JPH10103266A - Helical blade type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the reliability of a helical blade type compressor and increase its capacity by supporting compression load which acts on a blade on both sides of an inner peripheral face of a cylinder and an outer peripheral face of a piston. SOLUTION: A spiral cylinder groove 10 formed in such a manner that a part of a blade 3 can be inserted is provided on an inner peripheral face of a cylinder 1. The blade 3 comes in and out of a piston groove 4 formed mainly on an outer surface of a roller piston 2 while a compressor is operated, but a part thereof is inserted into the cylinder groove 10 formed on an inner surface of the cylinder 1. Consequently, even when the blade 3 is pressed from a compression chamber 6b on a high pressure side to a compression chamber 6a on a low pressure side due to, for example, a difference in pressure, load due to the difference in pressure which acts on the blade 3 can be supported by both of the spiral piston groove 4 and cylinder groove 10, namely, on both sides of the blade 3. As a result, it is possible to reduce the concentration of stress in a contact part of the piston groove 4 and the cylinder groove 10 of the blade 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid compressor used for a refrigeration cycle apparatus for compressing a refrigerant gas as a working fluid, and more particularly to a helical blade type compressor having a helical blade.

[0002]

2. Description of the Related Art Conventionally, various types of compressors, such as a reciprocating type and a rotary type, have been known. The structure of the compression section is complicated, the number of parts is large, and the cost is high. Further, noise may be generated due to vibration caused by imbalance of the rotating part.

Therefore, a helical blade type fluid compressor having a helical blade has recently been proposed as a solution to the above-mentioned problem. A conventional helical blade type fluid compressor (compressor) will be described with reference to FIG.

[0004] The compressor has a compressor section 100 as a main section and an electric motor section 110, and these are housed concentrically in a closed casing 120. The motor unit 110 has an annular stator 110a fixed to the inner surface of the closed casing 120, and an annular rotor 110b provided inside the stator 110a.

Next, the structure of the compressor section 100 as a main section and the compression principle thereof will be briefly described with reference to the drawings. A roller piston 102 is provided inside a hollow cylindrical cylinder 101 so as to be rotatable around a parallel axis slightly eccentric from the center line O of the cylinder 101. The cylinder 101
Rotates while being fixed to the rotor 110b. On the outer peripheral surface of the roller piston 102, a piston groove 104 is provided in a spiral shape having unequal intervals in the axial direction, that is, such that the pitch gradually changes from one end to the other end.
Also, the piston groove 104 of the eccentric roller piston 102
, A helical blade 103 is mounted. In addition,
At one end of the roller piston 102, an engagement groove (not shown) is provided from the peripheral surface in the axial direction, and a driving pin (not shown) projecting from the inner peripheral surface of the cylinder 101 is provided in the engagement groove. ) Are inserted so as to be able to advance and retreat along the radial direction of the cylinder 101. A rotational force transmission mechanism is constituted by the engagement groove and the drive pin.

With such a configuration, the inner peripheral surface of the cylinder 101, the outer peripheral surface of the roller piston 102, and the helical blade 103 form a plurality of compression chambers 106a, 106b,
106c are formed. Helical blade 1
Numeral 03 moves along the piston groove 104 with the turning movement of the roller piston 102 with respect to the cylinder 101, and moves in and out in the depth direction. Both ends of the cylinder 101 and the roller piston 102 are bearings 109a and 109
b, the bearings are provided with a working fluid suction port 107 and a working fluid discharge port 108a, respectively. The closed casing 120 has a discharge port 108.
b is formed to discharge compressed fluid from the compressor body.

As described above, the pitch of the piston groove 104 formed in the roller piston 102 is gradually narrowed from the suction port 107 to the discharge port 108. Therefore, the piston 101 has the cylinder 101, the roller piston 102, and the helical blade 103. The volume of the partitioned space gradually decreases from the suction port 107 to the discharge port 108a. The working fluid sucked from the suction port 107 in this way sequentially passes through a plurality of compression chambers 106a, 106a as the roller piston 102 rotates.
b and 106c, and are transferred to the space on the discharge side and gradually compressed, and discharged from the discharge port 108a and the discharge port 108b.

