JP3805911B2 - Fluid compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a fluid compressor called, for example, a helical blade compressor, and more particularly to an improvement in a structure for closely attaching a blade to a cylinder.
[0002]
[Prior art]
Conventionally, as shown in FIG. 11 and FIGS. 12A and 12B, in a fluid compressor called a helical blade compressor, the blade A that is spirally wound is formed in a direction along the spiral groove f. A blade stopper S is provided to regulate the range of movement.
[0003]
A part of the blade stopper S protrudes from the cylinder C toward the compression chamber D and faces the end surface of the blade A, and the protruding surface t blocks the end surface of the blade A to restrict the movement of the blade A.
[0004]
The protruding surface t on which the blade stopper S restricts the movement of the blade A is formed to be substantially parallel to a line m along the radial direction with respect to the cylinder center o in a cross section perpendicular to the center o of the cylinder C. .
[0005]
In particular, a differential pressure is generated between the compression chambers Da and Db during the compression operation, and the blade A peripheral surface is pressed against the inner peripheral surface of the cylinder C by a force due to the differential pressure. Therefore, the space between the compression chambers Da and Db is reliably sealed, and the volumetric efficiency is kept high.
[0006]
Further, the blade A has a so-called “tension” due to its own shape structure and material selection. The sealing performance of the compression chamber is ensured by the synergistic effect of the tension of the blade A and the differential pressure.
[0007]
[Problems to be solved by the invention]
By the way, during the compression operation, the blade A enters and exits the spiral groove f provided in the roller R, and when the blade A exits the groove f, the frictional force with the groove f is determined by the blade A from the inner peripheral surface of the cylinder C. Acts in the direction of leaving.
[0008]
However, when the total force of the pressing force due to the differential pressure and the tension of the blade A itself is larger than the frictional force, the blade A peripheral surface does not move away from the inner peripheral surface of the cylinder C, and the volumetric compression operation is good. Is done.
[0009]
Naturally, under normal operating conditions, the total force of the pressing force due to the differential pressure and the tension of the blade A itself is designed to be larger than the frictional force when the blade A enters and exits the spiral groove f. When the operating conditions change and the temperature of the blade A rises, the blade A tends to soften and the tension tends to decrease.
[0010]
At this time, the force for pressing the blade A against the inner peripheral surface of the cylinder C becomes insufficient, and the blade A does not come into reliable contact with the inner peripheral surface of the cylinder C, so that the sealing performance against the compression chambers Da and Db is deteriorated. The efficiency will be reduced.
[0011]
In addition, since there is no differential pressure when starting the compression operation, the force for pressing the blade A against the inner peripheral surface of the cylinder C is weak. For this reason, the compression chambers Da and Db cannot be sealed, and an idle operation is performed for a while.
[0012]
In addition, since the compression chamber D is opened to the suction side or the discharge side at both ends of the blade A facing the suction portion and the discharge portion of the compression chamber D, the differential pressure is smaller than the other portions. .
[0013]
Therefore, at both ends of the blade A, the pressing force of the blade A against the cylinder C is weaker than the other portions, and it is easy to leak from the seal portion with the compression chamber D, leading to a decrease in volume efficiency. there were.
[0014]
The present invention has been made by paying attention to the above circumstances, and its purpose is to improve the pressing state of the blade against the inner peripheral surface of the cylinder, and to surely seal against the compression chamber, and thus volume efficiency. It is an object of the present invention to provide a fluid compressor capable of improving the above.
[0015]
[Means for solving the problems]
In order to satisfy the above object, a fluid compressor according to the present invention includes, as claimed in claim 1, a cylindrical cylinder, a roller arranged eccentrically in the cylinder, and an outer peripheral surface of the roller from one end to the other end. A spiral groove provided at a gradually smaller pitch, a blade that is fitted into the spiral groove so as to freely enter and exit and forms a plurality of compression chambers between the cylinder and the roller, and a portion that faces the end surface of the blade. A blade stopper for stopping the blade end surface and restricting the movement of the blade in the spiral direction, and the blade stopper surface of the blade stopper is inclined with respect to the center line of the cylinder. The blade peripheral surface is biased so that the blade peripheral surface comes into close contact with the cylinder inner peripheral surface in a state where the blade end surface is stopped.
