EP1995461A1 - Prévention de fuites dans un compresseur utilisé dans un cycle de réfrigération - Google Patents

Prévention de fuites dans un compresseur utilisé dans un cycle de réfrigération Download PDF

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Publication number
EP1995461A1
EP1995461A1 EP08016146A EP08016146A EP1995461A1 EP 1995461 A1 EP1995461 A1 EP 1995461A1 EP 08016146 A EP08016146 A EP 08016146A EP 08016146 A EP08016146 A EP 08016146A EP 1995461 A1 EP1995461 A1 EP 1995461A1
Authority
EP
European Patent Office
Prior art keywords
cylinder block
compressor
seal member
front head
head
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.)
Withdrawn
Application number
EP08016146A
Other languages
German (de)
English (en)
Inventor
designation of the inventor has not yet been filed The
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.)
Valeo Thermal Systems Japan Corp
Original Assignee
Valeo Thermal Systems Japan 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 Valeo Thermal Systems Japan Corp filed Critical Valeo Thermal Systems Japan Corp
Publication of EP1995461A1 publication Critical patent/EP1995461A1/fr
Withdrawn legal-status Critical Current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
    • F04B27/10—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
    • F04B27/1081—Casings, housings
    • 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
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders

Definitions

  • the present invention relates to a compressor for use in an automotive air-conditioning system or the like.
  • a vapor critical compression refrigeration cycle in which a coolant such as CO2 circulates at a fairly high pressure, requires that special care be taken to prevent coolant leakage and assure safety.
  • Technologies proposed in the related art to address these needs include the following. Namely, in an air-conditioning system in which a carbon dioxide gas coolant is used, the design pressure safety factors of the cabin-side devices disposed on the cabin side, among the various devices and the coolant piping constituting the refrigeration cycle, are set higher than the overall design pressure safety factors of the devices constituting the refrigeration cycle.
  • the wall thickness of the cabin-side piping may be set higher than that of the outside piping so as to assure a higher wall thickness for the entire flow passage through which the coolant flows at the cabin-side devices compared to the wall thickness of the flow passages at the outside devices (see Japanese Unexamined Patent Publication No. 2002-243320 ). It is assumed that since any damage to a component caused by an abnormal pressure increase is bound to occur at an outside device, leakage of the CO2 gas into the cabin can be prevented by adopting these measures.
  • an object of the present invention is to provide a compressor that allows the size or the number of fastening members used therein to be minimized by optimizing the contact pressures at seal members held between the plurality of housing members so as to achieve miniaturization while also preventing coolant leakage and assuring safety.
  • the present invention provides a compressor comprising at least two housing members in which a compression mechanism is housed, a seal member held between the housing members and fastening members that fasten the housing members and the seal member as one, with the contact pressure applied to the seal member as the housing member and the seal members are fastened via the fastening members set within a range over which a critical seal pressure of the seal member is higher than the maximum operating pressure of the compressor and lower than the breaking pressure of the compressor, characterized in that the contact pressure is set within a range 2 to 5 times the contact pressure at which the critical seal pressure is equal to the maximum operating pressure and that the maximum operating pressure is within a range of 15 to 20 MPa.
  • the term "contact pressure” in this context refers to the pressure applied to the surfaces of the seal member at which it is pressed in contact against the adjacent housing members. The contact pressure can be measured by using pressure sensitive paper or the like of the known art.
  • the contact pressure be set within a range 2 to 5 times the contact pressure at which the critical seal pressure is equal to the maximum operating pressure in the compressor. It is even more desirable to set it within a range of 3 to 4 times the contact pressure at which the critical seal pressure is equal to the maximum operating pressure.
  • the maximum operating pressure be within a range of 15 to 20 MPa.
  • the seal member include a rubber layer formed at each of the two surfaces of a metal plate and that the thickness of the metal plate be within a range of 0.2 to 0.8 mm.
  • the seal member include a bead portion assuming a plateau shape or a mound shape and that the height of the bead portion be within a range of 0.1 to 0 .4 mm.
  • FIG. 9 presents an example of a structure that may be adopted in a seal member 100, with reference numeral 105 indicating a bead portion (full bead) assuming the mound shape and reference numeral 106 indicating a bead portion (half bead) assuming the plateau shape in the figure.
