JP2922343B2 - Scroll machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multifunction floating seal for a scroll type machine, particularly a scroll type compressor having an axially flexible scroll member.

[0002]

2. Description of the Related Art A typical scroll-type machine is a orbiting scroll member having a spiral wing on one surface, a non-orbiting scroll member having a spiral wing meshed with the spiral wing on one surface,
There is provided orbiting driving means for orbiting the orbiting scroll member relative to the non-orbiting scroll member so as to form the above-mentioned spiral wings with a fluid pocket whose volume changes.

In order to increase mechanical efficiency, it is important that the tip of each scroll member be sealingly engaged with the end plate of the other scroll member to minimize fluid leakage therebetween. One approach that has been used to achieve this is to not use tip sealing (tip sealing is very difficult to assemble and often creates reliability problems). ), A method in which one scroll member is moved and urged toward the other scroll member in the axial direction. This method, of course, requires a seal to isolate the energizing fluid at the desired pressure. For this reason, there is a constant need in the field of scroll machines for improved axial biasing techniques and, consequently, improved seals.

[0004]

Accordingly, it is a primary object of the present invention to provide an improved seal which is relatively simple in construction, easy to assemble and service, and which effectively provides the desired composite sealing function. An object of the present invention is to provide a scroll-type machine having a mechanism.

[0005]

SUMMARY OF THE INVENTION The present invention includes a orbiting scroll member 40 and a non-orbiting scroll member 58 inside a sealed outer shell 10 , in which one of the scroll members is moved relative to the other scroll member. The present invention relates to a scroll-type machine, particularly a scroll-type compressor, which is supported and provided so as to enable axial movement within a limited range. One surface of one of the scroll members (preferably the non-orbiting scroll member 58 ) has a groove 78 (preferably annular) for pressure application on one surface thereof, that is, the inside thereof. A concave groove for urging the one scroll member toward the other scroll member by a pressure fluid is provided. A pressure fluid supply means 82 for supplying a pressure fluid (preferably a fluid at a pressure intermediate the suction pressure and the discharge pressure) is provided in the concave groove 78 .
Sealing means 80 is provided in the groove to isolate the pressure fluid in the groove from the discharge pressure area and the suction pressure area. This sealing means is in particular a first seal 108, 116; 20 which isolates the pressure fluid in the groove from the discharge pressure area.
4,214; 306 and a second isolated from the suction pressure area
Is preferably an integral seal assembly with the seals 108; According to the present invention, the scroll fluid is moved and biased relatively to each other by the pressure fluid in the groove 78 to promote the sealing of the blade tip. The present invention in which the groove 78 is isolated from the discharge pressure area and the suction pressure area by the integral seal assembly 80 having the first and second seals as described above, The structure of the sealing means for sealing the groove is simple, and its installation and inspection are easy. No sealing means mentioned above
The seal assembly 80 has the following sandwich structure.
That is, the first annular member 100; 200; 300 and the second
Having annular members 118; 216, 222; 310;
First seals 108, 116; 204, 214; 3
06 and the second seal 108; 208;
And a structure that is fixedly fastened between the second annular members.
It is preferable to configure the above. Tightening the first and second seals
The fixation penetrates the second annular member 118;
The plurality of pillars 102; 302 are connected to the first annular member 100;
300, the free ends 123;
It can be performed by that writing, first annular member
200 is provided with an annular rib 202 and a second annular portion.
The material was arranged on the inner peripheral surface side and the outer peripheral surface side of the rib 202.
It is composed of two annular parts 216 and 222,
The free end of the annular rib 202 is provided at a plurality of positions in the circumferential direction,
To hold the annular part and the first and second seals.
It can also be done by swallowing. The first and such
And a second annular member between which the first and second seals are formed.
Machine as first and second clamp members for clamping and tightening
Works.

According to the present invention, a fluid leakage passage 150 is provided between the concave groove 78 and the stationary member 16 in the outer shell 10 so as to communicate the discharge pressure region and the suction pressure region. A third seal 112; 21 provided on the sealing means 80 and engaged with the stationary member 16 ;
8; closed by 312 . This third seal is
The aforementioned second annular member 118; 216, 222; 31
0 can be provided integrally. The stationary member is outside
The inside of the shell 10 is divided into a suction pressure region and a discharge pressure region.
Partition wall 16 having a discharge hole 75 for discharge fluid.
Preferably, the partition wall 16 is a partition wall. The above-described fluid leakage passage 150 , when opened, allows the fluid at the discharge pressure to flow directly to the suction pressure region, thereby preventing a highly depressurized state from occurring in the suction pressure region. The present invention provides a third seal for closing such a fluid leakage passage, a first seal for isolating the pressure fluid in the recess from the discharge pressure area and a second seal for isolating the pressure fluid from the suction pressure area. Provided in the means. Then, the sealing means 80 is inserted into the concave groove 78.
In the suction pressure region, a high pressure reduction state occurs in the suction pressure region, the pressure difference between the discharge pressure region and the suction pressure region causes the sealing means to be in contact with the stationary member. It automatically moves out of engagement to allow direct fluid flow from the discharge pressure region into the suction pressure region. This sealing means is of a combined sealing function which provides three types of sealing, is particularly sensitive to the pressure ratio of the scroll machine, especially in the case of reduced pressure, such as occurs when the machine is reversed or the suction path is blocked. It has been found that it provides excellent protection. In the above-mentioned reduced pressure state, the sealing means eliminates one sealing function and allows the discharge gas to flow directly to the suction pressure region of the suction pressure. Thereby, both scroll members 40, 58
A high degree of reduced pressure at the inlet side of the compressor is avoided, which could over-draw and damage each other. In particular, arcing or burning out of the motor protector connection pin, which often occurs under a constant decompression condition, is prevented.

