Suspension device

Abstract

A suspension device mounted on a vehicle includes a motor, a torsion bar, a coupling member, and a support member. The torsion bar connects a first portion to an output shaft of the motor. The connecting member is configured so as to connect the second portion of the torsion bar and the unsprung member. The support member is configured so as to support the motor on a sprung structure via a first elastic member, and is disposed so that the motor and the torsion bar integrally rotate in a direction orthogonal to the first direction with the position of the support member as a rotation center. The first direction is an axial direction of the torsion bar.

Description

Technical Field

[0001] The present disclosure relates to a suspension device mounted on a vehicle. Background Art

[0002] Japanese Patent Application Laid-Open No. 2008-308098 discloses an active suspension device for a vehicle. The active suspension device is configured to enable the wheel to actively move up and down by using an actuator. More specifically, one end of a torsion portion is connected to an output rotating shaft of the actuator. The other end of the torsion portion is connected to a suspension arm via a connecting rod. If the torsion portion is twisted by the actuator, its torsional moment is converted into a force in the up and down direction via the connecting rod and applied to the suspension arm. In Japanese Patent Application Laid-Open No. 2008-308098, the actuator is supported by a rubber bushing at two locations separated along the axial direction of the torsion portion.

[0003] In an active suspension device that utilizes a torsion bar, the suspension stiffness increases by an amount corresponding to the stiffness of the torsion bar. For example, an increase in suspension stiffness is not desirable for controlling high-frequency vibrations. In order to suppress the increase in suspension stiffness, it is also possible to consider making the torsion bar itself softer. However, if the torsion bar is made thinner, it is easy for the torsion bar to break due to insufficient strength. In the case of making the torsion bar longer, problems such as increased weight and increased size arise. If the torsional stiffness of the torsion bar itself becomes lower, the problem of insufficient strength still arises. Thus, although reducing the suspension stiffness is important, it is not simple. Summary of the invention

[0004] The present disclosure provides a suspension device that can effectively reduce suspension stiffness in an active suspension device using a torsion bar.

[0005] The suspension device involved in the first form of the present disclosure is mounted on a vehicle. The suspension device includes a motor, a torsion bar, a connecting member, and a supporting member. The torsion bar is connected to a first portion on an output shaft of the motor. The connecting member is configured to connect a second portion of the torsion bar to an unsprung member. The supporting member is configured to support the motor on a sprung structure via a first elastic member, and is configured so that the motor and the torsion bar rotate integrally in a direction orthogonal to a first direction with the position of the supporting member as a rotation center. The first direction is an axial direction of the torsion bar.

[0006] In the suspension device according to the first aspect of the present disclosure, the support member may include a first support member and a second support member separated from each other in a second direction orthogonal to the first direction.

[0007] In the suspension device according to the first aspect of the present disclosure, the second portion of the torsion bar may be located on the first side when viewed from the motor. The support member may be located closer to the end of the second side of the motor than to the end of the first side of the motor. The second side of the motor may be the opposite side of the first side.

[0008] In the suspension device according to the first aspect of the present disclosure, the support member may be located at the end portion on the second side of the motor.

[0009] It can also be constructed that, based on the suspension device involved in the first form of the present disclosure, the above-mentioned support component includes: an outer tube, fixed to one side of the above-mentioned motor and the above-mentioned sprung structure; an inner tube, fixed to the other side of the above-mentioned motor and the above-mentioned sprung structure; and the above-mentioned first elastic component, sandwiched between the above-mentioned outer tube and the above-mentioned inner tube.

[0010] In the suspension device according to the first aspect of the present disclosure, the axial direction of the outer tube and the inner tube may be a direction intersecting the first direction.

[0011] In the suspension device according to the first aspect of the present disclosure, the torsion bar may be not supported by the sprung structure between the first portion and the second portion.

[0012] The suspension device according to the first aspect of the present disclosure may further include a rod support member configured to support the torsion bar to the sprung structure via a second elastic member.

