JP2010107000A - Active vibration control supporting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an active vibration control supporting device for supporting an engine of a vehicle and suppressing vibration transmitted to a vehicle body from the engine by periodic telescopic motion, which is excellent in vibration suppressing effect and can be miniaturized. <P>SOLUTION: The active vibration control supporting device includes a coil 46 having a densely wound conductor, for exciting by being energized; a movable core 54 displaced in accordance with energization/deenergization of the coil 46 to cause the telescopic motion; and a step surface 62a having step widths (m) and (n) of natural number times of a thickness of one layer of the wound conductor, wherein the conductor is wound so as to enlarge in diameter to an opening direction of the inner peripheral surface. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an active vibration isolating support device that supports an engine of a vehicle and suppresses vibration transmitted from the engine to a vehicle body by periodic expansion and contraction motion.

An active vibration isolating support device that supports the engine with respect to the vehicle body and applies a current according to the vibration state of the engine to the coil to expand and contract the actuator to suppress transmission of vibration from the engine to the vehicle body. It is disclosed in Patent Document 1.
The active vibration isolating support device disclosed in Patent Document 1 aims to improve the output of the expansion and contraction motion while suppressing the enlargement of the device, and the inner peripheral surface of the coil facing the movable core that guides the expansion and contraction motion is in the opening direction. It is the structure provided with the conical surface which expands in diameter.
By being configured in this way, the number of turns of the conducting wire can be increased without increasing the coil, and the lines of magnetic force induced from the coil current can be increased to improve the output of the expansion and contraction motion.
JP 2007-57074 A (FIG. 2)

However, when the conical surface is provided near the opening of the coil as described above, the regularity of the coil arrangement wound in the vicinity of the conical surface is disturbed, as shown in FIG. In this case, the density of the magnetic field lines penetrating the movable core becomes non-uniform, and there is a problem that the periodic expansion and contraction motion of the active vibration isolating support device is disturbed to reduce the effect of suppressing the transmission vibration to the vehicle body.
Further, as shown in FIG. 4B, when the conductive wires are densely arranged so that the coil arrangement is not irregular, the angle of the inclined surface of the conical surface is limited to a constant of 30 deg. If the inclination angle of the conical surface is 30 deg, it is impossible to expect a large increase in the lines of magnetic force penetrating the movable core, so that there is a problem that the output of the expansion / contraction motion cannot be expected.

  An object of the present invention is to solve the above-described problems, and by improving the output and uniformity of periodic expansion and contraction motion, an active vibration-proof support device that is excellent in suppressing vibration transmitted from the engine to the vehicle body The purpose is to provide.

In order to solve the above-mentioned problems, the present invention is an active vibration-proof support device that supports an engine and suppresses vibration transmitted from the engine to the vehicle body by expansion and contraction, and is excited when a conductor is densely wound and energized. A coil and a movable core that is disposed at a position facing the inner peripheral surface of the coil and that is displaced in accordance with excitation / demagnetization of the coil to guide the expansion / contraction motion, and is a natural number of one-layer thickness of the wound conductive wire And a step surface around which the conducting wire is wound so that the inner circumferential surface has a diameter that is doubled in the opening direction.
Further, the step surface is provided at a connecting portion between a shaft body around which the conducting wire is wound and a flange plate on which both end surfaces of the coil are held, and these form a coil bobbin formed integrally with resin. It is characterized by being.

  By configuring the invention in this way, the conductive wire wound so as to expand in the opening direction on the inner peripheral surface of the coil does not have an irregular arrangement. Therefore, the density of the magnetic lines passing through the movable core is low. Make uniform. Furthermore, since a slope with a large inclination angle can be set in the vicinity of the opening on the inner peripheral surface of the coil, an increase in the lines of magnetic force passing through the movable core can be expected, and the output of the expansion and contraction motion can be improved.

