Vibration-proofing member and support structure of compressor

Abstract

A vibration-proofing member 12 is made of an elastic body and has a through-hole 12a penetrating in an axial direction Z. The vibration-proofing member 12 has a neck part 20 and a body part 24. The body part 24 has a plurality of thick-walled parts 40 and a plurality of thin-walled parts 42. When viewed from the axial direction Z, the protruding length of the thin-walled part 42 in the radial direction of the through-hole 12a with respect to the neck part 20 is smaller than the protruding length of the thick-walled part 40 with respect to the neck part 20. When viewed from the axial direction Z, the plurality of thick-walled parts 40 and the plurality of thin-walled parts 42 are alternately provided around the axis of the body part 24.

Description

Vibration-isolating member and compressor support structure

[0001] The present invention relates to a vibration-isolating member and a support structure for a compressor.

[0002] Conventionally, support structures have been proposed for refrigerators and air conditioning equipment (hereinafter referred to as refrigerators, etc.) to suppress transmission of vibrations generated in a compressor to other components (such as a housing) of the refrigerator, etc. For example, Patent Document 1 discloses a support device that supports a compressor using multiple support bodies. In the support device described in Patent Document 1, the multiple support bodies are made of elastic bodies, thereby absorbing vibrations of the compressor.

[0003] Japanese Patent Application Laid-Open No. 2002-235665

[0004] One way to reduce the manufacturing costs of the support device described above is to reduce the volume of each support member, thereby reducing material costs. However, simply reducing the dimensions of the support members reduces the vibration isolation function.

[0005] SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a vibration-isolating member that can maintain vibration-isolating function while reducing the volume, and a support structure including the same.

[0006] The inventors have carried out the following investigations into a configuration for reducing the volume of the vibration-isolating member while maintaining the vibration-isolating function.

[0007] Fig. 9 is a perspective view showing the appearance of a conventional vibration-damping member. The conventional vibration-damping member 100 shown in Fig. 9 is made of an elastic body. The vibration-damping member 100 has a through-hole 100a that penetrates in the axial direction Z.

[0008] The vibration-damping member 100 has a neck portion 102, a jaw portion 104, and a body portion 106. The neck portion 102 has a cylindrical shape. The jaw portion 104 is provided on one side of the neck portion 102 in the axial direction Z. The jaw portion 104 is formed in an annular shape so as to protrude radially from the neck portion 102 in the through hole 100a. The body portion 106 has a cylindrical shape and is provided on the other side of the neck portion 102 in the axial direction Z.

[0009] Fig. 10 is a diagram showing an example of use of the vibration-damping member shown in Fig. 9. In addition to the vibration-damping member 100, Fig. 10 also shows a part of a compressor 200. Specifically, one of a plurality of mounting legs 202 that the compressor 200 has is shown.

[0010] As shown in Fig. 10 , vibration-isolating member 100 is used to support compressor 200 on base 300 of a refrigerator or the like. In the example shown in Fig. 10 , neck portion 102 of vibration-isolating member 100 is fitted into mounting hole 202a formed in mounting leg 202. In this state, bolt 400 is inserted from below base 300 into mounting hole 300a formed in base 300 and through hole 100a (see Fig. 9 ) of vibration-isolating member 100, and nut 402 is fitted onto the tip of bolt 400. By tightening nut 402, jaw portion 104 presses mounting leg 202 against body portion 106, and body portion 106 is pressed against base 300. Vibration-isolating members 100 are attached to each of the multiple mounting legs 202 of compressor 200 in the same manner. As a result, the compressor 200 is elastically supported on the base 300 by the plurality of vibration-proof members 100 , and vibrations generated in the compressor 200 can be prevented from being transmitted to the base 300 .

[0011] In the above vibration-damping member 100, the inventors attempted to reduce the volume of the vibration-damping member 100 by reducing the outer diameter of the body portion 106. However, it was found that reducing the outer diameter of the body portion 106 resulted in a decrease in the vibration-damping function.

[0012] Next, the inventors attempted to reduce the volume of the body portion while ensuring a sufficient diameter of the circle circumscribing the body portion when viewed in the axial direction. Fig. 11 is a diagram illustrating the shape of the body portion investigated by the inventors. Fig. 11 also shows the shape of the outer edge of the body portion as viewed from one side in the axial direction of the vibration-damping member. In Fig. 11, the shape of the outer edge of the body portion 106 of the vibration-damping member 100 shown in Fig. 9 is shown by a dashed dotted line, and the shapes of the outer edges of body portions 106a, 106b, which have a reduced volume compared to the body portion 106, are shown by a solid line.

