EP0479421B1 - Compresseur à spirales avec joint flottant - Google Patents

Compresseur à spirales avec joint flottant Download PDF

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Publication number
EP0479421B1
EP0479421B1 EP91307172A EP91307172A EP0479421B1 EP 0479421 B1 EP0479421 B1 EP 0479421B1 EP 91307172 A EP91307172 A EP 91307172A EP 91307172 A EP91307172 A EP 91307172A EP 0479421 B1 EP0479421 B1 EP 0479421B1
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EP
European Patent Office
Prior art keywords
seal
scroll machine
scroll
cavity
seals
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP91307172A
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German (de)
English (en)
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EP0479421A1 (fr
Inventor
Gary Justin Anderson
James William Bush
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Copeland Corp LLC
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Copeland Corp LLC
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Publication date
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Publication of EP0479421A1 publication Critical patent/EP0479421A1/fr
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Publication of EP0479421B1 publication Critical patent/EP0479421B1/fr
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/06—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of other than internal-axis type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C28/265—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid

Definitions

  • the present invention relates to seals for scroll-type machinery, and more particularly to axially compliant scroll compressors including a multi-function floating seal.
  • a typical scroll machine has an orbiting scroll member having a spiral wrap on one face thereof, a non-orbiting scroll member having a spiral wrap on one face thereof, said wraps being intermeshed with one another, and means for causing said orbiting scroll member to orbit around an axis with respect to said non-orbiting scroll member, whereby said wraps will create pockets of progressively changing volume.
  • GB-A-2 162 899 discloses a scroll type machine in accordance with the prior art portion of claim 1 and in which fluid pressure in a sealed cavity urges one scroll member towards the other.
  • the present invention as defined in claim 1, provides better control of the pressure in the cavity used to bias the one scroll member towards the other in that a floating valve is used alternately to prevent and permit the flow of fluid between a discharge pressure zone and a suction pressure zone.
  • seals of the present invention are embodied in a compressor and suited for use in machines which use discharge pressure alone, discharge and an independent intermediate pressure, or solely an intermediate pressure only, in order to provide the necessary axial biasing forces to enhance tip sealing.
  • seals of the present invention which in most embodiments are three seals in one, are suitable for use in applications which bias the non-orbiting scroll or those which bias the orbiting scroll, although they are particularly suited for the former.
  • the seal has been discovered to be particularly sensitive to the pressure ratio of the scroll machine and consequently provides particularly good protection against vacuum conditions such as caused by reverse rotation or a blocked suction condition. In this condition, the seal will become ineffective and thus permit discharge gas to be bypassed directly into a zone of suction gas at suction gas pressure. This prevents the creation of a high vacuum on the inlet side of the compressor which might otherwise occur and which could cause excessive and damaging forces pulling the scroll members together. Even more importantly, it prevents the arcing or burning of the motor protector connector pins which has been observed to occur under some vacuum conditions.
  • the seals of the present invention also, in some applications, provide a degree of temperature protection, particularly in motor-compressors where suction gas is used to cool the motor. This is because the seal will leak from the high side to the low side at pressure differentials which are significantly higher than those for which the machine was designed. This leakage of discharge fluid to the suction side of the compressor will cause the machine to have a reduced output and the resulting heat build-up within the compressor enclosure due to the reduced flow of cooling gas will cause the standard motor protector to trip and shut the machine down.
