EP1512871A1 - Kontrollventil für einen verstellbaren Taumelscheibenkompressor - Google Patents

Kontrollventil für einen verstellbaren Taumelscheibenkompressor Download PDF

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Publication number
EP1512871A1
EP1512871A1 EP04020189A EP04020189A EP1512871A1 EP 1512871 A1 EP1512871 A1 EP 1512871A1 EP 04020189 A EP04020189 A EP 04020189A EP 04020189 A EP04020189 A EP 04020189A EP 1512871 A1 EP1512871 A1 EP 1512871A1
Authority
EP
European Patent Office
Prior art keywords
valve
control valve
pressure
opening area
flow rate
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Withdrawn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
EP04020189A
Other languages
English (en)
French (fr)
Inventor
Hisatoshi Hirota
Morimitsu Kajiwara
Ryosuke Yoshihiro
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 EP1512871A1 publication Critical patent/EP1512871A1/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction 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
    • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1877—External parameters

Definitions

  • the invention relates to a capacity control valve according to the preamble of claim 1, particularly for a variable displacement compressor in a refrigeration cycle of an automotive air conditioner.
  • compression pistons are connected to a wobble plate tiltably fitted on a shaft driven by the engine.
  • the angle of the wobble plate is varied to change the stroke of the pistons for changing the displacement of the compressor.
  • the wobble plate angle is continuously changed by introducing part of the compressed refrigerant into an airtight crankcase and changing the pressure Pc in the crankcase, thereby changing the balance between pressures applied to the opposite ends of each piston.
  • the capacity control valve comprises two control valves disposed in respective refrigerant passages between the discharge chamber and the crankcase and between the crankcase and the suction chamber. Both control valves operate in a manner interlocked with each other.
  • the capacity control valve controls the discharging capacity of the compressor such that the differential pressure (Pd - Ps) between the discharge pressure Pd and the suction pressure Ps of the compressor is held a predetermined value.
  • the first control valve (“the Pd-Pc valve”) for high pressure controls the flow rate from the discharge chamber into the crankcase.
  • the second control valve (the Pc-Ps valve) for low pressure controls the flow rate from the crankcase into the suction chamber in a manner interlocked with the operation of the first or Pd-Pc valve.
  • a solenoid serves to externally set a predetermined differential pressure (Pd - Ps) by a current value.
  • Fig. 7 shows characteristics of the capacity control valve of EP 1 279 831 A2
  • Fig. 8 shows characteristics of the variable displacement compressor of EP 1 278 983 A2.
  • the known compressor suffers from the problem that when the current is stepwise changed, the pressure Pc in the crankcase is largely changed, which causes a large change in the differential pressure (Pd - Ps), which is to be controlled, causing a large overshoot. This means that the torque momentarily consumed by the compressor is largely changed only at the moment when the solenoid current is changed. This causes a large variation of the load on the engine. More specifically, when the solenoid current is stepwise increased (Fig. 8), the Pd-Pc valve rapidly moves in the valve-closing direction and the Pc-Ps valve as well rapidly moves in the valve-opening direction.
  • a too rapid drop in the pressure Pc in the crankcase is then the result so that the pressure Pc once undergoes a sharp drop and then changes such that it settles to the predetermined pressure.
  • the discharging capacity is excessively increased in response to the sharp drop in the pressure Pc in the crankcase, resulting in a sharp increase of the torque consumed by the compressor, and in an overshoot.
