WO2017158573A1

WO2017158573A1 - A gear system

Info

Publication number: WO2017158573A1
Application number: PCT/IB2017/051576
Authority: WO
Inventors: Omer Abdulkadir BNDEAN; Andrew Donald MACLEOD
Original assignee: Gearpower Group Ltd
Priority date: 2016-03-17
Filing date: 2017-03-17
Publication date: 2017-09-21
Also published as: GB201604630D0

Abstract

A gear system (10) comprises a modular gear assembly (124,125,127) which is housed in a gear assembly housing (114). The gear assembly housing (114) is adapted to be connected to another gear assembly (124,125,127) which drives an output drive shaft (99). The gear assembly (124,125,127) is sealed in the first gear assembly housing (1 14). The input drive (222) is operative to be driven by an output drive (223) of a second gear assembly (124,125,127) so that in use the angular speed (ω1_input) of the input drive (222) is different from the angular speed (ω2_output) of the output drive (223) and one or more stabilisers (63, 67) engage with the containment structure (113) so as to maintain the gear system in position. Gear assembly housings can be connected together so that a high speed or very high speed output is obtained. Ideally the gear assembly comprises a sun and planetary gear assembly.

Description

A GEAR SYSTEM

Field

The present invention relates to a gear system. More particularly, but not exclusively, the present invention relates to a gear system for use in the exploration and extraction of oil and gas.

Background

In many industrial applications, in particular in oil and gas exploration, there is a need to drill at high speeds. This is the case when initially forming a wellbore and within wellbores, for example as part of wellbore completions or extensions. When completing or extending a wellbore cutting and high speed friction welding may be required to be carried out on a well casing. Such specific applications require high speed devices (capable of operating in excess of 500 RPM) or very high speed devices (capable of operating in excess of 5000 RPM) for transmitting torque to tools remote from the surface in a controllable and reliable manner. Gear systems are employed in the process of transmitting power to remote locations.

Prior Art

US Patent US 2 701 123 (Standard Oil Development Company) discloses a gear system used for drilling well bore holes which has an outer casing containing a planet gear frame and a chamber that is in communication with an interior of a pipe string. The gear system engages with walls of a well bore by way of a plurality of pivotal dogs mounted in the gear frame.

US 4 314 615 (Sodder) discloses a self-propelled drilling head which has a base section, including gripper shoes, mounted for extension and retraction to selectively grip the wall of a hole being drilled. An actuator is provided for extending and retracting the gripper shoes. A drilling section is mounted on the base. A second actuator is provided for urging the drilling section downwardly relative to the base section when the gripper shoes are extended. A power transmitting mechanism is operably connected to a drive transmitting torque to rotate a cutter bit.

US Patent US 3 477 314 (Rutkowski) discloses a three speed transmission planetary gear unit for transmitting torque from an input drive to an output drive at one of three different user selectable speeds.

US 2015/00758871 (Halliburton Energy Services Inc) discloses a drill string assembly and a powertrain for a bottom hole assembly (BHA). The BHA includes a housing, a drill bit that is coupled to the housing and a fluid driven motor assembly. The motor assembly includes a differential gear set with a first gear member coupled to a drive shaft. A second gear member intermeshes with the first gear member. A third gear member is coupled to a drill bit. A differential gear set transmits rotational drive from the drive shaft to the drill bit and rotates the drill bit at a speed greater than the drive speed.

The present invention is an improved gear system which provides a wide range of input speed to output speed ratios to an operator.

An aim of the present invention is to provide a gear system which is easily and quickly repaired in the event of a failure or for maintenance.

A further objective of the present invention is to provide a gear system for use in remote and hazardous environments, including down hole locations, where a high speed (in excess of 500 RPM) or very high speed (in excess of 5000 RPM) drive is required in order to perform specific repair or construction operations. Summary of the Invention

According to a first aspect of the invention there is provided a modular gear system which operates in a containment structure comprises: a gear assembly which is housed in a first gear assembly housing, an input drive drives the gear assembly which drives an output drive shaft; the gear assembly is sealed in the first gear assembly housing; the input drive is operative to be driven by an output drive of a second gear assembly, whereby in use the angular speed (u)1 _inpL,t) of the input drive is different from the angular speed (u2_0Utput) of the output drive; and at least one stabiliser is adapted to engage with the containment structure so as to maintain the gear system in position.

Preferably gear assembly housings are connected so that the output axis of the first housing is coaxial with the input of the second gear assembly.

It is appreciated that the invention enables an input rotation to be applied to a plurality of gear assembly housings in a connected manner so that a faster output is obtained at each output stage which increases to a high speed or very high speed suing a plurality of connected gear assembly housings.

The invention can be utilised in many situations where input high torque low speed rotation can be converted to high speed rotation.

Ideally the gear assembly comprises a sun and planetary gear set. Preferably the sun and planetary gear set are retained and operate in conjunction with a gear ring in order to stabilise planetary gear members.

Preferably an engagement means is provided on a first gear assembly housing for engaging with a second gear assembly housing or more preferably a wall of a container or a well bore liner. The engagement means prevents relative rotation of the two gear assembly housings so that when the first and second gear assembly housings are connected, for example when one is stacked atop another, the output drive from the first gear set, in the first gear assembly housing, is coupled to the input drive of the second gear set, in the second gear assembly housing. In the second gear assembly housing the relative angular speeds of the second input drive (u)3i_npirt) and second output drive (u)4_0Utpu,) are different.

The overall variation (reduction or increase) in speed, from the first input drive to the second output drive, when the first gear assembly housing is engaged, in a relatively fixed, non- rotational manner, with the second gear assembly housing, is therefore ω1 ,η_ρυι/ω4_ου,_ρυ, .

The engagement means that prevents relative rotation of adjacent gear assembly housings is preferably a stabiliser. The stabiliser ensures torque is transmitted from the first output drive to the second input drive. The combined gear assemblies thereby provide a variable output torque which may be altered by including one or more additional gear assembly housings.

Ideally stabilisers are provided on an outer surface of a gear assembly housing. The stabilisers are arranged to engage with a well bore or liner so as to provide stability to the, or each, gear assembly housing. Stabilisers are ideally remotely controllable so that they can be extended to engage with a well bore or liner prior to the gear being deployed; and retracted after use by a remote operator.

Ideally, in addition to the planetary gears is a ring gear, single, double or multiple planet gear set linked to a central sun gear. The gear sets are preferably housed between a lower and upper carrier plate and a non-rotational stabiliser is provided so that the gear system is able to operate in any angle of inclination. Preferably an isolation bearing seal separates rotation of planetary gear sets within the gear assembly housing from non-rotational items outside the gear assembly housing.

In one preferred embodiment of the invention a circulation chamber is provided and an output shaft is hollow and in fluid communication with the circulation chamber. An advantage of this feature is that coolant or mud may be delivered to a tool, such as a drill bit, for purposes of cooling and/or lubrication as well as removal of debris and drill cuttings.

Optionally tools are connected to an output drive or shaft by way of a male/female tool joint with a right or left hand thread connections.

Preferably the upper circulation chamber connected to the planetary housing can rotate freely on the planetary gear set isolation sealed bearing.

According to another aspect of the invention a system has a casing with an internally threaded surface and a moveable extender has a threaded surface which engages with the internally threaded surface of the casing, an actuator causes relative rotation of the casing with respect to the moveable extender thereby extending/retracting the moveable extender.

Ideally the casing has first and second groups of inter-digitated engaging portions arranged to move axially, one group with respect to another.

Preferably movement of the casing causes a fishing tool to close as the casing slides over sprung fingers thereby grabbing an item to be fished.

The internal section of the casing contains a central hollow or solid shaft which has the same outside diameter along the stage. The shaft is independent for each stage and is directly connected to the sun gear of a planetary gearing section.

The input drive may be a rotatable body and/or may be a rotatable portion of the gear assembly housing.

The output drive may be a rotatable body. The output drive may be or may comprise a shaft. The output drive may be operative to drive the output drive of another gear assembly.

In some embodiments, all of, or a portion of the gear assembly housing may be fixed with respect to, and rotate with, the input drive. The gear assembly housing may comprise the input drive.

The gear assembly may be a planetary gear set which may comprise a ring gear, a sun gear and a plurality of planet gears. The ring gear may be connected to and/or may rotate with the input drive. The sun gear may be connected to and/or may rotate with the output drive.

The planetary gear set ideally comprises one or more outer planet gears and one or more inner planet gears, each outer planet gear meshes with the ring gear and an inner planet gear.

In some embodiments, all of, or a portion of the gear assembly housing may be able to rotate with respect to the input drive and with respect to the output drive. This portion of the gear assembly may be isolated from the input drive and/or from the output drive by space or by one or more sealed bearings.

This portion of the gear assembly housing may support and/or may be connected to one of, a plurality of, or all of the one or more stabilisers. When the stabilisers engage with containment structure this portion of the gear assembly housing may be maintained in positon, and/or may be prevented from rotating with respect to the containment structure. The gear assembly housing may comprise a first portion which is fixed to, rotates with, and/or comprises the input drive, and a second portion which is rotatable with respect to the first portion, with respect to the input drive and with respect to the output drive. Bearings may separate the second portion from the output drive, the input drive and/or the first portion of the gear assembly housing. The second portion of the gear assembly housing may support and/or may be connected to one of, a plurality of, or all of the one or more stabilisers. The first potion may be an upper portion and the second portion may be a lower portion.

The containment structure may be a wellbore casing, may be a tube, may be the openhole portion of a wellbore, or may be the boundaries of any other cavity into which the modular gear system may be inserted.

The stabilisers preferably comprise arms which may extend from the modular gear system, from the gear assembly housing and/or may extend from a second or lower portion of the gear assembly as described above. The stabilisers may be extendable and/or retractable into and/or out of the gear assembly housing or contact with the containment structure. The stabilisers ideally comprise stabiliser pads which provide additional grip between the stabilisers and the containment structure. The gear system, the gear assembly housing, and/or a second portion of the gear assembly housing as described above, may comprise a jacking system for extending or retracting the stabilisers.

The input drive optionally comprises an engagement means. The engagement means may be operative to connect the other objects, such as rotating objects for driving the modular gearing system. The engagement means may be operative to connect the input drive to the output drive of a second gear system, and or to the output drive of a second gear system according to the invention.

The output drive may comprise an engagement means which may be operative to connect the output drive to other objects, such as a drill bit, or a milling tool. The engagement means may be operative to connected the output drive to the input drive of a second gear assembly and/or to the input another gearing system, and/or to the input drive of another gear system according to the invention.

In a preferred embodiment the modular gear system may comprise an outer housing which may be rotatable with respect to the input drive and the output drive. The outer housing may be may be connected to a second portion of the gear assembly housing as described above. The outer housing may be tubular and may entirely or partially enclose all of, or a portion of the modular gear system. Bearings, gaps and/or seals may be located between the outer housing and the input drive, the output drive and/or a first portion of the gear assembly housing as described above. In some embodiments, a single outer housing may enclose and/or be connected to a plurality of interconnected modular gear systems according to the invention.

Preferred embodiments of the invention will now be described with reference to the Figures in which:

Brief Description of the Drawings

Figure 1 is an isometric view of one embodiment of a gear system showing internal detail;

Figure 2 is an isometric view of two stacked gear systems within a vertical containment structure, such as a well bore casing;

Figure 3 is a vertical elevation showing three stacked gear systems with stabilisers extended in a vertical containment structure;

Figure 4 is a part sectional view of Figure 3; Figure 5 is an outer sectional view showing four gear systems;

Figure 6 is an isometric view of a single gear system and shows a hollow shaft with a circulation bore;

Figure 7 is an isometric view of a single gear system and shows three transmission shafts at right angles to a main axis of the gear system;

Figure 8 is an overall schematic of a fishing well construction casing for an upstream fishing operation;

Figure 9 is a diagrammatic view of an example of a drill string or pipe assembly with two single gear systems;

Figure 10 is an isometric view of a single gear system with electrical generators and a pump;

Figure 1 1 is an isometric view of the gear system in Figure 10 and shows adjustable non- rotatable stabilisers;

Figure 12 is a vertical schematic of an example of a combination fishing and milling tool without its outer tool protection housing;

Figure 13 is an isometric view of the tool in Figure 12 and shows internal components;

Figure 14 is an isometric view of the tool in Figure 12 and shows the internal components from an alternative angle;

Figure 15 is an isometric view of a bottom part of a fishing locking mechanism;

Figure 16 is an isometric view of the fishing locking mechanism in Figure 15 and shows in detail a milling structure;

Figure 17 is an isometric view of a combination fishing and milling tool and shows the fishing locking mechanism.

Figure 18 is an isometric view from above of the fishing locking mechanism shown in Figures 16 and 17;

Figure 19 is an isometric view of the mechanical fishing locking mechanism including the items indicated in Figures 17 and 18;

Figure 20 is an overall schematic view of a drill collar including a drill pipe and a fishing neck engagement profile;

Figure 21 is an isometric view of Figure 20 from above;

Figure 22 is an isometric view of an example of a drill pipe tool joint;

Figure 23 is an isometric view displaying a locked finger mechanism over the drill pipe tool joint shown in Figure 22;

Figure 24 is an isometric view of a drill collar;

Figure 25 is a sectional isometric view of the drill collar, depicting its use in fishing, and shows a male pin end connection; Figure 26 is a sectional schematic and depicts a casing cutting and window milling operation in a typical upstream oil and gas well construction;

Figure 27 is an isometric, view, showing internal detail, of a casing cutting and window milling assembly without its tool outer protection housing in a well bore casing:

Figure 28 is an isometric view of Figure 27 but from a different angle.

Figure 29 is an isometric view of the casing cutting and window milling assembly and shows internal detail;

Figure 30 is a schematic showing a casing section milling operation in a typical upstream oil and gas well construction;

Figure 31 is an isometric view of an example of a casing section milling assembly;

Figure 32 is a longitudinal cross sectional, isometric view of the casing section milling assembly shown in Figure 31 ;

Figure 33 is a schematic depicting friction welding in a typical example of an upstream oil and gas well construction casing;

Figure 34 is a longitudinal sectional view of a multi stage friction welding tool assembly inside a containment structure;

Figure 35 is an isometric view of an example of a single stage friction welding assembly;

Figure 36 is an isometric overall view of a vertical or horizontal dual water turbine unit;

Figure 37 is a plan view of three dual water turbine units, of the type shown in Figure 36, connected together for larger current flowing systems;

Figure 38 is an overall diagrammatical plan view of a water current power generation system; Figure 39 is a schematic side elevation of Figure 38;

Figure 40 is an isometric view of the water current power generation system shown in Figures 38 and 39 where the water current power generation system is deployed as a water pumping system;

Figure 41 is a schematic side elevation of a wind generation system which includes the gear system shown in Figure 1 ;

Figure 42 is a schematic side elevation of a vertical wind powered water and a pump well accessing water from a subsurface aquifer or reservoir;

Figure 43A is schematic side elevation view of a ship, boat or yacht with a marine engine which includes the system shown in Figure 1 ;

Figure 43B is a schematic side elevation view of a ship, boat or yacht with a wind powered drive connected via the system shown in Figure 1 , to a propeller;

Figure 44 is a vertical isometric view of a screw driver or drill includes the system shown in Figure 1 ;

Figure 45 is a vertical isometric view of a hand powered drill includes the system shown in Figure 1 ; Figure 46 is a horizontal isometric view of an industrial power mixing system includes the system shown in Figure 1 ;

Figure 47 is a horizontal isometric view of a rotary handled power drill includes the system shown in Figure 1 ;

Figure 48 is a schematic of a well bore oil production pumping well for pumping heavy oil and comprising perforated sections and pumping units which include the system shown in Figure 1 ;

Figure 49 is an isometric view of a lower stage of the oil production pumping system shown in Figure 48;

Figures 50A and 50B show isometric views of an electrical double or single flush mounted socket profile drill, for cutting square or rectangular shaped profiles;

Figure 51 is an isometric view of a domestic or industrial air or liquid vacuum appliance which includes the gear system shown in Figure 1 ; and

Figure 52 is an overall block diagram for a stabilised gearing energy system with a programmable control system.

Detailed Description of Preferred Embodiments of the Invention

Figure 1 is an isometric partially cut away view of an embodiment of a single stage gear system comprising an upper assembly 114, a lower assembly 115, and a shaft 99. A tool connector 86 is located at the lower end of the single stage gear system (in some embodiments a tool connector 86 may additionally, or alternatively be located at the upper end of the single stage gear system, as shown in Figure 6).

The single stage gear system also comprises a planetary gear set which is housed within the upper assembly 114 and which connects the upper assembly 114 to the shaft 99, such that when the upper assembly 114 is rotated, the shaft 99 is rotated at a greater angular velocity. The lower assembly 115 comprises a plurality of extending or extendable stabilisers, and may comprise a power system and/or may comprise a control means.

The lower tool connector 86 is a male screw thread connector, and may have either a left or right handed thread. In use the lower tool connector may be used to connect the single stage gear system to a tool or device to be rotated by the single stage gear system, or to another single stage gear system so as to form a multiple stage gear system 111. An upper tool connector 86 may connect the single stage gear system to another device (such as another single stage gear system, or an input rotational power source 8) which rotates the upper tool connector thereby driving the single stage gear system.

An input rotational power source 8 may be connected to the upper end of the single stage gear system and/or to the upper assembly 114, by an upper tool connector 86, or otherwise. The input rotational power source 8 may create clockwise or anti-clockwise rotation, and may be, or may comprise a mechanical, electrical alternating current or direct current motor, hydraulic motor or pneumatic motor or any other source of power rotation.

In use, the single stage gear system (or multiple stage gear system 111 ) may be arranged inside a containment structure 113 (as shown in Figures 2 to 7), such that the containment structure 113 surrounds the gear system. The containment structure provides a surface against which the stabiliser pads 63 of the stabilisers may be extended so as to fix the gear system in place and prevent rotation of the lower assembly 115. The lower assembly 115 comprises three or more stabiliser arms, which in use may extend or be extended from the lower assembly 115 such that their stabiliser pads 63 abut, and exert a force upon the inner surface of the containment structure 113, thereby stabilising the lower assembly and preventing it from rotating with respect to the containment structure 113.

The upper assembly 114 and the lower assembly 115 are separated by an assembly isolating bearing 121 which allows the upper assembly 114 to rotate freely with respect to the lower assembly 115.

The containment structure 113 may be a casing, pipe or tubing; and may be made of any material with sufficient strength to resist the extension force of the stabiliser arms, thereby providing purchase for the stabiliser pads 63, for example steel, stainless steel, concrete, plastic, or wood.

The single stage gear system has a low-speed end 222 and a high-speed end 223. The low- speed 222 end is comprised by the upper assembly 114 (and optionally by an upper tool connector 86). In use this low speed end may be connected to a device which drives the rotation of the single stage gear system (for example, an input rotational power source 8, or the high-speed end 223, or lower tool connector 86 of another single stage gear system). In use the single stage gear system is typically arranged such that the low speed end 222 is at the top of the single stage gear system, above the high-speed end 223. In other embodiments the high speed end 223 may be driven and/or rotated, so as to rotate the low-speed end 222, for example the input rotational power source 8 may be connected to and may drive the high speed end 223.

The high-speed end 223 is comprised by the shaft 99 (and optionally by a tool connector 86 connected thereto). In use the high-speed end 223 is connected to a device to be rotated by the single stage gear system (for example a tool, or the low-speed 222 and/or upper tool connector 86 of another single stage gear system). In use the single stage gear system is typically arranged such that the high-speed end 223 is at the bottom of the single stage gear system, below the low-speed end 222.

The upper assembly 114 comprises a circulation chamber housing 57, a circulation chamber 109 defined by the circulation chamber housing 57, and a planetary gear mechanism housing 96. The circulation chamber 109 and the circulation chamber housing 57 are arranged above the planetary gear mechanism, at the low speed end 222 of the single stage gear system, and may be connected to an upper tool connector 86 (as shown in figure 6). The circulation chamber 109 and the circulation chamber housing 57 are both substantially cylindrical. The planetary gear mechanism housing 96 comprises a substantially cylindrical portion with a greater radius than that of the circulation chamber housing 57. In the illustrated embodiment, the circulation chamber housing 57 and the cylindrical portion of the planetary gear mechanism housing 109 are connected by a conical frustum shaped portion of the planetary gear mechanism housing 109, although they may be connected by other means. The planetary gear mechanism housing 96 has an open lower end and surrounds a planetary gear set which is comprised by the single stage gear system and which transmits rotation from the upper assembly 114 to the shaft 99.

