EP0175929B1 - Twin cylinder slurry pump with a pipe switch - Google Patents

Twin cylinder slurry pump with a pipe switch Download PDF

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Publication number
EP0175929B1
EP0175929B1 EP19850110538 EP85110538A EP0175929B1 EP 0175929 B1 EP0175929 B1 EP 0175929B1 EP 19850110538 EP19850110538 EP 19850110538 EP 85110538 A EP85110538 A EP 85110538A EP 0175929 B1 EP0175929 B1 EP 0175929B1
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EP
European Patent Office
Prior art keywords
swivel
cylinder
rocker arm
sliding block
hydraulic
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.)
Expired - Lifetime
Application number
EP19850110538
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German (de)
French (fr)
Other versions
EP0175929A2 (en
EP0175929A3 (en
Inventor
Friedrich Dipl.-Ing. Schwing
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Friedrich Wilhelm Schwing GmbH
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Friedrich Wilhelm Schwing GmbH
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Filing date
Publication date
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Priority to AT85110538T priority Critical patent/ATE60112T1/en
Publication of EP0175929A2 publication Critical patent/EP0175929A2/en
Publication of EP0175929A3 publication Critical patent/EP0175929A3/en
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Publication of EP0175929B1 publication Critical patent/EP0175929B1/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
    • F04B7/0233—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated a common distribution member forming a single discharge distributor for a plurality of pumping chambers
    • F04B7/0258—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated a common distribution member forming a single discharge distributor for a plurality of pumping chambers and having an orbital movement, e.g. elbow-pipe type members
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86847—Pivoted valve unit
    • Y10T137/86855—Gate
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18888—Reciprocating to or from oscillating
    • Y10T74/1892—Lever and slide
    • Y10T74/18944—Link connections
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18888—Reciprocating to or from oscillating
    • Y10T74/1892—Lever and slide
    • Y10T74/18952—Lever and slide toggle transmissions

Definitions

  • the invention relates to a two-cylinder slurry pump according to the preamble of claim 1.
  • the invention relates to such concrete pumps.
  • the mode of operation of such points consists in sucking the thick material to be conveyed with the piston of one of the pump cylinders in the course of this, and thereby this cylinder mostly from a so-called Fill the pre-fill container, while the piston of the other pump cylinder in the inlet pushes the previously sucked thick matter into the delivery line.
  • the tube switch of the pumps is used to separate the previously pumping pump cylinder from the delivery line and to connect the other pump cylinder filled with the previously sucked in thick matter to the delivery line when the cycle is changed.
  • the swivel tube of the pipe switch measures a swivel path in each of two possible directions.
  • the ends of the swivel path are given by the alignment of the swivel tube opening with one or the other pump cylinder.
  • the drive of the swivel tube by one or more working cylinders via a crank arm enables the direct implementation of the back and forth movement of the piston rods serving as the drive of the working cylinders via the reciprocating swivel movement of the crank in the curved path, which the swivel tube connected to the crank arm contributes to of its swiveling movement.
  • the working cylinders actuating the crank arm are preferably hydraulically driven and switched in such a way that an essentially uniform piston speed over the working stroke results in them.
  • the pump cylinders in the thick matter pump according to the invention are in turn preferably driven by hydraulic drive cylinders, which can normally only be acted upon when the pipe switch has measured their swivel path, the hydraulic working cylinders of the pipe switch can be switched into a single-circuit system of the hydraulic system and therefore acted upon by the pressure generator , which also provides the hydraulic drive for the pump cylinders.
  • the invention can also be implemented with two-circuit systems which provide a different pressure generator for driving the swivel tube than for driving the pump.
  • the return flow of the thick matter from the delivery line is based on the missing overlap of the swivel tube with one of the cylinder openings of the pump after the swivel process has started and the alignment of the swivel tube with the opening of the pumping pump cylinder is canceled until it is aligned with the pump cylinder, which is filled by suction is.
  • This can mainly be counteracted by shortening the swiveling time of the swivel tube.
  • the geometric relationships of the crank mechanism lead to undesirable side effects even at relatively low swivel tube speeds.
  • crank arm accelerates the swivel tube depending on the size of the swivel angle towards the end of the swivel movement in both swivel directions if the piston speed in the working cylinder driving the swivel tube is kept approximately constant over the swivel range of the swivel tube. The result is a hard movement of the pipe switch combined with considerable dynamic loads on your organs and the machine parts interacting with them.
  • the invention relates to a previously known two-cylinder thick matter pump (DE-A 32 43 576).
  • an electrohydraulic circuit of the pump drive cylinder and the working cylinder of the pipe switch should ensure that the hydraulic pump used to generate pressure with variable amounts of swallowing above zero in the opposite direction with synchronous operation of the working cylinder of the swivel pipe, which is driven via the main circuit or a second hydraulic circuit, due to its hydraulic coupling with the actuating cylinders of the hydraulic pressure generator, the time is favorably influenced, which elapses between the end of the piston movement in the pumping pump cylinder until the pumping movement of the other pump cylinder begins during the pivoting movement of the pivoting tube.
  • the delivery rate of the hydraulic medium is linearly reduced to zero in the first half of the reversal process and linearly increased to the maximum delivery rate in the opposite direction in the second half of the reversal process.
  • the drive cylinders of the pump cylinders in addition to the described lack of suction due to suction, a further hydraulic failure occurs, which considerably extends the time of the pump interruption.
  • the invention has for its object to reduce the residual energy of the swivel tube at the ends of the swivel path in the interest of reducing the dynamic stresses while reducing the return of the thick material from the delivery line between the ends of the swivel tube movement, in order to thus the To improve the degree of uniformity of the thick matter conveyance through the conveying line.
  • the speed of the swiveling movement of the swivel tube is forcibly maintained regardless of the hydraulic loading of the working cylinder by means of a slip-free transmission which consists at least of the crank arm, the output of the working cylinder of the swivel tube and at least one further swing arm according to the invention.
  • a slip-free transmission which consists at least of the crank arm, the output of the working cylinder of the swivel tube and at least one further swing arm according to the invention.
  • the speed of the swiveling movement is continuously changed by changing the spacing from A / B via A '/ B' to A / B.
  • the swivel pipe of the thick matter pump according to the invention has, at the same total switching time, a much higher speed on the middle extent of the swivel path than in the end positions in which the speed can be reduced to a fraction of the mean swivel pipe speed.
  • the invention has the advantage that the total switching time of the swivel tube can be kept extremely short compared to comparable swivel tubes. Due to the non-uniform speed distribution over the swivel path, the opening of the swivel tube on the pump cylinder side passes the middle position, which is unfavorable for the thick material to flow back from the delivery line, e.g. about twice as fast as usual, so that consequently the amount of thick matter flowing back from the line is reduced to about 1/4. This is based on the quadratic dependence of the path or the amount on the time with constant acceleration of the line content. On the other hand, at the ends of the swivel path it is possible to set the swivel speed to e.g.
  • the transmission is realized with the minimum number of transmission members.
  • gearbox also allows driving through significant swivel angles, which can be achieved with the features of claim 3.
  • crank arm 1 With the help of a crank arm 1, a shaft is driven, the pivot axis of which penetrates the drawing plane at 2.
  • a pivot tube 4 is switched along an arcuate pivot path 6 via a pivot lever 3 'seated on the pivot shaft.
  • One of the end positions is shown at 5 in FIG. 1.
  • the crank arm is connected to a rocker arm 3 via a pair of elements.
  • the pair of elements consists of a bushing 7 and a rod 8 guided in the bushing, which is formed in one piece with the crank arm.
  • the rocker 3 is designed as a ternary gear member and with a width forming a joint Ren pair of elements, which is arranged at the opposite end of the rocker 3 and designated 9, attached to the frame at 10.
  • a third pair of elements 11 which is also formed by a joint.
  • This joint serves to connect the piston rod 12 of a hydraulic working cylinder 13, which is arranged fixed to the frame via a joint 14 at 15.
  • the piston rod 12 forms the output of the drive formed by the cylinder 13, via which the crank arm 1 is driven.
  • the rocker 3 is switched into the kinematic chain from the output 12 to the crank arm 1.
  • the crank arm 1 shown in its left extreme position can be adjusted beyond the central position shown broken off into a right end position which is not shown or can be reset from this into the left end position.
  • the rod 8 moves continuously in the bushing 7, which is rotatably mounted on the rocker 3, when the crank arm 1 measures the swivel path required until the swivel tube is in its final position.
  • the swivel tube 4 has a higher speed in the middle position, which is unfavorable for the thick material to flow back out of the conveying line, than at the end of the swivel movement. That is, the speed is reduced at the ends of the swivel path 6 compared to the average speed, whereby the load and wear are reduced.
  • FIG. 2 has not been changed with regard to the arrangement of the crank arm, the penetration point 2 of the geometric axis of the pivot shaft and the pivot lever 3 '.
  • the rocker 3 sits on its own pivot shaft, the geometric axis of which pierces the drawing plane at 16.
  • the shaft is driven by means of a gear wheel or a toothed segment 17, which rolls on a rack 18.
  • the rack 18 connects a piston 19 or 20, each of which a working cylinder 21, 22 is assigned.
  • the working cylinder 22 moves along the stationary piston rod 23 of the piston 20, which is arranged fixed to the frame at 24.
  • the piston rod 25 of the piston 19 is also fixed to the frame at 26, so that the working cylinder 21 moves along the piston rod 25.
  • the effective lever arms A of the rocker 3 and B of the crank rocker 1 are also entered in FIG. 2, as in the following illustrations.
  • the rocker 3 is also designed as a crank rocker and is connected to the joint 29 of the crank rocker 1 with the aid of a coupling which is only indicated by a dash at 27 or 28.
  • the embodiment according to FIG. 3 differs from the embodiment according to FIG. 2 primarily by the fixed arrangement of a double working cylinder 30, which is arranged fixed to the frame at 31. Between the two pistons 32, 33 extends as a connection of a toothed rack 34 which drives the rocker arm 3, which is designed as a rocker arm, via a toothed segment 35, the coupling being shown at 36.
  • crank arm 1 is in turn connected to the rocker arm 3 via a coupling shown at 37 or 38.
  • the rocker arm 3 is designed as a triangular bell crank.
  • the connecting joint 38 of the coupling 37 or 38 lies in the apex of the triangle.
  • a further connecting joint 40 or 41 is used to connect articulated levers 42, 43, which in turn are connected to a curved articulated lever 44 and of which the lever 43 is arranged fixed to the frame.
  • In the connecting joint 45 of the articulated levers 42 and 44 is the connection of the piston rod 12 acting as an output of the hydraulic working cylinder 13, which forms the drive of the swivel tube 4 via the swivel path 6.
  • two hydraulic drive cylinders 46, 46 ' are used for driving the swivel tube 4 via the swivel path 6, which are connected with their piston rods 47, 47' to the respective free ends of the swivel levers 3 designed as binary links.
  • the swivel levers 3 are in turn arranged fixed to the frame via their other pair of elements (joint) 48, 49 at 50 and 51.
  • the connection of the articulated lever 3 with the crank arm 1 takes place via coupling 52, 53, which together with the binary arm 3 result in a knee joint.
  • the working cylinders 46, 46 ' are controlled via a 2/4-way valve 54, as can be seen from the partial representation of the hydraulic working group.
  • the control processes described above are reversed analogously.

