EP3914828B1 - Système de pompage et installation de refoulement de fluide - Google Patents

Système de pompage et installation de refoulement de fluide Download PDF

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Publication number
EP3914828B1
EP3914828B1 EP19712256.7A EP19712256A EP3914828B1 EP 3914828 B1 EP3914828 B1 EP 3914828B1 EP 19712256 A EP19712256 A EP 19712256A EP 3914828 B1 EP3914828 B1 EP 3914828B1
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EP
European Patent Office
Prior art keywords
fluid
piston
chamber
drive
trigger
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Active
Application number
EP19712256.7A
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German (de)
English (en)
French (fr)
Other versions
EP3914828C0 (fr
EP3914828A1 (fr
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Wan Hoi Armand
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Wan Hoi Armand
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Publication of EP3914828A1 publication Critical patent/EP3914828A1/fr
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Publication of EP3914828C0 publication Critical patent/EP3914828C0/fr
Publication of EP3914828B1 publication Critical patent/EP3914828B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/113—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • F03C1/0073—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1095—Valves linked to another valve of another pumping chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F7/00—Pumps displacing fluids by using inertia thereof, e.g. by generating vibrations therein
    • F04F7/02—Hydraulic rams

Definitions

  • the invention generally relates to a fluid delivery system.
  • the invention relates more particularly to a pumping system which ensures the delivery of a fluid, such as water, from an area at low altitude to an area at higher altitude.
  • discharge pumps using heat engines or electric motors as the driving source.
  • These discharge pumps make it possible to discharge water situated in a first zone at low altitude towards a second zone at higher altitude.
  • delivery pumps have good energy efficiency, their installation as well as their use generate significant costs.
  • the principle of a hydraulic ram is based on the use of a phenomenon called "water hammer" which corresponds to an overpressure created when a fluid flowing in a column at a certain speed is suddenly interrupted by a valve.
  • the overpressure makes it possible to raise a certain quantity of fluid much higher than the height of the initial column.
  • such a hydromechanical pump 1000 comprises a motor chamber 280 inside which a motor piston 220 slides.
  • the motor piston 220 is integral with a central shaft 340 which extends in a first multiplier chamber 300 and in a second multiplier 320 arranged on either side of the motor chamber 280.
  • the first multiplier chamber 300 and the second multiplier chamber 320 comprise an inlet 400, 360 and an outlet 420, 380 for, respectively, receiving a fluid and evacuating a fluid under pressure.
  • the pump 1000 includes a device for alternating the direction of distribution of a fluid under pressure on either side of the driving piston 220.
  • the device for alternating the direction of distribution of the fluid includes a distribution 340, 460, 480, 500 sliding inside a distribution chamber 200 so as to close off and/or release a network of intake and discharge ducts 520, 540, 560, 680, 600, 620 communicating with the motor chamber 280 as well as with the inputs 400, 360 of the multiplier chambers 300, 320.
  • the distribution carriage 340, 460, 480, 500 of the distribution chamber 200 is set in motion by actuators which are controlled by mechanical or hydraulic devices, by information feedback depending on the position of the driving piston 220 in the motor chamber 280.
  • the setting in motion of the carriage distribution 340, 460, 480, 500 in the distribution chamber 200 ensures the reversal of the direction of circulation of the pressurized fluid in the motor chamber 280.
  • This principle allows the pump 1000 to operate autonomously with very little energy and to ensure sufficient pressurization of the fluid for discharge in an area located at altitude.
  • the invention thus aims to propose a pumping system having increased reliability at high fluid pressures, and in fact generating a sufficiently high fluid discharge pressure to allow in particular applications aimed at treating the discharged fluid.
  • the invention also relates to a fluid discharge installation arranged in a body of water subjected to a current of the river or river type, comprising a Venturi tube immersed in the body of water so that the fluid pressure at the inlet of the tube is lower than the fluid pressure at the outlet of the tube, at least one reach-type structure arranged to channel and generate a laminar flow at the level of the inlet and the outlet of the Venturi tube, and a pumping system as described above arranged so that the first and second fluid inlets of the pumping system are connected to the inlet of the Venturi tube and the first and second fluid outlets of the pumping system are connected to the outlet of the Venturi tube.
  • the pumping system 1, 1a of the invention finds particular application in the field of the discharge of a fluid such as water, using the motive power of a static or dynamic manometric column.
  • the pumping system 1, 1a thus makes it possible to discharge this fluid from a zone located at low altitude, called low point, towards a zone at higher altitude, called high point.
  • the pumping system 1, 1a is thus driven by renewable energy.
  • the pumping system 1, 1a can also be integrated into a discharge installation 128 specially adapted to a river or river FL at low current speed.
  • pump will denote the pumping system 1, 1a of the invention.
  • discharge fluid will also designate a fluid circulating in this pump 1, 1a and which is intended to be discharged towards the high point.
