JPH02201091A - Fluid compressor - Google Patents

Abstract

PURPOSE:To prevent swell of compressed fluid and enhance the efficiency of a fluid compressor, in which a rotor with a spiral blade fitted in a spiral groove formed at the periphery is fitted in a cylinder, by equipping the rotor at the periphery of its suction side end with a suction groove in such a way as across the spiral groove. CONSTITUTION:A stator 5 of an electromotive element 3 is fixed to the inner surface of an enclosed case 2, and a cylinder 7 is fitted on a rotor 6 arranged inside thereof, wherein the two ends are supported rotatably by bearings 8, 9. A piston 11 is fitted in this cylinder 7 as a rotating element eccentrically in an amount (e). This piston 11 is provided at its periphery with a spiral groove 19 reducing its pitch from the suction end side gradually toward the discharge end side, and a spiral blade 21 is fitted in this groove 19 in such a way that it can advance and retreat freely. Across the spiral groove 19 a suction groove 31 is formed at the periphery of that of the piston ends which is situated on the suction side, and through this suction groove 31 the compressed fluid can be introduced only to No.1 working chamber 22 formed on the suction end side.

Description

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

(Prior Art) Various types of compressors, such as reciprocating type and rotary type, have been known so far. However, in these compressors, the structure of the drive section such as a crankshaft that transmits rotational force to the compressor section and the compressor section is IQI, and the number of parts is large. Furthermore, in order to increase 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 inverse ratio valve is extremely 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, but this increases manufacturing costs.

On the other hand, the present applicant previously filed an application for a helical blade type compressor shown in FIG. 11 as a hermetic compressor that does not have the problems described in I:. Figure 11 shows the main parts of a conventional helical blade type fluid compressor, which consists of cylinder a,
If there is a rotating body that is arranged eccentrically (see Figure 12 shows the amount of eccentricity) inside this cylinder a and rotates (eccentric rotational movement) relative to the cylinder a, then the outer surface of the rotating body The blade d is inserted into a spiral groove C (see FIG. 12). The blade d slides in the groove C and moves in and out in the depth direction of the groove C as the rotating body rotates relative to the cylinder a.

Both ends of the cylinder a and the rotating body are bearings f and g.
l: fli1 is rotatably supported, and each bearing f, H is provided with an inlet port and a discharge port j, respectively. the above? 71jc has a pitch that gradually narrows from the suction port to the discharge port.

Due to the frictional force between the blade d moving in and out in the depth direction and the rotating body based on this pinch change, the pushing force of the blade d in the direction of the cylinder nose j at the suction end side becomes smaller, and therefore the blade d and the cylinder at the suction end side A gap is likely to occur between the Therefore, in order to solve such G , the blade end can be easily moved in and out on the suction end side.

In such a configuration, when the cylinder a and the rotating body are rotated relative to each other, cylinder a is moved from the suction port.
The fluid to be compressed, such as gas, sucked into the air E between the rotating body and the rotating body is compressed. In other words, the above space is moved toward the discharge port j side with the rotational movement of the rotating body relative to the cylinder a, but since the pitch of the space c gradually decreases, the space is partitioned by the blade d. -1- The volume of the space, that is, the working chamber of the number of stages, gradually decreases toward the discharge port j side. Therefore, the fluid to be compressed that has entered the l:2 space 181 is gradually compressed and finally discharged from the discharge port J.

In this compression operation, the fluid to be compressed is introduced into the first working chamber on the suction side through an introduction passage formed by the suction side end of the blade d, the cylinder a, and the rotating body. The working chamber at this time is formed by using the end portion of the blade d, whose pitch is narrowed by one turn or more at the suction side end, and which is indicated by the reference numeral d2. For this reason,
In this case, a situation occurs in which the volume of the working chamber g is smaller than that of the working chamber g where the electrodynamic k is 2 and 1, and there is a drawback that the sucked gas expands.

Therefore, there is a drawback that the input for compression increases.

(Problems to be Solved by the Invention) This invention was made based on the above circumstances, and its purpose is to prevent loss due to expansion of the compressed fluid in a helical blade system. The aim is to improve the fluid compressor, which can improve efficiency.

[Structure of the Invention] (Means for Solving the Problems) In order to achieve the above object, the present invention provides a structure in which the cylinder is arranged eccentrically within the cylinder and a part of the cylinder is in contact with the inner circumferential surface of the cylinder. A suction groove is provided on the outer periphery of the suction end side of a relatively rotatable cylindrical rotating body, and the suction groove crosses a spiral groove provided on the outer periphery of the rotating body and into which a spiral blade is fitted. is formed to be colder than the spiral groove, and of the working chambers formed between the cylinder and the rotating body partitioned by the blades, only the first working chamber on the suction end side is compressed. It is designed to introduce fluid.

(Function) In the fluid compressor of the present invention, since the suction groove provided on the outer surface of the end of the rotating body is deeper than the spiral groove, even when the blade is fully buried in the spiral groove, the blade The suction groove will not be blocked. Since the suction groove crosses the spiral, the first actuating current always maintains communication with the suction side through this suction groove.

In other words, a passage for introducing the compressed fluid into the first working chamber can be ensured at all times. Therefore, the substantial volume of the first working chamber communicating with the suction side can be ensured to be larger than the volumes of the second and subsequent working chambers, thereby preventing the sucked compressed fluid from expanding.

(Embodiment) An embodiment of the present invention will be described below with reference to FIGS. 1 to 10. FIG. 1 shows a hermetic compression 4111 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 two electric elements include 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.

As shown in FIGS. 1 and 2, 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 8.9 fixed to the inner surface of the sealed case 2, and both ends of the cylinder 7 are hermetically closed by these bearings 8.9. That is, the bearing 8.9 has boss portions 8a and 9a into which the end of the work cylinder 7 is rotatably fitted, and the bearing 8.9 has a larger diameter than the boss portions 8a and 9a and is fixed to the inner surface of the sealed case 2. base 8
b, 9b.

Inside the cylinder 7, a piston 11 as a cylindrical rotating body having an outer diameter smaller than the inner diameter of the cylinder 7 is disposed along the axial direction of the cylinder 7. The piston 11 is made of iron or other material, and its central axis A is eccentrically disposed downward in FIGS. 1 and 2 by a distance Me with respect to the central axis B of the cylinder 7, so that the piston A part of the outer circumferential surface of cylinder 11 is in line contact with the inner circumferential surface of cylinder 7 .

The piston 11 has a support shaft portion 1 at each end in the axial direction.
2a, 12b are provided, and these support shafts 12a, 12b
are the bearing holes 8C% formed in the above bearings 8 and 9, respectively.
It is rotatably inserted and supported by 9C.

No. 3.4 is attached to one support shaft portion 12a of the piston 11.
As shown in the figures, prismatic portions 13 having a square cross section are formed. As shown in FIG. 4, this prismatic portion 13 is provided with an Oldham ring 15 in which a rectangular long hole 14 is bored. In other words, the Oldham ring 1 is attached to the prismatic portion 13.
5 is slidably fitted along the longitudinal direction of the elongated hole 14. On the outer peripheral surface of the Oldham ring 15,
- One end of a pair of bins 16 is slidably inserted in the radial direction perpendicular to the longitudinal direction of the leg elongated hole 14, respectively. The other ends of these bottles 16 are fitted and fixed into fitting holes 17 bored in the peripheral wall of the cylinder 7.

Thereby, the piston 11 is coupled to the cylinder 7 so as to be eccentric with respect to the radial direction of the cylinder 7. Therefore, when the cylinder 7 and the rotor 6 are driven to rotate together by applying an electric current to the electric power source 3, the rotational force of the cylinder 7 is transmitted to the piston 11 via the Oldham ring 15. It has become. Note that the -1-2 fitting hole 17 is hermetically closed by the male member 18.

Then, the piston 11 internally rotates within the cylinder 7 with a portion of the piston 11 in contact with the inner surface of the cylinder 7.

A spiral groove 19 is formed on the outer peripheral surface of the piston 11 along the axial direction of the piston 11, as shown in FIGS. 1 and 2, respectively. The pitch of the grooves 19 is gradually reduced from the right side to the left side in these drawings, that is, from the suction end side to the discharge end side of the cylinder 7.

A spiral blade 21 is fitted into the groove 19. The blade 21 is made of synthetic resin or other material, and both ends thereof are provided in a plane substantially perpendicular to the axis of the piston 11. This end treatment makes it easy for the blade 21 to move in and out of the cylinder 19, and prevents a gap from forming between the blade 21 and the cylinder 7. Furthermore, the thickness dimension of the blade 21 is almost the same as the width dimension of the spiral shape 19, and each part of the blade 21 is? : The piston 11 can move forward and backward in substantially the radial direction with respect to P119. The outer peripheral surface of the blade 21 is in close contact with the inner peripheral surface of the cylinder 7,
In this state, it slides on the inner peripheral surface of the cylinder 7.

The space between the inner circumferential surface of the cylinder 7 and the outer circumferential surface of the piston 11 is formed by the blade 21 into a plurality of working chambers 22.
It is divided into That is, each working chamber 22 is formed between two adjacent windings of the blade 21, and extends along the blade 21 from the contact point between the piston 11 and the inner peripheral surface of the cylinder 7 to the next contact point. It is crescent-shaped.

The volume of the working chamber 22 gradually decreases from the suction side to the discharge side of the cylinder 7.

As shown in FIG. 1, one of the bearings 8 located on the suction end side of the cylinder 7 has a suction hole 23 passing through it in the axial direction. One end of this suction hole 23 communicates with the inside of the cylinder 7,
A suction tube 24 of a refrigeration cycle is connected to the other end. Further, the other bearing 9 located on the discharge end side of the cylinder 7 is provided with a discharge hole 25 as shown in FIG.

One end of the discharge hole 25 is communicated with the discharge end side of the cylinder 7, and the other end is opened into the inside of the sealed case 2.

” - The piston 11 has an oil introduction passage 2 as shown in Fig. 1.
6 is bored along its central axis A.

One end of this oil introduction path 26 communicates with the bottom of the spiral groove 19 on the discharge side, and the other end communicates with a through hole 27 bored in one of the bearings 8.
It is connected to one end of the. The other end of this through hole 27 is connected to the other end of an introduction pipe 28 whose one end is located at the bottom of the sealed case 2 . Lubricating oil 29 is placed at the bottom of the sealed case 2.
is stored. Therefore, if the pressure inside the sealed case 2 is one y7, the lubricating oil 29 will flow through the introduction pipe 28,
The oil is introduced into the space between the bottom of the groove 19 and the blade 21 through the through hole 27 and the oil introduction path 26 .

Furthermore, the outer circumferential surface of the end of the piston 11 located on the suction side has a spiral groove 19 as shown in FIGS. 1 to 3.
A suction groove 31 is cut across. This suction groove 3
1 is formed deeper than the spiral shape 19, and is formed, for example, along the axial direction of the piston 11, and one end thereof is open to the end of the large diameter H11a of the piston 11. Moreover, in this embodiment, since the Oldham ring 15 is disposed on the suction side, one end of the upper shim d faces the elongated hole 14 of this ring 15 (see FIGS. 1 and 4) and is the end of the large diameter portion 11a. It is open to the public.

Due to the positional relationship between the long hole 14 and one end of the suction groove 31, the long hole 14 is used as a passage for refrigerant gas, and the Oldham ring 15 is sucked into the refrigerant gas Jl! This reduces the occurrence of J-way resistance. Further, the other end side of the suction groove 31 is connected to the first working chamber 22 located on the suction end side of the cylinder 7.
It is open and connected only to the

By the suction groove 31 having the above structure, the suction tube 24
The refrigerant gas sucked into the cylinder 7 from the refrigerant gas is reliably introduced into the working chamber 22 at the upper 21st port through the suction groove 31 without interruption.

Further, as shown in FIG. 3, the suction groove 31 is provided at a position offset from the blade end 21a on the suction end side in the circumferential direction of the piston 11, thereby making the axial dimension of the first working chamber approximately maximum. The refrigerant gas is sucked in through the suction groove 31 arranged in the area where the refrigerant gas is formed, and the gas can be compressed more efficiently without being expanded.

Furthermore, as shown in FIG. 1, a discharge tube 32 is connected to the sealed case 2 to communicate the inside and outside thereof.

Next, the operation of the compressor configured as above 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.

When the cylinder 7 rotates, 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 . Note that, as shown by the arrow in FIG.
゛It is a circular direction. Such relative rotational movement (rotational eccentric movement) between the piston 1 and the cylinder 7 is prevented by the Oldham ring 15 provided on the prismatic portion 13 of the piston 11. It rotates integrally with the piston 11.

Since the blade 21 rotates with its outer peripheral surface in contact with the inner peripheral surface of the cylinder 7, each part of the blade 21 is
As it approaches the contact area between the outer circumferential surface of the piston 11 and the inner circumferential surface of the cylinder 7, it is pushed into the L groove 19, and as it moves away from the contact area, it moves in the direction of protruding from the groove 19.

Due to the operation of the compression element 4 as described above, the suction tube 2
4 and the suction hole 23 are sucked into the cylinder 7. This suction is performed continuously without interruption.

That is, since the suction groove 31 provided across the spiral groove 19 on the outer surface of the end of the piston 11 is deeper than the spiral groove 19, when the blade 21 is pushed in and buried in the groove 19 to the maximum, However, the suction groove 31 is not blocked by the blade 21. Therefore, the first working chamber 22 and the suction end side space (the space on the Oldham ring 15 side) can always maintain communication through the suction groove 31. That is, an introduction passage for refrigerant gas to the first working chamber 22 can be always ensured by the suction groove 31.

Therefore, each time the piston 11 makes one revolution in the cylinder 7 due to the relative rotational movement between the cylinder 7 and the piston 11, the blade end 21 at the suction side end of the blade 21
a is completely buried in the cylinder 19, and the entrance of the introduction passage formed by the blade 21, the cylinder 7, and the piston 11 is closed by the inner peripheral surface of the cylinder 7.
Refrigerant gas is always introduced into the first working chamber 22 on the suction side through the suction groove 31 .

Therefore, expansion of refrigerant gas during compression operation, which will be described later, can be prevented. In other words, the substantial volume of the first working chamber 22 that communicates with the suction side through the communication of the suction groove 31 can always be secured to be larger than the volumes of the second and subsequent working chambers 22. It can prevent expansion. Therefore, an increase in the input for compression can be suppressed, and the efficiency of the compressor can be improved.

As described above, the refrigerant gas sucked into the first working chamber 22 as shown in FIG. 5 is trapped there as the piston 11 rotates. As shown in the figure, they are sequentially transferred to the working chamber 22 on the discharge end side. The transferred and compressed refrigerant gas is then discharged into the space inside the sealed case 2 from the discharge hole 25 formed in the bearing 9 on the discharge end side, and is returned to the refrigeration cycle through the discharge tube 32.

Incidentally, the spiral groove 19 formed on the piston 11 is formed such that the pitch thereof gradually decreases from the suction end side to the discharge end side of the cylinder 7. In other words, the working chamber 22 partitioned by the blade 21 is formed so that its volume gradually decreases toward the discharge end side.

Therefore, while the refrigerant gas is transferred from the suction end side to the discharge end 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 22, the refrigerant gas can be efficiently compressed without providing a check valve on the discharge side of the compressor.

When the compressed refrigerant gas is discharged into the sealed case 2 and the pressure inside the sealed case 2 increases, the lubricating oil 29 stored inside is pressurized, and the lubricating oil 29 passes through the oil introduction path 26 and spirals. The blade 21 is introduced into the space between the bottom of the shaped groove 19 and the blade 21. Therefore, the blade 21 is always pressed in the direction in which it is pushed out by the force 19 due to hydraulic pressure, that is, toward the inner peripheral surface of the cylinder 7. therefore,
The outer circumferential surface of the blade 21 is always kept in close contact with the inner circumferential surface of the cylinder 7, which prevents gas from leaking between the working chambers 22.

Further, since the check valve can be omitted in this compressor as described above, 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 to one man-hour.

In addition, in this invention, the synchronous rotation means, such as the Oldham ring part which rotates the cylinder 7 and the piston 11 relatively, may be arrange|positioned not at the suction end side but at the discharge end side.

In this case, the passage resistance of the sucked compressed fluid can be further reduced.

[Effects of the Invention] As described above, the present invention provides a rotating body eccentrically and inscribed in a cylinder, and a spiral shape whose pitch gradually changes from one end to the other end is formed on the outer periphery of the rotating body. In addition to providing a groove, a spiral blade is fitted into this groove so as to be able to move in and out, and the space between the cylinder and the rotating body is divided into a plurality of working chambers by the blade, and the cylinder and the rotating body are separated into two pairs. In a helical blade type fluid compressor, the fluid to be compressed flowing into the working chamber from the suction end of the cylinder is compressed while being sequentially transferred to the working chamber at the discharge end of the cylinder. A groove is formed on the outer circumferential surface of the end of the piston located at Since the groove is provided, it is possible to prevent the fluid to be compressed from expanding, and therefore,
Efficiency can be improved.

[Brief explanation of the drawing]

FIGS. 1 to 10 show an embodiment of the present invention.
The figure is a longitudinal sectional view showing the entire fluid compressor, Figure 2 is an exploded view of the compression element, Figure 3 is a perspective view of the piston with a blade attached, and Figure 4 is the connection between the piston and cylinder using an Oldham ring. The sectional views, FIGS. 5 to 9 are explanatory diagrams sequentially showing the compression process of refrigerant gas, and FIG. 10 is a side view of the compression element. FIG. 11 is a sectional view of a compression element in a conventional helical blade type compressor, and FIG. 12 is a sectional view of a rotating body used in FIG. 3... Electric element (driving means), 7... Cylinder, 1
DESCRIPTION OF SYMBOLS 1...Piston (rotating body), 15...Oldham ring, 19...Groove, 21...Blade, 22...Working chamber, 31...Suction groove, e...Eccentric port. Applicant's agent Patent attorney Takehiko Kataura Figure 4 Figure Figure Figure Figure Figure Figure Figure

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 rotating body,
A spiral groove is provided on the outer periphery of the rotating body and is formed at a pitch that gradually decreases from the suction end side to the discharge end side of the cylinder, and a spiral groove is fitted into the groove so as to be able to move in and out. a spiral blade having an outer circumferential surface in close contact with the cylinder 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 rotating the rotating body synchronously with the cylinder; An end of the rotating body located on the suction end side of a fluid compressor including a mechanism for sequentially transferring fluid flowing into the working chamber from the suction end side of the cylinder to the working chamber on the discharge end side of the cylinder. On the outer surface,
Fluid compression characterized in that a suction groove is provided which is formed deeper than the spiral groove and introduces the fluid to be compressed only into the first working chamber formed on the suction end side. Machine.