EP0139709B1 - Double acting reciprocating piston pump - Google Patents

Double acting reciprocating piston pump Download PDF

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Publication number
EP0139709B1
EP0139709B1 EP84901584A EP84901584A EP0139709B1 EP 0139709 B1 EP0139709 B1 EP 0139709B1 EP 84901584 A EP84901584 A EP 84901584A EP 84901584 A EP84901584 A EP 84901584A EP 0139709 B1 EP0139709 B1 EP 0139709B1
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EP
European Patent Office
Prior art keywords
piston
piston rod
pump
cylinder
drive
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Expired
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EP84901584A
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German (de)
French (fr)
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EP0139709A1 (en
Inventor
Ernst Korthaus
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Individual
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Individual
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Priority to AT84901584T priority Critical patent/ATE29273T1/en
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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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/02—Arrangements for cooling cylinders or cylinder heads

Definitions

  • the invention relates to a double-acting reciprocating piston pump for conveying liquids with occasional idling without liquid, the piston pump having a piston provided with a piston seal, which reciprocates in the pump cylinder and which is connected to a piston rod which forms a cylinder head wall of the Penetrates the pump housing, is sealed by means of a seal and the piston rod is driven hydraulically.
  • a problem with such piston pumps is that they are safe to run dry. When the pump runs dry, there is a risk that the packings in the area of the pump piston and the stuffing box will overheat and burn, particularly if relatively large sealing pressures are required.
  • a pressurized water generator with commercially available seals for the hydraulic drive can be found in the DE-AS 23 34 245 which has become known. Neither stuffing box packs are provided in the known pressurized water generator, nor can liquids containing solids be conveyed with it.
  • the invention proposes, starting from a piston pump of the type mentioned, that the piston seal and the pump housing seal are stuffing boxes, the cylindrical walls of the pump cylinder are provided with cavities, the piston rod has at least one cavity and the cavities are connected to at least one liquid circuit are.
  • the inventive design of the piston rod and the cylindrical walls of the pump cylinder and the formation of the seals have the consequence that the bezw with the piston rod.
  • the cylindrical walls of the pump cylinder in contact with the sealing surfaces of the stuffing box packs are continuously cooled immediately, so that the packing material cannot burn even when the pump is running dry. Since the coolant is encapsulated in the cavities in relation to the interior of the pump cylinder, no coolant can get into the interior of the pump cylinder.
  • the highly thermally conductive metallic walls between the friction surfaces and the coolant can dissipate the heat generated when the piston pump runs dry much faster than the poorly thermally conductive packing material.
  • An advantageous embodiment of the piston pump according to the invention provides that the piston rod of the pump piston is hollow and at the same time serves as a cylinder part of the hydraulic drive cylinder, which is slidably mounted on the fixed drive piston and the drive piston rod connected to it.
  • this results in the advantage of a particularly short overall length, so that the entire pump unit with drive can be made particularly short.
  • Another particular advantage is that in this embodiment the outside of the piston rod of the pump piston does not come into contact with the hydraulic drive medium, so that there is no risk that hydraulic drive medium will be introduced into the pump cylinder.
  • This embodiment in particular is therefore suitable for conveying food.
  • the hydraulic drive medium is supplied to the hydraulic drive cylinder via the fixed drive piston rod and the fixed drive piston, which are provided with corresponding feed bores.
  • the fixed piston is expediently provided on both end faces with shock absorbers for end position damping. This prevents jerky blows when the end positions are reached.
  • the shock absorbers consist appropriately Rubber rings that lie inside on the drive piston rod or on a corresponding cylindrical extension on the full surface of the drive piston and leave an annular space with a defined volume on the inner wall of the cylinder part of the drive cylinder, which is deformed when the rubber rings are deformed when they stop at the ends of the cylinder part with rubber compound fills, which becomes practically inelastic after the annular gap has been completely filled.
  • shock absorbers are simple in construction and are practically not subject to wear.
  • the rubber rings can of course also be provided at the ends of the cylinder part and leave a corresponding annular gap with a defined volume towards the drive piston rod.
  • piston pump provides that the piston rod of the pump cylinder is at the same time the drive piston rod of the drive cylinder, the cylinder part of which is arranged in a fixed manner and receives the drive piston connected to the drive piston rod in a longitudinally displaceable manner, the piston rod consisting of an outer tube and a concentrically radial one therein There is a spaced inner tube and the hydraulic drive medium flows through the annular space between the outer tube and the inner tube and the interior of the inner tube at least during part of the stroke.
  • This embodiment of the piston pump according to the invention has the advantage over the first embodiment of the piston pump according to the invention that the drive piston can have an arbitrarily large diameter, so that greater drive forces can be applied.
