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EP0340201A1 - Hydraulically actuated piston pump - Google Patents

Hydraulically actuated piston pump Download PDF

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Publication number
EP0340201A1
EP0340201A1 EP19890890085 EP89890085A EP0340201A1 EP 0340201 A1 EP0340201 A1 EP 0340201A1 EP 19890890085 EP19890890085 EP 19890890085 EP 89890085 A EP89890085 A EP 89890085A EP 0340201 A1 EP0340201 A1 EP 0340201A1
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EP
European Patent Office
Prior art keywords
piston
pump
end plates
pressure
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP19890890085
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German (de)
French (fr)
Inventor
Josef Brosowitsch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BROSOWITSCH, JOSEF
Original Assignee
M-U-T Maschinen-Umwelttechnik- Transportanlagen GmbH
Brosowitsch Josef
MUT Maschinen Umwelttechnik Transportanlagen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by M-U-T Maschinen-Umwelttechnik- Transportanlagen GmbH, Brosowitsch Josef, MUT Maschinen Umwelttechnik Transportanlagen GmbH filed Critical M-U-T Maschinen-Umwelttechnik- Transportanlagen GmbH
Publication of EP0340201A1 publication Critical patent/EP0340201A1/en
Withdrawn legal-status Critical Current

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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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/115—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by two single-acting liquid motors, each acting in one direction

