JP2014040880A - Damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper capable of actively changing oscillation attenuation characteristics.SOLUTION: A damper includes: a hub 10; a mass body 20 that is formed in an annular shape and is arranged outward in the radial direction of the hub 10; an elastic body 30 that elastically connects the outer peripheral surface of the hub 10 and the inner peripheral surface of the mass body 20; an actuator 50 that deforms the elastic body 30 by relatively rotating the mass body 20 with respect to the hub 10 to thereby change the resonance frequency of a mass spring system including the mass body 20 and the elastic body 30; an oscillation detector 60 that detects oscillation of the hub 10 in a rotation direction; and a control unit 70 that controls the actuator 50 on the basis of the oscillation of the hub 10 in the rotation direction detected by the oscillation detector to thereby change the resonance frequency.

Description

  The present invention relates to a damper device that attenuates torsional vibration of a rotating shaft.

  As a damper device, for example, Patent Document 1 discloses a device including a hub connected to a rotating shaft, an annular mass body, and an elastic body interposed therebetween. In the damper device, when a torsional vibration is generated on the rotating shaft, the elastic body is deformed, and the mass body reciprocates in the circumferential direction with respect to the hub, thereby attenuating the torsional vibration of the rotating shaft. Since such a damper device has a vibration damping characteristic determined by the mass body and the elastic body, for example, when the damper device is installed on a crankshaft of a vehicle, the damper device is adjusted for torsional vibration generated in the crankshaft. ing.

  However, the frequency of torsional vibration generated in the crankshaft varies depending on the rotation speed of the crankshaft, the state of the driven auxiliary machinery, and the like. Therefore, if the difference between the frequency corresponding to the set vibration damping characteristic and the frequency of the actually generated torsional vibration becomes large, the torsional vibration may not be sufficiently attenuated. Therefore, for example, Patent Document 2 discloses a configuration in which a vibration component remaining without being attenuated by the mass body and the elastic body is suppressed by an electromagnetic action between a magnet provided on the hub or the mass body and a coil provided on the fixing member. Is disclosed.

JP 2002-106640 A JP 2004-150508 A

On the other hand, if the vibration damping characteristics of the damper device can be actively changed, the torsional vibration generated on the rotating shaft in a wider frequency range can be attenuated.
The present invention has been made in view of such circumstances, and an object thereof is to provide a damper device capable of actively changing vibration damping characteristics.

  (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. And an actuator that elastically couples the mass body with respect to the hub and deforms the elastic body to change the resonance frequency of a mass spring system including the mass body and the elastic body. A vibration detector that detects vibration in the rotation direction of the hub, and a control unit that controls the actuator based on the vibration in the rotation direction of the hub detected by the vibration detector to change the resonance frequency. .

  (Claim 2) The actuator includes a rotating member that rotates integrally with the hub and an electromagnet provided on one member of the mass body, and the electromagnet opposed to the rotating member and the other member of the mass body. The control unit may control power feeding to the electromagnet based on the rotation speed of the hub and vibration in the rotation direction of the hub.

(Claim 3) The electromagnet and the magnet may be arranged so as to face each other in the circumferential direction.
(Claim 4) The rotating member may be a flywheel provided on a crankshaft to which the hub is connected.
(Claim 5) The mass body may be a pulley having a belt suspended on the outer periphery.

  (Claim 1) The actuator changes the resonance frequency of the mass spring system according to the vibration in the rotational direction of the hub. That is, the vibration damping characteristic of the damper device can be actively changed. As a result, even when torsional vibration is generated on the rotating shaft to which the hub is connected, the torsional vibration can be attenuated by changing to a vibration damping characteristic corresponding to the frequency of the torsional vibration. Thus, the damper device can cope with a wide frequency range without depending on the frequency of the generated torsional vibration.

  (Claim 2) In the damper device, the amount of electromagnetic action between the electromagnet and the magnet can be changed and the deformation amount of the elastic body can be adjusted by the control unit controlling power feeding to the electromagnet. Thereby, the damper device can appropriately change the resonance frequency of the mass spring system. Thus, the damper device can reliably attenuate torsional vibrations corresponding to a wide frequency range.

  (Claim 3) The actuator efficiently changes the resonance frequency of the mass spring system by rotating the hub and the mass body relative to each other in the circumferential direction by the electromagnetic action of the electromagnets and deforming the elastic body to twist. Can do. Further, since the axial force generated in the rotating member and the mass body by the electromagnetic action can be reduced, the influence of the electromagnetic action on the rotation of the damper device can be reduced.

