DEVICE FOR GENERATING COLD AND HOT FLUIDS IN SEPARATE PHASES

Abstract

Device (10a) for generating a cold fluid (Ff) during a cooling phase, and at least a first hot fluid (Fc1) during a heating phase, implemented at separate times, comprising:- a cold unit (13) comprising a first heat exchanger (16) between a first refrigerant (F1) and the cold fluid (Ff) on the evaporator side; and a second heat exchanger (17) between the first refrigerant (F1) and an intermediate fluid (Fi) on the condenser side;- a first hot unit (18) comprising a third heat exchanger (21) between a second refrigerant (F2) and the intermediate fluid (Fi) on the evaporator side; and a fourth heat exchanger (22) between the second refrigerant (F2) and the first hot fluid (Fc1) on the condenser side;- a circulation pump (30) for the intermediate fluid (Fi) and at least one reservoir (23) for storing calories from the intermediate fluid (Fi) between the cooling and heating phases, so that: - during the cooling phase, the calories carried by the intermediate fluid (Fi) at the outlet of the second heat exchanger (17) are stored in the reservoir (23) increasing the temperature of the reservoir (23); and - during the heating phase, the calories carried by the intermediate fluid (Fi) at the outlet of the third heat exchanger (21) are stored in the reservoir (23) decreasing the temperature of the reservoir (23). Figure for the abstract: Fig 1;

Description

Title of the invention: DEVICE FOR GENERATING COLD AND HOT FLUIDS IN SEPARATE PHASES Technical field

[0001] The invention relates to a device for generating hot and cold thermal fluids at separate times for use in industrial processes.

[0002] The invention can be implemented in a large number of technical fields for which it is desired to produce two heat transfer fluids at distinct temperatures and in distinct phases. For example, the invention finds a particularly suitable application for a process requiring a hot fluid for a heating phase during the production of a product in a reactor and a cold fluid for cooling the finished product before packaging. In addition, the production of hot fluid also allows the preparation of hot water for cleaning the production workshop at the end of the emptying phase. Prior art

[0003] Typically, in the pharmaceutical, cosmetic or food industry, the product manufacturing process includes a formulation phase with heating of the products to a controlled temperature, typically between 30 and 90°C. These temperatures are generally obtained by means of an industrial steam circuit from a gas or oil boiler.

[0004] At the end of this product formulation phase, which can last one or more days, the product is cooled to be packaged in marketing packaging at room temperature, and in particular between 20 and 25°C. This cooling phase uses iced water between 6 and 12°C from a refrigeration unit.

[0005] In addition, a hot energy source is conventionally used to clean and sterilize production equipment at the end of each production phase. These industries, which are subject to strict hygiene and production standards, generally implement a so-called Clean-in-Place (CIP) system to clean their process equipment or highly sensitive areas. Such a CIP system uses hot cleaning solutions where hot water is produced using a gas boiler-type installation and a steam network. This hot water is used to heat the cleaning fluid, for example water, to temperatures of up to 85°C.

[0006] The production cycle of a product therefore includes a production phase during which heat is generated, followed by a packaging phase during which cold is generated, and optionally ends with a cleaning during which heat is generated.

[0007] Thus, the refrigeration unit and the gas boiler used in a production unit (or production workshop) are used at very different times, and the “hot” calories from the heat generated by the refrigeration unit are often evacuated and therefore lost.

[0008] Given the energy crisis and the instability of gas prices, there is currently a need to improve the energy efficiency of these devices for generating hot and cold fluids at separate times. The reuse of the fatal heat from production units remains an important source of cost optimization but also of the reduction of CO2 production linked to gas combustion.

[0009] There are recovery systems for capturing the calories lost by the refrigeration unit, in order to reuse them to supply heating to homes or offices for example, the temperature obtained generally being only suitable for such use, and not being sufficient for supplying hot calories to a production unit. Presentation of the invention

[0010] In this context, the present invention therefore aims to propose an alternative solution for producing hot thermal fluid and cold thermal fluid with characteristics allowing the supply of calories to a production unit, while eliminating the fatal heat from this same production unit.

[0011] In particular, the present invention aims to make available both a low temperature heat transfer fluid and a very high temperature heat transfer fluid which can be used at different times.

[0012] The invention also aims to reduce energy consumption in the production of hot heat transfer energy required for certain manufacturing processes, and in particular in the production of fluid at a temperature above 115°C, suitable for example for heating production reactors as well as for NEP cleaning.