The lower assembly 115 comprises the stabilisers, a stabiliser base plate 122, a planetary gear set lower carrier plate 200 and a stabiliser housing 72. The stabiliser base plate 122 and the planetary gear lower carrier plate 200 are both circular and are connected to the stabiliser housing 72. The stabiliser housing 72 is a cylindrical casing which extends between the stabiliser base plate and the upper assembly 114 (the lower portion of the stabiliser housing 72 is shown entirely cut away in Figures 1 , 2, 3, 6, 7, 9, 13, 14, 27, 28, 29, 31 , 32, 34, and 35 so as to allow the internal components of the stabiliser housing may be seen, a full exterior view of the stabiliser housing 72 may be seen in Figure 12, and partially cut away views of the full length of the stabiliser housing 72 wall may be seen in Figures 10 and 1 1 ). The assembly isolating bearing 121 is arranged between the upper assembly 114 and the lower assembly 115, between the planetary gear mechanism housing 96 and the stabiliser housing 72. The assembly isolating bearing 121 therefore allows the upper assembly 114 to rotate with respect to the lower assembly 115.

When the stabilisers are extended from the lower assembly 115 - such that the stabiliser pads 63 are forced against the inner surface of the containment structure 113 - and the upper assembly 115 is rotated - for example by rotating the low speed end 222 and/or an upper tool connector 86 - the assembly isolating bearing 121 prevents lower assembly 115 from being forced to rotate with the upper assembly 114 and the lower assembly do not rotate.

A planetary gear set which comprises a ring gear 127, a sun gear 124, and a plurality of inner and outer planet gears 125 is located inside the planetary gear set housing 96. The ring gear 127 fixed to the inner surface of the planetary gear set housing 96, and rotate when the upper assembly 114 is rotated. The rotation of the ring gear 127 causes the planet gears 125 and the sun gear 124 to rotate. The sun gear 124 rotates with a greater angular velocity than the ring gear 127 and the upper assembly 114.

When the three or more stabilisers are not extended, they are housed within the stabiliser bladed sealed inner housing 72. When the upper assembly 127 is rotated while the stabilisers are not extended (or while the stabilisers are extended but the stabiliser pads 63 are not forced against the interior of a containment structure 113) the lower assembly 115 also rotates, in the same direction as the upper assembly 114.

The planetary gear mechanism housing 96 of the upper assembly 114 contains a planetary gear set upper carrier plate 198. The planetary gear set upper carrier plate 198 is isolated from the rotation of the shaft 99 by a shaft bearing 102 and from rotation of the planetary gear mechanism housing by a gap, or optionally by a bearing.

The lower assembly 115 comprises the planetary gear set lower carrier plate 200, the stabiliser base plate 122 and the stabiliser housing 72 into which the stabilisers are retractable. These components are all isolated from rotation of the upper assembly 114 by the assembly isolating bearing 121.

The planetary gear set lower carrier plate 200 and the stabiliser base plate 122, are each isolated from the shaft 99 by shaft bearings 102.

The shaft 99 extends between the circulation chamber 57 and the lower tool connector 86 at the high-speed end, passing through the upper and lower assemblies 114, 115. The shaft 99 is isolated from rotation of the circulation chamber 57, the planetary gear set upper carrier plate 198, and the planetary gear set lower carrier plate 200, and the stabiliser base plate 122 by shaft bearings 102. The shaft 99 is rigidly connected to the sun gear 124 of the planetary gear set, and to the lower tool connector 86. Therefore, when the ring gear 127 is rotated, the shaft 99, lower tool connector 86 and high speed end 223 are rotated.

A circulation bore 105 extends through the length of the single stage gear system. The circulation bore 105 forms a tubular passageway along the central axis of rotation of the single stage gear system. The circulation bore 105 is formed through the centre of any upper tool connector 86, through the centre of the wall of the circulation chamber housing 57 at the low speed end 222, and through the length of the shaft 99, thereby forming a tubular passage from the circulation chamber 109 to the high-speed end 223 and the lower tool connector 86.

The circulation chamber housing 57 - which is connected to the planetary gear mechanism housing 96 - is isolated from the top 66 of the shaft 99 by a shaft bearing 102. This shaft bearing 102 is sealed to prevent fluid escaping from the circulation chamber to the interior of the planetary gear mechanism housing 96 when liquid passes through the circulation bore 105. One or more single stage gear systems as shown in Figure 1 may be connected in series, highspeed end 223 to low-speed end 222, thereby forming a multiple stage gear system 111 as show in Figures 2 to 5. Each individual single stage gear system having its own shaft 99, and each single stage multiplying the output rotational speed of the lower end of the combined system.

In some embodiments, a single stage gear system may have no circulation bore 105, and/or the shaft 99 may be hollow, solid, round or any other shape.

When the shaft 99 is hollow, or has a circulation bore 105 formed therethrough, fluids may be circulated through the shaft in use. This may be used for circulating fluids for flushing debris, such as for the removal of cuttings in upstream oil and gas subsurface fishing, casing cutting, window milling and section milling operations (as shown in Figures 8 to 32). Alternatively, or additionally, the system may be used in the subsurface oil and gas production industry for circulating steam (as shown in Figure 48).

Fluids may also be circulated through the circulation bore 105 and/or hollow shaft 99 for cooling purposes. Examples of areas where cooling would be beneficial are welding, grinding and milling, mixing or any application with high speed rotation. The use of cooling will be further explained with reference to Figures 43A and 43B.

When the shaft 99 is solid, it may be used as a rotational support shaft for external tool accessories as explained in Figure 44, Figure 45, Figure 46, Figure 47 and Figure 50.

Obtaining variable output rotation speeds requires the lower assembly 115 to not rotate. This is achieved by extending the three or more stabilisers, such that the stabiliser pads 63 abut the inner surface of the containment structure 113 and exert sufficient force to prevent the lower assembly 115 from rotating.

A stabiliser jacking mechanism 67 may be used to extend the stabilisers from their retracted position. The stabiliser jacking mechanism may optionally comprise a spring retainer. The optional spring retainer of the stabiliser jacking mechanism 67 is not indicated and can be used as a back-up mechanism to return the blades to the closed position in the event of a failure of the jacking power system. The use of a jacking mechanism 67 allows the stabiliser arms to have a variable length dependent on the size of the containment structure 113 and the application of the gear system.

In other embodiments, suitable for other applications, the stabiliser arms may have a fixed arm length without a jacking mechanism 67 if suitable (as shown in Figures 35 to 49).

The shape, and/or design of the stabiliser pads 63 of the three or more stabilisers may be dependent upon the application for which the gear system is to be used, and/or upon the containment structure 113. For example, the stabiliser pads 63 may be designed to match the curvature of the internal diameter of the containment structure 113.

In Figures 1 to 13, and 27 to 35, the three or more stabiliser pad blades 63 have a grooved profile, however any suitable shaped profile may be used.

The stabiliser 63 arms may be have length. In some embodiments, designed for applications where downward movement of the gear system is not required, the stabiliser arms may be orientated downwards, with ends of the arms connected to the stabiliser pads 63 lower than the ends connected to the remainder of the lower assembly 115. In such a configuration the weight of the gear system may result in extra force being exerted against the inner surface of the containment structure 113.

The three or more stabilisers each comprise a pair of stabiliser pads 63 and a stabiliser wheel 62. The stabiliser wheel 62 is located at the end of the stabiliser arm between the pair of stabiliser pads 63. The stabiliser wheel 62 may have be solid, may be soft, may have any texture and/or may be made of any material. In some embodiments the stabiliser may not comprise a stabiliser wheel 62, for example, the power ratchet screw driver or drill 255 shown in Figure 44, or hand powered drill 261 shown in Figure 45.

The lower assembly 115 may comprise a power system which may provide power to operate the stabiliser jacking mechanism 67. The power system 129 may be hydraulic, electrical, and/or pneumatic; may be supported by, and/or affixed to the stabiliser base plate 122; and/or may be contained within the stabiliser housing 72.

One or more of the stabiliser may comprise a stabiliser antennae 68 for wireless data communications.

The gear system may be used in vertical inclinations, horizontal inclinations, or in any other inclination. It should be understood that references to top, bottom, upper and lower throughout the detailed description are with reference to a gear system in a vertical inclination with the low- speed end 222 at the top of the gear system, and the high-speed end 223 at the bottom of the gear system, but are not intended to preclude the possibility of the gear system being reoriented or utilised in any other orientation.

The planetary gear set lower carrier plate 200 and the stabiliser housing 72 are isolated from the upper assembly 114 by the assembly isolating bearing 121 , and from the shaft 99 by a shaft bearing 102. The assembly isolating bearing 121 and the shaft bearing 102 may be in a vertical plane, a horizontal plane, or in any other plane.

When the three or more stabilisers are extended, such that their pads 63 are forced against the inner surface of the containment structure 113, clockwise rotation of the upper assembly 114 rotates the ring gear 127 in a clockwise direction. This causes the outer planetary gears 125 to rotate in a clockwise direction, the inner planetary gears 125 to rotate in an anti-clockwise direction and the sun gear 124 and the shaft 99 to rotate in a clockwise direction with a greater angular velocity than that of the ring gear 127.

The outer planet gears 125 are supported on outer planet gear shafts 194 and the inner planet gears are supported on inner planet gear shafts 197. The inner and outer planet gear shafts 197, 194 are isolated from the planetary gear set upper carrier plate 198 and the planetary gear set lower carrier plate 200 by planet gear shaft bearings 227.

The planetary gear set is arranged such that one rotation of the ring gear 127 rotates the sun gear 124 and the shaft 99 significantly more than one rotation. The sun gear 124 is weld connected, or otherwise fixed to the shaft 99. Therefore, rotation at various angular velocities of the upper assembly 114 at the low-speed end 222 produces rotations at various greater angular velocities of the shaft 99 at the high-speed end 223. The shaft 99 is therefore rotated by the sun gear 124, as it is isolated from other components of the upper and lower assemblies 114, 115 by shaft bearings 102.

A cross section of the planetary gear set is shown in detail in Figure 1 1. An even number of planet gears 125 in a gear train between the ring gear 127 and the sun gear 124 converts clockwise rotation of the ring gear 127 to clockwise rotation of the sun gear 124 and the shaft 99, and converts anti-clockwise rotation of the ring gear 127 to anti-clockwise rotation of the sun gear 124 and the shaft 99.

A single planet gear 125, or a gear train with an odd number of planet gears 125 between the ring gear 127 and the sun gear 125 converts clockwise rotation of the ring gear 127 to anticlockwise rotation of the sun gear 124 and the shaft 99 and converts anti-clockwise rotation of the ring gear 127 to clockwise rotation of the sun gear 124 and the shaft 99. Multiple single stage gear systems may be combined in series, thereby forming a multiple stage gear system 111 and may be used for certain applications. In some embodiments, a single stage gear system or a multiple stage gear system may be configured to reverse the direction of rotation between the upper most low-speed end 222 and the lower most high-speed end 223, or to have the same direction of rotation, depending on whether the desired output rotation at the base of the gear system is clockwise or anti-clockwise.

In some embodiments, a single stage gear system as described above, or a tool comprising a single stage gear system as described above may comprise an outer housing 84 (as shown in Figures 13 and 14). The outer housing 84 may be substantially cylindrical and may surround or enclose all or part of the upper assembly 114, the lower assembly 115, and/or a tool connected to the high-speed end 223 of the gear system. The outer housing 84 may be welded, or otherwise rigidly connected to the stabiliser housing 72. An outer housing bearing 138 may separate the outer housing 84 from the circulation chamber housing 57 of the upper assembly 114. If the outer housing 84 surrounds the lower assembly 115, it may have apertures through which the stabilisers may be extended. The outer housing 84 may be an outer tool housing.

Figures 13 and 14 show views of a tool comprising a single stage gear system with an upper tool connection 86 at its low-speed end 222 and a fishing and milling assembly 116 attached to its high-speed end 223. A cylindrical outer housing 84 surrounds the tool between the circulation chamber housing 57 and the lower end of the fishing and milling assembly 116. The outer housing 84 is open at its lower end - so as to allow access to the fishing and milling assembly 116 - and surrounds the circulation chamber housing 57 at its upper end. A sealed outer housing bearing 138 is located between the outer housing 84 and the circulation chamber housing 57, and the outer housing 84 is fixed to the stabiliser housing 72, such that the outer housing 84 rotates with the lower assembly 115 and not the upper assembly 114.

The internal diameter of the outer housing 84 is required to be greater than the diameter of exterior of the planetary gear mechanism housing 96. The outer housing bearing 138 separates the rotation of the planetary gear mechanism housing 96 from that of the outer housing 84.

The components comprising the gear system, and its constituent parts such as the upper and lower assemblies 114, 115 may be manufactured using materials suitable for the application and environmental conditions for which the gear system is intended; and to strengths that are selected as suitable for the application and the environmental conditions for which the gear system is intended.

Figure 2 is an isometric view of a multiple stage gear system 111 comprising two single stage gear systems connected in series. The multiple stage gear system 111 is contained within a tubular vertical containment structure 113 which is shown partially cut away.

The lower assembly 115 comprises a hydraulic, electrical and pneumatic power system 129 which is attached to the stabiliser base plate 122 and components of which are located above and below the stabiliser base plate 122. The power system 129 powers the stabiliser jacking mechanism 67.

In alternative embodiments of single and multiple stage gear systems, the stabilisers may be permanently extended and un retractable, the stabiliser arms may have a fixed length and the arms and/or the stabiliser pads 63 fixed to the interior of the containment structure 113 (for example they may be screwed into or welded to the containment structure 113); or may pass through or interlock with the containment structure 113.

The angular velocity of a rotating high-speed end 223 of a single stage gear system driven by a source of rotation at the low-speed end 222 of the single stage gear system may be increased by inserting one or more additional single stage gear systems between the source of rotation and the low speed end 222 so as to form a multiple stage gear system 111. This significantly increases the angular velocity of the high-speed end 223 of the lower most single stage gear system relative to the angular velocity of the source of rotation and the low-speed end of the uppermost single stage gear system. Note that the shafts 99 of each single stage of the multiple stage gear system 111 are not directly connected to each other, instead rotation is transmitted via the upper assemblies 114 and the planetary gear sets which separate the shafts 99.

The connections between the single stage gear systems is made between the high-speed end 223 of an upper single stage gear system and the low-speed end 222 of a lower single stage gear system. The single stage gear systems are connected by an upper tool connector or engagement means 86 and a lower tool connector or engagement means 86. The tool joint connections 86 may have either a right handed or left-handed thread.

As indicated if a single stage gear system comprises a single, or any odd number of planet gears 125 in the individual gear trains connecting the ring gear 127 to the sun gear 124 and multiple such single stage gear systems are connected in series, clockwise rotation of the low- speed end 222 of the first single stage gear system results in anti-clockwise rotation of the shaft 99 of the first gear system and of the low-speed end 222 of the second single stage gear system, thereby resulting in clockwise rotation of the shaft 99 at the high speed end 223 of the second single stage gear system. In this case the tool connection 68 at the connection 123 between the first and second stage may require being a left handed thread, right handed thread or any other type of connection. The tool connection 68 may be a male connector, or a female connector.

Figure 3 shows a multiple stage gear system 111 for the creation of variable high speed rotation comprising a plurality of single stage gear systems connected in series and housed within an outer housing 84. The multiple stage gear system 111 is located within a vertical containment structure 113 which is partially cut away in the Figure.

The illustrated vertical containment structure 113 has a constant internal diameter, but in some embodiments, the internal diameter of the containment structure may vary, for example the containment structure may be tapered from its upper end to its lower end. The dimensions of the single stage gear systems may also be varied according to the required application of the embodiment.

Although the multiple stage gear system 111 is shown in a vertical orientation, it may be arranged horizontally or at any other inclination required for the application of the embodiment.

The outer housing 84 may be separated from each single stage gear system's circulation chamber housing 57 by a sealed outer housing bearing 138 and may be connected by welding or otherwise to the stabiliser housing 72 of each single stage gear system.

The assembly isolating bearing 121 of a single stage gear system prevents the stabiliser housing 72 being forced to rotate when the upper assembly 114 rotated if the three or more stabilisers are extended such that their stabiliser pads 63 press against the inner surface of the containment structure 113.

The input rotation of each single stage gear system (the rotation of the low-speed end 222 of the gear system) is greater for each subsequent stage from the source of rotation. One rotation of the low-speed end 222 of the uppermost single stage gear system causes many rotations of the shaft 99 at the high speed end 223 of the lowermost single stage gear system.

Figure 4 is a sectional view of the multiple stage gear system 111 shown in Figure 3.

The top 66 of the shaft 99 is isolated from the upper assembly 114 by a sealed shaft bearing 102 located inside the circulation chamber 109. The shaft 99 is directly connected to the internal diameter of the sun gear 124 such that when the sun gear is rotated by rotation of the upper assembly 114, the shaft 99 rotates and this allows the speed of rotation of each subsequent single stage gear system to be increased.

The top 66 of the illustrated shaft 99 comprises a lip which extends radially from the top of the shaft 99 over the top of the shaft bearing 102.

In the embodiment shown in Figure 4, the stabilisers may be extended utilising the stabiliser jacking mechanism 67 such that the stabiliser pads 63 and the stabiliser wheel 62 are located against the inside surface of the containment structure 113.

The planetary gear set ring gear 127 is attached to or formed on the inside surface of the planetary gear mechanism housing and extends between the upper planetary gear set carrier plate 198 and lower planetary gear set carrier plate 200.

The connection 123 may be made using either right handed or left handed threaded tool connectors 86 depending on the embodiment and the intended application of the system. For example, if a single stage gear system comprises a single or any odd number of planet gears 125 in the gear trains connecting the ring gear 127 and the sun gear 124 and multiple such single stage gear systems are connected in series, clockwise rotation of the low-speed end 222 of the first (uppermost) single stage gear system results in anti-clockwise rotation of the shaft 99 as the high-speed end 223. This anti-clockwise rotation is applied to the low-speed end 222 of the second single stage gear system resulting in clockwise rotation of the shaft 99 of the second single stage gear system. In such an embodiment the connection 123 between the first and second stage would be required to be made by left handed threaded tool connectors 86.

Figure 5 is a side view of a multiple stage stabilised gear system 111 comprising four single stage gear systems connected in series and located within a vertical containment structure 113 which has been cut away in the Figure except in the portions where the stabilisers are extended. The optional outer housing 84 is not included in this embodiment.

Any number of single stage gear systems may be connected in series so as to define a multiple stage gear system 111. The stages may be located within a containment structure 113 and each single stage gear system may be connected by male or female tool joint connections 86. Such an arrangement allows an input variable rotation speed at the low-speed end 222 of the uppermost single stage gear system to be increased to a higher variable rotation speed at the high-speed end 223 of the lowermost single stage gear system.

The containment structure 113 may be vertical, horizontal or at any other angle or inclination.

The position of the hydraulic, electrical and pneumatic power system 129 is displayed and will be further described with reference to Figure 6.

Figure 6 is an isometric view of a single stage gear system located in a containment structure 113 with its stabilisers extended by the stabiliser jacking mechanism 67. The containment structure 113 is show partially cut away, except in the portion where the stabilisers are extended. The optional outer housing 84 is not been included in this embodiment.

The upper assembly 114 comprises an upper male or female tool connector 86 connected to the circulation chamber housing 57. When the upper tool connector 86 is rotated so is the entire upper assembly including the circulation chamber housing 57, the planetary gear mechanism housing 96, and the ring gear 127. The lower assembly 115 is isolated from this rotation by the assembly isolating bearing 121.

Components of the hydraulic, electrical and pneumatic power system 129 are positioned above and below the stabiliser base plate 122 comprised by the lower assembly 115. The power system 129 provides power to operate the stabiliser jacking mechanism 67. In some embodiments there is no power system 129 and the stabilisers have fixed arm lengths which are not extendable, the stabilisers may for example, be welded onto, screwed into, or otherwise connected to the containment structure 113.

The shaft 99 is isolated from the stabiliser base plate 122 by a sealed shaft bearing 102. In some embodiments, the circulation bore 105 may pass through the upper and lower tool connectors 86 thereby forming a complete passage connecting the two ends of the single stage gear system. The circulation bore may also run along the centre of the shaft 99.

