EP0486898A1 - Procédé et dispositif pour ajustage des caractéristiques de travail d'un mécanisme à coup à la dureté des materiaux à broyer - Google Patents

Procédé et dispositif pour ajustage des caractéristiques de travail d'un mécanisme à coup à la dureté des materiaux à broyer Download PDF

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Publication number
EP0486898A1
EP0486898A1 EP91119042A EP91119042A EP0486898A1 EP 0486898 A1 EP0486898 A1 EP 0486898A1 EP 91119042 A EP91119042 A EP 91119042A EP 91119042 A EP91119042 A EP 91119042A EP 0486898 A1 EP0486898 A1 EP 0486898A1
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EP
European Patent Office
Prior art keywords
stroke
limit value
measured variable
impact
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP91119042A
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German (de)
English (en)
Other versions
EP0486898B1 (fr
Inventor
Friedrich Karl Dr.-Ing. Arndt
Robert-Jan Dr.-Ing. Bartels
Heribert Vielhaber
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.)
SIG Plastics GmbH and Co KG
Original Assignee
Krupp Maschinentechnik 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 Krupp Maschinentechnik GmbH filed Critical Krupp Maschinentechnik GmbH
Publication of EP0486898A1 publication Critical patent/EP0486898A1/fr
Application granted granted Critical
Publication of EP0486898B1 publication Critical patent/EP0486898B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
    • E02F3/966—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements of hammer-type tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof

Definitions

  • the invention relates to a method for adapting the working behavior of an impact mechanism, also with stroke adjustment, the impact piston of which performs reciprocating movements under the action of the hydraulic drive means supplied by a conveying unit, to the hardness of the comminution material and a device suitable for carrying out the adaptation method.
  • Hydraulically operated striking mechanisms form a chain of action with the conveyor unit on one side and the tool (in particular chisel) with the comminution material on the other side, through which an energy flow flows in both directions.
  • the primary energy flow is directed from the conveyor unit via the striking mechanism and the tool to the comminution material (in particular rock); the secondary energy flow reflected by the shredding material acts via the striking mechanism to the conveyor unit.
  • the properties of the shredding material and the tool are expressed by the reflection factor R, which is an indirectly measurable quantity and is defined by the ratio of primary impact energy / reflected impact energy.
  • the energy balance and the Impact characteristics ie the ratio of impact number to single impact energy of an impact mechanism.
  • the working behavior of a striking mechanism should be adapted in such a way that the individual impact energy increases with increasing material hardness, that is to say with increasing size of the reflection factor.
  • a single impact energy which is too low leads to undesired reflections, with the result that only a low comminution performance can be achieved with high tool and impact mechanism stress.
  • the invention is based on the object of developing a method and a device for hydraulically operated percussion mechanisms for automatically adapting the working behavior to the hardness of the comminution material, the essential and sensitive components (in particular sensors and controllers) of which can optionally also be arranged independently of the percussion mechanism, are therefore reliable and easy to repair and can be used on differently designed striking mechanisms.
  • the method and the device should be such that the individual impact energy required for material shredding is automatically adapted to the changing hardness of the shredding material. If, due to the design, it is not possible to adapt the individual impact energy, the impact energy recovered by reflection processes should be prevented from causing an undesirable increase in the number of percussion pistons.
  • the invention preferably comes from striking mechanisms with (the aforementioned) energy recovery for use (described in EP publication 0 183 093). This version assumes that the percussion piston is temporarily connected to the pressure line with the operating pressure after the impact during the return stroke.
  • the object is achieved by a method which has the features of claim 1.
  • the basic idea of the invention is to build up the control for adapting the working behavior by at least one measuring operation outside the striking mechanism on the measured variable percussion piston stroke number or the measured variables of percussion piston stroke number and input quantity flow into the striking mechanism to convert and use the internal resistance of one of the two interacting working units, namely the conveyor unit or the striking mechanism: If the number of impacts or a performance parameter formed from the measured quantity of the number of impacts and the input flow rate to an adjustable limit value, the internal resistance of one of the two working units is increased . With striking mechanisms with a non-adjustable stroke, this change causes the number of strokes to be reduced.
  • the invention makes use of the knowledge known per se that the impact rate of a percussion mechanism changes with the properties of the comminution material, that is to say increases with increasing size of the reflection factor, and that the ratio of impact rate and input flow rate also increases with the size of the reflection factor.
  • the quantities to be measured i.e. the number of blows and, if necessary, additionally the input flow into the striking mechanism, can be detected by means of sensors known per se as part of a sound wave or vibration measurement or a flow measurement influenced by the number of blows and converted into a control command.
  • the internal resistance of the percussion mechanism can be increased by changing the pressure in the return line (return resistance) against which the percussion piston executes the return stroke (claim 2);
  • a throttle valve which defines the cross section of the return line is adjusted on the basis of the control command obtained from the stroke number measured variable (claim 3). If the measured variable of the number of strokes increases to a predetermined limit value with increasing size of the reflection factor, the return resistance is increased via the control command obtained from this measured variable, whereby the maximum return stroke speed of the percussion piston, i. H. the return stroke start speed, reduced and thus the increase in the number of strokes is limited.
  • the adaptation of the working behavior of the striking mechanism to the changing hardness of the shredding material can, however, also be brought about by influencing the internal resistance of the conveyor unit (claim 4); by definition, their internal resistance increases when the emerging flow rate is reduced by reducing the delivery volume. If the measured quantity of the stroke rate rises to the specified limit value, the flow is reduced by the control command until until the number of strokes has again reached the specified limit.
  • the method can be carried out in such a way that the drive means input quantity received by the striking mechanism is also determined as a measured variable and an actual measured variable ratio value is formed from the measured quantity ratio of the stroke rate / input quantity. If this rises to a limit value which is specified as a function of the size of the striking mechanism stroke set in each case, the striking mechanism internal resistance is increased by stroke adjustment (claim 5). Since the mentioned measured variable ratio actual value also increases with increasing size of the reflection factor, the increase in the stroke of the striking mechanism which is finally triggered by the control command leads to a corresponding change in the individual impact energy acting on the comminution material.
  • the relevant measurement variable ratio limit value is adapted to the currently set size of the hammer stroke; the method accordingly works with a switchable measurement variable ratio limit.
  • the previously described embodiment of the method can be further developed in that the impact number limit value is specified as a function of the size of the impact mechanism stroke set in each case (claim 6); In this way it is ensured that the number of impacts always returns below the associated impact number limit in the area which is determined by the size of an impact mechanism stroke.
  • the size of the flow can be influenced by adjusting the delivery volume of the delivery unit, this will - if necessary also additionally - reduced if the operating pressure in the flow increases to a predetermined pressure limit (claim 7);
  • This configuration presupposes that the operating pressure in the delivery flow is detected by means of a pressure sensor and converted into a controlled variable by means of a pressure regulator.
  • the pressure limit value is expediently specified as a function of the size of the impact mechanism stroke set in each case (claim 8); this creates the possibility of adapting the pressure limit value to different areas determined by the size of the striking stroke.
  • a striking mechanism with stroke adjustment is described in the previously mentioned prior publication DE-C3-26 58 455.
