EP3542060B1 - Viscous material pump with adjustable limitation of the delivery pressure - Google Patents

Viscous material pump with adjustable limitation of the delivery pressure Download PDF

Info

Publication number
EP3542060B1
EP3542060B1 EP17816475.2A EP17816475A EP3542060B1 EP 3542060 B1 EP3542060 B1 EP 3542060B1 EP 17816475 A EP17816475 A EP 17816475A EP 3542060 B1 EP3542060 B1 EP 3542060B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
pilot valve
valve
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17816475.2A
Other languages
German (de)
French (fr)
Other versions
EP3542060A1 (en
Inventor
Andreas Lehmann
Anke WIEDERMANN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Friedrich Wilhelm Schwing GmbH
Original Assignee
Friedrich Wilhelm Schwing GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Friedrich Wilhelm Schwing GmbH filed Critical Friedrich Wilhelm Schwing GmbH
Publication of EP3542060A1 publication Critical patent/EP3542060A1/en
Application granted granted Critical
Publication of EP3542060B1 publication Critical patent/EP3542060B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/34—Control not provided for in groups F04B1/02, F04B1/03, F04B1/06 or F04B1/26
    • 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
    • F04B49/002—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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate

Definitions

  • the invention relates to a thick matter pump comprising a hydraulically driven two-cylinder piston pump for generating a thick matter delivery pressure, and a hydraulic pump which acts on the two-cylinder piston pump with hydraulic fluid via a drive line, the thick matter delivery pressure being adjustable.
  • Such a thick matter pump is off, for example DE 195 03 986 A1 known.
  • Such thick matter pumps are used, for example, to convey concrete from a feed hopper into a delivery line.
  • the thick matter delivery pressure in the delivery line can be well over 200 bar with stationary thick matter pumps.
  • the delivery lines used must be designed for such a thick matter delivery pressure.
  • the DE 37 09 504 A1 relates to a valve device for controlling the pressure medium paths between a pressure medium source, a consumer and a tank, with a directional control valve, a pressure compensator arranged upstream of the directional control valve, which can be actuated by the difference between the pressure upstream of the directional control valve and the load pressure, and with one to the Load pressure line connected pressure relief valve to limit the load pressure acting on the pressure compensator in order to limit the pressure upstream of the directional control valve to a predetermined value, the trigger pressure of the pressure relief valve being remotely adjustable.
  • the DE 100 40 737 A1 discloses a valve arrangement for supplying a hydraulic consumer with pressure medium, which can be sucked in from a tank by a variable displacement pump, with a preload valve whose baffle, which is pretensioned against a valve seat via a preloading spring, opens the connection to the consumer when a minimum pressure required to adjust the variable displacement pump is reached, and with a pressure relief valve for limiting the maximum consumer pressure, the pressure relief valve being assigned a pilot valve arrangement for changing the maximum consumer pressure which can be set via the pressure relief valve.
  • a concrete placing boom is often connected to the upper end of the delivery lines in order to distribute the concrete conveyed up the building to the top level of the construction site.
  • Such a concrete placing boom usually comprises an articulated boom with which the concrete is distributed.
  • the articulated mast usually has delivery pipes that are limited to a load from a thick matter delivery pressure of around 85 bar.
  • a critical thick matter delivery pressure can set, which causes the delivery line or the weaker delivery pipes of the placing boom to burst.
  • a simple and safe adjustable limitation of the thick matter delivery pressure is required.
  • the sludge delivery pressure of the sludge pump must be adapted to the situation on the construction site so that there are no critical feed pipes or lines connected to the sludge pump Can build up thick material delivery pressure, which can burst the pipes or lines.
  • the thick matter pumps used today have a preset pressure control of the hydraulic drive of the two-cylinder piston pump, which is usually set at the factory before the first start-up and is difficult to access.
  • the ratio of the thick matter delivery pressure to the hydraulic pressure in a two-cylinder piston pump can in principle simply be derived from the ratio of the piston areas of the hydraulic cylinder and the thick matter delivery cylinder to one another. If the hydraulic pressure rises above a fixed setpoint, the pressure control automatically reduces the delivery rate of the hydraulic pump in order to limit the hydraulic pressure and thus also the thick matter delivery pressure. This type of pressure control is also known as pressure cut-off.
  • an adjustable pressure limiting valve is also provided in the prior art, which limits the pressure of the hydraulic fluid in the drive line to a maximum value. If, however, the set maximum pressure is set lower than the setpoint pressure of the pressure control, this has the effect that the preset pressure control is deactivated so that the delivery rate of the hydraulic pump is no longer automatically reduced. This creates unnecessary losses and the hydraulic fluid is heated.
  • the object of the invention to provide an improved thick matter pump.
  • the target pressure should be Pressure regulation and the maximum pressure of the hydraulic fluid can be easily and safely adapted to the individual conditions on the respective construction site.
  • the invention based on a thick matter pump of the type mentioned in that the at least one hydraulic pump for limiting the thick matter delivery pressure has a pressure control that can be adjusted to a target pressure of the hydraulic fluid and limits the pressure of the hydraulic fluid in the drive line to an adjustable maximum pressure via an adjustable pressure relief valve is, the setpoint pressure of the pressure control and the maximum pressure of the hydraulic fluid being adjustable by a common adjusting element.
  • the advantages achieved by the invention result from the fact that the setpoint pressure of the pressure control and the maximum pressure of the hydraulic fluid can be adjusted easily and without error by a common adjusting element.
  • the pressure control which can be easily adjusted in this way, simplifies the limitation of the thick matter delivery pressure by means of the adjustable hydraulic pump.
  • the pressure of the hydraulic fluid in the drive line is automatically limited to a maximum value that matches the setpoint value of the pressure control via an adjustable pressure limiting valve.
  • the actuating element is designed to set the target pressure of the pressure control and the maximum pressure of the hydraulic fluid concurrently in such a way that the maximum pressure is always a predetermined differential pressure above the target pressure. In this way it is ensured that the settings via the common adjusting element do not lead to any change in the safety precautions and efficiency of the thick matter pump.
  • the actuating element has a first pilot valve which is adjustable to the setpoint pressure of the hydraulic fluid, which is connected on the inlet side to an adjusting slide for the pressure control of the hydraulic pump and on the outlet side is relieved into a hydraulic reservoir, the first pilot valve opening when the setpoint pressure is reached.
  • the actuating element has a second pilot valve, which is connected on the inlet side to a main stage of the pressure relief valve and on the outlet side to the inlet side of the first pilot valve, the second pilot valve opening from the specified differential pressure between the inlet and outlet side.
  • This second pilot valve thus ensures that the maximum pressure in the drive line specified by the pressure relief valve is automatically always the differential pressure above the setpoint pressure of the pressure cut-off, i.e. the maximum pressure is automatically set correctly to a suitable maximum pressure when the target pressure is set. This reliably prevents undesired interactions between the pressure regulation of the hydraulic pump and the pressure relief through the pressure limiting valve.
  • the predetermined differential pressure between the inlet and outlet side of the second pilot valve is optimally about 20 bar, since this ensures sufficient operational reliability of the thick matter pump.
  • the configuration that the second pilot valve cannot be adjusted is also advantageous. This ensures that the setting options via the adjusting element do not lead to restricted operational reliability of the thick matter pump due to manual settings on the second pilot valve.
  • An advantageous embodiment of the invention provides that the first pilot valve can be adjusted using a handwheel.
  • the ability to adjust the first pilot valve using a handwheel makes it particularly easy and safe to adapt the thick matter pump to the conditions on the respective construction site for the individual application.
  • the handwheel can be locked and / or locked.
  • the ability to lock the handwheel prevents unwanted changes to the settings on the first pilot valve and thus on the adjusting element.
  • the possibility of locking the handwheel also ensures that changes to the position of the handwheel can only be made by authorized personnel.
  • a further advantageous embodiment of the invention is that the adjusting element has a non-adjustable third pilot valve which is connected in parallel to the first pilot valve and which opens when a maximum permissible pressure is reached.
  • a third pilot valve connected in parallel to the first pilot valve, which opens at a maximum permissible pressure and relieves pressure control in a hydraulic reservoir, provides additional protection in the event of malfunctions or too high a setting of the adjustable first pilot valve.
  • a preferred embodiment provides that the first pilot valve is preceded by a switchover valve in such a way that the third pilot valve is connected in parallel to the arrangement of the first pilot valve and switchover valve, the switchover valve connecting the input side of the first pilot valve to the setting slide of the pressure control optionally manufactures or separates.
  • a switchover valve enables the setpoint pressure of the pressure control to be easily adjusted between the setpoint pressure set at the first pilot control valve and the maximum permissible pressure of the pressure control system, which is specified by the third pilot control valve.
  • the limitation of the thick matter delivery pressure at the thick matter pump can be adapted very quickly to the maximum permissible pressure without having to change the first adjustable pilot valve.
  • An advantageous embodiment of the invention provides that the switching valve is latching and / or lockable.
  • a latching option for the switchover valve prevents unintentional changes in position on the switchover valve and thus on the actuating element.
  • the ability to lock the changeover valve also ensures that changes to the position of the changeover valve are only made by authorized personnel.
  • FIG. 1 shows schematically and in sections a thick matter pump 1 with a hydraulically driven two-cylinder piston pump 2 for generating a thick matter delivery pressure according to the prior art.
  • the two hydraulic cylinders are indicated schematically and are connected to a drive line 8 via connecting lines and a switchover control 12, here for example an electrohydraulically piloted 4/3-way valve, via which the two-cylinder piston pump 2 is connected to a hydraulic pump 3, for example an axial piston variable displacement pump , is acted upon with hydraulic fluid.
  • a switchover control 12 takes place alternating loading of the two hydraulic cylinders of the two-cylinder piston pump.
  • delivery pistons (not shown) are arranged, which are pushed back and forth in delivery cylinders by the hydraulic cylinders and thus generate the thick matter delivery pressure.
  • the hydraulic lines shown in solid lines in the figures are so-called working lines that are designed for high hydraulic fluid flows, while the hydraulic lines shown with broken lines represent control or measuring lines that are designed for smaller hydraulic fluid flows.
