JP2017145863A - Vibration isolation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration isolation device in which an orientation of vibration whose transmittance is restricted is not limited to one direction, but vibrations in two directions that are different from each other can be restricted.SOLUTION: A first spiral spring 24 is a non-contact type spiral spring. In addition, a rod member 20 has a first inner abutting part 203. The first inner abutting part 203 abuts against the first spiral spring 24 from inside at a spring radial direction DRr. Further, a first outer abutting part 222 of a first holder 221 abuts against the first spiral spring 24 from outside of the first spiral spring 24 at the spring radial direction DRr. Along with this operation, a first axial abutting part 223 of the first holder 221 abuts against the first spiral spring 24 at a position shifted to the spring radial direction DRr in respect to a location 242 to which a first prescribed abutting part 26 abuts in the first spiral spring 24. Accordingly, a vibration isolation device 10 enables a transmittance of vibrations in two directions that are different from each other at a rod member axial direction DRa and the spring radial direction DRr to be restricted.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a vibration isolator that suppresses vibration transmission.

  As this type of vibration isolator, for example, a vibration isolating bush described in Patent Document 1 is conventionally known. In the anti-vibration bush described in Patent Document 1, a gap is provided in a part of an elastic body such as rubber disposed between the inner cylinder and the outer cylinder. As a result, when the amplitude is small, the air gap is deformed according to the vibration, and when the amplitude is large, the air gap wall surfaces facing the air gap are in contact with each other. As a result, the spring constant is low when the amplitude is small, and the spring constant is large when the amplitude is large. As described above, the anti-vibration bush disclosed in Patent Document 1 provides a non-linear spring characteristic in which the spring constant increases as the amplitude increases.

JP 2006-312949 A

  In the vibration-proof bushing of Patent Document 1 described above, the spring constant changes only in one direction in which the gap is deformed. When suppressing the transmission of the vibration in the one direction, it seems that the deformation of the gap secures a sufficient deformation amount to suppress the transmission of the vibration.

  However, when suppressing vibrations in directions other than the one direction, that is, vibrations in a direction in which the gap does not deform, the suppression of vibration transmission depends on the elastic deformation of the elastic body itself such as rubber. To do. Therefore, when suppressing the transmission of vibrations in directions other than the one direction, it is considered difficult to ensure a sufficient amount of deformation to suppress vibration transmission. Thus, as a result of detailed studies by the inventors, it was considered that the vibration isolating bush of Patent Document 1 is insufficient to suppress the transmission of vibrations in directions other than the one direction.

  In view of the above points, the present invention provides a vibration isolator capable of suppressing the transmission of vibrations in two different directions without limiting the direction of vibrations to be suppressed in one direction. With the goal.

In order to achieve the above object, according to the first aspect of the present invention, the vibration isolator is a vibration isolator that suppresses vibration transmission, and
A rod-shaped rod member (20) fixed to the first vibrating section (121);
A second vibrating part (22) connected to the first vibrating part by a bar member;
Spiral springs (24, 28) wound in a spiral around the rod member;
A predetermined contact portion (26, 30) fixed to the first vibrating portion and contacting the spiral spring in the axial direction (DRa) of the rod member;
The spiral spring is formed so as to generate a radial gap (24a) between portions adjacent to each other in the radial direction (DRr) of the spiral spring.
The rod member has an inner contact portion (203, 204) that contacts the spiral spring from the radially inner side of the spiral spring,
The second vibration part has holder parts (221, 225) in which spiral springs are fitted,
The holder part is displaced in the radial direction from the radially outer side of the spiral spring with respect to the outer contact part (222, 226) contacting the spiral spring and the part (242) of the spiral spring where the predetermined contact part contacts. In this position, there are axial contact portions (223, 227) that contact the spiral spring from the side opposite to the predetermined contact portion in the axial direction.

  Thereby, the spiral spring can bend in each of the axial direction of the rod member and the radial direction of the spiral spring. Therefore, the vibration isolator can suppress transmission of vibrations in two different directions.

  In addition, each code | symbol in the bracket | parenthesis described in a claim and this column is an example which shows a corresponding relationship with the specific content as described in embodiment mentioned later.

It is sectional drawing which showed the structure of the suspension part containing the function as a vibration isolator of 1st Embodiment. It is sectional drawing which cut | disconnected the 1st vibration isolator in the cross section orthogonal to a rod member axial direction in 1st and 2nd embodiment, ie, sectional drawing which showed the II-II cross section in FIG. 1 and FIG. In 1st Embodiment, it is a front view of the 1st spiral spring which showed the 1st spiral spring of the free state single-piece | unit. FIG. 4 is a cross-sectional view showing a cross section taken along line IV-IV in FIG. 3, in which only the left half of the first spiral spring is shown in cross section. In 1st Embodiment, it is a schematic diagram for demonstrating how the 1st spiral spring bends to a rod member axial direction, Comprising: It is the figure which showed the 1st spiral spring in the no-load state of a vibration isolator. FIG. 5B is a schematic diagram for explaining how the first spiral spring bends in the axial direction of the rod member in the first embodiment, and is a first spiral compressed by receiving an axial compression load from the no-load state of FIG. 5A. It is the figure which showed the spring. In 1st Embodiment, it is the graph which showed the spring characteristic of the 1st spiral spring in the rod member axial direction. In 1st Embodiment, it is a schematic diagram for demonstrating the bending method of the 1st spiral spring to a spring radial direction, Comprising: It is the figure which showed the 1st spiral spring in the no-load state of a vibration isolator. FIG. 7B is a schematic diagram for explaining how the first spiral spring bends in the spring radial direction in the first embodiment, and shows the first spiral spring deformed by receiving a radial load from the no-load state of FIG. 7A. It is a figure. In 1st Embodiment, it is a schematic diagram for demonstrating the bending method of the 1st spiral spring to a spring radial direction, Comprising: The 1st spiral spring which received the radial load and was further deform | transformed from the state of FIG. 7B was shown. FIG. In 1st Embodiment, it is the graph which showed the spring characteristic of the 1st spiral spring in the spring radial direction. It is sectional drawing which showed the structure of the suspension part containing the function as a vibration isolator of 2nd Embodiment, Comprising: It is a figure equivalent to FIG. 1 of 1st Embodiment.

  Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
FIG. 1 is a cross-sectional view illustrating a configuration of a suspension unit 10 including a function as a vibration isolator of the present embodiment. The suspension unit 10 connects the compressor 14 to the engine 12, and is provided at an attachment location where the compressor 14 is attached to the engine 12. The suspension unit 10 includes a part of the engine 12 and a part of the compressor 14. For example, the compressor 14 is attached to the outer surface of the engine 12.

  For example, the compressor 14 has a plurality of connection parts connected to the engine 12, and the suspension part 10 is provided by the number of the connection parts. FIG. 1 shows one of the suspension portions 10 provided in each of a plurality of connecting portions. The suspension unit 10 also has a function as a vibration isolator that suppresses transmission of vibration between the engine 12 and the compressor 14. FIG. 1 shows a state where neither the engine 12 nor the compressor 14 vibrates, that is, a no-load state of the suspension unit 10 as a vibration isolator.

  The engine 12 is, for example, an internal combustion engine installed in an engine room of a vehicle, and generates a driving force for traveling. The compressor 14 constitutes a part of a refrigeration cycle included in an air conditioner that performs air conditioning in the passenger compartment, and compresses the refrigerant circulating in the refrigeration cycle.

  By the way, the engine 12 and the compressor 14 both vibrate while being driven. For example, when the vibration of the compressor 14 is transmitted to the engine 12, a sound caused by the vibration of the compressor 14 is emitted from the engine 12 to the outside of the vehicle. Radiated. When the engine 12 is driven, the vibration of the engine 12 and the driving sound of the engine 12 are radiated to the outside of the vehicle, so the driver is not aware of the noise caused by the compressor 14. However, when the engine is stopped or idling is stopped, the sound caused by the vibration of the compressor 14 is not erased by the engine sound, so that it is necessary to prevent the vibration of the compressor 14 from being transmitted to the engine 12. .

  Therefore, the suspension unit 10 serving as a vibration isolator is required to have a spring characteristic with a small spring constant in order to effectively suppress transmission of vibration with a minute amplitude such as vibration of the compressor 14.

  On the other hand, the engine 12 may generate a large amplitude vibration depending on the usage situation. If such a large-amplitude vibration is generated from the engine 12 and the spring characteristic with a small spring constant is maintained as it is in the suspension part 10, the vibration amplitude is determined by the spring deformation allowed by the suspension part 10. The tolerance limit of width (ie the limit of absorbable amplitude) is easily reached. If so, the vibration of the engine 12 is transmitted between the engine 12 and the compressor 14 in the same manner as when the suspension unit 10 as a vibration isolator is directly attached, and the durability of the compressor 14 is improved. There is a risk of damage.

  Therefore, in the suspension part 10, in order to prevent the amplitude of the vibration from reaching the allowable limit of the spring deformation width, a spring characteristic having a large spring constant is required for a large amplitude vibration.

  As described above, the suspension unit 10 of the present embodiment has nonlinear spring characteristics in which the spring constant increases as the amplitude of vibration input to the suspension unit 10 increases.

  The structure of the suspension part 10 as a vibration isolator having such a non-linear spring characteristic will be described below. In the following description, the suspension unit 10 is also referred to as a vibration isolator 10.

  As shown in FIG. 1, the vibration isolator 10 includes a rod-shaped rod member 20, a second vibrating portion 22, a first spiral spring 24, a first predetermined contact portion 26, a second spiral spring 28, And a second predetermined contact portion 30. The vibration isolator 10 suppresses vibration transmission between the first vibration unit 121 and the second vibration unit 22. The second vibrating portion 22 is a part of the compressor 14 and corresponds to a connecting portion that is connected (in other words, connected) to the engine 12. The first vibration part 121 is a part of the engine 12 and corresponds to a connected part to which the second vibration part 22 is connected.

  The first vibrating portion 121 has a screw hole 121a, and a male screw portion 201 formed at one end of the rod member 20 is screwed into the screw hole 121a. Thereby, the rod member 20 is fixed to the first vibrating portion 121 so as to protrude from the surface of the first vibrating portion 121.

  The second vibrating portion 22 is formed with an insertion hole 22 a that passes through the second vibrating portion 22. The rod member 20 is inserted through the insertion hole 22a. Accordingly, the second vibrating portion 22 is connected to the first vibrating portion 121 by the bar member 20.