  • the stroke of the percussion piston can then be changed via a spring-loaded control slide, which - depending on the size of a control pressure acting on it - releases or blocks differently arranged control grooves and control channels, thereby influencing the reversal of the movement of the percussion piston.
  • the size of the control pressure - which can be detected in a simple manner by means of a pressure sensor - thus corresponds to a specific size of the percussion piston stroke currently set.
  • the object on which the invention is based is further achieved by a device having the features of claim 9.
  • Essential components of the device suitable for carrying out the method are a stroke number sensor which detects the percussion piston stroke number and is located outside the percussion mechanism, a stroke number regulator connected downstream of this and an actuator controlled by this, by means of which the internal resistance of the delivery unit or the percussion mechanism is increased, if the measurand of Number of strokes increases to a predetermined limit.
  • the actuator can in particular consist of an adjustment throttle, which is built into the return line of the striking mechanism (claim 10), or can be designed as an adjustment drive, via which the delivery volume of the delivery unit can be changed (claim 11).
  • Another type of device for carrying out the method has two sensors arranged outside the percussion mechanism, namely a stroke number sensor which detects the percussion piston stroke number and an input current sensor for determining the input quantity flow recorded by the percussion mechanism.
  • Other essential components of this device are an arithmetic unit for forming a z / Q actual value from the ratio between the measured variable of the beat number and the input quantity flow, a controller processing the z / Q actual value and an actuator connected downstream for influencing the internal movement of the percussion mechanism. This is increased under the influence of the controller if the actual value of the measured variable ratio rises to a predetermined, changeable limit value (claim 12).
  • a further development of the previously mentioned embodiment is characterized in that the size of the striking mechanism stroke can be changed via the actuator (normally step-by-step) (claim 13); the internal resistance of the striking mechanism can be increased by increasing the stroke of the striking mechanism.
  • the device according to claim 12 and 13 is in the return line of the striking mechanism controlled by a stroke number regulator throttle built-in.
  • the stroke number controller connected downstream of the stroke number sensor is designed in such a way that it only becomes effective if the measured quantity of the stroke number increases to a limit value which is specified as a function of the respectively set size of the stroke mechanism stroke (claim 14).
  • the stroke number controller ensures that the stroke number is repeatedly lowered below a limit value which is adapted to the size of the stroke stroke currently set.
  • the device according to claim 11 or claim 12 to 14 may additionally have a pressure sensor which records the operating pressure in the delivery line of the delivery unit, a downstream pressure regulator and an adjustment drive controlled by this, under whose influence the delivery volume of the delivery unit is reduced, if the measured variable of the operating pressure increases to a predetermined pressure limit (claim 15).
  • a further adaptation to the respective working area of the striking mechanism can be brought about by presetting the pressure limit value as a function of the size of the striking mechanism stroke set in each case by means of a pressure limit value sensor which detects it (claim 16); in such an embodiment, the pressure limit value is therefore also adapted to the currently set size of the striking mechanism stroke.
  • the hydraulic excavator 1 shown in FIG. 1 has a diesel engine 2 as a supply unit, which among other things drives a hydraulic pump 3; this is connected via a pressure line 4 and a return line 5 to a hydraulic hammer 6, which in turn is held in an adjustable manner on the boom 7 of the hydraulic excavator with two boom arms 7a, 7b.
  • the percussion piston 8 of the hydraulic hammer executes an alternating movement in the direction of its longitudinal axis 8a, strikes a tool designed as a chisel 9 at the end of its stroke and acts on the comminution material 10 via this; the kinetic energy of the percussion piston 8 is converted into impact energy.
  • the chisel 9 (cf. FIG. 1) is broken down into two active arrows 9a, 9b; the different properties of the Comminution material 10 are indicated by the symbol 11 with R as the reflection factor.
  • the delivery flow Q p supplied by the hydraulic pump 3 reaches the operating pressure via the pressure line 4 to the hydraulic hammer 6, which receives the input flow rate Q e and converts it into hydraulic impact power via the percussion piston. Any power recovery within the hydraulic hammer is indicated by the virtual pump 12 with the reflection flow Q R , through which the recovered mechanical power is converted into hydraulic power.
  • the reflection quantity flow Q R increases with the size of the reflection factor R: If the reflection factor has the value zero, the virtual pump 12 accordingly does not deliver a reflection quantity flow Q R.
  • the arrow 9a pointing to the right symbolizes the primary energy flow emanating from the hydraulic hammer, while the arrow 9b symbolizes the reflected energy flow acting on the hydraulic hammer, which may result in the generation of the reflection quantity flow Q R.
  • the reflection factor R of the comminution material 10 (cf. FIG. 1) does not have the value zero, the input quantity flow Q e received by the hydraulic hammer 6 is smaller than the delivery flow Q p supplied by the hydraulic pump 3; Unless countermeasures are taken, this operating state leads to the operating pressure in the pressure line 4 rising.
  • the device in question is equipped with a stroke rate sensor 13, which is arranged outside the hydraulic hammer.
  • the Impact rate sensor working in the manner of a sound wave or vibration sensor detects - indicated by the broken line 14 - the sound waves or vibrations which are caused by the operation of the hydraulic hammer and is converted into a measured variable z which is transmitted via a measuring line 15 in a beat number controller 16 is transferred; an adjustable beat number limit value z o is also transmitted to this via a limit value transmitter 17 along with line 18.
  • the stroke number controller 16 is followed by an actuator in the form of an adjusting motor 20 with the interposition of a control line 19, via which - indicated by line 21 - the delivery volume of the hydraulic pump 3 can be changed; in the present case it is designed as a variable displacement pump. If, during operation of the hydraulic hammer 6, the number of strokes z determined as the measured variable increases to the predetermined limit of the number of strokes z o , the stroke number controller 16 generates a control command which is forwarded to the adjusting motor 20 and which reduces the delivery flow in the pressure line 4 by reducing the delivery volume drives back until the beat number z has reached the predetermined beat number limit again.
  • the embodiment of the subject matter of the invention in question therefore makes it possible, on the basis of a continuous determination of the size of the number of blows, to adapt the working behavior of the striking mechanism to changing properties of the comminution material, embodied by the reflection factor R; the required stroke rate sensor 13 can be designed in a manner known per se and can be arranged outside the hydraulic hammer, for example in an environment largely free of shocks and vibrations.
  • the device in question can be used regardless of the design of the hydraulic hammer or hammer mechanism.
  • the hydraulic hammer 6 is connected via the pressure line 4 to a hydraulic pump 3 with a constant delivery volume; An undesirable increase in the operating pressure in the pressure line is prevented by a pressure relief valve 22, the connecting line 23 of which comes from the pressure line 4.
