JP2020114713A - Vibration-proof support structure for railway vehicle - Google Patents

Abstract

To provide a vibration-proof support structure which not only surely exhibits original vibration-proof effect by an elastic support structure but also prevents generation of fretting wear and noise.SOLUTION: In a vibration-proof support structure 3, a first hole 20 is so large that a first fastening body 11 does not contact with a socket 17 and a projection 11a for alignment of a first vibration-proof rubber 13 and a recess 11b for alignment of a second vibration-proof rubber 14 are formed in a neighborhood of the first hole 20 of the first fastening body 11. Second alignment holes 21 are formed penetrating the first fastening body 11 and a first plate 15.SELECTED DRAWING: Figure 8

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration-damping support structure for a railroad vehicle, and more particularly to a vibration-damping support structure for elastically supporting electric equipment for a railcar with vibration-proof rubber.

2. Description of the Related Art Conventionally, as a vibration isolation support structure for an electric device for a railway vehicle, one that is elastically supported by a vibration isolation rubber is known.

For example, Patent Document 1 discloses a vibration-proof 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 Document 1, such an anti-vibration support structure has an effect of preventing the vibration generated during the operation of the electric device from being transmitted to the railway vehicle and improving the riding 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 electric device is fastened with the upper elastic body and the lower elastic body in contact with the socket of the bolt. It In such a situation, when the electric device starts to operate, a frictional force is generated between the support member and the socket, so that the support member is in a fastening state that is more rigid than the state in which the support member is not in contact with the socket. However, there was a possibility that sufficient elastic support would not be achieved and the design vibration damping effect could not be obtained. Further, if the vibration generated by the electric device continues in the above state, fretting wear may occur between the support member and the socket, which may result in fatigue failure in a short time. Furthermore, it was expected that noise would be generated due to wear while fretting wear continued.

The present invention has been made in consideration of the above points, and an anti-vibration support structure for a railway vehicle capable of reliably exhibiting the original anti-vibration effect by elastic support and preventing the occurrence of fretting wear and noise. It is a proposal.

In order to solve such a problem, the present invention provides the following vibration damping support structure for a railway vehicle, in which at least one of a plurality of fastening bodies is fastened to an electrical device for a railway vehicle to elastically support the electrical device. To be done. The anti-vibration support structure includes a first fastening body, and a second fastening body that is disposed on the first surface side of the first fastening body and is substantially parallel to the first fastening body. A first plate disposed substantially parallel to the first fastening body on the side of the second surface of the first fastening body opposite to the first surface, and the first fastening body of the first fastening body. A first anti-vibration rubber laminated between the first surface and the second fastening body, and laminated between the second surface of the first fastening body and the first plate A second anti-vibration rubber, the first and second fastening bodies, the first and second anti-vibration rubber, and a first hole formed through the first plate Of the bolt penetrating from the plate side of the plate, and on the outer side of the concentric shaft with the bolt, sandwiched between the second fastening body and the first plate, the first and second anti-vibration rubber A socket for the bolt for defining a crushing amount. Further, in the present vibration-proof support structure, the first hole is large enough that the first fastening body does not come into contact with the socket, and the first fastening body is provided with the first fastening body near the first hole. 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 fastening body and the first plate.

According to the present invention, it is possible to surely exhibit the original vibration damping effect of the elastic support and prevent the occurrence of fretting wear and noise.

It is a figure (the 1) which shows the example of arrangement|positioning of the vibration isolating support structure which concerns on the 1st Embodiment of this invention. It is a figure (the 2) which shows the example of arrangement|positioning of the vibration isolating support structure which concerns on the 1st Embodiment of this invention. FIG. 3 is a cross-sectional view showing a detailed structure of the anti-vibration support structure shown in FIGS. 1 and 2. It is a figure explaining the alignment method in the vibration isolating support structure shown in FIG. It is a figure (the 1) which shows an example of a measurement result of the characteristic value of anti-vibration rubber. It is a figure (the 2) which shows an example of the measurement result of the characteristic value of anti-vibration rubber. It is sectional drawing which shows the detailed structure of the antivibration support structure which concerns on the 2nd Embodiment of this invention. It is sectional drawing which shows the detailed structure of the antivibration support structure which concerns on the 3rd Embodiment of this invention. It is a figure for demonstrating the structure of the antivibration support structure which concerns on the 4th Embodiment of this invention. It is sectional drawing which shows the detailed structure of the antivibration support structure which concerns on the 5th Embodiment of this invention.

