EP2318783B1 - Reversibles system zur rückgewinnung von wärmeenergie durch entnahme und übertragung von wärmeenergie von einem oder mehreren medien in ein oder mehrere andere solcher medien - Google Patents

Reversibles system zur rückgewinnung von wärmeenergie durch entnahme und übertragung von wärmeenergie von einem oder mehreren medien in ein oder mehrere andere solcher medien Download PDF

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Publication number
EP2318783B1
EP2318783B1 EP09761796.3A EP09761796A EP2318783B1 EP 2318783 B1 EP2318783 B1 EP 2318783B1 EP 09761796 A EP09761796 A EP 09761796A EP 2318783 B1 EP2318783 B1 EP 2318783B1
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point
refrigerant
heat exchanger
exchanger
fluid
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EP09761796.3A
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English (en)
French (fr)
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EP2318783A1 (de
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Jean-Luc Maire
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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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/004—Outdoor unit with water as a heat sink or heat source
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/009—Compression machines, plants or systems with reversible cycle not otherwise provided for indoor unit in circulation with outdoor unit in first operation mode, indoor unit in circulation with an other heat exchanger in second operation mode or outdoor unit in circulation with an other heat exchanger in third operation mode
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F25B2313/02331—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during cooling
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way valves
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B40/04—Desuperheaters
    • 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
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits

Definitions

  • the invention relates to a reversible recovery system by sampling and transfer of energy between at least two different media, for example between an external environment and a living environment or between a living environment and another living environment.
  • the caloric requirements in cold periods of a place of life, work or storage can be summed up in a quantity of calories devoted to heating.
  • Other caloric needs are needed during the cold season and even outside of it, we can identify the production of domestic hot water that must be provided all year, the heating of a swimming pool or other needs in the industrial or tertiary field.
  • the invention uses an innovative technology in the field of reversible heat pumps.
  • Heat pumps are refrigeration machines that transfer heat from one medium to another by using as a vehicle a refrigerant passing successively from a gaseous state to a liquid state and vice versa by the succession of compression and expansion phases.
  • Heat pumps and other energy recovery systems are characterized by a performance index (COP) that indicates the performance energy efficiency of the installation, that always being greater than 1, the heat pumps thus produce more heat energy than they consume of electrical energy thanks to the energy drawn from the free recovery medium.
  • COP performance index
  • the invention proposes an improvement which is achieved by a new organization of the refrigerant circuit and the creation of components having new functions, the objective of the invention being to increase the efficiency and the reliability of the refrigeration system.
  • this exchanger E3 is to function as under cooler of the liquid line when it is supplied with high pressure fluid in the liquid state in its inner tube and also as superheater of the suction gases in its outer tube (FIGS. 1, 2, 8, 11, 12, 18).
  • the refrigerant reservoir R contains a reserve of high pressure fluid in the liquid state.
  • the other particularity of the fluid / fluid exchanger E3 is that it functions as a degasser when it is supplied with low pressure fluid in the liquid state in its inner tube and also as a superheater for the suction gases in its external tube (FIGS. No. 4, 5, 6, 7, 14, 15, 16, 17).
  • the Refrigerant reservoir R contains a reserve of low pressure fluid in the liquid state with a variable ratio of fluid to the gaseous state.
  • valves VEM1 and VEM2 allow the operation of the exchanger E2 as a condenser with either the exchanger E4 as an evaporator or the exchanger E1 as an evaporator.
  • the presence and location of the regulator D2 increases the efficiency of the refrigeration system by allowing a different condensing pressure between the compressor CP1 and the compressor CP2 in the case of a heat production on the exchanger E2 and on the exchanger E1 with the valve V3 N ° 1 closed and the two compressors CP1 and CP2 in functions ( Figure N ° 18).
  • valves and expansion valves allow the possibility of managing in an isolated way the different heat exchangers and thus of being able to couple them in different combinations, this organization also allows the easy integration of one or more additional exchangers (Example in Figure N ° 8 ).
  • the invention makes it possible to oversize the energy recovery battery on the external medium and to increase its efficiency (E4 Figures 1 to 18 ).
  • the invention also allows the installation of a non-reversible heat exchanger which can be used in the desuperheater mode of the discharge gases of the compressor (s), or can be used in condenser mode for a total restitution of the energy of the refrigerant condensed in that or be used in partial condensation mode for partial recovery of the calories of the refrigerant flowing through this exchanger.
  • This exchanger is called E2 and is connected to a hydraulic circuit for a heat energy distribution to one or more media in calorie demand, this exchanger is not reversible.
  • the invention also allows the installation of a reversible heat exchanger which can be used in condenser mode of the discharge gas or compressors for a total return of the energy of the refrigerant condensed in it, or be used in evaporator for a total evacuation of the cooling energy of the refrigerant flowing through this exchanger.
  • This exchanger is called E1 and is connected to a hydraulic circuit for a distribution of heat or cooling energy to one or more media. requests for calories or frigories.
  • the invention also allows the heat exchanger E1 to recover the heat energy not absorbed by the exchanger E2 when it is in desuperheater mode or if E2 is in partial condensation mode.
  • the invention thus allows the energy transfer function which means the possibility of recovering calories on the exchanger E1 in evaporator mode for the production of chilled water on the hydraulic circuit E1 and at the same time the return of these calories for the heating of the hydraulic circuit E2 via the exchanger E2 in condenser mode or desuperheater mode. Either for an electrical consumption of 1kw, a refrigerated production of 3.5 KW and heat of 4.5 KW with a single machine.
  • This function is useful and very economical when a building is air conditioned and there is a simultaneous demand for heat production for the production of domestic hot water or the heating of a swimming pool.
  • an exchanger fluid / fluid E 3 It is composed of an internal cylinder which opens only on three nipples N ° 6, N ° 7 and N ° 19 (FIGURES N ° 9 and N ° 10 ), and an outer cylinder which opens on three nozzles No. 10, No. 11 and No. 12 (FIGURES No. 9 and No. 10).
