EP0489164A1 - Continuously variable capacity type swash plate compressor - Google Patents

Continuously variable capacity type swash plate compressor Download PDF

Info

Publication number
EP0489164A1
EP0489164A1 EP91910152A EP91910152A EP0489164A1 EP 0489164 A1 EP0489164 A1 EP 0489164A1 EP 91910152 A EP91910152 A EP 91910152A EP 91910152 A EP91910152 A EP 91910152A EP 0489164 A1 EP0489164 A1 EP 0489164A1
Authority
EP
European Patent Office
Prior art keywords
pressure
swash plate
valve
compressor
varying
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.)
Ceased
Application number
EP91910152A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0489164A4 (en
Inventor
Manabu Kabushiki Kaisha Toyoda Sugiura
Masafumi Kabushiki Kaisha Toyoda Ito
Kazuya Kabushiki Kaisha Toyoda Kimura
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.)
Toyota Industries Corp
Original Assignee
Toyoda Jidoshokki Seisakusho KK
Toyoda Automatic Loom Works 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 Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyoda Jidoshokki Seisakusho KK
Publication of EP0489164A4 publication Critical patent/EP0489164A4/en
Publication of EP0489164A1 publication Critical patent/EP0489164A1/en
Ceased legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • 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
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate

Definitions

  • the present invention relates to an improvement on a swash plate type continuously variable capacity compressor which employs a plurality of double headed pistons.
  • the swash plate type continuously variable capacity compressor includes a plurality of double headed pistons 53 which are accommodated in a plurality of bores 52 formed in a cylinder block 51, a driving shaft 54 which is disposed on an axial line being parallel with the bores 52, and a slider 55 which is disposed around the driving shaft 54 slidably.
  • a swash plate 57 is disposed, and it is engaged with the spherical supporting portion 55a at a corresponding spherical portion 57a thereof.
  • the swash plate 57 is engaged with the double headed pistons 53 by way of shoes 56 at the circumferential portions thereof.
  • a connecting portion 57b is projected from the swash plate 57, and it is provided with a guide pin 58.
  • the guide pin 58 is guided by a slot 54b which is drilled in a front shaft portion 54a of the driving shaft 54.
  • the swash plate 57 is made inclinable as the slider 55 slides on the driving shaft 54, and the center of the inclining movement of the swash plate 57 is adapted so that the position of the upper dead point of the double headed pistons 53 is invariable at the rear side.
  • the compressive reaction force of the double headed pistons 53 always acts as a moment "M” which woks in a direction reducing the inclination angle of the swash plate 57.
  • the moment "M” urges a plunger 60 by way of the slider 55 in the right direction of Figure 8.
  • a pressure control chamber 59 is formed between the plunger 60 and a rear housing 50.
  • a discharge pressure "Pd” and a suction pressure “Ps” are introduced selectively by a control valve 40 (See Figure 9.) which is described later.
  • the plunger 60 is also urged in the left direction of Figure 8.
  • the inclination angle of the swash plate 57 i.e., the discharge capacity of the compressor
  • the inclination angle of the swash plate 57 is defined by the equilibrium between these opposite urging forces which work by way of the plunger 60 and the slider 55.
  • FIG. 9 A general construction of the control valve 40 is illustrated in Figure 9.
  • a ball valve 43 is disposed, and it is brought into contact with a diaphragm 42.
  • the ball valve 43 is adapted to operate in accordance with the atmospheric pressure "Patm", the urging forces of opposing springs 44 and 45 and a pressure fluctuation in a pressure detection chamber 46.
  • the suction pressure "Ps” is introduced into the pressure detection chamber 46 which communicates with a swash plate chamber 61 (See Figure 8.) by way of a pressure detection pipe line "a."
  • a valve chamber 47 in which the ball valve 43 is accommodated always communicates with the above-described pressure control chamber 59 (See Figure 8.) by way of a supply pipe line "b.”
  • an upper chamber 48 is defined by a first valve seat 48a of the valve chamber 47, and the upper chamber 48 communicates with a discharge chamber 62 (See Figure 8.) by way of a high pressure pipe line "c.”
  • a lower chamber 49 is defined by a second valve seat 49a of the valve chamber 47, and the lower chamber 49 communicates with the swash plate chamber 61 by way of a low pressure pipe line "d" as the pressure detection chamber 46 communicates with the swash plate chamber 61.
  • the opening degree of the ball valve 43 within the control valve 40 is controlled by the expansion and contraction of the diaphragm 42 which operates in response to the suction pressure "Ps.”