  The present invention provides a small active vibration isolating support device that is excellent in suppressing vibration transmitted from the engine to the vehicle body.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
As shown in FIG. 1, the active vibration isolating support device M has a substantially axisymmetric structure with respect to the axis L, and has a substantially cylindrical upper housing 11 and a substantially cylindrical shape disposed below the upper housing 11. Lower housing 12, a substantially cup-shaped actuator case 13 accommodated in the lower housing 12 and having an open upper surface, a diaphragm 22 connected to the upper side of the upper housing 11, and an annular second housing housed in the upper housing 11. A first elastic body support ring 14, a first elastic body 19 connected to the upper side of the first elastic body support ring 14, an annular second elastic body support ring 15 accommodated in the actuator case 13, and a second elastic body support A second elastic body 27 connected to the inner peripheral side of the ring 15, and a drive housed in the actuator case 13 and disposed below the second elastic body support ring 15 and the second elastic body 27. And a unit (actuator) 41 and the like.
The active anti-vibration support device M configured as described above supports the engine and suppresses vibration transmitted from the engine to the vehicle body by the periodic expansion and contraction movement of the drive unit 41.

  Between the flange portion 11a at the lower end of the upper housing 11 and the flange portion 12a at the upper end of the lower housing 12, the flange portion 13a on the outer periphery of the actuator case 13, the outer periphery portion 14a of the first elastic body support ring 14, and the actuator case The upper cross section of the second elastic support ring 15 having an annular cross section disposed on the upper side of 13 and having a substantially U shape and having upper and lower outer peripheries is overlapped and joined by caulking. At this time, an annular first floating rubber 16 is interposed between the flange portion 12a and the flange portion 13a, and an annular shape is formed between the upper surface of the flange portion 13a and the lower surface of the upper surface outer peripheral portion 15a of the second elastic body support ring 15. By interposing the second floating rubber 17, the actuator case 13 is floatingly supported so as to be movable relative to the upper housing 11 and the lower housing 12 in the vertical direction.

The first elastic body support ring 14 and the first elastic body support boss 18 disposed in a recess provided on the upper surface side of the first elastic body 19 are a first elastic body 19 formed of a thick rubber. Are joined by vulcanization adhesion at the lower and upper ends. Further, 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 bonding is formed on the upper housing. 11 is bonded by vulcanization adhesion.
An engine mounting portion (operation point) 20a is integrally formed on the upper surface of the diaphragm support boss 20 and is fixed to an engine (not shown). In addition, the vehicle body attachment portion 12b at the lower end of the lower housing 12 is fixed to a vehicle body frame (not shown).

A flange portion 23 a at the lower end of the stopper member 23 is coupled to the flange portion 11 b at the upper end of the upper housing 11 by a bolt 24 and a nut 25, and a diaphragm support boss is attached to a stopper rubber 26 attached to the upper inner surface of the stopper member 23. An engine mounting portion 20a projecting from the upper surface of the 20 faces the abutable surface.
With such a structure, when a large load is input from the engine 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 inner peripheral surface of the second elastic body support ring 15 by vulcanization adhesion, and the second elastic body 27 is connected to the central portion of the second elastic body 27. The movable member 28 is joined by vulcanization adhesion so that the upper part is embedded.

  A disk-shaped partition wall member 29 is fixed between the upper surface of the second elastic body support ring 15 and the lower portion of the first elastic body support ring 14, and the first elastic body support ring 14, the first elastic body 19 and the first liquid chamber 30 defined by the partition member 29 and the second liquid chamber 31 defined by the partition member 29 and the second elastic body 27 are open to the center of the partition member 29. Communicate with each other via

The outer peripheral portion 27a of the second elastic body 27 is sandwiched between the lower surface of the second elastic body support ring 15 and a yoke 44 described later, and has a sealing function.
An annular communication path 32 is formed between the first elastic body support ring 14 and the upper housing 11. The communication path 32 communicates with the first liquid chamber 30 via the communication hole 33 and also communicates with the third liquid chamber 35 defined by the first elastic body 19 and the diaphragm 22 via the annular communication gap 34.

  The drive unit 41 includes a fixed core 42, a coil assembly 43, a yoke 44, a movable core 54, and the like mainly made of a metal or alloy having a high magnetic permeability.

The fixed core 42 has a substantially cylindrical shape having a flange portion of a receiving seat surface at a lower end portion, and the outer periphery of the cylindrical portion has a conical circumferential shape.
The movable core 54 has a substantially cylindrical shape, and its upper end protrudes in the inner circumferential direction to form a spring seat 54a. The inner circumference of the cylindrical portion below the spring seat 54a has a conical circumferential surface shape.