  • a manometer 19, on which the instantaneous pressure of the hydraulic fluid can be read, is coupled to the drive line 8, between the switchover control 12 and the hydraulic pump 3.
  • the thick matter delivery pressure can be derived from the ratio of the effective piston areas of the hydraulic cylinder and the thick matter delivery cylinder to one another.
  • the setting of the maximum setpoint of the pressure regulation of the hydraulic pump is set manually by means of an adjusting slide 4 arranged on the hydraulic pump 3. As soon as the pressure of the hydraulic fluid in the drive line 8 reaches this setpoint value, the pumping power of the hydraulic pump 3 is automatically reduced, so that when this limit value is reached, no losses occur in the hydraulic system.
  • This setpoint is usually permanently preset at the factory when the hydraulic pump is started up and should usually not be changed.
  • a pressure limitation unit 5a is also connected to the working line 8 for safety.
  • This pressure limiting unit 5 a comprises the main stage of the pressure limiting valve 15, with a downstream pilot valve 18.
  • the hydraulic pressure of the drive line 8 is passed through the passage channel 17, which is equipped with a nozzle, through the main stage 15 through a further damping nozzle 20 to the pilot valve 18.
  • the pilot valve 18 and thus also the main stage 15 of the pressure limiting unit 5a opens so that the drive line 8 is connected directly to the hydraulic reservoir 14 and thus the pressure built up by the hydraulic pump 3 is reduced.
  • the limit pressure of the pressure limiting unit 15 is also always somewhat higher, for example 20 bar, than the setpoint to be set on the hydraulic pump 3.
  • FIG. 2 shows schematically and partially a thick matter pump 1 with a hydraulically driven two-cylinder piston pump 2 for generating a thick matter delivery pressure according to the invention.
  • the functionality largely corresponds to that in Figure 1 pump 1 shown, which is why only the setting according to the invention of the thick matter delivery pressure will be discussed below.
  • a so-called open hydraulic system is used in which the hydraulic pump 3 always pumps the hydraulic fluid in the same direction and sucks the hydraulic fluid from a hydraulic reservoir (tank) 14.
  • the invention can also be applied, for example, to known closed hydraulic systems in which the pumping direction of the hydraulic cylinders of the two-cylinder piston pump 2 is switched over by reversing the pumping direction of the hydraulic pump 3 via a switchover control.
  • the thick matter delivery pressure generated by the thick matter pump 1 can be set adjustable.
  • the thick matter pump 1 has an adjusting element 6, via which the setpoint pressure of a pressure control and the maximum pressure of the hydraulic fluid in the drive line 8 can be set together.
  • the hydraulic pump 3 for cutting off the thick matter delivery pressure can be controlled via the pressure control by setting a setpoint pressure for the hydraulic fluid in the pressure control.
  • the adjusting element 6 is connected to the control slide 4 of the pressure regulator on the hydraulic pump 3 via the connection X.
  • the pressure of the hydraulic fluid generated by the hydraulic pump 3 in the drive line 8 is limited to a maximum pressure that can be set by the pressure limiting valve 5.
  • the actuating element 6 is connected to the main stage 15 of the pressure limiting valve 5 via the connection X1.
  • the adjusting element 6 is designed in such a way that the setpoint pressure of the pressure control and the maximum pressure of the hydraulic fluid in the drive line 8 can be adjusted simultaneously. In this way, the maximum pressure of the hydraulic fluid in the drive line 8 is always a predetermined differential pressure above the setpoint pressure of the pressure control.
  • the actuating element 6 has a first pilot valve 9 which is adjustable to the setpoint pressure of the hydraulic fluid and which is connected on the input side to the control slide 4 of the pressure control of the hydraulic pump 3 and is relieved into a hydraulic reservoir 14 on the output side.
  • the first pilot valve 9 opens automatically when the set target pressure is reached in the pressure control and in this way very simply ensures that the set target pressure is maintained.
  • the setpoint pressure in the pressure control can be set between 0 and 315 bar via the first pilot control valve 9.
  • a second pilot valve 7 of the adjusting element 6 is connected on the input side to the main stage 15 of the pressure limiting valve 5 and on the output side to the input side of the first pilot valve 9.
  • This second pilot valve 7 has the property of the back pressure from the outlet side directly to the Adjustment spring add up the set value and opens from a predetermined differential pressure between the inlet and outlet side and thus ensures that the pressure in the drive line 8 via the pressure relief valve 5 is limited to match the setpoint value.
  • the specified differential pressure in the exemplary embodiment is 20 bar.
  • the second pilot valve 7, shown here adjustable is preferably permanently preset at the factory, ie the predetermined pressure difference at which the pilot valve 7 switches cannot be changed.
  • the second pilot valve 7 acts on the main stage 15 of the pressure relief valve 5 for protection in such a way that the pressure relief valve 5 relieves the pressure in the drive line 8 as soon as the pressure of the hydraulic fluid in the drive line 8 exceeds a value that is above the preset pressure difference at the first pilot valve 9 setpoint of the pressure control of the hydraulic pump 3 is.
  • the actuating element 6 also has an optional, non-adjustable third pilot valve 10 connected in parallel to the first pilot valve 9, which relieves pressure in the hydraulic reservoir 14 when a maximum permissible pressure is reached.
  • the maximum permissible pressure that can be achieved here is specified as 320 bar in the exemplary embodiment. This maximum permissible system pressure is preset at the factory.
  • This third pilot valve 10 ensures that, in the event of errors in the first pilot valve 9, there is no overloading of the entire system of the thick matter pump. In this way, the first pilot valve 9 and the third pilot valve 10 act directly on the control slide 4 for the pressure separation of the hydraulic pump regulator. As a result of the parallel connection with the first pilot control valve 9, the protection provided by the third pilot control valve 10 is permanently guaranteed.
  • the nozzles 20 serve the purpose of limiting the flow volume of the hydraulic fluid while the hydraulic pressure is being passed through, so that the pilot valves 7, 9, 10 and the setting slide 4 are only addressed in a damped manner.
  • the Figure 3 shows schematically and partially a thick matter pump 1 according to Figure 1 , with the adjusting element 6 having an additional switching valve 11 having.
  • the switching valve 11 is connected upstream of the first pilot valve 9 in such a way that the third pilot valve 10 is connected in parallel to the arrangement of the first pilot valve 9 and the switching valve 11, the switching valve 11 connecting the input side of the first pilot valve 9 to the setting slide 4 of the Pressure control optionally establishes or separates.
  • the switching valve 11 enables the setpoint pressure of the pressure control to be easily adjusted between the setpoint pressure set on the first pilot control valve 9 and the maximum permissible system pressure on the third pilot control valve 10. In this way, the limitation of the thick matter feed pressure can be adjusted very quickly without changing the settings on the first adjustable pilot control valve 9 are necessary.
  • the switching valve 11 is preferably designed as a ball valve.
  • the adjusting element 6 can thus also be reset again easily to the lower, set pressure via the switching valve 11.
  • Figure 4 is a constructive implementation of the adjusting element 6 according to Figure 2 shown schematically from the outside.
  • the adjusting element 6 is designed as a special block and at a point of the thick matter pump 1 that is easily accessible by the user ( Fig. 1 or 2 ) positionable.
  • the first pilot valve 9 can be adjusted via a hand wheel 13.
  • the handwheel 13 is lockable and lockable. In this way, the setting value on the first pilot control valve 9 can be saved.
  • the switching valve 11 shown can also be handled easily and is designed to be latching and lockable.
  • the adjusting element 6 also has measuring connections 16 with which information on the pressure conditions in the adjusting element 6 can be tapped.
  • the machine operator can set the desired value of the pressure limitation of the hydraulic pump 3 at the pilot valve 9 in conjunction with the pressure gauge 19.
  • the two-cylinder piston pump 2 is blocked, for example by setting the switchover control 12 to the central (blocking) position and the hydraulic pump 3 to full power.
  • the pressure set at the pilot control valve 9 is then displayed on the manometer 19 because the output of the hydraulic pump 3, as described above, is automatically limited to this pressure.
  • a system pressure of 20 bar above the set target value is, still to the fact that the drive line 8 is relieved via the pressure relief valve 5.
  • the operator can easily set the hydraulic pressure so that the maximum thick matter delivery pressure cannot be exceeded.
  • the actuating element 6 shown here as a structural unit can, for example, also be integrated into a hydraulic control block for the thick matter pump, as long as the pilot valve 9 can be easily adjusted and / or accessed.
  • the pilot valve 9, but also the switching valve 11, could for example also be electrically adjustable by remote control.
  • a spatially separate arrangement of the valves of the actuating element 6 is conceivable.
  • FIG Figure 5 A variant of the invention in which the pilot valve 9 is electrically adjustable by remote control is shown in FIG Figure 5 shown.
  • the pilot valve 9 is designed here as an electrically controlled proportional pressure limiting valve and is controlled by control electronics 23.
  • the control electronics 23 measure the hydraulic drive pressure of the two-cylinder piston pump 2 by means of the pressure sensor 21 and derive the thick matter delivery pressure therefrom via the ratio of the effective piston areas of the hydraulic cylinders and the thick matter delivery cylinders to one another.
  • the operator here only specifies the desired maximum delivery pressure of the two-cylinder piston pump 2.
  • the control electronics 23 determine the correct setting of the pilot valve 9 from the hydraulic pressure measured by the pressure sensor 21 and the maximum thick matter delivery pressure specified by the operator, as already described above, when the two-cylinder piston pump 2 is blocked and adjusts it accordingly via the control line.
  • the control electronics 23 can, for example, also set the pilot valve 9 without blocking the two-cylinder piston pump 2. With the aid of the pressure sensor 21, the setting can be checked and, if necessary, readjusted.
  • the switching valve 11 shown can, if necessary, simply override the preset remote-controlled reduction of the limit pressure of the pressure cut-off. That is, by actuating the switchover valve 11, the maximum system pressure for the pressure cut-off set via the third pilot valve 10 is set again, which in the example shown here is 20 bar below the limit pressure of the limit pressure defined by the pilot valve 7 and the pressure limiting valve 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Die Erfindung betrifft eine Dickstoffpumpe umfassend eine hydraulisch angetriebene Zwei-Zylinder-Kolbenpumpe zur Erzeugung eines Dickstoffförderdrucks, und eine Hydraulikpumpe, welche die Zwei-Zylinder-Kolbenpumpe über eine Antriebsleitung mit Hydraulikfluid beaufschlagt, wobei der Dickstoffförderdruck einstellbar begrenzt ist.The invention relates to a thick matter pump comprising a hydraulically driven two-cylinder piston pump for generating a thick matter delivery pressure, and a hydraulic pump which acts on the two-cylinder piston pump with hydraulic fluid via a drive line, the thick matter delivery pressure being adjustable.

Eine solche Dickstoffpumpe ist beispielsweise aus DE 195 03 986 A1 bekannt.Such a thick matter pump is off, for example DE 195 03 986 A1 known.

