EP1647710A1 - Regelventil für einen Verdichter variabler Verdrängung - Google Patents

Regelventil für einen Verdichter variabler Verdrängung Download PDF

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Publication number
EP1647710A1
EP1647710A1 EP05022396A EP05022396A EP1647710A1 EP 1647710 A1 EP1647710 A1 EP 1647710A1 EP 05022396 A EP05022396 A EP 05022396A EP 05022396 A EP05022396 A EP 05022396A EP 1647710 A1 EP1647710 A1 EP 1647710A1
Authority
EP
European Patent Office
Prior art keywords
plunger
shaft
control valve
pressure
valve
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Withdrawn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
EP05022396A
Other languages
English (en)
French (fr)
Inventor
Katsumi Koyama
Morimitsu Kajiwara
Takeshi Kawaguchi
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.)
TGK Co Ltd
Original Assignee
TGK Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by TGK Co Ltd filed Critical TGK Co Ltd
Publication of EP1647710A1 publication Critical patent/EP1647710A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1854—External parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the invention relates to a control valve according to the preamble of claim 1, particularly to a displacement control valve for a variable displacement compressor for an automotive air conditioner.
  • Variable displacement compressors are employed in automotive air conditioners so as to obtain an adequate refrigerating capacity without being constrained by speed variations of the engine which drives the compressor.
  • the inclination angle of the wobble plate in a crankcase can be changed by changing the pressure in the crankcase, whereby the stroke of pistons driven by the wobble plate is changed for changing the refrigerant discharge amount.
  • the control valve controls the pressure in the crankcase.
  • a displacement control valve operates to introduce part of refrigerant at discharge pressure Pd discharged from the discharge chamber into the crankcase such that pressure Pc in the crankcase is controlled e.g. according to the suction pressure Ps in the suction chamber. That is, the control valve senses the suction pressure Ps and controls the refrigerant flow rate at the discharge pressure Pd from the discharge chamber into the crankcase, so as to maintain the suction pressure Ps at a constant level.
  • the control valve has a Ps pressure-sensing section and a valve section to open and close a passage between the suction chamber and the crankcase.
  • a solenoid is provided in order to carry out the settings of the pressure-sensing section by an external electric current.
  • a control valve for a variable displacement compressor of a so-called clutchless type is known from JP-2000-110731 A.
  • the driving engine is directly connected to a shaft without an electromagnetic clutch between the engine and the shaft of the wobble plate.
  • the control valve section controls the flow through a passage between the discharge chamber and the crankcase.
  • a solenoid generates, when energizied, an electromagnetic force causing the valve section to operate in valve closing direction.
  • the pressure-sensing section causes the valve section to operate in valve opening direction as the suction pressure Ps drops below the atmospheric pressure.
  • the solenoid When the solenoid is not energized, the valve section is fully open, whereby the pressure Pc in the crankcase is held close to discharge pressure Pd.
  • the wobble plate is adjusted substantially at right angles to the shaft.
  • the compressor operates at the minimum displacement. Thus, the refrigerant displacement can be substantially reduced to approximately zero. Even when the engine is directly connected to the shaft an electromagnetic clutch can be eliminated.
  • the pressure-sensing section and the valve section are arranged with the solenoid interposed therebetween.
  • the suction pressure Ps is introduced via or through the solenoid to the pressure-sensing section which compares the suction pressure Ps and the atmospheric pressure. This necessitates that the solenoid in its entirety is accommodated within a pressure chamber, and hence, the solenoid components need to be designed pressure resistant.
  • JP Patent Application 2003-289581 which is configured such that the solenoid plunger is divided into first and second plungers.
  • the Ps-pressure-sensing member such as a diaphragm or a bellows, is interposed therebetween, whereby the suction pressure Ps is isolated from the atmospheric pressure and from the solenoid.
