FR3009071A1 - REFRIGERATIVE CIRCUIT, INSTALLATION COMPRISING SUCH CIRCUIT AND CORRESPONDING METHOD - Google Patents

Abstract

The invention relates to a refrigerant circuit (2) for an installation, called thermofridge pump (1), comprising a compressor (200), a condenser exchanger (21, 22), a balancing exchanger (25), a node (NL1) connection between the condenser exchanger (21, 22) and the balancing exchanger (25), and an evaporator exchanger (23), two fluid management devices (51, 52) each comprising four channels. The invention also relates to an installation comprising such a refrigerant circuit and hot and cold fluid production circuits, and a method for heating and / or cooling fluid using such a facility.

Description

The present invention generally relates to installations and methods for heating and cooling fluids, in particular for a building.

It is known from the state of the art heating and cooling fluid systems, heat pump type. Thus, the document "The simultaneous production of ice water and hot water at 95 ° C by a thermofridge pump of a dairy", written in 1982 by E. Lecrivain, G. Laroche and A. Vallot, in the International Review Cold, describes an installation consisting of two cascade refrigerant circuits to supply water at 95 ° C and chilled water. Such an installation saves a significant amount of energy compared to an equivalent installation which would be composed of a refrigeration unit and a gas boiler.

However, the features offered by these known prior art installations are limited and their complexity has proved to be a source of problems.

It is therefore desirable to develop a new installation for heating and cooling fluids bringing a gain in energy efficiency compared to conventional solutions, while using a minimum of refrigerant and allowing the activation of different modes of operation to meet the need for heating and cooling fluids in a building, in a simplified architecture. The object of the present invention is to propose a new installation for heating and cooling fluids proposing an architecture allowing the heating of a fluid, for example for the production of domestic hot water and / or the heating of the building, and the cooling of another fluid, both simultaneously and independently of each other.

Another object of the invention is to propose a new installation for heating and cooling fluids using a minimum of refrigerant.

Another object of the invention is to limit the energy consumption of the installation. Another object of the invention is also to provide a heating and cooling fluid facility for defrosting, with reduced energy consumption, the portion of the installation subjected to frost. For this purpose, the subject of the invention is a refrigerant circuit for an installation, called a heat pump, for heating and / or cooling fluids, comprising: a compressor, an exchanger, called a condenser exchanger, comprising a condenser circuit; an exchanger, called a balancing exchanger, comprising a circuit called a condenser / evaporator circuit able to operate either in a condenser or in an evaporator, and preferably a fan associated with said balancing exchanger, a first connection node between a branch of the refrigerant circuit provided with the condenser exchanger and a branch of the refrigerant circuit provided with the equilibrium exchanger, the said connection node being situated on the side of the outlet 25 of the condenser exchanger, - an exchanger, referred to as the evaporator exchanger , comprising an evaporator circuit, - a first fluid management device comprising four channels, including a first channel, called input channel, connected to the output of the compressor, a second channel, called a low-pressure path, a third channel connected to the balancing exchanger on the opposite side to the first connection node, and a fourth channel connected to the input of said condenser exchanger; a second fluid management device comprising four channels, including a first channel, called an input channel, connected to said first connection node, a second channel, called a low-pressure channel, a third channel connected to the input of the second channel; evaporator exchanger, and a fourth channel connected to the balancing exchanger between the first connection node and the condenser / evaporator circuit of the balancing exchanger; a first expander located between the third channel of the second fluid management device and the evaporator exchanger, and a second expander situated between the fourth channel of the second fluid management device and the balancing exchanger, the second wherein the channels of the management devices are connected to a branch of the refrigerant circuit which extends between the evaporator exchanger circuit output and the compressor inlet, each fluid management device being configured to have a first configuration according to which the input channel is in communication with the third channel, the low-pressure path being communicated with the fourth channel, and a second configuration in which the input channel is put in communication with the fourth channel, the channel low pressure being communicated with the third channel. As detailed below, such an installation makes it possible to benefit from a simultaneous or alternating production of hot fluid and of cold fluid that can be used for heating, the production of domestic hot water, and cooling, particularly for a building for example residential or tertiary type. The balancing exchanger makes it possible to adjust the production of hot and cold by switching from one mode to another by controlling the fluid management devices so that in certain modes the balancing exchanger operates as a condenser. and in other modes the balancing exchanger operates as an evaporator.

Thanks to the connection of each second channel (low pressure path) to the part of the refrigerant circuit located downstream of the evaporator exchanger and upstream of the compressor, the four-way management devices make it possible to connect, according to the activated operating mode, the unused exchangers of the refrigerant circuit at the low-pressure part of the refrigerant circuit, while putting the exchangers used in this operating mode into communication with each other. This specificity of the architecture of the refrigerant circuit which makes it possible to connect the unused exchangers to the low-pressure part acts as a draw-off in the unused parts of the refrigerant circuit and makes it possible to reintegrate the refrigerant into the useful parts of the circuit. refrigerant by avoiding the trapping of refrigerant in unused parts of the circuit.

In particular, the fact of being able to put in communication the second channel (low pressure way) of the first management device with the fourth channel connected to the condenser exchanger or the third channel connected to the balancing exchanger, allows, when said condenser exchanger or the balancing exchanger is not active, because of the selected operating mode of the installation, to migrate the refrigerant vapor, trapped in these exchangers, in the low active pressure part of the circuit refrigeration. Likewise, the connection of the outlet of the evaporator exchanger to the low-pressure part makes it possible, when said evaporator exchanger is inactive, to recover in the active low-pressure part of the refrigerant circuit the vapor of refrigerant remaining in said evaporator exchanger. It is thus possible to reduce the refrigerant refrigerant circuit load to the minimum necessary for the operation mode that requires the most load.

According to a preferred embodiment of the invention, the refrigerant circuit also comprises an exchanger, called a subcooler exchanger, which comprises a first heat transfer circuit arranged between the input channel of the second management device and the first node. connecting, and preferably disposed between said inlet channel and a bottle of liquid.

As detailed below, the use of such a subcooler exchanger makes it possible to recover and store energy for using it in a delayed time in order to improve the fluid heating performance and / or to defrost the fluid. balancing exchanger.

According to an advantageous characteristic of the invention, said circuit comprises a non-return valve arranged between the outlet of the evaporator exchanger and said connection of the second channels of the management devices to prevent the fluid from flowing from said connection to the evaporator exchanger. .

According to an advantageous characteristic of the invention, said circuit comprises a non-return valve arranged between the first connection node and the condenser exchanger to prevent a fluid flow from said first connection node to the condenser exchanger.

According to an advantageous characteristic of the invention, said refrigerant circuit comprises a nonreturn valve arranged between, on the one hand, the first connection node and, on the other hand, a third connection node between the second expander and the balancing exchanger, for preventing fluid flow from said first link node to the third link node.

