Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B13/00—Compression machines, plants or systems, with reversible cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B30/00—Heat pumps
  • F25B30/02—Heat pumps of the compression type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B40/00—Subcoolers, desuperheaters or superheaters
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
  • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B6/00—Compression machines, plants or systems, with several condenser circuits
  • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
• • 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
  • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
  • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
  • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
  • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—Component parts or details not otherwise provided for in this subclass
  • F25B2400/04—Refrigeration circuit bypassing means
  • F25B2400/0409—Refrigeration circuit bypassing means for evaporators
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—Component parts or details not otherwise provided for in this subclass
  • F25B2400/04—Refrigeration circuit bypassing means
  • F25B2400/0411—Refrigeration circuit bypassing means for expansion valves or capillary tubes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—Component parts or details not otherwise provided for in this subclass
  • F25B2400/24—Thermal storage element
• • 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
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
  • Y02E60/14—Thermal energy storage

Definitions

• the invention relates to a thermodynamic device of the heat pump or air conditioning system type.
• 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.
• a conventional thermodynamic device compressor, expander, regulation
• 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.
• the consumption of heating, air conditioning and domestic hot water typically represents about 30% of the energy consumption of an industrialized country.
• Thermodynamic systems offer an alternative to conventional systems using electrical resistors or the combustion of fossil fuels to heat domestic water or space.
• Hydro Fluoro Carbon HFC
• 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 (CO 2 ) is a promising refrigerant, especially for heating domestic hot water and for heating and cooling vehicles.
• 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 the need for heating or cooling. 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 EP 1 572 479 DAIMLER CHRYSLER describes a system using a heat accumulator comprising a heat storage material as a cold reserve in a car 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 EP 1 632 734 of MATSUSHITA ELECTRIC presents 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 having several reservoirs for storing 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).
• 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 described in this patent includes a container defining an inner 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 a higher thermal conductivity.
• 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 chosen from paraffins, alcohols, gas hydrates, water, aqueous solutions of salts, hydrated salts, eutectic mixtures of salts, 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.
• a similar material is described in patent application WO 98/04644 (ZAB discussion Bay, Zentrum fur Angewandte Energytechnik). It allows the manufacture of heat or cold storage blocks with a phase change temperature between -25 ° C and +150 0 C.
• 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.
• the Module Usable for Storage and Thermal Transfer (MUSTT) which represents a first object of the present invention, is a hybrid module comprising the following components:
• the MUSTT module may further include, if necessary or useful: - Regulating and electrical power components to supply the various elements of the thermodynamic system reliably and optimally energy;
• 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 in such a way as to that the refrigerant 20 leaves the discharge of the compressor 1 by passing first through the high temperature block 2 and then through the medium temperature block 3, then
• said refrigerant 20 passes through the low temperature block 4, the expander 5, a heat exchanger (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;
• a heat exchanger such as an exchanger on the extracted air or a geothermal loop
• 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
• the first heat 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 thermal load (such as underfloor heating, radiator, fresh air heat exchanger, fan coil) that can be used either in heating mode or in cooling mode, (i) in heating mode: refrigerant passes firstly through a first check valve 26, then by the medium temperature block 3, then by the exchanger of the second heat load, then by the expander 5, then by the exchanger of the first source of heat, then by the low temperature block 4 used as exchanger of the second heat source, then again by the four-way valve of cycle 6 inversion, in a different circuit, then the refrigerant 20 enters the suction of the compressor 1, and the cycle resumes;
• the second thermal load such as underfloor heating, radiator, fresh air heat exchanger, fan coil
• the third thermal load being preferentially the sanitary water (of capacity more limited compared to the case (a)), this third thermal load being connected by an independent circuit to the high temperature block 2, the first thermal loads being preferably a floor heating, a radiator, a fresh air heating exchanger , a fan coil, (i) in heating mode: the refrigerant 20 passes first through 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 heat exchanger of the first heat source, then by the low temperature block 4 used as exchanger of the second heat source, 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;
• 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 the second charge, then by the medium temperature block 3 used as exchanger of the first charge, then by the four-way valve to cycle reversal 6, in a different circuit, then the refrigerant 20 enters the suction of the compressor 1 , and the cycle resumes.
• FIGS 1 to 27 refer to the invention of which they illustrate the principle or specific embodiments.
• the figures show the operation in heating mode of the module according to the invention and systems comprising said module.
• Figure 1 describes the MUSTT module according to the invention in a non-reversible version.
• Figure 2 describes the MUSTT module in a reversible version with non-return valves that can be used for space heating and cooling.
• FIG. 3 represents the reversible module according to the invention not equipped with 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 18 and 26, 27 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 domestic hot water from an air exchanger (extract or outside) / refrigerant 7.
• Figure 5 describes a system provided with a non-reversible module used to heat 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.
• FIG. 6 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 / fluid exchanger refrigerant 12.
• 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 / fluid exchanger refrigerant 12 and a second source consisting of an exchanger air / 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 describes 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.
• 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 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 / fluid exchanger refrigerant 12 and 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, 17.
• FIG. 10 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. which transmits its heat to a water / refrigerant heat exchanger 12 and a solar thermal panel 10.
