EP3308019B1 - Reciprocating piston pump with input-side flow rate limitation - Google Patents

Reciprocating piston pump with input-side flow rate limitation Download PDF

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Publication number
EP3308019B1
EP3308019B1 EP16739020.2A EP16739020A EP3308019B1 EP 3308019 B1 EP3308019 B1 EP 3308019B1 EP 16739020 A EP16739020 A EP 16739020A EP 3308019 B1 EP3308019 B1 EP 3308019B1
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EP
European Patent Office
Prior art keywords
throttle
piston
reciprocating pump
displacement chamber
filter
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EP16739020.2A
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German (de)
French (fr)
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EP3308019A1 (en
Inventor
Olaf OHLIGSCHLÄGER
Thomas Rolland
Jeannette Kemper
Axel MÜLLER
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Thomas Magnete GmbH
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Thomas Magnete 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves

Definitions

  • the invention relates to a reciprocating pump according to the preamble of claim 1.
  • the invention further relates to a method for operating a reciprocating pump according to the preamble of claim 12.
  • DE 10 2014 000 627 B3 shows a reciprocating pump, comprising a movable by an electromagnet against a return spring piston which separates a first displacement chamber and a second displacement chamber, wherein the two displacement chambers are interconnected by a spill valve means.
  • An exhaust valve connects the second displacer with an outlet, while the first displacer is connected to an inlet through a throttle.
  • the throttle can be closed by a seal connected to the piston when the piston is under the load of the return spring in its inlet-side end position.
  • Reciprocating pumps with electromagnetic drive are known, for example DE 43 28 621 A1 and DE 10 2008 055 609 B4 , If such a reciprocating pump to be used to receive fluid from a pressurized housing needs, an input-side flow restriction is required so that the pressure in the housing does not affect the function of the reciprocating pump.
  • a cost-effective reciprocating pump should have an input-side pressure reduction and / or flow limitation and should work reliably even with liquids of different composition with pollution by small particles.
  • the reciprocating pump is an electromagnetically driven pump with two displacement chambers, which is flowed through by the liquid to be delivered.
  • the flow rate of the reciprocating pump is limited according to this invention by a throttle or orifice.
  • a pressure may be present, which is higher than the maximum value of the pressure in the input-side first displacement chamber for trouble-free operation of the reciprocating pump.
  • the said throttle is also used to lower the pressure in the first displacement chamber to a permissible level, when the theoretical flow rate of the pump, which is equal to the product of the stroke volume of the single stroke and the frequency, is greater than the inflow through the throttle , In this working state of the pump, the real flow rate is also smaller than said product, the reciprocating pump gets even further in the state of a cavitation induced flow reduction, because not enough liquid flows in the suction in the second displacement. The cavitation does not cause any damage in this case because the pressure is low.
  • the throttle ultimately determines the flow rate of the reciprocating pump.
  • the throttle In the case of the pump stall, the throttle is closed by a spring, which also returns the piston of the pump to its rest position, presses a seal by means of the piston against the throttle.
  • the throttle In order to achieve the described effect, the throttle must have a very small effective diameter at a high pressure in said housing. Chokes with a very small effective diameter (eg less than 0.5 mm) tend to block because every technical fluid contains particles that have not been filtered out by an upstream filter.
  • the shock wave is caused on the one hand by the striking and on the other hand by an invagination of the seal in the throttle.
  • a throttle is used with a movable insert, which is displaced against a spring with each impact of the piston and its movement prevents the blockage.
  • a pressure relief valve in the piston of the reciprocating pump is optionally provided, which limits the pressure difference between the first and the second displacement to a value that is only so high that the function of the reciprocating pump always secured remains.
  • the reciprocating pump is operated at the start of its operation with a higher than usual voltage.
  • the reciprocating pump (1) accordingly Fig. 1 is driven by an electromagnet (2) acting against a return spring (11).
  • the reciprocating pump includes two displacement chambers (3, 4), which are separated by a piston (5) moved by the electromagnet, and an overflow valve device (6) for connecting the two displacement chambers with each other and an outlet valve (7).
  • the first displacement chamber (3) is connected to an inlet (9) through a throttle (8), the throttle (8) being closed by a seal (24) connected to the piston (5) when the piston (5) moves located in its inlet-side end position.
  • the force of the return spring (11) is greater than the pressure force resulting from the pressure at the inlet (9) and the Effective area (25) of this pressure between the throttle (8) and the seal (24) results when the seal (24) rests on the throttle (8).
  • the stroke of the piston (5) is designed so that the piston (5) by means of the seal (24) alsani on the throttle (8) when in the non-driven state of the electromagnet (2) the return spring (11) the piston (5) brings to its rest position.
  • the effective inner diameter D of the throttle (8) is designed so that in one of the electromagnet (2) caused working stroke of the piston (5) from the second displacement chamber (4) to the outlet geometrie employment displaceable liquid volume is greater than that at the same time because of the pressure difference between the inlet (9) and the first displacement chamber (3) through the throttle (8) during the working cycle of the piston (5) in the first displacement chamber (3) inflow volume.
  • the flow rate of the reciprocating pump from the throttle (8) and not by the displacement effect of the piston (5) is limited, and in the first displacement chamber (3) sets a pressure that is considerably lower than the pressure at the inlet, for example, less than 1 bar.
  • the throttle (8) has, for example, an effective inner diameter D which is greater than or equal to 0.1 mm and less than or equal to 1 mm.
  • the length of the throttle bore (12) is preferably less than or equal to 50 * D and greater than or equal to 5 * D, so that predominantly laminar flow is achieved in the throttle.
  • a shutter which has a bore length shorter than D.
  • a filter (10) with a nominal filter fineness of less than D / 4 upstream of the throttle (8) is provided.
  • the filter (10) in a housing part (13) of the reciprocating pump is arranged so that the pumped liquid on the way from the inlet (9) to the throttle (8) must pass completely through the filter.
  • the filter (10) outside the housing part (13) of the reciprocating pump in a filter housing (14) is arranged, being ensured by the connection of the housing of the reciprocating pump with the filter housing (14) that only such liquid to the throttle (8) that has previously passed the filter (10).
  • the throttle (8) is corresponding Fig. 2 designed as a screw-threaded body with a first thread, wherein the body is screwed into a second thread, which is mounted in the housing part (13). Alternatively, said body is pressed into the housing part.
  • the throttle (8) consists of at least two components, a sleeve (20) and an insert (21), wherein the insert (21) in the sleeve (20) is movable.
  • a flow path (23) is arranged between the insert (21) and the sleeve (20).
  • the insert (21) is held by its own weight or a spring (22) in its rest position and pressed by the piston (5) in a working position when in the idle state of the electromagnet (2), the return spring (11) the piston in its rest position brings.
  • the piston (5) contains a pressure limiting valve (not shown) which, when a limiting pressure difference between the first displacer space (3) and the second displacer space (4), exceeds a volume flow between the first displacer space (3) and the second displacer space (FIG. 4) releases.
  • the reciprocating pump is corresponding Fig. 3 arranged in a vertical or nearly vertical position below the filter housing (14).