[0016]
According to a second aspect of the present invention, in the fluid compressor according to the first aspect, the blade end surface is formed such that a surface direction thereof is inclined with respect to a center line of the cylinder so as to follow the blade stop surface of the blade stopper. And
[0017]
In order to satisfy the above object, according to a third aspect of the present invention, a fluid compressor includes a cylindrical cylinder, a roller eccentrically disposed in the cylinder, and an outer peripheral surface of the roller from one end to the other end. A spiral groove provided at gradually smaller pitches, a blade that is fitted into the spiral groove so as to freely enter and exit and forms a plurality of compression chambers between the cylinder and the roller, and an end of the blade and the cylinder. And a tension elastic body that is interposed therebetween and elastically pulls and biases the blade peripheral surface so as to be in close contact with the inner peripheral surface of the cylinder.
[0021]
By acting the means for solving such a problem, the blade peripheral surface is surely brought into close contact with the cylinder inner peripheral surface, the sealing performance against the compression chamber is ensured, and thus the volume efficiency is improved.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 shows a helical blade type compressor that is a fluid compressor, which includes a compression mechanism unit 3 connected to a hermetic case 1 via a rotary shaft 2 and a motor unit 4 shown with a part omitted. Is housed.
[0023]
A discharge refrigerant pipe (not shown) is connected to the upper end portion of the sealed case 1, and a suction refrigerant pipe 7 is connected to the side surface portion. A condenser, an expansion valve, and an evaporator are sequentially connected from the discharge refrigerant pipe to the suction refrigerant pipe 7 via a refrigerant pipe (all not shown), and these constitute, for example, a refrigeration cycle of an air conditioner. Is done.
[0024]
Next, the compression mechanism unit 3 will be described in detail.
In the figure, reference numeral 8 denotes a cylinder, and a flange 8a integrally projecting on the outer peripheral surface of the upper end of the cylinder 8 is fitted to the inner peripheral wall of the sealed case 1 and is attached and fixed by welding means from the outer peripheral side of the sealed case 1. The
[0025]
The upper end opening of the cylinder 8 is closed by the main bearing 10 and the lower end opening is closed by the auxiliary bearing 11. The main bearing 10 pivotally supports a substantially intermediate portion of the rotating shaft 2, and the auxiliary bearing 11 pivotally supports the lower end of the rotating shaft 2. A receiving plate 14 is attached to the lower surface of the auxiliary bearing 11 and supports the lower end surface of the rotating shaft 2.
[0026]
A roller 18 is eccentrically disposed in the cylinder 8. The lower end surface of the roller 18 is supported by the auxiliary bearing 11, and the eccentric amount of the roller 18 with respect to the central axis of the rotating shaft 2 is the same as the eccentric amount of the eccentric crank portion 2a.
[0027]
The roller 18 is rotatably fitted to the circumferential surface of the eccentric crank portion 2a provided integrally with the rotary shaft 2. Therefore, when the eccentric crank portion 2a rotates eccentrically with the rotation of the rotating shaft 2, the roller 18 moves eccentrically, and a part of the outer peripheral surface of the roller 18 rolls in contact with the inner peripheral surface of the cylinder 8 along the axial direction. It has become.
[0028]
Further, a rotation restricting member 20 such as an Oldham mechanism is provided between the auxiliary bearing 11 and the lower end portion of the roller 18 to control the rotation of the roller 18 so as to make a revolving motion.
[0029]
On the peripheral surface of the roller 18, a spiral groove 23 having a gradually decreasing pitch is provided from the lower end to the upper end. A spiral blade 24 is fitted into the spiral groove 23 so as to freely protrude and retract, and the outer diameter surface of the blade 24 is in close contact with the inner peripheral surface of the cylinder 8.
[0030]
The roller 18 and the peripheral surface of the cylinder 8 are partitioned by a blade 24 into a plurality of continuous spaces. These space portions are called compression chambers 25. From the setting of the pitch of the spiral groove 23, the volume of each compression chamber 25 gradually increases from the upper compression chamber 25 to the lower compression chamber 25.
[0031]
The lowermost compression chamber 25 communicates with the suction pipe 7 and thus serves as a suction portion 25S. The uppermost compression chamber 25 communicates with the discharge port 12 provided in the main bearing member 10, and thus forms the discharge portion 25D.
[0032]
The end of the blade 24 facing the suction portion 25S and the discharge portion 25D is restricted from moving in a spiral direction by a blade stopper (not shown in FIG. 1) described later.