[0013] The inventor first considered making the outer peripheral edge of the body portion 106a into a substantially square shape, as shown in Fig. 11(a) . In this case, the diameter of the circle circumscribing the body portion 106a can be kept equal to the diameter of the body portion 106, while the volume of the body portion 106a can be sufficiently reduced compared to the body portion 106.

[0014] Furthermore, the inventors conducted experiments to evaluate the vibration transmission characteristics (vibration isolation characteristics) of the vibration isolation member 100 including the body portion 106 and the vibration isolation member including the body portion 106a in the axial direction and in the direction perpendicular to the axial direction. The results showed no significant difference in the vibration transmission characteristics between the vibration isolation member 100 including the body portion 106 and the vibration isolation member including the body portion 106a. In other words, the vibration isolation function of the vibration isolation member could be maintained while reducing the volume of the vibration isolation member. Regarding the direction perpendicular to the axial direction, the vibration transmission characteristics were evaluated in the two directions indicated by arrows X1 and X2 in FIG. 11(a). The results showed no significant difference in the vibration transmission characteristics depending on the vibration direction. These results demonstrate that the vibration isolation member including the body portion 106a can adequately perform its vibration isolation function regardless of the mounting direction to the compressor 200 (mounting leg 202).

[0015] Next, the inventors considered forming the outer periphery of the body portion 106b into a substantially triangular shape, as shown in FIG. 11(b). Experiments were also conducted to evaluate the vibration transmission characteristics (vibration isolation characteristics) of the vibration-isolating member including the body portion 106b in the axial direction and in the direction perpendicular to the axial direction. As a result, no significant difference in the vibration transmission characteristics was found between the vibration-isolating member 100 including the body portion 106 and the vibration-isolating member including the body portion 106b. That is, the volume of the body portion 106b was further reduced compared to the body portion 106, while maintaining the vibration-isolating function of the vibration-isolating member. Furthermore, for the direction perpendicular to the axial direction, the vibration transmission characteristics were investigated in the two directions indicated by arrows X3 and X4 in FIG. 11(b). As a result, no significant difference in the vibration transmission characteristics was found depending on the vibration direction. That is, it was found that the vibration-isolating member including the body portion 106b can also adequately perform its vibration-isolating function regardless of the mounting direction to the compressor 200 (mounting leg 202).

[0016] The present invention was completed based on the above findings.

[0017] (1) A vibration-damping member according to one embodiment of the present invention is a hollow vibration-damping member made of an elastic body and having a through hole formed therethrough in the axial direction, and comprises: a cylindrical body portion; and a cylindrical neck portion provided on one side of the body portion in the axial direction, wherein the body portion has a plurality of thick-walled portions provided so as to protrude radially from the through hole relative to the neck portion when viewed in the axial direction, and a plurality of thin-walled portions whose protruding length from the neck portion in the radial direction is smaller than the protruding length of the thick-walled portions from the neck portion, and wherein the plurality of thick-walled portions and the plurality of thin-walled portions are provided alternately around the axis of the body portion when viewed in the axial direction.

[0018] (2) When viewed from the axial direction, the plurality of thick portions and the plurality of thin portions may be provided alternately at intervals of 45° or 60° around the axis of the body portion.

[0019] (3) When viewed from the axial direction, the body portion may be tangent to an imaginary circle at tip ends of the plurality of thick portions in the radial direction.

[0020] (4) The tip end of the thick portion in the radial direction may be formed into a rounded or chamfered shape when viewed from the axial direction.

[0021] (5) The body portion may have a quadrangular shape when viewed from the axial direction, or a quadrangular shape in which each vertex is formed into an R-surface or C-surface.

[0022] (6) The body portion may have a triangular shape when viewed from the axial direction, or a shape in which each vertex of the triangle is formed into an R-surface or C-surface.

[0023] (7) The vibration-damping member may further include an annular jaw portion provided on one side of the neck portion in the axial direction and protruding in the radial direction relative to the neck portion.

[0024] (8) A support structure according to one embodiment of the present invention is a support structure for supporting a compressor having a plurality of mounting legs on a base, wherein the plurality of mounting legs are supported on the base by a plurality of the vibration-damping members.

