EP1843040B1 - Procédé d'utilisation d'une pompe volumétrique oscillantes et pompes volumétriques oscillantes - Google Patents

Procédé d'utilisation d'une pompe volumétrique oscillantes et pompes volumétriques oscillantes Download PDF

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Publication number
EP1843040B1
EP1843040B1 EP20070006624 EP07006624A EP1843040B1 EP 1843040 B1 EP1843040 B1 EP 1843040B1 EP 20070006624 EP20070006624 EP 20070006624 EP 07006624 A EP07006624 A EP 07006624A EP 1843040 B1 EP1843040 B1 EP 1843040B1
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EP
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Prior art keywords
displacer
precompression
displacers
pump
liquid
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Application number
EP20070006624
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German (de)
English (en)
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EP1843040A2 (fr
EP1843040A3 (fr
Inventor
Frank Hofmann
Egbert Junge
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Hofmann GmbH Maschinenfabrik und Vertrieb
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Hofmann GmbH Maschinenfabrik und Vertrieb
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Publication of EP1843040A3 publication Critical patent/EP1843040A3/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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
    • 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
    • F04B9/117—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 the pumping members not being mechanically connected to each other
    • F04B9/1172—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 the pumping members not being mechanically connected to each other the movement of each pump piston in the two directions being obtained by a double-acting piston liquid motor

