EP3722703A1 - Thermodynamische maschine vom typ wärmepumpe zum erzeugen von wärme und kälte, und ihr funktionsverfahren - Google Patents

Thermodynamische maschine vom typ wärmepumpe zum erzeugen von wärme und kälte, und ihr funktionsverfahren Download PDF

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Publication number
EP3722703A1
EP3722703A1 EP19167757.4A EP19167757A EP3722703A1 EP 3722703 A1 EP3722703 A1 EP 3722703A1 EP 19167757 A EP19167757 A EP 19167757A EP 3722703 A1 EP3722703 A1 EP 3722703A1
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EP
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Prior art keywords
refrigerant
heat exchanger
heat
exchanger
circuit
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EP19167757.4A
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English (en)
French (fr)
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EP3722703B1 (de
Inventor
Bruno Seguin
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X Terma SAS
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X Terma SAS
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Priority to ES19167757T priority Critical patent/ES2909327T3/es
Priority to EP19167757.4A priority patent/EP3722703B1/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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the field of the invention is installations for the production of heating and cooling energy by thermodynamic cycle, to meet the heating, cooling and domestic hot water production needs in the building and industrial sectors.
  • thermofrigopumps which simultaneously ensure the supply of heat energy to a consumer of heat energy on the one hand and the supply of cooling energy to a consumer of cooling energy. 'somewhere else.
  • the refrigeration energy consumer also called cold consumer, is defined as one or more elements absorbing refrigerating energy via a heat transfer fluid.
  • the cooling power transferred to the consumer is directly proportional to the difference between the temperature of the heat transfer fluid in the direction of the cold consumer and the temperature of the heat transfer fluid on return from the cold consumer.
  • the temperature of the heat transfer fluid is regulated at the outset towards the cold consumer.
  • Heat pumps produce heat energy which is transferred to the outside through a heat exchanger called a condenser exchanger, at the primary of which the condensation of a refrigerant takes place, and at the secondary of which circulates the heat transfer fluid conveying heat energy to the hot consumer.
  • Heat pumps simultaneously produce cooling energy which is transferred to the outside through a heat exchanger called an evaporator exchanger, at the primary of which the evaporation of a refrigerant takes place, and at the secondary of which circulates the heat transfer fluid conveying the refrigerating energy towards the cold consumer.
  • the ratio between the heating and cooling powers produced by the machine at a given time essentially depends on the type of refrigerant used and the values of temperature of condensation and evaporation of the refrigerant at the time considered. These temperature values are directly linked to the temperature values of the coolant at the outlet of the secondary of the condenser exchanger and at the outlet of the secondary of the evaporator exchanger. The ratio between the heating and cooling powers produced by the machine at a given time cannot therefore be freely adjusted.
  • the ratio between the calorific power required by the heat consumer and the cooling power required by the cold consumer is completely independent of the thermodynamic machine, can vary at any time, and can also take n ' any value.
  • thermofrigopump is incapable of adapting at any time both the calorific power and the refrigeration capacity produced to the values of calorific and refrigeration capacity required respectively by the heat consumer and the cold consumer.
  • the machine adapts the heat output produced to the heat output required by the heat consumer, and in this case the cooling output produced by the machine does not correspond to the power level required by the consumer of cold.
  • the machine adapts the cooling power produced to the cooling power required by the cold consumer, and in this case the heat output produced by the machine does not correspond to the power level required by the heating consumer.
  • the machine can adapt the heating capacity produced to the heating capacity required by the heat consumer. However, it produces a cooling capacity greater than the cooling capacity required by the cold consumer. In this case, the machine operates according to the mode called priority heat production, heat production then being called priority production and refrigeration production then being called non-priority production.
  • the machine can adapt the cooling capacity produced to the cooling capacity required by the cold consumer. However, it produces more heat output than the heat output required by the heat consumer. In this case, the machine operates according to the mode called priority refrigeration production, refrigeration production then being called priority production and heat production then being called non-priority production.
  • priority heat production mode In priority heat production mode, only part of the cooling energy produced by the machine is actually supplied to the cold consumer, and a residue of the cooling energy produced by the machine must be evacuated to an external element. In priority cooling production mode, only part of the heat energy produced by the machine is actually supplied to the heat consumer, and it is a heat energy residue produced by the machine which must be evacuated to an external element.
  • This external element ensuring the energy balance of the system by absorbing the residue of non-priority production, which may be heat energy or refrigeration energy, is called an external source.
  • the external source is defined as one or more elements capable of absorbing heat energy or cooling energy indifferently.
  • thermofrigopumps A first major drawback of thermofrigopumps lies in the fact that on the non-priority production side, the adjustment of the part of energy produced which must be exchanged with the external source is not ensured by the machine itself.
  • priority heat production mode all of the cooling energy produced by the machine is exchanged with the outside through the evaporator exchanger, this energy then being directed partly to the cold consumer and for the other part to the external source, using a circuit external to the machine.
  • priority refrigeration production mode all of the heat energy produced by the machine is exchanged with the outside through the condenser exchanger. This energy is then directed partly to the heat consumer and for the other part to the external source, using a circuit external to the machine.
  • thermofrigopumps lies in the fact that on the priority production side, the regulation of the starting temperature of the coolant to the consumer is carried out in stages to achieve the perfect adaptation of the power produced to the power required by the consumer.
  • each stage corresponds to the unit capacity of the compressors of the machine, which operate in all or nothing mode.
  • each start or stop of a compressor generates a variation of the heating and cooling powers produced by the thermodynamic machine, which causes a variation in the temperatures of the heat transfer fluid at the outlet of the secondary of the condenser exchanger and at the outlet of the secondary of the evaporator exchanger.
  • a third drawback of heat pumps lies in the fact that on the non-priority production side, all of the energy produced is transferred by the machine through an exchanger.
  • the management of energy flows between the consumer on the one hand and the external source on the other hand is carried out by a circuit external to the machine. It is then necessary for the machine to produce this energy at an adequate temperature level so that both the consumer and the external source can absorb part of it.
  • the temperature of the heat transfer fluid at the secondary of the evaporator exchanger must be at most equal to the lowest of the temperatures required by the cold consumer on the one hand and the external source on the other.
  • the temperature of the heat transfer fluid at the secondary of the condenser exchanger must be at least equal to the highest of the temperatures required by the heating consumer on the one hand and the external source on the other hand.
  • the energy efficiency of a refrigerant circuit depends on the work performed by the compressors, and therefore on the difference between high pressure and low pressure in the refrigerant circuit.
  • the temperature of change of state of a fluid being directly related to the pressure of this fluid, the efficiency of the circuit depends on the difference between the condensing temperature of the refrigerant when it is in the high circuit portion. pressure and evaporation temperature of the refrigerant when it is in the low pressure circuit portion.