  • FIG. 2 shows this control valve.
  • the control valve of FIG. 2 receives the discharge pressure Pd of the compressor to supply the controlled pressure Pc to the crankcase.
  • the valve section comprises a valve seat 101, a downstream side valve element 102 and a spring 103 urging the valve element 102 in valve closing direction.
  • the valve element 102 is integral with an axially moveable shaft 104 having an outer diameter equal to the inner diameter of a valve hole.
  • a solenoid comprises a core 106 and a first plunger 107, both disposed within a bottomed sleeve 105, and a second plunger 108 and a coil 109 both disposed outside the bottomed sleeve 105.
  • a diaphragm 110 is provided between the first and second plungers 107, 108. The diaphragm 110 seals the open end of the bottomed sleeve 105.
  • the first plunger 107 is fixed to a shaft 111 that extends through the core 106.
  • the shaft 111 is urged by a spring 112 in a direction of causing the first plunger 107 to be moved away from the core 106 into contact with the diaphragm 110.
  • the suction pressure Ps from the suction chamber of the compressor is introduced into a space where the second plunger 108 is disposed.
  • the second plunger 108 is firmly fixed to an end of the shaft 104 remote from the valve element 102.
  • the second plunger 108 is urged by a spring 113 having stronger spring force than the spring 103 away from the diaphragm 110.
  • the valve section is fully-open. Even if the compressor is directly driven by the engine, the compressor is operated at the minimum displacement. If control current is supplied to the coil 109 of the solenoid, the first and second plungers 107, 108 become magnetically coupled to each other with the diaphragm 110 therebetween so as to behave like one plunger.
  • the axial positions of the first and second plungers 107, 108 determine a certain valve lift set according to the value of the control current.
  • the diaphragm 110 receives the suction pressure PS, and is axially displaced accordingly.
  • the diaphragm displacement is transmitted to the valve element 102 via the second plunger 108 and the shaft 104.
  • the control valve introduces refrigerant at pressure Pc into the crankcase by controlling the flow of refrigerant at discharge pressure Pd to a flow rate dependent on the value of the control.
  • the compressor operates at a displacement dependent on the control current. In this state, if the suction pressure Ps rises or drops, the diaphragm 110 is displaced downward or upward in FIG.
  • the shaft is integral with the valve element and also has the function of guiding the second plunger.
  • the second plunger When the second plunger is axially moved by the solenoid, the second plunger may become tilted depending on the state of the spring axially urging the second plunger. The tilt tendency creates a couple of forces and/or a bending torque which act on the shaft which is axially guided in the body and which has to guide the second plunger. This effect markedly spoils the axial slidability of the shaft in the body so that the valve element cannot move smoothly.
  • the control valve the guided shaft provided for transmitting a change in suction pressure to the valve element is set-free from the function of guiding the second plunger. Even if the second plunger is tilted when the second plunger is axially moved by an attractive force generated by the solenoid, the sliding movement of the shaft will no longer be detrimentally influenced by the operational behavior of the second plunger but has the sole function to transmit the axial force and the axial component of the movement of the second plunger to the valve element. This enhances the controllability of the control valve and assures a smooth movement of the valve element in relation to the valve seat without any parasitary lateral shaft braking forces between the shaft and the shaft guidance in the body.
  • the control valve in FIG. 1 has a valve section including a body 11 with a side port 12 communicating with a discharge chamber of the variable displacement compressor for receiving the discharge pressure Pd.
  • a strainer 13 is fixed at the side port 12.
  • the port 12 communicates via an inner refrigerant passage with a top port 14 of the body 11.
  • the top port 14 communicates with the crankcase to deliver the controlled pressure Pc.
  • a valve seat 15 is integral with the body 11. On a pressure Pc side of the valve seat 15, an axially movable valve element 16 is disposed.
