EP0318976A1 - Compresseur à plateau en biais avec mécanisme à déplacement variable - Google Patents

Compresseur à plateau en biais avec mécanisme à déplacement variable Download PDF

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Publication number
EP0318976A1
EP0318976A1 EP88120012A EP88120012A EP0318976A1 EP 0318976 A1 EP0318976 A1 EP 0318976A1 EP 88120012 A EP88120012 A EP 88120012A EP 88120012 A EP88120012 A EP 88120012A EP 0318976 A1 EP0318976 A1 EP 0318976A1
Authority
EP
European Patent Office
Prior art keywords
crank chamber
plate
cylinder block
compressor
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
EP88120012A
Other languages
German (de)
English (en)
Other versions
EP0318976B1 (fr
Inventor
Kiyoshi Terauchi
Shigemi 425 Higashi-Arai Shimizu
Kazuhiko Takai
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 EP0318976A1 publication Critical patent/EP0318976A1/fr
Application granted granted Critical
Publication of EP0318976B1 publication Critical patent/EP0318976B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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
    • F04B27/10—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
    • F04B27/109—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
    • 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
    • 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
    • F04B2027/189—Open (not controlling) fluid passage between crankcase and discharge chamber
    • 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
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]

Definitions

  • the present invention generally relates to a refrigerant compressor and, more particularly, to a slant plate type compressor, such as a wobble plate type compressor, with a variable displacement mechanism suitable for use in an automotive air conditioning system.
  • a wobble plate type compressor with a variable displacement mecha­nism suitable for use in an automotive air conditioning system is disclosed in U.S. Patent No. 3,861,829 issued to Roberts et al .
  • the compression ratio of the compressor may be controlled by changing the slant angle of the sloping surface of the wobble plate.
  • the slant angle of the wob­ble plate is adjusted so as to maintain a constant suction pressure in response to changes in the pressure differential between the suction chamber and the crank chamber.
  • the difference in pressure between the suction chamber and the crank chamber is generated by a valve control mechanism which controls communication between the suction chamber and the crank cham­ber.
  • the valve control mechanism varies the crank chamber pressure in response to the suction chamber pressure.
  • crank chamber pressure which generates the changes in the slant angle of the wobble plate is obtained by compressed refrigerant gas which passes through a gap between the cylinder and the piston.
  • This gap is due to the use of a cast iron piston ring disposed at an outer peripheral surface of an aluminum allow piston housed within a cast iron lined cylinder.
  • cylinder blocks have been formed of aluminum allows in order to reduce the weight of the compressor.
  • a seamless piston ring made of polytetrafluoroethylene resin has been disposed at an outer peripheral surface of the piston to prevent wear of both the piston and the cylinder block due to friction therebetween.
  • the piston rings enlarge due to swelling during use, thereby significantly reducing the amount of compressed refrigerant gas which is passed to the crank chamber. It is therefore difficult to obtain a crank chamber pressure which satisfactorily generates appropriate changes in the slant angle of the wobble plate.
  • U.S. Patent No. 4,428,718 discloses a valve control mechanism respon­sive to both suction and discharge pressures which controls communication of these pressures with the compressor crank chamber to control compressor displacement.
  • extremely precise machining of the component parts and accurate assembly thereof are required.
  • an increased amount of discharge gas flows into the crank chamber through a communication passage of the valve control mechanism due to a lag between the action of the valve control mechanism and the response of the external circuit including the compressor.
  • the efficiency of the compressor decreases and the dura­bility of the compressor components is reduced.
  • the type of capacity adjustment described above using fluid communi­cation between the discharge chamber and the crank chamber may be used in any type of compressor which uses a slanted plate or surface in the drive mechanism.
  • U.S. Patent No. 4,664,804 to Terauchi discloses a swash plate type compressor.
  • the swash plate like the wobble plate, is dis­posed at a slant angle and drivingly couples the pistons to the drive source.
  • the wobble plate only nutates
  • the swash plate both nutates and rotates.
  • the term slant plate type compressor will therefore be used herein to refer to any type of compressor, including wobble and swash plate types, which use a slanted plate or surface in the drive mechanism.
  • variable capacity slant plate type compressor which generates the appropriate changes in the slant angle of the slant plate.
