JPH07259771A - Refrigerant gas discharge device of rotary compressor - Google Patents

Abstract

PURPOSE: To eliminate another delivery valve, and reduce compression loss in association with excessive compression with refrigerant remaining in a delivery port after a compression refrigerant is delivered by delivering the compression refrigerant by a rotary phase angle of a crank for driving a roller in order to revolve an intake chamber and a compression chamber. CONSTITUTION: A third discharge passage 42 and a second discharge passage 41 of an eccentric body 21 are connected to each other. When the second discharge passage 41 of the eccentric body 21 is not matched with a connecting passage 40, a bottom surface of an upper flange and an upper surface of the eccentric body 21 are brought into surface contact with each other, and the second discharge passage 41 is not communicated with a first discharge passage 40. When the second discharge passage 41 is communicated with the first discharge passage 40 of a revolving roller 22 without rotation by an engaging part while rotating the eccentric body 21, refrigerant gas compressed in a compression chamber 12 is discharged outward a cylinder 10 through the first discharge passage 40, the second discharge passage 41, and the third discharge passage 42. It is thus possible to eliminate another discharge valve when the refrigerant is discharged.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant gas discharge device for a rotary compressor, and in particular, the discharge port is formed on a main shaft,
The present invention relates to a refrigerant gas discharge device for a rotary compressor formed on an eccentric body that revolves eccentrically.

[0002]

2. Description of the Related Art Generally, a rotary compressor is installed in a refrigeration cycle of various air conditioners for the purpose of cooling and freezing, and compresses a refrigerant gas at high temperature and high pressure. For example, as shown in FIG. 1, a rotary shaft 20 is provided which is rotatably driven by a motor 2 in a housing 100. The rotary shaft 20 is eccentrically located below the rotary shaft 20. 121 is provided and is configured to compress the inside of the cylinder 110.

Further, the eccentric body 21 (FIG. 2A) is attached to the rotary shaft 20.
And is configured to rotate freely within the roller 121. When the rotary shaft 20 is rotated by the motor 2, the roller 121 provided below the rotary shaft 20 compresses the refrigerant gas sucked through the suction pipe 16 while being eccentrically rotated in the cylinder 110 at high temperature and high pressure. Then, the compressed refrigerant gas is discharged to the outside of the cylinder 110, and the compressed refrigerant gas is repeatedly circulated in the refrigeration cycle through the discharge pipe 17 provided in the upper portion of the housing 100.

In such a rotary compressor, the conventional discharge process in which the refrigerant gas compressed in the cylinder 110 at high temperature and high pressure is discharged to the outside of the cylinder 110 is as follows. As shown in FIGS. 2A and 2B, a roller 121 installed eccentrically on the rotary shaft 20 is provided inside the cylinder 110, and at the same time, a spring 11 is installed on one side of the cylinder 110 by a spring 11. A vane 130 is provided to divide the inside of the cylinder 110 into a suction portion 111 and a compression portion 112, and is configured to be capable of advancing and retreating in accordance with the rotational driving of the roller 121. Further, the vane 130 is used as a reference. , Cylinder 110 on one side
A suction port (not shown) for sucking the refrigerant gas therein and a discharge port 113 communicating with the compression chamber 112 are provided on the other side.

The roller 12 is driven by the rotation of the rotary shaft 20.
When the cylinder 1 is eccentrically driven to rotate in the cylinder 110, the refrigerant gas is introduced through the suction port into the cylinder 110.
While being sucked into the inside, it is compressed at a high pressure and is discharged from the discharge port 113.
Through the cylinder 110, and at this time, the discharge port 113 is provided with a plate-shaped opening / closing member 115 (FIG. 2B) having a certain elasticity, and when the refrigerant gas is discharged, Discharge port 113 depending on pressure
After opening, the discharge port 113 is closed by the elasticity of itself during the suction and compression strokes of the refrigerant gas.

[0006]

However, since the length of the discharge port 113 connecting the compression chamber 112 and the inside of the housing 100 is long, the compressed refrigerant remaining in the discharge port 113 is not discharged yet. To exist.
The compressed refrigerant existing in this way is sucked into the suction chamber 111, mixed with the refrigerant to be compressed, and then re-expanded, so that the suction volume of the suction chamber 111 is reduced and the compression efficiency is further reduced. There was a problem.

In view of the above problems, a refrigerant discharge structure as shown in FIG. 3 is disclosed in Japanese Patent Publication No. 3-67089. This is because the valve plate 115 (FIG. 2B) is removed and the slide valve 2 is attached to the discharge port 113 in a state where the slide valve 2 has the same configuration as that of FIG.
00 is installed.