[0013] The suspension device involved in the second form of the present disclosure is mounted on a vehicle. The suspension device includes a motor, a torsion bar, a connecting member, and a supporting member. The torsion bar is connected to the first part of the output shaft of the motor. The connecting member is configured to connect the second part of the torsion bar to the unsprung member. The supporting member is configured to support the motor on the sprung structure via the first elastic member and is located at a position in the first direction. The first direction is the axial direction of the torsion bar.

[0014] In the suspension device according to the second aspect of the present disclosure, the support member may include a first support member and a second support member separated from each other in a second direction orthogonal to the first direction.

[0015] In the suspension device according to the second aspect of the present disclosure, the second portion of the torsion bar may be located on the first side when viewed from the motor. The support member may be located closer to the end of the second side of the motor than to the end of the first side of the motor. The second side of the motor may be the opposite side of the first side.

[0016] In the suspension device according to the second aspect of the present disclosure, the support member may be located at the end portion on the second side of the motor.

[0017] It can also be constructed that, based on the suspension device involved in the second form of the present disclosure, the above-mentioned support component includes: an outer tube, fixed to one side of the above-mentioned motor and the above-mentioned sprung structure; an inner tube, fixed to the other side of the above-mentioned motor and the above-mentioned sprung structure; and the above-mentioned first elastic component, sandwiched between the above-mentioned outer tube and the above-mentioned inner tube.

[0018] In the suspension device according to the second aspect of the present disclosure, the axial direction of the outer tube and the inner tube may be a direction intersecting the first direction.

[0019] In the suspension device according to the second aspect of the present disclosure, the torsion bar may be not supported by the sprung structure between the first portion and the second portion.

[0020] The suspension device according to the second aspect of the present disclosure may further include a rod support member configured to support the torsion bar to the sprung structure via a second elastic member.

[0021] According to the present disclosure, a suspension device using a motor and a torsion bar is provided. The supporting component supports the motor on the sprung structure via an elastic component. In addition, the supporting component is configured so that the motor and the torsion bar can rotate integrally in the direction orthogonal to the axis with the position of the supporting component as a fulcrum. When an external force is input, the motor and the torsion bar rotate integrally in the direction orthogonal to the axis with the position of the supporting component as a fulcrum. According to the above structure, the torsion amount of the torsion bar caused by the external force is reduced. That is, the suspension stiffness is effectively reduced. Since the suspension stiffness is effectively reduced, the control effect of high-frequency vibration can be improved.

[0022] Here, please note that it is not necessary to soften the torsion bar itself in order to reduce the suspension stiffness. Since it is not necessary to make the torsion bar itself thinner, the strength of the torsion bar is ensured and fracture is prevented. In addition, it is not necessary to lengthen the torsion bar itself, so the weight does not increase, and the carrying space is not compressed. In this way, according to the present disclosure, the suspension stiffness can be effectively reduced without causing problems such as insufficient strength of the torsion bar and increased weight, thereby improving the control effect of high-frequency vibration.

[0023] Features, advantages, and technical and industrial significance of exemplary embodiments of the present invention are described below with reference to the accompanying drawings, in which like reference numerals denote like elements. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 This is a schematic diagram for explaining a suspension device mounted on a vehicle according to an embodiment.

[0025] Figure 2 This is a schematic diagram for explaining the mechanism of the suspension device according to the embodiment.

[0026] Figure 3 It is a schematic diagram showing a configuration example of a motor and a torsion bar according to an embodiment.

[0027] Figure 4 It is a schematic diagram showing a configuration example of a support member according to the first embodiment.

[0028] Figure 5 This is a schematic diagram showing an example of arrangement of support members according to the first embodiment.

[0029] Figure 6 (a) and (b) are schematic diagrams for explaining the operation and effects of the first embodiment.

[0030] Figure 7 (a) and (b) are schematic diagrams for explaining the operation and effects of the first embodiment.

[0031] Figure 8 It is a figure which shows a comparative example.