  • the impact rate controller 16 is connected on the output side via a control line 24 to an adjusting throttle 25 which is installed in the return line 5 of the hydraulic hammer 6. By actuating the adjusting throttle, the return resistance - and thus the return pressure in the return line 5 - can be influenced, with the result that the return stroke speed of the percussion piston 8 changes.
  • the adjusting throttle 25 executes a closing movement under the influence of a regulator command generated by the stroke number controller 16, on the basis of which, with increased internal resistance of the hydraulic hammer 6, the movement of the Percussion piston 8 is delayed until the measured quantity of the stroke number z again matches the stroke number limit value.
  • a change in the internal resistance of the hydraulic hammer may become more consequent Lowered stroke rate triggered.
  • the increase in the operating pressure occurring in the pressure line 4 may lead to the pressure relief valve 22 opening and a partial flow Q V beginning to flow off.
  • the regulation for adapting the working behavior of the hydraulic hammer 12 is based on two continuously determined measured variables, namely the number of strokes z detected by the stroke number sensor 13 and the input quantity flow into the hydraulic hammer 6 detected by an input current sensor 26.
  • the input current sensor which operates in a manner known per se in the manner of a flow meter, is installed in the pressure line 4 between the connecting line 23 for the pressure limiting valve 22 and the hydraulic hammer 6.
  • the measured variables obtained by means of the sensors 13 and 26 - number of blows z and input quantity flow Q e - are fed via a control line 27 or 28 to a computing element 29, in which a z / Q actual value is formed from the ratio between the two measured variables, which an input 30 is transmitted to a controller 31.
  • This in turn is connected via a control line 32 to an actuator 33, via which - indicated by an arrow 34 - the size of the striking stroke can be changed; the embodiment in question therefore requires the use of a hydraulic hammer with stroke adjustment.
  • the impact mechanism stroke ⁇ s can be changed in a manner known per se in several stages, which are indicated by "n" (cf. also the already mentioned DE-C3-26 58 455).
  • the actuator 33 is connected to the input side of the controller 31 with the interposition of a z / Q limit transmitter 35. From The actuator 33 receives the component 35 control commands which adapt the limit value (z / Q) 0 to the stroke of the percussion piston 8 which is currently set.
  • the controller 31 acts on the actuator 33 via a controller command and on the hydraulic hammer 6 in the sense of a change in the internal resistance if the actual z / Q value supplied by the computing element 29 reaches the limit value specified by the z / Q limit transmitter 35 .
  • the control is based on the knowledge that the ratio between the measured variable of the beat number z and the input quantity flow Q e also increases with increasing values of the reflection factor R.
  • the actuator 33 increases the percussion piston stroke and thus a corresponding change in the internal resistance of the hydraulic hammer 6, which increases with otherwise unchanged working conditions the single impact energy and a decrease in the impact rate. Accordingly, the actual z / Q value also decreases.
  • the embodiment according to FIG. 4 can advantageously be designed such that the impact number limit value z0 is also specified as a function of the size of the impact piston stroke set in each case.
  • Such an embodiment can be seen from FIG. 5, the hydraulic hammer 6 being shown for the sake of clarity without the virtual pump 12 indicating energy recovery (cf. FIG. 4).
  • the one in question is Device additionally equipped with a stroke ⁇ number limit transmitter 17, a stroke number controller 16 and an actuator connected downstream thereof in the form of an adjusting throttle 25; the latter is - as already explained with reference to FIG. 3 - installed in the return line 5 of the hydraulic hammer 6.
  • the impact rate controller 16 is connected on the input side via a measuring line 36 to the impact rate sensor 13 and via the input 18 to the impact rate limit value transmitter 17.
  • the latter receives control commands from the actuator 33 via a signal line 37, which switch the stroke number limit value z0 according to the size of the percussion piston stroke.
  • the stroke number controller 16 triggers a reduction in the flow cross section in the return line 5, which is determined by the adjusting throttle 25, via the control line 24; this change has the consequence that the internal resistance of the hydraulic hammer 6 (associated with an increase in the return pressure in the return line 5) increases and the number of strokes z decreases.
  • the described configuration thus ensures that the impact number in each area, which is determined by the size of the respective impact piston stroke, is limited to the size of the adjusted number of impact limits z0 (n) under the action of the impact number controller 16.
  • the hydraulic pump 3 can also be designed as a variable displacement pump with a variable delivery volume, the operating state of which is monitored and, if necessary, adapted by means of a pressure control (FIG. 6 ).
  • the hydraulic pump 3 with a Pressure sensor 38 equipped, which acts on an adjustment drive 40 via a control line 39;
  • the size of the delivery volume of the hydraulic pump 3 can be changed via this - indicated by an arrow 41.
  • the pressure regulator 38 is connected on the input side with the interposition of a pressure sensor 42 via a measuring line 43 to the pressure line 4 and is also connected via an input 44 to a pressure limit indicator 45.
  • the advantage achieved with this additional pressure control is that the hydraulic hammer 6 can be acted upon with the maximum permissible operating pressure.
  • FIG. 7 shows an advantageous embodiment of the embodiment according to FIG. 5 in the event that the hydraulic pump 3 - according to FIG. 6 - is designed as a variable displacement pump with a variable delivery volume and pressure control.
  • the pressure limit transmitter 45 is additionally connected via a line 46 to the actuator 33 for influencing the size of the percussion piston stroke. By control commands coming from the actuator 33, the pressure limit value pwert predetermined by the pressure limit transmitter 45 is adapted in size to the currently set percussion piston stroke.
  • the measurement of the performance parameter of interest of the percussion mechanism is carried out using sensors which are arranged outside the percussion mechanism.
  • the advantage achieved by the invention is therefore that the adaptation of the working behavior of hydraulically operated striking mechanisms to the measurement of at least one of the two performance parameters of the striking mechanism - percussion piston stroke number z and input flow rate Q e into the striking mechanism - is attributed to the outside of the striking mechanism - and thus largely regardless of this - is executed; Corresponding controllers can accordingly be optimally designed and attached and also used with differently designed striking mechanisms.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Chutes (AREA)
  • Disintegrating Or Milling (AREA)
  • Crushing And Pulverization Processes (AREA)
EP91119042A 1990-11-20 1991-11-08 Procédé et dispositif pour ajustage des caractéristiques de travail d'un mécanisme à coup à la dureté des materiaux à broyer Expired - Lifetime EP0486898B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4036918A DE4036918A1 (de) 1990-11-20 1990-11-20 Verfahren zur anpassung des arbeitsverhaltens eines schlagwerks an die haerte des zerkleinerungsmaterials und einrichtung zur durchfuehrung des verfahrens
DE4036918 1990-11-20