[0013] The invention thus relates to a device for generating a so-called "cold" fluid at a first predefined temperature range, during a cooling phase, and at least one first so-called "hot" fluid at a second predefined temperature range higher than the first temperature range, during a heating phase. The cooling and heating phases are implemented at separate times in the same production cycle. The generation (or production) device comprises a cold unit and a first hot unit.

[0014] The cold group comprises at least: . a compression unit for a first refrigerant fluid; . a unit for expanding the first refrigerant; . a first heat exchanger, incorporating an evaporator, between the first refrigerant fluid and the cold fluid; and . a second heat exchanger, incorporating a condenser, between the first refrigerant and an intermediate fluid.

[0015] The first hot group comprises at least: . a compression unit for a second refrigerant fluid; . a second refrigerant expansion unit; . a third heat exchanger, incorporating an evaporator, between the second refrigerant and the intermediate fluid; and . a fourth heat exchanger, incorporating a condenser, between the second refrigerant and the first hot fluid.

[0016] The generation device of the invention further comprises at least one circulation pump for the intermediate fluid and at least one reservoir for storing calories from the intermediate fluid between the cooling and heating phases, the at least one reservoir being connected to the second heat exchanger and to the third heat exchanger, so that: - during the cooling phase, the calories carried by the intermediate fluid at the outlet of the second heat exchanger are stored in the at least one reservoir, increasing the temperature of the at least one reservoir; and - during the heating phase, the calories carried by the intermediate fluid at the outlet of the third heat exchanger are stored in the at least one tank, reducing the temperature of the at least one tank.

[0017] Thus, the installation of the invention proposes to recover and store the non-useful “hot” calories evacuated by the cold group when the cold group is used, and to reuse these calories subsequently to generate intermediate temperatures suitable for the production of a hot fluid when the hot group is used.

[0018] Similarly, the installation of the invention also proposes to recover and store the “cold” calories not used by the hot group when the hot group is in demand, and to reuse these calories subsequently to generate intermediate temperatures suitable for the production of a cold fluid, and in particular suitable for capturing the fatal calories of the cold group.

[0019] By using two groups that are substantially structurally identical, the installation of the invention thus takes advantage of the fact that the cold group and the hot group are used at very different times, and therefore do not necessarily operate simultaneously, but alternately. The invention thus makes it possible to store the calories evacuated on the condenser side of the cold group to make them available for the hot group, then to store the “non-absorbed” calories on the evaporator side of the hot group. in order to make them available for the capture of calories in the cold group in the next cycle, and so on.

[0020] Advantageously, the generation device may further comprise means for cooling the intermediate fluid stored in the at least one reservoir, these cooling means being coupled to the at least one reservoir and being configured to reduce the temperature of the stored intermediate fluid, when, in the cooling phase, the temperature of said stored intermediate fluid is greater than a first threshold value. The temperature thus reduced is preferably within a temperature range suitable for the recovery of calories in the second heat exchanger of the cold group.

[0021] The cooling means are for example in the form of an air heater.

[0022] Advantageously, the generation device may further comprise means for heating the intermediate fluid stored in the at least one tank, these heating means being coupled to the at least one tank and being configured to increase the temperature of the stored intermediate fluid, when, in the heating phase, the temperature of said stored intermediate fluid is lower than a second threshold value. The temperature thus increased is preferably within a temperature range suitable for providing calories in the third heat exchanger of the heating group.

[0023] These heating means can be of the heating pin type powered by the network or photovoltaic panels or exchangers, and can be integrated into at least one tank.

[0024] In practice, these cooling and heating means are configured to act as emergency equipment providing support in exceptional situations, for example when the demands for heat and / or cold are occasionally higher.

[0025] According to one embodiment, the at least one reservoir consists of a single reservoir, this reservoir being connected to the outlet of the second heat exchanger and to the inlet of the third heat exchanger.

[0026] In this embodiment, the inlet of the second heat exchanger can be connected to the outlet of the third heat exchanger via the cooling means.

[0027] According to another embodiment, said at least one reservoir consists of two calorie storage reservoirs, namely: - a first calorie storage tank connected to the outlet of the second heat exchanger and to the inlet of the third heat exchanger, and - a second heat storage tank separate from the first tank, and connected to the outlet of the third heat exchanger and to the inlet of the second heat exchanger; so that: . in the cooling phase, the calories carried by the intermediate fluid at the outlet of the second heat exchanger are stored in the first tank, increasing the temperature of the first tank; and . in the heating phase, the calories carried by the intermediate fluid at the outlet of the third heat exchanger are stored in the second tank, reducing the temperature of the second tank.

