EP0211726B1 - Wärmepumpvorrichtung und eine solche Vorrichtung benutzende thermische Trennungsanlage - Google Patents

Wärmepumpvorrichtung und eine solche Vorrichtung benutzende thermische Trennungsanlage Download PDF

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Publication number
EP0211726B1
EP0211726B1 EP86401532A EP86401532A EP0211726B1 EP 0211726 B1 EP0211726 B1 EP 0211726B1 EP 86401532 A EP86401532 A EP 86401532A EP 86401532 A EP86401532 A EP 86401532A EP 0211726 B1 EP0211726 B1 EP 0211726B1
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EP
European Patent Office
Prior art keywords
transformer
heat pump
driving
heat
compressor
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 - Lifetime
Application number
EP86401532A
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English (en)
French (fr)
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EP0211726A1 (de
Inventor
Luc Muller
Christian Chatelain
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.)
Rodie-Talbere Henri
Electricite de France SA
Original Assignee
Rodie-Talbere Henri
Electricite de France SA
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Application filed by Rodie-Talbere Henri, Electricite de France SA filed Critical Rodie-Talbere Henri
Priority to AT86401532T priority Critical patent/ATE52135T1/de
Publication of EP0211726A1 publication Critical patent/EP0211726A1/de
Application granted granted Critical
Publication of EP0211726B1 publication Critical patent/EP0211726B1/de
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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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure

Definitions

  • the present invention relates to a heat pumping device and to a thermal separation installation using this device.
  • a “heat pump” is understood to mean any thermodynamic system borrowing outside heat at a low level and returning it to a higher level by means of an energy supply.
  • mechanical Depending on the cycle, there are three types of heat pump.
  • open cycle heat pumps in which a mechanical compressor raises the energy level of the fluid from the cold source for its use at the hot source.
  • closed cycle compression heat pumps where an intermediate fluid is used to draw its energy from the fluid of the cold source constituted by an evaporator.
  • the intermediate fluid compressed using a mechanical compressor, yields to the fluid of the hot source formed by a condenser, the energy thus valued, before being recycled to the cold source through an expansion device .
  • closed-cycle resorption and compression heat pumps in which the cold source fluid as well as the hot source fluid exchange with an absorption-absorption machine operating without thermal input, but only with thermal input. 'mechanical energy.
  • thermo - compressors it is known that to raise the pressure of the vaporized fluid, heat pumps describing a Rankine cycle, use various types of compression machine, such as for example dynamic centrifugal or axial compressors, or volumetric compressors, or even thermo - compressors. It is also possible to absorb the vapor in a liquid solvent, the pressure of which will then be raised before desorbing the working fluid from the cycle.
  • thermodynamic systems do not give attractive performances compared to the investment cost, so that it is necessary to adapt the characteristics of the heat pump to conditions of use different from those in his preferred area.
  • Refrigeration installations are known in which a heat pump is coupled to a thermodynamic transformer of the "ejector" type where the exchange is carried out by mixing quantities of movements between a working fluid and a receiving fluid.
  • thermodynamic transformers of the "ejector" type have an average efficiency, so that in certain ranges of use, the heat pump-ejector coupling is incompatible with the compression ratio which it is desired to obtain and results in excessive energy consumption.
  • the invention makes it possible to avoid this drawback by transforming the characteristics of the heat pump to adapt them to conditions of use different from those of its preferred field.
  • Document US Pat. No. 4,313,305 relates to a system for improving the thermal energy efficiency of industrial installations by combining a three-phase heat transformer constituted by an ejector with a heat pump.
  • Document US 4,218,891 relates to an air conditioning device which implements a turbocharger where the outlet of the compressor is interconnected with the inlet of the turbine.
  • the subject of the invention is a heat pumping device of the type described in the preamble of claim 1, the features of which emerge in particular from the characterizing part of the latter.
  • the invention also relates to the application of such a device as indicated in claim 6.
  • FIGS. 1 and 2 several diagrams have been shown, according to the invention, showing different modes of coupling between a heat pump 1 and a thermodynamic transformer 2.
  • the transformer 2 is a thermodynamic system exchanging energy with the outside, for example in the form of heat at at least three distinct levels.
  • the quantity of heat exchanged at the intermediate level is equal and in the opposite direction to the sum of the quantities exchanged at the two extreme levels.
  • the transformer 2 receives a fluid at a level TM and restores this fluid at two levels TH and TB.
  • the heat pump 1 is placed at the level of the output TB of the transformer 2 and raises the temperature of the fluid from the level TB to the level TH for its use at the same time as the fluid exiting directly from the transformer to the TH level, defining a downstream compression system.
  • the heat pump 1 also placed at the level of the output TB of the transformer, raises the temperature of the fluid from the level TB to the level TM to reintroduce it at this level into the transformer, defining a drive system.
  • the heat pump 1 placed as in the case of FIG. 1b is in addition used to raise the temperature of the external fluid arriving at a low temperature, up to the temperature TM of input of the transformer, defining an upstream drive and compression system.
  • the heat pump is placed upstream of the transformer 2.
  • This transformer receives part of the fluid at a temperature level TB, and the other part passes through the heat pump 1 which records its temperature from TB level to TH level before introduction into the transformer.
  • the transformer yields, at an intermediate temperature level TM, an amount of heat equal to the sum of that which it has received, defining an upstream compression system.
  • the heat pump 1 is placed downstream of the transformer and part of the fluid leaving said transformer at the temperature level TM is taken, and passes through the heat pump which raises the temperature of said fluid to the TH level, before its reintroduction into the transformer, defining a drive system.
  • the heat pump 1 is also placed downstream of the transformer and all of the fluid leaving the transformer at the temperature level TM is channeled towards the heat pump 1 which raises its temperature at the level TH. At the outlet of said heat pump, part of the fluid is recycled to the inlet of the transformer at temperature TH and the other part is sent to use, defining a downstream drive and compression system.
  • thermodynamic cycle In a transformer with three energy levels, as used in the examples above, the thermodynamic cycle always comprises two parts traversed in opposite directions, one is “driving”, that is to say that l energy is degraded thereby allowing the system to provide work to the outside, and the second is “receiving”, that is to say that it receives the work provided by the previous one thus allowing to upgrade the level of energy in exchanges with the outside. These two parts of the cycle must be coupled.
  • the internal structure of the tritherm transformer can also have three possible configurations for each of the types A and B indicated above.
  • the flow of the intermediate level can be shared between the driving and receiving part of the transformer, or pass entirely through the driving part of the transformer, or even cross entirely through the receiving part of said transformer.
