EP2761180B1 - Positive displacement pump - Google Patents
Positive displacement pump Download PDFInfo
- Publication number
- EP2761180B1 EP2761180B1 EP12770085.4A EP12770085A EP2761180B1 EP 2761180 B1 EP2761180 B1 EP 2761180B1 EP 12770085 A EP12770085 A EP 12770085A EP 2761180 B1 EP2761180 B1 EP 2761180B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- diaphragm
- piston
- pump
- membrane
- channel
- 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
Links
Images
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.
- the EP 0 484 575 A1 shows a pump with a membrane in which the defined by the membrane active plane, which in turn is defined by the clamped in the diaphragm housing edge, extending vertically.
- the DE 12 54 968 B shows a pump that has no membrane.
- WO 2010/098707 A1 and US 4 188 170 A disclose pumps in which the cylinder and the diaphragm always lie in line and are not spaced by a channel extending obliquely to the cylinder.
- the US 4,427,350 A discloses a pump in which the membrane is moved by a heating and cooling process and no cylinder with a piston whose movement is transferable to the membrane, is provided.
- the US 4,008,009 shows a pump in which openings are integrated into the diaphragm housing and no extending from the cylinder channel to the flange of which the diaphragm receiving diaphragm housing is attached, is provided.
- the DE 28 55 167 A1 shows a pump with a displacer, which acts without a channel extending obliquely to a cylinder on a membrane and in which no working volume is provided, which is partially formed by a diagonally from the horizontal cylinder Vietnameserteckenden channel.
- the DE 10 61 186 which shows a pump according to the preamble of claim 1.
- the working volume is not partially formed by an obliquely extending from the horizontal cylinder upwardly extending channel, at the flange of which the membrane receiving membrane housing is attached. This document does not show a flanged diaphragm housing and no obliquely upwardly extending from the cylinder channel.
- the invention has set itself the task of creating such a pump with improved life.
- the diaphragm is arranged at a position different from a vertical position, in particular by 45 ° to 90 °, very particularly by approximately 70 °.
- the piston diaphragm pump according to the invention is - as usual for the promotion of sludge in excavation planned piston diaphragm pump - arranged such that the (or in multiple pumps the) cylinder with its (their) longitudinal axis (s) is arranged horizontally (are). So it can drive and piston /
- the working volume is partially formed by a channel extending obliquely upwardly from the cylinder.
- the channel is straight and formed on the channel housing forming the channel is a perpendicular to the longitudinal axis of the channel aligned flange, on which a membrane receiving membrane housing is attached.
- the membrane is preferably formed approximately circular and has an edge which is clamped in the diaphragm housing approximately in a plane, wherein the plane in a vertical position preferably by 45 ° to 90 °, more preferably arranged at such an angle location is, so that the highest point of the working volume is formed at a lateral edge region.
- the drive unit 1 comprises a drive shaft 19, which is rotated by a motor, not shown, for example, an electric motor in rotation.
- 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 gear of the crankshaft 18.
- the drive shaft 19 is made on both sides the housing of the drive unit ( 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
- Fig. 1 The positions of the piston 7 and the diaphragm 6 to each other do not correspond to the ordinary 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 forms together with a part of the diaphragm housing 6a a working space 4. This is about check valves 13 with a pressure tube 17 and a in Fig. 1 Not shown suction pipe connected.
- 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 Auslass Wegtschsventilsils 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 Saugventilgephase 15.
- 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 the displacement or displaced piston volume corresponding volume of delivery volume via the now open outlet check valve with displacement of the membrane based Fig. 1 to the right.
- FIGS. 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 illustrated pump according to the invention is substantially identical to the drive unit 1 of the single-acting triplex pump known from the prior art (US Pat. Figures 1 and 2 ) match.
- FIGS. 1 and 13 show, assume the previous piston 7 and the previous cylinder 5 ( Fig. 1 ) now at least also management tasks.
- On the previous piston is right (based on Fig. 1 ) arranged an extension of the piston rod 9, to which now the piston 7 is fixed.
- the piston 7 separates the cylinder 5 in a region which is connected to a working medium space 23 inclined to the drive unit and a region which communicates with a working medium space 23 'inclined away from the drive unit.
- In the working medium spaces 23, 23 'working or transmission medium 22, 22' is arranged, which may be, for example, hydraulic oil.
- the left surface 10 'of the piston displaces the working medium 22 arranged in the left working medium space 23, which leads to an upward pushing of the left diaphragm 6'. Both in his right movement, as well as in his left movement of the piston 7 thus causes an admission of one of the two membranes 6, 6 'with pressure.
- Fig. 7 shows, the working spaces 4, 4 'in each case via a pressure valve in a pressure valve housing 14, 14' connected to a pressure pipe 17, 17 'and a suction valve in a Saugventilgephaseuse 15 with a suction pipe 16.
- Fig. 9 shows that per membrane 6 exactly one suction valve and exactly one pressure valve are provided. The suction valves act on a single suction pipe 16, while the pressure valves on two pressure pipes 17, 17 'distribute.
- 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 l, 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, 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 Rear: 27.6 l, required membrane type in liters: 47 I.
- FIGS. 1 and 2 The single-acting triplex pump shown requires three diaphragms with a size of 60 l, the operating hours of the membrane are set at 3,000, and the number of membrane changes per year (8,000 h) is 2.67.
- the positive displacement pump according to the invention shown requires six membranes, whose size is designed for 47 l, the operating hours are set at 4,500, it is expected up to 8,000 operating hours with a possible new development 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 in Fig. 1 Single-acting triplex pump shown requires six API 13 valves, 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.
