EP1283361B1 - Regelventil für einen kompressor mit veränderlichem hubraum - Google Patents

Regelventil für einen kompressor mit veränderlichem hubraum Download PDF

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Publication number
EP1283361B1
EP1283361B1 EP01932108A EP01932108A EP1283361B1 EP 1283361 B1 EP1283361 B1 EP 1283361B1 EP 01932108 A EP01932108 A EP 01932108A EP 01932108 A EP01932108 A EP 01932108A EP 1283361 B1 EP1283361 B1 EP 1283361B1
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EP
European Patent Office
Prior art keywords
valve
variable capacity
pressure
capacity compressor
valve rod
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.)
Expired - Lifetime
Application number
EP01932108A
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English (en)
French (fr)
Other versions
EP1283361A4 (de
EP1283361A1 (de
Inventor
T. Kabushiki Kaisha Saginomiya Seisakusho IKEDA
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.)
Saginomiya Seisakusho Inc
Original Assignee
Saginomiya Seisakusho Inc
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 Saginomiya Seisakusho Inc filed Critical Saginomiya Seisakusho Inc
Publication of EP1283361A1 publication Critical patent/EP1283361A1/de
Publication of EP1283361A4 publication Critical patent/EP1283361A4/de
Application granted granted Critical
Publication of EP1283361B1 publication Critical patent/EP1283361B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a control valve for a variable capacity compressor and, more specifically, to a capacity control valve for a swash plate-type variable capacity compressor, which is used in an on-vehicle air conditioner and so forth.
  • a control valve for a variable capacity compressor has been known as a swash plate-type variable capacity compressor, in which there is provided a valve element driven by an action of a pressure sensitive element such as bellows, generated load of an electromagnetic coil device responds to that of the pressure sensitive element, the setting pressure of the pressure sensitive element is variably set in response to the generated load of the electromagnetic coil device, and pressure in a crankcase of the variable capacity compressor is controlled in response to the opening of the valve element, thereby controlling the capacity of the variable capacity compressor.
  • a pressure sensitive element such as bellows
  • a plunger chamber of an electromagnetic coil device having a plunger therein communicates with a delivery side or a crankcase of the variable capacity compressor and delivery pressure or pressure in a crankcase is introduced into the plunger chamber, therefore a plunger tube which forms the plunger chamber must have burst pressure strength resistant to the delivery pressure.
  • EP 0 396 017 A2 discloses an automotive air tempering apparatus for use in an automotive vehicle having a duct through which air is directed into a passenger compartment.
  • the apparatus comprises an air chilling unit including an evaporator provided in the duct and a compressor having a displacement variable for supplying a controlled amount of refrigerant to the evaporator for chilling the air in the duct.
  • a control unit controls the displacement of the compressor to bring the refrigerant temperature to a target value when air is introduced into the duct from the atmosphere
  • the control units controls the displacement of the compressor to bring the chilled air temperature to a target value when air is introduced into the duct from the passenger.
  • EP 0 953 765 A2 discloses a compressor including a swash plate, which is tiltably supported by a drive shaft. The displacement of the compressor changes in accordance with the inclination angle of the swash plate.
  • the minimum inclination angle of the swash plate is less than three to five degrees relative to a plane perpendicular to the axis of the drive shaft.
  • the swash plate can be moved from its minimum inclination to increase its angle, despite the small minimum inclination angle, due to a return spring, which urges the swash plate to increase the inclination angle.
  • the return spring positively moves the swash plate in a direction increasing the inclination angle.
  • JP-2000-018172 discloses a capacity control valve mechanism of a capacity variable compressor that improves pressure control accuracy in the intake chamber and enables forcible maintenance at the minimum capacity.
  • a control valve for a variable capacity compressor of the present invention described in claim 1 is a control valve for a variable capacity compressor, in which there is provided a valve element driven by an action of a pressure sensitive element arranged in a pressure sensitive element chamber into which suction pressure of the variable capacity compressor is introduced, generated load of an electromagnetic coil device responds to generated load of the pressure sensitive element, setting pressure of the pressure sensitive element is variably set in response to the generated load of the electromagnetic coil device, and pressure in a crankcase of the variable capacity compressor is controlled in response to opening of the valve element, thereby controlling capacity of the variable capacity compressor, characterized in that the electromagnetic coil device comprises a plunger chamber having a plunger therein, the plunger chamber communicates with the pressure sensitive element chamber, and the suction pressure is introduced into the plunger chamber.
  • the control valve 10 for a variable capacity compressor includes a cylindrical valve housing 11.
  • the valve housing 11 there are a passage 12 formed at a crankcase-side and a passage 13 formed at a delivery port-side, both of which extend crossing intermediate portion of the valve housing 11 in the direction of diameter of the valve housing 11, and there is formed a valve port 14 which communicates the passage 12 to the passage 13.
