Classifications

• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
  • E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
  • E02D7/02—Placing by driving
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
  • E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
  • E02D7/02—Placing by driving
  • E02D7/06—Power-driven drivers
  • E02D7/08—Drop drivers with free-falling hammer

Definitions

• the invention relates to a hammering device comprising a hammer connected to a winch by means of cable means.
• the invention further relates to a method for operating a hammering device.
• Hammering devices such as pile drivers, breakers, hydraulic hammers and the like are used for a number of purposes e.g. in the mining and quarry industry for breaking boulders and the like, in the steel industry for ladle deskulling, for slag crushing or for other purposes such as breaking up large concrete surfaces like runways, roads and factory floors.
• a hammering device typically comprises a very heavy hammer head traveling inside a hammer guide e.g. in the form of a large tube.
• the device further comprises some sort of lifting mechanism arranged to lift the hammer to a certain height where after the hammer head is released and by free fall (i.e. gravity pull) is brought to impact on an object whether it be a pile, a rock or other objects which need to be crushed or impacted.
• the hammer head will have a weight of from a couple of tonnes to more than 10 tonnes and in order to make such hammering devices economically attractive, it is necessary to design the device so that it is able to create a certain number of full impacts per minute.
• the invention provides for a hammering device comprising a hammer connected to a winch by means of cable means, wherein the rotation of the winch is driven by one or more hydraulic motors, and wherein the hammering device further comprises position detection means for detecting a position of the hammer.
• Providing the hammering device with position detection means for detecting the actual position of the hammer is advantageous in that it enables that a braking procedure may be commenced before the hammer reaches impact.
• the cable means overshoots and the hammer can therefore be lifted again immediately after impact, which among other severely increases the capacity of the hammering device.
• the term "cable means" in this context should be interpreted as any kind of line, rod, rope, wire, chain or any other kind of cable suitable for lifting a very heavy hammer and for being wound around a winch.
• position detection means in this context should be interpreted as any kind of incremental encoder, absolute encoder, tachometer, revolution-counter, RPM gauge or any kind of contact or none-contact sensors capable of detecting position (by means of distance detection or detecting increments) e.g. by means of laser, light, sound, magnetism, radar or any other kind of position detector capable of detecting the actual position of a hammer in a hammering device.
• said hammering device further comprises winch rotation braking means.
• Providing the hammering device with winch rotation braking means is advantageous in that such means enables simple and inexpensive braking means.
• said hammering device further comprises control means for activating said winch rotation braking means in accordance with an input from said position detection means.
• Activating the winch rotation braking means in accordance with the actual position of the hammer is advantageous in that it enables a more controlled and precise braking process.
• said control means comprises reset means for resetting said position detection means when said hammer reached impact.
• said hammering device further comprise impact position detection means for detecting when said hammer reached impact.
• the object will most likely deform, break or at least move so that if the same object is hit several times, the impact position will typically move further and further down.
• the brake system will absorb too much energy before the hammer reaches impact on succeeding strikes, which will strain the braking system and reduce the energy in the impact.
• the impact position could e.g. be detected by monitoring the oil pressure in the hydraulic motor circuit, by means of strain gauges on/at the winch or cable means, by means of accelerometers, acoustic monitors or by other means.
• said hammering device comprises direct short circuit flow path means for optionally creating a direct short circuit flow path between an input port and an output port of said hydraulic motor.
• said winch rotation braking means comprises short circuit flow path blocking means for blocking a flow through said short circuit flow path.
