FR3002598A1 - System for pumping water in water distribution network, has pump sucking fluid to be pumped via sucking port and discharging sucked fluid via discharge port under action of flow of pressurized working fluid arriving via supply port - Google Patents

Abstract

The system (1) has a working fluid pressurizing device (3) including a pressurized thermal fluid inlet port (PV1) connected to an outlet (So1) of a heat exchanger (Eth) i.e. solar exchanger, a working fluid inlet port (P1), and a working fluid outlet port (P2). A pump (2) includes a supply port (Pp3), which is provided in working fluid connection to the working fluid outlet port. The pump sucks fluid to be pumped via a sucking port (Pp1) and discharges the sucked fluid via a discharge port (Pp2) under an action of a flow of the pressurized working fluid arriving via the supply port.

Description

The invention relates to the general field of systems for pumping a fluid to be pumped using energy in thermal form to operate the pumping system.

More particularly, the invention relates to a system for pumping a fluid to be pumped comprising: - a heat exchanger containing a thermal fluid and arranged to vaporize the thermal fluid under the action of a heat input to the exchanger and for delivering this vaporized thermal fluid via an outlet of the exchanger; - A pump with a suction port of the fluid to be pumped and a discharge port of said fluid to be pumped. The pump is arranged to operate with energy captured by the exchanger and it would be desirable to improve the operation of the system. OBJECT OF THE INVENTION An object of the present invention is to allow the heat exchanger to move away from the pump so that the heat exchanger can be positioned at a location suitable for thermal energy collection, and that the pump can be positioned at another location adapted to its function of pumping the fluid to be pumped. SUMMARY OF THE INVENTION To respond to this object, it is proposed according to the invention, a pumping system of a fluid to be pumped comprising: - a heat exchanger containing a thermal fluid arranged to vaporize the thermal fluid under the action of adding heat to the exchanger and delivering this vaporized thermal fluid via an outlet of the exchanger; - A pump with a suction port of the fluid to be pumped and a discharge port of said fluid to be pumped. This pumping system according to the invention is essentially characterized in that it further comprises: a device for pressurizing a working fluid provided with at least one inlet port for the thermal fluid under pressure connected to the outlet of the exchanger and the engine fluid inlet and outlet ports, said pressurizing device being adapted to use the pressure of the thermal fluid to generate a flow of motor fluid from the engine fluid inlet port to the engine fluid outlet port and to increase the fluid pressure between said inlet and outlet ports; the pump comprising a motor fluid pump supply port connected to the engine fluid outlet port, this pump, under the action of a flow of pressurized engine fluid arriving via its supply port, being adapted to aspirate the fluid to be pumped via its suction port and pump the fluid to pump and sucked through its discharge port. The system according to the invention thus makes it possible to transfer energy in the form of heat energy collected by means of the heat exchanger to a device for pressurizing a liquid driving fluid. This transfer is done by vaporization of a thermal fluid which is thus pressurized in the exchanger. It should be noted that in order to promote this pressurization and to reduce the pressure drops, it is ensured that the exchanger and the pipes connecting the exchanger to the ports of the pressurizing device have constant volumes.

The flow of thermal fluid in the form of pressurized steam feeds the device for pressurizing the working fluid, via the connection / conduit between the outlet of the exchanger and the inlet port of the thermal fluid under pressure. The thermal fluid stream vaporized under pressure allows the pressurizing device to operate so as to generate a flow of liquid engine fluid from the inlet port (suction) of the working fluid to the outlet port (delivery) of motor fluid. The pressurized liquid driving fluid is then simply transported to the pump for operation and pumps the fluid to be pumped. This transport is done via a pipe adapted to the transport of liquid under pressure. The advantage of this solution is to be able to use thermal energy to convert it into hydraulic energy transmitted to the pump to make it work. The hydraulic energy is first transported via the vaporized thermal fluid and under pressure to the pressurizing device. With this hydraulic energy, the pressurizing device generates a pressurized liquid engine fluid stream which is conveyed to the hydraulic type pump in order to operate it away from the heat exchanger.

The invention thus makes it possible to transport the steam thermal fluid only over a short distance between the heat exchanger and the pressurizing device and to transport liquid engine fluid over a longer distance between the pressurizing device and the pump. In doing so, and even if this pump is at a great distance from the heat exchanger receiving thermal energy, the invention makes it possible to reduce the energy loss in the form of heat dissipation or gaseous fluid flow.

The overall operation of the pumping system can thus be improved by optimizing the respective locations of the exchanger and the pump.

