The invention relates to a device for creating a local water flow or water jet in a body of water, in such a way that bed material from the bed below said body of water can be displaced, which device comprises a jet pipe, a screw disposed rotatably in the jet pipe, and means for supplying a countertorque in the opposite direction to the torque exerted on the device through the rotation of the screw.

Such a device is known from EP-A-289520. With this known device it is possible to make a trench in a water bed, in which trench a pipeline, for example, can be laid. For this purpose, the device is moved at some distance above the water bed along the path in which the trench is to be made. The rotating screw in this case supplies the desired water flow.

Since the rotating screw exerts a torque on the device, unless countermeasures were taken, the device would start to rotate uncontrollably about its axis, which is, of course, very undesirable. On account of that, blades are provided in the outlet of the jet pipe, which blades exert a countertorque on the device as a result of the water flow in the jet pipe, in such a way that the device is stabilized as regards such a rotary movement.

A great disadvantage of this device is that the torque generated and the countertorque are the same for a specific outflow rate of the water flow in the jet pipe only within a limited speed of rotation range. On variation of the distance of the device from the bottom, said outflow rate varies, and therefore so does the countertorque.

The torque generated and the countertorque are not easy to keep the same during operation of the device. Rotation of the device therefore has to be prevented by other, additional means.

The object of the invention is therefore to provide a device of the above mentioned type which does not have these disadvantages. That is achieved through accommodating a second screw in the jet pipe, which second screw is rotatable in the opposite direction to the direction of rotation of the first screw, the screw direction of which being opposite and the combination of pitch with its speed of rotation being such that the torque generated is the same or virtually the same as that of the first screw. The pitch angle is preferably opposite to that of the first screw.

The second screw not only provides the desired countertorque, as a result of which the device remains stable, but also contributes to more

efficient functioning of the device as regards the displacement of bed material such as, for example, during the making of a trench in the water bed. This means that no energy is lost during the stabilization of the device. Through a suitable choice of the second screw it can also be ensured that the required countertorque is always supplied, with the result that no further measures need be taken for synchronizing the operation of the screws.

The first screw and the second screw are preferably accommodated coaxially in the jet pipe; in that case one of the screws can be connected to a hollow driving shaft, and the other screw can be connected to a central driving shaft running coaxially through the hollow driving shaft.

Both driving shafts can project from the jet pipe at the inlet end thereof, and can each be connected to a drive unit. At the top end of the jet pipe suspension means can also be provided, for suspension of the device from a bearing element such as a cable, which is in turn connected to a vessel on the water surface.

The device can also be used for covering pipes, levelling the water bed, jet washing articles or moving quantities of soil etc. At the outlet side of the jet pipe the device can have various types of nozzles, which can be a round, oval or rectangular shape.

The means for driving the screws may include a drilling motor.

The drilling motor may be a "Moineau", hydraulic or suitably adapted electric motor. Alternatively and advantageously the drilling motor may comprise a stator and a rotor rotatably mounted in the stator, the stator being provided with a rod recess and an exhaust port, the rotor being provided with a rotor channel and at least one channel for conducting motive fluid from the rotor channel to a chamber between the rotor and the stator, the rod recess being provided with a rod which, in use, forms a seal between the stator and the rotor. Such a drilling motor is described in pending US 08/191.693 (SUSMAN et al) .

Although not essential it is highly desirable that the rotor be provided with a seal for engagement with the stator. Preferably, the seal is made from a material selected from the group consisting of plastics materials, polyethylethylketone, metal, copper alloys and stainless steel.

Advantageously, the rod is made from a material selected from the group

consisting of plastics materials, polyethylethylketone, metal copper alloys and stainless steel.

Preferably, the stator is provided with two rod recesses which are disposed opposite one another and two exhaust ports which are disposed opposite one another, each of the rod recesses being provided with a respective rod, the rotor having two seals which are disposed opposite one another.

The drilling motor may advantageously comprise two drilling motors arranged with their respective rotors connected together each motor comprising a stator and a rotor rotatably mounted in the stator, the stator being provided with a rod recess and an exhaust port, the rotor being provided with a rotor channel and at least one channel for conducting motive fluid from the rotor channel to a chamber between the rotor and the stator. the rod recess being provided with a rod which, in use, forms a seal between the stator and the rotor.

Preferably, the drilling motors are connected in parallel, although they could be connected in series if desired.

