Torsional vibration damping device

Abstract

In a rotational variation reduction device, a first coil spring (32) having low rigidity and a second coil spring (34) having high rigidity are arranged in series between a pair of first retainers (16) and second retainers (18), which are separated in the circumferential direction and each of which is made of resin, and are arranged so as to be connected via an intermediate retainer (36). The first coil spring (32) and the intermediate retainer (36) are disposed in a bottomed recess (40) of the first retainer (16), and the intermediate retainer (36) slides radially outward with respect to the bottomed recess (40) of the first retainer (16) during deformation. The second coil spring (34) is housed in a bottomed recess (42) of the second holder (18). The damping control is performed in a low torque region with a low torsional rigidity formed by the series connection of the first coil spring (32) and the second coil spring (34), and in a common torque region with a high torsional rigidity formed separately by the second coil spring (34). The purpose of the present invention is to achieve low noise in idling operation and low abnormal noise caused by switching to resin-metal contact.

Description

Technical Field

[0001] The present invention relates to a torsional vibration damper device for damping torsional vibration of a rotating shaft of a motor by connecting a low-rigidity coil spring and a high-rigidity coil spring in series. Background Art

[0002] As a technology for obtaining a wide torsional angle range in a low-rigidity state for the purpose of reducing noise during idling, etc., a two-stage torsional vibration reduction device (torsion damper) is known in which a low-rigidity coil spring and a high-rigidity coil spring are arranged in series (Patent Documents 1 and 2). The low-rigidity coil spring and the high-rigidity coil spring are arranged in series between the rotating plate on the engine side and the rotating plate on the transmission side, and are arranged between the surfaces facing each other in the rotation direction. When the torsional angle between the input-output shaft is small, the low-rigidity coil spring and the high-rigidity coil spring act in series, and the torsional rigidity as a combined value becomes smaller, so the increase in torque corresponding to the increase in the torsional angle becomes smaller, and the increase in torsional torque can be suppressed in a wide torsional angle range.

[0003] When the operation is transferred from idling to the normal torque used for normal driving, and the torsional torque increases to the limit value (just before reaching complete crushing or adhesion), the low-rigidity coil spring is invalidated, and the high-rigidity coil spring acts alone against the torsional torque, and the increase in torsional torque relative to the torsional angle becomes more rapid than when the coil springs are connected in series.

[0004] In order to realize the above-mentioned action, in the technology of Patent Document 1, the low-rigidity coil spring is located radially inward and the high-rigidity coil spring is located radially outward, respectively. In the low torque region, the rotation of the hub on the inner diameter side is transmitted to the clutch plate via the low-rigidity coil spring, and low torsional rigidity is obtained by the series connection of the low-rigidity coil spring and the high-rigidity coil spring. In the high torque region, the low-rigidity coil spring is invalidated by restricting the rotation of the hub relative to the clutch plate, and only the high-rigidity coil spring is attenuated, thereby obtaining high torsional rigidity. The technology of Patent Document 2 is also in the low torque region, the low-rigidity coil spring and the high-rigidity coil spring are connected in series via a support plate, and in the high torque region, the low-rigidity coil spring is invalidated by locking the support plate on the input side or the output side, and the high-rigidity coil spring is operated alone. This is the same as Patent Document 1, but there is a structural difference in that the low-rigidity coil spring and the high-rigidity coil spring are located on the same circumference. Prior art literature Patent Literature

[0005] Patent Document 1: Japanese Patent Application Laid-Open No. 9-42311 Patent Document 2: Japanese Patent Application Publication No. 2015-161371 Summary of the invention Technical problem to be solved by the invention

[0006] In the prior art, the hub and / or support plate for controlling the connection between the low-rigidity coil spring and the high-rigidity coil spring are metal main body components arranged coaxially with the input-output shaft and occupying the entire circumference, occupying a considerable amount of space in the entire damping device, and requiring additional dedicated components for its installation and / or positioning in addition to the low-rigidity coil spring, which inevitably leads to the problem of increased number of components and / or increased cost due to more assembly man-hours. In addition, the inactivation of the low-rigidity coil spring when switching from the series connection of the low-rigidity coil spring and the high-rigidity coil spring to the single action of the high-rigidity coil spring depends on the engagement of the hub with the clutch plate or the engagement of the support plate with the rotating member on the input side or the output side, and the direct contact between the metals will produce a large abnormal noise.

[0007] The present invention has been made in view of the above-mentioned problems of the prior art, and an object of the present invention is to realize a damper in which a low-rigidity coil spring and a high-rigidity coil spring are connected in series with a minimum increase in parts, and to improve suitability for noise countermeasures. Technical solutions adopted to solve technical problems

[0008] The torsional vibration reduction device of the present invention comprises: an input member for rotationally connecting to the driving side; an output member having the same rotation center line as the input member and for rotationally connecting to the driven side; and an elastic body arranged in the circumferential direction between the input member and the output member; and the rotational fluctuation when the input member on the driving side drives the output member on the driven side is reduced by the circumferential elastic deformation of the elastic body.

[0009] One of the input member and the output member has a guide portion, which extends in an arc shape from the radially outer side toward the elastic body so that the rotation center line is the same as the input member and the output member. The other of the input member and the output member has a central support plate and an extension plate extending from the support plate to between adjacent elastic bodies in the circumferential direction. Each guide portion forms a locking portion extending radially inward at both ends in the circumferential direction, and each extension plate forms a pressurizing portion extending radially outward at both ends in the circumferential direction.

[0010] It also has a retainer, which is respectively arranged at both ends of the elastic body in the circumferential direction, has an axial and radial support structure for the input component and / or the output component, and can move in the circumferential direction along the guide portion. The retainer has bottomed recesses that respectively accommodate the opposite end portions of the elastic body in the circumferential direction. The retainer is arranged relative to the locking portion close to the guide portion and the pressurizing portion close to the extension plate at the pressure-receiving portion which is one end of the side separated from the bottomed recess in the circumferential direction.

[0011] The elastomer has a low-rigidity first elastic member, a high-rigidity second elastic member and an intermediate member connecting the first elastic member and the second elastic member in series at at least one end of the retainer, and the ends of the first elastic member, the intermediate member and the second elastic member close to the intermediate member are accommodated in the bottomed recess of the corresponding retainer, and the intermediate member is slidably supported by the radially opposite surface of the bottomed recess of the retainer.

[0012] In the paired retainers, the retainer located on the upstream side in the torque transmission direction abuts against the pressure-applying portion close in the circumferential direction, and moves toward the retainer located on the downstream side in the torque transmission direction and locked by the locking portion close to the guide portion. In a transmission torque area lower than the commonly used area, the retainer resists a low elastic force based on the series composite value of the elastic modulus of the first elastic member and the elastic modulus of the second elastic member, and in the commonly used transmission torque area, the retainer resists a high elastic force based on the high elastic modulus value brought by the second elastic member alone, and moves in the circumferential direction along the guide portion.

[0013] The first elastic member and the second elastic member are respectively constituted as a first coil spring and a second coil spring, and include: a first retaining portion, which retains the first coil spring without bottoming out before transferring to the second coil spring to act alone; and a second retaining portion, which retains the end of the second coil spring on the side close to the first coil spring when the retainer of the intermediate member slides during series action and individual action.

[0014] The first retaining portion may be composed of a small diameter portion and a protrusion, wherein the small diameter portion is formed in the center of the bottom surface of the bottomed concave portion of the retainer and accommodates one end of the first coil spring from the outer diameter side, and the protrusion is formed on the surface of the intermediate member on the side separated from the second coil spring and inserts the other end of the first coil spring. As a general means, the first retaining portion may also be composed of a small diameter portion and a concave portion, wherein the small diameter portion is formed in the center of the bottom surface of the bottomed concave portion of the retainer and accommodates one end of the first coil spring, and the concave portion is formed on the surface of the intermediate member on the side separated from the second coil spring and accommodates the other end of the first coil spring. As a further alternative means, the first retaining portion may also be composed of a protrusion and a concave portion, wherein the protrusion is formed in the center of the bottom surface of the bottomed concave portion of the retainer in a manner protruding toward the intermediate member and inserts one end of the first coil spring, and the concave portion is formed on the surface of the intermediate member on the side separated from the second coil spring and accommodates the other end of the first coil spring.

