JP7157668B2 - Anti-vibration support structure for railway vehicles - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an anti-vibration support structure for railway vehicles, and more particularly to an anti-vibration support structure for elastically supporting electrical equipment for railway vehicles with anti-vibration rubber.

2. Description of the Related Art Conventionally, as an anti-vibration support structure for electrical equipment for railway vehicles, one that is elastically supported by an anti-vibration rubber is known.

For example, Patent Literature 1 discloses an anti-vibration support structure in which a support member (fastening body) attached to an electric device of a railway vehicle is elastically supported by being sandwiched between an upper elastic body and a lower elastic body. In Patent Literature 1, such an anti-vibration support structure has the effect of preventing transmission of vibrations generated by electric devices during operation to a railway vehicle, thereby improving the ride comfort of the railway vehicle.

JP 2017-030422 A

However, in the case of the anti-vibration support structure disclosed in Patent Document 1, it is assumed that the support member attached to the electrical equipment is fastened with the upper elastic body and the lower elastic body in contact with the socket of the bolt. be. Under such circumstances, when the electric device starts to operate, a frictional force is generated between the support member and the socket, resulting in a rigid fastening state compared to the state where the support member is not in contact with the socket. , there is a possibility that the designed anti-vibration effect cannot be obtained due to insufficient elastic support. Further, if the vibration generated by the electrical equipment continues in the above state, fretting wear may occur between the supporting member and the socket, leading to fatigue failure in a short period of time. Furthermore, while fretting wear continued, noise due to wear was expected.

The present invention has been made in consideration of the above points, and provides an anti-vibration support structure for railway vehicles that can reliably exhibit the original anti-vibration effect of elastic support and prevent fretting wear and noise. I am trying to propose.

In order to solve such a problem, the present invention provides the following anti-vibration support structure for a railway vehicle, in which at least one of a plurality of fasteners is fastened to an electrical device for a railway vehicle to elastically support the electrical device. be done. The anti-vibration support structure includes a first fastening body and a second fastening body arranged substantially parallel to the first fastening body on the side of the first surface of the first fastening body. , a first plate arranged substantially parallel to the first fastening body on the side of the second surface opposite to the first surface of the first fastening body, and the first fastening body A first anti-vibration rubber layer laminated between the first surface and the second fastening body, and a rubber layer laminated between the second surface and the first plate of the first fastening body A first hole formed through the second rubber vibration isolator, the first and second fasteners, the first and second rubber vibration insulators, and the first plate a bolt penetrating from the side of the plate of the first and second anti-vibration rubbers; a socket of the bolt that defines the amount of crushing. Furthermore, in this anti-vibration support structure, the first hole is large enough to prevent the first fastening body from contacting the socket, and the first fastening body has the Concavities and convexities for alignment of the first and second anti-vibration rubbers are formed, and a second hole for alignment is formed through the first fastener and the first plate.

According to the present invention, it is possible to reliably exhibit the original anti-vibration effect of elastic support, and to prevent fretting wear and noise.

FIG. 2 is a diagram (part 1) showing an arrangement example of a vibration-damping support structure according to the first embodiment of the present invention; FIG. 2 is a diagram (part 2) showing an arrangement example of the anti-vibration support structure according to the first embodiment of the present invention; FIG. 3 is a sectional view showing the detailed structure of the anti-vibration support structure shown in FIGS. 1 and 2; It is a figure explaining the alignment method in the anti-vibration support structure shown in FIG. FIG. 5 is a diagram (part 1) showing an example of measurement results of characteristic values of anti-vibration rubber. FIG. 10 is a diagram (part 2) showing an example of measurement results of characteristic values of anti-vibration rubber; FIG. 5 is a cross-sectional view showing the detailed structure of the anti-vibration support structure according to the second embodiment of the present invention; FIG. 11 is a cross-sectional view showing the detailed structure of a vibration-damping support structure according to a third embodiment of the present invention; It is a figure for demonstrating the structure of the anti-vibration support structure which concerns on the 4th Embodiment of this invention. FIG. 10 is a cross-sectional view showing the detailed structure of a vibration-damping support structure according to a fifth embodiment of the present invention;

Several embodiments of the present invention will be described in detail below with reference to the drawings. In addition, in the drawings shown in each embodiment, constituent elements having the same or similar structure are denoted by the same numbers, and repeated explanations are omitted.