  • the efficiency of a refrigerant circuit therefore depends on the difference between the temperature at the secondary of the condenser exchanger and the temperature at the secondary of the evaporator exchanger. The higher this difference, the lower the yield.
  • All of the energy is therefore produced by the heat pump with the temperature level on the non-priority side which is the most unfavorable for the efficiency of the machine. It is not possible to optimize the overall efficiency of the machine by producing part of the energy intended for the non-priority consumer with one efficiency and another part of the energy destined for the external source with another efficiency. .
  • the object of the present invention is to solve the above-mentioned problems and in particular to provide a thermodynamic machine which is capable of directly exchanging the residue of heat or cooling energy produced by the thermodynamic machine on the production side with the external source. non-priority and not consumed by the corresponding consumer, preferably without having recourse to external circuits for managing the energy flow between the consumer and the external source.
  • the second holder is a two-way regulator.
  • the compressor comprises a first compressor and a second compressor mounted in parallel between the first heat exchanger and the second heat exchanger, the first compressor being a compressor with variable speed of rotation and the second compressor being an all or all type compressor. nothing whose activation is triggered when a heat power transferred through the first heat exchanger reaches a threshold value or when a cooling power transferred through the second heat exchanger reaches a threshold value.
  • the first expansion valve has a variable opening rate and the machine comprises a control circuit configured to control the opening rate of the first expansion valve in order to regulate the proportion of refrigerant passing through the expansion valve and the second heat exchanger to adjust the cooling power transmitted through the second heat exchanger or to control the opening rate of the first expansion valve in order to regulate the proportion of refrigerant passing through the expansion valve and the first heat exchanger to adjust the calorific power transmitted through the first heat exchanger
  • control circuit is configured to regulate the temperature of the heat transfer fluid at the outlet from the first heat exchanger or at the outlet from the second heat exchanger to a set value.
  • the second regulator has a variable open rate and the control circuit is configured to control the ratio of the open rate of the first regulator to the second regulator.
  • the thermodynamic machine comprises a second refrigerant circuit inside which a second refrigerant circulates, the second refrigerant circuit connecting the first heat exchanger, the second heat exchanger and the third heat exchanger.
  • the second refrigerant circuit has a compressor, a first expansion valve, a first link node, a second link node, a third link node, a fourth link node, a first switching device, a second switching device and a second expansion valve arranged similarly to the arrangement of the first refrigerant circuit.
  • thermodynamic machine comprises a control circuit configured to define an operating mode in which the first and the second switching devices of the first refrigerant circuit prevent the circulation of the refrigerant in the third heat exchanger and wherein the first and second switching devices of the second refrigerant circuit prevent the circulation of the second refrigerant in the second heat exchanger.
  • thermodynamic machine comprises a control circuit configured to define an operating mode in which the first and second switching devices of the first refrigerant circuit prevent the circulation of the refrigerant in the first heat exchanger and in which the first and second switching devices of the second refrigerant circuit prevent the circulation of the second refrigerant in the third heat exchanger.
  • Another subject of the invention is a method of operating a machine which makes it possible to better regulate the calorific power supplied and the cooling power supplied.
  • the thermodynamic machine 100 is of the thermofrigopump type, ie the thermodynamic machine has at least one heat pump whose useful energy is rejected on a hot source and is taken from a cold source.
  • the thermodynamic machine 100 has a plurality of pipes in which one or more fluids can circulate.
  • the fluids can be in liquid or gas form.
  • the direction of flow of the fluid is shown by arrows on the figures 2 , 3 , 4 , 5 , 6 , 7 , 9 , and 10 .
  • the pipes allowing a circulation of fluid are represented by a solid line while the pipes not allowing a circulation of fluid are shown by dotted lines.
  • Valves and regulators in the open position are shown in white. Valves and regulators in the closed position are shown in black. In the open position, the valve allows the circulation of a fluid while it prevents this circulation when it is in the closed position.
  • the black arrows placed on the heat exchangers indicate a transfer of heat through the heat exchangers.
  • the direction of the black arrows indicates the direction of heat flow.
  • a black arrow coming out of the thermodynamic machine 100 indicates a transfer of heat power from the machine 100 to the outside, while a black arrow entering the thermodynamic machine 100 indicates a transfer of cooling power from the machine 100 to the outside. .
  • the heat pump 100 comprises a refrigerant circuit 1 in which circulates a refrigerant or at least one refrigerant.
  • a refrigerant can be pure or be a mixture of fluids.
  • the refrigerant can be in gaseous or liquid form depending on the pressure and temperature in the refrigerant circuit and in particular in the heat exchangers.
  • the liquid-gas state change temperatures of the refrigerant are located within the operating temperature range of the thermodynamic machine.
  • the refrigerant is preferably chosen from Hydro Fluoro Carbones, for example R134a (1,1,1,2-tetrafluoroethane), R410A (mixture of difuoromethane and 1,1,1,2,2-pentafluoroethane), R407C (mixture of 1,1,1,2-tetrafluoroethane, 1,1,1,2,2-pentafluoroethane and difuoromethane) or from Hydro Fluoro Olefins, for example R1234ze (trans-1,3,3,3- Tetrafluoroprop-1-ene), or R-1233zd (trans-1-chloro-3,3,3-trifluoro-1-propene).
  • the liquid-gas state change temperature of the refrigerant is between -50 ° C and 100 ° C.
  • the heat pump 100 has a first heat exchanger 2 which produces heat energy.
  • the first heat exchanger 2 supplies a calorific energy consumer 200 also called a hot source by means of a first heat transfer fluid.
  • the first heat transfer fluid circulates in pipes 201 and 202 which connect a secondary of the first heat exchanger 2 with the heat energy consumer 200.
  • the heat energy consumer is for example a heating system or a hot water producer.
  • the heat pump 100 produces cooling energy through a second heat exchanger 3.
  • the second heat exchanger 3 supplies a cold consumer 300 also called cold source by means of a second heat transfer fluid circulating in pipes 301 and 302.
  • the pipes 301 and 302 connect a secondary of the second heat exchanger 3 with the cold consumer 300.
  • the cold consumer is for example a cooling system.
  • the heat pump 100 has a third heat exchanger 4, the secondary of which is thermally connected with an external element 401 which can be the external source 400 itself or a third heat transfer fluid supplying this external source 400.
  • the heat pump is able to exchange heat with the external source 400.
  • the temperature of the external source is advantageously between -40 ° C and 50 ° C.
  • the external source can be ambient air.
  • the first, second and third heat transfer fluids can be the same or different and be present independently pure or as a mixture.
  • the heat transfer fluid can also contain mineral substances.
