JPH06341387A - Scroll type machine - Google Patents

Abstract

PURPOSE: To tightly seal a recess groove, to which fluid pressure for movably energizing one scroll member to the other scroll member is applied, by a simply structured sealing means assembled easily and provided with a composite sealing function. CONSTITUTION: An annular recess groove, to which a fluid pressure is applied, is sealed by means of a single seal assembly 80 provided with inside diameter sealing parts 124, 126, an outside diameter sealing part 128, and a top end sealing part 130. The sealing assembly 80 can float inside the annular recess groove, and a function of its top end sealing part is released in case of an abnormal condition.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type machine, and more particularly to a multifunctional floating seal for a scroll type compressor having a scroll member having flexibility in the axial direction.

[0002]

2. Description of the Related Art A typical scroll type machine has an orbiting scroll member having a spiral blade on one surface, a non-orbiting scroll member having a spiral blade meshing with the spiral blade on one surface,
An orbiting drive means is provided which orbitally drives the orbiting scroll member relative to the non-orbiting scroll member to form fluid pockets of varying volumes in the above-mentioned spiral blades.

In order to improve the mechanical efficiency, it is important that the tip of each scroll member is sealingly engaged with the end plate of the other scroll member to minimize fluid leakage therebetween. One method that has been used to achieve this is not to use tip sealing (the tip sealing method is very difficult to assemble and often causes reliability problems). ), A method of urging one scroll member 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, in the field of scroll machines, there is a constant demand for improved axial biasing techniques and, consequently, improved seals.

[0004]

SUMMARY OF THE INVENTION 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 combined sealing function. It is to provide a scroll type machine provided with a mechanism.

[0005]

SUMMARY OF THE INVENTION When embodying the invention as a scroll compressor, the axial biasing force required to promote tip sealing is discharge pressure only, or discharge pressure and an intermediate pressure independent thereof, or It can be produced using only intermediate pressures. The sealing means according to the present invention is generally constructed by integrally assembling three kinds of seals, and is for urging the non-orbiting scroll member or the non-orbiting scroll member (the former scroll member is preferable). It is suitable for use in.

The sealing means according to the invention are particularly sensitive to the pressure ratio of a scroll type machine and provide particularly good protection against depressurized conditions such as those which occur when the machine is reversed or the suction path is blocked. Is heading. In the depressurized state, the sealing means cancels the one sealing function,
Allows the exhaled gas to flow directly to the suction gas region at suction pressure. This prevents a high degree of depressurization on the inlet side of the compressor that would draw the scroll members too far from each other and cause damage. And especially,
This prevents arcing or burning of the motor protector connecting pin, which often occurs under constant decompression conditions.

The sealing means according to the invention also provide 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 that was designed at the time of mechanical design occurs. The leakage of this discharge fluid to the compressor suction side causes a reduction in the discharge amount of the machine, and the decrease in the flow of cooling gas causes heat to accumulate in the outer shell of the compressor. Stops the machine. In certain applications, due to this feature of the sealing means according to the invention, it may be caused by loss of fill working fluid, by shutting down the condenser fan in the refrigeration system, or by (for whatever reason) excessive discharge pressure. Some protection against possible excessive exhaled gas temperatures will be provided. All of these undesired conditions result in the scroll machine operating at a higher pressure ratio than was planned in the form of a constant fixed volume ratio during machine design.

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 Although the present invention can be implemented in any type of scroll type machine, an example implemented in the scroll type refrigerant compressor shown in FIG. 1 will be described below. Generally speaking, this refrigerant compressor has a cylindrical outer shell 10 having a cap 12 welded to its 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 laterally facing partition wall 16 having a peripheral edge welded to the outer shell 10 at the same point as the cap 12, and appropriately attached to the outer shell 10 at a plurality of points. 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 section, but with its corners chamfered in an arc, is provided by being press-fitted into the outer shell 10. The flat surface between the chamfered corners of the stator 20 indicates 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. Give a passage to promote. A crankshaft 24 having an eccentric crankpin 26 at the upper end is attached to the main bearing box 1
A bearing 28 inside the bearing 8 and a second bearing (not shown) inside the lower bearing housing are rotatably supported. The crankshaft 24 has a relatively large diameter ordinary oil pumping hole or pump hole (not shown) in the lower end thereof, which is tilted outward in the radial direction and is provided at the upper end of the crankshaft 24. It communicates with a hole 30 having a smaller diameter, which has been drilled through. The lower part 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 a hole 30.
In cooperation with, the hole 30 acts as a secondary pump and acts as a secondary pump to deliver lubricating oil to all of the various parts of the compressor that require lubrication.

