BACKGROUND TO THE INVENTION In many mechanical devices motion is transferred between members. For example, in a transmission rotational motion is transferred from a prime mover, such as internal combustion engine, to a driven shaft.

In the case of a continuously variable transmission there are no discreet gears through which the rotational motion is transferred. Instead the ratio of the input motion to output motion may be set at any value between a maximum and minimum. In one embodiment, generally referred to as a ratcheting system, this is achieved by using a variable speed linkage to set the ratio of input motion to output motion to any value between predetermined minimum and maximum values thereby providing an infinite amount of ratios for the transmission.

Motion is typically transferred from one member to another for a predetermined portion of an engagement cycle. To ensure a smooth energy transfer a couple of these members would cooperate. Each member transfers motion for its

predetermined portion of a full cycle of 360° of rotation and overlaps with another member to ensure a smooth handover.

To limit energy losses and to ensure smooth handover during such motion transmission a ratchet system has been used to limit relative movement between the members through which the motion is transferred, which means the members need to engage each other with discrete teeth. A problem with this connecting means is that it is not possible to have infinitely random connection between members, since the members need to engage each other at precise intervals determined by the pitch of the teeth on the ratchet mechanism. This means very precise timing is required to ensure reliable functioning of the transmission and limit wear on the ratchet components, which is difficult and expensive to achieve.

OBJECT OF THE INVENTION It is an object of this invention to provide a mechanical speed variator which incorporates actuated two way gripping that at least partly overcomes the mentioned problems.

SUMMARY OF THE INVENTION In accordance with this invention there is provided a mechanical speed variator configured to transmit rotational motion from a prime mover to a driven member; the mechanical speed variator including a variable speed device, a plurality of actuated two way grippers and a driven member; the variable speed device having an input shaft rotatably connectable to a prime mover and being configured to transmit a predetermined range of rotation from the prime mover to the driven member at a transmission ratio in a predetermined transmission ratio range;

the actuated two way grippers connected to the variable speed device and being operable to sequentially grip and release the driven member over the predetermined range of rotation of each actuated gripper to rotate the driven member around a driven member axis of rotation, thereby transmitting rotational motion from the prime mover to the driven member at a transmission ratio in the transmission ratio range.

There is further provided for a grip member to be secured to the driven member, for the grip member to include a grip surface at a predetermined radial position from the driven member axis of rotation, and for the actuated grippers to operatively grip and release the grip member on the grip surface.

There is further provided for the grip member to comprise a disc having dual grip surfaces on opposing sides thereof, and for each actuated gripper to comprise a caliper gripper configured to grip both sides of the disc substantially simultaneously, alternatively for the grip member to include a set of two discs each having dual grip surfaces on opposing sides thereof, and for each actuated gripper to comprise a set of dual caliper grippers configured to substantially simultaneously each grip both sides of a disc.

According to a preferred feature of the invention there is further provided for each caliper gripper to include a frame, at least two gripping shoes with means to selectively force each gripping shoe to grip a grip surface of the disc, the frame including a base and two legs, and the legs straddling at least part of the grip surface.

There is also provided for the frame to be rotatably located in a guide associated with the disc, preferably for the legs of the frame to be rotatably or slidingly guided in a guide track located substantially concentric and parallel with the grip disc.

There is still further provided for the forcing means of the caliper gripper to comprise at least two actuation levers, an end of each lever located between a portion of the leg of the frame and one gripping shoe and each lever operable to pivot against the leg to force the gripping shoe against the grip surface.

There is still further provided for each lever to include two offset opposed pivots proximate a first end thereof, the first pivot having a complimentary pivot seat in the frame and the second pivot having a complimentary pivot seat in the gripping shoe, each lever operable to move its second end between an engaged position and a disengaged position in which movement of the second end of the lever into the engaged position pivots the gripping shoe against the disc, and movement of the second end into the disengaged position pivots the gripping shoe away from the disc, the caliper gripper including biasing means to urge the gripping shoe and the lever against the frame.

There is also provided for the lever to be operable to move the second end thereof between the engaged position and disengaged position by angular movement of the second end of the lever, for the second ends of both levers to be connected by two links pivotally connected to each other by means of a pin, and for radial movement of the connecting pin between a first and a second position to move the second ends of the lever between the engaged and disengaged position.

According to an alternative feature of the invention there is also provided for each lever to comprise two substantially parallel arms connected at their first ends by an elongate pivot member, the pivot member including two offset opposed pivot faces complimentary shaped and configured to elongate pivot seats in the leg of the frame and the gripping shoe, and for each gripping shoe to be located between the arms of the lever associated with it.

