EP0537666A2 - Appareil pour la récupération d'un fluide frigorigène - Google Patents

Appareil pour la récupération d'un fluide frigorigène Download PDF

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Publication number
EP0537666A2
EP0537666A2 EP92117430A EP92117430A EP0537666A2 EP 0537666 A2 EP0537666 A2 EP 0537666A2 EP 92117430 A EP92117430 A EP 92117430A EP 92117430 A EP92117430 A EP 92117430A EP 0537666 A2 EP0537666 A2 EP 0537666A2
Authority
EP
European Patent Office
Prior art keywords
piston
crankarm
cylinder wall
compressor
motor
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Withdrawn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
EP92117430A
Other languages
German (de)
English (en)
Other versions
EP0537666A3 (en
Inventor
Carmelo J. Scuderi
Charles K. Forner
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.)
Engineering & Sales Associates Inc
Original Assignee
Engineering & Sales Associates Inc
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
Application filed by Engineering & Sales Associates Inc filed Critical Engineering & Sales Associates Inc
Publication of EP0537666A2 publication Critical patent/EP0537666A2/fr
Publication of EP0537666A3 publication Critical patent/EP0537666A3/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/002—Collecting refrigerant from a cycle

Definitions

  • the present invention relates to an apparatus for recovering a refrigeration fluid from a refrigeration system and delivering the recovered fluid to a refrigerant receiver.
  • refrigerant recovery devices be readily portable, e.g. so that a service person may transport the recovery device from his vehicle to a rooftop air conditioning unit without undue time and effort.
  • Known portable CFC recovery units include a conventional refrigerant compressor for transferring refrigerant from an apparatus, e.g. a refrigeration unit, to a receiver, e.g. a pressure vessel.
  • a conventional refrigerant compressor for transferring refrigerant from an apparatus, e.g. a refrigeration unit, to a receiver, e.g. a pressure vessel.
  • the use of a conventional refrigerant compressor in a portable CFC recovery unit has several drawbacks.
  • a conventional 1/2 HP refrigerant compressor weights about 40 pounds and accounts for a significant portion of the overall weight, i.e. between about 70 lb and about 100 lb, of a typical recovery unit.
  • conventional refrigerant compressors are designed to operate on a closed loop wherein lubricant is carried in the refrigerant and is continuously cycled through the system.
  • lubricant is not returned to the compressor potentially resulting in insufficient lubrication and premature wear of the compressor. This problem is aggravated by the need to pull a vacuum on the unit from which the refrigerant is being recovered.
  • the lubricant in the refrigerant being recovered may include contaminants, e.g. hydrochloric acid and/or hydrofluoric acid, which may damage the compressor.
  • the object of the present invention is to propose a recovery apparatus for transfering a gas phase fluid from a refrigeration unit to a refrigerant receiver, that is better suited to this task than prior art apparatuses using conventional refrigerant compressors.
  • the invention proposes an apparatus including a light-weight refrigerant compressor for transferring refrigerant.
  • the compressor includes a tubular cylinder wall, a cylinder head enclosing one end of the cylinder wall and defining an intake port and an outlet port, and valve means for controlling flow through the intake and outlet ports.
  • a piston is slidably received within the cylinder wall and provided with self lubricating bidirectional annular seal means for sealing between the piston and cylinder wall.
  • the compressor further includes means for reciprocally moving the piston within the cylinder wall to provide an intake stroke and an outlet stroke.
  • the self lubricating feature of the compressor of the present invention avoids the problems of oil loss, oil contamination and associated compressor damage as well as eliminating the need for an oil separator.
  • the bidirectional seal feature allows the compressor of the present invention to provide a vacuum intake stroke and thereby completely empty a system of used refrigerant.
  • the cylinder wall comprises hardened steel and the inner diametral surface of the cylinder wall is honed to a finish between about 2 microns and about 16 microns.
  • the piston comprises aluminum or an aluminum alloy.
