EP0508823A1 - Schiefscheiberverdichter mit variablem Hubmechanismus - Google Patents

Schiefscheiberverdichter mit variablem Hubmechanismus Download PDF

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Publication number
EP0508823A1
EP0508823A1 EP92303249A EP92303249A EP0508823A1 EP 0508823 A1 EP0508823 A1 EP 0508823A1 EP 92303249 A EP92303249 A EP 92303249A EP 92303249 A EP92303249 A EP 92303249A EP 0508823 A1 EP0508823 A1 EP 0508823A1
Authority
EP
European Patent Office
Prior art keywords
piston
compressor
change
cylinders
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.)
Granted
Application number
EP92303249A
Other languages
English (en)
French (fr)
Other versions
EP0508823B1 (de
Inventor
Kiyoshi Terauchi
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 EP0508823A1 publication Critical patent/EP0508823A1/de
Application granted granted Critical
Publication of EP0508823B1 publication Critical patent/EP0508823B1/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
    • F04B25/00—Multi-stage pumps
    • F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B27/10—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 having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • 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
    • F04B51/00—Testing machines, pumps, or pumping installations
    • 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
    • F04B2027/1831—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
    • F04B2027/1845—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
    • F04B2201/00—Pump parameters
    • F04B2201/02—Piston parameters
    • F04B2201/0201—Position of the piston

