EP0283963B1 - 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
EP0283963B1
EP0283963B1 EP88104389A EP88104389A EP0283963B1 EP 0283963 B1 EP0283963 B1 EP 0283963B1 EP 88104389 A EP88104389 A EP 88104389A EP 88104389 A EP88104389 A EP 88104389A EP 0283963 B1 EP0283963 B1 EP 0283963B1
Authority
EP
European Patent Office
Prior art keywords
chamber
compressor
plate
central bore
cylinder block
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 - Lifetime
Application number
EP88104389A
Other languages
German (de)
English (en)
Other versions
EP0283963A2 (fr
EP0283963A3 (en
Inventor
Hideto Kobayashi
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 EP0283963A2 publication Critical patent/EP0283963A2/fr
Publication of EP0283963A3 publication Critical patent/EP0283963A3/en
Application granted granted Critical
Publication of EP0283963B1 publication Critical patent/EP0283963B1/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
    • F04B25/00—Multi-stage pumps
    • 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a refrigerant compressor, and more particularly, to a wobble plate type piston compressor for an air conditioning system in which the compressor includes a mechanism for adjusting the capacity of the compressor.
  • thermal control is accomplished by intermittent operation of the compressor in response to a signal from a thermostat located in the room being cooled.
  • the refrigerant capacity of the air conditioning system generally need not be very large in order to handle supplementary cooling due to further temperature changes in the room or for keeping the room at the desired temperature.
  • the most common technique for controlling the output of the compressor is by intermittent operation of the compressor.
  • intermittent operation of the compressor results in intermittent application of a relatively large load to the driving mechanism of the compressor in order to drive the compressor.
  • the compressor In automobile air conditioning compressors, the compressor is driven by the engine of the automobile through an electromagnetic clutch. These automobile air conditioning compressors face the same intermittent load problems described above once the passenger compartment reaches a desired temperature. Control of the compressor normally is accomplished by intermittent operation of the compressor through the electromagnetic clutch which couples the automobile engine to the compressor. Thus, the relatively large load which is required to drive the compressor is intermittently applied to the automobile engine.
  • passageway 391 through cylinder block 101 tends to decrease the mechanical strength and structural integrity of cylinder block 101.
  • the mechanical strength and structural integrity of the cylinder block in a wobble plate type compressor is of considerable importance due to the high pressures which are present inside the cylinder block during operation of the compressor.
  • the diameter of the cylinder block 101 must be enlarged, further adding to manufacturing cost, weight and overall size of the compressor.
  • a refrigerant compressor is provided as indicated in claim 1.
  • One embodiment of this invention is providing a refrigerator compressor wherein the central bore connects a part of the communicating path with a female thread portion for an adjusting screw which adjusts the axial location of the compressor drive shaft.
  • Figure 1 is a vertical cross-sectional view of a refrigerant compressor according to one embodiment of this invention.
  • Figure 2 is a cross-sectional view taken substantially along line A-A of Figure 1.
  • Figure 3 is a vertical cross-sectional view of a refrigerant compressor according to a second embodiment of this invention.
  • Figure 4 is a vertical cross-sectional view of a refrigerant compressor according to a third embodiment of this invention.
  • Figure 5 is a vertical cross-sectional view of a refrigerant compressor according to a fourth embodiment of this invention.
  • Figure 6 is a vertical cross-sectional view of a refrigerant compressor according to a fifth embodiment of this invention.
  • Figure 7 is a cross-section view taken along line A-A of Figure 1 according to a sixth embodiment of this invention.
  • Figure 8 is a vertical cross-sectional view of a prior art refrigerant compressor.
  • the compressor 1 includes a closed cylindrical housing assembly 10 formed by a cylinder block 101, a crank chamber 13 within the cylinder block 101, a front end plate 11 and a rear end plate 25.
