Damper device

Abstract

A damper device comprising a hub body 11, a hub flange 15, an input-side rotating member having a first plate 19 and a second plate 21, an integrated bush that is positioned between the first plate 19 and a set of the hub body 11 and the hub flange 15 and that rotates integrally with the first plate 19, an inner peripheral bush 31 that is positioned between the second plate 21 and the hub body 11 and that rotates integrally with the second plate 21, an inner peripheral disk spring 34 that is positioned between the inner peripheral bush 31 and the second plate 21, an outer peripheral bush 35 that is positioned between the second plate 21 and the hub flange 15 and that integrally rotates with the second plate 21, and an outer peripheral disk spring 38 that is positioned between the outer peripheral bush 35 and the second plate 21.

Description

Damper Device

[0001] The present invention relates to a damper device.

[0002] Patent Document 1 (JP 2021-004637 A) discloses a clutch disc as a damper device. The clutch disc includes a clutch plate, a retaining plate, a splined hub, and a hub flange. Furthermore, a coil spring elastically connects the clutch plate and the splined hub in the rotational direction. When the clutch plate and the splined hub rotate relative to each other, several components generate hysteresis torque. The splined hub and the hub flange are rotatable relative to each other in a first torsion angle region. Furthermore, they rotate synchronously in a second torsion angle region larger than the first torsion angle region. The entire contents of Patent Document 1 are incorporated herein by reference.

[0003] The several components that generate hysteresis torque in Patent Document 1 include a first bushing that rotates in synchronization with the splined hub. The several components that generate hysteresis torque also include a first friction member that rotates in synchronization with the hub flange. The first friction member is in frictional contact with the first bushing to generate first hysteresis torque. The first friction member is also in frictional contact with the clutch plate to generate second hysteresis torque. Since the first hysteresis torque and second hysteresis torque are generated using a single friction member in this way, the structure of the clutch disc can be simplified.

[0004] Japanese Patent Application Laid-Open No. 2021-004637

[0005] An object of the present invention is to provide another method for simplifying the structure of a damper device by generating two types of hysteresis torque with one member.

[0006] a hub flange elastically coupled to the hub body in a rotational direction on the outer circumferential side of the hub body; and an input side rotating member elastically coupled to the hub flange in a rotational direction on the outer circumferential side of the hub flange, wherein the input side rotating member has a first plate and a second plate that rotate integrally with each other, and the set of hub body and hub flange is located between the first plate and the second plate; the damper device further comprises: an integrated bushing located between the first plate and the set of hub body and hub flange and rotating integrally with the first plate; an inner bushing located between the second plate and the hub body and rotating integrally with the second plate; an inner disc spring located between the inner bushing and the second plate; an outer peripheral bushing located between the second plate and the hub flange and rotating integrally with the second plate; and an outer peripheral disc spring located between the outer peripheral bushing and the second plate. a damper device in which the inner disc spring presses the inner bushing, the hub body, and the integrated bushing toward the first plate, causing frictional contact between the inner bushing and the hub body and between the hub body and the inner region of the integrated bushing, respectively, wherein the frictional contact on the hub body generates a first hysteresis; and the outer disc spring presses the outer bushing, the hub flange, and the integrated bushing toward the first plate, causing frictional contact between the outer bushing and the hub flange and between the hub flange and the outer region of the integrated bushing, respectively, wherein the frictional contact on the hub flange generates a second hysteresis.

[0007] The present invention simplifies the structure of the damper device by using a component that integrates an inner bushing that makes frictional contact with the hub body and an outer bushing that makes frictional contact with the hub flange.