- valves also the 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 speed (velocitiy)
- the valve changes per year are 4.44 and the expected valve changes per year are 3.7.
- FIG Fig. 1 Reduced piston rod load by more than 20%, reduced crankshaft load due to double action, 33% reduction in piston speed, extended service life of bearings and all pump drive unit components, up to full 30 years of service life, less wear and tear and increased pump unit life by at least 25%, at least twice the diaphragm life, higher pump efficiency, a potentially higher volumetric flow rate with lower piston rod loading, lower maintenance costs due to fewer maintenance cycles per year, less production downtime and reduced holding head (NPSHr) of the pump.
- NPSHr reduced holding head
- Fig. 13 also shows that the membranes 6, 6 'are not vertical, 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 formed cylindrically 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 ⁇ from the vertical.
- This angle can be 0 ° to 89 °. In the illustrated embodiment, it is about 20 °.
- the angles ⁇ and ⁇ are combined for symmetry reasons always 90 °.
- Fig. 14 and 15 as a whole with 200 designated piston diaphragm pump is - as in Fig. 14 can be seen - again designed as a three-piston diaphragm pump.
- Fig. 15 shows a longitudinal section through the middle 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 110, which is designed as a double-acting piston and operates in a cylinder 111.
- a piston 110 which is designed as a double-acting piston and operates in a cylinder 111.
- Fig. 2 the right dead center is shown.
- the cylinder 111 is arranged within a working volume, which is divided by the piston 110 into two working sub-volumes 112a, 112b. This in Fig. 2 right end of the working part volume 112b is closed by means of a cover 113. At the left end of the working volume 12a, a lid 114 is also attached, which is, however, provided with a central opening 115 for the passage of the piston rod 109. On the cover 114, a seal assembly 116 is provided, which seals the piston rod 109 against the lid 114 against leakage of working fluid from the working part volume 112.
- the working fluid not shown in the drawing - usually hydraulic oil, therefore also called oil reservoir - fills the working volume 112a, 112b up to two membranes 117a, 117b, the in Fig. 15 (in terms of the dead center position of the piston 110 incorrectly) are shown in its central position.
- the diaphragm shown at the left would be deflected downwards, the diaphragm 117b accordingly upward, as qualitatively in FIG Fig. 15 indicated by dashed lines.
- the diaphragms 117a, 117b are disposed in diaphragm housings 118a, 118b and separate diaphragm chambers 119a, 119b from the oil reservoir located in the working volume 112a, 112b.
- the diaphragm housings 118a, 118b are fixed to flanges 120a, 120b of duct housings 121a, 121b.
- the channel housings 121a, 121b include channels 122a, 122b which form parts of the working volume 112a, 112b.
- the two channel housings 121a, 121b which are substantially straight, each form an angle of approximately 20 ° to the vertical, such that the distance between the two channel housings 121a, 121b increases in the upward direction.
- the membrane housings 118a, 118b in which the membranes 117a, 117b are clamped with their flat edge regions 123a, 123b, are fastened to the flanges 120a, 120b in such a way that the membranes 117a, 117b are perpendicular to the longitudinal axis of the respective channel in their plane middle position 122a, 122b.
- the two membranes 117a, 117b 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 (s. Fig. 14 ) is flanged.
- the membrane chambers 119a, 119b comprise outlets 126a, 126b, to each of which an outlet check valve 127a, 127b is flanged.
- a rotational operation of the crankshaft 101 causes the working fluid in the working fluid volume 112a, 112b and the diaphragms 117a, 117b to be reciprocated 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, in Fig. 15 Dashed extreme position.
- the two membrane housings in the highest edge area of the membranes 117a, 117b are marked with 128a, 128b in the drawing provided not shown vent valves.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Description
Die Erfindung betrifft eine Verdrängerpumpe.The invention relates to a positive displacement pump.
Die
Die
Auch die in der
Aus der
Die
Die
Die
Die
als nächstliegender Stand der Technik kann die
as the closest prior art, the
Die Erfindung hat es sich zur Aufgabe gemacht, eine derartige Pumpe mit verbesserter Lebensdauer zu schaffen.The invention has set itself the task of creating such a pump with improved life.
Diese Aufgabe wird durch die in Anspruch 1 wiedergegebene Pumpe gelöst.This object is achieved by the reproduced in
Bei der erfindungsgemäßen Kolben-Membranpumpe ist die die Membran an einer von einer Senkrechtstellung verschiedenen Lage, insbesondere um 45° bis 90°, ganz besonders um etwa 70° angeordnet.In the piston-diaphragm pump according to the invention, the diaphragm is arranged at a position different from a vertical position, in particular by 45 ° to 90 °, very particularly by approximately 70 °.
Die erfindungsgemäße Kolben-Membranpumpe ist - wie bei zur Förderung von Schlamm bei Erdarbeiten vorgesehenen Kolben- Membranpumpe üblich - derart angeordnet, dass der (oder bei Mehrfachpumpen die) Zylinder mit seiner (ihrer) Längsachse(n) waagrecht angeordnet ist (sind). Es können also Antriebs- und Kolben/The piston diaphragm pump according to the invention is - as usual for the promotion of sludge in excavation planned piston diaphragm pump - arranged such that the (or in multiple pumps the) cylinder with its (their) longitudinal axis (s) is arranged horizontally (are). So it can drive and piston /
Zylindereinheiten wie auch beim Stand der Technik Verwendung finden.Cylinder units as used in the prior art.
Das Arbeitsvolumen ist teilweise von einem sich schräg von dem Zylinder nach oben erstreckenden Kanal gebildet.The working volume is partially formed by a channel extending obliquely upwardly from the cylinder.
