WO2007054204A1 - Machine frigorifique a alimentation solaire - Google Patents

Machine frigorifique a alimentation solaire Download PDF

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Publication number
WO2007054204A1
WO2007054204A1 PCT/EP2006/010262 EP2006010262W WO2007054204A1 WO 2007054204 A1 WO2007054204 A1 WO 2007054204A1 EP 2006010262 W EP2006010262 W EP 2006010262W WO 2007054204 A1 WO2007054204 A1 WO 2007054204A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
refrigerant
working
working fluid
heat exchanger
Prior art date
Application number
PCT/EP2006/010262
Other languages
German (de)
English (en)
Inventor
Richard Engelmann
Original Assignee
Richard Engelmann
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 Richard Engelmann filed Critical Richard Engelmann
Publication of WO2007054204A1 publication Critical patent/WO2007054204A1/fr

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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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/002—Machines, plants or systems, using particular sources of energy using solar energy
    • F25B27/005—Machines, plants or systems, using particular sources of energy using solar energy in compression type systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/006—Solar operated
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/123—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber
    • F04B9/125—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting elastic-fluid motor
    • 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
    • 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
    • F25B2400/12—Inflammable refrigerants
    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/46—Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines

Definitions

  • the degree of cold is dimensionless and indicates the ratio of the amount of cold produced to the amount of energy used.
  • Electrically operated chillers have a degree of cooling of about 4
  • solar-electric chillers have a relation to the sunlight Cooling degree of about 0, 4
  • conventional solar thermal operated absorption chillers have a degree of cold of about 0.1.
  • the invention is based on the object to provide a solar-powered chiller, which is simple in construction and operates in a wide operating range with consistently good degrees of cold.
  • a refrigerating machine with a working medium circuit and with a refrigerant circuit wherein the working medium circuit comprises a working machine, a first condenser, a condensate pump and a first evaporator, and wherein the refrigerant circuit comprises a reciprocating compressor, a second condenser, an expansion valve and a second Evaporator includes, solved by the working machine is designed as a piston engine that the working fluid circuit and the refrigeration cycle are mechanically coupled and that the working fluid circuit and the refrigerant circuit are thermally coupled by means of a first heat exchanger and a second heat exchanger.
  • the relatively low working pressure of the working fluid can be efficiently and easily converted into mechanical energy.
  • the efficiency of the conversion is based inter alia on the fact that in a piston machine, the mechanical work is essentially caused by the pressure of the working gas on the piston and only a small part by an expansion of the gaseous working fluid.
  • Piston engines are also relatively robust in terms of their operating characteristics, so that in the naturally changing solar radiation performance, the quality of the cycle in the working fluid circuit remains almost constant.
  • this can be coupled directly to a piston compressor of the refrigerant circuit, so that there are no conversion losses and the turnover of the refrigerant circuit is coupled to the turnover of the working fluid circuit.
  • the degree of cooling can be improved by thermally coupling the working medium circuit and the refrigerant circuit by means of two heat exchangers.
  • the piston engine can be designed as a steam engine or as a steam engine.
  • the steam engine can work as an expansion or displacement machine. Which of these piston engines is given preference in individual cases depends on the types and outputs available on the market.
  • the piston engine comprises two or more pistons and cylinders. Dimensions and number of pistons and cylinders naturally depend on the required drive power for the reciprocating compressor.
  • the warm side of the first heat exchanger is arranged between an outlet of the piston engine and the first condenser and if the cold side of the first heat exchanger is arranged between the evaporator and an inlet of the piston compressor.
  • a second heat exchanger is provided between the outlet of the condensate pump and the solar collector of the working medium circuit on the one hand and the outlet from the piston compressor and the inlet to the second condenser of the refrigerant circuit, so that here in the refrigerant after compression existing thermal energy at the appropriate temperature level can be transferred to the working fluid.
  • Both heat exchangers can be used both individually and in combination with each other. It goes without saying that by using two heat exchangers and two internal heat recovery systems, the degree of cold is better than when only one heat exchanger is used.
  • the first evaporator is designed as a solar collector.