[0007] The sealing means according to the invention also provides a certain protection against temperature in certain applications, especially in electric compressors which use suction gas to cool the motor. This is because the sealing means causes a fluid leak from the high pressure side to the low pressure side when a pressure difference that is substantially higher than the pressure difference expected at the time of the mechanical design is generated. This leakage of the discharged fluid to the compressor suction side causes a reduction in the discharge amount of the machine, and a reduction in the flow of the cooling gas causes heat to accumulate in the outer shell of the compressor. Stopped the machine. In certain applications given the present features of the sealing means according to the present invention, it may be caused by loss of the filling working fluid, or by shutting off the condenser fan in the refrigeration system, or also by excessive discharge pressure (for any reason). Some protection against possible over-discharge gas temperatures will be provided. All of these undesired conditions cause the scroll machine to operate at a higher pressure ratio than planned at the time of machine design in a fixed volume ratio.

Other features and advantages of the present invention will be clearly understood from the following description with reference to the accompanying drawings.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention can be applied to any type of scroll type machine. Hereinafter, an embodiment applied to a scroll type compressor shown in FIG. 1 will be described. Generally speaking, this refrigerant compressor has a cylindrical outer shell 10 with a cap 12 welded to the upper end, and the cap 12 can have a normal discharge valve (not shown) inside. It has a refrigerant discharge pipe joint 14. Other components attached to the outer shell 10 include a horizontal partition wall 16 whose peripheral end is welded to the outer shell 10 at the same point as the cap 12, and a plurality of points which are appropriately attached to the outer shell 10. There is a main bearing housing 18 and a suction gas inlet pipe joint 17 communicating with the inside of the outer shell 10.

A motor stator 20 having a square cross-sectional shape but having chamfered corners in an arc shape is provided by press-fitting in the outer shell 10. The flat surface between the chamfered corners of the stator 20 directs the flow of lubricating oil from the top to the bottom in the outer shell 10 between the stator and the outer shell as indicated by reference numeral 22. Provides a facilitating passage. The crankshaft 24 having the eccentric crankpin 26 at the upper end is connected to the main bearing housing 1.
8 and a second bearing (not shown) in the lower bearing box so as to be rotatably supported. Crankshaft 24 has a relatively large diameter conventional oil pumping or pumping hole (not shown) in its lower end, which is inclined radially outwardly at the upper end of crankshaft 24. The hole 30 communicates with a hole 30 having a smaller diameter. The lower portion of the outer shell 10 is filled with lubricating oil as usual, and the pump hole at the lower end of the crankshaft 24 is
And the bore 30 acts as a secondary pump, delivering lubricating oil to all of the various parts of the compressor that require lubrication.

The crankshaft 24 includes the stator 20, a winding 32 penetrating through the stator 20, and the crankshaft 2.
The rotor 34 is rotationally driven by an electric motor having a rotor 34 press-fitted on the rotor 4 and has one or more counterweights 36. An ordinary type of motor protector 35 is provided close to the winding 32, and when the motor exceeds a normal temperature range, the motor is stopped by the protector 35.

An annular flat thrust receiving surface 38 is provided on the upper surface of the main bearing housing 18.
An orbiting scroll member 40 having an end plate 42 is disposed on the upper side. The end plate 42 has a conventional spiral wing 44 on its upper surface, and has an annular flat thrust surface 46 on its lower surface, and a cylindrical hub 48 having a plain bearing 50 therein from the thrust surface 46. The drive bush 52 is rotatably disposed in the hub 48 so as to protrude downward.
The crankpin 26 protrudes into the second hole 54. The crank pin 26 has a flat surface (hereinafter, not shown) on a part of the outer peripheral surface which engages with a flat surface formed on a part of the inner peripheral surface of the hole 54, thereby allowing the applicant to possess the same. U.S. Pat. A radially flexible drive mechanism such as that shown in US Pat. No. 4,877,382 is provided.

