EP3390818B1 - Diaphragm pump comprising dust suction from below - Google Patents

Diaphragm pump comprising dust suction from below Download PDF

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Publication number
EP3390818B1
EP3390818B1 EP16822973.0A EP16822973A EP3390818B1 EP 3390818 B1 EP3390818 B1 EP 3390818B1 EP 16822973 A EP16822973 A EP 16822973A EP 3390818 B1 EP3390818 B1 EP 3390818B1
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EP
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Prior art keywords
dust
pressure
diaphragm pump
diaphragm
hydraulic
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EP16822973.0A
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German (de)
French (fr)
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EP3390818A1 (en
Inventor
Frank Hannemann
Thomas Metz
Sebastian RAHM
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Dipl Ing Ernst Schmitz & Co KG Maschinen U GmbH
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Dipl Ing Ernst Schmitz & Co KG Maschinen und Apparatebau GmbH
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    • 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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
    • 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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • 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
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston

Definitions

  • the invention relates to a diaphragm pump for the pneumatic high-pressure delivery of 1 to 10 MPa of fluidized dusts and a method for operating such a diaphragm pump.
  • screw conveyors with slight bulk material compression and subsequent gas injection are used in practice for pneumatic bulk material conveyance, see DD000000081606A1 , DE000003035745A1 , DE000000656009A , DE000000650988A , DE000000615779A , DE000000596565A , DE000000568999A , DE000000551066A , DE000000485635A , DE000000449676A , DE000000427455A .
  • cellular wheels are used instead of screws, see DE102009016191B4 , DE102009016191A1 .
  • dust pumps are used industrially for low pressures, today only lock processes are industrially established for high pressure processes in the order of 1 to 10 MPa, see DE 10 2005 047 583 B4 , DD 147 188 A3 , DE102008052673A1 .
  • dust pumps for high pressure applications are also being developed, the following processes being known: For high-pressure applications in the order of 1 to 10 MPa, dust pumps based on the principle of the extrusion press are known.
  • the bulk material is mechanically as in an extrusion press in a tapered channel to form a briquette, thereby forming a high pressure barrier from the channel and briquette, which is necessary for sealing between the high and low pressure parts, see US000008851406B2 , US020100021247A1
  • the disadvantage here is the high wear due to the high friction forces that occur, as well as the problem that the mechanical properties of the bulk material are changed significantly by this process, since the bulk material is present in briquette-like bulk material agglomerations after the pump. Particularly for consumers such as dust combustion or dust gasification, it is then necessary to re-grind under pressure, which represents a problem that has not yet been solved.
  • the piston pump principle is also known for high-pressure applications.
  • Known designs are in DE000001008201A , DE000001175653A , DE000002722931A1 , DE102008009679A1 described.
  • the main disadvantage here is the high, previously unresolved wear on the dry-running piston rings. This problem can be solved by using membranes as in DE102011007066A1 shown to be solved.
  • due to the gravity-driven filling - as with all other known dust pumps and lock systems relatively large cross sections and dimensions are required.
  • the document CH 466 134 discloses a hydraulically operated dust pump which has spring-loaded valves.
  • the membrane is arranged vertically.
  • the invention is based on the problem of specifying a pump head for the pneumatic high-pressure delivery of fluidized bulk material and a method for operating the pump head, in which the bulk material is kept in a loosened, fluidized state over the entire pumping process.
  • the filling is carried out by pneumatic suction, the bulk material being kept in a loosened, flowable state throughout the entire pumping process and dust compaction being avoided in a targeted manner.
  • a highly compact and therefore economical construction is achieved.
  • Pneumatic suction has several decisive advantages over known dust pump systems:
  • the cross section of the suction line 17 and thus the size of the inlet valve 8 and the connection to the pump head are significantly smaller compared to gravity-driven filling, which means that the pump head can be designed accordingly smaller.
  • the filling can take place from below into the dust chamber.
  • This has the advantage that the design of the pump head in the area of the diaphragm and in the hydraulic area is simplified, since no dust passage from above is required, which would otherwise be the case when filled by gravity.
  • this arrangement makes it possible to constructively realize a very large loosening area 4, which is necessary to avoid dust densification and short cycle times.
  • the in Fig. 3 The pressure intensifier shown and thus also the separation of the hydraulic system into a primary hydraulic system 15 - between pressure intensifier and hydraulic unit - and a secondary hydraulic system 16 - between membrane 3 and pressure intensifier 13 - offer the following advantages:
  • the pressure of the hydraulic unit can be selected independently of the process pressure, which means that inexpensive standard Hydraulic units can be used instead of custom-made products. Since the pressure of the hydraulic unit (20-30 MPa) is generally much higher than the required process pressure in the dust system (1-10 MPa), the volume flows in the hydraulic unit and thus the costs of the hydraulic unit are significantly lower than if the hydraulic unit were designed for the process pressure of the dust system.
  • the pressure ratio (primary pressure / secondary pressure) is usually around 2-30.
