WO2013071384A1 - Conjunto de pistão e cilindro para um compressor linear aerostático - Google Patents
Conjunto de pistão e cilindro para um compressor linear aerostático Download PDFInfo
- Publication number
- WO2013071384A1 WO2013071384A1 PCT/BR2012/000450 BR2012000450W WO2013071384A1 WO 2013071384 A1 WO2013071384 A1 WO 2013071384A1 BR 2012000450 W BR2012000450 W BR 2012000450W WO 2013071384 A1 WO2013071384 A1 WO 2013071384A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- cylinder
- cylinder assembly
- assembly according
- clearance
- Prior art date
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
- F04B39/0005—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 adaptations of pistons
-
- 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
- F04B39/122—Cylinder block
-
- 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
- F04B39/126—Cylinder liners
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
Definitions
- the present invention relates to a piston and cylinder assembly of a linear compressor for aerostatic bearing refrigeration, more particularly to the dimensional relationships of the assembly in order to minimize losses.
- the basic structure of a refrigerant circuit comprises four components, namely the compressor, the condenser, the expansion device and the evaporator. These elements characterize a refrigerant circuit in which a fluid circulates in order to allow the temperature of an internal environment to decrease, removing the heat of this medium and moving it to an external environment through the mentioned elements.
- the fluid circulating in the refrigerant circuit generally follows the flow sequence: compressor, condenser, expansion valve, evaporator and again the compressor, thus a closed loop is characterized.
- the fluid undergoes variations in pressure and temperature that are responsible for changing the state of the fluid, as
- the compressor acts as the heart of the refrigeration system, creating the flow of refrigerant along the system components.
- the compressor raises the coolant temperature by increasing the pressure inside it and
- piston bearing Due to the relative movement between the piston and the cylinder, piston bearing is required.
- This bearing consists of the presence of a fluid in the clearance between the piston outer diameter and the cylinder interior, avoiding contact between them and the consequent premature wear of the piston and / or cylinder.
- the presence of fluid between the two mentioned components also serves to reduce the friction between them, making the mechanical loss of the compressor less.
- the gas compression mechanism occurs by the axial and oscillatory movement of a piston inside a cylinder.
- the cylinder head At the top of the cylinder is the cylinder head which, together with the piston and cylinder, forms the compression chamber.
- the discharge and suction valves are positioned, which regulate the gas inlet and outlet in the cylinder.
- the piston is driven by an actuator that is connected to the linear motor of the compressor.
- the linear motor driven compressor piston has the function of developing a linear reciprocating motion, causing the movement of the piston within the cylinder to exert a compressive action of the gas admitted by the suction valve to the extent that it can be discharged to the high pressure side through the discharge valve.
- the main sources of leakage in a compressor are the discharge and suction valves and the piston to cylinder clearance.
- the clearance between the piston and the cylinder will hereinafter also be called the perimetral clearance.
- Leakage is defined as the amount of gas that flows between the high pressure region (above the piston top) and the low pressure region (below the piston base) through the perimeter clearance. This leakage phenomenon always occurs when the piston is in the compression phase, ie moving towards the cylinder head. When this piston movement occurs, the gas is compressed to a discharge pressure (Pd) that flows through the perimeter clearance across the entire length of the clearance (Cf) reaching the suction pressure region (Ps) located opposite the chamber. compression Note that this gas does not come out of the compressor into the refrigeration system to play the main role of generating cold.
- irreversibility is a feature of all real processes and its sources are dissipative processes. Aerostatically controlled systems suffer from the phenomenon of irreversibility in compression caused by the presence of a small portion of gas in the gap between the cylinder and the piston. Irreversibility can be understood as the energy loss resulting from the flow of the small portion of gas into and out of the perimeter clearance.
- Figure 5 shows experimental results that relate the power consumed by the two effects as a function of piston to cylinder clearance. Note that irreversibility losses and leakage occurs simultaneously.
- the present invention achieves a geometrical and dimensional relationship designed to inhibit loss of bearing efficiency by reducing specific perimeter clearance, as well as providing a solution that is easily productive to implement, ensuring benefits for the end user. and, as a result of better energy efficiency, for the environment.
- the objects of the present invention are achieved by providing a piston and cylinder assembly, the piston being relocably positioned within the cylinder, the piston moving between an upper dead center and a lower dead center, between the inner wall of the piston.
