EP1752662B1 - Vorrichtung zum Aufkonzentrieren einer Flüssigkeit und Differentialkolbenpumpe - Google Patents

Vorrichtung zum Aufkonzentrieren einer Flüssigkeit und Differentialkolbenpumpe Download PDF

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Publication number
EP1752662B1
EP1752662B1 EP05017334A EP05017334A EP1752662B1 EP 1752662 B1 EP1752662 B1 EP 1752662B1 EP 05017334 A EP05017334 A EP 05017334A EP 05017334 A EP05017334 A EP 05017334A EP 1752662 B1 EP1752662 B1 EP 1752662B1
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EP
European Patent Office
Prior art keywords
differential piston
piston pump
valve
drive shaft
pump according
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.)
Active
Application number
EP05017334A
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German (de)
English (en)
French (fr)
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EP1752662A1 (de
Inventor
Peter-Bernhard Kathmann
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.)
SENECA SA
Original Assignee
SENECA SA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to ES05017334T priority Critical patent/ES2302105T3/es
Application filed by SENECA SA filed Critical SENECA SA
Priority to EP05017334A priority patent/EP1752662B1/de
Priority to PT05017334T priority patent/PT1752662E/pt
Priority to AT05017334T priority patent/ATE386884T1/de
Priority to DE502005002928T priority patent/DE502005002928D1/de
Priority to PCT/EP2006/005573 priority patent/WO2007016988A1/de
Priority to AU2006278957A priority patent/AU2006278957A1/en
Priority to EA200800551A priority patent/EA200800551A1/ru
Priority to JP2008528359A priority patent/JP2009504992A/ja
Priority to US11/989,803 priority patent/US20090246045A1/en
Priority to ZA200802182A priority patent/ZA200802182B/xx
Priority to CNA2006800287927A priority patent/CN101238288A/zh
Publication of EP1752662A1 publication Critical patent/EP1752662A1/de
Application granted granted Critical
Publication of EP1752662B1 publication Critical patent/EP1752662B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B5/00—Machines or pumps with differential-surface pistons
    • 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
    • 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

