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EP0175929B1 - Zweizylinder-Dickstoffpumpe mit Rohrweiche - Google Patents

Zweizylinder-Dickstoffpumpe mit Rohrweiche Download PDF

Info

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
Authority
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
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0175929A3 (en
EP0175929A2 (de
Inventor
Friedrich Dipl.-Ing. Schwing
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.)
Friedrich Wilhelm Schwing GmbH
Original Assignee
Friedrich Wilhelm Schwing 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 Friedrich Wilhelm Schwing GmbH filed Critical Friedrich Wilhelm Schwing GmbH
Priority to AT85110538T priority Critical patent/ATE60112T1/de
Publication of EP0175929A2 publication Critical patent/EP0175929A2/de
Publication of EP0175929A3 publication Critical patent/EP0175929A3/de
Application granted granted Critical
Publication of EP0175929B1 publication Critical patent/EP0175929B1/de
Anticipated expiration legal-status Critical
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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Transmission Devices (AREA)
EP19850110538 1984-09-25 1985-08-22 Zweizylinder-Dickstoffpumpe mit Rohrweiche Expired - Lifetime EP0175929B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85110538T ATE60112T1 (de) 1984-09-25 1985-08-22 Zweizylinder-dickstoffpumpe mit rohrweiche.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3435052 1984-09-25
DE3435052 1984-09-25
DE3524033 1985-07-05
DE19853524033 DE3524033A1 (de) 1984-09-25 1985-07-05 Zweizylinder-dickstoffpumpe mit rohrweiche

Publications (3)

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

Family

ID=25825054

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850110538 Expired - Lifetime EP0175929B1 (de) 1984-09-25 1985-08-22 Zweizylinder-Dickstoffpumpe mit Rohrweiche

Country Status (12)

Country Link
US (1) US4681022A (es)
EP (1) EP0175929B1 (es)
JP (1) JPS61182474A (es)
KR (1) KR940009535B1 (es)
AU (1) AU576459B2 (es)
BR (1) BR8504676A (es)
CA (1) CA1246389A (es)
DE (1) DE3524033A1 (es)
ES (1) ES8608635A1 (es)
HU (1) HU195868B (es)
MX (1) MX162377A (es)
SU (1) SU1496641A3 (es)

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 (de) * 1993-08-13 1995-02-16 Putzmeister Maschf Anordnung zum Öffnen und Schließen einer Verschlußkappe
DE4344632A1 (de) * 1993-12-24 1995-06-29 Putzmeister Maschf Schiebervorrichtung für eine Zweizylinder-Dickstoffpumpe
WO2007111689A2 (en) * 2005-11-08 2007-10-04 Good Earth Tools, Inc. Sealing rings for abrasive slurry pumps
JP5453918B2 (ja) 2009-05-18 2014-03-26 トヨタ自動車株式会社 流量制御弁
KR101068025B1 (ko) * 2009-11-06 2011-09-28 주식회사 드림피아 유체펌프
KR101335345B1 (ko) * 2010-12-31 2013-12-03 신재희 압축기
WO2014059016A1 (en) 2012-10-10 2014-04-17 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 (de) * 1953-09-16 1956-08-09 Torkret Ges Mit Beschraenkter Hydraulisch angetriebene Kolbenpumpe zur Foerderung von dickfluessigen, breiigen Massen, z. B. Beton
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 (de) * 1969-02-21 1970-09-03 Schwing Dipl Ing Friedrich Wil Kolbenpumpe zum Foerdern von Beton
US4102613A (en) * 1977-01-06 1978-07-25 Vukich Martin T Concrete pumping machine
DE2841183C2 (de) * 1978-09-22 1982-07-15 Industrie-Werke Karlsruhe Augsburg AG Zweigniederlassung Keller & Knappich Augsburg, 8900 Augsburg Handhabungsgerät mit einem Auslegerarm
DE2903749C2 (de) * 1979-02-01 1983-11-10 Karl Dipl.-Ing. 7000 Stuttgart Schlecht Kolbenpumpe mit S-förmig gekrümmtem Schwenkrohr
DE2931814A1 (de) * 1979-08-06 1981-02-12 Schlecht Karl Rohrweichenpumpe
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 (ja) * 1982-06-25 1984-02-14 ウイバウ・アクチエンゲゼルシヤフト 粥状材料、特にコンクリ−トの搬送装置
DE3243576A1 (de) * 1982-11-25 1984-05-30 Karl Dipl.-Ing. 7000 Stuttgart Schlecht Zweizylinder-kolbenpumpe, insbesondere fuer dickstoffe

Also Published As

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

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