Figure 7 is an isometric view of a single stage gear system without the optional outer housing 84 and comprising three rotation transmitting shafts 126 which extend at right angles to the axis of shaft 99 and exit the a containment structure 113. The Figure shows the containment structure as partially cut away.

The outer planet gear shafts 194 are connected to gearing mechanisms 196 which are located below the stabiliser base plate 122. The gearing mechanisms 196 convert rotation about the axes of the outer planet gear shafts 194 to rotation about the axes of the transmission shafts 126, and rotates the rotation transmitting shafts 126, thereby transmitting rotation from the upper assembly 114 to the exterior of the containment structure 113. The rotation transmitting shafts 126 may be at right angles to the outer planet gear shafts 194

In the embodiment shown in Figure 7, the single stage gearing mechanism and the containment structure 113 are arranged vertically with the shaft 99, the circulation bore 105, and the outer planetary gear shafts 194 being vertical. The rotation transmitting shafts 126 are all within the horizontal plane at approximately 40 degrees to each other.

This embodiment may be used when a multiple stage gear system 1 1 1 is installed in a containment structure 113 and where different rotational output speeds are required at different lengths along the length of the containment structure 113.

Figure 43 shows an engine powered propeller 189 and a wind powered propeller 189, both of which comprise a multiple stage gear system 111 which may comprise single stages as described in Figure 7. Rotation transmitting shafts may be used to transmit rotation to other devices, such as a bilge pumping system which may require a different rotational speed to the propeller. In this embodiment, the multiple stage gear system may comprise a circulation bore 105 which be utilised for cooling the gear system.

In some embodiments, the single stage gear systems comprise hydraulic, electrical and pneumatic power systems 129 positioned below the stabiliser base plates 122 which provide power to operate the stabiliser jacking mechanisms 67. Some embodiments may not comprise a power system 129 as it may not be required. For example, in embodiments where a fixed stabiliser arm length is used, and/or where the stabiliser arms or stabiliser pads 63 are attached to the internal surface of the containment structure 113, for example, by welding or screwing.

Single stage gear systems, and/or multiple stage gear systems 111 may be used in a plurality of industrial applications.

Figures 8 to 32 show embodiments of gear systems, tools which comprise gear systems for use in the upstream oil and gas industry, and component parts of or for said tools.

Figures 12 to 14 show views of a multi-purpose fishing and milling tool 17. The fishing and milling tool 17 comprises a single stage gear system as described above, this allows components of the tool mechanism to be rotated faster than a source of rotational power which drives the tool (such as a top drive unit or a rotating drill string component). In alternative embodiments the fishing and milling tool 17 may comprise multiple single stage gear systems which may be connected end to end so as to further increase the rotation speed. The single stage gear system comprised by the fishing and milling tool 17 comprises stabilisers which allow the fishing and milling tool 17 to be stabilised within a containment structure 113. The fishing and milling tool 17 may be used for multiple functions and tasks, including, but not limited to fishing and milling, thereby providing a combination fishing milling stabilised drilling tool. In some embodiments, the fishing and milling tool 17 may be automated.

A single stage gear system comprising fishing and milling tool 17 may be combined with additional single stage gear systems so as to allow further increases in the rotational speed of a tool component without increasing the speed of the source of rotational power. Alternative embodiments of fishing and milling tools, and other drilling tools, may comprise multiple stage gear systems so as to produce high speed rotation of tool components.

The use of a single or multiple stage gear system as described above to produce variable high speed rotation of tool components may improve the efficiency of operations such as fishing with milling and washover, casing cutting, window milling and casing section milling operations in the upstream oil and gas industry.

The high-speed rotation produced by the multiple stage gear system 111 in a fishing and milling tool 17 is dependent upon the number of single stage gear systems installed into the tool.

The use of a fishing and milling tool 17 comprising a gear system as described above is expected to improve the time taken by, and thereby the success rate of fishing operations in the upstream oil and gas industry.

The use of a single or multiple stage gear system as described above allows jarring to be performed in both a downwards and an upwards direction when a fishing neck 10 comprised by the fish 117 is engaged by the fishing and milling tool 17. Conventional fishing assemblies are only able to jar in an upwards direction as the method to release the fishing overshot involves bumping downwards on the tool.

The fishing and milling tool 17 allows right hand torque to be applied and the fishing and milling tool 17 to be jarred downwards which is a recognised industry method for freeing stuck pipe if the sticking occurs while pulling out.

The fishing and milling tool 17 may be used in situations where the top hole subsurface formations are too soft to drill and washout easily. These situations may present operational problems, especially in deep water well construction when running the initial conductor pipe, and in other situations where casing jetting and drilling is considered. The fishing and milling tool 17 may be modified for use in these situations. The fishing and milling tool 17 can be modified to be run with a conductor pipe or a casing in order to perform jetting, and/or jetting and drilling to place the conductor pipe or the casing shoe of the casing in a consolidated formation. A combined jetting and drilling operation can be performed using the fishing and milling tool 17.

Figures 27 to 29 show views of a casing cutting and window milling assembly 119 and figures 31 and 32 show views of a casing section milling assembly 118. These assemblies each comprise a single stage gear system as described above. These assemblies may be utilised when an oil or gas well has been abandoned over the reservoir section and a decision has been taken to side-track the well utilising the same well surface casing strings. This can be achieved in one of two ways, dependent on the side-track section length and depth. A window can be milled in the casing, or the casing can be cut above the top of cement, the casing may then be retrieved and the casing section milled in order to provide a sufficient clearance below the preceding casing shoe.

Figures 26 to 32 illustrate the use of the casing cutting and window milling assembly 119 and the casing section milling assembly 118 to perform these operations. The process of milling a window and a section of casing may be time consuming process involving multiple separate runs to achieve the objectives. The casing cutting and window milling assembly 119 may reduce the time taken and the costs involved in casing milling and casing cutting in the upstream oil and gas industry. The use of the single stage gearing mechanism gives the casing cutting and window milling assembly a high speed rotation capability which may increase the milling rate. The increased rotation speed may also allow for lighter assemblies to be run as lower weights may be used for milling. With high speed milling, smaller steel cuttings are expected to be produced allowing for quicker and easier wellbore clean-ups.

Figures 33 to 35 illustrate a use of the single stage gear system to perform single stage friction welding 174 or multiple stage friction welding 175.

Further applications of the single stage gear system are displayed in figures 36 to 51. These applications relate to the renewable power generation industry, the construction industry and the oil and gas production industry. They include a well bore and pipeline oil production pumping system.

Figure 8 is a sectional view of a well construction for a fishing operation 1 in the upstream oil and gas industry. Fishing is the removal of fish from a wellbore, a fish is anything left in a wellbore, and it may be debris, junk metal, a tool or a component for construction of a wellbore. Fish may be retrieved from a wellbore in order to recover valuable equipment, or to remove an obstruction from the wellbore. In the illustrated embodiment the fish 117 comprises drilling components that have been left in the open hole section 21 (the uncased portion) of the wellbore, for example due to a mechanical failure.

The illustrated fish 117 comprises a drill bit 6, a near bit stabiliser 3, drill collars 9 (spiral or flat profile), and a string stabiliser 7. The upper end 11 of the fish 117 has a fishing neck 10. A fishing neck is the point or surface with which a fishing tool engages in order to retrieve a fish, tools and equipment may comprise fishing necks so as to facilitate their retrieval from a wellbore in the event that a fishing operation is required to retrieve them.

The design of the fishing neck 10 may be conventional or may be a new design of fishing neck engagement profile 69 which is further detailed in Figures 20 and 21.

The well construction for the fishing operation 1 comprises a multi-purpose fishing and milling tool 17 as shown in detail in figures 12 to 14, which may be used for both fishing and milling. The fishing and milling tool 17 is capable of fishing for both conventional fishing neck profiles (as shown in Figures 22 to 25), and for the new fishing neck engagement profile 69 shown in Figures 20 and 21 .

The fishing and milling tool 17 is the first oil and gas industry tool which can perform either wash-over, milling, fishing or a combination of these operations during a single trip inside a well bore. The fishing and milling tool 17 comprises a single stage gear system.

The multi-purpose fishing and milling tool 17 may be run down the well bore on drill pipe 43, a heavy weight drill pipe 5 and a fishing bottom hole assembly 19 to above the upper end 11 of the fish 117 in preparation to recover the fish 117.

The multi-purpose fishing and milling tool 17 indicated comprises a single stage gear system. Additional stages may also be used in order to increase the speed of the rotation of the drilling tool 17 with respect to the speed of rotation of the drill pipe 43, heavy-weight drill pipe 5 and the fishing bottom hole assembly 19.

The lower assembly 115 of the single stage gear system comprises three or more stabilisers which may be extended such that their stabiliser pads 63 are pressed against the walls of the open hole section 21. The tool mechanism of the fishing and milling tool 17 driven by the single stage gear system comprises a lower fishing and milling tool shaft 77 and three or more fishing fingers 53.

The single stage gear system comprised by the multi-purpose drilling tool 17 provides variable high speed subsurface rotation with a greater angular velocity than, and dependent upon the angular velocity of the surface input rotational power source 8 which is located at the upper end 45 of the drill pipe 43 on the rig floor 39.

The well construction for the fishing operation 1 comprises a circulation bore 105 which passes through the upper end 45 of drill pipe 45, through the length of the drill pipe 43, through the length of the heavy weight drill pipe 5, through the fishing bottom hole assembly 19, through the single stage gear system comprised by the fishing and milling tool 17, through an internal cavity of a ball housing cylinder 97, through a shaft end ball 101 , through the upper fishing and milling and tool shaft 88, through the fishing and milling tool shaft mechanism 65, through the lower fishing and milling tool shaft 77 and through the jetting nozzle 75 (as shown in Figures 17 and 19).

The well construction for a fishing operation 1 comprises a pump pressure gauge 49 which indicates the pumping pressure through the circulation bore 105. The pump pressure gauge 49 may be either digital or analogue. The pump pressure may be utilised to aid with tool functions which will be explained in more detail when describing the functions of the fishing and milling tool 17. The well construction 1 further comprises a drill string weight indicator 47 which may be used to monitor the up and down weight of the drill string in order to aid the functions of the fishing and milling tool 17.

The well shown in Figure 8 may comprise blowout preventer equipment and a wellhead 37, which may be located on the seabed, on a mobile drilling rig substructure or on the cellar base 41 of a land based drilling rig as shown in Figure 8. The casing of the well may comprise multiple casing intervals including: surface conductor casing 35, surface casing 31 , intermediate casing 27 and production casing 23. The casing intervals may all be cemented in place 33.

Figure 9 shows an example of a drill string - or pipe assembly - which comprises two single stage gear systems as described above. The outer housings 84 comprised by the two single stage gear systems are not shown. The drill string is located within a production casing 23.

In use, the high-speed end 223 of the drill string illustrated in Figure 9 rotates with a greater angular velocity than the low speed end of the drill string. Rotation is transferred from the upper assembly 114 of a first uppermost single stage gear system, to the shaft 99 of the first single stage gear system, to a heavy weight drill pipe 5, to the upper assembly of a second lower single stage gear system, to the shaft 99 of the second single stage gear system, to a drill bit 6. The lower assemblies 115 of the first and second single stage gear systems have stabilisers which are extended against the interior of a production casing 23 within which the dill string is located, thereby stabilising the drill string and fixing its location within the production casing 23.

The heavy weight drill pipe 5 comprises tool connectors 42 at each end which connect to a lower tool connector 86 of the first single stage gear system and an upper tool connector 86 of the second single stage gear system.

Additional single stage gear systems may be used if the application of the drill string and/or the speed or desired speed or rotation of the drill bit 6 requires it. The one or more additional single stage gear system(s) may be connected directly to one of the two single stage gear systems - for example between two tool connectors comprised by the two single stage gear systems - or may be connected by one or more additional intermediate heavy weight drill strings 5, or other drill strings. By increasing t e number of gear system stages, the angular velocity of the rotation of the drill bit 6 may be increased to many times the rotation of the low-speed end 222 of the drill string created by the input rotational power source 8 which may be connected to the top of the upper assembly 114 of the first single stage gear system.

The drill string shown in Figure 9 comprises a fluid path through its length connecting the upper end of the uppermost single stage gear system to the drill bit 6. The fluid path comprising circulation bores 105 through each of the single stage gear systems, through the heavy weight drill pipe 5 and through the drill bit 6. The drilling fluid circulation path is through the circulation bores 105, out through the drill bit 6, and upwards through the annulus between the outside of the drill collars 9 and the inside of the production casing 23 as indicated by the arrows in Figure 9.

The stabilisers comprise stabiliser pads 63 which may be extended against the inner surface of a cavity within which the illustrated drill string and the single stage gear systems are located, such as a containment structure 113 or the open hole section of a wellbore. For example, the inner surface of the production casing 23, the inner surface of a containment structure 113, the inner surface of any other casing, or the inner surface of an open hole section 21.

The single stage gear systems may comprise hydraulic, electrical and pneumatic power systems 129 which are located above and below the stabiliser base plates 122 and which provide power to operate the stabiliser jacking mechanisms 67 comprised by the single stage gear systems. Power systems 129 may or may not be required or comprised by the single stage gear systems, depending on whether or not, or how the stabilisers are extended.

Before the illustrated drill string assembly is returned to the surface, the direction of rotation of the system may be reversed, for example, by reversing the direction of rotation of the input rotational power source. Control systems comprised by the single stage gear system may detect the change in direction of rotation and may retract the stabilisers into the stabiliser housings 72.

The connections of a conventional oil field heavy weight drill pipe 5 and drill collars 9 are right handed threaded connections. Therefore, the planetary gear sets comprised by the single stage gear systems require an even number of planetary gears 125 in each gear train between the ring gear 127 and the sun gear 124, in order to ensure the all the external components of the drill string rotate in the same clockwise direction.

The illustrated drill string comprises two crossover subs 44 (which allow components of different dimensions to be attached to each other). The crossover subs may correspond to the size of the connections of the tool connector 86 of the second single stage gear system, the drill bit 6, and the drill collar 9.

The illustrated system may be used as an alternative to the conventional oil and gas industry drilling mud motors, in order to create high speed rotation of the drill bit 6.

Figure 10 is an isometric partially cut away view of the single stage gear system comprised by the fishing and milling tool 17 shown in Figures 12 to 14 and described above, which shows the lower assembly 115 in detail.

A sealed shaft bearing 102 isolates the rotation of the shaft 99 from the rotation of the outer housing 57 of the circulation chamber 109 of the upper assembly 114.

The upper assembly 114 surrounds the planetary gear set upper carrier plate 198, the rotation of which is isolated from the rotation of the shaft 99 by a sealed shaft bearing 102.

The sealed assembly isolating bearing 121 isolates rotation of the upper assembly 1 14 from rotation of the lower assembly 115 and the stabiliser housing 72. The outer housing 84 of the single stage gear system may be seen more clearly in Figure 13.

The lower assembly 115 comprises a power system 129 which comprises a hydraulic tank, an air tank and a cooling system 128. The power system 129 further comprises three power generating means 131. The power generating means may comprise a hydraulic pump, an electrical alternating current, a direct current generator, and/or an air compressor. These components are used to operate the stabiliser jacking mechanism 67 to extend and retract the stabilisers and the stabiliser pad blades 63.

The outer planet gear shafts 194 are connected to the three power generating systems 131 (as shown in Figure 1 1 ).

The control system 132 of the power system 129 may be connected to the three power generating means 131 by cable conduits 136. The control system 132 may transmit or receive data either wirelessly, or via a wired connection.

The fishing and milling drilling tool 17 comprises one or more electrical, hydraulic or pneumatic motors 154 with a motor gear shaft 133 which connected to the underside of the stabiliser base plate 122 with a motor support arm 130. The motor 154 rotates a motor gear shaft 133 which rotates a gear 166, which meshes with and rotates a fishing and milling casing element ring gear 153. This motor arrangement will be described in more detail with reference to Figures 18 and 19.

A rotary electrical connector or slip ring may transmit data and/or power from the control system 132 to components which are rotated along with the shaft 99 of the single stage gear system.

In the illustrated embodiment, three or more electrical brush contacts 156 are attached to and supported on the underside of stabiliser base plate 122. The electrical brush contacts 156 interface with a rotating electrical contact 152 on the shaft 99 which may for example be a metal ring. The rotating electrical contact 152 is connected to three or more electrical transfer conduits 155. Data and power is transmitted from the electrical brush contacts 156 to the rotating electrical contact 152 and then to the electrical transfer conduits 155.

The three or more electrical transfer conduits 155 are connected to a battery 144. The electrical trunking conduits and the battery rotate with the shaft 99 when the upper assembly 14 is rotated.

The electrical transfer conduits 155 may comprise trunking.

Figure 1 1 is an isometric view of the lower assembly 115 and the planetary gear set of the single stage gear system.

The planetary gear set comprises a sun gear 124 which is formed around the shaft 99 through which the circulation bore 105 is formed; a ring gear 127 which is formed around the inside of the planetary gear mechanism housing 96; and outer and inner planet gears 125 which are connected to the outer planet gear shafts 194 and the inner planet gear shafts 197 respectively. The inner and outer planet gears 125 being arranged such that two planet gear long gear trains are arranged between the ring gear 127 and the sun gear 124, such that the ring and sun gear rotate in the same direction.

The planetary gear set is located between the planetary gear set upper carrier plate 198 and the planetary gear set lower carrier plate 200 and is surrounded by the cylindrical wall of the planetary gear mechanism housing 96. The planet gear shafts 194, 197 are supported by the carrier plates 198, 200, but are able to rotate with respect to the carrier plates 198, 200 due to the sealed planet gear shaft bearings 227. Rotation of the ring gear 127 in a clockwise direction imparts clockwise and anticlockwise rotation to the outer and inner high speed gears 125 respectively and clockwise rotation to the sun gear 124 which is directly connected to the outer diameter of the shaft 99. The shaft 99 is isolated from the planetary gear set upper and lower carrier plates 198, 200 by sealed shaft bearings 102.

The lower assembly 115 comprises a sealed stabiliser housing 72 for the stabilisers when they are retracted. The lower assembly 115 is isolated from the rotation of the components of the upper assembly 115 by the assembly isolating bearing which is located between the planetary gear mechanism housing and the stabiliser housing 72.

The outer housing 84 is not shown in Figure 1 1 but is indicated in Figures 12 and 13.

Figure 1 1 shows the three or more stabilisers in the extended position activated by the stabiliser jacking mechanism 67. The ends of the stabilisers each comprise two stabiliser pads 63 which may be grooved to prevent debris build-up while moving down and to allow fluid to circulate around and along the grooves. The stabilisers may have ends of any shape, for example one or more rollers may be supported on the ends of the arms in some embodiments.

In the illustrated embodiment, the stabilisers comprise a sealed stabiliser wheel bearing mechanism located between the two blades which support a stabiliser wheel 62. The stabiliser wheel 62 may facilitate movement of the device comprising the single stage gear system upwards or downwards inside a containment structure 1 13.

In some embodiments, the stabilisers may not comprise a stabiliser wheel bearing mechanism or a stabiliser wheel 62, and in other embodiments the stabiliser wheel bearing mechanism and/or the stabiliser wheel 62 may be removable or detachable from the stabiliser.

The stabiliser antennae 68 may be located on and/or supported by the stabiliser arms or stabiliser jacking mechanism 67 extensions. The stabiliser antennae 68 may be used for wireless communication where appropriate.

Three power generating means 131 are located between the stabiliser jacking mechanisms 67 within the stabiliser housing 72. The power generating means are connected to and/or driven by the outer planet gear shafts 194 which may drive the generating means so as to generate power when the upper assembly 114 is rotated, thereby rotating the planetary gear set.

Cable conduits 136 connect the power generating means 131 to the control systems 132 of the electrical hydraulic or pneumatic power system 129 which are located on the stabiliser base plate 122. The control systems 132 may transmit or receive data via either wired or wireless connections, and may be connected to the stabiliser antennae 68, for example, for wireless data communication to the surface.

The software which controls the control systems 132 may adaptable and/or updatable for present and future developments to operate a variety of mechanical and electrical tool functions.

The control systems 132 may comprise three or more junction distributors 134 for the hydraulic, electrical and pneumatic power system 129. The central electrical, hydraulic or pneumatic control systems 132 may be cooled by air, may be thermally insulated or may be otherwise arranged.

Figure 12 is an exterior isometric view of a fishing and milling tool 17 which comprises a single stage gear system as described above. The outer protection housing 84 of the fishing and milling tool 17 is not shown (a cut away view of the housing 84 is shown in Figure 13).

