JPS6179884A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To improve the sealing performance of a thrust receiving chamber and improve the faculty of a compressor by forming tapered groove onto a pressure receiving ring for receiving the thrust force of a swing scroll and forming a thrust pressure receiving chamber by arranging two elastic sealing rings into the groove. CONSTITUTION:The fluid pressure in a working chamber is introduced onto the back surface of a swing scroll 30 through a passage 36, and a pressure receiving ring 29 for supporting the thrust force of the swing scroll is arranged. A groove having the tapered inclined surface 40a and 40b is formed onto the pressure receiving ring 29, and elastic sealing rings 37a and 37b for forming a pressure receiving chamber are arranged in this groove. Therefore, even if the swing scroll moved vertically, the elastic sealing rings follow, and the leak of the fluid in the pressure receiving chamber is prevented, and the thrust force of the swing scroll can be supported stably.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a scroll compressor, and particularly relates to a scroll compressor [1] which can improve the sealing performance of a high pressure chamber formed between an orbiting scroll and a frame. -Relating to a compacting machine for a round shape.

[Technical Overview of the Invention and its Problems] Recently, there has been a tendency to adopt scroll compressors for compression in refrigeration cycles and the like. As shown in Figs. 9 and 10, this scroll compressor consists of a fixed scroll 1 and an orbiting scroll 2, which form spiral wraps 1a and 2a such as involutes, and are rotated by a fixed angle (180°). The fixed scroll 1 and the orbiting scroll 2 are engaged with each other in a rotatable position to form a closed crescent-shaped compressed space 3, and the orbiting scroll 2 is set at a certain eccentric distance e with respect to the center 01 of the fixed scroll 1.
By causing the refrigerant to revolve while maintaining the vortex, the compression space 3 is moved toward the center of the vortex (1) while being contracted, and the refrigerant is almost continuously sucked into the FF.

FIG. 11 shows a conventional depiction of the compression element 4 of a single-loop compressor. As shown in the figure, the outer peripheral edge 5 of the fixed scroll 1 is fixed to a frame 6 by pins 1 to 7 and the like. In addition, the orbiting scroll 2 that engages with the I-rule 1 is rotatably housed in the frame 6, and the back surface 8 on the opposite side of the wrap 2a slides on the high pressure receiving ring 9. It is supported by the frame 6 via.

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. Back side 8 of orbiting scroll 2
An annular high pressure chamber 12 for reducing the thrust pressure of the orbiting scroll 2 is formed between the high pressure receiving ring 9 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 .

YOA: , /I:r times A 4.1'+th bearing part 15 is formed approximately at the center of the back surface 8 of the scroll 2, and this bearing part 15 supports the eccentricity of the crankshaft 1G supported by the frame 6. Connected to the shaft part 17 'C11i+, rotation scroll 2
It is configured so that it can be driven in rotation.

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, the conventional compression element 4 configured as described above has a problem in that the sealing performance of the 1δ moving part between the high pressure receiving ring and the orbiting scroll 2 is low, and high pressure gas leaks T from the high pressure chamber 12. was there. That is, high pressure gas at pressure Pd is supplied to the high pressure chamber 12 from the communication hole 14, and the high pressure chamber 1
When the orbiting scroll 2 is pushed to the rear surface 8 of the orbiting scroll 2, a gap S is created between the high pressure receiving ring and the back surface 8 of the orbiting scroll 2. This is due to leakage. Therefore, the gas pressure in the high pressure chamber 12 is f
l(T" L), there was a problem that the thrust pressure of the orbiting scroll 2 could not be sufficiently reduced. Also, since the leaking high-pressure gas was refrigerant supplied from the compression space 3 during or after compression, This also causes a decrease in the compression capacity of the compressor.

