WO2008026496A1 - Compresseur à palettes amovible - Google Patents

Compresseur à palettes amovible Download PDF

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Publication number
WO2008026496A1
WO2008026496A1 PCT/JP2007/066338 JP2007066338W WO2008026496A1 WO 2008026496 A1 WO2008026496 A1 WO 2008026496A1 JP 2007066338 W JP2007066338 W JP 2007066338W WO 2008026496 A1 WO2008026496 A1 WO 2008026496A1
Authority
WO
WIPO (PCT)
Prior art keywords
cam ring
chamber
pressure chamber
high pressure
flange portion
Prior art date
Application number
PCT/JP2007/066338
Other languages
English (en)
Japanese (ja)
Inventor
Keiichi Kanesugi
Hidetoshi Arahata
Mitsuya Ono
Hidehiko Takayama
Original Assignee
Valeo Thermal Systems Japan 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 Valeo Thermal Systems Japan Corporation filed Critical Valeo Thermal Systems Japan Corporation
Priority to JP2008532032A priority Critical patent/JP5120721B2/ja
Publication of WO2008026496A1 publication Critical patent/WO2008026496A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3446—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions

Definitions

  • the present invention relates to a vane type compressor, and more particularly to a vane type compressor capable of reducing pressure pulsation in a discharge path in the compressor.
  • a vane compressor is, for example, a cam ring, a rotor rotatably accommodated in the cam ring, fixed to a drive shaft, and a vane inserted into a plurality of vane grooves provided in the rotor. And a front side member fixed to one end surface of the cam ring and a rear side member fixed to the other end surface.
  • the drive shaft is rotatably supported by the front side member and the rear side member via bearings.
  • the front side member has a suction chamber for communicating with a suction port for working fluid (refrigerant gas) and the suction port. (Low pressure chamber) is formed, and the discharge port (high pressure chamber) in which the discharge port of the working fluid and the discharge port communicate with each other is formed on the rear side member (see Patent Document 1; FIGS. 4 to 6). Constitution).
  • a compression space is defined between the inner peripheral surface of the cam ring and the outer peripheral surface of the rotor.
  • the compression space is partitioned by vanes to form a plurality of compression chambers. Changes as the rotor rotates.
  • a suction port that guides refrigerant gas from the suction chamber to the compression chamber in the suction stroke is formed on the front side end surface of the cam ring, and a discharge valve housing chamber that leads to the discharge chamber is formed in the cam ring.
  • the inner wall is provided with a discharge port corresponding to the compression space. This discharge port opens into the discharge valve storage chamber and is opened and closed by a discharge valve stored in the discharge valve storage chamber.
  • the working fluid when rotational power is transmitted to the drive shaft and the rotor rotates, the working fluid enters the suction chamber from the suction port and is sucked into the compression space from the suction chamber via the suction port. Since the volume of the compression chamber partitioned by the vanes in the compression space changes with the rotation of the rotor, the working fluid confined between the vanes is compressed and is discharged from the discharge port to the discharge valve accommodating chamber through the discharge valve. After that, it is discharged from the discharge chamber (high pressure chamber) through the discharge port. Discharged to the road.
  • the vane type compressor includes a cam ring, a rotor fixed to a drive shaft and rotatably accommodated in the cam ring, a vane inserted into a plurality of vane grooves provided in the rotor, and a cam ring.
  • the front side member arranged on the front side and the shell member surrounding the rear side and the outer peripheral surface of the cam ring are configured, and the drive shaft is rotatably supported by the front side member and the shell member via a bearing.
  • a discharge chamber (high pressure chamber) is provided inside the shell member, and the discharge chamber communicates with a discharge port provided in the shell, and between the outer peripheral surface of the cam ring and the inner peripheral surface of the shell member. It communicates with the discharge valve storage chamber that is formed.
  • the discharge valve storage chamber stores a discharge valve for opening and closing a discharge port that can communicate with the compression chamber formed between the vanes.
  • the working fluid compressed in the compression chamber between the vanes is discharged from the discharge port to the discharge valve storage chamber via the discharge valve, and then discharged from the discharge chamber (high pressure chamber). It is discharged to an external circuit through the mouth.
  • Patent Document 1 Japanese Patent Laid-Open No. 9 158868
  • the working fluid discharged from the compression chamber to the discharge valve storage chamber is guided from the discharge valve storage chamber to the discharge port through the high pressure chamber, and the discharge force, Therefore, the pressure pulsation of the discharge gas discharged into the discharge valve storage chamber is directly transmitted from the discharge port to the external circuit. For this reason, a force that requires a device to reduce pressure pulsation in the discharge path in the compressor. If this is to be realized by another member, the number of parts will increase and the number of seals will increase. Furthermore, in order to adjust the pressure pulsation, it is desirable to have a structure in which the discharge path can be easily adjusted.
