EP1420162A2 - Kontrollventil für einen verstellbaren Taumelscheibenkompressor - Google Patents

Kontrollventil für einen verstellbaren Taumelscheibenkompressor Download PDF

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Publication number
EP1420162A2
EP1420162A2 EP03025917A EP03025917A EP1420162A2 EP 1420162 A2 EP1420162 A2 EP 1420162A2 EP 03025917 A EP03025917 A EP 03025917A EP 03025917 A EP03025917 A EP 03025917A EP 1420162 A2 EP1420162 A2 EP 1420162A2
Authority
EP
European Patent Office
Prior art keywords
valve
control valve
relatively high
passage
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.)
Withdrawn
Application number
EP03025917A
Other languages
English (en)
French (fr)
Other versions
EP1420162A3 (de
Inventor
Satoshi Umemura
Hideki Mizutani
Masakazu Murase
Tatsuya Hirose
Yuji Hashimoto
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
Toyota Industries 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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1420162A2 publication Critical patent/EP1420162A2/de
Publication of EP1420162A3 publication Critical patent/EP1420162A3/de
Withdrawn legal-status Critical Current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
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/16—Filtration; Moisture separation
    • 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
    • F04B2027/185—Discharge 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
    • F04B2027/1886—Open (not controlling) fluid passage
    • F04B2027/1895—Open (not controlling) fluid passage 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
    • F04B2205/00—Fluid parameters
    • F04B2205/05—Pressure after the pump outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0403—Refractory metals, e.g. V, W
    • F05C2201/0406—Chromium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0466—Nickel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0469—Other heavy metals
    • F05C2201/0475—Copper or alloys thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the present invention relates to a control valve for controlling the displacement of a variable displacement compressor in a refrigeration cycle.
  • a variable displacement swash plate type compressor for use in a refrigeration cycle optionally varies the inclination angle of a swash plate or the displacement of the compressor by adjusting pressure in a crank chamber or a chamber for accommodating the swash plate, as disclosed in page 15 to 16 and FIG. 12 of Unexamined Japanese Patent Publication No. 2001-173556.
  • the compressor provides a control valve for adjusting the pressure in the crank chamber.
  • the control valve for example, varies the opening degree of a supply passage that interconnects a relatively high pressure region of the refrigeration cycle and the crank chamber.
  • a relatively low pressure region of the refrigeration cycle and the crank chamber are interconnected through a bleed passage.
  • the opening degree of the control valve is adjusted to control a balance between the amount of relatively high pressure refrigerant gas introduced from the relatively high pressure region to the crank chamber through the supply passage and the amount of refrigerant gas delivered from the crank chamber to the relatively low pressure region through the bleed passage.
  • the pressure in the crank chamber is determined.
  • the inclination angle of the swash plate is varied in accordance with the variation of the pressure in the crank chamber. As a result, the stroke of pistons, that is, the displacement of the compressor, is adjusted.
  • a seat surface of a valve seat and a valve surface of a valve body for opening and closing the control valve constitute a portion for adjusting the opening degree of the control valve.
  • a variable displacement compressor optionally varies displacement based upon pressure in a crank chamber for adjusting the pressure in the crank chamber by varying an opening degree of a passage that interconnects the crank chamber and one of relatively high and low pressure regions of the refrigeration cycle.
  • a control valve of the variable displacement compressor has a valve seat and a valve.
  • the valve seat has a seat surface for adjusting the opening degree of the passage.
  • the valve has a valve surface for adjusting the opening degree of the passage. At least one of the seat surface and the valve surface is made of a material with relatively high hardness.
  • FIGs. 1 A and 1 B A preferred embodiment of the present invention will now be described with reference to FIGs. 1 A and 1 B.
  • FIG. 1 A illustrates a schematic view of a variable displacement swash plate type compressor 1 (hereinafter the compressor 1) for a refrigeration cycle of a vehicle air conditioner.