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

Description

Die Erfindung betrifft eine Zweizylinder-Dickstoffpumpe gemäß dem Oberbegriff des Patentanspruches 1. Insbesondere bezieht sich die Erfindung auf derartige Betonpumpen.The invention relates to a two-cylinder slurry pump according to the preamble of claim 1. In particular, the invention relates to such concrete pumps.

Die Arbeitsweise solcher beispielsweise aus DE-A29 31 814, DE-A 29 03 749 und DE-A 32 43 576 bekannten Punkten besteht darin, mit dem Kolben eines der Pumpenzylinder im Hergang den zu fördernden Dickstoff anzusaugen und dadurch diesen Zylinder meistens aus einem sogenannten Vorfüllbehälter zu füllen, während mit dem Kolben des anderen Pumpenzylinders im Hingang der früher angesaugte Dickstoff in die Förderleitung gedrückt wird. Die Rohrweiche der Pumpen dient dazu, beim Taktwechsel den vorher fördernden Pumpenzylinder von der Förderleitung zu trennen und den mit dem vorher angesaugten Dickstoff gefüllten anderen Pumpenzylinder mit der Förderleitung zu verbinden. Dazu durchmißt das Schwenkrohr der Rohrweiche einen Schwenkweg jeweils in einer von beiden möglichen Richtungen. Die Enden des Schwenkweges sind durch die Ausfluchtun der Schwenkrohröffnung mit dem einen oder dem anderen Pumpenzylinder gegeben. Der Antrieb des Schwenkrohres durch einen oder mehrere Arbeitszylinder über eine Kurbelschwinge ermöglicht die unmittelbare Umsetzung der Hin- und Herbewegung der als Antrieb dienenden Kolbenstangen der Arbeitszylinder über die hin- und hergehende Schwenkbewegung der Kurbel in die gekrümmte Bahn, welche das mit der Kurbelschwinge verbundene Schwenkrohr bei seiner Schwenkbewegung durchmißt.The mode of operation of such points, for example known from DE-A29 31 814, DE-A 29 03 749 and DE-A 32 43 576, consists in sucking the thick material to be conveyed with the piston of one of the pump cylinders in the course of this, and thereby this cylinder mostly from a so-called Fill the pre-fill container, while the piston of the other pump cylinder in the inlet pushes the previously sucked thick matter into the delivery line. The tube switch of the pumps is used to separate the previously pumping pump cylinder from the delivery line and to connect the other pump cylinder filled with the previously sucked in thick matter to the delivery line when the cycle is changed. For this purpose, the swivel tube of the pipe switch measures a swivel path in each of two possible directions. The ends of the swivel path are given by the alignment of the swivel tube opening with one or the other pump cylinder. The drive of the swivel tube by one or more working cylinders via a crank arm enables the direct implementation of the back and forth movement of the piston rods serving as the drive of the working cylinders via the reciprocating swivel movement of the crank in the curved path, which the swivel tube connected to the crank arm contributes to of its swiveling movement.

