Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
  • F24D17/00—Domestic hot-water supply systems
  • F24D17/0005—Domestic hot-water supply systems using recuperation of waste heat
  • F24D17/001—Domestic hot-water supply systems using recuperation of waste heat with accumulation of heated water
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
  • F24D17/00—Domestic hot-water supply systems
  • F24D17/02—Domestic hot-water supply systems using heat pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
  • F24H4/00—Fluid heaters characterised by the use of heat pumps
  • F24H4/02—Water heaters
  • F24H4/04—Storage heaters
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B30/00—Heat pumps
  • F25B30/02—Heat pumps of the compression type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B39/00—Evaporators; Condensers
  • F25B39/04—Condensers
• • 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
  • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
  • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
• • 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
  • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
  • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
  • F28F3/14—Elements constructed in the shape of a hollow panel, e.g. with channels by separating portions of a pair of joined sheets to form channels, e.g. by inflation
• • 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
  • F25B2339/045—Condensers made by assembling a tube on a plate-like element or between plate-like elements
• • 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
  • 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
  • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
  • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
  • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
  • F28D2021/007—Condensers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F2210/00—Heat exchange conduits
  • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
  • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
  • Y02B30/18—Domestic hot-water supply systems using recuperated or waste heat
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
  • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
  • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency

Definitions

• the invention relates to a thermodynamic water heater using a reduced amount of refrigerant.
• the invention aims to obtain a maximum thermal efficiency by using a minimum refrigerant volume in a thermodynamic water heater, implementing a gas compression heat pump (PAC).
• PAC gas compression heat pump
• a heat pump transfers heat from a cold source to a hot source.
• the cap uses a refrigerant fluid, able to change phase depending on temperature and pressure.
• the operating principle of a PAC is known from the prior art and is recalled here only for memory.
• the refrigerant passes from a low-pressure evaporator, where it takes thermal energy from the liquid source to the gaseous state with the absorption of a latent heat of evaporation.
• a compressor increases the pressure of this gas before directing it to a condenser, where said pressurized gas returns heat to the hot source from the gaseous state to the liquid state and releases latent heat of condensation.
• a pressure reducer reduces the pressure of the refrigerant in the liquid state leaving the condenser, before said fluid is again directed towards the evaporator.
• the heat transport circuit comprising, the evaporator, the compressor, the condenser and the expander, is a sealed closed circuit whose volume is dictated by the intended thermal performance and defines the amount of refrigerant necessary for the operation of the installation.
• the refrigerant is a gas such as a hydrofluorocarbon (HFC). These fluorinated gases are potentially harmful for the environment, especially with regard to the greenhouse effect.
• heat transfer fluids such as ammonia or liquefied petroleum gases (LPG) such as isobutane or propane can be used, but their toxicity, or their flammable nature, with respect to hydrocarbons, strictly limit the amount of fluid usable in this case. In the presence of a reduced amount of refrigerant, the volume of the heat transport circuit must be reduced.
• LPG liquefied petroleum gases
• thermodynamic water heater In the case of a thermodynamic water heater, the hot source is constituted by the domestic hot water produced by the water heater.
• the document FR2963416 describes a thermodynamic water heater, including in particular the condenser is optimized to allow the use of a reduced amount of refrigerant.
• the thermodynamic water heater described in this document of the prior art is satisfactory, however, this embodiment of the prior art is not suitable for producing a thermodynamic water heater whose capacity is greater than 200. liters and whose maximum operating pressure is greater than 15 bar, (absolute pressure).
• condensation pressures between 15 bars and 25 bars depending on the refrigerants must to be used.
• thermodynamic water heater in particular with a capacity of 400 liters, comprising a heat transfer circuit forming a heat pump, comprising:
• a low pressure circuit comprising an evaporator
• a high pressure circuit comprising a condenser in contact with the tank of said water heater, said condenser comprising: bi. two plates superimposed and pressed against each other, one of the plates comprising a continuous boss forming, in cooperation with the other plate, a conduit forming a condensation circuit in parallel channels;
• a gas phase refrigerant inlet in a single channel, followed by a distribution zone comprising a plurality of division bifurcations, each distributing the fluid conveyed from a channel of current section into two channels of the same current section;
• biii a single channel output of the refrigerant in phase liquid, which output is preceded by at least one grouping zone comprising a plurality of concentration bifurcations, said grouping zone grouping N channels of the same current section into channels of the same current section in (
• This condenser takes up several characteristics of the condenser described in document FR2963416 by perfecting them.
• the organization of division and concentration bifurcations makes it possible to distribute the flow rate of the heat transfer fluid homogeneously in all the parallel channels and thus to improve the efficiency of the heat exchange between the condenser and the domestic hot water.
• a bifurcation, division or concentration zone is a geometric zone whose section of passage is variable.
• a channel is defined by a section of constant passage.
