EP0276845B1 - Pfahlramme - Google Patents

Pfahlramme Download PDF

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Publication number
EP0276845B1
EP0276845B1 EP19880101219 EP88101219A EP0276845B1 EP 0276845 B1 EP0276845 B1 EP 0276845B1 EP 19880101219 EP19880101219 EP 19880101219 EP 88101219 A EP88101219 A EP 88101219A EP 0276845 B1 EP0276845 B1 EP 0276845B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
self
equilibration
vibration
pile
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.)
Revoked
Application number
EP19880101219
Other languages
English (en)
French (fr)
Other versions
EP0276845A3 (en
EP0276845A2 (de
Inventor
Yasuo Tasaki
Seizo Kumai
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.)
TAKAHASHI ENGINEERING KK
Original Assignee
TAKAHASHI ENGINEERING KK
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
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Application filed by TAKAHASHI ENGINEERING KK filed Critical TAKAHASHI ENGINEERING KK
Publication of EP0276845A2 publication Critical patent/EP0276845A2/de
Publication of EP0276845A3 publication Critical patent/EP0276845A3/en
Application granted granted Critical
Publication of EP0276845B1 publication Critical patent/EP0276845B1/de
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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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
    • E02D7/18—Placing by vibrating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D13/00—Accessories for placing or removing piles or bulkheads, e.g. noise attenuating chambers
    • E02D13/10—Follow-blocks of pile-drivers or like devices

