JP4676293B2 - Vibration isolator - Google Patents

Description

  The present invention relates to an anti-vibration device used for an engine mount or the like, and more particularly, to an apparatus having improved durability when using an insulator having a thin portion.

As an anti-vibration device used for automobile engine mounts, etc., a substantially dome-shaped insulator that constitutes a part of the liquid chamber is provided, and main vibration is input from a vibration input section provided at the center of the insulator. There is known a liquid seal vibration isolator configured as described above. In addition, the thickness of the insulator is relatively changed to provide a thin portion and a thick portion, and the thin portion is used as a whole with a low spring to suppress an increase in hydraulic pressure during excessive input (for example, patents). Reference 1).
JP 2000-186739 A

  FIG. 5 schematically shows the insulator 103 provided with such a thin portion from the main vibration input direction. The thin portion 111 is formed in a cross shape, and the adjacent thin portions 111 are relatively thick. The thick-walled portion 112 (shown by lattice-like hatching) has a substantially sector shape. A vibration input unit 104 is provided at the center, and main vibrations are input here.

  By providing the thin portion 111, the thick portion 112 has a fan shape, and the width a of the outer peripheral portion 112A is significantly larger than the width b of the central portion 112B. When the elastic deformation mainly consisting of tensile and compressive deformation is performed between the outer peripheral portion 112A and the central portion 112B of the thick portion 112 by inputting a direction orthogonal to the direction (hereinafter referred to as a lateral direction), the outer peripheral portion 112A and the center The difference in rigidity of the portion 112B becomes remarkable. As a result, a large stress concentration is generated on the side of the central portion 112B having a lower rigidity, and the durability is likely to be lowered.

In addition, when the vertical spring is Z and the two orthogonal springs in the same plane in the horizontal direction are X and Y, the stress concentration becomes significant when the horizontal spring is made larger than the vertical direction. Even if it is desired to increase the lateral spring, it cannot be increased so much from the viewpoint of durability, and the spring ratio Z: X: Y in each direction is at most about 1: 0.8: 0.4. However, in recent years, there has been a demand for greatly improved spring ratios such that X and Y are 1.0 or more than Z.
Therefore, the main purpose of the present application is to improve the durability of the insulator even when a thin wall portion is provided, and to improve the spring ratio so as to increase the lateral spring. Also aimed.

In order to solve the above-mentioned problems, the invention according to claim 1 relating to the vibration isolator of the present application is arranged between the engine and the vehicle body, and has a main body portion having a metal cylindrical metal fitting, and is integrated with the main body portion to reduce the input vibration. An insulator for interrupting transmission by elastic deformation is provided, and a main vibration input portion is embedded and integrated in the center of a concave curved surface portion formed in the insulator, and is fitted inside a cylindrical metal fitting forming the main body portion. In the vibration isolator in which a part of the inner cylindrical fitting is embedded and integrated in the outer peripheral portion, and the thickness of the insulator around the vibration input portion is relatively changed to provide a thin portion and a thick portion,
Concave surface portion of the insulator, as well as can form a circular shape and viewed from the input direction of the principal vibration, the thick portion forms a band-shaped one constant width, transverse to the radial direction through the vibration input unit, wherein Protrudes into the space from the surface of the thin portion facing the space surrounded by the concave curved surface portion of the insulator,
In the longitudinal direction of the thick-walled portion that crosses in the diameter direction, the outer peripheral portion that is coupled to the inner cylindrical metal fitting and the central portion that is coupled to the vibration input portion are provided. with the width of the intermediate portion is one Jode between width and their outer periphery at the position of the outer peripheral portion toward the central portion,
The elastic deformation portion of the insulator between the input portion of the upper and principal vibration of the inner cylindrical member is the initial load of the engine, is what was without a shaped cross-section of those Hatsuha initially until horizontal It is characterized by being deformed.

A second aspect of the present invention in the claim 1, wherein the symmetrically across the thick portion of the semicircular the thin portion.

  According to a third aspect of the present invention, the vibration isolator according to the first aspect is mounted on a vehicle and used, and the thick portion is disposed in the front-rear direction of the vehicle when mounted on the vehicle.