• a bifurcation zone terminates at the entrance to a channel, and begins at the end of a channel in the direction of flow.
• a bifurcation of concentration or division of the condenser hydraulically connects several channels and preferably 3 channels of current section, in a bifurcation chamber and the ratio between the projected surface of the bifurcation chamber and the holding perimeter of said bifurcation chamber is less than 6 mm 2 / mm and preferably less than 5.5 mm 2 / mm. This ratio makes it possible to obtain increased resistance to fatigue in the bifurcation zones by maximizing the length of the welds applied, the holding perimeter, facing the surface of the bifurcation subjected to pressure.
• the current section of the condenser channels is a disk segment whose arc is formed by the boss and whose ratio between the section and the length of the string is between 0.7 mm 2 / mm and 1, 1 mm 2 / mm, preferably between 0.9 mm 2 / mm and 1 mm 2 / mm.
• This configuration makes it possible to obtain a high exchange surface with respect to the volume of the channel, while ensuring the resistance of said channel to the stresses generated by the pressure and keeping the pressure drop within acceptable limits.
• the flattened shape of the channels makes it possible to roll the condenser around the tank of the water heater without the risk of pinching said channels.
• the path length of the refrigerant in a channel of constant section between two division bifurcations is less than or equal to 2 chord lengths of the channel section.
• the distance separating two parallel channels is greater than or equal to 1.5 rope length and less than or equal to 5 rope lengths of the current section of the channels. This configuration ensures both the mechanical strength of the zone separating two channels and a large exchange surface, by wing effect.
• the plates superposed and pressed against each other constituting the condenser are made of an aluminum alloy with a total thickness of between 1.5 mm and 2 mm and the length of rope the current channel section of said condenser is equal to 7 mm.
• This embodiment is particularly suitable for a domestic thermodynamic water heater implementing a refrigerant whose maximum operating pressure is between 15 and 25 bars such as propane.
• the developed form of the condenser is rectangular, the inlet and the outlet of the refrigerant in said condenser being located at the center of the same large side of the rectangle.
• the positions of the inlet and the outlet of the condenser in the thermodynamic water heater are perfectly controlled during the driving of the condenser around the tank of said water heater.
• the evaporator of the water heater object of the invention comprises a heat exchange circuit consisting of a finned tube with an outer diameter of 5 mm.
• a small diameter tube for this evaporator cooperates with the condenser to reduce the amount of refrigerant used.
• the evaporator comprises as input a distribution box comprising a bypass of the flow of refrigerant to two parallel circuits and preferably to 3 parallel circuits with finned tube of the same diameter.
• the refrigerant used in the water heater object of the invention is a hydrocarbon, the amount of fluid included in the heat transfer circuit being less than 150 grams.
• the heat transfer circuit of the water heater object of the invention is adapted for the use, safely, of a gas whose Global Warming Potential, or GWP, at 100 years, is less than or equal to 150.
• the GWP of a gas measures its capacity to absorb infrared radiation emitted by the Earth, ie its capacity to generate a greenhouse effect, over a period of 100 years, in comparison with the capacity of the same mass of carbon dioxide (C0 2 ) over the same period.
• FIGS. 1 to 6 in which:
• FIG. 1 is a front view of an exemplary embodiment of a condenser adapted to the thermodynamic water heater that is the subject of the invention
• FIG. 2 shows in a partial detail view in section AA defined in Figure 1, an embodiment of a refrigerant transport channel in the condenser shown in Figure 1;
• FIG. 3 represents, in a detailed view, a grouping area of
• FIG. 4 illustrates in detail view, the distribution zone of a condenser according to the embodiment of Figure 1, distributing 1 channel in 6 channels by a series of bifurcations of 1 channel in 2 channels;
• FIG. 5 shows, in a perspective view and cut away, an embodiment of a water heater according to the invention
• FIG. 6 schematically illustrates in a front view, an embodiment of an evaporator adapted to the water heater object of the invention.
• the invention relates more particularly to a thermodynamic water heater with a capacity between 150 liters and 270 liters, and up to 400 liters, while using a total amount of refrigerant less than 150 grams.
• the condenser (100) of the thermodynamic water heater according to the invention is in the form of a rectangular plate, comprising a condensation circuit extending between an inlet (110) where the refrigerant arrives in the form of vapor, and an outlet (120) where said fluid leaves the condenser in the liquid phase.
• Said condenser (100) is able to be rolled elastically to be placed around the tank of a water heater.
• Fastening means (151, 152) on the short sides of the rectangle, to maintain it in this rolled configuration, as described in FR2963416.
• the condensation circuit is comprised of a plurality of parallel channels extending over the surface of the condenser.
• the vapor feed stream is rapidly divided into a plurality of channels over a short distance in a distribution area (1 1 1).