[0032] Fig. 9 This is a schematic diagram showing another example of the arrangement of the support members according to the first embodiment.

[0033] Fig.10 It is a schematic diagram showing an example of arrangement of a support member and a rod support member according to the second embodiment.

[0034] Fig.11 It is a schematic diagram showing a configuration example of a rod support member according to a second embodiment.

[0035] Fig.12 It is a diagram showing a suspension device according to a third embodiment.

[0036] Fig.13 It is a diagram showing a suspension device according to a third embodiment.

[0037] Fig.14It is a diagram for explaining a motor according to a third embodiment. DETAILED DESCRIPTION

[0038] Embodiments of the present disclosure will be described with reference to the drawings.

[0039] 1. First Implementation Method

[0040] 1-1. Overview of suspension device

[0041] Figure 1 1 is a schematic diagram for explaining a suspension device 10 mounted on a vehicle 1. The suspension device 10 suspends wheels 2 of the vehicle 1. The suspension device 10 includes a spring 11 and a shock absorber 12. The spring 11 and the shock absorber 12 are provided between the unsprung member 3 and the sprung structure 5.

[0042] The suspension device 10 is a so-called fully active suspension device, and is configured to actively apply vertical force to the unsprung member 3. To this end, the suspension device 10 also includes a motor (actuator) 20. The motor 20 is supported on the sprung structure 5. In addition, the operation of the motor 20 is controlled by the controller 100. The torque generated by the operation of the motor 20 is converted into a vertical force and applied to the unsprung member 3 (for example, a suspension arm).

[0043] Figure 2 This is a schematic diagram for explaining the mechanism of the suspension device 10. According to the present embodiment, a "torsion bar 30" is used to transmit the torque generated by the action of the motor 20 to the unsprung member 3. In the following description, for convenience, the axial direction of the torsion bar 30 is referred to as the Y direction (first direction). The X direction (second direction) and the Z direction (third direction) are axially orthogonal directions that are orthogonal to the Y direction. The X direction and the Z direction are also orthogonal to each other. In addition, the recording of X, Y, and Z is for convenience, and the Z direction does not necessarily refer to the vertical direction. The Z direction can also be a vertical direction, in which case the XY plane is a horizontal plane.

[0044] like Figure 2 As shown, the torsion bar 30 extends in the Y direction. More specifically, the torsion bar 30 includes a first portion 31 and a second portion 32 separated in the Y direction. For example, the first portion 31 is one end of the torsion bar 30, and the second portion 32 is the other end of the torsion bar 30. The first portion 31 of the torsion bar 30 is connected to the output shaft of the motor 20. The first portion 31 may also be fixed to the output shaft of the motor 20. The second portion 32 of the torsion bar 30 is connected to the control rod 40. The second portion 32 may also be fixed to the control rod 40.

[0045] The control rod 40 extends in a direction perpendicular to the Y direction. More specifically, the control rod 40 includes a first portion 41 and a second portion 42 separated in a direction perpendicular to the Y direction. The first portion 41 of the control rod 40 is connected to the second portion 32 of the torsion bar 30. The first portion 41 may also be fixed to the second portion 32 of the torsion bar 30. The second portion 42 of the control rod 40 is connected to the unsprung member 3 (e.g., suspension arm) via a connecting rod 50. It can be said that the control rod 40 and the connecting rod 50 constitute a connecting member that connects the second portion 32 of the torsion bar 30 and the unsprung member 3.

[0046] The torsion bar 30 and the control rod 40 may be formed integrally. In this case, it can be said that the control rod 40 and the connecting rod 50 constitute a connecting member that connects the second portion 32 of the torsion bar 30 and the unsprung member 3 .

