THERMODYNAMIC BOILER WITH THERMAL COMPRESSOR

专利摘要:
A thermodynamic boiler for exchanging (supplying or withdrawing) calories with a heating circuit (30), the boiler comprising a thermal compressor (1), the thermal compressor acting on a compressible fluid and comprising at least one piston compression stage (71) ), separating a first chamber (81) and a second chamber (82), and a first hot source fuel burner (11) coupled to the first chamber, and using the heating circuit as a cold source coupled to the first chamber (82), second chamber, the thermal compressor forming the compression function of a reversible heat pump type loop (31, 34).
公开号:FR3042857A1
申请号:FR1560169
申请日:2015-10-23
公开日:2017-04-28
发明作者:Jean-Marc Joffroy
申请人:BOOSTHEAT；
IPC主号:

专利说明:

Thermodynamic boiler with thermal compressor
The present invention relates to heating systems that include devices called boilers. We are particularly interested in thermodynamic boilers taking advantage of a device known as heat pump (called 'PAC' abbreviated).
Background and prior art
Several technical solutions already exist to implement a heat pump device in the context of a boiler.
Firstly, the use of electric compressors for compressing and circulating a coolant working fluid is known. There is also talk of 'electric heat pump'. However, the efficiency of these systems decreases sharply with the decrease in outside temperature which leads to resort in most cases to a conventional auxiliary booster fuel burner.
Gas-powered heat pumps ('gas-powered PAC') are also known. This system involves the use of an internal combustion engine that is noisy and requires regular maintenance.
Desorption / adsorption gas heat pumps are also known, for example those using a water / ammonia or water / zeolite pair, for example from US5729988-Tcherne. But these devices are complex and expensive; moreover, they use potentially polluting or harmful materials.
In addition, in general, it is preferable that this type of boiler is adaptable in power and is also intended to provide hot water (called 'DHW').
In addition, in general, most of the systems described above can operate reversibly in cooling mode.
Given the aforementioned drawbacks, there remains a need to provide improved solutions for heat pump thermodynamic boiler systems. For this purpose, it is proposed a thermodynamic boiler for exchanging calories with at least one heating circuit, comprising a thermal compressor, the thermal compressor acting on a compressible fluid and comprising at least one compression stage with a reciprocating piston separating a first chamber and a second chamber and a first hot source fuel burner coupled to the first chamber, and using the heating circuit as a cold source coupled to the second chamber, the thermal compressor forming the compression function of a loop type reversible heat pump.
Thanks to these provisions, it takes advantage of a direct heat transfer between the burner and the working fluid to be compressed, the compressor is simple and compact, the reversible heat pump type loop can be used either to bring calories to the circuit in heating mode ('winter' mode), or in some cases to take heat from the heating circuit in cooling mode ('summer' mode).
In addition, such a boiler requires very little maintenance and maintenance operations can be substantially spaced.
Note 1: Regarding the vocabulary used in this document, it should be noted that what is called here heating circuit should be interpreted broadly as a main heat exchange circuit with an entity of interest, usually a local , the goal being to warm or cool the entity of interest.
Note 2: in the aforementioned heat pump-type loop, a compressible two-phase heat-transfer fluid is used, and advantage is taken of an evaporation phenomenon on one exchanger and a condensation phenomenon on another exchanger.
According to a so-called heating configuration, the thermodynamic boiler supplies calories to the heating circuit ('heating' or 'winter' mode), and the reversible heat pump type loop takes heat from an outdoor unit.
Under these conditions, from the point of view of thermal efficiency, all the energy expended on the burner is either used directly for compression or diffused into the heating circuit. In addition, the compression and the associated fluid circuit induce a 'free' calorie intake on the outside. As a result, a very satisfactory coefficient of performance is obtained under these conditions.
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 thermodynamic boiler may comprise a booster device, the booster device comprising an auxiliary burner, distinct from the first burner and a booster exchanger arranged on the heating circuit. One can thus ensure on the one hand operation in very cold external temperature conditions, or if the PAC circuit is unavailable and on the other hand the peak passage (s) of need, especially for domestic hot water accumulated with the need heating.
According to one aspect of the invention, the fuel is advantageously gas. Advantageously, one uses either gas of fossil origin or bio gas.
According to one aspect of the invention, the heat-transferable fluid is CO 2; it is a fluid available, non-polluting and safe.
