EP2895743A1 - Device for the drive control of a two-cylinder thick matter pump - Google Patents
Device for the drive control of a two-cylinder thick matter pumpInfo
- Publication number
- EP2895743A1 EP2895743A1 EP13732483.6A EP13732483A EP2895743A1 EP 2895743 A1 EP2895743 A1 EP 2895743A1 EP 13732483 A EP13732483 A EP 13732483A EP 2895743 A1 EP2895743 A1 EP 2895743A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- line
- drive
- cylinder
- delivery
- 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
Links
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
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0019—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers
- F04B7/0026—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers and having an oscillating movement
-
- 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
-
- 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
- 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
- F04B15/023—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 supply of fluid to the pump by gravity through a hopper, e.g. without intake valve
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/02—Pumping installations or systems having reservoirs
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
-
- 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
- F04B49/002—Hydraulic systems to change the pump delivery
-
- 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
- F04B49/22—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 by means of valves
-
- 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
- F04B49/22—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 by means of valves
- F04B49/225—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 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
-
- 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
- F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
Definitions
- the invention relates to a device for controlling the drive of a Zweizylin- the Dickstoffpumpe specified in the preamble of claim 1 genus.
- Two-cylinder thick matter pumps of this type have two delivery openings opening into a material feed container via end openings, the delivery pistons of which can be actuated alternately by means of hydraulically actuated drive cylinders while carrying out a filling stroke and a delivery stroke.
- a pipe switch is arranged, which is connected by means of a hydraulic drive mechanism on the inlet side alternately to the opening of one of the delivery cylinder and the opening of the respective other delivery cylinder releases, and the outlet side is connected to a delivery line for the conveyed thick materials.
- the sludge pump further has a motor-driven hydraulic variable displacement pump which has a suction inlet connected to a reservoir and a high-pressure outlet.
- the drive cylinders for the delivery pistons can be alternately connected to the high-pressure outlet of the variable-displacement pump via a pressure line, and to the reservoir via a return line via a respective hydraulic connection located at one end thereof by means of a first reversing valve. At the other end, the drive cylinders are connected to each other via a swing oil line.
- the hydraulic drive mechanism of the pipe switch on a two-sided controlled cylinder arrangement for example in the form of two series Plunger cylinders, their connections via a second reversing valve alternately leading to the high pressure output of the hydraulic variable delivery pressure line and leading to the reservoir return line can be connected.
- a central control is provided, which responds to end position signals of the passing drive piston at least one of the drive cylinder.
- the thick matter delivery and the diverter diverter take place alternately in a single-circuit system via the same variable-displacement pump, which can be adjusted continuously between a zero delivery and a predetermined maximum delivery.
- the adjustment in the thick matter delivery depends on a specified by the operator on a setting, adapted to the demand flow rate, while for the reversal of the pipe switch, regardless of the set in the machine flow rate a defined switching time is sought.
- the variable displacement pump has a flow regulator, the control input is acted upon in the delivery phase with a variable, adapted to the set flow control pressure, while it is acted upon in the Um Kunststoffphase with a defined Um Kunststoff Kunststoff.
- control input of the flow control valve in the delivery phase and in the reversal phase must be acted upon with different pressure control signals, including in the prior art designed as a directional valve switch-over valve (SOS valve) is used.
- SOS valve directional valve switch-over valve
- a disadvantage of this type of control is that two control signals which are generated independently of one another are used for the regulation of the variable-displacement pump, for the intended selection of which an electromagnetically actuated switch-over valve is required in the course of the conveying and reversing phase. This requires both hardware and control a considerable effort. Proceeding from this, the present invention seeks to improve the known device for controlling the drive of a sludge pump to the effect that a simplification of the hydraulic circuit arrangement can be achieved without loss of functionality.
- the solution according to the invention consists essentially in that in the pressure line between the high pressure output of the variable displacement pump and the first reversing valve a setting throttle is arranged, that is branched off from the pressure line downstream of the adjusting a directly leading to an adjustment mechanism of the variable displacement control line, and that of the pressure line upstream of the variable throttle is branched off to a supply connection of the second reversing valve connecting line, in which a fixed throttle can be arranged if necessary.
- a special feature of the invention is therefore that the adjusting mechanism containing a load-sensing controller of the variable displacement is controlled only via a control line, and that thus eliminates the known switch-over valve.
- the variable displacement pump additionally includes a pressure regulator for regulating the delivery rate when a predetermined maximum pressure at the high-pressure outlet is exceeded. This maximum pressure is always reached when the drive piston reach its end stop in the course of the delivery process and the pressure difference which can be tapped off at the setting throttle becomes zero. This is exactly the state in which the reversal of the pipe switch is initiated via the second reversing valve.
- the maximum pressure which adjusts itself to the high-pressure outlet of the variable-displacement pump is present at the fixed throttle, leading to a delivery flow leading via the defined flow cross-section of the connecting line to the plunger cylinder which is currently pressurized.
- This flow can so Preferably over the flow cross section of a fixed throttle in the connecting line and the maximum pressure can be preset that the Rohr Hughesum facedung takes place in a predetermined time, for example, 200 ms. It follows that the variable displacement pump is flow-regulated during the actual delivery process, whereas it is pressure-controlled over the predetermined maximum pressure during the changeover process, unlike previously.
- a further preferred embodiment of the invention provides that the load-sensing hydraulic has a arranged in the variable displacement, mechanically adjustable swash plate as an adjustment member and connected to the swash plate, the force side spring-assisted pressure compensator, to which the load side, the downstream of the setting throttle branched off control line is connected ,
- the drive cylinder have at least two responsive to the drive piston cylinder switch sensors, the output side connected to signal inputs of the central control are.
- the drive mechanism of the pipe switch also has at least one pipe path which responds to the position, the speed or the end positions of the pipe switch. on the output side is connected to a signal input of the central control.
- the reversing valves are designed as directional control valves with electromagnetic pilot control elements whose pilot control elements are each connected to a control output of the central control.
- FIG. 1 shows a detail of a two-cylinder slurry pump in partially cut perspective view
- Fig. 2 is a circuit diagram of a drive hydraulic for the two-cylinder slurry pump.
- the drive hydraulic system shown in the hydraulic circuit diagram of FIG. 2 is determined for a two-cylinder slurry pump according to FIG. 1.
- the sludge pump has two delivery cylinders 14, 14 'whose front-side openings 12, 12' open into a material supply container 10.
- the delivery pistons 16, 16 'of the slurry pump can be actuated alternately in push-pull manner by hydraulically controlled drive cylinders 18, 18' while carrying out a filling stroke (arrow 19 ') and a delivery stroke (arrow 19 "). which is connectable on the inlet side alternately to the opening 12 of one of the delivery cylinders 14 by means of a hydraulic drive mechanism 24, while it releases the opening 12 'of the respective other delivery cylinder 14.
- the transfer tube 22 is connected to a delivery line 26.
- a motor 27 driven hydraulic variable displacement pump 28 is provided, which has a suction port 32 connected to a non-pressurized reservoir 30 and a high pressure port 36 connected to a pressure line 34.
- the drive cylinders 18,18 ' are connected to each other at the other end via a swing oil pipe 44.