  • the means for reciprocally moving comprises an electric motor, a crankarm operatively associated with the electric motor and a connecting rod operatively associated with the crankarm and with the piston.
  • the crankarm is mounted on an input shaft and the crankarm and motor are operatively associated by reduction means for coupling the motor and the shaft.
  • the motor comprises an open frame universal Class A electric motor having an operating speed range of about 8,000 rpm to about 25,000 rpm
  • the reduction gear means provides a reduction between about 4:1 and about 6:1
  • the shaft and crankarm operate in the range of about 2,000 rpm to about 4,000 rpm.
  • the motor of the compressor of the present invention is very lightweight, but runs at a relatively high speed.
  • the reduction means of the compressor of the present invention allow use of the lightweight high speed motor by reducing the speed of the input shaft so that the piston and cylinder assembly of the compressor of the present invention operates in a range within which self lubricating piston seals may be employed.
  • the piston is laterally displaced, toward the compression side, relative to the crankarm such that an extension of the centerline of the piston is laterally displaced from the center of rotation of the crankarm.
  • the lateral displacement of the piston relative to the center of rotation of the crankarm dramatically reduces piston seal wear and thereby prolongs the service life of the corresponding embodiment of the compressor of the present invention.
  • Each of the embodiments of the bidirectional seal of the compressor of the present invention allow operation at relatively high speed, i.e. between about 2,000 rpm and 4,000 rpm, at elevated pressure, i.e. about 400 psig, while exposed to a variety of refrigerants and associated contaminants.
  • the piston defines a first annular groove and a pair of peripheral annular grooves.
  • the peripheral grooves are spaced apart from and disposed on opposite sides for the first annular groove.
  • An annular seal is disposed in the first annular groove and elastomeric means are disposed in the first groove between the piston and the annular seal for urging the annular seal toward the cylinder wall.
  • Guide rings are disposed in each of the respective peripheral grooves for maintaining the piston in a parallel orientation relative to the cylinder wall.
  • the annular seal comprises a carbon filled PTFE matrix composite material
  • the guide rings comprise a graphite filled PTFE matrix composite material
  • the elastomeric means comprises a ring of chlorosulfonated elastomer, a polychloroprene elastomer, a perfluorinated elastomer or an EPDM elastomer.
  • the piston defines a pair of annular grooves and the seal means includes a first unidirectional annual seal, disposed in one of said grooves, for sealing between the piston and cylinder wall to provide a vacuum intake stroke and a second unidirectional seal, disposed in the other of said annular grooves, for sealing between the piston and cylinder to provide a high pressure outlet stroke.
  • FIGURE 1 shows a schematic diagram of the apparatus of the present invention.
  • FIGURE 2 shows a schematic top view of the compressor of the present invention.
  • FIGURE 3 shows a cross sectional view of a portion of the compressor of the present invention.
  • FIGURE 4 shows a schematic drawing of a portion of an embodiment of a compressor according to the present invention.
  • FIGURE 5 shows a schematic drawing of a portion of an alternative embodiment of a compressor according to the present invention.
  • FIGURE 6 shows a cross sectional view of a portion of an embodiment of the compressor of the present invention.
  • FIGURE 7 shows a cross sectional view of a portion of a second embodiment of the compressor of the present invention.
  • FIGURE 8 shows a cross sectional view of a portion a third embodiment of the compressor of the present invention.
  • FIGURE 9 shows a schematic diagram of an alternative embodiment of the compressor of the present invention.
  • the apparatus of the present invention allows recovery of a compressible refrigeration fluid from a refrigeration system 2 and delivery of the recovered fluid to a refrigerant receiver 6.
  • the refrigeration system includes a port 4, the receiver includes first port 8 and second port 10.
  • the apparatus of the present invention includes a discriminator chamber 12.