  • the flow rate-restricting means suppresses a resulting sharp change in the pressure in the crankcase such that an excessive rise or excessive drop in the pressure cannot occur. This prevents overshooting of the differential pressure between the discharge pressure and the suction pressure, and reduces variations of the torque consumed by the compressor. As a result, it is possible to reduce variation of the load on the engine that drives the compressor.
  • the capacity control valve in Fig. 1 has a valve section 1 and a solenoid section 2.
  • the valve section 1 includes a body 3 having a top opening receiving an open plug 4.
  • the plug 4 has an axial hole forming a port 5 for receiving refrigerant at a discharge pressure Pd from a not shown discharge chamber of a variable displacement compressor, and forming a valve seat 6.
  • a ball valve element 7 is disposed axially movable A space receiving the ball valve element 7 communicates with the not shown crankcase of the variable displacement compressor via a port 8 formed in the body 3.
  • the ball valve element 7 and the valve seat 6 form a Pd-Pc valve (first control valve) that controls the flow rate of refrigerant at the discharge pressure Pd to fill the crankcase with a pressure Pc.
  • the body 3 has a port 9 communicating with a not shown suction chamber of the variable displacement compressor.
  • a valve seat 10 is integrally formed with the body 3 in a passage between the ports 8, 9.
  • a valve element 11 which also holds the ball valve element 7 of the Pd-Pc valve is axially disposed opposed to the valve seat 10.
  • Interposed between the valve element 11 and the plug 4 is a spring 12 urging the ball valve element 7 in valve-opening direction and the valve element 11 in valve-closing direction.
  • the valve element 11 and the valve seat 10 form a Pc-Ps valve (second control valve) which controls the flow rate of refrigerant at pressure Pc in the crankcase to fill the suction chamber with refrigerant at suction pressure Ps.
  • the capacity control valve in Fig. 1 is characterized in that the second control valve includes a spool valve structure whose opening area does not change at least as long as the valve element 7 of the Pd-Pc valve is open but is not fully open.
  • a spool valve element 11 a disposed within a valve hole of the valve seat 10 of the second or Pc-Ps valve is integrally formed with the valve element 11 at an end face of the valve element 11 opposed to the valve seat 10.
  • the second or Pc-Ps valve forms a spool valve for which in a stroke region where the valve element 11 moves axially to start to open the first or Pd-Pc valve, the dimension of the opening area of the second or Pc-Ps valve solely will be defined by a clearance between the spool valve element 11 a and the valve hole.
  • the dimension of the clearance first does not change. Only in a stroke region in which the first or Pd-Pc valve is close to or in the fully-open position, the dimension of the opening area between the valve element 11 and the valve seat 10 changes until the second or Pc-Ps valve closes, i.e. the dimension of the opening area provided by the valve element 11 and the valve seat 10 then will become smaller than the dimension of the opening area provided by the flow restricting areas.
  • the clearance which first does not change its opening area forms flow rate-restricting means.
  • the body 3 has a strainer 13 on the upper end.
  • the port 9 is connected with a passage 14 in the body 3 transmitting the suction pressure Ps to the inside of the solenoid 2.
  • the diameter of the valve hole of the valve seat 10 is larger than that of the valve hole of the valve seat 6 of the Pd-Pc valve, allowing refrigerant to instantly flow at a large flow rate.
  • the solenoid section 2 has a central core 15. An upper end of the core 15 is screwed into a lower end of the body 3. A yoke 16 encloses the core 15. An upper end of the yolk 16 is screwed onto the body 3. A sleeve 17 is disposed in the yoke 16. A hollow cylindrical holder 18 is provided on the lower ends of the yoke 16 and of the sleeve 17. The holder 18 receives an adjustment screw 19.
  • the core 15 has a central through hole receiving a shaft 20.
  • the shaft 20 has one end supported in a through hole formed in the body 3, and another end supported in a recess in the adjustment screw 19.
  • the shaft 20 has a shaft 21 integrally formed at the one end.