Erfindungsgemäß sind die die Kurbelschwinge betätigenden Arbeitszylinder vorzugsweise hydraulisch angetrieben und so geschaltet, daß sich in ihnen eine im wesentlichen gleichmäßige Kolbengeschwindigkeit über den Arbeitshub ergibt. Da die Pumpenzylinder in der erfindungsgemäßen Dickstoffpumpe vorzugsweise ihrerseits mit hydraulischen Antriebszylindern angetrieben sind, welche normalerweise erst beaufschlagt werden können, wenn die Rohrweiche ihren Schwenkweg durchmessen hat, können die hydraulischen Arbeitszylinder der Rohrweiche in ein Einkreissystem der hydraulischen Anlage eingeschaltet und daher von dem Druckerzeuger beaufschlagt werden, der auch den hydraulischen Antrieb der Pumpenzylinder besorgt. Die Erfindung läßt sich ab der auch mit Zweikreissystemen verwirklichen, welche für den Antrieb des Schwenkrohres einen anderen Druckerzeuger als für den Antrieb der Pumpe vorsieht. Dadurch ist es möglich, die Voraussetzungen für die zeitliche Begrenzung des Umschaltvorganges der Rohrweiche zu schaffen, welche einerseits den Gleichförmigkeitsgrad der Dickstofförderung durch die Förderleitung und andererseits die Förderleistung bestimmt. Zwar werden diese Kennwerte von der gesamten Unterbrechung der Pumpwirkung zwischen den Arbeitstakten der Pumpenzylinder bestimmt und diese ergibt sich nicht allein aus der Verschwenkzeit, welche das Schwenkrohr zwischen den Takten benötigt, sondern u.a. auch aus dem Ausgleich des Fehlvolumens, das durch den volumetrischen Saugwirkungsgrad zustande kommt, sowie aus dem Dickstoffrückfluß aus der Förderleitung, der ebenfalls ausgeglichen werden muß, jedoch hängt auch der Rückfluß von der Verschwenkzeit ab.According to the invention, the working cylinders actuating the crank arm are preferably hydraulically driven and switched in such a way that an essentially uniform piston speed over the working stroke results in them. Since the pump cylinders in the thick matter pump according to the invention are in turn preferably driven by hydraulic drive cylinders, which can normally only be acted upon when the pipe switch has measured their swivel path, the hydraulic working cylinders of the pipe switch can be switched into a single-circuit system of the hydraulic system and therefore acted upon by the pressure generator , which also provides the hydraulic drive for the pump cylinders. The invention can also be implemented with two-circuit systems which provide a different pressure generator for driving the swivel tube than for driving the pump. This makes it possible to create the prerequisites for the time limitation of the switching process of the pipe switch, which on the one hand determines the degree of uniformity of the thick matter conveyance through the delivery line and on the other hand the delivery rate. These parameters are determined by the total interruption of the pumping action between the work cycles of the pump cylinders, and this does not only result from the swivel time that the swivel tube requires between the cycles, but also, among other things. also from the compensation of the missing volume, which is caused by the volumetric suction efficiency, and from the thick material return flow from the delivery line, which also has to be compensated, but the return flow also depends on the pivoting time.

Der Rückfluß des Dickstoffes aus der Förderleitung beruht auf der fehlenden Überdeckung des Schwenkrohres mit einer der Zylinderöffnungen der Pumpe, nachdem der Schwenkvorgang eingesetzt hat und die Ausfluchtung des Schwenkrohres mit der Öffnung des fördernden Pumpenzylinders aufgehoben ist bis zur Ausfluchtung mit dem Pumpenzylinder, welche durch Ansaugen gefüllt ist. Dem kann hauptsächlich mit einer Verkürzung der Verschwenkzeit des Schwenkrohres entgegengewirkt werden. Andererseits führen die geometrischen Verhältnisse des Kurbeltriebes bereits bei relativ geringen Schwenkrohrgeschwindigkeiten zu unerwünschten Nebenwirkungen. Denn die Kurbelschwinge beschleunigt das Schwenkrohr je nach der Größe des Schwenkwinkels gegen Ende der Schwenkbewegung in beiden Schwenkrichtungen, wenn die Kolbengeschwindigkeit in dem das Schwenkrohr antreibenden Arbeitszylinder über den Schwenkbereich des Schwenkrohres annähernd konstant gehalten wird. Die Folge ist ein harter Gang der Rohrweiche verbunden mit erheblichen dynamischen Belastungen ihrer Organe und der mit diesen zusammenwirkenden Maschinenteile.The return flow of the thick matter from the delivery line is based on the missing overlap of the swivel tube with one of the cylinder openings of the pump after the swivel process has started and the alignment of the swivel tube with the opening of the pumping pump cylinder is canceled until it is aligned with the pump cylinder, which is filled by suction is. This can mainly be counteracted by shortening the swiveling time of the swivel tube. On the other hand, the geometric relationships of the crank mechanism lead to undesirable side effects even at relatively low swivel tube speeds. Because the crank arm accelerates the swivel tube depending on the size of the swivel angle towards the end of the swivel movement in both swivel directions if the piston speed in the working cylinder driving the swivel tube is kept approximately constant over the swivel range of the swivel tube. The result is a hard movement of the pipe switch combined with considerable dynamic loads on your organs and the machine parts interacting with them.