Hereinafter, some embodiments of the present invention will be described in detail with reference to the drawings. Note that, in the drawings shown in each embodiment, constituent elements having the same or similar structure are denoted by the same reference numerals, and repeated description will be omitted.

(1) First Embodiment FIGS. 1 and 2 are views (No. 1 and No. 2) showing an arrangement example of a vibration-proof support structure according to a first embodiment of the present invention. 1A and 2A are cross-sectional views, and FIGS. 1B and 2B are perspective views. The anti-vibration support structure 1 according to the first embodiment elastically supports the electric device 9 at a plurality of support points 10 arranged on both sides of the electric device 9 for a railway vehicle, as shown in FIG. 1, for example. To 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. 2, a plurality of support points arranged above the electric device 9 are provided. It may be elastically supported by 10, or may be elastically supported by a plurality of support points 10 (not shown) arranged at other positions (for example, below).

FIG. 3 is a sectional view showing a detailed structure of the vibration-proof support structure shown in FIGS. 1 and 2. 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, and a first plate. 15, the second plate 16, the socket 17, the bolt 18, and the nut 19 are provided. Further, in order from the lower side of FIG. 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 hole 20 formed in the center thereof, 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) side and a second surface (lower surface in FIG. 3). It is sandwiched between the second anti-vibration rubber 14 and elastically supported. Further, as shown in FIG. 3, in the first fastening body 11, the alignment between the convex portion 11 a for aligning the first anti-vibration rubber 13 and the second anti-vibration rubber 14 along the hole 20. Recessed portions 11b are formed, and the anti-vibration rubbers 13 and 14 are aligned so as not to move to the socket 17 side by these uneven portions. Further, the hole 20 is sufficiently large with respect to the diameter of the bolt 18, and a size is ensured such that the first fastening body 11 (more specifically, the convex portion 11a) does not come into contact with the socket 17.

The second fastening body 12 is a fastening body that can be attached to, for example, a box of a railway vehicle in which the electric device 9 is stored, and the first fastening body is provided on the first surface side of the first fastening body. It is arranged almost parallel to. 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. Received and pinched. Although described in detail in the third embodiment, the second plate 16 is the second fastening member when the second fastening body 12 has a small thickness (specifically, for example, less than 5 mm). The plate-shaped member is arranged to reinforce the withstand load of the second fastening body 12 in consideration of the fact that the body 12 locally deforms and the vibration damping effect may be adversely affected. 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 is not provided and the second fastening body 12 is provided between the second fastening body 12 and the first fastening body 11. The first anti-vibration rubber 13 may be sandwiched, and in consideration of such a case, the second plate 16 may be replaced with the second fastening body 12 in the following description.

The first anti-vibration rubber 13 and the second anti-vibration rubber 14 are elastic bodies used to elastically support the first fastening body 11. The type of elastic body used for the first and second anti-vibration rubbers 13 and 14 is not limited, and an elastic body employed in a general anti-vibration support structure can be used. In the present embodiment, the first and second anti-vibration rubbers 13 and 14 may have a donut shape in which the hole 20 is formed at the center.

The first plate 15 is a plate-shaped member that is arranged so as to sandwich the second anti-vibration rubber 14 between the first plate 15 and the first fastening body 11. Further, the first plate 15 and the second plate 16 sandwich the socket 17 so as to come into contact with each other in the vertical direction when the bolts 18 are fastened, so that the first and second anti-vibration rubbers 13 and 14 are provided with a predetermined distance. It is possible to maintain the state in which the amount of compression is added.

The socket 17 is arranged outside the concentric shaft with the bolt 18 so as to be sandwiched between the first plate 15 and the second plate 16 (which may be read as the second fastening body 12 ). Since the socket 17 arranged in this way regulates the crush amount of the first and second anti-vibration rubbers 13 and 14, a predetermined compression amount is applied to the first and second anti-vibration rubbers 13 and 14. In this state, the first fastening body 11 is elastically supported by being sandwiched between the anti-vibration rubbers 13 and 14.