According to a fourth aspect of the present invention, in the first aspect, when the spring in the input direction of the main vibration is Z and the springs in two directions orthogonal to each other in a plane orthogonal to the input direction of the main vibration are X and Y, Z X or Y spring ratio to
Z: X or Y = 1: 1 or more.

According to a fifth aspect of the present invention, in the vibration isolator according to the first aspect of the invention, the incompressible liquid is sealed in the space surrounded by the concave curved surface portion, so that the insulator constitutes a part of the liquid chamber. It is a sealing vibration isolator.
A sixth aspect of the present invention is the above-mentioned fifth aspect, wherein the liquid seal vibration isolator includes a main liquid chamber and a sub liquid chamber that are partitioned by a partition member as the liquid chamber and communicated by an orifice passage. Is provided with a hole opened in the main liquid chamber, and the opposite side of the hole to the main liquid chamber is closed by an elastic membrane member,
Resonance due to the hole, resonance due to the elastic membrane member, first resonance and second resonance due to the thin-walled portion, and resonance due to the thick-walled portion are generated according to changes in the frequency of the input vibration in the mid-high frequency range. It is characterized by doing. Here, the medium-high frequency range refers to a frequency range of 100 to 2000 Hz.

According to the present invention, the circular shape can saw the concave surface of the insulator from the input direction of the principal vibration, since the quasi-strip across the thick portion in one of constant width to the diameter direction, the thick portion The width of the outer peripheral portion and the width of the central portion are substantially constant, and the difference in rigidity in the longitudinal direction of the thick portion is reduced. For this reason, when the thick portion elastically deforms in the longitudinal direction with respect to the input in the lateral direction, a large stress concentration on the center portion side can be suppressed, and uniform elastic deformation in the entire thick portion can be achieved. As a result, the durability of the insulator can be further improved despite the provision of the thin wall portion.

According to the invention of claim 2, by arranging the thin-walled portion of the semicircular symmetrically across the thick portion can be increased a thin portion, the longitudinal direction of the thick portion, the direction of which is perpendicular thereto The spring ratio can be changed clearly.

  According to the invention of claim 3, the anti-vibration device can be used for a vehicle, and the spring in the front-rear direction can be increased by arranging the thick portion in the vehicle-mounting direction in the front-rear direction of the vehicle.

  According to the invention of claim 4, since the spring ratio of the two-way spring X or Y perpendicular to the transverse direction with respect to Z is 1: 1 or more, the vertical spring is set to 1: 1 or more. Each spring ratio of the springs X and Y can be greatly improved to 1 or more.

  According to invention of Claim 5, durability of the liquid seal vibration isolator provided with the insulator which has a thin part by enclosing an incompressible liquid in the space by a concave curved surface part to make a liquid seal vibration isolator. Can be improved.

According to the invention of claim 6, the liquid seal vibration isolator includes a main liquid chamber and a sub liquid chamber which are partitioned by a partition member and communicated by an orifice passage, and the partition member has a hole opened to the main liquid chamber. And is configured so that the opposite side of the hole to the main liquid chamber is closed by an elastic film member, and according to the frequency change of the input vibration in the middle to high frequency range, resonance by the hole, resonance by the elastic film member, Since the first and second resonances due to the thin-walled portion and the resonance due to the thick-walled portion are generated, the dynamic characteristics can be improved in a wide frequency range by sequentially generating these many resonances. .

  Hereinafter, an embodiment configured as an automobile engine mount will be described. FIG. 1 is a plan view of the engine mount 1, and an insulator 3 is integrated with an upper portion of a circular main body 2. A vibration input portion 4 made of a block-shaped metal fitting is embedded and integrated in the center portion of the insulator 3, and one end of the engine bracket 6 is attached to the top portion and a bolt 5. The other end of the engine bracket 6 is attached to an engine (not shown) with a bolt. Reference numeral 7 denotes a fitting that is welded and integrated with the lower portion of the main body 2 and is bolted to the vehicle body side.

    2 is a cross-sectional view taken along line 2-2 of FIG. The main body 2 has an outer cylindrical metal fitting 8 having a cylindrical shape made of metal and a stopper 9 made of a composite of metal and rubber attached to the upper part thereof. The stopper 9 surrounds the periphery of the insulator 3, and the insulator 3 is fitted to the upper inside of the outer tubular fitting 8.

