EP2761180A2 - Pompe volumétrique et procédé d'exploitation de ladite pompe volumétrique - Google Patents

Pompe volumétrique et procédé d'exploitation de ladite pompe volumétrique

Info

Publication number
EP2761180A2
EP2761180A2 EP12770085.4A EP12770085A EP2761180A2 EP 2761180 A2 EP2761180 A2 EP 2761180A2 EP 12770085 A EP12770085 A EP 12770085A EP 2761180 A2 EP2761180 A2 EP 2761180A2
Authority
EP
European Patent Office
Prior art keywords
pump
diaphragm
membrane
piston
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.)
Granted
Application number
EP12770085.4A
Other languages
German (de)
English (en)
Other versions
EP2761180B1 (fr
Inventor
Alfred GIESSBACH
Norbert Jaeger
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
Aker Wirth 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
Priority claimed from DE102011054074A external-priority patent/DE102011054074A1/de
Priority claimed from DE102011054073A external-priority patent/DE102011054073A1/de
Application filed by Aker Wirth GmbH filed Critical Aker Wirth GmbH
Publication of EP2761180A2 publication Critical patent/EP2761180A2/fr
Application granted granted Critical
Publication of EP2761180B1 publication Critical patent/EP2761180B1/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
    • 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
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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
    • F04B9/1095—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 having two or more pumping chambers in series

