EP1605160B1 - Compresseur volumetrique a pistons - Google Patents

Compresseur volumetrique a pistons Download PDF

Info

Publication number
EP1605160B1
EP1605160B1 EP03772804A EP03772804A EP1605160B1 EP 1605160 B1 EP1605160 B1 EP 1605160B1 EP 03772804 A EP03772804 A EP 03772804A EP 03772804 A EP03772804 A EP 03772804A EP 1605160 B1 EP1605160 B1 EP 1605160B1
Authority
EP
European Patent Office
Prior art keywords
mounting
connecting portion
projected
cylinder block
projected portion
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
EP03772804A
Other languages
German (de)
English (en)
Other versions
EP1605160A4 (fr
EP1605160A1 (fr
Inventor
Satoshi ZEXEL VALEO CLIM. CONTROL CORP. WATANABE
Minoru ZEXEL VALEO CLIM. CONTROL CORP. KANAIZUKA
Yasunori ZEXEL VALEO CLIMATE CONTROL CORP FUJITA
Ryosuke ZEXEL VALEO CLIMATE CONTROL CORP. IZAWA
Toshiaki ZEXEL VALEO CLIM. CONTROL CORP KURIBARA
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 EP1605160A1 publication Critical patent/EP1605160A1/fr
Publication of EP1605160A4 publication Critical patent/EP1605160A4/fr
Application granted granted Critical
Publication of EP1605160B1 publication Critical patent/EP1605160B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0891—Component parts, e.g. sealings; Manufacturing or assembly thereof 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
    • F04B27/1045—Cylinders

