JP2009002419A - Vibration control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce shock feeling which is aroused when a stopper rubber is suddenly compressed in significant displacement input, for example, sudden acceleration. <P>SOLUTION: In a combination type engine mount 40 in which a cylindrical bush-like horizontal vibration control part 21 is placed over a vertical vibration control part 20, a first metal mount fitting 2 of the vertical vibration control part 20 is extended upward and integrated with an inner cylinder 23 of the horizontal vibration control part 21. A bracket 12 is fastened with the first metal mount fitting 2 with a bolt 11. As an elastic body of the horizontal vibration control part 21 and an elastic body of the vertical vibration control part 20 are respectively chiefly shearing-deformed, displacement restriction is performed accompanying small shock feeling. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a liquid seal vibration isolator used for an engine mount for automobiles and the like, and in particular, when an input direction of a main vibration to be vibrated with respect to the liquid seal vibration isolator is Z, it is orthogonal on a plane perpendicular thereto. The present invention relates to a device provided with stoppers in the biaxial directions X and Y.

  FIG. 8 shows an example of a conventional automobile engine mount. The engine mount 1 connects a first mounting bracket 2 and a substantially cylindrical second mounting bracket 3 to an insulator 4 made of an elastic body such as an anti-vibration rubber, and an opening of the second mounting bracket 3 is connected to a diaphragm 5. The liquid chamber formed on the inner side is covered with a partition member 6 into a main liquid chamber 7 and a sub liquid chamber 8, and the main liquid chamber 7 and the sub liquid chamber 8 are separated by an orifice passage 9 provided in the partition member 6. Communicate. The partition member 6 is provided with an elastic movable thin film 10 to absorb the hydraulic pressure fluctuation of the partition member 6.

A bracket 12 is connected to the first mounting bracket 2 by a bolt 11 and is connected to an engine (not shown) via the bracket 12. The second mounting bracket 3 is attached to the vehicle body 14 by an integral mounting leg 13.
The engine mount 1 is arranged with the vertical direction aligned with the central axis Z and the longitudinal direction of the vehicle body as the X direction (the Y direction is the horizontal direction).
A stopper fitting 15 is provided at the upper end of the second mounting bracket 3 so as to extend upward in an approximately arch shape. The stopper bracket 15 surrounds the upper portion of the first mounting bracket 2 and is attached through the opening 15b provided on the upper surface 15a thereof. The upper end of the metal fitting 2 and the bolt 11 protrude upward.

A portion of the first mounting bracket 2 inside the stopper bracket 15 is provided with a stopper projection 16 projecting in the front-rear direction below the upper surface 15a and above the insulator 4, and a stopper rubber 17 is provided on the projecting end surface. Covered. There is a predetermined gap D between the stopper rubber 17 and the rear upper and lower portion 15c of the stopper fitting 15, and the stopper rubber 17 abuts on the rear upper and lower portion 15c when a large displacement occurs in the front-rear direction during sudden acceleration or the like. Is to regulate. At the time of sudden deceleration, the front upper and lower portions 15d and the front stopper rubber 17 are in contact with each other to perform the same displacement restriction, but the rear displacement will be described in the following description.
In addition, the stopper protrusion 16 is not provided integrally with the first mounting bracket 2 but may be provided separately (see Patent Document 1).
JP 2005-61592 A

By the way, in the stopper structure of the conventional example, since the stopper rubber 17 acts as a compression spring, the first mounting bracket 2 is relatively displaced rearward as shown in the graph of FIG. When it comes into contact with 15c, the stopper rubber 17 is compressed, and as a result, the spring in the front-rear direction of the engine mount 1 rapidly increases. The inflection point P1 of the graph indicates this, and when the amount of displacement becomes larger than the inflection point P1, the load increases suddenly, and a shock is given to the occupant by this sudden load change. There has been a demand for a reduction in such a feeling of shock.
Accordingly, the present invention aims to realize such a demand.

