JPH084670A - Seal mechanism of scroll type compressor - Google Patents

Abstract

PURPOSE:To provide the seal mechanism of a scroll type compressor in which even if the seal members are thermally expanded, the sealing function of the seal members is not impaired. CONSTITUTION:Grooves 15, 16 are formed on the end surfaces of the spiral walls 12, 14 of a fixed scroll 1 and a movable scroll 9 respectively. Spiral tip seals 17, 18 are made of nylon resins, and the inner end part 28 thereof is constitute so as to have a wider width. These tip seals 17, 18 are housed inside the respective grooves 15, 16 for securing the sealing performance of a compression chamber 100. The clearances of the tip seals 17, 18 with regard to the grooves 15, 16 are provided much in the clearances 202, 203 in the spiral direction as compared with the clearances 201 in the width direction. In the clearances 202, 203 in the spiral direction, the clearance 203 on the outside end part is made larger than the clearance 202 on the inner end part 24 for each of the spiral walls 12, 14. On the other hand, the clearances 201 in the width direction are provided so as to have a given width along the nearly entire circumference of the spiral outer circumference.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a seal mechanism for ensuring the tightness of a compression chamber in a scroll type compressor.

[0002]

2. Description of the Related Art Generally, in a scroll compressor, a fixed scroll and a movable scroll each having a base plate and a spiral wall are meshed with each other at the spiral wall to form a compression chamber therebetween. Then, the movable scroll is revolved around the axis of the fixed scroll, so that the compression chamber is moved to the center side and the gas is compressed.

In order to ensure the airtightness of the compression chamber, grooves are formed on the end faces of the spiral walls of the fixed scroll and the movable scroll along the direction of extension of the spiral, and the grooves of the scrolls facing each other are formed in the grooves. A spiral seal member that contacts the substrate is housed.

However, as described above, the compression chamber is moved from the outer portion toward the central portion while decreasing the capacity. Therefore, the pressure in the compression chamber becomes highest at the center, the center becomes hot, and the seal member thermally expands, so that the clearance between the seal member and the groove disappears. Therefore, the seal member may protrude from the groove due to thermal expansion. In that case, the protruded portion is damaged by friction with the substrate, and the sealing function is deteriorated. Further, the seal member lacking and separated becomes a foreign matter, and the compression function is deteriorated, and in the worst case, it leads to a failure of the compressor. Further, if the seal member protrudes from the groove, the frictional force between the seal member and the scroll substrate that comes into contact with the seal member increases, and a large torque is required to rotate the movable scroll, resulting in energy loss.

In order to solve the above problems, there is one disclosed in Japanese Utility Model Laid-Open No. 62-95101. That is, as shown in FIG. 5, the width of the tip seal 35 as a seal member is narrow near the inner end 36 of the spiral wall and wide near the outer end 37. That is, as described above, the clearance 4 in the width direction between the tip seal 35 and the groove 38 near the inner end 36 where the temperature becomes high.
01 is the outer end portion 37 of the tip seal 35 with a small thermal expansion.
This is to secure a large amount in comparison with the above, and to obtain an optimum seal form at the time of thermal expansion.

[0006]

However, since the tip seal 35 has a spiral shape whose total length is longer than its width,
During thermal expansion, the amount of expansion in the spiral direction is larger than that in the width direction. However, in the one disclosed in the above publication, the clearance 401 in the width direction and the clearance 402 in the spiral direction of the tip seal 35 are formed substantially constant near the inner end 36 of the spiral wall. Therefore, even if the clearance 401 in the width direction of the tip seal 35 is brought to an optimum state due to thermal expansion, the clearance 402 in the spiral direction with a large amount of expansion disappears, and further, the tip end portion of the tip seal 35 has a groove 38. Since it sometimes protruded from the inside, the conventional problems could not be solved.

Further, since the clearance 401 in the width direction is large, there is a possibility that the high gas pressure in the compression chamber on the scroll center side may leak gas through the clearance 401 and reduce the compression efficiency.

Furthermore, since the compression chamber on the center side is intermittently formed by the revolution of the movable scroll, the pressure at the center of the scroll also changes intermittently. For this reason, the inner end portion of the tip seal 35 may swing in the groove 38 in a swinging manner, leading to a decrease in the durability of the tip seal 35.