• the heat exchanger or heat exchanger space or are water exchangers 15, 17, connected to a refrigerant / water intermediate exchanger or brine 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 (Extracted air or outside air) and a solar thermal panel 10.
• the exchanger or heat exchanger or space cooling are exchangers refrigerant / air type 16.
• FIG. 12 describes a system provided with a reversible module provided with non-return valves 26, 36 on the block 3 used for heating domestic hot water and for heating / cooling a space from a geothermal water or brine loop. which transmits its heat to a water / refrigerant exchanger 12 and an air / refrigerant exchanger 7 (extract air or outside air)
• the space heating or cooling exchanger (s) are water exchangers (15, 17) connected to an intermediate exchanger refrigerant / water or brine 11.
• FIG. 13 describes a system provided with a non-reversible module used to heat domestic hot water and a space from an air / refrigerant exchanger 7 (extracted air or outside air) and a solar thermal panel.
• the space-heating exchanger or exchangers are water exchangers 15, 17, such as water radiators, connected directly to the medium-temperature exchange and storage block 3.
• FIG. 14 describes 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 (exhaust air or outside air) and a solar panel 10.
• the space heating or cooling exchanger (s) are water exchangers (15, 17) directly connected to the medium temperature exchange and storage unit (3). Only the high temperature exchange and storage unit heats the heat exchanger. sanitary water.
• 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 water / refrigerant exchanger 12 and a second source constituted by a solar thermal panel 10.
• the heat exchanger or heat exchanger or space cooling are water exchangers 15, 17 connected directly to the exchange and storage block to average temperature 3. Only the high temperature exchange and storage block 2 heats the domestic hot water.
• a refrigerant / space-type space heating or cooling exchanger 16 is added to the system.
• FIG. 16 describes a system provided with a reversible module not equipped with non-return valves, 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 solar thermal panel 10.
• the heat exchanger or heat exchanger space are water exchangers 15, 17 connected directly to the exchange unit and storage medium temperature 3.
• a heat exchanger or cooling refrigerant / air space space 16 is added to the system.
• an exchange and storage block 300 is added to the circuit of the solar thermal panel 10. The domestic hot water passes in series first by this exchange and additional storage block, then by the block of high temperature exchange and storage 2.
• FIG. 17 is similar to FIG. 10, except that each exchange and storage block 2, 3, 4 is replaced by a set of exchange and storage sub-blocks, respectively 210, 220 for block 2, 310, 320, 330, 340 for block 3 and 410, 420, 430 for block 4.
• FIG. 18 depicts a system provided with a reversible module provided with non-return valves 26, 36 on the block 3 used for heating domestic hot water and for heating / cooling a space from a geothermal water or brine loop. which transmits its heat to a water / refrigerant exchanger 12, an air / refrigerant exchanger 7 in series with the loop 14 and a solar thermal panel 10.
• the heat exchanger or exchangers or space cooling are water exchangers 15, 17, connected to a refrigerant / water or brine 11 intermediate heat exchanger.
• FIG. 19 represents a block diagram representing the exchange and storage blocks according to the technological approach of plate heat exchangers.
• Figure 19a is a top view
• Figure 19b is a side view.
• FIG. 20 represents a block 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. 21 shows a way of organizing the components in one of the systems according to the invention.
• Fig. 22 shows a way of organizing the components in one of the systems according to the invention.
• FIG. 23 shows a way of organizing the components in one of the systems according to the invention.
• FIG. 24 represents a block diagram representing the exchange and storage blocks according to the technological approach of plate heat exchangers.
• Figure 24a is a view from above
• Figure 24b is a side view.
• FIG. 25 represents a schematic diagram representing the exchange and storage blocks provided with three fluid circuits and an electrical heating resistor.
• Figure 26 describes a system with a non-reversible module and three sources and three thermal loads, used to heat domestic hot water, heat a space and heat a pool or spa, from a water geothermal loop or brine 14 which transmits its heat to a water / refrigerant exchanger 12, an air / refrigerant exchanger 7 in series with the loop 14 and a solar thermal panel 10.
• an exchange block and very low temperature storage 50 with two circuits is placed upstream of the non-reversible module, before the exchange block and low temperature storage.
• Figure 27 describes a system with a non-reversible module and 4 sources and 3 heat loads used to heat domestic hot water, heat or cool a space, and heat a pool or spa from a geothermal loop water or brine 14 which transmits its heat to a water / refrigerant exchanger 12, an air / refrigerant exchanger 7 in series with the loop 14 and a solar thermal panel 10.
• a block exchange and storage very low temperature 50 to three circuits is placed upstream of the non-reversible module.
• a hydraulic three-way valve 34 is placed on the space heating circuit and connected to the very low temperature block 50.
• Air / refrigerant type exchanger typically extract air or outside air
• Thermodynamic system assembly comprising a compressor and several exchangers in which circulates a specific transfer fluid usually called refrigerant.
• - Geothermal loop set of pipes placed in the ground typically in vertical or horizontal position and intended to exchange the heat between the heating or cooling system and the ground.
• Transfer fluid fluid used to transfer heat; conventional examples are refrigerant, water or brine sometimes called brine.
• Thermal source or source by convention, the terms source and heat load refer to the 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 actually rejects heat from the building.