  • the compressor according to the present invention comprising at least two housing members in which a compression mechanism is housed, a seal member held between the housing members and fastening members that fasten the housing members and the seal member as one, with the contact pressure applied to the seal member as the housing members and the seal member are fastened via the fastening members set within a range over which a critical seal pressure of the seal member is higher than the maximum operating pressure of the compressor and lower than the breaking pressure of the compressor, may be characterized in that the seal member includes a bead portion formed to assume a plateau shape or a mound shape and that the bead portion located closer to any of the fastening members is formed so as to have a lower height.
  • a bead line pressure representing a force applied to the bead portion per unit distance during the fastening process be within a range 10 to 25 times the maximum operating pressure.
  • the housing members in the compressor may include a substantially cylindrical cylinder block with a plurality of bores formed therein to define compression spaces, a front head with a crankcase formed therein, which seals off one end surface of the cylinder block and a rear head with an intake chamber and an outlet chamber formed therein, which seals off another end surface of the cylinder block.
  • the fastening members in this compressor may include a plurality of bolts passing through areas of the front head, the cylinder block and the rear head near the outer edges thereof.
  • the diameter of a pitch circle formed by connecting the individual bolts be equal to or less than 110 mm.
  • the housing members in the compressor may include a cylinder block having a plurality of bores formed therein to define compression spaces, a front head with a crankcase formed therein, which seals off one end surface of the cylinder block and assumes a size and a shape that allow the front head to enclose the cylinder block, and a rear head with an intake chamber and an outlet chamber formed therein, which seals off another end surface of the cylinder block.
  • the fastening members in this compressor may include a threaded portion formed at an outer wall of the front head near its end toward the rear head and a ring nut constituted with a threaded portion to interlock with the threaded portion and a holding portion that holds the rear head.
  • the housing members in the compressor may include a cylinder block having a plurality of bores formed therein to define compression spaces, a front head with a crankcase formed therein, which seals off one end surface of the cylinder block and assumes a size and a shape that allow the front head to enclose the cylinder block, and a rear head with an intake chamber and an outlet chamber formed therein, which seals off another end surface of the cylinder block.
  • the fastening members in this compressor may include a threaded portion formed at an outer wall of the front head near its end toward the rear head and a threaded portion formed at an inner wall of the rear head near its end toward the front head to interlock with the threaded portion.
  • the compressor be utilized in a refrigeration cycle in which CO2 is used as a coolant.
  • the contact pressure at the seal members held between the plurality of housing members is optimized, which allows the size or number of the fastening members to be minimized.
  • the compressor can be provided as a compact unit while effectively preventing coolant leakage and assuring safety.
  • a compressor 1 in FIG. 1 constituting part of a refrigeration cycle in an automotive air-conditioning system, in which CO2 is used as a coolant, comprises a cylinder block 2, a front head 3, a rear head 4, a drive shaft 5, a swashplate mechanism 6, pistons 7, a valve plate 10, intake valves 11, outlet valves 12, gaskets 13, 14 and 15 and the like.
  • the cylinder block 2 is a substantially cylindrical member with a plurality of bores 20 arrayed circumferentially. Inside each bore 20, a compression space 21 where the coolant is compressed is formed.
  • the front head 3 is a member that seals off one end surface of the cylinder block 2, with a crankcase 22 formed inside.
  • the rear head 4 with an intake chamber 25 and an outlet chamber 26 formed therein seals off another end surface of the cylinder block 2.
  • the drive shaft 5 is a member assuming a substantially rod-like shape. It is rotatably held at bearings and seal members disposed at the cylinder block 2 and the front head 3, and its portion 5a projecting beyond the front head 3 is connected to a pulley (not shown) which is caused to rotate by a drive source such as an engine or a motor.
  • the swashplate mechanism 6, which is disposed inside the crankcase 22, includes a swashplate 30, shoes 31, an angle adjustment mechanism 32, a thrust flange 33 and the like. It converts the rotational force of the drive shaft 5 to a reciprocal motion of the pistons 7 and the angle of the swashplate 30 is adjusted in conformance to predetermined conditions.
  • the pistons 7 are each linked to the shoes 31 so as to be allowed to move reciprocally and are also each slidably fitted inside one of the bores 20.
