US3568466A - Refrigeration system with multi-stage throttling - Google Patents

Refrigeration system with multi-stage throttling Download PDF

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Publication number
US3568466A
US3568466A US819685A US3568466DA US3568466A US 3568466 A US3568466 A US 3568466A US 819685 A US819685 A US 819685A US 3568466D A US3568466D A US 3568466DA US 3568466 A US3568466 A US 3568466A
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United States
Prior art keywords
compressor
ports
throttling
admission
refrigeration system
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Expired - Lifetime
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US819685A
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Tore Brandin
Knut Anders Lennart Lundberg
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Stal Refrigeration AB
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Stal Refrigeration AB
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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • a refrigerating system provided with multi-stage throtfling and with a positive displacement compressor of the rotary type, the casing of the compressor being provided between its low pressure and high pressure ports with one or more admission ports for intermediate pressure gas from liquid separators located between throttling points.
  • the gas formed during throttling is supplied through these admission ports to the working compartment of the compressor.
  • the opening and closing of the admission ports is achieved by the action of the compressor which has its rotor lobes operative as valves for the admission ports.
  • multi-stage throttling is used in conjunction with multi-stage compression and with or without intercooling.
  • the advantage of this arrangement is that, for a given swept volume, a greater refrigerating effect is obtained, since a larger enthalpy difference is obtained on the low pressure side.
  • Multi-stage compression provides an even lower pressure rise per stage which gives even higher volumetric and total efliciencies. It is usual to employ more than one compressor or one compressor with more than one working compartment, this is, high pressure and low pressure cylinders in piston compressors or several wheels operating at different pressure levels in centrifugal compressors.
  • the present invention relates to a refrigeration system provided with multi-stage throttling and with a positive displacement compressor of the rotary type and is principally characterized by the fact that there is provided between the low pressure and high pressure ports in the compressor, one or several admission ports in the casing of the compressor, for the admission of intermediate pressure gas from liquid separators located between the throttling points.
  • the gas formed during throttling is supplied through these admission ports to the working compartment of the compressor.
  • the opening and closing of the admission ports is achieved by the compressor and in a screw compressor this is carried out by the rotor lobes.
  • the ports are located in the wall of the working compartment to obtain the necessary intermediate pressure.
  • the intermediate pressure of the refrigeration system is determined by the mean pressure in that part of the working compartment in which the port is located.
  • FIG. 1 shows the diagrammatic arrangement of a refrigeration system in accordance with the present invention
  • FIG. 2 is a longitudinal sectional view through a screw compressor in which the improvements are embodied.
  • the compressor is designated at 1.
  • the gas compressed by the compressor is discharged through a pipe 2 to a condenser 3 from which the refrigerant liquid flows through pipe 4 and through a throttling device 5 to a liquid separator 6.
  • the refrigerant liquid at intermediate pressure flows through another throttling device 8 to an evaporator 9 from which the gas is drawn back into the compressor.
  • the gas formed during throttling through the throttling device 5 is drawn through a pipe 10, provided with a control valve 11, to the compressor through one of several ports 12 in the wall of the compressor casing.
  • the ports 12 consist of several small holes located along a spiral line which has the same pitch angle as the rotor lobes 16 and grooves between the same. This arrangement decreases the amount of leakage across the periphery of the rotor lobes from one working compartment which is at a higher pressure, to the succeeding compartment which is at a lower pressure.
  • the positions at which the ports open and close are more readily defined.
  • the port 12 for the intermediate pressure gas is connected to a distribution chamber 13 integrally formed on the compressor casing.
  • the advantage of a system made in accordance with the present invention is that for a given compressor size, the refrigerating effect increases roughly proportionately with the enthalpy difference.
  • the specific power consumption of the compressor is improved since the power consumption due to the altered shape of the PV diagram after filling does not increase by the same amount as the enthalpy difference.
  • the port or ports 12 should preferably be located at a point where gas is supplied to the low pressure gas when the volume of the latter has decreased by 30% or more.
  • the low pressure port is designated at 14 and the high pressure port at 15.
  • a refrigeration system with multi-stage throttling and with a positive displacement compressor of the rotary type having a casing provided with high pressure and low pressure ports, said casing having at least one admission port, a liquid separator providing intermediate pressure gas to the compressor through the admission port in its casing, the liquid separator being located between throttling devices, the compressor being of the screw type and the admission port consisting of several holes disposed along a spiral line having the same pitch angle as lobes and grooves of a rotor of the compressor.
  • a refrigeration system wherein the admission ports in the casing for the gas of intermediate pressure, are connected to a collecting chamber provided on the casing and in communication with the liquid separator.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A REFRIGERATING SYSTEM PROVIDED WITH MULTI-STAGE THROTTLING AND WITH A POSITIVE DISPLACEMENT COMPRESSOR OF THE ROTARY TYPE, THE CASING OF THE COMPRESSOR BEING PROVIDED BETWEEN ITS LOW PRESSURE AND HIGH PRESSURE PORTS WITH ONE OR MORE ADMISSION PORTS FOR INTERMEDIATE PRESSURE GAS FROM LIQUID SEPARATORS LOCATED BETWEEN THROTTLING POINTS. THE GAS FORMED DURING THROTTLING IS SUPPLIED THROUGH THESE ADMISSION PORTS TO THE WORKING COMPARTMENT OF THE COMPRESSOR. THE OPENING AND CLOSING OF THE ADMISSION PORTS IS ACHIEVED BY THE ACTION OF THE COMPRESSOR WHICH HAS ITS ROTOR LOBES OPERATIVE AS VALVES FOR THE ADMISSION PORTS.

