WO2011015731A1 - Modular multi-energy thermodynamic device - Google Patents

Abstract

The invention relates to a system (1) for simultaneously producing very hot water at a temperature T2, hot water (14) at a temperature T1, and/or cold water (13) at a temperature T3, and electricity (20), and optionally, producing a refrigerant at an evaporation temperature T4, and/or producing a refrigerant at an evaporation temperature T5, and including at least one current-generating unit that includes a combustion engine (2) connected to an alternator (18) or to a fuel cell, and said system (1) also including at least one heat pump (3), or a refrigeration unit and optionally an electrical battery (19), said system (1) being characterized in that (a) the compressor (17) or the circulation pump is driven by an electric motor, which may be powered by one of said current generators, and in that (b) said system (1) includes at least one module Pc referred to as a “heat pump module” (36) or at least one module Pr referred to as a “refrigeration module” or at least one so-called "mixed" heat pump and refrigeration module Pm, and in that said generator unit is inside a generator module (G), each of said modules (G1Pc, Pa, Pr, Pm) being provided with a frame and a unit forming an assembly interface that are produced such that said modules (G1Pc, Pa, Pr, Pm) can be assembled together, one after the other, to form a single unit.

Description

 Modular multi-energy thermodynamic device

Field of the invention

The invention relates to a system or device of modular design comprising at least one electric power generating module and one or more modules of the following types: heat pumps, refrigeration or mixed heat pump / refrigeration modules, allowing the simultaneous production of hot water for example for heating buildings, very hot water, for example hot water, cold water, for example for air conditioning, possibly refrigerant typically for refrigeration and possibly electricity.

State of the art

 There are known systems consisting of heat pumps operated by internal combustion engines and using a vapor compression refrigeration cycle. Patent Application EP 1 628 096 (LG Electronics Inc.) describes such a system. These systems are commonly used in Japan for several years for air conditioning (cooling) in the summer and heating in winter buildings such as office buildings or hotels, and the simultaneous production of hot water. These systems are most of the time so-called direct expansion systems that is to say that they directly send a refrigerant to individual indoor units. These are generally VRV (variable refrigerant volume) or VRF (variable refrigerant flow) type installations.

 Such systems allow the production of hot water, for example domestic hot water, through the use of the heat generated by the combustion engine in operation. However, one of the major drawbacks of these systems is that the heat pump can not function properly by taking the necessary calories from the outside air when the outside temperature is less than about

10 ⁰ C because it causes frosting of the evaporator. In practice, in winter, the engine heat is used to heat the evaporator to allow the thermodynamic system to continue to operate with good efficiency when the outside temperature is below 10 ⁰ C (up to about -20 ⁰ C), the disadvantage being in this case that no more water is produced at very high temperature and the overall efficiency of the system becomes quite low.

 Furthermore, the document EP 1 628 096 only provides the end user with water at a single temperature, that of hot water, and when the system is in air conditioning mode. In a variant, the system comprises several units, in particular indoor units and outdoor units, connected by refrigerant pipes. In this case also, a single water temperature can be provided by the system, it is the domestic hot water provided in cooling system mode.

To overcome this drawback, the system described in EP 2 085 721 of the applicant uses a cogeneration assembly connected to a heat pump so as to provide the user, simultaneously, with water at several different temperatures. However, the described system is designed for specific refrigeration, heating and electrical power values, specific to a given application. The system is designed as a single, indivisible set, so it does not allow any design or usage flexibility and must be fully resized for any new application.

 On the other hand, the existing systems have powers limited to maximum values of the order of 75 kW because they use motor motors of limited power, and refrigeration components also do not allow to operate at higher powers.

 Another disadvantage of existing systems is that their sizing must be adapted to the specific needs of the user in water at different temperatures. However, these needs, both for their total quantity and for their distribution over the different water temperatures, can vary according to the season, the way of life or during a day. Systems according to the state of the art lack, on the one hand, flexibility in their use. On the other hand, their correct sizing according to the needs of their user generally requires a custom design, or at least the ability to select the appropriate system in a wide range of different sizing products.

The problem that the present invention aims to solve is to overcome these disadvantages of the state of the art. Object of the invention

 A first object of the invention is a system (1) for the simultaneous production of very hot water at temperature T2, hot water (14) at temperature T1 and / or cold water (13) at temperature T3, and electricity (20), and optionally also the production of refrigerant at T4 evaporation temperature, and / or the production of refrigerant at T5 evaporation temperature, and said system comprising at least one current generating assembly which comprises either a combustion engine (2) connected to an alternator (18) or a fuel cell (22), each of the current generators also having a heat exchanger (8) producing very hot water at temperature T2, and said system (1) or current generating assembly optionally including one or more other current generators selected from the group consisting of a combustion engine (2) connected to an alternator (18), a fuel cell (22), a photovoltaic solar panel (23), or a wind turbine,

and said system (1) also comprising at least one heat pump (3), or a refrigeration unit and possibly an electric accumulator (19), said heat pump or said refrigeration unit being (i) of the compression type of steam and then comprising at least one compressor (17) of refrigerant, a first heat exchanger (11, 66) located at the suction of the compressor (17) when the system (1) is in cooling mode, a pressure reducer ( 10), and a second heat exchanger (12) placed at the discharge of the compressor (17) when the system (1) is in cooling mode, and possibly a third heat exchanger (15) located at the discharge of the compressor (17) when the system (1) is in the cooling mode and used for heating the hot water (14), (ii) the absorption type and then comprising an absorber (28), a circulation pump (30), a generator of steam (29), a first exchanger heat sink (31) at the inlet of said absorber (28), an expander (32) and a second heat exchanger (33) at the outlet of said steam generator (29),

 Said system (1) being characterized in that

(a) the compressor (17) or circulation pump (30) is driven by an electric motor, which can be powered by one of said current generators, and in that

(b) said system (1) comprises at least one module Pc ₁ Pa called "heat pump module" (36,37) or at least one module Pr said "refrigeration module" (36A) or at least one module Pm ( 36B) said "mixed: heat pump and refrigeration" comprising, (b1) in the case of a compression heat pump module Pc (36), each at least one heat pump assembly comprising at least one refrigerant compressor (17), said first heat exchanger (11) ), said expander (10), said second heat exchanger (12), and optionally said third heat exchanger (15);

 (b2) if it is an absorption heat pump module Pa (37), each an absorber (28), said circulation pump (30), said steam generator (29), said first heat exchanger heat (31), said expander (32) and said second heat exchanger (33);

(b3) if it is a refrigeration module Pr (36A), each at least one refrigeration assembly comprising at least one compressor (17) of refrigerant, said expander (10), said second heat exchanger ( 12), and optionally said third heat exchanger (15), as well as refrigerant conduits (16a, 16b) for connection to an air / water refrigerant exchanger (66) external to the Pr module (36A);

 (b4) if it is a mixed module Pm (36B), two sets, one of the heat pump type and the other of the refrigeration type, where

 the entire heat pump type comprises at least one refrigerant compressor (17), said first heat exchanger (11), said expander (10), said second heat exchanger (12), and possibly said third exchanger heat (15), and

the refrigeration type assembly comprises at least one refrigerant compressor (17), said expander (10), said second heat exchanger (12), and optionally said third heat exchanger (15) as well as refrigerant conduits; (16a, 16b) for connection to an air / water refrigerant exchanger (66) external to the Pm module (36) and in that said generator assembly is included within a generator module (G), said modules (G ₁ Pc, Pa, Pr, Pm) each being provided with a frame and an assembly forming a mounting interface made so that said modules (G ₁ Pc, Pa, Pr, Pm) can be to assemble between them, one after the other, and form a unitary whole. By system allowing the simultaneous production of water at several temperatures, and possibly refrigerant, includes a system capable of producing and supplying the user with water and possibly refrigerant at specified temperatures via appropriate collectors which connect the unitary unit thus obtained to the installation of the user.

 According to the invention, the number and type of modules is chosen as a function of the heating and / or refrigerating and electrical power required to operate the system to adapt it to a given application, and this from its conception. Such a modular construction offers a wide range of system design solutions, adapting the number and type of modules to each use case. Furthermore, the system also has a flexibility of use because it takes into account a multiplicity of energies that can feed the system, as well as a multiplicity of energy flows that can be produced by the system.

The system of the invention is of modular construction, it allows to connect together several complex modules, including cogeneration and thermodynamics, by simplifying the interfaces to obtain a unitary unit or unit, preferably easily transportable by truck. Thus, the complexity of the design is concentrated inside the modules, the interfaces between modules being simplified to the maximum. The modules preferably have frames of identical height and width to connect to each other by means of appropriate mechanical connection means.

 This allows standardization of components, reduction of component purchase costs by increasing volumes, reduction of development time, simplification of production.

 A system will therefore be defined by optimally choosing the modules that will be standardized, in particular by their internal functions and the choice of interfaces in order to obtain a system corresponding to the needs of the end user.

 The system of the invention meets the needs of applications such as:

1 / Heating, domestic hot water and air conditioning of tertiary or residential buildings:

This leads to a variable thermal need according to the sizes of buildings, according to their insulation levels, according to their types (hospitals, hotels, retirement homes or offices) and according to their location (north or south of Europe). The preferred fluid is water at temperature T1 (heating), T2 (domestic hot water) and (T3) (air conditioning). For some applications, there may be simultaneous cooling and heating requirements in some parts of the building.

2 / Heating, domestic hot water, air conditioning and supply of cooling energy for refrigeration needs for supermarket applications.

 In addition to the points discussed in the previous paragraph, the need for cooling capacity in the form of refrigerant at temperature T4 and T5 in variable proportion according to the applications is added.

3 / Heating, electricity production and possibly air conditioning of agricultural greenhouses:

 In this case, there are large heating requirements in the form of hot water at temperatures T1 and T2 and often have competitive natural gas tariffs. Any excess of electricity can be resold.

Al Agricultural installation of biomass producing biogas:

 There is local production of primary energy to cover the needs of heating and electricity with the resale of the surplus of it; There is a need for hot water at temperatures T1 and T2. Excess electricity can be resold

The different modules used by the system will be described and the powers provided to the system will be given by way of example in the following:

 - The cogeneration module (or generator module G) which allows the generation of heating power in the form of hot water at T2 temperature and electricity

Internal functions of the module:

Each engine includes one or two engines among the possible choices (non-limiting) of 2 liters and 4.6 liters

 The electrical power can be used locally by other modules or sent externally on the customer's power grid

The thermal power is transferred via a regulated valve to central hot water pipes T1 or hot water T2 according to the respective needs of the application. 2-liter engine: up to 25 kW of electricity and up to 35 kW of heat output at T2

 4.6 liter engine: up to 55 kW of electricity and simultaneously 80 kW of heat output at T2 temperature

Minimum power: 1 engine 2 liters: 25 kW electric and 35 kW heat

 Maximum power: 2 engines 4.6 liters: 110 kW electric and 160 kW heat

- The reversible heat pump module (Pc) that allows the production of hot water at temperature T1 or cold water at temperature T3 using the compression refrigeration cycle

Internal functions of the module: Each module includes two independent refrigeration units connected to the central water pipes, and a control system.

 Each set produces about 65kW of cold water at T3 temperature or about 80kW of hot water at T1 temperature (not simultaneously)

Each module of this type produces: about 13OkW of cold water at T3 temperature or about 16OkW of hot water at T1 temperature (non-simultaneous way)

 - The heat pump module with optional heat exchanger (Pc) which allows the production of hot water at temperature T1 and cold water at simultaneous temperature T3 using the compression refrigeration cycle

Internal functions: Each module includes two independent refrigeration units connected to the central water pipes, and a control system.