Solche Dickstoffpumpen werden beispielsweise zur Förderung von Beton aus einem Aufgabetrichter in eine Förderleitung verwendet. Der Dickstoffförderdruck in der Förderleitung kann bei stationären Dickstoffpumpen weit über 200 bar betragen. Die verwendeten Förderleitungen müssen für einen solchen Dickstoffförderdruck ausgelegt sein.Such thick matter pumps are used, for example, to convey concrete from a feed hopper into a delivery line. The thick matter delivery pressure in the delivery line can be well over 200 bar with stationary thick matter pumps. The delivery lines used must be designed for such a thick matter delivery pressure.

Die DE 37 09 504 A1 betrifft eine Ventileinrichtung für die Steuerung der Druckmittelwege zwischen einer Druckmittelquelle, einem Verbraucher und einem Tank, mit einem Wegeventil, einer stromauf des Wegeventils angeordneten Druckwaage, die von der Differenz zwischen dem Druck stromauf des Wegeventils und dem Lastdruck betätigbar ist, und mit einem an die Lastdruckleitung angeschlossenen Druckbegrenzungsventil zur Begrenzung des die Druckwaage beaufschlagenden Lastdruckes, um den Druck stromauf des Wegeventils auf einen vorbestimmten Wert zu begrenzen, wobei der Auslösedruck des Druckbegrenzungsventils fernverstellbar ist.The DE 37 09 504 A1 relates to a valve device for controlling the pressure medium paths between a pressure medium source, a consumer and a tank, with a directional control valve, a pressure compensator arranged upstream of the directional control valve, which can be actuated by the difference between the pressure upstream of the directional control valve and the load pressure, and with one to the Load pressure line connected pressure relief valve to limit the load pressure acting on the pressure compensator in order to limit the pressure upstream of the directional control valve to a predetermined value, the trigger pressure of the pressure relief valve being remotely adjustable.

Die DE 100 40 737 A1 offenbart eine Ventilanordnung zur Versorgung eines hydraulischen Verbrauchers mit Druckmittel, das von einer Verstellpumpe aus einem Tank ansaugbar ist, mit einem Vorspannventil, dessen über eine Vorspannfeder gegen einen Ventilsitz vorgespannter Staukörper bei Erreichen eines zur Verstellung der Verstellpumpe erforderlichen Mindestdruckes die Verbindung zum Verbraucher aufsteuert, und mit einem Druckbegrenzungsventil zur Begrenzung des maximalen Verbraucherdruckes, wobei dem Druckbegrenzungsventil eine Pilotventilanordnung zur Veränderung des über das Druckbegrenzungsventil einstellbaren maximalen Verbraucherdruckes zugeordnet ist.The DE 100 40 737 A1 discloses a valve arrangement for supplying a hydraulic consumer with pressure medium, which can be sucked in from a tank by a variable displacement pump, with a preload valve whose baffle, which is pretensioned against a valve seat via a preloading spring, opens the connection to the consumer when a minimum pressure required to adjust the variable displacement pump is reached, and with a pressure relief valve for limiting the maximum consumer pressure, the pressure relief valve being assigned a pilot valve arrangement for changing the maximum consumer pressure which can be set via the pressure relief valve.

Beim Bau hoher Bauwerke, wie zum Beispiel Hochhäusern oder Brückenpylonen, werden die Förderleitungen senkrecht an dem Gebäude nach oben verlegt und können Höhen von bis zu 500 m oder mehr überbrücken. Am oberen Ende der Förderleitungen wird oftmals ein Betonverteilermast angeschlossen, um den am Gebäude nach oben geförderten Beton auf der obersten Ebene der Baustelle zu verteilen. Ein derartiger Betonverteilermast umfasst in der Regel einen Knickmast mit dem der Beton verteilt wird. Aus Gewichtsgründen weist der Knickmast in der Regel Förderrohre auf, die auf eine Belastung durch einen Dickstoffförderdruck von etwa 85 bar begrenzt sind. Kommt es in den Förderleitungen oder Förderrohren des Verteilermastes durch Verstopfungen zu einem Stillstand kann sich, insbesondere wenn der Betonverteilermast in geringerer Höhe an die Förderleitung angeschlossen ist, ein kritischer Dickstoffförderdruck einstellen, der die Förderleitung oder die schwächeren Förderrohre des Verteilermastes zum Bersten bringt. Für diesen Anwendungsfall ist eine einfache und sichere einstellbare Begrenzung des Dickstoffförderdrucks erforderlich.When building tall structures, such as high-rise buildings or bridge pylons, the delivery lines are laid vertically upwards on the building and can bridge heights of up to 500 m or more. A concrete placing boom is often connected to the upper end of the delivery lines in order to distribute the concrete conveyed up the building to the top level of the construction site. Such a concrete placing boom usually comprises an articulated boom with which the concrete is distributed. For weight reasons, the articulated mast usually has delivery pipes that are limited to a load from a thick matter delivery pressure of around 85 bar. If the delivery lines or delivery pipes of the placing boom come to a standstill due to blockages, especially if the concrete placing boom is connected to the delivery line at a lower height, a critical thick matter delivery pressure can set, which causes the delivery line or the weaker delivery pipes of the placing boom to burst. For this application a simple and safe adjustable limitation of the thick matter delivery pressure is required.

Auch bei anderen Anwendungsfällen ist zur Absicherung von an die Dickstoffpumpe angeschlossenem Equipment, wie z.B. Betonförderschläuchen, die einstellbare Begrenzung des Dickstoffförderdrucks sinnvoll.In other applications too, equipment connected to the slurry pump, such as Concrete delivery hoses, the adjustable limitation of the thick matter delivery pressure makes sense.

In jedem Fall ist der Dickstoffförderdruck der Dickstoffpumpe an die Situation auf der Baustelle anzupassen, sodass sich in den an die Dickstoffpumpe angeschlossenen Förderrohren oder -leitungen kein kritischer Dickstoffförderdruck aufbauen kann, der die Rohre oder Leitungen zum Bersten bringen kann.In any case, the sludge delivery pressure of the sludge pump must be adapted to the situation on the construction site so that there are no critical feed pipes or lines connected to the sludge pump Can build up thick material delivery pressure, which can burst the pipes or lines.

Um eine Begrenzung des Dickstoffförderdrucks vorzusehen, weisen heute verwendete Dickstoffpumpen eine voreingestellte Druckregelung des hydraulischen Antriebes der Zwei-Zylinder-Kolbenpumpe auf, die in der Regel vor der ersten Inbetriebnahme werkseitig fest eingestellt wird und nur schwer zugänglich ist. Das Verhältnis vom Dickstoffförderdruck zum Hydraulikdruck bei einer Zwei-Zylinder-Kolbenpumpe ist prinzipiell einfach über das Verhältnis der Kolbenflächen der Hydraulikzylinder und der Dickstoff-Förderzylinder zueinander ableitbar. Steigt der Hydraulikdruck über einen fest vorgegebenen Sollwert wird durch die Druckregelung die Förderleistung der Hydraulikpumpe automatisch zurückgenommen, um den Hydraulikdruck, und damit auch den Dickstoffförderdruck zu begrenzen. Diese Art der Druckregelung wird auch als Druckabschneidung bezeichnet.In order to limit the thick matter delivery pressure, the thick matter pumps used today have a preset pressure control of the hydraulic drive of the two-cylinder piston pump, which is usually set at the factory before the first start-up and is difficult to access. The ratio of the thick matter delivery pressure to the hydraulic pressure in a two-cylinder piston pump can in principle simply be derived from the ratio of the piston areas of the hydraulic cylinder and the thick matter delivery cylinder to one another. If the hydraulic pressure rises above a fixed setpoint, the pressure control automatically reduces the delivery rate of the hydraulic pump in order to limit the hydraulic pressure and thus also the thick matter delivery pressure. This type of pressure control is also known as pressure cut-off.

Um die Dickstoffpumpe gegen Fehler in der voreingestellten Druckregelung abzusichern, ist zudem im Stand der Technik ein einstellbares Druckbegrenzungsventil vorgesehen, das den Druck des Hydraulikfluids in der Antriebsleitung auf einen maximalen Wert begrenzt. Wenn aber der eingestellte Maximaldruck niedriger eingestellt ist als der Solldruck der Druckregelung führt dies dazu, dass die voreingestellte Druckregelung außer Kraft gesetzt wird, so dass die Förderleistung der Hydraulikpumpe nicht mehr automatisch zurückgenommen wird. Hierdurch entstehen unnötige Verluste und das Hydraulikfluid wird erhitzt.In order to protect the thick matter pump against errors in the preset pressure control, an adjustable pressure limiting valve is also provided in the prior art, which limits the pressure of the hydraulic fluid in the drive line to a maximum value. If, however, the set maximum pressure is set lower than the setpoint pressure of the pressure control, this has the effect that the preset pressure control is deactivated so that the delivery rate of the hydraulic pump is no longer automatically reduced. This creates unnecessary losses and the hydraulic fluid is heated.

Wird hingegen nur die Druckregelung der Hydraulikpumpe verändert, wird ein Fehler in dieser Regelung unter Umständen nicht durch das Druckbegrenzungsventil, das den Druck des Hydraulikfluids in der Antriebsleitung auf einen maximalen Wert begrenzt, früh genug abgefangen, was zu einer Herabsetzung der Betriebssicherheit der Dickstoffpumpe mit den an diese angeschlossenen Förderleitungen und -rohren führt.If, however, only the pressure control of the hydraulic pump is changed, an error in this control may not be caught early enough by the pressure relief valve, which limits the pressure of the hydraulic fluid in the drive line to a maximum value, which leads to a reduction in the operational reliability of the thick matter pump with the leads to these connected delivery lines and pipes.

Vor diesem Hintergrund ist es Aufgabe der Erfindung, eine verbesserte Dickstoffpumpe bereitzustellen. Insbesondere sollen der Solldruck der Druckregelung und der Maximaldruck des Hydraulikfluids einfach und sicher an die individuellen Gegebenheiten auf der jeweiligen Baustelle anpassbar sein.Against this background, it is the object of the invention to provide an improved thick matter pump. In particular, the target pressure should be Pressure regulation and the maximum pressure of the hydraulic fluid can be easily and safely adapted to the individual conditions on the respective construction site.

Diese Aufgabe löst die Erfindung ausgehend von einer Dickstoffpumpe der eingangs genannten Art dadurch, dass die mindestens eine Hydraulikpumpe zur Begrenzung des Dickstoffförderdrucks eine auf einen Solldruck des Hydraulikfluids einstellbare Druckregelung aufweist und der Druck des Hydraulikfluids in der Antriebsleitung über ein einstellbares Druckbegrenzungsventil auf einen einstellbaren Maximaldruck begrenzt ist, wobei der Solldruck der Druckregelung und der Maximaldruck des Hydraulikfluids durch ein gemeinsames Stellelement einstellbar sind.This object is achieved by the invention based on a thick matter pump of the type mentioned in that the at least one hydraulic pump for limiting the thick matter delivery pressure has a pressure control that can be adjusted to a target pressure of the hydraulic fluid and limits the pressure of the hydraulic fluid in the drive line to an adjustable maximum pressure via an adjustable pressure relief valve is, the setpoint pressure of the pressure control and the maximum pressure of the hydraulic fluid being adjustable by a common adjusting element.