According to one aspect, it is advantageously provided a modulation unit and a motor (electromagnetic actuator linked to the movement of the piston) for regulating (increasing and / or decreasing) the speed of rotation of the compressor. Such a power modulation makes it possible to obtain an ideal comfort / seasonal performance compromise, and makes it possible to maximize the utilization rate of the heat pump.
In one aspect, the heat pump-type loop comprises two cascade circuits, namely a compressible gas working circuit (31,1,5,7,6) and a brine circuit (34,4, 6); which makes it possible to have a compressible gas working circuit confined in a boiler assembly, sealed directly in the factory, which prevents the plumber or the installer from worrying about the tightness of this circuit; conversely the brine circuit which is easier to implement can be installed by the plumber.
In one aspect, the compressor may comprise at least two compression stages in series, namely at least one second compression stage U2, in addition to the first U1. By means of which one can use a CO 2 type fluid (R744) with a large pressure excursion and fluid temperatures CO 2 adapted according to the temperatures of the water circuits to be heated. We thus obtain a good overall thermodynamic efficiency.
In one aspect, the compressor may comprise 3 stages; whereby the staging of the pressure surges and the suitability of the adapted CO 2 fluid temperatures as a function of the temperatures of the water circuits to be heated and the thermal power to be delivered are optimized.
The stages are advantageously independent. This facilitates sizing and increases the modulation possibilities of each stage.
The thermodynamic boiler comprises an air preheater at the inlet of the first burner; calories are recovered in the combustion fumes and injected into the air for the burner; which improves the overall coefficient of performance.
The thermodynamic boiler comprises a main exchanger (5) forming the essential thermal interface between the compressible fluid circuit (31) and the heating circuit (30), and the compressor is cooled by the return of the heating circuit which passes from first in at least one main exchanger 5, then in the cold section of the thermal compressor; which is the most sensible choice for the good performance and efficiency of the system.
In addition, the return of the heating circuit passes, after cooling the compressor, in the exchanger booster. This maximizes the calories supplied to the heating circuit. The main exchanger comprises a high temperature exchanger ΉΤ 'and a low temperature exchanger' BT '; it is thus possible to provide a supply of calories to two different heating circuits, one having a high average temperature (coupled to the HT) and the other having a moderate high temperature (coupled to the BT);
The thermodynamic boiler includes a domestic hot water circuit; it can thus fulfill all the functions of a domestic boiler. The domestic hot water is heated by means of the high temperature exchanger (50) which is arranged on the compressible fluid circuit directly at the outlet of the thermal compressor; this contributes to the priority given for hot water.
According to a so-called air-conditioning configuration, the thermodynamic boiler takes heat from the heating circuit 30 and delivers these calories either in the domestic hot water circuit ECS or in the outdoor unit 4 (summer mode); thus the boiler can provide an air conditioning function, and in addition to the free hot water energetically. Other aspects, objects and advantages of the invention will appear on reading the following description of an embodiment of the invention, given by way of non-limiting example. The invention will also be better understood with reference to the accompanying drawings, in which: FIG. 1 schematically represents a heating system comprising a boiler according to the invention, FIG. 2 represents a system similar to FIG. 1, the boiler being a hybrid and including a backup burner; FIG. 3 shows a system similar to FIG. 1, in which an air preheating exchanger is provided and the compressor of the boiler comprises two compression stages; FIG. a system analogous to FIG. 3, in which in addition the supply of domestic hot water is ensured; FIG. 5 represents a system similar to FIG. 4, the compressor of the boiler comprising three compression stages; FIG. a stage in more detail, that is to say a compression unit used in the thermal compressor; - FIG. 7 represents the thermodynamic cycle in a stage, - FIG. 8 represents the central parts of a compressor in the three-stage configuration, FIG. 9 represents a very general diagram of the use of a thermal compressor according to the invention in a reversible heat pump-type loop. , usable in heating mode or in cooling mode.
In the different figures, the same references designate identical or similar elements.
Figure 1 shows an overview of a heating system typically provided for heating an industrial premises, an individual or collective housing. The heating system comprises a boiler 10 which will be described below.
The system comprises a heating circuit marked 30; as announced at the beginning, the term "heating circuit" does not exclude that circuit draws calories, however in the first example as illustrated, the heating circuit includes caloric receiving entities 3 in the form of radiators / convectors 3 and / or a floor heating, located in rooms of the room to be heated.
There may be several calorie-receiving entities, for example one at low temperature (underfloor heating) and another at higher temperature (convectors, domestic hot water). A circulator M3 circulates water in the heating circuit 30.
