JP2003021084A - Scroll type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce mechanical loss by reducing load of a seal material in a thrust support back pressure chamber, even when a scroll type compressor is operated at an extremely high operating pressure. SOLUTION: A middle housing 13 is disposed at the back of a turning scroll 6 and supports thrust load by a compression reaction force, but the back pressure chamber 19 is formed in one of the back surface of an end plate part 6a of the turning scroll and a surface of the middle housing 13 facing to it, and pressure of compressed fluid is introduced to generate a force by the back pressure to cancel the thrust load. However, the back pressure must be also increased when the operating pressure is high, so that load of the seal material increases to increase abrasion and the mechanical loss. A plurality of coil springs 12 are provided as an additional energizing means and their ends are mounted to the turning scroll 6 side and the middle housing 13 side, thereby generating an axial force/without causing the friction. A magnet may the used.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor for pressurizing a fluid to an extremely high pressure,
The present invention relates to a scroll compressor that compresses a refrigerant to a high pressure in a refrigeration cycle that uses a supercritical fluid such as CO2 as a refrigerant.

[0002]

2. Description of the Related Art Japanese Utility Model Application Laid-Open No. 9-310687, Japanese Patent Application Laid-Open No. 2-161191, or Japanese Patent Application Laid-Open No. 1-27168.
As described in Japanese Patent No. 0, in a scroll compressor, either the back surface of the end plate portion of the orbiting scroll or the flat surface on the housing side that faces the end plate portion and axially supports the orbiting scroll. A back pressure chamber is formed as a hollow space on either side, and the orbiting scroll is axially urged by the force due to the back pressure generated by introducing the compressed fluid from the discharge side into this back pressure chamber, and the compression reaction There is known a means for reducing a large contact load acting between the back surface of the orbiting scroll and the flat surface on the housing side due to the thrust load generated by the force.

When implementing the prior art as described above,
If the fluid to be compressed has a low working pressure, such as CFC generally used as a refrigerant in a refrigeration cycle, the thrust load generated by the compression reaction force is 1000.
Since it is around N, the pressure of the fluid introduced into the back pressure chamber on the back surface of the orbiting scroll may be small, so that the load acting on the seal material used for holding the pressure in the back pressure chamber is also small. In addition, since the sliding surface of the sealing material is presumed to be in the fluid lubrication area because the contact load is small, an oil film is reliably formed on the housing-side surface that makes sliding contact with the sealing material. Therefore, it is considered that sliding contact is performed under a low friction coefficient. Therefore, mechanical loss due to sliding of the sealing material can be suppressed to a low level.

However, in a refrigeration cycle using a so-called supercritical pressure fluid such as carbon dioxide (CO 2) as a refrigerant, when the refrigerant is compressed by the scroll type compressor shown in the above-mentioned prior art, it is swirled. Since the thrust load acting on the scroll reaches 7,000 N, which is about seven times that when using a refrigerant with a low working pressure such as CFC, the pressure of the fluid introduced into the back pressure chamber is also 7
Since the high pressure is about double, the high pressure acts on the sealing material. Further, since the load acting on the seal material is high, it is considered that the lubrication state of the sliding surface of the seal material is not in the fluid lubrication area but in the mixed lubrication area or boundary lubrication area having a large friction coefficient. Therefore, there has been a problem that mechanical loss due to sliding of the sealing material increases, which causes a reduction in efficiency of the compressor.

[0005]

SUMMARY OF THE INVENTION The present invention addresses the above-mentioned problems in the prior art and solves them by a novel means.

[0006]

The present invention provides a scroll type compressor described in claim 1 as a means for solving the above-mentioned problems in the prior art.

In the scroll type compressor of the present invention,
At least one back pressure chamber into which high-pressure fluid is introduced is formed on one of the back surface of the end plate portion of the orbiting scroll and the surface of the middle housing facing it, and
Since additional biasing means for compensating the back pressure force generated in the back pressure chamber to press the orbiting scroll in the axial direction toward the fixed scroll is provided, sliding for supporting the orbiting scroll in the axial direction by the middle housing. Even if the thrust load acting on the contact surface becomes small and the operating pressure becomes extremely high due to the compressor being used for the purpose of compressing supercritical fluid, etc. Since it is in a lubricated state, the coefficient of friction becomes small and the mechanical loss is reduced. Further, since the additional biasing means is provided, it is not necessary to significantly increase the pressure in the back pressure chamber, so that even when compressing the supercritical pressure fluid, the differential pressure acting on the seal material becomes small, Its wear is reduced and durability is improved.