However, since the slide valve 200 having a larger inertial weight than that of the reed valve is used, a delay in opening / closing of the valve cannot be solved and there are many sliding parts, so that the operation reliability becomes a problem. .

On the other hand, in consideration of the above problems, a refrigerant discharge structure as shown in FIG. 4 has been disclosed in Japanese Patent Publication No. 3-70890. This is a hollow cylinder 110 and the cylinder 11
Piston body 121 inscribed in 0 and revolvingly driven by a crank 120, and a blade 3 standing upright on the piston body 121 and moving in and out of the cylinder 110.
00 and the horizontal swing of the blade, the discharge passage 31
A blade shoe 310 that opens and closes 1 is provided. In such a structure, there is a problem in that the blade shoe 310 penetrates and the outer peripheral portion of the cylinder 110 is constrained, so that the blade 300 cannot freely swing to the left and right.

Further, since the discharge passage 311 is formed to be long, the compressed refrigerant remaining without being discharged may re-expand.

On the other hand, as shown in FIG. 5, the spring 11 inserted into the back surface 131 of the vane 130 is
0 linearly moves up and down in accordance with the rotating action of the roller 121 to define the suction chamber 111 and the compression chamber 112, and at the same time, the tip end surface thereof is elastically brought into close contact with the outer peripheral surface of the roller 121 to enable compression of the refrigerant. Provided resilience, so that. A compressor employing a spring having such a typical structure is shown in Japanese Unexamined Patent Publication No. 5-164072.

However, in the spring having such a structure, the spring 11 is designed and installed so that the elastic force of the spring 11 acts only in the reciprocating direction of the vane 130. Due to the differential pressure in the chamber 111, the vane 130 receives a force toward the low-pressure suction chamber 111, and stress is concentrated on the vane slot low pressure side inner peripheral tip 115 and the high pressure side outer peripheral tip 117 formed in the cylinder 110. As a result, not only sliding loss but also abrasion increases.

[0013]

The present invention is to solve the above-mentioned problems and the like, and the object of the present invention is to
According to the rotation phase angle of the crank that drives the roller to revolve the suction chamber and the compression chamber, the compressed refrigerant is discharged so that a separate discharge valve is unnecessary, and further,
It is an object of the present invention to provide a refrigerant gas discharge device for a rotary compressor in which the compression loss due to overcompression is reduced by the refrigerant remaining in the discharge port after discharging the compressed refrigerant.

Another object of the present invention is to compensate the force that the vane receives toward the low-pressure suction chamber by the differential pressure between the compression chamber and the suction chamber during compression, so that the vane and the sliding loss of the vane are, of course, lost. An object of the present invention is to provide a refrigerant gas discharge device for a rotary compressor that can reduce wear.

The refrigerant gas discharge device of the rotary compressor for this purpose has a cylinder for enclosing a compression chamber to which a fluid is supplied and a refrigerant introduced through a suction port of the cylinder. A rotatably housed roller, a vane housed in the body of the cylinder so as to always contact the roller, and an eccentric body that eccentrically rotates to be eccentric to the main shaft installed in the roller. The roller is for discharging compressed fluid,
A first discharge passage communicating with the compression chamber is provided, and the eccentric body is provided with a second discharge passage communicating with the first discharge passage.

Further, the first discharge passage and the second discharge passage are formed to communicate with each other during the compressed fluid discharge cycle. As a result, the exhaust gas from the second exhaust passage is formed to be exhausted to the outside of the compression chamber via the third exhaust passage on the main shaft.

Further, an engaging portion is formed on the vane and a part of the roller which is in constant contact with the vane, so that the first discharge passage can only revolve. On the other hand, in the refrigerant gas discharge device of the present invention, a loop-type spring is provided on the back surface of the vane, one end of the spring exerts a force to bring the vane into contact with the roller, and the other end of the spring is supported by the inner wall of the body. To form. As a result, one end of the spring supported by the inner wall of the body is formed such that the other end of the spring for contacting the vane with the roller is separated by the diameter of the spring toward the first discharge passage.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A preferred embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

FIG. 6 is an exploded perspective view of the present invention, which shows a hollow cylinder 10, a roller 22 that revolves in a state of being inscribed in the cylinder 10, and a motor (not shown) housed in the roller 22. Driven by the main shaft 20, an eccentric body 21 which is formed to be eccentric to the main shaft 20, and rotates eccentrically, and the cylinder 22 in contact with the roller 22.
The inside of 0 is formed by a vane 30 that divides the inside of the chamber into a suction chamber 11 and a compression chamber 12. Further, the refrigerant gas discharge device of the present invention is provided with an engaging portion 31 that connects the end portion of the vane 30 and the outer peripheral surface of the roller 22 so that the roller 22 revolves without rotating.

