EP0095439B1 - Installation de pompe à chaleur - Google Patents

Installation de pompe à chaleur Download PDF

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Publication number
EP0095439B1
EP0095439B1 EP83730048A EP83730048A EP0095439B1 EP 0095439 B1 EP0095439 B1 EP 0095439B1 EP 83730048 A EP83730048 A EP 83730048A EP 83730048 A EP83730048 A EP 83730048A EP 0095439 B1 EP0095439 B1 EP 0095439B1
Authority
EP
European Patent Office
Prior art keywords
heat
liquid
pump
consumer
ring pump
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.)
Expired
Application number
EP83730048A
Other languages
German (de)
English (en)
Other versions
EP0095439A3 (en
EP0095439A2 (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
Original Assignee
Siemens AG
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 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 engineering and apparatus 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 cooling 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 a little over 90 ° C in the limit range of their application possibilities and therefore in high-temperature heat pumps with heating temperatures of 100 to 120 ° C.
  • a heat pump system is already known in whose coolant circuit water is used as the refrigerant and in which a liquid ring pump is provided as a compressor for compressing the water vapor.
  • This liquid ring pump is operated with water as a barrier liquid.
  • the effect of such a compressor is, however, very low, since the sealing liquid also evaporates under reduced pressure on the suction side of the compressor and at temperatures above 100 ° C. (US-A4 260 335, corresponds to DE-A-2 754 977).
  • the invention has for its object to design the system so that with it the efficiency Heating temperatures above 100 ° C can also be achieved from previously conventional three-circuit heat pump systems with comparable efficiency.
  • the liquid ring pump is operated with a thermal oil as the sealing liquid and that a heat exchanger is arranged in the circuit of the sealing liquid, the heat emission side of which is in the primary or secondary heat transfer circuit of the heat consumer.
  • a thermal oil is used instead of the previously used sealing liquid in the form of water, 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.
  • water vapor in the overpressure range can be generated with temperatures of 110 to 120 ° C.
  • the water vapor compressed with low 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 vacuum pump
  • Liquid ring pump is used, it is recommended to arrange the heat exchanger of the liquid ring pump between the condenser and the heat consumer to improve the efficiency of the system and to increase the heating temperature of the condensate.
  • 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 that 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 To arrange 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, the cooling water of the internal combustion engine is expediently supplied 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 steam is supplied to the vacuum pump 1 via the steam line 6 and from there, after compression and temperature increase, to 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 is supplied to the evaporator 16 again via the throttle valve 9.
  • 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.
  • 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.

Claims (4)

1. Installation de pompe à chaleur, dans laquelle un collecteur agencé en évaporateur, un condenseur et au moins une installation consommant de la chaleur sont montés dans un circuit frigorifique et dans laquelle le condenseur est constitué par une pompe à anneau liquide de l'eau étant utilisée comme fluide frigorigène, caractérisée en ce que la pompe à anneau liquide (1) fonctionne avec une huile thermique comme liquide de barrage et en ce que dans le circuit du liquide de barrage est monté un échangeur de chaleur (3), dont le côté cédant de la chaleur est situé dans le circuit primaire ou secondaire pour l'agent caloporteur de l'installation consommant de la chaleur (17, 19).
2. Installation de pompe à chaleur suivant la revendication 1, caractérisée en ce qu'une pompe primaire (14) est raccordée au conduit pour la vapeur (13) entre la pompe à anneau liquide (1) et l'installation consommant de la chaleur (8) et en ce qu'une vanne (10), susceptible d'être commandée et destinée à contrôler la quantité de produit condensé dans l'installation consommant de la chaleur, est montée en aval de l'installation consommant de la chaleur (8).
3. Installation de pompe à chaleur suivant la revendication 1, caractérisée en ce que, entre la pompe à anneau liquide (1) et l'installation consommant de la chaleur (19), est monté un condenseur (20) direct de liquide, dont le conduit d'amenée (22) du liquide communique avec la sortie de l'installation consommant de la chaleur.
4. Installation de pompe à chaleur suivant la revendication 2 ou 3, caractérisée en ce que l'échangeur de chaleur (3) est monté entre le condenseur (20) et l'installation consommant de la chaleur (19).
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 EP0095439A2 (fr) 1983-11-30
EP0095439A3 EP0095439A3 (en) 1985-05-22
EP0095439B1 true 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)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60147067A (ja) * 1984-01-10 1985-08-02 協和醗酵工業株式会社 ヒ−トポンプ
DE58902718D1 (de) * 1988-05-30 1992-12-17 Siemens Ag Prozessanlage.
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
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
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
US20070119816A1 (en) * 1998-04-16 2007-05-31 Urquhart Karl J Systems and methods for reclaiming process fluids in a processing environment
EP1702140B1 (fr) * 2003-12-22 2007-08-22 Ecoenergy Patent GmbH Procede de conversion d'energie thermique en energie mecanique par un dispositif de detente basse tension
US20070109912A1 (en) * 2005-04-15 2007-05-17 Urquhart Karl J Liquid ring pumping and reclamation systems in a processing environment
JP5151014B2 (ja) 2005-06-30 2013-02-27 株式会社日立製作所 ヒートポンプ装置及びヒートポンプの運転方法
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

Also Published As

Publication number Publication date
DE3219680A1 (de) 1983-11-24
EP0095439A3 (en) 1985-05-22
EP0095439A2 (fr) 1983-11-30
ATE36401T1 (de) 1988-08-15
DE3377665D1 (en) 1988-09-15
US4580720A (en) 1986-04-08

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