Die durch die Erfindung erreichten Vorteile ergeben sich daraus, dass der Solldruck der Druckregelung und der Maximaldruck des Hydraulikfluids durch ein gemeinsames Stellelement einfach und fehlerunanfällig einstellbar sind. Die auf diese Weise einfach einstellbare Druckregelung vereinfacht die Begrenzung des Dickstoffförderdrucks durch die einstellbar geregelte Hydraulikpumpe. Um weiterhin ein hohes Maß an Sicherheit zu gewährleisten, wird der Druck des Hydraulikfluids in der Antriebsleitung über ein einstellbares Druckbegrenzungsventil automatisch auf einen zu dem Sollwert der Druckregelung passenden Maximalwert begrenzt.The advantages achieved by the invention result from the fact that the setpoint pressure of the pressure control and the maximum pressure of the hydraulic fluid can be adjusted easily and without error by a common adjusting element. The pressure control, which can be easily adjusted in this way, simplifies the limitation of the thick matter delivery pressure by means of the adjustable hydraulic pump. In order to continue to ensure a high level of safety, the pressure of the hydraulic fluid in the drive line is automatically limited to a maximum value that matches the setpoint value of the pressure control via an adjustable pressure limiting valve.

Die oben erwähnten Nachteile des Standes der Technik werden dadurch behoben.The above-mentioned disadvantages of the prior art are thereby eliminated.

Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen.Advantageous configurations and developments of the invention emerge from the subclaims.

Gemäß einer vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, dass das Stellelement ausgelegt ist, den Solldruck der Druckregelung und den Maximaldruck des Hydraulikfluids in der Weise gleichlaufend einzustellen, dass der Maximaldruck stets um einen vorgegebenen Differenzdruck oberhalb des Solldrucks liegt. Auf diese Weise ist sichergestellt, dass die Einstellungen über das gemeinsame Stellelement zu keiner Veränderung der Sicherheitsvorkehrungen und Effizienz der Dickstoffpumpe führen.According to an advantageous embodiment of the invention, it is provided that the actuating element is designed to set the target pressure of the pressure control and the maximum pressure of the hydraulic fluid concurrently in such a way that the maximum pressure is always a predetermined differential pressure above the target pressure. In this way it is ensured that the settings via the common adjusting element do not lead to any change in the safety precautions and efficiency of the thick matter pump.

Eine bevorzugte Ausführung sieht vor, dass das Stellelement ein auf den Solldruck des Hydraulikfluids einstellbares erstes Vorsteuerventil aufweist, das eingangsseitig mit einem Stellschieber der Druckregelung der Hydraulikpumpe verbunden ist und ausgangsseitig in ein Hydraulikreservoir entlastet ist, wobei das erste Vorsteuerventil ab Erreichen des Solldrucks öffnet. Mit diesem ersten Vorsteuerventil ist eine einfache, aber sichere Möglichkeit gegeben den Druck des Hydraulikfluids bei dem Solldruck abzuschneiden.A preferred embodiment provides that the actuating element has a first pilot valve which is adjustable to the setpoint pressure of the hydraulic fluid, which is connected on the inlet side to an adjusting slide for the pressure control of the hydraulic pump and on the outlet side is relieved into a hydraulic reservoir, the first pilot valve opening when the setpoint pressure is reached. With this first pilot valve, a simple but safe possibility is given to cut off the pressure of the hydraulic fluid at the setpoint pressure.

Besonders vorteilhaft ist die Weiterbildung, dass das Stellelement ein zweites Vorsteuerventil aufweist, das eingangsseitig mit einer Hauptstufe des Druckbegrenzungsventils und ausgangsseitig mit der Eingangsseite des ersten Vorsteuerventils verbunden ist, wobei das zweite Vorsteuerventil ab dem vorgegebenen Differenzdruck zwischen Eingangs- und Ausgangsseite öffnet. Dieses zweite Vorsteuerventil stellt somit sicher, dass der durch das Druckbegrenzungsventil vorgegebene Maximaldruck in der Antriebsleitung automatisch immer um den Differenzdruck oberhalb des Solldrucks der Druckabschneidung liegt, d.h. der Maximaldruck wird automatisch mit der Einstellung des Solldrucks korrekt auf einen dazu passenden Maximaldruck eingestellt. Damit kommt es zuverlässig nicht zu unerwünschten Wechselwirkungen zwischen der Druckregelung der Hydraulikpumpe und der Druckentlastung durch das Druckbegrenzungsventils. Gleichzeitig ist die Sicherheit stets gewährleistet, da die Hauptstufe des Druckbegrenzungsventils öffnet, wenn der Druck in der Antriebsleitung den Sollwert überschreitet und einen um den geeignet gewählten Differenzdruck oberhalb des Solldrucks liegenden Druckwert erreicht. Der vorgegebene Differenzdruck zwischen Eingangs- und Ausgangsseite des zweiten Vorsteuerventils beträgt optimalerweise etwa 20 bar, da hierdurch eine ausreichende Betriebssicherheit der Dickstoffpumpe gewährleistet ist.The development is particularly advantageous that the actuating element has a second pilot valve, which is connected on the inlet side to a main stage of the pressure relief valve and on the outlet side to the inlet side of the first pilot valve, the second pilot valve opening from the specified differential pressure between the inlet and outlet side. This second pilot valve thus ensures that the maximum pressure in the drive line specified by the pressure relief valve is automatically always the differential pressure above the setpoint pressure of the pressure cut-off, i.e. the maximum pressure is automatically set correctly to a suitable maximum pressure when the target pressure is set. This reliably prevents undesired interactions between the pressure regulation of the hydraulic pump and the pressure relief through the pressure limiting valve. At the same time, safety is always guaranteed, since the main stage of the pressure relief valve opens when the pressure in the drive line exceeds the setpoint and reaches a pressure value above the setpoint pressure by the suitably selected differential pressure. The predetermined differential pressure between the inlet and outlet side of the second pilot valve is optimally about 20 bar, since this ensures sufficient operational reliability of the thick matter pump.

Weiter vorteilhaft ist die Ausgestaltung, dass das zweite Vorsteuerventil nicht einstellbar ist. Hierdurch kann gewährleistet werden, dass die Einstellmöglichkeiten über das Stellelement nicht durch manuelle Einstellungen am zweiten Vorsteuerventil zu einer eingeschränkten Betriebssicherheit der Dickstoffpumpe führen.The configuration that the second pilot valve cannot be adjusted is also advantageous. This ensures that the setting options via the adjusting element do not lead to restricted operational reliability of the thick matter pump due to manual settings on the second pilot valve.

Eine vorteilhafte Ausführungsform der Erfindung sieht vor, dass das erste Vorsteuerventil über ein Handrad einstellbar ist. Die Einstellmöglichkeit des ersten Vorsteuerventils über ein Handrad macht die Anpassung der Dickstoffpumpe an die Gegebenheiten auf der jeweiligen Baustelle für den individuellen Einsatzzweck besonders einfach und sicher.An advantageous embodiment of the invention provides that the first pilot valve can be adjusted using a handwheel. The ability to adjust the first pilot valve using a handwheel makes it particularly easy and safe to adapt the thick matter pump to the conditions on the respective construction site for the individual application.

Gemäß einer vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, dass das Handrad feststellbar und / oder abschließbar ist. Eine Feststellmöglichkeit des Handrades verhindert ungewollte Veränderungen der Einstellungen an dem ersten Vorsteuerventil und damit an dem Stellelement. Die Abschließmöglichkeit des Handrades stellt zudem sicher, dass Veränderungen an der Stellung des Handrades nur durch befugtes Personal erfolgen.According to an advantageous embodiment of the invention it is provided that the handwheel can be locked and / or locked. The ability to lock the handwheel prevents unwanted changes to the settings on the first pilot valve and thus on the adjusting element. The possibility of locking the handwheel also ensures that changes to the position of the handwheel can only be made by authorized personnel.

Eine weitere vorteilhafte Ausführung der Erfindung ist, dass das Stellelement ein zu dem ersten Vorsteuerventil parallel geschaltetes, nicht einstellbares drittes Vorsteuerventil aufweist, das ab Erreichen eines maximal zulässigen Drucks öffnet. Ein zu dem ersten Vorsteuerventil parallel geschaltetes drittes Vorsteuerventil, welches bei einem maximal zulässigen Druck öffnet und die Druckregelung in ein Hydraulikreservoir entlastet, bietet eine zusätzliche Absicherung bei Störungen oder zu hoher Einstellung des einstellbaren ersten Vorsteuerventils.A further advantageous embodiment of the invention is that the adjusting element has a non-adjustable third pilot valve which is connected in parallel to the first pilot valve and which opens when a maximum permissible pressure is reached. A third pilot valve connected in parallel to the first pilot valve, which opens at a maximum permissible pressure and relieves pressure control in a hydraulic reservoir, provides additional protection in the event of malfunctions or too high a setting of the adjustable first pilot valve.

Eine bevorzugte Ausführung sieht vor, dass dem ersten Vorsteuerventil ein Umschaltventil vorgeschaltet ist, in der Weise, dass das dritte Vorsteuerventil zu der Anordnung aus erstem Vorsteuerventil und Umschaltventil parallel geschaltet ist, wobei das Umschaltventil die Verbindung der Eingangsseite des ersten Vorsteuerventils mit dem Stellschieber der Druckregelung wahlweise herstellt oder trennt. Ein solches Umschaltventil ermöglicht die einfache Verstellung des Solldruckes der Druckregelung zwischen dem am ersten Vorsteuerventil eingestellten Solldruck und dem maximal zulässigen Druck der Druckregelung, der durch das dritte Vorsteuerventil vorgegeben ist. Hierdurch kann die Begrenzung des Dickstoffförderdrucks an der Dickstoffpumpe auf den maximal zulässigen Druck sehr schnell angepasst werden, ohne dass eine Änderung am ersten einstellbaren Vorsteuerventil nötig ist.A preferred embodiment provides that the first pilot valve is preceded by a switchover valve in such a way that the third pilot valve is connected in parallel to the arrangement of the first pilot valve and switchover valve, the switchover valve connecting the input side of the first pilot valve to the setting slide of the pressure control optionally manufactures or separates. Such a switchover valve enables the setpoint pressure of the pressure control to be easily adjusted between the setpoint pressure set at the first pilot control valve and the maximum permissible pressure of the pressure control system, which is specified by the third pilot control valve. As a result, the limitation of the thick matter delivery pressure at the thick matter pump can be adapted very quickly to the maximum permissible pressure without having to change the first adjustable pilot valve.