In addition, considering the high pressure in the center of the scroll, the tip seal 35 has
If the width of the inner end portion of the tip seal 35 is narrowed, the durability will be deteriorated as in the above case.

The present invention has been made by paying attention to the problems existing in the above-mentioned prior art, and the object thereof is not to impair the sealing function of the seal member even if the seal member is thermally expanded, and to improve efficiency. It is an object of the present invention to provide a seal mechanism of a scroll type compressor that can perform effective compression.

[0011]

In order to solve the above problems, in the invention of claim 1, a groove is formed in the end face of the scroll wall of both scrolls along the extension direction of the scroll wall, and in each groove. A scroll-shaped sealing member that comes into contact with the substrates of the scrolls that face each other is housed, and the clearance between the groove and the sealing member is made larger in the spiral direction than in the width direction of the sealing member.

According to the second aspect of the invention, the inner end portion of the seal member is formed wider than the other portions.
According to the third aspect of the invention, the clearance in the spiral direction is larger on the outer end side than on the spiral inner end side.

According to the fourth aspect of the invention, the clearance in the width direction between the seal member and the groove is formed to have a substantially constant width along the spiral shape. In the invention of claim 5, the clearances in the width direction and the spiral direction almost eliminate the gap between the seal member and the groove when the seal member expands, and
The size is such that the expansion operation of the seal member is allowed.

In the invention of claim 6, the clearance on the inner end side in the spiral direction is 1.5 to 1 with respect to the clearance in the width direction.
It is 0 times. In the invention of claim 7, the clearance on the inner end side in the spiral direction is about three times as large as the clearance in the width direction.

In the invention of claim 8, the clearance on the outer end side in the spiral direction is 2 to 30 times the clearance in the width direction. In the invention of claim 9, the clearance on the outer end side in the spiral direction is about 10 times the clearance in the width direction.

In the invention of claim 10, the seal member is made of resin.

[0017]

According to the first aspect of the invention having the above-mentioned structure, the clearance between the groove and the seal member is larger in the spiral direction than in the width direction of the seal member. For this reason, even if the seal member expands during operation of the compressor, it is possible to allow it and ensure an appropriate clearance, and it is possible to prevent deterioration of the sealing function. Further, it is possible to prevent the compression performance of the compressor from being deteriorated due to the seal member protruding from the groove.

According to the second aspect of the invention, since the vicinity of the inner end portion of the seal member is formed wide, the sealing function between the opposing substrates can be ensured even in the central portion of the scroll having a high pressure. Also excellent in durability.

In the invention of claim 3, for example, since a large clearance in the spiral direction is provided on the outer end side of the spiral, expansion in the spiral direction of the portion occupying most of the seal member is concentrated on the outer end side. Can also tolerate that expansion.

According to the fourth aspect of the invention, the widthwise clearance between the seal member and the groove is formed to have a substantially constant width along the spiral shape. Therefore, the expansion operation of the seal member is smoothly performed.

According to the inventions of claims 5 to 9, the relationship between the seal and the groove is optimized when the seal member is expanded,
The desired sealing function is exhibited. According to the tenth aspect of the invention, since the seal member is made of resin having a small wear coefficient, the sliding resistance between the seal member and the substrate can be suppressed low, and efficient rotation of the movable scroll can be secured.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment embodying a seal mechanism of a scroll type compressor according to the present invention will be described below with reference to FIGS.

As shown in FIG. 1, a fixed scroll 1 made of an aluminum material also serves as a center housing, and a front housing 2 and a rear housing 3 are fixed to both front and rear end surfaces thereof. The rotary shaft 4 is rotatably supported in the front housing 2 by a bearing 5, and an eccentric shaft 6 is provided at the inner end of the rotary shaft 4 so as to project therefrom. The bush 7 is rotatably supported by the eccentric shaft 6, and a bearing 8 is fitted to the outer periphery of the bush 7.

Movable scroll 9 made of aluminum material
Is rotatably supported by the bush 7 via the bearing 8 and is prevented from rotating about its own axis by a well-known restriction mechanism 10. When the rotating shaft 4 is rotated, the orbiting scroll 9 is revolved around the axis of the rotating shaft 4 by the eccentric shaft 6 via the bush 7 and the bearing 8.