  Further, the second vibration unit 22 includes a first holder unit 221 and a second holder unit 225. The first holder portion 221 is provided on one side of the rod member axial direction DRa that is the axial direction DRa of the rod member 20 with respect to the insertion hole 22a. Conversely, the second holder portion 225 is provided on the other side of the rod member axial direction DRa with respect to the insertion hole 22a.

  Moreover, the 1st holder part 221 has comprised the concave shape opened toward the one side of the rod member axial direction DRa. A first spiral spring 24 is fitted into the first holder part 221.

  On the other hand, the 2nd holder part 225 has comprised the concave shape opened toward the other side of the rod member axial direction DRa. A second spiral spring 28 is fitted into the second holder part 225.

  The rod member 20 is, for example, a hexagonal bolt, and includes a male screw portion 201, an intermediate shaft portion 202, and a head portion 206. The male screw portion 201, the intermediate shaft portion 202, and the head portion 206 are arranged in series along the rod axis CLb as the axis of the rod member 20. In the axial direction of the rod axis CLb, that is, the rod member axial direction DRa, the male screw portion 201 is connected to one side which is the first vibrating portion 121 side with respect to the intermediate shaft portion 202, and the head portion 206 is connected to the intermediate shaft portion 202. Is connected to the other side.

  Further, the intermediate shaft portion 202 has the first inner contact portion 203 at the one end portion and the second inner contact portion 204 at the other end portion. The first inner contact portion 203 is configured as a cylindrical outer peripheral surface as shown in FIGS. 1 and 2, and is in contact with the first spiral spring 24 from the inner side in the radial direction DRr of the first spiral spring 24. Yes.

  Similarly, the second inner contact portion 204 is also configured as a cylindrical outer peripheral surface, and contacts the second spiral spring 28 from the radial inner side of the second spiral spring 28. That is, both the first spiral spring 24 and the second spiral spring 28 are wound around the rod member 20 in a spiral shape. Therefore, the rod member 20 is not in direct contact with the second vibrating portion 22 in the no-load state of the vibration isolator 10, and indirectly through the first spiral spring 24 and the second spiral spring 28, respectively. 2 It is connected to the vibration part 22. Thereby, the rod member 20 connects the second vibrating portion 22 to the first vibrating portion 121 so as to be relatively displaceable in the rod member axial direction DRa and the radial direction DRr.

  In the following description, the radial direction DRr of the first spiral spring 24 is also referred to as a spring radial direction DRr. As can be seen from FIGS. 1 and 2, the radial direction DRr of the second spiral spring 28 is the same as the radial direction DRr of the first spiral spring 24.

  The head portion 206 of the bar member 20 includes a shape capable of locking a tightening tool such as a spanner, for example, a shape having a hexagonal cross section. Therefore, when the head portion 206 is rotated, the male screw portion 201 of the rod member 20 is screwed into the screw hole 121a of the first vibrating portion 121.

  The first predetermined abutting portion 26 is constituted by, for example, a washer, and the washer is sandwiched between the intermediate shaft portion 202 of the rod member 20 and the first vibrating portion 121 in the rod member axial direction DRa, thereby causing the first vibration. It is fixed to the part 121. The first predetermined contact portion 26 is in contact with the first spiral spring 24 in the rod member axial direction DRa.

  Further, the second predetermined contact portion 30 is also constituted by a washer, for example. The washer as the second predetermined contact portion 30 may be a member different from the rod member 20, but is configured integrally with the head portion 206 of the rod member 20 in this embodiment. Accordingly, the second predetermined contact portion 30 is fixed to the first vibrating portion 121 via the bar member 20. The second predetermined contact portion 30 is in contact with the second spiral spring 28 in the rod member axial direction DRa.

  Here, when viewed functionally, the vibration isolator 10 includes a first vibration isolator 101 and a second vibration isolator 102 that suppress transmission of vibration. The first vibration isolation unit 101 includes a first spiral spring 24, a first predetermined contact portion 26, a first inner contact portion 203, and a first holder portion 221. The second vibration isolator 102 includes a second spiral spring 28, a second predetermined contact portion 30, a second inner contact portion 204, and a second holder portion 225.

  The first vibration isolator 101 is disposed on the opposite side of the second vibration isolator 102 with the insertion hole 22a in the rod member axial direction DRa. Furthermore, the first vibration isolator 101 has a symmetrical configuration with respect to the second vibration isolator 102 in the rod member axial direction DRa.

  That is, in the first vibration isolator 101, the first predetermined contact portion 26 side in the rod member axial direction DRa with respect to the first spiral spring 24 is one side in the rod member axial direction DRa. At the same time, the second predetermined contact portion 30 side in the rod member axial direction DRa with respect to the second spiral spring 28 in the second vibration isolator 102 is the other side in the rod member axial direction DRa.

  Specifically, the second spiral spring 28 of the second vibration isolation unit 102 corresponds to the first spiral spring 24 of the first vibration isolation unit 101, and the second predetermined contact unit 30 is connected to the first predetermined contact unit 26. Correspond. The second inner contact portion 204 corresponds to the first inner contact portion 203, and the second holder portion 225 corresponds to the first holder portion 221.