However, such a conventional helical blade type compressor has the following disadvantages. That is, while the compressor is operating, the blade 103 moves in and out of the piston groove 104.
As shown in (a), the pressure difference between the plurality of compression chambers 106 causes, for example, the blade 103 to move the compression chamber 106 on the high pressure side.
b into the low pressure side compression chamber 106a and the piston groove 1
The contact portion 103a of the blade 103 with the piston groove 104 is liable to be worn because it comes into contact with the wall of the compression chamber 106a on the low pressure side of 04 and slides.

This is because the portion supporting the load corresponding to the differential pressure acting on the blade 103 is only the contact portion 103a between the blade 103 and the wall of the compression chamber on the low pressure side of the piston groove 104, so that the moment is balanced. This is because a large concentrated stress is generated in the vicinity of the contact portion 103a of the blade 103 as shown in FIG. FIG. 10 (b)
The distribution of the contact stress σ on the surface of the contact portion 103a of the blade 103 is shown.

[0010] In the conventional helical blade type compressor, how to reduce the stress concentration in this portion is a major issue in order to ensure the reliability of the blade. on the other hand,
In order to increase the capacity of the helical blade type compressor, it is necessary to increase the amount of eccentricity of the roller piston 102 with respect to the cylinder 101. However,
Since the generated stress increases with the amount of eccentricity, the conventional structure has a limit in increasing the capacity by increasing the amount of eccentricity.

[0011]

As described above, in the conventional helical blade type compressor, a large concentrated stress is generated in the vicinity of the helical groove contact portion of the blade due to moment balance, and the reliability is reduced. In addition, the contact stress increases with an increase in the amount of eccentricity of the roller piston with respect to the cylinder. With the conventional structure, there is a limit in increasing the capacity of the compressor by increasing the amount of eccentricity.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and has as its object to provide a helical blade type compressor capable of improving reliability and increasing capacity.

[0013]

To achieve the above object, according to the first aspect of the present invention, a hollow cylinder, a roller piston eccentrically arranged in the cylinder, and a A helical groove formed on at least one of the peripheral surface or the outer peripheral surface of the roller piston, and a helical blade wound around the helical groove so as to freely enter and exit the helical groove. In a helical blade type compressor that performs compression while sucking and gradually transferring to a discharge side, a compression load acting on the blade is configured to be supported on both sides of an inner peripheral surface of the cylinder and an outer peripheral surface of the piston. ing.

According to the second aspect of the present invention, a hollow cylinder, a roller piston eccentrically arranged in the cylinder, and a first spiral groove formed along the outer peripheral surface of the roller piston And a helical blade which is wound around the first helical groove so as to be freely inserted into and retracted from the first helical groove, and compresses while sucking the working fluid from the suction side of the cylinder and gradually transferring it to the discharge side. In the helical blade type compressor to be performed, a second spiral groove is formed on the inner peripheral surface of the cylinder, the blade is inserted into the second spiral groove, and the blades are first and second.
The spiral groove is supported on both sides.

According to a third aspect of the present invention, there is provided a hollow cylinder, a roller piston eccentrically disposed in the cylinder, and a spiral groove formed along the outer peripheral surface of the roller piston. A helical blade wound around the helical groove so as to freely enter and exit,
In a helical blade type compressor that compresses while sucking the working fluid from the suction side of the cylinder and gradually transferring it to the discharge side, a supporting means for supporting the blade on the inner peripheral surface of the cylinder is provided, and the blade is provided with the blade. The piston is supported on both sides of the inner peripheral surface of the cylinder and the outer peripheral surface of the piston.

According to a fourth aspect of the present invention, there is provided a hollow cylinder, a roller piston eccentrically disposed in the cylinder, and a spiral groove formed along an inner peripheral surface of the cylinder. A spiral blade wound around the spiral groove so as to freely enter and exit, and a support means provided on an outer peripheral surface of the roller piston to support the blade, and a working fluid is supplied from a suction side of the cylinder. In a helical blade type compressor that performs compression while sucking and gradually transferring to a discharge side, a compression load acting on the blade is supported on both sides of an inner peripheral surface of the cylinder and an outer peripheral surface of the piston. It is characterized by:

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION

(First Embodiment) A first embodiment according to the present invention will be described with reference to FIG.
An embodiment will be described. FIG. 1 is a diagram showing a main part (compressor part) of the compressor according to the first embodiment, and illustration and description of an electric motor part and a closed casing similar to those of a conventional compressor are omitted.