Definitions

  • the invention relates to a positive displacement pump with a drive unit and a pump unit and an operating method thereof.
  • the pump unit has a plurality of working spaces, a plurality of displacement elements and often at least three cylinders.
  • Such positive displacement pumps are already known.
  • FIGS. 1 and 2 show such a positive displacement pump manufactured by Aker Wirth GmbH.
  • Such positive displacement pumps are used as flushing pumps for drilling fluid and as so-called "slurry pumps", ie for the transport of solids in liquid, which are also referred to as "thick matter pumps.” Thick substances are mixtures of liquid and solid components Pressure of up to 500 bar, they have a capacity of up to 300 l per minute and often outputs of more than 700 kW.
  • the object of the invention is to provide such an improved life pump as well as an operating method for such a pump, while at the same time maintaining or expanding the advantages of such a pump having at least three cylinders.
  • the displacement pump according to the invention has a drive unit and a pump unit.
  • the pump unit comprises a plurality of working spaces and a plurality of displacement elements.
  • the pump unit comprises at least three cylinders. It is double-acting, so two working spaces are provided per cylinder. Overall, therefore, at least six workrooms are provided.
  • the pump is therefore a triplex pump, (also called triple pump), which acts twice.
  • the advantages of a triplex pump are thus combined with the advantages of a double-acting pump.
  • the three-cylinder positive displacement pump (triplex) shown in FIGS. 1 and 2 is single-acting.
  • their displacement elements diaphragms
  • a displacement stroke ie they move from left to right (with reference to FIG. 1).
  • a suction stroke the membranes thus move from right to left (based on Fig. 1), which means no or only a small load on the pump.
  • the displacement elements are membranes. These are further preferably actuated by means of pistons.
  • the positive displacement pump according to the invention is thus a piston diaphragm pump.
  • the medium to be pumped is separated from the drive by the membrane. By this separation membrane thus the drive is shielded from harmful influences of the pumped medium.
  • the fluid is separated from harmful influences of the drive.
  • the transfer the oscillating movement of the piston on the membranes is preferably done by means of a working medium or transmission medium.
  • the working medium can be water with a water-soluble mineral additive or hydraulic oil. Due to the constant volume of the working medium between the piston and diaphragm, the movement of the piston directly causes a deflection of the diaphragm and thus causes suction and pressure pulses.
  • exactly one piston is provided in each cylinder.
  • the pump is preferably a slurry pump. It pumps mixtures of liquid and solid components. This may be mud in earthworks or the like.
  • Such piston diaphragm pumps are designed for continuous use and must work reliably over long periods, up to years, as trouble-free as replacement of a defective piston diaphragm pump due to their size is regularly associated with a considerable amount of work and time.
  • diaphragm damage can have particularly serious consequences for these piston diaphragm pumps. For one thing occurs when a membrane damage, the working fluid in the diaphragm chamber or the working space and mixes with the pumped liquid, which requires time-consuming cleaning. On the other hand, fluid enters the working fluid, which contaminates the entire pump and the drive piston can be damaged.
  • Such piston diaphragm pumps are known by the company Aker Wirth GmbH, Erlen, Germany under the designations "DPM” and “TPM”. They are designed as duplex pumps with two double-acting pistons or as triplex pumps with three single-acting pistons.
  • the cylinders are always arranged horizontally, so that the pistons perform their oscillating movement along a horizontal axis.
  • the connected via the working fluid with the displacement of the respective associated cylinder on the working fluid membranes are always arranged vertically.
  • vertical arrangement is meant that the plane of action defined by the membrane extends vertically and is defined by a diaphragm clamped in the membrane housing in the case of a membrane which is flat in the undeflected state.
  • the inlet is regularly at the bottom, the outlet at the top, as this can escape through the membrane chamber located air upwards.
  • the drive unit is preferably provided in such a way as is used in a conventional single-acting triplex pump.
  • a drive shaft is provided, which is driven by a motor, not shown, and transmits its torque by means of meshing gears on a crankshaft, are arranged on the connecting rod.
  • All connecting rods are arranged on a single crankshaft and act in the same direction. They transfer their movement via a crosshead, that is to say, to crosshead bars which run parallel to one another and are arranged relatively close to each other. These interact with piston rods.
  • the cylinders are at a small distance parallel to each other. It is thus resorted to a drive unit, which is proven and compact builds. In addition to the saving of development costs of recourse to proven elements is of particular importance here, since it depends in the typical fields of application of the positive displacement pump according to the invention to a high degree of reliability.
  • the cylinders are preferably lying, so arranged horizontally.
  • the speed of the positive displacement pump according to the invention compared to a common single-acting triplex pump is reduced.
  • This can be achieved for example by a slower running of the drive motor.