  As described above, the first vibration isolation unit 101 and the second vibration isolation unit 102 have the same configuration. Therefore, the first vibration isolation unit 101 will be basically described below, and the second vibration isolation unit 102 will be described. Description of is omitted.

  As shown in FIGS. 1 to 4, in the unloaded state of the vibration isolator 10, the first spiral spring 24 has a radial clearance 24 a between portions of the first spiral spring 24 adjacent to each other in the spring radial direction DRr. It is formed to produce. In short, the first spiral spring 24 is a non-contact spiral spring.

  Moreover, the 1st spiral spring 24 is comprised by winding the spring material which is a strip | belt-shaped spring steel plate, for example. The width of the spring material constituting the first spiral spring 24, that is, the material width in the rod member axial direction DRa is, for example, uniform over the entire length of the spring material. And the 1st spiral spring 24 has comprised the spiral shape wound so that it might shift | deviate to the 1st predetermined contact part 26 side of the rod member axial direction DRa, so that the inner side of the spring radial direction DRr.

  The first holder part 221 has a first outer contact part 222 and a first axial contact part 223. The first outer abutting portion 222 is configured by an inner peripheral surface facing the inner side of the first holder portion 221 in the spring radial direction DRr. The first outer contact portion 222 is in contact with the first spiral spring 24 from the outer side of the first spiral spring 24 in the spring radial direction DRr.

  Specifically, the first outer abutment portion 222 surrounds the first spiral spring 24 over the entire circumference of the first spiral spring 24. The first outer contact portion 222 is in contact with the outer peripheral end 241 provided on the outer side in the spring radial direction DRr of the first spiral spring 24 in the spring radial direction DRr.

  Further, the first axial contact portion 223 is configured by a plane facing the first predetermined contact portion 26 side in the rod member axial direction DRa. The first axial contact portion 223 is in contact with the first spiral spring 24 in the rod member axial direction DRa from the side opposite to the first predetermined contact portion 26.

  Specifically, the first predetermined contact portion 26 is in contact with the inner peripheral end portion 242 provided on the inner side in the spring radial direction DRr of the first spiral spring 24 in the rod member axial direction DRa. On the other hand, in the unloaded state of the vibration isolator 10, the first axial contact portion 223 is opposed to the first predetermined contact portion 26 with respect to the outer peripheral end portion 241 of the first spiral spring 24. Is in contact with the rod member axial direction DRa. And the space | interval between the 1st axial direction contact part 223 and the 1st spiral spring 24 in the rod member axial direction DRa becomes large toward the inner side in the spring radial direction DRr.

  That is, the first axial contact portion 223 is shifted in the spring radial direction DRr with respect to the inner peripheral end portion 242 which is a portion of the first spiral spring 24 where the first predetermined contact portion 26 contacts. It is in contact with the first spiral spring 24.

  In the vibration isolator 10 of the present embodiment, the first spiral spring 24 is fitted into the first holder portion 221 in a state of being compressed to some extent in both the rod member axial direction DRa and the spring radial direction DRr. It has been. Accordingly, the first spiral spring 24 is slightly shrunk in the rod member axial direction DRa and the spring radial direction DRr as compared with the free state of the first spiral spring 24 in the unloaded state of the vibration isolator 10. It has become.

  The second holder portion 225 has a second outer contact portion 226 corresponding to the first outer contact portion 222 and a second axial contact portion 227 corresponding to the first axial contact portion 223. doing.

  Next, how the first spiral spring 24 bends in the rod member axial direction DRa and the spring radial direction DRr will be described. First, how the first spiral spring 24 bends in the rod member axial direction DRa will be described with reference to FIGS. 5A and 5B. 5A and 5B are schematic diagrams for explaining how the first spiral spring 24 bends in the rod member axial direction DRa. 5A and 5B, the first outer abutting portion 222 of the first holder portion 221 is not illustrated, and the first axial abutting portion 223 of the first holder portion 221 is schematically illustrated as a mere plane. Has been. 5A shows the first spiral spring 24 in the unloaded state of the vibration isolator 10, and FIG. 5B shows the first spiral that has been compressed by receiving the compressive load Fa in the rod member axial direction DRa from the unloaded state. A spring 24 is shown.

  As shown in FIGS. 5A and 5B, the second vibrating portion 22 vibrates with respect to the first vibrating portion 121 in, for example, the rod member axial direction DRa, and the compressive load Fa in the rod member axial direction DRa, that is, the axial compressive load Fa is the first. When applied to one spiral spring 24, the first spiral spring 24 contracts in the rod member axial direction DRa. Thereby, the first spiral spring 24 absorbs the vibration in the rod member axial direction DRa.

  At this time, the first axial contact portion 223 is an axial displacement restricting portion (in short, a stopper in the rod member axial direction DRa) that regulates the displacement of the rod member axial direction DRa at each portion of the first spiral spring 24. ). Then, the first spiral of the first spiral spring 24 so that the contact range Wc of the first spiral spring 24 that contacts the first axial contact portion 223 expands inward in the spring radial direction DRr as the axial displacement amount La increases. The spring 24 bends. The axial displacement amount La is a displacement amount by which the first axial contact portion 223 is displaced toward the rod member axial direction DRa with respect to the first predetermined contact portion 26 in FIG. This is the amount of contraction of the first spiral spring 24 in the member axial direction DRa.