Description

Die Erfindung betrifft eine Hubkolbenpumpe entsprechend dem Oberbegriff des Patentanspruchs 1. Die Erfindung betrifft ferner ein Verfahren zum Betrieb einer Hubkolbenpumpenach dem Oberbegriff des Patentanspruchs 12.The invention relates to a reciprocating pump according to the preamble of claim 1. The invention further relates to a method for operating a reciprocating pump according to the preamble of claim 12.

DE 10 2014 000 627 B3 zeigt eine Hubkolbenpumpe, umfassend einen durch einen Elektromagneten entgegen einer Rückstellfeder bewegbaren Kolben, der einen ersten Verdrängerraum und einen zweiten Verdrängerraum trennt, wobei die beiden Verdrängerräume durch eine Überströmventileinrichtung miteinander verbunden sind. Ein Auslassventil verbindet den zweiten Verdrängerraum mit einem Auslass, während der erste Verdrängerraum durch eine Drossel mit einem Einlass verbunden ist. Hierbei ist die Drossel durch eine mit dem Kolben verbundene Dichtung verschließbar, wenn der Koben sich unter der Last der Rückstellfeder in seiner einlassseitigen Endlage befindet. DE 10 2014 000 627 B3 shows a reciprocating pump, comprising a movable by an electromagnet against a return spring piston which separates a first displacement chamber and a second displacement chamber, wherein the two displacement chambers are interconnected by a spill valve means. An exhaust valve connects the second displacer with an outlet, while the first displacer is connected to an inlet through a throttle. In this case, the throttle can be closed by a seal connected to the piston when the piston is under the load of the return spring in its inlet-side end position.

