EP0041911A2 - Wärmepumpen - Google Patents

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Publication number
EP0041911A2
EP0041911A2 EP81420089A EP81420089A EP0041911A2 EP 0041911 A2 EP0041911 A2 EP 0041911A2 EP 81420089 A EP81420089 A EP 81420089A EP 81420089 A EP81420089 A EP 81420089A EP 0041911 A2 EP0041911 A2 EP 0041911A2
Authority
EP
European Patent Office
Prior art keywords
group
motor
compressor
evaporators
heat
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
EP81420089A
Other languages
English (en)
French (fr)
Other versions
EP0041911B1 (de
EP0041911A3 (en
Inventor
Robert Meric
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.)
Helpac Applications Thermodynamiques Et Solaires SA
Original Assignee
Helpac Applications Thermodynamiques Et Solaires SA
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 Helpac Applications Thermodynamiques Et Solaires SA filed Critical Helpac Applications Thermodynamiques Et Solaires SA
Priority to AT81420089T priority Critical patent/ATE10028T1/de
Publication of EP0041911A2 publication Critical patent/EP0041911A2/de
Publication of EP0041911A3 publication Critical patent/EP0041911A3/fr
Application granted granted Critical
Publication of EP0041911B1 publication Critical patent/EP0041911B1/de
Expired 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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • F25D21/12—Removing frost by hot-fluid circulating system separate from the refrigerant system
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
    • F25D2317/0684—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans the fans allowing rotation in reverse direction