Der Kanal ist gerade ausgebildet und an dem den Kanal bildenden Kanalgehäuse ist ein senkrecht zur Längsachse des Kanals ausgerichteter Flansch vorgesehen, an welchem eine die Membran aufnehmendes Membrangehäuse befestigt ist. Als Membran und Membrangehäuse können somit wiederum dieselben Bauteile wie im Stand der Technik Verwendung finden, so dass mit Hilfe der Erfindung eine wesentliche Verbesserung einer Kolben-Membranpumpe erzielt wird, ohne dass dies mit konstruktionsbedingten Zusatzkosten verbunden wäre.The channel is straight and formed on the channel housing forming the channel is a perpendicular to the longitudinal axis of the channel aligned flange, on which a membrane receiving membrane housing is attached. As the membrane and membrane housing can thus again use the same components 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.
Dementsprechend ist die Membran vorzugsweise etwa kreisrund ausgebildet und weist einen Rand auf, der in dem Membrangehäuse etwa in einer Ebene eingespannt ist, wobei die Ebene in einer von einer Senkrechtstellung vorzugsweise um 45° bis 90°, besonders bevorzugt um einen derartigen Winkel verschiedenen Lage angeordnet ist, so dass die höchste Stelle des Arbeitsvolumens an einem seitlichen Randbereich gebildet ist. Ein bei einer zum Stand der Technik gehörenden Kolben-Membranpumpe vorgesehenes, etwa senkrecht nach oben weisendes Entlüftungsventil kann dann weiterhin zur Entlüftung des Arbeitsvolumens Verwendung finden.Accordingly, the membrane is preferably formed approximately circular and has an edge which is clamped in the diaphragm housing approximately in a plane, wherein the plane in a vertical position preferably by 45 ° to 90 °, more preferably arranged at such an angle location is, 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.
Die Erfindung soll nun anhand eines in den Zeichnungen gezeigten Ausführungsbeispiels näher erläutert werden. Es zeigen:
- Fig. 1
- eine Querschnittsdarstellung einer aus dem Stand der Technik bekannten gängigen dreifachwirkenden Triplexpumpe;
- Fig. 2
- eine Draufsicht der in
Fig. 1 gezeigten Pumpe; - Fig. 3
- eine perspektivische Darstellung einer aus dem Stand der Technik bekannten doppeltwirkenden Duplexpumpe;
- Fig. 4
- eine Ansicht wie in
Fig. 3 , aus einer anderen Blickrichtung; - Fig. 5
- eine Seitenansicht einer erfindungsgemäßen Pumpeneinheit;
- Fig. 6
- eine Ansicht von der Antriebseinheit auf eine erfindungsgemäße Pumpeneinheit;
- Fig. 7
- eine Querschnittsdarstellung der erfindungsgemäßen Pumpeneinheit;
- Fig. 8
- eine Ansicht von oben auf die erfindungsgemäße Pumpeneinheit;
- Fig. 9
- eine perspektivische Darstellung der erfindungsgemäßen Pumpeneinheit;
- Fig. 10
- eine Seitenansicht der erfindungsgemäßen Verdrängerpumpe;
- Fig. 11
- eine Ansicht von oben auf die erfindungsgemäße Verdrängerpumpe;
- Fig. 12
- eine perspektivische Darstellung der erfindungsgemäßen Verdrängerpumpe;
- Fig. 13
- eine Querschnittsdarstellung der erfindungsgemäßen Verdrängerpumpe in größerem Maßstab;
- Fig. 14
- eine vergrößerte Darstellung der
Fig. 4 ; - Fig. 15
- den Schnitt A-A in
Fig. 14 .
- Fig. 1
- a cross-sectional view of a known from the prior art common triple-acting triplex pump;
- Fig. 2
- a top view of the
Fig. 1 shown pump; - Fig. 3
- a perspective view of a known from the prior art double-acting duplex pump;
- Fig. 4
- a view like in
Fig. 3 , from another perspective; - Fig. 5
- a side view of a pump unit according to the invention;
- Fig. 6
- a view from the drive unit to a pump unit according to the invention;
- Fig. 7
- a cross-sectional view of the pump unit according to the invention;
- Fig. 8
- a view from above of the pump unit according to the invention;
- Fig. 9
- a perspective view of the pump unit according to the invention;
- Fig. 10
- a side view of the positive displacement pump according to the invention;
- Fig. 11
- a view from above of the positive displacement pump according to the invention;
- Fig. 12
- a perspective view of the positive displacement pump according to the invention;
- Fig. 13
- a cross-sectional view of the positive displacement pump according to the invention in a larger scale;
- Fig. 14
- an enlarged view of
Fig. 4 ; - Fig. 15
- the cut AA in
Fig. 14 ,
Die in
An der Antriebseinheit 1 ist eine Pumpeneinheit 2 vorgesehen. Dieses stellt einen an jeden Zylinder 5 angrenzenden Arbeitsmediumsraum 23 bereit, in dem Arbeitsmedium 22, beispielsweise Hydrauliköl, vorgesehen ist, welches die Bewegung des Kolbens 7 auf die Membran 6 überträgt. In
Eine Drehbewegung der Kurbelwelle 18 führt dazu, dass Arbeitsmedium 22 in dem Arbeitsmediumsraum 23 hin und her bewegt wird und die Membran 6, 6' damit abwechselnd nach rechts und links auslenkt. Eine Auslenkung nach links führt zu einem Schließen des Auslassrückschlagsventils bzw. Druckventils in dem Druckventilgehäuse 14 und zu einem Ansaugen von Fördermedium durch das geöffnete Einlass-Rückschlagsventil bzw. Saugventil in dem Saugventilgehäuse 15. Die anschließende Verlagerung des Kolbens gemäß
Die
Die
Die Antriebseinheit 1 der gezeigten erfindungsgemäßen Pumpe stimmt im Wesentlichen mit der Antriebseinheit 1 der aus dem Stand der Technik bekannten einfachwirkenden Triplexpumpe (
Bei einer nach rechts Bewegung des Kolbens 7 (bezogen auf
Die Membranen bilden zusammen mit einem Teil der Membrangehäuse 6a, 6a' jeweils einen Arbeitsraum 4, 4'. Wie insbesondere
Die technischen Daten der in
Die technischen Daten des gezeigten Ausführungsbeispiels der erfindungsgemäßen Verdrängerpumpe lauten wie folgt: Kolbendurchmesser: 275 mm, Kolbenhub: 508 mm, Volumenstrom (Design normal) 351 m3/h, maximaler Volumenstrom 385 m3/h, theoretische Fördermenge pro Kurbelwellendrehung: 173,4 l, volumetrischer Wirkungsgrad: 0,94, normale Hubzahl: 35,9 min-1, maximale Hubzahl: 39,4 min-1, normaler Förderdruck: 80,0 bar, maximaler Förderdruck: 96,0 bar, Übersetzungsverhältnis der innen liegenden Zahnräder ("Internal gear ratio"): 3,8077, Kolbenstangenbelastung bei normalem Förderdruck: 475 kN, Kolbenstangenbelastung bei maximalem Förderdruck: 570 kN, Lagerlebensdauer bei Betrieb mit Maximallast: 445.700 h, Lagerlebensdauer bei Normalbetrieb: 810.500 h, verdrängtes Kolbenvolumen Vorderseite: 30,2 l, verdrängtes Kolbenvolumen Rückseite: 27,6 l, benötigte Membransorte in Litern: 47 I.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 l, 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, 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 Rear: 27.6 l, required membrane type in liters: 47 I.
Hinsichtlich der Membran ergeben sich folgende Unterschiede: die in
Dagegen benötigt die gezeigte erfindungsgemäße Verdrängerpumpe sechs Membranen, deren Größe ist auf 47 l ausgelegt, die Betriebsstunden sind mit 4.500 angesetzt, es werden bis zu 8.000 Betriebsstunden bei möglicher Neuentwicklung der Membranen erwartet, die Zahl der Membranwechsel pro Jahr beträgt 1,78, bzw. die Zahl der erwarteten Membranwechsel pro Jahr beträgt 1.In contrast, the positive displacement pump according to the invention shown requires six membranes, whose size is designed for 47 l, the operating hours are set at 4,500, it is expected up to 8,000 operating hours with a possible new development of the membranes, the number of membrane changes per year is 1.78, or the number of expected membrane changes per year is 1.
Hinsichtlich der Ventile ergibt sich die folgende Situation: Die in
Dagegen benötigt das gezeigte Ausführungsbeispiel der erfindungsgemäßen Verdrängerpumpe 12 Ventile, ebenfalls der Größe API 13, mit 1.800 Betriebsstunden. Die Durchschnittsgeschwindigkeit (average velocity) beträgt 1,29, die erwarteten Betriebsstunden betragen aufgrund der reduzierten Geschwindigkeit (velocitiy) 2.160, die Ventilwechsel pro Jahr betragen 4,44 und die erwarteten Ventilwechsel pro Jahr betragen 3,7.In contrast, the illustrated embodiment of the positive displacement pump 12 according to the invention requires valves, also the
Es lassen sich also insbesondere folgende Vorteile des gezeigten Ausführungsbeispiels der erfindungsgemäßen Verdrängerpumpe verglichen mit der in
Durch das Schrägstellen der Membranen 6, 6', also deren Neigung aus der Senkrechten, werden mehrere Vorteile erreicht. Zum einen wird die Platz sparende Anordnung der Membrangehäuse an den kompakt nebeneinander parallel verlaufenden Zylindern 5 erreicht, was den Aufbau einer kompakten doppelt wirkenden Triplexpumpe mit eng nebeneinander verlaufenden Zylindern ermöglicht. Zum anderen ergibt sich verglichen mit einer senkrecht stehenden Membran eine Verringerung der ungleichmäßig auf die Membran wirkenden hydraulischen Druckkomponente. Dies führt zu einer erhöhten Lebensdauer der Membran. Auch der die Membranlebensdauer herabsetzende Einfluss von möglichem Gasvorkommen in dem Fördermedium 24, 24', möglicherweise hervorgerufen oder verstärkt durch Kavitation, wird verringert. Die zur Schrägstellung der Membranen getroffenen Maßnahmen und Wirkungen sollen nun im Detail unter Bezugnahme auf
Die in
Die dargestellte Kolben-Membranpumpe 200 umfasst eine motorisch angetriebene Kurbelwelle 10, auf deren mittleren Kurbelzapfen 102 ein Pleuel 103 mit Hilfe eines Pleuellagers 104 gelagert ist. An dem anderen Ende des Pleuels 103 ist ein Kreuzkopf 105 über ein Kreuzkopflager 106 gelagert. Der Kreuzkopf 105 umfasst Gleitschuhe 107, welche seiner linearen Lagerung an Gleitlagerwandungen 108 dienen.The illustrated piston-
An dem Kreuzkopf 105 ist eine Kolbenstange 109 einenends befestigt. Das andere Ende der Kolbenstange 109 trägt einen Kolben 110, der als doppelt wirkender Kolben ausgebildet ist und in einem Zylinder 111 arbeitet. In
Der Zylinder 111 ist innerhalb eines Arbeitsvolumens angeordnet, welches von dem Kolben 110 in zwei Arbeitsteilvolumina 112a, 112b unterteilt ist. Das in
Die in der Zeichnung nicht dargestellte Arbeitsflüssigkeit - meist Hydrauliköl, daher auch Ölvorlage genannt - füllt das Arbeitsvolumen 112a, 112b bis zu zwei Membranen 117a, 117b, die in
Die Membranen 117a, 117b sind in Membrangehäusen 118a, 118b angeordnet und trennen Membrankammern 119a, 119b von der im Arbeitsvolumen 112a, 112b befindlichen Ölvorlage.The