  • This characteristic of the seals of the present invention therefore provides a degree of protection in certain applications from excessive discharge temperatures which could result from loss of working fluid charge, or from a blocked condensor fan In a refrigeration system, or from an excessive discharge pressure (for whatever reason). All of these undesirable conditions will cause a scroll machine to function at a pressure ratio is greater than that which is designed into the machine in terms of its predetermined fixed volume ratio.
  • the compressor comprises a cylindrical hermetic shell 10 having welded at the upper end thereof a cap 12, which is provided with a refrigerant discharge fitting 14 optionally having the usual discharge valve therein (not shown).
  • affixed to the shell include a transversely extending partition 16 which is welded about its periphery at the same point that cap 12 is welded to shell 10, a main bearing housing 18 which is affixed to shell 10 at a plurality of points in any desirable manner, and a suction gas inlet fitting 17 having a gas deflector 19 disposed in communication therewith inside the shell.
  • a motor stator 20 which is generally square in cross-section but with the corners rounded off is press fit into shell 10.
  • the flats between the rounded corners on the stator provide passageways between the stator and shell, indicated at 22, which facilitate the flow of lubricant from the top of the shell to the bottom.
  • a crankshaft 24 having an eccentric crank pin 26 at the upper end thereof is rotatably journaled in a bearing 28 in main bearing housing 18 and a second bearing in a lower bearing housing (not shown).
  • Crankshaft 24 has at the lower end the usual relatively large diameter oil-pumping concentric bore (not shown) which communicates with a radially outwardly inclined smaller diameter bore 30 extending upwardly therefrom to the top of the crankshaft.
  • the lower portion of the interior shell 10 is filled with lubricating oil in the usual manner and the pump at the bottom of the crankshaft is the primary pump acting in conjunction with bore 30, which acts as a secondary pump, to pump lubricating fluid to all of the various portions of the compressor which require lubrication.
  • Crankshaft 24 is rotatively driven by an electric motor including stator 20, windings 32 passing therethrough, and a rotor 34 press fit on the crankshaft and having one or more counterweights 36.
  • a motor protector 35 of the usual type, is provided in close proximity to motor windings 32 so that if the motor exceeds its normal temperature range the protector will deenergize the motor.
  • main bearing housing 18 The upper surface of main bearing housing 18 is provided with an annular flat thrust bearing surface 38 on which is disposed an orbiting scroll member 40 comprising an end plate 42 having the usual spiral vane or wrap 44 on the upper surface thereof, an annular flat thrust surface 46 on the lower surface, and projecting downwardly therefrom a cylindrical hub 48 having a journal bearing 50 therein and in which is rotatively disposed a drive bushing 52 having an inner bore 54 in which crank pin 26 is drivingly disposed.
  • Crank pin 26 has a flat on one surface (not shown) which drivingly engages a flat surface in a portion of bore 54 (not shown) to provide a radially compliant driving arrangement, such as shown in assignee's U.S. Letters Patent No. 4,877,382, the disclosure of which is herein incorporated by reference.
  • non-orbiting scroll member 58 has a plurality of circumferentially spaced mounting bosses 60, one of which is shown, each having a flat upper surface 62 and an axial bore 64 in which is slidably disposed a sleeve 66 which is bolted to main bearing housing 18 by a bolt 68 in the manner shown.
  • Bolt 68 has an enlarged head having a flat lower surface 70 which engages surface 62 to limit the axially upper or separating movement of non-orbiting scroll member, movement in the opposite direction being limited by axial engagement of the lower tip surface of wrap 56 and the flat upper surface of orbiting scroll member 40.
  • Non-orbiting scroll member 58 has a centrally disposed discharge passageway 72 communicating with an upwardly open recess 74 which is in fluid communication via an opening 75 in partition 16 with the discharge muffler chamber 76 defined by cap 12 and partition 16.
  • Non-orbiting scroll member 58 has in the upper surface thereof an annular recess 78 having parallel coaxial side walls in which is sealingly disposed for relative axial movement an annular floating seal 80 which serves to isolate the bottom of recess 78 from the presence of gas under suction and discharge pressure so that it can be placed in fluid communication with a source of intermediate fluid pressure by means of a passageway 82.
