EP2739918B1 - System und verfahren zur optimierung des betriebs eines wärmepumpensystems - Google Patents

System und verfahren zur optimierung des betriebs eines wärmepumpensystems Download PDF

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Publication number
EP2739918B1
EP2739918B1 EP12759659.1A EP12759659A EP2739918B1 EP 2739918 B1 EP2739918 B1 EP 2739918B1 EP 12759659 A EP12759659 A EP 12759659A EP 2739918 B1 EP2739918 B1 EP 2739918B1
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EP
European Patent Office
Prior art keywords
cycle fluid
evaporator
exchanger
exchanger system
installation
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EP12759659.1A
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English (en)
French (fr)
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EP2739918A1 (de
Inventor
Fernando RAMOS
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PrestiClim
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PrestiClim
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    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • F25B2347/021—Alternate defrosting
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • the present invention relates to the field of heat pumps.
  • the invention more particularly relates to a method for optimizing the operation of a heat pump installation, in which the cycle fluid undercooled by the defrosting of a heat exchanger makes it possible to improve the efficiency of the installation.
  • the invention also relates to an improved performance heat pump installation operating continuously.
  • a heat pump captures thermal energy from an external environment or more generally from a source of heat called a cold source to restore it in a heating circuit, water circulating in this circuit , usually inside a building.
  • a heat pump conventionally comprises a compressor, a condenser for supplying heat, an expander preparing the vaporization reaction by lowering the liquid pressure (to provide a low pressure liquid to the evaporator) and an evaporator.
  • the evaporator generally consists of a heat exchanger in which the liquid refrigerant is vaporized by the heat extracted from the cold source.
  • the coefficient of performance COP of a heat pump is defined as the ratio between the heat output delivered at the condenser and the work supplied. This work corresponds to the electric power consumed by the engine to move the compression system, also called "power absorbed".
  • the coefficient of performance is often much lower than 3 for heat pumps operating in environments where the outside temperature is for example below 0 ° C. For a long time, there has been a need to increase the coefficient of performance of heat pumps.
  • the present invention therefore aims to overcome one or more of the disadvantages of the prior art by proposing a heat pump installation recovering a maximum of energy so as to increase its coefficient of performance, and providing heat continuously all defrosting part of the installation when necessary.
  • the operating mode of the installation depends on the outside temperature, measured by thermometric measurement means controlled by a processor and software, actuating the control means according to the mode required for the corresponding outside temperature.
  • the installation is designed to operate in different modes depending on the outside temperature, to ensure in all cases a continuous return of heat in the heating circuit.
  • each exchanger in operation can receive a lateral air flow which will instantly cool in the area corresponding to the inlet and outlet sides of the air flow, on which there is the pipe of the evaporator in which circulates the cycle fluid.
  • the zone in the center of the exchanger system heats and defrosts the zone by taking calories from the circulating fluid in the channel of the exchange zone.
  • the second heat exchange zone surrounding the first heat exchange zone of each exchanger system, is of the finned tube type.
  • each exchanger system comprises a radiator including the two exchange zones.
  • each of said exchange zones extends over the entire height of a volume occupied by each exchange system.
  • a further object of the invention is to provide a method of optimizing the operation of a heat pump installation, with improved efficiency and continuous heat exchange.
  • the method comprises a step of simultaneous operation, the means of derivation of the cycle fluid flow being open and the control means being closed, allowing the heating of the cycle fluid in the two evaporators simultaneously.
  • the method comprises a step of switching from one mode of operation to another when the external temperature, measured using at least one thermometric sensor, crosses a threshold value.
  • the method comprises a step of subcooling the cycle fluid and defrosting the exchanger systems only performed with the heat pump system heat exchanger systems, without interrupting the upstream stage of cooling the fluid. cycle in the condenser.
  • the cycle fluid is brought to a supercritical state in a part of the circuit.
  • the latter is located under conditions of pressure and temperature such that there is coexistence of the liquid and gaseous phases.