According to a further feature of the invention there is provided for the mechanical speed variator to include a substantially stationary cam profile plate located around the driven member axis of rotation, for the cam profile plate to include a profiled track, for each actuated gripper to include a gripping action cam follower and releasing action cam follower ; for the gripping action cam follower to be configured upon activation by the cam profile to radially move the connecting pin from the first to the second position thereby moving the second ends of the levers from the disengaged to the engaged position, and for the releasing action cam follower to be configured to radially move upon activation by the cam profile the connecting pin from the second to the first position, thereby moving the second ends of the levers from the engaged to the disengaged position.

According to a still further feature of the invention there is provided for the variable speed device to include means to adjust the axis of rotation of the input shaft between a first position and a second position on a plane of adjustment, and wherein adjustment of the input shaft axis of rotation between the first and second positions changes the transmission ratio in the predetermined transmission ratio range.

There is further provided for the input shaft of the variable speed device to be connectable to the prime mover by means of two universal joint coupling, alternatively a gear train, configured to accommodate adjustment of the axial position of the input shaft axis of rotation on the plane of adjustment and for the means to adjust the axial position of the input shaft axis of rotation to comprise jacking of the input shaft, alternatively jacking of the axis of rotation of a gear from the gear train.

There is still further provided for the variable speed device to include a slideway disc secured to the input shaft, for the disc to include a plurality of radial sideways, preferably at least six radial slideways ; for a slider to be slidingly

located in each slideway and for the slider to be rotatably secured to at least one actuated gripper, preferably a caliper gripper.

There is further provided for a plurality of wedge plates to be secured to the slideway disc, for a wedge plate to be located between adjacent sideways, for each slider to be slidingly located between a set of linear bearings, and for each wedge plate to include a raceway for each linear bearing.

According to a preferred embodiment of the invention the slider comprises a slider drive pin extending through the slideway in the slideway disc, for a set of two wedge plates to be secured to the slideway disc on opposing sides thereof, each wedge plate having two raceways with linear bearings of slides adjacent to it, for each slideway to have two wedge plates associated with it on either side of the slideway disc, and for each slider to be slidingly located between four linear bearings located in the raceways of the four wedge plates associated with its respective slideway.

There is still further provided for the preload on a linear bearing to be adjustable by adjustment of the radial position of the wedge plates associated with the linear bearing.

There is further provided for the plane of adjustment to include a point of coincidence at which the variable speed device axis of rotation is coaxial with the driven member axis of rotation, and for substantially synchronous rotation to be transmitted from the prime mover to the driven member when the input shaft axis of rotation is located on the point of coincidence.

There is further provided for the point of coincidence to be located intermediate the first and second positions, for movement of the axis of rotation of the input shaft towards the first position to decrease the transmitted speed of rotation, and

for movement of the movement of the axis of rotation of the input shaft towards the second position to increase the transmitted speed of rotation.

There is still further provided for the mean speed of rotation of each actuated gripper over the predetermined range of rotation to be transmitted to the driven member by means of the actuated gripping of the driven member by the actuated gripper, and for the driven member to be driven substantially continuously by the sequential actuated gripping by the plurality of actuated grippers.

There is still further provided the predetermined range of rotation of each actuated gripper to have at least some overlap with the actuated gripper adjacent to it, thereby providing uninterrupted transmission to the driven member.

According to a further and preferred feature of the invention there is provided for the mechanical speed variator to be incorporated into a stepshift or a synchronous shift or a parallel path epicyclic geartrain or geartrains to provide a continuously variable transmission over an expanded variable speed range.

BRIEF DESCRIPTION OF THE DRAWINGS Embodiments of the invention are described below by way of example and with reference to the accompanying drawings in which: Figures 1 A to 1 C are schematic representations of the mechanical speed variator including Prime Mover, Hooke's Coupling, input shaft, radial slideway plate and output carriages, Figures 2A and 2B are schematic representations of the input shaft, radial slideway plate, slider drive pin, adjustable wedge plates and linear slideway bearings.

Figure 3 is a schematic representation of the slider drive pin, stub axles and actuated gripper mechanisms Figures 4A and 4B are schematic representations of the output drum, output gripper discs, cam plate, cam profile trackway, cam lifters, cam pivot shaft, cam followers, radial arm and input shaft.