  • the fact that the inner cylinder has been placed in the outer cylinder serves only to effect a heat exchange between the cold refrigerant passing through the outer tube before being sucked by the compressor or compressors and the hotter refrigerant through the tube internal.
  • the heat exchange is through the wall of the inner tube in the section in contact with the refrigerant contained in the outer tube.
  • the purpose of the small section tube at point 19 is to evacuate a part of the fluid in the gaseous state created by the expansion valve by the expander D1 when the latter is passed from point 8 to point 7.
  • the inner cylinder is fed with low pressure liquid refrigerant with a minority ratio of fluid in the gaseous state.
  • the purpose of the tube of small section at point 19 is to reduce the ratio of fluid in the gaseous state by evacuating it from the inner tube at point 19 towards point 20.
  • the function of capillary 2 is to limit the flow rate of point 19 to point 20 so as not to discharge fluid in the liquid state.
  • the pressure drops of this capillary must be calculated so that the volume of refrigerant in the gaseous state discharged from point 19 to point 20 is less than the volume of gaseous refrigerant generated by the expander D1 when this it is crossed by the fluid from point 8 to point 7.
  • the fluid / fluid exchanger E3 is an innovative cooling unit whose function is to cool the high pressure liquid and superheat the suction gases when the exchanger E1 is in condenser mode.
  • the diameter of the inner cylinder is at least 4 times greater than the liquid line at points 6 and 7 (FIGURES No. 9 and No. 10)
  • the high-pressure fluid in gaseous form will inevitably be recovered largely at the top of the cylinder. internal and part of this fluid will be condensed by the frigories recovered on the suction gas passing through the outer cylinder.
  • FIG. 1 is shown the operation of the system with one compressor out of two in function and a heat production ensured on the exchanger E1 and E2.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore colder than at point N ° 1.
  • the refrigerant passes through the valve V3 No. 1, the point No. 3, the point No. 4 and the point No. 20 to then enter the exchanger E1.
  • the refrigerant condenses in exchanger E1 and leaves it in high pressure liquid form at point No. 5.
  • the fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.
  • the fluid temperature is 35 ° C.
  • the high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.
  • the temperature at point 7 will be 30 ° C or sub-cooling of 5 ° C thanks to the exchanger E3.
  • the fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8.
  • the temperature of the fluid at point 8 is -15 ° C.
  • the fluid passes through the exchanger E4 which is ventilated by the fan VENT.
  • the fluid boils while evacuating the frigories on the through air E4.
  • the refrigerant leaves E4 at point 9 in low pressure gaseous form will be -10 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is -5 ° C.
  • FIG. 2 shows the operation of the system with two compressors in operation and a heat production provided on the exchanger E1 and E2.
  • the presence of the exchanger E3 in this case is innovative because it is placed on a high pressure liquid section of the refrigerant circuit which is not always supplied with high pressure liquid in its inner tube.
  • the design and the innovative location of the E3 exchanger allow this body to perform different functions according to the calorie and frigory needs of the different exchangers installed.
  • the exchanger E3 serves as superheater for the suction gases, undercooler for the high pressure liquid before the expander D1 and makes it possible to store a large quantity of fluid in the liquid state in its inner tube.
  • the superheating of the suction gases and the subcooling of the liquid before the expansion valve D1 makes it possible to increase the percentage of fluid in the liquid state in the exchanger E4 and thus to increase the average coefficient of conductivity of the exchanger E4, a gain for the overall energy efficiency.
  • the temperature of the high pressure fluid at point 13 is 90 ° C.
  • the fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.
  • the fluid temperature is 40 ° C
  • the high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.
  • the temperature at point 7 will be 35 ° C, a subcooling of 5 ° C thanks to the exchanger E3.
  • the fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8.
  • the fluid temperature at point 8 is -18 ° C.
  • the fluid passes through the exchanger E4 which is ventilated by the fan VENT.
  • the fluid boils while evacuating the frigories on the through air E4.
  • the refrigerant leaves E4 at point 9 in low pressure gaseous form.
  • the fluid temperature at point 9 will be -13 ° C.
  • the fluid passes through V3 N ° 2 for point 10.
  • the fluid enters the outer tube of exchanger E3 and is superheated in contact with the inner tube of exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and 12 and is sucked by the compressors CP1 and CP2.
  • the fluid temperature at point 12 is -8 ° C.
  • FIG. 3 is shown the operation of the system with one compressor out of two in function and a heat production ensured on the exchanger E2.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the refrigerant leaving the exchanger E2 at point 2 is condensed and is colder than at point N ° 1.
  • the fluid passing through the expander D2 is expanded and is therefore in low pressure liquid form with a minority gas phase ratio at point 18.
  • the temperature of the fluid at point 18 is -15 ° C.
  • the fluid passes through the exchanger E4 which is ventilated by the fan VENT.
  • the fluid boils while evacuating the frigories on the through air E4.
  • the refrigerant leaves E4 at point 9 in low pressure gaseous form.
  • the fluid temperature at point 9 will be -10 ° C.
  • the fluid enters the outer tube of the exchanger E3, because the flow of refrigerant in the inner cylinder of the exchanger E3 is zero, no overheating of the suction gas is performed.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the temperature of the refrigerant at point No. 11 is the same as at point No. 10.
  • the presence of the exchanger E3 in this case is innovative because it is placed on a low pressure liquid section of the refrigerant circuit which is not always supplied with low pressure liquid in its inner tube.
  • the design and the innovative location of the E3 exchanger allow this body to perform different functions according to the calorie and frigory needs of the different exchangers installed.
  • the exchanger E3 has its internal tube cooled by the suction gases passing through its external tube, this enables it to store at 100% of its capacities a large quantity of fluid in the liquid state in its tube. internal.
  • This function is important because the exchanger E1, not being supplied with fluid, is empty of all its fluid in the liquid state, it is therefore useful to be able to store this fluid in the volume of the inner cylinder of the exchanger E3 which remains cold to him.
  • FIG. 4 shows the operation of the system with one compressor out of two in operation and a heat production ensured on the exchanger E2 and a refrigeration production ensured on the exchanger E1.
  • This mode of function is called energy transfer.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the fluid is condensed to 100% in the exchanger E2.
