EP3030784A1 - Pompe volumétrique - Google Patents

Pompe volumétrique

Info

Publication number
EP3030784A1
EP3030784A1 EP14736732.0A EP14736732A EP3030784A1 EP 3030784 A1 EP3030784 A1 EP 3030784A1 EP 14736732 A EP14736732 A EP 14736732A EP 3030784 A1 EP3030784 A1 EP 3030784A1
Authority
EP
European Patent Office
Prior art keywords
unit
pump
valve unit
hydraulic
inline
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.)
Granted
Application number
EP14736732.0A
Other languages
German (de)
English (en)
Other versions
EP3030784B1 (fr
Inventor
Norbert Jäger
Andreas KARWOWSKI
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.)
Mhwirth GmbH
Original Assignee
Mhwirth GmbH
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
Application filed by Mhwirth GmbH filed Critical Mhwirth GmbH
Publication of EP3030784A1 publication Critical patent/EP3030784A1/fr
Application granted granted Critical
Publication of EP3030784B1 publication Critical patent/EP3030784B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22—Arrangements for enabling ready assembly or disassembly
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0054—Special features particularities of the flexible members
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections

Definitions

  • the invention relates to a positive displacement pump with a drive unit and a pump unit.
  • Displacement pumps are already known in many designs.
  • a disadvantage of the known positive displacement pumps is that they are either not suitable for high pressures and high volume flows or that they are difficult to maintain.
  • the invention has set itself the task of creating a positive displacement pump which is improved, at least with regard to one of the disadvantages mentioned.
  • the term "positive displacement pump” refers in particular to a pump which has at least one displacement element in at least one working space through which the medium to be pumped, that is to say the conveying medium, flows.
  • the positive displacement pump according to the invention has a drive unit.
  • a pump unit is provided with at least one inline valve unit.
  • two inline valve units are provided per working space.
  • the inline valve unit is braced in an operating position between two flanges of the pump unit. This distortion of the valve units between two flanges can also be referred to as Eisenflanscheinbau.
  • the flanges are interconnected by means of connecting and / or spacing means, preferably at a fixed distance from one another.
  • the clamping is therefore preferably not by successively moving the flanges, but preferably by the spreading (in other words: clamping) of a clamping device.
  • a displacement of the valve unit is possible without disassembly of a connecting and / or spacer means. It must therefore be disassembled for the displacement of the inline valve unit no connection and / or spacer means by means of which or the flanges are connected to each other. As a result, the maintenance of the inline valve units is significantly simplified and accelerated.
  • the distance between two adjacent connection and / or spacer means is preferably greater than the outer dimensions - such as the diameter - of the inline valve unit.
  • connection and / or spacer means may be arranged such that adjacent connection and / or spacer means always have the same distance from each other. However, they can also be arranged so that different distances between adjacent connecting and / or spacers result. If the connecting and / or spacing means are arranged such that at least the greatest distance (more precisely, the clear width) between two adjacent connecting and / or spacing means is greater than the outer dimensions - such as the diameter - of the in-line valve unit, then this is a prerequisite for a displacement of the inline valve unit between two connection and / or spacer means through, without their disassembly, created.
  • a valve displacement device is provided by means of which the inline valve unit can be displaced from an operating position into a maintenance position.
  • the valve unit is preferably displaceable on a path deviating from a circular path.
  • the valve displacement device is preferably fixedly connected to the rest of the pump.
  • the inline valve unit is preferably braced exclusively with the flanges.
  • the inline valve unit is therefore preferably clamped exclusively between the flanges, a requirement for a simplified and quick maintenance is created.
  • in-line valve unit refers in particular to a valve unit which is flowed through in a straight line.
  • straight through means in particular that the flow direction immediately before the valve is at least approximately in the direction of flow immediately after the valve corresponds. This distinguishes inline valve units of angle valve units, in which the fluid enters, for example, on the bottom and at an angle of 90 degrees laterally exit.