  • operating fluid will designate a fluid circulating in the pump 1, 1a to allow its actuation, but this operating fluid is not intended to be discharged by the pump 1, 1a towards the high point.
  • the pump 1 comprises a driving enclosure 2, preferably of generally cylindrical shape, extending along a longitudinal axis X.
  • This driving enclosure 2 is closed at these axial ends by closure elements of the flange type 22, 23.
  • these two flanges 22, 23 are curved to better withstand the pressures exerted by the operating fluid moving in the drive enclosure 2.
  • the drive enclosure 2 is thus formed of a cylindrical wall 15 whose ends are closed by the curved walls 22, 23.
  • the drive enclosure 2 is also made of a metallic or composite material designed to withstand fluid pressures at least equal to three times the pressure of the manometric column.
  • the domed flanges 22, 23 and the cylindrical part 15 of the drive enclosure 2 are interconnected by annular flanges 160 - 163.
  • annular flanges 160 - 163 are represented on the picture 2 two flanges 160, 163 respectively fixed to the ends of circular section of the domed flanges 22, 23 and two flanges 161, 162 respectively fixed to the opposite ends of the cylindrical part 15.
  • the flanges rings 160 - 163 are also interconnected via tie rods 17 connecting the opposite flanges 160 - 163 of the cylindrical part 15 of the drive enclosure 2.
  • these tie rods 17 are made of metallic material.
  • the drive enclosure 2 comprises first and second operating fluid inlets E1, E2 opposed with respect to a transverse axis Y, as well as first and second operating fluid outlets S1, S2 opposed with respect to the transverse axis Y
  • These inputs E1, E2 and outputs S1, S2 are arranged in the cylindrical wall 15 of the enclosure 2.
  • the inputs E1, E2 and the outputs S1, S2 are respectively provided on opposite edges of the drive enclosure 2 with respect to the longitudinal axis X.
  • the pump 1 comprises a driving piston 13 positioned inside the driving enclosure 2 and configured to slide therein along the longitudinal axis X between first and second end positions P1, P2 under the action of the operating fluid. under pressure.
  • the driving piston 13 thus separates the driving enclosure 2 into a first 3 and a second 4 driving chamber, the first and second operating fluid inlets E1, E2 opening respectively into the first and second driving chambers 3, 4, while the operating fluid is discharged from the first and second drive chambers 3, 4 respectively through the second and first fluid outlets S2, S1.
  • the static manometric column is the water column whose height is expressed by the difference between the altitude at which the fluid inlets E1, E2 are fluidically connected by at least a first conduit (reference 129 on the figure 6 ) and the altitude at which the fluid outlets e S1, S2 are fluidically connected by at least one second conduit (reference 130 on the figure 6 ).
  • the second pipe 130 is connected to water located in a low altitude zone while the first pipe is connected to water located at a higher altitude, this difference in altitude having to be sufficient to generate a column of water capable of setting the motor piston 13 in motion.
  • a static manometric column is particularly feasible in mountainous streams, which flow along steep slopes.
  • An advantage of the pump 1, 1a of the invention resides in particular in the possibility of adapting the height of the manometric column (static or dynamic) according to the desired operating fluid pressure.
  • the pump 1, 1a operating using renewable energy, makes it possible to avoid the use of non-renewable energies and in particular of fossil energies.
  • the movement of the driving piston 13 towards its first end position P1 or its second end position P2 depends on the operating fluid distribution cycle circulating in the driving enclosure 2.
  • the operating fluid circulates in the drive enclosure 2 from the first fluid inlet E1 opening into the first drive chamber 3, and is evacuated by the first fluid outlet S1 from the second chamber motor 4. Under the pressure of the operating fluid during this first dispensing cycle, the driving piston 13 then moves towards its second end position P2.
  • the operating fluid circulates in the motor enclosure 2 from the second fluid inlet E2 opening into the second motor chamber 4, and is evacuated by the second fluid outlet S2 from the first motor chamber 3. Under the pressure of the operating fluid during this second dispensing cycle, the driving piston 13 then moves towards its first end position P1.
  • a seal (not shown), for example made of polytetrafluoroethylene, is mounted around the motor piston 13 so as to prevent the passage of the operating fluid from one motor chamber 3, 4 to the other.
  • the pump comprises a first and a second multiplier chambers 5, 6 arranged on either side of the drive enclosure 2 coaxially with the latter.
  • Each drive chamber 5, 6 is therefore integral with the relevant domed flange 22, 23 via a flange 18, 20.
  • the first multiplier chamber 5 is adjacent to the first drive chamber 3, while the second multiplier chamber 6 is adjacent to the second motor chamber 4.
  • the multiplier chambers 5, 6 are cylindrical.
  • Each multiplier chamber 5, 6 comprises a multiplier piston 52, 62 configured to slide in said chamber along its longitudinal axis, that is to say along the longitudinal axis X.