According to an advantageous characteristic of the invention, said circuit comprises a non-return valve arranged between the fourth channel of the second management device and the second expander to prevent a circulation of fluid from the second expander to the fourth channel of the second management device . The presence of these non-return valves makes it possible to benefit from the different modes of operation of the installation without having to provide specific solenoid valves. According to an advantageous characteristic of the invention, said first fluid management device is a 4-way valve which comprises a member, called a slide, movable between two positions respectively corresponding to said first and second configurations of the first fluid management device. According to an advantageous characteristic of the invention, said second device 10 fluid management is a 4-way valve which comprises a member, called drawer, movable between two positions respectively corresponding to said first and second configurations of the second fluid management device. The design of such a communication architecture between the exchangers of the refrigerant circuit and the use of two 4-way valves makes it possible to use only a small number of actuators to control the various modes of operation of the installation. and thereby reduce the cost and improve the reliability of the installation, and optimally manage the refrigerant charge. Indeed, the use of two 4-way valves for distributing the refrigerant in the exchangers used in the different modes simplifies the transition from one mode to another compared to a solution with four solenoid 2- ways. The number of actuators and controller outputs is therefore limited. In addition, as detailed below, the connection of the second channel of each management device to the inlet of a bottle anti-liquid stroke whose output is itself connected to the compressor inlet, allows to ensure a pressure difference between the pair of channels of the management device placed in communication in order to ensure a good displacement of the drawer of the corresponding management device. Indeed, each second channel is put at low pressure by its connection with the inlet of the bottle anti-coup de liquid. The channel of the management device placed in communication with this second channel is then also reduced to the low pressure, and the input channel of each management device, as well as the channel with which said input channel is placed in communication , are at high pressure. Advantageously, said circuit comprises an additional exchanger, arranged in series with the condenser exchanger, between said first connection node and the fourth channel of the first management device. Thus, as detailed below, one of the two heat exchangers can be used for heating the domestic hot water and the other for heating a heating circuit fluid. Alternatively, said two exchangers can be used to heat a fluid, gas or liquid, at two different temperature levels. According to an advantageous characteristic of the invention, said circuit comprises a reservoir, called anti-blow bottle of liquid, positioned between the compressor and the connection of the second channels of the management devices. The use of an anti-liquid bottle thus positioned upstream of the compressor makes it possible to ensure that the compressor is well fed with fluid in the vapor state and not in the liquid state. Any fluid in the liquid state entering the bottle would be trapped in the bottle and then naturally vaporized before suction by the compressor. According to an advantageous characteristic of the invention, said circuit comprises a reservoir, called a liquid bottle, and said inlet channel of the second fluid management device is connected to said first connection node via the liquid bottle. . The use of such a liquid bottle makes it possible to ensure that the regulators are supplied with refrigerant in the liquid state and not in the vapor state. Said liquid bottle also allows as detailed below to ensure that the subcooling heat exchanger, which works by sensitive transfer, is fed with liquid fluid and not with steam.

The invention also relates to an installation comprising a refrigerant circuit as described above, characterized in that, the condenser exchanger comprising a heat transfer circuit, said installation comprises a heating circuit which comprises said transfer circuit of the heat transfer circuit. condenser exchanger, a circulation pump, and preferably a fluid storage tank, called a hot water tank, and in that, the evaporator exchanger comprising a heat transfer circuit, said installation comprises a cooling circuit which comprises said evaporator exchanger transfer circuit, a circulation pump, and preferably a fluid storage tank, called cold fluid balloon. According to an advantageous characteristic of the invention, the additional exchanger comprising a heat transfer circuit, said installation comprises an additional hot fluid production circuit which comprises said exchanger transfer circuit, a circulation pump, and preferably a fluid storage tank, called a hot water tank. According to an advantageous characteristic of the invention, the subcooling exchanger comprising a second transfer circuit, said second transfer circuit of the subcooler exchanger is mounted on the bypass cooling circuit of the transfer circuit of the evaporator exchanger.

In particular, a first solenoid valve is positioned between the inlet of the transfer circuit of the evaporator exchanger and the connection of the inlet of the second transfer circuit of the subcooler exchanger to the cooling circuit. Similarly, a second solenoid valve is positioned between the inlet of the second transfer circuit of the subcooler heat exchanger and the connection of this input of the second transfer circuit of the subcooler heat exchanger to the cooling circuit.

Such an arrangement of solenoid valve makes it possible to control the passage of fluid of the cooling circuit by the subcooler exchanger or by the evaporator exchanger.

According to an advantageous characteristic of the invention, the installation comprises a control unit comprising control means for controlling the stopping and running of each of the circulation pumps, independently of one another.

