WO2018131316A1 - Vibration damping device - Google Patents

Abstract

This vibration damping device connects a first vibration generation section (EG) and a second vibration generation section (24) and prevents the transmission of vibration. The vibration damping device is provided with: a bar-like member (40) for connecting the first vibration generation section and the second vibration generation section; and an elastic member for preventing the vibration of one of the first vibration generation section and the second vibration generation section from being transmitted to the other through the bar-like member. Further, the vibration damping device is provided with a displacement limiting section for limiting the displacement of the elastic member in a direction intersecting the axial direction of the bar-like member. The elastic member has characteristics such that the elastic constant of the elastic member in the axial direction of the bar-like member increases as a load acting in the axial direction increases, and the elastic member is configured such that the area of contact of the elastic member with the displacement limiting section increases as the amount of displacement of the elastic member in the intersecting direction increases.

Description

Vibration isolator Cross-reference to related applications

This application is based on Japanese Application No. 2017-3464 filed on Jan. 12, 2017 and Japanese Application No. 2017-221141 filed on Nov. 16, 2017. The description is incorporated.

This disclosure relates to a vibration isolator that suppresses vibration transmission.

Conventionally, a vibration isolator capable of changing a spring constant is known (for example, see Patent Document 1). Patent Document 1 discloses a vibration isolating bush in which a gap is provided in a part of a rubber elastic body disposed between an inner cylinder and an outer cylinder. This anti-vibration bushing has a structure in which a non-linear spring characteristic is obtained in which a part of the elastic body is in contact with the wall of the air gap facing the elastic body when the amplitude is large, and the spring constant is larger than that when the amplitude is small. .

JP 2004-282250 A

By the way, the anti-vibration bush disclosed in Patent Document 1 changes the spring constant in one direction in which the shape of the gap of the elastic member changes, and vibrations having different amplitudes in the direction in which the shape of the gap in the elastic member does not change. If this works, vibration transmission cannot be sufficiently suppressed.

This disclosure is intended to provide a vibration isolator having non-linear elastic characteristics in two different directions.

This disclosure is directed to a vibration isolator that connects the first vibration generation unit and the second vibration generation unit and suppresses transmission of vibration.

According to one aspect of the present disclosure, the vibration isolator is
The invention described in claim 1
A rod-shaped member connecting the first vibration generating unit and the second vibration generating unit;
An elastic member that suppresses transmission of one vibration of the first vibration generating unit and the second vibration generating unit to the other through the rod-shaped member;
A displacement restricting portion that restricts displacement of the rod-like member in the elastic member in the intersecting direction intersecting the rod axis direction.

The elastic member has a characteristic that the elastic constant in the rod axis direction increases as the load acting in the rod axis direction increases, and the displacement limiter and the displacement limiting portion increase as the displacement amount in the cross direction in the elastic member increases. The contact area is configured to be large.

In this way, if an elastic member having the characteristic that the elastic constant in the rod axis direction increases as the load acting on the rod axis direction of the rod member increases, vibrations with different amplitudes act in the rod axis direction. Even in this case, the transmission of vibration can be suppressed by the elastic member.

Further, the elastic member is configured such that when the load acting in the intersecting direction is increased, the contact area with the displacement limiting portion is increased, so that the elastically deformable range is reduced.

According to this, since the elastic member has the characteristic that the elastic constant in the cross direction increases as the load acting in the cross direction increases, even if vibrations with different amplitudes act in the rod diameter direction The transmission of vibration can be suppressed by the elastic member.

Therefore, according to the present disclosure, it is possible to realize a vibration isolator having non-linear elastic characteristics with respect to two different directions, ie, the rod axis direction of the rod-shaped member and the intersecting direction intersecting the rod axis direction.

According to another aspect of the present disclosure, the vibration isolator is
A rod-shaped member connecting the first vibration generating unit and the second vibration generating unit;
An elastic member that suppresses transmission of one vibration of the first vibration generating unit and the second vibration generating unit to the other through the rod-shaped member;
A first axial direction defining portion for defining a position of one end side of the rod-shaped member of the rod-shaped member in the elastic member;
A second axial direction defining portion that defines a position on the other end side in the rod axial direction of the elastic member.

The elastic member has a characteristic that the elastic constant in the crossing direction increases as the load acting in the crossing direction crossing the rod axis direction increases. Furthermore, the elastic member is configured such that the contact area with one of the first axial direction defining portion and the second axial direction defining portion increases as the amount of displacement of the elastic member in the rod axial direction increases.

In this way, if an elastic member having the characteristic that the elastic constant in the crossing direction increases as the load acting in the crossing direction of the rod-shaped member increases, vibrations with different amplitudes act in the rod radial direction. Even if it exists, transmission of a vibration can be suppressed by an elastic member.

In addition, when the load acting in the rod axis direction increases, the elastic member has a larger contact area with one of the first axial direction defining portion and the second axial direction defining portion, thereby reducing the elastic deformation range. It is configured as follows.

According to this, since the elastic member has the characteristic that the elastic constant in the rod axis direction increases as the load acting in the rod axis direction increases, this is the case when vibrations with different amplitudes act in the rod axis direction. However, the transmission of vibration can be suppressed by the elastic member.

Therefore, even with this configuration, it is possible to realize a vibration isolator having non-linear elastic characteristics with respect to two different directions, ie, the rod axis direction of the rod-shaped member and the intersecting direction intersecting the rod axis direction.

It is a schematic block diagram of a vehicle air conditioner. It is a typical perspective view which shows the attachment structure of an engine and a compressor. It is typical sectional drawing which shows the structure of the suspension apparatus of 1st Embodiment. It is the schematic diagram which illustrated typically the state of the 1st coil spring in the unloaded state of the suspension apparatus of 1st Embodiment. It is the schematic diagram which illustrated typically the state of the 1st coil spring when a compressive load acted on the axial direction with respect to the suspension apparatus of 1st Embodiment. It is explanatory drawing for demonstrating the spring characteristic of the bar axial direction in each coil spring of 1st Embodiment. It is the schematic diagram which illustrated typically the relationship between the 1st coil spring and the 1st holder part in the unloaded state of the suspension apparatus of 1st Embodiment. It is the schematic diagram which illustrated typically the relationship between the 1st coil spring and the 1st holder part at the time of a load acting on the suspension apparatus of 1st Embodiment in the rod diameter direction. It is explanatory drawing for demonstrating the spring characteristic of the rod radial direction in each coil spring of 1st Embodiment. It is typical sectional drawing which shows the structure of the suspension apparatus of 2nd Embodiment. It is an enlarged view of the XI part of FIG. It is typical sectional drawing which shows the structure of the suspension apparatus of 3rd Embodiment. It is an enlarged view of the XIII part of FIG. It is typical sectional drawing which shows the structure of the suspension apparatus of 4th Embodiment. It is a typical front view in the free state of each coil spring of a 5th embodiment. It is a typical front view in the state where each coil spring of a 5th embodiment was stored in each holder part. It is typical sectional drawing which shows the structure of the suspension apparatus of 6th Embodiment. It is an enlarged view of the XVIII part of FIG. It is the schematic diagram which illustrated typically the state at the time of a load acting on the suspension apparatus of 6th Embodiment in the rod diameter direction. It is the schematic diagram which illustrated typically the state at the time of a load having acted on both the rod-axis direction and the rod radial direction with respect to the suspension apparatus of 6th Embodiment. It is explanatory drawing for demonstrating the measurement result of the vibration of the compressor at the time of using the suspension apparatus used as the comparative example of 6th Embodiment. It is explanatory drawing for demonstrating the measurement result of the vibration of the compressor at the time of using the suspension apparatus of 6th Embodiment. It is typical sectional drawing which shows the structure of the suspension apparatus of 7th Embodiment. It is a typical half section view of the spiral spring of a 7th embodiment. It is a typical front view of the spiral spring of the seventh embodiment. It is an enlarged view of the XXVI part of FIG. It is the schematic diagram which illustrated typically the state at the time of a load acting with respect to the suspension apparatus of 7th Embodiment to the rod-axis direction. It is the schematic diagram which illustrated typically the state at the time of a load acting on both the rod-axis direction and the rod radial direction with respect to the suspension apparatus of 7th Embodiment.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same or equivalent parts as those described in the preceding embodiments are denoted by the same reference numerals, and the description thereof may be omitted. Further, in the embodiment, when only a part of the constituent elements are described, the constituent elements described in the preceding embodiment can be applied to the other parts of the constituent elements. The following embodiments can be partially combined with each other even if they are not particularly specified as long as they do not cause any trouble in the combination.

(First embodiment)
This embodiment will be described with reference to FIGS. A vehicle air conditioner 10 shown in FIG. 1 is an apparatus that is applied to a vehicle such as an automobile equipped with an engine EG, and adjusts the temperature in the passenger compartment to a desired temperature.

The vehicle air conditioner 10 of the present embodiment is composed of an auto air conditioner system in which an air conditioning unit 11 that air-conditions a passenger compartment is controlled by a control device ECU. The control device ECU is a device that controls the operation of various control devices for air conditioning.

The air conditioning unit 11 is disposed inside the instrument panel at the forefront of the vehicle interior. The air conditioning unit 11 houses an indoor blower 13, an evaporator 14, a heater core 15 and the like inside an air conditioning case 12 that forms an outer shell thereof.

The air conditioning case 12 has an air passage for air to be blown into the vehicle interior, and is formed of, for example, a resin such as polypropylene. On the most upstream side of the air flow in the air conditioning case 12, an inside / outside air switching box 16 for switching and introducing the inside air as the cabin air and the outside air as the cabin outside air is arranged.

An indoor blower 13 is disposed on the downstream side of the air flow of the inside / outside air switching box 16 to blow the air sucked through the inside / outside air switching box 16 toward the vehicle interior. The indoor blower 13 is composed of an electric blower that drives an impeller by an electric motor.

An evaporator 14 is disposed on the downstream side of the air flow of the indoor blower 13. The evaporator 14 is a cooling heat exchanger that cools the blown air by exchanging heat between the refrigerant flowing through the evaporator 14 and the blown air. In the air conditioning case 12, on the downstream side of the air flow of the evaporator 14, the hot air passage 20 and the cold air passage 21 through which the air after passing through the evaporator 14 flows, and the air that has flowed out of the hot air passage 20 and the cold air passage 21. A mixing space 22 for mixing the two is formed.

A heater core 15 for heating the air after passing through the evaporator 14 is disposed in the hot air passage 20. The heater core 15 is a heat exchanger for heating that heats the blown air by exchanging heat between the hot water flowing inside the blower air. Hot water warmed by the engine EG flows into the heater core 15, and air is heated by heat exchange between the flowing warm water and air.

The cold air passage 21 is an air passage for guiding the air after passing through the evaporator 14 to the mixing space 22 without passing through the heater core 15. Therefore, the temperature of the air mixed in the mixing space 22 varies depending on the air volume ratio of the air passing through the hot air passage 20 and the air passing through the cold air passage 21.

In the present embodiment, the air mix that changes the air volume ratio of the cold air flowing into the hot air passage 20 and the cold air passage 21 on the downstream side of the air flow of the evaporator 14 and on the inlet side of the hot air passage 20 and the cold air passage 21. A door 23 is arranged. The air mix door 23 functions as a temperature adjusting means for adjusting the air temperature in the mixing space 22.

Here, the evaporator 14 constitutes a vapor compression refrigeration cycle together with the compressor 24, the condenser 25, the expansion valve 26, the gas-liquid separator 28, and the like. The compressor 24 is disposed in the engine room. The compressor 24 sucks refrigerant in the refrigeration cycle and compresses and discharges the sucked refrigerant. The compressor 24 is driven by an engine EG mounted in the engine room of the vehicle.

The condenser 25 is a radiator that is arranged in the engine room and causes the compressed refrigerant to be condensed and liquefied by exchanging heat between the refrigerant circulating inside and the outside air. The gas-liquid separator 28 separates the gas-liquid two-phase refrigerant flowing out from the condenser 25 into a liquid refrigerant and a gas refrigerant. The expansion valve 26 is decompression means for decompressing and expanding the liquid refrigerant separated by the gas-liquid separator 28. The evaporator 14 is a heat absorber that evaporates and evaporates the refrigerant decompressed and expanded by the expansion valve 26 by heat exchange between the refrigerant and the blown air.