As shown in FIG. 1, the fixed scroll 1
Is a spiral wall 1 that is integrally erected on the substrate 11 and its inner peripheral surface.
2 is provided. Similarly, as shown in FIGS. 1 and 2, the movable scroll 9 also includes a substrate 13 and a spiral wall 14 that is integrally provided upright on the inner peripheral surface of the substrate 13. The scrolls 1 and 9 are meshed with each other on the scroll walls 12 and 14, and the end faces of the scroll walls 12 and 14 in the axial direction are opposed to the substrates 13 and 11 of the scrolls 9 and 1 facing each other.

The inner end portions 24 of both spiral walls 12, 14 are thicker than other portions in order to ensure strength. Inner edge 2
5 is formed in a substantially arc shape. The grooves 15 and 16 are formed on the end faces of the spiral walls 12 and 14 of the scrolls 1 and 9 so as to extend in the direction of extension of the spiral shape, and the inner end portion 2 thereof.
6 is wide, and the inner edge 27 is formed in an arc shape. The spiral tip seals 17 and 18 as seal members are made of nylon resin and have a similar shape to the grooves 15 and 16. Therefore, the inner ends 28 of the tip seals 17 and 18 are wide, and the inner end edge 29 is formed in an arc shape. The tip seals 17 and 18 are housed in the respective grooves 15 and 16 having a shape corresponding to the tip seals 17 and 18, and the outer surfaces of the tip seals 17 and 18 are in pressure contact with the substrates 13 and 11 of the opposing scrolls 9 and 1. This seals between the end faces of the spiral walls 12 and 14 and the substrates 13 and 11. And with this seal,
Substrates 11 and 13 of both scrolls 1 and 9 and spiral wall 12,
A compression chamber 100 surrounded by 14 is formed.

The pressure receiving ring 30 is arranged between the movable scroll 9 and the front housing 2, and
On the other hand, it receives a compression reaction force acting in the axial direction. The compression reaction force acting on the pressure receiving ring 30 is received by the front housing 2.

As shown in FIG. 1, the suction chamber 19 is formed between the outer peripheral portions of the spiral walls 12 and 14 of the scrolls 1 and 9, and the refrigerant gas is sucked into the inside thereof. The discharge hole 20 is formed in the base plate 11 of the fixed scroll 1, and the compression chamber 1
00 is communicated with the discharge chamber 21 in the rear housing 3.
The discharge valve 22 is arranged at the outer end of the discharge hole 20, and its open position is regulated by the retainer 23.

In this embodiment, as shown in FIGS. 3 and 4, the tip seals 17 and 18 and the grooves 15 and 1 are formed.
6, the clearance 200 in the spiral direction is larger than that in the clearance 201 in the width direction.
02 and 203 are largely secured. Further, the clearances 202 and 203 in the spiral direction are secured larger on the outer end side than on the inner end side. Since the clearance 201 in the width direction is provided with a substantially constant width over the entire circumference of the spiral, the groove 1 of the tip seals 17 and 18 is provided.
Good fit for 5 and 16. The clearance 202 on the inner end side in the spiral direction with respect to the clearance 201 in the width direction
Is about 1.5 to 10 times, preferably about 3 times. The clearance 203 on the outer end side in the spiral direction is 2 to 30 times, preferably about 10 times, the clearance 201 in the width direction.

Next, the operation of the seal mechanism of the scroll compressor having the above construction will be described. When the rotary shaft 4 of the compressor is rotated, the movable scroll 9 is revolved around the axis of the rotary shaft 4 due to the eccentric rotation of the eccentric shaft 6. This causes the refrigerant gas to flow from the suction chamber 19 to the scrolls 1,
It is taken into the compression chamber 100 between 9 and. As the movable scroll 9 revolves, the compression chamber 100 becomes
2 and 14 are moved from the outer peripheral side to the central side, and the volume is gradually reduced to perform the compression action. Therefore, the refrigerant gas is compressed in the compression chamber 1
00 is gradually compressed, and the discharge valve 22 is pushed open from the discharge hole 20 and discharged into the discharge chamber 21.

During operation of the compressor, both scrolls 1, 9
The pressure in the compression chamber 100 in between increases gradually as it moves from the outer peripheral side of the spiral walls 12, 14 to the center side. Therefore, the temperature on the center side becomes high, and the tip seals 17 and 18 and the spiral walls 12 and 14 are thermally expanded.