In order to solve the above-mentioned problem, the invention according to claim 1 relating to the vibration isolator includes a first mounting bracket to which vibration is input, a second mounting bracket to be mounted on the vehicle body side, and coupling between the first and second mounting brackets. A liquid seal vibration isolating means having a first elastic body and a liquid chamber in which a liquid is sealed;
A cylindrical vibration isolating means having an inner cylinder, an outer cylinder, and a second elastic body connecting the inner and outer cylinders;
In the vibration isolator with
The liquid seal vibration isolating means mainly arranges the axis of the first mounting bracket in the vertical direction so as to reduce the vibration in the vertical direction,
The cylindrical vibration isolating means is overlaid on the liquid seal vibration isolating means, and combines an inner cylinder with the first mounting bracket,
By providing the outer cylinder integrally or separately with the second mounting bracket,
A cylindrical vibration isolating means is integrated with the liquid seal vibration isolating means to reduce mainly vibrations in the front-rear direction.

  According to a second aspect of the present invention, in the first aspect, the second elastic body of the cylindrical vibration isolating means has a substantially V-shape convex in the front-rear direction in a plan view and extends from the left and right of the inner cylinder to the outer cylinder. And having first and second stoppers that protrude toward the inner cylinder on the inner surfaces of the front and rear portions of the outer cylinder.

  According to a third aspect of the present invention, in the second aspect, the second elastic body of the cylindrical vibration isolating means is provided with the substantially V-shaped elastic legs on the front and rear of the inner cylinder so that the front and rear elastic legs can be seen in a plan view. It is characterized by an approximately X shape.

  According to a fourth aspect of the present invention, in the first aspect, the inner cylinder of the cylindrical vibration isolating means has a through hole in the vertical direction, and a shaft member that is relatively movable in the vertical direction passes through the through hole. The lower end of this is connected to the first mounting bracket, and the other end is connected after the vibration input.

  According to a fifth aspect of the present invention, in the first aspect, the inner cylinder and the first mounting bracket are coupled to each other while being prevented from rotating.

A sixth aspect of the present invention is characterized in that in the second aspect, the first mounting bracket is provided with a rebound stopper capable of contacting at least a part of the first or second stopper in the vertical direction.

According to the first aspect of the present invention, the anti-vibration mainly prevents the horizontal vibration in the front-rear and left-right directions on the anti-vibration part (hereinafter referred to as the vertical anti-vibration part) that mainly prevents the vibration in the vertical direction. The parts (hereinafter referred to as horizontal vibration isolator) are overlapped to connect the first mounting bracket of the vertical vibration isolator and the inner cylinder of the horizontal vibration isolator, and the outer cylinder is the second mounting bracket of the vertical vibration isolator. And was further connected to the outer cylinder with elastic legs extending in the left-right direction from the inner cylinder.
For this reason, when a large rearward displacement that causes the engine to move rearward relative to the vehicle body occurs, the inner cylinder moves rearward together with the first mounting bracket. At this time, the outer cylinder is integrated with the second mounting bracket. Since the inner cylinder does not move, the inner cylinder moves backward while shearing and deforming the elastic leg to absorb the large rear displacement.
In the shear deformation, the spring is much weaker than the compressive deformation, so the spring change in the front-rear direction at the time of large rearward displacement is gentle compared to the conventional, and can keep linear between larger displacement strokes, Absorbs large rear displacement with a soft spring. For this reason, it is possible to reduce the feeling of shock that has conventionally occurred and to improve the riding comfort.

  According to the second aspect of the present invention, the elastic legs are substantially V-shaped in a plan view, and the stoppers are provided before and after the outer cylinder.

  According to the invention of claim 3, since the pair of front and rear elastic legs are substantially X-shaped in plan view, it can cope with not only front-rear displacement but also left-right displacement.

  According to the invention of claim 4, since the first mounting bracket of the vertical vibration isolator is separated from the inner cylinder of the horizontal vibration isolator, the vertical vibration isolator alone corresponds to the input in the vertical direction. Therefore, there is no influence of the horizontal vibration isolator, and the vertical spring is not increased.

  According to the invention of claim 5, since the first mounting bracket and the inner cylinder are prevented from rotating, when the bolt is mounted on the vibration side, the first mounting bracket and the inner cylinder rotate relative to each other and the mounting position changes. Therefore, when the spring value is given directionality, the spring value can be accurately realized in each direction.

According to the sixth aspect of the present invention, since the first mounting bracket is provided with the rebound stopper that can come into contact with the stopper of the horizontal vibration isolating portion, the horizontal vibration isolating portion is prevented from being excessively displaced in the vertical direction with a simple structure. Can be regulated.

