EP0945617B1 - Displacement control valve for use in variable displacement compressor - Google Patents

Displacement control valve for use in variable displacement compressor Download PDF

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Publication number
EP0945617B1
EP0945617B1 EP19990105008 EP99105008A EP0945617B1 EP 0945617 B1 EP0945617 B1 EP 0945617B1 EP 19990105008 EP19990105008 EP 19990105008 EP 99105008 A EP99105008 A EP 99105008A EP 0945617 B1 EP0945617 B1 EP 0945617B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
chamber
passage
control valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19990105008
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0945617A2 (en
EP0945617A3 (en
Inventor
Kiyoshi C/O Sanden Corporation Terauchi
Yukihiko C/O Sanden Corporation Taguchi
Toshiyuki C/O Sanden Corporation Ogura
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 EP0945617A2 publication Critical patent/EP0945617A2/en
Publication of EP0945617A3 publication Critical patent/EP0945617A3/en
Application granted granted Critical
Publication of EP0945617B1 publication Critical patent/EP0945617B1/en
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
    • F04B2027/1822—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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a displacement control valve for use in a variable displacement compressor which is suitable for being used in an air conditioner of a vehicle, particularly of an automotive vehicle or the like.
  • variable displacement compressor is, for example, disclosed in USP No. 4,606,705.
  • the variable displacement compressor is provided with a displacement control valve for controlling a displacement.
  • the displacement control valve includes a bellows which senses a pressure within a suction chamber of the compressor and first and second valve mechanisms which adjusts an opening degree of a passage in an interlocking manner in accordance with the pressure of the suction chamber.
  • An electromagnetic actuator is connected to the bellows, and is structured such that an electromagnetic force acts on the first valve mechanism.
  • a pressure control point of the suction chamber is changed due to the pressure of the suction chamber even when an energizing amount of the electromagnetic actuator is fixed. That is, the pressure control point of the suction chamber is not definitely determined with respect to the energizing amount, so that a control method for obtaining an optimum discharge displacement becomes complex. Further, since a control for the suction chamber pressure has an upper limit, there is generated a case that a desired discharge displacement can not be maintained under a certain drive condition, so that a serious influence is given to a traveling performance of the vehicle.
  • a displacement control valve for use in a variable displacement compressor having a discharge chamber, a suction chamber, and a crank chamber.
  • a passage is provided between the crank chamber and the discharge chamber.
  • a valve mechanism serves for adjusting an opening in the passage in response to a pressure sensed by a pressure sensing member.
  • variable displacement compressor is provided as set forth in claim 8.
  • the illustrated displacement control valve corresponds to a structure used in the variable displacement compressor disclosed in USP No. 4,606,705, which includes a bellows 1 sensing a pressure of a suction chamber, a first valve mechanism 2 adjusting an opening degree of a passage extending from a crank chamber of a compressor to the suction chamber and a second valve mechanism 3 adjusting an opening degree of a passage extending from a discharge chamber of the compressor to the crank chamber.
  • the first and second valve mechanisms 2 and 3 are interlocked with each other and controlled to be opened and closed.
  • An electromagnetic actuator 4 is connected to the bellows 1, so that it is structured such that an electromagnetic force acts on the first valve mechanism 2. Accordingly, it is possible to change a pressure control point of the suction chamber in accordance with an energizing amount to the electromagnetic actuator 4.
  • the second valve mechanism 3 is structured such that the valve body thereof receives the pressure of the discharge chamber, the pressure control point of the suction chamber changes as shown by Pd1, Pd2 and Pd3 in Fig. 2 due to the pressure of the discharge chamber even when the energizing amount of the electromagnetic actuator 4 is fixed. That is, the pressure control point of the suction chamber is not definitely determined with respect to the energizing amount, so that there is a problem that a control method for obtaining an optimum discharge displacement becomes complex.
  • a control for the pressure of the suction chamber has an upper limit, so that, for example, it is impossible to control at the pressure of the suction chamber of 3.7 kg/cm 2 G or more.
  • the pressure of the suction chamber is frequently controlled near a state of 2 kg/cm 2 G.
  • the discharge displacement is controlled so as to maintain the pressure when the discharge displacement is reduced and the pressure of the suction chamber is increased to 3.7 kg/cm 2 G. Accordingly, in some drive conditions, there is generated the case that the minimum displacement can not maintained, so that a serious influence may be given to a traveling performance of the vehicle.
  • variable displacement compressor provided with a displacement control valve in accordance with a first embodiment of the present invention will be described below with reference to Fig. 3.
  • the shown compressor is used for a vehicle air conditioner and comprises a tubular casing 31, a front housing 32 closing one axial end of the casing 31, and a cylinder head 34 attached to the other axial end of the casing 31 via a valve plate assembly 33.
  • the casing 31, the front housing 32 and the cylinder head 34 are fixed together by means of bolts 35.