  • Another advantage of the entire process is that the high-pressure gas requirement compared to that in DE102011007066A1 described system is further reduced, because on the one hand the dead volume to be relaxed after the discharge can be made even smaller due to the smaller pipe cross-sections and on the other hand the previously supplied covering gas is also used for the pneumatic conveying during discharge.
  • the membrane is mechanically guided by one or more pistons but also guide rods 10, as a result of which undesired deformations of the membrane are avoided.
  • a position measurement of the diaphragm 3 is given via the position of the piston or the guide rod 10 relative to the housing 9.
  • the dust pump according to the invention and the method carried out with it are suitable for fine-grained bulk goods or dusts which can be loosened and fluidized by adding gas, such as coal dust, and are particularly aimed at supplying pressure-charged coal dust gasifiers with dry coal dust feed.
  • the process pressures are of the order of 1 to 10 MPa. In principle, the method can also be used for all other processes where fluidizable dusts are to be pumped dry to high pressure.
  • a pressure-bearing housing 9 which hermetically separates the dust chamber 1 from the hydraulic chamber 2.
  • the membrane is guided centrally over a guide rod 10 and moved down or up by adding or removing hydraulic fluid via the connecting line 6. Dust is sucked into the dust chamber via the inlet valve 8 and conveyed out of the dust chamber via the outlet valve 7. For loosening, loosening and relaxation, gas is added or removed via the connecting lines 5 and the gas-permeable loosening surfaces 4.
  • Fig. 2 the pump cycle is shown using four process steps A) to D).
  • step A liquid is withdrawn from the hydraulic chamber, which pulls the membrane upwards and creates a vacuum in the dust chamber. As a result, dust is sucked out of the storage bunker 11. It is assumed that the dust in the feed bunker is in a fluidized state due to the addition of gas. During the pneumatic conveying into the dust chamber 1 by deflecting the membrane 3, a negative pressure is generated in the dust chamber 1, which supports the conveyance.
  • step B) by closing the inlet fitting 8 and adding gas via the gas connections 5, the dust space is stretched to the pressure caused by the pressure of the consumer 20 plus the pneumatic delivery pressure loss between the pump head 14 and the consumer (approx 0.1 to 1 MPa) is given.
  • step C the outlet fitting 7 is opened for conveying and the dust is conveyed out via the gas connections 5 with the addition of gas.
  • the volume of the dust chamber is reduced by adding hydraulic fluid via the hydraulic connection 6 into the hydraulic chamber, by means of the membrane 3.
  • step D the structurally unavoidable residual volume of the dust chamber is relaxed and the pump cycle begins with step A from the beginning.
  • the pressure in the dust chamber 1 is approximately 0.01 to 0.08 MPa below the pressure in the storage container 11 (differential pressure).
  • the negative pressure is generated in the dust chamber 1 by applying negative pressure via the gas connection 5.
  • the delivery differential pressure is generated by means of a vacuum pump.
  • the negative pressure applied via the gas connection (5) is equal to the amount after the differential pressure or is as large as the differential pressure.
  • a single pump head 14 operates batchwise, as shown in FIG FIG 3 shown, several pump heads connected to a dust pump system, wherein a continuous dust flow can be achieved. At least 2 pump heads are arranged for this. Depending on the required throughput and availability requirements, any number of pump heads can be interconnected. If a plurality of n pump heads are arranged, they can be operated out of phase with one another by 2n / n of the pump cycle. In addition to the advantage of continuous dust delivery, the hydraulic unit can be dimensioned smaller for a given throughput than would be the case with discontinuous operation. With this configuration, the effects on the pressure regime of the consumer 20 are also reduced.
  • An entrained-flow gasifier is supplied with coal dust at 100 t / h at 5 MPa gasification pressure.
  • the pressure loss between the dust pump and the carburetor is 1 MPa, which means that the delivery pressure is 6 MPa.
  • the cycle time of a pump head is 20 s, which results in a required volume of the dust chamber of 0.15 m 3 and the suction volume flow of 270 m 3 / h.
  • the hydraulic unit works at an operating pressure of 30 MPa and with a volume flow of 54 m 3 / h. Since gas is still added during stringing and discharge, the pressure flow volume flow corresponds to 300 m 3 / h.
  • the fittings namely the outlet valve 7 and the inlet valve 8, are given a wear-resistant design.
  • the dust space 1 is covered or expanded with gas via a large-area, gas-permeable loosening surface 4 which is tight for the dusty bulk material.
  • a large, gas-permeable loosening surface 4 is integrated at the bottom of the dust chamber 1, through which the inlets and outlets of the dust to be conveyed pass.
  • the loosening area in relation to the inner surface of the dust space is chosen to be large if possible (at least 30% of the inner surface of the dust space), which results in lower gas velocities in the bulk material and compression of the bulk material is avoided.
  • the pressure in the dust space is approximately 0.1 to 1 MPa above the pressure of the receiving container but also the metering vessel 20.
  • the hydraulic system is divided into primary and secondary hydraulics, the primary hydraulics being connected to the diaphragm 3 and being driven by the secondary hydraulics via a pressure booster.
  • the pressure ratio (primary pressure / secondary pressure) may be approximately 2 to 30.
  • the primary and Secondary hydraulics can be operated with different hydraulic fluids.
  • the pressure intensifier can be designed as a pressure intensifier piston.
  • the pressure intensifier can be designed to be resettable by a return spring, the return spring being able to be designed as a mechanical spring or as a pneumatic gas pressure spring.
  • At least two pump heads are combined to form a system, the pressure delivery lines 18 of which are brought together 19, which enables uninterrupted bulk material delivery.
  • a suction conveyor line 17 branches out of the supply bunker 11 and branches onto several pump heads.