- the hydraulic drive mechanism 24 of the pipe switch 22 comprises two plunger cylinders 46 connected in series, which can be connected alternately via a second changeover valve 48 to the pressure line 34 leading to the high pressure outlet 36 of the hydraulic variable displacement pump 28 and to a return line 50 leading to the reservoir 30.
- a central control 56 which responds to end position signals of the passing drive pistons 20, 20 'of at least one of the drive cylinders 18, 18' is provided, via which sequence control for the first and the second reversing valves 40, 48 can be triggered.
- a setting throttle 58 is arranged in the pressure line 34 between the high-pressure outlet 36 of the variable displacement pump 28 and the first reversing valve 40 and is infinitely adjustable by the operator.
- a peculiarity of the invention is that of the pressure line 34 downstream (58 ') of the setting throttle 58 is fed back directly to an adjusting mechanism 60 of the variable displacement pump 28 leading control line 62, and that of the pressure line 34 upstream (58 ") of the setting 58 a branching to a supply connection 64 of the second reversing valve 48 connecting line 66 is branched off, in which, if necessary, a fixed throttle 68 is arranged.
- the adjustment mechanism 60 includes a load-sensing hydraulic 70 that provides hydraulic power control in which both the pressure and the flow rate of the adjustment pump 28 are adjusted to the conditions required by the consumer. As a controlled variable, the pressure drop at the setting throttle 58 is used.
- the load-sensing hydraulic system 70 has a mechanically adjustable swashplate 72 arranged as an adjusting element in the variable-displacement pump 28 and a pressure-compensated spring-based pressure compensator 73 connected to the swash plate 72, to which the downstream side of the adjusting throttle 58 branches off on the load side Control line 62 is connected.
- the variable displacement pump 28 is infinitely adjustable from zero flow rate to full delivery. In the zero position of the 4/3-way valves formed Um tenuventile 40,48 flows except for leakage oil losses no hydraulic oil through the lines. At the same time, the variable displacement pump 28 maintains a standby pressure.
- variable displacement pump 28 conveys only so much hydraulic fluid to maintain the currently required delivery pressure at the required delivery volume.
- the variable displacement pump 28 additionally comprises a pressure regulator, not shown, for regulating the flow rate when a predetermined maximum pressure is exceeded. This Abregelungsfunktion is used in the control of the drive mechanism 24 for the pipe switch 22.
- the drive cylinder 18,18 'two on the passing drive piston 20,20' responsive Zylinderschaltsensoren Have 52.54, the output side with signal inputs 52 ', 54' of the central control 56 are connected.
- the anti-knocking mechanism 24 of the pipe switch 22 has a pipe switch sensor 74, which responds to the position, the speed or the end positions of the pipe switch, and which is connected on the output side to a further signal input 74 'of the central control 56.
- the changeover valves 40, 48 are designed as directional control valves with electromagnetic pilot control elements 76, 78.
- the pilot control elements are each connected to a control output 76 ', 78' of the central control 56.
- the control signals for the changeover valves 40, 48 of the delivery piston drive and the tube transfer drive are calculated from the signals coming from the cylinder shift sensors 52, 54 and optionally from the tube deviation sensor 74.
- hydraulic oil flows from the variable displacement pump 28 via the pressure line 34, the setting throttle 58 and the reversing valve 40 into the drive cylinder 18, 18 'for the delivery piston 16, 16' for the delivery stroke 19.
- the oil quantity of the variable displacement pump 28 during the Feed phase via the load-sensing hydraulic 70 is set by adjusting a pressure drop across the setting throttle 58 via the control line 62.
- hydraulic oil flows via the connecting line 66 and the reversing valve 48 into the plunger cylinder 46 performing a pressure stroke Drive piston 20,20 'at their end stops, so that sets the maximum pressure at the high pressure outlet 36 of the variable displacement 28.
- the amount of oil passing through the connecting line 66 under the effect of the maximum pressure is such that the diverter 22 via the plunger cylinder 46 in a defined time in size 200 ms within the material feed container 10 is reversed. If necessary, a fixed throttle 68 can be arranged in the connecting line for this purpose.
- the invention relates to a device for controlling the drive of a two-cylinder slurry pump with a arranged in a material feed container 10 manifold 22 and a motor-driven hydraulic variable displacement pump 28, via which both the drive cylinder 18,18 'of the slurry pump and the drive mechanism 24 of the pipe switch are controlled.
- a special feature of the invention is that a setting throttle 58 is arranged in a pressure line 34 between the high-pressure outlet 36 of the variable displacement pump 28 and the drive cylinders 18, 18 'of the thick matter pump, that of the pressure line 34 downstream of the setting throttle 58 directly to an adjusting mechanism 60 of the variable displacement pump 28 leading control line 62 is fed back and that is branched off from the pressure line 34 upstream of the adjusting throttle 58 leading to a supply port 64 of the cross-over hydraulic connection line 66, in which a fixed throttle 68 may be arranged.
- This ensures that the oil flow in the delivery phase is flow-regulated, while it is pressure-controlled in the reversal phase.
- the variable displacement pump 28 additionally comprises a pressure regulator for regulating the flow rate when a predetermined maximum pressure is exceeded.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Reciprocating Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
Vorrichtung zur Antriebssteuerung einer Zweizylinder-Dickstoffpumpe Beschreibung Die Erfindung betrifft eine Vorrichtung zur Antriebssteuerung einer Zweizylin- der-Dickstoffpumpe der im Oberbegriff des Patentanspruchs 1 angegebenen Gattung. The invention relates to a device for controlling the drive of a Zweizylin- the Dickstoffpumpe specified in the preamble of claim 1 genus.
Zweizylinder-Dickstoffpumpen dieser Art weisen zwei über stirnseitige Öff- nungen in einen Materialaufgabebehälter mündende Förderzylinder auf, deren Förderkolben mittels hydraulisch angesteuerter Antriebszylinder im Gegentakt abwechselnd unter Ausführen eines Füllhubs und eines Förderhubs betätigbar sind. Innerhalb des Materialaufgabebehälters ist eine Rohrweiche angeordnet, die mittels eines hydraulischen Antriebsmechanismus eintritts- seitig abwechselnd an die Öffnung eines der Förderzylinder anschließbar ist und die Öffnung des jeweils anderen Förderzylinders freigibt, und die aus- trittsseitig mit einer Förderleitung für die zu fördernden Dickstoffe verbunden ist. Die Dickstoffpumpe weist ferner eine motorisch angetriebene hydraulische Verstellpumpe auf, die einen mit einem Vorratsbehälter verbundenen Saugeingang und einen Hochdruckausgang aufweist. Two-cylinder thick matter pumps of this type have two delivery openings opening into a material feed container via end openings, the delivery pistons of which can be actuated alternately by means of hydraulically actuated drive cylinders while carrying out a filling stroke and a delivery stroke. Within the material feed container, a pipe switch is arranged, which is connected by means of a hydraulic drive mechanism on the inlet side alternately to the opening of one of the delivery cylinder and the opening of the respective other delivery cylinder releases, and the outlet side is connected to a delivery line for the conveyed thick materials. The sludge pump further has a motor-driven hydraulic variable displacement pump which has a suction inlet connected to a reservoir and a high-pressure outlet.