The crankshaft 24 includes the stator 20, windings 32 passing through the stator 20, and the crankshaft 2.
4 is rotatably driven by an electric motor having a rotor 34 press fitted onto it, the rotor 34 having one or more counterweights 36. An ordinary type motor protector 35 is provided close to the winding 32, and when the motor exceeds a normal temperature range, the motor protector 35 stops the motor.

An annular flat thrust receiving surface 38 is provided on the upper surface of the main bearing box 18, and the thrust receiving surface 38 is formed.
An orbiting scroll member 40 having an end plate 42 is arranged on the upper side. The end plate 42 has a normal spiral blade 44 on its upper surface, and has an annular and flat thrust surface 46 on its lower surface, and a cylindrical hub 48 having a plain bearing 50 therein is formed from the thrust surface 46. The drive bush 52 is rotatably disposed in the hub 48 by protruding downward.
The crank pin 26 is inserted into the second hole 54. The crank pin 26 has a flat surface (above, not shown) which engages with a flat surface formed on a part of the inner peripheral surface of the hole 54 on a part of the outer peripheral surface, which is owned by the applicant. U.S. Patent No. A radial drive mechanism such as that shown in US Pat. No. 4,877,382 is provided.

The spiral blade 44 is meshed with the non-orbiting spiral blade 56 forming a part of the non-orbiting scroll member 58, and the non-orbiting scroll member 58 is restricted by the scroll member 58 on the main bearing housing 18. It is supported in any suitable manner that allows for axial movement. Although this supporting system itself 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 which are intermittently arranged in the circumferential direction, only one of which is illustrated. Each support boss 60 has a flat upper surface 62 and an axial hole 6.
4, a sleeve 66 is slidably fitted in the hole 64, and the sleeve 66 is fixed to the main bearing housing 18 by bolts 68 as shown in the drawing. The bolt 68 has a head having a flat lower surface 70, and the non-orbiting scroll member 5
The ascending movement of 8 and the separating movement from the orbiting scroll member are limited by the engagement of the boss upper surface 62 with the bolt head lower surface 70. The movement of the non-orbiting scroll member 58 in the opposite direction is limited by the lower blade tip surface of the blade 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 arranged at the center thereof, and the discharge passage 72 is communicated with a concave groove 74 whose upper end is open, and the concave groove 74 forms a hole 75 in the partition wall 16. Through, it communicates with the 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, there is formed an annular groove 78 having two circumferentially parallel circumferential wall surfaces, and an annular floating seal 80 is movable in the axial direction in the annular groove 78. It is fitted airtightly. The floating seal 80 isolates the inner bottom portion of the annular groove 78 from the gas having the suction pressure and the discharge pressure, and the inner bottom portion is formed by the passage 82 to form an intermediate fluid pressure source (a fluid having an intermediate pressure formed between the spiral blades 44 and 56). (In the movable fluid pocket, including). Therefore, the non-orbiting scroll member 58 has a force based on the discharge pressure applied to the center 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 toward the orbiting scroll member 40 in the axial direction. Powered by.
Various techniques for supporting the axial pressure and the non-orbiting scroll member 58 so as to be movable in the axial direction within a limited range are described in the above-mentioned US Pat. 4,877,32
8 are described in detail.

