FR3079920A1 - THERMODYNAMIC TYPE THERMOFRIGOPOMPE MACHINE AND METHOD OF OPERATION - Google Patents

Abstract

Thermodynamic machine comprising a refrigerant circuit passing through a first heat exchanger (2), a second heat exchanger (3) and a third heat exchanger (4) for circulating a refrigerant. A compressor (5, 6) is mounted between an outlet of the second heat exchanger (3) and an inlet of the first heat exchanger (2). A first pressure reducer (7) is mounted between an outlet of the first heat exchanger (2) and an inlet of the second heat exchanger (3). Four connecting nodes (15, 16, 17, 18) connect different inputs and outputs to define several channels for circulation of the refrigerant. First and second switching devices (10, 11, 12, 13, 19, 20) selectively define a channel mounting the third heat exchanger (4) in parallel with the first heat exchanger (2) or mounting the third heat exchanger (4) in parallel with the second heat exchanger (3).   

Description

THERMODYNAMIC MACHINE OF THE THERMOFRIGOPOMP TYPE AND OPERATING METHOD

Technical field of the invention

The invention relates to installations for the production of heat and cooling energy by thermodynamic cycle, to meet the heating, cooling and domestic hot water production needs, in the building and industrial sectors.

More particularly, the invention relates to thermodynamic machines called thermofrigopompes, which simultaneously ensure the supply of heat energy to a consumer of heat energy on the one hand and the supply of refrigeration energy to a consumer of cooling energy d 'somewhere else.

State of the art

The consumer of heat energy, also called heat consumer, is defined as one or more elements absorbing heat through a heat transfer fluid. The calorific power transferred to the consumer is directly proportional to the difference between the temperature of the heat transfer fluid towards the heat consumer and the temperature of the heat transfer fluid when the heat consumer returns. In order to adapt the heat capacity transferred to the heat consumer to the required value, that is to say the heat demand, the temperature of the heat transfer fluid is generally regulated in the direction of the heat consumer.

The consumer of refrigerating energy, also called cold consumer, is defined as one or more elements absorbing refrigerating energy through a heat transfer fluid. The cooling capacity transferred to the consumer is directly proportional to the difference between the temperature of the heat transfer fluid towards the cold consumer and the temperature of the heat transfer fluid when the cold consumer returns. Generally, in order to adapt the cooling power transferred to the cold consumer to the required value, that is to say the cooling demand, the temperature of the heat transfer fluid is regulated at the outset towards the cold consumer.

Heat pumps produce heat energy which is transferred outside through a heat exchanger called condenser exchanger, at the primary of which the condensation of a refrigerant takes place, and at the secondary of which circulates the heat transfer fluid carrying heat energy to the hot consumer. The heat pumps produce simultaneously a cooling energy which is transferred to the outside through a heat exchanger called an evaporator exchanger, at the primary of which the evaporation of a refrigerant takes place, and at the secondary of which circulates the heat transfer fluid carrying the refrigerating energy towards the cold consumer.

By the very principle of operation of the machine, based on the thermodynamic cycle of a refrigerant, the ratio between the heating and cooling powers produced by the machine at a given time, essentially depends on the type of refrigerant used and the values of temperature of condensation and evaporation of the refrigerant at the instant considered. These temperature values are directly linked to the temperature values of the heat transfer fluid at the outlet of the secondary of the condenser exchanger and at the outlet of the secondary of the evaporator exchanger. The ratio between the heating and cooling capacities produced by the machine at a given time cannot therefore be freely adjusted.

On the other hand, the ratio between the calorific power required by the consumer of heat and the refrigerating power required by the consumer of cold, is completely independent of the thermodynamic machine, can vary at any moment, and can moreover take n ' no matter what value.

A heat pump is unable to adapt both the heat output and the cooling capacity produced at all times to the heating and cooling capacity values required by the heat consumer and the cold consumer respectively. Either the machine adapts the heating power produced to the heating power required by the heat consumer, and in this case the cooling power produced by the machine does not correspond to the power level required by the cold consumer. Either the machine adapts the cooling power produced to the cooling power required by the cold consumer, and in this case the heat power produced by the machine does not correspond to the power level required by the hot consumer.

There are then two modes of operation of the machine, depending on the respective level of the demand for heat energy and the demand for cooling energy.

When the ratio between the calorific and refrigerating powers called up by the consumers is greater than the ratio between the calorific and refrigerating powers produced by the machine, the machine can adapt the calorific power produced to the calorific power required by the heat consumer. However, it produces a cooling power greater than the cooling power required by the cold consumer. In this case the machine operates in the mode called priority heat production, heat production then being called priority production and refrigeration production then being called non-priority production.

Conversely, when the ratio between the heating and cooling powers demanded by consumers is lower than the ratio between the heating and cooling powers produced by the machine, the machine can adapt the cooling power produced to the cooling power required by the cold consumer. However, it produces a calorific power higher than the calorific power required by the heat consumer. In this case the machine operates in the mode called priority refrigeration production, the refrigeration production then being called priority production and the heat production then being called non-priority production.

In priority heat production mode, only part of the refrigeration energy produced by the machine is actually supplied to the cold consumer, and a residue of the refrigeration energy produced by the machine must be evacuated to an external element. In priority refrigeration production mode, only part of the heat energy produced by the machine is actually supplied to the heat consumer, and it is a residue of heat energy produced by the machine which must be evacuated to an external element.

This external element, ensuring the energy balance of the system by absorbing the residue of non-priority production, which can be heat energy or cooling energy, is called an external source.

The external source is defined as one or more elements capable of absorbing either calorific energy or refrigeration energy.

The external source can be a natural element, such as the ambient air, the thermofrigopompe then functions according to the principle known as of the aerothermie; water from the natural environment, the thermofrigopompe then works according to the so-called principle of aquathermy; or the ground, the thermofrigopompe then operates according to the so-called geothermal principle; and can be fitted with one or more intermediate heat exchange systems.

A first major drawback of heat pumps is that on the side of non-priority production, the control of the share of energy produced which must be exchanged with the external source is not ensured by the machine itself. In priority heat production mode, all of the cooling energy produced by the machine is exchanged with the outside through the evaporator exchanger, this energy then being directed partly towards the cold consumer and for the other part towards the external source, using a circuit external to the machine. In priority refrigeration production mode, all of the heat energy produced by the machine is exchanged with the outside through the condenser exchanger. This energy is then directed partly to the heat consumer and partly to the external source, using a circuit outside the machine.

These external circuits, which allow the management of the energy flow between the non-priority consumer and the external source, are often complex and costly.

A second disadvantage of heat pumps is that on the priority production side, the regulation of the flow temperature of the heat transfer fluid to the consumer is carried out in stages to achieve the perfect adaptation of the power produced to the power required by the consumer. During the adaptation in stages, each stage corresponds to the unit power of the compressors of the machine, which operate in all or nothing mode. However, each start or stop of a compressor generates a variation in the heat and cooling capacities produced by the thermodynamic machine, which causes a variation in the temperatures of the heat transfer fluid leaving the secondary of the condenser exchanger and leaving the secondary of the evaporator exchanger. In order to avoid excessive fluctuations in the flow temperature of the fluid to the consumers, due to these variations in power caused by the starting or stopping of a compressor, it is necessary to install a buffer tank on the circuit supplying the heat consumer as on the cold consumer supply circuit. These buffer cylinders add complexity to the hydraulic circuit, and can also reach large volumes to ensure long enough compressor start and stop cycles.

A third drawback of heat pumps is that on the non-priority production side, all of the energy produced is transferred by the machine through an exchanger. The energy flows between the consumer on the one hand and the external source on the other are managed by a circuit external to the machine. It is therefore necessary for the machine to produce this energy at an adequate temperature level so that both the consumer and the external source can absorb some of it. Thus in priority heat production mode, the temperature of the heat transfer fluid at the secondary of the evaporator exchanger must be at most equal to the lowest of the temperatures required by the cold consumer on the one hand and the external source on the other hand.

In priority refrigeration production mode, the temperature of the heat transfer fluid at the secondary of the condenser exchanger must be at least equal to the highest of the temperatures required by the hot consumer on the one hand and the external source on the other hand . However, the energy efficiency of a refrigerant circuit depends on the work provided by the compressors, and therefore on the difference between the high pressure and the low pressure in the refrigerant circuit. The temperature of change of state of a fluid being directly related to the pressure of this fluid, the efficiency of the circuit depends on the difference between the condensing temperature of the refrigerant when it is in the portion of circuit at high pressure and the evaporation temperature of the refrigerant when it is in the low pressure circuit portion. These condensation and evaporation temperatures being continuously adapted to the temperatures required at the secondary of the condenser and evaporator exchangers, the efficiency of a refrigerant circuit therefore depends on the difference between the secondary temperature of the condenser exchanger and the secondary temperature of the evaporator exchanger. The higher this difference, the lower the yield.