  Therefore, in other words, as the amount of contraction of the first spiral spring 24 in the rod member axial direction DRa increases, the area in which the first spiral spring 24 contacts the first axial contact portion 223 increases. Then, elastic deformation is limited at a portion of the first spiral spring 24 that contacts the first axial contact portion 223. That is, as the amount of contraction increases, the elastic deformation portion Wae serving as the portion Wae in the first spiral spring 24 responsible for elastic deformation corresponding to the displacement of the first axial contact portion 223 relative to the first predetermined contact portion 26 is Get smaller.

  In short, of the total length of the spring material along the spiral of the first spiral spring 24, the effective length of the spring that elastically deforms according to the displacement of the second vibrating portion 22 with respect to the first vibrating portion 121 has a large axial displacement amount La. It gets shorter.

  Since the first spiral spring 24 is deformed in the rod member axial direction DRa in this way, as shown in FIG. 6, the larger the shrinkage amount, that is, the axial displacement amount La, is expressed by the spring constant of the first spiral spring 24. The elasticity becomes greater. FIG. 6 is a graph showing the spring characteristics of the first spiral spring 24 in the rod member axial direction DRa. In FIG. 6, the horizontal axis indicates the axial displacement amount La, and the vertical axis indicates the magnitude of the axial compression load Fa.

  Next, how the first spiral spring 24 bends in the spring radial direction DRr will be described with reference to FIGS. 7A, 7B, and 7C. 7A, 7B, and 7C are schematic diagrams for explaining how the first spiral spring 24 bends in the spring radial direction DRr. 7A, 7B, and 7C, the first axial contact portion 223 of the first holder portion 221 is not shown, and the first outer contact portion 222 has a radial load Fr in the spring radial direction DRr. Is schematically illustrated as a mere plane opposite to. FIG. 7A shows the first spiral spring 24 in the no-load state of the vibration isolator 10. 7B shows the first spiral spring 24 deformed by receiving the radial load Fr from the unloaded state, and FIG. 7C shows the first spiral further deformed from the state of FIG. 7B by receiving the radial load Fr. A spring 24 is shown.

  As shown in FIGS. 7A, 7B, and 7C, when the second vibrating portion 22 vibrates with respect to the first vibrating portion 121, for example, in the spring radial direction DRr, and the radial load Fr is applied to the first spiral spring 24, The first spiral spring 24 contracts in the spring radial direction DRr. Thereby, the first spiral spring 24 absorbs vibration in the spring radial direction DRr.

  At this time, the first outer abutment portion 222 functions as a radial displacement restricting portion (in short, a stopper in the spring radial direction DRr) that restricts the displacement of the first spiral spring 24 in the spring radial direction DRr of that portion. To do. And the site | parts adjacent to the spring radial direction DRr among the 1st spiral springs 24 mutually contact. Therefore, only the inner part in the spring radial direction DRr with respect to the contact point Pct between the adjacent parts is elastically deformed corresponding to the displacement of the first outer contact part 222 with respect to the first inner contact part 203 in FIG. To become responsible. The contact point Pct moves inward in the spring radial direction DRr as the radial load Fr increases.

  That is, as the radial displacement Lr by which the second vibrating portion 22 in FIG. 1 is displaced in the spring radial direction DRr with respect to the first vibrating portion 121 is larger, the elastic deformation portion Wae responsible for elastic deformation of the first spiral spring 24 is Get smaller. In short, the effective spring length of the entire length of the spring material of the first spiral spring 24 becomes shorter as the radial displacement Lr becomes larger. In FIGS. 7A, 7B, and 7C, the elastically deformable portion Wae is represented by point hatching.

  As described above, the first spiral spring 24 is deformed in the spring radial direction DRr. Therefore, as the radial displacement Lr of the first spiral spring 24 increases, the first spiral spring 24 is expressed by the spring constant of the first spiral spring 24 as shown in FIG. The elasticity is increased. FIG. 8 is a graph showing the spring characteristics of the first spiral spring 24 in the spring radial direction DRr. In FIG. 8, the horizontal axis indicates the radial displacement amount Lr, and the vertical axis indicates the magnitude of the radial load Fr.

  6 and 8 show the spring characteristics of the first spiral spring 24. In the present embodiment, the first spiral spring 24 and the second spiral spring 28 are the same component, and thus the spring of the second spiral spring 28 is used. The characteristics are also the same as those shown in FIGS.

  As described above, according to the present embodiment, as shown in FIGS. 1 and 2, the first spiral spring 24 has a diameter between portions adjacent to each other in the spring radial direction DRr of the first spiral spring 24. A directional gap 24a is formed. Further, the bar member 20 has a first inner contact portion 203, and the first inner contact portion 203 is in contact with the first spiral spring 24 from the inside in the radial direction DRr of the first spiral spring 24. . The second vibrating portion 22 has a first holder portion 221 in which a first spiral spring 24 is fitted, and the first holder portion 221 is in contact with the first outer abutting portion 222 and the first axial direction. Part 223. Further, the first outer contact portion 222 contacts the first spiral spring 24 from the outer side of the first spiral spring 24 in the spring radial direction DRr. At the same time, the first axial contact portion 223 is shifted in the spring radial direction DRr with respect to the inner peripheral end portion 242 which is a portion of the first spiral spring 24 where the first predetermined contact portion 26 contacts. , Is in contact with the first spiral spring 24.