Publications (2)

Publication Number Publication Date
EP0486898A1 true EP0486898A1 (fr) 1992-05-27
EP0486898B1 EP0486898B1 (fr) 1996-05-01

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EP91119042A Expired - Lifetime EP0486898B1 (fr) 1990-11-20 1991-11-08 Procédé et dispositif pour ajustage des caractéristiques de travail d'un mécanisme à coup à la dureté des materiaux à broyer

Country Status (5)

Country Link
US (1) US5174387A (fr)
EP (1) EP0486898B1 (fr)
JP (1) JPH04289083A (fr)
AT (1) ATE137431T1 (fr)
DE (2) DE4036918A1 (fr)

Cited By (4)

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Publication number Priority date Publication date Assignee Title
EP0778110A3 (fr) * 1995-12-07 1998-06-10 Krupp Bautechnik GmbH Procédé pour la modification du mode de fonctionnement d'un mécanisme de percussion actionné par un fluide et mécanisme de percussion pour la mise en oeuvre du procédé
WO2009083716A1 (fr) * 2008-01-02 2009-07-09 Gj Tulett Ensemble outil excavateur
WO2014198515A1 (fr) * 2013-06-12 2014-12-18 Montabert Procédé de commande d'un paramètre d'alimentation d'un appareil à percussions
WO2014198514A1 (fr) * 2013-06-12 2014-12-18 Montabert Procédé de commande de l'énergie d'impact d'un piston de frappe d'un appareil à percussions