[0008] FIG. 1 is a partial cross-sectional view of a damper device. FIG. 2 is a front view of a hub body and a hub flange according to a first embodiment. FIG. 3 is a front and back perspective view of an integrated bushing according to the first embodiment. FIG. 4 is a front and back perspective view of an inner peripheral bushing according to the first embodiment. FIG. 5 is a front and back perspective view of an outer peripheral bushing according to the first embodiment. FIG. 6 is an exploded view of a damper device according to the first embodiment. FIG. 7 is a front and back perspective view of an integrated bushing according to a second embodiment. The left side of FIG. 8 is a graph showing the time change in input torque. The right side is a graph showing the change in tamper torque according to the torsion angle between the input shaft and the output shaft according to a reference example. The left side of FIG. 9 is a graph showing the time change in input torque. The right side is a graph showing the change in tamper torque according to the torsion angle between the input shaft and the output shaft according to a second embodiment. FIG. 10 is a graph showing the change in gain magnitude according to the input frequency according to the second embodiment. FIG. 11 is a partial cross-sectional view of an integrated bushing according to a third embodiment. FIG. 12 shows the change in load magnitude received by the friction surface between the hub flange and the integrated bushing according to displacement of the hub flange from its mounting position in the third embodiment.

[0009] FIG. 1 shows a partial cross section of a damper device 10. The damper device 10 is also called a torsional damper or a dynamic damper. The damper device 10 transmits torque input from an input side to an output side. An input shaft is assumed to be on the left side of the figure. An output shaft coaxial with the input shaft is assumed to be on the right side of the figure. The damper device 10 damps torque fluctuations. Here, the term torque fluctuation refers to fluctuations or vibrations of torque. Torque fluctuations may be periodic or transient. The damper device 10 damps torque fluctuations while quickly responding to intended increases or decreases in torque and transmitting them from the input shaft to the output shaft.

[0010] In this embodiment, the damper device 10 shown in Figure 1 will be described as being used in a clutch disc provided between an engine and a transmission. The damper device 10 includes an output rotating member having a hub body 11, also called an inner hub, and a hub flange 15, also called an outer hub. The hub body 11 may have splines that engage with an output shaft 40. The shaft 40 is, for example, an input shaft for the transmission.

[0011] 1 is elastically connected to the hub body 11 in the rotational direction on the outer periphery of the hub body 11. For example, the hub body 11 and the hub flange 15 are connected by a spring 13.

[0012] The damper device 10 shown in Figure 1 includes a clutch plate 19, which is a first plate. The damper device 10 further includes a retaining plate 21, which is a second plate. The damper device 10 includes an input side rotating member made up of the clutch plate 19 and the retaining plate 21. The clutch plate 19 and the retaining plate 21 rotate integrally. The clutch plate 19 and the retaining plate 21 are connected by, for example, a pin (not shown). A cushioning plate (not shown) may be attached to the outer periphery of the clutch plate 19.

[0013] 1, a retaining plate 21 of the input side rotation member is elastically connected to the hub flange 15 in the rotational direction on the outer periphery side of the hub flange 15. For example, the hub flange 15 and the retaining plate 21 are connected by a spring 17.

[0014] As shown in FIG. 1, the set of hub body 11 and hub flange 15 is positioned between a clutch plate 19 and a retaining plate 21.

[0015] 1 , the damper device 10 includes an integrated bushing 23. The integrated bushing 23 is located between the hub body 11 and the hub flange 15. The integrated bushing 23 rotates integrally with the clutch plate 19. For this purpose, the integrated bushing 23 has, for example, a protrusion 24. For example, the protrusion 24 is fitted into a notch or hole in the clutch plate 19.

[0016] 1, the integrated bushing 23 has an inner peripheral region 25 and an outer peripheral region 27. The inner peripheral region 25 faces the hub body 11. The outer peripheral region 27 faces the hub flange 15.

[0017] As shown in Figure 1, the damper device 10 includes an inner bushing 31 and an inner disc spring 34. The inner bushing 31 is located between the retaining plate 21 and the hub body 11. The inner disc spring 34 is located between the inner bushing 31 and the retaining plate 21. The inner bushing 31 rotates integrally with the retaining plate 21. For this reason, the inner bushing 31 has, for example, a protrusion 32. For example, the protrusion 32 is fitted into a notch or hole in the retaining plate 21.

