EP0907021A2 - Ventil zur Hubregelung zur Verwendung in einem Kompressor mit veränderlicher Fördermenge - Google Patents

Ventil zur Hubregelung zur Verwendung in einem Kompressor mit veränderlicher Fördermenge Download PDF

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Publication number
EP0907021A2
EP0907021A2 EP98118560A EP98118560A EP0907021A2 EP 0907021 A2 EP0907021 A2 EP 0907021A2 EP 98118560 A EP98118560 A EP 98118560A EP 98118560 A EP98118560 A EP 98118560A EP 0907021 A2 EP0907021 A2 EP 0907021A2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
communication passage
displacement control
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.)
Granted
Application number
EP98118560A
Other languages
English (en)
French (fr)
Other versions
EP0907021A3 (de
EP0907021B1 (de
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 EP0907021A2 publication Critical patent/EP0907021A2/de
Publication of EP0907021A3 publication Critical patent/EP0907021A3/de
Application granted granted Critical
Publication of EP0907021B1 publication Critical patent/EP0907021B1/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 displacement control valve for use in a variable displacement compressor which is included in, for example, a vehicle air conditioner.
  • variable displacement compressor there has been a type having a piston.
  • the compressor of the type comprises a crank chamber, a suction chamber, and a discharge chamber.
  • the piston has a piston stroke controlled in response to the pressure in the crank chamber. Therefore, the compressor has a displacement which is variable and determined in accordance with the piston stroke.
  • a displacement control valve is assembled to the variable displacement compressor to control the piston stroke.
  • Various displacement control valves have been known in the art.
  • the shown displacement control valve monitors the pressure in the suction chamber by means of a bellows 1 and opens/closes a ball valve 2 depending on the monitored suction chamber pressure so as to adjust the amount of gas introduced into the crank chamber from the discharge chamber.
  • This is a bellows valve structure of a so-called internal control type.
  • an electromagnetic actuator 3 is further disposed over the ball valve 2 so that an electromagnetic force is exerted on the ball valve 2.
  • the operation point of the bellows valve i.e. the pressure control point of the suction chamber, can be changed according to the current amount supplied to the electromagnetic actuator 3.
  • the suction chamber pressure control point changes, as shown in Fig. 8, depending on discharge chamber pressures Pd1, Pd2, Pd3, ... even if the current amount fed to the electromagnetic actuator 3 is constant. Accordingly, the suction chamber pressure control point can not be determined univocally relative to the current amount fed to the electromagnetic actuator 3, so that a control method becomes complicated for optimally controlling the discharge displacement of the compressor.
  • suction chamber pressure can not be controlled over 3.7kg/cm 2 G.
  • the pressure in the suction chamber is controlled across 2kg/cm 2 G so that no problem is raised.
  • the discharge displacement may be reduced for enhancing the acceleration performance.
  • the discharge displacement is reduced while the pressure in the suction chamber increases.
  • the pressure in the suction chamber increases up to 3.7kg/cm 2 G, the discharge displacement is controlled to keep this pressure. Accordingly, depending on the vehicle operating condition, the required minimum displacement can not be achieved to given a serious influence onto the vehicle running performance.
  • a displacement control valve to which the present invention is applicable is for use in a variable displacement compressor comprising a suction chamber, a crank chamber, and a discharge chamber.
  • the displacement control valve comprises a valve casing defining a communication passage for communicating the discharge chamber with the crank chamber to conduct gas from the discharge chamber to the crank chamber, a valve member placed in the communication passage and movable along the communication passage in a predetermined direction for adjusting a substantial opening degree of the communication passage, and moving means for moving the valve member in the predetermined direction.
  • the valve member has a first and a second surface opposite to each other in the predetermine direction.
  • the displacement control valve is characterized by further comprising pressure applying means for applying gas pressure to the first and the second surfaces in common in spite of adjusting the substantial opening degree.
  • variable displacement compressor including a displacement control valve according to a first embodiment of the present invention.
  • 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 mechanisms for those holes.
  • 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 control valve chamber 55 communicates with the crank chamber 43, the suction chamber 51 and the discharge chamber 52 via passages 56, 57 and 58, respectively. Further, the suction chamber 51 communicates with the crank chamber 43 via a narrow passage 59.
  • the displacement control valve 10 adjusts the pressure in the crank chamber 43 so as to control the stroke of the pistons 47.
  • the displacement control valve 10 comprises a valve casing 11 and a bellows 12 disposed in the valve casing 11.
  • the inside of the bellows 12 is under vacuum and provided with a spring.
