EP0561262A1 - Pompe pour matière épaisse ayant des cylindres, en particulier pompe à béton à deux cylindres - Google Patents

Pompe pour matière épaisse ayant des cylindres, en particulier pompe à béton à deux cylindres Download PDF

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Publication number
EP0561262A1
EP0561262A1 EP93103802A EP93103802A EP0561262A1 EP 0561262 A1 EP0561262 A1 EP 0561262A1 EP 93103802 A EP93103802 A EP 93103802A EP 93103802 A EP93103802 A EP 93103802A EP 0561262 A1 EP0561262 A1 EP 0561262A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
delivery
thick matter
cylinders
control slide
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.)
Granted
Application number
EP93103802A
Other languages
German (de)
English (en)
Other versions
EP0561262B1 (fr
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
Publication of EP0561262A1 publication Critical patent/EP0561262A1/fr
Application granted granted Critical
Publication of EP0561262B1 publication Critical patent/EP0561262B1/fr
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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • 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
    • F04B9/117—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 the pumping members not being mechanically connected to each other
    • F04B9/1176—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 the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • F04B9/1178—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 the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor the movement in the other direction being obtained by a hydraulic connection between the liquid motor cylinders
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04G—SCAFFOLDING; FORMS; SHUTTERING; BUILDING IMPLEMENTS OR AIDS, OR THEIR USE; HANDLING BUILDING MATERIALS ON THE SITE; REPAIRING, BREAKING-UP OR OTHER WORK ON EXISTING BUILDINGS
    • E04G21/00—Preparing, conveying, or working-up building materials or building elements in situ; Other devices or measures for constructional work
    • E04G21/02—Conveying or working-up concrete or similar masses able to be heaped or cast
    • E04G21/04—Devices for both conveying and distributing
    • E04G21/0418—Devices for both conveying and distributing with distribution hose
    • E04G21/0445—Devices for both conveying and distributing with distribution hose with booms
    • E04G21/0454—Devices for both conveying and distributing with distribution hose with booms with boom vibration damper mechanisms
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0075—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons connected in series
    • 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
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/90—Slurry pumps, e.g. concrete

