阅读说明：本技术 热力co2锅炉和热压缩机 (Thermal CO2 boiler and thermocompressor ) 是由 金-马克·乔夫罗伊 于 2018-04-12 设计创作，主要内容包括：一种将热量传递到至少一个加热回路(30)的热力锅炉,该锅炉包括使用R744型的可压缩流体形成热泵型回路(31,34)的压缩功能的至少一个压缩机(M1),锅炉进一步包括燃料燃烧器(11),其中所述燃烧器至少将热量传递到可压缩流体中。(A thermodynamic boiler for transferring heat to at least one heating circuit (30), the boiler comprising at least one compressor (M1) forming the compression function of a heat pump type circuit (31, 34) using a compressible fluid of the R744 type, the boiler further comprising a fuel burner (11), wherein said burner transfers at least heat into the compressible fluid.)

1. A thermodynamic boiler transferring heat to at least one heating circuit (30), the boiler comprising at least one compressor (M1) forming a compression function of the heat pump type circuit (31, 34) using a refrigerant, the boiler further comprising a fuel burner (11) transferring heat at least into the refrigerant, wherein the fuel burner transfers heat into the refrigerant downstream of the compressor.

2. The thermodynamic boiler according to claim 1, in which the refrigerant is a R744-type (CO2) compressible fluid.

3. A thermodynamic boiler as claimed in claim 1, wherein the compressor is a thermocompressor comprising at least one compression stage with a reciprocating piston (71), the fuel burner (11,11a) further forming a heating circuit for a heat source of the compressor and for a heat sink of the compressor.

4. The thermodynamic boiler according to claim 3, comprising a domestic hot water circuit (15, 16).

5. Thermodynamic boiler according to claim 3, in which the compressor's burner (11) forms the only burner of the boiler.

6. A thermodynamic boiler as claimed in claim 3, comprising a circuit (38) for the compressible fluid in the burner or in the immediate vicinity of the burner, and a pressure increase regulating valve (75) for selectively allowing the compressible fluid in the superheating circuit.

7. Thermodynamic boiler according to claim 3, in which the compressor's burner (11) allows the transfer of all the boiler's power.

8. -the device according to claim 4, characterized by comprising an exchanger (5), said exchanger (5) forming a basic thermal interface between the compressible fluid circuit (31) and the heating circuit (30), said exchanger (5) comprising a high temperature exchanger (50) and a low temperature exchanger (51), said high temperature exchanger being coupled with the domestic hot water circuit (15, 16).

9. A thermodynamic boiler as claimed in claim 3, wherein the heat pump type circuit comprises two cascaded circuits, a R744 type compressible gas working circuit (31, M1,5,7,6) and a glycol water circuit (34,4, 6).

10. Thermodynamic boiler according to claim 3, in which there is a modulation unit and an electric motor (17) to regulate, i.e. increase and/or decrease, the rotational speed of the compressor.

11. Thermodynamic boiler according to claim 3, in which the compressor comprises at least two compression stages in series, a first compression stage (U1) and a second compression stage (U2).

12. Thermodynamic boiler according to claim 11, comprising three stages (U1, U2, U3).

Technical Field

The present invention relates to a heating system comprising an apparatus called a boiler. The present invention relates in particular to thermal boilers using a plant known as heat pump (abbreviated to "HP").

Background

In the case of boilers, several solutions already exist for implementing heat pump devices.

First, it is known to compress and circulate a heat transfer working fluid using an electric compressor. The compressor is also referred to as "electric HP".

Gas engine heat pumps ("gas engines HP") are also known. The system involves the use of an internal combustion engine which is noisy and requires regular maintenance.

Desorption/adsorption type gas heat pumps are also known, for example using paired water/ammonia or water/zeolite gas heat pumps. But these devices are complex and expensive; in addition, these devices also use potentially contaminating or hazardous materials.

