JP2004324654A - Vibrationproof device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibrationproof device capable of generating a specified natural frequency, exerting a damping effect, and of being embodied at low cost with good durability. <P>SOLUTION: The vibrationproof device is equipped with a rubber-like elastic member 3 in the shape of hollow cylinder installed between the first plate 1 attached to the vibration source side and the second plate 2 positioned on the vibrated side, a supporting spring 4 installed in the hollow 3A of the elastic member 3 between the first 1 and second plates 2, and an intermediate restraining member 5 installed in the middle part of the cylindrical outside surface of the elastic member 3 so that the outside diameter of the place does not enlarge. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an anti-vibration device that supports a vibration source such as an engine, a motor, a compressor, or another machine that generates vibration during operation to achieve vibration isolation.
[0002]
[Prior art]
As an apparatus for supporting a machine that generates vibrations for general industry and performing vibration isolation, an apparatus using a rubber vibration-proof rubber, a metal coil spring, and a damper is known (for example, Patent Document 1). reference).
[0003]
[Patent Document 1]
JP-A-2002-295587
In the case of a machine that generates vibration at a low frequency such that vibration isolation is not established unless the natural frequency of the support system is set to 10 Hz or less, the vibration-proof rubber requires shear support or inclined support, There was a problem. In the case of anti-vibration rubber, it is generally desirable to use it on the compression side if the strength and settling at the time of load support are taken into account. The natural frequency of the system becomes 10 Hz or more. As a result, the input frequency range in which vibration can be prevented is 14 Hz (based on the vibration transmissibility curve in the vibration control theory, the forced frequency of 1.4 times or more the natural frequency of the support system). Otherwise, the vibration transmissibility does not fall below 1). On the other hand, in an engine of three cylinders or less rotating at 800 rpm or less (rpm) or the like, the generated forced frequency is 12 Hz or less, and the natural frequency of the support system necessary for vibration isolation support is about 8 Hz or less. (The same applies if the forced frequency generated is 12 Hz or less even if the engine is not used). In this case, depending on the load to be supported, the spring needs to be very soft, and it is impossible to construct it with a normal compression type due to its strength, and a shearing type or an inclined type is required. The type cannot solve the sagging problem. In the case of a metal coil spring, it is possible to obtain a natural frequency of 10 Hz or less, but there is a problem of surging because there is no damping action. To prevent this surging, an expensive damper had to be provided. Furthermore, even when an air spring is used, it is possible to obtain a natural frequency of 10 Hz or less, there is no sagging, and there is no fear of surging. However, additional equipment such as an air source and piping is required. It was difficult to install easily on industrial machines.
[0005]
[Problems to be solved by the invention]
In the conventional technology, as described above, there is no vibration isolation device that can be easily mounted on general industrial machines, is inexpensive and durable, can obtain a predetermined natural frequency, and has a damping action. Was.
[0006]
Accordingly, an object of the present invention is to provide an inexpensive and highly durable anti-vibration device that has a predetermined natural frequency and also has a damping action.
[0007]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a hollow cylindrical rubber-like elastic member between a first plate attached to a vibration source side and a second plate located on a vibration-receiving side. A support spring is provided between the first and second plates in the hollow interior of the member, and an intermediate restraining member is provided at an intermediate location on the cylindrical outer peripheral surface of the rubber-like elastic member so that the outer diameter of the location does not increase. It is.
[0008]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
[0009]
In the embodiment shown in FIGS. 1 and 2, a hollow cylindrical rubber-like elastic member 3 is provided between a first plate 1 attached to the vibration source side and a second plate 2 located on the vibration-receiving side. A support spring 4 is provided between the first and second plates 1 and 2 in a hollow interior 3A of the elastic member 3. An intermediate restraining member 5 is provided at an intermediate location on the cylindrical outer surface of the rubber-like elastic member 3 so that the outer diameter of the location does not increase. A frame plate 6 is provided at the end of the rubber-like elastic member 3 on the side to be oscillated, and the oscillated side is connected to the frame plate 6 directly or via another member. In this embodiment, the second plate 2 is fixed to the frame plate 6, and this second plate 2 is connected to the side to be vibrated.