The bolt 18 penetrates the hole 20 and is fastened by the nut 19. As shown in FIG. 3, in the first embodiment, the bolt 18 penetrates the hole 20 from the first plate 15 side and is fastened with the nut 19, so that the first plate 15 and the second plate 15 are connected. 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 anti-vibration rubber 13 and the second anti-vibration rubber 14. ..

Further, as shown in FIG. 3, in the vibration-proof support structure 1 according to the first embodiment, a hole 21 for alignment is formed through the first fastening body 11 and the first plate 15. Has been done. When the bolt 18 is fastened in the anti-vibration support structure 1, by inserting a predetermined positioning 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.

FIG. 4 is a diagram for explaining a position alignment method in the vibration-proof support structure shown in FIG. As shown in FIG. 4, the first fastening body 11 and the first plate 15 can be accurately aligned by inserting the alignment jig 22 into the hole 21 with the bolt 18 temporarily fixed. .. Then, while maintaining this state (for example, with the positioning jig 22 inserted in the hole 21), the bolt 18 is finally stopped and fastened with the nut 19, so that the first fastening body 11 contacts the socket 17. The anti-vibration support structure 1 can be fastened in a positional relationship (non-contact position) in which a predetermined space is secured between the first fastening body 11 and the socket 17 in the hole 20 to such an extent that it does not occur. It is more preferable that the non-contact position is a position where the first fastening body 11 does not come into contact with the socket 17 even if vibration occurs in the electric device 9 to which the first fastening body 11 is attached.

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

5 and 6 are views (No. 1 and No. 2) showing an example of the measurement result of the characteristic value of the anti-vibration rubber. Specifically, FIGS. 5 and 6 show vibrations when the elastic support body (first fastening body 11) is in contact with the socket 17 (contact) and 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 anti-vibration rubbers 13 and 14 change depending on the vibration frequency of the body (electrical device 9). Of these, P1 in FIG. 5 and Q1 in FIG. 6 indicate changes in the basic characteristic values of the rubber cushions 13 and 14, and P2 in FIG. 5 and Q2 in FIG. 6 indicate individual characteristic values (individual difference) in the non-contact state. ), and P3 in FIG. 5 and Q3 in FIG. 6 indicate changes in individual characteristic values (individual differences) in the contact state.

According to FIG. 5, if the first fastening body 11 is fastened to the electric device 9 in a state of being in contact with the socket 17 (contact state), as shown in P3, the anti-vibration rubbers 13, 14 are provided. The apparent dynamic spring constant tends to increase. That is, in the contact state, when vibration occurs in the electric device 9, the dynamic spring constants of the anti-vibration rubbers 13 and 14 greatly vary between P1 and P3. On the other hand, when the first fastening body 11 is fastened to the electric device 9 in a state where it does not come into contact with the socket 17 (non-contact state) as in the present embodiment, as shown in P2, the vibration-proof rubber is used. 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 the non-contact position where the first fastening body 11 does not come into contact with the socket 17, so that even if vibration is generated in the electric device 9, the vibration-proof rubbers 13 and 14 can be connected. It can be seen that the dynamic spring constant varies only between P1 and P2, and stable characteristics can be obtained.

Regarding the change of the loss coefficient in FIG. 6, the same as in FIG. 5 is obtained by comparing the variation in the contact state (between Q1 and Q3) and the variation in the non-contact state (between Q1 and Q2). I can say. That is, as in the present embodiment, the first fastening body 11 is fastened at the non-contact position where the first fastening body 11 does not come into contact with the socket 17, so that even if vibration is generated in the electric device 9, the vibration-proof rubbers 13 and 14 can be connected. It can be seen that the loss coefficient can obtain stable characteristics. The characteristic changes of the anti-vibration rubbers 13 and 14 shown in FIGS. 5 and 6 can also be applied to second to fifth embodiments described later.