In a particular embodiment, the device for pressurizing the working fluid is arranged at a first distance from said heat exchanger and at a second distance from said pump, the second distance being at least ten times the first distance. As indicated above, the system according to the invention makes it possible to limit the loss of mechanical power by bringing the heat exchanger as close as possible to the pressurizing device, thereby limiting the pressure drop of the steam that could occur. produce if it condenses when transported to the pressurizing device. The mechanical power is thus transferred from the thermal fluid in the form of vapor to the liquid engine fluid by pressurizing it. The engine fluid thus pressurized is in turn used to transfer the mechanical power of the pressurizing device of the working fluid to the pump. There is indeed less energy loss to transport a liquid engine fluid over a long distance to supply the pump with hydraulic energy than if one tried to supply the pump directly with the thermal fluid in the form of steam. In a particular embodiment, the pumping system comprises a solar ray reflection device such as a mirror having a parabolic shape. The heat exchanger is then a solar heat exchanger placed at least in part at the focus of a solar ray reflection device. This embodiment is particularly advantageous since it makes it possible to pump a liquid using the pump using only a source of solar energy. It should be noted that in this mode the system may also comprise means for orienting the ray reflection device and / or the heat exchanger with respect to the sun so as to follow its movement and maximize the energy uptake. BRIEF DESCRIPTION OF THE DRAWINGS Other features and advantages of the invention will emerge clearly from the description which is given below, by way of indication and in no way limitative, with reference to the accompanying drawings, in which: FIGS. 1 and 2 show the device for pressurizing a liquid driving fluid at different instants of its cyclic and reciprocating operation; FIGS. 3 and 4 show the pump of the pumping system at different times of its cyclic and reciprocating operation; FIG. 5 presents an overview of the pumping system according to the invention, in which the heat exchanger, the device and the pump of FIGS. 1 to 4 are diagrammatically shown; FIG. 6 shows a detailed view of one of the control means making it possible to alternatively operate the pump from a simple inlet of liquid engine fluid under pressure. DETAILED DESCRIPTION OF THE INVENTION As indicated above, the invention relates to a pumping system 1 of a liquid fluid Fl to be pumped using for its operation a thermal energy input captured using a heat exchanger Eth. It is noted that the pumping system 1 presented uses solar energy, but its heat exchanger Eth could also be combined with any other source of thermal energy such as a geothermal source or a fuel boiler furnace. The pumping system 1 is shown as a whole in FIG. 5, where the heat exchanger Eth with a thermal fluid inlet Enl and a vaporised thermal fluid sol F0 is shown. This Eth exchanger is arranged to vaporize this thermal fluid FO under the action of a heat input and to deliver this vaporized thermal fluid via the outlet of the ground heat exchanger. This output Sol is connected to a port of arrival of thermal fluid under pressure PV1 of the device for pressurizing a working fluid 3. The output of the exchanger Sol is equipped with a check valve 6 having an elastic setting . This valve 6: - allows the passage of thermal fluid FO via the ground outlet of the exchanger to a port PV1 only when the pressure inside the exchanger Eth passes above a predetermined minimum pressure threshold (the tare value is used to set this predetermined pressure threshold); and prohibits the passage of thermal fluid from the fluid inlet port PV1 to the Eth exchanger via the outlet Sol of the exchanger Eth. In doing so, when the heat / heat energy supplied to the heat exchanger Eth decreases, it is certain to stop the steam outlet as soon as it passes below the minimum pressure threshold thus ensuring the maintenance of a minimum quantity of fluid. thermal vapor in the interior of the exchanger Eth. Thus, when the heat input to the heat exchanger Eth is again sufficient to increase the temperature in the heat exchanger Eth, the minimum amount of water maintained in the heat exchanger is available to reinitiate the steam production and to cause again a circulation of thermal fluid in the form of steam to the device 3 for pressurizing engine fluid. A solar ray reflection device 4 which is here a parabolic mirror is implanted so as to focus sunlight towards the heat exchanger which may be a tube. The device 3 for pressurizing a working fluid is provided with the inlet port of the thermal fluid under pressure PV1 connected to the outlet of the ground heat exchanger and the inlet and outlet ports of the fluid P1, P2. This pressurizing device 3 is adapted to use the pressure of the vaporized thermal fluid FO to generate a flow of liquid engine fluid from the engine fluid inlet port P1 to the engine fluid outlet port P2 and to increase the fluid pressure between these input and output ports P1, P2. The operation of this device 3 will be explained later with reference to FIGS. 1 and 2. The pump 2 is provided with a suction port for the fluid to be pumped Ppl, a delivery port Pp2 for said fluid to be pumped. , a pump power supply port Pp3 connected to the output port P2 of the engine fluid. This pump 2, under the action of the flow of pressurized engine fluid arriving via its supply port Pp3, draws the fluid to pump Fl via its suction port Ppl and pressurizes it under pressure via its delivery port Pp2.