In the cooling cycle configured as described above, the refrigerant discharged from the compressor 24 flows in the order of the condenser 25, the gas-liquid separator 28, the expansion valve 26, and the evaporator 14, and then is sucked into the compressor 24 again. The

As shown in FIG. 2, the compressor 24 is attached to the engine EG via a suspension device 30 in the engine room. The suspension device 30 functions as an anti-vibration device that connects the engine EG that forms the first vibration generating unit and the compressor 24 that forms the second vibration generating unit, and suppresses vibration transmission.

Specifically, the compressor 24 of the present embodiment is attached to the engine EG via four suspension devices 30. In FIG. 2, for easy understanding, the outer shape of the compressor 24 is modeled into a cylindrical shape, and the outer shape of the engine EG is modeled into a rectangular parallelepiped shape.

Since the compressor 24 of this embodiment is attached to the engine EG, when the compressor 24 vibrates, the vibration is transmitted to the engine EG. When the engine EG is driven, the vibration caused by the vibration of the engine 24 and the driving sound of the engine EG are radiated to the outside of the passenger compartment.

However, when the noise on the engine EG side is low, such as when the engine EG is stopped, the sound caused by the vibration of the compressor 24 is not easily erased by the noise on the engine EG side. That is, when the noise on the engine EG side is small, noise due to the vibration of the compressor 24 is likely to be a problem.

Therefore, the suspension device 30 that connects the engine EG and the compressor 24 needs to have an elastic characteristic with a small elastic constant so that transmission of vibration with a minute amplitude such as vibration of the compressor 24 can be suppressed. Is done.

On the other hand, the engine EG may generate a vibration with a large amplitude depending on the operating condition. When the vibration with a large amplitude is generated in the engine EG, if the elastic characteristic of the suspension device 30 is maintained in a state where the elastic constant is small, it becomes difficult for the suspension device 30 to absorb the vibration. If the suspension device 30 cannot absorb vibration, the vibration of the engine EG is transmitted to the compressor 24, and the durability of the compressor 24 may be impaired.

As described above, the suspension device 30 needs not only a vibration with a small amplitude such as the vibration of the compressor 24 but also an elastic characteristic with a large elastic constant so that transmission of a vibration with a large amplitude can be suppressed. Is done.

In view of these circumstances, the suspension device 30 of the present embodiment has a non-linear elastic characteristic in which the elastic constant increases as the amplitude of vibration input to the suspension device 30 increases. Hereinafter, the structure of the suspension device 30 of the present embodiment will be described with reference to FIG.

As shown in FIG. 3, the suspension device 30 is provided at a connecting portion that connects the engine-side housing EGH of the engine EG and the compressor-side housing 240 of the compressor 24. The suspension device 30 of the present embodiment includes a rod-shaped member 40 formed in a rod shape, a first suspension portion 50 disposed on one end side of the rod-shaped member 40, and a second suspension portion disposed on the other end side of the rod-shaped member 40. 60.

The rod-shaped member 40 is disposed so as to extend along the intersecting direction (specifically, the horizontal direction) that intersects the vertical direction, which is the direction of gravity. That is, the rod-shaped member 40 is disposed such that the axis CL extends along the horizontal direction. In addition, DRa shown in FIG. 3 has shown the rod axial direction which is the direction where the axial center CL of the rod-shaped member 40 is extended. Further, DRr shown in FIG. 3 indicates a rod radial direction that is a direction orthogonal to the rod axis direction DRa of the rod-shaped member 40.

The rod-shaped member 40 of the present embodiment is composed of, for example, a hexagon bolt. The rod-shaped member 40 includes a male screw portion 41 formed on one end side in the rod axis direction DRa, a substantially hexagonal head portion 42 formed on the other end side in the rod axis direction DRa, a male screw portion 41 and the head portion 42. The intermediate shaft part 43 is provided.

Here, in the compressor-side housing 240, an insertion hole 241 through which the rod-shaped member 40 is inserted is formed at a connection portion with the engine EG. Further, the engine-side housing EGH is formed with a screw hole EGS at a connection portion with the compressor 24. The male screw portion 41 of the rod-shaped member 40 is screwed into the screw hole EGS. Thereby, the compressor side housing 240 and the engine side housing EGH are mutually connected via the rod-shaped member 40.

Further, the compressor-side housing 240 is formed with a first housing portion 242 and a second housing portion 243 for housing a first holder portion 52, a second holder portion 62, and the like, which will be described later, on both sides of the opening portion of the insertion hole 241. ing. The 1st accommodating part 242 and the 2nd accommodating part 243 are comprised by the bottomed hole used as a larger diameter than the insertion hole 241. FIG.

The first suspension part 50 is provided on one end side of the intermediate shaft part 43 of the rod-shaped member 40 that is close to the engine-side housing EGH. The first suspension unit 50 includes a first coil spring 51 that suppresses vibration transmission between the engine EG and the compressor 24, a first holder unit 52 that houses the first coil spring 51, and the first coil spring 51 in the rod axis direction DRa. A first end position defining portion 53 that defines the positions of both end portions is provided.

The first coil spring 51 is an elastic member that suppresses transmission of vibration of one of the engine EG and the compressor 24 to the other through the rod-shaped member 40. The first coil spring 51 is composed of a conical coil spring wound with a wire 510 so that the coil diameter increases from one end side toward the other end side. The first coil spring 51 is arranged such that the coil center axis connecting the centers of the coil diameters extends along the rod axis direction DRa of the rod-shaped member 40. The first coil spring 51 of the present embodiment is arranged so that the small diameter end portion with the smallest coil diameter is located on the engine EG side.

Also, the first coil spring 51 of the present embodiment is configured such that a part of the wire 510 adjacent in the rod axis direction DRa overlaps in the rod axis direction DRa. Accordingly, the first coil spring 51 is configured such that when a load is applied from the rod axis direction DRa, a part of the adjacent wire 510 is brought into contact.

Furthermore, the first coil spring 51 of the present embodiment is formed of a wire material in which the wire material 510 has a circular cross section. In addition, the 1st coil spring 51 may be comprised with the deformed wire which becomes a cross-sectional square shape, for example.

The first holder part 52 is fixed to the first housing part 242 by press fitting or the like. The 1st holder part 52 is comprised by the cylinder shape so that the 1st coil spring 51 can be accommodated in the inside. The first holder portion 52 has a first inner wall portion 520 that covers a portion of the first coil spring 51 that is exposed outside the rod radial direction DRr.

The first holder 52 is in contact with a part of the first coil spring 51 when a load exceeding a predetermined reference load is applied to the first coil spring 51 in the rod radial direction DRr. And the first coil spring 51 are set. In the first holder portion 52 of the present embodiment, the distance between the first inner wall portion 520 and the first coil spring 51 is such that the contact area with the first coil spring 51 increases as the load in the rod radial direction DRr increases. Is set.

More specifically, the first inner wall portion 520 is configured by an inner wall portion having a hole shape that increases from the small diameter side to the large diameter side of the first coil spring 51 in the first holder portion 52. The first holder portion 52 configured in this way is easily brought into contact with the first inner wall portion 520 even on the small diameter side where the coil diameter of the first coil spring 51 is small when a load in the rod radial direction DRr is applied. Yes.

The first end position defining portion 53 defines the positions of both end portions of the first coil spring 51 in the rod axis direction DRa. The first end position defining portion 53 defines the position of the first large diameter side defining portion 531 that defines the position of the large diameter side end portion of the first coil spring 51 and the position of the small diameter side end portion of the first coil spring 51. The first small diameter side defining portion 532 is configured.

The first large-diameter side defining portion 531 is formed of an annular member and is disposed at the bottom of the first accommodating portion 242. Further, the first small diameter side defining portion 532 is formed of an annular member, and is disposed between the male screw portion 41 and the intermediate shaft portion 43 of the rod-shaped member 40.

Here, the first coil spring 51 of the present embodiment has a pair of flat portions formed at the end portions facing the defining portions 531 and 532 so that the contact state with the defining portions 531 and 532 is stable. Portions 512 and 513 are provided. The pair of flat portions 512 and 513 can be formed by subjecting both end portions of the first coil spring 51 to a grinding process. The pair of flat portions 512 and 513 are provided, for example, in a range of about 3/4 winding at the end portion of the wire 510.

Further, in the first suspension part 50 of the present embodiment, the first coil spring 51 is compressed between the first large diameter side defining part 531 and the first small diameter side defining part 532 in a state compressed to some extent in the rod axis direction DRa. It is inserted in. Therefore, the first coil spring 51 fitted between the first large-diameter side defining portion 531 and the first small-diameter side defining portion 532 has a length in the rod axis direction DRa as compared with the first coil spring 51 in the free state. It is getting smaller.

Subsequently, the second suspension part 60 is provided on the other end side of the intermediate shaft part 43 of the rod-shaped member 40. The second suspension part 60 includes a second coil spring 61 that suppresses vibration transmission between the engine EG and the compressor 24, a second holder part 62 that houses the second coil spring 61, and the rod axis direction DRa of the second coil spring 61. A second end position defining portion 63 that defines the positions of both end portions is provided.

The second coil spring 61 is an elastic member that suppresses transmission of vibration of one of the engine EG and the compressor 24 to the other through the rod-shaped member 40. The second coil spring 61 is constituted by a conical coil spring wound with a wire 610 so that the coil diameter increases from one end side toward the other end side. The second coil spring 61 is arranged such that the coil center axis connecting the centers of the coil diameters extends along the rod axis direction DRa of the rod-shaped member 40. The second coil spring 61 of the present embodiment is arranged so that the small diameter end portion with the smallest coil diameter is positioned on the head 42 side of the rod-shaped member 40.

Further, the second coil spring 61 of the present embodiment is configured such that a part of the wire 610 adjacent to the rod axis direction DRa overlaps with the rod axis direction DRa. Thus, the second coil spring 61 is configured such that a part of the adjacent wire 610 contacts when a load is applied from the rod axis direction DRa.

Furthermore, the second coil spring 61 of the present embodiment is made of a wire material in which the wire material 610 has a circular cross section. In addition, the 2nd coil spring 61 may be comprised with the deformed wire which becomes a cross-sectional square shape, for example.

The second holder part 62 is fixed to the second housing part 243 by press fitting or the like. The 2nd holder part 62 is comprised by the cylinder shape so that the 2nd coil spring 61 can be accommodated in the inside. Specifically, the second holder portion 62 has a second inner wall portion 620 that covers a portion of the second coil spring 61 that is exposed outside the rod radial direction DRr.

The second holder 62 is in contact with a part of the second coil spring 61 when a load exceeding a predetermined reference load is applied to the second coil spring 61 in the rod radial direction DRr. And the second coil spring 61 are set. In the second holder portion 62 of this embodiment, the distance between the second inner wall portion 620 and the second coil spring 61 is such that the contact area with the second coil spring 61 increases as the load in the rod radial direction DRr increases. Is set.

More specifically, the second inner wall portion 620 includes an inner wall portion having a hole shape that increases from the small diameter side to the large diameter side of the second coil spring 61 in the second holder portion 62.

The second end position defining portion 63 defines the positions of both end portions of the second coil spring 61 in the rod axis direction DRa. The second end position defining portion 63 defines the position of the second large diameter side defining portion 631 that defines the position of the large diameter end portion of the second coil spring 61 and the position of the small diameter end portion of the second coil spring 61. The second small-diameter side defining portion 632 is configured.

The second large-diameter side defining portion 631 is formed of an annular member and is disposed at the bottom of the second accommodating portion 243. Further, the second small diameter side defining portion 632 is formed of an annular member, and is disposed between the head portion 42 of the rod-shaped member 40 and the intermediate shaft portion 43.

Here, the second coil spring 61 of the present embodiment has a pair of flat portions formed in a flat shape at the ends facing the defining portions 631 and 632 so that the contact state with the defining portions 631 and 632 is stable. Portions 612 and 613 are provided. The pair of flat portions 612 and 613 can be formed by subjecting both end portions of the second coil spring 61 to a grinding process. The pair of flat portions 612 and 613 are provided, for example, in a range of about 3/4 winding at the end of the wire 610.

