JP2006057753A - Active vibration control supporting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To accurately determine deterioration of an elastic body of an active vibration control supporting device by secular change or the like. <P>SOLUTION: This active vibration control supporting device M drives a movable core 54 by conducting electricity into a coil 46 of an actuator 41, and a second elastic body 27 partitioning a part of a second liquid chamber 31 is reciprocated to suppress transmission of vibration of an engine to a vehicle body frame. When the second elastic body 27 is deteriorated and air gap g of the movable core 54 is increased or decreased, it is determined that the second elastic body 27 is deteriorated when deviation of real current and target current exceeds a threshold value by focusing on change of inductance of the coil 46, change of real current, and non-agreement of real current and target current. When deterioration of the second elastic body 27 is determined, target current is compensated in accordance with the deviation to ensure a damping function of the active vibration control supporting device M. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an active antivibration support device that supports a load of a vibrating body and suppresses vibrations by periodically extending and contracting an actuator with a target current according to the vibration state of the vibrating body under the control of a control unit.

A conventional active vibration isolating support device calculates a crank angular velocity from a time interval of a crank pulse output at every predetermined rotation angle of the crankshaft, and calculates a crankshaft torque from a crank angular acceleration obtained by time differentiation of the crank angular velocity. The vibration state of the engine is estimated as the amount of torque fluctuation, and the vibration control function is exhibited by controlling the energization of the actuator coil in accordance with the vibration state of the engine (for example, see Patent Document 1 below). ).
JP 2003-113892 A

  By the way, in the active vibration isolating support device that generates vibration damping force by reciprocatingly driving an elastic body that partitions a part of the liquid chamber, an actuator connected to the elastic body when the elastic body deteriorates due to secular change or the like Since the air gap between the coil and the coil changes, the inductance of the coil changes and the actual current that flows through the coil does not match the target current even if a predetermined target current is supplied. Therefore, there is a possibility that the active vibration isolating support device cannot exhibit the desired vibration control function.

  The present invention has been made in view of the above-described circumstances, and an object of the present invention is to enable accurate determination of deterioration of an active vibration-proof support device.

  In order to achieve the above object, according to the first aspect of the present invention, the load of the vibrating body is supported, and the actuator is periodically operated at a target current corresponding to the vibration state of the vibrating body under the control of the control means. In the active vibration-proof support device that suppresses vibration by extending and contracting, the control unit determines a deterioration state of the device based on a deviation between the actual current of the actuator detected by the actual current detection unit and the target current. An active vibration isolating support device is proposed.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the actuator includes an armature that operates by energizing the coil to reciprocate an elastic body that defines a part of the liquid chamber. Further, there is proposed an active vibration isolating support device characterized in that the control means detects the deviation caused by a change in the position of the armature accompanying the deterioration of the elastic body.

  According to a third aspect of the present invention, in addition to the configuration of the first aspect, the control means corrects the target current in accordance with a deterioration state of the apparatus. A device is proposed.

  The engine E of the embodiment corresponds to the vibrating body of the present invention, the current sensor Sb of the embodiment corresponds to the actual current detection means of the present invention, and the electronic control unit U of the embodiment corresponds to the control means of the present invention. The second elastic body 27 of the embodiment corresponds to the elastic body of the present invention, the second liquid chamber 31 of the embodiment corresponds to the liquid chamber of the present invention, and the movable core 54 of the embodiment corresponds to the amateur of the present invention. Correspond.

  According to the configuration of the first aspect, when the control means suppresses the vibration of the vibrating body by supplying the target current to the actuator of the active vibration isolating support apparatus and periodically extending and contracting the active current detection means, Since the deterioration state of the device is determined based on the deviation between the detected actual current of the actuator and the target current, the active vibration isolation support device is sufficient by driving the actuator with the previous target current while the device is in a deteriorated state. It is possible to avoid a situation where the vibration control effect cannot be exhibited.

