JPS62184249A - Fluid enclosing-type vibro-isolating support body - Google Patents

Abstract

PURPOSE:To improve vibration cutting off operation against a vibration with a small amplitude, by forming a pair of void spaces on both sides of an elastic member disposed between an inner cylinder metal fitting and an intermediate metal fitting. CONSTITUTION:The first elastic member 16 is disposed between an inner cylinder metal fitting 10 and an intermediate metal fitting 14. A pair of void spaces 30 are formed on both sides of this elastic member 16 facing each other as placing the inner cylinder metal fitting 10 inbetween. In the diametrical direction in which those void spaces are facing each other, the inner cylinder metal fitting 10 and the intermediate metal fitting 14 are to be in relative motion by shear deforming operation of the first elastic member 16. Therefore, as far as the relative motion is admitted, flexible spring character can be obtained in the facing direction of those void spaces. In other words, any vibration input in the facing direction of void spaces, is effectively absorbed by a shear deforming means of the first elastic member, when its amplitude is small. Meanwhile, when the amplitude exceeds the specified level, the inner cylinder metal fitting 10 touches the intermediate metal fitting 14, so that relatively rigid conventional spring character can be obtained by the second elastic member for forming a fluid chamber 20 communicated through an orifice member 26.

Description

Detailed Description of the Invention (Technical Field) The present invention relates to a cylinder that exhibits a good vibration isolation function mainly against input vibration in the radial direction based on the elastic deformation of an elastic member and the flow resistance of fluid. This relates to a type of fluid-filled vibration isolating support body, and more specifically, when the frequency is relatively high and the amplitude is small for vibrations input in a specific radial direction, it is mainly based on the elastic deformation of the elastic member. The present invention relates to a fluid-filled vibration damping support that exhibits a good damping effect mainly based on fluid flow resistance, and has a relatively low frequency and a large amplitude.

(Prior art) A type of vibration isolating support used in a vibration system of a vehicle such as an automobile is a type of vibration isolating support that is interposed between a predetermined shaft member and a predetermined cylindrical member or a predetermined support member. There is a cylindrical type that connects them with vibration isolation.

In such a cylindrical type vibration-proof support, while maintaining a relatively stiff spring characteristic in one radial direction, there is a structure that provides good isolation against high-frequency, small-amplitude vibration in the radial direction perpendicular to the radial direction. There are some devices that are required to have a good damping effect against low-frequency, large-amplitude vibrations. For example, a cylindrical roll stopper used as an engine mount for FF engine vehicles is an example of such a roll stopper.

By the way, in a cylindrical type vibration-proof support that is required to have such a function, an elastic member has conventionally been interposed between the inner cylindrical metal fitting attached to the shaft member and the outer cylindrical metal fitting attached to the cylindrical member or support member. Since the vibration input in the radial direction is blocked or attenuated based only on the elastic deformation of the elastic member, it is possible to effectively block the vibration input in the radial direction. There is a limit to the ability to simultaneously obtain a good damping function and a sufficient damping function particularly for low frequency, large amplitude vibrations in the radial direction.

Therefore, in recent years, a pair of fluid chambers are formed inside the elastic member so as to face each other with the inner cylindrical fitting interposed therebetween, and the fluid chambers are communicated with each other by a predetermined orifice means, and a predetermined non-container sealed in the fluid chambers is formed in the elastic member. So-called fluid-filled anti-vibration supports have been proposed in which a compressible fluid can flow between the fluid chambers through orifice means. According to such a fluid-filled vibration isolating support, when vibration is input in the opposite direction of the fluid chambers, as the volume of each fluid chamber changes, vibration is transmitted from one fluid chamber to the other fluid chamber through the orifice means. An incompressible fluid is allowed to flow through the orifice means, and a good vibration damping effect is obtained based on the flow resistance of the incompressible fluid when passing through the orifice means. Furthermore, in the radial direction perpendicular to the direction in which the fluid chambers face each other, relatively stiff spring characteristics can be obtained based on the compressive deformation action of the elastic member.

