US3714789A - Automatically self-regulating variable-stroke, variable-rate and quiet-operating pile driver method and system - Google Patents

Automatically self-regulating variable-stroke, variable-rate and quiet-operating pile driver method and system Download PDF

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Publication number
US3714789A
US3714789A US00102325A US3714789DA US3714789A US 3714789 A US3714789 A US 3714789A US 00102325 A US00102325 A US 00102325A US 3714789D A US3714789D A US 3714789DA US 3714789 A US3714789 A US 3714789A
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Prior art keywords
pile
piston weight
bottom assembly
cylinder
fluid
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US00102325A
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English (en)
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S Chelminski
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Teledyne Bolt Inc
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Bolt Associates Inc
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Assigned to CONNECTICUT BANK AND TRUST COMPANY, N.A., THE reassignment CONNECTICUT BANK AND TRUST COMPANY, N.A., THE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BOLT TECHNOLOGY CORPORATION, A CT. CORP.
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    • 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
    • E02D13/04—Guide devices; Guide frames
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D11/00—Methods or apparatus specially adapted for both placing and removing sheet pile bulkheads, piles, or mould-pipes
    • 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
    • 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
    • E02D13/08—Removing obstacles
    • 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
    • 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
    • E02D7/10—Power-driven drivers with pressure-actuated hammer, i.e. the pressure fluid acting directly on the hammer structure
    • 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
    • E02D7/12—Drivers with explosion chambers
    • E02D7/125—Diesel drivers

Definitions

  • ABSTRACT Automatically self-regulating variable-stroke, variablerate and quiet-operating pile driver method and system are disclosed in which a massive piston weight is bounced upon a cushion of pressure fluid, the pile driver advantageously being adapted for operation in four different modes: (1) only double-acting, (2) single-acting automatically converting to double-acting at maximum stroke travel, (3) only single-acting, (4) pre-stressing plus impacting plus thrusting mode, and (5) pile extraction mode.
  • the prolongeddownward push YesiITtTngfroniTlie pfe ssiTzed fluid cfioh d bouncing action is more effective than the conven-' tional sharp hammer type blow resulting from impact of one solid mass against another.
  • the stroke of the piston weight automatically shortens while the number of bounces per minute automatically increase thus increasing the rate of the quiet powerful bounce thrusts for driving the pile faster, and when harder strata are encountered, the piston weight automatically bounces higher providing a longer stroke with fewer bounces per minute, thus increasing the force of each quiet powerful thrust for overcoming the increased impedance being encountered.
  • the double-acting mode when harder strata are encountered, the velocity and stroke length of the piston weight increase automatically to deliver more powerful thrusts.
  • a relatively large number of driving thrusts per minute can be provided in the double-acting mode by'changing the head plug mass to shorten the maximum stroke length to increase the frequency of thrusts per minute.
  • the noise of metal-to-metal Contact blows can be avoided, and in addition a muffler housing surrounding the ports through which the expanded pressure fluid is released muffles the sound of the flow of the fluid, such as air or steam; this muffler also serving to separate lubricating oil from the released fluid.
  • a cylinder bottom assembly below the bounce chamber is coupled to the pile being driven to transmit the quiet powerful bounce thrusts to the pile, moving in accordancewith the pile motion, and a driving fluid storage chamber and valve mechanism associated with this assembly control the flow of the pressure fluid in an automatically self-regulating manner to seek the most effective driving action from moment-to-moment as the pile encounters different strata. If desired, the bouncing action of the cushion of pressure fluid can be altered to permit the piston weight to strike bottom slightly to provide the driving mode (4) above.
  • a self-contained lubrication system may be actuated by the pressure impulses in the bounce chamber.
  • Such conventional pile drivers have a disadvantage in the fact that they transmit the energy of the falling mass by a strikingtype blow on an anvil surface.
  • Each blow produces a very loud noisy sound of metal-to-metal contact which is annoying to many persons, including persons who are located at a relatively great distance from the construction site.
  • This noisy blow especially in the conventional steam-type open striking hammer, is, in my opinion, a
  • shock-absorbing materials Because of the metal-to-metal contact, the impact tends to be destructive to the pile driver itself and to the pile being driven. There are many instances when shock-absorbing materials must be interposed between the striking parts and the pile.
  • the shock-absorbing materials which are conventionally used are wooden blocks, or pads, of phenolic laminates, or other plastic materials. The use of such shock absorbers wastes energy, and since they are expendable and need to be replaced, there is a resulting added cost for the pile driving operation.
  • Another objects of the present invention are to provide a novel advantageous and effective automatically selfregulating variable-stroke, variable-rate and quietoperating pile driver method and system wherein a massive piston weight is bounced upon a cushion of pressure fluid.
  • lt is an advantage of a pile driver embodying the present invention that a prolonged downward push or thrust results from the pressurized fluid-cushioned bouncing action of the massive piston weight assembly.
  • This prolonged downward push or thrust is more effective and more efficient than the conventional sharp hammer-type blow resulting from impact of a solid mass against an anvil.
  • This prolonged downward push or thrust is less damaging to the pile driver and to the pile than the sharp hammer-type blow ofa solid mass against an anvil which is typical of many prior art pile drivers.
  • the pile driver embodying these aspects of the invention is adapted for operation in five different modes: (1) solely double-acting, (2) single-acting automatically converting to double-acting at the maximum stroke travel, (3) only single-acting, (4) pre-stressing plus impacting plus thrusting mode, and (5) in a pile extraction mode.
  • the pile driver methods and systems embodying the present invention are those resulting from the fact that in the single-acting mode when the pile being driven encounters softer strata in the earth, the stroke of the piston weight automatically shortens while the number of bounces per minute automatically increase, thus increasing the rate of the quiet powerful bounce thrusts for driving the pile faster.
