JP2013117270A - Damper device - Google Patents

Abstract

A damper device capable of actively changing characteristics is provided.
A damper device elastically connects a hub 10, an annularly formed mass body 20 disposed radially outward of the hub 10, and an outer peripheral surface of the hub 10 and an inner peripheral surface of the mass body 20. The mass body 20 and the actuator 0 for changing the resonance frequency f0 of the mass spring system including the elastic body 30, the hub vibration detector 60 for detecting vibration in the rotational direction of the hub 10, and the mass body 20. Mass body vibration detector 70 for detecting vibrations in the rotation direction of the body 10, vibrations in the rotation direction of the hub 10 detected by the hub vibration detector 60, and rotation directions of the mass body 20 detected by the mass body vibration detector 70. And an actuator control unit 80 that controls the actuator 50 to change the resonance frequency f0 based on the phase difference Δθ with respect to the vibration.
[Selection] Figure 1

Description

  The present invention relates to a damper device including a hub, an annular mass body, and an elastic body interposed therebetween.

  As this type of damper device, for example, there is one described in JP-A-2002-106640 (Patent Document 1). The damper device reduces vibrations in the rotational direction of the hub, such as torsional vibrations and rotational fluctuations. The characteristics of the damper device are adjusted in advance by the elastic body and the mass body.

JP 2002-106640 A

If the characteristics of the damper device can be actively changed, vibrations can be reduced in a wider frequency range.
This invention is made | formed in view of such a situation, and it aims at providing the damper apparatus which can change a characteristic actively.

  (Claim 1) A damper device according to the present invention includes a hub, an annularly formed mass body that is disposed radially outward of the hub, an outer peripheral surface of the hub, and an inner peripheral surface of the mass body. An elastic body that elastically couples the mass body, an actuator that changes a resonance frequency of a mass spring system including the mass body, a hub vibration detector that detects vibration in the rotational direction of the hub, and A mass vibration detector for detecting vibrations in the rotation direction; vibrations in the rotation direction of the hub detected by the hub vibration detector; and vibrations in the rotation direction of the mass bodies detected by the mass body vibration detector. And an actuator controller that controls the actuator to change the resonance frequency based on the phase difference between the two.

  (Claim 2) Further, the actuator has one end supported by one of the hub and the mass body, the other end supported by the hub and the other of the mass body, and an expandable and contractable coil spring, and the coil spring. You may make it provide the expansion-contraction drive means which changes the resonance frequency of the said mass spring type | system | group by expanding and contracting and changing the storage elastic modulus of the said coil spring.

  (Claim 3) One end of the coil spring is supported in a state of being positioned on one of the hub and the mass body, and the other end of the coil spring is moved relative to the other of the hub and the mass body. The expansion / contraction drive means may expand / contract the coil spring by moving the other end of the coil spring relative to the other of the hub and the mass body.

  (Claim 4) Further, the actuator is configured to change a movable mass body attached to the mass body and a radial position of the movable mass body so as to be movable in the radial direction with respect to the mass body. You may make it provide the movable mass body drive means which changes the resonance frequency of the said mass spring system by changing the inertial mass of the said mass spring system.

  (Claim 5) Further, the movable mass body is supported so as to be movable in the radial direction in a cylinder fixed to the mass body, and the movable mass body driving means supplies a fluid pressure to be supplied into the cylinder. It is also possible to change the radial position of the movable mass body.

  (Claim 1) Based on the phase difference between the vibration in the rotation direction of the hub and the vibration in the rotation direction of the mass body, the resonance frequency of the mass spring system is changed by controlling the actuator of the hub, thereby depending on the vibration frequency. Therefore, the vibration can be reduced with respect to the vibration of any frequency. Here, the vibration in the rotational direction includes at least rotational fluctuation and torsional vibration.

(Claim 2) By changing the storage elastic modulus of the coil spring, the resonance frequency of the mass spring system can be positively changed reliably.
(Claim 3) One end of the coil spring is supported while being positioned on one of the hub and the mass body, and the other end of the coil spring is supported while allowing relative movement with respect to the other of the hub and the mass body. By attaching the coil spring to the hub and the mass body as described above, the extension amount of the coil spring can be reliably changed. Accordingly, the storage elastic modulus of the coil spring can be reliably changed, and as a result, the resonance frequency of the mass spring system can be actively changed.