Definitions

  • the invention relates to a device specified in the preamble of claim 1. Art and a differential piston pump according to the preamble of claim 2.
  • the differential piston with the piston rod remote side pumps the liquid to be concentrated, eg seawater, controlled by inlet and outlet valves on the acting, for example, as the principle of reverse osmosis membrane, behind the concentrate with high residual pressure and permeate.
  • the residual pressure concentrate is cycled to the piston rod side of the differential piston, controlled by the inlet and outlet valve assembly, to assist in pumping directly by the residual pressure before the concentrate is substantially depressurized.
  • the linear guided shaft of the differential piston is coupled via a connecting rod with a crank pin of the drive shaft designed as a crankshaft.
  • the inlet and outlet valve assembly of the pressure chamber on the piston rod side of the differential piston has separate inlet and outlet valves, which are actuated via linearly guided ram of arranged on the drive shaft control cam against spring force.
  • crankshaft / connecting rod arrangement not only leads to large size of the differential piston pump, but due to e.g. due to the Pleuelauslenkung a little harmonic piston stroke, resulting in the further power losses and pulsations in the pumped liquid.
  • the invention has for its object to provide a operable with minimal use of primary energy device of the type mentioned, and to provide a compact and extremely efficient differential piston pump.
  • the radial piston pump concept results in a small size, in pulsation-poor performance and thanks to the tensile and compressive couplings in high efficiency with minimal losses, so that very little primary energy sufficient and the energy contained in the concentrate is used optimally and above all directly.
  • the tensile and compressive couplings lead to an extremely harmonious stroke of the differential piston and the valve control member.
  • the control of the inlet and outlet valves to the pressure chamber in optimal adaptation to the stroke of the differential piston and with minimal wear over long periods.
  • the radial piston pump concept allows seawater desalination to create and deploy compact devices tailored to the needs of individual buildings or groups of buildings, with even primary DC power from solar panels delivering high throughput rates, for example in sunny and marginal areas, due to the low primary energy input.
  • compact devices can be used without mains connection or in areas where electricity is not or rarely available or would be too expensive for domestic use.
  • the differential piston pump with the radial piston concept without connecting rods and above all without energy-consuming, powerful valve springs is ideal for all applications, not only for seawater desalination. suitable in which a liquid is to pump, and the same or the concentrated or another liquid with significant residual pressure is available.
  • a single valve control member is provided for each of an exhaust and an intake valve to minimize energy losses. Thanks to the pressure and traction coupling with the eccentric on the drive shaft accounts for energy-consuming valve springs, which benefits the efficiency and durability, since the inlet and outlet valve assembly operates relatively low power and contains no damage-prone components.
  • a rotatably mounted on the eccentric towed body is provided, with which the shaft end is positively coupled so that the orbital motion of the eccentric is transmitted in a harmonious manner.
  • the sliding guide allows the transverse displacement movements between the rotating eccentric and the linearly movable shaft without significant wear and without noise or vibration.
  • the sliding guide which mediates between the rotating eccentric and the linearly guided shaft, a rotation of the shaft.
  • the sliding guide can also be designed so that the shaft can rotate for distribution of wear.
  • the towed body is either made of assembled halves from assembled halves or even integrally formed, and so that it has an outwardly open pocket for the shaft, which is narrower for the positive locking than the outer width of the shaft.
  • the interlocking interaction takes place between relatively large sized surfaces, which avoids local wear.
  • the shaft in a housing-fixed sliding guide.
  • the sliding guide can be an inserted sliding bushing.
  • the sliding guide should be molded with Sliding support shells into the pocket with a sliding fit to support the shaft over as long a length as possible.
  • a base of the pocket should form a pressure surface for the shaft end (pressure coupling), which is longer because of the required sliding movement than the outer width of the shaft end.
  • pressure coupling pressure coupling
  • parallel grooves are formed in the shank defining a width approximately corresponding to the inside width of the pocket and forming outboard stems on the shank end as engagement members (on one or both sides of the shank) which engage undercuts in the pocket (pull coupling).
  • the undercuts in the pocket extend parallel to a tangent to the eccentric, wherein the undercuts in this direction are longer than the drivers in order not to hinder the relative sliding movement.
  • the undercuts can be formed continuously, which can simplify the mounting of the shaft end in the towed body, so that the towed body if necessary. Can be integrally formed.
  • the eccentric for the valve control member of a differential piston associated exhaust and inlet valve assembly relative to the eccentric for this differential piston is offset by 90 ° about the axis of the drive shaft and in the drive direction of rotation leading.
  • valve control members for the outlet and inlet valve arrangements of the plurality of differential pistons are also expediently distributed in a star shape around the axis of the drive shaft, wherein a common eccentric and a common towed body should be provided for the valve control members for constructional reasons.
  • the exhaust and intake valve assembly includes an intake valve seat and an exhaust valve seat fixed radially to the axis of the drive shaft and coaxial with the exhaust valve seat suitably closer to the drive shaft than the intake valve seat.
  • the valve control member should extend through the exhaust valve seat with sufficient clearance into the intake valve seat, with a sealing area provided between the valve seats, and also with respect to the drive shaft.
  • First and second shoulders on the valve control member serve to lift the respective valve body from their seats, wherein the lift-off movements of the valve body take place in opposite directions. That is, the valve control member opens the intake valve when lifting, while when lowering, the exhaust valve opens.