The spiral wing 44 is meshed with a non-orbiting spiral wing 56 which forms a part of the non-orbiting scroll member 58. Supported in any suitable manner that allows for axial movement. Although this support system is irrelevant to the present invention, it is as follows in the illustrated example. That is, the non-orbiting scroll member 58 has a plurality of support bosses 60 intermittently arranged in the circumferential direction, only one of which is shown, and each support boss 60 has a flat upper surface 62 and an axial hole 6.
The sleeve 66 is slidably fitted in the hole 64, and the sleeve 66 is fixed to the main bearing housing 18 by a bolt 68 as shown in the figure. The bolt 68 has a head with a flat lower surface 70, and the non-orbiting scroll member 5
8 is limited by the engagement of the upper surface 62 of the boss with the lower surface 70 of the bolt head. The movement of the non-orbiting scroll member 58 in the opposite direction is limited by the lower wing tip surface of the wing 56 of the scroll member 58 engaging with the flat upper surface of the end plate 42 of the orbiting scroll member 40.

The non-orbiting scroll member 58 has a discharge passage 72 disposed at the center thereof. The discharge passage 72 communicates with a concave groove 74 having an open upper end, and the concave groove 74 defines a hole 75 in the partition wall 16. Through this, it communicates with a discharge muffling chamber 76 defined by the cap 12 and the partition wall 16. On the upper surface of the non-orbiting scroll member 58, an annular concave groove 78 having two parallel concentric peripheral wall surfaces is formed, in which the annular floating seal 80 is movable in the axial direction. It is fitted airtight. The floating seal 80 separates the inner bottom of the annular groove 78 from the gas at the suction pressure and the discharge pressure, and separates the inner bottom from the intermediate fluid pressure source (the intermediate pressure fluid formed between the spiral blades 44 and 56) by the passage 82. (Within a movable fluid pocket). Therefore, the non-orbiting scroll member 58 moves toward the orbiting scroll member 40 in the axial direction with a force based on the discharge pressure applied to the central portion of the non-orbiting scroll member 58 and a force based on the intermediate fluid pressure applied to the inner bottom surface of the annular groove 78. Inspired by
This axial biasing and various techniques for supporting the non-orbiting scroll member 58 so that it can move axially within a limited range are described in the aforementioned U.S. Pat. 4,877,32
8 is described in detail.

The relative rotation between the scroll members 40 and 58 is prevented by a conventional Oldham coupling having a ring 82. The ring 82 is provided in the non-orbiting scroll member 52 so as to be radially opposed to each other. A first pair of keys 84 (only one shown) slidably fitted into a pair of slots 86 (only one shown) and radially opposed in orbiting scroll member 40 And a second pair of keys (not shown) which are slidably fitted in a pair of slots (not shown) provided as described above.

In the compressor, the inflowing suction gas is supplied to the deflection plate 19.
It is preferably of the “low side” type, which allows the motor to cool down partly into the outer shell. As long as there is a proper flow of the return intake gas, the motor is kept within the desired temperature range. However, when the flow is interrupted, the cooling is stopped and the motor protector 35 is activated to stop the motor.

The structure of the scroll compressor outlined above is already known or is the subject of other patent applications of the applicant. Hereinafter, several embodiments of a novel multifunctional floating seal embodying the principle of the present invention will be described in detail.

FIG. 1-3 shows a floating seal 80 according to a first embodiment of a coaxial sandwich structure. The floating seal 80 has an annular substrate 100 formed by casting aluminum or the like. The substrate 100 includes a plurality of upstanding integral projections 102, each having an enlarged base 104, arranged at equal intervals. An annular gasket 106 made of an epoxy resin-coated fiber gasket material is provided on the substrate 100, and the gasket 106 has a plurality of equally spaced holes for receiving the base 104. On the upper surface of the gasket 106 is disposed a pair of equal (lower packing) lower lip seals 108 which are normal (uncompressed) and which are glass (about 5%) filled PTFE.
PT which is (polytetrafluoroethylene) and may optionally contain 5% by weight of MoS2 (molybdenum disulfide)
It is made from FE. The seal 108 is also provided on the base 10.
It has a plurality of holes for receiving 4 at equal intervals. An annular spacer plate 110, which may be made of stamped steel, is provided on the upper surface of the seal 108,
This spacer plate 110 has annular grooves 112 on the upper and lower surfaces,
114 and a plurality of holes for receiving the base 104 at even intervals. On the upper surface of the spacer plate 110, a pair of upper lip seals (lip packings) 116, which are made of the same material as the lip seals 108 and are flat in a normal state, are provided. An annular upper seal plate 118 having equally spaced holes and an annular rim 120 located within annular groove 112.
Are concentrically held. The seal plate 118, which may be made of gray cast iron, has a flat sealing lip or lip seal 122 protruding upwardly around its inner peripheral edge. Floating seal 80
Are fixed to each other by swaging the end of each projection 102 as indicated by reference numeral 123.