Definitions

  • the present invention relates to a pile driver utilizing a vibration cylinder receiving a fluid pressure as energy source to generate a mechanical vibration under which a pile is driven into the ground.
  • a pile driver according to the preamble of claim 1 using a vibration cylinder has been proposed in the West Germany Patent No. 28 21 339 , in which, as shown in Figure 1, the vibration cylinder itself has a function of self-equilibration and a pile P is coupled with a piston 101 of a vibration cylinder 100 by means of a chuck 102, an inertial weight 103 being coupled with the other end of the vibration cylinder 100 in line with the pile P, whereby a vibratory force of a periodic function is generated between the inertial weight 103 and the pile P which in turn will be driven into a ground E.
  • the vibratory force is damped when the inertial weight is applied with a pull-down force by any other construction machine such as crane truck, leader, etc.
  • the present invention has an object to overcome the above-mentioned drawbacks of the prior-art pile drivers by providing a pile driver of which the inertial weight can be pulled up and down by any other construction machine without damping the alternate vibratory force of the vibration cylinder.
  • the above object can be attained by providing a pile driver utilizing a fluid pressure as energy source to generate a mechanical vibration under which a pile is driven into the ground in which the pile driver comprises an intertial weight, a vibration generating mechanism including a vibration cylinder and a change over valve to supply and discharge a pressurized fluid to and from the vibration cylinder, and a chuck which is provided at the lower end of a rod of the vibration cylinder to grasp the pile, characterized in that said vibration cylinder and a self-equilibration cylinder are so provided vertically in series with each other that the axes of their respective rods lie on the center line passing through the center of gravity of said inertial weight, the rods of the vibration and self-equilibration cylinders are coupled to each other, the self-equilibration mechanism has provided therein a control valve responsive to the rods of the self-equilibration cylinder to supply and discharge the pressurized fluid to and from a control chamber in the self-equilibration cylinder and the piston of the self-
  • the vibration cylinder and self-equilibration cylinder are so provided in series with each other that the axes of the rods thereof lie on the center line passing through the center of gravity of the inertial weight, a control valve is provided which operates in response to the rod of the vibration cylinder to supply and discharge the pressurized fluid to and from the control chamber in the self-equilibration cylinder, and the piston of the self-equilibration cylinder is supported with a low rigidity to the inertial weight by means of the accumulators provided as communicating with the control chamber or the spring provided inside the self-equilibration, whereby the piston of the self-equilibration cylinder is held in position within the inertial weight and also has a damping effect.
  • the vibration cylinder has its alternate vibratory force reduced due to the displacement of the piston of the self-equilibration cylinder. Also, owing to the damping effect of the self-equilibration cylinder, the weight of the inertial weight is conveyed to the pile without being damped so that the pile is effectively driven into the ground. Especially, when the inertial weight is applied with a pull-down or pull-up force by any other construction machine, no vibration is conveyed to the pull-down or pull-up equipment and the vibratory force is conveyed to the pile as a driving force or extraction force resulted from the superposition on the pull-up or pull-down force without being cancelled by the pull-up or pull-down force.
  • the pile driver according to the present invention comprises an intertial weight 1, a vibration generating mechanism 2 composed of a vibration cylinder 3 having rods 4 and 5, and a self-equalibration mechanism 6 composed of a self-equalibration cylinder 7 having rods 8 and 9, these cylinders 3 and 7 being so disposed vertically in series with each other that the axes of the rods 4 and 5 and those of the rods 8 and 9 lie on the center line passing through the center of gravity of the inertial weight 1.
  • the rods 5 and 8 are integrally formed into a one-piece structure.
  • the vibration cylinder 3 is provided with a changeover valve 10 to produce an alternate vibratory force.
  • the vibration cylinder 3 and the changeover valve 10 form together the vibration generating mechanism 2.
  • the self-equilibration cylinder 7 is provided with a control valve 11 responsive to the rods 8 and 9 of the self-equilibration cylinder 7 to supply and discharge a pressurized fluid to and from the self-equilibration cylinder.
  • accumulators 14 communicating with oil chambers 12 and 13 in the self-equilibration cylinder 7. Owing to the spring effect due to the volume change of these accumulators 14, the vertical vibration of the piston 15 of the self-equilibration cylinder 7 is prevented from being conveyed to the inertial weight 1, or to prevent the alternate vibratory force from being reduced by the inertial weight 1, the piston 15 of the self equilibration cylinder 7 is flexibly (with a low rigidity) coupled to the inertial weight 1.