The insulator 3 is made of a well-known anti-vibration rubber material having appropriate physical properties, and has a hollow conical shape or a substantially dome shape as a whole, and forms a concave curved surface portion 10 having a concave surface whose inner surface is substantially hemispherical in the illustrated cross section. On the concave curved surface portion 10 side of the insulator 3, thin portions 11 are provided at appropriate intervals in the circumferential direction, and portions other than the thin portion 11 are relatively thick portions 12. The outer periphery of the insulator 3, the small diameter portion 13a which forms a substantially U-shaped cross section at the top of the inner side cylindrical member 13 is embedded integrally.

  Here, in the illustrated state, a direction corresponding to the axis of the vibration input unit 4 and the bolt 5 is defined as a main vibration input direction (vertical direction). Further, the direction orthogonal to this is the horizontal direction, and of the two orthogonal directions in the horizontal direction, the direction parallel to the front-rear direction of the vehicle body in use is the front-rear direction, and the direction parallel to the left-right direction is the left-right direction (see FIG. 1 and 3). As apparent from FIG. 2, the thin portion 11 appears in the cross section in the left-right direction, and the thick portion 12 appears in the cross section in the front-rear direction. Of the springs in each direction of the insulator 3, those in the front-rear direction are X, those in the left-right direction are Y, and those in the vertical direction are Z.

  The concave curved surface portion 10 forming the dome shape of the insulator 3 constitutes a part of the main liquid chamber 14. The bottom of the main liquid chamber 14 is closed with a first partition member 15. The first partition member 15 has a circular disk shape, and an orifice groove 16 that is open upward is formed on the outer peripheral portion, and an orifice passage 18 is formed by covering the top with a lid 17.

  Although not shown in the drawing, the orifice passage 18 communicates with the main liquid chamber 14 through an inlet formed in the lid 17 and is formed at the bottom of the orifice groove 16 from the outlet that is also not shown in the drawing. It communicates with the orifice groove 20 of the member 19.

  The second partition member 19 has a circular disk shape formed by opening the orifice groove 20 upward on the outer peripheral portion, and is covered by the first partition member 15 stacked on the upper surface thereof. An outlet not visible in the figure is formed at the bottom of the orifice groove 20, and communicates with the secondary liquid chamber 21 below the second partition member 19. Therefore, the orifice passage 18 communicates with the main liquid chamber 14 and the sub liquid chamber 21 and is set so as to generate liquid column resonance in a relatively low frequency range (for example, about 20 Hz or less) such as during idle operation. Has been.

  An incompressible liquid is sealed in the secondary liquid chamber 21, the orifice passage 18, and the main liquid chamber 14. The lower part of the sub liquid chamber 21 is covered with a diaphragm 22, and the capacity of the sub liquid chamber 21 is made variable according to the liquid movement through the orifice passage 18. The orifice passage 18 is tuned to generate liquid column resonance for a predetermined input vibration frequency. When the liquid flows between the main liquid chamber 14 and the sub liquid chamber 21 via the orifice passage 18 by the vibration input to the main liquid chamber 14 via the vibration input unit 4, the liquid column resonance is generated and the energy of the input vibration is generated. Is absorbed and vibration transmission is cut off.

  A metal ring 23 is integrated with the outer peripheral portion of the diaphragm 22 and is press-fitted inside the enlarged diameter portion 13 c forming a part of the inner cylindrical metal fitting 13. The inner tubular fitting 13 is generally cylindrical, and is made of a metal having a smaller thickness than the outer tubular fitting 8, and the portion embedded in the outer peripheral portion of the insulator 3 constitutes a small diameter portion 13a, and the step below it. It becomes a diameter-expanded portion 13c that overlaps the inner peripheral surface of the outer cylindrical fitting 8 via the portion 13b and extends downward.

  An elastic membrane member 24 is sandwiched between the first partition member 15 and the second partition member 19. The elastic membrane member 24 faces the main liquid chamber 14 via a circular hole first hole 25 formed in the central portion of the first partition member 15, and is also a circular hole formed in the central portion of the second partition member 19. When the liquid pressure in the main liquid chamber 14 rises due to the input vibration, it is elastically deformed to cancel this.

