EP2025940A2 - Drehflügelverdichter - Google Patents

Drehflügelverdichter Download PDF

Info

Publication number
EP2025940A2
EP2025940A2 EP08013463A EP08013463A EP2025940A2 EP 2025940 A2 EP2025940 A2 EP 2025940A2 EP 08013463 A EP08013463 A EP 08013463A EP 08013463 A EP08013463 A EP 08013463A EP 2025940 A2 EP2025940 A2 EP 2025940A2
Authority
EP
European Patent Office
Prior art keywords
pressure
vane
activation
chamber
vanes
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Withdrawn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
EP08013463A
Other languages
English (en)
French (fr)
Inventor
Yoshitake Ueshima
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.)
Marelli Corp
Original Assignee
Calsonic Kansei 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 Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Publication of EP2025940A2 publication Critical patent/EP2025940A2/de
Withdrawn legal-status Critical Current

Links

Images

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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid

Definitions

  • the present invention relates to a vane compressor with a compression chamber being formed in a cylinder chamber by use of vanes which protrude out of a rotor.
  • the vanes sometimes retract to the bottom portions of the vane grooves due to the gravitation and the differential pressure generated by the reverse rotation of the rotor. This is because the discharge pressure and the vane back pressure generated by the volute pump disappear.
  • the vanes Once the compressor is activated again under this state, the vanes repeatedly hit the cylinder chamber during their incomplete compression and discharge strokes due to a centrifugal force until a stable pressure is supplied to the vane back-pressure chamber. This causes the vanes to chatter under the start-up operation, and accordingly causes continuous impulsive sounds.
  • An object of the present invention is to provide a vane compressor which causes the compression to start without delay, and which prevents the vanes from chattering under its start-up operation.
  • a first aspect of the present invention is a vane compressor characterized by including: a cylinder chamber; a rotor rotatably arranged in the cylinder chamber; vane grooves provided in the rotor at equal intervals in the circumferential direction of the rotor; vanes arranged in the respective vane grooves in a way that the vanes are capable of protruding to, and retracting from, the cylinder chamber; a vane back-pressure chamber communicating with the bottom portions of the respective vane grooves, and configured to apply a back pressure to the vanes; and a back-pressure supplying unit configured to push up the vanes to the sliding surface of the cylinder chamber by transmitting the back pressure to the vane back-pressure chamber when an activation mode for rotating the rotor.
  • the back-pressure supplying unit transmits the back pressure to the vane back-pressure chamber, as well as the vanes are thus pushed up to, and brought into intimate contact with, the sliding surface of the cylinder chamber, before the rotor starts to rotate. For this reason, the start of real compression does not lag the activation of the compressor, unlike the vane compressor of the current type in which a pressure starts to be applied to the vane back-pressure chamber after the rotor starts to rotate. As a result, the compressor is no sooner activated than the compression starts. This increases the compression performance.
  • the rotor starts to rotate only after the vanes are at once pushed up to, and brought into intimate contact with, the sliding surface of the cylinder chamber due to the pressure supplied by the back-pressure supplying unit. For this reason, the vanes no longer chatter as a consequence of repeated hit of the vanes against the cylinder chamber under the start-up operation.
  • a second aspect of the present invention is the vane compressor according to the first aspect, characterized in that the back-pressure supplying unit includes: a back-pressure cylinder communicating with the vane back-pressure chamber; an activation piston configured to generate the back pressure by moving in the back-pressure cylinder; an activation spring configured to bias the activation piston in a direction in which the back pressure is generated (hereinafter referred to as a "back-pressure generating direction"); and a position holding module configured to hold the activation piston in its resting position against the activation spring.