  (Claim 4) The rotating member and the mass body must be held close to each other to some extent so that the electromagnet or the electromagnetic action of the magnet can reach. Here, since the mass body is disposed radially outward of the hub, the rotating member needs to extend from the rotating shaft to which the hub is coupled to at least the radial position where the mass body is disposed. . Therefore, by using the rotary member as a flywheel, an electromagnet or a magnet can be suitably provided without adding a new member.

  (Claim 5) The mass body which is a pulley constitutes a damper pulley together with the hub and the elastic body. Therefore, the damper pulley can attenuate the torsional vibration of the crankshaft when transmitting the rotational driving force from the crankshaft to the belt, so that the operation of various accessories driven via the belt is further stabilized. it can. In this way, it is particularly useful to apply the configuration for damping torsional vibration to the damper pulley.

It is the figure which looked at the damper apparatus in the embodiment from the axial direction. It is sectional drawing of the axis orthogonal direction in FIG. It is a flowchart which shows the control processing of a damper apparatus.

<Embodiment>
The damper device of the embodiment will be described with reference to FIGS. 1 and 2. The damper device is attached to, for example, a crankshaft of an internal combustion engine of an automobile. This damper device is used for the purpose of attenuating vibration in the rotational direction of a crankshaft driven by an internal combustion engine. More specifically, the damper device attenuates torsional vibrations (also referred to as rotational fluctuations) 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.

(Configuration of damper device)
The damper device according to the present embodiment includes the damper pulley 1, the actuator 50, the vibration detector 60, and the actuator control unit 70. The damper pulley 1 is attached to the crankshaft 2 and is used with a V belt suspended on the outer periphery. The damper pulley 1 transmits the rotational driving force of the crankshaft 2 by the internal combustion engine to various auxiliary machines mounted on the automobile via a V-belt, for example, an alternator, a water pump, a cooler compressor, etc. Drive these accessories. The damper pulley 1 includes a hub 10, a pulley body 20, and an elastic body 30.

  The hub 10 is formed in a metal disk shape, and a cylindrical boss portion 11 is formed in the center. As shown in FIG. 2, the hub 10 is set in a state where the collar 4 is interposed between the boss portion 11 fitted on the outer peripheral surface of the crankshaft 2 and the flywheel 3 fixed to the crankshaft 2. They are connected by bolts 5. Thus, the hub 10 is disposed at the central shaft portion of the damper pulley 1 and rotates integrally with the crankshaft 2.

  As shown in FIG. 1, the pulley main body 20 is formed in a trapezoidal metal annular shape from the hub 10, and is disposed radially outward of the hub 10. The pulley body 20 corresponds to a mass body in the damper device. As shown in FIG. 2, a plurality of V grooves 21 around which a V belt (not shown) is suspended are formed on the outer peripheral surface of the pulley body 20 in the axial direction. Further, the pulley body 20 has a rotation balance weight 22 on its end face. The rotation balance weight 22 is disposed on the opposite side of the magnet 52 of the actuator 50 with respect to the rotation axis, and is provided in order to eliminate the rotation imbalance caused by the magnet 52.

  The elastic body 30 is formed in a cylindrical shape from rubber, and elastically connects the outer peripheral surface of the hub 10 and the inner peripheral surface of the pulley body 20. More 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 pulley body 20 are bonded with an adhesive or fixed by press-fitting. Yes. The elastic body 30 constitutes a mass spring type elastic member in the damper pulley 1 and absorbs the phase difference between the hub 10 and the pulley body 20. That is, the elastic body 30 reduces the torsional vibration by transmitting the vibration of the pulley body 20 to the hub 10 when the torsional vibration is transmitted from the crankshaft 2 to the hub 10. In the present embodiment, the elastic body 30 is the only member (mass spring type elastic member) that elastically connects the hub 10 and the pulley body 20.

  The actuator 50 changes the resonance frequency of the mass spring system including the pulley body 20 and the elastic body 30 by deforming the elastic body 30 by rotating the pulley body 20 relative to the hub 10. The actuator 50 includes an electromagnet 51, a magnet 52, a rectifying plate 53, and a brush 54. The electromagnet 51 is fixed to the end surface of the flywheel 3 (corresponding to the “rotating member” of the present invention) that rotates integrally with the hub 10.

  The magnet 52 is fixed to the end surface of the pulley body 20 and is disposed so as to face the electromagnet 51 provided on the flywheel 3 in the circumferential direction. As shown in FIG. 2, a conductive rectifying plate 53 is provided over the entire outer peripheral surface of the cylindrical portion 3 a formed at the center of the flywheel 3. The brush 54 is located radially outward of the rectifying plate 53 and is fixed to an engine block that is a fixed side of the internal combustion engine. The brush 54 is always in contact with a part of the rectifying plate 53 so as to maintain a state of being electrically connected to the rectifying plate 53 even when the rectifying plate 53 rotates integrally with the flywheel 3. Yes. As described above, the rectifying plate 53 and the brush 54 constitute an electric circuit that can supply power to the electromagnet 51.

