Thermal machine with compressor supplied by a manometric column

Abstract

The invention relates to a thermal machine (200, 210) comprising a closed circuit in which a refrigerant circulates, including a compressor (201, 211) adapted to compress the refrigerant, a condenser (202, 212) adapted to condense the refrigerant, an expansion valve (203, 213) adapted to expand the refrigerant, and an evaporator (204, 214) adapted to evaporate the refrigerant, wherein the compressor (201, 211) comprises a discharge pump (1) of the type with a drive chamber (2) and a piston motor (13) supplied by a pressure column and with at least one multiplying chamber (5, 6) and as many multiplying pistons (52, 62), adapted to compress the refrigerant. Abbreviated figure: Figure 2

Description

Title of the invention: Thermal machine with compressor powered by a manometric column Technical field

[0001] The invention relates to a thermal machine, intended to produce cold or heat. Prior art

[0002] It is known to produce a thermal machine or refrigeration unit. Such a thermal machine comprises a closed circuit in which a refrigerant circulates. Said circuit comprises, in sequence in the direction of circulation of the refrigerant, a compressor, a first exchanger or condenser, an expansion valve and a second exchanger or evaporator. The compressor is capable of sucking in the refrigerant at low pressure and low temperature, compressing it to produce refrigerant at high pressure and high temperature. The refrigerant is then transmitted to the condenser which cools the refrigerant by providing heat to the outside. The refrigerant is then transmitted to an expansion valve which expands the refrigerant by reducing its pressure. The refrigerant is then transmitted to the evaporator which heats the refrigerant by cooling the outside. The refrigerant is then transmitted again to the compressor.

[0003] Such a thermal machine is thus capable of producing cold, at the level of the evaporator and / or heat, at the level of the condenser.

[0004] If the condenser, expansion valve and evaporator are passive elements, energy must be supplied for the compressor to operate. Also, depending on the energy used, the cost of producing cold can be measured by the energy expended to operate the compressor. Thus, in a refrigerator, electrical energy is consumed to operate the compressor and produce cold.

[0005] Also known from the applicants' document WO 2020152402 is a discharge pump capable of being supplied by a manometric column. Such a pump is conventionally used for pumping or lifting water, for example for irrigation, but also for consumption. The operating fluid is water from the manometric column. The discharge fluid is irrigation or consumption water. Such a pump is advantageous in that it operates using gravity energy from a manometric column, which is easily renewable and therefore substantially free. Summary of the invention

[0006] Also, the ingenuity of the present invention consists in using said pump, powered by a pressure column, to form the compressor and compress the refrigerant of a thermal machine, in order to produce cold and / or heat from renewable energy, abundantly available and therefore substantially free.

[0007] For this purpose, the invention relates to a thermal machine comprising a closed circuit in which a refrigerant fluid circulates, comprising, in sequence in the direction of circulation of the refrigerant fluid, a compressor capable of sucking in the refrigerant fluid at low pressure and low temperature, of compressing it to produce refrigerant fluid at high pressure and high temperature, a first heat exchanger between refrigerant fluid and first medium or condenser capable of condensing the refrigerant fluid by cooling it by supplying heat to the first medium, an expansion valve capable of expanding the refrigerant fluid by reducing its pressure and a second heat exchanger between refrigerant fluid and second medium or evaporator capable of evaporating the refrigerant fluid by heating it by absorbing heat from the medium, and transmitting it again to the compressor,where the compressor comprises a delivery pump of the type with a driving chamber and a driving piston supplied by a pressure column and at least one multiplier chamber and as many multiplier pistons, capable of compressing the refrigerant fluid.