  • turbocharger is meant a machine constituted either by a dynamic compressor driven by an expansion turbine or a set of two positive displacement machines, one driving, the other receiving, this set having no mechanical connection with external sources d mechanical energy.
  • FIG. 3a shows a turbocharger 30 formed by a dynamic compressor 31 driven by an expansion turbine 32. Upstream of the dynamic compressor 31 is arranged the mechanically driven compressor 10 forming the heat pump. This compressor 10 supplies the suction of the dynamic compressor 31 and the intake of the turbine 32 in parallel. The exhaust of the turbine 32 is connected to the suction of the compressor 10.
  • a flow control element constituted by a rolling valve 5 associated with a deheating device 6 can optionally be placed on the exhaust of the turbine 32 upstream of the compressor 10. This valve 5 can also be placed on the inlet of the turbine 32 or on the suction of the dynamic compressor 31, or even on the supply 11 of the compressor 10.
  • the machine with mechanical drive has a moderate speed of rotation, due to the increased flow rate and the reduced compression rate.
  • the additional compression is ensured by the turbocharger which is a machine without any mechanical transmission link with the outside and therefore providing high speed rotation.
  • the suction of the dynamic compressor 31 is directly supplied by the external fluid and the mechanically driven compressor 10 supplies the intake of the turbine 32. It is also possible to mount a flow control element on the compressor 10 suction.
  • This regulating element can be constituted, for example, by a rolling valve or a door locker in the case of centrifugal compressors.
  • This device can be used in a separation installation for example of the evaporator, crystallizer, distillation column, dryer, steam production, etc. type with closed or open cycle, and in the latter case, there may be coupling. between the hot source and the cold source.
  • the diluted liquor is partly evaporated in an exchanger-evaporator.
  • the two liquid and vapor phases are then separated in a separator.
  • the concentrated liquor is evacuated and the evaporation vapors are then sent to a heat pump which records its pressure level and therefore of saturated temperature, in order to supply the heat which feeds the evaporator.
  • the heating steam is desuperheated before being introduced into the evaporator. After condensation, the steam supplies condensates from which the desuperheating flow rates can be taken.
  • the present invention premet to solve this problem by using an existing compressor to provide this torque. For this, or adapts to the compressor a system which transforms the flow rate-saturation temperature difference of the compressor into a torque imposed by the installation.
  • the diluted ticker 40 is partly evaporated in an exchanger-evaporator E.
  • the two liquid and vapor phases are then separated in a separator S and the concentrated liquor is evacuated to 41.
  • a turbocharger 30 is associated with the compressor 10 in such a way that the assembly behaves like a compressor, except for desuperheating, that is to say that it receives mechanical energy from the compressor 10 and vapor has coming from the separator S, and returns a heating vapor in g to the evaporator E. After condensation, the vapor supplies condensates at 42 from which the desuperheating flow rates can be taken D.
  • the mechanical energy to be used is substantially proportional to the product of the flow at use by the difference in saturated temperature during use Since the irreversibilities of the machines used are fairly low, the mechanical power to be supplied to the compressor 10 is slightly greater than that required by the operating circuit, which means that for a power and a temperature difference given during use, the product flow x saturation temperature difference of the compressor varies little. Consequently, two possibilities arise for adapting a compressor to the use, either to decrease its flow, by increasing its temperature difference, or to increase its flow and decrease its temperature difference.
  • FIG. 4a makes it possible to reduce the flow rate of the compressor 10 by increasing its compression rate.
  • FIGS. 5a and 6a are roughly equivalent in energy consumption and carry out the opposite, that is to say that they increase the flow rate of the compressor 10 by decreasing their compression ratio.
  • FIG. 4a which represents an assembly with upstream drive and compression
  • it is sought to obtain a pressure difference at the level of the compressor 10 greater than that of the installation, and therefore with a lower flow rate.
  • the evaporated vapors a are compressed, one part by the compressor 10 from PB to PH and the other part by the compressor 31 of the turbocharger 30 from PB to PM, as can be seen in the enthalpy diagram corresponding to this coupling ( Figure 4b).
  • the compressor 31 is driven by the turbine 32 which works between PH and PM with the steam supplied by the compressor 10.
  • the two streams of steam leaving the turbocharger 30 are at the same pressure and supply the operating circuit in h after desuperheating D. In this diagram, no desuperheating is necessary in the mechanical compressor 10 and turbocharger device 30.
  • a flow control element 5 can be inserted between the compressor 10 and the turbine 32 of the turbocharger 30.
  • a flow control element 5 can be arranged at the exhaust of the turbine 32 in order to adapt the system to variations in the needs of the installation.
  • the evaporation vapors a are compressed in the compressor of the turbocharger 30 from the pressure PB to the pressure PM (point b on the diagram Figure 6b). These vapors are then mixed at c with the exhaust vapor e from the turbine 31 of the turbocharger and then desuperheated D1 (point d) before being compressed by the mechanical compressor 10 from PM to PH (point g). Part g1 of this steam is then sent to the evaporator E, while the other part g2 supplies the driving steam to the turbine 32 of the turbocharger 30.
  • a flow control element 5 can be inserted in the circuit of the turbine 32.
  • this mode of coupling has the advantage compared to the coupling of FIG. 5a, of obtaining a suction pressure of the mechanical compressor 10 (PM) greater than that of use (PB).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (6)