  • the warming of the cycle fluid in the evaporator will cause a gain of enthalpy at constant pressure and induce a gradual transition to the gaseous state of the cycle fluid.
  • the method comprises a step of air circulation at the level of the exchanger systems reaching a speed of at least 2 m / s.
  • the process comprises an evaporation step in the exchange zone which fulfills the evaporator function carried out at a maximum temperature of between -10 ° C. and -20 ° C.
  • the heat pump installation operates from a cold source (A).
  • the installation conventionally comprising a circuit provided with at least one compressor (1), a condenser (2), at least two expander (3, 3 ') of at least two evaporators (4, 4') and at least two fans (5, 5 ').
  • the cycle fluid circulating in the circuit may for example be a refrigerant known per se (refrigerant R134a, R22 or other similar fluid), may or may not be brought to a supercritical state.
  • the condenser (2) is cooled by a fluid to be heated.
  • the installation comprises at least two systems (12, 12 ') exchangers with the cycle fluid, each having a first zone (Z1, Z1') for heat exchange for cooling the cycle fluid and a second zone (Z2, Z2 ') for heat exchange surrounding the first (Z1, Z1') and for heating the cycle fluid.
  • the second zone (Z2, Z2 ' ) corresponds to the evaporator (4, 4 ') of the circuit.
  • bladed fans (5, 5 ') placed next to the exchanger systems (12, 12') generate a flow, for example circular or helical, passing right through the second exchange zone (Z2, Z2 ') before exit the box enclosing the fan-system exchanger assembly (5, 5 ', 12, 12').
  • the figure 4 shows a positioning of the fans (5, 5 ') at the side portions of a box (50) enclosing the components (1, 2, 12, 12', 3, 3 ', 4, 4') of the pump heat.
  • Said casing ( fig 4 , 50) is provided with downward openings (51, 51 ') and below (52, 52') of the evaporators (4, 4 ') so that the air flow generated by the operation of the fans ( 5, 5 ') and passing right through the second exchange zone (S2, Z2') of the exchanger systems (12, 12 '), enters and out of the bottom of the box (50).
  • the semi-enclosed space (53, 53 ') formed by the box and existing between each fan (5, 5 ') adjacent to an evaporator (4, 4') and the inner wall of the box (50) facing each fan (5, 5 '), allows when a fan (5, 5') ) is stopped to maintain the warm air heated by the cycle fluid in the top of the box (50), the density of the hot air is lower than that of the cold air, thus promotes the defrosting of the evaporator (4, 4 ') adjacent to the fan (5, 5') when stopped.
  • the exchanger systems (12, 12 ') consist of two disjoint zones (Z1 and Z1', Z2 and Z2 ') of exchange, in which the cycle fluid circulates. While the first zone (Z1, Z1 ') of exchange, upstream of the expander (3, 3') in the direction of circulation, is traversed by the cycle fluid so as to heat the system (12, 12 ') exchanger, the second zone (Z2, Z2 ') is crossed downstream of the expander (3, 3') so that the evaporator (4, 4 ') heats the cycle fluid by extracting heat from the source cold (A).
  • the supply of the evaporator (4, 4') after the outlet of the expander (3, 3 ') can be carried out with a distributor (E2, E2 ').
  • a distributor E2, E2 '
  • several circuits of the second exchange zone (Z2, Z2 ') are fed in parallel.
  • the first zone (Z1, Z1 ') constitutes a liquid / air exchanger.
  • the system (12, 12 ') exchanger may comprise parallel fins aligned along an axis. These fins may be spaced apart by 3.2 mm or any other conventional gap.
  • This system (12, 12 ') is distributed between a first side, common to a plurality of fins, of said second zone (Z2, Z2') which receives the flow of air entering the system (12, 12 ') exchanger in a component direction perpendicular to the axis of alignment of the fins or parallel to the fins, and a second common side to the same plurality of fins which is opposite the first side to bring out said air flow of the system ( 12, 12 ') exchanger.
