WO2010063764A1 - Mécanisme vibrant pour pilon, et pilon - Google Patents

Mécanisme vibrant pour pilon, et pilon Download PDF

Info

Publication number
WO2010063764A1
WO2010063764A1 PCT/EP2009/066244 EP2009066244W WO2010063764A1 WO 2010063764 A1 WO2010063764 A1 WO 2010063764A1 EP 2009066244 W EP2009066244 W EP 2009066244W WO 2010063764 A1 WO2010063764 A1 WO 2010063764A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
fluid
vibration
vibratory mechanism
vibration member
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.)
Ceased
Application number
PCT/EP2009/066244
Other languages
English (en)
Inventor
Jasper Stefan Winkes
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.)
Fistuca BV
Original Assignee
Fistuca BV
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 Fistuca BV filed Critical Fistuca BV
Priority to EP09765087A priority Critical patent/EP2370642A1/fr
Priority to US13/132,988 priority patent/US20110240323A1/en
Publication of WO2010063764A1 publication Critical patent/WO2010063764A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses

Definitions

  • the invention relates to a vibratory mechanism comprising a static part and a dynamic part being movable with respect to the static part.
  • Such a vibratory mechanism is known from US 5 / 088,565.
  • the static part of the prior art mechanism is attached to a cable of a crane and the dynamic part comprises jaws for clamping a pile to be driven into the ground or to be extracted out of the ground.
  • the dynamic part is provided with a pair of eccentrically rotatable weights which can be rotatably driven by a hydraulic motor. The weights rotate in opposite directions with respect to each other resulting in a vertical vibration of the dynamic part.
  • a disadvantage of the known mechanism is that bearings of the rotatable weights are heavily loaded resulting in relatively high operational costs due to maintenance and replacement of the bearings.
  • SU 631 597 is related to a vibrating hammer which comprises an inner casing that is provided with a crankshaft which is connected to a piston via a connecting rod.
  • the piston is movable within a cylinder.
  • the crankshaft is driven via compressed air which is fed to the cylinder through a pipe being provided with a control valve for allowing compressed air to the cylinder.
  • the mechanism is unbalanced.
  • the inner casing is connected to an outer casing through springs. Under operating conditions, the inner casing will vibrate within the outer casing due to the unbalanced mechanism. Under certain conditions the inner casing hits the outer casing at the upper or lower inner side thereof, depending on the presence of hitting plates at the outer casing.
  • the object of the invention is to provide a simple and robust vibratory mechanism which creates the opportunity to minimize vibrational forces at the static part.
  • the static part is provided with a drivable crankshaft and the dynamic part comprises a housing and a vibration member being drivably coupled to the crank- shaft through a connecting rod and linearly movable with respect to the housing in a direction of vibration, wherein said housing is resiliently coupled to the vibration member via a fluid spring, wherein the mechanism is adapted such that under operating conditions the vibration member is driven upon driving the crankshaft by driving means.
  • the vibration member Upon driving the crankshaft the vibration member will vibrate linearly with respect to the housing of the dynamic part. Due to the resilient coupling between the vibration member and the housing, the housing of the dynamic part will vibrate as well. In case the vibratory mechanism is applied in a pile driver the housing of the dynamic part may be provided with clamping means for clamping a pile.
  • the mechanism according to the invention provides the opportunity to select the rotation speed of the crankshaft, the weights of the vibration member and the housing and the degree of resiliency between the vibration member and the housing such that the dynamic part vibrates at a certain frequency, whereas transfer of inertia forces in the mechanism via the crankshaft to the remainder of the static part is minimized.
  • the reciprocating forces of the first order can be used to balance the vibrational forces of the housing of the dynamic part on the crankshaft under certain conditions. This means that forces on crankshaft bearings in the static part are minimized, hence reducing wear and operational costs.