Definitions

  • heat pumps are called reverse operating heat pumps, that is to say to which mechanical power is supplied to obtain heat.
  • these machines operate according to the Carnot cycle, their action is twofold, namely that on the one hand they transform mechanical power into heat, but on the other hand they take heat from a cold source for the transfer to a hot source, that is, they raise the temperature level of the heat thus transferred, which explains the name they were given.
  • the heat taken from the cold source is free, if the temperature difference between it and the hot source is not too high and if the mechanical efficiency of the machine considered is good, we can thus arrive at have at the hot source a quantity of heat much greater than that which would result from the direct transformation into thermal energy of the mechanical energy applied to this machine.
  • water from a river or a lake it is advantageously used to constitute the external fluid for supplying calories to the cold source, but this is rare in practice.
  • the usual heat pumps are therefore generally designed to use atmospheric air for this purpose.
  • the cold source of a conventional heat pump is in practice constituted by a heat exchanger or "evaporator" in which a suitable heat transfer fluid (freon in general) evaporates by absorbing the heat of the external fluid used (water or air) which obviously cools down.
  • a suitable heat transfer fluid frreon in general
  • this cooling can lead to a phenomenon of condensation.
  • the surface of the evaporator exposed to the air remains above 0 ° C, the water thus condensed flows and can be removed without difficulty. But below this limit, there is icing.
  • frost which isolates it by considerably reducing the exchange coefficient and consequently lowering the vaporization temperature of the heat transfer fluid, which in turn decreases the performance of the machine.
  • frost more or less obstructs the passage of the air flow, thus acting in the same unfavorable direction as the insulation of the evaporator. It is therefore essential to carry out a defrosting operation from time to time, taking care that the energy expended does not reduce the final energy balance too significantly.
  • the invention aims to remedy these drawbacks and to make it possible to reduce icing while ensuring the melting of residual frost, without additional energy consumption, or at the very least by reducing such consumption as much as possible.
  • the pump comprises two elementary pumps, the evaporators of which are arranged in series on the same air stream, while on the one hand means are provided for circulating this air at will in one direction or in the other, on the other hand, means which, when the evaporator which is located downstream on the air stream is covered with frost or ice, stop the corresponding motor-compressor group, reverse the direction of flow of said draft, then, when the evaporator of the group thus stopped is defrosted, restart this group without changing the direction of air circulation.
  • the double heat pump shown in the drawing comprises two motor-compressor groups 1a, 1b each constituted by a compressor proper 2a, 2b and by an electric drive motor 3a, 3b, controlled by an appropriate contactor 4a, 4b with actuation electric inserted on a supply line 5a, 5b, for example three-phase.
  • Each group expels the heat transfer fluid, which we will assume to be a freon to fix the ideas, by a pipe 6a, 6b, in one of the elements 7a, 7b of a double condenser 8 forming a heat exchanger between the freon and the water which arrives through the line 9 to exit through another line 10 after having absorbed the heat of condensation from the two elements 7a, 7b.
  • these two elements consist of coils arranged inside the same water chamber 11. Means must be provided so that these two coils or others are in the same conditions heat exchange with water, which we very roughly schematized by arranging the outlet of the channeling of the room. In practice, it is possible to use flat coils with overlapping turns, or else to provide a large number of deflecting partitions so that the water circulates in multiple zigzags in contact with the two elements such as 7a, 7b.
  • the liquid freon under pressure leaving each of the elements 7a, 7b is brought by a line 12a, 12b to a pressure reducer 13a, 13b from which it arrives under reduced pressure by a line 14a, 14b to an evaporator 15a, 15b arranged so that a stream of reheating air can pass through it.
  • evaporators can for example be produced for this purpose in the form of a flat leaf or a tubular bundle joining an inlet body to an outlet body.
  • the two evaporators 15, 15b are arranged at one and at the other end of a sort of tubular box 16 inside which is provided a reversible fan 17 controlled by a motor 18 supplied by a line 19, by three-phase example, on which is interposed an electrically operated inverter 20.
  • box 16 must be of circular section in the plane of the fan 17, but nothing prevents this section from gradually passing to a square or rectangular shape towards each end to facilitate the production of the evaporators.
  • the freon vaporized in the evaporators 15a, 15b is brought back to the compressors 2a, 2b by individual pipes 21a, 21b.
  • the evaporators 15a, 15b are associated with individual icing detectors 22a, 22b established in the form of electrical transducers, of known type, which send their signals by lines 23a, 23b to a microprocessor 24.
  • the latter has three outputs, namely a first 25 which leads to the inverter 20 and two others 26a, 26b connected to the respective contactors 4a, and 4b.
  • the two groups 1a and 1b operate simultaneously, the fan 17 rotating in any direction, for example to determine a current of air following the arrows 27.
  • the outside air causing a temperature tl passes through the evaporator 15a to which it gives up heat while cooling itself; it leaves it at a temperature t2 and, if we neglect the heat given off by the fan motor 17-18, it arrives at this same temperature at the evaporator 15b.
  • the outlet temperature t3 is significantly higher than 0 ° C and any risk of icing is excluded.
  • the machine then operates as a double pump with the small difference that the half which corresponds to compressor 2b works with an evaporator temperature slightly lower than that of the other, which implies a slightly lower coefficient of performance. But if the air flow passing through the evaporators 15a, 15b, has a sufficient flow, this difference is practically negligible.
  • tl While remaining above 0 ° C, is below a certain limit (for example 5 ° C), t3 lowers below 0 ° C and therefore, unless the air is particularly dry, the risk of icing appears for evaporator 15b. Its heat exchange coefficient then tends to decrease, the resistance it opposes to the passage of air to increase and the performance coefficient of the machine to decrease. But as soon as the icing layer has reached a notable thickness, the detector 22b operates and alerts the microprocessor 24. The latter is programmed so as to then reverse the fan 17-18 by the inverter 20 and to stop the group lb by contactor 4b.
  • a certain limit for example 5 ° C
  • the detector 22b As soon as the detector 22b has detected the disappearance of the frost, it sends a signal to the microprocessor 24 which restarts the group lb without re-inverting the fan 17-18. We thus return roughly to the initial operating conditions, with the difference however that the air flow is reversed and that it is therefore the evaporator 15a which receives the air at temperature t2 and which carries the risk. icing.
  • the detector 22a comes into play and it alerts the microprocessor which stops the group la and reverses the fan 17-18. There is again defrosting and when this is finished, the microprocessor 24 restarts the group 1a, thus bringing the whole assembly back exactly to the initial conditions without any exception.
  • the machine therefore operates without stopping, without the intervention of additional energy to ensure defrosting, with only relatively short periods during which one of the groups is stopped, the power being momentarily reduced by half.
  • the microprocessor 24 can be programmed to initiate such defrosting operations itself and to monitor their execution thanks to the detectors 22a, 22b which continuously send them their information.
  • Fig. 2 indicates in partial view an embodiment in which two separate condensers 8a, 8b are used, each comprising an element or coil 7a, 7b traversed by the freon and a water chamber lla, llb, these two chambers being mounted in parallel between the pipes 9 and 10, but with the interposition of electromagnetic valves 29a, 29b whose control inputs are connected to the output lines 26a, 26b of the microprocessor 24.
  • the arrangement is such that when a group, such as for example that Ib (fig. 1), is stopped by the microprocessor 24, the corresponding valve, such as 29b, is closed. It follows that during the operation of a single group, only the corresponding elementary condenser intervenes (ie 8a in the aforementioned example).
  • the outlet temperature is lower than during the operation of the two groups with half-flow in each elementary condenser.
  • the coefficient of performance of the group alone in operation (group la) is thus improved, which partially compensates for the stoppage of the other group (lb).
  • the invention is applicable to the case where the external cold source fluid consists of water at a temperature low enough that there is a risk of ice forming on the evaporators. It also applies to pumps which do not use the phenomenon of liquefaction and evaporation of the internal heat transfer fluid by implementing the compression and expansion of a non-liquefiable gas at the temperatures in question at the hot source.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Defrosting Systems (AREA)
  • Air Conditioning Control Device (AREA)
  • Central Heating Systems (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Reciprocating Pumps (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP81420089A 1980-06-06 1981-06-04 Wärmepumpen Expired EP0041911B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81420089T ATE10028T1 (de) 1980-06-06 1981-06-04 Waermepumpen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8013026 1980-06-06
FR8013026A FR2484065A1 (fr) 1980-06-06 1980-06-06 Perfectionnements aux pompes a chaleur