As described above, in the vibration-isolating support structure 1 according to the present embodiment, the holes 20 for fastening the bolts 18 are made sufficiently large with respect to the bolt diameter, so that the socket 17 and the first fastening. Prevents contact with body 11. The first fastening body 11 and the socket 17 can be securely fastened at an appropriate non-contact position by the positioning method of FIG. 4 using the holes 21. Further, the first fastening body 11 is provided with the convex portion 11a and the concave portion 11b for alignment, so that the first and second anti-vibration rubbers 13 and 14 can be reliably aligned with each other, and the positional deviation can be achieved. Can be prevented. Thus, in the vibration-proof support structure 1 according to the present embodiment, when the electric device 9 starts operating, the first fastening body 11 and the socket 17 come into contact with each other, and a frictional force is generated between them. It is possible to prevent the situation where the designed anti-vibration effect is not obtained, and it can be expected to obtain the anti-vibration effect as designed. Further, 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. It is also possible to prevent noise due to wear. Thus, the anti-vibration support structure 1 according to the present embodiment can obtain a stable anti-vibration effect as designed by elastic support, and prevents the vibration generated by the electric device 9 from being transmitted to the railway vehicle. As a result, 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 the anti-vibration support structure according to the second embodiment of the present invention. The structure of the anti-vibration support structure 2 according to the second embodiment shown in FIG. 7 is similar to that of the anti-vibration support structure 1 according to the first embodiment shown in FIG. The penetration direction is reversed and the arrangement of the nut 19 is on the lower side of the first plate 15.

That is, in the anti-vibration support structure 2 shown in FIG. 7, the bolt 18 penetrates the hole 20 from the second fastening body 12 side (upper side in FIG. 7), and is attached to the lower side of the first plate 15. It is fastened by the arranged nut 19. As a result, the directions of the convex portions 11a and the concave portions 11b of the first fastening body 11 with respect to the fastening direction of the bolts 18 are opposite to those of the vibration isolation support structure 1 (see FIG. 3) according to the first embodiment. Become.

The anti-vibration support structure 2 according to the second embodiment has the above-mentioned structural differences, but the hole 20 is formed large enough to prevent the first fastening body 11 from coming into contact with the socket 17. In addition, the first fastening body 11 near the hole 20 is provided with the convex portion 11a for aligning the first anti-vibration rubber 13 and the concave portion 11b for aligning the second anti-vibration rubber 14, and The vibration-isolating support structure 1 according to the first embodiment is characterized in that the positioning hole 21 is formed through the first fastening body 11 and the first plate 15. Have in common. Therefore, the anti-vibration support structure 2 according to the second embodiment can stably exhibit the original anti-vibration effect due to the elastic support, and at the same time between the first fastening body 11 and the socket 17. It is possible to obtain the same effects as in the first embodiment, such as preventing fretting wear and noise due to vibration of the electric device 9.

(3) Third Embodiment FIG. 8 is a sectional view showing a detailed structure of a vibration-isolating 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. 8 is similar to that of the anti-vibration support structure 1 according to the first embodiment shown in FIG. The difference is that the plate 16 is not provided. However, the third embodiment is predicated on the case where the plate thickness of the second fastening body 12 is a predetermined value (specifically, for example, 5 mm) or more.

Generally, in an anti-vibration support structure using elastic support, a "plate-shaped member (anti-vibration support structure in the anti-vibration support structure 3 in which the first anti-vibration rubber 13 and the second anti-vibration rubber 14) are sandwiched 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 when the plate thickness is thin. There is. When such local deformation occurs in the plate member, it is not possible to apply a uniform force to the elastic body, and it becomes impossible to obtain a stable vibration damping effect. Therefore, when the plate thickness of the plate-shaped member is below a predetermined reference value, it is necessary to add a plate or the like to reinforce the withstand load (total plate thickness). Conversely speaking, if the plate thickness of the plate-shaped member is equal to or greater than the predetermined reference value, a stable vibration damping effect can be expected without any special reinforcement. The predetermined reference value can be determined based on calculation, measurement, empirical rules, etc., in consideration of the material of the plate member, the compression amount of the elastic body, and the like.