  • the shaft 21 is reduced in diameter and is inserted into the valve element 11 for centering both the valve element 11 and the ball valve element 7.
  • the shaft 20 has the same diameter as the valve hole of the valve seat 6 of the Pd-Pc valve.
  • a pressure-receiving area of the ball valve element 7 where the discharge pressure Pd is received and a pressure-receiving area of the lower end of the shaft 20 where the suction pressure Ps introduced into the solenoid section 2 via the passage 14 is received are equal.
  • the solenoid section 2 further includes a plunger 22 fixed to the shaft 20 at a location between the core 15 and the adjustment screw 19.
  • a spring 23 is disposed between the core 15 and the plunger 22.
  • Another spring 24 is disposed between the plunger 22 and the adjustment screw 19.
  • a coil 25 is disposed between the sleeve 17 and the yoke 16. The coil 25 is electrically connected to a harness 27 extending out of the solenoid section 2 via a waterproof coupler 26.
  • the plunger 22 When no current is supplied to the coil 25 (e.g. when the automotive air conditioner is not in operation, or when the refrigerating load is the minimum), the plunger 22 is urged by the spring 23 away from the core 15, and the ball valve element 7 and the valve element 11 are urged by the spring 12 in a direction toward the solenoid section 2.
  • the first or Pd-Pc valve for high pressure is in the fully-open position.
  • the second or Pc-Ps valve for low pressure is in the fully-closed position.
  • Introduced discharge pressure Pd is introduced into the crankcase via the first or Pd-Pc valve.
  • the pressure Pc in the crankcase becomes closer to the discharge pressure Pd, minimizing the differential pressure between the pressures applied to the opposite end faces of the pistons of the compressor. This brings the wobble plate to an inclination angle which minimizes the stroke of the pistons.
  • the compressor is controlled to the minimum displacement operation.
  • the plunger 22 When no current is supplied to the coil 25 increases, the plunger 22 is attracted by the core 15 to move upward, and the shaft 20 fixed to the plunger 22 moves as well. As shown in Fig. 2, the opening area of the first or Pd-Pc valve decreases from a maximum as the ball valve element 7 moves toward the valve seat 6. The opening area of the second or Pc-Ps valve increases from zero as the valve element 11 moves away from the valve seat 10. Accordingly, the pressure Pc in the crankcase progressively decreases, so that the variable displacement compressor is controlled to operation with a displacement dependent on the value of the solenoid current.
  • the opening area of the first or Pd-Pc valve continues to decrease but the increase of the opening area of the second or Pc-Ps valve stops at a time point when the opening area between the valve element 11 and the valve seat 10 becomes larger than the opening area defined by the dimension of the clearance between the spool valve element 11a and the valve hole of the valve seat 10 of the second or Pc-Ps valve. Even if the solenoid current then increases further the Pc-Ps valve will show a flat characteristic such that the opening area does not change relative to the travel or stroke amount of the valve element 11 since the opening area remains restricted by the dimension of the clearance between the spool valve element 11a and the valve hole of the valve seat 10.
  • the Pd-Pc valve and the Pc-Ps valve are controlled to respective stroke positions dependent on the value of the solenoid current.
  • the capacity control valve accordingly will change the travel or stroke amounts of the valve elements 7, 11 of the Pd-Pc valve and the Pc-Ps valve to vary the displacement of the compressor. This provides a control such that the differential pressure Pd-Ps is held at a predetermined value as determined by the solenoid current.
  • the Pc-Ps valve has the flat characteristic such that the opening area does not change in a region where the opening area of the Pd-Pc valve is small, and when the solenoid current is changed stepwise, the pressure Pc in the crankcase does not largely change relative to the change in the solenoid current, as shown in Fig. 3. If the solenoid current is increased, e.g. stepwise, in a region where the opening area of the Pc-Ps valve changes, the ratio of change of the opening area in opening direction of the Pc-Ps valve with respect to the stroke amount is larger than that of the change of the opening area in closing direction of the Pd-Pc valve with respect to the same stroke amount.