In addition, it is generally desirable for this type of boiler to be power-scalable and capable of providing domestic hot water ("DHW") on demand.

Furthermore, it is generally known that when the external temperature is low, especially in pneumatic thermal energy systems, in particular below 0 ℃, the heat pump loop performance is greatly reduced and the heat energy collection from the outside becomes almost negligible and almost zero when the external temperature is below-10 ℃.

This is why many boilers are equipped with an auxiliary burner (or "backup" burner) separate from the heat pump compressor, which transfers heat into the heating cycle, as described for example in WO 2014083440. These boilers are called "hybrid" because they have a heat pump circuit and a conventional backup burner. However, these "hybrid" boilers are relatively complex and expensive.

Disclosure of Invention

In this case, there is still a need to provide a more optimal solution for a thermodynamic boiler system with heat pump action.

To this end, a thermodynamic boiler for transferring heat to at least one heating circuit (30) is proposed, the boiler comprising at least one compressor (M1) forming the compression function of the heat-pump type circuit (31, 34) using a refrigerant, the boiler further comprising a fuel burner (11), wherein the burner transfers heat at least into the refrigerant and the fuel burner transfers heat into the refrigerant downstream of the compressor.

By these arrangements, the "auxiliary" or "backup" heat is transferred into the refrigerant circuit, which simplifies the system architecture of the boiler and makes it possible to use preferably a single heat exchanger with a heating circuit for both the HP function and the "backup" function.

Advantageously, a compressible fluid of the R744 type (in other words, substantially CO2) is chosen as refrigerant.

Note 1: in the above-described heat pump type circuit with R744 type compressible fluid, there is an evaporation phenomenon in one exchanger and a cooling/condensation phenomenon in the other exchanger. It should be noted that any type of refrigerant having physical properties close to those of R744 may be used as well in accordance with the present invention.

Note 2: with respect to the terminology used herein, it should be noted that "heating circuit" should be broadly construed as the primary circuit that exchanges heat with the associated entity, typically the house, with the goal of supplying heat to the house, but in some cases, particularly when the heat pump is reversible, the system may be used to cool the house.

In various embodiments of the invention, one or more of the following arrangements may also be used.

According to one aspect of the invention, the compressor is a thermocompressor comprising at least one compression stage with a reciprocating piston, the fuel burner further forming a heat source for the compressor and a heating circuit forming a heat sink for the compressor. Under these conditions, all the energy generated in the combustor can be used directly for compression or diffusion into the compressible fluid, and a portion diffused into the heating circuit in the form of exhaust gases, from a thermal efficiency point of view.

According to one aspect of the invention, the thermal boiler comprises a domestic hot water circuit. Advantageously, it is possible to release sufficient power with almost instantaneous availability of domestic hot water, without the need for a large-sized water storage tank.

According to one aspect of the invention, the combustor of the compressor forms the only combustor of the boiler. With such a single burner one can meet the energy needs, including high peak during peak periods (hot water is drawn out, allowing the second housing to get a normal temperature).

According to one aspect, a thermal boiler comprises a circuit (38) for superheating a compressible fluid circulating in a combustor of a compressor, and a pressure boost regulating valve (75) allowing a controlled portion of the compressible fluid in the superheating circuit; the boiler can thus be operated with modulated boost or without boost, depending on the position of the booster control valve. In addition, the booster power can be conveniently adjusted depending on the amount of gas injected into the burner and the degree to which the booster regulator valve is opened.

According to one aspect, the combustor of the compressor may allow for the discharge of all the power of the boiler, and the power is preferably between 20 and 25 kW. This power is sufficient for use by a conventional house of 100 square meters and 4/6 people.

According to one aspect, a thermal boiler can form an important thermal interface between a compressible fluid circuit (31) and a heating circuit (30), the heat exchanger comprising a high temperature heat exchanger (50) and a low temperature heat exchanger (51), the high temperature heat exchanger being coupled with a domestic hot water circuit; this arrangement makes it possible to obtain almost immediately hot water which can be produced at high temperatures.