  • *reciprocating forces of the first order is typically used in case of balancing reciprocating piston-crank- connecting rod mechanisms, such as present in internal com- bustion engines, in order to indicate inertial forces of the piston acting in the direction of piston movement and occurring at the frequency of rotation of the crank.
  • crank-connecting rod mechanism is that it can be built in a compact way compared to a conventional dynamic part comprising oppositely rotating weights, since in the latter case at least two rotatable weights must be located next to each other as seen in horizontal direction so as to achieve a vertical vibration.
  • sudden peak forces on the housing are not directly transferred to the vibration member and the static part.
  • Such a sudden peak force may typically happen in a pile driver if a pile is fixed to the housing to be driven into the ground and the pile touches a rigid layer or a stone or the like.
  • the resulting so-called rebound effect is smoothly transferred to the static part by the mechanism according to the invention.
  • the fluid spring of the mechanism could be replaced by an alternative resiliency, for example a coil spring.
  • crankshaft and the piston in the mechanism as disclosed in SU 631 597 is mounted in the same inner casing.
  • This is fundamentally different from the mechanism according to the present invention since the known mechanism does not provide the opportunity to create a static part having minimized vibrational forces; on the contrary the vibrational forces are required to effect hammering of the inner casing onto the outer casing. This results in heavy loads onto the crankshaft bearings.
  • the vibratory mechanism according to the present invention enables to solve the problem due to providing the static part with the crankshaft and providing the dynamic part with the vibration member. This also allows to have a direct and simple coupling between the crankshaft and a driving means for driving the crankshaft. Furthermore, the crankshaft bearings are not adversely affected by sudden loads on the dynamic part.
  • the characteristics of the fluid spring can be adjusted.
  • the characteris- tics can be manipulated such that the natural frequency of the mass-spring system comprising the vibration member and the fluid spring is similar to or approaches the frequency of the crankshaft under operating conditions. If this situation is achieved under operating conditions the inertia force of the vibration member on the crankshaft is minimized.
  • the relationship between the mentioned frequencies may be slightly influenced by the weight of the housing of the dynamic part, but this weight will be high with respect to the weight of the vibration member, in practice, such that the weight ratio is rather stable under operating conditions.
  • the natural frequency of the mass-spring system comprising the vibration member and the fluid spring is much higher than the natural frequency of the mass-spring system comprising the housing of the dynamic part and the fluid spring.
  • the fluid spring characteristics can be influenced by modifying its fluid properties, for example.
  • the spring characteristics could be influenced by an actuator.
  • the vibration member is a piston and the housing comprises a cylinder within which the piston is slidable, and the fluid spring is formed by a fluid chamber being present between the piston and the cylinder.
  • the fluid chamber functions as a fluid spring. It is noted that a part of the connecting rod weight contributes to the vibration member weight.
  • the fluid spring is formed by two fluid chambers located at opposite sides of the piston. This provides more flexibility in influencing the spring characteristics of the resiliency between the piston and the cylinder.
  • the fluid chambers may be allowed to communicate with each other through a controllable valve.
  • a controllable valve When opening the valve and moving the piston within the cylinder the fluid will flow from the fluid chamber of which the volume reduces to the fluid chamber of which the volume increases. If the valve is open such that no compression/expansion occurs in the fluid chambers the spring characteristics created by the fluid chambers are negligible. This may be desired under certain conditions, for example in case of a pile driver which is starting-up. In that case the housing should not be driven before the piston vibration has reached a certain frequency.