Further, in the second suspension portion 60 of the present embodiment, the second coil spring 61 is between the second large diameter side defining portion 631 and the second small diameter side defining portion 632 in a state where the second coil spring 61 is compressed to some extent in the rod axis direction DRa. It is inserted in. Therefore, the second coil spring 61 fitted between the second large-diameter side defining portion 631 and the second small-diameter side defining portion 632 has a length in the rod axis direction DRa as compared with the second coil spring 61 in the free state. It is getting smaller.

Next, how the first coil spring 51 and the second coil spring 61 are bent in the rod axis direction DRa and the rod diameter direction DRr will be described. The first coil spring 51 and the second coil spring 61 have the same way of bending in the rod axis direction DRa and the rod radial direction DRr. For this reason, below, the bending method of the 1st coil spring 51 is fundamentally demonstrated and the description about the bending method of the 2nd coil spring 61 is abbreviate | omitted.

First, how the first coil spring 51 bends in the rod axis direction DRa will be described with reference to FIGS. As shown in FIG. 4, the first coil spring 51 is in a state in which the wires 510 adjacent to each other in the rod axis direction DRa are separated from each other in the unloaded state of the suspension device 30. In this state, the spring effective length L that can be elastically deformed in the first coil spring 51 is the entire length of the first coil spring 51 in the rod axis direction DRa. That is, the first coil spring 51 of the present embodiment is in a range where the entire rod axis direction DRa of the first coil spring 51 can be elastically deformed when the suspension device 30 is in an unloaded state.

For example, when the compressor 24 vibrates in the rod axis direction DRa and the compression load Fa in the rod axis direction DRa acts on the first coil spring 51, the first coil spring 51 contracts in the rod axis direction DRa. Thereby, vibrations acting in the rod axis direction DRa are absorbed by the first coil spring 51.

Here, in the first coil spring 51, the spring constant of the large diameter portion where the coil diameter is large is smaller than the spring constant of the small diameter portion where the coil diameter is small. For this reason, when the compressive load Fa in the rod axis direction DRa acting on the first coil spring 51 increases, as shown in FIG. 5, the adjacent wire rods 510 start to come into close contact with each other in order from the portion on the large diameter side. The part where the wires 510 are in close contact with each other loses the function as a spring. For this reason, when the compressive load Fa in the rod axis direction DRa increases, the spring effective length L that can be elastically deformed in the rod axis direction DRa in the first coil spring 51 becomes small.

As described above, in the first coil spring 51 of the present embodiment, when the compressive load Fa acting in the rod axis direction DRa is increased, the contact area between the wires 510 is increased, so that the elastically deformable range is reduced. For this reason, the first coil spring 51 of the present embodiment has a nonlinear elastic characteristic in which the elastic constant (that is, the spring constant) in the rod axis direction DRa increases as the load Fa acting in the rod axis direction DRa increases. Will have.

As shown in FIG. 6, the first coil spring 51 having such non-linear elastic characteristics has a displacement amount of the first coil spring 51 in the rod axis direction DRa as the load Fa acting in the rod axis direction DRa increases. (That is, the amount of deflection) becomes small. Since the second coil spring 61 is configured in the same manner as the first coil spring 51, the second coil spring 61 has a non-linear elastic characteristic in the rod axis direction DRa similarly to the first coil spring 51.

Subsequently, how the first coil spring 51 bends in the rod radial direction DRr will be described with reference to FIGS. As shown in FIG. 7, the first coil spring 51 is in a state of being separated from the first inner wall portion 520 of the first holder portion 52 facing the rod radial direction DRr in the unloaded state of the suspension device 30. In this state, the spring effective length L that can be elastically deformed in the first coil spring 51 is the entire length of the first coil spring 51 in the rod axis direction DRa. That is, the first coil spring 51 of the present embodiment is in a range where the entire rod axis direction DRa of the first coil spring 51 can be elastically deformed when the suspension device 30 is in an unloaded state.

For example, when the compressor 24 vibrates in the rod radial direction DRr and a load Fr in the rod radial direction DRr acts on the first coil spring 51, the first coil spring 51 is elastic in the rod radial direction DRr. Bend. Thereby, the vibration acting in the rod radial direction DRr is absorbed by the first coil spring 51.

Here, in the first coil spring 51, the spring constant of the large diameter portion where the coil diameter is large is smaller than the spring constant of the small diameter portion where the coil diameter is small. For this reason, when the load Fr in the rod radial direction DRr acting on the first coil spring 51 increases, as shown in FIG. 8, the first inner wall portion 520 of the first holder portion 52 is sequentially applied from the portion on the large diameter side. Start to abut. The portion of the first coil spring 51 where the wire 510 is in contact with the first inner wall portion 520 loses its function as a spring. For this reason, when the load Fr acting in the rod radial direction DRr increases, the effective spring length L of the first coil spring 51 that can be elastically deformed in the rod radial direction DRr becomes small.

Thus, the first coil spring 51 of the present embodiment can be elastically deformed by increasing the contact area between the wire 510 and the first inner wall portion 520 when the load Fr acting in the rod radial direction DRr increases. The range becomes smaller. For this reason, the first coil spring 51 of the present embodiment has a nonlinear elastic characteristic in which the elastic constant (that is, the spring constant) in the rod radial direction DRr increases as the load Fr acting in the rod radial direction DRr increases. That is, it has spring characteristics.

As shown in FIG. 9, the first coil spring 51 having such non-linear elastic characteristics has a displacement amount of the first coil spring 51 in the rod radial direction DRr as the load Fr acting in the rod radial direction DRr increases. (That is, the amount of deflection) becomes small. Since the second coil spring 61 is configured in the same manner as the first coil spring 51, the second coil spring 61 has a non-linear elastic characteristic in the rod radial direction DRr as in the first coil spring 51.

Here, in the present embodiment, the first coil spring 51 and the second coil spring 61 constitute an elastic member that suppresses transmission of one vibration of the engine EG and the compressor 24 to the other through the rod-shaped member 40. ing.

Moreover, in this embodiment, the 1st holder part 52 and the 2nd holder part 62 comprise the displacement restriction | limiting part which restrict | limits the displacement to the crossing direction which cross | intersects the rod-axis direction DRa of the rod-shaped member 40 in an elastic member. . When the first inner wall portion 520 and the second inner wall portion 620 are subjected to a load exceeding a predetermined reference load in the intersecting direction with respect to the coil springs 51 and 61, the displacement of one part of the coil springs 51 and 61 is changed. A displacement restricting portion for restricting the movement.

The suspension device 30 according to the present embodiment described above includes the first coil spring 51 and the second coil spring 61 as elastic members that suppress transmission of vibration of one of the engine EG and the compressor 24 to the other through the rod-shaped member 40. It has. In addition, the suspension device 30 includes a first holder portion 52 and a second holder as deformation restriction portions that restrict deformation of the rod-shaped member 40 in the first coil spring 51 and the second coil spring 61 in the intersecting direction intersecting the rod axis direction DRa. A portion 62 is provided.

The first coil spring 51 and the second coil spring 61 of the present embodiment have a characteristic that the elastic constant in the rod axis direction DRa increases as the load Fa acting on the rod axis direction DRa increases. According to this, even when vibrations having different amplitudes act in the rod axis direction DRa, vibration transmission between the engine EG and the compressor 24 is performed by the first coil spring 51 and the second coil spring 61 that constitute the elastic member. Can be suppressed.

Further, the first coil spring 51 and the second coil spring 61 of the present embodiment have a contact area with the first holder part 52 and the second holder part 62 as the displacement amount in the intersecting direction intersecting the rod axis direction DRa increases. It is configured to be large. That is, the first coil spring 51 and the second coil spring 61 according to the present embodiment have a small contactable area with the holder portions 52 and 62 when the load acting in the intersecting direction is increased. It is comprised so that it may become.

According to this, even when vibrations having different amplitudes act in the rod radial direction DRr, transmission of vibrations between the engine EG and the compressor 24 by the first coil spring 51 and the second coil spring 61 constituting the elastic member. Can be suppressed.

Thus, according to the suspension device 30 of the present embodiment, the vibration isolator having nonlinear elastic characteristics with respect to two different directions, ie, the rod axis direction DRa of the rod-shaped member 40 and the intersecting direction intersecting the rod axis direction DRa. Can be realized.

Specifically, in the suspension device 30 of the present embodiment, each of the coil springs 51 and 61 is configured by a conical coil spring having a non-linear spring characteristic with respect to a load acting in the rod axis direction DRa. Further, in the suspension device 30 of the present embodiment, the first holder 52 and the second holder 62 are displaced in the intersecting direction intersecting the rod axis direction DRa of the rod-shaped member 40 in the first coil spring 51 and the second coil spring 61. It is the structure which restricts.

According to the suspension device 30 of the present embodiment, a vibration isolator having non-linear elastic characteristics with respect to two different directions can be realized with a simple configuration of the coil springs 51 and 61 and the holder portions 52 and 62. .

Here, in the suspension device 30 of the present embodiment, the inner wall portions 520 and 620 of the holder portions 52 and 62 constituting the displacement restricting portion are increased from the small diameter side to the large diameter side of the coil springs 51 and 61. It is comprised so that it may become a hole shape. According to this, not only the large diameter side but also the small diameter side of the coil springs 51 and 61 can easily come into contact with the inner wall portions 520 and 620 of the holder portions 52 and 62, so that a sufficient variable range of the spring constant can be secured. It becomes possible to do.

In addition, the suspension device 30 of the present embodiment is provided with a pair of flat portions 512, 513, 612, and 613 formed in a flat shape at portions facing the end position defining portions 53 and 63 in the coil springs 51 and 61, respectively. It has been. According to this, since the contact state between the coil springs 51 and 61 and the end position defining portions 53 and 63 can be stabilized, for example, it is biased toward a part of the end position defining portions 53 and 63. It can suppress that a load acts.

(Second Embodiment)
Next, a second embodiment will be described with reference to FIGS. This embodiment demonstrates the example which changed the shape of the both ends side of each coil spring 51 and 61 with respect to 1st Embodiment.

In the first embodiment described above, a pair of flat portions 512, 513, 612, 613 are provided at portions of the coil springs 51, 61 that face the end position defining portions 53, 63. In such a configuration, when the pair of flat portions 512, 513, 612, and 613 function as springs that are elastically deformed in the rod radial direction DRr, the spring characteristics of the coil springs 51 and 61 in the rod radial direction DRr become unstable. End up.

Based on this, in the suspension device 30 of the present embodiment, the pair of flat portions 512, 513, 612, 613 in the coil springs 51, 61 does not function as a spring that is elastically deformed in the rod radial direction DRr. Yes.

As shown in FIGS. 10 and 11, the first coil spring 51 of the present embodiment has a rod-like shape in which at least one turn of the wire rod 510 a connected to the flat portion 512 on the small diameter side of the pair of flat portions 512, 513 is a rod-like shape. The size of the member 40 is in contact with the outer periphery of the member 40. In other words, at least one turn of the wire 510a connected to the flat portion 512 on the small diameter side of the wire 510 constituting the first coil spring 51 is in contact with the rod-shaped member 40 of the present embodiment.

Further, in the first coil spring 51 of the present embodiment, at least one turn of the wire rod 510 b connected to the flat portion 513 on the large diameter side of the pair of flat portions 512 and 513 of the wire rod 510 is the first coil portion 51 of the first holder portion 52. The size is abutted against the inner wall portion 520. In other words, at least one turn of the wire rod 510b connected to the flat portion 513 on the large diameter side of the wire rod 510 constituting the first coil spring 51 is in contact with the first holder portion 52 of the present embodiment.

Subsequently, in the second coil spring 61 of the present embodiment, as shown in FIG. 10, at least one turn of the wire 610 a connected to the flat portion 612 on the small diameter side of the pair of flat portions 612 and 613 is rod-shaped. The size of the member 40 is in contact with the outer periphery of the member 40. In other words, at least one turn of the wire 610 a connected to the flat portion 612 on the small diameter side of the wire 610 constituting the second coil spring 61 is in contact with the rod-shaped member 40 of the present embodiment.

