WO2016092514A1 - Compresseur alternatif pour un dispositif de refroidissement - Google Patents

Compresseur alternatif pour un dispositif de refroidissement Download PDF

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Publication number
WO2016092514A1
WO2016092514A1 PCT/IB2015/059534 IB2015059534W WO2016092514A1 WO 2016092514 A1 WO2016092514 A1 WO 2016092514A1 IB 2015059534 W IB2015059534 W IB 2015059534W WO 2016092514 A1 WO2016092514 A1 WO 2016092514A1
Authority
WO
WIPO (PCT)
Prior art keywords
port
cylinder
flow rate
compressor
coolant
Prior art date
Application number
PCT/IB2015/059534
Other languages
English (en)
Inventor
Maurizio Ascani
Original Assignee
Angelantoni Cleantech S.R.L.
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 Angelantoni Cleantech S.R.L. filed Critical Angelantoni Cleantech S.R.L.
Priority to EP15830841.1A priority Critical patent/EP3230587B1/fr
Priority to JP2017549863A priority patent/JP6738347B2/ja
Priority to CA2969506A priority patent/CA2969506A1/fr
Priority to RU2017124220A priority patent/RU2690543C2/ru
Priority to ES15830841T priority patent/ES2901963T3/es
Priority to CN201580073935.5A priority patent/CN107407265B/zh
Priority to BR112017012316A priority patent/BR112017012316A2/pt
Priority to US15/534,647 priority patent/US20180258922A1/en
Publication of WO2016092514A1 publication Critical patent/WO2016092514A1/fr
Priority to IL252605A priority patent/IL252605A0/en

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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Definitions