In the present invention, as an additional biasing means, at least one coil spring can be mounted between the orbiting scroll and the middle housing. If there are multiple coil springs, one end of which is fixed to the orbiting scroll and the other end of which is fixed to the middle housing, the coil spring makes a conical motion (or swinging motion) when the orbiting scroll revolves. Since there is no part that makes sliding motion with friction, there is no risk of mechanical loss or wear. These additional biasing means are preferably provided in the back pressure chamber.

The additional biasing means is not limited to the coil spring described above, but may be a magnet. The magnet is
For example, the orbiting scroll and the fixed scroll can be attached to either one of a pair of surfaces facing each other in the outer peripheral portion. Further, when a plurality of magnets are used, by arranging them so that the same magnetic poles face each other, it is possible to configure an additional biasing means of the type that utilizes magnetic repulsion. The scroll type compressor of the present invention is suitable for operation in a state where the operating pressure is high, and is therefore suitable for use as a refrigerant compressor in a refrigeration cycle using a so-called supercritical fluid as a refrigerant.

[0010]

BEST MODE FOR CARRYING OUT THE INVENTION A first embodiment of the scroll compressor according to the present invention will be described with reference to FIGS. Figure 1
Reference numeral 1 denotes a shaft, and a crank portion 1a eccentric to the shaft center by a predetermined amount is formed at the lower end thereof. Reference numeral 2 denotes a motor, which drives the shaft 1 to rotate when it is supplied with electric power. In the illustrated embodiment, the motor 2 is constructed inside a motor housing 3 which is integral with the housing part of the compressor. Reference numeral 4 denotes a front radial bearing mounted on the upper portion of the motor housing 3, and rotatably supports the shaft 1 together with a rear radial bearing 5 also mounted on the lower portion.

Reference numeral 6 denotes an orbiting scroll, which is formed on a substantially disk-shaped end plate portion 6a, a spiral blade portion 6b formed so as to project in the axial direction from the end plate portion 6a, and a rear surface of the end plate portion 6a. And a cylindrical boss 6c and the like. The orbiting scroll 6 as a whole is provided with a shaft 1 through an orbiting scroll bearing 16 which is press-fitted and attached to a boss portion 6c.
Is rotatably supported by the crank portion 1a of
It revolves around the central axis of the shaft 1. Reference numeral 7 denotes a plurality of rotation preventing pins which allow only the orbital movement of the orbiting scroll 6 to prevent the orbiting scroll 6 from rotating.

A fixed scroll 8 has an end plate portion 8a and a spiral blade portion 8b similar to those of the orbiting scroll 6, and is assembled so as to mesh with the orbiting scroll 6. As a result, a plurality of working chambers 9 that look like a crescent when viewed in the axial direction are formed between the blade portion 6b of the orbiting scroll 6 and the blade portion 8b of the fixed scroll 8.

Then, when the working chamber 9 opens toward the suction chamber 14 on the outer circumference, a fluid such as a gas refrigerant that returns from a refrigeration cycle (not shown) and is introduced into the suction chamber 14 from the suction port 8d is activated. The fluid is compressed by sucking it into the chamber 9 and reducing the working chamber 9 while moving in the radial direction toward the center of the orbiting scroll 6 and the fixed scroll 8 while the orbiting scroll 6 revolves. Finally, when the working chamber 9 is opened toward the working chamber 9a at the center, the refrigerant that has reached the discharge pressure passes through the discharge hole 8c provided in the end plate portion 8a of the fixed scroll 8 and the end plate portion 8
The liquid is discharged into a discharge chamber 15 formed between a and a rear housing 18 fixed to the fixed scroll 8 by a bolt (not shown) or the like.

Reference numeral 18a denotes a discharge port formed in the rear housing 18, which communicates with the refrigeration cycle by a pipe (not shown) and guides the high-pressure refrigerant discharged into the discharge chamber 15 to the condenser of the refrigeration cycle. A discharge valve 17 is mounted on the end plate portion 8a so that the refrigerant in the discharge chamber 15 does not flow backward through the discharge hole 8c. Note that FIG.
10 is a balancer, which is fixed to the shaft 1 or is fitted to the shaft 1 so as to be slightly movable in the radial direction so that the eccentric amount of the crank portion 1a can be increased or decreased. There is.