  FIG. 1 is an overall cross-sectional view along the Z-axis direction of a composite engine mount that is an engine mount for automobiles according to a first embodiment, and FIG. 2 is a plan view. The composite engine mount 40 has the same vertical vibration isolator except for the conventional structure shown in FIG. 8 and a partial structure of the first mounting bracket. Therefore, the same reference numerals are used for the common parts, and a duplicate description is omitted. The engine mount 40 is obtained by integrating the vertical vibration isolator 20 and the horizontal vibration isolator 21.

  1 and 2, the horizontal vibration isolator 21 includes an outer cylinder 22, an inner cylinder 23, and elastic legs 25 that connect them. The elastic legs 25 are substantially V-shaped in a plan view, extend from the inner cylinder 23 in the left-right direction, and have their tip portions baked and integrated with the inner periphery of the outer cylinder 22 to form the tops of the left and right elastic legs 25 forming a mountain shape. A certain inner cylinder 23 part is located on the X-axis so as to protrude most forward.

  A front stopper 26 and a rear stopper 27 (FIG. 2) project in the direction of the inner cylinder 23 through a through hole 24 provided in the center of the inner cylinder 23 at the inner circumferential front and rear portions of the outer cylinder 22 on the X axis. The front stopper 26 and the rear stopper 27 are continuously and integrally formed of the same material as that of the elastic legs 25, but different materials such as materials and hardness can be formed integrally with the outer cylinder 22 simultaneously or in different steps. .

  The rear end of the front stopper 26 forms a substantially straight rear edge portion 26a parallel to the Y-axis direction, and a front straight hole 28 is formed between the rear edge portion 26a and the inner cylinder 23 and the elastic leg 25. . The rear stopper 27 has a substantially mountain shape so that the front end portion 27 a protrudes in the direction of the inner cylinder 23, and a rear straight hole 29 is formed between the inner cylinder 23 and the elastic leg 25.

Bolts 11 are passed through through holes 24 provided in the central portion of the inner cylinder 23, and the bracket 12 and the first mounting bracket 2 placed on the inner cylinder 23 are fastened and integrated on a common axis.
In addition, a part of the flange-shaped stopper protrusion 16 that protrudes in the radial direction of the first mounting bracket 2 is further protruded outward to form a rebound stopper 16a, which is rebounded by an impact load input in the vertical direction. Excessive upward movement due to this can be prevented by the rebound stopper portion 16 a coming into contact with the lower surface of the front stopper 26. In normal times, an appropriate clearance d is maintained between the rebound stopper portion 16a and the front stopper 26. This simplifies the stopper structure against rebound.

  The lower part of the outer cylinder 22 forms a connecting peripheral wall part 22a extending long downward, the lower end part of which is slightly enlarged in diameter, and is integrated with the outer periphery of the upper end part of the connecting cylinder 22b. The lower part of the connecting cylinder 22b forms a flange part 22c, is overlapped with an outer flange 3b formed at the upper end part of the cylindrical part 3a of the second mounting bracket 3, and is joined and integrated by roll caulking.

  As shown in the blowing portion in FIG. 1, the lower end 23 a of the inner cylinder 23 and the upper end portion of the first mounting bracket 2 are fitted in a non-rotating state. In this blowing portion, a downward view with respect to the lower end 23 a of the inner cylinder 23 and an upward view with respect to the upper end of the first mounting bracket 2 are shown. The lower end 23a of the inner cylinder 23 is formed with a fitting recess 23b having a rectangular opening that opens downward, and the upper end of the first mounting bracket 2 has a rectangular parallelepiped shape that fits into the fitting recess 23b. A protruding fitting protrusion 2a is formed.

The fitting recess 23b and the fitting protrusion 2a are non-circular shapes such as a rectangular shape on the opening and the top surface, respectively. A non-rotating structure that does not shift relative to each other.
For this reason, when the composite engine mount 40 is assembled, if the spring value is set in each direction in advance, the accuracy during assembly can be increased so that the spring value in each direction can be accurately realized. .