In addition, in the second coil spring 61 of the present embodiment, at least one turn of the wire 610 b connected to the large-diameter flat portion 613 of the pair of flat portions 612 and 613 of the wire 610 is the second of the second holder portion 62. The size is in contact with the inner wall portion 620. In other words, at least one turn of the wire 610b connected to the flat portion 613 on the large diameter side out of the wire 610 constituting the second coil spring 61 is in contact with the second holder portion 62 of the present embodiment.

Other configurations are the same as those in the first embodiment. The suspension device 30 of the present embodiment can obtain the same effects as those of the first embodiment with the same configuration as the suspension device 30 of the first embodiment.

In the suspension device 30 of the present embodiment, the wire rods 510a and 610a connected to the flat portions 512 and 612 on the small diameter side of the coil springs 51 and 61 are in contact with the rod-shaped member 40. In the suspension device 30 of the present embodiment, the wire members 510b and 610b connected to the flat portions 513 and 613 on the large diameter side of the coil springs 51 and 61 are in contact with the holder portions 52 and 62, respectively. According to this, since the flat portions 512, 513, 612, 613 provided on the coil springs 51, 61 hardly function as springs deforming in the rod radial direction DRr, the spring characteristics of the coil springs 51, 61 in the rod radial direction DRr are It becomes possible to stabilize.

Therefore, according to the suspension device 30 of the present embodiment, the contact state between the coil springs 51 and 61 and the end position defining portions 53 and 63 is stabilized, and the springs in the rod radial direction DRr of the coil springs 51 and 61 are provided. It becomes possible to stabilize the characteristics.

(Third embodiment)
Next, a third embodiment will be described with reference to FIGS. In the present embodiment, an example in which the shape of the end portions of the coil springs 51 and 61 and the shape of the end position defining portions 53 and 63 are changed with respect to the first embodiment will be described.

As shown in FIGS. 12 and 13, the wire 511 of the first coil spring 51 of the present embodiment has a cross-sectional shape on both ends in the rod axis direction DRa that is the same as the cross-sectional shape of other portions. That is, the first coil spring 51 of the present embodiment is not provided with a configuration corresponding to the pair of flat portions 512 and 513 described in the first embodiment on both end sides in the rod axis direction DRa.

The first coil spring 51 configured as described above has more stable spring characteristics in the rod radial direction DRr of the first coil spring 51 than the configuration in which the pair of flat portions 512 and 513 are provided on both ends in the rod axis direction DRa. It becomes possible to make it.

On the other hand, in the configuration in which the cross-sectional shape of the portion of the wire 511 of the first coil spring 51 facing the first end position defining portion 53 is the same as the cross-sectional shape of the other portions, the first coil spring 51 and the first end position defining There is a contradiction that the contact state with the portion 53 is not stable.

Therefore, in the present embodiment, the first end position defining portion 53 has the first end position defining portion 53 so that the first end position defining portion 53 abuts more than half of the portions located on both ends of the first coil spring 51. A portion facing the coil spring 51 is inclined with respect to the rod radial direction DRr. Specifically, the first large-diameter side defining portion 531 and the first small-diameter side defining portion 532 of the present embodiment are such that the portion on the opposite side of the contact portion that contacts the first coil spring 51 is in the rod diameter direction DRr. Inclined, and a portion of the first coil spring 51 opposite to the contact portion extends along the rod radial direction DRr.

Subsequently, as shown in FIG. 12, the wire 611 of the second coil spring 61 of the present embodiment has a cross-sectional shape at both ends in the rod axis direction DRa that is the same as the cross-sectional shape of other portions. In other words, the second coil spring 61 of this embodiment is not provided with a configuration corresponding to the pair of flat portions 612 and 613 described in the first embodiment on both ends in the rod axis direction DRa.

The second coil spring 61 configured in this way has more stable spring characteristics in the rod radial direction DRr in the second coil spring 61 than in the configuration in which the pair of flat portions 612 and 613 are provided on both ends in the rod axis direction DRa. It becomes possible to make it.

Further, in the present embodiment, the second end position defining portion 63 has the second end position defining portion 63 so that the second end position defining portion 63 abuts more than half of the portions located on both ends of the second coil spring 61. A portion facing the coil spring 61 is inclined with respect to the rod radial direction DRr. Specifically, the second large-diameter side defining portion 631 and the second small-diameter side defining portion 632 according to the present embodiment are such that the portion on the opposite side of the contact portion that contacts the second coil spring 61 is in the rod diameter direction DRr. Inclined, and a portion of the second coil spring 61 opposite to the contact portion extends along the rod radial direction DRr.

Other configurations are the same as those in the first embodiment. The suspension device 30 of the present embodiment can obtain the same effects as those of the first embodiment with the same configuration as the suspension device 30 of the first embodiment.

In the suspension device 30 of the present embodiment, the cross-sectional shapes of both ends in the rod axis direction DRa of the wire rods 511 and 611 constituting the coil springs 51 and 61 are the same as the cross-sectional shapes of other portions. In the suspension device 30 of the present embodiment, the portions facing the coil springs 51 and 61 in the end position defining portions 53 and 63 are applied more than half turns of the portions positioned on both ends of the coil springs 51 and 61. Inclined to touch. According to this, it is possible to stabilize the contact state between the coil springs 51 and 61 and the end position defining portions 53 and 63 and to stabilize the spring characteristics of the coil springs 51 and 61 in the rod radial direction DRr. Become.

(Fourth embodiment)
Next, a fourth embodiment will be described with reference to FIG. This embodiment demonstrates the example which changed the internal structure of each suspension part 50 and 60 with respect to 1st Embodiment.

As shown in FIG. 14, the first coil spring 51 of the first suspension part 50 of the present embodiment is arranged so that the large-diameter end having the largest coil diameter is located on the engine EG side. That is, the first coil spring 51 of the present embodiment has a coil diameter that decreases from the engine EG side toward the bottom surface side of the first housing portion 242.

Further, the first inner wall portion 520 of the first holder portion 52 of the present embodiment is configured by an inner wall portion having a hole shape that decreases from the engine EG side toward the bottom surface side of the first housing portion 242.

Further, in the first end position defining portion 53, the first large diameter side defining portion 531 is disposed between the male screw portion 41 and the intermediate shaft portion 43 of the rod-shaped member 40, and the first small diameter side defining portion 532 is the first end portion defining portion 531. 1 is disposed at the bottom of the accommodating portion 242.

Here, the first small diameter side defining portion 532 of the present embodiment is configured integrally with the first holder portion 52. The first small diameter side defining portion 532 may be configured separately from the first holder portion 52.

Subsequently, the second coil spring 61 of the second suspension unit 60 of the present embodiment is arranged so that the large-diameter end having the largest coil diameter is located on the head 42 side of the rod-shaped member 40. That is, the second coil spring 61 of the present embodiment has a coil diameter that decreases from the head portion 42 side of the rod-shaped member 40 toward the bottom surface side of the second housing portion 243.

In addition, the second inner wall portion 620 of the second holder portion 62 of the present embodiment is an inner wall portion having a hole shape that decreases from the head portion 42 side of the rod-shaped member 40 toward the bottom surface side of the second housing portion 243. It is configured.

Further, in the second end position defining portion 63, the second large diameter side defining portion 631 is disposed between the head portion 42 of the rod-shaped member 40 and the intermediate shaft portion 43, and the second small diameter side defining portion 632 is the second accommodation. It is arranged at the bottom of the part 243.

Here, the second small diameter side defining portion 632 of the present embodiment is configured integrally with the second holder portion 62. The second small diameter side defining portion 632 may be configured separately from the second holder portion 62.

Other configurations are the same as those in the first embodiment. The suspension device 30 of the present embodiment has the same configuration as that of the suspension device 30 of the first embodiment, although the internal structure of each suspension portion 50, 60 is reversed in the rod axis direction DRa with respect to the first embodiment. I have. For this reason, the suspension apparatus 30 of this embodiment can obtain the effect produced from a structure common to 1st Embodiment similarly to 1st Embodiment.

(Fifth embodiment)
Next, a fifth embodiment will be described with reference to FIGS. 15 and 16. This embodiment demonstrates the example which changed the shape of each coil spring 51 and 61 with respect to 1st Embodiment.

When the coil springs 51 and 61 are designed so that the coil center axis on the small diameter side coincides with the coil center axis on the large diameter side in the free state, when the coil springs 51 and 61 are accommodated in the holder portions 52 and 62, There is a possibility of hanging down. That is, when each coil spring 51, 61 is designed so that the small-diameter side coil central axis and the large-diameter side coil central axis coincide with each other in a free state, a part of the wire 510, 610 is not intended. There is a possibility that the inner wall portions 520 and 620 may come into contact with each other.

If a part of the wire rods 510 and 610 unintentionally contacts the inner wall portions 520 and 620, the elastic constants in the rod radial direction DRr of the coil springs 51 and 61 are increased. This is not preferable because when the vibration having a small amplitude acts in the rod radial direction DRr, it becomes difficult for the coil springs 51 and 61 to suck the vibration.

Considering this, the coil springs 51 and 61 of the present embodiment are designed so that the small-diameter side coil central axis Cs and the large-diameter side coil central axis Cb are displaced in a free state as shown in FIG. Has been. In other words, in the coil springs 51 and 61 of the present embodiment, the small diameter side of each coil spring 51 and 61 is offset in the direction opposite to the direction of gravity in comparison with the large diameter side in the free state. Accordingly, as shown in FIG. 16, the coil springs 51 and 61 of the present embodiment are prevented from drooping downward due to their own weight when installed in the holder portions 52 and 62.

Other configurations are the same as those in the first embodiment. The suspension device 30 of the present embodiment can obtain the same effects as those of the first embodiment with the same configuration as the suspension device 30 of the first embodiment.

In the suspension device 30 of the present embodiment, the small diameter side of each of the coil springs 51 and 61 is offset in the direction opposite to the direction of action of gravity compared to the large diameter side. According to this, it becomes possible to suppress that a spring characteristic changes with the deformation | transformation by the dead weight of each coil spring 51,61.

(Sixth embodiment)
The first end position defining portion 53 of the first embodiment includes a first large-diameter side defining portion 531 disposed in a first accommodating portion 242 formed in the compressor-side housing 240 and a male screw portion 41 of the rod-shaped member 40. And the first small diameter side defining portion 532 disposed between the intermediate shaft portion 43 and the intermediate shaft portion 43. In addition, the second end position defining portion 63 of the first embodiment includes the second large-diameter side defining portion 631 disposed in the second housing portion 243 formed in the compressor-side housing 240 and the head of the rod-shaped member 40. 42 and a second small diameter side defining portion 632 disposed between the intermediate shaft portion 43 and the intermediate shaft portion 43.

Moreover, in 1st Embodiment, each inner wall part 520,620 which functions as a displacement restriction | limiting part is formed in each holder part 52,62 press-fit in each accommodating part 242,243 of the compressor side housing 240. FIG. . For this reason, in the first embodiment, the large diameter side defining portions 531 and 631 and the inner side wall portions 520 and 620 are set on the compressor 24 side, and the small diameter side defining portions 532 and 632 are fixed to the engine side housing EGH. It is set to the rod-shaped member 40 side. In the first embodiment and the present embodiment, the large diameter side defining portions 531 and 631 constitute a first axial direction defining portion, and the small diameter side defining portions 532 and 632 constitute a second axial direction defining portion. ing.

The present inventors diligently studied the above-described structure in order to further improve the suspension device 30. As a result, it has been found that, in the above-described structure, when the load in the rod radial direction DRr acts, the small diameter side defining portions 532 and 632 and the inner side wall portions 520 and 620 may contact each other. When the small diameter side defining portions 532 and 632 and the inner wall portions 520 and 620 come into contact with each other, the nonlinear elastic characteristics of the coil springs 51 and 61 are not exhibited, so that the effect of suppressing vibration transmission cannot be sufficiently obtained. There is a risk of it.

Therefore, in the present embodiment, in order to suppress contact between the small diameter side defining portions 532 and 632 and the inner wall portions 520 and 620, the shape of the small diameter side defining portions 532 and 632 is different from that of the first embodiment. It has changed. In the present embodiment, portions different from those in the first embodiment will be mainly described, and descriptions of portions similar to those in the first embodiment may be omitted.