Definitions

  • the invention relates to a method for operating an oscillating positive displacement pump for the simultaneous pulsation of several liquids, with at least two pump chambers for each liquid and movable displacers therein, of which each sucks a displacer during the actual delivery phase of the other displacer liquid, at the end of Suction stroke reverses its direction of movement, precompresses the sucked into the associated pump chamber liquid in a Vorkompressionsphase and comes to a standstill upon reaching a predetermined Vorkompressions réellees and so long at standstill until the other displacer has finished its liquid promotion and then to this promotion then in turn with the promotion starts.
  • the invention relates to an oscillating positive displacement pump for the simultaneous pulsation of several liquids, with at least two pump chambers for each liquid and movable displacers therein, each of which a displacer during the actual delivery phase of the other displacer liquid sucks, at the end of the suction stroke its direction of movement reversed, precompresses the sucked into a corresponding pump chamber liquid in a Vorkompressionsphase and upon reaching a predeterminable pre-compression pressure comes to a standstill and remains at a standstill until the other displacer has finished its fluid delivery and then subsequently to this promotion in turn begins with the promotion.
  • the displacer for the individual pump chambers are rigidly connected to each other and have a common drive, usually in the form of a hydraulic cylinder.
  • Extraordinary pulsation poverty without the use of so-called pulsation dampers is achieved by oscillating positive displacement pumps with two displacers for each liquid, of which one displacer sucks liquid during the actual delivery phase of the other displacer at the end of the suction stroke reverses its direction of movement sucked into the pump chamber Pre-compressed liquid and comes to a standstill upon reaching a predetermined pressure from the system and remains as long as at standstill until the other displacer has finished its fluid delivery and then to this promotion the resting at the end of the pre-compression phase displacer begins its promotion.
  • the applied in the hydraulic drive cylinder hydraulic pressure is in such pumps, for example, by a control device according to DE 197 27 623 C1 as a function of the pressure of the currently pumping side just so regulated that it always remains at a safe distance below the pressure of the currently pumping side, so that liquid outlet valves of the pump chambers can not open due to the higher in the liquid line to the consumer pressure prevailing.
  • the area ratio of the two displacers Of great influence on the difference of the precompression pressures is the area ratio of the two displacers. The larger the area difference, the faster and so on, the precompression pressure in the displacer with the small area increases because of the small pump chamber volume via the Vorkompressionstik the pump chamber with the large-area displacer.
  • the precompression pressure in the other cylinder increases to twice the pressure as is set with a uniform distribution would. Is at a Verdränger lake, for example, 49: 1 in the cylinder with the pre-compression does not reach the large displacement, in the other cylinder the pressure rises to 49 times the pressure.
  • the unevenly pre-compressed pump chamber fillings on one side of the pump at the beginning of the delivery stroke with lines to the consumer, e.g. a spray gun to be connected, the promotion of the two liquids begins unevenly and staggered.
  • the delivery cylinder with the opposite of a consumer line pressure increased pressure is at its pressure release to consumer pressure jerky a corresponding amount of liquid in addition to the target amount in the consumer line.
  • the other delivery cylinder with the opposite of the consumer pressure lower Vorkompressionstik must first be further compressed to consumer pressure before material is pressed into the consumer line. To do this, the displacement stroke, i. Time, necessary. While one pump chamber, based on one pump side, starts with excess delivery, the delivery from the other pump chamber begins too late, so that the consumer lacks fluid from the supply cylinder, which is too low for a short time.
  • a method of the type mentioned is proposed, which is characterized in that during the Vorkompressionsphase a pressure equalization between the individual pump chambers is performed and during the subsequent delivery stroke pressure equalization between the individual pump chambers is prevented.
  • Embodiments of the method are specified in claims 2 to 5.
  • a first embodiment provides that for each liquid to be conveyed, rigidly connected to a single drive piston pistons transmit their power via a fluid to each of the piston associated displacer, wherein fluid spaces between the individual pistons and the associated displacer during the Vorkompressionsphase with each other connected and decoupled from each other during the delivery.
  • the fluid spaces associated with the displacers are thus interconnected during the precompression phase, so that the displacers can move relative to one another until the pressure equality in the pump chambers is reached.
  • the connection of the fluid spaces is interrupted, so that then no pressure compensation can take place and the displacer perform the delivery stroke as rigidly coupled together.
  • the pressure compensation be effected by displacement of operatively connected, exposed to the vorzukomprimierenden liquids, lockable piston becomes.
  • a displaceable in a housing the housing is used in two chambers dividing balance piston with two equal piston surfaces, each chamber is connected to one of the pump chambers.