Definitions

  • the invention relates to a hydraulically operated, double-acting piston pump for conveying liquids loaded with abrasive particles, such as filtered sludge water, thick matter and the like, in particular for use on a vehicle, for example a sewer cleaning vehicle, with a completely enclosed oscillating inside a pump cylinder
  • Controlled pump piston which in turn is designed as a hollow cylinder and is slidably mounted on a fixed piston on fixed piston rods with axial bores and with inlet and outlet bores, the pump cylinder having end plates with suction and pressure valves and the piston rods being fastened in the end plates.
  • Piston pumps of this type are already known, in which a reciprocating movement is achieved by means of a hydraulic cylinder, on the elongated piston rod of which the water pump piston is arranged, and the suction and pressure valves for the medium to be conveyed are provided in the end plates of the cylinder chambers.
  • This embodiment has the disadvantage that different piston surfaces are used depending on the direction of movement, since the entire piston surface is effective and only the piston ring surface is effective during the return stroke. This results in different flow velocities in the piston chamber and thus additional pulsations in the flow.
  • Another disadvantage is the large overall length due to the lining up of hydraulic and pump cylinders and the large number of surfaces to be sealed from the outside.
  • Hydraulically operated plunger pumps are also known, in which the plunger cylinder simultaneously forms the piston for the hydraulic drive.
  • This has the disadvantage that the pump piston has to be sealed off from the outside and that a tube is additionally inserted in the hollow bore of the piston rod that is necessary must be brought in order to be able to act on the hydraulic piston on both sides.
  • two plunger pumps must always be arranged side by side, which perform opposite strokes in order to achieve a reasonably constant flow rate.
  • a pressure medium-driven thrust piston pump which has an axially displaceable hollow piston in the interior of a compressed air cylinder, which includes an immovable piston which is placed on a continuous, stationary piston rod.
  • the hollow piston is pushed back and forth in compressed air cylinders via valves and a control system. This changes the volume of the hollow cylinder on both sides of the fixed piston.
  • liquid is sucked in or pressed out through the bores of the piston rod.
  • the fixed piston can not be kept free of play in this version. It is subject to a permanent alternating load and thus to an oscillating movement within the manufacturing tolerances or the assembly play, so that at higher pressures the pump has to malfunction in the shortest possible time and enormous wear is the result.
  • the invention aims to overcome the known disadvantages. This is achieved in that the fixed piston is clamped rigidly between the piston rods and the piston rods are pressurized in the axial direction against one another in particular by lag screws, which connect the two end plates, and the pressure oil is supplied in a manner known per se through the axial bores of the piston rods . It is expedient if the pump cylinder is also clamped between the end plates clamped together by the tension screws.
  • a special embodiment is characterized in that pressure lines of a closed hydraulic circuit are connected to the axial bores of the piston rods passing through the end plates in the center, and that a ramp control for moving to the end positions of the pump piston and for reversing in the pump cylinder is provided with non-contact pressure-resistant proximity switches which respond to the pump piston are.
  • the construction is simple and functional and allows long-term interference, especially in rough use free operation because the central fixed piston is clamped between the split fixed piston rods without play. Any manufacturing-related tolerances are reduced to zero by clamping the assembly together.
  • Fig. 1 shows a tube 1, which forms the pump cylinder and in which a pump piston in the form of a hollow cylinder 2 is located. Inside the piston 3 is clamped at rest by two piston rods 4, 5. The cylinder 2 is pushed back and forth hydraulically and has two end plates 6, 6a, which slide back and forth in a sealing manner on the piston rods 4, 5. The suction and pressure valves 8, 8a, 9, 9a are arranged in the two end plates 7, 7a of the pump piston 1. The two end plates 7, 7a are clamped together using four lag screws 10a, b, c, d.
  • a gas pressure accumulator 12 is arranged in the pressure lines 11, 11a and is attached to the tension screws 10a, b, c, d.
  • the piston rods 4, 5 have axial bores 4c, 5c and on the side of the hydraulic piston 3 each have a transverse bore 4a, 5a, through which the hydraulic oil is supplied via the connections 4b, 5b.
  • the common connection 13 of the two pressure lines 11, 11a leads to the various consumers, such as. B. sewer cleaning nozzles, etc.
  • the suction sides 14, 14a of the pump are connected to a liquid tank 16 via suction filters 15, 15a.
  • the suction filters 15, 15a are installed in the liquid tank 16, which has a central connection 17 for a suction nozzle.
  • the complete pump is connected to the liquid tank 16 by means of rubber vibrating elements 18, 18a.
  • FIG. 2 shows a side view of the end plate 7 as well as the tie rods or tie screws 10a, b, c, d and the gas reservoir 12 that has been built up.
  • Fig. 3 shows a hydraulic circuit diagram with Steuerein direction, wherein the pump in question is operated by means of a closed hydraulic circuit.
  • the closed circuit is particularly useful in vehicle construction because the smaller oil volume required can save weight and a much higher degree of efficiency can be achieved by means of radial or axial piston pumps that swivel through the zero position. The control edge losses during slide operation, which occur as heat losses, are therefore eliminated.
  • the hydraulic piston can be "hydraulically clamped", which means that a much more precise reversal can be achieved in the end positions than when controlling in an open circuit.
  • the hydraulic pump unit 20 When mounted on the vehicle, the hydraulic pump unit 20 is driven by the auxiliary drive 26.
  • the two lines 21, 22 of the control pump 23 are connected directly to the hydraulic cylinder 2 of the piston pump (tube 1).
  • the control pump 23 carries the feed pump 24 and the control oil pump 25 in tandem.
  • the respective suction line is continuously supplied by the feed pump during operation, so that the minimum operating pressure that occurs prevents cavitation at the rear of the hydraulic pump 23.
  • the control oil pump 25 increases the response of the hydraulic system.
  • a part of the edible oil flow is constantly fed into the oil tank 29 by changing the directional control valve 27 via a cooler 28.
  • the built-in electronics 30 are used to compare the setpoint and actual value specification and to switch over in the end positions via two non-contact limit switches 31, 31 a.
  • the maximum pressure of the system is secured by the pressure relief valve 32.
  • the setting of the desired pressure is infinitely variable via a potentiometer 33, the regulation ensuring that the pump always delivers just as much as is necessary to maintain the set pressure (energy saving).
  • a pressure-voltage converter 34 can also be used to maintain the set pressure, which leads the control signal into the electronics 30.
  • the variable displacement pump 23 is controlled by means of the control valve 35, the valve being adjusted by means of proportional valve technology via the two solenoid coils 36a, b, which receive the regulating and control signals from the electronics 30.
  • a temperature switch 37 monitors the hydraulic oil temperature, so that when over exceed a certain, adjustable value, the oil circuit is switched through the valve 38 in a non-circulating manner.
  • the exemplary embodiment shown represents only one of many possibilities within the scope of the inventive concept.
  • the tensioning of the hydraulic cylinder by means of lag screws 10a, b, c, d could be omitted if the two end plates 7, 7a could be screwed tight by means of a thread on the pump tube 1 for clamping the piston rods and the piston 3.
  • the two suction connections 14, 14a could also be combined to form a line, so that a larger suction filter would suffice.
  • the hydraulic part of the piston pump could easily be provided with end position damping if the end plates 6, 6a have a projection which covers the transverse bore 4a, 5a for the backflow and is designed such that the transverse bores are successively closed when the cylinder 2 is displaced.
  • the resulting pressure change in the system could also be used to reverse the piston.

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

Abstract

A hydraulically actuated double-acting piston pump (thrust piston pump) has a pump cylinder (1), which encloses a pump piston (2), which in turn is designed as a hollow cylinder and, hydraulically actuated, slides to and fro on a central, fixed piston (3). The piston (3) is held in position by two fixed piston rods (4, 5), which emerge from the end plates (7, 7a) of the pump cylinder (1), pass through the hollow pump piston (2) and clamp the fixed piston (3) between their free ends. For clamping the piston (3) the two end plates (7, 7a) of the pump cylinder can be clamped together by means of draw-in bolts (10a, b, c, d) or the end plates (7, 7a) are firmly bolted on the pump cylinder (1) or the piston rods (4, 5) are firmly bolted in the end plates (7, 7a) and clamping-tight of the piston (3) can be achieved by tightening the bolts so that a compact assembly is formed, free of play (Fig. 1). <IMAGE>