Definitions

  • the present invention relates to a reciprocating compressor which is installed by fastening mounting leg parts of the cylinder block at specific positions with mounting bolts or the like.
  • a reciprocating compressor includes a cylinder block having a plurality of cylinders formed therein, a shaft rotatably disposed so as to pass through the cylinder block and pistons engaged in reciprocating movement inside the cylinders as the shaft rotates. It is installed at a specific location such as an engine compartment by fastening and locking mounting leg parts formed at the external circumferential surface of the cylinder block or the like at specific positions with mounting bolts or the like.
  • the mounting leg parts formed at the cylinder block or the like may assume any of various structures, it is essential that they be firmly locked at the mounting positions. For this reason, in the structure disclosed in Japanese Unexamined Utility Model Publication No. H2-43478 , having mounting leg parts with cylindrical front ends formed at the external circumference of the compressor main unit as an integrated part thereof and bolt insertion holes formed at the cylindrical front ends so as to extend along a direction or perpendicular to the axis of the compressor main unit, the mounting bolts passing through the bolt insertion holes are fastened to mounting brackets locked onto mounting eyes.
  • Another compressor mounting structure that is widely known in the related art (see Japanese Unexamined Patent Publication No. 2001-182650 ) is adopted in conjunction with a compressor having a bore housing having a plurality of cylinders formed therein and a side housing having housed therein a piston drive means.
  • Two main mounting portions each having a mounting hole or a mounting groove at which a main locking bolt means is mounted, are disposed at the external circumferential surface of the side housing and at least one sub-mounting portion having a mounting hole or a mounting groove at which a sub locking bolt means is mounted is disposed at the external circumferential surface of the bore housing so as to allow the compressor to be locked at the main mounting portions while it is held at the sub-mounting portion.
  • This structure allows the compressor to be installed without having to mount the sub-mounting portion with an excessive level of firmness which may cause deformation of the bore housing.
  • a further compressor mounting structure is known from European patent application No. EP 1 170 503 A2 .
  • the cylinder block i.e. the compressor housing is made of aluminum and comprises a mounting section in form of two mounting pieces that are aligned parallel as protrusions from the housing and that comprise insertion holes into which a bolt can be inserted for mounting the compressor at a corresponding structure.
  • a highly-rigid bush made of steel is inserted between these mounting pieces, in order to prevent the compressor housing from disadvantageous deformations.
  • a solution for coupling the cylinder block of a compressor together with the front and rear housing of the compressor is known from United States Patent No. US 5,456,158 .
  • This document discloses a reciprocating type refrigerant compressor that comprises. besides common inner components, a cylinder block and front and rear housings. The cylinder block and the front and rear housings are fastened together by a plurality of bolts to close the opposite ends of the cylinder block and thus the compressor.
  • Each bolt has a head that is supported on a circular-shaped bearing surface.
  • the bearing surface is part of an annular projection which is formed on the corresponding side of the housing and which is concentric with the bore in the housing.
  • the cylinder block of the compressor is often constituted of an aluminum alloy in order to keep down the weight, and there is a problem in that as the mounting leg parts are fastened by tightening mounting bolts as in the structure described above, the tightening pressure occurring while the mounting leg parts are fastened deforms the mounting leg parts and the deformation propagated to the cylinders compromises the shape of the cylinders, which, in turn, prevents smooth movement of the pistons.
  • the piston clearance may be set to a large value by taking into consideration such cylinder deformation, the quantity of working fluid leaking along the side surfaces of the pistons is bound to increase when the piston clearance is large, which will require more rigorous allowance management. If the management is not rigorous enough, the performance of the compressor will become poorer due to the leakage.
  • an object of the present invention is to provide a reciprocating compressor that does not require rigorous management of the piston clearance while assuring secure installation via the mounting leg parts and also assuring smooth movement of the pistons by keeping the extent of cylinder deformation occurring during the installation within an allowable range.
  • a reciprocating compressor comprising a cylinder block having formed therein a plurality of cylinders, a shaft rotatably passing through the cylinder block and pistons engaged in reciprocating movement inside the cylinders as the shaft rotates, which is installed by fastening mounting leg parts disposed at the cylinder block at mounting positions characterized in that the mounting leg parts are each constituted with a connecting portion extending from the cylinder block and a projected portion formed continuously to the connecting portion to project on one side or both sides of the connecting portion along the tightening direction and that the projected portion has a lower level of rigidity compared to said connecting portion so as to concentrate deformation occurring during installation into said projected portion.
  • the tightening pressure occurring as the mounting bolts are tightened causes deformation of the mounting leg parts, but since the projected portions formed at the mounting leg parts are formed to have a relatively low level of rigidity compared to the connecting portions, the deformation occurring during the tightening process manifests in a concentrated manner at the projected portions.
  • the deformation of the mounting leg parts occurring during the tightening process can be absorbed at the projected portions, reducing the extent to which the tightening pressure is transmitted to the cylinders via the connecting portions, which makes it possible to ensure that the extent of the cylinder deformation is kept within the allowable range.
  • sectional area of the projected portions is set smaller than the sectional area of the connecting portions so as to concentrate deformation occurring during installation into said projected portion.
  • the deformation occurring during the tightening process manifests first and foremost at the projected portions since the sectional area of the projected portions formed at the mounting leg parts is set smaller than the sectional area of the connecting portions.
  • the deformation of the mounting leg parts occurring during the tightening process can be absorbed at the projected portions, reducing the extent to which the tightening pressure is transmitted to the cylinders via the connecting portions, which makes it possible to ensure that the extent of the cylinder deformation is kept within the allowable range.