(Claim 4) By providing the movable mass body so as to be movable in the radial direction with respect to the mass body, the inertial mass of the mass spring system can be reliably changed. As a result, it is possible to positively change the resonance frequency of the mass spring system reliably.
(Claim 5) By using the fluid pressure, the radial position of the movable mass body with respect to the cylinder can be easily changed. Therefore, the inertial mass of the mass spring system can be easily changed, and as a result, the resonance frequency of the mass spring system can be easily changed actively.

1st embodiment: It is the figure which looked at the damper apparatus from the axial direction, Comprising: It is II sectional drawing of FIG. FIG. 1 shows a state in which the coil spring is closest to the no-load state. It is II-II sectional drawing of FIG. FIG. 3 is a sectional view taken along line III-III in FIG. 1. It is IV-IV sectional drawing of FIG. The figure seen from the axial direction of the damper apparatus in the state which extended the coil spring with respect to the damper apparatus of FIG. It is a graph which shows the time passage of the acceleration of the hub and mass body in FIG. FIG. 6 shows a case where the phase difference Δθ is 90 °. The phase difference Δθ and the amplitude A with respect to the vibration frequency f in the mass spring system are shown. f0 is a resonance frequency. 2nd embodiment: It is the figure which looked at the damper apparatus from the axial direction, Comprising: It is VIII-VIII sectional drawing of FIG. FIG. 8 shows a state where the coil spring is closest to the no-load state. It is IX-IX sectional drawing of FIG. It is XX sectional drawing of FIG. It is XI-XI sectional drawing of FIG. The figure seen from the axial direction of the damper apparatus in the state which extended the coil spring with respect to the damper apparatus of FIG. It is radial direction sectional drawing of FIG. 12, Comprising: It is a figure corresponding to FIG. Third Embodiment: FIG. 16 is a view of the damper device viewed from the axial direction, and is a cross-sectional view taken along the line XIV-XIV in FIG. FIG. 14 shows a state in which the movable mass body is located radially inward. It is XV-XV sectional drawing of FIG. It is XVI-XVI sectional drawing of FIG.

<First embodiment>
The damper device of the first embodiment will be described with reference to FIGS. The damper device is attached to, for example, a crankshaft (rotary shaft) of an internal combustion engine of an automobile. The vibration in the rotational direction of the crankshaft driven by the internal combustion engine can be absorbed and attenuated. Specifically, the damper device absorbs torsional vibration and rotational fluctuation in the rotational direction. Here, the damper device is not limited to the crankshaft, and can be applied to any rotating body that generates vibration in the rotational direction.

  The damper device includes a hub 10, a mass body 20, an elastic body 30, an end surface cover 40, an actuator 50, a hub acceleration sensor 60, a mass body acceleration sensor 70, an actuator control unit 80, and a power generation unit 90. And.

  The hub 10 is formed of a metal in a cylindrical shape, is attached to the outer peripheral surface of the crankshaft 100, and rotates integrally with the crankshaft 100. The mass body 20 is formed in a metal annular shape having a larger diameter than the hub 10. The mass body 20 is disposed radially outward of the hub 10. On the end surface of the mass body 20, a groove 21 extending in the circumferential direction and slightly inclined in the radial direction is formed. In FIG. 1, the end 21 in the counterclockwise direction of the groove 21 is located radially outward from the end in the clockwise direction. The mass body 20 has a rotation balance weight 22 on its end face. The rotation balance weight 22 is for eliminating the rotation imbalance of the actuator 50, the actuator controller 80, and the like.

  The elastic body 30 is formed in a cylindrical shape with rubber, and elastically connects the outer peripheral surface of the hub 10 and the inner peripheral surface of the mass body 20. Specifically, the inner peripheral surface of the elastic body 30 and the outer peripheral surface of the hub 10, and the outer peripheral surface of the elastic body 30 and the inner peripheral surface of the mass body 20 are bonded with an adhesive or fixed by press-fitting. ing. The elastic body 30 absorbs the phase difference between the hub 10 and the mass body 20. That is, when the rotational fluctuation is transmitted from the crankshaft 100 to the hub 10, the elastic body 30 absorbs the transmitted rotational fluctuation.