  • the drive piston rod has a second drive piston at an axial distance from the drive piston so that the interior of the inner tube with the annular space between the two drive pistons is connected that the annular space between the inner tube and outer tube of the drive piston rod is connected directly next to the second drive piston with the annular space between the drive piston rod and the cylinder part of the drive cylinder and that two pressure medium connections are provided in the wall of the cylinder part of the drive cylinder, the pressure medium connections of which Distance in the axial direction corresponds to the axial length of the second drive piston, the distance between the cylinder cover of the drive cylinder and the first pressure medium connection being smaller or is equal to the axial distance between the two drive pistons.
  • the housing of the piston pump is designated by the reference numeral 1.
  • the pump housing 1 has two suction chambers 2 and 3 and a pressure chamber 4, which are connected to one or the other end of a pump cylinder 9 via check valves 5 and 6 or 7 and 8.
  • a double-acting pump piston 10 can be pushed back and forth in the pump cylinder 9.
  • the pump piston 10 is sealed against the inner wall of the pump cylinder 9 by annular packings 11.
  • the packs 11 preferably consist of a self-lubricating, dry-running material.
  • the cylindrical walls of the pump cylinder 9 are provided with through openings 9 a extending over the entire axial length for a cooling liquid flowing through them.
  • a piston rod 12 is attached to the pump piston 10 and is guided through a stuffing box 13.
  • the piston rod 12 of the pump piston 10 is hollow and accommodates a fixed drive piston 14 which is connected to a likewise fixed drive piston rod 15.
  • the hollow piston rod 12 is guided on the fixed drive piston 14 and its likewise fixed drive piston rod 15 and together with this forms the double-acting drive cylinder 12, 14, 15, the cylinder part (piston rod 12) of which is axially displaceable.
  • Bores 16 and 17 in the fixed drive piston rod 15 and the fixed drive piston 14 serve to alternately act upon the pressure chambers of the drive cylinder 12, 14, 15 with the hydraulic drive medium.
  • the hydraulic drive medium is supplied by a hydraulic circuit 18 which has a pump 18a, a changeover valve 18b and a reservoir 18c.
  • the through openings 9a are in the cylindrical Walls of the pump cylinder 9, the bores 16 and 17 and the pressure chambers of the drive cylinder 12, 14, 15 included.
  • the hydraulic drive medium cools both the cylindrical walls of the pump cylinder 9 and the piston rod 12 over their entire length, so that the heat generated on the friction surfaces of the packs 11 and 13a is continuously and intensively dissipated. This constant cooling prevents the packs from burning even if they run dry for a long time.
  • the pump according to the invention is therefore absolutely safe to run dry.
  • FIG. 2 fully corresponds to the embodiment according to FIG. 1 as far as the parts belonging to the pump housing and pump piston 10 are concerned, so that the same reference numerals have been used for the corresponding parts.
  • the piston rod 12 of the pump piston 10 also serves as the drive piston rod of the drive cylinder and is therefore connected to a double-acting drive piston 21, which is mounted in a fixed longitudinally displaceable cylinder part 22.
  • the piston rod 12 consists of an outer tube 12 a and an inner tube 12 b, which are arranged concentrically with one another at a radial distance are.
  • the interior 12c of the inner tube 12b and the annular space 12d between the outer tube 12a and the inner tube 12b form a passage opening through which the drive medium flows, so that the piston rod 12 can be cooled to the required extent.
  • the piston rod 12 has a second drive piston 23 at an axial distance from the drive piston 21. Furthermore, the interior of the inner tube 12 b is connected to the annular space between the two drive pistons 21 and 23 in a pressure medium-conducting manner. Likewise, the annular space between the outer tube 12 a and the inner tube 12 b is connected directly next to the second drive piston 23 to the annular space between the piston rod 12 and the cylinder part 21 of the drive cylinder 22, 21, 12.
  • FIG. 3 corresponds to the embodiment of FIG. 2 with regard to the design of the pump cylinder 9, the pump piston 10 and the piston rod 12, so that the same reference numerals have been used for the corresponding parts.
  • the piston rod 12 here also consists of an outer tube 12a and an inner tube 12b, which are arranged concentrically one inside the other at a radial distance.
  • the interior 12c of the inner tube 12 and the annular space 12d between the outer tube 12a and the inner tube 12b form passage openings for a cooling medium which is fed into the piston rod 12 from a separate coolant circuit 26.
  • the passage openings 9a are also included in the cylindrical walls of the pump cylinder 9.
  • the separate coolant circuit 26 contains a coolant pump 26a and a reservoir 26b.
  • the pumping piston 10 is driven by a separate hydraulic drive cylinder 27, the piston rod 28 of which is attached to the extreme end of the piston rod 12.
  • the separate hydraulic working cylinder 27 is shared by a separate hydraulic circuit 29 Pressure medium supplied, which has a hydraulic pump 29a, a reservoir 29b and a changeover valve 29c.
  • Another drive unit, which drives the piston rod 12 of the piston pump back and forth, can optionally take the place of the drive cylinder 27.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Piston pump of which the pumping piston (10) is made tight with respect to the pumping cylinder (9) by means of linings (11) and which is connected to a piston rod (12) guided in a packing box (13) joined to the cover of the pumping cylinder (9) and which is driven according to a reciprocating motion. In order to protect such a piston pump against the burning of the linings (11, 13a) of the pumping piston (10) and of the packing box (13) when operating in dry conditions, the present invention proposes to provide the piston rod (12) and the cylindrical walls of the pumping cylinder (9) throughout their length with passage openings (9a; 12c, 12d) to allow a cooling medium to pass through. When the piston pump is hydraulically operated, the hydraulic driving medium is also used as cooling medium.