  • the inline valve units are preferably flowed through at least approximately vertically. This means in particular that the flow direction is at least approximately perpendicular immediately before and immediately after the valve unit. It is also conceivable that the valve units are not flowed through at least approximately vertically.
  • the pump can have exactly one or more working spaces. It can be single-acting or double-acting.
  • the displacement device can also significantly simplify the maintenance of the in-line valve units by making the valve units accessible to a crane installation.
  • the two flanges, between which the inline valve unit is braced are preferably oriented at least approximately horizontally and, with particular preference, are arranged exactly above one another.
  • the inline valve unit is preferably no longer arranged between the flanges, but freely accessible from all sides.
  • the in-line valve unit may also be referred to as an in-line delivery valve unit.
  • the displacement pump is preferably a rinsing pump for drilling fluid or a so-called "slurry pump", ie a pump for transporting solids in liquid Slurry pumps are also referred to as thick matter pumps
  • the thick materials are mixtures of liquid and solid components
  • the pump generates a pressure of up to 300 bar and preferably has a capacity of up to 1500 m 3 / h
  • the power of the pump is preferably more than 500 kW In one embodiment, it is about 2400 kW and In another embodiment, about 5000 kW.
  • the pump unit is a flat membrane pump unit.
  • the displacement element thus preferably comprises a flat membrane.
  • the membrane is arranged vertically in its center position.
  • the membrane is not arranged vertically in its central position. This can be effected for example by a non-horizontal installation of the pump.
  • the displacer element is preferably actuated by a working fluid, which in turn is preferably pressurized by an oscillating piston of a drive unit.
  • the piston pressurizing the working fluid is completely separated from the fluid to be pumped by the diaphragm.
  • connection and / or spacer means preferably comprise threaded bolts, which more preferably pass through spacer sleeves.
  • connection and / or spacer means are preferably arranged such that different distances result between two adjacent connection and / or spacer means.
  • connection and / or spacer means are arranged such that the greatest distance between adjacent connection and / or spacer means is provided in the region of the movement path of the inline valve unit.
  • connecting and / or spacing means are arranged such that the largest distance (more precisely, the clear width) between two adjacent connecting and / or spacing means is only slightly larger than the outer dimensions - such as the diameter - of the inline Valve unit, then on the one hand a requirement for a compact pump unit is created. In addition, the bending load on the flanges caused by the distortion of the valve units is reduced, compared to an arrangement with adjacent connecting and / or spacing means of greater spacing. On the other hand, this continues to be a prerequisite for a displacement of the inline valve unit between two connecting and / or spacer means, without their disassembly, created.
  • the greatest distance (more precisely, the clear width) between two adjacent connecting and / or spacing means can be only less than thirty and in particular only less than ten percent of the outer dimensions of the in-line valve unit greater than this.
  • connecting and / or spacing means are provided, which are arranged in the form of a rectangle.
  • Another number of connecting and / or spacers is conceivable. In a conceivable alternative embodiment with equal distances between connection and / or spacer means, this is preferably slightly larger than the outer dimensions - such as the diameter - of the inline valve unit.
  • the in-line valve unit is displaceable by means of the valve displacement device on a movement path deviating from the circular path, even with such a small (largest) distance between adjacent connection and / or spacer means, a displacement of the inline valve unit from an operating position take place in a maintenance position by means of the valve displacement device, without disassembly of a connecting and / or spacer means is required.
  • a maintenance position can be achieved, which is characterized by a desirably large distance from the rest of the pump unit, without an elaborate, in turn much tree space-consuming displacement device would be required.
