EP2318783B1 - Reversible system for recovering thermal energy by sampling and transfer of calories from one or more media into one or more other such media - Google Patents

Description

The invention relates to a reversible recovery system by sampling and transfer of energy between at least two different media, for example between an external environment and a living environment or between a living environment and another living environment.

The caloric requirements in cold periods of a place of life, work or storage can be summed up in a quantity of calories devoted to heating. Other caloric needs are needed during the cold season and even outside of it, we can identify the production of domestic hot water that must be provided all year, the heating of a swimming pool or other needs in the industrial or tertiary field.

In air-conditioned premises, extraction of excess calories from the building must be ensured.

In conventional air conditioning systems, the calories extracted from the building are often dissipated outside the building and lost. The document WO 02/39033 A shows all the technical features of the preamble of claim 1.

Currently, building heating is provided by fuel combustion in boilers, by the use of solar thermal energy, by the use of joule effect with electric boilers or by the use of heat pumps drawing much of their energy on the outside air or a free water source.

The invention uses an innovative technology in the field of reversible heat pumps.

Heat pumps are refrigeration machines that transfer heat from one medium to another by using as a vehicle a refrigerant passing successively from a gaseous state to a liquid state and vice versa by the succession of compression and expansion phases.

As most systems are reversible, it is therefore possible to use these heat pumps for air conditioning.

• Radiateurs,
• Plancher chauffant/ rafraîchissant,
• ventilo-convecteurs,
• Caisson de traitement d'air.

The heat pumps are connected to different types of reversible or non-reversible terminals such as:

• radiators,
• Heated / refreshing floor,
• fan coils,
• Air treatment cabinet.

Heat pumps and other energy recovery systems are characterized by a performance index (COP) that indicates the performance energy efficiency of the installation, that always being greater than 1, the heat pumps thus produce more heat energy than they consume of electrical energy thanks to the energy drawn from the free recovery medium.

Technological advances in recent years have improved the efficiency of heat pumps due to improved components of heat pumps.

The invention proposes an improvement which is achieved by a new organization of the refrigerant circuit and the creation of components having new functions, the objective of the invention being to increase the efficiency and the reliability of the refrigeration system.

• au moins un compresseur principal (CP1) complété en cas de besoin d'un ou plusieurs autres compresseurs (CP2, CP3 ..),
• la présence d'un échangeur E4 pour la récupération ou l'évacuation des calories sur le milieu extérieur, l'échangeur E4 étant un échangeur à ailettes pour les pompes à chaleur de type AIR/EAU ou un échangeur à plaques, voir un échangeur multitubulaire ou coaxiale pour les pompes à chaleur EAU/ EAU,
• un échangeur Fluide/ Fluide E3 raccordé au point 6 au capillaire 1 de détente final et au réservoir R, au point 7 du détendeur thermostatique BI-FLUX à égalisation externe D1, au point 19 du capillaire 2 pour la limitation du débit massique sur cette branche, au point 10 l'admission des gaz froid provenant de V3 N°2, au point 11 l'aspiration des gaz surchauffés par le compresseur CP1, au point 12 l'aspiration des gaz surchauffés par le compresseur CP2 (Figures 9 et 10).

The innovation lies in the creation, presence and location in the installation of the following components:

• at least one main compressor (CP1) completed in case of need of one or more other compressors (CP2, CP3 ..),
• the presence of an exchanger E4 for the recovery or the evacuation of the calories on the external medium, the exchanger E4 being a finned exchanger for the AIR / WATER type heat pumps or a plate heat exchanger, see a multitubular exchanger or coaxial for WATER / WATER heat pumps,
• a fluid / fluid exchanger E3 connected to point 6 to the final expansion capillary 1 and to the reservoir R, at point 7 of the thermostatic expansion valve BI-FLUX with external equalization D1, at point 19 of the capillary 2 for the limitation of the mass flow rate on this branch at the point 10 the admission of the cold gases from V3 N ° 2, at point 11 the suction of superheated gases by the compressor CP1, at point 12 the suction of superheated gases by the compressor CP2 ( Figures 9 and 10 ).

The particularity of this exchanger E3 is to function as under cooler of the liquid line when it is supplied with high pressure fluid in the liquid state in its inner tube and also as superheater of the suction gases in its outer tube (FIGS. 1, 2, 8, 11, 12, 18).

In this case, from the organization of the fluid diagram, the refrigerant reservoir R contains a reserve of high pressure fluid in the liquid state.

The other particularity of the fluid / fluid exchanger E3 is that it functions as a degasser when it is supplied with low pressure fluid in the liquid state in its inner tube and also as a superheater for the suction gases in its external tube (FIGS. No. 4, 5, 6, 7, 14, 15, 16, 17).

In this case, due to the organization of the flow diagram, the Refrigerant reservoir R contains a reserve of low pressure fluid in the liquid state with a variable ratio of fluid to the gaseous state.

The presence of the three-way valves and the three exchangers E1, E2 and E4, allow the desuperheater and condenser functions for the exchanger E2, condenser and evaporator for the exchangers E1 and E4.

The presence and location of the valves VEM1 and VEM2 allow the operation of the exchanger E2 as a condenser with either the exchanger E4 as an evaporator or the exchanger E1 as an evaporator.

The presence and location of the regulator D2 increases the efficiency of the refrigeration system by allowing a different condensing pressure between the compressor CP1 and the compressor CP2 in the case of a heat production on the exchanger E2 and on the exchanger E1 with the valve V3 N ° 1 closed and the two compressors CP1 and CP2 in functions (Figure N ° 18).

The arrangement of the various valves and expansion valves allows the possibility of managing in an isolated way the different heat exchangers and thus of being able to couple them in different combinations, this organization also allows the easy integration of one or more additional exchangers (Example in Figure N ° 8 ).

The invention makes it possible to oversize the energy recovery battery on the external medium and to increase its efficiency (E4 Figures 1 to 18 ).

The invention also allows the installation of a non-reversible heat exchanger which can be used in the desuperheater mode of the discharge gases of the compressor (s), or can be used in condenser mode for a total restitution of the energy of the refrigerant condensed in that or be used in partial condensation mode for partial recovery of the calories of the refrigerant flowing through this exchanger.

This exchanger is called E2 and is connected to a hydraulic circuit for a heat energy distribution to one or more media in calorie demand, this exchanger is not reversible.

The invention also allows the installation of a reversible heat exchanger which can be used in condenser mode of the discharge gas or compressors for a total return of the energy of the refrigerant condensed in it, or be used in evaporator for a total evacuation of the cooling energy of the refrigerant flowing through this exchanger. This exchanger is called E1 and is connected to a hydraulic circuit for a distribution of heat or cooling energy to one or more media. requests for calories or frigories.

The invention also allows the heat exchanger E1 to recover the heat energy not absorbed by the exchanger E2 when it is in desuperheater mode or if E2 is in partial condensation mode.

By the presence of these two heat exchangers E1 and E2 and without the addition of additional regulations or other mixing valves on the hydraulic circuits, we therefore have available a heat pump equipped with two hydraulic circuits.

A non-reversible hydraulic circuit E2 for the distribution of the calories drawn from the external exchanger E4 or from the exchanger E1 operating in evaporator mode.

A reversible hydraulic circuit E1 for the distribution of calories drawn on the exchanger E4 and also the same circuit for the distribution of chilled water and a heat removal to the exchanger E2, E4 or E2 + E4.

The invention thus allows the energy transfer function which means the possibility of recovering calories on the exchanger E1 in evaporator mode for the production of chilled water on the hydraulic circuit E1 and at the same time the return of these calories for the heating of the hydraulic circuit E2 via the exchanger E2 in condenser mode or desuperheater mode. Either for an electrical consumption of 1kw, a refrigerated production of 3.5 KW and heat of 4.5 KW with a single machine.

This function is useful and very economical when a building is air conditioned and there is a simultaneous demand for heat production for the production of domestic hot water or the heating of a swimming pool.

To allow these functions and improve the energy efficiency of the whole, some refrigeration components were created and others were used in an innovative refrigeration scheme.

Among the elements created, we have an exchanger fluid / fluid E 3. It is composed of an internal cylinder which opens only on three nipples N ° 6, N ° 7 and N ° 19 (FIGURES N ° 9 and N ° 10 ), and an outer cylinder which opens on three nozzles No. 10, No. 11 and No. 12 (FIGURES No. 9 and No. 10).

No flow of fluid passes from the inner cylinder to the outer cylinder or from the outer cylinder to the inner cylinder.

The fact that the inner cylinder has been placed in the outer cylinder serves only to effect a heat exchange between the cold refrigerant passing through the outer tube before being sucked by the compressor or compressors and the hotter refrigerant through the tube internal.

