JPH02264185A - fluid compressor - Google Patents

Abstract

PURPOSE:To prevent liquid compression or excessive compression and further to prevent the generation of starting failure so as to improve compression efficiency by providing a communicating hole for providing communication between the outer part of a cylinder and one compression chamber and a pressure control valve for the inflow fluid of the compression chamber in other one of a cylinder and a piston. CONSTITUTION:When GaS pressure in the second chamber 33b or the third chamber 33c of a compression chamber is increased to reach the operating values of valves 34, 35, the valves 34, 35 corresponding to the respective compression chambers 33b, 33c operate, to be elastically deformed so as to open communication holes 36, 37. The valves 34, 35 discharge the cooling medium gas of the corresponding compression chambers 33b, 33c to the outer outside of a cylinder 23 so as to lower gas pressure in the compression chambers 33b, 33c to a normal value. Since the pressure in the compression chambers 33b, 33c is thus kept at a value lower than a fixed value, liquid compression or excessive compression of the cooling medium gas can be prevented. And generation of starting failure can be reduced and the damage of a blade can be prevented. Since the excessive compression of the cooling medium gas can be prevented, compression efficiency can be improved, and pulsation of discharged pressure and noise can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Field of Industrial Application) The present invention relates to a fluid compressor that is provided in, for example, a refrigerator or an air conditioner and compresses refrigerant gas in a refrigeration cycle.

(Prior art) For example, a compressor as disclosed in Japanese Patent Application No. 170692/1983 filed by the same applicant]
It has been known. Zunawaji, this type of compressor] is
As shown in FIG.
This is to rotate a cylinder 6 fixed to. In the compressor 1, a piston 7 having an eccentric amount e with respect to the axis A of the cylinder 6 is supported inside the cylinder 6. Furthermore, a spiral groove 8 is formed on the outer periphery of the piston 7, and a flexible spiral blade 9 is fitted into this groove 8.

Furthermore, this compressor 1 is inside the cylinder 6.

1. It has a plurality of compression chambers 10 which are partitioned by the blades 9 and whose volumes are gradually smaller as they are located closer to the discharge side. Then, for example, refrigerant gas in a refrigeration cycle is sucked into the suction chamber 10a located on the suction end side of the cylinder 6, and the cylinder 6 and the piston 7 are rotated synchronously to compress the refrigerant gas while the refrigerant gas is compressed on the discharge end side of the cylinder 6. Transfer to. The transferred and compressed refrigerant gas is then returned to the refrigeration cycle.

(Problem to be solved by the invention) By the way, the type of compressor mentioned above.

Liquid compression may occur because the fluid is sealed in multiple adjacent compression chambers via the blade and compressed continuously, and in such cases, startup failure may occur or the blade may break. there were.

Further, even when only gas is sealed in the compression chamber, overcompression may reduce compression efficiency and may also increase pressure pulsation and noise.

It is an object of the present invention to prevent the occurrence of startup failures, blade breakage, etc. due to liquid compression.

An object of the present invention is to provide a fluid compressor that does not overcompress.

[Structure of the Invention] (Means and Effects for Solving the Problems) In order to achieve the object 1. A cylindrical piston is arranged along the axial direction and eccentrically, and is rotatable relative to the cylinder with a part of the piston in contact with the inner peripheral surface of the cylinder. The helical groove is formed at a pitch that gradually decreases from the radial direction toward the discharge end side, and the helical groove is flexible. a spiral blade having an outer circumferential surface that is in close contact with the cylinder;

Opening/closing a plurality of compression chambers lined up from the suction end side to the discharge end side of the cylinder, and a communication hole provided in at least one of the cylinder and the piston, which communicates at least one compression chamber with the outside of the cylinder. A pressure control valve that controls the pressure of the fluid flowing into the compression chamber, the cylinder and the piston are rotated relative to each other, and the fluid flowing into the cylinder is sequentially transferred from the suction end of the cylinder to the discharge end of the cylinder. The invention also includes a driving means.

By doing so, the present invention makes it possible to prevent startup failures, blade breakage, etc. due to liquid compression.

(Example) Below, two examples of the present invention will be described based on FIGS. 1 to 4. Components that are the same as those described in the prior art section are given the same numerals and their explanations will be omitted.

FIG. 1 shows a main part of an embodiment of the present invention. Reference numeral 21 in Fig. 1 indicates a compression mechanism section of a compressor used in the freezing cycle. and.

This compression mechanism section 21 has a piston 22 and a cylinder 23.

Since the piston 22 is formed into a cylindrical shape, it has cylindrical bearing support parts 24 and 25 having a smaller diameter than the piston 22 at both ends thereof.

