JPH09242807A - Vibrationproof support structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the transmission of vibration by restricting the compression condition of support elastic member through contact between a stopper member and a restricting part. SOLUTION: Two stopper metal fittings 59b are fixed to a caulking part at an upper end of a device case 43, and a bound stopper member 59a made of elastic member is fixed to the upper surface. A rebound restricting member 60 crosses a line connecting connection bolts 30a to each other at right angles, and is fixed to the case 43 while extending upward of an engine side connection member 30. The member 60 is composed of a restriction body 60a facing a rebound stopper member 31 fixed to the upper surface of the member 30 and a pair of stopper leg parts 60b, 60c gradually lowered from both ends of the restriction member 60a and fixed to the outer circumference of the case 43. Accordingly, deterioration of support elastic member at the time of abrupt deceleration is surely prevented, thereby reducing the transmission of vibration.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for supporting a vibrating body side against a supporting body while vibration-proofing the vibrating body side. In particular, a vibrating body and a supporting elastic body interposed between the supporting bodies are excessively compressed. The present invention relates to an anti-vibration support device that regulates

[0002]

2. Description of the Related Art In general, an engine mount, which is an anti-vibration support device used to support a power unit of a vehicle, mainly has a good anti-vibration function against idle vibration, muffled sound vibration, noise vibration during acceleration, and the like. It is required to be exerted, but among these various vibrations, 20 to 30
In order to reduce the idle vibration, which is a vibration with a relatively large amplitude of about Hz, the characteristics required of the anti-vibration support device are a high dynamic spring constant and a high damping, whereas a characteristic of 80-800 Hz is relatively high. The characteristics required for the anti-vibration support device in order to reduce the muffled noise vibration and the noise noise during acceleration, which are small and medium amplitude vibrations, are a low dynamic spring constant and a low damping. Therefore, it is difficult to prevent all vibrations with an engine mount including only a normal elastic body or a conventional liquid-filled engine mount.

Therefore, as an anti-vibration support device capable of actively damping and supporting a vibrating body such as an automobile engine, it is disclosed in, for example, Japanese Unexamined Patent Publication No. 5-060168 (hereinafter referred to as "prior art"). Known technology.

In this prior art, a support is fixed to the vehicle body side of an automobile, an outer shell is arranged above the support at a predetermined interval, and a hollow is provided between the outer shell and the support. A support elastic body (referred to as an expansion spring in the publication) made of a conical rubber-like elastic body is connected, and is provided between the outer shell and the support body so as to cover an outer lower portion of the support elastic body. A bellows is arranged, and a vibrating plate that is magnetizable is supported by a leaf spring arranged on the upper part of the outer shell, and is connected to the upper part of the outer shell so as to face the upper surface of the vibrating plate. The supporting member is fixed to the supporting member, and the supporting member is provided with a permanent magnet so as to face the vibrating plate, and a magnet body made of an electromagnet is provided around the permanent magnet. A closed main fluid chamber (referred to as a working chamber in the publication) is formed between the upper surface of the expansion spring and the lower surface of the diaphragm, and the lower surface of the support elastic body and the upper surface of the bellows are formed. A sub-fluid chamber (referred to as a pressure-regulating chamber in the publication) sealed between them is formed, and a liquid is enclosed in the main fluid chamber and the sub-fluid chamber.
The main fluid chamber and the sub-fluid chamber are communicated with each other via a buffer hole formed in the outer shell.

In this prior art, when the diaphragm vibrates due to the electromagnetic force generated by the electromagnet, a volume change occurs in the main fluid chamber, and the volume change acts on the elastic support body to generate an active support force there. Therefore, the vibration plate is appropriately vibrated according to the vibration generation state to reduce the vibration transmitted to the support body side. Further, the main fluid chamber communicates with the sub fluid chamber through the buffer hole, and when the supporting elastic body is deformed by the vibration input from the vibrating body side and a volume change occurs in the main fluid chamber, Since the liquid enclosed in the body chamber and the liquid enclosed in the sub-fluid chamber move with each other through the buffer holes to generate a damping force, the action of a passive fluid-filled type vibration damping support device can also be obtained. You can

[0006]

By the way, when the anti-vibration supporting device having the above-mentioned structure is arranged, for example, in the longitudinal direction of the vehicle body of an engine mounted horizontally, due to a sudden torque change of the engine when the vehicle suddenly decelerates, The supporting elastic body is likely to be excessively compressed. Therefore, it is necessary to provide a stopper device that regulates the compressed state of the support elastic body to improve the durability of the support elastic body.

When a stopper device is provided in the conventional vibration-proof support device, for example, the stopper member is fixed to the outer shell so as to extend radially outward from the outer shell, while the supporting member is fixed to the outer shell. A structure is conceivable in which the stopper regulating member is fixed so as to surround the stopper member from both sides in the vibrating body supporting direction. When the support elastic body is in a compressed state when the vehicle is rapidly decelerated, the stopper member moving in the vibration body supporting direction abuts the stopper regulating member to prevent the support elastic body from being in an excessively compressed state. You can

However, in the above-described structure, the stopper member and the stopper regulating member have a structure protruding outward in the radial direction of the device, and the height of the device also increases, leading to an increase in the size of the anti-vibration supporting device. Therefore, it is difficult to apply the anti-vibration support device including the stopper device of the support elastic body to a vehicle or the like in which the mounting space is largely restricted.