Definitions

  • the invention relates to a thick matter pump with delivery cylinders, in particular a two-cylinder concrete pump according to the preamble of claim 1.
  • the basic mode of operation of known thick matter pumps, in particular those used for concrete delivery, in two-cylinder piston pumps is that the two delivery pistons in the delivery cylinders are usually driven by hydraulic cylinders in such a way that during the one delivery the other sucks in.
  • the piston play changes in the stroke end positions.
  • the movement of the pistons is synchronized, i. i.e. when the hydraulic cylinder driving the feed cylinder, e.g. B. on the piston side with hydraulic oil, the piston rod-side displaced oil is passed via a bridge line to the piston rod side of the suction feed cylinder, so that this travels its suction stroke at the same speed as the advancing cylinder because of the identical area ratios of the two drive cylinders.
  • both pistons reach their end positions in the feed cylinders at the same time.
  • a logic circuit which controls the concrete flow between the strokes after reaching the end of the stroke and the connection of the delivery cylinders with the delivery line or with the Inlet funnel reverses.
  • a compensating cylinder is provided for this purpose, which presses thick material into the delivery line during the switching over of a swivel tube designed as a uniform hollow body and one of the during the subsequent delivery stroke
  • Both feed cylinders are filled with thick matter from the feed line.
  • the logic circuit works with limit switches, which are actuated by the delivery cylinder pistons and initiate the suction or delivery stroke of the compensating cylinder.
  • Such a two-cylinder concrete pump does not achieve the goal of even concrete delivery through the delivery line. This is because the lack of compression of the concrete sucked in at such a pump at the beginning of each piston stroke leads to a standstill of the concrete flow.
  • the invention is based on a new way of looking at the previously known two-cylinder high-density pumps, which is illustrated by the example of a known pump II Art is explained below, which has neither a pre-compression nor a compensating cylinder.
  • pump stroke the time for the effective delivery stroke (pump stroke) is determined by the actually required concrete delivery quantity and by the volumetric efficiency ⁇ .
  • the factor f 1 is determined by which the running speed of the pistons for suction and compression in a pump (I) according to the prior art (B) must be greater than that Running speed of the pistons for pumping, namely as a quotient of Q * and Q o
  • a conveying stroke of the compensating cylinder directly adjoins the conveying stroke of a conveying cylinder, and the conveying pause that has previously occurred in this phase is thus avoided.
  • the delivery stroke of the other delivery cylinder is connected directly to the delivery stroke of the compensating cylinder, so that overall delivery pauses can no longer occur. This also ensures the invention in that the switching of the control slide including the various hydraulic valves and the compression stroke take place during the delivery stroke of the compensating cylinder.
  • the volume (V A ) of the compensating cylinder is determined by the first time and volume equivalence consideration, which relates to the pumping phase of the compensating cylinder.
  • the volume V A of the compensating cylinder is thus calculated
  • the second consideration of time and volume equivalence is intended to determine the running time or running speed of the piston of the delivery cylinder during the pumping stroke.
  • V P The volume (V P ) driven by the piston of a delivery cylinder during the effective pumping stroke
  • the compensation takes place Reduction of the effective delivery volume of the pumping delivery cylinder an acceleration of the effective running speed of the piston in this pumping delivery cylinder, which results in a pump delivery rate Q ***, which is increased and must be such that the delivery rate effectively delivered to the delivery line is equal to Q o is.
  • the representations of the figures are based on a two-cylinder concrete pump.
  • the two feed cylinders are labeled L and R.
  • the letter A denotes a compensating cylinder which opens into the delivery line 105.
  • the feed cylinder and the compensating cylinder are each driven by a hydraulic working cylinder, the letters each referring to the unit consisting of the feed cylinder and drive cylinder.
  • the end positions of the pistons in the cylinders are conveyed to the logic circuit by pulses from sensors which are designated by the letters a-f. These sensors control valves that are identified with Arabic numbers.
  • the control pulses of the sensors can be electrical, hydraulic, mechanical or pneumatic.
  • the concrete flow control provided in the invention is carried out with a swivel tube 100, which has a control plate 101 and 102 on opposite sides of its inlet opening and is therefore referred to as a control slide (104).
  • a hydraulic drive is used to impart motion is generally designated B. This is also controlled via a directional valve, which is shown at 3.
  • a filling funnel has on its side opposite the openings of the delivery cylinders L and R a pivot bearing 103 for the control slide 104 and the non-rotatable connection of the pump-side end of a concrete delivery line 105.
  • the logic circuit accelerates the drive piston of the conveying cylinder currently being conveyed, so that its conveying piston runs faster and thereby conveys more in this phase, which corresponds to the amount of the concrete quantity removed from the compensating cylinder A from the hopper 100. This is done by adding additional hydraulic medium (oil). If the area ratio of the compensating cylinder drive piston to the compensating cylinder feed piston is the same as that of the feed cylinders, the hydraulic drive medium which the rear of the compensating cylinder drive piston displaces through the outlet cylinder feed piston when the concrete is sucked in from the delivery line is sufficient.
  • the control slide 104 is switched between the piston clearances of the delivery cylinders R and L.
  • the switching takes place in two successive steps, the first of which holds the control slide in a central position between the openings of the two delivery cylinders.
  • one of the slide plates 101 and 102 closes the delivery cylinder opening of the delivery cylinder switched from suction to delivery. This enables the piston of this feed cylinder to compress the previously sucked concrete.
  • the logic circuit causes the second switching step of the control slide 104 into the respective end position. Thereby the inlet opening 106 of the control slide 104 is aligned with the opening of the conveying cylinder and the previously compacted concrete is pressed into the conveying line 105.
  • the middle switching position of the control slide 104 is controlled by the directional valve 7.
  • the control hole for the return oil is closed in the middle switch position, causing the control spool to come to a standstill in the middle switch position.
  • Valve 7 is switched on at intervals and moves to the other switching position. This will clear a return control bore at the end of the drive cylinder.
  • the control spool can be switched to the end position.
  • the middle switching position of the control slide is determined by the fact that two drive cylinders according to FIG. 5 are connected in series for driving the control slide.
  • the middle position is established.
  • the second cylinder 108 is actuated at intervals, by means of which the control slide 104 reaches its end position.
  • the first cylinder 107 is activated by the valve 3 and the second cylinder 108 by the valve 31.
  • the required limitation of the compression stroke is done with a cylinder 33 in which a piston 38 is arranged.
  • the stroke volume 40 corresponds to the selected compression stroke limitation.
  • a valve 51 controls the cylinder in such a way that in the phase of the compression stroke the valve 51 is switched by one of the sensors a, b.
  • pressure oil from a reservoir 60 acts on the side 36 of the piston 38 via the line 35.
  • the amount of oil displaced by the piston side 37 becomes via a line 34, 28 to the compressing feed cylinder until the piston 38 has reached its end position.
  • the switching back of the valve 51 by a sensor acts on the accumulator side 37 of the piston 38.
  • the oil displaced from the side 36 flows out to the tank.
  • the piston 38 can thus be returned in its starting position for the next compression.
  • the piston in the other delivery cylinder stands still, i. H. its suction stroke does not start yet.
  • the compression stroke limitation is carried out with a multi-chamber cylinder 41. This corresponds to the cylinder 33 according to FIG. 3 with regard to the stroke limitation in terms of dimension, function and control. However, it has a further chamber 42 which is dimensioned such that it does so during the compression stroke of the drive cylinder of the compressing delivery cylinder in the bridge line displaces hydraulic oil displaced via line 43 and feeds it back into the bridge in the course of the following delivery stroke and thus restores the synchronization of the running of the delivery cylinders.
  • a continuous concrete flow is achieved in that the same piston area ratios as well as the same hydraulic quantities for the delivery stroke are available for the different cylinders L, R and A.
  • the hydraulic pump P1 ensures the continuity of the concrete delivery. It is therefore advantageous to provide one or more separate other drive sources for all other drives of the valves or control slides, the suction stroke of the compensating cylinder A, etc.
  • a second hydraulic circuit which has a reservoir 60 fed by a pump P2, serves this purpose.
  • an auxiliary pump P3 is provided, which is switched so that in the phase in which the compensating cylinder conveys the concrete, the pump P3 is not switched off, but the hydraulic medium supplied by it via line 9 additionally to the accumulator 60 is supplied.
  • a correspondingly enlarged pump P2 can be provided in connection with a larger work volume.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • On-Site Construction Work That Accompanies The Preparation And Application Of Concrete (AREA)
EP93103802A 1992-03-19 1993-03-10 Pompe pour matière épaisse ayant des cylindres, en particulier pompe à béton à deux cylindres Expired - Lifetime EP0561262B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4208754A DE4208754A1 (de) 1992-03-19 1992-03-19 Dickstoffpumpe mit foerderzylindern, insbesondere zweizylinderbetonpumpe
DE4208754 1993-03-19