(1) First Embodiment FIGS. 1 and 2 are diagrams (parts 1 and 2) showing an arrangement example of a vibration-damping support structure according to a first embodiment of the present invention. 1(A) and 2(A) are sectional views, and FIGS. 1(B) and 2(B) are perspective views. The anti-vibration support structure 1 according to the first embodiment elastically supports an electrical device 9 for a railway vehicle at a plurality of support points 10 arranged on both sides of the electrical device 9, as shown in FIG. do. The anti-vibration support structure 1 according to the present embodiment is not limited to elastic support from the side, and as shown in FIG. 10, or may be elastically supported at a plurality of supporting points 10 (not shown) arranged at other positions (for example, below).

FIG. 3 is a sectional view showing the detailed structure of the anti-vibration support structure shown in FIGS. 1 and 2. FIG. As shown in FIG. 3, the anti-vibration support structure 1 includes a first fastening body 11, a second fastening body 12, a first anti-vibration rubber 13, a second anti-vibration rubber 14, a first plate 15 , a second plate 16 , a socket 17 , a bolt 18 and a nut 19 . 3, the first plate 15, the second anti-vibration rubber 14, the first fastening body 11, the first anti-vibration rubber 13, the second plate 16, and the second fastening The body 12 has a central hole 20 through which the bolt 18 passes.

The first fastening body 11 is, for example, a fastening body that can be attached to the electric device 9, and includes a first anti-vibration rubber on the first surface (upper surface in FIG. 3) and a second surface (lower surface in FIG. 3) It is sandwiched and elastically supported by the second rubber vibration isolator 14 on the side. Further, as shown in FIG. 3 , in the first fastening member 11 , along the hole 20 , the protrusion 11 a for alignment of the first rubber vibration isolator 13 and the second rubber vibration isolator 14 are aligned. A concave portion 11b is formed for each of the vibration-proof rubbers 13 and 14 so as to prevent them from moving toward the socket 17 by these concave/convex portions. Further, the hole 20 is sufficiently large for the diameter of the bolt 18 , and is large enough to prevent the first fastening member 11 (more specifically, the convex portion 11 a ) from coming into contact with the socket 17 .

The second fastening body 12 is, for example, a fastening body that can be attached to a box body of a railroad vehicle in which the electric device 9 is stored, and the first fastening body is attached to the first surface side of the first fastening body. are arranged substantially parallel to the A second plate 16 is provided in contact with the lower surface of the second fastening body 12, and the first anti-vibration rubber 13 applies a predetermined amount of pressure between the second plate and the first fastening body. caught and pinched. Although the details will be described in a third embodiment, the second plate 16 is used when the plate thickness of the second fastening body 12 is thin (specifically, for example, less than 5 mm). It is a plate-shaped member arranged to reinforce the load bearing capacity of the second fastening member 12 in consideration of the fact that the body 12 may locally deform and adversely affect the anti-vibration effect. Therefore, if the plate thickness of the second fastening body 12 is a predetermined value (for example, 5 mm) or more, the second fastening body 12 and the first fastening body 11 are separated from each other without providing the second plate 16 . A configuration in which the first anti-vibration rubber 13 is sandwiched is also possible, and in consideration of such a case, the second plate 16 can be read as the second fastening member 12 in the following description.

