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EP0513475A2 - Compresseur hermétique - Google Patents

Compresseur hermétique Download PDF

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Publication number
EP0513475A2
EP0513475A2 EP92102316A EP92102316A EP0513475A2 EP 0513475 A2 EP0513475 A2 EP 0513475A2 EP 92102316 A EP92102316 A EP 92102316A EP 92102316 A EP92102316 A EP 92102316A EP 0513475 A2 EP0513475 A2 EP 0513475A2
Authority
EP
European Patent Office
Prior art keywords
compressing mechanism
refrigerant
piston
compressor according
lubricating oil
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Withdrawn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
EP92102316A
Other languages
German (de)
English (en)
Other versions
EP0513475A3 (en
Inventor
Akihiko Ishiyama
Takeshi Odajima
Tadashi Iizuka
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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 Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP0513475A2 publication Critical patent/EP0513475A2/fr
Publication of EP0513475A3 publication Critical patent/EP0513475A3/en
Withdrawn legal-status Critical Current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
    • 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
    • F04B39/0094—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 crankshaft
    • 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
    • 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
    • F04B39/02—Lubrication
    • F04B39/0215—Lubrication characterised by the use of a special lubricant
    • 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
    • F04B39/125—Cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/04—Phosphor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/08—Ceramics; Oxides
    • F05C2203/0804—Non-oxide ceramics
    • F05C2203/0856—Sulfides
    • F05C2203/086—Sulfides of molybdenum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the present invention relates to a sealed type compressor and, more particularly, to a sealed compressor which exhibits improved reliability and performance in a case where it is operated with alternate refrigerant R134a which meets the freon (fluorocarbon) regulation.
  • freon 12 which has been used in the refrigeration cycle of a refrigerating apparatus such as a refrigerator, is regulated. Therefore, R134a tends to be used as an alternate refrigerant.
  • a reciprocating compressor A which belongs to the sealed compressors for use in refrigerators, freezing chambers or air conditioning apparatuses, has a compressing mechanism 2 and an electric motor 3 both accommodated in a sealed container 1. Furthermore, refrigerator or lubricant oil 4 is contained in the bottom portion of the sealed container 1.
  • a piston 22 is slidably disposed in a cylinder 21 of the compressing mechanism 2. The piston 22 thus disposed is reciprocated by the eccentric rotation of an eccentric portion 24 of a crank shaft 23 which transmits the rotational force of the electric motor 3. As a result, the refrigerant gas can be sucked, compressed and discharged.
  • the refrigerant compressed by the compressing mechanism 2 and discharged from the compressor A is at a high temperature and under a high pressure. Therefore, the refrigerant gas radiates heat and is liquefied when it passes through a condensor B formed by a zigzag pipe as shown in Fig. 8.
  • the pressure of the liquefied refrigerant is lowered by a pressure-reducing mechanism C comprising a capillary tube before it is introduced into an evaporator D.
  • a pressure-reducing mechanism C comprising a capillary tube
  • R12, R22, or R502 or the like is used as the refrigerant.
  • the temperature at which the sealed compressor is operated, the material of each of the elements of the movable portions and the volume of the cylinder and the like have been determined in consideration of the type of the refrigerant employed. Therefore, in a case where R134a is used as the alternate refrigerant, a problem is predicted that the reliability at the temperature at which the conventional compressor has been operated.
  • the reason for this lies in the degradation of the refrigerating machine oil (lubricating oil), the lubricating performance thereof, and the stability of the material of an enameled wire 31 and that of an insulating member 32, for example, deterioration in the facility in origomer extraction.
  • an object of the present invention is to provide a sealed type compressor which is capable of overcoming the above-described problems, designed to use R134a which does not destruct ozone and displays reliability and performance comparable to those obtained in the case in which R12 is used.