  • the front end plate 11 is mounted on the left end portion of the crank chamber 13, as shown in Figure 1, by a plurality of bolts (not shown).
  • the rear end plate 25 and a valve plate 24 are mounted on cylinder block 101 by a plurality of bolts (not shown).
  • An opening 111 is formed in front end plate 11 for receiving drive shaft 12.
  • Drive shaft 12 is rotatably supported by front end plate 11 through a bearing 20 which is disposed within opening 111.
  • the inner end portion of drive shaft 12 is also rotatably supported by cylinder block 101 through a bearing 23 which is disposed within a central bore 102.
  • Central bore 102 is a cavity formed in the center portion of cylinder block 101.
  • a thrust needle bearing 22a is disposed between the inner end surface of front end plate 11 and the adjacent axial end surface of a cam rotor (input drive rotor) 14.
  • Cam rotor 14 is fixed on drive shaft 12 by a pin member 15 which penetrates cam rotor 14 and drive shaft 12.
  • Cam rotor 14 is provided with an arm 141 having slot 142.
  • a slant plate 16 has an opening 161 through which passes drive shaft 12.
  • An axial annular projection 162 extends from the circumference of opening 161 in the front end surface of slant plate 16.
  • Slant plate 16 includes an arm 163 having a pin 21 which is inserted in slot 142.
  • Cam rotor 14 and slant plate 16 are joined by the hinged joint of pin 21 and slot 142. The pin 21 is able to slide within slot 142 so that the angular position of slant plate 16 can be changed with respect to the longitudinal axis of drive shaft 12.
  • a wobble plate 17 is rotatably mounted on slant plate 16.
  • the rotation of wobble plate 17 is prevented by a fork-shaped slider 172 which is attached to the outer peripheral end of wobble plate 17 and is slidably mounted on a sliding rail 173 held between front end plate 11 and cylinder block 101.
  • wobble plate 17 wobbles in a non-rotating manner in spite of the rotation of cam rotor 14.
  • Cylinder block 101 has a plurality of annularly arranged cylinder chambers 32 in which respective pistons 33 slide. All pistons 33 are connected to wobble plate 17 by a corresponding plurality of connecting rods 34. A ball 34a at one end of rod 34 is received in a socket 331 of pistons 33 and ball 34b at the other end of rod 34 is received in a socket 171 of wobble plate 17. It should be understood that, although only one such ball socket connection is shown in the drawing, there are a plurality of sockets arranged peripherally around wobble plate 17 to receive the balls of various rods, and that each piston 33 is formed with a socket for receiving the other ball of rods 34.
  • Rear end plate 25 is shaped to define suction chamber 35 and a discharge chamber 36.
  • the axial position of drive shaft 12 can be adjusted by an adjusting screw 27 into a threaded portion 41 of central bore 102. That is to say, the axial clearance between cam rotor 14 and front end plate 11 through bearing 22a can be adjusted by adjusting screw 27.
  • Central bore 102 is partitioned into a front chamber 102a and a rear chamber 102b by adjusting screw 27.
  • Front chamber 102a communicates with crank chamber 13.
  • a plurality of axial grooves 42 are formed at inner peripheral threaded portion 41 of central bore 102 to communicate between front chamber 102a and rear chamber 102b of central bore 102.
  • a groove 43 is formed at the front end surface of cylinder block 101 facing gasket 37. Groove 43 extends radially from rear chamber 102b of central bore 102 to a pressure sensitive chamber 44 which is formed in the cylinder block 101. Therefore the crank chamber 13 communicates with pressure sensitive chamber 44 through grooves 42 and groove 43. A hole 45 is formed through gasket 37, valve plate 24 and gasket 38 to connect pressure sensitive chamber 44 and suction chamber 35.
  • a bellows valve device 46 is fixed to one surface of pressure sensitive chamber 44 with a valve 461 arranged to close off hole 45 in response to the pressure within pressure sensitive chamber 44. The operation of bellows valve device 46 is as follows: The pressure within crank chamber 13 is communicated to pressure sensitive chamber 44 through grooves 42 and 43.
  • the pressure within pressure sensitive chamber 44 is the same as the pressure within crank chamber 13.