  • the pipe (21, 22) for receiving heat from the outgoing air flow forms all or part of the evaporator (4, 4 ') of the circuit and is positioned on either side of the sides of the system ( 12, 12 ') exchanger.
  • the relative humidity percentage of the air flow used can be 90%.
  • the air circulation is carried out with a speed of between 1 and 2.5 m / s, for an inlet face in the exchanger system (12, 12 ') having an area of the order of 0.1 of 5 m 2 and even more.
  • the flow can also reach 15m 3 / s and even more for applications to industrial buildings.
  • the exchanger system (12, 12 ') may also be free of fins and essentially comprise a smooth tube of stainless material, which makes it suitable for use in corrosive or charged atmospheres.
  • the temperature of the cycle fluid (liquid) is 65 ° at the inlet (E1, E1 ') of a heat exchanger system (12, 12'), the condensation temperature being 67 ° C.
  • the cycle fluid leaving the first zone (Z1, Z1 ') is cooled to a temperature of 8 ° C and is led via the outlet (S1, S1') to the expander (3, 3 ').
  • each exchanger system (12, 12 ') may have a substantially constant height (h).
  • the air flow passes through a complete surface of this generally parallelepipedal volume, entering through the second zone (Z2, Z2 ') of exchange, that is to say by the first side.
  • the height (h) is preferably greater than the depth (d) of the exchanger system (12, 12 '). This depth can be constant and of the order of 0.1 to 0.2 m while the surface of the inlet face of the air flow can correspond to 1 m 2 and more.
  • the exchanger systems (12, 12 ') can advantageously be positioned vertically, as illustrated in FIG. 1.
  • each of the exchange zones (Z1 and Z1', Z2 and Z2 ') extends over the entire height (h) of the volume occupied by the exchanger system (12, 12 ').
  • the thickness of the second exchange zone (Z2, Z2 ') where the evaporator (4, 4') is located may be comparable to or at least three times the thickness of the first zone (Z1, Z1 ') exchange. With reference to the figure 3 There are four rows for the exchange made in the evaporator (4, 4 ') and a single row for the exchange of subcooling. The thickness of said second zone (Z2, Z2 ') is therefore much greater in this case than the thickness of the first exchange zone (Z1, Z1').
  • the size of the exchanger system (12, 12 ') including the two zones (Z1 and Z1', Z2 and Z2 ') is variable as a function of the powers envisaged.
  • the total thickness of the exchange surface can be 180 mm for 5 rows: 4 rows for the evaporator (4, 4 ') and 1 row for the zone (Z1, Z1') forming the subcooler and the defroster.
  • the pumping of calories to the cycle fluid in the second exchange zone (Z2, Z2 ') requires a surplus of thickness with respect to the calorie release operation performed in the zone (Z1, Z1') of -cooling.
  • the size of the system (12, 12 ') exchanger of the figure 1 is 1000 x 1000 x 150. It should be noted here that this type of dimensioning with joining according to the largest section (1 m 2 in this case) of the subcooler of the exchanger (12, 12 ') against the evaporator (4, 4 ') optimizes defrosting.
  • the circuit splits into at least two pipes (21, 22) at the outlet of the condenser (2), each of the pipes (21, 22) being connected to the inlet (E1, E1 ') of the first zone (Z1, Z1 ') of an exchanger system (12, 12').
  • a control system (6, 6') of the circulation of the cycle fluid for example a solenoid valve, driven for example by software on the basis of temporal data and data collected by example using temperature sensors.
  • the regulators (3, 3 ') and the control systems (6, 6') are external to the exchanger systems (12, 12 ').
  • the pipes (21, 22) divide upstream of the inlet into the first exchange zone (Z1, Z1 ') and merge downstream of the control means (6, 6'), creating a bypass to prevent the circulation of the cycle fluid in the first zone (Z1, Z1 ') of exchange.