  • the gasket 13, the intake valve 11, the valve plate 10, the outlet valve 12 and the gasket 14 disposed in this order starting from the cylinder block side are held between the cylinder block 2 and the rear head 4, whereas the gasket 15 is held between the cylinder block 2 and the front head 3.
  • the front head 3, the gasket 15, the cylinder block 2, the gasket 13, the intake valve 11, the valve plate 10, the outlet valve 12, the gasket 14 and the rear head 4 are held together with a predetermined level of fastening force via a plurality (8) of bolts 40 passing through the areas near their outer edges and nuts 41.
  • the gasket 13, the intake valve 11, the valve plate 10, the outlet valve 12, the gasket 14 and a retainer 42 are held at the central area of the cylinder block 2 via a bolt 43.
  • valve plate 10 which is a disk-shaped member constituted of metal, an intake port constituting part of intake passages 45 communicating between the intake chamber 25 and the compression spaces 21, an outlet port constituting part of outlet passages 46 communicating between the compression spaces 21 and the outlet chamber 26, through holes at the outer edge thereof through which the bolts 40 pass and a through hole through which the central bolt 43 passes, are formed.
  • the gaskets 13, 14 and 15 are members formed by covering both surfaces of a metal plate with a rubber layer.
  • the gaskets 13 and 14 disposed between the cylinder block 2 and the rear head each have communicating holes formed therein communicating between the intake passages 45 and the outlet passages 46, through holes at the outer edge thereof through which the bolts 40 pass and an opening through which the central bolt 43 passes.
  • the retainer 42 which restricts the movement of the lead portion of the outlet valve 12 along the opening direction, is disposed.
  • a hole with a diameter equal to that of the crankcase 27 and through holes through which the bolts 40 pass at the outer edge thereof are formed.
  • the front head 3, the cylinder block 2, the valve plate 10 in the rear head 4 constitute housing members that are sealed by the gaskets 13, 14 and 15 used as seal members.
  • specific types of seal members may be disposed between the valve plate 10 and the intake valve 11 and between the valve plate 10 and the outlet valve 12, as necessary.
  • the contact pressure at the seal members (gaskets 13, 14 and 15) generated as the bolts 40 used as fastening members are tightened in the structure described above is set as shown in FIG. 2 .
  • the term "contact pressure” in this context refers to the pressure applied at a surface of each seal member (gasket 13, 14 or 15) at which the seal member is pressed in contact against an adjacent housing member (the front head 3, the cylinder block 2 or the rear block 4).
  • This pressure can be measured by using pressure sensitive paper or the like of the known art.
  • the relationship between the pressure measured by using the pressure sensitive paper and the corresponding fastening force imparted via the fastening members (bolts 40) must be ascertained in advance through testing or the like.
  • Pa indicates the maximum operating pressure of the compressor 1
  • Pb indicates the breaking pressure of the compressor 1
  • P1 indicates the contact pressure at which the critical seal pressure is equal to the maximum operating pressure Pa. It is desirable that the maximum operating pressure Pa be within a range of 15 to 20 MPa and if the compressor includes an abnormally high pressure preventing means such as a relief valve, the maximum operating pressure is represented by the operating pressure of the abnormally high pressure preventing means.
  • the contact pressure at the seal members is set within a range R1, which is 2 to 5 times the contact pressure P1 in the compressor 1 adopting the structure described above. It is even more desirable to set the seal member contact pressure within a range R2, which is 3 to 4 times the contact pressure P1. With the seal member contact pressure set within these ranges, the coolant is made to leak through the seal member before the pressure inside the compressor 1 having exceeded the maximum operating pressure Pa under abnormal conditions reaches the breaking pressure Pb, thereby improving safety.
  • the compressor 1 can be provided as a more compact, lighter weight unit.
  • the research conducted by the inventor of the present invention et al. indicates that by adopting the structure described above, the outer diameter of the compressor 1 can be reduced by approximately 10 mm and the weight of the compressor 1 can be reduced by 15 to 20%.
  • FIG. 3 shows a structure that may be adopted in the gasket 13 disposed between the cylinder block 2 and the intake valve 11.
  • communicating holes 50 each formed at a position facing opposite one of the bores 20 to communicate between the compressor 21 and the corresponding intake passages 45 and between the compressor 21 and the corresponding outlet passages 46
  • bead portions 55 each formed so as to range around one of the communicating holes 50, through holes 51 through which the bolts 40 pass at the outer edge thereof, a through hole 52 through which the central bolt 43 passes, a bead portion 56 formed so as to range around the through hole 52 and a bead portion 57 formed so as to range along an area near the outer edge of the gasket 13 are formed.