The case where a calorie-receiving entity is a pool or a greenhouse can also be treated. Similarly, the heating system can be used in an industrial context with the calorie-receiving entity in the form of industrial process equipment.
The boiler 10 comprises a thermal compressor 1 which constitutes the driving component of a heat pump circuit. In the example shown, only the outdoor unit marked 4 is arranged outside the room (building, home, etc.) the rest of the main components is arranged inside the room, or even in the envelope of the boiler 10.
It is noted that in the figures, the pipes are represented symbolically.
The heat pump device comprises on the one hand a brine circuit 34 which circulates in the outdoor unit 4, and a circuit 31 of working fluid which passes through the compressor 1. In the illustrated example, the Working fluid is R744 ie CO2, but another fluid with similar properties could be chosen. In order to distinguish it from other fluids, the working fluid of the circuit 31 will be referred to as the "compressible" fluid, also called "refrigerant" fluid in the art. This as opposed to the fluid flowing outwardly into the outdoor unit (circuit 34) which is mainly water-based (brine), and also as opposed to the fluid flowing in the already mentioned heating circuit 30 which is also mainly water-based, so not compressible.
The various fluids used in the circuits 30, 31, 34 are heat transfer fluids, whether they are compressible or not, they make it possible to transfer calories mainly from the outdoor unit 4 to the receiving entities 3, but also from the burner 11 from the compressor to the receiving entities 3.
The air conditioning mode, also possible, will be described later.
It should be noted that the outdoor unit 4 may be an aerothermal or geothermal unit.
It is noted that the capture of external calories by the heat pump effect uses two fluid circuits in series which are interfaced by the exchanger 6 called interface exchanger 6, exchanger preferably cross flow. The brine circuit 34 comprises a circulator M4, recovers calories from the outdoor unit 4 and delivers these calories to the interface exchanger 6. It can be seen that the entire compressible fluid circuit 31, namely the CO 2 is confined inside the boiler 10 which is prepared in the manufacturing plant; only the brine circuit 34 must be implemented by a professional on the target installation.
In addition, the heat pump device comprises a pressure regulator 7, known per se, which acts as the inverse of the compressor for the pressure, and a main exchanger 5 which thermally couples the compressible fluid circuit at the compressor outlet with the compressor circuit. Heating 30. The main exchanger 5 is preferably configured as a cross-flow exchanger. Instead of a single heat exchanger 51 as shown, the main exchanger may consist of several exchangers, either in parallel or in series as will be seen later.
The compressible fluid circuit 31 contains fluid in two-phase form which recovers heat from the interface exchanger 6 (so-called 'evaporator' side where the two-phase fluid goes from the liquid state to the vapor state) and delivers these calories. on the main exchanger 5 (so-called 'condenser' side where the two-phase fluid goes from the vapor state to the liquid state).
Note that the return of the heating circuit 30 passes first through this main heat exchanger 5 and is then directed to the cold zone of the compressor at which the fluid of the heating circuit cools the compressor 1.
It is noted that the flue gas discharge circuit (noted 32) of the burner 11 passes inside an exchanger 21 coupled with the heating circuit, where the fumes yield their calories to the fluid of the main circuit. heating 30; it will be seen later that this exchanger 21 can also be called in some cases "exchanger booster" 21.
The amount of gas introduced and burned by the burner 11 is controlled by a control unit (not shown) of the boiler.
The burner 11 is typically sized to deliver up to 6 kW; in practice when the compressor is in operation, the regulation adjusts the power between 2 kW and 6 kW.
More specifically, with regard to the compressor 1, with reference to FIG. 6, it is a so-called 'regenerative' thermal compressor with a calorie supply zone (hot zone) a cooling zone (cold zone), a closed chamber 8 which communicates with the outside through two check valves, namely an inlet valve 41 (inlet) and an outlet valve 42 (discharge).
In the example of FIG. 1, there is only one compression stage denoted U1.
In the closed chamber 8, the compressible fluid occupies an almost constant volume, and a displacer piston 71 is configured to move alternately, from top to bottom in the example shown, in order to move the bulk of the compressible fluid volume. to the hot zone or to the cold zone. The piston is connected to a crankshaft and crankshaft system in a drive system that will be seen later.
As shown in FIG. 6, the compressor is structured around an axial direction X, which is preferably arranged vertically, but another arrangement is not excluded. According to this axis can move the piston 71 mounted to move in a cylindrical jacket 90. Said piston separates the first chamber 81 and the second chamber 82, these two chambers being included in the work enclosure 8 with the sum of their volumes V1 + V2 substantially constant. The piston 71 has an upper dome-shaped portion, for example hemispherical. The working chamber 8 is structurally contained in an assembly formed by a hot casing 96 and a cold cylinder head 95, with the interposition of a thermal insulating ring 97.
