The present invention relates to an apparatus and method, notably to an apparatus for causing a body to move linearly in response to the energy stored in an elastomeric driver unit and to a method for causing such movement.

BACKGROUND TO THE INVENTION:

Typically, pile drivers and hydraulic hammers incorporate a weight which is carried upon a guide frame for reciprocating travel. The weight is raised against gravity by an hydraulic ram to which high pressure fluid is applied to extend the ram. When the weight has been raised to the desired extent, the high pressure fluid is vented from the ram and the weight is allowed to fall under gravity upon the pile, ground compaction foot, ground breaker tool or other object upon which the weight is to act. The hydraulic ram can act directly upon the weight, for example as when the weight is attached to the piston rod of the ram and is raised as the piston within the cylinder of the hydraulic ram is raised. Alternatively, the hydraulic ram can act indirectly upon the weight, as when the weight is attached to the piston rod of the hydraulic cylinder by a rope which passes over a pulley at or adjacent the top of the guide frame or as when the hydraulic cylinder acts upon the end of a lever arm connected to the weight.

The operation of the hydraulic ram serves to raise the weight against gravity to the desired extent to achieve the desired impact blow upon the object being acted upon when the ram is allowed to contract. The object can be, for example the top of a pile which is to be driven into the ground, a ground compaction foot which is used to compact or level the ground, or an earth or concrete breaker tool which it is desired to

SUMMARY OF THE INVENTION:

Accordingly, the present invention provides apparatus for applying additional momentum to the movement of a body adapted to reciprocate or flex through a substantially linear or arcuate path, notably for increasing the impact velocity of a linearly travelling weight upon an object, which apparatus comprises means for retracting the body from its rest position, notably for retracting a weight from the point of impact between the weight and an object located at the rest position of the weight, means for biassing the body towards its rest position, notably for urging the weight towards the object so as to impart additional impact velocity to the weight as it travels towards the object, characterised in that: a. the means for biassing the body towards its rest position is an elastic polymeric material which is retained under tension or compression when the body is in its rest position; and b. the biassing means is one which undergoes strain crystallisation.

The invention also provides a method for breaking up or penetrating a surface by applying impact blows to a tool in contact with the surface, characterised in that impact blows are applied by an apparatus of the invention.

The term rest position is used herein to denote that position which the weight or structure adopts during operation of the apparatus in the absence of the retracting force. In the case of a structure which is being flexed under the influence of the retracting and biassing forces, the rest position will be that position adopted by the structure in the absence of the retracting force but the biassing force may or may not continue

to be applied. Thus, the biassing force may simulate a constant load which is applied to the structure, for example the lifting force of an aircraft wing during normal flight, and the retracting force simulates abnormal loading of the wing, as may occur during turbulence. In this case, the wing will be subjected to a continuous biassing force which will cause the wing to adopt an upwardly flexed configuration which is the rest position about which the wing flexes. In other cases, the biassing force may represent some other load imposed upon the wing which is not normally present, in which case the rest position would be that position adopted by the wing in the absence of both the retracting and biassing forces. In the case of a falling weight of a hammer, the rest position is the position of impact between the weight and the object which it is to strike, in which case the weight may still be subject to some residual biassing force. However, it will be appreciated that the weight may travel beyond the point of impact, for example during over-run of the travel of the weight or when the hammer operation is completed and the weight is allowed to fall to its lowest or out of operation point at which the residual biassing force may be negligible. This over-run extreme of travel or out of operation point will usually be ^' located axially beyond the rest position at which the weight would impact upon the object and is not considered to be the rest position for the purposes of the present invention.

The retracting force is generated by any suitable means, for example a cam and follower type mechanism where the movement required of the body is small, as may be the case with a fatigue test. However, it will usually be desired to retract the body a distance of tens of centimetres from its rest position and it will therefore be preferred to generate the retracting force by means of an hydraulic ram or rams. For convenience, the invention will be described hereinafter in

rams to adjust the fore and aft and side to side inclination of the guide rails or other supports upon the which the weight travels.