This pump 2 has a cylindrical shape adapted to be inserted into a tube of an artesian bore 7 with a diameter of less than 200 millimeters. A pump piston / pump rod 2b linearly displaces cyclically within the pump 2 under the action of the liquid motor fluid stream. The displacement of this pump piston 2b is used to generate the flow of fluid to be pumped from the port Ppl to the port Pp2. Ideally and for reasons of space, the pump rod 2b slides along a sliding axis parallel to the axis of revolution of the cylindrical shape. A strainer 8 with an anti return function is connected outside the pump to said suction port Ppl to allow the passage of fluid to pump only the strainer to the suction port Ppl. The discharge port Pp2 is equipped with a discharge pipe 9 of the pumped fluid. This discharge port Pp2 of the pump 2 is connected, via the pipe 9, on the one hand to a distribution network Dist and on the other hand, via a check valve 18, to the fluid inlet port. motor P1 of the pressurizing device 3 so that a portion of the fluid pumped by the pump 2 also serve as the driving fluid used by the device 3 for pressurizing the working fluid. In the present case, the driving fluid and the pumped fluid F1 by the pump 2 are water. However, it could be envisaged that the driving fluid which is necessarily liquid is different from the fluid to be pumped Fl, which would reduce the risk of contamination of the driving fluid by elements present in the fluid to be pumped Fl. For this, it would be possible to envisage that the working fluid flows in a closed circuit between the pressurizing device 3 and the pump 2. In this case, the pump comprises a motor fluid return port distinct from the delivery port Pp2 of the fluid to be pumped and the connection between this motor fluid return port and the engine fluid inlet port Pl would be realized by a specific pipe distinct from the pipe 9. The output port Pp2 is equipped with a check valve 13 to prevent the passage of fluid to pump 2 through this port Pp2.

The detailed operation of this pump 2 will be explained later with reference to FIGS. 3, 4 and 6. In summary, the pressurizing device 3 visible in FIGS. 1 and 2 makes it possible to pressurize the working fluid by using the flow for this purpose. vaporized thermal fluid and under pressure generated by the exchanger Eth. DESCRIPTION OF THE PRESSURE DEVICE As seen in Figures 1 and 2, the device 3 comprises a body 3a and a piston rod 3b mounted in the body 3a to slide thereon along a sliding axis. This rod 3b defined with the body 3a: - first and second control chambers Cd1, Cd2 of the sliding of the rod between first and second extreme positions of sliding rod Xl, X2; and first and second circulating chambers of the driving fluid Cp1, Cp2. This pressurizing device 3 furthermore comprises control means 3d, 3e arranged to alternately connect the thermal fluid arrival port PV1 to the first control chamber Cd1 and then the thermal fluid arrival port PV1 to the second control chamber Cd2 so as to generate the reciprocating displacement of the rod 3b in opposite directions of displacement Sl, S2. The rod 3b and the circulation chambers Cp1, Cp2 as well as check valves 3c1, 3c2, 3c3, 3c4 are arranged in such a way that under the effect of this reciprocating movement of the rod 3b, the circulation chambers of Fluid Cp 1, Cp 2 pass alternately into suction and then backflow of motor fluid and in such a way that when one of the circulation chambers Cp1, Cp2 is in suction of motor fluid coming from the inlet port P1, the other circulation chamber Cpl, Cp2 is necessarily backflow of fluid to the output port P2. Thus we create a motor fluid flow from the port Pl to the port P2. This flow of pressurized fluid passes via the output port P2 to the supply port Pp3 of the pump 2. More specifically, the nonreturn valves 3c1, 3c2, 3c3, 3c4 are arranged so that a circulation chamber in suction is connected to the input port Pl and isolated from the output port P2 and a flow chamber Cpl, Cp2 discharge is connected to the output port P2 and isolated from the input port Pl. The control means of the device motor fluid pressurizing means which comprise valves 3d and 3e are arranged to selectively adopt first and second distinct configurations. In the first configuration, visible in FIG. 1, the first control chamber Cd1 is connected to the inlet port of the thermal fluid under pressure PV1 and the second control chamber Cd2 is isolated from the port Pv1 and connected with a first thermal fluid exhaust port PV2 so as to force the displacement of the rod 3b in a first direction S1 and to generate an increase in volume of the first circulation chamber Cpl associated with a decrease in volume of the second circulation chamber Cp2. In the second configuration, visible in FIG. 2, the second control chamber Cd2 is connected to the arrival port of the thermal fluid under pressure PV1 and the first control chamber Cd1 is isolated from the port PV1 and connected to the first thermal fluid exhaust port PV2 so as to force the displacement of the rod 3b in a second direction S2 opposite the first direction S1. This rod displacement 3b in the first direction Sl, generates an increase in volume of the second circulation chamber Cp2 associated with a volume decrease of the first circulation chamber Cp1.