Description

Die Erfindung betrifft eine doppeltwirkende hin- und hergehende Kolbenpumpe zum Fördern von Flüssigkeiten mit zeitweisem Leerlauf ohne Flüssigkeit, wobei die Kolbenpumpe einen mit einer Kolbendichtung versehenen Kolben aufweist, welcher im Pumpenzylinder hin- und hergeht und welcher verbunden ist mit einer Kolbenstange, die eine Zylinderkopfwand des Pumpengehäuses durchdringt, abgedichtet wird mittels einer Dichtung und wobei die Kolbenstange hydraulisch angetrieben wird.The invention relates to a double-acting reciprocating piston pump for conveying liquids with occasional idling without liquid, the piston pump having a piston provided with a piston seal, which reciprocates in the pump cylinder and which is connected to a piston rod which forms a cylinder head wall of the Penetrates the pump housing, is sealed by means of a seal and the piston rod is driven hydraulically.

Pumpen des Oberbegriffs wurden zum Prioritätsdatum in der Praxis verwendet, wie z. B. GEHO Hydraulik-Schlammpumpen.Pumps of the generic term were used in practice on the priority date, e.g. B. GEHO hydraulic slurry pumps.

Ein problem bei derartigen Kolbenpumpen besteht darin, sie trockenlaufsicher zu machen. Beim Trockenlauf der Pumpe besteht nämlich die Gefahr, daß die Packungen im Bereich des Pumpkolbens und der Stopfbuchse überhitzt werden und verbrennen, insbesondere, wenn verhältnismäßig große Abdichtdrücke erforderlich sind.A problem with such piston pumps is that they are safe to run dry. When the pump runs dry, there is a risk that the packings in the area of the pump piston and the stuffing box will overheat and burn, particularly if relatively large sealing pressures are required.

Aus der US-PS 27 51 144 ist ein Apparat für die Kompression von Gasen bekannt, der als Kolbenkompressor mit Kolbenringen hydraulisch angetrieben wird. Bei solch einem Gaskompressor tritt das Problem eines zeitweisen Trockanlaufs nicht auf.From US-PS 27 51 144 an apparatus for the compression of gases is known which is hydraulically driven as a piston compressor with piston rings. With such a gas compressor, the problem of a temporary dry start does not arise.

Nach der BE-PS 423 910 ist ein mechanisch angetriebener Kolben-Gaskompressor mit Kolbenringen bekannt. Auch hier tritt das Problem eines zeitweisen Trockenlaufs nicht auf.According to BE-PS 423 910, a mechanically driven piston gas compressor with piston rings is known. The problem of occasional dry running does not arise here either.

Aus der bekanntgewordenen DE-AS 23 34 245 ist ein Preßwassererzeuger mit handelsüblichen Dichtungen für den hydraulischen Antrieb zu entnehmen. Es sind weder Stopfbuchspackungen bei dem bekannten Preßwassererzeuger vorgesehen, noch lassen sich mit diesem Flüssigkeiten, die Feststoffe enthalten, fördern.A pressurized water generator with commercially available seals for the hydraulic drive can be found in the DE-AS 23 34 245 which has become known. Neither stuffing box packs are provided in the known pressurized water generator, nor can liquids containing solids be conveyed with it.

Nachdem Flüssigkeitspumpen allgemein keiner Kühlung bedürfen, ist dem vorstehend erläuterten Stand der Technik keine übertragbare Lehre auf das der Erfindung zugrunde liegende Problem zu entnehmen.Since liquid pumps generally do not require cooling, no transferable teaching to the problem on which the invention is based can be gathered from the prior art explained above.

Es ist deshalb Aufgabe der Erfindung, die Kolbenpumpe der eingangs genannten Art mit Dichtungen dahingehend weiterzubilden, daß sie im Bereich der Dichtungen über lange Zeiträume beim Fördern von mit Feststoffen beladenen Flüssigkeiten trocken laufsicher ist, ohne daß Hydraulikflüssigkeit in den Pumpzylinder gelangt.It is therefore an object of the invention to further develop the piston pump of the type mentioned at the outset with seals in such a way that it is dry-running in the area of the seals over long periods of time when liquids containing solids are being conveyed without hydraulic fluid getting into the pump cylinder.

Zur Lösung dieser Aufgabe schlägt die Erfindung ausgehend von einer Kolbenpumpe der eingangs genannten Art vor, daß die Kolbendichtung und die Pumpengehäusedichtung Stopfbuchspackungen sind, die zylindrischen Wandungen des Pumpenzylinders mit Hohlräumen versehen sind, die Kolbenstange mindestens einen Hohlraum aufweist und die Hohlräume an mindestens einen Flüssigkeitskreislauf angeschlossen sind.To achieve this object, the invention proposes, starting from a piston pump of the type mentioned, that the piston seal and the pump housing seal are stuffing boxes, the cylindrical walls of the pump cylinder are provided with cavities, the piston rod has at least one cavity and the cavities are connected to at least one liquid circuit are.

Die erfindungsgemäß vorgeschlagene Ausbildung der Kolbenstange und der zylindrischen Wandungen des Pumpzylinders und die Ausbildung der Dichtungen haben zur Folge, daß die mit der Kolbenstange bezw. den zylindrischen Wandungen das Pumpzylinders in Berührung stehenden Dichtflächen der Stopfbuchspackungen ständig unmittelbar gekühlt werden, so daß das Packungsmaterial auch bei Trockenlauf der Pumpe nicht verbrennen kann. Da die Kühlflüssigkeit in den Hohlräumen gegenüber dem Innenraum des Pumpzylinders abgekapselt ist, kann keine Kühlflüssigkeit in den Innenraum des Pumpzylinders gelangen. Die gut wärmeleitfähigen metallischen Wandungen zwischen den Reibungsflächen und der Kühlflüssigkeit können die beim Trockenlauf der Kolbenpumpe entstehende Wärme wesentlich schneller abführen als das schlecht wärmeleitfähige Packungsmaterial.The inventive design of the piston rod and the cylindrical walls of the pump cylinder and the formation of the seals have the consequence that the bezw with the piston rod. the cylindrical walls of the pump cylinder in contact with the sealing surfaces of the stuffing box packs are continuously cooled immediately, so that the packing material cannot burn even when the pump is running dry. Since the coolant is encapsulated in the cavities in relation to the interior of the pump cylinder, no coolant can get into the interior of the pump cylinder. The highly thermally conductive metallic walls between the friction surfaces and the coolant can dissipate the heat generated when the piston pump runs dry much faster than the poorly thermally conductive packing material.