Relative rotation between the scroll members 40, 58 is prevented by a conventional Oldham coupling having a ring 82, which is provided in the non-orbiting scroll member 52 so as to face each other in the radial direction. And a first pair of keys 84 (only one shown) slidably fitted in a pair of slots 86 (only one shown) and radially disposed within the orbiting scroll member 40. And a second pair of keys (not shown) slidably fitted in a pair of slots (not shown) provided in the same manner.

In the compressor, the inflowing suction gas is deflected by the deflection plate 19
It is preferably of the "low side" type, in which the motor can be partly dissipated into the shell to cool the motor. The motor remains within the desired temperature range as long as there is adequate flow of the return intake gas. However, if the flow is interrupted, the cooling is not performed and the motor protector 35 operates to stop the motor.

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

FIGS. 1-3 show a floating seal 80 according to a first embodiment having a coaxial sandwich structure. The floating seal 80 has an annular substrate 100 made of cast aluminum or the like. The substrate 100 comprises a plurality of upstanding, unitary protrusions 102, each having an enlarged base 104, arranged at equal intervals. An annular gasket 106 made of skeet material of epoxy resin coated fibers is disposed on the substrate 100, and the gasket 106 has a plurality of holes at regular intervals for receiving the base 104. On the upper surface of the gasket 106, a pair of flat lower lip seals (lip packings) 108 which are in a normal state (non-compressed state) and are equal to each other are arranged, and the lip seals 108 are glass (about 5%) filled PTFE.
PT (polytetrafluoroethylene) optionally containing 5% by weight MoS ₂ (molybdenum disulfide)
It is made from FE. The seal 108 is also the base 10
It has a plurality of holes for receiving 4 at regular intervals. Arranged on the upper surface of the seal 108 is an annular spacer plate 110, which may be made of stamped steel.
The spacer plate 110 has an annular groove 112 on the upper and lower surfaces,
114, and also has a plurality of holes at regular intervals for receiving the base 104. On the upper surface of the spacer plate 110, a pair of normally flat upper lip seals (lip packings) 116, which are made of the same material as the lip seal 108 and which are flat in the normal state, are arranged. An annular top seal plate 118 having equally spaced holes and an annular rim 120 located within the annular groove 112.
Are held concentrically by. Seal plate 118, which may be made of gray cast iron, is provided with a flat sealing lip or lip seal 122 projecting upwardly around its inner peripheral edge. Floating seal 10
The above-mentioned various members of No. 8 are fixed to each other by inserting the ends of the respective protrusions 102 as indicated by reference numeral 123.

The floating seal or seal assembly 108 as a whole provides three different seals, namely an inner diameter seal 124, 126, an outer diameter seal 128 and a top seal 130 as shown in FIG. Let 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 the lip seal 11.
It is obtained between the inner peripheral edge of 6 and the inner peripheral wall surface of the annular groove 78. These inner diameter sealing portions 124 and 126 isolate the fluid having an intermediate pressure at the bottom of the annular groove 78 from the fluid having a discharge pressure in 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 annular groove 7 is formed.
8. Isolate intermediate pressure fluid in the inner bottom from suction pressure fluid in the outer shell 10. The top end sealing portion 130 is the lip seal 12
2 and an annular wear ring 132, which isolates suction pressure fluid from discharge pressure fluid in a direction transverse to the top end of the seal assembly. 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 in a position surrounding the hole 75 of the partition wall 16. Instead of providing the separate wear-resistant ring 132 for sealing the top end, the lower surface of the partition wall 16 surrounding the hole 75 can be partially hardened by nitriding or carbonitriding.

The diameter of the top end seal 130 is selected to provide a positive upward sealing force on the floating seal 80 under normal compressor operating conditions, ie, in the presence of normal pressure differentials. Therefore, when an excessive pressure difference occurs, the floating seal 80 is urged downward by the discharge pressure, whereby the discharge gas on the high pressure side may cross the seal 80 and leak directly to the intake gas region on the low pressure side. Has become. If the motor cooling due to the intake gas flow is impaired as a result of the leakage and discharge gas having a large amount of this leakage, the motor protector 35 is activated and the motor is stopped.
The width of the top end sealing portion 130 is such that the unit pressure applied to the seal itself (that is, between the lip seal 122 and the ring 132) is larger than the discharge pressure under normal conditions, and a tight seal is ensured. It is set.