  • the circulation of the cycle fluid in these branch circuits is controlled by bypass means (7, 7 '), which may be of the same type as the control means (6, 6').
  • the inlet (E2, E2 ') and / or the outlet (S2, S2') of the evaporators can be placed at the same height level as the input (E1, E1 ') or the output (S1, S1') of the circuit part upstream of the regulators (3, 3 ') placed in the first zone (Z1, Z1 ') exchange.
  • the cooling of the cycle fluid upstream of the expander (3, 3 ') results in subcooling with respect to a normal cycle (C1).
  • the cycle (C2) obtained thus makes it possible to start the expansion with a fluid of less enthalpy.
  • the effect of this subcooling is to obtain at the end of expansion (isenthalpic) an increase in the liquid level for the cycle fluid arriving in the evaporator (4, 4 '). Therefore, the capacity of the evaporator (4, 4 ') can be improved.
  • the exchanger system (12, 12 ') may comprise a radiator including the two exchange zones (Z1 and Z1', Z2 and Z2 ').
  • one of the control systems for example the second (6 ') is closed, thus preventing the circulation of the cycle fluid in the first zone (Z1') of the second system (12 ') exchanger, while the first system of control (6) is open.
  • the cycle fluid is thus directed by the inlet (E1) in the first exchange zone (Z1) of the first exchanger system (12).
  • the subcooled cycle fluid then exits the first zone (Z1) of the first exchanger system (12), goes from the outlet (S1) to the expander (3 ') and then enters the second zone (Z2'). exchange of the second system (12 ') exchanger, thus allowing the cycle fluid to extract the heat from the cold source (A) (the fan (5') operates and allows the circulation of air) and to heat up at the level of the evaporator (4 ').
  • the cycle fluid then flows from the outlet (S2 ') of the second zone (Z2') of the second system (12 ') exchanger to the compressor (1), then from the compressor (1) to the condenser (2) where it is cooled.
  • the state of the control systems (6, 6 ') is reversed, ie the first control system (6) is closed and prevents circulation of the cycle fluid while the second (6') is open and allows circulation of the cycle fluid.
  • the cycle fluid is thus directed to the inlet (E1 ') of the first zone (Z1') of the second exchanger system (12 '), where it will be sub-cooled while de-icing the second exchanger system (12').
  • the fan (5 ') is stopped, stopping the circulation of air at the system (12') exchanger, the hot air heated by the remaining cycle fluid more trapped in the box (50) near the exchanger (12 ') and the fan (5') at a standstill, favoring the defrosting of the evaporator (4 ') adjacent to the fan (5') at standstill.
  • the sub-cooled cycle fluid then flows from the outlet (S1 ') of the first zone (Z1') of the second system (12 ') exchanger to the expander (3), before entering the second zone (Z2) for exchanging the first exchanger system, where it is cooled at the level of the evaporator (4), the fan (5) operating and allowing the circulation of air and the heat exchange between the cycle fluid and the cold source (AT).
  • the cycle fluid is then directs the output (S2) of the second zone (Z2) of the first system (12) exchanger to the compressor (1), then the compressor (1) to the condenser (2) where it is cooled.
  • T ' the state of the control systems (6, 6') is reversed again to de-ice again the first system (12) exchanger.
  • This alternation of the state of the control means (6, 6 ') which is carried out for example by means of a timer, continues as long as the temperature of the outside air is below a threshold value, for example 7 ° C, this temperature being measured for example by means of a thermometric sensor.
  • the bypass means (7, 7 ') are closed.
  • the control means (6, 6 ') are closed and the bypass means (7, 7') are open.
  • the cycle fluid thus circulates at the outlet of the condenser (2) in the two branch circuits leading to the two zones (Z2, Z2 ') of the systems (12, 12') exchangers, the cycle fluid not circulating in the two zones (Z1, Z1 ') exchange systems (12, 12') exchangers.