[Object of the Invention 1] The present invention has been devised in view of the above-mentioned 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 1 The present invention provides an orbiting scroll and a fixed scroll that are interlocked with each other on a frame in order to achieve the following objectives.
An annular high-pressure chamber is formed between the frame and the orbiting scroll to introduce compressed refrigerant to reduce the thrust pressure of the orbiting scroll. The circumferential surface and the outer circumferential surface are formed into tapered inclined surfaces, and along the inclined surfaces are provided a J-shaped elastic seal ring having a tapered welding surface, and a part of each elastic seal ring is The separated ends are overlapped with each other in the circumferential direction of the ring and are movably engaged to form a meshing part that allows the ring diameter to be expanded and contracted, and the overlapped part of the meshing part is used as the contact part of the ring. It is configured to be located at the center of the surface in the i direction.

[Embodiment 1 of the Invention A preferred embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

As shown in FIG. 2, a fixed scroll 22 and an orbiting scroll 23 are provided on a frame 24, which constitute a scroll type pressure w6 and a separate compression element 21.

These fixed scroll 22 and orbiting scroll 23 are
Inpoly'-1, etc., each formed in the same shape
The fixed scroll 22 and the orbiting scroll 23 are
Then, the wraps 22a and 23a are inserted inwardly so that they can be freely engaged with each other, and a compressed space 25 that is closed in the shape of a moon is defined inside the engaged area. The compressed refrigerant in this compression space 25 is supplied to the compression element 2 through a discharge hole 26 formed in the upper part of the compression space 25.
1. It is designed to be discharged outside.

The fixed scroll 22 is fixed on the frame 24 by bolts 28 at seven flange 27 forming its outer peripheral edge. The orbiting scroll 23 is supported on the frame 24 via a high pressure receiving ring 29, and is rotatably housed between the frame 1124 and the fixed scroll 22. Further, the orbiting scroll 23 has a bearing portion 31 on a flat plate portion 30 forming the bottom of the wrap 23a.

These three bearings are a crank supported by the frame 24.
32 is connected to the eccentric shaft portion 33. The orbiting scroll 23 is driven to rotate by a crankshaft 32 and is configured to revolve around the center of the fixed scroll 22 with a constant eccentric radius. By doing so, the crescent-shaped compression space 25 is wrapped around the fixed scroll 22 and the orbiting scroll 23 22a.

23a 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.

Furthermore, there is an I between the fixed scroll 22 and the frame 24.
A high pressure chamber 35 shaped like a bell is provided.

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 by the flat plate part 30 of the hk scroll 22 at the top. 1n1
The first chamber 35 is provided with a communication hole 36 that extends from the upper part by bending the flat plate part 24 of the first rule 23 and communicates with the compression space 25.The high pressure chamber formed in this way 354, the refrigerant compressed by the compressed air 125 is introduced through the communication hole 36, and the thrust pressure of the rotating sphere 23 applied in the direction of gravity is reduced by the n force.

Further, an elastic seal ring 37 for sealing the high pressure chamber 35 is provided between the orbiting scroll 23 and the two high pressure receiving rings.
a and 37b are provided.

Specifically, as shown in FIG. 1, a groove 38 is formed along the circumferential direction of the two high pressure receiving rings that partition the bottom of the annular high pressure chamber 35. Tapered inclined surfaces 40a and 40b are formed on the inner circumferential surface 39a and outer circumferential surface 39b, which partition both sides of the groove 38, facing each other, so as to approach each other sequentially from the upper end to the lower end at an angle of /υ. Ru.

Inner and outer elastic seal rings 37a and 37b for sealing the high pressure chamber 35 are pressed into contact with these J-shaped inclined surfaces 40a and 40b from above by thrust pressure. The inner fill and outer elastic seal rings 37a, 37b have contact surfaces 41a, 41b with large tapers J along the inclined surfaces 40a, 40b at one end of the seal ring. In the illustrated example, a contact surface 41a is provided on the lower end side.

41b is formed.

By the way, the elastic seal rings 37a and 37b are one bird r'
E? In order to fully seal i35, turn the rotating shaft [1-L down along the inclined surfaces 40a and 40b that form the bottom of the high-pressure chamber 35 following the vertical movement of the rule 23 (E)+L. Must be.

For this purpose, the elastic seal rings 37a and 37b are
Requires a cutout by cutting out a part of the groove.