All of the energy is therefore produced by the heat pump with the temperature level on the non-priority side which is the most unfavorable for the efficiency of the machine. It is not possible to optimize the overall efficiency of the machine by producing part of the energy for the non-priority consumer with one yield and another part of the energy for the external source with another yield. .

Summary of the invention

The object of the present invention is to solve the problems mentioned above and in particular to propose a thermodynamic machine which is capable of directly exchanging with the external source the heat or refrigeration energy residue produced by the thermodynamic machine on the non-priority production side. and not consumed by the corresponding consumer, preferably without having recourse to external circuits for managing the energy flow between the consumer and the external source.

We tend to solve these needs by means of a thermodynamic machine simultaneously producing heat energy and refrigeration energy and which comprises:

a first heat exchanger having at least one primary circuit through which a refrigerant circulates and at least one secondary circuit intended to be traversed by a first heat transfer fluid, the first heat exchanger being configured to condense the refrigerant;

a second heat exchanger having at least one primary circuit through which the refrigerant circulates and at least one secondary circuit intended to be traversed by a second heat transfer fluid, the second heat exchanger being configured to evaporate the refrigerant;

a third heat exchanger having at least one primary circuit through which the refrigerant circulates and at least one secondary circuit intended to be traversed by a third heat transfer fluid, the third heat exchanger being configured to evaporate or condense the refrigerant;

at least one refrigerant circuit inside which the refrigerant circulates, the at least one refrigerant circuit connecting the first heat exchanger, the second heat exchanger and the third heat exchanger;

The at least one refrigerant circuit includes:

a compressor mounted between an outlet of the second heat exchanger and an inlet of the first heat exchanger;

a first regulator mounted between an outlet of the first heat exchanger and an inlet of the second heat exchanger;

a first connecting node connecting the outlet of the compressor to the inlet of the first heat exchanger and to a first switching device;

a second link node connecting an outlet of the first heat exchanger to an inlet of the first regulator and a second switching device;

a third link node connecting an inlet of the second heat exchanger with an outlet of the first regulator and with the second switching device;

a fourth connecting node connecting an outlet of the second heat exchanger to the inlet of the compressor and to the first switching device;

the first switching device being configured to selectively define a first configuration or a second configuration, the first configuration defining a first refrigerant circulation channel connecting a first inlet / outlet of the third heat exchanger to the fourth connection node and preventing circulation refrigerant through the first switching device from the first connection node, the second configuration defining a second refrigerant circulation channel connecting the first connection node to the first inlet / outlet of the third heat exchanger and preventing circulation refrigerant through the first switching device to the fourth link node;

the second switching device being configured to selectively define a first configuration or a second configuration, the first configuration defining a first refrigerant circulation channel connecting the second connection node to a second input / output of the third heat exchanger and preventing the refrigerant circulation through the second switching device to the third connection node, the second configuration defining a second refrigerant circulation channel connecting the second inlet / outlet of the third heat exchanger to the third connection node and preventing the circulation of the refrigerant through the second switching device from the second connection node;

a second holder mounted between the second switching device and the second input / output of the third heat exchanger.

In a development, the second holder is a two-way regulator.

Advantageously, the compressor comprises a first compressor and a second compressor mounted in parallel between the first heat exchanger and the second heat exchanger, the first compressor being a variable speed compressor and the second compressor being an all or nothing whose activation is triggered when a heat power transferred through the first heat exchanger reaches a threshold value or when a cooling power transferred through the second heat exchanger reaches a threshold value.

In a particular embodiment, the first expansion valve has a variable opening rate and the machine has a control circuit configured to control the opening rate of the first expansion valve in order to regulate the proportion of refrigerant passing through the expansion valve and the second heat exchanger to adjust the cooling capacity transmitted through the second heat exchanger or to control the opening rate of the first expansion valve in order to regulate the proportion of refrigerant flowing through the expansion valve and the first heat exchanger to adjust the heating capacity transmitted through the first heat exchanger

It is advantageous to provide that the control circuit is configured to regulate the temperature of the heat transfer fluid at the outlet of the first heat exchanger or at the outlet of the second heat exchanger at a set value.

In another development, the second regulator has a variable opening rate and the control circuit is configured to control the ratio of the opening rate of the first regulator and the second regulator.

Preferably, the thermodynamic machine comprises a second refrigerant circuit inside which a second refrigerant circulates, the second refrigerant circuit connecting the first heat exchanger, the second heat exchanger and the third heat exchanger. The second refrigerant circuit has a compressor, a first expansion valve, a first link node, a second link node, a third link node, a fourth link node, a first switching device, a second switching device and a second pressure reducer arranged similarly to the arrangement of the first refrigerant circuit.

In another particular embodiment, the thermodynamic machine comprises a control circuit configured to define an operating mode in which the first and second switching devices of the first refrigerant circuit prevent the circulation of the refrigerant in the third heat exchanger and wherein the first and second switching devices of the second refrigerant circuit prevent the circulation of the second refrigerant in the second heat exchanger.

In a preferred configuration, the thermodynamic machine comprises a control circuit configured to define an operating mode in which the first and second switching devices of the first refrigerant circuit prevent the circulation of the refrigerant in the first heat exchanger and in which the first and second switching devices of the second refrigerant circuit prevent the circulation of the second refrigerant in the third heat exchanger.

The subject of the invention is also a method of operating a machine which makes it possible to better regulate the calorific power supplied and the refrigerating power supplied.

We tend to solve these needs by means of an operating method of a thermodynamic machine comprising the steps:

- Provide a thermodynamic machine according to one of the preceding embodiments with a refrigerant circuit;

- Switch between a first operating mode and a second operating mode, the first operating mode defining a parallel mounting of the third heat exchanger and the second heat exchanger between the output of the first heat exchanger and the input of the compressor, the second operating mode defining a parallel mounting of the third heat exchanger and the first heat exchanger between the outlet of the compressor and the inlet of the second heat exchanger.

There is also a tendency to resolve these needs by means of an operating method of a thermodynamic machine comprising the steps:

- Provide a thermodynamic machine according to one of the preceding embodiments with two refrigerant circuits;

- Switch between a first operating mode and a second operating mode, the first operating mode defining a first refrigerant circuit in which the refrigerant does not pass through the third heat exchanger and a second refrigerant circuit in which the second fluid refrigerant does not pass through the second heat exchanger, the second operating mode defining a first refrigerant circuit in which the refrigerant does not pass through the first heat exchanger and a second refrigerant circuit in which the second refrigerant does not pass not through the third heat exchanger.

Brief description of the drawings

Other advantages and characteristics will emerge more clearly from the description which follows of particular embodiments given by way of nonlimiting examples and illustrated with the aid of the appended drawings, in which:

Figure 1 shows, schematically, a heat pump according to the invention at the interface between a consumer of heat energy, a consumer of refrigeration energy, and an external source, according to an embodiment with a single refrigerant circuit;

Figure 2 shows, schematically, a heat pump according to the invention, operating in a mode called priority heat production;

Figure 3 shows, schematically, a heat pump according to the invention operating in a mode called heat production alone;

Figure 4 shows, schematically, a heat pump according to the invention operating in a mode called balanced heat production;

Figure 5 shows, schematically, a heat pump according to the invention, operating according to the mode called priority refrigeration production;

Figure 6 shows, schematically, a heat pump according to the invention operating according to the mode called refrigeration production only;

Figure 7 shows, schematically, a heat pump according to the invention operating according to the mode called balanced refrigeration production;

Figure 8 shows, schematically, another configuration of heat pump according to the invention at the interface between a consumer of heat energy, a consumer of refrigeration energy, and an external source with two refrigerant circuits;

Figure 9 shows, schematically, a heat pump according to the invention, and according to the embodiment described in Figure 8, operating generally according to the mode called priority heat production;

FIG. 10 represents, diagrammatically, the heat pump according to the invention, and according to the embodiment described in FIG. 8, operating globally according to the mode called priority refrigeration production.

Description of a preferred embodiment of the invention

The thermodynamic machine 100 is of the thermofrigopompe type, that is to say that the thermodynamic machine has at least one heat pump whose useful energy is discharged to a hot source and is taken from a cold source.

The thermodynamic machine 100 has a plurality of pipes through which one or more fluids can flow. The fluids can be in liquid or gaseous form. The direction of circulation of the fluid is indicated by arrows in FIGS. 2, 3, 4, 5, 6, 7, 9, and 10. The pipes allowing a circulation of fluid are represented by a solid line whereas the pipes do not not allowing fluid circulation are indicated by dotted lines.

Valves and regulators in the open position are shown in white. Valves and regulators in the closed position are shown in black. In the open position, the valve allows the circulation of a fluid while it prevents this circulation when it is in the closed position.

The black arrows arranged on the heat exchangers indicate a transfer of heat through the heat exchangers. The direction of the black arrows indicates the direction of heat flow. A black arrow leaving the thermodynamic machine 100 indicates a transfer of heat capacity from the machine 100 to the outside, while a black arrow entering the thermodynamic machine 100 indicates a transfer of cooling power from the machine 100 to the outside .