  Thereby, the first spiral spring 24 can be bent in each of the rod member axial direction DRa and the spring radial direction DRr. The amount of bending of the first spiral spring 24 in both the rod member axial direction DRa and the spring radial direction DRr can be easily secured according to the shape of the first spiral spring 24. Therefore, the vibration isolator 10 can suppress the transmission of vibrations in two different directions that are the rod member axial direction DRa and the spring radial direction DRr.

  In addition, according to the present embodiment, as shown in FIGS. 7A to 7C and FIG. 8, of the total length of the spring material along the spiral of the first spiral spring 24, the second vibrating portion 22 with respect to the first vibrating portion 121. The effective length of the spring that is elastically deformed according to the displacement becomes shorter as the radial direction displacement amount Lr becomes larger. Therefore, in the spring radial direction DRr, it is possible to obtain a non-linear spring characteristic in which the spring constant increases as the amplitude of vibration input to the vibration isolator 10 increases.

  Further, according to the present embodiment, as shown in FIGS. 5A, 5B, and 6, the effective spring length of the total length of the spring material of the first spiral spring 24 becomes shorter as the axial displacement amount La becomes larger. . Therefore, in the rod member axial direction DRa, it is possible to obtain a non-linear spring characteristic in which the spring constant increases as the amplitude of vibration input to the vibration isolator 10 increases.

  As described above, in any direction of the rod member axial direction DRa and the spring radial direction DRr, the spring constant increases as the amplitude of vibration input to the vibration isolator 10 increases as shown in FIGS. It is possible to obtain the spring characteristics.

  Further, according to the present embodiment, as shown in FIGS. 1 and 2, the first spiral spring 24 is displaced toward the first predetermined contact portion 26 side in the rod member axial direction DRa toward the inner side in the spring radial direction DRr. It has a spiral shape wound around. Therefore, the configuration in which the effective spring length is shortened as the axial displacement amount La is increased as described above, and the first axial contact is made in a simple planar shape with the rod member axial direction DRa as the normal direction as in this embodiment. This can be realized by configuring the unit 223.

  Further, according to the present embodiment, as shown in FIGS. 5A, 5B, and 6, the contact range Wc that contacts the first axial contact portion 223 of the first spiral spring 24 is displaced in the axial direction. As the amount La increases, the first spiral spring 24 bends so as to expand inward in the spring radial direction DRr. Therefore, in the rod member axial direction DRa, it is possible to obtain a non-linear spring characteristic in which the spring constant increases as the amplitude of vibration input to the vibration isolator 10 increases.

  Further, according to the present embodiment, the first spiral spring 24 among the plurality of spiral springs 24, 28, the first predetermined contact portion 26 among the plurality of predetermined contact portions 26, 30, and the plurality of inner contacts. The first inner contact portion 203 among the portions 203 and 204 and the first holder portion 221 among the plurality of holder portions 221 and 225 constitute the first vibration isolation portion 101. Of the plurality of spiral springs 24, 28, the second spiral spring 28, the plurality of predetermined contact portions 26, 30 among the second predetermined contact portions 30, and the plurality of inner contact portions 203, 204 The second inner abutment portion 204 and the second holder portion 225 among the plurality of holder portions 221 and 225 constitute the second vibration isolation portion 102. And the 1st vibration isolator 101 is arrange | positioned on the other side on both sides of the insertion hole 22a of the 2nd vibration part 22 with respect to the 2nd vibration isolator 102 in the rod member axial direction DRa. Therefore, it is possible to provide the two anti-vibration units 101 and 102 while sharing parts.

(Second Embodiment)
Next, a second embodiment will be described. In the present embodiment, differences from the first embodiment will be mainly described. The same or equivalent parts as those in the first embodiment will be omitted or simplified for explanation.

  As shown in FIG. 9 and FIG. 2, the second vibrating portion 22 of the present embodiment is not composed of a single member but is composed of a plurality of members. This embodiment is different from the first embodiment in this point. 9 is the same as the II-II cross section in FIG. 1, FIG. 2 shows the II-II cross section in FIG. 1, and also shows the II-II cross section in FIG. .

  Specifically, the second vibrating portion 22 of the present embodiment includes a second vibrating portion main body 228 in addition to the first holder portion 221 and the second holder portion 225. And the 1st holder part 221, the 2nd holder part 225, and the 2nd vibration part main body 228 are comprised as a mutually different member.

  For example, the first holder portion 221 is fixed by being press-fitted into the second vibrating portion main body 228 from one side in the rod member axial direction DRa. The second holder portion 225 is fixed by being press-fitted into the second vibrating portion main body 228 from the other side in the rod member axial direction DRa.

  Further, the first holder part 221 and the second holder part 225 have a common configuration. Thereby, the parts commonality of the 1st holder part 221 and the 2nd holder part 225 is achieved.

  In the present embodiment, the effects produced from the configuration common to the first embodiment described above can be obtained as in the first embodiment.