The heat exchange is through the wall of the inner tube in the section in contact with the refrigerant contained in the outer tube.

The purpose of the small section tube at point 19 is to evacuate a part of the fluid in the gaseous state created by the expansion valve by the expander D1 when the latter is passed from point 8 to point 7.

In this case, the inner cylinder is fed with low pressure liquid refrigerant with a minority ratio of fluid in the gaseous state.

The purpose of the tube of small section at point 19 is to reduce the ratio of fluid in the gaseous state by evacuating it from the inner tube at point 19 towards point 20. The function of capillary 2 is to limit the flow rate of point 19 to point 20 so as not to discharge fluid in the liquid state.

The pressure drops of this capillary must be calculated so that the volume of refrigerant in the gaseous state discharged from point 19 to point 20 is less than the volume of gaseous refrigerant generated by the expander D1 when this it is crossed by the fluid from point 8 to point 7.

Thus, we will have a fluid with a ratio of refrigerant gas phase lower at point 6 when E1 is in evaporator mode, which will increase the efficiency of the exchanger E1 due to a better liquid supply.

In the case where the expander D1 is traversed by the refrigerant from point 7 to point 8 (FIGURES Nos. 1, 2 and 8), the fluid / fluid exchanger E3 is an innovative cooling unit whose function is to cool the high pressure liquid and superheat the suction gases when the exchanger E1 is in condenser mode.

Since the diameter of the inner cylinder is at least 4 times greater than the liquid line at points 6 and 7 (FIGURES No. 9 and No. 10), the high-pressure fluid in gaseous form will inevitably be recovered largely at the top of the cylinder. internal and part of this fluid will be condensed by the frigories recovered on the suction gas passing through the outer cylinder.

The absence of a four-way valve, the presence and placement of the two-way and three-way valves, the placement of the two regulators, the presence and placement of a capillary and the placement of the two regulators make an innovative flow diagram.

To better understand the operation of this system, it is necessary to refer to Figures 1 to 18 which show the state and the path of the refrigerant according to the requirements of frigories or calories of the different exchangers.

• Les conduites frigorifiques isolées ayant un débit de fluide frigorigène nul, sont représentées par des petits points.
• Les conduites frigorifiques traversées par un débit de fluide frigorigène haute pression et à l'état gazeux sont représentées par des petits tirets.
• Les conduites frigorifiques traversées par un débit de fluide frigorigène haute pression et à l'état liquide sont représentées par des traits pleins.
• Les conduites frigorifiques traversées par un débit de fluide frigorigène basse pression et à l'état liquide sont représentées par des doubles traits.
• Les conduites frigorifiques traversées par un débit de fluide frigorigène basse pression et à l'état gazeux sont représentées par des traits mixtes.
• Les électrovannes sont représentées par deux triangles opposés qui sont noirs si l'électrovanne est fermée et blanc si l'électrovanne est ouverte.
• Les détendeurs sont représentés par deux triangles opposés qui sont noirs si le détendeur est fermé et blancs si le détendeur est ouvert et passant.
• Les vannes trois voies sont représentées par trois triangles opposés qui sont

noirs si la vanne trois voies est fermée et blancs si la vanne trois voies est ouverte en indiquant quels sont les branches passantes.For FIGS. 1 to 8 and 11 to 18, the lines were shown as follows:

• Insulated refrigerant lines with zero refrigerant flow are represented by small dots.
• Refrigerant pipes crossed by a flow of high pressure refrigerant and in the gaseous state are represented by small dashes.
• Refrigerant pipes with a flow of high-pressure refrigerant and in the liquid state are represented by solid lines.
• Refrigerant pipes with a flow of low pressure refrigerant and in the liquid state are shown in double lines.
• Refrigerant pipes crossed by a flow of low pressure refrigerant and in the gaseous state are represented by mixed lines.
• The solenoid valves are represented by two opposite triangles which are black if the solenoid valve is closed and white if the solenoid valve is open.
• Regulators are represented by two opposing triangles that are black if the regulator is closed and white if the regulator is open and running.
• The three-way valves are represented by three opposite triangles which are

black if the three-way valve is closed and white if the three-way valve is open indicating which branches are passing.

• Les circulateurs P1 et P2 sont représentés par un triangle dans un cercle, triangle orienté dans le sens d'écoulement d'eau et compris dans un cercle :
  • Si le triangle est blanc, cela signifie que le circulateur est en fonction et que l'eau traverse l'échangeur raccordé à celui-ci.
  • Si le triangle est noir, cela signifie que le circulateur est hors fonction et que l'échangeur raccordé à celui-ci n'est pas alimenté en eau.

The plate heat exchangers are supplied with water by circulators that pulsate the water through them.

• Circulators P1 and P2 are represented by a triangle in a circle, triangle oriented in the direction of flow of water and included in a circle:
  • If the triangle is white, it means that the circulator is running and the water is flowing through the heat exchanger connected to it.
  • If the triangle is black, it means that the circulator is off and that the exchanger connected to it is not supplied with water.

In FIG. 1 is shown the operation of the system with one compressor out of two in function and a heat production ensured on the exchanger E1 and E2. The compressor CP1 compresses and represses the refrigerant towards the point N ° 1.

For example, we can have a reference temperature at point No. 1 of 90 ° C.

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

For example, we can have a water circuit temperature at the entrance 45 ° C and 48 ° C output.

The refrigerant leaving the exchanger E2 at point 2 is therefore colder than at point N ° 1.

For example, we can have a reference temperature at point N ° 2 of 45 ° C

The refrigerant passes through the valve V3 No. 1, the point No. 3, the point No. 4 and the point No. 20 to then enter the exchanger E1.

The water passing through the exchanger E1 being colder than the fluid, the calories leave the fluid for the water circuit E1.

The refrigerant condenses in exchanger E1 and leaves it in high pressure liquid form at point No. 5.

For example, we can have a condensing temperature of 36 ° C, a water circuit temperature E1 at the inlet of 33 ° C and an outlet of 35 ° C.

The fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.

For example, in point 6, the fluid temperature is 35 ° C.

The high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.

For example, the temperature at point 7 will be 30 ° C or sub-cooling of 5 ° C thanks to the exchanger E3.

The fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8. For example, the temperature of the fluid at point 8 is -15 ° C.

The fluid passes through the exchanger E4 which is ventilated by the fan VENT.

The fluid boils while evacuating the frigories on the through air E4.

The refrigerant leaves E4 at point 9 in low pressure gaseous form. For example, the fluid temperature at point 9 will be -10 ° C.

The fluid passes through V3 N ° 2 for point 10.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.

For example, the fluid temperature at point 11 is -5 ° C.

FIG. 2 shows the operation of the system with two compressors in operation and a heat production provided on the exchanger E1 and E2.

The presence of the exchanger E3 in this case is innovative because it is placed on a high pressure liquid section of the refrigerant circuit which is not always supplied with high pressure liquid in its inner tube.

The design and the innovative location of the E3 exchanger allow this body to perform different functions according to the calorie and frigory needs of the different exchangers installed.

In FIG. 1, the exchanger E3 serves as superheater for the suction gases, undercooler for the high pressure liquid before the expander D1 and makes it possible to store a large quantity of fluid in the liquid state in its inner tube.

The superheating of the suction gases and the subcooling of the liquid before the expansion valve D1 makes it possible to increase the percentage of fluid in the liquid state in the exchanger E4 and thus to increase the average coefficient of conductivity of the exchanger E4, a gain for the overall energy efficiency.

• Augmentation du débit massique de fluide du fait de la mise en service du compresseur N°2.
• Compression et refoulement du fluide au point 13 et mélange de ce flux avec le flux du premier compresseur au point N°4.

The operation described in FIG. 2 is close to the operation described in FIG. 1, the differences are described below:

• Increase in the mass flow of fluid due to the commissioning of compressor No. 2.
• Compression and discharge of the fluid at point 13 and mixing of this flow with the flow of the first compressor at point N ° 4.

For example, the temperature of the high pressure fluid at point 13 is 90 ° C.

Due to the mixing of the gas flow from compressor No. 1 having a temperature of 45 ° C and the gas flow from compressor No. 2 having a temperature of 90 ° C the mixture of the two streams will have a temperature of 67.5 ° C if the mass flow rate of the two compressors is identical.

In this case, the calories of the compressor No. 2 will be evacuated exclusively by the exchanger E1 in favor of the water circuit E1.

For example, because of the increase in heat dissipated power on the exchanger E1, the condensing temperature increases to 40 ° C and the water of the hydraulic circuit No. 1 enters 33 ° This spell to 38 ° C

The fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.

For example, in point 6, the fluid temperature is 40 ° C

The high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.

For example, the temperature at point 7 will be 35 ° C, a subcooling of 5 ° C thanks to the exchanger E3.

The fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8.

For example, the fluid temperature at point 8 is -18 ° C.

The fluid passes through the exchanger E4 which is ventilated by the fan VENT.

The fluid boils while evacuating the frigories on the through air E4. The refrigerant leaves E4 at point 9 in low pressure gaseous form.

For example, the fluid temperature at point 9 will be -13 ° C.

The fluid passes through V3 N ° 2 for point 10. The fluid enters the outer tube of exchanger E3 and is superheated in contact with the inner tube of exchanger E3. The fluid leaves the exchanger E3 at point 11 and 12 and is sucked by the compressors CP1 and CP2.

For example, the fluid temperature at point 12 is -8 ° C.

The functions of the exchanger E3 are identical for the figures 1 and 2 .

In FIG. 3 is shown the operation of the system with one compressor out of two in function and a heat production ensured on the exchanger E2.

The compressor CP1 compresses and represses the refrigerant towards the point N ° 1.

For example, we can have a reference temperature at point N ° 1 of 110 ° C

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories. The fluid passing through the exchanger E2 is at high pressure and at high temperature.

The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2. In this case, the fluid is condensed to 100% in the exchanger E2.

For example, we can have an inlet water temperature of 60 ° C and an outlet temperature of 65 ° C with a condensing temperature of 65 ° C.

The refrigerant leaving the exchanger E2 at point 2 is condensed and is colder than at point N ° 1.

For example, we can have a reference temperature at point N ° 2 of 64 ° C

With the valve V3 No.1 closed, the refrigerant passes through the point 15, the filter F, the point 16, the valve VEM2, the expander D2.

The fluid passing through the expander D2 is expanded and is therefore in low pressure liquid form with a minority gas phase ratio at point 18. For example, the temperature of the fluid at point 18 is -15 ° C.

The fluid passes through the exchanger E4 which is ventilated by the fan VENT.

The fluid boils while evacuating the frigories on the through air E4. The refrigerant leaves E4 at point 9 in low pressure gaseous form.

For example, the fluid temperature at point 9 will be -10 ° C.

The fluid passes through V3 N ° 2 for point 10.

The fluid enters the outer tube of the exchanger E3, because the flow of refrigerant in the inner cylinder of the exchanger E3 is zero, no overheating of the suction gas is performed.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1. In this case, the temperature of the refrigerant at point No. 11 is the same as at point No. 10.

The presence of the exchanger E3 in this case is innovative because it is placed on a low pressure liquid section of the refrigerant circuit which is not always supplied with low pressure liquid in its inner tube. The design and the innovative location of the E3 exchanger allow this body to perform different functions according to the calorie and frigory needs of the different exchangers installed.

In FIG. 3, the exchanger E3 has its internal tube cooled by the suction gases passing through its external tube, this enables it to store at 100% of its capacities a large quantity of fluid in the liquid state in its tube. internal.

This function is important because the exchanger E1, not being supplied with fluid, is empty of all its fluid in the liquid state, it is therefore useful to be able to store this fluid in the volume of the inner cylinder of the exchanger E3 which remains cold to him.

If this function were not ensured, the exchanger E2 would have a reduced efficiency due to a too large amount of fluid in the liquid state in the refrigerant circuit and in the same exchanger E2.

FIG. 4 shows the operation of the system with one compressor out of two in operation and a heat production ensured on the exchanger E2 and a refrigeration production ensured on the exchanger E1.

This mode of function is called energy transfer.

The compressor CP1 compresses and represses the refrigerant towards the point N ° 1. For example, we can have a reference temperature at point No. 1 of 90 ° C.

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

In this case, the fluid is condensed to 100% in the exchanger E2. For example, we can have a water circuit temperature at the inlet of 60 ° C and output of 65 ° C with a temperature of condensation of 65 ° C.

The refrigerant leaving the exchanger E2 at point 2 is condensed and is colder than at point N ° 1.

For example, we can have a reference temperature at point No. 2 of 64 ° C.

With the valve V3 No.1 closed, the refrigerant passes through the point 15, the filter F, the point 16, the open valve VEM1, the point 17, the point 8 and the expander D1. The fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.

For example, the fluid temperature at point 7 is + 10 ° C.

The fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.

The ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.

Part of this volume of low pressure refrigerant is then discharged through the degassing tube at point 19 which is a tapping at the top of the inner tube of the fluid / fluid exchanger E3.

The low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor No. 1.

All the low-pressure refrigerant in the liquid state and the remainder of the low-pressure refrigerant in the gaseous state not discharged by the degassing tube at point 19 exit at the point 6 of the internal tube of the exchanger E3 with a temperature equal to 10 ° C and with a low pressure fluid ratio in the gaseous state lower than point 7.

The fluid passes through the capillary 1 which has a loss of pressure equivalent to a temperature drop of 9 ° C.

The fluid being expanded by the capillary passes through point 5 with a temperature of +1 ° C.

The fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.

The refrigerant leaves E1 in low pressure gaseous form.

The refrigerant exits the exchanger E1, passes through point 20, V3 N ° 2 and point 10.

For example, the fluid temperature at point 10 will be + 5 ° C.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.

For example, the fluid temperature at point 11 is + 7 ° C

The presence of the exchanger E3 in this case is innovative because it is placed on a low pressure liquid section of the refrigerant circuit which is not always supplied with low pressure liquid in its inner tube.

The design and the innovative location of the E3 exchanger allow this body to perform different functions according to the calorie and frigory needs of the different exchangers installed.

In FIG. 4, the exchanger E3 has its internal tube cooled by the suction gases passing through its external tube, the inner tube being fed with a low-pressure liquid with a percentage of fluid in the gaseous state, it is advisable to minimize the amount of fluid in the gaseous state, the exchanger E3 allows this function by discharging a portion of this gas via the tube 19 and condensing another part of this gas due to the cooling caused by the cold gases through the outer tube of the exchanger E3.

If this function were not ensured, the exchanger E1 would have a reduced efficiency due to a smaller amount of fluid in the liquid state in the refrigerant circuit at point 5 and in the exchanger E1 in evaporator mode. this would decrease the average coefficient of conductivity in the exchanger E1 and thus the energy efficiency of the assembly.

FIG. 5 shows the operation of the system with one compressor out of two in operation, a heat production ensured on the exchanger E2 and E4 and a refrigeration production ensured on the exchanger E1.

This function mode is called partial energy transfer.

The compressor CP1 compresses and represses the refrigerant towards the point N ° 1. For example, we can have a reference temperature at point No. 1 of 80 ° C.

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

In this case, the fluid is desuperheated or partially condensed in the exchanger E2.

For example, in the case of using E2 as a desuperheater without any condensation, we can have a water circuit temperature E2 at the inlet of 75 ° C and output of 77 ° C with a condensation temperature of 50 ° C.

The refrigerant leaving the exchanger E2 at point 2 is desuperheated and in the high pressure gas state.

For example, we can have a reference temperature at point No. 2 of 75 ° C.

The refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 or it is condensed to 100%.

To do this, the fan VENT is in operation for the cooling of the exchanger E4.

In this case, the heat dissipation is done on the exchanger E2 in favor of the water circuit E2 and on the exchanger E4 to evacuate excess heat energy to the outside.

This function is useful for the storage of domestic hot water with a temperature higher than 65 ° C for the elimination of bacteria in summer. The fluid exits the exchanger E4 at point 8, through the expander D1.

The fluid passing through the expander D1 is expanded and is therefore in low pressure liquid form with a minority gas phase ratio at point 7. For example, the temperature of the fluid at point 7 is + 10 ° C. The fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.

The ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.

Part of this volume of low pressure refrigerant is then discharged through the degassing tube at point 19 which is a tapping at the top of the inner tube of the fluid / fluid exchanger E3.

The gaseous low-pressure refrigerant then passes through the capillary 2, the non-return valve C2, the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor N ° 1 ;

All the low-pressure refrigerant in the liquid state and the remainder of the low-pressure refrigerant in the gaseous state not discharged by the degassing tube at point 19 exit at the point 6 of the internal tube of the exchanger E3 with a temperature equal to 10 ° C and with a low pressure fluid ratio in the gaseous state lower than point 7.

The fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C

The fluid being expanded by the capillary passes through point 5 with a temperature equal to +1 ° C.

The fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.

The refrigerant leaves E1 in low pressure gaseous form. The refrigerant exits the exchanger E1, passes through point 20, V3 N ° 2 and point 10.

For example, the fluid temperature at point 10 will be + 5 ° C.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.

For example, the fluid temperature at point 11 is + 7 ° C.

The operation of the exchanger E3 in this case is identical to the previous case of the figure 4 .