Further, the support member is attached to the engine through the bracket, but the vibration characteristics of the bracket and the support member greatly affect the vibration transmission characteristics in the frequency range related to idle vibration, muffled sound vibration and the like. Therefore, it is effective to reduce the idle vibration and the muffled sound vibration by increasing the resonance point in this frequency region as much as possible and suppressing the vibration level. However, in the prior art, the rigidity of the bracket is low, which lowers the resonance point of the bracket and the support member and increases the vibration level at resonance, which is disadvantageous in reducing idle vibration and muffled sound vibration.

The present invention has been made by paying attention to the problems to be solved by such a conventional technique, in which a member for restricting an excessively compressed state of a supporting elastic body is arranged while miniaturizing. It is an object of the present invention to provide a vibration-damping support device that can reduce the vibration transmission transmitted from the vibrating body side by increasing the rigidity of the bracket.

[0011]

In order to achieve the above object, a vibration-isolating support device according to a first aspect of the present invention comprises a vibration member and a first member fixed to one of the support member via a bracket,
A second member fixed to the other of the vibrating body and the support body about the vibrating body support direction as an axis; and a support elastic body interposed between the first member and the second member about the vibrating body support direction as an axis. A fluid chamber defined by a supporting elastic body and having a fluid enclosed therein, and a fluid chamber disposed on the second member side so as to be displaceable in a direction forming a part of a partition wall of the fluid chamber and changing the volume of the fluid chamber. An anti-vibration support device comprising: a movable member that is provided; and an actuator that is disposed on the side of the second member and that displaces the movable member, wherein the first member in a direction orthogonal to the vibrating body supporting direction is provided. By making the shape smaller than the bracket and the second member,
The bracket and the second member are provided with facing surfaces facing each other in the vibrating body supporting direction, and a stopper member made of an elastic body is fixed to the facing surface on the second member side, and the bracket facing the stopper member. When the bracket and the second member relatively move in a direction in which they are close to each other and the support elastic body is in a compressed state, the stopper member and the restriction member contact each other, The compressed state of the support elastic body is regulated.

The invention described in claim 2 is the first invention.
In the anti-vibration support device described above, at least two connecting bolts protruding toward the bracket while being separated from each other are fixed to the first member, and the first member is integrated with the bracket through the connecting bolts. Connected to.

[0013]

According to the vibration isolating support device of the first aspect,
When the bracket and the second member relatively move in a direction in which they approach each other and the support elastic body is in a compressed state, a stopper member fixed to the facing surface of the second member and a bracket configured to face the stopper member Since the member comes into contact with the member to regulate the compressed state of the support elastic body, it is possible to prevent the support elastic body from being excessively compressed. When this anti-vibration support device is applied as an engine mount arranged on the vehicle rear side of an engine as a vibrating body, for example, when a large external force is input to the anti-vibration support device, such as during sudden deceleration of the vehicle, the support elastic body is However, in the present invention, since the stopper member and the restriction member prevent the support elastic body from being excessively compressed, deterioration of the support elastic body during sudden deceleration can be reliably prevented. .

Further, the stopper member and the regulating member are configured such that the shape of the first member in the direction orthogonal to the vibrating body supporting direction is smaller than that of the bracket and the second member, so that the vibrating body of the bracket and the second member is formed. Since the anti-vibration support device is provided on the opposing surfaces that face each other in the support direction, the radial dimension of the anti-vibration support device does not increase, and the device can be downsized. And, it is a very advantageous device for an engine mount of a vehicle, which has a large restriction on mounting space.

The invention according to claim 2 can obtain the effect according to claim 1, and the bracket is
Since at least two connecting bolts of the first member that are spaced apart from each other and project toward the bracket are connected to the formed pair of bracket connecting members, the first member serves as a reinforcing member for the bracket, and the durability of the bracket is improved. Is improved.
Since the bracket is integrated with the first member via the two connecting bolts, the rigidity of the bracket is increased, so that the resonance point of the bracket and the first member is increased and the vibration level at the time of resonance is suppressed. can do.
Accordingly, when the first member is fixed to the vibrating body side, it is possible to reduce the vibration transmission transmitted from the vibrating body side.

[0016]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a perspective view showing a so-called active engine mount (hereinafter simply referred to as an engine mount) that actively reduces vibration transmitted from an engine side as a vibrating body to a vehicle body-side member as a support. ). The engine mount indicated by reference numeral 20 in FIG. 1 is disposed on the rear side of the vehicle body of the horizontally mounted engine 22, the upper part of which is attached to the bracket 24, and the lower part thereof is fixed to the vehicle body 26 by a member 28 as a support. Attached to.

Further, FIG. 2 shows the above-mentioned bracket 24.
And the engine mount 2 connected to the bracket 24
0 shows the superstructure of 0. The bracket 24
Is integrated with the first bracket member 24a, which is fixed to the vehicle rear side of the engine 22 through an engine fixing bolt, and is integrated with the first bracket member 24a, and is connected to the engine mount 20 through a connecting bolt 30a. It is composed of the second bracket member 24b. That is, the first bracket member 24a has an engine side connecting plate 24a in which a bolt insertion hole 24a ₁ for inserting a fixing bolt is formed.
₂ and a pair of reinforcing plates 24a ₃ that are bent from both sides in the width direction of the engine side connecting plate 24a ₂ and extend in parallel toward the rear side of the vehicle body. In addition, the second bracket member 2
4b, the engine-side connecting plate 24a ₂ and the fixing plate 24b ₁ that are joined together by joint means such as welding, provided a space width of a predetermined length L from the top of the fixing plate 24b ₁ therebetween It is provided with a pair of mount side connecting plates 24b ₂ as bracket connecting members extending in parallel toward the rear side of the vehicle body. Then, the pair of mount-side connecting plate 24b _2, bolt insertion holes 24b ₃ that connecting bolts 30a are inserted
Are formed.