[0028] In other words, the intermediate fluid heated by the cold group in the cooling phase is stored in the first tank, and the intermediate fluid cooled by the hot group during the heating phase is stored in the second tank. The use of two tanks makes it possible to independently store the fatal calories from the second exchanger of the cold group and the third exchanger of the hot group, in particular when the temperature difference of the tanks is significant, which avoids the implementation of complex systems for regulating the temperature of the tanks.

[0029] In this other embodiment, the cooling means are preferably coupled to the second tank; and the heating means are preferably integrated into the first tank.

[0030] According to another embodiment, said at least one reservoir consists of a single reservoir, this single reservoir being connected to the outlet of the third heat exchanger and to the inlet of the second heat exchanger.

[0031] According to this other embodiment, the cooling means may be an air heater coupled to the single tank and configured to be activated during the cooling phase; and the heating means integrated in the single tank are preferably activated during the heating phase.

[0032] In practice, the generation device may further comprise: - a first distribution valve comprising an inlet connected to the outlet of the second heat exchanger, and an outlet configured to selectively direct the intermediate fluid towards the inlet of the third heat exchanger in the heating phase, and towards the inlet of the single reservoir in the cooling phase; and - a second distribution valve comprising an inlet connected to the outlet of the single tank, and an outlet configured to selectively direct the intermediate fluid to the inlet of the second heat exchanger in the cooling phase, and to the inlet of the first valve in the heating phase.

[0033] In other words, the first and second valves are similar to by-pass valve type valves, so as not to stress the heat exchangers of the hot unit or the cold unit which is not operating, or to adapt the flow rates of the inter fluid mediator in circulation according to the needs of the cold or hot groups.

[0034] According to a variant, the generation device may further comprise a circulation pump for the first hot fluid and a second hot group configured to generate, during the heating phase, a second so-called “hot” fluid at a third predefined temperature range higher than the second temperature. The second hot group comprises: - a compression unit for a third refrigerant fluid; - an expansion unit for said third refrigerant; - a fifth heat exchanger between the third refrigerant and the first hot fluid of the fourth heat exchanger, incorporating an evaporator; and - a sixth heat exchanger between the third refrigerant and said second hot fluid, and incorporating a condenser.

[0035] Cascading the first and second hot groups makes it possible to ensure the generation of fluid at very high temperature, in particular above 115°C. In addition, this makes it possible to limit the number of thermal regulation systems for the intermediate fluid contained in the storage tank, since the cold and hot groups could be sized so that the temperature of the intermediate fluid leaving the cold group and the temperature of the intermediate fluid leaving the first hot group are in close temperature ranges. This configuration makes it possible to improve the efficiency of the production of high-temperature hot fluid, with in particular an energy coefficient of performance (COP) of between 3 and 4.

[0036] In practice, the second temperature range of the first hot fluid is between 60 and 95°C and the third temperature range of the second hot fluid is between 115°C and 160°C.

[0037] In a variant suitable for processes including cleaning of the cleaning-in-place type, the generation device may further comprise a seventh heat exchanger between the cold fluid leaving the first heat exchanger and post-cleaning water from a so-called cleaning-in-place CIP process having a temperature of between 40 and 85°C. This seventh heat exchanger is in particular configured to heat the cold fluid generated at the outlet of the refrigeration unit to a temperature suitable for being injected at the inlet of the first heat exchanger, the post-cleaning water being in particular intended to be discharged into the sewer, in particular with a temperature of between 10 and 20°C.

[0038] This variant thus makes it possible to recover the calories carried by these post-cleaning waters before they are discharged into the sewer. For example, by lowering the temperature of the post-cleaning waters to between 15 and 20°C, to recover all the calories from the CIPs. Brief description of the figures

[0039] Other characteristics and advantages of the invention will emerge clearly from the description given below, for information purposes only and in no way limiting, with reference to the appended drawings, in which:

[0040] [Fig.l] is a simplified diagram of the generation device of the invention, according to an embodiment implementing a calorie storage tank;

[0041] [Fig.2] is a simplified diagram of the generation device of the invention, according to another embodiment implementing two calorie storage tanks;

[0042] [Fig. 3] is a simplified diagram of the generation device of the invention, according to another embodiment implementing a heat storage tank; and

[0043] [Fig. 4] is a simplified diagram of the generation device of the invention, according to another embodiment implementing two hot groups in cascade.