[0025] According to the present invention, it is possible to reduce the volume of the vibration-isolating member while maintaining the vibration-isolating function of the vibration-isolating member.

[0026] FIG. 1 is a schematic diagram showing a support structure according to one embodiment of the present invention. FIG. 2 is an external perspective view showing a vibration-damping member according to one embodiment of the present invention. FIG. 3 is a front view showing the vibration-damping member of FIG. 2. FIG. 4 is a cross-sectional view showing the A-A portion of FIG. 3. FIG. 5 is a cross-sectional view showing the B-B portion of FIG. 3. FIG. 6 is an external perspective view showing a vibration-damping member according to another embodiment of the present invention. FIG. 7 is a front view showing a vibration-damping member. FIG. 8 is a cross-sectional view showing the A-A portion of FIG. 7. FIG. 9 is an external perspective view showing a conventional vibration-damping member. FIG. 10 is a diagram showing an example of use of the vibration-damping member shown in FIG. 9. FIG. 11 is a diagram for explaining the shape of the body portion studied by the present inventors.

[0027] Hereinafter, a vibration-damping member and a support structure for a compressor according to an embodiment of the present invention will be described with reference to the drawings. Fig. 1 is a schematic diagram showing a support structure according to an embodiment of the present invention, and Fig. 2 is an external perspective view showing a vibration-damping member according to an embodiment of the present invention. Fig. 3 is a front view of the vibration-damping member, Fig. 4 is a cross-sectional view showing the A-A portion of Fig. 3, and Fig. 5 is a cross-sectional view showing the B-B portion of Fig. 3.

[0028] As shown in FIG. 1 , a support structure 10 according to this embodiment is provided to support a compressor 200 on a base 300. The support structure 10 includes a plurality of (three in this embodiment) vibration-damping members 12 corresponding to the plurality of mounting legs 202 of the compressor 200. Each vibration-damping member 12 is made of an elastic material such as rubber. Various rubbers can be used as the material for the vibration-damping members 12. Specifically, the vibration-damping members 12 can be made of one or more rubbers selected from the group consisting of isobutylene-isoprene copolymer rubber (IIR), natural rubber (NR), isoprene rubber (IR), butadiene rubber (BR), styrene-butadiene copolymer rubber (SBR), acrylonitrile-butadiene copolymer rubber (NBR), and ethylene-propylene copolymer rubber. It is particularly preferable to include isobutylene-isopropylene copolymer rubber (IIR), which has high vibration-damping performance, in the material for the vibration-damping members 12. This also applies to the embodiments described below.

[0029] Each vibration-damping member 12 has a through-hole 12a formed therethrough in the axial direction Z (see FIG. 2 ). A rod-shaped member (such as a bolt) is inserted into the through-hole 12a to fix the vibration-damping member 12. In this embodiment, each vibration-damping member 12, like the vibration-damping member 100 described above, is attached to the base 300 and the mounting legs 202 with bolts 400 and nuts 402, thereby supporting the compressor 200 on the base 300.

[0030] 2 to 5, the vibration-damping member 12 has a neck portion 20, a jaw portion 22, and a body portion 24. The neck portion 20 is formed in a tubular shape (cylindrical in this embodiment). The jaw portion 22 is provided on one side of the neck portion 20 in the axial direction Z of the vibration-damping member 12. The jaw portion 22 is formed in an annular shape so as to protrude in the radial direction of the through hole 12a relative to the neck portion 20. In this embodiment, the jaw portion 22 is formed in a tapered shape so that the diameter becomes smaller on one side in the axial direction Z.

[0031] The body 24 is provided on the other side of the neck 20 in the axial direction Z of the vibration-damping member 12. The body 24 is formed in a cylindrical shape (a rectangular cylindrical shape in this embodiment). Note that in this embodiment, the through hole 12a has a circular cross section; however, the cross section of the through hole 12a is not limited to a circular shape. If the cross section of the through hole 12a is not circular, the radial direction of the through hole 12a refers to the radial direction of an imaginary circle centered at the center of the through hole 12a as viewed from the axial direction Z. This also applies to the embodiments described below. Hereinafter, the radial direction of the through hole 12a will be simply referred to as the radial direction. Note that in FIG. 4 , the position of the outer edge of the neck 20 as viewed from the axial direction Z is indicated by a dashed line, and an imaginary circle 26 circumscribing the body 24 is indicated by a dashed line. In this embodiment, the imaginary circle 26 is a circle centered at the center of the through hole 12a as viewed from the axial direction Z.