The upper part of the engine mount 20 is
The two connecting bolts 30a from the engine-side coupling member 30 protrudes upwardly as a first member, inserted from below into the bolt insertion holes 24b ₃ of the bracket 24 described above, by screwing the nut It is connected to the bracket 24.

Next, a specific structure of the engine mount 20 will be described with reference to FIGS. The engine mount 20 includes, in a device case 43 as a second member, an elastic support 32 that defines a main fluid chamber, a plurality of orifices and a sub fluid chamber, an inner cylinder 34, a first orifice component member 36,
An actuator that incorporates mount components such as the outer cylinder 38 and that displaces a movable member that is elastically supported while forming a part of a partition wall of the main fluid chamber in a lower portion of these mount components in a direction in which the volume of the main fluid chamber changes. Is a device incorporating the electromagnetic actuator 52.

That is, the engine mount 20 is
As described above, the engine-side connecting member 30 in which the two connecting bolts 30a spaced apart from each other in parallel are fixed upward
It has. A hollow cylindrical portion 30b having an inverted trapezoidal cross section is fixed to a lower portion of the engine side connecting member 30.

On the upper surface of the engine-side connecting member 30, an elastic body having a predetermined thickness to serve as the rebound stopper member 31 is vulcanized and adhered in a direction orthogonal to the line connecting the two connecting bolts 30a. A support elastic body 32 is fixed to the lower surface side of the engine side connecting member 30 that is continuous with the rebound stopper rubber 31 so as to cover the lower side of the engine side connecting member 30 and the periphery of the hollow cylindrical portion 30b. It is fixed by vulcanization adhesion.

The support elastic body 32 is a substantially cylindrical elastic body having a wall thickness that gently inclines downward from the central portion toward the outer peripheral portion, and the outer peripheral surface thereof has a hollow cylindrical portion 30b with an axial center. It is joined by vulcanization adhesion to the inner peripheral surface of the inner cylinder 34 that is coaxially oriented in the vibrating body supporting direction (in this case, the vertical direction).

As shown in FIG. 3, the inner cylinder 34 is gradually reduced in diameter from an upper end cylinder portion 34a to form an inclined portion 34b, and an inclined portion 34b is formed at a lower end portion thereof toward a lower end. A small diameter portion 34c having a diameter smaller than that of the tubular portion 34a is formed. An annular portion 34d is formed radially outward from the lower end of the small diameter portion 34c, and the upper end cylinder portion 34a is formed downward from the outer peripheral end of the annular portion 34d.
It is a member in which a lower end cylindrical portion 34e having the same outer peripheral diameter as that of is formed. Then, in the small diameter portion 34c, the first opening hole 34f and the second opening hole 34g are provided at positions symmetrical to each other with respect to the axis.
Are formed. Then, the inclined portion 34b of the inner cylinder 34,
A thin film elastic body 32a continuous from the lower side of the support elastic body 32 is coupled to the inner peripheral surface of the small diameter portion 34c.
It extends to the 4e side and is joined to the inner peripheral surfaces of the annular portion 34d and the lower end tubular portion 34e. Here, the lower end portion of the thin film elastic body 32a has a thickened shape. Also, the first
The opening hole 34f is closed by the thin film elastic body 32a to form the first diaphragm 32c, but the second opening hole 34g is formed.
Is open without being blocked by the thin film elastic body 32a.

A hollow portion 32b having a mountain-shaped cross section is formed inside the support elastic body 32, and the first orifice constituting member 36 is fitted into the inner cylinder 34 so as to be located under the hollow portion 32b. Has been done. The first orifice component member 36 includes a minimum diameter tubular portion 36a formed to have a diameter smaller than that of the small diameter portion 34c of the inner tubular member 34, and an annular portion is formed at the upper and lower ends of the minimum diameter tubular portion 36a so as to extend radially outward. It is a tubular member in which 36b and 36c are formed. The annular portion 36b on the upper side is formed such that the outer peripheral diameter thereof is slightly smaller than the small diameter portion 34c of the inner cylinder 34. The lower annular portion 36c is
The diameter of the inner cylinder 34 is smaller than that of the lower end cylinder portion 34e, and the cylindrical end portion 36c extends downward from the outer peripheral end portion thereof.
₁ is formed. Furthermore, in the minimum diameter tubular portion 36a,
A third opening hole 36d is formed at a position facing the second opening hole 34g formed in the inner cylinder 34. Here, the lower end portion of the thin film elastic body 32a having the increased thickness as described above is sandwiched between the lower end tubular portion 34e of the inner cylinder 34 and the tubular end portion 36c _{1 of} the first orifice component 36. As a result, it slightly protrudes downward from the sandwiched portion while being compressed in the radial direction.

An outer cylinder 38 is fitted onto the inner cylinder 34, and the recess formed by the outer peripheral surfaces of the inclined portion 4b, the small diameter portion 34c and the annular portion 34d is surrounded by the inner peripheral surface of the outer cylinder 38. An annular space is defined in the circumferential direction. The second orifice component 40 and the second diaphragm 42 are arranged in this annular space.

That is, the outer cylinder 38 is a cylindrical member whose inner diameter is the same as the outer diameter of the inner cylinder 34 and whose axial length is the same as that of the inner cylinder 34. A thin liquid-tight sealing material 38a made of an elastic body is joined to the. Then, in the outer cylinder 38, approximately 1 of the recess is formed.
So that it is possible to face the part of / 3 from the outer peripheral side,
A slit-shaped opening 38b whose longitudinal direction extends in the circumferential direction is formed.