As shown in FIG. 17, the suspension device 30 of the present embodiment has a cylindrical portion 44 in which a rod-shaped member 40 is formed in a cylindrical shape. The cylindrical portion 44 covers the outer periphery of the intermediate shaft portion 43, and the inner diameter is set to be approximately the same as the outer diameter of the intermediate shaft portion 43.

The cylindrical portion 44 is inserted into the insertion hole 241 of the compressor side housing 240 together with the intermediate shaft portion 43. The insertion hole 241 of the present embodiment is set to such a size that a gap is formed between the coil springs 51 and 61 and the cylindrical portion 44 of the rod-shaped member 40 even when the displacement amount in the rod radial direction DRr is maximized. Has been. According to this, it is possible to prevent the rod-shaped member 40 and the inner wall of the insertion hole 241 from coming into direct contact when a load in the rod radial direction DRr is applied.

The first small diameter side defining portion 532 of the present embodiment is integrally provided on the male screw portion 41 side in the tubular portion 44. The first small diameter side defining portion 532 of the present embodiment has a first defining side contact portion 533 that contacts the first coil spring 51. The first defining side contact portion 533 is a first holder portion in the rod diameter direction DRr in a state where no load is applied to either the rod axis direction DRa or the rod diameter direction DRr of the first small diameter side defining portion 532. 52 is a part overlapping with 52.

The first regulation side contact part 533 is a part that regulates the displacement of the first coil spring 51 when a load is applied in the rod axis direction DRa. For this reason, as shown in FIG. 18, the 1st prescription | regulation side contact part 533 is comprised so that a contact state with the 1st coil spring 51 may be maintained even if a load acts on the rod axial direction DRa. That is, the first prescribed-side contact portion 533 has an outer diameter Dpe1 larger than a line center diameter Dsc that is intermediate between the outer diameter Dse1 and the inner diameter of the first spring-side contact portion 514 of the first coil spring 51. ing. The first spring-side contact portion 514 described above is a portion of the first coil spring 51 that contacts the first specified-side contact portion 533. Further, the line center diameter Dsc can be interpreted as an average diameter obtained by averaging the outer diameter Dse1 and the inner diameter of the first spring-side contact portion 514.

Here, the first prescribed-side contact portion 533 overlaps the first holder portion 52 in the rod radial direction DRr, and may contact the first inner wall surface 520 when a load in the rod radial direction DRr is applied. There is.

For this reason, the 1st regulation side contact part 533 is the shape spaced apart from the 1st inner side wall surface 520 so that a clearance gap may be formed between the 1st inner side wall surface 520 even if the load of rod diameter direction DRr acts. It has become. In other words, the outer diameter Dpe1 of the first specified-side contact portion 533 is smaller than the outer diameter Dse1 of the first spring-side contact portion 514.

Further, when a load is applied in the rod axis direction DRa, a portion of the first small diameter side defining portion 532 that is opposite to the first defining side contact portion 533 overlaps the first holder portion 52 in the rod diameter direction DRr. May be in a state. When a load in the rod diameter direction DRr is applied in this state, a portion of the first small diameter side defining portion 532 that is opposite to the first defining side contact portion 533 may come into contact with the first inner wall surface 520. .

For this reason, the first small-diameter side defining portion 532 has a shape in which a gap is formed between the first inner wall surface 520 even if a load acts on both the rod axis direction DRa and the rod diameter direction DRr. That is, the first small-diameter side defining portion 532 has a rod shaft so that the outer diameter Dpe1 of the first defining-side contact portion 533 is larger than the outer diameter of the portion on the opposite side of the first defining-side contact portion 533. An inclined surface 534 inclined with respect to the direction DRa is provided. The inclined surface 534 of the first small diameter side defining portion 532 is formed such that the inclination angle θα1 with respect to the rod axis direction DRa is larger than the inclination angle θβ1 with respect to the rod axis direction DRa of the first inner wall surface 520.

Returning to FIG. 17, the second small-diameter side defining portion 632 of the present embodiment is disposed between the end portion on the head portion 42 side of the tubular portion 44 and the head portion 42. The second small diameter side defining portion 632 of the present embodiment has a second defining side abutting portion 633 that abuts on the second coil spring 61. The second defining side contact portion 633 is a second holder portion in the rod diameter direction DRr in a state where no load is applied to either the rod axis direction DRa or the rod diameter direction DRr of the second small diameter side defining portion 632. This is a part overlapping with 62.

The second regulation side contact part 633 is a part that regulates the displacement of the second coil spring 61 when a load is applied in the rod axis direction DRa. For this reason, the 2nd regulation side contact part 633 is comprised so that a contact state with the 1st coil spring 51 may be maintained even if a load acts on the rod axial direction DRa. That is, the outer diameter Dpe2 of the second specified-side contact portion 633 is larger than the line center diameter Dsc that is intermediate between the outer diameter Dse2 and the inner diameter of the second spring-side contact portion 614 of the second coil spring 61. ing. The second spring-side contact portion 614 described above is a portion that contacts the second specified-side contact portion 633 in the second coil spring 61. Further, the interline center diameter Dsc can be interpreted as an average diameter obtained by averaging the outer diameter Dse2 and the inner diameter of the second spring-side contact portion 614.

In addition, the second prescribed-side contact portion 633 is shaped to be separated from the second inner wall surface 620 so that a gap is formed between the second inner wall surface 620 and the load in the rod radial direction DRr. It has become. In other words, the outer diameter Dpe2 of the second prescribed-side contact portion 633 is smaller than the outer diameter Dse2 of the second spring-side contact portion 614.

Furthermore, the second small-diameter side defining portion 632 has a shape in which a gap is formed between the first inner wall surface 520 even if a load acts on both the rod axis direction DRa and the rod diameter direction DRr. That is, the second small-diameter side defining portion 632 is configured so that the outer diameter Dpe2 of the second defining-side contact portion 633 is larger than the outside diameter of the portion on the opposite side of the second defining-side contact portion 633. An inclined surface 634 that is inclined with respect to the direction DRa is provided. The inclined surface 634 of the second small diameter side defining portion 632 is formed such that the inclination angle θα2 with respect to the rod axis direction DRa is larger than the inclination angle θβ2 with respect to the rod axis direction DRa of the second inner wall surface 620.

Subsequently, an operation state when a load is applied to the suspension device 30 of the present embodiment will be described. In the suspension device 30, for example, when the compressor 24 vibrates in the rod radial direction DRr and a load in the rod radial direction DRr acts on the coil springs 51, 61, the coil springs 51, 61 are in an elastic state. Deflection in the rod radial direction DRr. As a result, vibrations acting in the rod radial direction DRr are absorbed by the coil springs 51 and 61.

When the load in the rod radial direction DRr acting on the coil springs 51 and 61 is increased, the inner wall portions 520 and 620 of the holder portions 52 and 62 are contacted in order from the portion on the large diameter side, and finally, As shown in FIG. 19, the portion on the small diameter side comes into contact with the respective inner wall portions 520 and 620.

At this time, each of the small-diameter side defining portions 532 and 632 has an outer diameter Dpe1 and Dpe2 of each defining- side contact portion 533 and 633 larger than the line center diameter Dsc of each spring- side contacting portion 514 and 614. The contact state between the small diameter side defining portions 532 and 632 and the coil springs 51 and 61 is maintained.

Further, in each of the small diameter side defining portions 532 and 632, the outer diameters Dpe1 and Dpe2 of the respective defined side contact portions 533 and 633 are smaller than the outer diameters Dse1 and Dse2 of the respective spring side contact portions 514 and 614. Therefore, the small diameter side defining portions 532 and 632 are in a state of being separated from the inner wall portions 520 and 620.

As described above, in the suspension device 30 according to the present embodiment, even if a load in the rod radial direction DRr acts on the coil springs 51 and 61, the small diameter side defining portions 532 and 632 are separated from the inner wall portions 520 and 620, respectively. It is a structure in which the separated state is maintained. For this reason, in the suspension device 30 of the present embodiment, even if a load in the rod radial direction DRr acts on the coil springs 51 and 61, the small diameter side defining portions 532 and 632 are directly applied to the inner wall portions 520 and 620, respectively. Can be prevented from touching.

Here, in the suspension device 30, for example, when the compressor 24 vibrates in the rod axis direction DRa, the load in the rod axis direction DRa and the load in the rod radial direction DRr simultaneously act on the coil springs 51 and 61. .

In this case, for example, as shown in FIG. 20, a portion of the first small-diameter side defining portion 532 other than the first defining-side contact portion 533 is located in the first holder portion 52 and at the same time, the small diameter of the first coil spring 51 The side portion may come into contact with the first inner wall portion 520. In such a state, there is a possibility that parts of the first small diameter side defining part 532 other than the first defining side contact part 533 may contact the first inner wall surface 520.

On the other hand, in the present embodiment, inclined surfaces 534 and 634 are provided for the respective small diameter side defining portions 532 and 632, and the inclination angles θα1 and θα2 of the inclined surfaces 534 and 634 are set to the respective inner wall surfaces 520 and 620. The inclination angles are larger than θβ1 and θβ2. According to this, the clearance dimension between each small diameter side definition part 532,632 and each inner wall surface 520,620 becomes large as it leaves | separates from the each definition side contact part 533,633 in the rod axis direction DRa.

For this reason, in the suspension device 30 of the present embodiment, even if the loads in the rod axis direction DRa and the rod radial direction DRr act simultaneously, the small diameter side defining portions 532, 632 other than the defined side contact portions 533, 633 Can be prevented from coming into direct contact with the inner wall surfaces 520 and 620.

Here, FIG. 21 shows a measurement result of vibration of the compressor 24 when the suspension device 30 as a comparative example of the present embodiment is used. FIG. 22 shows a measurement result of vibration of the compressor 24 when the suspension device 30 as a comparative example of the present embodiment is used. The suspension device 30 as a comparative example is configured in the same manner as in the first embodiment.

As shown in FIGS. 21 and 22, when the suspension device 30 as a comparative example is used, the vibration of the compressor 24 increases. This is considered to be due to the fact that the small diameter side defining portions 532 and 632 are in direct contact with the respective inner wall surfaces 520 and 620 in the suspension device 30 as the comparative example.

On the other hand, when the suspension device 30 of the present embodiment is used, the vibration of the compressor 24 becomes smaller than when the suspension device 30 as a comparative example is used. This is presumed to be due to the fact that in the suspension device 30 of the present embodiment, the respective small diameter side defining portions 532 and 632 are maintained in a state of being separated from the respective inner wall surfaces 520 and 620.

(Modification of the sixth embodiment)
As in the sixth embodiment described above, it is desirable to provide the inclined surfaces 534 and 634 with respect to the small diameter side defining portions 532 and 632, but the present invention is not limited to this. For example, the suspension device 30 may have a configuration in which the inclined surfaces 534 and 634 are not provided for the small-diameter side defining portions 532 and 632.

In the above-described sixth embodiment, the example in which the first small diameter side defining portion 532 is configured integrally with the cylindrical portion 44 has been described, but the present invention is not limited to this. The first small diameter side defining portion 532 may be configured separately from the cylindrical portion 44.

In the above-described sixth embodiment, the configuration in which the cylindrical portion 44 is added to the rod-shaped member 40 is exemplified, but the present invention is not limited to this. The rod-shaped member 40 may be configured not to have the cylindrical portion 44 as in the first embodiment.

(Seventh embodiment)
Next, a seventh embodiment will be described with reference to FIGS. This embodiment is different from the first embodiment in that the elastic member of the first suspension part 50A is constituted by the first spiral spring 51A and the elastic member of the second suspension part 60A is constituted by the second spiral spring 61A. is doing. In the present embodiment, portions different from those in the first embodiment will be mainly described, and descriptions of portions similar to those in the first embodiment may be omitted.

As shown in FIG. 23, the suspension device 30 of the present embodiment has a cylindrical portion 44 in which a rod-shaped member 40 is formed in a cylindrical shape, similarly to the sixth embodiment. The cylindrical portion 44 covers the outer periphery of the intermediate shaft portion 43, and the inner diameter is set to be approximately the same as the outer diameter of the intermediate shaft portion 43.