The hydraulic ram is operated by the application and release of high pressure fluid to the cylinder of the ram which extends or retracts a piston rod extending from the piston within the cylinder of the ram. The means for generating the high pressure fluid, controlling its flow to and from the cylinder and any accumulators required to accommodate the flow of fluid can be of conventional design and construction. The operation of the hydraulic ram is preferably controlled by sensors which detect the upper and lower extremes of the travel -of the weight and control the operation of the valve mechanisms controlling the flow of high pressure fluid into and out of the cylinder of the ram. Such control sensors can be of conventional design and operation. Preferably, the hammer assembly incorporates means whereby the weight can travel beyond its rest position, for example when the chisel tool is accidentally removed from the equipment so that the weight does not impact upon an object at the end of its travel or if the operative tip of the chisel tool is not in contact with the ground or the concrete or stone to be broken up. Typically, such excess travel or over-run is provided with energy absorbing means whereby the impact energy of the weight is at least in part absorbed or dissipated before the end of the over-run of the weight is reached. For example, the over-run can be against friction pads, rubber stops, hydraulic accumulators, or other elastic, viscous or visco- elastic means. Preferably, sensor means are incorporated in the hammer assembly to detect when over-run occurs, notably to de-active further operation of the hammer and to provide an audible and/or visual alarm to an operator.

The means for generating the biassing force for driving the

weight downwardly upon the object when the ram reaches the extreme of its lifting stroke comprises an elastic polymeric material which acts under compression and/or tension to store energy as the weight is retracted from the object by the hydraulic ram. The elastomeric polymer can be formed into any suitable shape to suit the configuration of the hammer assembly into which it is to be incorporated. For example,- the polymeric material can be moulded, extruded or cast as an axially elongated solid rod, bar or strip of material, notably one having radially enlarged terminal portions to form the means by which the lengths of material can be secured to the moving weight and a static part of the hammer assembly. However, it is preferred to form a plurality of substantially linear strands of the polymer into a rope or similar body which is tensioned as the weight is raised. Typically, such a rope will comprise a plurality of linear untwisted individual strands of a suitable polymer or a mixture of strands of different polymers. If desired, the rope formed from the individual strands can be sheathed in a sleeve to form a coherent structure to the rope and to reduce damage to the strands due to abrasion and/or contact with hydraulic fluids or the like. For convenience hereinafter the term 'internal structure of the rope will be used to denote the strands of polymer within the protective sheath and the term rope will be used to denote the overall construction of the strands and the protective sheath. Preferably, such sheath is in the form of a braided relatively inextensible textile yarn which is applied, for example by means of a conventional braiding machine, to form a close fitting sheath upon the internal structure of the rope whilst the internal structure of the rope is held in an extended condition. Typically, this extension is from 40 to 200% of the untensioned state of the rubber strands before they enter the braiding process. Upon relaxation of the tension on the internal structure of the rope, the close fit of the sheath

structure of the rope are held under tension at all times and are thus retained under strain crystallisation at all times. As indicated above, at least part of this extension is due to the close fit of the sheath upon the internal structure of the rope. However, it is preferred to locate the mountings for the rope upon the hammer assembly so that the weight in its rest position imparts at least 15% further extension to the rope, this further extension being over and above the extension imparted in its sheathed state as manufactured as described above. However, it is preferred that the maximum upward travel of the weight should not extend the rope by more than 95% of its length in the sheathed state as manufactured. It is also preferred that the extra travel of the weight which may occur during any over-run as described above does not allow the rope to return to the unextended state of its sheathed form.

The rope can be secured to the weight, the yoke carrying the weight or any other suitable part of the hammer assembly which travels with the weight; and to any part of the hammer assembly which does not travel with the weight as it falls to provided the static anchorage point for the rope. The rope can be secured using any suitable securing means. Where the rope is formed as a solid bar or rod of the polymeric material, the securing means can be formed integrally with the rod or bar as ^• an enlarged end to the rod or bar during the moulding, extrusion or other process for forming the rod or bar from the polymeric material so that the bar or rod has a generally dumbbell configuration. Where the biassing force is generated by a rope comprising a plurality of thin strands, it may not be practicable to form the securing means in this manner and we have devised a particularly compact and effective means as described below for securing the ends of the strands of the rope in position in a terminal bobbin unit which resists detachment during the repeated tensioning and slackening of the

of a cup into which the free ends of the strands are inserted and secured by the adhesive or cement.