Description

Die Erfindung betrifft eine hydraulisch betriebene, doppelt wirkende Kolbenpumpe zur Förderung von mit abrasiven Teilchen beladenen Flüssigkeiten wie beispielsweise von gefiltertem Schlammwasser, von Dickstoffen und dgl., insbesondere zum Ein­satz auf einem Fahrzeug, beispielsweise einem Kanalreinigungs­fahrzeug, mit einem vollständig im Inneren eines Pumpenzylin­ders eingeschlossenen oszillierend gesteuerten Pumpenkolben, der seinerseits als Hohlzylinder ausgebildet ist und auf einem feststehenden Kolben auf feststehenden Kolbenstangen mit axialen Bohrungen sowie mit Einlaß- und Auslaßbohrungen verschiebbar gelagert ist, wobei der Pumpenzylinder Endplatten mit Saug- und Druckventilen aufweist und in den Endplatten die Kolbenstangen befestigt sind.The invention relates to a hydraulically operated, double-acting piston pump for conveying liquids loaded with abrasive particles, such as filtered sludge water, thick matter and the like, in particular for use on a vehicle, for example a sewer cleaning vehicle, with a completely enclosed oscillating inside a pump cylinder Controlled pump piston, which in turn is designed as a hollow cylinder and is slidably mounted on a fixed piston on fixed piston rods with axial bores and with inlet and outlet bores, the pump cylinder having end plates with suction and pressure valves and the piston rods being fastened in the end plates.

Es sind bereits Kolbenpumpen dieser Bauart bekannt, bei wel­chen mittels eines Hydraulikzylinders, an dessen verlängerter Kolbenstange der Wasserpumpenkolben angeordnet ist, eine hin­und hergehende Bewegung erreicht wird und wobei die Saug- und Druckventile für das zu fördernde Medium in den Endplatten der Zylinderräume vorgesehen sind. Diese Ausführungsart besitzt den Nachteil, daß je nach Bewegungsrichtung unterschiedliche Kol­benflächen zum Einsatz kommen, da einmal die gesamte Kolben­fläche und beim Rückhub nur die Kolbenringfläche wirksam wird. Dadurch ergeben sich unterschiedliche Strömungsgeschwindigkei­ten im Kolbenraum und somit zusätzliche Pulsationen im Förder­strom. Ein weiterer Nachteil ist die große Baulänge durch die Aneinanderreihung von Hydraulik- und Pumpenzylinder sowie die große Anzahl der nach außen abzudichtenden Flächen. Es sind ferner hydraulisch betriebene Plungerpumpen bekannt, bei wel­chen der Plungerzylinder gleichzeitig den Kolben für den Hy­draulikantrieb bildet. Dies hat den Nachteil, daß der Pumpen­kolben nach außen abzudichten ist, und daß in der dabei notwen­digen Hohlbohrung der Kolbenstange zusätzlich ein Rohr einge­ bracht werden muß, um den Hydraulikkolben beiderseits beauf­schlagen zu können. Zudem müssen immer zwei Plungerpumpen ne­beneinander angeordnet werden, welche gegensinnige Hubbewe­gungen ausführen, um einen halbwegs konstanten Förderstrom zu erreichen.Piston pumps of this type are already known, in which a reciprocating movement is achieved by means of a hydraulic cylinder, on the elongated piston rod of which the water pump piston is arranged, and the suction and pressure valves for the medium to be conveyed are provided in the end plates of the cylinder chambers. This embodiment has the disadvantage that different piston surfaces are used depending on the direction of movement, since the entire piston surface is effective and only the piston ring surface is effective during the return stroke. This results in different flow velocities in the piston chamber and thus additional pulsations in the flow. Another disadvantage is the large overall length due to the lining up of hydraulic and pump cylinders and the large number of surfaces to be sealed from the outside. Hydraulically operated plunger pumps are also known, in which the plunger cylinder simultaneously forms the piston for the hydraulic drive. This has the disadvantage that the pump piston has to be sealed off from the outside and that a tube is additionally inserted in the hollow bore of the piston rod that is necessary must be brought in order to be able to act on the hydraulic piston on both sides. In addition, two plunger pumps must always be arranged side by side, which perform opposite strokes in order to achieve a reasonably constant flow rate.