Besondere Vorteile ergeben sich darüber hinaus dadurch, daß ein gesonderter Kühlmittelkreislauf nicht mehr erforderlich ist. Zur Kühlung wird vorzugsweise der in diesem Fall ohnehin vorhandene Hydraulikkreislauf verwendet.Special advantages also result from the fact that a separate coolant circuit is no longer required. For cooling, the hydraulic circuit which is present in any case is preferably used.

Eine zweckmäßige Ausführungsform der Kolbenpumpe gemäß der Erfindung sieht vor, daß die Kolbenstange des Pumpkolbens hohl ausgebildet ist und zugleich als Zylinderteil des hydraulischen Antriebszylinders dient, der verschiebbar auf dem feststehenden Antriebskolben und der mit diesem verbundenen Antriebskolbenstange gelagert ist. Neben einer ständigen Kühlung der Kolbenstange des Pumpzylinders ergibt sich hierdurch der Vorteil einer besonders kurzen Baulänge, so daß das gesamte Pumpaggregat mit Antrieb besonders kurzbauend ausgeführt werden kann. Ein weiterer besonderer Vorteil liegt darin, daß bei dieser Ausführungsform die Außenseite der Kolbenstange des Pumpkolbens nicht mit dem hydraulischen Antriebsmedium in Berührung kommt, so daß keinerlei Gefahr besteht, daß hydraulisches Antriebsmedium in den Pumpzylinder eingeschleppt wird. Insbesondere diese Ausführungsform ist deshalb für die Förderung von Lebensmitteln geeignet.An advantageous embodiment of the piston pump according to the invention provides that the piston rod of the pump piston is hollow and at the same time serves as a cylinder part of the hydraulic drive cylinder, which is slidably mounted on the fixed drive piston and the drive piston rod connected to it. In addition to constant cooling of the piston rod of the pump cylinder, this results in the advantage of a particularly short overall length, so that the entire pump unit with drive can be made particularly short. Another particular advantage is that in this embodiment the outside of the piston rod of the pump piston does not come into contact with the hydraulic drive medium, so that there is no risk that hydraulic drive medium will be introduced into the pump cylinder. This embodiment in particular is therefore suitable for conveying food.

Um bei der zuletzt genannten Ausführungsform bewegliche Druckmittelanschlüsse zu vermeiden, ist weiterhin vorgesehen, daß das hydraulische Antriebsmedium dem hydraulischen Antriebszylinder über die feststehende Antriebskolbenstange und den feststehenden Antriebskolben zugeführt wird, die mit entsprechenden Zuführungsbohrungen versehen sind.In order to avoid movable pressure medium connections in the last-mentioned embodiment, it is further provided that the hydraulic drive medium is supplied to the hydraulic drive cylinder via the fixed drive piston rod and the fixed drive piston, which are provided with corresponding feed bores.

Weil bei der zuletzt genannten Ausführungsform verhältnismäßig große Massen hin- und herbewegt werden müssen, ist zweckmäßig der feststehende Kolben an beiden Stirnflächen mit Stoßdämpfern für eine Endlagendämpfung versehen. Hierdurch werden ruckartige Schläge bei Erreichen der Endlagen vermieden.Because relatively large masses have to be moved back and forth in the last-mentioned embodiment, the fixed piston is expediently provided on both end faces with shock absorbers for end position damping. This prevents jerky blows when the end positions are reached.

Die Stoßdämpfer bestehen zweckmäßig aus Gummiringen, die innen an der Antriebskolbenstange bzw. an einer dieser entsprechenden zylindrischen Verlängerung an der Vollfläche des Antriebskolbens anliegen und zur Innenwand des Zylinderteiles des Antriebszylinders einen Ringraum mit definiertem Volumen belassen, der sich beim Verformen der Gummiringe beim Anschlag an den Enden des Zylinderteiles mit Gummimasse füllt, die nach vollständiger Füllung des Ringspaltes praktisch unelastisch wird. Derartige Stoßdämpfer sind einfach im Aufbau und unterliegen praktisch keinem Verschleiß. In kinematischer Umkehr können die Gummiringe selbstverständlich auch an den Enden des Zylinderteiles vorgesehen sein und einen entsprechenden Ringspalt mit definiertem Volumen zur Antriebskolbenstange hin freilassen.The shock absorbers consist appropriately Rubber rings that lie inside on the drive piston rod or on a corresponding cylindrical extension on the full surface of the drive piston and leave an annular space with a defined volume on the inner wall of the cylinder part of the drive cylinder, which is deformed when the rubber rings are deformed when they stop at the ends of the cylinder part with rubber compound fills, which becomes practically inelastic after the annular gap has been completely filled. Such shock absorbers are simple in construction and are practically not subject to wear. In kinematic reversal, the rubber rings can of course also be provided at the ends of the cylinder part and leave a corresponding annular gap with a defined volume towards the drive piston rod.

Eine andere Ausführungsform der Kolbenpumpe gemäß der Erfindung sieht vor, daß die Kolbenstange des Pumpzylinders zugleich die Antriebskolbenstange des Antriebszylinders ist, dessen Zylinderteil feststehend angeordnet ist und den mit der Antriebskolbenstange verbundenen Antriebskolben längsverschiebbar aufnimmt, wobei die Kolbenstange aus einem Außenrohr und einem darin konzentrisch mit radialem Abstand angeordneten Innenrohr besteht und der Ringraum zwischen dem Außenrohr und dem Innenrohr sowie der Innenraum des Innenrohres zumindest während eines Teiles des Hubes vom hydraulischen Antriebsmedium durchströmt werden.Another embodiment of the piston pump according to the invention provides that the piston rod of the pump cylinder is at the same time the drive piston rod of the drive cylinder, the cylinder part of which is arranged in a fixed manner and receives the drive piston connected to the drive piston rod in a longitudinally displaceable manner, the piston rod consisting of an outer tube and a concentrically radial one therein There is a spaced inner tube and the hydraulic drive medium flows through the annular space between the outer tube and the inner tube and the interior of the inner tube at least during part of the stroke.

