WO1999011871A1

WO1999011871A1 - A method system and apparatus for driving and pulling pilings

Info

Publication number: WO1999011871A1
Application number: PCT/US1997/018212
Authority: WO
Inventors: Stephen Chelminski
Original assignee: Stephen Chelminski
Priority date: 1997-09-04
Filing date: 1997-10-15
Publication date: 1999-03-11
Also published as: AU4897197A

Abstract

A combination linear vibratory and hammer-type pile driver apparatus (10), system and method for using the apparatus to drive or to pull pilings. The apparatus is comprised of a lifting shaft (12) isolated from but slideably mounted within a piston assembly (16) which piston assembly is attached to a frame assembly. There is a cylinder assembly attached to a reaction mass and the piston assembly is vibratorily positioned within the cylinder assembly and vibratorily driven by hydraulic fluid at a selectable frequency thereby vibrating the piston/frame assembly relative to the cylinder/reaction mass assembly. The cylinder/reaction mass may also be operated to act as a hammer driving the piston/frame assembly either upwardly or downwardly. A clamp device such as jaws is attachable to a clamp-end of the frame assembly and the lifting shaft is attachable to a cable of a lifting apparatus such as a crane.

Description

A Method System and Apparatus for Driving and Pulling Pilings

BACKGROUND OF THE INVENTION

HELD OF THE INVENTION

This application is a Continuation-in- Part Application of Application Serial Number 646,844, filed May 8, 1996. The present invention relates to the field of pile driving and pulling. More particularly, the invention relates to a method, system and apparatus for driving and pulling pilings utilizing intense vibrations in combination with vibratory and conventional hammering. The method, system and apparatus allows the operator to drive pilings using a linear hydraulic vibrator supplied with hydraulic fluid at high pressure from a high pressure, large volume, hydraulic pump through suitable hydraulic hoses. The pile driving system may be "tuned" to take into consideration soil conditions and site requirements to obtain a high degree of driving efficiency, utilizing vibration sensing pickup units on the ground and/or on the pile driving system apparatus to feed information of driving frequency and driving rate to an electronic control unit which controls the vibration frequency of the pile driving apparatus. The pile driving system may also be used as a conventional hammer type system. For example, the system may be used in a vibratory mode to initially drive a piling into place, and once the piling is in place, the system may be adjusted to be used as a conventional hammer type system to test the piling to a "blow count". Therefore, the invention which may function as both a vibratory and a hammer type pile driver, eliminates the previous need for two separate types of pile driving systems.

DESCRIPTION OF THE PRIOR ART

The use of machines for driving elements into the ground has widespread applications in the formation of foundations for structures of all types, the elements which can be driven into the ground may vary in shape depending upon the particular purpose.

Pile driving has traditionally been done using hammers powered by steam, compressed air, or hydraulic power and more recently methods using vibrations have been employed. It has been found that when a pile is subjected to intense linear vibrations along the axis of the pile, and when the weight of the vibratory pile driver apparatus is added to the weight of the pile, (usually a steel pile), and where the soil conditions are suitable for this method of pile driving, the rate of penetration is most frequently found to be considerably faster than would be obtained using hammer methods and apparatus.

The conventional rotary vibratory pile driver has a heavy housing provided with at least two shafts which carry eccentπc weights. Typically, slugs of heavy metal are set, off-center, into gears. Other eccentπc mass rotors are also used. The weight of the eccentric masses are typically measured in tens or hundreds of pounds as compared to the weight of the mass of the remaining frame and support system of rotary vibratory drivers being measured thousands of pounds. Thus there is an inherent disfavor against the reaction mass, i.e., the eccentπc rotor weights, which may be as high as about 1 to 10. I.e., the ratio of the weight of the reaction mass to the mass being vibrated should preferably be greater than one.

The shafts of the rotary vibrator are rotated at high speed, typically 1200 rpm (20 Hz), thereby vibrating the housing assembly which is clamped to the pile to be dπven or set. This vibration, combined with the weight of the dπver, causes the pile to sink into the ground or conversely pulled out of the ground when tension is applied by use of a crane or like machine. Typically, the housing is suspended from the cable of a crane by means of an elastomeπc vibration damper so that the vibration is transferred to the pile and not back up the cable to the crane. These known vibratory drivers cannot be used to both hammer and vibrate

The rotary vibratory type of pile dπvers have the disadvantages of generating the linear vibrations to the pile by using heavy eccentπc weighted masses which must be rotated synchronously using a substantial amount of energy to do so. There are inherent inefficiencies related to the conversion of the rotational energy to linear vibratory energy. To vary the frequency of the linear vibrations, the synchronous rotary speed of the eccentπc masses must be altered at a substantial energy cost and because of the size of the masses being dnven into synchronous rotation, there is substantial inertia to overcome when either increasing the frequency or decreasing the frequency. The rotary units need to be "run up" through a range of frequencies to arrive at the desired frequency. When they "run up" as they are put into use, they may run through frequencies which could momentaπly damage sensitive nearby structures. These pile dπvers also have an ideal speed of rotation and consequently an ideal frequency of vibration. Lower frequency requires less hydraulic fluid to the hydraulic motors driving the eccentπc rotors. With the loweπng of frequency and less hydraulic fluid there is produced a corresponding lower energy output. Increasing the frequency results in an increased flow of hydraulic fluid from the power supply and an increased πsk of gear and beaπng wear or burn-out.

Another disadvantage with usual practice is that when load-bearing piles are dπven using vibratory pile dπvers, even when the piles are dπven to a specified depth, the amount of load the piles will bear is not known. Therefore, the piles must be either "load tested" by applying static loads to the top of the pile to represent a specified load, including a safety factor of, for example, 1.5 times the expected service load. Alternatively the piles may be tested to a "blow count" by hammering them with a hammer type pile driver having a known energy level. A table is then used to iterate the "blow count" (how many blows per inch of penetration) with the energy of the hammer, le. how many foot pounds of energy is employed by each drop of the hammer weight. When a pile has been dπven into place using a vibratory pile driver, and is then tested using a hammer type driver, the vibratory pile dnver must be disengaged and the hammer type engaged, thus requiπng two types of dπvers. There is a considerable waste of time and effort in switching of the drivers.

The following is a bπef descπption and discussion of patents defining the most closely related inventions.

United States Patents No. 5,088,565, "Vibratory Pile Dπver" to Evarts, Kingsley S., Issued 02/18/92 discloses a vibratory pile dπver having a clamping means for clamping onto a pile, hydraulic gear motor having two oppositely rotatable shafts and a pair of semicircular weights aligned in the same vertical plane and each is secured to a shaft parallel to the motor shafts. There are dπve and dπven pulleys, sprockets or the like connected by toothed timing belts, chains or the like for dnving the weights synchronously.

United States Patents No. 4,625,811, "Hydraulic Vibratory Pile Driver" to Tuenkers, Josef-Gerhard, Issued 12/02/86 discloses a vibratory pile dπver with a πgid housing, a pair of parallel and horizontally spaced shafts journaled for rotation wholly independently of each other about respective parallel and horizontally spaced axes m the housing, respective generally equally massive and eccentrically mounted weights on the shafts, respective hydraulic dπve motors on the housing connected to the shafts for oppositely rotating the shafts and the weights.

United States Patents No. 4,819,740, "Vibratory Hammer/Extractor" to Warπngton, Don C, Issued 04/11/89 discloses a vibratory hammer/extractor for use with elongated pilings and the like. The vibratory exciter includes, among other elements, one pair of eccentπc weights mounted on shafts for rotation about an axis transversely of the clamped piling for imparting vibratory forces to the piling as the eccentπcs are dπven in rotation.

Clearly, none of these Patents disclose the invention taught and claimed herein.

Applicant has some familiarity with seismic vibrators which operate without the use of rotary eccentric masses. The seismic vibrators are useful for imparting vibration energy into the earth but ha\ e no use in the field of construction and particularly in the field of dnving and extracting pilings.