According to one aspect, the heat pump type circuit may include two circuits in cascade, namely a working circuit of R744 type compressible gas (31, M1,5,7,6) and a circuit of glycol water (34,4,6), so the CO2 circuit can be limited to the boiler range without the need for a plumber process to coordinate with the final field installation required for the CO2 circuit.

According to one aspect, the modulation unit and the motor (17) may be configured to adjust, i.e. increase and/or decrease, the rotational speed of the compressor; the compressor speed can thus be adapted to the heating and hot water requirements in real time.

According to one aspect, the compressor may comprise at least two compression stages in series, a first compression stage (U1) and a second compression stage (U2); the CO2 type fluid (R744) can be used for large pressure fluctuations and a CO2 fluid temperature adapted according to the temperature of the water circuit being heated. Thus a better overall thermodynamic effect is obtained.

According to one aspect, the compressor may include three stages, according to which staged increases in pressure and optimization of temperature is achieved with sufficient CO2 fluid depending on the temperature of the water circuit to be heated and the temperature of the water circuit from which thermal power is to be released.

According to one aspect, the stages are advantageously independent. This helps in sizing and increases the adjustment possibilities for each stage.

According to one aspect, the compressor may comprise at least two parallel compression stages. This represents an alternative configuration in the series of configurations.

According to one aspect, the thermal boiler may comprise an air preheater (9) at the first burner inlet. Whereby thermal energy is recovered from the combustion exhaust gases and injected into the air for the burner, which improves the overall coefficient of performance.

According to one configuration, called heating, the thermal boiler supplies thermal energy to a heating circuit ("heating" or "winter" mode) and the reversible heat pump type circuit receives heating from an external device.

According to another configuration, called air conditioning, the thermal boiler receives heating from the heating circuit 30 and releases this heat either into the domestic hot water circuit DHW or into the external device 4 (summer mode); whereby the boiler can provide an air conditioning function and reheating domestic hot water is a free energy approach

Drawings

Other characteristics, objects and advantages of the invention will become clear from reading the following description of an embodiment of the invention, given as a non-limiting example. The invention may be better understood by reference to the accompanying drawings in which:

fig. 1 schematically shows a heating system according to the invention, comprising a boiler,

fig. 2 shows a system similar to that of fig. 1, the boiler comprising a thermocompressor,

fig. 3 shows a system similar to fig. 2, wherein the boost pressure is transferred directly to the high temperature portion of the thermocompressor,

figure 4 schematically shows a stage of the thermocompressor,

figure 5 shows a graph of power versus temperature,

figure 6 shows a stage of the thermocompressor in more detail,

figure 7 shows a thermodynamic cycle in which,

figure 8 shows a three stage configuration of the thermocompressor,

figure 9 schematically shows a schematic view of the adjustment system,

fig. 10 illustrates the reversibility of the heat pump circuit.

Detailed Description

The same reference numbers in different drawings identify the same or similar elements.

Fig. 1 shows an overview of a heating system typically used for heating an industrial plant or an individual or collective premises. The heating system includes a boiler 10, which will be described below.

The system includes a heating circuit, designated 30; as mentioned in the opening paragraph, the term "heating circuit" does not exclude a heat absorption circuit, but in the first example shown the heating circuit comprises a heated body 3 in the form of a radiator/convector 3 and/or a floor heating, located in the room of the site to be heated.

There may be several heated entities, for example one low temperature (floor heating) heated entity and another higher temperature (convection room warmer, domestic hot water) heated entity. Circulator M3 circulates water in heating loop 30.

It is also possible to handle the case where the heated entity is a pool or a greenhouse. Likewise, the heating system may be used in an industrial environment with a heated entity in the form of an industrial process plant.

The production of domestic hot water ("DHW") is provided, and the tank 16 of known domestic hot water is not described in detail herein. As the water flows through the DHW exchanger 15, the water in the tank is heated by circulation of a fluid 36.