  • the non-orbiting scroll member is thus axially biased against the orbiting scroll member by the forces created by discharge pressure acting on the central portion of scroll member 58 and those created by intermediate fluid pressure acting on the bottom of recess 78.
  • This axial pressure biasing, as well as various techniques for supporting scroll member 58 for limited axial movement, are disclosed in much greater detail in assignee's aforesaid U.S. Letters Patent No. 4,877,328.
  • Oldham coupling comprising a ring 83 having a first pair of keys 84 (one of which is shown) slidably disposed in diametrically opposed slots 86 (one of which is shown) in scroll member 58 and a second pair of keys (not shown) slidably disposed in diametrically opposed slots (not shown) in scroll member 40.
  • the compressor is preferably of the "low side" type in which suction gas entering via deflector 19 is allowed, in part, to escape into the shell and assist in cooling the motor. So long as there is an adequate flow of returning suction gas the motor will remain within desired temperature limits. When this flow ceases, however, the loss of cooling will cause motor protector 35 to trip and shut the machine down.
  • the floating seal of the first embodiment is of a coaxial sandwiched construction and comprises an annular base plate 100, cast out of aluminum or the like, having a plurality of equally spaced upstanding integral projections 102 each having an enlarged base portion 104.
  • annular gasket 106 formed of epoxy coated fiber gasket material having a plurality of equally spaced holes which receive base portions 104, on top of which is disposed a pair of normally flat identical lower lip seals 108 formed of glass filled PTFE (approximately 5%) and optionally including 5% MoS2, by weight. Seals 108 have a plurality of equally spaced holes which receive base portions 104.
  • annular spacer plate 110 On top of seals 108 is disposed an annular spacer plate 110, which can be a simple steel stamping, having annular recesses 112 and 114 on the top and bottom surfaces thereof and a plurality of equally spaced holes which receive base portions 104, and on top of plate 110 are a pair of normally flat identical annular upper lip seals 116 formed of the same material as lip seals 108 and maintained in coaxial position by means of an annular upper seal plate 118 having a plurality of equally spaced holes receiving projections 102 and an annular rim 120 disposed in recess 112.
  • Seal plate 118 which may be formed of grey cast iron, has disposed about the inner periphery thereof an upwardly projecting planar sealing lip 122. The assembly is secured together by swaging the ends of each of the projections 102, as indicated at 123.
  • the overall seal assembly therefore provides three distinct seals; namely, an inside diameter seal at 124 and 126, an outside diameter seal at 128 and a top seal at 130, as best seen in Figure 1.
  • Seal 124 is between the inner periphery of lip seals 108 and the inside wall of recess 78
  • seal 126 is between the inner periphery of lip seals 116 and the inside wall of recess 78.
  • Seals 124 and 126 isolate fluid under intermediate pressure in the bottom of recess 78 from fluid under discharge pressure in recess 74.
  • Seal 128 is between the outer periphery of lip seals 108 and the outer wall of recess 78, and isolates fluid under intermediate pressure in the bottom of recess 78 from fluid at suction pressure within shell 10.
  • Seal 130 is betwen lip seal 122 and an annular wear ring 132, formed of cast iron or the like and affixed to partition 16 by a suitable adhesive in a position surrounding opening 75, and isolates fluid at suction pressure from fluid at discharge pressure across the top of the seal assembly.
  • an annular wear ring 132 for the upper seal the lower surface of partition 16 surrounding opening 75 can be locally hardened, by nitriding, carbo-nitriding or the like.
  • the diameter of seal 130 is chosen so that there is a positive upward sealing force on seal 80 under normal operating conditions, i.e., at normal pressure differentials. Therefore, when excessive pressure differentials are encountered, the seal will be forced downwardly by discharge pressure, thereby permitting a leak of high side discharge gas directly across the seal to a zone of low side suction gas. If this leakage is great enough, then the resultant loss of flow of motor-cooling suction gas (aggravated by the excessive temperature of the leaking discharge gas) will cause the motor protector to trip, thereby deenergizing the motor.
