EP0207613B1 - Taumelscheibenverdichter mit veränderlicher Fördermenge - Google Patents

Taumelscheibenverdichter mit veränderlicher Fördermenge Download PDF

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Publication number
EP0207613B1
EP0207613B1 EP19860303825 EP86303825A EP0207613B1 EP 0207613 B1 EP0207613 B1 EP 0207613B1 EP 19860303825 EP19860303825 EP 19860303825 EP 86303825 A EP86303825 A EP 86303825A EP 0207613 B1 EP0207613 B1 EP 0207613B1
Authority
EP
European Patent Office
Prior art keywords
slider
wobble plate
pistons
chamber
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19860303825
Other languages
English (en)
French (fr)
Other versions
EP0207613A1 (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 EP0207613A1 publication Critical patent/EP0207613A1/de
Application granted granted Critical
Publication of EP0207613B1 publication Critical patent/EP0207613B1/de
Expired 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
    • F04B27/10—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
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms
    • 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
    • F04B2027/1854—External parameters

Definitions

  • the present invention relates to a wobble plate type compressor for a refrigerating system, and more particularly to a variable capacity mechanism utilized on such compressors.
  • Wobble plate type compressors which reciprocate pistons by changing the rotational movement of a cam rotor into the wobble movement of a wobble plate are well-known.
  • Variable capacity mechanisms in which the compression capacity changed by altering the stroke volume of pistons by changing the angle of the inclined surface of the cam rotor are also well-known, as shown in US-A-3861829.
  • variable capacity mechanism the angle of the inclined surface of the cam rotor is changed by differential pressure between a crank chamber, in which the cam rotor is disposed, and a suction chamber, thus changing the stroke volume of the pistons and in turn changing the compression capacity of the compressor.
  • the volume of the crank chamber is larger than that of the suction chamber. For this reason, the response for the angle of the inclined surface of the cam rotor is not sufficient.
  • the oil may flow into the crank chamber from the suction chamber.
  • a variable capacity compressor which does not use the differential pressure between the crank chamber and the suction chamber, so as to resolve the above-mentioned problems, is shown in US-A-4061443.
  • a modulating cylinder for controlling the angle of the inclined surface of the cam rotor is disposed in the crank chamber and connects with a compressor sump area through a rear head return bore, a valve plate slot, a hole, a valve disc hole, a cylinder block axial return bore, a crossover tube, aligned axial bore, radial bore, aperture, shaft radial front bore and shaft front radial exit bore in series.
  • Lubricating oil flowing into the modulating cylinder is compressed by an oil gear pump assembly disposed in the cylinder block.
  • the modulating cylinder is operated by the pressure of lubricating oil and the angle of the inclined surface of the cam rotor is varied in accordance with the operation of the modulating cylinder.
  • the modulating cylinder in the above mentioned compressor is disposed in the crank chamber, the crank chamber must be large to accommodate it. Accordingly, the size of such a compressor is larger than that of a conventional compressor.
  • a further object is to provide a wobble plate type compressor with a variable capacity mechanism which includes an actuator for changing the stroke volume of pistons in the centre of a cylinder block.
  • a wobble plate type compressor with a variable capacity mechanism including a plurality of pistons reciprocating in cylinder bores of a cylinder block, the wobble plate changing rotational movement into wobble movement and reciprocating the pistons through piston rods connecting the pistons with the wobble plate; a cam rotor connected to the drive shaft; by a disc member connected to the cam rotor for rotation with the shaft by means of a link portion formed on the disc member and having a hole receiving a pin slidably disposed in an elongate hole in the cam rotor, the disc member having a slider slidably disposed around the drive shaft; an actuator, for changing the angle of the disc member and the wobble plate by moving the slider, an electromagnetic valve, and thus changing the stroke volume of the pistons, characterised in that the actuator is disposed in the centre of the cylinder block, is operated by the differential pressure between the crank chamber and the discharge chamber, the pressure from the discharge chamber being applied through an electromagnetic valve.
  • Figure 1 shows a wobble plate type compressor 1 including a front housing 2, cylinder casing 3 having a cylinder block 31, valve plate 4 and cylinder head 5.
  • the front housing 2 is fixed on one end surface of the casing 3 by bolts 6.
  • An axial hole 21 is formed through the front housing 2 at the centre thereof for receiving the drive shaft 7.
  • a radial bearing 8 is disposed in the hole 21 to support drive shaft 7 rotatably.
  • a sleeve portion 22 projects from front housing 2 and surrounds drive shaft 7 to define a seal cavity 23 in which is disposed a mechanical seal 9.
  • the cylinder housing 3 is also provided with a crank chamber 32 at the opposite end from the cylinder block 31.
  • cam rotor 10 is fixed to the inner end of drive shaft 7 and a thrust needle bearing 11 is disposed between the inner wall surface of front housing 2 and the adjacent axial end surface.
  • An ear-shaped portion 101 of cam rotor 10 extends in the direction of cylinder block 31 and a rectangular shaped hole 102 is formed in the ear-shaped portion 101.