[0010]
The rubber-like elastic member 3 is made of natural rubber, synthetic rubber or the like, and has an internal damping effect against vibration. In the case of rubber, the first plate 1 and the frame plate 6 can be set in a vulcanization mold when vulcanizing the rubber, and these can be integrated with the rubber by vulcanization. After that, the second plate 2 is attached to the frame plate 6 on the lower end side of the rubber-like elastic member 3. Before attaching the second plate 2, the support spring 4 is set in the hollow interior 3 </ b> A of the rubber-like elastic member 3. The rubber-like elastic member 3 has a flange 3B projecting radially outward at an intermediate portion thereof, and the intermediate restraining member 5 is partially embedded in the flange 3B. Constrictions 3C and 3D constricted toward the center are formed above and below the flange 3B. Although only one flange-shaped portion 3B is formed in this embodiment, two or more flange-shaped portions may be formed. In addition, the shape of the rubber-like elastic member 3 is not limited to the illustrated one, but may be a bellows-like shape, or a shape in which the middle portion is inwardly recessed and the constricted portion is outwardly opposed to the illustrated one. It may have a bulging shape.
[0011]
As the support spring 4 provided in the hollow interior 3A of the rubber-like elastic member 3 and present between the first and second plates 1 and 2, it is preferable to use a coil spring as a metal spring. Depending on the natural frequency to be obtained, a resin spring may be used. The support spring 4 is mounted between a protruding portion 1A formed on the first plate 1 and a dish portion 2A formed on the second plate 2. An orifice 7 is formed at the center of the plate portion 2A of the second plate 2 so as to communicate air between the hollow interior 3A and the outside. In the illustrated embodiment, each of the first and second plates 1 and 2 is an iron plate having a thickness of about 1 mm, the frame plate 6 is made of the same iron plate, and the orifice 7 has a diameter of 1 mm.
[0012]
In the embodiment shown in FIGS. 1 and 2, the intermediate restraining member 5 is used. However, if the intermediate restraining member 5 is not used, the entire rubber-like elastic member 3 is formed of rubber. In this case, when the internal air is discharged by compression, escape deformation occurs in a direction in which the outer diameter of the intermediate portion increases. If such escape deformation occurs, sufficient attenuation cannot be obtained for the design value. On the other hand, in the above-described embodiment, when the intermediate restraining member 5 is provided, it is possible to prevent the outer diameter of the intermediate portion from increasing. In this embodiment, the rubber-like elastic member 3 can be effectively deformed in order to obtain an air damping effect, not to increase the outer diameter. As shown in the illustrated embodiment, the one provided with the intermediate restraint member 5 is denoted by reference numeral X, and the one not provided with the intermediate restraint member 5 is denoted by reference numeral Y. The results of the respective attenuation comparisons are shown in the graph of FIG.
[0013]
In the embodiment described above, air is used as a fluid in the hollow interior 3A of the rubber-like elastic member 3 to communicate with the outside through the orifice 7 so as to enhance the damping effect. However, a liquid may be used. When a liquid is used, a closed chamber 40 is formed below the orifice 7. For example, as shown in FIG. 4, the lid member 8 and the rubber film 9 may be attached to the second plate 2 so that the liquid communicates between the room 40 and the hollow interior 3A via the orifice 7. it can. By circulating the fluid between the hollow interior 3A and the outside through such an orifice 7, a damping effect can be produced. Further, it is desirable to set the natural frequency to 10 Hz or less. Furthermore, it is desirable that the support spring 4 supports half or more of the load supported by the entire apparatus.
[0014]
The embodiment of the invention shown in FIGS. 5 to 7 shows a vibration isolator 30 for attenuating the vibration of the engine 21 of the compaction machine 20 used for the road leveling work. It is provided at a connection point between the operation handle 22 and the engine 21 of the ground compaction machine 20 for walking leveling work. The vibration isolator 30 includes a hollow cylindrical rubber-like elastic member 3 between a first plate 1 mounted on the engine 21 (vibration source) side and a second plate 2 positioned on the operation handle 22 (vibrated) side. Is provided at an intermediate location on the cylindrical outer peripheral surface of the rubber-like elastic member 3 so that the outer diameter of the location is not enlarged. is there.
