JP2006002831A - Active vibration control supporting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide effective vibration control function by compensating positional deviation of a movable member of an active vibration control supporting device. <P>SOLUTION: When current corresponding to a vibration condition of an engine being a vibration body is supplied to an actuator 41 of the active vibration control supporting device M and volume of liquid chambers 30, 31 is changed by the movable member 28 reciprocated by the actuator 41 to provide vibration control function, the movable member 28 is driven with excellent precision to make the active vibration control supporting device M exert the effevtive vibration control function because a duty value of the current supplied to the actuator 41 is controlled to compensate positional deviation (fluctuation from a reference value of an air gap g between a fixed core 42 and a movable core 54) of a reference position of the movable member 28 detected by a lift amount sensor Sb. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an elastic body that receives a load of a vibrating body, a liquid chamber in which the elastic body forms at least a part of a wall surface, an actuator that reciprocates upon receiving a supply of current according to a vibration state of the vibrating body, and an actuator The present invention relates to an active vibration isolating support device including a movable member that reciprocates to change the volume of a liquid chamber and a control unit that controls a current supplied to an actuator.

  Such an active vibration isolating support device is known from Patent Document 1 below.

This 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, calculates a crankshaft torque from a crank angular acceleration obtained by time-differentiating the crank angular velocity, The vibration state of the engine is estimated as a torque fluctuation amount, and the vibration control function is exhibited by controlling the energization of the coil of the actuator according to the vibration state of the engine.
JP 2003-113892 A

  By the way, when the position of the movable member driven by the actuator of the active vibration isolating support apparatus is displaced from the reference position, the size of the air gap of the actuator fluctuates with respect to the reference value. However, it is difficult to control the displacement of the movable member with high accuracy so that the active vibration isolating support device exhibits an effective anti-vibration function.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to compensate for the displacement of the movable member of the active vibration isolating support device and to exhibit an effective vibration isolating function.

  To achieve the above object, according to the first aspect of the present invention, an elastic body that receives a load of the vibrating body, a liquid chamber in which the elastic body forms at least a part of a wall surface, and a vibration state of the vibrating body Active vibration isolator comprising: an actuator that reciprocates upon receipt of a current corresponding to the current; a movable member that reciprocates by the actuator to change the volume of the liquid chamber; and a control means that controls the current supplied to the actuator. The support device includes a displacement sensor that detects a displacement of the reference position of the movable member, and the control unit controls the current supplied to the actuator so as to compensate for the displacement detected by the displacement sensor. A mold anti-vibration support device is proposed.

  The first elastic body 19 of the embodiment corresponds to the elastic body of the present invention, the first and second liquid chambers 30 and 31 of the embodiment correspond to the liquid chamber of the present invention, and the engine of the embodiment corresponds to the present invention. The lift amount sensor Sb of the embodiment corresponds to the displacement sensor of the present invention, and the electronic control unit U of the embodiment corresponds to the control means of the present invention.

  According to the configuration of claim 1, when the current corresponding to the vibration state of the vibrating body is supplied to the actuator and the volume of the liquid chamber is changed by the movable member reciprocating by the actuator, the displacement is exerted. Since the current supplied to the actuator is controlled so as to compensate for the displacement of the reference position of the movable member detected by the sensor, the movable member is driven with high accuracy and the active vibration isolation support device exhibits an effective vibration isolation function. be able to.

  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 3 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. It is.

  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). A flange-like vehicle body mounting portion 12b provided 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 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 44 are opposed to each other via the conical air gap g. The rod 55 and the nut 56 are loosely fitted inside an opening 42 a formed at the center of the fixed core 42.

  The electronic control unit U that controls energization to the actuator 41 of the active vibration isolating support device M includes a crank pulse sensor Sa that detects a crank pulse that is output as the crankshaft of the engine rotates, and a position of the movable member 28. A lift amount sensor Sb that detects (that is, the size of the air gap g) is connected. The engine crank pulse is output 24 times per revolution of the crankshaft, that is, once every 15 ° of the crank angle.

  The lift amount sensor Sb provided at the lower portion of the actuator 41 includes a sensor housing 59 coupled to the lower surface of the vehicle body mounting portion 12b of the lower housing 12 by bolts 66. A sensor rod 61 is slidably supported on a guide member 60 fixed inside the sensor housing 59, and the lower end of the sensor rod 61 is attached upward by a coil spring 62 provided between the sensor housing 59 and the bottom. By being biased, the upper end of the sensor rod 61 contacts the lower surface of the nut 56.