  • An ear-shaped portion 122 is formed on the outer surface of the flange portion 121 of cylinder member 12 so as to face the ear shaped portion 101 of cam rotor 10.
  • a hole 123 is formed on ear-shaped portion 122 at a position adjacent to that of the rectangular-shaped hole 102 and a pin-shaped member 13 fitted into hole 123 is inserted into rectangular-shaped hole 102 to slidably move along the inner edge of the long hole 102.
  • Ring-shaped wobble plate 14 is mounted on the outer surface of cylinder member 12 through a radial needle bearing 15.
  • a thrust needle bearing 16 is disposed in a gap between the flange portion 121 and ring-shaped wobble plate 14.
  • the other end of drive shaft 7 is rotatably supported by a radial ball bearing 17 disposed in the centre bore of cylinder block 31.
  • a sliding shaft 141 is fixed into wobble plate 14 and projected in the direction of the bottom surface of the cylinder casing 3.
  • An axially extended groove 321 is disposed along the path of motion of the sliding shaft 141, the end of which is disposed in the groove 321 and slides along the inner edge of groove 321, thereby to prevent rotating motion of the wobble plate 14.
  • piston rods 17' is rotatably connected to receiving surfaces 142 of the wobble plate 14 and the other ends of the piston rods 17 are rotatably connected to pistons 18 slidably disposed in cylinder bores 33.
  • Suction holes 19 and discharge holes 20 are formed in valve plate 4.
  • a suction reed valve (not shown) is disposed on the valve plate 4 and a discharge reed valve (not shown) is disposed on the valve plate 4 at the opposite side to the suction reed valve.
  • the cylinder head 5 is connected to cylinder casing 3 through gasket 41 and valve plate 4.
  • An axially extending partition wall 51 is formed in the inner surface of cylinder head 5 and divides the interior of cylinder head 5 into two chambers, such as a suction chamber 52 and discharge chamber 53.
  • a slider 24 is slidably disposed on the outer surface of the drive shaft 7 and is connected to cylinder member 12 so that the cylinder member 12 is rotatably and slidably disposed on drive shaft 7.
  • Coil spring 25 is disposed between cam rotor 10 and one end of slider 24 surrounding the drive shaft 7.
  • Actuator 26 which comprises a disc-shaped plunger 261, coil spring 262 and pressure chamber 263, is disposed on an inner terminal end of drive shaft 7.
  • the disc-shaped plunger 261 is slidably disposed on the inner end of drive shaft 7 so that it closes the opening of pressure chamber 263 which is formed on the outer end portion of central bore of cylinder block 31, and is in sliding contact with cylinder block 31 and normally pushed towards the crank chamber by coil spring 262.
  • the other end of slider 24 is connected to disc-shaped plunger 261 through thrust needle bearing 27 so that the rotational force of slider 24 cannot be communicated to the plunger 261 and the axial force of plunger 261 can be transmitted to the slider 24.
  • An aperture 311 which connects pressure chamber 262 with discharge chamber 53 is formed through cylinder block 31.
  • the opening and closing of aperture 311 is controlled by an electromagnetic valve 28.
  • Valve seat 29 is disposed on valve plate 4 at the side of discharge chamber 53 to seat a valve portion 281 of electromagnetic valve 28.
  • the gas pressure ⁇ Fpi urges pistons 18 to the left as seen and, if the force with which coil spring 125 urges slider 24 to the right is expressed as Fsp, the force with which plunger 261 (not shown in Figure 2) urges slider 24 to the left is expressed as Fc, the drag at the supporting portion of pin-shaped member 13 is expressed as F L , and the coefficient of friction between drive shaft 7 and slider 25 is expressed as u, the gross gas pressure ⁇ Fpi can be determined from the following equation. Where P is the angle made by the drag F L with the Y axis, and Fp is the gas pressure on the rear of the piston. Fp can be determined from the following equation, (where n is the number of pistons, D is the diameter of the pistons, and Pc is the pressure in the crank chamber).
  • F R is the force component of the drag F L which is othogonal to the drive shaft 7
  • the distance between the acting point (P) of the force given to the supporting portion of pin-shaped member 13 and the underside of drive shaft 7 is L1
  • the distance between the acting point (P) and ⁇ Fpi is L2
  • the distance between the acting point (P) and the centre axis of drive shaft 7 is L3
  • the distance between the acting point (P) and the component F R is L4
  • Cylinder member 12 and wobble plate 14 are inclined so that the moment can be balanced.
  • pressure chamber 263 is connected to discharge chamber 53 through aperture 311 by opening of electromagnetic valve 28. Since high pressure compressed gas from discharge chamber 53 flows into pressure chamber 263 through aperture 311, the pressure in pressure chamber 263 is increased. Accordingly, plunger 261 is moved to the left as shown against the tensile stress of coil spring 262 and the urging force of coil spring 25, and slider 24 is moved to the left. Since slider 24 and cylindrical member 12 are freely connected, cylindrical member 12 receives the moment of right-handed rotation by movement of slider 24, and cylindrical member 12 is inclined so as to satisfy formula (3).
  • bellows 34 is disposed instead of actuator 26 in the compressor shown in Figure 1.
  • Bellows 34 is connected to discharge chamber 53 through electromagnetic valve 28.
  • Slider 24 is moved whereby bellows 34 is shrunken or swollen by opening or closing electromagnetic valve 28. Accordingly, the angle of the inclined surface of cylindrical member 12 is varied.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (3)