Description

March 9, 1971 BRANDlN ET AL REFRIGERATION SYSTEM WITH MULTI-STAGE THROTTLING Filed April 28, 1969 Fig.
3,568,466 REFRIGERATION SYSTEM WITH MULTI-STAGE THROTTLING Tore Brandin and Knut Anders Lennart Lundberg, Norrkoping, Sweden, assignors to Stal Refrigeration Aktiebolag, Norrkoping, Sweden Filed Apr. 28, 1969, Ser. No. 819,685 Claims priority, application Sweden, May 6, 1968, 6,054/ 68 Int. Cl. F251) 1/10 US. Cl. 62-510 2 Claims ABSTRACT OF THE DISCLOSURE A refrigerating system provided with multi-stage throtfling and with a positive displacement compressor of the rotary type, the casing of the compressor being provided between its low pressure and high pressure ports with one or more admission ports for intermediate pressure gas from liquid separators located between throttling points. The gas formed during throttling is supplied through these admission ports to the working compartment of the compressor. The opening and closing of the admission ports is achieved by the action of the compressor which has its rotor lobes operative as valves for the admission ports.
In refrigerating systems multi-stage throttling is used in conjunction with multi-stage compression and with or without intercooling. The advantage of this arrangement is that, for a given swept volume, a greater refrigerating effect is obtained, since a larger enthalpy difference is obtained on the low pressure side. Multi-stage compression provides an even lower pressure rise per stage which gives even higher volumetric and total efliciencies. It is usual to employ more than one compressor or one compressor with more than one working compartment, this is, high pressure and low pressure cylinders in piston compressors or several wheels operating at different pressure levels in centrifugal compressors.
The present invention relates to a refrigeration system provided with multi-stage throttling and with a positive displacement compressor of the rotary type and is principally characterized by the fact that there is provided between the low pressure and high pressure ports in the compressor, one or several admission ports in the casing of the compressor, for the admission of intermediate pressure gas from liquid separators located between the throttling points. The gas formed during throttling is supplied through these admission ports to the working compartment of the compressor. The opening and closing of the admission ports is achieved by the compressor and in a screw compressor this is carried out by the rotor lobes. The ports are located in the wall of the working compartment to obtain the necessary intermediate pressure.
The intermediate pressure of the refrigeration system is determined by the mean pressure in that part of the working compartment in which the port is located.
Reference is to be had to the accompanying drawing wherein an illustrative embodiment of the invention is disclosed and in which FIG. 1 shows the diagrammatic arrangement of a refrigeration system in accordance with the present invention and FIG. 2 is a longitudinal sectional view through a screw compressor in which the improvements are embodied.
States Patent Ofice Patented Mar. 9, 1971 The compressor is designated at 1. The gas compressed by the compressor is discharged through a pipe 2 to a condenser 3 from which the refrigerant liquid flows through pipe 4 and through a throttling device 5 to a liquid separator 6. From the separator 6 the refrigerant liquid at intermediate pressure flows through another throttling device 8 to an evaporator 9 from which the gas is drawn back into the compressor.
The gas formed during throttling through the throttling device 5 is drawn through a pipe 10, provided with a control valve 11, to the compressor through one of several ports 12 in the wall of the compressor casing. As illustrated on the screw compressor in FIG. 2, the ports 12 consist of several small holes located along a spiral line which has the same pitch angle as the rotor lobes 16 and grooves between the same. This arrangement decreases the amount of leakage across the periphery of the rotor lobes from one working compartment which is at a higher pressure, to the succeeding compartment which is at a lower pressure. In addition, the positions at which the ports open and close are more readily defined.
The port 12 for the intermediate pressure gas is connected to a distribution chamber 13 integrally formed on the compressor casing.
Compared with a refrigeration system with single stage throttling, the advantage of a system made in accordance with the present invention is that for a given compressor size, the refrigerating effect increases roughly proportionately with the enthalpy difference. In addition, the specific power consumption of the compressor is improved since the power consumption due to the altered shape of the PV diagram after filling does not increase by the same amount as the enthalpy difference.
The port or ports 12 should preferably be located at a point where gas is supplied to the low pressure gas when the volume of the latter has decreased by 30% or more.
The low pressure port is designated at 14 and the high pressure port at 15.
What is claimed is:
1. A refrigeration system with multi-stage throttling and with a positive displacement compressor of the rotary type, the compressor having a casing provided with high pressure and low pressure ports, said casing having at least one admission port, a liquid separator providing intermediate pressure gas to the compressor through the admission port in its casing, the liquid separator being located between throttling devices, the compressor being of the screw type and the admission port consisting of several holes disposed along a spiral line having the same pitch angle as lobes and grooves of a rotor of the compressor.
2. A refrigeration system according to claim 1, wherein the admission ports in the casing for the gas of intermediate pressure, are connected to a collecting chamber provided on the casing and in communication with the liquid separator.
References Cited UNITED STATES PATENTS 2,274,391 2/ 1942 Zwickl 62-510 2,277,647 3/1942 Jones 62-5 10 2,888,809 6/1959 Rachfal 62-5l0 FOREIGN PATENTS 76078 10/1954 Netherlands 62510 MEYER PERLIN, Primary Examiner
US819685A 1968-05-06 1969-04-28 Refrigeration system with multi-stage throttling Expired - Lifetime US3568466A (en)