  • various types of conventional thermal solar collectors such as concentrating or non-concentrating collectors can be used. It is also possible to use vacuum flat collectors or evacuated tube collectors, depending on the temperature of the working medium.
  • a first control valve is provided and at the outlet of the piston engine, a second control valve is provided.
  • the first control valve As with any steam engine, it is possible to alternately flow the pressurized working fluid into a first working space and into a second working space of the reciprocating engine. This will be the caused oscillating movement of the piston of the piston engine.
  • the second control valve is provided at the outlet of the piston engine. This control valve is controlled so that the one working space that is not acted upon by high pressure working fluid from the solar collector, with a capacitor or a first heat exchanger is hydraulically in communication.
  • the second control valve also makes it possible to operate the piston engine hermetically and to prevent the escape of working fluid into the environment.
  • FIG. 1 shows the process scheme
  • FIG. 2 shows the temperature range of the two circuits
  • FIG. 3 shows the pressure range of the two circuits
  • FIG. 4 shows the working medium circuit
  • FIG. 5 shows the refrigerant circuit
  • FIG. 6 the combination of both circuits
  • Figure 7 shows a piston engine with two working pistons and directly coupled reciprocating compressor
  • FIG. 8 shows a piston machine with two membranes for driving a compressor piston.
  • FIG. 1 shows a flow chart of the solar-powered refrigerating machine according to the invention.
  • the refrigerating machine according to the invention has a working medium circuit and a refrigerant circuit.
  • the working fluid circuit comprises a solar collector in which a working fluid is vaporized and overheated. This means that the solar collector assumes the function of an evaporator in a conventional right-handed cycle.
  • a piston machine is subjected to the pressurized working fluid and thereby generates mechanical energy.
  • the emerging from the piston engine working fluid is condensed in a condenser and supplied to the solar collector with the aid of a condensate pump, not shown.
  • the refrigerant circuit is shown schematically. In the refrigerant circuit is using an evaporator located under low pressure Working fluid evaporates. The heat required for this is taken from the medium to be cooled.
  • the vaporized refrigerant is brought to a higher pressure in a reciprocating compressor. At the same time, this increases the temperature of the refrigerant to such an extent that the refrigerant can deliver heat to the environment or to another medium. This process takes place in a condenser.
  • an unillustrated expansion valve is provided.
  • FIG. 2 shows, by way of example, the temperature deviation of a working cycle.
  • This temperature can, for example, between 45 ° C and 60 0 C, if the working fluid in the solar collector is not overheated. If the working fluid overheats, the temperature in the solar collector can also be higher. Since the working cycle does not fall below a temperature of 45 ° C. during operation, but the refrigeration cycle in the region of the evaporator, for example, temperatures of about 0 0 C, it is possible to couple heat from the condenser of the working fluid circuit in the evaporator of the refrigerant circuit.
  • the solar chiller invention satisfies the main theorems of thermodynamics.
  • the temperatures and pressures are dependent on the working fluids and refrigerants used.
  • the solar chiller according to the invention can be adapted to specific work areas and operating conditions.
  • the working medium circuit comprises a solar collector 1, which is connected via a line (without reference numeral) to an inlet 3 of a steam engine 5.
  • the steam engine 5 comprises a cylinder 7 in which a double-acting piston 9 oscillates.
  • the oscillation movement of the piston 9 is indicated by a double arrow 11.
  • the piston 9 divides the interior of the cylinder 7 in a first working space 13 and a second working space 15th
  • An outlet 17 of the steam engine 5 is connected to a first condenser 19 via another line (not numbered).
  • the working fluid heat Q a b is withdrawn, so that the working fluid is condensed and with the aid of a condensate pump 20 again the solar collector 1 can be supplied.
  • a first 3/2-way control valve is provided at the inlet 3 of the steam engine 5.
  • the first control valve 23 connects the solar collector 1 with the first working space 13.
  • the piston 7 moves to the right and reduces the volume of the second working space 15th
  • a second control valve 25 is provided, which connects the outlet 17 and thus the second working chamber 15 of the steam engine 5 with the condenser 19 in the first switching position shown in FIG.
  • control of the control valves 21 and 23 is not shown in Figure 4, however, various concepts are known from the field of steam engine technology and compressed air technology, with the aid of the movement of the piston 9 for controlling the control valves 21 and 23 can be used. Also electrical and pneumatic controls are common.
  • FIG. 5 a refrigerant circuit is now shown, which can be used in the solar cooling machine according to the invention.
