EP0276623A2 - Compresseurs rotatifs - Google Patents

Compresseurs rotatifs Download PDF

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Publication number
EP0276623A2
EP0276623A2 EP87630230A EP87630230A EP0276623A2 EP 0276623 A2 EP0276623 A2 EP 0276623A2 EP 87630230 A EP87630230 A EP 87630230A EP 87630230 A EP87630230 A EP 87630230A EP 0276623 A2 EP0276623 A2 EP 0276623A2
Authority
EP
European Patent Office
Prior art keywords
bellows
sides
pressure
generally equal
equal
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.)
Withdrawn
Application number
EP87630230A
Other languages
German (de)
English (en)
Other versions
EP0276623A3 (fr
Inventor
Mark Kushnir
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.)
ICE CRYOGENIC ENGINEERING LTD.
Original Assignee
ICE CRYOGENIC ENGINEERING Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from IL81414A external-priority patent/IL81414A0/xx
Priority claimed from IL82318A external-priority patent/IL82318A0/xx
Application filed by ICE CRYOGENIC ENGINEERING Ltd filed Critical ICE CRYOGENIC ENGINEERING Ltd
Publication of EP0276623A2 publication Critical patent/EP0276623A2/fr
Publication of EP0276623A3 publication Critical patent/EP0276623A3/fr
Withdrawn legal-status Critical Current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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/047—Sealing between piston and carter being provided by a bellow

Definitions

  • the present invention relates to compressors generally and more particularly to rotary compressors.
  • cryocoolers and other devices employing rotary compressors contamination of the working gas volume by lubricants and other debris.
  • conventional Stirling cycle cryocoolers have a measured reliability of 300 hours MTBF.
  • Four major failure modes have been identified in these cryocoolers: rotary bearing failure, compressor piston seal failure, contamination of the working gas volume by debris and lubricants and helium leakage.
  • a dynamic seal of Teflon-like plastic is employed in conventional cryocoolers.
  • the use of such seal continuously introduces debris into the cryocooler, hastening total breakdown of the system due to blockage of the heat exchanger.
  • the use of a dynamic seal also contributes to breakdown in another way. In the final stages of seal breakdown, at the 200 - 300 hours stage of operation, the dynamic seal becomes thin and thus improves the seal. This causes a large increase in pressure wave amplitude, causing failure of bearings and other components under excessive loading.
  • Cryogenic refrigerators including clearance seals are known in the art, as exemplified by U.S. Patents 4,539,818 and 4,520,629.
  • U.S. Patent 4,539,818 employs a ceramic clearance seal which, due to its low thermal conductivity, would appear to be unsuitable for use with a rotary drive compressor in which friction at the seal is significant.
  • U.S. Patent 4,520,629 employs a piston guide, which is relatively complex and space-­consuming.
  • the present invention seeks to provide an improved rotary compressor which will have an MTBF of up to 4,000 - 5,000 hours.
  • a rotary compressor comprising a rotary power source, a crankshaft driven by the rotary power source, a piston formed with a dynamic clearance seal and apparatus for sealing the working volume surrounding the piston from the volume surrounding the crankshaft.
  • the dynamic clearance seal comprises a labyrinth seal.
  • the dynamic clearance seal comprises a metal/metal clearance seal.
  • the apparatus for sealing comprises a bellows.
  • the apparatus of the present invention overcomes three of the four failure modes identified above in connection with conventional Stirling cryocoolers, rotary bearing failure, compressor piston seal failure and contamination of the working gas volume by debris and lubricants.
  • FIG. 1 illustrates a compressor constructed and operative in accordance with a preferred embodiment of the present invention and comprising a housing 30 in which is disposed an electric motor 32 having an eccentric output crankshaft 34.
  • Crankshaft 34 is supported in housing 30 by means of bearings 36 and 38.
  • a static seal 40 seals the electric motor 32 from the volume 41 surrounding the crankshaft.
  • a connecting rod 42 is bearing mounted at one end onto crankshaft 34 by means of a bearing 44 and onto a wrist pin 46 which is mounted onto a first piston portion 48.
  • First piston portion 48 is slidably mounted in a cylindrical mounting sleeve 50 which is formed with an air relief channel 52.
  • First piston portion is fixedly coupled to a second piston portion 54 which is slidably and sealingly disposed within a cylindrical channel 56 defining a second piston portion working volume 58.
  • Volume 58 may communicate with a regenerator and heat exchanger (not shown) of a Stirling cryocooler or any other suitable compressor output device via an output channel 60.
  • second piston portion 54 is formed with a dynamic clearance seal 62, such as a labyrinth seal or a maetal/metal clearance seal typically formed of stainless steel.
  • a dynamic clearance seal 62 such as a labyrinth seal or a maetal/metal clearance seal typically formed of stainless steel.
  • the second piston portion working volume 58 is sealed from the remainder of the interior of the compressor, i.e. from volume 41, in order to prevent contamination of the working volume 58.
  • This sealing is effected, in a preferred embodiment of the invention by means of a bellows 66, which is sealed at one end between a flange 68 integrally formed with mounting sleeve 50 and a butt end 70 of channel 56.
  • the opposite end of bellows 66 is sealed between the first piston portion 48 and the second piston portion 54 by means of a sealing ring 72.
  • the bellows 66 is typically formed of stainless steel.
  • the bellows 66 is compressed by a maximum amount which is a very small percentage of its overall length, typically under 10%.
  • the pressures on opposite sides of the bellows are maintained generally the same, thus preventing premature bellows failure. This is made possible by location of the bellows upstream of the working gas volume 58, so that the pressure pulses generated by the compressor are not applied thereto.
  • An end plate 74 is typically sealed onto the remainder of housing 30 by means of a sealing ring 76.
  • FIG. 2 illustrates a compressor similar in all relevant respects to the compressor of Fig. 1, with the exception of the structural features described hereinbelow. Similar structural components are identified by the same reference numerals in Figs. 1 and 2.
  • piston portions 148 and 154 are typically integrally formed.
  • bellows 166 is sealingly mounted at one end thereof onto a shoulder 168 of the first piston portion 148 and sealingly mounted at an opposite end thereof onto a cylindrical protrusion 170 of cylindrical channel 56.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Mechanical Sealing (AREA)
EP87630230A 1987-01-28 1987-11-05 Compresseurs rotatifs Withdrawn EP0276623A3 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
IL81414A IL81414A0 (en) 1987-01-28 1987-01-28 Rotary compressor
IL81414 1987-01-28
IL82318A IL82318A0 (en) 1987-04-23 1987-04-23 Rotary compressors
IL82318 1987-04-23