[0044] It will be noted that in these figures, the same references designate identical or similar elements and the different structures are not to scale. Furthermore, only the elements essential to the understanding of the invention are represented in these figures for reasons of clarity. Detailed description of the invention

[0045] Devices for generating hot and cold fluids at separate times, according to different embodiments, are illustrated in Figures 1 to 4.

[0046] These 10a-10d generation devices allow the production of a so-called fluid "cold" at a first predefined temperature range during a cooling phase, then the production of a first fluid called "hot" at a second predefined temperature range, higher than the first temperature range, during a heating phase. The cooling and heating phases are thus implemented at separate times.

[0047] These generation devices 10a-10d all comprise a cold group 13, at least one hot group 14, and at least one reservoir for alternately storing calories from an intermediate fluid Fi during the cooling phase and during the heating phase, as well as a circulation pump 30, 31 for the intermediate fluid Fi.

[0048] In practice, these devices 10a-10d further integrate means for regulating the temperature of the intermediate fluid Fi to be injected into the heat exchangers of the hot and cold groups, so as to ensure that the intermediate fluid Fi remains within a temperature range suitable for the operation of the hot and cold groups.

[0049] In particular, these regulation means can be implemented and configured to manage the different needs for hot thermal fluid required by the unit of production, for example for heating reactors, producing hot water for CIPs or producing process hot water. This management is generally carried out by a specific program loaded into a control unit of the installation.

[0050] Furthermore, other means of regulation known as "back-up" can be coupled to the heat storage tank in order to meet the needs in the event of random or abnormal operation of the installation. These other means of regulation can be in the form of an air heater and a heating unit, and configured to ensure the production of cold or the production of heat during abnormal use of the installation, for example when a demand for hot fluid or cold fluid is occasionally greater than a predefined standard operating flow rate.

[0051] The cold group 13 operating according to the principle of a refrigeration group, comprises: . one or more compression units 14 of a first refrigerant fluid Fl; . one or more expansion units 15 of the first refrigerant fluid Fl; . a first or more heat exchangers 16 between the first refrigerant fluid Fl and the cold fluid Ff, this first heat exchanger 16 integrating an evaporator which thus defines for the first refrigerant fluid Fl a circulation path going from the expansion unit 15 to the compression unit 14; and . a second or more heat exchangers 17 between the first refrigerant fluid Fl and an intermediate fluid Fi, this second heat exchanger 17 integrating a condenser which thus defines for the first refrigerant fluid a circulation path from the compression unit 14 to the expansion unit 15.

[0052] The first hot group 18, which operates according to the principle of a heat pump, comprises: . one or more compression units 19 of a second refrigerant fluid F2; . one or more expansion units 20 of the second refrigerant fluid F2; . one or more third heat exchangers 21 between the second refrigerant fluid F2 and the intermediate fluid Fi, this third heat exchanger 21 also integrating an evaporator which defines for the second refrigerant fluid a circulation path from the expansion unit 20 to the compression unit 19; and . one or more fourth heat exchangers 22 between the second refrigerant fluid F2 and the first hot fluid Fc, thus also integrating a condenser defining for the second refrigerant fluid a circulation path from the compression unit 19 to the expansion unit 20.

[0053] The generated cold fluid Ff is sent, via a circulation pump 32, to a cold distribution unit 11 to be used. Similarly, the hot fluid Fc can be sent, via another circulation pump 33, to a hot distribution unit 12 to be used.

[0054] According to an embodiment illustrated in [Fig.l], the generation device 10a integrates a reservoir 23 for storing calories from the intermediate fluid Fi, between the cooling and heating phases. This reservoir 23 is connected to the second heat exchanger 17 and to the third heat exchanger 21. In operation: - during the cooling phase, that is to say when the refrigeration unit 13 is used for the production of cold, the calories recovered and carried by the intermediate fluid Fi at the outlet of the second heat exchanger 17 are stored in the reservoir 23, increasing the internal temperature of the reservoir 23; and - during the heating phase, the calories which have not been transferred to the heating unit and which are therefore carried by the intermediate fluid Fi at the outlet of the third heat exchanger 21, are stored in the tank 23, reducing the internal temperature of the tank 23.

[0055] The intermediate fluid Fi therefore circulates in a closed circuit formed by the second heat exchanger 17, the reservoir 23 and the third heat exchanger 21. A circulation pump 30 ensures this circulation.