A main part of the compressor is a hollow cylindrical cylinder 1, a roller piston 2 eccentrically disposed inside the cylinder 1 and revolving relative to the cylinder 1, and an outer peripheral surface of the roller piston 2. And a helical blade 3 inserted into a helically formed piston groove 4. The blade 3 slides in the piston groove 4 with the turning movement of the roller piston 2 with respect to the cylinder 1 so that the blade 3 can move in and out in the depth direction. The space defined by the inner peripheral surface of the cylinder 1, the peripheral surface of the roller piston 2, and the blade 3 is formed by the compression chambers 6a, 6b,
6c... Function.

Here, a feature of the first embodiment is that a spiral cylinder groove 10 is formed on the inner peripheral surface of the cylinder 1 so that a part of the blade 3 can be inserted. The provision of the cylinder groove 10 allows the blade 3 to move into and out of the piston groove 4 formed mainly on the outer surface of the roller piston 2 during operation of the compressor. It is inserted into the formed cylinder groove 10. Therefore, for example, even when the blade 3 is pushed from the high-pressure side compression chamber 6b to the low-pressure side compression chamber 6a due to the differential pressure between the plurality of compression chambers 6, the blade 3
Can be supported by both the spiral piston groove 4 and the cylinder groove 10, that is, both sides of the blade 3.

Therefore, the concentration of stress at the contact portion between the blade 3 and the piston groove 4 and the cylinder groove 10 is reduced as compared with the conventional case in which the piston 3 slides only on the wall of the piston groove. Wear of the contact part is significantly reduced,
The durability and reliability of the blade 3 are dramatically improved.

(Second Embodiment) Hereinafter, a second embodiment will be described with reference to FIG. FIG. 2 shows the first
It is a diagram mainly showing a difference from the embodiment of the present invention, is a diagram showing a further enlarged characteristic portion of the main part of the compressor, the same motor unit and a sealed casing as the conventional compressor, The illustration and description are omitted, and the same parts as those in FIG.
Some parts are not shown and described.

The feature of the second embodiment is that, as shown in FIG. 2, the cylinder 1 is made up of an outer cylinder 1a having a double cylindrical structure.
It is constituted by the inner cylinder 1b, and is characterized in that a spiral through cylinder groove 11 into which a part of the blade 3 can be inserted is formed on the inner cylinder 1b side.

According to the second embodiment configured as described above, the blade 3 moves in and out of the piston groove 4 formed mainly on the outer surface of the roller piston 2 during operation of the compressor. A part is inserted into a spiral through-cylinder groove 11 formed in the inner cylinder 1b of the cylinder 1.
Therefore, for example, even when the blade 3 is pushed from the high-pressure side compression chamber 6b to the low-pressure side compression chamber 6a due to the differential pressure between the plurality of compression chambers 6, the load due to the differential pressure acting on the blade 3 is reduced. It is possible to support the spiral piston groove 4 and the spiral through cylinder groove 11 on both sides of the boom 3.

Therefore, the stress concentration at the contact portion between the blade groove 3 and the piston groove 4 and the helical penetrating cylinder groove 11 is alleviated, as compared with the conventional case where the piston slides only on the wall of the piston groove. As a result, the wear of the contact portion is remarkably suppressed, and the durability and reliability of the blade 3 are dramatically improved.

According to the structure of the second embodiment, only the inner cylinder 1b of the cylinder 1 needs to be formed with a through groove. There is an effect that the groove processing on the inner surface is significantly facilitated.

(Third Embodiment) Hereinafter, a third embodiment will be described with reference to FIG. FIG. 3 shows the second
3A and 3B are views for explaining different parts from the embodiment shown in FIG. 2, and the same parts as those in FIG. 2 are denoted by the same reference numerals, and detailed description is omitted.

The configuration of the third embodiment is characterized in that the cylinder 1 as shown in FIG.
a, the inner cylinder 1b is formed, and the helical penetrating cylinder groove 11 into which a part of the blade 3 can be inserted is formed on the inner cylinder 1b side. The configuration is such that an adhesive 12 is adhered between the cylinder groove 11 and the blade 3 inserted in the groove 11.