  • the bellows of the bellows valve device 46 expands causing valve 461 to close hole 45. Therefore when the compressor is not being driven, the pressure within crank chamber 13 is balanced pressure, valve 461 of the bellows valve device 46 closes the hole 45.
  • the bellows of bellows valve device 46 is compressed causing valve 461 to open hole 45.
  • drive shaft 12 is rotated by the engine of the vehicle through an electromagnetic clutch.
  • Cam rotor 14 is rotated together with drive shaft 12 to cause a non-rotating wobbling motion of wobble plate 17.
  • Rotating motion of wobble plate 17 is prevented by fork-shaped slider 172 which is attached to the outer peripheral end of wobble plate 17 and is slidably mounted on sliding rail 173 held between front end plate 11 and cylinder block 101.
  • a wobble plate 17 moves, pistons 33 reciprocate out of phase in their respective cylinders 32.
  • the refrigerant gas which is introduced into suction chamber 35 from a fluid inlet port 35a, is taken into each cylinder 32 and compressed.
  • the compressed refrigerant is discharged to discharge chamber 36 from each cylinder 32 through discharge port 24b, and therefrom into an external fluid circuit, for example, a cooling circuit, through a fluid outlet port 36b.
  • crank chamber 13 At the beginning of compressor operation, hole 45 is closed by valve 461 of the bellows valve device 46 because the pressure within crank chamber 13 is low. As the compressor operates, the pressure within crank chamber 13 gradually rises to create a small pressure difference between crank chamber 13 and suction chamber 35. This pressure difference occurs because blow-by gas, which leaks from the cylinder chambers to crank chamber 13 through a gap between pistons 33 and cylinders 32 during the compression stroke, is contained in crank chamber 13.
  • pistons 33 The movement of pistons 33 is hindered by the pressure difference between crank chamber 13 and suction chamber 35, i.e., as the pressure in the crank chamber approaches the mid-pressure of the compressed gas in the cylinder chambers during the suction stroke, movement of the pistons is hindered because the slant angle of slant plate 16 gradually decreases until it approaches zero, i.e., slant plate 16 would be perpendicular to the drive shaft 12. As the slant angle of slant plate 16 decreases, the stroke of pistons 33 in the cylinders 32 is reduced and the capacity of the compressor gradually decreases.
  • crank chamber 13 When the pressure of crank chamber 13 and pressure sensitive chamber 44 rises over the predetermined pressure, the bellows of bellows valve device 46 is sufficiently compressed and valve 461 of bellows valve device 46 opens hole 45. Simultaneously, crank chamber 13 communicates with suction chamber 35 through a central bore 102 via grooves 42 and groove 43 formed at the front end surface of cylinder block 101, pressure sensitive chamber 44 and hole 45. Accordingly, the pressure of crank chamber 13 falls to the pressure of suction chamber 35. In this condition, wobble plate 17 usually is urged toward slant plate 16 during the compression stroke of the pistons 33 so that slant plate 16 moves toward rotor 14.
  • the bellows valve device 46 is disposed in pressure sensitive chamber 44 formed in the cylinder block 101. Bellows valve device 46 also may be disposed in suction chamber 35 as shown in Figure 3. In the embodiment shown in Figure 3, the opening and closing of hole 45 are accordingly controlled by the change of pressure in suction chamber 35.
  • annular shim 51 is disposed between adjusting screw 27 screwed into the threaded portion 41 of central bore 102 and the inner end of the drive shaft 12. Shim 51 prevents friction which would otherwise occur by the contact of rotating drive shaft 12 with adjusting screw 27.
  • An annular thrust bearing 61 may also be used in place of shim 51 as shown in Figure 5.
  • a refrigerant compressor 1 is shown in accordance with a further embodiment of the present invention.
  • an electromagnetic valve 40 is disposed in suction chamber 35 in place of bellows valve device 46 which is shown in Figure 3.
  • an adjusting screw 271 is shown in accordance with another embodiment of the present invention.
  • a plurality of axial grooves 421 are formed at an outer peripheral surface of adjusting screw 271 to communicate the front chamber 102a and rear chamber 102b of central bore 102.