- cylinder and the outer wall of the piston there is a perimeter clearance for aerostatic piston bearing, and the minimum perimeter clearance occurs at the upper portion of the piston when the piston is at its top dead center and linear compressor comprising the piston and cylinder assembly described .
- the objects of the present invention are also achieved by means of a linear compressor piston and cylinder assembly, the piston being displaceablely positioned within the cylinder, piston moving between a high pressure portion and a low pressure portion, the piston portion.
- high pressure having greater gas density than the low pressure portion
- a perimeter clearance being defined between an inner cylinder wall and an outer piston wall for aerostatic gas piston bearing, and the perimeter clearance size varies inversely proportional to the gas density in the perimeter clearance.
- Figure 1 is a sectional view of a prior art aerostatic bearing linear compressor.
- Figure 2 is a cross-sectional view of a prior art aerostatic bearing linear compressor showing gas pressures.
- Figure 3 is a cross-sectional view of a prior art aerostatic bearing linear compressor showing the gas pressures at time i).
- Figure 4 - is a cross-sectional view of a state-of-the-art linear compressor with aerostatic bearing showing the pressures of gas at time ii).
- Figure 5 is a graph of the power loss resulting from the clearance between the cylinder and the piston.
- Figure 6 is a graph of the pressure profile in the piston / cylinder clearance as a function of pressure, position and time.
- Figure 7 is a graph of gas mass flows in the piston / cylinder clearance in the top and bottom region of the piston.
- Figure 8 is a graph of gas mass flows in the piston / cylinder clearance in the piston top region.
- Figure 9 is a graph of gas mass flows in the piston / cylinder clearance in the piston base region.
- Figure 10 is a cross-sectional view of a cylinder piston assembly showing a deficient solution.
- Figure 11 is a cross-sectional view of a possible configuration of the piston cylinder assembly of the present invention.
- Figure 12 is a cross-sectional view of a possible configuration of the piston-cylinder assembly of the present invention.
- Figure 13 is a cross-sectional view of a possible configuration of the cylinder piston assembly of the present invention.
- Figure 14 is a cross-sectional view of a possible configuration of the piston-cylinder assembly of the present invention.
- the present invention proposes a technological advancement in the piston and cylinder assembly of aerostatic linear linear compressors both in terms of their energy efficiency and the production process.
- the gas compression mechanism occurs by the axial and oscillatory movement of a piston 1 inside a cylinder 2.
- a head 3 which together with the piston 1 and the cylinder 2 form the compression chamber 4.
- the discharge valves 5 and suction 6 that regulate the gas inlet and outlet in the cylinder. 2.
- piston 1 is driven by an actuator 7 connected to the compressor linear motor, which motor is not explained further in this document.
- the piston 1 of a compressor when driven by the linear motor, has the function of developing a linear reciprocating motion, promoting a movement of the piston 1 inside the cylinder 2 which exerts a gas compression action admitted by the suction valve 6 to the point at which gas can be discharged to the high pressure side through the discharge valve 5.
- Cylinder 2 is mounted inside a block 8 and over the head
- a cover 9 is mounted with the discharge dowel 10 and the suction dowel 11, which connect the compressor with the rest of the system.
- piston 1 which consists of the presence of a fluid in the perimeter clearance 12 between the two parts in order to separate them during movement.
- An advantage of using the gas itself as a lubricating fluid is the absence of an oil pumping system.
- the gas used for the bearing may be the gas itself pumped by the compressor and used in the refrigeration system.
- the gas is diverted, after its compression, from the discharge chamber 13, the cap 9 through the channel 14 to the pressurized region 15 around cylinder 2, and the pressurized region 15 is formed by the outer diameter of cylinder 2 and inner diameter of block 8.
- At least three restrictors 16,17,18,19 are required in a given section of cylinder 2 and at least two restrictor sections 6,17, 8,19 are required.
- the restrictors must be in such a position that even with the oscillating movement of piston 1 the restrictors 16,17,18,19 will never be uncovered, ie piston 1 does not leave the actuator operating area. 16, 7.18.19.
- Figure 2 provides information regarding the pressures within the cylinder 2 and piston 1 assembly.