  • the casing 31 is integrally provided with a cylinder block 36 therein.
  • a shaft 37 axially extends at the center of the casing 31.
  • the shaft 37 is rotatably supported by the front housing 32 and the cylinder block 36.
  • a pulley 38 is rotatably supported on the front housing 32.
  • the pulley 38 is driven by an engine of the vehicle.
  • a ring-shaped armature 41 is supported on an outer end of the shaft 37 via a rubber member 39 so as to be movable axially.
  • the armature 41 confronts an axial end surface of the pulley 38 and is controlled to be attached to or detached from the pulley 38 by means of an electromagnetic attracting unit 42. Specifically, when the electromagnetic attracting unit 42 is energized, the armature 41 is attracted and attached to the pulley 38 by an electromagnetic force, so that the torque of the engine is transmitted to the shaft 37. On the other hand, when the energization to the electromagnetic attracting unit 42 is stopped, the armature 41 is detached from the pulley 38 by a restoring force of the rubber member 39, so that the torque of the engine is not transmitted to the shaft 37.
  • a crank chamber 43 is defined between the front housing 32 and the cylinder block 36.
  • a rotor 44 is fixed on the shaft 37.
  • a swash plate 46 is coupled to the rotor 44 via a hinge mechanism 45.
  • the hinge mechanism 45 renders variable an inclination of the swash plate 46 relative to an axis of the shaft 37.
  • the swash plate 46 rotates together with the rotor 44.
  • a plurality of pistons 47 engage with peripheral portions of the swash plate 46 via shoes, respectively.
  • the pistons 47 are received in corresponding cylinder bores 48 formed in the cylinder block 36 so as to be axially slidable.
  • each of the pistons 47 makes a reciprocating motion in the corresponding cylinder bore 48 with a stroke determined by an inclination of the swash plate 46.
  • the cylinder head 34 is formed with a suction chamber 51 along its peripheral portion and with a discharge chamber 52 at the center thereof. Between the suction chamber 51 and the discharge chamber 52 is connected a known refrigeration circuit.
  • the valve plate assembly 33 is provided with suction holes 53 and discharge holes 54 for establishing communication of the cylinder bores 48 with the suction chamber 51 and the discharge chamber 52, and with valve mechanism for those holes.
  • the compression displacement of the variable displacement compressor depends on the stroke of the pistons 47 determined by the inclination of the swash plate 46.
  • a displacement control valve 10 is further provided in a control valve chamber 55 formed in the cylinder head 34.
  • the suction chamber 51 is communicated with the crank chamber 43 through passages 59, 23a, and, 23b, and a particularly narrow passage 57, the discharge chamber 52 being communicated with the crank chamber 43 through passages 58, 10a, 10b, and 56.
  • a combination of the passages 59, 23a, 23b, and 57 is referred to as a first passage.
  • a combination of the passages 58, 10a, 10b, and 56 is referred to as a second passage.
  • the displacement control valve 10 is for adjusting the pressure in the crank chamber 43 so as to control the stroke of the pistons 47.
  • the displacement control valve includes a first valve mechanism, a second valve mechanism, and an electromagnetic coil mechanism, as described below.
  • the first valve mechanism includes a valve casing 21, a bellows 22 arranged within the valve casing 21, having a vacuumed inner portion, having a spring arranged and receiving the pressure of the crank chamber, a valve body 24 adhered to the bellows 22 and opening and closing a communication passage 23 between the crank chamber and the suction chamber, a fixed throttle 25 bypassing the valve body 24, a guide 26 supporting a lower end in the drawing of the bellows 22 and movably supported to the valve casing 21, a spring 27 urging the guide 26 upward in the drawing, and an adjusting screw 28 adjusting an expansion and contraction amount of the bellows 22 and constituting a part of the valve casing 21.
  • the passage 10a is communicated with the discharge chamber 52 through the passage 58 and referred to as a first portion of the second passage.
  • the passage 10b is communicated with the crank chamber 43 through the passage 56 and referred to as a second portion of the second passage.
  • the second valve mechanism comprises a valve seat 10c between the passages 10a and 10b and a second valve body 11 placed in the passage 10a in the vicinity of the valve seat 10c.
  • the second valve body 11 is movable in a predetermined direction, namely, an upward and downward direction.
  • the second valve mechanism further includes a transmission rod 29 having an end brought into contact with an upper end in the drawing of the first valve body 24 and movably supported to the valve casing 21.
  • the second valve body 11 is brought into contact with the other end of the transmission rod 29 and cooperated with the valve seat 10c to open and close the second passage with movement thereof in the predetermined direction in accordance with an expansion and contraction of the bellows 22.
  • the electromagnetic coil mechanism includes an electromagnetic coil 14 positioned above the second valve body 11.
  • the electromagnetic coil 14 generates an electromagnetic force for urging the second valve body 11 to a valve close direction via a plunger 12 and a transmission rod 13.
  • the electromagnetic coil mechanism is referred to as an external operation mechanism.
  • a side surface 11a of the second valve body 11 is movably supported to the valve casing21, and a gap between the side surface 11a and an inserting portion in the side of the valve casing 21 is set such as to be significantly narrow.
  • a surface 11c of the second valve body 11 in a side opposite to a contact surface 11b with the valve seat 10c is structured such as to receive the pressure of the crank chamber by a pressure introduction passage 15, adjusts a pressure receiving area of the pressure of the crank chamber in the side of the contact side 11b with the valve seat and a pressure receiving area of the pressure of the crank chamber of the opposite surface 11c, and removes the force of the pressure of the discharge chamber acting in an opening and closing direction of the second valve body 11.
  • the second valve body 11 has a first surface 11b facing the valve seat 10c in the predetermined direction and a second surface 11c opposite to the first surface 11b in the predetermined direction. Each of the first and the second surfaces 11b and 11c is inclined relative to the predetermined direction as shown in Fig. 5. Since the discharge pressure Pd is mutually negated on the first and the second surfaces 11b and 11c of the second valve body 11, an influence of the pressure of the discharge chamber is a little or can be lost.
  • the contact point below the second valve body 11 is preferably structured such that the pressure in the upper portion and the pressure from the lower portion to the upper portion are balanced, that is, in the drawing, a contract point and an operation point of the pressure in the upper portion are, of course, aligned on the same line.
  • a combination of the first and the second surface 11b and 11c serves as a pressure canceling arrangement which is of making the second valve body be canceled with influence of pressure of the second passage in the predetermined direction.
  • the discharge force affects, so that the pressure of the crank chamber is also adjusted by the back pressure (for example, the case that the valve seat is in a surface contact is considered).
  • the back pressure for example, the case that the valve seat is in a surface contact is considered.
  • the pressure of the crank chamber is employed, however, only the pressure of the suction chamber can be sufficient for keeping a balance.
  • the structure is made such that when the second valve body 11 is opened, the first valve body 24 is opened, and when the first valve body 24 moves to a closing direction, the second valve body 11 is opened, so that the opening degree of the valve is increased. Further, the opening degree of the fixed throttle 25 is set to be sufficiently smaller than the maximum opening degree of the second valve body 11.
  • the second valve body 11 can be closed and the first valve body 24 can be opened.
  • the second valve body 11 is closed, and the first valve body 24 is opened. Accordingly, since the pressure of the crank chamber is reduced to the same value as the pressure of the suction chamber, the compressor is maintained in the maximum displacement and the pressure of the suction chamber is gradually reduced.
  • the opening degrees of the first valve body 24 and the second valve body 11 are adjusted so that the pressure of the suction chamber becomes a predetermined value, so that the discharge displacement is controlled. Accordingly, as shown in Fig. 6, the control point of the pressure of the suction chamber is substantially determined in a definite manner by the current value.
  • the bellows 22 when making the current value 0 from the state, the bellows 22 is extended, the first valve body 24 is fully closed, and the second valve body 11 is fully opened, so that the pressure difference between the crank chamber and the suction chamber is significantly increased and moves to the minimum displacement in a moment. Therefore, even when the pressure of the suction chamber is increased and the bellows is contracted, the bellows 22 is urged by the spring 27 upward in the drawing, so that the first valve body 24 is closed and the second valve body 11 is maintained in an open valve state. Accordingly, in the case that the current value is 0, the minimum displacement is always in the minimum displacement.
  • the structure is made such as to adjust the pressure receiving area on the surface in the contact side with the valve seat of the valve body of the second valve mechanism and in the opposite side so as to substantially remove the pressure of the discharge chamber acting in the opening and closing direction of the valve body, a pressure control characteristic in the suction chamber can be obtained stably and without affected by the pressure of the discharge chamber. Since the crank chamber and the suction chamber are communicated with each other by the fixed throttle even when the valve body of the first valve mechanism is fully closed, the pressure difference between the crank chamber and the suction chamber does not become excessive at the minimum displacement, and a durability of the compressor is not deteriorated.
  • the pressure sensing member is shifted upward in the drawing by the spring member, the valve body of the first valve mechanism is closed and the valve body of the second valve mechanism is opened, so that the minimum displacement can be always maintained.
  • the valve body of the first valve mechanism is shifted upward in the drawing by the spring member so as to close the valve and the valve body of the second valve mechanism is opened, so that the minimum displacement can be always maintained.
  • the minimum displacement can be always maintained, so that a stable traveling of the automotive vehicle can be secured without giving an excessive load.
  • a displacement control valve in accordance with a second embodiment of the present invention will be described below with reference to Figs. 7A and 7B.
  • the same reference numerals are attached to the same elements, and an explanation thereof will be omitted.
  • the first valve body 24 is movably supported to a guide 26 fixed to the bellows 22.
  • a spring 27 is interposed between the first valve body 24 and the bellows 22 and urges the first valve body 24 in a closing direction.

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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)
EP19990105008 1998-03-27 1999-03-19 Displacement control valve for use in variable displacement compressor Expired - Lifetime EP0945617B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP10036698 1998-03-27
JP10036698A JP4149558B2 (ja) 1998-03-27 1998-03-27 可変容量圧縮機の容量制御弁

Publications (3)

Publication Number Publication Date
EP0945617A2 EP0945617A2 (en) 1999-09-29
EP0945617A3 EP0945617A3 (en) 2000-02-02
EP0945617B1 true EP0945617B1 (en) 2001-12-19

Family

ID=14272072

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19990105008 Expired - Lifetime EP0945617B1 (en) 1998-03-27 1999-03-19 Displacement control valve for use in variable displacement compressor

Country Status (3)

Country Link
EP (1) EP0945617B1 (ja)
JP (1) JP4149558B2 (ja)
DE (1) DE69900614T2 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9631612B2 (en) 2014-02-03 2017-04-25 Kabushiki Kaisha Toyota Jidoshokki Variable displacement type swash plate compressor

Families Citing this family (15)

* Cited by examiner, † Cited by third party
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
JP3928832B2 (ja) * 1998-08-10 2007-06-13 株式会社豊田自動織機 可変容量型圧縮機
JP3991556B2 (ja) * 1999-10-04 2007-10-17 株式会社豊田自動織機 容量可変型圧縮機の制御弁
JP2002332962A (ja) * 2001-05-10 2002-11-22 Toyota Industries Corp 容量可変型圧縮機の制御弁
JP4246975B2 (ja) 2002-02-04 2009-04-02 イーグル工業株式会社 容量制御弁
JP4316955B2 (ja) * 2003-08-11 2009-08-19 イーグル工業株式会社 容量制御弁
US7611335B2 (en) 2006-03-15 2009-11-03 Delphi Technologies, Inc. Two set-point pilot piston control valve
CN101365879B (zh) * 2006-03-29 2011-04-13 伊格尔工业股份有限公司 可变容量型压缩机用控制阀
JP5699259B2 (ja) * 2011-01-07 2015-04-08 株式会社テージーケー 可変容量圧縮機用制御弁
JP5665722B2 (ja) 2011-11-17 2015-02-04 株式会社豊田自動織機 容量制御弁
JP6103586B2 (ja) * 2013-03-27 2017-03-29 株式会社テージーケー 可変容量圧縮機用制御弁
JP6127994B2 (ja) 2014-01-30 2017-05-17 株式会社豊田自動織機 可変容量型斜板式圧縮機
JP7399950B2 (ja) 2019-04-03 2023-12-18 イーグル工業株式会社 容量制御弁
CN113661322B (zh) * 2019-04-03 2023-06-23 伊格尔工业股份有限公司 容量控制阀
US11988296B2 (en) 2019-04-24 2024-05-21 Eagle Industry Co., Ltd. Capacity control valve

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US4606705A (en) 1985-08-02 1986-08-19 General Motors Corporation Variable displacement compressor control valve arrangement
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
DE69200356T2 (de) * 1991-01-28 1995-02-16 Sanden Corp Schiefscheibenverdichter mit einer Vorrichtung zur Hubveränderung.
JP3178631B2 (ja) * 1993-01-11 2001-06-25 株式会社豊田自動織機製作所 可変容量型圧縮機用制御弁
JP3355002B2 (ja) * 1993-10-15 2002-12-09 株式会社豊田自動織機 可変容量型圧縮機用制御弁
JP3255008B2 (ja) * 1996-04-17 2002-02-12 株式会社豊田自動織機 可変容量圧縮機及びその制御方法

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9631612B2 (en) 2014-02-03 2017-04-25 Kabushiki Kaisha Toyota Jidoshokki Variable displacement type swash plate compressor

Also Published As

Publication number Publication date
JP4149558B2 (ja) 2008-09-10
DE69900614D1 (de) 2002-01-31
EP0945617A2 (en) 1999-09-29
DE69900614T2 (de) 2002-07-18
JPH11280660A (ja) 1999-10-15
EP0945617A3 (en) 2000-02-02

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