JP2000266118A - Mount - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a vibration control property by lowering a dynamic spring constant of a mount and to improve a settling property and durability of an elastomer elastic body. SOLUTION: An elastic body 11 and a connecting disc spring 15 are serially arranged against the working direction of a load. As the connecting disc spring 15 has characteristics that its spring constant becomes higher in a low load region and lower in a high load region, it is possible to restrain compression displacement of the elastic body 11 by an allotted load from the supported side small and to make a dynamic spring constant against vibration input low. It is possible to maintain a vibration control property by the elastic body 11 by preventing generation of hammering sound of the connecting disc spring 15 and a spring bearing flange 13 or a center bolt 14 at the time of inputting vibration displacement in the tensile direction by the spring bearing flange 13 in the extending direction of the connecting disc spring 15 and a set load adjusting screw part 17 to limit relative displacement of the center bolt 14.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an anti-vibration technique and, more particularly, to a mount for supporting an apparatus by using an elastic body made of an elastomer and a spring.

[0002]

2. Description of the Related Art As a typical prior art of this type of mount, for example, as shown in FIG. 7, an elastic body 101 made of an elastomer, and a metal plate 102 bonded to both upper and lower end surfaces of the elastic body 101 are used. , 103 and mounting bolts 104 protruding from the upper metal plate 103. That is, in this mount, the lower metal plate 102 is mounted on the upper surface of a frame or the like on the support side 1 with a plurality of bolts 105 on the outer peripheral portion, and the upper metal plate 103 is mounted on the supported side 2 with the mounting bolts 104.
By being attached to the lower end of a device (e.g., a device that generates vibration by driving), the supported side 2 floats above the supporting side 1 via the elastic body 101 and is supported by the elasticity of the elastic body 101. It absorbs and attenuates the transmitted vibration from the side 2.

[0003]

According to the conventional mount described above, a hard elastomer (rubber) is used for the elastic body 101 as shown by a characteristic line A having a large inclination in the load / displacement characteristic diagram of FIG. As a result, when the static spring constant is increased, the shared load W given by the weight of the supported side 2 is increased.
o, the amount of compressive displacement δ ₁ becomes small,
The set (compression set) can be suppressed and the durability can be improved. However, in this case, the dynamic spring constant at the time of vibration input is also increased, so that the vibration isolation is deteriorated. vice versa,
As shown by the characteristic line B having a small slope in the characteristic diagram, if the static spring constant is reduced by using a soft elastomer for the elastic body 101, the vibration isolation is improved, but the compression by the shared load Wo is improved. displacement [delta] ₂ is increased, sag resistance and durability is deteriorated. For this reason, a problem is pointed out that it is difficult to achieve both the improvement of the vibration proof property and the improvement of the sag property and the durability.

[0004] Further, in order to achieve both the improvement of the vibration proofing property and the improvement of the elasticity of the elastic body 101 and the durability, the height h of the elastic body 101 must be remarkably increased. There is a problem of increasing the size.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its technical subjects the improvement of vibration damping properties by lowering the dynamic spring constant and the setting of elastomer elastomers. The purpose is to improve the performance and durability.

[0006]

Means for Solving the Problems The technical problems described above are:
This can be effectively solved by the present invention. That is, the mount according to the present invention includes an elastic body made of an elastomer, a first attachment member joined to one end of the elastic body and fixed to one of the support side and the supported side, and the other end of the elastic body. A spring receiving flange coaxially joined to the first mounting member, and coaxially and axially movable with respect to the spring receiving flange, and fixed to the other of the support side and the supported side. A second mounting member; and a spring interposed between the spring receiving flange and the second mounting member, the spring constant of which decreases in a predetermined high load range. Also,
As a more preferable configuration added to the above configuration, the device includes a displacement restricting unit that restricts displacement of the spring in a restoring direction with respect to compression through the spring receiving flange and the second mounting member.