It would be desirable to have a vibratory pile dnver apparatus, system and method for driving pilings \ \ hich overcomes many of the deficiencies and disadvantages of the pπor art pile dπvers. The present invention disclosed and claimed herein has the particular objectives, features and ad\ antages of: 1) a low height, which is advantageous for application under bridges and m buildings, 2) producing a linear vibration without the need to convert from rotary motion to linear motion; 3) compatibility with a wide range of power units, from about 50 to 300 gpm; 4) providing a constant level of energy over a wide range of frequencies; 5) capable of rapid and simple control of a wide range of frequencies; 6) may be started at a set frequency, particularly advantageous where sensitive nearby structures can be damaged by certain frequencies; 7) may be used for jarπng or hammenng up or down while vibrating; and 8) having a reaction mass to vibratory load ratio substantially greater than one (1), i.e., having the reaction mass being substantially heavier than the vibratory load rather than ratio of reaction mass to vibratory load ratio being substantially less than one (1), i.e., the vibratory load being substantially heavier than the reaction mass and 9) having the capability to function in both a linear vibratory mode and a hammer mode.

Summary of the Invention

Basically the present invention in its most simple form or embodiment is directed to a combination linear vibratory pile dnver apparatus and hammer type pile dπver apparatus and the method for using the apparatus to drive or to pull pilings. The apparatus is compnsed of a lifting shaft isolated from but slideably mounted within a piston assembly which is attached to a frame assembly and a cylinder assembly attached to a reaction mass. The piston assembly is \ lbratoπly positioned within the cylinder assembly and vibratoπly dπven by hydraulic fluid at a selectable frequency thereby vibrating the piston/frame assembly (the piston assembly and the attached frame assembly) relative to the cylinder/reaction mass assembly (the cylinder assembly and the attached reaction mass). A clamp device is attachable to a clamp-end of the frame assembly and the lifting shaft is attachable to a cable of a lifting apparatus such as a crane. Collectively, the piston/frame assembly and the cylinder/reaction mass assembly may be referred to as the vibratory assembly.

The frequency of the vibration and the power of the vibration, which power is related to the stroke length of the piston (also the stroke length of the pile driver), i.e., the vibration amplitude, may be vaπed independently. By positioning the piston toward either the clamp- end or the cable end, and by adjusting the power, i.e., the stroke length, the linear vibratory pile dnver may function as a hammer and a vibrator concurrently using vibratory hammenng. For example, if the piston were positioned near the clamp end, the vibration amplitude would allow the reaction mass to slightly stπke the excursion limiting means of the frame, thus vibrating and hammenng concurrently. Loweπng the frequency of the vibrations and positioning the piston toward one end or the other will result in the apparatus functioning solely as a hammer for either dnving or pulling a pile.

It is a pnmary object of the present invention to provide a pile dπver apparatus to dnve and to pull pilings compnsing: a lifting shaft vibration isolated from, but slideably mounted within, a piston assembly. The piston assembly is attached to a frame assembly and the frame assembly restπcts sliding movement of the lifting shaft within the piston assembly. A means for vibration isolating (a vibration isolator) the lifting shaft from the piston assembly is positioned within the inside cavity of the piston assembly. The vibration isolator acts to dampen or isolate the vibration of the piston and frame assembly from the lifting shaft and further limits sliding movement of the lifting shaft within the piston inside cavity. A c\ Under assembly is attached to a reaction mass and the piston assembly is vibratonly positioned within the cylinder assembly. There is also a means for vibratoπly dnving the piston assembly by hydraulic fluid at a selectable frequency thereby vibrating the piston assembly and the attached frame assembly, i.e., vibrating the piston/frame assembly relative to the cylinder assembly attached to the reaction mass assembly, i.e., the cylinder/mass assembly. There is also provided means for causing the reaction mass to move relative to the piston assembly a distance of at least about 12 inches and hammenngly drive the piston assembly, by hydraulic fluid, at a selectable frequency.

It is another pnmary object of the present invention to provide a combination linear vibrator}' pile driver apparatus and hammer type pile dπver apparatus to drive and to pull pilings compnsing: means for vibration isolating the cable from vibration of the pile dπver The means for isolating also limits movement of the lifting shaft relative to a vibratory assembly. The vibratory assembly compnses: a piston assembled and positioned concentrically around and in sliding association with the lifting shaft; a piston πng member extending radially from an outer surface of the piston; a frame assembly rigidly affixed to the piston. The frame assembly has a cable-end member, a clamp-end member and at least one connecting member connecting the cable-end member and the clamp-end member of the frame assembly. The frame cable-end member and the clamp-end member each cooperate v\ ith the means for isolating the cable and each are configured to limit sliding movement of the lifting shaft. The clamp-end attaches to the means for clamping (jaws). Further there is a reaction mass which has a cylinder wall member configured and assembled concentπcally around and in sliding association with the piston. The cylinder wall member to define, in combination with the piston and the piston nng member, a cylinder head cavity with two portions, a cylinder head cable-end cavity and a cylinder head clamp-end cavity. The cylinder head cavity is configured to permit the piston and the frame assembly movement of at least about 12 inches relative to the reaction mass and the cylinder wall, and wherein the cable-end member and the clamp-end member are located relative to the reaction mass to permit the movement of at least about 12 inches. The combination linear vibratory and hammer type pile driver further compnsing: means for providing fluid into the cylinder head cavity; and means for relative pressunzing at a determined and controlled frequency, each the cylinder head cable-end cavity and the cylinder head clamp-end cavity relative each to the other.

It is another pnmary object of the present invention to provide the combination linear vibratory and hammer type pile dnver apparatus as above where there may also be provided combination of the additional elements such as 1) a plurality of means for fluid-tight sealing of the fluid within the cylinder head cavity between the sliding association of the cylinder wall member and the piston; 2) a plurality of cylinder wall member beanng devices to make substantially fπctionless the sliding association of the cylinder wall member and the piston; 3) a plurality of lifting shaft beanng devices to make substantially fπctionless the sliding association of the piston with the lifting shaft; 4) means for indicating a position of a valve spool member within a spool valve; 5) means for determining location of the reaction mass relative to the frame assembly; 6) means for controUably varying the determined and controlled frequency of the relative pressuπzing; and 7) means for controlling a magnitude of pressure of the fluid into the cylinder head cavity.

It is yet another pnmary object of the present invention to provide the combination linear vibratory and hammer type pile dnver apparatus as above wherein the piston πng member extends radially from an outer surface of the piston and may be substantially at an axial midpoint of the piston and wherein the means for isolating is a form of spnng or spnngs such as dished washers, compression spnngs and elastomers. The means for providing fluid into the cylinder head cavity compnses: 1) at least one cable-end fluid port in fluid flow communication with the cylinder head cable-end cavity and in fluid flow communication with at least one first fluid channel; 2) at least one clamp-end fluid port in fluid flow communication with the cylinder head clamp-end cavity and in fluid flow communication with at least one second fluid channel. The means for relative pressunzing at a determined and controlled frequency, both the cylinder head cable-end cavity and the cylinder head clamp-end cavity relative each to the other compnses preferably a spool valve having a valve spool member and a spool controller; 3) a manifold block positioned adjacent to the spool valve to provide the proper porting configuration between each of the first fluid channel and each of the second fluid channel; 4) at least one excursion limiting means which is preferably a bumper pad fixedly attached to the frame clamp-end member; 5) at least one excursion limiting means which is preferably a bumper pad fixedly attached to the frame cable-end member for protecting the frame assembly from said reaction mass; and 6) a bumper cushion disposed between the lifting shaft clamp end and the frame clamp-end member.