  • the valve element 16 is integral with a shaft 17.
  • the shaft 17 extends through a valve hole of the valve seat 15 and is axially movably guided in a bore of the body 11.
  • the discharge pressure Pd is introduced to a small-diameter portion of the shaft 17 between the valve element 16 and a lower part of the shaft 17.
  • the outer diameter of the lower part of the shaft 17 is equal to the inner diameter of the valve hole of the valve seat 15 such that the pressure-receiving area of the valve element 16 is equal to that of the lower part of the shaft 17.
  • An upward force generated by the discharge pressure Pd on the valve element 16 is cancelled by a downward force on the lower part of the shaft 17. This prevents the control behavior of the valve section being adversely affected by the value of the discharge pressure Pd which can be relatively high.
  • valve element 16 is urged by a spring 18 in valve closing direction.
  • the force of the spring 18 is adjusted by an adjustment screw 19 screwed into the top port 14.
  • Another side port 20 communicating with a suction chamber (suction pressure Ps) is formed in a lower portion of the body 11 as viewed in FIG. 1.
  • the lower end of the body 11 is rigidly press-fitted in a body 21 of a magnetic material forming a part of the solenoid.
  • the body 21 contains a second plunger 22 as one of two divided plungers of the solenoid.
  • the second plunger 22 has a central blind hole 10 in an upper end face.
  • the blind hole 10 has an inner diameter larger than the outer diameter of the lower part of the shaft 17.
  • the lower part of the shaft 17, which is axially slidably guided by the body 11 without almost any clearance, has a lower end face 8 which is brought into contact with a bottom 9 of the blind hole 10.
  • the lower end face 8 is formed to be arcuate in cross-section, i.e. is convexly rounded versus the e.g. planar bottom 9 of the blind hole 10.
  • the end face 8 could be planar while the bottom 9 is convexly rounded in a central region. Even both the end face 8 and the bottom 9 could be convexly rounded in relation to each other.
  • the second plunger 22 has a T-shaped cross-section with a lower surface of a flange 23 situated opposed to an upper surface 7 of the body 21. This causes an axial attractive force to be generated between the opposed surfaces of the flange 23 and the body 21 thereby assisting the valve element 16 to promptly move in valve closing direction.
  • the second plunger 22 is urged upward by a spring 24 seated on a stepped shoulder inside the body 21.
  • the spring 24 has a larger spring force than the spring 18 urging the valve element 16 in valve closing direction.
  • the second plunger 22 can push the shaft 17 upward until the shaft 17 is brought into contact with the ceiling of a chamber communicating with the port 20 to hold the valve element 16 in the fully open position.
  • the spring 24 also centers a part of the second plunger 22 below the flange 23 such that the spring 24 tends to guide the second plunger 22 axially.
  • the pressure-sensing section and the remaining component parts of the solenoid are arranged below the second plunger 22.
  • the opening of the bottomed sleeve 25 is sealed by a metal diaphragm 29.
  • the core 27 is rigidly press-fitted into the bottomed sleeve 25.
  • the first plunger 26 is axially movably disposed on the upper side of the core 27.
  • the first plunger 26 is rigidly press-fitted on one end of a shaft 33 which axially movably extends through the center of the core 27.
  • the other lower end of the shaft 33 is slidably supported and guided by a bearing 34 which is slidably disposed in the core 27.
  • a stop ring 35 on an intermediate portion of the shaft 33 limits the upward movement of a spring-receiving member 36.
  • the spring 28 is interposed between the spring-receiving member 36 and the bearing 34. The first plunger 26 is urged by the spring 28 via the shaft 33 in a direction away from the core 27.
  • bottom of the bottomed sleeve 25 is pushed or stamped to be deformed inward, whereby the axial position of the bearing 34 is adjusted and fixed to accordingly adjust the force of the spring 28 and to adjust the set point of the control valve, e.g. when assembling the control valve.
  • the bottomed sleeve 25 is sealed by welding the diaphragm 29 to a flange portion formed on the open end of the bottomed sleeve 25.
  • the inside of the gastight assembly is maintained under vacuum.
