relative to each other, the first coil spring, the second coil spring, A pair of spring seats and a support member are provided. The second coil spring is set to have a shorter free length than the first coil spring, and is disposed on the inner periphery of the first coil spring. The pair of spring seats are disposed opposite to both ends of the first coil spring. The pair of spring seats includes a support portion, an engagement portion, and a through hole. The support part supports both ends of the first coil spring. The engaging part is provided in the support part and is engaged with the inner peripheral part of the first coil spring. The through hole is formed through the engaging portion in the rotation direction. The support member is inserted through the inner peripheral portion of the second coil spring, and both end portions are slidably engaged with the pair of through holes.

  In this spring assembly, when at least two members of the torsional vibration damper start relative rotation, the end of the support member slides through the through hole of the spring seat, and the support portion of the pair of spring seats is the first coil spring. The first coil spring is compressed by pressing both ends. At this time, the engaging portions of the pair of spring seats are engaged with the inner peripheral portion of the first coil spring. When the relative rotation of the at least two members of the torsional vibration damper is further increased, the first coil spring is compressed, and the engaging portion of the pair of spring seats is disposed on the inner peripheral portion of the first coil spring. Compress the coil spring. Also at this time, the end portion of the support member slides through the through hole of the spring seat.

  Here, the engaging portions of the pair of spring seats are engaged with the inner peripheral portion of the first coil spring, and the support member is inserted through the inner peripheral portion of the second coil spring, so that both ends of the support member are paired with the pair of spring seats. Since it is slidably engaged with the through hole of the spring seat, the track on which the first and second coil springs can be stabilized by the spring seat and the support member. As described above, since the track on which the first coil spring operates is ensured and the track on which the second coil spring operates is also stably maintained, the second coil disposed on the inner peripheral portion of the first coil spring. The spring is less likely to contact the outer periphery of the first coil spring. Thereby, the abrasion which may arise between a 1st coil spring and a 2nd coil spring can be reduced. In this state, since the first and second coil springs are compressed by the pair of spring seats, the performance of the first and second coil springs can be stably exhibited.

  A spring assembly according to a second aspect is the spring assembly according to the first aspect, wherein the engaging portion is formed in a circular convex shape having a smaller diameter than the inner diameter of the first coil spring. In this spring assembly, since the engaging portion is formed in a circular convex shape having a diameter smaller than the inner diameter of the first coil spring, the engaging portion is easily positioned and engaged with the inner peripheral portion of the first coil spring. be able to.

  According to a third aspect of the present invention, in the second aspect, the outer diameter of the engaging portion is larger than the outer diameter of the second coil spring. In this spring assembly, since the outer diameter of the engaging portion is larger than the outer diameter of the second coil spring, the outer periphery of the second coil spring is less likely to contact the inner periphery of the first coil spring. As a result, the inner periphery of the first coil spring and the outer periphery of the second coil spring are less likely to wear.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, the contact surface is formed at the tips of the pair of engaging portions. Then, in a state where at least two members of the torsional vibration damper are relatively rotated and the pair of contact surfaces are in contact with both ends of the second coil spring, the pair of contact surfaces are formed to be substantially parallel to each other. ing. In this spring assembly, the pair of contact surfaces are formed so as to be substantially parallel to each other in a state where the pair of contact surfaces are in contact with both ends of the second coil spring. When the is pressed by the pair of contact surfaces, the second coil spring can be compressed in a stable state.

  According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the through hole is provided with a sliding portion and a clearance portion. The sliding portion is formed on the second coil spring side and slides along the support member. The clearance portion is formed to expand from the sliding portion toward the support portion side of the spring seat. In this spring assembly, since the support member is slid by the sliding portion so that both ends of the support member do not contact the clearance portion, the support member and the spring seat can be stably operated.

  According to a sixth aspect of the present invention, in any one of the first to fifth aspects, the support member presses the inner periphery of the second coil spring. In this spring assembly, since the support member presses the inner periphery of the second coil spring, it is possible to make it difficult to move the second coil spring in the rotational direction. As a result, the inner periphery of the first coil spring and the outer periphery of the second coil spring are less likely to wear. In addition, since the support member presses the inner periphery of the second coil spring, when the second coil spring is compressed, a sliding resistance is generated between the support member and the second coil spring. The vibration damping effect due to the sliding resistance can be expected.