  • the heat transfer fluid does not change state during heat transfer between a heat exchanger and a hot / cold consumer or an external source.
  • the heat transfer fluid can be chosen from water, air, an aqueous solution, monopropylene glycol, monoethylene glycol, alcoholic solutions or salts.
  • the external source 400 has a or more exterior elements 401.
  • An exterior element 401 is a natural element, such as ambient air, water from the natural environment, the ground or any type of exterior element.
  • the thermodynamic machine can be provided with one or more intermediate heat exchange systems to address each of the external elements.
  • the refrigerant circuit 1 is connected to the primary of the first heat exchanger 2, to the primary of the second heat exchanger 3 and to the primary of the third heat exchanger 4.
  • the refrigerant circulates so as to displace calories between the heat exchangers.
  • the first heat exchanger also called condenser exchanger 2 transfers heat from the refrigerant circulating in the primary of the condenser exchanger 2 to a heat transfer fluid circulating in the secondary of the condenser exchanger 2, while ensuring condensation. refrigerant.
  • the second heat exchanger 3 also called evaporator exchanger 3, allows heat to be transferred from a coolant circulating in the secondary of the evaporator exchanger 3 to the refrigerant. circulating at the primary of the evaporator exchanger 3, while ensuring the evaporation of the refrigerant.
  • the third heat exchanger 4 also called the source exchanger 4, makes it possible to exchange heat between the refrigerant circulating in the primary of the source exchanger 4 and the external element 401, in contact with the secondary of the exchanger. source 4, while ensuring either condensation or evaporation of the refrigerant.
  • the heat pump 100 advantageously comprises a first temperature sensor 21 configured to measure the temperature TCH of the heat transfer fluid at the outlet of the secondary of the condenser exchanger 2 and advantageously a second temperature sensor 31 configured to measure the temperature TFR of the heat transfer fluid at the outlet of the heat transfer fluid. secondary of the evaporator exchanger 3.
  • the measurement of the two temperatures can be sent to a control circuit 500 to ensure the regulation of each of the temperatures TFR and TCH to a set value.
  • a third temperature sensor 23 can be used to measure the temperature T3 of the refrigerant at the outlet of the primary circuit of the exchanger condenser 2.
  • a fourth temperature sensor 32 can be used to measure the temperature T1 at the outlet of the primary circuit of the evaporator exchanger 3.
  • a compressor makes it possible to compress the refrigerant in the refrigerant circuit 1 when the latter is in the gaseous state.
  • the compressor is arranged in a pipe which connects the outlet of the second heat exchanger 3 and the inlet of the first heat exchanger 2.
  • the compressor comprises a first compressor 5 and a second compressor 6 mounted in parallel.
  • the first compressor 5 can be driven by a first electric motor 53 provided with an electronic speed variator 54 to adapt its speed to the calorific or cooling power requested.
  • the second compressor 6 can be driven by a second electric motor 63.
  • the refrigerant circuit 1 also comprises a first pressure sensor 51 configured to measure the pressure PHP at the outlet of the compressor and a second pressure sensor 52 configured to measure the pressure PBP at the inlet of the compressor.
  • a reservoir 14 is mounted in the refrigerant circuit 1 at the inlet of the compressor.
  • the reservoir 14 is configured to trap the refrigerant in the liquid state.
  • the compressor is supplied with a refrigerant in the gaseous state.
  • a first expansion valve 7 is mounted in the refrigerant circuit 1 so as to lower the pressure of the refrigerant when the latter circulates in the expansion valve 7 in the liquid state.
  • the first expander 7 is arranged in a pipe which connects the outlet of the first heat exchanger 2 with the inlet of the second heat exchanger 3.
  • the first expander 7 is preferably electronically controlled.
  • a second, preferably bidirectional, expansion valve 8 is mounted in the refrigerant circuit 1 so as to lower the pressure of the refrigerant when the latter circulates in the expansion valve 8 in the liquid state.
  • the second expansion valve 8 is arranged in a pipe where the refrigerant circulates between a connection node 20 and the third heat exchanger 4.
  • the connection node 20 being able to connect the second expansion valve 8 to the first heat exchanger 2 and / or to the second heat exchanger 3.
  • the second expansion valve 8 is preferably electronically controlled.
  • the refrigerant circuit 1 is configured so as to supply each heat exchanger with refrigerant and ensure the transfers of calories between the heat exchangers.
  • the refrigerant circuit 1 has multiple pipes connecting the inlets and outlets of the heat exchangers to one another in order to be able to define different directions of circulation of the refrigerant and thus different operating modes.
  • the refrigerant circuit 1 has a first connection node 15 which connects the output of the compressor to the input of the first heat exchanger 2 and to a first switching device which defines or comprises a fifth connection node 19.
  • a second link node 16 makes the connection between the output of the first heat exchanger 2, a first terminal of the first expansion valve 7 and a second switching device which defines or comprises a sixth link node 20.
  • a third link node 17 makes the connection between a second terminal of the first expansion valve 7, the input of the second heat exchanger 3 and the second switching device.
  • a fourth link node 18 makes the connection between the inlet of the compressor, the outlet of the second heat exchanger 3 and a fifth link node 19.
  • the fourth link node can be arranged between the outlet of the second heat exchanger 3 and the tank 14.
  • the fifth link node 19 makes the connection between the first link node 15, the fourth link node 18 and a first input / output of the third heat exchanger 4.
  • the sixth link node 20 makes the connection between the third link node 17, the second link node 16 and a second inlet / outlet of the third heat exchanger 4 via the second expansion valve 8.
  • a fifth temperature sensor 42 can be used to measure the temperature T2 of the refrigerant between the connecting node 19 and the first inlet / outlet of the source exchanger 4. For example, when the primary of the source exchanger 4 operates as an evaporator, the fifth temperature sensor measures the temperature T2 of the refrigerant at the outlet of the primary of the source 4 exchanger.
  • a sixth temperature sensor 43 can be used to measure the temperature T4 of the refrigerant between the second inlet / outlet of the source exchanger 4 and the sixth connection node 20, preferably between the second inlet / outlet of the exchanger. source 4 and the second expansion valve 8.
  • the sixth sensor 43 measures the temperature T4 of the refrigerant at the outlet of the primary of source exchanger 4.
  • the first switching device is configured to selectively define a first configuration or a second configuration.
  • the first configuration defines a first refrigerant circulation channel connecting the first inlet / outlet from the third heat exchanger 4 to the fourth link node 18 and preventing the flow of refrigerant through the switching device from the first link node 15 as illustrated in figure 2 .
  • the second configuration defines a second refrigerant circulation channel connecting the first connecting node 15 to the first inlet / outlet of the third heat exchanger 4 as illustrated in figure 5 , and preventing the flow of refrigerant through the switching device to the fourth link node 18.