  • the valve When the valve is open the piston may vibrate within the cylinder without driving the housing of the dynamic part.
  • the valve may be closed at a piston frequency exceeding for example 1200 rpm, such that the starting-up period during which the frequency of the housing of the dynamic part is relatively low, is short.
  • the fluid chambers communicate with the ambient air through a controllable valve during the starting-up period.
  • the mechanism com- prises at least two vibration members, wherein the mechanism is adapted such that under operating conditions the vibration members can be driven in opposite directions, for example in counter phase.
  • the vibration members can be driven in opposite directions, for example in counter phase.
  • the vibration frequency of the vibration members to a relatively high level, for example the operational frequency in case of a pile driver, whereas the vibration of the housing in the direction of vibration remains negligible, because the forces of the oppositely moving vibration members on the housing via the resiliency can be balanced.
  • the characteristics of the resiliency between the housing and the vibration members can be varied.
  • the resiliency can be adjusted such that the counter force of the resiliency on the vibration members at least partly reduce the inertia forces of the vibration members on the static part during the increase of the vibration frequency of the vibration members whereas the vibration of the housing remains negligible.
  • the mechanism can be set such that the vibration members move synchronously in the same direction. In practice, during increase of the frequency the resiliency will be adjusted to a stiffer level.
  • the vibrating members are pistons moving oppositely in corresponding cylinders and the resiliency is formed by the fluid chambers located at opposite sides of each of the pistons
  • the fluid pressure in the fluid chambers can be increased during the period of increasing the frequency of the reciprocating speed of the pistons in order to reduce the reciprocating inertial forces of the pistons on the static part.
  • the fluid chamber of one cylinder can communicate with the fluid chamber of the other cylinder such that under operating conditions a decreasing fluid chamber volume in one cylinder can communicate with an increasing fluid chamber volume in the other cylinder.
  • the fluid chambers can be connected to each other in fluid communication which means that the piston in one cylinder pushes the fluid from the fluid chamber in that cylinder to the fluid chamber of the other cylinder, whereas the piston of the other cylinder synchronously sucks the fluid from the one cylinder.
  • the pistons vibrate within the cylinders without driving the housing of the dynamic part.
  • two cylinders may be disposed parallel to each other and the fluid chambers at the same side of the pistons can be con- nected to each other.
  • the pistons can be driven in counter phase such that the volumes of the mutually connected fluid chambers at the same side of the pistons also vary in counter phase.
  • the sum of the volumes of the connected fluid chambers substan- tially remains the same.
  • the fluid communication can be effected by a controllable valve or the like.
  • the mechanism may comprise adjusting means for adjusting the stroke of the vibration member with respect to the eccentricity of the crankshaft in order to minimize the amplitude of the vibration member during a starting-up period.
  • the fluid spring can communicate with compressing means for increasing or decreasing the pressure of the fluid in the fluid spring. This feature provides the opportunity to influence the amplitude of the housing, for example.
  • a variable pressure, depending on the operation frequency is also conceivable.
  • Alternative adjusting means for manipulating the fluid spring characteristics are conceivable.
  • the housing of the dynamic part and the static part may be connected to each other via a spring and/or a damper so as to create a coupling between the static part and the dynamic part in addition to the coupling via the connecting rod, and to reduce any transfer of vibrations from the dynamic part to the static part.
