EP2118501A1 - Procédé de détermination automatique de l'état d'un groupe hydraulique - Google Patents

Procédé de détermination automatique de l'état d'un groupe hydraulique

Info

Publication number
EP2118501A1
EP2118501A1 EP08701388A EP08701388A EP2118501A1 EP 2118501 A1 EP2118501 A1 EP 2118501A1 EP 08701388 A EP08701388 A EP 08701388A EP 08701388 A EP08701388 A EP 08701388A EP 2118501 A1 EP2118501 A1 EP 2118501A1
Authority
EP
European Patent Office
Prior art keywords
wear
pressure
hydraulic
unit
load
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08701388A
Other languages
German (de)
English (en)
Other versions
EP2118501B1 (fr
Inventor
Bernd Thelen
Paul-Heinz Wagner
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.)
Wagner Vermoegensverwaltungs GmbH and Co KG
Original Assignee
Wagner Vermoegensverwaltungs GmbH and Co KG
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 Wagner Vermoegensverwaltungs GmbH and Co KG filed Critical Wagner Vermoegensverwaltungs GmbH and Co KG
Priority to PL08701388T priority Critical patent/PL2118501T3/pl
Publication of EP2118501A1 publication Critical patent/EP2118501A1/fr
Application granted granted Critical
Publication of EP2118501B1 publication Critical patent/EP2118501B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
    • F15B19/005—Fault detection or monitoring
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/004—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type
    • B25B21/005—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type driven by a radially acting hydraulic or pneumatic piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/16—Wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/80—Diagnostics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/86—Detection

