JP2001174086A - Compressor and refrigerator provided with the compressor - Google Patents

Abstract

(57) Abstract: Provided is a compressor capable of suppressing a twist in a circumferential direction generated in a coil spring elastically supporting a vibration isolator, and a refrigerator including the compressor. A compressor (11) includes a balance weight (31) supported reciprocally in an axial direction coaxial with a compression piston (22), and the balance weight (31) is controlled by a coil spring (32) and a bearing (33). Are attached to the top plate 21a and the bottom plate 21b. The coil spring 32 is supported by the bearing 33 so as to be rotatable in the circumferential direction with respect to the compressor body 21 and the balance weight 31.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor and a refrigerator provided with the compressor.

[0002]

2. Description of the Related Art Conventionally, various compressors having a vibration isolator have been proposed.
One described in the prior art of Japanese Patent No. 6104 is known. The vibration isolator provided in the compressor includes a vibration isolator supported by the compressor main body so as to be slidable in an axial direction coaxial with the compression piston, and a vibration isolator is provided between the vibration isolator and the compressor main body. Is provided with a coil spring.

[0003] This vibration isolator suppresses the vibration of the compressor by elastically vibrating the vibration isolator so as to cancel the vibration based on the vibration generated by the reciprocating movement of the compression piston.

[0004]

In the vibration isolator provided in the compressor, the coil spring is fixed to the compressor body, so that the vibration (expansion and contraction) of the coil spring accompanying the vibration of the vibration isolator is performed. This causes a circumferential twist in the coil spring. When such torsional stress is concentrated on the coil spring, the life of the coil spring is reduced.

Further, since a part of the force for vibrating the vibration isolator is consumed as a frictional force for generating a torsional stress on the coil spring, the amplitude of the vibration isolator is reduced and sufficient vibration prevention is achieved. The vibration effect cannot be obtained.

Further, remarkable heat is generated by the frictional force generated by the torsion stress of the coil spring. An object of the present invention is to provide a compressor capable of suppressing a circumferential twist generated in a coil spring elastically supporting a vibration isolator, and a refrigerator including the compressor.

[0007]

In order to solve the above-mentioned problems, the invention according to claim 1 is supported so as to be reciprocally movable in an axial direction coaxial with a compression piston, and at least one end is provided with a coil spring. In a compressor provided with a vibration isolator attached to the compressor body, the coil spring is rotatably supported in at least one of the compressor body and the vibration isolator in a circumferential direction. That is the gist.

According to a second aspect of the present invention, there is provided a vibration isolator supported reciprocally in an axial direction coaxial with the compression piston and having at least one end attached to the compressor body via a coil spring. In the compressor, the gist is that the coil spring is supported by at least one of the compressor body and the vibration isolator via a thrust bearing.

The invention described in claim 3 is the first or second invention.
The gist of the present invention is that the refrigerator includes the compressor described in (1). According to a fourth aspect of the present invention, in a refrigerator including the compressor according to the first or second aspect and an expander communicated with the compressor, the refrigerator is reciprocally movable in an axial direction coaxial with the expansion piston. And an expander-side vibration isolator attached at least one end to the expander body via an expander-side coil spring,
The gist of the present invention is that the expander-side coil spring is rotatably supported in at least one of the expander body and the expander-side vibration isolator in a circumferential direction.

[0010] The invention described in claim 5 is the invention according to claim 1 or 2.
In the refrigerator having a compressor and an expander connected to the compressor, the compressor is supported so as to be able to reciprocate in the axial direction coaxial with the expansion piston, and at least one end is provided via an expander-side coil spring. And an expander-side vibration isolator attached to the expander main body, and the expander-side coil spring is provided on at least one of the refrigerator main body and the expander-side vibration isolator via an expander-side thrust bearing. The point is that they are supported.

According to the first and second aspects of the present invention, the coil spring is supported by at least one of the compressor body and the vibration isolator so as to be rotatable in the circumferential direction. . Therefore, the torsion in the circumferential direction generated in the coil spring due to the vibration (expansion and contraction) of the coil spring based on the vibration of the vibration isolator is suppressed. Thereby, the concentration of the torsional stress generated in the coil spring is suppressed, and the life of the coil spring is extended.

Further, since a part of the force for vibrating the vibration isolator is suppressed from being consumed as a frictional force for generating a torsional stress on the coil spring, the amplitude of the vibration isolator is preferably reduced. And vibration is prevented.