  • the slant plate type compressor in accordance with the present invention includes a compressor housing having a cylinder block with a front end plate and a rear end plate attached thereto.
  • a crank chamber is defined between the front end plate and the cylinder block and a plurality of cylin­ders are formed in the cylinder block.
  • a piston is slidably fitted within 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 compressor housing, a rotor coupled to the drive shaft and rotatable therewith, and a coupling mechanism for drivingly cou­pling the rotor to the pistons such that they rotary motion of the rotor is converted into reciprocating motion of the pistons.
  • the coupling mechanism includes a plate having a surface disposed at a slant angle relative to the drive shaft. The slant angle changes in response to a change in pressure in the crank chamber to change the capacity of the compressor.
  • the rear end plate includes a suction chamber and a discharge cham­ber defined therein.
  • a first communication path links the crank chamber with the suction chamber.
  • a valve control mechanism controls the opening and closing of the communication path to generate changes in pressure in the crank chamber.
  • a second communication path formed in the cylinder block links the crank chamber with the discharge chamber.
  • a flow control mechanism formed in the second communication path controls the flow of refrigerant gas from the discharge chamber to the crank chamber.
  • the flow control mechanism includes a mechanism for reducing the pressure of refrig­erant gas which flows from the discharge chamber to the crank chamber in order to control the slant angle of the slant plate.
  • Compressor 10 includes cylindrical housing assembly 20 including cylinder block 21, front end plate 23 disposed at one end of cylinder block 21, crank chamber 22 formed between cylinder block 21 and front end plate 23, and rear end plate 24 attached to the other end of cylinder block 21.
  • Front end plate 23 is secured to one end of cylinder block 21 by a plurality of bolts 101.
  • Rear end plate 24 is secured to the opposite end of cylinder block 21 by a plurality of bolts 102.
  • Valve plate 25 is disposed between rear end plate 24 and cylinder block 21. Opening 231 is formed centrally in front end plate 28 for support­ing drive shaft 26 through bearing 30 disposed therein.
  • drive shaft 26 is rotatably supported by bearing 31 disposed within central bore 210 of cylinder block 21.
  • Bore 210 extends to a rearward (to the right in Figure 1) and surface of cylinder block 21 and houses valve control mechanism 19 described in detail below.
  • Cam rotor 40 is fixed on drive shaft 26 by pin member 261 and rotates therewith.
  • Thrust needle bearing 32 is disposed between the inner end sur­face of front end plate 23 and the adjacent axial end surface of cam rotor 40.
  • Cam rotor 40 includes arm 41 having pin member 42 extending there­from.
  • Slant plate 50 is disposed adjacent cam rotor 40 and includes opening 53 through which drive shaft 26 passes.
  • Slant plate 30 includes arm 51 hav­ing slot 52.
  • Cam rotor 40 and slant plate 30 are coupled by pin member 42 which is inserted in slot 52 to form a hinged joint. Pin member 42 slides within slot 52 to allow adjustment of the angular position of slant plate 30 with respect to the longitudinal axis of drive shaft 26.
  • Wobble plate 60 is rotatably mounted on slant plate 50 through bear­ings 61 and 62.
  • Fork shaped slider 63 is attached to the outer peripheral end of wobble plate 60 by pin member 64 and is slidably mounted on sliding rail 65 disposed between front end plate 23 and cylinder block 21.
  • Fork shaped slider 63 prevents rotation of wobble plate 60.
  • Wobble plate 60 nutates along rail 65 when cam rotor 40 rotates.
  • Cylinder block 21 includes a plurality of peripherally located cylinder chambers 70 in which pistons 71 reciprocate. Each piston 71 is coupled to wobble plate 60 by a corresponding connecting rod 72.
  • a pair of seamless piston rings 73 made of polytetrafluoroethylene is disposed at an outer peripheral surface of piston 71. Piston rings 73 prevent the wear of both aluminum alloy piston 71 and aluminum allow cylinder block 21 due to friction therebetween and prevent any direct contact between piston 71 and the inner surface of cylinder 70.
  • Rear end plate 24 includes peripherally positioned annular suction chamber 241 and centrally positioned discharge chamber 251.
  • Valve plate 25 is located between cylinder block 21 and rear end plate 24 and includes a plurality of valved suction ports 242 linking suction chamber 241 with respective cylinders 70.
  • Valve plate 25 also includes a plurality of valved discharge ports 252 linking discharge chamber 251 with respective cylinders 70.
  • Suction ports 242 and discharge ports 252 are provided with suitable reed valves as described in U.S. Patent No. 4,011,029 to Shimizu.
  • Suction chamber 241 includes inlet portion 241a which is connected to an evaporator of an external cooling circuit (not shown).
  • Discharge chamber 251 is provided with outlet portion 251a connected to a condenser of the cooling circuit (not shown).
  • Gaskets 27 and 28 are positioned between cylin­der block 21 and the inner surface of valve plate 25 and the outer surface of valve plate 25 and rear end plate 24 respectively. Gaskets 27 and 28 seal the mating surfaces of cylinder block 21, vale plate 25 and rear end plate 24.