The whole floating seal or seal assembly 80 viewed as the seal having different three, i.e. the inner diameter seal 124 and the outer径密seal portion 128 as shown in FIG. 1 top
The end seal 130 is obtained. The inner diameter sealing portion 124 is obtained between the inner peripheral edge of the lip seal 108 and the inner peripheral wall surface of the annular groove 78, and the other inner diameter sealing portion 126 is formed by the lip seal 116.
And the inner peripheral wall surface of the annular groove 78. These inner diameter seal portions 124 and 126 isolate the intermediate pressure fluid at the inner bottom of the annular groove 78 from the discharge pressure fluid within the groove 74. The outer diameter sealing portion 128 is obtained between the outer peripheral edge of the lip seal 108 and the outer peripheral wall surface of the annular groove 78, and
The intermediate pressure fluid at the inner bottom is isolated from the suction pressure fluid in the outer shell 10. The top seal 130 is a lip seal 122
And the seal assembly obtained between the annular wear-resistant ring 132
The fluid at suction pressure is isolated from the fluid at discharge pressure in a direction across the top end of 80 . The wear-resistant ring 132 is made of cast iron or the like, and is attached to the partition wall 16 by an appropriate bonding means so as to surround the hole 75 of the partition wall 16. A separate wear-resistant ring 132 for sealing the top end
Instead, the lower surface of the partition wall 16 surrounding the hole 75 may be partially hardened by nitriding or carbonitriding.

The diameter of the top seal 130 is selected so that a positive upward sealing force is applied to the floating seal assembly 80 under normal compressor operating conditions, ie, in the presence of a normal pressure differential. I have. Therefore, when an excessive pressure difference occurs, the floating seal assembly 80 is urged downward by the discharge pressure, whereby a high-pressure side discharge gas is formed between the seal assembly 80 and the partition wall 16. fluid
It can leak directly to the low pressure side intake gas region through the leak passage 150 . If this leakage is so great that the motor cooling due to the suction gas flow is impaired as a result of the hot leaked and discharged gas, the motor protector 35 is activated and the motor is stopped. The width of the top seal 130 is such that the unit pressure applied to the seal itself (i.e., between the lip seal 122 and the ring 132) is greater than the normal discharge pressure to ensure a tight seal. Is set.

FIG. 4-7 also shows a floating seal according to a second embodiment of the coaxial sandwich structure, which comprises an annular substrate 200 made of aluminum or the like. An upright annular rib 202 is integrally formed on the substrate 200. 5 on the substrate 200
% Glass and PT filled with 5% molybdenum disulfide
An outer lip seal 208 made of the same material as the lower inner lip seal 204 made of FE is provided, and these lip seals 204 and 208 are respectively provided.
It has frustoconical resilient sealing lips 206,210. An annular metal separating plate 212 is disposed on the inner lip seal 204 in the annular rib 202, and the separating plate 212 is finely divided in order to increase the mechanical engagement strength with the seals 204 and 214. It has an upper surface and a lower surface with irregularities. Lip seals 204 and 208 are provided on the separation plate 212.
A pair of mutually identical annular upper lip seals 214 made of the same material are provided, and the lip seals 214 are also held in position by the annular ribs 202. On the lip seal 214, an upper seal plate 216 having a flat sealing lip 218 protruding upward is provided around the inner peripheral end. The lip seal 214 has a frustoconical resilient sealing lip 220 and the sealing plate 21.
6 is made of cast iron. Outer lip seal 208
Is held in position by an annular metal ring 222, and the entire seal assembly is secured by swaging the upper end of annular rib 202 at a plurality of spaced apart locations as indicated at 224.

This seal assembly also has three different seals, namely the inner diameter seals 226, 228, as shown in FIG.
And the outer diameter sealing portion 230 and the top end sealing portion 232 are obtained. The inner diameter sealing portion 226 is formed between the inner peripheral edge of the lip seal 204 and the inner peripheral wall surface of the annular groove 78, and the other inner diameter sealing portion 2 is formed.
28 is obtained between the inner peripheral edge of the lip seal 214 and the inner peripheral wall surface of the annular groove 78. These inner diameter sealing portions 226, 22
8 is a groove 74 for transferring fluid at an intermediate pressure in the inner bottom of the annular groove 78.
Isolate from fluid at discharge pressure within. The outer diameter sealing portion 230 is formed between the outer peripheral edge of the lip seal 208 and the outer peripheral wall surface of the annular groove 78, and isolates the intermediate pressure fluid in the inner bottom of the annular groove 78 from the suction pressure fluid in the outer shell 10. Top sealing part 2
32 is obtained between the lip seal 218 and an annular wear ring 132 surrounding the hole 75 in the partition wall 16, isolating suction pressure fluid from discharge pressure fluid in a direction across the top end of the seal assembly. I do. The diameter and width of the top end sealing portion 232 are set as in the first embodiment.

FIGS. 8-10 show a floating seal according to a third embodiment of the coaxial sandwich structure, which is an annular substrate 30 made of aluminum or the like.
0 is provided. The substrate 300 is a ring-shaped rib 3 having a low height.
There are a plurality of equally spaced, integral upstanding projections 302 protruding from the head. Substrate 30 in annular rib 304
On the top surface of the zero is disposed a pair of normally flat inner lip seals 306 made of PTFE with suitable filling. Substrate 30 in annular rib 304
On the top surface of the 0 there is provided a pair of equally flat annular outer lip seals 308 made of the same material as the lip seal 306. These two pairs of lip seals 306 and 308 are concentrically positioned by an annular rib 304 and are clamped and restrained by an annular upper seal plate 310 having a plurality of equally spaced holes through which the projections 302 are inserted. . The seal plate 310, preferably made of gray cast iron, forged steel or powdered metal, has a flat sealing lip 312 protruding upwardly around its inner peripheral edge. The entirety of the seal assembly is denoted by reference numeral 3.
It is fixed by swaging the end of each projection 302 as indicated by 14.