The first rubber vibration insulator 13 and the second rubber vibration insulator 14 are elastic bodies used to elastically support the first fastening body 11 . The type of elastic body used for the first and second vibration-isolating rubbers 13 and 14 is not limited, and any elastic body employed in general vibration-isolating support structures can be used. In this embodiment, the shape of the first and second rubber vibration insulators 13 and 14 may be donut-shaped with a hole 20 formed in the center.

The first plate 15 is a plate-shaped member arranged so as to sandwich the second anti-vibration rubber 14 between itself and the first fastening body 11 . When the bolts 18 are tightened, the first plate 15 and the second plate 16 sandwich the socket 17 so as to abut on the first and second anti-vibration rubbers 13 and 14 from above and below. A state in which the amount of compression is applied can be maintained.

The socket 17 is sandwiched between the first plate 15 and the second plate 16 (which may be read as the second fastening body 12) outside the bolt 18 and the coaxial axis. Since the socket 17 arranged in this manner defines the amount of crushing of the first and second rubber vibration insulators 13 and 14, the first and second rubber vibration insulators 13 and 14 are compressed by a predetermined amount. In this state, the first fastening body 11 is elastically supported by being sandwiched between these anti-vibration rubbers 13 and 14 .

A bolt 18 passes through the hole 20 and is fastened with a nut 19 . As shown in FIG. 3, in the first embodiment, the bolts 18 pass through the holes 20 from the side of the first plate 15 and are fastened with nuts 19, thereby connecting the first plate 15 and the second plate 15 together. The plate 16, the second fastening body 12, and the socket 17 are fixedly supported, and the first fastening body 11 is elastically supported via the first rubber vibration isolator 13 and the second rubber vibration isolator 14. .

Further, as shown in FIG. 3, in the anti-vibration support structure 1 according to the first embodiment, an alignment hole 21 is formed through the first fastening member 11 and the first plate 15. It is When fastening the bolts 18 in the anti-vibration support structure 1, by inserting a predetermined alignment jig 22 (see FIG. 4) into the hole 21, the first fastening body 11 and the first plate 15 are accurately positioned. can be matched.

4A and 4B are diagrams for explaining an alignment method in the anti-vibration support structure shown in FIG. As shown in FIG. 4, by inserting the positioning jig 22 into the hole 21 with the bolt 18 temporarily fixed, the first fastening body 11 and the first plate 15 can be precisely positioned. . Then, while maintaining this state (for example, with the positioning jig 22 inserted into the hole 21 ), the first fastening body 11 comes into contact with the socket 17 by finally fastening the bolt 18 and fastening it with the nut 19 . The anti-vibration support structure 1 can be fastened in a positional relationship (non-contact position) in which a predetermined gap is secured between the first fastening body 11 and the socket 17 in the hole 20 to the extent that it does not occur. More preferably, the non-contact position is a position where the first fastening body 11 does not come into contact with the socket 17 even if the electrical equipment 9 to which the first fastening body 11 is attached vibrates.

Here, the characteristics of the anti-vibration rubbers 13 and 14 obtained by fastening the first fastening member 11 at a non-contact position where it does not contact the socket 17 will be described with reference to measurement results.

5 and 6 are diagrams (part 1 and part 2) showing an example of the measurement results of the characteristic values of the anti-vibration rubber. Specifically, FIGS. 5 and 6 show vibration when the elastic support (first fastening body 11) is in contact with the socket 17 (contact) and when it is not in contact (non-contact). The graph shows how the characteristic values (the dynamic spring constant in FIG. 5 and the loss coefficient in FIG. 6) of the rubber vibration insulators 13 and 14 change depending on the vibration frequency of the body (electrical equipment 9). Of these, P1 in FIG. 5 and Q1 in FIG. 6 show changes in the basic characteristic values of the rubber vibration isolators 13 and 14, and P2 in FIG. 5 and Q2 in FIG. ), and P3 in FIG. 5 and Q3 in FIG. 6 show changes in the individual characteristic value (individual difference) in the contact state.