 Each of the two assemblies can produce about 65kW of cold water at T3 temperature or about 80kW of hot water at T1 temperature as the reversible heat pump module but it can also produce if necessary these two powers simultaneously

Each module of this type can therefore produce: about 13OkW of cold water at temperature T3 or about 160 kW of hot water at temperature T1 as the reversible heat pump module but it can also produce if necessary these two powers simultaneously is about 13OkW refrigeration energy in the form of cold water at temperature T3 and about 160 kW of heat energy in the form of hot water at temperature T1. - The refrigeration module (Pr) which allows the production of refrigerant at temperature T4 or T5 using the compression refrigeration cycle

 Internal functions: Each module includes two independent refrigeration units connected to the central refrigerant piping, and a control system

 Each of the two assemblies can produce approximately 40kW of cooling capacity in the form of refrigerant at temperature T4 or approximately 20kW of refrigerant at temperature T5.

Each module of this type can therefore produce about 8OkW of cooling capacity in the form of refrigerant at temperature T4 or about 40 kW of refrigerant at temperature T5.

 - The reversible heat pump / refrigeration module (Pm):

 Furthermore, each of the three modules above (heat pump modules and refrigeration module) is composed of two independent assemblies achieving the desired function, so we can have mixed modules including for example a reversible heat pump assembly and a set refrigeration (example in figure 13):

 So hot water is produced at temperature T1 (about 8OkW) or cold water at temperature T3 (about 65kW) and simultaneously production of refrigerant at temperature T4 (about 4OkW) or at temperature T5 (about 2OkW)

 - The absorption heat pump module (Pa): Production of hot water at temperature T1 using the absorption cycle. The heat output is approximately 35 kW

Advantageously, said assembly interface assembly comprises: a mechanical interface, an electrical interface and a fluid interface.

The system of the invention is of modular construction and comprises at least one electric current generating module and one or more so-called "production" modules each comprising one or two sets of heat pump or refrigeration. By modular building system, it comprises a system comprising at least two modules, each module having a chassis forming support for its components, as well as mechanical, electrical and fluidic connection means to the adjacent module. Preferably, the modules are made so that, when connected, they have the same template at least in one dimension (for example the width of the module), and even more advantageously in two dimensions (width and height). A production module may include a heat pump assembly or a refrigeration assembly. In an advantageous variant of the invention, a production module may comprise two sets of the same type, for example two heat pump assemblies or two refrigeration assemblies, on a common chassis. In another advantageous variant of the invention, a production module is a mixed module, that is to say that it comprises a heat pump assembly and a refrigeration assembly on a common chassis.

Interfaces between modules are limited to the maximum, they are of three types:

- Mechanical interfaces: the modules have frames of identical height and width to connect to each other by means of appropriate mechanical connection means

 - Electrical and electronic interfaces: the regulation specific to each module makes it possible to limit the electronic interfaces (mainly by communication bus) and electrical interfaces (in particular the power cables of the compressors)

- Fluidic interfaces, especially hydraulic and refrigerant: they are located in the same place for all modules (preferably in the central part, such as the product shown in the drawings). They constitute the path of passage and transfer of heat energy to the outside of the modular system of the invention.

Once these interfaces are made, the product is in the form of a single unit or unitary unit transportable in one piece for example by truck.

Advantageously, up to six modules can be assembled together, including one or two cogeneration modules (a cogeneration module at each end of the machine).

The electrical and thermal powers of the various modules of this monobloc assembly are then combined. For example, the megawatt is approaching in terms of heat energy. The available electrical energy will be used locally by the modules or sent externally to the customer network according to the respective needs.

 The regulation of the whole will then aim at the overall energy optimization of the machine

Thus, a system comprising six modules thus defined, advantageously makes it possible to fulfill the functions corresponding to the following applications:

 1 / Heating, domestic hot water and air conditioning of tertiary or residential buildings:

 Depending on the respective power requirements on the one hand air conditioning and heating (possibly simultaneous in a given proportion), on the other hand domestic hot water and finally possible electrical back up, we can configure one or two modules generators associated with heat pump modules of possibly different type. This in order to stick to the needs with a single machine.

2 / Heating, domestic hot water, air conditioning and supply of cooling energy for refrigeration needs for supermarket applications.

 The response to multiple needs will rely on refrigeration modules

 We can then have a set consisting of one or two cogeneration modules associated with one or more refrigeration modules themselves supplemented with heat pump modules. The set allows an adapted, coherent and monobloc answer to a complex problem.

 3 / Heating, electricity production and possibly air conditioning of agricultural greenhouses:

 The maximum cogeneration power associated with heat pump modules will typically be found. The monobloc product avoids the use or construction of a technical room.

 4 / Agricultural plant of biomass producing biogas:

The available primary energy powers are related to the size of the biogas-producing biogas plants by biomass. This available power range is well adapted to the cogeneration modules of the system of the invention. The system 1 of the invention also comprises at least one refrigeration module 36A ₁ and optionally an electric accumulator 19, said module comprising at least one refrigeration assembly which is of the vapor compression type and then comprising at least one compressor 17 of refrigerant, an expander 10, a heat exchanger 12 placed at the discharge of the compressor 17, and optionally a third heat exchanger 15 located at the discharge of the compressor 17 when the system 1 is also used for heating the hot water 14, the system also comprising refrigerant conduits intended to be connected to a refrigerant / air type exchanger 66 situated outside the module, or even outside the system, typically, but not exclusively, in particular for refrigeration applications of foodstuffs. The exchanger 66 is essential for operation. However, it is not located physically in the module comprising the compressors. The exchanger 66 may be located in a specific isothermal module forming part of the modular design system (role of cold room outside the building for example). The exchanger 66 may also be located away from the modular design system, in the enclosure of a building (supermarket-type application, for example). More particularly according to the invention in this case,

 (a) the compressor 17 is driven by an electric motor, which can be powered by one of said current generators, and

 (b) said system 1 comprises at least one module Pr said "refrigeration module" comprising, each at least one refrigerant compressor 17, said expander 10, said heat exchanger 12, possibly said heat exchanger 15, and ducts of refrigerant (16a, 16b) intended to be connected to a heat exchanger 66 not being physically located in the module, but being essential to its operation.

The combustion engine type current generator may be included in a module G said current generator module; this module G may comprise one or more other current generators selected from combustion engines and fuel cells, or these other current generators may be integrated into a second current generator module. The current generating module (s) may advantageously comprise connections for connecting one or more external current sources such as a photovoltaic solar panel (23), a wind turbine, or an electrical network. Said current generators can be AC or DC generators. In an advantageous embodiment, the first current generator is a combustion engine 2 connected to an alternator 18. In this case, the alternating current can supply said compressor 17 with alternating current (a part that can be introduced into an external electrical network to the system 1), or it can be converted into direct current for supplying said compressor 17 operating with direct current and / or for recharging the electric accumulator 19. The same is true for the other generators of currents if they produce current alternative (such as a combustion engine, a wind turbine or a turbine). If one of the other current generators is a direct current generator (for example the fuel cell 22 or the photovoltaic panel 23), this direct current can either be used directly by the compressor 17, if the latter operates with direct current and / or by the electric accumulator 19, be converted into alternating current, for use by the compressor 17 operating with alternating current, and / or to be introduced into an external electrical network to the system 1.

 Advantageously, said heat pump or refrigeration unit uses the refrigeration cycle by vapor compression.

 The system according to the invention is very advantageously designed so that it can be powered by an external electrical network to cover, in part or in full, its electrical energy requirements, and so as to be able to send to said external electrical network at least one part of the electrical energy produced by said system.

 A second object of the invention is a method of regulating a system according to the invention.

Description of figures

 Figures 1 to 19 refer to the invention which they illustrate particular embodiments.

 FIG. 1 represents a schematic diagram of the system according to the invention, in the case where the AC generator is a combustion engine connected to an alternator and the heat pump uses the vapor compression refrigeration cycle.

FIG. 2 represents a schematic diagram of the system according to the invention, in the case where the alternating current generator is a photovoltaic solar panel or a fuel cell connected to an AC direct current converter and the heat pump uses the vapor compression refrigeration cycle.

 Figure 3 shows the energy efficiency of the system according to the invention in the case of the heat pump compared to the yields of various systems of the state of the art.

 FIG. 4 represents a schematic diagram of the system according to the invention, in the case where the AC generator is a combustion engine connected to an alternator and the refrigeration module uses the vapor compression refrigeration cycle.

FIG. 5 represents a block diagram of a system of the invention according to a variant of the invention, the system comprising several current generator modules connected to several heat pump modules.

 FIG. 6 represents a block diagram of a system of the invention according to a variant of the invention, the system comprising a plurality of current generator modules connected to a heat pump module and to several refrigeration modules. Figure 7 shows a block diagram of a system of the invention in the case where the AC generator is a combustion engine connected to an alternator and the heat pump uses the absorption refrigeration cycle.

 FIG. 8a is a side view, FIG. 8b is a front view and FIG. 8c is a sectional view along the AA plane of FIG. 8b of a system according to another variant of the invention in which the system comprises a module. generator connected to several heat pump modules of different types.

 FIGS. 9a to 9f represent different views of a compression heat pump module according to the invention comprising two heat pump assemblies provided with the optional exchanger 15.

FIG. 10a is a side view, FIG. 10b is a front view and FIG. 10c is a sectional view along plane C-C of FIG. 10b of an absorption heat pump module according to the invention.

 FIG. 11a is a side view, FIG. 11b is a front view, and FIG. 11c is a sectional view along the D-D plane of FIG. 11b of a generator module according to the invention.

Figures 12a to 12f show different views of a refrigeration module having two refrigeration assemblies. Figures 13a to 13f show different views of a mixed heat pump and refrigeration module.

 FIGS. 14a to 14c show different views of an exemplary system of the invention comprising a generator module and a mixed heat pump and refrigeration module.

 FIG. 15 represents an exemplary system comprising a generator module, a mixed heat pump and refrigeration module and a refrigeration module type module comprising two refrigeration units.

 FIG. 16 represents an example of a system according to the invention comprising a generator module, a mixed heat pump and refrigeration module, of the refrigeration module type comprising two refrigeration assemblies and two isothermal modules.

 Figure 17 shows a block diagram of the compression heat pump assembly made according to a first mode of operation.

Fig. 18 shows a block diagram of the compression heat pump assembly constructed in a second mode of operation.

 FIG. 19 represents a block diagram of a fuel cell equipped with a reforming or reformer assembly, said battery belonging to the generator module.

List of landmarks

 System according to the invention

 2 combustion engine

 3 Heat pump

 4 Liquid or gaseous fuel input

 5 Mechanical energy produced by the engine

 6 Heat emitted by the AC generator in operation

7 Energy losses

 8 Heat exchanger for heat exchange between the AC generator and hot water

 9 Very hot water circuit

 10 Regulator

 10A Expansion valve A (optional circuit with exchanger 15)

1B Expansion valve B (optional circuit with exchanger 15) OC Expansion valve C (optional circuit with exchanger 15) 1 Water / refrigerant heat exchanger (evaporator in cooling mode)

2 Air / refrigerant heat exchanger - (evaporator in heating mode, and condenser in cooling mode)

3 Water circuit - cold water circuit when the heat pump is in cooling mode

4 Hot water circuit

5 Refrigerant heat exchanger / recovery water circuit 6 Refrigerant circuit

6a Refrigerant suction line

6b Liquid refrigerant line

7 Compressor

8 Alternator

9 Storage battery

0 Electric energy

1 Motorcycle fan

2 Fuel cell

2A reformer

2B Stack Heart

2C Reforming reactor

2D Desulphurization unit

2E WGS unit (water gas shift)

2F Combustible fluid (natural gas, bio gas etc ...)