  A spring assembly according to a seventh aspect is the spring assembly according to the sixth aspect, wherein the support member is a spring pin formed in a C-shaped cylindrical shape. In this spring assembly, since the support member is formed of a spring pin formed in a C-shaped cylindrical shape, the support member can stably maintain the track on which the second coil spring operates, but the second coil spring can be stably operated. The inner circumference can also be pressed simultaneously.

  According to an eighth aspect of the present invention, in any one of the first to seventh aspects, a pair of seating surfaces are formed at both ends of the first and second coil springs. Further, the pair of seating surfaces are processed so as to be parallel to each other in a state where at least two members of the torsional vibration damper are not relatively rotated. In this spring assembly, the pair of seating surfaces formed at both ends of the first and second coil springs are parallel to each other in a state where at least two members of the torsional vibration damper are not rotating relative to each other. Has been ground. Thereby, when relative rotation occurs and the seating surfaces of the first and second coil springs are pressed by the spring seat, the first and second coil springs can be compressed in a stable state.

  In the spring assembly according to the present invention, the wear of the coil spring can be reduced and the performance of the coil spring can be exhibited stably.

[Configuration of clutch disk assembly]
A clutch disk assembly 1 according to an embodiment of the present invention is shown in FIGS. The clutch disk assembly 1 is used for a vehicle clutch, and a flywheel (not shown) is disposed on the left side (axial engine side) of the clutch disk assembly 1 in FIG. A transmission (not shown) is arranged on the side. 1 is the rotational axis of the clutch disc assembly 1, R1 in FIG. 2 is the direction of rotation of the flywheel and clutch disc assembly 1, and R2 is the opposite direction. The clutch disc assembly 1 shown in FIG. 1 is a cross-sectional view taken along line O-I in FIG. 2 at the upper half and a cross-sectional view taken along line O-II in the lower half.

  As shown in FIG. 1, the clutch disk assembly 1 mainly includes an input side rotating member 3 including a clutch disk 2, a clutch plate 6 and a retaining plate 7, and an output side rotation including a hub flange 8 and an output hub 9. It comprises a member 4, a spring assembly 5 that couples the input side and output side rotating members 3 and 4 in the rotational direction, and a frictional resistance generating part 13 that generates a frictional resistance during relative rotation.

  As shown in FIG. 1, the clutch disk 2 is pressed against the friction surface of the flyhole to transmit the torque on the engine side, and the friction facing 11 attached to both sides of the cushioning plate 10 and the cushioning plate 10. And have.

  The clutch plate 6 is a steel plate member formed in an annular shape. As shown in FIG. 1, the clutch plate 6 is drawn by being inflated toward the axial engine side in the circumferential direction. The clutch plate 6 is positioned in the radial direction so as to be coaxial with the output hub 9 and is rotatably supported on the outer peripheral surface of the end portion on the axial direction engine side of the output hub 9 at the inner peripheral portion. A friction facing 11 is fixed to the outer peripheral portion of the clutch plate 6 by a plurality of rivets 14 via a cushioning plate 10. On the other hand, a plurality of first window holes 6a are formed in the clutch plate 6 at a predetermined interval in the rotational direction at the intermediate portion in the radial direction. A holding portion 19 is provided at the circumferential end of the first window hole 6a. The spring assembly 5 is disposed inside the first window hole 6 a, and the spring assembly 5 is supported by the holding portion 19.

  Similar to the clutch plate 6, the retaining plate 7 is a steel plate formed in an annular shape. As shown in FIG. 1, the retaining plate 7 is drawn by being expanded toward the axial transmission side. The retaining plate 7 is disposed to face the clutch plate 6, and a predetermined interval is provided in the axial direction between the retaining plate 7 and the clutch plate 6. Further, the retaining plate 7 is disposed in the inner peripheral portion with a gap from the outer peripheral surface of the end portion on the axial transmission side of the output hub 9. In this state, the retaining plate 7 is fixed to the clutch plate 6 by a plurality of stop pins 15 arranged at predetermined intervals in the circumferential direction. Thereby, the clutch plate 6 and the retaining plate 7 can rotate integrally. On the other hand, in the retaining plate 7, second window holes 7 a are formed at positions corresponding to the plurality of first window holes 6 a formed in the clutch plate 6 in the intermediate portion in the radial direction. A holding portion 23 is provided at the circumferential end of the second window hole 7a. And the spring assembly 5 is arrange | positioned inside the 2nd window hole 7a, and this spring assembly 5 is supported by the holding | maintenance part 23. As shown in FIG.