  • the shoulder of the ends of a set on the valve control member preferably screwed tube formed in order to achieve the largest possible contact areas.
  • valve bodies are urged to their seats by only weak springs, with the inlet valve body being a disc or plate which can be centered by the spring.
  • the exhaust valve body is an annular disc or an annular plate which is guided on the valve control member and can move relative thereto.
  • valve bodies With regard to perfect sealing conditions with attached valve bodies conical or spherical sealing surfaces could be provided on the valve bodies, and also the valve seats could be formed with conical or spherical sealing surfaces.
  • the dimensioning is carried out here so that both valve bodies are placed at the top and bottom dead center of the differential piston and the valve control member is a match to each shoulder.
  • This game can for example be between about 0.1 and 0.4 mm.
  • valve control member is expediently guided repeatedly over its length.
  • valve seats and a guide for the valve control member may be arranged in sleeve bodies, which are clamped in a housing chamber between a housing wall adjacent the drive shaft and a housing cover.
  • These sleeve bodies may have an inlet and two outlets while another inlet is disposed in the wall of the housing chamber. This concept simplifies installation and makes it possible to place the intake and exhaust valves close to each other to save space.
  • the eccentric for the differential piston and the valve control member are the same size and formed with the same eccentricity.
  • the eccentricity of the eccentric can be adjusted relative to the axis of the drive shaft in order to adjust the flow rate and / or performance as needed.
  • the eccentric could also be replaceably mounted on the drive shaft, so that a change in the eccentricity can be accomplished by replacing the eccentric.
  • FIG. 1 schematically shown device V for concentrating a liquid F in a concentrate or a concentrated liquid F K , for example, with simultaneous formation of pure liquid F R , could be operating on the principle of reverse osmosis seawater desalination plant, or a plant for concentrating fruit juice, or like. More. Basically, it is provided in the device V, to promote the liquid F with a radial piston pump R and to pressurize, to pass through a concentrator 3, from which the concentrated liquid F K is obtained with considerable residual pressure, while the pure liquid F R substantially depressurized eg as pure water permeate in seawater desalination, is collected.
  • the concentrated liquid F K with the considerable residual pressure is used in the radial piston pump R, with the energy directly support the promotion of the liquid F to the operation of the radial piston pump R only a little primary energy, such as electric power or the power of a motor P, too consume.
  • the concentrator 3 would be, for example, a membrane system that operates on the principle of reverse osmosis.
  • the radial piston pump R in Fig. 1 sucks the liquid F, which is optionally provided with a small pre-pressure, via a line 1 and a supply valve 16 by means of at least one differential piston K (intake stroke), and promotes the delivery cycle via a discharge valve 17 in a line 2.
  • the line 2 leads to the concentrator 3, from which the pure liquid F R emerges and in a line 4, the concentrated liquid F K is conveyed under the residual pressure to an inlet 5. After the concentrated liquid F K has been used in a pressure chamber 36 for acting on the differential piston K during the delivery cycle, it flows from an outlet 6 substantially without pressure.
  • a valve device 7 may be provided in the line 2, which promotes via a line 8 directly in de inlet 5, but is hardly or only used under certain circumstances in normal operation.
  • the radial piston pump R has a housing wall 10 which separates the conveying and working area of a chamber 11 of a drive shaft 12, and, for example, a removable housing cover. 9
  • an eccentric 13 for driving the differential piston K and another eccentric 14 for actuating an inlet and outlet valve assembly A are arranged, the eccentric 14 in the drive direction of rotation 40 about an axis 38 of the drive shaft 12 relative to the eccentric 13 by about 90 ° is offset.
  • the two eccentrics 13 are dimensioned differently sized and arranged with different eccentricities on the drive shaft 12.
  • the eccentrics 13, 14 may be fixedly formed on the drive shaft 12 or interchangeable wedged thereon.
  • each eccentric 13 or 14 consists of two rotatable relative to each other and definable in selectable relative positions eccentric sleeves.
  • axis of the eccentric 13 with 37 and the eccentric 14 are designated 39.
  • the differential piston K has on the piston rod side a shaft 15 which is connected via a train-pressure coupling directly to the eccentric 13, in the housing wall directly or indirectly guided linearly at 37, and sealed.
  • the differential piston K includes a sealing arrangement that separates a pumping chamber from the pressure chamber 36.
  • the intake and exhaust valve assembly A includes an intake valve of a valve body 32 and a valve seat 27, and an exhaust valve of a valve body 29 and a valve seat 28.
  • the valve seats 27, 28 are radially aligned with the axis 38 of the drive shaft 12 and coaxial, wherein the Outlet valve seat 28 to the drive shaft 12 has and is disposed closer to this, as the inlet valve seat 27 facing away from the drive shaft 12.
  • Both valves associated with a common valve control member 18 which is at least once in the housing wall 10 directly or indirectly linearly guided and sealed, and is articulated directly to the eccentric 14 via a compression and traction coupling S, wherein a shaft 19 of the valve control member 18 extends from the coupling S through the outlet valve seat 28 with radial clearance up to the inlet valve seat 27.
  • the seals 29 seal between the outlet valve and the chamber 11 and between the outlet 6 and the inlet valve seat 27, respectively.
  • a further guide 21 is provided for the valve control member 18 between the valve seats.
  • a tube 22 is fixed, for example screwed, which forms a first, to the outlet valve body 29 facing shoulder 23 and a second, the inlet valve body 32 facing shoulder 24.
  • the distance between the shoulders 23, 24 is smaller than the distance between the valve bodies 29, 32, when they are placed on their valve seats 27, 28, such that with the valves closed, for example, between each shoulder 23 or 24 and the adjacent valve body 32 or 29 a game between 0.1 to about 0.4 mm is present.
  • the inlet valve body 32 may be a disc or a plate and is centered by a weak spring 33 and applied to the inlet valve seat 27.