  • the compensation piston moves under the influence of the larger pressure in the direction of the pump chamber with the smaller pressure until the pressure difference has reduced to zero.
  • a shut-off device should be present, which is opened during the Vorkompressionsphase for pressure equalization between the pump chambers and closed during the delivery stroke, so that the displacer connected to the delivery stroke as rigid To run.
  • the compensating piston should be forced into its central position by at least one centering spring, preferably two centering springs.
  • the entire pressure equalization capacity of the pressure compensation device is available again for the subsequent precompression phase.
  • a two-sided acted upon by the two liquids to be delivered compensating piston and two unilaterally acted upon by the liquids balance piston can be used, which are operatively connected to each other via a lever assembly.
  • the displacers are driven independently of each other during the precompression phase, come to a standstill independently upon reaching the desired Vorkompressions réellees and coupled together during the delivery stroke become.
  • the small-area displacer should be rigidly coupled to the large-area displacer during the delivery stroke.
  • the small-area displacer should be displaceable relative to the large-area displacer relative thereto and preferably generate approximately the same precompression end pressure by an associated hydraulic cylinder of appropriate size in the liquid enclosed in the associated pump chamber as in the liquid in the pump chamber with the large-area displacer ,
  • the small-area displacer is expediently brought into a zero position with the aid of a cylinder, preferably a pneumatic cylinder, during the suction stroke, from which the full intended pressure compensation capacity is available in both directions for the subsequent precompression phase.
  • a cylinder preferably a pneumatic cylinder
  • the invention proposes that the precompression is performed by the second and each further displacer associated with a pump side, each acting on the same liquid to be delivered, hydraulically decoupled driven, during the delivery stroke lockable Vorkompressionsverdränger.
  • the precompression is performed by the second and each further displacer associated with a pump side, each acting on the same liquid to be delivered, hydraulically decoupled driven, during the delivery stroke lockable Vorkompressionsverdränger.
  • two displacers are to be used which act on the same amount of liquid trapped in the delivery cylinder.
  • the one displacer should always be rigidly coupled to the large-area displacer and take over the liquid conveying function, while the other small-area displacer should take over the pressure equalization during the precompression phase.
  • This further small-area displacer should therefore be opposite the other small-area displacer relatively displaceable and be connected to a cylinder, preferably hydraulic cylinder, corresponding size, which generates in the trapped liquid in about the same Vorkompressionsendtik as in the pump chamber with the large-area displacer.
  • a cylinder preferably hydraulic cylinder, corresponding size, which generates in the trapped liquid in about the same Vorkompressionsendtik as in the pump chamber with the large-area displacer.
  • the displaceability of this further small-area displacer should be eliminated, for example by closing a shut-off valve arranged in a hydraulic line to the associated hydraulic cylinder.
  • the further small-area displacer is expediently brought into a zero position during the suction stroke, from which the full intended movement possibility is available in both directions for the subsequent precompression phase.
  • the solution of the second part of the object succeeds according to the invention with an oscillating positive displacement pump of the type mentioned, which is characterized by during the Vorkompressionsphase a pressure equalization between the individual pump chambers and performing during the subsequent delivery stroke a pressure equalization between the individual pump chambers preventing agent.
  • All displacement pumps exemplified are used for pulsation-free and in terms of flow ratio constant and uniform delivery of two liquids 10 and 11 from respectively associated reservoirs 10 'and 11' via suction lines 10 "and 11" through the positive displacement pump to a consumer, not shown here, to which Positive displacement pump downstream delivery lines 19 and 19 'lead.
  • the liquids 10 and 11 may e.g. be the two components of a two-component coating material for pavement markings, in which case the consumer e.g. a discharge nozzle or similar means for discharging the coating material on a roadway to be marked is.
  • FIG. 1 is the force of a drive piston 3, here a hydraulic piston, via two pistons 6 and 7 via a trapped in two fluid spaces 8 and 9 fluid, here hydraulic oil, and two displacers 4 and 5 on two enclosed in pump chambers 1 and 2 liquids 10 and 11th transfer.
  • the fluid spaces 8 and 9 are connected to each other via a line 12 in which a check valve 13 is arranged.
  • shut-off valve 13 Before the beginning of a subsequent delivery stroke, the shut-off valve 13 is closed, thus preventing fluid displacement between the fluid spaces 8 and 9 during the delivery stroke.
  • the displacers 4 and 5 are rigidly connected to the drive piston 3 and perform the axial movements together without relative displacements to each other.
  • the first pump chamber 1 is connected to a first chamber 20 and the second pump chamber 2 is connected to a second chamber 22 of a pressure compensation device 21 in each case via a line 12.1 or 12.2.