The seal assembly as a whole is also different.
Seed seals, i.e. inner diameter seals 31 as shown in FIG.
6. The outer diameter sealing portion 318 and the top end sealing portion 320 are obtained. The inner diameter sealing portion 316 is formed between the inner peripheral edge of the lip seal 306 and the inner peripheral wall surface of the annular groove 78, and isolates the intermediate pressure fluid in the inner bottom of the annular groove 78 from the discharge pressure fluid in the concave groove 74. The outer diameter sealing portion 318 is obtained between the outer peripheral edge of the lip seal 308 and the outer peripheral wall surface of the annular groove 78, and
8 isolates the intermediate pressure fluid at the inner bottom from the suction pressure fluid in the outer shell 10. The top sealing part 320 is the lip seal 31
2 and an annular wear ring 132 surrounding the hole 75 in the partition wall 16 to isolate fluid at suction pressure from fluid at discharge pressure in a direction across the top end of the seal assembly. The diameter and width of the top seal 320 are set as in the first embodiment.

In order to prevent excessive intermediate pressure from being created between the inner and outer seals of the floating seal in a liquid slugging situation that could damage the high pressure seal, reference is made to FIG. A suitable vent passage may be provided at 125 and as shown at 316 in FIG.

[Brief description of the drawings]

FIG. 1 is a scroll-type machine that uses fluid pressure to axially move and bias a non-orbiting scroll member toward an orbiting scroll member, embodying principles of the present invention. 3 is a partially omitted longitudinal sectional view of FIG.

FIG. 2 is an enlarged longitudinal sectional view showing the floating seal according to the first embodiment forming a part of the machine of FIG. 1 in a relaxed state;

FIG. 3 is a cross-sectional view taken along line 2-2 of FIG. 2;

FIG. 4 is a longitudinal sectional view similar to FIG. 1, showing a floating seal according to a second embodiment;

FIG. 5 is an enlarged longitudinal sectional view of a part of the floating seal shown in FIG. 4;

FIG. 6 is an enlarged longitudinal sectional view showing the floating seal shown in FIG. 4 in a relaxed state, and a cut surface is along a line 6-6 in FIG. 7;

FIG. 7 is a transverse sectional view taken along the line 7-7 in FIG. 6;

FIG. 8 is a partial longitudinal section similar to FIG. 1, showing a floating seal according to a third embodiment;

9 is an enlarged vertical sectional view showing the floating seal shown in FIG. 8 in a relaxed state.

FIG. 10 is a transverse sectional view taken along the line 10-10 in FIG. 9;

[Explanation of symbols]

 Reference Signs List 10 outer shell 16 partition wall 18 main bearing box 40 orbiting scroll member 44 spiral blade 56 spiral blade 58 non-orbiting scroll member 60 support boss 66 sleeve 68 bolt 72 discharge passage 75 opening 76 discharge muffler chamber 78 annular groove 80 floating seal (seal) Assembly) 82 Passage 100 Substrate 102 Projection 108 Lip seal 110 Spacer plate 116 Lip seal 118 Upper seal plate 122 Sealing lip (lip seal) 124, 126 Inner diameter sealing portion 128 Outer diameter sealing portion 130 Top end sealing portion 132 Wear-resistant ring 200 Substrate 202 Annular rib 204 Inner lip seal 206 Outer lip seal 212 Separator plate 214 Lip seal 216 Upper seal plate 218 Sealing lip 226, 228 Inner diameter sealing section 230 Outer diameter sealing section 232 Top sealing section 300 Substrate 30 Protrusions 306 inner lip seal 308 outside lip seal 310 upper seal plate 312 sealing lip 316 inside diameter seal 318 outside 径密 seal portion 320 apical seal

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-63-80088 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04C 18/02 311

Claims (53)