According to the third embodiment constructed as described above, similarly to the second embodiment, the load caused by the differential pressure acting on the blade 3 is applied to the helical piston groove 4 and the helical penetrating cylinder groove 11. Of the blade 3 in contact with the piston groove 4 and the helical penetrating cylinder groove 11 as compared with the conventional case in which the blade 3 slides on the wall having only the piston groove. As a result, the wear of the contact portion is remarkably suppressed, and the durability and reliability of the blade 3 are dramatically improved.

Further, according to the third embodiment, as compared with the second embodiment, there is also an effect that the assemblability is improved by previously bonding and fixing the inner cylinder 1b and the blade 3 with an adhesive. .

(Fourth Embodiment) A fourth embodiment according to the present invention will be described with reference to FIG. FIG. 4 is a view showing a main part (compressor part) of a compressor according to the fourth embodiment, similarly to FIG. 1, and the same parts as those in FIG. Omitted.

In the fourth embodiment, the cylinder 1, the roller piston 2, and the blade 3 have the same structure as that of a conventional helical blade type compressor. That is, the inner peripheral surface is bonded with the adhesive 13. That is, blade 3
And the inner peripheral surface of the cylinder 1 opposed to the outer peripheral surface of the blade 3 are adhered and fixed.

According to the fourth embodiment configured as described above, the load caused by the differential pressure acting on the blade 3 is applied to the helical piston groove 4, the outer peripheral surface of the blade 3 and the inner peripheral surface of the cylinder 1. Can be supported by both the adhesive portion and the adhesive portion. Therefore, the stress concentration at the contact portion of the blade 3 with the piston groove 4 and the helical penetrating cylinder groove 11 is reduced as compared with the conventional case where the piston slides only on the wall of the piston groove. Wear of the contact portion is remarkably suppressed, and the durability and reliability of the blade 3 are dramatically improved.

(Fifth Embodiment) Next, a fifth embodiment will be described with reference to FIG. Note that FIG.
FIG. 5 is a partially enlarged view for explaining portions different from the third embodiment, and the same portions as those in FIG. 4 are denoted by the same reference numerals, and detailed description is omitted.

A feature of the fifth embodiment lies in a specific method of bonding the outer peripheral surface of the blade 3 and the inner peripheral surface of the cylinder 1 of the fourth embodiment shown in FIG. That is, a concave portion 3b is provided on the entire circumference or a part of the outer peripheral surface of the blade, and through holes 1c are formed in the cylinder 1 at several places where the cylinder 3 comes into contact with the blade 3. Then, an adhesive is injected into the concave portion 3b on the outer peripheral surface of the blade 3 from the through hole 1c, and the outer peripheral surface of the blade 3 is bonded to the inner peripheral surface of the cylinder 1.

Adopting a structure suitable for bonding facilitates the bonding and assembling steps. The outer peripheral surface of the blade 3 and the inner peripheral surface of the cylinder 1 opposed to the outer peripheral surface of the blade 3 are bonded and fixed, so that the load due to the differential pressure acting on the blade 3 is spirally wound in the same manner as in the fourth embodiment. Can be supported by both the piston groove 4 in a shape of a circle and the bonding portion between the outer peripheral surface of the blade 3 and the inner peripheral surface of the cylinder 1, and when sliding with the wall of only the piston groove as in the conventional case. The stress concentration at the contact portion between the blade 3 and the inner peripheral surface of the piston groove 4 and the cylinder groove 11 is reduced, and as a result, the wear of the contact portion is remarkably suppressed, and the durability and reliability of the blade 3 are improved. Is dramatically improved.

(Sixth Embodiment) Next, a sixth embodiment will be described with reference to FIG. Note that FIG.
FIG. 6 is a partially enlarged view for explaining a portion different from the third embodiment, and the same portions as those in FIGS. 4 and 5 are denoted by the same reference numerals, and detailed description is omitted.

The feature of the sixth embodiment is that a pin 14 is used instead of the adhesive fixing in the fifth embodiment.
That is, was used. In other words, the concave portion 3b is provided on the entire circumference or a part of the outer peripheral surface of the blade, and the through holes 1c are formed in the cylinder 1 at several locations where the blade 3 contacts.
Then, the recess 3 on the outer peripheral surface of the blade 3 is
b, and insert the pin 14 into the blade 3
The outer peripheral surface and the inner peripheral surface of the cylinder 1 are fixed.

According to the sixth embodiment configured as described above, the same operation and effect as those of the fifth embodiment can be obtained.

