EP2016346A2 - Dispositif à pompe à chaleur - Google Patents

Dispositif à pompe à chaleur

Info

Publication number
EP2016346A2
EP2016346A2 EP07727186A EP07727186A EP2016346A2 EP 2016346 A2 EP2016346 A2 EP 2016346A2 EP 07727186 A EP07727186 A EP 07727186A EP 07727186 A EP07727186 A EP 07727186A EP 2016346 A2 EP2016346 A2 EP 2016346A2
Authority
EP
European Patent Office
Prior art keywords
heat pump
piston
heat
working medium
cyclone unit
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Withdrawn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
EP07727186A
Other languages
German (de)
English (en)
Inventor
Michael Löffler
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP2016346A2 publication Critical patent/EP2016346A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • F04B39/062—Cooling by injecting a liquid in the gas to be compressed
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression 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
    • F25B41/00—Fluid-circulation arrangements

Definitions

  • the present invention relates to a heat pump device.
  • heat pumps with a compressor work with a phase change, the working fluid absorbs heat during evaporation and gives off heat during condensation.
  • heat pump as a heat engine, for example, for space heating and / or domestic water heating
  • heat pumps as a chiller
  • a heat pump device with a cyclone unit and a piston machine with a cylinder space is provided.
  • a liquid working fluid is injected into the cyclone unit, while vaporous working fluid is compressed by the piston engine or relaxed during vaporous working fluid in the piston engine.
  • the injected liquid working medium moves in a circular manner in the cyclone unit.
  • the liquid working medium is thus kept in the cyclone unit, while vaporous working medium from the cylinder chamber can penetrate into the cyclone unit or escape from the cyclone unit into the cylinder chamber.
  • the invention relates to the idea that maximum theoretically achievable operating numbers for heating or cooling of a medium are not achieved with the cold vapor process, but with a substantially triangular in the T-s diagram cycle.
  • FIG. 1 shows a representation of a Ts diagram
  • Fig. 3 shows a schematic structure of a heat pump according to a first embodiment
  • FIG. 4 shows a schematic representation of a construction of a cyclone unit of a heat pump according to a first exemplary embodiment
  • Fig. 5 shows a sectional view through a cyclone according to a second embodiment
  • FIG. 6 shows an illustration of a T-s diagram according to a third exemplary embodiment.
  • Fig. 1 shows a Ts diagram of a triangular heat pump cycle.
  • the ideal process flows for a heat pump for the delivery of useful heat with the ideal cold vapor process (line 1-2-3-4-5-6-1) and the triangular process (dashed, 1 -2-6-1) are shown.
  • the presentation of the ideal processes is sufficient here.
  • the exergy loss in the processes is the proportion of the total energy of a system which can perform work when brought into thermodynamic equilibrium with its environment.
  • this exergy loss corresponds approximately to the area between the curves of the heat sink, dotted, 6-2, sensible heat, and the corresponding curve of the cold vapor process 2-3-4-5-6.
  • the exergy loss in the triangular process corresponds to the area between the curves of the heat sink 6-2 and the curve of the triangular process 2-6.
  • the cycle to be achieved is located in or directly at the wet steam zone of the working medium.
  • the triangular process consists of a horizontal sub-process (the catheter 1: isothermal evaporation or condensation), a vertical sub-process (the catheter 2), (ideally a reversible adiabatic, ie isentropic evaporation or condensation) and a heat exchange process with the medium to be cooled or heated , the hypotenuse in the triangle.
  • the latter sub-process which appears as a hypotenuse, is in a first approximation a straight line.
  • hypotenuse is an exponential function in assuming constant heat capacities and densities of the working medium as well as the medium which absorbs the heat. It turns out that the heat exchange process is usually carried out between two liquid media. Since very good countercurrent heat exchangers are available for liquid media, this sub-process can be expected to have an extremely low exergy loss.
  • the area of the cycle in the T-s diagram is a measure of the mechanical power that must flow into the heat pump. Since the area of the triangle is about half the area of the cold vapor process, the triangular process achieves twice the number of working hours compared to the cold vapor process.
  • Fig. 2 shows a schematic representation of four different types of heat pumps.
  • Q nutz refers to the Net power, Q from the power delivered and ö z "the power supplied to the machine.
  • the machines 3 and 4 are heat mirrors and come with appropriate dimensioning and design of the temperatures without the supply of mechanical energy.
  • Q are heat outputs that are introduced into the machine or removed from the machine depending on the direction of the arrow.
  • W meCh is the mechanical power supplied.
  • T Nutz are the temperature levels of useful power taken from the machine or into the machine be delivered. Depending on the type of machine, this temperature is higher or lower than the level of the ambient temperature
  • T To g ⁇ T ab and T to are temperature levels at which power must be dissipated from the machine or fed to the machine
  • T to 60 ° C
  • ambient temperature 30 ° C.
  • the machine type Temperature mirror cold from heat
  • the machine can deliver cooling capacity at a temperature level of around 5 ° C.
  • the amount of cooling capacity is about as large as the heat supplied to the machine from the collector.
  • the dissipated to the environment heat output consists of the sum of the amount of cooling capacity and the collector heat output, that is about twice as large as the collector heat output.