• Thermal load or load The load is the medium where the heat is rejected in heating mode. This heat rejection is achieved with certain physical characteristics such as the thermal inertia or the available power that characterize the load, so the load is the place where the heat is removed in cooling mode.
• Secondary fluid fluid flowing in one of the circuits of an exchange and storage block that is not traversed by the refrigerant.
• gas cooler or gas cooler.
• the term gas cooler is often used in cycles using CO 2 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 liquid refrigerant in order to increase the performance of the refrigeration cycle.
• hybrid module as well as the systems that incorporate it according to the invention bring together, on the one hand, the conventional components of thermodynamic systems and, on the other hand, storage and heat exchange elements using a material capable of storing heat.
• hybrid is related to this dual function of exchange and storage of heat.
• the hybrid module is the main basis of multiple systems adaptable to many facilities for heating sanitary water and / or heating and / or cooling a space.
• the module according to the invention 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 a plurality of blocks 2, 3, 4, 50 d. exchange and storage of heat.
• 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 / porous-graphite composite matrix as a high and constant power thermal storage material "by Xavier Py, Régis Olives and Sylvain Mauran (International Journal of Heat and Mass Transfer 44 (2001) 2727-2737).
• Other storage materials such as new or known phase-change materials, such as fatty acids or melted 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 invention.
• Storage materials with change of phase are well adapted to the invention presented. Any other constant or near constant temperature storage material, present or future, could be employed in the storage exchanger blocks described in 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 (CO 2 ), or with any other suitable refrigerant.
• the compressor is volumetric, pallet type or spiro-orbital type for HFCs and hydrocarbons. Piston models can also be used for CO 2 or other suitable performance compressors.
• 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 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, in particular in the case where the second source is a solar thermal collector 10.
• the compressor 1 is supplied with direct current of photovoltaic origin in order to maximize the energy efficiency of the module.
• 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 "inverter" type)
• Each heat exchange and storage block consists of a storage part and an exchanger part.
• the storage of heat uses materials with high thermal conductivity.
• an expanded natural paraffin / graphite composite material is advantageously used.
• the phase change temperature of the material is adapted to the needs.
• at least one of the heat exchange and storage blocks 2, 3, 4 is composed of several sub-blocks, respectively 210, 220, 230 for block 2.
• each of the sub-blocks being characterized by its own phase change temperature, said phase change temperatures being chosen so as to for each block 2, 3, 4, the phase change temperatures of the successive sub-blocks increase or decrease in the direction of the refrigerant flow 20 according to the intended use of said module, and decrease in the blocks 2 and 3 and grow in block 4 in the case where said module is used in heating mode.
• the thermal conductivity of pure paraffin is 0.24 W / M / K.
• the thermal conductivity of the expanded natural graphite / paraffin composite material can reach values between 4 and 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 part allows the transfer of heat on the one hand between the refrigerant and the storage material and on the other hand 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.
• the 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.
• the high-temperature exchange and storage block can be a single block or can be divided into several independent sub-blocks 210, 220, 230, for example in the form of plates, as in FIG. 20.
• each sub-blocks comprise materials having different phase change temperatures to create a temperature gradient.
• the temperature.de phase change of each of the blocks and sub-blocks of exchange and storage at high temperature is set to a value advantageously between 60 and 75 ° C and preferably 65 to 70 0 C for HFC fluids and hydrocarbons. This value is between 75 and 90 ° C. and preferably 80 to 85 ° C. for the CO 2 taking into account the operating conditions of this fluid.
• the secondary exchange fluid is domestic hot 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 blocks and sub-blocks 2, 200, 210, 220, 230 are used as storage of the sensible heat of the refrigerant, thus as a gas cooler or desuperheater, as well in the case where the refrigerant is an HFC or a hydrocarbon only in the case where the refrigerant is CO 2 .
• the sanitary water as it circulates, recovers the sensible and latent heat stored by the phase change material, and thus it heats up.
• the high temperature blocks or sub-blocks are located before the cycle reversal valve. Therefore, their mode of operation remains the same in heating mode and in cooling mode.
• the medium-temperature exchange and storage block may be a single block or be divided into several independent sub-blocks 310, 320, 330, for example in the form of plates as in FIG. 20.
• each sub-blocks comprise materials having different phase change temperatures to create a temperature gradient.
• the phase change temperature of each of the medium temperature storage and exchange blocks and sub-blocks 3, 300, 310, 320, 330, 340 is set to a value between 32 and 45 °. C and preferably between 35 to 40 0 C for HFC fluids, hydrocarbons and for CO 2 .
• the secondary fluid is domestic water 25 (example Figure 10) or water heating circuit 24 (Figure 11).
• These blocks and sub-blocks are mainly used 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 CO 2 (second gas cooler).
• the recovered heat is first stored in latent form by the material at its specific phase change temperature.
• the material is liquid, a sensitive additional storage intervenes by raising the temperature of the liquid material.
• cooling mode the refrigeration cycle is reversed.
• the system is equipped with non-return valves, because of these valves the blocks or sub-blocks average temperature do not "see" refrigerant, so the stored heat remains stored, and can be used for heating the sanitary water.
• the blocks or sub-blocks cool down until the storage material is solid and then their temperature drops to reach the operating condition of the system.