  • This measure can be made due to the principle higher delivery capacity of the double-acting pump unit, compared with a common single-acting triplex pump constant flow.
  • the size of the piston surfaces is reduced compared to a common single-acting triplex pump. Since the pump unit is double-acting, it conveys twice the volumetric flow of pumped medium, with the same volume and speed, as a single acting pump unit. In order to obtain a comparable volume flow, as in a single-acting, conventional triplex pump, can therefore alternatively or additionally To reduce the speed of the stroke volume can be reduced by means of a cross-sectional reduction of the piston surfaces. As a result, a reduction of the rod force (piston rod, or crosshead rod, or connecting rod) is achieved.
  • the membranes are rotated with respect to the vertical by an angle of 1 ° to 90 °.
  • the membranes are thus, unlike a common single-acting triplex pump, not vertical.
  • the position of the membranes refers to their neutral center position.
  • the membranes are arranged higher than the cylinders.
  • the diaphragms are thus "folded" upwards compared to a conventional single-acting triplex pump
  • the pump preferably has a power of at least 700 kW.
  • the invention also relates to a pump unit of a pump according to the invention.
  • the invention is also based on the object of providing an operating method for a piston-diaphragm pump and a piston-diaphragm pump operating according to this method of operation, whose service life is increased with the same delivery rate as in the prior art or its delivery rate with a constant service life regardless of whether it is a single- or double-acting pump and regardless of the number of cylinders.
  • This object is achieved by the reproduced in claim 1 operating method and by the recited in claim 4 piston diaphragm pump.
  • the membrane stroke is effected at a membrane position which is different from a vertical position of the membrane.
  • the duration of the membrane can be significantly increased by this technically simple measure.
  • This surprising effect may be due to the fact that in the operating method according to the prior art, in which the membrane is oriented vertically, air inclusions accumulate, for example, near the inlet in the lower region of the membrane, whereby this unbalanced especially in the thrust deflection which can lead to an acceleration of the aging or fatigue of the membrane material, in particular close to the clamped edges.
  • the membranes are deflected in the prior art piston diaphragm pumps regularly only up to seventy percent of the maximum diaphragm stroke. It has surprisingly been found that it is possible with the operating method according to the invention while maintaining the expected membrane life, to increase the stroke to up to ninety percent of the maximum deflection, thereby increasing the flow rate of the piston diaphragm pump, without this being further, requires complex technical measures. A particularly long life extension or performance increase can be achieved if - as preferred - the membrane stroke is effected at a different position of the vertical by 45 ° to 90 ° membrane position.
  • the inclination of the diaphragm stroke from the vertical about 70 °, since in otherwise usual dimensions and configurations of a piston diaphragm pump possibly located in the working fluid gas - usually air - collects at the highest edge region of the membrane and can be easily drained by a vent valve located at this point.
  • the piston-diaphragm pump according to the invention is characterized in that the membrane is arranged at a position different from a vertical position, in particular by 45 ° to 90 °, especially by approximately 70 °.
  • the piston diaphragm pump according to the invention is - as usual for the promotion of sludge in earthworks piston diaphragm pumps - arranged such that the (or in multiple pumps) cylinder with its (their) longitudinal axis (s) is arranged approximately horizontally (are). So it can drive and piston / cylinder units as used in the prior art.
  • the working volume is partially formed by a channel extending obliquely upwardly from the cylinder.
  • the channel is approximately straight and provided on the channel housing forming a channel approximately perpendicular to the longitudinal axis of the channel aligned flange on which a diaphragm receiving membrane housing is attached.
  • the membrane and membrane housing in turn, the same components can be used as in the prior art, so that a significant improvement of a piston diaphragm pump is achieved by means of the invention, without this being associated with design-related additional costs.
  • the membrane is preferably approximately circular in shape and has an edge which is inserted in the membrane housing approximately in one plane. is biased, wherein the plane is arranged in a vertical position preferably by 45 ° to 90 °, more preferably at such an angle different position, so that the highest point of the working volume is formed at a lateral edge region.
  • a provided in a state of the art piston-diaphragm pump provided, approximately vertically upwardly facing vent valve can then continue to use for venting the working volume.
  • Figure 1 is a cross-sectional view of a known from the prior art common triple-acting triplex pump.
  • Fig. 2 is a plan view of the pump shown in Fig. 1;
  • Fig. 3 is a perspective view of a known from the prior art double-acting duplex pump; 4 shows a view as in FIG. 3, from a different viewing direction;
  • FIG. 5 shows a side view of a pump unit according to the invention
  • FIG. 6 shows a view of the drive unit on a pump unit according to the invention
  • FIG. 7 is a cross-sectional view of the pump unit according to the invention.
  • FIG. 8 is a top view of the pump unit according to the invention.