Die Erfindung geht aus von einer vorbekannten Zweizylinder-Dickstoffpumpe (DE-A 32 43 576). Hierbei soll eine elektrohydraulische Schaltung der Pumpenantriebszylinder und der Arbeitszylinder der Rohrweiche dafür sorgen, daß die zur Druckerzeugung dienende hydraulische Pumpe mit veränderlicher Schluckmenge über Null in entgegengesetzter Richtung bei synchronem Lauf des über den Hauptkreis oder einen zweiten hydraulischen Kreis angetriebenen Arbeitszylinders des Schwenkrohres infolge seiner hydraulischen Kupplung mit den Stellzylindern des hydraulischen Druckerszeugers die Zeit günstig beeinflußt, welche zwischen dem Ende der Kolbenbewegung im fördernden Pumpenzylinder bis zum Einsetzen der Pumpbewegung des anderen Pumpzylinders während der Schwenkbewegung des Schwenkrohres verstreicht. Hierdurch wird also die Fördermenge des hydraulischen Mediums in der ersten Hälfte des Umsteuervorganges linear auf Null reduziert und in der zweiten Hälfte des Umsteuervorganges linear auf die Maximalfördermenge in entgegengesetzter Richtung gesteigert. In den Antriebszylindern der Pumpenzylinder entsteht dadurch jedoch zusätzlich zu dem beschriebenen saugbedingten Fehlvolumen ein weiteres hydraulisches Fehlvolumen, was die Zeit der Pumpunterbrechung erheblich verlängert. Im allgemeinen ergeben sich hieraus auch keine nennenswerten Geschwindigkeitsunterschiede der Kolben in den Arbeitszylindern des Schwenkrohres und des Schwenkrohres auf seinem Schwenkweg. Infolgedessen müssen im wesentlichen die bei der Bewegung des Schwenkrohres auftretenden schädlichen dynamischen Beanspruchungen weiterhin in Kauf genommen werden.The invention relates to a previously known two-cylinder thick matter pump (DE-A 32 43 576). Here, an electrohydraulic circuit of the pump drive cylinder and the working cylinder of the pipe switch should ensure that the hydraulic pump used to generate pressure with variable amounts of swallowing above zero in the opposite direction with synchronous operation of the working cylinder of the swivel pipe, which is driven via the main circuit or a second hydraulic circuit, due to its hydraulic coupling with the actuating cylinders of the hydraulic pressure generator, the time is favorably influenced, which elapses between the end of the piston movement in the pumping pump cylinder until the pumping movement of the other pump cylinder begins during the pivoting movement of the pivoting tube. As a result, the delivery rate of the hydraulic medium is linearly reduced to zero in the first half of the reversal process and linearly increased to the maximum delivery rate in the opposite direction in the second half of the reversal process. In the drive cylinders of the pump cylinders, however, in addition to the described lack of suction due to suction, a further hydraulic failure occurs, which considerably extends the time of the pump interruption. In general, there are no significant differences in the speed of the pistons in the working cylinders of the swivel tube and the swivel tube its swivel path. As a result, the damaging dynamic stresses that occur during the movement of the swivel tube must essentially still be accepted.

Der Erfindung liegt die Aufgabe zugrunde, bei kurzer Schwenkzeit der Rohrweiche die Restenergie des Schwenkrohres an den Enden des Schwenkweges im Interesse der Verminderung der dynamischen Beanspruchungen zu reduzieren und dabei den Rücklauf des Dickstoffes aus der Förderleitung zwischen den Enden der Schwenkrohrbewegung zu vermindern, um derart den Gleichförmigkeitsgrad der Dickstofförderung durch die Förderleitung zu verbessern.The invention has for its object to reduce the residual energy of the swivel tube at the ends of the swivel path in the interest of reducing the dynamic stresses while reducing the return of the thick material from the delivery line between the ends of the swivel tube movement, in order to thus the To improve the degree of uniformity of the thick matter conveyance through the conveying line.

Diese Aufgabe löst die Erfindung mit den kennzeichnenden Merkmalen des Anspruches 1. Zweckmäßige Ausführungsformen der Erfindung sind Gegenstand der Unteransprüche.This object is achieved by the invention with the characterizing features of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

Gemäß der Erfindung wird die Geschwindigkeit der Schwenkbewegung des Schwenkrohres unabhängig von der hydraulischen Beaufschlagung des Arbeitszylinders zwangsweise durch ein schlupfloses Getriebe eingehalten, welches mindestens aus der Kurbelschwinge, dem Abtrieb der Arbeitszylinder des Schwenkrohres und mindestens einer weiteren erfindungsgemäßen Schwinge besteht. In diesem Getriebe wird durch die Änderung der Abstandsverhältnisse von A/B über A'/B' in A/B die Geschwindigkeit der Schwenkbewegung kontinuierlich geändert. Gegenüber den bekannten Schwenkrohren hat das Schwenkrohr der erfindungsgemäßen Dickstoffpumpe bei gleicher Gesamtschaltzeit auf der mittleren Erstreckung des Schwenkweges eine vielfach höhere Geschwindigkeit als in den Endlagen, in denen sich die Geschwindigkeit auf einen Bruchteil der mittleren Schwenkrohrgeschwindigkeit reduzieren läßt.According to the invention, the speed of the swiveling movement of the swivel tube is forcibly maintained regardless of the hydraulic loading of the working cylinder by means of a slip-free transmission which consists at least of the crank arm, the output of the working cylinder of the swivel tube and at least one further swing arm according to the invention. In this transmission, the speed of the swiveling movement is continuously changed by changing the spacing from A / B via A '/ B' to A / B. Compared to the known swivel pipes, the swivel pipe of the thick matter pump according to the invention has, at the same total switching time, a much higher speed on the middle extent of the swivel path than in the end positions in which the speed can be reduced to a fraction of the mean swivel pipe speed.

Die Erfindung hat den Vorteil, daß die Gesamtschaltzeit des Schwenkrohres gegenüber vergleichbaren Schwenkrohren extrem kurz gehalten werden kann. Durch die ungleichförmige Geschwindigkeitsverteilung über den Schwenkweg überfährt die pumpenzylinderseitige Öffnung des Schwenkrohres die für das Zurückströmen des Dickstoffes aus der Förderleitung ungünstige Mittelstellung z.B. etwa doppelt so schnell als gewöhnlich, so daß folglich die aus der Leitung zurückströmende Dickstoffmenge auf ca. 1/4 reduziert wird. Das beruht auf der quadratischen Abhängigkeit des Weges bzw. der Menge von der Zeit bei konstanter Beschleunigung des Leitungsinhaltes. Andererseits ist es möglich, an den Enden des Schwenkweges die Schwenkgeschwindigkeit auf z.B. 1/3 der mittleren Geschwindigkeit der Schwenkrohrgeschwindigkeit zu reduzieren. Dadurch ist die Restenergie des Schwenkrohres beim Anschlagen in der Endlage auf ca 1/ 9 reduziert, was zu einer erheblichen Reduzierung der Belastung und des Verschleißes führt. Endlich sind die Kräfte am Schwenkrohr der Geschwindigkeit umgekehrt proportional. Dadurch steigen die Kräfte unter den geschilderten Verhältnissen in den Endlagen auf das Dreifache der mittleren Kräfte an. Das entspricht der Forderung der Praxis nach sicherem Durchschalten des Schwenkrohres, was bei der Betonförderung u.U. das Zerbrechen von Steinen erforderlich macht.The invention has the advantage that the total switching time of the swivel tube can be kept extremely short compared to comparable swivel tubes. Due to the non-uniform speed distribution over the swivel path, the opening of the swivel tube on the pump cylinder side passes the middle position, which is unfavorable for the thick material to flow back from the delivery line, e.g. about twice as fast as usual, so that consequently the amount of thick matter flowing back from the line is reduced to about 1/4. This is based on the quadratic dependence of the path or the amount on the time with constant acceleration of the line content. On the other hand, at the ends of the swivel path it is possible to set the swivel speed to e.g. Reduce 1/3 of the average speed of the swivel tube speed. As a result, the residual energy of the swivel tube when struck in the end position is reduced to approx. 1/9, which leads to a considerable reduction in the load and wear. Finally, the forces on the swivel tube are inversely proportional to the speed. As a result, the forces in the end positions increase to three times the average forces. This corresponds to the requirement of practice for safe switching of the swivel tube, which may be the case with concrete delivery. requires the breaking of stones.

