FR2906603A1 - Heat storage and transfer module for e.g. ship, has high, medium and low temperature heat storage and exchange blocks, anti-return valves allowing passage of gas in one direction, and valve allowing operation in heating and cooling modes - Google Patents

Abstract

The module has a coolant compressor (1) operating at a low pressure. A high temperature heat storage and exchange block (2) is located at a suction part of the compressor. The block (2) and medium and low temperature heat storage and exchange blocks (3, 4) are made of strong thermal conductivity material. Anti-return valves allow passage of gas in one direction. A four way valve (6) allows operation in heating and cooling modes. An injection valve (19) performs injection on top of the compressor and limits flow temperature of the compressor in heating mode. An independent claim is also included for a system comprising a module for heat storage and heat transfer.

Description

1 Module Usable for Storage and Thermal Transfer Field of

  The invention relates to a thermodynamic device of the heat pump type or air conditioning system. More particularly, the invention relates to a hybrid module for storage and heat transfer, comprising on the one hand known elements of a conventional thermodynamic device (compressor, expander, regulation) and on the other hand specific exchange blocks and heat storage to increase the performance of the device. The module can be equipped with additional storage blocks if the application requires it. The module applies flexibly to many different types of systems. Typical use is in individual or collective housing, but other uses may be considered, for example for larger buildings, such as office buildings, or for non-permanent dwellings (because in module according to the invention there is no hot water storage) or for mobile applications.