According to the configuration of the present invention, since the elastic body and the spring are arranged in series in the direction of the load applied from the supported side, the spring constant of the combination is the spring constant of the elastic body. Therefore, the spring constant can be increased by using a hard elastomer for the elastic body. In particular, since the spring has a characteristic that the spring constant is high in a low load region and low in a high load region, the compression displacement of the elastic body due to the shared load from the supported side is suppressed and the dynamic spring against vibration input is reduced. The constant can be reduced. As such a spring, for example, a disc spring is suitably adopted. Further, by providing displacement limiting means for limiting displacement of the spring in the restoration direction with respect to compression, it is possible to prevent occurrence of a tapping sound between the spring and the spring receiving flange or the second mounting member at the time of vibration displacement input in the tensile direction. In addition, it is possible to maintain the vibration damping property of the elastic body.

[0008]

FIG. 1 shows a first preferred embodiment of a mount according to the present invention. That is, the mount 10 according to this embodiment includes an elastic body 11 made of an elastomer and a mounting plate 1 as a first mounting member that is vulcanized and bonded to one end (lower end) of the elastic body 11 in the axial direction.
2, a spring receiving flange 13 which is vulcanized and bonded to the other end (upper end) in the axial direction of the elastic body 11, and a second mounting member disposed above the spring receiving flange 13 so as to be vertically displaceable by vibration input. and a center bolt 14, the disc spring 15 _{1-15 4} of a plurality of the same shape and size (four sheets in the illustrated example) is connected to the upper and lower between the flange portion 14a of the spring receiving flange 13 and the center bolt 14 And a connecting disc spring 15 interposed therebetween.

The mounting plate 12 is made by punching a metal plate such as a steel plate into an annular shape.
Overhangs 12a extending outwardly from the joint with 1 are formed at predetermined intervals in the circumferential direction, and mounting holes 12b are formed in each overhang 12a. It is attached to, for example, a frame on the support side 1 via a bolt 16 inserted into each of the attachment holes 12b.

On the other hand, the spring receiving flange 13 is also formed by punching out a metal plate of the same material as the mounting plate 12 in an annular shape, and has an outer periphery projecting in a direction opposite to the mounting plate 12 and continuously projecting in the circumferential direction. edge 13a is formed, the inner diameter of the flange portion 13a is slightly become larger diameter than the outer diameter of the connecting disc spring 15 (belleville spring 15 _{1-15 4),} whereby the connecting plates The spring 15 is centered. The elastic body 11 is vulcanized and formed into a coaxial cylindrical shape with an elastomer, and is integrated between the mounting plate 12 and the bottom portion 13b of the spring receiving flange 13 which are arranged to face each other in the axial direction.

The center bolt 14 has a connecting disc spring 15
Than (disc spring ₁₅ 1-15 ₄₎ of the large diameter flange portion 14
and a bolt body portion 14b vertically projecting upward from the center of the upper surface of the flange portion 14a and having a thread groove formed therein.
And a columnar projection 14c vertically projecting downward from the center of the lower surface of the flange 14a. The axial length of the cylindrical projection 14c is longer than the sum of the axial length (free length) of the connecting disc spring 15 when no load is applied and the thickness of the spring receiving flange 13, and the lower end of the elastic body 11 Has reached the inner circumference space.

The center bolt 14 is attached to the supported side 2 such as a bracket of a device that generates vibration when driven by a bolt body portion 14b and a nut (not shown) screwed thereto. Further, the columnar protrusion 14
By being inserted through the inner circumferences of the connecting disc spring 15 and the spring receiving flange 13 so as to be relatively movable in the axial direction, the connecting disc spring 15 and the spring receiving flange 13 are held coaxially with each other.

Each of the disc springs 15 ₁ to 15 ₁ in the connecting disc spring 15.
15 _4, the steel plate of the metal plate or fiber-reinforced plastic plate or the like, the inner circumference as also shown in the perspective view of FIG. 2 is obtained by forming the open tapered. Of these, the outer peripheral edge of the disc spring 15 ₁ positioned at the bottom side, spring receiving contact with the upper surface outer peripheral portion of the bottom portion 13b of the flange 13, the disc spring 15 ₄ located closest to the upper outer peripheral edge of the center bolt 14 It is in contact with the lower surface of the flange portion 14a. Also,
Disc spring 15 _{1-15 4} vertically adjacent, as its outer periphery and between the inner peripheral edges are abutting each other, are arranged so as to be upside down alternately.