Further, the second diaphragm 42 is a rubber-like thin film elastic body, and as shown in FIG. 6, the second diaphragm 42 is connected to the entire circumference of the opening edge portion of the opening portion 38b to close the opening portion 38b and to close the above-mentioned concave portion. It is arranged in a state of bulging toward the approximately 1/3 portion. Further, the second orifice constituting member 40 is arranged in the remaining annular space (an annular space corresponding to approximately ⅔ of the concave portion) which has become a small space due to the disposition of the second diaphragm 42. As shown in FIGS. 6 and 7, the partition wall member 40a and the passage forming member 40b are made of an elastic material.

The partition member 40a is provided in an annular space adjacent to one longitudinal end 42a of the second diaphragm 42.
The partition wall member 40a is disposed so as to be fitted between the inner cylinder 34 and the outer cylinder 38 forming the annular space, and the partition wall member 40a allows the second diaphragm 42 from the passage forming member 40b side.
Fluid flow to the side is blocked. Further, the passage forming member 40b is continuously formed in an annular space from a position close to the partition member 40a to a position close to the other end 42b in the longitudinal direction of the second diaphragm, and the one end opening 4 is formed.
0b ₃ extending along the second opening hole 34g and communication with the circumferential direction of the inner cylinder 34, the first passage 40b ₁ to the other end opening is open towards the partition wall member 40a, the first passage 40b _As a different passage on the upper part of ₁ , it extends in the circumferential direction with a length approximately twice as long as that of the first passage 40b ₁ , one end opening is open toward the partition member 40a, and the other opening 40b ₄ is the second diaphragm. Four
2 is a member having a second passage 40b ₂ opening toward the other end 42b of the second. The outer cylinder 38 is fitted inside the upper part of the device case 43.

The apparatus case 43 has an upper end crimped portion 43a having a circular opening having a diameter smaller than the outer peripheral diameter of the inner cylinder 34 at the upper end thereof, and the shape of the case body continuous with the upper end crimped portion 43a. The inner diameter is 3
8 is a cylindrical member having the same outer diameter as the outer peripheral diameter 8 and continuing to the lower end opening (the lower end opening is shown by the broken line in FIG. 3). Then, the outer cylinder 38 integrated with the supporting elastic body 32 and the inner cylinder 34 is fitted into the inside of the lower end opening of the device case 43, and the outer cylinder 38 and the inner cylinder 34 are attached to the lower surface of the upper end caulking portion 43a. When the upper end portions come into contact with each other, they are arranged in the upper portion of the device case 43. Here, as shown in FIGS. 3 and 6, an air chamber 42c is formed in a portion surrounded by the inner peripheral surface of the device case 43 and the first diaphragm 32c.
Is defined, but an air hole 42d is formed at a position facing this air chamber 42c, and the air chamber 4 is formed through this air hole 42d.
2c communicates with the atmosphere.

Further, a plurality of actuator parts such as an electromagnetic actuator 52 are sequentially arranged in the lower part of the device case 43, and after all the parts are arranged, the device case 4
By deforming the lower end of 3 toward the inside in the radial direction,
As shown by the solid line in FIG. 3, a lower end caulking portion 43c is formed.

That is, in the lower part of the outer cylinder 38, the seal ring 44, the leaf spring 48 integrated with the magnetic path member 46, the gap holding ring 50, the electromagnetic actuator 52, the load sensor 54, and the vehicle body side connecting member 56 are provided. Device case 43
Are sequentially arranged from the lower opening. Here, in the present embodiment, the magnetic path member 46 and the leaf spring 48 constitute a movable member.

As shown in FIG. 3, the seal ring 44 has the same outer diameter as the inner diameter of the device case 43.
This is an annular member having an inner diameter smaller than that of the lower annular portion 36c of the first orifice constituting member 36, and an O-ring 44a is formed on the lower surface thereof in a ring groove formed in a circumferential direction of a predetermined radius.
Is installed. The seal ring 44 is arranged with its upper surface in contact with the lower end of the outer cylinder 38. The leaf spring 48 is a disk member whose outer diameter is slightly smaller than the inner diameter of the device case 43, and a magnetic path made of magnetizable metal such as iron is provided under the leaf spring 48. The member 46 is fixed coaxially. Then, after contacting the upper peripheral portion of the leaf spring 48 with the lower surface of the seal ring 44, the leaf spring 48
Of the gap retaining ring 50 in a state of being in contact with the peripheral portion of the lower surface of the
Is arranged. Further, the gap retaining ring 50 has an axial length from the lower surface of the leaf spring 48 to the magnetic path member 46 so that a predetermined gap is provided between the lower surface of the magnetic path member 46 and the upper surface of the electromagnetic actuator 52. The annular member is set to a value obtained by adding the dimension of the gap to the axial length to the lower surface of the.

The electromagnetic actuator 52 disposed in contact with the lower surface of the gap retaining ring 50 has a cylindrical yoke 52a and an excitation coil wound around the upper end surface of the yoke 52a with the axial direction being the vertical direction. Coil 52b
And a permanent magnet 52c whose magnetic pole is fixed in the vertical direction on the upper surface of the yoke 52a within the range surrounded by the exciting coil 52b.