[0018] As shown in Figure 1, the damper device 10 includes an outer circumferential bushing 35 and an outer circumferential disc spring 38. The outer circumferential bushing 35 is located between the retaining plate 21 and the hub flange 15. The outer circumferential disc spring 38 is located between the outer circumferential bushing 35 and the retaining plate 21. The outer circumferential bushing 35 rotates integrally with the retaining plate 21. For this reason, the outer circumferential bushing 35 has, for example, a protrusion 36. For example, the protrusion 36 is fitted into a notch or hole in the retaining plate 21.

[0019] As shown in FIG. 1 , the inner disc spring 34 presses the inner bushing 31, hub body 11, and integrated bushing 23 toward the clutch plate 19. This causes frictional contact between the inner bushing 31 and the hub body 11. Furthermore, as shown in the figure, the back surface of the integrated bushing 23 is supported by the surface of the clutch plate 19, and preferably is in close contact with the surface of the clutch plate 19 on the back side of the outer circumferential region 27. In addition, the retaining plate 21 and the clutch plate 19 are integral in the axial direction. Therefore, the hub body 11 and integrated bushing 23 are pressed toward the clutch plate 19, causing frictional contact between the hub body 11 and the inner circumferential region 25 of the integrated bushing 23. As a result, a first hysteresis occurs on the hub body 11.

[0020] 1, the outer disc spring 38 presses the outer bushing 35, the hub flange 15, and the integrated bushing 23 toward the clutch plate 19. This causes frictional contact between the outer bushing 35 and the hub flange 15. Furthermore, frictional contact occurs between the hub flange 15 and the outer peripheral region 27 of the integrated bushing 23. As a result, a second hysteresis loop is generated on the hub flange 15.

[0021] As shown in Figure 1, the inner bushing 31 and the outer bushing 35 are separated on the retaining plate 21 side. Therefore, the inner disc spring 34 and the outer disc spring 38 press independently. By individually selecting the stiffness of these disc springs, the required magnitudes of first hysteresis and second hysteresis can be obtained.

[0022] As shown in Figure 1, the integrated bushing 23 has a structure in which an inner bushing that makes frictional contact with the hub body 11 and an outer bushing that makes frictional contact with the hub flange 15 are integrated into one body. This simplifies the structure of the damper device 10.

[0023] FIG. 2 shows an example of a hub body 11 and hub flange 15 viewed from the front from the input side. The hub flange 15 is located on the outer periphery of the hub body 11. The hub body 11 is tubular, while the hub flange 15 is disc-shaped. The hub body 11 has teeth on its outer periphery. The hub flange 15 has teeth on its inner periphery. These teeth intermesh. There is a gap between these teeth. The magnitude of torsion between the hub body 11 and hub flange 15 is limited to the range of this gap. When this torsion varies, the hub body 11 and hub flange 15 rotate relative to each other.

[0024] As shown in Figure 2, springs 13 are provided alongside the teeth of the hub flange 15 and the hub body 11. The springs 13 connect the hub flange 15 and the hub body 11. The springs 13 absorb the shock of torsional fluctuations between the hub body 11 and the hub flange 15.

[0025] The spring 13 shown in Figure 2 acts as a pre-damper. The spring 13 has lower rigidity than the spring 17 shown in Figure 1. The spring 13 is compressed before the spring 17. When the spring 13 compresses and the teeth of the hub body 11 and hub flange 15 mesh, the spring 13 cannot compress any further, and instead the spring 17 begins to compress. The spring 17 acts as a main damper.

[0026] Preferably, the hub body 11, spring 13, and hub flange 15 shown in Figure 2 are made of metal. Furthermore, the spring 17 shown in Figure 1 is also made of metal. This allows switching between the pre-damper and the main damper using only metal members.