  • the displacement control valve 10 further comprises a guide 13 receiving a lower end (in the figures) of the bellows 12 and disposed in a cavity of the valve casing 11 so as to be movable, a spring 14 for biasing the guide 13 upward (in the figures), an adjusting screw 15 forming a part of the valve casing 11 and adjusting the expansion/ contraction amount of the bellows 12, a transfer rod 16 engaging at its one end with an upper end (in the figures) of the bellows 12 and supported by the valve casing 11 so as to be movable, a valve member 18 engaging with the other end of the transfer rod 16 so as to open/close a communication passage 17 between the discharge chamber 52 and the crank chamber 43 depending on the expansion/contraction of the bellows 12, and an electromagnetic coil 21 for generating an electromagnetic force urging the valve member 18 in a valve closing direction via a plunger 19 and a transfer rod 20.
  • a combination of the electromagnetic coil 21, the plunger 19 and the transfer rod 20 is referred to as an externally biasing mechanism.
  • the communication passage 17 comprises an inlet portion 17a communicated with the discharge chamber 52 through the passage 58, a plurality of outlet portions 17b communicated with the crank chamber 43 through the passage 56, and an intermediate portion 17c between the inlet portion 17a and the outlet portions 17b.
  • the intermediate portion 17c is formed with a valve seat 17d radially extended.
  • the valve member 18 has a first surface 18a facing the valve seat 17d and a second surface 18b opposite to the first surface 18a.
  • first surface 18a rests on the valve seat 17d
  • second surface 18b is arranged to receive the pressure of the crank chamber 43 via a pressure introducing passage 22 which is made to the valve casing 11.
  • Crank chamber pressure receiving areas of the first surface and the second surfaces 18a and 18b are set equal to each other when the first surface 18a of the valve member 18 rests on the valve seat.
  • a circumference surface 18c of the valve member 18 is supported by the valve casing 11 so as to be movable with a gap therebetween set to be minimum.
  • the valve casing 11 has a plurality of lateral holes 11a.
  • the adjusting screw 15 has a through hole 15a.
  • Each of the lateral holes 11a and the through hole 15a communicates the cavity of the valve casing 11 with the suction chamber 51 through the passage 57 and the control valve chamber 55. Therefore, the cavity of the valve casing 11 is subjected to the pressure of the suction chamber 51.
  • the biasing force of the spring 14 is set to be small, for example, smaller than an electromagnetic force generated by a current value i0(A) supplied to the electromagnetic coil 21.
  • the valve member 18 can be closed in a current region of i0(A) or greater.
  • the bellows 12 As the pressure in the suction chamber 51 is lowered, the bellows 12 is expanded to cause a lower end (in the figures) of the guide 13 to abut the adjusting screw 15, so that a function of the spring 14 is lost. At this time, the pressure in the crank chamber 43 applied to the valve member 18 is canceled at the sides of the first and the second surfaces 18a and 18b, and the pressure in the discharge chamber 52 does not work in an axial direction of the valve member 18. Accordingly, the valve member 18 is open/close controlled depending on the electromagnetic force and the pressure in the suction chamber 51 applied to the bellows 12. Specifically, when the pressure in the suction chamber 51 is lowered to 2kg/cm 2 G, the bellows 12 is expanded to move the valve member 18 in a valve opening direction.
  • the gas in the discharge chamber 52 is introduced into the crank chamber 43 to increase a pressure differential between the crank chamber 43 and the suction chamber 51, so that the discharge displacement is reduced.
  • the bellows 12 is contracted to move the valve member 18 in the valve closing direction. Accordingly, the pressure in the crank chamber 43 is lowered to reduce a pressure differential between the crank chamber 43 and the suction chamber 51, so that the discharge displacement increases.
  • the opening degree of the valve member 18 is adjusted to converge the pressure in the suction chamber 51 to a given value, so that the discharge displacement is controlled.
  • the pressure control point of the suction chamber 51 is univocally determined by a value of current supplied to the electromagnetic coil 21. If the current value is set to be zero in this state, the bellows 12 is expanded to cause the valve member 18 to be fully open.
  • the minimum displacement is realized. Even if this increases the pressure in the suction chamber 51 up to greater than 3.5kg/cm 2 G in Fig. 3 to contract the bellows 12, since the valve member 18 is urged upward (in the figures) by the spring 14 to be constantly opened, the compressor is kept at the minimum displacement.
  • Fig. 4 the description will be directed to a displacement control valve according to a second embodiment of the present invention. Similar parts are designated by like reference numerals.
  • the pressure introducing passage 22 is made to penetrate the valve member 18 in the upward and downward direction of the figure.
  • Fig. 5 the description will be directed to a displacement control valve according to a third embodiment of the present invention. Similar parts are designated by like reference numerals.
  • the valve member 18 is slidably fitted in the intermediate portion 17c of the communication passage 17.
  • the inlet portion 17a of the communication passage 17 is opened or closed in response to movement of the valve member 18 in the upward and downward direction in the figure.
  • Fig. 6 the description will be directed to a displacement control valve according to a fourth embodiment of the present invention. Similar parts are designated by like reference numerals. Also in the displacement control valve, the pressure introducing passage 22 is made to penetrate the valve member 18 in the upward and down ward direction of the figure.
  • the bellows may expands/contracts in response to a pressure in at least one of the suction chamber and the crank chamber.