On the lower side of the electromagnetic actuator 52, two vehicle-body-side mounting bolts 56a, which are spaced apart from each other, are fixed downward and fixed to each other.
The load sensor 54 is provided between the upper surface of the vehicle body side connecting member 56 and the lower surface of the yoke 52a.

When the lower end caulking portion 43d is formed on the lower end portion of the device case 43 as described above, the peripheral portion of the vehicle body side connecting member 56 is fixed in a state of being covered from the outside. At this time, since the electromagnetic actuator 52 is pushed toward the outer cylinder 38 side, the lower end cylindrical portion 34e and the cylindrical end portion 36c ₁
The lower end portion of the thin film elastic body 32a sandwiched between and is pressed upward by the upper surface of the seal ring 44 to be in a compressed state. The O-ring 44a mounted on the lower surface of the seal ring 44 is also pressed upward by the leaf spring 48 and deformed over the entire circumference. The upper and lower surfaces of the gap retaining ring 50 are the lower surface of the leaf spring 48 and the yoke 5.
Since it abuts on the upper surface of 2a, a predetermined gap is provided between the lower surface of the magnetic path member 46 and the upper surface of the electromagnetic actuator 52.

On the other hand, as shown in FIGS. 2, 4 and 5,
A bound stopper member 59a as a stopper member and a rebound regulating member 60 as a regulating member are fixed to the upper portion of the device case 43.

That is, two stopper fittings 59b are fixed to the upper case caulking portion 43a of the apparatus case 43 at positions spaced apart from each other in the circumferential direction, and the upper surface of these stopper fittings 59b is bounded by an elastic body having a predetermined thickness. The stopper member 59a is fixed. The fixed position of these two bound stopper members 59a is the bracket 24.
Connecting bolts 30a when coupled, there is a pair of mount-side connecting plate 24b ₂ and a position facing.

The rebound restricting member 60 is orthogonal to the line connecting the two connecting bolts 30a, and is fixed to the device case 43 while extending above the engine side connecting member 30 in an arch shape. A restricting body 60a facing the rebound stopper member 31 fixed to the upper surface of the engine-side connecting member 30, and a pair of stopper leg portions 60b fixed to the outer circumference of the device case 43 by gradually descending from both ends of the restricting body 60a, And 60c.

Then, as shown in FIG. 8, the two connecting bolts 20a are inserted into the bolt insertion holes 24b ₃ of the pair of mount side connecting plates 24b ₂ from below to connect the connecting bolts 20a.
When the nut 61 is screwed into the pair, the pair of mount side connecting plates 2
With the upper surface of the engine side connecting member 30 in contact with the lower surface of 4b ₂ , the upper portion of the engine mount 20 is attached to the bracket 2
4. In this case, two bound stopper member 59a is opposed to a pair of mounting side connecting plate 24b ₂ and a predetermined clearance C _1. As a result, in the present embodiment, the pair of mount-side connecting plates 24b ₂ constitute a bound regulating member as a regulating member that faces the bound stopper member 59a.

The rebound restricting member 60 extends between a pair of mount side connecting plates 24b ₂ which are spaced apart from each other by providing a space having a width of a predetermined length L, and the restricting body 60a.
, But faces the rebound stopper member 31 fixed to the upper surface of the engine side connecting member 30 with a predetermined clearance C ₂ .

By the way, the engine mount 20 according to the present embodiment is arranged such that the outer circumference of the first orifice component member 36 and the first orifice component member 36.
The inside of the orifice forming member 36 communicates with each other through the third opening hole 36d, and the inside of the first orifice forming member 26 and the first passage 40b ₁ of the second orifice forming member 40 pass through the second opening hole 34g. The second passage 4 communicates with the space where the second diaphragm 42 bulges from the first passage 40b ₁ .
It is connected via 0b ₂ .

When a portion defined by the hollow portion 32b of the support elastic body 32 and the outer peripheral surface of the upper portion of the first orifice constituting member 36 is defined as a main fluid chamber 66, the second diaphragm described above from the main fluid chamber 66 is defined. A fluid such as oil is enclosed in the communication passage up to the space where 42 swells. And
By the above-described first and second orifice component members 36 and 40 and the first and second diaphragms 32c and 42c,
Three first to third orifices 68A, 70A, 72A that generate fluid resonance when the volume of the main fluid chamber 66 changes
Also, the first to third sub-fluid chambers 68B, 70B, 72B are formed.

That is, the first orifice 68A is shown in FIG.
As shown in FIG. 5, the first sub-fluid chamber 68B is an internal space surrounded by the minimum diameter cylindrical portion 36a of the first orifice component 36 and the small diameter portion 34c of the inner cylinder 34.
It is the internal space of the first orifice component 36 near c. As shown in FIGS. 6 and 7, the second orifice 70A is a space from the first passage 40b ₁ to the position where the second diaphragm 42 bulges inward through the second passage 40b ₂ . The second sub-fluid chamber 70B is a space in which the second diaphragm 42 bulges inward. Further, the third orifice 72A is a space on the inner peripheral side of the minimum diameter tubular portion 36a, and the third sub-fluid chamber 72B is a space from the lower end surface of the minimum diameter tubular portion 36a to the leaf spring 48. The characteristic of the fluid resonance system configured by the one orifice 68A and the first sub-fluid chamber 68B is that the damping peak frequency (the frequency at which the damping is maximum) is at the frequency of idle vibration (about 20 to 30 Hz) generated while the vehicle is stopped. It has been adjusted to match. In addition, the second orifice 70A and the second
The characteristics of the fluid resonance system configured by the sub-fluid chamber 70B are adjusted so that the attenuation peak frequency matches the frequency of shake vibration (20 Hz or less) generated during braking. Furthermore, the third orifice 72A and the third sub-fluid chamber 7
The characteristic of the fluid resonance system configured by 2B is that the damping peak frequency is such that muffled sound vibration in the passenger compartment / noise vibration at acceleration (80 to 8
The frequency is adjusted to match the frequency of 00 Hz or more).