  • the refrigerant leaving the exchanger E2 at point 2 is condensed and is colder than at point N ° 1.
  • the refrigerant passes through the point 15, the filter F, the point 16, the open valve VEM1, the point 17, the point 8 and the expander D1.
  • the fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.
  • the fluid temperature at point 7 is + 10 ° C.
  • the fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.
  • the ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.
  • the low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor No. 1.
  • the fluid passes through the capillary 1 which has a loss of pressure equivalent to a temperature drop of 9 ° C.
  • the fluid being expanded by the capillary passes through point 5 with a temperature of +1 ° C.
  • the fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.
  • the fluid temperature at point 10 will be + 5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is + 7 ° C
  • the presence of the exchanger E3 in this case is innovative because it is placed on a low pressure liquid section of the refrigerant circuit which is not always supplied with low pressure liquid in its inner tube.
  • the design and the innovative location of the E3 exchanger allow this body to perform different functions according to the calorie and frigory needs of the different exchangers installed.
  • the exchanger E3 has its internal tube cooled by the suction gases passing through its external tube, the inner tube being fed with a low-pressure liquid with a percentage of fluid in the gaseous state, it is advisable to minimize the amount of fluid in the gaseous state, the exchanger E3 allows this function by discharging a portion of this gas via the tube 19 and condensing another part of this gas due to the cooling caused by the cold gases through the outer tube of the exchanger E3.
  • the exchanger E1 would have a reduced efficiency due to a smaller amount of fluid in the liquid state in the refrigerant circuit at point 5 and in the exchanger E1 in evaporator mode. this would decrease the average coefficient of conductivity in the exchanger E1 and thus the energy efficiency of the assembly.
  • FIG. 5 shows the operation of the system with one compressor out of two in operation, a heat production ensured on the exchanger E2 and E4 and a refrigeration production ensured on the exchanger E1.
  • This function mode is called partial energy transfer.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the fluid is desuperheated or partially condensed in the exchanger E2.
  • the refrigerant leaving the exchanger E2 at point 2 is desuperheated and in the high pressure gas state.
  • the refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 or it is condensed to 100%.
  • the fan VENT is in operation for the cooling of the exchanger E4.
  • the heat dissipation is done on the exchanger E2 in favor of the water circuit E2 and on the exchanger E4 to evacuate excess heat energy to the outside.
  • This function is useful for the storage of domestic hot water with a temperature higher than 65 ° C for the elimination of bacteria in summer.
  • the fluid exits the exchanger E4 at point 8, through the expander D1.
  • the fluid passing through the expander D1 is expanded and is therefore in low pressure liquid form with a minority gas phase ratio at point 7.
  • the temperature of the fluid at point 7 is + 10 ° C.
  • the fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.
  • the ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.
  • the gaseous low-pressure refrigerant then passes through the capillary 2, the non-return valve C2, the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor N ° 1 ;
  • the fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C
  • the fluid being expanded by the capillary passes through point 5 with a temperature equal to +1 ° C.
  • the fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.
  • the fluid temperature at point 10 will be + 5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is + 7 ° C.
  • FIG. 6 is represented the operation of the system with two compressors out of two in function, a heat production ensured on the exchanger E4 for defrosting and a refrigeration production ensured on the exchanger E1.
  • This function mode is called the defrost mode.
  • the defrosting of the external battery is used to remove the ice that closes and isolates the outer coil battery which recovers the heat energy from the outside air.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2.
  • the circulator P2 is stopped in order not to transmit the calories to the water circuit E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore in the gaseous state at high pressure and at the same temperature as at point 1.
  • the refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 or it is condensed to 100%.
  • the VENT fan is off to conserve all the heat energy of the refrigerant for defrosting the battery.
  • the fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.
  • the fluid temperature at point 7 is + 10 ° C.
  • the fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.
  • the ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.
  • the low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor No. 1.
  • the fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C.
  • the fluid being expanded by the capillary passes through point 5 with a temperature of +1 ° C.
  • the fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.
  • the fluid temperature at point 10 will be + 5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is + 7 ° C.
  • the compressor CP2 is activated to reduce the defrost duration by increasing the defrosting power by a level equal to the power consumption of the compressor CP2.
  • Compressor CP2 delivers the refrigerant to point 13.
  • the refrigerant passes point 4, the three-way valve No. 2, the point 10, the exchanger E3 and is sucked by the compressor CP2 after point 13.
  • the gas thus conveyed was responsible for the heat energy consumed by the compressor No. 2 and allows to superheat the mixed suction gases of the two compressors in the outer tube of the fluid / fluid exchanger E3.
  • FIG. 7 shows the operation of the system with one of two compressors in operation, a heat production provided on the exchanger E4 for evacuating the calories outside the building and a refrigerating production ensured on the exchanger E1.
  • This function mode is called simple chilled water production mode.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • N ° 1 For example, we can have a reference temperature at point N ° 1 of 80 ° C
  • the fluid passes through the exchanger E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore in the gaseous state at high pressure and at the same temperature as at point 1.
  • the refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 where it is condensed to 100%.
  • the VENT fan is turned on to cool the E4 outer fin exchanger.
  • the fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.
  • the temperature of the fluid at point 7 is + 10 ° C.
  • the fluid enters the cylinder internal fluid / fluid E3 exchanger in low pressure liquid state and at a temperature of 10 ° C with a variable ratio of low pressure fluid in the gaseous state.
  • the ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.
  • the gaseous low-pressure refrigerant then passes through the capillary 2, the non-return valve C2, the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor N ° 1 ;
  • the fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C.
  • the fluid being expanded by the capillary passes through point 5 with a temperature of +1 ° C.
  • the fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.
  • the fluid temperature at point 10 will be + 5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is + 7 ° C.
  • FIG. 8 is shown the operation of the system with two compressors out of two in function and a heat production ensured on the exchanger E1 and E2.
  • the peculiarity of the figure 8 is to represent the addition of an additional exchanger E5 supplied with water by an additional water circuit which would serve as an example of recovering calories on the extraction of air from a building.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • N ° 1 For example, we can have a reference temperature at point N ° 1 of 90 ° C
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore colder than at point N ° 1.