  • the compressor 1 introduces refrigerant gas from a suction chamber 2 into a compression chamber 1 a, then compresses the introduced refrigerant gas and discharges the compressed refrigerant gas to a discharge chamber 3 as the volume of the compression chamber 1 a is varied by the rotation of a swash plate (not shown).
  • An oil separator 4 is arranged near an outlet of the discharge chamber 3 for separating misty lubricating oil contained in the refrigerant gas from the refrigerant gas.
  • carbon dioxide is employed as refrigerant for the refrigeration cycle.
  • a crank chamber 5 which accommodates the swash plate, communicates with the suction chamber 2, which is a relatively low pressure region in the refrigeration cycle, through a bleed passage 6.
  • the oil separator 4 which is a relatively high pressure region in the refrigeration cycle, communicates with the crank chamber 5 through a supply passage 7.
  • the supply passage 7 doubles as a feeding passage for feeding the lubricating oil separated by the oil separator 4 to the crank chamber 5.
  • a filter 8 is arranged at the upstream side (the side of the oil separator 4) of the supply passage 7 for removing foreign particles in the refrigerant gas.
  • the filter 8 has a mesh size for only removing the foreign particles of 20 to 30 ⁇ m or above in view of interference against the flow of refrigerant gas.
  • a control valve CV is arranged in the supply passage 7 and optionally adjusts the opening degree of the supply passage 7.
  • the adjustment of the opening degree of the control valve CV controls a balance between the amount of relatively high pressure refrigerant gas introduced from the discharge chamber 3 into the crank chamber 5 through the supply passage 7 and the amount of refrigerant gas delivered from the crank chamber 5 to the suction chamber 2 through the bleed passage 6.
  • the pressure in the crank chamber 5 is determined.
  • the inclination angle of the swash plate is varied in accordance with the variation of the pressure in the crank chamber 5 so that the displacement of the compressor 1 is adjusted.
  • the inclination angle of the swash plate increases so that the displacement of the compressor 1 increases.
  • the inclination angle of the swash plate reduces so that the displacement of the compressor 1 reduces.
  • a valve housing 10 of the control valve CV includes a valve body 11 on the upper side and an actuator housing 12 on the lower side in the drawing.
  • a valve chamber 22 Starting from the lower side of the drawing, a valve chamber 22, a communication passage 23 and a pressure sensing chamber 24 are respectively defined in the valve body 11.
  • a valve rod 25 is movably arranged through the valve chamber 22 and the communication passage 23 so as to extend in the axial direction of the valve housing 10 (the vertical direction of the drawing). The upper end of the valve rod 25 inserted through the communication passage 23 separates the communication passage 23 from the pressure sensing chamber 24.
  • the communication passage 23 communicates with the oil separator 4 of the compressor 1 through the upstream portion of the supply passage 7.
  • the valve chamber 22 communicates with the crank chamber 5 of the compressor 1 through the downstream portion of the supply passage 7.
  • the valve chamber 22 and the communication passage 23 constitute a portion of the supply passage 7.
  • a valve portion 31 formed at the middle portion of the valve rod 25 is arranged in the valve chamber 22.
  • a step between the valve chamber 22 and the communication passage 23 forms a valve seat 32, and accordingly the communication passage 23 forms a valve hole.
  • a coil spring 60 for urging the valve rod 25 is arranged in the valve chamber 22. The coil spring 60 urges the valve rod 25 in a direction in which the valve portion 31 leaves away from the valve chamber 32.
  • a bellows 33 which has a cylindrical shape, is accommodated in the pressure sensing chamber 24.
  • the upper end of the bellows 33 is fixed to the valve housing 10.
  • the upper end of the valve rod 25 is fitted to the lower end of the bellows 33.
  • the bellows 33 has a bottom at one end and partitions the pressure sensing chamber 24 into a first pressure chamber 49 and a second pressure chamber 50.
  • a fixed throttle 41 is provided in a discharge passage 40, which interconnects the discharge chamber 3 with an external refrigerant circuit (not shown).
  • the first pressure chamber 49 communicates with the discharge passage 40 through a first pressure introducing passage 42 and connects at the upstream side (the side of the discharge chamber 3) relative to the fixed throttle 41.
  • the second pressure chamber 50 communicates with the discharge passage 40 through a second pressure introducing passage 43 and connects at the downstream side relative to the fixed throttle 41.