  • the structure described above simply represents an example of a structure that may be adopted in the gasket 13, and the present invention is in no way limited by the example.
  • the shapes and quantities of the communicating holes 50, the through holes 51 and 52 and the bead portions 55, 56 and 57 should be adjusted as necessary and the present invention may be achieved without including all of them.
  • the bead portions 55, 56 and 57 are all formed as full beads, some of them may instead be half beads (see FIG. 9 ).
  • FIG. 4 shows a sectional view of the gasket 13 adopting the structure described above taken along A-A.
  • the gasket 13 is formed by covering the two surfaces of a metal plate 58 respectively with rubber layers 59a and 59b, with the bead portions 55, 56 and 57 formed as projections cresting toward the cylinder block 2.
  • the thickness t of the metal plate 58 is within a range of 0.2 to 0.8 mm, with the heights of the bead portions 55, 56 and 57 all set within a range of 0.1 to 0.4 mm and the bead portions formed so as to have higher height further away from the through holes 51 through which the bolts 40 pass.
  • the bead line pressure is a value calculated as; (total fastening force achieved via the bolts 40)/(total distance over which the central lines of bead portions 55, 56 and 57 extend).
  • the central lines of the bead portions 55, 56 and 57 are indicated as L1 to L 10 in FIG. 5 , and the total distance is represented by the grand total (L1 + L2 + L3... L10) of the sum of the distances over which the central lines L1 to L8 (only L1 to L3 are shown in FIG. 5 ) of the eight bead portions 55, the distance over which the central line L9 of the bead portion 56 extends and the distance over which the central line L10 of the bead portion 57 extends.
  • the diameter Dc of a pitch circle C formed by connecting the eight bolts 40 in the compressor 1 adopting the structure described above be equal to or less than 110 mm, as shown in FIG. 6 , so as to prevent the central portion of the valve plate 10 or the like from becoming lifted off by the internal pressure, which tends to occur readily when the diameter Dc is very large.
  • the housing members of the compressor 60 include a cylinder block 61, a front head 62 that seals off one end surface of the cylinder block 61 and assumes a size and shape that allow the front head 62 to enclose the cylinder block 61 and a rear head 63 that seals off another end surface of the cylinder block 61.
  • the fastening members include a threaded portion 65 formed at the outer wall of the front head 62 near its end toward the rear head 63, a ring nut 70 constituted with a threaded portion 66 to interlock with the threaded portion 65 and a flange 67 that holds the end of the rear head 63 at the circumferential edge thereof, and a bolt (not shown) that firmly holds the cylinder block 61 to the rear head 63.
  • a gasket 71 is held between the front head 62 and the rear head 63, and a gasket 72, an intake valve 73, a valve plate 74 and an outlet valve 75 disposed in this order from the cylinder block side, are held between the gasket 71 and the cylinder block 61.
  • the contact pressure at the gasket 71 can be adjusted through adjustment of the fastening force imparted via the ring nut 70, whereas the contact pressure at the gasket 72 can be adjusted through adjustment of the fastening force imparted via the bolts.
  • This structure allows the housing to be provided as a compact unit, which, in turn, contributes to miniaturization of the compressor.
  • the present invention may be adopted in a compressor 80 shown in FIG. 8 .
  • the housing members of the compressor 80 include a cylinder block 81, a front head 82 that seals off one end surface of the cylinder block 81 and assumes a size and shape that allow the front head 82 to enclose the cylinder block 81 and a rear head 83 that seals off another end surface of the cylinder block 81.
  • the fastening members include a threaded portion 85 formed at the outer wall of the front head 82 near its end toward the rear head 83, a threaded portion 86 formed at the inner wall of the rear head 83 near its end toward the front head 82 to interlock with the threaded portion 85 and a bolt (not shown) that firmly holds the cylinder block 81 to the rear head 83.
  • a gasket 91 is held between the front head 82 and the rear head 83, and a gasket 92, an intake valve 93, a valve plate 94 and an outlet valve 95 disposed in this order from the cylinder block side, are held between the gasket 91 and the cylinder block 81.
  • the contact pressure at the gasket 91 can be adjusted through adjustment of the fastening force imparted via the threaded portions 85 and 86, whereas the contact pressure at the gasket 92 can be adjusted through adjustment of the fastening force imparted via the bolts.
  • This structure also allows the housing to be provided as a compact unit, which, in turn, contributes to miniaturization of the compressor.
  • the contact pressure at the seal members held between the plurality of housing members is optimized and thus the size or the number of fastening members can be minimized according to the present invention.
  • the compressor can be provided as a compact unit while effectively preventing coolant leakage and assuring a high level of safety.