- the instant of figure 2 corresponds to a gas compression movement effected by piston 1. At this time there is a gas discharge pressure which is much higher than the pressure in the opposite region of piston 1.
- the region between the top of piston 1 and cylinder head 3 will be referred to as the high pressure region.
- the region between the base of piston 1 and the portion of cylinder 2 opposite the cylinder head 3 will be referred to as the low pressure region.
- the thermal exchange of the refrigerator is based on the "General Equation of Perfect Gases" which demonstrates that in a gaseous mass the volumes and pressures are directly proportional to their absolute temperatures and inversely proportional to each other.
- Gas is a compressible fluid, so that the loss of charge causes the gas pressure to vary over the backlash, and therefore its density to vary.
- Moment 1 corresponds to figure 3 and occurs when the piston is at its top dead center.
- moment 2 corresponds to figure 4 and occurs at the moment when piston 1 is at the beginning of its suction movement.
- Figure 6 shows the pressure profile in the perimeter clearance as a function of the pressure, position and time of piston 1 relative to cylinder 2.
- This graph shows that the X axis corresponds to the oscillating motion cycle of piston 1, and it is possible to identify, around 150 ms, the instant 1 and 2 the dotted line (see indications i1 and i2).
- the increasing variation on the Y axis corresponds to a position along the clearance of cylinder 2 with the step 1.
- the increase in the Z axis corresponds to the increase in pressure.
- the pressure profile along the perimeter clearance 12 (dotted line) has its maximum in the piston top region 1 and the minimum in the piston base region 1, in other words , the pressure at the base is always the minimum, regardless of the pressure at the top of the piston 1.
- the pressure profile along the perimeter clearance 12 (dotted line) has its maximum in the central region of the perimeter clearance 12 having the minimum pressure at the base and an intermediate pressure at the top of the perimeter clearance 12.
- the gas mass flow through the perimeter clearance 12 between piston 1 and cylinder 2 behaves, at each moment, according to the pressure profile shown in figure 6 and the gas density along the clearance 12.
- the diagram in figure 7 shows the mass flows in the base and top regions of piston 1 over time equivalent to an oscillation of piston 1, also being shown the moments 1 and 2 (i1 and i2) already mentioned in the graph of figure 6.
- the graph in figure 7 shows that the negative mass flow corresponds to the flow leaving the compression chamber 4, either in the top (TP) or base (BP) region of piston 1.
- a positive flow represents the gas returning to the compression chamber 4.
- the continuous line that corresponds to the mass flow in the clearance The perimeter 12 in the top region of the piston 1 shows that the gas exits the compression chamber 4 and enters the perimeter clearance 12 over a period of time (negative mass flow - line continues below the abscissa axis) but returns from the perimeter clearance 12 for compression chamber 4 (positive mass flow - continuous line above the abscissa axis).
- the high density gas mass flows (GAD) are in the top region of the perimeter clearance 12
- the low density gas flows (GBD) are present. in the base region of the perimeter clearance 12.
- the highest gas densities are in the top region of piston 1 when it is closest to the head 3, this is because the high pressures of this region are able to compress the gas in a smaller volume.
- the way to reduce the effect of irreversibility caused by the gap between piston 1 and cylinder 2 is to keep the clearance as low as possible, so that less volume is available for high pressure gas accumulation in the perimeter clearance. 12 during the compression phase. Thus, it is possible to establish a lower gas flow and reflux between compression chamber 4 and perimeter clearance 12.
- the decrease in perimeter clearance 12 between piston 1 and cylinder 2 finds its limits within the precision limits of the manufacturing processes (machining processes) used for making piston 1 and cylinder 2. As a rule, the perimeter clearance between piston 1 and cylinder 2 may be smaller, the lower the cylindricity errors on the outer surface of piston 1 and the inner surface of cylinder 2. Currently this clearance in refrigeration compressors is about a few micrometers.
- the cylindricity error obtained in parts such as pistons 1 and cylinders 2 is dependent on the length of the cylindrical surfaces, ie the length of piston 1 and cylinder 2. The relationship is established such that the greater the length the greater the cylindricity error it presents.
- an option to decrease the cylindricity error to enable the reduction of perimeter clearance 12 could simply be to decrease the length of piston 1 and / or cylinder 2.