  • the activation piston is released from the position at which the activation piston has been held by the position holding module, and the activation spring thus moves the activation piston in the back-pressure generating direction of the cylinder.
  • the back pressure is supplied to the vane back-pressure chamber, and brings the vanes into intimate contact with the sliding surface of the cylinder chamber.
  • a third aspect of the present invention is the vane compressor according to the second aspect, characterized in that the position holding module includes: an engagement part provided between the activation piston and a stopper member, and configured to hold the activation piston in its resting position; an engagement spring configured to bias the stopper member in an engagement direction of the engagement part; and an electromagnetic solenoid configured to release the engagement part from its engagement against the engagement spring.
  • the engagement spring holds the engagement part in the holding condition until the activation mode is selected.
  • the electromagnetic solenoid moves the stopper member against the engagement spring, and thus releases the engagement part from the engagement.
  • the activation spring moves the activation piston in the back-pressure generating direction, and the back pressure is thus supplied to the vane back-pressure chamber.
  • the back pressure brings the vanes into intimate contact with the sliding surface of the cylinder chamber.
  • the electromagnetic solenoid is operated only a moment at which the engagement part is released from the engagement by moving the stopper member. For this reason, the electromagnetic solenoid consumes only a very small amount of electric power.
  • a fourth aspect of the present invention is the vane compressor according to the third aspect, characterized in that: the activation piston is provided with a cam configured to cause the stopper member to retract against the engagement spring when the activation piston retracts due to a return pressure which is transmitted from the vane back-pressure chamber after the completion of the activation thereof; and the engagement spring is that configured to cause the engagement part to engage by pressing the stopper member once retracted.
  • the activation piston and the activation spring as well as the engagement spring and the engagement part of the position holding module are automatically reset in their respective resting positions where they rest before the activation mode is selected in accordance with the following scheme. That is because, when the activation piston retracts to its resting position side with the return pressure being applied from the vane back-pressure chamber, the cam provided to the activation piston causes the stopper member to retract against the engagement spring in the middle of its retraction. Subsequently, the engagement spring presses the stopper member once retracted, and thus causes the engagement part to engage.
  • a fifth aspect of the present invention is the vane compressor according to any one of the second to fourth aspects, characterized in that the low-pressure side of the back-pressure cylinder communicates with the inlet port.
  • the low-pressure side of the back-pressure cylinder communicates with the inlet port.
  • a sixth aspect of the present invention is the vane compressor according to the first aspect, characterized in that the back-pressure supplying unit includes: a high-pressure tank communicating with the vane back-pressure chamber, and filled with a highly-pressurized fluid; a valve configured to allow and shut off the flow of the fluid between the vane back-pressure chamber and the high-pressure tank; an opening/closing module configured to open the valve, and thus to cause the back pressure to be transmitted from the high-pressure tank to the vane back-pressure chamber, once the activation mode is selected.
  • the valve opens the high-pressure tank, and the back pressure is thus transmitted to the vane back-pressure chamber.
  • the vanes are pushed up, and brought into intimate contact with, the sliding surface of the cylinder chamber.
  • the start of real compression does not lag the activation of the compressor.
  • the compressor is no sooner activated than the compression starts. This increases the compression performance.