According to FIG. 5, if the first fastening body 11 is fastened to the electric device 9 in a state (contact state) in contact with the socket 17, as shown in P3, the anti-vibration rubbers 13, 14 , the apparent dynamic spring constant tends to be high. In other words, it can be seen that the dynamic spring constants of the anti-vibration rubbers 13 and 14 vary greatly between P1 and P3 when the electric device 9 vibrates in the contact state. On the other hand, when the first fastening body 11 is fastened to the electric device 9 in a state (non-contact state) in which the first fastening body 11 does not contact the socket 17 as in the present embodiment, as shown in P2, the anti-vibration rubber The apparent dynamic spring constants of 13 and 14 tend to be lower and stable than in the non-contact state (P3). That is, as in the present embodiment, the first fastening body 11 is fastened at a non-contact position where it does not contact the socket 17, so that even if the electric device 9 vibrates, the anti-vibration rubbers 13 and 14 It can be seen that the dynamic spring constant varies only between P1 and P2, and stable characteristics can be obtained.

Also, regarding the changes in the loss factor in FIG. 6, the same results as in FIG. I can say That is, as in the present embodiment, the first fastening body 11 is fastened at a non-contact position where it does not contact the socket 17, so that even if the electric device 9 vibrates, the anti-vibration rubbers 13 and 14 It can be seen that stable characteristics can be obtained for the loss factor. 5 and 6 can also be applied to second to fifth embodiments, which will be described later.

As described above, the anti-vibration support structure 1 according to the present embodiment has the socket 17 and the first fastening by making the fastening hole 20 of the bolt 18 sufficiently large with respect to the diameter of the bolt. Prevents contact with body 11. 4 using the hole 21 ensures that the first fastening body 11 and the socket 17 can be securely fastened at an appropriate non-contact position. Furthermore, by providing the projections 11a and recesses 11b for alignment on the first fastening member 11, it is possible to reliably align the first and second rubber vibration isolators 13 and 14, and to prevent misalignment. can be prevented. Thus, in the anti-vibration support structure 1 according to the present embodiment, when the electric device 9 starts operating, the first fastening member 11 and the socket 17 come into contact with each other, and frictional force is generated between them. It is possible to prevent a situation in which the designed anti-vibration effect cannot be obtained, and it can be expected to obtain the designed anti-vibration effect. In addition, since the first fastening body 11 and the socket 17 do not come into contact with each other, fretting wear does not occur between the first fastening body 11 and the socket 17 even when the vibration generated by the electric device 9 continues. , the generation of noise due to wear can also be prevented. Thus, the vibration-isolating support structure 1 according to the present embodiment can obtain a stable vibration-isolating effect as designed by elastic support, and can prevent the vibration generated by the electrical equipment 9 from being transmitted to the railway vehicle. Therefore, the riding comfort of the railway vehicle can be improved.

(2) Second Embodiment FIG. 7 is a cross-sectional view showing the detailed structure of a vibration isolation support structure according to a second embodiment of the present invention. The structure of the vibration isolation support structure 2 according to the second embodiment shown in FIG. 7 is compared with the vibration isolation support structure 1 according to the first embodiment shown in FIG. is reversed, and the nut 19 is arranged below the first plate 15.

That is, in the anti-vibration support structure 2 shown in FIG. 7, the bolt 18 passes through the hole 20 from the side of the second fastening body 12 (upper side in FIG. 7) and extends to the lower side of the first plate 15. It is fastened by a nut 19 which is arranged. As a result, the direction of the projection 11a and the recess 11b of the first fastening body 11 with respect to the fastening direction of the bolt 18 is opposite to that of the anti-vibration support structure 1 (see FIG. 3) according to the first embodiment. Become.

