WO2002055878A1 - Compresseur frigorifique a double action - Google Patents

Compresseur frigorifique a double action Download PDF

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Publication number
WO2002055878A1
WO2002055878A1 PCT/JP2001/000188 JP0100188W WO02055878A1 WO 2002055878 A1 WO2002055878 A1 WO 2002055878A1 JP 0100188 W JP0100188 W JP 0100188W WO 02055878 A1 WO02055878 A1 WO 02055878A1
Authority
WO
WIPO (PCT)
Prior art keywords
suction
valve
cylinder
depth
recess
Prior art date
Application number
PCT/JP2001/000188
Other languages
English (en)
Japanese (ja)
Inventor
Ryosuke Izawa
Minoru Kanaizuka
Katsuhiko Arai
Katsumi Sakamoto
Original Assignee
Zexel Valeo Climate Control Corporation
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 Zexel Valeo Climate Control Corporation filed Critical Zexel Valeo Climate Control Corporation
Priority to US10/460,963 priority Critical patent/US20040052665A1/en
Priority to PCT/JP2001/000188 priority patent/WO2002055878A1/fr
Publication of WO2002055878A1 publication Critical patent/WO2002055878A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • 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
    • F04B27/1009—Distribution members

Definitions

  • the present invention relates to a reciprocating type refrigerant compressor used as a refrigerant compressor of an air conditioner for automobiles, wherein a piston reciprocates, for example, as a wobble plate type compressor or a swash plate type compressor.
  • a reciprocating type refrigerant compressor used as a refrigerant compressor of an air conditioner for automobiles, wherein a piston reciprocates, for example, as a wobble plate type compressor or a swash plate type compressor.
  • the oscillating plate type compressor includes a cylinder block having a plurality of cylinder pores, a plurality of pistons reciprocating in the cylinder pore, and a valve plate attached to an end surface of the cylinder block. It has a fixed cylinder head and a plurality of suction valves for opening and closing a plurality of suction ports formed in a valve plate.
  • a compression chamber is formed inside the cylinder, and the volume of the compression chamber changes as the piston moves.
  • a suction chamber is formed in the cylinder head to contain low-pressure refrigerant gas flowing from the evaporator side.
  • the number of suction valves and the number of suction ports in the valve plate, as well as the number of compression chambers and pistons, are each equal to the number of cylinder pores.
  • the suction chamber communicates with the compression chamber via the suction port.
  • Fig. 13 is a partially enlarged plan view of the valve plate of a conventional rocking plate compressor.
  • a suction port 315 is formed in the valve plate 302, and a discharge port 305 is formed inside the suction port 315 (radially inside the valve plate 302). 16 are formed.
  • a hole 363 is formed in the suction valve 321 so that the discharge port 316 is not closed by the suction valve 321.
  • the stopper recess 3 is located at the position where the cylinder pore opening ⁇ 306a faces the projection 321d of the suction valve 3221.
  • the depth dimension of the stopper recess 370 is reduced, the suction efficiency is reduced, and the performance of the refrigerant compressor is reduced.
  • the area of the suction port 315 must be increased. If the area of the suction port 3 15 is increased, it is necessary to increase the size of the suction valve 3 21 accordingly.
  • FIG. 14 is a perspective view showing a valve plate and a valve sheet proposed by the inventor of the present application
  • FIG. 15 is a plan view of the valve plate of FIG. 14
  • FIG. 16 is a cylinder block.
  • Fig. 17 is a partial view of the end face of the valve and the valve sheet as viewed from the valve sheet side.
  • Fig. 17 is a cross-sectional view taken along the line XVII-XVII in Fig. 16;
  • FIG. 2B is a diagram showing a state before the valve is opened,
  • FIG. 2B is a diagram showing a state after the suction valve is opened, and
  • FIG. 18 is a partially enlarged perspective view of the cylinder opening.
  • the suction port 15 and the suction valve 4 21 are larger than the conventional suction port 3 15 and the suction valve 3 21 of FIG.
  • the suction port 15 bulges in an arc along the opening ⁇ 406 a of the cylinder pore 406.
  • the port closing part 4 2 la of the suction valve 42 1 is the opening edge 4 It bulges along an arc along 06 a.