[0047] like Figure 2 As shown, the torsion bar 30 is twisted by the rotation of the motor 20. Due to the torsion torque of the torsion bar 30, the control rod 40 rotates in the XZ plane orthogonal to the Y direction with the first part 41 (torsion bar 30) as the rotation center. As a result, the second part 42 of the control rod 40 moves in the direction orthogonal to the Y direction. Figure 2 In the example shown, the second portion 42 of the control rod 40 is separated from the first portion 41 in the general X direction. When the control rod 40 rotates with the first portion 41 (torsion bar 30) as the rotation center, the second portion 42 moves in the general Z direction. Such movement of the second portion 42 of the control rod 40 is converted into the movement of the unsprung member 3 in the up-down direction via the link 50.

[0048] Thus, the torsion torque of the torsion bar 30 twisted by the motor 20 is converted into a vertical force and applied to the unsprung member 3. It can be said that the control rod 40 and the connecting rod 50 constitute a transmission member that converts the torsion torque of the torsion bar 30 into a vertical force and transmits it to the unsprung member 3.

[0049] On the contrary, if the unsprung member 3 moves up and down due to an external force (road input, etc.), the up and down movement is converted into the movement of the second portion 42 of the control rod 40 via the connecting rod 50. If the second portion 42 of the control rod 40 moves in a direction orthogonal to the Y direction, the torsion bar 30 is also twisted accordingly. It can be said that the control rod 40 and the connecting rod 50 constitute a transmission member that transmits the up and down movement of the unsprung member 3 to the torsion bar 30.

[0050] Figure 3 2 is a schematic diagram showing a configuration example of the motor 20 and the torsion bar 30. Figure 3In the example shown, the motor 20 has an insertion hole 21. A portion of the torsion bar 30 is inserted into the insertion hole 21. The motor 20 also has a motor portion 22, a gear portion 23, and a connecting portion 24. The motor portion 22 is arranged around the insertion hole 21. The motor portion 22 is connected to the connecting portion 24 via the gear portion 23. The connecting portion 24 is connected to the first portion 31 of the torsion bar 30. The connecting portion 24 may also be fastened to the first portion 31 of the torsion bar 30. The connecting portion 24 is an example of an output shaft of the motor 20. The rotational force generated by the motor portion 22 is transmitted to the connecting portion 24 via the gear portion 23, so that the connecting portion 24 rotates. The torsion bar 30 is twisted by the rotation of the connecting portion 24.

[0051] In addition, the structure of the motor 20 and the torsion bar 30 is not limited to Figure 3 Example shown.

[0052] 1-2. Issues

[0053] In the suspension device 10 using the torsion bar 30, the suspension stiffness increases by the rigidity of the torsion bar 30. This is because, as described above, when the unsprung member 3 moves up and down due to an external force (road input, etc.), the torsion bar 30 is twisted via the transmission member, generating a reaction force of the torsion bar 30.

[0054] For example, for the control of high-frequency vibration, the increase in suspension stiffness is not expected. If it is a frequency band that is easy to control, the influence of the increase in suspension stiffness can be mitigated by performing control such as suppressing the torsion of the torsion bar 30 caused by external force (for example, feedback control such as skyhook damper control, pre-control using mapping). However, it is not necessarily easy to perform such control on the input of the high-frequency band. As a result, there is a concern that the high-frequency vibration will worsen.

[0055] In order to suppress the increase in suspension rigidity, it is also possible to soften the torsion bar 30 itself. However, if the torsion bar 30 is made thinner, the torsion bar 30 is easily broken due to insufficient strength. If the torsion bar 30 is made longer, problems such as increased weight and increased size arise. If the torsion rigidity of the torsion bar 30 itself is reduced, the problem of insufficient strength still arises.

[0056] Thus, in the suspension device 10 using the torsion bar 30, reducing the suspension stiffness is important but not simple. This embodiment proposes a method that can effectively reduce the suspension stiffness based on a new viewpoint. The method that can effectively reduce the suspension stiffness is described in detail below.

[0057] 1-3. Reduction of suspension stiffness

[0058] The motor 20 is supported on the sprung structure 5 (e.g., suspension member, vehicle body). The suspension device 10 includes a "support member 60" that supports the motor 20 on the sprung structure 5. This embodiment is characterized in the structure and arrangement of the support member 60, thereby effectively reducing the suspension stiffness.