  State of the art The consumption of heating, air conditioning and domestic hot water typically represent about 30% of the energy consumption of an industrialized country.  The gains in efficiency of heating, air conditioning and hot water production equipment are essential because the cost of energy is increasing and there is a strong need to reduce the dependence on fossil fuels.  At the same time, air conditioning is developing, which goes against energy savings.  The size of heating and air-conditioning devices is becoming more and more important because of the cost per square meter of real estate 2906603 2 The production of domestic hot water represents a growing part of the total energy bill. 'a home.  This trend should be confirmed in the future, in particular due to improved insulation of buildings (eg passive houses in Germany and the Minergie label in Switzerland).  In addition, the hot water requirements are specific: they exist all year but are discontinuous during the day from which a need for heat power and / or storage of hot water.  There is therefore a need for thermal systems capable of effectively managing continuous and discontinuous heating and cooling requirements at different temperature levels throughout the year.  Thermodynamic systems, and more particularly heat pumps, offer an alternative to conventional systems using electrical resistors or the combustion of fossil fuels to heat domestic water or space.  With regard to refrigerants, Hydro Fluoro Carbon (HFC) is currently commonly used for domestic heat pumps and air conditioning systems.  Hydrocarbons, particularly alkanes such as butane and propane, are also used in household refrigerators, and their use should extend to heat pumps and air conditioners in the coming years.  Carbon dioxide (CO2) is a promising refrigerant, especially for heating domestic hot water and for heating and cooling the vehicles.  Conventional heat pump systems equipped with a gas cooler (gas cooler) or desuperheater are currently commercially available.  In these systems, the sensible heat of the compressor discharge gases is used to heat the water of a water storage.  The energy efficiency of such systems is potentially high.  However, the heat pump does not heat the domestic water without heating or cooling the space.  Moreover, the amount of heat recovered is often too low due to the operating conditions of the compressor.  In this case, very common in Europe, a complementary heating system is necessary.  It is typically an electric resistance heating or heating based on fossil fuels.  This system is therefore used preferentially in parts of the world where there are heating or cooling needs throughout the year.  2906603 3 Conventional heat pumps with 3-way valves are also available on the condensate circuit.  In this case, the domestic hot water is heated by the sensible heat and the latent heat of the compressor discharge gases.  It is possible to heat domestic hot water without heating or cooling demand.  However, the efficiency of the system decreases sharply as the temperature of the hot water increases.  In addition, it is not possible to simultaneously heat the domestic hot water and heating or cooling the space.  Patent No. 1,572,479 to DAIMLER CHRYSLER discloses a system using a heat accumulator having a heat storage material as a cold store in an automotive air-conditioning system.  The heat accumulator serves as a cold accumulator and condenser.  This system makes it possible to cool the interior of a vehicle when the compression refrigeration circuit is stopped.  The preferred refrigerant in this patent is carbon dioxide.  The patent application No. EP 1632734 to MATSUSHITA ELECTRIC discloses a heat pump system with heat storage.  The system is based on a different adsorption cycle of the conventional thermodynamic compression system used in heat pumps.  This system is relatively complex and requires several reservoirs for storage of the heat storage material.  The storage of heat is carried out by the decomposition of a compound (for example decomposition of 2-propanolol into acetone and hydrogen) and adsorption of the decomposition products if they are in the gaseous state (case of hydrogen). Patent Application No. WO98 / 11397 by Marius POCOL and Constantin PANDURU discloses a storage tank used on a water loop of conditioned air in order to smooth the consumption of the system over time.  US Patent 5,680,898 discloses a heat pump including a heat storage device having phase change materials with different phase change temperatures.  The exchange and storage device disclosed in this patent includes a container defining an interior region configured to receive a first unencapsulated phase change material with a first phase change temperature, which material may be water.  The exchange and storage device also includes a refrigerant loop.  The exchange and storage device further comprises a plurality of capsules containing a second phase change material with a second phase change temperature greater than that of the first material.  The second material is immersed in the first.  The heat is transferred to the encapsulated phase-change material which has low thermal conductivity by the unencapsulated material having higher thermal conductivity. US Patent Application 2005/0258349 to SGL discloses a phase change material used for the storage of heat in latent form, as well as devices using this material.  The phase change material of this invention is a composite material comprising a phase change material in which graphite particles are incorporated, the graphite being natural graphite or anisotropic synthetic graphite.  The phase change material has a melting point between -100 and +500 ° C, and is selected from paraffins, alcohols, gas hydrates, water, aqueous salt solutions, hydrated salts, mixtures Salt eutectics, alkali metal hydroxides, and mixtures of these materials.  The preferred phase change materials are sodium acetate trihydrate and calcium chloride hexahydrate.  SGL patent application WO 2006/034829 discloses a container-based beverage cooling system charged with a phase change material using expanded natural graphite.  All of these existing systems have at most one heat storage element.  Either they do not allow simultaneous heating of domestic hot water and space, or the system is inefficient.  The present invention provides a thermodynamic device based on a system comprising, in addition to conventional elements of thermodynamic systems, at least 2, and preferably at least 3, distinct elements for the storage of heat.  OBJECT OF THE INVENTION The Usable Module for Storage and Thermal Transfer (MUSTT) according to the invention, which represents a first object of the present invention, is a hybrid module comprising the following components: (a) A compressor 1 refrigerant; (b) a heat exchange and storage block said high temperature block 2 located at the suction of the compressor 1; (c) a heat exchange and storage block said medium temperature block 5 3; (d) another heat exchanger, or preferably a heat exchange and storage block said low temperature block 4; (e) a four-way valve 6 located at the outlet of the high temperature module 2, this valve being mandatory if said module is intended to operate in a reversible mode; (f) optionally at least two nonreturn valves 26, 36, in particular for using the module as a reversible heating / cooling system; (g) optionally an injection valve 19 for limiting the discharge temperature of the compressor in heating mode, said injector valve 19 upstream of the compressor 1; (h) a pressure regulator 5.  The MUSTT module may furthermore include, if necessary or useful: the regulation and electric power components for supplying the different elements of the thermodynamic system in a reliable and energy-efficient manner; - one or more additional heat exchange and storage blocks if necessary or useful for the proposed installation; Other useful or necessary components for the intended use.  More particularly, a second object of the present invention is a system operating in non-reversible mode and integrating a module according to the invention as described above (MUSTT module), said system being characterized in that said components are arranged the refrigerant 20 leaves the discharge of the compressor 1 by first passing through the high temperature block 2 and then through the medium temperature block 3, then 2906603 6 (a) for use in a system with a heat source and a heat load, preferably domestic hot water, said refrigerant 20 passes through the low temperature block 4, the expander 5, a heat source exchanger (such as an exchanger on the extracted air or a loop 5 geothermal), then, by a circuit different from that of the first passage, again by the low temperature block 4, then said refrigerant 20 enters the suction of compres 1, and the cycle resumes; (b) for use in a system with a heat source and a first heat load, this first heat load being preferentially hot water, and a second heat load (such as underfloor heating, radiator, a fresh air heat exchanger, a fan convector), said refrigerant 20 passes through the exchanger of the second heat load, then passes through the low temperature block 4, through the expander 5, by a heat exchanger source (such as an exchanger on the extracted air or a geothermal loop), then, by a circuit different from that of the first passage, again by the low temperature block 4, then said refrigerant 20 enters the suction of the compressor 1, and the cycle resumes; (c) for use in a system with two heat sources and two heat loads, one of said heat loads being preferentially hot water (the other may be for example underfloor heating, a radiator , a fresh air heating exchanger, a conventional fan), said refrigerant 20 passes through a first exchanger on the heat load, then by the expander 5, then by an exchanger of a first heat source, then by the low temperature block 4 used as exchanger 25 of a second heat source, then the refrigerant 20 enters the suction of the compressor 1, and the cycle resumes.  