  • the width of seal 130 is chosen so that the unit pressure on the seal itself (i.e., between seal 122 and seat 132) is greater than normally encountered discharge pressure, thus insuring consistant sealing.
  • the floating seal of the second embodiment is also of a coaxial sandwiched construction and comprises an annular base plate 200, cast out of aluminum or the like and having an annular upstanding integral rib 202.
  • plate 200 Disposed on plate 200 is a lower inner lip seal 204 formed of 5% glass and 5% molydisulfide filled PTFE and having a conical resilient sealing lip 206; and an outer lip seal 208 of the same material having a resilient conical sealing lip 210.
  • annular metal separator plate 212 Disposed on top of inner seal 204 and inside rib 202 is an annular metal separator plate 212 having minutely ribbed upper and lower surfaces to increase mechanical contact with the seals.
  • a pair of identical annular upper lip seals 214 formed of the same material as lip seals 206 and 208, also maintained in coaxial position by means of an annular rib 202, and an upper seal element 216 having disposed about the inner periphery thereof an upwardly projecting planar sealing lip 218.
  • Seals 214 have resilient conical inner sealing lips 220.
  • Seal plate 118 is preferably formed of cast iron. Outer seal 208 is retained in place by an annular metal ring 222, and the entire assembly is secured together by swaging the top of rib 202 at spaced locations, as indicated at 224.
  • This seal assembly also provides three distinct seals; namely, an inside diameter seal at 226 and 228, an outside diameter seal at 230 and a top seal at 232, as best seen in Figure 4.
  • Seal 226 is between the inner periphery of lip seal 204 and the inside wall of recess 78
  • seal 228 is between the inner periphery of lip seals 214 and the inside wall of recess 78.
  • Seals 226 and 228 isolate fluid under intermediate pressure in the bottom of recess 78 from fluid under discharge pressure in recess 74.
  • Seal 230 is between the outer periphery of lip seal 208 and the outer wall of recess 78, and isolates fluid under intermediate pressure in the bottom of recess 78 from fluid at suction pressure within shell 10.
  • Seal 232 is between lip seal 218 and annular wear ring 132 surrounding opening 75 in partition 16, and isolates fluid at suction pressure from fluid at discharge pressure across the top of the seal assembly.
  • the diameter and width of the top seal are chosen in the same manner as for the first embodiment.
  • the floating seal of the third embodiment is also of a coaxial sandwiched construction and comprises an annular base plate 300, cast out of alumminum or the like, having a plurality of equally spaced upstanding integral projections 302 projecting from a shallow annular rib 304. Disposed on the inner periphery of plate 300 inside rib 304 are a pair of normally flat identical inner lip seals 306 formed of suitably filled PTFE. Disposed on top of the outer periphery of plate 300, outside rib 304, are a pair of normally flat identical annular outer lip seals 308 formed of the same material as lip seals 306.
  • Both pairs of seals are maintained in coaxial position by means of rib 304, and are clamped in place by an annular upper seal plate 310 having a plurality of equally spaced holes receiving projections 302.
  • Seal plate 118 which is preferably formed of grey cast iron, stamped steel or powered metal, has disposed about the inner periphery thereof an upwardly projecting planar sealing lip 312. The assembly is secured together by swaging the ends of each of the projections 302, as indicated at 314.
  • seal 316 is between the inner periphery of lip seals 306 and the inside wall of recess 78. Seal 316 isolates fluid under intermediate pressure in the bottom of recess 78 from fluid under discharge pressure in recess 74. Seal 318 is between the outer periphery of lip seals 308 and the outer wall of recess 78, and isolates fluid under intermediate pressure in the bottom of recess 78 from fluid at suction pressure within shell 10.
  • Seal 320 is between lip seal 312 and annular wear ring 132 surrounding opening 75 in partition 16, and isolates fluid at suction pressure from fluid at discharge pressure across the top of the seal assembly.
  • the diameter and width of the top seal are chosen in the same manner as for the first embodiment.
  • a suitable vent can be provided, such as at 125 in Figure 2 and at 316 in Figure 8.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Claims (35)