Next, the structural portion of the first embodiment corresponding to the features of the present invention will be described. Reference numeral 6e shown in FIG. 1 is an annular groove formed on the back surface of the end plate portion 6a of the orbiting scroll 6, and by facing the surface of the middle housing 13 around the center of the end plate portion 6a, An annular back pressure chamber 19 is formed in the. And the back pressure chamber 19
Since the pressure introducing hole 6d is provided so as to communicate with the working chamber 9 formed at a predetermined position, a high pressure having a predetermined size is introduced into the back pressure chamber 19. Reference numeral 11 denotes a sealing material, which seals between the inner and outer wall surfaces of the back pressure chamber 19 in the radial direction and the surface of the middle housing 13 so that a gap for refrigerant leakage does not occur. The back pressure chamber 19 is formed in a single annular shape by the annular groove 6e, but it goes without saying that it can be formed by being divided into a plurality of parts.

The most characteristic part is a plurality of coil springs 12 provided as additional biasing means in the first embodiment, one end of which is fixed to the surface of the middle housing 13. The other ends thereof are fixed to the bottom surface of the back pressure chamber 19, that is, the end plate portion 6a of the orbiting scroll 6. Since the coil spring 12 is a compression spring, the orbiting scroll 6 is biased downward in FIG. 1 while its base is supported by the middle housing 13.

Since the scroll compressor C1 of the first embodiment has such a structure, in the operating state in which the orbiting scroll 6 revolves, a plurality of crescent-shaped working chambers 9 are formed.
Due to the differential pressure between the pressure of the refrigerant compressed inside and the pressure inside the suction chamber 14, a thrust load Fs acts on the end plate portion 6a of the orbiting scroll 6 in the upward direction in FIG. Due to the thrust load Fs based on the compression reaction force, the end plate portion 6a is strongly pressed against the surface of the middle housing 13 to generate a large frictional force with respect to the revolution force of the orbiting scroll 6. Since a predetermined high pressure is introduced into the back pressure chamber, a differential pressure between the pressure in the back pressure chamber 19 and the pressure in the suction chamber 14 generates a downward thrust load Fs of the same magnitude as the upward thrust load Fs. Since the two thrust loads having opposite directions cancel each other out, the contact force between the end plate portion 6a and the middle housing 13 is the same as the pressure in the back pressure chamber 19 and the pressure in the suction chamber 14. The load is reduced only to the load acting on the sealing material 11 due to the differential pressure.

As described above, the above-mentioned conventional technique is used to counter the pressure of the refrigerant compressed in the working chamber 9 by the pressure in the back pressure chamber 19, but in the first embodiment. In the scroll compressor C1, the coil spring 12 as an additional urging means is mounted in the back pressure chamber 19, and the spring force Fk acts in the direction opposite to the thrust load Fs, as shown in FIG. Therefore, the pressure of the refrigerant introduced into the back pressure chamber 19 can be made lower than in the case of the conventional technique.

As a result, the pressure difference between the back pressure chamber 19 and the suction chamber 14 acting on the sealing material 11 is reduced to reduce the load on the sealing material 11 and prevent its abrasion to improve the durability. be able to. Further, since the contact force between the end plate portion 6a of the orbiting scroll 6 and the surface of the middle housing 13 that supports the end plate portion 6a in the axial direction can be reduced, the lubrication state can be changed to fluid lubrication with a small friction coefficient. Since it can be set as a region, it becomes possible to further reduce the frictional force on the thrust load supporting surface as compared with the prior art and further reduce the mechanical loss.

At this time, the spring force Fk and the force generated by the pressure Pc in the back pressure chamber 19, that is, the force Fp due to the back pressure Pc.
And the thrust load Fs are set so as to satisfy the following relational expression (see FIG. 3). Fs = F
p + Fk

In view of this relational expression, by adopting a configuration in which the force Fp due to the back pressure is zero, that is, the back pressure chamber 1
If 9 is eliminated and only the spring force Fk of the coil spring 12 opposes the compression reaction force due to the refrigerant in the working chamber 9, a simpler configuration can be considered. Although the compression reaction force is zero at the time of starting, the spring force Fk of the coil spring 12 acts so as to press the orbiting scroll 6 against the fixed scroll 8. Therefore, this excessive pressing force causes a problem at the time of starting. become.

