EP0095439A2 - Installation de pompe à chaleur - Google Patents

Installation de pompe à chaleur Download PDF

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Publication number
EP0095439A2
EP0095439A2 EP83730048A EP83730048A EP0095439A2 EP 0095439 A2 EP0095439 A2 EP 0095439A2 EP 83730048 A EP83730048 A EP 83730048A EP 83730048 A EP83730048 A EP 83730048A EP 0095439 A2 EP0095439 A2 EP 0095439A2
Authority
EP
European Patent Office
Prior art keywords
heat
consumer
pump
vacuum pump
pump system
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.)
Granted
Application number
EP83730048A
Other languages
German (de)
English (en)
Other versions
EP0095439A3 (en
EP0095439B1 (fr
Inventor
Heinz Ing. Strop (Grad.)
Werner Ing. Kohler (Grad.)
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to AT83730048T priority Critical patent/ATE36401T1/de
Publication of EP0095439A2 publication Critical patent/EP0095439A2/fr
Publication of EP0095439A3 publication Critical patent/EP0095439A3/de
Application granted granted Critical
Publication of EP0095439B1 publication Critical patent/EP0095439B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B3/00—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass
    • F22B3/04—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass by drop in pressure of high-pressure hot water within pressure-reducing chambers, e.g. in accumulators
    • F22B3/045—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass by drop in pressure of high-pressure hot water within pressure-reducing chambers, e.g. in accumulators the drop in pressure being achieved by compressors, e.g. with steam jet 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
    • 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