  • a bolt insertion hole at which a mounting bolt is inserted may be formed at the center of each projected portion and thinning out the wall thickness of the connecting portion along the direction running perpendicular to the bolt insertion hole is not required. In such a case, sufficient rigidity of the connecting portions can be assured with an even higher level of reliability.
  • a bolt insertion hole at which a mounting bolt is inserted may be formed at the center of each projected portion with at least one projected portion disposed on one side or both sides of the corresponding connecting portion along the tightening direction having a length along the axial direction set approximately equal to or greater than the internal diameter of the bolt insertion hole, so as to allow the deformation manifesting as the bolt is tightened to concentrate at the projected portion.
  • a reciprocating compressor 1 shown in FIGS. 1 through 3 which is used in a refrigerating cycle with a coolant used as a working fluid, comprises a front-side cylinder block 2, a rear-side cylinder block 3 mounted at the front-side cylinder block 2, a front-side cylinder head 5 mounted at the front side (the left side in FIGS. 1 and 2 ) of the front-side cylinder block 2 via a valve plate 4 and a rear-side cylinder head 7 mounted at the rear side (the right side in FIGS. 1 and 2 ) of the rear-side cylinder block 3 via a valve plate 6.
  • the front-side cylinder head 5, the front-side cylinder block 2, the rear-side cylinder block 3, and the rear-side cylinder head7 are fastened together along the axial direction with a tightening bolt (not shown) and constitute the housing for the whole compressor.
  • a shaft support hole 10 that rotatably supports a shaft 9 to be detailed later, a plurality of (5) cylinders 11 extending parallel to the shaft support hole 10 and disposed over equal intervals on a circumference of a circle centered on the shaft 9, two discharge passages 12 extending parallel to the cylinders 11 and intake passages 13 through which a low pressure working fluid flows, are formed.
  • the discharge passages 12 communicate with each other via a guide passage 12a, and individually communicating with a discharge chamber 14 formed at the front-side cylinder head 5 to be detailed later and the other discharge passage communicating with a discharge chamber 14 formed at the rear-side cylinder head 7.
  • one of the discharge passages 12 is connected to a discharge port 16 through which the working fluid is let out to an external cycle via a passing hole 15 formed at the valve plate 6 or the like.
  • the intake passages 13 are connected to a swashplate housing chamber 21 to be detailed below and they are further connected with a low-pressure passage 18 communicating with intake chambers 17 at the cylinder heads 5 and 7 via the swashplate housing chamber 21.
  • a double-ended piston 19 is slidably inserted at each cylinder 11. It is to be noted that reference numeral 20 in FIG. 3 indicates a bolt insertion hole formed between adjacent cylinders 11, at which a tightening bolt is inserted.
  • the swashplate housing chamber 21 formed by assembling the front-side cylinder block 2 and the rear-side cylinder block 3 is present inside the cylinder blocks, and the shaft 9 inserted at the shaft support hole 10 formed at the front-side cylinder block 2 and the rear-side cylinder block 3 with one end projecting out through the front-side cylinder head 5 and fixed to the armature of an electromagnetic clutch (not shown) is disposed in the swashplate housing chamber 21.
  • the swashplate 22 is rotatably supported at the front-side cylinder block 2 and the rear-side cylinder block 3 via thrust bearings 23, with the circumferential edge thereof held at shoe pockets 25 formed at the center of the double ended pistons 19 via semispherical shoes 24 disposed along the front/rear direction.
  • An intake hole 27 and a discharge hole 28 are formed at each valve plate 4 and 6, in correspondence to each of the cylinders 11.
  • the intake chambers 17, in which the working fluid to be supplied to the compression spaces 26 is stored, and the discharge chambers 14 in which the working fluid discharged from the compression spaces 26 is stored, are defined.
  • the intake chambers 17 are allowed to communicate with the compression spaces 26 via the intake holes 27 formed at the valve plates 4 and 6, whereas the discharge chambers 14 formed continuously around the intake chambers 17 are allowed to communicate with the compression spaces 26 via the discharge holes 28 formed at the valve plates 4 and 6.
  • the intake holes 27 are opened/closed with intake valves 29 disposed at the end surfaces of the valve plates 4 and 6 toward the cylinder blocks, whereas the discharge holes 28 are opened/closed with discharge valves 30 disposed at the end surfaces of the valve plates 4 and 6 toward the cylinder heads.
  • the working fluid is taken into the compression spaces 26 from the intake chamber 17 via the intake hole 27 and the intake valve 29, whereas during a compression stroke in which the volumetric capacity of the compression space 26 decreases, the working fluid having been compressed in the compression space 26 is discharged via the discharge hole 28 and the discharge valve 30 to the discharge chamber 14 and is forced to the outside of the compressor from the discharge port 16 via the discharge passage 12.
  • mounting leg parts 31 used when installing the compressor at a specific mounting location in an engine room or the like are formed at positions symmetrical to each other relative to the axis (upper and lower positions in the figure).
  • the mounting leg parts 31 each include a connecting portion 31a extending from the cylinder block 2 or 3 along a substantially radial direction and a projected portion 31b formed continuous to the connecting portion 31a so as to project on one side of the connecting portion along the tightening direction running perpendicular to the shaft 9.
  • a bolt insertion hole 32 at which a mounting bolt (not shown) to interlock with a mounting hole formed at the mounting area is inserted, is formed to range over to the connecting portion 31a.
  • the wall thickness of the connecting portion 31a at the mounting leg part 31 is not thinned out from the direction running perpendicular to the bolt insertion hole 32.
  • the mounting leg parts 31 are formed as an integrated part of the cylinder blocks 2 and 3 by using an aluminum alloy, with the projected portions 31 b formed to have a lower level of rigidity compared to the connecting portions 31a to form more deformable crush zones. More specifically, the rigidity at each projected portion 31b is set lower than the rigidity at the corresponding connecting portion by setting the area of a section of the projected portion 31b perpendicular to the axial line of the bolt insertion hole 32 smaller than the area of a section of the connecting portion 31a.
  • the sectional area of the projected portion is reduced by forming the bolt insertion hole 32 to have a uniform internal diameter over the full range and setting the external diameter of the projected portion 31 b to a relatively small value so as to form a stage at the surface over which the connecting portion 31a turns into the projected portion 31 b.
