JPH0219684A - Fluid compressor - Google Patents

Abstract

PURPOSE:To improve the capacity and the reliability by fitting spiral blades into two spiral grooves made in a rotary body while inclining in the opposite directions and partitioning the section between the inner circumferential face of a cylinder and the outer circumferential face of the rotary body with the blade into a plurality of working chambers. CONSTITUTION:In a compressor 1, two spiral blades 15, 16 are wound around a piston 10 while inclining in the opposite directions and refrigerant gas is sucked from the opposite sides of the piston 10 into a cylinder 7. The refrigerant gas is then carried to the intermediate section of the piston 10 while being compressed and delivered into an enclosed case 2. Since the refrigerant gas is sucked from two directions, carrying capacity can be increased without enlarging the pitch of the grooves 13, 14 and the size of the cylinder 7 and the piston 10. By such arrangement, the efficiency can be improved without causing excessive stress in the blades 13, 14 and a high capacity compressor can be obtained. Furthermore, suction efficiency is improved because the suction ports are provided at two points.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Field of Industrial Application) The present invention relates to a fluid compressor for compressing refrigerant gas, for example, in a refrigeration cycle.

(Prior Art) Various types of compressors have been known, such as a reciprocating type and a rotary type. but.

In these compressors, the structure of the drive section such as a crankshaft that transmits one rotational force to the compressor section and the compression section is complicated, and the number of parts is large. Furthermore, in order to improve compression efficiency in such conventional compressors, it is necessary to install a check valve on the discharge side, but since the pressure difference on both sides of this check valve is very large, Gas easily leaks and compression efficiency is low. In order to solve these problems, it is necessary to improve the dimensional accuracy and assembly accuracy of each component, which increases manufacturing costs.

Further, a screw pump is disclosed in US Pat. No. 2,401,189. According to this pump,
A cylindrical rotating body is disposed within the sleeve, and a spiral groove is formed on the outer peripheral surface of the rotating body. Further, a spiral blade is slidably fitted into this groove. By driving the one rotating body to rotate, the fluid trapped between two adjacent windings of the blade between the outer circumferential surface of the one rotating body and the inner circumferential surface of the sleeve is transferred from one end of the sleeve to the other end. do. In other words, the screw pump described above only transfers fluid from one end to the other, and does not have the function of compressing fluid.

(Problems to be Solved by the Invention) As described above, the conventional fluid compressor has a complicated structure and has a large number of eight parts. Furthermore, gas sometimes leaked from the check valve provided at the boundary between the high pressure side and the low pressure side, resulting in low compression efficiency. Furthermore, a type of screw pump in which a rotary body wrapped with a spiral blade was placed inside a sleeve transferred fluid to the ili, and did not have a compression effect.

SUMMARY OF THE INVENTION An object of the present invention is to provide a fluid compressor that has a relatively simple structure, improves sealing performance, can perform efficient compression, and is easy to manufacture and assemble as two parts.

[Structure of the invention]

(Means and operations for solving the problems) In order to achieve the above object, the present invention includes a sealed case, a cylinder provided in the sealed case and having a suction side and a discharge side, and a cylinder disposed in the cylinder. It is arranged eccentrically along the axial direction.

a cylindrical rotating body that is rotatable relative to the cylinder with a part of the rotating body in contact with the inner circumferential surface of the cylinder; Two spiral grooves are formed from both ends of the rotating body to the middle part, and the grooves are fitted into the two grooves so as to be able to move in and out in the approximate radial direction of the rotating body, and are tightly attached to the inner circumferential surface of the cylinder. two spiral blades having an outer circumferential surface and dividing a space between the inner circumferential surface of the cylinder and the outer circumferential surface of the rotating body into a plurality of working chambers, and relatively rotating the cylinder and the rotating body; The present invention further includes a driving means for sequentially transferring fluid flowing into the working chamber from the suction side of the cylinder to the working chamber on the discharge side of the cylinder.

By doing so, the present invention can achieve high performance and reliability with a simple configuration.