  • the rotor starts to rotate only after the vanes are at once pushed up to, and brought into intimate contact with, the sliding surface of the cylinder chamber due to the pressure coming from the high-pressure tank. For this reason, the vanes no longer chatter as a consequence of repeated hit of the vanes against the cylinder chamber under the start-up operation.
  • the electromagnetic solenoid consumes only a very small amount of electric power.
  • a seventh aspect of the present invention is the vane compressor according to the sixth aspect, characterized in that the opening/closing module includes: a stopper spring configured to close the valve; and an electromagnetic solenoid configured to cause the back pressured to be transmitted from the high-pressure tank to the vane back-pressure chamber by opening the valve against the stopper spring once the activation mode is selected.
  • the valve before the activation mode is selected, the valve is stopped by the stopper spring. Once the activation mode is selected, the electromagnetic solenoid releases the valve against the stopper spring, and the back pressure is thus transmitted to the vane back-pressure chamber.
  • the valve is configured in such a way as to be released against the stopper spring. For this reason, once the vane compressor starts a compression operation, the valve is released against the stopper spring with the return pressure being applied from the vane back-pressure chamber, and the high-pressure tank is thus filled with the oil. Additionally, once the internal pressure of the high-pressure tank becomes equal to the pressure of the vane back-pressure chamber, the valve is stopped by the stopper spring, and is thus reset to its resting position at which the valve is located before the activation mode is selected.
  • the valve can be reset to the resting position without use of an external force or electric power.
  • valve is reset to the resting position without operating the electromagnetic solenoid. All the more for this, the electromagnetic solenoid saves its power consumption.
  • Fig. 1 shows a first embodiment, and is a configuration diagram of a chief section of a vane compressor which is put in a resting condition before an activation mode is selected.
  • Fig. 2 shows the first embodiment, and is a configuration diagram of the chief section of the vane compressor in which a back pressure is being transmitted to a vane back-pressure chamber after the activation mode is selected.
  • Fig. 3 shows the first embodiment, and is a configuration diagram of the chief section of the vane compressor in which a back-pressure supplying unit and a position holding module are reset after a compression operation starts.
  • Fig. 4 shows a second embodiment, and is a configuration diagram of a chief section of a vane compressor which is put in a resting condition before an activation mode is selected.
  • Fig. 5 shows the second embodiment, and is a configuration diagram of the chief section of the vane compressor in which a back pressure is being transmitted to a vane back-pressure chamber after the activation mode is selected.
  • Fig. 6 shows the second embodiment, and is a configuration diagram of the chief section of the vane compressor in which a back-pressure supplying unit and an opening/closing module are reset after a compression operation starts.
  • the vane compressor 1 includes: a cylinder chamber 3; a rotor 5 rotatably arranged in the cylinder chamber 3; vane grooves 7 provided in the rotor 5 at equal intervals in a circumferential direction thereof; vanes 9 arranged in the vane grooves 7 in a way that the vanes 9 are capable of protruding to, and retracting from, the cylinder chamber 3; a vane back-pressure chamber 11 communicating with the bottom portions of the vane grooves 7, and configured to apply a back pressure to the vanes 9; and a back-pressure supplying unit 13 configured to push up the vanes 9 to a sliding surface of the cylinder chamber 3 by transmitting the back pressure to the vane back-pressure chamber 11 when an activation mode for rotating the rotor 5 is selected.
  • the back-pressure supplying unit 13 includes: a back-pressure cylinder 15 communicating with the vane back-pressure chamber 11; an activation piston 17 configured to generate the back pressure by moving in the back-pressure cylinder 15; an activation spring 21 configured to bias the activation piston 17 in a back-pressure generating direction; and a position holding module 19 configured to hold the activation piston 17 in its resting position against the activation spring 21.