1. Wärmepumpvorrichtung, die für den Betrieb mit der äußeren Umgebung zwischen zwei Temperaturniveaux bestimmt ist und eine Wärmepumpe (1, 10) für den Betrieb zwischen zwei festliegenden Temperaturniveaus und einen trithermischen thermodynamischen Wandler (2, 30), in dem ein Energiefluß zirkuliert, umfaßt, wobei der Wandler (2, 30) drei Wärmeaustauschstellen auf drei verschiedenen Temperaturniveaus (TB, TM, TH) aufweist und die Wärmepumpe (1, 10) zwischen zwei der drei Wärmeaustauschstellen des Wandlers (2, 30) geschaltet ist, um die Vorrichtung mit einer von derjenigen der Wärmepumpe (1, 10) verschiedenen Temperaturdifferenz zu betreiben, dadurch gekennzeichnet, daß der Wandler (2, 30) von Turboverdichterbauart ist und einen von einem Motorteil (32) angetriebenen Aufnahmeteil (31) aufweist, wobei die Anschlußstellen der Rohrstutzen des Aufnahmeteils und des Motorteils miteinander verbunden sind, um die drei Austauschstellen (TB, TM, TH) derart auszubilden, daß entweder der Einlaß des Aufnahmeteils (31) direkt mit der Einströmöffnung des Motorteils (32) oder der Auslaß des Aufnahmeteils (31) direkt mit dem Auslaß des Motorteils (32) verbunden ist.
2. Vorrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß der thermodynamische Wandler (2, 30) einen Energieflußeingang auf mittlerem Temperaturniveau (TM) und zwei Ausgänge auf hohem und auf niedrigem Temperaturniveau (TH bzw. TB) aufweist, die eine Kopplung mit der Wärmepumpe (1, 10) entsprechend dreier Konfigurationen ermöglichen: mit unterstromiger Kompression, mit Antrieb oder mit Antrieb und oberstromiger Kompression.
3. Vorrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß der thermodynamische Wandler (2, 30) zwei Energieflußeingänge auf hohem und auf niedrigem Temperaturniveau (TH bzw. TB) und einen Ausgang auf mittlerem Temperaturniveau (TM) aufweist, die eine Kopplung mit der Wärmepumpe (1, 10) entsprechend dreier Konfigurationen ermöglichen: mit oberstromiger Kompression, mit Antrieb oder mit Antrieb und unterstromiger Kompression.
4. Vorrichtung gemäß einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß der thermodynamische Wandler (2, 30) je nach Verwendung drei innere Konfigurationen aufweisen kann, damit der Energiefluß auf einem dazwischenliegenden Temperaturniveau entweder aufgeteilt zwischen dem Motorteil (32) und dem Aufnahmeteil (31) des Wandlers den Motorteil (32) und den Aufnahmeteil (31) oder in seiner Gesamtheit den Motorteil (32) oder in seiner Gesamtheit den Aufnahmeteil (31) durchströmt.
5. Vorrichtung gemäß einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Wärmepumpe (1, 10) einen offenen Kreislauf besitzt und einen Kompressor (10) aufweist, der eventuell zu einem Regelsystem (5) und/oder zu einem Heißdampfkühlsystem (6, D1, D2) gehört.
6. Anwendung der Vorrichtung gemäß einem der Ansprüche 1 bis 5 auf eine Anlage zur thermischen Separation mittels Verdampfung, Destillation oder Trocknung.
EP86401532A 1985-07-10 1986-07-09 Wärmepumpvorrichtung und eine solche Vorrichtung benutzende thermische Trennungsanlage Expired - Lifetime EP0211726B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86401532T ATE52135T1 (de) 1985-07-10 1986-07-09 Waermepumpvorrichtung und eine solche vorrichtung benutzende thermische trennungsanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8510591A FR2584801B1 (fr) 1985-07-10 1985-07-10 Dispositif et installation de pompage de chaleur
FR8510591 1985-07-10

