WO2012166051A1 - Plaque de clapet pour compresseur - Google Patents

Plaque de clapet pour compresseur Download PDF

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Publication number
WO2012166051A1
WO2012166051A1 PCT/SG2012/000189 SG2012000189W WO2012166051A1 WO 2012166051 A1 WO2012166051 A1 WO 2012166051A1 SG 2012000189 W SG2012000189 W SG 2012000189W WO 2012166051 A1 WO2012166051 A1 WO 2012166051A1
Authority
WO
WIPO (PCT)
Prior art keywords
plate
compressor
valve plate
suction
thermally insulating
Prior art date
Application number
PCT/SG2012/000189
Other languages
English (en)
Inventor
Kok How Wan
San Haw CHONG
Original Assignee
Panasonic 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 Panasonic Corporation filed Critical Panasonic Corporation
Priority to US13/809,702 priority Critical patent/US20130108493A1/en
Priority to CN2012800019878A priority patent/CN103003570A/zh
Publication of WO2012166051A1 publication Critical patent/WO2012166051A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • 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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1066—Valve plates

Definitions

  • the present invention relates generally to valve plate for a compressor, a compressor, and to a method of thermal insulation applied in a compressor.
  • Gas-compression refrigeration has been and still is the most widely used method for fridges and air-conditioning of large public buildings, private residences, hotels, hospitals, theatres, restaurants and automobiles etc.
  • the gas-compression refrigeration system uses a circulating refrigerant as a medium, which absorbs and removes heat from a location or space to be cooled and subsequently dissipates the heat elsewhere.
  • a typical gas-compression system has four components: a compressor, a condenser, an expansion valve (also called a throttle valve), and an evaporator.
  • the compressor sucks low-temperature and low-pressure saturated gas from the evaporator and compresses the gas to high-pressure, resulting in higher temperature as well.
  • To improve the volumetric and energetic efficiencies of the compressor which is to draw larger volume of the gas within a compressor's single compression cycle, it is desired to thermally insulate the drawn low-temperature gas in the suction line from hotter parts of the compressor so that the low-temperature gas from the evaporator can be pumped in larger volume when its temperature is kept low.
  • One of the major causes responsible for heating the internal components of the compressor is its discharge system, as the refrigerant gas reaches its highest temperature levels during the compression cycle. The heat generated by the compression is dissipated to other components of the compressor.
  • the suction line There are many components along the suction line. These components include a muffler, a cylinder head, and some pipelines, etc.
  • the muffler Inside a commonly adopted reciprocating compressor for a refrigeration system, the muffler is usually provided inside the compressor shell at a gas suction side for conducting the received gas to a suction valve of the compressor.
  • the valve with its valve plate, is the interface between the suction and discharge gas.
  • One approach is to improve thermal insulation for the storage or interface medium of the suction gas. These mediums can be manufactured from materials of low thermal conductivity, such as resins or plastics. Recently, there are also some structural approaches to improve thermal insulation of the muffler.
  • One suction muffler suggested in WO02/101239A1 has designed two acoustic chambers for refrigerant gas communication inside a muffler.
  • a first acoustic chamber of the muffler which directly receives low-temperature gas outside the compressor, is surrounded by a second acoustic chamber of the muffler.
  • This structure provides additional thermal insulation to the received low-temperature gas in the first acoustic chamber because heat flow from the exterior has to cross surrounding walls of the second acoustic chamber to reach the low-temperature gas inside the first acoustic chamber.
  • valve plate for a compressor having a thermally insulating capability for thermally insulating a suction muffler of the compressor from a discharge plenum in a cylinder head of the compressor.
  • the valve plate may comprise a first plate element made from thermally insulating material and a second plate element made from metal.
  • the first and second plate elements may be joint by one or more of a group consisting of press-fitting, injection molding, induction heating, bonding adhesive, and ultrasonic welding.
  • the first plate element may be disposed to face the discharge plenum.
  • the valve plate may further comprise a third plate element made from metal, and the first plate element is sandwiched between the first and second plate elements.
  • the first, second and third plate elements may be joint by one or more of a group consisting of press-fitting, injection molding, induction heating, bonding adhesive, and ultrasonic welding.