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Application Number Priority Date Filing Date Title
SE06054/68A SE338576B (en) 1968-05-06 1968-05-06

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DE (1) DE6918573U (en)
FR (1) FR1571880A (en)
GB (1) GB1256391A (en)
SE (1) SE338576B (en)

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4863348A (en) * 1971-12-07 1973-09-03
US3808835A (en) * 1972-11-03 1974-05-07 Calspan Corp Refrigerant handling apparatus employing roots type compressor
JPS4954943A (en) * 1972-09-26 1974-05-28
US3827250A (en) * 1973-07-23 1974-08-06 Carrier Corp Economizer pressure regulating system
JPS49119252A (en) * 1973-03-19 1974-11-14
US3859814A (en) * 1973-10-03 1975-01-14 Vilter Manufacturing Corp Variable capacity rotary screw compressor
US3931718A (en) * 1970-04-16 1976-01-13 Hall-Thermotank Products Ltd. Refrigerant screw compression with liquid refrigerant injection
JPS5121163U (en) * 1974-08-02 1976-02-16
US3945219A (en) * 1970-08-25 1976-03-23 Kabushiki Kaisha Maekawa Seisakusho Method of and apparatus for preventing overheating of electrical motors for compressors
JPS51104459U (en) * 1975-02-20 1976-08-20
US3981703A (en) * 1974-04-23 1976-09-21 Stal-Refrigeration Ab Multistage vane type rotary compressor
US4005949A (en) * 1974-10-10 1977-02-01 Vilter Manufacturing Corporation Variable capacity rotary screw compressor
US4014182A (en) * 1974-10-11 1977-03-29 Granryd Eric G U Method of improving refrigerating capacity and coefficient of performance in a refrigerating system, and a refrigerating system for carrying out said method
JPS52101753A (en) * 1976-02-23 1977-08-26 Mayekawa Mfg Co Ltd Refrigerating apparatus
US4059968A (en) * 1974-06-28 1977-11-29 H. A. Phillips & Co. Refrigeration system
JPS5389059A (en) * 1977-01-12 1978-08-05 Toshiba Corp Air conditioner
JPS5532998U (en) * 1979-09-04 1980-03-03
JPS5564073U (en) * 1979-11-19 1980-05-01
US4211093A (en) * 1979-04-04 1980-07-08 Midolo Lawrence L Vapor cycle cooling system
JPS55135261U (en) * 1980-03-07 1980-09-26
JPS55144945U (en) * 1980-03-27 1980-10-17
US4467621A (en) * 1982-09-22 1984-08-28 Brien Paul R O Fluid/vacuum chamber to remove heat and heat vapor from a refrigerant fluid
WO1987003048A1 (en) * 1985-11-15 1987-05-21 Svenska Rotor Maskiner Ab Screw rotor compressor and refrigeration plant
US4742694A (en) * 1987-04-17 1988-05-10 Nippondenso Co., Ltd. Refrigerant apparatus
US5063750A (en) * 1988-06-17 1991-11-12 Svenska Rotor Maskiner Ab Rotary positive displacement compressor and refrigeration plant
DE4115905A1 (en) * 1990-05-15 1991-11-21 Toshiba Kawasaki Kk REFRIGERATION CIRCUIT ARRANGEMENT WITH A COMPRESSOR DEVICE HAVING TWO SIMULTANEOUSLY DRIVED COMPRESSOR UNITS
EP0768464A2 (en) * 1995-10-11 1997-04-16 Denso Corporation Scroll compressor
US5634350A (en) * 1994-09-20 1997-06-03 Microtecnica S.P.A. Refrigeration system
US5816055A (en) * 1994-02-03 1998-10-06 Svenska Rotor Maskiner Ab Refrigeration system anad a method for regulating the refrigeration capacity of such a system
US20040040332A1 (en) * 2002-09-03 2004-03-04 Bitzer Kuehlmaschinenbau Gmbh Screw compressor
US20050226758A1 (en) * 2002-12-03 2005-10-13 Bitzer Kuehlmaschinenbau Gmbh Screw compressor
CN103925753A (en) * 2013-01-16 2014-07-16 珠海格力电器股份有限公司 Air conditioning equipment
JP2015155652A (en) * 2014-02-20 2015-08-27 日立アプライアンス株式会社 Screw fluid machine and refrigeration cycle apparatus
CN105546893A (en) * 2016-02-26 2016-05-04 珠海格力电器股份有限公司 Flash tank, compressor system and air conditioner
US20180156501A1 (en) * 2015-08-11 2018-06-07 Carrier Corporation Screw Compressor Economizer Plenum for Pulsation Reduction
EP1751476B1 (en) * 2004-05-18 2021-10-20 Carrier Corporation Compressor lubrication