2G Hydrogen

2H Electricity

3 Photovoltaic solar panel

4 AC DC Converter

5 Solar energy

6 Fuel (for the fuel cell)

7 Heat pump using the absorption cycle

8 Absorber

9 Generator

0 Circulation pump

1 Evaporator of the absorption cycle

2 Regulator adapted to the absorption cycle 33 Absorption Cycle Condenser

 34 Refrigerant

 35 Absorber

 36 Compression heat pump module

36A Refrigeration module

 36B Mixed module: heat pump and refrigeration

 36C Isothermal module

 36D Heat pump assembly

 36E Refrigeration set

 37 Absorption heat pump module

 38 Current generator module

 39a, b, c, Collectors connecting water exchangers

d,

 40 Gas piping connecting the heat pump modules by absorption

 41 Power cable

 42 Control cable

 44 Heat Pump Module Chassis

 46 4-way valve

 47 Refrigeration compressor

 48 Bottle anti-blow of liquid

 50 Liquid tank

 51 Absorber

 52 Generator

 53 Refrigerant / water plate heat exchanger in the absorption cycle

 54 Refrigerant / air plate heat exchanger in absorption cycle

 55 Fuel inlet

 56 Heat engine assembly and its alternator

 57 Fuel cell and its inverter block

 58 Connecting external thermal sources

 59 Heat exchanger for heat exchange between the generator and the hot water

 60 Cabinet power and global regulation system

 61 Power cabling for energy input from photovoltaic panel

 62 Power wiring for mains supply

 63 Power wiring for sending electrical power to the network

64 chassis generator current module 65A, 65B, Two way refrigerant valves

65C, 65D

 66 Refrigerant / air exchanger

 67 Non-return valve on refrigerant circuit

 68 Control box

 Pc Compressor heat pump module

 Pa Absorption heat pump module

 Refrigeration module

 Mixed module: heat pump and refrigeration

 G Current generator module

 Ce1, Customer Inlet Collector

 Ce 2, Ce 3

 Cs1, Cs2, Customer Exit Collector

cs3

Description of the invention

 Definitions

 In this document, we mean

 Thermodynamic system of the heat pump or refrigeration type: Device comprising a compressor and several exchangers in which circulates a specific transfer fluid commonly called refrigerant, said device for absorbing thermal energy at a first temperature, and to restore thermal energy at a second temperature, the second temperature being higher than the first.

 • Geothermal Loop: A set of pipes placed in the ground typically in a vertical or horizontal position and intended to exchange heat between the heating or cooling system and the ground.

 • Heat exchanger: Device intended to transfer heat between several circuits.

 • Transfer Fluid: Heat transfer fluid used to transfer heat; conventional examples are refrigerant, water or brine sometimes called brine.

• Thermal source or source: By convention, the terms source and thermal load refer to the heating mode. The source is the medium from which the heat is extracted in heating mode. This heat extraction is carried out with certain physical characteristics such as the thermal inertia or the available power that characterize the source. It may be noted that the source term is unsuitable in cooling mode because it actually rejects heat from the building.

• Thermal load or load: The load is the environment where heat is rejected in heating mode. This heat rejection is achieved with certain physical characteristics such as the thermal inertia or the available power that characterize the load, so the load is the place where the heat is removed in cooling mode.

• COP or coefficient of performance: the COP or coefficient of performance of a system in heating mode is defined as the ratio between the heating power available on the electrical power consumed by the system. In the system according to the invention, COP "electrical equivalent" means the COP that would have the facility if we used electricity instead of gas or biofuel.

 • AC Generator: A device that generates alternating current either directly or through an additional converter that converts the DC current generated into AC current.

 • Combustion engine: Engine that, by combustion, converts the chemical energy contained in a fuel into mechanical energy.

 • Internal combustion engine: A combustion engine in which the combustion of fuel producing the energy required for operation takes place in the engine itself, typically in a combustion chamber.

 • Photovoltaic solar panel: DC electric generator consisting of a set of photovoltaic cells electrically interconnected.

 • Solar thermal collector: Device in which the temperature of a solid, liquid or gaseous medium is increased by total or partial absorption of solar radiation.

• Fuel cell: A device that produces electricity by oxidation on one electrode of a reducing fuel (for example hydrogen) coupled to the reduction on the other electrode of an oxidant, such as oxygen air. detailed description

 The combustion engine 2 of the system according to the invention is preferably an internal combustion engine, it is part of the current generator module G. It is preferably fed with natural gas. Depending on the needs, it can also be powered by other gaseous or liquid fuels such as gasoline, fuel oil, kerosene, alcohol, biofuels such as vegetable oils, bioethanol, biogas.

It may also be other types of combustion engines, such as external combustion engines such as Stirling engines. The alternator 18 assembled to the combustion engine is also part of the generator G.

The fuel cell 22 of the system according to the invention may be any type of fuel cell known to those skilled in the art, typically operating, but not exclusively, at temperatures below 200 ^° C., but may in some cases case to reach a temperature of 800 ⁰ C to 1000 ⁰ C (for example a "solid oxide" type battery) and supplied with a suitable fuel, such as hydrogen, methane or another hydrocarbon mixture such as gasoline or the fuel. The fuel cell is composed at least of a hydrogen fuel cell core 22B (in the case of fuel cell cores based on proton membranes) or powered by the plurality of hydrocarbon fuels already mentioned (in the case of high temperature battery cores). solid oxide type). If the cell is of the type based on proton membranes and hydrogen is not readily available, then the fuel cell 22 is composed of a reformer 22A and a battery core 22B. The role of the reformer is to extract the Hydrogen required at the core from chemically more complex and already mentioned fuels such as natural gas, methane, biogas or another hydrocarbon mixture. The hydrogen thus extracted feeds the cell core based on proton membranes.

An exemplary operation of a reformer fuel cell 22A is shown in Fig. 19 and will be described in the following. The fuel 22F (which may be natural gas, bio gas, etc.) undergoes in the reformer 22A a series of transformations to extract the hydrogen 22G, while limiting the level of impurities (typically sulfur) and the carbon monoxide. For this, the fuel first goes through a reforming reactor which, following the addition of water, extract the hydrogen. In the case of methane, for example, the chemical reaction is of the CH ₄ + 2H ₂ O = Cθ ₂ + 4H _{2 type} . The function of the unit 22D is to reduce the sulfur content, which may affect the behavior of the battery core 22B. The unit 22E realizes, she, the so-called "water gas shift" transformation that decreases the carbon monoxide content of the mixture which can also affect the behavior of the pile core. The chemical reaction in this unit is of the type: CO + H ₂ O = CO ₂ + H ₂ .

 The photovoltaic solar panels 23 of the system according to the invention can be any type of panel known to those skilled in the art, in particular, the semiconductor constituting the photovoltaic cells can be, in a nonlimiting manner, amorphous silicon, polycrystalline or monocrystalline, an organic semiconductor material, or a combination thereof. A plurality of photovoltaic solar panels can be used.

In preferred embodiments, the system according to the invention is reversible, that is to say it can operate in heating mode by providing hot water at temperature T1 ("heating mode") or in a mode favoring cooling by supply cold water at temperature T3 ("cooling mode"). To do this, a four-way cycle reversal valve 46 (Fig.δc) is installed on the refrigerant circuit 16. It can also have non-reversible systems, particularly for certain refrigeration applications. When the system is equipped with the optional heat exchanger 15, it is then possible to supply hot water simultaneously at the temperature T1, and cold water at the temperature T3 in variable proportion for each in order to meet the needs of the use. The valve four cycle inversion channels 46 is then replaced by four refrigeration valves two channels 65A ₁ B, C, D The expander 10 is then completed by two additional regulators causing the circuit comprises three expansion valves: 10A, 1Ob, 1OC.

 In the case where the heat pump 3 is reversible, the heat exchangers 11 and 12 are reversible heat exchangers. It should be noted that we have chosen to describe in detail the operation of the system according to the invention in cooling mode. When the heat pump is operating in heating mode, the water circuit 13 becomes a hot water circuit.

 On the other hand, the heat exchanger 11 is preferably a plate heat exchanger.

With reference to FIG. 1, the heat pump 3 of the system 1 according to the invention is a Pc module 36 which comprises

 one or two closed and sealed circuits in which circulates a transfer fluid such as a refrigerant 16,

at least one compressor 17 per circuit driven by an electric motor, a regulator 10,

 a first heat exchanger 11, located at the suction of the compressor 17 when the system operates in air conditioning mode,

 a second heat exchanger 12, located at the discharge of the compressor 17 when the system operates in air conditioning mode.

 A third optional heat exchanger 15 located at the discharge of the compressor 17 when the system is in air conditioning mode and simultaneous heating by heat recovery.

 These components are arranged inside a frame, not shown in FIG. 1. According to the invention also, the compressor 17 is driven by an electric motor. This electric motor can be electrically powered by the first current generator and / or by one or more of the other current generators, or the electrical network, depending on the choice made by the overall system control method chosen. A DC or AC motor can be used. The fact of using an electric motor to operate the compressor 17 (and in particular, the fact of not driving the compressor 17 directly (mechanically) by the combustion engine 2) has the advantage of being able to use hermetic compressors, avoiding thus the risks of leakage related to the use of open compressors. In a particular embodiment, the compressor 17 is driven by an electric motor powered electrically by a combustion engine 2, the electricity required being generated by the alternator 18 driven by said combustion engine 2.

For the reasons mentioned above, the compressor of the heat pump is preferably a hermetic compressor. Hermetic compressor means a compressor composed of a closed casing, usually a welded steel casing, inside which there is a compression unit for compressing the refrigerant, and a motor which drives the compression unit . However, it is also possible to use semi-hermetic compressors, in which one can have access to certain internal organs during maintenance or possible repairs.

 The heat pump 3 of the system 1 according to the invention may be provided with a third heat exchanger 15. This exchanger is preferably (like the second heat exchanger 11) a plate heat exchanger.

The heat pump 3 of the system 1 according to the invention allows the use of all types of thermal loads known to those skilled in the art for heating and cooling. air conditioning, such as refreshing heating floors, fan coil units. The loads can also be air handling units for the dehumidification of swimming pools and the treatment of fresh air premises, or industrial process water circuits requiring the use of hot water and / or Cold water.

 In a variant of the invention, the heat pump 3 of the system 1 according to the invention may be an air / water type heat pump, that is to say a heat pump using the outside air and / or air extracted as a heat source in heating mode or a water / water type heat pump, ie a heat pump using a water circuit in the outdoor soil as a source of heat. heating mode. An advantageous thermal source for the heat pump 3 is a geothermal loop.

 The heat exchangers on the source and the load are adapted to the type of heat pump and the type of application according to the criteria well known to those skilled in the art.

 With reference to FIG. 4, the refrigeration assembly according to the invention is a module Pr 36A which comprises:

 at least one circuit in which circulates a transfer fluid such as a refrigerant 16; the circuit is closed and sealed after final installation of exchanger 11 (at the factory or on the final site)

 at least one compressor 17 driven by an electric motor,

 a regulator 10,

 - Refrigerant suction ducts 16a and 16b liquid to be connected to a heat exchanger 66 by refrigeration circuit located at the suction of the compressor 17. This exchanger is not located in the module

Pr 36A including compressors 17. It may be located in an isothermal module 36C, as shown in FIG. 16, or it may be located outside the modular assembly according to the invention (typically in a building close to the modular assembly). This exchanger makes it possible to close the circuit and is necessary for the operation of the system. A module may comprise two independent refrigerant circuits, and therefore two exchangers 66. Each of these exchangers may be located in an isothermal module 36C or outside the modular assembly as described above. a second heat exchanger 12 located at the discharge of the compressor 17. These components are arranged inside a frame, not shown in FIG. 4.

According to the invention also, the compressor 17 is driven by an electric motor. This electric motor can be electrically powered by the first current generator and / or by one or more of the other current generators, or the electrical network, depending on the choice made by the overall system control method chosen. A DC or AC motor can be used. The fact of using an electric motor to operate the compressor 17 (and in particular, the fact of not driving the compressor 17 directly (mechanically) by the combustion engine 2) has the advantage of being able to use hermetic compressors, avoiding thus the risks of leakage related to the use of open compressors. In a particular embodiment, the compressor 17 is driven by an electric motor powered electrically by a combustion engine 2, the necessary electricity being generated by the alternator 18 driven by said combustion engine 2. For the reasons mentioned above above, the compressor of the heat pump is preferably a hermetic compressor. Hermetic compressor means a compressor composed of a closed casing, usually a welded steel casing, inside which there is a compression unit for compressing the refrigerant, and a motor which drives the compression unit . However, it is also possible to use semi-hermetic compressors, in which one can have access to certain internal organs during maintenance or possible repairs.