  • the present invention relates to a reciprocating compressor for a cooling device.
  • the present reciprocating compressor is used in those cooling devices comprising a closed circuit in which a determined flow rate of coolant circulates and that is provided with a main branch and at least one economizer and/or secondary branch.
  • a main branch In such branches of the closed circuit two defined fractions of the overall flow rate of the coolant circulate, then exiting from the compressor.
  • Such an economizer, or secondary, branch is fluidically connected to a section of the closed circuit comprised between the condenser and the expansion valve, on the one hand, and to the cylinder of the reciprocating compressor for the re-injection, into the compressor itself, of the fraction of flow rate crossing the secondary branch, on the other hand.
  • the fraction of coolant circulating in the economizer, or secondary, branch that can comprise an additional expansion valve and an heat exchanger or an additional evaporator, has a pressure value intermediate between the highest and the lowest of the circuit of the cooling device, i.e. between the pressure of the fluid to the condenser and that one to the evaporator being along the main branch.
  • the exact point of the compressor in which the aforementioned fraction of flow rate coming from the secondary economizer branch is entered can always be determined.
  • a screw compressor in which as it is known the pressure increases along the compressor axis according to a known law, the exact point of injection of the fraction of flow rate coming from the secondary economizer branch can always be located.
  • other types of compressors such as, for example, screw or scroll compressors, although the operating principle as well as the pressure distribution inside the compression chamber are different with respect to that one of the screw compressors, however also in the scroll compressor it can always be known how great is the pressure in any point of the compression chamber.
  • object of the present invention is to realize a reciprocating compressor that can be used in cooling devices provided with at least one economizer, or secondary, branch, but that - the performance being the same - has a displacement lower than the displacement at present employed in such cooling devices.
  • Further object of the invention is to realize a reciprocating compressor that, in addition to achieving the afore mentioned object, is highly simple to implement, even starting from know compressors free of side port.
  • the reciprocating compressor for cooling device provided with a closed circuit having a main branch, in which a first flow rate of circulating coolant enters in said compressor, and at least one first economizer branch, or secondary branch, in which a second flow rate of coolant circulates under a pressure different from the pressure of said first flow rate of coolant
  • said compressor being provided with at least one cylinder and at least one piston reciprocatingly moving in said at least one cylinder, between a top dead centre and a bottom dead centre, and comprising at least one suction duct for the entrance of said first flow rate of coolant, and at least one port obtained in the wall of said cylinder for the entrance of said second flow rate of coolant, in such a way that said piston exposes at least in part said at least one first inlet port, at least during its inlet stroke, and covers said at least one port at least during its compression stroke, characterized in that said at least one first inlet port has a slit shape with the main dimension substantially transverse to the axis of said cylinder
  • a first inlet port having the shape of a slit with the main dimension, the length one, substantially transverse to the axis of the cylinder, allows a remarkable amount of flow rate of coolant coming from an economizer, or secondary, branch to enter the cylinder, without this concretely affecting the dimensions of the displacement of the compressor itself.
  • the slit dimensions are highly limited along the axial direction of the cylinder, thus in height, whereas they are remarkably larger transversely to the cylinder axis, thus in length. As mentioned, this allows a remarkable flow rate of coolant to flow in the cylinder in the same very short time equal to the piston stroke during the opening and subsequent closing of the side port.
  • the term slit has to be intended as any notch, of any shape, made in the cylinder wall and having a dominant dimension (also named as main dimension) with respect the other.
  • the main or dominant or more relevant dimension is that one lying on a plane transverse to the axis of the compressor cylinder, thus not the slit dimension parallel to the axis of the compressor cylinder and defined as slit height.
  • said at least one first port is arranged next to the bottom dead centre of said at least one piston and, preferably, said at least one first port has a lower side substantially flush with the bottom dead centre of said piston.
  • said at least one closed circuit of said cooling device further comprises at least an additional economizer branch, or secondary branch, in which an addition flow rate of said coolant is circulating
  • said compressor further comprising at least one second port obtained in the wall of said cylinder for the entrance of said additional flow rate of said coolant in said at least one compressor, wherein said at least one second port has a slit shape with the main dimension substantially transverse to the axis of said cylinder and is arranged at a distance from said bottom dead centre greater than the distance at which said at least one first port is positioned, so that said piston exposes said at least one second inlet port at least during its inlet stroke, and covers said at least one port at least during its compression stroke.
  • Such a configuration is particularly suited in case the additional flow rate coming from an additional economizer, or secondary, branch has a pressure lower than the pressure of said second flow rate coming from the economizer, or secondary, branch, and entering the cylinder of the compressor through said at least one first port.
  • said at least one first port and said at least one second port both having a slit shape, are substantially or mainly rectangular-shaped, i.e. the slit surface, that one facing the inner face of the compressor cylinder, has substantially the shape of a rectangle lying on the inner cylindrical surface of the compressor cylinder.
  • the ratio between height and length dimensions, i.e. along the main direction, of said at least one first port and/or said at least one second port is smaller than 0.5, preferably 0.2.
  • the Applicant tested that such dimensional values are those that allow obtaining the best performances.
  • the slit length has to be calculated along the arc of a circle of the cylinder along which the same slit extends, on a plane transverse to the cylinder axis and passing in the middle of the slit height.
  • the lower side of said at least one second port is flush with the upper side of said at least one first port.
