EP0855506A2 - Compresseur à capacité variable - Google Patents

Compresseur à capacité variable Download PDF

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Publication number
EP0855506A2
EP0855506A2 EP98101411A EP98101411A EP0855506A2 EP 0855506 A2 EP0855506 A2 EP 0855506A2 EP 98101411 A EP98101411 A EP 98101411A EP 98101411 A EP98101411 A EP 98101411A EP 0855506 A2 EP0855506 A2 EP 0855506A2
Authority
EP
European Patent Office
Prior art keywords
variable
communication path
displacement compressor
chamber
crank chamber
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.)
Granted
Application number
EP98101411A
Other languages
German (de)
English (en)
Other versions
EP0855506A3 (fr
EP0855506B1 (fr
Inventor
Yukihiko Taguchi
Kiyoshi Terauchi
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.)
Sanden Corp
Original Assignee
Sanden 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 Sanden Corp filed Critical Sanden Corp
Publication of EP0855506A2 publication Critical patent/EP0855506A2/fr
Publication of EP0855506A3 publication Critical patent/EP0855506A3/fr
Application granted granted Critical
Publication of EP0855506B1 publication Critical patent/EP0855506B1/fr
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
    • F04B2027/1822—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

  • This invention relates to a variable-displacement compressor and, more particularly, to a variable-displacement compressor for use in an air conditioning apparatus for an automobile.
  • variable-displacement compressor In general, a variable-displacement compressor is used in an air conditioning apparatus for an automobile.
  • a conventional variable-displacement compressor is disclosed in Japanese Patent Publication (JP-A) Tokko Hei 4-74549 (74549/1992).
  • the conventional variable-displacement compressor is a variable-displacement compressor of a wobble plate type and comprises a compressor housing in which a crank chamber is formed.
  • a rotor is located in the crank chamber and is attached to a driving shaft.
  • a slant plate is attached to the rotor through a hinge mechanism.
  • the driving shaft penetrates through the slant plate which is attached to a sleeve.
  • the driving shaft is surrounded by the sleeve.
  • a space is formed between the outer surface of the sleeve and the inner surface of the slant plate so that the slant plate has a variable slant angle for the driving shaft.
  • the hinge mechanism makes the variable slant angle be varied in concern with the driving shaft, as will be described later.
  • a wobble or rock plate is positioned on the slant plate through a bearing.
  • a plurality of piston rods are connected to the wobble plate.
  • the piston rods have piston members, respectively.
  • the piston members are located in cylinder portions which are formed in the compressor housing. More particularly, the cylinder portions are formed in the compressor housing at a predetermined interval so as to surround the driving shaft.
  • a guide rod is supported by the compressor housing to be located in parallel to the driving shaft in the crank chamber.
  • the wobble plate is attached to the guide rod so as to slide along the guide rod.
  • the rotor is rotated by the rotation of the driving shaft.
  • the slant plate is connected to the rotor through the hinge mechanism, the slant plate is rotated in accordance with the rotation of the rotor.
  • the wobble plate wobbles or oscillates inasmuch as the wobble plate is slidably attached to the guide rod as described above.
  • the piston members are reciprocated in the cylinder portions, respectively.
  • the compressor housing has a suction chamber and a discharge chamber each of which communicates with the cylinder portions.
  • refrigerant is taken from the suction chamber to cylinder portions to be compressed into a compressed refrigerant which is discharged as a discharged gas to the discharge chamber.
  • the slant plate has the variable slant angle as described above, it is possible to make the stroke of each piston member vary under control of the variable slant angle.
  • the conventional variable-displacement compressor varies its compression capacity under control of the variable slant angle.
  • first and second communication paths are formed in the compressor housing in the conventional variable-displacement compressor.
  • the conventional variable-displacement compressor further comprises a switching valve for opening and closing the first communication path.
  • the switching valve opens and closes the first communication path to make a suction pressure become a predetermined pressure.
  • the crank chamber always communicates with the suction chamber in order to escape the discharged gas from the crank chamber to the suction chamber.
  • the crank chamber always communicates with suction chamber in the conventional variable-displacement compressor.