It is still another pnmary object of the present invention to provide a method of dnving a pile using the combination linear vibratory and hammer type pile dπver as above descπbed. The method compnses the steps of: attaching and suspending, at a cable-end, the combination linear vibratory and hammer type pile driver to a cable of a crane; clamping a pile between gnpper jaws at a clamp-end of the pile dnver; placing the pile where it is to be dπven; providing means for isolating the cable from vibration of the pile dπver; imparting linear vibration to the pile, at the clamp-end by means of a vibratory assembly. The vibratory assembly compnses: a piston portion positioned concentrically around and in sliding association with a means for attaching and suspending the pile dπver, the piston portion having a piston ring member; a frame ngidly affixed to the piston, the frame having a cable- end member, a clamp-end member and at least one connecting member connecting the cable- end member and the clamp-end member. The cable-end member and the clamp-end member each cooperate with the means for isolating the cable and each configured to limit sliding movement of a means for attaching and suspending. The clamp-end is attachable to the means for clamping. A reaction mass is positioned concentπcally around and in sliding association with the piston portion and the reaction mass has a cylinder wall member configured to define, in combination with the piston πng, a cylinder cavity having a cylinder cable-end cavity and a cylinder clamp-end cavity. The cylinder head cavity being configured to permit the piston and the frame assembly movement of at least about 12 inches relative to the reaction mass and the cylinder wall, and wherein the cable-end member and the clamp-end member are located relative to the reaction mass to permit the movement of at least about 12 inches. Each of the cable-end cavity and clamp-end cavity is in fluid flow communication with a source of pressunzed fluid and a means for cyclically providing each of the cylinder cable-end cavity and cylinder clamp-end cavity with pressunzed fluid. The pressunzed fluid is provided into the cylinder head cavity. Each of the cavities is cyclically pressunzed relative to each other at a predetermined frequency. The frequency of relative pressuπzing is controllable frequency. The magnitude of relative pressure is also controllable independent of the controlled frequency and without effecting the controlled frequency.

It is a further pnmary object of the present invention to provide the method of dnving and pulling pilings as above wherein the following additional steps may be provided: 1) implanting at least one transducer in the ground; and 2) controlling the frequency of the vibration of the pile by integrating, in an electronic control unit, the output from each of the transducers implanted in the ground and the output from each of the transducers attached to the pile dnver.

It is a further object of the invention to provide a pile dnver which can both vibrate and hammer, either concurrently or separately.

It is a still further object of the invention to provide the combination linear vibratory and hammer type pile dnver descnbed above with an operating stroke length adjustable in such a manner so that the pile dπver may be used solely as a hammer type pile dnver.

It is a still further object of the invention to provide a pile dπver which can set piles to a predetermined "blow count", in a hammer type mode after the pile has been linearly vibratorily dnven to a predetermined depth using the same combination linear vibratory and hammer type pile dπver.

It is still a further object of the invention to provide a linear hydraulic vibratory pile dπver of such a configuration that it can fit between two sheet pilings without compromising power or efficiency. In such an embodiment, the central hydraulic section of the pile dnver can be relatively large, and the protruding outward portions can be relatively narrow (to fit between sheet pilings) while providing adequate mass to the total reaction mass. The frame assembly and the reaction mass are configured with an overall external geometry permitting locating the pile driver between sheet pilings when the pile driver is clamped onto a center section of a sheet piling to be dnven and extracted from between the sheet pilings.

These and further objects of the present invention will become apparent to those skilled in the art after a study of the present disclosure of the invention and with reference to the accompanying drawings which are a part hereof, wherein like numerals refer to like parts throughout, and in which:

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a front partial section view showing concentnc relationship of piston, isolator, cylinder, cylinder cavity, piston πngs, seals and beanngs;

FIG. 2 is a partial left side view of the device of figure 1 showing reaction mass position indicator attachment in cross section along with mass/frame slide alignment bearing,

FIG. 3 is a top partial view showing some of the bolt patterns needed for assembly of the pile dnver, the cable-end frame member is not shown so as to improve clanty;

FIG. 4 is a top section view of an alternate embodiment using rods as the frame connecting members but having the same concentnc relationship between elements;

FIG. 5 is a schematic sketch of the spool valve and valve spool member along with the spool valve position sensor and the control box; and

FIG. 6 is a sketch representing the linear vibratory pile dnver in use attached to a cable of a crane, a pile attached to the driver and a hydraulic power unit along with vibration sensors and control of the dnver based upon input from the sensors.

FIG. 7 is a partial side view of the pile dnver apparatus having a longer (over conventional vibratory drivers) maximum possible stroke length, longer internal hydraulic cylinder cavities and longer piston shaft length.

FIG 8 is a top partial view showing the pile dπver, either embodiment 10 or 100, fitting between two sheet pilings.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

The construction and the design of the combination linear vibratory and hammer type pile dnver 10 will be descπbed with reference to Figs. 1 - 8 collectively. Clearly, it is obvious that many sizes, power capabilities and forms and vaneties of geometπc configurations of the vanous basic parts of the pile dπver such as the shape of the reaction mass, the shape of the frame assembly (the frame connecting members could be rods instead of plates of mateπal) and the surface geometry may be used. However, the basic structure of the apparatus and the basic method of using the apparatus remains the same and the objectives and the advantages are clearly, lower cost, lower maintenance, more effective and efficient, constant vibratory power at different frequencies, adjustability to hammenng power alone, and an advantageous greater-than-one ratio of reaction mass to frame mass and no rotary eccentnc rotors.

COMBINATION LINEAR VIBRATORY AND HAMMER TYPE PILE DRIVER APPARATUS

The linear vibratory pile dnver 10 (shown in Figures 1-6) and the combination linear vibratory and hammer type pile driver 100 of Figure 7 are compnsed of two fundamental and basic assemblies - a lifting assembly, and a vibrator assembly. The two ends of dnver 10 are designated as the cable-end and the clamp-end. The dnver cable-end is the end of the dnver attachable to the cable 3 of a crane 2. The dnver clamp-end is the end of the dnver attachable to a piling 9 to be dnven or pulled. Cylinder/reaction mass assembly 50, dunng operation, is stable relative to piston/frame assembly 40 and consequently pile 9, if attached by jaws 23a, is caused to vibrate.

Figure 8 shows either embodiment 10 or 100 having a shape or configuration that it fits conveniently between two sheet pilings which are already in place and which may need to be further set deeper or which may need to be extracted. The shape is such that there is no compromising power or efficiency of the pile dnver. In such an embodiment, the central hydraulic section of the pile dnver can be relatively large, and the protruding outward portions can be relatively narrow (to fit between sheet pilings) while still providing adequate mass for the total reaction mass so that the dπver can linearly vibrate "against" or relative to the reaction mass.

Generalh , for linear vibratory pile dnver 10, lifting shaft 12 is within piston 16, piston ring portion 16c is within cylinder member 17 (preferably a machined sleeve 17 which inner wall 17c cooperates with piston rings 16d to create a seal) which is within a reaction mass central portion 25c. Frame 20 is connected to piston 16 at both the cable end and the clamp end Cylinder 17 is positioned within or connected to reaction mass central portion 25c. Toward the cable end and around piston 16 is piston/cylinder cable-end beanng 18a and toward the clamp end and around piston 16 is piston/cylinder clamp-end beanng 18b. Piston/reaction mass beanng and seal retainers 18 keeps beanngs 18a and 18b positioned within mass 25 and against cylinder sleeve 17 thereby keeping cylinder 17 positioned within mass 25 at both the cable end and the clamp end. Reaction mass first side member 25a and second side member 25b lie withm frame 20. Located on and withm reaction mass first side member 25a is means 29 for relatn e pressunzing at a determined and controlled frequency including means for providing fluid to each cylinder cable-end cavity 17a and cylinder clamp- end cavity 17b relative each to the other. I.e., the fluid under pressure is frequency controUably alternated between cable-end fluid conduit 17d to cable-end port 17c' and clamp- end fluid conduit 17e to clamp-end port 17c", i.e., the means for providing fluid to each cylinder. Means 29 is preferably a spool valve 29a, a valve spool member 29b and a manifold block 29c, and is attachable to reaction mass 25. There is also provided a means 28 for indicating spool position or centering the stroke of the pile dπver.

