JPH0551071B2 - - Google Patents

Description

Detailed Description of the Invention [Technical Field of the Invention] The present invention relates to a scroll compressor, and particularly to a scroll compressor that can improve the sealing performance of a high pressure chamber formed between an orbiting scroll and a frame. Regarding.

[Technical background of the invention and its problems] Recently, there has been a tendency to adopt scroll compressors as compressors for refrigeration cycles and the like. As shown in FIGS. 9 and 10, this scroll compressor has a spiral wrap 1a, such as an involute,
A crescent-shaped compression space 3 is closed by the fixed scroll 1 and the orbiting scroll 2, which are rotatably engaged with each other at a position rotated by a certain angle (180°), forming the fixed scroll 1 and the orbiting scroll 2a. and its orbiting scroll 2
By rotating the fixed scroll 1 while maintaining a certain eccentric distance e with respect to the center O ₁ of the fixed scroll 1, the compression space 3 is moved toward the center of the vortex while contracting, and the refrigerant is sucked and compressed almost continuously. It is something to do.

FIG. 11 shows the compression element 4 of a scroll compressor.
This figure shows the conventional structure of . As shown in the figure, the outer peripheral edge 5 of the fixed scroll 1 is fixed to a frame 6 with bolts 7 or the like. The orbiting scroll 2 that meshes with the fixed scroll 1 is rotatably housed in a frame 6, and its rear surface 8 opposite to the wrap 2a is in sliding contact with a high pressure receiving ring 9.
is supported by

Specifically, as shown in FIG. 12, the high pressure receiving ring 9 is provided on a mounting surface 10 of the high pressure receiving ring formed in the upper part of the frame 6. An annular high pressure chamber 12 for reducing the thrust pressure of the orbiting scroll 2 is formed between the back surface 8 of the orbiting scroll 2 and the high pressure receiving ring 9.
The high pressure chamber 12 is configured to be supplied with the refrigerant in the compression space 3 through a communication hole 14 formed through a flat plate portion 13 of the orbiting scroll 2 .

Further, a bearing portion 15 is formed approximately at the center of the back surface 8 of the orbiting scroll 2;
is connected to an eccentric shaft portion 17 of a crankshaft 16 that is pivotally supported by the frame 6, and is configured to rotate the orbiting scroll 2.

An Oldham ring 18 is interposed between the orbiting scroll 2 and the frame 6 to prevent rotation of the orbiting scroll 2 when the orbiting scroll 2 is driven to orbit.

However, in the conventional compression element 4 configured as described above, the sealing performance of the sliding portion between the high pressure receiving ring 9 and the orbiting scroll 2 is low, and the high pressure chamber 12
There was a problem with a large amount of high pressure gas leaking from the That is, pressure Pd is supplied to the high pressure chamber 12 from the communication hole 14.
When a force Pm is applied to the high pressure chamber 12 to push up the orbiting scroll 2 by supplying high pressure gas of
This pushing up force Pm creates a gap S between the high pressure receiving ring 9 and the back surface 8 of the orbiting scroll 2, and this is due to the fact that high pressure gas leaks from this gap. For this reason, there was a problem in that the gas pressure in the high pressure chamber 12 decreased and the thrust pressure of the orbiting scroll 2 could not be sufficiently reduced. In addition, since the leaking high-pressure gas is refrigerant supplied from the compression space 3 during or after compression,
This was also a factor in reducing the compression capacity of the compressor.

[Object of the Invention] The present invention has been devised in view of the above problems and to effectively solve them.

SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll compressor in which the sealing performance of a high pressure chamber formed between an orbiting scroll and a frame is improved.

[Summary of the Invention] In order to achieve the above object, the present invention provides an orbiting scroll and a fixed scroll on a frame in mesh with each other, and introduces a compressed refrigerant between the frame and the orbiting scroll to reduce the thrust pressure of the orbiting scroll. In a scroll compressor having an annular high pressure chamber formed therein, the inner and outer peripheral surfaces of the annular high pressure chamber are formed into tapered inclined surfaces, and a tapered contact surface is formed along the inclined surfaces. At the same time, a part of each elastic seal ring is separated, and the separated ends are superimposed on each other in the circumferential direction of the ring and are movably engaged with each other to freely expand and contract the ring diameter. The overlapping portion of the engaging portion is located at the center in the radial direction of the contact surface of the ring.

