US20160138837A1 - Heat pump arrangement and method for operating heat pump arrangement - Google Patents

Heat pump arrangement and method for operating heat pump arrangement Download PDF

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Publication number
US20160138837A1
US20160138837A1 US14/897,914 US201414897914A US2016138837A1 US 20160138837 A1 US20160138837 A1 US 20160138837A1 US 201414897914 A US201414897914 A US 201414897914A US 2016138837 A1 US2016138837 A1 US 2016138837A1
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United States
Prior art keywords
fluid
heat
heat pump
temperature
heating capacity
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Abandoned
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US14/897,914
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English (en)
Inventor
Bernd Gromoll
Florian Reißner
Jochen Schäfer
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Siemens AG
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Siemens AG
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: REISSNER, Florian, SCHÄFER, Jochen, GROMOLL, BERND
Publication of US20160138837A1 publication Critical patent/US20160138837A1/en
Abandoned legal-status Critical Current

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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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency

Definitions

  • Heat pump arrangements are used for industrial heat provision.
  • a heat pump is a machine which, by using technical work, absorbs thermal energy in the form of heat at a lower temperature from a heat source and, together with the drive energy of a compression machine, releases it as waste heat at a higher temperature to a heat sink.
  • a fluid is used, which is conveyed within the heat pump in a cycle process by the compression machine. This cycle process is also known as a thermodynamic vapor compression cycle.
  • Various embodiments described herein relate to a method and a heat pump arrangement by which useful heat at particularly high temperatures may be provided.
  • Various embodiments described herein relate to a method for operating a heat pump arrangement in which a first fluid flows through a first heat pump, a second fluid flows through a second heat pump, and heat is transferred from the first fluid to the second fluid using a heat exchanger.
  • Useful heat is extracted from the second fluid at a fluid temperature of at least 120° C., wherein the useful heat of the second fluid is released at a volumetric heating capacity of the first fluid and of the second fluid of at least 500 kJ/m 3 .
  • the volumetric heating capacity (VHC) is crucial for the theoretically achievable coefficient of performance (COP) of heat pumps.
  • COP coefficient of performance
  • the higher the volumetric heating capacity is above the stated 500 kJ/m 3 the higher also is the coefficient of performance (COP) of the respective heat pump.
  • the second heat pump particularly high fluid temperatures may be achieved.
  • useful heat at a particularly high temperature may be extracted from the second fluid as a function of the heat transferred by the first fluid.
  • Various embodiments described herein provide for the useful heat to be extracted from the second fluid at a fluid temperature of at least 150° C., and particularly of at least 160° C.
  • a fluid temperature of at least 150° C., and particularly of at least 160° C.
  • At least one fluoroketone flows through the first heat pump as the first fluid.
  • Fluoroketones are particularly safe to use in industry, since there is no need to take special protective measures in the event of an incident. Since the use of fluoroketones is not governed by environmental requirements, use thereof is particularly future-proof. Moreover, they have a particularly low global warming potential and are non-flammable and non-toxic. For this reason, fluoroketones are particularly suitable for use as fluids in heat pump arrangements, in particular if industrial process heat, in particular useful heat at a temperature of greater than 120° C., is provided using these heat pump arrangements.
  • water or at least one fluoroketone is used as the second fluid. Since they are both environmentally friendly and unobjectionable from the point of view of safety, both water and fluoroketones are suitable in particular as fluids in applications in which high fluid temperatures occur, given that they are neither flammable nor toxic.
  • the coefficient of performance (COP) of the respective heat pump depends on the respective temperature rise.
  • the temperature rise of a heat pump is understood to mean the temperature difference which may be achieved between a respective condenser of the heat pump and a respective evaporator of the heat pump.
  • waste heat at a particularly high temperature may thus be provided and transferred by the heat exchanger to the second fluid of the second heat pump.
  • the maximum temperature of the second fluid which can be reached using the second heat pump thus depends directly on the quantity of heat transferred by the first fluid.
  • Particularly high coefficients of performance may be achieved using particularly large temperature rises of the respective heat pump, wherein it is advantageous for fluids of different composition to be used in each case for the first and second fluids.