Description

Die Erfindung betrifft eine Membranpumpe zur pneumatischen Hochdruckförderung von 1 bis 10 MPa fluidisierter Stäube und ein Verfahren zum Betrieb einer solchen Membranpumpe.The invention relates to a diaphragm pump for the pneumatic high-pressure delivery of 1 to 10 MPa of fluidized dusts and a method for operating such a diaphragm pump.

Für Niederdruckanwendungen im Bereich von ca. 0,1 bis 0,2 bar Druckerhöhung werden in der Praxis Förderschnecken mit leichter Schüttgutkomprimierung und anschließender Gasinjektion zur pneumatischen Schüttgutförderung eingesetzt, s. DD000000081606A1 , DE000003035745A1 , DE000000656009A , DE000000650988A , DE000000615779A , DE000000596565A , DE000000568999A , DE000000551066A , DE000000485635A , DE000000449676A , DE000000427455A . Für etwas höhere Drücke bis ca. 0,3 MPa werden statt Schnecken Zellenräder verwendet, s. DE102009016191B4 , DE102009016191A1 . Werden mehrere Staubpumpen in Reihe geschaltet können entsprechend höhere Drücke erreicht werden, was jedoch für Hochdruckanwendungen mit einem sehr großen apparativen Aufwand verbunden ist, s. DE102008049542B4 , DE102008049542A1 , DE102008007033A1 , WO002010037601A1 , WO002009095290A3 , WO002009095290A2 . Neben diesem Funktionsprinzip der Schneckenförderer und Zellenräder werden auch Staubpumpen nach dem Prinzip der Druckluftmembranpumpen eingesetzt, wobei auch hier nur geringe Drücke möglich sind DE 3909800 A1 .
Während für niedrige Drücke Staubpumpen industriell eingesetzt werden, sind für Hochdruckprozesse in der Größenordnung von 1 bis 10 MPa heute nur Schleusenprozesse industriell etabliert, s. DE 10 2005 047 583 B4 , DD 147 188 A3 , DE102008052673A1 . Um die Investitions- und Betriebskosten solcher Schleusensysteme zu reduzieren, werden auch Staubpumpen für Hochdruckanwendungen entwickelt, wobei folgende Verfahren bekannt sind:
Für Hochdruckanwendungen in der Größenordnung von 1 bis 10 MPa sind Staubpumpen basierend auf dem Prinzip der Strangpresse bekannt. Hierbei wird das Schüttgut mechanisch wie in einer Strangpresse in einem sich verjüngenden Kanal zu einem Brikett verdichtet und dadurch eine hohe Druckbarriere aus Kanal und Brikett gebildet, was zur Abdichtung zwischen Hoch- und Niederdruckteil erforderlich ist, siehe US000008851406B2 , US020100021247A1 Nachteilig hierbei ist der hohe Verschleiß aufgrund der hohen auftretenden Reibungskräfte als auch die Problematik, dass die mechanischen Schüttguteigenschaften durch diesen Vorgang stark verändert werden, da das Schüttgut nach der Pumpe in brikettähnlichen Schüttgut-agglomerationen vorliegt. Insbesondere für Verbraucher wie die Staubverbrennung oder Staubvergasung ist dann unter Druck eine erneute Aufmahlung erforderlich, was ein bisher ungelöstes Problem darstellt.
Neben dem Prinzip der Strangpresse ist für Hochdruckanwendungen auch das Kolbenpumpenprinzip bekannt. Hierzu bekannte Ausführungen sind in DE000001008201A , DE000001175653A , DE000002722931A1 , DE102008009679A1 beschrieben. Wesentlicher Nachteil hierbei ist der hohe, bisher ungelöste Verschleiß an den trocken laufenden Kolbenringen. Dieses Problem kann durch die Verwendung von Membranen wie in DE102011007066A1 dargestellt gelöst werden.
Hierbei sind jedoch aufgrund des schwerkraftgetriebenen Befüllens - wie auch bei allen anderen bekannten Staubpumpen und Schleusensystemen - relativ große Querschnitte und Abmessungen erforderlich.For low pressure applications in the range of approx. 0.1 to 0.2 bar pressure increase, screw conveyors with slight bulk material compression and subsequent gas injection are used in practice for pneumatic bulk material conveyance, see DD000000081606A1 , DE000003035745A1 , DE000000656009A , DE000000650988A , DE000000615779A , DE000000596565A , DE000000568999A , DE000000551066A , DE000000485635A , DE000000449676A , DE000000427455A . For somewhat higher pressures up to approx. 0.3 MPa, cellular wheels are used instead of screws, see DE102009016191B4 , DE102009016191A1 . If several dust pumps are connected in series, correspondingly higher pressures can be achieved, but this is associated with a very large outlay on equipment for high-pressure applications, see FIG. DE102008049542B4 , DE102008049542A1 , DE102008007033A1 , WO002010037601A1 , WO002009095290A3 , WO002009095290A2 . In addition to this functional principle of the screw conveyors and cellular wheels, dust pumps based on the principle of compressed air diaphragm pumps are also used, although only low pressures are possible here DE 3909800 A1 .
While dust pumps are used industrially for low pressures, today only lock processes are industrially established for high pressure processes in the order of 1 to 10 MPa, see DE 10 2005 047 583 B4 , DD 147 188 A3 , DE102008052673A1 . In order to reduce the investment and operating costs of such lock systems, dust pumps for high pressure applications are also being developed, the following processes being known:
For high-pressure applications in the order of 1 to 10 MPa, dust pumps based on the principle of the extrusion press are known. The bulk material is mechanically as in an extrusion press in a tapered channel to form a briquette, thereby forming a high pressure barrier from the channel and briquette, which is necessary for sealing between the high and low pressure parts, see US000008851406B2 , US020100021247A1 The disadvantage here is the high wear due to the high friction forces that occur, as well as the problem that the mechanical properties of the bulk material are changed significantly by this process, since the bulk material is present in briquette-like bulk material agglomerations after the pump. Particularly for consumers such as dust combustion or dust gasification, it is then necessary to re-grind under pressure, which represents a problem that has not yet been solved.
In addition to the principle of the extrusion press, the piston pump principle is also known for high-pressure applications. Known designs are in DE000001008201A , DE000001175653A , DE000002722931A1 , DE102008009679A1 described. The main disadvantage here is the high, previously unresolved wear on the dry-running piston rings. This problem can be solved by using membranes as in DE102011007066A1 shown to be solved.
However, due to the gravity-driven filling - as with all other known dust pumps and lock systems - relatively large cross sections and dimensions are required.

Das Dokument US 6 447 216 offenbart eine hydraulisch betriebene Staubpumpe.The document US 6,447,216 discloses a hydraulically operated dust pump.

Das Dokument CH 466 134 offenbart eine hydraulisch betriebene Staubpumpe, welche federkraftbeaufschlagte Ventile aufweist. Die Membran ist vertikal angeordnet.The document CH 466 134 discloses a hydraulically operated dust pump which has spring-loaded valves. The membrane is arranged vertically.

Der Erfindung liegt das Problem zugrunde, einen Pumpenkopf zur pneumatischen Hochdruckförderung von fluidisiertem Schüttgut und ein Verfahren zum Betrieb des Pumpenkopfes anzugeben, bei denen das Schüttgut über den gesamten Pumpvorgang hinweg in einem aufgelockerten, fluidisierten Zustand gehalten wird.The invention is based on the problem of specifying a pump head for the pneumatic high-pressure delivery of fluidized bulk material and a method for operating the pump head, in which the bulk material is kept in a loosened, fluidized state over the entire pumping process.

Das Problem wird durch eine Membranpumpe zur pneumatischen Hochdruckförderung von fluidisierten Stäuben mit den Merkmalen des Patentanspruchs 1 und ein Verfahren zum Betrieb einer solchen Membranpumpe mit den Merkmalen des Patentanspruchs 8 gelöst.The problem is solved by a diaphragm pump for the pneumatic high-pressure delivery of fluidized dusts with the features of patent claim 1 and a method for operating such a diaphragm pump with the features of patent claim 8.