(57) [Claims] 1. A scroll-type machine comprising: (a) a sealed outer shell (10) , (b) disposed within said outer shell (10) and having a first spiral wing (44) on one surface. orbiting scroll member (4 having a)
0) , (c) disposed in the outer shell (10) and on one surface,
The second spiral blade meshed with the first spiral blade (44)
( D) a non-orbiting scroll member (58) having (56) ; and (d) an orbiting scroll member (40) orbiting relative to the non-orbiting scroll member (58) to form the two spiral wings (44, 56) described above. Turning drive means (20 , 24 , 26 , 34) for forming a fluid pocket whose volume sequentially changes between the suction pressure area and the discharge pressure area; and (e) one of the two scroll members
( F) supporting means (18 , 66 , 68) for supporting the (58) so as to be able to move in the axial direction within a limited range relative to the other scroll member (40); An annular groove (78) having an outer peripheral wall surface and communicating with the suction pressure area and the discharge pressure area, respectively;
Wherein one of the scroll members is formed on one surface of one of the scroll members (58) , and the one of the scroll members is changed to the other by a pressure fluid inside.
Annular groove (78) which moves biasing (40) facing, by supplying pressure fluid in (g) said annular groove (78),
A pressure fluid supply means (82) in which both scroll members (40, 58) are relatively biased to move toward each other;
And (h) an integral annular seal assembly (80) disposed within the annular groove (78) , the first seal (108, 116; ) sealingly engaging the inner peripheral wall surface . 20
4, 214; 306) and a second seal (108; 208; 308) which sealingly engages the outer peripheral wall so that the pressure fluid in the groove (78) is discharged and suctioned. Assembly (8)
0) A scroll-type machine comprising: 2. The scroll-type machine according to claim 1, wherein said inner peripheral wall surface and said outer peripheral wall surface are concentric cylindrical surfaces. 3. The scroll machine according to claim 1, wherein the scroll machine is a compressor, and the pressure fluid is a working fluid compressed from a suction pressure to a discharge pressure. 4. The scroll-type machine according to claim 3, wherein the pressure fluid has an intermediate pressure between the suction pressure and the discharge pressure. 5. The scroll machine according to claim 1, wherein said seal assembly (80) is axially floatable within said annular groove (78) . 6. The seal assembly (80) comprises a first annular member (100; 200; 300) and a second annular member.
(118; 216, 222; 310) , and the first seal and the second seal described above.
Of the first annular member (100; 20)
0; 300) and the second annular member (118; 216, 22).
2; 310) between the substantially flat inner annular lip seals (108, 116; 204, 214;
306) and outer annular lip seal (108; 20).
8; 308) . 7. The scroll-type machine according to claim 6, wherein the inner lip seal and the outer lip seal are integrated with each other (108) . 8. The inner lip seal (204,
214; 306) and the outer lip seal (208; 30).
The scroll-type machine according to claim 6, wherein ( 8) and ( 8) are separate from each other. 9. Each of the lip seals (108, 11)
6; 204, 208, 214; 306, 308) are made from filled polytetrafluoroethylene. 10. The polytetrafluoroethylene,
10. The scroll-type machine according to claim 9, wherein the scroll-type machine is filled with glass. 11. The scroll machine of claim 10 wherein said glass loading is about 5% by weight. 12. The method according to claim 12, wherein the polytetrafluoroethylene is
10. The scroll-type machine according to claim 9, which is filled with molybdenum disulfide. 13. The method according to claim 13, wherein the filling amount of the molybdenum disulfide is about 5%.
13. The scroll-type machine according to claim 12, which is in weight percent. 14. The lip seal (108, 116;
7. The scroll-type machine according to claim 6, wherein each of said scroll-type machines has a flat shape without stress. 15. The lip seal (204, 208,
7. A scroll-type machine according to claim 6, wherein each of said 214) has a slightly conically curved peripheral edge without stress. 16. The inner and outer lip seals (1).
08, 116; 306, 308) , respectively. 17. The inner annular lip seal (1)
08, 116; 204, 214) , wherein the scroll type machine is provided with a plurality of annular spacers (110; 212) interposed therebetween. 18. The inner lip seal (204 , 2 ) wherein said spacer (212) is made of a relatively rigid material.
The scroll machine according to claim 17 which is formed in one having an uneven surface portion for engaging with 14). 19. The first annular member (100; 30).
0) protrudes along the axial direction of the second annular member (1).
18; 310) a plurality of penetrating the intermittently arranged pillar portions in the circumferential direction (102; 302) in which scroll machine according to claim 6, comprising a. 20. Free end of said post (102; 302)
(123; 314) to the first annular member (10
0; 300) and the second annular member (118; 310) between the lip seals (108, 116; 306, 308).
20. The scroll-type machine according to claim 19, further comprising: 21. The inner lip seal and the outer lip seal are integrally formed with each other to form the pillar portion (1).
20. The scroll-type machine according to claim 19, wherein 02) extends through the integrated lip seal (108) . 22. The inner lip seal (30)
6) and the outer lip seal (308) are separate from each other, and the column (302) projects between the inner lip seal (306) and the outer lip seal (308). Item 19. The scroll-type machine according to Item 19. 23. The first annular member (200) is provided with an annular rib (202) projecting in the axial direction, and the second annular member is connected to the inner peripheral surface side of the annular rib (202). Two annular parts (216, 22 ) arranged on the outer peripheral surface side