  • a first communication path between the crank chamber and the suc­tion chamber is formed in the cylinder block.
  • This first communication path includes valve control mechanism 19 which includes cup-shaped casing member 191 which defines valve chamber 192 therein.
  • O-ring 19a is dis­posed between an outer surface of casing member 191 and an inner surface of bore 210 to seal the mating surface of casing member 191 and cylinder block 21.
  • a plurality of holes 19b is formed at the closed end (to the left in Figure 1) of cup-shaped casing member 191 to permit crank chamber pres­sure into valve chamber 192 through gap 31a existing between bearing 31 and cylinder block 21.
  • Circular plate 194 having hole 194a formed at the center thereof is fixed to the open end of cup-shaped casing member 191.
  • Bellows 193 is disposed within valve chamber 192 and contracts and expands longitudinally in response to the crank chamber pressure.
  • the forward (to the left in Figure 1) end of bellows 193 is fixed to the closed end of casing member 191.
  • Valve member 193a is attached at rearward (to the right in Figure 1) end of bellows 193 to selectively control the opening and closing of hole 194a.
  • Valve chamber 192 and suction chamber 241 are linked by hole 194a, bore portion 211 of bore 210, conduit 195 formed in cylinder block 21 and hole 196 formed in valve plate assembly 200.
  • Valve plate assembly 200 includes valve plate 25 and gaskets 27 and 28.
  • Valve retainer 13 is secured to the rear end surface of valve plate assembly 200 by bolt 151.
  • Communication path 18 which is bored longitudinally from a forward end surface of cylinder block 21 to a rear end surface of valve retainer 15, is a second communication path formed in the cylinder block to link discharge chamber 251 to crank chamber 22.
  • Communication path 18 controls the flow of refrigerant gas from discharge chamber 251 to crank chamber 22.
  • Large diameter conduit portion 181 of communication path 18 has filter screen 182 disposed therein.
  • Capillary tube 183 which performs a throttling function to reduce the pressure of refrigerant gas passing from discharge chamber 251 to crank chamber 22, is fixed within communication path 18 and is coupled to filter screen 182.
  • drive shaft 26 is rotated by the engine of the vehicle (not shown) through electromagnetic clutch 300.
  • Cam rotor 40 is rotated with drive shaft 28 causing slant plate 50 to rotate.
  • the rotation of slant plate 50 causes wobble plate 60 to nutate.
  • the nutating motion of wobble plate 60 reciprocates pistons 71 in their respective cylin­ders 70.
  • pistons 71 are reciprocated, refrigerant gas which is introduced into suction chamber 241 through inlet portion 241a is drawn into cylinders 70 through suction ports 242 and subsequently compressed.
  • the compressed refrigerant gas is discharged from cylinders 70 to discharge chamber 251 through respective discharge ports 252 and then into the cooling circuit through outlet portion 251a.
  • a portion of the discharged refrigerant gas in discharge chamber 251 flows into crank chamber 22 through conduit 18 with a reduced pressure generated by capillary tube 183.
  • Valve control mechanism 19 is responsive to the reduced discharge gas pressure in crank chamber 22.
  • hole 194a When the reduced discharge gas pressure in crank chamber 22 exceeds a predetermined value, hole 194a is opened by the contraction of bellows 193. The opening of hole 194a permits communi­cation between crank chamber 22 and suction chamber 241. As a result, the slant angle of slant plate 50 is maximized to maximize the displacement of the compressor.
  • hole 194a is closed by valve member 193a attached to bellows 193. This action blocks communication between crank chamber 22 and suction chamber 241.
  • the slant angle of slant plate 50 is controlled by changes in the reduced discharge gas pressure admitted to crank chamber 22 via communication path 18 to vary the displacement of the compressor.
  • the variation of the slant angle of slant plate 50 is disclosed in DE-A 35 06 060, especially on page 11, line 19 to page 13, line 16, and in EP-A 0 281 819.
  • Figure 2 illustrates a second embodiment of the present invention in which the same numerals are used to denote the corresponding elements shown in Figure 1.
  • a small diameter narrowed portion 184 of communication path 18 performs the throttling function to reduce the pressure of discharged refrigerant gas admitted to crank chamber 22.
  • the pressure reduction (decompression) generated as the refrigerant gas flows from discharge chamber 251 to crank chamber 22 through commu­nication path 18 is determined by the inner diameter and length of capillary tube 183 or narrowed portion 184. Thus, the amount of decompression desired may be fixed through the choice of these dimensions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP88120012A 1987-11-30 1988-11-30 Compresseur à plateau en biais avec mécanisme à déplacement variable Expired - Lifetime EP0318976B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP303050/87 1987-11-30
JP62303050A JPH01142277A (ja) 1987-11-30 1987-11-30 容量可変圧縮機