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

Claims (9)

  1. Compresseur (1) comprenant un carter (10) de compresseur comprenant un bloc cylindres (101) muni d'une pluralité de cylindres (32) et une chambre de manivelle (13) contenue dans ledit bloc cylindres (101), un piston (33) coulissant dans chacun desdits cylindres (32) et entraîné en mouvement alternatif par un mécanisme d'entraînement qui comprend un plateau oscillant (17), un rotor d'entraînement d'entrée (14) et un arbre d'entraînement (12) solidaire du rotor d'entraînement d'entrée (14), un plateau (16) à inclinaison réglable muni d'une surface inclinée, solidaire dudit rotor d'entraînement d'entrée (14) en formant avec lui un angle d'inclinaison réglable à grande proximité dudit plateau oscillant (17), un flasque d'extrémité avant (11) porté par le carter (10) du compresseur et comprenant un palier (20) qui supporte ledit arbre d'entraînement (12) libre en rotation, un flasque d'extrémité arrière (25) et une plaque de distributeur (24) qui sont disposés à l'extrémité opposée dudit carter (10) du compresseur, ledit flasque d'extrémité arrière (25) comprenant une chambre d'aspiration (35) et une chambre de refoulement (36), un perçage central (102) formé dans ledit bloc cylindres (101), dans lequel ledit arbre d'entraînement (12) est supporté libre en rotation, une vis de réglage (27) étant vissée dans ledit perçage central (102) pour régler la position axiale dudit arbre d'entraînement (12) et pour diviser ledit perçage central (102) en une chambre avant (102a) et une chambre arrière (102b), un passage de communication qui établit la communication entre ladite chambre de manivelle (13) et ladite chambre d'aspiration (35), des moyens (46) de commande d'obturateur commandant l'ouverture et la fermeture dudit passage de communication, l'angle de la surface inclinée dudit angle d'inclinaison réglable pouvant être modifié en réponse à la variation de la pression régnant dans ladite chambre de manivelle (13), ladite modification de la pression étant réalisée par lesdits moyens obturateurs (46) qui commandent l'ouverture et la fermeture dudit passage de communication, la course desdits pistons (33) dans lesdits cylindres (32) pouvant être modifiée par réglage de l'angle de pente de ladite plaque à inclinaison réglable (16), caractérisé en ce que ledit passage de communication est formé par un premier trou ou une première gorge (42,421) situé dans ledit perçage central (102) et qui relie ladite chambre avant (102a) à ladite chambre arrière (102b) dudit perçage central (102), et par une gorge (43) formée dans la surface d'extrémité dudit bloc cylindres (101) qui regarde ledit plateau de distributeur (24), et qui relie ladite chambre arrière (102b) dudit perçage central (102) à un deuxième trou (45) formé au niveau dudit plateau de distributeur (24) pour relier une première extrémité de ladite gorge (43) à ladite chambre d'aspiration (35).
  2. Compresseur de réfrigérant (1) selon la revendication 1, caractérisé en ce que lesdits moyens de commande d'obturateur (46) sont disposés dans une chambre (44) formée dans ledit bloc cylindres (101) et sont reliés à une première extrémité de ladite gorge (43) et audit deuxième trou (45).
  3. Compresseur de réfrigérant (1) selon la revendication 1, caractérisé en ce que lesdits moyens de commande d'obturateur (46) sont disposés dans ladite chambre d'aspiration (35).
  4. Compresseur de réfrigérant (1) selon une des revendications 1 à 3, caractérisé en ce que lesdits moyens de commande d'obturateur (46) sont constitués par une soupape à soufflet (46) qui capte la pression de ladite chambre de manivelle (13) ou de ladite chambre d'aspiration (35).
  5. Compresseur de réfrigérant (1) selon une des revendications 1 à 3, caractérisé en ce que lesdits moyens de commande d'obturateur (46) sont constitués par une valve électromagnétique (40).
  6. Compresseur de réfrigérant (1) selon une des revendications 1 à 5, caractérisé en ce que ledit premier trou ou ladite première gorge (42) est formé dans une surface périphérique intérieure dudit trou central (102).
  7. Compresseur de réfrigérant (1) selon une des revendications 1 à 5, caractérisé en ce que ledit premier trou (421) est formé dans une surface périphérique extérieure de ladite vis de réglage (27).
  8. Compresseur de réfrigérant (1) selon une des revendications 1 à 7, caractérisé en ce qu'une entretoise annulaire (51) est interposée entre ladite vis de réglage (27) et une extrémité intérieure dudit arbre d'entraînement (12).
  9. Compresseur de réfrigérant (1) selon une des revendications 1 à 7, caractérisé en ce qu'un palier de butée annulaire (61) est interposé entre ladite vis de réglage (27) et une extrémité intérieure dudit arbre d'entraînement (12).
EP88104389A 1987-03-24 1988-03-18 Compresseur à plateau en biais avec mécanisme à déplacement variable Expired - Lifetime EP0283963B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP42022/87U 1987-03-24
JP1987042022U JPH0649918Y2 (ja) 1987-03-24 1987-03-24 容量可変型圧縮機