  • the body 21, the case 31, and the handle 32 are made of magnetic substances to serve as the yoke of the magnetic circuit of the solenoid. Magnetic lines of force generated by the coil 30 pass through the magnetic circuit formed by the case 31, the body 21, the second plunger 22, the first plunger 26, the core 27, and the handle 32.
  • FIG. 1 the solenoid is de-energized.
  • the suction pressure Ps is relatively high, i.e. like in the state in which the air conditioner is not operating. Since the suction pressure Ps is high, the diaphragm 29 is displaced downward against the load of the spring 28.
  • the first plunger 26 is in contact with the core 27.
  • the second plunger 22 is urged upward by the spring 24 such that it is moved away from the diaphragm 29 to urge the valve element 16 via the shaft 17 toward the fully open position. Even when the variable displacement compressor is directly driven by the engine in the above state, the compressor is operated at the minimum displacement.
  • the first plunger 26 When maximum control current is supplied to the coil 30, as in the case of the start of the automotive air conditioner, the first plunger 26 remains pressed downward as in FIG. 1 by the high suction pressure Ps into contact with the core 27. Even if the first plunger 26 is attracted by the core 27, it remains in this position. Therefore, in this case, the first plunger 26 and the core 27 behave as if they were a fixed core, so that the first plunger 26 attracts the second plunger 22 via the diaphragm 29 against the urging force of the spring 24 into contact with the diaphragm 29.
  • the spring 18 pushes the valve element 16 downward to be seated on the valve seat 15 and to fully close the valve section. This blocks the passage between the discharge chamber and the crankcase, so that the compressor is promptly shifted into the operation at the maximum displacement.
  • the second plunger 22 is only axially in contact with the end face 8 of the shaft 17 but is not constrained thereby, so that even when the second plunger 22 is about to be moved in a tilted state depending on the condition of the spring 24 guiding the second plunger 22, no couple of forces can act on the shaft 17 and, hence, the axial slidability of the shaft 17 is not spoiled.
  • the diaphragm 29 attempts to move upward, in FIG. 1.
  • the control current supplied to the coil 30 is decreased according to the set temperature of the air conditioner, the second and first plungers 22, 26 in an attracted state move upward in unison to respective positions where the suction pressure Ps, the forces of the springs 18, 24, and 28, and the attractive force of the solenoid are balanced.
  • the valve element 16 is pushed upward by the second plunger 22 and moves away from the valve seat 15, thereby being set to a predetermined valve lift.
  • Refrigerant at the discharge pressure Pd is introduced into the crankcase at a flow rate controlled to a value dependent on the valve lift, whereby the variable displacement compressor is shifted to an operation with the displacement corresponding to the control current.
  • the diaphragm 29 senses the suction pressure Ps as an absolute pressure to thereby control the valve lift of the valve section. For example, when the refrigeration load increases, the suction pressure Ps becomes high and the first plunger 26 is displaced downward. The valve element 16 moves downward to decrease the valve lift causing the compressor to operate in a direction of increasing the displacement. When the refrigeration load decreases and the suction pressure Ps becomes low, the first plunger 26 is displaced upward to increase the valve lift causing the compressor to operate in a direction of decreasing the displacement. Thus, the control valve controls the displacement of the compressor such that the suction pressure Ps becomes equal to a value set by the control current for the solenoid.
  • a section accommodating the first plunger 26 could be open to the atmospheric pressure to thereby compare the suction pressure Ps and the atmospheric pressure.
  • a bellows could be provided instead of the a diaphragm 29, a bellows could be provided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Magnetically Actuated Valves (AREA)
EP05022396A 2004-10-13 2005-10-13 Regelventil für einen Verdichter variabler Verdrängung Withdrawn EP1647710A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004298794A JP2006112271A (ja) 2004-10-13 2004-10-13 可変容量圧縮機用制御弁