  • the piston weight automatically bounces higher providing a longer stroke with fewer bounces per minute, thus increasing the force of each quiet powerful thrust for overcoming the increased impedance being encountered.
  • the present invention can be equipped with a muffler housing surrounding the ports through which the expanded pressure fluid is released to muffle the sound of the escaping pressure fluid, such as air or steam.
  • the muffler also can be used to separate lubricating oil from the released fluid.
  • the quiet, powerful driving thrust applied to the top of the pile endures for a longer period of time during each driving bounce, and destructive forces on the pile are substantially reduced as compared to a prior art impact-type pile driver providing a comparable driving rate.
  • a controlled release of pressure applied to the pile is provided.
  • the pressurized driving fluid is released into the bounce chamber from a driving energy chamber.
  • This driving energy chamber is positioned closely adjacent the bounce chamber, and it is adapted to communicate directly with the bounce chamber when a release valve is actuated by the piston weight.
  • the piston weight is re-accelerated upwardly, in a bounce by a cushion of the pressure fluid, thereby providing further extension in time of the useful driving thrust, thereby driving piles in an effective and efficient method.
  • the energy provided by. the injected pressurized fluid is effectively utilized because the portion of this energy which was not used to drivethe pile is employed to re-accelerate the piston weight upwardly at an increased velocity.
  • this portion of the energy is substantially conserved (minus friction and heat losses) by being converted into increased potential energy to be utilized to provide a more powerful thrust on the next bounce.
  • the deceleration and re-acceleration of the massive piston weight effectively utilizes not only the force applied in decelerating the piston weight at the end of its downward stroke, but also effectively utilizes the reaction to the re-accelerating force applied to the piston weight during the period of time such force is being apresulting driving mode on the pile is to pre-stress the pile, then impact, then thrust it down.
  • the pre-stressing occurs while the cushion of pressure fluid is decelerating the piston. This pre-stressing removes all of the play between the cylinder bottom assembly and the pile. Then, when the piston weight strikes bottom with an' impact, the resulting blow starts the pile moving downwardly.
  • the subsequent re-acceleration of the piston weight upwardly by the pressure fluid provides an enduring thrust which continues to push the moving pile down further.
  • the cylinder bottom assembly includes a second piston located below the bounce chamber in which the pressure fluid operates.
  • This second piston is coupled to the pile being driven to transmit the quiet powerful bounce thrusts to the pile, moving in accordance with the pile motion.
  • a driving energy pressurized fluid chamber is associated with this second piston and a valve mechanism injects a quantity of the pressure fluid automatically from the driving energy chamber into the bounce chamber.
  • a self-regulating driving action occurs as explained above to seek'the most effective driving action from moment-to-moment as the pile encounters different strata.
  • An advantageous self-contained lubrication system is actuated by the pressure impulses in the bounce .chamber.
  • a muffler housing surrounds the ports through which the expanded pressure fluid is discharged into the atmosphere to muffle the sound of the flow of fluid. This muffler also serves to separate the lubricating oil from the discharged fluid so as to recapture the lubricating oil. This-recaptured oil is returned to the self-contained lubricating system for re-use therein.
  • the pressure fluid utilized can be compressed air or steam or any other suitable pressurized gas'or vapor.
  • pressurized fluid or pressurefluid is intended to include compressed air, steam or other suitable pressurized gas or vapor. In the illustrative embodiments shown, it is my preference to utilize compressed air as the pressurized fluid to operate the pile driver.
  • FIG. 1 is a side elevational view of a pressure fluid actuated pile driver system embodying the present invention, shown on greatly reduced scale from actual.
  • FIG. 2 is a cross-sectional view taken along the line 2-2 in FIG. 1 as seen looking downward, being shown on a slightly larger scale than FIG. 1;
  • FIG. 3 is a vertical axial sectional view, shown somewhat further enlarged, with the massive piston weight being shown descending and coming into contact with the control valve actuator;
  • FIG. 4 is a partial cross-sectional view taken along the line 4-4 in FIG. 3 as seen looking downward;
  • FIG. 7 is drawn on a scale of approximately onehalf actual size
  • FIG. 8 is an elevational sectional view of the inlet arrangement for the pressurized fluid, with the connection for injecting the lubricating oil into the pressure fluid being shown;
  • FIGS. 9, 10, 1 1, 12, 13 and 14 are vertical axial sectional views similar to FIG. 3, but shown on somewhat smaller scale than in FIG. 3. These FIGS. 9, 10, 11, 12, 13 and 14 show the successive operating positions of the few moving parts of the pile driver system occurring during one cycle of'operation for delivering a powerful push or thrust to the pile being driven. It is noted that the operating positions shown in FIG. 3 are intermediate those shown in FIGS. 9 and 10;
  • FIG. 14 shows the massive piston weight being operated in the double-acting mode
  • FIG. 15 is a vertical axial sectional view of the upper portion of the pile driver, with the operation being in the single-acting mode;
  • FIG. 16 is similar to FIG. 15, except that the operating mode issingle-acting converting to double-acting at maximum stroke travel as shown;
  • FIG. 17 is a side elevational view of the pile driver operating in the extraction mode with a pressure fluid cylinder and piston included in the suspension line for limiting the maximum load applied to the suspension equipment, such as a crane, and for isolating the suspension from the jarring effects of the pile driver when acting in the extraction mode;
  • FIG. 18 is a side elevational view and partial sectional view as seen along the line l8l8 in FIG. 17;
  • FIG. 19 is an elevational sectional view of the pile driver adapter and conical guide used for driving wooden piles
  • FIG. 20 is a vertical axial sectional view showing a modified embodiment of the invention.