  • said at least one first inlet port and/or said at least one second inlet port comprises/comprise at least one functionally-combined non-return valve.
  • Such non-return valves allow preventing the coolant entered the compressor through the first and the second port from being biased towards them in the opposite way, during the rising step of the piston, i.e. the coolant compression step.
  • at least one non-return valve is of deformable reed type and is housed in the wall of said at least one cylinder. This makes the compressor even more compact, however avoiding the presence of complicated elements employed for synchronizing the opening or closing of the side ports.
  • figure 1 is a schematic view of a cooling device provided with a reciprocating compressor according to the invention
  • figure 2 is a P-h diagram of the refrigeration cycle relating to the refrigeration device of figure 1 ;
  • FIGS. 3a-3d are schematic and sectional longitudinal views of the inside of the compressor cylinder during the inlet and compression steps;
  • FIGS. 4a and 4b are respectively two longitudinal and transverse sectional views of the cylinder of the reciprocating compressor according to the invention, with particular reference to the first and the second port obtained in the wall of the compressor cylinder;
  • figure 5 is a schematic view of another cooling device provided with a reciprocating compressor according to the invention.
  • figure 6 is a P-h diagram of the refrigeration cycle relating to the refrigeration device of figure 5.
  • FIG 1 the scheme of a cooling device 200 provided with a reciprocating compressor 100 according to the invention provided with a cylinder 110 and a piston 111 reciprocatingly moving in the cylinder 110, between a top dead centre S (see figure 3d) and a bottom dead centre I (see figure 3c), is shown.
  • the refrigeration device 200 comprises a closed circuit C in which a certain flow rate of coolant is circulating.
  • a closed circuit C comprises, in its turn, a main branch M, in which a first flow rate X of coolant is circulating and enters the compressor 100 through a suction duct 109, a first secondary branch E and a second secondary branch E'.
  • the cooling device 200 further comprises a condenser 101, a first expansion valve 102 and a first evaporator 103.
  • Both the first expansion valve 102 and the first evaporator 103 are located along the main branch M of the closed circuit C so that the flow rate X circulating in the same, which is given by the difference between the overall flow rate circulating in the closed circuit C and the flow rates XI and X2 circulating in the two secondary branches E and E', directly enters the reciprocating compressor 100 through the suction duct 109 (see figure 3a) being in the reciprocating compressor 100, above the cylinder 110.
  • the two secondary branches E and E' each comprise a second expansion valve 130, 130' and a respective second evaporator 140 and 140'; in practice, in each secondary branch E, E', all the values of the circulating flow rate and the pressure and temperature will be different.
  • the cooling device 200 is able to cool three different chambers connected to the respective evaporators 103, 140 and 140'.
  • the second flow rate XI and the additional flow rate X2 respectively circulating along the secondary branch E and the additional secondary branch E' are at different temperatures and pressures.
  • the pressure of the flow rate XI circulating along the secondary branch E is intermediate between the pressure of the fluid at the condenser 101 and the pressure at the first evaporator 103, whereas the pressure of the additional flow rate X2 of coolant circulating in the additional secondary branch E' has an intermediate value between the value of the fluid of the first flow rate X and that of the fluid of the second flow rate XI .
  • thermodynamic states of the coolant circulating in the closed circuit C of the refrigeration device 200 are denoted in brackets, with numbers from 1 to 8.
  • thermodynamic cycle made by the coolant in the device 200 is shown, with the information of the thermodynamic condition of the fluid in the corresponding points of the closed circuit C.
  • the references 9 and 10 shown in the graph of figure 2 correspond to the thermodynamic state of the coolant in the compressor 100 in the inlet step (figure 3 b and 3 c) at the opening of the second port 112 and the first port 107 that are on the wall 110a of the cylinder 110 of the reciprocating compressor 100, as it will be described later.
  • the cooling device 200' comprises a closed circuit C comprising a main branch M along which a first flow rate X of the coolant is circulating at a defined pressure, a condenser 101, an evaporator 103, and a first expansion valve 102 arranged between the condenser 101 and the evaporator 103.
  • a closed circuit C also comprises a first economizer branch E along which a second flow rate XI of the coolant circulates.
  • Such a first economizer branch E is fluidically connected to the compressor 100 and to a section 106 of the closed circuit C comprised between the condenser 101 and the expansion valve 102.
  • the closed circuit C further comprises an additional economizer branch E' for an additional flow rate X2 of the coolant.
  • the economizer branch E and the additional secondary economizer branch E' comprise a second expansion valve 150, 150' and at least one heat exchanger 160, 160' with the section 106 of the closed circuit C comprised between the condenser 101 and the expansion valve 102.
  • such a second flow rate XI has an inlet pressure P 8 in the cylinder 110 of the compressor 100 intermediate between the pressure at the condenser P 2 and the inlet pressure in the cylinder 110, i.e. the pressure Pj of the flow rate X of fluid entering the cylinder 110 of the compressor from the suction duct 109, during the inlet step of the compressor 100.
  • thermodynamic states of the coolant circulating in the closed circuit C of the refrigeration device 200' are denoted in brackets, with numbers from 1 to 10.
  • thermodynamic cycle made by the coolant in the closed circuit C is shown, with the information of the respective thermodynamic condition of the coolant.
  • the references 11 and 12 shown in the graph of figure 6 correspond to the thermodynamic states of the coolant in the compressor 100 in the inlet step (figures 3b and 3 c) at the opening of the second port 112 and the first port 107 that are on the wall 110a of the cylinder 110 of the reciprocating compressor 100, as it will be described later.
  • the reciprocating compressor 100 comprises a first side port 107 obtained on the wall 110a of the cylinder 110 for the entrance of the aforementioned second flow rate XI of coolant.
  • the compressor 100 further comprises a second inlet port 112 for the entrance of such an additional flow rate X2 of coolant. More specifically, the second inlet port 112 is arranged at a distance D from the bottom dead centre I of the piston 111 greater than the distance d at which the first port 107 is located. Such a distance is assessed with respect to two planes P and PI transverse to the axis A of the cylinder 110 and passing in the middle of the height H of the port 107, 112.