Advantageously, the drilling motors are arranged so that, in use, one drilling motor operates out of phase with the other. Thus, in a preferred embodiment each drilling motor has two chambers and the chambers in the first drilling motor are 90° out of phase with the chambers in the second drilling motor. Similarly, in an embodiment in which each drilling motor has four chambers, the chambers in the first drilling motor would preferably be 45° out of phase with the chambers on the second drilling motor. This arrangement helps ensure a smooth power output and inhibits stalling.

The device may provide means for steering the device, in use. Preferably the steering means comprises at least four apertures on the device, the apertures being equally spaced around a plane through the device, which plane is intended to be substantially horizontal in use, openable gates on each of the four apertures, and means for controlling the opening and closing of each gate, each gate preferably providing a portion which portion extends inwardly when the gate is open (so as to direct or scoop - water through the respective aperture) the portion further closing the aperture when the gate is closed.

Preferably the control means comprises an electric or hydraulic actuator for each gate, each actuator being controlled by means of an umbilical extending above surface.

Alternatively, the steering means may comprise one or more openable flaps located on the outlet.

Each screw may include a plurality of blades, the blades of one screw being offset by 180° with respect to the blades of the other screw of the pair.

The screws may be in the form of propellers. For example, the screws may be in the form of propellers provided with water jets on the tips thereof as disclosed in GB 2240568.

The invention will be explained in greater detail below with reference to a number of exemplary embodiments shown in the figures.

Fig la shows a longitudinal cross-sectional view of a drilling motor for use in an embodiment of the present invention.

Fig 2A-2D shows a series of cross-sectional views along line A-A of Fig 1 showing the motor in four different positions. Fig 3A-3D shows a series of cross-sectional views along line B-B of Fig 1 showing the motor in four different positions.

Fig 4 shows a longitudinal cross-sectional view of a first embodiment of an underwater excavation apparatus according to the present invention. Fig 5A-5C shows a series of views of a first propeller for use in the apparatus of Fig 4.

Fig 6A-6C shows a series of views of a second propeller for use in the apparatus of Fig .

Fig 7 shows a schematic side view of the apparatus for Fig connected to a hose reel provided, for example, at the stern of a ship.

Fig 8 shows a longitudinal cross-sectional view of a second embodiment of an underwater excavation apparatus according to the present invention.

Figure 9 shows a third embodiment of the apparatus according to the invention, partially in longitudinal section.

Figure 10 shows an outflow nozzle for the apparatus. Figure 11 shows a first possible application of the apparatus. Figure 12 shows a second possible application of the apparatus. Figure 13 shows an alternative embodiment of Figure 12. Figure l shows a further possible embodiment of the apparatus.

Figure 15 shows a first alternative outflow nozzle. Figure 16 shows a second alternative outflow nozzle. Some embodiments of an underwater excavation apparatus according

to the present invention are disclosed herein. Two embodiments comprise a drilling motor. In order to facilitate understanding of the embodiments of the underwater excavation apparatus disclosed, a detailed description will firstly be given of the drilling motor. Referring to Fig 1 there is shown the drilling motor generally designated 10. The drilling motor 10 comprises a first motor 20 and a second motor 50.

The first motor 20 comprises a stator 21 and a rotor 23. A top portion 22 of the rotor 23 extends through an upper bearing assembly 2 which comprises a thrust bearing 26 and seals 25.

Motive fluid, e.g. water, drilling mud or gas under pressure, flows down through a central sub channel 12 into a central rotor channel

27, and then out through rotor flow channels 28 into action chambers 31 and

32. Following a motor power stroke, the motive fluid flows through exhaust ports 33 in stator 21, and then downwardly through an annular channel circumjacent the stator 21 and flow channels 35 in a lower bearing assembly 34. A portion 3 of the rotor 23 extends through the lower bearing assembly 34 which comprises a thrust bearing 37 and seals 38. The ends of the stator 21 are castellated and the castellations engage in recesses in the respective upper bearing assembly 2 and lower bearing assembly 34 respectively to inhibit rotation of the stator 21. The upper bearing assembly 2k and lower bearing assembly 3 are a tight fit in an outer tubular member Ik and are held against rotation by compression between threaded sleeves 16 and 84.

A splined union 39 joins a splined end of the rotor 23 to a splined end of a rotor 53 of the second motor 50- The second motor 50 has a stator 51-

A top portion 52 of the rotor 53 extends through an upper bearing assembly k . Seals 55 are disposed between the upper bearing assembly 5k and the exterior of the top portion 52 of the rotor 53- The rotor 53 moves on thrust bearings 56 with respect to the upper bearing assembly 5 .