Here, in view of the above circumstances, in the vibration isolating support structure 3 according to the third embodiment, as described above, the plate thickness of the second fastening body 12 is the predetermined value corresponding to the reference value. Since the precondition is that it is (specifically, for example, 5 mm) or more, the second fastening body 12 does not locally deform even if the second plate 16 is not provided. Therefore, the anti-vibration support structure 3 is formed by the second fastening body 12 and the first plate 15 into the first anti-vibration rubber 13 and the second anti-vibration rubber 14 as in the first embodiment. It is possible to maintain a state in which a predetermined amount of compression is added.

As described above, the vibration-damping support structure 3 according to the third embodiment has the structural differences as described above, but the holes 20 are small enough to prevent the first fastening body 11 from coming into contact with the socket 17. Is formed to be large, and the first fastening body 11 near the hole 20 is provided with a convex portion 11a for aligning the first anti-vibration rubber 13 and a concave portion 11b for aligning the second anti-vibration rubber 14. The vibration damping device according to the first embodiment is characterized in that the first fastening body 11 and the first plate 15 are formed with the positioning holes 21. It is common to the support structure 1. Therefore, the anti-vibration support structure 3 according to the third embodiment can stably exhibit the original anti-vibration effect due to the elastic support, and at the same time between the first fastening body 11 and the socket 17. It is possible to obtain the same effects as in the first embodiment, such as preventing fretting wear and noise due to vibration of the electric device 9.

Furthermore, since the vibration-proof support structure 3 according to the third embodiment does not have the second plate 16, it is possible to reduce the overall weight and the manufacturing cost as compared with the first embodiment. ..

(4) Fourth Embodiment FIG. 9 is a diagram for explaining the structure of a vibration-proof support structure according to a fourth embodiment of the present invention. FIG. 9A shows a cross-sectional view of the vibration isolation support structure 4 according to the 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. , And the 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 railway vehicle in which the electric device 9 is stored, and the lower side of the first plate 15 (opposite to the first fastening body 11). Side) and is arranged substantially parallel to the first fastening body. Further, the third fastening body 23 is formed with a hole 21 for alignment, like the first fastening body 11 and the first plate 15. Therefore, when the bolts 18 are fastened in the anti-vibration support structure 4, by inserting a predetermined positioning jig 22 (see FIG. 4) into the holes 21, the first fastening body 11, the first plate 15, and the first The fastening bodies 23 of No. 3 can be accurately aligned.

From the above, according to the vibration-isolating support structure 4 according to the fourth embodiment, three fastening bodies (first fastening body 11, second fastening body 12, third fastening body 23) are provided. Since it is possible to increase the number of fastening points as compared with the first to third embodiments (see FIG. 9B), a more stable fastening state can be realized.

In addition, the vibration-isolating support structure 4 according to the fourth embodiment has the hole 20 formed so large that the first fastening body 11 does not come into contact with the socket 17, although the structural difference is as described above. In addition, the first fastening body 11 near the hole 20 is provided with the convex portion 11a for aligning the first anti-vibration rubber 13 and the concave portion 11b for aligning the second anti-vibration rubber 14. It is common to the anti-vibration support structure 1 according to the first embodiment in that it has the feature of being. Furthermore, in the vibration-proof support structure 4 according to the fourth embodiment, the positioning hole 21 is formed through the first fastening body 11, the first plate 15, and the third fastening body 23. Therefore, each of these members can be accurately aligned by the alignment using the hole 21, and a position where a predetermined space is secured between the first fastening body 11 and the socket 17 in the hole 20. The vibration-proof support structure 4 can be fastened in a relationship (non-contact position). Therefore, the anti-vibration support structure 4 according to the fourth embodiment can stably exhibit the original anti-vibration effect due to the elastic support, and at the same time between the first fastening body 11 and the socket 17. It is possible to obtain the same effects as in the first embodiment, such as preventing fretting wear and noise due to vibration of the electric device 9.

(5) Fifth Embodiment FIG. 10 is a cross-sectional view showing the detailed structure of the anti-vibration support structure according to the 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 the same as that of the anti-vibration support structure 4 according to the fourth embodiment shown in FIG. The difference is that the plate 15 is not provided. However, the fifth embodiment is premised on the case where the plate thickness of the third fastening body 23 is equal to or greater than a predetermined value (specifically, 5 mm, for example).