[0015]
The vibration isolator 30 has a rigid cylindrical sleeve 31 having open ends at both ends between the first plate 1 and the second plate 2 at a center position in the hollow portion 3A of the rubber-like elastic body 3. In the above embodiment, the support spring 5 is provided, but in this embodiment, a sleeve 31 is provided instead of the support spring 5. A hole 1B is formed in the first plate 1 of the vibration isolator 30 at a position where the sleeve 31 is located, and a portion of the second plate 2 facing the hollow portion 3A is open. The length of the sleeve 31 does not protrude from the opening but fits in the hollow portion 3A. The first plate 1 is fastened and fixed to a side surface of the engine 21 with a bolt (not shown) that passes through the inside of the sleeve 31 from the hole 1B of the first plate 1. A mounting hole 4A is provided in the intermediate restraining member 4, and the vibration isolator 30 is mounted on the operation handle 22 through the mounting hole 4A.
[0016]
By attaching the first plate 1 to the engine 21 via bolts (not shown) and attaching the intermediate restraint member 4 to the operation handle 22, the displacement of the intermediate restraint member 4 is limited by the sleeve 31 while softly supporting the operation handle 22 by shearing. Therefore, a structure incorporating a stopper mechanism is possible. Further, by fixing the first plate 1 to the engine 21 via the sleeve 31, a structure in which the rubber-like elastic body 3 is subjected to a certain compression is expected to improve durability.
[0017]
As described in the previous embodiment, the rubber-like elastic body 3 is made of natural rubber, synthetic rubber or the like, and has an internal damping effect against vibration. In the case of rubber, when the rubber is vulcanized, the first plate 1 and the second plate 2 can be set in a vulcanization mold, and these and the rubber can be vulcanized and bonded to be integrated. The rubber-like elastic member 3 has a flange 3B projecting radially outward at an intermediate portion thereof, and the intermediate restraining member 5 is partially embedded in the flange 3B. Constrictions 3C and 3D constricted toward the center are formed above and below the flange 3B. Although only one flange-shaped portion 3B is formed in this embodiment, two or more flange-shaped portions may be formed. In addition, the shape of the rubber-like elastic member 3 is not limited to the illustrated one, but may be a bellows-like shape, or a shape in which the middle portion is inwardly recessed and the constricted portion is outwardly opposed to the illustrated one. It may have a bulging shape. Further, it is desirable to set the natural frequency to 10 Hz or less.
[0018]
In the embodiment shown in FIGS. 8 and 9, the first plate 1 attached to the vibration source side in the embodiment shown in FIG. 1 becomes the first plate 1 located on the vibration source side, and this first plate 1 is A rubber elastic member 3 having a hollow cylindrical shape is provided between the elastic member 3 and the second plate 2 located on the side, and a support spring 4 is provided between the first and second plates 1 and 2 in the hollow interior 3A of the rubber elastic member 3. Is provided. An intermediate restraining member 5 is provided at an intermediate location on the cylindrical outer surface of the rubber-like elastic member 3 so that the outer diameter of the location does not increase. A frame plate 6 is provided at the end of the rubber-like elastic member 3 on the side to be oscillated, and the oscillated side is connected to the frame plate 6 directly or via another member. In this embodiment, the second plate 2 is fixed to the frame plate 6, and this second plate 2 is connected to the side to be vibrated. A rubber-like elastic plate 10 is laminated on the first plate 1, and a third plate 11 is provided on the rubber-like elastic plate 10 so as to be attached to the vibration source side. The rubber-like elastic plate 10 is made of natural rubber, synthetic rubber or the like, and has an internal damping effect against vibration.
[0019]
Also in this embodiment, the rubber-like elastic member 3 has a flange-shaped portion 3B projecting radially outward at an intermediate portion thereof, and the intermediate restraining member 5 is provided in the flange-shaped portion 3B by being partially embedded. It is. Constrictions 3C and 3D constricted toward the center are formed above and below the flange 3B. Although only one flange-shaped portion 3B is formed in this embodiment, two or more flange-shaped portions may be formed. In addition, the shape of the rubber-like elastic member 3 is not limited to the illustrated one, but may be a bellows-like shape, or a shape in which the middle portion is inwardly recessed and the constricted portion is outwardly opposed to the illustrated one. It may have a bulging shape. Further, as the support spring 4, the same one as described above can be used.