  • fluid temperatures of at most 140° C. are to be achieved using the first heat pump, the use of fluoroketone NOVEC 524 is particularly recommended.
  • Fluoroketone NOVEC 524 has a particularly high volumetric heating capacity (VHC) in the range from 100° C. to 140° C. Since, however, NOVEC 524 is suitable only up to the stated maximum fluid temperature of 140° C., in order to achieve a temperature rise from 140° C. to 200° C. using the second heat pump, it is recommended that water be used as the second fluid, water also being suitable for greater fluid temperatures than 140° C.
  • VHC volumetric heating capacity
  • the heat release from the first to the second fluid proceeds largely isothermally.
  • the temperature of the released quantity of heat is kept particularly constant, whereby temperature fluctuations are particularly largely ruled out and thus also a largely constant temperature rise may be achieved using the second heat pump.
  • the first fluid has to be operated sub-critically, i.e. the first fluid can only be used below its critical temperature.
  • the first fluid has to be operated at a temperature at which both the liquid and the gaseous physical states may be present.
  • the useful heat is released at a volumetric heating capacity of at least 1000 kJ/m 3 , possibly of at least 1200 kJ/m 3 and possibly of at least 1500 kJ/m 3 of the second fluid.
  • COP coefficient of performance
  • heat may be transferred from the first fluid to the second fluid using a heat exchanger.
  • Useful heat may be transferred using the second fluid at a fluid temperature of at least 120° C., wherein the first fluid and the second fluid have a volumetric heating capacity of at least 500 kJ/m 3 .
  • Useful heat at a particularly high temperature may in this case be extracted from the second fluid as a function of the heat transferred by the first fluid.
  • a maximally high volumetric heating capacity of the first fluid of the first heat pump is favorable, wherein it is favorable if the quantity of heat transferred from the first to the second fluid is transferred at a particularly high temperature.
  • At least one temperature rise resulting from a relatively high pressure ratio of the first fluid and/or the second fluid may be increased by at least two-stage compression. If particularly large temperature rises are to be achieved with a fluid in a heat pump, two- or multistage compression is recommended.
  • intermediate cooling may be fitted between the compression apparatuses effecting the respective compression stage. This is sensible in particular where water is used as the fluid.
  • the heat of the intermediate cooling may be fed in a particularly energy-efficient manner to an evaporation apparatus of the respective heat pump. To bring about very high temperature rises, cascades of more than two heat pump circuits are also possible.
  • the second fluid is largely isothermally compressible using a liquid ring compressor. Compression of the fluid may proceed largely isothermally using a liquid ring compressor. The liquid ring of the liquid ring compressor is then in direct contact with the fluid to be compressed, whereby heat of compression may be transferred particularly effectively from the fluid to the ring liquid from which the liquid ring is formed. The heat transfer resistance is thus particularly low, since the fluid and the ring liquid are not divided from one another by a wall.
  • FIG. 1 is a schematic representation of a heat pump cascade according to the related art, which corresponds to a heat pump arrangement with in the present case two heat pump circuits;
  • FIG. 2 is a schematic diagram of the respective curves of the volumetric heating capacities of various fluids of the heat pump arrangement plotted against temperature
  • FIG. 3 is a schematic representation of a heat pump cascade which corresponds to a heat pump arrangement with two heat pump circuits, wherein one of the heat pump circuits is operated with a fluoroketone as fluid.
  • FIG. 1 is a schematic representation of a heat pump arrangement which comprises two heat pump circuits and is known in accordance with the related art as a cascade heat pump 1 .
  • the cascade heat pump 1 includes a first heat pump 2 through which a first fluid flows and a second heat pump 3 through which a second fluid flows.
  • the first and second fluids are coupled together for heat transfer by a heat exchanger 19 .
  • the heat exchanger 19 includes a condenser 6 of the first heat pump 2 and an evaporator 8 of the second heat pump 3 .
  • the first fluid of the first heat pump 2 is evaporated by an evaporator 4 , wherein the evaporator 4 is supplied with thermal energy by a heat source 12 .
  • the first fluid heated by the evaporator 4 is delivered in the direction of an arrow 14 by the first heat pump 2 by a compressor 5 of the first heat pump 2 . Then, the heated and compressed first fluid in the condenser 6 releases heat to the evaporator 8 , wherein the second fluid of the second heat pump 3 is evaporated by the evaporator 8 . Subsequent to this release of heat, the first fluid is expanded by an expansion valve 7 of the first heat pump 2 and thereupon once again absorbs heat through the evaporator 4 . The circuit of the first heat pump 2 is thus closed.