  • a first part of the con- necting rod is guided by a crosshead guide in the static part or in the dynamic part and a second part thereof being fixed to the vibration member is movable along its longitudinal centre line only. This means that the second part has a one- dimensional motion in the direction of vibration of the vi- bration member.
  • the vibration speed of the vibration member, the weight of the housing and the characteristics of the resiliency between the housing and the vibration member are selected such that the vibration member and the housing substantially vibrate in counter phase under operating conditions, and the weight of the vibration member is selected such that its inertia force of the first order substantially balances the inertia force of the housing.
  • the weight of the vibration member and the housing may be selected first and the characteristics of the resiliency between the housing and the vibration member is then adjusted to optimize the functioning of the mechanism.
  • the characteristics of the resiliency can be influenced by the volume of the fluid chamber in case of a fluid spring.
  • the invention is also related to a pile driver comprising a vibratory mechanism as described hereinbefore.
  • the static part of the vibratory mechanism may be provided with driving means for driving the crankshaft.
  • driving means for driving the crankshaft.
  • the driving means is an internal combustion engine.
  • Fig. 1 is a schematic view of an embodiment of the vibratory mechanism according to the invention.
  • Fig. 2 is a perspective view of an alternative embodiment of the vibratory mechanism of Fig. 1.
  • Fig. 3 is a similar view as Fig. 1 of an alternative embodiment on a smaller scale.
  • Fig. 4 is a similar view as Fig. 2 of another al- ternative embodiment.
  • Fig. 1 shows an embodiment of the vibratory mechanism 1 according to the invention.
  • the vibratory mechanism 1 is part of a pile driver in this example, but may be suitable for alternative technical devices.
  • the vibratory mechanism 1 as shown in Fig. 1 comprises a static part 2 and a dynamic part 3.
  • the dynamic part 3 is movable with respect to the static part 2.
  • the static part 2 is provided with a lifting eye 4.
  • the lifting eye 4 suspends from a cable of a crane (not shown) .
  • the dynamic part 3 is provided with a pair of clamps 5 for clamping a pile to be driven into the ground or to be extracted out of the ground.
  • the pair of clamps 5 may be driven mechanically, hydraulically or the like.
  • the dynamic part 3 os- cillates in vertical direction at a predetermined frequency and with a predetermined amplitude with respect to the static part 2.
  • Fig. 1 shows that the static part 2 is provided with a drivable crankshaft 6.
  • the crankshaft 6 comprises two crankpins located eccentrically with respect to the centre line of the crankshaft 6.
  • the dynamic part 3 is provided with two pistons 7 as vibration members.
  • Each of the pistons 7 is coupled to the crankshaft 6 through a connecting rod 8.
  • the connecting rod 8 comprises a first part 9 which is guided by a crosshead guide 10 in the static part 2, and a second part 11 which is movable along its longitudinal centre line only.
  • the piston 7 is fixed to the second part 11.
  • a through hole in the dynamic part 3 through which the second part 11 of the connecting rod 8 moves up and down may have the shape of the cross-sectional area of the second part 11 and the dimensions of the cross- sectional area of the through hole may be slightly larger than those of the second part 11.
  • crankshaft 6 is driven by an internal combustion engine 12.
  • Alternative driving means are conceivable, for example a hydraulic or electric motor.
  • An advantage of applying the internal combustion engine 12 is that it can be used as stand-alone unit in the static part 2.
  • the dynamic part 3 further comprises a housing in the form of cylinders 13 which function as guides for guiding the pistons 7.
  • the cylinders 13 have a fixed position with respect to the dynamic part 3.
  • the pistons 7 are slidable within the cylinders 13.
  • the cylinders 13 are filled with a fluid, for example air.
  • each of the cylinders 13 the pis- ton 7 divides the cylinder space into two fluid chambers 14, 15 located at opposite sides of the piston 7. If the fluid chambers 14, 15 are closed spaces or nearly closed spaces, they form a fluid spring. This means that the housing of the dynamic part 3 or the cylinder 13 is resiliently coupled to the piston 7. In case the fluid is a gas, the fluid chambers 14, 15 form a gas spring.