In FIG. 6 is represented the operation of the system with two compressors out of two in function, a heat production ensured on the exchanger E4 for defrosting and a refrigeration production ensured on the exchanger E1.

This function mode is called the defrost mode.

The defrosting of the external battery is used to remove the ice that closes and isolates the outer coil battery which recovers the heat energy from the outside air.

The compressor CP1 compresses and represses the refrigerant towards the point N ° 1. For example, we can have a reference temperature at point No. 1 of 80 ° C.

The fluid passes through the exchanger E2.

The circulator P2 is stopped in order not to transmit the calories to the water circuit E2. The refrigerant leaving the exchanger E2 at point 2 is therefore in the gaseous state at high pressure and at the same temperature as at point 1.

The refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 or it is condensed to 100%.

The VENT fan is off to conserve all the heat energy of the refrigerant for defrosting the battery.

The fluid exits the exchanger E4 at point 8, through the expander D1.

The fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.

For example, the fluid temperature at point 7 is + 10 ° C.

The fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.

The ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.

Part of this volume of low pressure refrigerant is then discharged through the degassing tube at point 19 which is a tapping at the top of the inner tube of the fluid / fluid exchanger E3.

The low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor No. 1.

All the low-pressure refrigerant in the liquid state and the remainder of the low-pressure refrigerant in the gaseous state not discharged by the degassing tube at point 19 exit at the point 6 of the internal tube of the exchanger E3 with a temperature equal to 10 ° C and with a low pressure fluid ratio in the gaseous state lower than point 7.

The fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C.

The fluid being expanded by the capillary passes through point 5 with a temperature of +1 ° C.

The fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.

The refrigerant leaves E1 in low pressure gaseous form.

The refrigerant exits the exchanger E1, passes through point 20, V3 N ° 2 and point 10.

For example, the fluid temperature at point 10 will be + 5 ° C.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.

For example, the fluid temperature at point 11 is + 7 ° C.

The compressor CP2 is activated to reduce the defrost duration by increasing the defrosting power by a level equal to the power consumption of the compressor CP2.

Compressor CP2 delivers the refrigerant to point 13.

The refrigerant passes point 4, the three-way valve No. 2, the point 10, the exchanger E3 and is sucked by the compressor CP2 after point 13.

On this path, no expansion valve is installed, the discharge gases of the compressor CP2 are low pressure and in the gaseous state.

The gas thus conveyed, was responsible for the heat energy consumed by the compressor No. 2 and allows to superheat the mixed suction gases of the two compressors in the outer tube of the fluid / fluid exchanger E3.

Thus we increase the temperature of the gas stream at point 11 and thus also the discharge temperature of CP1 at point 1.

This has the consequence of increasing the defrosting power by proposing a mixed defrosting system by cycle inversion and also by hot gas.

The operation of the exchanger E3 in this case is identical to the previous case of the figure 4 and 5 .

FIG. 7 shows the operation of the system with one of two compressors in operation, a heat production provided on the exchanger E4 for evacuating the calories outside the building and a refrigerating production ensured on the exchanger E1.

This function mode is called simple chilled water production mode.

The compressor CP1 compresses and represses the refrigerant towards the point N ° 1. For example, we can have a reference temperature at point N ° 1 of 80 ° C

The fluid passes through the exchanger E2.

In this case, we consider that the water circuit 2 has no need for calories and therefore the circulator P2 is stopped in order not to transmit the calories to the water circuit E2.

The refrigerant leaving the exchanger E2 at point 2 is therefore in the gaseous state at high pressure and at the same temperature as at point 1.

The refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 where it is condensed to 100%.

The VENT fan is turned on to cool the E4 outer fin exchanger.

The fluid exits the exchanger E4 at point 8, through the expander D1.

The fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7. For example, the temperature of the fluid at point 7 is + 10 ° C. The fluid enters the cylinder internal fluid / fluid E3 exchanger in low pressure liquid state and at a temperature of 10 ° C with a variable ratio of low pressure fluid in the gaseous state.

The ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.

Part of this volume of low pressure refrigerant is then discharged through the degassing tube at point 19 which is a tapping at the top of the inner tube of the fluid / fluid exchanger E3.

The gaseous low-pressure refrigerant then passes through the capillary 2, the non-return valve C2, the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor N ° 1 ;

All the low-pressure refrigerant in the liquid state and the remainder of the low-pressure refrigerant in the gaseous state not discharged by the degassing tube at point 19 exit at the point 6 of the internal tube of the exchanger E3 with a temperature equal to 10 ° C and with a low pressure fluid ratio in the gaseous state lower than point 7.

The fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C.

The fluid being expanded by the capillary passes through point 5 with a temperature of +1 ° C.

The fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.

The refrigerant leaves E1 in low pressure gaseous form.

The refrigerant exits the exchanger E1, passes through point 20, V3 N ° 2 and point 10.

For example, the fluid temperature at point 10 will be + 5 ° C.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.

For example, the fluid temperature at point 11 is + 7 ° C.

The operation of the exchanger E3 in this case is identical to the previous case of the figure 4 , 5 and 6 .

In FIG. 8 is shown the operation of the system with two compressors out of two in function and a heat production ensured on the exchanger E1 and E2.

The peculiarity of the figure 8 is to represent the addition of an additional exchanger E5 supplied with water by an additional water circuit which would serve as an example of recovering calories on the extraction of air from a building.

The compressor CP1 compresses and represses the refrigerant towards the point N ° 1. For example, we can have a reference temperature at point N ° 1 of 90 ° C

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

For example, we can have an inlet water temperature of 45 ° C and an outlet temperature of 48 ° C.

The refrigerant leaving the exchanger E2 at point 2 is therefore colder than at point N ° 1.

For example, we can have a reference temperature at point N ° 2 of 45 ° C

The refrigerant passes through the valve V3 N ° 1, the point N ° 3, the point N ° 4 and N ° 20 to then enter the exchanger E1.

The water passing through the exchanger E1 being colder than the fluid, the calories leave the fluid for the water circuit E1.

The refrigerant condenses in exchanger E1 and leaves it in high pressure liquid form at point No. 5.

For example, we can have a condensing temperature of 36 ° C, a water circuit temperature E1 at the inlet of 33 ° C and an outlet of 35 ° C.

The fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.

For example, in point 6, the fluid temperature is 35 ° C.

The high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.

For example, the temperature at point 7 will be 30 ° C or sub-cooling of 5 ° C thanks to the exchanger E3.

The fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8. For example, the temperature of the fluid at point 8 is -15 ° C.

The fluid passes through the exchanger E4 which is ventilated by the fan VENT.

The fluid boils while evacuating the frigories on the through air E4.

The refrigerant leaves E4 at point 9 in low pressure gaseous form.

Upstream of the regulator D1 at point 7, a branch derives a portion of the fluid in the high pressure liquid state to the expander D3. The fluid passes through the expansion valve D3 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase.

For example, the fluid temperature at point 8 is +1 ° C.

The fluid passes through the exchanger which is supplied with water by the circulator P3.

For example, the feed water of the E5 exchanger has a temperature + 12 ° C inlet temperature and + 7 ° C outlet temperature.

The low pressure refrigerant boils and exits in the gaseous state of the exchanger 6 and then passes through the regulation valve P.

The control valve P is an automatic constant pressure valve which maintains the pressure of the refrigerant in the exchanger E5 at a minimum equivalent value of 0 ° C so that the evaporation temperature is higher than the ice setting temperature. of the E3 water circuit.

For example, we will consider that the evaporation temperature in exchanger E5 is + 1 ° C and that the temperature of the refrigerant gas passing through the constant pressure valve has a temperature of + 10 ° C and a 100% gaseous state. .

The gas flows from exchanger E5 and exchanger E4 mix at point 9.

For example, the fluid temperature at point 9 will be -5 ° C.

The fluid passes through V3 N ° 2 for point 10.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and 12, it is sucked by the compressors CP1 and CP2.

For example, the fluid temperature at point 11 and 12 is + 1 ° C.

The compressor CP2 draws the low-pressure gas at point 12 and discharges at point 13 the high-pressure gaseous fluid.

FIG. 9 explains the operation of the fluid / fluid exchanger E3 corresponding to the figures 1 , 2 and 8 .

At point 10 between a flow of low pressure refrigerant in the gaseous and cold state in the outer cylinder of the exchanger E3.

The temperature of this fluid can be, for example, at a temperature of -10 ° C.

This flow of cold fluid in the gaseous state is in contact with the outer wall of the inner tube of the fluid / fluid exchanger E3.

The inner tube being fed with high pressure fluid in the liquid state and at a temperature, for example, 60 ° C, the flow of low pressure refrigerant gas from the point 10 and out at point 11 to be sucked by the compressor N ° 1 and the point 12 to be sucked by the compressor No. 2, is heated by the outer wall of the inner tube of the exchanger E3.