  • the refrigerant passes through the valve V3 N ° 1, the point N ° 3, the point N ° 4 and N ° 20 to then enter the exchanger E1.
  • the refrigerant condenses in exchanger E1 and leaves it in high pressure liquid form at point No. 5.
  • the fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.
  • the fluid temperature is 35 ° C.
  • the high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.
  • the temperature at point 7 will be 30 ° C or sub-cooling of 5 ° C thanks to the exchanger E3.
  • the fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8.
  • the temperature of the fluid at point 8 is -15 ° C.
  • the fluid passes through the exchanger E4 which is ventilated by the fan VENT.
  • the fluid boils while evacuating the frigories on the through air E4.
  • a branch derives a portion of the fluid in the high pressure liquid state to the expander D3.
  • the fluid passes through the expansion valve D3 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase.
  • the fluid temperature at point 8 is +1 ° C.
  • the fluid passes through the exchanger which is supplied with water by the circulator P3.
  • the feed water of the E5 exchanger has a temperature + 12 ° C inlet temperature and + 7 ° C outlet temperature.
  • the low pressure refrigerant boils and exits in the gaseous state of the exchanger 6 and then passes through the regulation valve P.
  • the control valve P is an automatic constant pressure valve which maintains the pressure of the refrigerant in the exchanger E5 at a minimum equivalent value of 0 ° C so that the evaporation temperature is higher than the ice setting temperature. of the E3 water circuit.
  • the fluid temperature at point 9 will be -5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid temperature at point 11 and 12 is + 1 ° C.
  • the compressor CP2 draws the low-pressure gas at point 12 and discharges at point 13 the high-pressure gaseous fluid.
  • FIG. 9 explains the operation of the fluid / fluid exchanger E3 corresponding to the figures 1 , 2 and 8 .
  • the temperature of this fluid can be, for example, at a temperature of -10 ° C.
  • This flow of cold fluid in the gaseous state is in contact with the outer wall of the inner tube of the fluid / fluid exchanger E3.
  • the inner tube being fed with high pressure fluid in the liquid state and at a temperature, for example, 60 ° C, the flow of low pressure refrigerant gas from the point 10 and out at point 11 to be sucked by the compressor N ° 1 and the point 12 to be sucked by the compressor No. 2, is heated by the outer wall of the inner tube of the exchanger E3.
  • the temperature at point 11 and 12 may be 10 ° C higher than point 10.
  • the diameter of the inner tube must be at least 5 times greater than the diameter of the connections 6 and 7 so that the flow of the tube 6 does not pass directly to the tube 7.
  • the temperature of this fluid may be, for example, at a temperature of + 6 ° C.
  • This flow of cold fluid in the gaseous state is in contact with the outer wall of the inner tube of the fluid / fluid exchanger E3.
  • the inner tube being supplied at point 7 with low pressure fluid in the liquid state and at a temperature of, for example, + 10 ° C., the flow of low pressure refrigerant gas from point 10 and exiting at point 11 to be sucked by the compressor No. 1 and the point 12 to be sucked by the compressor No. 2, is heated by the outer wall of the inner tube of the exchanger E3.
  • the temperature at point 11 and 12 may be 2 ° C higher than point 10.
  • the low-pressure liquid in the liquid state which enters the inner tube of the exchanger E3 is cooled by the wall of the inner tube in contact with the cold gases of the outer tube.
  • the diameter of the inner tube must be at least 5 times greater than the diameter of the connections 7 and 6 so that the flow of the tube 7 does not pass directly to the tube 6.
  • the low pressure liquid that enters the inner tube of the exchanger E3 is in the liquid state with a low ratio in the gaseous state of the fact relaxation in D1.
  • the heat exchange in E3 will have the effect of cooling the inner tube and thus condense a small portion of the low pressure fluid in the gaseous state present at the top of the inner tube.
  • the flow of gas will be limited by the capillary 2 which will be calibrated so as not to be able to evacuate the entire gas bag at the top of the inner tube of the exchanger E3.
  • the capillary can be replaced by a thermostatic expansion valve with an overheating set to 5 ° C.
  • the fluid ratio in the liquid state at point 6 is greater than the liquid ratio present at point 7.
  • R is a refrigerant reservoir.
  • this version is particularly suitable for single-compressor machines or machines with at least two compressors but with a discharge pipe of compressor No. 2 which joins the discharge pipe of compressor No. 1 in point 1 instead of joining in point 4 as indicated on the Figures 1 to 8 .
  • the regulator D2 is eliminated and the pipe passing at point 17 leads to point 6 instead of reaching point 8 as indicated in Figures 1 to 8 .
  • FIG. 11 the path of the fluid is identical to that of FIG. In FIG. 11 is shown the operation of the system with a compressor on two in function and a heat production ensured on the exchanger E1 and E2.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore colder than at point N ° 1.
  • the refrigerant passes through the valve V3 No. 1, the point No. 3, the point No. 4 and the point No. 20 to then enter the exchanger E1.
  • the refrigerant condenses in exchanger E1 and leaves it in high pressure liquid form at point No. 5.
  • the fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.
  • the fluid temperature is 35 ° C.
  • the high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.
  • the temperature at point 7 will be 30 ° C or sub-cooling of 5 ° C thanks to the exchanger E3.
  • the fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8.
  • the fluid temperature at point 8 is -15 ° C.
  • the fluid passes through the exchanger E4 which is ventilated by the fan VENT.
  • the fluid boils while evacuating the frigories on the through air E4.
  • the fluid temperature at point 9 will be -10 ° C.
  • the fluid passes through V3 N ° 2 for point 10.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is -5 ° C.
  • the presence of the exchanger E3 in this case is innovative because it is placed on a high pressure liquid section of the refrigerant circuit which is not always supplied with high pressure liquid in its inner tube.
  • the innovative design and location of the E3 exchanger allows this unit to have different functions depending on the calorie and frigory needs of the different heat exchangers installed.