Bei der erfindungsgemäßen Staubpumpe erfolgt die Befüllung durch pneumatisches Ansaugen, wobei das Schüttgut über den gesamten Pumpvorgang hinweg in einem aufgelockerten, fließfähigen Zustand gehalten wird und Staubverdichtungen gezielt vermieden werden. Dabei wird eine in hohem Maße kompakte und damit wirtschaftliche Bauweise erzielt.In the dust pump according to the invention, the filling is carried out by pneumatic suction, the bulk material being kept in a loosened, flowable state throughout the entire pumping process and dust compaction being avoided in a targeted manner. A highly compact and therefore economical construction is achieved.

Das pneumatische Ansaugen hat mehrere entscheidende Vorteile gegenüber bekannten Staubpumpensystemen: Der Querschnitt der Saugleitung 17 und damit die Größe des Einlassventils 8 und der Anschluss am Pumpenkopf fällt im Vergleich zu einer schwerkraftgetriebenen Befüllung wesentlich kleiner aus, wodurch der Pumpenkopf entsprechend kleiner ausgelegt werden kann. Des Weiteren kann die Befüllung von unten in den Staubraum hinein erfolgen. Das hat den Vorteil, dass die Konstruktion des Pumpenkopfes im Bereich der Membran und im Hydraulikbereich vereinfacht ist, da keine Staubdurchführung von oben benötigt wird, was sonst bei Befüllung durch Schwerkraft der Fall wäre. Des Weiteren ist es möglich, die Staubpumpe neben, anstatt unterhalb des Vorlagebunkers 11 zu platzieren, was wiederum Bauhöhe einspart und die Wirtschaftlichkeit solcher Anlagen erhöht. Schließlich ist es durch diese Anordnung möglich, eine sehr große Auflockerungsfläche 4 konstruktiv zu realisieren, was für die Vermeidung von Staubverdichtungen und kurze Zykluszeiten erforderlich ist.Pneumatic suction has several decisive advantages over known dust pump systems: The cross section of the suction line 17 and thus the size of the inlet valve 8 and the connection to the pump head are significantly smaller compared to gravity-driven filling, which means that the pump head can be designed accordingly smaller. Furthermore, the filling can take place from below into the dust chamber. This has the advantage that the design of the pump head in the area of the diaphragm and in the hydraulic area is simplified, since no dust passage from above is required, which would otherwise be the case when filled by gravity. Furthermore, it is possible to place the dust pump next to, rather than below, the storage bunker 11, which in turn saves overall height and increases the economy of such systems. Finally, this arrangement makes it possible to constructively realize a very large loosening area 4, which is necessary to avoid dust densification and short cycle times.

Der in Fig 3 dargestellte Druckübersetzer und damit auch die Trennung des Hydrauliksystems in eine Primärhydraulik 15 - zwischen Druckübersetzer und Hydraulikaggregat - und eine Sekundärhydraulik 16 - zwischen Membran 3 und Druckübersetzer 13 - bieten folgende Vorteile: Der Druck des Hydraulikaggregates kann unabhängig vom Prozessdruck gewählt werden, wodurch kostengünstige Standard-Hydraulikaggregate anstelle von Spezialanfertigungen verwendet werden können. Da in der Regel der Druck des Hydraulikaggregates (20-30 MPa) wesentlich höher als der geforderte Prozessdruck im Staubsystem (1-10 MPa) liegt, sind die Volumenströme im Hydraulikaggregat und damit die Kosten des Hydraulikaggregates deutlich geringer, als würde das Hydraulikaggregat auf den Prozessdruck des Staubsystems ausgelegt werden. Das Druckübersetzungsverhältnis (Primärdruck/Sekundärdruck) liegt damit in der Regel bei circa 2-30. Durch die Verringerung der Volumenströme in der Primärhydraulik und die dort ablaufenden Schaltvorgänge können Druckschläge reduziert oder ganz vermieden werden. Im Falle eines Membranbruches bleibt das Hydraulikaggregat unbeschadet, da Staub dann nur in die Primärhydraulik eindringen kann, nicht aber in die Sekundärhydraulik. Für Primär- und Sekundärhydraulik können unterschiedliche Hydraulikflüssigkeiten verwendet werden, was eine bessere Anpassung an die jeweiligen Prozessbedingungen ermöglicht. Durch die Trennung in Primär- und Sekundärhydraulik wird es möglich, mit einem Hydraulikaggregat mehrere Pumpenköpfe zu betreiben und auch bei Ausfall eines oder mehrerer Pumpenköpfe, die jeweils anderen Pumpenköpfe weiter zu betreiben.The in Fig. 3 The pressure intensifier shown and thus also the separation of the hydraulic system into a primary hydraulic system 15 - between pressure intensifier and hydraulic unit - and a secondary hydraulic system 16 - between membrane 3 and pressure intensifier 13 - offer the following advantages: The pressure of the hydraulic unit can be selected independently of the process pressure, which means that inexpensive standard Hydraulic units can be used instead of custom-made products. Since the pressure of the hydraulic unit (20-30 MPa) is generally much higher than the required process pressure in the dust system (1-10 MPa), the volume flows in the hydraulic unit and thus the costs of the hydraulic unit are significantly lower than if the hydraulic unit were designed for the process pressure of the dust system. The pressure ratio (primary pressure / secondary pressure) is usually around 2-30. By reducing the volume flows in the primary hydraulics and the switching processes taking place there, pressure surges can be reduced or avoided entirely. In the event of a diaphragm rupture, the hydraulic unit remains undamaged, since dust can only penetrate the primary hydraulics, but not the secondary hydraulics. Different hydraulic fluids can be used for primary and secondary hydraulics, which enables better adaptation to the respective process conditions. The separation into primary and secondary hydraulics makes it possible to operate several pump heads with one hydraulic unit and to continue to operate the other pump heads even if one or more pump heads fail.