  1. Machine à volutes comprenant :
    (a) un corps hermétique (10);
    (b) un élément de volute orbital (40) disposé dans ledit corps (10) et ayant une première enveloppe spirale (44) sur une face de cet élément;
    (c) un élément de volute non orbital (58) disposé dans ledit corps (10) et ayant une seconde enveloppe spirale (56) sur une face de cet élément, lesdites enveloppes étant engrénées l'une avec l'autre;
    (d) un moyen pour amener ledit élément de volute orbital (40) à tourner autour d'un axe par rapport audit élément de volute non orbital (58), grâce à quoi lesdites enveloppes vont créer des poches changeant progressivement de volume entre une zone de pression d'aspiration et une zone de pression de décharge;
    (e) un moyen pour monter l'un desdits éléments de volute avec un mouvement axial limité par rapport à l'autre élément de volute;
    (f) un moyen définissant une cavité (78) exposée à une surface de l'un desdits éléments de volute qui amènera le fluide pressurisé dans ladite cavité (78) à actionner ledit un élément de volute (58) vers l'autre élément de volute (40), ladite cavité (78) ayant une surface de paroi intérieure et une surface de paroi extérieure;
    (g) un moyen (82) pour amener le fluide sous pression à la cavité (78) pour actionner ensemble axialement lesdits éléments de volute; et
    (h) un moyen d'étanchéité annulaire disposé dans ladite cavité, ledit moyen d'étanchéité ayant des premiers (124, 226, 316) et seconds (128, 230, 318) joints en engagement étanche respectivement avec lesdites surfaces de parois intérieure et extérieure, afin d'isoler ledit fluide pressurisé dans ladite cavité (78);
       caractérisée en ce que ledit moyen d'étanchéité annulaire est disposé pour flotter dans ladite cavité (78), entre une première position dans laquelle ledit moyen d'étanchéité ferme un chemin de fuite de fluide entre ladite cavité (78) et l'intérieur dudit corps (10), afin d'isoler une zone dans ledit corps à la pression de décharge d'une zone dans ledit corps à la pression d'aspiration; et une seconde position dans laquelle une fuite de fluide à la pression de décharge dans le fluide à la pression d'aspiration est permise.
  2. Machine à volutes selon la revendication 1, dans laquelle lesdites surfaces de parois intérieure et extérieure sont cylindriques et coaxiales.
  3. Machine à volutes selon la revendication 1 ou 2, dans laquelle ladite machine est un compresseur, et ledit fluide pressurisé est le fluide de travail qui est compressé depuis une pression d'aspiration jusqu'à une pression de décharge.
  4. Machine à volutes selon l'une quelconque des revendications 1 à 3, dans laquelle ledit moyen d'étanchéité est de construction en sandwich, comprenant un premier élément annulaire (100, 200, 300) et un second élément annulaire (118, 216, 310), et dans laquelle lesdits premier et second j oints comprennent généralement des j oints plats à lèvres annulaires intérieure et extérieure serrés entre lesdits éléments.
  5. Machine à volutes selon la revendication 4, dans laquelle lesdits joints à lèvres intérieure et extérieure sont formés d'un seul tenant l'une avec l'autre.
  6. Machine à volutes selon la revendication 4, dans laquelle lesdits joints à lèvres intérieure et extérieure constituent des parties séparées.
  7. Machine à volutes selon l'une quelconque des revendications 4 à 6, dans laquelle lesdits joints à lèvres sont de configuration plane quand ils sont dans un état sans contrainte.
  8. Machine à volutes selon l'une quelconque des revendications 4 à 6, dans laquelle lesdits joints à lèvres ont chacun une périphérie exposée légèrement conique quand ils sont dans un état sans contrainte.
  9. Machine à volutes selon l'une quelconque des revendications 4 à 8, dans laquelle il y a une pluralité de joints à lèvre intérieure.
  10. Machine à volutes selon la revendication 9, dans laquelle il y a une pluralité de joints à lèvre extérieure.
  11. Machine à volutes selon la revendication 9 ou 10, dans laquelle un élément d'espacement annulaire (110, 212) est disposé entre les joints à lèvre intérieure.
  12. Machine à volutes selon la revendication 11, dans laquelle ledit élément d'espacement (212) est formé d'un matériau relativement rigide, ayant une pluralité d'arêtes sur les parties de sa surface qui sont en engagement avec lesdits joints à lèvres.
  13. Machine à volutes selon l'une quelconque des revendications 4 à 12, dans laquelle ledit premier élément a une pluralité de montants en saillie axialement et espacés de façon circonférentielle (102, 302), s'étendant à travers ledit second élément.
  14. Machine à volutes selon la revendication 13, dans laquelle les extrémités libres desdits montants sont embouties pour serrer lesdits joints à lèvres entre lesdits éléments.
  15. Machine à volutes selon la revendication 13 ou 14, dans laquelle lesdits montants s'étendent à travers lesdits joints à lèvres.
  16. Machine à volutes selon la revendication 13, 14 ou 15, quand elle est dépendante de la revendication 6, dans laquelle lesdits montants s'étendent entre lesdits joints à lèvres intérieure et extérieure.
  17. Machine à volutes selon l'une quelconque des revendications 4 à 16, dans laquelle ledit premier élément a une nervure annulaire (202) s'étendant axialement, et ledit second élément est formé de deux parties annulaires (216, 222) disposées sur les côtés opposés de ladite nervure.
  18. Machine à volutes selon la revendication 17, dans laquelle ladite nervure est emboutie en des points espacés de façon circonférentielle, pour serrer lesdites deux parties annulaires et lesdits joints à lèvres entre lesdits éléments.