  The actuator 50 having such a configuration generates a force that attracts or repels the magnet 52 when electric current is supplied to the electromagnet 51. That is, the actuator 50 generates a magnetic force corresponding to the supplied current value in the electromagnet 51 and causes the pulley body 20 to circulate around the hub 10 fixed to the crankshaft 2 by the electromagnetic action of the electromagnet 51 and the magnet 52. Rotate relative to direction. Then, since the elastic body 30 interposed between the hub 10 and the pulley body 20 is deformed so as to be twisted, the resonance frequency of the mass spring system including the pulley body 20 and the elastic body 30 is changed.

  The flywheel 3 to which the electromagnet 51, the current plate 53, etc. are fixed has a rotation balance weight 3b on the end surface. The rotation balance weight 3b is arranged on the opposite side of the electromagnet 51 of the actuator 50 across the rotation axis, and is provided to eliminate rotation imbalance caused by the electromagnet 51 and the like.

  The vibration detector 60 includes a magnetic sensor 61 and a target 62. The target 62 is fixed to the outer peripheral surface of the crankshaft 2 over the entire circumference, and rotates integrally with the crankshaft 2. The target 62 has through holes formed at equal intervals in the circumferential direction. The magnetic sensor 61 is fixed to the engine block at a predetermined interval from the target 62 outside the target 62 in the radial direction. The magnetic sensor 61 sends a signal corresponding to the unevenness due to the plurality of through holes formed in the target 62 to the vibration detector 60.

  With this configuration, the vibration detector 60 can detect the movement of the target 62 in the circumferential direction based on the signal input from the magnetic sensor 61. Further, the vibration detector 60 detects torsional vibration of the crankshaft 2 based on the number of rotations of the crankshaft 2 and the amount of change in the circumferential movement of the target 62. Thus, the vibration detector 60 is configured to detect vibration in the rotational direction of the hub 10 that rotates integrally with the crankshaft 2.

  The actuator controller 70 controls the actuator 50 based on the vibration in the rotational direction of the hub 10 detected by the vibration detector 60 to change the resonance frequency of the mass spring system. That is, when the torsional vibration generated in the hub 10 is detected, the actuator control unit 70 controls the current supplied to the electromagnet 51 of the actuator 50 to rotate the pulley body 20 relative to the hub 10 by a predetermined amount. Let Thereby, the actuator control part 70 is deform | transforming so that the elastic body 30 may be twisted, and the resonance frequency of the mass spring type | system | group containing the pulley main body 20 and the elastic body 30 is changed. As a result, the vibration damping characteristic of the damper pulley 1 as a whole can be actively changed, so that the torsional vibration generated in the crankshaft 2 can be attenuated in a wider frequency range than before.

(Control processing by damper device)
Control processing by the damper device having the above-described configuration will be described with reference to FIG. Here, the control in which the damper device suppresses vibration in the rotation direction of the crankshaft 2 in a state where the rotational driving force is transmitted to the crankshaft 2 by the internal combustion engine will be described as an example. When the control is started, a control program as shown in FIG. 3 is called and executed every predetermined period.

  In such control, first, the vibration detector 60 inputs the rotation speed information of the crankshaft 2 and a detection signal from the magnetic sensor 61 (S11). Here, the rotational speed information of the crankshaft 2 includes information such as a change state of the rotational speed, that is, an ascending gradient or a descending gradient, in addition to the current rotational speed. Then, the vibration detector 60 detects vibration (torsional vibration) in the rotation direction of the crankshaft 2 based on the input information and the detection signal (S12).

  Next, the actuator control unit 70 determines whether torsional vibration is occurring in the crankshaft 2 based on the detection result by the vibration detector 60 (S13). Here, when torsional vibration is generated (S13: Yes), there is a difference between the resonance frequency of the mass spring system in the damper pulley 1 in the current state and the frequency of the generated torsional vibration, and the torsional vibration is sufficiently generated. Is considered to have not been attenuated.

  Therefore, the actuator control unit 70 controls the actuator 50 in order to change the vibration damping characteristics of the damper pulley 1. Therefore, the actuator control unit 70 first determines the supply current value Ap so as to change the current value Ap supplied to the electromagnet 51 of the actuator 50 by a predetermined current value Ad (S14). Then, the damper device supplies power with the current value Ap determined by the actuator controller 70 to the electromagnet 51 (S15). Then, the electromagnet 51 and the magnet 52 are attracted or repelled by the electromagnetic action of the electromagnet 51 and the magnet 52.