The circulation bore 105 enters the top of the tool at the male or female tool connector 86 into the outer housing 57 of the circulation chamber 109, through the top 66 and along the length of the shaft 99 of the single stage gear system. The circulation bore passes through the fishing and milling tool upper and lower tool shafts 88, 77 and exits to the fishing and milling tool 17 via the jetting nozzle 75.

The jetting guide nozzle has an outer diameter smaller than the internal diameter of the upper end 1 1 of the fish 1 17 indicated in Figure 8. The jetting nozzle 75 serving as a cutting and high pressure jetting guide.

The upper end of the milling and fishing tool 17 may have a male or a female tool connector 86 with either a right or left hand thread. The tool connector 86 may comprise a drilling rig elevator lifting recess profile 61 which can be of any design to suit the drilling rig lifting equipment.

The fishing and milling tool 17 comprises two main sections. A single stage gear system and a fishing and milling assembly 1 16.

The hydraulic, electrical and pneumatic power system 129 indicated in Figure 1 1 is housed inside the lower assembly 1 15.

The fishing and milling assembly 116 comprises a first fishing and milling casing element 48 and a second fishing and milling casing element 50. The two fishing and milling casing elements 48, 50 are displaceable with respect to each other. The two fishing and milling casing elements 48, 50 are interlocking, the first fishing and milling casing element 48 comprising a plurality of elongate and substantially flat finger portions which interlock with elongate grooves or depressions formed in the exterior of the second fishing and milling casing element.

The fishing and milling assembly 116 of the fishing and milling tool 17 comprises a plurality of fishing fingers 53 (preferably three or more). The fishing fingers 53 comprise a fishing finger milling and cutting profile 90 on the distal ends of their inner surface from the single stage gearing mechanism comprised by the fishing and milling tool 17. The fishing fingers 53 being located inside the second fishing and milling casing element 50.

The second fishing and milling casing element 50 is displaceable in an axial direction with respect to the first fishing and milling casing element 48, the single stage gear system comprised by the fishing and milling tool 17 and the outer housing 84. The axial direction being parallel to the shafts 99, 88, 77 and the circulation bore 105. The second fishing and milling casing element 50 being displaceable upwards and downwards when the fishing and milling tool 17 is in a vertical arrangement, for example within a vertical well or vertical containment structure 113.

The second fishing and milling casing element 50 may be displaced in the axial direction with respect to the other components, 48, 84, by rotation of second fishing and milling casing element 48.

The first fishing and milling casing element 48, may be rotated by rotating the fishing and milling casing ring gear 153 which is fixed to or formed integrally with the second fishing and milling casing element 48 as shown in figures 17 to 1 9. The fingers of the first fishing and milling casing element 48 which interlock with the grooves of the second fishing and milling casing element 50 cause the second fishing and milling casing element 50 to rotate when the first fishing and milling casing element 50 is rotated.

The second fishing and milling casing element 50 has a cylindrical inner surface which is threaded 70 and which engages with an externally threaded tube 71 . The externally thread tube 71 is located at a fixed distance along the axial length of the fishing and milling tool 17 and does not rotate with the first fishing and milling casing element 48. Therefore, when the first fishing and milling casing element 48 is rotated, the second fishing and milling casing element 50 is rotated with respect to the externally threaded tube 71 and as such the interlocking threads causes the second fishing and milling casing element 50 to be displaced axially with respect to the externally threaded tube 71 and the first fishing and milling casing element 48.

The internal threading 70 of the second fishing and milling casing element 50 is male and the external threading of the externally threaded tube 71 is female.

The first and second fishing and milling casing elements 48, 50 having interlocking fingers and slots so as to allow axial movement of the two fishing and milling casing elements 48, 50 with respect to each other as they are rotated by the rotation of the ring gear 153.

The distal end of the second fishing and milling casing element 50 with respect to the single stage gear system and the first fishing and milling casing element 48 (typically the lower end in use) comprises an end connector 56 which enables the attachment of different ends and accessories to the end of the second fishing and milling casing element 50. The illustrated end connector 56 being annular.

Accessories which are attachable to the second fishing and milling casing element 50 by use of the end connector 56 include a sealing element to provide a seal against the outer housing 84, a washover sub 55 (as shown in Figures 12 to 17), and/or a interchangeable size locking sub 91 (as shown in Figures 23 and 25).

The illustrated washover sub 55 is a substantially circular hollow mill which is connected to the end of the second fishing and milling casing element 50 by the end connector 56. The washover sub 55 comprises a plurality of external cutting blades, male locator profile and internal fishing neck male profile engagement thread 70 can be interchangeable to extend the length and the diameter of the external cutting blades and locator profile; or to install an extension sub with internal thread to match a design of fishing neck engagement profile 69. Any extensions can be made up at the connection 56 to the second fishing and milling casing element 50. This situation may arise for example if the drill pipe 43, drill collar 9 has parted in the body and an extension section is required to reach the fishing neck sleeve 15 or fishing neck 10.

The fishing and milling tool 17 may be used to retrieve in a single run, conventional drill string components which have been lost downhole, (these are examples of what are termed fish 117 in the industry). The fishing and milling tool 17 may also be used retrieve any fish 117 which comprises a new design of fishing neck engagement profile 69. If the upper end 11 of a fish 117 has been damaged, for example where it has been bevelled out, this may prevent conventional overshot assemblies from swallowing the upper end 11 of the fish 117 as a result of tight tool internal dimensional tolerances. The fishing and milling tool 17 may mill and washover the upper end 11 of the fish 117 with high rotational speed using the milling structure 80 prior to engagement.

Figures 13 and 14 are isometric cut away views of the fishing and milling tool 17 shown in Figure 12 with the outer housing 84 included. Figure 13 being a view from below the fishing and milling tool 17 in its typical arrangement, and Figure 14 being a view from above.

The fishing and milling tool has a female treaded tool connector 86 at its upper end which is fixed to or comprised by the upper assembly 114 of the single stage gear system comprised by the single stage gear system comprised by the fishing and milling tool 17. The fishing and milling tool 17 comprises an outer housing 84 which is cylindrical and surrounds and encloses portions of the fishing and milling tool 17 between the circulation chamber housing 57 and the lower far end of the second fishing and milling casing element 50 proximate to the end connector 56. Sealed outer housing bearings 138 are located between a first (upper) end of the outer housing 84 and the circulation chamber housing 57, and between a circumference of the inner surface of the outer housing 84 approximately mid-way along its length and the upper end of the first fishing and milling casing element 48, coplanar with the fishing and milling casing element ring gear 153. The outer housing 84 comprises apertures through which the stabilisers may be extended from the lower assembly 115 of the single stage gear system. In use the outer housing 84 rotates with the lower assembly 115, as such it does not rotate when the stabilisers are extended and braced against some surface, but is free to rotate when the stabilisers are retracted.

An annular outer housing end seal 120 is fixed to the inner wall of the outer housing 84 adjacent its lower end. The outer housing end seal 120 is located between the outer housing 84 and the second fishing and milling casing element 50. The second fishing and milling casing element 50 is displaceable with respect to the first fishing and milling casing element 48, the outer housing 84 and the outer housing end seal 120, but the outer housing end seal 120 is arranged to maintain a seal against the second fishing and milling casing element 50 as it is displaced. The outer housing end seal 120 may be a packing seal. The outer housing end seal 120 may seal with upwards, downwards rotational movement of the second fishing and milling casing element 50.

The female tool connector or engagement means 86 at the top of the milling and fishing tool 17 has a drilling rig elevator lifting recess profile 61 .

The fishing and milling tool 17 comprises a single stage gear system as described earlier in the detailed description, a hydraulic, electrical and/or pneumatic power system 129 and the fishing and milling assembly 116.

Fluid passing through the circulation bore 105 enters the circulation chamber housing 57 of the upper assembly 114 which is isolated from the top 66 of the shaft 99 by a sealed shaft bearing 102. The fluid enters the circulation bore 105 formed through top 66 of the shaft 99 and continues through the shaft 99 into the ball housing cylinder 97 comprised by the fishing and milling assembly 116.

The ball housing cylinder encloses the shaft end ball 101 which is formed on the end of the upper fishing and milling tool shaft 88. The lower fishing and milling tool shaft 77, the upper fishing and milling tool shaft 88, and the shaft end ball 101 form a combined unit which is displaceable with respect to the ball housing cylinder 97 and the other components of the tool.

In use a mechanical means, gravity, and/or the pressure of liquid passing through the circulation bore, is locates combined upper and lower fishing and milling tool shafts 77, 88, and shaft end ball 101 is usually be located such that the shaft end ball 101 is at the lower end of the ball housing cylinder 97. In this arrangement, the shaft end ball 101 blocks the circular aperture formed in the lower end of the ball housing cylinder 97 such that fluid may only exit the ball housing cylinder 97 through the circulation bore 105 formed through the shaft end ball 101 and the remainder of the shaft.

When the lower end of the fishing and milling tool shaft 77, 88, 101 where the jetting nozzle 75 is located is pressed against some external object, for example the upper end 11 of a fish 117, the fishing and milling tool shaft 77, 88, 101 is axially displaced upwards. The shaft end ball 101 is therefore displaced upwards within the ball housing cylinder 97. The motion sensors 94 comprised by the ball housing cylinder detect that the ball has been displaced, thereby detecting that the end of the fishing and milling tool 17 has been pressed against some debris or an item to be recovered.

When the shaft end ball 101 has been raised, this allows fluid to exit the ball housing cylinder 97 via the circular aperture in the lower end 95 of the ball housing cylinder 97 in addition to via the circulation bore 105 through the shaft 77, 88, 101. Fluid which passes through the circular aperture in the lower end 95 of the ball housing cylinder 97 enters a space between the lower end 95 of the ball housing cylinder 97 and a plate 93 which forms the upper end of the lower hollow cylinder housing. The fluid may continue through the nozzle ports 108 in plate 93 and into the lower hollow cylinder housing 58 before exiting through the milling circulation and cooling nozzles 78. If the end of the shaft 77, 88, 101 is pressed sufficiently against some external object the shaft end ball 101 is displaced to the upper end of the ball housing cylinder 97, where it blocks the entrance of the circulation bore 105 through the shaft 99 into the ball housing cylinder 97. As such, fluid is only be able to pass through the tool 17 through the circulation bores 105 through the shafts 99, 77, 88, 101 , before exiting via the jetting nozzle 75. This results in an increase in the fluid pressure within the circulation bore 105, this pressure increase may be detected thereby allowing the fact the drilling tool 17 has been pressed against something such that the fishing and milling tool shaft 77, 88, 101 has been fully axially displaced to its uppermost position.

The pressure increase and the motion sensors 94 allow users to determine when the fishing and milling tool has contacted a fish 117 within a wellbore. The pressure increase allows users to determine when the fishing and milling tool shaft 77, 88, 101 has been fully displaced such that the fishing and milling tool is in a suitable arrangement for milling to occur.

The upper fishing and milling tool shaft 88 has a hexagonal cross section and is received by a slot with a hexagonal cross section through the plate 93. The plate 93 is rotated with the cylindrical ball housing 97 and the shaft 99 of the single stage gear system, such that the fishing and milling tool shaft 77, 88, 101 rotate with the shaft 99 of the single stage gear system. Plate 93 also comprises a plurality of nozzle ports 108 and supports the spring 89 which presses the lower end 95 of the ball housing cylinder against the annular sealing seat 150.

The lower end 95 of the ball housing cylinder 97 is displaceable with respect to the curved wall of the ball housing cylinder 97 and the upper end 106 of the ball housing cylinder 97, but is held in positon by a spring 89. As such if the pressure of the fluid inside the ball housing cylinder is increased sufficiently, the lower end 95 is displaced downwards away from an annular sealing seat 150 formed around the lower end of the curved wall of the ball housing cylinder, thereby creating a gap through which fluid may exit the ball housing cylinder 97 into the milling circulation path 107, through the nozzle ports 108 in plate 93 and into the lower hollow cylinder housing 58 before exiting through the milling circulation and cooling nozzles 78

The ball housing cylinder 97 comprises three or more motion sensors 94 and the intermediate fishing and milling tool shaft mechanism 65 comprises motion sensors 103.

The shaft of fishing and milling mechanism 116 comprises a fishing and milling tool shaft connector 199 which is fixed to the end of the fishing and milling tool shaft mechanism 65 (which in turn is located at the end of the upper fishing and milling tool shaft 88). The fishing and milling tool shaft connector allows a variety of different attachments to be attached to the fishing and milling tool shaft mechanism so as to form the end of the rotating central axial shaft of the fishing and milling tool 17. Attachments which may be attached include the lower fishing and milling tool shaft 77.

The lower fishing and milling tool shaft 77 has an annular shaft seal 104 which is formed around the lower fishing and milling tool shaft 77, a sealed shaft seal bearing 82 is located between the annular shaft seal 104 and the lower fishing and milling tool shaft 77, thereby allowing the lower fishing and milling shaft 77 to continue to rotate when the annular shaft seal 104 has created as seal between the lower fishing and milling tool shaft 77 and some other object, such as part of the upper end 11 of a fish 117.

The lower fishing and milling tool shaft 77 of the fishing and milling tool 17 may comprise a jetting nozzle 75 through which the circulation bore exits the fishing and milling tool 17. Jetting is the process wherein soft materials are drilled by hydraulic impact loading only, through the use of high pressure fluid exiting the circulation bore. The jetting nozzle may be interchangeable, for example to allow differently sized and/or shaped jetting nozzles to be used, such as an asymmetric nozzle which may allow the well to be deviated. An interchangeable jetting nozzle 75 may be removable from the lower fishing and milling tool shaft 77, or a plurality of lower fishing and milling tool shafts 77 may be available and attachable to the fishing and milling tool 17 by use of the fishing and milling tool shaft connector 199.

The fishing and milling tool 17 comprises a heavy duty high speed milling structure 80.

The jetting guide 75 and interchangeable heavy duty high speed milling structure 80 may be modified to be used for jetting, drilling, or a combination of jetting and drilling dependent on the formations and environment in which the fishing and milling tool 17 is to be used

The hydraulic tank, air tank and cooling system 128 are attached to the base of the planetary gear set lower carrier plate 200.

The lower assembly 115 of the single stage gear system comprised by the fishing and milling tool 17 comprises three power generating means 131 which are located between the stabilisers and the stabiliser jacking mechanisms 67. The cable conduits 136 transfer electrical power generated by the power generating means 131 to the central electrical, hydraulic or pneumatic control systems 132 which are positioned above the stabiliser base plate 122.

The one or more electrical, hydraulic or pneumatic motors 154 with motor gear shafts 133 are each connected with a motor support arm 130 (as shown in Figure 18) to the underside of the stabiliser base plate 122 and may be connected to the central electrical, hydraulic or pneumatic control systems 132 in order to be powered and controlled.

The shaft 99 which passes through a central aperture in the stabiliser base plate 122 is separated from the stabiliser base plate 122 by a sealed shaft bearing 102.

The three or more electrical brush contacts 156 attached to the underside of the stabiliser base plate 122 are connected to the central electrical, hydraulic or pneumatic control systems 132 and may transmit data and/or power via the rotating electrical contact 152 to the three or more data and power transfer electrical conduits 155.

The three or more data and power transfer electrical conduits 155 may be connected to the battery 144 which may store electricity, to the three or more motion sensors 94, the motion sensors 103 on the fishing and milling tool shaft mechanism 65, the one or more leadscrew motors 60, the fishing finger sensor mechanism 79, the fishing finger outer magnetised plate surfaces and inward facing with sensors 85, sensors on the one or more of the stop mechanism slots 64 , or any other installed sensors. These sensors may for example be resistance, torque, pressure, temperature, photo resistance, and/or camera monitoring sensors, or may be any other type of sensors.

The lower section of the fishing and milling tool 17 indicated in Figure 12 as the fishing and milling assembly 116, comprises the electrical storage battery 144 for storing and transmitting power generated by the three power generating systems 131 , a hollow ball housing cylinder 97 with three or more motion sensors 94 which are used to detect the position of the shaft end ball 101. The ball housing cylinder 97 is connected to the circulation bore 105 through the shaft 99 and upper fishing and milling tool shaft 88 as indicated in Figure 17.

The three or more motion sensors 94 comprised by the ball housing cylinder 97 are spaced along the inner surface of the ball housing cylinder 97 and may be aligned in a vertical orientation, a helical orientation, or any other orientation.

The one or more leadscrew motors 60 have a gear shaft 133 with a gear 166 which meshes with and rotates the inner cog profile of a fishing and milling tool internal ring gear 36 which is separated from the shaft 99 by a sealed shaft bearing 102.

The one or more leadscrew motors 60 are attached directly to the shaft 99 below the battery 144. The leadscrew motors 60 may create high torque with micro processed control, and may be used to extend or retract the three or more fishing fingers 53 by rotating the outer cog profile of the fishing and milling tool internal ring gear 36.

The fishing and milling tool internal ring gear 36 comprises both internal and external cog teeth. The internal cog teeth mesh with the gear or gears 166 driven by the one or more leadscrew motors 60. The external cog teeth mesh with and drive two or more leadscrew gears 59 (as shown in Figure 19).

The two or more leadscrew gears 59 are each attached to a leadscrew shaft 76. The leadscrew shafts 76 are partially or entirely threaded, and are received by threaded apertures in the fishing finger support outer section 54 (as shown in Figure 15).

Therefore, when the one or more leadscrew motors 60 rotate their associated gear shafts 133, their associated gears 36 are rotated, the fishing and milling tool internal ring gear 36 is rotated, the leadscrew gears 59 are rotated and the leadscrew shafts 76 are rotated. The rotation of the leadscrew shafts 76 causes the fishing finger support outer section 54 to be displaced along the length of the leadscrew shafts 76.

The fishing fingers 53 are connected to the fishing finger support outer section 54 and is axially displaced along with the fishing finger support outer section 54. Therefore, the fishing fingers 53 which are supported by the fishing finger supporting body 96 is axially displaced with respect to the single stage gear system, and the first fishing and milling casing element 48 when the one or more lead-screw motors 60 rotate their gear shafts 133.

The mechanism for extending and retracting the three or more variable fishing fingers 53 will be explained further with reference to Figure 15.

The washover sub 55 is connected to the connection 56 at the end of the second fishing and milling casing element 50. The washover sub 55 may comprise cutting blades radially extending from its external surface (as shown in Figure 16). These blades may enable washover of the fishing neck protection locked sleeve 15 and engagement of the fishing neck with the thread 70 formed on inside of the second fishing and milling casing element 50. . This can be achieved by extending the second fishing and milling casing element 50 using the rotation of the second fishing and milling casing element against the externally threaded tube 71.

The externally threaded tube 71 surrounds the fishing finger support outer section 54 and connects with a tube support means 16 which comprises three arms which are connected to the exterior of the cylindrical ball housing 97. The fishing finger support outer section 54 is slotted to allow the movement downwards and upwards of the three or more fishing fingers 53.

The three or more fishing fingers 53 are connected to the fishing finger support outer section 54 by three or more removable hinges or other fixing mechanisms 52.

When the three or more fishing fingers 53 are axially displaced downwards or upwards by clockwise or anti-clockwise rotation of the two or more lead-screw shafts 76, the three or more fishing fingers 53 moves down or up along three or more corresponding guide slots of the guide slotted body 98.

The fishing finger support outer section 54 comprises stop mechanism fingers 110. The stop mechanisms fingers comprise rigid downwards protruding strips which are located between the fishing fingers 53 and which are displaced with the fishing finger support outer section 54. As the fishing finger support outer section 54 is displaced downwards, the stop mechanism fingers 110 strips are displaced into stop mechanism slots 64. When the fishing finger support outer body 54 is in its lowest position, such that the fishing fingers 53 are fully extended, the presence of the stop mechanism fingers 110 will activate sensors in the stop mechanism slots 64, thereby producing a signal that indicates that the fishing fingers are in their fully extended arrangement. The inner surfaces of the lower parts of the fishing fingers 53 have protrusions 92 formed thereon. The protrusions 92 are in the form of a smooth arcuate hump which protrude from the inner surface of the lower parts of the fishing fingers 53. As the fishing fingers 53 are displaced axially downwards, the ends of the fishing fingers 53 are displaced outwards when the protrusion come into contact with the outer surface of the milling structure 80.