Further, heat generated by frictional force due to generation of torsional stress of the coil spring is reduced. According to the configuration of the invention described in claim 3, a refrigerator having reduced heat generation due to friction caused by torsional stress of the coil spring of the compressor is disposed in a vacuum space such as an outer space. Even in this case, cooling measures and the like are suppressed to a minimum.

According to the fourth and fifth aspects of the present invention, the expander-side coil spring is rotatably supported in at least one of the expander body and the expander-side vibration isolator in the circumferential direction. Have been. Therefore, the torsion in the circumferential direction generated in the expander-side coil spring due to the vibration (expansion and contraction) of the expander-side coil spring based on the vibration of the expander-side vibration isolator is suppressed.
Thereby, the concentration of the torsional stress generated in the expander-side coil spring is suppressed, and the life of the expander-side coil spring is extended.

Further, a part of the force for vibrating the expander-side vibration isolator is suppressed from being consumed as a frictional force for generating a torsional stress on the expander-side coil spring. Vibration is prevented by suitably holding the amplitude of the container-side vibration isolator.

Further, the heat generated by the frictional force generated by the torsion stress of the expander-side coil spring is also reduced. Furthermore, by using a refrigerator in which heat generated by the torsion stress of the coil spring is reduced in the compressor and the expander, for example, even when the refrigerator is arranged in a vacuum space such as outer space, cooling measures are minimized. It is suppressed to the limit.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIGS. FIG. 1 is a sectional view showing a split-type Stirling refrigerator to which the present embodiment is applied. The refrigerator is shown in a compressor 11 shown in FIG. 1A and in FIG. 2B. An expansion device 12 and a connection pipe 13 that connects the compressor 11 and the expansion device 12 are provided.

The compressor 11 includes a compressor main body 21, a compression piston 22, a coil 23, a permanent magnet 24, and a compressor-side vibration isolator 25. The compressor body 2
1 is formed in a substantially cylindrical shape, and one side thereof (FIG. 1)
A flange-shaped top plate 21a and a bottom plate 21b are provided in the openings on the upper side (a) and on the other side (the lower side), respectively. The compressor body 21 is provided with the bottom plate 21b.
Are arranged to contact the floor surface.

The inner peripheral surface of the compressor main body 21 is reduced in diameter on the side of the top plate 21a through a step, and a compression cylinder 26 is formed by the reduced inner wall surface. In addition, a communication hole 21c penetrating in the axial direction is formed in the top plate 21a corresponding to the compression cylinder 26.

The compression piston 22 has an outer diameter slightly smaller than the inner diameter of the compression cylinder 26, and is formed in a substantially cylindrical body. The compression piston 22 has a piston ring 27 mounted on its outer peripheral surface. Thus, it is slidably supported by the compression cylinder 26 in an airtight manner. The inner peripheral surface of the compression cylinder 26, the compression piston 2
The space S1 defined on the top plate 21a side by the outer wall surface 2 and the piston ring 27 and the like forms a part of a compression space described later. The compression piston 22
A rod 22a is provided on the bottom plate 21b side, and the compression piston 22 is connected to an end of the rod 22a and the bottom plate 21b.
b, it is elastically supported by the compressor main body 21 (bottom plate 21b) by a movable portion spring 28 interposed therebetween.

The coil 23 has a wound wire and is connected to a power supply (not shown) for supplying an AC power of a predetermined frequency. The coil 23 is fixed to the compression piston 22 so as to surround the rod 22a. Therefore, the coil 23 and the compression piston 22
Move together.

The permanent magnet 24 is formed in a cylindrical shape, and is fixed to the compressor body 21 via a fixture (not shown) so as to surround the outer peripheral surface of the coil 23. The permanent magnet 24 forms a magnetic field extending in the radial direction.

Accordingly, when AC power is supplied to the coil 23, an AC current flowing through the coil 23 and a Lorentz force based on the magnetic field of the permanent magnet 24 act on the coil 23, and the coil 23 and the compression piston 22 Reciprocates at the above-mentioned predetermined frequency.