  • the first plate element may be configured to be received in a recess formed in the second plate element.
  • the recess may be formed around a suction orifice in the second plate element.
  • the second plate element may comprise a raised portion around a discharge orifice in the second plate element, and the first plate element comprises an opening for receiving the raised portion.
  • the valve plate may comprise a first plate element made from thermally insulating material and a metal coating on one or both sides of the first plate.
  • a method of thermal insulation applied in a compressor comprising using a valve plate having a thermally insulating capability for thermally insulating a suction muffler of the compressor from a discharge plenum in a cylinder head of the compressor.
  • Figure 1 shows a schematic diagram illustrating a temperature profile of a refrigerant gas path inside a reciprocating compressor
  • Figure 2 shows schematic drawings illustrating heat flow from high temperature discharge gas to the suction path at the suction and discharge interface, using (a) a conventional valve plate and (b) an valve plate structure according to an example embodiment.
  • Figure 3 shows a schematic drawing of a compressor according to an example embodiment.
  • Figure 4 shows a schematic drawing illustrating a valve plate structure according to an example embodiment.
  • Figure 5 shows a schematic drawing illustrating a valve plate structure according to an example embodiment.
  • Figure 6 shows a schematic drawing illustrating a valve plate structure according to an example embodiment.
  • Figure 7 shows a schematic drawing illustrating a valve plate structure according to an example embodiment.
  • Figure 8 shows a schematic drawing illustrating a valve plate structure according to an example embodiment.
  • Figure 9 shows a schematic drawing illustrating a valve plate structure according to an example embodiment.
  • a compressor 100 for hermetic gas- compression refrigeration is exposed for indicating a temperature profile of a refrigerant gas along its travelling path inside the compressor 100.
  • the present invention is applicable to both Hermetic and semi-hermetic compressors.
  • the difference between the hermetic and semi-hermetic compressors is that the hermetic compressors use a one-piece welded steel casing that cannot be opened for repair.
  • a semi-hermetic compressor uses a large cast metal shell with gasketed covers that can be opened to replace motor and pump components.
  • the compressor 100 comprises a suction inlet pipeline 102, a suction muffler
  • the suction muffler 104 is disposed inside the shell 106 of the compressor 100.
  • the suction muffler 104 connects to the cylinder head 108 which has a suction plenum 116 and a discharge plenum 114 at its interior.
  • the suction plenum 116 receives the gas with lower temperature while the discharge plenum 114 receives the compressed gas from the cylinder chamber (hidden) at higher temperature.
  • the suction plenum 116 and the discharge plenum 114 are connected to a cylinder chamber (hidden) via a suction valve and a discharge valve (not shown) respectively.
  • the discharge plenum 114 is further connected to the discharge pipeline 118 of the compressor 100 via muffler cover discharge 110 and discharge line 112 for discharging compressed gas at high temperature for the refrigeration system.
  • the low- temperature refrigerant gas is drawn into the suction muffler 104 via the suction inlet pipeline 102, either directly or indirectly.
  • the gas has the lowest temperature inside the compressor shell 106, typically at about 40.5 degree Celsius.
  • the gas is drawn further towards the muffler 104, it is heated up by the surroundings to typically about 47.9 degree Celsius at the entrance (point 2) of the muffler 104.
  • the gas temperature is typically further raised to about 60.3 degree Celsius (point 3) before reaching the cylinder head 108.
  • the temperature of the gas has typically reached about 66.9degree Celsius (point 4).
  • the gas is then drawn via the suction valve (not shown) to be compressed in the cylinder chamber (hidden).
  • the compressed gas leaves via the discharge valve (not shown) and enters the discharge plenum 114 of the cylinder head 108.
  • the temperature of the compressed gas is typically about 1 17.9 degree Celsius (point 5).
  • the gas starts to cool down.
  • the high temperature and high pressure gas typically cools to about 82.8degree Celsius at the point (point 7) where the discharge pipeline exits the shell 106.
  • the gas has a large temperature difference between the adjacent suction 116 and discharge plenums 1 14. It has been recognised by the applicant that the high temperature gas contained in the discharge plenum 114 constitutes a heat source which can significantly contribute to the temperature increase in the low temperature suction refrigerant gas in the suction plenum 116 prior to compression.