[0032] As shown in FIGS. 2 and 4 , the body 24 has a plurality of thick-walled portions 40 and a plurality of thin-walled portions 42. When viewed from the axial direction Z, the protruding length of the thin-walled portions 42 relative to the neck 20 in the radial direction (the thickness of the thin-walled portions 42 in the radial direction) is smaller than the protruding length of the thick-walled portions 40 relative to the neck 20 in the radial direction (the thickness of the thick-walled portions 40 in the radial direction). The plurality of thick-walled portions 40 and the plurality of thin-walled portions 42 are alternately arranged around the axis of the body 24. In this embodiment, the plurality of thick-walled portions 40 and the plurality of thin-walled portions 42 are arranged at 45° intervals around the axis of the body 24. Note that, as shown in FIG. 4 , in this embodiment, the entire plurality of thick-walled portions 40 and the entire plurality of thin-walled portions 42 are arranged to protrude radially outward from the neck 20 when viewed from the axial direction Z. However, a portion of the thin-walled portion 42 does not have to protrude radially outward from the neck 20. For example, in the circumferential direction of the body 24, the outer surface of the center of each thin-walled portion 42 (the intermediate portion between the thick-walled portions 40) may be flush with the outer peripheral surface of the neck 20. The same applies to the embodiments described below.

[0033] As shown in FIG. 1 , an end surface 24a on one side of the body portion 24 in the axial direction Z functions as a support surface that supports the compressor 200 (mounting leg 202). Hereinafter, the end surface 24a will be referred to as the support surface 24a. As shown in FIG. 2 , in this embodiment, the support surface 24a is formed in a flat shape. The support surface 24a includes a plurality of wide portions 40a and a plurality of narrow portions 42a. The wide portions 40a are end surfaces of the thick portions 40, and the narrow portions 42a are end surfaces of the thin portions 42. When viewed in the axial direction Z, the protruding length of the narrow portions 42a relative to the neck portion 20 in the radial direction is smaller than the protruding length of the wide portions 40a relative to the neck portion 20.

[0034] As shown in Figures 2 and 4, the tip end portions 40b of the thick-walled portions 40 in the radial direction are formed in a rounded (arcuate) shape when viewed from the axial direction Z. In this embodiment, the body portion 24 has a shape in which each vertex of a rectangle is curved in a rounded shape when viewed from the axial direction Z. In this embodiment, the body portion 24 has a shape in which each vertex of a square is curved in a rounded shape when viewed from the axial direction Z. In this embodiment, the body portion 24 is formed so that the tip end portions 40b of the multiple thick-walled portions 40 are tangent to a common imaginary circle 26 when viewed from the axial direction Z. Furthermore, each tip end portion 40b is formed in a rounded shape so as to coincide with a part of the imaginary circle 26 when viewed from the axial direction Z.

[0035] (Effects) In the vibration-damping member 12 according to this embodiment, the body 24 has a plurality of thick-walled portions 40 and a plurality of thin-walled portions 42. By increasing the amount that each thick-walled portion 40 protrudes from the neck 20, the diameter of the imaginary circle 26 circumscribing the body 24 can be increased. In this case, the body 24 can stably support the compressor 200, thereby achieving sufficient vibration-damping functionality. Meanwhile, by providing the thin-walled portions 42 between adjacent thick-walled portions 40, the volume of the body 24 can be reduced. In other words, the vibration-damping member 12 according to this embodiment can maintain its vibration-damping functionality while reducing its volume.

[0036] The vibration-damping member 12 can be manufactured, for example, using a mold having multiple cavities corresponding to the shape of the vibration-damping member 12. In this embodiment, when viewed from the axial direction Z, the outer edge of the thin-walled portion 42 is arranged to pass inside the imaginary circle 26 that circumscribes the body portion 24 (the multiple thick-walled portions 40). In this case, compared to when multiple cavities corresponding to a circular body portion are formed in a mold, the multiple cavities for molding the body portion 24 can be arranged with smaller gaps between them. This not only reduces the material cost of the vibration-damping member 12, but also allows a larger number of vibration-damping members 12 to be produced from a single mold. Therefore, the vibration-damping member 12 can be manufactured efficiently at low cost.