Die Antriebszylinder für die Förderkolben sind über je einen an ihrem einen Ende befindlichen Hydraulikanschluss abwechselnd mittels eines ersten Um- steuerventils über eine Druckleitung mit dem Hochdruckausgang der Ver- stellpumpe und über eine Rücklaufleitung mit dem Vorratsbehälter verbindbar. An ihrem anderen Ende sind die Antriebszylinder über eine Schaukelölleitung miteinander verbunden. Andererseits weist der hydraulische Antriebsmechanismus der Rohrweiche eine zweiseitig angesteuerte Zylinderanordnung beispielsweise in Form von zwei in Reihe geschalteten Plunger- Zylindern auf, deren Anschlüsse über ein zweites Umsteuerventil abwechselnd an die zum Hochdruckausgang der hydraulischen Verstellpumpe führende Druckleitung und an die zum Vorratsbehälter führende Rücklaufleitung anschließbar sind. Zur Auslösung einer Folgesteuerung für das erste und das zweite Umsteuerventil ist eine Zentralsteuerung vorgesehen, die auf Endlagensignale der vorbeilaufenden Antriebskolben mindestens eines der Antriebszylinder anspricht. The drive cylinders for the delivery pistons can be alternately connected to the high-pressure outlet of the variable-displacement pump via a pressure line, and to the reservoir via a return line via a respective hydraulic connection located at one end thereof by means of a first reversing valve. At the other end, the drive cylinders are connected to each other via a swing oil line. On the other hand, the hydraulic drive mechanism of the pipe switch on a two-sided controlled cylinder arrangement, for example in the form of two series Plunger cylinders, their connections via a second reversing valve alternately leading to the high pressure output of the hydraulic variable delivery pressure line and leading to the reservoir return line can be connected. To trigger a sequence control for the first and the second reversing valve, a central control is provided, which responds to end position signals of the passing drive piston at least one of the drive cylinder.
Die Dickstoffförderung und die Rohrweichenumsteuerung erfolgt abwechselnd in einem Einkreissystem über dieselbe Verstellpumpe, die kontinuierlich zwischen einer Nullförderung und einer vorgegebenen Maximalförderung eingestellt werden kann. Die Einstellung bei der Dickstoffförderung richtet sich nach einer vom Bediener an einem Einstellorgan vorgegebenen, an den Bedarf angepassten Fördermenge, während für die Umsteuerung der Rohrweiche unabhängig von der in der Maschine eingestellten Fördermenge eine definierte Umschaltzeit angestrebt wird. Zur Einstellung des Förderstroms hat die Verstellpumpe einen Förderstromregler, dessen Steuereingang in der Förderphase mit einem variablen, an die eingestellte Fördermenge angepassten Steuerdruck beaufschlagt wird, während er in der Umsteuerphase mit einem definierten Umsteuerdruck beaufschlagt wird. Deshalb muss der Steuereingang des Förderstromreglers in der Förderphase und in der Umsteuerphase mit unterschiedlichen Drucksteuersignalen beaufschlagt wer- den, wozu im Stand der Technik ein als Wegeventil ausgebildetes Switch- Over-Ventil (SOS-Ventil) verwendet wird. Mit anderen Worten heißt dies, dass die Steuersignale für den Förderstromregler an verschiedenen Steuerleitungen anstehen, die in den jeweiligen Betriebsphasen durch ein Umsteuerventil auf den Steuereingang geschaltet werden. The thick matter delivery and the diverter diverter take place alternately in a single-circuit system via the same variable-displacement pump, which can be adjusted continuously between a zero delivery and a predetermined maximum delivery. The adjustment in the thick matter delivery depends on a specified by the operator on a setting, adapted to the demand flow rate, while for the reversal of the pipe switch, regardless of the set in the machine flow rate a defined switching time is sought. To adjust the flow, the variable displacement pump has a flow regulator, the control input is acted upon in the delivery phase with a variable, adapted to the set flow control pressure, while it is acted upon in the Umsteuerphase with a defined Umsteuerdruck. Therefore, the control input of the flow control valve in the delivery phase and in the reversal phase must be acted upon with different pressure control signals, including in the prior art designed as a directional valve switch-over valve (SOS valve) is used. In other words, this means that the control signals for the flow controller are pending on different control lines, which are switched to the control input in the respective operating phases by a reversing valve.
Ein Nachteil dieser Steuerungsart besteht darin, dass für die Regelung der Verstellpumpe zwei unabhängig voneinander erzeugte Steuersignale verwendet werden, für deren bestimmungsgemäße Auswahl im Zuge der Förder- und Umsteuerphase ein elektromagnetisch angesteuertes Switch-Over- Ventil erforderlich ist. Dies erfordert sowohl hardwaremäßig als auch steuerungsmäßig einen erheblichen Aufwand. Ausgehend hiervon liegt der Erfindung die Aufgabe zugrunde, die bekannte Vorrichtung zur Antriebssteuerung einer Dickstoffpumpe dahingehend zu verbessern, dass eine Vereinfachung der hydraulischen Schaltungsanordnung ohne Einbuße an Funktionstüchtigkeit erzielt werden kann. A disadvantage of this type of control is that two control signals which are generated independently of one another are used for the regulation of the variable-displacement pump, for the intended selection of which an electromagnetically actuated switch-over valve is required in the course of the conveying and reversing phase. This requires both hardware and control a considerable effort. Proceeding from this, the present invention seeks to improve the known device for controlling the drive of a sludge pump to the effect that a simplification of the hydraulic circuit arrangement can be achieved without loss of functionality.