  • the increase in the suction refrigerant gas temperature causes an increase in its specific volume and reduces the mass flow rate of the refrigerant gas, which in turn leads to a drop in the compressor's efficiency due to a reduction in cooling performance.
  • FIG. 2a shows the cross sectional view of a cylinder head 202 bolted to the cylinder body 203. The inventors have recognized that significant heat transmission takes place between the hot gas in the discharge plenum 204 and the gas in suction muffler 205 though the valve plate 201 , which is typically made from a metal.
  • FIG. 2b shows the resultant heat flow diagram when a valve plate structure 210 comprising first and second metal plate elements 212, 214 and an inlet 215 made from an insulating material in the plate element 212 1s provided, according to an example embodiment.
  • the inlet 215 functions as a thermal barrier to hinder heat transmission from the gas in the discharge plenum 216 to the gas in the suction muffler 218. This advantageously improves the overall thermal efficiency of the compressor.
  • Valve plate structure 210 acts as a seal between different pressure zones within the compressor. It contains both a suction orifice 220 and a discharge orifice 222, and thus provides fluid communication of the refrigerant. It is positioned between suction reed 224 and discharge reed 226, which open when differential pressures between zones are reached and allow gases to flow from high to low pressure regions during the compression cycle. Due to its functional attributes, valve plate structure 210 preferably is corrosion, chemical and wear resistant, as well as preferably being able to withstand high temperature. It also provides the seal to prevent leakage of refrigerant. Preferably, the valve plate structure 210 also allows run-time low noise and smooth movement.
  • FIG. 3 a schematic drawings of a compressor according to an example embodiment is shown. More particular, a cylinder head 300 is exposed to show its interior structure and assembly.
  • the cylinder head 300 is generally rectangular in shape with its four corners rounded off. At the four corners, four equal sized apertures 308a-d are provided for bolting, using part 309a-d, the cylinder head 300 to the cylinder body 307.
  • Other components in the cylinder head assembly include valve plate structure 301 , comprising valve plate 301a and an insulating material inlet 301 b, a discharge reed 302, a suction reed 303, and sealing gaskets 304, 305.
  • a suction muffler 306 fits into the suction plenum (hidden) in the cylinder head 300.
  • FIGS 4 to 8 show different types of valve plate structures according to different embodiments.
  • Figure 4 shows a valve plate structure 400, comprising two plates 401 and 402.
  • Plate 401 is made of thermally insulating material, while plate 402 is made of metal to provide strength.
  • the thermally insulating material plate 401 will be located towards the discharge reed (not shown).
  • the surface of the valve plate structure 400 facing the cylinder bore (not shown) is made of metal, i.e. metal plate 402. This preferably prevents deformation under high pressure.
  • a flat surface finish of the thermally insulating material plate 401 is preferably ensured to prevent leakage.
  • the flatness of the thermally insulated valve plate can be ensured through flatness control methods such as, but not limited to, lapping.
  • valve plate may be rubbed on a flat surface with an abrasive such as sandpaper there between, by hand movement or by machine.
  • abrasive such as sandpaper
  • the cross sectional view 414 shows the protrusions from plate 401 inserted in the corresponding holes in plate 402 so that plate 401 can be aligned and press fitted with plate 402.
  • Figure 5 shows a valve plate structure 500, comprising two plates 501 and 502.
  • Plate 501 is made of thermally insulating material, while plate 502 is made of metal to provide strength.
  • the thermally insulating material plate 501 will be located towards the discharge reed (not shown).
  • the surface of the valve plate structure 500 facing the cylinder bore (not shown) is made of metal, i.e. metal plate 502. This preferably prevents deformation under high pressure.
  • a flat surface finish of the thermally insulating material plate 501 is preferably ensured to prevent leakage.
  • plates 501 , 502 can be assembled by for example, but not limited to, injection molding, induction heating, bonding adhesive, press fitting, ultrasonic welding etc.
  • Figure 6 shows a valve plate structure 600, comprising three plates 601 , 602, 603.
  • Plate 602 is made of thermally insulating material, while plates 601 , 603 are made of metal to provide strength.
  • the surface of the valve plate structure 600 facing the cylinder bore (not shown) is made of metal, i.e. metal plate 603. This preferably prevents deformation under high pressure.
  • a flat surface finish of the thermally insulating material plate 601 is preferably ensured to prevent leakage.
  • the metal plates 601 , 603 are thus in contact with the discharge reed (not shown) and the suction reed (not shown) respectively.