Similarly, FIGS. 4-7 show a floating seal according to a second embodiment of the coaxial sandwich structure. The floating seal has an annular substrate 200 formed by casting aluminum or the like. The substrate 200 is integrally formed with an upright annular rib 202. 5 on board 200
% Glass and 5% molybdenum disulfide filled PT
A lower inner lip seal 204 made of FE and an outer lip seal 208 made of the same material are provided, and these lip seals 204 and 208 are respectively
It has frustoconical elastic sealing lips 206, 210. On the inner lip seal 204, an annular metallic separating plate 212 is arranged in the annular rib 202, and the separating plate 212 is finely divided in order to enhance the mechanical engagement strength with the seals 204 and 214. It has an uneven upper surface and a lower surface. Lip seals 204 and 208 are provided on the separating plate 212.
A pair of identical annular upper lip seals 214 made of the same material as the above is disposed, 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 edge. The lip seal 214 has a frustoconical elastic sealing lip 220, and also the sealing plate 21.
6 is made of cast iron. Outer lip seal 208
Is held in place by an annular metal ring 222 and the entire seal assembly is secured by snapping the upper end of the annular rib 202 at a number of spaced locations, as indicated at 224.

This seal assembly also includes three different seals, namely inner diameter seals 226 and 228 as shown in FIG.
The outer diameter sealing portion 230 and the top end sealing portion 232 are obtained. The inner diameter sealing portion 226 is obtained 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 provided.
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 seals 226, 22
8 is a groove 74 for allowing fluid having an intermediate pressure in the inner bottom of the annular groove 78.
Isolate from discharge pressure fluid inside. The outer diameter sealing portion 230 is provided between the outer peripheral edge of the lip seal 208 and the outer peripheral wall surface of the annular groove 78, and isolates the fluid of intermediate pressure at the inner bottom of the annular groove 78 from the fluid of suction pressure in the outer shell 10. Top end sealing part 2
32 is obtained between the lip seal 218 and an annular wear ring 132 surrounding the bore 75 in the partition 16 to isolate suction pressure fluid from discharge pressure fluid in a direction transverse to the top end of the seal assembly. To 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. The floating seal is an annular substrate 30 formed by casting aluminum or the like.
It has 0. The substrate 300 includes the annular rib 3 having a low height.
04 has a plurality of equally spaced, upstanding, integral projections 302. Substrate 30 within annular rib 304
On the upper surface of 0 is disposed a pair of normally flat inner lip seals 306 made of PTFE with an appropriate filling. Substrate 30 within annular rib 304
A pair of normally flat annular outer lip seals 308, which are made of the same material as the lip seal 306 and which are normally flat, are disposed on the upper surface of 0. These two pairs of lip seals 306 and 308 are positioned concentrically by an annular rib 304, and are clamped and restrained by an annular upper seal plate 310 having a plurality of holes arranged at equal intervals through which the protrusion 302 is inserted. . Seal plate 310, which is preferably made of gray cast iron, forged steel or powder metal, is provided with a flat sealing lip 312 projecting upwardly around its inner peripheral edge. The seal assembly as a whole is designated by reference numeral 3.
It is fixed by sliding the end of each protrusion 302 as indicated by 14.

The overall seal assembly is also different.
Seed seal, ie inner diameter seal 31 as shown in FIG.
6. Obtain the outer diameter sealing portion 318 and the top end sealing portion 320. The inner diameter sealing portion 316 is obtained between the inner peripheral edge of the lip seal 306 and the inner peripheral wall surface of the annular groove 78, and isolates the fluid of intermediate pressure at the inner bottom of the annular groove 78 from the fluid of discharge pressure in the 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 the annular groove 7 is formed.
8. Isolate intermediate pressure fluid in the inner bottom from suction pressure fluid in the outer shell 10. The top end sealing portion 320 is the lip seal 31.
2 and an annular wear ring 132 surrounding the hole 75 in the partition wall 16 to isolate suction pressure fluid from discharge pressure fluid in a direction transverse to the top end of the seal assembly. The diameter and width of the top end sealing part 320 are set as in the first embodiment.