• this distribution zone (1 1 1) in the direction of flow of the refrigerant, the number of channels decreases so that the refrigerant leaves the condenser in the liquid phase through a single outlet (120).
• Channel grouping is performed in clustering areas (121, 122) for evenly distributing refrigerant flow from N channels into ([N / 2J + 1) channels.
• N / 2j represents the default integer part of the quantity N / 2.
• a first grouping area (121) makes it possible to transfer the flow of refrigerant from 6 channels in 4 channels, then a second grouping area (122) makes it possible to distribute the stream coming from these 4 channels in 3 channels.
• each channel before entering the first grouping area (121), each channel carries a 1/6 th of the flow, then at the exit of this grouping area (121), each vehicle channel 1/4 flow.
• a grouping area concentrates 8 channels into 5 channels, 5 channels into 3, 3 channels into 2 or even 7 channels into 4.
• the steam flow is systematically separated first 2 to ensure a uniform distribution of the flow and the mechanical strength of the distribution area.
• each channel resulting from this first division is then separated into two channels and so on, so that, according to this exemplary embodiment, the number of channels arriving in the first grouping zone is necessarily even, equal to 2, 4, 6, 8, 10 or more channels.
• the condenser of the water heater object of the invention consists of two plates (201, 202), for example aluminum alloy, pressed one on the other and assembled.
• the assembly of said plates (201, 202) is achieved by localized welds (230), by soldering or by diffusion bonding.
• the first plate (201) is kept flat and the second plate (202) is embossed so that when said plates (201, 202) are assembled, said boss defines a channel whose current section (210) is, according to this example embodiment, in the form of a disk segment.
• the embossing of the second plate is performed prior to the assembly of said plates by stamping or forming the wheel.
• the embossing is performed after the assembly of the plates, for example by inflation.
• a diffusion barrier agent is applied to one of the plates in a pattern reproducing the condensation circuit, so that the two plates are not tied to the location of the future channels during diffusion bonding. two plates.
• the condensation circuit is made by inflation, hot deformation.
• the total thickness of the plates is between 1.5 mm and 2 mm.
• this pressure tends to move the plates (201, 202) away from each other.
• this bias is proportional to the width (21 1) of the channel.
• This width (211) is substantially equal to the length of the chord of the disk segment.
• the use of a ratio between the current section (210) and the width (21 1) of the channel, between 0.7 mm 2 / mm and 1.1 mm 2 / mm, and more particularly between 0.9 mm 2 / mm and 1 mm 2 / mm makes it possible to reach the best compromise between these contradictory constraints for the intended application. More particularly, according to an advantageous embodiment, the width (21 1) of the channel is 7 mm, for a current section of 9.52 mm 2 , a ratio of 0.93 mm 2 / mm.
• the channels are organized in a network of parallel channels constituting the condensation circuit.
• the distance (130) separating two parallel channels is at least equal to 1.5 channel width and preferably at least equal to 2 channel widths.
• FIG. 3 in a detail view of a grouping area (121), it includes several bifurcations (320) of concentration.
• a bifurcation whether of concentration or division, puts in hydraulic communication the flow of 3 channels.
• Said 3 channels are of substantially equivalent section and extend in directions at 120 ° (2 ⁇ / 3 radians) from each other.
• the current section of each channel opens into a bifurcation chamber, whose volume is proportional to the projected surface (325) of said chamber on the unembossed plate.
• This chamber is subjected to the pressure of the refrigerant, which pressure generates a bias tending to separate the two plates.
• This bias is proportional to the projected area (325) of the chamber, projected area that corresponds to the area in which the current section of fluid flow is enlarged.
• the widening of the section increases the stress on the edge welds (321, 322, 323) of said bifurcation chamber.
• the added length of said edges constitutes a perimeter for maintaining the bifurcation (320).
• the weld zones located on the edges (321, 322, 323) of a bifurcation chamber are the most stressed zones in the condenser during operation of the thermodynamic water heater. Solicitation of said the higher the projected area (325) of the bifurcation chamber and the smaller the holding perimeter.
• the ratio between the projected surface (325) and the holding perimeter is less than 6 mm and preferably 5.5 mm.
• this geometric constraint determined by fatigue tests in thermomechanical cycling of the condenser, can not be respected if a bifurcation chamber puts in hydraulic communication more than 3 channels.
• the concentration bifurcations are associated with each other in a network, in a hexagonal pattern.
• hexagonal emotive superimposed bifurcations allow to group (K + 3) channels in AT channels, or (K + 2) channels in ( K + 1), the maximum number of channels connected to said pattern being (2K + 3).
• the same type of bifurcation association pattern also makes it possible to divide the flow, for example from K channels into (K + 3) channels, with however the constraint that the flow of arrival of steam must first be divided in 2 to ensure a good distribution of the flow.
• the area (1 10) of distribution comprises a plurality of bifurcations (410) divisions.