[0015] The second retaining portion may be a flange portion that abuts the inner diameter portion of the first coil spring separation side of the intermediate member and the end of the second coil spring on the side close to the first coil spring, thereby retaining the second coil spring, and abutting the inner surface of the bottomed recess of the retainer to slide freely in the circumferential direction. As an alternative, the second retaining portion may be a truncated cone-shaped protrusion that is inserted into the central opening of the second coil spring on the first coil spring separation side of the intermediate member. The first retainer and the second retainer are preferably injection-molded products made of synthetic resin.

[0016] In the present invention, in order to realize the support structure of the first retainer and the second retainer, a groove-protrusion fitting structure and a surface-surface contact structure can be provided, which are formed between the surfaces of the first retainer and the second retainer that are opposite to the input member and the output member, and are used to support the first retainer and the second retainer themselves in the axial direction and the radial direction on the input member and the output member. In this case, the relative movement of the input member and the output member corresponding to the rotational change causes the relative movement in the circumferential direction between the first retainer and the second retainer supported by the self-contained support structure according to the elastic force.

[0017] The supporting structure can be constructed as an axially aligned structure of multiple plates, that is, one of the input member and the output member for supporting the first retainer and the second retainer axially and radially with the other of the input member and the output member placed in the middle. In this case, the relative movement of the other of the input member and the output member with respect to one of the input member and the output member corresponding to the rotational change can also cause the circumferential relative movement between the first retainer and the second retainer supported by one of the input member and the output member corresponding to the elastic force of the elastic body. Effects of the Invention

[0018] In the torsional vibration damping device of the present invention, a low-rigidity first elastic member and an intermediate member connecting the first elastic member and the second elastic member are accommodated in a first retainer and / or a second retainer. The deformation of the first elastic member and / or the second elastic member can be provided by sliding of the relative surfaces of the retainer of the intermediate member. The metallic rotating member coaxially arranged with the rotation center of the transmission and / or the additional metal parts for fixing the elastic member in the prior art become unnecessary, which can achieve a significant reduction in the number of parts and a significant reduction in cost due to shortened working hours.

[0019] The first retainer and the second retainer are relatively large in size because they are structures for accommodating the ends of the elastic member, and can be made into resin parts by selecting suitable raw materials. In addition, the connecting member can be made of metal, but it can also be made of resin parts by selecting appropriate raw materials. Therefore, when the connecting member is seated when switching between low rigidity and high rigidity, it can form a resin-to-metal or resin-to-resin contact, thereby greatly reducing abnormal noise caused by impact during switching. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 This is a front view of the torsional vibration damper device according to the first embodiment as viewed from the transmission side. Figure 2 This is a rear view of the torsional vibration damper device according to the first embodiment as viewed from the prime mover side. Figure 3 is along Figure 1 Cross-sectional view along line III-III. Figure 4A The left half of the perspective view of the torsional vibration damper device according to the first embodiment is shown in an exploded state. Figure 4B The right half of the perspective view of the torsional vibration damper device according to the first embodiment is shown in an exploded state. Figure 5A 1 is a cross-sectional view of a pair of first and second retainers and a coil spring assembly in the torsional vibration damper device of the first embodiment. The coil spring assembly is composed of a first coil spring, a second coil spring, and an intermediate retainer therebetween, and is shown in an initial setting state. Figure 5B is with Figure 5A This is a cross-sectional view of the same first retainer, second retainer, and coil spring assembly, but shows the state when the coil spring assembly is switched from the low-rigidity first coil spring to the high-rigidity second coil spring. Figure 5C is with Figure 5A and Figure 5B The same cross-sectional view shows the state where the first retainer and the second retainer are in contact with each other. Figure 6 Graph schematically showing the relationship between the torsion angle and the torsion torque of the coil spring assembly according to the first embodiment. Figure 7 It is a cross-sectional view of a pair of first and second retainers and a coil spring assembly in another embodiment. The coil spring assembly is composed of a first coil spring, a second coil spring, and an intermediate retainer therebetween, and is shown in an initial setting state. Figure 8 and Figure 7 Other embodiments are also contemplated. Fig. 9 and Figure 7 , Figure 8 Other embodiments are also contemplated. Fig.10 This is a front view of the torsional vibration damper device according to the second embodiment as viewed from the transmission side. Fig.11 is along Fig.10 A cross-sectional view taken along line XI-XI. Fig.12 is along Fig.10 Cross-sectional view along line XII-XII. Fig.13 1 is a cross-sectional view of a pair of first and second retainers and a coil spring assembly in a torsional vibration damper device according to a second embodiment. The coil spring assembly is composed of a first coil spring, a second coil spring, and an intermediate retainer therebetween, and is shown in an initial setting state. DETAILED DESCRIPTION

[0021] Hereinafter, description will be given with reference to the accompanying drawings. Figures 1 to 3 The torsional vibration damper device of the first embodiment is shown in an assembled state. In the torsional vibration damper device, both the input member and the output member are stamped from a single steel plate, so that the retainer for retaining the coil spring end has a supporting function for the input member and the output member only by itself, and comprises: an input member 10, which is connected to a flywheel (a part of which is Figure 3 The flywheel is connected to the crankshaft (indicated by the imaginary line 11) of the internal combustion engine (prime mover) (driving side of the present invention); the output member 12 is connected to the transmission (driven side of the present invention); a plurality of coil spring sets 14 (elastic body of the present invention) are arranged at equal intervals along the circumferential direction (three in this embodiment); a first retainer 16 is provided at one end of each coil spring set 14 in the longitudinal direction (circumferential direction); and a second retainer 18 is provided at the other end of the coil spring set 14 in the longitudinal direction (circumferential direction). Therefore, three sets of the first retainer 16 and the second retainer 18 are provided to match the number of the coil spring sets 14.

[0022] Each coil spring set 14 is composed of a first coil spring 32 (first elastic member of the present invention) having low rigidity and short size and a second coil spring 34 (second elastic member of the present invention) having high rigidity and long size connected in series via an intermediate retainer 36 (intermediate member of the present invention).

[0023] The first retainer 16 and the second retainer 18 are molded products of plastic such as nylon resin, and each has a self-contained support structure described later that supports the input member 10 and the output member 12 in both the axial and radial directions without impairing the original function of each retainer 16 and the second retainer 18. The intermediate retainer 36 can be made of a stamped product of a metal plate of appropriate thickness from the viewpoint of cost, but can be made of resin by appropriately selecting the raw material and / or the wall thickness, which is advantageous from the viewpoint of reducing abnormal noise because switching between low rigidity and high rigidity will cause a resin-resin conflict.

[0024] The input member 10 is a stamped product made of a steel plate and is formed into an annular disk. The input member 10 is formed with: six bolt holes 20 arranged at equal intervals in the circumferential direction and used for fixing to the flywheel; and two knock pin holes 21 having a smaller diameter than the bolt holes 20 and arranged at diametrically opposite positions (to avoid complexity, only one figure number is shown for each).

[0025] The inner peripheral surface of the input member 10 is formed with arc-shaped recessed portions of a predetermined depth, namely, guide portions 22, at equal intervals in the circumferential direction. Figure 1 and Figure 2 The groups of the first retainers 16 and 18 shown are respectively provided in the guide portion 22. The inner circumferential concave surface of the input member 10 forming the guide portion 22 makes the rotation center coincide with the rotation center line O of the input-output shaft, and serves as a sliding guide surface for the first retainers 16 and 18 during torsional vibration between the input-output shaft as described later. The first retainers 16 and 18 of each group are arranged close to and opposite to the circumferential ends of the corresponding guide portion 22.

[0026] Output member 12 (shape reference Figure 4A ) is also a stamped product made of steel plate as the raw material, like the input member 10. Figure 1 As shown, it comprises: a support plate 24 with a pseudo-triangular shape (rice ball shape) with a circular shape; and three extension plates 28, which are integrally bent from the outer peripheral protrusion 24-2 at the vertex of the triangular shape of the support plate 24. Each extension plate 28 is arranged between adjacent coil spring sets 14 in the circumferential direction. The output member 12 also forms an integral spline shaft 30 coaxial with the rotation center line O of the input-output shaft on the central portion of the extension plate 28, and the spline shaft 30 can be connected to the transmission input shaft (not shown) via an inner peripheral spline (not shown). The extension plate 28 extends radially outward on the outer diameter side, but is integrally connected to the outer peripheral portion 24-2 of the support plate 24 on the inner peripheral side via the axial extension plate 26 ( Figure 3 ).

