US20060182647A1 - Screw compressor - Google Patents

Screw compressor Download PDF

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Publication number
US20060182647A1
US20060182647A1 US10/544,770 US54477005A US2006182647A1 US 20060182647 A1 US20060182647 A1 US 20060182647A1 US 54477005 A US54477005 A US 54477005A US 2006182647 A1 US2006182647 A1 US 2006182647A1
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US
United States
Prior art keywords
screw
oil
casing body
compressor
rotor
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.)
Abandoned
Application number
US10/544,770
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English (en)
Inventor
Masaaki Kamikawa
Hiroyuki Yoneda
Souichi Shiraishi
Hiroyuki Yamakawa
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Assigned to MITSUBISHI DENKI KABUSHIKI KAISHA reassignment MITSUBISHI DENKI KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAMIKAWA, MASAAKI, SHIRAISHI, SOUICHI, YAMAKAWA, HIROYUKI, YONEDA, HIROYUKI
Publication of US20060182647A1 publication Critical patent/US20060182647A1/en
Abandoned 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw 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
    • 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
    • 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
    • F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/17—Tolerance; Play; Gap
    • 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
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • 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
    • F04C28/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/04—Thermal properties
    • F05C2251/048—Heat transfer

Definitions

  • the present invention relates to a screw compressor for compressing refrigerant gas.
  • the invention relates to a screw compressor in which the oil to be introduced into the compression chamber and bearings to seal gaps in the compression chamber and lubricate the bearings is cooled to achieve high adiabatic efficiency and high volumetric efficiency.
  • the present invention also relates to a screw compressor in which the difference in thermal expansion between the screw rotor and the screw bore portion of the casing body due to their temperature difference is reduced to prevent contact between the screw rotor and the screw bore portion due to a reduction in the gap between them.
  • the present invention also relates to a screw compressor which prevents liquid compression by causing the liquid refrigerant to exchange heat when it flows into the compressor, thereby achieving increased resistance to returned liquid refrigerant.
  • Conventional screw compressors have been configured such that the oil for sealing gaps in the compression chamber and lubricating the bearings is introduced from the high pressure side into the compression chamber and the bearings at nearly the discharge gas temperature. Since a conventional screw compressor has a configuration in which the oil for sealing gaps in the compression chamber and lubricating the bearings is introduced from the high pressure side into the compression chamber and the bearings at nearly the discharge gas temperature, the temperature of the compression chamber becomes higher than necessary, which increases the discharge gas temperature and hence the oil temperature, falling into a vicious circle. If liquid refrigerant is injected into the compressor to prevent this, the adiabatic efficiency and volumetric efficiency of the compressor decreases.
  • Some conventional screw compressors use the discharge gas to heat the screw bore portion of the casing to reduce the difference in thermal expansion between the screw rotor and the screw bore portion of the casing.
  • Japanese Laid-Open Patent Publication No. 6-42474 discloses a screw compressor in which the discharge gas path is extended close to the edge of the screw rotor in the axial direction on the suction side. This structure can prevent the temperature of the low pressure chamber from greatly affecting the inner cylinder of the casing which covers the outer circumferential surface of the screw rotor, thereby preventing seizure between the screw rotor and the inner cylinder of the casing while maintaining high performance without increasing the seal gap between the screw rotor and the inner cylinder.
  • the present invention has been devised to solve the above problems. It is, therefore, an object of the present invention to provide a screw compressor in which the oil to be introduced into the compression chamber and bearings to seal gaps in the compression chamber and lubricate the bearings is cooled to achieve high adiabatic efficiency and high volumetric efficiency.
  • Another object of the present invention is to provide a screw compressor in which the difference in thermal expansion between the screw rotor and the screw bore portion of the casing body due to their temperature difference is reduced to prevent contact between the screw rotor and the screw bore portion due to a reduction in the gap between them.
  • Still another object of the present invention is to provide a screw compressor which prevents liquid compression by causing the liquid refrigerant to exchange heat when it flows into the compressor, thereby achieving increased resistance to returned liquid refrigerant.
  • Yet another object of the present invention is to provide a screw compressor in which dew is prevented from being formed on the power terminal portion of the motor disposed in the casing body.
  • an oil path is provided in the casing body such that the oil for sealing gaps in the compression chamber and lubricating the bearings is circulated to the vicinity of the low pressure side.
  • the above oil path is provided in the screw bore outer circumferential portion of the casing body.
  • a heat sink is provided to increase the heat transfer area for exchanging heat with refrigerant gas or liquid refrigerant passed through the motor chamber.
  • FIG. 1 is a cross-sectional view of a screw compressor according to a first embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of a screw compressor according to a second embodiment of the present invention.
  • FIG. 3 is a cross-sectional view of a screw compressor according to a third embodiment of the present invention.
  • FIG. 4 is a partial structural view of the screw compressor according to the third embodiment of the present invention.