[0008] Particular characteristics or embodiments, usable alone or in combination, are: - the thermal machine also comprises a pneumatic motor supplied, via an inlet pipe, by the refrigerant coming from the compressor and discharging the refrigerant via an outlet pipe, the pneumatic motor comprising a throttle at its exhaust forming the expansion valve, the outlet pipe surrounding the inlet pipe so as to form a first exchanger or condenser, the outlet pipe serving the second exchanger or evaporator, - the outlet pipe is insulated, - the thermal machine also includes an electric generator driven by the pneumatic motor, - the refrigerant is dry air without carbon dioxide, - the closed refrigerant circuit is pre-compressed to a high pressure, preferably equal to 40 bars, - the second medium, cooled by the second exchanger or evaporator, circulates in a closed circuit, - the delivery pump comprises a driving enclosure inside which a driving piston slides along an axis alternately between a first end position and a second end position under the action of a pressurized operating fluid, the driving piston separating the driving enclosure into a first driving chamber and a second driving chamber, a first multiplier chamber comprising an inlet and an outlet and a second multiplier chamber comprising an inlet and an outlet, for respectively receiving and discharging a discharge fluid, a first multiplier piston, connected to the driving piston, sliding in the first multiplier chamber to ensure the compression of the discharge fluid in the first multiplier chamber, a second multiplier piston, connected to the driving piston, sliding in the second multiplier chamber to ensure the compression of the discharge fluid in the first multiplier chamber, an alternating fluid distribution device for alternating the direction of circulation of the operating fluid in the driving chamber and the direction of sliding of the driving piston,the first driving chamber comprising a first inlet for receiving the operating fluid during a first dispensing cycle and the second driving chamber comprising a first outlet for discharging the operating fluid during a first dispensing cycle, the second driving chamber comprising a second inlet for receiving the operating fluid during a second dispensing cycle and the first driving chamber comprising a second outlet for discharging the operating fluid during a second dispensing cycle, the alternating dispensing device comprising at least one closure device comprising four movable members for closing the first and second inlets and the first and second outlets and at least one trigger configured to actuate said closure members between two positions, respectively closure and opening,the alternating distribution device being actuable between: - a first arrangement associated with the first distribution cycle in which the engine piston moves to its second position, two of the moving members respectively close the second inlet and the second outlet, and the other two moving members respectively open the first inlet and the first outlet, - a second arrangement associated with the second distribution cycle in which the engine piston moves to its first position, two of the moving members respectively close the first inlet and the first outlet, and the other two moving members respectively open the second inlet and the second outlet, , - the trigger is configured to be actuated by the engine piston, at least when the latter is in one of its end positions, - the manometric column comprises a pipe bypassing a river, between an upstream intake and a downstream return, the discharge pump being connected in series, the upstream of the pipe being connected to the first and second inlets and the downstream of the pipe being connected to the first and second outlets, via a first pressure regulator, - the manometric column includes a pipe bypassing a river, between an upstream intake and a downstream return, the discharge pump being connected in bypass, an upstream tap connecting the pipeline to the first and second inlets and a downstream tap connecting the pipeline to the first and second outlets, the pipeline further comprising a second pressure regulator between the upstream tap and the downstream tap, - the pipeline also includes a third pressure regulator, located downstream of the downstream tapping. Brief description of the drawings

[0009] The invention will be better understood on reading the following description, given solely by way of example, and with reference to the appended figures in which:

[0010] [Fig-1] shows a schematic diagram of a simple expansion heat engine,

[0011] [Fig.2] shows a schematic diagram of a Joule-Thomson expansion machine,

[0012] [Fig.3] shows, in sectional view, a delivery pump capable of being supplied by a manometric column,

[0013] [Fig.4] shows a first installation diagram of such a thermal machine,

[0014] [Fig.5] shows a second installation diagram of such a thermal machine. Description of the embodiments

[0015] With reference to [Fig. 1], a thermal machine 200 comprises a closed circuit in which a refrigerant circulates. This circuit comprises, in sequence in the direction of circulation of the refrigerant, a compressor 201, a condenser 202, an expansion valve 203 and an evaporator 204.

[0016] The compressor 201 is capable of sucking in the low-pressure, low-temperature refrigerant from the evaporator 204 and compressing it to produce high-pressure, high-temperature refrigerant. Due to its circulation, induced by the compressor 201, the refrigerant then reaches the condenser 202.

[0017] The condenser 202 is a first heat exchanger between the refrigerant and a first medium. The first medium may be another separate circuit or simply an external environment surrounding the condenser 202, such as ambient air. The condenser 202 is capable of condensing the refrigerant by cooling it. This is done by taking the cold from the first medium, or by supplying heat to the first medium. The refrigerant continues its circulation to reach the expansion valve 203.