The compressor-side vibration isolator 25 is disposed substantially coaxially with the compression piston 22 at a substantially axially intermediate portion of the compressor main body 21 and is a substantially ring-shaped vibration isolator surrounding the compressor main body 21. , A coil spring 32 for elastically supporting the balance weight 31, and a bearing 33 as a thrust bearing. More specifically, the bearing 33 is a rolling bearing that receives an axial force, and as shown in FIG.
It comprises an inner ring 33b and a ball 33c housed between the outer ring 33a and the inner ring 33b. Outer rings 33a of a plurality of bearings 33 (only two are shown in FIG. 1) are fixed to the opposing surfaces of the balance weight 31 and the top plate 21a and the opposing surfaces of the balance weight 31 and the bottom plate 21b, respectively. ing. On the other hand, inner races 33b of the bearings 33 are fixed to both ends of the coil spring 32, and the coil springs 32 are interposed between the bearings 33 facing each other. Each of the coil springs 32 has a biasing force for pushing back the balance weight 31. The balance weight 31
And the spring constant of the coil spring 32 are set such that the compressor-side vibration isolator 25 is excited by vibration generated by the reciprocation of the compression piston 22 to cancel the vibration, that is, the balance weight. 31 are substantially synchronized with the reciprocating movement of the compression piston 22, and the phases are substantially 18
It is set so as to reciprocate (vibrate) with a shift of 0 °.

Since the coil spring 32 is fixed to the top plate 21a, the bottom plate 21b and the balance weight 31 via a bearing 33, for example, as shown in FIG.
As shown in (2), the circumferential torsion generated in the coil spring 32 due to the vibration (expansion and contraction) of the coil spring 32 is:
As the bearing 33 rotates, it is absorbed.

The expander 12 includes an expander main body 41, an expansion piston 42, and an expander-side vibration isolator 43. The expander main body 41 is formed in a substantially closed cylindrical shape, and a flange-shaped bottom plate 41a is provided at an opening on one side (lower side in FIG. 1B) and a substantially middle part in the axial direction.
And a flange 41b. An expansion cylinder 44 is formed by the inner wall surface of the expander main body 41. The bottom plate 4 corresponds to the expansion cylinder 44.
In 1a, a communication hole 41c penetrating in the axial direction is formed.

The expansion piston 42 has an outer diameter slightly smaller than the inner diameter of the expansion cylinder 44 and is formed in a substantially cylindrical shape. The expansion piston 42 has a piston ring 45 mounted on its outer peripheral surface. Thus, it is slidably supported by the expansion cylinder 44 in an airtight manner. The inner peripheral surface of the expansion cylinder 44 and the expansion piston 4
The space S2 defined on the opening side (the communication hole 41c side) by the outer wall surface of the second and the piston ring 45 and the like forms a part of the compression space like the space S1. Also,
The space defined by the inner peripheral surface of the expansion cylinder 44, the outer wall surface of the expansion piston 42, the piston ring 45, and the like on the closing side (back side) is an expansion space 46.
The expansion piston 42 is elastically supported by the expander main body 41 (the bottom plate 41a) by a movable portion spring 47 interposed between the end on the bottom plate 41a side and the bottom plate 41a.

In the hollow portion of the expansion piston 42, a regenerator 48 made of mesh such as stainless steel or phosphor bronze is provided.
(Compression space) is communicated via the regenerator 48.

A freezer 49 for heat exchange with the object to be cooled is fixed along the inner peripheral surface of the expansion cylinder 44 on the closed side (back side). One side and the other side of the connection pipe 13 are connected to the communication holes 21c and 41c, respectively. Then, the spaces S1, S2 and the connection pipe 1
The space formed by the hollow portions 3 is a compression space 50.

The compression space 50 and the expansion space 46
Is closed with a working gas such as helium, for example. Therefore, when the compression piston 22 reciprocates at the predetermined frequency, the working gas periodically reciprocates between the compression space 50 and the expansion space 46 via the regenerator 48. At this time, the expansion piston 42 is
Driven by the fluid resistance of the working gas passing through the inside, the expansion piston 42 reciprocates in the expansion cylinder 44.

The expansion piston 42 (cool storage unit 48)
), The spring constant of the movable portion spring 47, the fluid resistance of the regenerator 48, and the like, the expansion piston 42 is substantially synchronized with the reciprocating movement of the compression piston 22, and the phases are substantially 90
It is set to reciprocate (vibrate) with a shift of °.
Therefore, when the compression piston 22 reciprocates,
The working gas in the working space constitutes a thermodynamic cycle known as a reverse Stirling cycle.