For example, when the thrust load Fs reaches 7,000 (N) because the refrigerant is CO 2 and the compression reaction force during steady operation is large, the coil spring 12 which produces a large spring force Fk to match it. However, since a compression reaction force has not yet been generated at the time of startup, a large spring force F close to 7000 (N)
Since k acts as it is between the orbiting scroll 6 and the fixed scroll 8, the lubricating state of the sliding contact portion may be insufficient at the time of startup, and the tip end portions of the blade portions of the orbiting scroll and the fixed scroll may be insufficient. May be damaged by a large frictional force, or the starting torque may be so large that it may not start depending on the motor 2. Therefore, there is a problem in the structure in which the back pressure chamber 19 is eliminated and only the coil spring 12 opposes the compression reaction force, and therefore it is not used in the present invention.

As described above, in the scroll compressor C1 of the first embodiment, in addition to providing the back pressure chamber 19 to utilize the force Fp by the back pressure Pc, the back pressure chamber 19 is additionally provided. A spring force F is also provided by providing a coil spring 12 as a biasing means.
The feature is that k is used together. According to the experiment, the magnitude of the spring force Fk in this case is about 2000 (N)
By doing the following, it is possible to avoid the problem at the time of starting as described above and solve the problem of the conventional technique.

Since the coil spring 12 is mounted between the end plate portion 6a of the orbiting scroll 6 that orbits and the stationary middle housing 13, if an annular corrugated spring or the like is used in that portion, Although the surface of the spring may come into sliding contact with both the orbiting scroll 6 and the middle housing 13 in a frictional state, mechanical loss may occur, but the coil spring 12 is used as in the first embodiment. Since both ends of the coil spring 12 are fixed to the orbiting scroll 6 and the middle housing 13, respectively, when the orbiting scroll 6 revolves with respect to the middle housing 13, the center line of the coil spring 12 moves substantially on a conical surface. Since the direction of the inclination is changed, that is, only elastic deformation is performed like shaking the neck, sliding with friction does not occur. Mechanical loss and wear does not occur since.

More specifically, referring to FIG. 3, the coil spring 12 is operated while the compressor C1 is operating.
With the orbiting motion of the orbiting scroll 6, the other end on the orbiting scroll 6 side also makes an orbital motion without rotation about the fixed point of the end on the middle housing 13 side as a fulcrum. This orbital motion causes the coil spring 12 to flex in the radial direction, and a load Fb is generated by this flexion. However, as shown in FIG. 4, since this load Fb is a load that acts in a direction that does not affect the drive torque of the compressor C1, it causes no mechanical loss.

In each of FIGS. 4 (a) to 4 (d), each time the shaft 1 rotates by 90 °, the center of the shaft 1 (and thus the center of the middle housing 13) Cf is
The position where the center Cm of the orbiting scroll 6 that revolves revolves and the back pressure chamber 19 that has the sealing material 11 together with the position.
In the figure, how the coil spring 12 inclines and the direction in which the load Fb generated by the coil spring 12 acts are shown by arrows with time. In FIG. 4, (a) shows a rotation angle of the shaft 1 of 0 °.
Similarly, the case of (b) is 90 °, and the case of (c) is 1
The case of 80 ° and the case of (d) of 270 ° are shown.

In the scroll compressor C1 of the first embodiment, the vertical contact load at the sliding contact portion between the orbiting scroll 6 and the middle housing 13 can be reduced by the above-mentioned means. This is not limited to simply reducing the absolute value of the contact load Fs that causes mechanical loss. As can be seen from the Stribeck diagram shown in FIG. 2, the friction coefficient μ itself in the sliding contact portion is lowered. It is also useful to do. In addition,
The number of lubrication characteristics s shown on the horizontal axis of the diagram of FIG. The velocity can be calculated from the following equation, where v is the load, and F is the load acting vertically between the sliding contact surfaces. s = η · v / F

As described above, in the scroll compressor C1 of the first embodiment, that is, in the scroll compressor of the present invention, in addition to the force Fp by the back pressure, the spring by the coil spring 12 which is an additional biasing means. A force Fk is applied to reduce the vertical load F, that is, the thrust load Fs, and the friction coefficient is also reduced by increasing the number of lubrication characteristics s to operate in the fluid lubrication region shown in the diagram of FIG. As a result, it is possible to provide a back pressure type thrust support mechanism which has little mechanical loss and wear of the sliding contact portion, has a simple structure, and can be manufactured at low cost.