[0056] In practice, throughout the cooling phase during which only the cold unit 13 is operating, the intermediate fluid Fi circulates in the second heat exchanger 17 to capture the fatal heat from the cold unit 13, then in the calorie storage tank 23, and finally in the third heat exchanger 21, before being reinjected into the second heat exchanger 17 if the cooling phase is to continue. If the cooling phase ends, the calories stored in the tank 23 are therefore injected into the third heat exchanger 21 and participate in the operation of the hot unit 18.

[0057] Similarly, during the entire heating phase, during which only the hot group 18 operates. The circulation of the intermediate fluid Fi remains unchanged. The intermediate fluid Fi cooled in the third heat exchanger 21 circulates in the second heat exchanger 17 before being stored in the tank 23, and reinjected into the hot group 18 if the heating phase is not finished or into the cold group 13 if the heating phase ends.

[0058] To ensure that the circulating intermediate fluid Fi remains within a temperature range suitable for the operation of the hot and cold units, the generation device 10a of [Fig.l] furthermore incorporates means for regulating the condensation temperature so that the temperature of the fluid Fi allows the storage or release of calories depending on the random operation of the compressors 14 or 19. An air heater 25 arranged upstream of the second heat exchanger 17 makes it possible to compensate during exceptional or abnormal operation.

[0059] According to another embodiment illustrated in [Fig.2], the generation device 10b integrates two calorie storage tanks. A first calorie storage tank 23 is connected to the outlet of the second heat exchanger 17 and to the inlet of the third heat exchanger 21. A second calorie storage tank 24 separate from the first tank 23 is connected to the outlet of the third heat exchanger 21 and to the inlet of the second heat exchanger 17. This configuration allows simultaneous or alternating operation of the hot and cold groups, depending on the needs and in particular the duration of the heating and cooling phases, while allowing the storage of calories from the cold group and their reinjection into the hot group.

[0060] The intermediate fluid Fi therefore circulates in a closed circuit formed by the second heat exchanger 17, the reservoir 23, the third heat exchanger 21 and the second reservoir 24. Circulation pumps 30, 31 ensure this circulation.

[0061] In this configuration, the first tank 23 is intended for storing the calories carried by the intermediate fluid Fi having a temperature included in a first temperature range, and the second tank 24 is intended for storing the calories carried by the intermediate fluid Fi having a temperature included in a second temperature range, preferably lower than the first temperature range. For example, the first tank 23 is intended for temperatures between 50 and 70°C, particularly suitable for the operation of the heating unit for the generation of a thermal fluid at a high useful temperature, for example between 80°C and 140°C, and the second tank 24 is intended for temperatures between 20 and 40°C particularly suitable for the recovery of calories from the operation of the cooling unit for the generation of a cold thermal fluid between -6 and 10°C.

[0062] Thus, in the cooling phase, the calories carried by the intermediate fluid Fi at the outlet of the second heat exchanger 17 can be stored in the first tank 23, and in the heating phase, the calories carried by the intermediate fluid Fi at the outlet of the third heat exchanger 21 can be stored in the second tank 24.

[0063] By way of example, the refrigeration unit 13 can be sized to have the following characteristics: - a thermal regime at the outlet: between -6 and 6°C; - return thermal regime: between 0 and 12°C; - temperature of the intermediate fluid Fi at the inlet of the second heat exchanger 17: between 30 and 50°C; - temperature of the intermediate fluid Fi at the outlet of the second heat exchanger 17: between 50 and 70°C.

[0064] The heating unit 18 can be sized to have the characteristics following:

[0065] - a thermal regime at the outlet: between 80 and 140°C; - return thermal regime: between 80 and 115°C; - temperature of the intermediate fluid Fi at the inlet of the third heat exchanger 21: between 50 and 70°C; - temperature of the intermediate fluid Fi at the outlet of the third heat exchanger 21: between 30 and 50°C.

[0066] The first reservoir 23 can be sized to store calories corresponding to the temperature range 50 to 70°C, and the second reservoir 24 can be sized to store calories corresponding to the temperature range 20 to 40°C.

[0067] In this embodiment, the additional cooling means, such as an air heater 25, are preferably coupled to the second tank 24 and the additional heating means 26 are preferably integrated into the first tank 23. In [Fig. 2], the air heater 25 is, for example, positioned upstream of the second tank 24, following the direction of circulation of the intermediate fluid Fi.