  • the fluid spring characteristics can be adjusted by modifying the fluid properties in the fluid chambers 14, 15.
  • the fluid chambers 14, 15 can communicate with each other through a controllable valve 16.
  • the valve 16 When the valve 16 is fully opened the fluid chambers 14, 15 communicate with each other. This means that in case of a downward displacement of the piston 7 the fluid from the lower fluid chamber 15 is pressed to the upper fluid chamber 14 via the valve 16. In that case the housing of the dynamic part 3 or the cylinder 13 will not follow the displacement of the piston 7.
  • the valve 16 is closed and the piston 7 is displaced downwardly the fluid in the lower fluid chamber 15 will be compressed and the fluid in the upper fluid chamber 14 will be expanded. As a result the cylinder 13 will follow this displacement in downward direction.
  • the weight of the housing of the dynamic part 3 and the properties of the fluid in the fluid chambers 14, 15 the housing of the dynamic part 3 will follow the piston movement at a certain phase shift, comparable to a conventional spring-mass system.
  • the weights of the pistons 7 and the housing 13 are more or less fixed; in practice it is desired that the natural frequency of the spring-mass system comprising the pistons 7 and the fluid springs is similar to the actual frequency of the crankshaft 6 under operating conditions. This can be achieved by manipulating the characteristics of the fluid spring under operating conditions.
  • the valve 16 can also be used in case of starting- up the vibratory mechanism 1. In case of driving a pile into the ground it may be desired to avoid low frequency vibrations which might occur during a starting-up period of the mechanism 1. This can be avoided by opening the valve 16 during increase of frequency of the piston 7 such that the housing of the dynamic part 3 remains in a non-vibration mode. Once a predetermined desired frequency has been reached the valve 16 is closed and the starting-up period of vibration of the housing of the dynamic part 3 up to its desired frequency is relatively short.
  • an adjusting mechanism (not shown) for adjusting the piston stroke with respect to the eccentricity of the crankshaft 6 may be present.
  • the spring characteristics of the fluid chambers 14, 15 can be influenced by varying the pressure of the fluid. This can be achieved by applying a compressor (not shown) which increases or decreases the fluid pressure in the fluid chambers 14, 15 via a press line 17.
  • fluid chambers 14, 15 can communicate with each other. It is also possible to vent the fluid chambers 14, 15 to the ambient air during the starting-up period, such that pressure build-up in the fluid chambers 14, 15 is negligible.
  • the vibratory mechanism 1 further comprises springs 18 to hold the static part 2 and the dynamic part 3 at a substantially constant distance with respect to each other.
  • the spring 18 may also have damping characteristics to eliminate any residual vibrations between the static part 2 and the dynamic part 3.
  • Fig. 2 shows an alternative embodiment of the vibratory mechanism 1 as part of a pile driver.
  • the reference signs of the embodiment of Fig. 2 refer to similar components as being present in the embodiment of Fig. 1.
  • the embodiment as shown in Fig. 2 is provided with a single piston 7. This provides the opportunity to design a compact vibratory mecha- nism 1 as seen in a direction perpendicular to the direction of vibration of the piston 7.
  • Fig. 3 shows another alternative embodiment, which is provided with four pistons 7 in line.
  • the reference signs in Fig. 3 refer to corresponding components as shown in Fig. 1. It can be seen that each piston 7 is coupled to a separate crankshaft 6a-6d. Two inner crankshafts 6b, 6c located between two outer crankshafts 6a, 6d are driven by the internal combustion engine 12 via a first transmission 19 and the outer crankshafts 6a, 6d are driven via a second transmission 20. During a starting-up period the first and second transmissions 19, 20 are controlled such that the two inner pistons 7 located in the middle of the dynamic part 3 are moving in counter phase with respect to the two outer pistons 7 located at the outer sides of the dynamic part 3, as indicated by arrows in Fig. 3.
  • valves 16 are open.