Figure 5 is a partial schematic representation of the actuated gripper mechanism caliper gripping device, the circular trackway, the track rollers, the output disc located about the axis of rotation.

Figure 6 is a more detailed schematic representation of the output disc and trackway with the caliper frame in position.

Figure 7 is a further partial schematic representation of the actuator arms, the gripping shoes, the radial offset arrangement and the caliper frame about the output disc.

Figures 8A and 8B are partial schematic representations of the gripping shoe applied and resulting forces acting upon the output disc.

Figures 9A and 9B are partial schematic representations of the two side arms comprising each actuation lever and the forces applied.

Figures 10A and 10B are partial schematic representations of the half scissor linkage arranged to simultaneously operate the two actuation levers and the cam lifter and follower arrangement employed to timeously actuate the gripping shoes.

Figure 11 is a partial schematic representation of the gripping shoes and the vacuum releasing grooves incorporated into the gripping surfaces.

DETAILED DESCRIPTION OF THE INVENTION With reference to Figure 1, an embodiment of the mechanical speed variator which is configured to transmit rotational motion from a prime mover to a driven member is shown.

In the Figures 1A to 1C the mechanical speed variator is generally indicated by numeral (200). The prime mover (1) may include any internal combustion engine, gas turbine, rotary jet engine, wind turbine, water turbine or electric motor arranged to drive input shaft (2) by means of a variable position compensation coupling arrangement such as a Hooke's coupling (3G) or a suitably arranged swing arm gear train (not shown).

Hooke's coupling (3G) comprises first universal joint coupling (8) mounted on output shaft (1A) of prime mover (1) and suitably arranged to transmit power and torque to and from first end (9A) of intermediate shaft (9); universal joint coupling (10) is mounted to second end (9B) of intermediate shaft (9) and suitably arranged to transmit power and torque to and from input shaft (2); splined coupling (2S) is suitably arranged within intermediate shaft (9) to accommodate any change in length within predetermined limits of intermediate shaft (9) that may be required during operation.

Input shaft (2) is suitably arranged to be rotatable in bearings (2A, 2B) and rigidly connected to rotatable input radial slideway plate (22) which is rotatable thereby; input shaft (2) axis of rotation (13) is adjustable (by means not shown) to any position (13A) along suitably arranged plain of adjustment (14) that includes point of concentricity (23) with common axis of rotation (24) of output carriages (25);

axis of rotation (24) is also concentric with axis of rotation (24) of output drum assembly (26).

With reference to Figures 2A and 2B, six radial sideways (28) are suitably incorporated into radial slideway plate (22) and arrayed symmetrically about input shaft (2) axis of rotation (13). Each radial slideway (28) incorporates slider drive pin (29) suitably arranged to be radially slidable in its respective slideway (28) by means of linear bearings (30) a first pair (30A, 30B) of which are arranged symmetrically about each radial slideway plate (22) radial slideway (28) to cater for torque loading in a first rotational direction (31) and a second pair (30C, 30D) similarly arranged to cater for torque loading in a second rotational direction (32).

Radial slideway plate (22) is suitably arranged to incorporate attachable wedge plates (33), of which only two are shown for the sake of clarity, adjacent to each radial slideway (28) suitably arranged such that the raceway (34) of each linear bearing (30A, 30B, 30C, 30D) is mounted onto or incorporated into each adjustable wedge plate (33) (by conventional means not shown). Each adjustable wedge plate (33) is arranged to facilitate reloading of each linear bearing (30A, 30B, 30C, 30D) through adjustment of the radial position (35) of each adjustable wedge plate (33) by means of suitably arranged radial screw jack (not shown) or similar arrangement incorporated into radial sideway plate (22).

With reference to Figure 3, each slider drive pin (29) incorporates four linear bearings (30A, 30B, 30C, 30D) arranged to slide as described above; each slider drive pin (29) incorporates stub axle (38) at first end (29A) and stub axle (39) at second end (29B). One actuated gripper mechanism (100) output carriage assembly (25) is pivotally mounted upon each stub axle (38,39) of drive pin (29).

The actuated gripper (100) is only shown diagrammatically in Figure 3, but the precise functioning of the actuated gripping mechanism (100) is described below.