Publications (2)

Publication Number Publication Date
EP0276623A2 true EP0276623A2 (fr) 1988-08-03
EP0276623A3 EP0276623A3 (fr) 1989-02-15

Family

ID=26321642

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87630230A Withdrawn EP0276623A3 (fr) 1987-01-28 1987-11-05 Compresseurs rotatifs

Country Status (2)

Country Link
EP (1) EP0276623A3 (fr)
JP (1) JPS6445979A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0340150A1 (fr) * 1988-04-27 1989-11-02 Digital Equipment Corporation Compresseur à vilebrequin rotatif
FR2635830A1 (fr) * 1988-08-23 1990-03-02 Commissariat Energie Atomique Machine volumetrique de type pompe ou compresseur depourvue de lubrification
DE19633170A1 (de) * 1996-08-17 1998-02-19 Teves Gmbh Alfred Eelektromotor-/Pumpenaggregat
EP1813810A2 (fr) * 2006-01-30 2007-08-01 Ingersoll-Rand Company Pompe à piston avec soufflets atmosphériques

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR703152A (fr) * 1929-12-30 1931-04-25 Compresseur
GB656498A (en) * 1948-10-05 1951-08-22 Jean Lavigne Fluid compressors
FR994679A (fr) * 1949-09-05 1951-11-21 Compresseur perfectionné
FR1046551A (fr) * 1940-10-18 1953-12-08 Perfectionnements aux compresseurs
US2791372A (en) * 1945-04-26 1957-05-07 Anthony A Abbatiello Pump
FR1570963A (fr) * 1967-07-07 1969-06-13

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR703152A (fr) * 1929-12-30 1931-04-25 Compresseur
FR1046551A (fr) * 1940-10-18 1953-12-08 Perfectionnements aux compresseurs
US2791372A (en) * 1945-04-26 1957-05-07 Anthony A Abbatiello Pump
GB656498A (en) * 1948-10-05 1951-08-22 Jean Lavigne Fluid compressors
FR994679A (fr) * 1949-09-05 1951-11-21 Compresseur perfectionné
FR1570963A (fr) * 1967-07-07 1969-06-13

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0340150A1 (fr) * 1988-04-27 1989-11-02 Digital Equipment Corporation Compresseur à vilebrequin rotatif
FR2635830A1 (fr) * 1988-08-23 1990-03-02 Commissariat Energie Atomique Machine volumetrique de type pompe ou compresseur depourvue de lubrification
DE19633170A1 (de) * 1996-08-17 1998-02-19 Teves Gmbh Alfred Eelektromotor-/Pumpenaggregat
US6200109B1 (en) 1996-08-17 2001-03-13 Continental Teves Ag & Co., Ohg Electromotor/pump assembly
EP1813810A2 (fr) * 2006-01-30 2007-08-01 Ingersoll-Rand Company Pompe à piston avec soufflets atmosphériques
EP1813810A3 (fr) * 2006-01-30 2007-09-12 Ingersoll-Rand Company Pompe à piston avec soufflets atmosphériques
US8632322B2 (en) 2006-01-30 2014-01-21 Ingersoll-Rand Company Plunger pump with atmospheric bellows

Also Published As

Publication number Publication date
JPS6445979A (en) 1989-02-20
EP0276623A3 (fr) 1989-02-15

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Inventor name: KUSHNIR MARK