The cylindrical portion 44 is inserted into the insertion hole 241 of the compressor side housing 240 together with the intermediate shaft portion 43. The insertion hole 241 of the present embodiment is large enough to form a gap with the cylindrical portion 44 of the rod-like member 40 even if the displacement amount in the rod radial direction DRr of each of the spiral springs 51A and 61A described later is maximized. Is set. Specifically, the insertion hole 241 has a gap Ga formed between the cylindrical portion 44 in the rod radial direction DRr and the thickness t of the plate material 510A of the spiral spring 51A and the number of turns N of the spiral spring 51A. It is formed so as to be larger than a value obtained by multiplying. Further, the insertion hole 241 has an outer diameter Dh smaller than outer diameters Dpi1 and Dpi2 of spiral springs 51A and 61A described later.

Further, the first suspension portion 50A of the present embodiment is provided on one end side of the intermediate shaft portion 43 of the rod-like member 40 that is close to the engine-side housing EGH. The first suspension part 50A includes a first spiral spring 51A, a first displacement restriction part 54 that restricts displacement of the first spiral spring 51A in the rod radial direction DRr, and both ends of the first spiral spring 51A in the rod axis direction DRa. A first outer circumferential side defining portion 55 and a first inner circumferential side defining portion 56 that define the position are provided.

The first spiral spring 51 </ b> A is an elastic member that suppresses transmission of vibration of one of the engine EG and the compressor 24 to the other through the rod-shaped member 40. 51 A of 1st spiral springs are arrange | positioned with the attitude | position which the coil center axis | shaft which tied the center of the coil diameter extended along the rod-axis direction DRa of the rod-shaped member 40. As shown in FIG. The first spiral spring 51A of the present embodiment is arranged so that the end portion on the inner peripheral side with the smallest coil diameter is located on the engine EG side.

Here, as shown in FIGS. 24 and 25, the first spiral spring 51A is a spring configured by winding a rectangular plate 510A in a conical shape. The first spiral spring 51A is formed such that a gap is generated between portions of the plate material 510A adjacent to each other in the rod radial direction DRr. The plate material 510A constituting the first spiral spring 51A has a uniform length in the rod axis direction DRa. 51 A of 1st spiral springs have comprised the spiral shape wound so that the inner peripheral side might protrude in the rod-axis direction DRa with respect to the outer peripheral side.

Further, the first spiral spring 51A of the present embodiment is configured such that a part of the plate material 510A adjacent to the rod radial direction DRr overlaps with the rod radial direction DRr. Thus, the first spiral spring 51A is configured such that a part of the adjacent plate material 510A contacts when a load is applied from the rod radial direction DRr.

23, the first displacement limiting portion 54 is configured by an inner wall surface extending along the rod axis direction DRa in the first accommodating portion 242. The first displacement limiting portion 54 has a size that allows the first spiral spring 51A to be accommodated therein. Specifically, the first displacement limiting portion 54 is sized to abut on the entire portion located on the outer peripheral side in the rod radial direction DRr of the first spiral spring 51A.

The first outer peripheral side defining portion 55 defines the position of the portion located on the outermost peripheral side in the first spiral spring 51A. The first outer peripheral side defining portion 55 is configured by a bottom portion of the first accommodating portion 242 that extends along the rod radial direction DRr.

The first outer circumferential side defining portion 55 is configured to overlap with a portion located on the innermost circumferential side in the first spiral spring 51A in the rod axis direction DRa. Thereby, when a predetermined compressive load is applied to the first spiral spring 51A in the rod axis direction DRa, the first outer peripheral side defining portion 55 is not limited to the inner peripheral portion of the first spiral spring 51A. The peripheral part is also easily abutted. In the present embodiment, the outer diameter Dh of the insertion hole 241 is smaller than the outer diameter Dpi1 of the portion located on the innermost peripheral side of the first spiral spring 51A. For this reason, the site | part on the inner peripheral side of 51 A of 1st spiral springs does not displace to the inner side of the insertion hole 241. FIG.

The first inner circumferential side defining portion 56 defines the position of the portion located on the innermost circumferential side in the first spiral spring 51A. The first inner peripheral side defining portion 56 is integrally provided on the male screw portion 41 side in the tubular portion 44. The first inner circumferential side defining portion 56 of the present embodiment has a first defining side contact portion 561 that contacts the first spiral spring 51A.

The first defining side contact portion 561 has a first displacement in the rod radial direction DRr in a state where no load is applied to either the rod axial direction DRa or the rod radial direction DRr in the first inner circumferential side defining portion 56. This is a part that overlaps with the restriction part 54.

The first regulation side contact part 561 is a part that regulates the displacement of the first spiral spring 51A when a load is applied in the rod axis direction DRa. For this reason, the 1st regulation side contact part 561 is comprised so that a contact state with 51 A of 1st spiral springs may be maintained even if a load acts on the rod axial direction DRa. That is, as shown in FIG. 26, the first prescribed-side contact portion 561 has an outer diameter Dve1 larger than the inner diameter Dsi1 of the first spring-side contact portion 514 located on the innermost side of the first spiral spring 51A. It is getting bigger. The first spring-side contact portion 514 described above is a portion that contacts the first specified-side contact portion 561 in the first spiral spring 51A.

Here, the first inner circumferential side defining portion 56 has a portion overlapping the first displacement limiting portion 54 in the rod radial direction DRr, and when the load in the rod radial direction DRr is applied, the first displacement limiting portion 54 may come into contact.

For this reason, the first inner circumferential side defining portion 56 is separated from the first displacement limiting portion 54 so that a gap is formed between the first inner circumferential side defining portion 56 and the first displacement limiting portion 54 even when a load in the rod radial direction DRr is applied. It is configured to do. That is, the first inner circumferential side defining portion 56 has a gap size Gb1 with the first displacement limiting portion 54 in the rod radial direction DRr so that the plate thickness 510 of the plate material 510A of the first spiral spring 51A and the effective winding of the spiral spring 51A. It is configured to be larger than a value obtained by multiplying the number Ne. Note that the effective number of turns Ne of the spiral spring 51A is the number of turns obtained by removing the first spring-side contact portion 514 from the actual number of turns N of the spiral spring 51A (ie, Ne = N−1).

Subsequently, the second suspension 60A of the present embodiment will be described. The second suspension portion 60 </ b> A of the present embodiment is provided on the other end side of the intermediate shaft portion 43 of the rod-shaped member 40. The second suspension portion 60A includes a second spiral spring 61A, a second displacement restriction portion 64 that restricts displacement of the second spiral spring 61A in the rod radial direction DRr, and both end portions of the second spiral spring 61A in the rod axis direction DRa. A second outer peripheral side defining portion 65 and a second inner peripheral side defining portion 66 that define the position are provided.

The second spiral spring 61 </ b> A is an elastic member that suppresses transmission of vibration of one of the engine EG and the compressor 24 to the other via the rod-shaped member 40. The second spiral spring 61 </ b> A is arranged in such a posture that the coil center axis connecting the centers of the coil diameters extends along the rod axis direction DRa of the rod-shaped member 40. The second spiral spring 61 </ b> A of the present embodiment is arranged so that the end portion on the inner peripheral side having the smallest coil diameter is located on the head 42 side of the rod-shaped member 40.

The second spiral spring 61A is a spring configured by winding a rectangular plate 510A in a conical shape. Note that the second spiral spring 61A is configured in the same manner as the first spiral spring 51A, and therefore a detailed description thereof is omitted.

The second displacement limiting portion 64 is configured by an inner wall surface extending along the rod axis direction DRa in the second accommodating portion 243. The second displacement limiting portion 64 has a size that allows the second spiral spring 61A to be accommodated therein. Specifically, the second displacement limiting portion 64 is sized to abut on the entire portion of the second spiral spring 61A located on the outer peripheral side in the rod radial direction DRr.

The second outer peripheral side defining portion 65 is for defining the position of the most outer peripheral side portion of the second spiral spring 61A. The 2nd outer peripheral side prescription | regulation part 65 is comprised by the bottom part extended along the rod radial direction DRr among the 2nd accommodating parts 243. As shown in FIG.

The second outer peripheral side defining portion 65 is configured to overlap in the rod axial direction DRa with a portion located on the innermost peripheral side in the second spiral spring 61A. As a result, the second outer peripheral side defining portion 65 is not limited to the inner peripheral portion of the second spiral spring 61A when a predetermined compressive load is applied to the second spiral spring 61A in the rod axis direction DRa. The peripheral part is also easily abutted. In the present embodiment, the outer diameter Dh of the insertion hole 241 is smaller than the outer diameter Dpi2 of the portion located on the innermost side of the second spiral spring 61A. For this reason, the site | part of the inner peripheral side of 2nd spiral spring 61A does not displace to the inner side of the insertion hole 241. FIG.

The second inner circumferential side defining portion 66 defines the position of the portion located on the innermost circumferential side in the second spiral spring 61A. The second inner peripheral side defining portion 66 is disposed between the end portion of the tubular portion 44 and the head portion 42 of the rod-shaped member 40. The second inner circumferential side defining portion 66 of the present embodiment has a second defined side contact portion 661 that contacts the second spiral spring 61A.

The second regulation side contact part 661 is a part that regulates the displacement of the second spiral spring 61A when a load is applied in the rod axis direction DRa. For this reason, the 2nd regulation side contact part 661 is comprised so that a contact state with 61 A of 2nd spiral springs may be maintained even if a load acts on the rod axial direction DRa. That is, the second prescribed side contact portion 661 has an outer diameter Dve2 larger than the inner diameter Dsi2 of the second spring side contact portion 614 located on the innermost peripheral side of the second spiral spring 61A. The second spring-side contact portion 614 described above is a portion that contacts the second specified-side contact portion 661 in the second spiral spring 61A.

Further, the second inner circumferential side defining portion 66 is separated from the second displacement limiting portion 64 so that a gap is formed between the second inner circumferential side defining portion 66 and the second displacement limiting portion 64 even when a load in the rod radial direction DRr is applied. It is configured. That is, the second inner circumferential side defining portion 66 has a gap size Gb2 with the second displacement limiting portion 64 in the rod radial direction DRr so that the plate thickness t of the plate material 610A of the second spiral spring 61A and the effective winding of the spiral spring 51A. It is configured to be larger than a value obtained by multiplying the number Ne. Note that the effective number of turns Ne of the second spiral spring 61A is the number of turns obtained by removing the second spring-side contact portion 614 from the actual number of turns N of the second spiral spring 61A (ie, Ne = N−1). .

Here, in this embodiment, the displacement limiting portions 54 and 64 and the outer peripheral side defining portions 55 and 65 are set in the accommodating portions 242 and 243 of the compressor-side housing 240, respectively. In the present embodiment, the inner peripheral side defining portions 56 and 66 are set on the rod-like member 40 side fixed to the engine side housing EGH. Therefore, in the first embodiment and the present embodiment, the outer peripheral side defining portions 55 and 65 constitute the first axial direction defining portion, and the inner peripheral side defining portions 56 and 66 constitute the second axial direction defining portion. is doing.

Subsequently, an operation state when a load is applied to the suspension device 30 of the present embodiment will be described. In the suspension device 30, the plate members 510A and 610A adjacent to each other in the rod radial direction DRr of the spiral springs 51A and 61A are separated from each other in the unloaded state, and the inner portions of the spiral springs 51A and 61A are the outer peripheral side defining portions. It is in a state of being separated from 55 and 65.

In this state, for example, when the compressor 24 vibrates in the rod radial direction DRr and a load in the rod radial direction DRr acts on the spiral springs 51A and 61A, the spiral springs 51A and 61A have elasticity. To bend in the rod radial direction DRr. As a result, vibrations acting in the rod radial direction DRr are absorbed by the spiral springs 51A and 61A.

When the load in the rod radial direction DRr acting on the spiral springs 51A and 61A increases, the adjacent plate members 510A and 610A start to come into close contact with each other from the outer peripheral side. The part where the plate members 510A and 610A are in close contact with each other loses the function as a spring. For this reason, when the load in the rod radial direction DRr increases, the effective spring length that can be elastically deformed in the rod radial direction DRr in each of the spiral springs 51A and 61A decreases.

As described above, the spiral springs 51A and 61A of the present embodiment increase the contact area between the plate members 510A and 610A when the load acting in the rod radial direction DRr increases, thereby reducing the elastically deformable range. . For this reason, each spiral spring 51A, 61A of the present embodiment has nonlinear elastic characteristics in which the elastic constant in the rod radial direction DRr increases as the load acting on the rod radial direction DRr increases.