Eine vorteilhafte Ausführungsform der Erfindung sieht vor, dass das Umschaltventil rastend und / oder abschließbar ist. Eine Einrastmöglichkeit des Umschaltventils verhindert unbeabsichtigte Stellungsänderungen an dem Umschaltventil und damit an dem Stellelement. Die Abschließmöglichkeit des Umschaltventils stellt zudem sicher, dass Veränderungen an der Stellung des Umschaltventils nur durch befugtes Personal erfolgen.An advantageous embodiment of the invention provides that the switching valve is latching and / or lockable. A latching option for the switchover valve prevents unintentional changes in position on the switchover valve and thus on the actuating element. The ability to lock the changeover valve also ensures that changes to the position of the changeover valve are only made by authorized personnel.

Weitere Merkmale, Einzelheiten und Vorteile der Erfindung ergeben sich aufgrund der nachfolgenden Beschreibung sowie anhand der Zeichnungen. Ausführungsbeispiele der Erfindung sind in den folgenden Zeichnungen rein schematisch dargestellt und werden nachfolgend näher beschrieben. Einander entsprechende Gegenstände oder Elemente sind in allen Figuren mit den gleichen Bezugszeichen versehen. Es zeigen

Figur 1:
Dickstoffpumpe nach dem Stand der Technik
Figur 2:
erfindungsgemäße Dickstoffpumpe,
Figur 3:
erfindungsgemäße Dickstoffpumpe mit Umschaltventil,
Figur 4:
erfindungsgemäßes Stellelement,
Figur 5:
Variante der Dickstoffpumpe mit fernsteuerbarem Vorsteuerventil.
Further features, details and advantages of the invention emerge from the following description and from the drawings. Embodiments of the invention are shown purely schematically in the following drawings and are described in more detail below. Objects or elements that correspond to one another are provided with the same reference symbols in all figures. Show it
Figure 1:
State of the art thick matter pump
Figure 2:
thick matter pump according to the invention,
Figure 3:
thick matter pump according to the invention with switching valve,
Figure 4:
adjusting element according to the invention,
Figure 5:
Variant of the thick matter pump with remotely controllable pilot valve.

Die Darstellung gemäß Figur 1 zeigt schematisch und ausschnittsweise eine Dickstoffpumpe 1 mit einer hydraulisch angetriebenen Zwei-Zylinder-Kolbenpumpe 2 zur Erzeugung eines Dickstoffförderdrucks gemäß dem Stand der Technik. Die beiden Hydraulikzylinder sind schematisch angedeutet und über Verbindungsleitungen und eine Umschaltsteuerung 12, hier beispielsweise ein elektrohydraulisch vorgesteuertes 4/3-Wegeventil, mit einer Antriebsleitung 8 verbunden, über welche die Zwei-Zylinder-Kolbenpumpe 2 von einer Hydraulikpumpe 3, beispielweise eine Axialkolben-Verstellpumpe, mit Hydraulikfluid beaufschlagt wird. Über die Umschaltsteuerung 12 erfolgt eine abwechselnde Beaufschlagung der beiden Hydraulikzylinder der Zwei-Zylinder-Kolbenpumpe. An den oberen Enden der schematisch angedeuteten Kolbenstangen der Hydraulikzylinder, die nach oben aus den Hydraulikzylindern herausragen, sind nicht dargestellte Förderkolben angeordnet, die in Förderzylindern von den Hydraulikzylindern hin und her geschoben werden und somit den Dickstoffförderdruck erzeugen.The representation according to Figure 1 shows schematically and in sections a thick matter pump 1 with a hydraulically driven two-cylinder piston pump 2 for generating a thick matter delivery pressure according to the prior art. The two hydraulic cylinders are indicated schematically and are connected to a drive line 8 via connecting lines and a switchover control 12, here for example an electrohydraulically piloted 4/3-way valve, via which the two-cylinder piston pump 2 is connected to a hydraulic pump 3, for example an axial piston variable displacement pump , is acted upon with hydraulic fluid. About the switchover control 12 takes place alternating loading of the two hydraulic cylinders of the two-cylinder piston pump. At the upper ends of the schematically indicated piston rods of the hydraulic cylinders, which protrude upward from the hydraulic cylinders, delivery pistons (not shown) are arranged, which are pushed back and forth in delivery cylinders by the hydraulic cylinders and thus generate the thick matter delivery pressure.

Die in den Figuren mit durchgängigen Linien dargestellten Hydraulikleitungen sind sogenannte Arbeitsleitungen, die für hohe Hydraulikfluidströme ausgelegt sind, während die mit unterbrochenen Linien dargestellten Hydraulikleitungen Steuer- oder Messleitungen darstellen die für kleinere Hydraulikfluidströme ausgelegt sind.The hydraulic lines shown in solid lines in the figures are so-called working lines that are designed for high hydraulic fluid flows, while the hydraulic lines shown with broken lines represent control or measuring lines that are designed for smaller hydraulic fluid flows.

An der Antriebsleitung 8, zwischen der Umschaltsteuerung 12 und der Hydraulikpumpe 3, ist ein Manometer 19 angekoppelt, an dem der momentane Druck des Hydraulikfluids ablesbar ist.A manometer 19, on which the instantaneous pressure of the hydraulic fluid can be read, is coupled to the drive line 8, between the switchover control 12 and the hydraulic pump 3.

Der Dickstoffförderdruck kann über das Verhältnis der wirksamen Kolbenflächen der Hydraulikzylinder und der Dickstoff-Förderzylinder zueinander abgeleitet werden.The thick matter delivery pressure can be derived from the ratio of the effective piston areas of the hydraulic cylinder and the thick matter delivery cylinder to one another.

Die Einstellung des maximalen Sollwertes der Druckregelung der Hydraulikpumpe wird mittels eines an der Hydraulikpumpe 3 angeordneten Stellschiebers 4 manuell eingestellt. Sobald der Druck des Hydraulikfluids in der Antriebsleitung 8 diesen Sollwert erreicht, wird die Pumpleistung der Hydraulikpumpe 3 automatisch verringert, so dass bei Erreichen dieses Grenzwertes keine Verluste im Hydrauliksystem entstehen. Dieser Sollwert wird in der Regel bei der ersten Inbetriebnahme an der Hydraulikpumpe werksseitig fest voreingestellt und sollte in der Regel nicht verändert werden.The setting of the maximum setpoint of the pressure regulation of the hydraulic pump is set manually by means of an adjusting slide 4 arranged on the hydraulic pump 3. As soon as the pressure of the hydraulic fluid in the drive line 8 reaches this setpoint value, the pumping power of the hydraulic pump 3 is automatically reduced, so that when this limit value is reached, no losses occur in the hydraulic system. This setpoint is usually permanently preset at the factory when the hydraulic pump is started up and should usually not be changed.

Falls die Druckbegrenzung an der Hydraulikpumpe 3, z.B. durch einen klemmenden Stellschieber 4, nicht anspricht, ist zur Sicherheit noch eine Druckbegrenzungseinheit 5a an die Arbeitsleitung 8 angeschlossen. Diese Druckbegrenzungseinheit 5a umfasst die Hauptstufe des Druckbegrenzungsventils 15, mit einem nachgeschalteten Vorsteuerventil 18. Der Hydraulikdruck der Antriebsleitung 8 wird durch den mit einer Düse ausgestatten Durchlasskanal 17 durch die Hauptstufe 15 durch eine weitere Dämpfungsdüse 20 zu dem Vorsteuerventil 18 durchgeleitet. Bei Erreichen eines Grenzdruckes, der etwas höher als der Sollwert des an der Hydraulikpumpe 3 eingestellten Sollwertes liegen sollte, öffnet das Vorsteuerventil 18 und damit auch die Hauptstufe 15 der Druckbegrenzungseinheit 5a, so dass die Antriebsleitung 8 direkt mit dem Hydraulikreservoir 14 verbunden wird und damit der von der Hydraulikpumpe 3 aufgebaute Druck abgebaut wird. Weil das Öffnen der Druckbegrenzungseinheit 5a aber eine hohe Verlustleistung verursacht, sollte dieses nur beim Versagen der Druckreglung über die Hydraulikpumpe 3 geschehen. Aus diesem Grund ist der Grenzdruck der Druckbegrenzungseinheit 15 auch immer etwas höher, beispielsweise 20 bar, als der Sollwert an der Hydraulikpumpe 3 einzustellen.If the pressure limitation on the hydraulic pump 3 does not respond, for example due to a jammed adjusting slide 4, a pressure limitation unit 5a is also connected to the working line 8 for safety. This pressure limiting unit 5 a comprises the main stage of the pressure limiting valve 15, with a downstream pilot valve 18. The hydraulic pressure of the drive line 8 is passed through the passage channel 17, which is equipped with a nozzle, through the main stage 15 through a further damping nozzle 20 to the pilot valve 18. When a limit pressure is reached, which should be slightly higher than the setpoint of the setpoint set on the hydraulic pump 3, the pilot valve 18 and thus also the main stage 15 of the pressure limiting unit 5a opens so that the drive line 8 is connected directly to the hydraulic reservoir 14 and thus the pressure built up by the hydraulic pump 3 is reduced. However, because opening the pressure limiting unit 5a causes high power loss, this should only happen if the pressure control via the hydraulic pump 3 fails. For this reason, the limit pressure of the pressure limiting unit 15 is also always somewhat higher, for example 20 bar, than the setpoint to be set on the hydraulic pump 3.

Falls eine Verringerung des maximal zulässigen Dickstoffförderdruckes notwendig ist, wenn beispielsweise Förderleitungen an die Zwei-Zylinder-Kolbenpumpe 1 angeschlossen sind, die nur geringere Förderdrücke vertragen, müssten deshalb beide Grenzwerte manuell getrennt verstellt werden, was aber in der Praxis nur mit sehr hohem Aufwand möglich ist.If it is necessary to reduce the maximum permissible thick matter delivery pressure, for example if delivery lines are connected to the two-cylinder piston pump 1 that can only tolerate lower delivery pressures, the two limit values would therefore have to be adjusted separately, which in practice is only possible with a great deal of effort is.