[0033]
The electric motor unit 4 is opposed to a rotor fitted to the rotary shaft 2 and a stator (both shown) facing the circumferential surface of the rotor via a narrow gap and fitted to the inner circumferential surface of the sealed case 1. Not).
[0034]
This is a helical blade type compressor configured as described above, and energizes the motor unit 4 to rotationally drive the rotary shaft 2. The rotational force of the rotary shaft 2 is transmitted to the roller 18 via the eccentric crank portion 2a.
[0035]
Since the rotation restricting member 20 restricts the rotation of the roller 18, the roller 18 performs a revolving motion. As the roller 18 revolves, the rolling contact position with respect to the cylinder 8 gradually moves in the circumferential direction. The blade 24 protrudes and retracts in the radial direction of the roller 18 while entering and exiting the spiral groove 23.
[0036]
Through these series of operations, low-pressure refrigerant gas is sucked from the evaporator through the suction refrigerant pipe 7 into the suction portion 25S which is the lowermost compression chamber 25. As the roller 14 revolves, it is sequentially transferred to the upper compression chamber 25.
[0037]
Since the volume of each compression chamber 25 is sequentially reduced from the lower side, which is the suction portion 25S, to the upper side, which is the discharge portion 25D, the refrigerant gas is compressed while being sequentially transferred through the compression chambers 25. In the uppermost compression chamber 25, the pressure is increased to a predetermined pressure.
[0038]
The high-pressure gas in the compression chamber 25 in the discharge unit 25D is once discharged into the sealed case 1 from the discharge port 12, and after being filled there, it is led to the condenser via the discharge refrigerant pipe, and a known refrigeration cycle action is performed. Done.
[0039]
FIG. 2 shows a first embodiment relating to the relationship between the blade 24 and the blade stopper 30 .
The blade stopper 30 has a base end embedded in the cylinder 8 and one end protruding into the compression chamber 25. One side surface 30a of the protruding portion of the blade stopper 30 serves as an actual stop surface for the blade 24, and restricts the movement of the blade 24 in the spiral direction.
[0040]
At least the surface direction of the blade stopper surface 30a of the blade stopper 30 and its extension line La are the center line of the cylinder 8 (line connecting the center o of the cylinder 8 and the tip of the stopper surface 30a of the blade stopper 30) Ls. It is inclined with respect to.
[0041]
In other words, in a cross section perpendicular to the axis o of the cylinder 8, the blade stop surface 30 a of the blade 30 is attached so as to face outward from a direction parallel to the radial direction of the cylinder 8.
[0042]
On the other hand, the end surface 24a of the blade 24 is formed along the center line Ls of the cylinder 8 and is not different from the conventional one. In other words, in a cross section perpendicular to the axis o of the cylinder 8, the direction is parallel to the radial direction of the cylinder 8.
[0043]
Since the blade 24 does not attempt to move in the spiral direction as shown in the figure during the stop, a triangular space 31 is formed between the blade stop surface 30 a of the blade stopper 30 and the end surface 24 a of the blade 24.
[0044]
When the compression operation is started, the blade 24 is pushed toward the suction portion 25S from the differential pressure between the discharge pressure and the suction pressure, or the blade 24 moves along the spiral direction with the movement of the roller 18 during compression. Due to factors such as being pushed toward the discharge unit 24D, force is applied in the spiral direction, which is the length direction of the blade 24, and the blade 24 tends to move in that direction.
[0045]
However, since the blade stopper 30 protrudes in the moving direction of the blade 24, the blade end surface 24a is stopped by the stopping surface 30a of the blade stopper 30, and the movement of the blade 24 in the spiral direction is restricted.
[0046]
In this state, since the blade 24 has a certain degree of flexibility, the blade 24 is deformed so that the end surface of the blade 24 advances through the triangular space portion 31 to fill it, and is in close contact with the stop surface 30 a of the blade stopper 30.
[0047]
From the shape and surface direction of the blade stop surface 30 a of the blade stopper 30, particularly at the end of the blade 25, the peripheral surface bulges toward the outer diameter side so as to be in close contact with the inner peripheral surface of the cylinder 8.
[0048]
That is, the presence of the blade stopper 30 generates a force that presses the peripheral surface of the blade 24 against the inner peripheral surface 8 a of the cylinder 8, and the blade 24 is stably and reliably pressed against the cylinder 8.