The expander-side vibration isolator 43 is provided with the bottom plate 4.
A balance weight 51 as a substantially ring-shaped expander-side vibration isolator that is disposed coaxially with the expansion piston 42 at a substantially intermediate portion in the axial direction between the flange 1a and the flange 41b and surrounds the expander body 41; A coil spring 52 as an expander-side coil spring that elastically supports 51 and a bearing 53 as an expander-side thrust bearing are provided. More specifically, the bearing 53 is a bearing having the same structure as that of the bearing 33. A plurality of the bearings 53 are provided on the opposing surfaces of the balance weight 51 and the bottom plate 41a, and on the opposing surfaces of the balance weight 51 and the flange 41b. 1 only two bearings are shown)
Outer ring is fixed. On the other hand, the inner ring of the bearing 53 is fixed to both ends of the coil spring 52, and the coil spring 52 is interposed between the bearings 53 facing each other. The coil springs 52 have a biasing force for pushing back the balance weight 51. The mass of the balance weight 51 and the coil spring 5
The spring constant and the like of 2 are such that the expander-side vibration isolator 43 is excited by vibration generated by the reciprocating movement of the coil spring 52 to cancel the vibration. It is set so as to be substantially synchronized with the reciprocating movement of 52 and to reciprocate (vibrate) with a phase shifted from each other by about 180 °.

Here, since the coil spring 52 is fixed to the bottom plate 41a, the flange 41b and the balance weight 51 via the bearing 53, respectively, the coil spring 52 accompanies the vibration (expansion and contraction) of the coil spring 52.
Is absorbed by the rotation of the bearing 53.

Next, the operation of the above-structured Stirling refrigerator will be described. Coil 2 of the compressor 11
When the AC power is supplied to the coil 3, the alternating current flowing through the coil 23 and the Lorentz force based on the magnetic field of the permanent magnet 24 act on the coil 23, and the compression piston 22 reciprocates with the coil 23 at the predetermined frequency. Moving. When the compression piston 22 reciprocates at the predetermined frequency, the working gas flows into the compression space 50 and the expansion space 4.
6 periodically reciprocate via the regenerator 48. At this time, the expansion piston 42 is driven by the fluid resistance of the working gas passing through the regenerator 48, and the expansion piston 42 is substantially synchronized with the reciprocating movement of the compression piston 22 and has a phase shift of about 90 ° from each other. Reciprocate (vibrate). Therefore, the working gas in the working space constitutes a thermodynamic cycle known as a reverse Stirling cycle, so that refrigeration occurs in the expansion space 46 and heat is absorbed from the cooled object via the freezer 49.

The vibration generated by the reciprocating movement of the compression piston 22 is such that the balance weight 31 of the compressor-side vibration isolator 25 is substantially synchronized with the reciprocating movement of the compression piston 22 and the phases thereof are mutually different. It is offset by reciprocating (vibrating) with a shift of about 180 °. At this time, the circumferential torsion generated in the coil spring 32 due to the vibration (expansion and contraction) of the coil spring 32 is caused by the bearing 33
Is absorbed by the rotation.

On the other hand, the vibration generated by the reciprocating movement of the expansion piston 42 is substantially synchronized with the reciprocating movement of the expansion piston 42 by the balance weight 51 of the expander-side vibration isolator 43 and the phases are mutually different. It is offset by reciprocating (vibrating) with a shift of about 180 °. At this time, the circumferential torsion generated in the coil spring 52 due to the vibration (expansion and contraction) of the coil spring 52 is caused by the bearing 53
Is absorbed by the rotation.

As described in detail above, according to the present embodiment, the following effects can be obtained. (1) In the present embodiment, the circumferential twist generated in the coil spring 32 due to the vibration (expansion and contraction) of the coil spring 32 based on the vibration of the balance weight 31 is applied to the bearing 33.
Can be absorbed and suppressed by the rotation of. Therefore,
The concentration of torsional stress generated in the coil spring 32 can be suppressed, and the life of the coil spring 32 can be extended.

Further, since a part of the force for vibrating the balance weight 31 is suppressed from being consumed as a frictional force for generating a torsional stress in the coil spring 32, the amplitude of the balance weight 31 is reduced. It is possible to obtain an anti-vibration effect by suitably holding.

Further, the heat generated by the frictional force for generating the torsional stress of the coil spring 32 can be reduced. (2) In the present embodiment, the circumferential torsion generated in the coil spring 52 due to the vibration (expansion and contraction) of the coil spring 52 based on the vibration of the balance weight 51 is applied to the bearing 53.
Can be absorbed and suppressed by the rotation of. Therefore,
The concentration of torsional stress generated in the coil spring 52 can be suppressed, and the life of the coil spring 52 can be extended.