The first chamber 81, also called 'hot chamber', is arranged above the piston and thermally coupled to a hot source 11 (a fuel burner 11) which supplies calories directly to the gaseous fluid in the first chamber 81. The first chamber is of revolution with a cylindrical portion of diameter corresponding to the diameter DI of the piston and a hemispherical portion in the upper part, which comprises a central opening 83 for the inlet and the outlet of the compressible fluid. The hot source 11 forms a cap arranged all around the hot chamber 81, with a burner injector 11a.
The second chamber 82, also called "cold room", is arranged below the piston and thermally coupled to a cold source (here the return of the heating circuit 91) to thereby transfer heat from the compressible fluid to the heating circuit. The second chamber is cylindrical, of diameter D1, and comprises several openings 84 arranged in a circle about the axis, under the piston, for the inlet and the outlet of the compressible fluid.
Around the wall of the cylindrical liner 90 is arranged a regenerative exchanger 19, of the type conventionally used in thermodynamic machines Stirling machine type. This exchanger 19 (which will also be called simply "regenerator" in the following) comprises fluid channels of small section and thermal energy storage elements and / or a tight network of metal son. This regenerator 19 is arranged at an intermediate height between the upper end and the lower end of the enclosure and has a hot side 19a upwards and a cold side 19b downwards. Inside the regenerator, there is a high temperature gradient between the hot side and the cold side, the hot side having a temperature close to the temperature of the burner cap, namely 700 ° C., the cold side having a temperature of temperature close to the temperature of the heating circuit, namely a temperature between 30 ° C and 70 ° C depending on the entity (s) present (s) on the heating circuit.
An annular circulation gap 24 arranged against the inner surface of the hot casing 96 connects the opening 83 of the first chamber to the hot side 19a of the regenerator.
Channels 25 in the cylinder head 95 connect the openings 84 of the second chamber to the cold side 19b of the regenerator.
Thus, when the piston rises, the compressible gas is driven from the first chamber 81 by the circulation gap 24, the regenerator 19 and the channels 25 towards the second cold chamber 82. Conversely, when the piston goes down again. the compressible gas is removed from the second cold chamber 82 through the channels 25, the regenerator 19 and the circulation gap 24, towards the first chamber 81.
The operation of the compressor is ensured by the reciprocating movement of the piston 71 between the bottom dead point PMB and the high point PMH, as well as by the action of a suction valve 41 on the inlet, a check valve 42 discharge on the outlet. The various steps A, B, C, D described below are shown in FIGS. 6 and 7.
Step A.
The piston, initially at the top, moves downwards and the volume of the first chamber 81 increases while the volume of the second chamber 82 decreases. By the fact, the fluid is pushed through the regenerator 19 from bottom to top, and warms up in the process. The pressure Pw increases concomitantly.
Step B.
When the pressure Pw exceeds a certain value, the outlet valve 42 opens and the pressure Pw is established at the outlet pressure P2 of the compressed fluid and the fluid is expelled to the outlet (the inlet valve 41 remains well sure closed during this time). This continues until the bottom dead center of the piston.
Step C.
The piston now moves from bottom to top and the volume of the second chamber increases as the first volume of the chamber decreases. As a result, the fluid is pushed through the regenerator 19 from top to bottom, and cools as it passes. The pressure Pw decreases concomitantly. The outlet valve 42 closes at the beginning of rise.
Step D.
When the pressure Pw falls below a certain value, the inlet valve 41 opens and the pressure Pw is established at the pressure P1 of fluid inlet and the fluid is sucked by the inlet (the valve output 42 of course remains closed during this time). This continues to the top dead center of the piston. The inlet valve 41 will close at the beginning of the descent of the piston.
The movements of the rod 18 are controlled by a self-driving device 14 acting on one end of the rod. This self-driving device comprises an inertial flywheel 142, a rod 141 connected to said steering wheel by a pivot connection, for example a rolling bearing 143. The connecting rod 141 is connected to the rod by another pivot connection, for example a bearing rolling 144.
The auxiliary chamber 88 filled with the gaseous working fluid at a pressure Pa. When the device is in operation, the pressure Pa in the auxiliary chamber 88 converges towards an average pressure substantially equal to the half-sum of the minimum pressure P1 and the maximum pressure P2 . Indeed, due to the reduced functional clearance between the ring 118 and the rod 18, in dynamic mode, this very small leakage does not impair operation and remains negligible.