As detailed below, the control unit makes it possible to control the various components of the installation to obtain the desired operating mode, and in particular: the positioning of the spool of the first or second fluid management device in first or second position ; 20 - switching on or off the balancing exchanger fan; - starting or stopping the heating circuit pump; - switching on or off the cooling circuit pump; - starting or stopping the pump of the DHW production circuit; the control of the solenoid valve at the inlet of the subcooler exchanger; The control of the solenoid valve at the inlet of the evaporator exchanger. According to an advantageous characteristic of the invention, the installation comprises a control unit configured to execute a sequence of instructions, called the heating mode, comprising the following steps: for each of the first and second management devices, placing in communication the fourth lane with the first lane; - Activation of the heating circuit pump, - preferably activation of the fan associated with the balancing exchanger. According to an advantageous characteristic of the invention, the installation comprises a control unit configured to execute a sequence of instructions, called simultaneous mode, comprising the following steps: for the first management device, putting in communication the first track with the fourth lane; for the second management device, placing the first channel in communication with the third channel; 10 - activation of the heating circuit pump and the cooling circuit pump. According to an advantageous characteristic of the invention, the installation comprises a control unit configured to execute a sequence of instructions, called the energy storage mode, comprising the following steps: in heating mode, activate the circuit pump cooling and control the solenoid valves so as to circulate the cooling circuit fluid through the second transfer circuit of the subcooler heat exchanger, and the corresponding balloon. According to an advantageous characteristic of the invention, the control unit is configured to execute a sequence of instructions, called the mode of use of the energy stored on the cooling circuit, which comprises the following steps; In a delayed mode and in an operating mode of the installation corresponding to the simultaneous mode or the cooling mode, preferably without ventilation, activate the cooling circuit pump and control the solenoid valves so as to circulate the hot fluid contained in the balloon. of the cooling circuit through the transfer circuit of the evaporator exchanger. According to an advantageous characteristic of the invention, the installation comprises a control unit configured to execute a sequence of instructions, called refresh mode, comprising the following steps: for each management device, putting the first channel into communication with the third way; - Activation of the cooling circuit pump, - preferably activation of the fan associated with the balancing exchanger. According to an advantageous characteristic of the invention, said heating circuit being a heating circuit of domestic hot water, called ECS circuit, said installation comprises a control unit configured to execute a sequence of instructions, called simultaneous ECS mode, comprising the following steps: for the first management device placed in communication of the first channel with the fourth channel; for the second management device placed in communication of the first channel with the third channel; - activation of the DHW circuit pump and the cooling circuit pump. According to an advantageous characteristic of the invention, said heating circuit 20 being a hot water heating circuit, called ECS circuit, said installation comprises a control unit configured to execute a sequence of instructions, called ECS mode alone, comprising the following steps: - for each management device, placing the first channel 25 in communication with the fourth channel; - Activation of the DHW circuit pump and preferably the fan associated with the balancing exchanger. According to an advantageous characteristic of the invention, the installation comprises a control unit configured to execute a sequence of instructions, called defrosting mode, comprising the following steps: for each management device, putting the first channel into communication with the third way; the solenoid valves are controlled so as to prevent the circulation of fluid of the cooling circuit by the second transfer circuit of the subcooler exchanger and to allow the circulation of said fluid by the transfer circuit of the evaporator exchanger; activation of the cooling circuit pump, - preferably, stop of the fan associated with the balancing exchanger. When operating in heating mode, the balancing exchanger 10 operates as an evaporator. When outside temperatures are below about 6 ° C (and especially when they are between 0 ° C and 6 ° C), the accumulation of frost on the balancing exchanger significantly degrades the performance of the installation. Therefore, it is useful to include an efficient de-icing system to ensure high energy efficiency and preferably continuous hot water production. The de-icing method used is similar to a cycle reversal as a means of removing frost from the balancing exchanger. Indeed, the balancing exchanger operates alternately either evaporator or condenser. This allows, during a transition to defrost mode, to inject the hot gases directly to the discharge of the compressor in the air exchanger. In this sequence, the evaporator exchanger is connected to the cold fluid flask that previously stored hot fluid. The energy previously recovered and stored in the cold fluid flask is then used to ensure the evaporation of the refrigerant. This defrosting method 25 makes it possible not to draw energy from the heating balloon and thus constitutes an advantage over the state of the art. Indeed, calculations from experimental measurement show that the seasonal yield (COP) is improved by 13% because of this deicing solution. In defrost mode, the operating logic of the installation corresponds to operation of the cooling circuit in cooling mode, preferably without ventilation. Stopping the fan allows more heat transfer to the frost layer and saves electrical energy. According to an advantageous characteristic of the invention, each flask is equipped with a sensor of a value representative of the temperature of the fluid contained inside said flask, the compressor is equipped with a sensor of a value representative of the inlet pressure and a sensor of a value representative of the outlet pressure, and the refrigerant circuit preferably comprises a sensor of a value representative of the temperature at the inlet 10 of the balancing exchanger and a sensor of a value representative of the temperature of the outer surface of the balancing exchanger, said control unit is configured to control the transition from one operating mode of the installation to another depending on the measured values and predefined threshold values. The invention also relates to a method for heating and / or cooling fluids using an installation as described above. The invention will be better understood on reading the following description of exemplary embodiments, with reference to the appended drawings in which: FIG. 1 is a schematic view of the installation according to the invention coupled to a set of networks fluid distribution; FIG. 2 is a view of the hot fluid recovery system of the plant according to the invention, in a configuration for storing hot fluid in a flask; FIG. 2A is a view of the hot fluid recovery system of the installation according to the invention, in the circulation configuration of the hot fluid, previously stored, through the evaporator exchanger; - Figure 3 is a schematic view of the architecture of the refrigerant circuit of the installation according to the invention; - Figure 4 is a view of the refrigerant circuit of Figure 3 according to a first mode of operation, called heating mode; - Figure 5 is a view of the refrigerant circuit of Figure 3 according to a second mode of operation, called simultaneous mode; - Figure 6 is a view of the refrigerant circuit of Figure 3 according to a third mode of operation, called cooling mode; - Figure 7 is a view of the refrigerant circuit of Figure 3 according to a fourth mode of operation, called simultaneous ECS mode; - Figure 8 is a view of the refrigerant circuit of Figure 3 according to a fifth mode of operation, called ECS mode; FIG. 9 is a view of the refrigerant circuit of FIG. 3 according to a sixth mode of operation, called the deicing mode; FIG. 10 is a schematic view of the installation according to the invention, showing measuring probes associated with various components of the installation; FIGS. 11 to 13 show logic diagrams based on differential thermostats and logic comparators expressing heating, cooling, hot water and defrosting needs; FIGS. 14 to 16 are graphs illustrating performance tests carried out on a prototype thermofridge pump according to the invention. With reference to the figures, there is shown an installation, called thermofridge pump 1, for heating and cooling fluids, for example in a residential or tertiary building. Of course, industrial applications of such an installation are also conceivable. In the example illustrated in the figures and as detailed below, said installation makes it possible to heat the fluid of a heating circuit, to produce domestic hot water (DHW), and to cool the fluid of a circuit. cooling type air conditioning. Thanks to the following detailed architecture of the installation, these features can be activated simultaneously or independently. Said plant comprises a refrigerant refrigerant circuit 2 which comprises a compressor 200. Said compressor 200 makes it possible to compress refrigerant vapor. Preferably, said installation comprises a reservoir 201 called anti-blow liquid bottle. Said anti-blow bottle 201 has an inlet and an outlet connected to the inlet of the compressor 200. Said anti-blow bottle 201 is configured in such a way that the fluid leaving said bottle is in the vapor state. even if some of the incoming fluid contains drops of liquid.

The refrigerant circuit 2 also comprises an exchanger 21, called the heat exchanger ECS, which comprises a condenser circuit, that is to say a circuit adapted to ensure the condensation of the refrigerant, and a circuit, called a transfer circuit connected to a circuit 31 of domestic hot water production, called ECS circuit 31 to allow, by heat transfer from the condenser circuit to the transfer circuit of said exchanger 21, to heat the water of said ECS circuit 31. Alternatively, it can be provided that the circuit 31 contains a fluid which may be a gas or a liquid intended to be brought to a high temperature, that is to say at least 55 ° C.