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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)
EP08016146A 2004-06-03 2005-03-03 Prévention de fuites dans un compresseur utilisé dans un cycle de réfrigération Withdrawn EP1995461A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004165728A JP2005344625A (ja) 2004-06-03 2004-06-03 圧縮機
EP05719890A EP1775471A4 (fr) 2004-06-03 2005-03-03 Compresseur

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP05719890A Division EP1775471A4 (fr) 2004-06-03 2005-03-03 Compresseur

Publications (1)

Publication Number Publication Date
EP1995461A1 true EP1995461A1 (fr) 2008-11-26

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EP08016146A Withdrawn EP1995461A1 (fr) 2004-06-03 2005-03-03 Prévention de fuites dans un compresseur utilisé dans un cycle de réfrigération
EP05719890A Withdrawn EP1775471A4 (fr) 2004-06-03 2005-03-03 Compresseur

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP05719890A Withdrawn EP1775471A4 (fr) 2004-06-03 2005-03-03 Compresseur

Country Status (3)

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EP (2) EP1995461A1 (fr)
JP (1) JP2005344625A (fr)
WO (1) WO2005119061A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9212747B2 (en) 2010-02-04 2015-12-15 Agilent Technologies, Inc. Sealing configuration with metal-coated structure

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008064035A (ja) * 2006-09-07 2008-03-21 Toyota Industries Corp ピストン式圧縮機
JP4922729B2 (ja) * 2006-10-20 2012-04-25 三洋電機株式会社 圧縮機及びその製造方法
JP2010065600A (ja) * 2008-09-10 2010-03-25 Sanden Corp 流体機械

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US3817540A (en) * 1971-04-27 1974-06-18 T Nicholson Washers and gaskets
US5582415A (en) * 1993-08-31 1996-12-10 Kokusan Parts Industry Co., Ltd. Metal gasket
JPH11343974A (ja) * 1998-05-29 1999-12-14 Toyota Autom Loom Works Ltd 往復動型圧縮機
US6068265A (en) * 1996-12-12 2000-05-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Gasket for sealing a refrigerant compressor
JP2002243320A (ja) 2001-02-16 2002-08-28 Mitsubishi Heavy Ind Ltd 炭酸ガス冷媒を用いた空調装置，及び空調装置の炭酸ガス冷媒漏れ防止方法