  The hub flange 8 is a steel plate member formed in an annular shape. As shown in FIGS. 1 and 2, the hub flange 8 is formed with a plurality of notches 20 opened outward in the outer peripheral portion. The stop pin 15 passes through the notch 20 in the axial direction. The hub flange 8 is formed with a plurality of inner peripheral teeth 37 at the inner peripheral portion. The hub flange 8 is disposed between the clutch plate 6 and the retaining plate 7 in the axial direction. At this time, both side surfaces of the hub flange 8 have a predetermined distance between the side surface of the clutch plate 6 on the axial transmission side and the side surface of the retaining plate 7 on the axial direction engine side. On the other hand, the hub flange 8 has third window holes 8a at positions corresponding to the plurality of first window holes 6a of the clutch plate 6 and the plurality of second window holes 7a of the retaining plate 7 in the intermediate portion in the radial direction. Is formed. And the spring assembly 5 is arrange | positioned inside the 3rd window hole 8a.

  The output hub 9 is a steel member formed in a cylindrical shape. As shown in FIGS. 1 and 2, the output hub 9 is provided on these members 6, 7, 8 so that the rotational axes of the clutch plate 6, the retaining plate 7, and the hub flange 8 are coaxial. In the center hole formed. The output hub 9 has a plurality of outer peripheral teeth 38 formed on the outer peripheral surface. When the outer peripheral teeth 38 and the inner peripheral teeth 37 of the hub flange 8 mesh with each other, the output hub 9 and the hub flange 8 can rotate together. Here, the outer peripheral teeth 38 and the inner peripheral teeth 37 are engaged with each other with a predetermined gap in the circumferential direction. As a result, the output hub 9 and the hub flange 8 can be relatively rotated by the angle of the circumferential clearance between the inner peripheral teeth 37 and the outer peripheral teeth 38. The output hub 9 has a plurality of spline holes 39 extending in the axial direction on the inner peripheral surface. The spline of the shaft extending from the transmission is engaged with the spline hole 39, so that torque can be transmitted from the output hub 9 to the transmission.

  The spring assembly 5 is compressed in the rotational direction when the clutch plate 6 and the retaining plate 7 and the hub flange 8 rotate relative to each other. As shown in FIGS. 3 and 4, the spring assembly 5 includes a first coil spring 51, a second coil spring 52, a pair of spring seats 53, and a support member 54. A pair of seating surfaces 51a and 52a are formed at both ends of the first and second coil springs 51 and 52, respectively. The pair of seating surfaces 51a and 52a are ground so as to be parallel to each other when the clutch plate 6, the retaining plate 7 and the hub flange 8 are not relatively rotated. Thereby, when the seating surfaces 51a and 52a of the first and second coil springs 51 and 52 are pressed by the spring seat 53, the first and second coil springs 51 and 52 can be compressed in a stable state. . The second coil spring 52 is set to have a shorter free length than the first coil spring 51, and is disposed on the inner peripheral portion of the first coil spring 51.

  The pair of spring seats 53 are disposed opposite to both ends of the first coil spring 51 and are in contact with the circumferential ends of the first to third window holes 6a, 7a, 8a. The pair of spring seats 53 are supported by holding portions 19 and 23 formed in the first and second window holes 6a and 7a.

  The pair of spring seats 53 includes a support portion 53a, an engagement portion 53b, and a through hole 53c. The support portion 53 a supports both ends of the first coil spring 51. The engaging portion 53 b is provided so as to protrude from the support portion 53 a in the compression direction of the first coil spring 51, and is formed in a columnar shape having a smaller diameter than the inner diameter of the first coil spring 51. By forming the engaging portion 53 b in this way, the engaging portion 53 b can be easily positioned and engaged with the inner peripheral portion of the first coil spring 51. Further, the outer diameter of the engaging portion 53 b is formed to be larger than the outer diameter of the second coil spring 52. Thereby, the outer periphery of the second coil spring 52 is less likely to contact the inner periphery of the first coil spring 51, and the inner periphery of the first coil spring 51 and the outer periphery of the second coil spring 52 are less likely to wear. The outer peripheral edge 53f of the engaging portion 53b is chamfered. Such an engaging portion 53 b can be engaged with the inner peripheral portion of the first coil spring 51 at the outer peripheral surface.