  19. Machine à volutes selon l'une quelconque des revendications 4 à 18, dans laquelle lesdits joints à lèvres sont formés d'un matériau PTFE chargé.
  20. Machine à volutes selon la revendication 19, dans laquelle ledit PTFE est chargé avec du verre qui, de préférence, comprend approximativement 5 % en poids du matériau de joint.
  21. Machine à volutes selon la revendication 19 ou 20, dans laquelle ledit PTFE chargé contient du MoS₂, de préférence 5% en poids du matériau de joint.
  22. Machine à volutes selon l'une quelconque des revendications précédentes, dans laquelle ladite machine est un compresseur, et ledit chemin de fuite comprend un premier et un second chemins de fuite, ledit premier chemin étant défini entre ladite cavité et une zone dans ledit corps à la pression d'aspiration, et ledit second chemin étant défini entre ladite cavité et une zone dans ledit corps à la pression de décharge.
  23. Machine à volutes selon la revendication 22, dans laquelle lesdits premier et second joints isolent également ladite cavité de ladite zone à la pression de décharge.
  24. Machine à volutes selon la revendication 22, dans laquelle une face dudit moyen d'étanchéité est exposée au fluide dans ladite cavité, ledit premier joint isolant ladite cavité de ladite zone à la pression de décharge, et ledit second joint isolant ladite cavité de l'intérieur dudit corps, la face opposée dudit moyen d'étanchéité étant exposée à la fois à l'intérieur dudit corps et à la pression de décharge, ledit moyen d'étanchéité comprenant un troisième joint annulaire (130, 232, 320) pour isoler l'intérieur dudit corps de la pression de décharge en travers de ladite face opposée dudit moyen d'étanchéité.
  25. Machine à volutes selon la revendication 24, dans laquelle ledit troisième joint fait partie intégrante dudit second élément dudit moyen d'étanchéité.
  26. Machine à volutes selon la revendication 24 ou 25, dans laquelle ledit compresseur a un orifice de décharge de fluide (75) dans un compartiment (16) disposé dans ledit corps (10), ledit troisième j oint entourant ledit orifice de décharge de fluide.
  27. Machine à volutes selon la revendication 26, comprenant de plus un siège de soupape durci (132) sur ledit compartiment et entourant ledit orifice de décharge de fluide.
  28. Machine à volutes selon la revendication 27, dans laquelle ledit siège de soupape est un élément annulaire séparé attaché audit compartiment et entourant ledit orifice de décharge de fluide.
  29. Machine à volutes selon la revendication 27, dans laquelle ledit joint de soupape est une surface localement durcie sur ledit compartiment entourant ledit orifice de décharge de fluide.
  30. Machine à volutes selon l'une quelconque des revendications précédentes, dans laquelle ledit un élément de volute est ledit élément de volute non orbital.
  31. Machine à volutes selon l'une quelconque des revendications précédentes, dans laquelle le moyen d'amenée du fluide (82) est destiné à amener le fluide dans ladite cavité à une pression intermédiaire entre lesdites pression d'aspiration et de décharge.
  32. Machine à volutes selon l'une quelconque des revendications précédentes, dans laquelle la zone de pression de décharge est une zone radialement intérieure dans ledit corps à la pression de décharge, et la zone de pression d'aspiration est la zone radialement extérieure dans ledit corps à la presssion d'aspiration.
  33. Machine à volutes selon l'une quelconque des revendications précédentes, dans laquelle un premier chemin de fuite de fluide s'étend entre la cavité (78) et la zone de pression d'aspiration, et un second chemin de fuite de fluide s'étend entre la cavité (78) et la zone de pression de décharge, ledit moyen d'étanchéité ayant quatre joints coaxiaux, lesdits premier et troisième joints isolant dudit premier chemin de fuite ledit fluide pressurisé dans ladite cavité, lesdits deuxième et quatrième joints isolant dudit second chemin de fuite ladite cavité, ledit fluide en action étant disposé entre lesdits premier et deuxième joints, et entre lesdits troisième et quatrième joints.
  34. Machine à volutes selon l'une quelconque des revendications précédentes, dans laquelle ledit moyen d'étanchéité est disposé, dans des conditions normales de fonctionnement de ladite machine à volutes, dans ladite première position, et dans laquelle ledit moyen d'étanchéité est déplaçable à l'intérieur de ladite cavité (78) vers ladite seconde position quand le rapport de la pression de décharge à la pression d'aspiration est suffisamment grand.
  35. Machine à volutes selon l'une quelconque des revendications précédentes, dans laquelle le moyen annulaire d'étanchéité est composé d'un agencement d'étanchéité à fonctions multiples, comprenant
    (a) un joint annulaire à lèvre intérieure adapté pour s'engager de façon étanche avec l'extérieur d'une première surface cylindrique;
    (b) un joint annulaire à lèvre extérieure adapté pour s'engager de façon étanche avec l'intérieur d'une seconde surface cylindrique, ledit agencement d'étanchéité étant monté pour un mouvement le long des axes centraux desdits joints;
    (c) des premier et second éléments de serrage, serrant lesdits premier et deuxième joints entre eux; et
    (d) un troisième joint annulaire associé de façon opérationnelle avec l'un desdits éléments, et étant adapté pour s'engager de façon étanche avec une surface d'étanchéité annulaire généralement plane.
EP91307172A 1990-10-01 1991-08-05 Compresseur à spirales avec joint flottant Expired - Lifetime EP0479421B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US59145490A 1990-10-01 1990-10-01
US591454 1990-10-01

