SHAFT PHASE CONTROL MECHANISM

Abstract: The phase control mechanism includes first gears (3, 4) coupled to the output shafts which are to be phase controlled. A transfer gear (5) is provided for rotation or operation independent of the input and is coupled to the first gears (3, 4) to allow rotary motion to be transferred between the first gear members and a phase adjuster (10) causes the first gears (3, 4) to advance on regress relative to one another to change the phase relationship between the outputs.

Description: SHAFTPHASECONTROLMECHANISM This invention relates to a phase control mechanism for controlling a predetermined phase relationship of at least one output. Many situations exist in industry and transport where it is necessary to be able to alter the phase relationship between concentric rotating shafts, parallel shafts or other similar elements while they are in motion and under load. Examples of this need, include the control of the pitch of propellers of aircraft and boats, particularly ships; controlling the pitch of power producing windmills; opening and closing lathe and drill chucks while they are in motion during production runs; controlling the eccentricity of some forms of continuously variable transmissions and determining the valve timing of cam shafts in internal combustion engines. Operations of the type mentioned above is usually achieved by using electric devices or sliding mechanical mechanisms. These mechanisms all have difficulty with high levels of torςrue, and in general, with reliability. A need therefore exists for a mechanical rotating mechanism which is able to alter the phase relationship between two or more concentric or parallel shafts while they are in motion and under load. The invention may be said to reside in a phase control mechanism including: an input for supplying input rotary power; a plurality of outputs each for providing output rotary power; a plurality of first gear members each coupled to a corresponding output of the plurality of outputs; drive means for transmitting rotary power from the input to the outputs so that when the input iβ driven, power is supplied to the outputs for driving the outputs; a phase adjusting means for causing the first gear members to advance or regress relative to one another; and means for actuating the phase adjusting means to thereby cause the first gear members to advance or regress relative to one another to change the phase relationship between the outputs. Thus, in order to change the phase relationship between the outputs the actuating means is moved to adjust the position of the adjusting means which in turn causes the first gear members to regress or advance relative to each other to change the phase relationship between the outputs. The phase between the outputs can therefore be adjusted to not only supply rotary power from the input to the outputs but also to alter the position of a device or article coupled on the outputs relative to one another. The phase relationship can be changed with the mechanism operating (that is supplying rotary power) or with the mechanism stationary. It is not necessary to stop the mechanism to change the phase relationship and therefore the phase relationship of the input and output can then be adjusted during operation as required. In one embodiment of the invention the input is integral with a first of the output shafts and a second of the output shafts is mounted concentrically on the first output shaft, the drive means comprises: in respect of the first output, the integral coupling of that output to the input, and in respect of the second output comprises; (a) a fixed spur gear having a first set of teeth which mesh with teeth of the first gear member on the first output, the fixed spur gear having a second set of teeth which mesh with teeth on an idler gear rotatable relative to the outputs; a second spur gear which has a first set of teeth meshing with the idler gear and a second set of teeth meshing with the first gear member coupled to the second outpu ; and wherein said second spur gear is mounted in a yoke pivotal relative to the outputs and wherein the second spur gear forms said phase adjusting means and the yoke forms said actuating means so that when the yoke is pivoted relative to the input and output, the second spur gear is driven around the first gear on the second output and the idler gear to cause the first gear on the second output to regress or advance relative to the first gear on the first output to alter the phase relationship between the input and output. In a second embodiment of the invention, the input has a cage which supports at least one pinion gear, the pinion gear engaging a first bevel gear mounted on first output and a second bevel gear mounted on a second output; wherein said pinion gear and said first and second bevel gears form said drive means; said first gear member coupled to the first output being arranged on said cage and being coupled to the first output by the cage, the pinion gear and the first bevel gear, the first gear member on the cage engaging a first set of teeth of a fixed spur gear, the fixed spur gear having a second set of teeth for engaging an idler gear rotatable relative to the outputs, a second spur gear mounted in a yoke pivotable relative to the outputs, the second spur gear having a first set of teeth engaging said idler