  • the conventional variable-displacement compressor has been put out of operation during a long time and when liquid refrigerant exists in a low pressure side of a refrigeration circuit which is connected to the conventional variable-displacement compressor, the liquid refrigerant flows from the refrigeration circuit into the crank chamber through the suction chamber inasmuch as the crank chamber always communicates with the suction chamber. More specifically, an amount of liquid refrigerant flows into the crank chamber through the suction chamber in case where a room temperature is high in an automobile and a temperature of an engine room is low in which the conventional variable-displacement compressor is located.
  • the opening area of the second communication path lacks in concern with the amount of the liquid refrigerant which exists in the crank chamber.
  • a pressure difference occurs between the crank chamber and the suction chamber.
  • the variable slant angle becomes a predetermined minimum angle so that the conventional variable-displacement compressor has a minimum compression capacity. Therefore, it is difficult to obtain a desired compression capacity until the liquid refrigerant sufficiently flows out of the crank chamber. In other words, it is difficult to obtain the desired compression capacity just after the conventional variable-displacement compressor is put into operation.
  • variable-displacement compressor capable of obtaining a desired compression capacity just after the variable-displacement compressor is put into operation.
  • a variable-displacement compressor comprises a compressor housing having a crank chamber, a discharge chamber, and a suction chamber.
  • the variable-displacement compressor further comprises a driving shaft rotatably supported by the compressor housing to be located in the crank chamber and a slant plate located in the crank chamber to be coupled to the driving shaft.
  • the slant plate has a variable slant angle for the driving shaft.
  • the variable-displacement compressor varies the variable slant angle in accordance with a pressure difference between the crank chamber and the suction chamber to control a compression capacity.
  • variable-displacement compressor comprises (A) a first communication path through which the crank chamber communicates with the discharge chamber, the first communication path having a first opening area, (B) a first valve device for adjusting the first opening area to control the pressure in the crank chamber, (C) a second communication path through which the crank chamber communicates with the suction chamber, the second communication path having a second opening area, and (D) a second valve device for adjusting the second opening area in accordance with a pressure difference between the crank chamber and the suction chamber. More specifically, the second valve device perfectly closes the second communication path when the pressure difference becomes a predetermined pressure difference.
  • variable-displacement compressor 10 according to a first embodiment of this invention.
  • the illustrated variable-displacement compressor comprises a compressor casing 11 at which a penetration portion is formed along a transversal direction of Fig. 1.
  • a driving shaft 12 is inserted from the penetration portion into the compressor casing 11 and is rotatably supported to the compressor casing 11 by bearings 11a and 11b.
  • the compressor casing 11 has a crank chamber 13 in which a rotor 14 is located.
  • the rotor 14 is attached to the driving shaft 12.
  • a slant plate 15 is attached to the rotor 14 through a hinge mechanism 14a.
  • the driving shaft 12 penetrates through the slant plate 15 so that the driving shaft 12 is in contact with the slant plate 15. More particularly, the surface of the driving shaft 12 is in contact with the inner wall surface of the slant plate 15 so that the slant plate 15 is able to slide along the direction of the driving shaft 12.
  • the slant plate 15 has a variable slant angle for the driving shaft 12 that is varied by the hinge mechanism 14a.
  • a wobble plate 16 is attached to the slant plate 15 through a bearing 15a.
  • a plurality of piston rods 17 is connected to the wobble plate 16.
  • the piston rods 17 are connected to piston members 18, respectively.
  • a plurality of cylinder portions 19 are formed in the compressor casing 11 at a predetermined interval so as to surround the driving shaft 12.
  • the piston members 18 are positioned in the cylinder portions 19, respectively.
  • a guide rod 20 is supported by the compressor casing 11 to be located in parallel to the driving shaft 12 in the crank chamber 13.
  • the wobble plate 16 is attached to the guide rod 20 at its one end so as to slide along the guide rod 20.
  • a valve plate 21 and a cylinder head 22 are positioned at the right end portion of the compressor casing 11 in Fig. 1. As a result, the right opening portion of the compressor casing 11 is closed by the cylinder head 22 in Fig. 1.
  • a compressor housing is composed of the compressor casing 11 and the cylinder head 22.