Vorzugsweise wird mit den Merkmalen des Anspruches 2 das Getriebe mit der minimalen Anzahl von Getriebegliedern verwirklicht.Preferably, with the features of claim 2, the transmission is realized with the minimum number of transmission members.

Das Getriebe ermöglicht jedoch auch das Durchfahren erheblicher Schwenkwinkel, was mit den Merkmalen des Anspruches 3 zu erreichen ist.However, the gearbox also allows driving through significant swivel angles, which can be achieved with the features of claim 3.

Es ist auch nicht erforderlich, in dem Getriebe nur schwenkende Glieder zu verwirklichen. Mit den Merkmalen des Anspruches 4 lassen sich Drehbewegungen über beliebige Schwenkwinkel erzielen.It is also not necessary to implement only pivoting links in the transmission. With the features of claim 4, rotary movements can be achieved over any pivot angle.

Mit den Merkmalen des Anspruches 5 ist es möglich, jeder Richtung der Schwenkbewegung einen eigenen Arbeitszylinder zuzuordnen.With the features of claim 5, it is possible to assign a separate working cylinder to each direction of the pivoting movement.

Eine Umgehung der Gleitführung der Anschlußelemente nach Anspruch 2 einerseits bzw. bei unterschiedlichsten räumlichen Verhältnissen jeweils anwendbare Bauweisen (Alternativen) ermöglichen die Merkmale der Ansprüche 3, 4, 5.Bypassing the sliding guidance of the connection elements according to claim 2, on the one hand, or the construction methods (alternatives) which can be used in each case in the most varied spatial conditions, enable the features of claims 3, 4, 5.

Die Einzelheiten der Erfindung ergeben sich aus ihrer nachfolgenden Beschreibung anhand mehrerer Ausführungsbeispiele, die in den Figuren der Zeichnung wiedergegeben sind;

  • Fig. 1 schematisch, d.h. unter Fortlassung aller für das Verständnis der Erfindung nicht erforderlichen Einzelheiten den Antrieb eines Schwenkrohres in einer Dickstoffpumpe gemäß der Erfindung und in einer ersten Ausführungsform,
  • Fig. 2 in der Fig. 1 entsprechender Darstellung eine geänderte Ausführungsform der Erfindung,
  • Fig. 3 in den Fig. 1 und 2 entsprechender Darstellung eine weiter abgeänderte Ausführungsform der Erfindung,
  • Fig. 4 in den Fig. 1 bis 3 entsprechender Darstellung eine andere Ausführungsart der Erfindung,
  • Fig. 5 in den Fig. 1 bis 4 entsprechender Darstellung unter teilweise Wiedergabe des hydraulischen Arbeitskreises eine andere Ausführungsart der Erfindung und
  • Fig. 6 ein Diagramm, in dem auf der Abszisse Zeit und Schwenkweg sowie auf der Ordinate die Geschwindigkeit der Schwenkbewegung abgetragen sind und in dem die Kennlinien der bekannten und der erfindungsgemäßen Dickstoffpumpen, sowie der mittlere Geschwindigkeitsverlauf angegeben sind.
The details of the invention emerge from the description below with reference to several exemplary embodiments which are shown in the figures of the drawing;
  • 1 schematically, ie omitting all details not necessary for understanding the invention, the drive of a swivel tube in a thick matter pump according to the invention and in a first embodiment,
  • 2 corresponding representation of a modified embodiment of the invention,
  • 3 in FIGS. 1 and 2 corresponding representation a further modified embodiment of the invention,
  • 4 in FIGS. 1 to 3 corresponding representation another embodiment of the invention,
  • Fig. 5 in Figs. 1 to 4 corresponding representation with partial reproduction of the hydraulic working group another embodiment of the invention and
  • 6 shows a diagram in which the speed of the swiveling movement is plotted on the abscissa time and swivel path and on the ordinate and in which the characteristic curves of the known and the thick matter pumps according to the invention and the average speed curve are given.

Mit Hilfe einer Kurbelschwinge 1 wird eine Welle angetrieben, deren Schwenkachse bei 2 die Zeichenebene durchstößt. Über einen auf der Schwenkwelle sitzenden Schwenkhebel 3' wird ein Schwenkrohr 4 längs eines bogenförmigen Schwenkweges 6 geschaltet. Eine der Endstellungen ist bei 5 in Fig. 1 dargestellt.With the help of a crank arm 1, a shaft is driven, the pivot axis of which penetrates the drawing plane at 2. A pivot tube 4 is switched along an arcuate pivot path 6 via a pivot lever 3 'seated on the pivot shaft. One of the end positions is shown at 5 in FIG. 1.

Die Kurbelschwinge ist über ein Elementenpaar an eine Schwinge 3 angeschlossen. Das Elementenpaar besteht aus einer Buchse 7 und einer in der Buchse geführten Stange 8, welche einteilig mit der Kurbelschwinge ausgebildet ist. Die Schwinge 3 ist als ternäres Getriebeglied ausgebildet und mit einem ein Gelenk bildenden weiteren Elementenpaar, das am gegenüberliegenden Ende der Schwinge 3 angeordnet und mit 9 bezeichnet ist, gestellfest bei 10 angebracht. Zwischen den beiden Elementenpaaren 7, 8 bzw. 9 liegt ein drittes Elementenpaar 11, das ebenfalls von einem Gelenk gebildet wird. Dieses Gelenk dient zum Anschluß der Kolbenstange 12 eines hydraulischen Arbeitszylinders 13, welcher über ein Gelenk 14 bei 15 gestellfest angeordnet ist. Die Kolbenstange 12 bildet den Abtrieb des vom Zylinder 13 gebildeten Antriebes, über den die Kurbelschwinge 1 angetrieben wird.The crank arm is connected to a rocker arm 3 via a pair of elements. The pair of elements consists of a bushing 7 and a rod 8 guided in the bushing, which is formed in one piece with the crank arm. The rocker 3 is designed as a ternary gear member and with a width forming a joint Ren pair of elements, which is arranged at the opposite end of the rocker 3 and designated 9, attached to the frame at 10. Between the two pairs of elements 7, 8 and 9 is a third pair of elements 11, which is also formed by a joint. This joint serves to connect the piston rod 12 of a hydraulic working cylinder 13, which is arranged fixed to the frame via a joint 14 at 15. The piston rod 12 forms the output of the drive formed by the cylinder 13, via which the crank arm 1 is driven.