The lifting assembly is made up of a lifting shaft 12 having a lifting shaft cable-end 12a, a lifting shaft middle portion and a lifting shaft clamp-end 12b. Lifting shaft clamp-end 12b is configured with a flange portion below which may be a cushion pad 13c and on the flange surface rests a clamp-end of vibration isolator 14. Vibration isolator 14 also limits the movement of lifting shaft 12 within a piston inner cavity defined by piston inner wall 16a because the cable-end of isolator 14 is retained by isolator and lifting shaft cable-end beanng retainer 13 which is attached to frame cable-end member 21. Isolator 14 is further held in place by a cable-end frame member 21 and a clamp-end frame member 23 in addition to piston inner wall 16a Vibration isolator 14, which may be dished washers, compression spnngs, an elastomer matenal, gas spnngs or any other mateπal suitable for the purpose of vibration isolating. There is a lifting shaft cable-end bearing or bushing 13a and a lifting shaft clamp- end bushing 13b These bearing or bushings permit the smooth movement of lifting shaft 12 relative to clamp-end of piston 16 and a lifting shaft cable-end bearing retainer and isolator retainer 13.

Vibrator assembly is compπsed of piston 16 attached to a frame assembly 20, and a cylinder assembly or member 17 which cylinder member 17 is attached to or held within reaction mass 25. The piston/frame assembly 40 is in shdeable relation with cylinder/reaction mass assembly 50. Lifting shaft 12 of the lifting assembly is contained substantially within piston 16 and m shdeable relation with piston 16. There is also means for vibratonly dnving piston/frame assembly 40, by hydraulic fluid, at a selectable frequency thereby vibrating piston/frame assembly 40 relative to cylinder/reaction mass assembly 50. Such mean for vibratorily dnving includes piston ring portion 16c, rings 16d, cylinder cavities 17a and 17b, fluid ports 17c' and 17c", conduits 17d and 17e and means 29 for relative pressunzing at a determined and controlled frequency.

Lifting Assembly

In the present and preferred embodiments_, of the invention, lifting assembly compnses a lifting shaft 12 which is preferably in the form of a rod. Lifting shaft 12 has a cable-end portion 12a , a middle portion, and a clamp-end portion 12b. Clamp-end portion 12b has a diameter which is less than the inside diameter of piston 16 preferably by an amount which permits use of lifting shaft clamp-end beanng 13b. The lifting shaft middle portion and cable- end portion have a diameter around which will fit isolator 14 and isolator 14 has an outer diameter which fits inside the inner cavity of piston 16. Cable-end portion 12a may be fitted with a bale which connects to a lifting cable 3 of a crane 2. Lifting shaft 12 is fitted within the inner cavity of piston 16 on top of a cushion pad 13c. Cushion pad 13c rests on or is attached to a clamp-end frame member 23. On the lifting shaft clamp-end portion 12b there is a flange 12c. On a surface of flange 12c opposed from the surface on which lifting shaft 12 rests on cushion pad 13c there rests concentncally configured vibration isolator 14 which isolator 14 is sufficiently long to reach the lifting shaft cable-end portion 12a. A lifting shaft retainer 13 is attached to cable-end frame member 21. Lifting shaft retainer 13 also limits the movement or excursion of lifting shaft 12 relative to frame 20. Preferably, a cable-end and a clamp-end beanng or bushing 13a and 13b respectively is provided to reduce sliding fnction between lifting shaft cable-end portion 12a and frame 20 and between clamp-end portion 12b and piston inner wall 16a defining the lifting shaft/isolator cavity i.e., the inner cavity of piston 16.

Vibration isolator 14 in the preferred embodiment as shown, utilizes dished spnng washers which start to flatten out when strain is put on lifting cable 3 from crane 2 thus acting as a spnng to lessen the amplitude of vibration going from pile dπver apparatus 10 up cable 3 to crane 2. To

e isolator 14 a broader spring range, some of the disc spnngs may be thicker than others, the thinner ones flattening out first and the thicker ones taking over as more strain is exerted by hoisting cable 3. The spnng members instead of dished spring washers may be made from an elastomer such as synthetic rubber or polyurethane. As a yet different embodiment, the spring member may be a gas spnng or any other suitable form of compression spnng.

Vibrator Assembly

Piston Assembly

Piston 16 of piston assembly is preferably a thick walled tube. Within the inner cavity of piston 16 is located lifting shaft 12, the bushings 13a and 13b and cushion pad 13c along with isolator 14. In the present preferred embodiment there is a piston nng portion 16c about centrally located between the cable-end and the clamp-end of the piston 16 and which extends radially outward from the outer wall 16b of piston 16. At least one means for sealing but preferably a plurality of piston rings 16d are attachable to piston ring portion 16c. Piston 16 is attached to frame assembly 20 at cable-end frame member 21 and at clamp-end frame member 23. Piston nng portion 16c also defines a piston nng cable-end cavity wall 16c' and a piston nng clamp-end cavity wall 16c". These cavity walls 16c' and 16c" define, along with other defining walls, cylinder head cable-end cavity 17a and cylinder head clamp-end cavity 17b.

In the embodiment which can be used to both linearly vibrate and hammer piles, dπver 100, piston/frame assembly 40' as shown in Figure 7, differs from dnver 10 and piston/frame assembly 40 as follows: 1) piston shaft 16' has a length greater than the length of piston shaft 16 of dnver 10; 2) preferably, a portion of the increased length lies above and a portion lies below the piston nng portion 16c such that the pile dnver can have a total possible stroke of preferably about 12 to about 48 inches; 3) the lengths of cylinder cavities 17a' and 17b' are increased over the lengths of cylinder cavities 17a and 17b to permit the increase in the length of the stroke; 4) a cable-end fluid conduit 17d and a clamp-end fluid conduit 17e being within reaction mass 25 and particularly reaction mass first side member 25a, is redirected so as to enter cylinder cavities 17a' and 17b' at the top and at the bottom respective ; 5) the cylinder attached to the reaction mass forms cylinder/reaction mass assembly 50' ; 6) piston/cylinder cable-end beanng 18a and piston/cylinder clamp-end beanng 18b will necessanly be shorter than the beanngs used in dπver 10; and 7) means for indicating reaction mass location 27, if used, may also be lengthened to the same stroke capability. When used only as a linear vibratory pile driver, the machine may be used so that piston/frame assembly 40' will vibrate approximately in the center of the stroke at any appropnate frequency and within reaction mass 25. By positioning the piston toward either the clamp-end or the cable end, and by adjusting the power, i.e., the stroke length, the linear vibratory pile dπver 10 and 100 may function as a hammer and a vibrator concurrently using vibratory hammenng. For example, if the piston were positioned near the clamp end, the vibration amplitude would allow the reaction mass to slightly strike the excursion limiting means of the frame 19a, thus vibrating and hammenng concurrently. However, if the frequency of the vibrations is lowered and the piston is positioned toward either the clamp end or the cable end, the apparatus may function solely as a hammer type pile driver for either driving or pulling a pile. When used as a hammer type pile dnver, the reaction mass 25 becomes a hammer ram weight. Lowenng the frequency of the hydraulic cycling of fluid in and out of cylinder cavities 17a' and 17b' , to, for example, 1 Hz preferably, by lengthening the stroke from, for example, 12 inches to about 12 to 48 inches, and adjusting the center of the stroke so that the reaction mass 25, now turned into a hammer, strikes the lower excursion limiting means, bumpers, or cushion blocks 19a. In operation, this pile driving system can be used as a linear vibratory and a hammer type pile dnver. For example, a pile may be dnven to a specified depth using the vibratory mode, and then the stroke may be lengthened to, for example, the full possible 12 to 48 inches and the reaction mass allowed to fully impact on the lower end of the frame unit, on the excursion limiting means, bumpers, shock pads, or cushion blocks 19a, thus using the hammer mode to drive the pile to a given "blow count".