  • the pressure compensation device 21 has a displaceable, in the two opposing chambers 20 and 22 immersed balancing piston 24.
  • a check valve 13 ' is installed in one of the lines 12.1, 12.2, here in the line 12.1, a check valve 13 'is installed.
  • shut-off valve 13 ' is closed, thus preventing further displacement of the liquids in the pressure compensation device 21.
  • the compensating piston 21 is clamped between two axially acting compression springs 25 which, during the suction stroke with the shut-off valve 13 'open, return the balancing piston 21 to its central position, which again ensures the intended full movement possibility in both directions for the following precompression phase.
  • the first displacer 4 is rigidly connected to the drive piston 3, while the second displacer 5 relative to the displacer 4 is relatively displaceable.
  • the pressure from the drive cylinder chamber 14 acts via a line 12 '' in which a shut-off valve 13 "is arranged, in a rigidly connected to the drive piston 3 cylinder 42 on a second displacer 5 associated piston 43rd
  • the ratio of the effective area of the piston 43 to the effective area of the second displacer 5 corresponds to the area ratio of the driving piston 3 and the displacer 4.
  • FIG. 4 shows a section FIG. 3 with the small-area displacer 5, wherein here this displacer 5 is shown in its relative to the displacer 4 starting position, in which he provided upwards and downwards full movement possibility with respect to the displacer 4 has.
  • the second displacer 5 moves to reach the desired Vorkompressionsendibiles in a relative to the first displacer 4 leading, ie down here shifted position, the same section as FIG. 4 displayed FIG. 5 is shown.
  • the size of the relative displacement depends on the size of the filling degree difference in the pump chambers 1 and 2.
  • the piston 43 has on its side facing away from the displacer 5, a piston rod 44, which is led out of the cylinder chamber of the cylinder 42 and passed through a subsequent cylinder chamber 46.
  • a piston rod 44 On the piston rod 44, an axially displaceable piston 45 is arranged.
  • the piston rod 44 On the side facing away from the displacer 5, the piston rod 44 has a collar 47 forming an increase in diameter.
  • the cylinder chamber 46 on the side facing away from the displacer 5 has a collar 48 forming a taper.
  • the initial position of the displacer 5 according to FIG. 4 is defined by the fact that Piston 45 on the collar 48 of the cylinder chamber 46 and the piston rod collar 47 abuts the piston 45.
  • the piston 45 is driven in the same direction by the piston rod collar 47.
  • the piston 45 and over the collar 47 of the displacer 5 are returned back up to the starting position.
  • shut-off valve 13 ' is closed, whereby a displacement of the displacer 5 relative to the displacer 4 is no longer possible, so that both displacers 4 and 5 perform the delivery stroke as rigidly connected.
  • FIGS. 7 to 10 are the functions "conveying" and "pre-compression pressure build-up" divided into two displacers 5 and 51.
  • a rigidly connected to the first, large-area displacer 4 second, small-area displacer 5 takes over the fluid promotion; the further, freely displaceable displacer 51 assumes the structure of the Vorkompressionsend réellees.
  • the further displacer 51 and its actuator are not, as in the embodiment of the FIGS. 4 to 7 assigned to the large-area displacer 4, but the second pump chamber 2.
  • the rigidly interconnected displacer 4 and 5 are adjustable over the common drive piston 3.
  • the overlying the drive piston 3 drive cylinder chamber 14 is connected via a hydraulic line 12 '''arranged therein with a shut-off valve 13''' with a cylinder chamber 53 for adjusting the other displacer 51.
  • FIG. 8 shows a section with the small-area displacer 5 FIG. 7 with the further displacer 51 in its initial position, in which he has up and down the full intended movement possibility to compensate for degree of filling differences in the pump chambers 1 and 2.
  • the operating principle of the actuator corresponds to the operating principle of the actuator according to FIG. 4 ,
  • the second pump chamber 2 has a lower degree of filling than the first pump chamber 1, then the further displacer 51 moves, as in FIG FIG. 9 shown in a position below the starting position.
  • the size of the shift depends on the size of the filling degree difference.
  • a hydraulic piston 52 fixedly connected to the further displacer 51 has, on its side facing away from the displacer 51, a piston rod 55 which is led out of the associated cylinder space 53 and passed through a subsequent cylinder space 54.
  • an axially displaceable piston 56 is arranged on the piston rod 55.
  • the piston rod 55 On the side facing away from the further displacer 51, the piston rod 55 has a collar 58 forming an increase in diameter.
  • the cylinder chamber 54 on the side facing away from the further displacer 51 on a collar 57 forming taper.
  • the starting position of the other displacer 51, as they FIG. 8 shows and in which the further displacer 51 has the full intended movement possibility in both directions, is defined by the fact that the piston 56 rests against the collar 57 of the cylinder chamber 54 and the piston rod collar 58 on the piston 56.
  • the piston rod 55 pushes through the voltage applied to the cylinder collar 57 piston 56 through, wherein the piston rod collar 58 from the piston 56 away.
  • the further displacer 51 is so far returned by a remaining small hydraulic pressure in the cylinder chamber 53 until the piston rod collar 58 on the piston 56, which is pressed in the pressurized cylinder chamber 54 against the cylinder collar 57 comes to rest and so that his starting position again.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (15)