Die Membrangehäuse 118a, 118b sind an Flanschen 120a, 120b von Kanalgehäusen 121a, 121b befestigt. Die Kanalgehäuse 121a, 121b umfassen Kanäle 122a, 122b, welche Teile des Arbeitsvolumens 112a, 112b bilden. Die beiden Kanalgehäuse 121a, 121b, die im Wesentlichen gerade ausgebildet sind, schließen zur Senkrechten jeweils einen Winkel von etwa 20° ein, dergestalt, dass sich der Abstand der beiden Kanalgehäuse 121a, 121b nach oben hin vergrößert. Die Membrangehäuse 118a, 118b, in denen die Membranen 117a, 117b mit ihren ebenen Randbereichen 123a, 123b eingeklemmt sind, sind derart an den Flanschen 120a, 120b befestigt, dass sich die Membranen 117a, 117b in ihrer ebenen Mittelstellung senkrecht zur Längsachse des jeweiligen Kanals 122a, 122b erstrecken. Bei dem in
Jede Membrankammer umfasst einen Einlass 124a, 124b, an den jeweils ein Einlass-Rückschlagventil 125a, 125b (s.
Auf der den Einlässen 124a, 124b gegenüberliegenden Seiten umfassen die Membrankammern 119a, 119b Auslässe 126a, 126b, an welchen jeweils ein Auslassrückschlagventil 127a, 127b angeflanscht ist.On the sides opposite the inlets 124a, 124b, the membrane chambers 119a, 119b comprise
Eine Drehbetätigung der Kurbelwelle 101 führt dazu, dass die Arbeitsflüssigkeit in dem Arbeitsflüssigkeitsvolumen 112a, 112b und die Membranen 117a, 117b zwischen den gestrichelt dargestellten Extremauslenkungen hin und her bewegt werden. Dabei führt eine Auslenkung jeweils nach unten zu einem Ansaugen von Schlamm durch das jeweils geöffnete Einlass-Rückschlagventil. Diese Pumpphase ist als Saugtakt bezeichnet. Die anschließende Verlagerung des Kolbens führt zu einem Schließen des zuvor geöffneten Einlass-Rückschlagventils und einer Abgabe des dem Hubraum entsprechenden Volumens an Schlamm über das nun geöffnete Auslass-Rückschlagventil unter Verlagerung der Membran in die nach oben gewölbte, in
Um eventuell in dem Arbeitsvolumen 112a, 112b befindliches, sich in dem Bereich unterhalb einer Membran angelagertes Gas - insbesondere Luft - ablassen zu können, sind die beiden Membrangehäuse im höchstliegenden Randbereich der Membranen 117a, 117b, in der Zeichnung mit 128a, 128b gekennzeichnet, mit nicht dargestellten Entlüftungsventilen versehen.In order to be able to discharge gas, in particular air, located in the working area 112a, 112b in the area below a membrane, the two membrane housings in the highest edge area of the
- 100100
- Verdrängerpumpedisplacement
- 11
- Antriebseinheitdrive unit
- 22
- Pumpeneinheitpump unit
- 3, 3'3, 3 '
- Verdrängerelementedisplacement
- 4, 4'4, 4 '
- Arbeitsräumeworkrooms
- 55
- Zylindercylinder
- 5a5a
- Zylindergehäusecylinder housing
- 6, 6'6, 6 '
- Membranenmembranes
- 6a, 6a'6a, 6a '
- Membrangehäusemembrane housing
- 77
- Kolbenpiston
- 88th
- freifree
- 99
- Kolbenstangepiston rod
- 10, 10'10, 10 '
- Kolbenflächenpiston surfaces
- 1111
- Einlassinlet
- 1212
- Auslassoutlet
- 1313
- Rückschlagventilcheck valve
- 14, 14'14, 14 '
- DruckventilgehäusePressure valve housing
- 1515
- SaugventilgehäuseSaugventilgehäuse
- 1616
- Saugrohrsuction tube
- 17, 17'17, 17 '
- Druckrohrpressure pipe
- 1818
- Kurbelwellecrankshaft
- 18a18a
- Pleuelpleuel
- 1919
- Antriebswelledrive shaft
- 2020
- KreuzkopfPhillips
- 2121
- KreuzkopfstangePhillips rod
- 22, 22'22, 22 '
- Arbeits- bzw. ÜbertragungsmediumWorking or transmission medium
- 23, 23,23, 23,
- ArbeitsmediumsraumWorking medium space
- 24, 24'24, 24 '
- Fördermediumconveying medium
- SS
- Senkrechtevertical
- α, βα, β
- Winkelangle
- 200200
- Kolben-MembranpumpePiston diaphragm pump
- 101101
- Kurbelwellecrankshaft
- 102102
- Kurbelzapfencrank pin
- 103103
- Pleuelpleuel
- 104104
- Pleuellagerconnecting rod bearing
- 105105
- KreuzkopfPhillips
- 106106
- KreuzkopflagerCrosshead bearing
- 107107
- Gleitschuheskids
- 108108
- GleitlagerwandungGleitlagerwandung
- 109109
- Kolbenstangepiston rod
- 110110
- Kolbenpiston
- 111111
- Zylindercylinder
- 112a, 112b112a, 112b
- Arbeitsteilvolumina, Zusammen ArbeitsvolumenWorking Part Volumes, Together Work Volume
- 113113
- Deckelcover
- 114114
- Deckelcover
- 115115
- Öffnungopening
- 116116
- Dichtungsanordnungsealing arrangement
- 117a, 117b117a, 117b
- Membranenmembranes
- 118a, 118b118a, 118b
- Membrangehäusemembrane housing
- 119a, 119b119a, 119b
- Membrankammerndiaphragm chambers
- 120a, 120b120a, 120b
- Flanscheflanges
- 121a, 121b121a, 121b
- Kanalgehäusechannel housing
- 122a, 122b122a, 122b
- Kanälechannels
- 123a, 123b123a, 123b
- Randbereicheborder areas
- 124a, 124b124a, 124b
- Einlässeinlets
- 125a, 125b125a, 125b
- Einlass-RückschlagventileInlet check valves
- 126a, 126b126a, 126b
- Auslässeoutlets
- 127a, 127b127a, 127b
- Auslass-RückschlagventileOutlet check valves
- 128a, 128b128a, 128b
- Bereicheareas
Claims (4)