Publications (2)

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EP0211726A1 EP0211726A1 (de) 1987-02-25
EP0211726B1 true EP0211726B1 (de) 1990-04-18

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AT (1) ATE52135T1 (de)
DE (1) DE3670530D1 (de)
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120193912A1 (en) * 2009-10-06 2012-08-02 Pdm Solar Inc. Thermal Transformer

Family Cites Families (20)

* Cited by examiner, † Cited by third party
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US2182453A (en) * 1936-01-18 1939-12-05 William H Sellew Heat transfer process and apparatus
DE673984C (de) * 1938-01-12 1939-04-05 Rudolf Fuchs Dipl Ing Kontinuierlich wirkende Absorptionskaeltemaschine
CH244033A (de) * 1944-10-31 1946-08-31 Bbc Brown Boveri & Cie Verfahren zur thermischen Behandlung feuchten Gutes mit Luft und Einrichtung zur Ausübung dieses Verfahrens.
US2513361A (en) * 1944-11-01 1950-07-04 Specialties Dev Corp Method and system for producing low-temperature refrigeration
FR923898A (fr) * 1946-03-16 1947-07-21 Neu Lille Sa Des Ets Procédés et dispositifs utilisant le principe de la pompe de chaleur pour produirechaleur et froid
US2519010A (en) * 1947-08-02 1950-08-15 Philco Corp Refrigeration system and method
GB795109A (en) * 1955-03-23 1958-05-14 Garrett Corp Improvements in or relating to a closed cycle refrigeration system
FR1246733A (fr) * 1957-03-15 1960-11-25 American Mach & Foundry Cycle de puissance de vapeur
US3423293A (en) * 1965-02-04 1969-01-21 Robert B Holden Apparatus for vapor compression distillation of impure water
FR2315068A1 (fr) * 1975-06-16 1977-01-14 Guerin Robert Installation de pompage de chaleur permettant la multiplication de coefficients de performance
US4186060A (en) * 1976-04-28 1980-01-29 Fogel S J Method and apparatus for high volume distillation of liquids
GB1602095A (en) * 1977-07-22 1981-11-04 British Aerospace Air conditioning apparatus in surface vehicles
US4239603A (en) * 1978-02-22 1980-12-16 Dan Egosi Fuel-efficient generation of ejecting steam
US4218891A (en) * 1978-05-22 1980-08-26 Schwartzman Everett H Cooling and heat pump systems and methods
FR2441135A1 (fr) * 1978-11-10 1980-06-06 Armines Transformateur a absorption
US4313305A (en) * 1979-09-18 1982-02-02 Dan Egosi Feedback energy conversion system
DE3040507A1 (de) * 1980-10-28 1982-05-19 Horst 2000 Wedel Gnaß Verfahren fuer die nutzung von waermeenergie mittels hintereinander geschalteter waermepumpen
US4480444A (en) * 1983-05-23 1984-11-06 Alsthom-Atlantique Deep mine cooling system
DE3327752A1 (de) * 1983-08-01 1985-02-14 Interatom Internationale Atomreaktorbau Gmbh, 5060 Bergisch Gladbach Verfahren und vorrichtung zur erhoehung des wirkungsgrades von turbinenprozessen
US4506524A (en) * 1983-08-15 1985-03-26 Schlichtig Ralph C Absorption type heat transfer system functioning as a temperature pressure potential amplifier

Also Published As

Publication number Publication date
FR2584801A1 (fr) 1987-01-16
ATE52135T1 (de) 1990-05-15
FR2584801B1 (fr) 1990-06-15
DE3670530D1 (de) 1990-05-23
EP0211726A1 (de) 1987-02-25

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