  • the second fluid of the second heat pump 3 heated by the heat exchanger 19 i.e.
  • the second fluid flows in the direction of an arrow 15 through an expansion valve 11 of the second heat pump 3 and is expanded there. Then, the second fluid again absorbs heat by the heat exchanger 19 and the circuit of the second heat pump 3 is thus closed.
  • FIG. 2 is a schematic diagram of different curves of volumetric heating capacities, wherein the y axis of the diagram plots a volumetric heating capacity 20 and the x axis plots a fluid temperature 21 , which corresponds to the condensing temperature of the fluid.
  • FIG. 2 shows that a heating capacity curve 16 , which corresponds to the heating capacity curve of a fluoroketone known as NOVEC 524, in each case has higher values for the same fluid temperatures 21 than a heating capacity curve 17 , which corresponds to the heating capacity curve of a fluoroketone known as NOVEC 649.
  • NOVEC 524 the heating capacity curve 16
  • the heating capacity curve 16 of the fluoroketone NOVEC 524 is limited by reaching a critical point 28 at 148° C. and the heating capacity curve 17 of the fluoroketone NOVEC 649 is limited by reaching a critical point 29 at for instance 169° C.
  • a heating capacity curve 18 which corresponds to the heating capacity curve of water has the lowest volumetric heating capacity 20 in each case for the same fluid temperatures 21 compared with the two fluoroketones, water may be used over a particularly wide range of fluid temperatures 21 , without the critical point thereof being reached. As is additionally clear from FIG.
  • the heating capacity curve 18 of water at fluid temperatures below the critical point 28 and the critical point 29 is respectively below the heating capacity curve 16 and the heating capacity curve 17
  • the heating capacity curve 18 of water rises at high fluid temperatures 21 to greater values than can be achieved with the heating capacity curve 16 and the heating capacity curve 17 as a consequence of the respective critical points 28 and 29 respectively being reached.
  • a quantity of heat with a working temperature of at least 160° C. may be released by the cascade heat pump 1 to the heat sink 13 if the fluoroketone NOVEC 649 is used as the first fluid of the first heat pump 2 .
  • the second fluid of the second heat pump 3 Since, on the basis of the quantity of heat transferred by the heat exchanger 19 from this first fluid to the second fluid at a temperature of up to 160° C., the second fluid of the second heat pump 3 is heated further, a temperature of the useful heat even higher than 160° C. may be reached by the second heat pump 3 .
  • a fluoroketone 26 such as NOVEC 524
  • the fluid temperature 21 to which the fluoroketone 26 is heated remains below the fundamental critical temperature of the critical point 28 , in order to allow isothermal heat release by the heat exchanger 19 to the second fluid of the second heat pump 3 .
  • Water 27 is used, for example, as the second fluid of the second heat pump 3 .
  • the cascade heat pump 1 illustrated in a schematic representation in FIG. 3 substantially includes the components already described in FIG. 1 , for which reason only the differences will be examined below.
  • the heat exchanger 19 includes a high temperature condenser 22 of the first heat pump 2 and a high temperature evaporator 23 of the second heat pump 3 . Moreover, as is visible in FIG. 3 , a liquid ring compressor 24 is used to deliver the water 27 , rather than the compressor 9 . In the liquid ring compressor 24 , the water 27 , which has been previously evaporated as the result of an input of heat by the high temperature evaporator, is compressed and supplied to a high temperature condenser 25 .
  • a quantity of heat is transferred at a fluid temperature 21 of 140° C. of the fluoroketone 26 , which does not exceed the critical temperature of the critical point 28 , by the high temperature condenser 22 of the first heat pump 2 to the high temperature evaporator 23 of the second heat pump 3 .
  • a quantity of heat at a particularly high temperature may be released to the water 27 by the high temperature evaporator 23 , wherein as a consequence a quantity of useful heat at a particularly high temperature may be released to the heat sink 13 by the high temperature condenser 25 .
  • the water 27 which is conveyed as a fluid in the second heat pump 3 is heated to a temperature of for example 200° C. by the quantity of heat at 140° C. transferred by the heat exchanger 19 from the fluoroketone 26 to the water 27 , this corresponds to a rise in temperature of 60° C. of the water 27 .
  • the volumetric calorific value 20 of water 27 amounts to over 4000 kJ/m 3 , i.e. a markedly higher value than 1500 kJ/m 3 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
US14/897,914 2013-06-14 2014-06-04 Heat pump arrangement and method for operating heat pump arrangement Abandoned US20160138837A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102013211087.1 2013-06-14
DE102013211087.1A DE102013211087A1 (de) 2013-06-14 2013-06-14 Verfahren zum Betrieb einer Wärmepumpenanordnung und Wärmepumpenanordnung
PCT/EP2014/061528 WO2014198593A1 (de) 2013-06-14 2014-06-04 Verfahren zum betrieb einer wärmepumpenanordnung und wärmepumpenanordnung