Aus der GB-A1 21 50 646 ist eine druckmittelgetriebene Schubkolbenpumpe bekannt, die im Inneren eines Druckluftzylin­ders einen axial verschiebbaren Hohlkolben aufweist, der einen unverschiebbaren Kolben einschließt, welcher auf einer durch­gehenden ortsfesten Kolbenstange aufgesetzt ist. Über Ventile und eine Steuerung wird der Hohlkolben in Druckluftzylinder hin- und hergeschoben. Dadurch ändert sich das Volumen des Hohl­zylinders zu beiden Seiten des feststehenden Kolbens. Über die Bohrungen der Kolbenstange wird je nach Bewegungsrichtung des Hohlzylinders Flüssigkeit angesaugt bzw. herausgepreßt. Der feststehende Kolben kann bei dieser Ausführung jedoch nicht spielfrei gehalten werden. Er ist einer permanenten Wechselbe­lastung und damit einer oszillierenden Bewegung innerhalb der Herstellungstoleranzen bzw. dem Montagespiel unterworfen, sodaß bei größeren Drücken in kürzester Zeit Störungen der Pumpe auf­treten müssen und ein enormer Verschleiß die Folge ist.From GB-A1 21 50 646 a pressure medium-driven thrust piston pump is known which has an axially displaceable hollow piston in the interior of a compressed air cylinder, which includes an immovable piston which is placed on a continuous, stationary piston rod. The hollow piston is pushed back and forth in compressed air cylinders via valves and a control system. This changes the volume of the hollow cylinder on both sides of the fixed piston. Depending on the direction of movement of the hollow cylinder, liquid is sucked in or pressed out through the bores of the piston rod. The fixed piston can not be kept free of play in this version. It is subject to a permanent alternating load and thus to an oscillating movement within the manufacturing tolerances or the assembly play, so that at higher pressures the pump has to malfunction in the shortest possible time and enormous wear is the result.

Die Erfindung zielt darauf ab, die bekannten Nachteile zu beseitigen. Dies wird dadurch erreicht, daß der feststehende Kolben zwischen den Kolbenstangen starr eingespannt ist und die Kolbenstangen in axialer Richtung gegeneinander insbesondere durch Zugschrauben, welche die beiden Endplatten verbinden, un­ter Druck stehen und die Druckölzufuhr in an sich bekannter Wei­se durch die axialen Bohrungen der Kolbenstangen erfolgt. Dabei ist es zweckmäßig, wenn zwischen den durch die Zugschrauben zu­sammengespannten Endplatten auch der Pumpenzylinder eingespannt ist. Eine besondere Ausführungsform ist dadurch gekennzeichnet, daß an die axialen Bohrungen der die Endplatten mittig durch­setzenden Kolbenstangen Druckleitungen eines geschlossenen Hy­draulikkreislaufes angeschlossen sind, daß eine Rampensteuerung zum Anfahren der Endlagen des Pumpenkolbens und zur Umsteuerung im Pumpenzylinder berührungslose druckfeste Näherungsschalter, die auf den Pumpenkolben ansprechen, vorgesehen sind.The invention aims to overcome the known disadvantages. This is achieved in that the fixed piston is clamped rigidly between the piston rods and the piston rods are pressurized in the axial direction against one another in particular by lag screws, which connect the two end plates, and the pressure oil is supplied in a manner known per se through the axial bores of the piston rods . It is expedient if the pump cylinder is also clamped between the end plates clamped together by the tension screws. A special embodiment is characterized in that pressure lines of a closed hydraulic circuit are connected to the axial bores of the piston rods passing through the end plates in the center, and that a ramp control for moving to the end positions of the pump piston and for reversing in the pump cylinder is provided with non-contact pressure-resistant proximity switches which respond to the pump piston are.

Die Konstruktion ist einfach und zweckmäßig und gestattet besonders auch im rauhen Einsatz einen langfristig störungs­ freien Betrieb, weil der zentrale feststehende Kolben spiel­frei zwischen den geteilten feststehenden Kolbenstangen ein­gespannt ist. Eventuelle herstellungsbedingte Toleranzen wer­den durch das Zusammenspannen der Baueinheit auf null redu­ziert.The construction is simple and functional and allows long-term interference, especially in rough use free operation because the central fixed piston is clamped between the split fixed piston rods without play. Any manufacturing-related tolerances are reduced to zero by clamping the assembly together.

Anhand von Zeichnungen wird ein Ausführungsbeispiel des Er­findungsgegenstandes näher beschrieben.

  • Fig. 1 zeigt einen Längsschnitt durch die erfindungsgemäße Pumpe,
  • Fig. 2 eine Seitenansicht derselben Ausführung und
  • Fig. 3 einen Schaltplan der hydraulischen Anlage.
An exemplary embodiment of the subject matter of the invention is described in more detail with reference to drawings.
  • 1 shows a longitudinal section through the pump according to the invention,
  • Fig. 2 is a side view of the same embodiment and
  • Fig. 3 is a circuit diagram of the hydraulic system.

