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WO2002057628A1 - Controleur de cylindree de compression pour cycle frigorifique - Google Patents

Controleur de cylindree de compression pour cycle frigorifique Download PDF

Info

Publication number
WO2002057628A1
WO2002057628A1 PCT/JP2002/000364 JP0200364W WO02057628A1 WO 2002057628 A1 WO2002057628 A1 WO 2002057628A1 JP 0200364 W JP0200364 W JP 0200364W WO 02057628 A1 WO02057628 A1 WO 02057628A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
chamber
discharge
suction
control valve
Prior art date
Application number
PCT/JP2002/000364
Other languages
English (en)
Japanese (ja)
Inventor
Hisatoshi Hirota
Original Assignee
Tgk Co., 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 Tgk Co., Ltd. filed Critical Tgk Co., Ltd.
Priority to EP02715833A priority Critical patent/EP1363021A1/fr
Publication of WO2002057628A1 publication Critical patent/WO2002057628A1/fr
Priority to US10/217,556 priority patent/US20030035733A1/en

Links

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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F04B2027/1886—Open (not controlling) fluid passage
    • F04B2027/1895—Open (not controlling) fluid passage between crankcase and suction chamber

Definitions

  • the present invention relates to a compression capacity control device for a refrigeration cycle used for an air conditioner for a vehicle or the like.
  • the compressor used in the refrigeration cycle of an automotive air conditioner cannot control the rotation speed because it is directly connected to the engine by a belt. Therefore, in order to obtain an appropriate cooling capacity without being restricted by the engine speed, a variable displacement compressor that can change the compression capacity (discharge rate) is used.
  • Such a variable displacement compressor generally compresses refrigerant sucked from a suction chamber leading to a suction pipe and discharges the compressed refrigerant into a discharge chamber leading to a discharge pipe.
  • the discharge amount of the refrigerant is changed by the pressure change.
  • an electromagnetic clutch or the like is provided on a part of a pulley that receives rotation of a belt directly connected to an engine in order to prevent the compressor from being driven in an operating state where it is not necessary to compress the refrigerant.
  • the equipment cost was incurred. Disclosure of the invention
  • an object of the present invention is to provide a compression capacity control device for a refrigeration cycle that does not require a clutch for preventing the operation of the compressor and can greatly reduce the cost of the device.
  • a compression capacity control device for a refrigeration cycle compresses refrigerant sucked from a suction chamber leading to a suction pipe, discharges the compressed refrigerant to a discharge chamber leading to a discharge pipe, and uses an electromagnetic control valve.
  • a compression capacity control device for a refrigeration cycle having a variable capacity compressor in which the discharge amount of refrigerant is changed by a change in pressure in a pressure-controlled pressure regulating chamber. When the solenoid valve is not energized, the variable displacement compressor is set to a variable discharge range with a minimum discharge amount.
  • the electromagnetic control valve communicates between the pressure regulating chamber and the discharge chamber such that the pressure difference between at least one of the pressure in the pressure regulating chamber and the pressure in the suction chamber and the pressure in the discharge chamber is maintained at a predetermined pressure.
  • the pressure difference may be changed by changing the electromagnetic force of the electromagnetic control valve to change the pressure of the pressure regulating chamber, thereby controlling the discharge amount of the refrigerant.
  • a biasing means is provided for maintaining the electromagnetic control valve in the open state when the electromagnetic control valve is not energized. May be set to the minimum discharge amount.
  • a suction path opening / closing valve that closes between the suction pipe line and the suction chamber when the pressure difference between the discharge chamber and the suction chamber becomes equal to or less than a predetermined value may be provided.
  • FIG. 1 is a longitudinal sectional view showing the overall configuration of a compression capacity control device for a refrigeration cycle according to a first embodiment of the present invention.
  • FIG. 2 is a longitudinal sectional view of a capacity control solenoid valve according to a second embodiment of the present invention.
  • FIG. 3 is a longitudinal sectional view showing an overall configuration of a compression capacity control device for a refrigeration cycle according to a third embodiment of the present invention.
  • reference numeral 10 denotes a swash plate type variable displacement compressor which is used for an air conditioning refrigeration cycle of an automobile.
  • R134A or the like is used as the refrigerant, but the present invention may be applied to a refrigeration cycle using carbon dioxide as the refrigerant.
  • Reference numeral 1 denotes a rotating shaft disposed in an airtight crank chamber 12 (pressure regulating chamber), which is a rotary shaft driven by a drive belt (not shown) directly connected to the engine. 3 is connected to the axis position, and the rotation axis The swing plate 14 arranged in the crank chamber 12 at an angle with respect to 11 swings.
  • a piston 17 is arranged reciprocally in a cylinder 15 arranged in a peripheral part in the crank chamber 12, and the piston 17 and the rocking plate 14 are connected by a rod 18. I have.
  • Refrigerant is fed into the suction chamber 3 from the upstream side of the evaporator (not shown) via the suction pipe 1, and from the discharge chamber 4 to the downstream side of the condenser (not shown).
  • the high-pressure refrigerant is sent out via the discharge line 2.
  • the tilt angle of the oscillating plate 14 changes depending on the pressure in the crank chamber 12 (crank chamber pressure P c), and the amount of refrigerant discharged from the cylinder 15 (ie, , Compression capacity).
  • the discharge amount is often large when the oscillating plate 14 is inclined as shown by the solid line, and decreased when it is not inclined as shown by the two-dot chain line.
  • the discharge amount becomes zero.
  • the discharge amount should not be less than about 3 to 5%.
  • Such an operation state in which the discharge amount is minimum is called minimum operation.