Definitions

  • the present invention relates to a compressor with a variable displacement mechanism, and more particularly, to a slant plate type compressor with a variable displacement mechanism, of which the top dead center position of the piston can be changed in response to the change of the piston stroke.
  • a conventional slant plate type compressor with a variable displacement mechanism as used in an automotive air conditioning system controls the displacement of the compressor in response to the condition of the air conditioning load and the other requirements.
  • the mechanism for detecting the displacement of the compressor is complicated on the construction thereby to be in high cost, such a mechanism is not generally used.
  • the information can be usefully utilized for the control of an engine control system or a monitor of an air conditioning system.
  • a conventional detecting device for detecting the displacement of the compressor is disclosed in, e.g., Japanese Patent Laid-Open Gazette No. 62-21867.
  • the detecting device includes a non-contact type position detecting device, which has a detected object, for utilizing the change of the electrostatic volme or the change of the magnetic flux density.
  • This non-contact type position detecting device can detect only the range of about 1 mm. Accordingly, it is difficult for the detecting device to directly detect the change of the position of the slant plate which largely varies on angle. Likewise, it is difficult for the detecting device to directly detect the change of the position of the piston, i.e., the change of the piston stroke since the piston stroke changes within the range of 1-30 mm.
  • FIG. 1 is a cross-sectional view of a slant plate type compressor with a variable displacement mechainism, of which the inclined angle of the slant plate is at the largest, in accordance with the first embodiment of this invention.
  • FIG. 2 is a cross-sectional view of a slant plate type compressor with a variable displacement mechainism, of which the inclined angle of the slant plate is at the least, in accordance with the first embodiment of this invention.
  • FIG. 3 is a cross-sectional view of a part of a slant plate type compressor with a variable displacement mechanism in accordance with the second embodiment of this invention.
  • FIG. 4 is a cross-sectional view of a part of a slant pate type compressor with a variable displacement mechanism in accordance with the third embodiment of this invention.
  • FIG. 5 is a graph of showing the relationship between a piston stroke and a position of a top dead center of a piston.
  • a slant plate type compressor with a variable displacement mechanism comprises a compressor housing which encloses a crank chamber.
  • the housing includes a cylinder block.
  • a plurality of cylinders are formed for defining compression space in the cylinder block.
  • a piston is slidably fitted with each of the cylinders.
  • a drive mechanism is coupled to the pistons to reciprocate the pistons within the cylinders.
  • the drive mechanism includes a drive shaft rotatably supported in the housing.
  • Coupling means drivingly couples the the pistons with the drive shaft and converts rotary motion of the drive shaft into reciprocating motion of the pistons.
  • the coupling means includes a slant plate having a surface disposed at a slant angle relative to a plane perpendicular to the drive shaft.
  • the slant angle changes in response to a change in pressure in the crank chamber.
  • the stroke of the piston changes in response to the change of the slant angle and defines compression volume in the compression space to change the capacity of the compressor.
  • the position of the top dead center of the piston changes within a certain range in response to the change of the stroke of the piston.
  • a suction chamber a discharge chamber are enclosed within the compressor housing.
  • a communication path links the crank chamber with the suction chamber.
  • a control valve varies the capacity of the compressor by controlling the link between the crank and the suction chambers through the path.
  • the sensor means is disposed adjacent the cylinder for detecting the position of the top dead center of the piston in the compression space.
  • wobble plate type compressor 1 includes front end plate 2, cylinder casing 3 having cylinder block 31, valve plate 4, and cylinder head 5.
  • Front end plate 2 is fixed on one end of cylinder casing 3 by securing bolts (not shown).
  • Axial hole 21 which is formed through the center of front end plate 2 receives drive shaft 7.
  • Radial bearing 8 is disposed in axial hole 21 to rotatably support drive shaft 7.
  • Annular sleeve portion 22 projects from front end plate 2 and and surrounds drive shaft 7, defining seal cavity 23.
  • Cylinder casing 3 is provided with cylinder block 31 and crank chamber 32.
  • Cylinder block 31 has a plurality of equiangularly spaced cylinders 33 formed therein.
  • Cam rotor 10 is fixed on drive shaft 7 by pin 103.
  • Thrust needle bearing 11 is disposed between the inner surface of front end plate 2 and the adjacent axial end surface of cam rotor 10.
  • Arm portion 101 of cam rotor 10 extends in the direction of cylinder block 31.
  • Hole 102 is formed on arm portion 101.
  • Cylindrical member 12, provided with flange portion 121 is disposed around drive shaft 7 and is rotatably supported on drive shaft 7 through spherical element 13 slidably fitted on drive shaft 7.