Said DHW circuit 31 comprises said transfer circuit of the DHW exchanger 21, a circulation pump 310, and preferably a fluid storage tank, called hot water tank 311. Similarly, the refrigerant circuit 2 also comprises an exchanger 22, called a heat exchanger, which comprises a condenser circuit, that is to say a circuit adapted to ensure the condensation of the refrigerant, and a circuit, called a cooling circuit. transfer, connected to a heating circuit 32 to allow, by heat transfer from the condenser circuit to the transfer circuit of said exchanger 22, to heat the fluid of said heating circuit 32. The fluid may be a gas or a liquid. Said heating circuit 32 comprises said transfer circuit of the heat exchanger 22, a circulation pump 320, and preferably a fluid storage tank, called a hot water cylinder 321. The exchangers 21, 22 are arranged in series on the same branch of the refrigerant circuit. The exchanger 21 is positioned upstream of the heat exchanger 22. Another branch of the refrigerant circuit also comprises an exchanger 25, called a balancing exchanger, which comprises a circuit, called a condenser / evaporator circuit, capable of operating either as a condenser or in the evaporator according to the operating mode of the installation as detailed below. In the example illustrated in the figures, the balancing exchanger 25 operates by heat exchange between said fluid flowing through the condenser / evaporator circuit and the air. Preferably, a fan is arranged with the exchanger 25 to generate a forced convection movement around the balancing exchanger. Alternatively, it can be provided that the medium with which the condenser / evaporator circuit of said balancing exchanger 25 exchanges is another heat transfer circuit fluid circuit. Said refrigerant circuit 2 has a first connection node NL1 between the branch of the refrigerant circuit 2 provided with the exchangers 21, 22 ECS and heating and the branch of the refrigerant circuit 2 provided with the equilibrium exchanger 25. Said connecting node NL1 is located on the output side of the exchanger 22. The circuit comprises an exchanger 23, called evaporator exchanger, which has an evaporator circuit, that is to say a circuit capable of vaporizing the fluid 30 refrigerant, the output of which is connected to the inlet of the bottle 201 anti-coup of liquid, and a transfer circuit connected to a cooling circuit 33, to allow heat transfer from the transfer circuit to the evaporator circuit of said evaporator exchanger 23, to cool the fluid of said cooling circuit 33. Said fluid of the cooling circuit 33 may be a gas or a liquid.

Said cooling circuit 33 comprises said transfer circuit of the evaporator exchanger 23, a circulating pump 330, and preferably a fluid storage tank, called a cold-fluid balloon 331. The presence of the flasks 311, 321, 331 makes it possible to decouple the production of cold fluid and hot fluid, with respect to the distribution towards the corresponding networks 4. For each circuit 31, 32, 33, the corresponding circulation pump 310, 320, 330 is placed between the exchanger 21, 22, 23 and the corresponding balloon 311, 321, 331. The thermofridge pump 1 thus comprises two sets: - The refrigerant circuit 2 which allows the production of heat energy or refrigeration simultaneous or alternating, 20 - all the hydraulic circuits 31, 32, 33 connected to the different distribution networks 4, here a cold fluid network, a hot water network and a hot water network. A first fluid management device 51 makes it possible to direct and / or stop the circulation of fluid between the components, in particular the exchangers, of the refrigerant circuit. Said first fluid management device 51 comprises four channels, of which: a first channel, called an input channel 511, connected to the output of the compressor 200, a second channel, called a low-pressure channel 512, connected to the inlet of the bottle 201 anti-coup de liquid, that is to say connected to a low-pressure part of the refrigerant circuit 2, - a third channel 513 is connected to the condenser / evaporator circuit of the balancing exchanger 25 side of said exchanger opposite the first link node NL1; and a fourth channel 514 is connected to the input of the condenser circuit of said heat exchanger 21. Said refrigerant circuit also comprises a second fluid management device 52 also comprising four channels, of which a first channel, called input channel 521, connected to said first connection node NL1 via a liquid bottle 202. As detailed below, the connection between this input channel 521 and the first connection node NL1 is made via a heat exchanger 24 subcooler. A second path, called a low-pressure path 522, is connected to the inlet of the anti-blow-off cylinder 201, corresponding to a low-pressure portion of the refrigerant circuit 2. A third path 523 is connected to the inlet of the refrigerant. evaporator exchanger 23, and a fourth channel 524 is connected to the balancing exchanger 25, between the first link node NL1 and the balancing exchanger, via a node NL3. Each fluid management device 51, 52 is a 4-way valve which comprises a member, called a slide, movable between a first position and a second position. In said first position, the input channel 511, 521 is placed in communication with the third channel 513, 523, the second channel 512, 522 being placed in communication with the fourth channel 514, 524. In said second position, the channel 511, 521 is placed in communication with the fourth channel 514, 524, the second channel 512, 522 being placed in communication with the third channel 513, 523. Said refrigerating circuit also comprises a first expander 203 located between the third track 523 of the valve 52 and the exchanger 23 evaporator, and a second expander 205 located between the fourth channel 524 of the valve 52 and the balancing exchanger 25.

Said liquid bottle 202 is a reservoir arranged on a branch of the refrigerant circuit defined between the link node NL1 and the input channel 521 of the second management device 52. The bottle 202 of liquid is placed on the liquid line to optimize the refrigerant charge circulating in the refrigerant circuit in all modes of operation. In the example illustrated in the figures, the subcooler exchanger 24 (detailed below) is located on this branch of the circuit downstream of the bottle 202.

The bottle of liquid 202 is configured to trap the fluid in the vapor state that arrives at this level of the refrigerant circuit, that is to say the fluid present in the high pressure part of the circuit upstream of the 4-way valve. 52, so that it is ensured that the fluid passing through the regulator (s) 203, 205 is in the liquid phase in order to obtain an efficient operation of the installation. Said liquid bottle 202 contains in practice a liquid-vapor mixture of refrigerant. A separation of the liquid and vapor phases is carried out by gravity. The outlet of this liquid bottle 202 draws refrigerant at the bottom of the tank which contains refrigerant in the liquid state. The exchanger 24 subcooler comprises a first transfer circuit forming part of the refrigerant circuit 2 and disposed between the inlet channel 521 of the valve 52 and the liquid bottle 202. The exchanger 24 subcooler also comprises a second transfer circuit enabling the fluid flowing through it to recover heat from the fluid flowing through the first transfer circuit of said exchanger 24. Said second transfer circuit of exchanger 24 subcooler is mounted on the cooling circuit 33 in parallel with the transfer circuit of the exchanger 23 evaporator. A first solenoid valve 333 is positioned between the inlet of the transfer circuit of the exchanger 23 evaporator and the connection of the inlet of the recovery circuit of the exchanger 24 subcooler on the cooling circuit 33. A second solenoid valve 334 is positioned between the inlet of the second transfer circuit of the exchanger 24 subcooler and the connection of this input of the second transfer circuit to the cooling circuit 33. Said solenoid valves define the path traveled by the liquid in the cooling circuit 33. The presence of the bottle 202 upstream of the first transfer circuit of the subcooler heat exchanger 24 ensures that the fluid flowing through the subcooler heat exchanger 24 is in the liquid state, which, in energy storage mode as detailed below, ensures a good heat transfer sensible heat between the first transfer circuit traveled by the refrigerant and the second transfer circuit traversed by the fluid of the cooling circuit. The refrigerant circuit includes a low pressure portion and a high pressure portion. The low pressure part corresponds to the branches of the refrigerant circuit traversed by the fluid which are located downstream of the holder (s) and upstream of the compressor. The high pressure part corresponds to the branches of the refrigerant circuit traversed by the fluid which are located upstream of the pressure regulator (s) and downstream of the compressor. As illustrated more particularly in FIG. 3, the refrigerant circuit 2 comprises a second connection node NL2 between the inlet of the anti-blow bottle 201, the low pressure path 512 of the valve 51, the low pressure path 522 of the the valve 52 and the outlet of the evaporator circuit of the exchanger 23 evaporator.