- A positive displacement pump designed as a piston diaphragm pump (200), having a piston (110) performing an oscillating movement within a cylinder (111), said movement being transmittable through a working fluid to a diaphragm (117a; 117b), which separates a working volume (112a; 112b), in which the working liquid is positioned, from a diaphragm chamber (119a; 119b), through which a fluid to be fed is conducted, wherein the diaphragm (117a; 117b) is arranged in a position which differs from a vertical position, and the longitudinal axis of the cylinder (111) is arranged in a horizontal position, characterized in that the working volume (112a; 112b) is partially formed by a channel (122a; 122b), which partially obliquely extends upwards from the cylinder and the channel (122a; 122b), is designed to be straight and on the channel housing (121a; 121b) forming the channel (122a; 122b) a flange (120a; 120b) is provided, which is perpendicular to the longitudinal axis of the channel (125a, 125b) and a diaphragm housing (118a; 118b) for housing the diaphragm (117a; 117b) is attached to the flange.
- The piston diaphragm pump of claim 1, characterized in that the diaphragm (117a; 117b) is arranged in a position which differs by 45° to 90° from a vertical position.
- The piston diaphragm pump of claim 2, characterized in that the diaphragm (117a; 117b) is arranged in a position which differs by 70° from a vertical position.
- The piston diaphragm pump of any of claims 1 to 3, characterized in that the diaphragm (117a; 117b) has a circular shape and is provided with an edge region (123a; 123b), which extends within the diaphragm housing (118a; 118b) in a plane arranged in a position which differs by 45° to 90° from a vertical position, and that the highest point of the working volume (112a; 112b) is formed on a lateral edge region (128a; 128b).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011054074A DE102011054074A1 (en) | 2011-09-30 | 2011-09-30 | Displacement pump e.g. slurry pump, has pump unit comprising working areas, displacement elements designed as diaphragms, and piston for operating displacement elements, where pump unit is designed in double-acting manner |
DE102011054073A DE102011054073A1 (en) | 2011-09-30 | 2011-09-30 | Method for operating piston diaphragm pump used for pumping slurry in e.g. hydraulic oil, involves producing membrane stroke with one of vertical position of membranes among various membrane positions |
PCT/EP2012/069160 WO2013045598A2 (en) | 2011-09-30 | 2012-09-28 | Positive displacement pump and operating method thereof |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2761180A2 EP2761180A2 (en) | 2014-08-06 |
EP2761180B1 true EP2761180B1 (en) | 2018-11-21 |
Family
ID=47008582
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12770085.4A Active EP2761180B1 (en) | 2011-09-30 | 2012-09-28 | Positive displacement pump |
Country Status (9)
Country | Link |
---|---|
US (1) | US9695808B2 (en) |
EP (1) | EP2761180B1 (en) |
AU (2) | AU2012314408B2 (en) |
BR (1) | BR112014007364B1 (en) |
CA (1) | CA2861136C (en) |
CL (1) | CL2014000755A1 (en) |
IN (1) | IN2014CN03132A (en) |
PE (1) | PE20141978A1 (en) |
WO (1) | WO2013045598A2 (en) |
Families Citing this family (37)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013108672A1 (en) * | 2013-08-09 | 2015-02-12 | Aker Wirth Gmbh | displacement |
US10351929B2 (en) | 2015-02-12 | 2019-07-16 | Sumitomo Metal Mining Co., Ltd. | Sulfuric acid adding facility and operation method therefor |
US11624326B2 (en) | 2017-05-21 | 2023-04-11 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
GB2581164A (en) | 2019-02-06 | 2020-08-12 | Mhwirth Gmbh | Fluid pump, pump assembly and method of pumping fluid |
GB201904054D0 (en) | 2019-03-25 | 2019-05-08 | Mhwirth Gmbh | Pump and associated system and methods |
CA3092859A1 (en) | 2019-09-13 | 2021-03-13 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11015594B2 (en) | 2019-09-13 | 2021-05-25 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
CA3191280A1 (en) | 2019-09-13 | 2021-03-13 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
CA3092865C (en) | 2019-09-13 | 2023-07-04 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11002189B2 (en) | 2019-09-13 | 2021-05-11 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US10815764B1 (en) | 2019-09-13 | 2020-10-27 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11604113B2 (en) | 2019-09-13 | 2023-03-14 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US10895202B1 (en) | 2019-09-13 | 2021-01-19 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
CA3092868A1 (en) | 2019-09-13 | 2021-03-13 | Bj Energy Solutions, Llc | Turbine engine exhaust duct system and methods for noise dampening and attenuation |
US11708829B2 (en) | 2020-05-12 | 2023-07-25 | Bj Energy Solutions, Llc | Cover for fluid systems and related methods |
US10968837B1 (en) | 2020-05-14 | 2021-04-06 | Bj Energy Solutions, Llc | Systems and methods utilizing turbine compressor discharge for hydrostatic manifold purge |
US11428165B2 (en) | 2020-05-15 | 2022-08-30 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11208880B2 (en) | 2020-05-28 | 2021-12-28 | Bj Energy Solutions, Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11208953B1 (en) | 2020-06-05 | 2021-12-28 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11109508B1 (en) | 2020-06-05 | 2021-08-31 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US11066915B1 (en) | 2020-06-09 | 2021-07-20 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11111768B1 (en) | 2020-06-09 | 2021-09-07 | Bj Energy Solutions, Llc | Drive equipment and methods for mobile fracturing transportation platforms |