Wie aus Fig. 1 ersichtlich ist, ist die Schwinge 3 in die kinematische Kette vom Abtrieb 12 bis zur Kurbelschwinge 1 eingeschaltet. Dabei kann die in ihrer linken Extremstellung wiedergegebene Kurbelschwinge 1 über die abgebrochen dargestellte Mittellage hinaus in eine rechte und nicht wiedergegebene Endlage verstellt bzw. aus dieser in die linke Endlage zurückgestellt werden. Infolge der Ausbildung des Elementenpaares 7, 8 verschiebt sich die Stange 8 in der drehbar auf der Schwinge 3 gelagerten Buchse 7 kontinuierlich, wenn die Kurbelschwinge 1 den bis zur Endstellung des Schwenkrohres erforderlichen Schwenkweg durchmißt. Mit B ist der wirksame Hebelarm der Kurbelschwinge 1 und mit A der wirksame Hebelarm der Schwinge 3 in den Endstellungen des Schwenkrohres 4 bezeichnet und mit B' ist der wirksame Hebelarm der Kurbelschwinge 1 und mit A' ist der wirksame Hebelarm der Schwinge 3 in der Mittellage der Schwenkbewegung bezeichnet. Das Hebelarmverhältnis A'/B' macht ein Vielfaches, z.B. ein 3- bis 7-Faches des entsprechenden Hebelarmverhältnisses A/B des Getriebes aus. Dadurch wird die Geschwindigkeit der Bewegung des Schwenkrohres 4 über den Schwenkweg 6 beim Hin- und Hergang der Kurbelschwinge 1 kontinuierlich geändert. Aufgrund der wiedergegebenen Geometrie hat das Schwenkrohr 4 in der für das Zurückströmen des Dickstoffes aus der Förderleitung ungünstigen Mittelstellung eine größere Geschwindigkeit als am Ende der Schwenkbewegung. Das heißt, die Geschwindigkeit wird an den Enden des Schwenkweges 6 gegenüber der mittleren Geschwindigkeit reduziert, wodurch die Belastung und der Verschleiß gemindert werden.As can be seen from Fig. 1, the rocker 3 is switched into the kinematic chain from the output 12 to the crank arm 1. In this case, the crank arm 1 shown in its left extreme position can be adjusted beyond the central position shown broken off into a right end position which is not shown or can be reset from this into the left end position. As a result of the formation of the pair of elements 7, 8, the rod 8 moves continuously in the bushing 7, which is rotatably mounted on the rocker 3, when the crank arm 1 measures the swivel path required until the swivel tube is in its final position. With B the effective lever arm of the rocker arm 1 and with A the effective lever arm of the rocker arm 3 in the end positions of the swivel tube 4 is designated and with B 'is the effective lever arm of the crank arm 1 and with A' is the effective lever arm of the rocker arm 3 in the central position called the pivoting movement. The lever arm ratio A '/ B' makes a multiple, e.g. 3 to 7 times the corresponding lever arm ratio A / B of the gearbox. As a result, the speed of the movement of the swivel tube 4 via the swivel path 6 is continuously changed during the back and forth movement of the crank arm 1. Because of the geometry shown, the swivel tube 4 has a higher speed in the middle position, which is unfavorable for the thick material to flow back out of the conveying line, than at the end of the swivel movement. That is, the speed is reduced at the ends of the swivel path 6 compared to the average speed, whereby the load and wear are reduced.

Die Ausführungsform nach Fig. 2 ist hinsichtlich der Anordnung der Kurbelschwinge, des Durchstoßungspunktes 2 der geometrischen Achse der Schwenkwelle und des Schwenkhebels 3' nicht geändert. Die Schwinge 3 sitzt jedoch auf einer eigenen Schwenkwelle, deren geometrische Achse die Zeichenebene bei 16 durchstößt. Die Welle wird mit Hilfe eines Zahnrades bzw. eines Zahnsegmentes 17 angetrieben, das sich auf einer Zahnstange 18 abwälzt. Die Zahnstange 18 verbindet je einen Kolben 19 bzw. 20, denen jeweils ein Arbeitszylinder 21, 22 zugeordnet ist. Der Arbeitszylinder 22 bewegt sich längs der stillstehenden Kolbenstange 23 des Kolbens 20, die bei 24 gestellfest angeordnet ist. Auch die Kolbenstange 25 des Kolbens 19 ist bei 26 gestellfest angeordnet, so daß sich der Arbeitszylinder 21 längs der Kolbenstange 25 bewegt. Zum besseren Verständnis sind auch in Fig. 2 ebenso wie in den nachfolgenden Darstellungen die wirksamen Hebelarme A der Schwinge 3 und B der Kurbelschwinge 1 eingetragen. Im Ausführungsbeispiel nach Fig. 2 ist auch die Schwinge 3 als Kurbelschwinge ausgebildet und mit Hilfe einer lediglich bei 27 bzw. 28 durch einen Strich angedeuteten Koppel mit dem Gelenk 29 der Kurbelschwinge 1 verbunden.The embodiment according to FIG. 2 has not been changed with regard to the arrangement of the crank arm, the penetration point 2 of the geometric axis of the pivot shaft and the pivot lever 3 '. However, the rocker 3 sits on its own pivot shaft, the geometric axis of which pierces the drawing plane at 16. The shaft is driven by means of a gear wheel or a toothed segment 17, which rolls on a rack 18. The rack 18 connects a piston 19 or 20, each of which a working cylinder 21, 22 is assigned. The working cylinder 22 moves along the stationary piston rod 23 of the piston 20, which is arranged fixed to the frame at 24. The piston rod 25 of the piston 19 is also fixed to the frame at 26, so that the working cylinder 21 moves along the piston rod 25. For better understanding, the effective lever arms A of the rocker 3 and B of the crank rocker 1 are also entered in FIG. 2, as in the following illustrations. In the exemplary embodiment according to FIG. 2, the rocker 3 is also designed as a crank rocker and is connected to the joint 29 of the crank rocker 1 with the aid of a coupling which is only indicated by a dash at 27 or 28.