  • the sealed compressor according to the present invention is used in a refrigeration cycle in which R134a is used as the refrigerant gas.
  • the basic structure of the compressor comprises a sealed container, a reciprocating piston type compressing mechanism disposed in the container and an electric motor for driving the compressing mechanism.
  • the bottom portion of the container forms an oil reservoir for accumulating lubricating oil.
  • the present invention is characterized in that the oil reservoir is provided with a cooling device.
  • the cooling device cools the lubricating oil in the oil reservoir to lower the temperature of the discharged gas from the compressor and that of the coil of the electric motor below the temperatures realized in a case where the compressor uses refrigerant R12. therefore, deterioration of the lubricating oil (refrigerator oil) can be prevented. Furthermore, the quantity of origomer extracted from the enamel wire and the insulating member which are exposed to refrigerant. R134a can be the same or smaller than that obtained in the case in which they are exposed to refrigerant R12.
  • the refrigeration cycle includes a condenser for condensing the refrigerant gas discharged from the compressing mechanism and an evaporator for evaporating the condensed refrigerant.
  • the condenser includes a first portion adjacent to the compressing mechanism and a second portion adjacent to the evaporator.
  • the cooling device is disposed in the oil reservoir and has its inlet and outlet ports respectively connected to an outlet port of the first portion of the condenser and an inlet port of the second portion of the same, so that the refrigerant, which has passed through the first portion of the condenser, flows in a heat exchange relationship with the lubricating oil in the oil reservoir to cool the lubricating oil and, then, is introduced into the second portion of the condenser.
  • a manganese phosphate layer is formed in at least a portion of the surface of a crank shaft which connects the compressing mechanism with the electric motor.
  • a molybdenum disulfide sprayed layer may be formed on the manganese phosphate layer. Since the compression ratio in the case where refrigerant R134a is used is higher than in the case where refrigerant R12, the frictional forces acting on the surface of the crank shaft and the surface of the piston, which are sliding surfaces of the compressing mechanism, are larger in the case where R134a is used. The manganese phosphate layer and the molybdenum disulfide sprayed layer improve the self-lubricating performance of the sliding surfaces. Therefore, even when R134a is used, the reliability of the operation of the moving portions can be kept for a long time.
  • the compressing mechanism includes a cylinder head having a discharge port formed at a position which confronts the head of the piston and the head of the piston has a projection at a position aligned with the discharge port of the cylinder head, so that the projection is received by the discharge port when the piston reaches its top dead center.
  • a sealed compressor A is designed to be used with R134a to cool a refrigerator and has a sealed container 1 of a metal.
  • the container 1 accommodates compressing mechanism 2 and electric motor 3 which are drivingly connected to each other by a crank shaft 23.
  • the electric motor 3 has a stator 3a which has a coil 31 wound around a stator core via an insulating material 32.
  • a rotor 3b of the electric motor 3 is secured to an end portion of the crank shaft 23 for rotation therewith.
  • the compressing mechanism 2 has a cylinder 21 and a piston 22 which is reciprocally disposed in the cylinder bore in the cylinder 21.
  • the piston 22 is connected to an eccentric portion 24 of the crank shaft 23 so as to be driven in such a manner that it is reciprocated in the cylinder 21.
  • a cylinder head 25 forms a closed working-chamber 21a in cooperation with the cylinder 21 and the piston 22.
  • the volume of the working chamber 21a is changed when the piston 22 is reciprocated.
  • the cylinder head 25 has a discharge port 26 formed at a position which confronts the head of the piston 22.
  • a projection 22a is formed on the head of the piston 22 so that the projection 22a is received into the discharge port 26 when the piston 22 reaches its top dead center.
  • the bottom portion of the sealed container 1 forms an oil reservoir 4 for accumulating lubricating oil (also called “refrigerator oil”) for lubricating movable portions of the compressing mechanism 2 such as the eccentric portion 24 and the peripheral surface of the piston 22.
  • lubricating oil also called "refrigerator oil”