1. Taumelscheibenverdichter mit einem Mechanismus für veränderliche Fördermenge mit einer Mehrzahl von sich in Zylinderbohrungen eines Zylinderblockes (31) hin- und herbewegenden Kolben (18), wobei die Taumelscheiben (14) Drehbewegung in Taumelbewegung ändert und die Kolben durch Kolbenstangen (17'), die die Kolben mit der Taumelscheibe verbinden, hin- und herbewegt; einem mit der Antriebswelle (7) verbundenen Nockenrotor (10); einem Scheibenteil (221), das mit dem Nockenrotor zum Drehen mit der Welle (7) mit Hilfe eines Verbindungsabschnittes (122) verbunden ist, der auf dem Scheibenteil gebildet ist und ein Loch (123) aufweist, das einen Stift (13) aufnimmt, der verschiebbar in einem länglichen Loch (102) in dem Nockenrotor angeordnet ist, wobei das Scheibenteil (121) einen verschiebbar um die Antriebswelle angebrachten Rutscher (24) aufweist; einem Betätigungselement (26) zum Ändern des Winkels des Scheibenteiles und der Taumelscheibe durch Bewegen des Rutschers (24) und somit Ändern des Hubvolumens der Kolben, dadurch gekennzeichnet, daß das Betätigungselement (26) in dem Zentrum des Zylinderblockes (31) angeordnet ist, durch den differentiellen Druck zwischen der Kurbelkammer (32) und der Entleerungskammer (53) betätigt wird, wobei der Druck in der Entleerungskammer durch ein elektromagnetisches Ventil (28) angelegt ist.
2. Kompressor nach Anspruch 1, indem das Betätigungselement eine mit der Entleerungskammer (53) durch eine Öffnung verbundene Druckkammer (263); einen mit dem Rutscher durch ein Drucknadellager (27) verbundenen Kolbenmechanismus (261) aufweist; und das elektromagnetische Ventil (28) den Kolbenmechanismus zum Verschieben des Rutschers durch Öffnen oder Schließen der Öffnung zwischen der Druckkammer und der Entleerungskammer betätigt.
3. Kompressor nach Anspruch 1, bei dem das Betätigungselement einen mit dem Rutscher durch ein Drucknadellager (27) verbundenen Balagen (34) aufweist, der Ventilmechanismus den Balgen zum Verschieben des Rutschers gemäß des Gasdruckflusses in den Balgen durch Öffnen oder Schließen der Öffnung zwischen dem Inneren des Balgens und der Entleerungskammer betätigt.
EP19860303825 1985-05-20 1986-05-20 Taumelscheibenverdichter mit veränderlicher Fördermenge Expired EP0207613B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP1985073575U JPH037583Y2 (de) 1985-05-20 1985-05-20
JP73575/85 1985-05-20