With reference to Figures 4A and 4B, each pair of actuated gripping mechanisms (100) mounted upon each stub axle (38,39) of each drive pin (29) is arranged to timeously and substantially simultaneously grip and release two output discs (50,51). First actuated gripping mechanism (100a) is suitably arranged to grip and release output disc (50) and second actuated gripper mechanism (100b) is suitably arranged to grip and release output disc (51). Each output disc (50,51) is suitably mounted within output drum assembly (26) and arranged to rotate concentrically about axis of rotation (24) together with drum (26). The axis of rotation (24) is suitably arranged to be parallel with axis of rotation (13) of the radial slideway plate (22) and to include a position of concentricity (23) with radial slideway plate (22) axis of rotation (13) as described above.

Timeous gripping action of each pair of actuated gripping mechanisms (100a, 100b) is achieved by means of stationary cam profile plate (52) suitably arranged about output drum (26) axis of rotation (24). The cam profile plate (52) is suitably arranged to incorporate slot profiled trackway (53) arranged to suitably actuate gripping action cam follower roller (54) and releasing action cam follower roller (55) through suitable rotation of first actuated gripper mechanism (100A) output carriage (25A) rotated together with second actuated gripper mechanism (100B) output carriage (25B) by slider drive pin (29) rotated about axis (24) through rotation of radial slideway plate (22) by prime mover (1).

Radial arm (56) is suitably arranged to pivot cam lifter (57A, 57B) pivot shaft (58) suitably arranged to pivot within first output carriage (25A) and second output carriage (25B); cam lifter (57A, 57B) pivot shaft (58) is arranged to timeously actuate cam lifter (57A) arranged within actuated gripping mechanism (100A) and cam lifter (57B) arranged within actuated gripping mechanism (100B) upon suitably arranged cam follower (54,55) motion imparted by stationary cam profile plate (52) slot profiled trackway (53) as each pair of output carriages (25A, 25B) is rotated about common output carriage (25A, 25B) axis of rotation (24) around circular trackway (26T) suitably arranged concentrically within output drum (26).

With reference to Figures 1B, 1C, 4A and 4B, adjustment of radial slideway plate (22) axis of rotation (13) position (13A) along adjustment plane (14) enables mean speed of rotation (25m) of each pair of output carriages (25A, 25B) about axis of rotation (24) to be selected over gripping range angle (70) by timeous sequential actuation of each pair of actuated gripper mechanisms (100A, 100B) through the suitably arranged action of stationary cam profile (52). Mean speed of rotation (25M) of each pair of actuated gripper mechanisms (100A, 100B) in sequence is thereby imparted to output drum (26) through output discs (50,51).

With reference to Figure 1B, gripping range angle (70) is suitably arranged to ensure simultaneous gripping by each successive pair of actuated gripper mechanisms (100A, 100B) for a small limited overlapping angle of rotation (70A) about axis (24); continuous uninterrupted torque transmission is thereby achieved at all actuated gripper mechanism torque transfer activities.

With reference to Figures 1B, 4A and 4B, gripping range angle (70) is suitably arranged to be variable over some predetermined range by suitable adjustment of circumferential position of stationary cam profile plate (52) lift and lower ramp profiles (71,72) about output drum (26) axis of rotation (24) by means not shown; adjustment of gripping range angle (70) is suitably arranged to be synchronous with and proportional to adjustment position of radial slideway plate (22) axis of rotation (13) along adjustment plane (14).

With reference to Figure 4A, output drum (26) is arranged to be rotatable about bearings (26A, 26B). Bearing (26B) at first end (26E) of output drum (26) is arranged to provide suitable radial internal clearance within inner race journal to facilitate operation of actuating cam mechanism (54,55, 56,57, 58) by stationary cam profile Plate (52) slot trackway profile (53). Bearing (26a) at second end (26F) of output drum (26) is similarly suitably arranged to accommodate planar positional adjustment of radial slideway plate (22) input shaft (2) axis of rotation (13) along adjustment plane (14).

The arrangement thus described results in an infinitely adjustable speed of rotation to be imparted to output drum (26) within predetermined limits by actuated gripping mechanisms (100) from any constant speed of rotation prime mover (1) by adjustment of input shaft (2) axis of rotation (13) position along plane of adjustment (14) Output drum (26) is suitably arranged to incorporate access holes (26H) through its shell to facilitate access to actuated gripping mechanism (100) gripper adjustment screws (not shown), and output drum (26) is suitably arranged to incorporate output flange (26G) for mounting of output gear or similar output arrangement (not shown).

With reference to Figure 5, output carriage (25) caliper frame (25) is suitably rotatably mounted about circular trackway (26t) by means of two pairs of track rollers (3A, 3B); caliper frame (25) motion is suitably arranged by means described above to rotate about axis of rotation (24); as described above caliper frame (25) is arranged to rotate over predetermined gripping range angle (70) about axis of rotation (24) at a substantially constant but adjustable rotational velocity.