The scroll machine according to claim 6 that is configured to consist of 2). 24. The annular rib (202) tightens and holds the two annular parts (216, 222) and the first and second annular members (200, 21).
6,222) between the lip seals (204,208,
24. The scroll-type machine according to claim 23, wherein the scroll-type machine is set in a plurality of places spaced apart in the circumferential direction so as to tighten and hold ( 214) . 25. The inner lip seal (10)
8. The scroll-type machine according to claim 6, wherein a plurality of the scroll machines are provided. 26. The seal assembly (80) is brought into contact with the fluid in the annular groove (78) on one side in the axial direction, and the other side in the axial direction of the seal assembly (80) is in contact with the other side in the axial direction. Between the stationary member (16 ) in the outer shell (10) ,
Wherein the discharge pressure region and the suction pressure region is provided fluid leakage path for communicating (150), said stationary member (16)
An annular third seal (122; 218; 312) for sealingly engaging the fluid leakage passage (150 ).
The scroll-type machine according to claim 6 which is provided on the other surface in the axial direction of the seal assembly (80). 27. The third seal (122; 218;
27. The scroll machine of claim 26, wherein 312) is integrally provided on the second annular member (118; 216, 222; 310) of the seal assembly (80) . 28. The scroll machine of claim 26, wherein the seal assembly (80) is axially floatable within the annular groove (78) . 29. The stationary member includes a fluid discharge hole (75).
A partition wall (16) having the third seal
(122; 218; 312) with the fluid discharge hole (75).
27. The scroll-type machine according to claim 26, wherein the scroll-type machine is arranged to surround the scrolling machine. 30. The scroll-type machine according to claim 29, wherein a hardening valve seat (132) surrounding the fluid discharge hole (75 ) is provided on the partition wall (16) . 31. The fluid discharge hole (75) , wherein the valve seat is connected to the fluid discharge hole (75).
Member attached to the partition wall (16) surrounding the partition wall (16)
31. The scroll machine of claim 30, wherein the scroll machine is formed by (132) . 32. The fluid discharge hole (75) , wherein the valve seat is connected to the fluid discharge hole (75).
31. The scroll machine according to claim 30, wherein the partition wall (16) is formed by locally hardening the partition wall (16) in a region surrounding the scroll wall. 33. The scroll-type machine according to claim 1, wherein said one scroll member is said non-orbiting scroll member (58) . 34. The seal assembly (80) is brought into contact with the fluid in the annular groove (78) on one side in the axial direction, and the other side in the axial direction of the seal assembly (80) is in contact with the other side in the axial direction. Between the stationary member (16 ) in the outer shell (10) ,
Wherein the discharge pressure region and the suction pressure region is provided fluid leakage path for communicating (150), said stationary member (16)
An annular third seal (122; 218; 312) for sealingly engaging the fluid leakage passage (150 ).
2. The scroll-type machine according to claim 1, wherein the seal assembly (80) is provided on the other axial side of the seal assembly (80) . 35. A scroll type compressor comprising: (a) a sealed outer shell (10) , (b) disposed in the outer shell (10) , and having a first spiral blade ( Orbiting scroll member (4 ) having
0) , (c) disposed in the outer shell (10) and on one surface,
The second spiral blade meshed with the first spiral blade (44)
( D) a non-orbiting scroll member (58) having (56) ; and (d) an orbiting scroll member (40) orbiting relative to the non-orbiting scroll member (58) to form the two spiral wings (44, 56) described above. (E) one of the scroll members of the orbiting drive means (20 , 24 , 26 , 34) for forming a fluid pocket whose volume decreases from the suction pressure region to the discharge pressure region;
(58), supporting means for supporting to allow axial movement of the ranges that are relatively limited with respect to the other scroll member (40) (18,66,68), of (f) both scroll members One of the scroll members
A concave groove (78) formed on one surface of the (58) for urging the one scroll member (58 ) toward the other scroll member (40) by a pressure fluid therein;
Grooves (78) communicating with the suction pressure area and the discharge pressure area, respectively; (g) provided between the groove (78) and the stationary member (16) in the outer shell (10); fluid leakage passage for providing communication between the region and the suction pressure region (150), by supplying a fluid of the intermediate pressure between the suction pressure and the discharge pressure in (h) above the groove (78), both scroll members (4
0,58) are relatively pressure fluid supply means to be moved biased in another direction (82), and (i) sealing means disposed on the groove (78) in (8
0) wherein the first seal (108, 116; 20 ) isolates the pressure fluid in the groove (78) from the discharge pressure area.
4, 214; 306) , a second seal (108; 2 ) for isolating the pressure fluid in the concave groove (78) from the suction pressure area.
08; 308) and a sealing means (8 ) having a third seal (122; 218; 312) for engaging with the stationary member (16 ) and blocking the fluid leak passage (150).
0) A scroll compressor comprising: 36. The sealing means (80) comprising:
Along the axial direction within (78) , the first seal (10
36. The scroll compressor according to claim 35, wherein the scroll compressor is floatable while maintaining the function of the second seal (108; 208; 308) and the function of the second seal (108; 208; 308) . 37. The sealing means (80) comprising a first annular member (100; 200; 300) and a second annular member.
(118; 216, 222; 310) , and the first seal and the second seal described above.
Of the first annular member (100; 20)
0; 300) and the second annular member (118; 216, 22).