• a second block or set of medium temperature exchange and storage sub-blocks may be used in some systems having a solar collector as a source of heat.
• the use of this second block or set of sub-blocks will increase the power available for heating the sanitary water.
• the medium-temperature blocks are provided with an additional electrical resistance to enable a heating cycle to be carried out with a final temperature of the domestic hot water greater than 60 ° C. sufficient to ensure a thermal shock capable of killing any legionella.
• the cycle can be done once a week, or once a day if necessary. It is programmable, and ensured by the regulation of the system.
• the power of the electrical resistance is of the order of 1 to 3 kW; preferably 2 kW for a heat pump with a power of 10 kW.
• the low-temperature exchange and storage block may be a single block or be divided into several independent sub-blocks 410, 420, 430, for example in the form of plates as in FIG. 20.
• each sub-blocks comprise materials having different phase change temperatures to create a temperature gradient.
• the phase change temperature of the material of each of the low temperature blocks and sub-blocks is set to a value between 15 and 25 ° C and preferably 17 and 22 0 C regardless of the refrigerant.
• 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 (according to the systems of FIGS. 9 to 22)
• the low temperature block has two main functions.
• the low temperature block can serve as a heat source used separately or in conjunction with another source.
• the machine control controls the pressure and temperature parameters 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.
• the recovered heat is first stored in latent form by the material at its specific phase change temperature.
• the material is liquid and the second source is sufficiently hot, a sensitive additional storage occurs by raising the temperature of the liquid material (case of Figure 8 equipped with a solar collector) up to the maximum value accepted by the regulation .
• the low-temperature exchange and storage block may be a single block or be divided into several independent sub-blocks 510, 520, 530, 540, for example in the form of plates as in FIG. 20.
• each of the sub-blocks comprises materials having different phase change temperatures to create a temperature gradient.
• the phase change value of the material of each of the low temperature blocks is set to a value between 5 and 15 ° C and preferably 7 and 12 0 C regardless of the refrigerant.
• the low-pressure circuit of the refrigerant must be sufficiently sized to limit the losses.
• the set of very low temperature blocks has two main functions:
• the very low temperature block stores a quantity of heat that can be used punctually by the compressor to meet the hot water needs. 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. It is thus possible to assemble a slightly more powerful compressor on a lower power source to allow a higher instantaneous power.
• the very low temperature block can be used to cool the space using a non-reversible module.
• the 3-circuit very low temperature exchanger can be connected by a hydraulic circuit (water) and a three-way valve to the heating / cooling circuit of the space. This allows a transfer of heat directly from the space to the very low temperature block.
• heating mode the heat thus recovered at the source is first stored in latent form by liquefaction by the material at its specific phase change temperature.
• cooling mode and exclusively for a non-reversible system, the block will be cooled by the compressor if there is a heat demand for hot water and / or a spa or pool. The block will cool until the phase change material is solid. It will also continue to cool in sensible. This cooling can also be provided by a sufficiently cold source.
• This regulator is typically constituted by a valve whose opening and closing are controlled by a stepper motor. It regulates the flow of refrigerant in the circuit according to the command sent by the regulation.
• This valve makes it possible to reverse the direction of the refrigerant in the circuit and thus ensure heating and cooling operation as required.
• the air used by this exchanger is typically extracted air (by the controlled mechanical ventilation of the apartment or the living space on which the system is installed) or outside air.
• This exchanger is a source of heat in heating mode. It can also reject heat in cold mode.
• Water Pump and Expansion Tank 9 This pump circulates water or brine (typically ethylene or propylene glycol) between system heat exchangers.
• water or brine typically ethylene or propylene glycol
• the water pump may be on the heating water circuit and / or on the heat source circuit when this source is a geothermal loop.
• Solar thermal panel 10 This panel captures solar energy and transmits it to the fluid (such as propylene glycol) from its own circuit.
• the solar thermal panel powers the low temperature exchange and storage block
• the low temperature block during the duration of its liquefaction tends to stabilize a certain time the return temperature of the fluid to the solar panel at a low level, which increases its efficiency.
• This exchanger makes it possible to transfer the heat between the refrigerant and the heating water of a space and consequently allows the use of different types of water exchangers described in 15 and 17.
• 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).
• This loop transfers energy between the soil and the brine.
• the current devices that can be used in the context of the present invention are fan coils, water-air exchangers for heating or cooling the fresh air and floor heating - refreshing water circulation.
• the current devices that can be used in the context of the present invention are wall units, consoles and refrigerant batteries for air new.
• HFC fluids e.g., 134A, 407C, 404A & 410A
• hydrocarbons e.g., propane
• propane e.g., propane
• CO 2 e.g., CO 2 or any other suitable fluid.
• the module according to the invention adapts to all types of fluids.
• the high operating pressures of systems using CO 2 require specific sizing according to principles known to those skilled in the art.
• the pressure is given by the water supply network.
• 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 and the medium temperature exchange and storage block. . 21 - Domestic hot water mixing valve 23:
• This optional valve makes it possible to avoid burns of the user of domestic hot water by maintaining a water outlet temperature of approximately 50 ° C before use by mixing a water at approximately 10-20 ° C. the water supply network and a water at 60-70 0 C from the high temperature exchange and storage block. It is indeed necessary to heat (store) domestic hot water at a temperature of 60 ° C and if possible to 7O 0 C for storage at temperatures between 25 and 60 0 C promotes the development of colonies of legionella.