  • the exchanger E3 serves as a superheater for the suction gases, a subcooler for a high-pressure liquid before the expander D1 and makes it possible to store a large quantity of fluid in the liquid state in its inner tube.
  • the superheating of the suction gases and the subcooling of the liquid before the expansion valve D1 makes it possible to increase the percentage of fluid in the liquid state in the exchanger E4 and thus to increase the average conductivity coefficient of the exchanger E4, a gain for the energy efficiency of the whole.
  • FIG. 12 shows the operation of the system with two compressors in operation and a heat production provided on the exchanger E1 and E2.
  • FIG. 12 The operation described in FIG. 12 is close to the operation described in FIG. 11, the differences are described below: Increase in the mass flow of fluid due to the commissioning of compressor No. 2.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high pressure temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore colder than at point N ° 1.
  • the refrigerant passes through the valve V3 No. 1, the point No. 3, the point No. 4 and the point No. 20 to then enter the exchanger E1.
  • the refrigerant condenses in exchanger E1 and leaves it in high pressure liquid form at point No. 5.
  • the fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.
  • the fluid temperature is 35 ° C.
  • the high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.
  • the temperature at point 7 will be 30 ° C or sub-cooling of 5 ° C thanks to the exchanger E3.
  • the fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8.
  • the fluid temperature at point 8 is -15 ° C.
  • the fluid passes through the exchanger E4 which is ventilated by the fan VENT.
  • the fluid boils while evacuating the frigories on the through air E4.
  • the fluid temperature at point 9 will be -10 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is -5 ° C.
  • the functions of the exchanger E3 are identical for the figures 11 and 12 .
  • the fluid temperature at point 12 is -5 ° C
  • FIG. 13 is shown the operation of the system with one compressor out of two in function and a heat production ensured on the exchanger E2.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the fluid is condensed to 100% in the exchanger E2.
  • the fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gaseous phase at point 8.
  • the temperature of the fluid at point 8 is -15 ° C.
  • the fluid passes through the exchanger E4 which is ventilated by the fan VENT.
  • the fluid boils while evacuating the frigories on the through air E4.
  • the refrigerant leaves E4 at point 9 in low pressure gaseous form.
  • the fluid temperature at point 9 will be -10 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is -5 ° C.
  • the fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP2.
  • the fluid temperature at point 12 is -5 ° C.
  • This function is important because the exchanger E1, not being supplied with fluid, is empty of all its fluid in the liquid state, so it is useful to store this fluid in the volume of the inner cylinder of the exchanger E3 remains cold.
  • FIG. 14 shows the operation of the system with two compressors out of two in function and a heat production ensured on the exchanger E2 and a refrigeration production ensured on the exchanger E1.
  • This mode of function is called energy transfer.
  • the compressor CP1 and the compressor CP2 compress and discharge the refrigerant towards the point N ° 1 and N ° 13.
  • the junction of the discharge pipe of compressor No. 2 is at point 1.
  • a reference temperature at point No. 1 of 90 ° C.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the fluid is condensed to 100% in the exchanger E2.
  • the refrigerant leaving the exchanger E2 at point 2 is condensed and is colder than at point N ° 1.
  • the fluid passing through the expansion valve D1 is expanded and is thus in low pressure liquid form with a minority ratio in the gas phase in point 7.
  • the fluid temperature at point 7 is + 10 ° C.
  • the fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.
  • the ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.
  • the low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor No. 1.
  • the fluid passes through the capillary 1 which has a loss of pressure equivalent to a temperature drop of 9 ° C.
  • the fluid being expanded by the capillary 1 passes through the point 5 with a temperature equal to + 1 ° C.
  • the fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.
  • the fluid temperature at point 10 will be + 5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is + 7 ° C.
  • the fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP2.
  • the fluid temperature at point 12 is + 7 ° C.
  • the presence of the exchanger E3 in this case is innovative because it is placed on a low pressure liquid section of the refrigerant circuit which is not always supplied with low pressure liquid in its tube internal.
  • the design and the innovative location of the E3 exchanger allow this body to perform different functions according to the calorie and frigory needs of the different exchangers installed.
  • the exchanger E3 has its internal tube cooled by the suction gases passing through its external tube, the inner tube being supplied with a low-pressure liquid with a percentage of fluid in the gaseous state, it is advisable to minimize the amount of fluid in the gaseous state, the exchanger E3 allows this function by discharging a portion of this gas via the tube 19 and condensing another part of this gas due to the cooling caused by the cold gases through the outer tube of the exchanger E3.
  • the exchanger E1 would have a reduced efficiency due to a smaller amount of fluid in the liquid state in the refrigerant circuit at point 5 and in the exchanger E1 in evaporator mode. this would decrease the average coefficient of conductivity in the exchanger E1 and thus the energy efficiency of the assembly.
  • FIG. 15 shows the operation of the system with two compressors out of two in operation, a heat production ensured on the exchanger E2 and E4 and a refrigeration production ensured on the exchanger E1.
  • This function mode is called partial energy transfer.
  • the compressor CP1 and the compressor CP2 compress and discharge the refrigerant towards the points N ° 1 and N ° 13.
  • the junction of the discharge pipe of compressor N ° 2 is at point 1.
  • N ° 1 80 ° C
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.
  • the fluid is desuperheated or partially condensed in the exchanger E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore desuperheated and in the high pressure gaseous state.
  • the refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 where it is condensed to 100%.
  • the fan VENT is in operation for the cooling of the exchanger E4.
  • This function is useful for the storage of domestic hot water with a temperature higher than 65 ° C for the elimination of bacteria in summer.
  • the fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority gas phase ratio at point 7.
  • the temperature of the fluid at point 7 is + 10 ° C.
  • the fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.
  • the ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.
  • the low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and 12 is sucked by the compressor CP1 and CP2 .
  • the fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C.
  • the fluid being expanded by the capillary passes through point 5 with a temperature of +1 ° C.
  • the fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.
  • the fluid temperature at point 10 will be + 5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is + 7 ° C.
  • the fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP2.