 The compressor 17 typically has, not exclusively, an electric power consumed from 10 to 30 kW depending on the models and operating conditions of the compressor (rotational speed, suction pressure and discharge pressure). The cooling capacity will vary from 5 to 80 kW depending on the operating conditions. However, it is preferred, in order to increase the available cooling capacity, to use two compressors 17 connected in parallel, and in this case, all of the two compressors will have a cooling and electrical power consumed doubled.

 The refrigeration assembly of the system according to the invention may be provided with a third heat exchanger 15. This exchanger is preferably a plate heat exchanger.

In the present invention, the refrigerant is preferably selected from HFC hydrofluorocarbons (for example R134A, R407C, R404A & R410A) which are the most common. It is also possible to use hydrocarbons, and more particularly propane as a refrigerant. CO ₂ can also be used. A preferred refrigerant for the system of the present invention is R134A or 410A for the heat pump. A preferred refrigerant for the system of the present invention is typically, but not exclusively R404A for the refrigeration assembly. However, the operation of the present invention is not limited to the selection of one of the existing fluids on the market, and other fluids can be envisaged.

The heat pump 3 of the system 1 according to the invention allows the use of all types of thermal loads known to those skilled in the art for heating and air conditioning, such as heated floors, cooling fan convectors. The loads can also be air handling units for the dehumidification of swimming pools and the treatment of fresh air premises, or industrial process water circuits requiring the use of hot water and / or Cold water.

 In a variant of the invention, the heat pump 3 of the system 1 according to the invention may be an air / water type heat pump, that is to say a heat pump using the outside air and / or air extracted as a heat source in heating mode or a water / water type heat pump, ie a heat pump using a water circuit in the outdoor soil as a source of heat. heating mode. An advantageous thermal source for the heat pump 3 is a geothermal loop.

The refrigeration assembly 36A of the system 1 according to the invention comprises an air / air refrigeration circuit, that is to say that the air is cooled to a temperature T4 said refrigeration average temperature typically allowing the conservation of fresh food (forming, milk etc.) or is cooled to a lower T5 temperature called low temperature refrigeration typically allowing the preservation of frozen products. The captured heat is typically discharged into the outside air via the compressor 17 and the refrigerant / air exchanger 12.

 The heat exchangers on the source and the load are adapted to the type of refrigeration assembly and the type of application according to the criteria generally known to those skilled in the art.

Optionally, the system 36A may be provided with a heat exchanger 15 for delivering hot water at the temperature T1.

In a particular embodiment, as best seen in FIG. 7, the system 1 also comprises a heat pump of modular construction using the absorption cycle 27, and at least one electric accumulator 19. The module Pa 37 of said heat pump comprising an absorber 28, a generator 29, a circulation pump 30, an evaporator 31 located at the inlet of the absorber, a suitable expansion valve 32 and a condenser 33 placed at the generator outlet, a refrigerant 34 and an absorbent 35. This system forms a second object of the invention. The heat pump using the absorption cycle 27 is based on decreasing the solubility of a gas in a refrigerant when the temperature increases. Advantageously, the refrigerant / absorbent current pairs are respectively the ammonia / water pair and the water / lithium bromide pair. The refrigerant is absorbed in a deg C solution of the absorber 28, the solution enriched with refrigerant is transferred to the generator 29 through the circulation pump 30. The solution is then heated, which causes the separation of the refrigerant and an increase in pressure and temperature. The refrigerant flows to the condenser 33 where it condenses by rejecting heat. It then passes through an expansion system 32 and reaches the evaporator 31 where it evaporates by absorbing heat. He then joins the absorber 28, and the cycle begins again.

 Heat pumps using the absorption cycle are known as such. They are less used because they are more expensive than heat pumps using the mechanical vapor compression refrigeration cycle. However, heat pumps using the absorption cycle require little electrical power, mainly for auxiliary components and control. Most of the energy required for the absorption cycle is thermal and typically comes from the combustion of fossil energy in a burner. In the system according to the invention, the heat pump using the absorption cycle 27 can be supplied with thermal energy by any suitable source, in particular by the heat generated by one of the combustion engines 2, by the fuel cell 22 or by a solar thermal collector.

In an advantageous embodiment of the invention, the system 1 comprises a generator module connected to a heat pump module, said system simultaneously allows:

the cooling of water by the heat pump 3 at a temperature T3, the heating of water by the heat pump 3 at a temperature T1, The production of very hot water at a temperature T2 by recovery of the thermal energy released by the current generator (which may be a combustion engine 2 connected to an alternator 18) during operation, the production of electricity.

The system 1 according to this mode of the invention also allows the production of one or two or three elements selected from cold water, hot water, hot water and electricity.

The cold water has a temperature T3 typically between -8 and +15 ^C (case of water added with glycol) or between 4 and 15 and 15 ° C (case of water). This temperature is preferably between 5 and 9 ° C.

The so-called hot water produced by the heat pump 3 has a temperature T1 typically between 20 and 60 ⁰ C, and preferably between 30 and 60 ⁰ C.

The so-called hot water (typically domestic hot water) reaches a temperature T2> T1 typically between 40 and 75 ° C, and preferably 55 and 75 ° C.

In another embodiment of the invention, the system 1 comprises a generator module connected to a refrigeration module, said system simultaneously allows:

 The supply of refrigerant to thermodynamic conditions (evaporation temperature T4 or T5) allowing, after connection to a heat exchanger 66 refrigerant / air, the supply of very cold air for refrigeration applications;

 optionally heating water at temperature T1;

 the production of very hot water at temperature T2 by recovering the thermal energy released by the current generator (which may be a combustion engine 2 connected to an alternator 18) during operation;

- the production of electricity.

A system 1 comprising one or more heat pump and refrigeration modules according to the invention thus makes it possible to provide:

- Production of elements among cold water, hot water, very hot water, refrigerant with the thermodynamic conditions of medium temperature refrigeration, Refrigerant to the thermodynamic conditions of low temperature refrigeration and electricity;

- The cold water has a temperature T3 typically between -8 and +15 ⁰ C (case of water added glycol) or between 4 and 4 and 15 ⁰ C (water case). This temperature is preferably between 5 and 9 ^° C.

- The so-called hot water produced by the heat pump 3 is typically a temperature T1 between 20 and 6O ⁰ C, and preferably between 30 and 60 ⁰ C;

- The so-called hot water (typically domestic hot water) reaches a temperature T2> T1 typically between 40 and 75 ° C, and preferably 55 and 75 ° C;

- The refrigerant at the thermodynamic conditions of the medium temperature refrigeration has a T4 evaporation temperature typically between -15 ° C and 5 ° C and preferably between -10 ⁰ C and -5 ° C;

- The refrigerant at the thermodynamic conditions of low temperature refrigeration has a T5 evaporation temperature typically between -40 ⁰ C and

-25 ° C and preferably between -35 ° C and -30 ⁰ C.

 When the current generator is a combustion engine, possibly associated with an alternator, the heat is recovered at a time on the cooling circuit of the combustion engine 2 and on the exhaust gases of the engine.

When the electric power generator is a fuel cell 22, possibly associated with an AC direct current converter, the heat is recovered on the cooling circuit of the fuel cell 22, to which an exchange circuit is optionally added. thermal placed on the power converter.

When the electric power generator is a photovoltaic solar panel 23, possibly associated with an AC direct current converter, the heat is advantageously recovered by a heat exchange circuit placed under the photovoltaic cells, and / or by a light circuit. heat exchange placed on the power converter. This has a more favorable energy efficiency than using an electrical resistance to heat the water.

The so-called cold water is obtained at a temperature T3 <T1 typically between typically between -8 and +15 ⁰ C (case of water containing glycol) or between 4 and 15 ° C (water case). This temperature is preferably between 5 and 9 ° C.

In an advantageous embodiment, T1 is between 20 ^° C. and 60 ^° C., T2> T1 is between 40 ^° C. and 75 ° C., and T3 <T1 is between -5 ° C. and + 15 ° C.

T4 <T3 is between -15 and 5 ° C

T5 is between -45 ° C and -25 ° C

 The system 1 according to the invention is further provided with a control system, preferably electronic (not shown, preferably located in a cabinet called cabinet power and regulation, which it is preferably located in the module generator G 38). This regulation system can operate with several set points, thus enabling the start-up of the system according to the invention as a function of the cold water requirements at temperature T3, and / or hot water at temperature T1 and / or water very hot at T2 temperature, or refrigerant at temperatures T4 or T5 and make the choice to return some of the electrical energy generated by the system to the external power network. It will be described in greater detail below.

 With reference to FIG. 1, the engine 2 is supplied with fuel via an inlet 4.

 Typically, about 32 to 37% of the energy supplied to the combustion engine in the form of fuel is recovered as mechanical energy to drive the alternator 18, and to produce electricity. compressor 17 of the heat pump 3 with electricity 20 thus produced. Any surplus electricity generated by the alternator 18 in the case of a partial load or a dimensioning for this purpose can be used to recharge the accumulator 19 or be reinjected onto the network.

In addition, the electricity produced by the AC generator is used to operate the electrical and / or electronic elements of the system according to the invention, such as solenoid valves, one or more motor fans 21 associated with the heat exchanger 12 , and the electronic control system. On the other hand, a portion of the electricity produced by the AC generator can be used for powering devices or electrical devices located outside the system according to the invention, such as lighting for example. Typically, when the AC generator is a combustion engine 2, about 40 to 60% of the energy supplied to said engine 2 is recovered as heat energy 6 for heating the domestic hot water. The rest of the energy (typically between 3 and 25%) being dissipated in the form of losses 7.

Referring still to Figure 1, and considering the air conditioning mode, the heat pump 3 whose compressor 17 is supplied with electricity 20 produced by the AC generator provides cold water 13, with a COP "air conditioning" between 2.9 and 3.5. The system also supplies hot water 14 at the same time, with a heating COP of between 3 and 5.

 In addition, when the AC generator is a combustion engine 2, at least one heat exchanger 8 placed on the combustion engine 2 can recover heat 6 emitted by the engine 2.

 Preferably, at least one heat exchanger (not shown) is placed on the exhaust gas circuit of the engine, and at least one second heat exchanger is placed on the liquid cooling circuit of the engine 2.

According to the invention, the system 1 is of modular design and comprises at least one electric power generator module G 38 and one or more (N) production modules P each comprising one or two sets of heat pump 36D or refrigeration 36E . The electric power generator module may comprise at least one combustion engine 2.

 According to this modular embodiment, each of the N heat pump modules Pc and / or refrigeration Pr (i.e. of vapor compression type) of the system 1 according to the invention comprises

 a closed and sealed circuit in which circulates a transfer fluid such as a refrigerant 16,

 a compressor 17 driven by an electric motor,

 a regulator 10,

- In the case of heat pump sets Pc, a first heat exchanger 11, preferably plates, located at the suction of the compressor 17 when the system operates in air conditioning mode, a second heat exchanger 12, located at the discharge of the compressor 17 when the system operates in air conditioning mode,

 optionally a third heat exchanger 15, preferably a plate heat exchanger,

in the case of refrigeration units Pr _1, a heat exchanger 66 which may be located in a specific isothermal module forming part of the modular design system or may be situated away from the modular design system, in the enclosure of a building.

 These components are arranged inside a frame having.

The heat pump modules Pc are preferably identical, in particular as regards their essential components and their dimensioning. This allows them to be mass-produced. This also facilitates their maintenance and repair, because one can simply exchange a faulty module by a module in working condition and repair the faulty module without being connected to the system 1.

In general, in the context of the present invention, the heat pump module Pc comprises two compression heat pump assemblies 36D, or the mixed module Pm comprises a heat pump assembly 36D and a refrigeration assembly 36D. or the refrigeration module 36A comprises two refrigeration units 36E. These modules are made in the form of a chassis, said chassis being traversed by collector pipes, possibly by a fuel inlet pipe, and by electric power and regulation cables. Said frame is also provided with means for connecting the various pipes and cables to the system. By way of example, the dimensions of such a so-called production module frame are: length 1700 mm, width 2200 mm, height 2420 mm.