[0018] The expansion valve 203 is typically a calibrated hole allowing the refrigerant to pass through. The expansion valve 203 is capable of expanding the refrigerant by reducing its pressure. The expansion thus achieved is the main source of cold production. The refrigerant continues its circulation to reach the evaporator 204.

[0019] The evaporator 204 is a second heat exchanger between the refrigerant and a second medium. The second medium may be another separate circuit or simply an external medium surrounding the evaporator 204, such as ambient air. The evaporator 204 is capable of evaporating the refrigerant by heating it by absorbing heat from the second medium.

[0020] The refrigerant fluid continues its course and is transmitted again to the compressor 201.

[0021] Such a thermal machine 200, operating cyclically, makes it possible to produce heat at the condenser 202 and cold at the evaporator 204.

[0022] According to a characteristic of the invention, the compressor 201 is produced by a delivery pump 1 of the type with a driving chamber 2 and a driving piston 13 supplied by a manometric column and with two multiplying chambers 5, 6 and two multiplying pistons 52, 62, capable of compressing the refrigerant fluid.

[0023] Such a pump 1, invented by the applicants, is described in detail in document WO 2020152402, to which reference will be made with profit.

[0024] The heat engine 200 of [Fig. 1] is a simple or direct expansion machine. It is also possible to produce an indirect or Joule Thomson expansion machine. As illustrated in [Fig. 2], such a machine 210 has all the characteristics of a direct expansion heat engine 200. It comprises a closed circuit in which a refrigerant circulates. This circuit comprises, in sequence in the direction of circulation of the refrigerant, a compressor 211, a condenser 212, an expansion valve 213 and an evaporator 214. It also comprises a pneumatic motor 215. This pneumatic motor 215 is supplied via an inlet pipe 216 by the refrigerant coming from the compressor 211. It discharges the refrigerant via an outlet pipe 217. The pneumatic motor 215 comprises a throttle at its exhaust, i.e. at its outlet. This throttle forms the expansion valve 213. The expansion cools the refrigerant.The outlet pipe 217 surrounds the inlet pipe 216 and has with the latter a large common heat exchange surface, so as to form a first exchanger between the inlet pipe 216 and the outlet pipe 217. This exchanger acts as a condenser 212. The outlet pipe 217 joins a second exchanger which acts as an evaporator 214. Also, the heat engine 210 has all the characteristics of a direct expansion heat engine 200.

[0025] According to another characteristic, in the thermal machine 210 the outlet pipe 217, at least in the part where it envelops the inlet pipe 216, is heat-insulated, in order to limit the thermal exchanges with the ambient environment and favor the exchanges between the inlet pipe 216 and the outlet pipe 217.

[0026] In the case of a Joule Thomson type expansion, it is advantageous, for the efficiency of the thermal machine, that the pneumatic motor 215 is braked by a resistive torque. Also, according to another characteristic, the thermal machine 210 also advantageously comprises an electric generator 218 driven by the pneumatic motor 215. This has a double advantage of improving the thermal operation of the thermal machine 210 while allowing cogeneration of electricity.

[0027] This electricity can advantageously be used to ensure the diffusion of the cold produced, by circulation in the secondary cooling circuit 219.

[0028] According to another characteristic, the thermal machine 210 operates with air as refrigerant. This air is advantageously dry so as not to risk producing ice. This air is also free of any carbon dioxide, so as not to risk producing dry ice. Such a refrigerant is particularly advantageous in that it is environmentally friendly and does not cause any danger in the event of a leak.

[0029] It is known that the same amount of energy is required to compress a gas from 1 to 10 bars or from 10 to 100 bars. However, the production of cold resulting from the expansion in the second case produces 10 times more cold than in the first case. Also, it is advantageous for the closed circuit containing the discharge fluid, here the refrigerant, to be pre-compressed to a high pressure, preferably equal to 40 bars.

[0030] It has been seen that the cold is available at the evaporator 214. This evaporator 214 is a heat exchanger between the refrigerant and a second medium. This second medium can be directly the outside air around the evaporator 214. According to another characteristic, the second medium, cooled by the second exchanger or evaporator 214, circulates preferentially in a secondary closed cooling circuit 219. Such a characteristic makes it possible to diffuse, by means of a circulation of the second medium, the cold produced by the thermal machine 210 in more distant places to cool them. In this case the second medium is advantageously a heat transfer liquid.