US10954770B1 (en) | 2020-06-09 | 2021-03-23 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11125066B1 (en) | 2020-06-22 | 2021-09-21 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11028677B1 (en) | 2020-06-22 | 2021-06-08 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11933153B2 (en) | 2020-06-22 | 2024-03-19 | Bj Energy Solutions, Llc | Systems and methods to operate hydraulic fracturing units using automatic flow rate and/or pressure control |
US11939853B2 (en) | 2020-06-22 | 2024-03-26 | Bj Energy Solutions, Llc | Systems and methods providing a configurable staged rate increase function to operate hydraulic fracturing units |
US11473413B2 (en) | 2020-06-23 | 2022-10-18 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11466680B2 (en) | 2020-06-23 | 2022-10-11 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11220895B1 (en) | 2020-06-24 | 2022-01-11 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11149533B1 (en) | 2020-06-24 | 2021-10-19 | Bj Energy Solutions, Llc | Systems to monitor, detect, and/or intervene relative to cavitation and pulsation events during a hydraulic fracturing operation |
US11193360B1 (en) | 2020-07-17 | 2021-12-07 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US20220065752A1 (en) * | 2020-08-27 | 2022-03-03 | University Of Idaho | Rapid compression machine with electrical drive and methods for use thereof |
US11767840B2 (en) | 2021-01-25 | 2023-09-26 | Ingersoll-Rand Industrial U.S. | Diaphragm pump |
US11639654B2 (en) * | 2021-05-24 | 2023-05-02 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
WO2023117320A1 (en) | 2021-12-22 | 2023-06-29 | Mhwirth Gmbh | Fluid pump, pump assembly and method of pumping fluid |
WO2024101998A1 (en) | 2022-11-09 | 2024-05-16 | Mhwirth Gmbh | Double acting pump |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB586862A (en) * | 1944-12-03 | 1947-04-02 | Cyril Alphonso Pugh | Improvements in or relating to reciprocating pumps and compressors |
US2778315A (en) * | 1954-02-24 | 1957-01-22 | Exxon Research Engineering Co | Pump for abrasive fluids |
DE946769C (en) | 1955-01-12 | 1956-08-02 | Pleuger & Co | Diaphragm-protected piston pump with leakage oil return |
DE1107512B (en) | 1957-08-03 | 1961-05-25 | Hydraulik Gmbh | Multi-cylinder piston press pump system for high fluid pressures |
DE1061186B (en) | 1957-11-27 | 1959-07-09 | Karl Schlecht Dipl Ing | Diaphragm pump |
DE1763709U (en) | 1957-11-27 | 1958-03-20 | Schlecht Karl | DIAPHRAGM PISTON PUMP. |
DE1254968B (en) | 1960-03-23 | 1967-11-23 | Kobe Inc | Hydraulically operated multiple piston pump for pumping oil from deep wells |
US3847511A (en) * | 1973-10-16 | 1974-11-12 | Halliburton Co | Hydraulically powered triplex pump and control system therefor |
US4008009A (en) | 1975-09-30 | 1977-02-15 | Endre Kovacs | Fuel injection pump |
AU515126B2 (en) | 1977-05-02 | 1981-03-19 | Yamada Yuki Seizo Co. Ltd. | Diaphragm pump |
DE2855167A1 (en) | 1978-12-20 | 1980-07-03 | Siemens Ag | Diaphragm pump for liq. - uses external heat in Stirling cycle to move displacement member and diaphragm with liquid as coolant |
AU6989381A (en) * | 1980-04-29 | 1981-11-05 | Mark, F.E. | Double acting diaphragm pump |
US4406595A (en) * | 1981-07-15 | 1983-09-27 | Robertson William C | Free piston pump |
US4427350A (en) | 1982-01-11 | 1984-01-24 | Hare Louis R O | Solar diaphragm pump |
IT1190613B (en) | 1986-04-11 | 1988-02-16 | Taiver Srl | ALTERNATIVE MEMBRANE VOLUMETRIC PUMP, PARTICULARLY FOR ABRASIVE, CORROSIVE LIQUIDS, WITH SUSPENSION PARTS OR SIMILAR |
US4963075A (en) * | 1988-08-04 | 1990-10-16 | The Charles Machine Works, Inc. | Radial diaphragm pump |
EP0484575A1 (en) * | 1990-11-07 | 1992-05-13 | Abel-Pumpen Gmbh & Co. Kg | Device for pumping mud and for adding a dosed filtering assistance agent |
DE4122538A1 (en) | 1991-07-08 | 1993-01-14 | Friedhelm Schneider | Hydraulically actuated double membrane pump - uses piston controlled by eccentric disc to impart hydraulic pressure |
US6547537B2 (en) | 1999-09-14 | 2003-04-15 | Lawrence P. Olson | Air operated radial piston and diaphragm pump system |
NL1033204C2 (en) | 2007-01-10 | 2008-07-11 | Weir Minerals Netherlands Bv | Single-acting displacement device. |
EP2154371B1 (en) | 2008-08-14 | 2018-09-19 | Bran + Lübbe GmbH | Pumping device |
SE0900233A1 (en) | 2009-02-24 | 2010-08-25 | Tetra Laval Holdings & Finance | Diaphragm pump head for a homogenizer |
-
2012
- 2012-09-28 BR BR112014007364-3A patent/BR112014007364B1/en not_active IP Right Cessation
- 2012-09-28 WO PCT/EP2012/069160 patent/WO2013045598A2/en active Application Filing
- 2012-09-28 AU AU2012314408A patent/AU2012314408B2/en not_active Ceased
- 2012-09-28 EP EP12770085.4A patent/EP2761180B1/en active Active
- 2012-09-28 CA CA2861136A patent/CA2861136C/en not_active Expired - Fee Related