Publications (3)

Publication Number Publication Date
EP0283963A2 EP0283963A2 (fr) 1988-09-28
EP0283963A3 EP0283963A3 (en) 1989-08-02
EP0283963B1 true EP0283963B1 (fr) 1991-07-31

Family

ID=12624541

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88104389A Expired - Lifetime EP0283963B1 (fr) 1987-03-24 1988-03-18 Compresseur à plateau en biais avec mécanisme à déplacement variable

Country Status (5)

Country Link
EP (1) EP0283963B1 (fr)
JP (1) JPH0649918Y2 (fr)
KR (1) KR960012113B1 (fr)
AU (1) AU606139B2 (fr)
DE (1) DE3863949D1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01142276A (ja) * 1987-11-27 1989-06-05 Sanden Corp 容量可変型斜板式圧縮機
JPH1162823A (ja) * 1997-08-08 1999-03-05 Sanden Corp 可変容量圧縮機
JPH1182300A (ja) * 1997-09-05 1999-03-26 Sanden Corp 可変容量圧縮機
JP2003028057A (ja) * 2001-07-13 2003-01-29 Toyota Industries Corp 可変容量型圧縮機における絞り構造
PL396589A1 (pl) 2011-10-10 2013-04-15 Janusz Marcin Ejma Maszyna z manipulatorem narzedzia, zwlaszcza narzedzia precyzyjnego
CN116557256A (zh) * 2023-07-10 2023-08-08 耐力股份有限公司 车用无油空气压缩机

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60135680A (ja) * 1983-12-23 1985-07-19 Sanden Corp 揺動式圧縮機
JPH0637874B2 (ja) * 1984-12-28 1994-05-18 株式会社豊田自動織機製作所 可変容量圧縮機
JPS61171886A (ja) * 1985-01-25 1986-08-02 Sanden Corp 容量可変型斜板式圧縮機
JPS61215468A (ja) * 1985-03-20 1986-09-25 Toyoda Autom Loom Works Ltd 可変容量圧縮機

Also Published As

Publication number Publication date
KR960012113B1 (ko) 1996-09-12
JPH0649918Y2 (ja) 1994-12-14
DE3863949D1 (de) 1991-09-05
AU606139B2 (en) 1991-01-31
EP0283963A2 (fr) 1988-09-28
JPS63150090U (fr) 1988-10-03
EP0283963A3 (en) 1989-08-02
KR880011469A (ko) 1988-10-28
AU1339788A (en) 1988-09-22

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