The exciting coil 52b of the electromagnetic actuator 52 is connected to the controller 74 via a harness, and as shown in the block diagram of FIG. 1, a drive signal y as a drive current supplied from the controller 74.
, A predetermined electromagnetic force is generated.

The controller 74 is a microcomputer, a necessary interface circuit, an A / D converter, a D / A.
It is configured to include a converter, amplifier, etc., and when high-frequency vibration of idle vibration frequency or higher (for example, muffled sound vibration) is input, control vibration of the same cycle as the vibration is input to the engine mount. 20 so that the transmission force of the vibration to the member 28 becomes “0” (more specifically, the exciting force input to the engine mount 20 by the vibration of the engine 22 side is applied to the electromagnetic actuator 5).
The driving signal y is generated and supplied to the exciting coil 52b so as to be canceled by the control force obtained by the electromagnetic force of 2).

Here, idle vibration and muffled sound vibration are
For example, in the case of a reciprocating four-cylinder engine,
The main cause is that the engine vibration of the next component is transmitted to the member 28 via the engine mount 20, so if the drive signal y is generated and output in synchronization with the secondary component of the engine rotation, the vibration transmission rate. Can be reduced. Therefore,
In the present embodiment, the rotation is synchronized with the rotation of the crankshaft of the engine 22 (for example, in the case of a reciprocating four-cylinder engine,
A pulse signal generator 76 is provided for generating an impulse signal (each time the crankshaft rotates 180 degrees) and outputting the impulse signal as a reference signal x.
Is supplied to the controller 74 as a signal indicating the state of occurrence of the vibration at.

On the other hand, as described above, the engine mount 2
0 has a built-in load sensor 54, detects the vibration state of the member 28 in the form of a load, outputs it as a residual vibration signal e, and supplies the residual vibration signal e to the controller 74 as a signal representing the vibration after interference. Has been done.

Then, the controller 74, based on the reference signal x and the residual vibration signal e, is a Filtered-X LM which is one of the adaptive algorithms of the successive update type.
The drive signal y is generated and output according to the S algorithm.

Next, the operation of the vibration isolation mechanism of this embodiment will be described. When the engine 22 starts and vibrations are input to the engine mount 20, the controller 7
4 executes a predetermined calculation process, and the electromagnetic actuator 5
The drive signal y is output to 2 to cause the engine mount 20 to generate an active control force capable of reducing vibration.

That is, the filter coefficient of the adaptive digital filter W is sequentially output to the electromagnetic actuator 52 of the engine mount 22 from the controller 74 at a predetermined sampling clock interval from the time when the reference signal x is input. supplied as y. As a result,
A magnetic force corresponding to the drive signal y is generated in the exciting coil 52b, but since a constant magnetic force is already applied to the magnetic path member 46 by the permanent magnet 52c, the magnetic force of the exciting coil 52b is the magnetic force of the permanent magnet 52c. Can be considered to act to strengthen or weaken. That is, in a state where the drive signal y is not supplied to the exciting coil 52b, the magnetic path member 46 is displaced to a neutral position where the elastic supporting force of the leaf spring 48 and the magnetic force of the permanent magnet 52c are balanced. . Then, in this neutral state, the exciting coil 52b
When the drive signal y is supplied to the magnetic field member 46, if the magnetic force generated in the exciting coil 52b by the drive signal y is in the opposite direction to the magnetic force of the permanent magnet 52c, the magnetic path member 46 increases the clearance with the electromagnetic actuator 52. Is displaced to. Conversely, the magnetic force generated in the exciting coil 52b is
If it is in the same direction as the magnetic force of, the magnetic path member 46 is displaced in the direction in which the clearance with the electromagnetic actuator 52 decreases.

Thus, the leaf spring 48 can be displaced up and down by the magnetic force generated by the electromagnetic actuator 52. If the leaf spring 48 is displaced up and down, the main fluid chamber 66 can be moved.
Of the supporting elastic body 32 due to the change in volume.
, The active support force in both the forward and reverse directions is generated in the engine mount 20. Then, each filter coefficient W ₁ of the adaptive digital filter W that becomes the drive signal y is a synchronous Filtered-X
Since the sequentially updated according to the LMS algorithm, after converged to optimum values each filter coefficient W _i of the adaptive digital filter W has passed a certain time, the drive signal y
Is supplied to the engine mount 20, so that the member 2 is moved from the engine 22 through the engine mount 20.
Idle vibrations and muffled sound vibrations transmitted to the side 8 are reduced.

Here, if the frequency of the vibration input from the engine 22 side to the engine mount 20 is near the shake vibration frequency during braking, in the present embodiment, the main fluid chamber 66 is set to the second orifice 70A. Second through
Since it is communicated with the sub-fluid chamber 70B and the resonance frequency of the fluid resonance system is made to coincide with the shake vibration frequency, when the volume of the main fluid chamber 66 changes, the main fluid chamber 66 and the second fluid chamber 66 and the second fluid flow through the second orifice 70A. Fluid resonance occurs due to fluid movement between the sub fluid chambers 70B. As a result, a high damping force can be applied to the shake vibration, and a good vibration damping effect can be obtained.