  Further, according to the present embodiment, the second vibrating portion 22 includes the second vibrating portion main body 228 in addition to the first holder portion 221 and the second holder portion 225. The first holder part 221 and the second holder part 225 are each configured as a member different from the second vibrating part main body 228.

  Therefore, if the first and second holder portions 221 and 225 of the second vibrating portion 22 are configured to withstand the wear caused by the first and second spiral springs 24 and 28, respectively, the first and second holders thereof. In parts other than the parts 221 and 225 (for example, the second vibration part main body 228), it is possible to select a material or the like without being restricted by being resistant to wear by the spiral springs 24 and 28. In short, it is possible to increase the degree of design freedom in the second vibrating section 22.

  For example, a steel material can be used as the material of the first and second holder parts 221 and 225, while an aluminum alloy material can be used as the material of the second vibration part main body 228.

  In addition, the first and second holder portions 221 and 225 can be easily configured as parts having a simple shape. If the first and second holder portions 221 and 225 are configured in this way, the assembly work of fitting the first and second spiral springs 24 and 28 into the first and second holder portions 221 and 225, respectively, is facilitated. Is possible.

(Other embodiments)
(1) In each of the above-described embodiments, the vibration isolator 10 includes the two vibration isolators 101 and 102, but this is an example. For example, if the second vibration part 22 is connected to the first vibration part 121 so as to be relatively displaceable in the rod member axial direction DRa and the spring radial direction DRr, one of the two vibration isolation parts 101 and 102 is used. There is no problem.

  Further, the vibration isolator 10 may have three or more vibration isolators.

  (2) In each of the above-described embodiments, the first predetermined contact portion 26 is configured by a washer fixed to the first vibrating portion 121, for example. In this regard, the first predetermined contact portion 26 need not be a washer. For example, the first predetermined contact portion 26 is configured integrally with the first vibrating portion 121, and the first predetermined contact portion 26 and the first vibrating portion 121 may be a single component.

  (3) In each of the embodiments described above, the first spiral spring 24 and the second spiral spring 28 are the same parts, but they may be different parts.

  (4) In the second embodiment, the first holder part 221 and the second holder part 225 are fixed to the second vibrating part main body 228 by press-fitting, for example. It may be fixed with respect to the vibration part main body 228.

  The present invention is not limited to the above-described embodiment, and includes various modifications and modifications within an equivalent range. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes.

  Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case. In each of the above embodiments, when referring to the material, shape, positional relationship, etc. of the constituent elements, etc., unless otherwise specified, or in principle limited to a specific material, shape, positional relationship, etc. The material, shape, positional relationship, etc. are not limited.

(Summary)
According to the first aspect shown in a part or all of the above embodiments, the spiral spring has a radial clearance between portions adjacent to each other in the radial direction of the spiral spring. Is formed. Further, the bar member has an inner abutting portion, and the inner abutting portion abuts on the spiral spring from the radial inner side of the spiral spring. The second vibration part has a holder part into which a spiral spring is fitted, and the holder part has an outer contact part and an axial contact part. Further, the outer contact portion comes into contact with the spiral spring from the radially outer side of the spiral spring, and the axial contact portion is located at a position shifted in the radial direction with respect to the portion of the spiral spring with which the predetermined contact portion comes into contact. Thus, it comes into contact with the spiral spring in the axial direction from the side opposite to the predetermined contact portion.

  Further, according to the second aspect, of the total length of the spring material along the spiral of the spiral spring, the effective length of the spring that is elastically deformed according to the displacement of the second vibrating portion relative to the first vibrating portion is the second vibrating portion. The larger the radial displacement amount that is displaced in the radial direction with respect to the first vibrating portion, the shorter it becomes. Therefore, in the radial direction, it is possible to obtain a nonlinear spring characteristic in which the spring constant increases as the amplitude of vibration input to the vibration isolator increases.

  Further, according to the third aspect, in addition to the second aspect, the greater the amount of axial displacement that the axial contact portion is displaced closer to the axial direction with respect to the predetermined contact portion, the more effective the spring. The length is shortened. Therefore, in any of the radial direction and the axial direction, it is possible to obtain nonlinear spring characteristics in which the spring constant increases as the amplitude of vibration input to the vibration isolator increases.

  According to the fourth aspect, the effective spring length of the total length of the spring material of the spiral spring becomes shorter as the axial displacement amount becomes larger. Therefore, in the axial direction, it is possible to obtain a non-linear spring characteristic in which the spring constant increases as the amplitude of vibration input to the vibration isolator increases.

  Further, according to the fifth aspect, the spiral spring has a spiral shape wound so as to be displaced toward the predetermined contact portion side in the axial direction toward the inner side in the radial direction. Therefore, a configuration in which the effective spring length is shortened as the amount of axial displacement increases can be realized by configuring the axial contact portion in a simple flat shape with the axial direction as the normal direction, for example. It is.

  According to the sixth aspect, the spiral spring bends so that the contact range of the spiral spring that contacts the axial contact portion expands radially inward as the axial displacement amount increases. . Therefore, in the axial direction, it is possible to obtain a non-linear spring characteristic in which the spring constant increases as the amplitude of vibration input to the vibration isolator increases.