Said frame typically encloses

 at least one compressor, advantageously with variable power,

 at least one reversible battery V,

- at least one fan,

at least one plate exchanger, - Auxiliary components of a heat pump or refrigeration system of known type, such as a four-way valve, two-way refrigerant valves, and one or more refrigeration valves.

 - A liquid tank for containing coolant.

In general, in the context of the present invention, the absorption heat pump module Pa can be made in the form of a chassis, said chassis being traversed by collecting pipes, by a pipe of arrival of fuel and electric power and regulation cables. Said frame is also provided with means for connecting the various pipes and cables to the system. Said frame typically contains at least the following elements:

 a refrigerant / water exchanger,

 - a generator,

 - an absorber,

a refrigerant / water plate heat exchanger,

 - and other auxiliary components of an absorption heat pump, such as: a pump, pressure reducers.

In a general manner, in the context of the present invention, the current generating module G can be made in the form of a chassis, said chassis being traversed by a fuel supply pipe and by power cables and regulation. Said frame is also provided with means for connecting the various pipes and cables to the system. Said frame typically contains at least one heat engine type current generator connected to its alternator or a fuel cell, an exchanger for heat exchange between the current generator (s) and very hot water, a power cabinet and overall system regulation; optionally, other current-generating sources, such as a fuel cell and possibly its alternator, or even other external thermal sources (such as connections to the solar thermal collectors) can be arranged in the same frame of the current generator module. By way of example but without this being essential, the dimensions of such a generator module frame are: length 2300 mm, width 2300 mm, height 2420 mm. In general, in the context of the present invention, the combustion engine 2 is preferably a motor adapted for natural gas. This may be for example a motor of a displacement of 2 liters to 4.6 liters of the standard type as used in certain motor vehicles with gasoline or diesel industrial vehicles, but specifically adapted for the use with natural gas. In a preferred embodiment of the current generator module, a combination of two motors 2 of identical or different displacement is used, according to the needs of the user.

It is advantageous to provide in the system 1 at least one connection for an external heat transfer fluid that provides thermal energy, for example from a solar thermal collector or a geothermal loop; this connection is advantageously at the generation level because it simplifies both the design and regulation of the system 1.

In general, in the context of the present invention, a single electric current generator is advantageously used, but this depends on the energy dimensioning of the system. Two electric current generators can be used, preferably arranged in the same generator module G; one of these two generators is advantageously a combustion engine 2. Two combustion engines can be used, either in the same current generator module, or in two separate modules. It is preferable to integrate them in the same module, because this makes it possible to share certain components such as the lubrication and / or cooling circuits.

The use of two combustion engines 2 optimizes their use according to the needs of hot water, very hot water, cold water and electrical power generated. For example, if both engines are gasoline or natural gas engines, and the energy requirement they must provide is quite low, it may be preferable, in order to preserve the life of the engines or to optimize their COP, to use only one of the two engines, whereas in the case where the two combustion engines 2 are diesel engines, it may be preferable to use two at partial load that one at full load. The existence of two motors therefore increases the flexibility of use of the system 1 and also provides redundancy in case of engine failure. Of course we can also use more than two engines. In an advantageous embodiment, current type motors developed for mass-produced automobiles are used because this ensures a very attractive purchase price and reliable maintenance.

 In a particular embodiment, which may be combined with all other embodiments, the alternators are contacted with a heat exchanger to recover at least a portion of the heat energy in which a portion of the heat is transformed. electrical energy, knowing that the energy efficiency of an alternator is always less than 100%. This heat exchanger then heats a coolant that has entered a heat pump circuit.

It is also possible to combine in a module, on the one hand, a generator consisting of a combustion engine and an alternator with another fuel cell generator. It is thus possible to take advantage of the particularities of each of the generators: lower price for combustion engines, silence of operation and higher energy efficiency for fuel cells.

Finally, when the price of fuel cells has decreased or for particular applications (industrial sites with non-upgraded hydrogen), two fuel cell generators will be installed.

FIG. 5 illustrates a particular embodiment comprising two cogeneration assemblies, which can be integrated in the same generator module G, connected to a plurality of steam compression type heat pump modules Pc. The different heat pump modules are interconnected by customer input collectors Ce1, Ce3, and customer output collectors Cs1, Cs3. Customer input ducts Ce2 and customer output ducts Cs2 are provided at the level of the hot water circuit 9. FIGS. 8a to 8c illustrate better an exemplary embodiment of a system comprising several compression heat pump modules 36, in this case three modules, connected to two absorption heat pump modules 37, which are connected to a current generator module 38. These modules 36, 37, 38 are individually illustrated in FIGS. 9a to 9f, 10a, b, c and 11a, bc In the side view of FIG. 8a, a frame 44 of the heat pump module 36 or 37 is seen through which four collectors 39a, 39b, 39c, 39d pass through, the diameter of the collectors being able to be adapted to water flows necessary for the application, by power cables 41 and control cables 42. The frame 44 forms an open housing on the sides so that it can be traversed by the fluid collectors and electric cables ues, possibly even be crossed by piping 40 gas if necessary (for example to connect a remote absorption heat pump module 37 to the generator module 39 through a compression heat pump module 36). The manifold 39a is a manifold for the inlet, the manifold 39b a manifold for the fluid outlet. The other two collectors 39c for the input and 39d for the output, are intended for heat recovery in cooling mode; they are then connected to the third optional heat exchanger 15 present in this variant in the compression heat pump module 36, and operating on the same principle as the exchanger 15 of the Pc module. Alternatively, a third recovery heat exchanger (not shown) may also be present in the absorption heat pump module 37.

 As mentioned above, the generator module 38 is also constructed as a frame 64, forming an open housing on the sides so that fluid manifolds and electrical cables can pass therethrough.

 As best seen in FIGS. 9a to 9f and FIGS. 8b and 8c, a compression heat pump module 36 comprises, inside its chassis 44, two heat pump assemblies each comprising a ventilation 21, a refrigerant exchanger. 12, a four-way valve 46, a refrigeration compressor 17, a liquid cut-off bottle 48, a refrigerant / water plate heat exchanger 11, a liquid reservoir 50 and an optional plate heat exchanger, refrigerant / reclaimed water 15. Under this option, the four-way valve is replaced by four two-way refrigerated valves 65A, 65B, 65C, 65D

(fig.9e) whose operation will be described in the following. An absorption heat pump module 37 comprises, inside a frame 44, and as best seen in FIGS. 8a to 8c and 6b and 6c, a ventilation 21, a refrigerant / air exchanger 54, an absorber 51 , a generator 52 and a refrigerant / water plate heat exchanger 53. These modules 36,37 operate on the same principle as the modules Pc and Pa, as previously described.

 The operating principle of a vapor compression heat pump assembly which composes a heat pump module Pc, 36 will now be described in more detail with reference to FIGS. 17 and 18.

FIG. 17 schematically represents a heat pump assembly according to a first embodiment of the invention, in particular a reversible heat pump with a four-way valve 46. In the following, its operation will be described in the modes : heating and cooling. When the heat pump assembly of FIG. 17 is operating in heating mode, the regulation of the machine will satisfy the heating power requirement by regulating the power of the refrigerating compressor in order to respect the hot water temperature T1. Thus, all the available heat is discharged to the water of the heating network through the heat exchanger 11. The four-way valve 46 connects the discharge pipe of the compressor to the heat exchanger 11. The regulator 10 regulates the flow of fluid refrigerant to maintain an overheating of this fluid when leaving the heat exchanger 12. The four-way valve 46 connects the exchanger 12 to the suction pipe of the compressor 17. The control loop relates to the hot water temperature T1 Leaving the heat exchanger 11. When the heat pump assembly of Figure 17 is operating in cooling mode, the control of the machine will satisfy the cooling capacity requirement by regulating the power of the refrigeration compressor in order to respect the cold water temperature. T3. All available heat is then rejected to the outside air through the heat exchanger 12. The regulator 10 regulates the flow of fluid as it leaves the heat exchanger 11. The four-way valve 46 connects the discharge pipe of the compressor 17 at the exchanger 12. The regulator 10 regulates the flow of refrigerant to maintain an overheating of this fluid when it leaves the heat exchanger 11. The four-way valve 46 connects the exchanger 11 to the suction pipe of the compressor 17. The control loop concerns the cold water temperature T3 leaving the heat exchanger 11. FIG. 18 schematically represents a heat pump assembly according to a second embodiment of the invention, in particular a reversible heat pump with a recovery exchanger 15 and four two-way refrigerated valves (or self-contained valves) 65A, 65B, 65C, 65D. We will describe in the following its operation according to its six possible modes of operation.

When the heat pump assembly of FIG. 18 operates in cooling mode, the machine will satisfy the cooling capacity requirement by regulating the power of the refrigerating compressor 17 to respect the cold water temperature T3. All available heat is then rejected to the outside air through the heat exchanger 12. The solenoid valve 65B is open, all other solenoids are closed. The regulator 10A regulates the flow of refrigerant to maintain overheating of this fluid when it leaves the exchanger 11. The regulators 10B and 10C are closed. The regulation loop concerns the temperature of cold water T3 leaving the exchanger 11. When the heat pump assembly of FIG. 18 operates in cooling and heat recovery mode, the control of the machine will satisfy the cooling capacity requirement by regulating the power of the refrigeration compressor to respect the cold water temperature T3. The available heat is supplied to the water recovery circuit through exchanger 15. Solenoid valve 65C is open, all other solenoid valves are closed. The regulator 1OB regulates the flow of refrigerant to maintain overheating of this fluid when it leaves the exchanger 11. The regulators 10A and 10C are closed. The regulation loop concerns the temperature of cold water T3 leaving the exchanger 11.

When the heat pump assembly of FIG. 18 operates in cooling mode, heat recovery mode and unused heat rejection, the control of the machine will satisfy the cooling capacity requirement by regulating the power of the refrigeration compressor in order to respect the temperature of the heat pump. cold water T3. The available heat is sent to the water recovery circuit via the exchanger 15. If the amount of available heat is greater than the needs, then the excess is sent to the exchanger 12. The solenoid valves 65B and 65C are open, all other solenoid valves are closed. The regulators 10A and 10B together regulate the refrigerant flow rate to maintain an overheating of this fluid when it leaves the heat exchanger 11. The regulator 10C is closed. Two parallel control loops are found in operation: a first relating to the cold water temperature T3 leaving the heat exchanger 11 and a second which controls the temperature of hot water T1 leaving the heat exchanger 15.

 When the heat pump assembly of FIG. 18 is operating in heating mode, the control of the machine will satisfy the heating power requirement by regulating the power of the refrigerating compressor in order to respect the hot water temperature T1. The available heat extracted from the air by the exchanger 12 is sent to the water recovery circuit via the exchanger 15. The solenoid valves 65A and 65C are open, all other solenoid valves being closed. The regulator 10C together regulates the refrigerant flow rate to maintain an overheating of this fluid when it leaves the exchanger 12. The regulators 10A and 10B are closed. The regulation loop concerns the temperature of hot water T1 leaving the exchanger 15.

When the heat pump assembly of FIG. 18 operates in heating and heat recovery mode, the regulation of the machine will satisfy the need for cooling capacity to respect the cold water temperature T3 (heat exchanger 11). Moreover, the regulation of the machine will satisfy the heat capacity requirement by regulating the power of the refrigerating compressor in order to respect the temperature of hot water T1 (exchanger 15). The additional power is extracted from the air through the exchanger 12. The solenoid valves 65A and 65C are open, all other solenoid valves are closed. The regulator 1OC regulates the refrigerant flow rate to maintain an overheating of this fluid when it leaves the exchanger 12. The regulator 1OB regulates the refrigerant flow rate to maintain an overheating of this fluid when it leaves the exchanger 11. The regulator 1OA is closed. Two parallel control loops are found in operation: a first relating to the temperature of hot water T1 leaving the exchanger 15 and a second relating to the temperature of cold water T3 leaving the exchanger 11.