  • the valve body 29 may be an annular disc or an annular plate, which is acted upon by a spring 31 against the outlet valve seat 28. Between the outlet valve body 29 and the stem 19 of the valve control member 18, a mechanical seal 30 may be provided.
  • the valve bodies 32, 29 may have tapered or rounded seating surfaces, as may the valve seats 27, 29.
  • the inlet valve seat 27 may be formed in a sleeve member 25 while the guide 21 and seal 29 and outlet valve seat 28 are in another Sleeve member 26 may be formed. The sleeve body 25, 26 are clamped in the housing between the housing wall 10 and the housing cover 9.
  • an outlet in the sleeve body 26 leads to an inlet 35 to the pressure chamber 36.
  • the inlet 35 is simultaneously connected to a chamber located below the sleeve body 26 and containing the outlet valve body 29 at the outlet valve seat 28.
  • the drive shaft 12 is driven by the primary drive source P, for example an electric motor or an internal combustion engine, in order to drive the differential piston K and the valve control member 18 back and forth via the couplings S.
  • the differential piston K sucks in the intake stroke over the piston rod far side liquid F via the open feed valve 16 at.
  • the intake valve 32, 27 is closed and the exhaust valve 29, 28 is open.
  • the concentrated liquid F K is pushed out of the pressure chamber 36 through the outlet 6 substantially without pressure.
  • the outlet valve 29, 28 Shortly before reaching or generally in the region of the bottom dead center of the differential piston K, the outlet valve 29, 28 is closed and then, without valve overlap, the inlet valve 27, 32 is opened.
  • the concentrated liquid F K under the residual pressure in the pressure chamber 36 pressurizes the piston rod side of the differential piston K to cooperate with the delivery cycle.
  • the inlet valve 32, 27 is closed again and only then the outlet valve 29, 28 opens without valve overlap.
  • a plurality of differential pistons K and also a plurality of inlet and outlet valve arrangements A are distributed in a star shape and regularly around the drive shaft 12, for example at least three or more.
  • the device V for seawater desalination can be operated autonomously, for example, for the drinking water needs of a building or a system via a DC motor of solar panels.
  • the area ratio between the rod side remote and the piston rod side of the differential piston K is adjusted to the proportions between the liquid to be pumped and the concentrated liquid so that the energy in the concentrated liquid can be optimally utilized for assistance.
  • the pressure difference at the sealing device of the differential piston K is relatively low, and also the sealing region 20 is acted upon only for a short time during the conveying cycle with the residual pressure.
  • In the housing chamber 11 may be provided an oil bath.
  • Fig. 2 illustrates the intake stroke of the differential piston K in the radial piston pump R.
  • the concentrated fluid F K in the pressure chamber 36 is above the open Exhaust valve 28, 29 relaxed and is ejected into the outlet 6, while in the inlet 5 with closed inlet valve 27, 32, the residual pressure is present.
  • the shoulder 23 holds the outlet valve 28, 29 open while the shoulder 24 is away from the inlet valve body 32.
  • At a residual pressure of, for example, 68 bar in the inlet 5 prevails in the pressure chamber 36 only a pressure of about 1 bar.
  • the suction pressure with open supply valve 16 is about 1 bar.
  • Fig. 3 illustrates the delivery stroke of the radial piston pump R, in which the differential piston K moves toward top dead center.
  • the valve control member 18 has the inlet valve 32, 27 open while the outlet valve 28, 29 is closed.
  • the concentrated liquid F K flows with the residual pressure of for example 68 bar into the pressure chamber 36 and assists the differential piston K.
  • the outlet valve 28, 29 is kept closed with this pressure.
  • the liquid to be pumped is under a pressure of about 70 bar, the supply valve 16 is closed and the discharge valve 17 is opened.
  • the pressure difference at the sealing device of the differential piston K is only about 2 bar.
  • the 4 and 5 illustrate an embodiment of the coupling S, for example, between the shaft 15 and the eccentric 13.
  • the leadership will be 37 of the Fig. 1 formed by a sliding bush 41 in the housing wall 10, which dips with two support shells 42 in the chamber 11 and the shaft 15 is supported in the direction of rotation of the eccentric 13 against transverse forces and leads.
  • the support shells 42 engage in a pocket 45 of a towed body 44, which is rotatably mounted on a plain bearing bush or a needle bearing 43 on the eccentric 13 and axially positioned on the eccentric 13, for example by the shaft 15 and / or the support shells 42.
  • the pocket 45 has an inner width which approximately corresponds to the outer dimension of the support shells 42, so that a slight sliding fit is created here.
  • a lower pressure surface 49 for the shaft end (pressure coupling) and in undercuts 46 in the side walls of the pocket 45 traction surfaces 50 (train coupling) are formed for the shaft end.
  • the shank end contains two mutually parallel grooves 47, so that two outwardly extending drivers 48 are formed on the shaft end, which engage in the undercuts 46.
  • the undercuts 46 are longer than the outer width of the end of the shaft 15 and optionally extend to the periphery of the towed body 44th
  • the towed body 44 may be formed in one piece, or ( Fig. 5 ) are assembled from two halves 44a and 44b.
  • the grooves 47 are combined in a circumferential groove and also form the two drivers 48 has a circumferentially round collar, so that the shaft 15 in the Coupling S can twist.
  • a widening is formed, which forms one or two drivers 48 ', and engages in the undercut 46' of the towed body 44.
  • In the transverse direction in Fig. 6 is between the dogs 48 'and the undercut 46' and between the shaft 15 and the inlet to the undercut 46 'sufficient clearance provided to allow the indicated by a double arrow sliding movement of the shaft 15 during the orbital movement of the eccentric 13 about the axis 37.
  • FIG Fig. 7 In the embodiment in FIG Fig. 7 are on the towed body 44 bearing blocks 51 integrally formed in which a sliding pin 52 is seated, which passes through the end of the shaft 15. Between the bearing blocks 51 enough clearance is provided to the in Fig. 7 indicated by a double arrow sliding movement in the sliding guide of the shaft 15 during the orbital movement of the eccentric about the axis 37 allow.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • External Artificial Organs (AREA)
  • Separation Using Semi-Permeable Membranes (AREA)
  • Centrifugal Separators (AREA)
EP05017334A 2005-08-09 2005-08-09 Vorrichtung zum Aufkonzentrieren einer Flüssigkeit und Differentialkolbenpumpe Active EP1752662B1 (de)