  • the central component of this refrigerant circuit is a piston compressor 27 with a cylinder 29 in the one Piston 31 oscillates.
  • a piston rod 33 is mounted on the piston 31, which is mounted.
  • the cylinder 29 and the piston 31 define a working space 35.
  • the piston 31 When the piston 31 is placed in an oscillating motion (see the double arrow 11), it conveys a refrigerant from a second evaporator 41 into a second condenser 43. At the same time, the pressure and temperature of the refrigerant in the reciprocating compressor 27 are increased.
  • the compression ratio of the reciprocating compressor 27 must be selected so that the refrigerant has a sufficiently high temperature when entering the second condenser 43, to be able to deliver heat either to another heat carrier or the environment. In this case, the refrigerant condenses in the second condenser 43.
  • the condensed refrigerant passes to an expansion valve 45 and is there to a low pressure, for example, 0.5 bar, expanded. This reduces the temperature of the refrigerant.
  • a low pressure for example, 0.5 bar
  • the expanded and low-temperature refrigerant enters the second evaporator 41, it may become relatively low Temperature of, for example, 0 ° C heat Q Z u absorb and evaporate.
  • FIG. 6 the working fluid circuit according to FIG. 4 and the refrigerant circuit according to FIG. 5 are connected to form a solar chiller according to the invention.
  • the solar chiller according to the invention not only the steam engine 5 and the piston compressor 27 are mechanically coupled, but with the aid of a first heat exchanger 47 and a second heat exchanger 49 are the
  • the working medium circuit and the refrigerant circuit are also thermally coupled by means of the first heat exchanger 47 and the second heat exchanger 49.
  • the first heat exchanger 47 and the second heat exchanger 49 have a so-called warm side and a cold side.
  • the warm side flows through the medium, which gives off its heat energy to the medium flowing through the cold side.
  • the working fluid gives heat to the between the outlet from the second evaporator 41 and the entry into the Piston compressor 27 located refrigerant from.
  • suction gas superheat is used for this transfer of heat energy at the inlet of the compressor.
  • the working fluid at the outlet from the steam engine 5 has a temperature of about 45 ° C, while the refrigerant at the outlet from the second evaporator has a temperature of about xx ° C. This temperature difference is sufficiently large to transfer the heat from the working fluid to the refrigerant can.
  • the second heat exchanger 49 is arranged with its warm side between the outlet from the piston compressor 27 and the inlet to the second condenser 43.
  • the cold side of the second heat exchanger 49 is arranged between the outlet from the condensate pump 20 and the inlet to the solar collector 1. This makes it possible to transfer heat from the refrigerant to the working fluid and thus to raise the inlet temperature of the working fluid in the solar collector 1 and to evaporate a large part of the working fluid.
  • the energy requirement is reduced with the same cooling capacity and the solar chiller according to the invention, provided the same solar irradiation, more efficient.
  • the solar chiller can operate at the following temperatures and pressures:
  • the pressure indications are absolute values, i. Normal pressure is 1 bar, vacuum is 0 bar.
  • the working medium is vaporous and overheated. Its temperature is about 90 ° C and its pressure about 5 bar.
  • the working fluid is still vaporous at a temperature of about 60 0 C and a pressure of about 3 bar.
  • the working fluid releases part of its heat energy to the refrigerant and becomes saturated steam at about 45 ° C. and 3 bar.
  • the saturated steam gives off further heat energy and condenses completely.
  • the condensate is brought by means of the condensate pump 20 to a pressure of 5 bar and conveyed into the second heat exchanger 49
  • the working fluid absorbs heat and flows at a temperature of 60 0 C back to the solar collector 1.
  • gaseous refrigerant is compressed from 0.5 bar to 7 bar.
  • the temperature rises from 30 0 C to 80 0 C; it remains gaseous.
  • Via a line it flows to the second heat exchanger 49. There, it cools at constant pressure to 60 0 C and becomes wet steam.
  • a line Via a line, it flows to a second condenser 43 and releases heat to the environment until complete condensation.
  • the temperature of the refrigerant exiting the second condenser 43 is dependent on the ambient temperature and is approximately at 45 ° C.
  • the refrigerant flows to the expansion valve 45 and expands to 0.5 bar.
  • the expansion valve has to ensure in its characteristic the evaporation pressure of 0.5 bar and is the only control element in the circuit.
  • the expansion of the refrigerant leads to a cooling of the refrigerant to about 0 ° C in saturated steam condition.
  • the refrigerant can absorb heat.
  • the second evaporator 41 is the refrigeration device for the air conditioning by heat is absorbed from the environment or by a heat transfer medium to be cooled.
  • the cold working fluid flows via a line into the first heat exchanger 47 and is there to superheated steam at a temperature of about 30 0 C. From there it is sucked via a line in the reciprocating compressor. This closes the refrigerant circuit.