The heat pump 100 includes a refrigerant circuit 1 in which circulates a refrigerant or at least one refrigerant. A refrigerant can be pure or a mixture of fluids. The refrigerant can be in gaseous or liquid form depending on the pressure and the temperature in the refrigerant circuit and in particular in the heat exchangers. Advantageously, the temperatures of change of liquid-gas state of the refrigerant are located within the operating temperature range of the thermodynamic machine. The refrigerant is preferably chosen from Hydro Fluoro Carbones, for example R134a (1,1,1,2-tetrafluoroethane), R410A (mixture of difuoromethane and

1.1.1.2.2- pentafluoroethane), R407C (mixture of 1,1,1,2-tetrafluoroethane,

1.1.1.2.2- pentafluoroethane and difuoromethane) or among the Hydro Fluoro Olefins, for example R1234ze (trans-1,3,3,3-Tetrafluoroprop-1-ene), or R-1233zd (trans-1- chloro-3,3,3-trifluoro-1-propene). Preferably, the temperature of change of liquid-gas state of the refrigerant is between -50 ° C and 100 ° C.

The heat pump 100 has a first heat exchanger 2 which produces heat energy. The first heat exchanger 2 supplies a consumer of heat energy 200 also called a hot source by means of a first heat transfer fluid. The first heat transfer fluid circulates in pipes 201 and 202 which connect a secondary of the first heat exchanger 2 with the consumer of heat energy 200. The consumer of heat energy is for example a heating system or a producer of hot water.

The heat pump 100 produces cooling energy through a second heat exchanger 3. The second heat exchanger 3 supplies a cold consumer 300 also called cold source by means of a second heat transfer fluid circulating in pipes 301 and 302. The pipes 301 and 302 connect a secondary of the second heat exchanger 3 with the cold consumer 300. The cold consumer is for example a cooling system.

The heat pump 100 has a third heat exchanger 4 the secondary of which is thermally connected with an external element 401 which can be the external source 400 itself or a third heat transfer fluid supplying this external source 400. The heat pump is capable of exchanging heat with the external source 400. The temperature of the external source is advantageously between -40 ° C and 50 ° C. The external source can be ambient air.

The first, second and third heat transfer fluids may be the same or different and be present independently pure or in the form of a mixture. The heat transfer fluid may also contain mineral substances. Preferably, the heat transfer fluid does not change state during the transfer of heat between a heat exchanger and a hot / cold consumer or an external source. The heat transfer fluid can be chosen from water, air, an aqueous solution, monopropylene glycol, monoethylene glycol, alcoholic solutions or salts.

In operation, part of the heat or cooling energy produced by the thermodynamic machine 100, also called heat energy residue or cooling energy residue, must be discharged to the external source 400. Preferably, the external source has a or several external elements 401. An external element 401 is a natural element, such as ambient air, water from the natural environment, the ground or any type of external element. The thermodynamic machine can be provided with one or more intermediate heat exchange systems to address each of the external elements.

The refrigerant circuit 1 is connected to the primary of the first heat exchanger 2, to the primary of the second heat exchanger 3 and to the primary of the third heat exchanger 4. The refrigerant circulates so as to move calories between the heat exchangers.

The first heat exchanger 2, also called condenser exchanger 2, makes it possible to transfer heat from the refrigerant circulating in the primary of the condenser exchanger 2 to a heat transfer fluid circulating in the secondary of the condenser exchanger 2, while ensuring condensation refrigerant.

The second heat exchanger 3, also called evaporator exchanger 3, makes it possible to transfer heat from a heat transfer fluid circulating in the secondary of the evaporator exchanger 3 to the refrigerant circulating in the primary of the evaporator exchanger 3, while ensuring the evaporation of the refrigerant.

The third heat exchanger 4, also called source exchanger 4, makes it possible to exchange heat between the refrigerant circulating in the primary of the source exchanger 4 and the external element 401, in contact with the secondary of the exchanger from source 4, while ensuring either the condensation or the evaporation of the refrigerant.

The heat pump 100 advantageously comprises a first temperature sensor 21 configured to measure the temperature TCH of the heat transfer fluid leaving the secondary of the condenser exchanger 2 and advantageously a second temperature sensor 31 configured to measure the temperature TFR of the heat transfer fluid at the outlet of the secondary of the evaporator exchanger 3. The measurement of the two temperatures can be sent to a control circuit 500 to ensure the regulation of each of the temperatures TFR and TCH to a set value.

A third temperature sensor 23 can be used to measure the temperature T3 of the refrigerant leaving the primary circuit of the condenser exchanger 2.

A fourth temperature sensor 32 can be used to measure the temperature T1 at the outlet of the primary circuit of the evaporator exchanger 3.

A compressor is used to compress the refrigerant in the refrigerant circuit 1 when it is in the gaseous state. The compressor is arranged in a pipe which connects the outlet of the second heat exchanger 3 and the inlet of the first heat exchanger 2. In the advantageous embodiment illustrated, the compressor comprises a first compressor 5 and a second compressor 6 mounted in parallel. The first compressor 5 can be driven by a first electric motor 53 provided with an electronic speed variator 54 to adapt its speed to the required heat or cooling power. The second compressor 6 can be driven by a second electric motor 63.

The refrigerant circuit 1 also comprises a first pressure sensor 51 configured to measure the pressure PHP at the outlet of the compressor and a second pressure sensor 52 configured to measure the pressure PBP at the inlet of the compressor.

In a preferred embodiment, a reservoir 14 is mounted in the refrigerant circuit 1 at the inlet of the compressor. The reservoir 14 is configured to trap the refrigerant in the liquid state. Thus, the compressor is supplied with a refrigerant in the gaseous state.

A first regulator 7 is mounted in the refrigerant circuit 1 so as to lower the pressure of the refrigerant when it circulates in the regulator 7 in the liquid state. The first regulator 7 is arranged in a pipe which connects the outlet of the first heat exchanger 2 with the inlet of the second heat exchanger 3. The first regulator 7 is preferably controlled electronically.

A second regulator 8, preferably bidirectional, is mounted in the refrigerant circuit 1 so as to lower the pressure of the refrigerant when it circulates in the regulator 8 in the liquid state. The second pressure reducer 8 is arranged in a pipe where the refrigerant circulates between a connection node 20 and the third heat exchanger 4. The connection node 20 being able to connect the second pressure reducer 8 to the first heat exchanger 2 and / or to the second heat exchanger 3. The second pressure reducer 8 is preferably electronically controlled.

The refrigerant circuit 1 is configured so as to supply each heat exchanger with refrigerant and ensure the transfer of calories between the heat exchangers. However, the refrigerant circuit 1 has multiple pipes connecting the inputs and outputs of the heat exchangers with each other in order to be able to define different directions of circulation of the refrigerant and thus different modes of operation.

The refrigerant circuit 1 has a first link node 15 which connects the outlet of the compressor to the inlet of the first heat exchanger 2 and to a first switching device which defines or comprises a fifth link node

19.

A second link node 16 makes the connection between the output of the first heat exchanger 2, a first terminal of the first regulator 7 and a second switching device which defines or comprises a sixth link node 20.

A third link node 17 makes the connection between a second terminal of the first regulator 7, the inlet of the second heat exchanger 3 and the second switching device.

A fourth link node 18 makes the connection between the inlet of the compressor, the outlet of the second heat exchanger 3 and a fifth link node 19. The fourth link node can be arranged between the outlet of the second heat exchanger 3 and the reservoir 14.

The fifth link node 19 makes the connection between the first link node 15, the fourth link node 18 and a first input / output of the third heat exchanger 4.

The sixth link node 20 makes the connection between the third link node 17, the second link node 16 and a second inlet / outlet of the third heat exchanger 4 via the second pressure reducer 8.

A fifth temperature sensor 42 can be used to measure the temperature T2 of the refrigerant between the connection node 19 and the first input / output of the source exchanger 4. For example, when the primary of the source exchanger 4 operates as an evaporator, the fifth temperature sensor measures the temperature T2 of the refrigerant leaving the primary of the source exchanger 4.

A sixth temperature sensor 43 can be used to measure the temperature T4 of the refrigerant between the second input / output of the source exchanger 4 and the sixth connection node 20, preferably between the second input / output of the exchanger source 4 and the second regulator 8. When the primary circuit of the source exchanger 4 operates as a condenser, the sixth sensor 43 measures the temperature T4 of the refrigerant leaving the primary of the source exchanger 4.

According to the regulation needs of the thermodynamic machine, the first switching device is configured to selectively define a first configuration or a second configuration. The first configuration defines a first refrigerant circulation channel connecting the first inlet / outlet of the third heat exchanger 4 to the fourth connection node 18 and preventing the circulation of the refrigerant through the switching device from the first connection node 15 as illustrated in the figure

2.

The second configuration defines a second refrigerant circulation channel connecting the first connection node 15 to the first inlet / outlet of the third heat exchanger 4 as illustrated in FIG. 5, and preventing the circulation of the refrigerant through the device switching to the fourth link node 18.