Publications (1)

Publication Number Publication Date
EP1647710A1 true EP1647710A1 (de) 2006-04-19

Family

ID=35311735

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05022396A Withdrawn EP1647710A1 (de) 2004-10-13 2005-10-13 Regelventil für einen Verdichter variabler Verdrängung

Country Status (5)

Country Link
US (1) US20060083625A1 (de)
EP (1) EP1647710A1 (de)
JP (1) JP2006112271A (de)
KR (1) KR20060052192A (de)
CN (1) CN1760544A (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4118181B2 (ja) * 2003-03-28 2008-07-16 サンデン株式会社 可変容量斜板式圧縮機の制御弁
JP4695032B2 (ja) * 2006-07-19 2011-06-08 サンデン株式会社 可変容量圧縮機の容量制御弁
JP2011252401A (ja) * 2010-05-31 2011-12-15 Shinhan Electro-Mechanics Co Ltd 可変容量圧縮機の容量制御弁、およびこの容量制御弁の組み立て方法
KR101249253B1 (ko) 2012-09-20 2013-04-02 주식회사 유텍솔루션 가변 용량 압축기의 전자제어밸브
US10655617B2 (en) 2017-12-05 2020-05-19 Hanon Systems Precise control of suction damping device in a variable displacement compressor
KR102692484B1 (ko) * 2019-05-20 2024-08-07 현대자동차주식회사 차량의 공기조화 시스템, 공기조화 시스템용 전자제어밸브 및 공기조화 시스템의 제어방법

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000110731A (ja) * 1998-10-08 2000-04-18 Tgk Co Ltd 容量可変圧縮機の容量制御装置
JP2000205549A (ja) * 1999-01-11 2000-07-25 Nippon Control Kogyo Co Ltd 石油燃焼器用バ―ナの燃料流量制御装置
EP1046818A2 (de) * 1999-04-21 2000-10-25 TGK Co., Ltd. Kapazitätsregelung für Verdichter mit veränderlicher Fördermenge
JP2002250456A (ja) * 2001-02-21 2002-09-06 Saginomiya Seisakusho Inc 電磁制御弁のソレノイド構造
EP1574711A2 (de) * 2004-03-12 2005-09-14 Tgk Company, Ltd. Kontrollventil für einen verstellbaren Taumelscheibenkompressor

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JP4446026B2 (ja) * 2002-05-13 2010-04-07 株式会社テージーケー 可変容量圧縮機用容量制御弁
JP3911443B2 (ja) * 2002-05-27 2007-05-09 太平洋工業株式会社 制御弁
JP4152674B2 (ja) * 2002-06-04 2008-09-17 株式会社テージーケー 可変容量圧縮機用容量制御弁
JP2004278511A (ja) * 2002-10-23 2004-10-07 Tgk Co Ltd 可変容量圧縮機用制御弁
JP2005098197A (ja) * 2003-09-04 2005-04-14 Tgk Co Ltd 可変容量圧縮機用容量制御弁
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000110731A (ja) * 1998-10-08 2000-04-18 Tgk Co Ltd 容量可変圧縮機の容量制御装置
JP2000205549A (ja) * 1999-01-11 2000-07-25 Nippon Control Kogyo Co Ltd 石油燃焼器用バ―ナの燃料流量制御装置
EP1046818A2 (de) * 1999-04-21 2000-10-25 TGK Co., Ltd. Kapazitätsregelung für Verdichter mit veränderlicher Fördermenge
JP2002250456A (ja) * 2001-02-21 2002-09-06 Saginomiya Seisakusho Inc 電磁制御弁のソレノイド構造
EP1574711A2 (de) * 2004-03-12 2005-09-14 Tgk Company, Ltd. Kontrollventil für einen verstellbaren Taumelscheibenkompressor

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PATENT ABSTRACTS OF JAPAN vol. 2000, no. 10 17 November 2000 (2000-11-17) *
PATENT ABSTRACTS OF JAPAN vol. 2003, no. 01 14 January 2003 (2003-01-14) *

Also Published As

Publication number Publication date
US20060083625A1 (en) 2006-04-20
CN1760544A (zh) 2006-04-19
KR20060052192A (ko) 2006-05-19
JP2006112271A (ja) 2006-04-27

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