[0027] The output member 12 forms a recessed portion for accommodating each coil spring assembly 14 between adjacent extension plates 28 in the circumferential direction. The bottom surface of the recessed portion is formed by the outer peripheral surface 24-1, which is each side of the pseudo-triangular shape of the support plate 24 that extends somewhat outward. The guide portion 22 and the recessed portion of the extension plate 28 together with the outer peripheral surface 24-1 form a window frame-shaped opening portion 15 for accommodating a corresponding one of the three coil spring assemblies 14.

[0028] Next, through Figure 4A and Figure 4BThe detailed structure of the torsional vibration damping device is explained in the exploded perspective view of FIG. The first retainers 16 and 18 are arranged in three groups, and a coil spring set 14 (composed of a low-rigidity first coil spring 32, a high-rigidity second coil spring 34 and an intermediate retainer 36, respectively) is provided for each group of the first retainers 16 and 18. The three groups are represented by A, B, and C, respectively. In addition, since the guides 22 of the input member 10 are also arranged in groups, they are respectively marked with (A), (B), and (C). The locking portions 22-1 and 22-2 at both ends of the guide 22 are also arranged in groups, so they are also marked with (A), (B), and (C), respectively. On the other hand, the two end surfaces in the circumferential direction of the extension plate 28 of the output member 12 form the driving portions 28-1 and 28-2, but since the relative driving portions 28-1 and 28-2 of the extension plates 28 adjacent in the circumferential direction are grouped, they are also marked with (A), (B), and (C) to represent them.

[0029] Below, through Figure 4A and Figure 4B , the structures of the first retainers 16 and 18 and the assembly structures of the first retainers 16 and 18 relative to the input member 10 and the output member 12 are described with group A as the main body. However, due to the nature of the stereogram, it is not possible to illustrate the entire structure with only group A, so the description is also appropriately referred to other groups B and C. First, the relationship between the first retainer 16 and the input member 10 is described. The first retainer 16 has a guide groove 16-1 (also refer to the outer peripheral surface of the first retainer 16 that is opposite to the guide portion 22 of the corresponding group (assuming group A) of the input member 10, which is extended over the entire length in the circumferential direction. Figure 3 ), the guide groove 16-1 is formed in a U-shaped cross section opening radially outward, and the thickness portion of the input member 10 is slidably accommodated in the circumferential direction with a suitable gap at the guide portion 22 of the input member 10, so that the first retainer 16 can rotate relative to the input member 10 in the circumferential direction, and the engagement between the guide groove 16-1 and the guide portion 22 is not substantially loose in the axial direction so as not to hinder smooth sliding, and the first retainer 16 functions as an axial support for the input member 10. Moreover, the bottom surface of the guide groove 16-1 extending in the circumferential direction can function as a support surface for supporting the first retainer 16 radially outward relative to the input member 10.

[0030] The first retainer 16 has a flat surface 16-2 (pressure receiving portion of the present invention) extending radially parallel to the rotation center line O at the circumferential end portion opposite to the protruding plate 28 adjacent thereto. With respect to the flat surface 16-2, an end surface 28-1 (a shape that is difficult to be seen from the perspective of the pressure receiving portion) opposite to the protruding plate 28 adjacent thereto in the circumferential direction is formed. Figure 4A and Figure 4BIt can be seen that, referring to the shape of the end faces 28-2 of the second retainer 18 in the set that are opposite in the circumferential direction, the flat surface 16-2 becomes a torque receiving surface that receives torque from the extension plate 28 during rotational fluctuation in the forward rotation direction (direction of arrow f1).

[0031] The plate-like protrusion 16-3 is integrally formed from the flat surface 16-2, and the outer peripheral side of the plate-like protrusion 16-3 extends flush with the outer peripheral surface of the first retainer 16, and the inner peripheral side terminates in the middle. The plate-like protrusion 16-3 forms an axial support surface 16-4 that is orthogonal to the rotation center line O and extends radially on the transmission side (the driven side in the present invention). In the assembled state, the axial extension plate 26 passes through the radial inner side of the plate-like protrusion 16-3, whereby the extension plate 28 abuts against the axial support surface 16-4 in the axial direction on the transmission side, and the axial support surface 16-4 functions as an axial support surface of the first retainer 16 toward the transmission side.

[0032] From the flat surface 16-2, a terrace-shaped protrusion 16-5 is separated from the plate-shaped protrusion 16-3 toward the prime mover side (driving side of the present invention) in the axial direction and established. The terrace-shaped protrusion 16-5 is flush with the outer peripheral surface of the first retainer 16 and the side surface on the prime mover side, but is aligned with the plate-shaped protrusion 16-3 and terminates in the radial inner side. In addition, a longitudinal groove 16-6 remains between the plate-shaped protrusion 16-3 and the terrace-shaped protrusion 16-5, and its bottom surface is a part of the flat surface 16-2 and is connected to the guide groove 16-1 on the outer peripheral surface via a curved portion 16-6'. The curved portion 16-6' of the longitudinal groove 16-6 is added to match the rounded shape of the root of the end surface 22-1 of the guide portion 22 opposite in the circumferential direction. That is, the longitudinal groove 16 - 6 and the curved portion 16 - 6 ′ accommodate the end surface 22 - 1 of the guide portion 22 in a neutral state without rotational change, and at this time, the input member 10 is restricted from rotating relative to the output member 12 by the flat surface 16 - 2 .

[0033] The inner circumferential wall 16-14 of the inner circumferential portion 16-7, which is narrower than the inner diameter surface 16-10, is formed to stand upright toward the radial inside over the entire length in the circumferential direction. The shape of the inner circumferential wall 16-14 is difficult to know based on the first retainer 16 of group A, but its shape can be understood from the first retainers 16 of groups B and C. The inner circumferential portion 16-7 forms a support surface 16-10' flush with the inner diameter surface 16-10 on the prime mover side of the inner circumferential wall 16-14. When the first retainer 16 is assembled relative to the input member 10 and the output member 12, the support surface 16-10' is opposite to the outer circumferential surface 24-1 of the support plate 24 from the radial outside, and the inner circumferential wall 16-14 is opposite to the support plate 24 from the axial transmission side. In addition, Figure 31 and 2 also show a structure in which the support surface 16 - 10 ′ of the first retainer 16 is opposite to (the outer peripheral surface 24 - 1 of) the support plate 24 in the radial direction, and the inner peripheral wall 16 - 14 is opposite to the transmission side of the support plate 24 in the axial direction.

[0034] The inner peripheral portion 16-7 has an arc-shaped protrusion 16-8 formed from the flat surface 16-2 at intervals from the plate-shaped protrusion 16-3 and the table-shaped protrusion 16-5 in the radial direction inward. That is, the arc-shaped protrusion 16-8 is an extension of the inner peripheral portion 16-7 on the side of the protruding plate 28. The arc-shaped protrusion 16-8 enters the axial extension plate 26 connecting the support plate 24 and the protruding plate 28 from the inner peripheral side (the arc-shaped protrusion 16-8 enters the axial extension plate 26 from the inner peripheral side). Figure 1 ). With this structure, the outer peripheral surface 16-9 of the arc-shaped protrusion 16-8 becomes a support surface for supporting the first retainer 16 from the radial inner side relative to the axially extending plate 26, that is, the output member 12, and provides a radial support structure for the first retainer 16 together with the bottom surface of the guide groove 16-1, that is, the support surface supported from the radial outer side. In the assembled state, the gap between the plate-shaped protrusion 16-3 and the arc-shaped protrusion 16-8 becomes a gap portion for the axially extending plate 26 of the output member 12 to pass through. The arc-shaped protrusion 16-8 forms an axial support surface 16-11 on the prime mover side that is axially orthogonal to the prime mover side and extends radially. The axial support surface 16-11 is opposite to and abuts against the support plate 24 in the assembled state (neutral state), and functions as an axial support surface of the first retainer 16 relative to the output member 12 toward the prime mover side. That is, the axial support surface 16-11 and the axial support surface 16-4 function as support surfaces for supporting the first retainer 16 on both sides of the axial direction with respect to the output member 12. The abutment structure of the axial support surface 16-11 with respect to the support plate 24 (outer circumferential protrusion 24-2) is difficult to understand in the first retainer 16 of group A, but can be understood from the positional relationship between the axial support surface 16-11 and the outer circumferential protrusion 24-2 of the support plate 24 of the first retainer 16 of group B. As described above, the arc-shaped protrusion 16-8 becomes the end portion on the side of the corresponding extension plate 28 of the inner circumferential portion 16-7, and the axial support surface 16-11 of the arc-shaped protrusion 16-8 forms an extension in the circumferential direction flush with the inner circumferential wall 16-14 surface.