Publications (2)

Publication Number Publication Date
EP0561262A1 true EP0561262A1 (fr) 1993-09-22
EP0561262B1 EP0561262B1 (fr) 1996-08-14

Family

ID=6454411

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93103802A Expired - Lifetime EP0561262B1 (fr) 1992-03-19 1993-03-10 Pompe pour matière épaisse ayant des cylindres, en particulier pompe à béton à deux cylindres

Country Status (12)

Country Link
US (1) US5316453A (fr)
EP (1) EP0561262B1 (fr)
JP (1) JPH0642454A (fr)
KR (1) KR100298500B1 (fr)
CN (1) CN1042258C (fr)
AT (1) ATE141389T1 (fr)
BR (1) BR9301249A (fr)
CA (1) CA2092044A1 (fr)
DE (2) DE4208754A1 (fr)
ES (1) ES2090737T3 (fr)
GR (1) GR3021480T3 (fr)
RU (1) RU2127829C1 (fr)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
US7407022B2 (en) 2004-07-27 2008-08-05 Clarke Uk, Ltd. Apparatus for pumping drill cuttings and dual cylinder positive displacement pump for moving drill cuttings and method of use
EP3063407A4 (fr) * 2013-10-29 2017-08-09 Thermtech Holdings AS Système d'acheminement et de pompage de substance moins apte à être pompée dans une conduite
DE102021100981B3 (de) 2021-01-19 2022-04-28 Putzmeister Engineering Gmbh Dickstoffventil und Verfahren zum Betätigen eines Dickstoffventils