Advantageously, the first switching device is further configured to define a blocking configuration in which no fluid passes through the first switching device.

The second switching device is configured to selectively define a first configuration or a second configuration. The first configuration defines a first refrigerant circulation channel connecting the second connection node 16 to a second inlet / outlet of the third heat exchanger 4 and preventing the circulation of the refrigerant through the switching device up to the third node link 17 as illustrated in FIG. 2.

The second configuration defines a second refrigerant circulation channel connecting the second inlet / outlet of the third heat exchanger 4 to the third connection node 17 and preventing the circulation of the refrigerant through the switching device from the second connection node 16 as shown in Figure 5.

Advantageously, the second switching device is further configured to define a blocking configuration in which no fluid passes through the second switching device.

As illustrated in FIG. 2, the first circulation channels defined by the first and second switching devices make it possible to form a circulation channel which connects the outlet of the first heat exchanger 2 with the inlet of the compressor passing through the third heat exchanger 4 to recover heat. Thus, it is possible to adjust the temperature of the secondary heat transfer fluid of the first heat exchanger 2 and to adjust the temperature of the secondary heat transfer fluid of the second heat exchanger 3.

As illustrated in FIG. 5, the second circulation channels defined by the first and second switching devices make it possible to form a circulation channel which connects the outlet of the compressor with the inlet of the second heat exchanger 3 passing through the third heat exchanger 4 to dissipate heat. Thus, it is possible to adjust the temperature of the secondary heat transfer fluid of the first heat exchanger 2 and to adjust the temperature of the secondary heat transfer fluid of the second heat exchanger 3.

The first switching device can be formed for example by two valves 10 and 11, preferably solenoid valves 10 and 11. As an exemplary embodiment, the first valve 10 can be mounted between the first connecting node 15 and the fifth link node 19 and the second valve 11 can be mounted between the fifth link node 19 and the fourth link node 18.

The first switching device is configured to authorize a first circulation of the refrigerant between the first inlet / outlet of the third heat exchanger 4 and the inlet of the compressor 5, 6, to authorize a second circulation of refrigerant between the outlet of the compressor 5, 6 and the first inlet / outlet of the third heat exchanger 4 or to block a flow of refrigerant between the outlet of the compressor and the first inlet / outlet of the third heat exchanger 4 and block a flow of refrigerant between the first input / output of the third heat exchanger 4 and the input of the compressor 5. The first switching device is advantageously configured to avoid directly connecting the input and the output of the compressor.

The second switching device can be formed for example by two valves 12 and 13, preferably solenoid valves 12 and 13. The valve 12 is advantageously arranged between the second connection node 16 and the sixth connection node 20. The valve 13 is advantageously disposed between the sixth link node 20 and the third link node 17.

The second switching device is configured to authorize a first circulation of the refrigerant between the output of the first heat exchanger 2 and the second inlet / outlet of the third heat exchanger 4, to allow a second circulation of refrigerant between the second inlet / outlet of the third heat exchanger 4 and the inlet of the second heat exchanger 3 or to block a flow of refrigerant between the second inlet / outlet of the third heat exchanger 4 and the inlet of the second heat exchanger 3 and block a refrigerant flow between the outlet of the first heat exchanger 2 and the second inlet / outlet of the third heat exchanger 4. The first switching device is advantageously configured to avoid directly connecting the outlet of the first heat exchanger and the inlet of the second heat exchanger which short-circuits the pressure reducer 7.

The first and second switching devices are configured to place the third heat exchanger 4 in parallel with the second heat exchanger 3 in order to dissociate the cooling power supplied to the second heat exchanger 3 from the cooling power delivered by the machine 100.

The first and second switching devices are configured to place the third heat exchanger 4 in parallel with the first heat exchanger 2 in order to dissociate the calorific power supplied to the first heat exchanger 2 from the calorific power delivered by the machine 100.

The first and second switching devices can also be configured to exit independently, the first heat exchanger 2, the second heat exchanger 3 and the third heat exchanger 4 of the refrigerant circuit by preventing the circulation of the refrigerant inside one of these exchangers. The first and second switching devices make it possible to easily adapt the heat and / or cooling power delivered to the first heat exchanger and to the second heat exchanger by adapting the operation of the third heat exchanger.

This configuration is particularly advantageous because it is compact. The first, second, third and fourth link nodes can be simply connection nodes and have no valves.

According to the embodiments, the thermodynamic machine 100 has a single refrigerant circuit, two refrigerant circuits or more than two refrigerant circuits.

FIG. 2 illustrates a mode of operation of the thermodynamic machine called priority heat production. In this operating mode, the calorific power produced by the thermodynamic machine 100 through the refrigerant circuit 1 is adapted to the calorific power required by the heat consumer 200. For example, the control circuit 500 regulates the calorific power to maintain the TCH temperature in a target range. The cooling power produced by the refrigerant circuit 1 is at least equal to the cooling power required by the cold consumer 300.

All of the heat output produced is transferred to the heat consumer 200 through the condenser exchanger 2. The black arrow 203 represents heat extraction from the refrigerant circuit to the heat consumer 200. Part of the refrigeration power produced , corresponding to the cooling power required by the cold consumer 300, is transferred to the cold consumer 300 through the evaporator exchanger 3. The black arrow 303 represents a heat extraction from the cold consumer 300 to the refrigerant circuit 1 Finally, the remaining part of the cooling power produced, not necessary for the cold consumer 300, is transferred to the source 400 through the source exchanger 4. The black arrow 403 represents an extraction of heat from the source 400 to the refrigerant circuit 1.

In this operating mode, the output of the first heat exchanger 2 is connected to the input of the second heat exchanger 3 and to the second input / output of the third heat exchanger 4 to allow a flow of refrigerant from the first exchanger heat 2 to the second and third heat exchangers 3 and 4. The outlet of the second heat exchanger 3 and the first inlet / outlet of the second heat exchanger meet for example before the inlet of the compressor and advantageously before the inlet of the reservoir 14.

In the particular example illustrated in Figure 2, the valve 12 is open and the valve 13 is closed. The valve 11 is open and the valve 10 is closed.

The valve 10 being closed, all of the refrigerant in gaseous state and at high pressure, coming from the compressor, circulates only through the primary of the condenser exchanger 2, inside which the refrigerant condenses in ceding heat to the heat transfer fluid circulating in the secondary of the condenser exchanger 2. The refrigerant comes out of the condenser exchanger 2 at a lower temperature T3 and advantageously in the liquid state and at high pressure.

The presence of the temperature sensor 23 is not essential for the operation of the machine. However, the measurement of the temperature T3 possibly combined with the pressure measurement PHP makes it possible to verify that the reduction in temperature linked to the condenser exchanger 2 is within the desired range and / or that the refrigerant leaving the primary of the condenser exchanger 2 is in the liquid phase.

The use of compressor 6 operating in all-or-nothing mode in combination with compressor 5, the rotational speed of which can be adjusted continuously, allows a continuous adjustment of the heat power transferred through the condenser exchanger 2. It is possible to provide that, below a threshold power, only the compressor 5 can be activated. The power that can be transferred through the condenser exchanger 2 is then determined by the speed of rotation of the compressor 5.

Beyond the threshold power, when the compressor 5 alone no longer allows the required power to be transferred, for example when the compressor reaches its maximum speed, the second compressor 6 is activated. This second compressor 6 then provides additional power and the speed of rotation of the compressor 5 is controlled in order to provide the additional power necessary to reach the power required at the condenser exchanger 2.

This operating mode of the compressors 5 and 6 which combines the activation or deactivation of the second compressor 6 and the adjustment of the speed of rotation of the first compressor 5, thus makes it possible to continuously adjust the calorific power transmitted through the 'condenser exchanger 2, and therefore to regulate the temperature TCH of the coolant outlet to its set value.

At the outlet of the condenser exchanger 2, the refrigerant passes through the second connecting node 16 where it splits into two parts. Part of the refrigerant is directed to the inlet of the second heat exchanger 3 through the expansion valve 7. In the expansion valve 7, the refrigerant undergoes a lowering of its pressure. At the outlet of the regulator 7, the fluid is at low pressure and advantageously in the liquid state. The refrigerant is directed through the third connection node 17 to the primary of the evaporator exchanger 3 inside which the refrigerant evaporates by capturing heat from the heat transfer fluid circulating in the secondary of the evaporator exchanger 3.

At the outlet of the evaporator exchanger primary 3, the refrigerant is mainly in the gaseous state and at low pressure. The refrigerant joins the reservoir 14 through the connection node 18.

The other part of the refrigerant leaving the condenser exchanger 2 is directed towards the third heat exchanger 4 through the expansion valve 8. The refrigerant in the liquid state undergoes a reduction in its pressure by means of the expansion valve 8. A the outlet of the regulator 8, the fluid in the liquid state and at low pressure passes through the primary of the source exchanger 4, then operating as an evaporator. The refrigerant evaporates in the third heat exchanger 4 by capturing heat from the external element which is in contact with the secondary of the source exchanger 4. On leaving the primary of the source exchanger 4, the refrigerant is in the gaseous state and at low pressure.