  • the inertial weight 1 is coupled to the piston 15 with a high rigidity by means of a pressurized fluid of a relatively small compressibility. If it is assumed that the amplitude of the vibration due to the vibration cylinder 3 is less than ⁇ 2 mm, the rigidity of the spring effect due to the accumulators 14 should desirably be more than 20 mm when the vibratory force of the vibration cylinder 3 is maximum.
  • Such spring effect of the self-equilibration cylinder 7 can be attained by providing floating pistons 21 as fitted on the rods 8 and 9, respectively, on the opposite sides of the piston 15 and also providing springs 22 between the floating pistons 21 and the piston 15, respectively as shown in Figure 3.
  • the rod 4 of the vibration cylinder 3 has provided at the lower end thereof a chuck 17 which grasps a pile 16.
  • the vibration cylinder 3 has oil chambers 19 and 20 on the opposite sides, respectively, of the piston 18.
  • FIG. 4 A preferred embodiment of pile driver according to the present invention will be described with reference to Figure 4.
  • This embodiment is provided with a suspender 23 consisting of a hook 24 to be supported by a crane or the like, and a suspender body 25 having a C-shaped section and which is supported by the hook 24.
  • the inertial weight 1 is to be attached to the suspender body 25 with such a rubber cushion 26 placed betwen them that the vibration of the inertial weight 1 will not be conveyed directly to the suspender body 25.
  • the entire cylinders are made by relatively thick materials, and a sound-proof cover (skirt) 27 which also works as inertial weight is provided outside the cylinders. These are intended to reduce the manufacturing costs of the cylinders as a whole while isolating the sound and protecting the valves.
  • a servo-controlled valve which operates with an electric signal is used as shown in Figures 5 and 6.
  • This changeover valve 10 is provided inside the valve body 28 therof with a four-way valve 30 accomodating a spool 29 of which the shaft 29A is connected to a spool displacement detector 31 and which is driven by a electro-hydraulic servo valve 32.
  • the position of the spool 29 is converted into an electric signal which is fed back to a differential amplifier 33, and the spool 29 is moved following up with an instruction signal applied to the differential amplifier 33. Therefore, by applying the instruction signal as an electric waveform to the differential amplifier 33, the frequency and amplitude of vibration waveform to the displacement of the spool 29 can be simply controlled.
  • the reference numeral 34 indicates an oil port and 35 indicates a return port. Ports 36 and 37 communicate with the vibration cylinder 3. The flow direction and flow rate of the oil under pressure to the vibration cylinder 3 can be controlled by the four ports 34 thru 37 bades on the position of th spool 29.
  • the self-equilibration mechanism 6 is constructed as shown in Figures 5 and 7.
  • the self-equilibration cylinder 7 has control oil chambers 12 and 13 on either side, respectively, of the piston 15 and accumulators 14 communicating with the control oil chambers 12 and 13, respectively.
  • the responsive control valve 11 is a four-way valve using a spool 42 and works to connect any of pressurized oil supply port P and discharge port T to the oil path 43 or 44 provided within the responsive control valve and which communicate with the oil paths 39 and 40, respectively, according to the position of the spool 42.
  • the spool 42 of the responsive control valve 11 is forced upward by a spring 46 and the upper end of the shaft 42A of the spool 42 is projected outside of the valve body 45.
  • a member 48 pivotably installed to a fulcrum bracket 47 provided on the top of the self-equilibration cylinder body 38.
  • the other end of the member 48 is in contact with the rod 9 of the self-equilibration cylinder 7 (which serves in the same manner as the rods 4 and 5 of the vibration cylinder).
  • the fulcrum bracket 47 and member 48 form together a coupling means 41.
  • the spool 42 moves in response to the rods of the self-equilibration cylinder 7 and vibration cylinder 3.
  • the self-equilibration cylinder 7 has various functions; however, one of them will be described below: Namely, the oil pressure in the oil chambers 12 and 13 of the self-equilibration cylinder 7 is controlled as in the following. Assume that the pistons 15 and 18 vibrate at a high frequency of more than 20 Hz and with an amplitude of less than ⁇ 2 to 3 mm. The spool 42 of the responsive control valve 11 coupled to the pistons 15 and 18 by means of the coupling means 41 vibrate vertically. The self-equilibration mechanism 6 is so arranged as not to respond to the vibration.
  • the four-way valve is designed to have an overlap structure, or such an arrangement is made that even when the oil in the control oil chambers 12 and 13 is supplied and discharged at a high frequency owing to the compression of the accumulators 14, the pressure in the chambers will change little.
  • the rod 4 is applied with an external force, not the above-mentioned vibration of high frequency, or a pull-down force acts on the inertial weight, so that the pistons 15 and 18 vibrate at positions displaced upward, the spool 42 of the responsive control valve 11 is pressed down by the coupling means 41.
  • the oil chamber 13 in the self-equilibration cylinder is supplied with the oil from the oil supply port P through the oil paths 43 and 39, with the result that the oil pressure is raised, while the oil in the oil chamber 12 at the opposite side is discharged to the oil discharge port T through the oil paths 44 and 40 so that the oil pressure is lowered. Therefore, the piston 15 is pushed down and returned from the position upwardly displaced to the center.