  • valve rod 16 movable up-and-down integrally including a valve element 15, which opens or closes the valve port 14, that is, communicates or shuts the passage 12 to the passage 13 quantitatively controlling the communication between the passage 12 and the passage 13 in response to the movement of the valve rod 16 in the direction of the valve axis (i.e. up-and-down direction).
  • a bellows receiving chamber 17 is formed at the lower end of the valve housing 11.
  • a bellows device 22 having a sealing structure as a pressure sensitive element, which is screwed to the valve housing 11 and includes an adjusting screw member 18 functioning as one end member and an inner stopper of the bellows device 22, a bellows body 19 linked integrally with the adjusting screw member 18 at one end (fixed end) thereof, an opposite end member 20 linked integrally with an opposite end (movable end) of the bellows body 19 functioning as an inner stopper, and an internal compensating spring 21 made of a compression coil spring.
  • a spring retainer 23 is fixed to the end member 20, and a main spring 24 made of a compression coil spring is provided between the spring retainer 23 and the adjusting screw member 18.
  • a suction pressure introducing port 25 from which suction pressure Ps of a swash plate-type variable capacity compressor is introduced into the bellows receiving chamber 17.
  • the interior of the bellows device 22 is a vacuum, therefore the bellows device 22 responds to the suction pressure Ps as absolute pressure.
  • stretching quantity (LbA to LbB) and generated load (WbA to WbB) correspond to a working pressure range of the suction pressure Ps of a compressor in a supercritical vapor compression-type refrigerating cycle device.
  • An lower end 16a of the valve rod 16 penetrates through a hole 26 formed in the valve housing 11 and protrudes in the bellows receiving chamber 17.
  • the lower end 16a engages with a spring retainer 27.
  • a set spring 28 made of a compression coil spring is provided between the spring retainer 27 and the spring retainer 23 at the bellows device 22-side.
  • the set spring 28 converts a pressure-sensitive action (stretching displacement) to elastic deformation action and transfer it to the valve rod 16.
  • a generated load characteristic of the set spring 28 is shown in Fig. 4, wherein the generated load (WhA to WhB) of the set spring 28 in the variable setting range is as low as about 1/15 of the generated load (WbA to WbB) of the bellows device 22 in the variable setting range.
  • the electromagnetic coil device 30 is mounted on the upper end of the valve housing 11.
  • the electromagnetic coil device 30 includes a body 32 fixed to the valve housing 11 having integrally a suction part 31, a plunger tube 33 and an outer box 34 fixed to the body 32, a coil bobbin 35, winding 36 and magnetic guide member 37 fixed to the outer box 34, a plug member 39 fixed to the outer box 34 with a bolt 38 covering the plunger tube 33, a plunger 40 provided in the plunger tube 33 (plunger chamber 53) movable up-and-down, a plunger spring 41 provided between the plug member 39 and the plunger 40, and a guide pin 43 fixed to the plug member 39 slidably fitting into a guide hole 42 formed in the plunger 40 so as to carry out the centering.
  • Figure 5 illustrates a generated load characteristic of the plunger 40 and the plunger spring 41, in which the generated load (WcA - WcB) in the control range is approximately in proportion to a coil current.
  • the generated load (WcA to WcB) in the control range becomes equal to the generated load (WhA to WhB) of the set spring 28 in the variable setting range and is as low as about 1/15 of the generated load (WbA to WbB) of the bellows device 22 in the variable setting range.
  • the body 32 is screwed to the valve housing 11, into which a valve rod guide member 46 is screwed.
  • the upper end side of the valve rod 16 fits movably up-and-down into a guide hole 47, which is formed in the central portion of the valve rod guide member 46.
  • the upper end 16b of the valve rod 16 protrudes from the valve rod guide member 46 in a space 48 formed between the valve rod guide member 46 and the body 32.
  • an equalizing hole (through hole) 49 which communicates the bellows receiving chamber 17 to the space 48.
  • a mounting flange 52 for mounting the control valve 10 on a variable capacity compressor engages with the outside of the body 32.
  • the suction pressure Ps of the compressor is introduced from the suction pressure introducing port 25 into the bellows receiving chamber 17 so as to actuate the bellows device 22, which expands and contracts in response to a pressure difference between the suction pressure Ps of the compressor and an internal pressure (vacuum pressure) of the bellows device 22.
  • the set spring 28 is elastically deformed in relation to the amount Lb of the expansion and contraction of the bellows device 22.
  • FIG. 6 is a graph illustrating a valve opening characteristic of the control valve 10 for a variable capacity compressor.
  • the suction pressure Ps of the compressor is introduced from the suction pressure introducing port 25 into the bellows receiving chamber 17, introduced into the space 48 by way of the equalizing hole 49, and introduced into the plunger chamber 53 by way of the equalizing holes 50 and 51.
  • the suction pressure Ps of the compressor is introduced into the plunger chamber 53 and therefore the pressure in the plunger chamber 53 never becomes high due to the delivery pressure Pd.
  • the plunger tube 33 is not necessary to be thick-walled, a gap between the winding 36 disposed outside the plunger tube 33 and the plunger 40 does not increase, and there is no necessity of enlarging the electromagnetic coil device 30.