Advantageously, in the case of the present invention, the tank 16 can be very small in volume, for example 5 litres, typically less than 10 litres.

In this DHW, the switch 15 loops back to the bypassed branch 33 of the acknowledgement loop 30. This bypass branch absorbs heat from a high temperature heat exchanger (HT), indicated with 50, and transfers the heat to the domestic hot water through the DHW exchanger 15.

The flow rate of fluid in the bypass branch 33 can be controlled by a known DHW control valve 78. The flow rate is proportionally determined according to the requirements of a domestic hot water tank regulating system.

The boiler 10 comprises a compressor M1, wherein the compression mechanism forms the driving part of the heat pump circuit. In the example shown, the external unit (building, house, etc.) labeled 4 is provided only outside the house, with the remainder of the major components being provided on the in-range side, or within the boiler 10 enclosure.

Note that in the drawings, the pipes are symbolically represented.

The heat pump apparatus comprises a glycol water circuit 34 circulating in the external unit 4, and a working fluid circuit 31 passing through a compressor M1. In the example shown, the working fluid is R744, in other words CO2, but another fluid with similar properties may be chosen. To distinguish it from other fluids, the working fluid of the circuit 31 is hereinafter referred to as a "compressible" fluid (also referred to in the art as "refrigerant"). This is in contrast to the fluid flowing outwardly in the external device (loop 34), which is predominantly water-based (glycol water), and also in contrast to the fluid flowing in the already mentioned heating loop 30, which is also predominantly water-based and therefore incompressible.

The various fluids used in the circuits 30, 31, 34 are heat transfer fluids. The heat transfer fluid, whether it is compressible or not, makes it possible to transfer mainly the heat of the external unit 4 to the heated entity 3, and also from the burner 11 to the heated entity 3.

The same possible air conditioning modes will be described further below.

It should be noted that the external unit 4 may be a pneumatic thermal unit or a geothermal unit.

It will be noted that the collection of external heat by the heat pump effect uses two fluid circuits in series, which are interfaced by a heat exchanger, referred to as the interface heat exchanger 6, which is preferably cross-flow. The glycol water 34 includes a circulator M4 that recovers heat from the external unit 4 and transfers the heat to the interface heat exchanger 6. It can be seen that the entire compressible fluid circuit 31, i.e. the CO2 circuit, is enclosed inside the boiler 10, which is manufactured in a production plant; only the glycol water circuit 34 has to be performed by a professional on the target device.

In addition, the heat pump device comprises a known relief valve 7, which exerts an anti-phase effect on the pressure to the compressor, and a heat exchanger 5 thermally connected to the compressible fluid circuit 31, the compressible fluid circuit 31 exiting the compressor with the heating circuit 30.

The exchanger 5 here comprises two exchangers arranged in series on the CO2 loop 31: a "high temperature HT" heat exchanger 50, in which a bypass 33 for heating domestic hot water circulates, and a "low temperature LT" heat exchanger 51, which forms the main coupling of the CO2 loop 31 with the heating loop 30.

The main heat exchanger 5 can also form a single heat exchanger with a first portion coupled with the domestic hot water circuit 33 and a second portion coupled with the heating circuit 30.

The compressible fluid circuit 31 contains the fluid in a two-phase form, wherein on the one hand heat is recovered from the interface heat exchanger 6 (the "evaporator" side, where the two-phase fluid passes from the liquid to the vapor state) and on the other hand this heat is released to the main heat exchanger 5 (the "condenser" side, where the two-phase fluid is cooled down). The compressible fluid is cooled in exchanger 5, but remains substantially in the vapour phase; the compressible fluid expands at the expansion valve 7, substantially changing into a liquid phase.