Publications (2)

Publication Number Publication Date
EP0207613A1 EP0207613A1 (de) 1987-01-07
EP0207613B1 true EP0207613B1 (de) 1988-12-14

Family

ID=13522220

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860303825 Expired EP0207613B1 (de) 1985-05-20 1986-05-20 Taumelscheibenverdichter mit veränderlicher Fördermenge

Country Status (5)

Country Link
EP (1) EP0207613B1 (de)
JP (1) JPH037583Y2 (de)
DE (1) DE3661434D1 (de)
IN (1) IN165913B (de)
SG (1) SG25791G (de)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BR8704487A (pt) * 1986-09-02 1988-04-19 Nippon Denso Co Compressor do tipo de placa oscilante de deslocamento variavel
US4875834A (en) * 1987-02-19 1989-10-24 Sanden Corporation Wobble plate type compressor with variable displacement mechanism
JPH0223829Y2 (de) * 1987-05-19 1990-06-28
DE68905641T2 (de) * 1988-04-20 1993-07-08 Honda Motor Co Ltd Steuerzylinder in einem kompressor mit veraenderlicher foerdermenge.
JPH0633769B2 (ja) * 1988-04-20 1994-05-02 本田技研工業株式会社 可変容量式圧縮機における始動時の容量設定装置
JPH10148177A (ja) * 1996-11-20 1998-06-02 Toyota Autom Loom Works Ltd 可変容量型圧縮機
JP4506031B2 (ja) * 2001-05-22 2010-07-21 株式会社日本自動車部品総合研究所 可変容量式圧縮機
JP6003547B2 (ja) * 2012-11-05 2016-10-05 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6028525B2 (ja) * 2012-11-05 2016-11-16 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6003546B2 (ja) * 2012-11-05 2016-10-05 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6015614B2 (ja) * 2013-09-25 2016-10-26 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP2016098679A (ja) * 2014-11-19 2016-05-30 株式会社豊田自動織機 容量可変型斜板式圧縮機

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2711135A (en) * 1952-10-06 1955-06-21 Ollen L Dunlap Wabble plate type pump
US2964234A (en) * 1954-05-13 1960-12-13 Houdaille Industries Inc Constant clearance volume compressor
JPS58162782A (ja) * 1982-03-20 1983-09-27 Toyoda Autom Loom Works Ltd 可変容量型斜板圧縮機
US4526516A (en) * 1983-02-17 1985-07-02 Diesel Kiki Co., Ltd. Variable capacity wobble plate compressor capable of controlling angularity of wobble plate with high responsiveness

Also Published As

Publication number Publication date
JPS61190483U (de) 1986-11-27
EP0207613A1 (de) 1987-01-07
SG25791G (en) 1991-06-21
IN165913B (de) 1990-02-10
DE3661434D1 (en) 1989-01-19
JPH037583Y2 (de) 1991-02-25

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