  • the position holding module 19 includes: an engagement part 25 provided between the activation piston 17 and a stopper member 23, and configured to hold the activation piston 17 in a position where the activation piston 17 rests before being pushed into the activation piston 17; an engagement spring 27 configured to bias the stopper member 23 in an engagement direction of the engagement part 25; and an electromagnetic solenoid 29 configured to release the engagement part 25 from its engagement against the engagement spring 27.
  • the activation piston 17 is provided with a cam 31 configured to cause the stopper member 23 to retract against the engagement spring 27 when the activation piston 17 retracts due to a return pressure from the vane back-pressure chamber 11 after the completion of the activation thereof.
  • the engagement spring 27 causes the engagement part 25 to engage by pressing the stopper member 23 once retracted.
  • the low-pressure side of the back-pressure cylinder 15 communicates with the inlet port 49.
  • the cylinder chamber 3 is almost elliptical, and is formed in a position inside a front-side block (not illustrated), a cylinder block 33 and a rear-side block (not illustrated).
  • the rotor 5 is fixed to a rotor shaft 35, and is arranged coaxial with the cylinder chamber 3.
  • the vane back-pressure chamber 11 is provided, for example, between the front-side block (not illustrated) and the cylinder block 33, and between the rear-side block (not illustrated) and the cylinder block 33.
  • the vane back-pressure chamber 11 communicates with the bottom portions of the vane grooves 7 of the rotor 5.
  • the cylinder block 33 is provided with two cylinder outlet ports 37 in its two portions. Each cylinder outlet port 37 is provided with a check valve 39. Each cylinder outlet port 37 communicates with the outlet port 45 of the compressor housing 43 through an oil separator 41. The outlet port 45 communicates with a condenser (not illustrated).
  • Two cylinder inlet ports 47 are provided in a position between the front-side block (not illustrated) and the cylinder block 33, and in a position between the rear-side block (not illustrated) and the cylinder block 33.
  • Each cylinder inlet port 47 communicates with the inlet port 49 of the compressor housing 43.
  • the inlet port 49 communicates with an evaporator (not illustrated).
  • the compressor housing 43 is filled with a predetermined amount of oil 51. Part of this oil 51 is mixed with the coolant.
  • the cylinder 15 in the back-pressure supplying unit 13 communicates with the vane back-pressure chamber 11 through an oil passage 53.
  • the activation spring 21 biases the activation piston 17 in the back-pressure generating direction (or the direction indicated by an arrow 71 in Fig. 2 ).
  • the low-pressure side of the cylinder 15 (or the opposite side of the oil passage 53) communicates with the cylinder inlet ports 47 through the communicating passage 55.
  • the engagement part 25 of the position holding module 19 is constituted of: a concave part 57 formed in the outer periphery of the activation piston 17; and the tip portion of the stopper member 23.
  • the electromagnetic solenoid 29 includes an electromagnetic coil 59 and an armature 61.
  • the armature 61 and the stopper member 23 are integrated into a single unit.
  • the engagement spring 27 biases the stopper member 23 to the concave part 57 in the activation piston 17 with the armature 61 being interposed in between.
  • the cam 31 causes the stopper member 23 to retract against the engagement spring 27 to a position at which the stopper member 23 releases the engagement part 25 from the engagement.
  • the electromagnetic solenoid 29 is turned on immediately. Once the electromagnetic solenoid 29 is turned on, the stopper member 23 retracts from its engagement position, and the engagement part 25 is thus released from the engagement. Once the engagement part 25 is released from the engagement, the activation spring 21 moves the activation piston 17 in the back-pressure generating direction, and the hydraulic pressure (or the back pressure) is thus generated. Thereby, the back pressure is supplied to the vane back-pressure chamber 11 through the oil passage 53 as indicated by an arrow 73. In response to this, the vanes 9 are pushed up to, and brought into intimate contact with, the sliding surface of the cylinder chamber 3.