Definitions

  • the invention relates to a method for automatically determining the state of a hydraulic unit for supplying a hydraulic cylinder for performing load strokes.
  • DE 10 2004 017979 A1 describes a method for the angle-controlled turning of a part, in which a hydraulic unit supplies a pressure for the hydraulic cylinder of a power wrench.
  • the hydraulic unit is provided with a control device which switches over a control valve as a function of the pressure generated.
  • the pressure increases at each load stroke initially with a higher pitch and then with a lower slope until the end stop of the hydraulic cylinder is reached.
  • the maintenance is carried out at regular time intervals or after a certain number of operating hours of the device.
  • Such interva 11 specific fixing of maintenance works only to a small extent on the actual workload of the device. Thus, it is disregarded whether the hydraulic implement has performed only light strokes or possibly was operated up to the load limit.
  • Condition Monitoring For complex systems that are subject to different load conditions, Condition Monitoring has been developed to determine the state of the system in order to avoid system failures. The state determined indicates how far away the monitored system is from a fault or failure that can be expected soon This enables early detection of creeping system changes and limitation of causes.Condition monitoring enables condition-based plant maintenance and replaces the previous preventive maintenance that has been maintained at fixed maintenance intervals In addition, the possibility of online status diagnostics.
  • the invention has for its object to provide a method for automatically determining the state of a hydraulic power unit, which allows a realistic state determination.
  • a wear-determining characteristic number is calculated for at least one unit component from the pressure of the duration of operation since start-up, that a degree of wear is determined from the characteristic number and a wear limit defined for the unit component and that for the entire unit under the Wear levels of all aggregate components determines the maximum and from this a total degree of wear is formed.
  • the magnitude of the resulting pressure provides information about the applied power, from which, in conjunction with the duration of the load stroke, the work or an associated quantity can be determined.
  • the method thus distinguishes the load strokes according to the resistance that was opposed to them. Therefore, heavy load strokes are rated higher than smooth load strokes.
  • the inventive method is particularly suitable for hydraulic units for operating hydraulic power Schauber for tightening screws, nuts and similar rotatable parts.
  • the pressure which arises during a load stroke depends on the resistance which the part of the rotation to be rotated opposes.
  • the degree of wear indicates the accumulated workload. This means that, since the last maintenance, all the operations performed on the hydraulic unit will increase the degree of wear, depending on the work done.
  • a heavy-duty hydraulic power unit reaches the upper limit, the wear limit, earlier than a hydraulic power-limited unit, with the same number of operating hours.
  • the degree of wear is to a certain extent a measure of the device's "fatigue level.”
  • the degree of wear can be used to calculate the number of operating hours remaining until the next maintenance operation, which is automatically calculated in the control unit of the hydraulic power unit
  • the average weight of the previous workload shall be used as a basis for the work to be carried out in the future.
  • the time integral of the pressure is formed for the ratio.
  • a simplified embodiment provides that the pressure and the duration of a load stroke are processed as parameters for the determination or further development of the degree of wear.
  • the pressure and the duration of a load stroke are processed as parameters for the determination or further development of the state variable. This may conveniently be done so that the product of pressure and duration is formed to obtain a load size of the respective load stroke. To this load size of the previous accumulated degree of wear is increased.
  • Pressure and duration of the load strokes are not necessarily the only parameters that influence the state quantity.
  • the extraction of the state variable can also include the number of load strokes or the temperature of the hydraulic medium.
  • the type of involvement can be done in different ways. For example, each parameter may be weighted.
  • the signals from sensors which display error messages can also be included in the extraction of the state variable. For example, the frequent exceeding of a limit temperature would lead to an unscheduled increase in the state quantity. It is also possible to measure the operating time of the hydraulic unit below and above a limit temperature. An example of this is: The hydraulic power unit has run for 50 hours, of which 30 hours are above 50 ° C.
  • the invention further relates to a hydraulic unit for supplying a hydraulic cylinder for performing load strokes according to claim 7.
  • the hydraulic power unit can acquire and store other monitored parameters, such as the number of operating hours from the beginning and last servicing, the product of operating time, current and voltage of the motor as electrical work, the product of operating time of the motor, pressure and volumetric flow as hydraulic work, the product of temperature and time, the current peak value, the voltage peak and / or the minimum voltage value, the temperature peak value, the pressure peak value as well as the product of volume flow and time to determine the accumulated pumped volume.
  • a self-test of the hydraulic unit In addition to the state determination, other functions may be provided, such as a self-test of the hydraulic unit.
  • the two hoses flow and return are connected and the maximum pressure is set to a predetermined value, for. B. 400 bar, set. Due to the elasticity of the tubes sealed at the ends, the pressure builds up linearly with time, according to a reference curve that is recorded or stored. Then it is checked whether the measured Kurzve has the predetermined course of the reference curve.
  • a diagnostic connector can be plugged into the control unit to read out wear-relevant data or the entire device history. In this way, the state of the unit is available at any time. The fault diagnosis is facilitated because the device caches critical conditions.
  • a networking of the controller with the Internet or another data network is possible.
  • the data from the aggregate transmitted daily to a maintenance server.
  • Parameter adjustments can be stored on the maintenance server and automatically programmed at the next diagnosis.
  • FIG. 1 shows a schematic embodiment of a screwing device with a hydraulic unit and a power screwdriver for rotating a screw
  • Fig. 2 is a schematic representation of the power wrench
  • Piston cylinder drive contains,
  • Fig. 3 is a view of the entire hydraulic unit including
  • a power wrench 10 is shown schematically.
  • This has a hydraulic piston-cylinder drive 11 with a hydraulic cylinder 12 and a piston 13 movable therein.
  • the piston is connected to a piston rod 14, and the end of the piston rod engages a lever 15 which engages with a latching pawl 15a on the toothing of a ratchet wheel 17.
  • the ratchet wheel 17 is part of a ring piece 18, which has a socket 19 for inserting a key nut or a screw head to be rotated. By reciprocating movement of the piston 13, the ring piece 18 is rotated, and with this the screw.
  • the Ring piece 18 is mounted in a housing 20 which also contains the piston cylinder drive 11.
  • the pressure for the piston-cylinder drive 11 is supplied by the hydraulic unit 25 shown in FIG. 1, which has a positive displacement pump 26, e.g. B. includes a gear pump, a speed-controlled synchronous motor and a tank.
  • the motor drives the pump 26.
  • the hydraulic unit 25 is connected to a pressure line 28 and a return line 29. These two lines are connected via a control valve 30 to the piston-cylinder drive 11. By switching the control valve 30, the piston 13 can be moved either forward or backward.
  • control unit 31 For controlling the hydraulic unit 25 and the control valve 30, the control unit 31 is provided. This includes a frequency converter that generates a variable drive frequency for the motor. The control unit 31 thus determines the speed of the pump 26. The pump speed determines the volume flow, which is the pressure line 28 is supplied.
  • a pressure sensor 32 is provided which measures the hydraulic pressure p in the pressure line.
  • the pressure sensor is connected via a line 33 to the control unit 31.
  • the hydraulic unit 25 has a housing 35 containing the hydraulic oil.
  • a pump is housed, which is designed as a submersible pump and the pressure for the hose system 28, 29 generates. It is a volumetric pump of a gear pump or more, distributed pump segments, which are driven by a motor.
  • an adjustable pressure relief valve 36 and a shoulder 37 for the tubes 28 and 29 At the front end of the housing 35 is an adjustable pressure relief valve 36 and a shoulder 37 for the tubes 28 and 29. There is also the pressure sensor 32 for the pressure line 28 is provided. Another pressure sensor is provided for the return line 29.
  • the control unit 31 has a housing, in the top of which a display 40 is arranged.
  • the housing is connected to a remote control 41, with which a manual control of the control valve 30 can take place.
  • the programming unit 42 which forms a user interface with the keyboard and the display, can be connected to the control unit.
  • FIG. 4 shows the course of the pressure p over the time ⁇ at several successive load strokes of the power shifter. It is the pressure that is measured by the pressure sensor 32.
  • FIG. 4 shows the load strokes LH1-LH4 of the piston.
  • Each load stroke has an initial section 45, in which a relatively steep increase in pressure takes place to overcome the friction or to reach the state in which the preceding load stroke has been completed.
  • the piston 13 At the end of the load stroke, the piston 13 abuts against the front stop of the cylinder (FIG. 2). This creates a steep pressure build-up represented by section 47.
  • a sloping section 48 in which the return stroke of the piston takes place and the pressure p goes back to 0.
  • the height of the resulting pressure is determined and stored at each load stroke. This is the pressure p of section 47 at the switchover from the load stroke to the return stroke takes place.
  • the level of pressure reached is a parameter for determining the workload.
  • Another parameter for determining the workload is the duration of the load stroke. In this case, the duration from the beginning of the starting section 45 to the end of the section 46 can be evaluated. However, it is also possible to evaluate only the duration of section 46 or to include the duration of section 48, which represents the return stroke. Preferably, the duration of the two sections 45 and 46 is evaluated.
  • the control unit 31 forms the product of the pressure level and duration of the load stroke and sums the products thus formed from load stroke to load stroke, so that a state variable is obtained which indicates the wear. If this state variable has reached a predetermined value, a maintenance or inspection is due. The difference between the wear limit and the instantaneous value can be displayed to determine the proximity of the upcoming maintenance time.
  • the described extraction of the state quantity indicating the accumulated workload is not necessarily the sole criterion for determining the time of the next maintenance. Regardless of the accumulated workload, the number of load strokes may represent an alternative or additional criterion. Other criteria, such as As the temperature of the hydraulic medium can be used to perform an emergency shutdown or included in the state determination, for example, by load strokes, in which the temperature exceeds a threshold, receive an additional weighting.
  • FIGS. 1-4 A second embodiment of the invention will be described below, reference being also made to FIGS. 1-4. From the actual load of the hydraulic power pack, parameters are calculated that allow conclusions to be drawn about the (wear) condition of individual power unit components. For this purpose, the pressure-time characteristic curve (FIG. 4) recorded during screwing is essentially consulted, possibly also with oil temperature and further measured data acquired continuously.
  • the pressure-time characteristic curve contains the data relevant to the wear of the unit, regardless of the periphery used for the screw connection (hoses, hydraulic drives, screwdrivers %) and regardless of the screwdriving cases (torque, friction torque, inclination ).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)