To prevent excessive intermediate pressure from being created between the inner and outer seals of the floating seal in the liquid slugging condition which could damage the high side seal, reference is made to FIG. Suitable vent passages may be provided at 125 and as shown at 316 in FIG.

[Brief description of drawings]

FIG. 1 is a scroll-type machine that uses fluid pressure to axially urge a non-orbiting scroll member toward an orbiting scroll member, and embodies the principle of the present invention. FIG.

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

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

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

5 is an enlarged vertical cross-sectional view of a portion of the floating seal shown in FIG.

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

7 is a cross-sectional view taken along line 7-7 of FIG.

FIG. 8 is a vertical partial view 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.

10 is a cross-sectional view taken along the line 10-10 in FIG.

[Explanation of symbols]

 10 Outer Shell 16 Partition Wall 18 Main Bearing Box 40 Orbiting Scroll Member 44 Helical Blade 56 Helical Blade 58 Non-orbiting Scroll Member 60 Support Boss 66 Sleeve 68 Bolt 72 Discharge Passage 75 Opening 76 Discharge Silence Chamber 78 Annular Groove 80 Floating Seal 82 passage 100 substrate 102 protrusion 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 separation plate 214 lip seal 216 upper seal plate 218 sealing lip 226, 228 inner diameter sealing part 230 outer diameter sealing part 232 top end sealing part 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

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Claims (50)