Advantageously, the combined measurement of temperatures T1 and T2 is used to determine the superheating value of the refrigerant at the outlet of the evaporator exchanger 3 on the one hand, and at the outlet of the source exchanger 4 d ' somewhere else. In a preferred embodiment, the measurement of temperatures T1 and T2 is used in order to impose the superheat value of the refrigerant at the outlet of the evaporator exchanger 3 and at the outlet of the source exchanger 4.

Advantageously, the combined measurement of temperatures T1 and T2 is used to control the rate of opening of the regulator 7 and the rate of opening of the regulator 8 if necessary. Temperature measurements is used to ensure complete evaporation of the refrigerant both in the primary of the evaporator exchanger 3 and in the primary of the source exchanger 4. In a particularly advantageous manner, the temperature measurement is associated PBP pressure measurement to better control the value of overheating.

It is advantageous to control the opening rate of the expansion valve 7 relative to the opening rate of the expansion valve 8 in order to regulate the proportion of fluid passing through the expansion valve 7 and the evaporator exchanger 3 relative to the proportion of fluid passing through the expansion valve 8 and the third heat exchanger 4. The control of the proportion of fluid passing through the primary of the evaporator exchanger 3 makes it possible to continuously adjust the power transmitted through the evaporator exchanger 3, and therefore to regulate the temperature of TFR heat transfer fluid outlet at its setpoint. The excess power is removed by the third heat exchanger 4.

Thus the heat pump 100, in priority heat production mode, makes it possible to continuously adjust the heat and cooling powers transmitted respectively through the condenser exchanger 2 and the evaporator exchanger 3, and therefore regulate the temperature of the heat transfer fluid TCH in secondary output of the condenser exchanger 2 and the temperature of the heat transfer fluid TFR at the output of the secondary of the evaporator exchanger 3, at their set value.

FIG. 3 represents the thermodynamic machine in an operating mode called priority heat production and more particularly heat production alone. The cooling power required by the cold consumer 300 is zero. All of the heat power produced by the thermodynamic machine 100 is therefore transferred to the heat consumer 200 through the condenser exchanger 2. The black arrow 203 represents the extraction of heat from the machine 100 to the heat consumer 200.

The entire refrigerating power produced by the refrigerating machine 100 is transferred to the source 400 through the source exchanger 4. The black arrow 403 represents the injection of heat from the external source to the refrigerant circuit. In this particular case, no heat exchange takes place through the evaporator exchanger 3, the regulator 7 is completely closed, thus allowing no refrigerant to pass into the primary of the evaporator exchanger 3. All of the outgoing refrigerant from the condenser exchanger 2 in the liquid state and at high pressure, is directed towards the regulator 8 in which this refrigerant undergoes a lowering of its pressure.

At the outlet of the regulator 8, the fluid in the liquid state and at low pressure passes through the primary of the source exchanger 4 inside which the refrigerant evaporates while capturing heat at the external element. finding in contact with the secondary of the source exchanger 4. On leaving the primary of the source exchanger 4, the refrigerant in gaseous state and at low pressure joins the reservoir 14. The degree of opening of the regulator 8 is advantageously controlled in order to ensure sufficient overheating of the refrigerant at the outlet of the source exchanger 4, thus ensuring the complete evaporation of the refrigerant in the primary of the source exchanger 4. The embodiment illustrated in FIG. 3 represents a particular case of the operation illustrated in FIG. 2 where the cooling power consumed by the cold consumer 300 is zero.

FIG. 4 represents the thermodynamic machine in substantially the same operating mode as that illustrated in FIG. 2. The figure represents an operating mode called balanced heat production, where the refrigerating power produced by the thermodynamic machine reaches exactly the refrigerating power required by the cold consumer 300.

All of the heat output produced by the thermodynamic machine 100 is transferred to the heat consumer 200 through the condenser exchanger 2 as shown by the black arrow 203. All of the refrigeration output produced by the refrigeration machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as shown by the black arrow 303.

In this particular case, no heat exchange takes place through the source exchanger 4, the regulator 8 can be completely closed, thus letting no refrigerant pass through the primary of the source exchanger 4. It is also possible to close the valves 12 and 13. Thus, all of the refrigerant leaving the liquid state and at high pressure from the condenser exchanger 2 is directed to the pressure reducer 7 in which the refrigerant undergoes a lowering of its pressure. At the outlet of the regulator 7, the fluid in the liquid state and at low pressure passes through the primary of the evaporator exchanger 3 inside which the refrigerant evaporates by capturing heat from the heat transfer fluid circulating in the secondary of the evaporator exchanger 3.

At the outlet of the primary of the evaporator exchanger 3, the refrigerant in gaseous state and at low pressure joins the reservoir 14. The rate of opening of the regulator 7 is controlled in order to ensure sufficient overheating of the fluid refrigerant at the outlet of the evaporator exchanger 3, thus ensuring complete evaporation of the refrigerant in the primary of the evaporator exchanger 3.

FIG. 5 represents the thermodynamic machine in a mode of operation which is called priority refrigeration production. In this operating mode, the cooling power produced by the refrigerant circuit 1 is adapted to the cooling power required by the cold consumer 300, and the heat power produced by the thermodynamic machine is at least equal to the heat power required by the consumer. 200. For example, the control circuit 500 regulates the cooling power to maintain the TFR temperature in a target range. All of the cooling power produced by the thermodynamic machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as shown by the black arrow 303.

Part of the heat output produced by the refrigeration machine 100, corresponding to the heat output required by the heat consumer 200, is transferred to the heat consumer 200 through the condenser exchanger 2 as shown by the black arrow 203.

The remaining part of the heat output produced by the refrigerating machine 100 not necessary for the heat consumer 200, is transferred to the source 400 through the source exchanger 4. The black arrow 403 represents a heat extraction from the refrigerant circuit to the external source.

In this operating mode, the output of the compressor feeds the input of the first heat exchanger 2 and the first input / output of the third heat exchanger 4. In the example illustrated, the valve 10 is open and the valve 11 is closed . The second inlet / outlet of the third heat exchanger 4 is connected to the inlet of the second heat exchanger 3. In the example illustrated, the valve 13 is open and the valve 12 is closed.

At the outlet of the compressor, the refrigerant is in the gaseous state and at high pressure and it crosses the first connecting node 15 where it splits into two parts. Part of the refrigerant is directed to the primary of the condenser exchanger 2, inside which the refrigerant condenses by ceding heat to the heat transfer fluid circulating in the secondary of the condenser exchanger 2. The refrigerant comes out of the condenser exchanger 2 in the liquid state and at high pressure, and at the temperature T3. It is advantageous to close the valve 12 so that the refrigerant leaving the condenser exchanger 2 is directed towards the expansion valve 7. The refrigerant in the liquid state undergoes a reduction in its pressure inside the expansion valve 7. At the outlet of the regulator 7, the fluid in the liquid state and at low pressure is directed towards the connection node 17.

The other part of refrigerant is directed to the primary of the source exchanger 4 then operating as a condenser. Inside the source exchanger 4, the refrigerant condenses by yielding heat to the external element in contact with the secondary of the source exchanger 4.

The presence of the temperature sensor 43 is not essential for the operation of the machine. However, a measurement of the temperature T4 makes it possible to verify that the value of the cooling of the refrigerant at the outlet of the primary of the source exchanger 4 is in the range sought when the source exchanger 4 operates as a condenser. The temperature measurement is advantageously used to control that the refrigerant is in the liquid state at the outlet of the primary of the source exchanger 4. It is advantageous to combine the measurement of the temperature T4 with the measurement of the PHP pressure to control that the refrigerant is in the liquid state at the outlet of the primary of the source exchanger 4.

On leaving the primary of the source exchanger 4, the refrigerant is directed towards the expansion valve 8, in which the refrigerant in the liquid state undergoes a lowering of its pressure. At the outlet of the regulator 8, the fluid in the liquid state and at low pressure is directed through the valve 13, which is open, towards the connection node 17.

At the third connection node 17, the part of refrigerant coming from the condenser exchanger 2 then the regulator 7 and the part of refrigerant coming from the source exchanger 4 then the regulator 8, mix before d 'enter the primary of the evaporator exchanger 3. All of the refrigerant, in the liquid state and at low pressure, circulates through the primary of the evaporator exchanger 3, inside which the refrigerant s' evaporates by capturing heat from the heat transfer fluid circulating in the secondary of the evaporator exchanger 3.

At the outlet of the evaporator exchanger primary 3, the refrigerant is in the gaseous state and at low pressure. The refrigerant advantageously reaches the reservoir 14. As before, it is advantageous to use a second compressor 6 operating in all or nothing mode in association with the first compressor 5, the rotation speed of which can be adjusted continuously. This allows a continuous adjustment of the cooling power transferred through the evaporator exchanger 3. The control of the compressors 5 and 6, combining the activation or deactivation of the compressor 6 and the adjustment of the rotation speed of the compressor 5, allows thus to continuously adjust the cooling power transmitted through the evaporator exchanger 3, and therefore to regulate the outlet temperature of the heat transfer fluid TFR to its set value.

