JPH0584393B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a scroll compressor, and more particularly to a scroll compressor in which a high pressure receiving ring supporting an orbiting scroll is improved.

[Technical background of the invention and its problems] Recently, there has been a tendency to use scroll compressors for compressors such as refrigeration cycles. As shown in FIGS. 6 and 7, this scroll compressor has spiral wraps 1a, 2, such as an involute.
The fixed scroll 1 and the orbiting scroll 2 forming a are rotatably engaged with each other at a position where they are rotated by a certain angle (180°).
By forming a crescent-shaped compressed space 3 closed by the orbiting scroll 2 and the orbiting scroll 2, and revolving the orbiting scroll 2 while maintaining a constant eccentric distance e with respect to the center O ₁ of the fixed scroll 1, the above-mentioned The fluid is sucked and compressed substantially continuously by moving the compression space 3 toward the center of the vortex while contracting it.

FIG. 8 shows the conventional structure of the compression element 4 of a scroll compressor. As shown in the figure, the fixed scroll 1 has an outer peripheral edge 5 fixed to a frame 6 with bolts 7 or the like.
The orbiting scroll 2 engaged with the frame 6
The wrap 2a is rotatably stored inside the
The back surface 8 on the opposite side was in sliding contact with a high pressure receiving ring 9 and was supported by the frame 6 via this high pressure receiving ring 9.

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, and an upper surface 11 on which the orbiting scroll 2 slides has a high pressure chamber for reducing the thrust pressure. 1
2 was formed. The high pressure chamber 12 is configured to be supplied with compressed air 3 during or after compression 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, and the eccentric shaft portion 17 of the crankshaft 16 is supported by the frame 6.
The orbiting scroll 2 was configured to be connected to and driven to revolve. An Oldham ring 18 is interposed between the orbiting scroll 2 and the frame 6 to prevent the orbiting scroll 2 from rotating 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 large amount of high pressure gas leaking from the For this reason,
The gas pressure in the high pressure chamber 12 decreased, and the thrust pressure of the orbiting scroll 2 could not be reduced sufficiently. Furthermore, the lubricating oil on the sliding parts is blown away due to the leakage of high-pressure gas, so there is a problem in the lubricity of the sliding surfaces. Furthermore, since the leaking high-pressure gas is the compressed fluid supplied from the compression space 3 during or after compression, it has also been 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.

An object of the present invention is to provide a scroll compressor with improved sealing performance between an orbiting scroll and a high pressure receiving ring.

[Summary of the Invention] The present invention comprises a fixed scroll and an orbiting scroll each having a spiral wrap formed therein, which are rotatably engaged with each other with the wraps inside,
The peripheral edge of the fixed scroll is fixedly supported by a frame, and the orbiting scroll is rotatably housed within the frame, and the back surface of the orbiting scroll is interposed between the orbiting scroll and the frame and is always in operation. It is slidably supported by an annular high-pressure receiving ring forming an annular high-pressure chamber for reducing the thrust pressure of the orbiting scroll, and is attached to the sliding surface of the high-pressure receiving ring along the circumferential side of the high-pressure chamber. The above object is achieved by forming an annular seal ring groove and inserting the annular seal ring into the seal ring groove via an elastic member.

[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. 5, the scroll compressor 21 is supported by a frame 23 within a casing 22, has an electric element 24 at its lower part, and a compression element 25 at its upper part. compression element 2
Reference numeral 5 mainly consists of a fixed scroll 26 and an orbiting scroll 27, each of which has a spiral wrap 26a such as an involute formed in the same shape.
27a is erected. The fixed scroll 26 and the orbiting scroll 27 are rotatably engaged with each other with their wraps 26a, 27a inside, and their spiral wraps 26a, 27a
A compressed space 28 closed in a crescent shape by
is formed. A supply pipe 30 for supplying compressed fluid to the compression space 28 is connected to the side wall portion 29 of the casing 22, and the compressed fluid is discharged through a discharge pipe 31.