• Blocking the flow through the short circuit flow path is a fast and efficient way of providing winch rotation braking means. Furthermore, it is relatively easy to control the braking process by means of such short circuit flow path blocking means and in contrast to ordinary brake means such as disk brakes or drum brakes, the short circuit flow path blocking means does substantially not comprise wear parts.
• said direct short circuit flow path means comprises overpressure relieve means.
• said overpressure relieve means is arranged to relieve the pressure in said direct short circuit flow path if said pressure exceeds 700 Bar, preferably if said pressure exceeds 500 Bar and most preferred if said pressure exceeds 300 Bar. If the pressure in the direct short circuit flow path is too low when it is relieved, the brake will be inefficient and if the pressure is too high the risk of damage due to overpressure is increased. Thus, the present pressure levels present an advantageous relation between efficiency and safety.
• said direct short circuit flow path means comprises refilling means for increasing the pressure in said short circuit flow path.
• said winch is driven by more than one hydraulic motor.
• Two or more hydraulic motors will typically be less expensive that a single hydraulic motor with equivalent capacity - particularly in relation to the present heavy duty hydraulic motors - and driving the winch by means of two or more hydraulic motors will also provide reciprocity to the lifting system - thus increasing the safety level of the system.
• At least one of said more than one hydraulic motor comprises freewheeling means.
• Providing the additional motor(s) with freewheeling means is advantageous in that the freewheeling means enables that substantially no energy is absorbed by these motors during the drop - thus increasing the capacity of the hammering device.
• said freewheeling means comprises means for connecting an output port of said hydraulic motor to tank means.
• said position detection means comprise a rotary encoder.
• a rotary encoder is a simple and efficient way of detecting the position of hammer by detecting the rotations of the winch.
• said rotary encoder is connected to a winch shaft around which said winch rotates.
• the invention further provides for a method for operating a hammering device.
• the method comprises the steps of:
• said method further comprises the step of detecting a position of said hammer at least during said drop.
• Detecting the position of the hammer during the drop is advantageous in that enables that the braking process can be initiated more precisely and efficiently.
• detecting e.g. the initial position is advantageous in that it hereby is possible to determine the energy delivered by the drop and detecting the impact position is advantageous in that it hereby is possible to initiate the braking process more accurately at the next drop.
• said flow through said short circuit flow path if broken or reduced in response to said detected position of said hammer.
• Reducing the flow through the direct short circuit flow path in response to the detected position of the hammer is advantageous in that this enables that the flow can be reduced or completely broken just before the hammer reaches impact and thereby ensure that the kinetic energy of the rotation/motion of the winch and cable means is absorbed by the winch rotation braking means - thus reducing the risk of the cable means overshooting.
• said position of said hammer is detected in relation to the latest impact position of said hammer.
• said breaking or reducing said flow through said direct short circuit flow path is initiated in response to the latest impact position of said hammer.
• said predetermined initial position is selected manually by an operator.
• the hammering device of the present invention comprises hammer position detection means it is advantageous to enable that the initial position of the hammer is chosen by the operator to ensure that a more correct amount of energy is delivered at each stroke.
• said hammering device is a hammering device according to any of the previously mentioned hammering devices.
• fig. 1 illustrates a hammering device mounted on a heavy duty excavator, as seen from the side
• fig. 2 illustrates a hammering device, as seen from the front
• fig. 3 illustrates a cross section through a hammering device, as seen from the side
• fig. 4 illustrates the hydraulic diagram of a hammering device comprising a single hydraulic motor
• fig. 5 illustrates the hydraulic diagram of a hammering device comprising two hydraulic motors.
• Fig. 1 illustrates a hammering device 1 mounted on a heavy duty excavator 18, as seen from the side.
• the excavator 18 weighs in excess of 50 ton in order to be able to handle the large hammering device 1 mounted on the arm 19 of the excavator 18.