  • the electrical solenoid 29 is turned on momentarily when the activation mode is selected. After that, the electromagnetic solenoid 20 is turned off immediately.
  • the vanes 9 After the rotor 5 starts to rotate with the vanes 9 being in intimate contact with the sliding surface of the cylinder chamber 3, the vanes 9 continue to be held in the state of being in intimate contact with the cylinder chamber 3 due to the centrifugal force generated by the rotation of the rotor 5 and the discharge pressure (or the back pressure) supplied to the vane back-pressure chamber 11, as described below, even when the electromagnetic solenoid 29 is turned off and the electromagnetic coil 59 stops being excited.
  • the vane compressor 1 is thus activated.
  • the coolant is taken in through the inlet port 49 as indicated by the arrow 77, and is subsequently compressed.
  • the resultant coolant is discharged through the outlet port 45 as indicated by the arrow 79.
  • the electromagnetic solenoid 29 is turned off.
  • the highly-pressurized oil (or the return pressure) which occurs due to the discharge pressure flows into the back-pressure cylinder 15 from the oil passage 53 as indicated by an arrow 81.
  • the highly-pressurized oil (or the return pressure) moves the activation piston 17 to its resting position against the activation spring 21.
  • the cam operates, and causes the stopper member 23 to retract against the engagement spring 27.
  • the stopper member 23 engages with the concave part 57 due to the biasing force of the engagement spring 27.
  • the activation piston 17 is reset to its resting position.
  • the activation piston 17 retracts due to the discharge pressure, the compression of the activation spring 21, the operation of the cam 31 and the compression of the engagement spring 27 are facilitated by the negative pressure applied to the low-pressure side of the back-pressure cylinder 15 from the communicating passage 55 communicating with the inlet ports 47 on the low-pressure side. Thereby, the activation piston 17 is assuredly reset to its resting position.
  • the start of the real compression does not lag the activation of the compressor. That is because, before the rotor 5 starts to rotate, the back-pressure supplying unit 13 transmits the back pressure to the vane back-pressure chamber 11, and the vanes 9 are thus pushed up to, and brought into intimate contact with, the sliding surface of the cylinder chamber 3. As a result, the vane compressor 1 starts a compression operation immediately after the vane compressor 1 is activated. This increases the compression performance.
  • the rotor 5 starts to rotate only after the vanes 9 come into intimate contact with the sliding surface of the cylinder chamber 3, the vanes 9 do not chatter under the start-up operation, either.
  • the cam 31 provided to the activation piston 17 causes the stopper member 23 to retract against the engagement spring 27 in the middle of the movement of the activation piston 17.
  • the engagement spring 27 causes the engagement part 25 to engage by pressing the retracted stopper member 23.
  • the electromagnetic solenoid 29 only needs to be on in a moment at which the engagement part 25 is released from the engagement by moving the stopper member 23 after the activation mode is selected.
  • the electromagnetic solenoid 29 need not be operated after the vane compressor 1 starts a compression operation and when the vane compressor 1 resets the activation piston 17 to its resting position. For this reason, the electromagnetic coil 59 consumes only a very small amount of electric power.
  • the vane compressor according to the present invention is applicable to any type of scheme for inputting driving torque.
  • the present invention is capable of being operated as an integrated motor-driven compressor obtained by assembling the vane compressor and an electric motor together, and as a pulley-driven compressor driven by driving torque inputted through a pulley.
  • the application of the vane compressor according to the present invention is not limited to a cooling system in a vehicle air-conditioning apparatus.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP08013463A 2007-08-09 2008-07-25 Drehflügelverdichter Withdrawn EP2025940A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007208016A JP2009041470A (ja) 2007-08-09 2007-08-09 ベーン形圧縮機