  Further, the elastic membrane member 24 resonates with respect to a specific input vibration frequency in a medium to high frequency range of about 100 to 2000 Hz by elastically deforming according to the liquid flow generated in the main liquid chamber 14 by the input vibration. This resonance is a membrane resonance caused by the resonance vibration of the elastic membrane member 24, and the resonance frequency at this time can be set relatively freely by adjusting the spring elasticity of the elastic membrane member 24.

  Further, when the liquid in the main liquid chamber 14 flows through the first hole 25, liquid column resonance (this is referred to as hole resonance) occurs at a specific frequency in the mid-high frequency range due to the liquid flow. Since this resonance frequency is related to the volume of the liquid flow space in the first hole 25, it can be set relatively freely by adjusting the passage opening area and the like.

  Further, since the thin portion 11 and the thick portion 12 of the insulator 3 also function as a kind of elastic membrane member, the membrane resonance occurs at a specific frequency by the input vibration in the middle and high frequency range. Each resonance frequency can be set relatively freely by adjusting the thickness of the thin portion 11 and the thick portion 12 and adjusting each spring elasticity. The dynamic characteristics due to these resonance points will be described later.

  Of the outer peripheral portion of the insulator 3, the vicinity of the small diameter portion 13a forms a stepped portion 27 projecting downward from the enlarged diameter portion 13c. Further, a relatively thin liner portion 28 is also formed integrally with the insulator 3 inside the enlarged diameter portion 13c.

  The lid 17, the first partition member 15, the second partition member 19, and the diaphragm 22 are placed in this order from the bottom of the figure into the cylindrical portion formed by the enlarged diameter portion 13 c and the liner portion 28, and the lower end of the enlarged diameter portion 13 c. The parts are folded inward to form a bent part 29, which is assembled and integrated.

  At this time, the bent portion 29 comes into contact with the metal ring 23 integrated with the outer peripheral portion of the diaphragm 22 by the metals and is firmly bonded. The lid 17 and the orifice groove 16 are positioned by the step portion 27 and sealed by being brought into close contact with the step portion 27.

  As described above, the insulator 3, the vibration input unit 4, the inner cylindrical metal fitting 13, the first partition member 15, the lid 17, the second partition member 19, and the diaphragm 22 are integrated as an intermediate assembly. The whole is assembled by fitting the inner tube fitting 13 into the outer tube fitting 8 and integrating it with the stopper 9.

  At this time, the upper end portion of the outer tubular fitting 8 forms an outward flange 30, the outward flange 31 formed on the upper end portion of the inner tubular fitting 13 is overlaid thereon, and the lower end portion 32 of the stopper 9 is further overlapped. Each member is connected and integrated by bending the lower end portion 32 around each flange 30 and 31 into a substantially U-shaped cross section and performing roll crimping.

  The outer side of the stopper 9 is made of metal, but a liner rubber 33 is integrated inside the stopper 9 so as to receive the movement of the protruding portion 34 protruding from the outer peripheral portion of the vibration input portion 4 while buffering. . Also on the surface of the protrusion 34, a covering portion 35 that is continuous with the insulator 3 is formed.

FIG. 3 is a view showing the concave curved surface portion 10 of the insulator 3 along the vertical direction from the bottom of FIG. 2, and the concave curved surface portion 10 has a substantially circular shape. The thick portion 12 (shown by lattice-like hatching) has a substantially band shape, passes through the vibration input portion 4 and traverses the concave curved surface portion 10 in the diameter direction, and becomes the width a of the outer peripheral portion 12A and the vicinity of the vibration input portion 4. The width b of the central portion 12B is substantially constant. The longitudinal direction of the thick portion 12 is arranged in the front-rear direction, and the thin portions 11 having a substantially semicircular shape are provided on the left and right sides of the thick portion 12 symmetrically .

  The thin portion 11 is a portion for weakening the springs Y and Z in the vertical direction and the horizontal direction in the insulator 3. On the other hand, since the thick portion 12 is thicker than the thin portion 11, the rigidity is relatively high, and the spring X in the front-rear direction is increased. That is, the springs in three orthogonal directions, X, Y, and Z, have different sizes.