Claims (14)

  1. Wärmepumpenanlage, die auf der Basis einer Kältequelle (A) arbeitet, umfassend einen Kreislauf, ausgestattet mit wenigstens einem Kompressor (1), einem Kondensator (2), Entspannungsmitteln (3, 3'), wenigstens einem Verdampfer (4, 4'), einem in dem Kreislauf zirkulierenden Umlauffluid, wobei der Kondensator (2) von einem zu erhitzenden Fluid gekühlt wird, wobei die Anlage Folgendes umfasst:
    - wenigstens zwei Austauschersysteme (12, 12'), jeweils zusammengesetzt aus zwei fluidisch getrennten und thermisch verbundenen Wärmeaustauschzonen (Z1 und Z1', Z2 und Z2'), wobei die erste Austauschzone (Z1, Z1') die Funktion des Unterkühlens des Umlauffluids und des Entfrostens der zweiten Austauschzone (Z2, Z2') erfüllt, wobei Letztere die Verdampfungsfunktion (4, 4') erfüllt, wobei die beiden Austauschersysteme (12, 12') parallel mit Bezug auf den Satz aus Kompressor (1) und Kondensator (2) auf beiden Seiten von wenigstens zwei Entspannungsmitteln (3, 3') montiert sind;
    - Mittel zum Zirkulieren des Umlauffluids zwischen dem Satz aus Kompressor (1) und Kondensator (2) und den Austauschersystemen (12, 12') sowie Mittel zum Steuern (6, 6') und Mittel zum Ableiten (7, 7') des Umlauffluidflusses in dem Kreislauf, so dass die Anlage in einem wechselweisen Umlauffluidzirkulationsmodus im Entfroster eines ersten Austauschersystems (12, 12') und dann im Verdampfer (4, 4') des zweiten Austauschersystems (12, 12') arbeiten kann,
    wobei die Wärmepumpenanlage ferner dadurch gekennzeichnet ist, dass die Mittel zum Steuern (6, 6') und die Mittel zum Ableiten (7, 7') des Umlauffluidflusses in dem Kreislauf den Betrieb der Anlage gemäß einem gleichzeitigen parallelen Zirkulationsmodus zulassen,
    wobei Umlauffluid im Verdampfer (4, 4') der beiden Austauschersysteme (12, 12') fließt,
    wobei die Anlage ferner einen Kasten (50) umfasst, der die Komponenten (1, 2, 12, 12', 3, 3') der Wärmepumpe umschließt, wobei der Kasten (50) halbgeschlossene Räume (53, 53') zwischen jedem Ventilator (5, 5') und einer Innenwand des Kastens (50) gegenüber jedem Ventilator (5, 5') bildet, wobei jeder Ventilator (5, 5') an jedem Austauschersystem (12, 12') entlang seiner Höhe h platziert ist, wobei der von jedem Ventilator (5, 5') erzeugte Luftstrom durch eine untere Öffnung (51, 51') des Kastens (50) eintritt und in Richtung eines Austauschersystems (12, 12') aufsteigt, wobei er die zweite Austauschzone (Z2, Z2') des genannten Austauschersystems (12, 12') durchquert und dann wieder absteigt und den Kasten (50) durch eine Öffnung (52, 52') verlässt, die sich unter jedem Verdampfer (4, 4') im unteren Teil des Kastens (50) befindet, wobei es diese halbgeschlossenen Räume (53, 53') zulässt, das Entfrosten der Verdampfer (4, 4') durch die Anwesenheit von Heißluft im oberen Teil des Kastens (50) zu begünstigen.
  2. Anlage nach Anspruch 1, bei der der Betriebsmodus von der Außentemperatur abhängt, gemessen mit thermometrischen Messmitteln, gesteuert durch einen Prozessor und einer Software, die die Steuermittel (6, 6') in Abhängigkeit von dem für die entsprechende Außentemperatur benötigten Betriebsmodus betätigen.