  • a minimum securing spring 19 is publicly known, and has, for example, a configuration in which a corrugated panel and a coil panel are combined.
  • Reference numeral 20 denotes a capacity control solenoid valve (electromagnetic control valve) for electromagnetic solenoid control for performing compression capacity control by automatically controlling the crank chamber pressure (P c).
  • 21 is an electromagnetic coil and 22 is a fixed iron core.
  • the movable iron core 23 and the valve body 25 are arranged so as to pass through the fixed iron core 22 and are connected by an axially movable rod 24, and are urged by compression coil springs 27, 28 from both ends. ing.
  • the biasing force of the two compression coil springs 27, 28 is set to be larger in the valve-opening spring 28 than in the valve-closing spring 27.
  • the valve seat 26 is formed between the crank chamber communication passage 5 communicating with the crank chamber 12 and the discharge chamber communication passage 6 communicating with the discharge chamber 4, and the valve body 25 is connected to the valve seat from the crank chamber communication passage 5 side. It is arranged facing 26.
  • the communication between the crank chamber communication passage 5 and the suction pipe line 1 is communicated via a thin leak passage 7.
  • the differential pressure (Pd_Pc) between the discharge pressure (Pd) and the crank chamber pressure (Pc) acts on the valve body 25 in the opening direction, and in the closing direction, the electromagnetic force of the displacement control solenoid valve 20
  • the force (including the biasing force of the compression coil springs 27 and 28) acts.
  • the differential pressure (Pd—Pc) between the discharge pressure (Pd) and the crank chamber pressure (Pc) is The valve body 25 is opened and closed in accordance with the fluctuation, and the differential pressure (Pd-Pc) is kept constant, whereby the crank chamber pressure (Pc) is controlled to a value corresponding to the discharge pressure (Pd), and the compression is performed.
  • the volume (discharge volume) is kept constant.
  • the electromagnetic force of the displacement control solenoid valve 20 is increased, the pressure difference (Pd—Pc) that is kept constant increases, so that the crank chamber pressure (Pc) moves away from the discharge pressure (Pd). And the inclination angle of the swing plate 14 with respect to the rotating shaft 11 increases, so that the refrigerant discharge amount increases.
  • the current supplied to the electromagnetic coil 21 is controlled by detecting signals from the engine, the temperature inside and outside the vehicle, evaporator sensors, and other sensors for detecting various conditions. And a control signal based on the calculation result is sent from the control unit 40 to the electromagnetic coil 21 to be performed.
  • the drive circuit of the electromagnetic coil 21 is not shown.
  • the compressor 10 enters the minimum operation state, so that even when it is not necessary to operate the compressor 10, the rotating shaft 11 can be operated. It can be kept in a state of being driven to rotate.
  • FIG. 2 shows a displacement control solenoid valve 20 according to a second embodiment of the present invention.
  • the compressor 10 is the same as that of the first embodiment and is not shown.
  • leak paths will be arranged as appropriate.
  • a piston rod 25p having the same pressure receiving area as the valve seat 26 is provided on the back side of the valve body 25, and suction is performed in a space facing the back surface of the piston rod 25p.
  • the chamber communication passage 8 is connected, the crank chamber communication passage 5 is connected to the space facing the side surface of the piston rod 25 p, and the discharge chamber connection is provided in the space behind the valve seat 26 when viewed from the valve body 25 side. Passage 6 is connected.
  • crank chamber pressure (P c) applied to the piston rod 25 p and the valve body 25, etc. is canceled, and the differential pressure (P d -P d) between the discharge pressure (P d) and the suction pressure (P s) s) causes the valve body 25 to open and close, which causes the crank chamber 12 and the discharge chamber
  • valve body 25 Due to the difference between the urging forces of 7, 28, the valve body 25 is opened away from the valve seat 26, A state in which the minimum operation is maintained.
  • the pressure difference between at least one of the pressure (Pc) in the crank chamber 12 and the pressure (Ps) in the suction pipe 1 and the pressure (Pd) in the discharge chamber 4 is reduced to a predetermined pressure difference.
  • the pressure difference between the crank chamber 12 and the discharge chamber 4 is changed by changing the electromagnetic force of the displacement control solenoid valve 20 by changing the electromagnetic force of the displacement control solenoid valve 20 to maintain the pressure (Pc ) Can be applied to a device in which the discharge amount changes accordingly, and further to a device controlled by another method.
  • FIG. 3 shows a third embodiment of the present invention.
  • a valve body 32 disposed on a valve seat 31 formed between the suction pipe 1 and the suction chamber 3 so as to face from the suction pipe 1 side is provided with a compression coil spring in a valve closing direction. It is arranged biased by 33.
  • Reference numeral 34 denotes a spring receiver in which a large cutout is formed so as not to hinder the passage of the refrigerant.
  • a pressure receiving piston 35 that receives the pressure (Pd) of the discharge chamber 4 and the pressure (P s) of the suction chamber 3 from both sides is connected to the valve body 32, and the pressure (Pd) of the discharge chamber 4 and the suction chamber
  • the pressure difference (Pd_Ps) from the pressure (Ps) in Step 3 is larger than a certain value
  • the valve body 32 separates from the valve seat 31 and the suction passage opening / closing valve 30 is opened.
  • (Pd-Ps) becomes smaller than a certain value, the valve element 32 is pressed against the valve seat 31, and the suction path on-off valve 30 is closed.
  • the low-pressure refrigerant in the suction line 1 is not sucked into the compressor 10 during the minimum operation, so that the fins of the evaporator do not freeze during the minimum operation when the load is small as in winter. be able to.
  • variable displacement compressor maintains the state of the minimum discharge amount in the variable range in a state where power is not supplied to the electromagnetic control valve, so that the compressor is not operated. This eliminates the need for a clutch, thus greatly reducing equipment costs.