When the flywheel rotates by one revolution, the piston sweeps a volume corresponding to the distance between the neutral point and bottom dead point, multiplied by the diameter DI.
The thermodynamic cycle, as shown in FIG. 7, gives a positive work to the self-entrainment device.
However, on the one hand for the initial start-up and for rotational speed regulation needs, a motor 17 is provided coupled to the flywheel 142.
This motor can be housed advantageously in the auxiliary chamber 88 or outside with a magnetic coupling to the wall.
The motor 17 is controlled by a control unit, not shown in the figures; the engine control makes it possible to accelerate or slow down the speed of rotation of the flywheel, the heat flows exchanged being in almost proportional relation with the speed of rotation of the flywheel. With the motor 17, the control unit can adjust the rotation speed between typically 100 trs / m and 500 trs / m, preferably in the range [200 - 300 trs / m].
It is also noted that the motor 17 serves to start the self-drive device 14.
Note that the piston 71 is not a power receiver piston (unlike an internal combustion engine or a conventional Stirling engine) but simply a displacer piston; the power is supplied as an increase in working gas pressure.
It is noted that VI + V2 + Vcanal = Vtotal if we ignore variations in the volume of the rod 18, VI being the volume of the first chamber, V2 being the volume of the second chamber and Vcanal being the volume of the pipes 24,25 . Preferably it is arranged to have a dead volume of lower possible with small section pipes, for example we will obtain
V channel <10% of V1 + V2.
As illustrated in FIG. 2, the boiler may advantageously be hybridized, that is to say contain an auxiliary burner 20, distinct from the first burner 11 and an exchanger 21. This auxiliary burner 20 will be used mainly in the case of operation in very cold outdoor temperature, and to pass the peak requirements of the heating system (this accumulated with hot water when it is present, see below).
The auxiliary burner 20 of the booster exchanger is generally dimensioned for a heat output around 20 kW, typically for a single house, which is much greater than the thermal power required for the compressor compression function as seen above.
More specifically, the control unit measures the outside temperature, and various fluid temperatures of the circuits involved (30, 31, 32, 34), to determine the need to operate the makeup burner 20.
As already mentioned, the flue gas outlet circuit 32 of the first burner passes inside the exchanger 21, where it transfers its heat to the fluid of the main heating circuit 30.
Note that the fluid of the heating circuit 30 receives heat from the main exchanger 5,51, and from the cold part of the compressor (zone 91) and finally from the combustion gases burned in the exchanger 21. If the auxiliary burner 20 is in operation, there is more a supply of calories directly from the auxiliary burner 20.
FIG. 3 illustrates two additional characteristics that may be present in the boiler of the invention. On the one hand, two compression stages are installed, in other words two compression units U1, U2 in series, one U2 after the other U1, each having its own burner 11, 12.
The second stage U2 is similar or analogous in every respect to the first stage U1; it comprises a burner 12 at which the combustion of gas mixed with the intake air occurs, and a displacer piston 72 similar to that of the first stage and whose movement and speed of rotation are independent of the first. The sum of the power of the two burners 11,12 can be sized around 10kW.
In practice, the outlet of the non-return valve 42 of the first stage is injected into the non-return valve 43 of the inlet of the second stage. In an integrated version or the cold parts are pooled, the valves 42,43 are merged. The output of the second stage U2, that is to say the valve 44 forms the compressor outlet 1. On the other hand, it is possible to provide an air intake preheating exchanger, marked 9, by which it is possible to take advantage of the calories present in the output of the gases leaving the burners 11, 12 to preheat the fresh air admitted 35 to the flame of these burners. The preheating exchanger 9 is here an air / air exchanger, known per se, used at cross flow in the example shown. The air entering the injector 11a of the burner 11 is thus at a temperature of between 100 ° C. and 300 ° C.
FIG. 4 illustrates on the one hand a main heat exchanger 5 formed by two series heat exchangers (a characteristic which will be detailed below) and another complementary characteristic, namely the supply of domestic hot water (abbreviated as 'DHW'). . There is provided a reserve tank 16 of domestic hot water as known per se, therefore not described in detail here. The water of this reserve tank is heated by a circulation of the fluid 36 during its passage through an exchanger ECS 15.
In this heat exchanger ECS circulates a branch branch 33 of the heating circuit 30. This bypass branch takes heat from a main heat exchanger high temperature (HT) marked 50 and transmits them to the domestic hot water in the exchanger ECS 15 .