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DE4336087A1 (de) * 1993-10-22 1995-04-27 Korthaus Ernst Dickstoffspeicher
DE19542258A1 (de) * 1995-11-13 1997-05-15 Putzmeister Maschf Verfahren und Vorrichtung zur Steuerung einer Zweizylinder-Dickstoffpumpe
DE102004015181A1 (de) * 2004-03-25 2005-10-13 Putzmeister Ag Materialaufgabebehälter für eine Dickstoffpumpe
DE102004015419A1 (de) * 2004-03-26 2005-10-13 Putzmeister Ag Vorrichtung und Verfahren zur Steuerung einer Dickstoffpumpe
DE102004015415A1 (de) * 2004-03-26 2005-10-13 Putzmeister Ag Vorrichtung und Verfahren zur Steuerung einer Zweizylinder-Dickstoffpumpe
KR100606203B1 (ko) * 2004-04-19 2006-07-31 주식회사 디앤에스 펌프카의 콘크리트 압송변환시스템
DE102004025910B4 (de) * 2004-05-27 2009-05-20 Schwing Gmbh Antriebseinrichtung für eine Zweizylinderdickstoffpumpe und Verfahren zum Betrieb derselben
US20060193738A1 (en) * 2005-02-26 2006-08-31 Friedrich Schwing Pump apparatus and method for continuously conveying a viscous material
DE102005008938B4 (de) * 2005-02-26 2007-01-25 Schwing, Friedrich, Dipl.-Ing. Pumpvorrichtung und Verfahren zur kontinuierlichen Förderung breiiger Massen
DE102005024174A1 (de) * 2005-05-23 2006-12-07 Schwing, Friedrich, Dipl.-Ing. Verfahren zum Steuern einer Pumpvorrichtung zur Förderung breiiger Massen sowie Steuerung einer Pumpvorrichtung zur Förderung breiiger Massen
WO2007111689A2 (fr) * 2005-11-08 2007-10-04 Good Earth Tools, Inc. Bagues d'etancheite pour pompes a boue abrasive
US8727740B2 (en) * 2007-01-05 2014-05-20 Schlumberger Technology Corporation Cylinder assembly for providing uniform flow output
DE102009005318B3 (de) 2009-01-16 2010-09-30 Schwing, Friedrich, Dipl.-Ing. Verfahren zur Förderung breiiger Massen und Pumpvorrichtung zur Förderung breiiger Massen
DE102009008517B4 (de) * 2009-02-11 2018-01-04 Götz Hudelmaier Hydraulischer Antrieb einer Dickstoffpumpe mit Ladedruckeinrichtung
KR101113142B1 (ko) * 2010-04-20 2012-02-16 주식회사 데코엔지니어링 고점성 공압펌프 구동장치
DE102010046649A1 (de) 2010-09-27 2012-03-29 Schwing Gmbh Dickstoffpumpe und Verfahren zur kontinuierlichen Förderung von Dickstoff
CN102297312B (zh) * 2011-06-28 2013-01-09 北京市三一重机有限公司 降低流体脉动冲击的机构、双缸换向泵送系统及混凝土泵
DE102012107933B4 (de) * 2012-08-28 2017-09-21 Götz Hudelmaier Dickstoffpumpe zur Erzeugung eines kontinuierlichen Dickstoffstroms sowie Verfahren zum Betrieb einer Dickstoffpumpe zur Erzeugung eines kontinuierlichen Dickstoffstroms
DE102012216242A1 (de) * 2012-09-13 2014-03-13 Putzmeister Engineering Gmbh Vorrichtung zur Antriebssteuerung einer Zweizylinder-Dickstoffpumpe
CN102979693B (zh) * 2012-11-27 2015-08-19 长安大学 一种可实现混凝土连续恒流量泵送的装置及其控制方法
CN103590996B (zh) * 2013-11-22 2015-08-26 中联重科股份有限公司 泵送设备及泵送方法
IN2013MU03871A (fr) * 2013-12-12 2015-09-25 Arun Gokhale Amit
US9765768B2 (en) * 2014-01-15 2017-09-19 Francis Wayne Priddy Concrete pump system and method
CN103982411B (zh) * 2014-05-20 2016-08-24 徐州徐工施维英机械有限公司 锁缸方法和装置、及混凝土泵
CN104329315B (zh) * 2014-10-23 2017-04-12 徐州徐工施维英机械有限公司 输送设备、输送设备计量装置和方法
CN104763154A (zh) * 2014-11-25 2015-07-08 李树本 拖式混凝土泵车
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US10001114B1 (en) * 2017-03-28 2018-06-19 Jessop Initiatives LLC Continuous flow pumping system
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CN107355358A (zh) * 2017-08-04 2017-11-17 中铁工程装备集团隧道设备制造有限公司 无间隙连续泵送的活塞式泵送装置及其控制方法
CN109113763B (zh) * 2018-07-24 2019-09-24 山东科技大学 无脉冲湿喷机
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RU191862U1 (ru) * 2019-04-29 2019-08-26 АО Триада-Холдинг Установка для подачи высоковязких быстросхватывающихся ремонтных составов
CN110409833B (zh) * 2019-07-16 2021-04-02 江西鑫通机械制造有限公司 一种湿喷机的控制方法
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CN110701015B (zh) * 2019-10-09 2020-12-15 湖南慧盟重工科技有限公司 一种气动泵射小型混凝土输送泵
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EP0315750A1 (fr) * 1987-11-12 1989-05-17 Putzmeister-Werk Maschinenfabrik Gmbh Pompe pour matière épaisse