Further, since a part of the force for vibrating the balance weight 51 is suppressed from being consumed as a frictional force for generating a torsional stress on the coil spring 52, the amplitude of the balance weight 51 is reduced. It is possible to obtain an anti-vibration effect by suitably holding.

Further, the heat generated by the frictional force for generating the torsional stress of the coil spring 52 can be reduced. (3) In the present embodiment, the heat generated by the frictional force for generating the torsional stress of the coil springs 32 and 52 is reduced. Therefore, for example, even when this Stirling refrigerator is arranged in a vacuum space such as outer space, cooling measures and the like can be minimized.

(4) In the present embodiment, the vibrations generated in the compressor 11 and the expander 12 of the Stirling refrigerator are canceled by the compressor-side vibration isolator 25 and the expander-side vibration isolator 43, respectively. Therefore, for example, it is possible to avoid that the object to be cooled is damaged by the vibration.

The embodiment of the present invention is not limited to the above embodiment, but may be modified as follows. In the above-described embodiment, the rolling bearing 33 is adopted as the thrust bearing. However, for example, a pivot bearing 61 as shown in FIG. 3 may be used. More specifically, a support piece 62 having a sharp tip is fixed to both ends of the coil spring 32, while the top plate 21 a
A smooth tapered hole 63 is provided on the facing surface of the balance weight 31. And the coil spring 3
The support piece 2 is supported so as to be rotatable in the circumferential direction by accommodating and supporting the support piece 62 in the tapered hole 63.

The same bearing 61 is connected to the bottom plate 21b.
Alternatively, it may be provided on the facing surface of the balance weight 31 or may be provided on the coil spring 52 on the expander 12 side.
The structure is not limited to such a thrust bearing, and the structure is arbitrary as long as the coil springs 32 and 52 are supported so as to be rotatable in the circumferential direction.

In the above embodiment, both ends of the balance weights 31 and 51 are respectively connected to the coil springs 3.
Although the elastic weights 2 and 52 are elastically supported, for example, only one end surface of the balance weights 31 and 51 may be elastically supported by the coil springs 32 and 52, respectively.

In the above embodiment, bearings 33, 53 are provided at both ends of the coil springs 32, 52, respectively.
The bearings 33 and 53 may be provided only at one end of the coil springs 32 and 52, respectively.

In the above embodiment, the compressor body 2
The balance weights 31 are arranged such that the balance weights 31 are disposed substantially at the intermediate portions between the top plate 21a and the bottom plate 21b.
Was elastically supported, but this is an example. The point is that it is only necessary to be supported so as to be able to reciprocate in the axial direction coaxial with the compression piston 22.

In the above embodiment, the inflator body 4
The balance weight 51 is elastically supported so that the balance weight 51 is disposed substantially in the middle of the bottom plate 41a and the flange 41b, but this is an example. The point is that it is only necessary to be supported reciprocally in the axial direction coaxial with the expansion piston 42.

In the above embodiment, the compressor main body 21 is arranged so that the bottom plate 21b is in contact with the floor surface. However, such an arrangement is arbitrary. In the above embodiment, the compression piston 22 is reciprocated by the Lorentz force based on the alternating current flowing through the coil 23 and the magnetic field of the permanent magnet 24, but is reciprocated by a link mechanism such as a crank. Is also good.

In the above-described embodiment, the Stirling refrigerator has been described in which the compressor 11 and the expander 12 are each one. However, these may be a plurality of each of the refrigerators. In this case, each compressor 1
A compressor-side vibration isolator 25 and an expander-side vibration isolator 43 may be provided for each of the compressors 11 or the expanders 12.
A single compressor-side vibration isolator 25 or expander-side vibration isolator 43 may be provided so as to be substantially coaxial with the average axis of the two axes.

In the above embodiment, the present invention is applied to a Stirling refrigerator, but may be applied to, for example, a pulse tube refrigerator if a similar compressor is provided. Next, technical ideas other than the claims that can be grasped from the above embodiments are described below together with their effects.

(A) An expander-side vibration isolator is supported so as to be reciprocally movable in the axial direction coaxial with the expansion piston, and has at least one end attached to the expander body via an expander-side coil spring. In the expander of the refrigerator, the expander-side coil spring is supported on at least one of the expander body and the expander-side vibration isolator so as to be rotatable in a circumferential direction. Machine inflator.