(Problem) However, in such a fluid-filled vibration damping support, as described above, while maintaining relatively stiff spring characteristics in one radial direction, Although a good vibration damping effect can be obtained in the opposite direction of the fluid chamber, it is difficult to say that a sufficient vibration damping effect can be obtained in the direction opposite to the fluid chamber. The incompressible fluid sealed in each fluid chamber follows the vibration input and flows relatively well when the input vibration is of low frequency (generally large amplitude), so in this case, the incompressible fluid flows relatively well. Although the member is allowed to deform relatively well, if the input vibration is of high frequency (generally small amplitude), it becomes difficult for the incompressible fluid to follow the vibration force and flow. The incompressible fluid acts as a rigid body in response to input vibrations, and the elastic deformation of the elastic member tends to be inhibited by the incompressible fluid becoming rigid. And therefore,
There was a problem in that the vibration isolation effect based on the elastic deformation of the elastic member could not be expected to be sufficient against high frequency (small amplitude) vibration human force.

(Solution Means) Against this background, the present invention provides a spring constant that is hard in one direction in the radial direction,
A cylindrical type that can effectively obtain both a good vibration damping effect and a good vibration and isolation effect based on the flow resistance of an incompressible fluid and the elastic deformation of an elastic member in the radial direction perpendicular to the above. The purpose of this work is to provide a fluid-filled vibration isolating support body, and its main points are (a) an inner cylindrical metal fitting, and (b) a predetermined distance outside the inner cylindrical metal fitting. and (c) located between the outer cylinder metal fitting and the inner cylinder metal fitting and spaced apart from each other by a predetermined distance from the outer cylinder metal fitting and the inner cylinder metal fitting. (d) a first elastic member interposed between the intermediate metal fitting and the inner cylindrical metal fitting to connect the metal fittings at positions symmetrical about the axis; ) a pair of spaces extending in the axial direction and positioned between the intermediate metal fitting and the inner cylinder metal fitting so as to sandwich the inner cylinder metal fitting in the radial direction; (g) a cylindrical second elastic member interposed between the cylindrical metal fitting and having a pair of pocket portions located at portions corresponding to the pair of voids and opening on the outer circumferential surface; A pair of pockets formed in the second elastic member have their openings fluid-tightly closed by the outer cylindrical metal fitting, and a predetermined non-compressible fluid is respectively enclosed in a pair of fluid chambers. and (h) orifice means for interconnecting the pair of fluid chambers and allowing the incompressible fluid sealed in the fluid chambers to mutually flow between the fluid chambers. This is because it is configured like this.

(Function/Effect) In such a fluid-filled vibration damping support, there are elastic members on both sides of the first elastic member interposed between the inner cylindrical metal fitting and the intermediate metal fitting, so as to face each other with the inner cylindrical metal fitting in between. , since a pair of cavities are formed, in the radial direction in which these cavities face each other, the inner cylindrical metal fitting moves relative to the intermediate metal fitting due to the shearing deformation action of the first elastic member. Therefore, while the relative movement between the inner cylindrical metal fitting and the intermediate metal fitting is allowed, a soft spring characteristic can be obtained in the opposing direction of the space. In other words, if the vibration input between the inner cylinder metal fitting and the outer cylinder metal fitting in the opposite direction of the spaces between them is small in amplitude, it is effectively absorbed by the shear deformation action of the first elastic member. Therefore, it is possible to obtain a good vibration isolation effect against small amplitude vibration (high frequency) in that direction.

On the other hand, when the amplitude (low frequency) of the vibration input in the opposing directions of the spaces between the inner and outer metal fittings reaches a certain level, the inner metal fitting comes into contact (directly) with the intermediate metal fitting. The second elastic member interposed between the intermediate metal fitting and the outer cylinder metal fitting is elastically deformed. Since a pair of fluid chambers are formed in opposite directions and communicated by orifice means, one fluid chamber contracts according to the elastic deformation of the second elastic member, and the other fluid chamber expands and contracts. The incompressible fluid sealed in the fluid chambers is caused to flow from the side fluid chambers to the expanding side fluid chambers through the orifice means. That is, in this case, a good vibration damping effect can be effectively obtained based on the flow resistance when the incompressible fluid passes through the orifice means.