Fig. 1 zeigt ein Rohr 1, welches den Pumpenzylinder bildet und in welchem sich ein Pumpenkolben in Form eines Hohlzylin­ders 2 befindet. In dessen Innerem ist ein Kolben 3 durch zwei Kolbenstangen 4, 5 ruhend eingespannt. Der Zylinder 2 wird hy­draulisch hin- und herverschoben und weist zwei Stirnplatten 6, 6a auf, welche auf den Kolbenstangen 4, 5 dichtend hin- und hergleiten. In den beiden Endplatten 7, 7a des Pumpenkolbens 1 sind die Saug- und Druckventile 8, 8a, 9, 9a angeordnet. Die beiden Endplatten 7, 7a werden mit Hilfe von vier Zugschrauben 10a, b, c, d zusammengespannt. Zwecks Glättung der Pulsation ist in den Druckleitungen 11, 11a ein Gasdruckspeicher 12 an­geordnet, welcher an den Zugschrauben 10a, b, c, d befestigt ist. Die Kolbenstangen 4, 5 weisen axiale Bohrungen 4c, 5c und an der Seite des Hydraulikkolbens 3 jeweils eine Querbohrung 4a, 5a auf, durch welche das Hydrauliköl über die Anschlüsse 4b, 5b zugeführt wird. Der gemeinsame Anschluß 13 der beiden Druckleitungen 11, 11a führt zu den diversen Verbrauchern, wie z. B. Kanalreinigungsdüsen, etc. Die Saugseiten 14, 14a der Pumpe sind über Saugfilter 15, 15a mit einem Flüssigkeitstank 16 verbunden. Die Saugfilter 15, 15a sind dabei im Flüssigkeits­tank 16 eingebaut, welcher einen zentralen Anschluß 17 für ei­nen Saugrüssel aufweist. Die komplette Pumpe ist mittels Gummi­schwingelementen 18, 18a mit dem Flüssigkeitstank 16 verbunden.Fig. 1 shows a tube 1, which forms the pump cylinder and in which a pump piston in the form of a hollow cylinder 2 is located. Inside the piston 3 is clamped at rest by two piston rods 4, 5. The cylinder 2 is pushed back and forth hydraulically and has two end plates 6, 6a, which slide back and forth in a sealing manner on the piston rods 4, 5. The suction and pressure valves 8, 8a, 9, 9a are arranged in the two end plates 7, 7a of the pump piston 1. The two end plates 7, 7a are clamped together using four lag screws 10a, b, c, d. For the purpose of smoothing the pulsation, a gas pressure accumulator 12 is arranged in the pressure lines 11, 11a and is attached to the tension screws 10a, b, c, d. The piston rods 4, 5 have axial bores 4c, 5c and on the side of the hydraulic piston 3 each have a transverse bore 4a, 5a, through which the hydraulic oil is supplied via the connections 4b, 5b. The common connection 13 of the two pressure lines 11, 11a leads to the various consumers, such as. B. sewer cleaning nozzles, etc. The suction sides 14, 14a of the pump are connected to a liquid tank 16 via suction filters 15, 15a. The suction filters 15, 15a are installed in the liquid tank 16, which has a central connection 17 for a suction nozzle. The complete pump is connected to the liquid tank 16 by means of rubber vibrating elements 18, 18a.

Fig. 2 zeigt in Seitenansicht die Endplatte 7 sowie die Zug­stangen bzw. Zugschrauben 10a, b, c, d und den aufgebauten Gas­speicher 12.2 shows a side view of the end plate 7 as well as the tie rods or tie screws 10a, b, c, d and the gas reservoir 12 that has been built up.