The flow of fluid flowing in the branch branch 33 can be controlled by a control valve 78 known per se. This flow rate is determined in proportion to the needs of the regulation system of the domestic hot water storage tank. The main heat exchanger 5 here comprises two heat exchangers arranged in series on the CO 2 circuit 31: the 'high' heat exchanger 50 in which the bypass 33 configured for heating the domestic hot water circulates, and the 'low' heat exchanger temperature 51 which forms the main coupling of the CO 2 circuit 31 with the heating circuit 30. It is noted that it is also possible to have the combination of the two exchangers (high and low) even without domestic hot water circuit, for example if has 2 heating circuits receivers, one at low temperature and high temperature.
Typically, the average temperature of the compressible fluid in the high temperature exchanger 50 will be much greater than 100 ° C., whereas the average temperature of the compressible fluid in the low temperature exchanger 51 will be substantially lower than the outlet temperature of the high temperature exchanger, most often less than 150 ° or preferably less than 100 °.
FIG. 5 illustrates a complementary characteristic, namely a configuration with three compression stages, in other words three compression units U1, U2, U3.
It is expected to have a burner 11 on the first stage and a burner 12 on the second stage and a third burner 13 on the third stage U3. Each stage is similar to what is written about FIG. 6. The sum of the power of the three burners 11, 12, 13 can be sized around 13kW or even 15kW.
Advantageously, the stages operate independently, the speed of rotation may be different from one stage to another; The second and third stages respectively have pistons rated 72, 73.
Note that the heating circuit cools the three cold zones of the compressors, through the successive channels 93, 92 and 91.
The output of the first stage, that is to say the valve 42 is connected to the inlet of the second stage that is to say the valve 43, the output of the second stage that is to say the valve 44 is connected to the inlet of the third stage, that is to say the valve 45. The output of the valve 46 forms the general output of the compressor 1. The pressure staging can be typically the following, the inlet pressure of the U1 first stage is of the order of 30 bar, the discharge pressure of the first stage (second stage admission) is of the order of 45 bars; the discharge pressure of the second stage U2 (third stage admission) is of the order of 60 to 65 bars; the output of the third stage U3 may be of the order of 90 bars.
It can be expected that the three cold zones of the three stages U1 U2 U3 form a single piece called cold cylinder head as that shown in dotted lines 95 '(Figure 5).
Another optional feature of the boiler is illustrated in Figure 5; a so-called defrosting exchange 75 makes it possible to directly couple the brine circuit 34 with the heating circuit 30, without involving the circuit of the compressible gas 31.
An auxiliary circuit 76 can be activated by a valve 74 (manual or controlled) which activates this defrost exchanger.
As its name suggests, this defrost exchanger 75 is used to defrost the outdoor unit 4 by transferring calories from the heating circuit.
It should be noted that this exchanger can also be used in certain cases for so-called passive cooling, according to the same principle of transferring calories from the heating circuit to the external exchanger. In general, it is noted that the fuel used in the burner may be natural gas, or bio gas of plant or animal origin, or hydrocarbon compounds light industrial petroleum process waste.
As illustrated in Figure 9, the thermal compressor 1 described above can be used in the context of the diagrams of Figures 1 to 5, of course in a heating mode, but also with its reversibility in a so called air conditioning.
In this case, in this air-conditioning mode, heat will be taken from the heating circuit 30 (for example at a heated floor) and the calories taken will be directed towards the domestic hot water circuit 15, 16, or to the outdoor unit 4.
This result can be obtained by reversing the role of the exchangers 5 ', 6' of evaporation and condensation on the loop of the compressible gas 31.
For the sake of clarity, the four-way valve 77 which makes it possible to reverse the flow direction of the fluid has not been shown in FIGS. 1 to 5, but the principle is shown in FIG. 9 where the four-way valve 77 lanes has a so-called normal heating mode position and a special (inverted) so-called cooling mode position.
When the four-way valve 77 is in the normal position, the heat exchanger marked 6 'operates in condenser mode and the heat exchanger marked 5' operates in evaporator mode.
Conversely when the valve 77 is in the inverted position it is the exchanger 5 'which operates in condenser mode and it is the exchanger 6' which operates in evaporator mode.
In the boiler system, for reasons of clarity, some components have not been shown although they may also be present. These include: - expansion vessels on water circuits 34 30 - filling and purging valves of the heating circuit - filling and purging valves of the C02 circuit - various pressure gauges and sensors temperature required for control of the system by the control unit Summary of the circuits 30: heating circuit 31: compressible fluid C02 32: combustion fumes
33: bypass for DHW 34: brine (exchange with outside) 35: heated intake air
36: DHW specific circuit 76: bypass for defrost