[0068] According to another embodiment illustrated in [Fig. 3], the generation device 10c incorporates a single reservoir 24 for storing calories. The reservoir 24 is connected to the outlet of the third heat exchanger 21 and to the inlet of the second heat exchanger 17. On the same principle as the reservoir 23 of the generation device 10a of [Fig. 1], the reservoir 24 of the generation device 10c of [Fig. 3] is configured to alternately store the calories captured from the cold group in the cooling phase and the calories remaining unabsorbed by the hot group in the heating phase. The regulation of the condensation temperatures makes it possible to store the calories from the cold group or to release the calories to the hot group depending on the needs.

[0069] To prevent the circulation of the intermediate fluid Fi in the cold group when only the hot group is operating, and to prevent the circulation of the intermediate fluid Fi in the hot group 18 when only the cold group 13 is operating, a set of distribution valves, of the by-pass valve type for example, can be installed.

[0070] Thus, as illustrated in [Fig.3], the generation device 10c can further comprise: - a first distribution valve 27 comprising an inlet connected to the outlet of the second heat exchanger 17, and an outlet configured to selectively direct the intermediate fluid Fi towards the inlet of the third heat exchanger 21 in the heating phase, and towards the inlet of the single reservoir 24 in the cooling phase; and - a second distribution valve 28 comprising an inlet connected to the outlet of the single reservoir 24, and an outlet configured to selectively direct the intermediate fluid Fi towards the inlet of the second heat exchanger 17 in the cooling phase, and towards the inlet of the first valve 27 in the heating phase.

[0071] In other words, in this embodiment: - during the entire cooling phase during which only the cold unit 13 operates, the intermediate fluid Fi circulates in a closed circuit formed by the second heat exchanger 17 and the reservoir 24; and - during the entire heating phase during which only the heating group 18 operates, the intermediate fluid Fi circulates in a closed circuit formed by the third heat exchanger 21 and the tank 24.

[0072] Just like the previous embodiments, additional thermal regulation means can be arranged in the generation device 10c, for example in the form of an air heater 25 and a heating unit 26. In [Fig. 3], the air heater 25 is positioned downstream of the reservoir 24, following the direction of circulation of the intermediate fluid Fi. Thus, when the temperature of the intermediate fluid Fi leaving the reservoir 24 is not suitable for the operation of the refrigeration unit 13, the intermediate fluid 24 first passes through the air heater 25 via for example a bypass valve 29, before being injected into the second heat exchanger 21.

[0073] A circulation pump 31 ensures the circulation of the intermediate fluid Fi.

[0074] A variant of the generation device 10c of [Fig.3] is illustrated in [Fig.4], in which an additional hot group 60 cascaded with the hot group 18 of the generation device 10c of [Fig.3]. This cascading may sometimes be necessary, in particular when one wishes to generate high or very high temperatures and maintain optimum COP efficiency for the use of these needs.

[0075] The generation device 10d of [Fig.4] thus comprises, in addition to the generation device 10c of [Fig.3] in which the hot group 18 therefore constitutes the first hot group, a second hot group 60 configured to generate, during the heating phase, a second so-called “hot” fluid Fc2 at a third predefined temperature range higher than the second temperature. This second hot group 60, operating according to the principle of a heat pump, comprises in particular: - a compression unit 29 of a third refrigerant fluid F3; - an expansion unit 30 of said third refrigerant fluid F3; - a fifth heat exchanger 63 between the third refrigerant fluid F3 and the first hot fluid Fcl of the fourth heat exchanger 22, and incorporating an evaporator; and - a sixth heat exchanger 64 between the third refrigerant fluid F3 and said second hot fluid Fc2, and integrating a condenser.

[0076] For this variant, as an example, the cold group 13 can be sized for have the following characteristics: - a thermal regime at the outlet: between -6 and 6°C; - return thermal regime: between 0 and 12°C; - temperature of the intermediate fluid Fi at the inlet of the second heat exchanger 17: between 30 and 45°C; - temperature of the intermediate fluid Fi at the outlet of the second heat exchanger 17: between 35 and 50°C.

[0077] The first hot group 18 can be sized to have the following characteristics: - a thermal regime at the outlet: between 70 and 80°C; - return thermal regime: between 60 and 70°C; - temperature of the intermediate fluid Fi at the inlet of the third heat exchanger 21: between 35 and 50°C; - temperature of the intermediate fluid Fi at the outlet of the third heat exchanger 21: between 30 and 45°C.

[0078] The second hot group 60 can be sized to have the following characteristics: - a thermal regime at the outlet: between 115 and 160°C; - return thermal regime: between 100 and 120°C.