The control means 3d, 3e are arranged to move from the first to the second configuration when the rod 3b is substantially in its second extreme position X2 and to pass from the second to the first configuration when the rod 3b is substantially in its first extreme position Xl. The non-return valves 3c1, 3c2, 3c3, 3c4 are arranged to allow the passage of motor fluid from the arrival port P1 to the circulation chambers Cp1, Cp2 and to prevent the passage of motor fluid from the respective circulation chambers. , Cp2 to the input port Pl. The valves 3c1, 3c2, 3c3, 3c4 further prohibit the communication of the circulation chambers Cpl between them, Cp2 and allow the passage of motor fluid circulating chambers Cpl, Cp2 to the output port P2 and prohibit the passage of motor fluid from the output port P2 to the circulation chambers Cp1, Cp2. The pressurizing device 3 is designed to segregate the engine and thermal fluids in order to prevent the passage of vapor (thermal fluid) compressible in the liquid engine fluid which is said to be incompressible. As previously explained, the reciprocating displacement of the rod 3b in the opposite direction of displacement S1, S2 is controlled automatically, using the control means 3d, 3e, by simply supplying the thermal fluid under pressure from the port of arrival of thermal fluid PV1. Under the effect of this reciprocating movement, the fluid flow chambers Cp1 and Cp2 each pass alternately into suction and then discharge of motor fluid in such a way that when one of the circulation chambers Cp1, Cp2 is in suction of fluid from the input port P1, the other is necessarily in fluid discharge to the output port P2. The check valves 3c1, 3c2, 3c3, 3c4 are arranged so that a circulation chamber Cpl or Cp2 in suction is connected to the input port P1 and isolated from the output port P2 and a circulation chamber Cpl, Cp2 discharge is connected to the output port P2 and is isolated from the input port Pl thus creating a flow of fluid under pressure via the output port P2 to the supply port Pp3 of the pump. The circulation chambers Cp1, Cp2 and control Cd1, Cd2 and the rod 3b are arranged so that by moving the rod 3b: - in the first direction of movement Sl, the volumes of the first control chamber Cd1 and of the first circulation chamber Cpl then increase that the volumes of the second control chamber Cd1 and circulation Cp2 decrease; and - according to the second direction of movement S2 opposite the first direction S1, the volumes of the second control chamber Cd2 and the circulation chamber Cp2 decrease while the volumes of the first control chamber Cd1 and the circulation chamber Cp2 decrease. In the case illustrated in FIGS. 1 and 2, each of the control means 3d and 3e is formed of a plunger sliding in a recess corresponding to the body 3a and opening into one of the control chambers Cd1 or Cd2 which matches. The plunger 3d which opens into the chamber Cd1 is arranged to be pushed by the rod 3b to a position of connection of the port Pvl with the control chamber Cd1 when the rod 3b arrives in its extreme position Xl. Similarly, the plunger 3e which opens into the chamber Cd2 is arranged to be pushed by the rod 3b to a position of connection of the port Pvl with the control chamber Cd2 when the rod 3b arrives in its extreme position X2. In this way as soon as the rod 3b arrives in one of its extreme positions X1 or X2, its displacement is then reversed by feeding from the port PV1 one of the control chambers. Thus, an alternating movement of the rod is obtained as long as the port PV1 is supplied with thermal fluid under pressure. For this reciprocating movement to be possible, it is necessary that at each instant only one of the control chambers Cd1 or Cd2 be fed via the port PV1, the other of the control chambers Cdl or Cd2 then being exhausted to exhaust ports PV2, PV3. For this, the displacement of the plungers is synchronized so that when one of the plunger 3d, 3d is pushed by the rod 3b, then the other plunger is moved to the control chamber in which it opens. For this, a line 10a connects the chamber Cd2 to an operating chamber of the plunger 3d so that when the pressure in the chamber Cd2 passes a predetermined pressure threshold, then the plunger 3d moves to the chamber Cdl to feed it with pressurized fluid from port PV1. Similarly, a pipe 10b connects the chamber Cdl to an operating chamber of the plunger piston 3 so that when the pressure in the chamber Cdl passes a predetermined pressure threshold, then the plunger piston 3 moves to the chamber Cd2 for the supplying fluid under pressure from the port PV1.

