JPH0219682A - Fluid compressor - Google Patents

Abstract

PURPOSE:To improve sealing performance and compression efficiency and to facilitate manufacture and assembly of parts by performing compression while transferring fluid supplied from the suction side of a cylinder into a working chamber through relative rotation of the cylinder and a rotary body sequentially into a delivery working chamber. CONSTITUTION:A compression element 4 functions to suck refrigerant gas through a suction tube 17 and a suction hole 16 into a cylinder 7. The sucked gas is confined in a crescent working chamber 15 arranged between the blades 14 thence it is transferred sequentially into a delivery working chamber 15 as a piston 11 rotates. The transferred compressed refrigerant gas is then delivered through the delivery hole 18 of a bearing 9 into the space of an enclosed case 2 thence it is returned through a delivery tube 19 to the refrigeration cycle. Working chambers 15... partitioned by the blades 14 decrease their volume gradually toward the delivery. Consequently, the refrigerant gas can be compressed when it is transferred from the suction side to the delivery side. Furthermore, since the refrigerant gas is transferred and compressed while being confined in the working chamber 15, the refrigerant gas can be compressed efficiently even when no delivery valve is provided.

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 drive section such as a crankshaft that transmits one rotational force to the compressor section, and the structure of the compression section are complicated, and there are many five parts. 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.

A screw pump is also 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 rotating the 1-rotator, the fluid trapped between two adjacent windings of the blade between the outer peripheral surface of the 9-rotator and the inner peripheral 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 complex structure and a large number of nine parts. moreover.

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. Further, a screw pump of the type in which a rotating body wrapped with a spiral blade is placed inside a sleeve simply transports fluid and does not have a compression effect.

It is an object of the present invention 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 a single part.

[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 end side and a discharge end side,
A spiral groove is provided on the inner circumference of the cylinder and is formed at a pitch that gradually decreases from the suction end side to the discharge end side of the cylinder. , a cylindrical rotating body that is rotatable relative to the cylinder while a part of the rotating body is in contact with the inner circumferential surface of the cylinder, and the groove.

It is fitted in and out of the cylinder approximately in the radial direction and has an inner circumferential surface that closely contacts the outer circumferential surface of the rotating body, and the space between the inner circumferential surface of the cylinder and the outer circumferential surface of the rotating body is A spiral blade defining a working chamber, the cylinder, and the rotating body are rotated relative to each other, and fluid flowing into the working chamber from the suction end side of the cylinder is sequentially transferred to the working chamber on the discharge side of the cylinder. The invention also includes a driving means.

By doing this, the present invention enables miniaturization and high performance with a simple configuration, improves sealing performance, enables efficient compression, and facilitates manufacturing and assembly of one part. It's because I did it.

(Example) An embodiment of the present invention will be described below based on 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 includes 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, a spiral groove 10 extending between both ends of the cylinder 7 is formed on the inner circumferential surface of the cylinder 7 . and,
The pitch of this spiral groove 10 is:

It is formed gradually smaller from the right side to the left side in both figures, that is, from the suction side to the discharge side of the cylinder 7.

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.
1 are arranged along the axial direction of the cylinder 7. This piston 11 is arranged such that its center axis A is offset from the center axis B of the cylinder 7 by a distance e, and a portion of the outer circumferential surface of the piston 11 is in contact with the inner circumferential surface of the cylinder 7 .

Both ends of the piston 11 are rotatably supported by the bearings 8 and 9, respectively. Further, as shown in FIGS. 1 and 3, an engagement groove 12 is formed on the outer periphery of one end of the piston 7. A drive pin 13 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 to rotate the cylinder 7 together with the rotor 6, the rotational force of the cylinder 7 is transmitted to the piston 11 via the drive pin 13. Then, the piston 11 internally rotates within the cylinder 7 with its negative portion contacting the inner surface of the cylinder 7.