A third object of the present invention is a system operating in reversible mode and integrating a module according to the invention as described above (MUSTT module) and characterized in that said components are arranged so that the refrigerant 20 leaves the discharge of the compressor 1 by first passing through the high temperature block 2 and then by the four-way valve cycle reversal 6, then 2906603 7 (a) for use with two heat sources and two heat loads, the first thermal load preferably being domestic hot water, this first heat load being connected by an independent circuit in series to the high temperature and medium temperature blocks, the second heat load (such as underfloor heating, a radiator, a heat exchanger new air heater, a fan coil) that can be used in either heating or cooling mode, (i) in heating mode: said refrigerant first goes through a first non-return valve 26, then through the medium temperature block 3, then through the exchanger of the second heat load, then through the expander 5, then through the exchanger of the first source of heat, then by the low temperature block 4 used as heat exchanger of the second heat source, then again by the four-way valve of cycle reversal 6, in a different circuit, then the refrigerant 20 enters the suction compressor 1, and the cycle resumes; (ii) in cooling mode: said refrigerant 20 passes through the low temperature block 4 used as exchanger of the second source, then by the exchanger of the first source, then by the expander 5, then by the exchanger of the second thermal load, then by a second non-return valve 36, and then by the four-way valve with cycle reversal 6, in a different circuit, then the refrigerant 20 enters the suction of the compressor 1, and the cycle resumes; (b) for use with two heat sources and three heat loads, the third heat load being preferentially the sanitary water (of more limited capacity compared to the case (a)), this third heat load being connected by a circuit independent at the high temperature block 2, the first thermal loads preferably being underfloor heating, a radiator, a fresh air heating exchanger, a fan coil, (i) in heating mode: the refrigerant 20 passes from firstly by means of the medium temperature block 3 used as exchanger of the first heat load, then by the exchanger of the second heat load, then the expander 5, then by the exchanger of the first heat source, then by the low temperature block 4 used as heat exchanger of the second heat source, then by the four-way valve with cycle reversal 6, in a different circuit, then the fluid f rigorigen 20 enters the suction of the compressor 1, and the cycle resumes; (ii) in cooling mode: the refrigerant 20 passes first through the low temperature block 4 used as the exchanger of the second source, then by the exchanger of the first source, then by the expander 5, then by the exchanger of the second load, then by the medium temperature block 3 used as exchanger of the first load, then by the four-way valve to cycle 6 reversal, in a different circuit, and the refrigerant 20 enters the suction of the compressor 1, and the cycle resumes.  DESCRIPTION OF THE FIGURES FIG. 1 describes the MUSTT module according to the invention in a non-reversible version.  Figure 2 depicts the MUSTT module in a reversible version with non-return valves usable for space heating and cooling.  FIG. 3 represents the reversible module according to the invention without check valves, on which additional storage blocks 200, 300 have been added by way of example for the eventual needs of a specific installation.  FIGS. 4 to 16 describe, in a non-exhaustive manner, various embodiments of particular installations according to the invention (in a non-reversible and reversible version).  Figures 4 to 6 more specifically describe embodiments based on a single heat source in a non-reversible module.  FIG. 4 describes a system provided with a non-reversible module used solely for heating the domestic hot water from an air exchanger (extract or external) / refrigerant 7.  FIG. 5 depicts a system provided with a non-reversible module used to heat the domestic hot water and a space from an air exchanger (extract or outside) / refrigerant.  The space heating exchanger is a refrigerant / air type exchanger 16.  Figure 6 depicts a system provided with a non-reversible module used to heat domestic hot water and a space from a geothermal loop charged with refrigerant 13.  The intermediate refrigerant / water exchanger 11 is completed by one or more water exchangers 15, 17.  FIG. 7 describes a system provided with a non-reversible module used for heating domestic hot water and a space from a first source constituted by a water or brine 14 geothermal loop that transmits its heat to a water / water heat exchanger. refrigerant 11 and a second source consisting of an air exchanger / refrigerant 7 (extract air or outside air).  The intermediate refrigerant / water cooler 11 is completed by one or more water exchangers 15 and 17.  FIG. 8 depicts a system provided with a non-reversible module used to heat domestic hot water and a space from an air / refrigerant exchanger 7 (extract air or outside air) and a solar thermal panel 10.  The intermediate refrigerant / water exchanger 11 is completed by one or more water exchangers 15, 17.  FIG. 9 describes a system provided with a non-reversible module used to heat domestic hot water and a space from a first source constituted by a water or brine 14 geothermal loop which transmits its heat to a water / heat exchanger. refrigerant 12 and a second source constituted by a solar thermal panel 10.  The intermediate refrigerant / water exchanger 11 is completed by one or more water exchangers 15, 17.  FIG. 10 depicts a system provided with a reversible module provided with nonreturn valves 26, 36 on block 3 used to heat domestic hot water and to heat / cool a space from a geothermal water or brine loop. 14 which transmits its heat to a water / refrigerant exchanger 12 and a solar thermal panel 10.  The heat exchanger or heat exchanger space are water exchangers 15, 17, 30 connected to a refrigerant / water or brine intermediate heat exchanger 11.  FIG. 11 describes a system provided with a reversible module provided with check valves 26, 36 on the block 3 used for heating domestic hot water and heating / cooling a space from an air / refrigerant exchanger 7 (extract air or outside air) and a thermal solar panel 10.  The exchanger (s) heating or cooling the space are exchangers type refrigerant / air 16.  FIG. 12 depicts a system provided with a reversible module provided with non-return valves 26, 36 on the block 3 used to heat domestic hot water and to heat / cool a space from a geothermal water or brine loop. 14 which transmits its heat to a water / refrigerant exchanger 12 and an air exchanger / refrigerant 7 (extract air or outdoor air.  The heat exchanger or heat exchanger or space cooling are water exchangers 15, 17, connected to a refrigerant / water or brine 11 intermediate heat exchanger.  FIG. 13 depicts a system provided with a non-reversible module used to heat domestic hot water and a space from an air / refrigerant exchanger 7 (extract air or outside air) and a solar thermal panel 10.  The heat exchanger or heat exchangers are water exchangers 15, 17, such as water radiators, connected directly to the exchange and storage unit at medium temperature 3.  Only the high temperature exchange and storage block 2 heats the domestic hot water.  In addition, a refrigerant / air space heat exchanger 16 is added to the system.  FIG. 14 depicts a system provided with a reversible module used to heat domestic hot water and to heat / cool a space from an air / refrigerant exchanger 7 (extract air or outside air) and a panel solar thermal 10.  The heat exchanger (s) heating or cooling the space are water exchangers 15, 17 connected directly to the exchange and storage unit at medium temperature 3.  Only the high temperature exchange and storage block heats the sanitary water.  In addition, there is added to the system a refrigerant / air space heating or cooling exchanger 16.  FIG. 15 describes a system provided with a reversible module used to heat domestic hot water and to heat / cool a space from a first source constituted by a water or brine 14 geothermal loop that transmits or takes its heat to a exchanger water / refrigerant 12 and a second source constituted by a solar thermal panel 10.  The heat exchanger (s) heating or cooling the space are water exchangers 15, 17 connected directly to the exchange and storage unit at medium temperature 3.  Only the high temperature exchange and storage block 2 heats the domestic hot water.  In addition, a refrigerant / refrigerant space cooling or heating exchanger 16 is added to the system.  FIG. 16 describes a system provided with a reversible module not equipped with check valves, used for heating domestic hot water and for heating / cooling a space from an air / refrigerant exchanger 7 (extract air or outside air) ) and a solar thermal panel 10.  The heat exchanger (s) heating or cooling the space are water exchangers 15, 17 connected directly to the exchange and storage unit at medium temperature 3.  A refrigerant / refrigerant space heating or cooling exchanger 16 is added to the system.  In addition, an exchange and storage block 3 "is added to the circuit of the solar thermal panel 10.  The domestic hot water is passed in series first by this additional exchange and storage block, then by the high temperature exchange and storage block 2.  FIG. 17 represents a block diagram representing the exchange and storage blocks according to the technological approach of the plate heat exchangers.  Figure 17a is a top view, Figure 17b is a side view.  FIG. 18 represents a schematic diagram representing the exchange and storage blocks according to the technological approach of the copper tubular exchangers.  Figure 18a is a front view, Figure 18b is a top view.  Fig. 19 shows a way of organizing the components of the system of Fig. 20 with the components of Fig. 24.  List of marks used in the figures: 1.  Refrigerant compressor 25 2, 200.  High temperature heat exchange and storage block 3, 300.  Heat exchange and storage block medium temperature 4.  Low temperature heat exchange and storage block 5 / Expansion valve controlled remotely by an electronic control unit 6/4-way cycle reversal valve 30 7 / Air / refrigerant type exchanger (typically extract air or outside air) 8 / Motorcycle fan 2906603 12 9 / Water pump and expansion tank 10 / Solar thermal panel 11 / Refrigerant heat exchanger to water type 12 / Water source or brine / refrigerant type exchanger 5 13 / Refrigerant geothermal loop 14 / Water or brine geothermal loop (typically propylene glycol) 15 / Apparatus for heating or cooling using water as a transfer medium 16 / Apparatus for heating or cooling using refrigerant 10 as a transfer medium 17 / Hot water radiator 18 / Classic AC power supply 19 / Injection valve to limit the compressor discharge temperature in heating mode 15 20 / Refrigerant 21 / Electronic control 22 / Domestic hot water circuit 23 / Domestic hot water mixing valve 24 / Water or brine (Ethylene Glycol or equivalent) 20 25 / Domestic hot water 26, 36 / Check valve Non-return valve 27, 28 / Refrigerant connection 29, 30 / Refrigerant connection 31 / Copper tubes 25 32 / Heat exchange and storage material 33 / Plates Detailed description of the invention 2906603 13 a) Definitions In the present document, the term "thermodynamic system" means an assembly comprising a compressor and a plurality of exchangers in which circulates a specific transfer fluid, usually called a refrigerant fluid.  • Geothermal loop: A set of pipes placed in the ground typically in a vertical or horizontal position and intended to exchange heat between the heating or cooling system and the ground.  Heat exchanger: Device for transferring heat between several circuits Transfer fluid: fluid used to transfer heat; conventional examples are refrigerant, water or brine Sometimes referred to as brine Heat Source or Source: By convention, the terms source and heat load refer to heating mode.  The source is the medium from which the heat is extracted in heating mode.  This heat extraction is carried out with certain physical characteristics such as the thermal inertia or the available power that characterize the source.  It may be noted that the source term is unsuitable in cooling mode because it is in fact rejecting the heat coming from the building. Thermal load or load: The load is the medium where the heat is rejected in heating mode.  This heat rejection is effected with certain physical characteristics such as the thermal inertia or the available power which characterize the source, and the charge is the place from which the heat is removed in cooling mode.  Secondary fluid: this term is used to designate the fluid flowing in the circuit of the exchanger block which is not traversed by the refrigerant.  • Desuperheater: gas cooler in cycles using conventional refrigerants (such as HFCs).  This exchanger only carries out a sensible heat exchange.  There is no condensation in the exchanger.  ^ gas cooler or gas cooler.  The term gas cooler is often used in cycles using CO2 since there is no condensation in this cycle, which prohibits the use of the term condenser used for conventional refrigerants.  • Subcooler: Located downstream of the condenser, this exchanger performs additional cooling of the refrigerant in liquid form in order to increase the performance of the refrigeration cycle.  • Loop open: in an open loop, the transfer fluid is constantly renewed.  It does not circulate indefinitely on the same circuit as in the case of a so-called closed loop.  B) General description The hybrid module as well as the systems which incorporate it according to the invention combine, on the one hand, the conventional components of thermodynamic systems and, on the other hand, storage and heat exchange elements using a suitable material. to store the heat.  The term hybrid is related to this dual function of exchange and storage of heat.  The hybrid module (MUSTT) is the main basis for multiple systems that can be adapted to many installations for domestic hot water heating and / or space heating and / or cooling.  When placed in one of the various systems described below, the module according to the invention transfers the heat energy and the charge of one or more heat sources into three exchange blocks 2, 3, 4 and heat storage.  In a preferred embodiment of the module according to the invention, the storage of heat is obtained through the use of solid / liquid phase change materials which make it possible to store the heat in latent form.  Each block has a different phase change temperature.  The heat energy stored in each block is used by the system according to the needs of hot water and / or heating.  A specific version of the module also provides the cooling function.  Heat storage materials usable for the manufacture of heat exchange and storage blocks according to the invention are the composites consisting of a porous matrix of graphite and paraffin as described in the publication entitled Paraffin Composite matrix porousugraphite as a high and constant thermal thermal storage material by Xavier Py, Régis Olives and Sylvain Mauran 2906603 15 (PROMES Laboratory - Perpignan-France) (International Journal of Heat and Mass Transfer 44 (2001) 2727-2737).  Other novel or known phase-change materials, such as fatty acids or molten salts mixed with expanded natural graphite can also be used for the manufacture of the exchange and storage blocks of the module according to the invention.  The module according to the invention is usable with the current HFC refrigerants, such as 134A, 410A, 407C or 404A, these references being known to those skilled in the art.  The module according to the invention is also usable with hydrocarbons and in particular propane, butane and their mixtures.  It can also work with carbon dioxide (CO2), or with any other suitable refrigerant.  We will first describe each of the elements of the system according to the invention and their role.  We will specify if necessary the case of the two main types of refrigerant considered: on the one hand the fluids of the type HFC (hydro fluoro carbon) such as R134a, R407C, R404A, R410A, or hydrocarbons such as propane, and on the other hand the specific case of CO2.  C) Detailed Description of Components 1 - Refrigerant Compressor 1 Typically, the compressor is volumetric, vane type or spiroorbital type for HFCs and hydrocarbons.  25-piston models can also be used for CO2.  Advantageously, the operating range of the compressor accepts the highest possible low pressure to maximize the coefficient of performance, in particular when a solar thermal collector 10 is connected to the low temperature exchange and storage block.  The COP of the heating system is all the higher as the suction pressure of the compressor is high.  The heat input of the second heat source makes it possible to increase the low pressure, particularly in the case where the second source is a solar thermal collector 10.  In a variant of the module according to the invention, the compressor 1 is supplied with direct current of photovoltaic origin in order to maximize the energy efficiency of the module.  In fact, the electrical energy of photovoltaic origin will be deducted from the electrical energy consumption of the system.  The power of the compressor at a given operating condition may be fixed because the exchange and storage blocks limit by their thermal inertia the frequency of starts.  It will, however, also be possible to connect a variable power compressor (for example of the type invented). 2 - Heat exchange and storage blocks 2, 3, 4, 200, 300 Each exchange and storage block of the heat consists of a storage part and an exchanger part.  Heat storage uses materials with high thermal conductivity.  In the heat exchange and storage blocks of the module according to the invention, an expanded natural paraffin / graphite composite material is advantageously used.  The phase change temperature of the material is adapted to the needs.  The thermal conductivity of pure paraffin is 0.24 W / M / K.  The thermal conductivity of the expanded natural graphite / paraffin composite material can range from 4 to 70 W / M / K.  The thermal conductivity of the expanded natural paraffin / graphite composite material is equal to that of the graphite matrix (the thermal conductivity of paraffin being very low compared to that of graphite).  The exchanger portion allows the transfer of heat between the refrigerant and the storage material and between the storage material and the secondary exchange fluid.  These 2 types of exchanges are made for example by the exchanger shown in FIG. 24.  Recovered heat is first stored in latent form by the material at its specific phase change temperature.  When the material is liquid, a sensitive additional storage intervenes by raising the temperature of the liquid material.  The material may solidify in part or in full depending on the amount of heat exchanged.  The regulation of the machine will intervene then to start the compressor and thus reload the material in amount of heat.  The amount of material will be optimized for medium intensity use.  It can be adapted to specific needs with additional blocks 200, 300 shown in FIG.  High temperature exchange and storage block 2, 200 According to the invention, the phase change value of the high temperature block is adjusted to a value advantageously between 60 and 75 ° C. and preferably 65 and 70 ° C. for the fluids HFCs and hydrocarbons.  This value is between 75 and 90 C and preferably 80 to 85 C for the CO2 given the operating conditions of this fluid.  In the case of the high temperature block, the secondary exchange fluid is hot sanitary water.  The heat exchange between the refrigerant and the water is through the storage material.  This tends to restrict the performance but allows to have a double wall effect between the sanitary water and the refrigerant.  This double wall effect is a legal requirement in some countries.  The high temperature exchange and storage block 2 is used as storage of the sensible heat of the refrigerant, thus as a gas cooler or desuperheater, both in the case where the refrigerant is an HFC or a hydrocarbon only in the case where the refrigerant is CO2.  The sanitary water, as it circulates, recovers the sensible and latent heat stored by the phase change material, and thus it heats up.  In the circuit, the high temperature block is located before the cycle reversal valve.  Therefore, its mode of operation remains the same in heating mode and in cooling mode.  Medium temperature exchange and storage block 3, 300: 30 According to the invention, the phase change value of the medium temperature block 3 is set to a value of between 32 and 45 ° C. and preferably of between 35 ° C. and 40 ° C. for HFC fluids, hydrocarbons and for CO2.  The secondary fluid is domestic water 25 (example Figure 10) or water heating circuit 24 (Figure II).  This block is used mainly as storage of the latent heat of the refrigerant, thus as a condenser in the case of HFCs and hydrocarbons or as storage of the sensible heat of the refrigerant in the case of CO2 (second gas cooler).  In heating mode, the recovered heat is first stored in latent form by the material at its specific phase change temperature.  When the material is liquid, sensitive additional storage occurs by raising the temperature of the liquid material.  In cooling mode, the refrigeration cycle is reversed.  When the system is equipped with check valves, because of these valves the medium temperature block does not see any refrigerant, so the stored heat remains stored, and can be used for heating the sanitary water.  When the system is not equipped with a check valve, the block cools down until the storage material is solid and then its temperature falls to reach the operating condition of the system.  There is a sensible thermal inertia related to the mass of the material.  A second medium temperature storage exchange block may be used in some systems having a solar collector as a heat source.  The use of this second block will increase the power available for heating domestic water.  Low temperature exchange and storage block 4: 25 The phase change value of the low temperature block material is set to a value between 15 and 25 C and preferably 17 and 22 C regardless of the refrigerant.  In addition, the low-pressure circuit of the refrigerant must be sufficiently sized to limit the losses.  The secondary fluid is the refrigerant itself (in the case of the internal exchanger of FIGS. 4 to 8), water or brine (as a function of the systems of FIGS. 9 to 22). The low temperature block has two main duties.  On the one hand, as is the case in FIGS. 4 to 8, it acts as an internal exchanger which withdraws heat at the outlet of the condenser.  It is a subcooler in the case of HFCs or hydrocarbons or a third gas cooler (gas cooler) in the case of CO2.  Simultaneously, it heats the suction gases of the compressor.  Thus, it helps to heat the discharge gases and therefore to increase the amount of heat that is stored by the high temperature block.  But the amount of heat stored by the high temperature block is a critical point for the instantaneous heating of domestic hot water.  In addition, the low temperature block stores a quantity of heat that can be used punctually by the compressor to meet the hot water requirements.  This is useful in particular if there is only one continuous source but of low power, for example when the source is only a heat exchanger on the extracted air.  On the other hand, as is the case in FIGS. 9 to 23, the low temperature block can serve as a heat source used separately or in conjunction with another source.  The machine control controls pressure and temperature settings to optimize system efficiency within the reliable operating range.  The regulation takes place on the compressor 1, the position of the electronic expansion valve 5 and the activation of the circulation pumps 9.  In heating mode, the recovered heat is first stored in latent form by the material at its specific phase change temperature.  When the material is liquid and the second source is sufficiently hot, a substantial additional storage takes place by raising the temperature of the liquid material (case of the