[0059] First, the support member 60 includes an elastic member (buffer member) 63 . The elastic member 63 is an example of a first elastic member. The elastic member 63 is, for example, rubber. The support member 60 may also be a rubber bush. The support member 60 supports the motor 20 on the sprung structure 5 via the elastic member 63 .

[0060] Figure 4 : is a schematic diagram showing a structural example of the support member 60. The support member 60 includes an outer cylinder 61, an inner cylinder 62, and an elastic member 63. The outer cylinder 61 and the inner cylinder 62 are made of metal. The outer cylinder 61 and the inner cylinder 62 are coaxial, and the inner cylinder 62 is inserted into the outer cylinder 61. The elastic member 63 is configured to be sandwiched between the outer cylinder 61 and the inner cylinder 62. One of the outer cylinder 61 and the inner cylinder 62 is fixed to the motor 20, and the other is fixed to the sprung structure 5. For example, the outer cylinder 61 is fixed to the motor 20, and the inner cylinder 62 is fixed to the sprung structure 5. Thus, the motor 20 is supported on the sprung structure 5 via the elastic member 63.

[0061] Figure 5 1 is a schematic diagram showing an example of the arrangement of the support member 60 according to the present embodiment. Figure 5 In the example shown, the position of the support member 60 in the Y direction (first direction) is one location. In addition, the Y direction position of the support member 60 is relatively far from the second portion 32 of the torsion bar 30. In more detail, when viewed from the motor 20, the second portion 32 of the torsion bar 30 is present on the A side. The B side is the opposite side of the A side. When viewed from the center position C of the motor 20, the support member 60 is not arranged on the A side, but on the B side. In other words, the Y direction position of the support member 60 is closer to the B side end of the motor 20 than the A side end of the motor 20. The support member 60 may also be located at the B side end of the motor 20.

[0062] In addition, Figure 5 In the example shown, the support member 60 includes a first support member 60-1 and a second support member 60-2 separated in the X direction (second direction) orthogonal to the Y direction. The first support member 60-1 and the second support member 60-2 have the same Y direction position. The first support member 60-1 and the second support member 60-2 support the motor 20 on the sprung structure 5 via the elastic member 63, respectively. By supporting the motor 20 at two X-direction positions, the motor 20 does not rotate in the circumferential direction and is stable.

[0063] In addition, Figure 5In the illustrated example, the Z-direction position of the support member 60 is substantially the same as the Z-direction position of the torsion bar 30 .

[0064] Figure 5 Each support member 60 may also have Figure 4 In this case, the axial direction of the outer cylinder 61 and the inner cylinder 62 may be a direction intersecting the Y direction. For example, the axial direction of the outer cylinder 61 and the inner cylinder 62 may be a Z direction orthogonal to the Y direction.

[0065] Figure 6 6 is a schematic diagram for explaining the functions and effects of the present embodiment. As described above, the support member 60 is not entirely formed of a rigid body, but also includes an elastic member 63. The support member 60 supports the motor 20 on the sprung structure 5 via the elastic member 63. Figure 6 As shown, the motor 20 and the torsion bar 30 rotate integrally in a direction perpendicular to the axis orthogonal to the Y direction with the position of the support member 60 as a fulcrum (rotation center). It can also be said that the support member 60 is configured so that the motor 20 and the torsion bar 30 can rotate integrally in a direction perpendicular to the axis orthogonal to the Y direction with the position of the support member 60 as a fulcrum.

[0066] exist Figure 5 In the example shown, the first support member 60-1 and the second support member 60-2 are arranged apart in the X direction. In this case, the motor 20 and the torsion bar 30 can easily rotate integrally in the Z direction orthogonal to the X direction and the Y direction with the position of the support member 60 as a fulcrum.