The fishing fingers 53 have tips with fishing finger milling and cutting profiles, at the bottom of which are outer magnetised plate surfaces and inward facing sensors 85.

Below the guide slotted body 98 is the lower shaped sub 83 which has a lower diameter within which the protrusions 92 are located when the fishing fingers are in the their uppermost location, such that the outer ends of the fishing fingers 53 are not expanded and they remain in the slots of the guide slotted body 98.

The lower shaped sub 83 comprises a female milling structure connector 81 (shown in Figure 15) which may be used to connect the pin end of the interchangeable heavy duty high speed milling structure 80 or any other tool accessory, such as a lead impression block, a flat bottom mill or a hollow drill bit which is able to accommodate the fishing and milling tool shaft mechanism 65.

Figure 15 is an isometric view of the fishing and milling tool 17 from below.

The circulation bore 105 enters the upper section of the tool through the shaft end ball 101 . The shaft end ball 101 comprises shaped slots or with nozzles 40 and is attached to the upper end of the upper fishing and milling tool shaft 88. The shaft end ball 101 mates with an indent formed in the lower end 95 of the ball housing cylinder 97.

The fishing fingers 53 attached to the fishing finger support outer section 54 by removable hinges or other fixing mechanisms 52 and are displaceable in an axial direction upwards and downwards by rotating clockwise or anti-clockwise the two or more lead-screw shafts 76.

The guide slotted body 98 may have a hexagonal outside shape or other outside shape and is connected directly to the lower hollow cylinder housing 58. The outside shape is slotted to accommodate the two or more lead-screw shafts 76 which can provide up and down axial movement of the three or more fishing fingers 53 when rotated by the one or more leadscrew motors 60.

The outside shape of the guide slotted body 98 enables the fishing finger support outer section 54 to rotate together at high speed when rotating the shaft 99 connected to the moveable ball housing cylinder 97 which in turn is connected to the lower hollow cylinder housing 58.

At the bottom and on the outside of the fishing fingers 53 are outer magnetised plate surfaces inward facing with sensors 85 which aid with confirmation of the location of the upper end 11 of the fish 117.

The lower part of the fishing fingers 53 have shaped protrusions 92 to extend them outwards when they come in contact with the exterior of the milling structure 80 as the fishing finger support outer section 54 is moved in a downward direction along the two or more lead-screw shafts 76.

The fishing finger milling and cutting profile 90 is used to dress any external damage to the female connector 12 and any surface damage to the upper end 11 of the fish 117 may be milled with the milling structure 80.

Different sizes of milling structure 80 and other connectable tool accessories, such as a lead impression block may be connected to the lower section utilising the female milling structure connector 81 of the lower shaped sub 83. The milling structure 80 may comprise one or more stop mechanism slots 64 with sensors for detecting the one or more stop mechanism fingers 110 attached to the fishing finger support outer section 54 when they are in their lowermost position.

On the internal surface of the second fishing and milling casing element 50 is a thread 70 for engaging the fishing neck profile. The second fishing and milling casing element 50 comprises an end connector 56 which may be used to change the washover sub 55 to be suitable for the dimensions of the upper end 11 of a fish 117, and/or to be suitable for use with the new generation of fishing neck engagement profile 69 further described with reference to Figure 20.

Extending from the inside of the lower section is the lower fishing and milling tool shaft 77 with the shaft seal 104 positioned over a shaft seal bearing 82. When the shaft seal 104 enters the upper end 11 of the fish 117 and seals, the lower fishing and milling tool shaft 77 is free to rotate on the shaft seal bearing 82. Once sealed, attempts may be made to circulate through the fish 117.

The jetting nozzle 75 is located at the end of the lower fishing and milling tool shaft 77. High pressure liquid 75 may be emitted from the jetting nozzle 75 and may be used to clear any debris from the top and/or inside of a fish 117 as the fishing and milling tool 17 is lowered.

A seal may be created between the outer housing 84 and the washover sub 55 and/or the Second fishing and milling casing element 50 by an outer housing seal 120 or equivalent installed on the inner surface of the bottom section of the outer housing 84. The outer housing seal 120 may seal with upwards, downwards rotational movement of the surface of the second fishing and milling casing element 50.

The first fishing and milling casing element 48 comprises an interdigitated connection with the second fishing and milling casing element 50. When the first fishing and milling casing element 48 is rotated, it rotates the second fishing and milling casing element 50 against the externally threaded tube 71. This causes the second fishing and milling casing element 50 to be axially displaced upwards or downwards with respect to second fishing and milling casing element 50. The externally threaded bearing 71 surrounds the fishing finger support outer section 54 and is connected with three armed tube support means 16 to the exterior of the ball housing cylinder 97.

Figure 16 is an isometric view of the fishing and milling assembly 116 from below, displaying the interchangeable heavy duty high speed milling structure 80 which comprises a plurality of shaped cutters and adjustable milling circulation and cooling nozzles 78.

The lower fishing and milling tool shaft 77, and the high pressure jetting nozzle 75 have outer diameters smaller than the internal diameter of the upper end 11 of the fish 117 . The activation shaft seal 104 is made rotatable with respect to the lower fishing and milling tool shaft 77 by a shaft seal bearing 82.

The connection 56 allows the connection of accessories such as the washover sub 55 which has an external cutting profile to enable washover milling and a male locator profile for engagement of a female locator alignment profile 51 comprised by a fishing neck sleeve 15 (as shown in Figure 21 ).

The fishing and milling tool 17 may comprise a camera and light system 140 in order to allow the monitoring of a fishing operation.

The fishing finger milling and cutting profile 90 which is located on the inner surface of the tips of the fishing fingers 52 may be used to cut or mill away any damaged material from the upper end 11 of a fish 117, the outside diameter of which may be regulated by a fishing finger sensor mechanism 79 comprising sensors supported on the inner surface of the fishing fingers 53 above the milling and cutting profiles 90 and below the protrusions 92. This may aid with mechanical engagement of the new generation of fishing neck engagement profile 69 which is shown in Figure 20. Once the fishing neck engagement profile 69 has been located the fishing finger sensor mechanism 79 retracts. The sensors can be pre-programmed to suit the dimensions of the upper end 1 1 of a specific fish 117.

Slot profiles 87 are formed in the milling structure 80 (as shown in figure 16) and contain the fishing finger sensor mechanisms 79. An outward movement of the fishing finger sensor mechanism 79 increases the outside diameter of the three or more fishing fingers 53 to enable them to surround, enclose and thereby grip the upper end 11 of the fish 117.

Figure 17 is an isometric cross sectional view of the fishing and milling assembly 116 of the fishing and milling tool 17.

The location of the upper end 11 of a fish 117 may be determined by means of a pump pressure increase registered on the surface pump pressure gauge 49 (indicated in Figure 8) and/or by a signal indicative of magnetic detection by the sensors located on the outer magnetised plate surfaces 85 of the fishing finger guides 53.

The pump pressure increases may be as a result of the jetting nozzle 75, the lower fishing and milling tool shaft 77, and the fishing and milling tool shaft mechanism 65 which comprises motion sensors 103, entering the upper end 11 of the fish 117, such that the shaft seal bearing 82 is located in and seals with the restricted fish tool joint internal diameter.

As the drill string is lowered further after this seal has been made, the shaft end ball 101 which is attached to the upper end of the upper fishing and milling tool shaft 88 is displaced upwards in an axial direction off of the spring 89 retained lower end of the ball housing cylinder 97. The three or more motion sensors 94 indicated in Figure 13 determines the position of the shaft end ball 101 within the ball housing cylinder 97.

The shaft end ball 101 may be held in place either electrically or mechanically against the spring 89 retained lower end of the ball housing cylinder 97, until a pre-set force has exerted on the jetting nozzle 75.

The upper fishing and milling tool shaft 88 is shaped (for example with a hexagonal cross section) to maintain orientation to ensure the three or more motion sensors 94 detect the shaft end ball 101 and to enable the upper fishing and milling tool shaft 88 to be rotate when the ball housing cylinder 97 and the lower hollow cylinder housing 58 are rotated by the shaft 99.

Sensors indicate when the shaft end ball 101 with ball circulation shaped slots or nozzles 40 formed on its upper half has mated with the upper end 106 of ball housing cylinder 97.

The ball circulation shaped slots or nozzles 40 allows the circulation fluid to bypass the shaft end ball when the shaft end ball 101 mates with the upper end 106 of ball housing cylinder 97.

Increasing the circulation through the circulation bore 105 increases the pump pressure and moves the lower end 95 of ball housing cylinder 97 downwards along with the annular sealing seat 150 located thereon. This compresses the spring 89 and allows the circulation fluid to escape the cylindrical ball housing 97, through the milling circulation path 107 and through the plate 93 nozzle ports 108 into the lower hollow cylinder housing 58 and out through the milling circulation and cooling nozzles 78. Circulation can be required to flush any milled cuttings up the well bore to the surface and to cool the interchangeable heavy duty high speed milling structure 80.

The internal profile of the plate 93 and the lower end 95 of ball housing cylinder 97 matches the external profile of the shaft end ball 101 and the upper fishing and milling tool shaft 88 such that the upper fishing and milling tool shaft 88 will rotate when he ball housing cylinder 97 is rotated by the rotation of the shaft 99 (for example the upper fishing and milling tool shaft 88 may have a hexagonal cross section, and the plate 93 may have a hexagonal aperture through which it is arranged).

The fishing finger sensor mechanism 79 may be used to increase or decrease the fishing fingers 53 outer diameter. When extended, this increases the outside diameter of the three or more fishing fingers 53, thereby allowing differently dimensioned fish 117 to be retrieved.

On the internal surface of the second fishing and milling casing element 50 is a fishing neck male profile engaging thread 70. With the shaft 99 stationary, rotation of the first fishing and milling casing element 48 by fishing and milling casing element ring gear by the one or more electrical, hydraulic or pneumatic motors 154 rotates the thread 70 against the externally threaded tube 71 with outer female thread profile. This causes the washover sub 55 to be axially displaced downwards and lowered over the upper end 11 of the fish 117 increasing the machined tolerance gap 74 between the interdigitating portions of the first fishing and milling casing element 48 and the second fishing and milling casing element 50. The fishing neck sleeve 15 may be released with high torque and rotated downwards. The new generation of fishing neck engagement profile 69 shown in Figure 21 may be engaged with the fishing neck male profile engagement thread 70.

The second fishing and milling casing element 50 with the fishing neck male profile engagement thread 70 formed on its internal surface extends upwards underneath the smooth interior surface of the interdigitating portions of the first fishing and milling casing element 48.

The milling structure 80 and the lower shaped sub 83 at the base of the lower hollow cylinder housing 58 connected to the ball housing cylinder 97 is rotated by the upper fishing and milling tool shaft 88 when the shaft 99 is rotated.

The outer housing 84 is attached and isolated from the first fishing and milling casing element 48 by a sealed bearing 138 as part of the fishing and milling tool casing end plate 149.

The three or more data and power electrical conduits 155 continue downwards along the shaft 99 to the electrical storage battery 144 and to any sensor equipment such as the motion sensors 103.

A camera and light system 140 may be included if monitoring of fishing operations is required. Figure 18 is an isometric detailed view of the upper end of the fishing and milling assembly 116 with the outer housing 84 partially cut away.

The slotted section outside surface of the second fishing and milling casing element 50 has a smooth machined surface and as it moves downwards the machined tolerance gap 74 - between the bottom of the slots formed in the outer surfaces of second fishing and milling casing element 50 and the lower ends of the finger portions comprised by the first fishing and milling casing element 48 - increased.

The three or more electrical brush contacts 156 are connected to the underside of the stabiliser base plate 122 as indicated in Figure 17 and mate with the rotating electrical contact 152 which is formed around on the exterior of the shaft 99.

The one or more electrical, hydraulic or pneumatic motors 154 each with a motor gear shaft 133 are each connected with a motor support arm 130 to the underside of the stabiliser base plate 122 and are connected to the central electrical, hydraulic or pneumatic control systems 132 indicated in Figure 14 for power, control signals, and/or programmable functions.

The motor gear shaft 133 connected to the motor gear 166 can rotate the fishing and milling casing element ring gear 153 situated on the fishing and milling casing end plate 149. This can extend and retract the second fishing and milling casing element 50 to connect and lock onto the fishing neck sleeve 15 indicated in Figure 21 . This can only be performed when the shaft 99 is not rotating.

Clockwise motion of the motor gear 166 rotated the fishing and milling casing element ring gear 153 clockwise. The fishing and milling casing element ring gear 153 is attached to the interior surface of the first fishing and milling casing element 48 and to the fishing and milling casing end plate 1 9. This rotates the first fishing and milling casing element 48 in a direction either to extend or retract the second fishing and milling casing element 50. Clockwise motor rotation moves the second fishing and milling casing element 50 downwards to connect and lock onto the fishing neck engagement profile 69 and anticlockwise motor motion moves the second fishing and milling casing element 50 upwards to release from the fishing neck engagement profile 69 indicated in Figure 20.

The second fishing and milling casing element 50 with an internal thread 70 which is an internal fishing neck male profile engagement thread, rotates against the fixed female thread externally threaded tube 71 resulting in downward axial displacement of the second fishing and milling casing element 50.

Anti-clockwise rotation of the motor gear 166 rotates the fishing and milling casing element ring gear 153 anti-clockwise and move upwards the second fishing and milling casing element 50 of the fishing and milling assembly 116.

The power to operate the one or more electrical, hydraulic or pneumatic motors 154 is transmitted from the central electrical, hydraulic or pneumatic control systems 132 which convert either clockwise or anti-clockwise movement of the motor gear 166 to anti-clockwise or clockwise movement of the fishing and milling casing element ring gear 153.

The motor gear 166 is able to rotate freely either in a clockwise or anti-clockwise direction when the motor is not active. This ensures the gear 166 does not prevent rotation of the fishing and milling casing element ring gear 153 when rotation of the shaft 99 rotates the second fishing and milling casing element 50 via the externally threaded tube 71 which thereby rotates the first fishing and milling casing element 48.

The circulation bore 105 passes through the shaft 99 which is separated from the fishing and milling casing element ring gear 153 and fishing and milling casing end plate 149 by a shaft sealed bearing 102 seal.

The three or more electrical brush contacts 156 which are connected to the underside of the stabiliser base plate 122 connect while stationary and while rotating to one or more rotating electrical contacts 152 which in some embodiments may comprise three or more insulated armature data transfer mechanisms. The rotating electrical contact 152 is fixed to and rotates with the shaft 99. Data may be sent and received and power may be transmitted via the three or more electrical transfer conduits 155 attached to the shaft 99. The three or more electrical transfer conduits 155 extend downwards along the exterior of the shaft 99 to the electrical storage battery 144, to the three or more motion sensors 94, and/or to any other sensors.

Insulated armature data transfer mechanisms 152 are insulated from each other and can be placed anywhere suitable along the shaft 99 where data communication between stationary and rotatable parts is required.

Figure 19 is an isometric cross sectional view of the fishing and milling assembly 116.

The outer housing 84 is attached to and rotationally isolated from the first fishing and milling casing element 48 by a sealed bearing mechanism 138 which contacts part of the fishing and milling casing end plate 149.

The electrical storage battery 144 is attached to and rotates with the shaft 99. With the shaft 99 stationary, engagement of the fishing neck protection sleeve 15 may be attempted by rotating the first fishing and milling casing element 48 with the motor gear 166 against the fishing and milling casing element ring gear 153 which rotates the fixed externally threaded tube 71 with outer female thread profile. This in turn rotates the second fishing and milling casing element 50 internal fishing neck male profile engagement thread 70 lowering the washover sub 55 to release the fishing neck protection sleeve 15 and engage the new fishing neck engagement profile 69 indicated in Figure 20. During this operation, the shaft 99 is isolated from the fishing and milling casing element ring gear 153 by the shaft sealed bearing 102 seal.

The second fishing and milling casing element 50 which comprise the fishing neck male profile engagement thread 70 extends upwards behind the smooth interior surface of the extending finger or tab shaped portions of the first fishing and milling casing element 48.

The circulation flow path is through the circulation bore 105, the shaft 99 into the attached ball housing cylinder 97, through the shaft end ball 101 ; the upper fishing and milling tool shaft 88; the intermediate fishing and milling tool shaft mechanism 65 with the shaft seal bearing 82; the lower fishing and milling tool shaft 77 and out through the jetting nozzle 75.

When the circulation pressure is sufficiently increased the spring 89 may be compressed and the lower end 95 of the ball housing cylinder 97 may be displaced downwards off its sealing seat 150, thereby allowing the fluid to by-pass the lower end 95 of the ball housing cylinder 97 and flow through the nozzle ports 108 in the plate 93 into the lower hollow cylinder housing 58 and through the milling circulation and cooling nozzles 78.

The fishing finger milling and cutting profile 90 may have outer magnetised plate surfaces and inward facing sensors 85. This may be used to locate the upper end 11 of a fish 117.

When the fishing fingers 53 are lowered by rotating clockwise the two or more lead-screw shafts 76 the shaped protrusions 92 extends the fingers radially outwards as they are pressed outwards when they contact the exterior of the milling structure 80 (which has a greater radius than the lower shaped sub 83 adjacent to which the protrusions are located when the fishing fingers 53 are retracted). This may facilitate in the surrounding the upper end 11 of a fish 117.

The one or more leadscrew motors 60 have a gear shaft 166 with a gear 166 connected to the inner cog profile of the fishing and milling tool internal ring gear 36 which is isolated from the activation shaft by a sealed shaft bearing 102.

The variable speed geared leadscrew motors 60 which are attached to the shaft 99 by supports create high torque with micro processed control which can be used to extend or retract the fishing fingers 53 by rotating the outer cog profile of the fishing and milling tool internal ring gear 36 which rotates two or more leadscrew gears 59 which are fixed to the end of the two or more leadscrew shafts 76. The two or more lead-screw shafts 76 attached to the leadscrew gears 59 extend through threaded apertures in the fishing finger support outer section 54 into the slots of the three or more guide slotted body 98 and terminate above the top of the lower shaped sub 83.

When the shaft 99 rotates, the fishing and milling assembly 116 assembly rotates as a unit inside the outer housing 84. The two or more leadscrew shafts 76 may or may not be simultaneously rotated by the leadscrew motors 60 so as to lower or raise the three or more fishing fingers 53 by the rotation of the fishing and milling tool internal ring gear 36. The fishing and milling tool internal ring gear is isolated from the activation shaft by a sealed shaft bearing 102 which is situated on the top of the upper end 106 of the ball housing cylinder 97.

A seal may be created between the outer housing 84 of the tool and the fishing and milling assembly 116 by an outer housing seal 120 which may be a packing seal or equivalent. The outer housing seal 120 may be installed on the inner surface of the outer housing 84 and may contact the exterior of the washover sub 55, the connection 56 or the second fishing and milling tool casing element 50. Alternatively, the outer housing seal 120 may be installed on the exterior of the fishing and milling assembly 116.

Figure 20 is side view of a drill string component 158 such as a drill collar 9, drill pipe 43 or heavy weight drill pipe 5 comprising a unique design of fishing neck engagement profile 69. The fishing neck engagement profile 69 may be used to replace the conventional fishing neck 10 of other drill string components, such as a string stabiliser 7 and/or near bit stabiliser 3.

The new design of fishing neck engagement profile 69 may have a recessed female threaded profile positioned below or as a part of the upper tool connector 42 or upper engagement means 42 of the component 158. This engagement profile or thread corresponds to the fishing neck male profile engagement thread 70 comprised by the fishing and milling assembly 116. The fishing neck male profile engagement thread 70 can be sized to suit the upper end 11 of the fish 117. In some embodiments, the fishing neck engagement profile 69 and the fishing neck male profile engagement thread 70 may be left handed or right handed threads with a wide thread pitch and square type crest. This may ease make-up and break-out of the fish 117.

The upper tool connector 42 or engagement means 42 comprises a female threaded indent 12. The drill string component 158 also comprises a lower tool connector 42 or engagement means 42 which in the illustrated embodiment comprises a male threaded connector 18. A circulation bore 105 enters the female connector 12, extends through the length of the drill string component 158 and exits through the male threaded connector 18.

The fishing neck sacrificial wear ring 73 and the lower tool connector 42 or engagement means 42 each comprise circulation cut-outs 157 or grooves 157 so as to provide circulation flow by pathways. The fishing neck sacrificial wear ring 73 may have a hardness greater than that of the body of the drill string component 158 so as to extend the usage life of the fishing neck engagement profile before replacement is necessary.