gear and a second set of teeth engaging said first gear member coupled to the second shaft; and wherein said second spur gear forms the phase adjusting means and wherein the yoke forms the actuating means so that upon pivoting movement of the yoke, the second spur gear is rotated around the idler gear and the first gear member on the second output to thereby cause the second gear member on the second output and the second bevel gear to advance or regress relative to the first gear member on the cage and the first bevel gear on the first output to thereby alter the phase relationship between the outputs. In the second embodiment of the invention, the bevel gears and pinion gears, together with the intermediate shaft, take up a reaction caused by torque in the system rather than having the reaction applied against the moveable yoke. Further, the bevel gears also distribute the torque equally between the output shafts. Furtherstill, these arrangements cause both shafts to be counter-rotated equally during the phase change operation. In a third embodiment of the invention, the drive means comprises a cage coupled to the input which carries at least one planet shaft, the planet shaft carrying a first planet gear which meshes with the first gear fixed to the first output, the planet shaft also carrying a second planet gear which meshes with the first gear mounted on the second output; a first orbit gear arranged for rotation relative to the outputs and meshing with the first planet gear and a second orbit gear arranged for rotation relative to the outputs and engaging the øeconc planet gear, one of the first or second orbit gears be: \g fixed and the other of the first or second orbit gears being moveable relative to the said one of the orbit gears; wherein the phase adjusting means comprises the moveable orbit gear which, upon rotation relative to the fixed orbit gear, causes the first gear fixed to the first output to advance or regress relative to the first gear fixed to the second output to in turn cause the phase relationship between the outputs to change; and wherein the actuating means comprises a handle on the moveable orbit gear for moving the moveable orbit gear relative to the fixed orbit gear. In a fourth embodiment of the invention, a first of the output shafts includes a first cage and a second of the output shafts includes a concentric second cage: the plurality of first gear members comprising a plurality of first bevel gears and a plurality of second bevel gears; the first plurality of bevel gears being mounted on the first cage, and the second plurality of bevel gears being mounted on the second cage; the input having a first bevel gear for engaging the first plurality of bevel gears on the first cage for driving the first cage to in turn rotate the first output shaft; the input having a second bevel gear for engaging the second plurality of bevel gears on the second cage for rotating the second cage to in turn rotate the second output shaft; the drive means comprising the first and second bevel gears of the input and the first and second plurality of bevel gears mounted on the first cage and the second cage. In the fourth embodiment of the invention, the phase adjusting means comprises at least one control rod having a bevel gear thereon for engaging the first plurality of bevel gears or the second plurality of bevel gears so that upon rotation of the control rod, the bevel gear on the control rod is rotated to causes the first plurality of bevel gears to advance or regress relative to the second plurality of bevel gears to thereby change the phase relationship between the first and second output shafts. Preferably the means for actuating the phase adjusting means comprises a bevel gear mounted on the control rod and a motor for driving the bevel gear on the control rod to in turn rotate the control rod. Preferably first and second control rods are included each carrying first and second bevel gears for engaging respectively the first plurality of bevel gears on the inner cage and the second plurality of bevel gears on the outer cage and preferably first and second motors and first and second bevel gear arrangements are arranged for rotating the first and second control rods to cause the first plurality of bevel gears on the inner cage to advance or regress relative to the second plurality of bevel gears on the outer cage to thereby change the phase relationship between the first and second output shafts. The invention in a further aspect may be said to reside in a phase control mechanism, including: an input for supplying input rotary power; a plurality of outputs, each for providing output rotary power; a plurality of first gear members each coupled to a corresponding output of the plurality of outputs; drive means for transmitting rotary power from the inputs to the outputs so that when the input is driven, power is supplied to the outputs for driving the outputs; a transfer gear for rotation or operation independently of the input, the transfer gear being meaningly coupled to the first gear members for allowing rotary motion to be transferred between the first gear members; and phase adjusting means for causing the first gear members to advance or regress relative to one another to change the phase relationship between the outputs. In some embodiments of the invention, the transfer gear