  • This oscillating plate type compressor has a point that a discharge port 16 is formed inside a suction port 15, a point that a hole 463 is formed in a suction valve 42 1,
  • a stock notch 470 is formed in the suction block 401 and faces the projection 42 of the suction valve 4 I do.
  • An object of the present invention is to provide a reciprocating refrigerant compressor that can prevent deformation and breakage of a suction valve and low-pressure pulsation when the area of a suction port is increased. Disclosure of the invention
  • a reciprocating compressor includes a cylinder block having a plurality of cylinder pores, and a valve plate provided on an end face of the cylinder block.
  • a cylinder head fixed to the cylinder head, a low-pressure chamber formed in the cylinder head, and the valve plate, which communicates the low-pressure chamber and the cylinder pore.
  • Multiple suction ports to open and close the multiple suction ports A reciprocating refrigerant compressor, wherein the suction port cutoff portion of the suction valve is formed in a substantially circular arc shape.
  • a main stopper recess that supports the center-side protrusion provided so as to protrude outward in the radial direction of the damper in the suction stroke is formed at an opening edge of the cylinder bore of the cylinder block.
  • a lid recess is formed at an opening edge of the cylinder pore of the cylinder block.
  • the bottom surface of the sub-stopper recess is inclined.
  • the side projection collides with the substopper recess, but the side projection at this time is the bottom surface of the substopper recess. Since the surface contact is made, the impact of the collision is reduced, and noise is suppressed.
  • the center of the suction port blocking portion is largely recessed, so that the refrigerant gas is more easily sucked and the suction efficiency is further improved.
  • the depth of the main flange is greater than the depth of the main flange.
  • the bottom surface of the sub-stopper recess is inclined, and the depth of the sub-stopper recess is greater than the depth of the main stopper recess.
  • the depth of the sub-stopper recess is smaller than the depth of the main stopper recess.
  • the side projection When the suction valve deflects to the compression chamber side during the suction stroke, the side projection first collides with the sub-stopper recess, restricting its lift. After that, the center projection is moved to the main stop. The lift collides with the recessed part and its lift is regulated. As described above, since the lift of the side projection is regulated before the lift of the sun projection is regulated, the vibration of the suction valve is more reliably prevented.
  • the bottom surface of the sub-stopper recess is inclined, and the depth of the sub-stopper recess is smaller than the depth of the main stopper recess.
  • the end face of the cylinder block and the valve sheet of the oscillating plate type compressor according to the first embodiment of the present invention are connected to the valve sheet side. It is a partial view as seen from above.
  • Fig. 2 is a cross-sectional view taken along the line II-II in Fig. 1.
  • Fig. 2 (a) shows the state before the intake valve opens
  • Fig. 2 (b) shows the state after the intake valve opens. It is a figure showing the state of.
  • FIG. 3 is a perspective view showing the entire valve plate and valve sheet.
  • FIG. 4 is a plan view showing the entire valve plate.
  • FIG. 5 is a partially enlarged perspective view of a cylinder block of the wobble plate compressor according to the first embodiment of the present invention.
  • FIG. 6 is a longitudinal sectional view showing a wobble plate compressor according to the first embodiment of the present invention.
  • FIG. 7 is a partially enlarged perspective view of a cylinder block of a rocking plate compressor according to a second embodiment of the present invention.
  • Fig. 8 is a partially enlarged cross-sectional view for explaining the relationship between the suction valve and each projection of the cylinder block.
  • Fig. 8 (a) shows the state before the suction valve is opened.
  • (B) is a view showing a state after the suction valve is opened.
  • FIG. 9 is a cross-sectional view of the state after the suction valve is opened, viewed from another angle.
  • FIG. 10 is a partially enlarged perspective view of a cylinder block of a rocking plate compressor according to a third embodiment of the present invention.
  • FIG. 11 is a partially enlarged cross-sectional view for explaining the relationship between the suction valve and each projection of the cylinder block.