  • This preferably ensures good surface contact and prevents leakage.
  • having the surfaces adjacent the discharge and suction reeds respectively made from metal preferably increases reliability, for example due to the metal surface better withstanding the reciprocating reed movements.
  • Plates 601 , 602 and 603 can be assembled by for example, but not limited to, press fitting, injection molding, induction heating, bonding adhesive, ultrasonic welding etc.
  • Figure 7 shows a valve plate structure 700, comprising one plate 701 and an inlet 702.
  • Inlet 702 is made of thermally insulating material, while plate 701 is made of metal to provide strength.
  • the surface of the valve plate structure 700 facing the cylinder bore (not shown) is made of metal, i.e. metal plate 701. This preferably prevents deformation under high pressure.
  • the thermally insulating material inlet 701 is inserted in a corresponding recess 704 and will be located towards the discharge reed (not shown).
  • thermally insulating material inlet 702 is again preferably ensured to prevent leakage, it will be appreciated that the majority of the surface facing the discharge reed (not shown) is made up by the surface of the metal plate 701 , which preferably ensures good surface contact and prevents leakage.
  • Plate 701 and inlet 702 can be assembled by for example, but not limited to, press fitting, injection molding, induction heating, bonding adhesive, ultrasonic welding etc. In this embodiment, because the regions where the screws are inserted are made of metal, deformation under high torque, e.g. when screws (not shown) are being tightened, is preferably prevented.
  • the metal plate 701 is thus in contact with both the discharge reed (not shown) and the suction reed (not shown). This preferably ensures good surface contact and prevents leakage. Also, having the surfaces adjacent the discharge and suction reeds respectively made from metal preferably increases reliability, for example due to the metal surface better withstanding the reciprocating reed movements
  • Figure 8 shows a valve plate structure 800, comprising two plates 801 and 802.
  • Plate 801 is made of thermally insulating material, while plate 802 is made of metal to provide strength.
  • plate 801 is made of thermally insulating material, while plate 802 is made of metal to provide strength.
  • the metal plate 802 facing the cylinder bore is made of metal, i.e. metal plate 802. This preferably prevents deformation under high pressure.
  • the metal plate 802 in this embodiment comprises a raised region 803 around discharge orifice 804. When assembled, the raised region 803 is received in a corresponding opening 805 formed in the insulating material plate 801. This preferably enhances the reliability, for example due to the metal surface of the raised region 803 better withstanding the reciprocating reed movements.
  • a flat surface finish of the thermally insulating material inlet 802 is again preferably ensured. It will be appreciated that by having the metal surface of the raised region 803, in use, adjacent the discharge reed (not shown) preferably ensures good surface contact and prevents leakage and may provide improved reliability. Plates
  • FIG. 801 and 802 can be assembled by for example, but not limited to, press fitting, injection molding, induction heating, bonding adhesive, ultrasonic welding etc.
  • the metal plate 802 and the raised region 803 are thus in contact with the suction reed (not shown) and the discharge reed (not shown) respectively. This preferably ensures good surface contact and prevents leakage.
  • having the surfaces adjacent the discharge and suction reeds respectively made from metal preferably increases reliability, for example due to the metal surface better withstanding the reciprocating reed movements
  • Figure 9 shows a valve plate structure 900, with metal coatings 902, 904 on both surfaces of a thermally insulating material plate 906. This preferably ensures good surface contact and prevents leakage.
  • the thermally insulating material may include, but is not limited to, engineering plastics such as Polybutylene terephthalate (PBT) and Polyetherimide (PEI), Liquid Crystal Polymer (LCP), Polyether ether ketone (PEEK), Polyphenylene Sulphide (PPS) etc.
  • PBT Polybutylene terephthalate
  • PEI Polyetherimide
  • LCP Liquid Crystal Polymer
  • PEEK Polyether ether ketone
  • PPS Polyphenylene Sulphide
  • the metal used in the example embodiments described may include, but is not limited to cast/sintered iron.
  • the embodiments described can provide a hybrid valve plate structure in which a thermal barrier provided by respective materials, of thermally insulating characteristics, can improve the thermal insulation such that the suction gas temperature in the compressor may be reduced. Since a reduction in the suction gas temperature decreases its specific volume and increases the mass flow rate of the refrigerant, this can lead to improved compressor efficiency due to an increase in cooling performance.