  • the in-line valve unit is displaceable without disengaging a screw connection on the pump unit-in one embodiment, except for the hydraulic tensioner. It must therefore preferably be solved for displacing the inline valve unit at most a screw of the hydraulic tensioning device.
  • the in-line valve unit is displaceable already after loosening a threaded element of the clamping device. To relocate the inline valve unit, so a threaded element of the clamping device - if necessary after hydraulic relief of the threaded element - and no threaded element of the remaining pump to be solved.
  • the inline valve unit after the release of a single threaded element, preferably a lock nut of the clamping device, displaced.
  • the maintenance of the in-line valve units is thereby facilitated and accelerated.
  • the valve displacement device comprises an articulated articulated arm.
  • the articulated arm is mounted on a connecting and / or spacer means. An arranged between the flanges, only the storage of the articulated arm on the other pump unit serving element can therefore, as preferred, omitted.
  • the articulated arm is also hinged to the inline valve unit.
  • the inline valve unit is at least partially displaceable on a translational movement path. In another embodiment, the in-line valve unit is displaceable exclusively on a translatory movement path.
  • the valve displacement device comprises a telescopic arm.
  • valve displacement device comprises lateral telescopic rails - preferably two per inline valve unit - there is a suitable, then drawer-like, displaceability of the valve unit.
  • the hydraulic tensioning device preferably adjoins one of the flanges.
  • the hydraulic tensioning device preferably adjoins the lower flange.
  • the hydraulic tensioning device is therefore preferably arranged between the lower flange and the inline valve unit.
  • the hydraulic tensioner is a stand-alone unit, which preferably is not fixedly connected to the pump unit, such as an adjacent flange, then it can be easily replaced or serviced (e.g., replacement of gaskets).
  • the hydraulic tensioning device is removable without tools in the relaxed state.
  • An alternative embodiment, in which the hydraulic tensioning device can not be removed without tools in the relaxed state, is conceivable in particular if the two flanges are not exactly one above the other, but are arranged obliquely one above the other or next to one another, for example. It can then be provided securing means which fix the hydraulic tensioning device against falling out. These securing means can be designed so that they can be solved only with tools.
  • the hydraulic tensioning device particularly preferably exactly - a hydraulic cylinder element.
  • the hydraulic cylinder element provides exactly one hydraulic cylinder in one embodiment. In one embodiment, exactly one pressure piston is provided.
  • the hydraulic tensioning device has exactly one annular piston in exactly one annular cylinder.
  • the hydraulic cylinder element preferably provides a plurality of cylindrical hydraulic cylinders. And with advantage, a plurality of single hydraulic piston is provided.
  • the single hydraulic piston can also be referred to as a pressure piston. Preferably, they are cylindrical.
  • the hydraulic tensioner is double-acting in one embodiment.
  • the hydraulic pistons can be pressurized selectively on two different sides of an effective surface and thereby moved in two directions.
  • the hydraulic tensioner is single acting and the individual pistons are each equipped with a piston return spring. It is conceivable that a plurality of counter-elements are provided to fix the hydraulic tensioning device in a tensioned state.
  • 1 shows an exemplary positive displacement pump with a drive unit and a pump unit
  • 2 shows a partially sectioned side view of a pump unit with upper inline valve unit in the operating position and lower inline valve unit in the maintenance position, the valve displacement device being designed as an articulated arm;
  • Fig. 3 is an enlarged detail of Fig. 2;
  • FIG. 4 is a perspective view of the pump unit shown in FIG. 2; FIG.
  • FIG. 5 shows a side view of the pump unit shown in FIG. 2, with the upper in-line valve unit in the maintenance position and the lower inline valve unit in the operating position;
  • Fig. 6 is an enlarged detail of Fig. 5;
  • Fig. 7 is a perspective view of the pump unit shown in Fig. 5;
  • FIG. 8 is a partially sectioned side view of a pump unit with telescopic arms.
  • Fig. 9 is an enlarged detail of Fig. 8.
  • FIG. 10 is a perspective view of the pump unit shown in FIG. 8; FIG.
  • Fig. 1 1 is a partially sectioned side view of a pump unit, wherein each valve displacement device comprises two telescopic rails;
  • Fig. 12 is a detail of Fig. 1 1;