Such a means for securing the ends of the strands of the internal structure of the rope provides adequate security for many applications. However, in order to minimise the risk of separation of the strands from the end cap, it is preferred to provide, a secondary securing means immediately adjacent the end cap which also is secured to the strands and co-operates with the end cap to provide protection of the end cap from at least part of any tension applied to the rope. Preferably, such secondary securing means comprises a sleeve member which secured to the strands of the internal structure of the rope and provides a member against which the end cap member can seat to provide a closed bobbin unit. It is preferred that the sleeve grips the strands frictionally over at least part of its length, for example by being crimped or otherwise formed with a reduced diameter portion which compresses the stands within it. The secondary securing means absorbs at least part of any tension applied to the rope and reduces the stresses applied to the adhesive or cement bond between the strands and the end cap.

Typically, the sleeve is secured to the strands by reducing its internal diameter over at least part of its length. As the strands are extended, their external diameter reduces and the reduced diameter portion is sized to ensure that it radially grips the strands frictionally at the maximum extension of the rope expected during use. Typically, the external diameter of the rope will reduce to about 20 to 45% of its untensioned diameter. The reduced diameter portion of the sleeve therefore preferably has an internal diameter which is from 15 to 40% of the diameter of the rope in its sheathed but otherwise untensioned state. Preferably, the reduced diameter portion of

within the sleeve, this conical member will be drawn with the strands into the flared portion of the sleeve and will exert an additional radial clamping action to trap the strands between the outer face of the conical member and the internal face of the sleeve.

Accordingly, from another aspect, the invention provides an extensible length of material formed from a polymeric material, preferably in the form of a plurality of strands of a natural or synthetic elastic polymeric material, notably one which undergoes strain crystallisation, having means for securing the length of material to an article, said securing means being located at or adjacent a free end of the length of material, characterised in that the securing means comprises an end cap secured to the said polymeric material by adhesive, notably an epoxy resin and the strands are subjected to a treatment with a cyanoacrylate resin.

Preferably, the securing means incorporates a sleeve member adapted to co-operate with the said end cap and to reduce the tension applied to said end cap by said strands, said sleeve member applying a radial compressive force to the said strands whereby the strands are secured within said sleeve by frictional forces.

Preferably, substantially the whole length of the strands of polymeric material are enclosed in a protective sheath or braid which applies radial compression to the said strands whereby the strands are extended between said securing means by from 25 to 150% of their uncompressed and untensioned state.

The elongated material of the invention is of especial use in providing the biassing force in the apparatus of the invention. However, the material can find a wide range of other uses where

in the apparatus of Figure 1; Figure 6 shows the hydraulic and electric controls and interconnections incorporated in the apparatus of Figure 1; Figure 7 is an isometric view of an arrangement for mounting the apparatus of Figure 1 on an excavator chassis; and Figure 8 is a side elevation of an implement for driving piles incorporating the invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS:

In the apparatus of Figure 1 a weight 1 is movable along guideways, shown in greater detail in Figures 3 and 4 described below, which are incorporated in a casing 2, to strike a tool 3 at the foot of its travel. The casing is provided with mounting points for mounting on the arm of an excavator as shown in Figure 7. The weight 1 is moved upwardly by two hydraulic rams 4 which provide the retracting force against the tension in two elastic ropes 5 which provide the biassing force. The upper ends of the piston rods of the rams and of the ropes are connected to the weight by means of a transverse yoke 6 which permits the rams and ropes to be aligned alongside the line of travel of the weight. The weight 1 falls under the influence of gravity and the tension in the rope.. 5 to strike a chisel tool 3 which bears upon rock, concrete or another surface which it is desired to break up or penetrate under the influence of the impact blow delivered by the weight 1 on tool 3. The flow of hydraulic fluid to and from the cylinders of rams 4 is controlled by hydraulic valves and electrical control circuits described in Figure 6. The terminal bobbins 7 by which the elastic ropes 5 are anchored to yoke 6 1 and casing 2 are shown in Figure 5.