Another way of synchronizing these plungers may also be to mechanically connect them to each other for example with the help of an imposing rod that these plungers always move together. The rod 3b is shaped so that when the volume of one of the control chambers Cd1, Cd2 increases by a given volume, the volume of one of the circulation chambers Cp1, Cp2 decreases by less than half of this volume. given and the volume of the other of the circulation chambers increases by less than half of said given volume. Thus, the rod serves as a pressure multiplier since, by admitting thermal fluid at a given pressure in one of the control chambers Cd1, Cd2, a pressure variation in the circulation chambers is generated greater than the pressure in the control chamber receiving the thermal fluid under pressure. Typically, it is arranged that the volume ratios are such that with a given thermal fluid inlet pressure via the port PV1, a motor fluid pressure can be obtained at the engine fluid output port P2 at least 2 times greater and preferably at least 10 times greater than the intake pressure at the PV1 port. In an ideal example, it is sought to have for a thermal fluid inlet pressure of the order of 3 to 5 bars, a motor fluid pressure at the port P2 greater than 50 bars and preferably equal to 60 bars. To perform this function of pressure multiplier, the rod 3b comprises first and second longitudinal portions 3f, 3g constituting longitudinal ends of the rod and a central portion 3H placed between these first and second portions 3f, 3g. The first and second portions of this rod 3b are arranged to slide respectively in the circulation chambers Cp1, Cp2. The central portion 3H slides inside the control chambers Cdl, Cd2 which it delimits between them and the first and second portions of this rod have respective cross-sections of surfaces equal to each other and less than one section. transverse of the central portion 3H of this rod 3b. The pump 2 visible in FIGS. 3 and 4 will now be presented. DESCRIPTION OF THE PUMP This pump 2 comprises a pump body 2a and a pump rod 2b forming a piston. This pump rod 2b is mounted in the pump body 2a to slide along an axis and to define therein: first and second actuating chambers Cd3, Cd4 of the sliding of the pump rod 2b between first and second extreme positions sliding the pump rod X3, X4; and - first and second fluid transfer chambers to be pumped Cp3, Cp4.

The pump 2 further comprises pump control means 2d, 2e arranged to alternately connect the pump power supply port Pp3 to the first operating chamber Cd3 and the motor fluid supply port Pp3 to the said operating chamber Cd4 is arranged so as to generate an alternating displacement of the pump rod in opposite directions of displacement S3, S4. These control means are here implemented using two plunger pistons 2d and 2e respectively disposed in corresponding recesses of the body 2a. The first plunger 2d is arranged so as to open into the chamber Cp3 in order to be able to move by linear sliding between: a first position of communication of the port Pp3 with the chamber Cd3 and the isolation of the chambers Cd3 and Cp3 one with respect to the other (visible in Figure 3); and a second position for placing in communication the chambers Cd3 and Cp3 and for isolating the port Pp3 with respect to these chambers Cd3 and Cp3 (visible in FIG. 4). The piston 2d opens into the chamber Cp3 to be pushed by the rod 2b when it is close to its position X3 and to be free to slide to the chamber Cp3 when the rod 2b moves to its position X4 and found away from its X3 position. Thus, the passage of the plunger 2d from its second position (Figure 4) to its first position (Figure 3) is controlled by the rod 2b.

In a symmetrical manner with respect to the first plunger 2d, the second plunger 2e is arranged to open into the chamber Cp4 in order to be able to move by linear sliding between: a first position of communication of the port Pp3 with the chamber Cd4 and isolation rooms Cd4 and Cp4 relative to each other (visible in Figure 4); and a second position for communicating chambers Cd4 and Cp4 and for isolating port Pp3 with respect to these chambers Cd4 and Cp4 (visible in FIG. 3). The second piston opens into the chamber Cp4 to be pushed by the rod 2b when it is close to its position X4 and to be free to slide to the chamber Cp4 when the rod 2b moves to its position X3 and found away from its X4 position. Thus, the passage of the plunger 2e from its second position (Figure 3) to its first position (Figure 4) is controlled by the rod 2b.

The displacement of these plunger pistons 2d, 2e are synchronized by means of synchronization of the pump 2 so that the first and second plunger pistons are always positioned so that only one of the control chambers Cd3 and Cd4 is supplied with power. both via the Pp3 port. Thus, as the control chambers Cd3 and Cd4 are fed in turn, the rod 2b moves from its position X3 to its position X4 when the chamber Cd3 is energized and the chamber Cd4 is exhausted, and then once the rod 2b arrives at position X4, the control chamber Cd4 is then fed via the port Pp3, the plunger 2d is then moved to prohibit the connection between the port Pp3 and the chamber Cd3 and connect this chamber Cd3 to the chamber Cp3 . The rod 2d then moves from its position X4 to its position X3. Once the rod has arrived at its position X3, the chamber Cd3 is again fed via the port Pp3 and the chamber Cd4 is put in the exhaust then imposing the rod displacement from the position X3 to the position X4. The two plunger pistons 2d and 2e are identical to each other and the detail of a plunger 2d is given in FIG. 6. To each plunger 2d, 2e corresponds to a control chamber 11a, 11b of plunger displacement 2d. , 2e which, when supplied with pressurized fluid via a synchronization line specific to each chamber 11a, 11b, generates a displacement force of the corresponding plunger 2d, 2e towards the transfer chamber Cp3, Cp4 into which it opens. One of the synchronization conduits 12a which opens into the chamber 11a corresponding to the first plunger 2d is selectively connected to the port Pp3 by the plunger 2e when the rod 2b in its position X4 pushes this plunger 2e.