  • the second switching device is configured to selectively define a first configuration or a second configuration.
  • the first configuration defines a first refrigerant circulation channel connecting the second connecting node 16 to a second inlet / outlet of the third heat exchanger 4 and preventing the circulation of the refrigerant through the switching device to the third cooling node. link 17 as shown in figure 2 .
  • the second configuration defines a second refrigerant circulation channel connecting the second inlet / outlet of the third heat exchanger 4 to the third connecting node 17 and preventing the circulation of the refrigerant through the switching device from the second connecting node 16 as shown in figure 5 .
  • the second switching device is further configured to define a blocking configuration in which no fluid passes through the second switching device.
  • the first circulation channels defined by the first and second switching devices make it possible to form a circulation channel which connects the outlet of the first heat exchanger 2 with the inlet of the compressor passing through the third heat exchanger 4 to recover heat.
  • the second circulation channels defined by the first and second switching devices make it possible to form a circulation channel which connects the outlet of the compressor with the inlet of the second heat exchanger 3 passing through the third heat exchanger 4 to evacuate heat.
  • the first switching device can be formed, for example, by two valves 10 and 11, preferably solenoid valves 10 and 11.
  • the first valve 10 can be mounted between the first connection node 15 and the fifth.
  • link node 19 and the second valve 11 can be mounted between the fifth link node 19 and the fourth link node 18.
  • the first switching device is configured to allow a first circulation of the refrigerant between the first inlet / outlet of the third heat exchanger 4 and the inlet of the compressor 5, 6, to allow a second circulation of the refrigerant between the outlet of the compressor 5, 6 and the first inlet / outlet of the third heat exchanger 4 or to block a flow of refrigerant between the compressor outlet and the first inlet / outlet of the third heat exchanger 4 and block a flow of refrigerant between the first input / output of the third heat exchanger 4 and the input of the compressor 5.
  • the first switching device is advantageously configured to avoid directly connecting the input and the output of the compressor.
  • the second switching device can be formed for example by two valves 12 and 13, preferably solenoid valves 12 and 13.
  • the valve 12 is advantageously arranged between the second connection node 16 and the sixth connection node 20.
  • the valve 13 is advantageously arranged between the sixth link node 20 and the third link node 17.
  • the second switching device is configured to allow a first circulation of the refrigerant between the outlet of the first heat exchanger 2 and the second inlet / outlet of the third heat exchanger 4, to allow a second circulation of the refrigerant between the second inlet / outlet of the third heat exchanger 4 and the inlet of the second heat exchanger 3 or to block a flow of refrigerant between the second inlet / outlet of the third heat exchanger 4 and the inlet of the second heat exchanger 3 and block a flow of refrigerant between the outlet of the first heat exchanger 2 and the second inlet / outlet of the third heat exchanger 4.
  • the first switching device is advantageously configured to avoid directly connecting the outlet of the first heat exchanger and the inlet of the second heat exchanger which bypasses the expansion valve 7.
  • the first and second switching devices are configured to arrange the third heat exchanger 4 in parallel with the second heat exchanger 3 in order to dissociate the cooling power supplied to the second heat exchanger 3 from the cooling power delivered by the machine 100.
  • the first and second switching devices are configured to arrange the third heat exchanger 4 in parallel with the first heat exchanger 2 in order to dissociate the caloric power supplied to the first heat exchanger 2 from the caloric power delivered by the machine 100.
  • the first and second switching devices can also be configured to independently exit, the first heat exchanger 2, the second heat exchanger 3 and the third heat exchanger 4 from the refrigerant circuit by preventing the circulation of the refrigerant inside the refrigerant circuit. one of these interchanges.
  • the first and second switching devices make it possible to easily adapt the calorific and / or cooling power delivered to the first heat exchanger and to the second heat exchanger by adapting the operation of the third heat exchanger.
  • the first, second, third and fourth link nodes can simply be connection nodes and have no valves.
  • the thermodynamic machine 100 has a single refrigerant circuit, two refrigerant circuits or more than two refrigerant circuits.
  • the figure 2 illustrates an operating mode of the thermodynamic machine called priority heat production.
  • the calorific power produced by the thermodynamic machine 100 through the refrigerant circuit 1 is adapted to the calorific power required by the heat consumer 200.
  • the control circuit 500 regulates the calorific power to maintain the heat output. TCH temperature within a target range.
  • the refrigeration capacity produced by the refrigerant circuit 1 is at least equal to the refrigeration capacity required by the refrigeration consumer 300.
  • the black arrow 203 represents heat extraction from the refrigerant circuit to the heat consumer 200.
  • Part of the refrigeration power produced corresponding to the cooling power required by the cold consumer 300, is transferred to the cold consumer 300 through the evaporator exchanger 3.
  • the black arrow 303 represents a heat extraction from the cold consumer 300 to the refrigerant circuit 1
  • the remaining part of the cooling power produced is transferred to the source 400 through the source exchanger 4.
  • the black arrow 403 represents an extraction of heat from the source 400 towards the refrigerant circuit 1.
  • the output of the first heat exchanger 2 is connected to the input of the second heat exchanger 3 and to the second input / output of the third heat exchanger 4 to allow a flow of refrigerant from the first exchanger heat 2 to the second and third heat exchangers 3 and 4.
  • the outlet of the second heat exchanger 3 and the first inlet / outlet of the second heat exchanger meet for example before the compressor inlet and advantageously before the inlet tank 14.
  • valve 12 is open and valve 13 is closed.
  • Valve 11 is open and valve 10 is closed.
  • valve 10 being closed, all of the refrigerant in the gaseous state and at high pressure, coming from the compressor, circulates only through the primary of the exchanger condenser 2, inside which the refrigerant condenses in yielding heat to the coolant circulating in the secondary of the condenser exchanger 2.
  • the refrigerant leaves the condenser exchanger 2 at a lower temperature T3 and advantageously in the liquid state and at high pressure.
  • the presence of the temperature sensor 23 is not essential for the operation of the machine.
  • the temperature measurement T3 possibly combined with the PHP pressure measurement makes it possible to check that the drop in temperature linked to the condenser exchanger 2 is in the desired range and / or that the refrigerant leaving the primary of the The condenser exchanger 2 is in the liquid phase.
  • the second compressor 6 is activated. This second compressor 6 then provides additional power and the speed of rotation of compressor 5 is controlled in order to provide the additional power necessary to reach the power required at the level of the condenser exchanger 2.
  • This mode of operation of compressors 5 and 6 which combines the activation or deactivation of the second compressor 6 and the adjustment of the rotational speed of the first compressor 5, thus makes it possible to continuously adjust the calorific power transmitted through the 'exchanger condenser 2, and therefore to regulate the outlet temperature TCH of the heat transfer fluid to its set value.