  • Fig. 3 shows a schematic representation of a structure of a heat pump as a heater with cyclone, inlet valve V, piston, piston rod and crankshaft with motor. Exhaust valves are not shown.
  • the heat pump device has a piston engine 10, an evaporator 20, a cyclone unit 30, an expansion valve 40, at least two non-return valves 50, a reservoir 60, a collecting container 70, an outlet valve 80 and a heat exchanger 90, via which heat can be delivered ,
  • a working medium in a liquid phase is introduced into the cyclone unit 30.
  • the compressed vapor condenses into the liquid working medium in the cyclone unit 30.
  • a liquid phase is injected during the compression process.
  • the cyclone unit 30 serves to receive the liquid phase and to prevent liquid phase from being injected into the cylinder space.
  • the liquid phase is injected on a circular path in the cyclone and thus remains in the cyclone.
  • the vaporous phase in the cylinder space is compressed and condenses with increasing pressure into the liquid phase, thereby heating the liquid phase.
  • the volume of the cyclone unit 30 not occupied by the liquid phase interacts with the cylinder volume 15 of the piston engine.
  • the cylinder volume extends into the cyclone unit 30, as it were.
  • the volume of the cyclone unit and the volume of the cylinder space 15 form an intersection.
  • the useful thermal power P nu t z is preferably taken off via a countercurrent heat exchanger.
  • water is at a temperature of 20 ° C at a pressure of 23mbar.
  • water is at 20 ° C and a pressure of 1 bar.
  • P ab is heat supplied from the environment in this case.
  • the figures 10% and 90% mean that the mass flows of the working medium at this branch, for example, in the ratio 10 to 90 split.
  • the piston engine has a first piston position, ie a top dead center OT, which is defined by the fact that the volume contained in the cylinder is minimal.
  • the piston engine has a second piston position (bottom dead center UT), which is defined by the fact that the volume contained in the cylinder is maximum.
  • Fig. 4 shows a schematic structure of the pre-chamber with a cyclone unit according to a first embodiment.
  • the liquid heat transfer medium moves on circular paths.
  • the gaseous heat transfer medium or the working medium can flow from the cylinder 10 into the cyclone 30 and, in the case of evaporation, from the cyclone 30 into the cylinder 10.
  • Fig. 5 shows a section through a cyclone with a twist according to a second embodiment. Not shown baffles in the cyclone and a tangential injection of the working medium provide a twist. This swirl promotes a mixing of the liquid working medium, which distributes the heat transferred by the phase change on the liquid surface evenly to the liquid phase.
  • Fig. 6 shows a T-s diagram of the novel process in direct injection after the suction of the steam (1) and in delayed injection (2) according to a third embodiment.
  • the figure shows the ideal course of the injection process immediately after steam extraction (1).
  • This process can e.g. be used for domestic water heating.
  • the delayed injection process (2) is shown.
  • the latter process can be used for space heating: steam at ambient temperature, e.g. 10 ° C, is first by adiabatic compression to z. B. 28 ° C compressed. Then 25 ° C warm liquid working medium is injected. Upon further compression, the condensation and heating of the working medium to z. B. 40 ° C a.
  • the non-specific entropy S (Ws / K) was chosen as x-axis.
  • Process type evaporation In the OT, liquid heat transfer medium is injected into the cylinder chamber. When the piston travels from the TDC to the TDC, the heat transfer medium is vaporized and the liquid heat transfer medium is cooled. In UT, the liquid heat transfer medium is removed from the cylinder chamber. On the way of the piston from BDC to TDC, the steam is expelled and condensed in a condenser. In the OT, the steam outlet valves are closed. The process starts from the beginning.
  • a machine that picks up heat from a higher temperature level than the ambient level and picks up heat from a lower temperature level than the surrounding level, or a machine that gives off heat to a higher temperature level than the surrounding level and gives off heat to a lower temperature level than the surrounding level also referred to here as a heat pump.
  • the latter two types of heat pumps are referred to as heat mirrors, when in an ideal course of the process, the temperature differences between the cold and the hot levels to the ambient level are equal in first approximation and the amounts of heat converted are the same.
  • a reciprocating engine As an example of a displacement machine, a reciprocating engine can be selected. In principle, however, the use of any type of displacement machine for the realization of the triangular processes according to the invention is possible.
  • the piston position top dead center also called OT
  • the lower dead point also called UT, defined by the fact that the volume contained in the cylinder is maximum in this piston position.
  • working fluid condenses in the working space (here: cylinder space) of the compression machine
  • working fluid evaporates in the working space (here: cylinder space) of the expansion machine.
  • the first type of triangular cycle is characterized in that first a working medium is evaporated to the temperature level of the environment while supplying heat in the evaporator (for example, evaporator 20) (heat consumption).
  • the steam is sucked into the cylinder during the expansion, in this case during the piston movement from top dead center OT to bottom dead center UT.
  • liquid and cold working medium is introduced into the cylinder chamber.
  • the trapped vapor condenses into and heats the injected liquid and cold phases.
  • the liquid phase is removed from the cylinder space. The heated liquid phase can then deliver the heat supplied to them as useful heat.