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US20160138837A1 true US20160138837A1 (en) 2016-05-19

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US (1) US20160138837A1 (ja)
EP (1) EP2989395A1 (ja)
JP (1) JP6526639B2 (ja)
KR (2) KR20160018795A (ja)
CN (1) CN105264306A (ja)
CA (1) CA2915305C (ja)
DE (1) DE102013211087A1 (ja)
WO (1) WO2014198593A1 (ja)

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US10662583B2 (en) * 2014-07-29 2020-05-26 Siemens Aktiengesellschaft Industrial plant, paper mill, control device, apparatus and method for drying drying-stock
US10976078B2 (en) 2016-03-14 2021-04-13 Efficient Energy Gmbh Heat pump system comprising two stages, method of operating a heat pump system and method of producing a heat pump system
EP4063762A1 (en) 2021-03-26 2022-09-28 Mitsubishi Electric R&D Centre Europe B.V. Cascaded heat pump system with low gwp refrigerant
WO2022266622A3 (en) * 2021-06-16 2023-01-26 Colorado State University Research Foundation Air source heat pump system and method of use for industrial steam generation

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DE102013214891A1 (de) * 2013-07-30 2015-02-05 Siemens Aktiengesellschaft Wärmetechnische Verschaltung einer Geothermiequelle mit einem Fernwärmenetz
DE112015004688T5 (de) * 2014-10-18 2018-01-18 Aerosol Dynamics Inc. Anhaltende Übersättigungen für Kondensationswachstum von Teilchen
EP3421105A4 (en) 2016-02-26 2019-10-30 Sinochem Lantian Co., Ltd. COMPOSITION COMPRISING A KETONE CONTAINING FLUORINE
DE102017011134B4 (de) 2017-12-01 2022-09-08 Emz-Hanauer Gmbh & Co. Kgaa Haushaltskältegerät sowie Verfahren zum Steuern einer in diesem angeordneten Lichtquellenanordnung

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US10662583B2 (en) * 2014-07-29 2020-05-26 Siemens Aktiengesellschaft Industrial plant, paper mill, control device, apparatus and method for drying drying-stock
US10976078B2 (en) 2016-03-14 2021-04-13 Efficient Energy Gmbh Heat pump system comprising two stages, method of operating a heat pump system and method of producing a heat pump system
EP4063762A1 (en) 2021-03-26 2022-09-28 Mitsubishi Electric R&D Centre Europe B.V. Cascaded heat pump system with low gwp refrigerant
WO2022266622A3 (en) * 2021-06-16 2023-01-26 Colorado State University Research Foundation Air source heat pump system and method of use for industrial steam generation

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JP2016526650A (ja) 2016-09-05
KR20180005281A (ko) 2018-01-15
JP6526639B2 (ja) 2019-06-05
WO2014198593A1 (de) 2014-12-18
EP2989395A1 (de) 2016-03-02
CN105264306A (zh) 2016-01-20
CA2915305A1 (en) 2014-12-18
KR20160018795A (ko) 2016-02-17
CA2915305C (en) 2018-04-10
DE102013211087A1 (de) 2015-01-15

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