  figure 9 equipped with a solar collector) up to the maximum value accepted by the regulation.  In cooling mode, the refrigeration cycle is reversed.  The block will heat up until the phase change material is liquid.  It will then heat in sensitive.  This heat may be partially removed if the material is connected to an air exchanger (FIG. 20).  Or, the block will be passive and the system heat will be transmitted to the first by the refrigerant (Figure 19).  2906603 20 3 - Regulator controlled remotely by an electronic control 5: This regulator will typically consist of a valve whose opening and closing are controlled by a stepper motor.  It will regulate the flow of refrigerant in the circuit according to the command sent by the regulation.  It will be ensured that the electronic expansion valve remains in the acceptable pressure range for the compressor.  4 - 4-way reversing valve 6: This valve makes it possible to reverse the direction of the refrigerant in the circuit and thus ensure heating and cooling operation as required.  5 -Exchanger of air / refrigerant type 7: The air used by this exchanger is typically extracted air (by the VMC of the apartment / dwelling on which the system is installed) or outside air 15 exchanger is a source of heat in heating mode.  It can also reject heat in cold mode.  6 - Motorcycle fan 8: It consists of a fan and its associated motor.  7 - Water Pump and Expansion Tank 9: This pump circulates water or brine (typically ethylene or propylene glycol) between system heat exchangers.  The water pump may be on the heating water circuit and / or on the heat source circuit when this source is a geothermal loop.  8 - Solar thermal panel 10: This panel captures solar energy and transmits it to the fluid (such as propylene glycol) from its own circuit.  In the present invention, the solar thermal panel supplies the low temperature exchange and storage block. The low temperature block, during the duration of its liquefaction, tends to stabilize for a certain time the temperature of return of the fluid to the solar panel at a temperature of 30.degree. low level, which increases its efficiency.  9 - Refrigerant to water heat exchanger 11: 5 This heat exchanger transfers heat between the refrigerant and the heating water of a space and therefore allows the use of different types of water exchangers described in 15 and 17.  10 - Source exchanger water or brine / refrigerant type 12: This exchanger makes it possible to transfer the heat between the water or the brine and the refrigerant.  It allows open-loop operation or the use of a geothermal water loop (Figure 7).  11 - Refrigerant geothermal loop 13: This loop transfers the energy between the ground and the refrigerant.  12 - Water or brine geothermal loop (typically propylene glycol) 14: 15 This loop transfers energy between the soil and the brine 13 - Apparatus for heating or cooling using water as a transfer medium 15: Common appliances are fan-convectors, water-air exchangers for heating or cooling fresh air and heating floor-cooling water circulation.  14 - Apparatus for heating or air conditioning and using refrigerant as a transfer fluid 16: Common appliances are wall units, consoles and refrigerant batteries for fresh air.  15 - Hot water radiator 17: These devices do not allow cooling because of the generated condensation.  16 - Power supply 18: 30 Generally, we will use a conventional AC power supply: 2906603 22 It is also possible to consider the use of a DC power supply, especially obtained from a photovoltaic solar panel.  17 - Injection valve to limit the discharge temperature of the compressor in 19: 5 heating mode This valve limits the discharge temperature of the compressor in heating mode.  As a result, it extends the operating range of the compressor in systems equipped with a liquid vapor exchanger.  18 - Refrigerant 20: HFC fluids (eg 134A, 407C, 404A & 410A) are the most common.  It is also possible to use hydrocarbons, and more particularly propane as a refrigerant.  It is also possible to use CO2. The module according to the invention adapts to all types of fluids.  The high operating pressures of systems using CO2 require specific sizing according to principles known to those skilled in the art.  15 19 Electronic control 21: It receives the information (pressure, temperatures, operating setpoints) and controls the various elements of the system (compressors, expansion valve, pumps, fans).  It should be noted that the regulation of the electronic expansion valve will be very different in the case of HFCs and in the case of CO2.  20 -Circuit of domestic hot water 22: The pressure is given by the water supply network.  Depending on the system, the domestic hot water passes either through the high temperature exchange and storage block or in series through the high temperature exchange and storage block 25 and the medium exchange and storage block. temperature.  21 - Domestic hot water mixing valve 23: This valve makes it possible to avoid burns by maintaining a water outlet temperature of approximately 50 C before use by mixing a water at approximately 10-20 C from the heating network. supply of water and water at 60-70 C from the exchange block and high temperature storage.  It is indeed necessary to store domestic hot water at a temperature of at least 60 C because storage at temperatures between 40 and 60 C promote the development of legionella colonies.  2906603 23 27 -Non-return valves 26, 36: They allow the passage of gas only in one direction.  Therefore, the two check valves used together allow the passage of the refrigerant through the medium temperature block in heating mode and allow a direct passage of the refrigerant in cooling mode.  d) Advantages of the invention The module according to the invention has many advantages over existing solutions, among which may be mentioned, in a non-exhaustive manner: The increase of the efficiency in heating mode of domestic hot water that there is or not a heating or cooling load, instantaneous heating of the water at high temperature to avoid the risk of legionellosis associated with storage at medium temperature, 15 reduction of the space requirement, - flexible installation due to at the simultaneous presence of refrigerant connections and water, the ease of installation at the origin or later thermal solar collectors (or photovoltaic with the appropriate option) 20 The removal of the buffer tank to avoid the cycling of the compressor The heating and simultaneous cooling of water and air for optimal comfort.  e) Detailed description of the operation of the devices according to the invention Increasing the efficiency of the heating of the sanitary water is a specific advantage of the invention.  The heating of sanitary water by a thermodynamic system such as a heat pump can be done conventionally in two ways: On the one hand, the heating of the water can be done by means of a gas cooler or a desuperheater.  This type of system has two major disadvantages.  The first disadvantage of systems using a gas cooler is the insufficient discharge temperature which does not generate enough heat output available in response to the discharge of the compressor.  The invention solves this first problem thanks to the low temperature exchange and storage block 4 used here as a vapor liquid exchanger, which increases the compressor suction temperature and consequently its discharge temperature.  It should be noted that a conventional liquid vapor exchanger without storage could also achieve this temperature rise, but with the following limitation: due to the phenomenon of heat transfer by a wall, the temperature rise of the gas is all the more more important than the temperature difference is large between the low pressure part of this exchanger and its high pressure part.  In practice, a vapor-liquid exchanger must not be oversized in a conventional system if it is desired to avoid excessively high discharge temperatures when the conditions change (lowering the suction pressure or increasing the discharge pressure).  This therefore limits the efficiency of this conventional vapor-liquid exchanger.  The advantage of using, as in the present invention, a heat exchanger block provided with a phase change heat storage material is to stabilize the suction temperature at the phase change value of the material for a certain time, during this time, the other storage blocks can be loaded.  Therefore, the exchanger block and the phase change temperature of the material can be dimensioned to maximize its efficiency at the conditions stabilized by the phase change materials.  This is true even for relatively low condensation temperatures such as that chosen for the medium temperature exchange and storage block.  Thus, the power recovered at high temperature will be higher which will be favorable for heating the domestic hot water.  This temperature stabilization is also useful in systems with two heat sources when one of the sources has a high instantaneous power under certain conditions.  This can be the case if said source is a solar thermal collector.  In case of strong sunlight, it is possible to turn on the circulation pump of the solar collector.  The exchange is at an acceptable temperature for the compressor by controlling the risk of excessive rise in pressure and / or suction temperature.  The operating time of the circulation pump determines the power transmitted per hour by the solar thermal collector to the thermodynamic circuit.  When using a phase change material for heat storage, this power is more constant over time due to the phase change process of the material, which stabilizes the operating conditions of the compressor.  Moreover, the energy stored in the low temperature block 4 is available for the compressor 1 for a power peak of limited duration to compensate more quickly for an intense draw of domestic hot water.  This available stored energy is added to that of the conventional source of the system and can in certain cases avoid the start-up of electrical resistance booster systems, which are not very energy efficient.  This case is particularly useful if the compressor 1 is provided with a speed variation.  Additional power can be added to the second source without the use of a phase change material exchanger but the temperature stabilization and power reserve described above will not be achieved.  The second disadvantage of systems using a gas cooler is the need for a heat load (heating or air conditioning) that is not used to heat domestic hot water.  The system according to the invention responds to it thanks to the combined use of the low 4, medium 3 and high temperature 2 blocks in a charge phase by thermodynamic cycle and a discharge phase by circulation of domestic hot water.  The coefficient of performance (COP) of this type of operation depends on the conditions and the system but is typically of the order of 4 to 4.5.  Conventionally, sanitary water heating can also be done by using the condensing power of the thermodynamic cycle.  In this case usually, a so-called three-way valve valve dries water from the condensation circuit to an exchanger located in the hot water storage.  The condensing temperature is increased to a value close to the temperature of the domestic hot water stored. The coefficient of performance will thus gradually decrease until it reaches values of the order of 2 to 2.5.  It can be estimated that the average COP during the period of heating and maintaining the temperature of the domestic hot water is about 3.  In addition, with such a system using a three-way valve 2906603 26 ways, it is not possible simultaneously to heat or cool the space and to heat the domestic hot water The reduction in consumption with the system according to the invention exceeds 30% for the 5 domestic hot water heating (COP of 4.5 instead of 3).  The simultaneous heating or cooling of the space remains possible.  We describe below several embodiments for systems according to the invention for detailing the operation of the systems shown in FIGS. 4 to 10.  1) Non-Reversible Embodiments A first embodiment is the non-reversible mode described above as a second object of the present invention.  This embodiment can be realized in different ways.  a) Use with a heat source and a heat load In this embodiment, the components are arranged so that the refrigerant 20 leaves the discharge of the compressor 1 by first passing through the high temperature block 2 and then by the medium temperature block 3, then passes through the low temperature block 4, by the expander 5, by a heat source heat exchanger (such as a heat exchanger on the extracted air or a geothermal loop), then by a circuit different from that of the first pass, again by the low temperature block 4, then said refrigerant 20 enters the suction of the compressor 1, and the cycle resumes.  A first embodiment of this type is described schematically in FIG. 4.  FIG. 4 represents a system provided with the module according to the invention which is not reversible and an air exchanger (extract or external) / refrigerant 7.  In the present system, the heat load is very preferably the hot water.  The heating power is typically about 2 KW on the extracted air.  In the case of outdoor air, the heating power is dependent on meteorological conditions and is typically between 2 and 10 kW for residential applications, but could reach higher values for other uses. .  During the charging period, the compressor 1 operates and charges the high temperature exchange and storage blocks 2 and medium temperature 3.  The charge is at a high performance ratio of operation, of the order of 4 to 5, in particular for the heating of the sanitary water, with typically 40 C of condensation for an HFC or a hydrocarbon.  The refrigerant then passes into an internal heat exchanger which transfers heat to the gases at the suction of the compressor.  It then passes through the electronic expansion valve and joins the heat source evaporator.  When there is demand for domestic hot water, it goes into series first in the medium temperature block 3 and then in the high temperature block 2.  This water is so necessary mixed with cooler water to avoid burns.  It was thus instantly generated water of suitable temperature that was not stored in the temperature range 40 to 50 C favorable to the development of legionellosis.  In this embodiment, the low temperature exchange and storage block 4 is used as an internal exchanger.  It should be noted that the air exchanger (extract or external) / refrigerant 7 can be replaced by another source of heat, for example by a geothermal loop loaded with refrigerant 13, or a geothermal loop loaded with water 14.  The operation of the system remains similar to that described above.  Refrigerant 13 or water 14 geothermal loops are usually more powerful and more stable than air / refrigerant exchangers, but are not usable on all homes / buildings.  b) Embodiment with a heat source and two heat loads In this embodiment, the components are arranged so that the refrigerant 20 leaves the discharge of the compressor 1 by first passing through the high temperature block 2 and then by the medium temperature block 3, then passes through the exchanger of the second heat load, then passes through the low temperature block 4, by the expander 5, by a heat source exchanger (such as a heat exchanger on the extracted air or a geothermal loop), then, by a circuit different from that of the first passage, again by the low temperature block 4, then said refrigerant 20 enters the suction of the compressor 1, and the cycle resumes.  This embodiment of the invention is represented in FIG. 5.  The system is similar to that of the first embodiment of FIG. 4 and is provided with the non-reversible module according to the invention and an air exchanger (extract or external) / refrigerant fluid 7.  The device of this embodiment also has an additional function of space heating, given by a refrigerant / air exchanger 16.  The first heat load is preferably hot water.  The second heat load may for example be underfloor heating, a radiator, a fresh air exchanger, a convector fan.  When the system is used simultaneously to heat the space and the sanitary water, the compressor 1 transfers refrigerant successively in the two exchange blocks and storage high temperature 2 and medium temperature 3 and the fluid passes through the heat exchanger. space heating. .  The regulation may be made to make arbitrations if the heat available at the source is insufficient.  Depending on the use, the heat energy may for example mainly be intended for heating the hot water.  In this case, the capacity of the heat exchanger will be limited for example by stopping the exchange fan or reducing its speed.  When the system is used solely to heat domestic water, its operation is similar to that described in the first embodiment.  In this embodiment, the low temperature exchange and storage block 4 is used as an internal exchanger.  It should be noted that the air exchanger (extract or external) / refrigerant 7 may be replaced by another source of heat if necessary, for example by a geothermal loop 25 charged with refrigerant.  The operation of the system will be similar to that described above.  The geothermal loop is usually more powerful and more stable than the air / refrigerant exchanger.  Another embodiment of this type is shown in FIG.  