Zur Lösung dieser Aufgabe wird die im Patentanspruch 1 angegebene Merkmalskombination vorgeschlagen. Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung ergeben sich aus den abhängigen Ansprüchen. Die erfindungsgemäße Lösung besteht im Wesentlichen darin, dass in der Druckleitung zwischen dem Hochdruckausgang der Verstellpumpe und dem ersten Umsteuerventil eine Einstelldrossel angeordnet ist, dass von der Druckleitung stromabwärts der Einstelldrossel eine unmittelbar zu einem Verstellmechanismus der Verstellpumpe führende Steuerleitung abgezweigt ist, und dass von der Druckleitung stromaufwärts der Verstelldrossel eine zu einem Versorgungsanschluss des zweiten Umsteuerventils führende Verbindungsleitung abgezweigt ist, in welcher bei Bedarf eine festeingestellte Drossel angeordnet sein kann. Eine Besonderheit der Erfindung besteht also darin, dass der einen Load-Sensing-Regler enthaltende Verstellmechanismus der Verstellpumpe nur über eine Steuerleitung angesteuert wird, und dass damit das bekannte Switch-Over-Ventil entfällt. Dies ist dadurch möglich, dass die Verstellpumpe zusätzlich einen Druckregler zur Abregelung der Fördermenge bei Überschreiten eines vorgegebenen Maximaldrucks am Hochdruckausgang umfasst. Dieser Maximaldruck wird stets dann erreicht, wenn die Antriebskolben im Zuge des Fördervorgangs zu ihrem Endanschlag gelangen und die an der Einstelldrossel abgreifbare Druckdifferenz zu Null wird. Dies ist genau der Zustand, in welchem die Umsteuerung der Rohrweiche über das zweite Umsteuerventil eingeleitet wird. In diesem Fall steht an der Festdrossel der sich am Hochdruckausgang der Verstellpumpe einstel- lende Maximaldruck an, der zu einem über den definierten Strömungsquerschnitt der Verbindungsleitung führenden Förderstrom zu dem im Augenblick mit Druck beaufschlagten Plungerzylinder führt. Dieser Förderstrom kann so vorzugsweise über den Ström ungsquerschnitt einer Festdrossel in der Verbindungsleitung und den Maximaldruck voreingestellt werden, dass die Rohrweichenumsteuerung in einer vorgegebenen Zeit von beispielsweise 200 ms erfolgt. Hieraus folgt, dass die Verstellpumpe während des eigentli- chen Fördervorgangs förderstromgeregelt ist, während sie beim Umsteuervorgang - anders als bisher - über den vorgegebenen Maximaldruck druckgeregelt ist. To solve this problem, the feature combination specified in claim 1 is proposed. Advantageous embodiments and modifications of the invention will become apparent from the dependent claims. The solution according to the invention consists essentially in that in the pressure line between the high pressure output of the variable displacement pump and the first reversing valve a setting throttle is arranged, that is branched off from the pressure line downstream of the adjusting a directly leading to an adjustment mechanism of the variable displacement control line, and that of the pressure line upstream of the variable throttle is branched off to a supply connection of the second reversing valve connecting line, in which a fixed throttle can be arranged if necessary. A special feature of the invention is therefore that the adjusting mechanism containing a load-sensing controller of the variable displacement is controlled only via a control line, and that thus eliminates the known switch-over valve. This is possible because the variable displacement pump additionally includes a pressure regulator for regulating the delivery rate when a predetermined maximum pressure at the high-pressure outlet is exceeded. This maximum pressure is always reached when the drive piston reach its end stop in the course of the delivery process and the pressure difference which can be tapped off at the setting throttle becomes zero. This is exactly the state in which the reversal of the pipe switch is initiated via the second reversing valve. In this case, the maximum pressure which adjusts itself to the high-pressure outlet of the variable-displacement pump is present at the fixed throttle, leading to a delivery flow leading via the defined flow cross-section of the connecting line to the plunger cylinder which is currently pressurized. This flow can so Preferably over the flow cross section of a fixed throttle in the connecting line and the maximum pressure can be preset that the Rohrweichenumsteuerung takes place in a predetermined time, for example, 200 ms. It follows that the variable displacement pump is flow-regulated during the actual delivery process, whereas it is pressure-controlled over the predetermined maximum pressure during the changeover process, unlike previously.
Eine weitere bevorzugte Ausgestaltung der Erfindung sieht vor, dass die Load-Sensing-Hydraulik eine in der Verstellpumpe angeordnete, mechanisch verstellbare Schrägscheibe als Versteilglied sowie eine mit der Schrägscheibe verbundene, kraftseitig federgestützte Druckwaage aufweist, an welche lastseitig die stromabwärts der Einstelldrossel abgezweigte Steuerleitung angeschlossen ist. A further preferred embodiment of the invention provides that the load-sensing hydraulic has a arranged in the variable displacement, mechanically adjustable swash plate as an adjustment member and connected to the swash plate, the force side spring-assisted pressure compensator, to which the load side, the downstream of the setting throttle branched off control line is connected ,
Um einen störungsfreien Wechsel zwischen der Förderphase und der Umsteuerphase des Pumpbetriebs der Zweizylinder-Dickstoffpumpe zu gewährleisten, wird gemäß einer bevorzugten Ausgestaltung der Erfindung vorgeschlagen, dass die Antriebszylinder mindestens zwei auf die vorbeilaufenden Antriebskolben ansprechende Zylinderschaltsensoren aufweisen, die aus- gangsseitig mit Signaleingängen der Zentralsteuerung verbunden sind. Mit dieser Maßnahme ist es möglich, den Umsteuervorgang bereits eine gewisse Zeit vor dem Anschlag des Antriebskolbens am Zylinderende auszulösen. Dies ist deshalb notwendig, weil der Umsteuervorgang über die Umsteuer- ventile nur mit einer zeitlichen Verzögerung möglich ist. Auf diese Weise lassen sich Anschläge der Antriebskolben an den Zylinderenden, die zu einem frühzeitigen Verschleiß führen könnten, vermeiden. Entsprechendes gilt auch für die Umsteuerung des ersten Umsteuerventils, die bereits ausgelöst werden sollte, bevor die Plungerzylinder bei der Umsteuerung der Rohrweiche ihre Endlage erreichen. Um dies zu ermöglichen, weist auch der Antriebsmechanismus der Rohrweiche mindestens einen auf die Position, die Geschwindigkeit oder die Endlagen der Rohrweiche ansprechenden Rohrwei- chensensor auf, der ausgangsseitig mit einem Signaleingang der Zentralsteuerung verbunden ist. Um all dies zu erreichen, sind gemäß einer weiteren vorteilhaften Ausgestaltung der Erfindung die Umsteuerventile als Wegeventile mit elektromagnetischen Vorsteuerorganen ausgebildet, deren Vor- Steuerorgane mit jeweils einem Steuerausgang der Zentralsteuerung verbunden sind. In order to ensure a trouble-free change between the delivery phase and the Umsteuerphase the pumping operation of the two-cylinder slurry pump, it is proposed according to a preferred embodiment of the invention that the drive cylinder have at least two responsive to the drive piston cylinder switch sensors, the output side connected to signal inputs of the central control are. With this measure, it is possible to trigger the Umsteuervorgang already some time before the stop of the drive piston at the cylinder end. This is necessary because the changeover process via the reversing valves is only possible with a time delay. In this way, stops of the drive piston at the cylinder ends, which could lead to premature wear, avoid. The same applies to the reversal of the first reversing valve, which should already be triggered before the plunger reach its end position in the reversal of the pipe switch. In order to make this possible, the drive mechanism of the pipe switch also has at least one pipe path which responds to the position, the speed or the end positions of the pipe switch. on the output side is connected to a signal input of the central control. In order to achieve all of this, according to a further advantageous embodiment of the invention, the reversing valves are designed as directional control valves with electromagnetic pilot control elements whose pilot control elements are each connected to a control output of the central control.
Im Folgenden wird die Erfindung anhand eines in der Zeichnung in schemati- scher Weise dargestellten Ausführungsbeispiels näher erläutert. Es zeigen In the following, the invention will be explained in more detail with reference to an embodiment shown schematically in the drawing. Show it
Fig. 1 einen Ausschnitt aus einer Zweizylinder-Dickstoffpumpe in teilweise geschnittener schaubildlicher Darstellung; 1 shows a detail of a two-cylinder slurry pump in partially cut perspective view;
Fig. 2 ein Schaltschema einer Antriebshydraulik für die Zweizylinder- Dickstoffpumpe. Fig. 2 is a circuit diagram of a drive hydraulic for the two-cylinder slurry pump.