  The tip of the engaging portion 53 b can come into contact with the second coil spring 52. A contact surface 53d is formed at the tip of the engaging portion 53b. The contact surface 53d is formed so as to incline from the inner peripheral part outer side of the first coil spring 51 toward the inner peripheral part inner side. That is, as shown in FIG. 4, the contact surface 53d is in contact with both ends of the second coil spring 52 with the clutch plate 6, the retaining plate 7 and the hub flange 8 rotating relative to each other. The surfaces 53d are formed so as to be substantially parallel to each other. Thereby, when both ends of the second coil spring 52 are pressed by the pair of contact surfaces 53d, the second coil spring 52 can be compressed in a stable state.

  The through hole 53c is formed through the engaging portion 53b in the rotation direction. The through hole 53c is provided with a sliding part 53g and a clearance part 53h. The sliding portion 53g is formed in an annular shape so as to protrude toward the inner peripheral portion of the through hole 53c on the second coil spring 52 side of the through hole 53c. The sliding portion 53g has a chamfered inner peripheral edge 53i on the second coil spring 52 side. The sliding portion 53g slides along a support member 54 described later. The clearance portion 53h is formed from the sliding portion 53g toward the support portion 53a side of the spring seat 53. Moreover, the clearance part 53h is formed so that an internal diameter may become larger than the internal diameter of the sliding part 53g. By forming the through hole 53c in this manner, a support member 54 described later slides on the sliding portion 53g so that both ends of the support member 54 do not contact the clearance portion 53h.

  The support member 54 is inserted into the inner peripheral portion of the second coil spring 52, and both end portions are slidably engaged with the pair of through holes 53c. Specifically, the support member 54 is formed of a spring pin formed in a C-shaped cylindrical shape, and presses the inner periphery of the second coil spring 52 in the radial direction. As a result, the second coil spring 52 is less likely to move in the rotational direction, and the inner periphery of the first coil spring 51 and the outer periphery of the second coil spring 52 are less likely to wear. Further, since a sliding resistance is generated between the support member 54 and the second coil spring 52, it is possible to expect a vibration damping effect due to the sliding resistance. Here, in a state where the clutch plate 6 and the retaining plate 7 and the hub flange 8 are not rotated relative to each other, the support member 54 is positioned so that both ends of the support member 54 are located in the clearance portion 53 h of the pair of spring seats 53. Is set to be shorter than the length between the end portions in the circumferential direction of the window holes 6a, 7a, 8a.

  As shown in FIG. 1, the frictional resistance generator 13 is disposed on the inner peripheral side of both side surfaces of the hub flange 8. By engaging the frictional resistance generator 13 with the side surface of the clutch plate 6 on the axial transmission side and the side surface of the retaining plate 7 on the axial direction engine side, frictional resistance is generated during relative rotation. .

[Operation of clutch disk assembly and spring assembly]
The operation of the clutch disk assembly 1 when torque from the engine is input to the clutch disk assembly 1 will be described. When torque is input to the clutch disc assembly 1 (R1 direction), the torque is transmitted from the friction surface of the flywheel to the friction facing 11 of the clutch disc 2, and is transmitted to the clutch plate 6 via the cushioning plate 10. ing. At this time, the clutch plate 6 and the retaining plate 7 are twisted with respect to the hub flange 8 at a twist angle (C1) corresponding to the magnitude of torque. The spring assembly 5 is compressed in the rotational direction in accordance with the magnitude of the twist angle (C1). In such a state, the output hub 9 engaged with the hub flange 8 is rotating. In this way, the torque input to the clutch disk assembly 1 is transmitted to the transmission.