[0035] like Figure 4A As shown, the first retainer 16 has a bottom recess 40 formed at the circumferential end of the flat surface 16-2, that is, the circumferential end of the side of the separation side that contacts the end surface 28-1 of the extension plate 28. The bottom recess 40 is used to accommodate the end of the first retainer 16 of the corresponding coil spring set 14, that is, the end close to the first coil spring 32 and the intermediate retainer 36 and the intermediate retainer 36 of the second spring 34. Figure 4AIt is difficult to understand the structure based on groups A and B, but the structure of the bottom recess 40 can be clearly seen in group C: it has bottom surfaces 40-1a and 40-2a of different depths, forming two layers of large diameter part 40-1 and small diameter part 40-2. In addition, cutouts 16-13 are formed on both side walls of the first retainer 16 from the side close to the coil spring kit 14, which can function as insertion holes for inserting a jig (assembly robot) for compressing the spring for installation into the inner side of the recess 40. In addition, it also has the following structure: a support protrusion 36-2 on the inner diameter side of the intermediate retainer 36 and a flange 36-3 provided on the radially outer side so as to face the second coil spring 34 (constituting the second retaining portion of the present invention for retaining (guiding) the second coil spring 34).

[0036] The second retainer 18 has the same structure as the first retainer 16 except that it is symmetrically arranged. Referring to the second retainers 18 of groups A and B, it can be seen that the circumferential sliding structure relative to the guide portion 22 based on the guide groove 18-1 and the inner peripheral wall 18-14 are formed upright from the circumferential inner surface 18-10 of the inner peripheral portion 18-7 to the radial inward direction. In addition, if the second retainer 18 of group C is observed, it can be seen that the plate-like protrusion 18-3 established on the flat pressure-bearing surface 18-2 and the axial support surface 18-4 formed by the plate-like protrusion 18-3, as well as the terrace-like protrusion 18-5 and the longitudinal groove 18-6 formed therebetween, and the arc-like protrusion 18-8 at the front end of the inner peripheral portion 18-7 and the axial support surface 18-11 formed by the arc-like protrusion 18-8. Furthermore, regarding the second retainer 18 of the set A, the shape of the bottomed recess 42 for accommodating the end of the second spring 34 and the shapes of the cutout portions 18 - 13 formed on both sides can be clearly identified.

[0037] The first retainers 16 and 18 are mounted relative to the input member 10 and the output member 12. The first retainers 16 and 18 are mounted by mounting the pin hole 21 of the input member 10 on the positioning pin of the flywheel 11, and are fixed to the flywheel 11 by bolts passing through the bolt holes 20. On the other hand, the output member 12 is mounted in a state where the spline shaft 30 is fixed to the input shaft of the transmission by spline fitting. The interval between the guide portion 22 of the input member 10 and the outer peripheral surface 24-1 of the support plate 24 of the output member 12 facing each other is the largest at the center between the opposite end surfaces 28-1 and 28-2 of the protruding plates 28 adjacent in the circumferential direction of the set (see FIG. 2 ). Figure 1 or Figure 2), by appropriately tilting the first retainer 16 relative to the input member 10, the first retainer 16 is introduced from the step surface 16-10 side into between the guide portion 22 and the support plate 24 (window frame-shaped opening portion 15), and by arranging the input member 10 and the first retainer 16 to be straight, the guide groove 16-1 can be embedded in the guide portion 22. Similarly, the second retainer 18 can also be introduced from the step surface 18-10 side to the window frame-shaped opening portion 15, so that the guide groove 18-1 is embedded in the guide portion 22. When the first retainers 16 and 18 are embedded in the guide portion 22, the step surfaces 16-10 and 18-10 are radially opposed to the circumferential outer surface 24-1 of the support plate 24, and the inner peripheral walls 16-14 and 18-14 are axially opposed to the support plate 24 from the transmission side. Therefore, the first retainers 16 and 18 are in a state of being uprightly supported in the axial direction from the transmission side. Furthermore, when the first retainer 16 embedded in the guide portion 22 is pressed in the circumferential direction toward the opposite end surface 22-1 of the guide portion 22, the longitudinal groove 16-6 of the first retainer 16 is embedded in the end surface 22-1 of the guide portion 22 on the input member 10, and at the same time, the extension plate 28 is engaged with the plate-like protrusion 16-3 on the transmission side on the output member, and the axial extension plate 26 is introduced between the terrace-like protrusion 16-5 and the arc-shaped protrusion 16-8, and the axial support surface 16-11 of the arc-shaped protrusion 16-8 contacts the outer peripheral convex portion 24-2 of the support plate 24, and the arc-shaped protrusion 16-8 is embedded in the axial extension plate 26 from the inside. Furthermore, in the final press-fitting completion state, the longitudinal groove 16-6 is engaged with the end surface 22-1, and the end surface 28-1 of the extension plate 28 is in contact with the flat surface 16-2 of the first retainer 16. In this state, the circumferential inner surface (bottom surface) 16-10 of the first retainer 16 and the circumferential outer surface 24-1 of the support plate 24 of the output member 12 are in close contact with each other (see Figure 3 ). The same operation is also performed on the second retainer 18. When the end face 22-2 of the guide portion 22 is inserted into the longitudinal groove 18-6, the end face of the extension plate 28 is in contact with the flat face 18-2 of the second retainer 18. In this state, the circumferential inner surface 18-10 of the second retainer 18 is in close contact with the circumferential inner surface 24-1 of the support plate 24 of the output member 12, and the second retainer 18 is supported in both the axial and radial directions relative to the input member 10 and the output member 12. At this time, the cutouts 16-13 and 18-13 are relatively located between the first retainers 16 and 18 of each group (refer to Figure 1 ), the coil spring kit 14 can obtain the following Figure 1 and Figure 2The assembled state is as follows: the first coil spring 32 and the second coil spring 34 are connected in series through the intermediate retainer 36, and after being compressed from both sides by the clamp, the clamp is inserted through the cutout portions 16-13 and 18-13 to be introduced between the first retainers 16 and 18, and the clamp is moved back and pulled out through the cutout portions 16-13 and 18-13, so that the coil spring kit 14 is accommodated in the bottomed recess 40 of the first retainer at one end and in the bottomed recess 42 of the second retainer at the other end under its elasticity.

[0038] Figure 5A The sectional view shows the state of accommodation of a corresponding coil spring set 14 composed of a first coil spring 32, a second coil spring 34 and an intermediate retainer 36 between a pair of first retainers 16 and 18 in the initial setting state after assembly, and the engagement state with the input member 10 and the output member 12 is omitted to avoid complexity. The first coil spring 32 is formed into a short-sized type using a steel wire with a small wire diameter as a raw material to obtain a desired low rigidity (relatively small torque value relative to the torsion angle), and the second coil spring 34 is formed into a long-sized type using a steel wire with a large wire diameter as a raw material to obtain a desired high rigidity (relatively large torque value relative to the torsion angle). In each coil spring set 14, the end of the first coil spring 32 separated from the intermediate retainer 36 in the length direction is accommodated in the bottomed recess 40 of the first retainer, and the end of the second coil spring 34 separated from the intermediate retainer 36 in the length direction is accommodated in the bottomed recess 42 of the second retainer 18.

[0039] The first retainer 16 and the second retainer 18 are further described in detail to accommodate the first coil spring 32 and the second coil spring 34. In the first retainer 16, the bottomed recessed portion 40 opened toward the second retainer 18 in the circumferential direction for accommodating the first coil spring 32 and the intermediate retainer 36 is formed into two stages: a large diameter portion 40-1 from the opening end; and a small diameter portion 40-2 which is further deepened and recessed from the bottom surface of the large diameter portion 40-1 and is set in a cylindrical shape (the two-stage shape of the bottomed recessed portion 40 is also referred to Figure 4A). In the first coil spring 32, one end in the longitudinal direction abuts against the bottom surface 40-2a of the small diameter portion 40-2, and the other end abuts against the opposite surface 36-1 of the intermediate retainer 36. In the initial setting state, a gap α is left between the bottom surface 40-1a of the large diameter portion 40-1 and the opposite surface 36-1 of the intermediate retainer 36, and the first coil spring 32 can be deformed from the initial setting state by an amount corresponding to the stroke of the gap α. After the gap α disappears, the second coil spring 34 alone participates in the suppression of rotational changes. That is, in order to guide the first coil spring 32, the intermediate retainer 36 has a support protrusion 36-2 for the first coil spring 32 which integrally protrudes toward the inside of the first coil spring 32 at the center (together with the small diameter portion 40-2 of the bottomed recess 40, it constitutes the first retaining portion of the present invention for retaining (guiding) the first coil spring 32), but the protruding height of the support protrusion 36-2 from the bottom surface 36-1 is smaller than the size of the gap α between the bottom surface 40-1a and the bottom surface 36-1, and the intermediate retainer 36 is seated on the bottom surface 40-1a of the large diameter portion 40-1 before the first coil spring 32 reaches the state where the winding wires are in close contact with each other, and after the first coil spring 32 is invalidated, the intermediate retainer 36 shifts to the action of the second coil spring 34. The structure in which one end of the first coil spring 32 is inserted into the support protrusion 36-2 and the other end is accommodated in the small diameter portion 40-2 can also contribute to the smooth deformation of the first coil spring 32 during torsional vibration through its guiding action.