Although the anti-vibration support structure 2 according to the second embodiment has the structural difference as described above, the hole 20 is formed so large that the first fastening member 11 does not come into contact with the socket 17. The first fastening member 11 in the vicinity of the hole 20 is formed with a protrusion 11a for alignment of the first rubber vibration insulator 13 and a recess 11b for alignment of the second rubber vibration insulator 14, and , through the first fastening member 11 and the first plate 15 and through which the alignment holes 21 are formed. common. Therefore, the anti-vibration support structure 2 according to the second embodiment can stably exhibit the original anti-vibration effect of elastic support, and the first fastening body 11 and the socket 17 Effects similar to those of the first embodiment, such as prevention of fretting wear and noise caused by vibration of the electrical equipment 9, can be obtained.

(3) Third Embodiment FIG. 8 is a cross-sectional view showing the detailed structure of a vibration isolation support structure according to a third embodiment of the present invention. The structure of the anti-vibration support structure 3 according to the third embodiment shown in FIG. plate 16 is not provided. However, the third embodiment assumes that the plate thickness of the second fastening body 12 is equal to or greater than a predetermined value (specifically, for example, 5 mm).

In general, in a vibration isolation support structure by elastic support, a "plate-like member (vibration isolation support structure In the body 3, it is known that the second fastening body 12 and the first plate 15) can locally deform when subjected to elastic force or vibration if the plate thickness is thin. there is If such local deformation occurs in the plate-like member, a uniform force cannot be applied to the elastic body, making it impossible to obtain a stable anti-vibration effect. Therefore, if the plate thickness of the plate member is below a predetermined reference value, it is necessary to reinforce the load resistance (the overall plate thickness) by adding a plate or the like. Conversely, if the thickness of the plate member is equal to or greater than a predetermined reference value, a stable vibration damping effect can be expected without special reinforcement. The predetermined reference value can be determined based on calculation, measurement, empirical rules, etc., taking into account the material of the plate member, the amount of compression of the elastic body, and the like.

Here, in view of the above circumstances, in the anti-vibration support structure 3 according to the third embodiment, as described above, the plate thickness of the second fastening body 12 is a predetermined value corresponding to the reference value (Specifically, for example, 5 mm) or more is a prerequisite, so even if the second plate 16 is not provided, the second fastening body 12 does not locally deform. Therefore, the anti-vibration support structure 3 is connected to the first anti-vibration rubber 13 and the second anti-vibration rubber 14 by the second fastener 12 and the first plate 15, as in the first embodiment. A state in which a predetermined amount of compression is applied can be maintained.

As described above, the anti-vibration support structure 3 according to the third embodiment has the structural difference as described above, but the holes 20 are formed so that the first fastening member 11 does not come into contact with the socket 17 . is formed large, and the first fastening body 11 near the hole 20 has a convex portion 11a for alignment of the first rubber vibration isolator 13 and a concave portion 11b for alignment of the second rubber vibration isolator 14 is formed, and the alignment hole 21 is formed through the first fastening body 11 and the first plate 15. It is in common with the support structure 1 . Therefore, the anti-vibration support structure 3 according to the third embodiment can stably exhibit the inherent anti-vibration effect of elastic support, and the first fastening body 11 and the socket 17 Effects similar to those of the first embodiment, such as prevention of fretting wear and noise caused by vibration of the electrical equipment 9, can be obtained.

Furthermore, since the anti-vibration support structure 3 according to the third embodiment is not provided with the second plate 16, the overall weight and manufacturing cost can be reduced compared to the first embodiment. .

(4) Fourth Embodiment FIG. 9 is a diagram for explaining the structure of a vibration isolation support structure according to a fourth embodiment of the present invention. FIG. 9A shows a cross-sectional view of a vibration isolation support structure 4 according to a fourth embodiment, and FIG. 9B shows an arrangement example of the vibration isolation support structure 4. there is The structure of the anti-vibration support structure 4 according to the fourth embodiment shown in FIG. 9A is compared with the anti-vibration support structure 1 according to the first embodiment shown in FIG. , in that a third fastening body 23 is provided.