[Claims] 1. A scroll type machine comprising: (a) a closed outer shell; (b) an orbiting scroll member disposed in the outer shell and having a first spiral blade on one surface thereof; ) Located in the outer shell and on one surface, the first
A non-orbiting scroll member having a second spiral blade meshed with the spiral blade of (4), An orbiting drive means for forming a going fluid pocket, (e) One scroll member of both scroll members is allowed to move in the axial direction within a limited range relative to the other scroll member. (F) An annular groove having an inner peripheral wall surface and an outer peripheral wall surface, which faces one surface of one scroll member of the two scroll members, and the one scroll member is pressed by an internal pressure fluid. An annular groove for urging the member to move toward the other scroll member, (g) a leak passage forming means for forming a fluid leak passage between the annular groove and the inside of the outer shell, h) a pressure fluid supply means for supplying a pressure fluid into the annular groove, and (i) an annular sealing means arranged in the annular groove, which is sealingly engaged with the inner peripheral wall surface. A scroll-type machine having a first seal and a second seal that is sealingly engaged with the outer peripheral wall surface, and a sealing means that isolates the pressure fluid in the annular groove from the leak passage. 2. The scroll machine according to claim 1, wherein the inner peripheral wall surface and the outer peripheral wall surface are cylindrical surfaces concentric with each other. 3. The scroll machine according to claim 1, wherein the scroll machine is a compressor, and the pressure fluid is a working fluid that is compressed from suction pressure to discharge pressure. 4. The scroll 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 of claim 1, wherein the sealing means is axially floatable within the annular groove. 6. The sandwich means has a sandwich structure having a first annular member and a second annular member,
The first seal and the second seal described above include a substantially flat inner annular lip seal and an outer annular lip seal clamped and fixed between the first annular member and the second annular member. The scroll type machine according to claim 1. 7. The scroll machine according to claim 6, wherein the inner lip seal and the outer lip seal are integrated with each other. 8. The scroll-type machine according to claim 6, wherein the inner lip seal and the outer lip seal are separate from each other. 9. The scroll machine according to claim 6, wherein each of the lip seals is made of polytetrafluoroethylene containing a filler. 10. The polytetrafluoroethylene is
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 the glass loading is about 5% by weight. 12. The polytetrafluoroethylene is
The scroll machine according to claim 9, wherein the scroll machine is filled with molybdenum disulfide. 13. The filling amount of molybdenum disulfide is about 5.
13. The scroll machine of claim 12 which is in weight percent. 14. The scroll machine according to claim 6, wherein each of the lip seals is flat in a stress-free state. 15. The scroll machine according to claim 6, wherein each of the lip seals has a slightly conical curved peripheral portion in a stress-free state. 16. The scroll type machine according to claim 6, wherein a plurality of inner and outer lip seals are provided respectively. 17. A scroll type machine according to claim 6, wherein a plurality of said inner annular lip seals are provided, and an annular spacer is interposed between them. 18. The scroll-type machine according to claim 17, wherein the spacer is made of a relatively rigid material and has an uneven surface portion that engages with the inner lip seal. 19. The scroll type according to claim 6, wherein the first annular member has a plurality of pillar portions intermittently arranged in the circumferential direction and projecting along the axial direction and penetrating the second annular member. machine. 20. The scroll type machine according to claim 19, wherein the free end of the column portion is swaged so as to clamp and hold the lip seal between the first annular member and the second annular member. 21. The inner lip seal and the outer lip seal are integrally formed with each other to form the pillar portion.
20. The scroll machine of claim 19, which is adapted to penetrate the integrated lip seal. 22. The inner lip seal and the outer lip seal are separate from each other, and the column portion is projected between the inner lip seal and the outer lip seal. Scroll type machine. 23. The first annular member is provided with an annular rib projecting in the axial direction, and the second annular member is arranged on the inner peripheral surface side and the outer peripheral surface side of the annular rib. 7. The scroll-type machine according to claim 6, wherein the scroll-type machine comprises an annular component. 24. The annular rib is adapted to clamp and hold the two annular parts and to clamp and hold the lip seal between the first and second annular members.
The scroll-type machine according to claim 23, wherein the scroll-type machine is installed at a plurality of locations spaced in the circumferential direction. 25. The scroll type machine according to claim 6, wherein a plurality of said inner lip seals are provided. 26. The scroll compressor according to claim 6, wherein the scroll machine is a compressor, and has a second fluid leakage passage between the annular groove and the discharge pressure region in the outer shell. . 27. The scroll type machine according to claim 26, wherein the sealing means is configured to isolate the annular groove from the discharge pressure region. 28. One side of the sealing means is provided for the fluid in the annular groove, and the annular groove is isolated from the discharge pressure region by the first seal, and the inside of the outer shell is formed by the second seal. And the other surface side of the sealing means is disposed so as to face the inside of the outer shell and the discharge pressure region, and the other surface of the sealing means is attached to the sealing means. 28. The scroll machine of claim 27, further comprising an annular third seal that isolates the interior of the outer shell from the discharge pressure region in a transverse direction. 29. The third seal is integrally provided on the second annular member of the sealing means.