  Here, the magnetic poles on the opposing surfaces of the electromagnet 51 and the magnet 52 are the same, and the magnet 52 provided on the pulley body 20 is moved in the direction attracted by the electromagnet 51 provided on the flywheel 3 by the above control. It shall be. Then, the pulley body 20 moves against the hub 10 by a predetermined amount according to the magnitude of the electromagnetic action in the circumferential direction against the elastic force of the elastic body 30. And since the elastic body 30 deform | transforms so that it may twist according to the movement amount of the pulley main body 20, the resonance frequency of the mass spring type | system | group containing the pulley main body 20 and the elastic body 30 is changed.

  When the control program is called up and executed again after a predetermined period of time, the vibration detector 60 receives the rotation speed information of the crankshaft 2 and a detection signal from the magnetic sensor 61 (S11), and detects torsional vibration. (S12). When the torsional vibration is attenuated to a predetermined value or less (S13: No), the process proceeds to S16. On the other hand, when the torsional vibration of the crankshaft 2 remains (S13: Yes), S11 to S15 are repeated and the torsional vibration is attenuated by gradually changing the current value Ap supplied to the electromagnet 51. .

  Here, in the above control, for example, even if the current value Ap supplied to the electromagnet 51 is increased, the torsional vibration may not be attenuated even though the rotation speed of the crankshaft 2 and the load of the auxiliary machinery are not changed. . In such a case, it is considered that the difference between the frequency corresponding to the vibration damping characteristic of the damper pulley 1 changed by the above control and the frequency of torsional vibration is increased. Therefore, when determining the current value Ap supplied to the electromagnet 51 in S14, the actuator control unit 70 may appropriately determine increase / decrease in the current value Ap based on the change in torsional vibration.

  Further, when it is determined that the torsional vibration is not generated in the crankshaft 2 (S13: No), the actuator control unit 70 performs an adjustment process of the current value Ap supplied to the electromagnet 51 (S16). In the adjustment process of the current value Ap, the operation amount of the actuator 50 is adjusted so that the vibration damping characteristic is returned to the initial state based on the state of the damper pulley 1.

  For example, when the rotation speed of the crankshaft 2 acquired in S11 is decreased as compared with the previous control, the actuator control unit 70 adjusts the current value Ap supplied to the electromagnet 51 to be reduced. . That is, when the torsional vibration is not generated in the crankshaft 2, the elastic body 30 is appropriately adjusted so as to return to the initial state where the elastic body 30 is not deformed. Thereby, the actuator control part 70 ensures the deformation amount of the elastic body 30 required when performing the control which attenuates the above-mentioned torsional vibration.

(Effects of the configuration of the embodiment)
According to the above-described damper device, the actuator 50 can change the resonance frequency of the mass spring system according to the torsional vibration of the crankshaft 2, that is, the vibration in the rotational direction of the hub 10. That is, the vibration damping characteristic of the damper pulley 1 can be actively changed. As a result, even when torsional vibration is generated in the crankshaft 2 to which the hub 10 is connected, the torsional vibration can be attenuated by changing to the vibration damping characteristic corresponding to the frequency of the torsional vibration. Thus, the damper device can cope with a wide frequency range without depending on the frequency of the generated torsional vibration.

  The actuator control unit 70 is configured to control power supply to the electromagnet 51. Accordingly, the damper device can adjust the deformation amount of the elastic body 30 by changing the magnitude of the electromagnetic action between the electromagnet 51 and the magnet 52. In addition, the electromagnet 51 and the magnet 52 are arranged so as to face each other in the circumferential direction. Thereby, the actuator 50 can be deformed so as to twist the elastic body 30. Furthermore, the axial force generated in the flywheel 3 and the pulley body 20 by the electromagnetic action of the electromagnet 51 and the magnet 52 can be reduced. Therefore, it is possible to reduce the influence of the magnetic action generated with the control of the damping of the torsional vibration on the rotation of the damper pulley 1 and the flywheel 3.

  Further, the electromagnet 51 of the actuator 50 is fixed to the flywheel 3. Thereby, the electromagnet 51 can be arrange | positioned in the magnet 52 at a suitable position so that an electromagnetic effect may reach the magnet 52 fixed to the pulley main body 20 using the existing flywheel 3.