The other of the synchronization lines 12b which opens into the chamber IIb corresponding to the second plunger 2e is selectively connected to the port Pp3 by the plunger 2d when the rod 2b is in its position X3 and pushes the plunger 2d. Each of the plungers 2d, 2e is associated with a return spring 14 tending to generate a resilient force opposing the displacement of the plunger corresponding thereto towards the transfer chamber in which it opens. Ideally the springs 14 are arranged so that the displacement of a plunger 2d, 2e towards the corresponding transfer chamber Cp3, Cp4 is only possible when the pressure in the control chamber 11a, 11b is close to the port pressure Pp3. It can be seen that each plunger 2d, 2e is perforated along its length 15 so that when the plunger has moved towards the corresponding chamber Cp3, Cp4, then the perforation makes it possible to limit the differential of the pressures applied to the ends of a given plunger. In this way the influence of the pressure in the chamber Cp3 on the displacement of the piston 2d towards the outside of the chamber Cp3 is limited. Similarly, the influence of the pressure in the chamber Cp4 on the displacement of the piston 2e towards the outside of the chamber Cp4 is also limited. Typically it is sought to limit the distance of the end sections of the piston 2d and the distance of the end sections of the piston 2e so that the control pressure of the displacement of these pistons is as low as possible in the chambers 11a and 11b. The involuntary displacement of each plunger 2d, 2e is thus limited.

Alternatively, these means for synchronizing the displacements of the plunger pistons may comprise mechanical means for connecting the plunger pistons 2d, 2e to each other so that any displacement of one of the plunger pistons corresponds to an equivalent displacement of the other. plungers.

These synchronization means allow reciprocating movement of the rod 2b when the pump is supplied with pressurized fluid under its port Pp3. The pump rod 2b, the transfer chambers Cp3, Cp4 as well as check valves 2c1, 2c2, 2c3, 3c4 belonging to the pump 2 are arranged: - so that under the effect of this reciprocating displacement of the rod pump 2b, the fluid transfer chambers to be pumped Cp3, Cp4 pass alternately suction and then discharge engine fluid; and in such a way that when one of the transfer chambers is in suction of fluid to be pumped from the suction port Pp1, the other is then necessarily in fluid discharge to be pumped towards the discharge port Pp2 thus allowing creating a flow of fluid to be pumped from the suction port Ppl to the delivery port Pp2. For any given displacement of the pump rod 2b, there is: on the one hand an increase in the volume of one of the first and second actuating chambers Cd3, Cd4 and a decrease in the volume of the other of these first and second second actuating chambers Cd3, Cd4; and on the other hand an increase in the volume of one of the first and second transfer chambers Cp3, Cp4 and a decrease in the volume of the other of these first and second transfer chambers Cp3, Cp4. The pump rod 2b is such that when the volume of one of the actuating chambers Cd3, Cd4 increases by a given volume, the volume of one of the transfer chambers Cp3, Cp4 increases by one volume. at least 1.2 times said given volume of increase of the actuating chamber Cd3, Cd4 and the volume of the other of the transfer chambers decreases by a volume equal to the volume of increase of the transfer chamber Cp3, cp4. Typically, for a displacement of rod 2b inducing an increase of 1 liter in the volume of one of the actuating chambers Cd3, Cd4, it can be seen that one of the transfer chambers Cp3, Cp4 will have an increased volume of at least 1.2 times the increase of 1 liter that is to say that its volume will have increased by at least 1.2 liters. The volume decrease of the other of the transfer chambers Cp3, Cp4 is equal to the increase of the volume of the other transfer chamber. Thus, the rod of the pump serves as a pressure reducer since, by admitting motor fluid at a given pressure in one of the actuating chambers Cd3, Cd4, a lower volume variation is created in these actuating chambers. it is in the transfer chambers Cp3, Cp4. Thus, the highest pressure of the transfer chambers is necessarily less than the pressure in the actuating chamber receiving the pressurized working fluid. It is ensured that the volume ratios are such that, with a given engine fluid inlet pressure via the port Pp3, it is possible to obtain a pumped fluid pressure at the level of the port Pp2 at least 2 times lower and preferably of at least 8 times less than the engine fluid inlet pressure. In an ideal example, it is sought to have for a motor fluid inlet pressure of the order of 50 bar, a pumped fluid pressure of less than 5 bar at the discharge port Pp2. To perform this pressure reduction function, the pump rod 2b comprises first and second longitudinal portions constituting longitudinal ends 2F, 2G of the rod 2b and a central portion 2H placed between these first and second portions 2F, 2G. The first and second portions of this pump rod are arranged to slide respectively in the actuating chambers Cd3, Cd4 and the central portion is arranged to slide inside the transfer chambers Cp3, Cp4 which it delimits between they. The first and second portions 2F, 2G of this pump rod 2a have respective cross sections of surfaces equal to each other and less than a cross section of the central portion 2H. The discharge port Pp2 is connected to the thermal fluid inlet Enl of the exchanger Eth via a flow restrictor 5 of thermal fluid passage section several times smaller than a thermal fluid passage section through the output Sol of the Eth exchanger. In this way, since the liquid fluid pressure at the inlet En 1 is greater than the internal pressure of the exchanger, there is a quantity limited by the flow restrictor 5 which enters the exchanger. In a particular embodiment, it is possible for an anti-return valve 16 to be connected to the inlet En1 in order to allow only the passage of thermal fluid via the flow restrictor 5 and towards the inlet En1 and to prohibit the passage of fluid to the outside of the exchanger via the Enl input. This non-return valve can be useful to prevent the Eth exchanger from losing too much pressure.