[0027] Figure 3 shows the front and back of the integrated bushing 23. The integrated bushing 23 is ring-shaped. Its central hole accommodates the hub body 11 and shaft 40 shown in Figure 1. As shown on the left side of Figure 3, the integrated bushing 23 has an inner circumferential region 25 and an outer circumferential region 27. The inner circumferential region 25 has a friction surface 26. The outer circumferential region 27 has a friction surface 28. The right side shows the opposite side. The integrated bushing 23 has a protrusion 24 on the back side of the friction surface 26. The integrated bushing 23 is preferably made of resin.

[0028] Figure 4 shows the front and back of the inner bushing 31. The inner bushing 31 is ring-shaped. Its central hole accommodates the hub body 11 and shaft 40 shown in Figure 1. As shown on the left side of Figure 4, the inner bushing 31 has a friction surface 33. The right side shows the opposite surface. The inner bushing 31 has a protrusion 32 on the back side of the friction surface 33. The inner bushing 31 is preferably made of resin.

[0029] Figure 5 shows the front and back of the outer bushing 35. The outer bushing 35 is ring-shaped. Its central hole accommodates the hub body 11, shaft 40, and inner bushing 31 shown in Figure 1. As shown on the left side of Figure 5, the outer bushing 35 has a ring-shaped friction surface 37. The right side shows the opposite side. The outer bushing 35 has a protrusion 36 on the back side of the friction surface 37. The outer bushing 35 is preferably made of resin.

[0030] Returning to Figure 2, as shown in Figure 2, the hub body 11 has a first friction surface 12. The first friction surface 12 is in frictional contact with a friction surface 26 of the inner peripheral region 25 of the integrated bushing 23 shown in Figure 3. The friction surface on the back side of the first friction surface 12 is in frictional contact with a friction surface 33 of the inner peripheral bushing 31 shown in Figure 4. This causes the first hysteresis.

[0031] As shown in Figure 2, the hub flange 15 has a second friction surface 16. The second friction surface 16 is in frictional contact with a friction surface 28 of the outer peripheral region 27 of the integrated bushing 23 shown in Figure 3. The friction surface on the back side of the second friction surface 16 is in frictional contact with a friction surface 37 of the outer peripheral bushing 35 shown in Figure 5. This causes a second hysteresis.

[0032] Figure 6 is an exploded view of the damper device 10. The input shaft is on the left side of the figure, and the output shaft, which is coaxial with the input shaft, is on the right side of the figure. The protrusion 24 of the integrated bushing 23 shown in Figure 3 is fitted into the notch 20 of the clutch plate 19. Therefore, the integrated bushing 23 and the clutch plate 19 rotate together.

[0033] 6, the protrusion 32 of the inner bushing 31 is fitted into the notch 22a of the retaining plate 21. The protrusion 36 of the outer bushing 35 is fitted into the hole 22b of the retaining plate 21. Therefore, the inner bushing 31, the outer bushing 35, and the retaining plate 21 rotate integrally.

[0034] 6, the hub flange 15 rotates relative to the clutch plate 19 and the retaining plate 21. This causes torsion within a predetermined angle range between the hub flange 15 and the clutch plate 19 and the retaining plate 21. The torsion occurs in response to torque fluctuations on the input side.

[0035] 6, when torsion of relative rotation occurs, a first hysteresis occurs between the integrated bushing 23, the hub body 11, and the inner circumferential bushing 31. The first hysteresis attenuates torque fluctuations on the input side, particularly in a range where torsion is small.

[0036] 6, when torsion of the relative rotation occurs, a second hysteresis occurs between the integral bushing 23, the hub flange 15, and the outer circumferential bushing 35. The second hysteresis attenuates torque fluctuations on the input side, particularly in the range where torsion is large.