2; 310) between the substantially flat inner annular lip seals (108, 116; 204, 214;
306) and outer annular lip seal (108; 20).
8; 308) . The scroll compressor according to claim 35, comprising: 38. The scroll compressor according to claim 37, wherein said inner lip seal and said outer lip seal are formed integrally with each other (108) . 39. The inner lip seal (20)
4,214; 306) and outer lip seal (208;
308) are separate from each other. 40. The inner lip seal (10)
38. The scroll compressor according to claim 37, wherein a plurality of (8 , 116; 204, 214) are provided with an annular spacer (110; 212) interposed therebetween. 41. The first, second, and third seals described above.
(108, 116, 122; 204, 208, 214,
218; 306, 308, 312 ) are all annular, and the diameter of the third seal (122; 218; 312) is increased by a positive sealing force against the third seal under normal operating conditions of the compressor. 36. The scroll compressor of claim 35 selected to participate. 42. The third seal (122; 218;
43. The scroll compressor according to claim 41, wherein the width of 312) is set such that a unit pressure applied to the third seal in the sealing direction is larger than a normal discharge pressure. 43. The method according to claim 43, wherein the sealing means (80) is provided with the groove.
(78) can float axially within the sealing means (8 ) when a pressure reduction occurs at the fluid inlet (17) of the compressor.
36. The scroll compressor of claim 35, wherein 0) moves axially to release the function of said third seal (122; 218; 312) . 44. A multi-function seal assembly, comprising: (a) an annular first lip seal (108, 116; 204, 204) adapted to sealingly engage a first cylindrical surface .
214; 306) , (b) an annular second lip seal (108; 208; 308) adapted to sealingly engage a second cylindrical surface concentric with said first cylindrical surface ; ) The first lip seal (108, 116;
204, 214; 306) and the second lip seal (10
8; 208; 308) and the first and second clamp members (100, 118; 200, 216,
222; 300 , 310) , and (d) coupled to one of the clamping members (118; 216, 222; 310) and sealing against a generally flat annular sealing surface (132). Annular third seal (122; 21)
8; 312) A multifunctional seal assembly comprising: 45. The first, second, and third seals described above.
(108, 116, 122; 204, 208, 214,
218; 306, 308, 312) are concentrically arranged with respect to each other. 46. A in which the first and second cylindrical surface described above forms an inner circumferential wall surface and the outer peripheral wall surface of the annular groove (78), said annular sealing surface (132) of said annular groove ( 7
45. The device according to claim 44, wherein the device is disposed on the side opposite to the bottom of the item ( 8).
Multifunctional seal assembly. 47. A scroll type compressor comprising: (a) a sealed outer shell (10) , (b) disposed in the outer shell (10) , and having a first spiral wing ( Orbiting scroll member (4 ) having
0) , (c) disposed in the outer shell (10) and on one surface,
The second spiral blade meshed with the first spiral blade (44)
( D) a non-orbiting scroll member (58) having (56) ; and (d) an orbiting scroll member (40) orbiting relative to the non-orbiting scroll member (58) to form the two spiral wings (44, 56) described above. (E) one of the scroll members of the orbiting drive means (20 , 24 , 26 , 34) for forming a fluid pocket whose volume decreases from the suction pressure region to the discharge pressure region;
(58), supporting means for supporting to allow axial movement of the ranges that are relatively limited with respect to the other scroll member (40) (18,66,68), of (f) both scroll members One of the scroll members
A concave groove (78) formed on one surface of the (58) for urging the one scroll member (58 ) toward the other scroll member (40) by a pressure fluid therein;
Grooves for respectively communicating to the suction pressure region and a discharge pressure region (78), by supplying a fluid of the intermediate pressure between the suction pressure and the discharge pressure in (g) above the groove (78), both scroll members (4
And (h) a pressure fluid supply means (82) to be biased to move relative to each other relative to each other; and (h) an integral seal assembly (80 ) disposed within said groove (78) . ) , The first seal (108, 1) isolating the pressure fluid in the groove (78) from the discharge pressure area.
16; 204, 214; 306) and the concave grooves (7
8) a seal assembly having a second seal (108; 208; 308) for isolating the pressure fluid therein from the suction pressure area ;
(80) A scroll compressor comprising: 48. A scroll compressor according to claim 47, wherein said groove (78) is formed in a non-orbiting scroll member (58) . 49. The first seal (204, 214; 49) .
306) and the second seal (208; 308)
48. The scroll compressor of claim 47, wherein the scroll compressors are separate components. 50. The non-orbiting scroll member (58) has a discharge port (72) , and one of the first and second seals (108, 116; 204, 21).
The scroll compressor according to claim 47, wherein said scroll compressor ( 4; 306) is disposed so as to surround said discharge port (72) . 51. The groove (78) is formed in the discharge port (7).
Non-orbiting scroll member is formed on one of the annular surrounding the 2) (58) scroll compressor according to claim 50 which is provided in the. 52. One of said first and second seals (108, 116; 204, 214; 30).
6) on the inner peripheral wall surface of the concave groove (78) ,
52. The scroll compressor according to claim 51, wherein (108; 208; 308) is engaged with an outer peripheral wall surface of said concave groove (78) . 53. A said shell (10), a partition wall for partitioning the interior of the outer shell to a region of the area between the discharge pressure of the suction pressure
(16) , wherein the partition wall comprises the discharge port
51. The scroll compressor of claim 50 including an opening (75) for directing fluid at discharge pressure from (72) to said discharge pressure region.