Die Ausführungsform nach Fig. 3 unterscheidet sich von der Ausführungsart nach Fig. 2 vor allem durch die ortsfeste Anordnung eines doppelten Arbeitszylinders 30, welcher bei 31 gestellfest angeordnet ist. Zwischen den beiden Kolben 32, 33 erstreckt sich als Verbindung eines Zahnstange 34, die über ein Zahnsegment 35 die als Kurbelschwinge ausgebildete Schwinge 3 antreibt, wobei die Koppel bei 36 wiedergegeben ist.The embodiment according to FIG. 3 differs from the embodiment according to FIG. 2 primarily by the fixed arrangement of a double working cylinder 30, which is arranged fixed to the frame at 31. Between the two pistons 32, 33 extends as a connection of a toothed rack 34 which drives the rocker arm 3, which is designed as a rocker arm, via a toothed segment 35, the coupling being shown at 36.

In der Ausführungsform der Fig. 4 ist die Kurbelschwinge 1 ihrerseits über eine bei 37 bzw. 38 dargestellte Koppel an die Schwinge 3 angeschlossen. Die Schwinge 3 ist als dreieckförmiger Umlenkhebel ausgebildet. Das Anschlußgelenk 38 der Koppel 37 bzw. 38 liegt im Scheitel des Dreiecks. Je ein weiteres Anschlußgelenk 40 bzw. 41 dient zum Anschluß von Gelenkhebeln 42, 43, die ihrerseits mit einem gekrümmten Gelenkhebei 44 verbunden sind und von denen der Hebel 43 gestellfest angeordnet ist. Im Anschlußgelenk 45 der Gelenkhebel 42 und 44 liegt der Anschluß der als Abtrieb wirkenden Kolbenstange 12 des hydraulischen Arbeitszylinders 13, der den Antrieb des Schwenkrohres 4 über den Schwenkweg 6 bildet.In the embodiment of FIG. 4, the crank arm 1 is in turn connected to the rocker arm 3 via a coupling shown at 37 or 38. The rocker arm 3 is designed as a triangular bell crank. The connecting joint 38 of the coupling 37 or 38 lies in the apex of the triangle. A further connecting joint 40 or 41 is used to connect articulated levers 42, 43, which in turn are connected to a curved articulated lever 44 and of which the lever 43 is arranged fixed to the frame. In the connecting joint 45 of the articulated levers 42 and 44 is the connection of the piston rod 12 acting as an output of the hydraulic working cylinder 13, which forms the drive of the swivel tube 4 via the swivel path 6.

In der Ausführungsform der Fig. 5 werden für den Antrieb des Schwenkrohres 4 über den Schwenkweg 6 zwei hydraulische Antriebszylinder 46, 46' benutzt, die mit ihren Kolbenstangen 47, 47' an die jeweiligen freien Enden der als binäre Glieder ausgebildeten Schwenkhebel 3 angeschlossen sind. Die Schwenkhebel 3 sind ihrerseits über ihre anderen Elementenpaar (Gelenk) 48, 49 bei 50 und 51 gestellfest angeordnet. Die Verbindung der Gelenkhebel 3 mit der Kurbelschwinge 1 erfolgt über Koppeln 52, 53, die zusammen mit den binären Schwingen 3 ein Kniegelenk ergeben.In the embodiment of FIG. 5, two hydraulic drive cylinders 46, 46 'are used for driving the swivel tube 4 via the swivel path 6, which are connected with their piston rods 47, 47' to the respective free ends of the swivel levers 3 designed as binary links. The swivel levers 3 are in turn arranged fixed to the frame via their other pair of elements (joint) 48, 49 at 50 and 51. The connection of the articulated lever 3 with the crank arm 1 takes place via coupling 52, 53, which together with the binary arm 3 result in a knee joint.

Die Steuerung der Arbeitszylinder 46, 46' erfolgt über ein 2/4-Wegeventil 54, wie sich aus der teilweisen Darstellung des hydraulischen Arbeitskreises ergibt. Dabei sind die beiden hydraulischen Antriebszylinder 46, 46' über Steuerleitungen miteinander verbunden, daß z.B. bei Zuleitungdes Drucköls P zum hydraulischen Antriebszylinder 46 der andere hydraulische Antriebszylinder 46' über die frei miteinander verbundenen Leitungen a, c und d kolbenstangenseitig beaufschlagt wird und bis zur Mittellage der Schwenkbewegung den Antrieb der Kurbelschwinge besorgt, worauf eine Umschaltung, d.h. Sperrung der Leitungsverbindung c-d und Öffnung der Leitungsverbindung d-c' erfolgt und von der Mittellage bis zur zweiten Endlage der nunmehr kolbenseitig beaufschlagte hydraulische Arbeitszylinder 46 den Antrieb der Kurbelschwinge besorgt. Bei entgegengesetzter Schwenkbewegung kehren sich die zuvor beschriebenen Steuervorgänge sinngemäß um.The working cylinders 46, 46 'are controlled via a 2/4-way valve 54, as can be seen from the partial representation of the hydraulic working group. The two hydraulic drive cylinders 46, 46 'are connected to one another via control lines so that, for example when the pressure oil P is fed to the hydraulic drive cylinder 46, the other hydraulic drive cylinder 46' is acted upon via the freely connected lines a, c and d on the piston rod side and up to the middle position of the Swiveling movement ensures the drive of the crank arm, whereupon a switchover, ie blocking of the line connection cd and opening of the line connection dc ', and from the middle position to the second end position of the hydraulic side now acted upon on the piston side Working cylinder 46 worried the drive of the crank arm. In the opposite pivoting movement, the control processes described above are reversed analogously.

Claims (6)