Die in dem hydraulischen Schaltschema gemäß Fig. 2 dargestellte Antriebshydraulik ist für eine Zweizylinder-Dickstoffpumpe entsprechend Fig. 1 bestimmt. Die Dickstoffpumpe weist zwei Förderzylinder 14,14' auf, deren stirn- seitige Öffnungen 12,12' in einen Materialaufgabebehälter 10 münden. Die Förderkolben 16,16' der Dickstoffpumpe sind mittels hydraulisch angesteuerter Antriebszylinder 18,18' im Gegentakt abwechselnd unter Ausführen eines Füllhubs (Pfeil 19') und eines Förderhubs (Pfeil 19") betätigbar. Innerhalb des Materialaufgabebehälters 10 befindet sich außerdem eine Rohrweiche 22, die mittels eines hydraulischen Antriebsmechanismus 24 eintrittsseitig abwechselnd an die Öffnung 12 eines der Förderzylinder 14 anschließbar ist, während sie die Öffnung 12' des jeweils anderen Förderzylinders 14' freigibt. Austrittsseitig ist die Rohrweiche 22 mit einer Förderleitung 26 verbunden. Außerdem ist eine mittels eines Motors 27 angetriebene hydraulische Ver- stellpumpe 28 vorgesehen, die einen mit einem drucklosen Vorratsbehälter 30 verbundenen Saugeingang 32 und einen an eine Druckleitung 34 angeschlossenen Hochdruckausgang 36 aufweist. Die Antriebszylinder 18,18' sind über je einen an ihrem einen Ende befindlichen Hydraulikanschluss 38,38' abwechselnd mittels eines ersten, als 4/3- Wegeventil ausgebildeten Umsteuerventils 40 über die Druckleitung 34 mit dem Hochdruckausgang 36 der Verstellpumpe 28 und über eine Rücklaufleitung 42 mit dem Vorratsbehälter 30 verbindbar. Außerdem sind die Antriebszylinder 18,18' an ihrem anderen Ende über eine Schaukelölleitung 44 miteinander verbunden. Der hydraulische Antriebsmechanismus 24 der Rohrweiche 22 umfasst zwei in Reihe geschaltete Plungerzylinder 46, die über ein zweites Umsteuerventil 48 abwechselnd an die zum Hochdruckausgang 36 der hydraulischen Verstellpumpe 28 führende Druckleitung 34 und an eine zum Vorratsbehälter 30 führende Rücklaufleitung 50 anschließbar sind. Weiter ist eine auf Endlagen- Signale der vorbeilaufenden Antriebskolben 20,20' mindestens eines der Antriebszylinder 18,18' ansprechende Zentralsteuerung 56 vorgesehen, über die eine Folgesteuerung für das erste und das zweite Umsteuerventil 40,48 auslösbar ist. Für die Förderstromsteuerung der Dickstoffpumpe ist in der Druckleitung 34 zwischen dem Hochdruckausgang 36 der Verstellpumpe 28 und dem ersten Umsteuerventil 40 eine Einstelldrossel 58 angeordnet, die vom Bediener stufenlos verstellbar ist. Eine Besonderheit der Erfindung besteht darin, dass von der Druckleitung 34 stromabwärts (58') der Einstelldrossel 58 eine unmit- telbar zu einem Verstellmechanismus 60 der Verstellpumpe 28 führende Steuerleitung 62 zurückgekoppelt ist, und dass von der Druckleitung 34 stromaufwärts (58") der Einstelldrossel 58 eine zu einem Versorgungsan- schluss 64 des zweiten Umsteuerventils 48 führende Verbindungsleitung 66 abgezweigt ist, in welcher bei Bedarf eine fest eingestellte Drossel 68 ange- ordnet ist. Der Verstellmechanismus 60 umfasst eine Load-Sensing-Hydraulik 70, die eine hydraulische Leistungsregelung bewirkt, bei der sowohl der Druck als auch der Volumenstrom der Verstellpunnpe 28 an die vom Verbraucher geforderten Bedingungen angepasst werden. Als Regelgröße wird der Druckab- fall an der Einstelldrossel 58 verwendet. The drive hydraulic system shown in the hydraulic circuit diagram of FIG. 2 is determined for a two-cylinder slurry pump according to FIG. 1. The sludge pump has two delivery cylinders 14, 14 'whose front-side openings 12, 12' open into a material supply container 10. The delivery pistons 16, 16 'of the slurry pump can be actuated alternately in push-pull manner by hydraulically controlled drive cylinders 18, 18' while carrying out a filling stroke (arrow 19 ') and a delivery stroke (arrow 19 "). which is connectable on the inlet side alternately to the opening 12 of one of the delivery cylinders 14 by means of a hydraulic drive mechanism 24, while it releases the opening 12 'of the respective other delivery cylinder 14. On the outlet side, the transfer tube 22 is connected to a delivery line 26. In addition, one is by means of a motor 27 driven hydraulic variable displacement pump 28 is provided, which has a suction port 32 connected to a non-pressurized reservoir 30 and a high pressure port 36 connected to a pressure line 34. The drive cylinders 18, 18 'are alternately connected by means of a first reversing valve 40 formed as a 4/3-way valve via the pressure line 34 to the high-pressure outlet 36 of the variable-displacement pump 28 and via a return line 42 via a respective hydraulic connection 38, 38' connectable to the reservoir 30. In addition, the drive cylinders 18,18 'are connected to each other at the other end via a swing oil pipe 44. The hydraulic drive mechanism 24 of the pipe switch 22 comprises two plunger cylinders 46 connected in series, which can be connected alternately via a second changeover valve 48 to the pressure line 34 leading to the high pressure outlet 36 of the hydraulic variable displacement pump 28 and to a return line 50 leading to the reservoir 30. In addition, a central control 56 which responds to end position signals of the passing drive pistons 20, 20 'of at least one of the drive cylinders 18, 18' is provided, via which sequence control for the first and the second reversing valves 40, 48 can be triggered. For the delivery flow control of the slurry pump, a setting throttle 58 is arranged in the pressure line 34 between the high-pressure outlet 36 of the variable displacement pump 28 and the first reversing valve 40 and is infinitely adjustable by the operator. A peculiarity of the invention is that of the pressure line 34 downstream (58 ') of the setting throttle 58 is fed back directly to an adjusting mechanism 60 of the variable displacement pump 28 leading control line 62, and that of the pressure line 34 upstream (58 ") of the setting 58 a branching to a supply connection 64 of the second reversing valve 48 connecting line 66 is branched off, in which, if necessary, a fixed throttle 68 is arranged. The adjustment mechanism 60 includes a load-sensing hydraulic 70 that provides hydraulic power control in which both the pressure and the flow rate of the adjustment pump 28 are adjusted to the conditions required by the consumer. As a controlled variable, the pressure drop at the setting throttle 58 is used.