  • the bellows 33 reflects the variation of pressure difference between the upstream side and downstream side of the fixed throttle 41 for positioning of the valve rod 25 (the valve portion 31) as the lower end portion of the bellows 33 moves in accordance with the pressure difference.
  • the bellows 33 moves the valve portion 31 in such a manner that the displacement of the compressor 1 varies to cancel the variation of the pressure difference between the upstream side and downstream side of the fixed throttle 41.
  • An electromagnetic actuator 51 is provided at the lower side of the valve housing 10.
  • the electromagnetic actuator 51 provides a cylindrical accommodating cylinder 52 with a bottom at one end in the middle of the actuator housing 12.
  • a center post 53 which has a columnar shape, is fixedly fitted to the opening of the accommodating cylinder 52 on the upper side. This fitting of the center post 53 defines a plunger chamber 54 at the lowest portion of the accommodating cylinder 52.
  • a plunger 56 is accommodated in the plunger chamber 54 and is movable in the axial direction (the vertical direction of the FIG. 1A).
  • a guide hole 57 extends through the center of the center post 53 in the axial direction of the center post 53.
  • the lower side of the valve rod 25 is movably arranged in the guide hole 57.
  • the lower end of the valve rod 25 is fixedly fitted to the plunger 56 in the plunger chamber 54. Accordingly, the plunger 56 and the valve rod 25 integrally move up and down anytime.
  • a coil 61 winds around the outer circumference of the accommodating cylinder 52 and partially covers an area from the center post 53 to the plunger 56.
  • the coil 61 is supplied with electric power based upon a command of an air conditioner ECU (not shown). Accordingly, the magnitude of electromagnetic force (electromagnetic attraction) corresponding to electric power supplied to the coil 61 is generated between the plunger 56 and the center post 53. The electromagnetic force is transmitted to the valve rod 25 (the valve portion 31) through the plunger 56.
  • the electromagnetic actuator 51 varies electromagnetic force applied to the valve portion 31 in accordance with the electric power externally supplied so that a control target for pressure difference between the upstream side and downstream side of the fixed throttle 41 (set pressure differential), which is a reference for positioning action of the valve portion 31 by the bellows 33, is optionally changed.
  • set pressure differential which is a reference for positioning action of the valve portion 31 by the bellows 33.
  • the control valve CV internally and autonomously positions the valve rod 25 (the valve portion 31) in accordance with the variation of the pressure difference so as to maintain the set pressure difference determined by electric power supplied to the coil 61.
  • this set pressure difference is externally varied by adjusting electric power supplied to the coil 61.
  • the refrigerant gas may flow through the supply passage 7 at relatively high speed.
  • the seat surface 32a of the valve seat 32 and the valve surface 31 a of the valve portion 31, which are portions for adjusting the opening degree of the control valve CV, both are made of materials with relatively high hardness for protection against erosion.
  • the word of "a material with relatively high hardness" in the preferred embodiment means that a material with Vickers hardness of 500 or above because pressure difference between relatively high and low pressures in the refrigeration cycle occasionally becomes approximately 10MPa and particles, which cause erosion are constituted of fine solid particles (10 to 20 ⁇ m) such as silicon oxide with relatively high hardness.
  • the material of the valve seat 32 is brass and has Vickers hardness of approximately 200. Accordingly, to obtain a material of the seat surface 32a of the valve seat 32 with relatively high hardness, the surface of the material of the valve seat 32 is coated with a high hardness layer 32b by nickel-phosphorus plating. Thus, the seat surface 32a of the valve seat 32 is constituted of a relatively high hardness material with Vickers hardness of 500 to 800.
  • the material of the valve rod 25 (the valve portion 31) is stainless steel (SUS) and has Vickers hardness of approximately 300. Accordingly, to obtain a material of the valve surface 31a of the valve portion 31 with relatively high hardness, the surface of the material of the valve portion 31 is coated with a high hardness layer 31b by salt-bath nitriding. Thus, the valve surface 31a of the valve portion 31 is constituted of a relatively high hardness material with Vickers hardness of 900 to 1100.