Figure 21 is an isometric view of a drill string component 158 as shown in Figure 20 with the new fishing neck engagement profile 69 covered by a fishing neck protection locked sleeve 15 viewed from a different angle. The fishing neck protection sleeve 15 which may be locked in place at its lower end by one or more locking recessed nuts 38 or by any other suitable locking mechanism which may break after a pre-determined torque has been reached.

The fishing neck sleeve female locator alignment profile 51 matches the washover sub 55 profile indicated in Figure 16.

When the second fishing and milling casing element 50 is lowered the washover sub 55 engages the fishing neck sleeve female locator alignment profile 51 and - with either left handed or right handed torque, dependent upon the thread profile - shears on the lower end underside the one or more protection sleeve locking recessed nuts 38 or other suitable locking mechanism.

Further rotation lowers the fishing neck protection sleeve 15 exposing the fishing neck engagement profile 69 which connects to the fishing neck male profile engagement thread 70 and create a seal.

If the drill string component 158 is to be recovered from a wellbore it may be an example of a fish 117.

The length of interior of the fish 117 such as the drill string component 158 may have liquid circulated through via the circulation bore 105. The fish 117 or the drill string component 158 may be worked on with the drilling jars in an upward or downward direction to free if stuck and recovered to surface. In the event the fish 117 cannot be freed, the fishing and milling tool 17 tool may be released from the fish 117 or drill string component 158 with anticlockwise or clockwise rotation of the washover sub 55 utilising the one or more electrical, hydraulic or pneumatic motors 154.

Figures 22 to 25 illustrate conventional drill pipe components comprising conventional fishing necks 10 instead of the new fishing neck engagement profile 69.

Figure 22 is an isometric view of a conventional length of drill pipe 43 with upper and lower tool connectors 42 or engagement means 42. The drill pipe comprises a lower male pin end connection 18, and an upper female connector 12 which is also the fishing neck 10. The circulation bore 105 enters through the upper female connector 12 and exits through the lower male pin end connection 18.

Figure 23 is an isometric view of the conventional length of drill pipe 43 shown in figure 22 with the end of the fishing and milling tool 17 enclosed over its upper end so as to retrieve it from a wellbore. The figure displays the fishing finger mechanism positioned over the end of conventional drill pipe 43 upper tool joint 42. The fishing fingers 53 can be locked by the locking sub 91 which compresses the finger mechanisms around the tool joint 42 when fishing for conventional drill pipe 43.

The locking sub 91 may have a cutting profile on the external surface which may aid with clearing debris around the upper end 11 of the fish 117 while washing over.

Differently sized locking subs 91 with external cutting profiles may be installed at the end connection 56 on the interchangeable sized second fishing and milling casing element 50 in order to correspond to differently dimensioned upper ends 11 of fish 117.

The external cutting profile of a sub 55, 91 may be any shaped design and used to wash over and clear debris from around the upper end 11 of a fish 117.

The outside profile of the fishing fingers 53 when fishing for conventional equipment can be conical shaped 167 with their tips extending radially outwards from their upper ends in order to aid with compressing and locking the fingers over the end fishing neck tool joint 42.

Figure 24 is an isometric view of a conventional drill collar 9 with either a spiral or a flat surface profile and where the fishing neck 10 has a smooth surface. The circulation bore 105 is through the upper female connector 12 and exits through the lower male pin end connection 18.

Figure 25 is a cross sectional isometric view of the conventional drill collar 9 shown in Figure 24 with the end of the fishing and milling tool 17 enclosing its upper end. The figure indicates the mechanism for locking with the locking sub 91 which may have cutting profiles on the external surface.

Each of the fishing fingers 53 has three or more male cutting profiles 173 on the inside diameter and may have magnetic plate surfaces with sensors on the outside diameter. Two or more grooves 46 can be cut into the fishing neck 10 surface of the drill collar 9 by rotation of the extended fishing finger support outer section 54.

The outside profile of the fishing fingers 53 may be conically or frustum shaped 167 outwards to aid with compressing and locking the fishing fingers 53 over the fishing neck 10 when the locking sub 91 , connected to the interchangeable sized second fishing and milling casing element 50 is moved downwards by rotation of the fishing and milling casing element ring gear 153.

Figure 26 is a cross sectional view of a well construction 4 for a casing cutting and window milling operation. The casing cutting and window milling assembly 119 is the first tool in the upstream oil and gas industry, which may perform high speed casing cutting or window milling or a combination of both operations.

The casing cutting and window milling assembly 119 may be run on drill pipe 43, a heavy weight drill pipe 5 and a casing cutting and window milling bottom hole assembly 29 inside the production casing 23 to the planned top casing cut or the window length to be milled 32.

The casing cutting and window milling assembly 119 comprises a single stage gear system as described earlier in the detailed description, with three or more stabiliser pads 63 extended against the inside of the production casing 23.

High speed rotation of the shaft 99 of the gear system may be induced by surface rotation of the top of the drill pipe 45 at the rig floor 39 and the input rotational power source 8.

The lever powered jacking system 160 can adjust the angle of the casing cutting and window milling head 168 and is explained further with reference to Figures 28 and 29.

The circulation bore 105 enters through the top of the drill pipe 45 and the drill pipe 43 with the pumping pressure indicated on the pump pressure gauge 49 (which may be either digital or analogue). The drill string weight indicator 47 may be used to monitor the up and down weight of the drill string to aid with the operational functions of the casing cutting and window milling assembly 119.

The well indicated can be made up of the blowout preventer equipment and wellhead 37, either positioned on the seabed, mobile drilling rig substructure or land rig cellar base 41.

The casing scheme may consist of a surface conductor casing 35, surface casing 31 , intermediate casing 27 and a production casing 23 all cemented in place 33. The watered-out perforations 26 in the production casing 23 may have been isolated with a cement plug 28 with the bottom casing shoe cement sealed 20.

Figure 27 is an isometric view of the casing cutting and window milling assembly 119 without its outer housing 84 in a well bore casing 23 with parts of the casing being shown cut away. The upper male or female tool connector or engagement means 86 may be either a right or left hand thread connection.

Figure 28 is another isometric view of the assembly 119 shown in Figure 27.

The device may be arranged in a well bore casing, for example the production casing 23 as indicated in Figure 26, positioned at the top of the casing cut, or the window length to be milled 32.

To achieve high speed casing cutting or window milling at the high-speed end 223, the casing cutting and window milling assembly 119 comprises a single stage gear system as described earlier in the detailed description. Three or more stabiliser pads 63 are extended against the inner surface of the production casing 23 and when retracted is flush with the outside diameter of the stabiliser housing 72. The input rotational power source 8 rotates the drill pipe 45, the heavy weight drill pipe 5 and the casing cutting and window milling bottom hole assembly 29 connected to the male or female tool connector or engagement means 86 at the low-speed end 222.

The lower assembly 115 is isolated from the shaft 99 by a sealed shaft bearing 102. The hydraulic, electrical and pneumatic power system 129 provides power to operate the stabiliser jacking mechanism 67 and the lever powered jacking system 160. Although only as single stage gear system is indicated, any number of stages in series may be included in the device dependent on the application and the speed of rotation required at the high-speed end 223.

The central tool shaft comprises an upper shaft 99 with two or more adjustable nozzle profiles 143 on the outer circumference, connected to an upper and lower solid or hollow window milling and casing cutting rotating shaft 164 separated by one or more orientable cardon mechanisms 161 to orientate the casing cutting and window milling head 168 from a horizontal to an inclined elevation in a vertical well.

The sealed bearing housing 165 around the lower solid window milling and casing cutting rotating shaft 164 may be connected by a hinged mechanism or similar to a lever 163 and lever powered jacking system 160.

The circulation bore 105 enters the top of the tool with fluid circulation to cool the casing cutting and window mill outward shaped cutting profile 169 with or without shaped regenerative cutters. This is achieved by jetting through the two or more adjustable nozzle profiles 143 in a down wards direction against the tool outer housing 84 (not shown in this figure) and the top of the casing cutting and window milling head 168.

The adjustable circulation nozzle profiles 143 can be replaced and connected to extension flexible hoses when the window milling and casing cutting rotating shaft 164 is hollow. The flexible hoses can be attached to the window milling and casing cutting rotating shaft 164 to allow circulation through the shaft and the adjustable sized guide with cutting profile 172. This aids with keeping the window mill outward shaped cutting profile 169 clear of milled debris with a return path for the circulation fluid via the inside diameter of the production casing 23 and the outside diameter of the outer housing 84.

The bottom of the casing cutting and window milling assembly 119 consists of a casing cutting and window milling head 168 with an attachment for a solid or hollow adjustable sized guide with cutting profile 172. The dimensions of the solid or hollow adjustable sized guide with cutting profile 172 can be sized to suit the production casing 23 inside diameter and planned angle of orientation of the casing cutting and window milling head 168.

When the casing cutting and window milling assembly 119 is used to cut casing and is positioned at the top of the casing cut 32 in the production casing 23, the casing cutting and window milling head 168 can be orientated by the hinged lever 163 and the lever powered jacking system 160 and a section of the production casing 23 cut with high speed and low downward weight utilising the single stage gear system. The device may then be rotated a third of a turn for example using surface rotation of the top of the drill pipe 45 and the remaining section of the production casing 23 cut.

When the casing cutting and window milling assembly 119 is used to mill a window at the planned top of the window length to be milled 32, the casing cutting and window milling head 168 can be orientated by the hinged lever 163 and lever powered jacking system 160. The rotation of the drill pipe 45 results in high rotational speed of the shaft 99 connected to the single stage gear system. The planned top of the window length to be milled 32 may then be cut while lowering the casing cutting and window milling assembly 119 monitoring the up and down weights indicated on the drill string weight indicator 47.

Figure 29 is an isometric view of the casing cutting and window milling assembly 119 with its outer housing 84 in an inclined well bore production casing 23 with parts of the casing being rendered transparent and the window milling head 168 in its initial position. The three or more stabiliser pads 63 are extended against the inside of the production casing 23. The sealed assembly isolating bearing 121 allows the upper assembly 114 to rotate without rotating the stabiliser housing 72 when the three or more stabiliser pads 63 are extended. Movement in an upwards or downwards direction of the hinged lever system 163 attached at the bottom to the sealed bearing housing 165 and at the top to the lever powered jacking system 160 can orientate the casing cutting and window milling head 168 and the window mill outward shaped cutting profile 169 to perform the cutting or window milling operations.

The hinged lever system 163 can be activated in an upwards or downwards direction by the lever powered jacking system 160 with hydraulic power received from the hydraulic, electrical and pneumatic power system 129 positioned above and below the stabiliser base plate 122. The planet gear shafts 194 are connected and provide rotation to the hydraulic, electrical and pneumatic power system 129 when input rotation is applied to the top tool connector or engagement means 86 maintaining a fully charged electrical storage battery 144.

The lever powered jacking system 160 is connected directly to the stabiliser base plate 122. When the hinged lever system 163 is activated in a downwards direction, the one or more orientated cardon mechanisms 161 orientates the casing cutting and window milling head 168 for example, against the upper surface of the inclined production casing 23 enabling the window mill outward shaped cutting profile 169 to cut the casing or mill a window in the production casing 23. Upwards movement of the hinged lever system 163 can return the casing cutting and window milling head 168 to its initial position. Further movement upwards may move the window mill outward shaped cutting profile 169 for example, against the lower surface of the inclined production casing 23 enabling the window mill outward shaped cutting profile 169 to cut the casing or mill a window in the production casing 23.

The sealed bearing housing 165 prevents rotation of the hinged lever system 163 and the lever powered jacking system 160 when the shaft 99 rotates.

Figure 30 shows a cross sectional view of a well assembly 2 for an upstream oil and gas well construction casing section milling operation.

The casing section milling assembly 118 can perform variable high speed casing section milling with regenerative, feeding cutting shaped profiles 112 indicated in Figure 31 and Figure 32.

The device can be run on drill pipe 43, heavy weight drill pipe 5 and a casing section milling bottom hole assembly 34 inside the intermediate casing 27 to the production casing 23 top cut 24 of the section length to be milled 22. The production casing 23 has previously been cut at the top cut 24 and the casing recovered to surface.

High speed rotation can be generated from the surface rotation of the top of the drill pipe 45 at the rig floor 39 and the input rotational power source 8.

The casing section milling assembly 118 indicated comprises the single stage gear system with three or more stabiliser pads 63 extended against the inside of the intermediate casing 27, the casing section milling head 147 and the casing section mill lower ported adjustable sized guide with cutting profile 170.

The circulation bore 105, enters through the top of the drill pipe 45 and the drill pipe 43 with the pumping pressure indicated on the pump pressure gauge 49 which may be either digital or analogue. The drill string weight indicator 47 can be used to monitor the up and down weight of the drill string to aid with the casing section milling assembly 118 tool operational functions.

The well indicated can be made up of the blowout preventer equipment and wellhead 37, either positioned on the seabed, mobile rig sub structure or the land rig cellar base 41 . The casing scheme may consist of a surface conductor casing 35, surface casing 31 , intermediate casing 27 and production casing 23 all cemented in place 33. The watered-out perforations 26 in the production casing 23 may have been isolated with a cement plug 28 with the bottom casing shoe cement sealed 20. Figure 31 is an isometric view of the casing section milling assembly 118 with an upper tool connector or engagement means 86 with either a right or left hand thread connected to the top of the circulation chamber 109 and with the outer housing 86 and the casing portions 23, 27 being partially cut away.

Figure 32 is a cross sectional isometric view of the assembly 118 shown in Figure 31 . The casing section milling assembly 1 8.

The outer housing 84 has been removed to display the internal components and can be connected to the top of the upper assembly 114 with a sealed bearing mechanism 138 as indicated in Figure 13. Permanent fixing can be made at the stabiliser base plate 122 and the upper plate 148 with the outer housing 84 extending down to above the section milling head circulation channels 141.

The casing section milling head 147 is positioned at the top of the planned casing section length to be milled 22 at the previously production casing 23 top cut 24.

The single stage gear system is indicated with three or more stabiliser pads 63 extended against the inside of the intermediate casing 27 positioned on the stabiliser base plate 122. The assembly converts the rotational speed of the casing section milling bottom hole assembly 34 connected to the male or female tool connector or engagement means 86 at the low speed end 222 to a variable higher speed at the casing section milling head 147 high speed end 223. Although one stage is indicated the casing section milling assembly 118 may comprise any number connected in series in order to increase the rotational speed at the high speed end 223.

Section milling fluid enters the circulation bore 105 through the shaft 99 partly exiting through the casing section mill lower nozzle ported adjustable sized guide 170 and with circulation cooling bores 171 through the casing section milling head 147 connected to the surface regenerative cutting shaped profile 112 channels. The return circulation path may partly bypass around the casing section milling head 147 with the remaining flow upwards through the section milling head circulation channels 141 , between the inside diameter of the intermediate casing 27 and the outside diameter of the outer housing 84.

The nozzle profile size can be adjusted dependent on how much flow is required through the nozzle ported adjustable sized guide 170 or around through the surface regenerative cutting shaped profiles 112.

The casing section mill lower nozzle ported adjustable sized guide 170 can be any size of outside diameter with a maximum being the drift size of the production casing 23 to be section milled. Circulation may cool the surface regenerative cutting shaped profiles 112, maintain the casing section milling head 147 clear of milled debris and circulate the milled cuttings to surface via the annulus between the outer housing 84 and the intermediate casing 27.

The casing section milling head 147 has on is exterior surface regenerative cutting shaped profiles 112 activated by three or more telescopic hydraulic-electrical controlled jacking devices 142 attached to the underside of the stabiliser base plate 122, powered by the hydraulic, electrical and pneumatic power system 129 positioned above and below the stabiliser base plate 122. The planet gear shafts 194 are connected and provide rotation to the hydraulic, electrical and pneumatic power system 129 when input rotation is applied to the upper tool connector or engagement means 86 thereby maintaining a fully charged electrical storage battery 144.

The mechanism for feeding the regenerative cutting shaped profiles 112 is by means of forcing downwards utilising the three or more telescopic hydraulic-electrical controlled jacking devices 142 the upper plate 148 against the regenerative cutting shaped profiles 112 encased in fixed cylinder housings 151 attached to the base of the lower rotational plate 146. This compresses the spring mechanism 145. The upper plate 148 is isolated from the shaft 99 by a sealed shaft bearing 102 and from the lower rotational plate 146 and the outer housing 84 by a full diameter sealed thrust bearing 137.

The compressed spring mechanism 145 returns the regenerative cutting shaped profiles 112 back inside the casing section milling head 147 when the jacking force is released thereby maintaining them free from locking with any corrosion or fluid debris.

An alternative means of locking the regenerative cutting shaped profiles 112 once extended can be to install a ratcheting mechanism to the upper non-rotational plate 148 to hold the plate in position thus allowing the jacking devices 142 not to be constantly activated by hydraulic pressure and only used when extending the regenerative cutting shaped profiles 112. Once the section length to be milled 22 indicated in Figure 30 has been completed the ratchetting mechanism can be disengaged and the regenerative cutting shaped profiles 112 retracted from the casing section milling head 147 by the compressed spring mechanism 145.

Figure 33 shows a cross sectional view of a well assembly for an upstream oil and gas well construction casing operation. The multiple stage friction welding 175 tool assembly comprises the high speed multiple stage gear system 111 as indicated in Figure 34.

The illustrated embodiment includes four single stage gear systems. Any number of stages can be used dependent on the rotational speed required at the high-speed end 223.

The multiple stage friction welding 175 tool assembly can perform high speed friction welding with one trip of the assembly.

A fish 117 may have been left in the open hole section 21 as a consequence mechanical failure. Attempts may be made to recover the fish with conventional fishing equipment or with the combination fishing milling stabilised automated drilling tool 17 as described above.

The multiple stage friction welding 175 tool assembly provides the option to friction weld and blank off the inner bore of the solid or hollow metallised item 180 if required. Attempts may then be made to recover the fish 117 or release from the fish 117 at the friction welding tool safety joint 176.

The fish 117 length components can be made up of a drill bit 6, a near bit stabiliser 3, drill collars 9 with a spiral or flat profile, string stabiliser 7 and the solid or hollow metallised item 180 to be high speed friction welded and blanked off utilising the inner insulation shaped friction welding conical profile 178 inside the outer adjustable sized friction welding housing 184.

Above the outer adjustable sized friction welding housing 184 is the friction welding tool safety joint 176 with easy release with anticlockwise rotation.

The multiple stage friction welding 175 tool assembly can be run on drill pipe 43, heavy weight drill pipe 5 and a friction welding bottom hole assembly 25 to above the upper end 1 1 of the fish 117 in preparation to weld and blank off the fish 117 length components.

The multiple stage friction welding 175 tool assembly comprises in this example of four single stage gear systems, each with the three or more stabiliser pads 63 which may be extended against the open hole section 21 above the friction welding tool safety joint 176.

The multiple stage gear system 111 can provide a variable high speed rotation dependent upon the surface rotation of the top of the drill pipe 45 at the rig floor 39 and the input rotational power source 8.

The circulation bore 105, is through the top of the drill pipe 45 and the drill pipe 43 with the pumping pressure indicated on the pump pressure gauge 49 which can be either digital or analogue. The drill string weight indicator 47 can be used to monitor the up and down weight of the drill string to aid with the multiple stage friction welding 175 tool functions.

The well indicated can be made up of the blowout preventer equipment and wellhead 37, either positioned on the seabed, mobile drilling rig substructure or land rig cellar base 41. The casing scheme may consist of a surface conductor casing 35, surface casing 31 , intermediate casing 27 and production casing 23 all cemented in place 33.

Figure 34 is a cross sectional view of the multiple stage friction welding 175 tool assembly inside a containment structure 113 with the outer housing 84 not shown.

The upper section consists of a multiple stage gear system 111 comprising four single stage gear systems connected in series.

The hydraulic, electrical and pneumatic power system 129 positioned above and below the stabiliser base plate 122 provides power to operate the stabiliser jacking mechanism 67. This may not be required in the situation when a solid stabiliser arm length is being used with the stabiliser ends attached to the internal surface of the containment structure 113, for example by welding or screwing.

The lower section of the multiple stage friction welding 175 tool assembly comprises a friction welding tool safety joint 176 with outer body circulation channels connected to the lower part of the multiple stage gear system 111.