Motive fluid flows into a central rotor channel 57 from the central rotor channel 27 and then out through rotor flow channels 58 into action chambers 61 and 62. Following a motor power stroke, the motive fluid flows through exhaust ports 63 in stator 51 and then downwardly through an annular channel circumjacent the stator 51 and flow channels 65 in a lower bearing assembly 64. A portion 66 of the rotor 53 extends through a lower

bearing assembly 64. The rotor 53 moves on thrust bearings 67 with respect to the lower bearing assembly 64 and seals 68 seal the rotor-bearing assembly interface. Also motive fluid which flowed through the flow channels 35 in the lower bearing assembly 34, flows downwardly through channels 79 in the upper bearing assembly 54, past stator and through flow channels 65 in the lower bearing assembly 64.

The upper bearing assembly 54 and lower bearing assembly 64 are a tight fit in an outer tubular member 18 and are held against rotation by compression between threaded sleeve 84 and a lower threaded sleeve (not shown) .

Figs 2A-2D and 3A-3D depict a typical cycle for the first and second motors 20 and 50 respectively, and show the status of the two motors with respect to each other at various times in the cycle. For example. Fig 2C shows an exhaust period for the first motor 20 while Fig 3C, at that same moment, shows a power period for the second motor 50.

As shown in Fig 2A, motive fluid flowing through the rotor flow channels 28 enters the action chambers 31 and 3 . Due to the geometry of the chambers (as discussed below) and the resultant forces, the motive fluid moves the rotor in a clockwise direction as seen in Fig 2B. The action chamber 31 is sealed at one end by a rolling vane rod 71 which abuts an exterior surface 72 of the rotor 23 and a portion 7 of a rod recess 75•

At the other end of the action chamber 31. a seal on a lobe 77 of the rotor 23 sealingly abuts an interior surface of the stator 21.

As shown in Fig 2B, the rotor 23 has moved to a point near the end of a power period.

As shown in Fig 2C, motive fluid starts exhausting at this point in the motor cycle through the exhaust ports 33-

As shown in Fig 2D, the rolling vane rods 7 and seals 76 have sealed off the action chambers and motive fluids flowing thereinto will rotate the rotor 23 until the seals 76 again move past the exhaust ports

33-

The second motor 50 operates as does the first motor 20; but. as preferred, and as shown in Figs 3A-3D. the two motors are out of phase by 90° so that as one motor is exhausting motive fluid the other is providing power.

The seals 76 are, in one embodiment, made of polyethylethylketone (PEEK). The rolling vane rods 71 are also made from PEEK. The rotors (23, 25) and stators (21, 51) are preferably made from corrosion resistant

materials such as stainless steel.

When a seal 7 in the first motor 20 rotates past an exhaust port 33. the motive fluid that caused the turning exits and flows downward, then through the channels 79. past the exhaust ports 63 and the flow channels 65.

Referring now to Fig 4 there is shown a first embodiment of an underwater excavation apparatus according to the present invention, generally designated 100.

The apparatus 100 comprises a connector body 105 having a frustoconical internally threaded portion 110 for connection to drill pipe, coiled tubing or any pipe capable of transporting motive fluid for driving the drilling motor 10 provided within the apparatus 100. The connector body

105 has a through bore 115 which communicates with the central sub channel

12 of motor 20. Rigidly connected to the connector body 105 is an outer tube 120, such that a portion of the connector body 105 is located with the outer tube 120. Around an outer surface of the portion of the connector body 105 there is rigidly connected a first part of a swivel 125. The swivel 125 comprises first and second parts rotatable with respect to one another. The second part of the swivel 125 is rigidly connected to an upper part 11 of the motor 10 which part is rigidly engaged with the stator 21. The swivel

125 is in this embodiment a known "stuffing box" including combined radial and thrust bearings.

It is, therefore, apparent that the rotors 23. 53 are rotatable with respect to the stators 21, 51 and with respect to the outer tube 120, while the stators 21, 1 are themselves rotatable with respect to the outer tube 120.

The portion 66 of the rotor 53 is rigidly connected to one end of a drive shaft 130 by means of a female spine coupling provided in the drive shaft 130. At the other end of the drive shaft 130 there is provided a first impeller in the form of a first propeller 135-

The stator 51 is rigidly engaged with a second impeller in the form of a second propeller 140 by means of bolts 145 connecting the second propeller l4θ to a flanged portion 1 0 on the end of the outer tubular member 18 of the motor 0.

The first and second propellers 135, 1 0 are connected between one another by a combined thrust and radial bearing 15 •

It is, therefore, apparent that the first propeller 135 rotates

with the rotors 23, 53, while the second propeller 140 rotates with the stators 21, 51-

At the end of the outer tube 120 there is provided a flanged portion 160. Below the flanged portion 160 there is provided a marine bearing 165- Connected to the flanged portion l6θ by means of bolts 169 is a hollow body 170. The hollow body 170 carries at an inlet thereto four inlet guide vanes 175- At an outlet to the body 170 there are provided a plurality of outlet guide vanes 180. The guide vanes 175. 180 are provided so as to produce a predefined flow of water through the hollow body 170, as is known in the art.

Within the inlet of the hollow body 170 there is provided a safety grid 185. Further equidistantly spaced circumferentially around the hollow body 170 are provided a plurality of (in this embodiment 8) longitudinal strengthening strips 186. Circumferentially around the outlet of the hollow body 170 there is provided steering means in the form of four apertures 190 equally spaced on the hollow body 170 in a plane through the apparatus 100, which plane is intended to be substantially horizontal in use. Each aperture 190 carries a gate 195- Each gate 195 provides a portion which portion extends inwardly when the gate 195 is open (so as to direct - or scoop - water through the respective aperture 190) , the portion further closing the aperture 190 when the gate 195 is closed. Each gate 195 is openable and closable by control means in the form of electric or hydraulic actuators 200 connected to the gate 195 by connecting members 205 and carried by a flange 210 provided around the hollow body 170. The actuators 200 are controlled by means of an umbilical (not shown) extending above surface.

Referring now to Figs 5A-5C and 6A-6C, there is shown detailed drawings of the first and second propellers 135, l4θ. As can be seen each propeller 135, 140 carries six blades. The propellers 135, 140 are substantially identical except that their blades are offset with respect to one another by l8θ° so that the propellers 135, 140 rotate in contrary rotating directions.

Referring to Fig 7 there is shown the apparatus 100, to be lowered into the sea, connected to a hose reel 215 provided, for example, at the stern of a ship 220.

In use, the apparatus 100 is lowered to the desired position, for example, just above the seabed as is known in the art. The position of the apparatus 100 may be controlled by the positioning means by suitable

controlled opening/closing of the gates 195 and operation of the propellers 135. 140.

Once in the desired position the apparatus 10 may be operated by pumping motive fluid into the drilling motor 10. The rotors 23, 53 consequently begin to rotate so driving the first propeller 135 in one direction. Further, the second propeller l4θ also begins to rotate by taking up reactive torque of the first propeller 135- The propellers 135, l4θ, therefore, rotate at the same speed in opposite directions.

Referring to Fig 8 there is shown a second embodiment of an underwater excavation apparatus according to the present invention. Parts of this second embodiment are identified by the same integers as the parts of the first embodiment, but suffixed with an "a".

The apparatus shown in Figure 9 comprises a jet pipe which is shown in its entirety by 301, and in which the first screw 302 and the second screw 303 are rotatably accommodated. The first screw 302 is mounted on the hollow shaft 304, while the second screw 303 is mounted on shaft

305. which runs coaxially through the hollow shaft 304. Both shafts 30 and

305 are drivable by means of drive unit 306, which can also contain a reversing device, in such a way that the shafts 304 and 30 . and thus the screws 302 and 303. are drivable in opposite directions of rotation. Since the pitch angle of the screw blades 307 of the first screw 302 is opposite to the pitch angle of the screw blades 308 of the second screw 303. the two screws 302, 303 here create a downward directed flow, running by way of the access grille 309 through the jet pipe 301 and out of the nozzle 310. An outflow nozzle 38 is shown in figure 10.

Flanges 31 can also act as flow guide baffles. Flow guide baffles 34l can be accommodated in the nozzle 310. It is also possible to fit flow guide baffles between screw 302 and 303. in order to reduce undesirable turbulence. Both shafts 304, 305 are accommodated in a casing 311, from which the encasement 313 of the jet pipe 301 is suspended by means of flanges 312. At its top end the casing 311 is connected by means of a rotary bearing to head 314, to which a hoisting cable 31 can be fixed, and from which head 31 one or more electrical and/or hydraulic lines 316 for the drive unit 306 are also guided.