The piston 22 extends one bearing support part 24 toward the side where the drive means 26 is present, and as shown by arrow C in FIG.
It is designed to be rotated integrally with the Here, B in Figure 1 indicates the piston 2] and both bearing support parts 24.
．． 25 axis.

Further, a spiral groove 27 is provided on the outer periphery of the piston 22. That is, this groove 27.

It is formed from one end side to the other end side of the piston 22, and its width is set to be substantially constant. In addition, 27
The depth direction is made to substantially coincide with the radial direction of the piston 2X-y. The pitch of the grooves 27 is set to gradually become smaller from one end of the piston 2 to the other end.

Further, a blade 28 is wound around the outer periphery of the piston 2v. The blade 28 is made of an elastic material such as synthetic resin and is formed into a spiral shape, and has flexibility. The blade 28 is attached to the piston 22 with its thickness being elastically deformed along substantially the same width as the groove 27 of the piston 2v.

On the other hand, the cylinder 23 is formed into a cylindrical shape having a substantially constant inner diameter, and both ends thereof are open. The piston 22 is inserted into the cylinder 23. The cylinder 23 has its axis A and the piston 2
A substantially constant eccentricity ffie is interposed between the shaft center B and the shaft center B of the shaft 2, which is substantially constant over the entire length in the axial direction. Furthermore, cylinder 2
3 has a part of its inner peripheral surface in contact with the outer peripheral surface of the piston 22. Further, the cylinder 23 presses the outer circumferential surface 28a of the blade 28 pushed into the cylinder 23 against its inner circumferential surface. Here, the cylinder 23 may be configured to rotate synchronously with the piston 22.

Also, in Fig. 8, 29.30 indicates a bearing.

The bearings 29, 30 pass through the bearing support portions 24, 25 and are hermetically fitted to both ends of the cylinder 23. One of the bearings 29 is disposed on the suction end side of the cylinder 23 and has a suction hole 31 extending substantially parallel to the axial direction.

Further, the other bearing 30 is disposed on the discharge end side of the cylinder 23 and has a discharge hole 32 extending substantially parallel to the axial direction.

Furthermore, inside the cylinder 23, there are four compression chambers 33a,
33b, 33c, and 33d are formed. The compression chambers 33a to 33d are connected to the outer peripheral surface of the piston 22 and the cylinder 2.
3, and are airtightly partitioned from each other by a blade 28. And compression chamber 3
3a to 33d have a crescent shape extending from one contact portion between the piston 22 and the cylinder 23 to the next contact portion.

These compression chambers 33a to 33d are the cylinder 23
The volume decreases from the suction chamber 33a located on the suction end side to the discharge chamber 33d located on the discharge end side.

In addition, the pressure control valve (hereinafter referred to as
(referred to as a valve). Both valves 34 and 35 have one end fixed to the outer peripheral surface of the cylinder 23, and their inner surfaces abut against the outer peripheral surface of the cylinder 23. The valves 34 and 35 can be elastically deformed with the joint portion with the cylinder 23 on the proximal end side.

Furthermore, the cylinder 23 is provided with communication holes 36 and 37. Both of the communication holes 36 and 37 are formed in the thickness direction of the cylinder 23, and one end thereof is open to the outer circumferential surface of the cylinder 23. The other end of one of the communication holes 36 opens to the second chamber 33b located next to the suction chamber 33a, and the other communication hole 37 opens to the second chamber 33b located next to the suction chamber 33a.
The other end side is open to the third chamber 33c located next to d.

That is, when the piston 22 is rotationally driven and refrigerant gas is sucked into the suction chamber 33a from the suction hole 31 as shown by the arrow, this refrigerant gas is transferred to the discharge chamber 33a side as the piston 22 rotates. Ru. The refrigerant gas is gradually compressed each time it moves to the compression chamber on the transfer side, and is discharged from the discharge chamber 33d to the outside of the cylinder 23 through the discharge hole 32, as shown by arrow E.

Further, when the gas pressure inside the second chamber 33b or the third chamber 33c increases and reaches the operating value of the valve 34.35, the valve 34.35 corresponding to each compression chamber 33b, 33c is operated.
It is elastically deformed to open the communicating holes 36 and 37. Then, the valves 34 and 35 release the refrigerant gas in the corresponding compression chambers 33b and 33c to the outside of the cylinder 23, and the compression chambers 33b and 33c
Reduce the gas pressure at 33c to a normal value.

And when the gas pressure drops to a normal value.

The valves 34 and 35 return due to their restoring force, and the communication hole 3637
Close. Here, the valves 34 and 35 may have respective operating values set to different values.

In such a configuration, the compression chamber 33b.

When the pressure of 33c reaches a certain value, overcompression of the valve 34 or the refrigerant gas can be prevented.