[0049]
Among the sealing surfaces of the compression chamber 25, the sealing performance on the surface constituted by the cylinder 8 and the blade 24 is improved, and a compression operation with high volumetric efficiency is performed. Naturally, there is no idling when starting up, and high performance is obtained.
[0050]
FIG. 3 shows a second embodiment relating to the relationship between the blade 24 and the blade stopper 30 . In addition, about the same component as the said embodiment, the same number is attached | subjected and new description is abbreviate | omitted. (same as below)
The blade stopper 30 previously described in the first embodiment has substantially the same width dimension as a whole and is mounted so as to be inclined with respect to the center line Ls of the cylinder 8. The stopper 30 </ b> A is attached along the center line Ls of the cylinder 8 as a whole.
[0051]
Only the surface direction of the blade stop surface 30a facing the blade end surface 24a of the blade stopper 30A and its extension line La are formed to be inclined with respect to the center line Ls of the cylinder 8.
[0052]
Since the blade end surface 24 a is formed along the center line Ls of the cylinder 8, a triangular space 31 is formed between the blade stopper 30 and the blade stop surface 30 a. As a result, the embodiment is the same as the embodiment described above, and thus the same operational effects are obtained.
[0053]
FIG. 4 shows a third embodiment relating to the relationship between the blade 24 and the blade stopper 30 .
The blade stopper 30A is the same as that described above with reference to FIG. Here, the shape of the end surface 24b of the blade 24 that is stopped by the blade stopper 30A is substantially aligned with the blade stopping surface 30a of the blade stopper 30A.
[0054]
That is, the blade end surface 24b and its extension line Lb are formed so as to be inclined with respect to the center line Ls of the cylinder 8, like the blade stop surface 30a and its extension line La. In other words, in the cross section perpendicular to the axis o of the cylinder 8, the blade end surface 24 b faces outward from the direction parallel to the radial direction of the cylinder 8.
[0055]
From the above configuration, the contact area between the blade end surface 24b and the blade stopper surface 30a of the blade stopper 30A is increased. Therefore, the surface pressure on this surface is reduced as compared with the configuration of the embodiment of claim 1 and wear is less likely to occur, the sealing performance against the compression chamber 25 is improved, and the compression operation with high volumetric efficiency is performed. In addition, reliability is further improved.
[0056]
FIG. 5 shows a fourth embodiment relating to the relationship between the blade 24 and the blade stopper 30 .
For example, a coil spring 35, which is a tensile elastic body, is interposed between at least one end portion of both ends of the blade 24 and the cylinder 8. The coil spring 35 is a tension spring, one end of which is attached and fixed to a fixing member 36 provided in the cylinder 8, and the other end is hooked on a latching pin 37 protruding from the blade end surface 24a.
[0057]
The end of the blade 24 is pulled toward the cylinder 8 by a coil spring 35. The coil spring 35 is a source of force for pressing the peripheral surface of the blade 24 against the inner peripheral surface 8a of the cylinder, and the blade 24 is pressed against the cylinder 8 stably and reliably.
[0058]
Therefore, among the sealing surfaces of the compression chamber 25, the sealing performance on the surface formed by the cylinder 8 and the blade 24 is improved, and a compression operation with high volumetric efficiency is performed. Naturally, there is no idling when starting up, and high performance is obtained.
[0059]
FIG. 6 shows a modification related to the relationship between the blade 24 and the blade stopper 30 .
A concave groove 23a is provided in the bottom surface portion of the spiral groove 23 of the roller 18 facing at least one of the two ends of the blade 24, and a pressing elastic body is provided between the concave groove 23a and the blade 24. For example, a coil spring 40 is interposed.
[0060]
Here, the coil spring 40 is a compression spring, one end of which is inserted into the concave groove 23a of the roller spiral groove 23, and the other end protrudes from the concave groove 23a and comes into contact with the end face of the blade 24. .
[0061]
The blade 24 end portion is pressed and urged toward the cylinder 8 by the coil spring 40, and the blade 24 peripheral surface is elastically pressed against the cylinder inner peripheral surface 8a. The coil spring 40 is a source of force that presses the peripheral surface of the blade 24 against the cylinder inner peripheral surface 8a, and presses the blade 24 against the cylinder 8 stably and reliably.