Hubkolbenpumpen mit elektromagnetischem Antrieb sind bekannt, zum Beispiel aus DE 43 28 621 A1 und DE 10 2008 055 609 B4 . Wenn eine solche Hubkolbenpumpe dazu verwendet werden soll, Flüssigkeit aus einem unter Druck stehenden Gehäuse bedarfsgerecht aufzunehmen, ist eine eingangsseitige Förderstrombegrenzung erforderlich, damit der Druck in dem Gehäuse die Funktion der Hubkolbenpumpe nicht beeinträchtigt.Reciprocating pumps with electromagnetic drive are known, for example DE 43 28 621 A1 and DE 10 2008 055 609 B4 , If such a reciprocating pump to be used to receive fluid from a pressurized housing needs, an input-side flow restriction is required so that the pressure in the housing does not affect the function of the reciprocating pump.

Dazu könnte man ein eingangsseitiges Druckminderventil verwenden, wie es in DE 10 2014 000 627 B3 dargestellt ist. Diese Lösung ist aber für diese Anwendung aufwendiger und kostspieliger als erforderlich.You could use an input-side pressure reducing valve, as in DE 10 2014 000 627 B3 is shown. However, this solution is more expensive and more expensive than necessary for this application.

Bei jeglicher Drosselung des Zuflusses oder des Abflusses stellt sich immer das Problem, dass bei sehr kleinen Querschnitten für die Strömung eine Verstopfung des Querschnitts mit Partikeln in der Flüssigkeit droht.With any throttling of the inflow or outflow, there is always the problem that with very small cross-sections for the flow a blockage of the cross section with particles in the liquid threatens.

Es ist die Aufgabe der Erfindung, eine verbesserte Hubkolbenpumpe und ein verbessertes Verfahren zum Betrieb einer Hubkolbenpumpe anzugeben.It is the object of the invention to provide an improved reciprocating pump and an improved method for operating a reciprocating pump.

Eine kostengünstige Hubkolbenpumpe soll eine eingangsseitige Druckreduzierung und/oder Förderstrombegrenzung aufweisen und soll auch mit Flüssigkeiten unterschiedlicher Zusammensetzung auch mit Verschmutzung durch kleine Partikel zuverlässig arbeiten.A cost-effective reciprocating pump should have an input-side pressure reduction and / or flow limitation and should work reliably even with liquids of different composition with pollution by small particles.

Die Aufgabe wird erfindungsgemäß durch eine Hubkolbenpumpe mit den Merkmalen des Anspruchs 1 bzw. durch ein Verfahren mit den Merkmalen des Anspruchs 12 gelöst. Vorteilhafte Weiterbildungen sind in den abhängigen Ansprüchen angegeben.The object is achieved by a reciprocating pump with the features of claim 1 and by a method having the features of claim 12. Advantageous developments are specified in the dependent claims.

Die Hubkolbenpumpe ist eine elektromagnetisch angetriebene Pumpe mit zwei Verdrängerräumen, die von der zu fördernden Flüssigkeit durchströmt wird.The reciprocating pump is an electromagnetically driven pump with two displacement chambers, which is flowed through by the liquid to be delivered.

Der Förderstrom der Hubkolbenpumpe wird gemäß dieser Erfindung durch eine Drossel oder eine Blende begrenzt.The flow rate of the reciprocating pump is limited according to this invention by a throttle or orifice.

In dem genannten Gehäuse kann ein Druck anstehen, der höher ist als der Maximalwert des Drucks in dem eingangsseitigen ersten Verdrängerraum für eine störungsfreie Funktion der Hubkolbenpumpe.In said housing, a pressure may be present, which is higher than the maximum value of the pressure in the input-side first displacement chamber for trouble-free operation of the reciprocating pump.

In diesem Fall dient die genannte Drossel auch dazu, den Druck im ersten Verdrängerraum auf ein zulässiges Maß abzusenken, wenn die theoretische Fördermenge der Pumpe, die gleich dem Produkt aus dem Hubvolumen des Einzelhubs und der Frequenz ist, größer ist als der Zufluss durch die Drossel. In diesem Arbeitszustand der Pumpe ist die reale Fördermenge auch kleiner als das genannte Produkt, die Hubkolbenpumpe gerät noch weiter in den Zustand einer kavitationsbedingten Förderstromreduzierung, weil beim Ansaugen in den zweiten Verdrängerraum nicht genügend Flüssigkeit nachströmt. Die Kavitation richtet in diesem Fall keinen Schaden an, weil der Druck niedrig ist. Die Drossel bestimmt letztlich die Fördermenge der Hubkolbenpumpe.In this case, the said throttle is also used to lower the pressure in the first displacement chamber to a permissible level, when the theoretical flow rate of the pump, which is equal to the product of the stroke volume of the single stroke and the frequency, is greater than the inflow through the throttle , In this working state of the pump, the real flow rate is also smaller than said product, the reciprocating pump gets even further in the state of a cavitation induced flow reduction, because not enough liquid flows in the suction in the second displacement. The cavitation does not cause any damage in this case because the pressure is low. The throttle ultimately determines the flow rate of the reciprocating pump.