  When torque is changed and torsional vibration is generated in the clutch disk assembly 1, the constant twist angle (C 1) maintained between the clutch plate 6 and the retaining plate 7 and the hub flange 8 is changed. . Due to this variation, the clutch plate 6 and the retaining plate 7 repeatedly rotate relative to the hub flange 8. At this time, the spring assembly 5 repeatedly expands and contracts in accordance with the magnitude of the fluctuation generated in the twist angle (C1) while being compressed in the rotational direction. A frictional resistance is generated in the frictional resistance generating unit 13. As described above, the torsional vibration generated in the clutch disk assembly 1 is absorbed and damped by the spring assembly 5 and the frictional resistance generator 13.

  The torsional characteristics of the clutch disk assembly 1 and the spring assembly 5 that operate in this manner will be described in correspondence with changes in the torsion angle. From the initial mounting state shown in FIG. 3, the clutch plate 6 and the retaining plate 7 are twisted with respect to the hub flange 8 in the R1 direction. Then, the spring assembly 5 is compressed in the rotation direction. In a range where the twist angle is small, the first coil spring 51 is compressed in the rotational direction between the support portion 53a of the spring seat 53 on the rotational direction R1 side and the support portion 53a of the spring seat 53 on the rotational direction R2 side. . The support member 54 slides at the sliding portion 53g so that the end portion does not contact the clearance portion in the through hole 53c of the spring seat 53. At this time, the second coil spring 52 is not compressed and is in a state where the inner periphery is only pressed in the radial direction by the support member 54. Thus, in the state where the first coil spring 51 is compressed, the torsional rigidity of the spring assembly 5 is kept relatively low. At this time, the frictional resistance generator 13 generates a frictional resistance between the clutch plate 6 and the retaining plate 7 and the hub flange 8.

  On the other hand, in the range where the torsion angle is large, as shown in FIG. 4, the contact surfaces 53 d formed on the engaging portions 53 b of the pair of spring seats 53 abut both ends of the second coil spring 52, and The two coil spring 52 is compressed together with the first coil spring 51. A sliding resistance is generated between the second coil spring 52 and the support member 54. Also at this time, the support member 54 slides at the sliding portion 53g so that the end portion does not contact the clearance portion in the through hole 53c of the spring seat 53. Thus, when the 1st and 2nd coil springs 51 and 52 are compressed simultaneously, the torsional rigidity of the spring assembly 5 becomes comparatively high. At this time, the frictional resistance generator 13 generates a frictional resistance between the clutch plate 6 and the retaining plate 7 and the hub flange 8.

  In the conventional clutch disk assembly 1, the spring assembly 5 has a small twist angle, and the second coil spring 52 disposed on the inner peripheral portion of the first coil spring 51 is subjected to centrifugal force by the first coil spring 51. Repeat contact and slide on the inner and outer sides of the. Then, depending on the situation, the second coil spring 52 may enter between the strands of the first coil spring 51, or the inner circumference of the first coil spring 51 and the outer circumference of the second coil spring 52 may be worn. Further, when the second coil spring 52 is compressed in a range where the torsion angle is large, when the second coil spring 52 expands and contracts in a state where the second coil spring 52 is in contact with the inner periphery of the first coil spring 51, There is a possibility that wear of the first and second coil springs 52 is further promoted. In particular, if the second coil spring 52 is compressed while the second coil spring 52 repeats contact outside the inner periphery of the first coil spring 51, the track on which the second coil spring 52 operates is not stable. In addition, the performance of the second coil spring 52 may vary. As described above, when the performance of the second coil spring 52 varies, it is difficult to stably exhibit the performance not only in the second coil spring 52 but also in the first and second coil springs 51 and 52 as a whole. .

  In the spring assembly 5 of the present embodiment, the engaging portions 53 b of the pair of spring seats 53 are engaged with the inner peripheral portion of the first coil spring 51, and the support member 54 is attached to the inner peripheral portion of the second coil spring 52. Since both ends of the support member 54 are slidably engaged with the through holes 53c of the pair of spring seats 53, the tracks on which the first and second coil springs 51 and 52 are operated are arranged on the spring seat. 53 and the support member 54 can be stabilized. Thus, since the track | orbit which the 2nd coil spring 52 act | operates is maintained stably after ensuring the track | orbit which the 1st coil spring 51 act | operates, it has arrange | positioned at the inner peripheral part of the 1st coil spring 51 The second coil spring 52 is less likely to contact the inner periphery of the first coil spring 51. As a result, wear that can occur between the first coil spring 51 and the second coil spring 52 can be reduced. In this state, since the first and second coil springs 51 and 52 are compressed by the pair of spring seats 53, the performance of the first and second coil springs 51 and 52 can be exhibited stably.