Diese Ausführungsform der Kolbenpumpe gemäß der Erfindung hat gegenüber der ersten Ausführungsform der Kolbenpumpe gemäß der Erfindung den Vorteil, daß der Antriebskolben einen beliebig großen Durchmesser erhalten kann, so daß größere Antriebskräfte aufgebracht werden können.This embodiment of the piston pump according to the invention has the advantage over the first embodiment of the piston pump according to the invention that the drive piston can have an arbitrarily large diameter, so that greater drive forces can be applied.

Um zu erreichen, daß das hydraulische Antriebsmedium des hydraulischen Antriebszylinders die gemeinsame Kolbenstange zumindest während eines Teiles des Antriebshubes durchströmt, ist vorgesehen, daß die Antriebskolbenstange mit axialem Abstand zum Antriebskolben einen zweiten Antriebskolben aufweist, daß der Innenraum des Innenrohres mit dem Ringraum zwischen den beiden Antriebskolben verbunden ist, daß der Ringraum zwischen Innenrohr und Außenrohr der Antriebskolbenstange unmittelbar neben dem zweiten Antriebskolben mit dem Ringraum zwischen der Antriebskolbenstange und dem Zylinderteil des Antriebszylinders verbunden ist und daß in der Wandung des Zylinderteiles des Antriebszylinders zwei an eine gemeinsame Druckmittelleitung angeschlossene Druckmittelanschlüsse vorgesehen sind, deren Abstand in axialer Richtung der axialen Länge des zweiten Antriebskolbens entspricht, wobei der Abstand zwischen dem Zylinderdeckel des Antriebszylinders und dem ersten Druckmittelanschluß kleiner oder gleich dem axialen Abstand zwischen den beiden Antriebskolben ist. Der besondere Vorteil dieser Maßnahmen liegt darin, daß der gemeinsamen Kolbenstange von Antriebszylinder und Pumpzylinder eine zur Kühlung ausreichende Menge des hydraulischen Arbeitsmediums zugeführt werden kann, ohne daß ein mit der Kolbenstange beweglicher Druckmittelanschluß vorgesehen werden muß.In order to ensure that the hydraulic drive medium of the hydraulic drive cylinder flows through the common piston rod at least during part of the drive stroke, it is provided that the drive piston rod has a second drive piston at an axial distance from the drive piston so that the interior of the inner tube with the annular space between the two drive pistons is connected that the annular space between the inner tube and outer tube of the drive piston rod is connected directly next to the second drive piston with the annular space between the drive piston rod and the cylinder part of the drive cylinder and that two pressure medium connections are provided in the wall of the cylinder part of the drive cylinder, the pressure medium connections of which Distance in the axial direction corresponds to the axial length of the second drive piston, the distance between the cylinder cover of the drive cylinder and the first pressure medium connection being smaller or is equal to the axial distance between the two drive pistons. The particular advantage of these measures is that the common piston rod of the drive cylinder and the pump cylinder can be supplied with a sufficient amount of the hydraulic working medium for cooling without a pressure medium connection movable with the piston rod having to be provided.

Ein Ausführungsbeispiel der Erfindung wird im folgenden anhand der Zeichnung näher erläutert.An embodiment of the invention is explained below with reference to the drawing.

Es zeigen:

  • Fig. einen horizontalen Schnitt durch eine Kolbenpumpe gemäß der Erfindung in einer ersten Ausführungsform;
  • Fig. einen horizontalen Schnitt durch eine Kolbenpumpe gemäß der Erfindung in einer zweiten Ausführungsform.
  • Fig. einen horizontalen Schnitt durch eine Kolbenpumpe gemäß der Erfindung in einer dritten Ausführungsform.
Show it:
  • Fig. A horizontal section through a piston pump according to the invention in a first embodiment;
  • Fig. A horizontal section through a piston pump according to the invention in a second embodiment.
  • Fig. A horizontal section through a piston pump according to the invention in a third embodiment.

In Figur 1 ist das Gehäuse der Kolbenpumpe mit dem Bezugszeichen 1 bezeichnet. Das Pumpengehäuse 1 weist zwei Ansaugkammern 2 und 3 sowie eine Druckkammer 4 auf, die über Rückschlagventile 5 und 6 bzw. 7 und 8 mit dem einen bzw. dem anderen Ende eines Pumpzylinders 9 verbunden sind.In Figure 1, the housing of the piston pump is designated by the reference numeral 1. The pump housing 1 has two suction chambers 2 and 3 and a pressure chamber 4, which are connected to one or the other end of a pump cylinder 9 via check valves 5 and 6 or 7 and 8.

In dem Pumpzylinder 9 ist ein doppeltwirkender Pumpkolben 10 hin- und herverschiebbar. Der Pumpkolben 10 ist durch ringförmige Packungen 11 gegen die Innenwand des Pumpzylinders 9 abgedichtet. Die Packungen 11 bestehen vorzugsweise aus einem selbstschmierenden trockenlauffähigen Material. Die zylindrischen Wandungen des Pumpzylinders 9 sind mit sich über die gesamte axiale Länge erstreckenden Durchtrittsöffnungen 9a für eine sie durchströmende Kühlflüssigkeit versehen.A double-acting pump piston 10 can be pushed back and forth in the pump cylinder 9. The pump piston 10 is sealed against the inner wall of the pump cylinder 9 by annular packings 11. The packs 11 preferably consist of a self-lubricating, dry-running material. The cylindrical walls of the pump cylinder 9 are provided with through openings 9 a extending over the entire axial length for a cooling liquid flowing through them.