The upper end of weight 1 is attached to a transverse yoke 6 to which are attached the rams 4 and the ropes 5 symmetrically located about the longitudinal axis of the weight. As shown in

Figure 3, the up and down travel of weight 1 is guided by means of wheels 30 carried between vertical tracks 31 in the casing 2. The wheels 30 are mounted by means of suitable stub axles extending laterally from the upper and lower portions of the weight so as to prevent twisting of the weight with respect to the tracks 31. As a result, the hydraulic ram (only one is shown in Figures 3 and 4 for clarity) can be mounted off the line of* travel of the weight and apply its lifting force via the yoke 6 which extends laterally from the weight as shown in Figure 1. The elastic ropes 5 can also be located off the line of travel of the weight as shown in Figure 1.

The terminal bobbin units 7 carried by the elastic ropes 5 are secured to anchorage cups or recesses 50 in the casing 2 and yoke 6, as shown in Figure 1 in a tensioned state. As shown in Figure 2, the bobbin unit 7 at the foot of the elastic ropes can be secured by means which allow the tension in the rope 5 to be adjusted. These means comprise, for example, a cup formed by two inter-engaging split collets 20 carried in a recess in a transverse mounting arm 21. The collets can be stepped or axially tapered so that they seat firmly home in the recesses 50 when rope 5 applies axial tension on the bobbin 7. Arm 21 is connected to casing 2 by adjustment bolts 22, whose heads are located in recesses in casing 2 as shown. Tightening bolts 22 draws the arm 21 downwards and increases the tension in rope 5.

Hydraulic fluid is fed to and from rams 4 via pipe 15 and control valve 16 which connects the cylinders of the rams to either high pressure fluid via pipe 17 or to a low pressure dump tank via pipe 18. Rams 4 are of conventional single acting design and operation.

The elastic ropes 5 are composed mainly of natural cis-

of the weight 1 at its normal impact or rest position 8 (shown dotted in Figure 1) on the chisel 3 applies a large impulsive force to chisel 3 which causes the tip of the chisel 3 to penetrate or displace the solid surface a short distance. In this short distance of movement of the chisel 3 the weight 1 i brought to rest. However, in the event that the solid surface provides less resistance than expected or the tip of the chise is not located against the solid surface, the weight would not be brought to rest by the resistance of the solid surface and would over-run its normal extent of travel. Buffers 9 are provided below the normal extent of travel of the weight 1 within the casing 2 which absorb the kinetic energy of the weight and bring it to a stop at a point 10 within the casing in the event of such an over-run condition existing.

A resilient block 11 may be carried by the weight or the casing 2 as shown in Figure 1 to cushion any over-run on the raising of the weight. Alternatively, as shown in Figure 3, the block 11 can be carried off the line of travel of the weight 1 and similarly buffer 9 can act on a side stop arm 12 rather than on the weight itself.

In the present example two rams 4 are shown, symmetrically disposed about the axis of the implement, but it will be understood that the invention is not limited to two rams 4 nor to symmetrical disposition. Thus, as shown in Figure 3, one ram may be used and this can be mounted to act off the' line of travel of the weight and any twisting effect this may have is counteracted by the disposition of the wheels 30 and guide tracks 31. Furthermore, the rams 4 may be connected to the base of weight 1 and contract to raise the weight.

As stated above, the casing is provided with means for mounting the apparatus on an excavator. Thus, as shown in Figure 7, the

casing can have a lateral bracket 70 which is attached to the free end of the dipper arm of the excavator. The casing is thus mounted alongside rather than co-axially upon the dipper arm, allowing the casing to be positioned as required by articulating the dipper arm without the casing impeding the freedom of movement of the dipper arm. The dipper arm will typically comprise two sections 71 and 72 pivotally connected and provided with a ram 73 whereby the dipper arm can be articulated about the pivot connection 74. Section 72 of the dipper arm is connected to bracket 70 by a pivotal connection 75 and with an hydraulic ram 76 whereby the orientation of casing 2 and hence the position and line of action of the chisel tool can be varied.