With reference to Figures 5 and 6, caliper frame (25) is suitably arranged to be mounted concentrically about faces (4,5) of each output disc (50,51). Each output disc (50,51) is suitably arranged integral with output drum (26) circular trackway (26T) concentrically rotationally mounted about axis of rotation (24) as described above; caliper frame (25) incorporates two opposing pivot seats (9,10) one at each side (4,5) of output disc (50,51) ; With reference to Figure 7, two actuation levers (11,12) are suitably arranged with first actuation lever (11) on first side (4) of output disc (50,51) and second actuation lever (12) at second side (5) of output disc (50,51). Each actuation lever (11,12) is arranged to pivot over a suitably small rotational sweep angle

(13) about it's appropriate caliper frame (25) pivot seat (9,10) by means of a suitably arranged mating pivot seat (16,17) incorporated into actuation levers (11,12). Each actuation lever (11,12) incorporates a further rotational pivot (18,19) suitably arranged at some predetermined radial offset dimension (20) to pivotally mate with gripping shoes (21,22) through mating pivot seats (21A, 22A).

Each gripping shoe (21,22) is arranged to contact output disc (50,51) on opposing sides (4,5) of the output disc (50,51) upon suitable simultaneous opposing pivotal action of actuation levers (11,12).

With reference to Figures 8A and 8B, gripping force (23) applied by means of actuation levers (11,12) causes gripping shoes (21,22) to grip output disc (50,51) producing a resulting predetermined circumferential force (23C). Force (23C) is suitably arranged to enable torque transmission from caliper frame (25) to output disc (50,51) through frictional contact of gripping shoes (21,22) utilising the prevailing coefficient of friction without slippage.

With reference to Figures 9A and 9B, actuation lever (11) incorporates two side arms (27A, 28A) and actuation lever (12) (not shown) incorporates two side arms (27B, 28B); side arms (27A, 28A, 27B, 28B) are arranged to protrude radially inwards substantially towards axis of rotation (24) of output disc (50,51) at each side (21A, 21B, 22A, 22B) of each gripping shoe (21,22).

Gripping shoe (21) acted upon by actuation lever (11) is circumferentially mechanically and rotationally located between suitably arranged location faces (25A, 26A) incorporated into actuation lever arm (11) side arms (27A, 28A).

Actuation lever (12) (not shown) is similarly arranged to circumferentially mechanically and rotationally locate gripping shoe (22) between suitably arranged location faces (not shown) incorporated into actuation arm (12) side arms (27B, 28B);

Caliper frame (25) is similarly circumferentially mechanically and rotationally located against side location faces (25A, 26A) of actuation lever (11) and actuation lever (12).

The assembly is suitably arranged so that torque applied to caliper frame (25) in either rotational direction about axis of rotation (24) by means described above is transmitted, in the gripping position, through applied frictional contact between caliper frame (25), pivot seats (9,10, 16,17, 18, 19, 21a, 22a) gripping shoes (21,22) and output disc (50,51) simultaneously to each side (4,5) of output disc (50,51).

In the non gripping position all components are mechanically located with respect to each other by suitably arranged clearance fit of side arms (27A, 28A, 27B, 28B), and gripping shoes (21,22) are biased towards pivot seats (18,19) by means of a spring (not shown) located around each gripping shoe (21,22) and secured to caliper frame (25).

Inner ends (31A, 31 B) of actuation lever (11) arms (27A, 28A) are suitably arranged to be at dimension (20A) suitably arranged to be some multiple of radial offset dimension (20) such that force (33) applied at inner ends (31 a, 31 b) is proportionately reduced from force (23) required to cause gripping shoes (21,22) to grip output disc (50,51) without slippage. Actuation lever (12) is similarly suitably arranged to provide opposing action that results in shoe (22) gripping output disc (50,51) on side (5) in gripping opposition to shoe (21) gripping output disc (50,51) on side (4).

Caliper frame (25) is suitably arranged to float axially parallel to axis of rotation (24) in order to become centralised about output disc (50,51) under opposing action of gripping shoes (21,22) by means of free floating location through drive pin (29) pivotal connection hole (24H).