  • the multiplier piston of each multiplier chamber 5, 6 is integral from the end of a shaft 12, 12', which shaft is connected in a non-rigid manner by its end opposite to the driving piston 13, for example via a flexible connection or a universal joint 14, 14'.
  • the flanges 18, 20 securing the multiplier chambers 5, 6 to the motor enclosure 2, as well as the end wall 54, 64 of each multiplier chamber 5, 6 secured to the flange in question 18, 20, are drilled for the passage respective shafts 12, 12'.
  • the bores of the flanges 18, 20 and the considered end walls of the multiplier chambers 5, 6 each comprise a sealed bearing (not shown) provided around the considered shaft 12, 12', to prevent fluid leaks between the motor enclosure 2 and the multiplier chambers 5, 6.
  • a seal (not shown), for example made of polytetrafluoroethylene, is mounted around each multiplier piston 52, 62 of the multiplier chambers 5, 6.
  • the driving piston 13 being connected to the two shafts 12, 12' respectively integral with the pistons 52, 62 of the first and second multiplier chambers 5, 6, this driving piston 13 subjected to the pressure of the operating fluid makes it possible to set the multiplier pistons in motion 5, 6 multiplier chambers 5, 6 to allow the discharge of water outside of said multiplier chambers 5, 6, as will be specified later.
  • the first multiplier chamber 5 comprises a first inlet 50 and a first outlet 51 for discharge fluid
  • the second multiplier chamber 6 comprises a second inlet 60 and a second outlet 61 for discharge fluid.
  • the first discharge fluid inlets 50, 60 are preferably connected to the first conduit 129 allowing the admission of operating fluid into the drive enclosure 2, but can also be connected to another source of fluid, in particular the effluents of a treatment plant connected to pump 1.
  • the inlet 50, 60 and the outlet 51, 61 are preferably provided on the free end wall 53, 63 of the multiplier chamber in question 5, 6, to allow the filling or emptying of the part of the multiplier chamber 5, 6 between the piston 52, 62 and the end wall 53, 63.
  • the inlets 50, 60 and outlets 51, 61 of the discharge fluid comprise check valves, for example of ball valves 55, 65.
  • each multiplier chamber 5, 6 it is necessary to provide pneumatic inlets 24, 26 and outlets 25, 27 for each multiplier chamber 5, 6, preferably formed in the wall cylindrical 56, 66 of each chamber 5, 6 in the vicinity of the considered flange 18, 20.
  • the part of the multiplier chamber between the multiplier piston 52, 62 and the end wall 54, 64 of the multiplier chamber considered 5, 6 is filled with gas, in particular air.
  • the pneumatic inlets 24, 26 and outlets 25, 27 make it possible to avoid overpressures and depressions during the movement of the multiplier piston considered 52, 62, allowing movement without constraints of said piston considered 52, 62.
  • the surface of the cross section of the multiplier chambers 5, 6 is less than the surface of the cross section of the cylindrical wall 15 of the motor enclosure 2.
  • the discharge fluid pressure at the outlet 51, 61 of each multiplier chamber 5, 6 is much higher than the operating fluid pressure exerted on the driving piston 13. It is this high fluid pressure at the outlet 51, 61 of the multiplier chambers 5, 6 which allows the discharge of the fluid at a high point whose altitude is higher than that of the manometric column.
  • the ratio between the two cross-sections respectively of the multiplier chambers 5, 6 and of the motor enclosure 2 is chosen according to the desired application.
  • a discharge fluid pressure of the order of 15 to 20 bars to allow the implementation of a membrane nanofiltration process
  • a discharge fluid pressure comprised between 50 and 80 bars is necessary for the implementation of reverse osmosis processes.
  • the dimensions of the driving chamber 2 and of the driving piston 13 will be chosen according to the manometric water column, and the ratio between the two sections will be chosen according to the desired application. It is also taken into account, for this dimensioning, the pressure losses caused by the friction dissipating the mechanical energy of the moving fluid. Finally, account is taken of the pre-eminence of thrust that the driving piston 13 must have, to prevent the opposing force generated by the work of delivery or compression generated by the multiplier pistons 52, 62 canceling the thrust force of the driving piston. 13, and this in order to ultimately allow the sliding of said motor piston 13 in the motor enclosure 2.
  • the design of the pumping system 1, 1a of the invention can be adapted according to the desired manometric column, it is possible to design such a pump 1, 1a of large size, allowing the production of pressurized water of several tens thousands of cubic meters per day, representing the consumption of the equivalent inhabitants of an average city.
  • the alternate distribution device comprises a shutter device 7 comprising four shutter members 70 - 73, respectively provided at the level of the first and second operating fluid inlets E1, E2 and the first and second operating fluid outlets S1, S2.
  • Each shut-off member 70-73 is formed by a guillotine valve which moves between a shut-off position and an open position.