Next, the operation of this embodiment will be described. When there is an input in the front-rear direction to the inner cylinder 23, for example, when the rear cylinder is displaced by a load F in FIG. 2, the inner cylinder 23 is moved rearward on the X axis by the bracket 12 and the bolt 11. At this time, the intermediate portion 25 a of the elastic leg 25 is between the restraining portion 25 c formed between the outer peripheral portion of the inner cylinder 23 and the restraining portion 25 b formed between the inner peripheral portion of the outer cylinder 22. , Shear deformation. At the same time, the insulator 4 is also elastically deformed by the first mounting bracket 2 which is integrated by the inner cylinder 23 and the bolt 11 and moves rearward together with the inner cylinder 23. This deformation is also mainly shear deformation.
For this reason, the springs in the front-rear direction are relatively small mainly composed of the respective shear deformations of the elastic legs 25 and the insulator 4 and restrict large rearward displacements with little shock.

  When the inner cylinder 23 has a predetermined large rear displacement, for example, 6 mm, the inner cylinder 23 comes into contact with the rear stopper 27 and is compressed and deformed. Although the spring in the front-rear direction increases rapidly due to this compression deformation, such a situation is rare, and during normal use, it can absorb a large rearward displacement before contacting the rear stopper 27. Enables large rearward displacement control with little shock due to deformation area.

  Note that the vibration input in the vertical direction is supported by a composite spring of the elastic leg 25 of the horizontal vibration isolator 21 and the insulator 4 of the vertical vibration isolator 20. For this reason, it becomes possible to make the spring of the insulator 4 small.

  FIG. 3 is a graph showing changes in the front and rear springs, and A changes to a substantially linear shape up to an inflection point P2 corresponding to the amount of displacement with which the inner cylinder 23 comes into contact with the rear stopper 27. Since the spring becomes larger than that, the rearward displacement of the inner cylinder 23 is slow, and there is no shock due to shear. When the inflection point P2 is reached, the rear stopper 27 is suddenly increased by compressive deformation, and a reliable large rear displacement is restricted.

4 and 5 relate to the second embodiment, FIG. 4 corresponds to FIG. 1, and FIG. 5 corresponds to FIG. In this example, the inner cylinder 23 has a relatively thin ring shape and surrounds a central hole 30 that is a relatively large-diameter through hole. The inner peripheral surface of the inner cylinder 23 is covered with a bearing portion 31 having corrugated irregularities. The bearing portion 31 is formed integrally with the elastic leg 25.
The upper part of the first mounting bracket 2 protrudes upward and forms an extended shaft part 32 penetrating the central hole 30 upward, and a side surface covering part 33 in which a part of the insulator 4 is continuously formed is formed on the side surface. Be done

The extension shaft portion 32 is inserted into the central hole 30 to penetrate upward, the bracket 12 is overlapped on the upper end portion, and the bolt 11 is coupled to the screw hole 34 formed in the shaft portion, so that only the extension shaft portion 32 is attached to the bracket 12. And the inner cylinder 23 side is uncoupled. At this time, a gap S is formed between the bearing portion 31 and the side surface covering portion 33 as shown in the enlarged portion of FIG. However, the bearing portion 31 and the side surface covering portion 33 may be slidably contacted, and the extension shaft portion 32 and the inner cylinder 23 may be fitted so as to slide substantially.
The bearing portion 31 and the side surface covering portion 33 avoid contact between metals and contact with each other between elastic bodies, thereby preventing noise such as hammering, preventing wear of metal fittings, and reducing shock at the time of contact. Can be planned. Note that either one can be omitted arbitrarily.

  If it does in this way, the extension shaft part 32 and the inner cylinder 2 can move relatively to an up-down direction, and move in the horizontal direction substantially integrally. For this reason, the input in the vertical direction enters only the vertical vibration isolator 20 from the extension shaft portion 32 and does not enter the horizontal vibration isolator 21. Accordingly, when there is an input in the vertical direction, only the extension shaft portion 32 is relatively movable up and down and is received by the insulator 4, so the vertical spring in the composite engine mount 40 is in the vertical vibration isolator 20. Only the spring of the insulator 4 is provided, and the spring of the elastic leg 25 in the horizontal vibration isolator 21 is irrelevant. Therefore, it is possible to prevent the vertical spring from becoming excessive.