  • Second arm portion 122 is formed on the outer surface of flange portion 121 of cylindrical member 12 and faces arm portion 101 of cam rotor 10.
  • Elongated hole 123, formed in arm portion 122, is aligned with hole 102.
  • Pin 14 inserted through hole 102, is slidably movable within elongated hole 123.
  • Ring-shaped wobble plate 15 is mounted on the outer surface of cylindrical member 12 through radial needle bearing 16.
  • Thrust needle bearing 17 is disposed in a gap between flange portion 121 and wobble plate 15.
  • the other end of drive shaft 7 is rotatably supported through radial bearing 18 in the central bore of cylinder block 31.
  • Sliding shaft 151 is attached on the outer peripheral portion of wobble plate 15 and projects toward the bottom surface of cylinder casing 3. The end of sliding shaft 151 is slidably disposed in groove 321 to prevent the rotation of wobble plate 15.
  • piston rod 19 is rotatably connected to receiving surface 152 of wobble plate 15.
  • the other end of piston rod 19 is rotatably connected to piston 20 which is slidably disposed in cylinder 33.
  • a suction port (not shown) and discharge port 42 are formed in valve plate 4.
  • a suction reed valve (not shown) is disposed on valve plate 4.
  • Discharge reed valve (not shown) is disposed on valve plate 4 opposite the suction reed valve.
  • Cylinder head 5 is connected to cylinder casing 3 through a gasket (not shown) and valve plate 4.
  • Partition wall 51 extends axially from the inner surface of cylinder head 5 and divides the interior of cylinder head 5 into suction chamber 52 and discharge chamber 53.
  • Suction chamber 52 is connected to the external fluid circuit through fluid inlet port 60 formed in cylinder head 5.
  • Discharge chamber 53 is connected to the external fluid circuit through fluid outlet port 61 formed in cylinder head 5.
  • Bellows 63 is disposed in cylindrical bore 62 formed in cylinder block 31. Bore 62 is communicated with suction chamber 52 through aperture 64 formed through valve plate 4 and is communicated with crank chamber 32 through passageway 65 formed through cylinder block 31. Aperture 64 is normally closed by needle element 631 disposed on one end of bellows 63. The communication between crank chamber 32 and suction chamber 52 is controlled in accordance with the movement of bellows 63.
  • Proximity position sensor 70 is a non-contact type position detecting device and has a cpacity for detecting the range of about 1 mm. Proximity position sensor 70 is disposed on valve plate 4 at the cylinder side to face to the top surface of piston 20.
  • rotational motion is applied to drive shaft 7 through an external driving source (not shown) and is communicated to cam rotor 10.
  • the rotational motion of cam rotor 10 is converted to nutational motion at wobble plate 15 through cylindrical member 12.
  • Sliding shaft 151 connected to wobble plate 15 and disposed in groove 321, prevents wobble plate 15 from rotating.
  • the nutational motion of wobble plate 15 is converted to the reciprocating motion of pistons 20 in cylinders 33 through piston rods 19. Accordingly, refrigeration fluid is sucked through inlet port 60 to suction chamber 52 and flows into cylinder 33 through suction port 41. Refrigeration fluid is compressed in cylinder 33 and is discharged into discharge chamber 53 through discharge port 42. The compressed refrigeration fluid then flows into the external fluid circuit through outlet port 61.
  • Distance ⁇ x between the inner surface of valve plate 4 and the top surface of piston 20 is 0.3 mm when the inclined angle of flange portion 121 as shown in FIG. 1 is at the largest and is 1.3 mm when the inclined angle of flange portion 121 as shown in FIG. 2 is at the least.
  • the change of the displacement of the compressor i.e., the relationship between the change of the inclined angle of slant plate 121 and the position of the top dead center of piston 20 is defined in accordance with the shape of elongated hole 123 formed in arm portion 122. Therefore, even though the detected output from position sensor 70 is non-linear to the value of distance ⁇ x, the detected output proportional to the piston stroke can be outputted by suitably selecting the shape of elongated hole 123.
  • Detected object 80 which is a permanent magnet is disposed in the top end surface of piston 20.
  • Hall generator 81 is on valve plate 4 at the cylinder side to face to detected object 80. Hall generator 81 can output the output corresponding to distance ⁇ x between itself and detected object 80.
  • Detected object 90 which is a permanent magnet is disposed on the side surface of piston 20.
  • Hall generator 81 is disposed on the side of cylinder casing 3. Hall generator 81 can output the output corresponding to distance ⁇ x between itself and detected object 80.
  • the displacement of the compressor can be directly detected by changing the position of the top dead center of a piston within the range between 0.3 - 1.3 mm and by a non-contact type position sensor which has a capacity for detecting range of about 1 mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP92303249A 1991-04-10 1992-04-10 Schiefscheiberverdichter mit variablem Hubmechanismus Expired - Lifetime EP0508823B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP3077938A JPH04311685A (ja) 1991-04-10 1991-04-10 圧縮機
JP77938/91 1991-04-10