  • FIG. 9 is a perspective view of the pump unit according to the invention.
  • Fig. 1 1 is a top view of the positive displacement pump according to the invention
  • FIG. 12 is a perspective view of the positive displacement pump according to the invention.
  • Fig. 13 is a cross-sectional view of the positive displacement pump according to the invention on a larger scale;
  • Fig. 14 is an enlarged view of Fig. 4;
  • the known single-acting triplex pump known from the prior art shown in FIG. 1 has a drive unit 1 and a pump unit 2.
  • the drive unit 1 comprises a drive shaft 19, which is rotated by a motor, not shown, for example, an electric motor in rotation.
  • On the drive shaft 19 at least one only indicated gear is arranged, which meshes with at least one much larger, merely indicated toothed wheel of the crankshaft 18.
  • the drive shaft 19 protrudes from the housing of the drive unit on both sides (FIG. 2).
  • On the crankshaft three connecting rods 18a are arranged relatively close together.
  • the connecting rods are mounted on the crankshaft with the help of a connecting rod bearing, which is designed as a roller bearing.
  • the connecting rods transmit their movement in each case by means of a crosshead 20 to a crosshead rod 21, which merges into a piston rod 9.
  • the crosshead bearing is also a rolling bearing.
  • the crosshead also includes sliding blocks, which serve its linear bearing on the Gleitlagerwandungen.
  • a piston 7 is arranged, which performs a rectilinear reciprocating movement in a cylinder 5.
  • a pump unit 2 On the drive unit 1, a pump unit 2 is provided. This provides a work medium space 23 adjacent to each cylinder 5, in which working medium 22, for example hydraulic oil, is provided, which transmits the movement of the piston 7 to the membrane 6.
  • working medium 22 for example hydraulic oil
  • the positives correspond to Ones of the piston 7 and the membrane 6 to each other not the usual operation.
  • the membrane 6 In normal operation, the membrane 6 is not shown in the extreme right position of the piston 7 shown in the left extreme position shown, but arranged in the right extreme position, not shown.
  • the membrane 6 together with a part of the membrane housing 6a forms a working space 4. This is connected via check valves 13 to a pressure pipe 17 and a suction pipe (not shown in FIG. 1).
  • the suction pipe is disposed below the Saugventilgebliuses 15 and connected thereto.
  • a rotational movement of the crankshaft 18 causes working fluid 22 to be moved back and forth in the working fluid space 23, deflecting the diaphragm 6, 6 ' alternately to the right and left.
  • a deflection to the left leads to a closing of the outlet check valve or pressure valve in the pressure valve housing 14 and to a suction of fluid through the open inlet check valve or suction valve in the Saugventilgephaseuse 15.
  • the subsequent displacement of the piston of 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 delivery volume through the now open outlet check valve with displacement of the diaphragm with respect to FIG. 1 to the right.
  • Figures 3 and 4 show a known from the prior art duplex pump, ie a pump with two connecting rods, piston rods, pistons and cylinders. This is double acting. It has four membrane housing 6a, 6a 'and is used in particular for larger volume flows.
  • FIGS. 5 to 9 show the pump unit 2 of a positive-displacement pump according to the invention.
  • This is a piston diaphragm pump.
  • the displacement elements 3, 3 ' are therefore membranes 6, 6 ' .
  • the illustrated embodiment of the pump according to the invention is designated as a whole by 100 (FIGS. 10 to 13). It can be seen that the illustrated pump 100 according to the invention is a triplet pump or triplex pump. So there are three connecting rods 18 a present, which cooperate with three moving in three cylinders 5 piston 7.
  • the drive unit 1 of the pump according to the invention shown substantially coincides with the drive unit 1 of the known from the prior art single-acting triplex pump ( Figures 1 and 2).
  • the technical data of the single-acting triplex pump shown in FIGS. 1 and 2 can be as follows: piston diameter: 310 mm, piston stroke: 508 mm, volume flow (design normal) 351 m 3 / h, maximum flow rate 385 m 3 / h, theoretical delivery per crankshaft revolution: 1 15.0 I, volumetric efficiency: 0.94, normal Working speed: 54.1 min "1, maximum stroke rate: 59.3 min" 1, normal pressure: 80 0 bar, maximum delivery pressure: 96.0 bar, internal gear ratio: 3.8077, piston rod load at normal delivery pressure: 604 kN, piston rod load at maximum delivery pressure: 725 kN, bearing life when operating at maximum load: 69,100 h, bearing life in normal operation: 126,800 h, displaced piston volume: 38.3 l, required membrane type in liters: 60 l.
  • the technical data of the illustrated embodiment of the positive displacement pump according to the invention are as follows: piston diameter: 275 mm, piston stroke: 508 mm, volume flow (design normal) 351 m 3 / h, maximum volume flow 385 m 3 / h, theoretical flow rate per crankshaft rotation: 173.4 I, volumetric efficiency: 0.94, normal number of strokes: 35.9 min "1 , maximum stroke rate: 39.4 min " 1 , normal delivery pressure: 80.0 bar, maximum delivery pressure: 96.0 bar, transmission ratio of the internal gears (Internal gear ratio): 3.8077, piston rod load at normal delivery pressure: 475 kN, piston rod load at maximum delivery pressure: 570 kN, bearing life when operating at maximum load: 445,700 h, bearing life in normal operation: 810,500 h, displaced piston volume Front: 30.2 l, displaced piston volume Backside: 27.6 l, required membrane type in liters: 47 l.
  • the single-acting triplex pump shown in FIGS. 1 and 2 requires three membranes whose size is designed for 60 l, the operating hours of the membrane are set at 3,000, the number of membrane changes per year (8,000 h) is 2 , 67th