  • the first inlet port 107 for the second flow rate XI of coolant that in the present instance is R404a, is a slit and is arranged at the bottom dead centre I of the piston 111, so that the piston exposes the first inlet port 107 during its inlet stroke and covers such a first inlet port 107 during its compression stroke.
  • the second inlet port 112 for the entrance of such an additional flow rate X2 of coolant arranged, as mentioned afore, at a distance D from the bottom dead centre I of the piston 111 greater than the distance d at which the first port 107 is located, is also a slit.
  • the second slit 112 is arranged on the wall 110a of the cylinder so that the piston exposes the second inlet port 112, during its inlet stroke, and before exposing the first inlet port 107, and covers it during its compression stroke, after covering the first port 107.
  • both the first inlet port 107 and the second inlet port 112 comprise a slit whose main dimension L is substantially transverse to the axis A of the cylinder 110.
  • the slit has a substantially rectangular-shaped surface, lying on the inner surface 110c of the cylinder 110, thus along an arc of a circle of the cylinder 110. More specifically, for example such a surface is obtained through a cutting by milling machine of the wall 110a of the cylinder 110, obtained with the rotation axis of the milling machine parallel to the axis A of the cylinder 110 and forward direction of the milling machine orthogonal to the axis of the cylinder 110.
  • the so obtained surface is substantially rectangular-shaped, despite the rectangle sides are not reciprocally connected by sharp edge, but are blent one to the other.
  • the ratio between the H height dimension and L length dimension (also main dimension), the latter being measured along the arc of a circle traveled by the slit along the inner surface of the cylinder 110c (see in particular the dotted line shown in figure 4b), is 0.2.
  • the length L has to be measured on a plane P, or PI, transverse to the axis of the cylinder A and passing in the middle of the height H of the respective slit.
  • any slit having a dimensional ratio of height H to length L smaller than 0.5 still falls within the protection scope of the present invention.
  • the slit i.e. the surface extending on the inner face 110c of the cylinder 110, has lower and upper sides blent to the respective connecting sides, since it follows the shape of the wall 110a of the cylinder 110 itself.
  • the first port 107 has a lower side 107a substantially flush with the bottom dead centre I of the piston 111. More particularly, the lower side 112a of the second port 112 is flush with the upper side 107b of the first port 107.
  • only the second inlet port 112 comprises a functionally-combined non-return valve 180; whereas, in the embodiment shown in figures 4a and 4b, both the first inlet port 107 and the second inlet port 112 comprise a functionally-combined non-return valve 180 of deformable reed type.
  • Such a non-return valve 180 is, in practice, dimensioned so as to deform only after a defined pressure is exceeded.
  • such a non-return valve 180 is housed in the wall 110a of the cylinder 110 of the compressor 101 and, when in a not deformed condition, is in abutment against a pair of projections 190 and 191 contacting the outer surface 110b of the cylinder 110.
  • the pressure of such an additional flow rate X2 of coolant is higher than the pressure being in the cylinder 110, thus resulting in a pressure increase inside the cylinder 110 (thermodynamic state 9 or 11, depending on the cooling device 200 or 200').
  • the non-return valve 180 remains open (see figure 3b).
  • the piston exposes the first port 107 thus allowing the second flow rate XI of coolant coming from the secondary economizer branch E accessing the cylinder 110.
  • the pressure of the second flow rate XI of coolant coming from such an economizer, or secondary, branch E is higher than the pressure of the additional flow rate X2 of coolant and the suction pressure.
  • first port 107 and/or the second port 112 preferably occurs through a simple milling operation, or similar technological operation, of the cylinder 110 along a plane transverse to the axis A of the cylinder 110 itself.
  • This allows the cylinders of existing reciprocating compressors, that are free of through side port, being converted by means of a simple milling operation of the cylinder 110.
  • such cylinders are made adapted to operate in cooling devices having at least one secondary, or economizer, branch without the need of subjecting the cylinder to complex interventions, from a technical point of view, or economically unattractive.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur alternatif (100) pour un dispositif de refroidissement (200) doté d'un circuit fermé (C) ayant une dérivation principale (M), dans laquelle un premier débit (X) de réfrigérant en circulation entre dans ledit compresseur et au moins une première dérivation d'économiseur ou dérivation secondaire (E), dans laquelle un second débit (XI) de réfrigérant circule à une pression différente de la pression dudit premier débit (X) de réfrigérant, ledit compresseur étant doté d'au moins un cylindre (110) et d'au moins un piston (111) effectuant un mouvement alternatif dans ledit au moins un cylindre, entre un point mort haut (S) et un point mort bas (I) et comprenant au moins un conduit d'aspiration pour l'entrée dudit premier débit de réfrigérant, ainsi qu'au moins un orifice (107) ménagé dans la paroi dudit cylindre pour l'entrée dudit second débit de réfrigérant, de telle manière que ledit piston expose au moins en partie ledit au moins un premier orifice d'entrée (107), au moins pendant sa course d'entrée et recouvre ledit au moins un orifice au moins pendant sa course de compression, caractérisé en ce que ledit au moins un premier orifice d'entrée (107) a une forme de fente dont la dimension principale est sensiblement transversale à l'axe (A) dudit cylindre.
PCT/IB2015/059534 2014-12-11 2015-12-11 Compresseur alternatif pour un dispositif de refroidissement WO2016092514A1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
EP15830841.1A EP3230587B1 (fr) 2014-12-11 2015-12-11 Compresseur alternatif pour un dispositif de refroidissement
JP2017549863A JP6738347B2 (ja) 2014-12-11 2015-12-11 冷却装置用往復圧縮機
CA2969506A CA2969506A1 (fr) 2014-12-11 2015-12-11 Compresseur alternatif pour un dispositif de refroidissement
RU2017124220A RU2690543C2 (ru) 2014-12-11 2015-12-11 Поршневой компрессор для охлаждающего устройства
ES15830841T ES2901963T3 (es) 2014-12-11 2015-12-11 Compresor de pistón para un dispositivo de enfriamiento
CN201580073935.5A CN107407265B (zh) 2014-12-11 2015-12-11 用于冷却设备的往复式压缩机
BR112017012316A BR112017012316A2 (pt) 2014-12-11 2015-12-11 compressor alternativo
US15/534,647 US20180258922A1 (en) 2014-12-11 2015-12-11 Reciprocating compressor for a cooling device
IL252605A IL252605A0 (en) 2014-12-11 2017-06-01 A reciprocating compressor for a refrigeration unit