  • the present invention has been made in view of such circumstances, and can reduce the pressure pulsation of the discharge gas without increasing the number of parts or the number of seals, and also reducing the pressure pulsation.
  • the main purpose is to provide a vane compressor with a discharge path structure that is easy to run. It is an issue.
  • a vane type compressor is provided with a cam ring, a rotor fixed to a drive shaft, and rotatably accommodated in the cam ring, and the rotor.
  • a vane inserted into a plurality of vane grooves; a side member disposed on one end side of the cam ring; and a shell member surrounding the other end side and the outer peripheral surface of the cam ring; And supporting the drive shaft on the shell member
  • the side member and the shell member are provided with a high-pressure chamber that is in communication with the discharge port by recessing an end surface facing the cam ring on one of the side members and the shell member, and an inner peripheral surface of the cam ring and the shell member.
  • a discharge valve accommodating chamber that can communicate with a compression chamber formed between the vanes is provided between a peripheral surface, and the discharge valve accommodating chamber and the high pressure chamber are provided by a flange portion provided in the cam ring. It is separated and communicated through a passage formed in the flange portion.
  • the working fluid discharged to the discharge valve storage chamber is guided to the high pressure chamber through the passage of the flange portion provided in the cam ring and is sent out from the discharge port. It is possible to reduce the pressure pulsation in the process of being guided to.
  • the high-pressure chamber formed on one of the side member and the shell member is formed by recessing the end surface of the side member or the shell member facing the cam ring! / It is possible to easily tune the pressure pulsation by adjusting the volume of the dent.
  • the side member and the shell member it is preferable to use a member in which a side block portion that contacts the cam ring and a head portion that surrounds the side block portion are integrated.
  • an oil separator is provided on the downstream side of the passage formed in the flange portion, and the high pressure chamber communicates with the discharge valve storage chamber via the passage, and the first high pressure chamber. And a second high-pressure chamber that communicates with the discharge port through an oil separator. Do it like that.
  • the high pressure chamber can be further separated by the oil separator, so that the high pressure pulsation in the discharge path can be further reduced in the process of passing through the oil separator.
  • the passage formed in the flange portion may be constituted by a hole penetrating the wall portion of the flange portion, or may be constituted by a notch in which the periphery of the wall portion of the flange portion is cut out.
  • the side member disposed on one end side of the cam ring and the shell member surrounding the other end side and the outer peripheral surface of the cam ring are provided.
  • the drive shaft is supported by the shell member, and the side member and the shell member are provided with a high-pressure chamber in which one of the end surfaces facing the cam ring is recessed, and the cam ring has an outer peripheral surface and an inner shell member.
  • a discharge valve storage chamber that can communicate with the compression chamber formed between the vanes is provided between the peripheral surface and the discharge valve storage chamber and the high pressure chamber are separated by a flange portion provided in the cam ring.
  • the high pressure chamber is formed by denting the end surface facing the cam ring! /, So the pressure pulsation can be easily tuned by adjusting the concave portion and the volume of the concave portion. It becomes possible.
  • the side member and the shell member have an integrated structure of the side block portion that contacts the cam ring and the head portion that surrounds the side block portion, so that the drive shaft that accommodates the rotor and to which the rotor is fixed is provided.
  • the compressor components that support the shaft and define the suction chamber and discharge chamber can be composed of three parts: side members, cam rings, and shell members. It is possible to further reduce the number of locations.
  • the oil separator disposed downstream of the passage formed in the flange portion communicates with the first high pressure chamber in which the high pressure chamber communicates with the discharge valve housing chamber via the passage, and the discharge port. Are separated from the second high-pressure chamber and communicated via an oil separator. Force pulsation can be further reduced as the working fluid passes through the oil separator.
  • FIG. 1 is a cross-sectional view showing a configuration example of a vane type compressor according to the present invention.
  • FIG. 2 is a cross-sectional view taken along line AA in FIG.
  • FIG. 3 is an exploded perspective view of the vane compressor according to the present invention.
  • FIG. 4 is a view showing a rear side member, (a) is a view seen from the cam ring side, and (b) is a cross-sectional view taken along line BB in (a).
  • FIG. 5 is a view showing a shell member, (a) is a view as seen from the cam ring side, and (b) is a cross-sectional view taken along line DD in (a).