[0037] FIG. 7 shows the front and back of an integrated bushing 43 according to a second embodiment. The integrated bushing 43 is identical to the integrated bushing 23, except for the following points. The integrated bushing 43 includes an intermediate region 29 between the inner circumferential region 25 and the outer circumferential region 27. The circumferential rigidity of the intermediate region 29 is lower than that of the other regions. The intermediate region 29 may be, for example, spoke-shaped. The intermediate region 29 in the figure is composed of multiple spoke portions 30 and the spaces between these spoke portions 30. From another perspective, by providing circumferentially aligned lightening holes in the intermediate region 29, the remaining portions can be used as spoke portions 30. Providing such lightening holes in the intermediate region 29 reduces the rigidity of the intermediate region 29. It is preferable that such lightening holes penetrate the intermediate region 29 from the front to the back. Furthermore, the intermediate region 29 does not come into frictional contact with either the hub body 11 or the hub flange 15.

[0038] 7, the spoke portions 30 tilt in the circumferential direction, causing the intermediate region 29 to twist. This causes relative rotation between the inner circumferential region 25 and the outer circumferential region 27. At this time, the way in which hysteresis occurs changes depending on the torsional angle of the input shaft and the output shaft.

[0039] The left side of Figure 8 is a graph showing the change in input torque over time. Torque fluctuations can be seen in the input torque. The input torque periodically increases and decreases over time. The input torque in this graph tends to remain at a small value, neither increasing nor decreasing.

[0040] The right side of Figure 8 is a graph showing the hysteresis loop of the damper torque generated by the damper device according to the torsion angle between the input shaft and output shaft of the damper device. The damper torque on the vertical axis represents the output torque. In the graph, the hysteresis loop is broken in the middle. The difference between the damper torque during loading and the damper torque during unloading is the hysteresis torque.

[0041] The graph on the right side of Figure 8 explains how the second hysteresis occurs in the damper device according to the hypothetical example. Explaining this hypothetical example with reference to Figure 1, the integrated bushing 23 does not elastically deform at all in the inner peripheral region 25, the outer peripheral region 27, and the region therebetween.

[0042] In the graph on the right side of Figure 8, damper torsional behavior B1 shows the range of possible damper torque and torsion angle when the input torque fluctuates greatly. Damper torsional behavior B1 represents the process in which damper hysteresis, i.e., contact friction at the friction surfaces, occurs due to fluctuations in input torque, and the torsion angle also increases or decreases.

[0043] In the graph on the right side of Figure 8, torque shift S1 indicates the range of possible damper torque and torsional angle in response to small fluctuations in input torque shown in the graph on the left side. Torque shift S1 represents the process in which fluctuations in input torque cause damper hysteresis, i.e., contact friction at the friction surfaces, but no further increase in torsional angle occurs. As mentioned above, the input torque tends to remain small and does not increase or decrease, so the torsional angle remains constant without increasing or decreasing. Therefore, torque shift S1, unlike damper torsional behavior B1, resembles a wall. In other words, damper torque changes only within the wall. The damper device cannot effectively damp input torque fluctuations, resulting in rattle noise under adverse conditions.

[0044] In this embodiment, it is possible to reduce the so-called wall stiffness in the torque shift S1 shown in the graph on the right side of Fig. 8. This will be explained with reference to Fig. 9.

[0045] The left side of Fig. 9 is a graph showing the time change of input torque, similar to the left side of Fig. 8. The right side of Fig. 9 is a graph showing a hysteresis loop, similar to the right side of Fig. 8. The graph on the right side of Fig. 9 explains how the second hysteresis occurs in the damper device according to this embodiment. In the integrated bushing 43 shown in Fig. 7, the middle region 29 elastically deforms prior to the inner circumferential region 25 and the outer circumferential region 27. This is because the rigidity of the middle region 29 is low.