  • the valves 70, 71 of the inlets E1, E2 of the motor enclosure 2 are longitudinally connected to each other, for example using a cable or a rod 28, so that the drive of one valves 70, 71 to one of its closed or open positions drives the other valve 70, 71 into the opposite position.
  • the valves 72, 73 of the outputs S1, S2 of the motor enclosure are longitudinally connected to each other, for example using a cable or a rod 29.
  • each knife gate valve 70 - 73 includes a shovel (references 700, 710, 720 and 730 on the figure 4 ), that is to say a through orifice, which is aligned with the inlet E1, E2 or the outlet S1, S2 considered when said valve 70 - 73 is in the open position.
  • a shovel references 700, 710, 720 and 730 on the figure 4
  • This type of valve 70 - 73 whose shovel 700, 71, 720, 730 traverses the flow of liquid perpendicularly in the open position, has better resistance to the static or dynamic pressure of the fluid.
  • the shutter device 7 comprises a first and a second activation members 10, 11.
  • the first activation member 10 is configured to simultaneously actuate the valves 70, 71 of the first and second inlets E1, E2 of the driving enclosure 2, while the second activation member 11 is configured to simultaneously actuate the valves 72, 73 of the first and second outputs S1, S2 of the motor enclosure 2.
  • the first activation member 10, respectively the second activation member 11, comprises a first, respectively a second, cylindrical activation chamber closed at its ends and in which slides a first 103, respectively a second 113, piston of activation.
  • each activation member 10, 11 comprises first 101, 102 and second 111, 112 pneumatic inlets formed on the cylindrical wall of the activation chamber, in the vicinity of the opposite ends of the considered activation member 10, 11.
  • the activation piston 103 is integral with the longitudinal link 28 between the two guillotine valves considered 70, 71, so that the movement of the piston 103 towards the first pneumatic inlet 101 of the activation simultaneously induces the closing of the first entrance E1 of the motor enclosure 2 and the opening of the second entrance E2 of the motor enclosure 2.
  • the activation piston 113 is also integral with the longitudinal link 29 between the two guillotine valves considered 72, 73, so that the movement of the piston 113 towards the first pneumatic inlet 112 of the member activation 11 simultaneously induces the closing of the first output S1 of the driving enclosure 2 and the opening of the second output S2 of the driving enclosure 2.
  • the alternate distribution device comprises first and second triggers 8, 9 configured to actuate the first and second activation members 10, 11.
  • the triggers 8, 9 are formed on either side of the driving enclosure 2 with respect to the transverse axis Y and are respectively secured to the domed flanges 22, 23 by means of flanges 19, 21 provided for this purpose.
  • Each trigger 8, 9 comprises a pneumatic compression chamber 83, 93 in which a trigger piston 84, 94 is arranged to slide along the longitudinal axis of the compression chamber 83, 93, between a rest position and a trigger position .
  • the compression chamber 83, 93 of each trigger 8, 9 further comprises two gas outlets 81, 82, 91, 92, preferably air, connected to the pneumatic inlets 101, 102, 111, 112 of the activation members 10 , 11.
  • the compression chamber 83, 93 comprises at least one exhaust orifice (references 121, 121' on the picture 3 ) forming a vent formed in the cylindrical wall of the chamber 83, 93 to allow the circulation of air between said chamber 83, 93 and the outside when the piston 84, 94 moves. This avoids creating excess pressure and mechanical opposition to the movement of the piston 84, 94.
  • the air outlets 81, 82 of the first trigger 8 are respectively connected to the first pneumatic inlets 101, 112 of the first and second activation members 10, 11.
  • the air outlets 91, 92 of the second trigger 9 are respectively connected to the second pneumatic inlets 102, 111 of the first and second activation members.
  • Each trigger 8, 9 further comprises a rod 80, 90 that can be actuated by the motor piston 13, which rod 80, 90 is movable between a rest position in which the considered trigger 8, 9 is inactive, and an actuation position of the activation member 10, 11.
  • the driving piston 13 induces the movement of the rod 80, 90 towards its actuating position
  • the piston 83, 93, 84, 94 of the associated trigger 8, 9 then moves towards its trigger position.
  • valves 70, 73 of the first inlets and outlets E1, S1 of the drive enclosure 2 are in their open position. while the valves 71, 72 of the second inlet and outlet E2, S2 of the motor enclosure 2 are in their closed position.
  • the operating fluid pressure in the drive enclosure 2 then induces the movement of the drive piston 13 towards its second end position P2. Discharge fluid then leaves the second multiplier chamber 6.
  • the alternate distribution device finds itself in its second arrangement associated with the second operating fluid distribution cycle.
  • the operating fluid pressure in the enclosure 2 then induces the movement of the driving piston 13 towards its first end position P1. Discharge fluid then leaves the first multiplier chamber 5.
  • the alternate dispensing device finds itself in its first arrangement associated with the first operating fluid dispensing cycle, then the alternation of cycles begins again.