A non-return valve CARI is arranged between the outlet of the evaporator circuit of the evaporator exchanger 23 and said second connection node NL2 to prevent the fluid from entering the evaporator exchanger 23 through the outlet of the evaporator circuit of said exchanger. Another check valve CAR2 is arranged between the first connection node NL1 and the exchanger 22 to prevent a fluid flow from said first connection node NL1 to the exchanger 22. A check valve CAR3 is arranged between on the one hand, the first link node NL1 and, on the other hand, a third link node NL3 connecting the second expander 205 and the balancing exchanger 25, to prevent a flow of fluid from said first node connecting link NL1 to the third link node NL3 and therefore to the balancing exchanger 25. Said circuit comprises a nonreturn valve CAR4 arranged between the fourth channel 524 of the second management device 52 and the second expander 205 to prevent a flow of fluid from the expander 205 to the fourth channel 524 of the valve 52. Said installation comprises a control unit 7 which comprises control means for controlling the stopping and running of each of the pumps 310, 320, 330 of circulation, independently of each other. The control unit is in the form of a programmable controller provided with a memory in which are recorded in particular threshold values as detailed below. When in the following description, it is specified that the unit is configured or comprises means for performing a given operation, it means that the corresponding controller comprises instructions for performing said operation. The heating circuit 32 and the DHW circuit 31 are independent of each other. The activation or stop of each of these circuits is achieved by controlling the running or stopping of the circulation pump of the corresponding circuit. There are six modes of operation detailed below: heating mode, simultaneous mode, cooling mode, simultaneous DHW mode, DHW mode only, and defrost mode. The controller uses control logic to switch from one mode to another as needed. The programmable controller is configured to control the engagement of the various operating modes according to the changing needs of the building. The controller may include means for determining requirements using sensors and instructions as detailed below. The different modes of operation are detailed below. The heating mode is activated by the control unit of the installation when it identifies a need for heating alone. As illustrated in FIG. 4, the activation of the heating mode corresponds to the following sequence of instructions. The slide of each valve 51, 52 is located in the position corresponding to a communication of the first channel 511, 521 with the fourth channel 514, 524 and therefore of the third channel 513, 523 with the second channel 512, 522, so as to connect the equilibrium exchanger 25 to the low pressure and the heat exchanger 22 to the discharge of the compressor 200. In parallel, the pump 320 of the heating circuit 32 is activated, as well as the fan associated with the exchanger 25. while the pump of the DHW circuit 31 is stopped. Thus, the refrigerant, which circulates in the refrigerant circuit through the compressor 200, condenses in the condenser circuit of the heat exchanger 22 to give up its heat to the fluid flowing through the transfer circuit of said heat exchanger 22 in order to It is stored in the tank 321 of the heating circuit 32. The exchanger 21 ECS behaves like a simple pipe. At the balancing exchanger 25, the fan is turned on and the fluid is vaporized as it passes through the evaporator circuit of said balancing exchanger, drawing heat from the outside air and then the vapors. are sucked at the level of the bottle 201 anticoup of liquid.

In this operating mode the refrigerant does not flow through the evaporator circuit to exchange the evaporator 23, but the latter remains connected to the suction of the compressor 200 by a branch which connects it to the bottle 201 anti-coup liquid. As mentioned above, this branch, equipped with the CARI nonreturn valve, makes it possible to recover the charge trapped in the evaporator and to overcome any malfunction of the compressor during transitions between modes. As detailed below, the energy storage can be activated in parallel with this heating mode. For this storage, as illustrated in FIG. 2, the pump 330 of the cooling circuit 33 is activated and the solenoid valves 333, 334 are in a position adapted to the circulation of the fluid of the cooling circuit 33 by the second transfer circuit of the exchanger 24 subcooler. Thus, the liquid that passes through the transfer circuit of the exchanger 24 subcooler yields by sensible transfer of heat to the fluid that flows through the pump 330 in the second transfer circuit of the heat exchanger 24 sub-cooler in order to The balloon 331 can thus store hot water for use in deferred time as explained hereinafter.

During the heating period, this installation thus offers the possibility of storing a certain quantity of energy at low temperature on the cooling circuit 33 by means of the exchanger 24 subcooler. This stored energy can be used in deferred time, in the simultaneous modes and / or defrosting, by circulation through the evaporator exchanger 23 by reversing the opening and closing order of the two solenoid valves 333, 334 (see FIG. 2A). .

This makes it possible to improve the performance of the installation in a simultaneous mode by increasing the evaporation temperature or, if necessary, deicing the balancing exchanger without having to draw heat from the medium to be heated. Indeed, the defrost logic of the thermofridge pump does not draw energy from the heating tank and does not consume energy for the fan. As explained above, the defrost is performed in a special mode corresponding to cooling mode without ventilation. The energy used for the defrosting comes from energy storage in the balloon, which improves the performance compared to the usual cycle reversal mode according to the state of the art of the so-called heat pumps. air / water ". As illustrated in FIG. 5, another mode, called simultaneous mode, is activated by the control unit when it identifies a need for heating concomitant with a need for refreshing. The control unit is then configured to perform the following steps. The slide of the valve 51 is in the communication position of the low pressure path 512 with the third path 513 so that the entry way 511 communicates with the fourth path 514. As a result, the entrance of the circuit condenser of the heat exchanger 22 is connected to the discharge outlet of the compressor, and that the balancing exchanger 25 is connected to the inlet of the bottle 201. Similarly, the slide of the valve 52 is in position placing the low-pressure path 522 in communication with the fourth path 524 so that the input path 521 communicates with the third path 523. The unit also controls the activation of the pump 320 of the heating circuit 32 and of the pump 330 of the cooling circuit 33. The pump 310 of the DHW circuit 31 is stopped, so that the condenser circuit of the exchanger 21 ECS 30 behaves as a single pipe. The solenoid valves 333, 334 are controlled so as to prevent the circulation of fluid by the second transfer circuit of the exchanger 24 subcooler and allow the circulation of said fluid by the transfer circuit of the exchanger 23 evaporator, so that the first transfer circuit of the heat exchanger 24 subcooler behaves as a simple pipe. Thus, the refrigerant, which circulates in the refrigerant circuit through the compressor 200, condenses in the condenser circuit of the heat exchanger 22 to transfer its heat to the fluid flowing through the transfer circuit of said heat exchanger 22 to be stored in the tank 321 of the heating circuit 32. At the outlet of the heat exchanger 22, the fluid in the liquid state is directed by the valve 52 to the expander 203. The refrigerant then passes through the evaporator circuit of the evaporator exchanger 23 where it is vaporized, while the fluid of the cooling circuit 33 flowing in the transfer circuit of the exchanger 23 is cooled.