In the fig. 1 configuration, compressor M1 may be a compressor with an electric motor; in this case, a booster burner 11 is provided downstream of the compressor, which transfers heat directly into the compressible fluid downstream of the compressor, the regulating power of which is sufficient to meet the energy demand in the heating circuit and/or in the domestic hot water circuit.

Note that the backup heat is transported in the compressible fluid and not in the exchanger directly with the heating circuit.

In the fig. 2 configuration, the compressor M1 may be a compressor driven by a gas engine. The gas engine uses a burner, indicated with 11 a. The gas engine drives the compressor M1 and the other combustor 11b forms a heat assist in the compressible fluid circuit as previously described, in other words, downstream of the compressor M1.

In the fig. 3 configuration, compressor M1 is a thermocompressor, meaning that it uses thermal energy as the heat source and uses the heat source to activate the piston, the reciprocating movement of which and the use of a check valve make up the compressor. See WO2014202885 and fig. 6 herein for exemplary details of this type of thermocompressor.

In the fig. 3 configuration, only one combustor 11 forms the hot compressor M1 and heat assisted heat source, since it is advantageous to direct the R744 compressible fluid to the compressor combustor environment at the compression stage exit and circulate it to extract heat energy from the combustor (this location does not require supplemental compression). In figures 3, 4,6 and 8, the circuit circulating in the hot part of the compressor is marked 38. Also referred to as the "superheat circuit" 38 in the remainder of this document. The superheating circuit 38 includes a first portion, also referred to as an upstream portion 38a, and a second portion, also referred to as a downstream portion 38 b.

It will be noted that the circulation in the compressor hot section is determined by the auxiliary control valve 75 which is open at any angle between the two positions, i.e. all CO2 pointing to the first extreme position of the compressor hot section (in case of need of auxiliary equipment) and all CO2 pointing directly to the second extreme position of the main heat exchanger 5 with heating circuit (all closed), not through the high temperature part of the compressor.

It will be noted that when the compressor M1 is running and the selector valve 75 is in the fully closed position, the working fluid stagnates in the superheating circuit 38, in which cycle its temperature rises close to that of the combustor, typically between 600 ℃ and 700 ℃ (see below). However, due to the physical properties of the selected fluid (in other words CO2), there is no risk of high overpressure or explosion.

When the compressor is running and the selector valve is in the first position, in the downstream portion 38b of the recirculation loop, the temperature of the CO2 compressible fluid is between 100 ℃ and 300 ℃, depending on the boost power provided on the combustor.

In the fig. 3 configuration, the power delivered to the individual burners 11 may be adjusted between 0 and 20 kW. The output power is in particular between 3 and 6kW when the compressor operates without any supercharging. When boost is required, the compressor is running (representing 3 to 6kW), and the combustor provides the remainder of the power (representing 2 to 15kW) directly to the working fluid recirculated in the superheating circuit 38.

A balance between powers is involved as shown in fig. 5. The "no auxiliary power available" curve, labeled 95, represents the sum of the power provided by the compressor and the free collection of energy in the external environment. Curves 96a, 96b, 96c represent the heating requirements of three types of dwellings at steady state.

The "need for assistance" condition occurs when the external temperature is in the region below the threshold of-5 ° to 0 ℃.

Furthermore, this figure does not represent a peak in demand, for example, the production of domestic hot water depending on the number of persons using showers, toilets, kitchens. This figure also does not show peaks in demand to return an occasional residential home to normal temperature.

In the configurations of fig. 2 and 3, it will be noted that the return of the heating circuit 30 passes first through the main heat exchanger 5, 51 and then towards the cold zone of the compressor where the fluid of the heating circuit cools the compressor M1.

In all configurations, it can be provided that the outlet circuit (referenced 32) of the combustion gases of the burner 11, through the inside of the exchanger 21 coupled to the heating circuit, where the (burnt) exhaust gases deliver their thermal energy to the fluid of the main heating circuit 30.