Further, a spiral blade 14 shown in FIG. 2 is fitted into the groove 10. The thickness t of this blade 14 almost matches the width of the spiral groove 10,
Each part of the blade 14 can move forward and backward with respect to the groove 10 along the radial direction of the cylinder 7. Also, blade 1
4 is fitted into a spiral groove 10 provided in the cylinder 7 and is wound around the outer periphery of the piston 11. The inner peripheral surface of the blade 14 is connected to the piston 11.
The piston 11 slides on the inner circumferential surface of the piston 11 while being in airtight contact with the outer circumferential surface of the piston 11. The blade 14 is made of an elastic material such as Teflon, and is screwed into the helical groove 10 by utilizing its elasticity.

The space between the inner peripheral surface of the cylinder 7 and the outer peripheral surface of the piston 11 is partitioned into a plurality of working chambers 15 by the blade 14. In other words.

Each working chamber 15 is formed between two adjacent windings of the blade 14, and has a substantially crescent shape extending along the blade 14 from one contact point between the piston 11 and the inner peripheral surface of the cylinder 7 to the next contact point. I am doing it.

The volume of the working chambers 15 gradually decreases from the suction side to the discharge side of the cylinder 7.

Further, as shown in FIG. 1, a bearing 8 located on the suction side of the cylinder 7 has a suction hole 1 extending in the axial direction of the cylinder 7.
6 is passing through. One end of this suction hole 16 opens into the cylinder 7, and a suction tube 17 of a refrigeration cycle is connected to the other end. Further, the other bearing 9 has a discharge hole 18 formed therein. One end of this discharge hole 18 is open to the discharge end side in the cylinder 7, and the other end is opened to the inside of the sealed case 2.

Here, reference numeral 19 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 11 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 11 and the cylinder 7 is ensured by a regulating means consisting of the drive pin 13 and the engagement groove 12. The blade 14 also rotates in unison with the cylinder 7 (and piston 11).

Further, since the blade 14 rotates with its inner circumferential surface in contact with the outer circumferential surface of the piston 11, each part of the blade 14 becomes closer to the contact area between the outer circumferential surface of the piston 11 and the inner circumferential surface of the cylinder 7, The cylinder 7 is pushed into the groove 10 of the cylinder 7, and as it moves away from the contact portion, it moves in the direction of protruding from the groove 10 toward the center of the cylinder 7. On the other hand, when the compression element 4 is activated, refrigerant gas (not shown) is sucked into the cylinder 7 through the suction tube 17 and the suction hole 16. Then, the sucked refrigerant gas is
As shown in a) to (d), as the two pistons 11 rotate, they are sequentially transferred to the discharge side working chamber 15 while being confined in the crescent-shaped working chamber 15 between the windings of the blade 14. The transferred and compressed refrigerant gas is then discharged into the space of the sealed case 2 from a discharge hole 18 formed in the bearing 9 on the discharge side, and further returned to the refrigeration cycle through the discharge tube 19.

According to the compressor configured as above, the piston 11
The spiral grooves 10 are formed such that the pitch thereof gradually decreases from the suction side to the discharge side of the cylinder 7. In other words, the working chamber 15 partitioned by the blade 14 is formed so that its volume gradually decreases toward the discharge side. Therefore, while the refrigerant gas is transferred from the suction side to the discharge side of the cylinder 7, this refrigerant gas can be compressed. Further, since the refrigerant gas is transferred and compressed while being confined within the working chamber 15, the gas can be efficiently compressed even if no discharge valve is 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.

Further, a spiral groove 10 is provided on the inner surface of the cylinder 7, and the blade 14 moves in and out of this groove 10, thereby transferring and compressing the refrigerant gas.

In other words, if the eccentricity me between the cylinder 7 and the piston 11 is increased, the volume of the working chamber 15 can be increased, and the transfer capacity will be increased. By moving it in and out, a sufficient transfer capacity can be ensured even if the eccentricity e is made small. Therefore, the eccentricity me can be reduced.

The deformation stress generated in the blade 14 is small. As a result, the material of the blade 14 can be freely selected, thereby reducing the cost. Furthermore, since the deformation stress generated in the blade 14 is small, it is possible to set the eccentricity Qe to a large value 1, for example, 1/4 or more of the inner diameter of the cylinder 7. In other words.

The eccentricity me and the inner diameter of the cylinder 7 can be set freely,
High performance can be achieved by setting the eccentricity me as large as possible. Furthermore, if it is not necessary to increase the capacity so much, it is possible to further reduce the inner diameter of the cylinder 7 while ensuring sufficient capacity, thereby making it possible to downsize the compressor 1.

Further, since the spiral groove 10 is provided on the inner surface of the cylinder 7, the spiral groove 10 is located at a position far from the axis B of the cylinder 7 (and the axis A of the piston 11) in the radial direction. Therefore, the spiral groove 10 is larger than the cylinder 7.
The total volume of the helical groove 10 is larger than when the groove is located radially closer to the axis B of the piston 11 (and the axis A of the piston 11).

The transfer capacity of the compressor is determined by the initial pitch of the blades 14, that is, the working chamber 1 located on the suction end side of the cylinder 7.
Determined by the capacity of 5. According to this embodiment, the pitch of the blades 14 gradually decreases from the suction side to the discharge side of the cylinder 7. Therefore, according to this embodiment, the initial pitch of the blade 14 can be made larger than in the case where the piston 11 has the same number of windings and the same pitch over the entire length of the piston 11. This allows the transfer capacity of the compressor to be increased. In other words, it is possible to realize a highly efficient compressor.

Although the transfer capacity decreases, as the number of turns of the blade 14 increases, the pressure difference between adjacent working chambers decreases, the amount of gas leakage between one working chamber is reduced, and the compression efficiency improves; 7 and the piston 11 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.

Furthermore, the compressor of the present invention can be applied not only to refrigeration cycles but also to other compressors.

〔Effect of the invention〕

As explained above, the present invention provides a cylindrical rotating body having a spiral groove on the inner periphery whose pitch gradually changes from one end to the other, and a spiral blade that can freely move in and out of the groove. The blades are arranged eccentrically in a fitted cylinder, and the space between the inner circumferential surface of the cylinder and the outer circumferential surface of the rotating body is divided into a plurality of working chambers, and the cylinder and the rotating body are arranged relative to each other. By rotating the cylinder, the fluid flowing into the working chamber from the suction end side of the cylinder is compressed while being sequentially transferred to the working chamber on the discharge side of the cylinder.

Therefore, the present invention has the following effects: it can be made smaller and have higher performance due to its simple structure, it can improve sealing performance, it can be compressed efficiently, and it can easily manufacture and assemble one part.

[Brief explanation of the drawing]

Figures 1 to 4 show one embodiment of the present invention.
The figure is a longitudinal side view showing the entire fluid compressor, Figure 2 is a side view of the blades, Figure 3 is a side view with a partially cutaway view of the compression element, and Figures 4(a) to 4(d). ) are partially longitudinal side views showing the compression process of refrigerant gas. 2... Sealed case, 3... Electric element, 7... Cylinder. 10...Spiral groove, 11...Piston, 14...
・Blade, 15... Working chamber. Applicant's agent Patent attorney Takehiko Suzue

Claims (1)

[Claims] A sealed case, a cylinder provided in the sealed case and having a suction end side and a discharge end side, and a cylinder provided on the inner periphery of the cylinder, formed at a pitch that gradually decreases from the suction end side to the discharge end side of the cylinder. a spiral groove arranged eccentrically in the cylinder along the axial direction of the cylinder, and rotatable relative to the cylinder with a part of the groove in contact with the inner circumferential surface of the cylinder. a cylindrical rotating body; and an inner circumferential surface that is fitted into the groove in a substantially radial direction of the cylinder so as to be able to come in and out, and that is in close contact with the outer circumferential surface of the rotating body; a spiral blade that divides a space between the cylinder and the rotating body into a plurality of working chambers;
1. A fluid compressor comprising driving means for sequentially transferring fluid flowing into the working chamber from the suction end side of the cylinder to the working chamber on the discharge side of the cylinder.