For example, the temperature at point 11 and 12 may be 10 ° C higher than point 10.

We thus generate an overheating of the suction gases between the point 10 and 11 as well as between point 10 and 12 when the compressor 2 is in operation. Conversely, a high-pressure fluid in the liquid state which enters the inner tube of the exchanger E3 is cooled by the wall of the inner tube in contact with the cold gases of the outer tube.

The diameter of the inner tube must be at least 5 times greater than the diameter of the connections 6 and 7 so that the flow of the tube 6 does not pass directly to the tube 7. By the heat exchange at E3, the fluid temperature at point 6 is higher than the temperature of the high-pressure liquid refrigerant exiting at point 7.

We thus generate an under cooling of the liquid between the point 6 and 7.

The stitching at point 19 has a zero flow because it leads to point 20 and the pressure at point 20 is equivalent to that at point 19. In Figure No. 10 is explained the operation of the exchanger Fluid / E3 fluid corresponding to figures4 , 5 , 6 and 7 .

At point 10 between a flow of low pressure refrigerant in the gaseous and cold state in the outer cylinder of the exchanger E3.

The temperature of this fluid may be, for example, at a temperature of + 6 ° C.

This flow of cold fluid in the gaseous state is in contact with the outer wall of the inner tube of the fluid / fluid exchanger E3.

The inner tube being supplied at point 7 with low pressure fluid in the liquid state and at a temperature of, for example, + 10 ° C., the flow of low pressure refrigerant gas from point 10 and exiting at point 11 to be sucked by the compressor No. 1 and the point 12 to be sucked by the compressor No. 2, is heated by the outer wall of the inner tube of the exchanger E3.

For example, the temperature at point 11 and 12 may be 2 ° C higher than point 10.

We thus generate an overheating of the suction gases between the point 10 and 11 as well as between the point 10 and 12 when the compressor 2 is in operation.

Conversely, the low-pressure liquid in the liquid state which enters the inner tube of the exchanger E3 is cooled by the wall of the inner tube in contact with the cold gases of the outer tube.

The diameter of the inner tube must be at least 5 times greater than the diameter of the connections 7 and 6 so that the flow of the tube 7 does not pass directly to the tube 6. The low pressure liquid that enters the inner tube of the exchanger E3 is in the liquid state with a low ratio in the gaseous state of the fact relaxation in D1.

The heat exchange in E3 will have the effect of cooling the inner tube and thus condense a small portion of the low pressure fluid in the gaseous state present at the top of the inner tube.

Another portion of gaseous fluid at the top of the inner tube will be evacuated by the stitching 19.

Thanks to the presence of the capillary 1, the exchanger E1 in evaporator mode and the point 20, are supplied with fluid having a pressure lower than that at point 19.

There will therefore be a gas flow between point 19 to point 20 because the pressure at point 19 is greater than point 20.

The flow of gas will be limited by the capillary 2 which will be calibrated so as not to be able to evacuate the entire gas bag at the top of the inner tube of the exchanger E3.

It would be detrimental to the system that low pressure refrigerant in the liquid state passes through the capillary 2 following the evacuation of all the fluid in the gaseous state.

For high power installations, the capillary can be replaced by a thermostatic expansion valve with an overheating set to 5 ° C.

By this innovative operation, the fluid ratio in the liquid state at point 6 is greater than the liquid ratio present at point 7.

The symbol named R is a refrigerant reservoir.

It compensates for the amount of fluid required for the correct operation of the system depending on the different functions of the exchangers, the external conditions and the different start temperatures on the water circuits.

There is a simplified version of this technology, this version is particularly suitable for single-compressor machines or machines with at least two compressors but with a discharge pipe of compressor No. 2 which joins the discharge pipe of compressor No. 1 in point 1 instead of joining in point 4 as indicated on the Figures 1 to 8 .

In addition to this change in the discharge, the regulator D2 is eliminated and the pipe passing at point 17 leads to point 6 instead of reaching point 8 as indicated in Figures 1 to 8 .

The representation of this is done on the Figures 11 to 17 .

In FIG. 11, the path of the fluid is identical to that of FIG.
In FIG. 11 is shown the operation of the system with a compressor on two in function and a heat production ensured on the exchanger E1 and E2. The compressor CP1 compresses and represses the refrigerant towards the point N ° 1.

For example, we can have a reference temperature at point No. 1 of 90 ° C.

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

For example, we can have an inlet water temperature of 45 ° C and an outlet temperature of 48 ° C.

The refrigerant leaving the exchanger E2 at point 2 is therefore colder than at point N ° 1.

For example, we can have a reference temperature at point N ° 2 of 44 ° C

The refrigerant passes through the valve V3 No. 1, the point No. 3, the point No. 4 and the point No. 20 to then enter the exchanger E1.

The water passing through the exchanger E1 being colder than the fluid, the calories leave the fluid for the water circuit E1.

The refrigerant condenses in exchanger E1 and leaves it in high pressure liquid form at point No. 5.

For example, we can have a condensing temperature of 36 ° C, a water circuit temperature E1 at the inlet of 33 ° C and at the outlet of 35 ° C.

The fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.

For example, in point 6, the fluid temperature is 35 ° C.

The high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.

For example, the temperature at point 7 will be 30 ° C or sub-cooling of 5 ° C thanks to the exchanger E3.

The fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8.

For example, the fluid temperature at point 8 is -15 ° C.

The fluid passes through the exchanger E4 which is ventilated by the fan VENT.

The fluid boils while evacuating the frigories on the through air E4.

The refrigerant leaves E4 at point 9 in gaseous form pressure. For example, the fluid temperature at point 9 will be -10 ° C. The fluid passes through V3 N ° 2 for point 10.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1. For example, the fluid temperature at point 11 is -5 ° C.

The presence of the exchanger E3 in this case is innovative because it is placed on a high pressure liquid section of the refrigerant circuit which is not always supplied with high pressure liquid in its inner tube.

The innovative design and location of the E3 exchanger allows this unit to have different functions depending on the calorie and frigory needs of the different heat exchangers installed.

In FIG. 11, the exchanger E3 serves as a superheater for the suction gases, a subcooler for a high-pressure liquid before the expander D1 and makes it possible to store a large quantity of fluid in the liquid state in its inner tube.

The superheating of the suction gases and the subcooling of the liquid before the expansion valve D1 makes it possible to increase the percentage of fluid in the liquid state in the exchanger E4 and thus to increase the average conductivity coefficient of the exchanger E4, a gain for the energy efficiency of the whole.

In FIG. 12, the function of the exchangers E1, E2 and E4 is identical to the function noted in FIG. 2, but the path of the fluid is different. FIG. 12 shows the operation of the system with two compressors in operation and a heat production provided on the exchanger E1 and E2.

The operation described in FIG. 12 is close to the operation described in FIG. 11, the differences are described below:
Increase in the mass flow of fluid due to the commissioning of compressor No. 2.

Compression and repression of the fluid at point 1 by the compressor CP1. Compression and discharge of the fluid at point 13 by the compressor CP2. Mixing of these two streams point No. 1.

In this case, the calories of the compressors No. 1 and No. 2 will be evacuated by the exchanger E1 and E2 in favor of the water circuit E1 and E2.

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high pressure temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

For example, we can have an inlet water temperature of 45 ° C and an outlet temperature of 48 ° C.

The refrigerant leaving the exchanger E2 at point 2 is therefore colder than at point N ° 1.

For example, we can have a reference temperature at point N ° 2 of 45 ° C

The refrigerant passes through the valve V3 No. 1, the point No. 3, the point No. 4 and the point No. 20 to then enter the exchanger E1.

The water passing through the exchanger E1 being colder than the fluid, the calories leave the fluid for the water circuit E1.

The refrigerant condenses in exchanger E1 and leaves it in high pressure liquid form at point No. 5.

For example, we can have a condensing temperature of 36 ° C, a water circuit temperature E1 at the inlet of 33 ° C and an outlet of 35 ° C. The fluid passes through the nonreturn valve C1, point 6 and enters the inner cylinder of the fluid / fluid exchanger E3.

For example, in point 6, the fluid temperature is 35 ° C.

The high pressure condensed fluid is cooled in exchanger E3 and exits at point 7.

For example, the temperature at point 7 will be 30 ° C or sub-cooling of 5 ° C thanks to the exchanger E3.

The fluid passes through the expansion valve D1 where it is expanded and thus in low pressure liquid form with a minority ratio in the gas phase at point 8.

For example, the fluid temperature at point 8 is -15 ° C.

The fluid passes through the exchanger E4 which is ventilated by the fan VENT.

The fluid boils while evacuating the frigories on the through air E4.