An dem Pumpkolben 10 ist eine Kolbenstange 12 befestigt, die durch eine Stopfbüchse 13 hindurchgeführt ist. Die Kolbenstange 12 des Pumpkolbens 10 ist hohl ausgebildet und nimmt einen feststehenden Antriebskolben 14 in sich auf, der mit einer ebenfalls feststehenden Antriebskolbenstange 15 verbunden ist. Die hohle Kolbenstange 12 ist auf dem feststehenden Antriebskolben 14 und dessen ebenfalls feststehender Antriebskolbenstange 15 geführt und bildet mit dieser zusammen den doppeltwirkenden Antriebszylinder 12,14,15, dessen Zylinderteil (Kolbenstange 12) axial verschiebbar ist. Zur abwechselnden Beaufschlagung der Druckräume des Antriebszylinders 12, 14, 15 mit dem hydraulischen Antriebsmedium dienen Bohrungen 16 und 17 in der feststehenden Antriebskolbenstange 15 und dem feststehenden Antriebskolben 14.A piston rod 12 is attached to the pump piston 10 and is guided through a stuffing box 13. The piston rod 12 of the pump piston 10 is hollow and accommodates a fixed drive piston 14 which is connected to a likewise fixed drive piston rod 15. The hollow piston rod 12 is guided on the fixed drive piston 14 and its likewise fixed drive piston rod 15 and together with this forms the double-acting drive cylinder 12, 14, 15, the cylinder part (piston rod 12) of which is axially displaceable. Bores 16 and 17 in the fixed drive piston rod 15 and the fixed drive piston 14 serve to alternately act upon the pressure chambers of the drive cylinder 12, 14, 15 with the hydraulic drive medium.

Das hydraulische Antriebsmedium wird von einem Hydraulikkreislauf 18 geliefert, der eine Pumpe 18a, ein Umschaltventil 18b und einen Vorratsbehälter 18c aufweist. In diesen Hydraulikkreislauf 18 sind die Durchtrittsöffnungen 9a in den zylindrischen Wandungen des Pumpzylinders 9, die Bohrungen 16 und 17 und die Druckräume des Antriebszyinders 12, 14, 15 einbezogen. Auf diese Weise kühlt das hydraulische Antriebsmedium sowohl die zylindrischen Wandungen des Pumpzylinders 9 als auch die Kolbenstange 12 jeweils über deren gesamte Länge, so daß die an den Reibflächen der Packungen 11 bzw. 13a entstehende Wärme ständig und intensiv abgeführt wird. Durch diese ständige Kühlung wird verhindert, daß die Packungen auch bei lang andauerndem Trockenlauf verbrennen. Die Pumpe gemäß der Erfindung ist also absolut trockenlaufsicher.The hydraulic drive medium is supplied by a hydraulic circuit 18 which has a pump 18a, a changeover valve 18b and a reservoir 18c. In this hydraulic circuit 18, the through openings 9a are in the cylindrical Walls of the pump cylinder 9, the bores 16 and 17 and the pressure chambers of the drive cylinder 12, 14, 15 included. In this way, the hydraulic drive medium cools both the cylindrical walls of the pump cylinder 9 and the piston rod 12 over their entire length, so that the heat generated on the friction surfaces of the packs 11 and 13a is continuously and intensively dissipated. This constant cooling prevents the packs from burning even if they run dry for a long time. The pump according to the invention is therefore absolutely safe to run dry.

Für die Endlagendämpfung der verhältnismäßig schweren hin- und hergehenden Kolbenstange 12 sind an beiden Stirnflächen des feststehenden Antriebskolbens 14 Gummiringe 19 und 20 vorgesehen, die am Außenumfang der Antriebskolbenstange 15 bzw. einer dieser entsprechenden zylindrischen Verlängerung 14 a des Kolbens 14 anliegen und zur Innenwand der Kolbenstange 12 (Zylinderteil des Antriebszylinders 12, 14, 15) einen Ringspalt mit genau definierten Volumen belassen. Beim Anstoß des feststehenden Kolbens 14 an den inneren Enden des Hohlraumes der axial bewegten Kolbenstange 12 verformen sich diese Gummiringe so lange elastisch, bis sie den Ringspalt vollständig ausfüllen und ein praktisch unelastisches Kissen bilden. Auf diese Weise ergibt sich mit verhältnismäßig geringem Aufwand eine hochwirksame und praktisch verschleißfrei arbeitende Endlagendämpfung.For the end position damping of the relatively heavy reciprocating piston rod 12 14 rubber rings 19 and 20 are provided on both end faces of the fixed drive piston, which abut the outer circumference of the drive piston rod 15 or one of these corresponding cylindrical extension 14 a of the piston 14 and the inner wall of the piston rod 12 (cylinder part of the drive cylinder 12, 14, 15) leave an annular gap with a precisely defined volume. When the fixed piston 14 abuts the inner ends of the cavity of the axially moving piston rod 12, these rubber rings deform elastically until they completely fill the annular gap and form a practically inelastic cushion. In this way, a highly effective and practically wear-free end position damping results with relatively little effort.

Das Ausführungsbeispiel gemäß der Figur 2 entspricht, was die zum Pumpengehäuse und Pumpkolben 10 gehörenden Teile angeht, voll und ganz dem Ausführungsbeispiel gemäß Figur 1, so daß für die einander entsprechenden Teile die gleichen Bezugszeichen verwendet worden sind.The embodiment according to FIG. 2 fully corresponds to the embodiment according to FIG. 1 as far as the parts belonging to the pump housing and pump piston 10 are concerned, so that the same reference numerals have been used for the corresponding parts.