On the other hand, in all configurations, an intake preheat exchanger, indicated at 9, may be provided, which uses the thermal energy present in the gas exiting the burner 11 to bring preheated fresh air 35 to the burner flame. The pre-heat exchanger 9 is known as an air-to-air exchanger, used in conjunction with the cross-flow in the example shown.

Thus, the temperature of the air entering the nozzle of the burner 11 is between 100 ℃ and 200 ℃.

The amount of gas introduced and combusted by the burner 11 is controlled by a control unit 1 (see fig. 9), which control unit 1 comprises at least one servo loop (typically between 600 ℃ and 700 ℃) for maintaining the temperature of the high temperature part of the compressor M1 at a target temperature. The control unit 1 controls not only the amount of gas delivered to the burner 11 (by rich amount control) but also the DHW control valve 78 and, if necessary, the rotational speed of the adjustment motor 17 to be described later. In addition, to manage the auxiliary heating demand, the control unit also controls the position of a selector valve 75, wherein said selector valve 75 activates or deactivates the overheating circuit 38.

Specifically, a temperature sensor 61 is provided, wherein the temperature sensor captures the temperature of the casing 110 of the combustor including the compressor (see fig. 6). The control unit may also receive various temperature and flow information 62,63 from the domestic hot water circuit for controlling a general thermostat in the house with a temperature 66 set by the user, etc.

Depending on the current configuration and temperature, such control may include all or none of the decisions (on/off cycles) and/or continuous servo control for the burner flow, for the boost regulator valve 75, and for the DHW control valve 78.

More specifically, with regard to the composition of the compressor M1, reference is made to fig. 6, which is a "regenerative" thermocompressor with a supply thermal energy zone (hot zone), a cooling zone (cold zone), a closed chamber 8 communicating with the outside through two non-return valves, an inlet valve 41 (feed) and an outlet valve 42 (discharge).

In the example of fig. 4 and 6, there is only one compression stage, labeled U1, wherein in the example of fig. 8, this compression stage has three stages of compression, in other words, three compression units U1, U2, U3.

In the closed chamber 8, the compressible fluid volume is almost constant and the displacement piston 71 is configured to alternate in the example shown from top to bottom movement to flow the majority of the compressible fluid to the hot or cold zone. The piston is connected to a connecting rod and crankshaft system in a self-driven system as shown below.

As shown in fig. 6, the compressor is designed around the shaft direction X, which is preferably vertical to the installation, but other arrangements are not excluded. The piston 71, which is mounted for movement within the cylindrical sleeve 90, is movable along the axis. The piston separates a first chamber 81 and a second chamber 82, which are comprised in the working chamber 8 and whose volume V1+ V2 is substantially constant in sum. The piston 71 has a dome-shaped upper portion, for example, a hemisphere.

The working chamber 8 is structurally housed in the assembly formed by the hot shell 96 and the cold cylinder head 95, with the interposition of an insulating ring 97.

The first chamber 81, also referred to as the "hot chamber," is disposed above the piston and is thermally coupled to the heat source 11 (the fuel-fired burner 11), which provides heat directly to the gaseous fluid. The first chamber is a body of revolution having a cylindrical portion with a diameter corresponding to the piston diameter D1 and a domed portion including a central opening 83 for the inflow and outflow of compressible fluid. The heat source 11 forms a cover 110 disposed around the hot chamber 81 with a burner nozzle in the center.

A second chamber 82, also referred to as a "cold chamber," is disposed below the piston and couples a cold source (here, the return of the heating cycle 91) to transfer heat from the compressible fluid to the heating cycle. The second chamber is cylindrical with a diameter D1 and includes a plurality of openings 84 arranged in a circle around the axis, below the piston, for the inflow and outflow of the compressible fluid.