The fixed scroll 26 is provided with its outer peripheral edge 32 fixed to the frame 23, and the orbiting scroll 27 is rotatably housed within the frame 23 and has a flat plate portion 3 formed with a lap 27a.
A bearing part 35 is formed on the back surface 34 of the crankshaft 3 which is supported by the frame 23.
It is connected to the eccentric shaft portion 37 of No. 6. In other words, the orbiting scroll 27 is driven to rotate by the crankshaft 36, and the fixed scroll 27 rotates at a constant eccentric radius.
By rotating the orbiting scroll 27 in a fixed direction with respect to the fixed scroll 26, the crescent-shaped compression space 28 is formed into a lap 26a between the fixed scroll 26 and the orbiting scroll 27, 27a toward the center of the spiral while being compressed.

FIG. 1 shows a support structure for the fixed scroll 26 and the orbiting scroll 27. As described above, the fixed scroll 26 has a flange 38 formed on its peripheral edge 32 that is connected to the upper end surface 39 of the frame 23.
It is fixedly supported by bolts or the like at appropriate intervals.
On the other hand, the back surface 3 of the flat plate portion 33 of the orbiting scroll 27
A high pressure receiving ring 40 is interposed between the high pressure receiving ring 40 and the frame 23, and the orbiting scroll 27 is slidably supported by the high pressure receiving ring 40.

As shown in FIGS. 1 to 4, the sliding surface 41 of the high pressure receiving ring 40 is designed to reduce the downward thrust pressure on the orbiting scroll 27 caused by compressing the compressed fluid. Hyperbaric chamber 43
is formed. This high pressure chamber 43 has an annular groove 44
is formed as. And the orbiting scroll 27
The flat plate portion 33 is provided with a communication hole 45 for supplying compressed fluid to the high pressure chamber 43 during compression or after completion of compression. The communication hole 45 is formed such that one end faces the crescent-shaped compression space 28 formed by the fixed scroll 26 and the orbiting scroll 27, and the other end faces the high pressure chamber 43.

Further, a seal ring groove 40a is formed in the sliding surface 41 of the high pressure receiving ring 40 along the outer circumferential side and the inner circumferential side of the high pressure chamber 43. An O-ring 46 serving as an elastic member is inserted into the lower part of the seal ring groove 40a, and a seal ring 47 is inserted into the upper part via this O-ring 46.
The seal ring 47 is urged by the O-ring 46 and is configured to be in pressure contact with the orbiting scroll 27 at all times. That is, as shown in FIG. 4, the thickness t47 of the seal ring 47 and the O-ring 4
The thickness t46 of 6 is set such that the sum t47+t46 is larger than the depth h40a of the seal ring groove 40a and t47+t46>h40a, and when the seal ring 47 is attached, the end surface 48 of the seal ring 47 is connected to the high pressure receiving ring 40. sliding surface 41
is configured to be higher than the

Further, as shown in FIG. 1, an Oldham ring 49 is provided between the orbiting scroll 27 and the fixed scroll 26 for regulating the rotation of the orbiting scroll 27 and allowing it to revolve only when the orbiting scroll 27 is driven to orbit. is intervened. The fixed scroll 26 and the orbiting scroll 27 are provided with key grooves 50 and 51 on the outer circumferential sides of opposing surfaces, and a key portion 52 of the Oldham ring 49 is engaged with the key grooves 50 and 51. In addition, the keyway 5
0 and 51 are formed at positions where the keyway 50 on the fixed scroll side and the keyway 51 on the orbiting scroll side are at right angles to each other, and the illustrated cross section is a cross section at the right angle position.

Next, the operation of this embodiment will be described.

As shown in FIG. 5, the crescent-shaped compression space 28 formed by the fixed scroll 26 and the orbiting scroll 27 is erected in a spiral shape by the orbiting scroll 27 being driven to rotate. It is moved along the wraps 26a and 27a toward the center of the spiral while being contracted. As a result, the compressed fluid supplied from the supply pipe 30 is compressed in the compression space 28 and discharged from the discharge pipe 31.

At this time, as shown in FIG. 1, the orbiting scroll 27 is supported by its back surface 34 sliding on the sliding surface 41 of the high pressure receiving ring 40. In addition, in the high pressure chamber 43 formed on this sliding surface 41,
The fluid to be compressed is supplied from the compression space 28 through the communication hole 45 during compression or after completion of compression.
Therefore, the downward thrust pressure on the orbiting scroll 27 caused by the internal pressure of the compressed fluid is offset and reduced by the pressure from the high pressure chamber 40.