The engaging portion 31 is provided with a hemispherical protrusion 32 formed on the outer peripheral surface of the roller 22 and a hemispherical groove 33 formed at the end of the vane 30 so as to come into contact with the protrusion 32. .

On the other hand, on the back surface of the vane 30 so that the vane 30 is always in contact with the protrusion 32 of the roller 22,
The elastic member 60 is elastically installed as shown in FIG.

Consequently, the refrigerant gas discharge device of the present invention is
A first discharge passage 40 formed on the upper surface of the roller 22 so that the inner and outer peripheral surfaces communicate with each other, a second discharge passage 41 formed on the outer peripheral surface of the eccentric body 21 with an arc of a constant length, and the eccentric body. 21, one end is connected to the second discharge passage 41 and the other end is connected to the outside of the cylinder 10.
A discharge passage 42 is provided. On the other hand, the elastic member 60 is similar to that shown in FIG.
As shown in FIG. 9, an upper end contacts the back surface 34 of the vane, and applies a pressing force to the vane 30, and a pressurizing portion 63 that extends in the pressurizing portion 63 and bends in a loop shape to form a centerline of the vane 30. Further, the support portion 65 is provided to support the compression chamber 12 so as to be isolated and supported by the diameter d of the spring. Further, the elastic member 60 can be formed as shown in FIG. 8B.

The first discharge passage 40 is formed on the upper surface of the roller 22 at the end of the compression chamber 12 formed by the roller 22 and the vane 30 installed between the upper and lower flanges 14 and 15 (FIG. 7). To do.

The operation of the refrigerant gas discharge device provided as described above will be described below. First, as shown in FIG. 7, the third discharge passage 4 of the eccentric body 21 is provided.
2 and the second discharge passage 41 are connected.

Therefore, the second discharge passage 4 of the eccentric body 21
When 1 does not coincide with the connection passage 40, the bottom surface of the upper flange 14 and the top surface of the eccentric body 21 are in surface contact with each other, so that the second discharge passage 41 does not communicate with the first discharge passage 40.

On the other hand, if the eccentric body 21 rotates and the second discharge passage 41 communicates with the first discharge passage 40 of the revolving roller 22 without revolving by the engaging portion 31, it rotates. The refrigerant gas compressed in the compression chamber 12 is the first exhaust passage 40, the second exhaust passage 41,
It is discharged to the outside of the cylinder 10 through the third discharge passage 42.

The process will be described in detail with reference to FIGS. 10A to 10D. FIG. 10A shows the process of sucking the refrigerant gas.

That is, when the eccentric body 21 rotates clockwise around the main shaft 20 and its phase angle changes, the roller 22 revolves around the projection 32 of the engaging portion 31 and the groove 33 without rotating. . At this time, the outer peripheral surface of the roller 22 and the inner peripheral surface of the cylinder 10 continuously contact with each other, and at the same time,
The vane 30 is moved forward by the spring 60 to move the groove 3
3 makes spherical contact with the protrusion 32, so that the suction chamber 11
And the compression chamber 12 are separated.

Therefore, when the roller 22 revolves clockwise, the suction chamber 11 is gradually expanded and the compression chamber 1 is expanded.
In the case of 2, the process of being gradually reduced occurs continuously.

On the other hand, the process of compressing and discharging the sucked refrigerant gas will be described. As described above, FIG. 10A shows that the refrigerant gas initially flows into the suction chamber 11 through the suction port 13. It is a process that has been done. Figure 10B
Is a process in which the refrigerant gas sucked by the rotation of the eccentric body 21 is compressed.

FIG. 10C shows that when the eccentric body 21 is rotated, the second discharge passage 41 of the eccentric body 21 of the first discharge passage 40 of the roller 22 is rotated by the rotation of the eccentric body 21 when the refrigerant gas is compressed to the maximum.
This is a process in which the compressed refrigerant gas in the compression chamber 12 communicates with each other and starts discharging.

At this time, the compressed refrigerant gas is
Through the discharge passage 40 and the second discharge passage 41, the main shaft 20
Along the third discharge passage 42 formed in the cylinder 1
0 is discharged to the outside.

In FIG. 10D, the second discharge passage 41 is displaced toward the suction chamber 11 by the rotation of the eccentric body 21 so as to pass through the first discharge passage 40 and rotate toward the suction chamber 11. Since the exhaust passage 41 and the first exhaust passage 40 are separated by the upper flange 14 of FIG. 7, the gas on the first exhaust passage 40 cannot move to the second exhaust passage 41.