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US3663129A (en) * 1970-09-18 1972-05-16 Leon A Antosh Concrete pump
DE2052583A1 (de) * 1970-10-27 1972-05-04 Bors, Heinz J., Campione (Schweiz) Vorrichtung zum Fördern dickflüssiger Stoffe, insbesondere Beton, Mörtel und dgl
US3963385A (en) * 1975-05-05 1976-06-15 Caban Angel M Valve assembly for concrete pumps
EP0016410A1 (fr) * 1979-03-14 1980-10-01 Friedrich Wilh. Schwing GmbH Pompe pour matières visqueuses, notamment pompe à béton
DE3243738A1 (de) * 1982-11-26 1984-05-30 Karl Dipl.-Ing. 7000 Stuttgart Schlecht Hydro-umsteuerung bei zweizylinder-kolbenpumpe
EP0315750A1 (fr) * 1987-11-12 1989-05-17 Putzmeister-Werk Maschinenfabrik Gmbh Pompe pour matière épaisse

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7407022B2 (en) 2004-07-27 2008-08-05 Clarke Uk, Ltd. Apparatus for pumping drill cuttings and dual cylinder positive displacement pump for moving drill cuttings and method of use
EP3063407A4 (fr) * 2013-10-29 2017-08-09 Thermtech Holdings AS Système d'acheminement et de pompage de substance moins apte à être pompée dans une conduite
DE102021100981B3 (de) 2021-01-19 2022-04-28 Putzmeister Engineering Gmbh Dickstoffventil und Verfahren zum Betätigen eines Dickstoffventils
WO2022157013A1 (fr) * 2021-01-19 2022-07-28 Putzmeister Engineering Gmbh Soupape pour matière épaisse et procédé d'actionnement d'une soupape pour matière épaisse

Also Published As

Publication number Publication date
CN1088664A (zh) 1994-06-29
ES2090737T3 (es) 1996-10-16
GR3021480T3 (en) 1997-01-31
EP0561262B1 (fr) 1996-08-14
JPH0642454A (ja) 1994-02-15
CA2092044A1 (fr) 1993-09-20
DE4208754A1 (de) 1993-09-23
US5316453A (en) 1994-05-31
BR9301249A (pt) 1993-09-21
KR100298500B1 (ko) 2002-04-06
ATE141389T1 (de) 1996-08-15
DE59303394D1 (de) 1996-09-19
KR930020015A (ko) 1993-10-19
CN1042258C (zh) 1999-02-24
RU2127829C1 (ru) 1999-03-20

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