Priority Applications (12)

Application Number Priority Date Filing Date Title
EP05017334A EP1752662B1 (de) 2005-08-09 2005-08-09 Vorrichtung zum Aufkonzentrieren einer Flüssigkeit und Differentialkolbenpumpe
PT05017334T PT1752662E (pt) 2005-08-09 2005-08-09 Dispositivo para concentrar um fluido e bomba de pistão diferencial
AT05017334T ATE386884T1 (de) 2005-08-09 2005-08-09 Vorrichtung zum aufkonzentrieren einer flüssigkeit und differentialkolbenpumpe
DE502005002928T DE502005002928D1 (de) 2005-08-09 2005-08-09 Vorrichtung zum Aufkonzentrieren einer Flüssigkeit und Differentialkolbenpumpe
ES05017334T ES2302105T3 (es) 2005-08-09 2005-08-09 Dispositivo para la concentracion de un liquido y bomba de piston diferencial.
AU2006278957A AU2006278957A1 (en) 2005-08-09 2006-06-09 Device for concentrating a liquid, and differential piston pump
PCT/EP2006/005573 WO2007016988A1 (de) 2005-08-09 2006-06-09 Vorrichtung zum aufkonzentrieren einer flüssigkeit und differentialkolbenpumpe
EA200800551A EA200800551A1 (ru) 2005-08-09 2006-06-09 Устройство для концентрирования жидкости и дифференциальный поршневой насос
JP2008528359A JP2009504992A (ja) 2005-08-09 2006-06-09 液体を濃縮する装置及び差動ピストンポンプ
US11/989,803 US20090246045A1 (en) 2005-08-09 2006-06-09 Device for Concentrating a Liquid, and Differential Piston Pump
ZA200802182A ZA200802182B (en) 2005-08-09 2006-06-09 Device for concentrating a liquid, and differential piston pump
CNA2006800287927A CN101238288A (zh) 2005-08-09 2006-06-09 液体浓缩装置及差动活塞泵