Hier dient jedoch die Kolbenstange 12 des Pumpkolbens 10 zugleich als Antriebskolbenstange des Antriebszylinders und ist deshalb mit einem doppeltwirkenden Antriebskolben 21 verbunden, der längsverschiebbar in einem feststehenden Zylinderteil 22 gelagert ist. Um zu erreichen, daß auch hier die Kolbenstange 12 über ihre gesamte Länge von dem hydraulischen Antriebsmedium des Antriebszylinders 22, 21, 12 gekühlt wird, besteht die Kolbenstange 12 aus einem Außenrohr 12 a und einem Innenrohr 12 b, die konzentrisch mit radialem Abstand ineinander angeordnet sind. Dabei bilden der Innenraum 12c des Innenrohres 12 b und der Ringraum 12d zwischen dem Außenrohr 12a und dem Innenrohr 12b eine vom Antriebsmedium aufeinanderfolgend durchströmte Durchtrittsöffnung,, so daß die Kolbenstange 12 im erforderlichen Maß gekühlt werden kann.Here, however, the piston rod 12 of the pump piston 10 also serves as the drive piston rod of the drive cylinder and is therefore connected to a double-acting drive piston 21, which is mounted in a fixed longitudinally displaceable cylinder part 22. In order to ensure that the piston rod 12 is also cooled over its entire length by the hydraulic drive medium of the drive cylinder 22, 21, 12, the piston rod 12 consists of an outer tube 12 a and an inner tube 12 b, which are arranged concentrically with one another at a radial distance are. The interior 12c of the inner tube 12b and the annular space 12d between the outer tube 12a and the inner tube 12b form a passage opening through which the drive medium flows, so that the piston rod 12 can be cooled to the required extent.

Zur Zuführung von Antriebsmedium in die Kolbenstange 12 unter Vermeidung von bewegten Druckmittelanschlüssen weist die Kolbenstange 12 in axialem Abstand zum Antriebskolben 21 einen zweiten Antriebskolben 23 auf. Weiterhin ist der Innenraum des Innenrohres 12 b mit dem Ringraum zwischen den beiden Antriebskolben 21 und 23 druckmittelleitend verbunden. Ebenso ist der Ringraum zwischen dem Außenrohr 12 a und dem Innenrohr 12b unmittelbar neben dem zweiten Antriebskolben 23 mit dem Ringraum zwischen der Kolbenstange 12 und dem Zylinderteil 21 des Antriebszylinders 22, 21, 12 verbunden. Schließlich sind in der Wandung des Zylinderteiles 22 des Antriebszylinders 22, 21, 12 zwei parallele, an den Druckmittelkreislauf 18 angeschlossene Druckmittelanschlüsse 24 und 25 vorgesehen, deren Abstand in axialer Richtung der axialen Länge des zweiten Antriebskolbens 23 entspricht. Dabei ist der Abstand b zwischen dem Zylinderdeckel des Antriebszylinders 22, 21, 12 und dem ersten Druckmittelanschluß 24 kleiner oder höchstens ebenso groß, wie der axiale Abstand a zwischen den beiden Antriebskolben 21 und 23.In order to supply drive medium to the piston rod 12 while avoiding moving pressure medium connections, the piston rod 12 has a second drive piston 23 at an axial distance from the drive piston 21. Furthermore, the interior of the inner tube 12 b is connected to the annular space between the two drive pistons 21 and 23 in a pressure medium-conducting manner. Likewise, the annular space between the outer tube 12 a and the inner tube 12 b is connected directly next to the second drive piston 23 to the annular space between the piston rod 12 and the cylinder part 21 of the drive cylinder 22, 21, 12. Finally, in the wall of the cylinder part 22 of the drive cylinder 22, 21, 12 there are two parallel pressure medium connections 24 and 25 connected to the pressure medium circuit 18, the distance between them in the axial direction corresponding to the axial length of the second drive piston 23. The distance b between the cylinder cover of the drive cylinder 22, 21, 12 and the first pressure medium connection 24 is smaller or at most as large as the axial distance a between the two drive pistons 21 and 23.

Wie aus Figur 2 ersichtlich ist, wird bei einer Verschiebung der Kolbenstange 12 nach rechts das vor dem zweiten Antriebskolben 23 befindliche Antriebsmedium in den Ringraum zwischen dem Außenrohr 12 a und dem Innenrohr 12 b gedrückt und gelangt anschließend durch das Innenrohr 12 b in den Ringraum zwischen beiden Antriebskolben 21 und 23 und von dort durch den Druckmittelanschluß 25 in den Druckmittelkreislauf 18. Ebenso durchströmt bei umgekehrter Beaufschlagung das Antriebsmedium zunächst die Kolbenstange 12 und kühlt diese.As can be seen from FIG. 2, when the piston rod 12 is shifted to the right, the drive medium located in front of the second drive piston 23 is pressed into the annular space between the outer tube 12 a and the inner tube 12 b and then passes through the inner tube 12 b into the annular space between two drive pistons 21 and 23 and from there through the pressure medium connection 25 into the pressure medium circuit 18. Likewise, with the reverse action, the drive medium first flows through the piston rod 12 and cools it.

Das Ausführungsbeispiel gemäß Figur 3 entspricht im Hinblick auf die Ausbildung des Pumpzylinders 9, des Pumpkolbens 10 und der Kolbenstange 12 dem Ausführungsbeispiel der Figur 2, so daß für die einander entsprechenden Teile die gleichen Bezugszeichen verwendet worden sind.The embodiment according to FIG. 3 corresponds to the embodiment of FIG. 2 with regard to the design of the pump cylinder 9, the pump piston 10 and the piston rod 12, so that the same reference numerals have been used for the corresponding parts.