  3. Anlage nach Anspruch 1, in der jedes Austauschersystem (12, 12') Folgendes umfasst:
    - parallele Rippen, die in einer Ebene (P) ausgerichtet sind;
    - eine Austauschzone (Z2, Z2'), gebildet von zwei fluidisch verbundenen Subzonen (Z2a und Z2a', Z2b und Z2b'), wobei die erste Subzone (Z2a, Z2a') auf einer ersten Seite positioniert ist und einen Luftstrom gemäß einer Komponente parallel zur Ebene P in dem Austauschersystem (12, 12') empfängt, wobei die zweite Subzone (Z2b, Z2b') auf einer zweiten Seite gegenüber der ersten Seite positioniert ist, um ein Austreten des genannten Luftstroms aus dem Austauschersystem (12, 12') zuzulassen;
    - eine Austauschzone (Z1, Z1'), die sich zwischen den beiden Austauschsubzonen (Z2a und Z2a', Z2b und Z2b') befindet und thermisch mit den genannten Austauschsubzonen (Z2a und Z2a', Z2b und Z2b') verbunden ist.
  4. Anlage nach einem der Ansprüche 1 bis 3, bei der die zweite Wärmeaustauschzone (Z2, Z2'), die die erste Wärmeaustauschzone (Z1, Z1') jedes Austauschersystems (12, 12') umgibt, vom Rippenrohrtyp ist.
  5. Anlage nach einem der Ansprüche 1 bis 4, bei der jedes Austauschersystem (12, 12') einen Radiator umfasst, der die beiden Austauschzonen (Z1 und Z1', Z2 und Z2') umfasst.
  6. Anlage nach einem der Ansprüche 1 bis 5, in der jede der genannten Austauschzonen (Z1 und Z1', Z2 und Z2') über die gesamte Höhe (h) eines von jedem Austauschersystem (12, 12') eingenommenen Volumens verläuft.
  7. Anlage nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass der Ventilator (5, 5') neben einem Verdampfer (4, 4') im Laufe des Entfrostens im Stillstand ist, um das Entfrosten des Verdampfers (4, 4') zu begünstigen.
  8. Verfahren zum Optimieren des Betriebs einer Wärmepumpenanlage, die auf der Basis einer Kältequelle (A) arbeitet, umfassend einen Kreislauf, ausgestattet mit wenigstens einem Kompressor (1), einem Kondensator (2), Entspannungsmitteln (3, 3'), einem in dem Kreislauf zirkulierenden Umlauffluid, wenigstens zwei Austauschersystemen (12, 12'), die eine Verdampferfunktion 4, 4') erfüllen können, Steuer- (6, 6') und Ableitungsmitteln (7, 7') und einem die Komponenten (1, 2, 12, 12', 3, 3') der Wärmepumpe umschließenden Kasten (50),
    dadurch gekennzeichnet, dass es Folgendes beinhaltet:
    - einen Schritt des Übertragens von Wärme des Umlauffluids zu einer Zone eines Wärmeaustauschers (12, 12'), die sich von der unterscheidet, die die Verdampferfunktion (4, 4') erfüllt, und mit der Wirkung des Unterkühlens des Umlauffluids und des Entfrostens des genannten Austauschersystems (12, 12');
    - einen Schritt des Zirkulierens der Luft in halbgeschlossenen Räumen (53, 53') des Kastens (50), wobei die Luft durch eine untere Öffnung (51, 51') des Kastens (50) eintritt, in Richtung eines Austauschersystems (12, 12') aufsteigt, die zweite Austauschzone (Z2, Z2') des genannten Austauschersystems (12, 12') durchquert, dann wieder absteigt und den Kasten (50) durch eine Öffnung (52, 52') verlässt, die sich in jedem Verdampfer (4, 4') im unteren Teil des Kastens (50) befindet;
    - einen Schritt des Zirkulierens des unterkühlten Umlauffluids in Richtung der Entspannungsmittel (3, 3'), dann in der zweiten Austauschzone (Z2, Z2') eines Austauschersystems (12, 12'), so dass das Umlauffluid am Verdampfer (4, 4') wieder erhitzt werden kann;
    - einen Schritt des gleichzeitigen Arbeitens, wobei die Mittel (7, 7') zum Ableiten des Umlauffluidflusses offen sind und die Steuermittel (6, 6') geschlossen sind, so dass Umlauffluid in den beiden Verdampfern (4, 4') gleichzeitig wieder erhitzt werden kann.