Ein weiterer Vorteil des gesamten Verfahrens ist, dass der Hochdruck-Gasbedarf gegenüber dem in DE102011007066A1 beschriebenen System nochmals weiter reduziert ist, da einerseits das nach dem Ausfördern noch zu entspannende Totvolumen aufgrund der kleineren Rohrleitungsquerschnitte noch geringer gestaltet werden kann und andererseits beim Ausfördern das vorher zugeführte Bespannungsgas für die pneumatische Förderung mit genutzt wird.Another advantage of the entire process is that the high-pressure gas requirement compared to that in DE102011007066A1 described system is further reduced, because on the one hand the dead volume to be relaxed after the discharge can be made even smaller due to the smaller pipe cross-sections and on the other hand the previously supplied covering gas is also used for the pneumatic conveying during discharge.

In weiterer Ausgestaltung arbeiten mehrere Pumpenköpfe phasenverschoben zueinander. Durch diese Maßnahme wird der Förderprozess vergleichmäßigt.In a further embodiment, several pump heads work out of phase with one another. This measure makes the funding process more even.

In einer besonderen Ausgestaltung wird die Membran durch einen oder mehrere Kolben aber auch Führungsstangen 10 mechanisch geführt, wodurch unerwünschte Verformungen der Membran vermieden werden. Über die Lage des Kolbens beziehungsweise der Führungsstange 10 relativ zum Gehäuse 9 ist eine Positionsmessung der Membran 3 gegeben.In a special embodiment, the membrane is mechanically guided by one or more pistons but also guide rods 10, as a result of which undesired deformations of the membrane are avoided. A position measurement of the diaphragm 3 is given via the position of the piston or the guide rod 10 relative to the housing 9.

Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben.Advantageous developments of the invention are specified in the subclaims.

Die Erfindung wird im Folgenden als Ausführungsbeispiel in einem zum Verständnis erforderlichen Umfang anhand von Figuren näher erläutert. Dabei zeigen:

Fig 1
einen erfindungsgemäßen Pumpenkopf
Fig 2
die wesentlichen Ablaufschritte des Pumpenzyklus' und
Fig 3
die Einbindung mehrerer Pumpenköpfe in ein Staubpumpen-system.
The invention is explained in more detail below as an exemplary embodiment to the extent necessary for understanding with reference to figures. Show:
Fig. 1
a pump head according to the invention
Fig. 2
the essential steps of the pump cycle and
Fig. 3
the integration of several pump heads in a dust pump system.

In den Figuren bezeichnen gleiche Bezeichnungen gleiche Elemente.In the figures, the same designations denote the same elements.

Die erfindungsgemäße Staubpumpe und das damit ausgeführte Verfahren sind für feinkörnige Schüttgüter oder Stäube geeignet, welche sich durch Gaszugabe auflockern und fluidisieren lassen, wie etwa Kohlestaub, und zielt insbesondere auf die Versorgung von druckaufgeladenen Kohlestaubvergasern mit trockener Kohlestaubeinspeisung ab. Die Prozessdrücke liegen hierbei in der Größenordnung von 1 bis 10 MPa. Grundsätzlich kann das Verfahren aber auch für alle anderen Prozesse eingesetzt werden, wo fluidisierbare Stäube trocken auf hohen Druck gepumpt werden sollen.The dust pump according to the invention and the method carried out with it are suitable for fine-grained bulk goods or dusts which can be loosened and fluidized by adding gas, such as coal dust, and are particularly aimed at supplying pressure-charged coal dust gasifiers with dry coal dust feed. The process pressures are of the order of 1 to 10 MPa. In principle, the method can also be used for all other processes where fluidizable dusts are to be pumped dry to high pressure.

Bei dem Pumpenkopf nach Fig 1 befindet sich in einem drucktragenden Gehäuse 9 eine elastische, bewegliche Membran 3, die den Staubraum 1 vom Hydraulikraum 2 hermetisch dicht trennt. Die Membran wird zentrisch über eine Führungsstange 10 geführt und durch Zugabe oder Entnahme von Hydraulikflüssigkeit über die Anschlussleitung 6 nach unten beziehungsweise nach oben bewegt. Staub wird über das Einlassventil 8 in den Staubraum gesaugt und über das Auslassventil 7 aus dem Staubraum herausgefördert. Zur Auflockerung, Be- und Entspannung wird über die Anschlussleitungen 5 und die gasdurchlässigen Auflockerungsflächen 4 Gas zugegeben beziehungsweise abgeführt.At the pump head after Fig. 1 there is an elastic, movable membrane 3 in a pressure-bearing housing 9, which hermetically separates the dust chamber 1 from the hydraulic chamber 2. The membrane is guided centrally over a guide rod 10 and moved down or up by adding or removing hydraulic fluid via the connecting line 6. Dust is sucked into the dust chamber via the inlet valve 8 and conveyed out of the dust chamber via the outlet valve 7. For loosening, loosening and relaxation, gas is added or removed via the connecting lines 5 and the gas-permeable loosening surfaces 4.

In Fig 2 ist der Pumpenzyklus anhand von vier Ablaufschritten A) bis D) dargestellt.In Fig. 2 the pump cycle is shown using four process steps A) to D).

In Schritt A) wird dem Hydraulikraum Flüssigkeit entzogen, wodurch die Membran nach oben gezogen wird und im Staubraum Unterdruck erzeugt wird. Dadurch wird Staub aus dem Vorlagebunker 11 angesaugt. Vorausgesetzt sei, dass der Staub im Vorlagebunker sich durch Gaszugabe in einem fluidisierten Zustand befindet. Während des pneumatischen Einförderns in den Staubraum 1 durch Auslenken der Membran 3 wird ein Unterdruck im Staubraum 1 erzeugt, wodurch die Förderung unterstützt wird.In step A), liquid is withdrawn from the hydraulic chamber, which pulls the membrane upwards and creates a vacuum in the dust chamber. As a result, dust is sucked out of the storage bunker 11. It is assumed that the dust in the feed bunker is in a fluidized state due to the addition of gas. During the pneumatic conveying into the dust chamber 1 by deflecting the membrane 3, a negative pressure is generated in the dust chamber 1, which supports the conveyance.