  Moreover, according to the 7th viewpoint, the 2nd vibration part has the 2nd vibration part main body to which a holder part is fixed. And the holder part is comprised as a member different from the 2nd vibration part main body. Accordingly, if the holder portion of the second vibrating portion is configured to withstand wear by the spiral spring, the portion other than the holder portion (for example, the second vibrating portion main body) is resistant to wear by the spiral spring. It is possible to select the material and the like without receiving. In short, it is possible to increase the degree of freedom of design in the second vibration part.

  According to the eighth aspect, the first spiral spring of the plurality of spiral springs, the first predetermined contact portion of the plurality of predetermined contact portions, and the first inner side of the plurality of inner contact portions. The contact portion and the first holder portion of the plurality of holder portions constitute a first vibration isolation portion. A second spiral spring of the plurality of spiral springs; a second predetermined contact portion of the plurality of predetermined contact portions; a second inner contact portion of the plurality of inner contact portions; and a plurality of The 2nd holder part of the holder parts comprises the 2nd vibration isolator. And the 1st vibration isolator is arrange | positioned on the opposite side on both sides of the insertion hole of the 2nd vibration part with respect to the 2nd vibration isolator in the axial direction. Therefore, it is possible to provide two vibration isolators while sharing parts.

DESCRIPTION OF SYMBOLS 10 Vibration isolator 20 Bar member 22 2nd vibration part 24 1st spiral spring 26 1st predetermined contact part 121 1st vibration part 203 1st inner contact part 221 1st holder part 222 1st outer contact part 223 1st Uniaxial contact part

Claims (8)

An anti-vibration device that suppresses vibration transmission,
A rod-shaped rod member (20) fixed to the first vibrating section (121);
A second vibrating part (22) connected to the first vibrating part by the rod member;
Spiral springs (24, 28) wound in a spiral around the rod member;
A predetermined contact portion (26, 30) fixed to the first vibrating portion and contacting the spiral spring in the axial direction (DRa) of the rod member;
The spiral spring is formed so as to generate a radial gap (24a) between portions adjacent to each other in the radial direction (DRr) of the spiral spring.
The bar member has an inner contact portion (203, 204) that contacts the spiral spring from the radial inner side of the spiral spring,
The second vibration part has a holder part (221, 225) in which the spiral spring is fitted,
The holder portion is configured so that the outer contact portion (222, 226) that contacts the spiral spring from the radially outer side of the spiral spring and the portion (242) of the spiral spring that the predetermined contact portion contacts. An anti-vibration device having axial contact portions (223, 227) that contact the spiral spring from a side opposite to the predetermined contact portion in a position shifted in a radial direction.   Of the total length of the spring material along the spiral of the spiral spring, the effective length of the spring that is elastically deformed in accordance with the displacement of the second vibrating portion relative to the first vibrating portion is the second vibrating portion is the first vibrating portion. On the other hand, the vibration isolator according to claim 1, wherein the vibration isolator is shorter as the radial displacement amount (Lr) displaced in the radial direction is larger.   The anti-vibration device according to claim 2, wherein the effective spring length decreases as the axial displacement amount (La) by which the axial contact portion is displaced toward the axial direction with respect to the predetermined contact portion increases. apparatus.   Of the total length of the spring material along the spiral of the spiral spring, the effective length of the spring that elastically deforms according to the displacement of the second vibrating portion relative to the first vibrating portion is the axial contact portion is the predetermined contact portion. The anti-vibration device according to claim 1, wherein the amount of axial displacement (La) displaced toward the side closer to the axial direction becomes shorter as the axial displacement amount (La) increases.   5. The vibration isolator according to claim 3, wherein the spiral spring has a spiral shape wound so as to be displaced toward the predetermined contact portion in the axial direction toward the inner side in the radial direction.   The said spiral spring bends so that the contact range (Wc) contact | abutted to the said axial direction contact part among this spiral spring may expand to the inner side of the said radial direction, so that the said axial direction displacement amount becomes large. The vibration isolator as described in any one of thru | or 5. The second vibration part has a second vibration part body (228) to which the holder part is fixed,
The vibration isolator according to any one of claims 1 to 6, wherein the holder part is configured as a member different from the second vibration part main body. A plurality of the spiral springs and the predetermined contact portions are provided,
The bar member has a plurality of the inner contact portions,
The second vibration part has a plurality of the holder parts,
The second vibrating part is formed with an insertion hole (22a) through which the rod member is inserted,
The first spiral spring (24) of the plurality of spiral springs, the first predetermined contact portion (26) of the plurality of predetermined contact portions, and the first inner contact of the plurality of inner contact portions. The contact portion (203) and the first holder portion (221) among the plurality of holder portions constitute a first vibration isolation portion (101),
The second spiral spring (28) of the plurality of spiral springs, the second predetermined contact portion (30) of the plurality of predetermined contact portions, and the second inner contact of the plurality of inner contact portions. The contact portion (204) and the second holder portion (222) among the plurality of holder portions constitute a second vibration isolation portion (102),
The first vibration isolator is disposed on the opposite side of the insertion hole with respect to the second vibration isolator in the axial direction,
The first predetermined contact portion side in the axial direction with respect to the first spiral spring in the first vibration isolating portion is one side in the axial direction,
The second predetermined contact portion side in the axial direction with respect to the second spiral spring in the second vibration isolating portion is the other side in the axial direction. Anti-vibration device.

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