[0046] In the graph on the right side of Figure 9, damper torsional behavior B2 shows the same range and stroke as damper torsional behavior B1 shown in Figure 8. Furthermore, torque shift S2 shows the same range and stroke as torque shift S1 shown in Figure 8. As described above, the input torque tends to remain small, neither increasing nor decreasing. What makes torque shift S2 different from torque shift S1 is that even with this level of input torque, the torsion in the intermediate region 29 shown in Figure 7 changes. Therefore, torque shift S2 slopes in the same way as damper torsional behavior B2. In other words, both the damper torque and the torsional angle change as if running up and down a slope. This allows the damper device to effectively damp fluctuations in input torque, thereby suppressing rattle noise under various conditions.

[0047] Fig. 10 is a graph showing the change in gain magnitude according to the frequency of the input shaft. Resonance frequency R1 is the resonant frequency at which the gain becomes maximum in the damper device of the hypothetical example shown in Fig. 8. Resonance frequency R2 is the resonant frequency at which the gain becomes maximum in the damper device of this embodiment shown in Fig. 9.

[0048] In Figure 10, the resonance frequency R2 is lower than the resonance frequency R1. Therefore, the gain begins to decrease at lower frequencies. Therefore, the graph shows that with the damper device of this embodiment, a damping effect can be obtained even when the engine speed is low and the torque is small.

[0049] Figure 11 is a partial cross-sectional view of the integrated bushing 53 according to this embodiment. The integrated bushing 53 includes an inner circumferential region 55, an outer circumferential region 57, and an intermediate region 59. The inner circumferential region 55 and the outer circumferential region 57 function in the same manner as the inner circumferential region 25 and the outer circumferential region 27 of the integrated bushing 23 shown in Figures 1 and 2. The intermediate region 59 functions in the same manner as the intermediate region 29 of the integrated bushing 43 shown in Figure 7. Next, the features of the integrated bushing 53 according to this embodiment will be described.

[0050] The inner circumferential region 55 and the outer circumferential region 57 shown in FIG. 11 are supported by the clutch plate 19. However, as shown by the dashed line, before the outer circumferential region 57 is pressed toward the clutch plate by the hub flange 15, the outer circumferential region 57 is floating above the clutch plate 19. As shown, a gap 60 is provided between the clutch plate 19 and the outer circumferential region 57. The intermediate region 59 also bends toward the hub flange 15. Here, as shown by the solid line, when the outer circumferential region 57 is pressed into the gap 60 and the bend of the intermediate region 59 is straightened, the intermediate region 59 exerts an elastic restoring force. Because the intermediate region 59 has an axial elastic force, it acts as a disc spring with the inner circumferential region 55 as a fulcrum, for example, and presses the outer circumferential region 57 toward the hub flange 15. Furthermore, when the gap 60 disappears and the back side of the outer circumferential region 57 is in contact with the surface of the clutch plate 19, the clutch plate 19 supports the outer circumferential region 57. At this time, the outer circumferential region 57 is also pressed toward the hub flange 15.

[0051] As shown in Figure 11, the outer peripheral region 57 has a friction surface 58. The friction surface 58 is in frictional contact with the hub flange 15. As shown by the two-dot chain line, when the friction surface 58 is not pressed against the hub flange 15, the friction surface 58 has an inclination that approaches the hub flange 15 the further it is from the center of the integrated bushing 53. This inclination becomes smaller when the friction surface 58 is pressed against the hub flange 15. As the inclination of the friction surface 58 becomes smaller and the entire friction surface 58 approaches the friction surface of the hub flange 15, they come into good frictional contact.

[0052] The graph in Figure 12 shows the relationship between the amount of displacement of the hub flange and the load applied to the hub flange. The horizontal axis of the graph represents the displacement when the hub flange 15 is pressed toward the integrated bushing 53 from the standard mounting position of the hub flange 15 as shown in Figure 11. The vertical axis represents the magnitude of the load applied between the friction surface of the hub flange 15 and the friction surface 58 of the outer circumferential region 57 of the integrated bushing 53.