Die Darstellung gemäß Figur 2 zeigt schematisch und ausschnittsweise eine Dickstoffpumpe 1 mit einer hydraulisch angetriebenen Zwei-Zylinder-Kolbenpumpe 2 zur Erzeugung eines Dickstoffförderdrucks gemäß der Erfindung. Die Funktionsweise entspricht weitestgehend der in Figur 1 dargestellten Pumpe 1, weshalb im Folgenden nur auf die erfindungsgemäße Einstellung des Dickstoffförderdruckes eingegangen wird.The representation according to Figure 2 shows schematically and partially a thick matter pump 1 with a hydraulically driven two-cylinder piston pump 2 for generating a thick matter delivery pressure according to the invention. The functionality largely corresponds to that in Figure 1 pump 1 shown, which is why only the setting according to the invention of the thick matter delivery pressure will be discussed below.

Bei dem hier dargestellten Ausführungsbeispiel wird ein sogenanntes offenes Hydrauliksystem eingesetzt bei dem die Hydraulikpumpe 3 das Hydraulikfluid immer in die gleiche Richtung pumpt und das Hydraulikfluid aus einem Hydraulikreservoir (Tank) 14 ansaugt. Die Erfindung ist aber beispielsweise auch auf bekannte geschlossene Hydrauliksysteme anwendbar, bei der die Umschaltung der Pumprichtung der Hydraulikzylinder der Zwei-Zylinder-Kolbenpumpe 2 erfolgt, indem die Pumprichtung der Hydraulikpumpe 3 über eine Umschaltsteuerung umgekehrt wird.In the embodiment shown here, a so-called open hydraulic system is used in which the hydraulic pump 3 always pumps the hydraulic fluid in the same direction and sucks the hydraulic fluid from a hydraulic reservoir (tank) 14. However, the invention can also be applied, for example, to known closed hydraulic systems in which the pumping direction of the hydraulic cylinders of the two-cylinder piston pump 2 is switched over by reversing the pumping direction of the hydraulic pump 3 via a switchover control.

Um die hohen Volumenströme in Verbindung mit den hohen Pumpdrücken des Hydraulikfluids umzusetzen, werden auch oftmals zwei parallel geschaltete Hydraulikpumpen 3 eingesetzt, was aus Gründen der Übersichtlichkeit hier nicht dargestellt ist.To implement the high volume flows in connection with the high pump pressures of the hydraulic fluid, two hydraulic pumps 3 connected in parallel are often used, which is not shown here for reasons of clarity.

Der durch die Dickstoffpumpe 1 erzeugte Dickstoffförderdruck lässt sich einstellbar begrenzen. Hierzu weist die Dickstoffpumpe 1 ein Stellelement 6 auf, über das der Solldruck einer Druckregelung und der Maximaldruck des Hydraulikfluids in der Antriebsleitung 8 gemeinsam einstellbar sind. Über die Druckregelung kann die Hydraulikpumpe 3 zur Abschneidung des Dickstoffförderdrucks geregelt werden, indem ein Solldruck des Hydraulikfluids in der Druckregelung eingestellt wird. Hierzu ist das Stellelement 6 über den Anschluss X mit dem Steuerschieber 4 der Druckregelung an der Hydraulikpumpe 3 verbunden. Der durch die Hydraulikpumpe 3 in der Antriebsleitung 8 erzeugte Druck des Hydraulikfluids wird auf einen durch das Druckbegrenzungsventil 5 einstellbaren Maximaldruck begrenzt. Hierzu ist das Stellelement 6 über den Anschluss X1 mit der Hauptstufe 15 des Druckbegrenzungsventils 5 verbunden. Das Stellelement 6 ist derart ausgelegt, dass der Solldruck der Druckregelung und der Maximaldruck des Hydraulikfluids in der Antriebsleitung 8 gleichlaufend eingestellt werden können. Auf diese Weise liegt der Maximaldruck des Hydraulikfluids in der Antriebsleitung 8 stets um einen vorgegebenen Differenzdruck oberhalb des Solldrucks der Druckregelung. Das Stellelement 6 weist ein auf den Solldruck des Hydraulikfluids einstellbares erstes Vorsteuerventil 9 auf, welches eingangsseitig mit dem Steuerschieber 4 der Druckregelung der Hydraulikpumpe 3 verbunden ist und ausgangsseitig in ein Hydraulikreservoir 14 entlastet ist. Das erste Vorsteuerventil 9 öffnet automatisch bei Erreichen des eingestellten Solldrucks in der Druckregelung und stellt auf diese Weise sehr einfach sicher, dass der eingestellte Solldruck eingehalten wird. Bei dem Ausführungsbeispiel kann der Solldruck in der Druckregelung zwischen 0 und 315 bar über das erste Vorsteuerventil 9 eingestellt werden. Ein zweites Vorsteuerventil 7 des Stellelementes 6 ist eingangsseitig mit der Hauptstufe 15 des Druckbegrenzungsventils 5 und ausgangsseitig mit der Eingangsseite des ersten Vorsteuerventils 9 verbunden. Dieses zweite Vorsteuerventil 7 hat die Eigenschaft den Staudruck von der Abgangsseite direkt auf den über die Stellfeder eingestellten Einstellwert aufzuaddieren und öffnet ab einem vorgegebenen Differenzdruck zwischen Eingangs- und Ausgangsseite und stellt somit die zu dem eingestellten Sollwert passende Begrenzung des Drucks in der Antriebsleitung 8 über das Druckbegrenzungsventil 5 sicher. Als vorgegebener Differenzdruck sind bei dem Ausführungsbeispiel 20 bar angegeben. Aus Gründen der Betriebssicherheit ist das hier einstellbar dargestellte zweite Vorsteuerventil 7 vorzugsweise werksseitig fest voreingestellt, d.h. die vorgegebene Druckdifferenz, bei der das Vorsteuerventil 7 schaltet, lässt sich nicht verändern. Auf diese Weise wirkt das zweite Vorsteuerventil 7 auf die Hauptstufe 15 des Druckbegrenzungsventils 5 zur Absicherung in der Weise, dass das Druckbegrenzungsventil 5 die Antriebsleitung 8 druckentlastet, sobald der Druck des Hydraulikfluids in der Antriebsleitung 8 einen Wert überschreitet, der um die voreingestellte Druckdifferenz oberhalb des am ersten Vorsteuerventil 9 eingestellten Sollwertes der Druckregelung der Hydraulikpumpe 3 liegt. Das Stellelement 6 weist weiter ein optionales, zu dem ersten Vorsteuerventil 9 parallel geschaltetes, nicht einstellbares drittes Vorsteuerventil 10 auf, welches bei Erreichen eines maximal zulässigen Druckes in das Hydraulikreservoir 14 entlastet. Der hier erreichbare maximal zulässige Druck ist im Ausführungsbeispiel mit 320 bar angegeben. Dieser maximal zulässige Systemdruck wird vom Werk voreingestellt. Dieses dritte Vorsteuerventil 10 stellt sicher, dass es bei Fehlern an dem ersten Vorsteuerventil 9 nicht zu einer Überlastung des gesamten Systems der Dickstoffpumpe kommt. Auf diese Weise wirken das erste Vorsteuerventil 9 und das dritte Vorsteuerventil 10 direkt auf den Steuerschieber 4 für die Druckabscheidung des Hydraulikpumpenreglers. Durch die Parallelschaltung mit dem ersten Vorsteuerventil 9 ist die Absicherung durch das dritte Vorsteuerventil 10 dauerhaft gewährleistet.The thick matter delivery pressure generated by the thick matter pump 1 can be set adjustable. For this purpose, the thick matter pump 1 has an adjusting element 6, via which the setpoint pressure of a pressure control and the maximum pressure of the hydraulic fluid in the drive line 8 can be set together. The hydraulic pump 3 for cutting off the thick matter delivery pressure can be controlled via the pressure control by setting a setpoint pressure for the hydraulic fluid in the pressure control. For this purpose, the adjusting element 6 is connected to the control slide 4 of the pressure regulator on the hydraulic pump 3 via the connection X. The pressure of the hydraulic fluid generated by the hydraulic pump 3 in the drive line 8 is limited to a maximum pressure that can be set by the pressure limiting valve 5. For this purpose, the actuating element 6 is connected to the main stage 15 of the pressure limiting valve 5 via the connection X1. The adjusting element 6 is designed in such a way that the setpoint pressure of the pressure control and the maximum pressure of the hydraulic fluid in the drive line 8 can be adjusted simultaneously. In this way, the maximum pressure of the hydraulic fluid in the drive line 8 is always a predetermined differential pressure above the setpoint pressure of the pressure control. The actuating element 6 has a first pilot valve 9 which is adjustable to the setpoint pressure of the hydraulic fluid and which is connected on the input side to the control slide 4 of the pressure control of the hydraulic pump 3 and is relieved into a hydraulic reservoir 14 on the output side. The first pilot valve 9 opens automatically when the set target pressure is reached in the pressure control and in this way very simply ensures that the set target pressure is maintained. In the exemplary embodiment, the setpoint pressure in the pressure control can be set between 0 and 315 bar via the first pilot control valve 9. A second pilot valve 7 of the adjusting element 6 is connected on the input side to the main stage 15 of the pressure limiting valve 5 and on the output side to the input side of the first pilot valve 9. This second pilot valve 7 has the property of the back pressure from the outlet side directly to the Adjustment spring add up the set value and opens from a predetermined differential pressure between the inlet and outlet side and thus ensures that the pressure in the drive line 8 via the pressure relief valve 5 is limited to match the setpoint value. The specified differential pressure in the exemplary embodiment is 20 bar. For reasons of operational safety, the second pilot valve 7, shown here adjustable, is preferably permanently preset at the factory, ie the predetermined pressure difference at which the pilot valve 7 switches cannot be changed. In this way, the second pilot valve 7 acts on the main stage 15 of the pressure relief valve 5 for protection in such a way that the pressure relief valve 5 relieves the pressure in the drive line 8 as soon as the pressure of the hydraulic fluid in the drive line 8 exceeds a value that is above the preset pressure difference at the first pilot valve 9 setpoint of the pressure control of the hydraulic pump 3 is. The actuating element 6 also has an optional, non-adjustable third pilot valve 10 connected in parallel to the first pilot valve 9, which relieves pressure in the hydraulic reservoir 14 when a maximum permissible pressure is reached. The maximum permissible pressure that can be achieved here is specified as 320 bar in the exemplary embodiment. This maximum permissible system pressure is preset at the factory. This third pilot valve 10 ensures that, in the event of errors in the first pilot valve 9, there is no overloading of the entire system of the thick matter pump. In this way, the first pilot valve 9 and the third pilot valve 10 act directly on the control slide 4 for the pressure separation of the hydraulic pump regulator. As a result of the parallel connection with the first pilot control valve 9, the protection provided by the third pilot control valve 10 is permanently guaranteed.