• the two check valves used together allow the passage of refrigerant through the medium temperature block in heating mode and allow a direct passage of the refrigerant in cooling mode.
• thermodynamic system such as a heat pump
• the heating of the water can be done by means of a gas cooler still called desuperheater.
• a gas cooler still called 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 sensitive 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 temperature at the suction of the compressor and therefore its discharge temperature.
• 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.
• a vapor-liquid exchanger 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 effectiveness of this conventional liquid vapor 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.
• the power recovered at high temperature will be greater, which will be favorable for heating 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.
• said source is a solar thermal collector.
• the exchange is done 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.
• 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 intense drawing 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 variation of speed. 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 to have 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 hot water circulation.
• 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.
• the sanitary water heating can be done also by the use of the condensing power of the thermodynamic cycle.
• a valve called “three-way valve” derives 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 reaching values of the order of 2 to 2.5. It can be estimated that the average COP during the period of heating and keeping water temperature Domestic hot water is about 3.
• 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 thermal load
• 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 exchanger (such as a heat exchanger on the extracted air or a geothermal loop), then by a different circuit of 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 heat source exchanger such as a heat exchanger on the extracted air or a geothermal loop
• 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.
• 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 depends on weather conditions and is typically between 2 and 10 kW for residential applications, but could reach higher values for other uses.
• load the compressor 1 operates and charges the exchange blocks and storage high temperature 2 and medium temperature 3.
• the load is at a high performance coefficient 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.
• the low temperature exchange and storage block 4 is used as an internal exchanger.
• 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 geothermal loops with refrigerant 13 or water 14 are usually more powerful and more stable than air / refrigerant exchangers, but are not usable on all homes / buildings.
• 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 extract 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 heat source exchanger such as a heat exchanger on the extract air or a geothermal loop
• FIG. 5 This embodiment of the invention is shown in FIG. 5.
• the system is similar to that of the first embodiment of FIG. 4 and is provided with the module according to the invention which is not reversible and with an air exchanger (extract or external) / refrigerant 7.
• the device of this embodiment further 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 can be for example underfloor heating, a radiator, a fresh air exchanger, a convector fan.
• 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.
• the heat energy may for example mainly be intended for heating the hot water health. In this case, the capacity of the heat exchanger will be limited for example by stopping the exchange fan or reducing its speed.
• the low temperature exchange and storage block 4 is used as an internal exchanger.
• air exchanger extract or external
• refrigerant 7 may be replaced by another source of heat if necessary, for example by a geothermal loop 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.
• FIG. 6 Another embodiment of this type is shown in FIG. 6.
• the device of the embodiment according to the invention of FIG. 6 is provided with a non-reversible module according to the invention, with a set consisting of a intermediate source exchanger water (or brine) / refrigerant 12 and a geothermal loop 14 as a heat source, an intermediate exchanger refrigerant / water 11 itself supplemented by one or more water exchangers 15 , 17.
• the operation is similar to that of the embodiment of Figure 5.
• the low temperature exchange and storage block 4 is used as an internal exchanger.
• 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 medium temperature block 3, then passes through a first heat 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 of a second heat source, then the refrigerant 20 enters the suction of the compressor 1, and the cycle resumes.
• One of said thermal 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.
• FIG. 7 describes a non-reversible module used for heating domestic hot water and a space from a first source constituted by a geothermal loop. which transmits its heat to a water / refrigerant exchanger 12 and a second source consisting of an air / refrigerant exchanger (extract air or outside air) 7.
• a refrigerant / intermediate refrigerant exchanger water 11 is completed by one or more water exchangers 15 and 17.
• FIG. 8 Another embodiment of this type is shown in FIG. 8.
• the system is provided with a non-reversible module according to the invention, with an air / refrigerant exchanger (air extract or outside air) 7 and a solar thermal panel 10 as heat sources and a refrigerant / water intermediate exchanger 11 supplemented by one or more water exchangers 15, 17 used for space heating .
• air / refrigerant exchanger air extract or outside air
• a solar thermal panel 10 as heat sources
• a refrigerant / water intermediate exchanger 11 supplemented by 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.
• the exchange and storage block is used both for the heating of the sanitary water and for space heating through the intermediate heat exchanger 11.
• the regulation manages the power distribution thanks to the regulator and the actuators (pumps or fan).
• FIG. 9 Another embodiment of the invention is shown in FIG. 9.
• FIG. 9 describes a non-reversible module used to heat domestic hot water and a space from a first source constituted by a geothermal loop 14 which transmits its heat to a water / refrigerant exchanger and 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.
• the temperature of the geothermal source is of the order of 0 0 C (case of a horizontal capture)
• the heat of the solar thermal panel 10 will have to first, the material of the low temperature block 4 will be liquefied.
• the discharge temperature will still be sufficient to charge the high temperature block 2.
• 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, used as a heat exchanger. thermal loads, then by the expander 5, then by a very low temperature block 50 used as exchanger of the first two heat sources, then by the low temperature block 4 used as exchanger of a third source of heat, then the refrigerant 20 enters the suction of compressor 1, and the cycle resumes.