  The end surface cover 40 is attached to one end surface side (left side in FIG. 2) of the mass body 20, and covers one end surface side (left side in FIG. 2) of the crankshaft 100, the hub 10, the mass body 20, and the elastic body 30. The end surface cover 40 is formed in a bottomed cylindrical shape, and the bottom portion is formed in a disk shape.

  The actuator 50 changes the resonance frequency of the mass spring system including the mass body 20 and the elastic body 30. The actuator 50 includes a hub side fixed seat 51, a circumferential slide body 52, a coil spring 53, a first electromagnet 54, and a second electromagnet 55. The hub-side fixing seat 51 is a rectangular parallelepiped member fixed to the end surface of the hub 10.

  The circumferential slide body 52 is supported on the end surface of the mass body 20 so as to allow relative movement in the circumferential direction with respect to the mass body 20. The circumferential slide body 52 protrudes from an arc-shaped main body portion 52a, magnets 52b and 52c provided at both ends in the circumferential direction of the main body portion 52a, and one axial surface of the main body portion 52a (the back surface in FIG. 1). Two pins 52d. The pin 52 d is inserted into the groove 21 of the mass body 20 and is movable along the groove 21. The movement of the pin 52d along the groove 21 allows the main body 52a to slide in the circumferential direction along the end surface of the mass body 20. Here, the groove 21 extends in the circumferential direction and is slightly inclined in the radial direction. Accordingly, when the circumferential slide body 52 moves in the circumferential direction with respect to the mass body 20, the circumferential slide body 52 slightly moves in the radial direction. In addition, the pin 52d is prevented from falling out of the groove 21 by restricting the other surface in the axial direction of the main body 52a (the front surface of the hand in FIG. 1) by the end surface cover 40.

  One end of the coil spring 53 is supported while being positioned on the hub-side fixed seat 51. However, one end of the coil spring 53 is only allowed to rotate at the mounting position of the hub side fixed seat 51. The other end of the coil spring 53 is supported while being positioned on the inner peripheral edge of the circumferential slide body 52. However, the other end of the coil spring 53 is only allowed to rotate at the mounting position of the circumferential slide body 52. That is, the coil spring 53 is attached between the hub 10 and the mass body 20 so as to be expandable and contractable in the radial direction, and is supported in a state in which relative movement with respect to the mass body 20 is allowed in the circumferential direction. . Therefore, the coil spring 53 expands and contracts as the circumferential slide body 52 moves relative to the mass body 20. That is, the storage elastic modulus of the coil spring 53 changes.

  The first electromagnet 54 is fixed to the end surface of the mass body 20 and is provided so as to face the magnet 52 b attached to one end in the circumferential direction of the circumferential slide body 52 in the circumferential direction. That is, the first electromagnet 54 generates a force that attracts the magnet 52b when supplied with current. The second electromagnet 55 is fixed to the end face of the mass body 20 and is provided so as to face the magnet 52c attached to the other circumferential end of the circumferential slide body 52 in the circumferential direction. That is, the second electromagnet 55 generates a force that attracts the magnet 52c when supplied with current. Therefore, when the attraction force by the first electromagnet 54 is larger than the attraction force by the second electromagnet 55, the circumferential slide body 52 moves to the first electromagnet 54 side, and the magnitude of the attraction force is reversed. The circumferential slide body 52 moves to the second electromagnet 55 side. When the suction force is balanced, the circumferential slide body 52 does not move.

  Therefore, the first electromagnet 54 and the second electromagnet 55 change the storage elastic modulus of the coil spring 53 by adjusting the attraction force thereof and moving the other end of the coil spring 53 relative to the mass body 20. be able to. Changing the storage elastic modulus of the coil spring 53 changes the resonance frequency f0 of the mass spring system including the mass body 20 and the elastic body 30. That is, by adjusting the attractive force of the first electromagnet 54 and the second electromagnet 55, the resonance frequency f0 of the mass spring system can be changed. Here, the circumferential slide body 52 and the first and second electromagnets 54 and 55 correspond to the expansion / contraction driving means of the present invention.