As for the embodiment illustrated in FIG. 2, the opening rate of the regulators 7 and 8 can be controlled in order to ensure sufficient overheating of the refrigerant at the outlet of the primary of the evaporator exchanger 3, thus ensuring complete evaporation of the refrigerant in the primary of the evaporator exchanger 3. The measurement of the temperature T1 possibly in combination with the measurement of the low pressure PBP, makes it possible to control that the value of the overheating of the refrigerant at the outlet of the evaporator exchanger 3 is in the desired range.

The control of the opening rates of the regulators 7 and 8, for example the relative value of the degree of opening of the regulator 7 with respect to the degree of opening of the regulator 8, makes it possible to regulate the proportion of fluid passing through the condenser exchanger 2 Control of the proportion of fluid passing through the primary of the condenser exchanger 2 makes it possible to continuously adjust the power transmitted through the condenser exchanger 2, and therefore to regulate the outlet temperature of the heat transfer fluid TCH to its value. setpoint.

Thus the heat pump 100, in priority refrigeration production mode, makes it possible to continuously adjust the heat and refrigeration powers transmitted respectively through the condenser exchanger 2 and the evaporator exchanger 3, and therefore regulate the temperature of the heat transfer fluid TCH in secondary output of the condenser exchanger 2 and the temperature of the heat transfer fluid TFR at the output of the secondary of the evaporator exchanger 3, at their set value.

FIG. 6 represents a particular mode of operation of what is illustrated in FIG. 5 and called only refrigeration production. The calorific power required by the consumer of heat 200 is zero. All of the cooling power produced by the thermodynamic machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as represented by the black arrow 303. All of the heat produced by the refrigerating machine 100 is transferred to the source 400 through the source exchanger 4 as shown by the black arrow 403.

In this particular case, no heat exchange takes place through the condenser exchanger 2, the regulator 7 is completely closed, thus letting no refrigerant pass through the primary of the condenser exchanger 2. Thus, all of the fluid refrigerant, in gaseous state and at high pressure at the outlet of the compressor, is directed to the primary circuit of the source exchanger 4, which operates as a condenser, and inside which the refrigerant condenses by transferring from the heat to the external element which is in contact with the secondary of the source exchanger 4. On leaving the primary of the source exchanger 4, the refrigerant in the liquid state and at high pressure enters the pressure reducer bidirectional 8 in which this refrigerant undergoes a lowering of its pressure.

In the example illustrated, the valve 10 is open and the valve 11 is closed. At its outlet from the expansion valve 8, all of the refrigerant in the liquid state and at low pressure is directed to the primary circuit of the evaporator exchanger 3, inside which the refrigerant evaporates while capturing heat. to the coolant circulating in the secondary of the evaporator exchanger 3. In the example illustrated, the valve 13 is open and the valve 12 is closed.

The refrigerant comes out of the evaporator exchanger 3 in the gaseous state and at low pressure, then advantageously joins the reservoir 14 through the connection node 18. The opening rate of the regulator 8 is controlled so as to obtain overheating sufficient refrigerant at the outlet of the evaporator exchanger 3, thus ensuring complete evaporation of the refrigerant in the primary of the evaporator exchanger 3.

Figure 7 shows another particular mode of operation of that illustrated in Figure 5 and called balanced refrigeration production. The calorific power produced by the thermodynamic machine reaches exactly the calorific power required by the heat consumer. All of the cooling power produced by the thermodynamic machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as shown by the black arrow 303.

All of the heat output produced by the refrigerating machine 100 is transferred to the heat consumer 200 through the condenser exchanger 2 as shown by the black arrow 203. No heat exchange takes place through the heat exchanger. source 4, the regulator 8 is completely closed, thus not allowing any refrigerant to pass into the primary of the source exchanger 4. It is also possible to close the valves 10 and 11. Thus, all of the refrigerant, at l gas and high pressure state at the outlet of the compressors 5 and 6, is directed to the primary circuit of the condenser exchanger 2, inside which the refrigerant condenses by yielding heat to the coolant circulating in the secondary of the condenser exchanger 2.

On leaving the primary of the condenser exchanger 2, the refrigerant in the liquid state and at high pressure enters the pressure reducer 7. The refrigerant then undergoes a lowering of its pressure. At its outlet from the expansion valve 7, all of the refrigerant in the liquid state and at low pressure is directed to the primary circuit of the evaporator exchanger 3, inside which the refrigerant evaporates while capturing heat. to the heat transfer fluid circulating in the secondary of the evaporator exchanger 3.

The refrigerant emerges from the evaporator exchanger 3 in the gaseous state and at low pressure, then advantageously joins the reservoir 14. The opening rate of the regulator 7 is controlled so as to obtain sufficient overheating of the refrigerant at the outlet of the evaporator exchanger 3, thus ensuring complete evaporation of the refrigerant in the primary of the evaporator exchanger 3.

According to the operating modes, the control circuit 500 modifies the state of the first and second switching devices so that they selectively define a circulation channel in which the third heat exchanger 4 is mounted in parallel with the first heat exchanger 2 or a circulation channel in which the third heat exchanger 4 is mounted in parallel with the second heat exchanger 3.

FIG. 8 schematically represents another embodiment of a heat pump 100 comprising two separate refrigerant circuits 1 and 101. Each 1/101 refrigerant circuit supplies a primary of the multiple heat exchangers. The first refrigerant circuit 1 is identical to what has been described previously in relation to the embodiments illustrated in FIGS. 1 to 7.

The two 1/101 refrigerant circuits are advantageously identical and each comprise a 5/6 and 105/106 compressor preferably arranged in the pipe which connects the second heat exchanger 3 with the first heat exchanger 2. Each refrigerant circuit 1 and 101 comprises also two regulators 7, 8 and 107, 108. The technical characteristics of the elements forming the second refrigerant circuit can take over the characteristics already indicated above for the first refrigerant circuit. The second refrigerant circuit has six connection nodes arranged identically to what has been described above and it also includes the two switching devices. The second refrigerant circuit may also include a reservoir 114, as well as temperature sensors. Each temperature sensor of the second refrigerant circuit being a sensor equivalent to what has been described in the first refrigerant circuit.

The second refrigerant circuit 101 allows the circulation of a second refrigerant which may be identical or different to the first refrigerant in its composition.

The refrigerant circuit 101 advantageously comprises a pressure sensor 151 configured to measure the pressure PHP101 at the outlet of the compressor 105/106. The refrigerant circuit 101 may also include another pressure sensor 152 configured to measure the pressure PBP101 at the inlet of the compressor 105/106.

The third regulator 107 makes it possible to lower the pressure of the second refrigerant when it circulates in the regulator 107 in the liquid state. The refrigerant circuit 101 also includes a fourth pressure reducer 108 which is advantageously electronically controlled. Preferably, the fourth expander 108 is bidirectional and makes it possible to lower the pressure of the refrigerant when it circulates in the expander 108 in the liquid state.

As indicated above, the second refrigerant circuit 101 includes a first refrigerant temperature sensor 132 configured to measure the temperature T101 at the outlet of the second primary circuit of the evaporator exchanger 3.

The second refrigerant circuit 101 includes a second refrigerant temperature sensor 142 configured to measure the temperature T102 of the refrigerant leaving the second primary circuit of the source exchanger 4 when the latter operates in the evaporator.

The second refrigerant circuit 101 includes a third refrigerant temperature sensor 123, configured to measure the temperature T103 of the refrigerant leaving the second primary circuit of the condenser exchanger 2.

The second refrigerant circuit 101 also includes a fourth refrigerant temperature sensor 143 configured to measure the temperature T104 of the refrigerant leaving the second primary circuit of the source exchanger 4 when the latter operates as a condenser.

In a first type of operation, the heat pump 100 with two refrigerant circuits can operate according to the same production modes as those illustrated in FIGS. 2, 3, 4, 5, 6 and 7. In these cases, the two refrigerant circuits are connected to the same heat exchangers and the two refrigerants circulate identically in the two circuits. The first switching device of the first refrigerant circuit is in the same state as the first switching device of the second refrigerant circuit. According to the same logic, the second switching device of the first refrigerant circuit is in the same state as the second switching device of the second refrigerant circuit.

However, it is advantageous to provide that the two refrigerant circuits 1 and 101 illustrated in FIG. 8 are considered as two thermodynamic sub-assemblies which can operate independently. Each of the two refrigerant circuits 1 and 101 can operate independently according to one or other of the two modes which are the priority heat production mode, including the specific cases of heat production alone and balanced heat production, and production mode. priority refrigeration, including the special cases of refrigeration alone and balanced refrigeration. FIGS. 9 and 10 give two exemplary embodiments of two operating modes of the refrigerant circuits 1 and 101.