  In this example, these spring ratios, Z: X: Y, are about 1: 1.5: 1. However, the spring ratio is such that X and Y are each 1 or more with respect to Z (Z is set to 1), and the ratio can be arbitrarily set according to use conditions and the like. In particular, when it is desired to strengthen the spring in the front-rear direction, it is preferable to set X to 1.5 or more. For example, Z: X: Y = 1: 1.7: 1.1 can be set. There is no upper limit for X and Y, but there is a certain limit.

  Further, the sizes of the springs X, Y, and Z in each direction can be freely set by adjusting the thickness and width of the thick portion 12 and the thin portion 11, and as a result, the X, Y, and Z The spring ratio can be adjusted freely.

  Next, dynamic characteristics in the engine mount 1 will be described. FIG. 4 is a graph showing the dynamic characteristics of the engine mount 1 according to this embodiment in order to show the setting of each resonance point. The horizontal axis represents frequency (Hz) and the vertical axis represents dynamic spring constant K * (N / mm). And the phase P (degree) is taken. This graph shows only the range of about 100 to 1000 Hz among the frequencies of the input vibration in the middle and high frequency range. Therefore, the liquid column resonance caused by the orifice passage 18 generated in the low frequency region is not displayed.

   In this figure, as is apparent from the upper phase curve, resonances A to E are sequentially generated as the frequency increases in the middle and high frequency range. A is the hole resonance caused by the first hole 25, B is the first membrane resonance caused by the thin portion 11, D is the membrane resonance caused by the elastic membrane member 24, D is the second membrane resonance caused by the thin portion 11, and E is thick. This is a membrane resonance by the section 12.

  When a large number of resonance points coexist in this way, a certain resonance point is influenced by another resonance point. Accordingly, each resonance point is a result of combining and combining other resonances (hereinafter referred to as coupling). This coupling acts to level out if adjacent resonance points are moderately separated and may amplify if they are too close. Therefore, in this embodiment, it is separated by 100 Hz or more. In particular, the membrane resonance (C) due to the elastic membrane member 24 and the second membrane resonance (D) due to the thin-walled portion 11 occur adjacent to each other due to the setting of the spring elasticity, but again between the CDs. Are provided with an interval of 100 Hz or more.

  The lower part of the figure shows dynamic spring characteristics, and shows the coupled results of these resonance points A to E. As is apparent from this characteristic, by sequentially generating the resonance points A to E as described above, the mid-high frequency range is leveled to a relatively low dynamic spring state, and a preferable dynamic characteristic can be realized. This leveling becomes more reliable by separating each resonance point by 100 Hz or more.

  The order of occurrence of resonance is also important for the above leveling, and the membrane resonances B to E are appropriately set by sandwiching the membrane resonance C by the elastic membrane member 24 between the membrane resonances B and D by the thin portion 11. It is possible to facilitate the adjustment that can be generated at intervals to realize the overall leveling. Therefore, if this order is changed, problems such as difficulty in adjusting the spring between the membrane resonance generators may occur.

  Further, in the spring adjustment in this membrane resonance, the spring setting of the elastic membrane member 24 is also important. When the elastic membrane member 24 is made too hard and the spring is raised, the distance from the second membrane resonance D by the thin portion 11 is increased. Becomes narrow and amplified coupled. For this reason, the spring setting of the elastic film member 24 needs to be set appropriately in consideration of the balance with the resonance points B and D on both sides.

  Next, the operation of this embodiment will be described. In FIG. 2, when the engine mount 1 is mounted on the vehicle body, the vibration input portion 4 is pushed downward and moved by an initial load from the engine, and the elastic deformation of the insulator 3 between the upper portion of the inner cylindrical metal fitting 13 and the vibration input portion 4 is performed. The portion initially having a substantially C-shaped cross section is initially deformed until it becomes substantially horizontal as indicated by a virtual line.

  If there is vertical vibration input to the vibration input unit 4 in this state, the elastically deforming part of the insulator 3 performs elastic deformation mainly of shearing, and in the lateral direction, elastic deformation mainly of compression and tension occurs. Further, the presence of the thin portion 11 further reduces the vertical spring Z. As a result, the spring ratio is significantly increased on the X and Y sides with respect to Z. That is, the engine mount 1 has a form in which the lateral spring is larger than the vertical direction.