The inlet and the outlet of the condenser / evaporator circuit of the equilibrium exchanger 25 are connected to the anti-blow bottle 201, which facilitates the reintegration of the charge of refrigerant trapped in the exchanger 25. balancing not used in this mode.

As illustrated in Figure 6, another mode, called cooling mode, is activated by the control unit when it identifies a need for cooling alone. This refresh mode includes the following steps. The slide of each valve 51, 52 is positioned for communication of the fourth channel 514, 524 with the low pressure path 512, 522. Thus, the balancing exchanger 25 communicates on the opposite side to the link node NL3 , with the discharge outlet of the compressor 200, and the other side of the balancing exchanger 25 communicates (through the bottle 202) with the inlet of the evaporator circuit of the exchanger 23 evaporator.

The solenoid valves 333, 334 are controlled to allow the circulation of the cooling circuit fluid by the transfer circuit of the evaporator exchanger 23 and the pump 330 of the cooling circuit 33 is running.

The refrigerant refrigerant circuit then passes through the evaporator circuit of the exchanger 23 evaporator where it is vaporized while the cooling circuit fluid flowing in the transfer circuit of the exchanger 23 evaporator is cooled. At the balancing exchanger 25, the fan is on and the fluid exiting the compressor 200 condenses in the condenser / evaporator circuit of the balancing exchanger by giving up its heat to the air. DHW exchangers 21, 22 and heating are not solicited in this mode and are connected to the bottle 201 anti-liquid stroke to facilitate the reintegration of the refrigerant charge. As illustrated in FIG. 7, another mode, called simultaneous DHW mode, is activated by the control unit when it identifies a simultaneous need for domestic hot water (DHW) and cooling. The slide of the valve 51 is positioned to put the third channel 513 in communication with the low pressure path 512 so that the inlet channel 511 communicates with the fourth channel 514. Thus, the inlet of the condenser circuit of the exchanger 21 DHW is connected to the discharge outlet of the compressor 200 and the balancing exchanger is connected to the low pressure by the inlet of the bottle 201. Similarly, the slide valve 52 is positioned to put the fourth channel 524 in communication with the low pressure path 25 522 so that the input channel 521 communicates with the third channel 523. Thus, the output of the condenser circuit of the exchanger 21 ECS communicates with the inlet of the evaporator circuit of the exchanger 23 evaporator. The unit controls the activation of the pump 310 of the DHW circuit 31 and the pump 330 of the cooling circuit 33. The operation of this mode corresponds to that of the simultaneous mode, with the difference that the condensation of the refrigerant s is performed in the exchanger 21 ECS, and not in the heat exchanger 22 which behaves like a simple pipe. As illustrated in Figure 8, another mode, called ECS mode alone, is activated by the control unit when it identifies a single need DHW DHW. This mode includes the following steps. The slide of each valve 51, 52 is in position ensuring the communication of the third channel 513, 523 with the low pressure path 512, 522, so that each input channel 511, 521 communicates with the fourth channel 514, 524.

Thus, the inlet of the condenser circuit of the exchanger 21 communicates with the discharge outlet of the compressor 200 and the outlet of the condenser circuit of the exchanger 21 communicates with the inlet of the condenser / evaporator circuit of the exchanger 25. balancing. The output of said condenser / evaporator circuit of the balancing exchanger 25 communicates with the inlet of the bottle 201.

The unit controls the activation of the pump 310 of the ECS circuit 31 and preferably the fan associated with the balancing exchanger. The operation of this mode is similar to that of the heating mode with the difference that the refrigerant condenses in the exchanger 21 ECS, 20 while the heat exchanger 22 behaves as a simple pipe. As mentioned above, the installation according to the invention makes it possible to defrost the balancing exchanger 25 in defrost mode (FIG. 9). For this purpose, the unit executes a mode, called the defrosting mode, which comprises the following steps. For each valve 51, 52, the fourth channel 514, 524 is put into communication with the low pressure pathway 512, 522 so that the inlet channel 511, 521 communicates with the third channel 513, 523. As illustrated in FIG. 2A, the solenoid valves 333, 334 of the cooling circuit 33 are controlled so as to prevent the circulation of fluid of the cooling circuit 33 by the second transfer circuit of the exchanger 24 subcooler and to allow the circulation of said fluid by the transfer circuit of the exchanger 23 evaporator. The unit controls the activation of the pump 330 of the cooling circuit 33. The unit controls the shutdown of the fan 250 associated with the balancing exchanger 25. The second transfer circuit of the exchanger 24 subcooler being by-passed, the hot fluid previously stored in the tank 33 during a heating mode, travels the transfer circuit of the exchanger 23 evaporator and gives up its heat the refrigerant circulating in the evaporator circuit of said exchanger 23 evaporator, which allows to vaporize and then pass through the balancing exchanger 25 and thus defrost its circuit. The energy stored in the coolant flask 331 can also be used in delayed time to vaporize the refrigerant in the exchanger 23 which condenses in the exchanger 21 or 22 during a simultaneous type mode or simultaneous DHW for which the pump 330 is turned on to use the energy stored in the balloon 331. When the balancing exchanger 25 operates either as a condenser or as an evaporator, the refrigerant flows through all the tubes of the exchanger balancing. As illustrated in FIG. 10, each flask 31, 32, 33 is equipped with a Tecs, Teec, Teef temperature probe disposed inside said flask. The compressor 200 is equipped with a BP pressure sensor input and an HP pressure sensor output. The refrigerant circuit preferably comprises a Teea temperature probe located at the inlet of the balancing exchanger and a Tcross temperature probe located on the outer surface of the condenser / evaporator circuit of the balancing exchanger. Said control unit 7 is configured to control the transition from one operating mode of the installation to another as a function of the measured pressure and temperature values and predefined threshold values.