  According to the configuration of the second aspect, the actuator of the active vibration isolating support device reciprocates the elastic body that partitions a part of the liquid chamber by energizing the coil and driving the armature. When the amateur air gap increases or decreases, the inductance of the coil changes and the actual current changes, so that the electronic control unit can determine the deterioration state of the elastic body from the deviation between the actual current and the target current.

  According to the configuration of the third aspect, since the target current of the actuator is corrected in accordance with the deterioration state of the apparatus, it is possible to automatically compensate for a decrease in the vibration suppression function of the active vibration isolating support apparatus accompanying the deterioration.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on examples of the present invention shown in the accompanying drawings.

  1 to 5 show an embodiment of the present invention. FIG. 1 is a longitudinal sectional view of an active vibration isolating support device, FIG. 2 is an enlarged view of a part 2 in FIG. 1, and FIG. FIG. 4 is a first part of a flowchart for explaining the action, and FIG. 5 is a second part of the flowchart for explaining the action.

  As shown in FIGS. 1 and 2, an active anti-vibration support device M (active control mount) used for elastically supporting an automobile engine on a body frame is substantially axisymmetric with respect to an axis L. A substantially cup-shaped actuator case having an open upper surface between a flange portion 11a at the lower end of the substantially cylindrical upper housing 11 and a flange portion 12a at the upper end of the generally cylindrical lower housing 12. The outer peripheral flange portion 13a, the outer peripheral portion of the annular first elastic body support ring 14, and the outer peripheral portion of the annular second elastic body support ring 15 are overlapped and joined by caulking. At this time, the annular first floating rubber 16 is interposed between the flange portion 12a of the lower housing 12 and the flange portion 13a of the actuator case 13, and the upper portion of the actuator case 13 and the inner surface of the second elastic body support member 15 By interposing the annular second floating rubber 17 therebetween, the actuator case 13 is floatingly supported so as to be movable relative to the upper housing 11 and the lower housing 12.

  The lower end and the upper end of the first elastic body 19 formed of thick rubber are joined to the first elastic body support ring 14 and the first elastic body support boss 18 disposed on the axis L by vulcanization adhesion. Is done. A diaphragm support boss 20 is fixed to the upper surface of the first elastic body support boss 18 with bolts 21, and the outer peripheral portion of the diaphragm 22 joined to the diaphragm support boss 20 by vulcanization adhesion is added to the upper housing 11. Joined by sulfur adhesion. An engine mounting portion 20a integrally formed on the upper surface of the diaphragm support boss 20 is fixed to an engine (not shown). Further, the vehicle body mounting portion 12b at the lower end of the lower housing 12 is fixed to a vehicle body frame (not shown).

  A flange portion 23a at the lower end of the stopper member 23 is coupled to the flange portion 11b at the upper end of the upper housing 11 by bolts 24 ... and nuts 25 ..., and a diaphragm support boss 20 is attached to a stopper rubber 26 attached to the upper inner surface of the stopper member 23. The engine mounting portion 20a that protrudes from the upper surface of the upper and lower surfaces faces each other so as to be able to come into contact therewith. When a large load is input to the active vibration isolating support device M, the engine mounting portion 20a abuts against the stopper rubber 26, thereby suppressing excessive displacement of the engine.

  The outer peripheral portion of the second elastic body 27 formed of a film-like rubber is joined to the second elastic body support ring 15 by vulcanization adhesion, and the movable member 28 is added so as to be embedded in the central portion of the second elastic body 27. Joined by sulfur adhesion. A disk-shaped partition wall member 29 is fixed between the upper surface of the second elastic body support ring 15 and the outer periphery of the first elastic body 19, and the first partition partitioned by the partition wall member 29 and the first elastic body 19. The liquid chamber 30 and the second liquid chamber 31 partitioned by the partition member 29 and the second elastic body 27 communicate with each other through a communication hole 29 a formed at the center of the partition member 29.

  An annular communication path 32 is formed between the first elastic body support ring 14 and the upper housing 11, and one end of the communication path 32 communicates with the first liquid chamber 30 through the communication hole 33. The other end communicates with the third liquid chamber 35 defined by the first elastic body 19 and the diaphragm 22 through the communication hole 34.