  • the projected portion 31b in the structure described above is formed in a cylindrical shape with a uniform thickness, with the length of the projected portion 31b along the axial direction set approximately equal to or greater than the internal diameter of the bolt insertion hole 32.
  • the mounting leg part 31 becomes deformed due to the tightening pressure.
  • the level of rigidity of the projected portion 31b formed at the mounting leg part 31 is set lower than the rigidity of the connecting portion 31 a and the wall of the connecting portion 31a is not thinned out, the deformation occurring during the tightening process manifests at the projected portion 31b in a concentrated manner.
  • the deformation of the mounting leg part 31 occurring during the tightening process can be absorbed at the projected portion 31b, which disallows ready transmission of the tightening pressure to the cylinder 11 via the connecting portion 31a. Consequently, the extent of deformation of the cylinder 11 is kept within the allowable range and the circularity of the cylinder can be maintained at a high degree of accuracy, assuring smooth movement of the piston 19.
  • the extent of deformation of the cylinder 11 is reduced, a large piston clearance for assuring a comfortable margin for the deformation of the cylinder 11 is not necessary.
  • rigorous allowance management for purposes of managing the working fluid leaking past the side surface of the piston 19 is not required.
  • the projected portion 31b of the mounting leg part 31 is formed in a cylindrical shape, the projected portion 31b becomes deformed with uniformity around the axis during the tightening process.
  • the extent to which the cylinder 11 becomes deformed can be reduced.
  • the length of the projected portion 31b along the axial direction is set approximately equal to or greater than the diameter of the bolt insertion hole 32, the deformation occurring as the mounting bolt is tightened can be concentrated at the projected portion 31b with an even higher degree of reliability, which also makes it possible to reduce the extent of deformation of the cylinder 11.
  • the projected portion 31b is formed only on one side of the connecting portion along the tightening direction in the example described above, the projected portion 31b may be disposed on each side along the tightening direction, as shown in FIG. 4(a) .
  • the mounting leg portion 31 may include projected portions 31b projecting on the two sides along the tightening direction at the connecting portion 31 a extending from the cylinder block 2 or 3 substantially along the radial direction with the bolt insertion hole 32 formed to have a uniform diameter ranging from one of the projected portions 31b through the other projected portion 31b and the sectional area of the projected portions set smaller by setting the external diameter of the projected portions 31b smaller than the diameter of the connecting portion 31 a so as to form a crush zone with lower rigidity at each end of the bolt insertion hole 32.
  • this structure which allows the deformation occurring during the tightening process to be dispersed onto the two sides of the connecting portion 31a, makes it possible to reduce the extent to which the tightening force is communicated to the cylinder 11 via the connecting portion 31a with an even higher degree of reliability.
  • the rigidity at the projected portions 31b is set smaller relative to the rigidity at the connecting portions by setting the external diameter of the projected portions 31b to a smaller value in the structures described above, the rigidity of the projected portions may be set smaller by adopting structures other than those explained above.
  • the projected portions 31c may be formed so that their exteriors range uniformly to the external contour of the connecting portions 31a without creating stages between the projected portions and the connecting portion 31a, and the internal diameter of the bolt insertion hole 32 may be set larger than the areas where the projected portions 31c are present relative to the internal diameter in the area over which the connecting portion 31a is present.
  • the sectional area of the projected portions 31c set smaller than the sectional area of the connecting portion 31 a, a crush zone with lower rigidity is formed at each end of the bolt insertion hole 32.
  • This structure makes it possible to concentrate the deformation occurring during the tightening process at the projected portions 31c, which, in turn, reduces the extent to which the mounting bolt tightening force is transmitted to the cylinder 11 via the connecting portion 31a, thereby achieving advantages similar to those of the previous structural
  • FIG. 6 A comparison of the extent of deformation occurring at cylinders 11 when the mounting leg parts 31 are fastened with mounting bolts by using the cylinder blocks 2 and 3 having the projected portions 31b, 31c or 31d forming crush zones at the mounting leg parts 31 as described above and by using a cylinder block 36 shown in FIG. 5 with no projected portions to form crush zones included at the mounting leg parts 31 and the wall thickness reduced over an area 35 from the direction running perpendicular to the bolt insertion holes 32 provided the results presented in FIG. 6 .
  • the bore numbers in FIG. 6 were assigned to identify the individual cylinders, with "No. V" assigned to the cylinder 11 located closest to the bottom where the mounting leg parts 31 are present in FIGS. 3 and 5 , and "No. IV", “No. III", "No.
  • the rigidity of the projected portions is lessened relative to the rigidity of the connecting portions by setting the sectional area of the projected portions smaller than the sectional area of the connecting portions or by forming the projected portions with a material different from the material used to form the connecting portions in the structural examples described above, the features of the structural examples described above may be adopted in combination as appropriate.
  • different levels of rigidity may be achieved chemically through a heat treatment or the like.
  • the reciprocating compressor according to the present invention comprising a cylinder block having a plurality of cylinders formed therein, a shaft rotatably passing through the cylinder block and pistons engaged in reciprocal motion in the cylinders as the shaft rotates, which is installed by fastening mounting leg parts disposed at the cylinder block at mounting positions, is characterized in that the mounting leg parts each include a connecting portion extending from the cylinder block and a projected portion formed continuous to the connecting portion and projecting on one side or both sides of the connecting portion along the tightening direction.
  • the projected portions are formed so as to have a lower level of rigidity compared to the connecting portions, the deformation occurring as the mounting bolts are tightened can be concentrated at the projected portions, which makes it possible to assure smooth movement of the pistons by keeping down the extent of cylinder deformation within the allowable range while assuring firm installation of the compressor via the mounting leg parts. As a result, rigorous management of the piston clearance is no longer required and a greater tolerance can be assumed for the piston clearance.