Publications (2)

Publication Number Publication Date
EP0318976A1 true EP0318976A1 (fr) 1989-06-07
EP0318976B1 EP0318976B1 (fr) 1992-05-13

Family

ID=17916313

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88120012A Expired - Lifetime EP0318976B1 (fr) 1987-11-30 1988-11-30 Compresseur à plateau en biais avec mécanisme à déplacement variable

Country Status (6)

Country Link
EP (1) EP0318976B1 (fr)
JP (1) JPH01142277A (fr)
KR (1) KR0129542B1 (fr)
AU (1) AU608668B2 (fr)
CA (1) CA1331369C (fr)
DE (1) DE3871093D1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0623744A1 (fr) * 1993-03-12 1994-11-09 Sanden Corporation Compresseur à plateau en biais avec mécanisme à déplacement variable
US5588807A (en) * 1992-11-12 1996-12-31 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
EP0844393A1 (fr) * 1996-11-25 1998-05-27 Sanden Corporation Compresseur à plateau en biais à capacité variable
DE19847159A1 (de) * 1998-10-13 2000-04-20 Hans Unger Kompressor zur Erzeugung ölfreier Druckluft

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0462279U (fr) * 1990-10-09 1992-05-28
JPH0489873U (fr) * 1990-12-15 1992-08-05
US5380161A (en) * 1992-12-11 1995-01-10 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash-plate compressor with electromagnetic clutch
JP3178630B2 (ja) * 1992-12-21 2001-06-25 株式会社豊田自動織機製作所 可変容量型圧縮機
US6325598B1 (en) * 1999-12-23 2001-12-04 Visteon Global Technologies, Inc. Variable capacity swash plate type compressor having pressure relief valve
CN113958494B (zh) * 2021-09-17 2023-07-25 北京化工大学 一种驱动端调速与气缸卸载融合的排气量调节方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4428718A (en) * 1982-02-25 1984-01-31 General Motors Corporation Variable displacement compressor control valve arrangement
DE3711979A1 (de) * 1986-04-09 1987-10-15 Toyoda Automatic Loom Works Taumelscheibenkompressor mit variabler foerderleistung
US4752189A (en) * 1986-12-09 1988-06-21 Diesel Kiki Co., Ltd. Valve arrangement for a variable displacement compressor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4428718A (en) * 1982-02-25 1984-01-31 General Motors Corporation Variable displacement compressor control valve arrangement
DE3711979A1 (de) * 1986-04-09 1987-10-15 Toyoda Automatic Loom Works Taumelscheibenkompressor mit variabler foerderleistung
US4752189A (en) * 1986-12-09 1988-06-21 Diesel Kiki Co., Ltd. Valve arrangement for a variable displacement compressor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5588807A (en) * 1992-11-12 1996-12-31 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
DE4395830C2 (de) * 1992-11-12 1998-05-28 Toyoda Automatic Loom Works Verstellkompressor
EP0623744A1 (fr) * 1993-03-12 1994-11-09 Sanden Corporation Compresseur à plateau en biais avec mécanisme à déplacement variable
EP0844393A1 (fr) * 1996-11-25 1998-05-27 Sanden Corporation Compresseur à plateau en biais à capacité variable
DE19847159A1 (de) * 1998-10-13 2000-04-20 Hans Unger Kompressor zur Erzeugung ölfreier Druckluft
US6318502B1 (en) 1998-10-13 2001-11-20 Hans Unger Compressor for producing oil-free compressed air
DE19847159C2 (de) * 1998-10-13 2001-12-06 Hans Unger Kompressor zur Erzeugung ölfreier Druckluft

Also Published As

Publication number Publication date
DE3871093D1 (de) 1992-06-17
KR890008450A (ko) 1989-07-10
AU2638788A (en) 1989-06-01
AU608668B2 (en) 1991-04-11
JPH0232479B2 (fr) 1990-07-20
KR0129542B1 (ko) 1998-04-08
JPH01142277A (ja) 1989-06-05
CA1331369C (fr) 1994-08-09
EP0318976B1 (fr) 1992-05-13

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