Fig. 3 zeigt ein hydraulisches Schaltschema mit Steuerein­ richtung, wobei die gegenständliche Pumpe mittels eines ge­schlossenen hydraulischen Kreislaufes betrieben wird. Beson­ders im Fahrzeugbau bietet sich der geschlossene Kreislauf an, da durch das kleinere erforderliche Ölvolumen eine Gewichts­ersparnis erreicht werden kann und ein wesentlich höherer Wir­kungsgrad mittels durch die Nullage schwenkenden Radial- bzw. Achsialkolbenpumpen erreichbar ist. Die Steuerkantenverluste im Schieberbetrieb, welche als Wärmeverluste auftreten, fallen so­mit weg. Zusätzlich dazu kann der Hydraulikkolben "hydraulisch eingespannt" werden, womit eine wesentlich exaktere Umsteuerung in den Endlagen erreichbar ist, als bei Steuerung im offenen Kreislauf. Bei Aufbau am Fahrzeug erfolgt der Antrieb des Hy­draulikpumpenaggregates 20 vom Nebenantrieb 26 her. Die beiden Leitungen 21, 22 der Regelpumpe 23 sind direkt mit dem Hydrau­likzylinder 2 der Kolbenpumpe (Rohr 1) verbunden. Die Regelpum­pe 23 trägt in Tandemausführung die Speisepumpe 24 und die Steuerölpumpe 25. Die jeweilige Saugleitung wird während des Be­triebes ständig von der Speisepumpe versorgt, sodaß der dabei auftretende Mindestbetriebsdruck Kavitation an der Rückseite der Hydraulikpumpe 23 verhindert. Die Steuerölpumpe 25 erhöht die Reaktion des Hydrauliksystems. Ein Teil des Speiseölstromes wird ständig, durch wechselnde Umsteuerung des Wegeventiles 27 über einen Kühler 28 in den Öltank 29 geleitet. Die eingebaute Elektronik 30 dient zum Vergleich der Soll- und Istwertvorgabe, sowie zum Umschalten in den Endlagen über zwei berührungslose Endschalter 31, 31 a. Der Maximaldruck der Anlage ist über das Überdruckventil 32 abgesichert. Die Einstellung des gewünschten Druckes erfolgt stufenlos über ein Potentiometer 33, wobei durch die Regelung erreicht wird, daß die Pumpe immer gerade soviel fördert, wie zur Erhaltung des eingestellten Druckes notwendig ist (Energieeinsparung). Zur Aufrechterhaltung des eingestell­ten Druckes kann auch ein Druck-Spannungswandler 34 dienen, wel­cher das Regelsignal in die Elektronik 30 leitet. Die Verstell­pumpe 23 wird mittels des Steuerventils 35 angesteuert wobei mittels Proportionalventiltechnik über die beiden Magnetspulen 36a, b, welche die Regel- bzw. Steuersignale von der Elektronik 30 erhalten, die Ventilverstellung erfolgt. Ein Temperaturschal­ter 37 überwacht die Hydrauliköltemperatur, sodaß bei Über­ schreiten eines bestimmten, einstellbaren Wertes der Ölkreis­lauf durch das Ventil 38 in durcklosem Umlauf geschaltet wird.Fig. 3 shows a hydraulic circuit diagram with Steuerein direction, wherein the pump in question is operated by means of a closed hydraulic circuit. The closed circuit is particularly useful in vehicle construction because the smaller oil volume required can save weight and a much higher degree of efficiency can be achieved by means of radial or axial piston pumps that swivel through the zero position. The control edge losses during slide operation, which occur as heat losses, are therefore eliminated. In addition, the hydraulic piston can be "hydraulically clamped", which means that a much more precise reversal can be achieved in the end positions than when controlling in an open circuit. When mounted on the vehicle, the hydraulic pump unit 20 is driven by the auxiliary drive 26. The two lines 21, 22 of the control pump 23 are connected directly to the hydraulic cylinder 2 of the piston pump (tube 1). The control pump 23 carries the feed pump 24 and the control oil pump 25 in tandem. The respective suction line is continuously supplied by the feed pump during operation, so that the minimum operating pressure that occurs prevents cavitation at the rear of the hydraulic pump 23. The control oil pump 25 increases the response of the hydraulic system. A part of the edible oil flow is constantly fed into the oil tank 29 by changing the directional control valve 27 via a cooler 28. The built-in electronics 30 are used to compare the setpoint and actual value specification and to switch over in the end positions via two non-contact limit switches 31, 31 a. The maximum pressure of the system is secured by the pressure relief valve 32. The setting of the desired pressure is infinitely variable via a potentiometer 33, the regulation ensuring that the pump always delivers just as much as is necessary to maintain the set pressure (energy saving). A pressure-voltage converter 34 can also be used to maintain the set pressure, which leads the control signal into the electronics 30. The variable displacement pump 23 is controlled by means of the control valve 35, the valve being adjusted by means of proportional valve technology via the two solenoid coils 36a, b, which receive the regulating and control signals from the electronics 30. A temperature switch 37 monitors the hydraulic oil temperature, so that when over exceed a certain, adjustable value, the oil circuit is switched through the valve 38 in a non-circulating manner.

Diese Beschreibung soll nur eine Ausführungsvariante schema­tisch darstellen. Selbstverständlich ist es auch möglich, die Anlage im offenen Kreislauf zu fahren, mit wesentlich geringe­rem Wirkungsgrad und weniger exakter Steuerungsmöglichkeiten. Grundsätzlich wird hier von einer Pumpe gesprochen, welche an einem Fahrzeug angeordnet ist, z.B. an einem Kanalreinigungs­fahrzeug mit Hochdruckspüleinrichtung. Vor allem im Hinblick auf die Wiederverwendung von gefiltertem Kanalwasser wurde es erforderlich, Pumpen herzustellen, welche weniger empfindlich als herkömmliche Kolbenpumpen mit Kurbelwellenantrieb sind, da das sogenannte Recyclingwasser größere Verunreinigungen in Form von Sand etc. beinhaltet. Darüber hinaus ist es aber auch durchaus möglich, eine gegenständliche Pumpe stationär zu be­treiben.This description is only intended to schematically represent an embodiment variant. Of course, it is also possible to run the system in an open circuit, with significantly lower efficiency and less precise control options. Basically, this is referred to as a pump which is arranged on a vehicle, e.g. on a sewer cleaning vehicle with high-pressure flushing device. Especially with regard to the reuse of filtered sewer water, it became necessary to manufacture pumps that are less sensitive than conventional piston pumps with crankshaft drive, since the so-called recycling water contains larger impurities in the form of sand, etc. In addition, however, it is also quite possible to operate a concrete pump stationary.