The coil assembly 43 is disposed between the fixed core 42 and the yoke 44, and includes a coil 46, a coil bobbin 62 that holds the coil 46, and a coil cover 47 that covers the side peripheral surface of the coil 46.
The coil cover 47 is formed by molding a coil bobbin 62 holding the coil 46 with a synthetic resin. The connector 48 formed integrally with the coil cover 47 penetrates the lower housing 12 and the actuator case 13 and extends to the outside, and a feed line for supplying power to the coil 46 is connected to the open end. .

The yoke 44 has a cylindrical shape with a flange. A thin cylindrical bearing member 51 is slidably fitted in the inner peripheral surface of the cylindrical portion in the vertical direction. The upper end is bent in a flange shape radially inward, and the lower end is bent in a flange shape radially outward.
A set spring 52 is disposed in a compressed state between the lower end of the bearing member 51 and the lower end of the cylindrical portion of the yoke 44, and the bearing member 51 is urged downward and fixed by the elastic force of the set spring 52. It is pressed against the upper surface of the core 42.

  A substantially cylindrical movable core 54 is fitted to the inner peripheral surface of the bearing member 51 so as to be slidable in the vertical direction. Further, each of the fixed core 42 and the movable core 54 has a hollow center portion on the symmetry axis L, and is connected to the center portion (on the symmetry axis L) of the movable member 28 and extends downward. A columnar rod 55 is inserted. A nut 56 is fastened to the lower end portion of the rod 55. The nut 56 has a hollow portion whose upper end is open at the center, and the lower end side of the rod 55 is accommodated in the hollow portion. The upper end portion of the nut 56 has a slightly larger outer diameter than below, and is in contact with the movable core 54.

A set spring 58 in a compressed state is disposed between the upper surface of the movable core 54 and the lower surface of the movable member 28, and the movable core 54 is urged downward by the elastic force of the set spring 58. Is pressed against the upper surface of the nut 56 and fixed. In this state, the inner peripheral surface of the conical peripheral surface of the cylindrical portion of the movable core 54 and the outer peripheral surface of the conical peripheral surface of the fixed core 42 are opposed to each other via the conical peripheral surface gap g1. ing.
The nut 56 is fastened to the rod 55 such that its position can be adjusted in the vertical direction, and the space is closed by a rubber cap 60.

The crank pulse sensor Sa detects a crank pulse that is output a plurality of times per rotation of a crankshaft (not shown) in the engine, that is, once for every fixed crank angle.
The electronic control unit 71 estimates the vibration state of the engine based on the crank pulse signal from the crank pulse sensor Sa and the TDC signal from the cam angle sensor Sb, and controls energization supplied to the drive unit 41.

  By the energization control from the electronic control unit 71, the coil 46 is excited, attracts the movable core 54, and moves the movable member 28 downward. As the movable member 28 moves, the second elastic body 27 defining the second liquid chamber 31 is deformed downward, and the volume of the second liquid chamber 31 increases. Conversely, when the coil 46 is demagnetized, the second elastic body 27 is deformed upward by its own elasticity, the movable member 28 and the movable core 54 are raised, and the volume of the second liquid chamber 31 is reduced.

  Here, when the vehicle is running, engine shake vibration, which is low frequency vibration generated by resonance of the rigid body of the vehicle body and resonance of the engine system, occurs in the coupled system of the engine, the vehicle body, and the suspension of low frequency (for example, 7 to 20 Hz). Suppose that At this time, when the first elastic body 19 is deformed by the load input from the engine via the diaphragm support boss 20 and the first elastic body support boss 18 and the volume of the first liquid chamber 30 is changed, the communication path 32 is used. The liquid flows between the first liquid chamber 30 and the third liquid chamber 35 connected to each other.

In this state, when the volume of the first liquid chamber 30 is expanded / reduced, the volume of the third liquid chamber 35 is decreased / expanded accordingly, but the volume change of the third liquid chamber 35 is caused by the elastic deformation of the diaphragm 22. Absorbed. 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. Vibration transmitted to the frame can be effectively reduced.
In the frequency region of the engine shake vibration, when the engine is in steady rotation, the drive unit 41 is kept in a non-operating state in which it is not driven.