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2044388A1 (en) * 1969-12-22 1972-02-10 VEB Kühlautomat Berlin, χ 1197 Berlin Screw compressor
JPS508526B1 (en) * 1970-08-25 1975-04-04
GB1564115A (en) * 1975-09-30 1980-04-02 Svenska Rotor Maskiner Ab Refrigerating system
FR2541437B1 (en) * 1982-05-13 1985-08-23 Zimmern Bernard CENTRIFUGAL ECONOMIZER FOR REFRIGERATION
DE10258145A1 (en) * 2002-12-03 2004-06-24 Bitzer Kühlmaschinenbau Gmbh screw compressors

Cited By (54)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3931718A (en) * 1970-04-16 1976-01-13 Hall-Thermotank Products Ltd. Refrigerant screw compression with liquid refrigerant injection
US3945219A (en) * 1970-08-25 1976-03-23 Kabushiki Kaisha Maekawa Seisakusho Method of and apparatus for preventing overheating of electrical motors for compressors
JPS4863348A (en) * 1971-12-07 1973-09-03
JPS5031658B2 (en) * 1971-12-07 1975-10-14
JPS517853B2 (en) * 1972-09-26 1976-03-11
JPS4954943A (en) * 1972-09-26 1974-05-28
US3808835A (en) * 1972-11-03 1974-05-07 Calspan Corp Refrigerant handling apparatus employing roots type compressor
JPS49119252A (en) * 1973-03-19 1974-11-14
JPS5240467B2 (en) * 1973-03-19 1977-10-12
US3827250A (en) * 1973-07-23 1974-08-06 Carrier Corp Economizer pressure regulating system
JPS554239B2 (en) * 1973-10-03 1980-01-29
US3859814A (en) * 1973-10-03 1975-01-14 Vilter Manufacturing Corp Variable capacity rotary screw compressor
JPS5061710A (en) * 1973-10-03 1975-05-27
US3981703A (en) * 1974-04-23 1976-09-21 Stal-Refrigeration Ab Multistage vane type rotary compressor
US4059968A (en) * 1974-06-28 1977-11-29 H. A. Phillips & Co. Refrigeration system
JPS5121163U (en) * 1974-08-02 1976-02-16
JPS5430212Y2 (en) * 1974-08-02 1979-09-22
US4005949A (en) * 1974-10-10 1977-02-01 Vilter Manufacturing Corporation Variable capacity rotary screw compressor
US4014182A (en) * 1974-10-11 1977-03-29 Granryd Eric G U Method of improving refrigerating capacity and coefficient of performance in a refrigerating system, and a refrigerating system for carrying out said method
JPS51104459U (en) * 1975-02-20 1976-08-20
JPS5833500Y2 (en) * 1975-02-20 1983-07-26 株式会社東芝 air conditioner
JPS52101753A (en) * 1976-02-23 1977-08-26 Mayekawa Mfg Co Ltd Refrigerating apparatus
JPS5389059A (en) * 1977-01-12 1978-08-05 Toshiba Corp Air conditioner
US4211093A (en) * 1979-04-04 1980-07-08 Midolo Lawrence L Vapor cycle cooling system
JPS5532998U (en) * 1979-09-04 1980-03-03
JPS5752590Y2 (en) * 1979-09-04 1982-11-15
JPS5564073U (en) * 1979-11-19 1980-05-01
JPS5835974Y2 (en) * 1979-11-19 1983-08-13 株式会社 前川製作所 Refrigeration or air conditioning equipment