[0037] Furthermore, in the vibration-damping member 12 according to this embodiment, the multiple thick-walled portions 40 and the multiple thin-walled portions 42 are alternately arranged at 45° intervals around the axis of the body portion 24. This prevents differences in vibration transmission characteristics depending on the direction of vibration transmitted to the vibration-damping member 12. For example, as shown by arrows X1 and X2 in FIG. 4 , even when vibrations are transmitted to the vibration-damping member 12 in different directions, differences in vibration transmission characteristics can be prevented. Furthermore, in the vibration-damping member 12 according to this embodiment, the body portion 24 is formed such that the tip ends 40b of the multiple thick-walled portions 40 are tangent to the imaginary circle 26 when viewed from the axial direction Z. By configuring the body portion 24 in this manner, a sufficient area can be secured for the portion of the body portion 24 that supports the compressor 200. As a result, the compressor 200 can be supported more stably.

[0038] Furthermore, in the vibration-damping member 12 according to this embodiment, the tip end 40b of each thick-walled portion 40 is curved in an R-shaped manner. In this case, the vibration-damping member 12 is easier to remove from the mold than when the tip end of each thick-walled portion is pointed. Furthermore, the width of the tip end 40b in the circumferential direction of the body portion 24 can be increased, thereby more stably supporting the compressor 200. Although not shown, the tip end 40b of each thick-walled portion 40 may be formed in a C-shaped (linear) manner. Similar effects can be achieved in this case as well. Even when each tip end 40b is formed in a C-shaped manner, the body portion 24 is formed so that the tip ends 40b of the multiple thick-walled portions 40 are tangent to a common imaginary circle when viewed, for example, from the axial direction Z.

[0039] Furthermore, in this embodiment, a jaw portion 22 is provided on one side of the neck portion 20 in the axial direction Z. This prevents the mounting legs 202 from slipping out of the vibration-isolating member 12 when the compressor 200 is supported by the vibration-isolating member 12. As a result, the compressor 200 can be supported more stably. This also applies to the embodiments described below.

[0040] (Other Embodiments) In the above-described embodiment, the case where the body portion 24 has a substantially rectangular shape when viewed from the axial direction Z has been described, but the shape of the body portion is not limited to the above-described example. Fig. 6 is an external perspective view showing a vibration-damping member according to another embodiment of the present invention, and Fig. 7 is a front view showing the vibration-damping member. Fig. 8 is a cross-sectional view showing the A-A portion of Fig. 7.

[0041] 6 to 8, the vibration-damping member 13 according to this embodiment has a neck 30, a jaw 32 provided on one side of the neck 30 in the axial direction Z of the vibration-damping member 13, and a body 34 provided on the other side of the neck 30 in the axial direction Z. In Fig. 8, the position of the outer edge of the neck 30 as viewed from the axial direction Z is indicated by a dashed line, and an imaginary circle 36 circumscribing the body 34 is indicated by a dashed two-dot line. In this embodiment, the imaginary circle 36 is a circle centered on the center of a through hole 13a, which will be described later, as viewed from the axial direction Z.

[0042] Similar to the vibration-damping member 12 described above, the vibration-damping member 13 is formed with a through-hole 13a that penetrates in the axial direction Z. Note that the neck portion 30 and the jaw portion 32 can be configured in the same manner as the neck portion 20 and the jaw portion 22 of the vibration-damping member 12 described above, and therefore a description thereof will be omitted.

[0043] 6 and 8 , the body portion 34 has a plurality of thick portions 46 and a plurality of thin portions 48. In this embodiment, the plurality of thick portions 46 and the plurality of thin portions 48 are provided in a portion of the body portion 34 that protrudes radially outward beyond the neck portion 30 as viewed from the axial direction Z. As viewed from the axial direction Z, the protruding length of the thin portions 48 relative to the neck portion 30 in the radial direction is smaller than the protruding length of the thick portions 46 relative to the neck portion 30. The plurality of thick portions 46 and the plurality of thin portions 48 are alternately provided around the axis of the body portion 34. In this embodiment, the plurality of thick portions 46 and the plurality of thin portions 48 are provided every 60° around the axis of the body portion 34.