  • the alternate dispensing device is therefore operable between a first arrangement associated with the first fluid dispensing cycle, and a second arrangement associated with the second fluid dispensing cycle.
  • the trigger 8, 9 comprises a parallelepipedal body 31, one end wall 310 of which is secured to the drive enclosure 2 via the flange described above.
  • this parallelepipedic body is directly bolted 32 to the flange 22, 23 of the drive enclosure 2.
  • the flange 22, 23 or the flange include a hole to allow the passage of the rod 80, 90 in the drive enclosure 2.
  • a first free end of the rod comprises a collar 42 intended to come into contact with the driving piston 13.
  • the rod 80, 90 comprises a means return 44 to its rest position, which return means 44 is formed for example by a helical spring mounted around the rod 80, 90 in a coaxial manner and the ends of which bear respectively against the flange 22, 23 of the driving enclosure 2 and the shoulder surface formed by the flange 42.
  • the rod 80, 90 comprises at its free end a guide 43 in the form of a plate which extends transversely to the axis of the rod 80, 90, on either side of the latter.
  • the trigger 8, 9 comprises two plates 39, 39' formed in the parallelepiped body 31 on either side of the rod 80, 90, parallel to the latter.
  • the distance separating the two plates 39, 39' is less than the length of the guide 43.
  • Each plate 39, 39' thus comprises at least one longitudinal slot 42, 42" formed between its ends 40, 41; 40', 41' to ensure the passage of the free ends of the guide 43 and allow the sliding of the rod 80, 90 between its rest and actuating positions.
  • the two plates thus form slideways 39, 39'.
  • first ends 40, 40 'Slides are secured to the end wall 310 of the parallelepipedic body 31.
  • the trigger 8, 9 comprises two unlocking elements 34, 34' mounted so as to slide longitudinally in the parallelepiped body 31, on either side of the rod 80, 90, between a rest position (shown on the picture 3 ) and an unlock position.
  • Each unlocking element 34, 34' has the shape of a plate which slides between one of the longitudinal walls of the parallelepipedal body 31 and one of the slides 39, 39'.
  • Each unlocking element 34, 34' further comprises a longitudinal opening 37, 37' to allow the passage of the free ends of the guide 43 and the longitudinal displacement of the rod 80, 90.
  • the trigger 8, 9 comprises means 38, 38' for returning the unlocking elements 34, 34' to their rest position, that is to say at a distance from the end wall of the parallelepipedal body 31 secured to the compression chamber 83, 93.
  • These return means 38, 38' are for example helical springs. In its unlocked position, the unlocking element 34, 34' is therefore closest to the aforementioned end wall because the spring 38, 38' is in a compressed state.
  • the guide 43 of the rod 80, 90 of the trigger 8, 9 is configured to move the unlocking elements 34, 34' towards their unlocking position. In effect, when the rod 80, 90 moves towards its actuating position, the guide 43 exerts pressure on the first free ends 35, 35' of the respective unlocking elements 34, 34', inducing the movement of said unlocking elements 34, 34 ' to their unlocked position.
  • the trigger 8, 9 further comprises a drive element 45 preferably of parallelepiped shape mounted around the rod 80, 90, in sliding contact with the slideways 39, 39'.
  • This drive element 45 is movable between an inactive position (shown on the picture 2 ) and a trigger position.
  • This element 45 is made of an anti-friction material of the polytetrafluoroethylene (PTFE) type, or else of metal covered with an anti-friction material.
  • PTFE polytetrafluoroethylene
  • the drive element 45 In the inactive position, the drive element 45 is pressed against the considered flange 22, 23 of the driving enclosure 2, or if necessary against the flange connecting the trigger 8, 9 to the driving enclosure 2. In the position of trigger, the drive element 45 is in a position away from the flange 22, 23 or the aforementioned flange.
  • the trigger 8, 9 comprises two axes 33, 33' integral with the drive element 45 and extending longitudinally on either side of the rod 80, 90. These axes 33, 33' pass through holes formed in the guide 43 and in the end wall of the parallelepipedic body 31 to open into the compression chamber 83, 93 of the trigger 8, 9. The free ends of these pins 33, 33' are integral with the pneumatic piston 84, 94 of the trigger 8, 9. The displacement of the drive element 45 towards its trigger position therefore causes the displacement of the pneumatic piston 84, 94 towards its trigger position.
  • the trigger 8, 9 further comprises a member 120 for returning the drive element 45 to its trigger position.
  • This return member is for example a helical spring mounted coaxially around the rod 80, 90 and whose ends are secured respectively to the drive element 45 and the guide 43.
  • the guide 43 exerts a tension on the return spring 120 which is then relaxed and which tends to bring the drive element 45 to its trigger position.
  • the trigger 8, 9 comprises indexing means 46 which will now be described with reference to the picture 3 .