  • the discriminator chamber 12 includes an inlet port 14, a liquid inlet port 15, a liquid outlet port 16, and a gas outlet port 18.
  • Conduit 20 provides a fluid flow connection between refrigeration system port 4 and inlet port 14 of the discriminator chamber 12.
  • a valve 22 allows control of flow through conduit 20 and a filter dryer 24 allows removal of moisture and particulate contaminants from the refrigerant removed from the refrigeration system 2.
  • a conduit 26 is provided for directing liquid phase refrigeration fluid from port 16 of discriminator chamber 12 to port 8 of receiver 6.
  • Conduit 26 is provided with a solenoid valve 28 for controlling flow through conduit 26 and an actuator 30 opening and closing solenoid valve 28.
  • the apparatus of the present invention includes a compressor 32, a condensor 34 and a back pressure regulator 36 for condensing gas phase refrigerant fluid and providing a low pressure stream of substantially liquid phase fluid to conduit 26.
  • Conduit 38 allows gas phase refrigerant fluid to flow from port 18 of discriminator chamber 12 to compressor 32.
  • Conduit 38 is provided with a solenoid valve 40 for controlling flow through conduit 38.
  • An actuator 42 is provided for opening and closing valve 40.
  • Conduit 44 establishes a fluid flow connection between compressor 32 and condensor 34.
  • Fan 46 provides a flow of air for removing heat from between the condenser 34 and the back pressure regulator 36.
  • Conduit 50 establishes a fluid flow connection between back pressure regulator 36 and conduit 26.
  • the compressor 32 may comprise a conventional refrigerant compressor or a compressor of the present invention.
  • a compressor 32' of the present invention includes a piston/cylinder/cylinder head assembly 101 having a a tubular cylinder wall 102.
  • the tubular cylinder wall 102 may comprise, e.g. steel or stainless steel.
  • the cylinder wall 102 comprises hardened steel.
  • the cylinder wall 102 comprises A2 steel, hardened to Rockwell C60-65.
  • the inner diametral surface of the cylinder wall 102 is honed to a very smooth finish, e.g. a 2 to 16 micron finish, to reduce wear on the piston seals (discussed further below) and reduce leakage.
  • the cylinder head 104 encloses one end of the tubular cylinder wall 102.
  • the cylinder head 104 is provided with an intake port 106 and an outlet port 108 as well as an intake valve and outlet valve (not shown) for controlling flow through intake port 106 and outlet port 108.
  • a piston 110 is slidably received within the tubular cylinder wall 102.
  • the compressor, housing, piston 110 and head 104 are each made from aluminum or a light-weight metal alloy.
  • Annular seal 112 circumscribes the piston.
  • Annular seal 112 is a bidirectional self lubricating annular seal for sealing between the piston 110 and tubular cylinder wall 102 so that the apparatus of the present invention provides a high pressure outlet stroke and a vacuum intake stroke.
  • a piston ring 113 is provided to maintain piston 110 axially aligned within the tubular wall 102.
  • a piston rod 114 is provided for reciprocally moving the piston within the tubular cylinder wall 102.
  • the piston rod 114 is rotatably mounted on wrist pin 116. Wrist pin 116 is secured to the end of crankarm 18.
  • Shaft 120 is provide for rotating crankarm 118.
  • Gears 122 and 124 couple shaft 120 with the output shaft 126 of motor 128.
  • motor 128 is an open frame Universal Class A electric motor having an operating speed between about 8,000 and about 25,000 rpm.
  • the gears 122 and 124 are selected to provide shaft 120 with an operating range of about 2,000 to 4,000 rpm, i.e. provide a reduction of from about 4:1 to about 6:1 relative to the operating range of the motor 128.
  • FIGURE 4 shows a schematic diagram of a first piston and cylinder arrangement 144 wherein the cylinder 146 is oriented so that an extension of the centerline 145 of the cylinder 146 and piston 150 passes through the center of rotation 149 of the crankarm 148.
  • the circle swept out by rotation of the crankarm 148 is shown by the dashed line in FIGURE 4.
  • Piston 150 is slidably received within the cylinder 146 and is connected to crankarm 148 by wrist pin 152, connecting rod 154 and crank pin 156.
  • the piston and cylinder arrangement 144 is shown in the middle of the compression stroke.
  • the compression stroke i.e.
  • crankarm 148 continues until the end of the crankarm 148 reaches the top center position and crank arm 148 is aligned with the centerline of the piston 146.