[0014] As shown in FIG. 3 (i), a load / displacement characteristic of the connecting disc spring 15 has a constant inflection point p derived from the cross-sectional shape of the disc spring ₁₅ 1-15 _4. That the load of the inflection point p in the low load region below (inflection point load) Wp, the disc springs 15 _{1-15 4} is hard to deform because inclination with respect to the plane perpendicular to the axis is large, therefore the electrostatic Although the spring constant is high, in the high load region exceeding the inflection point load Wp, the inclination is small and the shape is easily deformed, so that the static spring constant is reduced.

Therefore, as shown in FIG. 3 (ii), the load / displacement characteristic of the mount 10 due to the combination of the elastic body 11 and the connecting disc spring 15 also corresponds to the inflection point load Wp of the connecting disc spring 15. Has an inflection point p ′. The inflection point load Wp is a shared load W due to the weight of the supported side 2.
The load is appropriately set lower than o.

In a state where the connecting disc spring 15 is compressed by the displacement amount δx under the shared load Wo, the gap between the outer peripheral edge 13a of the spring receiving flange 13 and the lower surface of the flange 14a of the center bolt 14 is maintained. with a gap G ₁ is interposed, cylindrical projection 14c of the center bolt 14
When the gap G ₂ is interposed between the support side 1. Therefore, the vibration absorbing operation due to the repetitive deformation of the elastic body 11 and the connecting disc spring 15 at the time of the vibration input is not hindered.

According to the configuration of the first embodiment, since the elastic body 11 and the connecting disc spring 15 are arranged in series in the direction in which the load is applied from the supported side 2, the elastic body 11 is connected to the elastic body 11. The spring constant of the mount 10 due to the combination of the disc springs 15 is lower than the spring constant of the elastic body 11 alone. For this reason, a hard (high static spring constant) elastomer material is used for the elastic body 11, so that the sag property and durability can be improved.

In the mounted state shown in FIG. 1, the shared load Wo due to the weight of the supported side 2 is received in the low spring region where the load is higher than the inflection point load Wp. Demonstrates excellent vibration absorption performance. Here, assuming that a low dynamic spring equivalent to the low spring region is to be realized in a mount that receives a load only with the elastic body 101 made of an elastomer, as in the prior art of FIG. Since the load / displacement characteristic is substantially as shown by the dashed line in FIG. 3 (ii), the amount of compressive displacement with respect to the shared load Wo becomes δy,
According to 0, since the amount of compressive displacement δz in a low load region up to the inflection point load Wp is small, the amount of compressive displacement with respect to the shared load Wo is suppressed to δx.

Next, FIG. 4 shows a second preferred embodiment of the mount according to the present invention. In the mount 10 according to the second embodiment, a mounting plate 12 as a first mounting member is vulcanized and adhered to one end (lower end) in the axial direction basically similarly to the first embodiment described above. An elastic body 11 made of an elastomer having a spring receiving flange 13 vulcanized and bonded to the other end (upper end);
A center bolt 14 as a second mounting member arranged above and below the third mounting member so as to be vertically movable by vibration displacement input, and a plurality of the same shape and the same size between the spring receiving flange 13 and the flange portion 14a of the center bolt 14. (Four in the example shown)
By concatenating the disc spring 15 _{1-15 4} vertically and a connecting disc spring 15 is interposed.

In this embodiment, the axial length of the columnar projection 14c of the center bolt 14 is
5 is smaller than the sum of the axial length (free length) under no load and the thickness of the spring receiving flange 13, and the cylindrical projection 14c
A set load adjusting screw 17 is provided at the lower end of the set load adjusting means as a displacement limiting means for limiting the amount of displacement of the connecting disc spring 15 in the restoration direction with respect to the compression.

The set load adjusting screw 17 includes a male screw 17a coaxially projecting downward from the lower end surface of the columnar projection 14c of the center bolt 14, and a washer 17b inserted through the male screw 17a. , The washer 17b screwed into the male screw portion 17a and the spring receiving flange 13
And a nut 17c to be brought into contact with the lower surface of. The male screw portion 17 a reaches the inner peripheral space of the elastic body 11 through the inner periphery of the spring receiving flange 13.