  In FIG. 3, the vibration input in the lateral direction corresponds to the front-rear direction by elastic deformation mainly consisting of compression and tension in the longitudinal direction of the thick portion 12, and the thick portion 12 in the left-right direction. This is handled mainly by elastic deformation by bending in a direction perpendicular to the longitudinal direction. Further, in the left-right direction, the value of the spring Y becomes lower than X due to the presence of the thin portions 11, 11. Accordingly, the springs in each direction are set so as to generate a tendency that X> Y> Z.

  That is, the thick portion 12 is elastically deformed mainly by tension and compression between the outer peripheral portion 12A and the central portion 12B with respect to the vibration input in the front-rear direction. At this time, since the thickness of the thick portion 12 is large and force is applied to both ends in the longitudinal direction, the spring X in the front-rear direction becomes the highest spring, for example, 1.5 or more with respect to the spring Z in the vertical direction. The spring ratio is realized. However, the spring ratio of X to Z is preferably about 1.0 to 1.7 from the overall balance, even if the lateral spring is of a larger type.

  The vibration input in the left-right direction is dealt with by elastic deformation of the thick portion 12 and the thin portion 11, but since the spring of the thin portion 11 is small, the thick portion 12 is mainly bent. For this reason, the spring Y in the left-right direction is lower than the spring X in the front-rear direction, and the spring ratio of Y to Z is adjusted to be 1.0 or more and smaller than the spring ratio of X to Z.

Further, since the thick portion 12 has a substantially band shape, the width “a” of the outer peripheral portion 12A and the width “b” of the center portion 12B are substantially the same, and the width of the intermediate portion is also substantially constant. Absent. For this reason, even when elastically deforming in response to the input in the front-rear direction, the entire thick portion 12 is made uniform, and stress does not concentrate on a specific part such as the center side. The stress concentration avoidance in the thick portion 12 is the same in the elastic deformation of the thick portion 12 in the vertical and horizontal directions.
Therefore, even if it is the structure which provided the thin part 11, durability with respect to the repeated continuous elastic deformation of the thick part 12 can be improved.

  Moreover, since the durability of the thick portion 12 is improved, the lateral springs X and Y can be made higher than the vertical spring Z in the insulator 3 having the thin portion 11. Ratio improvement and durability improvement can be realized at the same time. Moreover, the freedom degree in the setting of each spring X, Y, and Z in three orthogonal directions becomes high.

  In addition, as in this embodiment, the insulator 3 is substantially horizontal due to the downward movement of the vibration input portion 4 when an initial load is applied, and the elastic deformation in the lateral direction is set to a high spring mainly consisting of compression and tension. It is also suitable for things.

  Further, since the substantially semicircular thin portions 11 are arranged symmetrically across the thick portion 12, the thin portion 11 can be enlarged, and the spring X in the longitudinal direction (front-rear direction) of the thick portion 12 is orthogonal to this. It is possible to clearly change the spring ratio of the spring Y in the direction (left-right direction). In addition, the spring X in the front-rear direction can be easily increased by arranging the thick portion 12 in the vehicle front-rear direction.

  In addition, as shown in FIG. 4, as the frequency of the input vibration in the middle and high frequency range increases, the hole resonance A by the first hole 25, the first film resonance B by the thin portion 11, and the film by the elastic film member 24 The resonance C, the second membrane resonance D due to the thin portion 11 and the membrane resonance E due to the thick portion 12 are generated in this order. Since the dynamic spring characteristics can be leveled to the low dynamic spring side, the dynamic characteristics can be improved.

  In addition, by sandwiching the membrane resonance C by the elastic membrane member 24 between the membrane resonances B and D by the thin-walled portion 11, each membrane resonance B to E can be generated at an appropriate interval so that the entire leveling can be realized. Adjustment can be facilitated. Depending on the adjustment of each resonance point in the Hall resonance and each membrane resonance, there are cases where the dynamic characteristics can be leveled even if the order of the plurality of resonances is changed variously. Therefore, the five types of resonances A to E are not limited to the generation order, and are distributed at a predetermined frequency interval so that the entire dynamic characteristic is leveled toward the low dynamic spring side. Can improve over a wide range.