  • the indexing means 46 comprise at least two indexes 47, 47' formed by tabs pivotally mounted around pivot points 49, 49' on a lateral face of the drive element 45, which face extends in a plane parallel to the transverse axis Y.
  • Each index 47, 47' comprises a first free end 470, 470' facing the aforementioned side face, and a second free end 471, 471' moving away from the 'drive element 45 and extending in the direction of the slides 39, 39'.
  • the first free ends 470, 470' of the indexes 47, 47' are interconnected by a return member 100 of said indexes in a so-called separated position (as represented on the figure 2 ): this return member 46, for example a spring, exerts a tension which brings the first free ends 470, 470' of the indexes 47, 47' closer together and moves the second free ends 471, 471' of the indexes apart.
  • this return member 46 for example a spring
  • a portion comprising the second free end 471, 471' of each index 47, 47' is included in a housing provided in each slideway 39, 39'.
  • the second free end 471, 471' of each index 47, 47' bears against a free end 41, 41' forming an abutment of each slideway 39, 39'.
  • the free ends 471, 471' of the indexes 47, 47' are housed in the slots 37, 37' of the unlocking elements considered 34, 34'. In this way, in the spaced apart position, the indexes 47, 47' block the drive element 45 in its inactive position.
  • each second free end 471, 471' of the indexes 47, 47' comprises a bearing 48, 48'.
  • the stops 41, 41' of slideways and the seconds free ends 36, 36' of the unlocking elements also include bearings 410, 410', 420, 420'.
  • the driving piston 13 which moves towards its second end position P2 moves the rod 90 of the second trigger 9 towards its position trigger. This induces the release of the indexes 47, 47' towards their approach position and the sudden sliding of the drive element 45 towards its release position. Concomitantly, the piston 94 of the trigger 9 moves towards its trigger position.
  • the alternate distribution device finds itself, following the actuation of the activation members 10, 11 which cause the movement of the guillotine valves 70-73, in its second arrangement associated with the second operating fluid distribution cycle.
  • the motor piston 13 which moves towards its first end position P1 releases the rod 90 of the second trigger 9 which moves, thanks to the considered return means 44, towards its rest position.
  • the unlocking elements 34, 34' slide, under the action of the return members considered 38, 38', towards their rest position.
  • the guide 43 exerts a compressive force on the return spring 120 of the drive element 45, which induces the movement of said drive element 45 towards its inactive position then the movement of the indexes 47, 47' towards their separated position, blocking the drive element 45 in its inactive position as soon as the second free ends 471, 471' of the indexes 47, 47' are housed in the housings of the slides 39, 39' provided for this purpose.
  • the motor piston 13 reaches its first end position P1 and actuates the rod 80 of the first trigger 8, which is actuated in the same way as the second trigger 9.
  • the alternate dispensing device finds itself in its first arrangement associated with the first operating fluid dispensing cycle, then the alternation of cycles begins again.
  • the drive enclosure 2a in this second embodiment has an identical shape, with the difference that the flanges 22a, 23a are preferably flat walls.
  • the main difference in this second embodiment resides in the activation members 10a, 11a which are in this case two members of the tilting lever type arranged at the level of the flanges 22a, 23a of the driving enclosure 2a on either side of a transverse axis Y of said drive enclosure 2a.
  • each tilting lever 10a, 11a comprises a main part of substantially oval shape, with two parallel rectilinear arms 121, 121' extending in the plane containing the transverse axis Y, on either side of the multiplier chamber considered 5a , 6a.
  • the two arms 121, 121' of a rocking lever 10a, 11a are interconnected at their opposite ends by two curved arms 122, 122'.
  • Each rectilinear arm 121, 121' is pivotally connected, at a central portion of said arm 121, 121', to the relevant flange 22a, 23a of the motor enclosure 2a via a rectilinear connecting element 124 , 124' extending perpendicular to said flange 22a, 23a.
  • Each curved arm 122, 122' includes a projection 123, 123' extending from the central portion of the convex portion of the curved arm 122, 122', in the main plane of the rocker lever 10a, 11a.
  • the free end of this projection is pivotally connected to a rectilinear connecting element 125, 125'; 126, 126' (see figure 4 ), integral with the guillotine valves 70a - 73a, which connecting element 125, 125'; 126, 126' is in the extension of the cable or the rod 28a, 29a ensuring the connection of two guillotine valves 70a - 73a between them.
  • each tilting lever 10a, 11a pivotally connected to the relevant flange 22a, 23a is also connected by the two opposite projections 123, 123' to the four guillotine valves 70a - 73a, via cables or rods 28a, 29a.
  • the tilting lever 10a, 11a can thus pivot between a first position bringing the guillotine valves 70a - 73a into their positions corresponding to the first fluid distribution cycle, and a second position bringing the guillotine valves 70a - 73a into their positions corresponding to the second cycle. fluid delivery.