The purpose is to improve sealing performance, enable efficient compression, and facilitate the manufacture and assembly of one part.

(Example) An embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 shows an embodiment of the present invention.

FIG. 1 shows a hermetic compressor 1 for refrigerant gas used in a refrigeration cycle. The compressor 1 includes a closed case 2, and an electric element 3 and a compression element 4 as driving means arranged inside the closed case 2. The electric element 3 has a substantially annular stator 5 fixed to the inner surface of the sealed case 2 and an annular rotor 6 provided inside the stator 5.

Further, the compression element 4 has a cylinder 7, and the rotor 6 is coaxially fixed to the outer peripheral surface of the cylinder 7. Both ends of the cylinder 7 are rotatably supported by bearings 8 and 9 fixed to the inner surface of the sealed case 2, and both ends of the cylinder 7 are hermetically closed by the bearings 8.9.

Furthermore, inside the cylinder 7, a piston 1 is provided as a cylindrical rotating body having an outer diameter smaller than the inner diameter of the cylinder 7.
G is arranged along the axial direction of the cylinder 7. This piston 1o is arranged such that its center axis A is offset by a distance e from the center axis B of the cylinder 7, and a part of the outer circumferential surface of the piston 1o is in contact with the inner circumferential surface of the cylinder 7.

Both ends of the piston 10 are rotatably supported by the bearings 8 and 9, respectively. Further, as shown in FIG. 1, an engagement groove 1] is formed on the outer periphery of one end of the piston 7, and a drive pin protruding from the inner circumferential surface of the cylinder 7 is provided in the engagement groove 11. 12 is inserted along the radial direction of the cylinder 7 so as to be freely movable forward and backward. Therefore, when the electric element 3 is energized and the cylinder 7 is driven to rotate together with the rotor 6, the rotational force of the cylinder 7 is transmitted to the piston 10 via the drive pin 12. Then, the piston 10 internally rotates within the cylinder 7 with a portion of the piston 10 in contact with the inner surface of the cylinder 7.

Further, on the outer circumferential surface of the piston 10, two spiral grooves 13.1 are formed, each extending between both ends of the piston 10 and the intermediate portion thereof, and inclined approximately symmetrically in different directions.
4 is formed. The pitch of these grooves 13 and 14 gradually decreases from one end of the piston 10 to the middle part, that is, from the suction side to the discharge side of the cylinder 7, as shown in FIG. It is formed to be.

Further, spiral blades 15, 16, shown in longitudinal section in FIG. 1, are respectively fitted into the grooves 13, 14. The thickness of these blades 15.16 is approximately the same as the width of the grooves 13 and 1.4, and each part of the blades 15.16 has a diameter of the piston 10 with respect to both grooves 13.14. It can move forward and backward in any direction. Further, the outer circumferential surfaces of the blades 15 and 16 slide on the inner circumferential surface of the cylinder 7 while being in close contact with the inner circumferential surface of the cylinder 7.

These blades 15 and 16 are made of Teflon (trade name), for example.
It is formed of an elastic material such as, and is wound around the piston 10 by screwing into the grooves 13 and 14, respectively, using its elasticity.

The space between the inner peripheral surface of the cylinder 7 and the outer peripheral surface of the piston 10 is partitioned into a plurality of working chambers 17 by the blades 15, 16.

That is, each working chamber 17 is formed between two adjacent windings of each of the blades 15,16.

Piston 10 along each of play 1” 15.16
It has a nearly crescent shape extending from the contact point between the inner peripheral surface of the cylinder 7 and the inner peripheral surface of the cylinder 7 to the next contact point. And working chamber 17...
The volume gradually decreases from both ends of the cylinder 7 to the middle part, that is, from the suction side to the discharge side.

Further, as shown in FIG. 1, the bearings 8 and 9 located on the suction side of the cylinder 7 are respectively penetrated by suction holes 18 and 19 that extend substantially opposite to each other in the axial direction of the cylinder 7. One end of these suction holes 18 and 19 opens into the cylinder 7, and the other end is connected to suction tubes 20 and 21 of the refrigeration cycle.

Here, 22 in FIG. 1 is a discharge passage provided in the rotor 6, one end of which communicates with a discharge hole 23 provided in the cylinder 7, and the other end of this discharge passage 22 is It opens into the space between the stator 5 and the stator 5. The discharge hole 23 is provided at a position corresponding to the intermediate portion of the piston 10. Further, 24 in FIG. 1 is a discharge tube that communicates the inside and outside of the sealed case 2.

Next, the operation of the compressor configured as one or more will be explained.

First, when the electric element 3 is energized, the rotor 6 rotates, and the cylinder 7 also rotates together with the rotor 6. At the same time, the piston 10 is driven to rotate with a portion of its outer circumferential surface in contact with the inner circumferential surface of the cylinder 7. Such relative rotational movement between the piston 10 and the cylinder 7 is ensured by a regulating means consisting of the drive pin 12 and the engagement groove 11. The blade 14 also rotates integrally with the piston 10.

Further, the blades 15, 16 have their outer peripheral surfaces connected to the cylinder 7.
Because it rotates while in contact with the inner peripheral surface of.

Each part of the blades 15, 16 is pushed into the grooves 13, 14 as it approaches the contact area between the outer peripheral surface of the piston 10 and the inner peripheral surface of the cylinder 7.

Moreover, as it moves away from the contact portion, it moves in the direction of protruding from both grooves 1314. On the other hand, when the compression element 4 is activated, refrigerant gas (not shown) is sucked into both ends of the cylinder 7 through the suction tube 20.21 and the suction holes 18, 19. and.

The sucked refrigerant gas is confined in the crescent-shaped working chamber 17 between the windings of the two blades 15 and 16, and as the piston 10 rotates, it flows into the working chamber 17 on the intermediate side, that is, on the discharge side. Transferred sequentially. And piston 1
The compressed refrigerant gas is transferred from both ends of the cylinder 7 to the middle part and is discharged into the space of the sealed case 2 through the discharge hole 23 formed in the cylinder 7.
through the refrigeration cycle.

According to the compressor configured as above, the piston 10
The two spiral grooves 13 and 14 are formed such that the pitch thereof gradually decreases from one end of the cylinder 7 toward the middle portion. In other words, the working chamber 17 partitioned by two blades 15° 16...
* is formed so that the volume gradually decreases toward the discharge side. Therefore, the refrigerant gas can be compressed while being transferred from the suction side to the discharge side at both ends of the cylinder 7. In addition, the refrigerant gas is supplied to the working chamber 17.
Since the gas is transferred and compressed while being confined inside, the gas can be efficiently compressed even if a discharge valve is not provided on the discharge side of the compressor.

Furthermore, since the discharge valve can be omitted, the configuration of the compressor can be simplified and the number of parts can be reduced. Further, since the rotor 6 of the electric element 3 is supported by the cylinder 7 of the compression element 4, there is no need to provide a dedicated rotating shaft, bearing, etc. for supporting the rotor 6. Therefore, the configuration of the compressor can be further simplified and the number of parts can be reduced by two.

The compressor 1 also includes two spiral blades 15.
16 are wound around the piston 10 so as to be inclined in different directions, and refrigerant gas is sucked into the cylinder 7 from both ends of the piston 10. The refrigerant gas sucked into the cylinder 7 is compressed and transferred to the middle part of the piston 10, and the compressed high-pressure gas is discharged into the closed case 2. In other words, since the refrigerant gas is sucked in from two directions, a large amount of transfer can be achieved without increasing the pitch of the two grooves 13 and 14, and without increasing the size of the cylinder 7 and piston 10. therefore.

Efficiency can be improved without causing excessive deformation stress to both blades 13, 14, and a high-capacity compressor can be obtained. Also, since the suction ports are provided at two locations, the suction efficiency is good. Furthermore, since suction is performed from both ends of the cylinder 7, both ends of the cylinder 7 and the piston 10 are placed under the same pressure environment. That is, the forces between both ends of the cylinder 7 and the piston 10 are balanced, and generation of thrust force due to differential pressure can be prevented. Therefore, it is possible to increase the differential pressure between the suction side and the discharge side, and it is possible to reduce the input pressure of refrigerant gas.

Further, the cylinder 7 and the piston 10 are in contact with each other while being rotated in the same direction.

Therefore, the friction between these members is small and each can rotate smoothly, resulting in less vibration and noise.

Although the transfer capacity decreases, the pressure difference between adjacent working chambers decreases as the number of turns of the blades 15 and 16 increases.
The amount of gas leaking between working chambers is reduced and compression efficiency is improved.

In this embodiment, the two grooves 13 and 14 of the piston 10 are
The pitch of the piston 10 is gradually reduced from both ends to the middle part of the piston 10, but the present invention is not limited thereto. may be formed. That is, in the one shown in FIG. 3, the two helical grooves 13, 14 have equal pitches, and one end of each is substantially wedge-shaped in the middle of the piston 10. As shown by arrows C in FIG. 9, the refrigerant gas sucked in from both ends of the piston 10 is transferred to the middle part of the piston 10.

It is compressed in this intermediate portion and discharged.

Moreover, in the one shown in FIG. 4, two spiral grooves 13.
The pitches 14 are formed to gradually become smaller from the middle part to both ends of the piston 10. As shown by arrows D in FIG. 1, the refrigerant gas is transferred from the middle part of the piston 10 to both ends while being compressed, and is discharged in two directions.

Note that the compressor of the present invention is applicable not only to refrigeration cycles but also to other compressors.

〔Effect of the invention〕

As described above, the present invention has two spiral grooves on the outer periphery that are formed between both ends and the middle part and are inclined in different directions.

A cylindrical rotating body with spiral blades fitted into these two grooves so that they can move in and out is placed eccentrically within the cylinder, and the blades are used to create a space between the inner circumferential surface of the cylinder and the outer circumferential surface of the rotating body. The space is divided into a plurality of working chambers, the cylinder and the rotating body are rotated relative to each other, and the fluid flowing into the working chamber from the suction side of the cylinder is sequentially transferred and compressed to the working chamber on the discharge side of the cylinder. This is how it was done.

Therefore, the present invention has the effect of making it possible to increase performance and reliability with a simple configuration, improve sealing performance, enable efficient compression, and facilitate manufacture and assembly of nine parts.

[Brief explanation of the drawing]

1 and 2 show an embodiment of the present invention,
Fig. 1 is a longitudinal side view showing the entire fluid compressor, Fig. 2 is a side view schematically showing the grooves provided in the piston, and Figs. 3 and 4 respectively show modified examples of the spiral grooves. It is also a side view. 2... Sealed case, 3... Electric element, 7... Cylinder. 10... Piston, 13.14... Spiral groove. 15.1.6...Blade, 17...Working chamber. Applicant's representative Patent attorney Takehiko Suzue Figure 2 Figure 3 Figure 4

Claims (1)

[Claims] A sealed case, a cylinder provided in the sealed case and having a suction side and a discharge side, and arranged eccentrically within the cylinder along the axial direction of the cylinder, with a part of the cylinder in contact with the inner circumferential surface of the cylinder. a cylindrical rotating body that is rotatable relative to the cylinder in a state in which the rotating body is rotated;
Two spiral grooves are formed from both ends of the rotating body to the middle part, and a groove is fitted into the two grooves so as to be able to move in and out in the approximate radial direction of the rotating body, and is fitted into the inner circumferential surface of the cylinder. two spiral blades having outer circumferential surfaces in close contact with each other and dividing a space between the inner circumferential surface of the cylinder and the outer circumferential surface of the rotary body into a plurality of working chambers; and the cylinder and the rotary body. 1. A fluid compressor comprising driving means for relatively rotating the fluid compressor and sequentially transferring fluid flowing into the working chamber from the suction side of the cylinder to the working chamber on the discharge side of the cylinder.