  • the pressure control point of the diaphragm 43 which works as a pressure sensitive means is defined by the atmospheric pressure "Patm” and the spring constants of the opposing springs 44 and 45.
  • the inclination angle of the swash plate 57 namely the discharge capacity of the compressor, is controlled only by the suction pressure "Ps."
  • the above-described conventional compressor cannot satisfy the requirement.
  • a vehicle air-conditioning apparatus which includes the above-described conventional compressor are adjusted so as to carry out an air-conditioning operation which meets the summer time requirements.
  • the above-described conventional compressor cannot satisfy the requirement immediately because the conventional compressor does not carry out the capacity control until the suction pressure "Ps" varies. All in all, it can be hardly said that the conventional compressor is a satisfactory one in view of the driving feeling of the vehicle and in view of the air-conditioning function.
  • a swash plate type continuously variable capacity compressor comprises: a cylinder block including a plurality of bores which are adapted for accommodating a plurality of double headed pistons; a driving shaft disposed on an axial line which is parallel with said bores; a slider disposed around said driving shaft slidably; a swash plate disposed around said slider in an inclinable manner, engaging with said double headed pistons and including a guide pin which engages with a slot drilled in said driving shaft; a plunger holding said slider rotatably and adapted for varying an inclination angle of said swash plate by way of an axial displacement of said slider; and a control valve adapted for varying said inclination angle of said swash plate by way of said plunger and said slider by means of a pressure sensitive means which is adapted for responding to either a suction pressure or a discharge pressure and by which the suction pressure and the discharge pressure are selectively introduced into a pressure control chamber formed between said plunger and a housing, wherein said control valve
  • the swash plate type continuously variable capacity compressor features that it employs the control valve, which includes the variable urging means, instead of the conventional control valve which is employed by the conventional swash plate type continuously variable capacity compressor.
  • the variable urging means is adapted for varying the pressure control point of the pressure sensitive means.
  • the pressure control point means a threshold point of the pressure sensitive means at which the pressure sensitive means is put into equilibrium with a predetermined suction pressure.
  • the present control valve includes a pressure introduction switching valve which is adapted for selectively introducing the discharge pressure and the suction pressure into the pressure control chamber, the variable urging means which is adapted for varying the pressure control point, and the pressure sensitive means which is adapted for driving the pressure introduction switching valve.
  • the pressure introduction switching valve is a component in which a movable valve member moves between valve openings which communicate with the suction pressure pipe line and the discharge pressure pipe line respectively in order to adjust the opening degrees of the both valve openings, whereby the suction pressure, the discharge pressure and an intermediate pressure of the suction pressure and the discharge pressure can be selectively introduced into the pressure control chamber.
  • a movable valve member moves between valve openings which communicate with the suction pressure pipe line and the discharge pressure pipe line respectively in order to adjust the opening degrees of the both valve openings, whereby the suction pressure, the discharge pressure and an intermediate pressure of the suction pressure and the discharge pressure can be selectively introduced into the pressure control chamber.
  • Preferred Embodiments of the present invention hereinafter described employ a ball valve as the movable valve member.
  • the present invention is not limited thereto.
  • the pressure sensitive means includes a pressure sensitive unit and the variable urging means.
  • the sensitive unit responds to either one of the suction pressure fluctuation and the discharge pressure fluctuation, and it drives the pressure introduction switching valve reciprocally.
  • the variable urging means varies the pressure control point.
  • a mechanism can be employed, in which the suction pressure or the discharge pressure acts on either one of the pressure chambers disposed on both sides of a diaphragm and which includes an urging means, such as a spring or the like.
  • the urging means opposes the suction pressure or the discharge pressure which acts on the either one of the pressure chambers.
  • the thus constructed sensitive means transmits the movements of the diaphragm to the movable valve member of the pressure introduction switching valve, thereby driving the movable valve member.