  • FIG. 21 is a vertical axial sectional view of another embodiment.
  • the pile driver system 20 comprises a cylinder wall 22 surrounding a cylinder 23 provided with a massive piston weight assembly, generally indicated at 24 (See FIG. 3).
  • a massive piston weight assembly generally indicated at 24 (See FIG. 3).
  • a cylinder bottom assembly generally indicated at 26, effectively closing off the lower end of the cylinder wall 22.
  • the cylinder bottom assembly 26' is coupled to the pile 28 being driven by a detachable coupling 30 and a pile-driving adapter 32 which is shaped so as to engage the upper end of theparticular pile being driven.
  • a pipe pile 28 is shown in FIGS. 1 and 3, but this is illustrative only. It is to be understood that the present invention can be used to advantage for driving any type of drivable pile.
  • This fluid injection means 36 includes a pressurized driving fluid storage chamber 38 and a control valve mechanism 40 which communicates with the bounce chamber 34.
  • the massive piston weight assembly 24 moves up and down within the cylinder 23, and it bounces upon a cushion of pressurized fluid in the bounce chamber 34.
  • the manner in which the pressurized fluid is injected into the bounce chamber, and the many advantages which accrue from the advantageous massive piston bouncing action are indicated in the introduction and will be described further below.
  • the massive piston weight assembly 24 includes a main weight 42 of suitable massive and strong material.
  • the main weight 42 is a solid steel member of generally cylindrical configuration with bearings, piston rings and end caps attached to its lower and upper ends. Its lower and upper ends are identicalin construction, and so only the lower end is shown in detail in FIG. 3 in order to simplify and clarify the drawings. If it is desired to see the upper end of the piston weight assembly 24, it is noted that this can be seen in FIGS. 2, l4, l5, and 16.
  • a bearing sleeve member 44 is mounted on each end of the mainweight 42.
  • This sleeve member 44 has an annular configuration and fits onto a reduced diameter end portion 46 at the end of the weight 42, abutting against an annular shoulder 48.
  • This bearing sleeve member 44 isformed' of suitable bearing material to run against the cylinder wall22, for example, it is formed of bearing bronze. It is retained by an end cap I 50 of tough hardened steel secured to the weight 42 by detachable fastening means shown as machine screws 52.
  • piston rings 54 are provided in order to form a fluid seal near the end of the-piston weight assembly 24, a plurality of piston rings 54 are provided. These piston rings 54 aremounted in an annular gland member 56 which is retained by the end cap 50 together with the bearing sleeve 44. There is a substantial annular clearance space 58 provided beneath the gland 56, so that it can: move to accommodate any relative sideward movement of piston assembly 24 relative to the cylinder wall 22.
  • the relatively movable or floating" gland 56 provides the rings 54 with accurate firm support, because the floating action of the gland 56 prevents it from wearing against the cylinder wall during the up and down motion of the massive piston weight 24.
  • the cylinder bottom assembly 26 includes a second piston 60.
  • This second piston 60 is adapted to move up and down for a limited travel distance within a second cylinder 61 which is defined by a lower extension of the cylinder wall 22 below the level of the bounce chamber 34.
  • an annular stop shoulder 63 surrounding the piston 60.
  • An annular retainer and bear ing element 65 defines the lower end of the cylinder 61.
  • the retainer and bearing element 65 is secured by large machine screws 67 to a mounting ring 69 which is welded to the exterior of the cylinder wall 22.
  • the detachable coupling 30 is formed by two semi-circular clamps with protruding mating flanges 73 which are secured together by bolts 75.
  • the cylinder bottom assembly 26 can be The driving fluid chamber means 38 is located within the second piston of the cylinder bottom assembly 26.
  • the chamber bore 64 is lined by a cylinder sleeve 66.
  • a bottom flange 68 of an upstanding valve stem guide lines the bottom of the driving fluid chamber 38.
  • the guide 70 has a bore 72, and a valve stem 74 of valve member 76 extends into this bore 72.
  • the valve member 76 has a conical valve surface 78 which seats upwardly against a conical valve seat 80 formed in the end cap 82 of the second piston 60.
  • This second piston is provided with a bearing sleeve member 84, piston rings 86 and an annular gland 88 having annular clearance 58 similar to those elements for both ends of the piston weight assembly 24.
  • actuator 91 In order to actuate the valve mechanism 40 by the piston weight 24, there is an upwardly extending actuator 91 integral with the valve member 76.
  • the actuator 91 is equipped with pressurized fluid trapping means 93 in the form of an enlarged cylindrical'plunger. This plunger 93 can be depressed to fit snugly into the port 62 to trap pressurized fluid in the bounce chamber 34.
  • pressurized fluid in the driving fluid chamber 38 can rush up through multiple channels (FIG. 4) to bypass the perimeter of the valve member 76 so .as to be injected through the port 62 into the bounce chamber 34.
  • the channels 90 are formed by grooves between lands 92 in the interior of the cylinderical liner 66.
  • the pressurized fluid is supplied from a suitable source, for example, such as the pressure storage tank (not shown) of an air compressor (not shown).
  • the compressed air is at a suitable pressure of, for example, 80 pounds per square inch (p.s.i.) to 3,000 p.s.i.
  • valve member 76 When the valve member 76 is depressed, its annular groove 95 (FIG. 3) cooperates with the upper end of the valve guide 70 (as seen in FIG. 12) to act as resilient'deceleration means by trapping fluid in the groove 95. This trapped fluid provides resilient deceleration for the depressed valve member to defined by a closed lower end ofthe cylinder 22.