Publications (3)

Publication Number Publication Date
EP0041911A2 true EP0041911A2 (de) 1981-12-16
EP0041911A3 EP0041911A3 (en) 1982-12-08
EP0041911B1 EP0041911B1 (de) 1984-10-24

Family

ID=9242988

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81420089A Expired EP0041911B1 (de) 1980-06-06 1981-06-04 Wärmepumpen

Country Status (4)

Country Link
EP (1) EP0041911B1 (de)
AT (1) ATE10028T1 (de)
DE (1) DE3166799D1 (de)
FR (1) FR2484065A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0104306A1 (de) * 1982-09-28 1984-04-04 Siemens Aktiengesellschaft Österreich Wärmepumpe
WO1986000977A1 (en) * 1984-07-24 1986-02-13 Conry Ronald D Modular refrigeration system
GB2183320A (en) * 1985-11-08 1987-06-03 Gossler Ewald Method and device for cooling gases
DE102006024871B4 (de) * 2006-05-24 2019-08-08 ait-deutschland GmbH Verfahren zum Abtauen des Verdampfers eines Wärmepumpenheizsystems

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR792390A (fr) * 1935-07-12 1935-12-30 Delas Mode de chauffage et de réfrigération des locaux au moyen de pompes de chaleur
CH182171A (de) * 1935-06-15 1936-01-31 Sulzer Ag Luftkühler.
US2062054A (en) * 1935-04-26 1936-11-24 Westinghouse Electric & Mfg Co Air conditioning apparatus
FR808335A (fr) * 1935-06-18 1937-02-03 Thomson Houston Comp Francaise Systèmes de
US2336549A (en) * 1941-11-28 1943-12-14 Clemeral Motors Corp Refrigerating apparatus
US2522484A (en) * 1948-10-04 1950-09-12 Trane Co Method of and apparatus for conditioning air
US2692481A (en) * 1951-03-16 1954-10-26 Gen Motors Corp Dual evaporator air cooling apparatus
US2763132A (en) * 1953-08-31 1956-09-18 Lawrence S Jue Dehumidifying apparatus
DE2612997A1 (de) * 1975-03-27 1976-10-07 Electricite & Isolation Elise Verfahren zum aufheizen oder abkuehlen eines raumes unter anwendung eines thermodynamischen kreisprozesses und vorrichtung zur durchfuehrung des verfahrens
FR2305699A1 (fr) * 1975-03-28 1976-10-22 Aznavorian Arachin Perfectionnement aux installations susceptibles de fonctionner en pompe de chaleur
FR2328163A1 (fr) * 1975-10-16 1977-05-13 Chauffe Cie Gle Perfectionnements aux dispositifs de chauffage des locaux par l'utilisation de pompes a chaleur
FR2378482A1 (fr) * 1977-02-01 1978-08-25 Electrolux Ab Procede et dispositif de degivrage d'un meuble-presentoir
EP0027604A2 (de) * 1979-10-22 1981-04-29 Carrier Corporation Kühleinrichtung mit zwei Kältekreisläufen