Bei dem gezeigten Ausführungsbeispiel weist die Load-Sensing-Hydraulik 70 eine in der Verstellpumpe 28 angeordnete, mechanisch verstellbare Schrägscheibe 72 als Versteilglied sowie eine mit der Schrägscheibe 72 verbunde- ne, kraftseitig federgestützte Druckwaage 73 auf, an welche lastseitig die stromabwärts der Einstelldrossel 58 abgezweigte Steuerleitung 62 angeschlossen ist. Die Verstellpumpe 28 ist stufenlos von Nullförderleistung bis Vollförderung verstellbar. In der Nullstellung der als 4/3-Wegeventile ausgebildeten Umsteuerventile 40,48 fließt ausgenommen von Leckölverlusten kein Hydraulikol durch die Leitungen. Gleichzeitig hält die Verstellpumpe 28 einen Standby-Druck aufrecht. Wird nun durch Öffnen eines der Umsteuerventile 40,48 Hydraulikflüssigkeit in die Antriebe im Bereich der Antriebszylinder 18,18' oder im Bereich der Plungerzylinder 46 geleitet, so wird die Förderleistung der Verstellpumpe 28 automatisch erhöht. Die Verstellpumpe 28 fördert jeweils nur so viel Hydraulikflüssigkeit, um bei dem benötigten Fördervolumen den aktuell benötigten Förderdruck aufrechtzuerhalten. Eine Besonderheit der Erfindung besteht darin, dass die Verstellpumpe 28 zusätzlich einen nicht dargestellten Druckregler zur Abregelung der Fördermenge bei Überschreiten eines vorgegebenen Maximaldrucks umfasst. Diese Abregelungsfunktion wird bei der Ansteuerung des Antriebsmechanismus 24 für die Rohrweiche 22 genutzt. In the exemplary embodiment shown, the load-sensing hydraulic system 70 has a mechanically adjustable swashplate 72 arranged as an adjusting element in the variable-displacement pump 28 and a pressure-compensated spring-based pressure compensator 73 connected to the swash plate 72, to which the downstream side of the adjusting throttle 58 branches off on the load side Control line 62 is connected. The variable displacement pump 28 is infinitely adjustable from zero flow rate to full delivery. In the zero position of the 4/3-way valves formed Umsteuerventile 40,48 flows except for leakage oil losses no hydraulic oil through the lines. At the same time, the variable displacement pump 28 maintains a standby pressure. If hydraulic fluid is now conducted into the drives in the area of the drive cylinders 18, 18 'or in the area of the plunger cylinders 46 by opening one of the changeover valves 40, 48, the delivery rate of the variable displacement pump 28 is automatically increased. The variable displacement pump 28 conveys only so much hydraulic fluid to maintain the currently required delivery pressure at the required delivery volume. A special feature of the invention is that the variable displacement pump 28 additionally comprises a pressure regulator, not shown, for regulating the flow rate when a predetermined maximum pressure is exceeded. This Abregelungsfunktion is used in the control of the drive mechanism 24 for the pipe switch 22.
Aus Fig. 2 ist zu ersehen, dass die Antriebszylinder 18,18' zwei auf die vorbeilaufenden Antriebskolben 20,20' ansprechende Zylinderschaltsensoren 52,54 aufweisen, die ausgangsseitig mit Signaleingängen 52', 54' der Zentralsteuerung 56 verbunden sind. Weiter weist der Antnebsmechanismus 24 der Rohrweiche 22 einen auf die Position, die Geschwindigkeit oder die Endlagen der Rohrweiche ansprechenden Rohrweichensensor 74 auf, der aus- gangsseitig mit einem weiteren Signaleingang 74' der Zentralsteuerung 56 verbunden ist. Die Umsteuerventile 40,48 sind als Wegeventile mit elektromagnetischen Vorsteuerorganen 76,78 ausgebildet. Die Vorsteuerorgane sind mit jeweils einem Steuerausgang 76', 78' der Zentralsteuerung 56 verbunden. Die Ansteuersignale für die Umsteuerventile 40,48 des Förderkol- benantriebs und des Rohrweichenantriebs werden aus den von den Zylinderschaltsensoren 52,54 und gegebenenfalls vom Rohrweichensensor 74 kommenden Signalen errechnet. From Fig. 2 it can be seen that the drive cylinder 18,18 'two on the passing drive piston 20,20' responsive Zylinderschaltsensoren Have 52.54, the output side with signal inputs 52 ', 54' of the central control 56 are connected. Furthermore, the anti-knocking mechanism 24 of the pipe switch 22 has a pipe switch sensor 74, which responds to the position, the speed or the end positions of the pipe switch, and which is connected on the output side to a further signal input 74 'of the central control 56. The changeover valves 40, 48 are designed as directional control valves with electromagnetic pilot control elements 76, 78. The pilot control elements are each connected to a control output 76 ', 78' of the central control 56. The control signals for the changeover valves 40, 48 of the delivery piston drive and the tube transfer drive are calculated from the signals coming from the cylinder shift sensors 52, 54 and optionally from the tube deviation sensor 74.
Während der Förderphase fließt Hydraulikol von der Verstellpumpe 28 über die Druckleitung 34, die Einstelldrossel 58 und das Umsteuerventil 40 in den Antriebszylinder 18,18' für den einen Förderhub 19" ausführenden Förderkolben 16,16'. Dementsprechend wird die Ölmenge der Verstellpumpe 28 während der Förderphase über die Load-Sensing-Hydraulik 70 durch Einstellung eines Druckabfalls an der Einstelldrossel 58 über die Steuerleitung 62 eingestellt. Während der Rohrweichenbewegung fließt Hydraulikol über die Verbindungsleitung 66 und das Umsteuerventil 48 in den einen Druckhub ausführenden Plungerzylinder 46. In dieser Phase befinden sich die Antriebskolben 20,20' an ihren Endanschlägen, so dass sich am Hochdruckausgang 36 der Verstellpumpe 28 der Maximaldruck einstellt. Die unter der Einwirkung des Maximaldrucks durch die Verbindungsleitung 66 gelangende Ölmenge ist so bemessen, dass die Rohrweiche 22 über die Plungerzylinder 46 in einer definierten Zeit in der Größenordnung von 200 ms innerhalb des Materialaufgabebehälters 10 umgesteuert wird. Bei Bedarf kann hierfür in der Verbindungsleitung eine Festdrossel 68 angeordnet werden. During the delivery phase, hydraulic oil flows from the variable displacement pump 28 via the pressure line 34, the setting throttle 58 and the reversing valve 40 into the drive cylinder 18, 18 'for the delivery piston 16, 16' for the delivery stroke 19. The oil quantity of the variable displacement pump 28 during the Feed phase via the load-sensing hydraulic 70 is set by adjusting a pressure drop across the setting throttle 58 via the control line 62. During the tube diverter movement, hydraulic oil flows via the connecting line 66 and the reversing valve 48 into the plunger cylinder 46 performing a pressure stroke Drive piston 20,20 'at their end stops, so that sets the maximum pressure at the high pressure outlet 36 of the variable displacement 28. The amount of oil passing through the connecting line 66 under the effect of the maximum pressure is such that the diverter 22 via the plunger cylinder 46 in a defined time in size 200 ms within the material feed container 10 is reversed. If necessary, a fixed throttle 68 can be arranged in the connecting line for this purpose.