The refrigerant leaves E4 at point 9 in low pressure gaseous form.

For example, the fluid temperature at point 9 will be -10 ° C.

The fluid passes through V3 N ° 2 for point 10.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1. For example, the fluid temperature at point 11 is -5 ° C.

The fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP2. The functions of the exchanger E3 are identical for the figures 11 and 12 .

For example, the fluid temperature at point 12 is -5 ° C,

In FIG. 13, the function of the exchangers E1, E2 and E4 is identical to the function noted in FIG. 3, but the path of the fluid is different.

In FIG. 13 is shown the operation of the system with one compressor out of two in function and a heat production ensured on the exchanger E2. The compressor CP1 compresses and represses the refrigerant towards the point N ° 1.

For example, we can have a reference temperature at point N ° 1 of 110 ° C.

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

In this case, the fluid is condensed to 100% in the exchanger E2.

For example, we can have a water circuit temperature at the inlet of 60 ° This output t of 65 ° C with a condensing temperature of 65 ° C The refrigerant leaving the exchanger E2 at point 2 is therefore condensed and is colder than at point N ° 1.

For example, we can have a reference temperature at point N ° 2 of 64 ° C

With the valve V3 No.1 closed, the refrigerant passes through the point 15, the filter F, the point 16, the valve VEM2, the point 17, the point 6, the exchanger E3, the point 7, the expander D1.

The fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gaseous phase at point 8. For example, the temperature of the fluid at point 8 is -15 ° C. The fluid passes through the exchanger E4 which is ventilated by the fan VENT.

The fluid boils while evacuating the frigories on the through air E4. The refrigerant leaves E4 at point 9 in low pressure gaseous form.

For example, the fluid temperature at point 9 will be -10 ° C.

The fluid passes through V3 N ° 2 for point 10.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1. For example, the fluid temperature at point 11 is -5 ° C.

The fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP2. For example, the fluid temperature at point 12 is -5 ° C.

This function is important because the exchanger E1, not being supplied with fluid,
is empty of all its fluid in the liquid state, so it is useful to store this fluid in the volume of the inner cylinder of the exchanger E3 remains cold.

If this function were not ensured, the exchanger E2 would have a reduced efficiency due to a too large amount of fluid in the liquid state in the refrigerant circuit and in the same exchanger E2.

In FIG. 14, the function of the exchangers E1, E2 and E4 is identical to the function identified in FIG. 4, but the path of the fluid is different.

FIG. 14 shows the operation of the system with two compressors out of two in function and a heat production ensured on the exchanger E2 and a refrigeration production ensured on the exchanger E1.

This mode of function is called energy transfer.

The compressor CP1 and the compressor CP2 compress and discharge the refrigerant towards the point N ° 1 and N ° 13.

The junction of the discharge pipe of compressor No. 2 is at point 1. For example, we can have a reference temperature at point No. 1 of 90 ° C.

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

In this case, the fluid is condensed to 100% in the exchanger E2. For example, we can have an inlet water temperature of 60 ° C and an outlet temperature of 65 ° C with a condensing temperature of 65 ° C.

The refrigerant leaving the exchanger E2 at point 2 is condensed and is colder than at point N ° 1.

For example, we can have a reference temperature at point No. 2 of 64 ° C.

With the valve V3 No.1 closed, the refrigerant passes through the point 15, the filter F, the point 16, the open valve VEM1, the point 18, the point 8 and the expander D1.

The fluid passing through the expansion valve D1 is expanded and is thus in low pressure liquid form with a minority ratio in the gas phase in point 7.

For example, the fluid temperature at point 7 is + 10 ° C.

The fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.

The ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.

Part of this volume of low pressure refrigerant is then discharged through the degassing tube at point 19 which is a tapping at the top of the inner tube of the fluid / fluid exchanger E3.

The low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor No. 1.

All the low-pressure refrigerant in the liquid state and the remainder of the low-pressure refrigerant in the gaseous state not discharged by the degassing tube at point 19 exit at the point 6 of the internal tube of the exchanger E3 with a temperature equal to 10 ° C and with a low pressure fluid ratio in the gaseous state lower than point 7.

The fluid passes through the capillary 1 which has a loss of pressure equivalent to a temperature drop of 9 ° C.

The fluid being expanded by the capillary 1 passes through the point 5 with a temperature equal to + 1 ° C.

The fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.

The refrigerant leaves E1 in low pressure gaseous form. The refrigerant exits the exchanger E1, passes through point 20, V3 N ° 2 and point 10.

For example, the fluid temperature at point 10 will be + 5 ° C.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1. For example, the fluid temperature at point 11 is + 7 ° C.

The fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP2. For example, the fluid temperature at point 12 is + 7 ° C.

In FIG. 15, the function of the exchangers E1, E2 and E4 is identical to the function recorded in FIG. 5, but the path of the fluid is different.

The presence of the exchanger E3 in this case is innovative because it is placed on a low pressure liquid section of the refrigerant circuit which is not always supplied with low pressure liquid in its tube internal.

The design and the innovative location of the E3 exchanger allow this body to perform different functions according to the calorie and frigory needs of the different exchangers installed.

In FIG. 14, the exchanger E3 has its internal tube cooled by the suction gases passing through its external tube, the inner tube being supplied with a low-pressure liquid with a percentage of fluid in the gaseous state, it is advisable to minimize the amount of fluid in the gaseous state, the exchanger E3 allows this function by discharging a portion of this gas via the tube 19 and condensing another part of this gas due to the cooling caused by the cold gases through the outer tube of the exchanger E3.

If this function were not ensured, the exchanger E1 would have a reduced efficiency due to a smaller amount of fluid in the liquid state in the refrigerant circuit at point 5 and in the exchanger E1 in evaporator mode. this would decrease the average coefficient of conductivity in the exchanger E1 and thus the energy efficiency of the assembly.

FIG. 15 shows the operation of the system with two compressors out of two in operation, a heat production ensured on the exchanger E2 and E4 and a refrigeration production ensured on the exchanger E1.

This function mode is called partial energy transfer.

The compressor CP1 and the compressor CP2 compress and discharge the refrigerant towards the points N ° 1 and N ° 13.

The junction of the discharge pipe of compressor N ° 2 is at point 1. For example, we can have a reference temperature at point N ° 1 of 80 ° C

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2.

In this case, the fluid is desuperheated or partially condensed in the exchanger E2.

For example, in the case of using E2 as a desuperheater without any condensation, we can have a water circuit temperature E2 at the inlet of 75 ° C and an outlet temperature of 77 ° C with a condensation temperature of 50 ° C.

The refrigerant leaving the exchanger E2 at point 2 is therefore desuperheated and in the high pressure gaseous state.

For example, we can have a reference temperature at point No. 2 of 75 ° C.

The refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 where it is condensed to 100%.

To do this, the fan VENT is in operation for the cooling of the exchanger E4.

In this case, the heat evacuation oe done on the exchanger E2 in favor of the water circuit E2 and the exchanger E4 to evacuate excess heat energy to the outside.

This function is useful for the storage of domestic hot water with a temperature higher than 65 ° C for the elimination of bacteria in summer.

The fluid exits the exchanger E4 at point 8, through the expander D1.

The fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority gas phase ratio at point 7. For example, the temperature of the fluid at point 7 is + 10 ° C.

The fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.

The ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.

Part of this volume of low pressure refrigerant is then discharged through the degassing tube at point 19 which is a tapping at the top of the inner tube of the fluid / fluid exchanger E3.

The low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and 12 is sucked by the compressor CP1 and CP2 .

All the low-pressure refrigerant in the liquid state and the remainder of the low-pressure refrigerant in the gaseous state not discharged by the degassing tube at point 19 exit at the point 6 of the internal tube of the exchanger E3 with a temperature equal to 10 ° C and with a low pressure fluid ratio in the gaseous state lower than point 7.

The fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C.

The fluid being expanded by the capillary passes through point 5 with a temperature of +1 ° C.

The fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.

The refrigerant leaves E1 in low pressure gaseous form. The refrigerant exits the exchanger E1, crosses the point 20, V3 N ° 2 and the point 10.

For example, the fluid temperature at point 10 will be + 5 ° C.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.

For example, the fluid temperature at point 11 is + 7 ° C.

The fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP2.

For example, the fluid temperature at point 12 is + 7 ° C

The operation of the exchanger E3 in this case is identical to the previous case of the figure 14 .

In FIG. 16, the function of the exchangers E1, E2 and E4 is identical to the function recorded in FIG. 6, but the path of the fluid is different.

In FIG. 16 is shown the operation of the system with one compressor out of two in operation, a heat production ensured on the exchanger E4 for defrosting and a refrigeration production ensured on the exchanger E1.

This function mode is called the defrost mode.