  Vibration at a frequency higher than the engine shake vibration, that is, vibration during idling due to rotation of a crankshaft (not shown) of the engine, vibration during cylinder deactivation operation in which a part of the engine cylinder is deactivated to drive the engine When this occurs, the liquid in the communication path 32 connecting the first liquid chamber 30 and the third liquid chamber 35 becomes sticky and cannot exhibit the vibration isolation function. To demonstrate anti-vibration function.

By the way, idle vibration is a low frequency vibration of the floor, seat and steering wheel in the idling state, and bull vibration is a 4-cylinder engine, for example, 20-35 Hz, a 6-cylinder engine, for example, 30-50 Hz. Yes, Yusa Yusa vibration is 5-10H
This is caused by non-uniform combustion at z, and the engine roll vibration is the main factor.

Next, referring to FIG. 1 and a sectional view of the coil bobbin 62 in which the stepped surface 62a shown in FIG. 2 is enlarged, the coil bobbin 62 that is a component of the coil assembly 43 and the coil 46 held by the coil bobbin 62 will be described. This will be described in detail.
The coil bobbin 62 is provided at both ends of a shaft body 63 that is a hollow cylinder so that a pair of flange plates 64 are opposed to each other, and has a substantially axisymmetric structure with respect to the symmetry axis L (see FIG. 1). is there. The inner peripheral surface of the coil bobbin 62 circumscribes the shaft body 63, and a movable core 54 (see FIG. 1) is disposed via the bearing member 51 at a position facing the inner peripheral surface of the shaft body 63.

A conical tapered surface 62b is provided in the opening of the coil bobbin 62 on the side where the movable core 54 is displaced. The tapered surface 62b forms a continuous surface extending from the inner peripheral surface of the shaft body 63 to the outer surface of the flange plate 64, and this continuous surface is a portion in close contact with the conical surface 44a (see FIG. 3A) of the yoke 44. It becomes.
The material of the coil bobbin 62 is preferably non-magnetic, for example, resin-molded.

A conductive wire 61 is densely wound around the shaft 63 around the shaft. Here, the term “dense” refers to a state in which the conductors 61 configured in a layered manner around the axis are stacked while being shifted by a radius in the direction of the symmetry axis L in the cross-sectional view of the coil 46 shown in FIG. Thereby, the current density which flows through the coil 46 annularly can be improved.
The flange plate 64 defines both ends of the conductive wires 61 that are densely laminated in this manner, and holds both end surfaces of the coil 46.

A step surface 62a is provided on the opposite surface of the tapered surface 62b. The step width n of the step surface 62a in the radial direction of the coil 46 is a natural number multiple (twice in the figure) of the thickness of the wound conducting wire 61. Further, the step width m of the step surface 62a in the direction of 30 degrees obliquely with respect to the symmetry axis L is also a natural number multiple (twice in the figure) of the thickness of the conducting wire 61.
Thus, by forming the step surface 62a, the conducting wire 61 is wound over the entire circumference without impairing the denseness thereof.
Furthermore, by arbitrarily changing the step widths m and n, it is possible to set the inclination angle θ of the tapered surface 62b to be larger than 30 deg and densely wind the conducting wire 61 so as to expand the diameter in the opening direction. become.

FIG. 2B shows another embodiment, which is different from the case of FIG. 2A in that the cross section of the conducting wire is a conducting wire 61 ′ having a regular hexagon. In this case, when the conducting wire 61 ′ is wound around the coil bobbin 62, the tension applied to the conducting wire 61 ′ is set high, and the portions where the conducting wires 61 ′ are in contact with each other are plastically deformed. As a result, the density of the conducting wire 61 ′ is further improved, and the current density flowing in the coil 46 in an annular shape can be further improved.
In the case of FIG. 2B, the thickness of the conductor 61 ′ can be made thinner than that of FIG. 2A. The set values of the step widths m and n also take into account the extension of the conductor 61 ′. Will be set accordingly.