  • the pressure Pc in the crankcase may tend to sharply decrease, but the range of this change is restricted by the flat characteristic of the Pc-Ps valve so that overshooting of the pressure Pc in the crankcase is prevented.
  • overshooting of the differential pressure (Pd - Ps) between the discharge pressure Pd and the suction pressure Ps does not occur, either, which reduces variation in torque consumed by the compressor and hence reduces variation in load on the engine.
  • the solenoid current is increased, e.g. stepwise, in a region where the opening area of the Pc-Ps valve does not change due to the spool valve body 11a, the Pc-Ps valve opening area does not change relative to a stroke amount even though the Pd-Pc valve undergoes a change of opening area in the valve-closing direction relative to the same stroke amount.
  • the solenoid current is stepwise decreased, an overshooting will be suppressed in the same manner.
  • the capacity control valve of Fig. 4 attains the same flat characteristic by an orifice 28 as the flow rate-restricting means whose opening area does not change.
  • the second or Pc-Ps valve has on the valve element 11 a surface with a tapered shape opposed to the valve seat 10.
  • the orifice 28 is provided between the downstream side of the valve element 11, and the port 9 and the passage 14.
  • the orifice 28 is disposed in series with the second or Pc-Ps valve.
  • the capacity control valve in Fig. 5 is configured such that the operation of the second or Pc-Ps valve is not adversely affected by the pressure Pc in the crankcase.
  • the capacity control valve in Fig. 5 is provided with a passage 14' which connects a space 11b between the Pd-Pc valve and the Pc-Ps valve, with the inside 2a of the solenoid section 2.
  • the pressure Pc is transmitted to the inside 2a of the solenoid section 2.
  • the valve element 11 receives the pressure Pc in the space 11b in valve-closing direction, and also receives the pressure Pc from the solenoid section 2 via the shaft 20 in valve-opening direction. Therefore, the influence of the pressure Pc on the valve element 11 is cancelled. Even when the pressure Pc in the crankcase changes, the change does not adversely affect the operation of the second or Pc-Ps valve.
  • the pressure received by the valve element 11 in valve-opening direction is the sum of the pressure Pc in the crankcase received from the solenoid section 2 and the suction pressure Ps.
  • the area where the pressure Pc is received is equal to the cross-sectional area of the shaft 20
  • the area where the suction pressure Ps is received is equal to an area obtained by subtracting the cross-sectional area of the shaft 20 from the opening area of the valve hole of the valve seat 10 of the Pc-Ps valve, and is equal to the area where the discharge pressure Pd is received by the first or Pd-Pc valve, i.e. the opening area of the valve hole of the valve set 6 of the first or Pd-Pc valve.
  • the capacity control valve of Fig. 5 also has the valve characteristic shown in Fig. 2.
  • the capacity control valve of Fig. 6 is configured such that the operation of the second or Pc-Ps valve is not adversely affected by the pressure Pc in the crankcase.
  • the capacity control valve in Fig. 6 is provided with the passage 14' which connects the space 11b between the Pd-Pc valve and the Pc-Ps with the inside 20 of the solenoid section 2, similar to the capacity control valve according to Fig. 5.
  • the pressure Pc is transmitted to the inside 2a of the solenoid section 2. The influence of the pressure Pc received by the valve element 11 in opposite directions is cancelled.
EP04020189A 2003-09-04 2004-08-25 Kontrollventil für einen verstellbaren Taumelscheibenkompressor Withdrawn EP1512871A1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2003312369 2003-09-04
JP2003312369 2003-09-04
JP2003332652 2003-09-25
JP2003332652A JP2005098197A (ja) 2003-09-04 2003-09-25 可変容量圧縮機用容量制御弁