  • the lubricating oil accumulated in the oil reservoir 4 is, by a known oil circulating mechanism (omitted from illustration), forcibly sent to the above-described movable portions so that they are lubricated. Then, the lubricating oil flows along the stator 3a of the electric motor 3 to cool the coil 31 and the insulating member 32 of the stator 3a and then drops and returns to the oil reservoir 4.
  • the cylinder head 26 has a suction port (omitted from illustration) in addition to the discharge port 26.
  • the discharge port 26 and the suction port are connected to a refrigeration cycle as shown in Fig. 2.
  • the reciprocating motion of the piston 22 changes the volume of the working chamber 21a, causing the working chamber 21a to suck the refrigerant R134a, compress the same and discharge the same.
  • the refrigeration cycle shown in fig. 2 comprises a condenser B for receiving high temperature and high pressure refrigerant gas discharged from the compressor A to condense it, a pressure reducing mechanism C for reducing the pressure of the condensed refrigerant and formed by a capillary tube and an evaporator D for evaporating the refrigerant the pressure of which has been reduced, to cause it to absorb heat of circumambient air.
  • the refrigeration cycle shown in Fig. 2 has a modification to be described below:
  • the oil reservoir 4 shown in Fig. 1 has a lubricating oil cooling device E which includes a pipe 5 which extends through the lubricating oil accumulated in the oil reservoir 4.
  • the condenser B shown in Fig. 2 includes a first portion, that is, an upstream portion B1, which has an inlet port E1 connected to the discharge port of the compressing mechanism 2.
  • the condenser B further includes a second portion, that is, a downstream portion B2, which has an outlet port E4 connected to the pressure reducing mechanism C.
  • the end portions of the pipe 5 shown in fig. 1 are respectively connected to the outlet port E2 of the first portion B1 and the inlet port E3 of the second portion B2 of the condenser B.
  • the refrigerant gas discharged from the compressor A passes first through the first portion B1 of the condenser B, then, through the pipe 5 of the cooling device E and then through the second portion B2 of the condenser B. Then, the gas is introduced into the pressure reducing mechanism C and passes through the refrigeration cycle in the above-described sequential order. Thus, the refrigerant gas returns to the compressor A.
  • the temperature of the lubricating oil in the compressor reaches 90°C to 100°C.
  • the temperature, at which the refrigerant gas discharged from the compressor is condensed is set to be of the order of 40°C to 50°C.
  • the refrigerant present in the outlet port E2 of the first portion B1 of the condenser B is in a state in which gas and liquid are mixed with each other.
  • the refrigerant in the above-described state passes through the pipe 5 of the cooling device E, it exchanges heat with the lubricating oil in the oil reservoir 4 and absorbs heat from the lubricating oil to lower the temperature of the lubricating oil. Since the thus cooled lubricating oil is supplied to the moving portions of the compressing mechanism, the compressing mechanism is lubricated and as well as cooled down. Furthermore, the lubricating oil, which has performed the lubricating operation, cools down the electric motor 3.
  • the temperature of the refrigerant, which passes through the pipe 5 of the cooling device, can be changed by adjusting the position at which the pipe 5 is connected to the condenser B to thereby change the ratio of the gas to the liquid of the refrigerant which is introduced into the pipe 5 of the cooling device.
  • the pipe 5 is connected to an intermediate portion (the intermediate portion in terms of the heat capacity) of the condenser B.
  • Fig. 3 illustrates the results of measurements of the degree of deterioration in the lubricating oil with respect to the time while compressors were operated, the measurement being carried out by means of the chromaticity.
  • the two solid line curves X and Y show the results measured when the compressor was operated with the refrigerant R134a
  • the broken line curve line Z shows the results measured when the compressor was operated with the refrigerant R12.
  • Curves X and Z respectively show the results obtained in the cases where the compressors had not the lubricating oil cooling device E and were operated with the refrigerant R134a and with the refrigerant R12 and both at the same operation temperature (the conventional operation temperature set for use with R12).
  • the curve Y shows the result obtained in the case where the compressor had the lubricating oil cooling device E and was operated with the refrigerant R134a.