FIG. 3A shows magnetic lines of force induced around the coil 46 (not shown) excited by energization. Since the fixed core 42, the actuator case 13, the yoke 44, and the movable core 54 disposed around the coil 46 are made of a ferromagnetic material such as iron, the excited coil 46 (see FIG. 2) to form a magnetic circuit.
Here, since the conical surface 44a of the yoke 44 is a portion in close contact with the tapered surface 62b (see FIG. 2A) of the coil bobbin 62, the same inclination angle θ is set (θ> 30 deg).
A bearing member 51 (see FIG. 1) is disposed in the gap g2 portion where the boundary between the yoke 44 and the movable core 54 is formed, but the description is omitted in FIG.

FIG. 3B is a comparative example, and shows a case where the conductors are densely arranged without using the stepped surface as shown in FIG. 4B (inclination angle θ = 30 deg). .
Here, when comparing the example of FIG. 3A and the comparative example of FIG. 3B, in the example, the magnetic path length of the magnetic circuit is shortened due to the large inclination angle θ. Furthermore, the orthogonal cross section of the magnetic force lines in the vicinity of the gap g2 where the yoke 44 and the movable core 54 are relatively displaced is enlarged, thereby greatly reducing the magnetic resistance of the magnetic circuit and increasing the induced magnetic force lines. Then, the displacement of the movable core 54 in accordance with the excitation / demagnetization of the coil 46 improves the output of the active vibration-proof support device M that expands and contracts.

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 stepped surface 62a is illustrated as being provided on the non-magnetic coil bobbin 62, but is not limited thereto. For example, if the coil 46 is directly wound around a magnetic member (for example, the yoke 44) forming the magnetic circuit, the step surface 62a may be provided on the magnetic member.
Further, in the embodiment, the step surface 62a is provided so as to increase in diameter on the upper side in the vertical direction of the active vibration isolation support device M, but may be provided so as to increase in diameter on the lower side.
Further, the step widths m and n of the step surface 62a are each twice as large as the thickness of the conducting wire 61. However, if the inclination angle θ can be set to 30 deg or more, any natural thickness of one layer can be obtained. It can be set in several times.

It is a longitudinal cross-sectional view of the active vibration-proof support apparatus which concerns on embodiment of this invention. (A) is the expanded sectional view of the level | step difference surface part of the coil bobbin holding the coil in the active vibration isolating support apparatus which concerns on embodiment, (b) has shown the other Example. (A) is a figure which shows the magnetic force line induced | guided | derived to a coil, when the inclination angle (theta) of the conical surface of a yoke is set large (> 30deg) in the active vibration isolating support apparatus which concerns on embodiment, (b) It is a figure which shows the magnetic force line induced | guided | derived to a coil, when inclination-angle (theta) is set to 30 deg as a comparative example. (A) shows a state in which the regularity of the coil arrangement in the vicinity of the conical surface is disturbed when a conical surface having a desired inclination angle θ (> 30 deg) is provided in the opening portion of the inner peripheral surface of the coil in the conventional example. (B) indicates that the inclination angle θ of the conical surface is limited to 30 deg when such regularity of the coil arrangement is obtained.

Explanation of symbols

DESCRIPTION OF SYMBOLS 41 Drive part 42 Fixed core 43 Coil assembly 44 Yoke 44a Conical surface 46 Coil 51 Bearing member 54 Movable core 61 Conductor 62 Coil bobbin 62a Step surface L Symmetric axis M Active type vibration-proof support device Sa Crank pulse sensor Sb Cam angle sensor m Step Width n Step width

Claims (2)

In the active vibration isolating support device that supports the engine and suppresses vibration transmitted from the engine to the vehicle body by a telescopic motion
A coil that is energized when a conducting wire is densely wound and energized;
A movable core that is arranged at a position facing the inner peripheral surface of the coil and is displaced according to excitation / demagnetization of the coil to guide the expansion and contraction;
A step surface on which the conductive wire is wound so as to have a step width that is a natural number multiple of the thickness of one layer of the wound conductive wire and to increase the diameter in the opening direction of the inner peripheral surface, Active vibration isolation support device.   The step surface is provided at a connecting portion between a shaft body around which the conducting wire is wound and a flange plate on which both end surfaces of the coil are held, and these form a coil bobbin formed integrally with resin. The active vibration isolating support device according to claim 1.

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