At 11 below! ! The ring diameter is expanded/contracted according to the FJI (111).

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

The present invention improves this point,
This will be explained in further detail.

The inner and outer elastic seal rings 37a and 37b are each formed with lζ meshing portions 42 that can freely expand and contract the μ ring diameter. In this embodiment, the outer elastic seal ring 37b will be explained in FIGS. 3 to 7. As shown in the figure, the engaging portion 42 is an outer elastic seal ring 37b.
The ends 43a, 43b are cut off and cut out.
are formed by overlapping each other in the circumferential direction of the ring, and are configured to mesh with each other while moving in the circumferential direction.

7! In accordance with the present invention, as shown in Figures 4 to 7,
The mating portion 43 forming the sliding surface of the engaging portion 42 is
'C' has a feature in that it is formed in the radial center of the contact surface 41b of the outer elastic seal ring 37b.

Specifically, as shown in FIG. 4, if the inner diameter of the outer elastic seal ring 37b is R1, the outer diameter is R2, and the radius at the overlapping portion 43 of the meshing portion 420 is R3, the following relationship is satisfied. Configure it so that

R3= (R+ +R2)/2 Also, if θ is 1% of the angle between the ends 43a and 43c of the joint portion 42 before the outer elastic seal ring 37b is assembled,
The configuration is such that this θ is 10° or less.

Furthermore, as shown in FIG. 3, an outer elastic seal ring 37b
The width of the lower end is 1+, the width of the contact surface 41b is 12,
The configuration is such that at least t1≦o and it2 are satisfied between these.

In addition, the inner elastic seal ring 37a has its inner diameter, outer i\,
The only difference is the radius at the overlapped portion from that of the outer elastic seal ring 37b, and the ground contact portion 42CF) t
i'+ and a relational expression similar to the above holds true t, L
There is a theory.

Next, the operation of the present embodiment 1ζ1 will be described.

As shown in FIG. 1, refrigerant that is being compressed or after compression is supplied to a high pressure chamber 35 formed between the orbiting scroll 23 and the high pressure receiving ring 29 through the communication hole 30 from the compression space 25.

The compressed refrigerant supplied to the high pressure chamber 35 is
acts on this as a force pushing it up against the thrust pressure acting in the direction of gravity, creating a gap S between the swing valve 1 and the high pressure receiving ring 29. On this occasion,
The elastic seal rings 37a and 37b, which are pressed between the two high pressure receiving rings and the orbiting scroll 23, change their pressure contact force and expand and contract in diameter due to the elastic force of the elastic seal rings 37a and 37b, and the high pressure receiving rings 29-j-bar-shaped inclined surface 4Q
a and 40b while moving upward to seal the gap S. That is, the seal rings 37a and 37b follow the orbiting scroll 233 to form a tapered inclined surface 40a,
40b and move up and down along the orbiting scroll 23
:! Eliminate the gap S that occurs between the I pressure receiving ring 29 7'c
Dishiru J can do it. This gap S is always 11”t
By being sealed, the sealing performance between the orbiting scroll 23 and the two high pressure receiving rings is improved, and leakage ω 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 overlapping portions 43 of the meshing portions 42 formed on the elastic seal rings 37a, 37b are in contact with the high pressure receiving rings 29 at their contact surfaces 41a, 41.
k) is formed at the radial center of the meshing portion 42.
The inclined surfaces 40a of the two high pressure receiving rings come down to the contact surfaces 41a and 41b.

Since a certain amount of contact area with the refrigerant 40b can be secured, gas leakage of the compressed refrigerant from the meshing portion 42 as shown by the broken line arrow in FIG. 6 can be prevented as much as possible.

J Saw, as shown in FIG.
E3.43Make the angle θ between C and 10 degrees or less and make the meshing part 14
2 and reduce the contact surface 4 as shown in Figure 3.
By increasing the contact area of 1D and 41b, the sealing performance of the elastic seal rings 37a and 37b can be greatly improved.