  • the refrigerant On leaving the condenser exchanger 2, the refrigerant passes through the second connection node 16 where it splits into two parts. Part of the refrigerant is directed to the inlet of the second heat exchanger 3 through the expansion valve 7. In the expansion valve 7, the refrigerant undergoes a lowering of its pressure. At the outlet of the regulator 7, the fluid is at low pressure and advantageously in the liquid state. The refrigerant is directed through the third connecting node 17 to the primary of the evaporator exchanger 3 inside which the refrigerant evaporates by capturing heat from the heat transfer fluid circulating at the secondary of the evaporator exchanger 3.
  • the refrigerant At the outlet of the primary of the evaporator exchanger 3, the refrigerant is mainly in the gaseous state and at low pressure. The refrigerant reaches the reservoir 14 through the connecting node 18.
  • the other part of the refrigerant leaving the condenser exchanger 2 is directed to the third heat exchanger 4 through the expansion valve 8.
  • the refrigerant in the liquid state undergoes a drop in its pressure by means of the expansion valve 8.
  • a the outlet of the expansion valve 8 the fluid in the liquid state and at low pressure passes through the primary of the source exchanger 4, then functioning as an evaporator.
  • the refrigerant evaporates in the third heat exchanger 4 by capturing heat from the external element which is in contact with the secondary of the source exchanger 4.
  • the refrigerant On leaving the primary of the source exchanger 4, the refrigerant is in a gaseous state and at low pressure.
  • the combined measurement of temperatures T1 and T2 is used to determine the superheat value of the refrigerant at the outlet of the evaporator exchanger 3 on the one hand, and at the outlet of the source exchanger 4 of somewhere else.
  • the measurement of temperatures T1 and T2 is used in order to impose the superheat value of the refrigerant at the outlet of the evaporator exchanger 3 and at the outlet of the source exchanger 4.
  • the combined measurement of the temperatures T1 and T2 is used to control the opening rate of the expansion valve 7 and the opening rate of the expansion valve 8, if applicable.
  • Temperature measurements are used to ensure complete evaporation of the refrigerant both in the primary of the evaporator exchanger 3 and in the primary of the source exchanger 4.
  • the temperature measurement is associated with a measurement of the pressure PBP in order to better control the value of the superheating.
  • the heat pump 100 in priority heat production mode, makes it possible to continuously adjust the heat and cooling powers transmitted respectively through the condenser exchanger 2 and the evaporator heat exchanger 3, and therefore to regulate the temperature of the heat transfer fluid TCH by outlet of the secondary of the condenser exchanger 2 and the temperature of the heat transfer fluid TFR at the outlet of the secondary of the evaporator exchanger 3, at their set value.
  • the figure 3 represents the thermodynamic machine in a mode of operation called priority heat production and more particularly heat production alone.
  • the cooling capacity required by the cold consumer 300 is zero. All of the heat output produced by the thermodynamic machine 100 is therefore transferred to the heat consumer 200 through the condenser exchanger 2.
  • the black arrow 203 represents the extraction of heat from the machine 100 to the heat consumer 200.
  • the black arrow 403 represents the injection of heat from the external source to the refrigerant circuit.
  • the expansion valve 7 is completely closed, thus not allowing any refrigerant to pass through the primary of the exchanger.
  • evaporator 3 All of the refrigerant leaving the condenser exchanger 2 in the liquid state and at high pressure, is directed to the expansion valve 8 in which this refrigerant undergoes a drop in its pressure.
  • the fluid in the liquid state and at low pressure passes through the primary of the source exchanger 4 inside which the refrigerant evaporates by capturing heat at the external element. in contact with the secondary of the source exchanger 4.
  • the refrigerant in gaseous state and at low pressure joins the tank 14.
  • the degree of opening of the expansion valve 8 is advantageously controlled in order to ensure sufficient superheating of the refrigerant at the outlet of the source exchanger 4, thus ensuring the complete evaporation of the refrigerant in the primary of the source exchanger 4.
  • the embodiment illustrated at figure 3 represents a particular case of the operation illustrated in figure 2 where the cooling power consumed by the cold consumer 300 is zero.
  • the figure 4 represents the thermodynamic machine in substantially the same operating mode as that illustrated in figure 2 .
  • the figure represents an operating mode called balanced heat production, where the cooling power produced by the thermodynamic machine exactly reaches the cooling power required by the cold consumer 300.
  • thermodynamic machine 100 The whole of the heat power produced by the thermodynamic machine 100 is transferred to the heat consumer 200 through the condenser exchanger 2 as represented by the black arrow 203.
  • the whole of the refrigeration power produced by the refrigeration machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as represented by the black arrow 303.
  • the expansion valve 8 can be completely closed, thus not allowing any refrigerant to pass through the primary of the source exchanger 4. It is also It is possible to close the valves 12 and 13. Thus, all of the refrigerant leaving the liquid state and at high pressure from the condenser exchanger 2 is directed to the expansion valve 7 in which the refrigerant undergoes a reduction in its pressure. At the outlet of the regulator 7, the fluid the liquid state and at low pressure passes through the primary of the evaporator exchanger 3 inside which the refrigerant evaporates by capturing heat from the coolant circulating in the secondary of the evaporator exchanger 3.
  • the refrigerant in gaseous state and at low pressure joins the reservoir 14.
  • the opening rate of the expansion valve 7 is controlled in order to ensure sufficient superheating of the fluid. refrigerant at the outlet of evaporator exchanger 3, thus ensuring complete evaporation of the refrigerant in the primary of evaporator exchanger 3.
  • the figure 5 represents the thermodynamic machine in a mode of operation called priority refrigeration production.
  • the cooling power produced by the refrigerant circuit 1 is matched to the cooling power required by the cold consumer 300, and the heat output produced by the thermodynamic machine is at least equal to the heat output required by the consumer. heat 200.
  • the control circuit 500 regulates the cooling capacity to maintain the temperature TFR within a target range. All of the refrigerating power produced by the thermodynamic machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as represented by the black arrow 303.
  • the black arrow 403 represents heat extraction from the refrigerant circuit. to the external source.
  • the compressor output supplies the input of the first heat exchanger 2 and the first input / output of the third heat exchanger 4.
  • valve 10 is open and valve 11 is closed.
  • the second inlet / outlet of the third heat exchanger 4 is connected to the inlet of the second heat exchanger 3.
  • the valve 13 is open and the valve 12 is closed.
  • the refrigerant On leaving the compressor, the refrigerant is in the gaseous state and at high pressure and it passes through the first connection node 15 where it splits into two parts. A part of the refrigerant is directed towards the primary of the exchanger condenser 2, inside which the refrigerant condenses by giving up heat to the coolant circulating in the secondary of the exchanger condenser 2.
