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
  • F04B51/00—Testing machines, pumps, or pumping installations
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
  • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/06—Control using electricity
  • F04B49/065—Control using electricity and making use of computers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
  • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
  • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
  • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
  • F04B9/111—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 with two mechanically connected pumping members
  • F04B9/113—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 with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B2201/00—Pump parameters
  • F04B2201/02—Piston parameters
  • F04B2201/0202—Linear speed of the piston
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • 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
  • F04B49/10—Other safety measures
  • F04B49/103—Responsive to speed

Definitions

• the invention relates to a method for monitoring the condition of a device, in particular for conveying thick matter, and to a device, in particular for conveying thick matter.
• the invention is based on the object of providing a method for monitoring the status of a device, in particular for conveying thick matter, and a device, in particular for conveying thick matter, which enable reliable status detection.
• the inventive method is used to monitor the condition of a device, in particular special for the promotion of thick matter, for example in the form of liquid concrete.
• the device can for example be a concrete pump.
• the device has a conventional first drive cylinder for receiving hydraulic fluid, for example in the form of hydraulic oil.
• the device also has a conventional first drive piston, which is movably, in particular longitudinally moveable, arranged in the first drive cylinder.
• the procedure has the following steps.
• the determined speed can be the instantaneous speed of the drive piston, which can for example be determined continuously or can only be determined at certain positions / positions of the drive piston.
• a speed profile of the first drive piston can also be determined.
• the first speed can be determined, for example, by means of a conventional displacement measuring system, by means of which a position of the first drive piston can be determined.
• the first speed can then be calculated by deriving the determined position over time.
• the first speed can also be determined based on a stroke time between two defined points of the drive cylinder.
• the expected speed is, for example, the speed that the first drive piston takes should theoretically have fault-free function, especially at a given position.
• the expected speed can be determined, for example, with knowledge of the properties of the device, such as piston gear drives, cylinder geometries, known or measured drive volume flows, etc., or is known a priori.
• Determining a fault condition of the device or of components of the device as a function of the difference formed or of an amount of the difference formed between the determined speed of the first drive piston and the expected speed of the first drive piston.
• the stroke time and / or the change in the stroke time in comparison to the respectively expected values can serve as an error criterion.
• the first drive piston and the first delivery piston each perform a purely translatory, oscillating movement with a specific stroke.
• the error state is determined when the difference between the determined speed of the first drive piston and the expected speed of the first drive piston exceeds an associated amount. Alternatively or additionally, the error state is determined if a change over time or derivation of the difference between the determined speed of the first drive piston and the expected speed of the first drive piston exceeds an associated amount.
• the respective dimension can be an absolute value or a relative value.
• the fault condition can be determined if the difference between the speed of the first drive piston determined and the expected speed of the first drive piston exceeds a predetermined percentage of the expected speed or the measured speed.
• the specified percentage value can, for example, be in a range between 0.1% and 10% of the expected speed or the measured speed.
• the error state can be determined if the change over time or derivation of the difference between the determined speed of the first drive piston and the expected speed of the first drive piston per unit of time, for example 60 seconds, a predetermined percentage of the expected speed or the measured speed exceeds.
• the given Percentage value can, for example, be in a range between 0.1% and 10% of the expected speed or the measured speed.
• the device further has a conventional drive pump which is designed to generate a drive volume flow of hydraulic fluid for moving the first drive piston in the first drive cylinder.
• a conventional drive pump which is designed to generate a drive volume flow of hydraulic fluid for moving the first drive piston in the first drive cylinder.
• the expected speed is then calculated as a function of the drive volume flow generated, with typical geometries and associated volumes of the hydraulic circuit being taken into account.
• the device is a device for conveying thick matter and further comprises: a conventional first conveying cylinder for receiving and dispensing thick matter, a conventional first conveying piston which is movably, in particular longitudinally movable, arranged in the first conveying cylinder, a conventional first Piston rod, which is attached to the first drive piston and to the delivery piston for coupling the movement of the first drive piston and the first delivery piston, a piston seal which in the de fect-free or intended state in connection with the first drive piston has a first volume or a volume on the drive pump side the first drive cylinder with respect to a second volume or a swing volume in the first drive cylinder seals, and a rod seal which, in conjunction with the first piston rod, seals the first drive cylinder from the surroundings of the device.
• the error condition is determined in the form of a defect in the piston seal and / or in the form of a de fect of the rod seal depending on the difference formed between the speed of the first drive piston determined and the expected speed of the first drive