(B) An expander-side vibration isolator is supported so as to be able to reciprocate in the axial direction coaxial with the expansion piston, and has at least one end attached to the expander body via an expander-side coil spring. In the expander of the refrigerator, the expander-side coil spring is supported by at least one of the refrigerator body and the expander-side vibration isolator via an expander-side thrust bearing. .

According to the configuration of the invention described in the above (A) and (B), the expander-side coil spring rotates in the circumferential direction with respect to at least one of the expander body and the expander-side vibration isolator. It is freely supported. Therefore, the torsion in the circumferential direction generated in the expander-side coil spring due to the vibration (expansion and contraction) of the expander-side coil spring based on the vibration of the expander-side vibration isolator is suppressed. Thereby, the concentration of the torsional stress generated in the expander-side coil spring is suppressed, and the life of the expander-side coil spring is extended.

Further, a part of the force for vibrating the expander-side vibration isolator is suppressed from being consumed as a frictional force for generating a torsional stress on the expander-side coil spring. Vibration is prevented by suitably holding the amplitude of the container-side vibration isolator.

Further, the heat generated by the frictional force for generating the torsional stress of the expander-side coil spring is also reduced.

[0057]

As described above in detail, according to the first and second aspects of the present invention, it is possible to suppress the circumferential twist generated in the coil spring elastically supporting the vibration isolator.

According to the third aspect of the present invention, the refrigerating machine in which the heat generated in the compressor is reduced can minimize cooling measures and the like. According to the fourth and fifth aspects of the present invention, it is possible to suppress a circumferential twist generated in the expander-side coil spring that elastically supports the expander-side vibration isolator. Thereby, the concentration of torsional stress generated in the expander-side coil spring can be suppressed, and the life of the expander-side coil spring can be extended.

Further, since a part of the force for vibrating the expander-side vibration isolator is suppressed from being consumed as a frictional force for generating a torsional stress on the expander-side coil spring, the same expansion is prevented. The vibration isolation effect can be obtained by suitably holding the amplitude of the container-side vibration isolator.

Further, the heat generated by the frictional force for generating the torsional stress of the expander-side coil spring can be reduced. Furthermore, by using a refrigerator in which heat generated in the compressor and the expander is reduced, cooling measures and the like can be minimized.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view showing the same embodiment.

FIG. 3 is an enlarged cross-sectional view showing another example of the embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 11 Compressor 12 Expander 21 Compressor main body 22 Compression piston 31 Balance weight as a vibration isolator 32 Coil spring 33 Bearing as a thrust bearing 41 Expander main body 42 Expansion piston 51 Balance weight as an expander side vibration isolator 52 Expansion Coil spring as an expander-side coil spring 53 Bearing as an expander-side thrust bearing 61 Bearing as a thrust bearing and an expander-side thrust bearing

Claims (5)

[Claims] 1. A compressor provided with a vibration isolator supported reciprocally in an axial direction coaxial with a compression piston and having at least one end attached to a compressor body via a coil spring. A compressor is rotatably supported in at least one of the compressor body and the vibration isolator in a circumferential direction. 2. A compressor provided with a vibration isolator supported reciprocally in an axial direction coaxial with a compression piston and having at least one end attached to a compressor body via a coil spring. Is supported by at least one of the compressor main body and the vibration isolator via a thrust bearing. 3. A refrigerator provided with the compressor according to claim 1. 4. A refrigerator comprising the compressor according to claim 1 and an expander connected to the compressor, wherein the refrigerator is supported so as to be reciprocally movable in an axial direction coaxial with the expansion piston. At least one end includes an expander-side vibration isolator attached to the expander body via an expander-side coil spring, and the expander-side coil spring is at least one of the expander body and the expander-side vibration isolator. A refrigerator that is rotatably supported in a circumferential direction with respect to the refrigerator. 5. A refrigerator comprising the compressor according to claim 1 and an expander communicated with the compressor, the refrigerator being supported so as to be reciprocally movable in an axial direction coaxial with an expansion piston, At least one end is provided with an expander-side vibration isolator attached to the expander body via an expander-side coil spring, wherein the expander-side coil spring is connected to the refrigerator body and the refrigerator via an expander-side thrust bearing. A refrigerator supported by at least one of the expander-side vibration isolators.