EP0567826A2 - Feststoffpumpe - Google Patents

Feststoffpumpe Download PDF

Info

Publication number
EP0567826A2
EP0567826A2 EP93105906A EP93105906A EP0567826A2 EP 0567826 A2 EP0567826 A2 EP 0567826A2 EP 93105906 A EP93105906 A EP 93105906A EP 93105906 A EP93105906 A EP 93105906A EP 0567826 A2 EP0567826 A2 EP 0567826A2
Authority
EP
European Patent Office
Prior art keywords
delivery
cylinder
stroke
feed
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP93105906A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0567826A3 (enrdf_load_stackoverflow
Inventor
Peter Dipl.-Ing. Zöllner
Winfried Dipl.-Ing. Bussmann
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.)
Abel GmbH and Co KG
Original Assignee
Abel & Co Handels- and Verwaltungsgesellschaft 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 Abel & Co Handels- and Verwaltungsgesellschaft GmbH filed Critical Abel & Co Handels- and Verwaltungsgesellschaft GmbH
Publication of EP0567826A2 publication Critical patent/EP0567826A2/de
Publication of EP0567826A3 publication Critical patent/EP0567826A3/xx
Withdrawn legal-status Critical Current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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04B9/1172—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 pump piston in the two directions being obtained by a double-acting piston liquid motor
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/02—Piston parameters
    • F04B2201/0201—Position of the piston
    • 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
    • F04B2203/00—Motor parameters
    • F04B2203/09—Motor parameters of linear hydraulic motors
    • F04B2203/0902—Liquid pressure in a working chamber
    • 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
    • F04B2203/00—Motor parameters
    • F04B2203/09—Motor parameters of linear hydraulic motors
    • F04B2203/0903—Position of the driving piston
    • 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
    • F04B2203/00—Motor parameters
    • F04B2203/12—Motor parameters of rotating hydraulic motors
    • F04B2203/1202—Pressure at the motor inlet