[0020]
In the embodiment shown in FIGS. 10 and 11, the rubber-like elastic plates 10 are stacked in three layers, and a metal plate 12 is interposed between each layer. With the multilayer structure, a further low spring (natural frequency of 10 Hz or less) can be achieved.
[0021]
In the embodiment shown in FIGS. 12 and 3, the stopper portion 13 is provided on the third plate 11 as a displacement control for a lateral movement when the third plate 11 is attached to a vibration source.
[0022]
In each of the embodiments shown in FIGS. 8 to 13, the vertical spring characteristics at the rubber-like elastic plate 10 are sufficiently harder than the support spring 4 (for example, a coil spring), so that the vertical spring characteristics are almost the same as the whole. Has no effect. In the embodiment shown in FIGS. 1 to 7 using only a coil spring as the support spring 4, the rigidity in the lateral direction changes according to the amount of bending of the coil, and the horizontal spring increases when the amount of bending increases. was there. Therefore, it is possible to secure a low spring constant by the shear spring of the rubber-like elastic plate 10 in the horizontal direction, and to lower the natural frequency of the support system not only in the vertical direction but also in the horizontal direction. The embodiment shown in FIG.
[0023]
The graph shown in FIG. 14 is a graph comparing the amount of vertical compression and the rigidity ratio of the vibration isolator of the embodiment shown in FIG. 8 with that used in FIG. 3 as a conventional example. In the embodiment of the present invention, the support spring 4 has a free length of 50 mm, an outer diameter of 28 mm, and a compression spring Kp of 31 N / mm.
[0024]
【The invention's effect】
As described above, according to the present invention, a hollow cylindrical rubber-like elastic member is provided between the first plate attached to the vibration source side and the second plate located on the vibration-receiving side. A support spring is provided between the first and second plates in the hollow interior of the member, and an intermediate restraining member is provided at an intermediate location on the cylindrical outer peripheral surface of the rubber-like elastic member so that the outer diameter of the location does not increase. There is no settling as in the case of the rubber-like elastic member alone, and no surging as in the case of only the support springs, a predetermined natural frequency is obtained, and a damping action is provided. It will be more durable. In particular, since the intermediate restraining member is provided, no escape deformation occurs in the direction in which the outer diameter of the rubber-like elastic member increases, and sufficient attenuation with respect to the design value can be obtained. In addition, when the natural frequency is set to 10 Hz or less, it is effective for vibration isolation of a machine that generates low-frequency vibration, is inexpensive, and can be easily installed on a vibration source. Further, in the present invention configured as described above, there is no sliding portion in the portion in contact with the external environment, and maintenance such as dustproofing and lubrication is not required.
[0025]
Further, a hollow cylindrical rubber-like elastic member is provided between a first plate attached to the vibration source side and a second plate located on the vibration-receiving side, and the first and second rubber-like elastic members are provided inside the hollow of the rubber-like elastic member. A structure in which a rigid sleeve is provided between two plates and an intermediate restraining member is provided at an intermediate location on the cylindrical outer peripheral surface of the rubber-like elastic member so that the outer diameter of the location is not enlarged, the stopper mechanism is built-in. And durability is also improved.
[0026]
Furthermore, a hollow cylindrical rubber-like elastic member is provided between the first plate located on the vibration source side and the second plate located on the vibrated side, and the first and second rubber-like elastic members are provided inside the hollow of the rubber-like elastic member. A support spring is provided between the two plates, an intermediate restraining member is provided at an intermediate location on the cylindrical outer peripheral surface of the rubber-like elastic member so that the outer diameter of the location does not increase, and a rubber-like elastic plate is provided on the first plate. In the case where the third plate is provided on the rubber-like elastic plate and attached to the vibration source side, the lateral rigidity changes according to the bending amount of the support spring, and when the bending amount increases, the horizontal rigidity changes. The disadvantage that the spring is high can be solved, and a low spring constant can be ensured even in the lateral direction.
[Brief description of the drawings]
FIG. 1 is an AOB cross-sectional view of FIG. 2 showing a preferred embodiment of the present invention.