As described above, according to the fluid-filled vibration isolating support according to the present invention, the cavity (fluid chamber) has both a good vibration isolation effect and a good vibration damping effect against the input vibration in the opposing radial direction. Moreover, in the radial direction perpendicular to the opposite direction of the cavity (the opposite direction of the fluid chamber),
Since the first and second elastic members are interposed in a solid state between the inner cylindrical metal fitting and the intermediate metal fitting, and between the intermediate metal fitting and the outer cylindrical metal fitting, the compression deformation action of these elastic members causes Therefore, relatively high spring characteristics can be maintained well.

(Example) Hereinafter, in order to clarify the present invention more specifically, one example thereof will be described in detail based on the drawings.

First, FIGS. 1 and 2 show an example of a roll stopper that is a cylindrical engine mount according to the present invention. As is clear from these figures, the roll stopper of this embodiment is A cylindrical inner metal fitting 10 that is inserted and attached to a predetermined shaft member, and a cylindrical outer metal fitting 10 that is inserted and attached to a predetermined cylindrical member that is arranged concentrically at a predetermined distance on the outside thereof. It is located between the cylindrical metal fitting 12, the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12, and is arranged at a predetermined distance from each of the two cylindrical metal fittings 10 and 12, and has a rectangular cross section. A square cylindrical intermediate fitting 14 and a first rubber elastic body 16 interposed between the inner cylindrical fitting 10 and the intermediate fitting 14 to elastically connect them.
and a cylindrical second rubber elastic body 1 interposed between the intermediate metal fitting 14 and the outer cylindrical metal fitting 12 to elastically connect them.
8, and a pair of fluid chambers 20.2 formed in the second rubber elastic body 18 so as to face each other with the inner cylinder fitting 10 interposed therebetween.
0, predetermined incompressible fluids 22 sealed in the fluid chambers 20 and 20, and the second rubber elastic body 18.
A cylindrical orifice member 26 is formed in cooperation with the outer cylindrical fitting 12 to form a circumferential spiral orifice 24 that allows the fluid chambers 20 to communicate with each other. It is configured to include a pair of semi-cylindrical orifice members 28 and 28.

In addition, examples of the incompressible fluid 22 include water, polyalkylene glycol, and silicone oil.

A low molecular weight polymer or the like will be used.

More specifically, the first rubber elastic body 6 and the second rubber elastic body 18 are integrally formed by vulcanization molding, as shown in FIGS. 3 and 4. The first rubber elastic body 16 is connected to the inner cylinder fitting 10 and the intermediate fitting 14, and the second rubber elastic body 18 is connected to the intermediate fitting 1.
4, they are each integrally fixed by vulcanization adhesive.

Here, the first rubber elastic body 16 connecting the inner cylinder fitting 1o and the intermediate fitting 14 is an inner surface on the short side of the rectangular cross section of the intermediate fitting 14, as shown in FIGS. 3 and 4. and the outer surface of the corresponding inner cylinder fitting IO are provided symmetrically about the axis. Furthermore, a pair of spaces 30 and 30 are formed on both sides of the first rubber elastic body 16 along the inner surface of the long side of the rectangular cross section of the intermediate fitting 14, so that the outer surface of the inner cylinder fitting 10 is These openings 30.degree. 30 are separated from each other and are faced to the inner surface of the long side of the intermediate fitting 14, respectively. As a result, the inner cylindrical metal fitting 10 does not directly interfere with (contact) the intermediate metal fitting 14, and the spaces 30 and 30 are opened based on the elastic deformation of the rubber elastic body 16 in the shear direction. They are designed to be able to move relative to each other by a minute distance in opposite directions. Also, the empty space 30.3
In the radial direction perpendicular to the facing direction of 0, the inner cylinder fitting 1
0 can move relative to the intermediate fitting 14 based on the elastic deformation of the rubber elastic body 16 in the compression direction.

The outer surface of the inner cylindrical fitting 1o facing the cavity 30°30 is covered with a rubber layer 32, 32 of a predetermined thickness formed integrally with the rubber elastic body 16, as will be described later.
When the inner cylindrical fitting 1o moves relative to the opposite direction of the space 30, 30 by a certain distance or more, the inner cylindrical fitting 10 moves to the intermediate fitting '14.
The rubber layer 32 is brought into contact with the rubber layer 32.