Definitions

  • the invention is in the field of heat generation by means of heat pumps and is to be used in the system design of a heat pump system.
  • the heat pump systems currently in use generally work with three circuits: a brine circuit on the heat source side, a refrigerant circuit in the compression process and a heating medium circuit on the consumer side. While water is primarily used as the heating medium on the consumer side, fluorocarbons are preferably used in the compression process. However, these are not to be used at temperatures of about 90 ° C in the limit range of their application and therefore in high-temperature heat pumps with heating temperatures of 100 to 120 ° C. Furthermore, at least two heat exchangers are required in the known systems for separating the various circuits (DE-AS 26 26 468).
  • the invention is based on the object of designing the heat pump system in such a way that it works with little equipment outlay with an efficiency comparable to that of the three-circuit heat pump systems and can also be used for the generation of heating temperatures above 90.degree.
  • the compressor when water is used as the refrigerant, the compressor consists of a vacuum pump.
  • the use of water results in the use of a refrigerant whose pressure range is an order of magnitude lower than that of the fluorocarbons normally used. This reduces the safety-related design and the requirements for operating and maintaining the system.
  • the control effort can also be reduced. Since water can be evaporated in the low vacuum range by using negative pressure, the effort for the evaporator and vacuum pump is also kept within narrow limits.
  • a particularly advantageous embodiment of the heat pump system is given when a liquid ring pump with a thermal oil as the sealing liquid is used as the vacuum pump.
  • a heat exchanger can be arranged in the circuit of the sealing liquid and the heat emission side of the heat exchanger can be located in the primary or secondary heat transfer circuit of the heat consumer.
  • liquid ring pump which has been known per se for decades, and which has hitherto been used primarily as a vacuum pump for extracting gases and vapors or as a compressor for compressing gases in the chemical industry (prospectus "Elmo gas pumps” from Siemens AG, July 1964)
  • a proven, low-wear ;;, unit introduced which provides a relatively large volumetric performance with a relatively low pressure increase. It can also work on the pressure side in the temperature range from 100 to 120 ° C.
  • the relatively large power loss of this pump is fed into the heating circuit as additional heating power via the heat exchanger assigned to the sealing liquid.
  • thermal oil is used, which is characterized by a high boiling point and by low viscosity at the intended evaporation temperatures.
  • a suitable thermal oil is sold, for example, by the company BP under the name "Transcal LT".
  • the new heat pump system can be used both in the low temperature range and in the high temperature range.
  • water vapor at temperatures of around 50 to 70 ° C can be generated in the vacuum region.
  • Radiators can be fed directly with the water vapor, whereby the water vapor condenses in the radiator.
  • the system is designed such that a fore-vacuum pump is connected to the steam line between the vacuum pump and the heat consumer and that a controllable valve for controlling the amount of condensate in the heat consumer is connected downstream of the heat consumer.
  • a district heating network with a temperature of about 50 0 C is used as a heat source, for example the reflux, water vapor can be generated over the pressure range at temperatures of 110 to 120 ° C.
  • the water vapor compressed with a slight overpressure can emit its heat directly or indirectly in an open or closed condenser.
  • a system is particularly expedient in which a direct liquid condenser is arranged between the vacuum pump and the heat consumer, the liquid inlet of which is connected to the outlet of the heat consumer. If a liquid ring pump is used as the vacuum pump, it is advisable to improve the efficiency of the system and to increase the heating temperature of the densats to arrange the heat exchanger of the liquid ring pump between the condenser and the heat consumer.
  • the compressed water vapor can also be fed to a heat exchanger, in whose secondary circuit the actual heat consumer lies.
  • a ring pump as a vacuum pump, it is recommended in this case to arrange the heat emission side of the heat exchanger arranged in the circuit of the sealing liquid of the ring pump in the secondary circuit of the heat exchanger.
  • the new heat pump system is particularly suitable for industrial processes in the higher temperature range and can also be used there for cooling and heating purposes. If the vacuum pump is driven by a water-cooled internal combustion engine, mari expediently supplies the cooling water of the internal combustion engine to the heat collector of the heat pump system as an additional heat source. As a result, especially at low temperatures of the heat source in the evaporator, an evaporation pressure can be achieved which is in the working range of the liquid ring pump.
  • Fig. 1 shows the circuit of a heat pump system that works in the low temperature range with water as a refrigerant.
  • a vacuum pump 1 in the form of a liquid ring pump is provided, in the sealing liquid circuit 2 of which the heat exchanger 3 is arranged.
  • a heat collector designed as an evaporator 4 is supplied with water in the temperature range from 0 to 10 ° C., for example river water, via the inlet 5 and evaporated directly or indirectly.
  • the water vapor is supplied to the vacuum pump 1 via the steam line 6 and from there, after compression and an increase in temperature, reaches the heat consumer 8, for example a radiator, via the supply lines 7 and 13.
  • the water vapor condenses in the heat consumer 8, and the condensate level is adjusted with the aid of a valve 10, which can be controlled via a sensor 11 and a control device 12.
  • the condensate is otherwise fed via the throttle valve 9 to the evaporator 4 for re-evaporation or, when using a direct evaporator, drained behind the valve 10.
  • the water used as the heat source leaves the evaporator 4 via the outlet 15.
  • the forevacuum pump 14 is connected to the feed line 13 and constantly maintains the condensation pressure required in this system with respect to the atmosphere.
  • the backing pump also serves to keep the entire system air-free at all times.
  • the return line of a district heating network is supplied to the evaporator 16 via the inlet 5 and leaves the evaporator via the outlet 15.
  • the vacuum pump 1 again designed as a liquid ring pump, generates water vapor in the temperature range from 110 to 120 ° C. which is condensed in the heat exchanger 17 with the aid of a secondary heat transfer circuit and via the throttle valve til 9 is supplied to the evaporator 16 again.
  • the heat exchanger of the liquid ring pump 1 is arranged in the circuit 18 of the secondary heat carrier behind the heat exchanger 17.
  • warm water at temperatures of 50 to 60.degree. C. is likewise supplied to the heat collector designed as an indirect evaporator 16, so that 1 water vapor is generated in the overpressure range with the aid of the liquid ring pump.
  • This water vapor is condensed in the direct liquid condenser 20 connected downstream of the vacuum pump, in that its liquid inflow is connected to the outlet of the heat consumer 19 via the feed line 21.
  • the condensate formed in the condenser 20 is further heated using the heat exchanger 3 of the liquid ring pump 1.
  • the liquid ring pump 1 can be driven by a water-cooled internal combustion engine 23, the water supply to the indirect evaporator 16 being designed such that the cooling water of the internal combustion engine is supplied to the evaporator 16 as an additional heat source.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Central Heating Systems (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
  • Other Air-Conditioning Systems (AREA)
EP83730048A 1982-05-21 1983-05-13 Installation de pompe à chaleur Expired EP0095439B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83730048T ATE36401T1 (de) 1982-05-21 1983-05-13 Waermepumpenanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3219680 1982-05-21
DE19823219680 DE3219680A1 (de) 1982-05-21 1982-05-21 Waermepumpenanlage

Publications (3)

Publication Number Publication Date
EP0095439A2 true EP0095439A2 (fr) 1983-11-30
EP0095439A3 EP0095439A3 (en) 1985-05-22
EP0095439B1 EP0095439B1 (fr) 1988-08-10

Family

ID=6164480

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83730048A Expired EP0095439B1 (fr) 1982-05-21 1983-05-13 Installation de pompe à chaleur

Country Status (4)

Country Link
US (1) US4580720A (fr)
EP (1) EP0095439B1 (fr)
AT (1) ATE36401T1 (fr)
DE (2) DE3219680A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0150014A3 (en) * 1984-01-10 1986-10-08 Kyowa Hakko Kogyo Co., Ltd. Heat pump
WO1989012201A1 (fr) * 1988-05-30 1989-12-14 Siemens Aktiengesellschaft Installation de traitement industriel
EP1762785A2 (fr) 2005-06-30 2007-03-14 Hitachi, Ltd. Système de pompe à chaleur et procédé de fonctionnement de la pompe à chaleur

