Vibration control member and support structure of compressor

Abstract

To provide a vibration control member capable of maintaining a vibration control function while reducing a volume.SOLUTION: A vibration control member 12 is made of an elastic body, and has a through hole 12a that penetrates in an axial direction Z. The vibration control member 12 has a neck part 20 and a trunk part 24. The trunk part 24 has a plurality of thick-walled parts 40, and a plurality of thin-walled parts 42. When viewed in the axial direction Z, a protruding length of the thin-walled parts 42 relative to the neck part 20 in a radial direction of the through hole 12a is smaller than a protruding length of the thick-walled parts 40 relative to the neck part 20. When viewed in the axial direction Z, the plurality of thick-walled parts 40 and the plurality of thin-walled parts 42 are arranged alternately around the axial center of the trunk part 24.SELECTED DRAWING: Figure 2

Description

[Technical field]

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

[0002] Conventionally, in refrigerators and air conditioning equipment (hereinafter referred to as refrigerators, etc.), support structures have been proposed for suppressing transmission of vibrations generated in compressors to other members (housings, etc.) of the refrigerator, etc. For example, Patent Document 1 discloses a support device that supports a compressor with multiple supports. In the support device described in Patent Document 1, the multiple supports are made of elastic bodies to absorb vibrations of the compressor. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2002-235665 A Summary of the Invention [Problem to be solved by the invention]

[0004] In order to reduce the manufacturing cost of the above-mentioned support device, it is possible to reduce the volume of each support and thereby reduce the material cost. However, simply reducing the dimensions of the support reduces the vibration isolation function.

[0005] Therefore, an object of the present invention is to provide a vibration-isolating member that can maintain its vibration-isolating function while reducing its volume, and a support structure including the same. [Means for solving the problem]

[0006] The present 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 an external perspective view showing a conventional vibration-proof member. The conventional vibration-proof member 100 shown in Fig. 9 is made of an elastic body. The vibration-proof member 100 is formed with a through-hole 100a penetrating in the axial direction Z.

[0008] The vibration-proof 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 in the radial direction of the through hole 100a relative to the neck portion 102. 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-proof member shown in Fig. 9. In addition to the vibration-proof member 100, a part of a compressor 200 is shown in Fig. 10. Specifically, one of a plurality of mounting legs 202 that the compressor 200 has is shown.

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

[0011] In the above vibration-proof member 100, the present inventors attempted to reduce the volume of the vibration-proof member 100 by reducing the outer diameter of the body 106. However, it was found that when the outer diameter of the body 106 was reduced, the vibration-proof function was reduced.

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

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

[0014] Furthermore, the inventors conducted experiments to evaluate the vibration transmission characteristics (vibration isolation characteristics) in the axial direction and in the direction perpendicular to the axial direction for the vibration isolation member 100 with the body portion 106 and the vibration isolation member with the body portion 106a. As a result, there was no significant difference in the vibration transmission characteristics between the vibration isolation member 100 with the body portion 106 and the vibration isolation member with the body portion 106a. In other words, it was possible to maintain the vibration isolation function of the vibration isolation member while reducing the volume of the vibration isolation member. Regarding the direction perpendicular to the axial direction, the vibration transmission characteristics were evaluated in two directions indicated by arrows X1 and X2 in FIG. 11(a). As a result, there was no significant difference in the vibration transmission characteristics depending on the vibration direction. From these results, it was found that the vibration isolation member with the body portion 106a can properly exhibit the 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). For the vibration-proofing member with the body portion 106b, the vibration transmission characteristics (vibration-proofing characteristics) in the axial direction and in the direction perpendicular to the axial direction were also evaluated by experiment. As a result, there was no significant difference in the vibration transmission characteristics between the vibration-proofing member 100 with the body portion 106 and the vibration-proofing member with the body portion 106b. That is, it was possible to maintain the vibration-proofing function of the vibration-proofing member while further reducing the volume of the body portion 106b compared to the body portion 106. In addition, for the direction perpendicular to the axial direction, the vibration transmission characteristics were investigated in two directions indicated by arrows X3 and X4 in FIG. 11(b). As a result, there was no significant difference in the vibration transmission characteristics depending on the vibration direction. That is, it was found that the vibration-proofing member with the body portion 106b can also appropriately exhibit the vibration-proofing function regardless of the mounting direction to the compressor 200 (mounting leg 202).

[0016] The present invention has been completed based on the above findings, and its gist is the following vibration-isolating member and compressor support structure.