[0044] In this embodiment, too, the end surface 34a on one side of the body portion 34 in the axial direction Z functions as a support surface that supports the mounting leg 202 (see FIG. 1 ). Hereinafter, the end surface 34a will be referred to as the support surface 34a. As shown in FIG. 6 , in this embodiment, the support surface 34a is formed in a flat shape. The support surface 34a includes a plurality of wide portions 46a and a plurality of narrow portions 48a. The wide portions 46a are end surfaces of the thick portions 46, and the narrow portions 48a are end surfaces of the thin portions 48. When viewed in the axial direction Z, the protruding length of the narrow portions 48a from the neck portion 30 in the radial direction is smaller than the protruding length of the wide portions 46a from the neck portion 30.

[0045] As shown in Figures 6 and 8, in this embodiment, the tip ends 46b of the thick-walled portions 46 in the radial direction are formed in an R-shaped (arcuate) shape when viewed from the axial direction Z. In this embodiment, the body portion 34 has a shape in which each vertex of a triangle is curved in an R-shaped shape when viewed from the axial direction Z. In this embodiment, the body portion 34 has a shape in which each vertex of an equilateral triangle is curved in an R-shaped shape when viewed from the axial direction Z. In this embodiment, the body portion 34 is formed so that the tip ends 46b of the multiple thick-walled portions 46 are tangent to the common imaginary circle 36 when viewed from the axial direction Z. Furthermore, each tip end 46b is formed in an R-shaped shape so as to coincide with a part of the imaginary circle 36 when viewed from the axial direction Z.

[0046] (Effects) In the vibration-damping member 13 according to this embodiment, the body 34 also has a plurality of thick-walled portions 46 and a plurality of thin-walled portions 48. By increasing the amount of protrusion of each thick-walled portion 46 relative to the neck 30, the diameter of the imaginary circle 36 circumscribing the body 34 can be increased. In this case, the body 34 can stably support the compressor 200, thereby achieving sufficient vibration-damping functionality. Meanwhile, by providing the thin-walled portions 48 between adjacent thick-walled portions 46, the volume of the body 34 can be reduced. Therefore, in the vibration-damping member 13 according to this embodiment, the volume can be reduced while maintaining the vibration-damping functionality.

[0047] Also in this embodiment, the outer edge of the thin-walled portion 48 is provided so as to pass inside the imaginary circle 36 that circumscribes the body portion 34 (plurality of thick-walled portions 46) when viewed from the axial direction Z. Therefore, the multiple cavities for molding the body portion 34 can be arranged with smaller gaps between them than when multiple cavities corresponding to a circular body portion are formed in a mold.

[0048] Furthermore, in the vibration-damping member 13 according to this embodiment, the multiple thick-walled portions 46 and the multiple thin-walled portions 48 are alternately arranged at 60° intervals around the axis of the body portion 34. This prevents differences in vibration transmission characteristics depending on the direction of vibration transmitted to the vibration-damping member 13. For example, as shown by arrows X3 and X4 in FIG. 8 , even when vibrations are transmitted to the vibration-damping member 13 in different directions, differences in vibration transmission characteristics can be prevented. Furthermore, in the vibration-damping member 13 according to this embodiment, the body portion 34 is formed such that the tip ends 46b of the multiple thick-walled portions 46 are tangent to the imaginary circle 36 when viewed from the axial direction Z. By configuring the body portion 34 in this manner, a sufficient area can be secured for the portion of the body portion 34 that supports the compressor 200. As a result, the compressor 200 can be supported more stably.

[0049] Furthermore, in the vibration-damping member 13 according to this embodiment, the tip end 46b of each thick portion 46 is curved in an R-shaped manner. This allows the vibration-damping member 13 to be easily removed from the mold. Furthermore, the width of the tip end 46b in the circumferential direction of the body portion 34 can be increased, allowing the compressor 200 to be supported more stably. Although not shown, the tip end 46b of each thick portion 46 may be formed in a C-shaped (linear) manner. This also achieves the same effect. Note that even when each tip end 46b is formed in a C-shaped manner, the body portion 34 is arranged so that the tip ends 46b of the multiple thick portions 46 are tangent to a common imaginary circle when viewed, for example, from the axial direction Z.

[0050] (Modifications) In the above-described embodiment, the case where the body portion 24 has a shape in which each vertex of a rectangle is formed into an R-faceted or C-faceted shape when viewed from the axial direction Z has been described, but the body portion 24 may also be a rectangle when viewed from the axial direction Z. For example, the body portion 24 may also be a square when viewed from the axial direction Z. Furthermore, in the above-described embodiment, the case where the body portion 34 has a shape in which each vertex of a triangle is formed into an R-faceted or C-faceted shape when viewed from the axial direction Z has been described, but the body portion 34 may also be a triangle when viewed from the axial direction Z. For example, the body portion 34 may also be an equilateral triangle when viewed from the axial direction Z.