权利要求:
Claims (16)
[1" id="c-fr-0001]
A thermodynamic boiler for exchanging calories with at least one heating circuit (30), the boiler comprising a thermal compressor (1), the thermal compressor acting on a compressible fluid and comprising at least one compression stage with a piston (71). ) with a reciprocating motion separating a first chamber (81) and a second chamber (82), and a first hot source fuel burner (11) coupled to the first chamber, and using the heating circuit as a cold source coupled to the second chamber (82) chamber, the thermal compressor forming the compression function of a reversible heat pump type loop (31,34).
[2" id="c-fr-0002]
2. A thermodynamic boiler according to claim 1, wherein the thermodynamic boiler provides calories to the heating circuit, the reversible heat pump type loop takes calories in an outdoor unit (4) (winter mode).
[3" id="c-fr-0003]
3. The thermodynamic boiler according to claim 2, further comprising a booster device (2), the booster device comprising an auxiliary burner (20), distinct from the first burner and a booster exchanger (21) arranged on the heating circuit (30).
[4" id="c-fr-0004]
4. thermodynamic boiler according to one of claims 1 to 3, wherein the compressible fluid is R744.
[5" id="c-fr-0005]
5. thermodynamic boiler according to one of claims 1 to 4, wherein there is provided a modulation unit and a motor (17) for controlling, namely increase and / or decrease the speed of rotation of the compressor.
[6" id="c-fr-0006]
6. A thermodynamic boiler according to one of claims 1 to 5, wherein the heat pump-type loop comprises two circuits arranged in cascade, namely a compressible qaz working circuit (31, 1, 5, 7,6). and a brine circuit (34, 4.6).
[7" id="c-fr-0007]
7. thermodynamic boiler according to one of claims 1 to 6, wherein the compressor comprises at least two compression stages in series, namely a second compression stage (U2).
[8" id="c-fr-0008]
8. thermodynamic boiler according to claim 7, with three stages (U1, U2, U3).
[9" id="c-fr-0009]
9. thermodynamic boiler according to one of claims 7 or 8, wherein the stages are independent.
[10" id="c-fr-0010]
10. thermodynamic boiler according to one of claims 1 to 9, comprising an air preheater (9) at the inlet to at least the first burner.
[11" id="c-fr-0011]
11. thermodynamic boiler according to one of claims 1 to 10, comprising a main heat exchanger (5) forming the essential thermal interface between the compressible fluid circuit (31) and the heating circuit (30), and the compressor is cooled by the return of the heating circuit which passes first in at least the main heat exchanger (5), then in the cold section of the thermal compressor.
[12" id="c-fr-0012]
12. A thermodynamic boiler according to one of claims 1 to 11, wherein the return of the heating circuit passes, after cooling the compressor, in the exchanger booster (21).
[13" id="c-fr-0013]
13. A thermodynamic boiler according to claim 11, wherein the main heat exchanger (5) comprises a high temperature exchanger (50) and a low temperature exchanger (51).
[14" id="c-fr-0014]
14. A thermodynamic boiler according to one of claims 1 to 13, comprising a hot water circuit (15,16).
[15" id="c-fr-0015]
15. A thermodynamic boiler according to claim 13 and claim 14, wherein the domestic hot water (33) is heated by means of the high temperature exchanger (50) which is arranged on the compressible fluid circuit directly at the outlet of the thermal compressor. (1).
[16" id="c-fr-0016]
16. The thermodynamic boiler according to claim 14, in which the thermodynamic boiler takes heat from the heating circuit (30) and delivers these calories either in the domestic hot water circuit ECS or in the outdoor unit (4), for provide an air conditioning function.