  • the refrigerant emerges from the condenser exchanger 2 in the liquid state and at high pressure, and at temperature T3. It is advantageous to close the valve 12 so that the refrigerant leaving the condenser exchanger 2 is directed towards the expansion valve 7.
  • the refrigerant in the liquid state undergoes a drop in its pressure inside the expansion valve 7. At the outlet of the regulator 7, the fluid in the liquid state and at low pressure is directed to the connection node 17.
  • the other refrigerant part is directed to the primary of the source exchanger 4 then operating as a condenser. Inside the source exchanger 4, the refrigerant condenses by transferring heat to the external element in contact with the secondary of the source exchanger 4.
  • the presence of the temperature sensor 43 is not essential for the operation of the machine.
  • a measurement of the temperature T4 makes it possible to verify that the value of the cooling of the refrigerant at the outlet of the primary of the source exchanger 4 is in the desired range when the source exchanger 4 operates as a condenser.
  • the temperature measurement is advantageously used to control that the refrigerant is in the liquid state at the outlet of the primary of the source exchanger 4. It is advantageous to combine the measurement of the temperature T4 with the measurement of the temperature. PHP pressure to control that the refrigerant is in the liquid state at the outlet of the primary of the source exchanger 4.
  • the refrigerant On leaving the primary of the source exchanger 4, the refrigerant is directed towards the expansion valve 8, in which the refrigerant in the liquid state undergoes a drop in its pressure.
  • the fluid in the liquid and low pressure is directed through the valve 13, which is open, to the connection node 17.
  • the refrigerant At the outlet of the primary of the evaporator exchanger 3, the refrigerant is in the gaseous state and at low pressure.
  • the refrigerant advantageously reaches the reservoir 14.
  • a second compressor 6 operating in all-or-nothing mode in association with the first compressor 5, the speed of rotation of which can be adjusted continuously. This allows a continuous adjustment of the cooling power transferred through the evaporator exchanger 3.
  • the control of compressors 5 and 6, combining the activation or deactivation of compressor 6 and the adjustment of the rotation speed of compressor 5, allows thus continuously adjusting the cooling power transmitted through the evaporator exchanger 3, and therefore regulating the outlet temperature of the heat transfer fluid TFR to its set value.
  • the opening rate of the expansion valves 7 and 8 can be controlled in order to ensure sufficient superheating of the refrigerant at the outlet of the primary of the evaporator exchanger 3, thus ensuring the complete evaporation of the refrigerant in the primary of the evaporator exchanger 3.
  • the measurement of the temperature T1 possibly in association with the measurement of the low pressure PBP, makes it possible to control that the value of the superheating of the refrigerant at the outlet of the evaporator exchanger 3 is in the desired range .
  • the control of the opening rates of the expansion valves 7 and 8, for example the relative value of the degree of opening of the expansion valve 7 compared to the degree of opening of the expansion valve 8, makes it possible to regulate the proportion of fluid passing through the exchanger condenser 2 .
  • Control of the proportion of fluid passing through the primary of the condenser exchanger 2 makes it possible to continuously adjust the power transmitted through the condenser exchanger 2, and therefore to regulate the outlet temperature of the heat transfer fluid TCH to its set value.
  • the figure 6 represents a particular mode of operation of what is illustrated on figure 5 and called refrigeration production only.
  • the heat output required by the hot consumer 200 is zero.
  • the totality of the cooling power produced by the thermodynamic machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as represented by the black arrow 303.
  • the totality of the heating power produced by the refrigeration machine 100 is transferred to the source 400 through the source exchanger 4 as represented by the black arrow 403.
  • valve 10 is open and the valve 11 is closed.
  • the expansion valve 8 On leaving the expansion valve 8, all of the refrigerant in liquid state and at low pressure is directed to the primary circuit of the evaporator exchanger 3, inside which the refrigerant evaporates by capturing heat at heat transfer fluid circulating in the secondary of the evaporator exchanger 3.
  • the valve 13 is open and the valve 12 is closed.
  • the opening rate of the expansion valve 8 is controlled so as to obtain overheating. sufficient refrigerant at the outlet of evaporator exchanger 3, thus ensuring complete evaporation of the refrigerant in the primary of evaporator exchanger 3.
  • the figure 7 represents another particular operating mode of that illustrated in figure 5 and called balanced refrigeration production.
  • the calorific power produced by the thermodynamic machine exactly reaches the calorific power required by the heat consumer. All of the refrigerating power produced by the thermodynamic machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as represented by the black arrow 303.
  • the refrigerant in the liquid state and at high pressure enters the expansion valve 7.
  • the refrigerant then undergoes a drop in its pressure.
  • all of the refrigerant in the liquid state and at low pressure is directed to the primary circuit of the evaporator exchanger 3, inside which the refrigerant evaporates by capturing heat the heat transfer fluid circulating in the secondary of the evaporator exchanger 3.
  • the opening rate of the expansion valve 7 is controlled so as to obtain sufficient superheating of the refrigerant at the outlet of evaporator exchanger 3, thus ensuring complete evaporation of the refrigerant in the primary of evaporator exchanger 3.
  • control circuit 500 modifies the state of the first and second switching devices so that they selectively define a circulation channel in which the third heat exchanger 4 is mounted in parallel with the first heat exchanger 2. or a circulation channel in which the third heat exchanger 4 is mounted in parallel with the second heat exchanger 3.
  • the figure 8 schematically shows another embodiment of a heat pump 100 comprising two separate refrigerant circuits 1 and 101. Each refrigerant circuit 1/101 supplies a primary of the multiple heat exchangers.
  • the first refrigerant circuit 1 is identical to what has been described previously in relation to the embodiments illustrated in figures 1 to 7 .
  • the two refrigerant circuits 1/101 are advantageously identical and each comprise a compressor 5/6 and 105/106 preferably arranged in the pipe which connects the second heat exchanger 3 with the first heat exchanger 2.
  • Each refrigerant circuit 1 and 101 comprises also two expansion valves 7, 8 and 107, 108.
  • the technical characteristics of the elements forming the second refrigerant circuit can take up the characteristics already indicated above for the first refrigerant circuit.
  • the second refrigerant circuit comprises six connection nodes arranged in an identical manner to what has been described above and it also comprises the two switching devices.
  • the second refrigerant circuit can also include a reservoir 114, as well as temperature sensors. Each temperature sensor of the second refrigerant circuit being a sensor equivalent to what has been described in the first refrigerant circuit.
  • the second refrigerant circuit 101 allows the circulation of a second refrigerant which may be identical or different to the first refrigerant in its composition.