  • the compressor having the lubricating oil cooling device E according to the present invention exhibits a deterioration in the lubricating oil substantially equal to the deterioration in the lubricating oil experienced with the conventional compressor having no lubricating oil cooling device and operated with the refrigerant R12.
  • Fig. 4 illustrates the results of measurements of the quantity of extracted origomer from the enamel wire 31 and that from the insulating member 32 with respect to the time (days) while the compressor was operated.
  • the two solid line curves x and y show the results obtained when compressors were both operated with the refrigerant R134a
  • the broken line curve z shows the results obtained when a compressor was operated with the refrigerant R12.
  • Curves x and z respectively show the results obtained in the case where the compressors which had not the lubricating oil cooling device E and operated respectively with refrigerant R134a and with the refrigerant R12 and both at the same operation temperature (the conventional operation temperature set for R12).
  • the curve y shows the result obtained in the case where the compressor had the lubricating oil cooling device E, and operated with the refrigerant R134a.
  • the compressor having the lubricating oil cooling device E according to the present invention exhibits thew extracted origomer quantity y which is smaller than the extracted origomer quantity z obtained in the case where the conventional compressor having no lubricating oil cooling device is operated with the refrigerant R12. Therefore, even if the compressor according to the present invention is operated with the refrigerant R134a, the moving portions of the compressing mechanism can be protected from problems caused due to the action of the origomer deposited from the enamel wire or the insulating member.
  • the projection 22a formed on the head of the piston 22 reduces the re-expansion loss due to the dead volume of the discharge port 26. Therefore, the volumetric efficiency of the compressor is improved by about 5%. Furthermore, since the whole of the compressor is cooled by the lubricating oil cooling device E and, thus, the temperature of the refrigerant gas contained in the sealed container 1 is lowered by about 10°C, the volumetric efficiency is additionally improved by about 3%. Thus, the total of the volumetric efficiency is improved by 8% because the improvement in the volumetric efficiency realized by the projection 22a of the piston 22 is about 5%, to thereby compensate for the deterioration in the refrigerating performance due to the physical properties of R134a.
  • the sliding surface of each of the piston 22 and the crank shaft 23 has formed thereon a manganese phosphate layer 27 to improve the self-lubricating performance of each of the sliding surfaces. Therefore, the reliability of the operation of the compressing mechanism can be improved. If the manganese phosphate layer 27 is formed only on either the piston 22 or the crank shaft 23, a corresponding effect can also be obtained.
  • a molybdenum disulfide sprayed layer 28 is formed on the manganese phosphate layer 27, molybdenum disulfide (MoS2) being a solid lubricant 28a.
  • the molybdenum disulfide sprayed layer 28 is formed in such a manner that a mixture of the solid lubricant 28a and a binder (an epoxy resin or an amidoimide resin) 28b dissolved by a solvent is sprayed onto the surface of the manganese phosphate layer 27. Then, the solvent is perfectly removed by heating, which is performed at about 100°C, so that the molybdenum disulfide sprayed layer 28 is formed. Then, the surface of the molybdenum disulfide sprayed layer 28 is brushed in a specific direction so as to forcibly orient the particles of the solid lubricant 28a.
  • the layer 28 is heated at about 120°C to 150°C so as to polymerize the binder 28b by a thermal setting reaction.
  • the solvent for the amideimide resin may be, for example, N-methylpyrolidone
  • the solvent for the epoxy resin may be, for example, a mixture of Cellosolve acetate and methylethylketone. Since the particles of the solid lubricant 28a, which have been forcibly oriented, are oriented in a specific direction, its surface is peeled due to cleavage when frictional force is added to the same. Therefore, it has a very small frictional resistance.
  • the present invention provides a reliable and high performance sealed compressor for use with the R134a refrigerant which will not destruct ozone.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
EP19920102316 1991-03-15 1992-02-12 Sealed type compressor Withdrawn EP0513475A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP3051111A JPH04287876A (ja) 1991-03-15 1991-03-15 密閉形圧縮機
JP51111/91 1991-03-15