On the other hand, for example, when the compressor 24 vibrates in the rod axis direction DRa and a load in the rod axis direction DRa acts on the spiral springs 51A and 61A, the spiral springs 51A and 61A Deflection in the axial direction DRa. As a result, vibrations acting in the rod axis direction DRa are absorbed by the spiral springs 51A and 61A.

When the load in the rod radial direction DRr acting on the spiral springs 51A and 61A increases, the outer peripheral side defining portions 55 and 65 start to contact in order from the outer peripheral side portion. The portions of the spiral springs 51A and 61A that are in contact with the outer peripheral side defining portions 55 and 65 lose their function as springs. For this reason, when the load in the rod axis direction DRa increases, the effective spring length that can be elastically deformed in the rod axis direction DRa in each of the spiral springs 51A and 61A decreases.

As described above, the spiral springs 51A and 61A of the present embodiment increase the contact area between the plate members 510A and 610A and the outer peripheral side defining portions 55 and 65 when the load acting in the rod axis direction DRa increases. The range in which elastic deformation is possible is reduced. For this reason, each spiral spring 51A, 61A of the present embodiment has nonlinear elastic characteristics in which the elastic constant in the rod axis direction DRa increases as the load acting in the rod axis direction DRa increases.

Here, when the load acting on the rod axis direction DRa increases, the first spiral spring 51A finally comes into contact with the first outer peripheral side defining portion 55 as shown in FIG. . In this state, the first defining side contact portion 561 of the first inner circumferential side defining portion 56 is located in the first accommodating portion 242.

At this time, for example, when a load in the rod radial direction DRr is applied to the first spiral spring 51A, the first inner circumferential side defining portion 56 is displaced in the rod radial direction DRr as shown in FIG. Thus, there is a possibility that the first displacement limiting portion 54 may come into contact.

On the other hand, in this embodiment, the dimension Gb1 of the gap between the first inner peripheral side defining portion 56 and the first displacement limiting portion 54 in the rod radial direction DRr is the thickness t of the plate material 510A of the first spiral spring 51A. And the effective number of turns Ne of the spiral spring 51A is configured to be larger than the value.

For this reason, in the suspension device 30 of the present embodiment, even if the loads in the rod axis direction DRa and the rod radial direction DRr are simultaneously applied, the inner peripheral side defining portions 56 and 66 are directly applied to the displacement limiting portions 54 and 64, respectively. It is possible to prevent contact.

Furthermore, in the present embodiment, the insertion hole 241 formed in the compressor-side housing 240 causes the cylindrical portion 44 of the rod-shaped member 40 even if the displacement amount in the rod radial direction DRr of each of the spiral springs 51A and 61A is maximized. Is set to such a size that a gap is formed between them. According to this, it is possible to prevent the rod-shaped member 40 and the inner wall of the insertion hole 241 from coming into direct contact when a load in the rod radial direction DRr is applied.

(Modification of the seventh embodiment)
In the above-described seventh embodiment, the example in which the first inner peripheral side defining portion 56 is configured integrally with the cylindrical portion 44 has been described, but the present invention is not limited to this. The first inner circumferential side defining portion 56 may be configured separately from the cylindrical portion 44.

In the above-described seventh embodiment, the configuration in which the cylindrical portion 44 is added to the rod-shaped member 40 is exemplified, but the present invention is not limited to this. The rod-shaped member 40 may be configured not to have the cylindrical portion 44 as in the first embodiment.

In the seventh embodiment described above, the example in which the displacement limiting portions 54 and 64 are configured by the wall surfaces of the accommodating portions 242 and 243 has been described, but the present invention is not limited to this. Each displacement limitation part 54 and 64 may be comprised by the holder part press-fitted in each accommodating part 242 and 243 like 1st Embodiment.

(Other embodiments)
As mentioned above, although typical embodiment of this indication was described, this indication is not limited to the above-mentioned embodiment, for example, can be variously changed as follows.

In the first to sixth embodiments described above, the conical coil spring is exemplified as the elastic member, but the present invention is not limited to this. The elastic member may be constituted by, for example, a drum-shaped coil spring having an intermediate coil diameter smaller than the coil diameters at both ends, or a barrel-shaped coil spring having an intermediate coil diameter larger than the coil diameters at both ends. Good.

In the first to sixth embodiments described above, the example has been described in which the inner wall portions 520 and 620 of the holder portions 52 and 62 have shapes corresponding to the outer shapes of the coil springs 51 and 61. However, the present invention is not limited to this. . Each inner wall part 520, 620 of each holder part 52, 62 may have a shape such that a cylindrical space is formed therein, for example.

In each of the above-described embodiments, the example in which the rod-shaped member 40 is arranged in a posture extending along the horizontal direction has been described, but the present invention is not limited to this. The rod-shaped member 40 may be arranged, for example, in a posture extending along the vertical direction or a posture extending along a direction intersecting both the vertical direction and the horizontal direction.

In each of the above-described embodiments, the example in which one end side of the rod-shaped member 40 is screw-fastened to the engine-side housing EGH is described. However, the present invention is not limited thereto. It may be fixed by welding or the like.

In the above-described first to third embodiments, the example in which each holder part 52, 62 is configured separately from each accommodating part 242, 243 has been described, but the present invention is not limited thereto, and each holder part 52, 62 has , And may be configured integrally with each of the accommodating portions 242, 243.

In the above-described first to third embodiments, the example in which each large-diameter side defining portion 531 and 631 is configured separately from each accommodating portion 242 and 243 has been described. The side defining portions 531 and 631 may be configured integrally with the accommodating portions 242 and 243.

Furthermore, in the first to third embodiments described above, an example in which the small diameter side defining portions 532 and 632 are configured separately from the engine side housing EGH has been described. 632 may be integrated with the engine-side housing EGH.

In each of the above-described embodiments, the example in which the suspension device 30 that functions as the vibration isolator is configured by the first suspension unit 50 and the second suspension unit 60 has been described. However, the present invention is not limited thereto, and the first suspension unit 50 is not limited thereto. Alternatively, one of the second suspension portions 60 may be configured.

In each of the above-described embodiments, the example in which the vibration isolator of the present disclosure is applied to the suspension device 30 that connects the engine EG and the compressor 24 has been described. However, the present invention is not limited thereto, The present invention can be widely applied to a connection portion between devices that generate vibration.

In the above-described embodiment, it is needless to say that elements constituting the embodiment are not necessarily indispensable except for the case where it is clearly indicated that the element is essential and the case where the element is clearly considered to be essential in principle.

In the above-described embodiment, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is particularly limited to a specific number when clearly indicated as essential and in principle. Except in some cases, the number is not limited.

In the above embodiment, when referring to the shape, positional relationship, etc. of the component, etc., the shape, positional relationship, etc. unless otherwise specified and in principle limited to a specific shape, positional relationship, etc. It is not limited to etc.

(Summary)
According to the first aspect shown in a part or all of the above-described embodiments, the prevention device has an elastic constant that increases in the rod axis direction as the load acting on the elastic member in the rod axis direction increases. It has the characteristic to do. Furthermore, the elastic member is configured such that the contact area with the displacement limiting portion increases as the amount of displacement in the intersecting direction of the elastic member increases.

Further, according to the second aspect, the vibration isolator is configured such that the elastic member includes a conical coil spring having a non-linear spring characteristic with respect to a load acting in the rod axis direction. Moreover, the displacement limiting part is comprised including the holder part which covers the site | part exposed to the outer side of the cross direction in an elastic member. The holder portion is provided with a displacement restricting portion that abuts against one portion of the coil spring when a load exceeding a predetermined reference load is applied to the coil spring in the crossing direction and restricts the displacement of the one portion of the coil spring. Yes.

When the contact area of the coil spring configured in this way with the displacement restricting portion of the holder portion increases, the spring effective length that can be elastically deformed decreases, and the spring constant increases. That is, according to the present disclosure, it is possible to realize a vibration isolator having a non-linear spring characteristic with respect to the rod axis direction and the intersecting direction intersecting the rod axis direction with a simple configuration of the coil spring and the holder portion. .

Further, according to the third aspect, the vibration isolator is configured by an inner wall portion having a hole shape in which the displacement restricting portion increases from the small diameter side to the large diameter side of the coil spring in the holder portion. In this way, if the displacement restricting portion is configured by the inner wall portion having a hole shape that increases from the small diameter side to the large diameter side of the coil spring, not only the large diameter side but also the small diameter side of the coil spring is the inner wall portion of the holder portion. Therefore, it is possible to sufficiently secure a variable range of the spring constant.

Further, according to the fourth aspect, the vibration isolator includes end position defining portions that define the positions of both end portions of the coil spring in the rod axis direction. The coil spring is provided with a pair of flat portions formed in a flat shape at portions facing the end position defining portions at both ends in the rod axis direction. The rod-shaped member is in contact with at least one turn of the wire connected to the flat portion on the small diameter side of the pair of flat portions. Further, at least one turn of the wire connected to the large diameter flat portion of the pair of flat portions is in contact with the holder portion.

In the configuration in which the flat portion is provided in the portion of the coil spring facing the end position defining portion, the contact state between the coil spring and the end position defining portion can be stabilized. It is possible to suppress the load from acting on the portion.

On the other hand, in the configuration in which the flat portion is provided in the portion facing the end position defining portion in the coil spring, if the flat portion provided in the coil spring functions as a spring that deforms in the rod radial direction, the spring characteristics in the rod radial direction of the coil spring are reduced. There is a trade-off that it becomes unstable.

In contrast, in the coil spring of the present disclosure, the wire connected to the flat portion on the small diameter side contacts the rod-shaped member, and the wire connected to the flat portion on the large diameter side contacts the holder portion. According to this, since the flat portion provided in the coil spring hardly functions as a spring that deforms in the rod radial direction, the spring characteristics in the rod radial direction of the coil spring are stabilized while stabilizing the contact state between the coil spring and the end position defining portion. Can be stabilized.

Further, according to the fifth aspect, the vibration isolator includes end position defining portions that define the positions of both ends of the coil spring in the rod axis direction. And the wire which comprises a coil spring is comprised similarly to the cross-sectional shape of the other site | part of the cross-sectional shape of the both ends side of a rod-axis direction. Further, the end position defining portion is inclined in the rod axis direction so that half or more of the portions located on both ends in the rod axis direction of the wire are in contact with each other.

In the configuration in which the cross-sectional shape of the portion facing the end position defining portion in the coil spring is the same as the cross-sectional shape of the other portion, compared to the configuration in which the cross-sectional shape of the portion facing the end position defining portion is flat, The spring characteristics in the rod radial direction of the coil spring can be stabilized.

On the other hand, in the configuration in which the cross-sectional shape of the part facing the end position defining part in the coil spring is the same as the cross-sectional shape of the other part, there is a contradiction that the contact state between the coil spring and the end position defining part is not stable.

In contrast, the end position defining portion of the present disclosure is inclined in the rod axis direction so that more than half turns of the portions located on both ends of the wire rod in the rod axis direction come into contact with each other. According to this, it is possible to stabilize the contact state between the coil spring and the end position defining portion while stabilizing the spring characteristics in the rod radial direction of the coil spring.

Further, according to the sixth aspect, in the vibration isolator, the coil spring is installed in a posture in which the coil central axis intersects the direction of gravity in the holder portion, and the small diameter side of the coil spring is large in the free state. Compared to the radial side, the direction of gravity is offset in the opposite direction. In this way, by taking into account deformation due to the weight of the coil spring, by offsetting the small diameter side of the coil spring, it is possible to suppress a change in spring characteristics due to the deformation due to the weight of the coil spring.

Further, according to the seventh aspect, the vibration isolator includes a first axial direction defining portion that defines the position of one end side of the elastic member in the rod axis direction, and the other end side of the elastic member in the rod axis direction. A second axial direction defining portion that defines the position of the end of the first axial direction. The displacement limiting part and the first axial direction defining part are set on one vibration generating part side of the first vibration generating part and the second vibration generating part. The rod-like member is fixed to the other vibration generating part among the first vibration generating part and the second vibration generating part, and is connected to one vibration generating part via an elastic member. And the 2nd axial direction prescription | regulation part is set to the rod-shaped member side, and even if one of a 1st vibration generation part and a 2nd vibration generation part vibrates, a clearance gap will be formed between displacement limitation parts. Further, it is separated from the displacement limiting portion.