  • the fluid temperature at point 12 is + 7 ° C
  • FIG. 16 is shown the operation of the system with one compressor out of two in operation, a heat production ensured on the exchanger E4 for defrosting and a refrigeration production ensured on the exchanger E1.
  • This function mode is called the defrost mode.
  • the defrosting of the external battery is used to remove the ice that closes and isolates the outer coil battery which recovers the heat energy from the outside air.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2.
  • the circulator P2 is stopped in order not to transmit the calories to the water circuit E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore in the gaseous state at high pressure and at the same temperature as at point 1.
  • the refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 where it is condensed to 100%.
  • the VENT fan is off to conserve all the heat energy of the refrigerant for defrosting the battery.
  • the fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.
  • the fluid temperature at point 7 is + 10 ° C
  • the fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.
  • the ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.
  • the low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor No. 1.
  • the fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C
  • the fluid being expanded by the capillary 1 passes through point 5 with a temperature equal to +1 ° C.
  • the fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.
  • the refrigerant leaves E1 in low pressure gaseous form.
  • the refrigerant exits the exchanger E1, passes through point 20, V3 N ° 2 and point 10.
  • the fluid temperature at point 10 will be + 5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is + 7 ° C
  • N ° 17 is represented the operation of the system with two compressors out of two in function, a heat production ensured on the exchanger E4 to evacuate the calories outside the building and a refrigerating production ensured on the exchanger E1.
  • This function mode is called simple chilled water production mode.
  • the compressor CP1 and the compressor CP2 compress and discharge the refrigerant towards the point N ° 1 and N ° 13.
  • the junction of the discharge pipe of compressor N ° 2 is at point 1.
  • N ° 1 For example, we can have a reference temperature at point N ° 1 of 80 ° C.
  • the fluid passes through the exchanger E2.
  • the refrigerant leaving the exchanger E2 at point 2 is therefore in the gaseous state at high pressure and at the same temperature as at point 1.
  • the refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 or it is condensed to 100%.
  • the VENT fan is on to cool the E4 outer fin exchanger.
  • the fluid exits the exchanger E4 at point 8, through the expander D1.
  • the fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.
  • the fluid temperature at point 7 is + 10 ° C
  • the fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.
  • the ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.
  • the gaseous low-pressure refrigerant then passes through the capillary 2, the non-return valve C2, the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor N ° 1 ;
  • the fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C.
  • the fluid being expanded by the capillary passes through point 5 with a temperature equal to +1 ° C,
  • the fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.
  • the fluid temperature at point 10 will be + 5 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is superheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.
  • the fluid temperature at point 11 is + 7 ° C.
  • the fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP1.
  • the fluid temperature at point 12 is + 7 ° C.
  • FIG. 18 is represented the operation of the system with two compressors out of two in function and a heat production ensured on the exchanger E2 and on the exchanger E1.
  • the figure 18 is not part of the simplifying system and thus integrates the regulator D2 in its fluidic scheme.
  • the compressor CP1 compresses and represses the refrigerant towards the point N ° 1.
  • the fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E2 is at high pressure and at high temperature.
  • the water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2. In this case, the fluid is condensed to 100% in the exchanger E2.
  • the refrigerant leaving the exchanger E2 at point 2 is condensed and is colder than at point N ° 1.
  • valve V3 No.1 With the valve V3 No.1 closed, the refrigerant passes through point 15, the filter F, point 16, valve VEM2, regulator D2.
  • the fluid passing through the expander D2 is expanded and is therefore low pressure liquid form with a minority gas phase ratio at point 18.
  • the fluid temperature at point 18 is -15 ° C
  • the compressor CP2 compresses and represses the refrigerant towards the point N ° 13.
  • a reference temperature at point N ° 13 of 60 ° C
  • the fluid passes through point 4, point 20 and enters the exchanger E1 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.
  • the fluid passing through the exchanger E1 is at high pressure and at high temperature.
  • the water passing through the exchanger E1 being colder than the fluid, the calories leave the fluid for the water circuit E1.
  • the fluid is condensed to 100% in the exchanger E1.
  • the refrigerant leaving the exchanger E1 at point 5 is condensed and is colder than at point N ° 20.
  • the refrigerant from point 5 passes through the non-return valve C1, point 6, enters the inner tube of the fluid / fluid exchanger E3, passes through point 7, passes through and is expanded by the expansion valve D1.
  • the fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority gas phase ratio at point 8.
  • the fluid temperature at point 8 is -15 ° C.
  • the flow of refrigerant from point 8 and point 18 are mixed at the inlet of exchanger E4.
  • the fluid passes through the exchanger E4 which is ventilated by the fan VENT.
  • the fluid boils, evacuating the cold air through the air E4.
  • the refrigerant leaves the exchanger E4 at point 9 in gaseous form low pressure.
  • the fluid temperature at point 9 will be -10 ° C.
  • the fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.