  • FIG. 6 is a view showing a cam ring, (a) is a side view thereof, and (b) is a cross-sectional view taken along the CC spring of (a).
  • Fig. 7 is a view of the rear side member as seen from the cam ring side, and is a view in which an end surface portion in contact with the cam ring is shown by hatching.
  • FIG. 8 is a cross-sectional view taken along the line AA in FIG. 1, showing another example of the configuration of the vane compressor according to the present invention.
  • FIG. 1 to 3 show a vane compressor suitable for a refrigeration cycle using a refrigerant as a working fluid.
  • the vane compressor is inserted into a cam ring 1, a rotor 3 rotatably accommodated in the cam ring, fixed to a drive shaft 2, and a plurality of vane grooves 4 provided in the rotor 3.
  • the rear side member 6 fixed to the rear side end surface of the cam ring 1, and the shell member 7 surrounding the front side end surface and the outer peripheral surface of the cam ring 1 and fitting to the rear side member 6. It is composed!
  • the drive shaft 2 is rotatably supported by the shell member 7 and the rear side member 6 via a plain bearing.
  • the shell member 7 has a working fluid (refrigerant gas) suction port 8 and a suction chamber (low pressure chamber) 9 communicating with the suction port 8, and the rear side member 6 has a working fluid discharge port 10 and this discharge port.
  • a discharge chamber (high pressure chamber) 11 communicating with the outlet 10 is formed.
  • a compression space 12 is defined between the inner peripheral surface of the cam ring 1 and the outer peripheral surface of the rotor 3, and the compression space 12 is partitioned by a vane 5 to form a plurality of compression chambers 13, The volume of each compression chamber changes with the rotation of the rotor 3.
  • the rear side member 6 is a side block portion that abuts on the cam ring 3.
  • the discharge chamber (high pressure chamber) 11 is formed by denting the end surface facing the force muling 1! /,
  • a plurality of separated recesses 11 la to ll id extending in the circumferential direction are formed in the vicinity of the outer peripheral edge of the end surface facing the cam ring 1, and the recesses 11 la to ll id are formed into the cam ring.
  • 1 end A closed space is formed by closing with a flange portion la, which will be described later, and a discharge chamber (high pressure chamber) 11 is configured using at least one of the closed spaces.
  • the discharge chamber 11 is configured using a closed space 11 lb communicating with the discharge port 10 provided on the outer peripheral surface of the rear side member and a closed space 11 la adjacent thereto.
  • the shell member 7 is formed by integrating a side block portion 7a that contacts the cam ring 1 and a shell-like head portion 7b that surrounds the side block portion 7a.
  • a pulley 30 for transmitting the rotational power to the drive shaft 2 is rotatably mounted on the boss 7c, and the rotational power is transmitted from the pulley 30 to the drive shaft 2 via the electromagnetic clutch 31. Yes.
  • the cam ring 1 is formed with flange portions 1 a and lb protruding radially at both ends thereof.
  • the flange portion lb on the front side is formed in a shape that matches the inner peripheral shape of the shell member 7 and is press-fitted into the shell member 7, and the flange portion 1 a on the rear side is formed on the rear side member 6. It is formed in a shape that matches the fitting portion 18, is press-fitted into the fitting portion 18, and comes into contact with the end surface of the rear side member 6. Therefore, when the rear flange portion la is inserted into the insertion portion 18 of the rear side member 6, the flange portion la is brought into contact with the end surface of the rear side member 6 at the portion indicated by the hatch in FIG.
  • the discharge chamber 11 is defined by closing the recesses 11 la ⁇ ;
  • a discharge port 14 is provided on the outer peripheral surface of the cam ring 1 so as to correspond to the compression space 12. Further, between the outer peripheral surface of the cam ring 1 and the inner peripheral surface of the shell member 7, a discharge valve housing chamber 15 defined by flange portions la and lb formed at both ends of the cam ring 1 is formed. The discharge port 14 opens into the discharge valve storage chamber 15, and a compression chamber 13 formed between the vanes can communicate with the discharge port 14. The discharge port 14 is opened and closed by a discharge valve 16 accommodated in the discharge valve accommodation chamber 15.
  • the discharge valve storage chamber 15 and the high pressure chamber 11 are separated by the flange portion la provided in the cam ring 1, and a through hole 17 (formed in the flange) is formed through the wall portion of the flange portion la. Are communicated only via one form of the passageway.
  • the through-holes 17 are formed at positions where the distances from the discharge ports 14 are substantially equal! /.
  • the rear side member 6 has a centrifugal oil separator 20 for separating oil mixed in the discharge gas downstream of the through hole 17 formed in the flange portion la of the cam ring 1. Is provided.