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DE19507348A1 (de) * 1995-03-02 1996-09-05 Krupp Maschinentechnik Verfahren zur Beeinflussung des Betriebsverhaltens eines fluidbetriebenen Schlagwerks und zur Durchführung des Verfahrens geeignetes Schlagwerk
WO1998004387A1 (fr) * 1996-07-25 1998-02-05 Komatsu Ltd. Defonceuse hydraulique avec dispositif de prevention de mouvement a vide
JP3888492B2 (ja) * 1997-12-19 2007-03-07 古河機械金属株式会社 衝撃装置
DE19803449A1 (de) * 1998-01-30 1999-08-05 Krupp Berco Bautechnik Gmbh Druckmittelbetriebene Schlagvorrichtung
FI105594B (fi) 1998-02-05 2000-09-15 Tamrock Oy Sovitelma hydraulisen rikotuslaitteen huollon tarpeen tunnistamiseksi
JP3286837B2 (ja) * 1998-02-25 2002-05-27 株式会社泉精器製作所 建設機械のアタッチメント
DE19923680B4 (de) * 1999-05-22 2004-02-26 Atlas Copco Construction Tools Gmbh Verfahren zur Ermittlung der Betriebsdauer und des Einsatz-Zustands eines hydraulischen Schlagaggregats, insbesondere Hydraulikhammer, sowie Vorrichtung zur Durchführung des Verfahrens
US6491114B1 (en) 2000-10-03 2002-12-10 Npk Construction Equipment, Inc. Slow start control for a hydraulic hammer
FI115037B (fi) * 2001-10-18 2005-02-28 Sandvik Tamrock Oy Menetelmä ja sovitelma kallionporauslaitteen yhteydessä
DE10160864A1 (de) * 2001-12-12 2003-06-26 Hilti Ag Axial schlagendes Elektrohandwerkzeuggerät
US6730227B2 (en) * 2002-03-28 2004-05-04 Nalco Company Method of monitoring membrane separation processes
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DE102004035306A1 (de) * 2004-07-21 2006-03-16 Atlas Copco Construction Tools Gmbh Druckmittelbetriebene Schlagvorrichtung insbesondere Hydraulikhammer
DE102004035289A1 (de) * 2004-07-21 2006-02-16 Kennametal Widia Gmbh & Co.Kg Werkzeug
SE528081C2 (sv) * 2004-08-25 2006-08-29 Atlas Copco Constr Tools Ab Hydraulisk slagmekanism
FI123634B (fi) * 2007-10-05 2013-08-30 Sandvik Mining & Constr Oy Kallionrikkomislaite, suojaventtiili sekä menetelmä kallionrikkomislaitteen käyttämiseksi
JP5374331B2 (ja) * 2009-11-25 2013-12-25 パナソニック株式会社 回転工具
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US9701003B2 (en) * 2014-05-23 2017-07-11 Caterpillar Inc. Hydraulic hammer having delayed automatic shutoff
KR101638451B1 (ko) * 2014-07-30 2016-07-25 대모 엔지니어링 주식회사 무단 가변 자동 스트로크 유압 브레이커 시스템
CN104532897B (zh) * 2014-12-23 2016-07-27 南京工业职业技术学院 一种自适应智能液气压冲击破碎锤
RU2611103C2 (ru) * 2014-12-24 2017-02-21 Федеральное государственное бюджетное образовательное учреждение высшего образования "Орловский государственный университет имени И.С. Тургенева" (ФГБОУ ВО "ОГУ им. И.С. Тургенева") Устройство ударного действия
KR101782535B1 (ko) * 2016-01-28 2017-10-24 대모 엔지니어링 주식회사 유압브레이커
KR101780154B1 (ko) * 2016-07-27 2017-09-20 대모 엔지니어링 주식회사 유압식 타격 기기 및 이를 포함하는 건설 장비
KR101926916B1 (ko) * 2016-07-27 2018-12-10 대모 엔지니어링 주식회사 유압식 타격 기기의 모니터링 방법 및 이를 수행하는 시스템
CN108343651B (zh) * 2017-12-21 2021-03-16 中国神华能源股份有限公司 养路机械作业装置应急救援方法
JP7033938B2 (ja) * 2018-01-26 2022-03-11 株式会社小松製作所 作業機械および作業機械の制御方法
SE542131C2 (en) 2018-03-28 2020-03-03 Epiroc Rock Drills Ab A percussion device and a method for controlling a percussion mechanism of a percussion device
CN110173485B (zh) * 2019-05-23 2020-06-05 山东临工工程机械有限公司 一种控制破碎锤打锤频率的方法及装置