[Embodiments of the Invention] A preferred embodiment of the present invention will be described below in detail with reference to the accompanying drawings.

As shown in FIG. 2, a fixed scroll 22 and an orbiting scroll 23, which constitute the compression element 21 of the scroll compressor, are provided on a frame 24.
These fixed scroll 22 and orbiting scroll 2
3 has spiral wraps 22a and 23a, such as involutes, which are each formed in the same shape. The fixed scroll 22 and the orbiting scroll 23 are rotatably engaged with each other with their laps 22a and 23a inside, and are configured to define a crescent-shaped closed compressed space 25 inside the engaged scroll. . The compressed refrigerant in this compression space 25 is discharged to the outside of the compression element 21 through a discharge hole 26 formed in the upper part of the compression space 25.

The fixed scroll 22 is attached to the frame 24 by bolts 28 at a flange 27 forming its outer peripheral edge.
fixed on top. The orbiting scroll 23 is supported on the frame 24 via a high pressure receiving ring 29, and is rotatably housed between the frame 24 and the fixed scroll 22. Further, the orbiting scroll 23 has a bearing portion 31 on a flat plate portion 30 forming the bottom portion of the lap 23a.

This bearing portion 31 is connected to an eccentric shaft portion 33 of a crankshaft 32 that is pivotally supported by the frame 24 . That is, the orbiting scroll 23 is connected to the crankshaft 3
2, and is configured to revolve around the center of the fixed scroll 22 with a constant eccentric radius.
By rotating the crescent-shaped compression space 25 in a fixed direction relative to the fixed scroll 22,
and laps 22a, 23a between the orbiting scroll 23 and the orbiting scroll 23.
It is configured to move along the spiral toward the center of the spiral while contracting. Note that 34 is an Oldham ring, which is configured to prevent the orbiting scroll 23 from rotating.

Further, an annular high pressure chamber 35 is provided between the fixed scroll 22 and the frame 24.

As shown in FIGS. 1 and 2, this high pressure chamber 35 is defined by the high pressure receiving ring 29 at the bottom and the flat plate 30 of the orbiting scroll 22 at the top. The high pressure chamber 35 is penetrated by bending the flat plate part 24 of the orbiting scroll 23 from the upper part thereof.
A communication hole 36 communicating with the compression space 25 is provided. The high pressure chamber 35 formed in this way is configured to introduce the refrigerant compressed in the compression space 25 through the communication hole 36 and reduce the thrust pressure of the orbiting scroll 23 that is applied in the direction of gravity with the resulting pressure. There is.

In addition, the orbiting scroll 23 and the high pressure receiving ring 29
Elastic seal rings 37a and 37b for sealing the high pressure chamber 35 are provided between the high pressure chamber 35 and the high pressure chamber 35.

Specifically, as shown in FIG. 1, a groove 38 is formed in the high pressure receiving ring 29 that partitions the bottom of the annular high pressure chamber 35 along its circumferential direction. This groove 3
Inner peripheral surface 39 that partitions both sides of 8 to face each other.
a and the outer circumferential surface 39b, a tapered inclined surface 40 is provided on the outer circumferential surface 39b so as to approach from the upper end to the lower end.
a, 40b are formed.

Inner and outer elastic seal rings 37a, 37b for sealing the high pressure chamber 35, respectively, are pressed into contact with the tapered inclined surfaces 40a, 40b by thrust pressure from above. The inner and outer elastic seal rings 37a, 37b each have a tapered contact surface 41a, 41b along the inclined surfaces 40a, 40b at one end thereof. In the illustrated example, a contact surface 41a is provided on the lower end side,
41b is formed.

By the way, in order for the elastic seal rings 37a and 37b to always seal the high pressure chamber 35, they must slide up and down along the inclined surfaces 40a and 40b that form the bottom of the high pressure chamber 35, following the vertical movement of the orbiting scroll 23. There must be.

For this purpose, elastic seal rings 37a, 37b are required.
requires, for example, a cutout section with a part cut out,
The ring diameter is configured to expand or contract in response to vertical sliding.