- Figure 0 shows a large clearance piston / cylinder assembly in the piston top region 1 due to the high cylinder cylindricity error.
- piston 1 or cylinder 2 length is not for compressors that use aerostatic bearings instead of oil as lubricant because they require longer pistons 1 and cylinders 2 so that aerostatic bearings provide the necessary support to piston 1, avoiding contact between the piston 1 and cylinder 2 assembly, otherwise the assembly would suffer premature wear and consequently loss of efficiency.
- the problem solved by the present invention is therefore a unique problem of compressors using aerostatic bearings.
- compressors with aerostatic bearings have a perimeter clearance 12 through which the refrigerant gas flows.
- the smallest perimeter clearance 12 possible is all the more necessary and beneficial the closer to the top of the piston 1, ie the closer to the top of the piston 1 region.
- the reduction of perimeter clearance 12 is performed, the greater the effect of reducing irreversibility, since it is in this region that the largest gas mass flows in and out of perimeter clearance 12 are found.
- a solution of the present invention for irreversibility involves the use of components (piston and / or cylinder) with variable cross section to create a specific portion in which the clearance is effectively reduced.
- components rod and / or cylinder
- variable cross section to create a specific portion in which the clearance is effectively reduced.
- These regions have lengths that are much shorter than the lengths of the components themselves and will therefore have lower cylindricity errors than those of whole components.
- Figures 11 to 14 show some possible shape configurations of the piston / cylinder assembly that ensure better compressor efficiency.
- Piston 1 due to its smaller diameter at the base, enables increased clearance at the base of the piston / cylinder assembly and consequent decrease in clearance at the top of the piston.
- Figures 12 and 13 show possible geometric configurations of the piston / cylinder assembly 1, 2 which make use of two distinct sections on one of the piston 1 or cylinder 2 elements to reduce perimeter clearance 12 as the piston 1 is Approach the top of the cylinder 2.
- piston 1 has two distinct sections, with the section adjacent to the top region of piston 1 having a larger diameter than the region adjacent to the lower portion of piston 1, that is, the upper portion of the piston is larger than the remaining portion of piston 1.
- the diametrical clearance 12 is reduced to a minimum when the top of the piston 1 is near the top of cylinder 2.
- This slightly arcuate shape of cylinder 2 in its longitudinal direction can be defined as a circle segment type shape.
- Figure 13 shows a situation analogous to figure 12 being that this time it is cylinder 2 which has two sections with different diameters
- cylinder 2 undergoes a narrowing of the section in the portion closest to the top of cylinder 2 (the top portion of cylinder 2 is smaller in size than the remaining portion of cylinder 2), which provides the necessary minimum diametric clearance 12.
- Figure 14 shows another of these possible configurations that can be reached through a cylinder 2 having a conical trunk-like geometry, where the smallest diameter portion would be in the top region of cylinder 2.
- the perimeter clearance 12 is reduced.
- the solution of the present invention is therefore achieved when a relationship is ensured in which the size of the perimeter clearance 12 varies inversely proportional to the density of the gas present in the perimeter clearance 12.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