• One of said thermal loads is preferably domestic hot water, the others may be for example for the second underfloor heating, a radiator, a new air heat exchanger, a convector fan, and for the third a pool or spa.
• FIG. 1 An embodiment of this type according to the invention is represented by FIG. 1
• Figure 26 describes a system with a non-reversible module and three sources and three heat loads, used to heat domestic hot water, heat a space and heat a pool or spa, from a geothermal loop 14 which transmits its heat to a water / refrigerant exchanger 12, an air / refrigerant exchanger 7 in series with the loop 14 and a solar thermal panel 10.
• the block medium temperature 3, 300, 310, 320, 330 is equipped with 4 fluid circuits, which makes it possible to exchange heat between the storage material and 4 fluids simultaneously.
• the 4 fluids are respectively: refrigerant, hot water, space heating water, heating water of a pool or spa.
• a two-circuit very low temperature exchange and storage block 50 is placed upstream of the non-reversible module, before the low temperature exchange and storage block, and thus creates a thermal inertia at the temperature of 50.degree. phase change.
• the components are arranged so that the refrigerant 20 leaves the discharge of the compressor 1 by passing first through the high temperature block 2 and then through the medium temperature block 3, used as a heat exchanger. thermal loads, then by the expander 5, then by a very low temperature block 50 used as exchanger of the first three heat sources, then by the low temperature block 4 used as exchanger of a third source of heat, then the refrigerant 20 enters the suction of compressor 1, and the cycle resumes.
• One of said thermal loads is preferably domestic hot water, the others may be for example for the second underfloor heating, a radiator, a new air heat exchanger, a convector fan, and for the third a pool or spa.
• FIG. 27 An embodiment of this type according to the invention is represented in FIG. 27.
• Figure 27 shows a system with a non-reversible module and 4 sources and 3 heat loads, used to heat domestic hot water, heat or cool a space, and heat a pool or spa from a loop geothermal 14 which transmits its heat to a water / refrigerant exchanger 12, an air / refrigerant exchanger 7 in series with the loop 14 and a solar thermal panel 10.
• the medium temperature block 3, 300, 310, 320 , 330 is equipped with 4 fluid circuits, which makes it possible to exchange heat between the phase-change material and 4 fluids simultaneously.
• the 4 fluids are respectively: refrigerant, hot water, space heating water, heating water of a pool or spa.
• a very low temperature exchange and storage block 50 Three circuits is placed upstream of the non-reversible module and thus creates a thermal inertia at the phase change temperature. Furthermore a hydraulic three-way valve 34 is placed on the space heating circuit and connected to the very low temperature block 50. This allows to cool the space although the module is not reversible.
• a second embodiment is the reversible mode described above as the third subject of the present invention. This embodiment can be realized in different ways. a) Embodiments with two heat sources and two heat loads
• the first heat load is preferably domestic hot water.
• This first thermal load is connected by an independent circuit in series to the high temperature and medium temperature blocks.
• the second heat load can be used in either heating or cooling mode.
• the components are arranged in such a way 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 reversing valve 6. then:
• FIG. 10 depicts a reversible module according to the invention provided with non-return valves as shown in FIG. 2, used to heat domestic hot water and a space from a first source constituted by a geothermal loop water or brine 14 which transmits its heat to a water / refrigerant exchanger 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 and 17.
• 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)
• the medium temperature block 3 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 flaps makes it possible to bypass the medium temperature block 3. The heat stored therein remains available for domestic hot water.
• FIG. 11 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 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).
• the exchanger is a refrigerant / air exchanger 16.
• 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 from a first source constituted by a geothermal water loop 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.
• a first source constituted by a geothermal water loop 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.
• the intermediate refrigerant fluid exchanger Water 11 is completed by one or more water exchangers 15 and 17.
• FIG. 18 Another embodiment of the invention is shown in FIG. 18.
• the system comprises three heat sources and two heat loads. Two of the heat sources are placed in series.
• FIG. 18 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 12, a second source placed in series in the circuit of the geothermal loop, and downstream of said geothermal loop and constituted by an exchanger on the extracted air 7.
• This second source usually at a temperature above the geothermal loop warms the water circuit and therefore improves the performance coefficient of the machine more specifically in heating mode.
• the system further comprises a third heat source constituted by a solar thermal panel 10.
• the intermediate refrigerant / water exchanger 11 is completed by one or more water exchangers 15 and 17.
• the third heat load is preferably domestic hot water (of more limited capacity than in the case 2a) described above).
• This third heat 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.
• 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 reversal valve 6, then:
• the refrigerant 20 passes first through 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 heat exchanger of the first heat source, then by the low temperature block 4 used as exchanger of the second heat source, 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.
• the refrigerant 20 passes first through the low temperature block 4 used as the exchanger of the second source, then through the exchanger of the first source, then through the expander 5, then through the exchanger the second charge, then by the medium temperature block 3 used as exchanger of the first charge, then by the four-way valve to cycle reversal 6, in a different circuit, then the refrigerant 20 enters the suction of the compressor 1 , and the cycle resumes.
• FIG. 14 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 air 7) and a solar thermal panel 10 as heat sources, as well as one or more exchangers heating or cooling the space.