- 2012-09-28 IN IN3132CHN2014 patent/IN2014CN03132A/en unknown
- 2012-09-28 PE PE2014000439A patent/PE20141978A1/en active IP Right Grant
- 2012-09-28 US US14/347,243 patent/US9695808B2/en active Active
-
2014
- 2014-03-27 CL CL2014000755A patent/CL2014000755A1/en unknown
-
2016
- 2016-05-10 AU AU2016203015A patent/AU2016203015B2/en not_active Ceased
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
US9695808B2 (en) | 2017-07-04 |
AU2012314408B2 (en) | 2016-05-26 |
EP2761180A2 (en) | 2014-08-06 |
AU2016203015B2 (en) | 2018-06-14 |
BR112014007364B1 (en) | 2021-09-28 |
AU2012314408A1 (en) | 2014-05-08 |
BR112014007364A2 (en) | 2017-04-04 |
CA2861136A1 (en) | 2013-04-04 |
PE20141978A1 (en) | 2014-12-18 |
AU2016203015A1 (en) | 2016-06-02 |
IN2014CN03132A (en) | 2015-07-03 |
CA2861136C (en) | 2018-04-24 |
CL2014000755A1 (en) | 2014-07-25 |
WO2013045598A3 (en) | 2013-05-30 |
WO2013045598A2 (en) | 2013-04-04 |
US20140248160A1 (en) | 2014-09-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2761180B1 (en) | Positive displacement pump | |
EP2999884B1 (en) | Axial piston pump | |
EP2912310B1 (en) | Piston membrane pump | |
DE112006003645T5 (en) | Pump / motor of variable-axis oblique-axis type | |
DE102014010108B4 (en) | Hydraulically driven diaphragm pump | |
WO2018091306A1 (en) | Method for operating a piston pump, and piston pump | |
DE2020317A1 (en) | Pumping device | |
DE19603109C2 (en) | Piston refrigerant compressor with improved sealing function | |
EP2464868B1 (en) | Diaphragm machine | |
WO2013060576A1 (en) | Hydrostatic piston machine | |
DE69929923T2 (en) | Axial piston pump and improved valve plate design | |
DE102017208755A1 (en) | HYDROSTATIC SUPPORT AND LUBRICATION ON VALV SEGMENT LOAD | |
EP1702162B1 (en) | Piston compressor for compressing gaseous media in at least two working chambers | |
DE3419054A1 (en) | OSCILLATING DEFLECTOR PUMP | |
EP2057376B1 (en) | Diaphragm pump with two diaphragm heads and two separate pump housings | |
EP0400693A2 (en) | High pressure pump | |
WO2012168083A2 (en) | Axial piston machine of swash-plate design | |
WO2010084002A2 (en) | Hydraulic machine assembly | |
WO2013068211A1 (en) | Hydrostatic piston engine | |
DE102017222354A1 (en) | Hydrostatic piston machine | |
DE10319671A1 (en) | pump | |
DE102014208406A1 (en) | Hydrostatic piston machine | |
EP1715183B1 (en) | Hydraulic axial piston pump | |
EP1700034B1 (en) | Axial piston machine for independent delivery into several hydraulic circuits | |
DE102011054074A1 (en) | Displacement pump e.g. slurry pump, has pump unit comprising working areas, displacement elements designed as diaphragms, and piston for operating displacement elements, where pump unit is designed in double-acting manner |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20140429 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
DAX | Request for extension of the european patent (deleted) | ||
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: MHWIRTH GMBH |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20170118 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20180717 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1067847 Country of ref document: AT Kind code of ref document: T Effective date: 20181215 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502012013876 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: FP |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190221 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190221 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190321 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190321 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190222 Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502012013876 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20190822 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190930 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190930 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190928 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190928 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20190930 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190930 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 1067847 Country of ref document: AT Kind code of ref document: T Effective date: 20190928 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190928 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20120928 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20210802 Year of fee payment: 10 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20210730 Year of fee payment: 10 Ref country code: GB Payment date: 20210730 Year of fee payment: 10 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181121 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502012013876 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20220928 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220930 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230401 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 20230816 Year of fee payment: 12 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220928 |