[0040] In addition, in order to guide or restrict the second coil spring 34 when deforming, the intermediate retainer 36 has a flange portion 36-3 on the radially outer side so as to face the second coil spring 34 (for the shape of the flange portion 36-3, refer to Figure 4B ). The first retainer 16 forms a guide surface 40-1b in the bottomed recess 40 opposite to the flange portion 36-3. Since the second coil spring 34 is urged radially outward by centrifugal force, when the first coil spring 32 is deformed during rotational change, the intermediate retainer 36 is guided by the guide surface 40-1b of the first retainer 16 opposite to the flange portion 36-3, thereby ensuring smooth movement toward the opposite surface 40-1a of the bottomed recess 40. An inner peripheral surface 40-1c is present at a position closer to the opening end side than the guide surface 40-1b in the bottomed recess 40, and is expanded in the axial direction to avoid interference with the second coil spring 34 during assembly. The flange portion 36-3 retains the end of the second coil spring 34, and functions as a guide member for smoothly guiding the intermediate retainer 36 relative to the inner periphery of the first retainer 16 relative to the deformation of the second coil spring 34 caused by torsional vibration.

[0041] like Figure 5A As shown in FIG. 1 , the second retainer 18 includes a cylindrical bottomed opening 42 that opens toward the first retainer 16. The cylindrical bottomed opening 42 is as shown in FIG. Figure 4BAs shown in the group A of FIG. 1 , the shape is as follows: the two side walls are cut off from the cylindrical body, and the wall portions forming the inner peripheral surface of the arc shape are left at the top and bottom. The end of the second coil spring 34 on the side separated from the intermediate retainer 36 abuts against the bottom surface 42-1 of the cylindrical bottomed opening 42. The radially outer inner peripheral surface 42-1c of the cylindrical bottomed opening 42 serves as a guide surface for the coil spring 34 to be displaced radially outward by the second centrifugal force.

[0042] about Figure 4A and Figure 4B The structures of the protrusions, grooves, and support surfaces of the outer surfaces of the first retainer 16 and the second retainer 18 facing the input member 10 and the output member 12 are shown in the cross-sectional view. Figure 5A and Figure 5B Visible parts are indicated by corresponding reference symbols, and descriptions of related functions are omitted to avoid repetition.

[0043] In the present embodiment, the first retainers 16 and 18 do not lose their original function of retaining the coil spring 14 at both ends in the circumferential direction, but have a self-contained support structure in which the retainer itself is supported in the axial direction and radial direction with respect to the input member 10 and the output member 12. That is, in explaining the support structure, the first retainer 16 is as follows: Figure 4A As described above, the guide groove 16-1 is engaged with the guide portion 22 of the input member 10, and the opposing surfaces of the guide groove 16-1 separated in the axial direction are supported in the axial direction by the input member 10. In addition, the axial support of the first retainer 16 relative to the output member 12 is performed by the following actions: the extension plate 28 abuts against the plate-like protrusion 16-3 (axial support surface 16-4) of the first retainer 16 from the transmission side, and the support plate 24 (outer peripheral convex portion 24-2) abuts against the axial support surface 16-11 (formed in the arc-shaped protrusion 16-8) of the first retainer 16 from the prime mover side. In addition, the radial support of the first retainer 1 is performed by the following actions: the guide portion 22 of the input member 10 abuts against the bottom surface of the guide groove 16-1 of the first retainer 16 from the radial outside, and the outer peripheral surface 16-9 of the arc-shaped protrusion 16-8 abuts against the inner peripheral surface of the axial extension plate 26 of the output member 12 from the radial inside.

[0044] The second retainer 18 also supports the input member 10 and the output member 12 in the same manner. The second retainer 18 is axially supported by the input member 10 by the contact between the guide groove 18-1 and the axially opposite side surface, and the second retainer 18 is axially supported by the output member 12 between the plate-like protrusion 18-3 (axial support surface 18-4) and the arc-shaped protrusion 18-8 (axial support surface 18-11). The radial support of the second retainer 18 is performed by the following actions: the guide portion 22 of the input member 10 contacts the bottom surface of the guide groove 18-1 of the second retainer 18 from the radial outside, and the outer peripheral surface 18-9 of the arc-shaped protrusion 18-8 contacts the axially extending plate 26 of the output member 12 from the radial inside.

[0045] The first retainers 16 and 18 are self-supporting structures for the input member 10 and the output member 12. Although the input member 10 and the output member 12 are one-piece parts of stamped products made of steel plates, the first retainer 16 itself is supported by the input member 10 and the output member 12 in the axial and radial directions without damaging the original function of the first retainers 16 and 18 of holding the coil spring set 14. Compared with the usual structure in which the input member 10 is a two-piece structure and the coil spring set 12 is held between them, at least one stamped part can be saved. In addition, rivets for integrating the two-piece structure are not required, and the number of parts can be suppressed in this regard, which is also advantageous from the perspective of workability. In addition, since there are no rivets, the degree of freedom in design on the outer diameter side can be increased to a corresponding degree.

[0046] Then through Figure 4A and Figure 4BThe rotational variation suppressing action of the torsional vibration damping device of the first embodiment will be described. When the output member 12 generates a rotational torque in the normal rotation direction (the direction of arrow f1) relative to the input member 10, the extension plate 28 causes the first retainer 16 to slide in the direction of arrow f1 along the guide portion 22 via the guide groove 16-1 by the contact between its end face 28-1 and the opposing flat face 16-2 of the first retainer 16 (the retainer located on the upstream side in the direction of torsional torque application). The first retainer 16 is released from the contact state with the end face 22-1 of the guide portion 22. On the other hand, the second retainer 18 of the group maintains the contact state between its flat face 18-2 and the guide portion end face 22-2 on the downstream side in the rotational variation direction. Therefore, the end face 28-2 of the extension plate 28 on the downstream side in the rotational variation direction is released from the opposing flat face 18-2 of the second retainer 18, causing further compression of the coil spring set 14 between the first retainers 16 and 18. As the torsional torque of the output member 12 increases in the forward rotation direction (direction of arrow f1) relative to the input member 10, the extended plate 28 on the downstream side of the rotation change direction f1 of the output member 12 is soon disengaged from the second retainer 18 (longitudinal groove 18-6) and the axially extending plate 26 is disengaged from the arc-shaped protrusion 18-8 (circumferential outer peripheral surface 16-9). At this time, the second retainer 18 is elastically locked to the guide portion end surface 22-2 at the flat surface 18-2, so the second retainer 18 is held fixed relative to the input member 10. In addition, the radially outer component of the elastic force generated by the coil spring set 14 and the centrifugal force generated on the second retainer 18 due to the rotation of the crankshaft contribute to the reliable retention of the second retainer 18 relative to the input member 10.

[0047] On the other hand, when the output member 12 rotates from the neutral state to the reverse direction (in the direction of arrow f2) relative to the input member 10, the extension plate 28 abuts against the flat surface 18-2 through the end surface 28-2, causing the second retainer 18 (the retainer located on the upstream side in the direction of torsional torque application) to slide in the reverse direction (in the direction of arrow f2) along the guide portion 22 via the guide groove 18-1. At this time, the flat surface 18-2 of the second retainer 18 is disengaged from the abutment state with the end surface 22-2 of the guide portion 22, and the flat surface 16-2 of the first retainer 16 located on the downstream side in the direction of rotational change is locked and retained on the end surface 22-1 of the guide portion 22, so that the end surface 28-1 of the extension plate 28 is separated from the first retainer 16, and at the same time, the second retainer 18 slides along the guide portion 22 toward the first retainer 16 opposite in the circumferential direction via the guide groove 18-1, causing further compression of the coil spring kit 14. The rotational fluctuation can be reduced by the compression operation of the coil spring set 14 according to the direction of the rotational fluctuation.