[0051] In the above-described embodiment, the vibration-isolating members 12, 13 have the jaws 22, 32, but the jaws may not be provided. However, from the viewpoint of reliably preventing the compressor 200 (mounting legs 202) from slipping out of the vibration-isolating members, it is preferable that the vibration-isolating members have jaws.

[0052] The effects of the vibration-isolating member according to the present invention will be explained below using examples, but the present invention is not limited to the following examples.

[0053] The vibration transmission characteristics (vibration isolation characteristics) were evaluated for the vibration isolation member 12 of Example 1 shown in Figures 2 to 5, the vibration isolation member 13 of Example 2 shown in Figures 6 to 8, and the vibration isolation member 100 of the comparative example shown in Figure 9. The vibration isolation member 12, the vibration isolation member 13, and the vibration isolation member 100 were made of the same material (elastic body). The heights (axial dimensions) of the vibration isolation members 12, 13, and 100 of Examples 1 and 2 and the comparative example were all equal, and the dimensions of the neck and jaw portions were also equal. The diameters of the imaginary circles 26, 36 (see Figures 4 and 8) circumscribing the body portions 24, 34 of the vibration isolation members 12, 13 of Examples 1 and 2 and the diameter of the body portion 106 (see Figure 9) of the vibration isolation member 100 of the comparative example were also equal.

[0054] A sine wave sweep vibration test was performed on the vibration-damping members 12, 13, and 100 of Examples 1 and 2 and the Comparative Example to measure the resonant frequency and the maximum value of vibration transmissibility (vibration transmissibility at resonance). In the vibration test of Example 1, three vibration-damping members 12 were prepared, and a weight member (7.5 kg) was supported on the stage of a vibration tester by the three vibration-damping members 12. Vibrations were applied to the stage in the vertical direction (axial direction Z) and horizontal directions (directions indicated by arrows X1 and X2 in Figure 4 , hereinafter referred to as horizontal directions X1 and X2), and the vibration (acceleration) transmitted from the stage to the weight member via the three vibration-damping members 12 was measured. The vibration transmitted to the weight member was measured using a vibrometer attached to the weight member. As shown in Figure 4 , when viewed from the axial direction Z of the vibration-damping member 12, the horizontal direction X1 is perpendicular to the outer surface 42b of any thin-walled portion 42. The horizontal direction X2 is inclined at 45° with respect to the horizontal direction X1. The vibration conditions applied to the stage during the test were acceleration: 0.3 G, frequency: 5 to 200 Hz, and sweep speed: 2 oct / min.

[0055] Similarly, in the vibration test of Example 2, a weight member (7.5 kg) was supported on the stage of the vibration tester by three vibration-isolating members 13. However, in the vibration test of Example 2, vibrations were applied to the stage in the vertical direction (axial direction Z) and the horizontal direction (directions indicated by arrows X3 and X4 in FIG. 8 ; hereinafter, referred to as horizontal directions X3 and X4), and the vibration (acceleration) transmitted from the stage to the weight member via the three vibration-isolating members 13 was measured. Note that, as shown in FIG. 8 , when viewed from the axial direction Z of the vibration-isolating members 13, the horizontal direction X3 is a direction perpendicular to the outer surface 48b of any thin-walled portion 48. The horizontal direction X4 is a direction inclined at 60° with respect to the horizontal direction X3. The vibration conditions applied to the stage during the test were the same as those in Example 1.

[0056] In the vibration test of the comparative example, three vibration-damping members 100 were prepared and the vibration test was carried out under the same conditions as in Examples 1 and 2. However, the horizontal vibration test was carried out in only one direction.