  • a suction chamber 23 and a discharge chamber 24 are formed in the cylinder head 22.
  • the suction chamber 23 is connected to an inlet port 23a.
  • the discharge chamber 24 is connected to an outlet port (not shown). Although no illustration is made in Fig. 1, each of the inlet port 23a and the outlet port is connected to a refrigeration circuit.
  • a suction hole 21a and a discharge hole 21b are formed on the valve plate 21.
  • the suction chamber 23 and the discharge chamber 24 are connected to the cylinder portions 19 through the suction hole 21a and the discharge hole 21b, respectively.
  • a bolt 25 and a nut 26 a suction valve and a discharge valve (not shown) are fixed together with a valve retainer 27 on the valve plate 21 at the central portion of the valve plate 21.
  • a first communication path 28 is formed in the bolt 25 and the cylinder head 22.
  • the crank chamber 13 communicates with the discharge chamber 24 through the first communication path 28.
  • a pressure control valve device 29 is positioned in the first communication path 28. As will be described later, the pressure control valve device 29 makes the crank chamber 13 selectively communicate with the discharge chamber 24 through the first communication path 28.
  • a second communication path 30 is formed through which the crank chamber 13 communicates with the suction chamber 23.
  • a valve seat 31 is formed in the second communication path 30.
  • a valve body 32 is mounted on the valve seat 31.
  • the valve body 32 is pushed towards a direction at which the second communication path 30 is closed.
  • the valve seat 31, the valve body 32, and the spring 33 collectively serves as an open and close valve device which operates in response to a pressure difference between the crank chamber 13 and the suction chamber 23.
  • the spring 33 has a predetermined spring force.
  • the valve body 32 When the pressure difference between the crank chamber 13 and the suction chamber 23 is not greater than the predetermined pressure difference, the valve body 32 is moved towards a left hand of Fig. 1 by the predetermined spring force to close the second communication path 30. More particularly, the second communication path 30 has an opening area. The valve body 32 adjusts the opening area of the second communication path 30 in accordance with the pressure difference between the crank chamber 13 and the suction chamber 23.
  • the predetermined pressure difference is less than a pressure difference at which the slant plate 15 starts varying the variable slant angle.
  • the second communication path 30 is perfectly closed when the pressure difference between the crank chamber 13 and the suction chamber 23 is not greater than the predetermined pressure difference. As a result, the crank chamber 13 does not communicate with the suction chamber 23.
  • the pressure control valve device 29 comprises a valve body 291 for use in opening and closing the first communication path 28.
  • the pressure control valve device 29 further comprises a bellows valve 292.
  • the bellows valve 292 maintains a vacuum therein and has a spring (not shown) therein.
  • the bellows valve 292 senses the pressure in the suction chamber 23 as a sensed suction pressure through a third communication path 34 which is for use in connecting the pressure control valve device 29 to the suction chamber 23.
  • the bellows valve 292 has a transmission rod 293 which drives the valve body 291 in accordance with a telescopic motion of the bellows valve 292, in order to open and close the first communication path 28. More particularly, the first communication path 28 has an opening area.
  • the bellows valve 292 adjusts the opening area of the first communication path 28 in accordance with the sensed suction pressure.
  • the valve body 291 is pushed by a spring 294 towards a direction at which the first communication path 28 is closed.
  • the pressure control valve device 29 controls the valve body 291 in response to the pressure in the suction chamber 23 that is sensed by the bellows valve 292.
  • the pressure control valve device 29 may have, for example, a pressure control characteristic shown in Fig. 2.
  • a suction pressure (Ps) linearly drops as a discharge pressure (Pd) becomes high.
  • the suction pressure (Ps) becomes 1.7kg/cm 2 G when the discharge pressure (Pd) is 15kg/cm 2 G.
  • variable-displacement compressor 10 When the variable-displacement compressor 10 is put out of operation, the pressure is well balanced in the refrigeration circuit. It will be assumed that the pressure is well balanced at 6kg/cm 2 G in the refrigeration circuit. Namely, it will be assumed that a balanced pressure is equal to 6kg/cm 2 G in the refrigeration circuit.
  • the pressure control valve device 29 has the pressure control characteristic which is higher than the balanced pressure. Therefore, the bellows valve 292 shrinks in the pressure control valve device 29 so that the valve body 291 closes the first communication path 28. Inasmuch as the pressure is well balanced in the refrigeration circuit, the valve body 32 closes the second communication path 30.