 When the heat pump assembly of FIG. 18 operates in defrosting mode, the machine will extract heat at the recovery circuit through the heat exchanger 15. This heat will be sent to the heat exchanger 12 in order to defrost. Solenoid valves 65B and 65D are open, the other solenoid valves are closed. The regulator 10C controls the overheating of the refrigerant leaving the exchanger 15, the other regulators being closed. The control of the machine starts the defrost and stops it based on the information given by the pressure and temperature sensors of the circuit.

As illustrated in FIGS. 11a, 11b and 8b and 8c, the current generating module 38 comprises a frame 64, provided with a fuel inlet 55 communicating with the pipe 40 of the module 37. The frame 64 comprises at least one generator current, which may be a combustion engine and its current generator 56, or a fuel cell with its inverter 57. A connection of the external thermal sources 58 may be provided for solar thermal collectors or other hot water sources. An exchanger 59 is provided to perform the heat exchange between the current generator and the very hot water. The frame 64 also contains a power cabinet and overall regulation system 60, said cabinet being provided with connections to a power cabling 61 for the arrival of energy from a photovoltaic panel, a wiring 62 for network arrival external electrical and power wiring 63 for sending electrical energy to the external power grid. Alternatively, a wiring 63 'can connect the cabinet 60 to the arrival of an auxiliary source of energy such as from a wind turbine, a turbine, or other. FIG. 6 illustrates another particular embodiment comprising two generator modules G, 38 connected to a steam compression type heat pump module Pc, 36 and to a plurality of refrigeration modules Pr, 36A. The various refrigeration modules Pr are interconnected and connected to the heat pump module Pc by customer input collectors Ce3 and by customer output collector Cs3. The balancing of the water flows in the modular heat exchangers is done in this case using balancing valves of the system.

 FIGS. 12a to 12f illustrate better an embodiment of a refrigeration module 36A comprising two refrigeration assemblies 36E on a common chassis. More particularly, the detail view 12f illustrates on an enlarged scale the inlet and outlet connection pipes to the cold water circuit 13, the inlet and outlet connection pipes to the hot water circuit 14, as well as the four refrigerant conduits including two suction 16a and two liquid 16b for connecting the two refrigeration units 36E to a refrigerant / air exchanger 66 located remotely, being external to the module 36A. Figs. 12a and 12b are front and rear views of the refrigeration module 36E, Fig. 12b shows a side view of a refrigeration module 36A having two refrigeration assemblies 36E, Fig. 12d is a perspective view of the refrigeration module. 36A and Figure 12e is a sectional view of the module 36A made with the plane DD of Figure 12b. As seen in these figures, the refrigeration module 36A comprising two refrigeration assemblies 36E has a total symmetry vertically, which allows to advantageously arrange all the components of the two refrigeration units on a common frame of the module.

FIGS. 13a to 13f better illustrate an exemplary embodiment of a mixed module 36B comprising a refrigeration assembly 36E and a heat pump assembly 36D on a common chassis. More particularly, the detail view 13f illustrates on an enlarged scale the inlet and outlet connection pipes to the cold water circuit 13, the inlet and outlet connection pipes to the hot water circuit 14, as well as the two refrigerant conduits including a suction 16a and a liquid 16b for connecting the refrigeration assembly 36E to a refrigerant / air exchanger 66 located remotely, being external to the module 36A. Figures 13a and 13b are front and rear views of the mixed module 36B, Figure 13b shows a side view of a module 36B, Figure 13d is a perspective view of the mixed module 36B and Figure 13e is a sectional view taken with the EE plane of Figure 13b.

FIGS. 14a to 14c illustrate better an exemplary embodiment of a system of the invention comprising a generator module 38 connected to a mixed module 36B comprising a refrigeration assembly 36E and a heat pump assembly 36D on a common chassis. FIG. 14a is a side view of the assembly, FIG. 14b is a front view of the assembly and FIG. 14c is a perspective view of the generator module assembly 38 and mixed module 36B.

Figure 15 is a front view illustrating an embodiment of a system of the invention comprising a generator module 38 connected to a compression heat pump module 36 and a refrigeration module 36A.

 FIG. 16 illustrates an exemplary embodiment of a system of the invention comprising a generator module 38 connected to a compression heat pump module 36, to a refrigeration module 36A, connected to a first isothermal module 36C comprising an evaporator 66 and a second isothermal module comprising an evaporator 66.

The main advantages of the system according to the invention compared to the systems of the state of the art are:

 - Multi-energy or multi-energy supply, typically electricity / natural gas or fuel

Operating up to a temperature of -20 ^° C. with a good yield,

A COP on total primary energy greater than 1.5, even when the outside temperature is low.

 - Integration of functions within a single modular package for simultaneous fluid supply applications (water or refrigerant) at temperatures ranging from -45 ° C to + 75 ° C.

 As can be seen in FIG. 3, the system according to the invention has a higher efficiency than the systems of the state of the art, even recent ones, such as gas-fired boilers.

This good performance is achieved by heat recovery within the system: On the one hand, the recovery in the heat pumps together through the third heat exchanger 15, placed in the refrigerant circuit.

 On the other hand the heat recovery in the current generators of the type combustion engine or fuel cell

This good performance is also achieved through the selection of high-performance components: for example, large-sized heat exchangers, compression-optimized combustion engines for the fuel used, modern variable speed ventilation with electronically commutated motors.

 A total power of 60 to 900 kW is typically obtained thanks to the modular structure of the system according to the invention, respecting the geometric dimensions of a truck of standard size in Europe (maximum length of the load: 13 meters).

 It is also quite possible to achieve all the characteristics described in the invention, for powers covering the range 20 to 150 kW, with dimensions allowing the passage in a door is 890 mm wide and 1800 mm. height. The characteristics described include the possibility of simultaneously obtaining water at 3 different temperatures T1.T2 and T3 as well as refrigerant at temperature T4 and T5

In a particular embodiment, the vapor compression heat pump module comprises two heat pump assemblies each comprising a compressor (typically scroll compressors, also called a scroll compressor), a fan, an air / refrigerant exchanger. (called "battery") reversible V and two plate heat exchangers water / refrigerant circuit (including an optional for the heat recovery circuit). This embodiment will be illustrated below by examples.

In air / water mode, the heat pump module can operate in heating alone mode or air conditioning only with possible recovery on an independent circuit. Thus, in winter, the battery on the air is in evaporator mode, while the plate heat exchanger operates in condenser mode. For the production of hot water at temperature T1, a supplement of heat can come if necessary from the heat recovered on the cooling circuit of the combustion engine and on its exhaust fumes. It is also possible to recover the heat of the engine at a very hot temperature T2. In summer, the battery on the outside air operates in condenser mode, while the plate heat exchanger operates in evaporator mode. This allows the production of cold water, and offers the possibility of also providing hot water at T2 temperature on an independent circuit through the recovery on the cooling circuit of the combustion engine and its exhaust gas.

In heating mode alone, the heat pump module partially heats the water, and the heat recovery on the combustion engine cooling and its exhaust gases provide additional heat, if necessary, to provide, for example, heat. water at a typical temperature of 45 ^C C.

 In cooling mode, the heat pump module cools the cold water, for example at a temperature of 7 ° C, while independently, it can be generated from the hot or very hot by recovering the heat generated by the electric power generator module (combustion engine), according to the needs of the consumer. In water / water mode, the system can simultaneously produce hot water for heating and cold water for cooling in both summer and winter. The batteries are then not used on the outside air, but only the reversible plate heat exchangers: one operates in condenser mode to produce hot water, the other operates in evaporator mode to produce water cold. The heat recovery module of the electrical energy generator is used for additional heat on the production of hot water or very hot (sanitary water).

In an advantageous embodiment, which can be implemented with all the other embodiments and their variants, the system 1 is controlled by at least one computer machine comprising at least one microprocessor and at least one data entry interface. . Data is entered into the microprocessor of said computer machine through said data entry interface.

The invention also relates to a method of regulating a system 1 according to the invention. Here we describe this mode of regulation.

In a first step (a), at least one piece of data called "base data" is entered into said microprocessor. This basic data is typically entered into the microprocessor either during its initial programming at the factory, or during the start-up of the system 1 at the user's site (parameterization of the control for the given installation), or again by the user over time during the use of the system 1 (first level setting to take account of basic evolutions, for example the cost of energy).

 This basic data concerns the technical characteristics of the modules and their components and consumables. They are selected in the group formed by:

 - (da1) the unit fuel cost of each combustion engine 2, fuel cell 22 and absorption heat pump used in the system 1;

- (da2) the energy content of each fuel;

- (da3) the CO ₂ impact of each fuel per unit mass;

- (da4) the energy efficiency of each combustion engine 2 according to its load and its rotational speed, which determines the amount of CO ₂ released per unit of mechanical power produced by the engine 2;

 - (da5) the nominal power at full load of each combustion engine 2 as a function of its rotation speed;

(da6) the percentage of thermal power recovered from the engine cooling system and the percentage of thermal power recovered from the exhaust gases, which makes it possible to determine the quantity of CO ₂ released per unit of thermal power produced by the engine with combustion

2

 (da7) the unit cost of the electric power supplied by the external network (instantaneous cost, its evolution as a function of time, and its evolution as a function of the requested power level);

 - (da8) the life of each generator (mainly the combustion engine 2 and the fuel cell 22) according to its load;

 (da9) the maintenance cost of each generator (mainly of the combustion engine 2 and the fuel cell 22) as a function of the number of hours of operation;

 - (da10) the cost of dismantling and replacing each generator

(mainly combustion engine 2 and fuel cell 22);

- (da11) the service life, maintenance cost, disassembly and replacement cost of each type of heat pump (using the vapor compression cycle or using the absorption cycle); - (da12) the efficiency of the alternator as a function of the electrical power it provides, which makes it possible to determine the mechanical power required of the combustion engine 2 for a supplied electrical power;

 (da13) the efficiency of the fuel cell 22 as a function of its charge when it is not equipped with a reformer (a typical but not exclusive case of a PEM -Proton Exchange Membrane fuel cell powered by hydrogen), or the efficiency of the fuel cell as a function of its charge when it is equipped with a reformer (a typical case of a PEM fueled by a fuel other than hydrogen);

 - (da14) the efficiency of the inverter of the fuel cell 22 or photo voltaic solar panels 23 when they exist;

 (da15) the power consumption and the fluid flow rate (typically glycol) of the circulating pump of the solar collectors;

 (da16) the unit selling price of the electrical energy supplied to the external network,

 (such as the instantaneous price, its evolution as a function of time and its evolution according to the level of power required).

 In an advantageous embodiment, for each type of heat pump, the performance tables giving the supplied cooling capacity, the heat output supplied, the electric power consumed, the quantity of fuel consumed if applicable (case of the absorption heat pump) within its operating range. These performance tables are defined by the water temperatures of each circuit (T1.T2 and T3, T4 and T5), the fluid flow of the associated exchangers, and the ambient air inlet temperature. The control mode may provide that any operation with one or more of these parameters outside the defined operating range is prohibited.

 In an advantageous embodiment, the following basic data are entered for each compressor used in the steam compression heat pumps:

 the performance tables giving the cooling capacity supplied,

 - the heating power supplied,

the electric power consumed as a function of the suction pressure and the discharge pressure of the compressor for a given refrigerant. These data allow cross-checking of the performance tables above. They can also be used as basic data to determine, for the complete system, the supplied cooling and heating capacities as well as the electrical power consumed by the steam compression heat pumps. These data include, for each compressor, the level of volumetric flow (expressed typically in percent) at which it operates (typically from 10% to 100%).

In a second step (b), at least one piece of data called "instantaneous data" is entered. These instantaneous data are typically input to the microprocessor during its operation by the measuring equipment that comprise the various components of the system 1, or by a device external to the system 1 (for example by an electrical contact of the type "erasing peak day of the electrical network ", via an Ethernet network etc ..) communicating some of these data to the installation.