Die Düsen 20 dienen dem Zweck, das Durchflussvolumen des Hydraulikfluids, bei gleichzeitigem Durchleiten des Hydraulikdruckes, zu begrenzen, so dass die Vorsteuerventile 7, 9, 10 und der Stellschieber 4 nur gedämpft angesprochen werden.The nozzles 20 serve the purpose of limiting the flow volume of the hydraulic fluid while the hydraulic pressure is being passed through, so that the pilot valves 7, 9, 10 and the setting slide 4 are only addressed in a damped manner.

Die Figur 3 zeigt schematisch und ausschnittsweise eine Dickstoffpumpe 1 gemäß Figur 1, wobei hier das Stellelement 6 ein zusätzliches Umschaltventil 11 aufweist. Das Umschaltventil 11 ist dem ersten Vorsteuerventil 9 vorgeschaltet, in der Weise, dass das dritte Vorsteuerventil 10 zu der Anordnung aus erstem Vorsteuerventil 9 und Umschaltventil 11 parallel geschaltet ist, wobei das Umschaltventil 11 die Verbindung der Eingangsseite des ersten Vorsteuerventils 9 mit dem Stellschieber 4 der Druckregelung wahlweise herstellt oder trennt. Hierdurch ermöglicht das Umschaltventil 11 die einfache Verstellung des Solldruckes der Druckregelung zwischen dem am ersten Vorsteuerventil 9 eingestellten Solldruck und dem maximal zulässigen Systemdruck am dritten Vorsteuerventil 10. Auf diese Weise kann die Begrenzung des Dickstoffförderdrucks sehr schnell angepasst werden, ohne dass Einstellungsänderungen am ersten einstellbaren Vorsteuerventil 9 nötig sind. Vorzugsweise ist das Umschaltventil 11 als Kugelhahn ausgebildet. Das Stellelement 6 kann somit auch einfach wieder über das Umschaltventil 11 auf den niedrigeren, eingestellten Druck zurückgestellt werden. In Figur 4 ist eine konstruktive Realisierung des Stellelementes 6 gemäß Figur 2 schematisch von außen gezeigt. Das Stellelement 6 ist als Sonderblock ausgebildet und an einer durch den Benutzer gut erreichbaren Stelle der Dickstoffpumpe 1 (Fig. 1 oder 2) positionierbar. Wie zu erkennen ist, lässt sich das erste Vorsteuerventil 9 über ein Handrad 13 einstellen. Zudem ist das Handrad 13 feststellbar und abschließbar ausgebildet. Auf diese Weise lässt sich der Einstellwert am ersten Vorsteuerventil 9 sichern. Auch das gezeigte Umschaltventil 11 lässt sich einfach handhaben und ist rastend sowie abschließbar ausgebildet. Das Stellelement 6 verfügt zudem über Messanschlüsse 16 mit denen sich Informationen zu den Druckverhältnissen im Stellelement 6 abgreifen lassen.The Figure 3 shows schematically and partially a thick matter pump 1 according to Figure 1 , with the adjusting element 6 having an additional switching valve 11 having. The switching valve 11 is connected upstream of the first pilot valve 9 in such a way that the third pilot valve 10 is connected in parallel to the arrangement of the first pilot valve 9 and the switching valve 11, the switching valve 11 connecting the input side of the first pilot valve 9 to the setting slide 4 of the Pressure control optionally establishes or separates. In this way, the switching valve 11 enables the setpoint pressure of the pressure control to be easily adjusted between the setpoint pressure set on the first pilot control valve 9 and the maximum permissible system pressure on the third pilot control valve 10. In this way, the limitation of the thick matter feed pressure can be adjusted very quickly without changing the settings on the first adjustable pilot control valve 9 are necessary. The switching valve 11 is preferably designed as a ball valve. The adjusting element 6 can thus also be reset again easily to the lower, set pressure via the switching valve 11. In Figure 4 is a constructive implementation of the adjusting element 6 according to Figure 2 shown schematically from the outside. The adjusting element 6 is designed as a special block and at a point of the thick matter pump 1 that is easily accessible by the user ( Fig. 1 or 2 ) positionable. As can be seen, the first pilot valve 9 can be adjusted via a hand wheel 13. In addition, the handwheel 13 is lockable and lockable. In this way, the setting value on the first pilot control valve 9 can be saved. The switching valve 11 shown can also be handled easily and is designed to be latching and lockable. The adjusting element 6 also has measuring connections 16 with which information on the pressure conditions in the adjusting element 6 can be tapped.

Die Einstellung des Sollwertes der Druckbegrenzung der Hydraulikpumpe 3 kann der Bediener der Maschine am Vorsteuerventil 9 in Verbindung mit dem Manometer 19 vornehmen. Dazu wird die Zwei-Zylinder-Kolbenpumpe 2 blockiert, indem beispielsweise die Umschaltsteuerung 12 in die Mittel-(Sperr-) stellung und die Hydraulikpumpe 3 auf volle Leistung gestellt wird. Auf dem Manometer 19 wird dann der am Vorsteuerventil 9 eingestellte Druck angezeigt, weil die Leistung der Hydraulikpumpe 3, wie weiter oben beschrieben, automatisch auf diesen Druck begrenzt wird. Bei einem Fehler am Stellschieber 4 an der Hydraulikpumpe 3 führt ein Systemdruck der um 20 bar über den eingestellten Sollwert liegt, immer noch dazu, dass die Antriebsleitung 8 über das Druckbegrenzungsventil 5 entlastet wird.The machine operator can set the desired value of the pressure limitation of the hydraulic pump 3 at the pilot valve 9 in conjunction with the pressure gauge 19. For this purpose, the two-cylinder piston pump 2 is blocked, for example by setting the switchover control 12 to the central (blocking) position and the hydraulic pump 3 to full power. The pressure set at the pilot control valve 9 is then displayed on the manometer 19 because the output of the hydraulic pump 3, as described above, is automatically limited to this pressure. In the event of a fault in the setting slide 4 on the hydraulic pump 3, a system pressure of 20 bar above the set target value is, still to the fact that the drive line 8 is relieved via the pressure relief valve 5.

Über ein entsprechendes Umrechnungsdiagramm kann der Bediener somit einfach den Hydraulikdruck so einstellen, dass der maximale Dickstoffförderdruck nicht überschritten werden kann.Using a corresponding conversion diagram, the operator can easily set the hydraulic pressure so that the maximum thick matter delivery pressure cannot be exceeded.

Das hier als bauliche Einheit dargestellte Stellelement 6 kann beispielsweise auch in einen Hydrauliksteuerblock für die Dickstoffpumpe integriert sein, solange eine einfache Einstellbarkeit und / oder Zugänglichkeit des Vorsteuerventils 9 gegeben ist. Das Vorsteuerventil 9, aber auch das Umschaltventil 11, könnten beispielsweise auch elektrisch ferngesteuert einstellbar sein. Weiterhin ist eine räumlich getrennte Anordnung der Ventile des Stellelementes 6 denkbar.The actuating element 6 shown here as a structural unit can, for example, also be integrated into a hydraulic control block for the thick matter pump, as long as the pilot valve 9 can be easily adjusted and / or accessed. The pilot valve 9, but also the switching valve 11, could for example also be electrically adjustable by remote control. Furthermore, a spatially separate arrangement of the valves of the actuating element 6 is conceivable.

Eine Variante der Erfindung, bei der das Vorsteuerventil 9 elektrisch ferngesteuert einstellbar ist, ist in Figur 5 dargestellt. Das Vorsteuerventil 9 ist hier als elektrisch gesteuertes Proportional-Druckbegrenzungsventil ausgeführt und wird von einer Steuerelektronik 23 angesteuert. Die Steuerelektronik 23 misst mittels des Drucksensors 21 den Hydraulik-Antriebsdruck der Zwei-Zylinder-Kolbenpumpe 2 und leitet daraus den Dickstoffförderdruck über das Verhältnis der wirksamen Kolbenflächen der Hydraulikzylinder und der Dickstoff-Förderzylinder zueinander ab.A variant of the invention in which the pilot valve 9 is electrically adjustable by remote control is shown in FIG Figure 5 shown. The pilot valve 9 is designed here as an electrically controlled proportional pressure limiting valve and is controlled by control electronics 23. The control electronics 23 measure the hydraulic drive pressure of the two-cylinder piston pump 2 by means of the pressure sensor 21 and derive the thick matter delivery pressure therefrom via the ratio of the effective piston areas of the hydraulic cylinders and the thick matter delivery cylinders to one another.

Mittels einer Bedieneinheit 22, die mit einer Tastatur und einem Bildschirm, wie dargestellt, oder beispielsweise auch mit einem Touchscreen ausgestattet ist, gibt der Bediener hier nur noch den gewünschten maximalen Förderdruck der Zwei-Zylinder-Kolbenpumpe 2 vor. Die Steuerelektronik 23 bestimmt aus dem vom Drucksensor 21 gemessenen Hydraulikdruck und dem vom Bediener vorgegebenen maximalen Dickstoffförderdruck, wie weiter oben schon beschrieben, bei blockierter Zwei-Zylinder-Kolbenpumpe 2 die richtige Einstellung des Vorsteuerventils 9 und stellt es über die Steuerleitung entsprechend ein. Anhand einer vorgegebenen, systemseitig abgespeicherten Ventilkennlinie, kann die Steuerelektronik 23 beispielsweise auch ohne die Blockierung der Zwei-Zylinder-Kolbenpumpe 2 das Vorsteuerventil 9 einstellen. Mit Hilfe des Drucksensors 21 kann die Einstellung kontrolliert und gegebenenfalls nachgeregelt werden.By means of an operating unit 22, which is equipped with a keyboard and a screen, as shown, or, for example, also with a touchscreen, the operator here only specifies the desired maximum delivery pressure of the two-cylinder piston pump 2. The control electronics 23 determine the correct setting of the pilot valve 9 from the hydraulic pressure measured by the pressure sensor 21 and the maximum thick matter delivery pressure specified by the operator, as already described above, when the two-cylinder piston pump 2 is blocked and adjusts it accordingly via the control line. On the basis of a predetermined valve characteristic stored in the system, the control electronics 23 can, for example, also set the pilot valve 9 without blocking the two-cylinder piston pump 2. With the aid of the pressure sensor 21, the setting can be checked and, if necessary, readjusted.