  • the tilting of the tilting lever 10a, 11a is actuated by the relevant trigger 8a, 9a.
  • the structure of this trigger 8a, 9a is slightly different in that it does not include a compression chamber, and in that the drive element 45a is connected to the tilting lever considered 10a, 11a, for example by the intermediate rods 127 integral with one of the curved arms 122'.
  • a first rocker lever 10a is connected by one of its curved arms 122' to the first trigger 8a, while a second rocker lever 11a is connected by one of its curved arms 122' to the second trigger 9a.
  • the driving piston 13a actuates the first trigger 8a.
  • This induces the movement of the drive element 45a which actuates, via the connecting rods 127, the tilting of the first tilting lever 10a.
  • This causes the movement of the guillotine valves 70a - 73a towards their position for closing the second inlets and outlets E2a, S2a of the driving enclosure 2a and for opening the first inlets and outlets E1a, S1a of the driving enclosure 2a.
  • the alternate dispensing device is found again in its arrangement associated with the first dispensing cycle, the driving piston 13a then moving towards its second end position.
  • the driving piston 13a actuates the second trigger 9a.
  • This induces the movement of the drive element 45a which actuates, via the rods 127, the tilting of the second tilting lever 11a.
  • This causes the movement of the guillotine valves 70a - 73a towards their position for closing the first inlet and outlet E1a, S1a of the driving enclosure 2a and for opening the second inlet and outlet E2a, S2a of the driving enclosure 2a.
  • the alternate dispensing device is found in its arrangement associated with the second dispensing cycle, the driving piston 13a then moving towards its first end position. Then the alternation of cycles starts again.
  • the rocking levers 10a, 11a can be connected to the pneumatic outlets 25, 27 of the multiplier chambers: the rocking levers 10a, 11a are then activated by pressurized air generated by the displacement of the associated multiplier piston.
  • This compressed air is led to a valve (not shown) placed on the relevant trigger 8a, 9a.
  • this valve is opened to allow the compressed air to actuate the tilting lever considered 10a, 11a.
  • the rods 127 of the triggers 8a, 9a are telescopic in order to be able to return to a rest position when the opposite trigger 8a, 9a is triggered, which causes the tilting levers 10a, 11a to tilt towards their opposite position.
  • This installation 128 finds its application in rivers FL with low current C, flowing along reliefs with low elevations.
  • the discharge installation 128 makes it possible to create a dynamic manometric column, generating sufficient fluid pressure to ensure the movement of the driving piston 13, 13a and the operation of the pump 1, 1a.
  • the installation 128 comprises a tube of the Venturi type 140, formed by first 141 and second frustoconical ducts 142 mounted head to tail on a cylindrical duct 143: the small bases of the first and second frustoconical ducts 141, 142 are therefore secured to the respective ends of the cylindrical duct 143.
  • the large base of the first tapered duct 141 is defined as being the inlet 144 of the Venturi tube 140, while the large base of the second tapered duct 142 is defined as being the outlet 145 of the Venturi tube 140.
  • the Venturi tube is arranged in the river FL parallel to the current C, so that the water from the river FL enters the venturi tube 140 through the first tapered conduit 141 and leaves it through the second tapered conduit 142.
  • the section of the large base of the first tapered duct 141 is greater than the cross section of the cylindrical duct 143.
  • the fluid pressure at the inlet 144 of the Venturi tube 140 is therefore greater than the pressure of fluid in the cylindrical conduit 143, which fluid pressure in the cylindrical conduit 143 is sufficient to allow applications implementing nanofiltration processes, that is to say between 15 bars and 20 bars, or reverse osmosis , ie between 50 bars and 80 bars.
  • the angle formed between the axis of the cylindrical duct 143 and any line of intersection between the frustoconical wall of each duct 141, 142 and a plane passing through the axis of said cylindrical duct is 6 degrees.
  • the first conduit 129 connected to the first and second inputs E1, E2; E1a, E2a of the pump 1, 1a captures the fluid at the inlet 144 of the Venturi tube 140, while the second conduit 130 connected to the first and second outlets S1, S2; S1a, S2a of the pump 1, 1a is in fluid communication with the water circulating in the cylindrical conduit 143.
  • the pressure difference between the inlets E1, E2; E1a, E2a and outputs S1, S2; S1a, S2a of the pump 1, 1a is therefore equivalent to a dynamic manometric column resulting from the difference between the fluid pressure at the inlet 144 of the Venturi tube 140 and the fluid pressure in the cylindrical conduit 143.
  • the fluid inlets 50, 60; 50a, 60 arranged in the end walls of the multiplier chambers 5, 6; 5a, 6a are in fluid communication with the outlet 145 of the Venturi tube 140, at the level of the free end of the second tapered conduit 142.
  • a masonry structure of the reach 146 type is provided at the level of the bank to channel the flow of part of the river at the inlet 144 of the tube.
  • Venturi 140 This has the effect of making the flow more laminar at the inlet 144 of the Venturi tube 140 and of avoiding the formation of vortices or other turbulence.
  • this makes it possible to further increase the fluid velocity - and therefore the dynamic pressure of the fluid - at the inlet 144 of the Venturi tube 140.
  • the discharge installation 128 comprises a second masonry work of the reach type 147 provided at the outlet of the Venturi tube 140.
  • This work 147 makes it possible to gradually slow down the flow at the outlet 145 of the Venturi tube 140 and to gradually slow the speed up to the flow velocity of the FL river. This avoids the formation of turbulence at the outlet 145 of the Venturi tube 140.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Multiple-Way Valves (AREA)
EP19712256.7A 2019-01-24 2019-01-24 Système de pompage et installation de refoulement de fluide Active EP3914828B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/FR2019/050159 WO2020152402A1 (fr) 2019-01-24 2019-01-24 Système de pompage et installation de refoulement de fluide

Publications (3)

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EP3914828A1 EP3914828A1 (fr) 2021-12-01
EP3914828C0 EP3914828C0 (fr) 2023-06-07
EP3914828B1 true EP3914828B1 (fr) 2023-06-07

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EP (1) EP3914828B1 (es)
JP (1) JP7321468B2 (es)
CN (1) CN113439160B (es)
AU (1) AU2019424710A1 (es)
BR (1) BR112021014258A2 (es)
CA (1) CA3127596A1 (es)
CO (1) CO2021010410A2 (es)
MX (1) MX2021008872A (es)
PE (1) PE20211677A1 (es)
WO (1) WO2020152402A1 (es)
ZA (1) ZA202105730B (es)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3122248A1 (fr) 2021-03-15 2022-10-28 Pierre Bignon Machine thermique avec compresseur alimenté par une colonne manométrique
FR3124553A1 (fr) 2021-05-07 2022-12-30 Pierre Bignon Système de relevage
WO2024044353A1 (en) * 2022-08-25 2024-02-29 Carlisle Fluid Technologies, LLC Positive displacement pump

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE38208C (de) * J. HlLLEN-BRAND in Mannheim Hahnsteuerung für eine durch Wasserdruck getriebene Pumpe
US3070023A (en) * 1959-09-28 1962-12-25 Nat Tank Co Fluid operated pump
US3312172A (en) * 1964-12-02 1967-04-04 Albert W Vaudt Switching valve
GB1133749A (en) * 1966-11-07 1968-11-13 Electronicon Ltd Improvements in and relating to electronic timing apparatus
JPS5512272A (en) * 1978-07-13 1980-01-28 Giichi Yamatani Booster pump
FR2441075A1 (fr) * 1978-11-07 1980-06-06 Tripette Et Renaud Sa Dispositif hydraulique utilisable comme moteur ou comme compteur, en particulier pour commander une pompe-doseuse
SE509378C2 (sv) * 1994-12-20 1999-01-18 Humanteknik Ab Vattenkraftmaskin
WO2001059300A1 (fr) * 2000-02-05 2001-08-16 Kanai Hirayama Pompe
RU2009106996A (ru) 2006-10-17 2010-11-27 Джи-И Хелткер АС (NO) Способ получения альфа-кетокислот и их эфиров
US20100290937A1 (en) * 2009-05-01 2010-11-18 Trout John F Fluid pump assembly
CN201461294U (zh) * 2009-06-05 2010-05-12 福田雷沃重机股份有限公司 方便液压油缸换向控制的泵送机构及混凝土泵车
US7955058B1 (en) * 2010-07-13 2011-06-07 Wayne Michael Angel Reciprocating piston to piston energy pump
US9713665B2 (en) * 2014-12-10 2017-07-25 Medtronic, Inc. Degassing system for dialysis
FR3039596B1 (fr) 2015-07-27 2019-09-06 Patrick Picard Pompe et dispositifs et installations comprenant une telle pompe
US11754060B2 (en) * 2020-09-01 2023-09-12 Fmc Technologies, Inc. Hydraulic fracturing pump system

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US20220120260A1 (en) 2022-04-21
CN113439160B (zh) 2023-06-20
EP3914828C0 (fr) 2023-06-07
JP7321468B2 (ja) 2023-08-07
WO2020152402A1 (fr) 2020-07-30
AU2019424710A1 (en) 2021-09-02
CN113439160A (zh) 2021-09-24
CA3127596A1 (fr) 2020-07-30
CO2021010410A2 (es) 2021-10-29
ZA202105730B (en) 2022-06-29
EP3914828A1 (fr) 2021-12-01
JP2022522268A (ja) 2022-04-15
BR112021014258A2 (pt) 2021-09-28
MX2021008872A (es) 2021-12-10
PE20211677A1 (es) 2021-08-31
US11815089B2 (en) 2023-11-14

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