  • a closed space 1 11 a communicating with the through hole 17 of the flange la and a closed space 11 lb communicating with the discharge port 10 adjacent thereto are provided, and the oil separator 20 is An oil separation chamber 22 communicating with the closed space 11 la through the introduction port 21, and the working fluid flowing into the oil separation chamber 22 is swung around the separation cylinder 23 accommodated in the oil separation chamber 22, In the process, the mixed oil is separated, and the discharge gas from which the oil has been separated is sent to the closed space 111b via the separation cylinder 23. The separated oil is returned to the lubricating portion of the compressor via an oil return passage (not shown) connected to the bottom of the oil separation chamber 22.
  • the discharge chamber (high pressure chamber) 11 is connected to the discharge valve storage chamber via the through hole 17 of the flange portion la.
  • Rotational power from a power source is transmitted to the drive shaft 7 via the pulley 30 and the electromagnetic clutch 31, and when the rotor 3 rotates, the working fluid flowing into the suction chamber 9 from the suction port 8 enters the suction port (not shown).
  • the suction port (not shown).
  • the compressed space 12 Since the volume of the compression chamber 13 partitioned by the vanes 5 in the compression space changes as the rotor 3 rotates, the working fluid confined between the vanes 5 is compressed, and the discharge port 14 is connected to the discharge valve 16.
  • the gas is discharged into the discharge valve housing chamber 15 and guided to the high pressure chamber 11 (first high pressure chamber 11a) formed in the rear side member 6 through the through hole 17 formed in the flange portion la of the cam ring 1.
  • the oil is introduced into the oil separator 20 through the introduction port 21, where the oil is separated and guided to the adjacent high pressure chamber 11 (second high pressure chamber l ib), and then from the discharge port 10 to the external circuit. Discharged.
  • the working fluid discharged into the discharge valve storage chamber 15 is guided to the high pressure chamber 11 only through the through hole 17 of the flange portion la provided in the cam ring 1. It is possible to reduce the pressure pulsation of the discharge gas in the process in which the dynamic fluid is guided to the high pressure chamber 11 (first high pressure chamber 1 la) 11. However, the refrigerant introduced into the first high pressure chamber 11a Since the oil is guided to the adjacent high pressure chamber (second high pressure chamber 1 lb) through the oil separator 20, the pressure pulsation can be further reduced even in the process of passing through the oil separator 20.
  • the high pressure chamber 11 described above is formed by the recesses 11 la and 11 lb formed on the end surface of the rear side member 6 facing the cam ring 1, the portion to be recessed, the volume of the recessed portion, etc. It is possible to tune pressure pulsation by adjusting.
  • the rotor 3 is formed by the shell member 7 and the rear side member 6 in which the side block portions 6a and 7a and the head portions 6b and 7b are integrated, and the cam ring 1. And the components of the compressor that support the drive shaft 2 to which the rotor 3 is fixed and that define the suction chamber 9 and the discharge chamber 11 are configured, so that the number of parts can be reduced. At the same time, it is possible to reduce the number of places to be sealed, thereby reducing costs and reducing refrigerant leakage.
  • the force shown in the example in which the through hole 17 is formed in the wall portion of the flange portion la as one form of the passage formed in the flange portion la is not limited to this.
  • the same effect can be obtained even if the passage is constituted by the notch 25 in which the peripheral edge of the wall portion of the flange portion la is cut out.
  • the force shown in the configuration example in which the high pressure chamber 11 is provided in the rear side member 6 may be the same as that described above by providing the high pressure chamber in the shell member 7 configuring the front side member. Good.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Compresseur à palettes amovible capable de réduire l'impulsion de pression d'un gaz de décharge sans augmenter le nombre de pièces ni le nombre de positions d'étanchéité et comportant un passage de décharge permettant le réglage facile de la réduction de l'impulsion de pression. Le compresseur à palettes amovible comprend un anneau à came (1), un rotor (3) fixé sur un arbre de transmission (2), des palettes (5) insérées dans des rainures de palettes (4) formées dans le rotor (3), un élément latéral (6) disposé au niveau d'une extrémité de l'anneau à came (1), et une coque (7) entourant l'autre extrémité et la surface périphérique externe de l'anneau à came (1). L'arbre de transmission (2) est supporté de manière pivotante sur l'élément latéral (6) et la coque (7). La surface d'extrémité d'un élément parmi l'élément latéral (6) et la coque (7) faisant face à l'anneau à came (1) est évidée pour former une chambre haute pression (11). Une chambre de logement de soupape d'évacuation (15) capable de communiquer avec une chambre de compression (13) est formée entre la surface périphérique externe de l'anneau à came (1) et la surface périphérique interne de la coque (7). La chambre de logement de soupape d'évacuation(15) et la chambre haute pression (11) sont séparées l'une de l'autre par la partie de bride (1a) de l'anneau à came (1), et sont autorisées à communiquer l'une avec l'autre via un passage formé dans la partie de bride (1a).
PCT/JP2007/066338 2006-08-29 2007-08-23 Compresseur à palettes amovible WO2008026496A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008532032A JP5120721B2 (ja) 2006-08-29 2007-08-23 ベーン型圧縮機