  In the present embodiment, the mass body of the damper device is a pulley (pulley main body 20) suspended on the outer periphery of the damper device, and the damper pulley 1 is configured by the hub 10, the pulley main body 20, and the elastic body 30. In such a damper pulley 1, when the rotational driving force is transmitted from the crankshaft 2 to the V-belt, the torsional vibration of the crankshaft can be attenuated, so that various auxiliary machines driven via the V-belt Can be more stable. Therefore, it is particularly useful to apply a configuration that attenuates torsional vibration to the damper pulley 1.

<Modification of Embodiment>
In the present embodiment, the electromagnet 51 of the actuator 50 is fixed to the flywheel 3 that rotates integrally with the hub 10, and the magnet 52 is fixed to the pulley body 20. In contrast, the installation positions of the electromagnet 51 and the magnet 52 may be interchanged. That is, the electromagnet 51 may be provided on the mass body that is the pulley body 20, and the magnet 52 may be provided on the flywheel 3 that is the rotating member. Even in such a configuration, the same effects as in the present embodiment can be obtained.

  In addition, the actuator control unit 70 supplies current to the actuator 50 operated by the electromagnetic action of the electromagnet 51 and the magnet 52 so that the current current Ap supplied to the electromagnet 51 is changed by a predetermined current value Ad. The value Ap was determined (S14). On the other hand, the actuator control unit 70 controls the actuator 50 by directly calculating the supply current value Ap from, for example, a map indicating the relationship between the rotational speed information of the crankshaft 2 and the torsional vibration characteristics. You may do it.

  In the present embodiment, the actuator 50 includes the electromagnet 51 and the magnet 52. In addition, the actuator 50 only needs to be able to deform the elastic body 30 by relatively moving the mass body (the pulley body 20) in the circumferential direction with respect to the hub 10, for example, a magnetic body such as an electromagnet and an iron plate, or hydraulic pressure. Mechanisms can be applied. Even in such a configuration, the actuator control unit 70 can change the vibration damping characteristics of the damper device by performing the same control as in the present embodiment.

  Moreover, in this embodiment, the damper apparatus demonstrated the aspect which comprises the pulley main body 20 by which a mass body is belt-suspended on the outer periphery, and comprises the damper pulley 1 demonstrated. On the other hand, the structure which attenuates the torsional vibration of the present invention can also be applied to a damper device in which the mass body does not transmit the rotational driving force of the crankshaft 2 to other auxiliary machines.

  The vibration detector 60 is composed of a magnetic sensor 61 and a target 62. In addition, the vibration detector 60 only needs to be able to detect vibration in the rotation direction of the hub 10, that is, torsional vibration of a rotating shaft that rotates integrally with the hub 10. For example, an acceleration sensor attached to the hub 10 or the crankshaft 2. It is good. That is, the vibration detector detects vibration based on the presence / absence of acceleration vibration in the rotational direction of the hub 10 detected by the acceleration sensor. Even in such a configuration, the same effects as in the present embodiment can be obtained.

  Further, since the electromagnet 51 and the magnet 52 of the actuator 50 are provided on the flywheel 3 and the pulley main body 20 which are rotating bodies, the rotation balance weights 3b and 22 are disposed on the flywheel 3 and the pulley main body 20, respectively. did. On the other hand, instead of the rotation balance weights 3b and 22, two sets of actuators may be provided so as to sandwich the rotation axis. Thereby, the same mechanism can be comprised, without producing the imbalance of rotation of a mass body and a rotation member.

1: damper pulley, 3: flywheel (rotating member), 10: hub, 20: pulley body (mass body), 30: elastic body, 50: actuator, 51: electromagnet, 52: magnet, 60: vibration detector, 70 : Actuator controller

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 the resonance frequency of a mass spring system including the mass body and the elastic body by deforming the elastic body by rotating the mass body relative to the hub;
A vibration detector for detecting vibration in the rotational direction of the hub;
A control unit that controls the actuator based on the vibration in the rotational direction of the hub detected by the vibration detector to change the resonance frequency;
A damper device comprising: The actuator includes: a rotating member that rotates integrally with the hub; and an electromagnet provided on one member of the mass body; and a magnet provided on the rotating member and the other member of the mass body so as to face the electromagnet; Have
2. The damper device according to claim 1, wherein the control unit controls power supply to the electromagnet based on a rotation speed of the hub and vibration in a rotation direction of the hub.   The damper device according to claim 2, wherein the electromagnet and the magnet are arranged to face each other in the circumferential direction.   The damper device according to claim 2 or 3, wherein the rotating member is a flywheel provided on a crankshaft to which the hub is connected. The damper device according to any one of claims 1 to 4, wherein the mass body is a pulley having a belt suspended on an outer periphery.

Images