However, when a cutout is provided, there is a problem that gas leaks from the cutout.

The present invention aims to improve this point, and this will be described in further detail.

Inner and outer elastic seal rings 37a, 37b
A meshing portion 42 is formed in each of the rings to allow the ring diameter to be freely expanded or contracted. In this embodiment, in FIGS. 3 to 7, the outer elastic seal ring 37b
I will explain about it. As shown in the figure, the meshing part 42 is formed by separating a part of the outer elastic seal ring 37b and overlapping the separated ends 43a and 43b with each other in the circumferential direction of the ring, so that it is movable in the circumferential direction. They are configured to be interlocked.

In particular, the present invention, as shown in FIGS. 4 to 7,
Overlapping portion 43 forming the sliding surface of the meshing portion 42
, the contact surface 41b of the outer elastic seal ring 37b
The feature is that it is formed at the center in the radial direction.

Specifically, as shown in FIG. 4, if the inner diameter of the outer elastic seal ring 37b is R ₁ , the outer diameter is R ₂ , and the radius at the overlapping portion 43 of the meshing portion 42 is R ₃ , then the relationship of the following equation is obtained. Configure to meet the requirements.

R ₃ =(R ₁ +R ₂ )/2 Furthermore, if the angle between the ends 43a and 43c of the meshing portion 42 before the outer elastic seal ring 37b is assembled is θ, the configuration is such that this θ is 10° or less. do.

Further, as shown in FIG. 3, if the width of the lower end of the outer elastic seal ring 37b is t ₁ and the width of the contact surface 41b is t ₂ , then at least t ₁ ≦0.1t ₂ is established between them.

Note that the inner elastic seal ring 37a has an inner diameter of
Of course, the only difference is the outer diameter and the radius at the overlapped portion from the outer elastic seal ring 37b, and the other configuration of the engaging portion 42 and the same relational expressions as above hold true.

Next, the operation of this embodiment will be described.

As shown in FIG. 1, refrigerant that is being compressed or after compression is supplied from the compression space 25 through a communication hole 36 to a high pressure chamber 35 formed between the orbiting scroll 23 and the high pressure receiving ring 29.

The compressed refrigerant supplied to the high pressure chamber 35 acts as a force to push up the orbiting scroll 23 against the thrust pressure acting on it in the direction of gravity, and the gap S between the orbiting scroll 23 and the high pressure receiving ring 29 is cause At this time, the pressure contact force of the elastic seal rings 37a and 37b pressed between the high pressure receiving ring 29 and the orbiting scroll 23 changes, and the diameters of the elastic seal rings 37a and 37b expand and contract respectively due to the elastic force, and the high pressure receiving ring 29 Tapered inclined surfaces 40a, 40b of
While sliding, move upward to seal the gap S. That is, the seal rings 37a and 37b follow the orbiting scroll 23 and form the tapered inclined surface 40.
a, 40b, and can constantly seal the gap S created between the orbiting scroll 23 and the high pressure receiving ring 29. By constantly sealing this gap S, the orbiting scroll 23
The sealing performance between the high-pressure receiving ring 29 and the high-pressure receiving ring 29 is improved, and the amount of leakage of high-pressure gas within the high-pressure chamber 35 can be reduced as much as possible.

In particular, as shown in FIGS. 6 and 7, the engaging portions 42 formed on the elastic seal rings 37a and 37b
Since the overlapping portion 43 of the meshing portion 42 is formed at the center in the radial direction of the contact surfaces 41a, 41b with the high pressure receiving ring 29, the contact surfaces 41a, 41 of the meshing portion 42
Inclined surfaces 40a, 4 of the high pressure receiving ring 29 at b
Since a certain amount of contact area with the compressed refrigerant 0b can be secured, the compressed refrigerant meshing part 4 as shown by the broken line arrow in FIG.
Gas leak from 2 can be prevented as much as possible.

Further, as shown in FIG.
By setting the angle θ between 3a and 43c to 10 degrees or less to reduce the meshing portion 42 and increasing the contact area of the contact surfaces 41a and 41b as shown in FIG. 3, the sealing of the elastic seal rings 37a and 37b is improved. can significantly improve gender.