That is, the set load adjusting screw 17
By rotating the nut 17c in the tightening direction, the spring receiving flange 13 is appropriately moved to the flange portion 14a side of the center bolt 14 via the washer 17b, so that the maximum extension length L of the connecting disc spring 15 can be freely adjusted. It can be shorter than the length. Thus, the minimum load (set load) at which the connecting disc spring 15 can expand and contract can be arbitrarily set.

As shown in FIG. 5, when the mount 10 is mounted and compressed by receiving the shared load Wo due to the weight of the supported side 2, the outer peripheral edge 13a of the spring receiving flange 13 and the center bolt 14 the flange gap G ₁ is interposed between the lower surface of 14a, interposed gap G ₃ are between the lower end of the male screw portion 17a of the set load adjusting screw 17 and the support side 1, receiving the spring Bottom 13b of flange 13
Gap G ₄ is interposed between the washer 17b and a set load adjusting screw 17. Thus, the vibration absorbing operation due to the repetitive deformation of the elastic body 11 and the connecting disc spring 15 at the time of vibration input is not hindered.

The structures of the elastic body 11, the mounting plate 12, the spring receiving flange 13, and the connecting disc spring 15 are the same as those of the first embodiment described above.

FIG. 6 shows the load / displacement characteristics according to the second embodiment having the above-mentioned configuration. In FIG. 6, a indicates a connecting disc spring 15 with the set load set to 0 by the set load adjusting screw 17 and an elastic body. 11 is a load / displacement characteristic line based on a combination of the elastic body 11 and b, and b is a load / displacement characteristic line based on a combination of the connecting disc spring 15 and the elastic body 11 in which the set load is set to Wq. Line.

That is, according to the configuration of this embodiment,
Similar to the first embodiment, the elastic body 11 and the connecting disc spring 1
Since 5 is in series with the load, the spring constant of the mount 10 due to the combination is lower than the spring constant of the elastic body 11 alone. For this reason, the elastic body 11
Is made of a hard (high static spring constant) elastomer material.
The settability and durability can be improved. In the mounted state shown in FIG. 5, the load Wo due to the weight of the supported side 2 is received in the low spring region where the load is higher than the inflection point load Wp of the connecting disc spring 15. Demonstrates excellent vibration absorption performance against vibration.

For example, the set load adjusting screw 17
When the maximum extension length L of the connecting disc spring 15 is equal to the free length of the connecting disc spring 15 (set load = 0), an axial compressive load is applied to the mount 10 so that the elastic body 11 Since the connecting disc springs 15 are simultaneously subjected to compressive deformation, the mount 10 exhibits a load / displacement characteristic as shown by line a in FIG. On the other hand, when the set load adjusting screw portion 17 limits the maximum extension length L of the connecting disc spring 15 to be shorter than its free length by ΔL, and the set load is set to Wq, it acts on the mount 10. Until the axial compressive load reaches the set load Wq, the characteristics of the mount 10 are the same as the load / displacement characteristic line c of the elastic body 11, and when the compressive load exceeds the set load Wq, the connecting disc spring By compressing 15 to the maximum extension length L or less, the characteristic changes as shown by the line b.

As a result, the amount of compressive displacement when receiving the shared load Wo due to the weight of the supported side 2 becomes δb,
It becomes smaller than the compressive displacement amount δa with respect to the shared load Wo when the set load is 0. Therefore, as the maximum extension length L of the connecting disc spring 15 by the set load adjusting screw portion 17 is restricted to be shorter, in other words, as the set load Wq is set higher (Wq <Wo), the compression during the action of the shared load Wo is performed. The amount of displacement is reduced, the height of the entire mount 10 in the no-load state shown in FIG. 4 is also reduced, and an increase in the size of the product is suppressed.