  • the second type of triangular cycle is distinguished by the fact that liquid working medium is introduced into the piston engine in the region of top dead center OT. If now the piston moves from top dead center OT to bottom dead center UT, part of the working medium evaporates and the working fluid cools down. If the piston is at bottom dead center UT, the cooled liquid phase is removed from the cylinder chamber and used for cooling purposes.
  • the prerequisite for the controlled phase change in both cycle types is that surfaces comprising the cylinder space have a higher temperature than the liquid phase; For these reasons, said surfaces may need to be heated and / or coated.
  • the piston machine is an example of a discontinuous displacement machine.
  • the triangular process can also be implemented in other displacement machines.
  • Essential for the process is essentially an isentropic compression or expansion.
  • An example of a displacement machine is a screw machine or a scroll compressor. The fact that currently available screw machines have too low a compression or expansion ratio, is noted marginally.
  • the two above-mentioned processes are realized in displacement machines as follows:
  • the first type of cycle is characterized by a compression of a fluid which exists in two phases. Consequently, steam is first generated in an evaporator and sucked by the compression machine. Before entering the steam in the compression machine or after a pre-compression of the steam in the compression machine, liquid phase is introduced into the steam. In the compression machine, the mixture is further compressed. The vapor condenses into the liquid phase. If the steam is completely condensed, then there is only liquid phase at the outlet of the machine. In this ideal case and with isentropic conditions, the complete triangular process can be realized. As with the piston engine, the hot liquid medium releases its heat as useful heat after it leaves the machine.
  • the second type of cycle is in the general case of the expansion machine as follows: liquid working medium is introduced into the expansion machine.
  • the expansion forces steam production.
  • the required evaporation capacity is taken from the liquid phase, whereby it cools and can be used after leaving the machine for cooling purposes.
  • Heat-insulating coatings on the surfaces of the working area favor isentropic process control.
  • the heat transfer from the cylinder wall to the gaseous working medium is slight due to the low gas velocities and the low density of the gas.
  • the heat transfer from the cyclone wall to the liquid working medium is achieved by coating the corresponding cyclone wall with a heat-insulating material, e.g. Teflon, ceramic or enamel and / or by special types of injection of the working fluid to be kept harmless level.
  • a heat-insulating material e.g. Teflon, ceramic or enamel
  • the liquid working medium is injected onto a circular path in an antechamber of the cylinder. Below we also call this circular path cyclone.
  • the liquid working medium remains in the prechamber, while the gaseous working medium can move through an overflow opening between the prechamber and the cylinder space, depending on the prevailing pressure conditions between the rooms.
  • the liquid working medium is atomized during the injection process into the smallest possible droplets.
  • the droplets are distributed in the cylinder space. Only droplets that come in the immediate vicinity of the heated surfaces can absorb heat on these surfaces. Since the heat absorption is associated with the evaporation of the droplets, the proportion of steam in the area of the heated surfaces increases and the vapor on the surfaces overheats. The superheated vapor inhibits further drops of liquid from moving toward the heated surfaces, reducing heat transfer.
  • Important in the condensation in the liquid working medium is a good distribution of the heat of condensation within the liquid phase.
  • the frictional flow of the liquid working medium leads to its mixed state.
  • the cyclone for mixing the working fluid having a special design that allows turbulence of the working fluid. Heat released by the condensation on the surface of the liquid phase is thus dispersed quickly enough throughout the liquid phase due to the mixing.
  • the cyclone has the advantage that removal of the liquid working medium from the cylinder can be carried out easily: if an outlet valve is opened on the cyclone bottom, the centrifugal forces help to remove the liquid working medium from the antechamber.
  • the distribution of the heat of condensation poses no problem: the liquid droplets can be chosen to be very small, so that the distribution of the heat within the droplets is very fast due to heat conduction.
  • the distribution of heat within the cloud of fog necessarily results from partial pressure differences: the condensation is always greatest at the coldest point and thus leads to a temperature compensation in the cloud.
  • the present invention relates to the structure and function of a heat pump with a phase change of the working medium in the cylinder space of a piston engine, wherein the heat transfer medium is liquid and vaporizable and is injected in liquid form into the cylinder chamber.
  • a heat pump is provided in which liquid working medium is injected.
  • the liquid working fluid is injected into a portion of the cylinder space of the engine, namely the pre-chamber.
  • the working medium moves in circular paths, the liquid heat transfer medium due to the high density and Because of the centrifugal forces caused thereby predominantly in the antechamber is kept, while vaporous working medium escape into the entire cylinder chamber and can penetrate from the cylinder chamber into the prechamber.
  • the heat pump has a working space consisting of cylinder space and pre-chamber, wherein the cylinder space and the pre-chamber are connected in such a way that an overflow of steam is possible.