Abstract

La présente invention concerne un groupe hydraulique servant à alimenter un vérin hydraulique en levées de charge (LHl, LH2,LH3, LH4) consécutives, dont la charge de travail est surveillée afin de provoquer une détermination automatique de l'état du groupe. A cet effet, l'intégrale de temps de pression est déterminée à chaque levée de charge. La pression et la durée sont traitées pour former un chiffre clé qui indique l'usure. A tout moment, un diagnostic de l'état du groupe hydraulique est possible par là-même.
EP08701388.4A 2007-01-12 2008-01-10 Procédé de détermination automatique de l'état d'un groupe hydraulique Active EP2118501B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL08701388T PL2118501T3 (pl) 2007-01-12 2008-01-10 Sposób automatycznego określania stanu agregatu hydraulicznego

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007001922A DE102007001922A1 (de) 2007-01-12 2007-01-12 Verfahren zur automatischen Zustandsbestimmung eines Hydraulikaggregates
PCT/EP2008/050240 WO2008084077A1 (fr) 2007-01-12 2008-01-10 Procédé de détermination automatique de l'état d'un groupe hydraulique

Publications (2)

Publication Number Publication Date
EP2118501A1 true EP2118501A1 (fr) 2009-11-18
EP2118501B1 EP2118501B1 (fr) 2016-01-06

Family

ID=39259515

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08701388.4A Active EP2118501B1 (fr) 2007-01-12 2008-01-10 Procédé de détermination automatique de l'état d'un groupe hydraulique

Country Status (6)

Country Link
US (1) US8370083B2 (fr)
EP (1) EP2118501B1 (fr)
JP (1) JP2010515588A (fr)
DE (1) DE102007001922A1 (fr)
PL (1) PL2118501T3 (fr)
WO (1) WO2008084077A1 (fr)

Families Citing this family (6)

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Publication number Priority date Publication date Assignee Title
US10240593B2 (en) * 2011-03-04 2019-03-26 Asco Power Technologies, L.P. Systems and methods of controlling pressure maintenance pumps and data logging pump operations
DE102014101714A1 (de) * 2014-02-12 2015-08-13 Juko Technik Gmbh Multifunktionales Hydraulikaggregat
CN107654361B (zh) * 2017-10-24 2023-05-26 吉林大学 用于手电泵的一体化检测的设备
US10837472B2 (en) 2018-02-22 2020-11-17 Caterpillar Inc. Hydraulic cylinder health monitoring and remaining life system
EP3653888B1 (fr) 2018-11-13 2023-01-25 Enerpac Tool Group Corp. Système d'alimentation hydraulique et son procédé de commande
USD1042067S1 (en) * 2023-02-28 2024-09-17 Primesource Consulting Llc Limited clearance tool

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Also Published As

Publication number Publication date
PL2118501T3 (pl) 2016-06-30
WO2008084077A1 (fr) 2008-07-17
DE102007001922A1 (de) 2008-07-17
US8370083B2 (en) 2013-02-05
US20100293933A1 (en) 2010-11-25
EP2118501B1 (fr) 2016-01-06
JP2010515588A (ja) 2010-05-13

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