  • the thicknesses of the above high hardness layers 31b, 32b range approximately from a few ⁇ m to 1 mm.
  • the thicknesses of the high hardness layers 31b, 32b in FIG. 1B are exaggerated for easier understanding.
  • the coil spring 60 is not shown in FIG. 1B.
  • either of the seat surface 32a of the valve seat 32 or the valve surface 31a of the valve portion 31 is made of a material with relatively high hardness.
  • the same advantageous effect to that of the paragraph (1) is obtained. That is, the leakage of the refrigerant gas is reduced in a state when the control valve CV is fully closed.
  • both of the seat surface 32a of the valve seat 32 and the valve surface 31a of the valve portion 31, which are respectively made of materials with relatively high hardness more reliably perform the above advantageous effect.
  • the seat surface 32a of the valve seat 32 is constituted of a material with relatively high hardness in such a manner that the material of the valve seat 32 is treated with surface hardening by nickel-phosphorus plating.
  • the surface hardening of the material of the valve seat 32 is selected from the group consisting of nickel plating, nickel-phosphorus-boron plating, nickel-boron plating, nickel-boron-tungsten plating, chrome plating and copper plating.
  • the seat surface 32a is constituted of a material with relatively high hardness.
  • the seat surface 32a of the valve seat 32 is not limited to be hardened with the surface hardening by plating but may be hardened by one of ion nitriding, gas nitrocarburizing and salt-bath nitriding.
  • the valve surface 31 a is constituted of a material with relatively high hardness.
  • valve surface 31a of the valve portion 31 is not limited to be hardened with the surface hardening by nitriding.
  • the valve surface 31a of the valve portion 31 may be hardened with the surface hardening of a material of the valve portion 31 by one of nickel plating, nickel-phosphorus plating, nickel-phosphorus-boron plating, nickel-boron plating, nickel-boron-tungsten plating, chrome plating and copper plating.
  • the material of the valve portion 31 (the valve rod 25) is steel for carburizing, and the surface of the material is hardened by carburizing so as to form the valve surface 31a with relatively high hardness.
  • the material of the valve seat 32 is not limited to brass but may be another copper series material, aluminum series material or stainless steel (SUS).
  • the control valve CV varies the opening degree of the supply passage 7 that interconnects the relatively high pressure region of the refrigeration cycle (the oil separator 4) and the crank chamber 5 so that the pressure in the crank chamber 5 is adjusted.
  • the present invention is embodied in a so-called supply-side control valve, in which the control valve is arranged in the supply passage 7.
  • a control valve varies the opening degree of the bleed passage 6 that interconnects the crank chamber 5 and the relatively low pressure region of the refrigeration cycle (for example, the suction chamber 2) so that the pressure in the crank chamber 5 is adjusted.
  • the present invention is embodied in a so-called bleed-side control valve, in which the control valve is arranged in the bleed passage 6.
  • control valve CV internally and autonomously positions the valve portion 31 in accordance with the variation of the pressure differential so as to maintain the set pressure differential determined by electric power externally supplied.
  • the present invention is embodied in a so-called external control valve.
  • the present invention is not limited to be embodied in the external control valve but may be embodied in an internal control valve or a mere electromagnetic valve.
  • a variable displacement compressor optionally varies displacement based upon pressure in a crank chamber for adjusting the pressure in the crank chamber by varying an opening degree of a passage that interconnects the crank chamber and one of relatively high and low pressure regions of the refrigeration cycle.
  • a control valve of the variable displacement compressor has a valve seat and a valve.
  • the valve seat has a seat surface for adjusting the opening degree of the passage.
  • the valve has a valve surface for adjusting the opening degree of the passage. At least one of the seat surface and the valve surface is made of a material with relatively high hardness.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP03025917A 2002-11-14 2003-11-12 Kontrollventil für einen verstellbaren Taumelscheibenkompressor Withdrawn EP1420162A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002330720A JP2004162640A (ja) 2002-11-14 2002-11-14 容量可変型圧縮機の制御弁
JP2002330720 2002-11-14