  • An evaporable working medium is introduced in liquid form into the pre-chamber, wherein the working medium is introduced onto a circle-like path.
  • the circular path of the liquid phase causes centrifugal forces which greatly radially accelerate the liquid phase due to the high density.
  • the radial acceleration and the structural design of the cyclone cause that the liquid phase can not escape from the antechamber.
  • the volume of the cyclone device (dead space) should be as small as possible in the structure. In other words, the volume between the piston at top dead center and the volume of the cyclone unit not required by the liquid phase should be as small as possible.
  • the working medium in the cyclone in addition to the circular movement receives a twist, whereby the mixing of the working medium is improved.
  • the cyclone is designed substantially circular in cross-section, so that the working medium can be provided with a swirl.
  • the swirl serves to promote an intimate mixing of the working medium and to prevent the formation of a harmful for the process efficiency temperature gradient in the working medium.
  • the walls of the cyclone which come into contact with the liquid phase, coated with a poor thermal conductivity material.
  • the cyclone wall is provided with a poorly heat-conductive coating.
  • This coating can be, for example, Teflon, ceramic or enamel.
  • the working medium is injected in liquid form into the cylinder chamber of the machine, wherein the liquid phase is atomized by means of an injection nozzle.
  • a heat pump is provided in which the liquid working medium is atomized as finely as possible during the injection process by means of an injection nozzle.
  • the surface of the piston facing the vapor-filled space of the cylinder is coated with a material having poor thermal conductivity.
  • the relevant surface of the piston is provided with a poorly heat-conductive coating.
  • This coating can be, for example, Teflon, ceramic or enamel.
  • the structural parts coming into contact with the resulting steam are designed to be heated.
  • the gaseous phase accessible components of the engine When the gas is compressed, the gaseous phase accessible components of the engine must be at a temperature greater than the condensation temperature at the instantaneous vapor pressure. If the surfaces of the components were colder, part of the gaseous phase would condense abruptly on these surfaces. The condensed phase would no longer be available for condensation in the working medium, and the machine's performance and workload would be reduced.
  • the exhaust valves are closed in the region of top dead center, followed by the admission of steam to bottom dead center, whereupon the inlet valves are closed and liquid working fluid is injected directly or with a delay, followed by compression and condensation of the vapor in the liquid phase, whereupon the exhaust valve is opened at top dead center and thus the ejection of the heated liquid phase takes place. Then the cycle starts again.
  • This aspect of the present invention relates to the process management in the process type condensation. With the machine one can of a Two-stroke talk. In the TDC, the inlet valves for the steam are opened. Steam is drawn from the evaporator until UT is reached. In UT, the inlet valves are closed and liquid working fluid is injected directly or with a delay.
  • the steam and the liquid working fluid are at the same temperature, they can be injected immediately after closing the intake valves. If the liquid phase to be injected is warmer than the vapor phase, it is not injected until the steam in the cylinder has been compressed until the pressure of the steam corresponds to the vapor pressure of the liquid phase.
  • the steam is compressed and it causes condensation of the vapor in the liquid phase.
  • the inlet valves are opened again, whereby the circuit is closed.
  • the vaporous working medium in the cylinder is compressed, whereby it condenses at the coldest point, namely in the injected liquid phase, thereby heating the liquid phase.
  • the injected liquid working fluid may also have a temperature lower than the ambient temperature. In this case, a sudden reduction of the vapor pressure occurs during the injection.
  • the injection variant cold water is used, for example, for the heat pump type heat from cold. With a suitable temperature selection of the cold liquid working medium operation of the heat pump without mechanically supplied drive energy is possible.
  • the exhaust valves are closed in the region of top dead center, whereupon liquid working medium is injected, whereupon the expansion begins and the evaporation from the liquid phase and thereby the cooling of the liquid phase takes place, whereupon at bottom dead center liquid phase is removed and the outlet valves are opened for the gaseous phase, followed by reaching the top dead center of the ejection of the gaseous phase.
  • This aspect of the present invention relates to the process control in the evaporation process.
  • TDC top dead center
  • the exhaust valve (s) is closed. and then injected the working medium.
  • the working medium evaporates a part of the working medium.
  • the injected heat transfer medium is water.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif à pompe à chaleur comprenant une unité à cyclone (30) et un moteur à piston (10) présentant un compartiment à cylindre (15). Un milieu de travail liquide est injecté dans l'unité à cyclone (30), pendant qu'un milieu de travail à l'état de vapeur est compressé dans le moteur à piston, ou pendant qu'un milieu de travail à l'état de vapeur est détendu dans le moteur à piston.
EP07727186A 2006-03-21 2007-03-21 Dispositif à pompe à chaleur Withdrawn EP2016346A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610012852 DE102006012852A1 (de) 2006-03-21 2006-03-21 Wärmepumpen mit Phasenwechsel des Arbeitsmediums im Arbeitsraum einer Verdrängungsmaschine
PCT/EP2007/052710 WO2007107593A2 (fr) 2006-03-21 2007-03-21 Dispositif à pompe à chaleur