Cylinder Assembly

The cylinder assembly compnses a cylinder 17 having an inner cylinder wall 17c. Cylinder 17 is attached to and concentncally located inside reaction mass 25, particularly inside of reaction mass center portion 25c and the piston assembly is vibratonly positioned within cylinder assembly 17 Cylinder inner wall 17c cooperates with piston outer wall 16b, piston ring portion 16c and the surfaces or walls of the piston πng portion, cable-end cavity wall 16c' and 16c" and one end of piston/reaction mass cable-end beanng 18a and one end of piston/reaction mass clamp-end beanng 18b to define respectively cylinder cable-end cavity 17a and cylinder clamp-end cavity 17b. Cable-end and clamp-end fluid ports 17c' and 17c" each respectively admit fluid into cavity 17a and 17b which fluid is provided via a cable-end fluid conduit 17d and a clamp-end fluid conduit 17e the fluid conduit being withm reaction mass 25 and particularly reaction mass first side member 25a. The cylinder attached to the reaction mass forms cylinder/reaction mass assembly 50.

Piston/reaction mass cable-end seal 18a', and piston/reaction mass clamp-end seal 18b' provide a means for sealing cavities 17a and 17b preventing the loss of pressunzed fluid from these cavities when the apparatus 10 is operating. Each of the beanngs and seals 18a, 18a' and 18b, 18b' are held in place by retainer 18 which is attachable to cylinder/reaction mass assembly 50.

Frame Assembly

Frame 20 is attached to piston 16 at both the cable-end and the clamp-end. Frame cable- end member 21 attaches to the cable end of piston 16 and frame clamp-end member 23 attaches to the clamp-end of piston 16. Between frame members 21 and 23 is frame connecting member 22. In the embodiment illustrated in Figs. 1 - 3 connecting member 22 is show n in the form of a plate. There are four (4) such plates connecting frame members 21 and 23. Between the plates is reaction mass 25. On a first side of apparatus 10 and 100 is reaction mass first side member 25a which lies between two (2) of the plates 22. On a second side of apparatus 10 and 100 is reaction mass second side member 25b which lies between two (2) of the plates 22. Alignment bearing 19, shown in Fig. 3, may be provided to keep aligned the parts of means 27 for indicating reaction mass location since means 27 connects between reaction mass second side member 25b and frame cable-end member 21. This beanng 19 keeps the reaction mass 25 aligned between frame connecting member plates 22 or rods 22a particularly so that a means 27, when used, will remain properly aligned and functioning.

The frame assembly also has excursion limiting means, or bumper pads, 19a located on frame cable end member 21 and frame clamp end member 23, on the surfaces facing reaction mass 25 such that reaction mass 25 does not strike the frame cable and clamp end members duπng vibration or hammenng while dnving or pulling a pile. In the combination linear vibratory and hammer type embodiment 100, excursion limiting means or bumper pads 19a may be replaced by an impact-resistant matenal such as used in cushion blocks on conventional "impact" or hammer type pile dπvers.

The frame connecting members may have other forms such as rods 22a as illustrated in Fig. 4. Preferably at least four frame connecting member rods 22a would be used. Alignment of reaction mass 25 relative to frame 20 would be maintained using similar type beanngs as beanngs 19. COMBINATION LINEAR VIBRATORY AND HAMMER PILE DRIVER SYSTEM AND METHOD OF USE

Hydraulic power is supplied to the pile dnver by hydraulic power unit 6 by way of hydraulic power supply and return lines 6a. Hydraulic power supply and return lines 6a are connected to manifold block 29c which is positioned relative to servo valve/spool valve 29a to provide the proper configuration for alternating/switching the relative pressure between the input hydraulic fluid conduits 17d and 17e formed m reaction mass 25.

The servo valve/spool valve 29a cyclically alternates the application of hydraulic pressure to cylinder cable-end cavity 17a causing movement of piston/frame assembly 40 downward toward clamp-end and then the application of hydraulic pressure to cylinder cable- end cavity 17b causing movement of piston/frame assembly 40 upward toward cable-end, thus causing piston/frame assembly 40 to vibrate relative to cylinder/reaction mass assembly 50. The rate of the cyclic application of hydraulic pressure is preferably controlled by controlling servo valve 29a through signals transmitted from operator control 30 by a control cable attached to servo valve 29a. Preferably, the hydraulic fluid passes to cable-end and clamp-end cavities 17a and 17b respectively through cable-end fluid conduit 17d and clamp- end fluid conduit 17e formed in the reaction mass 25.

It is important to note that the relative difference of the hydraulic fluid pressure with cavities 17a and 17b is substantially independent of the frequency of the vibration. Thus power and frequency are controllable independent of each other.

Figure 6 illustrates pile dnver 10 connected to a crane 2 by hoisting cable 3. As discussed above, hoisting cable 3 is attachable to the lifting bale which is attachable to lifting shaft 12. The hydraulic power unit 6 is connected to pile dnver 10 by hydraulic power supply and return lines 6a. Means for operator control 30 (control box 30 or spool controller 30) of dnver 10 is shown to include as inputs, a vibration sensing transducer 7 affixed to pile dnver 10 and a vibration sensing transducer 8 implanted in ground 5. Control cables communicate the control signal from control box 30 to means 29 for frequency controlling the vibration of dnver 10.

To dπve a pile using the present invention, the following steps may be followed. Pile 9 should be gnpped between the gnpper jaws 23a. Highly pressunzed hydraulic fluid from a hydraulic power supply 6 should be supplied from hydraulic power unit 6 through hydraulic power supply and return lines 6a to servo valve 29a. Pile 9 should be placed in the location where it is to be dnven. Pile 9 should then be vibrated using linear vibratory pile dnver apparatus 10 at a predetermined and selected frequency and power.

The method of the present invention may also include the step of adjusting the frequency of vibration by adjusting the frequency control of servo valve 29a using control means 30. Further, the method may also include attaching at least one vibration sensing transducer 7 to pile dπver 10 and monitonng the frequency of the vibration. Additionally, the method may include implanting at least one vibration sensing transducer 8 in ground 5 and monitonng the frequency of the vibrations transmitted through the ground. Or transducer 8 may be placed on nearby structures for the purpose of monitonng the vibrations transmitted in the ground by the pile dnving process. The sensing of these vibrations is essential to the ability of the operator to "tune out" those frequencies which may resonate the surrounding ground in a harmful way without impeding the progress of the pile dnving operation.

Preferably, when vibration sensing transducers 7 and 8 are employed, the vibration rate of pile dnver apparatus 10 and consequently the vibration of pile 9 may be automatically controlled by using the output of transducers and using or integrating this output to determine optimum frequency and power.

Vibration sensing transducers 7 and 8 may be accelerometers. The frequency of vibration and the progression of the pile may be both monitored and controlled by control means/box 30.

The method of the present invention may also include the step of dnving a pile to a specified depth using the vibratory mode of pile dnver 100. Driver 100 is then adjusted to operate in the hammenng mode to dnve the pile to a specific "blow count". This step is accomplished by lowenng the hydraulic fluid cycling frequency to preferably about one cycle per second (1 Hz) and adjusting the center of the stroke so that the reaction mass is allowed to fully impact on the lower end of the frame unit, on the bumpers, shock pads, or cushion blocks 19a, thereby using pile driver 100 in hammer mode to dnve the pile to a given "blow count".

Control device, or spool controller 30 is employed so that the operator may start, stop and control the vibration frequency of pile dnver apparatus 10 or 100 at will. Also, control box 30 may be programmed to seek the ideal vibration frequency at which the apparatus should best run, depending on the soil and site conditions. The optimal dnving frequency may be employed and undesirable frequencies may be excluded.

Within certain constraints, unit 6 is a "constant" power vibratory pile dnving power source. I.e. at a

en power unit pressure, where the frequency of vibration is lowered as controlled by electronic control unit 30, the amplitude (distance traveled by each stroke of the vibration) increases When the frequency is raised, the amplitude of each vibration decreases. The main constraint being the ability of a servo valve to deliver hydraulic fluid efficiently as the commanded frequency is increased. Most large size servo valves start to lose fluid delivery efficiency around 100 Hz. Obviously, the other constraint is the ability of the hydraulic power unit and hoses and dπlled passages such as those in the manifold block and the passages dnlled in the reaction mass, to supply hydraulic fluid with a minimum of pressure drop.