[0048] The operation of the coil spring assembly 14 according to this embodiment in response to the torque change will be described. In a state where no torsional torque is applied (neutral state), due to the elastic force of the first coil spring 32 and the second coil spring 34 in the coil spring assembly 14 connected in series via the intermediate retainer 36, the paired first retainers 16 and 18 abut against the locking portions 22-1 and 22-2 of the guide portion 22 of the input member 10 and the driving portions 28-12 and 28-2 of the extension plate 28 of the output member 12. Figure 1 and Figure 2 The state of the coil spring assembly 14 in the state without variable torque (torsion torque = 0) is Figure 5A Shown in.

[0049] The positive rotation direction ( Figure 1 The torque variation of arrow f1) causes the first retainer 16 to move toward the second retainer 18, reversing the direction ( Figure 1 The torque indicated by the arrow f2) causes the second retainer 18 to move toward the first retainer 16, but this causes the intermediate retainer 36 to slide along the inner diameter of the first retainer 16 when the torque is small. The torque causing the intermediate retainer 36 and the first retainer 16 to slide is set to a low torque such as the idling operation area of ​​the prime mover. Such sliding of the intermediate retainer 36 is Figure 5A As shown in FIG. 1 , when the intermediate retainer 36 has a gap with respect to the opposite surface 40 - 1 a , the torsional rigidity value K of the first coil spring 32 and the second coil spring 34 at this time is obtained. damp1 When the spring rigidities of the first coil spring 32 and the second coil spring 34 are set to k1 and k2, respectively, they are: K damp1 =k1k2 / (k1+k2).

[0050] The torque starts to rise from the idling operation area and enters the operation area under the normal torque, so that the relative movement of the first retainer 16 and 18 in the circumferential direction increases, and the increase soon becomes Figure 5B As shown in FIG. 1 , the intermediate retainer 36 is seated on the opposite surface 40-1a, and the function of the first coil spring 32 as a spring disappears. The relative movement of the first retainers 16 and 18 in the circumferential direction caused by the further increase in torque is only carried out against the elastic force of the second coil spring 34. At this time, the torsional rigidity value K damp2 can be K damp2 =K2 In order to invalidate the first coil spring 32 before the intermediate retainer 36 is seated on the seating surface 40-1a (to prevent the first coil spring 32 from being closely attached (completely crushed)), the intermediate retainer 36 is seated on 40-1a before the supporting protrusion 36-2 on the inner diameter side of the intermediate retainer 36 abuts against the opposite surface 42-2a in a manner that does not cause the first coil spring 32 to be closely attached (completely crushed).

[0051] Figure 5C The figure shows that the first retainers 16 and 18 reach a state where the opposing surfaces abut against each other due to further increase in the torsional torque, and the second coil spring 34 also loses its function. At this time, before the second coil spring 34 is tightly attached (completely crushed), the opposing surfaces 16-15 and 18-15 on the outer diameter side of the first retainers 16 and 18 abut against each other. Figure 5B and Figure 5C To avoid clutter, only relevant part numbers are shown.

[0052] Figure 6 The graph schematically shows the relationship between the torsion angle and the torsion torque. In the region where the relative torsion angle is smaller than the gap α (θ<θ1), the first coil spring 32 and the second coil spring 34 operate in series to damp the fluctuating torque transmitted from the input member.

[0053] In the normal torque region (θ1<θ<θ2) where the relative torsion angle caused by torque fluctuation is larger than the gap α, the gap α between the intermediate retainer 36 and the first retainer 16 completely disappears, and the bottom surface 40-1a of the bottomed recess 40 of the first retainer 16 abuts against the bottom surface 36-1 of the intermediate retainer 36 ( Figure 5B ), the first coil spring 32 is accommodated in the accommodation portion of the first retainer 16 in a compressed state that does not reach a close fit, so it does not bottom out during operation.

[0054] In the region where the fluctuating torque is the largest (θ>θ2), the opposing surface 16-15 provided at the upper portion of the first retainer 16 and the opposing surface 18-15 provided at the upper end portion of the second retainer 18 provided at the first retainer side abut ( Figure 5C ), thereby dispersing the excessive torque and alleviating the effect of the bottoming out of the second coil spring 34.

[0055] In the above-mentioned action of the coil spring kit 14 corresponding to the torque change, the impact caused by the abutment between the intermediate retainer 36 and the first retainer 16 (surface 40-1a) when transferring from low torque to normal torque is caused by the first retainer 16 being made of resin. Therefore, when the intermediate retainer 36 is made of metal as mentioned above, the contact between metal and resin can be suppressed to the point where it is not too noticeable to the driver as an abnormal noise. In addition, through appropriate selection of raw materials and / or wall thickness, when the intermediate retainer 36 is also made of resin, the resins are in contact with each other, so the abnormal noise can be further reduced.

[0056] Figure 7 The intermediate retainer 36 of another embodiment is shown, which has no flange portion 36-3 of the first embodiment, but is provided with a truncated cone-shaped portion 36-4 (constituting the second retaining portion of the present invention) instead, and the truncated cone-shaped portion 36-4 is inserted into the central opening of the second coil spring 34 from the first coil spring 32 side. That is, in this embodiment, the intermediate retainer 36 is formed into a structure that supports the end of the second coil spring 34 from the inner diameter side by the truncated cone-shaped portion 36-4.

[0057] In this embodiment, one end of the first coil spring 32 is accommodated and guided at the support protrusion 36-2 provided on the intermediate retainer 36 on the side close to the first coil spring 32, the guide structure composed of the support protrusion 36-2 provided on the intermediate retainer 36 and the small diameter portion 40-2 of the bottomed recess 40 of the first retainer 16, and the mechanism that makes the support protrusion 36-2 not contact with the opposite surface when the intermediate retainer 36 is seated to invalidate the first coil spring 32 is similar to the first embodiment ( Figure 5A-5C The structure of the recessed portion of the second retainer 18 for accommodating the second coil spring 34 is the same as that of the first embodiment, so detailed description thereof will be omitted. The support structure for the input member and / or the output member formed on the outer surfaces of the first and second first retainers 16 and 18 and utilizing surface-to-surface facing and groove-protrusion fitting is provided in the same manner as in the first embodiment, but the structural description is omitted.

[0058] Figure 8 In another embodiment, the structure of the truncated cone-shaped portion 36-4 for accommodating the second coil spring 34 is the same, but one end of the first coil spring 32 is accommodated in the recess 36-5 of the intermediate retainer 36, and the other end is accommodated in the small diameter portion 40-2 (which forms the first retaining portion of the present invention together with the recess 36-5) of the bottomed recess 40 of the first retainer 16 in order to guide the first coil spring 32. The structure of the first retainer 16 being seated on the opposite surface 40-1a of the small diameter portion 40-2 of the bottomed recess 40 is the same in order to make the first coil spring 32 inoperative before the first coil spring 32 is brought into close contact.

[0059] Fig. 9 The intermediate retainer 36 of another embodiment is shown, and the structure of the truncated cone-shaped portion 36-4 is provided. Figure 7 and Figure 8Similarly, the truncated cone-shaped portion 36-4 is provided on the side close to the second coil spring and is used to support the end of the second coil spring. The difference lies in the following structure: in order to guide the first coil spring 32, the intermediate retainer 36 is provided with a recessed portion 36-5 for accommodating one end of the first coil spring 32 on the side separated from the second coil spring 34, and a protrusion 36-6 for accommodating the other end of the first coil spring 32 is provided on the bottom surface of the bottomed recessed portion 40 of the first retainer 16. In this embodiment, the protrusion 36-6 is also set to a length that does not allow the first coil spring 32 to bottom out when the intermediate retainer 36 is seated on the opposite surface 40-1a of the bottomed recessed portion 40 (which together with the protrusion 36-6 constitutes the first retaining portion of the present invention).