The third fastening body 23 is a fastening body that can be attached to, for example, a box body of a railroad vehicle in which the electric equipment 9 is stored, and is located on the lower side of the first plate 15 (opposite to the first fastening body 11). side) and arranged substantially parallel to the first fastening body. Further, the third fastening body 23 is formed with a hole 21 for alignment, similarly to the first fastening body 11 and the first plate 15 . Therefore, when fastening the bolts 18 in the anti-vibration support structure 4, by inserting a predetermined alignment jig 22 (see FIG. 4) into the holes 21, the first fastening body 11, the first plate 15 and the second 3 fasteners 23 can be precisely aligned.

From the above, according to the anti-vibration support structure 4 according to the fourth embodiment, the three fastening bodies (the first fastening body 11, the second fastening body 12, and the third fastening body 23) are Since the number of fastening points can be increased compared to the first to third embodiments (see FIG. 9B), a more stable fastening state can be achieved.

In addition, although the anti-vibration support structure 4 according to the fourth embodiment has the structural difference as described above, the hole 20 is formed large enough to prevent the first fastening member 11 from coming into contact with the socket 17. In addition, a convex portion 11a for alignment of the first rubber vibration isolator 13 and a concave portion 11b for alignment of the second rubber vibration isolator 14 are formed on the first fastening member 11 near the hole 20. It is common to the anti-vibration support structure 1 according to the first embodiment in that it has the feature of Furthermore, in the anti-vibration support structure 4 according to the fourth embodiment, the alignment holes 21 are formed through the first fastening member 11, the first plate 15 and the third fastening member 23. Therefore, by aligning using the hole 21, each of these members can be aligned with high precision, and the position where a predetermined distance is secured between the first fastening body 11 and the socket 17 in the hole 20 In the relationship (non-contact position) the anti-vibration support structure 4 can be fastened. Therefore, the anti-vibration support structure 4 according to the fourth embodiment can stably exhibit the original anti-vibration effect of elastic support, and the first fastening member 11 and the socket 17 Effects similar to those of the first embodiment, such as prevention of fretting wear and noise caused by vibration of the electrical equipment 9, can be obtained.

(5) Fifth Embodiment FIG. 10 is a cross-sectional view showing the detailed structure of a vibration isolation support structure according to a fifth embodiment of the present invention. The structure of the anti-vibration support structure 5 according to the fifth embodiment shown in FIG. 10 is compared with the anti-vibration support structure 4 according to the fourth embodiment shown in FIG. plate 15 is not provided. However, the fifth embodiment assumes that the plate thickness of the third fastening member 23 is equal to or greater than a predetermined value (specifically, for example, 5 mm).

In the anti-vibration support structure 5 according to the fifth embodiment, the plate thickness of the third fastening body 23 is a reference value (5 mm in this example) that does not locally deform when subjected to elastic force or vibration. ) From the above, even if the first plate 15 is not provided as in the anti-vibration support structure 4 according to the fourth embodiment, the third fastening body 23 has sufficient load resistance. It can be expected to exhibit a stable anti-vibration effect.

Although the anti-vibration support structure 5 according to the fifth embodiment has the structural difference as described above, the hole 20 is formed large enough so that the first fastening member 11 does not come into contact with the socket 17. In addition, a convex portion 11a for alignment of the first rubber vibration isolator 13 and a concave portion 11b for alignment of the second rubber vibration isolator 14 are formed on the first fastening member 11 near the hole 20. It is common to the anti-vibration support structure 4 according to the fourth embodiment in that it has the feature of Furthermore, in the anti-vibration support structure 5 according to the fifth embodiment, although the first plate 15 is not provided, the first fastening body 11 and the third fastening body 23 are penetrated for alignment. Since the hole 21 is formed, these members can be precisely aligned by alignment using the hole 21 , and a predetermined gap between the first fastening body 11 and the socket 17 in the hole 20 can be achieved. The anti-vibration support structure 4 can be fastened in a positional relationship (non-contact position) in which an interval is ensured. Therefore, the anti-vibration support structure 5 according to the fifth embodiment can stably exhibit the original anti-vibration effect of elastic support, and the first fastening body 11 and the socket 17 Effects similar to those of the fourth embodiment, such as preventing the occurrence of fretting wear and preventing the occurrence of noise based on vibration of the electrical equipment 9 effect) can be obtained.