Thus, to dπve a pile using the present invention the following steps are followed:

1. The hydraulic power unit 6 is started and high pressure hydraulic fluid is supplied through the delivery hose 6a to servo valve 29a through manifold block 29c.

2. Pile 9 is placed between pile gnpper jaws 23a and the gnpper jaw piston (not shown) The clamping assembly is pressunzed by controls and hoses (not shown), to clamp the pile in place in line with the axis of the pile dnver 10 or dπver 100.

3. Pile 9 attached to pile driver apparatus 10 or dnver 100 is lowered by crane 2 to the point where the weight of the pile dπver and the pile are beanng on the ground (the pile and pile dπver may be guided by the use of "leads" which attached to can hold in proper position guide the pile dnver and pile to the specific place where the pile is to be dπven,) or the pile may be locked into engagement with a previously dπven pile as is the practice when dnving "sheet" pilings which are used for building either permanent or temporary retaining walls. Sometimes piles are "started" by carefully positioning the pile and dπver at the spot where the pile is to be dnven and then the pile is skillfully lowered as the vibratory pile dnver is turned on and lowered slowly until the pile has penetrated the ground sufficiently enough so that it will stand on its own, then the crane may slack the hoisting cable and allow the full weight of the pile dπver to bear on the top of the pile, this facilitating the dnving of the pile as the vibratory pile driver is turned up to full power.

4. Once pile 9 has started to be driven by linear vibratory driver 10 or by combination linear vibraton and hammer type driver 100, the operator may "tune" the apparatus to the most desirable frequency for speed of driving by manually adjusting the frequency control settings on the electronic control unit to the point where he observes that the pile is being driven fastest. Once he sets the control unit at a given frequency, it will stay there unless he changes the adjustment. In places where it is unsafe to use certain frequencies of vibration, for instance where they might cause damage to a structure or even be a nuisance, the electronic control unit be set to specifically exclude those frequencies, and the operator may then use either above or below the cπtical frequencies.

5. Electronic spool control unit 30 may be programmed to either exclude certain frequencies or not, but also it may be set up to sense the rate of driving by the use of an accelerometer attached to apparatus 10 or dπver 100, by which it will automatically seek the frequencies which will dnve the pile at the fastest rate for the given dnving site. The electronic control 30 unit may also monitor the vibrations being transmitted through the ground from the pile being dnven, utilizing ground implanted accelerometer 8. If the vibrations reach a level deemed to be harmful to nearby structures for instance, the control unit may automatically turn the pile dnver to a frequency which does not shake the ground as much. The electronic control unit may be programmed to integrate the input from the accelerometer transducer attached to the pile dnver which monitors dnving speed and frequency, as well as the ground implanted accelerometer transducer which monitors frequency and amplitude of the vibrations being transmitted through the ground using the data from both transducers, the monitor can automatically seek the best dnving frequency and at the same time make sure that no unwanted frequency amplitudes are emanating from the pile dnving site.

6. Once a piling is vibratoπly dπven to a specified depth, the combination linear vibratory and hammer type pile dnver 100 may be adjusted from a vibratory to a hammer mode to dnve the piling to a specific final blow count. The adjustment is made by using spool controller 30 to reduce the frequency of the cyclic hydraulic pressunzing to about 1 Hz, thereby increasing the amplitude of the vibrations, and therefore the length of each stroke of the pile driver, such that reaction mass 25 impacts on the lower excursion limiting means 19a of the frame portion to hammer the piling into final position. It is understood that dπver 100 may be used exclusively in the hammer mode to dπve a pile, i.e., the pile need not be vibrated.

Figure 6 illustrates pile dπver 10 connected to a crane 2 by hoisting cable 3. As discussed above, hoisting cable 3 is attachable to the lifting bale which is attachable to lifting shaft 12. The hydraulic power unit 6 is connected to pile dπver 10 by hydraulic power supply and return lines 6a. Means for operator control 30 (control box, or spool controller 30) of driver 10 is shown to include as inputs, a vibration sensing transducer 7 affixed to pile dnver 10 and a vibration sensing transducer 8 implanted in ground 5. Control cables communicate the control signal from control box 30 to means 29 for frequency controlling the vibration of driver 10

Figure 8 illustrates the advantages of the preferred shape of dπvers 10 and 100. Because of the geometry of drivers 10 and 100, they will fit between sheet piling 52 when clamped onto the center portion of the end of a sheet piling which is to be either inserted between or extracted from between two sheet pilings. Even with such a shape, the total weight of the cylinder/reaction mass assembly 50 or 50' is substantially heavier than the piston/frame assembly 40 or 40' . Reaction mass first side member and second side member 25a and 25b and reaction mass central portion/member 25c are all shaped to fit between two sheet pilings

It is also thought that linear vibratory pile dnvers 10 and 100 and their use, and manner of use and many of its attendant advantages will be understood from the foregoing descnption and it will be apparent that various changes may be made in the form, construction and arrangement of the parts thereof without departing from the spirit and scope of the invention or sacrificing all of its matenal advantages, the form hereinbefore descπbed being merely a prefeπed or exemplary embodiment thereof

Claims

CLAIMS What is claimed is:

1. A linear vibratory pile dnver apparatus to d╧Çve and to pull pilings compnsing: a lifting shaft vibration isolated from, but slideably mounted withm, a piston assembly, said piston assembly attached to a frame assembly, said frame assembly restncting sliding movement of said lifting shaft within said piston assembly; means for vibration isolating said hfing shaft from said pistion assembly; a cylinder assembly attached to a reaction mass, said piston assembly vibratonly positioned within said cylinder assembly; and means for vibratonly driving said piston assembly, by hydraulic fluid, at a selectable frequency thereby vibrating said piston assembly and said attached frame assembly relative to said cylinder assembly attached to said reaction mass assembly.

2 A linear vibiatory pile driver having a cable-end and a clamp-end thereof comprising a lifting shaft having a cable-end and a clamp-end, said lifting shaft adaptable for attaching and suspending said pile dnver, at said cable-end, to a cable; means for vibration isolating said cable from vibration of said pile dnver, said means for isolating also limiting movement of said lifting shaft relative to a vibratory assembly; said vibratory assembly compnsing: a piston assembled and positioned concentncally around and in sliding association with said lifting shaft; a piston ╧Çng member extending radially from an outer surface of said piston; a frame assembly rigidly affixed to said piston, said frame assembly having a frame cable-end member, a frame clamp-end member and at least one frame connecting member connecting said cable-end member and said clamp-end member, said cable-end member and said clamp-end member each cooperating with said means for isolating said cable and each configured to limit sliding movement of said lifting shaft, said frame clamp-end attachable to said means for clamping; a reaction mass having a cylinder wall member configured and assembled concentncally around and in sliding association with said piston, said cylinder wall member to define, in combination with said piston and said piston nng member a cylinder head cavity having a cylinder head cable-end cavity and a cylinder head clamp- end cavity; said linear vibratory pile d╧Çver further compnsing: means for providing fluid into said cylinder head cavity; and means for relative pressurizing at a determined and controlled frequency, each said cylinder head cable-end cavity and said cylinder head clamp-end cavity relative each to the other.

3. The linear vibratory pile d╧Çver according to claim 2 further compnsing a plurality of means for fluid-tight sealing of said fluid within said cylinder head cavity between said sliding association of said cylinder wall member and said piston.

4. The linear vibratory pile dnver according to claim 2 further compnsing a plurality of cylinder wall member beanng devices to make substantially fnctionless said sliding association of said cylinder wall member and said piston.

5. The linear vibratory pile d╧Çver according to claim 3 further compnsing a plurality of cylinder wall member bearing devices to make substantially f╧Çctionless said sliding association of said cylinder wall member and said piston.