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 vibration-isolating support structure 4 according to the fourth embodiment, the third fastening body 23 has a sufficient withstand load. Therefore, it can be expected to exert a stable anti-vibration effect.

Although the vibration-isolating support structure 5 according to the fifth embodiment has the above-mentioned structural differences, the hole 20 is formed so large that the first fastening body 11 does not come into contact with the socket 17. In addition, the first fastening body 11 near the hole 20 is provided with the convex portion 11a for aligning the first anti-vibration rubber 13 and the concave portion 11b for aligning the second anti-vibration rubber 14. The vibration-isolating support structure 4 according to the fourth embodiment is common in that the vibration-isolating support structure 4 according to the fourth embodiment is provided. Furthermore, in the vibration-isolating 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, each of these members can be accurately aligned by the alignment using the hole 21, and a predetermined distance 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 with a positional relationship (non-contact position) in which a space is secured. Therefore, the anti-vibration support structure 5 according to the fifth embodiment can stably exhibit the original anti-vibration effect due to the elastic support, and at the same time between the first fastening body 11 and the socket 17. It is possible to prevent the occurrence of fretting wear and the occurrence of noise based on the vibration of the electric device 9, and the like (therefore, the same effect as the first embodiment). Effect) can be obtained.

Further, the vibration isolation support structure 5 according to the fifth embodiment has three fastening bodies (the first fastening body 11, the second fastening body 12, and the third fastening body) as in the fourth embodiment. By providing the fastening body 23), the number of fastening points can be increased more than in the first to third embodiments (see FIG. 9B), and thus a more stable fastening state can be realized.

Furthermore, since the vibration isolation support structure 5 according to the fifth embodiment does not have the first plate 15, the overall weight and manufacturing cost can be reduced as compared with the fourth embodiment. ..

As described above, in each of the above-described embodiments, 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 (the first fastening body 11, the second fastening body). The mounting destinations of the second and third fastening bodies 23) are not limited, and when one is mounted on the electric device 9, at least the other one may be mounted on the box body of the railway vehicle or the like.

Moreover, the present invention is not limited to the above-described first to fifth embodiments, and various modifications are included. 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 configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of one embodiment can be added with the configuration of another embodiment. .. Further, it is possible to add/delete/replace other configurations with respect to a part of the configurations of the respective embodiments. Then, in any of these cases, a stable vibration damping 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 Recessed portion 12 Second fastening body 13 First anti-vibration rubber 14 Second anti-vibration rubber 15th 1 plate 16 2nd plate 17 socket 18 bolt 19 nut 20, 21 hole 22 alignment jig 23 third fastening body

Claims (5)

An anti-vibration support structure for a railway vehicle, wherein at least one of a plurality of fasteners is fastened to an electrical device for a railway vehicle to elastically support the electrical device,
A first fastening body,
A second fastening body arranged substantially parallel to the first fastening body on the first surface side of the first fastening body;
A first plate arranged substantially parallel to the first fastening body on the side of the second surface of the first fastening body opposite to the first surface;
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 that penetrates the first and second fastening bodies, the first and second anti-vibration rubbers, and the first hole formed through the first plate from the side of the first plate. When,
A socket for the bolt, which is arranged outside the concentric shaft of the bolt, sandwiched between the second fastening body and the first plate, and which defines a crush amount of the first and second vibration-proof rubbers; ,
Equipped with
The first hole is large enough that the first fastener does not come into contact with the socket,
In the vicinity of the first hole in the first fastening body, unevenness for positioning the first and second anti-vibration rubbers is formed,
An anti-vibration support structure for a railway vehicle, characterized in that a second hole for alignment is formed through the first fastening body 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, wherein the anti-vibration support structure is arranged. The anti-vibration support structure for a railway vehicle according to claim 1, wherein the third fastening body having the first and second holes is arranged in place of the 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. The anti-vibration support structure for a railway vehicle according to claim 3. The vibration isolating support structure for a railway vehicle according to claim 1, wherein the bolt penetrates the first hole from the side of the second fastening body.

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