Note that for the implementation of the invention, it is ensured that all the connections used to connect the pressurizing device, the pump and the exchanger are arranged to transport fluids under pressure while limiting the pressure drop and maintaining constant link volumes. Finally, to improve the efficiency of the device, it is possible, as illustrated in FIG. 5, to connect at least one of the thermal fluid exhaust ports PV2, PV3 to a heat recovery exchanger 17 arranged to transfer heat to the liquid. to be admitted to the Eth interchange via its Enl input. This uses heat that would have been lost to preheat the liquid to be vaporized before it is injected into the Eth exchanger.

Claims (12)

REVENDICATIONS1. Pumping system (1) of a fluid to be pumped comprising: - a heat exchanger (Eth) containing a thermal fluid and arranged to vaporize this thermal fluid under the action of a heat input to the exchanger and to deliver this thermal fluid vaporized via an outlet of the exchanger (Sol); - a pump (2) with a suction port of the fluid to be pumped (Ppl) and a discharge port (Pp2) of said fluid to be pumped; characterized in that the pumping system further comprises: - a device (3) for pressurizing a driving fluid provided with at least one inlet port for the thermal fluid under pressure (PV1) connected to the outlet of the exchanger (Sol) and engine fluid inlet and outlet ports (P1, P2), this pressurizing device being adapted to use the pressure of the thermal fluid to generate a flow of engine fluid from the port of entering the engine fluid (P1) to the engine fluid output port (P2) and increasing the engine fluid pressure between said input and output ports (P1, P2); the pump (2) comprising a pump fluid supply port (Pp3) connected to the engine fluid outlet port (P2), this pump (2), under the action of a fluid flow pressurized engine arriving via its supply port (Pp3), being adapted to suck up the fluid to be pumped via its suction port (Ppl) and to pump the fluid to be pumped in this way via its delivery port ( pP2). A pumping system according to claim 1, wherein the engine fluid pressurizing device is disposed at a first distance from said heat exchanger and at a second distance from said pump, the second distance being at least ten times the first distance. 3. System according to any one of the preceding claims, wherein the heat exchanger (Eth) is a solar heat exchanger placed at least partly at the focus of a solar ray reflection device. 4. System according to any one of the preceding claims, wherein the device for pressurizing (3) the driving fluid comprises a body and a piston rod (3b) mounted in the body (3a) to slide along an axis. and defining therein: - first and second control chambers (Cd1, Cd2) of the sliding of the rod between first and second extreme positions of rod sliding (X1, X2); and - first and second circulating chambers of the working fluid (Cpl, Cp2); the engine fluid pressurizing device (3) further comprising control means (3d, 3e) arranged to alternately connect the thermal fluid inlet port (PV1) to the first control chamber (Cdl) then the thermal fluid inlet port (PV1) to the second control chamber (Cd2) so as to generate an alternating movement of the rod in opposite directions of displacement (S1, S2), and the rod (3b) and the circulation chambers (Cpl, Cp2) and check valves 3c1, 3c2, 3c3, 3c4) are arranged so that under the effect of this reciprocating movement of the rod (3b), the chambers circulating fluid (Cpl, Cp2) pass alternately in suction and then in motor fluid discharge and in such a way that when one of the circulation chambers (Cpl, Cp2) is in suction of motor fluid coming from the inlet port (Pl), the other is necessarily in fluid discharge motor to the output port (P 2) thus making it possible to create a flow of pressurized engine fluid via the output port (P2) to the supply port (Pp3) of the engine fluid pump. 5. System according to claim 4, in which for any given displacement of the rod (3b) of the pressurizing device (3), there is: - on the one hand an increase in the volume of one of the first and second control chambers (Cd1, Cd2) and a decrease in the volume of the other of these first and second control chambers (Cdl, Cd2); and on the other hand an increase in the volume of one of the first and second fluid flow chambers (Cpl, Cp2) and a decrease in the volume of the other of these first and second circulation chambers (Cpl, Cp2), and the rod being such that when the volume of one of the control chambers (Cd1, Cd2) increases by a given volume, the volume of one of the circulation chambers (Cpl, Cp2) decreases by less than half of this given volume and the volume of the other of the circulation chambers increases by less than half of the given volume. 