  The hub acceleration sensor 60 (hub vibration detector) is attached to the end surface of the hub 10 and detects acceleration in the rotation direction of the hub 10. Here, when the hub 10 vibrates in the rotation direction, the magnitude of the acceleration in the rotation direction of the hub 10 vibrates. That is, the hub acceleration sensor 60 can detect vibration in the rotation direction of the hub 10.

  The mass body acceleration sensor 70 (mass body vibration detector) is attached to the end surface of the mass body 20 and detects the acceleration in the rotational direction of the mass body 20. Here, when the mass body 20 vibrates in the rotation direction, the magnitude of the acceleration in the rotation direction of the mass body 20 vibrates. That is, the mass body acceleration sensor 70 can detect vibration in the rotation direction of the mass body 20.

  Based on the phase difference Δθ between the vibration in the rotation direction of the hub 10 detected by the hub acceleration sensor 60 and the vibration in the rotation direction of the mass body 20 detected by the mass body acceleration sensor 70, the actuator control unit 80. The currents supplied to the first and second electromagnets 54 and 55 are controlled to change the resonance frequency f0 of the mass spring system.

  The power generation unit 90 generates power using the rotation of the crankshaft 100 and functions as a power source for the actuator control unit 80. The power generation unit 90 is provided with a coil 92 on the end surface of the hub 10 (the end surface opposite to the hub-side fixing seat 51) through which a cylindrical magnet 91 fixed to a fixing member such as an engine (not shown) can be inserted. Yes. That is, while the cylindrical magnet 91 is always fixed, an electromotive force is generated in the coil 92 as the coil 92 rotates as the crankshaft 100 rotates. The electric power generated by the power generation unit 90 is transmitted to the actuator control unit 80.

(Actuator operation)
Next, the operation of the actuator 50 will be described with reference to FIG. 1 and FIG. In the state shown in FIG. 1, the circumferential slide body 52 is located at the end in the clockwise direction in the movable range. At this time, the coil spring 53 is in a free length state or an extended state closest to the free length.

  A current is supplied to the first electromagnet 54 and the second electromagnet 55 based on the state of FIG. A large current is supplied to the first electromagnet 54 side. Then, as shown in FIG. 5, the circumferential slide body 52 moves counterclockwise in FIG. The other end of the coil spring 53 is supported by the circumferential slide body 52. Therefore, when the circumferential slide body 52 moves counterclockwise in FIG. 5, the separation distance between one end and the other end of the coil spring 53 changes. That is, the coil spring 53 is extended and deformed.

  In this way, the storage elastic modulus of the coil spring 53 can be changed by the current supplied to the first and second electromagnets 54 and 55. Since both ends of the coil spring 53 are connected to the hub 10 and the mass body 20, the change in the storage elastic modulus of the coil spring 53 changes the resonance frequency of the mass spring system.

(Operation of actuator controller)
Next, the operation of the actuator control unit 80 will be described with reference to FIGS. In the above description, it has been explained that the resonance frequency f <b> 0 of the mass spring system can be changed by controlling the current supplied to the first and second electromagnets 54, 55 by the actuator control unit 80.

  The actuator control unit 80 also supplies a current supplied to the first and second electromagnets 54 and 55 of the actuator 50 based on the phase difference Δθ between the vibration in the rotation direction of the hub 10 and the vibration in the rotation direction of the mass body 20. Control. Here, the phase difference Δθ will be described. When the acceleration in the rotation direction of the hub 10 changes as indicated by a solid line in FIG. 6 and the acceleration in the rotation direction of the mass body 20 changes as indicated by a broken line in FIG. This is a shift in the vibration cycle of the acceleration. FIG. 6 illustrates a case where the phase difference Δθ is 90 °.