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2698524A (en) * 1949-04-14 1955-01-04 Rygard Sune Ossian Heat transfer between two media according to the carnot principle
FR2305694A1 (fr) * 1975-03-27 1976-10-22 Villaume Michel Procede et dispositif utilisant des machines a cycle thermodynamique pour le chauffage ou la refrigeration d'un local

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2062054A (en) * 1935-04-26 1936-11-24 Westinghouse Electric & Mfg Co Air conditioning apparatus
CH182171A (de) * 1935-06-15 1936-01-31 Sulzer Ag Luftkühler.
FR808335A (fr) * 1935-06-18 1937-02-03 Thomson Houston Comp Francaise Systèmes de
FR792390A (fr) * 1935-07-12 1935-12-30 Delas Mode de chauffage et de réfrigération des locaux au moyen de pompes de chaleur
US2336549A (en) * 1941-11-28 1943-12-14 Clemeral Motors Corp Refrigerating apparatus
US2522484A (en) * 1948-10-04 1950-09-12 Trane Co Method of and apparatus for conditioning air
US2692481A (en) * 1951-03-16 1954-10-26 Gen Motors Corp Dual evaporator air cooling apparatus
US2763132A (en) * 1953-08-31 1956-09-18 Lawrence S Jue Dehumidifying apparatus
DE2612997A1 (de) * 1975-03-27 1976-10-07 Electricite & Isolation Elise Verfahren zum aufheizen oder abkuehlen eines raumes unter anwendung eines thermodynamischen kreisprozesses und vorrichtung zur durchfuehrung des verfahrens
FR2305699A1 (fr) * 1975-03-28 1976-10-22 Aznavorian Arachin Perfectionnement aux installations susceptibles de fonctionner en pompe de chaleur
FR2328163A1 (fr) * 1975-10-16 1977-05-13 Chauffe Cie Gle Perfectionnements aux dispositifs de chauffage des locaux par l'utilisation de pompes a chaleur
FR2378482A1 (fr) * 1977-02-01 1978-08-25 Electrolux Ab Procede et dispositif de degivrage d'un meuble-presentoir
EP0027604A2 (de) * 1979-10-22 1981-04-29 Carrier Corporation Kühleinrichtung mit zwei Kältekreisläufen

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0104306A1 (de) * 1982-09-28 1984-04-04 Siemens Aktiengesellschaft Österreich Wärmepumpe
WO1986000977A1 (en) * 1984-07-24 1986-02-13 Conry Ronald D Modular refrigeration system
GB2183320A (en) * 1985-11-08 1987-06-03 Gossler Ewald Method and device for cooling gases
GB2183320B (en) * 1985-11-08 1990-07-11 Ewald Gossler Method and device for compression of gases
DE102006024871B4 (de) * 2006-05-24 2019-08-08 ait-deutschland GmbH Verfahren zum Abtauen des Verdampfers eines Wärmepumpenheizsystems

Also Published As

Publication number Publication date
FR2484065A1 (fr) 1981-12-11
FR2484065B1 (de) 1984-02-03
EP0041911B1 (de) 1984-10-24
ATE10028T1 (de) 1984-11-15
DE3166799D1 (en) 1984-11-29
EP0041911A3 (en) 1982-12-08

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