MX2014005799A MX2014005799A (es) | 2011-11-16 | 2012-11-14 | Arreglo de piston y cilindro y un compresor lineal aerostatico. |
EP12813252.9A EP2781747B1 (en) | 2011-11-16 | 2012-11-14 | Piston cylinder arrangement of an aerostatic liner compressor |
SG11201402340VA SG11201402340VA (en) | 2011-11-16 | 2012-11-14 | Piston cylinder arrangement of an aerostatic liner compressor |
CN201280056508.2A CN104040177B (zh) | 2011-11-16 | 2012-11-14 | 空气静压线性压缩器的活塞汽缸装置 |
US14/358,277 US20140311337A1 (en) | 2011-11-16 | 2012-11-14 | Piston cylinder arrangement of an aerostatic linear compressor |
JP2014541488A JP6126110B2 (ja) | 2011-11-16 | 2012-11-14 | ピストン・シリンダアセンブリおよびリニア圧縮機 |
KR1020147011907A KR20140135146A (ko) | 2011-11-16 | 2012-11-14 | 기체정역학 선형 압축기의 피스톤 실린더 배치구조 |
ES12813252.9T ES2566020T3 (es) | 2011-11-16 | 2012-11-14 | Conjunto de pistón y cilindro de un compresor lineal aerostático |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BRPI1105479A BRPI1105479A2 (pt) | 2011-11-16 | 2011-11-16 | conjunto de pistão e cilindro e compressor linear |
BRPI1105479-4 | 2011-11-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013071384A1 true WO2013071384A1 (pt) | 2013-05-23 |
Family
ID=47552709
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/BR2012/000450 WO2013071384A1 (pt) | 2011-11-16 | 2012-11-14 | Conjunto de pistão e cilindro para um compressor linear aerostático |
Country Status (10)
Country | Link |
---|---|
US (1) | US20140311337A1 (pt) |
EP (1) | EP2781747B1 (pt) |
JP (1) | JP6126110B2 (pt) |
KR (1) | KR20140135146A (pt) |
CN (1) | CN104040177B (pt) |
BR (1) | BRPI1105479A2 (pt) |
ES (1) | ES2566020T3 (pt) |
MX (1) | MX2014005799A (pt) |
SG (1) | SG11201402340VA (pt) |
WO (1) | WO2013071384A1 (pt) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9322401B2 (en) * | 2014-02-10 | 2016-04-26 | General Electric Company | Linear compressor |
CN106768663B (zh) * | 2017-01-09 | 2023-07-28 | 广西大学 | 一种压缩机径向间隙泄漏的动态观测装置 |
CN108119341A (zh) * | 2018-02-22 | 2018-06-05 | 杨厚成 | 一种用于声能制冷的压缩机气缸缸体结构 |
KR102088331B1 (ko) * | 2018-07-03 | 2020-03-12 | 엘지전자 주식회사 | 리니어 압축기 |
DE102019104856A1 (de) * | 2019-02-26 | 2020-08-27 | Wabco Gmbh | Kolbenkompressor |
DE102019122877B4 (de) * | 2019-08-27 | 2021-08-19 | Man Energy Solutions Se | Kolben einer Brennkraftmaschine |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004106737A1 (en) * | 2003-05-30 | 2004-12-09 | Fisher & Paykel Appliances Limited | Compressor improvements |
WO2007009202A1 (en) * | 2005-07-22 | 2007-01-25 | Whirlpool S.A. | A piston-and-cylinder assembly |
DE102006052447A1 (de) * | 2006-11-07 | 2008-05-08 | BSH Bosch und Siemens Hausgeräte GmbH | Linearverdichter und Gasdrucklager dafür |
WO2009139135A1 (en) * | 2008-05-12 | 2009-11-19 | Panasonic Corporation | Hermetic compressor |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5228709A (en) * | 1975-08-29 | 1977-03-03 | Hitachi Constr Mach Co Ltd | Hand drum type piston |
FR2384102A1 (fr) * | 1977-03-18 | 1978-10-13 | Domenge Alberto | Systeme cylindre(s)-piston(s), notamment pour machines motrices |
US5213025A (en) * | 1990-01-26 | 1993-05-25 | Thomas Industries Inc. | Conical rod piston |
JPH10159737A (ja) * | 1996-12-03 | 1998-06-16 | Marushin Kogyo Kk | エアーポンプ |
JP2001200787A (ja) * | 2000-01-18 | 2001-07-27 | Matsushita Refrig Co Ltd | 振動式圧縮機 |
EP1205678A1 (en) * | 2000-11-07 | 2002-05-15 | Ingersoll-Rand Company | Gas bearing |
DE102004061941B4 (de) * | 2004-12-22 | 2014-02-13 | AeroLas GmbH Aerostatische Lager- Lasertechnik | Axial angetriebene Kolben-Zylinder-Einheit |