With reference to Figures 10A and 10B, inner end (31A) of actuation lever (11) side arm (27A) is arranged by means of half scissor linkage (34A) to be

mechanically coupled to inner end (32A) of opposing actuation lever (12) side arm (27B). Similarly, but not shown in Figures 10A and 10B, inner end (31 B) of actuation lever (12) side arm (28B) is suitably arranged by means of half scissor link (34B) to be mechanically coupled to inner end (32B) of opposing actuation lever (12) side arm (28B).

Simultaneous adjustment of the radial position (37) of scissor linkage (34A) knee joint pivot pin (41A) and half scissor linkage (34B) (not shown) knee joint pivot pin (41B) (not shown) causes both opposing gripping shoes (21,22) one on each side (4,5) of output disc (50,51) to grip output disc (50,51) with a suitable contact force (23) amounting to some predetermined multiple of radial force (40) applied at scissor linkages (34A, 34B) knee joints pivot pins (41A, 41 B).

Pivot pins (41A, 41B) are simultaneously acted upon by actuator slider (42) arranged to radially slide upon caliper frame (25) under action of suitably arranged cam lifter (57A, 57B). Cam lifter (57A, 57B) is suitably arranged to partially rotate within caliper frame (25) upon the action of suitably arranged cam follower (54,55) arranged as either a trailing (45) or a leading (56A) arm (56).

Cam follower (54,55) arm (56) is suitably arranged to be acted upon by suitably arranged cam profile (53) as described above. Cam profile (53) is suitably arranged to timeously exert actuation force (49) upon cam follower (54,55) causing gripping shoes (21,22) to grip output disc (50,51) when caliper frame (25) is rotated about axis of rotation (24) to the commencement of gripping range angle (70) and to release output disc (50,51) upon completion of gripping range angle (70).

With reference to Figure 11, gripping shoes (21,22) are suitably arranged to incorporate vacuum grooves (21B, 22B) arranged upon gripping shoe (21,22) gripping surfaces (21A, 22A) in such manner as to release any vacuum formed between gripping surfaces (21A, 22A) and output disc (50,51) upon removal of gripping force (49) applied by cam profile (53).

Cam profile (53) may be arranged to be stationary or rotatable about axis (24) independently of caliper frame (25) and output disc (50,51) by means not shown.

With reference to Figures 10A and 10B, the mechanical advantage resulting from the arrangement of the length ratio of cam follower (54,55) trailing (56) or leading (56A) Arm effective length (56B) to cam lifter (57) effective lift (57A), the working angular range (69) of the two simultaneously acting scissor linkages (34A, 34B) acted upon by actuator slider (42) acted upon by cam lifter (57) and the mechanical advantage of the length ratio of actuation levers (11,12) inner ends (31,32) length (71) to gripping shoe (21,22) pivot (18,19) radial offset dimension (20) are suitably combined to provide a suitable mechanical ratio that enables a relatively small cam profile (53) gripping force (49) to result in a large gripping shoe (21,22) reactive gripping force (23); gripping force (23) is thereby suitably generated to the required value for adequate torque transmission in a lubricated steel upon steel arrangement or a friction lining arrangement or any other friction contact surface and material arrangement between output disc (50,51) and gripping shoes (21,22).

The entire mechanism (200) as described is enclosed within suitably arranged casing (60). Casing (60) is suitably arranged to fully enclose Hooke's coupling (3G) and accommodate input shaft (2) adjustment position along adjustment plane (14), rotatable radial slideway plate (22), slider drive pins (29), actuated grippers (100), output discs (50,51), output drum assembly (26) and all components described within this device and to support outer or inner races of output drum (26) rotary bearings (26A, 26B) as appropriate. Casing assembly (60) is suitably arranged to contain a suitable volume of lubricating oil (not shown) without spillage when either standing or operating at any selected speed. Casing assembly (60) is further arranged to suitably attach to prime mover (1) or suitably arranged base plate by a suitable flange or foot mounting arrangement.

A suitable recirculation pump and filter system for the lubricating oil contained within the casing is also incorporated in order to filter and clean the oil as required. In addition suitable arrangements incorporating lifter plates and profiles (not shown) are incorporated into the radial slideway plate in order to ensure that lubricating oil residing in the casing sump is distributed to all areas within the casing (60) upon rotation of input radial slideway plate (22) by prime mover (1).

It will be appreciated that the invention is not limited to the above described embodiments thereof. It is possible to alter aspects of the described embodiments without departing from the scope of the invention.

It is for example possible to use a radial slideway plate with less or more than six radial slots with a complimentary number of radial sliders, wedge plates, and actuated grippers.