Das dargestellte Ausführungsbeispiel stellt nur eines von vielen Möglichkeiten im Rahmen des Erfindungsgedankens dar. Bei­spielsweise wäre es möglich, die Saug- und Druckventile 8, 9 in beliebiger Richtung im Kolbenboden 7, 7a einzubauen, z.B. auch von außen zugänglich. Die Verspannung des Hydraulikzylinders mittels Zugschrauben 10a, b, c, d könnte entfallen, wenn die beiden Endplatten 7, 7a mittels Gewinde am Pumpenrohr 1 zur Einspannung der Kolbenstangen und des Kolbens 3 festschraubbar wären. Die beiden Sauganschlüsse 14, 14a könnten auch zu einer Leitung zusammengefaßt werden, sodaß ein größerer Saugfilter genügen würde. Der Hydraulikteil der Kolbenpumpe könnte leicht mit einer Endlagendämpfung versehen werden, wenn die Stirnplat­ten 6, 6a einen die Querbohrung 4a, 5a für den Rückfluß ab­deckenden Vorsprung aufweisen, der so ausgebildet ist, daß die Querbohrungen bei Verschiebung des Zylinders 2 sukzessive ver­schlossen werden. Die dadurch entstehende Druckänderung im System könnte auch zur Umsteuerung des Kolbens herangezogen werden.The exemplary embodiment shown represents only one of many possibilities within the scope of the inventive concept. For example, it would be possible to install the suction and pressure valves 8, 9 in the piston head 7, 7a in any direction, e.g. also accessible from the outside. The tensioning of the hydraulic cylinder by means of lag screws 10a, b, c, d could be omitted if the two end plates 7, 7a could be screwed tight by means of a thread on the pump tube 1 for clamping the piston rods and the piston 3. The two suction connections 14, 14a could also be combined to form a line, so that a larger suction filter would suffice. The hydraulic part of the piston pump could easily be provided with end position damping if the end plates 6, 6a have a projection which covers the transverse bore 4a, 5a for the backflow and is designed such that the transverse bores are successively closed when the cylinder 2 is displaced. The resulting pressure change in the system could also be used to reverse the piston.

Claims (7)

1. Hydraulisch betriebene, doppelt wirkende Kolbenpumpe zur Förderung von mit abrasiven Teilchen beladenen Flüssigkei­ten wie beispielsweise von gefiltertem Schlammwasser, von Dickstoffen und dgl., insbesondere zum Einsatz auf einem Fahrzeug, beispielsweise einem Kanalreinigungsfahrzeug, mit einem vollständig im Inneren eines Pumpenzylinders ein­geschlossenen oszillierend gesteuerten Pumpenkolben, der seinerseits als Hohlzylinder ausgebildet ist und auf einem feststehenden Kolben auf feststehenden Kolbenstangen mit axialen Bohrungen sowie mit Einlaß- und Auslaßbohrungen ver­schiebbar gelagert ist, wobei der Pumpenzylinder Endplatten mit Saug- und Druckventilen aufweist und in den Endplatten die Kolbenstangen befestigt sind, dadurch gekennzeichnet, daß der feststehende Kolben (3) zwischen den Kolbenstangen (4, 5) starr eingespannt ist und die Kolbenstangen in axia­ler Richtung gegeneinander insbesondere durch Zugschrauben (10a, b. c, d), welche die beiden Endplatten (7, 7a) verbin­den, unter Druck stehen und die Druckölzufuhr in an sich be­kannter Weise durch die axialen Bohrungen der Kolbenstangen (4, 5) erfolgt.1.Hydraulically operated, double-acting piston pump for conveying liquids loaded with abrasive particles such as, for example, filtered sludge water, thick matter and the like, in particular for use on a vehicle, for example a sewer cleaning vehicle, with an oscillatingly controlled pump piston completely enclosed inside a pump cylinder , which in turn is designed as a hollow cylinder and is slidably mounted on a fixed piston on fixed piston rods with axial bores and with inlet and outlet bores, the pump cylinder having end plates with suction and pressure valves and the piston rods being fastened in the end plates, characterized in that that the fixed piston (3) is rigidly clamped between the piston rods (4, 5) and the piston rods in the axial direction against one another in particular by means of tension screws (10a, b. c, d) which connect the two end plates (7, 7a), are under pressure and the pressure oil is supplied in a manner known per se through the axial bores of the piston rods (4, 5). 2. Kolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß zwischen den durch die Zugschrauben (10a, b, c, d) zusammen­gespannten Endplatten (7, 7a) auch der Pumpenzylinder (1) eingespannt ist.2. Piston pump according to claim 1, characterized in that between the end plates (7, 7a) clamped together by the tension screws (10a, b, c, d) and also the pump cylinder (1) is clamped. 3. Kolbenpumpe nach den Ansprüchen 1 oder 2, dadurch gekenn­zeichnet, daß an die axialen Bohrungen (4c, 5c) der die End­platten (7, 7a) mittig durchsetzenden Kolbenstangen (4, 5) Druckleitungen (21, 22) eines geschlossenen Hydrualikkreis­laufes angeschlossen sind, daß eine Rampensteuerung zum An­fahren der Endlagen des Pumpenkolbens (2) und zur Umsteuerung am Pumpenzylinder (1) berührungslose, druckfeste Näherungs­ schalter (31, 31a), die auf den Pumpenkolben (2) ansprechen, vorgesehen sind.3. Piston pump according to claims 1 or 2, characterized in that to the axial bores (4c, 5c) of the end plates (7, 7a) centrally penetrating piston rods (4, 5) pressure lines (21, 22) of a closed hydrodynamic circuit are connected that a ramp control for moving to the end positions of the pump piston (2) and for reversing the pump cylinder (1) non-contact, pressure-resistant approximation switches (31, 31a) which respond to the pump piston (2) are provided. 4. Kolbenpumpe nach Anspruch 5, dadurch gekennzeichnet, daß den berührungslosen Näherungsschaltern (31, 31a) ein Zeit­glied nachgeschaltet ist und die Zeitdifferenz zwischen dem Schaltvorgang und der Reaktion des Hydrualiksystems regelbar ist.4. Piston pump according to claim 5, characterized in that the non-contact proximity switches (31, 31a) is followed by a timing element and the time difference between the switching process and the reaction of the hydraulic system is adjustable. 5. Kolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Regelpumpe (23) während der Umsteuerung der Kolbenbe­wegung des Pumpenkolbens (2) jeweils durch die Nullage schwenkt.5. Piston pump according to claim 1, characterized in that the control pump (23) pivots during the reversal of the piston movement of the pump piston (2) through the zero position. 6. Kolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Steuerelektronik (30) eine Soll-Istwertregelung auf­weist, wobei mittels eines Potentiometers (33) für die Ein­stellung des gewünschten Pumpendruckes der Ausschwenkwinkel der Pumpe, unabhängig von der geforderten Fördermenge zur Druckregelung vorgesehen ist.6. Piston pump according to claim 1, characterized in that the control electronics (30) has a target actual value control, with the aid of a potentiometer (33) for setting the desired pump pressure, the swivel angle of the pump, regardless of the required flow rate for pressure control. 7. Kolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Stirnplatten (6, 6a) des Pumpenkolbens an der Kolben­innenseite Steuerflächen zur Endlagendämpfung aufweisen, wobei bei Annäherung an die jeweiligen Endlagen die Rück­strömöffnungen (5a, 4a) des Hydraulikmediums kontinuierlich verschlossen werden.7. Piston pump according to claim 1, characterized in that the end plates (6, 6a) of the pump piston on the inside of the piston have control surfaces for end position damping, the return flow openings (5a, 4a) of the hydraulic medium being closed continuously as the end positions are approached.
EP19890890085 1988-03-25 1989-03-23 Hydraulically actuated piston pump Withdrawn EP0340201A1 (en)