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EP0112810A2 (fr) * 1982-12-27 1984-07-04 Atlas Copco Aktiebolag Appareil pour forer dans la roche, et procédé pour obtenir un forage par percussion de rendement optimal
EP0183093A1 (fr) * 1984-11-29 1986-06-04 Fried. Krupp Gesellschaft mit beschränkter Haftung Dispositif hydraulique de percussion
DE3523219C1 (de) * 1985-06-28 1986-06-26 Ing. Günter Klemm, Spezialunternehmen für Bohrtechnik, 5962 Drolshagen Hydraulischer Bagger
EP0214064A1 (fr) * 1985-07-16 1987-03-11 Etablissements Montabert Procédé de commande du mouvement du piston de frappe d'un appareil à percussions mû par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procédé
EP0256955A1 (fr) * 1986-08-07 1988-02-24 Etablissements Montabert Procédé de régulation des paramètres de percussion du piston de frappe d'un appareil mû par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procédé
WO1989004910A1 (fr) * 1987-11-18 1989-06-01 Caterpillar Inc. Systeme de commande pour scarificateur a tiges multiples

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EP0112810A2 (fr) * 1982-12-27 1984-07-04 Atlas Copco Aktiebolag Appareil pour forer dans la roche, et procédé pour obtenir un forage par percussion de rendement optimal
EP0183093A1 (fr) * 1984-11-29 1986-06-04 Fried. Krupp Gesellschaft mit beschränkter Haftung Dispositif hydraulique de percussion
DE3523219C1 (de) * 1985-06-28 1986-06-26 Ing. Günter Klemm, Spezialunternehmen für Bohrtechnik, 5962 Drolshagen Hydraulischer Bagger
EP0214064A1 (fr) * 1985-07-16 1987-03-11 Etablissements Montabert Procédé de commande du mouvement du piston de frappe d'un appareil à percussions mû par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procédé
EP0256955A1 (fr) * 1986-08-07 1988-02-24 Etablissements Montabert Procédé de régulation des paramètres de percussion du piston de frappe d'un appareil mû par un fluide incompressible sous pression, et appareil pour la mise en oeuvre de ce procédé
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EP0778110A3 (fr) * 1995-12-07 1998-06-10 Krupp Bautechnik GmbH Procédé pour la modification du mode de fonctionnement d'un mécanisme de percussion actionné par un fluide et mécanisme de percussion pour la mise en oeuvre du procédé
WO2009083716A1 (fr) * 2008-01-02 2009-07-09 Gj Tulett Ensemble outil excavateur
WO2014198515A1 (fr) * 2013-06-12 2014-12-18 Montabert Procédé de commande d'un paramètre d'alimentation d'un appareil à percussions
WO2014198514A1 (fr) * 2013-06-12 2014-12-18 Montabert Procédé de commande de l'énergie d'impact d'un piston de frappe d'un appareil à percussions
FR3007153A1 (fr) * 2013-06-12 2014-12-19 Montabert Roger Procede de commande d’un parametre d’alimentation d’un appareil a percussions
FR3007154A1 (fr) * 2013-06-12 2014-12-19 Montabert Roger Procede de commande de l’energie d’impact d’un piston de frappe d’un appareil a percussions
CN105339138A (zh) * 2013-06-12 2016-02-17 蒙塔博特公司 控制冲击设备电源参数的方法
CN105339138B (zh) * 2013-06-12 2017-12-22 蒙塔博特公司 控制冲击设备电源参数的方法

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JPH04289083A (ja) 1992-10-14
ATE137431T1 (de) 1996-05-15
DE4036918A1 (de) 1992-05-21
EP0486898B1 (fr) 1996-05-01
DE59107760D1 (de) 1996-06-05
US5174387A (en) 1992-12-29

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