Next, FIG. 5 shows a scroll type compressor C2 as a second embodiment of the present invention. The same parts as those of the scroll compressor C1 of the first embodiment are designated by the same reference numerals, and the duplicated description will be omitted. The characteristic of the compressor C2 of the second embodiment is that the back pressure chamber 19 formed by the annular groove 6e formed in the end plate portion 6a of the orbiting scroll 6 in the compressor C1 of the first embodiment has a middle housing. It is configured by an annular groove 13a formed on the 13 side. Therefore, the corresponding portion of the end plate portion 6a of the orbiting scroll 6 is a flat surface, but also in the second embodiment, a plurality of coil springs 12 are mounted in the annular groove 13a, and both ends thereof are The fixing to the bottom surface of the annular groove 13a and the surface of the end plate portion 6a, the mounting of the sealing material 11 in the annular groove 13a, and the like are the same as those in the first embodiment. The working effect of the embodiment is substantially the same as that of the first embodiment.

FIG. 6 shows a scroll type compressor C3 as a third embodiment of the present invention. The characteristic of the compressor C3 of the third embodiment is that the annular spring formed in the end plate portion 6a of the orbiting scroll 6 instead of the coil spring 12 used as the additional biasing means in the first and second embodiments. That is, the annular permanent magnet 20 is fixed in the groove by an adhesive or the like. The annular permanent magnet 20 may be divided into a plurality of parts. The permanent magnet 20 is magnetized in the axial direction, and the entire fixed scroll 8 or at least the portion in sliding contact with the permanent magnet 20 is made of a magnetic material such as iron. However, it is also possible to attach another permanent magnet to the fixed scroll 8 so that the opposite magnetic poles are located in this portion. End plate portion 6 of the orbiting scroll 6
As in the case of the first embodiment, a back pressure chamber 19 is formed by the annular groove 6e and a seal member 11 is provided in a, and the pressure introducing hole 6d communicates with the working chamber 9 of a predetermined high pressure. However, it is not necessary to provide the coil spring 12 in the back pressure chamber 19.

In the scroll compressor C3 of the third embodiment, the orbiting scroll 6 is fixed by the magnetic force of the permanent magnet 20 instead of the coil spring 12 as an additional biasing means. The permanent magnet 20 serves as an additional urging means, and cooperates with the back pressure acting in the back pressure chamber 19 to urge the orbiting scroll 6 downward in FIG. As is apparent from this configuration, the working effect of the third embodiment is also substantially the same as that of the first embodiment.

Further, FIG. 7 shows a scroll type compressor C4 as a fourth embodiment of the present invention. Compressor C of Fourth Embodiment
The feature of 4 is that a magnetic repulsion device 21 is provided in place of the coil spring 12 used as an additional biasing means in the first and second embodiments. Magnetic repulsion device 21
In the annular groove formed in the middle housing 13 and the first permanent magnet 21a attached to the bottom of the annular groove 6e formed in the end plate portion 6a of the orbiting scroll 6 by a method such as adhesion. The second permanent magnet 21b is attached by a method such as adhesion and has a lower end surface protruding so as to be close to the upper surface of the first permanent magnet 21a. The fact that the pressure introducing hole 6d for introducing high-pressure fluid into the back pressure chamber 19 formed of the annular groove 6e is opened, and that the back pressure chamber 19 is provided with the sealing material 11 is described in each of the above-described embodiments. It is similar to the case of.

The scroll type compressor C4 of the fourth embodiment is provided with a first permanent magnet 21a and a second permanent magnet 21b which form a pair as a magnetic repulsion device 21, both of which are attached in the axial direction. The magnets are magnetized, but the arrangement of the magnetic poles is opposite to each other.
Since the poles face each other or the S poles and the S poles face each other, the two magnets 21a and 21b repel each other. It is urged downward at 7.
In this way, the magnetic repulsion device 21 acts in the same manner as the coil spring 12, so that the fourth embodiment has substantially the same action and effect as the first embodiment and the like.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing a first embodiment of the present invention.

FIG. 2 is a Stribeck diagram showing changes in friction coefficient according to conditions.