  Further, the relationship between the phase difference Δθ and the amplitude A of the mass body 20 with respect to the vibration frequency is as shown in FIG. As shown in FIG. 7, the frequency at which the phase difference Δθ is 90 °, and the frequency at which the amplitude A of the mass body 20 peaks are the resonance frequency f0. That is, when the phase difference Δθ is set to 90 °, the mass body 20 vibrates greatly, and the vibration in the rotation direction of the hub 10 can be absorbed.

  Therefore, the actuator control unit 80 calculates the phase difference Δθ and controls the current supplied to the first and second electromagnets 54 and 55 so that the phase difference Δθ approaches 90 °. As a result, the phase difference Δθ can be actively adjusted to 90 ° regardless of the frequency of the vibration. As a result, the vibration in the rotation direction of the crankshaft 100 can be reduced without depending on the frequency of vibration.

<Second embodiment>
The damper device of the second embodiment will be described with reference to FIGS. The damper device of the second embodiment is substantially different in the actuator 150 from the damper device of the first embodiment. In the damper device of the second embodiment, the same components as those of the damper device of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  The actuator 150 changes the resonance frequency of the mass spring system including the mass body 20 and the elastic body 30. The actuator 150 includes a hub side fixed seat 151, a circumferential slide body 152, an annular coil spring 153, and an electromagnet 154. The hub-side fixing seat 151 is provided so as to protrude radially outward from the outer peripheral surface of the hub 10.

  The circumferential slide body 152 is supported on the end surface of the mass body 20 so as to allow relative movement in the circumferential direction with respect to the mass body 20. The circumferential slide body 152 includes a plate-like main body 152a and pins 152b. The plate-like main body 152a is made of a magnetic material and is formed in an L-shaped plate shape. The L-shaped piece is inserted between the outer peripheral surface of the hub 10 and the inner peripheral surface of the mass body 20, and the other L-shaped piece is provided to slide on the end surface of the mass body 20. ing. The pin 152b protrudes from the other L-shaped piece of the plate-like main body 152a, is inserted into the groove 21 of the mass body 20, and is movable along the groove 21. Due to the movement of the pin 152 b along the groove 21, the plate-like main body 152 a can slide in the circumferential direction along the end surface of the mass body 20.

  The annular coil spring 153 is disposed in the radial direction between the outer peripheral surface of the hub 10 and the inner peripheral surface of the mass body 20, and is disposed in the central portion in the axial direction of the elastic body 30. One end of the annular coil spring 153 is fixed to the hub-side fixing seat 151, and the other end is fixed to the plate-like main body 152 a of the circumferential slide body 152. That is, when the circumferential slide body 152 moves relative to the mass body 20, the annular coil spring 153 expands and contracts in the circumferential direction. That is, the storage elastic modulus of the annular coil spring 153 changes.

  The electromagnet 154 is fixed to the end surface of the mass body 20 and is provided to face the circumferential slide body 152 in the circumferential direction. That is, the electromagnet 154 generates a force that attracts the circumferential slide body 152 when supplied with current. Therefore, as shown in FIGS. 12 and 13, when the attractive force by the electromagnet 154 is larger than the contraction spring force of the annular coil spring 153, the circumferential slide body 152 moves to the electromagnet 154 side, and the magnitude of the force is reversed. The circumferential slide body 152 moves away from the electromagnet 154. When the attractive force of the electromagnet 154 and the contraction spring force are balanced, the circumferential slide body 152 does not move.

  Therefore, the electromagnet 154 can change the storage elastic modulus of the annular coil spring 153 by moving the other end of the annular coil spring 153 relative to the mass body 20 by adjusting the attractive force. Changing the storage elastic modulus of the annular coil spring 153 changes the resonance frequency f0 of the mass spring system including the mass body 20 and the elastic body 30. That is, by adjusting the attractive force of the electromagnet 154, the resonance frequency f0 of the mass spring system can be changed. Here, the circumferential slide body 152 and the electromagnet 154 correspond to the expansion / contraction driving means of the present invention. The damper device of the second embodiment configured as described above has the same effect as the damper device of the first embodiment.