Wenn die Membran die obere Endlage erreicht hat, wird in Schritt B) durch Schließen der Einlassarmatur 8 und Gaszugabe über die Gasanschlüsse 5 der Staubraum auf den Druck bespannt, welcher durch den Druck des Verbrauchers 20 zuzüglich des pneumatischen Förderdruckverlustes zwischen Pumpenkopf 14 und Verbraucher (circa 0,1 bis 1 MPa) gegeben ist.When the membrane has reached the upper end position, in step B) by closing the inlet fitting 8 and adding gas via the gas connections 5, the dust space is stretched to the pressure caused by the pressure of the consumer 20 plus the pneumatic delivery pressure loss between the pump head 14 and the consumer (approx 0.1 to 1 MPa) is given.

In Schritt C) wird zum Ausfördern die Auslassarmatur 7 geöffnet und der Staub unter Gaszugabe über die Gasanschlüsse 5 herausgefördert. Gleichzeitig wird das Volumen des Staubraumes durch Zugabe von Hydraulikflüssigkeit über den Hydraulikanschluss 6 in den Hydraulikraum, mittels der Membran 3 reduziert.In step C), the outlet fitting 7 is opened for conveying and the dust is conveyed out via the gas connections 5 with the addition of gas. At the same time, the volume of the dust chamber is reduced by adding hydraulic fluid via the hydraulic connection 6 into the hydraulic chamber, by means of the membrane 3.

In Schritt D) wird das konstruktiv unvermeidliche Restvolumen des Staubraumes entspannt und der Pumpenzyklus beginnt mit Schritt A von vorne.In step D), the structurally unavoidable residual volume of the dust chamber is relaxed and the pump cycle begins with step A from the beginning.

Beim Ansaugen des Schüttgutes liegt der Druck im Staubraum 1 circa 0,01 bis 0,08 MPa unterhalb dem Druck im Vorlagebehälter 11 (Förderdifferenzdruck). In einer besonderen Ausgestaltung der Erfindung wird der Unterdruck in dem Staubraum 1 erzeugt, indem Unterdruck über den Gasanschluss 5 angelegt wird. Hierbei wird während des pneumatischen Einförderns von Staub in den Staubraum über das Evakuieren des Staubraumes mittels einer Vakuumpumpe der Förderdifferenzdruck erzeugt. Der über den Gasanschluss (5) angelegte Unterdruck gleicht dem Betrag nach dem Förderdifferenzdruck oder ist ebenso groß wie der Förderdifferenzdruck.When the bulk material is sucked in, the pressure in the dust chamber 1 is approximately 0.01 to 0.08 MPa below the pressure in the storage container 11 (differential pressure). In a special embodiment of the invention, the negative pressure is generated in the dust chamber 1 by applying negative pressure via the gas connection 5. Here, during the pneumatic conveying of dust into the dust space, the evacuation of the dust space the delivery differential pressure is generated by means of a vacuum pump. The negative pressure applied via the gas connection (5) is equal to the amount after the differential pressure or is as large as the differential pressure.

Da ein einzelner Pumpenkopf 14 chargenweise (diskontinuierlich) arbeitet, werden, wie in FIG 3 dargestellt, mehrere Pumpenköpfe zu einem Staubpumpensystem zusammengeschaltet, wobei ein kontinuierlicher Staubförderstrom erzielt werden kann. Hierfür sind mindestens 2 Pumpenköpfe angeordnet. Je nach geforderter Durchsatzleistung und Verfügbarkeitsanforderungen können beliebig viele Pumpenköpfe zusammengeschaltet werden. Sind eine Mehrzahl von n Pumpenköpfen angeordnet, können diese um 2n/n des Pumpenzyklus' gegeneinander phasenverschoben betrieben werden. Neben dem Vorteil der kontinuierlichen Staubförderung kann hierbei das Hydraulikaggregat bei gegebener Durchsatzleistung kleiner dimensioniert werden, als es bei diskontinuierlichem Betrieb der Fall wäre. Bei dieser Ausgestaltung werden auch die Auswirkungen auf das Druckregime des Verbrauchers 20 reduziert.Since a single pump head 14 operates batchwise, as shown in FIG FIG 3 shown, several pump heads connected to a dust pump system, wherein a continuous dust flow can be achieved. At least 2 pump heads are arranged for this. Depending on the required throughput and availability requirements, any number of pump heads can be interconnected. If a plurality of n pump heads are arranged, they can be operated out of phase with one another by 2n / n of the pump cycle. In addition to the advantage of continuous dust delivery, the hydraulic unit can be dimensioned smaller for a given throughput than would be the case with discontinuous operation. With this configuration, the effects on the pressure regime of the consumer 20 are also reduced.

Ein Flugstromvergaser wird mit 100 t/h bei 5 MPa Vergasungsdruck mit Kohlestaub versorgt. Der Druckverlust zwischen Staubpumpe und Vergaser beträgt 1 MPa, womit der Förderdruck bei 6 MPa liegt. Das Staubpumpensystem ist mit n=10 Stück Pumpenköpfen ausgestattet. Ein Pumpenkopf leistet somit 10 t/h. Die Zykluszeit eines Pumpenkopfes beträgt 20 s, wodurch sich ein erforderliches Volumen des Staubraumes zu 0,15 m3 und der Ansaug-Volumenstrom zu 270 m3 /h ergibt. Das Hydraulikaggregat arbeitet bei einem Betriebsdruck von 30 MPa und mit einem Volumenstrom von 54 m3 /h. Da beim Bespannen und Ausfördern weiter Gas zugegeben wird, entspricht der Druckfördervolumenstrom 300 m3 /h. Es ergibt sich ein Hochdruck-Gasbedarf von circa 16.000 Nm3 /h. Dies entspricht einer elektrischen Antriebsleistung des Gasverdichters von circa 2,36 MW. Für ein konventionelles Schleusensystem wären etwa das 2,3-fache, nämlich 36.800 Nm3 /h und 5,43 MW an Verdichterleistung erforderlich. Mit einem Wirkungsgrad des Hydraulikaggregates von 80% ergibt sich die elektrische Leistungsaufnahme der Staubpumpe zu 0,5 MW. In diesem Beispiel wird mit dem hier vorgestellten Staubpumpenprozess gegenüber einem konventionellen Schleusensystem 2,57 MW an Elektroenergie oder 20.800 Nm3 /h Hochdruck-Fördergas eingespart.An entrained-flow gasifier is supplied with coal dust at 100 t / h at 5 MPa gasification pressure. The pressure loss between the dust pump and the carburetor is 1 MPa, which means that the delivery pressure is 6 MPa. The dust pump system is equipped with n = 10 pump heads. A pump head thus achieves 10 t / h. The cycle time of a pump head is 20 s, which results in a required volume of the dust chamber of 0.15 m 3 and the suction volume flow of 270 m 3 / h. The hydraulic unit works at an operating pressure of 30 MPa and with a volume flow of 54 m 3 / h. Since gas is still added during stringing and discharge, the pressure flow volume flow corresponds to 300 m 3 / h. There is a high-pressure gas requirement of approximately 16,000 Nm 3 / h. This corresponds to an electrical drive power of the gas compressor of approximately 2.36 MW. A conventional lock system would require approximately 2.3 times, namely 36,800 Nm 3 / h and 5.43 MW of compressor output. With an efficiency of Hydraulic unit of 80%, the electrical power consumption of the dust pump is 0.5 MW. In this example, the dust pump process presented here saves 2.57 MW of electrical energy or 20,800 Nm 3 / h high-pressure conveying gas compared to a conventional lock system.