Im Fall des Stillstands der Pumpe wird die Drossel verschlossen, indem eine Feder, die auch den Kolben der Pumpe in seine Ruhestellung zurückstellt, eine Dichtung mittels des Kolbens gegen die Drossel drückt.In the case of the pump stall, the throttle is closed by a spring, which also returns the piston of the pump to its rest position, presses a seal by means of the piston against the throttle.

Wenn die Wirkfläche dieses Andrückens klein genug ist, kann auch eine Rückstellfeder mit geringer Kraft eine sichere Abdichtung gegen einen hohen Druck bewirken.If the effective area of this Andrückens is small enough, even a return spring with little force can cause a secure seal against high pressure.

Um die beschriebene Wirkung zu erzielen, muss die Drossel bei einem hohen Druck im genannten Gehäuse einen sehr kleinen Wirkdurchmesser haben. Drosseln mit einem sehr kleinen Wirkdurchmesser (z. B. weniger als 0,5 mm) neigen zur Verstopfung, da jede technische Flüssigkeit Partikel enthält, die von einem vorgelagerten Filter nicht herausgefiltert wurden.In order to achieve the described effect, the throttle must have a very small effective diameter at a high pressure in said housing. Chokes with a very small effective diameter (eg less than 0.5 mm) tend to block because every technical fluid contains particles that have not been filtered out by an upstream filter.

Eine solche Verstopfung wird dadurch verhindert, dass der genannte Kolben regelmäßig mittels einer Dichtung auf die Drossel aufschlägt. Bei jedem Aufschlag entsteht eine Stoßwelle in der Flüssigkeit, die sich in der Drossel befindet, und diese Stoßwelle verhindert die Verstopfung.Such a blockage is prevented by the fact that said piston strikes regularly by means of a seal on the throttle. At each impact, there is a shock wave in the fluid in the throttle, and this shock wave prevents clogging.

Die Stoßwelle wird einerseits durch das Anschlagen und andererseits durch ein Einstülpen der Dichtung in die Drossel bewirkt.The shock wave is caused on the one hand by the striking and on the other hand by an invagination of the seal in the throttle.

Reichen die Stoßwellen wegen einer stärkeren Belastung der Flüssigkeit mit Partikeln nicht aus, wird eine Drossel mit beweglichem Einsatz verwendet, der bei jedem Aufschlagen des Kolbens gegen eine Feder verschoben wird und durch seine Bewegung die Verstopfung verhindert.If the shock waves are insufficient due to a greater load on the liquid with particles, a throttle is used with a movable insert, which is displaced against a spring with each impact of the piston and its movement prevents the blockage.

Wenn durch Erschütterungen im Betrieb der Hubkolbenpumpe oder durch andere Ursachen die Abdichtung zwischen dem Kolben und der Drossel im Ruhezustand der Hubkolbenpumpe undicht wird, kommt es zu einer die Funktion der Abdichtung beeinträchtigenden Druckerhöhung im ersten Verdrängerraum, was dann auch eine Funktionsstörung der Hubkolbenpumpe zur Folge hätte.If the seal between the piston and the throttle in the idle state of the reciprocating pump is leaking due to vibrations during operation of the reciprocating pump or other causes, it comes to a function of the sealing impeding pressure increase in the first displacement, which would then also a malfunction of the reciprocating pump result ,

Wenn die Pumpe auch für längere Zeit im Ruhezustand verbleiben soll, ist gegebenenfalls ein Druckbegrenzungsventil im Kolben der Hubkolbenpumpe vorzusehen, das die Druckdifferenz zwischen dem ersten und dem zweiten Verdrängerraum auf einen Wert begrenzt, der nur so hoch ist, dass die Funktion der Hubkolbenpumpe immer gesichert bleibt.If the pump is to remain at rest for a long time, a pressure relief valve in the piston of the reciprocating pump is optionally provided, which limits the pressure difference between the first and the second displacement to a value that is only so high that the function of the reciprocating pump always secured remains.