  In addition, this invention is not limited to the said embodiment, A various deformation | transformation and application are possible. For example, the spring ratio of X and Y is not necessarily X> Y, and can be freely set according to use conditions such as X = Y or X <Y. Furthermore, the directionality of such a spring can be freely set. In short, the input direction of the main vibration may be set to any one of up / down, front / rear, and left / right, and the other two orthogonal directions are set accordingly. It can be determined as appropriate.

  Further, if the thick portion 12 is formed in a cross shape in the front-rear and left-right directions, the front-rear and left-right springs can be enlarged. The width and thickness of the thick part 12 can be freely adjusted. Furthermore, the shape, number, and thickness of the thin portions 11 are arbitrary, and may be substantially elliptical, for example. Further, the present invention can be applied to various other vibration isolators for vehicles, and in the case of vehicles, can be applied to various uses other than engine mounts. The anti-vibration device is not limited to a liquid seal type, and can be applied to a device that does not use a liquid, such as a liquid seal structure that excludes the liquid.

The top view of the liquid seal vibration isolator which concerns on embodiment 2-2 sectional view of FIG. Diagram showing the insulator from the main vibration input direction The graph which shows the dynamic characteristic of an Example The figure which shows the insulator of a prior art example

Explanation of symbols

1: Engine mount, 3: Insulator, 4: Vibration input part, 10: Inner surface, 11: Thin part, 12: Thick part, 14: Main liquid chamber

Claims (6)

A concave portion formed in the insulator is provided between the engine and the vehicle body, and includes a main body portion having a metal cylindrical metal fitting, and an insulator integrated with the main body portion to block transmission of input vibration by elastic deformation. The main vibration input part is embedded and integrated in the center of the curved surface part, and a part of the inner cylindrical fitting that is fitted inside the cylindrical fitting that forms the main body is embedded and integrated in the outer peripheral part. In the vibration isolator provided with the thin part and the thick part by relatively changing the thickness of the insulator in
Concave surface portion of the insulator, as well as can form a circular shape and viewed from the input direction of the principal vibration, the thick portion forms a band-shaped one constant width, transverse to the radial direction through the vibration input unit, wherein Protrudes into the space from the surface of the thin portion facing the space surrounded by the concave curved surface portion of the insulator,
In the longitudinal direction of the thick-walled portion that crosses in the diameter direction, the outer peripheral portion that is coupled to the inner cylindrical metal fitting and the central portion that is coupled to the vibration input portion are provided. with the width of the intermediate portion is one Jode between width and their outer periphery at the position of the outer peripheral portion toward the central portion,
The elastic deformation portion of the insulator between the input portion of the upper and principal vibration of the inner cylindrical member is the initial load of the engine, is what was without a shaped cross-section of those Hatsuha initially until horizontal A vibration isolator that is deformed. Vibration isolating apparatus according to claim 1, characterized in that the thin portion across the thick portion provided on the semicircular and symmetrical. 2. The vibration isolator according to claim 1, wherein the anti-vibration device is used by being mounted on a vehicle, and the thick portion is arranged in the front-rear direction of the vehicle when mounted on the vehicle. When the spring in the input direction of the main vibration is Z and the springs in the two directions orthogonal to each other in the plane orthogonal to the input direction of the main vibration are X and Y, each spring ratio of X or Y to Z is expressed as Z: 2. The vibration isolator according to claim 1, wherein X or Y is 1: 1 or more. 2. The anti-vibration device according to claim 1, wherein the insulator is a liquid seal vibration isolator that constitutes a part of a liquid chamber by sealing an incompressible liquid in a space surrounded by the concave curved surface portion. Shaker. The liquid seal vibration isolator includes a main liquid chamber and a sub liquid chamber which are partitioned by a partition member and communicated by an orifice passage, and the partition member has a hole opened to the main liquid chamber. Provided, and closes the opposite side of the hole to the main liquid chamber with an elastic membrane member,
Resonance due to the hole, resonance due to the elastic membrane member, first resonance and second resonance due to the thin-walled portion, and resonance due to the thick-walled portion are generated according to changes in the frequency of the input vibration in the mid-high frequency range. The vibration isolator according to claim 5.

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