  • the positive displacement pump according to the invention shown requires six membranes whose size is designed for 47 I, the operating hours are set at 4,500, it is expected up to 8,000 operating hours in the event of possible rewinding of the membranes, the number of membrane changes per year is 1, 78, or the number of expected membrane changes per year is 1.
  • the single-acting triplex pump shown in FIG. 1 requires six valves of size API 13, with 1 .200 operating hours.
  • the average velocity of the valves is 1.72 and the number of valve changes per year (8.000 h) is 6.67.
  • the illustrated embodiment of the positive displacement pump 12 of the invention requires valves, also of size API 13, with 1, 800 operating hours.
  • the average velocity is 1.29
  • the expected operating hours are 2.160 due to the reduced velocity (velocitiy)
  • the valve changes per year are 4.44 and the expected valve changes per year are 3.7.
  • Fig. 13 also shows that the membranes 6, 6 'are not perpendicular, but are inclined from the vertical S by an angle ⁇ .
  • the angle ⁇ can be between 1 ° and 90 °, in particular 60 ° and 80 °. In the illustrated embodiment, it is about 70 °.
  • the working medium space 23, 23 ' is cylindrically shaped in its region adjacent to the membrane housing 6a, 6a'.
  • the cylinder axis is perpendicular to the diaphragm (in its neutral position).
  • the cylindrical region of the working medium space 23, 23 ' is thus inclined by an angle ß from the vertical. This angle can be 0 ° to 89 °. In the illustrated embodiment, it is about 20 °.
  • the angles ⁇ and ⁇ are always 90 °.
  • piston diaphragm pump 200 as shown in Fig. 14 can be seen - again designed as a three-piston diaphragm pump.
  • Fig. 15 shows a longitudinal section through the central pump part. The two other pump parts are designed accordingly.
  • the illustrated piston-diaphragm pump 200 comprises a motor-driven crankshaft 10, on the middle crank pin 102 of which a connecting rod 103 is mounted with the aid of a connecting rod bearing 104.
  • a crosshead 105 is mounted via a crosshead bearing 106.
  • the crosshead 105 includes sliding blocks 107, which serve its linear bearing on Gleitlagerwandungen 108.
  • a piston rod 109 is attached at one end.
  • the other end of the piston rod 109 carries a piston 1 10, which is designed as a double-acting piston and in a cylinder 1 1 1 operates.
  • Fig. 2 the right dead center is shown.
  • the cylinder 1 1 1 is arranged within a working volume, which is divided by the piston 1 10 in two working part volumes 1 1 2a, 1 12b.
  • the right in Fig. 2 end of the working part volume 1 12b is closed by means of a cover 1 13.
  • a lid 1 14 is also attached, which is, however, provided with a central opening 1 15 for the passage of the piston rod 109.
  • a seal assembly 1 16 is provided, which seals the piston rod 109 against the lid 1 14 against leakage of working fluid from the working part volume 1 12.
  • the working fluid not shown in the drawing - usually called hydraulic oil, so oil template - fills the working volume 1 12a, 1 12b up to two membranes 1 17a, 1 17b, in Fig. 15 (with respect to the dead center position of the piston 1 10 incorrectly ) are shown in their central position.
  • oil template - fills the working volume 1 12a, 1 12b up to two membranes 1 17a, 1 17b, in Fig. 15 (with respect to the dead center position of the piston 1 10 incorrectly ) are shown in their central position.
  • the diaphragm shown on the left would be bent downwards, the diaphragm 11b accordingly upward, as shown qualitatively in dashed lines in FIG.
  • the membranes 1 17a, 1 17b are arranged in membrane housings 1 18a, 1 18b and separate diaphragm chambers 1 19a, 1 19b from the oil reservoir located in the working volume 1 12a, 12b.
  • the membrane housing 1 18a, 1 18b are attached to flanges 120a, 120b of channel housings 121 a, 121 b.
  • the channel housing 121 a, 121 b include channels 122 a, 122 b, which form parts of the working volume 1 12 a, 1 12 b.
  • the two channel housings 121 a, 121 b which are essentially straight, each form an angle of approximately 20 ° to the perpendicular, such that the distance of the two channel housings 121 a, 121 b increases towards the top.
  • the membrane housings 1 18a, 1 18b in which the membranes 1 17a, 17b are clamped with their respective edge regions 123a, 123b, are fastened to the flanges 120a, 120b in such a way that the membranes 17a, 17b extend in their planar center position perpendicular to the longitudinal axis of the respective channel 122a, 122b.
  • the two membranes 1 17a, 1 17b thus arranged inclined by about 70 ° from the vertical.
  • Each diaphragm chamber comprises an inlet 124a, 124b, to each of which an inlet check valve 125a, 125b (see Fig. 14) is flanged.
  • the membrane chambers 1, 19a, 1, 19b comprise outlets 126a, 126b, to each of which an outlet check valve 127a, 127b is flanged.
  • a rotational actuation of the crankshaft 101 causes the working fluid in the working fluid volume 1 12a, 1 12b and the membranes 1 17a, 17b to be moved back and forth between the extreme deflections shown in dashed lines.
  • a deflection in each case leads down to a suction of sludge through the respective open inlet check valve.
  • This pumping phase is referred to as a suction cycle.
  • the subsequent displacement of the piston leads to a closing of the previously opened inlet check valve and a discharge of the volume corresponding volume of sludge via the now open outlet check valve with displacement of the membrane in the upwardly curved, shown in dashed lines in Fig. 15 extreme position.
  • 112a, 112b work part volumes, together work volume
  • 121a, 121b channel housing