Publications (2)

Publication Number Publication Date
EP0513475A2 true EP0513475A2 (fr) 1992-11-19
EP0513475A3 EP0513475A3 (en) 1992-12-23

Family

ID=12877699

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920102316 Withdrawn EP0513475A3 (en) 1991-03-15 1992-02-12 Sealed type compressor

Country Status (4)

Country Link
EP (1) EP0513475A3 (fr)
JP (1) JPH04287876A (fr)
KR (1) KR920018354A (fr)
CN (1) CN1026431C (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0890743A2 (fr) * 1997-06-26 1999-01-13 Taiho Kogyo Co., Ltd. Plateau oscillant pour compresseur à plateau oscillant
FR2845095A1 (fr) * 2002-06-24 2004-04-02 Toyota Jidoshokki Kk Piece coulissante

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3473776B2 (ja) * 1994-02-28 2003-12-08 東芝キヤリア株式会社 密閉形コンプレッサ
AU2003289340A1 (en) * 2002-12-16 2004-07-09 Matsushita Refrigeration Company Refrigerant compressor, and refrigerating machine using the same
CN100396921C (zh) * 2003-06-27 2008-06-25 乐金电子(天津)电器有限公司 密闭型压缩机的机架结构
JP4538307B2 (ja) * 2004-12-10 2010-09-08 日立アプライアンス株式会社 密閉型圧縮機
BRPI0902973B1 (pt) * 2009-08-27 2020-03-10 Embraco Indústria De Compressores E Soluções E Refrigeração Ltda. Bloco para compressor alternativo de refrigeração
CN103452854B (zh) * 2013-08-19 2016-06-29 广东美芝制冷设备有限公司 旋转式压缩机
CN108088104B (zh) * 2017-11-23 2020-07-03 中科美菱低温科技股份有限公司 一种自调节智能制冷系统

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2372404A1 (fr) * 1976-11-24 1978-06-23 Centre Techn Ind Mecanique Procede et dispositif de refroidissement d'un bain de fluide dans une enceinte fermee
DE3902745A1 (de) * 1989-01-31 1990-08-02 Stiebel Eltron Gmbh & Co Kg Waermepumpenanlage
EP0438922A1 (fr) * 1989-12-28 1991-07-31 Kabushiki Kaisha Toshiba Compresseur de refroidissement pour R 134A

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2372404A1 (fr) * 1976-11-24 1978-06-23 Centre Techn Ind Mecanique Procede et dispositif de refroidissement d'un bain de fluide dans une enceinte fermee
DE3902745A1 (de) * 1989-01-31 1990-08-02 Stiebel Eltron Gmbh & Co Kg Waermepumpenanlage
EP0438922A1 (fr) * 1989-12-28 1991-07-31 Kabushiki Kaisha Toshiba Compresseur de refroidissement pour R 134A

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0890743A2 (fr) * 1997-06-26 1999-01-13 Taiho Kogyo Co., Ltd. Plateau oscillant pour compresseur à plateau oscillant
EP0890743A3 (fr) * 1997-06-26 1999-03-31 Taiho Kogyo Co., Ltd. Plateau oscillant pour compresseur à plateau oscillant
US6123009A (en) * 1997-06-26 2000-09-26 Taiho Kogyo Co., Ltd. Swash plate of swash-plate compressor
FR2845095A1 (fr) * 2002-06-24 2004-04-02 Toyota Jidoshokki Kk Piece coulissante
US7241722B2 (en) 2002-06-24 2007-07-10 Kabushiki Kaisha Toyota Jidoshokki Sliding component

Also Published As

Publication number Publication date
EP0513475A3 (en) 1992-12-23
CN1026431C (zh) 1994-11-02
CN1065127A (zh) 1992-10-07
JPH04287876A (ja) 1992-10-13
KR920018354A (ko) 1992-10-21

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