Alternativ wird die Hubkolbenpumpe bei dem Start ihres Betriebs mit einer höhen als sonst üblichen Spannung betrieben.Alternatively, the reciprocating pump is operated at the start of its operation with a higher than usual voltage.

Die erfindungsgemäße Hubkolbenpumpe wird zum Ablassen oder Absaugen von Flüssigkeit aus einem Filtergehäuse, einem Wasserabscheider oder aus einem anderen Behälter verwendet, vorzugsweise an Dieselmotoren in Fahrzeugen.

  • Fig. 1 zeigt die erfindungsgemäße Hubkolbenpumpe mit dem Kolben in Ruhelage.
  • Fig. 2 zeigt eine Variante der Hubkolbenpumpe mit eingeschraubter Drossel.
  • Fig. 3 zeigt eine Variante der Hubkolbenpumpe, die an ein Filtergehäuse angeschraubt ist.
  • Fig. 4 zeigt eine Variante der Drossel im Detail.
The reciprocating piston pump according to the invention is used for draining or sucking off liquid from a filter housing, a water separator or from another container, preferably to diesel engines in vehicles.
  • Fig. 1 shows the reciprocating piston pump according to the invention with the piston in rest position.
  • Fig. 2 shows a variant of the reciprocating pump with screwed throttle.
  • Fig. 3 shows a variant of the reciprocating pump, which is screwed to a filter housing.
  • Fig. 4 shows a variant of the throttle in detail.

Beispielhafte AusführungExemplary embodiment

Die Hubkolbenpumpe (1) entsprechend Fig. 1 wird durch einen Elektromagneten (2) angetrieben, der gegen eine Rückstellfeder (11) wirkt.
Die Hubkolbenpumpe enthält zwei Verdrängerräume (3, 4), die durch einen von dem Elektromagneten bewegten Kolben (5) getrennt sind, sowie eine Überströmventileinrichtung (6) zur Verbindung der beiden Verdrängerräume miteinander und ein Auslassventil (7).The reciprocating pump (1) accordingly Fig. 1 is driven by an electromagnet (2) acting against a return spring (11).
The reciprocating pump includes two displacement chambers (3, 4), which are separated by a piston (5) moved by the electromagnet, and an overflow valve device (6) for connecting the two displacement chambers with each other and an outlet valve (7).

Der erste Verdrängerraum (3) ist durch eine Drossel (8) mit einem Einlass (9) verbunden, wobei die Drossel (8) durch eine mit dem Kolben (5) verbundene Dichtung (24) verschlossen wird, wenn der Kolben (5) sich in seiner einlassseitigen Endlage befindet. Dabei ist die Kraft der Rückstellfeder (11) größer als die Druckkraft, die sich aus dem Druck an dem Einlass (9) und der Wirkfläche (25) dieses Drucks zwischen der Drossel (8) und der Dichtung (24) ergibt, wenn die Dichtung (24) auf der Drossel (8) aufliegt. Durch dieses Abschließen des Zuflusses im Stillstand der Hubkolbenpumpe wird ein Druckaufbau im ersten Verdrängerraum verhindert.The first displacement chamber (3) is connected to an inlet (9) through a throttle (8), the throttle (8) being closed by a seal (24) connected to the piston (5) when the piston (5) moves located in its inlet-side end position. The force of the return spring (11) is greater than the pressure force resulting from the pressure at the inlet (9) and the Effective area (25) of this pressure between the throttle (8) and the seal (24) results when the seal (24) rests on the throttle (8). By completing the inflow at standstill of the reciprocating pump, a pressure build-up in the first displacement chamber is prevented.

Der Hub des Kolbens (5) ist so ausgelegt, dass der Kolben (5) mittels der Dichtung (24) auf die Drossel (8) aufschlägt, wenn im antriebslosen Zustand des Elektromagneten (2) die Rückstellfeder (11) den Kolben (5) in seine Ruhelage bringt.The stroke of the piston (5) is designed so that the piston (5) by means of the seal (24) aufschlägt on the throttle (8) when in the non-driven state of the electromagnet (2) the return spring (11) the piston (5) brings to its rest position.