This can reduce the occurrence of startup failures and further prevent damage to the blade 28. Furthermore, since overcompression of the refrigerant gas can be prevented, compression efficiency can be improved and discharge pressure pulsations and noise can be reduced.

FIGS. 2 to 4 show main parts of a second embodiment of the present invention. 22 in Fig. 2 is a piston, and 22 is a piston.
3 is a cylinder. Of these, the piston 22 has a pressure outlet path 41.

That is, the pressure derivation path 41 extends toward the suction side along the axis B of the piston 22, and has one end thereof opened at the end surface of the discharge side bearing support portion 25.

The other end side is located at a portion before reaching the suction side bearing support portion 24. The pressure outlet path 41 is connected to the second
It communicates with the chamber 33b and the third chamber 33c.

Further, inside the pressure outlet path 41, a pressure control valve (hereinafter referred to as
(referred to as a valve) 44.45 is provided. This valve 44
．． The reference numeral 45 is a rectangular plate shaped body, as shown in FIG. 4, and is formed into a circular arc shape. Furthermore, valve 44.45
flat portions 46 and 47 (only one of which is shown) formed on one end side are fixed to the inner surface of the pressure outlet path 41, and the outer surface thereof is aligned with the inner surface of the pressure outlet path 41. The valves 44 and 45 can be elastically deformed using the joint with the piston 22 as a fulcrum.

In other words, the valves 44 and 45 are connected to the second chamber 33b or the third chamber 3.
When the gas pressure inside 3C reaches the operating value of valve 34.35, it is elastically deformed to open communication hole 42.43. and,
The refrigerant gas in the compression chambers 33b, 33c is released to the outside of the cylinder 23, and the gas pressure in the compression chambers 33b, 33c is reduced to a normal value.

Then, when the gas pressure drops to a normal value, valve 44.
45 returns due to its restoring force and closes the communicating holes 42 and 43. Here, the valves 42 and 43 may have respective operating values set to different values.

In such a configuration, the compression chamber 33b.

Since the pressure of 33c can be maintained at a value lower than a certain value, it is possible to prevent liquid compression or overcompression of refrigerant gas. In addition, the occurrence of startup failures can be reduced, and further damage to the blade 28 can be prevented. Furthermore, since overcompression of the refrigerant gas can be prevented, it is possible to improve compression efficiency and reduce discharge pressure pulsations and noise.

[Effects of the Invention] As explained above, the present invention provides a cylinder having a suction end side and a discharge end side, and at least one of a piston disposed within the cylinder and wound with a spiral blade. A communication hole is provided for communicating between the outside of the cylinder and at least one of the plurality of compression chambers partitioned by the blade and arranged along the axial direction of the cylinder, and the communication hole is opened and closed. A pressure control valve is provided to control the pressure of the fluid flowing into the compression chamber.

Therefore, the present invention has the effect of being able to prevent liquid compression and over-compression, prevent starting failures, and improve compression efficiency.

[Brief explanation of drawings]

FIG. 1 is a side sectional view showing the main parts of the first embodiment of the present invention;
2 to 4 show a second embodiment of the present invention,
FIG. 2 is a side sectional view showing the main parts. 3 is a sectional view of the piston taken along the line FF in FIG. 2, FIG. 4 is a perspective view of the pressure control valve, and FIG. 5 is a side sectional view of a conventional example. 22...Piston, 23...Cylinder, 26...
Drive means, 27...Spiral groove, 28...Blades 33a, 33b, 33c, 33d-=compression chamber, 34°3
5...Pressure control valve, 36.37...Communication hole.

Claims (1)

[Claims] A cylinder having a suction end side and a discharge end side, and a cylinder disposed eccentrically along the axial direction of the cylinder within this cylinder, with a part of the cylinder in contact with the inner circumferential surface of the cylinder, and relative to the cylinder. A rotatable cylindrical piston, a spiral groove provided on the outer periphery of the piston and formed at a pitch that gradually decreases from the suction end side to the discharge end side of the cylinder, and the flexible piston. a spiral blade that is fitted into the spiral groove in a substantially radial direction of the piston and has an outer peripheral surface that comes into close contact with the inner peripheral surface of the cylinder; a plurality of compression chambers formed between the outer peripheral surface of the piston and arranged along the axial direction of the cylinder from the suction end side to the discharge end side of the cylinder; and at least one of the cylinder and the piston. a pressure control valve that opens and closes a communication hole that communicates at least one compression chamber with the outside of the cylinder to control the pressure of fluid flowing into the compression chamber, and relatively rotates the cylinder and the piston. A fluid compressor comprising a drive means for sequentially transferring fluid flowing into the cylinder from the suction end of the cylinder to the discharge end of the cylinder.