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

Abstract

L'invention porte sur une plaque de clapet pour un compresseur, sur un compresseur et sur un procédé d'isolation thermique appliqué à un compresseur. La plaque de clapet possède une capacité d'isolation thermique pour isoler thermiquement un silencieux d'aspiration du compresseur d'une chambre de refoulement dans une culasse du compresseur.
PCT/SG2012/000189 2011-06-01 2012-05-30 Plaque de clapet pour compresseur WO2012166051A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US13/809,702 US20130108493A1 (en) 2011-06-01 2012-05-30 Valve plate for a compressor
CN2012800019878A CN103003570A (zh) 2011-06-01 2012-05-30 用于压缩机的阀板

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SG201103971-6 2011-06-01
SG2011039716A SG185858A1 (en) 2011-06-01 2011-06-01 A valve plate for a compressor

Publications (1)

Publication Number Publication Date
WO2012166051A1 true WO2012166051A1 (fr) 2012-12-06

Family

ID=47259626

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SG2012/000189 WO2012166051A1 (fr) 2011-06-01 2012-05-30 Plaque de clapet pour compresseur

Country Status (4)

Country Link
US (1) US20130108493A1 (fr)
CN (1) CN103003570A (fr)
SG (1) SG185858A1 (fr)
WO (1) WO2012166051A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103147985A (zh) * 2013-03-26 2013-06-12 东莞市金瑞五金制品有限公司 一种转子式压缩机
WO2017191228A1 (fr) 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
WO2017191229A1 (fr) 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
WO2017194516A1 (fr) 2016-05-10 2017-11-16 Arcelik Anonim Sirketi Compresseur hermétique à étanchéité améliorée
WO2019091665A1 (fr) 2017-11-10 2019-05-16 Arcelik Anonim Sirketi Compresseur hermétique à étanchéité améliorée
WO2020015901A1 (fr) 2018-07-19 2020-01-23 Arcelik Anonim Sirketi Culasse d'un compresseur hermétique à mouvement de va-et-vient
WO2020015900A1 (fr) 2018-07-19 2020-01-23 Arcelik Anonim Sirketi Capuchon isolant
EP3763941A1 (fr) * 2019-07-10 2021-01-13 WABCO Europe BVBA Compresseur à piston axial d'un dispositif d'alimentation d'air comprimé pour automobiles