In the mounted state shown in FIG. 5, for example, the support side 1 and the supported side 2 are largely displaced (pulling direction) apart from each other due to, for example, the inclination of the supported side 2, and the set load adjusting screw 17 is set. When the relative displacement is continued even after the washer 17b abuts on the lower surface of the spring receiving plate 13b, the vibration absorbing operation is performed only by the tensile elasticity of the elastic body 11. When the washer 17b of the set load adjusting screw 17 is in contact with the lower surface of the spring receiving plate 13b, the maximum length L of the connecting disc spring 15 is limited to less than its free length. contact and separation of the flange portion 14a of the spring 15 and the spring bearing plate 13 or the center bolt 14 or hammering sound by connecting and disconnecting the respective disc springs ₁₅ 1-15 ₄ between the connecting disc spring 15 does not occur.

The present invention is not limited to the illustrated embodiment. For example, the number of disc springs in the connecting disc spring 15 interposed between the spring receiving plate 13 and the flange portion 14a of the center bolt 14 is not limited to four as shown in FIG. It is. In this case, as long as the number of the disc springs is the same, the spring constant of the connecting disc spring 15 as a whole decreases as the number thereof increases. Further, even if a bellows in which the outer peripheral edge and the inner peripheral edge of each of the adjacent disc springs in the connecting disc spring 15 are welded or joined by another method is used, the spring constant is high in the low load region, and the shared load Wo is reduced. In the corresponding high load range, it exhibits the characteristic of low spring constant.

The set load adjusting screw 17 is also provided with a male screw 17a, a washer 17b and a nut 17 as shown in the figure.
c is not particularly limited.
Integrated with the washer 17b and the nut 17c
It is possible to make various changes such as applying a detent to the nut 17c so that the set value of the maximum extension length L of the spring does not change due to careless rotation.

[0032]

According to the mount of the present invention, the spring constant of the combination of the elastic body and the spring is lower than the spring constant of the elastic body. Durability can be improved. In addition, since the spring has a low spring constant in the region where the shared load is applied from the supported side, the suppression of the compression displacement of the elastic body due to the shared load and the improvement in vibration isolation by the low dynamic spring can both be achieved. . In addition, by the displacement limiting means, the vibration damping property of the elastic body is maintained when the vibration displacement is input in the tensile direction,
It is possible to prevent occurrence of a hitting sound.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a mounted state showing a preferred first embodiment of a mount according to the present invention.

FIG. 2 is a perspective view showing a connecting disc spring in the first embodiment.

FIG. 3 shows an operation according to the first embodiment,
(I) is a load / displacement characteristic diagram of the connecting disc spring, and (ii) is a load / displacement characteristic diagram of the entire mount.

FIG. 4 is a longitudinal sectional view showing a second preferred embodiment of the mount according to the present invention.

FIG. 5 is a longitudinal sectional view of a mounted state showing the second embodiment.

FIG. 6 is a load / displacement characteristic diagram according to the second embodiment.

FIG. 7 is a longitudinal sectional view of a mounted state showing a mount according to the related art.

FIG. 8 is a load / displacement characteristic diagram according to the related art.

[Explanation of symbols]

REFERENCE SIGNS LIST 1 support side 2 supported side 10 mount 11 elastic body 12 mounting plate (first mounting member) 12a overhanging portion 12b mounting hole 13 spring receiving flange 13a protruding edge portion 14 center bolt (second mounting member) 14a flange portion 14b Bolt body 14c Cylindrical projection 15 Continuous disc spring (spring) 15 ₁ to 15 ₄ Disc spring 16 Bolt 17 Set load adjusting screw 17a Male screw 17b Washer 17c Nut

Claims (2)

[Claims] An elastic body made of an elastomer, and a first attachment joined to one end of the elastic body and fixed to one of a support side and a supported side. A member (12); and the first mounting member (1) at the other end of the elastic body (11).
Spring receiving flange (13) coaxially joined with 2)
A second mounting member (1) disposed coaxially and axially movable with respect to the spring receiving flange (13) and fixed to the other of the support side (1) and the supported side (2).
4) and a spring (15) interposed between the spring receiving flange (13) and the second mounting member (14) and having a reduced spring constant in a predetermined high load range. Mount. And a displacement limiting means (17) for limiting a displacement of the spring (15) in a direction of restoring the compression of the spring (15) via the spring receiving flange (13) and the second mounting member (14). The mount according to claim 1.