[0057] The vibration test results for Examples 1 and 2 and the comparative example are shown in Tables 1 to 3. The vibration transmissibility (dB) shown in Tables 1 to 3 is calculated by dividing the acceleration applied to the stage by G Ｉ, the acceleration measured by the vibrometer is G Ｏ The value is calculated by the following formula: Tables 1 to 3 below show the maximum vibration transmissibility calculated in each vibration test. When the vibration transmissibility exceeds 0, it means that the amplitude of the vibration transmitted from the stage to the weight member has increased, and when the vibration transmissibility is less than 0, it means that the amplitude of the vibration transmitted from the stage to the weight member has decreased. Vibration transmissibility (dB) = 20 log １０ (G Ｏ / G Ｉ )

[0058]

[0059] As shown in Tables 1 to 3, in the vibration tests of Examples 1 and 2 and the Comparative Example, no significant differences occurred in the resonant frequency and maximum vibration transmissibility for horizontal vibration. Furthermore, no significant differences occurred in the resonant frequency and maximum vibration transmissibility for vertical vibration for Examples 1 and 2 and the Comparative Example. These results demonstrate that the vibration-damping members 12 and 13 of Examples 1 and 2 and the vibration-damping member 100 of the Comparative Example have similar vibration transmission characteristics (vibration-damping characteristics) for vibration in the horizontal and vertical directions (axial direction Z). From the above, it can be seen that the vibration-damping members 12 and 13 of the present invention can reduce their volume while maintaining their vibration-damping function.

[0060] Furthermore, as shown in Table 1, there was no significant difference in the resonant frequency and the maximum vibration transmissibility of the vibration-damping member 12 of Example 1 when vibration was applied in the horizontal direction X1 and when vibration was applied in the horizontal direction X2. Similarly, as shown in Table 2, there was no significant difference in the resonant frequency and the maximum vibration transmissibility of the vibration-damping member 13 of Example 2 when vibration was applied in the horizontal direction X3 and when vibration was applied in the horizontal direction X4. These results demonstrate that the vibration-damping members 12, 13 of the present invention can adequately exhibit their vibration-damping function regardless of the mounting direction to the compressor 200 (mounting legs 202). More specifically, by providing multiple thick-walled portions and multiple thin-walled portions alternately at 45° or 60° intervals around the axis of the body portion and configuring the body portion so that the tips of the multiple thick-walled portions are tangent to an imaginary circle when viewed axially of the vibration-damping member, it was found that the vibration-damping function can be adequately exhibited regardless of the mounting direction of the vibration-damping member to the compressor.

[0061] According to the present invention, it is possible to reduce the volume of the vibration-isolating member while maintaining the vibration-isolating function.

[0062] 10 Support structure 12, 13 Vibration isolation member 20, 30 Neck portion 22, 32 Jaw portion 24, 34 Body portion 40, 46 Thick portion 42, 48 Thin portion 200 Compressor 300 Base

Claims

1. A hollow vibration-damping member made of an elastic body and having a through hole formed therethrough in the axial direction, comprising: a cylindrical body portion; and a cylindrical neck portion provided on one side of the body portion in the axial direction, wherein the body portion has a plurality of thick-walled portions provided to protrude radially from the through hole relative to the neck portion when viewed in the axial direction, and a plurality of thin-walled portions whose protruding length from the neck portion in the radial direction is smaller than the protruding length of the thick-walled portions from the neck portion, and wherein, when viewed in the axial direction, the plurality of thick-walled portions and the plurality of thin-walled portions are provided alternately around the axis of the body portion.

2. The vibration-proof member according to claim 1, wherein, when viewed in the axial direction, the plurality of thick-walled portions and the plurality of thin-walled portions are alternately provided at intervals of 45° or 60° around the axis of the body portion.

3. The vibration-proof member according to claim 2, wherein the body portion is tangent to an imaginary circle at the tips of the plurality of thick-walled portions in the radial direction when viewed from the axial direction.

4. An anti-vibration member according to any one of claims 1 to 3, wherein a tip end of the thick portion in the radial direction is formed into an R-surface or C-surface when viewed from the axial direction.

5. An anti-vibration member according to any one of claims 1 to 4, wherein the body portion has a rectangular shape or a rectangular shape with each vertex formed into an R-shaped or C-shaped surface when viewed from the axial direction.

6. An anti-vibration member according to any one of claims 1 to 4, wherein the body portion has a triangular shape or a shape in which each apex of a triangle is formed into an R-surface or C-surface shape when viewed from the axial direction.

7. An anti-vibration member as claimed in any one of claims 1 to 6, further comprising an annular jaw portion provided on one side of said neck portion in the axial direction and projecting in the radial direction relative to said neck portion.

8. A support structure for a compressor having a plurality of mounting legs for supporting the compressor on a base, the plurality of mounting legs being supported on the base by a plurality of vibration-isolating members as described in any one of claims 1 to 7.

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