  9. Verfahren nach Anspruch 8, das einen alternativen Betriebsschritt beinhaltet, wobei das Umlauffluid nicht in wenigstens einem der Verdampfer (4, 4') durch die Assoziation der Zeitschaltmittel und des Schließens von wenigstens einem der Steuermittel (6, 6') und den Ableitmitteln (7, 7') umläuft, wobei die Kühlung des Umlauffluids im Kondensator (2) und der Betrieb des Kompressors (1) kontinuierlich sind.
  10. Verfahren nach einem der Ansprüche 8 bis 9, das einen Schritt des Umschaltens von einem Betriebsmodus in den anderen beinhaltet, wenn die Außentemperatur, gemessen mit einem thermometrischen Sensor, einen Schwellenwert übersteigt.
  11. Verfahren nach einem der Ansprüche 8 bis 10, in dem der Schritt des Unterkühlens des Umlauffluids und des Entfrostens der Austauschersysteme (12, 12') nur mit den Austauschersystemen (12, 12') der Wärmepumpenanlage erfolgt, ohne den stromaufwärtigen Schritt des Kühlens des Umlauffluids im Kondensator (2) zu unterbrechen.
  12. Verfahren nach einem der Ansprüche 8 bis 11, bei dem das Umlauffluid in einem Teil des Kreislaufs in einen hyperkritischen Zustand gebracht wird.
  13. Verfahren nach einem der Ansprüche 8 bis 12, in dem der Luftzirkulationsschritt an den Austauschersystemen (12, 12') eine Geschwindigkeit von wenigstens 2 m/s erreicht.
  14. Verfahren nach einem der Ansprüche 8 bis 13, das einen Schritt des Verdampfens in der Austauschzone (Z2, Z2') beinhaltet, der die Verdampferfunktion (4, 4') erfüllt, realisiert bei einer maximalen Temperatur zwischen -10°C und -20°C.
EP12759659.1A 2011-08-04 2012-07-30 System und verfahren zur optimierung des betriebs eines wärmepumpensystems Not-in-force EP2739918B1 (de)

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FR1157148A FR2978816B1 (fr) 2011-08-04 2011-08-04 Installation et procede d'optimisation de fonctionnement d'une installation de pompe a chaleur
PCT/EP2012/064902 WO2013017572A1 (fr) 2011-08-04 2012-07-30 Installation et procédé d'optimisation de fonctionnement d'une installation de pompe à chaleur

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EP2739918B1 true EP2739918B1 (de) 2018-03-07

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CN104807268B (zh) * 2015-04-22 2017-07-25 广东芬尼克兹节能设备有限公司 一种热泵的水泵启动控制方法及系统
SE541960C2 (en) 2016-07-12 2020-01-14 Es Energy Save Holding Ab Heat pump apparatus module
CN108548349B (zh) * 2018-03-26 2020-10-30 广州西奥多科技有限公司 一种智能型热泵的除霜控制系统
FR3127554B1 (fr) * 2021-09-30 2023-10-20 Lemasson Procédé de régulation du fonctionnement d'une pompe à chaleur équipée de deux échangeurs évaporateurs et d'un échangeur condenseur

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FR2978816B1 (fr) 2018-06-22
EP2739918A1 (de) 2014-06-11
WO2013017572A1 (fr) 2013-02-07

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