In the operating mode illustrated in FIG. 9 and operating globally according to the mode called priority heat production, the heat power produced by the thermodynamic machine 100 is adapted to the heat power required by the heat consumer 200, and the refrigeration power produced by the thermodynamic machine exceeds the cooling capacity required by the cold consumer 300.

All of the heat output produced by the thermodynamic machine 100 is transferred to the heat consumer 200 through the condenser exchanger 2 as shown by the black arrow 203. Part of the refrigeration power produced by the refrigeration machine 100, corresponding to the cooling capacity required by the cold consumer 300, is transferred to the cold consumer 300 through the evaporator exchanger 3 as shown by the black arrow 303.

Finally, the remaining part of the cooling power produced by the thermodynamic machine 100, which has not been transferred to the cold consumer 300, is transferred to the source 400 through the source exchanger 4 as shown by the black arrow 403.

Even if the thermodynamic machine operates globally according to the priority heat production mode, each of the two circuits 1 and 101 operates according to its own mode. Thus the refrigerant circuit 1 operates according to the priority refrigeration production mode in the particular case called balanced refrigeration production, where the heat output produced by the refrigerant circuit 1 is entirely transferred to the heat consumer 200. This operating mode of the refrigerant circuit 1 is identical to the operating mode of the thermodynamic machine 100 with a single refrigerant circuit, which is illustrated in FIG. 7.

The refrigerant circuit 101 operates in turn according to the priority heat production mode in the particular case called heat production only, where the refrigeration power produced by the refrigerant circuit 101 is fully transferred to the source. This operating mode of the refrigerant circuit 101 is identical to the operating mode of the thermodynamic machine 100 with a single refrigerant circuit, which is illustrated in FIG. 3.

In the refrigerant circuit 1, the valve 11 and the pressure reducer 8 are closed. All of the refrigerant in gaseous state and at high pressure at the outlet of the compressors 5 and 6 is directed to a first primary circuit of the condenser exchanger 2, inside of which the refrigerant condenses by yielding heat to the heat transfer fluid circulating in the secondary of this condenser exchanger 2.

At the outlet of the primary of the condenser exchanger 2, the valve 12 is closed and all of the refrigerant in the liquid state and at high pressure enters the pressure reducer 7. The refrigerant undergoes a reduction in its pressure, then it is directed to a first primary circuit of the evaporator exchanger 3, inside which it evaporates by capturing heat from the heat transfer fluid circulating in the secondary of this evaporator exchanger 3. At the outlet of the first primary circuit of the evaporator exchanger 3, the refrigerant in gaseous state and at low pressure joins the reservoir 14 then the compressors 5 and 6.

In the refrigerant circuit 101, the valve 110 being closed, all of the refrigerant in the gaseous state and at high pressure at the outlet of the compressors 105 and 106 is directed to the second primary circuit of the condenser exchanger 2, at the inside which the refrigerant condenses by yielding heat to the heat transfer fluid circulating in the secondary of this condenser exchanger 2.

At the outlet of the second primary circuit of the condenser exchanger 2, the regulator 107 being closed, all of the refrigerant in the liquid state and at high pressure is directed through the valve 112, which is open, towards the regulator 108 The refrigerant undergoes a reduction in its pressure, then it enters the second primary circuit of the source exchanger 4, which then operates as an evaporator, and inside which the refrigerant evaporates by capturing heat. from the external element in contact with the secondary of this source exchanger 4. At the outlet of the second primary circuit of the source exchanger 4, the refrigerant in gaseous state and at low pressure joins the reservoir 114 then compressors 105 and 106.

In this operating mode, the refrigerant circuit 1 produces part of the heat energy transferred to the heat consumer 200 as well as all of the refrigeration energy transferred to the cold consumer 300, with an energy yield corresponding to the temperatures required at the secondary of the condenser exchanger 2 and the secondary of the evaporator exchanger 3. The refrigerant circuit 101 produces the other part of the heat energy transferred to the heat consumer 200 as well as all of the refrigeration energy transferred to the source 400, with an energy efficiency corresponding to the temperatures required at the secondary of the condenser exchanger 2 and at the secondary of the source exchanger 4. The temperature required at the outlet of the secondary of the evaporator exchanger 3 to transfer the cooling energy to the consumer of cold and the temperature required at the end of secondary school source exchanger 4 for discharging cooling energy to the source being generally different, each of the two refrigerant circuits 1 and 101 then works with its own performance, thereby optimizing the overall efficiency of the thermodynamic machine 100.

FIG. 10 illustrates another particular operating mode of a thermodynamic machine illustrated in FIG. 8, and operating generally according to the mode called priority refrigeration production. In this operating mode, the cooling power produced by the thermodynamic machine 100 is adapted to the cooling power required by the cold consumer 300, and the heat power produced by the thermodynamic machine exceeds the calorific power required by the heat consumer 200.

All of the cooling power produced by the thermodynamic machine 100 is transferred to the cold consumer 300 through the evaporator exchanger 3 as represented by the black arrow 303. Part of the heat power produced by the refrigerating machine 100, corresponding to the calorific power required by the heat consumer 200, is transferred to the heat consumer 200 through the condenser exchanger 2 as represented by the black arrow 203. Finally, the remaining part of the calorific power produced by the refrigerating machine 100, not necessary for the heat consumer 200, is transferred to the source 400 through the source exchanger 4 as shown by the black arrow 403.

Even if the machine operates overall according to the priority refrigeration production mode, each of the two circuits 1 and 101 operates according to its own mode. Thus, the refrigerant circuit 1 operates according to the priority refrigeration production mode in the particular case called refrigeration production only, where the heat output produced by the refrigerant circuit 1 is entirely transferred to the source. This operating mode of the refrigerant circuit 1 is identical to the operating mode of the thermodynamic machine 100 with a single refrigerant circuit, which is illustrated in FIG. 6.

The refrigerant circuit 101 operates in turn according to the priority heat production mode in the particular case called balanced heat production, where the refrigeration power produced by the refrigerant circuit 101 is entirely transferred to the cold consumer. This operating mode of the refrigerant circuit 101 is identical to the operating mode of the thermodynamic machine 100 with a single refrigerant circuit, which is illustrated in FIG. 4.

In the refrigerant circuit 1, the regulator 7 and the valve 12 are closed. All of the refrigerant in gaseous state and at high pressure at the outlet of the compressor is directed to the first primary circuit of the source exchanger 4, which then operates as a condenser, and inside which the refrigerant condenses. by yielding heat to the external element which is in contact with the secondary of this source exchanger 4.

At the outlet of the primary of the source exchanger 4, the refrigerant in the liquid state and at high pressure enters the pressure reducer 8 and it undergoes a lowering of its pressure, then it is directed to the first primary circuit of the 'evaporator exchanger 3, inside which it evaporates by capturing heat from the heat transfer fluid circulating in the secondary of this evaporator exchanger 3.

At the outlet of the evaporator exchanger primary 3, the refrigerant in the gaseous state and at low pressure joins the reservoir 14 then the compressors 5 and 6. In the refrigerant circuit 101, the valve 110 is closed. All of the refrigerant in gaseous state and at high pressure at the outlet of the compressor is directed to the second primary circuit of the condenser exchanger 2, inside which the refrigerant condenses by yielding heat to the coolant. circulating in the secondary of this condenser exchanger 2.

At the outlet of the primary of the condenser exchanger 2, the regulator 108 is closed. All the refrigerant in the liquid state and at high pressure is directed to the pressure reducer 107 in which the refrigerant undergoes a reduction in its pressure, then it enters the second primary circuit of the evaporator exchanger 3, inside from which the refrigerant evaporates by capturing heat from the heat transfer fluid circulating in the secondary of this evaporator exchanger 3. At the outlet of the evaporator exchanger primary 3, the refrigerant in gaseous state and at low pressure joins the tank 114 then the compressor.

In this operating mode, the refrigerant circuit 1 produces part of the cooling energy transferred to the cold consumer 200 as well as all of the heat energy transferred to the source 400, with an energy efficiency corresponding to the temperatures required at the secondary level of l evaporator exchanger 3 and at the secondary of the source exchanger 4. The refrigerant circuit 101 produces the other part of the refrigeration energy transferred to the cold consumer 300 as well as all of the heat energy transferred to the heat consumer 200 , with an energy efficiency corresponding to the temperatures required at the secondary of the evaporator exchanger 3 and at the secondary of the condenser exchanger 2.

The temperature required at the outlet of the source exchanger 4 to evacuate the heat energy towards the source and the temperature required at the outlet of the condenser exchanger 2 to transfer the heat energy to the heat consumer being generally different, each of the two refrigerant circuits 1 and 101 then operates with its own efficiency, thus optimizing the overall efficiency of the thermodynamic machine 100.

The thermodynamic machine 100 makes it possible to simultaneously produce heat energy and cooling energy, supplying respectively a consumer of heat and a consumer of cold, and to exchange directly with an external source the residue of thermal energy produced but not used by consumers. In priority heat production mode, this is the residual cooling energy produced but not used by the cold consumer. In priority refrigeration production mode, this is the residual heat energy produced but not used by the heat consumer.