Further, as shown in FIGS. 3 and 4, the second rubber elastic body 18 includes the first rubber elastic body 16.
A pair of pocket portions 34 of a predetermined depth are opened on the outer circumferential surface of the cavity 30.30 formed in the opposite directions.
．． 34 are formed, and these pocket portions 34
．． An annular groove 36 having a width equal to the opening width (opening length in the axial direction) of the pocket portions 34 and 34 is formed so that the openings of the pocket portions 34 and 34 communicate with each other in the circumferential direction.

As shown in FIG. 2, a pair of orifice members 28 and 28 are attached to the annular groove 36 formed on the outer periphery, as will be described later.
A cylindrical orifice member 26 is formed. Furthermore, the opening of the pocket portion 34.34 is closed by forming the orifice member 26 by attaching these orifice member half-holes 28.28, so that the fluid chamber 20.20 is formed. It has become. Note that, as shown in FIGS. 3 and 4, an annular groove 3 is provided in the outer peripheral portion of the second rubber elastic body 18.
A pair of outer sleeves 37, 37 are located on both sides of 6 and are fixed together by vulcanization adhesive.

On the other hand, the pair of orifice member half holes 28 and 28 forming the orifice member 26 each have three circumferential stripes i! on their outer peripheral surfaces, as shown in FIGS. 1i
38a, 38b, and 38c. Of the three circumferential grooves formed on the outer periphery of these orifice member half-holes 28, two grooves including the one formed in the center (3
8a and 38b) are formed such that both ends thereof are opened in the circumferential end surface of the orifice member half-hole 28, and the remaining one (38c) is formed such that one end thereof is opened in the circumferential direction end surface of the orifice member half-hole 28. At the same time, the other end is formed as a dead-end groove closed at the circumferential center of the orifice member half-hole 28, and is opened to the inner surface of the orifice member half-hole 28 through a through hole 40 formed at the dead-end end. In this embodiment, such an orifice member half-break 28, 28 is located in the annular groove 36 formed on the outer periphery of the second rubber elastic body 18 as shown in FIGS. 1 and 2. As described above, the second rubber elastic body 18 is mounted in a state in which the phases match with the pocket parts 34 and 34, respectively, and in a state in which their circumferential end surfaces are in contact with each other.
A cylindrical orifice member 26 is formed that closes the opening of each pocket 34, 34 formed in the cylindrical portion 34, forming a pair of fluid chambers 20.20. At the same time as the orifice member 26 is formed, three stripes a38a, 38b are formed on the outer circumference of the orifice member 26, as shown in FIG. , 38c are connected to the fluid chamber 2 at the through holes 40, 40 located at both ends.
0.20, a single spiral groove 42 is formed which extends two and a half times around the second rubber elastic body 18 and communicates with one side of the second rubber elastic body 18.

Note that the outer diameter of the orifice member 26 formed by butting the orifice member halves 28 is smaller than that of the previous second rubber elastic body 18, as shown in FIGS. 3 and 4. , has been made slightly smaller.

Further, as shown in FIG. 9, the outer cylindrical metal fitting 12 is integrally provided with a rubber layer 44 on its inner surface. Then, the orifice member 26 is fitted onto the outer circumferential surface of the second rubber elastic body 18 and subjected to an eight-way drawing process, and then roll caulking process is performed on both ends of the orifice member 26, as shown in FIG. As shown in FIG. 2, the orifice member 26 is integrally assembled with the second rubber elastic body 18, and the spiral groove 42 formed on the outer peripheral surface of the orifice member 26 is fluid-tightly closed. The spiral orifice 24 is formed therein.

Note that the rubber layer 44 formed on the inner surface of the outer cylinder fitting 12 is
An outer sleeve 37.37 is fixed to the outer periphery of the second rubber elastic body 18 by drawing the outer cylinder fitting 12 in all directions.
It is designed to be squeezed between the This ensures fluid tightness of each fluid chamber 20.20 with respect to the external space.

Further, as is clear from FIG. 1, the outer diameter of the second rubber elastic body 18 is matched with that of the orifice member 26 by drawing the outer cylinder fitting 12 in all directions.