In one of the applications of the invention, the heating, cooling and domestic hot water requirements of the building are determined by value comparison operations carried out using differential thermostats and comparators. As shown in Figure 11, the differential thermostats include a heating thermostat to define the need for heating, a cooling thermostat to define the need for cooling, and a hot water thermostat to define the need for water sanitary hot. CECS, CCH and CRAF are setpoint temperature values, and DIFECS, DIFCH and DIFRAF are temperature differential values. As illustrated in FIG. 12, when the difference between the dew point temperature of the refrigerant calculated from the pressure BP at the suction of the compressor, and the temperature Teea measured at the inlet of the exchanger 25. balancing exceeds a certain threshold, noted SDGIV, the defrost mode is engaged. The dew point temperature is determined from an equation with the input parameter of the compressor as the input parameter. When the surface Tcross temperature of the balancing exchanger is greater than a certain threshold SFDGIV, the defrosting phase is stopped. Figure 13 illustrates a tilt control logic in simultaneous ("simultaneous tilt") or heating ("tilt heating") mode. Failover in simultaneous mode during operation in heating mode is managed by another differential thermostat. CSR is a setpoint temperature value and DIFSR is a temperature differential value. By way of example, performance tests according to the EN14511 standard have been carried out on a prototype thermofridge pump according to the invention using propane as a refrigerant. The test results are presented below in connection with FIGS. 14 to 16. The performances are calculated from steady-state test reports. A 30 minute stabilization period precedes the one hour steady state acquisition period. The data acquisition step is 10 seconds. The consumption of the pumps and the fan is taken into account in the calculation of the Coefficient of Performance (COP) and the energy efficiency of cooling (EER) of the thermo-pump.

Figure 14 shows the coefficient of performance (COP) of the heat pump in heating mode as a function of the air temperature for a hot water production temperature of 35 ° C (curve "COP 35 ° C") and 45 ° C ("COP 45 ° C" curve). At a hot water production rate of 35 ° C, the heat output is 11 kW at -7 ° C outside air and 17.5 kW at 7 ° C. Figure 15 shows the cooling energy efficiency (EER) of the heat pump in cool mode for different air temperatures with a cold water production at 7 ° C ("EER SEF 7 ° C" curve) and 14 ° C (curve "EER SEF 14 ° C"). The cooling capacity delivered varies from 13.4 to 19 kW. Figure 16 shows the coefficient of performance (COP) of the thermo-pump in simultaneous mode as a function of the water temperature at the outlet of the heat exchanger and for a cold water production temperature of 7 ° C (curve "TFP SEF 7 ° C ") and 15 ° C (" TFP SEF 15 ° C "curve). These tests show that the heating capacity varies between 23 and 16 kW and the cooling capacity between 10 and 18 kW.

The present invention is not limited to the embodiments described and shown, but the skilled person will be able to make any variant

Claims (27)