  • the force acting on the piston 146 during the compression stroke may be separated into two components, i.e. the upwardly directed compressive force F1 and the side force F2, directed perpendicularly to the compressive force.
  • FIGURE 5 A preferred embodiment of the piston and cylinder arrangement 158 of the compressor of the present invention is shown in FIGURE 5.
  • the centerline 159 of the cylinder 160 and piston 164 is laterally displaced from the center of rotation 161 of the crankarm 162.
  • the centerline of the cylinder 160 is displaced from the center of rotation 161 of crankarm 162 by a distance equal to about one half of the diameter (D) of circle swept out by rotation of the crankarm 162.
  • Piston 164 is slidably received in cylinder 160 and connected to crankarm 162 by wrist pin 166, connecting rod 168 and crank pin 170.
  • crankarm 162 The piston and cylinder arrangement 158 is shown in the middle of the compression stroke. Further rotation of crankarm 162 continues the compression stroke until crank pin 170 reaches the top center position on crankarm 162 in a manner similar to that discussed above in regard to FIGURE 4. Unlike the embodiment shown in FIGURE 4, the top center position on the crank arm 162 is not aligned with the centerline of cylinder 160 and wrist pin 170 crosses the centerline of cylinder 160 as it sweeps from the piston shown in FIGURE 5 to the top center position on crankarm 162.
  • the forces acting on piston 164 may be separated into two components; i.e. upwardly directed compressive force F3 and side force F4, directed perpendicularly to compressive force F3.
  • the inventors have calculated that, other factors being equal, the preferred embodiment of FIGURE 5 provides several advantages over the embodiment shown in FIGURE 4, i.e.:
  • FIGURE 6 shows one embodiment of the self lubricating bidirectional annular seal of the compressor 32 of present invention.
  • Piston 110 defines an annular groove 130 which circumscribes the piston.
  • Annular seal 112 is disposed within groove 130.
  • the annular seal 112 comprises a graphite or carbon filled fluoropolymer, e.g. polytetrafluoroethylene.
  • a chemical resistant elastomeric ring 132 urges piston ring 112 towards cylinder wall 102 to provide a bidirectional seal.
  • the elastomeric ring 132 comprises a chlorosulfonated polyethylene elastomer, a polychloroprene elastomer, a perfluorinated elastomer or an ethylene propylene diene (EPDM) elastomer.
  • EPDM ethylene propylene diene
  • FIGURE 7 A schematic cross sectional view of a portion of a alternative embodiment 172 of the self lubricating bidirectional annular seal of the compressor 32 of the present invention is shown in FIGURE 7.
  • the embodiment 172 includes a cylinder wall 174 and a piston 176.
  • Piston 176 defines three spaced apart annular grooves 178, 180, 182.
  • Annular seal 184 is disposed in the central groove 180 and urged toward cylinder wall 174 by elastomeric ring 186 disposed in grooves 180 between annular seal 184 and piston 176.
  • Guide rings 188, 190 for maintaining piston 176 in axial alignment with cylinder wall 174 are disposed in peripheral grooves 178, 182, respectively.
  • annular seal 184 and guide rings 188, 190 comprise a graphite or carbon filled fluoropolymer matrix composite material.
  • annular seal 184 comprises a carbon filled polytetrafluoroethylene matrix material known as TURCITE ® 109. Suitable seals may be obtained commercially, e.g. from W.S. Shamban Company of Fort Wayne, Indiana.
  • the guide rings 188, 190 comprises a graphite filled polytetrafluoroethylene matrix material known as TURCITE® 51. Suitable wear rings may be obtained commercially, e.g. from W.S. Shamban Company.
  • the TURCITE® 109 material exhibits a tensile strength of 3000 psi and an elongation at break of 200% (each determined according to ASTM D 1457-81A), a specific gravity of 2.10 and a shore D hardness of 60 - 65.
  • the TURCITE® 51 material exhibits a tensile strength of 1800 psi and an elongation at break of 100% (each determined according to ASTM D 1457-81A), a specific gravity of 2.06 and a shore D hardness of 63.
  • elastomeric ring 186 comprises a CFC resistant, oil resistant and contaminant, e.g. HF or HCL, resistant, elastomer having good temperature resistance, i.e. is stable at temperatures in the rang of 300°F to 400°F.
  • Suitable materials include perfluorinated elastomers, chlorosulfonated polyethylene elastomers, a polychloroprene elastomers and ethylene propylene diene elastomers.
  • the elastomeric ring 186 comprises an elastomer known as TUREL® EGA. Suitable elastomeric rings may be obtained commercially, e.g. from W.S. Shamban. It should be noted that the choice of elastomer potentially limits the applicability of the compressor, since a single choice of elastomer cannot offer optimal resistance to all CFCS.
  • FIGURE 8 A schematic cross sectional view of another alternative embodiment of the self lubricating bidirectional annular seal of compressor 32 that offers broad based applicability is shown in FIGURE 8 in which piston body 110' and piston cap 111 sealingly connected to piston body 110' are slidably received within tubular cylinder wall 102 and in which two annular grooves 134, 139 circumscribe piston body 110'.
  • a pair of chemically resistant unidirectional seals 136 and 140 are disposed in the grooves 134, 139, respectively.
  • the seals 136, 140 are "U-cup" type seals, each defining an annular groove therein.
  • seals 136, 140 each comprise a fluoropolymer. More preferably, each of the unidirectional seals 136, 140 comprise a glass filled fluoropolymer matrix composite material. Most preferably, U-cup seals 136, 140 comprise a material known as TURCITE® 404.
  • the TURCITE® 404 material is a glass and molybdenum filled polytetrafluoroethylene having a tensile strength of about 3500 psi (ASTM D638), an elongation at break of about 230% (ASTM D638), a shore D hardness of about 55 (ASTM D2240) and a specific gravity of 2.18 (ASTM D792).
  • springs 138, 141 each comprises stainless steel.
  • the springs 138, 141 each comprise 302 stainless steel.
  • Suitable U-cup seal and spring assemblies are commercially available, e.g. from American Variseal of Broomfield, Colorado.
  • guide rings 142, 143 comprise a graphite filled polytetrafluoroethylene matrix material.
  • guide rings 142, 143 comprise the TURCITE® 51 material described above.
  • FIGURE 9 An alternative embodiment 32'' of the compressor of the present invention is shown in FIGURE 9.
  • the compressor 32'' includes a motor 128', a rotatably mounted output shaft 126', a rotatably mounted input shaft 120', a crankarm 118', a piston rod 114' and a piston/cylinder/cylinder head assembly 101' and is analogous to compressor 32' shown in FIGURES 2 with the exception that pulleys 194, 196 and belt 198 have been substituted for gears 122, 124 as a means for transmitting power from shaft 126' to shaft 120'.
  • the belt driven compressor is more cost effective than the gear driven embodiment and, while requiring maintenance more frequently than the gear driven embodiment, is easier and less expensive to repair.
  • the belt driven embodiment is also quieter and exhibits less vibration than the gear driven embodiment of FIGURE 2.
  • valve 28 is normally closed and valve 40 is normally open.
  • the discriminator chamber 12 includes float sensor 52 for sensing the level of liquid phase refrigerant fluid in the discriminator chamber 12.
  • Sensor 52 is responsive to the level of liquid phase refrigerant fluid in the discrimination chamber 12 and provides a control signal if the discriminator chamber 12 is full of liquid phase refrigerant fluid.
  • Actuators 30 and 42 are responsive to the control signal provided by sensor 52. In response to the control signal, actuator 42 closes valve 40 to prevent liquid from flowing from the discriminator chamber 12 to the compressor 32 and opens valve 28 to allow the liquid to drain from the discriminator chamber 12 through conduit 26 to receiver 6.
  • a bypass conduit 56 is provided to allow fluid to flow directly from condenser 34 to inlet port 8 of receiver 6.
  • the bypass conduit 56 is provided with a solenoid valve 58 for controlling flow through conduit 56.
  • An actuator 60 is provided to open and close solenoid valve 58. Valve 58 is normally closed.
  • a pressure sensor 62 is responsive to the pressure within discriminator chamber 12 and provides a control signal if the pressure in discriminator chamber 12 falls below a predetermined value.
  • Actuator 60 is responsive to the control signal from pressure sensor 62 and opens valve 58 in response to the control signal.
  • the recovery apparatus of the present invention includes a safety chamber 64.
  • Safety chamber 64 includes an inlet port 66, a gas outlet port 68 and a liquid outlet port 70.
  • a conduit 72 is provided for allowing fluid flow between port 10 of receiver 6 and inlet port 66 of safety chamber 64.