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006-231586 2006-08-29
JP2006231586 2006-08-29

Publications (1)

Publication Number Publication Date
WO2008026496A1 true WO2008026496A1 (fr) 2008-03-06

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ID=39135779

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Application Number Title Priority Date Filing Date
PCT/JP2007/066338 WO2008026496A1 (fr) 2006-08-29 2007-08-23 Compresseur à palettes amovible

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JP (1) JP5120721B2 (fr)
WO (1) WO2008026496A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010038144A (ja) * 2008-08-08 2010-02-18 Toyota Industries Corp ベーン圧縮機
CN102108968A (zh) * 2009-12-29 2011-06-29 法雷奥热***（日本）公司 叶片型压缩机
CN102108967A (zh) * 2009-12-29 2011-06-29 法雷奥热***（日本）公司 叶片型压缩机
JP2011153618A (ja) * 2009-12-29 2011-08-11 Valeo Japan Co Ltd ベーン型圧縮機
CN103032326A (zh) * 2011-09-29 2013-04-10 三菱电机株式会社 叶片旋转式压缩机
EP3460096A1 (fr) 2017-09-25 2019-03-27 Valeo Japan Co., Ltd Élément coulissant pour compresseur

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0222689U (fr) * 1988-07-26 1990-02-15
JPH0716073Y2 (ja) * 1989-04-07 1995-04-12 セイコー精機株式会社 気体圧縮機
JPH10252676A (ja) * 1997-03-10 1998-09-22 Seiko Seiki Co Ltd 気体圧縮機用シリンダおよび気体圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0222689U (fr) * 1988-07-26 1990-02-15
JPH0716073Y2 (ja) * 1989-04-07 1995-04-12 セイコー精機株式会社 気体圧縮機
JPH10252676A (ja) * 1997-03-10 1998-09-22 Seiko Seiki Co Ltd 気体圧縮機用シリンダおよび気体圧縮機

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010038144A (ja) * 2008-08-08 2010-02-18 Toyota Industries Corp ベーン圧縮機
CN102108968A (zh) * 2009-12-29 2011-06-29 法雷奥热***（日本）公司 叶片型压缩机
CN102108967A (zh) * 2009-12-29 2011-06-29 法雷奥热***（日本）公司 叶片型压缩机
JP2011137426A (ja) * 2009-12-29 2011-07-14 Valeo Japan Co Ltd ベーン型圧縮機
JP2011153618A (ja) * 2009-12-29 2011-08-11 Valeo Japan Co Ltd ベーン型圧縮機
CN103032326A (zh) * 2011-09-29 2013-04-10 三菱电机株式会社 叶片旋转式压缩机
EP3460096A1 (fr) 2017-09-25 2019-03-27 Valeo Japan Co., Ltd Élément coulissant pour compresseur

Also Published As

Publication number Publication date
JPWO2008026496A1 (ja) 2010-01-21
JP5120721B2 (ja) 2013-01-16

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