[0067] As described above, if the unsprung member 3 moves up and down due to an external force (road input, etc.), the up and down movement is converted into the movement of the second portion 42 of the control rod 40 via the connecting rod 50. If the second portion 42 of the control rod 40 moves in a direction orthogonal to the Y direction, the torsion bar 30 is also twisted accordingly. At the same time, the motor 20 and the torsion bar 30 are also rotated integrally in a direction orthogonal to the Y direction with the position of the support member 60 as a fulcrum by the force that moves the control rod 40 in a direction orthogonal to the Y direction. As a result, the second portion 32 of the torsion bar 30 is displaced in a direction orthogonal to the Y direction. That is, the second portion 32 of the torsion bar 30 is also displaced in a direction orthogonal to the Y direction by the force that moves the control rod 40 in a direction orthogonal to the Y direction. As a result, the force that twists the torsion bar 30 is actually reduced, and the amount of twisting of the torsion bar 30 caused by the external force is also reduced. This means that the suspension stiffness is actually reduced.

[0068] Reference Figure 7 , and provide a quantitative description. b It is the length from the position of the support member 60 to the second portion 32 of the torsion bar 30. l is the length of the control rod 40.bl θ is the displacement at the connection point between the torsion bar 30 and the control rod 40 (the second portion 32 of the torsion bar 30). b is equivalent to the displacement z bl The change angle of the motor 20 and the torsion bar 30. k is equivalent to the displacement z bl K is the angle of the integrated structure of the motor 20 and the torsion bar 30. b Directional rigidity. F is the external force input from the link 50. In this case, the following equations (1) to (4) hold true.

[0069]

[0070] z bl = l b θ b …(2)

[0071]

[0072] The rotation angle (torsion angle) θ of the torsion bar 30 decreases with θ k The torsion rigidity of the torsion bar 30 is K b In the case of , the moment M generated in the torsion bar 30 is expressed by the following equation (5).

[0073] M=(θ-θ k )K b …(5)

[0074] When the motor 20 and the torsion bar 30 do not rotate integrally, θ b Directional rigidity K is ∞, θ k On the other hand, when the motor 20 and the torsion bar 30 rotate integrally, θ b The directional stiffness K is a finite value, θ k Therefore, when the motor 20 and the torsion bar 30 rotate integrally, the torque M generated in the torsion bar 30 decreases by θ compared to when they do not rotate. k ·K b The corresponding size. That is, the suspension stiffness is effectively reduced. In addition, θ b The directional rigidity K can be adjusted by adjusting the rigidity of the support member 60 including the elastic member 63. In other words, by controlling the rigidity of the support member 60 including the elastic member 63, the desired θ b Directional rigidity K.

[0075] exist Figure 5 and Figure 6In the example shown, the position of the support member 60 in the Y direction is one location. In this case, the motor 20 and the torsion bar 30 are particularly easy to rotate integrally in a direction perpendicular to the Y direction with the position of the support member 60 as a fulcrum. Therefore, the suspension stiffness can be reduced more effectively.

[0076] Figure 8 A comparative example is shown (refer to Japanese Patent Laid-Open No. 2008-308098). In the comparative example, two support members 91 and 92 support the motor 20 in a manner that surrounds the outer periphery. Furthermore, these support members 91 and 92 are separated in the Y direction. In the case of such a support method, it is not easy for the motor 20 and the torsion bar 30 to rotate in a direction orthogonal to the Y direction with the support members 91 and 92 as fulcrums. Rather, the support members 91 and 92 separated in the Y direction act in a manner that aligns the axial directions of the motor 20 and the torsion bar 30 in the Y direction, thereby hindering the motor 20 and the torsion bar 30 from rotating in a direction orthogonal to the Y direction. Therefore, in Figure 8 In the comparative example shown, the suspension rigidity cannot be reduced.