The device of the embodiment according to the invention of FIG. 6 is provided with a non-reversible module according to the invention, of an assembly composed of an intermediate source exchanger of water (or brine) / refrigerant type 12 and of a water or brine geothermal loop 14 as a heat source, a refrigerant / water intermediate exchanger 11 itself supplemented with one or more water exchangers 15, 17.  In the embodiment shown in FIG. 6, the operation is similar to that of the embodiment of FIG.  In this embodiment, the low temperature exchange and storage block 4 is used as an internal exchanger.  c) Embodiment with two heat sources and two heat loads In this embodiment, the components are arranged so that the refrigerant 20 leaves the discharge of the compressor 1 by first passing through the high temperature block 2 and then by the medium temperature block 3, then passes through a first exchanger on the heat load, then by the expander 5, then by an exchanger of a first heat source, then by the low temperature block 4 used as exchanger a second source of heat, then the refrigerant 20 enters the suction of the compressor 1, and the cycle resumes.  One of said heat loads is preferably domestic hot water, the other may be for example a floor heating, a radiator, a fresh air heating exchanger, a convector fan.  An embodiment of this type according to the invention is shown in FIG. 7.  FIG. 7 describes a non-reversible module used to heat domestic hot water and a space from a first source constituted by a water or brine 14 geothermal loop that transmits its heat to a water / refrigerant exchanger 12 and 25. a second source consisting of an air / refrigerant exchanger (extract air or outside air) 7.  For space heating, a refrigerant / water intermediate heat exchanger 11 is completed by one or more water exchangers 15 and 17.  Another embodiment of this type is shown in FIG. 8.  In the embodiment according to the invention, the system is provided with a non-reversible module according to the invention, an air / refrigerant exchanger (extracted air or external air) 7 and a solar thermal panel 10 as heat sources and a refrigerant / water intermediate exchanger 11 supplemented with one or more water exchangers 15, 17 used for space heating.  The system of the embodiment shown in FIG. 8 is used to heat domestic hot water and a space.  In the embodiment shown in FIG. 8, when the system is used simultaneously to heat space and sanitary water, the exchange and storage block is used both for heating domestic water and for space heating through the intermediate heat exchanger 11.  When the system is used solely to heat domestic water, there is an overabundance of available power from both sources.  The regulation manages the power distribution thanks to the regulator and the actuators (pumps or fan).  Another embodiment of the invention is shown in FIG. 9.  FIG. 9 depicts a non-reversible module used to heat domestic hot water and a space from a first source constituted by a water or brine geothermal loop 14 which transmits its heat to a water / refrigerant exchanger and to a heat exchanger. a second source constituted by a solar thermal panel (10).  The intermediate refrigerant / water cooler 11 is completed by one or more water exchangers 15 and 17.  When the system is used simultaneously to heat the space and the domestic water, the temperature of the geothermal source is of the order of 0 C (case of a horizontal collection), also the heat of the solar thermal panel 10 will have to first liquefy the material of the low temperature block 4.  The discharge temperature will still be sufficient to charge the high temperature block 2.  Indeed, the lower suction pressure and the overheating of the solar thermal panel 10 will maintain sufficiently high suction superheat.  The performance will be worse than in the case of Figure 9 but the power in a well-sized system will be sufficient throughout the year.  When the system is used solely to heat domestic water, there is an excess of available power from both sources.  The regulation manages the distribution of power through the expander and the actuators (pumps or fan) 2906603 2) Reversible embodiments A second embodiment is the reversible mode described above as the third object of the present invention.  This embodiment can be realized in different ways.  a) Embodiment with two heat sources and two heat loads In this embodiment, the first heat load is preferably hot water.  This first heat load is connected by an independent circuit 10 in series to the high temperature and medium temperature blocks.  The second heat load can be used in either heating or cooling mode.  In this embodiment, the components are arranged so that the refrigerant (20) leaves the discharge of the compressor (1) by first passing through the high temperature block (2) and then through the four-way valve. cycle reversal (6), then: (i) If the second heat load is used in heating mode: said refrigerant first passes through a first non-return valve (26), then through the medium temperature block ( 3), then by the exchanger of the second heat load, then by the expander (5), then by the heat exchanger of the first heat source, then by the low temperature block (4) used as exchanger of the second heat source, then again by the four-way reversing valve (6), in a different circuit, then the refrigerant (20) enters the suction of the compressor (1), and the cycle resumes.  (Ii) If the second heat load is used in cooling mode: said refrigerant (20) passes through the low temperature block (4) used as exchanger of the second source, then by the exchanger of the first source, then by the expander (5), then by the exchanger of the second heat load, then by a second non-return valve (36), and then by the four-way reversing valve (6), in a different circuit, then the refrigerant (20) enters the suction of the compressor (1), and the cycle resumes.  An example of this embodiment of the invention is shown in FIG. 10.  FIG. 10 describes a reversible module according to the invention provided with non-return valves as represented in FIG. 2, used for heating domestic hot water and a space from a first source constituted by a geothermal water or brine loop. which transmits its heat to a water / refrigerant exchanger and a second source constituted by a solar thermal panel 10.  For the space heating part, the intermediate refrigerant / water exchanger 11 is completed by one or more water exchangers 15 and 17.  In this embodiment, the medium temperature block 3 is provided with non-return valve flaps.  The reversible module is thus adapted to the heating of sanitary water simultaneously with a thermal load (heating mode or cooling mode) In heating mode, the medium temperature block 3 is traversed by the refrigerant.  This block is therefore charged with heat for use by domestic hot water.  In cooling mode, the set of two valves makes it possible to bypass the medium temperature block 3.  The heat stored there is available for hot water.  Another embodiment of the invention is shown in FIG. 11 which describes a reversible module according to the invention provided with nonreturn valves 26, 36 as represented in FIG. 2, used to heat domestic hot water and a space from a first source constituted by an air exchanger (extract or external) / refrigerant 7 and a second source constituted by a solar thermal panel (10).  For the space heating part, the exchanger is a refrigerant / air exchanger 16.  The operation of the system of this embodiment is similar to that shown in FIG.  Another embodiment of the invention is shown in FIG.  FIG. 12 describes a reversible module according to the invention provided with nonreturn valves 26, 36 as represented in FIG. 2, used for heating domestic hot water and a space 30 from a first source constituted by a geothermal loop. water or brine 14 which transmits its heat to a water / refrigerant exchanger and a second source constituted by an air exchanger (extract or external) / refrigerant 7.  For the space heating part, the intermediate refrigerant / water exchanger 11 is completed by one or more water exchangers 15 and 17.  The operation of the system of this embodiment is similar to that shown in FIG.  B) Embodiment with two heat sources and three thermal charges In this embodiment, the third heat load is preferably hot water (of more limited capacity than in case 2a) described above).  This third thermal load is connected by an independent circuit to the high temperature block (2).  The other two heat loads can be used either in heating mode or in cooling mode.  In this embodiment, the components are arranged so that the refrigerant (20) leaves the discharge of the compressor (1) by first passing through the high temperature block (2) and then through the four-way valve. cycle reversal (6), then: (i) In heating mode: the refrigerant (20) passes firstly through the medium temperature block (3) used as exchanger of the first heat load, then by the exchanger of the second thermal load, then the expander (5), then by ('changer of the first source of heat, then by the low temperature block (4) used as exchanger of the second heat source, then by the valve four In a different circuit, then the refrigerant (20) enters the suction of the compressor (1), and the cycle resumes.  (ii) In cooling mode: the refrigerant (20) passes firstly through the low temperature block (4) used as exchanger of the second source, then by the exchanger of the first source, then by the expander (5). ), then by the exchanger of the second charge, then by the medium-temperature block (3) used as exchanger of the first charge, then by the four-way reversing valve 2906603 34 (6), in a different circuit, then the refrigerant (20) enters the suction of the compressor (1), and the cycle resumes.  An example of this embodiment of the invention is shown in FIG. 14: the system is provided with a reversible module according to the invention not equipped with non-return valves, with an air / refrigerant exchanger (extracted air or outside air) 7 and a solar thermal panel 10 as heat sources, as well as one or more exchangers heating or cooling the space.  The space heating or cooling exchanger (s) are water exchangers (15, 17) connected directly to the medium temperature storage and exchange unit (3).  In addition, a refrigerant / space-type space heating or cooling exchanger 16 is added to the system.  Only the high temperature exchange and storage block 2 heats the domestic hot water.  When the system is used simultaneously to heat space and sanitary water, the operation is similar to that of the embodiment shown in FIG. 13. Similarly, when the system is used solely for heating the sanitary water, the The operation is similar to that of the embodiment shown in FIG. 13. When the system is used simultaneously to cool the space and heat the sanitary water, the specified system as shown in FIG. 14 is to allow simultaneous cooling. by air and by water cooling (eg underfloor cooling).  The air cooling allows a rapid temperature drop and dehumidification of the room and the cooling of the ground gives the thermal inertia; Dehumidification of the air limits the risk of condensation on the floor.  The system easily enables this feature through its multiple connections.  The heat will be rejected at the exchanger 7 whose flow must be sufficient.  When the system is used simultaneously to cool the space and heat the sanitary water, the high temperature exchange and storage block 2 is always supplied with heat and thus allows the heating of domestic hot water.  The medium temperature exchange and storage block 3 is in solid form.  The preferred configuration from the point of view of heat transfer is that of the plate heat exchanger shown in FIG. 23.  Indeed, this configuration allows a direct exchange between the refrigerant and the water exchangers 15.  The low temperature exchange and storage block 4 is supplied with hot gas.  It does not reject summer heat because it is connected to a solar collector itself at high temperature.  The solar collector pump is therefore not powered. The solar collector pump will generally not be powered.  In fact, the cooling mode appears in summer when the temperature of the solar collector is high and higher than the condensing temperature of the system.  There would be no heat rejection but more likely a transfer to the geothermal sensor.  This mode is possible in some cases to recharge the geothermal sensor or to cool the circuit of the solar collector but it is not essential.  The heat will be rejected at the level of the exchanger 7 whose flow must be sufficient.  Another embodiment of the invention is shown in FIG.  In the embodiment shown in FIG. 15, the system is provided with a reversible module according to the invention not equipped with nonreturn valves, with a first source constituted by a geothermal water or brine loop 14 which transmits or takes its heat to a water / refrigerant exchanger 12, a second source constituted by a solar thermal panel 10, and exchangers heating or cooling the space.  The space heating or cooling exchanger (s) are water exchangers (15, 17) directly connected to the heat exchanger / medium temperature storage block (3).  In addition, a refrigerant / space-type space heating or cooling exchanger 16 is added to the system.  Only the high temperature exchange and storage unit heats the domestic hot water.  The system is similar in operation to that of Figure 14.  The heat rejection will be done by the geothermal loop with water or brine 14.  Another embodiment of the invention is shown in FIG.  In the embodiment shown in FIG. 16, the system is provided with a reversible module according to the invention not equipped with non-return valves, with a first source consisting of an air / refrigerant exchanger (extracted air or outside air) 7, a second source consisting of a solar thermal panel 10, and 2906603 36 heat exchangers heating or cooling space.  The space heating or cooling exchanger (s) are water exchangers (15, 17) directly connected to the heat exchanger / medium temperature storage block (3).  In addition, there is added to the system a refrigerant / air space heating or cooling exchanger 5 16.  In addition, in this embodiment, a medium temperature exchange and storage block is added in the circuit of the solar thermal panel 10.  When the circulation pump is activated, the heat will be stored in two exchange and storage blocks: on the one hand, the low temperature block 4 to ensure the superheating of the suction gases of the compressor and to create energy stored in case of compressor demand and secondly, in the medium temperature supplementary block 3 ".  In the discharge phase, the sanitary water will first pass through this medium temperature block and then into the high temperature block charged by the thermodynamic cycle.  Yet another embodiment of the invention, of the non-reversible type, is represented in FIG. 13.  In the embodiment shown in FIG. 13, the system is provided with a non-reversible module, an air / refrigerant exchanger (extracted air or outside air) 7 and a solar thermal panel 10 as sources. of heat, as well as heat exchangers exchanging space.  The heat exchanger or heat exchangers are on the one hand water exchangers 15, 17 connected directly to the exchange and storage unit at medium temperature 3, and on the other hand a refrigerant / refrigerant type heat exchanger. air 16.  Only the high temperature exchange and storage block 2 is used to heat the domestic hot water 25.  When the system is used simultaneously to heat space and sanitary water, the extracted air is typically already 20 C, solar thermal panel 10 will tend to quickly liquefy the low temperature block and overheat the gas.  The regulation manages overheating at the compressor and its suction pressure.  The solar panel provides additional power that is conveyed by the compressor to the high pressure portion of the circuit with high efficiency.  When the system is only used to heat the sanitary water, there is overabundance of available power from both sources.  The regulation manages the power distribution thanks to the expander and to the actuators (pumps or fans). The specified system of the embodiment of FIG. 13 is to allow heating of the space simultaneously by air and by heaters. water (underfloor heating for example), the air allowing a rapid warming of the room and the ground giving the thermal inertia and the radiating effect.  The system according to the invention easily allows this functionality.  On the other hand, the disadvantage of the system of the embodiment of FIG. 13 is a loss of efficiency for the heating of the sanitary water since only the exchange and storage block 2 is used for heating the water. health.  Figure 13 (2 sources, ECS + 2 heat exchangers in non-reversible mode is not covered by claims 2 or 3!) Figures 4 to 16 do not comprehensively address all configurations.  They aim to show the flexibility of the module for various installations.  FIG. 17 represents a block diagram representing the exchange and storage blocks according to the technological approach of plate heat exchangers.  This exchanger 20 allows a direct exchange respectively between refrigerant and storage material, refrigerant and secondary fluid which increases the thermal power exchanged but it is however necessary to add a second plate between the refrigerant and hot water so as to obtain a double wall.  A plate heat exchanger is already used in this way with 2 refrigerant circuits and a circuit