  • a pressure chamber On another side with respect to the diaphragm, there is formed a pressure chamber to which a predetermined pressure, such as an atmospheric pressure, vacuum or the like, is applied.
  • a predetermined pressure such as an atmospheric pressure, vacuum or the like
  • variable urging means urges the movable valve member with a variable urging force in a direction or in an opposing direction thereto while it assists the action of the pressure sensitive unit of the pressure sensitive means.
  • the variable urging means it is possible to employ a mechanical urging means which is controlled electrically, a pressurized fluid or the like. Since the discharge capacity of the present compressor is controlled in accordance with the seasonal changes and the external environmental changes, the variable urging means can be controlled by a detection and command signal which is derived from an outlet temperature of an evaporator, an external temperature resulting from a solar radiation or the like.
  • variable urging means can be controlled by a detection and control signal which is derived from an opening degree of an accelerator pedal (i.e., an opening degree of a throttle valve), a number of engine revolutions, a vehicle speed, or the like.
  • the pressure control point of the pressure sensitive member is varied in accordance with the quick acceleration of a vehicle, the seasonal changes, the external environmental changes or the like.
  • the present compressor can respond to the quick acceleration of a vehicle or the like, and accordingly it can control its discharge capacity immediately in accordance therewith. For instance, the discharge capacity of the present compressor can be dropped sharply in order to avoid the deterioration of the driving feeling during the quick acceleration of a vehicle.
  • Figures 1 through 4 relate to a compressor of a First Preferred Embodiment according to the present invention, in which:
  • the compressor of the First Preferred Embodiment includes a cylinder block 1 which is constituted by connecting a pair of a front block 1a and a rear block 1b each other, a swash plate chamber 2 which is formed in the cylinder block 1 at a middle portion therein, and a pair of a front housing 3 and a rear housing 4 which are connected respectively to a front end surface of the front block 1a and a rear end surface of the rear block 1b.
  • a plurality of pairs of bores 5a and 5b are formed at opposing positions on the front and rear sides of the swash plate chamber 2, and a plurality of double headed pistons 6 are accommodated in both of the bores 5a and 5b in a manner being movable back and forth.
  • a driving shaft 7 is supported rotatably on an axial line being parallel with the bores 5a and 5b.
  • the driving shaft 7 includes a front axis portion 7a, a rear axis portion 7b, and a flat connecting portion 7c formed between the front and rear axial portions 7a and 7b. Further, a slot 7d is drilled in the connecting portion 7c.
  • a cover pipe 8 is disposed in a manner being movable along the axial center line of the driving shaft 7.
  • the driving shaft 7 is supported by the front block 1a at the front axial portion 7a by way of a bearing 9a, and it is engaged with a slider 10 at the rear axial portion 7b.
  • the slider 10 is supported rotatably by the cover pipe 8 by way of a bearing 9b.
  • the swash plate 12 includes a main body portion 12a, and a rotary force transmitting portion 12b.
  • the main body portion 12a transmits the rotary and swing movement to the double headed pistons 6 by way of shoes 13, and it moves the double headed pistons 6 back and forth.
  • the rotary force transmitting portion 12b projects forward from the main body portion 12a, and it is connected to the slot 7d of the driving shaft 7 by way of a guide pin 15.
  • the guide pin 15 is guided by the slot 7d in accordance with the axial displacement of the slider 10 which moves together with the cover pipe 8, and accordingly the inclination angle of the swash plate 12 is varied in accordance therewith.
  • the center of the inclining movement of the swash plate 12 is adapted so that the position of the upper dead point of the double headed pistons 6 is invariable at the rear side.
  • valve plates 20 and 21 are interposed respectively.
  • a suction chamber 22 and a discharge chamber 24 In the front housing 3, there are formed a suction chamber 22 and a discharge chamber 24.
  • a suction chamber 23 and a discharge chamber 25 In the rear housing 4, there are formed a suction chamber 23 and a discharge chamber 25.
  • the discharge chambers 24 and 25 are connected to an external refrigerating circuit by way of a discharge port (not shown).
  • the front suction chamber 22 communicates with the swash plate chamber 2 by way of a front suction passage 26, and it further communicates with a front compression chamber by way of a suction valve mechanism (not shown) which is provided in the valve plate 20.