1. A twin-cylinder slurry pump with a pipe switch which alternately connects one of the pump cylinders to the feed pipe and disconnects the other pump cylinder by means of a swivel pipe, which is moved over its swivel path by a sliding block (1) by means of a rocking shaft by one or more variable speed hydraulic cylinders, characterised in that in the transmission of motion from the hydraulic cylinder or hydraulic cylinders to the sliding block (1) at least one rocker arm (3) is engaged which serves to vary the distance of the connector member (7, 8) of the sliding block (1) from the rocking shaft axis (2) proceeding from a maximum distance at the beginning and at the end of the swivel path (6) to a minimum distance at the middle of the swivel path (6) or has a moment-effective lever arm variation such that the transition from the middle of the swivel path to both end positions continuously decreases.
2. A twin-cylinder slurry pump according to Claim 1, characterised in that the rocker arm (3) is so arranged that the ratio of the moment-effective distance (A') of the swivel point (9) of the rocker arm (3) perpendicularly to the direction of force transmission (X) of the connecting member (7, 8) to the moment-effective distance (B') of the swivel point (2) of the sliding block (1) perpendicularly to the direction of force transmission of the connecting member (7, 8) in the middle position of the swivel movement amounts to a multiple of the corresponding distance ratio (A/B) in the end positions of the swivel movement.
3. A twin-cylinder slurry pump according to one of Claims 1 and 2, characterised in that the rocker arm (3) is arranged so that it can swivel and is fixed to a mount and the piston rod (12) of the hydraulic cylinder (13) is articulated on the rocker arm, and that the connecting member consists of a rotatable bush (7) in which the end of the sliding block (1) formed as a rod (8) is held.
4. A twin-cylinder slurry pump according to one of Claims 1 and 2, characterised in that the rocker arm (3) is constructed as a triangular-shaped shift lever, which is connected with the connecting member of the sliding block (1) by means of a rigid connecting rod (37, 38).
5. A twin-cylinder slurry pump according to one of Claims 1 and 2, characterised in that the rocker arm (3) is constructed as a crank on a shaft (16), whereby the shaft is driven via a rack and pinion drive (17, 18; 34, 35) and the rocker arm (3) formed as a crank is connected to the connecting member of the sliding block by a rigid connecting rod (27, 36).
6. A twin-cylinder slurry pump according to one of Claims 1 and 2, characterised in that the sliding block (1) is connected in both directions of swivel via a coupling (52, 53) to a respective rocker arm (3) whereby each rocker arm (3) has a hydraulic drive cylinder and both hydraulic drive cylinders are connected via control lines such that for example, with the supply lines for the pressure oil (P) to a hydraulic operating cylinder (46), the other hydraulic operating cylinder (46') is loaded via the pipes (a, c and d) connected freely with one another on the side of the piston rod and provides the drive of the sliding block up to the middle position of the swivel movement, whereupon a reversal occurs, that is closing of the pipe connection (c-d) and opening of the pipe connection (d-c) and provides the drive of the sliding block (1) from the middle position up to the second end position of the first hydraulic drive cylinder (46) loaded on the piston side and that these control processes are correspondingly reversed for the opposite swivel movement.
EP19850110538 1984-09-25 1985-08-22 Twin cylinder slurry pump with a pipe switch Expired - Lifetime EP0175929B1 (en)

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AT85110538T ATE60112T1 (en) 1984-09-25 1985-08-22 TWO-CYLINDER CYLINDER PUMP WITH TRANSDUCER.

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DE3435052 1984-09-25
DE3435052 1984-09-25
DE3524033 1985-07-05
DE19853524033 DE3524033A1 (en) 1984-09-25 1985-07-05 TWO-CYLINDER FUEL PUMP WITH Diverter

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EP0175929A2 EP0175929A2 (en) 1986-04-02
EP0175929A3 EP0175929A3 (en) 1989-02-08
EP0175929B1 true EP0175929B1 (en) 1991-01-16

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Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4800767A (en) * 1987-06-08 1989-01-31 Builders Equipment Company Acceleration control device for a hydraulic drive unit
US5157981A (en) * 1991-05-28 1992-10-27 Kim Chang H Motion lever
DE4327177A1 (en) * 1993-08-13 1995-02-16 Putzmeister Maschf Arrangement for opening and closing a cap
DE4344632A1 (en) * 1993-12-24 1995-06-29 Putzmeister Maschf Slide device for a two-cylinder slurry pump
WO2007111689A2 (en) * 2005-11-08 2007-10-04 Good Earth Tools, Inc. Sealing rings for abrasive slurry pumps
JP5453918B2 (en) 2009-05-18 2014-03-26 トヨタ自動車株式会社 Flow control valve
KR101068025B1 (en) * 2009-11-06 2011-09-28 주식회사 드림피아 Fluid pump
KR101335345B1 (en) * 2010-12-31 2013-12-03 신재희 Compressor
US9651313B2 (en) 2012-10-10 2017-05-16 Research Triangle Institute Particulate heat transfer fluid and related system and method

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE947040C (en) * 1953-09-16 1956-08-09 Torkret Ges Mit Beschraenkter Hydraulically driven piston pump for pumping thick, pulpy masses, e.g. B. Concrete
US3027155A (en) * 1958-12-23 1962-03-27 Transfer Tools Ltd Means for releasably clamping articles
US3109457A (en) * 1959-09-25 1963-11-05 Aerotec Ind Inc Gate valve
US3254660A (en) * 1963-12-19 1966-06-07 Itt Closure operator for valves
DE1908741A1 (en) * 1969-02-21 1970-09-03 Schwing Dipl Ing Friedrich Wil Piston pump for pumping concrete
US4102613A (en) * 1977-01-06 1978-07-25 Vukich Martin T Concrete pumping machine
DE2841183C2 (en) * 1978-09-22 1982-07-15 Industrie-Werke Karlsruhe Augsburg AG Zweigniederlassung Keller & Knappich Augsburg, 8900 Augsburg Handling device with a cantilever arm
DE2903749C2 (en) * 1979-02-01 1983-11-10 Karl Dipl.-Ing. 7000 Stuttgart Schlecht Piston pump with an S-shaped swivel tube
DE2931814A1 (en) * 1979-08-06 1981-02-12 Schlecht Karl Oscillating tube type concrete pump - has arm inside hopper resting on tube at one end and against hopper surface at other end
US4337017A (en) * 1979-09-26 1982-06-29 Evenson William R Hydraulic sleeve valve and seal arrangement for piston pump
JPS56106081A (en) * 1980-01-28 1981-08-24 Mitsubishi Heavy Ind Ltd Gate change-over device in concrete pump
JPS5928073A (en) * 1982-06-25 1984-02-14 ウイバウ・アクチエンゲゼルシヤフト Conveyor for gruel-like material, particularly, concrete
DE3243576A1 (en) * 1982-11-25 1984-05-30 Karl Dipl.-Ing. 7000 Stuttgart Schlecht Two-cylinder piston pump, especially for thick matter

Also Published As

Publication number Publication date
AU576459B2 (en) 1988-08-25
ES547235A0 (en) 1986-06-16
EP0175929A2 (en) 1986-04-02
HU195868B (en) 1988-07-28
DE3524033A1 (en) 1986-04-03
US4681022A (en) 1987-07-21
ES8608635A1 (en) 1986-06-16
SU1496641A3 (en) 1989-07-23
JPS61182474A (en) 1986-08-15
HUT44318A (en) 1988-02-29
KR860002649A (en) 1986-04-28
BR8504676A (en) 1986-07-22
CA1246389A (en) 1988-12-13
EP0175929A3 (en) 1989-02-08
KR940009535B1 (en) 1994-10-14
MX162377A (en) 1991-05-03
AU4768685A (en) 1986-04-10

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