The components below the friction welding tool safety joint 176 comprise the lower fishing neck profile 183 and the outer adjustable sized friction welding housing with circulation channels 184 with a shaped external washover cutting profile 179 at the lower end. The outer adjustable sized friction welding housing with circulation channels 184 has an inner shaped conical profile 178 which rotates at high speed against the top of the solid or hollow metallised item 180 generated from the high-speed end 223 of the multiple stage gear system 111.

The inner shaped conical profile 178 may be any suitable shape for the welding application.

Variable rotation at the low speed end 222 creates high-speed rotation at the high-speed end 223 dependent on the number of stages installed and the input rotational power source 8.

Figure 35 is an isometric view of a single stage friction welding 174 assembly without a containment structure 113 illustrating in further detail the lower stage of the multiple stage friction welding 175.

The female box of the friction welding tool safety joint 176 is easy to release with anticlockwise rotation and is made up to a friction welding male pin end safety joint sub 182 as part of the friction welding connection cross over sub 181 which attaches to the shaft 99 extending below the lower assembly 115.

The hydraulic, electrical and pneumatic power system 129 positioned above and below the stabiliser base plate 122 may provide power to operate the stabiliser jacking mechanism 67 if required.

The components below the friction welding tool safety joint 176 comprise the lower fishing neck profile 183, the adjustable sized shaped friction welding head 177 with inner shaped conical profile 178, the outer adjustable sized friction welding housing with circulation channels 184 with a shaped external washover cutting profile 179 at the lower end. The high-speed rotation of the inner shaped conical profile 178 mating with the top of the solid or hollow metallised item 180 can create the high temperature required to friction weld. Extension body lengths can be attached to the outer adjustable sized friction welding housing with circulation channels 184 dependent on the length of the solid or hollow metallised item 180 to be washed over, if required.

Friction welding heat is generated by the inner conical profile rotating at a high speed with weight against the internal diameter of the circulation bore 105 of the solid or hollow metallised pipe item 80.

Figure 36 is an isometric view of a vertical or horizontal dual water turbine unit 201 which comprises as part of the equipment a multiple stage gear system 1 1 1 for clockwise rotation and a gear system 206 for anti-clockwise rotation. Each system comprising a number of single stage gear systems as described earlier in the detailed description connected in series and installed inside vertical containment structures 1 13.

Figure 37 is a plan view of the dual water turbine unit 201 shown in figure 36 with one or more grouped arrow shaped vertical or horizontal dual water turbine units 271 connected together for a larger flowing system. Any number can be grouped where each unit has unobstructed current flow 250 either river, tidal or any other water flow.

In this instance the rotational power source 8 applied to the shaft 99 at the low speed end 222 is created by the current flow 250 entering the arrow shaped debris protection mesh 202 through the venturi shaped vertical housing 203 and between the vertical bladed turbine 204 and 205 rotating against each other. The turbine shafts 212 coupled to the drive mechanisms 208 on the submerged or not lower drive mechanism base support 210 rotate the activation shafts 99 connected to the low speed end 222 of the high speed multiple stage gear system 111 for clockwise rotation and the high speed stabilised multi-functional gearing energy system 206 for anti-clockwise rotation.

As an alternative to the vertical bladed turbine 204 an anti-clockwise rotational upper horizontal bladed turbine 253 can be used and a clockwise rotational lower horizontal bladed turbine 251 used to replace vertical bladed turbine 205. In this case a venturi shaped double horizontal housing 252 would replace the venturi shaped vertical housing 203 guiding the current flow between the upper horizontal bladed turbine 253 and the lower horizontal bladed turbine 251 rotating against each other.

The rotation of the bladed turbines rotate the horizontal turbine drive shafts 254 connected to internal shafts, inside the front two fixing or piling guide conduits 211 using a bevel gear mechanism or any other means. The internal shafts are connected to the activation shafts 99 at the low speed end 222 of the high speed multiple stage gear system 111 for clockwise rotation and the high speed stabilised multi-functional gearing energy system 206 for anti-clockwise rotation.

Electrical power can be generated at the high speed end 223 by the electrical generators 207 situated on the generator base support 209 elevated above the maximum current flow level in a dry environment.

The horizontal turbine system can be used for shallow fast current flow 250 or tidal flow currents.

The three or more stabiliser pads 63 of each of the lower assemblies 115 assemblies reference Figure 1 housed in the vertical containment structures 113 can be any shape and fixed to the internal surface of the containment structures 113 by means of a matching internal profile to maintain stability and non-rotation, or welded in place or attached by any means through the outside body.

The vertical or horizontal dual water turbine unit 201 can be used where there is unobstructed current flow 250 either river, tidal estuary or any other water flow. The arrow or chevron shaped debris protection mesh 202 can be design shaped in any way to satisfy the environmental conditions and to reduce debris build up.

Each vertical or horizontal dual water turbine units 201 can be transported in separate manageable parts dependent on the means of transport, reassembled and floated to their planned location to aid access and use for remote areas.

Once at the required installation position each unit can be secured utilising four fixing and piling guide conduits 211 with the base of each vertical or horizontal dual water turbine unit 201 positioned above the fluid bed to allow access underneath or to the sides for species movement and to increase the current flow 250 through the venturi shaped vertical housing 203 or the venturi shaped double horizontal housing 252.

The four fixing and piling guide conduits 211 may contain the fluid bed fixing pin devices, for example an auger with a right hand and left hand auger flight, which can be connected to the high speed multiple stage gear system 111 for clockwise rotation or the high speed stabilised multi-functional gearing energy system 206 for anti-clockwise rotation.

The fixing pin devices can be rotated clockwise or anti-clockwise to a consolidated formation utilising the power from the anti-clockwise rotational vertical bladed water turbine 204 and the clockwise rotational vertical bladed water turbine 205 coupled using the drive mechanisms 208 to the low speed end 222 and the shaft 99.

The drive mechanisms 208 can be belt, chain driven or any mechanical rotational transmission system.

The arrow or chevron shaped debris protection mesh 202 can be selected to stop debris entering the venturi shaped vertical housing 203 or the venturi shaped double horizontal housing 252 and to deflect debris away from the arrow point but can be design shaped in any way to satisfy the environmental conditions and to reduce debris build-up.

The multiple stage gear system 111 in the containment structure 113 can create variable high speed clockwise rotation at the high speed end 223, generating electrical power from the electrical generators 207 situated on the generator base support 209 elevated above the maximum current flow level in a dry environment.

The variable high speed multiple stage gear system 206 in the containment structure 113 can convert the anti-clockwise rotation at the low speed end 222 to variable high speed clockwise rotation at the high speed end 223, creating electrical power from the electrical generators 207 situated on the generator base support 209 above the maximum current flow level in a dry environment.

Figure 38 is a plan view of a water current power generation system 213.

The water current power generation system 213 comprises and utilises the multiple stage gear system 111.

The high speed multiple stage gear system 111 consists of a number of single stage gearing systems connected in series, installed inside a horizontal containment structure 113 supported on the hydro-power base structure support frame 219 further indicated in Figure 40.

The method described for obtaining variable high speed rotation when supplying an input rotational power source 8 which may create either clockwise or anti-clockwise. In this instance the rotational power source 8 applied to the low speed end 222 shaft 99 is created by the water current flow through the venturi water collection opening 226. The three or more stabiliser pads 63 of the lower assembly 115 may be any shape and fixed to the internal surface of the horizontal containment structure 113. For example, the containment structure 113 may have a matching internal profile to maintain stability and non-rotation, or the three or more stabiliser pad blades 63 can be welded in place or attached by any means through the outside body.

The water current flows through the arrow shaped debris protection mesh 202 over the hydro- power base structure 218 and structure support frame 219 through the venturi water collection opening 226.

The electrical power generator 220 is positioned above the high-speed end 223 of the high speed multiple stage gear system 111 . The high-speed rotation pulley 224 drives the electrical power generator 220.

Figure 39 is a schematic side elevation of the embodiment shown in Figure 38 of a water current power generation system 213.

The water current flows through the arrow shaped debris protection mesh 202 over the hydro- power base structure 218 and structure support frame 219 through the venturi water collection opening 226 into the water current collection funnel 214.

The venturi water collection opening 226 increases the flow speed which is used to rotate the hydro-power turbine generator 215 and generator rotation shaft 216 connected by a drive mechanism 217 to the shaft 99 at the low speed end 222.

The drive mechanism 217 can be belt, chain driven or any mechanical rotational transmission system.

Fluid may flow through shaft 99 to cool down the internal components of the multiple stage gear system 111.

At the high speed-end 223, the high speed rotation of the shaft 99 is connected to the high speed rotation end chain drive or other mechanism 217 driving the high speed rotation pulley 224. This in turn is connected to the power generator shaft 221 of the electrical power generator 220 converting variable high speed rotations into electrical power.

The electrical power generator is positioned on a support base 225, suitably sized to place the electrical generator above the maximum expected water level.

Figure 40 is an isometric view of the device illustrated in Figures 38 and 39 where the water current power generation system 213 has been converted to a water pumping system 185. The water pumping system 185 includes and utilises the multiple stage gear system 111.

At the high speed end 223 the water pump 186 positioned on the support base 225 is powered by the high-speed rotation of the shaft 99 connected to the chain drive or other mechanism 217, driving the high-speed rotation pulley 224.

Water is sourced from the mesh protected water pump suction inlet 187 below the river water level and is pumped out via the water pump outlet 188 which can deliver water to a higher level.

The water pumping system 185 may be used to pump and store water at a higher level for example from a valley to a mountain side, to generate electrical power when required, to supply water for an irrigation system, to fill storage tanks or helicopter transportable mobile storage tanks for firefighting or to supply water for domestic or industrial purposes.

Figure 41 is a schematic side elevation of a vertical wind power electrical generation system 228 comprising a multiple stage gear system 111 consisting of a plurality of single stage gear systems as describe earlier in the detailed description connected in series, installed inside a vertical containment structure 113 encompassed and housed in a wind power vertical tower structure 230 supported on a wind power base platform 229.

In this embodiment the input power source 8 is the wind rotating the wind powered propeller blade 232.

The three or more stabiliser pads 63 of each of the lower assemblies 115 can be any shape and may be fixed to the internal surface of the vertical containment structure 113. For example, the containment structure 113 can have a matching internal profile to maintain stability and non- rotation, or the three or more stabiliser pad blades 63 can be welded in place or attached by any means through the outside body.

Any appropriate shape of stabilisers and/or stabiliser pads 63 may be used.

The wind powered propeller blade 232 can be connected to the horizontal low speed drive shaft 240 operating the gearing room structure 234 converting high torque of the generated low propeller speed to high speed rotation of the gearing room vertical drive shaft 239 supported on the gearing room base support 233 at the top end of the vertical tower structure 230.

The drive mechanism 235 which rotates the rotation shaft end housing 236 connected to the shaft 99 at the low speed end 222 converts variable low speed to variable high speed rotation at the high-speed end 223. The drive mechanism 235 can be chain driven or any mechanical rotational transmission system.

At the high-speed end 223 the shaft 99 is joined by the electrical generator drive connection 237 to the generator rotation shaft 238 generating power from the electrical generator 231.

Fluid or gas may flow through shaft 99 to cool down the internal components of the multiple stage gear system 111 .

The wind power vertical tower structure 230 may either be stand alone or included as part of a high rise building with the wind generating system on the roof of the structure. The vertical multiple stage gear system 111 may contain along the vertical containment structure 113, outlets for right angled rotational power transmission shafts 126 as explained with reference to Figure 7. The right angled rotational power transmission shafts 126 have higher rotational speeds moving from the low speed end 222 at the top of the structure to the high speed end 223 at the base of the vertical multiple stage gear system 111. The variable rotational speeds at different levels can be used to generate power in the building for lighting or any other suitable application.

The gearing room structure 234 can be smaller with reduced weight compared with conventional wind powered equipment and may increase the stability and decrease the dimensions and strengths of the wind power vertical tower structure 230.

The height of the wind power vertical tower structure 230 can be selected for steady horizontal wind power used to generate variable high speed rotation at the high speed end 223.

Figure 42 is a schematic side elevation of a vertical wind powered surface or sub-surface water pump well 241 accessing water from a subsurface aquifer reservoir 273 with a subsurface or surface pumping system 242.

The equipment items on the ground surface generating the rotational speed of the shaft 99 are the same as those described in Figure 41 with the omission of the electrical generator 231 and inclusion of a pumping system control room with chargeable battery storage 245 with power generated from the high speed multiple stage gear system 111. The input power source 8 utilised is the wind rotating the wind powered propeller blade 232. For shallower water pumping wells the input power source 8 can be by any means available such as manual in order to create high torque with low speed to the rotation shaft end housing 236 of the low speed end 222 of the shaft 99.

The drive mechanism 235 which rotates the rotation shaft end housing 236 connected to the shaft 99 at the low speed end 222 converts variable low speed high torque to variable low torque, high speed rotation at the high-speed end 223 operating the subsurface or surface pumping system 242. The drive mechanism 235 can be chain driven or any mechanical rotational transmission system.

The shaft 99 which can be hollow or solid extends downwards through the water production tubing 274 run inside the water well casing 243 protecting the drilled hole section.

The shaft 99 operates the subsurface pumping system 242 positioned in the subsurface aquifer reservoir 273 or at the surface with a surface pumping system 242 installed in a suitable water well completion.

The water well delivery output 244 with valve system can be connected via piping through the wind power base platform 229 or otherwise to the well bore water production tubing 274.

Dependent on the depth of the aquifer the vertical multiple stage gear system 111 may be considered to drill the water well when the wind power vertical tower structure 230, the wind power base platform 229 and associated equipment have been installed.

Figures 43 are schematic side elevations of ships, boats or yachts with a marine engine or wind powered propeller 189 comprising a multiple stage gear system 111 consisting of a number of single stage gear assemblies connected in series housed in a horizontal containment structure 113.

The input rotational power source 8 in Figure 43 A is generated from the marine engine 190 output rotational power attached to the shaft 99 and in Figure 43 B generated from a wind powered propeller blade 232 connected to the gearing room structure 234 supported on the wind power vertical tower structure 230.

Both methods of power source 8 can be available on a single vessel.

In Figure 43 B the rotation of the vertical drive shaft (not indicated) inside the vertical tower structure 230 is attached to a bevel gear change mechanism 247 in the hull of the ship, boat or yacht converting the vertical rotation to horizontal rotation of the shaft 99 at the low speed end 222.

Orientation of the gearing room structure 234 and the wind powered propeller blade 232 can be able to maintain accessibility to any wind direction.

The three or more stabilisers or stabiliser pads 63 of the lower assemblies 1 15 may be any design shape and may be fixed or attachable to the internal surface of the horizontal containment structure 113. For example, the containment structure 113 may have a matching internal profile to maintain stability and non-rotation, or the three or more stabilisers or stabiliser pads 63 can be welded in place or attached by any means to or through the containment structure 113. In Figure 43 A, the low speed end 222 is connected to the marine engine 190 rotational power output and in Figure 43 B the low speed end 222 is connected to the bevel gear change mechanism 247 by the shaft 99.

In both Figures 43 A and 43 B the high speed end 223 is connected to the shaft union joint 193, the propeller shaft 191 and the high speed propeller 192.

The shaft 99 connects the high speed multiple stage gear system 1 1 1 to the low speed end 222 and to the high-speed end 223.

Circulation of fluid or gas may cool the internal components of the multiple stage gear system 1 1 1 in Figures 43 A and 43 B, the gear end of the marine engine 190 in Figure 43 A and the bevel gear change mechanism 247 in Figure 43 B.

The wind powered input power source 8 can be used as a back-up for the marine engine 190.

The multiple stage gear system 111 can contain along the horizontal containment structure 113, outlets for rotational power transmission shafts 126 as explained with reference to Figure 7. The rotational power transmission shafts 126 have higher rotational speeds as the speed increases from the low speed end 222 to high speed end 223 and can be used to generate power for example, running bilge pumps or any other suitable marine equipment requirement.

Figure 44 is a vertical isometric view of a power ratchet screw driver or drill 255 with manual, electric, hydraulic or pneumatic drive utilising the multiple stage gear system 1 1 1.

The containment structure 113 with a side support handle 269 houses any number of single stage high speed gear systems connected in series, dependent on the rotational speed required at the high speed end 223.

The side support handle 269 can be included for stability and to facilitate the use of the tool. The screw driver handle 257 can be powered by hand, electric, hydraulic or pneumatic motor. A ratchet spiral 258 is attached to the screw driver handle 257 with a locking mechanism 259 to enable right only, left only or both rotations and increases the rotation at the low speed end 222.

Rotation of the low speed end 222 creates high speed at the high-speed end 223 via the housed high speed multiple stage gear system 111.

The three or more stabilisers or stabiliser pads 63 of each lower assembly 115 inside the containment structure 113 may be of any shape or design and may be fixed to the internal surface of the horizontal containment structure 113. For example, the containment structure 113 can have a matching internal profile to maintain stability and non-rotation of the three or more stabiliser arm ends or stabiliser pads 63 or the three or more stabilisers may be welded in place or attached by any means to or through the containment structure 113.

Drill bit accessories 256, for example, screw heads, milling heads, sanding heads, routers or any application requiring high speed can be installed with the fixing attachment chuck and draw 260.

Figure 45 is a vertical isometric view of a hand power drill 261 utilising the multiple stage gear system 111.

The containment structure 113 may contain any number of single stage gear systems connected in series, dependent on the rotational speed required at the high speed end 223.

The power drill main handle 267 can be shaped round for hand use or curved to suit a human shoulder or any suitable shaped profile and can be attached to the handle support body 272 with a secondary side support 268. The hand and power drill side support handle 270 can be opposite the turning handle 265 which creates the input power source 8 which can be either clockwise or anti-clockwise rotation applied to the drive wheel 264 of the upper pinion 262 and the lower pinion 263 imparting clockwise or anti-clockwise rotation of the shaft 99 at the low speed end 222.

As an alternative, the turning handle 265 connected to the multiple stage gear system 111 can be replaced with a bicycle pedal gear individually or grouped. This can convert rotational energy to electrical power from a generator connected to the fixing attachment chuck and draw 260 to create for example electricity to heat water for a health club swimming pool.

The three or more stabiliser pad blades 63 of each stage of the adjustable stabiliser power generating and control room 115 assemblies inside the containment structure 113 can be any shaped design and fixed to the internal surface of the containment structure 113. For example, the containment structure 113 can have a matching internal profile to maintain stability and non- rotation of the three or more stabiliser pad blades 63 or the three or more stabiliser pad blades 63 may be welded in place or attached by any means through the outside body.

Attached to the high-speed end 223 can be the fixing attachment chuck and draw 260 for the drill bit accessories 256, for example screw heads, drills, milling heads, sanding heads, routers or any application requiring high speed.

Figure 46 is a horizontal isometric view of a mixing system 277 utilising a multiple stage gear system 111 housed in a containment structure 113.

The containment structure 113 contains any number of single stage gear systems connected in series, dependent on the rotational speed required at the high speed end 223.

The input rotational power source 8 can be from an alternating current or direct current electrical, hydraulic, or pneumatic motor to provide rotation of the shaft 99 at the low speed end 222. In the illustrated mixing system 277, the motor power input 8 has been selected as electrical with an electrical plug 279, connected by electrical wiring 278. High torque and low speed rotation at the low speed end 222 is converted by the multiple stage gear system 111 to high speed with low torque at the high-speed end 223.

Attached to the high-speed end 223 of the shaft 99 are the female 281 and the male 282 quick union connections and shaft 284 with the mixing head 283 or any other shaped accessory.

The double handle 280 can be required to prevent any rotation of the containment structure 113 caused by re-active torque generated while mixing and can be lowered or elevated utilising the adjustable double handle slot holding 285.

The power mixing system 277 can be converted for alternative applications by attaching different shaped accessories such as a liquid pumping system utilising an auger scroll for example positioned in a casement where the outside diameter of the auger scroll is slightly smaller than the inside diameter of the casement.

Other examples can be a conversion to a portable hammer drill or a portable boat propeller with a battery supply. Figure 47 is a horizontal isometric view of a rotary handled power drill 286 with a manual front power handle 289 drive utilising the high speed multiple stage gear system 111 inside the containment structure 113.

A manual power source can be required with variable high speed achieved in order to reduce noise emissions.

The containment structure 113 with adjustable positioned side support handle 287 houses any number of single gear systems connected in series, dependent on the rotational speed required at the high speed end 223.