6 The linear vibratory pile d╧Çver according to claim 2 further compnsing a plurality of lifting shaft beanng devices to make substantially fnctionless said sliding association of said piston with said lifting shaft.

7. The linear vibratory pile d╧Çver according to claim 3 further compnsing a plurality of lifting shaft bearing devices to make substantially fnctionless said sliding association of said piston with said lifting shaft.

8. The linear vibratory pile dnver according to claim 5 further compnsing a plurality of lifting shaft beanng devices to make substantially fnctionless said sliding association of said piston with said lifting shaft.

9. The linear vibratory pile d╧Çver according to claim 2 wherein said means for relative pressu╧Çzing at a determined and controlled frequency is a spool valve having a valve spool member, said linear vibratory pile dnver further compnsing means for indicating a position of said valve spool member within said spool valve.

10. The linear vibratory pile dnver according to claim 5 wherein said means for relative pressunzing at a determined and controlled frequency is a spool valve having a valve spool member, said linear vibratory pile dnver further compnsing means for indicating a position of said valve spool member within said spool valve.

11. The linear vibratory pile d╧Çver according to claim 8 wherein said means for relative pressunzing at a determined and controlled frequency is a spool valve having a valve spool member and a spool controller, said linear vibratory pile driver further compnsing means for indicating a position of said valve spool member within said spool valve.

12. The linear vibratory pile d╧Çver according to claim 2 further compnsing means for determining location of said reaction mass relative to said frame assembly.

13. The linear vibratory pile driver according to claim 11 further comprising means for determining location of said reaction mass relative to said frame assembly.

14 The linear vibratory pile d╧Çver according to claim 5 further comprising; means for controUably varying said determined and controlled frequency of said relative pressu╧Çzing; and means for controlling a magnitude of pressure of said fluid into said cylinder head cavity.

15. The linear vibratory pile d╧Çver according to claim 8 further compnsing; means for controUably varying said determined and controlled frequency of said relative pressurizing; and means for controlling a magnitude of pressure of said fluid into said cylinder head cavity

16. The linear vibratory pile driver according to claim 11 further compnsing; means for controUably varying said determined and controlled frequency of said relative pressurizing; and means for controlling a magnitude of pressure of said fluid into said cylinder head cavity.

17. The linear vibratory pile driver according to claim 13 further comprising; means for controUably varying said determined and controlled frequency of said relative pressu╧Çzing; and means for controlling a magnitude of pressure of said fluid into said cylinder head cavity.

18. The linear vibratory pile dnver according to claim 15 wherein said piston ╧Çng member extends radiall} from an outer surface of said piston and is substantially at an axial mid-pomt of said piston, wherein said means for isolating is at least one device selected from the group consisting of spnngs, dished washers, and elastomers; and wherein said means for providing fluid into said cylinder head cavity compnses: at least one cable-end fluid port in fluid flow communication with said cylinder head cable-end cavity and in fluid flow communication with at least one first fluid channel; at least one clamp-end fluid port in fluid flow communication with said cylinder head clamp-end cavity and in fluid flow communication with at least one second fluid channel, said means for relative pressunzing at a determined and controlled frequency, each said cylinder head cable-end cavity and said cylinder head clamp-end cavity relative each to the other comprises a spool valve having a valve spool member and a spool controller; a manifold block positioned adjacent to said spool valve to provide the proper porting configuration between each said at least one fluid channel and each said at least one second fluid channel; at least one bumper fixedly attached to said frame clamp-end member; at least one bumper fixedly attached to said frame cable-end member for protecting said frame assembly from said reaction mass; and a bumper disposed between said lifting shaft clamp end and said frame clamp-end member.

19. A method of dnving a pile using a linear vibratory pile dnver, comprising the steps of: attaching and suspending, at a cable-end, said linear vibratory pile dnver to a cable of a crane; clamping a pile between gnpper jaws at a clamp-end of said pile dnver; placing said pile where it is to be dnven; providing means for isolating said cable from vibration of said pile d╧Çver; imparting linear vibration to said pile, at said clamp-end, by means of a vibratory assembly, said vibratory assembly compnsing: a piston portion positioned concentrically around and in sliding association with a means for attaching and suspending said pile d╧Çver, said piston portion having a piston ╧Çng member ; a frame portion rigidly affixed to said piston portion, said frame portion having a cable-end member, a clamp-end member and at least one connecting member connecting said cable-end member and said clamp-end member, said cable-end member and said clamp-end member each cooperating with said means for isolating said cable and each configured to limit sliding movement of said means for attaching and suspending, said clamp-end attachable to said means for clamping; a reaction mass positioned concentncally around and in sliding association with said piston portion, said reaction mass having a cylinder wall member configured to define, in combination with said piston portion, said piston ring member a cylinder head cavity having a cylinder head cable-end cavity and a cylinder head clamp-end cavity, each said cable-end cavity and said clamp-end cavity in fluid flow communication with a source of pressunzed fluid and a means for cyclically providing each said cylinder head cable-end cavity and said cylinder head clamp-end cavity with said pressunzed fluid; providing said pressunzed fluid into said cylinder head cavity; and relative pressunzing, cyclically at a predetermined frequency, each said cylinder head cable-end cavity and said cylinder head clamp-end cavity; controlling frequency of said relative pressurizing; and controlling magnitude of relative pressure independent of said controlled frequency and without effecting said controlled frequency.

20. The method of claim 19 further compnsing the steps of: implanting at least one transducer in the ground; and controlling the frequency of the vibration of the pile by integrating, in an electronic control unit, the output from said at least one transducer implanted in the ground and the output from said at least one transducer attached to the pile dnver.

21. A combination linear vibratory and hammer type pile d╧Çver apparatus to d╧Çve and to pull pilings compnsing: a lifting shaft vibration isolated from, but slideably mounted withm, a piston assembly, said piston assembly attached to a frame assembly, said frame assembly restncting sliding movement of said lifting shaft within said piston assembly; means for vibration isolating said lifting shaft from said piston assembly; a cylinder assembly attached to a reaction mass, said piston assembly vibratonly positioned within said cylinder assembly; means for vibratonly dnving said piston assembly, by hydraulic fluid, at a selectable frequency thereby vibrating said piston assembly and said attached frame assembly relative to said cylinder assembly attached to said reaction mass assembly; and means for causing said reaction mass to move relative to said piston assembly a distance of at least about 12 inches and hamme╧Çngly drive said piston assembly, by hydraulic fluid, at a selectable frequency.

22. A combination linear vibratory and hammer type pile dnver having a cable-end and a clamp-end thereof compnsing: a lifting shaft having a cable-end and a clamp-end, said lifting shaft adaptable for attaching and suspending said pile dnver, at said cable-end, to a cable; means for vibration isolating said cable from vibration of said pile dnver, said means for isolating also limiting movement of said lifting shaft relative to a vibratory assembly; said vibratory assembly compnsing. a piston assembled and positioned concentncally around and in sliding association with said lifting shaft; a piston nng member extending radially from an outer surface of said piston; a frame assembly rigidly affixed to said piston, said frame assembly having a frame cable-end member, a frame clamp-end member and at least one frame connecting member connecting said cable-end member and said clamp-end member, said cable-end member and said clamp-end member each cooperating with said means for isolating said cable and each configured to limit sliding movement of said lifting shaft, said frame clamp-end attachable to said means for clamping; a reaction mass having a cylinder wall member configured and assembled concentncally around and in sliding association with said piston, said cylinder wall member to define, in combination with said piston and said piston nng member a cylinder head cavity having a cylinder head cable-end cavity and a cylinder head clamp-end cavity, said cylinder head cavity being configured to permit said piston and said frame assembly movement of at least about 12 inches relative to said reaction mass and said cylinder wall, and wherein said cable-end member and said clamp-end member are located relative to said reaction mass to permit said movement of at least about 12 inches, said combination linear vibratory and hammer type pile dnver further compnsing: means for providing fluid into said cylinder head cavity; and means for relative pressunzing at a determined and controlled frequency, each said cylinder head cable-end cavity and said cylinder head clamp-end cavity relative each to the other.