  • FIG. 5 is a cross-sectional view of a screw compressor according to a fourth embodiment of the present invention.
  • FIG. 6 is a cross-sectional view of a screw compressor according to a fifth embodiment of the present invention.
  • FIG. 1 is a cross-sectional view of a screw compressor according to a first embodiment of the present invention.
  • a motor 2 is fixed to the inside walls of a cylindrical casing body 1 constituting the body of the screw compressor.
  • the motor 2 includes: a stator 3 fixed to the inside walls of the casing body 1 ; and a rotor 4 disposed inside the stator 3 .
  • a screw rotor 5 is also disposed within the casing body 1 .
  • the screw rotor 5 and the motor rotor 4 are attached to a screw shaft 6 such that their axes are aligned.
  • the screw rotor 5 has a plurality of spiral compression grooves formed therein and is connected through the screw shaft 6 to the motor 2 , which rotates the screw rotor 5 . Further, a motor cover 7 and an oil separator 8 are each fixed to a respective end of the casing body 1 .
  • the oil to be introduced into a compression chamber 9 to seal the gap between the inner circumferential surface of the casing body 1 and the outer circumferential surface of the screw rotor 5 in the compression chamber 9 is circulated to the vicinity of the low pressure side such as a low pressure chamber 10 of the compressor. More specifically, within the casing body 1 , an oil path 11 is formed in a screw bore outer circumferential portion 1 b of a screw casing portion 1 a (inside of which the screw rotor 5 is disposed) such that the oil path 11 extends from the compression chamber 9 to the low pressure chamber 10 of the compressor.
  • the oil to be introduced into the compression chamber 9 is cooled by the cool refrigerant near the low pressure side, making it possible to remove the heat of compression when the cooled oil is put into the compression chamber 9 .
  • This arrangement also prevents the reduction in the adiabatic and volumetric efficiency due to the liquid refrigerant injected to remove the heat of compression.
  • the reduction in the temperature of the oil increases the viscosity of the oil and hence improves gap sealing performance, allowing the screw compressor to have high efficiency.
  • the oil path 11 for circulating the oil to the vicinity of the low pressure side is formed in the screw bore outer circumferential portion 1 b of the screw casing portion 1 a , the oil of nearly the discharge gas temperature warms the screw bore outer circumferential portion 1 b until it reaches the vicinity of the low pressure side (i.e., the low temperature portion) of the screw casing portion 1 a .
  • This improves the thermal response of the screw casing portion 1 a with respect to the discharge gas temperature, making it possible to reduce the difference in thermal expansion between the screw rotor 5 and the screw casing portion 1 a.
  • the oil path 11 is formed in the screw bore outer circumferential portion 1 b of the screw casing portion 1 a so as to warm the screw casing portion 1 a by the oil, as described above, a sufficient amount of oil is supplied even when the pressure differential is large and hence the discharge gas rate is reduced, meaning that the effect of warming the screw casing portion 1 a is not reduced. Therefore, it is possible to reduce the difference in thermal expansion between the screw rotor 5 and the screw casing portion 1 a , allowing the screw compressor to have high reliability.
  • the oil circulation path 11 may be formed to have the following configuration.
  • the oil path 11 runs from the oil separator 8 through the screw bore outer circumferential portion 1 b of the screw casing portion 1 a to warm the screw bore portion 4 b with the oil. Then, the path goes to the low pressure side (the low pressure chamber 10 of the compressor, the motor chamber, etc.) to cool the oil, which is then put into the compression chamber 9 .
  • Such an arrangement achieves the effect of warming the screw casing portion 1 a with the oil, as described above, as well as increasing the adiabatic efficiency and volumetric efficiency by cooling the oil, allowing the screw compressor to have high efficiency and high reliability.
  • FIG. 2 is a cross-sectional view of a screw compressor according to a second embodiment of the present invention.
  • an external oil path 11 a protruding externally of the casing body 1 is added to the oil path 11 .
  • a solenoid valve 12 is attached to this external oil path 11 a so as to control the oil flow, allowing or not allowing the oil to pass.
  • the solenoid valve 12 may be closed to stop the oil flow in order to prevent an increase in the gap between the screw rotor 5 and the screw bore portion of the screw casing portion 1 a .
  • the oil may be allowed to flow through the oil path 11 only when the gap between the screw rotor 5 and the screw bore portion of the screw casing portion 1 a is reduced due to the expansion of the screw rotor 5 caused by increased discharge gas temperature, etc.
  • it is possible to ensure the reliability of the screw compressor while preventing the reduction in the volumetric efficiency due to an increase in the gap in normal operation.
  • FIG. 3 is a cross-sectional view of a screw compressor according to a third embodiment of the present invention.
  • the oil trapped in the oil separator 8 is drawn into the oil path 11 .
  • the third embodiment is configured such that an oil temperature control device 13 is provided on the inlet side of the oil path 11 and the oil is introduced to the oil path 11 through the oil temperature control device 13 .
  • FIG. 3 shows an example in which the oil temperature control device 13 is provided in an oil tank 14 outside the compressor, it may be installed in the oil trapping portion (that is, the lower portion) of the oil separator 8 within the compressor.
  • the oil temperature may be adjusted in the oil temperature control device 13 so as to heat the screw casing portion 1 a and thereby expand the screw bore portion when the compression ratio or the discharge gas temperature is high, which makes it possible to minimize the difference in thermal expansion between the screw casing portion 1 a and the screw rotor 5 and prevent their contact.