[0031] Whether it is a simple expansion thermal machine 200 or a Joule Thomson expansion thermal machine 210, the compressor 201, 211 is a discharge pump 1 capable of operating with the energy supplied by a manometric column.

[0032] As illustrated in [Fig. 3], such a delivery pump 1 comprises a driving enclosure 2 inside which a driving piston 13 slides along an axis X alternately between a first end position PI and a second end position P2. This alternating sliding is produced by the action of a pressurized operating fluid. The driving piston 13 separates the driving enclosure 2 into a first driving chamber 3 and a second driving chamber 4. The pump 1 further comprises a first multiplier chamber 5 comprising an inlet 50 and an outlet 51. Optionally, it may further comprise a second multiplier chamber 6 comprising an inlet 60 and an outlet 61. The inlets 50, 60, allow a discharge fluid to be received. The outlets 51, 61 allow the discharge fluid to be evacuated.

[0033] In the heat engine, the two inlets 50, 60 are advantageously connected to the outlet of the closed circuit coming from the evaporator 204, 214. This connection is made, as illustrated in [Fig. 2], advantageously via non-return valves, arranged in the direction of circulation of the refrigerant. Similarly, the two outlets 51, 61 are advantageously connected to the inlet of the closed circuit joining the condenser 202, 212. This connection is made, as illustrated in [Fig. 2], advantageously via non-return valves, arranged in the direction of circulation of the refrigerant.

[0034] A first multiplier piston 52, connected to the driving piston 13, slides in the first multiplier chamber 5 to ensure the compression of the delivery fluid in the first multiplier chamber 5. Similarly, a second multiplier piston 62, connected to the driving piston 13, slides in the second multiplier chamber 6 to ensure the compression of the delivery fluid in the first multiplier chamber 5.

[0035] A first operating circuit is thus distinguished, comprising a driving chamber 2 in which an operating fluid circulates, here typically water from a pressure column. This alternately mobilizes the driving piston 13. By virtue of its mechanical connection with the multiplier pistons 52, 53, the movement of the driving piston 13 is transmitted to the multiplier pistons 52, 53. A second delivery circuit, fluidically isolated from the operating circuit, comprises the multiplier chambers 5, 6, in which a delivery fluid circulates, here the refrigerant. The movement of the multiplier pistons 52, 53 makes it possible to compress the refrigerant.

[0036] The pump 1 transforms pressure energy from the pressure column into an alternating translation of the driving piston 13. This alternation is obtained by means of an alternating fluid distribution device to alternate the direction of circulation of the operating fluid in the driving enclosure 2 and to alternate the direction of sliding of the driving piston 13. This is carried out according to a periodic succession comprising alternately a first distribution cycle and a second distribution cycle.

[0037] The first driving chamber 3 comprises a first inlet E1 for receiving the operating fluid during a first distribution cycle and the second driving chamber 4 comprises a first outlet S1 for discharging the operating fluid during the first distribution cycle. Thus, during a first distribution cycle distribution, the engine piston 13 moves in a first direction.

[0038] The second driving chamber 4 comprises a second inlet E2 for receiving the operating fluid during a second distribution cycle and the first driving chamber 3 comprises a second outlet S2 for discharging the operating fluid during a second distribution cycle. Thus, during a second distribution cycle, the driving piston 13 moves in a second direction, opposite to the first direction.

[0039] To obtain this alternation, the distribution device alternates between a distribution of operating fluid via the first inlet E1 with recovery via the first outlet S1 and a distribution of operating fluid via the second inlet E2 with recovery via the second outlet S2. For this, the alternating distribution device comprises at least one closure device 7 comprising four movable closure members 70-73 of the first and second inlets E1, E2 and of the first and second outlets S1, S2 and at least one trigger 8, 9 configured to actuate said closure members 70-73 between two positions respectively of closure and opening.