[0077] In addition, Figure 5 and Figure 6 In the example shown, the support member 60 is not arranged on the A side but on the B side when viewed from the center position C of the motor 20. In other words, the Y direction position of the support member 60 is closer to the B side end of the motor 20 than the A side end of the motor 20. This means that Figure 7 The length l shown b (the length from the position of the support member 60 to the second portion 32 of the torsion bar 30) is relatively large. According to the above formula (4), it can be seen that the length l b The larger the value, the k The larger the value, the greater the effect of reducing the moment M. That is, the suspension stiffness can be reduced more effectively. The support member 60 may be located at the B-side end of the motor 20 .

[0078] In the above Figure 5 and Figure 6 In the example shown, the Z-direction position of the support member 60 is almost the same as the Z-direction position of the torsion bar 30. However, this is not limited to this. Fig. 9 As shown, the support member 60 may also be configured to support the upper surface or the lower surface of the motor 20. Fig. 9 In the configuration shown, the motor 20 and the torsion bar 30 also rotate integrally in the direction perpendicular to the axis perpendicular to the Y direction with the position of the support member 60 as the fulcrum (rotation center). The support member 60 only needs to be configured so that the motor 20 and the torsion bar 30 can rotate integrally in the direction perpendicular to the axis perpendicular to the Y direction with the position of the support member 60 as the fulcrum.

[0079] 1-4. Effect

[0080] As described above, according to the present embodiment, a suspension device 10 utilizing a motor 20 and a torsion bar 30 is provided. The support member 60 supports the motor 20 on the sprung structure 5 via the elastic member 63. In addition, the support member 60 is configured so that the motor 20 and the torsion bar 30 can rotate integrally in a direction orthogonal to the Y direction with the position of the support member 60 as a fulcrum. When an external force is input, the motor 20 and the torsion bar 30 rotate integrally in a direction orthogonal to the Y direction with the position of the support member 60 as a fulcrum. As a result, the amount of torsion of the torsion bar 30 caused by the external force is reduced. That is, the suspension stiffness is effectively reduced. Since the suspension stiffness is effectively reduced, the control effect of high-frequency vibration can be improved.

[0081] Here, please note that it is not necessary to soften the torsion bar 30 itself in order to reduce the suspension rigidity. Since it is not necessary to make the torsion bar 30 itself thinner, the strength of the torsion bar 30 is ensured and fracture is prevented. In addition, it is not necessary to lengthen the torsion bar 30 itself, so the weight does not increase, and the loading space is not compressed. According to this embodiment, the suspension rigidity can be effectively reduced without causing problems such as insufficient strength and increased weight of the torsion bar 30, and the control effect of high-frequency vibration can be improved.

[0082] 1-5. Torsion bar support

[0083] In the first embodiment, there is no member supporting the torsion bar 30 between the first portion 31 and the second portion 32 of the torsion bar 30. That is, the torsion bar 30 is not supported by the sprung structure 5 between the first portion 31 and the second portion 32. In this case, the motor 20 and the torsion bar 30 can easily rotate integrally in a direction orthogonal to the Y direction with the position of the support member 60 as a fulcrum.

[0084] 2. Second Implementation Method

[0085] If the motor 20 and the torsion bar 30 are integrally structured, θ b If the directional rigidity K becomes excessively small, the moment M generated in the torsion bar 30 also becomes excessively small. In this case, it is difficult to transmit the control force from the motor 20 to the unsprung member 3 via the torsion bar 30. Therefore, it is necessary to appropriately set θ b Directional rigidity K. If the desired θ cannot be achieved only by the support member 60 on the motor 20 side b In the case of the directional rigidity K, a rod support member 70 may be added to the torsion bar 30 side.

[0086] Fig.101 is a schematic diagram showing an example of the configuration of the support member 60 and the rod support member 70 involved in the second embodiment. The rod support member 70 supports the torsion bar 30 on the sprung structure 5. Like the support member 60, the rod support member 70 also includes an elastic member (buffer member) 72. The elastic member 72 is an example of a second elastic member. The elastic member 72 is, for example, rubber. The rod support member 70 may also be a rubber bushing. The rod support member 70 supports the torsion bar 30 on the sprung structure 5 via the elastic member 72.