<Third embodiment>
A damper device according to a third embodiment will be described with reference to FIGS. The damper device of the third embodiment is substantially different from the damper device of the first embodiment in the actuator 250. In the damper device of the third embodiment, the same components as those of the damper device of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  The damper device includes two actuators 250. The two actuators 250 include a cylinder unit 251 and a fluid supply device 256. The two cylinder units 251 are provided at positions where the central axes are symmetrical. The cylinder unit 251 includes a cylinder 252, a movable mass body 253, and a support spring 254.

  The cylinder 252 is fixed to the end surface of the mass body 20 so that the cylinder axis direction coincides with the radial direction. The movable mass body 253 is supported in the cylinder 252 so as to be movable in the radial direction with respect to the mass body 20. The support spring 254 is provided in one of the two areas defined by the movable mass body 253 in the cylinder 252. Here, the support spring 254 is provided to connect the radially inner surface of the mass body 20 in the movable mass body 253 and the bottom surface of the cylinder 252 so that the support spring 254 can expand and contract in the cylinder axis direction of the cylinder 252. A fluid such as oil or air is sealed in the other region of the cylinder 252 that is partitioned by the movable mass body 253. That is, the movable mass body 253 moves in the radial direction in accordance with the magnitudes of the expansion spring force of the support spring 254 in one region in the cylinder 252 and the fluid pressure in the other region.

  The fluid supply device 256 (movable mass driving means) is a device that supplies fluid to the other region in the cylinder 252. The pressure of the fluid supplied by the fluid supply device 256 is controlled by the actuator controller 80.

  According to the present embodiment, the inertial mass of the mass spring system can be changed by changing the radial position of the movable mass body 253. As a result, the resonance frequency f0 of the mass spring system can be changed. Also in this case, the same effect as the first embodiment can be obtained.

10: Hub, 20: Mass body, 30: Elastic body, 50: Actuator, 52: Circumferential slide body (extension drive means), 52b, 52c: Magnet, 53: Coil spring, 54, 55: Electromagnet (extension drive means) , 60: Hub acceleration sensor (hub vibration detector), 70: Mass body acceleration sensor (mass body vibration detector), 80: Actuator control unit, 150: Actuator, 152 Circumferential slide body (extension / contraction drive means), 153: Annular coil spring, 154: electromagnet (extension / contraction drive means), 250: actuator, 252: cylinder, 253: movable mass body, 256: fluid supply device (movable mass body drive means)

Claims (5)

A hub,
A mass formed in an annular shape and disposed radially outward of the hub;
An elastic body that elastically connects the outer peripheral surface of the hub and the inner peripheral surface of the mass body;
An actuator for changing a resonance frequency of a mass spring system including the mass body and the elastic body;
A hub vibration detector for detecting vibration in the rotational direction of the hub;
A mass vibration detector for detecting vibration in the rotational direction of the mass body;
Based on the phase difference between the vibration in the rotational direction of the hub detected by the hub vibration detector and the vibration in the rotational direction of the mass body detected by the mass body vibration detector, the actuator is controlled to An actuator controller that changes the resonance frequency;
A damper device comprising: The damper device according to claim 1, wherein
The actuator is
A coil spring having one end supported by one of the hub and the mass body, the other end supported by the other of the hub and the mass body, and a telescopic coil spring;
Expansion / contraction drive means for changing the resonance frequency of the mass spring system by changing the storage elastic modulus of the coil spring by expanding and contracting the coil spring;
Is provided. The damper device according to claim 2,
One end of the coil spring is supported while being positioned on one of the hub and the mass body,
The other end of the coil spring is supported in a state allowing relative movement with respect to the other of the hub and the mass body,
The expansion / contraction driving means expands and contracts the coil spring by moving the other end of the coil spring relative to the other of the hub and the mass body. The damper device according to claim 1, wherein
The actuator is
A movable mass attached to the mass body so as to be movable in a radial direction with respect to the mass body;
A movable mass body drive means for changing a resonance frequency of the mass spring system by changing the inertial mass of the mass spring system by changing the radial position of the movable mass body;
Is provided. The damper device according to claim 4, wherein
The movable mass body is supported so as to be movable in the radial direction in a cylinder fixed to the mass body,
The said movable mass body drive means changes the fluid pressure supplied in the said cylinder, and changes the radial direction position of the said movable mass body.

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