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05017334A EP1752662B1 (de) 2005-08-09 2005-08-09 Vorrichtung zum Aufkonzentrieren einer Flüssigkeit und Differentialkolbenpumpe

Publications (2)

Publication Number Publication Date
EP1752662A1 EP1752662A1 (de) 2007-02-14
EP1752662B1 true EP1752662B1 (de) 2008-02-20

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ID=35311420

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05017334A Active EP1752662B1 (de) 2005-08-09 2005-08-09 Vorrichtung zum Aufkonzentrieren einer Flüssigkeit und Differentialkolbenpumpe

Country Status (12)

Country Link
US (1) US20090246045A1 (ja)
EP (1) EP1752662B1 (ja)
JP (1) JP2009504992A (ja)
CN (1) CN101238288A (ja)
AT (1) ATE386884T1 (ja)
AU (1) AU2006278957A1 (ja)
DE (1) DE502005002928D1 (ja)
EA (1) EA200800551A1 (ja)
ES (1) ES2302105T3 (ja)
PT (1) PT1752662E (ja)
WO (1) WO2007016988A1 (ja)
ZA (1) ZA200802182B (ja)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008005319A1 (de) 2008-01-21 2009-07-23 Seneca S.A. Vorrichtung zum Trennen von Flüssigkeiten in Fraktionen mit unterschiedlichen Konzentrationen an Inhaltsstoffen
DE102008009195A1 (de) 2008-02-15 2009-08-20 Pleiger Maschinenbau Gmbh & Co. Kg Vorrichtung zum Aufkonzentrieren einer Flüssigkeit mittels einer Differentialkolbenpumpe
JP5706850B2 (ja) * 2012-05-21 2015-04-22 株式会社丸山製作所 往復動ポンプ
CN107191347B (zh) 2012-12-18 2019-07-23 艾默生环境优化技术有限公司 具有蒸气注入系统的往复式压缩机
DE102015014835A1 (de) * 2015-11-12 2017-05-18 Oberzom S.A. Radial-Kolben-Pumpe mit Zweikreis-Hydromotor
CN112253821B (zh) * 2020-11-05 2021-07-30 中国矿业大学 一种快装联合供液阀、使用方法及快速拼接方法

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3923722C2 (de) * 1989-07-18 1997-07-10 Uraca Pumpen Kombination von Verdrängerpumpe, insbesondere Kolbenpumpe, und Verdrängermotor, insbesondere Kolbenmotor
EP0450257B1 (fr) * 1990-04-03 1995-01-11 Fabio Laratta Machine hydraulique apte à réaliser en même temps la détente d'un liquide et le pompage d'un autre liquide
IT240896Y1 (it) * 1996-09-19 2001-04-11 Telme S R L Dispositivo motorizzato di pompaggio per osmosi inversa
GB2391912A (en) * 2002-08-15 2004-02-18 Colin Alfred Pearson Energy recycling pump

Also Published As

Publication number Publication date
CN101238288A (zh) 2008-08-06
ATE386884T1 (de) 2008-03-15
ZA200802182B (en) 2009-09-30
US20090246045A1 (en) 2009-10-01
PT1752662E (pt) 2008-05-28
EP1752662A1 (de) 2007-02-14
AU2006278957A1 (en) 2007-02-15
ES2302105T3 (es) 2008-07-01
DE502005002928D1 (de) 2008-04-03
JP2009504992A (ja) 2009-02-05
EA200800551A1 (ru) 2008-06-30
WO2007016988A1 (de) 2007-02-15

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