Definitions

  • the invention relates to a solids pump according to the preamble of claim 1.
  • Solid pumps for conveying and dosing pasty materials for example sludges and the like, are known in various embodiments. It is also known to use self-priming, positive displacement piston pumps for this purpose.
  • the delivery piston of at least one delivery cylinder is connected to the drive piston of a hydraulic drive cylinder, the end positions of which are determined by end position transmitters or by corresponding directional control valves in order to generate control signals for a valve arrangement which connects the output of the delivery cylinder to a supply or discharge line optionally in time with the delivery cylinder .
  • a supply unit is normally connected to the supply line, for example a screw pump, which conveys the medium in the direction of the delivery cylinder.
  • a disadvantage of the known method is that the start of the flow of the medium is determined via a valve which opens prematurely at a low or zero counterpressure in the discharge line and therefore does not permit precise measured values.
  • the solid-state pump on the one hand and the feed unit on the other hand operate independently of one another. It is known to coordinate the delivery quantities with one another by visual inspection.
  • the adjustment on the feed element is carried out, for example, by mechanical throttle valve setting on site or by remote setting using a potentiometer and proportional valve. In this way, however, the maximum effectiveness of the pump is usually not achieved.
  • the invention has for its object to provide a solids pump with which a simple measurement of the delivery rate can be made, in particular to control the effectiveness of the pump.
  • a pressure meter is assigned to the hydraulic drive cylinder, which generates a pressure signal if, after leaving the drive piston, a first sudden pressure increase occurs from its end position. It is based on the knowledge that the pressure increase can be recorded at the moment when a cylinder of medium to be delivered has built up in the delivery cylinder. The volume displaced by the delivery piston from this point in time therefore corresponds to the actual delivery volume during the delivery stroke.
  • a computer determines the actual delivery volume per delivery stroke from the ratio of the stroke times and the maximum available delivery volume in order to determine the delivery rate from this.
  • the equipment measures required to carry out the method according to the invention are extremely small.
  • the end positions of the drive piston in the drive cylinder are also determined in a suitable manner in conventional solid fuel pumps of the type mentioned. It is therefore only necessary to assign a pressure measuring device to the drive cylinder, for example a pressure switch, in order to determine the pressure increase.
  • a pressure measuring device for example a pressure switch
  • Several pressure peaks can very well occur during the delivery stroke. Only the first pressure peak can be used to measure the delivery volume or the degree of filling.
  • Two time measuring devices determine the stroke times of the piston between the end positions and between the one end position at the beginning of the delivery stroke and the occurrence of the pressure peak. Despite the simple precautions, a relatively precise measurement of the delivery rate can be made.
  • the invention also makes it easy to adapt the delivery rate of the feed unit to the solids pump.
  • the stroke time between the one English and the occurrence of the pressure peak is a measure of the degree of filling. The longer this time, the lower the filling. Therefore, an embodiment of the invention provides that the drive unit and / or the feed unit are adjustable for the purpose of changing the feed quantity to the feed cylinder and a comparison device is provided which compares the delivery stroke time to the pressure increase in the drive cylinder with a predetermined time and a signal for increasing the feed amount on the drive unit and / or the feed unit if the measured stroke time specifies the ne time exceeds.
  • a fill level of 100% would undoubtedly be ideal. However, this point is relatively difficult to achieve in practice. It is therefore accepted that a minimal dead stroke time occurs during the conveying stroke in order to obtain a stable control.
  • a further embodiment of the invention provides that a controllable hydraulic or electric drive unit is provided and a measuring device measures the pressure or the current consumption and generates a signal for reducing the delivery rate when the pressure and / or the current exceeds a predetermined value.
  • Electric or hydraulic drive units in which a change in the drive torque can be determined by measuring pressure or delivery quantity or by measuring current are known.
  • An increase in torque is an indicator that the feed unit is conveying more medium than the feed cylinder is processing.
  • the delivery rate of the medium can be measured in a simple manner and the feed unit can be adapted to a desired delivery rate.
  • the apparatus precautions required for this are very simple and require little effort.
  • the single figure shows a two-cylinder piston pump with a feed unit in an extremely schematic manner.
  • Two delivery cylinders 10, 12 have delivery pistons 14, 16 which are connected via a piston rod to a piston 18 or 20 of hydraulic drive cylinders 22, 24.
  • the outputs of the delivery cylinders 10, 12 are connected to valve chambers 16 and 28, in which suction valves 30 and 32 are arranged, in order to connect the delivery cylinders 10, 12 optionally to a feed line 34 for the medium to be delivered, in which a screw pump 36 is arranged which in turn is driven by a hydraulic motor 38.
  • the valve chambers 26, 28 are in turn connected to valve chambers 40, 42, in which a pressure valve 44 or 46 is arranged.
  • the individual valves are actuated by hydraulic cylinders 48, 50, 52, 54.
  • the valve chambers 40, 42 are connected to a common delivery line 56.
  • the hydraulic cylinders 22, 24 are assigned end position transmitters S7, S8 and S9, S10, which generate a signal when the piston 18 or 20 reaches an end position.
  • the end position sensors are used to control the valves 30, 32, 44, 46.
  • the cylinders 10, 12 are actuated by the hydraulic cylinders 22, 24 such that when cylinder 10 performs a suction stroke, cylinder 22 simultaneously executes a pressure stroke and vice versa. This is achieved by connecting the two rod sides of the hydraulic cylinders 22, 24.
  • suction valve 30 is open and pressure valve 44 is closed.
  • the hydraulic piston 18 travels from the position sensor S7 to the end position sensor S8.
  • cylinder 12 executes a pressure stroke, suction valve 32 being closed and pressure valve 46 being open.
  • the piston 20 moves from the end position sensor S10 to the end position sensor S9.
  • the valves 30, 32, 44, 46 are switched immediately, while the supply of the hydraulic medium to the hydraulic cylinders 22, 24 is delayed by means of suitable directional valves (not shown).
  • the delivery cylinder 12 then starts a suction stroke and at the same time the delivery cylinder 10 starts a pressure stroke.
  • the delivery rates of the delivery cylinders 10, 12 and the feed unit 36 should be matched to one another if possible, ie the same throughput rates should be available.
  • the time t measured in the computer 62 is a measure of the free travel of the piston 14 or 16. The longer this time, the lower the degree of filling. In order to optimize the degree of filling, the time t ; and thus the free travel of the piston 14 or 16 should be as small as possible.
  • the delivery rate of the feed unit 36 is determined by the speed of the hydraulic motor 38, which is driven by a hydraulic pump, not shown. The speed of the motor 38 depends on the setting of a control valve 64 in the supply line for the motor 38.
  • a control device 66 which can be part of the computer 62, also receives a signal from the pressure switch 60 and compares the idle stroke time t j , which has already been mentioned several times. which either comes from the computer 62 or is determined by a separate time measuring device with a preset time. If the measured time t l exceeds the preset value, this means that more material has to be fed from the feed unit 36.
  • a control of the control valve 64 ensures that the speed of the motor 38 is increased in order to increase the supply quantity. The increase is continued until the measured times t are again less than the preset time.
  • a pressure measuring device 68 is provided, which also gives a signal to the controller 66, which compares the pressure with a preset pressure, so that the pressure is reduced Hydraulic amount to the motor 38 takes place, whereby the supply amount of medium is reduced.
  • other indicators can also be used which indicate when the feed quantity from the feed unit 36 is too high. In this case, the torque to be overcome by the motor 38 inevitably increases, which can be determined using suitable measurement methods. If the motor 38 is replaced by an electric motor, the current increase can be used for the control, for example.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Reciprocating Pumps (AREA)
EP93105906A 1992-04-29 1993-04-10 Feststoffpumpe Withdrawn EP0567826A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4214109 1992-04-29
DE19924214109 DE4214109C2 (de) 1992-04-29 1992-04-29 Feststoffpumpe