FIG. 3 is a cross-sectional view showing an enlarged main part of the first embodiment.

4 (a) to (d) are transverse cross-sectional views showing an operating state of the scroll compressor of the first embodiment with time.

FIG. 5 is a vertical cross-sectional view showing a second embodiment of the present invention.

FIG. 6 is a vertical sectional view showing a third embodiment of the present invention.

FIG. 7 is a vertical sectional view showing a third embodiment of the present invention.

[Explanation of symbols]

1 ... Shaft 1a ... crank part 2 ... motor 6 ... orbiting scroll 6a ... End plate 6b ... Swirl-shaped blade 6d ... Pressure introducing hole 6e ... groove 8 ... Fixed scroll 8a ... End plate 8b ... Swirl-shaped blade 9 ... Working chamber 11 ... Sealing material 12 ... Coil spring 13 ... Middle housing 19 ... Back pressure chamber 20 ... Permanent magnet 21 ... Magnetic repulsion device Fb ... Spring restoring force generated by revolution movement Fk ... Spring biasing force Fp ... power by back pressure Fs ... Thrust load Pc ... Back pressure Ps ... suction pressure

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Mitsuo Inagaki             14 Iwatani Shimohakaku-cho, Nishio-shi, Aichi Stock Association             Company Japan Auto Parts Research Institute (72) Inventor Shigehide Kimura             14 Iwatani Shimohakaku-cho, Nishio-shi, Aichi Stock Association             Company Japan Auto Parts Research Institute (72) Inventor Takeshi Sakai             1-1, Showa-cho, Kariya city, Aichi stock market             Inside the company DENSO F-term (reference) 3H039 AA04 AA12 BB01 CC02 CC08                       CC11 CC24 CC25 CC31

Claims (8)

[Claims] 1. A housing, a motor fixed to the housing, an eccentric crank portion, a shaft rotatably driven by the motor, a spiral vane portion and an end plate portion. An orbiting scroll that revolves by being driven by a crank portion of the shaft; and a fixed scroll that has a spiral blade portion and an end plate portion that mesh with the orbiting scroll and that is fixed to the housing. When the orbiting scroll is driven by the motor via the shaft and revolves, a plurality of working chambers formed between the blades of the orbiting scroll and the blades of the fixed scroll are centered from the outer peripheral portion. The volume of the working chamber is continuously reduced during the movement toward the portion to allow the fluid to flow in the working chamber. A scroll-type compressor for compressing, further comprising: an orbiting scroll for supporting a thrust load in the axial direction of the shaft that acts on the orbiting scroll as the compression pressure of the fluid in the working chamber rises. At least one middle housing is provided behind the housing as a part of the housing, and at least one is formed on one of the back surface of the end plate portion of the orbiting scroll and the surface of the middle housing that faces and supports it. And a back pressure chamber into which a high-pressure fluid of a predetermined size is introduced, and an axial line that supplements the back pressure force generated in the back pressure chamber to press the orbiting scroll in the axial direction toward the fixed scroll. A scroll compressor, characterized in that it is provided with additional biasing means for generating a directional force. 2. The scroll-type compressor according to claim 1, wherein the additional biasing means comprises at least one coil spring mounted between the orbiting scroll and the middle housing. 3. The additional urging means comprises a plurality of coil springs, wherein one ends of the coil springs are fixed to the orbiting scroll.
A scroll compressor, wherein the other end is fixed to the middle housing. 4. The method according to any one of claims 1 to 3,
A scroll compressor, wherein the additional biasing means is provided in the back pressure chamber. 5. The scroll compressor according to claim 1, wherein the additional biasing means comprises at least one magnet. 6. The magnet according to claim 5, wherein the magnet is attached to one of a pair of surfaces of the orbiting scroll and the fixed scroll which are opposed to each other at an outer peripheral portion, and the other surface is made of a magnetic material. A scroll type compressor characterized by being installed. 7. The scroll according to claim 5, wherein the magnet is composed of a plurality of magnets arranged so that magnetic poles of the same polarity face each other, and these magnets constitute a magnetic repulsion device. Type compressor. 8. The method according to claim 1, wherein
A scroll-type compressor, wherein the fluid is a refrigerant flowing in a refrigeration cycle, and the pressure of the compressed refrigerant is set to be higher than a critical pressure of the refrigerant.