Chip seal 1 made of nylon resin
Due to the difference in expansion coefficient between Nos. 7 and 18 and the spiral walls 12 and 14 made of aluminum material, the chip seals 17 and 18 are inserted into the groove 1
Inflated relative to 5, 16. At this time, groove 1
Since the clearance 201 in the width direction is formed with a substantially constant width between the chips 5, 16 and the chip seals 17, 18, the chip seals 17, 18 smoothly expand. That is, the clearance 201 in the width direction is equal to the tip seal 1
It is preferable that the minimum value that absorbs the thermal expansion of the tip seals 17 and 18 and does not hinder the thermal expansion of the tip seals 17 and 18 so that the gaps between the grooves 7 and 18 and the grooves 15 and 16 are almost eliminated. Therefore, the gas pressure on the center side is prevented from escaping to the outer peripheral side through the space between the outer side surfaces of the chip seals 17 and 18 in the width direction and the inner side surfaces of the grooves 15 and 16 in the width direction.
Good compression efficiency can be maintained.

The amount of thermal expansion of the tip seals 17, 18 is larger in the spiral direction than in the width direction due to the spiral shape. In this embodiment, since the clearance 202 in the spiral direction is larger than the clearance 201 in the width direction as described above, expansion of the tip seals 17 and 18 in the spiral direction is sufficiently permitted. Due to the expansion in the spiral direction, the inner end edges 29 of the tip seals 17 and 18 are brought into close proximity or contact with the inner end edges 27 without being pressed against the inner end edges 27 of the grooves 15 and 16.

Therefore, the tip seals 17 and 18 are provided in the groove 1.
Tip seal 1
The tip seals 17 and 18 can maintain a good sealing function with almost no gap between the grooves 7 and 18 and the grooves 15 and 16. Further, since there is almost no gap between the tip seals 17 and 18 and the grooves 15 and 16, even if a compressive load is applied to the tip seals 17 and 18 from inside and outside alternately, the tip seals 17 and 18 are not grooved. Fifteen, one
The delusion similar to the swinging movement is not performed in the position 6, and the durability of the tip seals 17 and 18 can be improved.

As shown in FIGS. 2 and 3, the tip seals 17 and 18 are wider in the vicinity of their inner ends 28 than in other parts. Therefore, the tip seal 1
7 and 18 are expanded in both spiral directions with the vicinity of the neck portion indicated by an arrow 300 in the drawing as a boundary. Therefore, the arrow 300
A large amount of expansion in the spiral direction is generated in a portion located near to the outer end portion side, that is, a portion occupying most in the tip seals 17 and 18, and this large extension is propagated to the outer end portion side, and the spiral direction in the outer end portion side is increased. Will be absorbed by the clearance 203. In this embodiment, the clearance 203 in the spiral direction at the outer end is larger than the clearance 202 in the spiral direction at the inner end. Therefore, it is possible to effectively absorb the expansion of the tip seals 17 and 18 and ensure an appropriate sealing function.

Further, in this embodiment, since the inner ends 28 of the tip seals 17 and 18 are formed thicker, they can withstand the high pressure in the compression chamber 200 that has moved to the center side, and a good seal can be obtained. Function can be maintained.

Moreover, since the tip seals 17 and 18 are made of nylon resin having a small wear coefficient, the sliding resistance between the opposing substrates 13 and 11 can be kept low, and the movable scroll 9 can rotate efficiently. Can be secured.

The present invention is not limited to the above embodiments, and can be carried out in the following modes without departing from the spirit of the present invention. (1) The clearance 201 in the width direction of the tip seals 17, 18 is made larger on the inner end side than on the outer end side of the tip seals. That is, unlike the above embodiment, the clearance 201 in the width direction is not provided uniformly, but the clearance 201 in the width direction at a portion (around the inner end portion) having a large thermal expansion is increased. (2) In the above embodiment, the tip seals 17 and 18 were made of nylon resin, but the tip seals 17 and 18 are not limited to this, and the tip may be made of other synthetic resin material such as polyether ether ketone or polyphenylene sulfide. The seals 17 and 18 may be configured. (3) The present invention is embodied in a tip seal having a constant width from the inner end portion to the outer end portion.

[0039]

According to the invention of claim 1 having the above structure, even if the seal member expands during operation of the compressor, the seal member can be tolerated and a proper clearance can be secured, and the deterioration of the sealing function can be prevented. You can Further, it is possible to prevent the compression performance of the compressor from being deteriorated due to the seal member protruding from the groove. According to the second aspect of the present invention, it is possible to maintain good contact with the opposing substrate even in the central portion of the scroll where the pressure is high, and the durability of the seal is improved.