  • the refrigerant does not flow from the discharge chamber 24 to the crank chamber 13 through the first communication path 28 when the variable-displacement compressor 10 is put out of operation. Similarly, the refrigerant does not flow from the suction chamber 23 to the crank chamber 13 through the second communication path 30 when the variable-displacement compressor 10 is put out of operation.
  • the discharged gas does not flow from the discharge chamber 24 to the crank chamber 13 inasmuch as the pressure control valve device 29 closes the first communication path 28.
  • the blow-by gas exists in the crank chamber 13.
  • the blow-by gas is supplied from the cylinder portions 19 to the crank chamber 13 on reciprocating the piston members 18.
  • the pressure reduces in the suction chamber 23.
  • the valve body 32 opens the second communication path 30 so that the gas flows from the crank chamber 13 to the suction chamber 23.
  • variable-displacement compressor 10 is driven in a maximum compression capacity with the maximum slant angle of the slant plate 15.
  • the bellows valve 292 stretches to make the transmission rod 293 push the valve body downwardly of Fig. 1 when the suction pressure lowers to 1.7kgcm 2 G in Fig. 2.
  • the valve body 291 opens the first communication path 28.
  • the first communication path 28 is opened by the valve body 291, an amount of the discharged gas flows from the discharge chamber 24 to the crank chamber 13 through the first communication path 28.
  • variable-displacement compressor 10 controls the pressure control valve device 29 so as to make the pressure in the suction chamber 23 become the prescribed pressure.
  • variable-displacement compressor is different in structure from the variable-displacement compressor illustrated in Fig. 1 and is therefore designated afresh by a reference numeral 40. More particularly, the pressure control valve device illustrated in Fig. 3 is different in structure from the pressure control valve device 29 illustrated in Fig. 1.
  • the variable-displacement compressor 40 comprises similar parts which are designated by like reference numerals. For a matter of convenience, the pressure control valve device illustrated in Fig. 3 will be designated by the reference numeral 29.
  • the pressure control valve device 29 comprises the valve body 291 which is for use in opening and closing the first communication path 28. Furthermore, the pressure control valve device 29 comprises the bellows valve 292.
  • the bellows valve 292 maintains a vacuum therein and has the spring therein.
  • the bellows valve 292 senses the pressure in the the suction chamber 23 through the third communication path 34 which is for use in connecting the pressure control valve device 29 to the suction chamber 23.
  • the bellows valve 292 has the transmission rod 293 which drives the valve body 291 in accordance with the telescopic motion of the bellows valve 292, in order to open and close the first communication path 28.
  • the pressure control valve device 29 comprises an electromagnetic coil 294 positioned in the cylinder head 22.
  • the pressure control valve device 29 further comprises a plunger 297 which is surrounded by the electromagnetic coil 294.
  • the plunger 297 is movably supported by cylinder head 22 to slide upwardly and downwardly of Fig. 3.
  • the plunger 297 has a transmission rod 295 which is for use in pushing the valve body 291. As shown in Fig. 3, the transmission rod 293 is opposite to the transmission rod 295 through the valve body 291.
  • the plunger 297 has a spring 296.
  • the plunger 297 is pushed upwardly by the spring force of the spring 296.
  • an electric power is supplied to the electromagnetic coil 294, an electromagnetic force is generated around the plunger 297.
  • the electromagnetic force makes the plunger 297 push downwardly of Fig. 3. therefore, the plunger 297 makes the transmission rod 295 selectively move upwardly and downwardly of Fig. 3 in accordance with the electromagnetic force of the electromagnetic coil 294 and the spring force of the spring 296.
  • valve body 291 is selectively moved upwardly and downwardly of Fig. 3 by a combination of the bellows valve 292, the plunger 297, the electromagnetic coil 294, and the spring 296. Therefore, the pressure control valve device 29 illustrated in Fig. 3 controls the valve body 291 in response to the pressure in the suction chamber 23 that is sensed by the bellows valve 292. It will be assumed that the bellows valve 292 operates at a prescribed suction pressure. The prescribed suction pressure will be varied on the basis of the electromagnetic force of the electromagnetic coil 294.
  • variable-displacement compressor of the wobble plate type in each of the first and the second embodiments, it is possible to apply this invention to another type variable-displacement compressor.