  • Conduit 72 is provided with a solenoid valve 74 for controlling flow through conduit 72.
  • An actuator 76 is provided for opening and closing solenoid valve 74.
  • Conduit 78 allows fluid to flow from gas exit port 68 of safety chamber 64 to conduit 38 and on to compressor 32.
  • Conduit 80 is provided with a solenoid valve 82 for controlling flow through conduit 80.
  • An actuator 84 is provided for opening and closing solenoid valve 82.
  • Inlet tube 86 extends into receiver 6 through port 10 of receiver 6 to an open end 88.
  • gas phase refrigerant fluid flows through conduit 72, safety chamber 64 and conduit 78 to compressor 32.
  • the apparatus of the present invention has two modes of operation and may be used to recover refrigeration fluid from a refrigeration system (recovery mode) and to charge refrigeration fluid from receiver to a refrigeration system (charging mode).
  • compressor 32 and condensor fan 46 are turned on.
  • Compressor 32 lowers the pressure in receiver 6 as well as compressing the influent stream 38 of gas phase fluid. Fluid evaporates from the receiver 6 is directed through conduit 72, inlet 66, chamber 64, outlet 68, conduit 78 and is combined with influent gas stream 38. Evaporation of refrigerant fluid from receiver 6 lowers the temperature of the liquid phase fluid remaining in receiver 6.
  • the apparatus maintains a pressure differential to drive fluid from refrigeration unit 2 to receiver 6 until substantially all refrigerant has been removed from the refrigeration unit.
  • the compressor 32 In the charging mode, the compressor 32 is turned on, fan 46 is turned off, back pressure regulator 36 is closed and valve 58 is open. Fluid is evaporated from the receiver and compressed in the compressor 32 to form a high pressure elevated temperature stream of refrigerant fluid.
  • the high pressure elevated temperature stream of refrigerant is introduced to the receiver 6 through conduit 26 to increase the pressure within receiver 6 and force fluid from receiver 6 through a conduit (not shown) to the refrigeration system 2 being charged.
  • the discrimination chamber of the present invention allows liquid phase refrigerant to bypass the compressor, condensor and back pressure regulator as it passes from the refrigeration unit to the refrigerant receiver and thereby allow refrigerant to be removed for the refrigeration unit in significantly less time than possible with the apparatus described in U.S. Patent No. 4,766,733.
  • Conventional refrigerant receivers are provided with a safety valve in order to preclude the generation of internal pressures within a refrigerant receiver that exceed the pressure rating of the container.
  • the safety valve opens at a predetermined maximum pressure that is below the maximum pressure rating of the receiver.
  • the amount of refrigerant introduced to a receiver must be controlled.
  • refrigerant containers are filled by weight.
  • a weighting apparatus constitutes a cumbersome additional piece of equipment to transport.
  • the safety chamber of the present invention allows control of the amount of refrigerant introduced to the receiver without requiring any equipment in addition to the apparatus of the present invention.
  • Conventional refrigeration compressors are typically heavy, e.g. typically about 40 lb, cumbersome devices which include a thick cast iron cylinder wall.
  • the compressor of the present invention is lightweight, i.e. about 10 lb, and easily portable, thereby making a lightweight, i.e. on the order of 30 lb, and easily portable refrigerant recovery unit feasible.
  • the materials of construction of conventional refrigerant compressors are not resistant to impurities, e.g. acids, present in used refrigerant fluids.
  • the compressor of the present invention is adapted for transferring contaminated refrigerants.
  • Conventional refrigerant compressors include unidirectional seals and are unable to provide a vacuum intake stroke.
  • the seals on the piston of the refrigerant compressor of the present invention are bidirectional and the refrigerant compressor of the present invention can thereof be used to pull the inlet pressure below atmospheric pressure, and allow a refrigerant system to be completely emptied of used refrigerant.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
EP19920117430 1991-10-18 1992-10-13 Apparatus for recovering a refrigerant fluid Withdrawn EP0537666A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US77873491A 1991-10-18 1991-10-18
US778734 1991-10-18