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IL103824A (en) * 1992-11-20 1996-12-05 Assaf Gad Liquid ring compressor/turbine and air conditioning systems utilizing same
US5636523A (en) * 1992-11-20 1997-06-10 Energy Converters Ltd. Liquid ring compressor/turbine and air conditioning systems utilizing same
US20070119816A1 (en) * 1998-04-16 2007-05-31 Urquhart Karl J Systems and methods for reclaiming process fluids in a processing environment
US7980753B2 (en) 1998-04-16 2011-07-19 Air Liquide Electronics U.S. Lp Systems and methods for managing fluids in a processing environment using a liquid ring pump and reclamation system
US7871249B2 (en) * 1998-04-16 2011-01-18 Air Liquide Electronics U.S. Lp Systems and methods for managing fluids using a liquid ring pump
ES2293384T3 (es) * 2003-12-22 2008-03-16 Ecoenergy Patent Gmbh Procedimiento para la conversion de energia termina en energia mecaniza con un dispositivo de expansion a baja presion.
US20070109912A1 (en) * 2005-04-15 2007-05-17 Urquhart Karl J Liquid ring pumping and reclamation systems in a processing environment
US8235580B2 (en) 2006-10-12 2012-08-07 Air Liquide Electronics U.S. Lp Reclaim function for semiconductor processing systems
NO20120734A1 (no) * 2012-06-25 2013-12-26 Vacuwatt As Varmepumpeanlegg
DE102013211084A1 (de) * 2013-06-14 2014-12-18 Siemens Aktiengesellschaft Verfahren zum Betrieb einer Wärmepumpe und Wärmepumpe
US20160296902A1 (en) 2016-06-17 2016-10-13 Air Liquide Electronics U.S. Lp Deterministic feedback blender
CN107514831A (zh) * 2017-07-20 2017-12-26 卢振华 一种以水为工作物质的热泵及工作方法

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE393061C (de) * 1920-06-12 1924-04-03 Siemens Schuckertwerke G M B H Verfahren zur Erzeugung von Wasserdampf
US1991733A (en) * 1931-12-29 1935-02-19 Foster Wheeler Corp Method and apparatus for cooling liquid
US2256201A (en) * 1937-02-26 1941-09-16 Siemens Ag Refrigerating apparatus of the compression type
US2653012A (en) * 1948-08-12 1953-09-22 Charles J Thatcher Method and system for air conditioning
DE955718C (de) * 1950-12-13 1957-01-10 Helmuth Speyerer Dr Ing Verfahren zum Betreiben einer Waermepumpe mit stufenweiser Entspannung und Absaugung
CH342583A (de) * 1956-06-21 1959-11-30 Rawyler Ernst Nach dem Prinzip der Wärmepumpe arbeitende Dampferzeugungsanlage
FR2305588A2 (fr) * 1975-03-28 1976-10-22 Technip Cie Procedes pour la production, le stockage et la distribution d'energies
US3940058A (en) * 1974-10-07 1976-02-24 Norris Orlin R Steam generating system including means for reinitiating the operation of a steam bound boiler feed pump
FR2371638A1 (fr) * 1976-11-19 1978-06-16 Lezier Gerard Installation de chauffage comportant une pompe a chaleur
FR2374539A1 (fr) * 1976-12-15 1978-07-13 Air Ind Procede de compression de vapeur d'eau, et circuits thermiques pour sa mise en oeuvre
US4282070A (en) * 1978-05-30 1981-08-04 Dan Egosi Energy conversion method with water recovery
DE2841906C2 (de) * 1978-09-26 1980-02-21 Siemens Ag, 1000 Berlin Und 8000 Muenchen Flüssigkeitsringverdichter oder -vakuumpumpe
FR2480864A1 (fr) * 1980-04-18 1981-10-23 Bernier Jean Paul Chauffe-eau solaire et pompes fluidiques polythermes a volume total constant
FR2492068B1 (fr) * 1980-10-13 1985-08-16 Entropie Sa Procede et installation de pompe a chaleur par ejectocompression pour le chauffage de l'eau

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0150014A3 (en) * 1984-01-10 1986-10-08 Kyowa Hakko Kogyo Co., Ltd. Heat pump
WO1989012201A1 (fr) * 1988-05-30 1989-12-14 Siemens Aktiengesellschaft Installation de traitement industriel
US5169502A (en) * 1988-05-30 1992-12-08 Siemens Aktiengesellschaft Installation for processing liquids
EP1762785A2 (fr) 2005-06-30 2007-03-14 Hitachi, Ltd. Système de pompe à chaleur et procédé de fonctionnement de la pompe à chaleur
EP1762785A3 (fr) * 2005-06-30 2007-03-21 Hitachi, Ltd. Système de pompe à chaleur et procédé de fonctionnement de la pompe à chaleur
US7861548B2 (en) 2005-06-30 2011-01-04 Hitachi, Ltd. Heat pump system and heat pump operation method
US7966840B2 (en) 2005-06-30 2011-06-28 Hitachi, Ltd. Heat pump system and heat pump operation method

Also Published As

Publication number Publication date
US4580720A (en) 1986-04-08
EP0095439A3 (en) 1985-05-22
ATE36401T1 (de) 1988-08-15
DE3377665D1 (en) 1988-09-15
DE3219680A1 (de) 1983-11-24
EP0095439B1 (fr) 1988-08-10

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