  • the lower end 16a of the valve rod 16 is located in the bellows receiving chamber 17, the upper end 16b of the valve rod 16 is located in the space 48, and the suction pressure Ps is introduced into the bellows receiving chamber 17 and the space 48, therefore the upper and lower ends of the valve rod 16 are affected by the same suction pressure Ps.
  • D1 is the outer diameter of the valve rod 16 for its portion between Ps and Pc
  • D2 is the outer diameter of the valve rod 16 for its portion between Pc and Pd
  • D3 is the outer diameter of the valve rod 16 for its portion between Pd and Ps
  • valve rod 16 receives the delivery pressure Pd as the axial force in the direction of valve-opening on its intermediate portion and therefore the Ps set value can be controllably adjusted to be increased in response to the rise in the delivery pressure Pd as shown in Fig. 7B.
  • valve rod 16 receives the delivery pressure Pd as the axial force in the direction of valve-closing on its intermediate portion and therefore the Ps set value can be controllably adjusted to be decreased in response to the rise in the delivery pressure Pd as shown in Fig. 7C.
  • the generated load (WcA to WcB) by the plunger 40 and plunger spring 41 in the control range is as low as about 1/15 of the generated load (WbA to WbB) of the bellows device 22 in the variable setting range, therefore there is no necessity of enlarging the electromagnetic coil device 30 even in a refrigerating cycle using CO 2 .
  • valve opening characteristic and the controllable adjustment described above can be optionally set according to the desired control characteristic.
  • the generated load of the set spring 28 in the variable setting range is as low as about 1/15 of the generated load of the bellows device 22 in the variable setting range.
  • this value can be optionally adjusted by changing the spring constant of the set spring 28 and the generated load by the electromagnetic coil device 30 (i.e., magnitude of the electromagnetic coil device 30) can be optionally adjusted according thereto.
  • Figure 8 is a cross sectional view illustrating the second preferred embodiment of a control valve for a variable capacity compressor of the present invention.
  • the same reference numerals are used as those in Fig. 1 if the pertinent element in Fig. 8 is equivalent to or the same as that in Fig. 1.
  • the main spring (24) is omitted by increasing the spring constant of the bellows body 19 of the bellows device 22 and that of the internal compensating spring 21, so that the outer diameter of the valve housing 11 becomes slim.
  • the mounting measure of the control valve 10 on the variable capacity compressor is changed from the fixing with a flange to the fixing with a retaining ring 54.
  • control valve 10 in the second preferred embodiment is constructed similarly to that in the first preferred embodiment. Therefore, in the second preferred embodiment shown in Fig. 8, the same function and effect can be attained as those in the first preferred embodiment.
  • Figure 9 is a cross sectional view illustrating the third preferred embodiment of a control valve for a variable capacity compressor of the present invention.
  • the same reference numerals are used as those in Fig. 1 if the pertinent element in Fig. 9 is equivalent to or the same as that in Fig. 1.
  • the electromagnetic coil device 30 is further made slim in comparison with that in the second preferred embodiment shown in Fig. 8, that is, the control valve 10 for a variable capacity compressor together with the electromagnetic coil device 30 can be embedded in the compressor.
  • control valve 10 in the third preferred embodiment is constructed similarly to that in the first preferred embodiment. Therefore, in the third preferred embodiment shown in Fig. 9, the same function and effect can be attained as those in the first preferred embodiment.
  • the control valve for a variable capacity compressor of the present invention since the suction pressure of the compressor is introduced into the plunger chamber and therefore the pressure in the plunger chamber never becomes high due to the delivery pressure Pd, therefore even if the delivery pressure becomes high in a supercritical vapor compression-type refrigerating cycle device in which a refrigerant such as CO 2 is used, the plunger tube is not necessary to be thick-walled, there is no necessity of enlarging the electromagnetic coil device 30, and a compact designing can be possible without raising the cost of materials.
  • valve rod is affected by the suction pressure of the variable capacity compressor on both ends of the valve rod and not affected by other pressure in the axial force direction on an intermediate portion of the valve rod, therefore the set value of the suction pressure is never affected by the delivery pressure and the electromagnetic coil device can be made compact due to the decrease in the driving force of the valve.
  • the valve rod is affected by the suction pressure of the variable capacity compressor on both ends of the valve rod, the valve rod receives delivery pressure of the variable capacity compressor on an intermediate portion of the valve rod as an axial force in the direction of valve-opening, and the set value of the suction pressure can be controllably adjusted to be increased in response to the rise in the delivery pressure.
  • the valve rod is affected by the suction pressure of the variable capacity compressor on both ends of the valve rod, the valve rod receives delivery pressure of the variable capacity compressor on an intermediate portion of the valve rod as an axial force in the direction of valve-closing, and the set value of the suction pressure can be controllably adjusted to be decreased in response to the rise in the delivery pressure.