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JPS5159904U (fr) * 1974-11-05 1976-05-12
JPS5372209A (en) * 1976-12-10 1978-06-27 Toyoda Autom Loom Works Ltd Compressor
JPH0612095B2 (ja) * 1985-05-09 1994-02-16 日本メタルガスケット株式会社 単板金属ガスケット
JPH0532695Y2 (fr) * 1986-10-30 1993-08-20
CA1290641C (fr) * 1988-06-24 1991-10-15 Stephen Farwell Element a disque de rupture composite
JPH0676661U (ja) * 1993-04-02 1994-10-28 サンデン株式会社 圧縮機
JPH08296559A (ja) * 1995-04-21 1996-11-12 Iwata Air Compressor Mfg Co Ltd 往復空気圧縮機
JP3119140B2 (ja) * 1995-11-15 2000-12-18 株式会社豊田自動織機製作所 圧縮機
JP3822661B2 (ja) * 1995-11-24 2006-09-20 日本ラインツ株式会社 メタルガスケット
JPH09264254A (ja) * 1996-01-26 1997-10-07 Toyota Autom Loom Works Ltd ピストン式圧縮機及びその組付方法
JP3293078B2 (ja) * 1996-02-28 2002-06-17 エヌオーケー株式会社 ガスケット
JP2000297698A (ja) * 1999-04-16 2000-10-24 Nok Corp 金属ガスケット
WO2000073657A1 (fr) * 1999-05-26 2000-12-07 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Compresseur
JP4431912B2 (ja) * 1999-09-09 2010-03-17 株式会社ヴァレオサーマルシステムズ 斜板式圧縮機
JP2001355732A (ja) * 2000-06-15 2001-12-26 Nippon Reinz Co Ltd 金属ガスケット
JP2002070739A (ja) * 2000-08-30 2002-03-08 Zexel Valeo Climate Control Corp 往復式冷媒圧縮機
JP2002115658A (ja) * 2000-10-05 2002-04-19 Toyota Industries Corp ピストン式圧縮機
JP2002317764A (ja) * 2001-04-20 2002-10-31 Toyota Industries Corp 圧縮機のシール構造及び圧縮機
JP2002364539A (ja) * 2001-06-07 2002-12-18 Sanden Corp 圧縮機
JP2003065232A (ja) * 2001-08-28 2003-03-05 Toyota Industries Corp 圧縮機のシール構造
JP4021232B2 (ja) * 2002-04-01 2007-12-12 サンデン株式会社 圧縮機のシール構造

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3817540A (en) * 1971-04-27 1974-06-18 T Nicholson Washers and gaskets
US5582415A (en) * 1993-08-31 1996-12-10 Kokusan Parts Industry Co., Ltd. Metal gasket
US6068265A (en) * 1996-12-12 2000-05-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Gasket for sealing a refrigerant compressor
JPH11343974A (ja) * 1998-05-29 1999-12-14 Toyota Autom Loom Works Ltd 往復動型圧縮機
JP2002243320A (ja) 2001-02-16 2002-08-28 Mitsubishi Heavy Ind Ltd 炭酸ガス冷媒を用いた空調装置，及び空調装置の炭酸ガス冷媒漏れ防止方法

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9212747B2 (en) 2010-02-04 2015-12-15 Agilent Technologies, Inc. Sealing configuration with metal-coated structure
US10300403B2 (en) 2010-02-04 2019-05-28 Agilent Technologies, Inc. Sealing configuration with metal-coated structure

Also Published As

Publication number Publication date
EP1775471A4 (fr) 2008-07-30
JP2005344625A (ja) 2005-12-15
WO2005119061A1 (fr) 2005-12-15
EP1775471A1 (fr) 2007-04-18

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