On the other hand, in FIG. 10C, when the second discharge passage 41 formed in an arc shape is rotated by the change of the rotation phase angle of the eccentric body 21, the compressed refrigerant gas is discharged,
Force F generated by the difference in compression between suction chamber 11 and compression chamber 12
c acts on the lower surface (that is, the surface facing the compression chamber 12) of the vane 30 adjacent to the groove 33 in the vane 30 of FIG. 9. At this time, the elastic member 60 is formed in a loop shape, and a force such as Fs acts on the back surface 34 of the vane. The force Fs is that the vane 30 is the protrusion 32
It can be divided into a horizontal component force Fx that tries to push the vane and a vertical component force Fy that pushes the back surface 34 of the vane to the suction chamber 11, that is, the slot wall 16A on the low pressure side.

While the force Fc in the compression chamber 12 is applied to the upper end portion of the vane 30 (that is, the portion adjacent to the groove 33), the vertical component force Fy acts on the back surface 34 of the vane 30. is there.

Therefore, due to the vertical component force Fy, the upper surface 30A of the vane moves while uniformly contacting the slot wall 16A on the low pressure side.

[0037]

As described above, according to the present invention,
In accordance with the rotation of the eccentric body, the revolving roller moves in the cylinder, sucks and compresses the refrigerant and discharges it through the first discharge passage. At this time, since the compressed refrigerant is discharged through the second discharge passage formed in the eccentric body and the third discharge passage formed in the main shaft, a separate discharge valve is unnecessary when discharging the refrigerant.

Furthermore, since the phase angle of the second discharge passage changes continuously while the eccentric body rotates, the compressed refrigerant gas is sufficiently discharged along the first discharge passage and the re-expansion is reduced. The effect is that the compression efficiency is improved.

Furthermore, the stress concentration at the inner peripheral tip of the low pressure side surface and the outer peripheral tip of the high pressure side surface of the vane slot, which is caused by the differential pressure during compression, is eliminated by the distributed load.
The sliding loss and wear between the vane slots and the vanes can be reduced, and the reliability can be improved.

[Brief description of drawings]

FIG. 1 is a sectional view of a conventional rotary compressor.

FIG. 2A is a plan view of a refrigerant gas discharge device, which is one example of the prior art, and B is a detailed view of the discharge valve plate of FIG.

FIG. 3 is a plan view of a refrigerant gas discharge device, which is another example of the conventional art.

FIG. 4 is a plan view of a refrigerant gas discharge device according to another example of the related art.

FIG. 5 is an enlarged sectional view of the spring used in FIG. 2A.

FIG. 6 is an exploded perspective view of the present invention.

7 is a cross-sectional view of the connection state of FIG.

8A is a perspective view of the elastic member used in FIG. 7, and FIG. 8B is a perspective view of another example of the elastic member used in FIG.

FIG. 9 is a partially enlarged plan view shown in FIG. 6A.

10A, 10B, 10C, and 10D are cross-sectional views taken along line XX in FIG. 7 and are operation state diagrams of the ejection device.

[Explanation of symbols]

 10: Cylinder 21: Eccentric body 22: Roller 30: Vane 32: Protrusion 33: Groove 40: First discharge passage 41: Second discharge passage 42: Third discharge passage 60: Elastic member

Claims (6)

[Claims] 1. A cylinder which is divided into a compression chamber and a suction chamber, a roller which is operably accommodated in the cylinder so as to compress a refrigerant that has flowed in through a suction port of the cylinder, and the roller is always provided on the roller. The vane housed in the body of the cylinder and the main shaft installed in the roller so as to come into contact with each other are formed to be eccentric, and the eccentric body is eccentrically rotated. A first discharge passage communicating with the compression chamber is provided to discharge the compressed fluid, and the eccentric body has the first discharge passage.
A refrigerant gas discharge device for a rotary compressor, comprising a second discharge passage communicating with the discharge passage. 2. The refrigerant gas discharge device for a rotary compressor according to claim 1, wherein the first discharge passage and the second discharge passage are formed to communicate with each other during a compressed fluid discharge cycle. 3. The exhaust gas flowing through the second exhaust passage is discharged to the outside of the compression chamber through a third exhaust passage formed on the main shaft.
A refrigerant gas discharge device for a rotary compressor as described. 4. The tip of the vane and a part of the roller with which the vane is in constant contact are formed with an engaging portion so that the first discharge passage can only revolve. The refrigerant gas discharge device of the rotary compressor according to claim 2. 5. The elastic member supported on the inner wall of the body is configured such that one end of the elastic member is in contact with the roller, and the other end of the elastic member is separated by the diameter of the elastic member toward the first discharge passage side. The refrigerant gas discharge device for a rotary compressor according to claim 1, wherein the refrigerant gas discharge device is installed. 6. The refrigerant gas discharge device for a rotary compressor according to claim 5, wherein the elastic member is formed of a loop-shaped spring.