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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)

Claims (4)

  1. Regelventil (10) für einen Kompressor mit veränderbarer Kapazität, in dem ein Ventilelement (15) vorgesehen ist, das durch die Arbeit eines druckempfindlichen Elements (22) angetrieben wird, das in einer Kammer (17) für das druckempfindliche Element angeordnet ist, in die der Ansaugdruck (Ps) des Kompressors mit veränderbaren Kapazität eingeführt wird, bei dem die erzeugte Last einer elektromagnetischen Spuleneinrichtung (30) auf die erzeugte Last des druckempfindlichen Elements (22) reagiert, bei dem der Einstelldruck des druckempfindlichen Elements (22) in Reaktion auf die erzeugte Last der elektromagnetischen Spuleneinrichtung (30) veränderbar eingestellt wird und bei dem der Druck im Kurbelgehäuse des Kompressors mit veränderbarer Kapazität in Reaktion auf das Öffnen des Ventilelements (15) geregelt wird, wodurch die Kapazität des Kompressors mit veränderbarer Kapazität geregelt wird, wobei die elektromagnetische Spuleneinrichtung (30) eine Plungerkammer (53) mit einem Plunger (40) in ihrem Inneren aufweist, die Plungerkammer (53) mit der Kammer (17) für das druckempfindliche Element in Verbindung steht und der Ansaugdruck (Ps) in die Plungerkammer (53) eingeführt wird, dadurch gekennzeichnet, dass
    das Regelventil (10) eine Ventilstange (16) aufweist, die einstückig mit dem Ventilelement (15) ausgebildet ist, und die Ventilstange (16) durch den Ansaugdruck (Ps) des Kompressors mit veränderbarer Kapazität an beiden Enden der Ventilstange (16) beeinflusst wird.
  2. Regelventil (10) für einen Kompressor mit veränderbarer Kapazität nach Anspruch 1, wobei die Ventilstange (16) an einem mittleren Bereich der Ventilstange (16) durch keinen anderen Druck in der Richtung der axialen Kraft beeinflusst wird.
  3. Regelventil (10) für einen Kompressor mit veränderbarer Kapazität nach Anspruch 1, wobei die Ventilstange (16) eine Unterschiedlichkeit ihres axialen Durchmessers derart aufweist, sodass die Ventilstange (16) den Zuführungsdruck des Kompressors mit veränderbarer Kapazität an einem mittleren Bereich der Ventilstange (16) als axiale Kraft in der Richtung des Öffnens des Ventils aufnimmt.
  4. Regelventil (10) für einen Kompressor mit veränderbarer Kapazität nach Anspruch 1, wobei die Ventilstange (16) eine Unterschiedlichkeit ihres axialen Durchmessers derart aufweist, dass die Ventilstange (16) den Zuführungsdruck des Kompressors mit veränderbarer Kapazität an einem mittleren Bereich der Ventilstange (16) als eine Kraft in der Richtung des Schließens des Ventils aufnimmt.
EP01932108A 2000-05-19 2001-05-17 Regelventil für einen kompressor mit veränderlichem hubraum Expired - Lifetime EP1283361B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2000148543A JP4395239B2 (ja) 2000-05-19 2000-05-19 容量可変型圧縮機用制御弁
JP2000148543 2000-05-19
PCT/JP2001/004107 WO2001088372A1 (fr) 2000-05-19 2001-05-17 Soupape de regulation pour compresseur a cylindree variable