  • (a) is a diagram showing a state before the suction valve is opened
  • (b) is a diagram showing a state after the suction valve is opened.
  • Fig. 12 shows the state after the suction valve is opened from another angle.
  • FIG. 13 is a partially enlarged plan view of a valve plate of a conventional rocking plate compressor. '
  • FIG. 14 is a perspective view showing a valve plate and a valve sheet proposed by the present inventors.
  • Fig. 15 is a plan view of the valve plate in Fig. 14.
  • Fig. 16 is a partial view of the end face of the cylinder block and the valve sheet as viewed from the valve sheet side. .
  • FIG. 17 is a cross-sectional view taken along the line XVII-XVII in Fig. 16 '.
  • Fig. 17 (a) shows the state before the suction valve opens
  • Fig. 17 (b) FIG. 4 is a diagram showing a state after the suction valve is opened.
  • FIG. 18 is a partially enlarged perspective view of a cylinder block.
  • FIG. 6 is a longitudinal sectional view showing the oscillating plate compressor according to the first embodiment of the present invention
  • FIG. 1 is a diagram showing the end face of the cylinder block and the valve sheet of the oscillating plate compressor.
  • 2 is a sectional view taken along the line II-II in FIG. 1, and FIG. 2 (a) shows a state before the suction valve is opened, and FIG. Figure
  • FIG. 3 is a perspective view showing the entire valve plate and the valve sheet
  • FIG. 4 is a plan view showing the entire valve plate
  • FIG. Figure 5 is a partially enlarged perspective view of the cylinder block.
  • One end of cylinder block 1 of this compressor has a valve
  • a cylinder (cylinder head) 3 is fixed via a plate 2, and a front head 4 is fixed to the other end face.
  • a plurality of cylinder pores 6 are arranged at predetermined intervals in the circumferential direction around the center 5.
  • a piston 7 is slidably accommodated in the cylinder 6.
  • a compression chamber 60 is formed inside the cylinder 6, and the volume of the compression chamber 60 changes as the piston 7 moves.
  • a main stopper recess 70 and sub-stopper recesses 71, 7 are provided in an opening a of the cylinder pore 6 (opening edge of the cylinder pore) 6a. 2 is formed.
  • the amount of flexure (opening) of the suction valve 21 is limited by the stopper recesses 70, 71, and 72.
  • a crank chamber 8 is formed in the front head 4, and swings around a hinge pole 9 in conjunction with the rotation of the shaft 5 in the crank chamber 8.
  • Rocking plate 10 is accommodated.
  • a discharge chamber 12 and a suction chamber 13 located around the discharge chamber 12 are formed.
  • the valve plate 2 has a plurality of discharge ports 16 for communicating the cylinder pore 6 with the discharge chamber 12, and a plurality of suction ports 1 for communicating the cylinder pore 6 with the suction chamber 13. 5 are provided at predetermined intervals in the circumferential direction.
  • the discharge port 16 is opened and closed by the discharge valve 17, and the discharge valve 17 is fixed to the end face of the valve plate 2 on the rear head side with the valve retainer 18 and the rivet 19. I have.
  • the suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is Located between plate 2 and cylinder block 1.
  • the discharge chamber 12 and the crank chamber 8 communicate with each other via a passage 79 and an orifice 80.
  • the number of the suction valves 21, the discharge valves 17, the suction ports 15, the discharge ports 16, and the compression chambers 60 is each equal to the number of the cylinder pores 6 (5 in this embodiment).
  • the inlet port 15 and the outlet port 16 are located inside the opening edge 6a of the cylinder pore 6, respectively.
  • the suction port 15 is located outside the discharge port 16 (radially outside the valve plate 2).
  • the five suction ports 15 protrude larger than the support point centers C 1 and C 2 (see FIG. 1), and accordingly, the suction port cut-off portions 21 a of the suction valve 21 are moved. It is larger than the suction port shut-off part 3 21 a of the conventional suction valve 32 1 .
  • the center C 1 of the support point is attached to the point supported by the projection 21 d on the sunset side.
  • the support point center C 2 is a straight line connecting the point supported by the center-side protrusion 21 d and the point supported by the base 21 c to the support point center C 2. .
  • each suction valve 21 is formed integrally with one valve sheet 62.