  • the fluid leaves the exchanger E3 at the points 11 and 12 and is sucked by the compressors CP1 and CP2.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Claims (18)

  1. Reversibles System zur Rückgewinnung, durch Entnahme und Übertragung, von Energie zwischen mindestens zwei verschiedenen Milieus, zum Beispiel zwischen einem äußeren Milieu und einem Lebensmilieu, oder zwischen einem Lebensmilieu und einem anderen Lebensmilieu, unter Verwendung als Vehikel eines Kältefluids, welches durch die Abfolge von Kompressions- und Entspannungsphasen nacheinander von einem gasförmigen Zustand in einen flüssigen Zustand und umgekehrt übergeht, dadurch gekennzeichnet, dass dieses System umfasst; - einen reversiblen Fluid/Wasser-Wärmetauscher (E1) zur Herstellung von Eiswasser oder von Warmwasser an einem Wasserkreis (E1), - einen nicht reversiblen Fluid/Wasser-Wärmetauscher (E2) zur Herstellung von Warmwasser an einem Wasserkreis (E2), - als Minimum einen Hauptkompressor (GP1), der an einem Punkt (11) an einen Fluid/Fluid-Wärmetauscher (E3) und an einem Punkt (1) an den nicht reversiblen Wärmetauscher (E2) angeschlossen ist, - eine Kapillare (KAPILLARE 2) zum Begrenzen des vom Wärmetauscher (E3) kommenden Fluidstroms im gasförmigen Zustand, - einen Wärmetauscher (E4) zum Rückgewinnen oder zum Abführen der Wärmeenergie am äußeren Milieu, wobei der Wärmetauscher (E4) ein Rippenwärmetauscher für eine Wärmepumpe vom Typ LUFT/WASSER oder ein Plattenwärmetauscher, oder auch ein Mehrröhren- oder Koaxial-Wärmetauscher für eine Wärmepumpe vom Typ WASSER/WASSER ist, - einen thermostatischen Zweistrom-Druckminderer mit externem Ausgleich (D1), um das Kältefluid von einer Abzweigung (7) zu einem Punkt (8) hin zu entspannen, wenn sich der Wärmetauscher (E4) im Verdampfermodus befindet, und um das Kältefluid vom Punkt (8) zur Abzweigung (7) hin zu entspannen, wenn sich der Wärmetauscher (E1) im Verdampfermodus befindet, - eine Kapillare (KAPILLARE 1), um eine finale Entspannung des durch den thermostatischen Druckminderer (D1) entspannten Fluids im flüssigen Zustand sicherzustellen, - wobei der Fluid/Fluid-Wärmetauscher (E3) über eine Abzweigung (6) an die Kapillare (KAPILLARE 1) zur finalen Entspannung, an eine Rückschlagklappe (C1), an ein Reservoir (R), über die Abzweigung (7) an den thermostatischen Zweistrom-Druckminderer mit externem Ausgleich (D1), über eine Abzweigung (19) an die Kapillare (KAPILLARE 2) zum Begrenzen des Massenstroms an diesem Zweig, über eine Abzweigung (10) an den Einlass der von einem Ventil (V3 Nr. 2) kommenden Kaltgase, über eine Abzweigung (11) an die Absaugung der durch den Kompressor (CP1) überhitzten Gase, und gegebenenfalls über eine Abzweigung (12) an die Absaugung der durch einen Kompressor (CP2) überhitzten Gase angeschlossen ist, - wobei der Fluid/Fluid-Wärmetauscher (E3) zwei Betriebsmodi aufweist: - wenn der Wärmetauscher (E3) an der Abzweigung (7) mit Niederdruckfluid im flüssigen Zustand mit einem geringen Anteil von Fluid im gasförmigen Zustand gespeist wird, kondensiert der Wärmetauscher einen Teil dieses Fluids im gasförmigen Zustand und führt über die Abzweigung (19) einen anderen Teil dieses Fluids im gasförmigen Zustand ab, sodass der Flüssigkeitsanteil an der Abzweigung (6) des Wärmetauschers (E3) erhöht wird, - wenn der Wärmetauscher (E3) an der Abzweigung (6) mit Hochdruckfluid im flüssigen Zustand gespeist wird, funktioniert der Wärmetauscher (E3) als Unterkühler dieses Hochdruckfluids im flüssigen Zustand und als Überhitzer der Absaugungsgase zwischen der Abzweigung (10) und mindestens der Abzweigung (11), - wobei das Kältefluid-Reservoir (R) eine Kältefluidreserve enthält,
    - wobei die Rückschlagklappe (C1) das Umleiten des Fluids von einem Punkt (5) zur Abzweigung (6) hin ermöglicht, wenn der Wärmetauscher (E1) als Kondensator verwendet wird, - eine Rückschlagklappe (C2) zum Unterbinden eines Rückstroms des Fluids von einem Punkt (20) zur Abzweigung (19) hin, wenn der Wärmetauscher (E1) als Kondensator verwendet wird, - ein motorbetriebenes Drei-Wege-Ventil (V3 Nr. 1), um den Betrieb des Wärmetauschers (E2) im Entüberhitzer-, Voll- oder Teilkondensatormodus, und das Umleiten des Kältefluidstroms zum Wärmetauscher (E1) oder dem Wärmetauscher (E4) hin zu gestatten, - ein motorbetriebenes Drei-Wege-Ventil (V3 Nr. 2), um den Betrieb des Wärmetauschers (E1) im Verdampfermodus, oder des Wärmetauschers (E4) im Verdampfermodus zu gestatten,
    - ein Magnetventil (VEM1), das vom Kältefluid von einem Punkt (16) zu einem Punkt (17) durchflossen wird, wenn sich der Wärmetauscher (E1) im Verdampfermodus, und der Wärmetauscher (E2) im Kondensatormodus befindet, - ein Magnetventil (VEM2), das vom Kältefluid vom Punkt (16) zu einem Punkt (18) durchflossen wird, wenn sich der Wärmetauscher (E4) im Verdampfermodus, und der Wärmetauscher (E2) im Kondensatormodus befindet, und einen Einstrom-Druckminderer (D2) zum Entspannen des Fluids zwischen dem Punkt (16) und dem Punkt (18), wenn sich der Wärmetauscher (E4) im Verdampfermodus, und der Wärmetauscher (E2) im Kondensatormodus befindet.
  2. System nach Anspruch 1, dadurch gekennzeichnet, dass es weiter entweder einen oder mehrere sekundäre Kompressoren (CP) umfasst, die über eine Rohrleitung (13) an der Abzweigung (12) an den Wärmetauscher (E3), und am Punkt (1) an den nicht reversiblen Wärmetauscher (E2) angeschlossen sind, oder einen oder mehrere sekundäre Kompressoren (CS), die über Rohrleitungen (13, 4) an der Abzweigung (12) an den Wärmetauscher (E3), und am Punkt (20) an den reversiblen Wärmetauscher (E1) angeschlossen sind.
  3. System nach Anspruch 1 oder 2, gekennzeichnet durch den Anschluss der Absaugung des oder der Kompressoren an den Fluid/Fluid-Wärmetauscher (E3), der neben anderen Funktionen das Überhitzen der Absaugungsgase vor Komprimieren derselben sicherstellt.