[0053] Here, due to the action of the outer circumferential disc spring 38 shown in Figure 11, a load is applied to the integrated bushing 53. As a result, the required load can be obtained within a predetermined range of displacement, as shown in the graph in Figure 12. Furthermore, if the outer circumferential region 57 of the integrated bushing 53 shown in Figure 11 becomes worn and thin, it can be seen that frictional contact between the two is not possible unless the hub flange 15 undergoes further large displacement. However, if the hub flange 15 undergoes further large displacement, the outer circumferential disc spring 38 will no longer be able to follow the displacement of the hub flange 15. For this reason, the graph in Figure 12 shows that the obtainable load drops significantly.

[0054] Here, as shown by the large arrow in Figure 11, the intermediate region 59 acts as a disc spring, pushing the outer peripheral region 57 back toward the hub flange 15. For this reason, even if the outer peripheral region 57 wears and becomes thinner, the displacement of the hub flange 15 can be kept within the range in which the required load is obtained, as shown in the graph in Figure 12. The benefit of this intermediate region 59 can be obtained even if the outer peripheral bushing 35 becomes thinner.

[0055] The damper device of the above-described embodiment and example reduces the shock of torque fluctuations on the input side. Therefore, this damper device is suitable as a damper for a clutch disc that transmits engine torque. However, the use of this damper device is not limited to this, and it can be applied to various torque transmission systems such as a lock-up clutch associated with a torque converter, a torque transmission system from the engine to the motor in a hybrid vehicle, and a torque transmission system from the motor to the transmission in an electric vehicle.

[0056] Summary of this embodiment The damper device 10 of this embodiment has at least the following configuration. The damper device 10 includes a hub body 11; a hub flange 15 that is elastically connected to the hub body 11 in the rotational direction on the outer circumferential side of the hub body 11; and an input side rotating member that is elastically connected to the hub flange 15 in the rotational direction on the outer circumferential side of the hub flange 15. Here, the input side rotating member has a clutch plate 19 which is a first plate and a retaining plate 21 which is a second plate that rotate integrally. Furthermore, the set of the hub body 11 and the hub flange 15 is located between the clutch plate 19 and the retaining plate 21.

[0057] The damper device 10 further includes an integrated bushing 43 located between the clutch plate 19 and the set of hub body 11 and hub flange 15 and rotating integrally with the clutch plate 19; an inner bushing 31 located between the retaining plate 21 and hub body 11 and rotating integrally with the retaining plate 21; an inner disc spring 34 located between the inner bushing 31 and the retaining plate 21; an outer bushing 35 located between the retaining plate 21 and hub flange 15 and rotating integrally with the retaining plate 21; and an outer disc spring 38 located between the outer bushing 35 and the retaining plate 21.

[0058] The inner disc spring 34 presses the inner bushing 31, the hub body 11, and the integrated bushing 43 toward the clutch plate 19, causing frictional contact between the inner bushing 31 and the hub body 11 and between the hub body 11 and the inner peripheral region 25 of the integrated bushing 43. Here, the frictional contact on the hub body 11 generates a first hysteresis.

[0059] The outer circumferential disc spring 38 presses the outer circumferential bushing 35, the hub flange 15, and the integrated bushing 43 toward the clutch plate 19, causing frictional contact between the outer circumferential bushing 35 and the hub flange 15 and between the hub flange 15 and the outer circumferential region 27 of the integrated bushing 43. Here, the frictional contact on the hub flange 15 generates a second hysteresis.

[0060] According to this configuration, two types of hysteresis torque are generated using one member, thereby simplifying the structure of the damper device 10.

[0061] In this embodiment, it is also preferable that the integrated bushing 43 has an intermediate region 29 between the inner circumferential region 25 and the outer circumferential region 27 , the intermediate region 29 having lower rigidity than the inner circumferential region 25 and the outer circumferential region 27 .

[0062] With this configuration, the damper device 10 can effectively damp fluctuations in input torque.