On the other hand, for the input in the horizontal direction, the inner cylinder 23 is pressed against the extension shaft portion 32 and moves together. Therefore, the spring in the horizontal direction is a composite of the insulator 4 and the elastic legs 25, and the front and rear direction is combined. As for the spring, it is possible to obtain a relatively large spring that is substantially the same as the previous embodiment. In addition, the spring ratio can be easily adjusted so that the lateral spring is relatively large with respect to the vertical spring, and the lateral spring ratio, which has been difficult to achieve in the past, is equal to or higher than the vertical spring ratio. It is possible to greatly improve the spring ratio. The ratio of the spring X in the front-rear direction and the spring Z in the vertical direction, where X: Z is about 1.3: 1 at most in the conventional structure, is made about 2: 1 according to the present embodiment. Will be able to.
As shown in FIG. 3, the same or slightly better characteristics as in the previous embodiment are shown, but the amount of displacement up to the inflection point P3 is the largest.

  6 and 7 relate to the third embodiment, in which the elastic leg portion of the second embodiment is changed. FIG. 6 corresponds to FIG. 4 and FIG. 7 corresponds to FIG. In this example, the elastic legs 25 are provided in front of and behind the inner cylinder 23, and two elastic legs forming V respectively forward and backward are integrated to form a substantially X shape in plan view. In this way, the same spring characteristics can be exhibited both before and after.

The present invention is not limited to the above-described embodiments, and various modifications and applications can be made within the principle of the invention. For example, in the first embodiment, the inner cylinder 23 and the first mounting bracket 2 can be integrated by press-fitting, or can be shared by the other one of which is omitted. Further, the outer cylinder 21 may be a common member integrated with the second mounting bracket 3.

Sectional view taken along line 1-1 of FIG. 2 according to the first embodiment. Plan view of the first embodiment Front and rear spring characteristics graph Sectional view taken along line 4-4 in FIG. 5 according to the second embodiment. Plan view of an engine mount according to the second embodiment Sectional view along line 6-6 in FIG. 7 according to the third embodiment. Plan view of the engine mount according to the third embodiment Overall sectional view of a conventional example

Explanation of symbols

1: engine mount, 2: first mounting bracket, 3: second mounting bracket, 4: insulator, 11: bolt, 12: bracket, 14: vehicle body, 20: vertical vibration isolator, 21: horizontal vibration isolator, 22: outer cylinder, 23: inner cylinder, 25: elastic leg, 30: central hole, 32: extension shaft, 40: composite engine mount

Claims (6)

A first mounting bracket for receiving vibration; a second mounting bracket mounted on the vehicle body; a first elastic body for connecting the first and second mounting brackets; and a liquid chamber in which a liquid is sealed. Liquid seal anti-vibration means;
A cylindrical vibration isolating means having an inner cylinder, an outer cylinder, and a second elastic body connecting the inner and outer cylinders;
In the vibration isolator with
The liquid seal vibration isolating means mainly arranges the axis of the first mounting bracket in the vertical direction so as to reduce the vibration in the vertical direction,
The cylindrical vibration isolating means is overlaid on the liquid seal vibration isolating means, and combines an inner cylinder with the first mounting bracket,
By providing the outer cylinder integrally or separately with the second mounting bracket,
A vibration isolator comprising a cylindrical vibration isolating means integrated with the liquid seal vibration isolating means to reduce mainly vibrations in the front-rear direction.
The second elastic body of the cylindrical vibration isolating means includes a first elastic leg that is substantially V-shaped convex in the front-rear direction in plan view and extends from the left and right of the inner cylinder to the outer cylinder, and the front and rear of the outer cylinder The vibration isolator according to claim 1, further comprising first and second stoppers projecting toward the inner cylinder on the inner surface of the part.
The second elastic body of the cylindrical vibration isolating means is characterized in that the front and rear elastic legs are substantially X-shaped in plan view by providing the substantially V-shaped elastic legs before and after the inner cylinder. 2. The vibration isolator described in 2.
The inner cylinder of the cylindrical vibration isolating means has a through hole in the vertical direction, a shaft member that is relatively movable in the vertical direction is passed through the through hole, and the lower end of the shaft member is coupled to the first mounting bracket. The anti-vibration device according to claim 1, wherein the other end is connected after the vibration input.
The vibration isolator according to claim 1, wherein the inner cylinder and the first mounting bracket are coupled to each other while being prevented from rotating.
  The vibration isolator according to claim 2, wherein a rebound stopper capable of contacting at least a part of the first or second stopper in the vertical direction is provided on the first mounting bracket.

Images