• the hammering device 1 could be mounted on an excavator 18 of another weight - both lesser or greater - the hammering device 1 could be mounted on another mobile or stationary apparatus such as a crane, a forklift, a digger or similar or the hammering device 1 could be arranged stationary or be provided with means for making it self-propelling.
• the hammering device 1 is supplied with oil pressure from the excavators internal oil pump but in another embodiment the hammering device 1 could be provided with its own independent oil pressurizing means or pressurized oil could be supplied from a pressurizing source external to both the excavator 18 and the hammering device 1.
• the hammering device 1 is first mounted on the arm 19 of the excavator 18 and the hammering device 1 is connected to the hydraulic system and/or the electrical system of the excavator 18. The operator will then initiate that the hammering device 1 will lift the hammer 2 inside the hammer guide means 20 up to an initial position.
• the initial position - i.e. the height to which the hammer 2 is initially lifted - could be chosen by the operator, it could be defined on basis of the latest impact position, it could be a fixed position inside the hammer guide means 20 or the initial position could be chosen or determined in another way.
• the excavator 18 then moves the hammering device 1 to the place of use and places the hammering device 1 so that the hammer guide means 20 rests on the object to be hammered on or places the bottom of the hammer guide means 20 immediately above the object.
• the operator then initiates the hammering process in the form of a single blow, a predefined series of blows or that the hammering process continues until the operator stops it again.
• the hammer 2 In the hammering process the hammer 2 is first dropped from its initial position where after gravity will pull the hammer 2 downwards until the hammer 2 hits the object over which the hammering device 1 is placed. Immediately thereafter the hammer 2 is lifter up to the initial position and e.g. dropped again.
• the actual impact position is determined each time the hammer 2 hits the object and the initial position is then adjusted accordingly to ensure that the hammer 2 travels substantially the same distance each time and thus delivers substantially the same amount of energy. The travel distance could also be continuously adjusted by the operator.
• Fig. 2 illustrates a hammering device 1, as seen from the front.
• the hammer guide means 20 are formed as a tube i.e. an elongated cylinder having an inside diameter a little greater than the outer diameter of the hammer 2.
• the hammer guide means 20 ensures that the hammer 2 travels up and down along a predefined path and in another embodiment the hammer guide means 20 could instead or also comprise rails, guidance or other or the tube and/or the hammer 2 could be formed with a square, a polygonal, an oval or another cross section.
• the hammering device 1 is provided with a winch 3 arranged on the outside of the hammer guide means 20.
• the winch means 3 is in this embodiment driven by two hydraulic motors 5 arranged on either sides of the winch 3.
• the winch 3 could be driven by another number of hydraulic motors 5 such as one, three, four or more or the winch 3 could be driven by one or more hydraulic motors 5 in combination with another motor type such as a combustion engine, an electrical motor or other.
• hammering device 1 only comprises a single winch 3 but in another embodiment the hammering device 1 could comprise more than one winch means 3 such as two, three or more e.g. coupled in parallel.
• Fig. 3 illustrates a cross section through the hammering device 1 disclosed in fig. 2, as seen from the side.
• the hammer 2 is connected to the winch 3 by means of cable means 4 extending from the winch 3 and up around a pulley 21 arranged at the upper end of the hammer guide means 20 and down to the hammer 2 inside the hammer guide means 20.
• the winch 3 could be arranged at the the upper end of the hammer guide means 20 thus rendering the pulley 21 superfluous.
• the hammering device 1 is also provided with means for braking the rotation of the winch 3 when the hammer 2 is dropping.
• these means are not provided to prevent the hammer 2 from reaching impact but to initiate a braking process just before the hammer 2 reaches impact to prevent that the cable means overshoots.
• the winch rotation baking means (not shown) will be discussed in details in relation with fig. 4.
• the hammering device 1 is in this embodiment also provided with position detection means 6.
• the position detection means 6 are formed as a rotary encoder comprising an encoder disk 22 and an inductive proximity sensor 23 detecting the holes in the encoder disk 22 as they rotate by.