Landscapes

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

Claims (5)

  1. Un compresseur à piston comprenant:
    un bloc-cylindres (3) comprenant une pluralité de cylindres (11) qui y est formée, un arbre (9) traversant rotativement ledit bloc-cylindres (3), et des pistons (19) engagés à l'intérieur desdits cylindres (11) mobile en va et vient lorsque ledit arbre (9) tourne, lequel est installé par des parties de corps de montage de fixation (31) disposées sur ledit bloc-cylindres (3) à des positions de montage, caractérisé en ce que
    lesdites parties de corps de montage (31) sont chacune formées d'une partie de couplage (31a) s'étendant à partir dudit bloc-cylindres (3) et d'une partie projetée (31b) formée de façon continue avec ladite partie de couplage (31a) pour projeter sur un ou sur les deux côtés de ladite partie de couplage (31a) dans la direction de serrage ;
    en ce que ladite partie de couplage (31a) et ladite partie projetée (31b) sont formées comme un seul corps par le même matériau, et
    en ce que ladite partie projetée (31b) a un niveau de rigidité inférieur comparé à ladite partie de couplage (31a) pour concentrer la déformation ayant lieu durant l'installation sur ladite partie projetée (31b).
  2. Compresseur à piston selon la revendication 1, dans lequel
    la section transverse de ladite partie projetée (31b) est ajustée plus petite que la section transverse de ladite partie de couplage (31a), de sorte de concentrer la déformation ayant lieu durant l'installation sur la partie projetée (31b).
  3. Compresseur à piston selon la revendication 1 ou 2, caractérisé en ce que :
    un orifice d'insertion de boulon (32) auquel est inséré un boulon de montage est formé au centre de chaque partie projetée (31b) et l'épaisseur de la paroi de ladite partie de couplage (31a) n'est pas diminuée le long d'une direction perpendiculaire à l'orifice d'insertion de boulon (32).
  4. Compresseur à piston selon l'une des revendications 1 à 3, caractérisé en ce que la forme externe de la partie projetée (31b) est cylindrique.
  5. Compresseur à piston selon l'une des revendications 1 à 4, caractérisé en ce qu'un orifice d'insertion de boulon (32) dans lequel est inséré un boulon de montage est formé au centre de chaque partie projetée (31b), au moins une partie projetée (31b) étant disposée sur un ou sur les deux côtés de la partie de couplage (31a) ayant une longueur dans la direction axiale ajustée approximativement égale ou supérieure au diamètre interne de l'orifice d'insertion de boulon (32).
EP03772804A 2003-02-21 2003-11-17 Compresseur volumetrique a pistons Expired - Lifetime EP1605160B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2003044680 2003-02-21
JP2003044680 2003-02-21
PCT/JP2003/014564 WO2004074683A1 (fr) 2003-02-21 2003-11-17 Compresseur volumetrique a pistons