  • second piston 60 is replaced by a fixed member 60A I which is welded or otherwise attached to the lower portion of the cylinder wall 22, so as to be effectively integral with the cylinder wall 22.
  • This de-coupling of the cylinder wall 22 from the pile 28 reduces the amount of mass to be driven downwardly when the powerful driving thrust is applied to drive the pile 28.
  • the fluid injection means 36 includes the driving fluid chamber 38 and the control prevent its banging down on the guide 70.
  • the pressurized fluid is fed to the pile driver system 20 through a flexible pressure hose line 94 and through a connection fitting 96.
  • This fitting 96 feeds into an input passage 98 which communicates with the bore 72 of the valve stem guide 70.
  • the pressurized fluid from the bore 72 flows through a constricted passageway 100 into the driving fluid chamber
  • the pressurized fluid can also flow through a less restricted passageway 102 into the chamber 38.
  • the two passageways 100 and 102 are in parallel flow relationship; the lower constricted one 100 is always open, but the upper unrestricted one 102 is shut off when the valve member 76 together with its stem 74 is depressed by the piston weight 24.
  • the expanded pressure fluid 104 is released from the cylinder 23 through a plurality of outlet ports 106 in the cylinder wall 22.
  • the outlet ports 106 communicate with an annular muffler chamber 108 defined by a removable muffler housing 109 which includes a pair of spaced cylindrical walls 110 and 112.
  • the muffler housing walls 110 and 112 are rigidly interconnected by a bottom ring plate 114 (FIG. 3) which is detachably secured to a mounting ring 116 by a plurality of bolts 118.
  • the mounting ring 116 is secured to the outside of the cylinder wall 22 by welding.
  • FIGS. 5 and 6 Shown in FIGS. 5 and 6 is the upper end of the removable muffler 109.
  • the annular muffler chamber 108 communicates through multiple ports 120 with a quantity of oil air separating material 122 in the top of an annular muffler chamber 123 (please see also FIG. 3) for separating droplets of lubricating oil from the expanded pressure fluid 104 after passing through the ports 120.
  • the material 122 is coarse stainless steel wool matting.
  • a removable cover 124 secured by screws 126 enables the oil separating material 122 to be removed and replaced. I
  • the expanded pressure fluid 104 flows down through the material 122, then down through the multiple holes 127 in a material support ring 129, and as shown in FIG. 6, the fluid 104 then flows into an inverted U- shaped fluid outlet baffle 128.
  • the interior of the baffle 128 communicates with an atmospheric vent 130 through which the expanded pressure fluid passes out into the atmosphere.
  • the purpose of the baffle 128 is to prevent the separated oil droplets from being blown out into the atmosphere.
  • the separated oil droplets 132 fall from the separation material 122 in the chamber 123; and as shown in FIG. 3, this oil collects in an annular reservoir 134 at the bottom of the chamber 123.
  • an oil reservoir is provided'for the self-contained lubrication system which will be explained further below.
  • the muffler housing 109 can be removed to provide access to the ports 106, if desired, by unscrewing the bolts 118 (FIGS. 3 and 7).
  • the top of the muffler housing 109 has an O-ring seal 136 for sealing the muffler chamber 108.
  • the seal 136 can be slid up along the exterior of the cylinder wall 22 for removing the muffler housing 109.
  • the mounting 138 for the lead guides and the upper muffler and air filter 140 can be removed so as to permit complete removal of the muffler housing 109, if desired.
  • the self-contained lubrication system is shown'in greatest detail in FIGS. 7 and 8.
  • the level L (FIG. 3) of the oil in the reservoir 134 can be seen by observing an oil 'gauge 135 having a transparent non-breakable plastic tube. Oil from the reservoir 134 can flow down through an oil supply passage 142 into an inlet passage 144 sealed by a seal 145 .and communicating with the inlet chamber 146 of an oil filter assembly 150.
  • An annular filter cartridge 148 of filter material such as felt separates the inlet chamber 146 from an outlet chamber 152 through which passes the end cap retainer bolt 154.
  • the filter element 148 can be removed and replaced by unscrewing the bolt 154 and up to an oil hole 172 (FIG. 1) for dispensing lubricating oil above the piston weight assembly 24 to lubricate the piston 24 and cylinder wall 22.
  • the other feed line 159 feeds through a check valve 174 into a high-pressure pump chamber 176 containing a smaller diameter piston 178.
  • This piston 178 pumps oil under high pressure through a check valve 179 into an oil line 180 extending down to a swivel 182 (FIG. 8) on the inlet connection fitting 96 for the pressurized fluid.
  • the swivel 182 has a passage 183 and an annular channel 184 for feeding oil inward through a pair of oil holes into the bore 97 of the fitting 96.
  • the lubricating oil is mixed with the incoming pressurized fluid, and thereby oil is dispensed up through the passage 98 so as to lubricate the fluid injection means 36 including the 'valve mechanism 40.
  • This oil entering through the passage 98 also serves to lubricate the bounce chamber 34, the piston 60 and the cylinder wall 22 surrounding the piston 60.
  • pistons 166 and 178 are connected together to form a double piston.
  • a spring 186 in the low-pressure pump chamber 164 urges both pistons 166 and 178 toward the left. In other words, the spring 186 urges the pistons 166 and 178 in the direction of their intake stroke.
  • the high pressures occuring in the bounce chamber 34 are utilized to drive the pistons 166 and 178 toward the right, i.e. in the direction of their expulsion (pumping) stroke.
  • a small port 188 in the cylinder wall 22 communicates through drilled passages 189 in a base plate 190 with a passage 192 leading into the piston-actuating chamber 194.