DE102004061940A1 (de) * | 2004-12-22 | 2006-07-06 | Aerolas Gmbh, Aerostatische Lager- Lasertechnik | Kolben-Zylinder-Einheit |
-
2011
- 2011-11-16 BR BRPI1105479A patent/BRPI1105479A2/pt not_active IP Right Cessation
-
2012
- 2012-11-14 ES ES12813252.9T patent/ES2566020T3/es active Active
- 2012-11-14 WO PCT/BR2012/000450 patent/WO2013071384A1/pt active Application Filing
- 2012-11-14 KR KR1020147011907A patent/KR20140135146A/ko not_active Application Discontinuation
- 2012-11-14 CN CN201280056508.2A patent/CN104040177B/zh not_active Expired - Fee Related
- 2012-11-14 MX MX2014005799A patent/MX2014005799A/es unknown
- 2012-11-14 JP JP2014541488A patent/JP6126110B2/ja active Active
- 2012-11-14 EP EP12813252.9A patent/EP2781747B1/en not_active Not-in-force
- 2012-11-14 SG SG11201402340VA patent/SG11201402340VA/en unknown
- 2012-11-14 US US14/358,277 patent/US20140311337A1/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004106737A1 (en) * | 2003-05-30 | 2004-12-09 | Fisher & Paykel Appliances Limited | Compressor improvements |
WO2007009202A1 (en) * | 2005-07-22 | 2007-01-25 | Whirlpool S.A. | A piston-and-cylinder assembly |
DE102006052447A1 (de) * | 2006-11-07 | 2008-05-08 | BSH Bosch und Siemens Hausgeräte GmbH | Linearverdichter und Gasdrucklager dafür |
WO2009139135A1 (en) * | 2008-05-12 | 2009-11-19 | Panasonic Corporation | Hermetic compressor |
Also Published As
Publication number | Publication date |
---|---|
CN104040177A (zh) | 2014-09-10 |
EP2781747A1 (en) | 2014-09-24 |
JP6126110B2 (ja) | 2017-05-10 |
KR20140135146A (ko) | 2014-11-25 |
JP2014533789A (ja) | 2014-12-15 |
SG11201402340VA (en) | 2014-10-30 |
MX2014005799A (es) | 2014-05-30 |
ES2566020T3 (es) | 2016-04-08 |
BRPI1105479A2 (pt) | 2016-01-19 |
US20140311337A1 (en) | 2014-10-23 |
CN104040177B (zh) | 2017-02-22 |
EP2781747B1 (en) | 2016-01-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2013071384A1 (pt) | Conjunto de pistão e cilindro para um compressor linear aerostático | |
BRPI1105471A2 (pt) | restritor e processo de produção de um restritor de vazão de um fluido para mancais aerostáticos | |
BR112017027478B1 (pt) | Compressor rotativo e dispositivo de ciclo de refrigeração | |
BRPI0503019B1 (pt) | Conjunto de pistão e cilindro com folga diametral variável e cilindro para uso em conjuntos de pistão e cilindro com folga diametral variável | |
US6099279A (en) | Displacement fluid machine | |
JPWO2018174100A1 (ja) | シングルスクリュー圧縮機 | |
JP2009156258A (ja) | シングルスクリュー圧縮機 | |
CN111670306B (zh) | 螺旋式压缩机 | |
KR102377227B1 (ko) | 백투백 베어링 밀봉 시스템 | |
CN100387842C (zh) | 旋转式压缩机 | |
JP2010275974A (ja) | ロータリ式圧縮機 | |
JP2015214904A (ja) | 密閉型圧縮機および冷凍冷蔵装置 | |
WO2016179813A1 (zh) | 旋转式压缩机及具有其的冷冻装置 | |
JP2012197769A (ja) | 密閉型圧縮機 | |
CN113286941A (zh) | 用于压缩机和发动机的冷却活塞和气缸 | |
JP2015158178A (ja) | 密閉型圧縮機および冷凍装置 | |
JP4576870B2 (ja) | 圧縮機 | |
JP2011163257A (ja) | 密閉型圧縮機 | |
JP2013064331A (ja) | スクリュー圧縮機および冷凍装置 | |
JP2004019506A (ja) | 密閉型回転圧縮機 | |
JP3985030B2 (ja) | 圧縮機 | |
KR100531279B1 (ko) | 로터리 압축기 | |
JP2014105588A (ja) | 密閉型圧縮機及びこれを用いた冷蔵・冷凍・空調装置 | |
JP5003085B2 (ja) | 回転式流体機械 | |
JP2018053874A (ja) | 密閉型圧縮機及び冷凍サイクル装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 12813252 Country of ref document: EP Kind code of ref document: A1 |
|
DPE1 | Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2012813252 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref document number: 2014541488 Country of ref document: JP Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 20147011907 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: MX/A/2014/005799 Country of ref document: MX |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14358277 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |