WO2004016947A1 - Pompe de recyclage d'energie - Google Patents

Pompe de recyclage d'energie Download PDF

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Publication number
WO2004016947A1
WO2004016947A1 PCT/GB2003/003593 GB0303593W WO2004016947A1 WO 2004016947 A1 WO2004016947 A1 WO 2004016947A1 GB 0303593 W GB0303593 W GB 0303593W WO 2004016947 A1 WO2004016947 A1 WO 2004016947A1
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WO
WIPO (PCT)
Prior art keywords
pump
piston
drive
valve
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/GB2003/003593
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English (en)
Inventor
Colin Pearson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AU2003259330A priority Critical patent/AU2003259330A1/en
Publication of WO2004016947A1 publication Critical patent/WO2004016947A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D61/00—Processes of separation using semi-permeable membranes, e.g. dialysis, osmosis or ultrafiltration; Apparatus, accessories or auxiliary operations specially adapted therefor
    • B01D61/02—Reverse osmosis; Hyperfiltration ; Nanofiltration
    • B01D61/06—Energy recovery
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • 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
    • F04B9/103—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 only one pumping chamber
    • F04B9/107—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 only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring
    • 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
    • F04B9/103—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 only one pumping chamber
    • F04B9/107—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 only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring
    • F04B9/1076—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 only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring with fluid-actuated inlet or outlet valve

Definitions

  • the invention herein described is a pump powered partly by a mechanical drive and partly by a pressurised fluid flow.
  • the pump is particularly applicable to reverse osmosis systems, which commonly waste a large part of their input energy by failing to recover the energy in a pressurised fluid flow. Energy savings of up to 90% are possible.
  • the pump consists of one or more piston-in- cylinder assemblies.
  • each piston reciprocates within its cylinder.
  • One face of each piston provides a pumping action while a pressurised driving fluid flow is applied to the opposite piston face, thus supplementing the drive force applied to each piston via a piston rod.
  • Input and output of the pumped flow is controlled by pump valves (preferably of a non-return type) operated by the pumped flow.
  • Input and output of the driving fluid is controlled by drive valves which are themselves controlled by operational connection to the pump valves.
  • a said pump valve is operated by the pressure differential across it of the pumped flow.
  • a feature of the pump is that it may conveniently use poppet valves for both pump and drive valves.
  • a poppet valve in this context is one in which the moving element or poppet has an axis of operational movement along a polar axis of. an annular valve seat having a radially-extending dimension.
  • the annular valve seat may be planar or a three-dimensional surface of revolution eg. part of a conical or spherical surface.
  • Poppet valves have advantages over other valve types in that there is little wear on their sealing surfaces and no requirement for expensive close-tolerance manufacture.
  • the pump differs from prior art in having the drive valves in operational connection to the pump valves, thus allowing simpler construction.
  • operation of the drive valves is by the mechanical drive, (eg. US4187173, US4288326, US4432876 and US4434056), or by the cylinder pressures, (eg. USRE33135, US4124488 and US4929347).
  • the invention provides a reciprocating-piston pump having a piston for impelling a pumped fluid flow, the pump when in operation being powered partly by a mechanical drive to the piston and partly by a driving fluid flow, the pumped fluid flow being impelled by a first face of the pump piston and the driving fluid flow being applied to a second face of the pump piston, the pump having valve means for controlling said driving fluid flow, the valve means being responsive to pressure applied to the pumped fluid by the first face of the piston, and means for limiting a pressure differential across the first and second piston faces during start-up or stroke-reversal of the pump.
  • the valve means preferably is disposed to be responsive also to a pressure against which the pump delivers fluid ie. the valve means is responsive to a pressure differential across it.
  • Figures 1 to 4 show a single cylinder of an embodiment of the pump according to the invention
  • Figure 5 gives an indication of piston travel and pressures during a start-up and stroke-reversal of the pump of figures 1 to 4;
  • Figures 6 to 10 show components of alternative embodiments of the pump;
  • Figure 11 shows a cam drive for the pump
  • Figure 12 shows a reverse osmosis or similar system incorporating the pump
  • Figure 13 shows part of a further embodiment of the pump.
  • the pump consists of a pump body 21 having a double- acting piston 23.
  • the piston 23 is free to reciprocate in a cylinder formed in the pump body 21.
  • the piston subdivides the cylinder into a pumping chamber 22 and a driving chamber 13.
  • Pumped flow can enter the pumping chamber via a pump inlet port 18 and a pump inlet valve 25, and can leave via a pump outlet valve 26 and pump outlet port 3.
  • Driving flow can enter the driving chamber via drive inlet port 8 and drive inlet valve 7, and can leave via drive outlet valve 12 and drive outlet port 1 1.
  • the pumped flow may be delivered for example to a reverse osmosis unit as described hereafter, the driving flow then being the return (waste) flow from that unit.
  • a piston seal 24 restricts leakage between the chambers 22 and 13.
  • a piston rod 10 passes through driving chamber 13 to a convenient source of mechanical power such as an electric motor, for example via a cam drive as described hereafter with reference to figure 11.
  • the piston rod drives the piston via a spring 14.
  • a rod seal 9 restricts leakage between the piston rod and the pump body 21.
  • the swept volume of the driving chamber is less than that of the pumping chamber by a fraction equal to the piston rod area divided by the piston area, plus or minus a relatively small quantity arising from relative movement between the piston 23 and the rod 10 when the spring 14 is expanding or contracting. Because of this difference in swept volumes, the driving fluid flow rate is less than the pumped fluid flow rate by the same fraction.
  • the pump inlet valve 25 is biassed towards its closed position by valve spring 17, and mechanically connected to the drive outlet valve 12 via a lost-motion linkage 16, which is sealed against leakage where it passes through the pump body 21 by a seal 15.
  • the linkage 16 allows limited relative motion between the pump inlet valve 25 and the drive outlet valve 12, thus compensating for manufacturing inaccuracies and allowing both pump inlet valve and drive outlet valve to close fully.
  • the pump outlet valve 26 is biassed by valve spring 5 and connected to the drive inlet valve 7 via lost-motion linkage 4, which is sealed against leakage where it passes through the pump body 21 by a seal 6.
  • the pump valves 26, 25 have poppets 1 and 20 which are surrounded by close- fitting bores, 2 and 19 respectively, for the first part of their travel from a closed position.
  • the close-fitting bores restrict flow through the pump valves, thus increasing the pressure differentials and the flow forces acting on them.
  • the effective opening 27 of valve 26 is less than the effective opening 28 of valve 7.
  • Valve 25 is similarly configured.
  • Figure 1 shows the pump prior to starting.
  • the piston and piston rod are stationary, all of the valves are shut and there is no flow.
  • a reverse osmosis system (not shown), to which the pump delivers fluid at outlet 3, and which delivers driving fluid to drive inlet 8 remains pressurised. Pressures are as shown in figure 5.
  • the pump inlet pressure could be around 0.2MPa (2 bar), the drive outlet pressure around 0.1 MPa (1 bar), the pump outlet pressure around 5.5MPa (55 bar) and the drive inlet pressure around 5MPa (50 bar). All of these pressures are absolute.
  • the driving flow rate would be around 60% of the pumped flow rate, requiring the piston rod area to be around 40% of the piston area.
  • Figure 2 shows the pump on a pumping stroke. Piston rod 10 and piston 23 are moving upwards, compressing the fluid in the pump and drive chambers as explained further below.
  • Pump chamber and drive chamber pressures have risen to levels at which the pressure force tending to open the pump outlet valve 26 has overcome the closing forces on the valve. These forces are those exerted by the spring 5, and the system pressure at outlet 3 on valve 26, and the driving fluid pressure force tending to close drive inlet valve 7.
  • the pump outlet and drive inlet valves thus are caused to open. This point is marked as 40 in figure 5.
  • Pumped flow is then free to pass out of the pump outlet port, and driving flow is free to enter the drive inlet port.
  • the pump outlet and drive inlet valves are held open by ensuring that the flow force tending to open the pump outlet valve overcomes both the closing force of valve spring 5 and the flow force tending to close the drive inlet valve.
  • the pump inlet valve 25 and drive outlet valve 12 are held closed by the pressure differentials across them.
  • the spring 14 allows the piston 23 and the piston rod 10 to move relative to each other.
  • the pressure differential between the pump chamber and the drive chamber is determined by the characteristics of piston spring 14.
  • Line 41 on figure 5 shows how, at start-up with drive inlet valve 7 closed, the drive chamber pressure would drop rather than rise if the piston were rigidly connected to the piston rod, thus increasing the pressure differential across the drive inlet valve 7 and preventing it from being opened.
  • the characteristics of the piston spring 14 are also chosen to avoid excessive relative travel between the piston rod and the piston, which would reduce the stroke of the piston and thereby the delivery of the pump.
  • the desired objective is to open both valves 7 and 26 with a pressure in chamber 13 iess than the drive inlet pressure, whilst avoiding the need for the mechanical drive to overcome an impractically high pressure differential between chambers 22 and 13. This is done by applying mechanically a limited force to the piston 24, in combination with a force exerted by adequate but not excessive pressurisation of the fluid in chamber 13. This is achieved by the compliance introduced into the system by the spring 14. Initial upward movement of the piston rod 10 into the chamber 13 pressurises the fluid in it to a value less than drive inlet pressure, but which nevertheless reduces the pressure differential across valve 7 and thereby the force holding it closed.
  • the fluid pressure in chamber 13 is applied through the piston 24 to the fluid in chamber 22, which is subjected also to further pressure generated by the mechanical force on the piston resulting from the piston rod having compressed the spring 14.
  • the resulting increased opening pressure differential across valve 26 is sufficient to overcome the reduced closing pressure differential across valve 7 and the closing force exerted by spring 5. Valves 26 and 7 thus open, drive fluid enters chamber 13 from drive inlet port 8 and the piston thereby is driven upwards.
  • Spring 14 is selected to have a spring characteristic that limits the pressure differential across the piston at the start of the stroke to a few bar.
  • An experimental model uses 3mm of spring compression and a spring stiffness giving 1 mm movement for 0.2MPa (2 bar) pressure differential across the piston.
  • the optimum spring characteristics depend on valve flow/force behaviour, valve area, and the effective bulk moduli of the water or other working fluid and of the casing 21. Suitable spring characteristics for other pumps can be found by computer simulation or by straightforward experiment on prototypes; in that the experimentation will consist mainly of substituting different springs, the latter is likely to lead quickly to a practical solution.
  • the flow/force characteristic of the pump outlet valve 26 is modified by the close- fitting bore 2 around the pump outlet valve poppet 1.
  • the bore restricts flow through the pump outlet valve during the first part of its opening travel, thereby causing the pressure differential and consequent flow force to be greater on the pump outlet valve than on the drive inlet valve 7, thus maintaining both valves open. It may be advantageous to use pump valves of larger diameter than the connected drive valves, to increase the net pressure force opening each pump and drive valve pair.
  • FIG 3 shows the pump at the end of the pumping stroke.
  • the flow rate through the pump outlet valve 26, and the consequent flow force on it reduce to zero. This allows valve spring 5 to close pump outlet valve 26, and allows flow force to close drive inlet valve 7 which is no longer being held open by the pump outlet valve via linkage 4.
  • Figure 4 shows the pump on a suction stroke. Piston rod 10 and piston 23 are moving downwards. Pump inlet valve 20 and drive outlet valve 12 have opened and remain open under the influence of pressure and flow, in a manner similar to that described above for the pumping stroke shown in figure 2.
  • Figure 5 also shows the continuation of pump operation into steady state running, to which figures 2, 3 and 4 also apply.
  • Points 40a and 40b are substantially equivalent to the pump states as described above for figures 2 and 3 respectively.
  • a single cycle of steady state running is shown by arrow 40c.
  • FIGS 6 to 9 show alternative features, which could be used singly or in combination, including in combination with spring 14.
  • Figure 6 shows a piston 50 incorporating a flexible diaphragm 52 which is rigidly attached to a piston rod 51.
  • the flexible portion serves the same function as the piston spring 14 shown in figure 1 , by permitting the piston rod 51 and the outer part of the piston 50 to move axially and elastically relative to each other, thereby moderating the difference in pressures between chambers 13 and 22 whilst generating sufficient pressure in chamber 22 to open valves 26 and 7.
  • Figure 7 shows a piston 55 which is mounted to piston rod 57 in a way which enables limited relative axial movement between piston rod and piston.
  • the piston rod 57 has a reduced diameter portion 57a between shoulders 57b which bear on respective axial faces of the piston 55 at extremes of movement of the piston on the reduced diameter portion.
  • the axial movement serves a similar function to piston spring 14 shown in figure 1 , and is equivalent to a variable-rate spring having a low rate over the range of free movement of the rod 57 in the piston and a very high rate at the extremes of movement.
  • initial movement of the piston rod pressurises both chambers 13 and 22 equally, the piston "floating" between the chambers and moving relative to the rod to prevent a pressure differential occurring.
  • a seal 56 restricts leakage between the piston rod and piston. It may alternatively be convenient to restrict the leakage by use of a small clearance between the piston and portion 57a of the piston rod, coupled with sealing faces on either side of the piston which cooperate with the shoulders 57b.
  • Figure 8 shows a piston configuration which is functionally equivalent to that embodying spring 14.
  • the piston 58 is rigidly attached to the piston rod 60, but there is limited relative axial movement between an elastomeric piston seal 59 and the piston, in operation the seal 59 slides or rolls between the position shown and a position 59a at the other end of the elongated peripheral groove 59b in which it is located.
  • the movement of the seal provides sufficient volume similarly to movement of the piston 55 of figure 7 to prevent an excessive pressure differential developing between chambers 22 and 13 whilst still permitting sufficient pressure to be developed to overcome the drive inlet pressure and spring 5 to open valves 26 and 7. It will be appreciated that the initial upward movement of the piston necessary to generate the valve-opening pressure is very small due to the high bulk modulus of the working fluid.
  • Figure 9 shows a piston 61 rigidly attached to a piston rod and incorporating pressure relief valves 62 and 63, which open when a predetermined pressure differential exists across them.
  • These serve a similar function to the piston spring 14 shown in figure 1 , in that they limit the pressure differential across the piston to a moderate non-zero value, but enable pressures to be developed on both sides of the piston to open valves 26 and 7 as described with reference to figures 1 and 2.
  • the pressure relief valves comprise balls 62a, 63a constituting poppets held against conforming (frustoconical or part-spherical) seats by leaf springs 62b, 63b.
  • the pressure relief valves could alternatively be incorporated in the pump body.
  • FIG 10 shows an alternative valve arrangement in a pump otherwise as illustrated in figures 1 to 4.
  • the pump inlet and outlet valves 85 & 80 incorporate elastically deformable elements 84 & 81. These elements firstly allow limited relative movement between the sealing surfaces of a pump valve and its connected drive valve, and secondly restrict pump valve flow. Both these characteristics are beneficial for pump operation, for reasons described above. Compression of a deformable element 81 , 84, permits full closure of a pump valve and its connected drive valve. Expansion of a deformable element 81 , 84 restricts flow through a pump valve, causing a pump valve opening travel 82 to be less than the opening travel 83 of its connected drive valve.
  • the deformable elements are shown as attached to the poppets but equally well could be attached to the pump body, surrounding the valve seats.
  • FIG 11 shows side and end views of a means for driving the piston rods of a two-cylinder version of the pump of figure 1.
  • a pump body 87 is substantially as described above.
  • a shaft 84 carries cams 82 & 83 and is driven to rotate by any convenient means.
  • the cams drive piston rods 85 & 81 on their upward strokes.
  • Return springs 86 & 80 drive the piston rods on their downward strokes.
  • the use of cams, rather than cranks, to drive the piston rods has the advantage that the cam profiles can be chosen to give a substantially constant output flow from a pump having two or more cylinders. Pressure and drive load fluctuations are thereby reduced.
  • FIG 12 shows a reverse osmosis system incorporating a pump as previously described.
  • An inlet solution flow at low pressure enters the pump 94 through pump inlet port 93 and leaves the pump through pump outlet port 95 at high pressure.
  • the inlet solution then enters a membrane assembly 96.
  • a proportion the solvent, but little of the solute passes through a semi-permeable membrane 97 and leaves the membrane assembly at low pressure through outlet 90.
  • the remaining flow of concentrated solution leaves the membrane assembly at high pressure, enters the pump through the drive inlet port 91 , and leaves the pump through drive outlet port 92 at low pressure.
  • the ratio of piston rod area to piston area determines the ratio of solvent flow through the membrane to the solution flow into the membrane assembly.
  • the pump could also be applied to ultrafiltration, using a system as described above for reverse osmosis, but having a filter medium in place of the semi-permeable membrane.
  • Figure 13 shows an alternative pump outlet valve in part section, consisting of a plug 98 sliding into a resilient sealing sleeve 99 to effect closure, and sliding out of the sleeve to open.
  • the sleeve 98 provides an overlap or delay between the opening of the drive inlet valve and the pump outlet valve, because the valve 98 moves and thus permits or causes valve 7 to open whilst the valve 98 is still closed due to it being within the sleeve 99.
  • Pump inlet valve 25 can be of similar configuration. This has the advantage of eliminating the need to allow limited lost motion in the linkage between each pair of connected pump and drive valves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Water Supply & Treatment (AREA)
  • Nanotechnology (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe alimentée en partie par une commande mécanique et en partie par un flux de fluide pressurisé, permettant de faire jusqu'à 90 % d'économies d'énergie dans un système à osmose inverse et autres systèmes semblables. La pompe comprend un ou plusieurs ensembles piston dans le cylindre. Une face de chaque piston génère une action de pompage tandis qu'un flux de fluide d'entraînement pressurisé est appliqué sur la face opposée du piston, renforçant ainsi la force d'entraînement appliquée sur chaque piston via une tige de piston. L'entrée et la sortie du flux pompé sont réglées par des clapets de pompe de non-retour commandés par le flux pompé. L'entrée et la sortie du fluide d'entraînement sont réglées par des soupapes d'entraînement qui sont elles-mêmes commandées par une connexion opérationnelle aux clapets de pompe. La pompe se caractérise en qu'elle peut être pourvue de soupapes à champignon, permettant ainsi d'éviter les coûts de matériaux résistant à l'usure et d'une fabrication à tolérance serrée.
PCT/GB2003/003593 2002-08-15 2003-08-15 Pompe de recyclage d'energie Ceased WO2004016947A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003259330A AU2003259330A1 (en) 2002-08-15 2003-08-15 Energy recycling pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0218995A GB2391912A (en) 2002-08-15 2002-08-15 Energy recycling pump
GB0218995.9 2002-08-15

Publications (1)

Publication Number Publication Date
WO2004016947A1 true WO2004016947A1 (fr) 2004-02-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2003/003593 Ceased WO2004016947A1 (fr) 2002-08-15 2003-08-15 Pompe de recyclage d'energie

Country Status (3)

Country Link
AU (1) AU2003259330A1 (fr)
GB (1) GB2391912A (fr)
WO (1) WO2004016947A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006114591A2 (fr) 2005-04-23 2006-11-02 Colin Alfred Pearson Pompe a fluide et unite de moteur
CN112649630A (zh) * 2020-07-01 2021-04-13 强一半导体（苏州）有限公司 功率器件测试探针卡用磁力式泄压结构的安装方法
US11378067B2 (en) 2016-10-20 2022-07-05 Katadyn Desalination, Llc Pump and a desalination system including the pump
WO2024077217A1 (fr) * 2022-10-06 2024-04-11 Championx Llc Appareil de pompage de liquide polymère en suspension
US12030792B2 (en) 2021-05-06 2024-07-09 Katadyn Desalination, Llc Recirculation loop reverse osmosis system with structurally fixed recovery rate and structurally stabilized full flow discharge
US12187959B2 (en) 2022-07-29 2025-01-07 Championx Llc Emulsion polymers and methods for improving pumpability

Families Citing this family (3)

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Publication number Priority date Publication date Assignee Title
DE502005002928D1 (de) * 2005-08-09 2008-04-03 Seneca S A Vorrichtung zum Aufkonzentrieren einer Flüssigkeit und Differentialkolbenpumpe
DE102008005319A1 (de) * 2008-01-21 2009-07-23 Seneca S.A. Vorrichtung zum Trennen von Flüssigkeiten in Fraktionen mit unterschiedlichen Konzentrationen an Inhaltsstoffen
DE102015014835A1 (de) * 2015-11-12 2017-05-18 Oberzom S.A. Radial-Kolben-Pumpe mit Zweikreis-Hydromotor

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Publication number Priority date Publication date Assignee Title
US4124488A (en) * 1976-02-27 1978-11-07 Ocean Water Limited Water purification by reverse osmosis
US4432876A (en) * 1980-07-30 1984-02-21 Seagold Industries Corporation Reverse osmosis apparatus and method incorporating external fluid exchange
DE3923722A1 (de) * 1989-07-18 1991-01-31 Uraca Pumpen Kombination von verdraenger- bzw. kolbenpumpe und verdraenger- bzw. kolbenmotor
US5193988A (en) * 1987-10-21 1993-03-16 Product Research And Development Reverse osmosis system and automatic cycling booster pump therefor
WO1998011979A1 (fr) * 1996-09-19 1998-03-26 Telme S.P.A. Dispositif de pompage pour osmose inverse entraine par un moteur

Family Cites Families (4)

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Publication number Priority date Publication date Assignee Title
US4187173A (en) * 1977-03-28 1980-02-05 Keefer Bowie Reverse osmosis method and apparatus
US4434056A (en) * 1979-04-06 1984-02-28 Keefer Bowie Multi-cylinder reverse osmosis apparatus and method
ES2103240B1 (es) * 1996-02-29 1998-04-16 Barreto Avero Manuel Bomba intercambiadora de salmuera por agua del mar para osmosis inversa.
GB9624205D0 (en) * 1996-11-21 1997-01-08 Pearson Colin A Fluid driven pump

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4124488A (en) * 1976-02-27 1978-11-07 Ocean Water Limited Water purification by reverse osmosis
US4432876A (en) * 1980-07-30 1984-02-21 Seagold Industries Corporation Reverse osmosis apparatus and method incorporating external fluid exchange
US5193988A (en) * 1987-10-21 1993-03-16 Product Research And Development Reverse osmosis system and automatic cycling booster pump therefor
DE3923722A1 (de) * 1989-07-18 1991-01-31 Uraca Pumpen Kombination von verdraenger- bzw. kolbenpumpe und verdraenger- bzw. kolbenmotor
WO1998011979A1 (fr) * 1996-09-19 1998-03-26 Telme S.P.A. Dispositif de pompage pour osmose inverse entraine par un moteur

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006114591A2 (fr) 2005-04-23 2006-11-02 Colin Alfred Pearson Pompe a fluide et unite de moteur
WO2006114591A3 (fr) * 2005-04-23 2007-05-03 Colin Alfred Pearson Pompe a fluide et unite de moteur
US8021128B2 (en) 2005-04-23 2011-09-20 Colin Alfred Pearson Fluid pump and motor unit
AU2006239003B2 (en) * 2005-04-23 2011-09-22 Colin Alfred Pearson Fluid pump and motor unit
US11378067B2 (en) 2016-10-20 2022-07-05 Katadyn Desalination, Llc Pump and a desalination system including the pump
CN112649630A (zh) * 2020-07-01 2021-04-13 强一半导体（苏州）有限公司 功率器件测试探针卡用磁力式泄压结构的安装方法
CN112698064A (zh) * 2020-07-01 2021-04-23 强一半导体（苏州）有限公司 功率器件测试探针卡用磁力式泄压结构的标定方法
CN112649630B (zh) * 2020-07-01 2022-08-16 强一半导体（苏州）有限公司 功率器件测试探针卡用磁力式泄压结构的安装方法
CN112698064B (zh) * 2020-07-01 2022-08-16 强一半导体（苏州）有限公司 功率器件测试探针卡用磁力式泄压结构的标定方法
US12030792B2 (en) 2021-05-06 2024-07-09 Katadyn Desalination, Llc Recirculation loop reverse osmosis system with structurally fixed recovery rate and structurally stabilized full flow discharge
US12187959B2 (en) 2022-07-29 2025-01-07 Championx Llc Emulsion polymers and methods for improving pumpability
WO2024077217A1 (fr) * 2022-10-06 2024-04-11 Championx Llc Appareil de pompage de liquide polymère en suspension

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