According to the third aspect of the invention, even if the expansion in the spiral direction is concentrated on the outer end side, the expansion can be allowed. According to the invention of claim 4, the expanding operation of the sealing member can be smoothly performed, which contributes to the improvement of the sealing property.

According to the fifth to ninth aspects of the invention, when the seal member is inflated, an optimum seal shape is obtained and a desired sealing function is exhibited. According to the tenth aspect of the invention, the sliding resistance between the substrate and the substrate can be kept low, and efficient rotation of the movable scroll can be secured.

[Brief description of drawings]

FIG. 1 is a view showing an embodiment embodying the present invention and is a vertical sectional view of a compressor.

FIG. 2 is a front view of a movable scroll.

FIG. 3 is a partial enlarged view showing a spiral inner end portion of a fixed scroll and a movable scroll.

FIG. 4 is a partially enlarged view showing a spiral outer end portion of a fixed scroll and a movable scroll.

FIG. 5 is a view showing a conventional sealing mechanism, and is a partially enlarged view showing an inner end portion and an outer end portion of a scroll wall of a scroll.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Fixed scroll, 9 ... Movable scroll, 11 ... Fixed scroll substrate, 12 ... Fixed scroll spiral wall, 1
3 ... Movable scroll substrate, 14 ... Movable scroll spiral wall, 15 ... Grooves in which seal member is accommodated, 16 ... Groove in which seal member is accommodated, 17 ... Chip seal as seal member, 18 ... As seal member Tip seal, 20
0 ... Clearance between seal member and groove, 201 ... Width clearance, 202 ... Inner end side spiral direction clearance, 203 ... Outer end side spiral direction clearance.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yasushi Watanabe 2-chome Toyota-cho, Kariya city, Aichi stock company Toyota Industries Corporation (72) Inventor Tetsuhiko Fukunuma 2-chome Toyota-cho, Kariya city, Aichi stock (72) Inventor, Yasushi Suzuki, 1-1, Showa-cho, Kariya, Aichi Prefecture, Nihon Denso Co., Ltd. (72), Inventor, Naoyuki Miyagawa, 1-1, Showa-cho, Kariya, Aichi Prefecture, Nippon Denso Within the corporation

Claims (10)

[Claims] 1. A fixed scroll having a base plate and a spiral wall, and a movable scroll having a base plate and a spiral wall mesh with each other at the spiral walls to form a compression chamber between the scrolls, thereby fixing the movable scroll to the fixed scroll. In the scroll compressor, which revolves around the axis of to move the compression chamber from the outer peripheral side to the center side of the spiral wall to perform the gas compression action, the scroll wall end surfaces of both scrolls are A groove is formed along the extension direction of the spiral wall, and a spiral seal member that comes into contact with the opposing scroll substrate is housed in each groove, and the clearance between the groove and the seal member is the same. A scroll type compressor seal mechanism that is larger in the spiral direction than in the width direction. 2. The seal mechanism according to claim 1, wherein an inner end portion of the seal member is formed wider than other portions. 3. The seal mechanism according to claim 1, wherein a clearance in the spiral direction is larger on the outer end side than on the spiral inner end side. 4. The seal mechanism according to claim 1, wherein the widthwise clearance between the seal member and the groove is formed to have a substantially constant width along the spiral shape. 5. The clearance in the width direction and the spiral direction is
5. The seal mechanism according to claim 1, which has a size such that a gap between the seal member and the groove is almost eliminated when the seal member is expanded and the expansion operation of the seal member is allowed. 6. The clearance on the inner end side in the spiral direction is 1.5 to 10 times the clearance in the width direction.
Sealing mechanism described in. 7. The seal mechanism according to claim 5, wherein the clearance on the inner end side in the spiral direction is about three times as large as the clearance in the width direction. 8. The seal mechanism according to claim 5, wherein the clearance on the outer end side in the spiral direction is 2 to 30 times the clearance in the width direction. 9. The sealing mechanism according to claim 5, wherein the clearance on the outer end side in the spiral direction is about 10 times the clearance in the width direction. 10. The seal member is made of resin.
9. The sealing mechanism according to any one of 9.