Publications (3)

Publication Number Publication Date
EP1605160A1 EP1605160A1 (fr) 2005-12-14
EP1605160A4 EP1605160A4 (fr) 2006-08-09
EP1605160B1 true EP1605160B1 (fr) 2009-01-07

Family

ID=32905461

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03772804A Expired - Lifetime EP1605160B1 (fr) 2003-02-21 2003-11-17 Compresseur volumetrique a pistons

Country Status (5)

Country Link
US (1) US20060275148A1 (fr)
EP (1) EP1605160B1 (fr)
JP (1) JP4496534B2 (fr)
DE (1) DE60325782D1 (fr)
WO (1) WO2004074683A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070292280A1 (en) * 2006-06-15 2007-12-20 Yomg-Wan Choi Inside and outside structures of discharging refrigerant in bi-directional swash plate type compressor
CN101535640B (zh) * 2006-11-09 2011-10-05 法雷奥热系统（日本）公司 活塞式压缩机
EP2390503B1 (fr) 2010-05-26 2013-07-10 Valeo Thermal Systems Japan Corporation Compresseur pour des climatiseurs de voiture
DE102020131798A1 (de) 2020-12-01 2022-06-02 Alfred Kärcher SE & Co. KG Kolbenpumpe für ein hochdruckreinigungsgerät

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0243478U (fr) * 1988-08-10 1990-03-26
JPH07158563A (ja) * 1993-12-06 1995-06-20 Toyota Autom Loom Works Ltd 往復動型圧縮機
JP2001182650A (ja) * 1999-12-27 2001-07-06 Toyota Autom Loom Works Ltd 圧縮機
US20020018726A1 (en) * 2000-07-06 2002-02-14 Shigeyuki Hidaka Compressor

Also Published As

Publication number Publication date
WO2004074683A1 (fr) 2004-09-02
DE60325782D1 (de) 2009-02-26
EP1605160A4 (fr) 2006-08-09
JP4496534B2 (ja) 2010-07-07
US20060275148A1 (en) 2006-12-07
EP1605160A1 (fr) 2005-12-14
JPWO2004074683A1 (ja) 2006-06-01

Similar Documents

Publication Publication Date Title
US6658986B2 (en) Compressor housing with clamp
KR0171416B1 (ko) 소음 감소용 압축기 가스킷 및 헤드 조립체
US5556261A (en) Piston type compressor
US6030184A (en) Housing construction for reciprocating piston type compressor
KR100189577B1 (ko) 왕복운동형 압축기
US5456158A (en) Reciprocating compressor
EP1605160B1 (fr) Compresseur volumetrique a pistons
US6368074B1 (en) Piston type compressor
JP3608299B2 (ja) 両頭ピストン式圧縮機
US5782613A (en) Piston type compressor with structure for reducing cylinder bore deformation
JP2006077766A (ja) 多気筒往復圧縮機
US6393964B1 (en) Compressor having piston rotation restricting structure with lubricating inclined guide surface
US7862307B2 (en) Swash plate compressor
US20030044294A1 (en) Sealing mechanism for compressor
CN1230634A (zh) 压缩机的冷却剂吸入结构
JP2001132629A (ja) 斜板式圧縮機
US20060140785A1 (en) Reciprocating compressor
JP2002070739A (ja) 往復式冷媒圧縮機
US20020127118A1 (en) Compressor
US6634868B2 (en) Compressor
US6378417B1 (en) Swash plate compressor in which an opening edge of each cylinder bore has a plurality of chamferred portions
JPH09264254A (ja) ピストン式圧縮機及びその組付方法
EP1164291A2 (fr) Compresseur à plateau en biais
JP3494197B2 (ja) コンプレッサ
JPH09203379A (ja) ピストン式圧縮機

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050921

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SK TR

RBV Designated contracting states (corrected)

Designated state(s): DE FR

A4 Supplementary search report drawn up and despatched

Effective date: 20060706

17Q First examination report despatched

Effective date: 20061027

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: VALEO TERMAL SYSTEMS JAPAN CORPORATION

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: VALEO THERMAL SYSTEMS JAPAN CORPORATION

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR

REF Corresponds to:

Ref document number: 60325782

Country of ref document: DE

Date of ref document: 20090226

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20091008

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20191014

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20201103

Year of fee payment: 18

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 60325782

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220601

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230629