Publications (2)

Publication Number Publication Date
EP0479421A1 EP0479421A1 (fr) 1992-04-08
EP0479421B1 true EP0479421B1 (fr) 1995-12-13

Family

ID=24366553

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91307172A Expired - Lifetime EP0479421B1 (fr) 1990-10-01 1991-08-05 Compresseur à spirales avec joint flottant

Country Status (9)

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EP (1) EP0479421B1 (fr)
JP (1) JP2922343B2 (fr)
KR (1) KR100188324B1 (fr)
CN (1) CN1028379C (fr)
AU (1) AU651606B2 (fr)
BR (1) BR9103456A (fr)
CA (1) CA2046548C (fr)
DE (1) DE69115422T2 (fr)
MX (1) MX9100629A (fr)

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US7752854B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring a condenser in a refrigeration system
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US7644591B2 (en) 2001-05-03 2010-01-12 Emerson Retail Services, Inc. System for remote refrigeration monitoring and diagnostics
US7885959B2 (en) 2005-02-21 2011-02-08 Computer Process Controls, Inc. Enterprise controller display method
US7885961B2 (en) 2005-02-21 2011-02-08 Computer Process Controls, Inc. Enterprise control and monitoring system and method
US7665315B2 (en) 2005-10-21 2010-02-23 Emerson Retail Services, Inc. Proofing a refrigeration system operating state
US7752854B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring a condenser in a refrigeration system
US7752853B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring refrigerant in a refrigeration system

Also Published As

Publication number Publication date
KR100188324B1 (ko) 1999-06-01
DE69115422D1 (de) 1996-01-25
CN1028379C (zh) 1995-05-10
BR9103456A (pt) 1992-06-16
AU8153991A (en) 1992-04-02
EP0479421A1 (fr) 1992-04-08
MX9100629A (es) 1992-06-05
CA2046548A1 (fr) 1992-04-02
CN1060699A (zh) 1992-04-29
CA2046548C (fr) 2002-01-15
AU651606B2 (en) 1994-07-28
KR920008353A (ko) 1992-05-27
JPH06341387A (ja) 1994-12-13
JP2922343B2 (ja) 1999-07-19
DE69115422T2 (de) 1996-05-02

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