  • both inner pistons 7 move upwardly and both outer pistons 7 move downwardly the fluid in the upper fluid chambers 14 of both inner cylinders 13 flow to the associat- ing upper fluid chambers 14 of both outer cylinders 13, and the fluid in the lower fluid chambers 15 of both outer cylinders 13 flow to the associating lower fluid chambers 15 of both middle cylinders 13.
  • the first and/or second transmission 19, 20 can be controlled such that the movement of the inner pistons 7 is opposite to the movement of the outer pistons 7, whereas the crankshafts 6a-6d remain running at the operational frequency.
  • the crosshead guide 10 is disposed in the dynamic part 3.
  • the advantage of this configuration is that it improves the flexibility of mu- tual displacement of the static part 2 with respect to the dynamic part 3.
  • Fig. 4 shows another alternative embodiment. This embodiment is comparable to that of Fig. 2 and corresponding reference signs are used.
  • the cross-head guide 10 is provided in the dynamic part 3.
  • Fig. 2 also illustrates that a combustion engine 12 drives the crankshaft 6 of the vibratory mechanism 1.
  • the piston is resiliently coupled to the housing of the dynamic part through a mechanical spring instead of a fluid spring.
  • the crankshaft may be replaced by an alternative shaft including an eccentric to which the connecting rod can be pivotalIy mounted.
  • the mechanism is not only suitable for pile drivers, but it can be applied in alternative devices, for example for inserting elements into the ground by vibration, for compacting soils, cement, concrete, asphalt or the like.
  • the invention is also related to the following aspects:
  • a vibratory mechanism (1) for a pile driver comprising a static part (2) and a dynamic part (3) being movable with respect to the static part (2), wherein the static part (2) is provided with a drivable crankshaft (6) and the dynamic part (3) comprises a housing (13) and a vibration member (7) being drivably coupled to the crankshaft
  • Aspect 3 A vibratory mechanism (1) according to aspect 2, wherein the vibration member is a piston (7) and the housing comprises a cylinder (13) within which the piston
  • the fluid spring is formed by a fluid chamber (14, 15) being present between the piston (7) and the cylinder (13) .
  • a vibratory mechanism (1) according to aspect 3 wherein the fluid spring is formed by two fluid chambers (14, 15) located at opposite sides of the piston (7).
  • Aspect 5 A vibratory mechanism (1) according to aspect 4, wherein the fluid chambers (14, 15) can communicate with each other through a controllable valve (16) .
  • Aspect 6 A vibratory mechanism (1) according to one of the preceding aspects, wherein the mechanism (1) comprises at least two vibration members (7), and wherein the mechanism (1) is adapted such that under operating conditions the vibration members (7) can be driven in opposite directions.
  • Aspect 9 A vibratory mechanism (1) according to one of the preceding aspects, wherein the mechanism (1) comprises adjusting means for adjusting the stroke of the vibration member (7) with respect to the eccentricity of the crankshaft (6) .
  • Aspect 10 A vibratory mechanism (1) according to one of the preceding aspects, wherein the housing (13) of the dynamic part (3) and the static part (2) are connected to each other via a spring and/or a damper (18) .
  • a vibratory mechanism (1) according to one of the preceding aspects, wherein a first part (9) of the connecting rod (8) is guided by a crosshead guide (10) in the static part (2) or in the dynamic part (3) and a second part (11) thereof being fixed to the vibration member (7) is movable along its longitudinal centre line only.
  • a vibratory mechanism (1) according to one of the preceding aspects, wherein the vibration speed of the vibration member (7), the weight of the housing (13) and the characteristics of the resiliency between the housing (13) and the vibration member (7) are selected such that the vibration member (7) and the housing (13) substantially vibrate in counter phase under operating conditions, and wherein the weight of the vibration member (7) is selected such that its inertia force of the first order substantially balances the inertia force of the housing (13) .
  • Aspect 13 ⁇ pile driver comprising a vibratory mechanism (1) according to one of the preceding aspects.
  • Aspect 14 A pile driver according to aspect 13, wherein the static part (2) is provided with driving means (12) for driving the crankshaft (6) .