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)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un contrôleur de cylindrée de compression pour cycle frigorifique, comportant un compresseur à cylindrée variable (10) conçu pour comprimer un liquide frigorigène aspiré par une chambre d'aspiration (3) reliée à une conduite d'aspiration (1), évacuer le liquide frigorigène vers une chambre d'évacuation (4) reliée à une conduite d'évacuation (2), et faire varier la quantité de liquide frigorigène évacué en raison d'une variation de pression dans une chambre de régulation de la pression (12) commandée en pression par un électrorobinet de commande (20). Lorsqu'aucun courant électrique n'alimente l'électrorobinet de commande (20), ce dernier, qui est disposé entre la chambre d'évacuation (4) et le robinet de régulation de la pression (12), est maintenu à l'état ouvert de sorte que le compresseur à cylindrée variable (10) peut être amené à évacuer une quantité minimale dans une plage variable, ceci permettant de ne pas avoir recours à un embrayage pour arrêter le fonctionnement du compresseur à cylindrée variable (10) et de réduire considérablement les coûts d'installation.
PCT/JP2002/000364 2001-01-19 2002-01-18 Controleur de cylindree de compression pour cycle frigorifique WO2002057628A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP02715833A EP1363021A1 (fr) 2001-01-19 2002-01-18 Controleur de cylindree de compression pour cycle frigorifique
US10/217,556 US20030035733A1 (en) 2001-01-19 2002-08-13 Compression capacity control device for refrigeration cycle

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2001011513 2001-01-19
JP2001-011513 2001-01-19
JP2001123750A JP4070425B2 (ja) 2001-01-19 2001-04-23 冷凍サイクルの圧縮容量制御装置
JP2001-123750 2001-04-23

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US10/217,556 Continuation US20030035733A1 (en) 2001-01-19 2002-08-13 Compression capacity control device for refrigeration cycle

Publications (1)

Publication Number Publication Date
WO2002057628A1 true WO2002057628A1 (fr) 2002-07-25

Family

ID=26607967

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2002/000364 WO2002057628A1 (fr) 2001-01-19 2002-01-18 Controleur de cylindree de compression pour cycle frigorifique

Country Status (4)

Country Link
US (1) US20030035733A1 (fr)
EP (1) EP1363021A1 (fr)
JP (1) JP4070425B2 (fr)
WO (1) WO2002057628A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1388719A2 (fr) * 2002-08-09 2004-02-11 TGK Co., Ltd. Système de climatisation