• the heat exchanger or heat exchanger space are water exchangers 15, 17 connected directly to the exchange block and storage medium temperature 3.
• a refrigerant / space type space heating or cooling exchanger 16 is added to the system a refrigerant / space type space heating or cooling exchanger 16.
• the solar thermal panel 10 Only the high temperature exchange and storage block 2 heats the domestic hot water.
• the extracted air is typically already at 20 0 C, the 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.
• the regulation manages the power distribution thanks to the regulator and the actuators (pumps or fan).
• the specified system as shown in Figure 14 is to allow simultaneous cooling by air and by water cooling (ground cooling). for example).
• 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.
• the high temperature exchange and storage block 2 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 preferable configuration from the point of view of heat transfer is that of the plate heat exchanger shown in FIG. 23. This configuration allows a direct exchange between the refrigerant and the water of the 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 will generally not be powered. Indeed, the cooling mode is used especially in summer when the temperature of the solar collector is high and higher than the condensing temperature of the system.
• FIG. 1 Another embodiment of the invention is shown in FIG. 1
• 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 exchanger / storage unit (at medium temperature).
• a space heating or cooling exchanger is added to the system. refrigerant / air 16.
• FIG. 1 Another embodiment of the invention is shown in FIG. 1
• the system is provided with a reversible module according to the invention not equipped with non-return valves, with a first source constituted by an air / refrigerant exchanger (extracted air or air 7), a second source constituted by a solar thermal panel 10, and exchangers heating or cooling the space.
• the exchanger (s) heating or cooling the space are water exchangers 15, 17 connected directly to the heat exchanger / storage unit at medium temperature 3.
• a system is added to the system. space heating or cooling exchanger of refrigerant / air type 16.
• a medium-temperature exchange and storage block is added in the circuit of the solar thermal panel 10.
• the heat will be stored in two exchange blocks and storage: on the one hand, the low temperature block 4 to ensure the superheating of the compressor suction gas and create stored energy in case of compressor demand and secondly, in the additional medium temperature block 300
• the sanitary water will first pass through this medium temperature block and then into the high temperature block charged by the thermodynamic cycle.
• FIG. 13 Yet another embodiment of the invention, of the non-reversible type, is represented in FIG. 13.
• the system is provided with a non-reversible module, an air / refrigerant exchanger (extract air or outside air) 7 and a solar thermal panel 10 as sources. of heat, as well as exchangers heating the 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.
• the solar thermal panel 10 When the system is used simultaneously to heat space and sanitary water, the extracted air is typically already at 20 0 C, the 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.
• the regulation manages the power distribution thanks to the regulator and the actuators (pumps or fan).
• the specificity of the system of the embodiment of Figure 13 is to allow space heating simultaneously by air and by water heaters (floor heating for example), the air for rapid warming up of the piece and the ground giving the thermal inertia and the radiating effect.
• the system according to the invention easily allows this functionality.
• the disadvantage of the system of the embodiment of FIG. 13 is a certain reduction in the amount of domestic hot water supplied since only the exchange and storage block 2 is used for the heating of the sanitary water.
• the exchange and storage blocks have been broken down into several independent sub-blocks (for example having the plate shape as in FIG. 20) loaded with materials having different phase change temperatures in order to create a temperature gradient.
• the interest is to maintain a high average coefficient of performance (COP) while increasing the temperature of the last high temperature exchange and storage block that is in contact with domestic hot water. This increases the destructive effect of legionellosis.
• COP average coefficient of performance
• the refrigerant 20 first passes through a series of high temperature sub-blocks having decreasing phase change temperature values over the range described in the detailed description (for example, can use the following sequence of sub-blocks: 75 ° C., 70 ° C. and 65 ° C.), then by a series of sub-blocks of medium temperature having decreasing phase change temperature values over the range described in the description detailed (we can for example have the following sequence of blocks: 45 ° C, 42 0 C and 39 0 C,
• the high temperature and medium temperature blocks are used here as exchangers of the first heat load.
• the fluid passes through the exchanger of the second heat load, then by the expander 5, then by the exchanger of the first heat source, then by the low temperature block.
• the Low temperature blocks are typically used as heat exchangers of the second source.
• the refrigerant then passes through the four-way valve to cycle reversal 6, in a different circuit, then the refrigerant 20 enters the suction of the compressor 1, and the cycle resumes.
• the high and medium temperature blocks having respectively the lowest phase change temperatures are loaded first with a maximum coefficient of performance. This corresponds to the lowest compressor output and condensation temperatures. Then the condensing temperature increases (under the control of the regulation if necessary) in order to charge the medium and high temperature blocks having the higher phase change temperature values. This decreases the coefficient of performance but it remains significantly higher than that obtained in a conventional system using only the condensation circuit.
• the medium and high temperature blocks are typically serially connected.
• the domestic hot water passes through the blocks having approximately the following temperatures: 33 ° C and then 36 ° C, 39 ° C, 42 ° C, 45 ° C and then the high temperature blocks 65 ° C, 70 ° C. 0 C and 75 ° C to maximize the thermal effect.
• the water thus heated is mixed if necessary with cold water to bring it to the desired value for use (typically about 45 ° C).