The encasement 313 of the jet pipe 301 is provided on the outside with radial ribs 317, which give the encasement 313 the necessary rigidity. The alternative nozzle 318 shown in Figure 10 is designed so that

it tapers downwards. When such a tapering nozzle 3 8 is used, a higher flow rate of the flow coming out of the jet pipe 301 can be obtained.

Since the first screw 302 rotates in the opposite direction to that of the second screw 303, and the screws 302 and 303 are further identical, with the exception of the pitch angle of their screw blades 307, 308, the resulting torque in operation about the longitudinal axis of the device is equal to zero. Very stable functioning of the device can be obtained in this way, without additional measures being necessary for stabilization. Figure 11 shows a first potential application of the apparatus according to the invention. The apparatus, indicated in its entirety by 319. is supported by means of cable 315 relative to the vessel 320. The distance from the bed 321 of the body of water in which the vessel 320 is situated in this case is selected in such a way that the water flows 322 coming out of the apparatus according to the invention can form a trench 323 in said water bed 321.

In order to keep the apparatus 319 in place during the forward movement of the vessel 320, a stabilizing cable 324 is provided, which cable 3 4 has at its bottom end a ballast weight 326. Said ballast weight 3 6 is moved along with the apparatus in a fixed position relative to the vessel 320 and the water bed, connecting cable 327 between the ballast weight 326 and the apparatus according to the invention ensuring a corresponding position of said apparatus.

Instead of the cables 32 and 3 7 and ballast weight 326, it is also possible to ensure correct positioning of the apparatus by means of a stabilizing cable 325-

In normal circumstances the vessel will make a movement relative to the water bed 321 which coincides with its course. This course changes, however, when there are transverse flows in the body of water. In that case it can happen that the apparatus 319 takes a path over the water bed 321 which forms an angle with the course of the vessel 320. The desired course of the trench 3 3 in the water bed 3 1 can be achieved by adjusting the course of the vessel 320, i.e. directed at an angle to any transverse flow.

In the embodiment in Fig. 12 the apparatus 319 according to the invention is connected to the vessel 320 by means of a single stabilizing cable 38 and the hoisting cable 315• The apparatus 39 in this case is slanted slightly forward and downward, in such a way that the jet 322 is directed not only downward, but also forward. This means that the material

flushed away is displaced better in a desired direction.

It is also possible to suspend the device at an angle in another direction by fixing the cables 31 and 328 in a different place on the vessel 320, for example at both sides. Another variant is that one of the cables 315 or 328 is fixed on another vessel.

Figure 13 shows the situation according to Figure 12, but in this case the device 329 is provided with controllable, transversely directed drive screws, which position the device 329 better. Instead of drive screws, water jets could also be used, possibly disposed in jet pipes.

In the possible embodiment of Figure 14 the apparatus 3 9 according to the invention is suspended from a floating vessel or platform 332 by means of a string of metal pipes 33 - As is customary in the case of drilling installations, the string 331 is suspended in a tower 333. which is equipped for assembling and taking in the string 331- Such an apparatus is very suitable for greater water depths, of several hundred metres.

Figure 15 shows an alternative outflow nozzle, comprising a pipe section 350 to be mounted on the apparatus. The pipe section 3 0 is connected to a support structure consisting of beams 3 1. At the lower end of said support structure, two regulating devices 352 are situated. Each regulating device 352 comprises an arc shaped deflection plate 353 as well as a flat closure plate 354. Plates 353, 354 of each device 352 are mutually connected by means of hinged structures 356, so as to move as a unity each around hinge 357•

Plates 353 are partly situated in the outflow path from pipe section 350, whereby the flow is partly deflected sidewardly and downwardly or upwardly (depending on the position of plates 353). as indicated by the arrows. Thus, the bottom material can be removed in a more efficient way from a trench

Cylinder-piston devices 358 are provided for setting the position of regulating devices 352.

As indicated by dotted lines 359, the regulating devices 352 can be placed in such position that plates 3 are closed, whereby the full flow is directed sidewardly.

Figure 16 shows an outflow nozzle comprising a pipe section 360, which opens out via a single downwardly directed pipe 361, and two opposing, bent pipes 362 which are directed sidewardly and downwardly or

upwardly .

This outflow nozzle offers an outflow in downward as well as in sideward and downward or upward direction.