Scrolling machine. 30. The scroll machine of claim 26, wherein said sealing means is axially floatable within said annular recess. 31. A scroll type machine, which is a compressor, is provided with a fluid discharge hole in a partition wall installed in the outer shell, and the third seal is arranged so as to surround the fluid discharge hole. 29. The scroll type machine according to claim 28. 32. The scroll type machine according to claim 31, wherein a hardening valve seat surrounding the fluid discharge hole is provided on the partition wall. 33. The scroll type machine according to claim 32, wherein said valve seat is formed by an annular member surrounding said fluid discharge hole and attached to said partition wall. 34. The scroll machine according to claim 32, wherein the valve seat is formed by locally hardening the partition wall in a region surrounding the fluid discharge hole. 35. The scroll type machine according to claim 1, wherein the one scroll member is the non-orbiting scroll member. 36. The scroll machine according to claim 1, wherein the scroll machine is a compressor having a discharge area of discharge pressure, and a second fluid leakage passage is provided between the annular groove and the discharge area. 37. The sealing means is configured to separate the annular groove from the discharge area as well.
6 scroll machines. 38. One surface of the sealing means is exposed to the fluid in the annular groove so that the annular groove is isolated from the discharge area by the first seal and is separated from the inside of the outer shell by the second seal. The sealing means is contacted so as to be separated, and the other surface side of the sealing means is disposed so as to face the inside of the outer shell and the discharge region, and the sealing means is traversed on the other surface side of the sealing means. 38. The scroll machine of claim 37, wherein an annular third seal is provided that separates the interior of the shell from the discharge area in a direction. 39. A scroll compressor, comprising: (a) a hermetically sealed outer shell, (b) an orbiting scroll member disposed in the outer shell, and having a first spiral blade on one surface thereof. c) is placed in the outer shell and is on one surface, the first
A non-orbiting scroll member having a second spiral blade meshing with the above-mentioned spiral blade, and An orbiting drive means for forming a going fluid pocket, (e) One scroll member of both scroll members is allowed to move in the axial direction within a limited range relative to the other scroll member. (F) A concave groove that faces one surface of one of the scroll members and that biases the one scroll member toward the other scroll member by an internal pressure fluid. (G) means for forming a first fluid leakage passage between the concave groove and the suction pressure region in the outer shell, (h) between the concave groove and the discharge pressure region in the outer shell, 2 means for forming a fluid leakage passage, (i) pressure fluid supply means for supplying a fluid having an intermediate pressure between the suction pressure and the discharge pressure into the groove, and (j) arranged in the groove. A sealing means for isolating the pressure fluid in the groove from the first fluid leakage passage, and a second seal for isolating the pressure fluid in the groove from the second fluid leakage passage. And a sealing means having a third seal separating the suction pressure area from the discharge pressure area in a direction transverse to the sealing means. 40. The scroll compressor according to claim 39, wherein said sealing means is floatable in said groove along the axial direction while maintaining the function of said first seal and the function of said second seal. . 41. The sealing means has a sandwich structure having a first annular member and a second annular member, and the first seal and the second seal are the same as the first annular member. 40. The scroll compressor according to claim 39, comprising a substantially flat inner annular lip seal and an outer annular lip seal clamped and secured between the second annular members. 42. The scroll compressor according to claim 41, wherein the inner lip seal and the outer lip seal are integrally formed with each other. 43. The inner lip seal and the outer lip seal are separate bodies from each other.
Scroll compressor. 44. The scroll compressor according to claim 41, wherein a plurality of said inner lip seals are provided with an annular spacer interposed therebetween. 45. The first, second, and third seals are all annular, and the diameter of the third seal is a positive seal with respect to the third seal in a normal operating state of the compressor. 40. The scroll compressor according to claim 39, wherein the scroll compressor is selected to exert force. 46. The scroll compressor according to claim 45, wherein the width of the third seal is set so that the unit pressure applied to the third seal in the sealing direction is larger than the normal discharge pressure. . 47. The sealing means is floatable axially within the recess so that the sealing means releases the function of the third seal when decompression occurs at the fluid inlet of the compressor. 40. The scroll compressor according to claim 39, which is adapted to move in the axial direction. 48. A multi-function seal assembly, comprising: (a) an annular inner lip seal adapted for sealing engagement with a first cylindrical surface; (b) concentric with said first cylindrical surface. An outer lip seal having an annular shape that is to be sealingly engaged with the second cylindrical surface of the first and second clamp surfaces, (c) first and second clamp members that clamp and clamp the inner lip seal and the outer lip seal, and (D) A multi-functional seal set comprising an annular third seal coupled to one of these clamping members and adapted for sealing engagement with a substantially flat annular sealing surface. Three-dimensional. 49. The multi-function seal assembly according to claim 48, wherein the first, second and third seals are concentrically arranged with respect to each other. 50. The first and second cylindrical surfaces form an inner peripheral wall surface and an outer peripheral wall surface of the annular groove,
49. The multi-function seal assembly of claim 48, wherein the annular sealing surface is located on the side opposite the bottom of the annular groove.