  • the base plate 190 serves to support both the oil filter assembly 150 and the oil pump 160. This base plate 190 can be detached from the outside of the' cylinder wall 22. As shown in FIG. 3, this base plate is removably secured by machine screws 196 (only one can be seen .in FIG. 3).'
  • the pile driver system When driving a pile, as shown in FIGS. 1' and 2, the pile driver system is guided by a pair of spaced parallel vertical guide rails 200 and 201, which are called leads.
  • leads are well known in the art of driving piles, and their usage is not claimed as novel.
  • the upper clampring 138- is formed in two semi-circles with protruding mating flanges 213 secured together by bolts 214.
  • FIG. 15 shows the atmospheric air 222 being expelled from the cylinder 23, because the piston weight 24 is rising. It will be understood that as soon as the piston 24 begins descending again, the atmospheric air will be sucked back into the cylinder 23. To exclude dust and dirt there is an air filter element 224 in thechamber 220 adjacent to the atmospheric vent 226.
  • head plugs 230 In order to provide various driving modes for the pile driver system 20, various sizes of head plugs 230 (FIG. 230A (FIG. 1) are utilized.
  • the head plugs are removably secured in the top of the cylinder wall 22, by detachable fastening means 232 shown as machine screws.
  • the deep head plug 230A shown in FIG. 1 extends down so far that it blocks the vent ports 216, thus producing the double-acting driving mode, as will be explained in detail further below.
  • the shallow head plug shown in FIG. 15 produces a single-acting driving mode.
  • the single-acting driving mode automatically converts to a double-acting mode.
  • the pile driver system (FIG. 1) or 20A (FIG. 20) or 208 (FIG. 21) can be supported by a cable 236 (FIG..1) from a suitable crane (not shown) attached to suitable support means (234), such as connection means attached to the upper end of the pile driver, for example, to the head plug 230 or 230A.
  • the support cable 236 can advantageously be fastened to connection means 238 attached to a pressure-fluid cylinder 240 having a piston 242 therein with a chamber 244 below the piston.
  • the piston rod serves as support means 234 attached to the upper end of the pile driver.
  • Pressurized fluid for example, such as compressed air or other gas under pressure, is supplied from a pressurized fluid source 246, such as'the receiver of an air compressor. This pressurized fluid is supplied through an adjustable pressure regulator 248 into the cylinder chamber 244.
  • the regulator 248 is adjusted by the operator such that the total force-developed by the pressurized fluid in the chamber 244 acting upwardly upon the working area of the piston 242 is moderately less than the safe maximum'lifting load of the crane pulling on the cable 236.
  • the cable 236 and crane or other lifting means are spared from experiencing the wear and tear which jarring action of the ward thrust on the pile driver during each stroke of the piston weight 24.
  • the upper end cap 50 of the reciprocating piston weight 24 can be arranged to strike up against the head plug 230 to exert an upward impact for jarring the pile loose. This upward striking is accomplished by installing a head plug which extends down to the level of the vent ports 216.
  • the pile 28 (FIGS. 17 and 18) is shown as an H-beam pile, but other types of piles can also be extracted with advantage by use of the invention.
  • the loose coupling 250 is shown as including a cylinder having an abutment 254 at its lower end.
  • An extractor rod 256 is attached to the pile 28 being extracted.
  • a head 252' on this rod strikes against the abutment 254 for delivering upward thrusts to the pile for extracting it.
  • FIG. 19 shows the pile driver system 20 (FIG. 1) or 20A (FIG. 20) or 208 (FIG. 21) being used for driving a timber pile 28.
  • a conical guide 258 is shown for centering the pile driver 20, or 20A, or 208 upon the timber pile 28.
  • the guide 258 is secured by a clamp to an attachment groove 260 (See also FIG.;3) in the pile adapter 32.
  • valve actuator 91A does not include fluid-trappingmeans in the form of an enlarged head such as shown at 93 (FIG. 3).
  • FIG. 20 is well adapted to provide the fourth mode set forth in the introduction, namely, pre-stress plus impact plus thrust.
  • the pre-stressing occurs while the cushion of pressure fluid injected into the bounce chamber by the valve means 40 plus any residual fluid in the bounce chamber is decelerating the piston weight. This prestressing removes all of the play between the second piston 60 and and the pile 28.
  • the piston weight 24 strikes the second piston 60 with an impact, as shown in FIG. 20, the resulting blow starts the pile moving downwardly, as indicated by the twin arrows near the coupling 30 in FIG. 20.
  • This powerful enduring thrust is delivered to the pile during the re-acceleration of the piston weight upwardly.
  • the actuator 91A is lengthened to decrease the amountof impact and is shortened to increase the amount of impact. This lengthening or shortening is accomplished by removing the valve member 76 and replacing it with one having a longer or shorter actuator 91A, as desired.
  • valve 40 When a longer actuator 91A is employed, the valve 40 is opened to inject the pressurized fluid beneath the descending piston weight 24 when it is farther from the cylinder bottom assembly 60.
  • the pressurized fluid thereby has a longer time to act and thus decelerates the piston weight 24 toa slower velocity before impact occurs, producing a reduced impact, and vice versa.
  • This pre-stress plus impact plus thrust driving mode can be used to advantage for driving very stubborn piles.
  • the amount of impact can be adjusted, in the manner explained above, so as to start the pile moving.
  • the pile driver provides a powerful, enduring thrust to push the moving pile on down further in an effective efficient operation.
  • the amount of impact can be just sufficient to start the pile moving, being very effective because the pile is already pre-stressed.
  • the powerful, enduring after thrust is very effective because it is delivered to an already moving pile.
  • FIG. 21 another modified pile driver system 20B is shown embodying the invention and adapted for practicing the method of theinvention.