  A contact 64 fixed to the sensor rod 61 is in contact with the resistor 63 fixed inside the sensor housing 59. An electrical resistance value between the lower end of the resistor 63 and the contact 64 is input to the electronic control unit U via the connector 65. The lift amount of the movable member 20 corresponds to the position of the contact 50, and the magnitude of the electrical resistance value output by the lift amount sensor Sb changes according to the position of the contact 64 (that is, the position of the movable member 20). The lift amount of the movable member 20 can be detected according to the electric resistance value.

  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.

  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.

  The electronic control unit U controls the energization of the coil 46 based on the signal from the crank pulse sensor Sa in order to operate the actuator 41 of the active vibration isolating support device M to exhibit the vibration isolating function.

That is, in the flowchart of FIG. 3, 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 (specific cylinder). And the time interval of the crank pulse is calculated. 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. The amplitude at the position of is calculated. In step S8, the duty waveform and timing (phase) of the current applied to the coil 46 of the actuator 41 are determined.

  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 in accordance with the period of vibration of the engine, it is possible to generate an active damping force that prevents the vibration of the engine from being transmitted to the body frame. .

  By the way, when the coil 46 of the actuator 41 is demagnetized, the air gap g between the fixed core 42 and the movable core 54 needs to be maintained at a constant size. It means you have to be in position. If the movable member 28 is displaced from the reference position when the coil 46 of the actuator 41 is demagnetized, and the air gap g does not match the predetermined reference value, the air flows even if a constant current is passed through the coil 46. When the gap g is excessively large, the attracting force of the movable core 54 becomes small, and when the air gap g is excessively small, the attracting force of the movable core 54 becomes large. Therefore, it is impossible to control the displacement of the movable member 28 with high accuracy. become.

  Such fluctuations in the air gap g are compressed by the active vibration-proof support device M because the engine tends to fall in the front-rear direction or the left-right direction due to the longitudinal acceleration when the vehicle starts or brakes or the lateral acceleration when the vehicle turns. It occurs not only when a load or tensile load is applied, but also when the second elastic body 27 and the set spring 58 are deteriorated due to secular change.

  Therefore, the lift amount sensor Sb detects whether or not the position of the movable member 28 is lower than the target position in step S9 in the flowchart of FIG. 3, and as a result, if the position of the movable member 28 is lower than the target position, that is, If the air gap g is smaller than the reference value, the duty value of the current supplied to the coil 46 is decreased in step S10 so that the attractive force of the movable core 54 by the coil 46 does not become excessive. On the contrary, if the position of the movable member 28 is higher than the target position, that is, if the air gap g is larger than the reference value, the coil 46 is applied to the coil 46 in step S11 so that the attractive force of the movable core 54 by the coil 46 does not become too small. Increase the duty value of the supplied current. At this time, the relationship between the fluctuation amount of the air gap g and the correction amount of the duty value is stored in advance in the electronic control unit U as a map.

  As described above, the fluctuation of the air gap g, which is a displacement from the reference position of the movable member 28, is detected by the lift amount sensor Sb, and the duty value of the current supplied to the coil 46 of the actuator 41 is determined based on the detection result. Since the correction is performed, the movable member 28 can be accurately driven with the target lift amount to effectively exhibit the vibration isolation effect of the active vibration isolation support device M.

  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, in the embodiment, the active vibration isolation support device M that supports the engine of the automobile is illustrated, but the active vibration isolation support device M of the present invention can be applied to support any vibration body other than the engine of the automobile. it can.

Longitudinal section of active vibration isolator 2 enlarged view of FIG. Flow chart explaining operation

Explanation of symbols

19 First elastic body (elastic body)
28 Movable member 30 First liquid chamber (liquid chamber)
31 Second liquid chamber (liquid chamber)
41 Actuator Sb Lift Sensor (Displacement Sensor)
U Electronic control unit (control means)

Claims (1)

An elastic body (19) that receives the load of the vibrating body;
A liquid chamber (30, 31) in which the elastic body (19) constitutes at least a part of the wall surface;
An actuator (41) that reciprocates upon receiving a supply of current according to the vibration state of the vibrating body; and a movable member (28) that reciprocates by the actuator (41) to change the volume of the liquid chamber (30, 31); ,
Control means (U) for controlling the current supplied to the actuator (41);
In an active vibration isolating support device comprising:
A displacement sensor (Sb) for detecting the displacement of the reference position of the movable member (28) is provided, and the control means (U) supplies the actuator (28) to compensate for the displacement detected by the displacement sensor (Sb). An anti-vibration support device for controlling a current to be generated.

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