  water. But the use with storage material is particular to this invention and therefore part of it. Note that the spacing of the plates will be greater for the storage material (see Figure 23) to allow sufficient thermal storage.

FIG. 18 represents a schematic diagram representing the exchange and storage blocks according to the technological approach of the copper tubular exchangers.

This approach is more conventional than that of plate heat exchangers, but it does not allow permanent contact two by two of the three fluids in the presence. The transition material is inserted between the two other fluids. The double-wall effect between the refrigerant and domestic hot water is respected. FIG. 19 represents one of the following ways of organizing the components of the system FIG. 20 equipped with the components of FIG. 24. f) Application example: Individual house 10 (i) Evolution of the thermal requirements: The proportion of the Domestic hot water increases in energy consumption, in fact: The insulation of buildings and individual houses improves, which decreases the amount of energy needed to heat the space. On the other hand, the heating needs of domestic hot water remain the same. For example, a detached house before 1980 requires a total heating energy of about 200 kWh / m2 / year, of which about 20 kWh / m2 / year, about 10% is used for hot water.

20 A house under 10 years old will require about 100Kwh / m2 / year. The share of domestic hot water (20 KWH / M2 / year) represents 20% The trend is towards very isolated houses that require about 65Kwh / M2 / year and less. The share of domestic hot water is 30% The efficiency of the hot water heating mode thus becomes an increasingly important point. (ii) Response to needs with the module described in the invention We will take the latter case and apply it to a house of 140 m2. Total heating requirements are therefore 65x140 = 9100KwhH including 2800Kwh 30 for hot water. Assuming the probable assumption of daily hot water demand throughout the year, a need of 2800/365 = 7.7Kwh / day = 27720 KJ / day This energy is used to heat 265 liters of water per day from 15 deg C to 40 deg C If a paraffin-type storage material is considered, an average latent heat value of 250 KJ / Kg and a density of 800 Kg / m 3 can be taken. . It will generally heat 27720/250 = 110 kg of material per day to ensure the needs. If we consider the realistic case of two cycles of melting and solidification of the material per day, we obtain the need for a mass of 55 kg of storage material. This quantity of matter applies to the sum of the masses of the high and medium temperature blocks. This represents a volume of 55/800 * 1000 = 69 cubic decimetre of material. Given the volume required for the water and refrigerant circuits, the total volume of the two exchanger blocks can be estimated at 100 cubic decimetres. We can divide the volumes between the two high and medium temperature blocks if we fix certain hypotheses. The distribution below is given as an example, it may vary depending on the assumptions made.