• the method has the following further steps: Bringing a drive pump-side drive volume flow and determining the fault condition in the form of the defect in the piston seal during the introduction of the drive pump-side drive volume flow as a function of the difference formed between the determined speed of the first drive piston and the expected speed of the first drive piston.
• the method has the following further steps: Bringing a swing volume-side drive volume flow and determining the fault condition in the form of the defect in the rod seal while the swing volume-side drive volume flow is being brought in, depending on the difference formed between the determined speed of the first drive piston and the expected speed of the first drive piston.
• the device for conveying thick matter further comprises: a second drive cylinder for receiving hydraulic fluid, a second drive piston which is movably arranged in the second drive cylinder, a second delivery cylinder for receiving and dispensing thick matter, a second delivery piston, which is movably arranged in the second feed cylinder, and a second piston rod which is attached to the second drive piston and to the second feed piston for coupling the movement of the second drive piston and the second feed piston.
• the first drive piston in the first drive cylinder delimits a first volume or a volume on the drive pump side from a second volume or swing volume.
• the second drive piston in the second drive cylinder delimits a first volume or volume on the drive pump side from a second volume or swing volume.
• the swing volume in the first drive cylinder and the swing volume in the second drive cylinder are connected to each other via a swing connection for exchanging hydraulic fluid in such a way that the first drive piston moves in phase opposition to the second drive piston.
• the speed of the second drive piston is determined, the expected speed of the first drive piston being equal to the determined speed of the second drive piston.
• the determined speed of the first drive piston is compared with the determined speed of the second drive piston, the error state being determined if the determined speeds differ from one another by more than a predetermined amount or if the temporal change in the difference in the determined speeds occurs exceeds the specified dimension. If wear on the piston or rod seals can be ruled out, a fault / wear in the remaining hydraulic system (in particular the hydraulic pumps) can also be detected in the event of a deviation in the piston speeds.
• hydraulic fluid is fed to or from a swing volume.
• the swing volume is formed from the swing volume in the first drive cylinder, the swing volume in the second drive cylinder and a volume of the swing connection.
• the supply or discharge takes place in such a way that a possible or maximum stroke of an oscillating movement of the first drive piston and the second drive piston has a desired dimension.
• the swing connection has the effect that the first drive cylinder and the second drive cylinder execute oscillating movements in phase opposition to one another, the maximum stroke of which depends on the swing volume.
• the stroke can consequently be adjusted by changing the rocking volume.
• the error state is determined when a frequency of feeding or discharging exceeds a predetermined level.
• the specified measure for the frequency can be determined empirically, for example, by test series. For example, frequencies less than or equal to 1 feeding or discharging per hour can be defined as error-free and frequencies higher than 1 feeding or discharging per hour can be defined as faulty.
• an error state of the device can be determined if a change over time or derivation of the frequency of feeding or discharging exceeds a predetermined amount. For example, an error state of the device can be determined if the change over time in the frequency of feeding or discharging per unit of time, for example 60 seconds, exceeds a predetermined percentage value of the expected frequency or the measured frequency. The given percentage value can for example be in a range between 0.1% and 10% of the expected frequency or the measured frequency.
• a fault condition of the device can be determined if a volume fed in or fed out exceeds a predetermined level. The specified measure for the volume can be determined empirically by test series, for example.
• the device in particular for conveying thick matter, as described above, is designed to carry out the method described above.
• FIG. 1 shows a device according to the invention for conveying thick matter.
• Fig. 1 shows a device 1 according to the invention for conveying thick matter DS.
• the Vorrich device 1 can embody a concrete pump, for example.
• the device 1 has a first drive cylinder 10a for receiving hydraulic fluid HF.
• the device 1 also has a first drive piston 11a, which is arranged in the first drive cylinder 10a such that it can move longitudinally.
• the device 1 also has a first delivery cylinder 12a for receiving and dispensing thick matter DS in the form of liquid concrete.
• the device 1 further has a first delivery piston 13a which is arranged in the first delivery cylinder 12a so as to be longitudinally movable.
• the device 1 also has a first piston rod 14a, which is attached to the first drive piston 11a for movement coupling with the first delivery piston 13a.
• the device 1 also has a second drive cylinder 10b for receiving hydraulic fluid HF.
• the device 1 further has a second drive piston 11b, which is arranged in the second drive cylinder 10b to be longitudinally movable.
• the device 1 also has a second conveying cylinder 12b for receiving and discharging thick matter DS.
• the device 1 also has a second delivery piston 13b, which is arranged in the second delivery cylinder 12b such that it can move longitudinally.
• the device 1 also has a second piston rod 14b, which is attached to the second drive piston 11b for movement coupling with the second delivery piston 13b.
• the first drive piston 11a in the first drive cylinder 10a delimits a drive pump-side volume V1 from a swing volume V2.
• the second drive piston 10b in the second drive cylinder 10b delimits a drive pump-side volume V1 from a swing volume V2.
• the swing volume V2 in the first drive cylinder 10a and the swing volume V2 in the second drive cylinder 10b are connected via a swing connection 60 for exchanging hydraulic fluid HF in such a way that the first drive piston 11a moves in phase opposition to the second drive piston 11b.