  • the front discharge chamber 24 communicates with the front compression chamber by way of a discharge valve mechanism (not shown).
  • the rear suction chamber 23 communicates with the swash plate chamber 2 by way of a rear suction passage 27, and it further communicates with a rear compression chamber by way of a similar suction valve mechanism (not shown) which is provided in the valve plate 21.
  • the rear discharge chamber 25 communicates with the rear compression chamber by way of a discharge valve mechanism (not shown).
  • a plunger 33 is disposed slidably in an axial direction while it is brought into contact with a sleeve portion 8a of the cover pipe 8. Between the plunger 33 and the rear housing 4, a pressure control chamber 32 is formed. Into the pressure control chamber 32, an actuating pressure "Pc" is supplied by a control valve 70 illustrated in Figure 2.
  • the control valve 70 mainly includes a valve main body 71, and a rod 80 which is disposed in the valve main body 71. Further, a ball valve 73 is fixed at an end of the rod 80, a diaphragm 72 is fixed at a substantially middle portion thereof. As a result, and a movable iron core 81 is fixed at another end thereof, and accordingly the ball valve 73 and the movable iron core 81 are pressed by opposing springs 74 and 75.
  • a valve chamber 77 of the control valve 70 accommodates the ball valve 73, and it always communicates with the above-described pressure control chamber 32 (See Figure 1.) by way of a supply pipe line "b." Further, an upper chamber 78 which is defined by a first valve seat 78a of the valve chamber 77 communicates with the rear discharge chamber 25 (See Figure 1.) by way of a high pressure pipe line "c," and a lower chamber 79 which is defined by a second valve seat 79a of the valve chamber 77 communicates with the swash plate chamber 2 (See Figure 1.) by way of a low pressure pressure pipe line "d.”
  • the portion which includes the ball valve 73 constitutes the pressure introduction switching valve according to the present invention.
  • a first pressure detection chamber 76 is defined by the diaphragm 72, and it is disposed on the side of the ball valve 73.
  • the first pressure detection chamber 76 communicates with the swash plate chamber 2 by way of a pressure detection pipe line "a."
  • a suction pressure "Ps” is introduced into the first pressure detection chamber 76.
  • a second pressure detection chamber 82 is defined by the diaphragm 72, and it is disposed on the side of the movable iron core 81. Into the second pressure detection chamber 82, an atmospheric pressure "Patm" is introduced by way of an opening 83.
  • an electromagnet 85 is provided integrally with the valve main body 71 on the side of the second pressure detection chamber 82 with respect to the movable iron core 81 (i.e., on a lower side of the valve main body 71 as illustrated in Figure 2).
  • the electromagnet 85 includes a fixed iron core 84, and it is connected to a control means 86.
  • the control means 86 includes a micro-computer to which a potentiometer (not shown) which is adapted for detecting an opening degree of an acceleration pedal (i.e., an opening degree of a throttle valve). Hence, an opening degree of an acceleration pedal is detected by the potentiometer, and accordingly a predetermined value of an electric current which associates with the detected opening degree of the acceleration pedal is applied to the electromagnet 85.
  • the part of the control valve 70 which includes the springs 74 and 75, the diaphragm 72 and the first pressure detection chamber 76 constitutes a major part of the pressure sensitive unit according to the present invention.
  • the actuating pressure "Pc” which is supplied to the pressure control chamber 32 is transmitted to the swash plate 12 by way of the plunger 33, the cover pipe 8 and the slider 10. Accordingly, the actuating pressure "Pc” opposes the moment "M” which results from the compression reaction force and which works in the direction always reducing the inclination angle of the swash plate 12.
  • the inclination angle of the swash plate 12 i.e., the discharge capacity of the present compressor, is defined by the equilibrium between the both of the forces.
  • the swash plate 7 is rotated together with the driving shaft 7 integrally and is swung at the same time. Accordingly, the double headed pistons 6b are moved by way of the shoes 13 reciprocally in the bores 5a and 5b. As the double headed pistons 6 are moved reciprocally, the return refrigerant gas which is introduced by way of an inlet pipe line is entered in the swash plate chamber 2 through an inlet portion. Then, the refrigerant gas is introduced into each of the front and rear suction chambers 22 and 23 by way of the front suction passage 26 and the rear suction passage 27 respectively.