REVENDICATIONS1. Refrigerant circuit (2) for an installation, called thermofridge pump (1), for heating and / or cooling fluids, comprising: - a compressor (200), - an exchanger (21, 22), called a condenser exchanger, comprising a condenser circuit, an exchanger (25), called a balancing exchanger, comprising a circuit referred to as a condenser / evaporator circuit capable of operating either as a condenser or an evaporator, and preferably a fan associated with said equilibrium exchanger, first link node (NL1) between a branch of the refrigerant circuit (2) provided with the condenser exchanger (21, 22) and a branch of the refrigerant circuit (2) provided with the balancing exchanger (25), said node linker being located on the outlet side of the exchanger (21, 22) condenser, - an exchanger (23), called evaporator exchanger, comprising an evaporator circuit, - a first device (51) for fluid management comprising four tracks, d have: a first channel, called an input channel (511), connected to the output of the compressor, a second channel, called a low-pressure path (512), a third channel connected to the exchanger (513); 25) on the opposite side to the first link node (NL1), and - a fourth path (514) connected to the input of said condenser exchanger; a second fluid management device (52) comprising four channels, of which: a first channel, called an input channel (521), connected to said first connection node (NL1), a second channel, called a low channel; pressure (522), - a third channel (523) connected to the inlet of the exchanger (23) evaporator, and- a fourth channel (524) connected to the exchanger (25) balancing, between the first of link node (NL1) and the condenser / evaporator circuit of the balancing exchanger (25); a first expander (203) located between the third channel (523) of the second fluid management device (52) and the evaporator exchanger (23), and a second expander (205) situated between the fourth channel (524); ) of the second fluid management device (52) and the balancing exchanger (25), the second channels (512, 522) of the management devices being connected (NL2) to a branch of the refrigerant circuit which extends between the evaporator circuit output of the evaporator exchanger (23) and the compressor inlet (200); each fluid management device (51, 52) being configured to selectively present a first configuration in which the input channel (511, 521) is communicated with the third channel (513, 523), the low-pressure channel ( 512, 522) being communicated with the fourth channel (514, 524), and a second configuration in which the input channel (511, 521) is in communication with the fourth channel (514, 524), the low pressure path (512, 522) being communicated with the third path (513, 523). 20 2. Refrigerant circuit (2) according to claim 1, characterized in that the refrigerant circuit also comprises an exchanger (24), called subcooler heat exchanger, which comprises a first heat transfer circuit arranged between the inlet channel ( 521) of the second management device (52) and the first link node (NL1), and preferably disposed between said input path (521) and a liquid bottle (202). 3. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said circuit comprises a nonreturn valve (CARI) 30 arranged between the outlet of the exchanger (23) evaporator and said connection (NL2) second channels (512, 522) management devices for preventing fluid from flowing from said fitting (NL2) to the evaporator exchanger (23). 4. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said circuit comprises a nonreturn valve (CAR2) arranged between the first connection node (NL1) and the condenser exchanger (21, 22). to prevent a flow of fluid from said first connecting node (NL1) to the condenser exchanger (21, 22). 5. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said refrigerant circuit (2) comprises a nonreturn valve (CAR3) arranged between, on the one hand, the first link node (NL1). and, on the other hand, a third node (NL3) connecting the second expander (205) and the balancing exchanger (25) to prevent fluid flow from said first link node (NL1) to the third node (NL3) link. 6. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said circuit comprises a nonreturn valve (CAR4) arranged between the fourth channel (524) of the second management device (52) and the second expander (205) to prevent a flow of fluid from the second expander (205) to the fourth channel (524) of the second management device. 7. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said first fluid management device (51) is a 4-way valve which comprises a member, called drawer, movable between two positions respectively corresponding to said first and second configurations of the first fluid management device. 8. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said second fluid management device (52) is a 4-way valve which comprises a member, called drawer, movable between two positions respectively corresponding to said first and second configurations of the second fluid management device. 9. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said circuit comprises an additional exchanger (22, 21), arranged in series with the condenser exchanger (21, 22), between said first node of link (NL1) and the fourth channel (514) of the first management device (51). 10. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said circuit comprises a reservoir (201), called anti-blow liquid bottle, positioned between the compressor (200) and the fitting (NL2) of second management device channels (51, 52). 11. Refrigerant circuit (2) according to one of the preceding claims, characterized in that said circuit comprises a reservoir, called the liquid bottle (202), and in that said input channel (521) of the second management device fluid (52) is connected to said first connecting node (NL1) via the liquid bottle (202). 12. Installation comprising a refrigerant circuit (2) according to one of the preceding claims, characterized in that, the condenser exchanger (21, 22) comprising a heat transfer circuit, said installation comprises a heating circuit (31). , 32) which comprises said transfer circuit of the condenser exchanger (21, 22), a circulation pump (310, 320), and preferably a fluid storage tank, referred to as a hot water tank; and in that, the evaporator exchanger (23) comprising a heat transfer circuit, said installation comprises a cooling circuit (33) which comprises said evaporator exchanger transfer circuit (23), a pump (330) circulation, and preferably a fluid storage tank, called balloon (331) of cold fluid. 13. Installation according to claim 12, the cooling circuit of which is in accordance with claim 9, characterized in that, the additional exchanger (22, 21) comprising a heat transfer circuit, said installation comprises an additional production circuit (32). , 31) of hot fluid which comprises said additional exchanger transfer circuit (22, 21), a circulation pump (320, 310), and preferably a fluid storage tank (321, 311), called a balloon hot water. 14. Installation according to claim 12 or 13, the refrigerant circuit of claim 2, characterized in that, the exchanger (24) subcooler comprising a second transfer circuit, said second transfer circuit of the exchanger (24) subcooler is mounted on the cooling circuit (33) bypassing the transfer circuit of the exchanger (23) evaporator. 15. Installation according to claim 14, characterized in that a first solenoid valve (333) is positioned between the inlet of the transfer circuit of the exchanger (23) evaporator and the connection of the inlet of the second transfer circuit of the exchanger (24) subcooler to the cooling circuit (33). 16. Installation according to claim 14 or 15, characterized in that a second solenoid valve (334) is positioned between the inlet of the second transfer circuit of the exchanger (24) subcooler and the connection of this inlet of the second transfer circuit of the exchanger (24) subcooler to the cooling circuit (33). 17. Installation according to one of claims 12 to 16, characterized in that it comprises a control unit (7) comprising control means for controlling the stopping and running of each of the pumps (310, 320, 330), independently of each other. 18. Installation according to one of claims 12 to 17, characterized in that it comprises a control unit (7) configured to execute a sequence of instructions, called heating mode, comprising the following steps: - for each of the first and second management devices (51, 52) communicating the fourth channel (514, 524) with the first channel (511, 521); - Activation of the pump (320) of the heating circuit (32), - preferably activation of the fan associated with the exchanger (25) balancing. 10 19. Installation according to one of claims 12 to 18, characterized in that it comprises a control unit (7) configured to execute a sequence of instructions, called simultaneous mode, comprising the following steps: - for the first management device (51), placing the first channel in communication with the fourth channel; for the second management device (52), placing the first channel in communication with the third channel; - Activation of the pump (320) of the heating circuit (32) and the pump (330) 20 of the cooling circuit (33). 20. Installation according to one of claims 12 to 19 taken in combination of claim 14, characterized in that it comprises a control unit (7) configured to execute a sequence of instructions, called storage mode of energy, comprising the following steps: in heating mode, activate the pump (330) of the cooling circuit and control the solenoid valves (333, 334) so as to circulate the cooling circuit fluid (33) through the second cooling circuit; transfer of the exchanger (24) subcooler, and the corresponding balloon (331). 30 21. Installation according to one of claims 12 to 20, characterized in that it comprises a control unit (7) configured to execute a sequence of instructions, called cooling mode, comprising the following steps: - for each management device (51, 52), placing the first channel in communication with the third channel; 5 - activation of the pump (330) of the cooling circuit (33), - preferably activation of the fan (250) associated with the balancing exchanger (25). 22. Installation according to one of claims 20 or 21, taken in combination 10 of claims 15 and 16, characterized in that the control unit (7) is configured to execute a sequence of instructions, called mode of use of the energy stored on the cooling circuit, which comprises the following steps: in deferred time with respect to the execution of the energy storage mode and in a mode of operation of the installation corresponding to the simultaneous mode or the cooling mode preferably without ventilation, activate the pump (330) of the cooling circuit and control the solenoid valves (333, 334) so as to circulate the hot fluid contained in the flask (331) of the cooling circuit (33) through the transfer circuit of the exchanger (23) evaporator. 20 23. Installation according to one of claims 12 to 22, characterized in that, said heating circuit (31) being a domestic hot water heating circuit, called ECS circuit (31), said installation comprises a control unit (7) configured to execute a sequence of instructions, called simultaneous ECS mode, comprising the following steps: for the first management device (51), putting the first channel in communication with the fourth channel; for the second management device (52), placing the first channel in communication with the third channel; 30 - activation of the pump (310) of the ECS circuit (31) and the pump (330) of the cooling circuit (33). 24. Installation according to one of claims 12 to 23, characterized in that, said heating circuit (31) being a domestic hot water heating circuit, called ECS circuit (31), said installation comprises a control unit (7) configured to execute a sequence of instructions, called ECS mode alone, comprising the following steps: - for each management device (51, 52), placing the first channel in communication with the fourth channel; - Activation of the pump (310) of the ECS circuit (31) and preferably the fan associated with the balancing exchanger. 25. Installation according to one of claims 12 to 24, characterized in that it comprises a control unit (7) configured to perform a sequence of instructions, called defrost mode, comprising the following steps: - for each device of management (51, 52), placing the first channel in communication with the third channel; the solenoid valves are controlled so as to prevent the circulation of fluid of the cooling circuit (33) by the second transfer circuit of the exchanger (24) subcooler and to allow the circulation of said fluid through the transfer circuit of the the exchanger (23) evaporator, - activation of the pump (330) of the cooling circuit (33), - preferably stop of the fan (250) associated with the exchanger (25) balancing 25 26. Installation according to one of claims 18 to 25, characterized in that each flask (311, 321, 331) is equipped with a sensor of a value representative of the temperature (Tecs, Teec, Teef) of the fluid contained inside said flask, in that the compressor is equipped with a sensor with a value representative of the pressure (BP) at the inlet and a sensor with a value representative of the outlet pressure (HP) in that the refrigerant circuit preferably comprises a sensor of a value representative of the temperature at the inlet of the balancing exchanger (25) and a sensor of a value representative of the temperature (Tcross) of the surface. external of the balancing exchanger (25), and in that said control unit (7) is configured to control the changeover from one operating mode of the installation to another depending on the measured values and predefined threshold values. 27. A method of heating and / or cooling fluids using an installation (1) according to one of claims 12 to 26. 10