  • Each suction valve 21 has a hole
  • Each intake valve 21 has three projections 21 d, 21 e, 21 f, one intake port cutoff 21 a, and two roots 21 b, 21 c. I have it.
  • the suction port cutoff section 2 la of the suction valve 21 is formed in a substantially arc shape in accordance with the shape of the suction port 15. I have.
  • a center-side protrusion 21 d is provided at the center of the suction port cutoff portion 21 a in the arc direction, and a side protrusion 21 d is provided at both ends of the suction port cutoff portion 21 a in the arc direction.
  • e and 21 f are provided.
  • Each projection 21 d, 21 e, 21 ⁇ protrudes radially outward from the opening ⁇ 6 a of the cylinder pore 6, and the center-side projection 21 d is a recess in the main stopper. 70 and the central axis direction of the cylinder pore 6, and the side projections 2 1 e and 21 f are located in the substant ⁇ ° recesses 7 1, 7 2 and the central axis direction of the cylinder pore 6. Opposed.
  • the side projections 21e and 21f are located outside the support point centers C1 and C2.
  • the two roots, 2 lb, 21c, support the inlet port cutoff 21a.
  • the cylinder block 1 is provided with a communication path 31 communicating the suction chamber 13 and the crank chamber 8, and a pressure regulating valve 32 is provided in the middle of the communication path 31.
  • the pressure between the inside of the suction chamber 13 and the inside of the crank chamber 8 is adjusted by the pressure adjusting valve 32.
  • the front end of the shaft 5 is the front head.
  • the radial end 26 of the shaft 5 is rotatably supported by the radial bearing 24 and the thrust bearing 25 by the radial bearing 26 in 4.
  • the thrust flange 40 is fixed to the shaft 5 and the drive hub 41 is mounted via a hinge pole 9 that can move in the axial direction.
  • the thrust flange 40 is supported on the inner wall of the front head 4 via a thrust bearing 33. Part of thrust flange 40 and drive hub 4 A part of 1 is connected by a link mechanism 42, and the rotation of the shaft 5 is transmitted from the thrust flange 40 to the drive hub 41 through the link mechanism 42.
  • a rocking plate 10 is mounted on the drive shaft 41 via a radial bearing 27 and a thrust bearing 28 so as to be relatively rotatable.
  • the oscillating plate 10 is connected to the piston 7 via the connecting groove 11.
  • a coil spring 44 as a destroke spring is interposed between the hinge pole 9 and the post 40b of the thrust flange 40.
  • the hinge pole 9 is urged toward the cylinder block 1 by the core spring 4 4 of FIG.
  • a fixed pusher 45 is fixed to the cylinder block 1 side of the shaft 5, and a straight spring is provided between the fixed pusher 45 and the hinge pole 9.
  • a plurality of force springs 46 and a coil spring 47 are interposed in series, and the hinges 9 form a thrust pole by the springs 46 and 47. It is urged to the to flange 40 side.
  • the volume of the compression chamber 60 gradually decreases as the piston 7 moves to the top dead center, and the pressure in the compression chamber 60 increases.
  • the suction valve 21 blocks the suction port 15 and the discharge valve 17 blocks the discharge port 16.
  • the discharge stroke the volume of the compression chamber 60 is minimized, and the pressure in the compression chamber 60 is maximized.
  • the discharge valve 17 is bent toward the discharge chamber 60, and the discharge port 16 is opened. At this time, the suction valve 21 blocks the suction port 15.
  • the suction valve 21 Since the vibration of the suction valve 21 is prevented, deformation and breakage of the suction valve 21 and low-pressure pulsation can be prevented.
  • FIG. 7 is a partially enlarged, large perspective view of a cylinder block of the oscillating plate compressor according to the second embodiment of the present invention
  • FIG. 8 is a perspective view of each protrusion of the suction valve and the cylinder block.
  • (A) is a view showing a state before the suction valve is opened
  • (b) is a view showing a state after the suction valve is opened.
  • Fig. 9 and Fig. 9 are cross-sectional views of the state after the suction valve is opened, viewed from another angle.
  • the structure of this rocking plate compressor other than the cylinder block is the same as that of the first embodiment, and a description thereof will be omitted.
  • This embodiment is based on two blocks, cylinder block 101.
  • the first embodiment differs from the first embodiment in that the bottoms 17 1 a and 17 2 a of the bush horn concave portions 17 1 and 17 2 are respectively inclined.