  • Mi is the mass flow of the working fluid
  • M2 the mass flow of the refrigerant
  • dpi the pressure stroke of the working fluid
  • dp2 the pressure stroke of the refrigerant
  • the power reduction caused by the difference in the mass flow and the loss of efficiency can be partially offset by the use of two different refrigerants.
  • the working fluid on the side of the working cycle must have the lowest possible specific evaporation energy, the refrigerant on the side of the refrigeration cycle as high as possible.
  • Propane has a specific evaporation energy of 18 KJ / mol while R 245 has a specific evaporation energy of 28 KJ / mol.
  • R 365 As a working medium or as a refrigerant can also be used: R 365; R 227; R 134 and mixtures of these refrigerants.
  • FIG. 7 schematically shows an exemplary embodiment of a steam engine 5 with two pistons. This makes it possible to double the force of the steam engine 5 with the same piston diameter.
  • the two pistons 9 act on the same piston rod 25, which, as in the previous embodiment, is coupled to the piston rod 33 of the piston compressor 27.
  • the first control valve 21 and the second control valve 23 are still 3/2-way valves. However, the connections are and the switch positions slightly different than in the control valves 21 and 23 according to FIG. 6.
  • the first control valve 21 has, like the second control valve 23 also, an inlet 51 which is connected to the solar collector 1. Furthermore, the control valves 21 and 23 each have a first outlet 53 which is connected to the first heat exchanger 47 (not shown). A second outlet 55 of the first control valve 21 is connected to the second working spaces 15 of the steam engine 5.
  • a second outlet 57 of the second control valve 23 is connected to the first working spaces 13 of the steam engine 5.
  • the piston compressor 27 is thereby simultaneously actuated and the refrigerant is compressed in the desired manner.
  • the pistons 9 are designed as membranes 59. This means that they are sealingly connected to the cylinder 7 on the one hand and the piston rod 25.
  • the membrane 59 separates both circuits to the outside and against each other hermetically.
  • the diaphragms 59 are flexible, so that, for example, when pressurized working fluid reaches the first working spaces 13 via the second outlet 57 of the second control valve 23, the diaphragms deform so that they move to the right in FIG. 8 and, because of them rigid connection with the piston rod 25 thereby move the piston rod 25 to the right.
  • Embodiment according to Figure 8 only a second working space 15 is present, which can be filled via the second outlet 55 of the first control valve 21 with working fluid from the solar collector 1. By filling the second working space 15, the return stroke of the piston 31 and the suction of the refrigerant in the piston compressor 27 are made.
  • a space 61 which is arranged between the diaphragm 59 arranged on the right in FIG. 8 and the piston compressor 27, has a connection, not shown, to the environment, so that no pressure is built up in the space 61 during the compression stroke of the piston 31 of the piston compressor 27.
  • this space 61 it would also be possible to close this space 61 tight and to use the gas in this space as a gas spring. This gas spring then supports the suction stroke of the piston 31 of the reciprocating compressor 27.
  • the variant according to FIG. 8 can advantageously be used when the working medium and the refrigerant are different and mixing of the two refrigerants in the area of the steam engine 5 and the reciprocating compressor 27 is to be avoided.
  • a special position in the invention assumes the structural design of the drive and compressor unit.
  • expansion or flow machines are not available on the market, especially the low pressures below 10 bar, the temperatures around 100 0 C and the small gas volume flows of less than 1000 liters / minute set here limits.
  • this unit should be constructed as simply as possible, the working fluid must act via a piston or a membrane directly on the refrigerant to be compressed. Translations or transmissions should not be used.
  • the unit should be hermetic. So it should come to a displacement machine on the drive side are used.
  • the hot, gaseous working fluid moves by displacement a piston or a membrane on the opposite side of which is to be compressed refrigerant.
  • the effective working piston must have a larger area than the piston of the compressor.
  • the ratio of effective areas must be at least 6.5 to 2 or higher.
  • Figures 7 and 8 show a unit with two working pistons and a compressor piston through the connection of the working piston creates a pressure boost.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne une machine frigorifique à alimentation solaire dans laquelle une machine d'évaporation (5) et un compresseur à piston (27) sont couplés directement l'un à l'autre, les circuits de fluide de travail et les circuits de fluide frigorifique étant couplés thermiquement les uns aux autres à l'aide de deux échangeurs de chaleur (47, 49).
PCT/EP2006/010262 2005-11-10 2006-10-25 Machine frigorifique a alimentation solaire WO2007054204A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005053589.5 2005-11-10
DE200510053589 DE102005053589A1 (de) 2005-11-10 2005-11-10 Solar betriebene Kältemaschine