Zusammenfassend ist folgendes festzuhalten: Die Erfindung bezieht sich auf eine Vorrichtung zur Antriebssteuerung einer Zweizylinder-Dickstoffpumpe mit einer in einem Materialaufgabebehälter 10 angeordneten Rohrweiche 22 und einer motorisch angetriebenen hydraulischen Verstellpumpe 28, über die sowohl die Antriebszylinder 18,18' der Dickstoffpumpe als auch der Antriebsmechanismus 24 der Rohrweiche angesteuert werden. Eine Besonder- heit der Erfindung besteht darin, dass in einer Druckleitung 34 zwischen dem Hochdruckausgang 36 der Verstellpumpe 28 und den Antriebszylindern 18,18' der Dickstoffpumpe eine Einstelldrossel 58 angeordnet ist, dass von der Druckleitung 34 stromabwärts der Einstelldrossel 58 eine unmittelbar zu einem Verstellmechanismus 60 der Verstellpumpe 28 führende Steuerleitung 62 zurückgekoppelt ist und dass von der Druckleitung 34 stromaufwärts der Einstelldrossel 58 eine zu einem Versorgungsanschluss 64 der Rohrweichenhydraulik führende Verbindungsleitung 66 abgezweigt ist, in welcher eine fest eingestellte Drossel 68 angeordnet sein kann. Damit wird erreicht, dass der Ölfluss in der Förderphase förderstromgeregelt ist, während er in der Umsteuerphase druckgeregelt ist. Letzteres ist vor allem dann der Fall, wenn die Verstellpumpe 28 zusätzlich einen Druckregler zur Abregelung der Fördermenge bei Überschreiten eines vorgegebenen Maximaldrucks um- fasst. In summary, the following should be noted: The invention relates to a device for controlling the drive of a two-cylinder slurry pump with a arranged in a material feed container 10 manifold 22 and a motor-driven hydraulic variable displacement pump 28, via which both the drive cylinder 18,18 'of the slurry pump and the drive mechanism 24 of the pipe switch are controlled. A special feature of the invention is that a setting throttle 58 is arranged in a pressure line 34 between the high-pressure outlet 36 of the variable displacement pump 28 and the drive cylinders 18, 18 'of the thick matter pump, that of the pressure line 34 downstream of the setting throttle 58 directly to an adjusting mechanism 60 of the variable displacement pump 28 leading control line 62 is fed back and that is branched off from the pressure line 34 upstream of the adjusting throttle 58 leading to a supply port 64 of the cross-over hydraulic connection line 66, in which a fixed throttle 68 may be arranged. This ensures that the oil flow in the delivery phase is flow-regulated, while it is pressure-controlled in the reversal phase. The latter is especially the case when the variable displacement pump 28 additionally comprises a pressure regulator for regulating the flow rate when a predetermined maximum pressure is exceeded.
Bezugszeichenliste LIST OF REFERENCE NUMBERS
10 Materialaufgabebehälter10 material supply containers
12,12' Öffnungen (Förderzylinder)12,12 'openings (delivery cylinder)
14,14' Förderzylinder 14,14 'delivery cylinder
16,16' Förderkolben 16.16 'delivery piston
18,18' Antriebszylinder 18.18 'drive cylinder
19' Füllhub 19 'filling stroke
19" Förderhub 19 "delivery stroke
20,20' Antriebskolben 20.20 'drive piston
22 Rohrweiche 22 pipe switch
24 Antriebsmechanismus 24 drive mechanism
26 Förderleitung 26 support line
27 Motor 27 engine
28 Verstellpumpe 28 variable displacement pump
30 Vorratsbehälter 30 storage tanks
32 Saugeingang 32 suction inlet
34 Druckleitung 34 pressure line
36 Hochdruckausgang 36 high pressure outlet
38,38' Hydraulikanschluss38.38 'hydraulic connection
40 erstes Umsteuerventil40 first reversing valve
42 Rücklaufleitung 42 return line
44 Schaukelölleitung 44 swing oil pipe
46 Plungerzylinder 46 plunger cylinders
48 zweites Umsteuerventil 48 second reversing valve
50 Rücklaufleitung 50 return line
52,54 Zylinderschaltsensoren 52.54 cylinder shift sensors
52',54' Endlagensignale 52 ', 54' end position signals
56 Zentralsteuerung 56 central control
58 Einstelldrossel 58 setting throttle
58' stromabwärts 58 'downstream
58" stromaufwärts Verstellmechanismus58 "upstream adjustment
Steuerleitungcontrol line
Versorgungsanschlusssupply terminal
Verbindungsleitungconnecting line
Drossel (fest eingestellt)Throttle (fixed)
Load-Sensing-HydraulikLoad-sensing hydraulics
Schrägscheibe swash plate
Druckwaage pressure compensator
Rohrweichensensor ' SignaleingangPipe softness sensor 'signal input
,78 Vorsteuerorgane ',78' Steuerausgänge '78 pilot control', 78 'control outputs
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012216242.9A DE102012216242A1 (en) | 2012-09-13 | 2012-09-13 | Device for drive control of a two-cylinder slurry pump |
PCT/EP2013/063530 WO2014040769A1 (en) | 2012-09-13 | 2013-06-27 | Device for the drive control of a two-cylinder thick matter pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2895743A1 true EP2895743A1 (en) | 2015-07-22 |
EP2895743B1 EP2895743B1 (en) | 2016-10-05 |
Family
ID=48703508
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13732483.6A Active EP2895743B1 (en) | 2012-09-13 | 2013-06-27 | Device for the drive control of a two-cylinder thick matter pump |
Country Status (8)
Country | Link |
---|---|
US (1) | US20150211503A1 (en) |
EP (1) | EP2895743B1 (en) |
JP (1) | JP6194360B2 (en) |
KR (1) | KR102020700B1 (en) |
CN (1) | CN104541054B (en) |
BR (1) | BR112015004524A2 (en) |
DE (1) | DE102012216242A1 (en) |
WO (1) | WO2014040769A1 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9760097B2 (en) * | 2015-06-03 | 2017-09-12 | Emerson Process Management Regulator Technologies, Inc. | Adjustable deadband control system |
EP3232057B1 (en) * | 2016-04-11 | 2018-06-13 | Epiroc Rock Drills Aktiebolag | Method for transmitting or conveying fluid or semi-fluid materials by means of a double piston pump and double piston pump therefor |
DE102016122392A1 (en) * | 2016-11-21 | 2018-05-24 | Schwing Gmbh | Slurry pump with adjustable limitation of the delivery pressure |
DE102018109866A1 (en) * | 2018-04-24 | 2019-10-24 | Nidec Gpm Gmbh | Controllable lubricating oil conveyor system for internal combustion engines |
DE102018208121A1 (en) * | 2018-05-23 | 2019-11-28 | Putzmeister Engineering Gmbh | System for detecting and solving a partial or complete thick matter clogging in a thick matter delivery line |
DE102018208125A1 (en) * | 2018-05-23 | 2019-11-28 | Putzmeister Engineering Gmbh | System for preventing thick matter clogging in a thick matter delivery line when pumping thick material in the thick matter delivery line |
WO2020068667A1 (en) * | 2018-09-28 | 2020-04-02 | Julio Vasquez | System for monitoring concrete pumping systems |
US11891987B2 (en) * | 2018-12-14 | 2024-02-06 | Schwing Gmbh | Piston pump and method for operating a piston pump |
DE102020200261A1 (en) * | 2020-01-10 | 2021-07-15 | Putzmeister Engineering Gmbh | Method for operating a thick matter pump and thick matter pump |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3667869A (en) * | 1970-03-04 | 1972-06-06 | Karl Schlecht | Dual cylinder-concrete pump |
US3663129A (en) * | 1970-09-18 | 1972-05-16 | Leon A Antosh | Concrete pump |