Around the wall of the cylindrical sleeve 90 is arranged a regenerative heat exchanger 19 of the type commonly used in stirling-type thermodynamic engines. The exchanger 19 (also referred to below simply as "regenerator") comprises a gapless engagement of fluid channels and/or wires with a small cross-sectional area and thermal energy storage elements. The regenerator 19 is disposed at an intermediate height between the upper and lower ends of the chamber and has a hot side 19a facing the top and a cold side 19b facing the bottom.

Inside the regenerator, a high temperature gradient can be observed between a hot side, the temperature of which is close to that of the burner cover, i.e. 700 ℃, and a cold side, the temperature of which is close to that of the burner, i.e. a temperature between 30 ℃ and 70 ℃, depending on the entities present on the heating circuit.

An annular circulation gap 24, located against the inner surface of the thermal housing 96, connects the opening 83 of the first chamber with the hot side 19a of the regenerator.

A channel 25 in cylinder head 95 connects opening 84 of the second chamber to the cold side 19b of the regenerator.

Thus, as the piston rises, the first chamber 81 drives the compressible gas through the circulation gap 24, regenerator 19 and channel 25 into the cold second chamber 82. Conversely, when the piston is lowered, the second chamber 82 drives the compressible gas, via the channel 25, regenerator 19 and circulation gap 24, into the first chamber 81.

The operation of the compressor is performed by the reciprocating movement of the piston 71 between the bottom dead center BDC and the top dead center TDC, and by the action of the inlet suction valve 41 and the outlet discharge check valve 42. Each of steps A, B, C, D, described below, is represented in fig. 6 and 7.

Step A

The piston is initially at the top, moving downwards and as the first chamber 81 increases in volume, the second chamber 82 decreases in volume. The fluid is thus pushed from below upwards, flows through the heat accumulator 19 and is heated in the process. The pressure Pw increases accordingly.

Step B

When the pressure Pw exceeds a certain value, the outlet valve 42 opens, and the pressure Pw may stabilize at the compressed fluid outlet pressure P2 and discharge the fluid to the outlet (of course, during which the inlet valve 41 remains closed). This continues until the piston reaches bottom dead center.

Step C

The piston now moves from bottom to top and the second chamber volume increases while the first chamber volume decreases. The fluid is thus pushed from above downwards, flows through regenerator 19, and cools in the process. The pressure Pw decreases accordingly. The outlet valve 42 closes at the beginning of the upward movement.

Step D

When the pressure Pw drops below a certain value, the inlet valve 41 opens, the pressure Pw stabilizes at the fluid inlet pressure P1, and fluid is drawn into the inlet (of course, the outlet valve 42 remains closed during this time). This continues until the piston reaches top dead center. When the piston begins to descend, the inlet valve 41 closes.

The movement of the lever 18 is controlled by a self-driving device 14 acting on one end of the lever. The self-propelled device comprises a flywheel 142 rotating about an axis Y1, a connecting rod 141 connected to said flywheel by a pivot connection, for example a rolling bearing 143. The link 141 is connected to the lever by another pivotal connection, for example, a roller bearing 144.

The auxiliary chamber 88 is filled with a gaseous working fluid, marked Pa. When the apparatus is operating, the pressure Pa in the auxiliary chamber 88 converges to an average pressure substantially equal to half the sum of the minimum P1 and maximum P2 pressures. In fact, since the functional clearance between the ring 118 and the stem 18 is reduced in the dynamic mode, very little leakage does not affect operation and is still negligible.

When the flywheel makes one revolution, the piston clears a volume corresponding to the distance between the neutral point and the bottom dead center, multiplied by the diameter D1.

As shown in fig. 7, the thermodynamic cycle provides positive power to the self-propelled device.

However, for initial start-up, in order to be able to adjust the rotational speed, an electric motor 17 is provided which is coupled to the flywheel 142.

The motor may advantageously be housed in the auxiliary chamber 88, or externally, and coupled to the wall by magnetic force.