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4152674B2 (ja) * 2002-06-04 2008-09-17 株式会社テージーケー 可変容量圧縮機用容量制御弁
JP4107141B2 (ja) * 2003-02-21 2008-06-25 株式会社デンソー リミッタ装置
JP2005098597A (ja) * 2003-09-25 2005-04-14 Tgk Co Ltd 冷凍サイクル
US20050089417A1 (en) * 2003-10-27 2005-04-28 Thar Technologies, Inc. Positive displacement pump
JP4412184B2 (ja) * 2005-01-27 2010-02-10 株式会社豊田自動織機 可変容量型圧縮機
WO2006109641A1 (fr) * 2005-04-08 2006-10-19 Eagle Industry Co., Ltd. Soupape de controle de capacite
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
JP5064918B2 (ja) * 2007-07-17 2012-10-31 サンデン株式会社 可変容量圧縮機の容量制御システム
WO2009044781A1 (fr) 2007-10-02 2009-04-09 Sanden Corporation Compresseur à déplacement variable
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
JP5281320B2 (ja) 2008-05-28 2013-09-04 サンデン株式会社 可変容量圧縮機の容量制御システム
DE112014001574T5 (de) * 2013-03-22 2015-12-03 Sanden Holdings Corporation Steuerventil und Verdichter mit variabler Verdrängung, der mit dem Steuerventil versehen ist

Citations (6)

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Publication number Priority date Publication date Assignee Title
JPH07189895A (ja) * 1993-12-27 1995-07-28 Toyota Autom Loom Works Ltd クラッチレス片側ピストン式可変容量圧縮機
JPH07189899A (ja) * 1993-12-27 1995-07-28 Toyota Autom Loom Works Ltd 可変容量圧縮機
JPH10153178A (ja) * 1996-11-22 1998-06-09 Toyota Autom Loom Works Ltd 可変容量圧縮機
EP0881387A2 (fr) * 1997-05-26 1998-12-02 Zexel Corporation Compresseur à plateau en biais à capacité variable sans embrayage
EP0953765A2 (fr) * 1998-04-13 1999-11-03 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur en plateau en biais à capacité variable avec soupape de contrÔle
JP2000161209A (ja) * 1998-11-27 2000-06-13 Calsonic Corp 斜板式可変容量圧縮機

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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
JPH08109880A (ja) * 1994-10-11 1996-04-30 Toyota Autom Loom Works Ltd 可変容量型圧縮機の動作制御システム
DE69822686T2 (de) * 1997-01-24 2004-09-23 Kabushiki Kaisha Toyota Jidoshokki, Kariya Kompressor mit variabler Fördermenge
JPH1182297A (ja) * 1997-09-08 1999-03-26 Toyota Autom Loom Works Ltd 可変容量圧縮機
JP4160669B2 (ja) * 1997-11-28 2008-10-01 株式会社不二工機 可変容量型圧縮機用制御弁
JP2000346241A (ja) * 1999-06-07 2000-12-15 Toyota Autom Loom Works Ltd 逆止弁

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07189895A (ja) * 1993-12-27 1995-07-28 Toyota Autom Loom Works Ltd クラッチレス片側ピストン式可変容量圧縮機
JPH07189899A (ja) * 1993-12-27 1995-07-28 Toyota Autom Loom Works Ltd 可変容量圧縮機
JPH10153178A (ja) * 1996-11-22 1998-06-09 Toyota Autom Loom Works Ltd 可変容量圧縮機
EP0881387A2 (fr) * 1997-05-26 1998-12-02 Zexel Corporation Compresseur à plateau en biais à capacité variable sans embrayage
EP0953765A2 (fr) * 1998-04-13 1999-11-03 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur en plateau en biais à capacité variable avec soupape de contrÔle
JP2000161209A (ja) * 1998-11-27 2000-06-13 Calsonic Corp 斜板式可変容量圧縮機

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1388719A2 (fr) * 2002-08-09 2004-02-11 TGK Co., Ltd. Système de climatisation
EP1388719A3 (fr) * 2002-08-09 2004-02-25 TGK Co., Ltd. Système de climatisation
US6966195B2 (en) 2002-08-09 2005-11-22 Tgk Co., Ltd. Air conditioning system

Also Published As

Publication number Publication date
JP4070425B2 (ja) 2008-04-02
EP1363021A1 (fr) 2003-11-19
JP2002285973A (ja) 2002-10-03
US20030035733A1 (en) 2003-02-20

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