(Seventh Embodiment) Next, a seventh embodiment will be described with reference to FIG. The seventh embodiment focuses on the configuration of the blade 3, and FIGS. 7A to 7F show examples of the configuration of the blade 3. FIG. 7A shows an example in which the blade 3 is formed of a metal material into a thin leaf spring-like structure. Blade 3
Are fitted into a piston groove 4 formed in the roller piston 2 and a cylinder groove 10 of the cylinder 1 (see the first embodiment shown in FIG. 1) to form a double-supported structure, and As described above, the width 3c of the blade 3 can be reduced by using a thin metal-based material. By adopting the configuration as shown in FIG. 7A, the operation and effect of improving the degree of freedom in designing the spiral shape and further improving the manufacturability of the blade 3 occur.

FIGS. 7B, 7C and 7D are all shown in FIG.
This is an example in which the blade 3 in (a) has a hybrid configuration of a metal material and a resin material or a rubber material. In the configuration example shown in FIG. 7B, the blade 3 has a two-layer composite structure in which a thin metal material and a resin or rubber material are bonded.

The configuration example shown in FIG. 7 (c) is a blade 3 having a composite structure of three layers of a sandwich structure by bonding a resin or rubber material on both sides with a thin metal material sandwiched in the center. It is.

In the configuration example shown in FIG. 7D, the blade 3 has a composite structure in which a thin metal material is coated with a resin or rubber material. As shown in FIGS. 7B to 7D, a hybrid structure in which a resin or a rubber-based material is used for the sliding surface of the blade 3 that slides with the piston groove 4 is used. The sliding characteristics of the friction surface between the blade 3 and the piston groove 4 are further improved as compared with the example shown in FIG.

FIGS. 7E and 7F show examples in which the piston groove 4 or the cylinder groove 10 is devised. In the example shown in FIG. 7E, the blade 3 is made of a metal material, and a resin or rubber material is stretched or coated inside the piston groove 4 (particularly, the side wall portion), and a friction surface with the blade 3 is formed. Are improved in sliding characteristics.

FIG. 7F shows an example in which, in addition to the structure shown in FIG. 7E, the side wall of the cylinder groove 10, that is, the joint with the blade 3 is covered with resin or a rubber material or coated. By adopting such a configuration, it is possible to further improve the life of the blade.

(Eighth Embodiment) Next, an eighth embodiment will be described with reference to FIG. The eighth embodiment is different from the first to seventh embodiments in the engagement configuration of the cylinder 1, the piston 2, and the blade 3.

That is, the groove through which the blade 3 normally enters and exits is the spiral piston groove 4 formed in the roller piston 2, but in the eighth embodiment, the groove through which the blade 3 enters and exits is provided on the cylinder 1 side. The feature is that it is formed.

More specifically, as shown in FIG.
Is composed of an outer cylinder 1a having a double cylindrical structure and an inner cylinder 1b having a thickness greater than that of the outer cylinder 1a, and a blade 3 is provided on the inner cylinder 1b side.
Is formed by attaching or coating a resin or rubber-based material on the side wall inside the cylinder groove 16 to improve the characteristics of the friction surface with the blade 3. doing. In addition,
The thickness of the inner cylinder 1b is set to a thickness capable of forming a sufficient cylinder groove 11 for the blade 3 to enter and exit.

In the eighth embodiment, the cylinder 1 may be integrally formed as a thick cylinder 1 without employing the above-described divided structure of the outer cylinder 1a and the inner cylinder 1b. That is clear. Further, a resin or rubber-based material may be attached to the piston groove on the roller piston 2 side or coated. The configuration of the blade 3 can employ any of the configurations disclosed in FIG.

[0049]

As described above, according to the present invention,
The blade reliability can be improved and a large capacity helical blade compressor can be obtained.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a main part of a helical blade type compressor according to a first embodiment of the present invention.

FIG. 2 is a sectional view showing a main part of a helical blade type compressor according to a second embodiment of the present invention.

FIG. 3 is a sectional view showing a main part of a helical blade type compressor according to a third embodiment of the present invention.

FIG. 4 is a sectional view showing a main part of a helical blade type compressor according to a fourth embodiment of the present invention.

FIG. 5 is a partial sectional view showing a main part of a helical blade type compressor according to a fifth embodiment of the present invention.