Der wirksame Innendurchmesser D der Drossel (8) ist so ausgelegt, dass bei einem von dem Elektromagneten (2) bewirkten Arbeitshub des Kolbens (5) das aus dem zweiten Verdrängerraum (4) zum Auslass geometriebedingt verdrängbare Flüssigkeitsvolumen größer ist als das gleichzeitig wegen der Druckdifferenz zwischen dem Einlass (9) und dem ersten Verdrängerraum (3) durch die Drossel (8) während des Arbeitsspiels des Kolbens (5) in den ersten Verdrängerraum (3) nachströmende Volumen. Damit wird die Fördermenge der Hubkolbenpumpe von der Drossel (8) und nicht von der Verdrängungswirkung des Kolbens (5) begrenzt, und im ersten Verdrängerraum (3) stellt sich ein Druck ein, der erheblich geringer ist als der Druck am Einlass, beispielsweise weniger als 1 bar.The effective inner diameter D of the throttle (8) is designed so that in one of the electromagnet (2) caused working stroke of the piston (5) from the second displacement chamber (4) to the outlet geometriebedingt displaceable liquid volume is greater than that at the same time because of the pressure difference between the inlet (9) and the first displacement chamber (3) through the throttle (8) during the working cycle of the piston (5) in the first displacement chamber (3) inflow volume. Thus, the flow rate of the reciprocating pump from the throttle (8) and not by the displacement effect of the piston (5) is limited, and in the first displacement chamber (3) sets a pressure that is considerably lower than the pressure at the inlet, for example, less than 1 bar.

Die Drossel (8) weist beispielsweise einen wirksamen Innendurchmesser D auf, der größer gleich 0,1 mm und kleiner gleich 1 mm ist.The throttle (8) has, for example, an effective inner diameter D which is greater than or equal to 0.1 mm and less than or equal to 1 mm.

Die Länge der Drosselbohrung (12) ist vorzugsweise kleiner gleich 50*D und größer gleich 5*D, damit wird überwiegend laminare Strömung in der Drossel erreicht.The length of the throttle bore (12) is preferably less than or equal to 50 * D and greater than or equal to 5 * D, so that predominantly laminar flow is achieved in the throttle.

Alternativ wird eine Blende verwendet, die eine Bohrungslänge aufweist, die kürzer als D ist.Alternatively, a shutter is used which has a bore length shorter than D.

Vorteilhafterweise ist ein Filter (10) mit einer nominalen Filterfeinheit von weniger als D/4 der Drossel (8) vorgeschaltet.Advantageously, a filter (10) with a nominal filter fineness of less than D / 4 upstream of the throttle (8).

In einer ersten Ausführung ist der Filter (10) in einem Gehäuseteil (13) der Hubkolbenpumpe so angeordnet, dass die geförderte Flüssigkeit auf dem Weg vom Einlass (9) zur Drossel (8) vollständig den Filter passieren muss.In a first embodiment, the filter (10) in a housing part (13) of the reciprocating pump is arranged so that the pumped liquid on the way from the inlet (9) to the throttle (8) must pass completely through the filter.

In einer zweiten Ausführung (Fig. 3) ist der Filter (10) außerhalb des Gehäuseteils (13) der Hubkolbenpumpe in einem Filtergehäuse (14) angeordnet, wobei durch die Verbindung des Gehäuses der Hubkolbenpumpe mit dem Filtergehäuse (14) sichergestellt ist, dass nur solche Flüssigkeit zur Drossel (8) gelangt, die vorher den Filter (10) passiert hat.In a second embodiment ( Fig. 3 ), the filter (10) outside the housing part (13) of the reciprocating pump in a filter housing (14) is arranged, being ensured by the connection of the housing of the reciprocating pump with the filter housing (14) that only such liquid to the throttle (8) that has previously passed the filter (10).

Vorteilhafterweise ist die Drossel (8) entsprechend Fig. 2 als einschraubbarer Körper mit einem ersten Gewinde ausgeführt, wobei der Körper in ein zweites Gewinde eingeschraubt ist, das in dem Gehäuseteil (13) angebracht ist. Alternativ ist der genannte Körper in das Gehäuseteil eingepresst.Advantageously, the throttle (8) is corresponding Fig. 2 designed as a screw-threaded body with a first thread, wherein the body is screwed into a second thread, which is mounted in the housing part (13). Alternatively, said body is pressed into the housing part.