[0062]
Therefore, among the sealing surfaces of the compression chamber 25, the sealing performance on the surface formed by the cylinder 8 and the blade 24 is improved, and a compression operation with high volumetric efficiency is performed. Naturally, there is no idling when starting up, and high performance is obtained.
[0063]
FIG. 7 shows still another modified example related to the relationship between the blade 24 and the blade stopper 30 .
A concave groove 24c is provided from the bottom surface side in the vicinity of at least one end portion of both ends of the blade 24, and is a pressing elastic body between the blade concave groove 24c and the bottom surface of the roller spiral groove 23, for example, a coil spring 40A. Is installed.
[0064]
Here, the coil spring 40A is a compression spring, and elastically presses the circumferential surface of the blade 24 toward the cylinder inner circumferential surface 8a. Therefore, the blade 24 is stably and surely pressed against the cylinder 8, and the same effect as the embodiment described above can be obtained.
[0065]
The pressing elastic bodies 40 and 40A are provided in the first winding on the suction portion 25S side or the first winding on the discharge portion 25D side, so that the pressing force of the blade 24 on the inner peripheral surface of the cylinder 8 is weak. The above-described effects can be obtained by minimizing the increase in the number of parts.
[0066]
Instead of the coil springs 35, 40, and 40A constituting the tensile elastic body and the pressing elastic body described in FIGS. 5 to 7, for example, a leaf spring may be used to perform the same function, or another elastic member may be used. It may be used.
[0067]
FIG. 8 shows still another modification relating to the relationship between the blade 24 and the blade stopper 30 .
A hole 38 having an elliptical cross section is provided in at least one end of both ends of the blade 24, and a core material 45 as a resistor is inserted therein. The blade 24 is made of, for example, a fluorine-based resin material, whereas the core material 45 is selected from a highly rigid material such as a metal material.
[0068]
When a spiral radial force is applied to the blade 24, the core member 45 resists at the end of the blade 24, and is less likely to be deformed in the spiral radial direction compared to a portion where no other core member is inserted. Become.
[0069]
In other words, during operation, the end portion of the blade 24 into which the core member 45 is inserted is particularly difficult to be separated from the cylinder inner peripheral surface 8a, and the blade 24 is pressed against the cylinder 8 stably and reliably.
[0070]
Therefore, among the sealing surfaces of the compression chamber 25, the sealing performance on the surface formed by the cylinder 8 and the blade 24 is improved, and a compression operation with high volumetric efficiency is performed. Naturally, there is no idling when starting up, and high performance is obtained.
[0071]
FIG. 9 shows still another modification relating to the relationship between the blade 24 and the blade stopper 30 .
A groove portion 39 having a substantially U-shaped cross section is provided on a side surface facing at least one end portion of both ends of the blade 24 and the bottom surface of the roller spiral groove 23, and a core member 45A as a resistor is provided here. Inserted. The blade 24 is made of a fluorine resin material, and the core material 45A is made of a highly rigid material such as a metal material.
[0072]
When a spiral radial force is applied to the blade 24, the core member 45A resists at the end of the blade 24, and is less likely to deform in the spiral radial direction compared to a portion where no other core member is inserted. Become.
[0073]
In other words, during operation, particularly the end of the blade 24 into which the core member 45 is inserted is difficult to be separated from the cylinder inner peripheral surface 8a, and the blade 24 is stably and reliably pressed against the cylinder 8 to perform the above-described operation. The same effect as that of the embodiment is obtained.
[0074]
In addition, by providing the core members 45 and 45A, which are the resistors, in the first winding on the suction portion 25S side or the first winding on the discharge portion 25D side, the pressing force of the blade 24 against the cylinder inner peripheral surface 8a is increased. The above-described effects can be obtained by minimizing the increase in the number of parts.
[0075]
FIG. 10 shows still another modified example related to the relationship between the blade 24 and the blade stopper 30 .
A low pressure introduction part 50 formed of a concave groove is provided along the cylinder 8 side peripheral surface of the blade 24. The low-pressure introduction part 50 is in communication with the suction part 25S or the suction refrigerant pipe 7 through appropriate means, and is at the same pressure as the suction pressure or lower than that.
[0076]
In this state, the upper and lower compression chambers 25a and 25b with the blade 24 as a boundary are the pressure Phigh in the high-pressure side compression chamber 25a and the pressure Plow in the low-pressure side compression chamber 25b, respectively. It is not less than the suction pressure Ps.