• the temperature gradation of the low temperature blocks is more suitable for circuits equipped with solar collectors whose temperature range is wider. This makes it easier for the control system to improve the COP in the summer by allowing the systems with sensors to have a high suction pressure on summer days with high overheating during the charging of the blocks.
• the refrigerant 20 passes firstly through the low temperature blocks 4 used as exchangers 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 blocks 3 used as exchangers of the first charge, then by the four-way valve to cycle reversal 6, in a different circuit, then the refrigerant 20 enters the suction of the compressor 1 then returns to the high temperature blocks, and the cycle resumes.
• Figures 4 to 18 do not exhaustively deal with all configurations. They aim to show the flexibility of the module for various installations.
• FIG. 19 represents a block diagram representing the exchange and storage blocks according to the technological approach of plate heat exchangers.
• This exchanger 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 domestic hot water so to obtain a double wall.
• a plate heat exchanger is already used in this way with two refrigerant circuits and one water circuit. But the use with storage material is particular to this invention and therefore part of it. It should be noted that the spacing of the plates must be greater for the storage material in order to allow sufficient thermal storage.
• FIG. 20 represents a schematic diagram representing the exchange and storage blocks according to the technological approach of the copper tubular exchangers, known as such.
• FIG. 21 represents one of the ways of organizing the components in one of the systems according to the invention.
• FIG. 22 represents one of the following ways of organizing the components in one of the systems according to the invention for the production of a water heater which comprises as heat source a geothermal loop 14.
• the dimensions of the module are 600 mm wide, 820 mm high and 600 to 650 mm deep.
• FIG. 23 represents one of the following ways of organizing the components in one of the systems according to the invention for the realization of a water / water heat pump with a heat storage according to the technology of plate heat exchangers, which comprises as heat sources a geothermal loop 14 and a heat exchanger on the extracted air (or outside) 7.
• the dimensions of the module are in this case 600 mm wide, 820 mm high and 600 at 650 mm depth.
• FIG. 24 represents a block diagram representing the exchange and storage blocks according to the technological approach of the plates. This type of plate, loaded with a low temperature storage material can be used for example in refrigerated trucks. This exchanger is similar to the conventional heat exchanger block.
• FIG. 25 represents a schematic diagram representing the exchange and storage blocks provided with three fluid circuits and an electrical heating resistor.
• a typical detached house before 1980 requires a total heating energy of about 200 kWh / m 2 / year of which about 20 kWh / m 2 / year, about 10% is used for domestic hot water.
• a house less than 10 years old will require about 100 kWh / m 2 / year.
• the proportion of domestic hot water (20 kWh / m 2 / year) represents 20% of the total.
• This energy makes it possible to heat 265 liters of water per day from 15 ° C to 40 ° C
• an average latent heat value of 250 kJ / kg and a density of 800 kg / m 3 can be taken .
• the total volume of the two exchanger blocks can be estimated at 100 cubic decimetres.
• the hypotheses taken 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. We consider a 100% hot water operation (no heating space charge).
• the blocks are loaded according to the operating condition below:
• the condensation temperature is 40 ° C, considered equal to the phase change temperature of the medium temperature block.
• 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 compressor suction temperature may be higher if necessary, by keeping the circuit of the compressor on. solar captor).
• the enthalpy of the refrigerant at 20 ° C. is 446 kJ / kg.
• the discharge temperature of the compressor is 95 ° C: the enthalpy of the refrigerant at the discharge of the compressor ⁇ 500 kJ / kg
• the phase change temperature of the high temperature block is 70 ° C.
• the enthalpy of the refrigerant at 70 ° C. is 470 kJ / kg.
• the change in enthalpy of the fluid during the condensation in the medium temperature block at 40 ° C. is equal to 160 kJ / kg.
• the ratio of enthalpy variations 30/160 gives about 20% for the high temperature block.
• the high temperature block we thus obtain 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. Indeed, during most of the year, the power available at the solar collector not only liquefies the storage material of the low temperature block, but also to increase the temperature of the low temperature storage material to a value significantly higher than its melting temperature. This has the consequence of raising the temperature at the suction of the compressor, and therefore at the discharge of the compressor. So we have an increase in the amount of sensible heat available at the level of the compressor discharge gases and therefore the energy that can be stored in the high temperature block, thus increasing the efficiency of the system.
• Circulation of domestic hot water in the medium and high temperature exchange blocks will be done so that 80% of the difference in temperature (from 15 ° C to 35 ° C) is made in the medium temperature block and 20% ( 35 ° C to 40 ° C) is made in the high temperature block.

Landscapes

• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Central Heating Systems (AREA)
• Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
• Heat-Pump Type And Storage Water Heaters (AREA)

Applications Claiming Priority (3)

Publications (1)

Family

ID=39185871

Family Applications (1)

Country Status (3)

Families Citing this family (8)

Family Cites Families (15)

• 2006
  • 2006-10-30 FR FR0609512A patent/FR2906604A1/fr not_active Withdrawn
• 2007
  • 2007-09-27 WO PCT/FR2007/001586 patent/WO2008037896A2/fr not_active Ceased
  • 2007-09-27 EP EP07848295A patent/EP2069696A2/de not_active Withdrawn

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events