  • Fig. 12a is a view as in Fig. 12, but on a smaller scale and fixed by the lock nut hydraulic cylinder element
  • FIG. 13 is a perspective view of the pump unit shown in FIG. 11; FIG.
  • FIG. 14 shows a partially sectioned side view of a pump unit, in which a plurality of valve units and a plurality of displacement devices are arranged on each pair of flanges;
  • Fig. 15 is a detail of Fig. 14;
  • FIG. 16 shows a perspective illustration of a pump unit in which a plurality of valve units and a plurality of displacement devices are provided on each pair of flanges, with an upper valve unit in the operating position and an upper valve unit in the maintenance position and both lower valve units in the maintenance position;
  • 17 is a sectional view of an in-line valve unit in the clamped state
  • Fig. 18 is a sectional view of an inline valve unit in the untensioned state.
  • Fig. 1 shows an exemplary positive displacement pump with a drive unit A and a pump unit 100.
  • the drive unit A comprises a drive shaft 15, which is rotated by a motor, not shown, for example, an electric motor in rotation.
  • On the drive shaft 15 at least one only indicated gear is arranged, which meshes with at least one much larger, also just indicated gear of the crankshaft 13.
  • the drive shaft 15 may protrude on both sides of the housing of the drive unit.
  • On the crankshaft a connecting rod 14 is arranged.
  • the connecting rod is mounted on the crankshaft with the help of a connecting rod bearing, which is designed as a rolling bearing.
  • the connecting rod transmits its movement by means of a crosshead 16 to a crosshead rod 17, which merges into the piston rod 18.
  • the crosshead bearing is also a rolling bearing.
  • the crosshead also includes sliding blocks, which serve its linear bearing on the Gleitlagerwandungen.
  • a working medium piston 19 is arranged, which carries out a rectilinear oscillating movement in a working medium cylinder 20.
  • a pump unit 100 is provided on the drive unit A.
  • This provides a work medium space adjoining the working medium cylinder 20, in which working medium 21, for example hydraulic oil, is provided, which transfers the movement of the working medium piston 19 to a flat membrane 24.
  • the flat membrane 24 is shown in Fig. 1 in its two extreme positions.
  • the flat membrane 24 forms together with a part of the diaphragm housing 26 has a working space 25. This is connected via check valves in inline valve units 1, V with a pressure tube and suction pipe, not shown in Fig. 1.
  • a rotational movement of the crankshaft causes the working medium in the working medium space to be moved back and forth, deflecting the flat membrane alternately to the right and left.
  • the deflection to the left in Fig. 1 leads to a closing of the outlet check valve or pressure valve and to a suction of fluid through the open inlet check valve or suction valve.
  • the subsequent displacement of the piston according to FIG. 1 to the right leads to a closing of the inlet check valve and a delivery of a displacement or displaced piston volume corresponding volume of fluid via the now open outlet check valve and the displacement of the membrane with respect to FIG to the right.
  • three connecting rods, working medium cylinders and pump units 100 can be arranged side by side. It can therefore be a triplex pump with three working spaces. It can also more or less - about exactly two - connecting rods, working medium cylinders and pump units are arranged side by side. Per working space 25, two inline valve units 1, 1 'are provided.
  • the inline valve units 1, 1 ' are traversed in a straight line by conveying medium.
  • the flow direction immediately before the valve thus corresponds at least approximately to the flow direction immediately after the valve.
  • a change of direction of the pumped medium does not take place in the area of these valves.
  • FIG. 2 shows that in the operating position each inline valve unit 1, 1 'is braced between two flanges 2, 2'. Two flanges 2, 2 'which are arranged parallel to one another and spaced from one another thus form a pair of flanges 2a, between which the inline valve unit 1, 1' is braced.
  • FIG. 2 also shows that a valve displacement device 3 fixedly connected to the rest of the pump is provided, with the aid of which each inline valve unit 1, 1 'is clamped from an operating position B, in which the inline valve unit 1 is braced between the flange pair 2 a Maintenance position W, in which the inline valve unit 1 'is not disposed between the pair of flanges, is displaced.
  • FIGS. 2 and 4 show that the flanges 2, 2 'are connected to one another in all exemplary embodiments shown by means of connecting and / or spacing means 4.
  • the connecting and / or spacing means 4 are designed in all embodiments shown as connecting and spacer means 4, which connect the flanges firmly together at a predetermined, fixed distance.