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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)
EP19980101411 1997-01-27 1998-01-27 Compresseur à capacité variable Expired - Lifetime EP0855506B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP12201/97 1997-01-27
JP1220197 1997-01-27
JP9012201A JPH10205443A (ja) 1997-01-27 1997-01-27 可変容量圧縮機

Publications (3)

Publication Number Publication Date
EP0855506A2 true EP0855506A2 (fr) 1998-07-29
EP0855506A3 EP0855506A3 (fr) 1999-01-07
EP0855506B1 EP0855506B1 (fr) 2001-11-14

Family

ID=11798799

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19980101411 Expired - Lifetime EP0855506B1 (fr) 1997-01-27 1998-01-27 Compresseur à capacité variable

Country Status (3)

Country Link
EP (1) EP0855506B1 (fr)
JP (1) JPH10205443A (fr)
DE (1) DE69802444T2 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0900937A3 (fr) * 1997-09-05 1999-10-13 Sanden Corporation Appareil et méthode pour la commande d'un appareil de déplacement de fluide avec mécanisme à déplacement variable
EP0900936A3 (fr) * 1997-09-05 1999-12-08 Sanden Corporation Compresseur à capacité variable sans entrée de réfrigérant dans la chambre de bielle
EP0997640A3 (fr) * 1998-10-30 2000-10-25 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur à capacité variable
US6257848B1 (en) 1998-08-24 2001-07-10 Sanden Corporation Compressor having a control valve in a suction passage thereof
US6474183B1 (en) 1999-03-11 2002-11-05 Sanden Corporation Variable-displacement inclined plate compressor
US6681587B2 (en) 2001-07-13 2004-01-27 Kabushiki Kaisha Toyota Jidoshokki Flow restricting structure in displacement controlling mechanism of variable displacement compressor
US7651321B2 (en) 2005-01-27 2010-01-26 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3933369B2 (ja) * 2000-04-04 2007-06-20 サンデン株式会社 ピストン式可変容量圧縮機
CN107110138A (zh) * 2014-12-18 2017-08-29 法雷奥日本株式会社 可变排量型压缩机

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0474549A (ja) 1990-07-16 1992-03-09 Iwata Air Compressor Mfg Co Ltd ２液混合スプレーガン

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62206277A (ja) * 1986-03-06 1987-09-10 Toyoda Autom Loom Works Ltd 揺動斜板型圧縮機におけるワツブルプレ−トの揺動傾斜角戻し機構
JPH0765567B2 (ja) * 1986-04-09 1995-07-19 株式会社豊田自動織機製作所 揺動斜板型圧縮機におけるクランク室圧力の制御機構
JPH0310389Y2 (fr) * 1987-02-25 1991-03-14
JP2567947B2 (ja) * 1989-06-16 1996-12-25 株式会社豊田自動織機製作所 可変容量圧縮機
JP3024315B2 (ja) * 1991-10-16 2000-03-21 株式会社豊田自動織機製作所 可変容量圧縮機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0474549A (ja) 1990-07-16 1992-03-09 Iwata Air Compressor Mfg Co Ltd ２液混合スプレーガン

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0900937A3 (fr) * 1997-09-05 1999-10-13 Sanden Corporation Appareil et méthode pour la commande d'un appareil de déplacement de fluide avec mécanisme à déplacement variable
EP0900936A3 (fr) * 1997-09-05 1999-12-08 Sanden Corporation Compresseur à capacité variable sans entrée de réfrigérant dans la chambre de bielle
US6074173A (en) * 1997-09-05 2000-06-13 Sanden Corporation Variable displacement compressor in which a liquid refrigerant can be prevented from flowing into a crank chamber
US6102670A (en) * 1997-09-05 2000-08-15 Sanden Corporation Apparatus and method for operating fluid displacement apparatus with variable displacement mechanism
US6257848B1 (en) 1998-08-24 2001-07-10 Sanden Corporation Compressor having a control valve in a suction passage thereof
EP0997640A3 (fr) * 1998-10-30 2000-10-25 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur à capacité variable
US6290468B1 (en) 1998-10-30 2001-09-18 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US6474183B1 (en) 1999-03-11 2002-11-05 Sanden Corporation Variable-displacement inclined plate compressor
US6681587B2 (en) 2001-07-13 2004-01-27 Kabushiki Kaisha Toyota Jidoshokki Flow restricting structure in displacement controlling mechanism of variable displacement compressor
US7651321B2 (en) 2005-01-27 2010-01-26 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor

Also Published As

Publication number Publication date
DE69802444T2 (de) 2002-08-01
EP0855506A3 (fr) 1999-01-07
DE69802444D1 (de) 2001-12-20
EP0855506B1 (fr) 2001-11-14
JPH10205443A (ja) 1998-08-04

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