In einer vorteilhaften Ausführung entsprechend Fig. 4 besteht die Drossel (8) aus mindestens zwei Bauteilen, einer Hülse (20) und einem Einsatz (21), wobei der Einsatz (21) in der Hülse (20) beweglich ist. Dabei ist zwischen dem Einsatz (21) und der Hülse (20) ein Strömungspfad (23) angeordnet. Der Einsatz (21) wird durch sein Eigengewicht oder eine Feder (22) in seiner Ruhelage gehalten und durch den Kolben (5) in eine Arbeitsstellung gedrückt, wenn im antriebslosen Ruhezustand des Elektromagneten (2) die Rückstellfeder (11) den Kolben in seine Ruhelage bringt.In an advantageous embodiment accordingly Fig. 4 the throttle (8) consists of at least two components, a sleeve (20) and an insert (21), wherein the insert (21) in the sleeve (20) is movable. In this case, a flow path (23) is arranged between the insert (21) and the sleeve (20). The insert (21) is held by its own weight or a spring (22) in its rest position and pressed by the piston (5) in a working position when in the idle state of the electromagnet (2), the return spring (11) the piston in its rest position brings.

In einer weiteren vorteilhaften Ausführung enthält der Kolben (5) ein nicht gezeigtes Druckbegrenzungsventil, das bei einer Überschreitung einer Grenzdruckdifferenz zwischen dem ersten Verdrängerraum (3) und dem zweiten Verdrängerraum (4) einen Volumenstrom zwischen dem ersten Verdrängerraum (3) und dem zweiten Verdrängerraum (4) freigibt.In a further advantageous embodiment, the piston (5) contains a pressure limiting valve (not shown) which, when a limiting pressure difference between the first displacer space (3) and the second displacer space (4), exceeds a volume flow between the first displacer space (3) and the second displacer space (FIG. 4) releases.

Vorteilhafterweise ist die Hubkolbenpumpe entsprechend Fig. 3 in senkrechter oder nahezu senkrechter Lage unterhalb des Filtergehäuses (14) angeordnet.Advantageously, the reciprocating pump is corresponding Fig. 3 arranged in a vertical or nearly vertical position below the filter housing (14).

Claims (14)