In this way, the recompression by the gas &11 in the compression system 21 increases and the compression capacity is improved.In addition, the pressure inside the high pressure chamber 35 is maintained high. , the thrust pressure of the orbiting scroll 23 can be sufficiently reduced.

Furthermore, by assembling the seal rings 37a and 37b between the swing frame 11-3 and the pressure receiving ring 29, the sealing performance can be improved and the assembling work can be facilitated.

1 Modified Embodiment j FIG. E3 shows a modified embodiment, in which 1r! An i-pressure chamber 35 is formed therein. As shown in the figure, the upper part of the high pressure chamber 35 is defined by an annular groove 38 provided in the flat plate portion 30 of the orbiting scroll 23. .

In this case, 1-bar-shaped inclined surfaces 45a and 45b are formed on the inner circumferential portion 44J] and the outer circumferential surface 44b that define one dimension on both sides of the groove 38, as in the above embodiment. Further, the inner and outer elastic seal rings 46a and 46b have a contact surface 47 along the inclined surfaces 45a and 45b on the -F side thereof.
a and 47b are formed respectively.

Effects of the Invention 1 In short, the present invention provides the following advantages.

+1) An elastic seal ring is provided on the i-1 royal ring formed between the Ia scroll frame and the 1
°! l Since the contact surface along the inclined surface formed at I-f/i'j' is formed on the elastic seal ring, the seal ring can be moved up and down by following the orbiting scroll, and the back surface of the orbiting scroll and the high pressure It is possible to constantly seal the gap between the receiving ring and the receiving ring.

+21. The seal f1 between the 111T receiving ring and the rotating scroll has been improved to further reduce the leakage of high pressure gas from the high pressure chamber and improve the performance of the compressor. It's a monkey.

(3) Since the gas pressure in the 8-pressure chamber can be maintained at 1α,
The thrust pressure of the orbiting scroll can be sufficiently reduced.3゜(・1) Since the sealing performance can be improved simply by incorporating a seal ring, its installation 1) can be easily performed.

[Brief explanation of drawings]

Fig. 1 is a sectional view showing the main part of an embodiment of the present invention, Fig. 2 is a side sectional view showing the main part of the compression element of the scroll type compression element, and Fig. 3 is a side sectional view showing the main part of the compression element of the scroll type compression element. ,Uraia
FIG. 4 is a view taken along the line A>TV-RV in FIG. 3, and FIG. 5 is a view taken along the V-V line in FIG. Figure 6 shows the main parts of Figure 4, Figure 7 shows the main parts of Figure 5, Figure 8 shows a modified example, and Figures 9 and 10 are fixed. 11 is a diagram showing the meshing state of the scroll and the orbiting scroll, FIG. 11 is a sectional view showing the main part of the compression element of a conventional scroll expansion pressure la machine, and FIG. 12 is a sectional view without showing the main part of FIG. be. In the figure, 22 is a fixed scroll, 23 is an orbiting scroll,
24 is a frame, 35 is a high pressure point, 30a and 44a1 are inner peripheral surfaces, 39b and 44b are outer peripheral parts, 1. Oa, 40
b, 45a, 45b are inclined surfaces, 41b, 47a, /17b are contact surfaces, 37a,
37b, 46a, 46bl and elastic seals)
'l 3a , /I 3 b , /13 has an end, 4
2 is a meshing portion, ・13[, 1・p is a mating portion. i, 'l u'l Applicant Toshiba Corporation Agent b i' 1! −[! samurai silk
Tani Iotto V Figure J 711E

Claims (1)

[Claims] In a scroll compressor, an orbiting scroll and a fixed scroll are provided on a frame in mesh with each other, and an annular high-pressure chamber is formed between the frame and the orbiting scroll to introduce compressed refrigerant to 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, and an annular elastic seal ring having a tapered contact surface is provided along the inclined surfaces, and
A part of each elastic seal ring is separated, and the separated ends are overlapped with each other in the circumferential direction of the ring and meshed movably to form a meshing part that allows the ring diameter to be freely expanded and contracted, and the meshing part A scroll compressor characterized in that the overlapping portion of the rings is located at the center in the radial direction of the contact surface of the ring.