[0079] The reservoir 24 can be sized to store calories corresponding to the temperature range 30 to 50°C.

[0080] In all the embodiments presented, different temperature and flow sensors 40-50 can be distributed in the generation device 10a-10d so as to ensure control and regulation of the different temperatures of the fluid circulating in the generation device 10a-10d. In addition, depending on the calorie requirements in the different cold and hot groups, all or part of the calories from the reservoir(s) can be used.

[0081] Furthermore, in a variant, when the generation device 10a-10d is implemented in processes including cleaning-in-place (CIP) type cleaning, it is possible to recover the calories carried by the post-cleaning water before their discharge to the sewer to slightly heat the cold fluid generated by the cold unit, via for example a heat exchange system. For example, the generation device 10a-10d may further comprise a seventh heat exchanger between the cold fluid at the outlet of the first heat exchanger of the cold unit and this post-cleaning water generally having a temperature of between 40 and 85°C. This seventh heat exchanger is advantageously configured to heat the cold fluid generated at the outlet of the cold unit to a temperature suitable for being injected at the inlet of the first heat exchanger of the cold unit.

[0082] Thus, the installation of the invention allows the production of hot and cold useful fluids at temperatures adapted to the requirements of industrial applications, and available at different times, while reducing the energy consumed in the production of these fluids. Preferably, the energy source allowing the operation of the installation of the invention will preferably be exclusively electrical from distribution networks or a renewable energy park such as a photovoltaic or wind panel.

[0083] Thus, the installation of the invention makes it possible to produce thermal fluids for an industrial process unit with an electrical energy consumption three times lower than the production of cold and hot thermal fluids, with an overall COP efficiency of around 3. The connection of the system of the invention to an industrial production unit makes it possible to compensate for the need for cold by the need for heat.

Claims

1. Claims Device for generating (10a-10d) a so-called "cold" fluid (Ff) at a first predefined temperature range during a cooling phase, and at least a first so-called "hot" fluid (Fcl) at a second predefined temperature range higher than the first temperature range, during a heating phase, the cooling and heating phases being implemented at separate times, said generating device (10a-10d) comprising: - a cold group (13) comprising: . a compression unit (14) of a first refrigerant fluid (Fl); . an expansion unit (15) of the first refrigerant fluid (Fl); . a first heat exchanger (16), incorporating an evaporator, between the first refrigerant fluid (Fl) and the cold fluid (Ff); and . a second heat exchanger (17), incorporating a condenser, between the first refrigerant fluid (Fl) and an intermediate fluid (Fi); - a first hot group (18) comprising: . a compression unit (19) of a second refrigerant fluid (F2); . an expansion unit (20) of the second refrigerant fluid (F2); . a third heat exchanger (21), incorporating an evaporator, between the second refrigerant fluid (F2) and the intermediate fluid (Fi); and . a fourth heat exchanger (22), incorporating a condenser, between the second refrigerant fluid (F2) and the first hot fluid (Fcl); characterized in that it further comprises at least one circulation pump (30, 31) for the intermediate fluid (Fi) and at least one reservoir (23, 24) for storing calories from the intermediate fluid (Fi) between the cooling and heating phases, the at least one reservoir (23, 24) being connected to the second heat exchanger (17) and to the third heat exchanger (21), so that: - during the cooling phase, the calories carried by the intermediate fluid (Fi) at the outlet of the second heat exchanger (17) are stored in the at least one reservoir (23, 24) increasing the temperature of the at least one reservoir (23, 24); and - during the heating phase, the calories carried by the intermediate fluid (Fi) at the outlet of the third heat exchanger (21) are stored in the at least one reservoir (23, 24) reducing the temperature of the at least one reservoir (23, 24) and in that it further comprises means (26) for heating the fluid intermediate fluid (Fi) stored in the at least one reservoir (23, 24), said heating means being coupled to the at least one reservoir (23, 24) and being configured to increase the temperature of the stored intermediate fluid (Fi), when, in the heating phase, the temperature of said stored intermediate fluid (Fi) is lower than a second threshold value, said increased temperature being within a temperature range suitable for providing calories in the third heat exchanger (21) of the heating group (18) for the generation of the first hot fluid (Fcl) at said second temperature range.