Landscapes

  • 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)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Abstract

L’invention concerne un mécanisme vibrant (1) pour un pilon. Ledit mécanisme comprend une partie statique (2) et une partie dynamique (3). La partie dynamique (3) est mobile par rapport à la partie statique (3). La partie statique (2) est équipée d’un vilebrequin pouvant être entraîné (6) et la partie dynamique (3) comprend un logement (13) et un élément vibrant (7). L’élément vibrant (7) est accouplé en entraînement au vilebrequin (6) par le biais d’une tige de connexion (8) et est mobile linéairement par rapport au logement (13) dans une direction de vibration. Le logement (13) est accouplé de façon élastique à l’élément vibrant (7).
PCT/EP2009/066244 2008-12-04 2009-12-02 Mécanisme vibrant pour pilon, et pilon Ceased WO2010063764A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP09765087A EP2370642A1 (fr) 2008-12-04 2009-12-02 Mécanisme vibrant pour pilon, et pilon
US13/132,988 US20110240323A1 (en) 2008-12-04 2009-12-02 vibratory mechanism for a pile driver and a pile driver

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP08170711.9 2008-12-04
EP08170711A EP2194191A1 (fr) 2008-12-04 2008-12-04 Mécanisme vibratoire pour appareil de fonçage de pieux et appareil de fonçage de pieux

Publications (1)

Publication Number Publication Date
WO2010063764A1 true WO2010063764A1 (fr) 2010-06-10

Family

ID=40283722

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/066244 Ceased WO2010063764A1 (fr) 2008-12-04 2009-12-02 Mécanisme vibrant pour pilon, et pilon

Country Status (3)

Country Link
US (1) US20110240323A1 (fr)
EP (2) EP2194191A1 (fr)
WO (1) WO2010063764A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150027744A1 (en) * 2012-03-15 2015-01-29 Aydin Ozkan Variable moment resonance-free vibro hammer
DE102014016400B4 (de) * 2014-11-07 2019-01-17 Thyssenkrupp Ag Vibrationsrammanordnung mit integriertem Antriebsaggregat
US11338326B2 (en) * 2019-04-07 2022-05-24 Resonance Technology International Inc. Single-mass, one-dimensional resonant driver
WO2021075971A1 (fr) 2019-10-18 2021-04-22 Cape Holland Holding B.V. Système vibrant et procédé d'insertion d'un élément de fondation dans le sol à l'aide d'éléments souples
CN114351704B (zh) * 2021-12-30 2022-11-18 徐州倍思特自动化工程有限公司 一种防偏移自锁微调式市政工程打桩装置
CN114354250A (zh) * 2022-01-04 2022-04-15 屠文水 一种建筑工程和道路工程质量检测设备及检测方法
NL2035355B1 (en) * 2023-07-12 2025-01-27 Iqip Holding Bv Vibrator assembly

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1100918A (en) * 1965-03-24 1968-01-24 Albert George Bodine Oscillator means for a vibratory pile driver
US3996912A (en) * 1971-05-06 1976-12-14 Allis-Chalmers Corporation Low compression ratio diesel engine
SU631597A1 (ru) * 1977-04-19 1978-11-05 Protsko Anatolij A Вибромолот
JPS5729730A (en) * 1980-07-31 1982-02-17 Kazuo Murazaki Vibrohammer
GB2095731A (en) * 1981-03-28 1982-10-06 Schmidt Paul Apparatus for driving and extracting sheet piles and other members
SU1481325A1 (ru) * 1986-06-09 1989-05-23 Ленинградское Высшее Военное Инженерное Строительное Краснознаменное Училище Им.Ген.Армии А.Н.Комаровского Вибромолот
SU1730359A2 (ru) * 1990-01-22 1992-04-30 Ленинградское высшее военное инженерное строительное Краснознаменное училище им.генерала армии А.Н.Комаровского Вибромолот
CN2818553Y (zh) * 2005-01-31 2006-09-20 中南大学 液压振动沉拔桩机调矩装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1954411A (en) * 1930-07-25 1934-04-10 Alfred A Heitzman Pneumatic hammer
US3054463A (en) * 1958-01-24 1962-09-18 Albert G Bodine Acoustic apparatus for driving piles
US3277970A (en) * 1965-03-30 1966-10-11 Albert G Bodine Sonic driver with pneumatic capacitance
US3344874A (en) * 1965-05-28 1967-10-03 Albert G Bodine Low-impedance isolator for vibratory pile driver machines
US3869003A (en) * 1971-12-25 1975-03-04 Sanwa Kizai Co Ltd Pile drivers
ATE31334T1 (de) * 1983-09-19 1987-12-15 Simson & Partner Vorrichtung zum rammen und ziehen.
US5088565A (en) 1990-03-23 1992-02-18 J & M Hydraulic Systems, Inc. Vibratory pile driver
US6378951B1 (en) * 1997-07-23 2002-04-30 Hydroacoustics, Inc. Vibratory pavement breaker