The defrosting of the external battery is used to remove the ice that closes and isolates the outer coil battery which recovers the heat energy from the outside air. The compressor CP1 compresses and represses the refrigerant towards the point N ° 1.

For example, we can have a reference temperature at point No. 1 of 80 ° C.

The fluid passes through the exchanger E2.

The circulator P2 is stopped in order not to transmit the calories to the water circuit E2. The refrigerant leaving the exchanger E2 at point 2 is therefore in the gaseous state at high pressure and at the same temperature as at point 1.

The refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 where it is condensed to 100%.

The VENT fan is off to conserve all the heat energy of the refrigerant for defrosting the battery.

The fluid exits the exchanger E4 at point 8, through the expander D1. The fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.

For example, the fluid temperature at point 7 is + 10 ° C,

The fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.

The ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.

Part of this volume of low pressure refrigerant is then discharged through the degassing tube at point 19 which is a stitching at the top of the inner tube of the fluid / fluid exchanger E3.

The low-pressure refrigerant in the gaseous state then passes through the capillary 2, the non-return valve C2 the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor No. 1.

All the low-pressure refrigerant in the liquid state and the remainder of the low-pressure refrigerant in the gaseous state not discharged by the degassing tube at point 19 exit at the point 6 of the internal tube of the exchanger E3 with a temperature equal to 10 ° C and with a low pressure fluid ratio in the gaseous state lower than point 7.

The fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C

The fluid being expanded by the capillary 1 passes through point 5 with a temperature equal to +1 ° C.

The fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1. The refrigerant leaves E1 in low pressure gaseous form. The refrigerant exits the exchanger E1, passes through point 20, V3 N ° 2 and point 10.

For example, the fluid temperature at point 10 will be + 5 ° C.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.

The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.

For example, the fluid temperature at point 11 is + 7 ° C

The operation of the exchanger E3 in this case is identical to the previous case of the figure 14 and 15 .

In FIG. 17, the function of the exchangers E1, E2 and E4 is identical to the function identified in FIG. 7, but the path of the fluid is different.

In figure N ° 17 is represented the operation of the system with two compressors out of two in function, a heat production ensured on the exchanger E4 to evacuate the calories outside the building and a refrigerating production ensured on the exchanger E1.

This function mode is called simple chilled water production mode.

The compressor CP1 and the compressor CP2 compress and discharge the refrigerant towards the point N ° 1 and N ° 13.

The junction of the discharge pipe of compressor N ° 2 is at point 1. For example, we can have a reference temperature at point N ° 1 of 80 ° C.

The fluid passes through the exchanger E2.

In this case, we consider that the water circuit E2 has no need for calories and therefore the circulator P2 is stopped in order not to transmit the calories to the water circuit E2.

The refrigerant leaving the exchanger E2 at point 2 is therefore in the gaseous state at high pressure and at the same temperature as at point 1.

The refrigerant passes through the valve V3 No. 1, the point 14, the point 9 enters the exchanger E4 or it is condensed to 100%.

The VENT fan is on to cool the E4 outer fin exchanger. The fluid exits the exchanger E4 at point 8, through the expander D1. The fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority ratio in the gas phase at point 7.

For example, the fluid temperature at point 7 is + 10 ° C

The fluid enters the inner cylinder of the fluid / fluid exchanger E3 in the low pressure liquid state and at a temperature of 10 ° C. with a variable ratio of low pressure fluid to the gaseous state.

The ratio of low pressure fluid in the gaseous state is found by gravity in the upper part of the inner tube of the exchanger E3.

Part of this volume of low pressure refrigerant is then discharged through the degassing tube at point 19 which is a stitching at the top of the inner tube of the fluid / fluid exchanger E3.

The gaseous low-pressure refrigerant then passes through the capillary 2, the non-return valve C2, the point 20, the valve V3 N ° 2, the point 10, the point 11 and is sucked by the compressor N ° 1 ;

All the low-pressure refrigerant in the liquid state and the remainder of the low-pressure refrigerant in the gaseous state not discharged by the degassing tube at point 19 exit at the point 6 of the internal tube of the exchanger E3 with a temperature equal to 10 ° C and with a low pressure fluid ratio in the gaseous state lower than point 7.

The fluid passes through the capillary which has a loss of pressure equivalent to a temperature drop of 9 ° C.

The fluid being expanded by the capillary passes through point 5 with a temperature equal to +1 ° C,

The fluid enters the exchanger E1 where it boils, evacuating the frigories on the water circuit E1.

The refrigerant leaves E1 in low pressure gaseous form.

The refrigerant exits the exchanger E1, passes through point 20, V3 N ° 2 and point 10.

For example, the fluid temperature at point 10 will be + 5 ° C.

The fluid enters the outer tube of the exchanger E3 and is superheated in contact with the inner tube of the exchanger E3.The fluid leaves the exchanger E3 at point 11 and is sucked by the compressor CP1.

For example, the fluid temperature at point 11 is + 7 ° C.

The fluid leaves the exchanger E3 at point 12 and is sucked by the compressor CP1.

For example, the fluid temperature at point 12 is + 7 ° C.

The operation of the exchanger E3 in this case is identical to the previous case of the figure 14 , 15 and 16 .

In FIG. 18 is represented the operation of the system with two compressors out of two in function and a heat production ensured on the exchanger E2 and on the exchanger E1.

The figure 18 is not part of the simplifying system and thus integrates the regulator D2 in its fluidic scheme.

The compressor CP1 compresses and represses the refrigerant towards the point N ° 1.

For example, we can have a reference temperature at point N ° 1 of 110 ° C.

The fluid passes through the exchanger E2 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E2 is at high pressure and at high temperature. The water passing through the exchanger E2 being colder than the fluid, the calories leave the fluid for the water circuit E2. In this case, the fluid is condensed to 100% in the exchanger E2.

For example, we can have an inlet water temperature of 60 ° C and an outlet temperature of 65 ° C with a condensing temperature of 65 ° C.

The refrigerant leaving the exchanger E2 at point 2 is condensed and is colder than at point N ° 1.

For example, we can have a reference temperature at point No. 2 of 64 ° C.

With the valve V3 No.1 closed, the refrigerant passes through point 15, the filter F, point 16, valve VEM2, regulator D2.

The fluid passing through the expander D2 is expanded and is therefore low pressure liquid form with a minority gas phase ratio at point 18.

For example, the fluid temperature at point 18 is -15 ° C

The compressor CP2 compresses and represses the refrigerant towards the point N ° 13. For example, we can have a reference temperature at point N ° 13 of 60 ° C

The fluid passes through point 4, point 20 and enters the exchanger E1 which is a plate exchanger irrigated with water by the circulator P2 for the distribution of calories.

The fluid passing through the exchanger E1 is at high pressure and at high temperature. The water passing through the exchanger E1 being colder than the fluid, the calories leave the fluid for the water circuit E1.

In this case, the fluid is condensed to 100% in the exchanger E1. For example, we can have an inlet water temperature of 30 ° C and output of 35 ° C with a condensing temperature of 38 ° C

The refrigerant leaving the exchanger E1 at point 5 is condensed and is colder than at point N ° 20.

For example, we can have a reference temperature at point No. 2 of 37 ° C.

The refrigerant from point 5 passes through the non-return valve C1, point 6, enters the inner tube of the fluid / fluid exchanger E3, passes through point 7, passes through and is expanded by the expansion valve D1.

The fluid passing through the expansion valve D1 is expanded and is therefore in low pressure liquid form with a minority gas phase ratio at point 8.

For example, the fluid temperature at point 8 is -15 ° C.

The flow of refrigerant from point 8 and point 18 are mixed at the inlet of exchanger E4. The fluid passes through the exchanger E4 which is ventilated by the fan VENT. The fluid boils, evacuating the cold air through the air E4. The refrigerant leaves the exchanger E4 at point 9 in gaseous form low pressure.

For example, the fluid temperature at point 9 will be -10 ° C.

The fluid passes through V3 N ° 2 for point 10.

The fluid enters the outer tube of the exchanger E3 and is overheated in contact with the inner tube of the exchanger E3.The fluid leaves the exchanger E3 at the points 11 and 12 and is sucked by the compressors CP1 and CP2.

In the case of Figure No. 18, we have a different condensing temperature between the exchanger E1 and E2 and therefore the compressor CP1 and CP2.

The lower the condensing temperature and the higher the energy efficiency of the compressor, this possibility is therefore beneficial to the overall efficiency of the installation.

This possibility of operation is particular to the principle in its fluid diagram with the integration of the regulator D2 ( Figures 1 to 8 and Figure 18 ).

The simplified version of the fluidic diagram that eliminates the regulator D2 does not allow a different condensing temperature between E1 and E2, but it allows a reduction in the cost of production ( Figures 11 to 17 ).