  1. Procédé pour faire fonctionner une pompe volumétrique oscillante pour le refoulement simultané à pulsations nulles de plusieurs liquides, avec, pour chaque liquide, au moins deux chambres de pompe (1, 2) et des déplaceurs (4, 5) mobiles dans celles-ci, dont respectivement l'un (4, 5) aspire du liquide pendant la phase de refoulement effective de l'autre déplaceur (5, 4), inverse son sens de mouvement à la fin de la course d'aspiration, précomprime dans une phase de précompression le liquide aspiré dans la chambre de pompe (1, 2) associée et, à l'obtention d'une pression de précompression prédéterminable, s'immobilise et reste à l'arrêt jusqu'à ce que l'autre déplaceur (5, 4) ait terminé son refoulement de liquide, et, à la suite de ce refoulement, commence ensuite, quant à lui, à refouler,
    caractérisé en ce que
    pendant la phase de précompression, une compensation de pression entre les différentes chambres de pompe (1, 2) est effectuée et, pendant la course de refoulement qui fait suite, une compensation de pression entre les différentes chambres de pompe (1, 2) est empêchée.
  2. Procédé selon la revendication 1, caractérisé en ce que, pour chaque liquide à refouler, des pistons existants (6, 7) solidaires d'un unique piston d'entraînement (3) transmettent leur force, via un fluide, aux déplaceurs (4, 5) associés respectivement à l'un des pistons (6, 7), des espaces de fluide (8, 9) entre les différents pistons (6, 7) et les déplaceurs y associés (4, 5) étant reliés entre eux pendant la phase de précompression et découplés l'un de l'autre pendant la course de refoulement.
  3. Procédé selon la revendication 1, caractérisé en ce que la compensation de pression est provoquée par déplacement de pistons (24) blocables conjoints par leur action qui sont exposés aux liquides à précomprimer.
  4. Procédé selon la revendication 1, caractérisé en ce que les déplaceurs (4, 5), pendant la phase de précompression, sont entraînés indépendamment l'un de l'autre, s'immobilisent indépendamment l'un de l'autre à l'obtention de la pression de précompression souhaitée et sont couplés l'un à l'autre lors de la course de refoulement.
  5. Procédé selon la revendication 1, caractérisé en ce que la précompression est effectuée par des déplaceurs de précompression (51) blocables pendant la course de refoulement, entraînés de manière découplée hydrauliquement, agissant respectivement sur le même liquide à refouler et associés au deuxième et à chaque autre déplaceur (5) d'un côté de la pompe.
  6. Pompe volumétrique oscillante pour le refoulement simultané à pulsations nulles de plusieurs liquides, avec, pour chaque liquide, au moins deux chambres de pompe (1, 2) et des déplaceurs (4, 5) mobiles dans celles-ci, dont respectivement l'un (4, 5) aspire du liquide pendant la phase de refoulement effective de l'autre déplaceur (5, 4), inverse son sens de mouvement à la fin de la course d'aspiration, précomprime dans une phase de précompression le liquide aspiré dans la chambre de pompe (1, 2) associée et, à l'obtention d'une pression de précompression prédéterminable, s'immobilise et reste à l'arrêt jusqu'à ce que l'autre déplaceur (5, 4) ait terminé son refoulement de liquide et, à la suite de ce refoulement, commence ensuite, quant à lui, à refouler,
    caractérisée par
    une compensation de pression entre les différentes chambres de pompe (1, 2) pendant la phase de précompression et des moyens empêchant une compensation de pression entre les différentes chambres de pompe (1, 2) pendant la course de refoulement qui fait suite.
  7. Pompe volumétrique selon la revendication 6, caractérisée en ce que, pour chaque liquide à refouler, des pistons (6, 7) solidaires entre eux sont prévus, dont la force peut être transmise, via un fluide, à respectivement l'un des déplaceurs (4, 5) associés et en ce que sont prévus, entre les différents pistons (6, 7) et les déplaceurs (4, 5) associés, des espaces de fluide (8, 9) qui sont reliables entre eux pour la précompression et sont découplables l'un de l'autre pour la course de refoulement.
  8. Pompe volumétrique selon la revendication 6, caractérisée en ce que sont prévus des pistons (24) conjoints par leur action et exposés aux liquides à précomprimer, lesquels pistons peuvent être débloqués l'un relativement à l'autre pour permettre la compensation de pression et sont déplaçables et qui peuvent être bloqués l'un relativement à l'autre pour empêcher une compensation de pression.
  9. Pompe volumétrique selon la revendication 6, caractérisée en ce que les déplaceurs (4, 5), pendant la phase de précompression, sont entraînables indépendamment l'un de l'autre, s'immobilisent indépendamment l'un de l'autre à l'obtention de la pression de précompression souhaitée et sont couplés l'un à l'autre pour la course de refoulement.
  10. Pompe volumétrique selon la revendication 6, caractérisée en ce que les déplaceurs (4, 5) pour un côté de la pompe sont couplés solidairement entre eux et en ce que sont associés au deuxième et à chaque autre déplaceur (5) d'un côté de la pompe des déplaceurs de précompression (51) qui agissent respectivement sur le même liquide à refouler, qui sont entraînables de manière découplée hydrauliquement pour la précompression et sont blocables pour la course de refoulement.
  11. Pompe volumétrique selon la revendication 6, caractérisée en ce que les déplaceurs (4, 5) pour un côté de la pompe sont couplés solidairement entre eux et en ce qu'est prévu, entre les chambres de pompe associées (1, 2), un dispositif de compensation de pression (21) qui comporte deux chambres (20, 22) reliées chacune à l'une des chambres de pompe (1, 2) et un piston de compensation (24) situé entre les chambres (20, 22) étant déplaçable en va-et-vient, au moins l'une des liaisons (12.1, 12.2) entre les chambres de pompe (1, 2), d'une part, et les chambres (20, 22) du dispositif de compensation de pression (21), d'autre part, pouvant être débloquée et bloquée au choix au moyen d'une soupape (13').
  12. Pompe volumétrique selon la revendication 7, caractérisée en ce que le fluide est une huile hydraulique et en ce que la liaison entre les espaces de fluide (8, 9) est formée par une conduite d'huile hydraulique (12) avec une soupape (13) située dedans.
  13. Pompe volumétrique selon la revendication 7 ou 12, caractérisée en ce qu'est situé, entre les pistons (6, 7) et les déplaceurs (4, 5) respectivement associés, respectivement un ressort (15, 16) permettant d'exercer sur le piston associé (6, 7) une force qui, à soupape (13) ouverte, amène celui-ci dans une position de départ définie.
  14. Pompe volumétrique selon la revendication 11, caractérisée en ce qu'est situé, dans au moins l'une des chambres (20, 22) du dispositif de compensation de pression (21), un ressort (25) permettant d'exercer sur le piston de compensation (24) une force qui, à soupape (13') ouverte, amène celui-ci dans une position de départ définie.
  15. Pompe volumétrique selon l'une des revendications 6 à 14, caractérisée en ce qu'il s'agit d'une pompe de refoulement et de dosage d'un équipement de fabrication de marquages routiers en une substance de revêtement bicomposite liquide qui durcit par réaction.
EP20070006624 2006-04-03 2007-03-30 Procédé d'utilisation d'une pompe volumétrique oscillantes et pompes volumétriques oscillantes Active EP1843040B1 (fr)