In einer besonderen Ausgestaltung der Erfindung sind die Armaturen, nämlich das Auslassventil 7 und das Einlassventil 8, in verschleißfester Ausführung gegeben.In a special embodiment of the invention, the fittings, namely the outlet valve 7 and the inlet valve 8, are given a wear-resistant design.

In einer besonderen Ausgestaltung der Erfindung erfolgt die Bespannung beziehungsweise Entspannung des Staubraumes 1 mit Gas über eine großflächige, gasdurchlässige Auflockerungsfläche 4, die für das staubförmige Schüttgut dicht ist.In a special embodiment of the invention, the dust space 1 is covered or expanded with gas via a large-area, gas-permeable loosening surface 4 which is tight for the dusty bulk material.

In einer besonderen Ausgestaltung der Erfindung ist am Boden des Staubraumes 1 eine großflächige, gasdurchlässige Auflockerungsfläche 4 integriertet, durch welche die Ein- und Ausläufe des zu fördernden Staubes hindurchtreten.In a special embodiment of the invention, a large, gas-permeable loosening surface 4 is integrated at the bottom of the dust chamber 1, through which the inlets and outlets of the dust to be conveyed pass.

In einer besonderen Ausgestaltung der Erfindung ist die Auflockerungsfläche im Verhältnis zur Innenfläche des Staubraumes nach Möglichkeit groß gewählt (mindestens 30% der Innenfläche des Staubraumes), wodurch sich geringere Gasgeschwindigkeiten im Schüttgut ergeben und eine Komprimierung des Schüttgutes vermieden wird.In a special embodiment of the invention, the loosening area in relation to the inner surface of the dust space is chosen to be large if possible (at least 30% of the inner surface of the dust space), which results in lower gas velocities in the bulk material and compression of the bulk material is avoided.

In einer besonderen Ausgestaltung der Erfindung liegt beim Ausfördern des Schüttgutes der Druck im Staubraum circa 0,1 bis 1 MPa über dem Druck des Empfangsbehälters aber auch Dosiergefäß 20.In a special embodiment of the invention, when the bulk material is conveyed out, the pressure in the dust space is approximately 0.1 to 1 MPa above the pressure of the receiving container but also the metering vessel 20.

In einer besonderen Ausgestaltung der Erfindung ist das Hydrauliksystem in eine Primär- und Sekundärhydraulik unterteilt, wobei die Primärhydraulik mit der Membran 3 verbunden ist und von der Sekundärhydraulik über einen Druckübersetzer angetrieben wird. Das Druckübersetzungsverhältnis (Primärdruck/Sekundärdruck) mag circa 2 bis 30 betragen. Die Primär-und Sekundärhydraulik können mit unterschiedlichen Hydraulikflüssigkeiten betrieben werden. Der Druckübersetzer kann als Druckübersetzerkolben ausgeführt sein. Der Druckübersetzer kann durch eine Rückstellfeder zurückstellbar ausgeführt sein, wobei die Rückstellfeder als mechanische Feder oder als pneumatische Gasdruckfeder ausgeführt sein kann.In a special embodiment of the invention, the hydraulic system is divided into primary and secondary hydraulics, the primary hydraulics being connected to the diaphragm 3 and being driven by the secondary hydraulics via a pressure booster. The pressure ratio (primary pressure / secondary pressure) may be approximately 2 to 30. The primary and Secondary hydraulics can be operated with different hydraulic fluids. The pressure intensifier can be designed as a pressure intensifier piston. The pressure intensifier can be designed to be resettable by a return spring, the return spring being able to be designed as a mechanical spring or as a pneumatic gas pressure spring.

In einer besonderen Ausgestaltung der Erfindung sind mindestens zwei Pumpenköpfe zu einem System kombiniert, deren Druckförderleitungen 18 zusammengeführt 19 sind, was eine unterbrechungsfreie Schüttgutförderung ermöglicht.In a special embodiment of the invention, at least two pump heads are combined to form a system, the pressure delivery lines 18 of which are brought together 19, which enables uninterrupted bulk material delivery.

In einer besonderen Ausgestaltung der Erfindung geht aus dem Vorlagebunker 11 eine Saugförderleitung 17 ab, die sich auf mehrere Pumpenköpfe verzweigt.In a special embodiment of the invention, a suction conveyor line 17 branches out of the supply bunker 11 and branches onto several pump heads.

Die vorliegende Erfindung wurde zu Illustrationszwecken anhand von konkreten Ausführungsbeispielen im Detail erläutert. Dabei können Elemente der einzelnen Ausführungsbeispiele auch miteinander kombiniert werden. Die Erfindung soll daher nicht auf einzelne Ausführungsbeispiele beschränkt sein, sondern lediglich eine Beschränkung durch die angehängten Ansprüche erfahren.The present invention has been explained in detail for the purposes of illustration on the basis of specific exemplary embodiments. Elements of the individual exemplary embodiments can also be combined with one another. The invention is therefore not intended to be limited to individual exemplary embodiments, but is only to be limited by the appended claims.