Publications (1)

Publication Number Publication Date
WO2007054204A1 true WO2007054204A1 (fr) 2007-05-18

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ID=37564118

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Application Number Title Priority Date Filing Date
PCT/EP2006/010262 WO2007054204A1 (fr) 2005-11-10 2006-10-25 Machine frigorifique a alimentation solaire

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WO (1) WO2007054204A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008013673B3 (de) * 2008-03-11 2009-09-17 Richard Engelmann Kolbendampfmaschine für einen solar betriebenen Rankine-Kreislauf
WO2009153143A1 (fr) * 2008-05-29 2009-12-23 Shell Internationale Research Maatschappij B.V. Procédé permettant de faire fonctionner un compresseur à l'énergie solaire concentrée et appareil à cet effet
DE102009057630A1 (de) * 2009-12-09 2011-06-16 Robert Bosch Gmbh Klimatisierungsvorrichtung und thermisch betriebenes Wärmepumpenmodul mit Druckübertrager sowie Verfahren zum Betreiben
WO2012122350A1 (fr) * 2011-03-08 2012-09-13 Poerio Wayne Climatisation à turbopompe solaire et chauffage hybride et procédé de fonctionnement
US9772127B2 (en) 2011-03-08 2017-09-26 JOI Scientific, Inc. Solar turbo pump—hybrid heating-air conditioning and method of operation
DE102011017433C5 (de) * 2011-04-18 2018-02-15 Compair Drucklufttechnik Zweigniederlassung Der Gardner Denver Deutschland Gmbh Verfahren zur intelligenten Regelung einer Kompressoranlage mit einer Wärmerückgewinnung

Citations (5)

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US3988901A (en) * 1975-02-18 1976-11-02 Scientific-Atlanta, Inc. Dual loop heat pump system
US4823560A (en) * 1988-05-27 1989-04-25 E Squared Inc. Refrigeration system employing refrigerant operated dual purpose pump
US5129236A (en) * 1990-09-06 1992-07-14 Solomon Fred D Heat pump system
US5761921A (en) * 1996-03-14 1998-06-09 Kabushiki Kaisha Toshiba Air conditioning equipment
US6739139B1 (en) * 2003-05-29 2004-05-25 Fred D. Solomon Heat pump system

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4103493A (en) * 1975-03-06 1978-08-01 Hansen, Lind, Meyer Solar power system
US5509274A (en) * 1992-01-16 1996-04-23 Applied Power Technologies Incorporated High efficiency heat pump system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3988901A (en) * 1975-02-18 1976-11-02 Scientific-Atlanta, Inc. Dual loop heat pump system
US4823560A (en) * 1988-05-27 1989-04-25 E Squared Inc. Refrigeration system employing refrigerant operated dual purpose pump
US5129236A (en) * 1990-09-06 1992-07-14 Solomon Fred D Heat pump system
US5761921A (en) * 1996-03-14 1998-06-09 Kabushiki Kaisha Toshiba Air conditioning equipment
US6739139B1 (en) * 2003-05-29 2004-05-25 Fred D. Solomon Heat pump system

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