Publications (1)

Publication Number Publication Date
EP2025940A2 true EP2025940A2 (de) 2009-02-18

Family

ID=40011331

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08013463A Withdrawn EP2025940A2 (de) 2007-08-09 2008-07-25 Drehflügelverdichter

Country Status (4)

Country Link
US (1) US20090041606A1 (de)
EP (1) EP2025940A2 (de)
JP (1) JP2009041470A (de)
CN (1) CN101363438A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2348232A1 (de) * 2010-01-21 2011-07-27 Showa Corporation Fahrzeughydrauliksteuereinheit
WO2012079573A3 (de) * 2010-12-15 2013-05-10 Ixetic Bad Homburg Gmbh Flügelzellenpumpe und verfahren zum betreiben einer flügelzellenpumpe
DE102013212009A1 (de) 2013-06-25 2015-01-08 Bayerische Motoren Werke Aktiengesellschaft Kältekreislauf-Anlage zur Klimatisierung eines Fahrzeugs, insbesondere eines Elektro- oder Hybridfahrzeuges sowie Verfahren und Verdichter zum Betrieb einer solchen Kältekreislauf-Anlage

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5433400B2 (ja) 2009-12-24 2014-03-05 カルソニックカンセイ株式会社 ベーン型圧縮機
JP5893957B2 (ja) * 2012-02-28 2016-03-23 カルソニックカンセイ株式会社 ベーン型圧縮機
US20170350391A1 (en) * 2014-12-24 2017-12-07 Calsonic Kansei Corporation Gas compressor
CN108894828A (zh) * 2018-07-20 2018-11-27 刘国强 叶片式气动马达
CN111502906B (zh) * 2020-05-12 2021-12-28 台州速益机电有限公司 一种叶片式液压马达的转子组件

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004190509A (ja) 2002-12-09 2004-07-08 Calsonic Compressor Seizo Kk 気体圧縮機
JP2007208016A (ja) 2006-02-02 2007-08-16 Denso Corp モールドパッケージ

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004190509A (ja) 2002-12-09 2004-07-08 Calsonic Compressor Seizo Kk 気体圧縮機
JP2007208016A (ja) 2006-02-02 2007-08-16 Denso Corp モールドパッケージ

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2348232A1 (de) * 2010-01-21 2011-07-27 Showa Corporation Fahrzeughydrauliksteuereinheit
WO2012079573A3 (de) * 2010-12-15 2013-05-10 Ixetic Bad Homburg Gmbh Flügelzellenpumpe und verfahren zum betreiben einer flügelzellenpumpe
DE102013212009A1 (de) 2013-06-25 2015-01-08 Bayerische Motoren Werke Aktiengesellschaft Kältekreislauf-Anlage zur Klimatisierung eines Fahrzeugs, insbesondere eines Elektro- oder Hybridfahrzeuges sowie Verfahren und Verdichter zum Betrieb einer solchen Kältekreislauf-Anlage
DE102013212009B4 (de) 2013-06-25 2019-05-23 Bayerische Motoren Werke Aktiengesellschaft Kältekreislauf-Anlage zur Klimatisierung eines Fahrzeugs, insbesondere eines Elektro- oder Hybridfahrzeuges sowie Verfahren und Verdichter zum Betrieb einer solchen Kältekreislauf-Anlage

Also Published As

Publication number Publication date
CN101363438A (zh) 2009-02-11
JP2009041470A (ja) 2009-02-26
US20090041606A1 (en) 2009-02-12

Similar Documents

Publication Publication Date Title
EP2025940A2 (de) Drehflügelverdichter
KR101083218B1 (ko) 압축 시스템, 다기통 회전 압축기 및 그것을 사용한 냉동장치
EP2639457A1 (de) Spiralverdichter
EP2549110A1 (de) Einzelschraubenverdichter
JP5938054B2 (ja) 圧縮機
EP1798373A2 (de) Mehrstufiger hermetischer Drehkolbenverdichter
JP5173908B2 (ja) ロータリ型膨張機及び流体機械
CN106704178B (zh) 涡旋压缩机及其泄压引流结构
JP2008128069A (ja) 密閉形２段ロータリ式圧縮機
JP2013245592A (ja) 気体圧縮機
CN209743154U (zh) 电动式压缩机装置
CN111075720B (zh) 压缩机和具有其的制冷循环系统
CN111734635A (zh) 一种泵体组件及转子压缩机
CN113614378A (zh) 涡旋压缩机
WO2005064161A1 (ja) 圧縮機
JP2001165081A (ja) 圧縮機およびその圧縮機を有する冷凍サイクルを備えた冷凍または冷却装置
CN101460705A (zh) 用于过压保护的滑阀致动
AU2007237797A1 (en) Fluid machine
JP2000297770A (ja) クラッチレススクロール型流体機械
JP2001342980A (ja) 圧縮機
JP3584703B2 (ja) スライディングベーン式圧縮機
KR100286714B1 (ko) 베어링부에 흡입구조를 가지는 로터리 압축기
JP5297212B2 (ja) 圧縮機
KR100539828B1 (ko) 용량 가변형 회전식 압축기의 바이패스밸브 조립체
JPH0528397Y2 (de)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20091102