  • Another function of the self-equilibration cylinder 7 is to provide a damping effect, namely, to prevent, owing to the compression of the accumulators 14 communicating with the oil chambers 12 and 13 of the self-equilibration cylinder 7, the vibration of the pistons 15 and 18 caused by the vibration cylinder 3 from being conveyed to the inertial weight 1 so that the vibration of the piston 18 is not restricted by the inertial weight 1.
  • the changeover valve 10 is not provided in the vibration cylinder 2 as in the West Germany Patent No. 28 21 339.0-09 but outside the vibration cylinder 3, which leads to a simplified construction of the piston 18 of the vibration cylinder 3.
  • the manufacturing costs of, especially, a large cylinder can be considerably reduced.
  • a pile driver in which, in addition to the frequency control element, an amplitude control element, namely, a servo-controlled valve is used as the changeover valve 10 according to the present invention, it is possible to control the amplitude of the pile 16 from zero to the maximum independently of the frequency. Thereby, it is possible to eliminate the shock to the crane, etc. by reducing to zero the amplitude at start and stop of the pile driver. Also, by changing the amplitude of the pile vibration, the vibration of the ground can be minimized when piles are driven into a complicate ground. For example, when the pile cannot be easily driven into the ground, the amplitude of pile vibration is increased. In case the pile can be easily driven into the ground, the amplitude is limited to a minimum necessary one.
  • the changeover valve 10 can be closed and opened following up with the waveform of electric signal, a changeover like a simple sinusoidal waveform can be done, and a changeover like a rectangular waveform can be done as well.
  • the pile driving ability can be improved owing to the hammer effect by changing the pressure in the vibration cylinder abrubtly at time of driving a pile into the ground.
  • by controlling the opening and closing of the changeover valve so that the opening area follows up with a sinusoidal waveform it is possible to reduce the high frequency component in the vibration waveform, whereby it is possible to reduce the noise generated by the chuck 17 and pile 16 as well.
  • the cylinders 3 and 7 are disposed vertically in series with each other so that the axes of their respective rods 4 and 5, and 8 and 9 (the rods 5 and 8 are integrally formed into a one-piece structure) lie on the center line passing through the center of gravity of the inertial weight 1.
  • the responsive control valve 11 is provided which responds to the rods 4 and 5 of the vibration cylinder 3 to supply and discharge the pressurized fluid to and from the oil chambers 12 and 13 of the self-equilibration cylinder 7.
  • the piston 15 of the self-equilibration cylinder 7 is supported to with a low rigidity by means of the accumulators 14 communicating with the oil chambers 12 and 13 or by means of the spring 22 provided in the self-equilibration cylinder 7.
  • the piston 15 of the self-equilibration cylinder 7 is held in position and has a damping effect.
  • the alternate vibratory force of the vibration cylinder 3 is prevented from being reduced due to the displacement of the piston 15 of the self-equilibration cylinder 7.
  • the weight of the inertial weight 1 is conveyed to the pile without being damped, whereby the pile can be effectively driven into the ground.
  • the vibration is not conveyed to the pull-down or pull-up equipment, and the vibratory force can be conveyed to the pile 16 as a driving force or extraction force resulted from superposition on the pull-down or pull-up force without being cancelled by the pull-down or pull-up force.
  • the pile driver according to the present invention is advantageous in that it is of a sound-proof structure, the alternate vibratory force of the vibration cylinder 3 can be conveyed to the pile 16 without being reduced and that the inertial weight 1 can be pulled down or up so that the pile driver itself may not be heavy.
  • Figure 8 shows a hydraulic circuit which supplies and discharges the pressurized fluid to and from the oil chambers 19 and 20, and 12 and 13 of the vibration cylinder 3 and self-equilibration cylinder 7, respectively.
  • the reference numeral 49 indicates a filter
  • 50 indicates a reducing valve.
  • the weight W of the inertial weight 1, pull-down force F1 and the alternate vibratory force of the vibration cylinder 3 are superposed on each other and applied to the pile 16.
  • the pile head is applied with a compressive force and tractive force alternately and the pile is likely to be broken when the tensile force is applied since the concrete is weak against a tensile force while being strong against a compressive force.
  • the tensile force of the vibration cylinder 3 to the concrete pile is reduced by pulling down the inertial weight by means of the pull-down equipment 51, so that the concrete pile can be driven into the ground without being broken.
  • the pull-up force indicated with F2 in Figure 9 is applied to the inertial weight 1 by a pull-up equipment 52.
  • the pile can be easily extracted with a static component (F2-W) of the extraction force and the alternate vibratory force applied as superposed on each other to the pile.