Publications (2)

Publication Number Publication Date
EP0567826A2 true EP0567826A2 (de) 1993-11-03
EP0567826A3 EP0567826A3 (enrdf_load_stackoverflow) 1994-03-23

Family

ID=6457741

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93105906A Withdrawn EP0567826A2 (de) 1992-04-29 1993-04-10 Feststoffpumpe

Country Status (3)

Country Link
EP (1) EP0567826A2 (enrdf_load_stackoverflow)
JP (1) JPH074351A (enrdf_load_stackoverflow)
DE (1) DE4214109C2 (enrdf_load_stackoverflow)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0621523A3 (de) * 1993-04-21 1995-01-25 Gsf Forschungszentrum Umwelt Verfahren zur Erzeugung von hochpräzischen Volumenströmen bei geringer Flussrate und Vorrichtung zur Durchführung des Verfahrens.
US5690478A (en) * 1994-12-30 1997-11-25 Abel Gmbh & Co. Solid material pump
WO2005093251A1 (de) * 2004-03-26 2005-10-06 Putzmeister Aktiengesellschaft Vorrichtung und verfahren zur steuerung einer dickstoffpumpe
WO2005093252A1 (de) * 2004-03-26 2005-10-06 Putzmeister Aktiengesellschaft Vorrichtung und verfahren zur steuerung einer zweizylinder-dickstoffpumpe
CN105727781A (zh) * 2016-02-14 2016-07-06 山东科技大学 高压恒流量试验用注浆泵