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同族专利:

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公开号 | 公开日

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CN108351121B|2020-12-25|

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FR3042857B1|2019-06-28|

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JP2018532941A|2018-11-08|

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US10539124B2|2020-01-21|

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RU2018118659A3|2020-02-12|

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RU2731140C2|2020-08-31|

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CN108351121A|2018-07-31|

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CA3000787A1|2017-04-27|

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RU2018118659A|2019-11-25|

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WO2017068066A1|2017-04-27|

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EP3365613A1|2018-08-29|

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US20190055932A1|2019-02-21|

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法律状态:
2016-09-30| PLFP| Fee payment|Year of fee payment: 2 |

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2017-04-28| PLSC| Publication of the preliminary search report|Effective date: 20170428 |

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2017-08-11| PLFP| Fee payment|Year of fee payment: 3 |

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2018-01-19| CA| Change of address|Effective date: 20171218 |

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2018-08-27| PLFP| Fee payment|Year of fee payment: 4 |

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2019-08-27| PLFP| Fee payment|Year of fee payment: 5 |

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2020-08-21| PLFP| Fee payment|Year of fee payment: 6 |

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2021-10-21| PLFP| Fee payment|Year of fee payment: 7 |

优先权:

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申请号 | 申请日 | 专利标题

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FR1560169|2015-10-23|

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FR1560169A|FR3042857B1|2015-10-23|2015-10-23|THERMODYNAMIC BOILER WITH THERMAL COMPRESSOR|FR1560169A| FR3042857B1|2015-10-23|2015-10-23|THERMODYNAMIC BOILER WITH THERMAL COMPRESSOR|

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JP2018520604A| JP2018532941A|2015-10-23|2016-10-20|Thermodynamic boiler with thermal compressor|

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RU2018118659A| RU2731140C2|2015-10-23|2016-10-20|Thermodynamic boiler with heat compressor|

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EP16787389.2A| EP3365613A1|2015-10-23|2016-10-20|Thermodynamic boiler with thermal compressor|

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CA3000787A| CA3000787A1|2015-10-23|2016-10-20|Thermodynamic boiler with thermal compressor|

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US15/770,482| US10539124B2|2015-10-23|2016-10-20|Thermodynamic boiler with thermal compressor|

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PCT/EP2016/075271| WO2017068066A1|2015-10-23|2016-10-20|Thermodynamic boiler with thermal compressor|

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CN201680060517.7A| CN108351121B|2015-10-23|2016-10-20|Thermodynamic boiler with thermocompressor|