  Next, the structure of the actuator 41 that drives the movable member 28 will be described.

  The fixed core 42, the coil assembly 43, and the yoke 44 are sequentially attached to the inside of the actuator case 13 from the bottom to the top. The coil assembly 43 includes a bobbin 45 disposed on the outer periphery of the fixed core 42, a coil 46 wound around the bobbin 45, and a coil cover 47 that covers the outer periphery of the coil 46. The coil cover 47 is integrally formed with a connector 48 that extends through the openings 13b and 12c formed in the actuator case 13 and the lower housing 12 and extends to the outside.

  A seal member 49 is disposed between the upper surface of the coil cover 47 and the lower surface of the yoke 44, and a seal member 50 is disposed between the lower surface of the bobbin 45 and the upper surface of the fixed core 42. These seal members 49 and 50 can prevent water and dust from entering the internal space 61 of the actuator 41 from the openings 13 b and 12 c formed in the actuator case 13 and the lower housing 12.

  A thin cylindrical bearing member 51 is fitted to the inner peripheral surface of the cylindrical portion 44a of the yoke 44 so as to be vertically slidable. An upper flange 51a bent radially inward is formed at the upper end of the bearing member 51. A lower flange 51b that is bent radially outward is formed at the lower end. A set spring 52 is disposed in a compressed state between the lower flange 51b and the lower end of the cylindrical portion 44a of the yoke 44. The elastic force of the set spring 52 causes the lower flange 51b to be fixed to the fixed core 42 via the elastic body 53. The bearing member 51 is supported by the yoke 44 by being pressed against the upper surface of the yoke 44.

  A substantially cylindrical movable core 54 is fitted to the inner peripheral surface of the bearing member 51 so as to be slidable up and down. A rod 55 extending downward from the center of the movable member 28 penetrates the center of the movable core 54 loosely, and a nut 56 is fastened to the lower end thereof. A set spring 58 in a compressed state is disposed between a spring seat 57 provided on the upper surface of the movable core 54 and the lower surface of the movable member 28, and the movable core 54 is pressed against the nut 56 by the elastic force of the set spring 58. Fixed. In this state, the lower surface of the movable core 54 and the upper surface of the fixed core 42 face each other via the conical air gap g. The rod 55 and the nut 56 are loosely fitted into an opening 42 a formed at the center of the fixed core 42, and the opening 42 a is closed by a plug 60 through a seal member 59.

  A crank pulse sensor Sa for detecting a crank pulse output as the crankshaft of the engine rotates, a current sensor Sb for detecting an actual current supplied to the actuator 41, and a battery for supplying power to the active vibration isolating support device M An electronic control unit U connected to a battery voltage sensor Sc for detecting the voltage of the engine, a temperature sensor Sd for detecting the temperature of the active vibration isolating support device M, and an engine speed sensor Se for detecting the engine speed, The target current supplied to the actuator 41 of the active vibration isolating support apparatus M is controlled. The engine crank pulse is output 24 times per revolution of the crankshaft, that is, once every 15 ° of the crank angle.

  Next, the operation of the embodiment of the present invention having the above configuration will be described.

  When low-frequency engine shake vibration is generated while the vehicle is running, the first elastic body 19 is deformed by a load input from the engine via the diaphragm support boss 20 and the first elastic body support boss 18, and the first liquid When the volume of the chamber 30 changes, the liquid goes back and forth between the first liquid chamber 30 and the third liquid chamber 35 connected via the communication path 32. When the volume of the first liquid chamber 30 is enlarged / reduced, the volume of the third liquid chamber 35 is reduced / expanded accordingly, but the volume change of the third liquid chamber 35 is absorbed by the elastic deformation of the diaphragm 22. At this time, the shape and size of the communication path 32 and the spring constant of the first elastic body 19 are set so as to exhibit a low spring constant and a high damping force in the frequency region of the engine shake vibration. The vibration transmitted to can be effectively reduced.