6. System according to at least one of claims 4 or 5, wherein the rod (3b) of the engine fluid pressurizing device (3) comprises first and second longitudinal portions (3f, 3g) constituting longitudinal ends of the rod and a central portion (3H) placed between these first and second portions (3f, 3g), the first and second portions of this rod (3b) being arranged to slide respectively in the circulation chambers (Cpl, Cp2 ) and the central portion (3H) sliding inside the control chambers (Cd1, Cd2) that it delimits between them, the first and second portions of this rod having respective cross sections of equal areas between them and lower to a cross section of the central portion (3H) of this rod of the pressurizing device. 7. System according to any one of the preceding claims, wherein the pump (2) comprises a pump body (2a) and a pump rod (2b) forming a piston therein, said pump rod (2b) being in the pump body (2a) for sliding on an axis and defining therein: - first and second actuating chambers (Cd3, Cd4) of the sliding of the pump rod between first and second extreme positions of sliding of the pump rod (X3, X4); and first and second fluid transfer chambers to be pumped (Cp3, Cp4); the pump further comprising pump control means (2d, 2e) arranged to alternatively connect the pump fluid port (Pp3) to the first actuating chamber (Cd3) and then the port of supplying motor fluid (Pp3) to the second actuating chamber (Cd4) so as to generate an alternating displacement of the pump shaft in opposite directions of displacement (S3, S4), the pump shaft (2b) , the transfer chambers (Cp3, Cp4) as well as check valves (2c1, 2c2, 2c3, 3c4) belonging to the pump (2) being arranged so that under the effect of this displacement alternately of the pump rod (2b), the fluid transfer chambers to be pumped (Cp3, Cp4) pass alternately into suction and then backflow of the working fluid and in such a way that when one of the transfer chambers is in suction of fluid to be pumped from the suction port (Ppl), the other is then necessarily in fluid discharge e to pump to the discharge port (Pp2) thereby creating a fluid flow to pump from the suction port (Ppl) to the discharge port (Pp2) of the pump. 8. System according to claim 7, in which for any given displacement of the pump rod (2b), there is: on the one hand an increase in the volume of one of the first and second actuating chambers (Cd3 , Cd4) and a decrease in the volume of the other of these first and second actuating chambers (Cd3, Cd4); and on the other hand an increase in the volume of one of the first and second fluid transfer chambers to be pumped (Cp3, Cp4) and a decrease in the volume of the other of these first and second transfer chambers (Cp3, Cp4 ), and the pump rod (2b) being such that when the volume of one of the operating chambers (Cd3, Cd4) increases by a given volume, the volume of one of the transfer chambers (Cp3, Cp4) increases by a volume of at least 1.2 times said given volume of increase of the operating chamber (Cd3, Cd4) and the volume of the other of the transfer chambers decreases by a volume equal to volume of increase of the transfer chamber (Cp3, Cp4). 9. System according to at least one of claims 7 or 8, wherein the pump rod (2b) comprises first and second longitudinal portions constituting longitudinal ends (2F, 2G) of the pump rod and a central portion ( 2H) placed between these first and second portions (2F, 2G), the first and second portions of this pump rod being arranged to slide respectively in the actuating chambers (Cd3, Cd4) and the central portion sliding at the interior of the transfer chambers (Cp3, Cp4) which it delimits between them, the first and second portions (2F, 2G) of this pump rod (2a) having respective cross sections of equal areas between the and less than a cross section of the central portion (2H) of this pump rod. 10. System according to any one of the preceding claims, wherein the discharge port (Pp2) of the pump (2) is connected on the one hand to a water distribution network (Dist) and on the other hand to engine fluid inlet port (Pl) of the pressurizing device such that a portion of the fluid pumped by the pump also serves as the driving fluid used by the engine fluid pressurizing device, the working fluid and the fluid pumped by the pump being water. 11. System according to any one of the preceding claims, wherein the discharge port (Pp2) of the pump is connected to a thermal fluid inlet (En1) in the exchanger (Eth) via a flow limiter (5). of thermal fluid passage section several times smaller than a thermal fluid passage section through the outlet (Sol) of the exchanger (Eth). A system according to any one of the preceding claims wherein the pump (2) is a cylindrical pump adapted to be inserted into a tube of an artesian bore (7) having a diameter of less than 200 millimeters. , the pump rod (2b) sliding along an axis of sliding parallel to the axis of revolution of the cylindrical shape, a strainer (8) with an anti-return function being connected to the outside of the pump at said port of suction (Ppl) to allow the passage of fluid to pump only the strainer to the suction port (Ppl).