The thermodynamic machine 100 also makes it possible to continuously regulate both the flow temperature of the heat transfer fluid to the consumer of heat energy and the flow temperature of the heat transfer fluid to the consumer of refrigeration energy, thereby continuously adjusting both the heating power and the cooling power supplied respectively to the heat consumer and the cold consumer.

According to one of the embodiments with several refrigerant circuits, it is possible to produce part of the energy with a temperature on the non-priority production side adapted to the temperature required by the consumer, and the other part of the energy with a temperature non-priority production side adapted to the temperature required by the external source, thus optimizing the overall efficiency of the machine.

The thermodynamic machine has a control circuit 500 which is configured to define an operating mode in which the first switching device and the second switching device of the first refrigerant circuit 1 prevent the circulation of the refrigerant in the first heat exchanger 2 and simultaneously the first and the second switching devices of the second refrigerant circuit 101 prevent the circulation of the second refrigerant in the third heat exchanger 4.

The control circuit 500 can also be configured to define an operating mode in which the first switching device and the second switching device of the first refrigerant circuit prevent the circulation of the refrigerant in the third heat exchanger 4 and simultaneously the first and the second switching devices of the second refrigerant circuit 101 prevent the circulation of the second refrigerant in the second heat exchanger 3.

The thermodynamic machine is configured to regulate the heating power and the cooling power simultaneously which is not achieved by the machines of the prior art.

Advantageously, the thermodynamic machine is configured to produce heat energy for heating and / or domestic hot water production applications, for example requiring the heating of a heat transfer fluid to a temperature between 20 ° C. and 100 ° C. The thermodynamic machine can also be configured to produce cooling energy for cooling applications of a heat transfer fluid preferably in the range 0 ° C - 20 ° C.

Although the invention has been described with reference to a particular embodiment, it is in no way limited to this embodiment. It includes all the technical equivalents of the means described as well as their combinations which fall within the scope of the invention.

Claims (11)

claims 1. Thermodynamic machine simultaneously producing heat energy and refrigeration energy, comprising: a first heat exchanger (2) having at least one primary circuit through which a refrigerant circulates and at least one secondary circuit intended to be traversed by a first heat transfer fluid, the first heat exchanger (2) being configured to condense the refrigerant ; a second heat exchanger (3) having at least one primary circuit through which the refrigerant circulates and at least one secondary circuit intended to be traversed by a second heat transfer fluid, the second heat exchanger (3) being configured to evaporate the refrigerant ; a third heat exchanger (4) having at least one primary circuit through which the refrigerant circulates and at least one secondary circuit intended to be traversed by a third heat transfer fluid, the third heat exchanger (4) being configured to evaporate or condense the Refrigerant ; at least one refrigerant circuit (1) inside which the refrigerant circulates, the at least one refrigerant circuit connecting the first heat exchanger (2), the second heat exchanger (3) and the third heat exchanger (4 ); in which the at least one refrigerant circuit (1) comprises: a compressor (5, 6) mounted between an outlet of the second heat exchanger (3) and an inlet of the first heat exchanger (2); a first pressure reducer (7) mounted between an outlet of the first heat exchanger (2) and an inlet of the second heat exchanger (3); a first connecting node (15) connecting the outlet of the compressor (5, 6) to the inlet of the first heat exchanger (2) and to a first switching device (10, 11, 19); a second link node (16) connecting an outlet of the first heat exchanger (2) to an inlet of the first regulator (7) and to a second switching device (12, 13, 20); a third link node (17) connecting an inlet of the second heat exchanger (3) with an outlet of the first regulator (7) and with the second switching device (12, 13, 20); a fourth connecting node (18) connecting an output of the second heat exchanger (3) to an input of the compressor (5, 6) and to the first switching device (10, 11, 19); the first switching device (10, 11, 19) being configured to selectively define a first configuration or a second configuration, the first configuration defining a first refrigerant circulation channel connecting a first inlet / outlet of the third heat exchanger (4 ) at the fourth connection node (18) and preventing the circulation of the refrigerant through the first switching device (10, 11, 19) from the first connection node (15), the second configuration defining a second circulation channel for the refrigerant connecting the first connecting node (15) to the first inlet / outlet of the third heat exchanger (4) and preventing the circulation of the refrigerant through the first switching device (10, 11, 19) up to the fourth link node (18); the second switching device (12, 13, 20) being configured to selectively define a first configuration or a second configuration, the first configuration defining a first refrigerant circulation channel connecting the second connection node (16) to a second input / outlet of the third heat exchanger (4) and preventing the circulation of the refrigerant through the second switching device (12, 13, 20) up to the third connection node (17), the second configuration defining a second channel of circulation of the refrigerant connecting the second inlet / outlet of the third heat exchanger (4) to the third connection node (17) and preventing the circulation of the refrigerant through the second switching device (12, 13, 20) from the second link node (16); a second holder (8) mounted between the second switching device (12, 13, 20) and the second input / output of the third heat exchanger (4). 2. Thermodynamic machine according to claim 1, characterized in that the second holder (8) is a bidirectional regulator. 3. Thermodynamic machine according to one of the preceding claims, characterized in that the compressor comprises a first compressor (5) and a second compressor (6) mounted in parallel between the first heat exchanger (2) and the second heat exchanger (3), the first compressor (5) being a variable speed compressor and the second compressor (6) being an all-or-nothing type compressor, the activation of which is triggered when a calorific power transferred through the first exchanger heat (2) reaches a threshold value or when a cooling power transferred through the second heat exchanger (3) reaches a threshold value. 4. Thermodynamic machine according to one of the preceding claims, characterized in that the first regulator (7) has a variable opening rate and in that it comprises a control circuit (500) configured to control the rate of opening of the first expansion valve (7) in order to regulate the proportion of refrigerant passing through the expansion valve (7) and the second heat exchanger (3) to adjust the cooling power transmitted through the second heat exchanger (3) or to control the opening rate of the first regulator (7) in order to regulate the proportion of refrigerant passing through the regulator (7) and the first heat exchanger (2) to adjust the calorific power transmitted through the first heat exchanger (2). 5. Thermodynamic machine according to the preceding claim, characterized in that the control circuit (500) is configured to regulate the temperature (TCH, TFR) of the heat transfer fluid at the outlet of the first heat exchanger (2) or at the outlet of the second exchanger heat (3) to a set value. 6. Thermodynamic machine according to one of claims 4 and 5, characterized in that the second regulator (8) has a variable opening rate and in that the control circuit (500) is configured to control the ratio of the rate opening the first regulator (7) and the second regulator (8). 7. Thermodynamic machine according to one of the preceding claims, characterized in that it comprises a second refrigerant circuit (101) inside which a second refrigerant circulates, the second refrigerant circuit (101) connecting the first heat exchanger (2), the second heat exchanger (3) and the third heat exchanger (4), the second refrigerant circuit (101) having a compressor (105, 106), a first expansion valve (107), a first connecting node , a second link node, a third link node, a fourth link node, a first switching device, a second switching device and a second pressure reducer (108) arranged similarly to the arrangement of the first refrigerant circuit. 8. Thermodynamic machine according to the preceding claim, characterized in that it comprises a control circuit (500) configured to define an operating mode in which the first and second switching devices of the first refrigerant circuit (1) prevent circulation refrigerant in the third heat exchanger (4) and wherein the first and second switching devices of the second refrigerant circuit (101) prevent the circulation of the second refrigerant in the second heat exchanger (3). 9. Thermodynamic machine according to the preceding claim, characterized in that it comprises a control circuit (500) configured to define an operating mode in which the first and the second switching devices of the first refrigerant circuit (1) prevent circulation refrigerant in the first heat exchanger (2) and wherein the first and second switching devices of the second refrigerant circuit (101) prevent the circulation of the second refrigerant in the third heat exchanger (4). 10. Operating method of a thermodynamic machine comprising the steps: Provide a thermodynamic machine according to one of claims 1 to 6; Switch between a first operating mode and a second operating mode, the first operating mode defining a parallel mounting of the third heat exchanger (4) and the second heat exchanger (3) between the output of the first heat exchanger (2 ) and the inlet of the compressor (5, 6), the second operating mode defining a parallel mounting of the third heat exchanger (4) and the first heat exchanger (2) between the outlet of the compressor (5, 6) and the inlet of the second heat exchanger (3). 11. Method of operating a thermodynamic machine comprising the steps: Provide a thermodynamic machine according to one of claims 7 to 9; Switch between a first operating mode and a second operating mode, the first operating mode defining a first refrigerant circuit (1) in which the refrigerant does not pass through the third heat exchanger (4) and a second refrigerant circuit (101) in which the second refrigerant does not pass through the second heat exchanger (3), the second operating mode defining a first refrigerant circuit (1) in which the refrigerant does not pass through the first heat exchanger heat (2) and a second refrigerant circuit (101) in which the second refrigerant does not pass through the third heat exchanger (4).