  In the frequency region of the engine shake vibration, the actuator 41 is kept in an inoperative state.

  When vibration having a higher frequency than the engine shake vibration, that is, vibration during idling or vibration during cylinder deactivation caused by rotation of the crankshaft of the engine occurs, the first liquid chamber 30 and the third liquid chamber 35 are connected. Since the liquid in the communication path 32 is in a stick state and cannot exhibit the anti-vibration function, the actuator 41 is driven to exhibit the anti-vibration function.

  By the way, the first elastic body 19 and the second elastic body 27 of the active vibration isolating support apparatus M gradually deteriorate due to secular change or the like, but in particular, when the second elastic body 27 connected to the movable member 28 deteriorates, the movable member 28, the vertical position of the movable core 54 connected via the rod 55 deviates from the initial position, so that the size of the air gap g formed between the lower surface of the movable core 54 and the upper surface of the fixed core 42 varies. To do. When the size of the air gap g changes in this way, the inductance of the coil 46 of the actuator 41 changes, so that even if a predetermined target current is supplied to the coil 46 by a command from the electronic control unit U, FIG. As shown, there is a possibility that the current actually flowing through the coil 46 (actual current detected by the current sensor Sb) does not match the target current, and the active vibration isolating support device M cannot exhibit a sufficient damping function. There is.

  Therefore, in the present embodiment, the above problem is solved as follows.

That is, in the flowcharts of FIG. 4 and FIG. 5, first, in step S1, a crank pulse output from the crank pulse sensor Sa every 15 ° of crank angle is read, and in step S2, the read crank pulse is used as a reference crank pulse ( The time interval of the crank pulse is calculated by comparing with the TDC signal of a specific cylinder). In the next step S3, the crank angular velocity ω is calculated by dividing the crank angle of 15 ° by the time interval of the crank pulse, and in step S4, the crank angular velocity ω is time-differentiated to calculate the crank angular acceleration dω / dt. In the following step S5, the torque Tq around the engine crankshaft is set as I, and the moment of inertia around the engine crankshaft is set as I.
Tq = I × dω / dt
Calculate by This torque Tq is zero assuming that the crankshaft is rotating at a constant angular velocity ω, but in the expansion stroke, the angular velocity ω increases due to acceleration of the piston, and in the compression stroke, the angular velocity ω decreases due to deceleration of the piston. Since the crank angular acceleration dω / dt is generated, a torque Tq proportional to the crank angular acceleration dω / dt is generated.

  In the subsequent step S6, the maximum value and the minimum value of the temporally adjacent torque are determined, and in step S7, the active vibration isolation support device M that supports the engine as a deviation between the maximum value and the minimum value of the torque, that is, the amount of torque fluctuation. In step S8, the waveform and timing (phase) of the current applied to the coil 46 of the actuator 41 are determined. In step S9, the target current of the actuator 41 is determined from the amplitude, waveform and timing. .

  In subsequent step S10, the battery voltage is detected by the battery voltage sensor Sc, and the target current is corrected according to the deviation between the detected voltage and the reference voltage. In step S11, the temperature of the active vibration isolating support device M is corrected by the temperature sensor Sd. The temperature is detected, and the target current is corrected according to the deviation between the detected temperature and the reference temperature. In step S12, the corrected target current is supplied to the actuator 41. In step S13, the actual current flowing through the actuator 41 is detected by the current sensor Sb.

  In the subsequent step S14, the absolute value of the deviation between the target current and the actual current of the actuator 41 is calculated. If the absolute value of the deviation is equal to or less than a predetermined threshold value, the active vibration isolating support device M (specifically, the second value) It is determined that the elastic body 27) has not deteriorated, and the process returns to step S1. On the other hand, if the absolute value of the deviation between the target current and the actual current of the actuator 41 exceeds a predetermined threshold value in step S14, the active vibration isolating support device M (specifically, the second elastic body 27) deteriorates. In step S15, the target current is corrected by changing the gain map when determining the target current from the vibration state of the engine in accordance with the deviation, thereby degrading the active vibration isolating support device M. To compensate for the effects of At this time, the target current can be corrected with higher accuracy by considering the engine speed detected by the engine speed sensor Se.