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)
EP19980118560 1997-10-03 1998-10-01 Ventil zur Hubregelung zur Verwendung in einem Kompressor mit veränderlicher Fördermenge Expired - Lifetime EP0907021B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP27151697A JP3754193B2 (ja) 1997-10-03 1997-10-03 可変容量圧縮機の容量制御弁
JP27151697 1997-10-03
JP271516/97 1997-10-03

Publications (3)

Publication Number Publication Date
EP0907021A2 true EP0907021A2 (de) 1999-04-07
EP0907021A3 EP0907021A3 (de) 1999-09-08
EP0907021B1 EP0907021B1 (de) 2002-02-06

Family

ID=17501165

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19980118560 Expired - Lifetime EP0907021B1 (de) 1997-10-03 1998-10-01 Ventil zur Hubregelung zur Verwendung in einem Kompressor mit veränderlicher Fördermenge

Country Status (3)

Country Link
EP (1) EP0907021B1 (de)
JP (1) JP3754193B2 (de)
DE (1) DE69803732T2 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0965754A3 (de) * 1998-06-18 2000-02-02 Sanden Corporation Ventil zur Hubregelung zur Verwendung in einem Kompressor mit veränderlicher Verdrängung
DE10014080C2 (de) * 1999-03-26 2002-06-13 Sanden Corp Verdrängungssteuerventil und Kompressor variabler Verdrängung, der das Verdrängungssteuerventil verwendet
EP2042732A1 (de) * 2006-07-19 2009-04-01 Sanden Corporation Leistungsregelungsventil eines verdichters mit variabler leistung

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4118414B2 (ja) 1998-10-29 2008-07-16 サンデン株式会社 可変容量圧縮機の容量制御弁の制御回路
JP4118587B2 (ja) 2002-04-09 2008-07-16 サンデン株式会社 可変容量圧縮機
JP4162419B2 (ja) 2002-04-09 2008-10-08 サンデン株式会社 可変容量圧縮機
JP4861900B2 (ja) 2007-02-09 2012-01-25 サンデン株式会社 可変容量圧縮機の容量制御システム
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
JP5075682B2 (ja) 2008-03-05 2012-11-21 サンデン株式会社 可変容量圧縮機の容量制御システム
JP4930440B2 (ja) * 2008-04-09 2012-05-16 株式会社デンソー 冷凍サイクル装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5063829A (en) * 1989-08-09 1991-11-12 Hitachi, Ltd. Variable displacement swash plate type compressor
EP0498552A1 (de) * 1991-01-28 1992-08-12 Sanden Corporation Schiefscheibenverdichter mit einer Vorrichtung zur Hubveränderung
US5145326A (en) * 1989-06-16 1992-09-08 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity wobble plate type compressor with capacity regulating valve
WO1994016225A1 (en) * 1993-01-11 1994-07-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control valve for a variable displacement refrigerant compressor
US5531572A (en) * 1993-10-15 1996-07-02 Kabushiki Kaisha Toyoda Jidoshokki Seisakushi Capacity control valve for a variable capacity refrigerant compressor
DE19716089A1 (de) * 1996-04-17 1997-11-06 Toyoda Automatic Loom Works Verdrängungsvariabler Kompressor und Verfahren für dessen Steuerung
EP0854288A2 (de) * 1997-01-21 1998-07-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Regelventil für einen Verdichter mit veränderlicher Förderleistung und Verfahren zur Herstellung

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5145326A (en) * 1989-06-16 1992-09-08 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity wobble plate type compressor with capacity regulating valve
US5063829A (en) * 1989-08-09 1991-11-12 Hitachi, Ltd. Variable displacement swash plate type compressor
EP0498552A1 (de) * 1991-01-28 1992-08-12 Sanden Corporation Schiefscheibenverdichter mit einer Vorrichtung zur Hubveränderung
WO1994016225A1 (en) * 1993-01-11 1994-07-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control valve for a variable displacement refrigerant compressor
US5531572A (en) * 1993-10-15 1996-07-02 Kabushiki Kaisha Toyoda Jidoshokki Seisakushi Capacity control valve for a variable capacity refrigerant compressor
DE19716089A1 (de) * 1996-04-17 1997-11-06 Toyoda Automatic Loom Works Verdrängungsvariabler Kompressor und Verfahren für dessen Steuerung
EP0854288A2 (de) * 1997-01-21 1998-07-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Regelventil für einen Verdichter mit veränderlicher Förderleistung und Verfahren zur Herstellung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0965754A3 (de) * 1998-06-18 2000-02-02 Sanden Corporation Ventil zur Hubregelung zur Verwendung in einem Kompressor mit veränderlicher Verdrängung
DE10014080C2 (de) * 1999-03-26 2002-06-13 Sanden Corp Verdrängungssteuerventil und Kompressor variabler Verdrängung, der das Verdrängungssteuerventil verwendet
EP2042732A1 (de) * 2006-07-19 2009-04-01 Sanden Corporation Leistungsregelungsventil eines verdichters mit variabler leistung
CN101495753B (zh) * 2006-07-19 2011-03-09 三电有限公司 可变容量压缩机的容量控制阀
EP2042732A4 (de) * 2006-07-19 2012-09-05 Sanden Corp Leistungsregelungsventil eines verdichters mit variabler leistung

Also Published As

Publication number Publication date
DE69803732D1 (de) 2002-03-21
JP3754193B2 (ja) 2006-03-08
EP0907021A3 (de) 1999-09-08
EP0907021B1 (de) 2002-02-06
JPH11107929A (ja) 1999-04-20
DE69803732T2 (de) 2002-10-17

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