[Other Embodiments]
(A) In the above-described embodiment, the spring assembly 5 has been described by taking the clutch disk assembly 1 used for a vehicle clutch as an example. However, the specific structure is not limited to the above-described embodiment. The present invention can also be applied to a spring assembly used in a type of clutch disk assembly. For example, a spring assembly used for a flywheel assembly, a lock-up clutch of a torque converter, or the like may be used.

  (B) In the above embodiment, the output hub 9 and the hub flange 8 are examples of the output side rotating member 4 configured as separate members. However, the output side rotating member 4 is not limited to the above embodiment, The hub flange 8 and the output hub 9 may be configured integrally.

  (C) In the said embodiment, as shown in FIG. 3, the example in case the length of the supporting member 54 is slightly shorter than the length between the edge parts of the circumferential direction of each window hole 6a, 7a, 8a is shown. However, the length of the support member 54 is not limited to the above embodiment, and both ends of the support member 54 are a pair of springs in a state where the clutch plate 6 and the retaining plate 7 and the hub flange 8 are not relatively rotated. As long as it is located in the clearance part 53h of the sheet 53, any length may be set.

1 is a schematic longitudinal sectional view of a clutch disk assembly as one embodiment of the present invention. The top view of the said clutch disc assembly. The enlarged view before the operation | movement of the spring assembly arrange | positioned at the said clutch disc assembly. The enlarged view at the time of operation | movement of the spring assembly arrange | positioned at the said clutch disc assembly.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Clutch disc assembly 2 Clutch disc 3 Input side rotating member 4 Output side rotating member 5 Spring assembly 6 Clutch plate 7 Retaining plate 8 Hub flange 9 Output hub 13 Friction resistance generating part 51 First coil spring 52 Second coil spring 51a, 52a Seat surface 53 Spring seat 53a Support portion 53b Engagement portion 53c Through hole 53d Contact surface 53g Sliding portion 53h Clearance portion 54 Support member

Claims (8)

A spring assembly that is compressed in a rotational direction when at least two members of a torsional vibration damper rotate relative to each other;
A first coil spring;
A second coil spring having a free length set shorter than that of the first coil spring and disposed on an inner periphery of the first coil spring;
The first coil spring is disposed opposite to both ends of the first coil spring and supports the both ends of the first coil spring. The support is provided on the support and engages with the inner periphery of the first coil spring. A pair of spring seats having a joint portion and a through hole formed through the engaging portion in the rotational direction;
A support member that is inserted into the inner peripheral portion of the second coil spring and that has both end portions slidably engaged with the pair of through holes;
Spring assembly with   The spring assembly according to claim 1, wherein the engaging portion is formed in a circular convex shape having a smaller diameter than an inner diameter of the first coil spring.   The spring assembly according to claim 2, wherein an outer diameter of the engaging portion is larger than an outer diameter of the second coil spring.   A pair of contact surfaces are formed at the tips of the pair of engaging portions, and the pair of contact surfaces abut against both ends of the second coil spring when the relative rotation is performed. The spring assembly according to any one of claims 1 to 3, wherein the spring assemblies are formed so as to be substantially parallel to each other.   The through hole is formed on the second coil spring side and slides along the support member, and the diameter is increased from the slide portion toward the support portion side of the spring seat. The spring assembly according to any one of claims 1 to 4, wherein a clearance portion is provided.   The spring assembly according to any one of claims 1 to 5, wherein the support member presses an inner periphery of the second coil spring.   The spring assembly according to claim 6, wherein the support member is a spring pin formed in a C-shaped cylindrical shape.   A pair of seating surfaces are formed at both ends of the first and second coil springs, respectively, so that the pair of seating surfaces are parallel to each other when the two members are not rotating relative to each other. The spring assembly according to any one of claims 1 to 7, wherein the spring assembly is processed.

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