2. Generation device (10a-10d) according to claim 1, further comprising means (25) for cooling the intermediate fluid (Fi) stored in the at least one reservoir (23, 24), said cooling means (25) being coupled to the at least one reservoir (23, 24) and being configured to reduce the temperature of the stored intermediate fluid (Fi), when, in the cooling phase, the temperature of said stored intermediate fluid (Fi) is greater than a first threshold value, said reduced temperature being within a temperature range suitable for the recovery of calories in the second heat exchanger (17) of the cold group (13).

3. Generation device (10a-10d) according to claim 2, in which the cooling means (25) are in the form of an air heater.

4. 4. Generation device (10a-10d) according to one of claims 1 to 3, wherein said heating means (26) are integrated in the at least one reservoir (23, 24).

5. 5. Generation device (10a-10d) according to one of claims 1 to 4, wherein the at least one reservoir (23, 24) consists of a reservoir (23) connected to the outlet of the second heat exchanger (17) and to the inlet of the third heat exchanger (21).

6. 6. Generation device (10a-10d) according to claim 5, wherein the inlet of the second heat exchanger (17) is connected to the outlet of the third heat exchanger (21) via said cooling means (25).

7. 7. Generation device (10a-10d) according to one of claims 1 to 4, in which the at least one reservoir consists of: - a first reservoir (23) for storing calories connected to the outlet of the second heat exchanger (17) and to the inlet of the third heat exchanger (21), and - a second reservoir (24) for storing calories separate from the first tank (23) and connected to the outlet of the third heat exchanger (21) and to the inlet of the second heat exchanger (17), and in which: . in the cooling phase, the calories carried by the intermediate fluid (Fi) at the outlet of the second heat exchanger (17) are stored in the first tank (23) increasing the temperature of the first tank (23); and . in the heating phase, the calories carried by the intermediate fluid (Fi) at the outlet of the third heat exchanger (21) are stored in the second tank (24) decreasing the temperature of the second tank (24).

8. 8. Generation device (10a-10d) according to claims 2 and 7, wherein: - the cooling means (25) are coupled to the second reservoir (24); and - the heating means (26) are integrated in the first reservoir (23).

9. 9. Generation device (10a-10d) according to one of claims 1 to 4, in which the at least one reservoir consists of a single reservoir (24) connected to the outlet of the third heat exchanger (21) and to the inlet of the second heat exchanger (17).

10. 10. Generation device (10a-10d) according to claims 2 and 9, wherein: - the cooling means (25) are an air heater coupled to the single tank (24) and configured to be activated during the cooling phase; and - the heating means (26) integrated in the single tank (24) are activated during the heating phase.

11. 11. Generation device (10a-10d) according to one of claims 9 or 10, wherein the device further comprises: - a first distribution valve (27) comprising an inlet connected to the outlet of the second heat exchanger (17), and an outlet configured to selectively direct the intermediate fluid (Fi) towards the inlet of the third heat exchanger (21) in the heating phase, and towards the inlet of the single reservoir (24) in the cooling phase; - a second distribution valve (28) comprising an inlet connected to the outlet of the single reservoir (24), and an outlet configured to selectively direct the intermediate fluid (Fi) towards the inlet of the second heat exchanger (17) in the cooling phase, and towards the inlet of the first valve (26) in the heating phase.

12. 12. Generation device (10a-10d) according to one of claims 1 to 11, further comprising a circulation pump (34) for the first hot fluid (Fcl) and a second hot group (60) configured to generate, during the heating phase, a second so-called "hot" fluid (Fc2) at a third predefined temperature range higher than the second temperature, said second hot group (60) comprising: - a compression unit (29) for a third refrigerant fluid (F3); - an expansion unit (30) for said third refrigerant fluid (F3); - a fifth heat exchanger (63), incorporating an evaporator, between the third refrigerant fluid (F3) and the first hot fluid (Fcl) of the fourth heat exchanger (22); - a sixth heat exchanger (64), incorporating a condenser, between the third refrigerant fluid (F3) and said second hot fluid (Fc2).

13. 13. Generation device (10a-10d) according to claim 12, wherein the second temperature range of the first hot fluid (Fcl) is between 60 and 95°C and the third temperature range of the second hot fluid (Fc2) is between 115°C and 160°C.

14. 14. Generation device (10a-10d) according to one of claims 1 to 13, further comprising a seventh heat exchanger (36) between the cold fluid leaving the first heat exchanger (16) and post-cleaning water from a so-called cleaning-in-place CIP process having a temperature between 40 and 85°C, and configured to heat said cold fluid (Ff), said post-cleaning water being intended to be discharged into the sewer with a temperature between 10 and 20°C.

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