On the other hand, the seal ring 47 provided on the sliding surface 41 of the high-pressure receiving ring 40 is configured such that its end surface 48 is higher than the sliding surface 41. As a result, the O-ring 46 is elastically deformed and the surfaces thereof are aligned. In other words, the seal ring 47 is urged by the O-ring 46 so as to be constantly pressed against the back surface 34 of the orbiting scroll 27. Therefore, the sealing performance between the back surface 34 of the orbiting scroll 27 and the sliding surface 41 of the high pressure receiving ring 40 is improved, and the amount of leakage of high pressure gas in the high pressure chamber 43 is reduced as much as possible. .

Therefore, the compression element 4 is free from recompression due to gas leakage, and its compression ability is improved. Further, since the pressure within the high pressure chamber 43 is also maintained high, the thrust pressure of the orbiting scroll 27 can be sufficiently reduced.

In addition, the orbiting scroll 27 is connected to the fixed scroll 2
6, the clearance factor that affects the performance of the compression element 4 is reduced and stable performance can be obtained. There is no need for special measures to replenish the lubricating oil between the two, and there is no need for lubricating oil to be blown away due to leakage of high-pressure gas.

On the other hand, the Oldham ring 49 is attached to the fixed scroll 2.
6 and the orbiting scroll 27,
Wrap 26a of fixed scroll 26 and keyway 50
The precision of the positional relationship between the fixed scroll 26, the orbiting scroll 27, and the Oldham ring 49 becomes the precision of the combination of the fixed scroll 26, the orbiting scroll 27, and the Oldham ring 49, and the precision of the frame 23 becomes unnecessary, making assembly easy. Also, the orbiting scroll 27
The space on the back side becomes larger, and the outer diameter of the high pressure receiving ring 40 and the amount of eccentricity of the crankshaft 36 can be increased.

The seal ring 47 is preferably made of cast iron, Teflon, or the like.

Further, the compressed fluid may be introduced into the high pressure chamber 43 after completion of compression.

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

(1) Since the high pressure receiving ring is provided with a seal ring groove and the seal ring is inserted into the groove through an elastic member, the sealing performance between the high pressure receiving ring and the orbiting scroll can be improved.

(2) Thereby, leakage of high pressure gas from the high pressure chamber can be reduced as much as possible, and the capacity 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) Also, since the size of the high pressure chamber can be freely set, it can be adjusted according to the pressure characteristics of the compressor.
By optimally setting the size of the high pressure chamber, etc., it is possible to optimally set the thrust pressure reduction force by the high pressure chamber.

[Brief explanation of the drawing]

FIG. 1 is a side sectional view showing the structure of the compression element of a preferred embodiment of the scroll compressor of the present invention;
Figure 3 is a plan view of the high pressure receiving ring, Figure 3 is its side cross-sectional view, Figure 4 is a partial cross-sectional view showing the state of the seal ring when it is installed, Figure 5 is a broken perspective view of the scroll compressor, Figure 6 is FIG. 7 and FIG. 7 are views showing the meshing state of a fixed scroll and an orbiting scroll, and FIG. 8 is a side sectional view showing the structure of a compression element portion of a conventional scroll compressor. In the figure, 23 is a frame, 26 is a fixed scroll, 27 is an orbiting scroll, 26a, 27a are spiral wraps, 32 is a peripheral part of the fixed scroll,
34 is the back surface of the orbiting scroll, 40 is a high pressure receiving ring, 41 is a sliding surface of the high pressure receiving ring, 43 is a high pressure chamber, 45 is a seal ring groove, 46 is an elastic member, 4
7 is a seal ring.

Claims (1)

[Claims] 1 A fixed scroll and an orbiting scroll, each having a spiral wrap, are engaged with each other so as to be able to rotate with the wraps inside, and the peripheral edge of the fixed scroll is fixedly supported on a frame, and the orbiting scroll is attached to the frame. The back of the rotating scroll is
The high pressure receiver is slidably supported by an annular high pressure receiving ring that is interposed between the orbiting scroll and the frame and forms an annular high pressure chamber for constantly reducing the thrust pressure of the orbiting scroll during operation. Scroll type compression characterized in that an annular seal ring groove is formed on the sliding surface of the ring along the circumferential side of the high pressure chamber, and the annular seal ring is inserted into the seal ring groove via an elastic member. Machine.