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DE102013019812A1 (de) * 2013-11-26 2015-05-28 Wabco Gmbh Zylinderkopf für einen Luftverdichter
DE102016215972A1 (de) 2016-08-25 2018-03-01 Ford Global Technologies, Llc Kraftstoffversorgungssystem, Brennkraftmaschine und Verfahren zum Versorgen eines Verbrennungsmotors mit einem LPG-Kraftstoff
CN106286230B (zh) * 2016-10-17 2018-10-19 珠海格力节能环保制冷技术研究中心有限公司 一种压缩机及其阀板
CN106762669A (zh) * 2017-01-24 2017-05-31 广东美芝制冷设备有限公司 压缩机
EP4105483A1 (fr) * 2020-02-14 2022-12-21 Nidec Global Appliance Brasil Ltda. Agencement de tête de compression alternatif
CN112392692B (zh) * 2020-10-26 2023-03-17 杭州钱江制冷压缩机集团有限公司 一种压缩机

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US4701114A (en) * 1986-07-25 1987-10-20 American Standard Inc. Compressor suction gas heat shield
US5577898A (en) * 1995-07-27 1996-11-26 Samsung Electronics Co., Ltd. Suction muffler arrangement for a hermetic reciprocating compressor
KR20100022827A (ko) * 2008-08-20 2010-03-03 한라공조주식회사 사판식 압축기용 개스킷

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JP4020986B2 (ja) * 1996-01-23 2007-12-12 松下冷機株式会社 密閉型電動圧縮機
US6553893B2 (en) * 2000-03-31 2003-04-29 Respironics, Inc. Piston assembly for reducing the temperature of a compressor cup seal
BRPI0505717B1 (pt) * 2005-12-16 2020-03-10 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda Compressor hermético com isolamento térmico interno
US8207261B2 (en) * 2009-03-25 2012-06-26 E.I. Du Pont De Nemours And Company Plastic articles, optionally with partial metal coating

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Publication number Priority date Publication date Assignee Title
US4701114A (en) * 1986-07-25 1987-10-20 American Standard Inc. Compressor suction gas heat shield
US5577898A (en) * 1995-07-27 1996-11-26 Samsung Electronics Co., Ltd. Suction muffler arrangement for a hermetic reciprocating compressor
KR20100022827A (ko) * 2008-08-20 2010-03-03 한라공조주식회사 사판식 압축기용 개스킷

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103147985A (zh) * 2013-03-26 2013-06-12 东莞市金瑞五金制品有限公司 一种转子式压缩机
CN103147985B (zh) * 2013-03-26 2015-09-09 东莞市金瑞五金制品有限公司 一种转子式压缩机
WO2017191228A1 (fr) 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
WO2017191229A1 (fr) 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
WO2017194516A1 (fr) 2016-05-10 2017-11-16 Arcelik Anonim Sirketi Compresseur hermétique à étanchéité améliorée
WO2019091665A1 (fr) 2017-11-10 2019-05-16 Arcelik Anonim Sirketi Compresseur hermétique à étanchéité améliorée
WO2020015901A1 (fr) 2018-07-19 2020-01-23 Arcelik Anonim Sirketi Culasse d'un compresseur hermétique à mouvement de va-et-vient
WO2020015900A1 (fr) 2018-07-19 2020-01-23 Arcelik Anonim Sirketi Capuchon isolant
EP3763941A1 (fr) * 2019-07-10 2021-01-13 WABCO Europe BVBA Compresseur à piston axial d'un dispositif d'alimentation d'air comprimé pour automobiles

Also Published As

Publication number Publication date
SG185858A1 (en) 2012-12-28
CN103003570A (zh) 2013-03-27
US20130108493A1 (en) 2013-05-02

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