Further, when the frequency of the vibration input from the engine 22 side to the engine mount 20 becomes close to the idle vibration frequency while the vehicle is stopped, even if the volume of the main fluid chamber 66 changes at that frequency, the second orifice is generated. Since the fluid in 70A cannot follow the idle vibration frequency and is in a stick state, the fluid does not move between the main fluid chamber 66 and the second auxiliary fluid chamber 70B via the second orifice 70A. Therefore, the volume fluctuation in the main fluid chamber 66 is transmitted to the first sub fluid chamber 68B via the first orifice 68A. Since the resonance frequency of this fluid resonance system matches the idle vibration frequency, the main flow Even if the volume of the body chamber 66 changes periodically at that frequency, the fluid in the first orifice 68A does not become a stick state, and the main flow occurs via the first orifice 68A to which the pressure change in the main fluid chamber 66 directly acts. The fluid moves between the body chamber 66 and the first sub-fluid chamber 68B. As a result, fluid resonance occurs between the main fluid chamber 66 and the second sub fluid chamber 68B through the first orifice 68A, so that a larger control force can be generated by the same electromagnetic actuator 52. In particular, the control vibration having a large amplitude can be superimposed on the idle vibration having a large amplitude generated on the engine 22 side, and a good vibration damping effect can be obtained.

Further, when the frequency of vibration input from the engine 22 side to the engine mount 20 becomes close to the frequencies of muffled sound vibration and noise vibration during acceleration, even if the volume of the main fluid chamber 66 changes at that frequency. First orifice 68
Since the fluid in A cannot follow the muffled sound vibration frequency and is in a stick state, the fluid does not move between the main fluid chamber 66 and the second auxiliary fluid chamber 68B via the first orifice 68A. Therefore, the volume variation in the main fluid chamber 66 is caused by the third auxiliary fluid chamber 72B via the third orifice 72A.
However, since the resonance frequency of this fluid resonance system matches the frequencies of muffled sound vibration and noise vibration during acceleration, even if the volume of the main fluid chamber 66 changes periodically at that frequency, The fluid in the orifice 72A does not become a stick state, and when the volume of the main fluid chamber 66 changes, the main fluid chamber 66 and the third sub-fluid chamber 72B pass through the third orifice 72A.
Fluid resonance occurs between the same electromagnetic actuator 52
Can generate a greater control force.

Next, the operation of the integrated structure of the bracket 24 and the upper portion of the engine mount 20, the bounce restriction member 24b ₂ , the bound stopper member 59a, and the rebound stopper member 31 arranged on the upper portion of the engine mount 20 will be described.
The operation of the rebound restricting member 60 will be described with reference to FIGS. 8 to 10.

First, as shown in FIG. 8, a pair of mount side connecting plates (bound restricting members) 24b ₂ extending from the engine 22 to the rear side of the vehicle body include two connecting bolts 3.
0a and a nut 61, the engine-side connecting member 30 is integrally connected, and the engine-side connecting member 30 serves as a reinforcing member for the bracket 24.
Durability is improved.

Further, the rigidity of the bracket 24 is increased by being integrated with the engine side connecting member 30, and the high rigidity of the bracket 24 increases the resonance point of the bracket 24 and the engine side connecting member 30.
The vibration level at resonance can be suppressed. This can reduce the transmission of idle vibration and muffled sound vibration transmitted from the engine 22 side.

When the vehicle accelerates or decelerates rapidly, the engine 2
Although the engine 22 rolls in the front-back direction of the vehicle body due to the rapid torque change of 2, the engine mount 20 arranged on the rear side of the vehicle body of the engine 22 has a vibrating body support direction in order to attenuate a large input by the roll of the engine 22. Bound state and rebound state are repeated.

That is, when the engine mount 20 is bound, the bracket 24 and the device case 43 relatively move in the direction of approaching each other, and the supporting elastic body coupled between the engine side connecting member 30 and the inner cylinder 34. 32
Is compressed in the vibrating body supporting direction. At this time, if a large external force is input to the engine mount 20 such as when the vehicle rapidly decelerates, the support elastic body 32 may be excessively compressed.

However, in the present embodiment, as shown in FIG. 9, when the bracket 24 and the device case 43 relatively move in the direction of approaching each other, the bounce regulation is performed at the time when the support elastic body 32 is in a predetermined compressed state. Bound stopper member 59a fixed to the upper end caulking portion 43a of the device case 43 with respect to the lower surface of the member (mount side connecting plate) 24b _2.
Abut while elastically deforming. As a result, the bracket 24 and the device case 43 are restrained from moving further in the direction of coming closer to each other, so that the support elastic body 32 is prevented from being excessively compressed.

On the other hand, when the engine mount 20 is in the rebound state, the bracket 24 and the device case 43 relatively move in the direction away from each other, and the engine side connecting member 3
The support elastic body 32, which is connected between 0 and the inner cylinder 34, extends in the vibrating body support direction. At this time, if a large external force is input to the engine mount 20 such as when the vehicle is rapidly accelerated, the support elastic body 32 may be excessively extended.

However, in the present embodiment, as shown in FIG. 10, when the bracket 24 and the device case 43 relatively move in the direction in which they are separated from each other, the rebound regulation occurs when the support elastic body 32 reaches a predetermined extended state. The rebound stopper member 31 is attached to the lower surface of the regulation body 60a of the member 60.
Abut while elastically deforming. As a result, the bracket 24 and the device case 43 are restrained from moving further relative to each other in a direction in which they are separated from each other, so that the support elastic body 32 is prevented from being excessively extended.