Publications (1)

Publication Number Publication Date
EP2016346A2 true EP2016346A2 (fr) 2009-01-21

Family

ID=38438226

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07727186A Withdrawn EP2016346A2 (fr) 2006-03-21 2007-03-21 Dispositif à pompe à chaleur

Country Status (3)

Country Link
EP (1) EP2016346A2 (fr)
DE (1) DE102006012852A1 (fr)
WO (1) WO2007107593A2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EA021498B1 (ru) * 2010-10-19 2015-06-30 Юрий Маркович ПЕТИН Способ горячего водоснабжения и способ отопления с его использованием

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Publication number Priority date Publication date Assignee Title
DE645746C (de) * 1936-06-17 1937-06-03 Georges Loeffler Verfahren zum Betriebe von Kaelteverdichtern
US2958209A (en) * 1958-11-03 1960-11-01 Basil G Egon Heat pump
FR1514272A (fr) * 1967-01-06 1968-02-23 Commissariat Energie Atomique Dispositif de circulation
US3732704A (en) * 1971-03-03 1973-05-15 Carrier Corp Refrigeration system including refrigerant metering means
DE2649363A1 (de) * 1976-10-29 1978-09-14 Karl Friedrich Vedder Verfahren zur umwandlung von waerme in mechanische arbeit
US4218891A (en) * 1978-05-22 1980-08-26 Schwartzman Everett H Cooling and heat pump systems and methods
US4213308A (en) * 1978-10-12 1980-07-22 Anderson J Hilbert Vortex generator for separating a gaseous and liquid refrigerant
DE4338939C1 (de) * 1993-11-15 1995-02-16 Bitzer Kuehlmaschinenbau Gmbh Verfahren und Vorrichtung zum Kühlen eines Kältemittelverdichters
JPH07332806A (ja) * 1994-04-12 1995-12-22 Nippondenso Co Ltd 冷凍装置
AU2001239966A1 (en) * 2000-03-03 2001-09-17 Vai Holdings, Llc. High efficiency refrigeration system

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Title
See references of WO2007107593A3 *

Also Published As

Publication number Publication date
WO2007107593A3 (fr) 2007-12-06
DE102006012852A1 (de) 2007-09-27
WO2007107593A2 (fr) 2007-09-27
WO2007107593B1 (fr) 2008-03-27

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