[0017] (1) A hollow vibration-proof member made of an elastic body and having a through hole passing through in the axial direction, A cylindrical body portion; A cylindrical neck portion is provided on one side of the body portion in the axial direction, the body portion has a plurality of thick-walled portions provided so as to protrude in a radial direction of the through hole relative to the neck portion when viewed in the axial direction, and a plurality of thin-walled portions each having a protruding length in the radial direction relative to the neck portion that is smaller than a protruding length of the thick-walled portions relative to the neck portion, A vibration-proof member, wherein when viewed in the axial direction, the multiple thick portions and the multiple thin portions are alternately arranged around the axis of the body portion.

[0018] (2) The vibration-damping member described in (1) above, wherein, when viewed from the axial direction, the multiple thick portions and the multiple thin portions are alternately arranged every 45° or 60° around the axis of the body portion.

[0019] (3) The vibration-proof member according to (1) or (2) above, wherein a tip end portion of the thick-walled portion in the radial direction is formed into an R-shaped or C-shaped surface when viewed from the axial direction.

[0020] (4) The vibration-damping member according to (1) or (2) above, wherein the body portion has a rectangular shape or a shape in which each vertex of a rectangle is formed into an R-shaped or C-shaped surface when viewed from the axial direction.

[0021] (5) The vibration-damping member according to (1) or (2) above, wherein the body portion has a triangular shape or a shape in which each apex of a triangle is formed into an R-shaped or C-shaped surface when viewed from the axial direction.

[0022] (6) The vibration-damping member according to (1) or (2) above, further comprising 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.

[0023] (7) A support structure for supporting a compressor having a plurality of mounting legs on a base, comprising: A support structure for a compressor, wherein the plurality of mounting legs are supported on the base by a plurality of the vibration isolation members. Effect of the Invention

[0024] 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. [Brief description of the drawings]

[0025] [Figure 1] FIG. 2 is a schematic diagram showing a support structure according to an embodiment of the present invention. [Diagram 2] FIG. 2 is an external perspective view showing a vibration-proof member according to one embodiment of the present invention. [Diagram 3] FIG. 3 is a front view showing the vibration-isolating member of FIG. [Figure 4] FIG. 4 is a cross-sectional view showing a portion AA in FIG. [Diagram 5] FIG. 5 is a cross-sectional view showing a portion BB in FIG. [Figure 6] FIG. 6 is an external perspective view showing a vibration-proof member according to another embodiment of the present invention. [Figure 7] FIG. 7 is a front view showing the vibration-isolating member. [Figure 8] FIG. 8 is a cross-sectional view showing a portion AA in FIG. [Figure 9] FIG. 9 is an external perspective view showing a conventional vibration-isolating member. [Figure 10] FIG. 10 is a diagram showing an example of use of the vibration-isolating member shown in FIG. [Figure 11] FIG. 11 is a diagram for explaining the shape of the body portion examined by the present inventors. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0026] Hereinafter, a vibration-isolating 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-isolating member according to an embodiment of the present invention. Fig. 3 is a front view showing the vibration-isolating member, Fig. 4 is a cross-sectional view showing part AA in Fig. 3, and Fig. 5 is a cross-sectional view showing part BB in Fig. 3.

[0027] As shown in FIG. 1, the 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-proof members 12 to correspond to a plurality of mounting legs 202 of the compressor 200. Each vibration-proof member 12 is made of an elastic body such as rubber. Various rubbers can be used as the material for the vibration-proof member 12. Specifically, for example, one or more types 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 can be suitably used as the material for the vibration-proof member 12. In particular, it is particularly suitable to include isobutylene-isopropylene copolymer rubber (IIR) which has high vibration-proofing performance. The same applies to the embodiments described later.

[0028] The vibration-proof member 12 has a through hole 12a that penetrates in the axial direction Z (see FIG. 2). A rod-shaped member (such as a bolt) for fixing the vibration-proof member 12 is inserted into the through hole 12a. In this embodiment, each vibration-proof member 12, like the above-mentioned vibration-proof member 100, is attached to the base 300 and the mounting legs 202 by bolts 400 and nuts 402, thereby supporting the compressor 200 on the base 300.

[0029] As shown in Figs. 2 to 5, the vibration-proof 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 shape 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-proof 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 toward one side in the axial direction Z.

[0030] The body 24 is provided on the other side of the neck 20 in the axial direction Z of the vibration-proof member 12. The body 24 is formed in a cylindrical shape (in this embodiment, a rectangular cylindrical shape). In this embodiment, the through hole 12a has a circular cross section, but the cross section of the through hole 12a is not limited to a circular shape. When the cross section of the through hole 12a is not circular, the radial direction of the through hole 12a means the radial direction of a virtual circle centered on 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. 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 a virtual circle 26 circumscribing the body 24 is indicated by a dashed line.

[0031] As shown in FIG. 2 and FIG. 4, the body 24 has a plurality of thick portions 40 and a plurality of thin portions 42. When viewed from the axial direction Z, the protruding length of the thin portion 42 relative to the neck 20 in the radial direction (thickness of the thin portion 42 in the radial direction) is smaller than the protruding length of the thick portion 40 relative to the neck 20 in the radial direction (thickness of the thick portion 40 in the radial direction). The plurality of thick portions 40 and the plurality of thin portions 42 are alternately provided around the axis of the body 24. In this embodiment, the plurality of thick portions 40 and the plurality of thin portions 42 are provided at 45° intervals around the axis of the body 24. Note that, as shown in FIG. 4, in this embodiment, the plurality of thick portions 40 and the plurality of thin portions 42 are provided so as to protrude radially outward from the neck 20 as a whole when viewed from the axial direction Z. However, a part of the thin portion 42 may not 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 portion 42 (the intermediate portion between the thick portions 40) may be flush with the outer circumferential surface of the neck 20. The same applies to the embodiments described below.

[0032] 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 faces of the thick portions 40, and the narrow portions 42a are end faces of the thin portions 42. When viewed from 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.

[0033] 2 and 4, the tip 40b of the thick-walled portion 40 in the radial direction is formed into a rounded (arcuate) shape when viewed from the axial direction Z. In this embodiment, the body 24 has a quadrangle shape with each vertex curved into a rounded shape when viewed from the axial direction Z.

[0034] (Action and effect) In the vibration-proof member 12 according to this embodiment, the body 24 has a plurality of thick portions 40 and a plurality of thin portions 42. By increasing the amount of protrusion of each thick portion 40 from the neck portion 20, the diameter of an imaginary circle 26 circumscribing the body 24 can be increased. In this case, the compressor 200 can be stably supported by the body 24, so that a sufficient vibration-proof function can be realized. On the other hand, by providing the thin portions 42 between the adjacent thick portions 40, the volume of the body 24 can be reduced. That is, in the vibration-proof member 12 according to this embodiment, the volume can be reduced while maintaining the vibration-proof function.

[0035] The vibration-proof member 12 can be manufactured, for example, by using a mold having a plurality of cavities corresponding to the shape of the vibration-proof member 12. In this embodiment, the outer edge of the thin-walled portion 42 is provided so as to pass inside the imaginary circle 26 circumscribing the body portion 24 (the plurality of thick-walled portions 40) as viewed from the axial direction Z. In this case, the plurality of cavities for molding the body portion 24 can be arranged with smaller gaps between them than when a plurality of cavities corresponding to a circular body portion are formed in a mold. This not only reduces the material cost of the vibration-proof member 12, but also makes it possible to increase the number of vibration-proof members 12 that can be obtained from one mold. Therefore, the vibration-proof member 12 can be manufactured efficiently at low cost.

[0036] Furthermore, in the vibration-proof member 12 according to this embodiment, the tip 40b of each thick portion 40 is curved in an R-surface shape. In this case, the vibration-proof member 12 can be removed from the mold more easily than when the tip of the thick portion has a pointed shape. Furthermore, the width of the tip 40b in the circumferential direction of the body 24 can be increased, so that the compressor 200 can be supported more stably. Although not shown in the drawings, the tip 40b of the thick portion 40 may be formed in a C-surface shape (straight line). In this case, the same effect can be obtained.

[0037] In this embodiment, a jaw portion 22 is provided on one side of the neck portion 20 in the axial direction Z. This makes it possible to prevent the mounting legs 202 from coming out of the vibration-proof member 12 upward when the compressor 200 is supported by the vibration-proof member 12. As a result, the compressor 200 can be supported more stably. The same applies to the embodiments described below.

[0038] (Other embodiments) In the above embodiment, the case where the body 24 has a substantially rectangular shape as viewed from the axial direction Z has been described, but the shape of the body is not limited to the above example. Fig. 6 is an external perspective view showing a vibration-proof member according to another embodiment of the present invention, and Fig. 7 is a front view showing the vibration-proof member. Fig. 8 is a cross-sectional view showing the AA portion of Fig. 7.

[0039] 6 to 8, vibration-proof member 13 according to this embodiment has a neck 30, a jaw 32 provided on one side of neck 30 in axial direction Z of vibration-proof member 13, and a body 34 provided on the other side of neck 30 in axial direction Z. In Fig. 8, the position of the outer edge of neck 30 as viewed from axial direction Z is indicated by a dashed line, and an imaginary circle 36 circumscribing body 34 is indicated by a dashed line.

[0040] Similar to the above-described vibration-proof member 12, the vibration-proof member 13 is formed with a through hole 13a penetrating in the axial direction Z. Note that the neck portion 30 and the jaw portion 32 can be configured similarly to the neck portion 20 and the jaw portion 22 of the above-described vibration-proof member 12, and therefore a description thereof will be omitted.

[0041] As shown in Figs. 6 and 8, the body 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 34 that protrudes radially outward from the neck 30 as viewed from the axial direction Z. As viewed from the axial direction Z, the protruding length of the thin portion 48 relative to the neck 30 in the radial direction is smaller than the protruding length of the thick portion 46 relative to the neck 30. The plurality of thick portions 46 and the plurality of thin portions 48 are alternately provided around the axis of the body 34. In this embodiment, the plurality of thick portions 46 and the plurality of thin portions 48 are provided at intervals of 60° around the axis of the body 34.

[0042] In this embodiment, the end surface 34a on one side of the body 34 in the axial direction Z also 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 faces of the thick portions 46, and the narrow portions 48a are end faces of the thin portions 48. When viewed from the axial direction Z, the protruding length of the narrow portions 48a relative to the neck 30 in the radial direction is smaller than the protruding length of the wide portions 46a relative to the neck 30.

[0043] 6 and 8, in this embodiment, the tip portion 46b of the thick portion 46 in the radial direction is formed into a rounded (arcuate) shape when viewed from the axial direction Z. In this embodiment, the body portion 34 has a shape in which each apex of a triangle is curved into a rounded shape when viewed from the axial direction Z.

[0044] (Action and effect) In the vibration-proof member 13 according to this embodiment, the body 34 also has a plurality of thick portions 46 and a plurality of thin portions 48. By increasing the amount of protrusion of each thick portion 46 from the neck portion 30, the diameter of the imaginary circle 36 circumscribing the body 34 can be increased. In this case, the compressor 200 can be stably supported by the body 34, so that a sufficient vibration-proofing function can be realized. On the other hand, by providing the thin portions 48 between the adjacent thick portions 46, the volume of the body 34 can be reduced. Therefore, in the vibration-proof member 13 according to this embodiment, the volume can be reduced while maintaining the vibration-proofing function.

[0045] 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.

[0046] Moreover, in the vibration-proof member 13 according to this embodiment, the tip 46b of each thick portion 46 is curved in an R-shaped manner. This allows the vibration-proof member 13 to be easily removed from the mold. Furthermore, the width of the tip 46b in the circumferential direction of the body 34 can be increased, so that the compressor 200 can be supported more stably. Although not shown in the drawings, the tip 46b of the thick portion 46 may be formed in a C-shaped (straight) shape. In this case as well, the same effect can be obtained.

[0047] (Modification) In the above embodiment, the case where the body portion 24 has a shape in which each vertex of a rectangle is formed into an R-shaped or C-shaped surface 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. Also, in the above embodiment, the case where the body portion 34 has a shape in which each vertex of a triangle is formed into an R-shaped or C-shaped surface 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.

[0048] In the above-mentioned embodiment, the vibration-isolating members 12, 13 have the jaws 22, 32, but the jaws do not have to be provided. However, from the viewpoint of reliably preventing the compressor 200 (mounting legs 202) from coming off the vibration-isolating members upward, it is preferable that the vibration-isolating members have jaws. EXAMPLES

[0049] The effects of the vibration-isolating member according to the present invention will be described below with reference to examples, but the present invention is not limited to the following examples.

[0050] The vibration transmission characteristics (vibration isolation characteristics) were evaluated for the vibration isolation member 12 of Example 1 shown in Figs. 2 to 5, the vibration isolation member 13 of Example 2 shown in Figs. 6 to 8, and the vibration isolation member 100 of the comparative example shown in Fig. 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 (dimensions in the axial direction) of the vibration isolation members 12, 13, and 100 of Examples 1 and 2 and the comparative example were made equal to each other, and the dimensions of the neck and jaw were also made equal. The diameters of the imaginary circles 26, 36 (see Figs. 4 and 8) circumscribing the body parts 24, 34 of the vibration isolation members 12, 13 of Examples 1 and 2 and the diameter of the body part 106 (see Fig. 9) of the vibration isolation member 100 of the comparative example were made equal.

[0051] A sine wave sweep vibration test was performed on the vibration-proof members 12, 13, and 100 of Examples 1 and 2 and Comparative Example to measure the resonance frequency and the maximum value of the vibration transmissibility (vibration transmissibility at resonance). In the vibration test of Example 1, three vibration-proof members 12 were prepared, and a weight member (7.5 kg) was supported on the stage of a vibration tester by the three vibration-proof members 12. Vibrations were applied to the stage in the vertical direction (axial direction Z) and the horizontal direction (directions indicated by arrows X1 and X2 in FIG. 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-proof members 12 was measured. The vibration transmitted to the weight member was measured by a vibration meter attached to the weight member. As shown in FIG. 4, the horizontal direction X1 is a direction perpendicular to the outer surface 42b of any thin-walled portion 42 as viewed from the axial direction Z of the vibration-proof member 12. The horizontal direction X2 is a direction 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.

[0052] 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-proof 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) to measure the vibration (acceleration) transmitted from the stage to the weight member via the three vibration-proof members 13. As shown in FIG. 8, when viewed from the axial direction Z of the vibration-proof member 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 by 60° with respect to the horizontal direction X3. The vibration conditions applied to the stage during the test were the same as those of Example 1.

[0053] In the vibration test of the comparative example, three vibration-proof 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.

[0054] The vibration test results for Examples 1 and 2 and the Comparative Example are shown in Tables 1 to 3 below. Note that 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 vibration meter is G O is a value calculated by the following formula. The following Tables 1 to 3 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) = 20log 10 (G O / G I )

[0055] [Table 1] [Table 2] [Table 3]

[0056] As shown in Tables 1 to 3, in the vibration tests of Examples 1 and 2 and the comparative example, there was no significant difference in the maximum values ​​of the resonant frequency and vibration transmissibility for vibration in the horizontal direction. In addition, in the vibration tests of Examples 1 and 2 and the comparative example, there was no significant difference in the maximum values ​​of the resonant frequency and vibration transmissibility for vibration in the vertical direction. From this result, it can be seen that the vibration-proof members 12 and 13 of Examples 1 and 2 and the vibration-proof member 100 of the comparative example have similar vibration transmission characteristics (vibration-proof characteristics) for vibration in the horizontal and vertical directions (axial direction Z). From the above, it can be seen that the vibration-proof members 12 and 13 according to the present invention can reduce the volume while maintaining the vibration-proof function.

[0057] Furthermore, as shown in Table 1, there was no significant difference in the maximum resonant frequency and vibration transmissibility between the vibration-proof member 12 of Example 1 being subjected to vibration in the horizontal direction X1 and the vibration in the horizontal direction X2. Similarly, as shown in Table 2, there was no significant difference in the maximum resonant frequency and vibration transmissibility between the vibration-proof member 13 of Example 2 being subjected to vibration in the horizontal direction X3 and the vibration in the horizontal direction X4. These results show that the vibration-proof members 12 and 13 according to the present invention can adequately exhibit their vibration-proofing function regardless of the mounting direction to the compressor 200 (mounting legs 202). [Industrial Applicability]

[0058] According to the present invention, it is possible to reduce the volume of the vibration-isolating member while maintaining the vibration-isolating function. [Explanation of symbols]

[0059] 10 Support structure 12,13 Vibration-proof members 20,30 Neck 22,32 Jaw 24,34 Torso 40,46 Thick wall part 42,48 Thin section 200 Compressor 300 base

Claims

1. A hollow vibration-proof member made of an elastic body and having a through hole penetrating in an axial direction, A cylindrical body portion; A cylindrical neck portion is provided on one side of the body portion in the axial direction, the body portion has a plurality of thick-walled portions provided so as to protrude in a radial direction of the through hole relative to the neck portion when viewed in the axial direction, and a plurality of thin-walled portions each having a protruding length in the radial direction relative to the neck portion that is smaller than a protruding length of the thick-walled portions relative to the neck portion, A vibration-proof member, wherein when viewed in the axial direction, the multiple thick portions and the multiple thin portions are alternately arranged around the axis of the body portion.

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

3. 3. The vibration-proof member according to claim 1, wherein a tip end portion of the thick-walled portion in the radial direction is formed into an R-surface shape or a C-surface shape when viewed from the axial direction.

4. 3. The vibration-proof member according to claim 1, wherein the body portion has a quadrangular shape or a quadrangular shape in which each vertex is formed into a rounded or chamfered shape when viewed from the axial direction.

5. 3. The vibration-proof member according to claim 1, 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.

6. The vibration-proof member according to claim 1 or 2, further comprising 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.

7. A support structure for supporting a compressor having a plurality of mounting legs on a base, comprising: A support structure for a compressor, wherein the plurality of mounting legs are supported on the base by a plurality of the vibration isolating members according to claim 1.

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