In this embodiment, the operation of attaching the orifice member 26 to the second rubber elastic body 18 and the operation of attaching the outer cylinder fitting 12 to the second rubber elastic body 18 to which the orifice member 26 is attached are performed in a predetermined manner. Incompressible fluid 2
2, the fluid chamber 20.
The incompressible fluid 22 is sealed into the fluid chamber 20.20 and the helical orifice 24 simultaneously with the formation of the fluid chamber 20.20 and the helical orifice 24, respectively.

This results in a roll stopper as shown in FIGS. 1 and 2.

In such a roll stopper, a pair of void spaces 30 and 30 are formed between the inner cylindrical metal fitting IO and the intermediate metal fitting 14 so as to face each other with the inner cylindrical metal fitting 10 in between, and the inner surface of each corresponding intermediate metal fitting 14 is formed. (on the long side) and the outer surface of the inner cylindrical fitting 10, these spaces 30
．． In the radial direction where the inner cylinder fittings 30 face each other, the inner cylinder fitting IO moves relative to the intermediate fitting 14 based on the shearing deformation action of the first rubber elastic body 16. Therefore, while the relative movement between the inner cylindrical fitting 10 and the intermediate fitting 14 is allowed, soft spring characteristics based on the shearing deformation action of the first rubber elastic body 16 are obtained in the opposing directions of the spaces 30 and 30. It is possible to obtain a good vibration isolation effect against small-amplitude (high-frequency) vibrations that are manually applied between the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12 in opposite directions of the spaces 30 and 30. can.

On the other hand, when the amplitude of the vibration (low frequency) applied manually between the inner tube fitting 10 and the outer tube fitting 12 in the opposite directions of the spaces 30 and 30 exceeds a certain level, the inner tube fitting 10 will cause the outer surface of the inner tube fitting 10 to In this case, the second rubber elastic body contacts (directly interferes with) the intermediate fitting 14 through the covering rubber layer 32 and moves the intermediate fitting 14 relative to the outer cylindrical fitting 12. 18 will be elastically deformed in a direction opposite the fluid chambers 20, 20. That is, according to the elastic deformation of the rubber elastic body 18, one fluid chamber 20 is contracted and the other fluid chamber 20 is expanded, and the fluid chamber 20 spirals from the contracted fluid chamber 20 to the expanding fluid chamber 20. Orifice 2
4, the incompressible fluid 22 is caused to flow through the helical orifice 24, and therefore a good vibration damping effect can be obtained based on the flow resistance when the incompressible fluid 22 passes through the helical orifice 24.

In addition, in this embodiment, in the radial direction perpendicular to the direction in which the fluid chambers 20.20 face each other (the direction in which the spaces 30.30 face each other), as is clear from FIG. 1 and FIG. 10 and the intermediate fitting 14, and between the intermediate fitting 14 and the outer cylinder fitting 12, a rubber elastic body t6. Since ta is interposed in a solid state, relatively hard spring characteristics can be obtained in the radial direction based on the compressive deformation action of the rubber elastic bodies 16 and 18.

As described above, the roll stopper of this embodiment maintains a relatively hard spring characteristic in one radial direction (the direction perpendicular to the opposing direction of the spaces 30 and 30), while maintaining the spring characteristic in the radial direction perpendicular thereto ( It is possible to effectively obtain both a good vibration isolation effect and a good vibration damping effect in the space 30° (opposite direction of 30 degrees), and the vibration isolation effect is particularly improved compared to the conventional fluid-filled type. This resulted in a significant improvement.

Further, according to this embodiment, as described above, the inner cylinder fitting 10
A rubber layer 32 of a predetermined thickness is provided on the outer surface that comes into contact with the intermediate metal fitting 14, and the inner cylinder metal fitting 0 is provided with a rubber layer 32 having a predetermined thickness.
Since the inner cylindrical metal fitting 10 and the intermediate metal fitting 14 are brought into contact with the intermediate metal fitting 14 via the These metal fittings 1o due to the impact caused by contact,
There is also the advantage that damage to 14 is well prevented. In addition, the rubber layer for absorbing such impact can be provided on the intermediate metal fitting 14 side, or can be provided on both of them.