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9421046U1 (de) * 1994-12-30 1995-03-09 ABEL GmbH & Co Handels- und Verwaltungsgesellschaft, 21514 Büchen Feststoffpumpe
JP4854123B2 (ja) * 2001-03-19 2012-01-18 Ｉｈｉ建機株式会社 コンクリートポンプ車のコンクリート吐出量表示装置
DE102020207970A1 (de) * 2020-06-26 2021-12-30 Putzmeister Engineering Gmbh Verfahren zum Betreiben einer Bau- und/oder Dickstoffpumpe zum Fördern von Bau- und/oder Dickstoff und Bau- und/oder Dickstoffpumpe zum Fördern von Bau- und/oder Dickstoff

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2852651A1 (de) * 1978-12-06 1980-06-12 Kustner Sa Vorrichtung zum fortlaufenden nacheinander austeilen gleicher portionen einer teigigen oder halbteigigen masse aus einem vorrat, aus welchen sie mit konstantem ausschank mittels einer mit konstanter drehbewegung in drehung gesetzten foerderschraube vorgeschoben wird
US5106272A (en) * 1990-10-10 1992-04-21 Schwing America, Inc. Sludge flow measuring system
SE8305997L (sv) * 1983-11-01 1985-05-02 Rovac Ab Doseringsanordning
DE3546189A1 (de) * 1985-12-27 1987-07-02 Ott Kg Lewa Verfahren und vorrichtung zur durchflussmessung bei oszillierenden verdraengerpumpen
DE4206576B4 (de) * 1992-03-02 2005-08-04 Putzmeister Ag Verfahren und Anordnung zur Bestimmung der Fördermenge oder des Förderstroms von mittels einer Kolbendickstoffpumpe transportiertem Fördergut
ES2090741T3 (es) * 1992-03-21 1996-10-16 Schwing Gmbh F Bomba para materiales consistentes.

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0621523A3 (de) * 1993-04-21 1995-01-25 Gsf Forschungszentrum Umwelt Verfahren zur Erzeugung von hochpräzischen Volumenströmen bei geringer Flussrate und Vorrichtung zur Durchführung des Verfahrens.
US5690478A (en) * 1994-12-30 1997-11-25 Abel Gmbh & Co. Solid material pump
WO2005093251A1 (de) * 2004-03-26 2005-10-06 Putzmeister Aktiengesellschaft Vorrichtung und verfahren zur steuerung einer dickstoffpumpe
WO2005093252A1 (de) * 2004-03-26 2005-10-06 Putzmeister Aktiengesellschaft Vorrichtung und verfahren zur steuerung einer zweizylinder-dickstoffpumpe
EA007369B1 (ru) * 2004-03-26 2006-10-27 Путцмайстер Акциенгезелльшафт Устройство и способ для управления двухцилиндровым насосом для густой массы
EA007861B1 (ru) * 2004-03-26 2007-02-27 Путцмайстер Акциенгезелльшафт Устройство и способ управления насосом для густой среды
EP1906012A1 (de) * 2004-03-26 2008-04-02 Putzmeister Concrete Pumps GmbH Vorrichtung und Verfahren zur Steuerung einer Zweizylinder-Dickstoffpumpe
US7581935B2 (en) 2004-03-26 2009-09-01 Putzmeister Concrete Pumps Gmbh Device and method for controlling a thick matter pump
US7611331B2 (en) 2004-03-26 2009-11-03 Putzmeister Concrete Pumps Gmbh Device and method for controlling a two cylinder thick matter pump
CN100595436C (zh) * 2004-03-26 2010-03-24 普茨迈斯特混凝土泵有限公司 用于控制双缸泥浆泵的装置和方法
KR101148579B1 (ko) * 2004-03-26 2012-05-25 푸츠마이스터 엔지니어링 게엠베하 농후 물질 펌프를 제어하는 장치 및 방법
CN105727781A (zh) * 2016-02-14 2016-07-06 山东科技大学 高压恒流量试验用注浆泵

Also Published As

Publication number Publication date
DE4214109A1 (de) 1993-11-04
EP0567826A3 (enrdf_load_stackoverflow) 1994-03-23
JPH074351A (ja) 1995-01-10
DE4214109C2 (de) 1994-07-28

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