[0040] The alternating distribution device is operable between a first arrangement, associated with the first distribution cycle, in which the engine piston 13 moves towards its second position P2 and a second arrangement, associated with the second distribution cycle, in which the engine piston 13 moves towards its first position PL

[0041] In the first arrangement, two of the movable members 71, 72 respectively close the second inlet E2 and the second outlet S2, and the other two movable members 70, 73 respectively open the first inlet E1 and the first outlet SL

[0042] In the second arrangement, two of the movable members 70, 73 respectively close the first inlet E1 and the first outlet S1, and the other two movable members 71, 72 respectively open the second inlet E2 and the second outlet S2.

[0043] Said at least one trigger 8, 9 actuates said closure members 70-73 and makes it possible to switch alternately from the first arrangement to the second arrangement.

[0044] Furthermore, according to another characteristic, said at least one trigger 8, 9 is configured to be actuated by the driving piston 13, when the latter moves towards one of its end positions PI, P2 and at least when the latter reaches one of its end positions PI, P2. This makes it possible to carry out the alternation: the driving piston 13, when it reaches the end of its travel in the end position PI or P2, actuates at least one trigger 8, 9 which changes the arrangement. The change in arrangement causes a change in the sliding direction of the driving piston 13, which will in turn actuate at least one trigger 8, 9, and so on.

[0045] It has been seen that the thermal machine 200, 210 draws its energy from a pressure column metric. Such a manometric column continuously supplies an operating fluid, typically water, under a pressure that allows the pump 1 to operate.

[0046] Such a manometric column is conventionally produced by a waterfall, the difference in water height continuously providing a pressure difference.

[0047] According to a first characteristic, illustrated in [Fig. 4], a manometric column comprises a pipe 220 bypassing a river, between an upstream intake and a downstream return. The discharge pump 1 is connected in series, the upstream of the pipe 220 being connected to the first and second inlets E1, E2 and the downstream of the pipe 220 being connected to the first and second outlets S1, S2, via a first pressure regulator 223. This assembly is more particularly suitable for a public network pipe of small or medium section.

[0048] According to another characteristic, illustrated in [Fig.5], the manometric column comprises a pipe 220 bypassing a river, between an upstream intake and a downstream return. The discharge pump 1 is connected in bypass, an upstream tapping 221 connecting the pipe 220 to the first and second inlets E1, E2 and a downstream tapping 222 connecting the pipe 220 to the first and second outlets S1, S2, the pipe 220 also comprising a second pressure regulator 224 between the upstream tapping 221 and the downstream tapping 222. This assembly is more particularly suited to a public network pipe of large section.

[0049] According to another characteristic, the pipe 220 also comprises a third pressure regulator 225, arranged downstream of the downstream tapping 222.

[0050] In the above, a pressure regulator 223, 224, 225 means any device capable of reducing the pressure in a controlled manner, such as a pressure regulator, a pressure reducer or any other equivalent device. Its function is to maintain a pressure difference between its upstream and downstream, so as not to risk stopping the pump 1 in the event of equilibrium of the upstream and downstream pressures.

[0051] Such a manometric column is typically created by a relief of the river present between the upstream capture and the downstream restitution. It is easy to set up in a country with such a relief. The energy, provided by gravity, is here infinitely renewable and thus appears to be almost free. The invention is thus particularly advantageous in that it allows the production of cold, and / or heat, as well as possibly a cogeneration of electricity from available and free energy. In addition, all the water captured upstream is entirely returned downstream. The thermal machine does not consume any water. It only takes its mechanical energy.

[0052] The invention has been illustrated and described in detail in the drawings and the preceding description. This should be considered as illustrative and given by way of example. and not as limiting the invention to this description alone. Numerous alternative embodiments are possible.

Claims

Claims

1. A heat engine (200, 210) comprising a closed circuit in which a refrigerant circulates, comprising, in sequence in the direction of circulation of the refrigerant, a compressor (201, 211) capable of sucking in the refrigerant at low pressure and low temperature, compressing it to produce refrigerant at high pressure and high temperature, a first heat exchanger between refrigerant and first medium or condenser (202, 212) capable of condensing the refrigerant by cooling it by supplying heat to the first medium, an expansion valve (203, 213) capable of expanding the refrigerant by reducing its pressure, and a second heat exchanger between refrigerant and second medium or evaporator (204, 214) capable of evaporating the refrigerant by heating it by absorbing heat from the medium, and transmitting it again to the compressor (201, 211), characterized in that the compressor (201,211) comprises a delivery pump (1) of the type with a driving chamber (2) and a driving piston (13) supplied by a pressure column and with at least one multiplier chamber (5, 6) and as many multiplier pistons (52, 62), capable of compressing the refrigerant fluid.