Although one embodiment of the present invention has been described above, this is a literal illustration, and it goes without saying that the present invention should not be interpreted as being limited to this specific example.

For example, in the above embodiment, the intermediate metal fitting 14 is described as having a rectangular tube shape with a rectangular cross section, but the cross-sectional shape of the intermediate metal fitting 14 is not limited to this, and may be other shapes such as an elliptical shape. It is also possible to adopt the shape of

Further, in the embodiment described above, the orifice means for communicating the fluid chambers 20, 20 was a spiral orifice 24 that made two and a half turns around the outer circumference of the second rubber elastic body 18, but the length and cross-sectional area of the orifice means Alternatively, the cross-sectional shape etc. can be changed as appropriate depending on the purpose, and the forming position and forming method etc. can also be changed, such as forming it in a state where it penetrates the second rubber elastic body 18 or the intermediate metal fitting 14. It can be formed in various forms depending on the situation.

Further, in the above embodiment, an example was described in which the present invention was applied to a roll stopper which is a cylindrical type engine mount, but the present invention is not limited to this, and the present invention is not limited to this. It can also be applied to swing supports, and is not limited to bush type types in which the outer cylindrical fitting is inserted into a predetermined cylindrical member. It is also possible to apply the present invention to a type of vibration-proof support that is attached to a predetermined support member via a mounting bracket.

Although not listed here, it goes without saying that the present invention can be practiced with various changes, modifications, and improvements within the scope of the spirit thereof.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view showing one embodiment of the present invention (I in FIG. 2).
-1 cross-sectional view), and FIG. 2 is a cross-sectional view (nn-1 cross-sectional view of FIG. 1). FIG. 3 shows the inner cylindrical fitting, the first rubber elastic body 16, and the intermediate fitting 14 of the embodiment shown in FIG.
and a second rubber elastic weight 8 (a cross-sectional view taken along line lll-l11 in FIG. 4);
The figure is also a cross-sectional view (IV-IV sectional view in FIG. 3). 5 is a front view showing a half-closed orifice member of the embodiment shown in FIG. 1, FIG. 6 is a right side view thereof, and FIG. FIG. 8 is an explanatory diagram showing the orifice member of the embodiment shown in FIG. 1 taken out. FIG. 9 is a longitudinal sectional view showing the outer cylindrical fitting of the embodiment shown in FIG. 1. 10: Inner tube fitting 12: Outer tube fitting 14: Intermediate fitting 16: First rubber elastic body 18: Second rubber elastic body 20: Fluid chamber 22: Incompressible fluid 24: Spiral orifice 26: Orifice member 28 Niorifice Parts half off

Claims (1)

[Scope of Claims] An inner cylindrical metal fitting, an outer cylindrical metal fitting arranged outside the inner cylindrical metal fitting at a predetermined distance, and located between the outer cylindrical metal fitting and the inner cylindrical metal fitting, A cylindrical intermediate metal fitting is arranged at a predetermined distance from the outer cylindrical metal fitting and the inner cylindrical metal fitting, and a cylindrical intermediate metal fitting is interposed between the intermediate metal fitting and the inner cylindrical metal fitting to center the metal fittings on the axis. a first elastic member connected at a symmetrical position to the intermediate metal fitting and the inner cylinder metal fitting; a pair of elastic members extending in the axial direction and positioned between the intermediate metal fitting and the inner cylinder metal fitting so as to sandwich the inner cylinder metal fitting in the radial direction; a cylindrical second tube having a hollow space, and a pair of pockets interposed between the intermediate metal fitting and the outer cylindrical metal fitting and opening to the outer circumferential surface and located at portions corresponding to the pair of hollow spaces; A second elastic member and a pair of pocket portions formed in the second elastic member are respectively enclosed in a pair of fluid chambers formed by fluid-tightly closing the openings of the outer cylinder fittings. an orifice means for interconnecting a predetermined incompressible fluid and the pair of fluid chambers, and for allowing the incompressible fluid sealed in the fluid chambers to mutually flow between the fluid chambers; A fluid-filled anti-vibration support comprising: