JPH02201095A - Fluid compressor - Google Patents

Abstract

PURPOSE:To prevent galling and abnormal wear of the cylinder end face of a fluid compressor in such a construction that a rotor with a spiral blade fitted in a spiral groove formed at the periphery is fitted in a cylinder, by interposing a thrust bearing between a bearing supporting the end of cylinder on its suction end side and the end face of the cylinder. 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 gradually, and a spiral blade 21 is fitted in this groove 19 in such a way that it can advance and retreat freely. A thrust bearing 10 is interposed between the cylinder end face one its one end in the axial direction and the end face of the base 8a of bearing 8 on the suction side, and the end face of a core 6a of the rotor 6 shall be dislocated toward the other end of cylinder 7 by an amount D with respect to the end face of a core 5a of stator 5.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to a fluid compressor that compresses 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 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 eliminate such problems, a helical blade type fluid compressor as shown in FIG. 11 has been considered.

That is, numeral 51 in the figure indicates a closed case, and supports 52 are provided on the inner surfaces of both ends of the closed case 51 in the axial direction. These supports 52 are formed from a base 52a and a boss 52b having a smaller diameter than the base 52a, and each support 52 is formed with a bearing hole 52c.

On the outer periphery of the boss portions 52b of the pair of supports 52, both ends of the cylinder 53 in the axial direction are rotatably supported. It has been f. Inside this cylinder 52, a rotating body 54 has its axis A aligned with the axis t of the cylinder 53! It is housed eccentrically with eccentricity me with respect to i1B. Support shaft portions 55 are provided at both ends of the rotating body 54 in the axial direction, and these support shaft portions 55 are connected to the support body 5.
It is rotatably supported in a bearing hole 52c formed in 2. One support body 52 has a suction hole 4L57 connected to a suction vibrator 56, and the other support body 52 has five discharge holes connected to a discharge vibrator 58.

A spiral groove 61 whose pitch gradually decreases from the suction side to the discharge side is formed on the outer circumferential surface of the rotary body 54, and a blade 62 can freely move in and out of the rotary body 54 in the radial direction. It is provided on the inner circumferential surface of the cylinder 5' so that the outer circumference is closely spaced by 6 degrees.

The space inside the cylinder 53 is divided into a plurality of working chambers 60 by the blade 62 .

A rotor 64 of a motor 63 is provided on the outer peripheral surface of the cylinder 53.
is externally fitted, and this rotor 64 is fitted with a two-legged sealed case 5.
It is housed in a stator 65 fixed to 1. The cylinder 53 and the rotating body 54 are coupled by a mechanism not shown so that they rotate in a 2:1 manner.

Therefore, if the motor 63 is energized to rotate the rotor 64 and rotate the cylinder 53 and the rotating body 54 relative to each other, the refrigerant supplied from the suction vibrator 56 to the working chamber 6o on the suction side in the cylinder 53 The gas is gradually compressed and discharged through the discharge vibrator 58.

By the way, in such a conventional fluid compressor, in order to facilitate manufacturing and to smooth the ITJ rotation of the cylinder 53, τj between the end faces of the boss portions 52b of the pair of supports 52 is
The length Z1 is set longer than the total length Z2 of the cylinder 53 in the axial direction. In other words, the cylinder 53 is moved between the pair of supports tJ! with play in the axial direction. It is rotatably supported by the body 52. Furthermore, the rotor 64 and the stator 65 are provided with the end surfaces of these cores 64a and 65a aligned in the axial direction.

Therefore, due to these factors, the rotor 6
4 causes hunting in the axial direction.

Then, the cylinder 53 also hunts together with the rotor 64, and its axial end face collides with the end face of the base portion 52a of the support body 52, which may cause abnormal wear.

(Problems to be Solved by the Invention) As described above, in the conventional fluid compressor, the cylinder rotatably supported by the support body cinches together with the rotor, and the end face of the cylinder collides with the support body and becomes galled. This may lead to abnormal wear and tear.

This invention was made based on the above circumstances, and part 1
The object of the present invention is to provide a fluid compressor which can prevent the cylinder from hunting together with the rotor using a relatively simple structure.

[Structure of the Invention (Means for Solving the Problems) To solve the above problems, the present invention provides an electric element consisting of a stem and a rotor, and a suction end side of the electric element held concentrically with the rotor. and a cylinder whose discharge end side is H, and which is arranged eccentrically along the axial direction of the cylinder within this cylinder and can rotate relative to the cylinder with a part of the cylinder in contact with the inner circumferential surface of the cylinder. a cylindrical rotating body; a support that rotatably supports both ends of the rotating body and the cylinder in the axial direction; A spiral groove formed at a gradually decreasing pitch and an outer 1114 surface that is fitted into the groove so as to be able to move in and out and that is in close contact with the inner circumferential surface of the cylinder are GT L, and the inner circumferential surface of the cylinder and the above rotation. A spiral blade that divides a space between the body and the outer circumferential surface of the body into a plurality of working chambers; In a fluid compressor equipped with a mechanism for sequentially transferring the fluid to a working chamber on the discharge side, the iron core of the rotor is disposed offset from the iron core of the stator by iJ toward one end in the axial direction, and A thrust bearing is provided at a portion facing the side end face.

(Function) By doing this, the present invention sets the direction in which the rotor slides in the axial direction when starting, stopping, or changing the operating condition due to the misalignment between the stator and rotor, and adjusts the direction in which the rotor slides. The end of the cylinder located in the direction is supported by a thrust bearing.

(Embodiment) Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 to 10. 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 power supply A3 and a compression power supply 1g4 disposed within the closed case 2 as driving means. The electric element 3 has a substantially annular stator 5 fixed to the inner surface of the closed case 2 and an annular rotor 6 provided inside the stator 5.

The compression element 4 has a cylinder 7 H, 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 as supports 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. There is. That is, the bearing 8
．． Reference numeral 9 denotes a boss portion 88 N 9 a into which the end of the cylinder 7 is rotatably fitted, and a boss portion 21 ! which has a larger diameter than the boss portions 3 a and 9 a and is fixed to the inner surface of the sealed case 2 ! It consists of i parts 8b and 9b.

The dimension Z between the ends of the bases 8a and 9a of the pair of bearings 8.9 is set shorter than the total length z2 of the cylinder 7 in the axial direction. 11 between the end face of the cylinder 7 on the one end side in the fIIIJj direction and the end face of the base 8a of one of the bearings 8.
At 41, a thrust bearing IO consisting of, for example, a rolling bearing is installed. In other words, thrust bearing 1
0 is provided in the bearing 8. In a state where the end of the cylinder 7 on one axial end side is joined to the thrust bearing 10, the end of the iron core 6a formed by stacking the blanks of the rotor 6 is attached to the end face of the iron core 5a of the stator 5. It is positioned so as to be shifted toward the other end in the axial direction of the cylinder 7 by a dimension indicated by D in FIG.

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. This piston 1
1, its central axis A is close to the central axis B of cylinder 7 = j
The piston 11 is eccentrically disposed in one direction in FIG.

Support shaft portions 32g and 12b are provided at both axial ends of the upper piston 11, respectively, and these support shaft portions 12a and 1
2b are bearing holes 8C formed in the bearings 8 and 9, respectively.
It is rotatably inserted and supported by 19c.

A prismatic portion 13 having a square cross section is formed on one support shaft portion 12a of the piston 11. As shown in FIG. 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 prismatic part]3
An Oldham ring 15 is fitted into the elongated hole 14 so as to be slidable along the longitudinal direction thereof. One end portion of a pair of pins 16 is slidably inserted into the outer peripheral surface of the Oldham ring 15 in a radial direction perpendicular to the longitudinal direction of the elongated hole 4. The other ends of these bottles 16 are fitted and fixed into fitting holes 17 bored in the peripheral wall of the cylinder 7.

Therefore, the upper cylinder piston 11 is connected to the cylinder 7,
It is coupled eccentrically with respect to the radial direction of the cylinder 7. Therefore, when the electric element 3 is energized and the cylinder 7 and rotor 6 are rotated together, the cylinder 7
The rotational force of is applied to the piston 1 via the Oldham ring 15.
1. Note that the above fitting hole 1
7 is hermetically closed by a lid 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 to 3.
is formed. 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 side to the discharge side of the cylinder 7.

A spiral blade 21 shown in FIGS. 2 and 3 is fitted into the groove 19. The thickness of this blade 21 -
・The j method is almost the same as the width of the spiral groove 13 -j method, and each part of the blade 21 has a distance between the piston 1 and the groove 19.
It can move forward and backward in approximately the radial direction of 1. The outer circumferential surface of the blade 21 is in close contact with the inner circumferential surface of the cylinder 7, and slides on the inner circumferential surface of the cylinder 7 in this state.

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 In other words, the 3 working chambers 22 are the blade 2
It is formed between two adjacent windings of 1, and the screw is along the blade 2! - It has a nearly crescent shape extending from the contact point between the cylinder 11 and the inner circumferential surface of the cylinder 7 to the next contact point.

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, a suction hole 23 penetrates in the axial direction of the bearing 8 located on the suction side of the cylinder 7, as shown in FIG. 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 is provided with a discharge hole 25 . One end of this discharge (L25) communicates with the discharge end side inside the cylinder 7, and the other end opens into the inside of the sealed case 2.

"2 The piston 11 has an auxiliary introduction passage 2 as shown in FIG.
6 is bored along its central axis A.

One end of this auxiliary introduction passage 26 communicates with the bottom of the uA spiral groove 19 on the discharge side, and the other end communicates with the through hole 2 bored in one of the bearings 8.
It is connected to one end of 7. The other end of the 20 through hole 27 is connected to the other end of an introduction pipe 28 whose one end is located at the bottom of the closed case 2. Lubricating oil 2 is placed at the bottom of the sealed case 2.
9 is stored. Therefore, when the pressure inside the sealed case 2 increases, the lubricating oil 29 is introduced into the space between the bottom of the groove 19 and the blade 21 through the introduction pipe 28, the through hole 27, and the auxiliary introduction passage 26. .

Further, a suction groove 31 is formed on the outer peripheral surface of the end of the piston 11 located on the suction side.

The second suction groove 31 is formed deeper than the spiral groove 19 formed on the outer circumferential surface of the piston 11, and one end thereof is located at the large diameter portion of the piston 11. 1a, and the other end is located on the suction end side of the cylinder 7.
It is located in a position that communicates with the Thereby, suction tube 2
The refrigerant gas sucked into the cylinder 7 from the cylinder 7 passes through the suction groove 31 and is reliably introduced into the working chamber 22 at the first port without interruption.

Note that, 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. cylinder 7
When the piston 11 rotates, the piston 11 is driven to rotate with a part 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 the Oldham ring 15 provided on the prismatic portion 13 of the piston 11. And blade 2]
The piston 11 also rotates integrally with the piston 11.

Top: Since the blade 21 rotates with its outer circumferential surface in contact with the inner circumferential surface of the cylinder 7, each part of the blade 21 rotates as it approaches the contact area between the outer circumferential surface of the piston 11 and the inner circumferential surface of the cylinder 7. Therefore, it is pushed into the groove 19, and moves in the direction of protruding from the upper 1d groove 19 as it moves away from the contact portion.

On the other hand, when the compression element 4 is activated, refrigerant gas is sucked into the cylinder 7 through the suction tube 24 and the suction hole 23. As shown in FIG. 6, the refrigerant gas sucked into the working chamber 22 of No. 1 is trapped there as the piston 11 rotates, as shown in FIGS. 6 to 9. Then, they are sequentially transferred to the working chamber 22 on the discharge side. The transferred and compressed refrigerant gas is then transferred to the bearing 9 on the discharge side.
It is discharged from the discharge hole 25 formed in the airtight case 2 into the space inside the sealed case 2, and is returned to the refrigeration cycle through the discharge tube 32.

When the refrigerant gas is discharged into the sealed case 2 and the pressure inside the sealed case 2 rises, the lubricating oil 29 stored inside is pressurized, and the lubricating oil 29 passes through the oil introduction path 26 into a spiral groove. It is introduced into the space between the bottom of 19 and the blade 21. Therefore, the blade 21 is always pressed in the direction in which it is pushed out from the groove 19 by hydraulic pressure, that is, toward the inner peripheral surface of the cylinder 7. Therefore, blade 2
The outer circumferential surface of cylinder 1 is kept in close contact with the inner circumferential surface of cylinder 7 at all times. This prevents gas from leaking between the working chambers 22.

Further, the spiral groove 19 formed on the piston 11 is 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 22 partitioned by the blade 21 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 22, the refrigerant gas can be efficiently compressed even if no check valve is provided on the discharge side of the compressor.

In addition, since the iron core 5a of the rotor 5 is shifted from the iron core 6a of the stator 6 by a certain amount in the axial direction, the above-mentioned A force is generated in the a-tube 6 that moves the iron core 6a in the direction opposite to the iron core 5a of the stator 5, as shown by the arrow in FIG. Thereby, the rotor 6
Since the end face of the cylinder 7 on the distal end side in the moving direction, which moves integrally with the cylinder 7, comes into pressure contact with the thrust bearing 10 provided on one of the bearings 8, the cylinder 7 rotates smoothly, and the end face touches the base 8a of the one bearing 8. This prevents galling or abnormal wear on the end face of the cylinder 7. In addition, the thrust bearing 10 is replaced by a rolling bearing, and the end face of the cylinder 7 or the end face of the base 8a of the bearing 8 is prevented from galling or abnormal wear. Alternatively, an oil groove may be provided on one side to form a sliding bearing.

According to the embodiments of the present invention, an example in which the cylinder is fitted and held in the rotor has been described, but it is sufficient that the rotor and the cylinder are arranged concentrically, and the arrangement of the persimmons can be Of course, it goes without saying that it is possible.

[Effects of the Invention] As described above, the present invention allows the rotor to be shifted toward one end in the axial direction with respect to the stator, and to rotate the rotor axially at the time of starting, stopping, or under different operating conditions such as lj, v, etc. The cylinder is forcibly moved toward the other end in the axial direction, and a thrust bearing that receives the end surface of the cylinder is provided at the other axial end of the cylinder that is provided integrally with the rotor.

Therefore, according to the present invention, even if the rotor slides during startup, the end face of the cylinder provided integrally with the rotor is received by the thrust bearing, so the end face of the cylinder collides with the end face of the support part. This can prevent galling and abnormal wear.

[Brief explanation of the drawing]

Figures 1 to 10 show one embodiment of the present invention (Figure 1 is a vertical sectional view showing the entire fluid compressor, Figure 2 is an exploded view of the compression element, and Figure 3 is a perspective view of the piston. Figure 4 is a cross-sectional view of the connection between the piston and cylinder using an Oldham ring, Figures 5 to 9 are explanatory diagrams sequentially showing the compression process of cold tofu gas, Figure 10 is a side view of the compression element, Fig. 11 is a longitudinal sectional view of a conventional fluid compressor. 2...i closed case, 3... electric element, 5... stator, 5a, 6a... iron core, 6... rotor ,7...
・Cylinder, 8.9... Bearing (support body) 10... Thrust bearing, 11... Piston (rotating body), 15...
・Oldham ring, 1...full, 21...blade, 22...operating chamber. Applicant's agent Patent attorney Takeshi Suzuru I3

Claims (1)

[Claims] An electric element consisting of a stator and a rotor, a cylinder having a suction end side and a discharge end side held concentrically with the rotor of the electric element, and a a cylindrical rotating body that is arranged eccentrically along the cylinder and can rotate relative to the cylinder while a part of the rotating body is in contact with the inner circumferential surface of the cylinder, and both axial ends of the rotating body and the cylinder; a support member that rotatably supports each of the rotating body; a spiral groove formed on the outer periphery of the rotating body with a pitch that gradually decreases from the suction end side to the discharge end side of the cylinder; a spiral blade that is fitted into the cylinder and has an outer circumferential surface that closely contacts the inner circumferential surface of the cylinder, and divides 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; , a fluid compressor comprising a mechanism for rotating the rotating body in synchronization with the cylinder and 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, A fluid compressor characterized in that the iron core is disposed offset toward one end in the axial direction with respect to the iron core of the stator, and a thrust bearing is provided at a portion facing the end surface of the other end in the axial direction of the cylinder.