  • the refrigerant circuit 101 advantageously comprises a pressure sensor 151 configured to measure the pressure PHP101 at the outlet of the compressor 105/106.
  • the refrigerant circuit 101 can also include another pressure sensor 152 configured to measure the pressure PBP101 at the inlet of the compressor 105/106.
  • the third expansion valve 107 makes it possible to lower the pressure of the second refrigerant when the latter circulates in the expansion valve 107 in the liquid state.
  • the refrigerant circuit 101 also includes a fourth expansion valve 108 which is advantageously controlled electronically.
  • the fourth expansion valve 108 is bidirectional and makes it possible to lower the pressure of the refrigerant when the latter circulates in the expansion valve 108 in the liquid state.
  • the second refrigerant circuit 101 comprises a first refrigerant temperature sensor 132 configured to measure the temperature T101 at the outlet of the second primary circuit of the evaporator exchanger 3.
  • the second refrigerant circuit 101 comprises a second refrigerant temperature sensor 142 configured to measure the temperature T102 of the refrigerant at the outlet of the second primary circuit of the source exchanger 4 when the latter operates as an evaporator.
  • the second refrigerant circuit 101 comprises a third refrigerant temperature sensor 123, configured to measure the temperature T103 of the refrigerant at the outlet of the second primary circuit of the exchanger condenser 2.
  • the second refrigerant circuit 101 also comprises a fourth refrigerant temperature sensor 143 configured to measure the temperature T104 of the refrigerant at the outlet of the second primary circuit of the source exchanger 4 when the latter operates as a condenser.
  • the heat pump 100 with two refrigerant circuits can operate according to the same production modes as those illustrated in figures 2 , 3 , 4 , 5 , 6 and 7 .
  • the two refrigerant circuits are connected to the same heat exchangers and the two refrigerants circulate identically in the two circuits.
  • the first switching device of the first refrigerant circuit is in the same state as the first switching device of the second circuit refrigerant.
  • the second switching device of the first refrigerant circuit is in the same state as the second switching device of the second refrigerant circuit.
  • the two refrigerant circuits 1 and 101 illustrated on figure 8 are considered as two thermodynamic sub-assemblies which can operate independently.
  • Each of the two refrigerant circuits 1 and 101 can operate independently according to one or the other of the two modes which are the priority heat production mode, including the special cases of heat production alone and balanced heat production, and the production mode priority refrigeration, including the special cases of refrigeration production alone and balanced refrigeration production.
  • the figures 9 and 10 give two exemplary embodiments of two operating modes of refrigerant circuits 1 and 101.
  • the heat power produced by the thermodynamic machine 100 is matched to the heat power required by the heat consumer 200, and the cooling power produced by the thermodynamic machine exceeds the cooling power required by the heat pump. cold consumer 300.
  • thermodynamic machine 100 All of the calorific power produced by the thermodynamic machine 100 is transferred to the heat consumer 200 through the condenser exchanger 2 as represented by the black arrow 203.
  • Part of the refrigeration power produced by the refrigeration machine 100 corresponding to the cooling power required by the cold consumer 300, is transferred to the cold consumer 300 through the evaporator exchanger 3 as represented by the black arrow 303.
  • thermodynamic machine 100 which has not been transferred to the cold consumer 300, is transferred to the source 400 through the source exchanger 4 as shown by the figure. black arrow 403.
  • thermodynamic machine Even if the thermodynamic machine operates globally according to the priority heat production mode, each of the two circuits 1 and 101 operates in a mode of its own.
  • the refrigerant circuit 1 operates according to the priority refrigeration production mode in the special case called balanced refrigeration production, where the calorific power produced by the refrigerant circuit 1 is entirely transferred to the heat consumer 200.
  • This operating mode of the refrigerant circuit 1 is identical to the operating mode of the thermodynamic machine 100 with a single refrigerant circuit, which is illustrated in figure 7 .
  • the refrigerant circuit 101 for its part operates according to the priority heat production mode in the special case called heat production alone, where the cooling power produced by the refrigerant circuit 101 is entirely transferred to the source.
  • This operating mode of the refrigerant circuit 101 is identical to the operating mode of the thermodynamic machine 100 with a single refrigerant circuit, which is illustrated in figure 3 .
  • valve 11 and expansion valve 8 are closed. All the refrigerant in the gaseous state and at high pressure at the outlet of the compressors 5 and 6 is directed to a first primary circuit of the condenser exchanger 2, inside which the refrigerant condenses by releasing heat to the heat transfer fluid circulating in the secondary of this exchanger condenser 2.
  • the valve 12 At the outlet of the primary of the condenser exchanger 2, the valve 12 is closed and all of the refrigerant in the liquid state and at high pressure enters the expansion valve 7. The refrigerant undergoes a drop in pressure, then it is directed towards a first primary circuit of the evaporator exchanger 3, inside which it evaporates by capturing heat from the coolant circulating in the secondary of this evaporator exchanger 3. At the outlet of the first primary circuit of the evaporator exchanger 3, the refrigerant in gaseous state and at low pressure goes to tank 14 then compressors 5 and 6.
  • the expansion valve 107 At the outlet of the second primary circuit of the exchanger condenser 2, the expansion valve 107 being closed, all of the refrigerant in the liquid state and at high pressure is directed through the valve 112, which is open, towards the expansion valve 108
  • the refrigerant undergoes a lowering of its pressure, then it enters the second primary circuit of the source exchanger 4, which then operates as an evaporator, and inside which the refrigerant evaporates by capturing heat from the external element being in contact with the secondary of this source exchanger 4.
  • the refrigerant in gaseous state and at low pressure joins the reservoir 114 then compressors 105 and 106.
  • the refrigerant circuit 1 produces part of the heat energy transferred to the heat consumer 200 as well as all of the refrigeration energy transferred to the cold consumer 300, with an energy yield corresponding to the temperatures required at the secondary of the condenser exchanger 2 and the secondary of the evaporator exchanger 3.
  • the refrigerant circuit 101 produces the other part of the heat energy transferred to the heat consumer 200 as well as all of the refrigeration energy transferred to the source 400, with an energy output corresponding to the temperatures required at the secondary of the condenser exchanger 2 and at the secondary of the source exchanger 4.
  • each of the two refrigerant circuits 1 and 101 then operates with its own efficiency, thus optimizing the overall efficiency of the thermodynamic machine 100.
  • the figure 10 illustrates another particular mode of operation of a thermodynamic machine illustrated on figure 8 , and operating globally according to the mode called priority refrigeration production.
  • the cooling power produced by the thermodynamic machine 100 is matched to the cooling power required by the cold consumer 300, and the heat output produced by the thermodynamic machine exceeds the heat output required by the heat consumer 200.