As shown in Figure 1, magnets 13 and 14 are shown fixed to the yoke 6 carrying the weight 1. The mountings of the magnets preferably incorporate adjustment means, not shown, which enable the magnets to be positioned at different axial positions with respect to the weight 1. A magnetic detector 13a, for example a reed switch or a Hall effect sensor, is mounted alongside the line of travel of weight 1 and detects the upward passage of magnet 13. Detector 13a gives a signal output to the hydraulic fluid control system, for example that shown in Figure 6, to disconnect the feed of hydraulic fluid to the cylinders of the rams 4 when the weight 1 approaches the end of its upward stroke. A second magnetic detector 14a is mounted alongside the line of travel of weight 1 and detects the passage of magnet 14 on the downward travel of the weight 1. Detector 14a generates a signal to connect the cylinders of the rams 4 to the supply of high pressure hydraulic fluid to initiate the lifting stroke of the rams when weight 1 is about to strike the chisel 3. A further magnetic detector 13b can be located at a lower level to detector 13a so as to detect when the weight 1 enters the over-run zone of its travel and to

disconnect the feed of high pressure fluid to the ram cylinders initiated by detector 14. The relative positions of the magnets and detectors can be selected according to the requirements of any given case using simple trial and error.

Preferably, detector 14a also triggers a timing sequence, for example by way of the timer module 27 in the control box 19 in Figure -S, which timing sequence would terminate in disconnection of the hydraulic feed to the rams should the weight 1 not first reach the position to actuate detector 13a.

As shown in Figure 6, the flow of hydraulic fluid to and from the cylinders of the rams is controlled by a valve assembly 16 under the influence of a control box 19. In the valve assembly

16, the pipes 15 from the cylinders of the rams connect with a vented pilot-to-open check valve 60 and with a pilot-to-close check valve 61. Valve 60 regulates the flow of high pressure hydraulic fluid from the pump (not shown) to the rams via pipe

17. Valve 61 is connected via a check valve 62 to the hydraulic fluid dump tank via pipe 18. The feed pipe 17 is connectable to pipe 18 by a vented pressure relief valve 63. The pilot gallery to which the pilot control connections of valves 60, 61 and 63 are made is joinable either to pipe 17 or to pipe 18 by a solenoid-controlled valve 64. A pressure switch 65 which closes on being subjected to hydraulic pressure is connected to pipe 17. A low pressure hydraulic accumulator 66 is connected to the pipe joining valves 61 and 62.

The control box 19 contains an assembly of electronic components as indicated in Figure 6, principally a 555 timer module 67 and a transistor 68.

Referring to Figures 1 and 6, the system operates as follows. When hydraulic fluid under pressure is not being fed through

In the next half cycle when the valves 61 and 63 are closed, the low pressure accumulator 66 is able to discharge its fluid contents through the pipe 18.

Should pressure in the pipe 17 acting in the rams 4 be inadequate to stretch the elastic ropes 5 sufficiently for magnet 13 to reach detector 13a, the timer module 67 will complete its pre-set timing period and de-energize the solenoid in valve 64.

When the weight 1 reaches its point of impact with the chisel 3, the magnet 14 reaches the detector 14a, which triggers the timer module 67. Through transistor 68, this re-energizes the solenoid in valve 64. Valves 61 and 63 close, valve 60 opens, high pressure hydraulic fluid flows to pipe 15 and the rams and the weight 1 is again raised away from the chisel 3.

The above cycle repeats as long as the flow of hydraulic fluid in pipe 17 remains connected, the electrical supply to the control box 19 is maintained and the chisel does not blank strike.

The time delay initiated by detector 14a may be controlled by the operator, for example by means of a variable resistor which controls the reference voltage on pin 5 of the timer device 27. By shortening the time delay the operator can reduce the lift of the weight 1 by the rams 4, so obtaining an increased frequency of blows each at a reduced energy. This facility enables the operator to match the impact blow delivered by the weight to the conditions of the concrete, rock or soil upon which the chisel is acting.

In the case of a weight 1 of mass 65 kg which is to be accelerated to a velocity at impact of 5 m per sec, suitable

it can be constructed to lower standards of precision using less specialized machine tools than a conventional breaker where the driving mass is provided by the piston of the hydraulic ram, which of necessity has to be accurately constructed.

The invention has been described above in terms of ^~ the elastic rope providing the biassing force to return the weight to its rest position. However, it is within the scope of the invention to use the hydraulic ram to drive the weight towards the rest position and to use the elastic rope to return the weight to its raised position. However, this configuration is less preferred since the tension in the elastic ropes will be opposing the action of the hydraulic ram on the impact stroke and will thus reduce the impact force which can be achieved by the ram.