The manual front power handle 289 powered by hand is attached to the outer casing 57 of the first planetary gear system enabling right or left hand rotation at the low speed end 222.

Rotation of the low speed end 222 creates high speed at the high-speed end 223 via the housed multiple stage gear system 111.

The adjustable positioned side support handle 287 is required to prevent any rotation of the containment structure 113 caused by re-active torque generated and can be lowered or elevated utilising the adjustable side handle slot holding 288.

Drill bit accessories 256 such as screw heads, drills, milling heads, sanding heads, routers or any application requiring high speed can be installed utilising the male 282 and female 281 quick union connections.

Figure 48 is a cross sectional view of a well assembly 14 for a well bore oil production pumping system 296 for heavy oil or any other produced fluid. The pumping unit 306 comprises a single stage or multiple stage gear system connected to an Archimedes type screw pump 297 to pump and produce heavy waxy oil or other well bore fluids from the perforations 26 in a subsurface oil well.

The Archimedes type screw pump 297 can be made of any material to suit the pumping and fluid composition requirements.

In heavy waxy oil situations, the viscosity can be reduced by injecting steam from the surface into the circulation bore 105, through the shaft 99 and out through the perforated section 298 and into the perforations 26. After soaking for a period of time the heavy waxy oil can be lifted and pumped out through the annulus between the outer surface of the Archimedes type screw pump 297, the shaft 99 and the inner surface of the production tubing 305 exiting through the production flow line 302.

To improve production while pumping and lifting the heavy oil or other well bore fluids, steam, oil associated gas, Nitrogen, wax inhibitor, scale inhibitor or any other fluid chemical can be injected down the shaft 99 and out through the perforated section 298 or via a one way valve or other situated where required along the shaft 99 into the production stream. Produced oil associated gas can be pumped through the circulation bore 105 and commingled with the pumped oil improving production utilising gas lift. In other situations oil can be produced naturally under its own pressure upwards through the circulation bore 105 of the shaft 99 as well as being pumped and lifted with the Archimedes type screw pump 297. Each pumping unit 306 in the well schematic comprises a single stage or multiple stage gear system connected to the Archimedes type screw pump 297. Each unit can be spaced out in series along the production tubing 305 and joined together by the shaft 99 to the outer housing 57 of the circulation chamber 109 as detailed in Figure 1.

One or more pumping units 306 can be installed dependent on the well depth and the particular application to achieve a regulated pumping flow along the wellbore.

The lower assemblies 115 may have three or more stabilisers and/or stabiliser pads 63 which may be extended against the inside of the production tubing 305.

Each stage has its own independent shaft 99 which runs through the centre and is directly connected to the Archimedes type screw pump 297. The top 66 of each independent shaft 99 terminates in the outer housing 57 of the circulation chamber 109 as detailed in Figure 1 . When the shaft 99 rotates the Archimedes type screw pump 297 can rotate with increased rotation along the well bore.

At the top of each pumping unit 306 the top 66 of the shaft 99 is isolated from the outer housing 57 of the circulation chamber 109 by a shaft sealed bearing 102 seal as detailed in Figure 1.

The rotation speed increases along the wellbore form the low speed end 222 to the high speed end 223 dependent on the surface rotation of the top of the shaft 99 exiting through the production tree 301 attached to the top of the wellhead 303 on the production deck 304.

The pumping units 306 may be made up as an individual assembly with the stabiliser pads extended 63 and weld attached for example to the inside of the production tubing 305 and made up and run into the well bore when installing the well completion or can be run separately as a spaced out pumping unit assembly after the production packer 299 has been set and the production tubing 305 run.

The casing scheme may consist of a surface conductor casing 35, surface casing 31 , intermediate casing 27 and production casing 23 all cemented in place 33. The production casing 23 shoe can be cement sealed 20.

Figure 49 is an isometric view of the lower stage of the well bore oil production pumping system 296 inside the production tubing 305.

The perforated section 298 if required may be connected at the connection 308 to the lower part of the shaft 99 directly connected as the central part of the Archimedes type screw pump 297.

At the base of the lower assembly 115, the shaft 99 is isolated from the outer housing 84 by a sealed bearing assembly 300. The three or more stabiliser pad blades 63 are extended against the inside of the production tubing 305.

The independent shaft 99 of the preceding stage connects to the male or female tool connector or engagement means 86 at the low speed end 222 increasing applied rotation to the single stage gear system, to a higher rotational speed at the high speed end 223.

The circulation bore 105 can be used to inject steam, oil associated gas, Nitrogen, wax inhibitor, scale inhibitor or any other fluid chemical or as an additional production conduit.

The well bore oil production pumping system 296 indicated can be used to increase production in a conventional oil well. It can be converted to pump heavy oil through a horizontal pipeline to a port or refinery and converted to pump pigging devices through the surface production lines.

Figures 50 A and 50 B are isometric views of an electrical double or single flush mounted socket profile power drill 310 to drill square, rectangular, circle or any shaped profiles, each comprising a multiple stage gear systems 1 1 1 housed in a containment structure 113. The containment structure 113 may contain any number of single stage gear systems connected in series, dependent on the rotational speed required at the high speed end 223.

The input rotational power source 8 can be from an alternating current or direct current electrical, hydraulic, or pneumatic motor 329 or any other source of power rotation to provide rotation of the shaft 99 at the low speed end 222.

The containment structure 113 side support handle 287 can be elevated up or down along the adjustable side handle slot holding 288. The lower drill base handle 311 provides extra handling for the device.

Attached to the quick union female 281 and male 282 connections is the variable high speed drive shaft 328 connected to the central double gear cog 315 of the upper gear support plate 312.

The variable high speed drive shaft 328 with clockwise rotation, rotates clockwise the top and bottom of the central double gear cog 315 directly below on the lower gear support plate 313 and anti-clockwise the top and bottom of the double gear cogs 315 on either side of the central double gear cog 315. The eight single gear cogs 314 on their cog shafts 331 on the upper gear support plate 312 attached to the drilling bits 330 are driven by the central and double gear cogs 315 which can rotate without conflict, the inner one rotating clockwise and the outer one rotating anti-clockwise.

The bottom gear cog of the three double gear cogs 315 on the lower gear support plate 313 can rotate without conflict and drive clockwise the middle single gear cog 314 on each of the outer rows with the adjacent single gear cog 314 rotating anti-clockwise and the outer peripheral single gear cog 314 clockwise, as seen from the top of the upper gear support plate 312.

The bottom gear cog of the central double gear cog 315 on the lower gear support plate 313 can drive the inner row and rotate the inner single gear cogs 314 anti-clockwise and the outer single gear cogs 314 clockwise, as seen from the top of the upper gear support plate 312.

Drilling bits 330 or other devices can be attached to the cog shafts 331 of the total of fourteen single gear cogs 314 on the lower gear support plate 313. The central extended drilling bit 330 attached to the central double gear cog 315 shaft is longer than the others in order to drill a pilot hole and act as a fixment to the surface drilled before the other drilling bits 330 commence drilling holes.

With this arrangement, a total of twenty-five drilling bits 330 may rotate to perform the task required. Any number of drilling bits 330 can be used. The shape of the gear support plates 313 are indicated to be square but can be designed for any shape required for the application.

The components such as gear cogs may be smooth, toothed or any shape and manufactured with materials and strengths selected suitable for the application and the environmental conditions.

Figure 51 is an isometric view of a domestic or industrial air or liquid vacuum appliance 316 comprising the multiple stage gear system 111 housed in a containment structure 113. The containment structure 113 may contain any number of single stage gar systems connected in series, dependent on the rotational speed required at the high speed end 223.

The input rotational power source 8 can be from an alternating current or direct current electrical motor 321 with electrical power from the electrical storage rechargeable sealed battery 320 creating rotation of the shaft 99 at the low speed end 222. High torque and low speed rotation at the low speed end 222 can be converted by the multiple stage gear system 111 to high speed with low torque at the high-speed end 223.

Attached to the high-speed end 223 of the shaft 99 is the reduction coupling with internal vacuum mechanism 319 connected to an upper 322 and lower 323 ball joint to support the electrical storage rechargeable sealed battery 320 and provide appliance stability. The vacuum head 324 including the roller mechanism 325 connects to the lower 323 ball joint.

The device can be utilised to air or fluid vacuum with the dust, debris or fluid being vacuumed up via the hollow shaft 99 to the removable collection bag or tank 317 situated below the alternating current or direct current electrical motor 321 and the device handle 317.

The domestic or industrial air or liquid vacuum 316 appliances can vacuum with high speed rotation for improved efficiency and can operate with reduced noise emissions resulting from the high torque lower input motor speed.

The domestic or industrial air or liquid vacuum 316 can be converted and utilised as a low noise emission drier or a low noise emission air blower.

Figure 52 is an operating block diagram for a gear system programmable control system 326 which can be digital, analogue or a combination of digital and analogue. This can be used for wellbore (W) fishing, window milling, casing cutting, casing section milling, friction welding, pumping operations and any other subsurface or surface operation comprising as part of the equipment a single or any number of single stage gear systems.

The gear system wireless sender and receiver (H) for automatic operating functions can be used for a downhole application of a gear system in a well bore (W) or a surface application.

Data (X) can be transmitted downhole generated from the monitoring and computer system (M) from the programmable logic controller (A), powered from the power source (P). Data (K) from the sensors (E) can be received from the gear system in the wellbore (W) which may be used to control the gear system (H) hydraulic pumps and mechanical, electrical, hydraulic and pneumatic motors and control tools (D).

The connection between the programmable logic controller (A) and the wellbore (W) gear system wireless sender and receiver (H) is by means of the wireless communication paths (U) and (N) from the wellbore (W).

Information from the down hole sensors (E) measuring torque, temperature, pressure, equipment positions, magnetic interference, camera or any other sensor (E) signals can be transmitted from the well bore (W) via the wireless communication path (U) and (N), combined with the information recorded on the one or more multi-functional analogue or digital surface gauge such as G1 for pump pressure and G2 for surface rotation may be sent to the programmable logic controller (A). The general wireless network (T) and the wired network (C) can be connected to the programmable logic controller (A) and can provide the information received by the programmable logic controller (A) instantaneously to any location where required. Each network can be used separately or both together.

The downhole camera monitoring system (R) may record and transmit information into the programmable logic controller (A).

The programmable logic controller (A) can be operated by current and future software interfaces (B) suitable for monitoring the sensors (E) utilised in the gear system or future robotic devices.

Although the invention has been described with reference from a low to high however it is appreciated that the invention may be used to convert a high speed drive to a low speed drive, that is the invention may be used as a speed reducer.

The invention has been described by way of exemplary embodiments and example applications only, and it will be appreciated that variation may be made to the embodiments described without departing from the scope of the invention as defined by the claims.

Parts List

1 Well construction for a fishing operation

2 Well assembly

3 Near bit stabiliser

4 Well assembly

5 Heavy weight drill pipe

6 Drill bit

7 String stabiliser

8 Input rotational power source

9 Drill collars (spiral or flat profile)

10 Fishing neck

1 1 Upper end (of a fish)

12 Female end connector

15 Fishing neck sleeve

16 Tube support means

17 Fishing and milling tool

19 Fishing bottom-hole assembly

21 Open-hole section

23 Production casing

27 Intermediate casing

31 Surface casing

33 Cementing location

35 Surface conductor casing

36 Fishing and milling tool internal ring gear

37 Wellhead

39 Rig floor

40 Nozzles

41 Cellar base (of a land based drilling rig)

43 Drill pipe

44 Crossover sub

45 Upper end of the drill pipe

47 Drill string weight indicator

48 First fishing and milling casing element

49 Pump pressure gauge

50 Second fishing and milling casing element

51 Female locator profile

52 Removable hinges or other fixing mechanisms

53 Fishing fingers

54 Fishing finger support outer section

55 Wash-over sub

56 End connector

57 Circulation chamber housing

58 Lower hollow cylinder housing

59 Leadscrew gears

60 Leadscrew motors

61 Drilling rig elevator lifting recess profile

62 Stabiliser wheel

63 Stabiliser pads

64 Stop mechanism slots

65 Fishing and milling tool shaft mechanism

66 Top of shaft (99)

67 Stabiliser jacking mechanism Stabiliser antennae

New design of fishing neck engagement profile

Thread formed on inside of wash-over sub (55)

Externally threaded tube

Stabiliser housing

Gap between interdigitating portions of

Jetting nozzle

Leadscrew shaft

Lower fishing and milling tool shaft

Fishing finger sensor mechanism

(heavy duty high speed) milling structure

Female milling structure connector

Shaft seal bearing

Lower shaped sub

Outer housing

Outer magnetised plate surfaces and inward facing sensors

Tool connector (or engagement means)

Slot profile

Upper fishing and milling tool shaft

Fishing finger milling and cutting profile

Interchangeable sized locking sub

Protrusions (formed on inner surfaces of the lower parts of the fishing fingers 53) Plate

Motion sensors

Lower end of ball housing cylinder 97

Planetary gear mechanism housing

Ball housing cylinder

Fishing Finger supporting body

Shaft

Shaft end ball

Shaft bearing

Motion sensors

(Annular) shaft seal

Circulation bore

Upper end of ball housing cylinder 97

Nozzle ports in plate 93

Circulation chamber

Stop mechanism fingers

Multiple stage gearing system

Containment structure

Upper assembly

Lower assembly

Fishing and milling assembly

(illustrated) fish

Casing section milling assembly

Casing cutting and window milling assembly

Outer housing seal

Assembly isolating bearing

Stabiliser base plate

Connection (between single stage gearing systems)

Sun gear

Planet gears

Rotation transmitting shafts

Ring gear

Hydraulic tank, air tank and cooling system

Power system (optionally hydraulic, electrical and pneumatic

Motor support arm Power generating means

Central electrical, hydraulic or pneumatic control system Motor gear shaft

Junction distributors

Cable conduits

Outer housing bearing

Camera and light system

Battery

Fishing and milling tool casing end plate

(Annular) sealing seat

Rotating electrical contact

Fishing and milling casing element ring gear mechanism (Electrical hydraulic or pneumatic) motor(s)

Electrical transfer conduits

Electrical brush contacts

Gear meshes with ring gear (153 or 36)

Single stage friction welding

Multiple stage friction welding

Wind / engine powered propeller

Outer planet gear shafts

Gearing mechanisms

Inner planet gear shafts

Planetary gear set upper carrier plate

Fishing and milling tool shaft connector

Planetary gear set lower carrier plate

Low-speed end

High-speed end

Planet Gear shaft bearings

Power ratchet screw driver or drill

Hand powered drill

Claims

1 . A modular gear system (1 0) which operates in a containment structure comprises: a gear assembly (124, 125,127) which is housed in a first gear assembly housing (1 14), an input drive (222) drives the gear assembly (124,125, 127) which drives an output drive shaft (99); the gear assembly (124,1 25,127) is sealed in the first gear assembly housing (1 14); the input drive (222) is operative to be driven by an output drive (223) of a second gear assembly (124, 125,127), whereby in use the angular speed (ω1_ίΠρί11) of the input drive (222) is different from the angular speed (ω2_0ί,,_ρί„) of the output drive (223); and at least one stabiliser (63, 67) is adapted to engage with the containment structure (1 13) so as to maintain the gear system in position.

2. A gear system according to claim 1 wherein a circulation chamber defines a fluid pathway through a hollow input and/or output shaft.

3. A gear system according to claim 1 wherein gear assembly housings are connected so that the axis of the output drive of a first gear assembly is coaxial with the axis of the input drive of a second gear assembly.

4. A gear system according to any preceding claim wherein the first gear assembly housing is larger than the second gear assembly housing and an output drive of the first gear assembly housing has a larger diameter than the output drive of the second gear assembly so that when the gear assembly housings are connected together they form a composite tapered assembly.

5. A gear system according to any preceding claim wherein the gear assembly comprises a sun and planetary gear set.

6. A gear system according to claim 5 wherein a gear ring retains and stabilises the planetary gear set.

7. A gear system according to claim 5 or 6 wherein the planetary gears are configured to convert a clockwise input to a counter-clockwise output, and vice versa.

8. A gear system according to any preceding claim wherein an engagement means is provided on a gear assembly, to engage with another gear assembly housing, so as to prevent the gear assembly housings from rotating one with respect to another.

9. A gear system according to any preceding claim wherein three stabilisers are provided, the stabilisers are disposed at approximately 1 20° one to another in order to engage with the containment structure, a wellbore or a liner.

10. A gear system according to claim 9 wherein the stabilisers are hydraulically actuated to extend and retract.

1 1 . A gear system according to claim 9 or 10 wherein the stabilisers comprise stabiliser arms and pads and include a jacking mechanism.

12. A gear system according to any preceding claim includes a right or left hand thread connection for connecting to a tool with a male or female connection which derives torque from an output drive.

13. A gear system according to any of claims 2 to 12 wherein a circulation chamber housing is adapted to deliver a coolant, lubricant, steam, acid, brine or nitrogen.

14. A gear system according to any preceding claim wherein the second gear assembly housing has a reduced diameter conical input connected to the output drive of the first second gear assembly housing.

15. A system according to claim 4, or any claim dependent on claim 4, includes a bevel gear system which is rotated by the planetary gears and a transmission shaft provides a drive which is at right angles to an input shaft.

16. A system according to any preceding claim includes a cutting and/or milling tool.

17. A system according to any preceding claim has a casing with an internally threaded surface and a moveable extender has a threaded surface which engages with the internally threaded surface of the casing, an actuator causes relative rotation of the casing with respect to the moveable extender thereby extending/retracting the moveable extender.

18. A system according to claim 17 wherein the casing has first and second groups of inter- digitated engaging portions arranged to move axially, one group with respect to another.

19. A system according to claim 17 or 18 wherein movement of the casing causes a fishing tool to close as outer casing slides over sprung fingers for grabbing an item to be fished.

20. A system as claimed in any of claims 1 to 15 is connected to a union joint or an elbow joint for transmitting torque at an angle with respect to its axis of rotational symmetry.

21 . A system according to any of claims 1 to 1 5 includes a friction welding tool.

22. A system as claimed in any of claims 1 to 15 is connected to a pump and is arranged to pump fluids through lines or to pump a pigging device for cleaning lines.

23. A system as claimed in any of claims 1 to 1 5 is connected to a funnel and debris protection mesh.

24. A power tool includes the gear system according to any of claims 1 to 15.

25. A drive for a household or industrial device includes the gear system according to any of claims 1 to 15.

26. A mud motor includes the gear system according to any of claims 1 to 15.

27. An electrical generator includes the gear system according to any of claims 1 to 1 5 and a rechargeable battery.

28. An electrical generator according to claim 27 includes a rechargeable battery.

29. An engine includes the system as claimed in any of claims 1 to 15

30. A downhole fishing system includes the gear system according to any of claims 1 to 15.

31 . A downhole fishing system according to claim 30 further comprising a mechanical fishing locking mechanism with a ring gear mechanism.

32. A downhole fishing system as claimed in claim 30 or 31 includes an interchangeable sized fishing neck sacrificial wear ring with flow by areas.

33. A downhole fishing system as claimed in any of claims 30 to 32 further comprises a fishing device whose fingers are interchangeable.

34. A downhole fishing system as claimed in any of claims 30 to 33 further comprises a magnetic plate surface and sensor so that a mechanical fishing lock mechanism is capable of controlled compression of a finger mechanism around an item being fished from a well.

35. A downhole fishing system as claimed in any of claims 30 to 34 whose external cutting profile is shaped to enable wash over and removal of debris from around a fishing tool.

36. A downhole fishing system as claimed in any of claims 30 to 35 further comprising a debris protection mesh.

37. An interchangeable connection for installing accessories downhole includes the gear system according to any of claims 1 to 15.

38. An interchangeable connection for installing accessories downhole according to claim 37 further comprises a movable ball hollow housing cylinder.

39. A system as claimed in any of claims 1 to 15 includes a wireless and/or wired communications.

40. A system as claimed in any of claims 1 to 1 5 includes a robotic device.

41 . A system as claimed in any of claims 1 to 1 5 is connected to an Archimedes screw.

42. A system as claimed in any of claims 1 to 1 5 is included in a dual water turbine unit.

43. A method of operating a system as claimed in any preceding claim.

44. A system has a casing with an internally threaded surface and a moveable extender has a threaded surface which engages with the internally threaded surface of the casing, an actuator causes relative rotation of the casing with respect to the moveable extender thereby extending/retracting the moveable extender.

45. A fishing tool includes the system of claim 44.