  • thermodynamic machine 100 All of the refrigeration power produced by the thermodynamic machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as represented by the black arrow 303. Part of the heat output produced by the refrigeration machine 100, corresponding to the calorific power required by the heat consumer 200, is transferred to the heat consumer 200 through the condenser exchanger 2 as represented by the black arrow 203. Finally, the remaining part of the calorific power produced by the refrigeration machine 100, not necessary for the heat consumer 200, is transferred to the source 400 through the source exchanger 4 as represented by the black arrow 403.
  • each of the two circuits 1 and 101 operates according to its own mode.
  • the refrigerant circuit 1 operates according to the priority refrigeration production mode in the particular case called refrigeration production alone, where the calorific power produced by the refrigerant circuit 1 is entirely transferred to the source.
  • This operating mode of the refrigerant circuit 1 is identical to the operating mode of the thermodynamic machine 100 with a single refrigerant circuit, which is illustrated in figure 6 .
  • the refrigerant circuit 101 for its part, operates according to the priority heat production mode in the particular case called balanced heat production, where the cooling power produced by the refrigerant circuit 101 is entirely transferred to the cold consumer.
  • This operating mode of the refrigerant circuit 101 is identical to the operating mode of the thermodynamic machine 100 with a single refrigerant circuit, which is illustrated in figure 4 .
  • refrigerant circuit 1 expansion valve 7 and valve 12 are closed. All of the refrigerant in the gaseous state and at high pressure at the outlet of the compressor is directed to the first primary circuit of the source exchanger 4, which then operates as a condenser, and inside which the refrigerant condenses by transferring heat to the external element in contact with the secondary of this source exchanger 4.
  • the refrigerant in gaseous state and at low pressure reaches the reservoir 14 then the compressors 5 and 6.
  • the valve 110 is closed. All the refrigerant in the gaseous state and at high pressure at the outlet of the compressor is directed to the second primary circuit of the exchanger condenser 2, inside which the refrigerant condenses by releasing heat to the heat transfer fluid circulating at the secondary of this exchanger condenser 2.
  • the expansion valve 108 is closed. All of the refrigerant in the liquid state and at high pressure is directed to the expansion valve 107 in which the refrigerant undergoes a lowering of its pressure, then it enters the second primary circuit of the evaporator exchanger 3, inside from which the refrigerant evaporates by capturing heat from the heat transfer fluid circulating in the secondary of this evaporator exchanger 3.
  • the refrigerant in gaseous state and at low pressure joins the reservoir 114 then the compressor.
  • the refrigerant circuit 1 produces part of the refrigeration energy transferred to the cold consumer 200 as well as all of the heat energy transferred to the source 400, with an energy yield corresponding to the temperatures required at the secondary of the 'evaporator exchanger 3 and at the secondary of source exchanger 4.
  • the refrigerant circuit 101 produces the other part of the refrigeration energy transferred to the cold consumer 300 as well as all of the heat energy transferred to the heat consumer 200 , with an energy yield corresponding to the temperatures required at the secondary of evaporator exchanger 3 and at the secondary of condenser exchanger 2.
  • each of the two refrigerant circuits 1 and 101 then operate with its own efficiency, thus optimizing the overall efficiency of the thermodynamic machine 100.
  • thermodynamic machine 100 makes it possible to simultaneously produce heat energy and cooling energy, supplying respectively a heat consumer and a cold consumer, and to exchange directly with an external source the residue of thermal energy produced but not used by consumers.
  • this is the residue of cooling energy produced but not used by the cold consumer.
  • priority refrigeration production mode this is the residual heat energy produced but not used by the heating consumer.
  • thermodynamic machine 100 also makes it possible to continuously regulate both the starting temperature of the heat transfer fluid to the heating energy consumer and the leaving temperature of the heat transfer fluid to the cooling energy consumer, thus continuously adjusting to both the calorific power and the cooling power supplied respectively to the heat consumer and to the cold consumer.
  • the thermodynamic machine has a control circuit 500 which is configured to define an operating mode in which the first switching device and the second switching device of the first refrigerant circuit 1 prevent the circulation of the refrigerant in the first heat exchanger 2 and simultaneously the first and the second switching devices of the second refrigerant circuit 101 prevent the circulation of the second refrigerant in the third heat exchanger 4.
  • the control circuit 500 can also be configured to define an operating mode in which the first switching device and the second switching device of the first refrigerant circuit prevent the circulation of refrigerant in the third heat exchanger 4 and simultaneously the first and second switching devices of the second refrigerant circuit 101 prevent the circulation of the second refrigerant in the second heat exchanger 3 .
  • thermodynamic machine is configured to regulate the heat power and the cooling power simultaneously which is not achieved by the machines of the prior art.
  • thermodynamic machine is configured to produce heat energy for heating and / or domestic hot water production applications, for example requiring the heating of a heat transfer fluid to a temperature between 20 ° C and 100 ° C. ° C.
  • the thermodynamic machine can also be configured to produce cooling energy for coolant cooling applications preferably in the range 0 ° C - 20 ° C.

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EP19167757.4A 2019-04-08 2019-04-08 Thermodynamische maschine vom typ wärmepumpe zum erzeugen von wärme und kälte, und ihr funktionsverfahren Active EP3722703B1 (de)

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EP19167757.4A EP3722703B1 (de) 2019-04-08 2019-04-08 Thermodynamische maschine vom typ wärmepumpe zum erzeugen von wärme und kälte, und ihr funktionsverfahren

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3431452A1 (de) * 1984-08-27 1986-02-27 Bosch-Siemens Hausgeräte GmbH, 7000 Stuttgart Als waermepumpe genutztes kuehl- oder gefriergeraet
FR2886388A1 (fr) * 2005-05-31 2006-12-01 Climatik Sarl Systeme de chauffage et de refrigeration
CN107449175A (zh) * 2017-08-01 2017-12-08 青岛理工大学 基于低温水蓄热的水环及空气源热泵供热系统
WO2018200868A1 (en) * 2017-04-26 2018-11-01 M-Trigen, Inc. Systems, apparatus, and methods for providing thermal balance

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3431452A1 (de) * 1984-08-27 1986-02-27 Bosch-Siemens Hausgeräte GmbH, 7000 Stuttgart Als waermepumpe genutztes kuehl- oder gefriergeraet
FR2886388A1 (fr) * 2005-05-31 2006-12-01 Climatik Sarl Systeme de chauffage et de refrigeration
WO2018200868A1 (en) * 2017-04-26 2018-11-01 M-Trigen, Inc. Systems, apparatus, and methods for providing thermal balance
CN107449175A (zh) * 2017-08-01 2017-12-08 青岛理工大学 基于低温水蓄热的水环及空气源热泵供热系统

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