  • the only change from the pile driver system and method 20, is that the cylinder bottom assembly 60A in the system 20B is secured to'the lower end of the cylinder wall 22.
  • This cylinder bottom assembly is attached by a large number of strong machine screws 262.
  • This attachment is an advantage because it reduces the number of moving parts in the pile driver system to two, namely, the piston weight assembly 24 and the valve member 76. (In counting the moving coupling the mass of the cylinder wall 22 (together with everything rigidly attached to the wall 22) from the pile being driven, thus making the driving job correspondingly easier.
  • the advantage of fewer moving parts may outweigh the advantage of reduction of the effective mass being driven.
  • valve actuator 91 or 91A is depressed so that the valvemember 76 is spaced from its seat.
  • the pressurized fluid enters the bounce chamber by leaking through the clearance around the plunger head 93.
  • the piston weight 24 is raised up by the entering fluid, and the pressure fluid in the bore 72 acts on the stem 74 to cause the valve member 76 to move up together with the piston weight 24.
  • the accumulated pressure fluid in the chamber 38 rushes up into the bounce chamber 34 to suddenly push the piston weight up.
  • the valve member 76 rises up against its seat to close the valve 40.
  • the passage 102 is unblocked because the stem 74 has moved up.
  • the operator starts the piston weight. 24 in the same way as for systems 20 and 20B, namely, by suddenly starting the flow of pressure fluid through the line 94.
  • the passage 100 allows pressure fluid to surge into the storage chamber 38, and it flows up through the open valve-40. This surge of pressure fluid up through the open'va'lve 40s uddenly pushes the piston weight 24 upwardly.
  • the sudden upward push on the piston weight 24 causes it to rise up, as shown in FIG. 13, to the point where the outlet ports 106 are unblocked.
  • the expanded pressure fluid-in the bounce chamber 34 is released through ports 106, allowing the piston weight 24 to fall, as shown in FIG. 9.
  • the valve 40 is suddenly opened to inject pressure fluid from the storage chamber 38 into thebounce chamber 34.
  • This second injection of the pressure fluid is greater than the first one, because the pressure in storage chamber 38 has become more early equal to supply pressure.
  • the piston weight 24 is ac celerated more and rises up, as shown in FIG. 13, further beyond the ports 106.
  • FIG. 9 shows the piston weight 24 descending. It
  • FIG. 3 shows the piston weight assembly at the moment it comes in contact with the head 93 of the actuator 91.
  • FIG. 10 shows the valve fully opened by depression of the actuator.
  • the pressure fluid is being injected through the port 62 into the bounce chamber.
  • the resultant sudden increase in pressure beneath the piston weight 24' increases its deceleration and produces a powerful down thruston the pile 28, as indicated in FIG. 10 by the twin arrows on the adaptor 32.
  • FIG. 11 shows the injection port 62 closed by the fluid trapping head means 93.
  • the injected pressure fluid and any residual pressure fluid remaining in the bounce chamberfrom the previous cycle are now trapped by blockage of the port 62. Accordingly, the
  • a resilient compressed fluid cushioned bouncing action occurs, i.e. the piston weight .is completely decelerated and is re-accelerated upwardly, as shown in FIG. 13.
  • the pile driver system 20A or 20B can also be used for pile extraction in the same general manner as the pile driver system 20.
  • the operator can increase the time duration of each fluid-cushioned powerful driving thrust and, decrease the peak force occuringduring each driving thrust by increasing the extent of trapping of pressurized fluid by the trapping means 93 (FIG. 3), and vice. versa.
  • the trapping means 93 By increasing the height of trapping means 93, port 62 becomes blocked when piston 24 is at a larger predetermined distance from the bottom assembly 26, thus increasing the extent of trapping, and
  • detachable the bottom assembly injecting pressurized compressible fluid into the region between the descending piston weight and the bottom assembly to decelerate the piston weight and to re-accelerate it upwardly within the cylinder with a sudden fluid-cushioned bouncing action for providing a powerful, fluid-cushioned thrust acting down upon said bottom assembly to be transmitted to the pile during the deceleration and re-acceleration 0f the piston weight, releasing the expanded pressure fluid from the cylinder, and again producing a descending motion of the piston weight within the cylinder, and repeating the steps to provide a sequence of powerful, fluid-cushioned thrusts acting down upon said bottom assembly to be transmitted to the pile for effectively driving the pile into the earth.
  • step of providing a cylinder having a bottom assembly includes thestep of decoupling the cylinder bottom assembly from the cylinder for effectively reducing the mass to be driven.
  • claimed in claim 1 including the step of temporarily trapping the'injected pressurized. fluid between the descending piston weight and the cylinder bottom assembly for preventing the massive piston weight from impacting against the bottom assembly.
  • claimed in claim 1 including the steps of providing a storage chamber for compressible pressurized fluid near the cylinder and supplying pressurized fluid into the storage chamber, and injecting thepressurized fluid from said storage chamber into said region between the descending piston weight and the bottom assembly.