[0060] Figures 10 to 13 A torsional vibration damper device according to a second embodiment of the present invention is shown, and means for realizing the present invention is shown for a type in which a normal type cage supported by an input member is provided instead of the self-supporting type cage of the first embodiment. The input member 110 is formed with four window frame-shaped openings 115 spaced at equal intervals in the circumferential direction, and each window frame-shaped opening 115 accommodates a coil spring set 114. Each coil spring set 114 is formed by connecting a first coil spring 132 (first elastic member of the present invention) with low rigidity and short size and a second coil spring 134 (second elastic member of the present invention) with a high rigidity and long size in series via an intermediate retainer 136 (connecting member of the present invention) as in the first embodiment. A first retainer 116 and a second retainer 118, which are injection-molded products of synthetic resin and are used to accommodate both ends of the coil spring set 114, are arranged in each window frame-shaped opening 115. Fig.13 The coil spring set 114 is shown with respect to the first retainer 116 and the second retainer 118 which form a pair. As in the first embodiment, the first retainer 116 has a bottomed recessed portion 140 for accommodating the first coil spring 132 and the intermediate retainer 136, and the second retainer 118 has a bottomed recessed portion 142 for accommodating the second coil spring 134. In this embodiment, as described above, the first retainer 116 and the second retainer 118 are supported axially and radially by the input member 110, so the outer peripheral surfaces of the first retainer 116 and the second retainer 118 are flat, which is different from the first embodiment. FIG. 5A to FIG. 5C It is clear from a comparison between the first retainers 16 and 18 that the first retainers 16 and 18 do not include an engaging portion such as a protrusion and / or a guide groove for a self-holding action.

[0061] like Fig.11 As shown, the input member 110 is a combined structure in which a pair of main body plates 160 and an outer peripheral plate 162 separated in the axial direction are combined by rivets 164. The outer peripheral plate 162 of the input member 110 is fastened with bolts and connected to the flywheel (prime mover side) by positioning pins and bolts as in the first embodiment. Fig.10In the embodiment, the bolt hole is indicated by 120 and the positioning pin hole is indicated by 121. The two main plates 160 in the input member 110 are respectively as shown in FIG. Fig.10 As shown, a structure is formed in which the central support plate portion 160-1 is connected to the outer peripheral circular plate portion 160-3 via the protruding plate portions 160-2 which are evenly spaced in the circumferential direction.

[0062] Fig.10 In the figure, the main plate 160 on the upper side of the screen of a pair of main plates 160 of the input member 110 is cut away between the section lines a and b, and the output member 112 can be seen therein. Similar to the first embodiment, the output member 112 has a central support plate 124 and extension plates 128 arranged at intervals in the circumferential direction on the outer periphery of the support plate 124. The number of extension plates 128 is four, similar to the first embodiment, but the extension plates 128 are extended radially outward as they are, which is different from the first embodiment (it does not have a portion equivalent to the axial extension plate 26 in the first embodiment). Fig.11 As shown, the output member 112 is configured to be clamped between the main body plates 160 of the input member 110 from both sides in the axial direction, and the central spline shaft 130 is spline-engaged with the input shaft of the transmission. Fig.10 In the setting state of the damper of the present embodiment shown in the figure, the extension plate 128 is arranged to overlap with the extension plate portions 160-2 of the two main body plates 160 constituting the input member 110, and this state cannot be directly obtained from Fig.10 It is clear that this can be understood from the configuration state of the extended plate 128 in the cut-away portion between the cutting lines a and b.

[0063] The radial and axial support methods of the first retainer 116 and the second retainer 118 by the input member 110 are well-known structures and are briefly described. The radial support of the first retainer 116 and the second retainer 118 relative to the input member 118 is performed by abutting the radial outer side surface and the radial inner side surface of the window frame-shaped opening portion 115 corresponding to the input member 110. In addition, in order to axially support the first retainer 116 and the second retainer 118, the outer peripheral circular plate portion 160-3 of the main body plate 160 of the input member 110 is formed with flange portions 160-3a provided along the opposing surfaces of the first retainer 116 and the second retainer 118 on both sides of the axial direction of the outer peripheral edge portion of the window frame-shaped opening portion 115, from Fig.11It can be seen that the eaves-shaped support portion 160-3a is extended along the sliding range of the first retainer 116 and the second retainer 118 in a manner that covers the first retainer 116 and the second retainer 118 to a certain extent from both sides of the axial direction, thereby ensuring the support of the first retainer 116 and the second retainer 118 on both sides of the axial direction. In this way, the first retainer 116 and the second retainer 118 are supported radially and axially, and the first retainer 116 and the second retainer 118 can move along the window frame-shaped opening portion 115 without falling off.

[0064] Fig.13 In the embodiment, the structure of a coil spring set 114 in the window frame-shaped opening 115 is the same as that of the coil spring set 14 of the first embodiment. The coil spring set 114 is composed of a first coil spring 132, a second coil spring 134, and an intermediate retainer 136. The first retainer 116 has a bottomed recess 140 for accommodating the first coil spring 132 and the intermediate retainer 136. The bottomed recess 140 is formed in two stages of a large diameter portion 140-1 and a small diameter portion 140-2 from the opening end. One end of the first coil spring 132 abuts against the bottom surface 140-2a of the small diameter portion 140-2, and the other end abuts against the opposite surface 136-1 of the intermediate retainer 136. The gap between the bottom surface 140-1a of the large diameter portion 140-1 and the opposing surface 136-1 of the intermediate retainer 136 remaining in the initial setting state is slightly larger than the height of the protrusion 136-2 of the intermediate retainer 136 inserted into the first coil spring 132 to retain the first coil spring 132. Therefore, when the amount of movement between the first and second retainers 116 and 118 is small, the first coil spring 132 and the second coil spring 134 act in series and the overall rigidity is low. After the intermediate retainer 136 is seated on the opposing surface 140-1a of the first retainer 116, the second coil spring 134 alone has high rigidity related to the suppression of rotational fluctuations. In addition, the intermediate retainer 136 has a flange 136-3 on the radially outer side. While the flange 136-3 retains the end of the second coil spring 134, it can also help the intermediate retainer 136 to slide smoothly according to the deformation. In addition, the second retainer 118 has a cylindrical bottomed opening 142 that opens to the first retainer 116 side. The end portion of the second coil spring 134 on the side separated from the intermediate retainer 136 abuts against the bottom surface 142 - 1 of the cylindrical bottomed opening 142 .

[0065] In order to explain the sliding action of the first retainer 116 and the second retainer 118 when the window frame-shaped opening 115 rotates, the inner arc-shaped surface of the two main body plates 160 constituting the input member 110 becomes the guide portion 122 (equivalent to the guide portion 22 of the first embodiment) for the first retainer 116 and the second retainer 118, but this can only be seen at the cut-away portion between the section lines a and b. The angle range of the guide portion 122 is Figure 4A The same as the middle guide 22, but in Fig.10In the figure, the upstream locking portion 122-1 and the downstream locking portion 122-2 of the adjacent guide portion 122 can be seen (see also Fig.12 The locking portions 122 - 1 and 122 - 2 are integral parts of the main body plate 160 constituting the input member 110 .

[0066] The action of the first retainer 116 and the second retainer 118 during torsional vibration is the same as that of the first embodiment. In the torque-free state, the first retainer 116 and the second retainer 118 cause elastic deformation of the coil spring kit 114 that abuts against the locking portions 122-1, 122-2 that are close to and opposite to the guide portion 122 and the driving portions 128-1, 128-2 that are close to and opposite to the extension plate 128, thereby suppressing rotational changes. Under the low torsional rigidity caused by the series action of the first coil spring 132 and the second coil spring 134 that constitute the coil spring kit 114 at low torque, and under the high torsional rigidity that invalidates the first coil spring 132 at normal torque (to prevent bottoming out), the suppression of rotational changes is the same as that of the first embodiment. That is, Fig.13 The state of the coil spring assembly 114 in a torque-free state between the first retainer 116 and the second retainer 118 is shown.

[0067] The increase in torsional torque between the first retainer 116 and the second retainer 118 causes elastic deformation under low torsional rigidity under the series arrangement of the first coil spring 132 and the second coil spring 134. The widening of the low torsional rigidity caused by the series arrangement can reliably achieve reduction in operating noise at low torque such as in the idling operation area.

[0068] The increase in torsional torque eventually causes the intermediate retainer 136 to sit on the opposite surface 140-1a of the large diameter portion 140-1 of the bottomed recess 140 of the first retainer 116, thereby disabling the first coil spring 132. In the initial setting state, the length of the protrusion 136-2 of the intermediate retainer 136 is set to be less than the gap between the intermediate retainer 136 and the opposite surface 140-1a, so that the first coil spring 132 can be protected because it does not touch the bottom when it is disabled. In this way, after the shift from the low torque operation to the normal torque operation region, the second coil spring 134 alone performs a vibration-damping operation at a high torsional rigidity.