The vibration isolator has a structure in which the displacement restricting portion and the second axial direction defining portion come into contact with each other when one of the first vibration generating portion and the second vibration generating portion vibrates. The function as a spring is not displayed.

On the other hand, the vibration isolator of the present disclosure has a gap between the displacement limiting portion and the second axial direction defining portion even if one of the first vibration generating portion and the second vibration generating portion vibrates. Therefore, the function of the elastic member as a spring can be exhibited.

Further, according to the eighth aspect, in the vibration isolator, the elastic member includes a conical coil spring having a non-linear spring characteristic with respect to a load acting in the rod axis direction. In the second axial direction defining portion, the outer diameter of the defined side contact portion that contacts the coil spring is smaller than the outer diameter of the spring side contact portion that contacts the second axial direction defining portion of the coil spring, and the spring side It is larger than the center diameter between the lines, which is intermediate between the outer diameter and the inner diameter of the contact portion. According to this, since the coil spring is interposed between the second axial direction defining portion and the displacement limiting portion, it is possible to prevent the displacement limiting portion and the second axial direction defining portion from coming into direct contact.

Further, according to the ninth aspect, in the vibration isolator, the displacement restricting portion has an inclined surface inclined with respect to the rod axis direction corresponding to the outer shape of the coil spring. The second axial direction defining portion is an inclined surface inclined with respect to the rod axis direction so that the outer diameter of the defined side contact portion is larger than the outer diameter of the portion opposite to the defined side contact portion in the rod axis direction. have. The inclined surface of the second axial direction defining portion has an inclination angle with respect to the rod axis direction larger than the inclination angle with respect to the rod axis direction of the inclined surface of the displacement limiting portion. According to this, since the gap dimension between the second axial direction defining portion and the displacement limiting portion increases as it moves away from the defined side contact portion in the rod axis direction, the defined side of the second axial direction defining portion. It is possible to prevent a part other than the contact part from coming into direct contact with the displacement limiting portion.

Further, according to the tenth aspect, the vibration isolator has a characteristic that the elastic constant of the elastic member increases in the intersecting direction as the load acting in the intersecting direction intersecting the rod axis direction increases. Furthermore, the elastic member is configured such that the contact area with one of the first axial direction defining portion and the second axial direction defining portion increases as the amount of displacement of the elastic member in the rod axial direction increases.

Further, according to the eleventh aspect, the vibration isolator includes a displacement limiting unit that limits the displacement of the bar-shaped member of the elastic member in the crossing direction intersecting the bar axis direction. The first axial direction defining portion and the displacement limiting portion are set on one vibration generating portion side of the first vibration generating portion and the second vibration generating portion. The rod-like member is fixed to the other vibration generating part among the first vibration generating part and the second vibration generating part, and is connected to one vibration generating part via an elastic member. The second axial direction defining portion is set on the rod-shaped member side, and even if one of the first vibration generating portion and the second vibration generating portion vibrates, a gap is formed between the displacement limiting portion, It is separated from the displacement limiting part.

The vibration isolator configured in this way forms a gap between the displacement limiting portion and the second axial direction defining portion even if one of the first vibration generating portion and the second vibration generating portion vibrates. Therefore, the function of the elastic member as a spring can be exhibited.

According to a twelfth aspect, the vibration isolator includes a spiral spring in which the elastic member is formed by winding a plate-like member in a spiral shape and has a non-linear spring characteristic with respect to a load acting in the intersecting direction. It is configured to include. In the second axial direction defining portion, the outer diameter of the defined side contact portion that contacts the spiral spring is larger than the inner diameter of the spring side contact portion that contacts the second axial direction defining portion in the spiral spring. Further, the dimension of the gap between the second axial direction defining portion and the displacement limiting portion in the direction orthogonal to the rod axis direction is an effective winding excluding the spring-side contact portion of the spiral spring plate thickness and the spiral spring winding number. It is larger than the value multiplied by the number. According to this, since the spiral spring is interposed between the second axial direction defining portion and the displacement limiting portion, it is possible to prevent the displacement limiting portion and the second axial direction defining portion from coming into direct contact.

Further, according to the thirteenth aspect, in the vibration isolator, the rod-shaped member is inserted through an insertion hole formed in one of the first vibration generating unit and the second vibration generating unit. The insertion hole is set to a size that allows a gap to be formed between the elastic member and the rod-shaped member even when the amount of displacement in the intersecting direction of the elastic member is maximized. According to this, even if one vibration generating part of the 1st vibration generating part and the 2nd vibration generating part vibrates, it can prevent that a rod-shaped member and the inner wall of an insertion hole touch directly.

Claims (13)

1. A vibration isolator that connects the first vibration generator (EG) and the second vibration generator (24) and suppresses transmission of vibrations,
   A rod-shaped member (40) connecting the first vibration generating unit and the second vibration generating unit;
   An elastic member (51, 61) for suppressing one vibration of the first vibration generating unit and the second vibration generating unit from being transmitted to the other through the rod-shaped member;
   A displacement restricting portion (52, 62) for restricting displacement of the elastic member in the intersecting direction intersecting the rod axis direction of the rod-shaped member,
   The elastic member has a characteristic that an elastic constant in the rod axis direction increases as a load acting in the rod axis direction increases, and the elastic member has a displacement amount in the intersecting direction increases. A vibration isolator configured to increase a contact area with the displacement limiting portion.
2. The elastic member includes a conical coil spring (51, 61) having a non-linear spring characteristic with respect to a load acting in the rod axis direction,
   The displacement limiting portion includes a holder portion (52, 62) that covers a portion of the elastic member that is exposed outside in the intersecting direction.
   A displacement restricting portion that abuts against a portion of the coil spring when a load exceeding a predetermined reference load is applied to the coil spring in the intersecting direction and restricts the displacement of the portion of the coil spring. 520, 620) is provided.
3. 3. The vibration isolator according to claim 2, wherein the displacement restricting portion includes an inner wall portion (520, 620) having a hole shape that increases from a small diameter side to a large diameter side of the coil spring in the holder portion. .
4. End position defining portions (53, 63) for defining the positions of both ends of the coil spring in the rod axis direction;
   The coil spring is provided with a pair of flat portions (512, 513) formed in a flat shape at portions facing the end position defining portion at both ends in the rod axis direction,
   The rod-shaped member is in contact with at least one turn of the wire connected to the flat portion (512) on the small diameter side of the pair of flat portions,
   The vibration isolator according to claim 2 or 3, wherein at least one turn of the wire connected to the large diameter flat portion (513) of the pair of flat portions is in contact with the holder portion.
5. End position defining portions (53, 63) for defining the positions of both ends of the coil spring in the rod axis direction;
   The wire constituting the coil spring has the same cross-sectional shape at both ends in the rod axis direction as the cross-sectional shape of other parts,
   4. The anti-vibration device according to claim 2, wherein the end position defining portion is inclined in the bar axis direction so that half or more of the portions located on both ends in the bar axis direction of the wire are in contact with each other. apparatus.
6. The coil spring is installed in a posture in which the coil central axis intersects the direction of gravity in the holder portion,
   The vibration isolator according to any one of claims 2 to 5, wherein the coil spring is offset in a direction opposite to a direction in which gravity acts as compared with a large diameter side on a small diameter side of the coil spring in a free state.
7. A first axial direction defining portion (531, 631) for defining a position of an end portion on one end side in the rod axial direction of the elastic member;
   A second axial direction defining portion (532, 632) for defining the position of the end portion on the other end side in the rod axial direction of the elastic member,
   The displacement limiting part and the first axial direction defining part are set on one vibration generating part side of the first vibration generating part and the second vibration generating part,
   The rod-shaped member is fixed to the other vibration generating portion of the first vibration generating portion and the second vibration generating portion, and is connected to the one vibration generating portion via the elastic member. ,
   The second axial direction defining portion is set on the rod-like member side, and even if one of the first vibration generating portion and the second vibration generating portion vibrates, a gap is formed between the displacement limiting portion and the second axial direction defining portion. The anti-vibration device according to claim 1, wherein the anti-vibration device is spaced apart from the displacement limiting portion.
8. The elastic member includes a conical coil spring (51, 52) having a non-linear spring characteristic with respect to a load acting in the rod axis direction,
   In the second axial direction defining portion, the outer diameters (Dpe1, Dpe2) of defined side contact portions (533, 633) that contact the coil spring are in contact with the second axial direction defining portion in the coil spring. It is smaller than the outer diameter (Dse1, Dse2) of the part (514, 614), and larger than the center diameter (Dsc) between the lines, which is intermediate between the outer diameter and the inner diameter of the spring-side contact part. Item 8. The vibration isolator according to item 7.
9. The displacement limiting portion has inclined surfaces (520, 620) inclined with respect to the rod axis direction corresponding to the outer shape of the coil spring,
   The second axial direction defining portion is configured so that the outer diameter of the defined-side contact portion is larger than the outer diameter of the portion on the opposite side of the defined-side contact portion in the rod axis direction. And inclined surfaces (534, 634),
   The inclined surface (θα1, θα2) of the inclined surface of the second axial direction defining portion is larger than the inclined angle (θβ1, θβ2) of the inclined surface of the displacement limiting portion with respect to the rod axis direction. The vibration isolator according to claim 8.
10. A vibration isolator that connects the first vibration generator (EG) and the second vibration generator (24) and suppresses transmission of vibrations,
    A rod-shaped member (40) connecting the first vibration generating unit and the second vibration generating unit;
    An elastic member (51A, 61A) that suppresses one vibration of the first vibration generating unit and the second vibration generating unit from being transmitted to the other through the rod-shaped member;
    A first axial direction defining portion (55, 65) that defines a position of one end side of the rod-shaped member of the elastic member in the rod axial direction;
    A second axial direction defining portion (56, 66) for defining a position of the elastic member on the other end side in the rod axial direction;
    The elastic member has a characteristic that an elastic constant in the intersecting direction increases as a load acting in the intersecting direction intersecting the rod axis direction increases, and a displacement amount of the elastic member in the rod axis direction An anti-vibration device configured such that a contact area with one of the first axial direction defining portion and the second axial direction defining portion increases as the value increases.
11. A displacement restricting portion (54, 64) for restricting displacement in the intersecting direction of the elastic member;
    The first axial direction defining portion and the displacement limiting portion are set on one vibration generating portion side of the first vibration generating portion and the second vibration generating portion,
    The rod-shaped member is fixed to the other vibration generating portion of the first vibration generating portion and the second vibration generating portion, and is connected to the one vibration generating portion via the elastic member. ,
    The second axial direction defining portion is set on the rod-like member side, and even if one of the first vibration generating portion and the second vibration generating portion vibrates, a gap is formed between the displacement limiting portion and the second axial direction defining portion. The anti-vibration device according to claim 10, wherein the anti-vibration device is spaced apart from the displacement limiting portion.
12. The elastic member is constituted by a spiral member (51A, 61A) having a non-linear spring characteristic with respect to a load acting in the intersecting direction, the plate-like member being wound in a spiral shape,
    The second axial direction defining portion is a spring side in which outer diameters (Dve1, Dve2) of defined side contact portions (561, 661) that contact the spiral spring are in contact with the second axial direction defining portion of the spiral spring. It is larger than the inner diameter (Dsi1, Dsi2) of the contact part,
    Further, the dimension of the gap between the second axial direction defining portion and the displacement limiting portion in the direction orthogonal to the rod axis direction is determined by the plate thickness (t) of the spiral spring and the number of turns (N) of the spiral spring. The vibration isolator according to claim 11, wherein the vibration isolator is larger than a value obtained by multiplying the effective winding number (Ne) excluding the spring-side contact portion.
13. The rod-shaped member is inserted through an insertion hole (241) formed in one of the first vibration generation unit and the second vibration generation unit,
    The said insertion hole is set to the magnitude | size in which a clearance gap is formed between the said rod-shaped members, even if the displacement amount of the said cross direction in the said elastic member becomes the maximum. Anti-vibration device as described in 1.

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