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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)

Claims (2)

  1. Pfahlramme, die für die Erzeugung mechanischer Vibrationen zum Eintreiben eines Pfahls (16) in den Grund ein Druckfluidum als Energiequelle benutzt, bestehend aus einem Trägheitsgewicht (1), einem Vibrationen erzeugenden Mechanismus (2) mit Vibrationszylinder (3) und einem Druckfluidum dem Vibrationszylinder zuund abführenden Wechselventil (10) sowie einem Futter (17) für das Erfassen des Pfahls (16) am unteren Ende einer Kolbenstange (4) des Vibrationszylinders, dadurch gekennzeichnet, daß der Vibrationszylinder (3) und ein Selbstausgleichszylinder (7) derart vertikal in Serie angeordnet sind, daß die Achsen ihrer Stangen (4,5,8,9) in der durch den Schwerpunkt des Trägheitsgewichts (1) liegenden Mittellinie liegen, daß die Stangen (4,5,8,9) des Vibrationszylinders (3) und Selbstausgleichszylinders (7) untereinander gekuppelt sind, daß der Selbstausgleichsmechanismus (6) ein auf die Stangen (8,9) des Selbstausgleichszylinders (7) wirkendes Steuerventil (11) aufweist, um ein Druckfluidum in die oder aus den Steuerkammern (12, 13) im Selbstausgleichszylinder (7) zu- oder abzuführen und daß der Kolben (15) des Selbstausgleichszylinders (7) mit geringer Steifheit mit dem Trägheitsgewicht (1) durch die mit den Steuerkammern (12,13) des Selbstausgleichszylinders (7) in Verbindung stehenden Sammler (14) oder durch eine Feder (22) im Selbstausgleichszylinder (7) verbunden ist.
  2. Pfahlramme nach dem Anspruch 1, dadurch gekennzeichnet, daß das Wechselventil (10) ein durch ein elektrisches Signal ausgelöstes servogesteuertes Ventil ist.
EP19880101219 1987-01-30 1988-01-28 Pfahlramme Revoked EP0276845B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012887A JPS63189522A (ja) 1987-01-30 1987-01-30 杭打ち装置
JP20128/87 1987-01-30

Publications (3)

Publication Number Publication Date
EP0276845A2 EP0276845A2 (de) 1988-08-03
EP0276845A3 EP0276845A3 (en) 1989-10-18
EP0276845B1 true EP0276845B1 (de) 1992-07-22

Family

ID=12018487

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880101219 Revoked EP0276845B1 (de) 1987-01-30 1988-01-28 Pfahlramme

Country Status (3)

Country Link
EP (1) EP0276845B1 (de)
JP (1) JPS63189522A (de)
DE (1) DE3872889T2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9938983B2 (en) 2012-11-07 2018-04-10 Thermodyn Sas Compressor with thrust balancing and method thereof

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2729969B2 (ja) * 1990-03-29 1998-03-18 株式会社高橋エンジニアリング 杭打ち装置
JP3724758B2 (ja) * 1996-12-05 2005-12-07 株式会社小松製作所 切換バルブ装置

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3721095A (en) * 1971-08-23 1973-03-20 Bolt Associates Inc Controllable force method and system of driving piles
SE370099B (de) * 1971-10-18 1974-09-30 B Ludvigson
DE2821339C3 (de) * 1977-05-18 1982-03-04 Kabushiki Kaisha Takahashi Engineering, Tokyo Hydraulische Kolbenzylindervorrichtung zum Erzeugen einer axialen Kolbenschwingung
US4317406A (en) * 1978-05-18 1982-03-02 Kabushiki Kaisha Takahashi Engineering Hydraulic cylinder for generating vibrations
JPS572856A (en) * 1980-06-06 1982-01-08 Showa Alum Corp Cathodically protecting brazing sheet for vacuum brazing
JPS5846963A (ja) * 1981-09-16 1983-03-18 横河電機株式会社 血液透析用超音波検出装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9938983B2 (en) 2012-11-07 2018-04-10 Thermodyn Sas Compressor with thrust balancing and method thereof

Also Published As

Publication number Publication date
EP0276845A3 (en) 1989-10-18
JPS63189522A (ja) 1988-08-05
DE3872889D1 (de) 1992-08-27
EP0276845A2 (de) 1988-08-03
DE3872889T2 (de) 1993-03-04

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