[0063] In this embodiment, it is preferable that at least a part of the region between the inner peripheral region 25 and the outer peripheral region 27 of the integrated bushing 43 is formed in a spoke shape.

[0064] With this configuration, the damper device 10 can effectively damp fluctuations in input torque.

[0065] In addition, in this embodiment, it is preferable that the integrated bushing 53 has an intermediate region 59 between the inner circumferential region 25 and the outer circumferential region 57; the inner circumferential region 25 and the outer circumferential region 57 of the integrated bushing 53 are supported by the clutch plate 19; the intermediate region 59 has elastic force in the axial direction, thereby pressing the outer circumferential region 57 toward the hub flange 15; and the surface of the outer circumferential region 57 that comes into frictional contact with the hub flange 15 has an inclination that approaches the hub flange 15 as it moves away from the center of the integrated bushing 53 when not pressed toward the hub flange 15.

[0066] With this configuration, even if the outer peripheral region 57 wears and becomes thinner, the displacement of the hub flange 15 can be limited to a range in which the required load can be obtained.

[0067] This application is based on Japanese Patent Application No. 2023-203248 entitled "Damper Device" filed on November 30, 2023, and claims the benefit of priority from this Japanese patent application, the entire contents of which are incorporated herein by reference.

[0068] 10: Damper device 11: Hub body 15: Hub flange 21: Retaining plate 23: Integrated bushing 25: Inner peripheral region 27: Outer peripheral region 29: Intermediate region 31: Inner peripheral bushing 34: Inner peripheral disc spring 35: Outer peripheral bushing 38: Outer peripheral disc spring 43: Integrated bushing 53: Integrated bushing 55: Inner peripheral region 57: Outer peripheral region 59: Intermediate region

Claims

1. A damper device comprising: a hub body; a hub flange elastically connected to the hub body in a rotational direction on the outer circumferential side of the hub body; and an input side rotating member elastically connected to the hub flange in a rotational direction on the outer circumferential side of the hub flange, wherein the input side rotating member has a first plate and a second plate which rotate integrally, and the set of the hub body and the hub flange is located between the first plate and the second plate; the damper device further comprising: an integrated bush located between the first plate and the set of the hub body and the hub flange and rotating integrally with the first plate; an inner bush located between the second plate and the hub body and rotating integrally with the second plate; an inner disc spring located between the inner bush and the second plate; an outer circumferential bush located between the second plate and the hub flange and rotating integrally with the second plate; and an outer circumferential disc spring located between the outer circumferential bush and the second plate. a damper device in which the inner disc spring presses the inner bush, the hub body, and the integrated bush toward the first plate, causing frictional contact between the inner bush and the hub body and between the hub body and the inner region of the integrated bush, respectively, wherein the frictional contact on the hub body generates a first hysteresis; and the outer disc spring presses the outer bush, the hub flange, and the integrated bush toward the first plate, causing frictional contact between the outer bush and the hub flange and between the hub flange and the outer region of the integrated bush, respectively, wherein the frictional contact on the hub flange generates a second hysteresis.

2. The damper device according to claim 1, wherein the integrated bush has an intermediate region between the inner circumferential region and the outer circumferential region, the intermediate region having a lower rigidity than the inner circumferential region and the outer circumferential region.

3. The damper device according to claim 1 or 2, wherein at least a portion of a region between the inner peripheral region and the outer peripheral region of the integrated bush is formed in a spoke shape.

4. A damper device as claimed in any one of claims 1 to 3, wherein the integrated bush has an intermediate region between the inner circumferential region and the outer circumferential region, the inner circumferential region and the outer circumferential region of the integrated bush are supported by the first plate, the intermediate region has an axial elastic force to press the outer circumferential region towards the hub flange, and a surface of the outer circumferential region that comes into frictional contact with the hub flange has an inclination that approaches the hub flange the further away from the center of the integrated bush when not pressed towards the hub flange.

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