  • the method of driving a pile into the earth comprising the steps of providing a cylinder having a bottom assembly coupled to the pile to be driven, providing a descending motion of a massive piston weight travelling within the cylinder toward the bottom assembly, when the descending piston weight reaches a first predetermined distance from the bottom assembly trapping compressible fluid within the cylinder between the descending piston weight and the bottom assembly to begin decelerating the descending piston weight, when the descending piston weight reaches a second predetermined distance from the bottom assembly injecting pressurized compressible fluid into the cylinder between the descending piston weight and the cylinder bottom assembly to further decelerate the descending piston weight, when the descending piston weight reaches a third predetermined distance from the bottom assembly trapping the injected pressurized fluid within the cylinder between the descending piston weight and the bottom assembly to completely decelerate the descending piston weight and to re-accelerate it upwardly with a sudden bouncing action for providing a powerful thrust to said bottom assembly to be transmitted to the pile during the deceleration and re
  • the method of extracting a pile from the earth comprising the steps of providing a cylinder having a bottom assembly and providing an upper head, producing a descending motion of a massive piston weight travelling down within said cylinder directly toward said bottom assembly, as said massive piston weight is travelling downwardly and before the piston weight reaches the bottom assembly injecting compressible pressurized fluid as defined herein into the region between the descending piston weight and the bottom assembly to prevent said massive piston weight from hitting said bottom assembly and to bounce the piston weight upwardly within the cylinder upon a cushion of said pressurized fluid, causing the upwardly travelling piston weight to exert an upward thrust against said upper head for producing an upward jarring action to be transmitted to the pile for extraction thereof, releasing the expanded fluid from beneath the piston weight into the atmosphere for producing another descending motion thereof, and repeating the steps for producing a sequence of upward jarring actions for extracting the pile.
  • claime'd'in claim 13 including the step of causing theupwardly travelling weight to impact against the upper head.
  • the method of driving a pile into the earth comprising the steps of cyclically bounding a mass up and down upon a cushion of compressible pressurized fluid, cyclically injecting additional compressible pressurized fluid into the cushion beneath the mass during the cycle of operation when the mass is moving downwardiy,

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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)
US00102325A 1970-12-29 1970-12-29 Automatically self-regulating variable-stroke, variable-rate and quiet-operating pile driver method and system Expired - Lifetime US3714789A (en)

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US (1) US3714789A (enrdf_load_stackoverflow)
BE (1) BE777480A (enrdf_load_stackoverflow)
BR (1) BR7108604D0 (enrdf_load_stackoverflow)
CA (1) CA946634A (enrdf_load_stackoverflow)
DE (1) DE2163933C3 (enrdf_load_stackoverflow)
DK (1) DK143418C (enrdf_load_stackoverflow)
ES (1) ES398394A1 (enrdf_load_stackoverflow)
FR (1) FR2121104A5 (enrdf_load_stackoverflow)
GB (1) GB1359030A (enrdf_load_stackoverflow)
IL (1) IL38435A (enrdf_load_stackoverflow)
IT (1) IT944463B (enrdf_load_stackoverflow)
LU (1) LU64529A1 (enrdf_load_stackoverflow)
NL (1) NL7117768A (enrdf_load_stackoverflow)
NO (1) NO136376C (enrdf_load_stackoverflow)
SE (1) SE389146B (enrdf_load_stackoverflow)
ZA (1) ZA718359B (enrdf_load_stackoverflow)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3797585A (en) * 1971-10-18 1974-03-19 B Ludvigson Apparatus for generating a pressure wave in an elongated body operatively connected to a drop hammer
US4060139A (en) * 1976-11-29 1977-11-29 Raymond International Inc. Underwater gas discharge hammer with gas reservoir
US4063599A (en) * 1975-05-21 1977-12-20 Hollandsche Beton Groep N.V. Method and apparatus for underwater pile driving
US4126191A (en) * 1977-06-03 1978-11-21 Raymond International Inc. Gas discharge type underwater hammer with liquid purge and reflood control
US4365306A (en) * 1980-06-30 1982-12-21 Conoco Inc. Method and apparatus for remotely monitoring and evaluating pile driving hammers
US4377355A (en) * 1979-07-31 1983-03-22 Bolt Technology Corporation Quiet bouncer driver thruster method with pressurized air chamber encircling massive bouncing piston
US4383582A (en) * 1979-07-31 1983-05-17 Bolt Technology Corporation Bouncer type pile driver
US4712641A (en) * 1984-03-19 1987-12-15 Bolt Technology Corporation Method and system for generating shear waves and compression waves in the earth for seismic surveying
US5419403A (en) * 1991-10-23 1995-05-30 Ing. G. Klemm Bohrtechnik Gmbh Pneumatic hammer
US5474138A (en) * 1993-12-08 1995-12-12 J & M Hydraulics, Inc. Hydraulic control circuit for pile driver
US5725329A (en) * 1996-05-08 1998-03-10 Chelminski; Stephen Method, system and apparatus for driving and pulling pilings