Mit dem in Figur 5 dargestellten Umschaltventil 11 kann bei Bedarf die voreingestellte ferngesteuerte Reduzierung des Grenzdrucks der Druckabschneidung einfach außer Kraft gesetzt werden. D.h. durch Betätigung des Umschaltventils 11 wird wieder der über das dritte Vorsteuerventil 10 vorgegebene maximale Systemdruck für die Druckabschneidung eingestellt, der in dem hier dargestellten Beispiel 20 bar unter dem Grenzdruck der vom Vorsteuerventil 7 und dem Druckbegrenzungsventil 5 definierten Grenzdruck liegt.With the in Figure 5 The switching valve 11 shown can, if necessary, simply override the preset remote-controlled reduction of the limit pressure of the pressure cut-off. That is, by actuating the switchover valve 11, the maximum system pressure for the pressure cut-off set via the third pilot valve 10 is set again, which in the example shown here is 20 bar below the limit pressure of the limit pressure defined by the pilot valve 7 and the pressure limiting valve 5.

BezuaszeichenlisteReference list

11
DickstoffpumpeThick matter pump
22
Zwei-Zylinder-KolbenpumpeTwo-cylinder piston pump
33
Hydraulikpumpehydraulic pump
44th
StellschieberControl slide
55
Druckbegrenzungsventil (Erfindung), 5a Druckbegrenzungseinheit (St.d.T)Pressure relief valve (invention), 5a pressure relief unit (St.d.T)
66
StellelementControl element
77th
zweites Vorsteuerventilsecond pilot valve
88th
AntriebleitungDrive line
99
erstes Vorsteuerventilfirst pilot valve
1010
drittes Vorsteuerventilthird pilot valve
1111
UmschaltventilChangeover valve
1212
Umschaltsteuerung (4/3 Wegeventil)Changeover control (4/3 way valve)
1313th
HandradHandwheel
1414th
HydraulikreservoirHydraulic reservoir
1515th
HauptstufeMain level
1616
MessanschlussMeasuring connection
1717th
DurchlasskanalPassage channel
1818th
Vorsteuerventil (St.d.T.)Pilot valve (St.d.T.)
1919th
Manometermanometer
2020th
DüsenNozzles
2121st
DrucksensorPressure sensor
2222nd
BedieneinheitControl unit
2323
SteuerelektronikControl electronics

Claims (10)

  1. High-density solids pump (1), comprising at least one hydraulically driven two-cylinder reciprocating pump (2) for generating a high-density solids delivery pressure, and a hydraulic pump (3) which supplies hydraulic fluid to the two-cylinder reciprocating pump (2) via a drive line (8), wherein the high-density solids delivery pressure is adjustably limited,
    characterised in that
    - the hydraulic pump (3) has pressure regulation that can be adjusted to a target pressure of the hydraulic fluid in order to limit the high-density solids delivery pressure, and
    - the pressure of the hydraulic fluid in the drive line (8) is limited to an adjustable maximum pressure by means of an adjustable pressure-limiting valve (5), wherein the target pressure for the pressure regulation and the maximum pressure of the hydraulic fluid can be adjusted by a common actuating element (6).
  2. High-density solids pump (1) according to claim 1, characterised in that the actuating element (6) is designed to adjust the target pressure for the pressure regulation and the maximum pressure of the hydraulic fluid in parallel, such that the maximum pressure is always above the target pressure by a predetermined differential pressure.
  3. High-density solids pump (1) according to claim 1 or 2, characterised in that the actuating element (6) comprises a first pilot valve (9) which can be adjusted to the target pressure of the hydraulic fluid and which is connected to an actuating slide (4) for the pressure regulation of the hydraulic pump (3) on the input side and is discharged into a hydraulic reservoir (14) on the output side, wherein the first pilot valve (9) opens once the target pressure is reached.
  4. High-density solids pump (1) according to claim 3, characterised in that the actuating element (6) comprises a second pilot valve (7) that is connected to the main stage (15) of the pressure-limiting valve (5) on the input side and to the input side of the first pilot valve (9) on the output side, wherein the second pilot valve (7) opens once the predetermined differential pressure between the input side and output side is reached.
  5. High-density solids pump (1) according to claim 4, characterised in that the second pilot valve (7) is not adjustable.
  6. High-density solids pump (1) according to any of claims 3 to 5, characterised in that the first pilot valve (9) is adjustable by means of a handwheel (13).
  7. High-density solids pump (1) according to claim 6, characterised in that the handwheel (13) can be fixed in position and/or locked.
  8. High-density solids pump (1) according to any of claims 3 to 7, characterised in that the actuating element (6) comprises a non-adjustable third pilot valve (10) that is connected in parallel with the first pilot valve (9) and opens once a maximum permissible pressure is reached.
  9. High-density solids pump (1) according to claim 8, characterised in that a switch valve (11) is connected upstream of the first pilot valve (9) such that the third pilot valve (10) is connected in parallel with the assembly of the first pilot valve (9) and the switch valve (11), wherein the switch valve (11) selectively establishes or disconnects the connection of the input side of the first pilot valve (9) to the actuating slide (4) of the pressure regulation.
  10. High-density solids pump (1) according to claim 9, characterised in that the switch valve (11) can be latched in position and/or locked.
EP17816475.2A 2016-11-21 2017-11-21 Viscous material pump with adjustable limitation of the delivery pressure Active EP3542060B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016122392.1A DE102016122392A1 (en) 2016-11-21 2016-11-21 Slurry pump with adjustable limitation of the delivery pressure
PCT/EP2017/079962 WO2018091747A1 (en) 2016-11-21 2017-11-21 Viscous material pump with adjustable limitation of the delivery pressure

Publications (2)

Publication Number Publication Date
EP3542060A1 EP3542060A1 (en) 2019-09-25
EP3542060B1 true EP3542060B1 (en) 2020-11-18

Family

ID=60702598

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17816475.2A Active EP3542060B1 (en) 2016-11-21 2017-11-21 Viscous material pump with adjustable limitation of the delivery pressure

Country Status (4)

Country Link
US (1) US11092143B2 (en)
EP (1) EP3542060B1 (en)
DE (1) DE102016122392A1 (en)
WO (1) WO2018091747A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019105817A1 (en) 2019-03-07 2020-09-10 Liebherr-Mischtechnik Gmbh Articulated arm control of a concrete pump
DE102019105871A1 (en) 2019-03-07 2020-09-10 Liebherr-Mischtechnik Gmbh Articulated arm control of a concrete pump
CN110701032A (en) * 2019-10-23 2020-01-17 徐州晟源环境科技有限公司 Constant-pressure constant-flow sludge pumping system

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3709504C2 (en) * 1987-03-23 1995-02-02 Rexroth Mannesmann Gmbh Valve device
DE3812753C2 (en) * 1988-04-16 1994-05-26 Rexroth Mannesmann Gmbh Valve arrangement for an adjustable pump
EP0411151B1 (en) * 1989-02-20 1994-07-06 Hitachi Construction Machinery Co., Ltd. Hydraulic circuit for working machines
DE19503986A1 (en) * 1995-02-07 1996-08-08 Hudelmaier Ulrike Method and device for conveying concrete or other thick materials
DE10040737A1 (en) 2000-08-17 2002-02-28 Mannesmann Rexroth Ag Valve arrangement for pressure medium supply hydraulic consumer has consumer pressure limitation valve with pilot valve unit
DE102005035981A1 (en) * 2005-07-28 2007-02-01 Putzmeister Ag Hydraulic circuit arrangement, in particular for the drive of concrete distributor masts
DE102012216242A1 (en) 2012-09-13 2014-03-13 Putzmeister Engineering Gmbh Device for drive control of a two-cylinder slurry pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102016122392A1 (en) 2018-05-24
WO2018091747A1 (en) 2018-05-24
EP3542060A1 (en) 2019-09-25
US20190309737A1 (en) 2019-10-10
US11092143B2 (en) 2021-08-17

Similar Documents

Publication Publication Date Title
EP1915538B1 (en) Circuit for controlling a double-action hydraulic drive cylinder
EP1092095B2 (en) Hydraulic circuit
EP1907706B1 (en) Hydraulic circuit arrangement, in particular for the drive of concrete distributor masts
EP3542060B1 (en) Viscous material pump with adjustable limitation of the delivery pressure
DE2343832B2 (en) Load detection and pressure limiting device for pressure medium-operated equipment
DE102012010266B4 (en) Hydraulic circuit arrangement
EP2767353A1 (en) Cooling section with power cooling and laminar cooling
EP0935713A1 (en) Valve system and manufacture of same
EP2444360B1 (en) Load-sensing regulated hydrostatic drive system
EP2404493B1 (en) Hoisting gear
EP0471166B1 (en) Control apparatus for regulating the delivery flow rate setting of several hydrostatic adjustable pumps
DE10219718B4 (en) Hydraulic valve arrangement
DE102017202899B4 (en) Control system for a hydraulic variable displacement pump, pump unit and hydraulic system with one pump unit
EP0346352B1 (en) Hydraulic device with regulable pump
EP1502027A1 (en) Regulatory device comprising a threshold value control valve
EP2251550B1 (en) mobile construction machine with a hydraulic system
EP3135924B1 (en) Hydraulic device
DE3844405C2 (en) Valve arrangement for a hydraulic system
DE10214225C1 (en) Hydraulic operating unit control method uses characteristic fields for hydrotransformers incorporated in hydraulic circuit as input values for movement control unit for hydraulic cylinder
DE3844399C2 (en) Control arrangement for several independently operable hydraulic consumers and their use
DE102009019068B4 (en) pressure monitoring circuit
DE3711050C2 (en)
EP3244072A1 (en) Hydrostatic valve assembly and hydrostatic lifting device with the valve assembly
DE102016123504B4 (en) Hydraulic valve section, connection section and hydraulic valve assembly as well as commercial vehicles with one
EP1515049B1 (en) Hydraulic control

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20190621

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

DAV Request for validation of the european patent (deleted)
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

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20200528

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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: 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: 502017008307

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1336065

Country of ref document: AT

Kind code of ref document: T

Effective date: 20201215

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20201118

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: 20201118

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: 20210318

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: 20201118

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: 20210219

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: 20210218

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20210218

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: 20201118

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: 20210318

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: 20201118

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: 20201118

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20201118

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20201118

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: 20201118

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: 20201118

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: 20201118

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: 20201118

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: 20201118

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201121

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20201130

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502017008307

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

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: 20201118

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: 20201118

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

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

26N No opposition filed

Effective date: 20210819

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20201118

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: 20201118

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201121

Ref country code: IT

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: 20201118

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: 20201118

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20201118

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20210318

Ref country code: TR

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: 20201118

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: 20201118

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: 20201118

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: 20201118

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: 20201130

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20231108

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1336065

Country of ref document: AT

Kind code of ref document: T

Effective date: 20221121

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20231121

Year of fee payment: 7

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: 20221121

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20231123

Year of fee payment: 7

Ref country code: DE

Payment date: 20231127

Year of fee payment: 7