US4710106A (en) * | 1984-11-26 | 1987-12-01 | Nippondenso Co., Ltd. | Volume controlling device for variable volume pump |
JP2685171B2 (en) * | 1984-11-26 | 1997-12-03 | 株式会社デンソー | Displacement control device for variable displacement pump |
DE3525003A1 (en) * | 1985-07-01 | 1987-01-08 | Gerhard Dr Hudelmaier | Method and device for conveying concrete from a container into a delivery pipe |
DE3910120A1 (en) * | 1989-03-29 | 1990-10-04 | Putzmeister Maschf | CONTROL ARRANGEMENT FOR A TWO-CYLINDER FUEL PUMP |
DE4127277A1 (en) * | 1991-08-17 | 1993-02-18 | Putzmeister Maschf | HYDRAULIC CONTROL DEVICE FOR A FUEL PUMP |
DE4208754A1 (en) * | 1992-03-19 | 1993-09-23 | Schwing Gmbh F | DICKER PUMP WITH CONVEYOR CYLINDER, IN PARTICULAR TWO-CYLINDER CONCRETE PUMP |
DE19538649C2 (en) * | 1995-10-17 | 2000-05-25 | Brueninghaus Hydromatik Gmbh | Power control with load sensing |
DE19542258A1 (en) * | 1995-11-13 | 1997-05-15 | Putzmeister Maschf | Method and device for controlling a two-cylinder thick matter pump |
DE10036202A1 (en) * | 2000-07-24 | 2002-02-07 | Putzmeister Ag | Slurry pump |
DE102004015415A1 (en) * | 2004-03-26 | 2005-10-13 | Putzmeister Ag | Device and method for controlling a two-cylinder slurry pump |
DE102004015419A1 (en) | 2004-03-26 | 2005-10-13 | Putzmeister Ag | Apparatus and method for controlling a slurry pump |
DE102005035981A1 (en) * | 2005-07-28 | 2007-02-01 | Putzmeister Ag | Hydraulic circuit arrangement, in particular for the drive of concrete distributor masts |
-
2012
- 2012-09-13 DE DE102012216242.9A patent/DE102012216242A1/en not_active Withdrawn
-
2013
- 2013-06-27 BR BR112015004524A patent/BR112015004524A2/en not_active IP Right Cessation
- 2013-06-27 EP EP13732483.6A patent/EP2895743B1/en active Active
- 2013-06-27 WO PCT/EP2013/063530 patent/WO2014040769A1/en active Application Filing
- 2013-06-27 US US14/419,492 patent/US20150211503A1/en not_active Abandoned
- 2013-06-27 CN CN201380042703.4A patent/CN104541054B/en active Active
- 2013-06-27 KR KR1020157006026A patent/KR102020700B1/en active Active
- 2013-06-27 JP JP2015531495A patent/JP6194360B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2014040769A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2014040769A1 (en) | 2014-03-20 |
DE102012216242A1 (en) | 2014-03-13 |
CN104541054B (en) | 2016-11-09 |
EP2895743B1 (en) | 2016-10-05 |
KR102020700B1 (en) | 2019-09-10 |
JP2015528541A (en) | 2015-09-28 |
KR20150054805A (en) | 2015-05-20 |
CN104541054A (en) | 2015-04-22 |
JP6194360B2 (en) | 2017-09-06 |
BR112015004524A2 (en) | 2017-07-04 |
US20150211503A1 (en) | 2015-07-30 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2895743B1 (en) | Device for the drive control of a two-cylinder thick matter pump | |
EP1851445B1 (en) | Hydraulic drive, especially for two-cylinder thick matter pumps | |
EP2855945B1 (en) | Hydraulic system | |
EP1907706B1 (en) | Hydraulic circuit arrangement, in particular for the drive of concrete distributor masts | |
EP0861375B1 (en) | Process and device for controlling a two-cylinder thick medium pump | |
WO2013045167A2 (en) | Hydraulic system with suction/return filter | |
EP1727981B1 (en) | Device and method for controlling a thick matter pump | |
CH634129A5 (en) | DIAPHRAGM PUMP. | |
EP0465474B1 (en) | Control arrangement for a two-cylinder pump for thick materials | |
DE2444844A1 (en) | AMPLIFIER OR PRESSURE INCREASE PUMP WITH A HALF-WAVE MODULATOR | |
EP0446206B1 (en) | Process and device for control of a twin-cylinder thick matter pump | |
EP0402390B1 (en) | Control arrangement for two-cylinder pumps for viscous liquids | |
AT8986U1 (en) | HYDRAULIC PRESSURE SUPPLY UNIT, AND ELECTRO-HYDRAULIC WORKING UNIT AND CLAMPING SYSTEM WITH SUCH A PRESSURE SUPPLY UNIT | |
EP0598736B1 (en) | Hydraulic control device for a viscous fluid pump | |
EP2682610B1 (en) | Regulator system of a hydraulic variable capacity pump | |
DE3844405C2 (en) | Valve arrangement for a hydraulic system | |
EP2600011A2 (en) | Hydraulic directional valve for the lifting gear of an agricultural vehicle | |
WO2012038050A1 (en) | Hydraulic machine with electronically controlled valves | |
EP1332288B1 (en) | Method for controlling a pump arrangement consisting of two hydraulically driven plunger piston pumps | |
DE3346820A1 (en) | Hydrostatic drive for a concrete piston pump | |
DE10025188B4 (en) | Booster station | |
DE3233438C2 (en) | ||
DE3640640A1 (en) | Hydrostatic drive system with a consumer with two connections | |
DE102012025229A1 (en) | Hydro-mechanical controller e.g. pressure regulator for adjustable hydraulic engine, has adjustment chambers that are connected through directional valve to control valve through directional valve pressure medium connections | |
DE10060357A1 (en) | Drive unit for conveyor system, has first hydraulic piston-cylinder connected in series with pneumatic piston-cylinder, pressure-dependent valve in each equalization line opposed to valve in other line |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20141211 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
DAX | Request for extension of the european patent (deleted) | ||
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20160518 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 834915 Country of ref document: AT Kind code of ref document: T Effective date: 20161015 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502013004874 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20161005 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170106 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170105 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170205 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170206 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502013004874 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170105 |
|
26N | No opposition filed |
Effective date: 20170706 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170627 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20180228 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170627 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170630 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170630 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170627 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170627 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170630 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20170630 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170630 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20130627 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 834915 Country of ref document: AT Kind code of ref document: T Effective date: 20180627 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180627 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161005 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: TR Payment date: 20240614 Year of fee payment: 12 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20240620 Year of fee payment: 12 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20250618 Year of fee payment: 13 |