• the first division consists in separating the incoming flow in two.
• the following successive divisions are made by separating the flow of each channel into two channels of the same current section.
• the conditions set out for the concentration bifurcations are applicable to division bifurcations, that is, for each bifurcation, the ratio of the projected area (415) of the bifurcation chamber to the retention perimeter corresponding to the sum of the lengths of segments (41 1, 412, 413) assembled bordering said bifurcation chamber, must be less than 6 mm and preferably less than 5.5 mm.
• the channel length (416) between two bifurcations is less than or equal to 2 channel widths.
• the condenser (100) of the water heater object of the invention is rolled on itself as described in FR2963416, the invention is an improvement.
• the inlet (110) and the outlet (120) of the refrigerant are advantageously placed substantially in the center of a large side of the rectangle.
• the locations of this inlet (110) and this outlet (120) are predictable and easily determined after rolling, which simplifies the hydraulic connection of said condenser (100) in the heat transfer circuit of the water heater.
• two grooves (191, 192, 193, 194) placed on either side of the arrival channel and the channel and the output channel provide flexibility to connect the inlet and outlet channels of the condenser to the heat transport circuit.
• the thermodynamic water heater (500) object of the invention comprises a vessel (502) cylindrical adapted to contain domestic hot water.
• the tank of the water heater (500) object of the invention is adapted to contain up to 400 liters of hot water.
• the cold water of the network enters said tank (502) through an inlet (503) located preferably in the lower part of the tank and the domestic hot water comes out of an outlet (504), preferably located in the upper part of the heater. water.
• the tank is surrounded by a thermal insulation (505).
• the heat transfer circuit of the water heater object of the invention forms a loop and comprises a compressor (509), the condenser (100) wound around the tank (502), a pressure regulator (51 1) and an evaporator (508).
• the compressor (509), the evaporator (508) and the expander (511) are located at the top of the water heater (500).
• the condenser (100) is preferably placed in the lower part of the water heater, between the tank (502) and the thermal insulation (505).
• the heat transport circuit comprises a low pressure circuit extending between the expander (51 1), the evaporator (508) and the compressor (509) and a high pressure circuit that is arranged between the compressor (509), the inlet ( 1 10) of the condenser (100), the outlet (120) of the condenser and up to the expander (51 1).
• the refrigerant, compressed by the compressor (509) enters the gas phase into the condenser via the inlet channel (110).
• the refrigerant condenses in the liquid phase and transfers its heat to the water contained in the tank (502) of the water heater.
• the condenser (100) is preferably installed so that the flow of the refrigerant after the zone (1 1 1) of distribution is essentially down.
• the microchannels carrying the adduction of the refrigerant in the condenser (100), reduce the amount of fluid required in the heat transport circuit, while taking advantage of a large exchange surface with the tank (502) of the water heater .
• the refrigerant in the liquid phase and at low pressure passes into the gas phase in contact with the ventilated ambient air, present in the room in which the water heater (500) is installed.
• said fluid takes from the environment a latent heat of vaporization.
• the air is brought from the outside by a sheathed circuit.
• the water heater object of the invention uses an evaporator (508) of reduced volume.
• said evaporator consists of a plurality of finned tubes (600), the tube (601) consisting of copper and the fins (602) of an aluminum alloy.
• such an evaporator consists of a plurality of loops, the refrigerant passing from one loop to the other, in cascade, by describing a coil.
• the typical diameter of the brass tubes is, according to the prior art, 7 mm, 7.94 mm or 9.52 mm.
• the evaporator of the water heater object of the invention uses a copper tube with a diameter less than or equal to 5 mm.
• the small diameter of the tube reduces the volume of the heat transport circuit, and therefore the amount of refrigerant required.
• this small diameter increases, at a given flow rate, the speed of circulation of the fluid, increases the Reynolds number of the flow and leads to an increase of the losses of charges, substantially equal, in first approximation, to the square of the coefficient of diameter reduction of the flow.
• the evaporator is configured so that the refrigerant flows in parallel, and not in cascade, said reduced diameter finned tubes.
• said evaporator comprises, according to an exemplary embodiment, a box (610) for dispensing refrigerant in the liquid state between the expander and the inlet of the evaporator.
• thermodynamic water heater with a domestic hot water capacity up to 400 liters, while limiting the amount of refrigerant used to less than 150 grams of hydrocarbon.

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• 2015
  • 2015-07-17 FR FR1556772A patent/FR3038966B1/fr not_active Expired - Fee Related
• 2016
  • 2016-02-01 CN CN201680042187.9A patent/CN108369031B/zh active Active
  • 2016-02-01 WO PCT/EP2016/052015 patent/WO2017012718A1/fr active Application Filing
  • 2016-02-01 EP EP16702130.2A patent/EP3325896A1/fr not_active Withdrawn

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