The motor 17 is controlled by a control unit not shown. The motor may be controlled to increase or decrease the speed of the flywheel, the heat flow being more or less proportional to the speed of the flywheel. Due to the motor 17, the control unit can adjust the rotation speed between typically 100rpm and 500rpm, preferably in the range of 200 and 300 rpm.

It is noted that the motor 17 is used to start the self-driving device.

Note that the piston 71 is not a power receiving piston (unlike an internal combustion engine or a conventional stirling engine), but is simply an exhaust piston; power is provided in the form of an increase in working gas pressure.

Note that if the rod 18 volume change is neglected, V1+ V2+ Vchannel is Vtotal, where V1 is the volume of the first chamber, V2 is the volume of the second chamber, and Vchannel is the volume of the catheter 24, 25. It is preferred to provide a device with as small a dead volume as possible and with a small cross-sectional area, for example, Vchannel < 10% V1+ V2 can be achieved.

Fig. 8 shows the complementary characteristics, i.e. a structure with three compression stages, in other words with three compression units U1, U2, U3.

The second and third stages U2 and U3 are identical or similar in all respects to the first stage U1; each stage comprises a burner 12, 13, in which combustion of the gas mixed with the intake air takes place, and a displacement piston 72, 73 which is independent of the first-stage piston and whose movement and rotation speed are independent of the first stage.

Advantageously, these phases are all operated independently; the rotation speeds of the stages may be different from each other.

It will be noted that the heating circuit cools the three cold zones of the compressor through the successive passages 93, 92 and 91.

The outlet of the first stage, valve 42, is connected to the inlet of the second stage, valve 43. The outlet of the second stage, valve 44, is connected to the inlet of the third stage, valve 45. The outlet of the valve 46 forms the general outlet of the compressor 1.

The phasing of the pressure is generally as follows: the inlet pressure of the first stage U1 was about 20 bar; the discharge pressure of the first stage (second stage inlet) was about 40 bar; the discharge pressure of the second stage U2 (third stage inlet) was about 60 bar; the outlet pressure of the third stage U3 was about 80 bar.

It can be arranged so that the three cold zones of the three stages Ul, U2, U3 form an integral part, i.e. the cold cylinder head.

Of course, a device may also have two-phase configurations U1, U2.

Further, a configuration may be provided in which two (or more) stages are arranged in parallel, which stages are similar to the above-described stages.

In general, it is noted that the fuel used in the burner may be natural gas, biogas of plant or animal origin, or light hydrocarbon waste from the processing of the petroleum industry.

In addition to domestic hot water, a large amount of power is required when heating the second set of houses, which are occasionally occupied, to normal temperature. The proposed arrangement allows 20kW of power to be provided but requires a longer time to be able to heat or cool the dwelling.

As shown in fig. 10, the above-described thermocompressor 1 can be used in the heating mode shown in fig. 1 to 3 and is also suitable for air conditioning due to its reversibility.

In this case, in the air conditioning mode, heat is taken from the heating circuit 30 (for example, in underfloor heating) and the collected heat is directed to the domestic hot water circuit 15,16 or the external unit 4.

This result can be obtained by reversing the function of the evaporation and condensation exchangers 5', 6' on the compressible gas circuit 31.

For clarity, the four-way valve 77 is not shown in fig. 1 and 2, and the four-way valve 77 can reverse the flow of fluid, but the principle is shown in fig. 10, wherein the four-way valve 77 has a normal position, i.e., heating mode, and a special position (inverted), i.e., air conditioning mode, which reverses the known function of the exchangers labeled 5' and 6.

For clarity, components in a portion of the boiler system may not be shown, and then such components may be present. These components include:

expansion vessels 34, 30 on the water circuit

Valve switch for filling and flushing heating circuit

Valve switch for injecting and flushing CO2 loop

Various pressure and temperature sensors required for the control system in the control unit

Loop summary

30 heating loop

31 CO2 compressible fluid

32 combustion gas

33 bypass of DHW

34 ethanolate Water (exchange with external)

35 heated intake air

DHW specific loop