  Thus, when the engine moves downward with respect to the vehicle body frame and the first elastic body 19 is deformed downward to reduce the volume of the first liquid chamber 30, the coil 46 of the actuator 41 is excited in accordance with the timing. Then, the movable core 54 moves downward toward the fixed core 42 by the suction force generated in the air gap g, and is pulled by the movable member 28 connected to the movable core 54 via the rod 55, so that the second elastic body 27. Deforms downward. As a result, since the volume of the second liquid chamber 31 increases, the liquid in the first liquid chamber 30 compressed by the load from the engine passes through the communication hole 29a of the partition wall member 29 and flows into the second liquid chamber 31. The load transmitted from the engine to the vehicle body frame can be reduced.

  Subsequently, when the engine moves upward with respect to the vehicle body frame and the first elastic body 19 is deformed upward to increase the volume of the first liquid chamber 30, the coil 46 of the actuator 41 is demagnetized in accordance with the timing. Since the attracting force generated in the air gap g disappears and the movable core 54 can move freely, the second elastic body 27 deformed downward is restored upward by its own elastic restoring force. As a result, since the volume of the second liquid chamber 31 decreases, the liquid in the second liquid chamber 31 passes through the communication hole 29a of the partition wall member 29 and flows into the first liquid chamber 30, and the engine is in contact with the vehicle body frame. It can be allowed to move upward.

  In this way, by exciting and demagnetizing the coil 46 of the actuator 41 according to the engine vibration cycle, it is possible to generate an active damping force that prevents the engine vibration from being transmitted to the vehicle body frame. .

  As described above, the deterioration state of the active vibration isolating support device M is determined by comparing the target current of the actuator 41 and the actual current, and when the deterioration affecting the performance is determined, the target current is set. Since it correct | amends, the active vibration-proof support apparatus M can exhibit the stable damping function over a long period of time.

  Although the embodiments of the present invention have been described above, various design changes can be made without departing from the scope of the present invention.

  For example, although the active vibration isolating support device M of the embodiment is applied to support an automobile engine, it can be applied to any other use.

  In the embodiment, when the deterioration of the active vibration isolating support device M is determined, the target current is corrected by changing the gain map when determining the target current from the vibration state of the engine. The correction may be performed by changing the map for searching for the correction value of the target current according to the deviation between the target current and the actual current, and adding the correction value searched from the map to the target current.

Longitudinal section of active vibration isolator 2 enlarged view of FIG. Graph showing mismatch between target current and actual current of actuator First part of the flowchart explaining the operation Second part of the flowchart explaining the operation

Explanation of symbols

E Engine (vibrating body)
Sb current sensor (actual current detection means)
U Electronic control unit (control means)
27 Second elastic body (elastic body)
31 Second liquid chamber (liquid chamber)
41 Actuator 46 Coil 54 Movable core (Amateur)

Claims (3)

The load of the vibrating body (E) is supported, and the actuator (41) is periodically expanded and contracted with a target current corresponding to the vibration state of the vibrating body (E) by the control means (U) to suppress vibration. In an active vibration isolating support device,
The control means (U) determines the deterioration state of the apparatus based on the deviation between the actual current of the actuator (41) detected by the actual current detection means (Sb) and the target current. Vibration support device.   The actuator (41) includes an armature (54) that operates by energizing the coil (46) to reciprocate an elastic body (27) that partitions a part of the liquid chamber (31), and the control means ( The active vibration-proof support device according to claim 1, wherein U) detects the deviation caused by a change in the position of the amateur (54) due to deterioration of the elastic body (27). The active vibration isolating support device according to claim 1, wherein the control means (U) corrects the target current in accordance with a deterioration state of the device.

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