BezugszeichenlisteReference symbol list

11
StaubraumDust room
22nd
HydraulikraumHydraulic room
33rd
Membranmembrane
44th
Gasdurchlässige Auflockerungsfläche, staubdichter FilterGas permeable loosening surface, dustproof filter
55
GasanschlussGas connection
66
HydraulikanschlussHydraulic connection
77
AuslassventilExhaust valve
88th
EinlassventilInlet valve
99
Drucktragendes GehäusePressure-bearing housing
1010th
Membran-FührungsstangeMembrane guide rod
1111
VorlagebunkerStorage bunker
1212
HydraulikaggregatHydraulic unit
1313
DruckübersetzerPressure translator
1414
PumpenkopfPump head
1515
PrimärhydraulikPrimary hydraulics
1616
SekundärhydraulikSecondary hydraulics
1717th
Pneumatische SaugleitungPneumatic suction line
1818th
Pneumatische DruckleitungPneumatic pressure line
1919th
ZusammenführungReunification
2020th
Verbraucher, Empfänger (z. B. Flugstromvergaser, Kohlenstaubbrenner)Consumers, receivers (e.g. entrained-flow gasifier, coal dust burner)
2121st
SchüttgutBulk goods
2222
Gasgas

Claims (13)

  1. Diaphragm pump for the pneumatic high-pressure delivery of 1 to 10 MPa fluidized dusts, in which:
    - a pressure-tight housing (9) is provided,
    - the volume in the housing is divided by a levelly (horizontally) arranged diaphragm (3) into a lower dust chamber (1) and an upper hydraulic chamber (2),
    - the dust chamber has, from below, an entrance for the dust which can be shut off by means of an inlet fitting (8),
    - the dust chamber has, from below, an exit for the dust which can be shut off by means of an outlet fitting (7),
    - at the base of the dust chamber, there is arranged a gas-permeable loosening surface (4) which is connected to a gas port (5),
    - the hydraulic chamber is connected to a hydraulic port (6) for the supply and discharge of hydraulic fluid.
  2. Diaphragm pump as claimed in claim 1,
    characterized in that
    the diaphragm (3) is guided centrally by means of a guide rod (10) .
  3. Diaphragm pump as claimed in any one of the preceding claims,
    characterized in that
    the hydraulic port (6) is connected via a pressure intensifier (13) to a hydraulic assembly (12).
  4. Diaphragm pump as claimed in claim 3,
    characterized in that
    the pressure intensifier (13) is designed as a pressure intensifier piston.
  5. Diaphragm pump as claimed in any one of the preceding claims,
    characterized in that
    the diaphragm pump is arranged at the same height as the hopper (11).
  6. Diaphragm pump as claimed in any one of the preceding claims,
    characterized in that
    the diaphragm pump is provided in a manifold arrangement.
  7. Diaphragm pump as claimed in any one of the preceding claims,
    characterized in that
    the entrance for the dust and the exit for the dust pass through the loosening surface (4).
  8. Method for the pneumatic high-pressure delivery of fluidized dusts by means of a diaphragm pump as claimed in any one of claims 1 to 7, in a dust delivery device,
    in which
    - the dust delivery device comprises a hopper (11),
    - the hopper (11) contains fluidized dust in bulk material form,
    - the outlet of the hopper (11) is connected via a pneumatic suction line (17) to the inlet fitting (8) of the diaphragm pump,
    whereupon
    - the diaphragm (3) is hydraulically deflected upward, a negative pressure is generated in the dust chamber (1) and fluidized dust is drawn into the dust chamber (1) via the opened inlet fitting (8),
    - the inlet fitting (8) is closed,
    - the dust chamber (1) is charged to the required high pressure with gas via the gas port (5),
    - the outlet fitting (7) is opened,
    - the dust is delivered out of the dust chamber (1) by means of a feed of gas via the gas port (5), while at the same time the volume of the dust chamber is reduced by hydraulic deflection of the diaphragm (3) downward.
  9. Method as claimed in claim 8,
    characterized in that
    the dust chamber (1) is relieved of pressure.
  10. Method as claimed in any one of the preceding claims 8 to 9 and claim 6,
    characterized in that
    the pump cycles of the diaphragm pumps take place in a phase-offset manner with respect to one another.
  11. Method as claimed in any one of claims 7 to 10,
    characterized in that
    the negative pressure in the dust chamber (1) is generated by virtue of negative pressure being applied via the gas port (5) .
  12. Method as claimed in claim 11,
    characterized in that
    a negative pressure equal in magnitude to the delivery pressure differential is applied via the gas port (5).
  13. Method as claimed in any one of the preceding claims,
    characterized in that
    the hopper (11) is at atmospheric pressure.
EP16822973.0A 2016-01-27 2016-12-20 Diaphragm pump comprising dust suction from below Active EP3390818B1 (en)

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DE102016201182.0A DE102016201182A1 (en) 2016-01-27 2016-01-27 Diaphragm pump with dust suction from below
PCT/EP2016/081838 WO2017129327A1 (en) 2016-01-27 2016-12-20 Diaphragm pump comprising dust suction from below

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EP (1) EP3390818B1 (en)
CN (1) CN108603498B (en)
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DE102016201182A1 (en) 2016-01-27 2017-07-27 Siemens Aktiengesellschaft Diaphragm pump with dust suction from below
DE102016216006A1 (en) 2016-08-25 2018-03-01 Siemens Aktiengesellschaft Double membrane for a dust pump
DE102016216016A1 (en) 2016-08-25 2018-03-15 Siemens Aktiengesellschaft Production of a porous aluminum filter for a membrane pump
DE102016216012A1 (en) 2016-08-25 2018-03-01 Siemens Aktiengesellschaft Diaphragm pump with porous, curved aluminum filter

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US20190063419A1 (en) 2019-02-28
CN108603498B (en) 2020-05-22
DE102016201182A1 (en) 2017-07-27
US10914299B2 (en) 2021-02-09
EP3390818A1 (en) 2018-10-24
CN108603498A (en) 2018-09-28

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