  • the above oil temperature control may be performed so as to cool the oil, which then may be put into the compression chamber 9 .
  • Such an arrangement allows prevention of seizure, etc. due to the expansion of the screw rotor 5 , achieving high reliability.
  • the increase in the oil viscosity results in an increase in the sealing performance, allowing the screw compressor to have high efficiency.
  • the above oil temperature control device 13 may be divided into two portions each disposed on a respective side of the screw bore outer circumferential portion 1 b of the screw casing portion 1 a .
  • the oil may be set at a high temperature before it is passed through the screw bore outer circumferential portion 1 b . Then, after the oil is passed through the screw bore outer circumferential portion 1 b , it may be set at a low temperature. This allows effectively providing increased adiabatic efficiency and volumetric efficiency through cooling of the oil, as well as increased reliability through warming of the casing.
  • the discharge gas temperature may be detected and the oil temperature may be controlled according to the temperature or the degree of superheat of the discharge gas. For example, when the discharge gas temperature is high (exceeding 100° C.), the oil temperature may be increased to further expand the screw casing portion 1 a and thereby prevent contact between the screw rotor 5 and the screw bore portion of the screw casing portion 1 a.
  • a noncontact/eddy current type gap detector 15 may be attached to detect the gap between the screw casing portion 1 a and the screw rotor 5 , as shown in FIG. 4 . Then, in the above oil temperature control, the oil temperature may be controlled while detecting the gap, allowing the gap between the screw rotor 5 and the screw casing portion 1 a to be minimized. This allows the screw compressor to achieve reduced internal leak, as well as high performance and high reliability.
  • the oil path 11 is formed in the screw bore outer circumferential portion 1 b , as described above.
  • the third embodiment is configured such that the temperature of the circulating oil is controlled, also as described above.
  • the oil path 11 may be divided into upper and lower paths.
  • the above lower path of the oil path 11 may be set to have a larger heat transfer area than the upper path, or the oil supplied to the lower path may be set at a higher temperature than the oil supplied to the upper path, or oil may be supplied to only the lower path, in order to warm the lower portion of the compressor.
  • Such arrangements reduce the temperature difference between the upper and lower portions of the compressor, allowing the compressor to have resistance to returned liquid refrigerant and high reliability.
  • the oil flow rate may be increased accordingly.
  • appropriately controlling the oil flow rate enhances the resistance to returned liquid refrigerant.
  • FIG. 5 is a cross-sectional view of a screw compressor according to a fourth embodiment of the present invention.
  • the oil path 11 is formed so as to circulate the high temperature oil to the vicinity of the low pressure side, as described above.
  • the fourth embodiment is configured such that part or all of the oil path, denoted by 11 b , is extended so as to circulate the oil close to the power terminal portion 16 and the terminal block 17 of the motor 2 disposed in the casing body 1 of the compressor.
  • the screw compressor is operated under low temperature conditions, that is, when the suction gas temperature is low, dew may be formed on the terminal block 17 and the power terminal portion 16 , depending on the ambient temperature and humidity conditions, which might lead to a short circuit in the power supply.
  • circulating the oil close to the power terminal portion 16 and the terminal block 17 and thereby warming them prevents dew from being formed thereon, allowing the screw compressor to have enhanced reliability.
  • FIG. 6 is a cross-sectional view of a screw compressor according to a fifth embodiment of the present invention.
  • the oil path 11 is formed so as to circulate the oil to the vicinity of the low pressure side, as described above.
  • the fifth embodiment is configured such that the oil path 11 is formed so as to circulate the oil to the vicinity of a boundary wall 1 c of the casing body 1 constituting the boundary between the motor chamber 2 and the compressor low-pressure chamber 10 on the low pressure side, as shown in FIG. 6 , for example.
  • a heat sink 18 may be attached to the boundary wall 1 c such that it sits on both the motor chamber 2 and the compressor low-pressure chamber 10 to increase the heat transfer area for cooling the oil circulated to the boundary wall 1 c . Even when refrigerant in a liquid state is injected into the compressor, the high temperature oil circulated to the vicinity of the low pressure side heats the refrigerant (as in other embodiments). At that time, the above heat sink 18 increases the heat transfer area for exchanging heat between the refrigerant and the oil, allowing the screw compressor to have increased resistance to returned liquid refrigerant and high reliability.
  • the heat sink 18 which is attached to the boundary wall 1 c of the casing body 1 such that it sits on both the motor chamber 2 and the compressor low-pressure chamber 10 may be provided with cooling fins to improve its heat exchange performance.
  • the oil to be introduced into the compression chamber is circulated to the vicinity of the low pressure side and thereby cooled.
  • the cooled oil is put into the compression chamber so as to be able to remove the heat of compression and thereby prevent the adiabatic efficiency and volumetric efficiency from being reduced.
  • the reduction in the oil temperature increases the viscosity of the oil and hence enhances the oil gap sealing performance, allowing the screw compressor to have high efficiency.
  • a heat sink is attached near the boundary position between the motor chamber and the compressor lower-pressure chamber on the low pressure side to increase the heat transfer area for cooling the oil.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US10/544,770 2003-12-22 2003-12-22 Screw compressor Abandoned US20060182647A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2003/016448 WO2005061900A1 (fr) 2003-12-22 2003-12-22 Compresseur a vis