Publications (1)

Publication Number Publication Date
EP1512871A1 true EP1512871A1 (de) 2005-03-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP04020189A Withdrawn EP1512871A1 (de) 2003-09-04 2004-08-25 Kontrollventil für einen verstellbaren Taumelscheibenkompressor

Country Status (3)

Country Link
US (1) US20050053474A1 (de)
EP (1) EP1512871A1 (de)
JP (1) JP2005098197A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101858340A (zh) * 2009-04-03 2010-10-13 福特环球技术公司 可变排量变速器油泵的控制
EP2743504A1 (de) * 2012-12-11 2014-06-18 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP2818707A3 (de) * 2013-06-28 2015-09-02 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP2821649A3 (de) * 2013-07-04 2015-10-07 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP3951171A4 (de) * 2019-04-03 2022-11-30 Eagle Industry Co., Ltd. Kapazitätssteuerungsventil
US11754194B2 (en) 2019-04-03 2023-09-12 Eagle Industry Co., Ltd. Capacity control valve
US11821540B2 (en) 2019-04-03 2023-11-21 Eagle Industry Co., Ltd. Capacity control valve

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006112271A (ja) * 2004-10-13 2006-04-27 Tgk Co Ltd 可変容量圧縮機用制御弁
CN101155990B (zh) * 2005-04-08 2012-08-08 伊格尔工业股份有限公司 容量控制阀
WO2006137270A1 (ja) * 2005-06-22 2006-12-28 Eagle Industry Co., Ltd. 容量制御弁
DE102005031511A1 (de) * 2005-07-06 2007-01-11 Daimlerchrysler Ag Steuerungsventil für einen Kältemittelverdichter und Kältemittelverdichter
JP2008038955A (ja) * 2006-08-02 2008-02-21 Tgk Co Ltd 制御弁
JP5235569B2 (ja) * 2008-09-12 2013-07-10 サンデン株式会社 容量制御弁、可変容量圧縮機及び可変容量圧縮機の容量制御システム
KR101617825B1 (ko) * 2010-01-19 2016-05-04 학교법인 두원학원 공기조화장치용 제어 밸브 및 차량용 공기조화장치
KR101781612B1 (ko) * 2010-07-16 2017-09-26 학교법인 두원학원 용량가변형 압축기의 용량제어밸브
EP2653723B1 (de) * 2010-12-09 2019-01-02 Eagle Industry Co., Ltd. Ventil zur kapazitätssteuerung
KR102051661B1 (ko) * 2017-05-30 2019-12-04 한온시스템 주식회사 컨트롤 밸브 및 가변 용량식 압축기

Citations (3)

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Publication number Priority date Publication date Assignee Title
US6010312A (en) * 1996-07-31 2000-01-04 Kabushiki Kaisha Toyoda Jidoshokki Seiksakusho Control valve unit with independently operable valve mechanisms for variable displacement compressor
EP1106831A2 (de) * 1999-12-09 2001-06-13 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Kontrollventil in einem Verdichter variabler Verdrängung
EP1279831A2 (de) * 2001-07-25 2003-01-29 TGK CO., Ltd. Hubregelungsventil zur Verwendung in einem Kompressor mit veränderlicher Fördermenge

Family Cites Families (3)

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Publication number Priority date Publication date Assignee Title
JP3783434B2 (ja) * 1998-04-13 2006-06-07 株式会社豊田自動織機 容量可変型斜板式圧縮機、及び空調用冷房回路
JP2000064957A (ja) * 1998-08-17 2000-03-03 Toyota Autom Loom Works Ltd 容量可変型斜板式圧縮機および抜き側制御弁
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

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6010312A (en) * 1996-07-31 2000-01-04 Kabushiki Kaisha Toyoda Jidoshokki Seiksakusho Control valve unit with independently operable valve mechanisms for variable displacement compressor
EP1106831A2 (de) * 1999-12-09 2001-06-13 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Kontrollventil in einem Verdichter variabler Verdrängung
EP1279831A2 (de) * 2001-07-25 2003-01-29 TGK CO., Ltd. Hubregelungsventil zur Verwendung in einem Kompressor mit veränderlicher Fördermenge

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101858340A (zh) * 2009-04-03 2010-10-13 福特环球技术公司 可变排量变速器油泵的控制
CN101858340B (zh) * 2009-04-03 2014-09-03 福特环球技术公司 可变排量变速器油泵的控制
EP2743504A1 (de) * 2012-12-11 2014-06-18 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP2916003A1 (de) * 2012-12-11 2015-09-09 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP2918833A1 (de) * 2012-12-11 2015-09-16 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP2818707A3 (de) * 2013-06-28 2015-09-02 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP2821649A3 (de) * 2013-07-04 2015-10-07 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP3951171A4 (de) * 2019-04-03 2022-11-30 Eagle Industry Co., Ltd. Kapazitätssteuerungsventil
US11754194B2 (en) 2019-04-03 2023-09-12 Eagle Industry Co., Ltd. Capacity control valve
US11821540B2 (en) 2019-04-03 2023-11-21 Eagle Industry Co., Ltd. Capacity control valve

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Publication number Publication date
US20050053474A1 (en) 2005-03-10
JP2005098197A (ja) 2005-04-14

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