  • the bottoms 17 1 &, 17 2 a of the substopper recesses 17 1, 17 2 are inclined toward the center of the suction port 15.
  • the suction valve 21 bends toward the compression chamber 60 during the suction stroke
  • the two side projections 21e and 21f respectively become the bottoms 17 of the sub-stopper recesses 17 1 and 17 2.
  • the side projections 2 1 e and 21 f are at the bottoms 17 1 a and 17 2 of the sub-stopper recesses 17 1 and 17 2, respectively.
  • Surface contact with 2a reduces the impact of collision.
  • the suction valve 21 when the suction valve 21 is bent, the substantially central portion of the suction port cutoff portion 21a is largely recessed, so that the refrigerant gas is easily sucked, and the suction efficiency is further improved.
  • the same effects as those of the first embodiment can be obtained, and the side projections 21 e and 21 f of the suction valve 21 are provided as sub-subs.
  • the impact when colliding with the bottoms 17 1 a and 17 2 a of the upper and lower recesses 17 1 and 17 2 is reduced, noise is suppressed, and the suction valve 21 is moved further.
  • the suction efficiency is further improved by the large deflection.
  • FIG. 10 is a partially enlarged perspective view of a cylinder block of a rocking plate compressor according to a third embodiment of the present invention.
  • FIG. 11 is a perspective view of the suction valve and each projection of the cylinder block.
  • (A) is a view showing a state before the suction valve is opened
  • (b) is a view showing a state after the suction valve is opened.
  • Fig. 12 is a cross-sectional view of the state after the suction valve is opened, as viewed from another angle.
  • This rocking plate compressor The structure other than the cylinder block is the same as that of the first embodiment, and a description thereof will be omitted.
  • the bottom surfaces 27 la and 272a of the two sub stopper recesses 27 1 and 27 2 of the cylinder block 201 are aligned with the center of the suction port 15.
  • the second embodiment is the same as the second embodiment in that it is inclined toward the center.
  • the sub-stopper recesses 27 1 and 27 2 are different from the sub-horn recesses 17 1 and 17 2 of the second embodiment. Also differs from the second embodiment in that it is located slightly in the center of the cylinder block 201.
  • the main stopper recesses 70, 170, 270 and the sub-stoke recesses 71, 72, 171, 172, 271, 271, 272 The relationship between the depth of the sub-stopper and the depth of the sub-stop recesses 71, 72, 171, 172, 271, 27 The depth may be smaller than the depth of the main recess 70 °, 170, 270.
  • the two side projections 21 e and 21 f are formed into the sub-horn recesses 71, 72, 17 1, 17 2 and 27 1 , .27, and then the projection 21d on the sensor side collides with the recesses 70, 170, 270 of the main stopper, so that the suction valve 21 Vibration is more reliably suppressed.
  • the center side projection 21 d first collides with the main tongue recesses 70, 170, 270 in the suction path, and then the two side projections 21. e and 21 f impinge on the substopper recesses 71, 72, .171, 172, 271, and 272. Since the timing of the lift regulation of the side projections 2 1 e and 21 ⁇ ⁇ is slower than the timing of the lift regulation of the center projection 21 d, the refrigerant is easily sucked.
  • the side projections 21 e and 21 f of the suction valve 21 are respectively provided at both ends in the arc direction, and two sub-stopper recesses are correspondingly provided. 7 1, 7 2, 17 1, 17 2, 27 1, 27 2 are formed in cylinder blocks 1, 101, 201, but the side of suction valve 21 When two or more projections 21e and 21f are provided at both ends in the arc direction, the projections 21e and 21f are formed in the two or more recesses corresponding to the projections.
  • the oscillating plate compressor is described as an example of the reciprocating refrigerant compressor.
  • the applicable range of the present invention is not limited to this. Industrial applicability in which the present invention can be applied to other reciprocating compressors such as a plate compressor.
  • the reciprocating refrigerant compressor according to the present invention is useful as a refrigerant compressor for an air conditioner for a vehicle.
  • the area of the suction port is large. Even if a large torsional load is not applied to the suction valve in the suction process, the vibration of the suction valve is prevented.