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AT79688 1988-03-25
AT796/88 1988-03-25

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19652298A1 (en) * 1996-12-16 1998-06-18 Rexroth Mannesmann Gmbh Car body deep-drawing press pump with primary-loaded pistons
CN107989767A (en) * 2017-12-11 2018-05-04 江苏精工泵业有限公司 A kind of motor-direct-drive type ball-screw-transmission reciprocating pump

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Publication number Priority date Publication date Assignee Title
DE809885C (en) * 1950-03-23 1951-08-02 Gerhard Sandmann Double-acting high pressure piston pump
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DE2020317A1 (en) * 1970-04-25 1971-11-11 Krueger Gmbh H Pumping device
EP0064481A1 (en) * 1981-04-30 1982-11-10 SAFE S.r.l. A reciprocating, hydraulically operated, positive displacement compressor
GB2150646A (en) * 1983-11-30 1985-07-03 Terry Blackler A pump
DE3428629A1 (en) * 1984-08-03 1986-02-13 Klaus 6107 Reinheim Obermann DUPLEX PLUNGER PUMP
US4611973A (en) * 1981-10-08 1986-09-16 P & B Industries Pumping system and method of operating the same

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Publication number Priority date Publication date Assignee Title
DE809885C (en) * 1950-03-23 1951-08-02 Gerhard Sandmann Double-acting high pressure piston pump
DE1267983B (en) * 1964-02-27 1968-05-09 Paul Hammelmann Pressure medium-driven piston pump
DE2020317A1 (en) * 1970-04-25 1971-11-11 Krueger Gmbh H Pumping device
EP0064481A1 (en) * 1981-04-30 1982-11-10 SAFE S.r.l. A reciprocating, hydraulically operated, positive displacement compressor
US4611973A (en) * 1981-10-08 1986-09-16 P & B Industries Pumping system and method of operating the same
GB2150646A (en) * 1983-11-30 1985-07-03 Terry Blackler A pump
DE3428629A1 (en) * 1984-08-03 1986-02-13 Klaus 6107 Reinheim Obermann DUPLEX PLUNGER PUMP

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19652298A1 (en) * 1996-12-16 1998-06-18 Rexroth Mannesmann Gmbh Car body deep-drawing press pump with primary-loaded pistons
CN107989767A (en) * 2017-12-11 2018-05-04 江苏精工泵业有限公司 A kind of motor-direct-drive type ball-screw-transmission reciprocating pump

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