  • the refrigerant gas is suctioned into the front and rear compression chambers, and accordingly it is subjected to a compression action. Then, the refrigerant gas which is discharged from the front and rear compression chambers to the discharge chambers 24 and 25 by way of the discharge valve mechanisms (not shown) is delivered out to an external refrigerant gas circuit by way of a discharge pipe line.
  • the diaphragm 72 is operated in the control valve 70 illustrated in Figure 2 as follows. Namely, the diaphragm 72 is turned reversively upward so as to lift the ball valve 73 off the second seat 79a by the pressure drop in the first pressure detection chamber 76 which has been in equilibrium with the urging force of the spring 75. Then, the diaphragm 72 is operated in this way until equilibrium with the suction pressure "Ps" is attained.
  • a set suction pressure "Pso'" which is greater than the "Pso” is determined by a value of an electric current which depends on the opening degree of the acceleration pedal at the moment.
  • the set suction pressure "Pso'” is adapted for keeping the diaphragm 72 in equilibrium. With the set suction pressure "Pso',” the control operation of the suction pressure "Ps" which is to be introduced into the pressure detection chamber 76 is resumed as follows.
  • a spring constant of the spring 75 is enhanced substantially in accordance with the increment in the electric current value, the increment in the opening degree of the acceleration pedal or the increment in the speed of the vehicle, and consequently the set suction pressure "Pso" is varied to a higher pressure side.
  • the value of the electric current to be applied to the electromagnet 85 is in a direct proportion to the set suction pressure "Pso" as illustrated in Figure 4.
  • the control valve 70 is controlled by detecting the opening degree of the acceleration pedal in order to control the discharge capacity in accordance with the various speeds of the vehicle.
  • the various speeds of the vehicle include the quick acceleration of the vehicle as well.
  • it is also effective to detect a number of engine revolutions or to detect a vehicle speed directly.
  • it is also possible to carry out such a control by controlling the control vale 70 in accordance with the values which are derived by detecting an outlet temperature of an evaporator, a solar radiation, an external temperature, or the like.
  • a control valve 170 can include a fixed iron core 184 of an electromagnet 185 which is disposed on an opposite side of a movable iron core 181 with respect to a second pressure detection chamber 82 (i.e., on a lower side of the movable iron core 181 with respect to the second pressure detection chamber 82 in Figure 5).
  • the fixed iron core 184 can be disposed on the opposite side with respect to the side where the fixed iron core 84 of Figure 2 is disposed.
  • the spring constant of a spring 175 is reduced substantially, and accordingly the value of the electric current to be applied to the electromagnet 185 is in a negative proportion to the set suction pressure "Pso" as illustrated in Figure 6.
  • the set suction pressure "Pso" is varied to a lower pressure side in accordance with the increment of the electric current value.
  • a control valve 270 is provided with a servomotor 281 and a nut 283.
  • the servomotor 281 is controlled by a control means.
  • a worm 282 is fixed on a rotary shaft of the servomotor 281, and it is meshed with the nut 283 which is made slidable by a valve main body 71 but which is inhibited from rotating by the valve main body 71.
  • a spring 275 is provided between an upper surface of the nut 283 and a lower surface of a diaphragm 72.
  • the servomotor 281 rotates its rotary shaft in accordance with pulses which are output by the control means, and accordingly the nut 283 is pushed up by way of the worm 282, thereby enabling to vary the spring constant of the spring 275 substantially.
  • the discharge capacity of the present compressor can be controlled in accordance with the pulses.
  • an electromagnet or a servomotor is employed as a mechanical urging means which is controlled electrically.
  • an electromagnetic valve though it is not illustrated herein, a fluid pressure can be utilized to carry out the same objective.
  • a pressure control point of a pressure sensitive member is varied by a variable urging means which applies a variable load to the pressure sensitive member, it is possible to not only carry out a discharge capacity control of a compressor steadily but also a discharge capacity control thereof whenever it is required in accordance with the present invention. Therefore, when the compressor of the present invention is employed in a vehicle air-conditioning apparatus, a favorable acceleration feeling can be obtained, and at the same time an air-conditioning can be carried out in accordance with the seasonal changes, the external environmental changes, or the like. Thus, the compressor of the present invention is fully satisfactory in view of the feeling of driving as well as the function of the air-conditioning.