The assumptions made for this example are as follows: The system under consideration comprises two sources: on the one hand, a brine geothermal loop, and on the other hand a solar panel. The system under consideration comprises the charge of the domestic hot water circuit and may optionally include another load constituted by a hot water heating circuit (the case of FIG. 9). The refrigerant chosen is: 410A. % domestic hot water (no space heating load) Blocks are charged according to the operating condition below: Condensing temperature is 40 C, considered equal to the phase change temperature of the medium temperature block .

2906603 The evaporation temperature is -5 C (usual case of a geothermal loop) The enthalpy of the refrigerant at -5 C is: 421 KJ / Kg The temperature at the suction of the compressor is 20 C, considered equal to the phase change temperature of the low temperature block (the temperature at the suction of the compressor may be higher if necessary by keeping the solar collector circuit switched on). The enthalpy of the refrigerant at 20 ° C. is 446 KJ / Kg The change in enthalpy of the fluid in the low temperature block is therefore equal to 446-421 = 25 KJ / Kg. The discharge temperature of the compressor is 95.degree. C. The enthalpy of the refrigerant at the discharge of the compressor = 500KJ / KgL 'The phase change temperature of the high temperature block is 70 C The enthalpy of the refrigerant at 70 deg C is 470 KJ / Kg The change in enthalpy of the fluid in the high temperature block is therefore equal to: 15 500-470 = 30 KJ / Kg The enthalpy change of the fluid during the condensation in the medium temperature block at 40 deg C is equal to 160 KJ / Kg. The ratio of the enthalpy variations 30/160 gives about 20% for the medium temperature block.

20 So we get about 20 liters for the high temperature block and 80 liters for the medium temperature block. In practice, it will oversize the high temperature block for example up to 40 liters to be able to benefit from certain favorable operating conditions at the solar collector and thus be able to store more energy at high temperature.

Applied to the low and high temperature blocks, the ratio of enthalpies gives 25/30 = 0.67 hence a volume for the low temperature block of 0.67 * 0.2 = 14 liters. In practice it will also oversize this block, for example up to 30 liters, so as to keep a storage reserve usable by the compressor. The following mean domestic water temperatures are assumed: mains water at 30 15 C and hot water outlet at 40 C, an average differential of 25 C 2906603 41 Circulation of domestic hot water in the medium and medium heat exchanger blocks High temperature will be made so that 80% of the temperature difference (15 C to 35 deg C) is made in the medium temperature block and 20% (35 C to 40 C) is made in the high temperature block.

We thus obtain an amount of about 30 + 80 + 40 = 150 liters for all the exchanger blocks. For comparison, the standard dimensions of a dishwasher are 600 mmx600mmx850mm generating a volume of 300 liters. It seems conceivable to make the system chosen for the example in a volume close to a dishwasher. 10

Claims (10)

  1) Module usable for storage and heat transfer, comprising the following components: (a) a compressor (1) refrigerant; (b) a heat exchange and storage block said high temperature block (2) located at the suction of the compressor (1); (c) a heat exchange and storage block said medium temperature block (3); (d) another heat exchanger, or preferably a heat exchange and storage block said low temperature block (4); (e) a four-way valve (6) located at the outlet of the high temperature module (2), this valve being mandatory if said module is intended to operate in reversible mode; (f) optionally two check valves (26, 36); (g) optionally an injection valve (19) said valve (19) injecting upstream of the compressor (1); (h) an expansion valve (5).   2) System incorporating a module according to claim 1, said system operating in non-reversible mode, and characterized in that said components are arranged so that the refrigerant (20) leaves the discharge of the compressor (1) passing from firstly by the high temperature block (2) and then by the medium temperature block (3), then (a) for use in a system with a heat source and a heat load, preferably domestic hot water, said fluid refrigerant (20) passes through the low temperature block (4), through the expander (5), through a heat source heat exchanger, then through a circuit different from that of the first passage, again by the low temperature block (4) then said refrigerant (20) enters the suction of the compressor (1), and the cycle resumes; (b) for use in a system with a heat source and a first heat load, this first heat load being preferentially hot water, and a second heat load, said refrigerant (20) passes through the exchanger of the second heat load, then passes through the low temperature block (4), by the expander (5), by a heat source heat exchanger, then, by a circuit different from that of the first pass, again by the block low temperature (4), then said refrigerant (20) enters the suction of the compressor (1), and the cycle resumes; (c) for use in a system with two heat sources and two heat loads, one of said heat loads being preferentially hot water, said refrigerant (20) passes through a first heat exchanger on the heat load, then by the expander (5), then by an exchanger of a first source of heat, then by the low temperature block (4) used as exchanger of a second heat source, then the refrigerant (20) enters the suction of the compressor (1), and the cycle resumes.   3) System incorporating a module according to claim 1, said system operating in reversible mode, and characterized in that said components are arranged so that the refrigerant (20) leaves the discharge of the compressor (1) passing from firstly by the high temperature block (2) and then by the four-way reversing valve (6), then (a) for use with two heat sources and two heat loads, the first heat load of which is preferentially the sanitary hot water, this first heat load being connected by an independent circuit in series to the high temperature and medium temperature blocks, the second heat load can be used either in heating mode, or in cooling mode, (i) in heating mode : said refrigerant first passes through a first check valve (26), then by the medium temperature block (3), then by the exchanger of the second load thermal, then by the expander (5), then by the heat exchanger of the first heat source, then by the low temperature block (4) used as exchanger of the second heat source, then again by the four-way valve the cycle reversal (6) in a different circuit, then the refrigerant (20) enters the suction of the compressor (1), and the cycle resumes; (ii) in cooling mode: said refrigerant (20) passes through the low temperature block (4) used as exchanger of the second source, then by the exchanger of the first source, then by the expander (5), then by the exchanger of the second heat load, then by a second non-return valve (36), and then by the four-way reversing valve (6), in a different circuit, and then the refrigerant (20) enters in the suction of the compressor (1), and the cycle resumes; (B) for use with two heat sources and three heat loads, the third heat load of which is preferably sanitary water (of more limited capacity compared with case (a)), this third heat load being connected by a independent circuit at the high temperature block (2), in heating mode: the refrigerant (20) passes firstly through the medium temperature block (3) used as exchanger of the first heat load, then by the exchanger of the second charge thermal, then the expander (5), then by the changer of the first source of heat, then by the low temperature block (4) used as heat exchanger of the second heat source, then by the four-way valve with reversal of cycle (6), in a different circuit, then the refrigerant (20) enters the suction of the compressor (1), and the cycle resumes; (ii) in cooling mode: the refrigerant (20) passes firstly through the low temperature block (4) used as exchanger of the second source, then by the exchanger of the first source, then by the expander (5); ), then by the exchanger of the second charge, then by the medium temperature block (3) used as exchanger of the first charge, then by the four-way valve with cycle reversal (6), in a different circuit, then the refrigerant fluid (20) enters the suction of the compressor (1), and the cycle resumes. 20 2906603 45   4) System according to claim 3, corresponding to the operating diagram shown in Figure 16   5) A module or system according to claim 1 to 4, wherein said high temperature block (2) comprises a phase change material whose phase change temperature is set to a value between 60 C and 75 C and advantageously 65 and 70 C, or at a temperature between 75 C and 90 C and preferably 80 to 85 C if the refrigerant (20) is CO2. 10   6) Module or system according to any one of claims 1 to 5, wherein said medium temperature block (3) comprises a phase change material whose phase change temperature is set to a value between 32 C and 45 C, and advantageously between 35 C and 40 C.   7) Module or system according to any one of claims 1 to 6, wherein said low temperature block (4) comprises a phase change material whose phase change temperature is set to a value between 15 C and 25 C, and advantageously between 17 C and 22 C.   8) Use of a module or system according to any one of claims 1 to 7 for cooling or heating railway cars, ships or trucks. 25   9) Use of the module or system according to any one of claims 1 to 7 for heating sanitary water of a building or part of a building.   The use according to claim 9, wherein said module or system is further used for heating air and / or for cooling said building or said building part. 15 20