Claims (18)

1. Reversible system for recovering energy by the sampling and transfer thereof between at least two different media, for example between an external medium and a living medium or between a living medium and another living medium, using a refrigerant as a transfer fluid, successively passing from a gaseous state to a liquid state and conversely by successive compression and expansion phases, characterised in that said system comprises:

   - a reversible Refrigerant/Water heat exchanger (E1) for producing chilled water or hot water, on a water circuit (E1),

   - a non-reversible Refrigerant/Water heat exchanger (E2) for producing hot water on a water circuit (E2),

   - at least one main compressor (GP1) connected to a Refrigerant/Refrigerant heat exchanger (E3) at a point (11) and to the non-reversible heat exchanger (E2) at a point (1),

   - a capillary tube (CAPILLARY TUBE 2) for limiting the rate of the refrigerant flow in the gaseous state originating from the heat exchanger (E3),

   - a heat exchanger (E4) for recovering or removing calories from the external medium, whereby the heat exchanger (E4) is a fin tube heat exchanger for a heat pump of the AIR/WATER type or a plate heat exchanger, or even a shell and tube heat exchanger or a coaxial heat exchanger for a WATER/WATER type heat pump,

   - a bi-flow thermostatic expansion valve with external equalisation (D1) for expanding the refrigerant from a tap (7) to a point (8) when the heat exchanger (E4) is in evaporator mode and for expanding the refrigerant from the point (8) to the tap (7) when the heat exchanger (E1) is in evaporator mode,

   - a capillary tube (CAPILLARY TUBE 1) for ensuring the final expansion of the refrigerant in the expanded liquid state by said thermostatic expansion valve (D1),

   - the Refrigerant/Refrigerant heat exchanger (E3) being connected, via a tap (6) to the final expansion capillary tube (CAPILLARY TUBE 1), to a check valve (C1), to a tank (R), via the tap (7) to said bi-flow thermostatic expansion valve with external equalisation (D1), via a tap (19) to said capillary tube (CAPILLARY TUBE 2) for limiting the mass flow rate on said branch, via a tap (10) at the intake of the cold gases originating from a valve (V3 No. 2), via a tap (11) at the suction of the gases superheated by the compressor (CP1), and potentially via a tap (12) at the suction of the gases superheated by a compressor (CP2),

   - said Refrigerant/Refrigerant heat exchanger (E3) having two modes of operation:

   - when said heat exchanger (E3) is fed at the tap (7) with low-pressure refrigerant in the liquid state with a low ratio of refrigerant in the gaseous state, said heat exchanger condenses a portion of said refrigerant in the gaseous state and removes, via the tap (19), another portion of said refrigerant in the gaseous state so as to increase the ratio of liquid at the tap (6) of the heat exchanger (E3),

   - when said heat exchanger (E3) is fed at the tap (6) with high-pressure refrigerant in the liquid state, said heat exchanger (E3) operates as a subcooler for said high-pressure refrigerant in the liquid state and as a superheater for the suction gases between the tap (10) and at least the tap (11),

   - said refrigerant tank (R) containing a refrigerant reserve,

   - said check valve (C1) allowing the refrigerant to be diverted from a point (5) to the tap (6) when the heat exchanger (E1) is used as a condenser,

   - a check valve (C2) for preventing any return of the refrigerant from a point (20) to the tap (19) when the heat exchanger (E1) is used as a condenser,

   - a motorised three-way valve (V3 No. 1) for allowing operation of the heat exchanger (E2) in desuperheater mode, total condenser mode or partial condenser mode, and for allowing the diversion of the refrigerant flow to the heat exchanger (E1) or to the heat exchanger (E4),

   - a motorised three-way valve (V3 No. 2) for allowing operation of the heat exchanger (E1) in evaporator mode or for allowing operation of the heat exchanger (E4) in evaporator mode,

   - a solenoid valve (VEM1) through which the refrigerant passes from a point (16) to a point (17) when the heat exchanger (E1) is in evaporator mode and when the heat exchanger (E2) is in condenser mode,

   - a solenoid valve (VEM2) through which the refrigerant passes from the point (16) to a point (18) when the heat exchanger (E4) is in evaporator mode and when the heat exchanger (E2) is in condenser mode, and a unidirectional expansion valve (D2) for expanding the refrigerant between the point (16) and the point (18) when the heat exchanger (E4) is in evaporator mode and when the heat exchanger (E2) is in condenser mode.
2. System according to claim 1, characterised in that it further comprises either one or more secondary compressors (CP) connected to said heat exchanger (E3) at the tap (12) and to said non-reversible heat exchanger (E2) at the point (1) via a manifold (13), or one or more secondary compressors (CS) connected to said heat exchanger (E3) at the tap (12) and to said reversible heat exchanger (E1) at the point (20) via manifolds (13, 4).
3. System according to either claim 1 or claim 2, characterised by the connection of the suction of the one or more compressors to the Refrigerant/Refrigerant heat exchanger (E3), which ensures, among other functions, the superheating of the suction gases before the compression thereof.
4. System according to claim 1, characterised by the presence of a bi-flow thermostatic expansion valve (D1) coupled to a Refrigerant/Refrigerant heat exchanger (E3) which ensures, among other functions, the subcooling of the high-pressure liquid at the point (7) when the refrigerant passes through the expansion valve (D1).
5. System according to claim 1, characterised by the presence of a bi-flow thermostatic expansion valve (D1) coupled to the Refrigerant/Refrigerant heat exchanger (E3) which ensures, among other functions, the partial degassing of the low-pressure liquid, via the tube and the capillary tube (CAPILLARY TUBE 2), upstream of the capillary tube (CAPILLARY TUBE 1) for final expansion when the refrigerant passes through the expansion valve (D1).
6. System according to claim 1, characterised by the presence of a tank supplied with high-pressure liquid when the heat exchanger (E1) is in condenser mode and supplied with low-pressure liquid with a minority percentage of refrigerant in the gaseous state when the heat exchanger (E1) is in evaporator mode.
7. System according to claim 1, characterised by the presence of a three-way valve (V3 No. 1) for supplying high-pressure refrigerant in the gaseous state or in the liquid state or in a mixed liquid and gaseous state, to the external heat exchanger (E4) or to the heat exchanger (E1).
8. System according to claim 1, characterised by the presence of a three-way valve (V3 No. 2) for supplying low-pressure refrigerant in the gaseous state to the Refrigerant/Refrigerant heat exchanger (E3) and for selecting the heat exchanger (E4) or (E1) in evaporator mode.
9. System according to claim 1, characterised by the presence of the Refrigerant/Water heat exchanger (E2) for desuperheating or for the full or partial condensation of the discharge gases of the one or more compressors connected to the point (1) for producing hot water on the circuit (E2) .
10. System according to claim 1, characterised by the presence of the Refrigerant/Water heat exchanger (E1) for the full condensation or full evaporation of the refrigerant passing therethrough in order to produce hot water or chilled water on the water circuit (E1).
11. System according to claim 1, characterised by the presence of the Refrigerant/Air heat exchanger (E4) for the full condensation or full evaporation of the refrigerant passing therethrough in order to recover or remove calories from an external medium.
12. System according to claim 1, characterised by the presence of the capillary tube (CAPILLARY TUBE 1) for the final expansion of the partially-degassed refrigerant originating from the heat exchanger (E3) when (E1) is in evaporator mode.
13. System according to claim 1, characterised by the presence of the capillary tube (CAPILLARY TUBE 2) for limiting the rate of the refrigerant flow originating from the heat exchanger (E3) in gaseous form when (E1) is in evaporator mode.
14. System according to claim 1, characterised by the presence of the check valve (C1) for diverting the refrigerant between the point (5) and the tap (6) when the heat exchanger (E1) is in condenser mode.
15. System according to claim 1, characterised by the presence of the check valve (C2) for preventing circulation of the refrigerant from the point (20) to the point (19) when the heat exchanger (E1) is in condenser mode.
16. System according to claim 1, characterised by the presence of the solenoid valve (VEM1) for allowing passage of the refrigerant from the point (16) to the point (17) when the heat exchanger (E2) is in condenser mode and when the heat exchanger (E1) is in evaporator mode.
17. System according to claim 1, characterised by the presence of the solenoid valve (VEM2) for allowing passage of the refrigerant from the point (16) to the point (18) when the heat exchanger (E2) is in condenser mode and when the heat exchanger (E4) is in evaporator mode.
18. System according to claim 1, characterised by the presence of the unidirectional thermostatic expansion valve (D2) for the expansion and supply of expanded liquid to the heat exchanger (E4) when said heat exchanger is in evaporator mode and when the heat exchanger (E2) is in condenser mode.

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