23. The combination linear vibratory and hammer type pile driver according to claim 22 further comprising a plurality of means for fluid-tight sealing of said fluid withm said cy linder head cavity between said sliding association of said cylinder wall member and said piston.

24. The combination linear vibratory and hammer type pile d╧Çver according to claim 22 further comprising a plurality of cylinder wall member bearing devices to make substantially fnctionless said sliding association of said cylinder wall member and said piston.

25. The combination linear vibratory and hammer type pile d╧Çver according to claim 23 further comprising a plurality of cylinder wall member beanng devices to make substantially fnctionless said sliding association of said cylinder wall member and said piston.

26. The combination linear vibratory and hammer type pile dnver according to claim 22 further compnsing a plurality of lifting shaft bearing devices to make substantially fnctionless said sliding association of said piston with said lifting shaft.

27. The combination linear vibratory and hammer type pile driver according to claim 23 further compnsing a plurality of lifting shaft beanng devices to make substantially fnctionless said sliding association of said piston with said lifting shaft.

28. The combination linear vibratory and hammer type pile dnver according to claim 25 further compnsing a plurality of lifting shaft beanng devices to make substantially fnctionless said sliding association of said piston with said lifting shaft.

29. The combination linear vibratory and hammer type pile dnver according to claim 22 wherein said means for relative pressunzing at a determined and controlled frequency is a spool valve having a valve spool member, said linear vibratory pile dnver further compnsing means for indicating a position of said valve spool member withm said spool valve.

30. The combination linear vibratory and hammer type pile driver according to claim 25 wherein said means for relative pressu╧Çzing at a determined and controlled frequency is a spool valve having a valve spool member, said linear vibratory pile dnver further compnsing means for indicating a position of said valve spool member within said spool valve.

31. The combination linear vibratory and hammer type pile dnver according to claim 28 wherein said means for relative pressunzing at a determined and controlled frequency is a spool valve having a valve spool member and a spool controller, said linear vibratory pile d╧Çver further compnsing means for indicating a position of said valve spool member within said spool valve.

32. The combination linear vibratory and hammer type pile dnver according to claim 22 further compnsing means for determining location of said reaction mass relative to said frame assembly.

33. The combination linear vibratory and hammer type pile d╧Çver according to claim 31 further compnsing means for determining location of said reaction mass relative to said frame assembly

34. The combination linear vibratory and hammer type pile driver according to claim 25 further compnsing; means for controUably varying said determined and controlled frequency of said relative pressu╧Çzing; and means for controlling a magnitude of pressure of said fluid into said cylinder head cavity.

35. The linear vibratory pile dnver according to claim 28 further compnsing; means for controUably varying said determined and controlled frequency of said relative pressu╧Çzing; and means for controlling a magnitude of pressure of said fluid into said cylinder head cavity

36. The combination linear vibratory and hammer type pile dnver according to claim 31 further compnsing; means for controUably varying said determined and controlled frequency of said relative pressu╧Çzing; and means for controlling a magnitude of pressure of said fluid into said cylinder head cavity.

37. The combination linear vibratory and hammer type pile dnver according to claim 33 further compnsing; means for controUably varying said determined and controlled frequency of said relative pressunzing; and means for controlling a magnitude of pressure of said fluid into said cylinder head cavity

38. The combination linear vibratory and hammer type pile d╧Çver according to claim 35 wherein said piston ╧Çng member extends radially from an outer surface of said piston and is substantially at an axial mid-point of said piston, wherein said means for isolating is at least one device selected from the group consisting of spnngs, dished washers, and elastomers; and wherein said means for providing fluid into said cylinder head cavity compnses: at least one cable-end fluid port in fluid flow communication with said cylinder head cable-end cavity and in fluid flow communication with at least one first fluid channel; at least one clamp-end fluid port in fluid flow communication with said cylinder head clamp-end cavity and in fluid flow communication with at least one second fluid channel, said means for relative pressunzing at a determined and controlled frequency, each said cylinder head cable-end cavity and said cylinder head clamp-end cavity relative each to the other compnses a spool valve having a valve spool member and a spool controller; a manifold block positioned adjacent to said spool valve to provide the proper porting configuration between each said at least one first fluid channel and each said at least one second fluid channel; at least one excursion limiting means fixedly attached to said frame clamp-end member; at least one excursion limiting means fixedly attached to said frame cable-end member for protecting said frame assembly from said reaction mass; and a bumper cushion disposed between said lifting shaft clamp end and said frame clamp- end member.

39 A method of dnving a pile using a combination linear vibratory and hammer type pile dnver, compnsing the steps of: attaching and suspending, at a cable-end, said linear vibratory and hammer type pile dnver to a means of suspending said linear vibratory and hammer type pile driver; clamping a pile between gnpper jaws at a clamp-end of said pile dnver; placing said pile where it is to be driven; providing means for isolating said cable from vibration of said pile driver; imparting linear vibration to said pile, at said clamp-end, by means of a vibratory assembly, said vibratory assembly compnsing: a piston assembled and positioned concentncally around and in sliding association with said lifting shaft; a piston nng member extending radially from an outer surface of said piston; a frame assembly ngidly affixed to said piston, said frame assembly having a frame cable-end member, a frame clamp-end member and at least one frame connecting member connecting said cable-end member and said clamp-end member, said cable-end member and said clamp-end member each cooperating with said means for isolating said cable and each configured to limit sliding movement of said lifting shaft, said frame clamp-end attachable to said means for clamping; a reaction mass having a cylinder wall member configured and assembled concentncally around and in sliding association with said piston, said cylinder wall member to define, in combination with said piston and said piston ╧Çng member a cylinder head cavity having a cylinder head cable-end cavity and a cylinder head clamp-end cavity, said cylinder head cavity being configured to permit said piston and said frame assembly movement of at least about 12 inches relative to said reaction mass and said cylinder wall, and wherein said cable-end member and said clamp-end member are located relative to said reaction mass to permit said movement of at least about 12 inches; providing said pressunzed fluid into said cylinder head cavity and relative pressunzing, cyclically at a predetermined frequency, each said cylinder head cable-end cavity and said cylinder head clamp-end cavity; controlling frequency of said relative pressunzing; controlling magnitude of relative pressure independent of said controlled frequency and without effecting said controlled frequency; thereby vibratonly driving said piling to a depth; reducing said controlled frequency; adjusting said pile d╧Çver such that said reaction mass strikes an excursion limiting means; and hammering said piling to a blow count.

40. The method of claim 39 further compnsing the steps of: implanting at least one transducer in the ground; controlling the frequency of the vibration of the pile by integrating, in an electronic control unit, the output from said at least one transducer implanted in the ground and the output from said at least one transducer attached to the pile d╧Çver.

41. The method of driving a pile using a combination linear vibratory and hammer type pile driver comprising the steps of: placing the pile in position to be dnven; vibrating the pile to a given depth; and hammenng the pile to a blow count using the same combination linear vibratory and hammer type pile dnver.

42. A combination linear \ ibratory and hammer type pile dnver apparatus to d╧Çve and pull a pile comprising: means for attaching said pile d╧Çver to a means for lifting, suspending and guiding said pile; means for vibratonly operating said pile d╧Çver at a vibrational frequency to dnve said pile; means for hamme╧Çngly operating said pile d╧Çver; and means for changing said pile d╧Çver operation from said vibratory operation to said hammering operation.

43. The combination linear vibratory and hammer type pile driver apparatus according to claim 42 further comprising: means for switching said pile driver operation to be concurrently both vibratorily operating and hammeringly operating.

44. The combination linear vibratory and hammer type pile driver according to claim 21 wherein said frame assembly and said reaction mass are configured with an overall external geometry permitting locating said pile driver between sheet pilings when said pile driver is clamped onto a center section of a sheet piling to be driven and extracted from between said sheet pilings.