In this manner, the present invention eliminates recompression due to gas leakage of the compression element 21, and can improve its compression ability. Further, since the pressure within the high pressure chamber 35 is also maintained high, the thrust pressure of the orbiting scroll 23 can be sufficiently reduced.

Furthermore, simply by incorporating the elastic seal rings 37a and 37b between the orbiting scroll 23 and the high pressure receiving ring 29, the sealing performance can be improved and the assembling work becomes easy.

[Modified Embodiment] FIG. 8 shows a modified embodiment in which a high pressure chamber 35 is formed between the flat plate portion 30 of the orbiting scroll 23 and the frame 24. As shown in the figure, this high pressure chamber 35 has its upper part covered by an orbiting scroll 2.
The section is formed by an annular groove 38 provided in the flat plate part 30 of No. 3.

In this case, tapered inclined surfaces 45a and 45b are formed on the inner circumferential surface 44a and outer circumferential surface 44b that partition both sides of the groove 38, as in the above embodiment. In addition, inner and outer elastic seal rings 46a, 46
b has tapered contact surfaces 47a and 47b formed along the inclined surfaces 45a and 45b, respectively, on its upper side.

[Effects of the Invention] In summary, the present invention provides the following excellent effects.

(1) An elastic seal ring is provided in the high pressure chamber formed between the orbiting scroll and the frame, and a contact surface along the inclined surface formed in the high pressure chamber is formed on the elastic seal ring, so that it follows the orbiting scroll. The seal ring can be moved up and down, and the gap created between the back surface of the orbiting scroll and the high pressure receiving ring can be constantly sealed.

(2) The sealing performance between the high pressure receiving ring and the orbiting scroll is improved, so that leakage of high pressure gas from the high pressure chamber can be reduced as much as possible, and the performance of the compressor can be improved.

(3) Since the gas pressure in the high pressure chamber can be maintained high, the thrust pressure of the orbiting scroll can be sufficiently reduced.

(4) Sealing performance can be improved simply by incorporating an elastic seal ring, making the installation process easier.

[Brief explanation of drawings]

Fig. 1 is a sectional view showing the main parts of an embodiment of the present invention, Fig. 2 is a side sectional view showing the main parts of the compression element of a scroll compressor, and Fig. 3 is a sectional view showing the outer elastic seal ring. , FIG. 4 is a view taken along the - line in FIG. 3, FIG. 5 is a view taken along the - line in FIG. 3, FIG. 6 is a view showing the main parts of FIG. 4, and FIG. 8 is a diagram showing a modified embodiment, FIGS. 9 and 10 are diagrams showing the meshing state of a fixed scroll and an orbiting scroll, and FIG. 11 is a diagram showing a conventional scroll compressor. Diagram showing the main parts of the compression element, 1st
FIG. 2 is a sectional view showing the main part of FIG. 11. In the figure, 22 is a fixed scroll, 23 is an orbiting scroll, 24 is a frame, 35 is a high pressure chamber, 39
a, 44a are inner peripheral surfaces, 39a, 44b are outer peripheral surfaces,
40a, 40b, 45a, 45b are inclined surfaces, 41
a, 41b, 47a, 47b are contact surfaces, 37a,
37b, 46a, 46b are elastic seal rings, 4
3a, 43b, 43c are end portions, 42 is a meshing portion, 4
3 is an overlapping portion.

Claims (1)

[Claims] 1. In a scroll compressor in which an orbiting scroll and a fixed scroll are disposed in mesh with each other on a frame, and an annular high pressure chamber is formed between the frame and the orbiting scroll to introduce compressed refrigerant and reduce the thrust pressure of the orbiting scroll. , the inner peripheral surface and the outer peripheral surface of the annular high pressure chamber are formed into tapered inclined surfaces, an annular elastic seal ring having a tapered contact surface is provided along the inclined surfaces, and each elastic seal is provided with an annular elastic seal ring having a tapered contact surface. A part of the ring is separated and the separated ends are overlapped with each other in the circumferential direction of the ring and are movably engaged to form an engaging part that allows the ring diameter to be freely expanded or contracted, and the overlapping part of the engaging part is is located at the radial center of the contact surface of the ring.