FIG. 2 is a plan view of FIG. 1;
FIG. 3 is a graph comparing the damping effect of a device provided with an intermediate restraining member and a device not provided.
FIG. 4 is a cross-sectional view showing another embodiment.
FIG. 5 is a cross-sectional view showing another embodiment.
FIG. 6 is a bottom view of FIG. 5;
FIG. 7 is a front view of the compaction machine.
FIG. 8 is a sectional view of the COD of FIG. 9 showing still another embodiment.
FIG. 9 is a plan view of FIG. 8;
FIG. 10 is a cross-sectional view of the EOF of FIG. 11 in which the rubber-like elastic plate in the embodiment of FIG. 8 has a plurality of layers.
FIG. 11 is a plan view of FIG. 10;
FIG. 12 is a GOH sectional view of FIG. 13 showing an example in which a stopper portion is provided on a third plate.
FIG. 13 is a plan view of FIG. 12;
FIG. 14 is a graph showing a vertical compression amount and a rigidity ratio of the embodiment shown in FIG. 8 and a conventional product.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 1st plate 2 2nd plate 3 Rubber-like elastic member 3A Hollow interior 4 Support spring 5 Intermediate restraint member 10 Rubber-like elastic plate 11 Third plate 30 Vibration isolator 31 Sleeve

Claims (16)

A hollow cylindrical rubber-like elastic member is provided between a first plate attached to the vibration source side and a second plate located on the vibration-receiving side,
A support spring is provided between the first and second plates inside the hollow of the rubber-like elastic member,
An anti-vibration device characterized in that an intermediate restraining member is provided at an intermediate location on the cylindrical outer peripheral surface of the rubber-like elastic member so that the outer diameter of the location does not increase. A hollow cylindrical rubber-like elastic member is provided between a first plate located on the vibration source side and a second plate located on the vibrated side,
A support spring is provided between the first and second plates inside the hollow of the rubber-like elastic member,
An intermediate restraining member is provided at an intermediate location on the cylindrical outer peripheral surface of the rubber-like elastic member so that the outer diameter of the location does not increase,
Laminating a rubber-like elastic plate on the first plate,
A vibration isolator characterized in that a third plate is provided on the rubber-like elastic plate and attached to the vibration source side. The vibration isolator according to claim 1, wherein the rubber-like elastic member is made of a rubber material having a hollow shape. The anti-vibration device according to any one of claims 1 to 3, wherein the support spring is a metal spring. The vibration isolator according to any one of claims 1 to 4, wherein the support spring is a coil spring. The vibration isolator according to any one of claims 1 to 5, wherein the natural frequency is set to 10 Hz or less. The vibration isolator according to any one of claims 1 to 6, wherein the support spring supports half or more of a load supported by the entire apparatus. The vibration isolator according to any one of claims 1 to 7, wherein an orifice is formed in the second plate. The vibration isolator according to claim 2, wherein a plurality of the rubber-like elastic plates are provided via a metal plate. 6. A flange-like portion projecting radially outward at least at an intermediate portion of the rubber-like elastic member, and an intermediate restraining member is partially embedded in the flange-like portion. Item 2. An anti-vibration device according to item 1. The vibration isolator according to claim 10, wherein a plurality of the flange portions are formed. A hollow cylindrical rubber-like elastic member is provided between a first plate attached to the vibration source side and a second plate located on the vibration-receiving side,
A rigid sleeve is provided between the first and second plates inside the hollow of the rubber-like elastic member,
An anti-vibration device characterized in that an intermediate restraining member is provided at an intermediate location on the cylindrical outer peripheral surface of the rubber-like elastic member so that the outer diameter of the location does not increase. The vibration isolator according to claim 12, wherein the rubber-like elastic member is made of a rubber material having a hollow shape. 14. The rubber-like elastic member according to claim 12, wherein a flange-like portion projecting radially outward is formed at least at an intermediate position, and an intermediate restraining member is partially embedded in the flange-like portion. Anti-vibration device. The vibration isolator according to claim 14, wherein a plurality of the flange portions are formed. The vibration isolator according to any one of claims 12 to 15, wherein the natural frequency is set to 10 Hz or less.

Images