[0087] Fig.11 1 is a schematic diagram showing a structural example of a rod support member 70. The rod support member 70 includes a bracket 71 and an elastic member 72. The bracket 71 is fixed to the sprung structure 5 (e.g., a suspension member, a vehicle body). The bracket 71 has a through hole extending in the Y direction, and the elastic member 72 is disposed in the through hole. In addition, the elastic member 72 also has a through hole extending in the Y direction, and the torsion bar 30 extends through the through hole. Thus, the torsion bar 30 is supported on the sprung structure 5 via the elastic member 72.

[0088] The integral structure of the motor 20 and the torsion bar 30 b The directional rigidity K is determined by the combination of the rigidity of the support member 60 on the motor 20 side and the rigidity of the rod support member 70 on the torsion bar 30 side. b In the case of the directional rigidity K, the second embodiment is useful.

[0089] 3. Third Implementation Method

[0090] Figure 12 to Figure 14 A specific example of the suspension device 10 is shown. The description overlapping with the first and second embodiments will be omitted as appropriate. Figure 12 to Figure 14 In the example shown, the X direction is the front-rear direction, the Y direction is the lateral direction, and the Z direction is the vertical direction.

[0091] The first support member 60-1 and the second support member 60-2 are arranged at the end of the motor 20. The first support member 60-1 and the second support member 60-2 are separated in the X direction. The first support member 60-1 and the second support member 60-2 have the same Y direction position. The first support member 60-1 and the second support member 60-2 each have the above Figure 4 In each of the first support member 60-1 and the second support member 60-2, the axial direction of the outer cylinder 61 and the inner cylinder 62 is the Z direction. The first support member 60-1 and the second support member 60-2 are fastened to the suspension member (sprung structure 5) to support the motor 20 on the suspension member.

[0092] A rod support member 70 is also provided. The rod support member 70 supports the torsion bar 30 on the suspension member.

Claims

1. A suspension device mounted on a vehicle, characterized in that: The suspension device comprises: motor; A torsion bar having a first portion connected to an output shaft of the motor; a connecting member configured to connect the second portion of the torsion bar and the unsprung member; and The support member is configured to support the motor on the sprung structure via a first elastic member, and is arranged so that the motor and the torsion bar rotate integrally with the position of the support member as a rotation center in a direction orthogonal to a first direction, which is an axial direction of the torsion bar.

2. A suspension device mounted on a vehicle, characterized in that: The suspension device comprises: motor; A torsion bar having a first portion connected to an output shaft of the motor; a connecting member configured to connect the second portion of the torsion bar and the unsprung member; and The support member is configured to support the motor on the sprung structure via a first elastic member and is located at one position in a first direction, the first direction being an axial direction of the torsion bar.

3. The suspension device according to claim 1 or 2, characterized in that: The supporting member includes a first supporting member and a second supporting member that are separated from each other in a second direction orthogonal to the first direction.

4. The suspension device according to claim 1 or 2, characterized in that: The second portion of the torsion bar is present on the first side when viewed from the motor; The support member is closer to an end portion on a second side of the motor than to an end portion on the first side of the motor; The second side of the motor is an opposite side to the first side.

5. The suspension device according to claim 4, characterized in that: The support member is located at the end portion on the second side of the motor.

6. The suspension device according to claim 1 or 2, characterized in that: The supporting member comprises: an outer cylinder fixed to one of the motor and the sprung structure; an inner cylinder fixed to the other of the motor and the sprung structure; and The first elastic member is sandwiched between the outer tube and the inner tube.

7. The suspension device according to claim 6, characterized in that: The axial directions of the outer tube and the inner tube are directions intersecting with the first direction.

8. The suspension device according to claim 1 or 2, characterized in that: The torsion bar is not supported by the sprung structure between the first portion and the second portion.

9. The suspension device according to claim 1 or 2, characterized in that: A rod support member is further provided, the rod support member being configured to support the torsion bar on the sprung structure via a second elastic member.

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