Landscapes

  • 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)
EP91910152A 1990-06-04 1991-05-31 Continuously variable capacity type swash plate compressor Ceased EP0489164A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP58899/90U 1990-06-04
JP1990058899U JPH0417183U (enrdf_load_stackoverflow) 1990-06-04 1990-06-04

Publications (2)

Publication Number Publication Date
EP0489164A4 EP0489164A4 (en) 1992-04-21
EP0489164A1 true EP0489164A1 (en) 1992-06-10

Family

ID=13097651

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91910152A Ceased EP0489164A1 (en) 1990-06-04 1991-05-31 Continuously variable capacity type swash plate compressor

Country Status (4)

Country Link
EP (1) EP0489164A1 (enrdf_load_stackoverflow)
JP (1) JPH0417183U (enrdf_load_stackoverflow)
KR (1) KR920702467A (enrdf_load_stackoverflow)
WO (1) WO1991019095A1 (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0857874A1 (en) * 1997-02-06 1998-08-12 Sanden Corporation Compressor
EP0798461A3 (en) * 1996-03-29 1998-10-21 Sanden Corporation Refrigerant circuit with fluid flow control mechanism
EP1363023A3 (en) * 2002-05-13 2006-10-04 TGK CO., Ltd. Capacity control valve for variable displacement compressor
DE10135727B4 (de) 2001-07-21 2019-07-04 Volkswagen Ag Regelventil gespeist mit Wechselspannung und Taumelscheibenkompressor mit diesem Regelventil

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0631614B2 (ja) * 1986-04-17 1994-04-27 株式会社豊田自動織機製作所 可変容量圧縮機
US4886423A (en) * 1986-09-02 1989-12-12 Nippon Soken, Inc. Variable displacement swash-plate type compressor
JPH01219363A (ja) * 1988-02-26 1989-09-01 Nippon Soken Inc 可変容量式斜板型圧縮機
JPH01144483U (enrdf_load_stackoverflow) * 1988-03-29 1989-10-04
JPH085310B2 (ja) * 1989-04-29 1996-01-24 日産自動車株式会社 車両用空調装置
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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0798461A3 (en) * 1996-03-29 1998-10-21 Sanden Corporation Refrigerant circuit with fluid flow control mechanism
EP0857874A1 (en) * 1997-02-06 1998-08-12 Sanden Corporation Compressor
DE10135727B4 (de) 2001-07-21 2019-07-04 Volkswagen Ag Regelventil gespeist mit Wechselspannung und Taumelscheibenkompressor mit diesem Regelventil
EP1363023A3 (en) * 2002-05-13 2006-10-04 TGK CO., Ltd. Capacity control valve for variable displacement compressor

Also Published As

Publication number Publication date
KR920702467A (ko) 1992-09-04
JPH0417183U (enrdf_load_stackoverflow) 1992-02-13
EP0489164A4 (en) 1992-04-21
WO1991019095A1 (fr) 1991-12-12

Similar Documents

Publication Publication Date Title
US4730986A (en) Variable displacement wobble plate type compressor with wobble angle control valve
US4526516A (en) Variable capacity wobble plate compressor capable of controlling angularity of wobble plate with high responsiveness
US5865604A (en) Displacement controlling structure for clutchless variable displacement compressor
US6361283B1 (en) Displacement control valve
US5145326A (en) Variable capacity wobble plate type compressor with capacity regulating valve
EP0985823B1 (en) Control valve for a variable displacement compressor
JP3789023B2 (ja) 電磁制御弁
EP1039129A2 (en) Device and method for controlling displacement of variable displacement compressor
US4729718A (en) Wobble plate type compressor
JPH02115577A (ja) 容量可変形揺動式圧縮機
EP1046818B1 (en) Capacity controller of a compressor with variable capacity
EP1024286A2 (en) Control valve for variable displacement compressor
US6425254B1 (en) Control device for variable displacement compressor
US4730987A (en) Variable delivery compressor
JP2003049782A (ja) 圧縮機の容量制御装置
JP3750397B2 (ja) 可変容量型圧縮機用の容量制御弁
EP0489164A1 (en) Continuously variable capacity type swash plate compressor
US6321545B1 (en) Control apparatus for variable displacement type compressor
JPH01190972A (ja) 可変容量式斜板型圧縮機
US6164926A (en) Variable displacement compressor
EP0947695B1 (en) Control valve for a variable displacement swash plate compressor
JP2000291542A (ja) 容量可変型圧縮機の制御弁
EP1070845A1 (en) Crank pressure control mechanism of variable displacement compressor
JP2002021722A (ja) ピストン式容量可変型圧縮機用容量制御弁
JPH03199677A (ja) 可変容量式斜板型圧縮機

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19920203

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 19921015

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

Free format text: STATUS: THE APPLICATION HAS BEEN REFUSED

18R Application refused

Effective date: 19930715