[0077]
That is, Phigh ≧ Plow ≧ Ps, and during the compression operation, the blade 24 receives a force that is pressed toward the cylinder inner peripheral surface 8a due to a pressure difference. The blade 24 becomes difficult to move away from the cylinder 8, and the blade 24 is pressed against the cylinder 8 stably and reliably.
[0078]
Therefore, among the sealing surfaces of the compression chamber 25, the sealing performance on the surface formed by the cylinder 8 and the blade 24 is improved, and a compression operation with high volumetric efficiency is performed. Naturally, there is no idling when starting up, and high performance is obtained.
[0079]
In each of the above-described embodiments, the description has been made by applying to the helical blade type compressor in which the rotor 18 performs the revolving motion in the fixed cylinder 8, but the present invention is not limited to this and is connected to the drive source. The present invention may be applied to a helical blade type compressor (for example, disclosed in Japanese Patent Publication No. 7-107391) of a type in which a rotor piston is eccentrically arranged in a cylinder that is driven to rotate.
[0080]
【The invention's effect】
As described above, according to the present invention, it is possible to improve the pressing state of the blade against the inner circumferential surface of the cylinder so as to securely seal the compression chamber, thereby improving the volume efficiency.
[Brief description of the drawings]
FIG. 1 is a sectional view of a helical blade compressor that is a fluid compressor according to an embodiment of the present invention.
FIG. 2 is a diagram showing a first embodiment relating to a relationship between a blade and a blade stopper.
FIG. 3 is a diagram showing a second embodiment relating to a relationship between a blade and a blade stopper.
FIG. 4 is a diagram showing a third embodiment relating to a relationship between a blade and a blade stopper.
FIG. 5 is a diagram showing a fourth embodiment relating to a relationship between a blade and a blade stopper.
FIG. 6 is a view showing a modified example related to the relationship between a blade and a blade stopper.
FIG. 7 is a view showing still another modified example related to the relationship between the blade and the blade stopper.
FIG. 8 is a view showing still another modified example related to the relationship between the blade and the blade stopper.
FIG. 9 is a view showing still another modified example related to the relationship between the blade and the blade stopper.
FIG. 10 is a view showing still another modified example related to the relationship between the blade and the blade stopper.
FIG. 11 is a diagram showing a relationship between a conventional blade and a blade stopper.
FIG. 12 is a diagram for explaining the configuration of the blade and the sealing configuration of the compression chamber by the blade.
[Explanation of symbols]
8 ... Cylinder, 18 ... Roller, 23 ... Spiral groove, 25 ... Compression chamber, 24 ... Blade, 30 ... Blade stopper, 35 ... Tensile elastic body (coil spring), 40, 40A ... Press elastic body (coil spring), 45, 45A ... resistor (core material), 50 ... low pressure introduction part.

Claims (3)

A cylindrical cylinder, a roller arranged eccentrically in the cylinder, a spiral groove provided on the outer peripheral surface of the roller at a gradually smaller pitch from one end to the other end, and the spiral groove entering and exiting A blade that is freely fitted and forms a plurality of compression chambers between the cylinder and the roller, and is provided at a portion facing the end surface of the blade, and the blade end surface is abutted to restrict movement of the blade in the spiral direction. A blade stopper
The blade stopper surface of the blade stopper is formed so that the surface direction is inclined with respect to the center line of the cylinder, and the blade peripheral surface is urged so that the blade peripheral surface is in close contact with the cylinder inner peripheral surface with the blade end surface stopped. A fluid compressor characterized by:   The fluid compressor according to claim 1, wherein the blade end surface is formed so that a surface direction thereof is inclined with respect to a center line of the cylinder so as to be along a blade stopping surface of the blade stopper. A cylindrical cylinder, a roller arranged eccentrically in the cylinder, a spiral groove provided on the outer peripheral surface of the roller at a gradually smaller pitch from one end to the other end, and the spiral groove entering and exiting A blade that is freely fitted and forms a plurality of compression chambers between the cylinder and the roller, and is interposed between the blade end and the cylinder so that the blade peripheral surface is in close contact with the cylinder inner peripheral surface. A tensile elastic body that elastically pulls and biases;
A fluid compressor characterized by comprising:

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