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Application Number Priority Date Filing Date Title
DE10615845 2006-04-03

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EP1843040A2 EP1843040A2 (fr) 2007-10-10
EP1843040A3 EP1843040A3 (fr) 2009-03-11
EP1843040B1 true EP1843040B1 (fr) 2010-04-21

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DE102010034585B4 (de) * 2010-08-17 2016-04-07 Lewa Gmbh Vorrichtung zur Durchführung von Chromatografie

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4359312A (en) * 1978-08-15 1982-11-16 Zumtobel Kg Reciprocating pump for the pulsation-free delivery of a liquid
US4543044A (en) * 1983-11-09 1985-09-24 E. I. Du Pont De Nemours And Company Constant-flow-rate dual-unit pump
US5141408A (en) * 1990-11-09 1992-08-25 Prc Product pumping apparatus
DE19727623C1 (de) * 1997-06-28 1998-07-30 Hofmann Walter Maschf Verfahren zur Förderung von Flüssigkeiten mit Hilfe einer aus zwei einzelnen oszillierenden Verdrängerpumpen bestehenden Pumpenkombination und Vorrichtung zur Durchführung des Verfahrens

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DE502007003483D1 (de) 2010-06-02
DK1843040T3 (da) 2010-08-09
EP1843040A3 (fr) 2009-03-11

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