Publications (1)

Publication Number Publication Date
US20060182647A1 true US20060182647A1 (en) 2006-08-17

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Family Applications (1)

Application Number Title Priority Date Filing Date
US10/544,770 Abandoned US20060182647A1 (en) 2003-12-22 2003-12-22 Screw compressor

Country Status (5)

Country Link
US (1) US20060182647A1 (fr)
EP (1) EP1705379B1 (fr)
JP (1) JP4473819B2 (fr)
CN (1) CN100387843C (fr)
WO (1) WO2005061900A1 (fr)

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JP4666106B2 (ja) * 2009-03-16 2011-04-06 ダイキン工業株式会社 スクリュー圧縮機
WO2015094464A1 (fr) 2013-12-18 2015-06-25 Carrier Corporation Dispositif de renforcement de la viscosité de lubrifiant d'un compresseur à fluide frigorigène
JP6453682B2 (ja) * 2015-03-19 2019-01-16 三菱重工サーマルシステムズ株式会社 圧縮機駆動用モータおよびその冷却方法
DE102016011504A1 (de) * 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH System für ein Nutzfahrzeug umfassend einen Schraubenkompressor sowie einen Elektromotor
BE1029289B1 (nl) * 2021-04-09 2022-11-17 Atlas Copco Airpower Nv Element, inrichting en werkwijze voor het samenpersen van samen te persen gas met een lage temperatuur

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US1409868A (en) * 1920-08-05 1922-03-14 W M Hardwick Pump
US1672571A (en) * 1926-03-27 1928-06-05 Leonard Pump & Motor Co Compressor
US1706829A (en) * 1928-05-28 1929-03-26 Joseph Mercadante Pump
US2388523A (en) * 1942-06-03 1945-11-06 Gen Electric Lubricant heating system for turbosuperchargers and the like
US2938664A (en) * 1955-01-17 1960-05-31 Leybold S Nachfolger Fa E Pump
US3129877A (en) * 1956-05-17 1964-04-21 Svenska Rotor Maskiner Ab Rotary piston, positive displacement compressor
US4648815A (en) * 1984-09-05 1987-03-10 The Hydrovane Compressor Company Limited Rotary air compressor with thermally responsive oil injection
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Publication number Publication date
EP1705379A4 (fr) 2011-12-21
EP1705379B1 (fr) 2015-04-01
CN1745252A (zh) 2006-03-08
JPWO2005061900A1 (ja) 2007-07-12
EP1705379A1 (fr) 2006-09-27
WO2005061900A1 (fr) 2005-07-07
CN100387843C (zh) 2008-05-14
JP4473819B2 (ja) 2010-06-02

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