  4. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein eines thermostatischen Zweistrom-Druckminderers (D1), der mit einem Fluid/Fluid-Wärmetauscher (E3) gekoppelt ist, der neben anderen Funktionen das Unterkühlen der Hochdruckflüssigkeit am Punkt (7) sicherstellt, wenn der Druckminderer (D1) von dem Fluid durchflossen wird.
  5. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein eines thermostatischen Zweistrom-Druckminderers (D1), der mit dem Fluid/Fluid-Wärmetauscher (E3) gekoppelt ist, der neben anderen Funktionen das teilweise Entgasen der Niederdruckflüssigkeit über das Rohr und die Kapillare (KAPILLARE 2) stromaufwärts der Kapillare (KAPILLARE 1) zur finalen Entspannung sicherstellt, wenn der Druckminderer (D1) von dem Fluid durchflossen wird.
  6. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein eines Reservoirs, das mit Hochdruckflüssigkeit gespeist wird, wenn sich der Wärmetauscher (E1) im Kondensatormodus befindet, und mit Niederdruckflüssigkeit mit einem minderheitlichen Prozentanteil an Fluid im gasförmigen Zustand gespeist wird, wenn sich der Wärmetauscher (E1) im Verdampfermodus befindet.
  7. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein eines Drei-Wege-Ventils (V3 Nr. 1) zum Speisen mit Hochdruck-Kältefluid im gasförmigen Zustand oder im flüssigen Zustand oder in einem Mischzustand von Flüssigkeit und Gas, die zum Wärmetauscher (E4) oder dem Wärmetauscher (E1) hin vermengt werden.
  8. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein eines Drei-Wege-Ventils (V3 Nr. 2) zum Speisen mit Niederdruck-Kältefluid im gasförmigen Zustand zum Fluid/Fluid-Wärmetauscher (E3) und zum Auswählen des Wärmetauschers (E4) oder (E1) im Verdampfermodus.
  9. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein des Fluid/Wasser-Wärmetauschers (E2) zum Entüberhitzen oder zum vollständigen oder teilweisen Kondensieren der Abgase des oder der am Punkt (1) angeschlossenen Kompressoren für eine Herstellung von Warmwasser am Kreis (E2).
  10. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein des Fluid/Wasser-Wärmetauschers (E1) zum vollständigen Kondensieren oder zum vollständigen Verdampfen des ihn durchfließenden Kältefluids für eine Herstellung von Warmwasser oder von Eiswasser am Wasserkreis (E1).
  11. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein des Fluid/Luft-Wärmetauschers (E4) zum vollständigen Kondensieren oder zum vollständigen Verdampfen des ihn durchfließenden Kältefluids für eine Rückgewinnung oder eine Ableitung der Wärmeenergie an einem äußeren Milieu.
  12. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein der Kapillare (KAPILLARE 1) zum finalen Entspannen des vom Wärmetauscher (E3) kommenden, teilweise entgasten Fluids, wenn sich (E1) im Verdampfermodus befindet.
  13. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein der Kapillare (KAPILLARE 2) zum Begrenzen des vom Wärmetauscher (E3) kommenden Fluidstroms in gasförmiger Form, wenn sich (E1) im Verdampfermodus befindet.
  14. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein der Rückschlagklappe (C1) zum Umleiten des Fluids zwischen dem Punkt (5) und der Abzweigung (6), wenn sich der Wärmetauscher (E1) im Kondensatormodus befindet.
  15. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein der Rückschlagklappe (C2), um das Zirkulieren des Kältefluids vom Punkt (20) zum Punkt (19) hin zu unterbinden, wenn sich der Wärmetauscher (E1) im Kondensatormodus befindet.
  16. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein des Magnetventils (VEM1), um den Übergang des Fluids vom Punkt (16) zum Punkt (17) hin zu gestatten, wenn sich der Wärmetauscher (E2) im Kondensatormodus, und der Wärmetauscher (E1) im Verdampfermodus befindet.
  17. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein des Magnetventils (VEM2), um den Übergang des Fluids vom Punkt (16) zum Punkt (18) hin zu gestatten, wenn sich der Wärmetauscher (E2) im Kondensatormodus, und der Wärmetauscher (E4) im Verdampfermodus befindet.
  18. System nach Anspruch 1, gekennzeichnet durch das Vorhandensein des thermostatischen Einstrom-Druckminderers (D2) zum Entspannen und zum Speisen des Wärmetauschers (E4) mit entspannter Flüssigkeit, wenn sich derselbe im Verdampfermodus befindet, und wenn sich der Wärmetauscher (E2) im Kondensatormodus befindet.
EP09761796.3A 2008-06-12 2009-06-12 Reversibles system zur rückgewinnung von wärmeenergie durch entnahme und übertragung von wärmeenergie von einem oder mehreren medien in ein oder mehrere andere solcher medien Active EP2318783B1 (de)

Applications Claiming Priority (2)

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FR0803258A FR2932553B1 (fr) 2008-06-12 2008-06-12 Systeme reversible de recuperation d'energie calorifique par prelevement et transfert de calories d'un ou plusieurs milieux dans un autre ou plusieurs autres milieux quelconques.
PCT/EP2009/057310 WO2009150234A1 (fr) 2008-06-12 2009-06-12 Système réversible de récupération d'énergie calorifique par prélèvement et transfert de calories d'un ou plusieurs milieux dans un autre ou plusieurs autres milieux quelconques

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FR3079918B1 (fr) 2018-04-06 2020-10-23 Maire Jean Luc Dispositif reversible de recuperation d'energie calorifique

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BRPI0915033A2 (pt) 2015-10-27
US8726684B2 (en) 2014-05-20
FR2932553B1 (fr) 2013-08-16
CA2727414C (fr) 2017-01-10
FR2932553A1 (fr) 2009-12-18
CA2727414A1 (fr) 2009-12-17
WO2009150234A1 (fr) 2009-12-17
EP2318783A1 (de) 2011-05-11
DK2318783T3 (en) 2019-01-21
BRPI0915033B8 (pt) 2020-01-28
BRPI0915033B1 (pt) 2019-12-31
US20110209491A1 (en) 2011-09-01

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