2. Thermal machine (200, 210) according to the preceding claim, where the closed circuit of refrigerant fluid is pre-compressed to a high pressure, preferably equal to 40 bars.

3. Thermal machine (200, 210) according to claims 1 or 2 where the second medium, cooled by the second exchanger or evaporator (204, 214), circulates in a closed circuit (219).

4. A heat engine (200, 210) according to any one of the preceding claims, wherein the delivery pump (1) comprises a drive chamber (2) inside which a drive piston (13) slides along an axis (X) alternately between a first end position (PI) and a second end position (P2) under the action of a pressurized operating fluid, the drive piston (13) separating the drive chamber (2) into a first drive chamber (3) and a second drive chamber (4), a first multiplier chamber (5) comprising an inlet (50) and an outlet (51) and a second multiplier chamber (6) comprising an inlet (60) and an outlet (61), for respectively receiving and discharging a delivery fluid, a first multiplier piston (52), connected to the drive piston

5. (13), sliding in the first multiplier chamber (5) to ensure the compression of the delivery fluid in the first multiplier chamber (5), a second multiplier piston (62), connected to the driving piston (13), sliding in the second multiplier chamber (6) to ensure the compression of the delivery fluid in the first multiplier chamber (5), an alternating fluid distribution device for alternating the direction of circulation of the operating fluid in the driving enclosure (2) and the sliding direction of the driving piston (13), the first driving chamber (3) comprising a first inlet (El) for receiving the operating fluid during a first distribution cycle and the second driving chamber (4) comprising a first outlet (SI) for evacuating the operating fluid during a first distribution cycle,the second driving chamber (4) comprising a second inlet (E2) for receiving the operating fluid during a second distribution cycle and the first driving chamber (3) comprising a second outlet (S2) for discharging the operating fluid during a second distribution cycle, the alternating distribution device comprising at least one closure device (7) comprising four movable closure members (70-73) for closing the first and second inlets (E1, E2) and the first and second outlets (S1, S2) and at least one trigger (8, 9) configured to actuate said closure members (70-73) between two positions respectively of closure and opening, the alternating distribution device being actuable between: - a first arrangement associated with the first distribution cycle in which the driving piston (13) moves towards its second position (P2), two of the movable members (71,72) respectively close the second inlet (E2) and the second outlet (S2), and the other two movable members (70, 73) respectively open the first inlet (El) and the first outlet (SI), - a second arrangement associated with the second distribution cycle in which the engine piston (13) moves to its first position (PI), two of the movable members (70, 73) respectively close the first inlet (El) and the first outlet (SI), and the other two movable members (71, 72) respectively open the second inlet (E2) and the second outlet (S2)., Thermal machine (200, 210) according to the preceding claim, where the trigger (8, 9) is configured to be actuated by the engine piston (13), at least when the latter is in one of its positions (PI, P2) end.

6. Thermal machine (200, 210) according to any one of claims 1 to 4, wherein the pressure column comprises a pipe (220) bypassing a river, between an upstream intake and a downstream return, the delivery pump (1) being connected in series, the upstream of the pipe (220) being connected to the first and second inlets (El, E2) and the downstream of the pipe (220) being connected to the first and second outlets (SI, S2), via a first pressure regulator (223).

7. Thermal machine (200, 210) according to any one of claims 1 to 4 where the manometric column comprises a pipe (220) bypassing a river, between an upstream intake and a downstream return, the delivery pump (1) being connected in bypass, an upstream tapping (221) connecting the pipe (220) to the first and second inlets (El, E2) and a downstream tapping (222) connecting the pipe (220) to the first and second outlets (S1, S2), the pipe (220) further comprising a second pressure regulator (224) between the upstream tapping (221) and the downstream tapping (222).

8. Thermal machine (200, 210) according to the preceding claim, where the pipe (220) also comprises a third pressure regulator (225), arranged downstream of the downstream tapping (222).

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