FIG. 6 is a partial sectional view showing a main part of a helical blade type compressor according to a sixth embodiment of the present invention.

FIG. 7 is a sectional view showing an example of a blade according to a seventh embodiment of the present invention.

FIG. 8 is a sectional view showing an example of a blade according to an eighth embodiment of the present invention.

FIG. 9 is a partial cross-sectional view showing a main part of a conventional compressor.

FIG. 10 is a distribution diagram showing contact stress generated in a conventional blade.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Cylinder 1a Outer cylinder 1b Inner cylinder 1c Through-hole 2 Roller piston 3 Blade 4 Piston groove (spiral groove) 6a, 6b, 6c Compression chamber 10, 11 Cylinder groove 12, 13 Adhesive

Claims (11)

[Claims] 1. A hollow cylinder, a roller piston eccentrically disposed in the cylinder, a spiral groove formed on at least one of an inner peripheral surface of the cylinder or an outer peripheral surface of the roller piston, A helical blade type compressor, which is provided with a helical blade which is wound around the groove so as to freely move in and out, and which compresses while sucking a working fluid from a suction side of the cylinder and gradually transferring the working fluid to a discharge side. A helical blade type compressor configured to support the compression load to be applied on both sides of an inner peripheral surface of the cylinder and an outer peripheral surface of the piston. 2. A hollow cylinder, a roller piston eccentrically arranged in the cylinder, a first spiral groove formed along the outer peripheral surface of the roller piston,
A helical blade type compressor having a compression element comprising a spiral blade freely wound into and out of a spiral groove of the cylinder, and performing compression while sucking a working fluid from a suction side of the cylinder and gradually transferring the working fluid to a discharge side. In the above, a second spiral groove is formed on the inner peripheral surface of the cylinder,
A helical blade type compressor, wherein the blade is inserted into the spiral groove of (1), and the blade is supported on both sides of the first and second spiral grooves. 3. A hollow cylinder, a roller piston eccentrically disposed in the cylinder, a spiral groove formed along the outer peripheral surface of the roller piston, and a spiral groove wound around the spiral groove. A helical blade type compressor comprising a compression element consisting of a helical blade to be compressed and sucking a working fluid from a suction side of the cylinder to gradually transfer the working fluid to a discharge side. A helical blade type compressor, wherein support means for supporting the blade is provided, and the blade is supported on both sides of an inner peripheral surface of the cylinder and an outer peripheral surface of the piston. 4. A hollow cylinder, a roller piston eccentrically arranged in the cylinder, a helical groove formed along the inner peripheral surface of the cylinder, and a spirally-woundable groove wound around the helical groove. And a supporting means provided on the outer peripheral surface of the roller piston for supporting the blade. The working fluid is sucked from the suction side of the cylinder and is gradually transferred to the discharge side while being compressed. A helical blade compressor configured to support a compressive load acting on the blade on both sides of an inner peripheral surface of the cylinder and an outer peripheral surface of the piston. 5. The helical groove is formed on both the inner peripheral surface of the cylinder and the outer peripheral surface of the roller piston, and one helical groove is formed deeper than the other helical groove. The helical blade type compressor according to claim 1, wherein the blade is configured so as to be able to move in and out of the spiral groove, and the blade is supported in the other spiral groove. 6. The cylinder comprises an outer cylinder and an inner cylinder,
The helical blade type compressor according to claim 2, wherein the second helical groove comprises a through hole formed in the inner cylinder. 7. A helical blade type compressor according to claim 1, further comprising means for fixing and supporting said blade on an inner peripheral surface of said cylinder. 8. The helical blade type compressor according to claim 1, wherein said blade is configured as a hybrid comprising a plurality of layers of a metal material and a resin or rubber material. 9. The blade according to claim 1, wherein a resin or rubber material is provided on both sides of the metal material provided at the center.
The helical blade type compressor according to claim 1, wherein the compressor is formed in layers. 10. The helical blade type compressor according to claim 7, wherein said fixing means is an adhesive provided at a contact portion between said blade and said inner peripheral surface of said cylinder. 11. A fixing device comprising: a recess provided at a portion of the blade facing the inner peripheral surface of the cylinder; a through hole formed at a position facing the recess of the cylinder; The helical blade type compressor according to claim 7, further comprising a pin member inserted into said recess.