Further, the anti-vibration support structure 5 according to the fifth embodiment includes three fastening bodies (first fastening body 11, second fastening body 12, third By providing the fastening body 23), it is possible to increase the number of fastening points compared to the first to third embodiments (see FIG. 9B), so that a more stable fastening state can be realized.

Furthermore, since the anti-vibration support structure 5 according to the fifth embodiment is not provided with the first plate 15, the overall weight and manufacturing cost can be reduced compared to the fourth embodiment. .

As described above, in each embodiment described above, the case where the first fastening body is attached to the electric device 9 has been mainly described, but in the present invention, each fastening body (first fastening body 11, second fastening body 12. The attachment destination of the third fastening member 23) is not limited, and when one is attached to the electrical equipment 9, at least one other may be attached to the box of the railcar or the like.

Moreover, the present invention is not limited to the above-described first to fifth embodiments, and includes various modifications. For example, the above-described embodiments have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the described configurations. Also, part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. . Moreover, it is possible to add, delete, or replace a part of the configuration of each embodiment with another configuration. In any of these cases, a stable anti-vibration effect can be obtained as described in each embodiment.

1, 2, 3, 4, 5 Anti-vibration support structure 9 Electrical equipment 11 First fastening body 11a Convex portion 11b Concave portion 12 Second fastening body 13 First anti-vibration rubber 14 Second anti-vibration rubber 15 Second 1 plate 16 second plate 17 socket 18 bolt 19 nut 20, 21 hole 22 alignment jig 23 third fastening body

Claims (5)

At least one of a plurality of fasteners is fastened to an electrical device for a railroad vehicle to elastically support the electrical device, the anti-vibration support structure for the railroad vehicle comprising:
a first said fastening body;
a second fastening body arranged substantially parallel to the first fastening body on the side of the first surface of the first fastening body;
a first plate disposed substantially parallel to the first fastening body on the side of the second surface opposite to the first surface of the first fastening body;
a first anti-vibration rubber laminated between the first surface of the first fastening body and the second fastening body;
a second anti-vibration rubber laminated between the second surface of the first fastening body and the first plate;
A bolt passing from the side of the first plate through a first hole formed through the first and second fastening bodies, the first and second anti-vibration rubbers, and the first plate. When,
a socket of the bolt disposed outside the concentric shaft of the bolt, sandwiched between the second fastening body and the first plate, and defining an amount of crushing of the first and second anti-vibration rubbers; ,
with
the first hole is large enough to prevent the first fastener from contacting the socket;
In the vicinity of the first hole in the first fastening body, unevenness is formed for alignment of the first and second anti-vibration rubbers,
A vibration isolation support structure for a railway vehicle, wherein a second alignment hole is formed through the first fastener and the first plate. When the plate thickness of the second fastening body is less than a predetermined threshold value, a second plate having the first hole is provided between the second fastening body and the first anti-vibration rubber. The anti-vibration support structure for a railway vehicle according to claim 1, characterized in that: 2. The anti-vibration support structure for a railway vehicle according to claim 1, wherein a third fastening member having said first and second holes is arranged in place of said first plate. When the plate thickness of the third fastening body is less than a predetermined threshold value, the first plate is arranged between the third fastening body and the second anti-vibration rubber. 4. The anti-vibration support structure for a railway vehicle according to claim 3. The anti-vibration support structure for a railway vehicle according to claim 1, wherein the bolt passes through the first hole from the side of the second fastening body.

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