As described above, when the engine mount 20 is in the rebound state, the support elastic body 32 is prevented from being excessively compressed by the abutment of the bounce restriction member (mount side connecting plate) 24b ₂ and the bounce stopper member 59a. In the rebound state, the restriction body 60a of the rebound restriction member 60 and the rebound stopper member 31 are in contact with each other, so that the support elastic body 32 is prevented from being excessively extended. Also, deterioration of the support elastic body 32 due to excessive compression / expansion can be reliably prevented.

Further, the bound stopper member 59a is
Fixed on the upper caulked portion 43a of the apparatus case 43, since the upper position of the bound stopper member 59a Bound regulating member (mount side connecting plate) 24b ₂ are located, bound stopper member 59a and bound regulating member 24b ₂ Does not increase the radial dimension of the engine mount 20.

Further, the rebound stopper member 31 is provided on the upper surface of the engine side connecting member 30, and is provided with the regulating body 60a.
The rebound restricting member 60 having a space extending a predetermined length L extends between the pair of mount-side connecting plates 24b ₂ which are spaced apart from each other, and therefore, the rebound stopper member 31 and the rebound restricting member. Arranging 60 does not increase the size of the engine mount 20 in the height direction.

As described above, since the engine mount 20 of this embodiment does not increase the radial dimension and the height dimension, the apparatus can be downsized. Then, the engine mount 2 of the vehicle, which has a large mounting space restriction.
0 is very advantageous.

The engine-side bracket 24 is not limited to the structure shown in the above embodiment, and is integrally connected to the engine-side connecting member 30 via two or more connecting bolts 30a, and a bounce restricting member is used. With the structure provided, it is possible to obtain the same effects as those of the above embodiment.

Further, in the above embodiment, the case where the anti-vibration support device according to the present invention is applied to the engine mount 20 that supports the engine 22 is shown. The present invention is not limited to the engine mount 20, and may be, for example, an anti-vibration support device for a machine tool that vibrates.

[Brief description of drawings]

FIG. 1 is an overall configuration diagram showing an arrangement state of an anti-vibration support device according to the present invention.

FIG. 2 is a diagram showing an upper structure of a bracket and a vibration isolation support device according to the present invention.

FIG. 3 is a view showing a cross section along an axial direction of a vibration isolation support device.

FIG. 4 is a plan view of the anti-vibration support device.

FIG. 5 is a side view of the anti-vibration support device.

FIG. 6 is a view showing a cross section of a vibration isolation support device cut in a direction orthogonal to the axial direction.

FIG. 7 is a perspective view showing a main part of a second orifice constituent member which is a constituent member of the vibration-damping support device.

FIG. 8 is a view showing a connecting structure of a bracket and a vibration isolation support device.

FIG. 9 is a diagram showing a compression regulating operation by a stopper member and a regulating member when the support elastic body is in a compressed state in the bound state of the vibration-proof support device.

FIG. 10 is a diagram showing an extension regulating operation by a rebound stopper member and a rebound regulating member when the support elastic body is in an extended state in the rebound state of the vibration isolation support device.

[Explanation of symbols]

Reference Signs List 20 engine mount (anti-vibration support device) 22 engine (vibration body) 24 bracket 24b ₂ mount side connecting plate (bound regulation member, regulation member) 28 member (support body) 30 engine side coupling member (first member) 30a connection bolt Reference Signs List 31 rebound stopper member 32 support elastic body 43 device case (second member) 43a upper end crimping portion 46 magnetic path member (movable member) 48 leaf spring (movable member) 52 electromagnetic actuator (actuator) 59a bound stopper member (stopper member) 60 Rebound regulating member 60a Regulators 60b, 60c Stopper leg 66 Main fluid chamber (fluid chamber) 68A First orifice (fluid chamber) 68B First sub fluid chamber (fluid chamber) 70A Second orifice (fluid chamber) 70B Second sub Fluid chamber (fluid chamber) 72A Third orifice (fluid chamber) 72B Third auxiliary fluid chamber (fluid chamber)

Front Page Continuation (72) Inventor Kazushige Aoki 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa Nissan Motor Co., Ltd. (72) Inventor Tsutomu Hamabe 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa Nissan Motor Co., Ltd.

Claims (2)

[Claims] 1. A first member fixed to one of a vibrating body and a support via a bracket, and a second member fixed to the other of the vibrating body and the support with the vibrating body supporting direction as an axis. A support elastic body interposed between the first member and the second member with the vibration body supporting direction as an axis, a fluid chamber defined by the support elastic body and having a fluid enclosed therein, and a partition wall of the fluid chamber. A movable member disposed on the second member side so as to be displaceable in a direction that forms a portion and changes the volume of the fluid chamber, and an actuator disposed on the second member side and displaces the movable member. In the anti-vibration support device including, by making the shape of the first member in the direction orthogonal to the vibrating body support direction smaller than the bracket and the second member, the bracket and the second member ,
Opposing faces in the vibrating body supporting direction are provided, a stopper member made of an elastic body is fixed to the opposing face on the second member side, and the opposing face on the bracket side facing the stopper member is a regulating member, When the bracket and the second member relatively move in a direction in which they approach each other and the support elastic body is in a compressed state, the compressed state of the support elastic body is regulated by abutment of the stopper member and the regulation member. An anti-vibration support device characterized in that 2. At least two connecting bolts projecting toward the bracket while being separated from each other are fixed to the first member, and the first member is integrally connected to the bracket through the connecting bolts. The anti-vibration support device according to claim 1, wherein