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPG20140062 2014-12-11
ITPG2014000062 2014-12-11

Publications (1)

Publication Number Publication Date
WO2016092514A1 true WO2016092514A1 (fr) 2016-06-16

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PCT/IB2015/059534 WO2016092514A1 (fr) 2014-12-11 2015-12-11 Compresseur alternatif pour un dispositif de refroidissement

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Country Link
EP (1) EP3230587B1 (fr)
ES (1) ES2901963T3 (fr)
WO (1) WO2016092514A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3083852A1 (fr) * 2018-07-12 2020-01-17 Valeo Systemes Thermiques Circuit de gestion thermique d'un vehicule automobile electrique ou hybride
FR3101698A1 (fr) * 2019-10-08 2021-04-09 Valeo Systemes Thermiques Circuit de gestion thermique d’un véhicule automobile électrique ou hybride

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57153977A (en) * 1981-03-20 1982-09-22 Hitachi Ltd Compressor making reciprocating motion
JPH07279842A (ja) * 1994-04-14 1995-10-27 Toyota Autom Loom Works Ltd 往復動型圧縮機における冷媒ガス吸入構造
WO2007064321A1 (fr) 2005-12-01 2007-06-07 Carrier Corporation Procede d'optimisation de la charge de refroidissement d'un systeme a compression de vapeur a economie en faisant varier la vitesse d'un compresseur mono-etage
US20140170003A1 (en) 2012-12-18 2014-06-19 Emerson Climate Technologies, Inc. Reciprocating compressor with vapor injection system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57153977A (en) * 1981-03-20 1982-09-22 Hitachi Ltd Compressor making reciprocating motion
JPH07279842A (ja) * 1994-04-14 1995-10-27 Toyota Autom Loom Works Ltd 往復動型圧縮機における冷媒ガス吸入構造
WO2007064321A1 (fr) 2005-12-01 2007-06-07 Carrier Corporation Procede d'optimisation de la charge de refroidissement d'un systeme a compression de vapeur a economie en faisant varier la vitesse d'un compresseur mono-etage
US20140170003A1 (en) 2012-12-18 2014-06-19 Emerson Climate Technologies, Inc. Reciprocating compressor with vapor injection system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3083852A1 (fr) * 2018-07-12 2020-01-17 Valeo Systemes Thermiques Circuit de gestion thermique d'un vehicule automobile electrique ou hybride
FR3101698A1 (fr) * 2019-10-08 2021-04-09 Valeo Systemes Thermiques Circuit de gestion thermique d’un véhicule automobile électrique ou hybride
WO2021069831A1 (fr) * 2019-10-08 2021-04-15 Valeo Systemes Thermiques Circuit de gestion thermique d'un véhicule automobile électrique ou hybride

Also Published As

Publication number Publication date
EP3230587B1 (fr) 2021-10-06
ES2901963T3 (es) 2022-03-24
EP3230587A1 (fr) 2017-10-18

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