Publications (2)

Publication Number Publication Date
EP1420162A2 true EP1420162A2 (de) 2004-05-19
EP1420162A3 EP1420162A3 (de) 2004-09-15

Family

ID=32171396

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03025917A Withdrawn EP1420162A3 (de) 2002-11-14 2003-11-12 Kontrollventil für einen verstellbaren Taumelscheibenkompressor

Country Status (6)

Country Link
US (1) US20040118140A1 (de)
EP (1) EP1420162A3 (de)
JP (1) JP2004162640A (de)
KR (1) KR20040042801A (de)
CN (1) CN1508426A (de)
BR (1) BR0305196A (de)

Cited By (2)

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EP1777412A4 (de) * 2004-07-13 2007-12-26 Sanden Corp Mengenregelventil für kupplungslosen verstellbaren schrägscheiben-verdichter
EP2963293A1 (de) * 2014-06-19 2016-01-06 TGK CO., Ltd. Regelventil für einen verdichter mit variabler verdrängung

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JP2007177627A (ja) * 2005-12-27 2007-07-12 Sanden Corp 可変容量圧縮機の吐出容量制御弁
JP4607047B2 (ja) * 2006-04-28 2011-01-05 サンデン株式会社 可変容量圧縮機の吐出容量制御弁
JP4599327B2 (ja) * 2006-05-23 2010-12-15 サンデン株式会社 可変容量圧縮機
JP2011099542A (ja) * 2009-11-09 2011-05-19 Fujikin Inc 調整弁装置
CN103547804B (zh) * 2011-05-23 2016-03-09 学校法人斗源学院 用于可变容量压缩机的控制阀及用于制造该控制阀的方法
DE102012202859B4 (de) * 2012-02-24 2025-12-31 Mahle International Gmbh Ventilsystem zur Ladungswechselsteuerung
CN104373650A (zh) * 2014-11-18 2015-02-25 温州仁谦汽车油泵有限公司 一种弹片式恒压阀
CN104697505B (zh) * 2015-03-20 2017-03-08 张家港海纳德智能科技有限公司 一种用于测绘仪器的转动部件及其制造方法
US11060493B2 (en) * 2019-03-29 2021-07-13 Delphi Technologies Ip Limited Fuel pump for gasoline direct injection
US12180950B2 (en) 2019-04-03 2024-12-31 Eagle Industry Co., Ltd. Capacity control valve
EP3951175B1 (de) 2019-04-03 2026-05-06 Eagle Industry Co., Ltd. Kapazitätssteuerungsventil
CN113692510B (zh) 2019-04-24 2023-07-04 伊格尔工业股份有限公司 容量控制阀
WO2020218284A1 (ja) 2019-04-24 2020-10-29 イーグル工業株式会社 容量制御弁
CN115427717A (zh) 2020-04-22 2022-12-02 伊格尔工业股份有限公司 容量控制阀

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EP2963293A1 (de) * 2014-06-19 2016-01-06 TGK CO., Ltd. Regelventil für einen verdichter mit variabler verdrängung

Also Published As

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KR20040042801A (ko) 2004-05-20
CN1508426A (zh) 2004-06-30
US20040118140A1 (en) 2004-06-24
JP2004162640A (ja) 2004-06-10
BR0305196A (pt) 2004-08-31
EP1420162A3 (de) 2004-09-15

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