• the position detection means 6 could comprise another type of rotary encoder e.g. connected to the pulley 21 instead, it could comprise another type of position detectors such means distance sensors detecting the position of the hammer 2 by means of sound, ultrasound, light, laser, radar or other or the actual position of the hammer 2 could be detected in a multitude of other ways.
• the hammering device 1 could be formed without position detection means 6. It such an embodiment the braking process could be initiated by means of a timer, in response to a particular sensor being activated or manually by an operator.
• Fig. 4 illustrates the hydraulic diagram of a hammering device 1 comprising a single hydraulic motor 5.
• the hammering device 1 comprises a hammer 2 connected to a winch 3 through cable means 4.
• the winch 3 is in this embodiment driven by a single hydraulic motor 5.
• Oil pressurizing means is connected to an inlet port 24 of a directional valve 26 and the outlet port 25 of the directional valve 26 is connected to tank.
• pressurized oil will be led to an input port 10 of the hydraulic motor 5 and the output port 11 of the hydraulic motor 5 is connected to tank, which will make the winch 3 rotate and lift hammer 2 upwards. If it for some reason was needed to lower the hammer 2 - e.g.
• the directional valve 26 could be changed to the right chamber so that the direction of the oil flow through the hydraulic motor 5 is reversed.
• the directional valve 26 is first changed to the left chamber to lift the hammer 2 and when the initial position has been reached the directional valve 26 is changed back to center position to lock the hammers position.
• the hammering device 1 is also provided with direct short circuit flow path means 9 comprising a direct short circuit flow path 14 and short circuit flow path blocking means 12 in the form of an on/off valve.
• direct short circuit flow path means 9 comprising a direct short circuit flow path 14 and short circuit flow path blocking means 12 in the form of an on/off valve.
• the hammering device 1 is further provided with an impact sensor 27 for detecting when impact occurs. This information is fed to the control means 8 and the initial position of the succeeding drop is then calculated in response to the latest impact position.
• the direct short circuit flow path means 9 comprises overpressure relieve means 13 in the form of a pressure valve that will bleed oil from the circuit to tank means 17 if the pressure exceeds an predefined level.
• the overpressure relieve means 13 could be located differently in the circuit and/or the function could be integrated with an exciting valve.
• the circuit is in this embodiment provided with refilling means 15 to ensure that the pressure in the circuit at all times during the drop is higher than the loss/resistance.
• the directional valve 26 is opened slightly in lifting direction to pressurize the circuit slightly.
• the refilling means 15 could comprise a dedicated valve connected to the common oil pressurising means or to dedicated oil pressurising means.
• Fig.5 illustrates the hydraulic diagram of a hammering device 1 comprising two hydraulic motors 5.
• the winch 3 is driven by a first hydraulic motor 5 which is setup as explained under fig. 4 and a second hydraulic motor 5 comprising freewheeling means 16.
• the freewheeling means 16 comprises a tank valve 28 that selectively can connect the output port 11 of the second hydraulic motor 5 to tank means 17.
• the short circuit flow path blocking means 12 and the tank valve 28 is substantially simultaneously activated so that the oil in the second hydraulic motor will be forced out of the output port 11 of the second hydraulic motor 5 and towards the tank means 17. Since the directional valve 26 is in closed centre position no oil is fed to the second hydraulic motor 5 during freewheeling and vacuum will then be established inside the motor 5.
• Tank means

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• Engineering & Computer Science (AREA)
• Life Sciences & Earth Sciences (AREA)
• General Life Sciences & Earth Sciences (AREA)
• Mining & Mineral Resources (AREA)
• Paleontology (AREA)
• Civil Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Structural Engineering (AREA)
• Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
• Earth Drilling (AREA)
• Percussive Tools And Related Accessories (AREA)

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Citations (2)

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• 2013
  • 2013-04-19 BR BR112015026472-7A patent/BR112015026472B1/pt active IP Right Grant
  • 2013-04-19 US US14/784,176 patent/US20160076216A1/en not_active Abandoned
  • 2013-04-19 EP EP13718294.5A patent/EP2986783B1/en active Active
  • 2013-04-19 WO PCT/DK2013/050115 patent/WO2014169917A1/en active Application Filing
  • 2013-04-19 CN CN201380075743.9A patent/CN105264144A/zh active Pending
• 2015
  • 2015-10-13 ZA ZA2015/07618A patent/ZA201507618B/en unknown

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