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1100918A (en) * 1965-03-24 1968-01-24 Albert George Bodine Oscillator means for a vibratory pile driver
US3996912A (en) * 1971-05-06 1976-12-14 Allis-Chalmers Corporation Low compression ratio diesel engine
SU631597A1 (ru) * 1977-04-19 1978-11-05 Protsko Anatolij A Вибромолот
JPS5729730A (en) * 1980-07-31 1982-02-17 Kazuo Murazaki Vibrohammer
GB2095731A (en) * 1981-03-28 1982-10-06 Schmidt Paul Apparatus for driving and extracting sheet piles and other members
SU1481325A1 (ru) * 1986-06-09 1989-05-23 Ленинградское Высшее Военное Инженерное Строительное Краснознаменное Училище Им.Ген.Армии А.Н.Комаровского Вибромолот
SU1730359A2 (ru) * 1990-01-22 1992-04-30 Ленинградское высшее военное инженерное строительное Краснознаменное училище им.генерала армии А.Н.Комаровского Вибромолот
CN2818553Y (zh) * 2005-01-31 2006-09-20 中南大学 液压振动沉拔桩机调矩装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
DATABASE WPI Week 197933, Derwent World Patents Index; AN 1979-H0826B, XP002513466 *

Also Published As

Publication number Publication date
EP2194191A1 (fr) 2010-06-09
US20110240323A1 (en) 2011-10-06
EP2370642A1 (fr) 2011-10-05

Similar Documents

Publication Publication Date Title
US20110240323A1 (en) vibratory mechanism for a pile driver and a pile driver
US6742960B2 (en) Vibratory compactor and method of using same
AU2004250089B2 (en) Sonic heads and assemblies and uses thereof
US4015909A (en) Tamping machine
US6584866B2 (en) Working tool, in particular rammer for soil compaction
JPH09512618A (ja) 自由慣性力の中和化を有する往復動機関
EP4045721A1 (fr) Système vibrant et procédé d'insertion d'un élément de fondation dans le sol à l'aide d'éléments souples
CA2396499A1 (fr) Dispositif de compression pour effectuer des operations de compression sur des corps moules a base de matieres granuleuses
KR20060040722A (ko) 왕복 내연기관
US11859532B2 (en) Vibratory plate and its engine
JP4435210B2 (ja) 回転・往復動装置
EP2582955B1 (fr) Nouveau moteur à combustion interne à cycle alterné à taux de compression variable régulé - cvcr -
RU2450860C2 (ru) Конусная дробилка
US6772962B2 (en) Low frequency acoustic converter
JP2003083396A (ja) レシプロ式エンジンのバランサ
CA1233061A (fr) Dispositif compacteur de sol, de beton et d'autres materiaux
SU1498559A1 (ru) Вибровозбудитель
SU631597A1 (ru) Вибромолот
SU1187501A1 (ru) Вибротрамбовка
AU2008200807A1 (en) Sonic Heads and Asemblies and Uses Thereof
KR800001232B1 (ko) 끌의 충격장치
JPH0681900A (ja) 内燃機関の振動低減装置
KR101876852B1 (ko) 출력 제어용 실린더베이스를 구비하는 자유 피스톤 엔진
KR20060088209A (ko) 자동차의 밸런스 액츄에이터
JPH0127201B2 (fr)

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09765087

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 13132988

Country of ref document: US

WWE Wipo information: entry into national phase

Ref document number: 2009765087

Country of ref document: EP