Publications (3)

Publication Number Publication Date
EP1283361A1 EP1283361A1 (de) 2003-02-12
EP1283361A4 EP1283361A4 (de) 2003-08-06
EP1283361B1 true EP1283361B1 (de) 2007-02-28

Family

ID=18654553

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01932108A Expired - Lifetime EP1283361B1 (de) 2000-05-19 2001-05-17 Regelventil für einen kompressor mit veränderlichem hubraum

Country Status (4)

Country Link
EP (1) EP1283361B1 (de)
JP (1) JP4395239B2 (de)
DE (1) DE60126931T2 (de)
WO (1) WO2001088372A1 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4316955B2 (ja) * 2003-08-11 2009-08-19 イーグル工業株式会社 容量制御弁
JP2006029150A (ja) * 2004-07-13 2006-02-02 Sanden Corp クラッチレス可変容量斜板式圧縮機の容量制御弁
JP2007138785A (ja) 2005-11-16 2007-06-07 Toyota Industries Corp 車両用冷凍回路の制御装置、容量可変型圧縮機及び容量可変型圧縮機用制御弁
JP5270890B2 (ja) * 2007-09-26 2013-08-21 サンデン株式会社 可変容量圧縮機のための容量制御システム
GB202008692D0 (en) 2020-04-24 2020-07-22 Lm Wind Power Blades India Pvt Ltd Wind turbine blade with reinforcing structure
GB202016561D0 (en) 2020-10-19 2020-12-02 Blade Dynamics Ltd Wind turbine blade with reinforcing structure

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH085310B2 (ja) * 1989-04-29 1996-01-24 日産自動車株式会社 車両用空調装置
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
JP3585150B2 (ja) * 1997-01-21 2004-11-04 株式会社豊田自動織機 可変容量圧縮機用制御弁
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
JP3728387B2 (ja) * 1998-04-27 2005-12-21 株式会社豊田自動織機 制御弁
JP4013328B2 (ja) * 1998-05-15 2007-11-28 株式会社豊田自動織機 可変容量圧縮機
JP4111593B2 (ja) * 1998-07-07 2008-07-02 サンデン株式会社 可変容量圧縮機の容量制御弁機構

Also Published As

Publication number Publication date
JP4395239B2 (ja) 2010-01-06
DE60126931T2 (de) 2007-06-28
JP2001329951A (ja) 2001-11-30
EP1283361A4 (de) 2003-08-06
EP1283361A1 (de) 2003-02-12
DE60126931D1 (de) 2007-04-12
WO2001088372A1 (fr) 2001-11-22

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