This at least one instantaneous data is selected from the group formed by:

 - (db1) the instantaneous electric power produced by each present current generator: alternator 18, fuel cell 22, solar photovoltaic panel 23;

 - (db2) the rotational speed of each combustion engine 2;

 - (db3) the instantaneous fuel consumption of the installation (combustion engine and absorption heat pump);

 - (db4) the temperature of the fluid recovering the thermal energy of the combustion engine 2 (including the thermal energy contained in the cooling circuit and in the exhaust gas);

 - (db5) the instantaneous electrical power consumed by the system 1 from the network, obtained by a direct measurement;

 - (db6) the instantaneous power supplied to the network by the system 1, obtained by a direct measurement;

 - (db7) the current, the voltage or the instantaneous electric power produced by the photovoltaic solar panel 23 (if this panel is present);

 - (db8) the instantaneous temperature T1;

 - (db9) the instantaneous temperature T2;

 - (db10) the instant T3 temperature

- (db11) the instantaneous T4 temperature - (db12) the instant T5 temperature

 - (db13) the temperature of the ambient air;

 - (db14) the number of hours of operation of each electric power generator (mainly combustion engine 2 and fuel cell 22); - (db15) the number of hours of operation of each heat pump circuit in the installation (vapor compression or absorption type).

 If one of the instantaneous temperatures T1, T2 or T3 is selected (data dbδ, db9, d10), it is advantageous to select all three.

In a third step (c), at least one datum called "target datum" is defined to which is assigned a value called "target value", said target datum being selected from the group formed by:

 - (dc1) T1 temperature and its evolution according to parameters such as the outdoor temperature, or the cost of energy, (the ideal comfort may leave room for economically acceptable comfort);

 - (dc2) the temperature T2 and its evolution according to parameters such as the external temperature or the cost of the energy;

 - (dc3) the temperature T3 and its evolution according to parameters such as the external temperature or the cost of the energy;

 - (dc4) the temperature T4 and its evolution as a function of parameters such as the desired temperature in the external refrigerated enclosure or the cost of energy;

 (dc5) the temperature T5 and its evolution as a function of parameters such as the desired temperature in the external refrigerated enclosure or the cost of energy;

- (dc6) the global COP as the maximum overall COP for system 1, this point being correlated with the overall minimum CO ₂ impact of system 1;

 - (dc7) energy cost as the minimum energy cost of system 1;

 - (dcδ) the total running cost as the minimum total running cost of system 1.

Whatever the chosen target data (or whatever the chosen target data), we can also have a complementary target data such as the minimum electrical power to be supplied to the network (in the case of emergency generator operation, for example).

 Said at least one target datum and its associated target value are input to the microprocessor.

In a fourth step (d), the system 1 is controlled with the aid of said computer machine so as to achieve, for each of the selected target data, the determined target value or values, said regulation being performed by comparing the current value of the selected target data, which is determined from time to time or in a regular or continuous manner, taking into account the selected basic data or data and the instantaneous data (s) selected, and adjusting at least one data item called "adjustment data" selected in the group formed by

 (dd1) the type, the number of current generators in operation, and the electrical power supplied by each of said generators (advantageously by selecting the generators according to their characteristics vis-à-vis the selected target data);

 - (dd2) the allocation of the electrical powers supplied by the generator or generators respectively to the installation and to the external network to the system 1;

 - (dd3) the type and number of heat pumps and / or refrigeration units in operation;

 (dd4) In the case of steam compression heat pumps and / or refrigeration units, the volumetric flow rate (expressed in percent) imposed by the compressor control to optimize the system 1.

to approach, for each selected target data, its current value to the target value.

 In the case where multiple target data are selected, the control method may include a weighting algorithm for determining a target parameter from the target values.

We give here three examples for such a method of regulation:

1) If the target data is the maximum global COP of the system 1, or its minimal CO ₂ impact (data dc4), one will seek inter alia to follow the following rules: - We will seek to operate the current generators in their area of maximum efficiency (full load for example for a combustion engine 2 running on natural gas);

 - We seek to recover the maximum thermal heat rejection of the combustion engine 2. For example, if the needs of the hot water installation site are lower than the production of the combustion engine 2, we will combine this heat production with the hot water supplied by the heat pump modules;

 - We will seek to operate all heat pump modules in partial load rather than stop some to reduce the load on each exchanger and thus allow more energy efficient operation.

2) If the priority target data is the energy cost as the minimum energy cost of system 1 (data dc5), the approach is similar to the optimization of the previous example, but the parameterizable coefficients for each type of energy become the following:

 - Cost of purchasing each energy outside system 1 (typically electrical energy from the grid or fossil fuel energy or biogas) at the time of use. (For example, the cost of electricity may vary according to the time of year but may also depend on consumption thresholds in the day or year, where these thresholds are related to This weighting can of course change over the life of the installation and can therefore be parameterized as part of the overall system control method).

 Possible resale price to the electrical energy network, if necessary to be produced by the generator module (s) of the device. (This price may also vary, according to rules generally similar to those that apply to the cost of purchasing electricity)

 - Taking into account evolution of target data such as temperatures T1, T2,

T3 and their possible evolution according to the costs of energy.

We will try to regulate the data listed in (d) (data dd1 to dd4) to obtain a minimal cost taking into account the energy sold and bought. 3) If the priority target data is the total operating cost (dc6) as the minimum total operating cost of system 1, the approach is similar to the previous optimization, but it also takes into account:

the lifetimes of each generator (data daδ),

 - maintenance costs (data da9),

 the cost of dismantling and the replacement cost of each generator (data da10),

 - the dismantling cost and replacement cost of each type of heat pump (data da11)

 This gives particular importance to the life of certain critical components such as combustion engines or fuel cells.

The system according to the invention can be advantageously used in balneotherapy, thalassotherapy, collective housing, for heating swimming pools, in hospitals or nursing homes, in hotels or tourist homes.

 The system can also be used advantageously in agricultural applications where there is a need for heating capacity, and possibly cooling capacity, or both simultaneously. The primary fuel of the system could then be natural gas of the biogas but it could also be biogas from the biomass that would be available, or even possibly generated on the site of the application itself. A first series of applications preferably concerns agricultural greenhouses using, for example, natural gas as a primary fuel.

A second series of applications relates to anaerobic digestion units, the system of the invention then using the biogas produced on site.

The system according to the invention is also used in industrial processes requiring simultaneous heating and cooling of water, used at different points of the process. This is the case for example of certain agrifood processes.

The system according to the invention is also used in industrial processes requiring the cooling of air at medium refrigeration temperatures and low temperature used at different points of the process. This is the case, for example, of certain agrifood processes, particularly in supermarket type applications.

 Another advantage of the system according to the invention is its design flexibility and its flexibility of use. The flexibility of use permanently allows the optimal choice of the type or types of energies used and / or provided, according to external parameters and target parameters (objectives), by means of an appropriate regulation method.

The design flexibility allows the optimization of the device according to the foreseeable needs of the user, especially in terms of heat capacity, water requirements of different temperatures. This optimization is exerted notably by the choice of the type and the number of heat pump modules, and by the choice of the type and number of electric generator module.

The design flexibility allows for the consideration of, among others, the following parameters:

a) Heat capacity and cooling capacity requirements, and simultaneous heating and cooling capacity of the site concerned throughout the year. These parameters will have a direct impact on the quantity of heat pump modules concerned and on the choice of the cycle used.

b) Potential need for an electrical generator on the installation (in standby solution to the network for example). The generator module (s) integrable with the device, combined with the flexibility of use of the device, allow to meet this need. The choice of generator module (s) will depend, among other things: on the power required to power the device; the existence of expensive electrical thresholds on the site (for example purchase of transformer, consumption thresholds) that it will be interesting not to cross, characteristics of the site (existence of renewable energy of the wind or photovoltaic type), the desired noise level or the desired efficiency (interest of the fuel cell).

c) Familiarity of users with any of the heat pump cycles device (compression or absorption) and the refrigeration cycle. d) CO ₂ impact: Importance of the CO ₂ impact for the installation in question (compliance with a HQE High Environmental Quality label, for example) and evaluation of the CO ₂ impact of the electrical energy of the network.

e) Finally, of course, and for all the modules, the optimal configuration will depend on the initial purchase cost and operating costs (taking into account energy consumption and maintenance).

 It can be noted that the device offers a combination of design solutions to adapt effectively to each case.

The flexibility of use takes into account in particular the multiplicity of energies capable of supplying the different components of the system 1 according to the invention, as well as the multiplicity of energy flows that can be produced by the system 1. All of the above modules are powered by one or more of the following energies: fossil fuels (including natural gas, liquefied petroleum gas, gas oil, gasoline), biofuels, hydrogen and electricity. The heat pump modules can typically utilize the following two conventional cycles: the mechanical vapor compression refrigeration cycle and the absorption cycle. The conventional water networks connected to the heat pumps can be completed in the device by a water network resulting from solar thermal collectors. The electricity generating modules can use various technologies such as heat engine and alternator, photovoltaic solar panel 23, wind turbine, turbine or fuel cell.

The flexibility of use is made possible thanks to the global regulation method for all the modules of the device (heat pump and electric generators) which allows optimal consideration among others of the following target (objective) parameters:

(i) Priority given to the COP of the installation. Parameterizable coefficients will make it possible to express the different energies external to the device (for example the electricity of the network, the thermal energy of the solar collectors and the photovoltaic electrical energy) in terms of primary energy and CO ₂ impact in order to give an overview of the COP of the multi-energy device. The overall regulation of the device will take account in the overall optimization the performance of each type of generator module. Thus and among other operating rules:

 - It will be sought to operate the current generators in their zone of maximum efficiency (at full load for example for a natural gas engine);

 - It will recover the maximum thermal heat rejection of the engine. For example, if the needs of the hot water installation site are lower than the production of the heat engine, this thermal production will be combined with the hot water supplied by the heat pump modules;

- We will try to operate all the heat pump modules in partial load rather than stop some to reduce the load on each exchanger and thus allow more energy efficient operation.

(ii) Priority given to the energy cost of the installation:

The approach is similar to the previous optimization, but the parameterizable coefficients for each type of energy become the following:

 The cost of purchasing each energy outside the device (typically electricity from the grid or fossil fuel or biogas energy) at the time of use. For example, the cost of electric energy may vary according to the period of the year but may also depend on consumption thresholds in the day or in the year, where these thresholds are linked to the subscription electrical installation. These weights can of course evolve during the life of the installation and are therefore configurable as part of the overall control method of the device.

 Possible resale price to the electrical energy network, if necessary to be produced by the generator module (s) of the device. This price may also vary, according to rules generally similar to those that apply to the cost of purchasing electricity.

(iii) Priority given on the total operating cost of the installation (in particular the energy cost, the maintenance cost, which includes dismantling cost and replacement cost). This gives a particular importance to the duration life of certain critical components such as combustion engines 2 or fuel cells 22.

 It follows from the foregoing that it is thanks to its modular design, the very wide range of temperature available for respective ranges of power for each temperature dimensioned to use, this finally combined with its global regulation which knows precisely the operation and performance of each of these modules, that the device allows an optimization of operation, both overall, adapted to the complexity of the problems encountered and their evolution.

Examples

The following exemplary embodiments illustrate certain embodiments of the invention. They do not limit the invention.

 In these examples, two types of automotive heat engines adapted to operate with natural gas were used: a 2.0-liter engine manufactured by the Volkswagen company and another engine with a capacity of 4.6 liters, manufactured by the MAN company. .

 Five different electrical generator modules (module G) have been manufactured:

(a) 2.0 liter engine alone, (b) 4.6 liter engine alone, (c) two 2.0 liter engine, (d) two 4.6 liter engine, (e) a 2.0 liter engine and a 4.6 liter engine.

 A unique model of heat pump module (module P) was manufactured, which included:

 two scroll compressors (also called scroll compressor) operating with the R410a fluid, including a variable power (digital control);

 - two fans;

 - two reversible V batteries;

 - 4 double circuit reversible plate heat exchangers (including two for the optional recovery circuit).

 These modules P, depending on their use, may further comprise a buffer tank, an expansion tank, a circulator, refrigerating and hydraulic valves. Auxiliary components are powered by the external power grid. The compressors are powered either by the electrical energy generated by the module or by the external electrical network.