  • the connecting and spacing means 4 in all the exemplary embodiments shown have threaded bolts screwed to the flanges 2, 2 'by means of nuts. As a spacer they have between the flanges arranged spacers, which are penetrated by the threaded bolt.
  • FIG. 7 shows that four connecting and stopping means 4, which are arranged in the form of a rectangle, are provided per valve unit 1, 1 '. There are therefore two different distances K, L between adjacent connection and spacer means 4.
  • the Fig. It can also be seen that the connecting and spacer means 4 are arranged so that the larger the two distances L is perpendicular to the direction of displacement V of the inline valve unit 1, 1 'extends and is slightly larger than the outer dimensions M of the inline valve unit. 1
  • the greatest distance L between two adjacent connecting and spacing means 4 is thus provided in the region of the movement path of the inline valve unit 1, 1 ' .
  • the perpendicularly running smaller distance K between two adjacent connection and spacer means 4 may be smaller than the outer dimensions M of the inline valve unit 1 (FIG. 5).
  • the displacement direction V simultaneously symbolizes a movement path of an inline valve unit 1. This deviates from a circular path. It can, as shown in Fig. 7, at least in sections be rectilinear.
  • the valve displacement device 3 comprises a hinged articulated arm 5.
  • valve displacement device 3 comprises a telescopic arm 6.
  • valve displacement device 3 comprises two telescopic rails 7, 7 ' .
  • a plurality of inline valve units 1, 1 ' namely two inline valve units 1, 1' and a plurality of displacement devices 3, namely two displacement devices 3, are provided on each flange pair 2a.
  • the displacement device 3 comprises in This embodiment, as in the embodiment shown in FIGS. 2 to 7, an articulated arm. 5
  • the in-line valve units 1, 1 ' are each clamped exclusively by means of a hydraulic tensioning device 8 between the flanges 2, 2'.
  • Fig. 3 shows that the hydraulic tensioning device 8 forms a self-contained unit which is not fixedly connected to the pump unit 100, such as the adjacent lower flange 2. It is in the relaxed state without tools, so without the aid of tools, removable.
  • the hydraulic tensioner 8 has a hydraulic cylinder element 9 which is annular and in which a plurality of cylinder bores 9a are arranged.
  • Fig. 3 also shows that the flange 2, on which the hydraulic tensioning device 8 is arranged, has an annular projection 2b.
  • the outer diameter of the annular projection 2b is slightly smaller than the inner diameter of the annular hydraulic cylinder member 9, so that the hydraulic cylinder element 9 on the annular projection 2b of the flange 2 - guided by means of a linear sliding bearing - and at the same time centered.
  • each cylinder bore 9a a cylindrical single hydraulic piston 10 is arranged in each cylinder bore 9a.
  • Each single hydraulic piston 10 has a collar 23.
  • each cylinder bore 9a can be filled above the piston collar 23 with hydraulic fluid and pressurized.
  • the hydraulic cylinder element 9 lifts and thereby biases the in-line valve unit 1, 1 '.
  • the hydraulic cylinder element 9 is based on the hydraulic fluid to the single hydraulic piston 10, which in turn are supported on the flange 2.
  • This tensioned state of the hydraulic tensioning device 8 is shown for example in FIG.
  • the lock nut 12 can be screwed down so far, until it is also supported on the lower flange 2 (only shown in Fig. 12a).
  • the hydraulic cylinder element 9 is fixed in this way and the hydraulic system of the hydraulic tensioning device 8 can be relieved.
  • the in-line valve unit 1 is thus securely located between the pair of flanges 2 a and 2 b. stressed. Also, Fig. 17 shows this state, wherein the lock nut 12 is not screwed down in Fig. 17 yet.
  • the pressure fluid of the hydraulic tensioning device is first pressurized again. Then the lock nut 12 can be easily solved. If the pressure of the hydraulic fluid in the cylinder bores is then reduced, then a piston return spring 1 1 arranged between the collar 23 of the pistons 10 and a collar 22 of the hydraulic cylinder element 9 ensures that the pistons 10 are displaced into the hydraulic cylinder element 9, as shown in Fig. 18 is shown. In the unstressed state of the hydraulic tensioning device 8 shown there, the in-line valve unit 1 can be displaced. A return connection between the hydraulic cylinder element 9 and the adjacent to the hydraulic tensioning device 8 flange 2 is not present. It has been shown that it is expendable. The hydraulic tensioning device 8 has seals 28 for sealing against pumped liquid (FIG. 12). LIST OF REFERENCES:

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Jib Cranes (AREA)

Abstract

L'invention concerne une pompe volumétrique qui comporte une unité d'entraînement (A) et une unité de pompe (100) équipée d'au moins une unité de vanne en ligne (1, 1'), chaque unité de vanne en ligne (1, 1') étant précontrainte dans la position de fonctionnement (B) entre deux brides (2, 2'), et un moyen de déplacement de vanne (3) permettant de déplacer chaque unité de vanne en ligne (1, 1') d'une position de fonctionnement (B) dans une position d'entretien (W), l'unité de vanne en ligne (1, 1') pouvant être déplacée sur une trajectoire autre qu'une trajectoire circulaire.
EP14736732.0A 2013-08-09 2014-07-02 Pompe volumétrique Active EP3030784B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013108672.1A DE102013108672A1 (de) 2013-08-09 2013-08-09 Verdrängerpumpe
PCT/EP2014/064070 WO2015018570A1 (fr) 2013-08-09 2014-07-02 Pompe volumétrique

Publications (2)

Publication Number Publication Date
EP3030784A1 true EP3030784A1 (fr) 2016-06-15
EP3030784B1 EP3030784B1 (fr) 2019-09-04

Family

ID=51162763

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14736732.0A Active EP3030784B1 (fr) 2013-08-09 2014-07-02 Pompe volumétrique

Country Status (6)

Country Link
US (1) US10190583B2 (fr)
EP (1) EP3030784B1 (fr)
CN (1) CN105658961B (fr)
AU (1) AU2014304881B2 (fr)
DE (1) DE102013108672A1 (fr)
WO (1) WO2015018570A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018091306A1 (fr) 2016-11-15 2018-05-24 Mhwirth Gmbh Procédé permettant de faire fonctionner une pompe à piston et pompe à piston
US11221004B2 (en) * 2017-07-12 2022-01-11 Blue-White Industries, Ltd. Multiple diaphragm pump

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1528456A1 (de) 1966-01-12 1970-09-03 Busse Dipl Ing Oswald Ventilanordnung und -Ausbildung fuer Verdraengerpumpe
US4491345A (en) * 1981-08-06 1985-01-01 Hughes Tool Company Marine conductor coupling
US4471799A (en) * 1982-01-11 1984-09-18 Grove Valve And Regulator Company Line removable ball valve
DE3430721A1 (de) * 1984-08-21 1986-03-06 Alldos Eichler Kg, 7507 Pfinztal Membranpumpe, insbesondere zum dosieren von fluessigkeiten
US6988626B2 (en) * 1998-07-31 2006-01-24 Varghese Paily T Computer component rack mounting arrangement
US20030032506A1 (en) * 2001-08-07 2003-02-13 Tien-Sheng Chi Elevation-adjustable baseball batting-training apparatus
DE102011001087A1 (de) * 2011-03-04 2012-09-06 Feluwa Pumpen Gmbh Doppel-Schlauchmembran-Prozeßpumpe
AR086188A1 (es) * 2011-04-20 2013-11-27 Spm Flow Control Inc Una bomba alternativa
BR112014007364B1 (pt) 2011-09-30 2021-09-28 Aker Wirth Gmbh Bomba de deslocamento positivo projetada como uma bomba de diafragma de pistão
CN202690386U (zh) 2012-07-23 2013-01-23 上海绩优机电设备有限公司 一种隔膜泵

Also Published As

Publication number Publication date
AU2014304881B2 (en) 2018-05-10
US10190583B2 (en) 2019-01-29
CN105658961B (zh) 2017-11-21
US20160177946A1 (en) 2016-06-23
WO2015018570A1 (fr) 2015-02-12
EP3030784B1 (fr) 2019-09-04
AU2014304881A1 (en) 2016-03-03
DE102013108672A1 (de) 2015-02-12
CN105658961A (zh) 2016-06-08

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