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

Abstract

L'invention concerne un évidement d'arrêt principal (70) supportant la projection d'une soupape d'aspiration (21) dans la course d'aspiration, et des évidements de sous-arrêt (71, 72) destinés à supporter les projections latérales (21e, 21f) de la soupape d'aspiration (21) dans la course d'aspiration, sont formés dans le bord d'ouverture (6a) de l'alésage du cylindre. Il en résulte de cet arrangement, que même si la zone d'un port d'aspiration (15) est augmentée, la soupape d'aspiration (21) est préservée de l'imposition d'une charge de torsion élevée ou de la présence de vibrations durant la course d'aspiration.
PCT/JP2001/000188 2001-01-15 2001-01-15 Compresseur frigorifique a double action WO2002055878A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US10/460,963 US20040052665A1 (en) 2001-01-15 2001-01-15 Double-acting refrigerant compressor
PCT/JP2001/000188 WO2002055878A1 (fr) 2001-01-15 2001-01-15 Compresseur frigorifique a double action

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2001/000188 WO2002055878A1 (fr) 2001-01-15 2001-01-15 Compresseur frigorifique a double action

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WO2002055878A1 true WO2002055878A1 (fr) 2002-07-18

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PCT/JP2001/000188 WO2002055878A1 (fr) 2001-01-15 2001-01-15 Compresseur frigorifique a double action

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WO (1) WO2002055878A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005071266A1 (fr) * 2004-01-21 2005-08-04 Behr Gmbh & Co. Kg Dispositif de compression pour milieux gazeux

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10436187B2 (en) 2015-10-29 2019-10-08 Emerson Climate Technologies, Inc. Cylinder head assembly for reciprocating compressor

Citations (4)

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Publication number Priority date Publication date Assignee Title
JPS5446012U (fr) * 1977-09-06 1979-03-30
JPH08261154A (ja) * 1995-03-22 1996-10-08 Toyota Autom Loom Works Ltd ピストン型圧縮機
JPH11315787A (ja) * 1998-03-02 1999-11-16 Carrier Corp コンプレッササクションバルブストレス低減のためのオイルフィルムを制御した往復型コンプレッサ
JP2000161229A (ja) * 1998-12-01 2000-06-13 Sanden Corp 往復動圧縮機

Family Cites Families (6)

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Publication number Priority date Publication date Assignee Title
JPH0335899Y2 (fr) * 1985-10-21 1991-07-30
JPH0819904B2 (ja) * 1987-01-27 1996-03-04 カルソニック株式会社 容量可変斜板式コンプレツサ
US5249939A (en) * 1990-01-09 1993-10-05 Sanden Corporation Valved discharge mechanism of a refrigerant compressor
JPH094563A (ja) * 1995-04-18 1997-01-07 Zexel Corp 往復式圧縮機
JPH10299656A (ja) * 1997-04-22 1998-11-10 Zexel Corp 往復式圧縮機
JP2000345966A (ja) * 1999-06-01 2000-12-12 Sanden Corp 圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5446012U (fr) * 1977-09-06 1979-03-30
JPH08261154A (ja) * 1995-03-22 1996-10-08 Toyota Autom Loom Works Ltd ピストン型圧縮機
JPH11315787A (ja) * 1998-03-02 1999-11-16 Carrier Corp コンプレッササクションバルブストレス低減のためのオイルフィルムを制御した往復型コンプレッサ
JP2000161229A (ja) * 1998-12-01 2000-06-13 Sanden Corp 往復動圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005071266A1 (fr) * 2004-01-21 2005-08-04 Behr Gmbh & Co. Kg Dispositif de compression pour milieux gazeux

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