Claims

1. System (1) for the simultaneous production of very hot water at temperature T2, hot water (14) at temperature T1 and / or cold water (13) at temperature T3, and electricity (20) , and optionally also the production of refrigerant at temperature of evaporation T4, and / or the production of refrigerant with evaporation temperature T5, and said system comprising at least one generating set of current which comprises either a combustion engine ( 2) connected to an alternator (18) is a fuel cell (22), each of the current generators also comprising a heat exchanger (8) producing very hot water at temperature T2, and said system (1) or current generator assembly optionally comprising one or more other current generators selected from the group consisting of a combustion engine (2) connected to an alternator (18), a fuel cell (22), a solar panel photo voltaic (23), or a wind turbine, and said system (1) also comprising at least one heat pump (3), or a refrigeration unit and possibly an electric accumulator (19), said heat pump or said refrigeration unit being (i) of the vapor compression type and then comprising at least one refrigerant compressor (17), a first heat exchanger (11, 66) located at the suction of the compressor (17) when the system (1) ) is in cooling mode, an expansion valve (10), and a second heat exchanger (12) placed at the outlet of the compressor (17) when the system (1) is in cooling mode, and possibly a third heat exchanger (15) located at the discharge of the compressor (17) when the system (1) is in the cooling mode and used for heating the hot water (14), (ii) the absorption type and then comprising an absorber (28), a circulation pump (30), a generator of vapor (29), a first heat exchanger (31) located at the inlet of said absorber (28), an expander (32) and a second heat exchanger (33) located at the outlet of said steam generator (29), Said system (1) being characterized in that (a) the compressor (17) or circulation pump (30) is driven by an electric motor, which can be powered by one of said current generators, and in that (b) said system (1) comprises at least one module Pc ₁ Pa called "heat pump module" (36,37) or at least one module Pr said "refrigeration module" (36A) or at least one module Pm ( 36B) said "mixed: heat pump and refrigeration" comprising, (b1) in the case of a compression heat pump module Pc (36), each at least one heat pump assembly comprising at least one refrigerant compressor (17), said first heat exchanger (11) ), said expander (10), said second heat exchanger (12), and optionally said third heat exchanger (15);  (b2) if it is an absorption heat pump module Pa (37), each an absorber (28), said circulation pump (30), said steam generator (29), said first heat exchanger heat (31), said expander (32) and said second heat exchanger (33);  (b3) if it is a refrigeration module Pr (36A), each at least one refrigeration assembly comprising at least one compressor (17) of refrigerant, said expander (10), said second heat exchanger ( 12), and optionally said third heat exchanger (15), as well as refrigerant conduits (16a, 16b) for connection to an air / water refrigerant exchanger (66) external to the Pr module (36A);  (b4) if it is a mixed module Pm (36B), two sets, one of the heat pump type and the other of the refrigeration type, where  the entire heat pump type comprises at least one refrigerant compressor (17), said first heat exchanger (11), said expander (10), said second heat exchanger (12), and possibly said third exchanger heat (15), and the refrigeration type assembly comprises at least one refrigerant compressor (17), said expander (10), said second heat exchanger (12), and optionally said third heat exchanger (15) as well as fluid conduits; refrigerant (16a, 16b) for connection to an air / water refrigerant exchanger (66) external to the Pm module (36) and in that said generator assembly is included within a generator module (G) said modules (G ₁ Pc ₁ Pa, Pr, Pm) each being provided with a frame and an assembly forming a mounting interface made in such a way that modules (G ₁ Pc, Pa, Pr, Pm) can be assembled together, one after the other, and form a unitary unit. The system of claim 1, characterized in that said mounting interface assembly comprises: a mechanical interface, an electrical interface, and a fluid interface. 3. System (1) according to claim 1 or 2, characterized in that it is designed so as to be powered by an external electrical network to cover, in part or in full, its electrical energy requirements, and so to be able to send to said external power network at least a portion of the electrical energy produced by said system (1). 4. System (1) according to one of claims 1 to 3 wherein each of said current generator modules (38), heat pump (36,37), refrigeration module (36A) or mixed module (36B) is formed as a frame forming a housing open on the sides so that it can be traversed by the fluid collectors and electrical cables. 5. System (1) according to one of claims 1 to 4, characterized in that the compression heat pump module Pc (36) comprises a frame (44), said frame being traversed by collecting pipes (39a - 39f), and by electric power cables (41) and regulation (42), and in that said chassis encloses:  at least one compressor (47), at least one reversible V battery (12),  at least one fan (21),  - at least one plate heat exchanger (11)  - auxiliary components of a refrigeration system, such as a four-way valve (46) and / or two-way refrigerated valves 6. System (1) according to one of claims 1 to 5, characterized in that the absorption heat pump module Pa (37) comprises a frame (44), said frame being traversed by collecting pipes (39a-39f), a fuel inlet pipe (40) and electric power (41) and regulating (42) cables and comprising:  a refrigerant / air exchanger (54), a generator (52),  an absorber (51),  a refrigerant / water plate heat exchanger (53),  and auxiliary components of an absorption heat pump, such as: a pump, regulators. 7. System (1) according to one of claims 1 to 6, characterized in that the current generating module G (38) comprises a frame (64), said frame (64) being traversed by a pipe of arrival of fuel (40) and by power cables (41) and regulation (42), as well as by customer input and output collectors (39a, 39b 39d, 39e), said chassis enclosing:  at least one combustion engine type current generator (2) connected to its alternator (56) or a fuel cell and its inverter (57),  an exchanger for exchanging heat between the current generator (s) and the very hot water (59),  a global power and regulation cabinet (60) for the system; and  - power wiring for the arrival or sending of power to the network or other sources (61, 62, 63, 63 '). 8. System (1) according to one of claims 1 to 7, characterized in that it comprises a plurality of heat pump modules (36,37) and refrigeration modules (36A), including at least one module Pc compression heat pump system (36) and at least one refrigeration module (36B) and / or at least one Pa absorption heat pump module (37). 9. System (1) according to claim 8, characterized in that each heat pump module (36,37) or refrigeration (36A) comprises two sets of heat pump (36D) or refrigeration (36E). 10. System (1) according to one of claims 1 to 9, comprising a current generating module comprising one or two combustion engines (2), and at least one steam compression type heat pump module (36). ) and / or at least one refrigeration module (36A). 11. System (1) according to any one of claims 1 to 10, characterized in that its operation is controlled by at least one computer machine comprising at least one microprocessor and at least one data entry interface. 12. Use of the system (1) according to one of claims 1 to 11 in balneotherapy facilities, thalassotherapy, collective housing, for heating swimming pools, in hospitals or nursing homes, in hotels or residences. tourism, in agricultural greenhouses, or in industrial processes or installations requiring the simultaneous heating and cooling of water, used at points other than the said process or installation, or installations requiring a medium or low temperature refrigeration system such as as supermarkets, cold rooms or other. 13. Use according to claim 12 wherein: a) T3 <T1; and b) T3 is between -8 and +15 ^° C., in the case where the refrigerant is water added with glycol, or, in the case where the refrigerant is water, it is between and 4 and 15 ° C, and preferably between 5 and 9 ° C b) T4 is between -15 ° C and + 5 ° C and preferably between -10 and -5 ⁰ C c) T5 is between -45 ° C and -25 ⁰ C and preferably between -35 and -30 ⁰ C 14. Use according to one of claims 12 or 13, wherein: a) T1 is between 20 ^° C. and 60 ^° C., preferably between 30 ^° C. and 60 ^° C., and b) T2 is between 40 ^° C. and 75 ° C., preferably between 55 ° C. and 75 ° C. , and c) T2> T1. The method of regulating a modular system according to claim 11 wherein:  (A) At least one piece of data called "basic data" is selected from the group consisting of:  - (da1) the unit fuel cost of each combustion engine (2), fuel cell (22) and absorption heat pump used in system 1; - (da2) the energy content of each fuel; 0 - (da3) the CO ₂ impact of each fuel per unit mass; - (da4) the energy efficiency of each combustion engine (2) as a function of its load and its rotation speed, which makes it possible to determine the quantity of CO ₂ released per unit of mechanical power produced by this combustion engine ( 2); 5 - (da5) the full load rated power of each combustion engine  (2) according to its speed of rotation; (da6) the percentage of thermal power recovered on the cooling circuit of the combustion engine (2) and the percentage of thermal power recovered from the exhaust gases and / or the quantity of CO ₂ released O per unit of thermal power produced by the combustion engine (2),  (da7) the unit cost of the electrical energy supplied by the external network; - (da8) the lifetime of each generator according to its load;  - (da9) the maintenance cost of each generator according to the number of hours of operation; 5 - (da 10) the cost of dismantling and replacing each generator;  - (da11) the service life, the cost of maintenance, the cost of dismantling and replacing each type of heat pump;  - (da12) the efficiency of the alternator as a function of the electric power it provides, which makes it possible to determine the mechanical power required by the combustion engine (2) for a supplied electrical power;  - (da13) the efficiency of the fuel cell (22) as a function of its load; - (da14) the efficiency of the inverter of the fuel cell (22) or photovoltaic solar panels (23) when they exist; - (da15) the power consumption and the flow rate of the circulation pump of the solar collectors;  - (da16) the unit selling price of the electrical energy supplied to the external network; (b) at least one piece of data known as "instantaneous data" is selected from the group formed by:  - (db1) the instantaneous electric power produced by each present current generator;  - (db2) the rotational speed of each combustion engine (2);  - (db3) the instantaneous fuel consumption of the system (1);  (db4) the temperature of the fluid recovering the thermal energy of the combustion engine (2);  - (db5) the instantaneous electrical power consumed by the system (1) from the network, obtained by a direct measurement;  - (db6) the instantaneous power supplied to the network by the system (1), obtained by a direct measurement;  (db7) current, voltage or instantaneous electrical power produced by the photovoltaic solar panel (23) (if this panel is present);  - (dbδ) the instantaneous temperature T1;  - (db9) the instantaneous temperature T2;  - (db10) the instantaneous temperature T3;  (db11) the instant T4 temperature  - (db12) the instant T5 temperature  (db13) the temperature of the ambient air;  - (db14) the number of hours of operation of each electric power generator (mainly combustion engine 2 and fuel cell 22); (db15) the number of hours of operation of each heat pump circuit in the installation (vapor compression or absorption type).  (c) defining at least one datum called "target datum" to which is assigned a value called "target value", said target datum being selected from the group formed by:  (dd) the temperature T1 and its evolution as a function, in particular, of the outside temperature; - (dc2) the temperature T2 and its evolution depending in particular on the outside temperature; - (dc3) the temperature T3 and its evolution depending in particular on the outside temperature;  - (dc4) the temperature T4 and its evolution depending in particular on the desired temperature in the refrigerated chamber  - (dc5) the temperature T5 and its evolution depending in particular on the desired temperature in the refrigerated chamber - (dc6) the global COP as being the maximum overall COP for the system (1) or the overall minimum CO ₂ impact of the system (1);  - (dc7) the energy cost as the minimum energy cost of the system (1);  (dcδ) the total operating cost as the minimum total operating cost of the system (1).  (d) controlling the system (1) with said computer machine so as to achieve, for each of the selected target data, the determined target value or values, said regulation being performed by comparing the present value of the target data item; selected, which is determined from time to time or in a regular or continuous manner, taking into account the selected basic data or data and the instantaneous data (s) selected, and adjusting at least one piece of data called "adjustment data" selected from the group formed by  - (dd1) the type, the number of current generators in operation, and the electric power supplied by each of said generators;  (dd2) the assignment of the electrical powers supplied by the generator or generators respectively to the installation and to the external network to the system (1);  - (dd3) the type and number of heat pumps in operation;  - (dd4) in the case of steam compression heat pumps, the volumetric flow control (expressed in percent) imposed by the compressor control to optimize the system (1). to approach, for each selected target data, its current value to the target value.  16. Control method according to claim 15, characterized in that said basic data are entered into the microprocessor either during its initial programming, or during the startup of the system (1), or by the user of said system (1) over time during use of the system (1).