  1. Reciprocating pump (1) driven by an electromagnet (2) which counteracts a return spring (11), comprising a first displacement chamber (3) and a second displacement chamber (4) which are separated by a piston (5) that is moved by the electromagnet (2), comprising an overflow valve device (6) for interconnecting the two displacement chambers (3, 4), and comprising an outlet valve (7) for connecting the second displacement chamber (4) to an outlet, the first displacement chamber (3) being connected to an inlet (9) by means of a throttle (8), the throttle (8) being closed off when the piston (5) is in its inlet-side end position by means of a seal (24) connected to the piston (5),
    characterized in
    that an effective internal diameter D of the throttle (8) is designed such that, during a power stroke of the piston (5) from the second displacement chamber (4) caused by the electromagnet (2), the volume of liquid that can be displaced, which is dependent on the geometry, towards the outlet by the piston (5) is greater than the volume of liquid flowing into the first displacement chamber (3) via the throttle (8) due to the pressure difference between the inlet (9) and the first displacement chamber (3) during a working cycle of the piston (5).
  2. Reciprocating pump according to claim 1, characterized in that the force of the return spring (11) is greater than a compressive force that results from pressure at the inlet (9) and an effective area (25) of said pressure between the throttle (8) and the seal (24) when the seal (24) abuts the throttle (8).
  3. Reciprocating pump according to either claim 1 or claim 2, characterized in that the length of a throttling port (12) of the throttle (8) is less than or equal to 50*D and greater than or equal to 5*D.
  4. Reciprocating pump according to any of claims 1 to 3, characterized in that a filter (10) having a nominal filter fineness of less than D/4 is arranged upstream of the throttle (8).
  5. Reciprocating pump according to claim 4, characterized in that the filter (10) is arranged in a housing part (13) of the reciprocating pump such that the conveyed fluid has to completely pass through the filter (10) on the way from the inlet (9) to the throttle (8).
  6. Reciprocating pump according to claim 4, characterized in that the filter (10) is arranged in a filter housing (14) outside the housing part (13) of the reciprocating pump, the connection of the housing of the reciprocating pump to the filter housing (14) ensuring that only liquid that has already passed through the filter (10) reaches the throttle (8).
  7. Reciprocating pump according to claim 6, characterized in that the reciprocating pump is arranged in a perpendicular or virtually perpendicular position below the filter housing (14).
  8. Reciprocating pump according to any of claims 1 to 7, characterized in that the throttle (8) is rigidly connected to the housing part (13) either by an internal and external thread or by means of a press-fit assembly.
  9. Reciprocating pump according to any of claims 1 to 8, characterized in that the throttle (8) consists of at least two components, a sleeve (20) and an insert (21), the insert (21) being movable in the sleeve (20), a flow path (23) being arranged between the insert (21) and the sleeve (20), and the insert (21) being held in the rest position thereof by means of the dead weight thereof and/or by means of a spring (22) and being pushed into a working position by the piston (5) when the return spring (11) brings the piston (5) into the rest position thereof in the undriven rest state of the electromagnet (2).
  10. Reciprocating pump according to any of claims 1 to 9, characterized in that the piston (5) contains a pressure relief valve which enables a volume flow between the first displacement chamber (3) and the second displacement chamber (4) when a threshold pressure difference between the first displacement chamber (3) and the second displacement chamber (4) is exceeded.
  11. Reciprocating pump according to any of claims 1 to 10, characterized in that the effective internal diameter D of the throttle (8) is greater than or equal to 0.1 mm and less than or equal to 1 mm.
  12. Method for operating a reciprocating pump, driven by an electromagnet (2) which counteracts a return spring (11), comprising a first displacement chamber (3) and a second displacement chamber (4) which are separated by a piston (5) that is moved by the electromagnet (2), comprising an overflow valve device (6) for interconnecting the two displacement chambers (3, 4), and comprising an outlet valve (7) for connecting the second displacement chamber (4) to an outlet, the piston (5) sealing a throttle (8) between the inlet (9) and the first displacement chamber (3) using the force of the return spring (11) when the reciprocating pump (1) is at a standstill,
    characterized in
    that the pressure in the first displacement chamber (3) is kept considerably lower than the pressure in the inlet (9), and
    that during a stroke of the piston (5) the volume of liquid that can be displaced, which is dependent on the geometry, by the piston (5) is greater than the influx of liquid through the throttle (8) during a working cycle of the piston (5).
  13. Method according to claim 12, characterized in that the conveyed liquid flows through a filter (10) arranged upstream of the throttle (3) and the piston (5) regularly strikes the throttle (8) and thus prevents particle deposition.
  14. Method according to claim 12, characterized in that particle deposition is prevented in or upstream of the throttle (8) by the piston (5) regularly pushing an insert (21) in the throttle (8) when the return spring (11) brings the piston into the rest position thereof in the undriven rest state of the electromagnet (2).
EP16739020.2A 2015-06-09 2016-06-06 Reciprocating piston pump with input-side flow rate limitation Active EP3308019B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015007464.4A DE102015007464A1 (en) 2015-06-09 2015-06-09 Reciprocating pump with inlet-side flow limitation
PCT/EP2016/000932 WO2016198156A1 (en) 2015-06-09 2016-06-06 Reciprocating piston pump with input-side flow rate limitation

Publications (2)

Publication Number Publication Date
EP3308019A1 EP3308019A1 (en) 2018-04-18
EP3308019B1 true EP3308019B1 (en) 2019-01-23

Family

ID=56413610

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16739020.2A Active EP3308019B1 (en) 2015-06-09 2016-06-06 Reciprocating piston pump with input-side flow rate limitation

Country Status (3)

Country Link
EP (1) EP3308019B1 (en)
DE (1) DE102015007464A1 (en)
WO (1) WO2016198156A1 (en)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1358832A (en) * 1963-06-06 1964-04-17 Controls Co Of America Electric pump
CS273485B1 (en) * 1988-10-20 1991-03-12 Stanislav Kucera Electromagnetic piston pump
DE4328621C2 (en) 1993-08-26 2002-11-28 Thomas Magnete Gmbh Electromagnetically operated pump, in particular metering pump
DE102006019584B4 (en) * 2006-04-27 2008-06-05 Thomas Magnete Gmbh metering
DE102008055609B4 (en) 2008-11-03 2011-12-29 Thomas Magnete Gmbh reciprocating pump
DE102014000627B3 (en) 2014-01-17 2015-05-21 Thomas Magnete Gmbh Dosing pump with pressure regulator for suction pressure as well as procedures for testing, adjusting and operating the dosing pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102015007464A1 (en) 2016-12-15
EP3308019A1 (en) 2018-04-18
WO2016198156A1 (en) 2016-12-15

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