• the device 1 also has piston seals 15 which, in a defect-free state, in conjunction with the first drive piston 11a and the second drive piston 11b, seal the volumes V1 on the drive pump side with respect to the rocking volumes V2.
• Rod seals 16 are also provided which, in conjunction with the first piston rod 14a and the second piston rod 14b, seal the first drive cylinder 10a and the second drive cylinder 10b from an environment.
• the device 1 further has a drive pump 20 which is designed to generate the drive volume flow AVF of the hydraulic fluid HF.
• the drive pump 20 is connected via pump connections 30a and 30b to the volumes V1 on the drive pump side for moving the first drive piston 11a in the first drive cylinder 10a or for moving the second drive piston 11b in the second drive cylinder 10b.
• the drive pump 20 can optionally feed a drive volume flow AVF either via the pump connection 30a or the pump connection 30b, so that either the first drive piston 11a or the second drive piston 11b moves to the right, the other drive piston then moving over due to the coupling the swing link 60 moves to the left.
• the drive pump 20 is controlled in such a way that the drive piston 11a or 11b driven via the active pump connection 30a or 30b moves to the right as far as a desired reversal point. Because of the rocking connection, the other drive piston 11a or 11b then moves to the left as far as an opposite reversal point.
• the first drive piston 11a and the second drive piston 11b therefore each perform a purely translatory movement that oscillates between two reversal points.
• Associated position sensors 17a and 17b are provided for detecting the position of the drive cylinders 10a and 10b.
• the respective instantaneous speed of the first drive piston 11a or of the second drive piston 11b is determined via a time derivative of the piston positions detected by means of the position sensors 17a and 17b.
• a control unit 50 controls the operation of the device 1.
• a speed of the first drive piston 11a and / or the second drive piston 11a is determined by means of the position sensors 17a and 17b, then a difference between the determined speed or speeds of the first drive piston 11a and / or the second drive piston 11b and an expected speed of the first is determined Drive piston 11a and / or the second drive piston 11b formed, and finally a fault condition determined as a function of the difference or differences formed.
• the error state can be determined if the difference between the determined speed and the expected speed exceeds an associated amount. and / or if a change over time in the difference between the determined speed and the expected speed exceeds an associated measure.
• the expected speed can for example be calculated as a function of the generated drive volume flow AVF.
• the expected speed of one of the two drive pistons 11a or 11b can also correspond to the measured speed of the other drive piston 11a or 11b.
• the determined speed of the first drive piston 11a is compared with the determined speed of the second drive piston 11b, the error condition being determined if the determined speeds differ by more than a predetermined amount, or if the change over time in the difference determined speeds exceeds a specified level.
• the fault condition can correspond to a defect in the piston seal (s) 15 and / or a defect in the rod seal (s) 16.
• a defect in the piston seal (s) during the introduction of the drive volume flow AVF on the drive pump side can be determined as a function of the difference formed between the determined speed and the expected speed.
• a defect in the rod seal (s) 15 can accordingly be determined during the introduction of the swing volume-side drive volume flow AVF as a function of the difference formed between the determined speed and the expected speed.
• a swing volume can be created from the swing volume V2 in the first drive cylinder 10a, the swing volume V2 is formed in the second drive cylinder 10b and a volume of the swing connection 60, the stroke can be adjusted.
• the feeding or discharging of hydraulic fluid HF into the swing volume can take place by means of conventional components that are known from the prior art. These components are provided with the reference symbol 18 by way of example.
• an error state can be determined if a frequency of feeding or discharging and / or a fed or discharged volume exceeds a predetermined level.
• the device can of course have other components known from the prior art, for example switching means for connecting the feed cylinders 12a and 12b to a thick matter feed line or source of thick matter, etc. Since these components are well known, their description is omitted.
• the method according to the invention for status or wear detection can be supplemented by taking into account further variables, for example a hydraulic pressure and / or a temperature of the hydraulic fluid.
• further variables for example a hydraulic pressure and / or a temperature of the hydraulic fluid.
• a history of the measured variables can be evaluated.
• the invention makes it possible to determine wear of components of the device 1 and thus to warn of failure of the component or to prevent it. This increases the availability of the device 1, since a required service can be planned in a targeted manner. In addition, the automated localization of wear can also significantly reduce service costs.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Computer Hardware Design (AREA)
• Control Of Positive-Displacement Pumps (AREA)
• Reciprocating Pumps (AREA)
• Fluid-Pressure Circuits (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=72234824

Family Applications (1)

Country Status (7)

Families Citing this family (2)

Family Cites Families (23)

• 2019
  • 2019-08-22 DE DE102019212631.6A patent/DE102019212631A1/de active Pending
• 2020
  • 2020-08-20 WO PCT/EP2020/073337 patent/WO2021032838A1/de unknown
  • 2020-08-20 CN CN202080059376.3A patent/CN114222860B/zh active Active
  • 2020-08-20 KR KR1020227005832A patent/KR20220047286A/ko not_active Application Discontinuation
  • 2020-08-20 EP EP20761183.1A patent/EP4018093A1/de active Pending
  • 2020-08-20 JP JP2022511293A patent/JP7522184B2/ja active Active
  • 2020-08-20 US US17/637,351 patent/US11959469B2/en active Active

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