Publications (2)

Publication Number Publication Date
EP0508823A1 true EP0508823A1 (de) 1992-10-14
EP0508823B1 EP0508823B1 (de) 1995-10-18

Family

ID=13648012

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92303249A Expired - Lifetime EP0508823B1 (de) 1991-04-10 1992-04-10 Schiefscheiberverdichter mit variablem Hubmechanismus

Country Status (7)

Country Link
EP (1) EP0508823B1 (de)
JP (1) JPH04311685A (de)
KR (1) KR100216388B1 (de)
CN (1) CN1029023C (de)
AU (1) AU650960B2 (de)
CA (1) CA2065831C (de)
DE (1) DE69205480T2 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001071186A2 (en) 2000-03-23 2001-09-27 Empresa Brasileira De Compressores S.A. - Embraco Position sensor and compressor
WO2003081040A1 (en) * 2002-03-21 2003-10-02 Empresa Brasileira De Compressores S.A. - Embraco A position sensor and a linear compressor
WO2005064162A1 (en) * 2003-05-12 2005-07-14 Empresa Brasileira De Compressores S.A.-Embraco A proximity-sensor support, a compressor, a valve plate and a cooler

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BR0203724B1 (pt) * 2002-09-12 2011-08-09 bomba de fluidos e placa de transferência de fluidos e sensor indutivo para bomba de fluidos.
CN102364099A (zh) * 2011-11-01 2012-02-29 无锡市苏立成汽车空调压缩机有限公司 汽车空调压缩机主轴斜盘结构
DE102019112237A1 (de) * 2019-04-12 2020-10-15 OET GmbH Hubkolbenkompressor
CN111997887A (zh) * 2020-09-01 2020-11-27 浙江三田汽车空调压缩机有限公司 变排量压缩机主轴窜动量检测装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0183295A1 (de) * 1984-11-15 1986-06-04 Dowell Schlumberger Corp. Verfahren um die Pumpenkennlinien einer Verdrängerpumpe zu ermitteln und eine geeignete Pumpe für dieses Verfahren
US4737079A (en) * 1986-03-19 1988-04-12 Diesel Kiki Co., Ltd. Variable capacity wobble plate compressor
EP0264148A1 (de) * 1986-10-08 1988-04-20 Pumptech N.V. Förderstrommessungs- und Überwachungssystem für Verdrängerpumpen und Pumpen mit diesem System
EP0282190A1 (de) * 1987-02-19 1988-09-14 Sanden Corporation Taumelscheibenverdichter
US4822252A (en) * 1986-07-28 1989-04-18 Nippondenso Co., Ltd. Variable capacity compressor
EP0342928A2 (de) * 1988-05-16 1989-11-23 Honda Giken Kogyo Kabushiki Kaisha Regelvorrichtung für Kühlventilator in einem Fahrzeug mit Klimaanlage
DE4015006A1 (de) * 1989-05-10 1990-11-15 Toyoda Automatic Loom Works Taumelscheibenkompressor mit variabler foerderleistung und foerderleistungsdetektor

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3824752A1 (de) * 1988-07-21 1990-01-25 Bosch Gmbh Robert Taumelscheibenkompressor

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0183295A1 (de) * 1984-11-15 1986-06-04 Dowell Schlumberger Corp. Verfahren um die Pumpenkennlinien einer Verdrängerpumpe zu ermitteln und eine geeignete Pumpe für dieses Verfahren
US4737079A (en) * 1986-03-19 1988-04-12 Diesel Kiki Co., Ltd. Variable capacity wobble plate compressor
US4822252A (en) * 1986-07-28 1989-04-18 Nippondenso Co., Ltd. Variable capacity compressor
EP0264148A1 (de) * 1986-10-08 1988-04-20 Pumptech N.V. Förderstrommessungs- und Überwachungssystem für Verdrängerpumpen und Pumpen mit diesem System
EP0282190A1 (de) * 1987-02-19 1988-09-14 Sanden Corporation Taumelscheibenverdichter
EP0342928A2 (de) * 1988-05-16 1989-11-23 Honda Giken Kogyo Kabushiki Kaisha Regelvorrichtung für Kühlventilator in einem Fahrzeug mit Klimaanlage
DE4015006A1 (de) * 1989-05-10 1990-11-15 Toyoda Automatic Loom Works Taumelscheibenkompressor mit variabler foerderleistung und foerderleistungsdetektor

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001071186A2 (en) 2000-03-23 2001-09-27 Empresa Brasileira De Compressores S.A. - Embraco Position sensor and compressor
WO2001071186A3 (en) * 2000-03-23 2002-04-04 Brasil Compressores Sa Position sensor and compressor
US6779984B2 (en) 2000-03-23 2004-08-24 Empresa Brasileira De Compressores S.A. - Embraco Position sensor and compressor
KR100742040B1 (ko) * 2000-03-23 2007-07-23 월풀 에쎄.아. 위치센서 및 이를 구비한 압축기
WO2003081040A1 (en) * 2002-03-21 2003-10-02 Empresa Brasileira De Compressores S.A. - Embraco A position sensor and a linear compressor
KR100891784B1 (ko) * 2002-03-21 2009-04-07 월풀 에쎄.아. 위치센서 및 선형압축기
WO2005064162A1 (en) * 2003-05-12 2005-07-14 Empresa Brasileira De Compressores S.A.-Embraco A proximity-sensor support, a compressor, a valve plate and a cooler
CN100445560C (zh) * 2003-05-12 2008-12-24 巴西压缩机股份有限公司 近程传感器支架、压缩机、阀板以及冷却器
US8628307B2 (en) 2003-05-12 2014-01-14 Empresa Brasileira de Compressores S.A.—Embraco Proximity-sensor support, a compressor, a valve plate and a cooler

Also Published As

Publication number Publication date
CN1067096A (zh) 1992-12-16
DE69205480T2 (de) 1996-04-18
DE69205480D1 (de) 1995-11-23
KR100216388B1 (ko) 1999-08-16
AU1477792A (en) 1992-10-15
CA2065831A1 (en) 1992-10-11
KR920020078A (ko) 1992-11-20
JPH04311685A (ja) 1992-11-04
CA2065831C (en) 1997-12-09
AU650960B2 (en) 1994-07-07
CN1029023C (zh) 1995-06-21
EP0508823B1 (de) 1995-10-18

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