[0069] In the second embodiment, the window frame-like opening 115 for supporting the first and second retainers 116 and 118 can also be formed in the output member 112. In this case, the output member is an aligned structure formed by two axially separated plates, and the input member 110 composed of one piece is arranged between the combined structure of the two plates.

[0070] Through the above embodiments and variations, the spring kits 14, 114 are constructed to have only one end with an intermediate retainer 36, 136 that connects the short-sized first coil spring 32, 132 with the long-sized second coil spring 34, 134 and slides in the first retainer 16, 116. However, although not shown in the figure, the following structure is also possible: short-sized springs are also provided at the other end of the spring kit 14, 114, that is, short-sized springs and intermediate retainers that connect the short-sized springs with the long-sized springs and slide in the second retainer 18, 118 are provided at both ends. The related structure has the following benefits: in order to ensure that the torsion angle in the low-rigidity area is wider and the torsion angle is dispersed, the sliding distance of each intermediate retainer can also be relatively shortened.

[0071] Moreover, the short-sized first coil spring 32, 132 (the first elastic member of the present invention) can be replaced by a disc spring, which is configured to abut against the bottom surface of the bottomed recess of the first and / or second retainer at one end and abut against the intermediate retainer at the other end. Explanation of symbols

[0072] 10; 110…Input component 12; 112… output components 14; 114… coil spring kit 16, 18…Retainer 16-1, 18-1…Guide groove 16-2, 18-2…Flat surface 16-3, 18-3…plate-like protrusions 16-4, 18-4…Axial bearing surface 16-5, 18-5…Terrace-shaped protrusions 16-6, 18-6…Vertical groove 16-7, 18-7…Inner circumference 16-8, 18-8…arc-shaped protrusions 16-11, 18-11…Axial bearing surface 16-14, 18-14…Inner wall 22; 122…Guide 22-1, 22-2; 122-1, 122-2 ... end surface of the guide portion 24; 124…Support plate 24-1; 124-1 ... Outer peripheral surface of the support plate 28; 128…extending board 28-1, 28-2; 128-1, 128-2... Pressurization part of the extended plate 30; 130…Spline shaft 32…First coil spring 34…No.? Coil Spring 36…Intermediate retainer 36-2…Support protrusion 36-3…Eaves 36-4…Frustum of cone 40 ... bottomed recess of first retainer 40-1…Large diameter part 40-1a…The bottom surface of the large diameter part 40-2…Small trail section 40-2a…Bottom of small diameter part 42 ... Bottomed concave portion of the second retainer 42-1…Bottom O…Center line of rotation.

Claims

1. A rotation variation reduction device, characterized in that: The torsional vibration reduction device comprises: an input member for rotationally connecting with the driving side; an output member having the same rotation center line as the input member and for rotationally connecting with the driven side; and an elastic body arranged in the circumferential direction between the input member and the output member; the torsional vibration reduction device reduces the rotational fluctuation when the input member of the driving side drives the output member of the driven side by the circumferential elastic deformation of the elastic body; One of the input member and the output member includes a guide portion, which extends from the radially outer side to the elastic body so that the rotation center line is the same as that of the input member and the output member and is arc-shaped, and the other of the input member and the output member includes a central support plate and an extension plate extending from the support plate to between the elastic bodies adjacent in the circumferential direction, each guide portion forms a locking portion extending radially inward at both ends in the circumferential direction, and each extension plate forms a pressurizing portion extending radially outward at both ends in the circumferential direction; The invention also comprises a retainer, which is respectively arranged at both ends of the elastic body in the circumferential direction, has an axial and radial support structure for the input member and / or the output member, and can move in the circumferential direction along the guide portion, the retainer has bottomed recessed portions for respectively accommodating the opposite end portions of the elastic body in the circumferential direction, and the retainer is arranged opposite to the locking portion close to the guide portion and the pressurizing portion close to the extension plate at the pressure receiving portion which is one end of the side separated from the bottomed recessed portion in the circumferential direction; The elastic body includes a first elastic member with low rigidity, a second elastic member with high rigidity, and an intermediate member connecting the first elastic member and the second elastic member in series at at least one end of the retainer, and the ends of the first elastic member, the intermediate member, and the second elastic member on the side close to the intermediate member are accommodated in the bottomed recessed parts of the corresponding retainer, and the intermediate member is slidably supported by the radially opposing surface of the bottomed recessed parts of the retainer; In the paired retainers, the retainer located on the upstream side in the torque transmission direction abuts against the pressure-applying portion close in the circumferential direction, and moves toward the retainer located on the downstream side in the torque transmission direction and locked by the locking portion close to the guide portion. In a transmission torque region lower than the usual transmission torque, the retainer resists a low elastic force based on the series composite value of the elastic modulus of the first elastic member and the elastic modulus of the second elastic member, and in the usual transmission torque region, resists a high elastic force based on the high elastic modulus value brought by the second elastic member alone, and moves in the circumferential direction along the guide portion.

2. The rotation fluctuation reduction device according to claim 1, characterized in that: The first elastic member and the second elastic member are respectively constituted as a first coil spring and a second coil spring, and include: a first retaining portion, which retains the first coil spring without bottoming out before transferring to the second coil spring to act alone; and a second retaining portion, which retains the end of the second coil spring on the side close to the first coil spring when the retainer of the intermediate member slides during series action and individual action.

3. The rotation fluctuation reduction device according to claim 2, characterized in that: The first retaining portion includes: a small diameter portion, which is formed in the center of the bottom surface of the bottomed recessed portion of the retainer and accommodates one end of the first coil spring from the outer diameter side; and a protrusion, which is formed on the surface of the intermediate member on the side separated from the second coil spring and is inserted into the other end of the first coil spring.

4. The rotation fluctuation reduction device according to claim 2, characterized in that: The first retaining portion includes: a small diameter portion formed at the center of the bottom surface of the bottomed recess of the retainer and accommodating one end of the first coil spring; and a recess formed on the surface of the intermediate member on the side separated from the second coil spring and accommodating the other end of the first coil spring.

5. The rotation fluctuation reduction device according to claim 2, characterized in that: The first retaining portion includes: a protrusion formed at the center of the bottom surface of the bottomed recess of the retainer in a manner protruding toward the intermediate member and into which one end of the first coil spring is inserted; and a recess formed on the surface of the intermediate member on the side separated from the second coil spring and accommodating the other end of the first coil spring.

6. The rotation fluctuation reduction device according to claim 2, characterized in that: The second retaining portion is a flange portion that abuts the inner diameter portion of the intermediate member on the side where the first coil spring is separated and the end of the second coil spring on the side close to the first coil spring, thereby retaining the second coil spring and abutting the inner surface of the bottomed recess of the retainer to be slidable in the circumferential direction.

7. The rotation fluctuation reduction device according to claim 2, characterized in that: The second retaining portion is a truncated cone-shaped protrusion that is inserted into a central opening of the second coil spring on the first coil spring separation side of the intermediate member.

8. The rotation variation reduction device according to any one of claims 1 to 7, characterized in that: At least the first holder and the second holder among the intermediate member and the first holder and the second holder are injection-molded products using synthetic resin as a raw material.

9. The rotation variation reduction device according to any one of claims 1 to 7, characterized in that: The support structure is a self-contained support structure composed of a groove-protrusion interlocking structure and a surface-to-surface abutment structure, wherein the groove-to-protrusion interlocking structure and the surface-to-surface abutment structure are formed between the surfaces of the first retainer and the second retainer that are opposite to the input member and the output member, and are used to support the first retainer and the second retainer themselves axially and radially on the input member and the output member, and the relative movement of the input member and the output member corresponding to the rotational change will cause the circumferential relative movement between the first retainer and the second retainer supported by the self-contained support structure corresponding to the elastic force.

10. The rotation variation reduction device according to any one of claims 1 to 7, characterized in that: The supporting structure is constituted as an axially aligned structure of multiple plates, that is, in order to support the first retainer and the second retainer in the axial and radial directions, one of the input member and the output member places the other of the input member and the output member in the middle, and the relative movement of the other of the input member and the output member relative to one of the input member and the output member corresponding to the rotational change will cause the first retainer and the second retainer supported by one of the input member and the output member to have a relative movement in the circumferential direction corresponding to the elastic force of the elastic body.

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