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

Abstract

L'invention concerne une pompe volumétrique (100) comprenant une unité d'entraînement (1) et une unité de pompe (2), dotée de plusieurs espaces de travail (4, 4'), de plusieurs éléments de refoulement (3, 3'), avec au moins trois cylindres (5), de préférence exactement trois cylindres (5), l'unité de pompe (2) étant à double effet et étant une pompe à piston et diaphragme formant une pompe volumétrique, dans laquelle une course de diaphragme est produite au moyen de liquide de travail sur la première face d'un diaphragme et, par suite de la course du diaphragme, un fluide à transporter est acheminé à travers une chambre à diaphragme limitée par la deuxième face du diaphragme, la course du diaphragme étant produite pour une position du diaphragme différente de la position verticale.
EP12770085.4A 2011-09-30 2012-09-28 Pompe volumétrique Active EP2761180B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102011054074A DE102011054074A1 (de) 2011-09-30 2011-09-30 Verdrängerpumpe
DE102011054073A DE102011054073A1 (de) 2011-09-30 2011-09-30 Betriebsverfahren einer Kolben-Membranpumpe sowie Kolben-Membranpumpe
PCT/EP2012/069160 WO2013045598A2 (fr) 2011-09-30 2012-09-28 Pompe volumétrique et procédé d'exploitation de ladite pompe volumétrique

Publications (2)

Publication Number Publication Date
EP2761180A2 true EP2761180A2 (fr) 2014-08-06
EP2761180B1 EP2761180B1 (fr) 2018-11-21

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP12770085.4A Active EP2761180B1 (fr) 2011-09-30 2012-09-28 Pompe volumétrique

Country Status (9)

Country Link
US (1) US9695808B2 (fr)
EP (1) EP2761180B1 (fr)
AU (2) AU2012314408B2 (fr)
BR (1) BR112014007364B1 (fr)
CA (1) CA2861136C (fr)
CL (1) CL2014000755A1 (fr)
IN (1) IN2014CN03132A (fr)
PE (1) PE20141978A1 (fr)
WO (1) WO2013045598A2 (fr)

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Also Published As

Publication number Publication date
US9695808B2 (en) 2017-07-04
WO2013045598A3 (fr) 2013-05-30
AU2016203015B2 (en) 2018-06-14
BR112014007364A2 (pt) 2017-04-04
CL2014000755A1 (es) 2014-07-25
CA2861136C (fr) 2018-04-24
US20140248160A1 (en) 2014-09-04
AU2016203015A1 (en) 2016-06-02
AU2012314408A1 (en) 2014-05-08
IN2014CN03132A (fr) 2015-07-03
PE20141978A1 (es) 2014-12-18
WO2013045598A2 (fr) 2013-04-04
BR112014007364B1 (pt) 2021-09-28
EP2761180B1 (fr) 2018-11-21
CA2861136A1 (fr) 2013-04-04
AU2012314408B2 (en) 2016-05-26

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