Die Kolbenstange 12 besteht auch hier aus einem Außenrohr 12a und einem Innenrohr 12b, die konzentrisch mit radialem Abstand ineinander angeordnet sind. Der Innenraum 12c des Innenrohres 12 und der Ringraum 12d zwischen dem Außenrohr 12a und dem Innenrohr 12b bilden Durchtrittsöffnungen für ein Kühlmedium, welches von einem gesonderten Kühlmittelkreislauf 26 her in die Kolbenstange 12 eingespeist wird. In diesem gesonderten Kühlmittelkreislauf 26 sind außerdem die Durchtrittsöffnungen 9a in den zylindrischen Wandungen des Pumpzylinders 9 einbezogen. Ferner enthält der gesonderte Kühlmittelkreislauf 26 eine Kühlmittelpumpe 26a und einen Vorratsbehälter 26b.The piston rod 12 here also consists of an outer tube 12a and an inner tube 12b, which are arranged concentrically one inside the other at a radial distance. The interior 12c of the inner tube 12 and the annular space 12d between the outer tube 12a and the inner tube 12b form passage openings for a cooling medium which is fed into the piston rod 12 from a separate coolant circuit 26. In this separate coolant circuit 26, the passage openings 9a are also included in the cylindrical walls of the pump cylinder 9. Furthermore, the separate coolant circuit 26 contains a coolant pump 26a and a reservoir 26b.

Der Antrieb des Pumpkolbens 10 erfolgt beim Ausführungsbeispiel gemäß Figur 3 durch einen gesonderten hydraulischen Antriebszylinder 27, dessen Kolbenstange 28 am äußersten Ende der Kolbenstange 12 befestigt ist. Der gesonderte hydraulische Arbeitszylinder 27 wird von einem gesonderten Hydraulikkreislauf 29 mit Druckmittel versorgt, der eine Hydraulikpumpe 29a, einen Vorratsbehälter 29b und ein Umschaltventil 29c aufweist. An die Stelle des Antriebszylinders 27 kann gegebenenfalls auch ein anderes Antriebsaggregat treten, welches die Kolbenstange 12 der Kolbenpumpe hin- und hergehend antreibt.In the exemplary embodiment according to FIG. 3, the pumping piston 10 is driven by a separate hydraulic drive cylinder 27, the piston rod 28 of which is attached to the extreme end of the piston rod 12. The separate hydraulic working cylinder 27 is shared by a separate hydraulic circuit 29 Pressure medium supplied, which has a hydraulic pump 29a, a reservoir 29b and a changeover valve 29c. Another drive unit, which drives the piston rod 12 of the piston pump back and forth, can optionally take the place of the drive cylinder 27.

Claims (3)

1. Double-acting reciprocating piston pump for handling liquids and designed for temporary idling without liquid, the piston pump having a piston (10) provided with a piston seal (11), the piston performing a reciprocating motion in pump cylinder (9) and being connected to a piston rod (12) penetrating through a cylinder head wall (1) of the pump housing and being provided with a seal (13), the piston rod (12) being driven hydraulically,
characterized in that
a) the piston seal (11) and the pump housing seal (13) are stuffing box packings,
b) the walls of the pump cylinder (9) are provided with cavities (9 a),
c) the piston rod (12) has at least one cavity (12 d),
d) the cavities (9 a, 12 d) are connected to at least one liquid cycle.
2. Double-acting reciprocating piston pump according to claim 1,
characterized in that
the hollow piston rod (12) serves simultaneously as cylinder of a hydraulic drive, the cylinder being movable on the stationary power piston (14) and on the piston rod (15) joined to the latter piston.
3. Double-acting reciprocating piston pump according to claim 1,
characterized in that
the hollow piston rod (12) serves simultaneously as piston rod of the power piston (21) which moves in a longitudinal direction in the stationary cylinder (22), the piston rod (12) consisting of an outer tube (12 a) and a concentric inner tube (12 b) positioned to leave a radial clearance, the annular space (12 d) between the outer tube (12 a) and the inner tube (12 b) as well as the inner space (12 c) of the inner tube (12 b) receiving a flow of hydraulic power fluid during at least part of the stroke.
EP84901584A 1983-04-06 1984-04-03 Double acting reciprocating piston pump Expired EP0139709B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84901584T ATE29273T1 (en) 1983-04-06 1984-04-03 DOUBLE ACTING RECIPROCATING PISTON PUMP.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3312357 1983-04-06
DE3312357 1983-04-06
DE3410911 1984-03-24
DE19843410911 DE3410911A1 (en) 1983-04-06 1984-03-24 PISTON PUMP

Publications (2)

Publication Number Publication Date
EP0139709A1 EP0139709A1 (en) 1985-05-08
EP0139709B1 true EP0139709B1 (en) 1987-09-02

Family

ID=25809744

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84901584A Expired EP0139709B1 (en) 1983-04-06 1984-04-03 Double acting reciprocating piston pump

Country Status (5)

Country Link
US (1) US4818192A (en)
EP (1) EP0139709B1 (en)
DE (2) DE3410911A1 (en)
IT (1) IT1175828B (en)
WO (1) WO1984003914A1 (en)

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Also Published As

Publication number Publication date
DE3410911A1 (en) 1984-10-11
EP0139709A1 (en) 1985-05-08
US4818192A (en) 1989-04-04
DE3465762D1 (en) 1987-10-08
WO1984003914A1 (en) 1984-10-11
IT8420405A0 (en) 1984-04-05
IT1175828B (en) 1987-07-15

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