WO1999011871A1 (en) * 1997-09-04 1999-03-11 Stephen Chelminski A method system and apparatus for driving and pulling pilings
US6224294B1 (en) * 1998-07-09 2001-05-01 Peter W. Mansfield Tubular piling driving apparatus and piling installation method
US20120111593A1 (en) * 2009-02-10 2012-05-10 Onesteel Wire Pty Limited Fence Post Driver
CN103899781A (zh) * 2014-03-26 2014-07-02 大连祥瑞阀门制造有限公司 自动转换喷冲方向的止回喷冲阀
CN103982666A (zh) * 2014-05-21 2014-08-13 济南高达信息技术有限公司 一种海洋钻井平台桩靴助升用涡轮驱动旋喷装置
US20150197988A1 (en) * 2012-07-03 2015-07-16 II Jae Lee Impact body for hydraulic impact device
US9834900B2 (en) * 2013-12-10 2017-12-05 Pentti HEINONEN Piling method and apparatus

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US3721095A (en) * 1971-08-23 1973-03-20 Bolt Associates Inc Controllable force method and system of driving piles
US3958647A (en) * 1975-06-04 1976-05-25 Bolt Associates, Inc. Powerful submersible deepwater pile driver powered by pressurized gas discharge
DE2716701C3 (de) * 1977-04-15 1983-01-05 Koehring Gmbh, 2086 Ellerau Rammgerät
DE3047375C2 (de) * 1980-12-16 1985-09-05 Koehring Gmbh, 2000 Hamburg Tauchfähige Rammvorrichtung
CN103953049B (zh) * 2014-05-21 2015-12-23 庞维晓 一种海洋钻井平台桩靴助升用上涡轮下涡孔驱动旋喷装置
CN103953045B (zh) * 2014-05-21 2016-08-24 齐宝兰 一种海洋钻井平台桩靴助升用上涡孔驱动旋喷装置
CN104652437B (zh) * 2015-02-13 2016-05-04 福建永强岩土股份有限公司 旋挖桩孔清孔器及其施工方法
CN106193036A (zh) * 2015-04-30 2016-12-07 五冶集团上海有限公司 大直径phc管桩施工方法

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US1622896A (en) * 1925-10-17 1927-03-29 Lowenstein Karl Prinz Zu Device for drilling or chiseling away rock
US3417828A (en) * 1965-02-03 1968-12-24 Hollandse Beton Mij N V Method for driving piles and similar objects
US3583499A (en) * 1969-09-08 1971-06-08 Hugo Cordes Hydraulic pile extractor

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NL6600863A (enrdf_load_stackoverflow) * 1966-01-24 1967-07-25
US3446293A (en) * 1966-12-28 1969-05-27 American Drilling & Boring Co Pile driver
US3547207A (en) * 1968-11-07 1970-12-15 Vulcan Iron Works Percussion hammer

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US1622896A (en) * 1925-10-17 1927-03-29 Lowenstein Karl Prinz Zu Device for drilling or chiseling away rock
US3417828A (en) * 1965-02-03 1968-12-24 Hollandse Beton Mij N V Method for driving piles and similar objects
US3583499A (en) * 1969-09-08 1971-06-08 Hugo Cordes Hydraulic pile extractor

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3797585A (en) * 1971-10-18 1974-03-19 B Ludvigson Apparatus for generating a pressure wave in an elongated body operatively connected to a drop hammer
US4063599A (en) * 1975-05-21 1977-12-20 Hollandsche Beton Groep N.V. Method and apparatus for underwater pile driving
US4060139A (en) * 1976-11-29 1977-11-29 Raymond International Inc. Underwater gas discharge hammer with gas reservoir
US4126191A (en) * 1977-06-03 1978-11-21 Raymond International Inc. Gas discharge type underwater hammer with liquid purge and reflood control
US4377355A (en) * 1979-07-31 1983-03-22 Bolt Technology Corporation Quiet bouncer driver thruster method with pressurized air chamber encircling massive bouncing piston
US4383582A (en) * 1979-07-31 1983-05-17 Bolt Technology Corporation Bouncer type pile driver
US4365306A (en) * 1980-06-30 1982-12-21 Conoco Inc. Method and apparatus for remotely monitoring and evaluating pile driving hammers
US4712641A (en) * 1984-03-19 1987-12-15 Bolt Technology Corporation Method and system for generating shear waves and compression waves in the earth for seismic surveying
US5419403A (en) * 1991-10-23 1995-05-30 Ing. G. Klemm Bohrtechnik Gmbh Pneumatic hammer
US5474138A (en) * 1993-12-08 1995-12-12 J & M Hydraulics, Inc. Hydraulic control circuit for pile driver
US5725329A (en) * 1996-05-08 1998-03-10 Chelminski; Stephen Method, system and apparatus for driving and pulling pilings
WO1999011871A1 (en) * 1997-09-04 1999-03-11 Stephen Chelminski A method system and apparatus for driving and pulling pilings
US6224294B1 (en) * 1998-07-09 2001-05-01 Peter W. Mansfield Tubular piling driving apparatus and piling installation method
US20120111593A1 (en) * 2009-02-10 2012-05-10 Onesteel Wire Pty Limited Fence Post Driver
US8955612B2 (en) * 2009-02-10 2015-02-17 Onesteel Wire Pty Limited Fence post driver
US20150197988A1 (en) * 2012-07-03 2015-07-16 II Jae Lee Impact body for hydraulic impact device
US9988843B2 (en) * 2012-07-03 2018-06-05 Il Jae Lee Impact body for hydraulic impact device
US9834900B2 (en) * 2013-12-10 2017-12-05 Pentti HEINONEN Piling method and apparatus
CN103899781A (zh) * 2014-03-26 2014-07-02 大连祥瑞阀门制造有限公司 自动转换喷冲方向的止回喷冲阀
CN103982666A (zh) * 2014-05-21 2014-08-13 济南高达信息技术有限公司 一种海洋钻井平台桩靴助升用涡轮驱动旋喷装置

Also Published As

Publication number Publication date
NO136376C (no) 1977-08-24
DE2163933A1 (de) 1972-07-20
DK143418C (da) 1982-01-04
GB1359030A (en) 1974-07-03
ES398394A1 (es) 1975-06-16
AU3733471A (en) 1973-06-28
NO136376B (enrdf_load_stackoverflow) 1977-05-16
IL38435A (en) 1974-11-29
DE2163933B2 (de) 1981-07-16
FR2121104A5 (enrdf_load_stackoverflow) 1972-08-18
SE389146B (sv) 1976-10-25
BE777480A (fr) 1972-04-17
IT944463B (it) 1973-04-20
NL7117768A (enrdf_load_stackoverflow) 1972-07-03
BR7108604D0 (pt) 1973-05-31
ZA718359B (en) 1972-09-27
IL38435A0 (en) 1972-02-29
DK143418B (da) 1981-08-17
CA946634A (en) 1974-05-07
LU64529A1 (enrdf_load_stackoverflow) 1972-06-20
DE2163933C3 (de) 1982-03-25

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