JPS55135261U (en) * 1980-03-07 1980-09-26
JPS6144122Y2 (en) * 1980-03-07 1986-12-12
JPS55144945U (en) * 1980-03-27 1980-10-17
JPS565726Y2 (en) * 1980-03-27 1981-02-06
US4467621A (en) * 1982-09-22 1984-08-28 Brien Paul R O Fluid/vacuum chamber to remove heat and heat vapor from a refrigerant fluid
WO1987003048A1 (en) * 1985-11-15 1987-05-21 Svenska Rotor Maskiner Ab Screw rotor compressor and refrigeration plant
US4742694A (en) * 1987-04-17 1988-05-10 Nippondenso Co., Ltd. Refrigerant apparatus
US5063750A (en) * 1988-06-17 1991-11-12 Svenska Rotor Maskiner Ab Rotary positive displacement compressor and refrigeration plant
DE4115905A1 (en) * 1990-05-15 1991-11-21 Toshiba Kawasaki Kk REFRIGERATION CIRCUIT ARRANGEMENT WITH A COMPRESSOR DEVICE HAVING TWO SIMULTANEOUSLY DRIVED COMPRESSOR UNITS
US5816055A (en) * 1994-02-03 1998-10-06 Svenska Rotor Maskiner Ab Refrigeration system anad a method for regulating the refrigeration capacity of such a system
US5634350A (en) * 1994-09-20 1997-06-03 Microtecnica S.P.A. Refrigeration system
EP0768464A2 (en) * 1995-10-11 1997-04-16 Denso Corporation Scroll compressor
EP0768464A3 (en) * 1995-10-11 1998-06-17 Denso Corporation Scroll compressor
US20040040332A1 (en) * 2002-09-03 2004-03-04 Bitzer Kuehlmaschinenbau Gmbh Screw compressor
EP1396640A2 (en) * 2002-09-03 2004-03-10 Bitzer Kühlmaschinenbau GmbH Screw compressor
EP1396640A3 (en) * 2002-09-03 2004-11-17 Bitzer Kühlmaschinenbau GmbH Screw compressor
US6898948B2 (en) 2002-09-03 2005-05-31 Bitzer Kuehlmaschinenbau Gmbh Screw compressor
CN1312402C (en) * 2002-09-03 2007-04-25 比泽尔制冷设备有限公司 Screw compressor
US20050226758A1 (en) * 2002-12-03 2005-10-13 Bitzer Kuehlmaschinenbau Gmbh Screw compressor
US7201569B2 (en) * 2002-12-03 2007-04-10 Bitzer Kuehlmaschinenbau Gmbh Screw compressor
EP1751476B1 (en) * 2004-05-18 2021-10-20 Carrier Corporation Compressor lubrication
CN103925753A (en) * 2013-01-16 2014-07-16 珠海格力电器股份有限公司 Air conditioning equipment
JP2015155652A (en) * 2014-02-20 2015-08-27 日立アプライアンス株式会社 Screw fluid machine and refrigeration cycle apparatus
US20180156501A1 (en) * 2015-08-11 2018-06-07 Carrier Corporation Screw Compressor Economizer Plenum for Pulsation Reduction
US10808969B2 (en) * 2015-08-11 2020-10-20 Carrier Corporation Screw compressor economizer plenum for pulsation reduction
CN105546893A (en) * 2016-02-26 2016-05-04 珠海格力电器股份有限公司 Flash tank, compressor system and air conditioner

Also Published As

Publication number Publication date
GB1256391A (en) 1971-12-08
FR1571880A (en) 1969-06-20
SE338576B (en) 1971-09-13
DE6918573U (en) 1969-09-24

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