Publications (2)

Publication Number Publication Date
EP0537666A2 true EP0537666A2 (fr) 1993-04-21
EP0537666A3 EP0537666A3 (en) 1993-11-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920117430 Withdrawn EP0537666A3 (en) 1991-10-18 1992-10-13 Apparatus for recovering a refrigerant fluid

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EP (1) EP0537666A3 (fr)
JP (1) JPH05240536A (fr)
AU (1) AU655678B2 (fr)
CA (1) CA2080760C (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1127620C (zh) * 1996-12-19 2003-11-12 诺瓦达里股份公司 往复式压缩机

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU671988B2 (en) * 1992-05-14 1996-09-19 Angelo Talarico Gas processor
JP2599086B2 (ja) * 1993-03-05 1997-04-09 岩谷産業株式会社 フッ素系ガスの回収方法及びその装置
CN116771637B (zh) * 2023-08-24 2023-10-24 麦金太尔(江苏)空调有限公司 一种空调压缩机

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3358914A (en) * 1964-10-06 1967-12-19 Tilghman S Ltd Compressors
EP0380302A2 (fr) * 1989-01-23 1990-08-01 Seismic Systems, Inc. Système d'étanchéification pour piston à haute pression
US4981020A (en) * 1990-02-02 1991-01-01 Scuderi Carmelo J Apparatus for recovering refrigerant

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4961020A (en) * 1989-03-03 1990-10-02 General Electric Company Sodium vapor lamp for sonic pulse operation

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3358914A (en) * 1964-10-06 1967-12-19 Tilghman S Ltd Compressors
EP0380302A2 (fr) * 1989-01-23 1990-08-01 Seismic Systems, Inc. Système d'étanchéification pour piston à haute pression
US4981020A (en) * 1990-02-02 1991-01-01 Scuderi Carmelo J Apparatus for recovering refrigerant

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1127620C (zh) * 1996-12-19 2003-11-12 诺瓦达里股份公司 往复式压缩机

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CA2080760C (fr) 1995-11-28
AU2709092A (en) 1993-04-22
AU655678B2 (en) 1995-01-05
EP0537666A3 (en) 1993-11-03
JPH05240536A (ja) 1993-09-17
CA2080760A1 (fr) 1993-04-19

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