may form part of the drive means and be one of the gears in the drive means for transmitting rotary power from the input to the outputs. In other embodiments, the transfer gear may be separate from the drive means and not directly be involved in transmitting drive from the input to the outputs. Preferably the transfer gear is meshingly coupled with the first gear members by being enmeshed with ancillary gears fixedly attached to the first gear members. Preferably the transfer gear is mounted on the input. Preferred embodiments of the invention will be described, by way of example, with reference to the accompanying drawings in which: Figure 1 is a view of a phase control mechanism according to a first embodiment of the invention; Figure 2 iβ a view of a phase control mechanism according to a second embodiment of the invention; Figure 3 is a view of a phase control mechanism according to a third embodiment of the invention; and Figure 4 is a view of a phase control mechanism according to a fourth embodiment of the invention; With reference to Figure 1, an input shaft 1 carries an integral first output shaft la which is provided with a concentric second output shaft 2 which are both supported in a suitable casing (such as casing 7 which is only partly shown in Figure 1) . The input shaft 1 and output shaft 2 can rotate freely relative to one another and thus the output shafts la and 2 rotate freely relative to one another. The output shaft la is provided with a first gear 3 which may be integral with the output shaft la or mounted on the shaft la for rotation with the shaft la. The output shaft 2 is also provided with a first gear 4 which may be integral with the output shaft 2 or fixed to the output shaft 2 for rotation with the output shaft 2. The casing 7 supports a fixed lay shaft 6 upon which is rotatably mounted a fixed spur cluster 8. The fixed spur cluster 8 has a first set of teeth 8a which mesh with teeth on the gear 3 and a second set of teeth 8b which mesh with a transfer gear 5 which is mounted on the shafts la and 2 for rotation relative to the shafts la and 2. A yoke 10 is rotatably mounted on the shafts la and 2 for pivoting movement about the shafts la and 2. The yoke 10 supports a lay shaft 11 upon which is mounted a spur cluster 9. The cluster 9 has a first set of teeth 9a which engage teeth on the gear 4 and a second set of teeth 9b which engage the transfer gear 5. A predetermined ratio exists between the teeth 9a and 9b, the purpose of which will be described in more detail hereinafter. Drive is transmitted from the input shaft 1 to rotate the shaft la by virtue of the integral nature of shafts 1 and la. Rotation of shaft la rotateβ the gear 3. Rotation of the gear 3 drives the spur cluster 8 which in turn rotates the transfer gear 5. The transfer gear 5 therefore rotates the spur cluster 9 which in turn rotates the gear 4 and the output shaft 2. Thus, drive is transmitted from the input shaft 1 to the output shaft 2. If the yoke 10 is held in one position and the input shaft 1 rotated, drive is therefore transmitted to the output shafts la and 2 as described above so that the output shaft la and output shaft 2 rotate in unison. To alter the phase relationship between the output shaft la and output shaft 2, the yoke 10 is pivoted about the shafts la and 2. Thus, if the yoke 10 is now rotated through some arc, the spur gear 9 and lay shaft 11 are moved with the yoke 10 about the shaftβ la and 2 and tranβfer gear 5 and gear . Movement of the spur gear 9 against the transfer gear 5 will cause the gear 4 to advance or regress its rotation in relation to the gear 3. This will therefore alter the phase relationship between the gear 3 and the gear 4 and therefore between the output shaft la and the output shaft 2. This action occurs both with the shafts rotating or stationary. Thus, in order to change the phase relationship between the output shaft la and output shaft 2, it is not necessary to stop a machine to which the mechanism is connected and the phase relationship between the shafts can be adjusted or changed simply by pivoting the yoke 10 about the shafts 1 and 2. The yoke 10 may be manually pivoted or depending on the environment in which the mechanism is used, pivoted or fully rotated by a suitable actuating mechanism (not shown) . The transfer gear 5 forms a transfer gear which, as explained above, meshes with the gears 8 and 9 which in turn mesh with the first gears 3 and 4 attached to the output shafts la and 2. The transfer gear is mounted on the input but iβ able to rotate or otherwise operate independently of the input and allows rotary motion to be transferred between the gears 3 and 4. In the embodiment of Figure 1, the torque of the system will cause a reaction in the moveable yoke 10 which, in some environments, may make it difficult or uncomfortable to move the yoke 10. Figure 2 showβ a second embodiment of the invention in which this problem is overcome. In Figure 2, similar reference numerals indicate similar parts to those described with reference to Figure 1. In this embodiment of the invention the input βhaft 1 carries a pinion cage 15. The pinion cage 15 carries the first gear 3 which meshes with the teeth 8a of fixed spur 8. The cage 15 carries a pair of shaftβ 15a upon which right angled pinion gears 14 are mounted. Gear 4 which is coupled to second output shaft 2 carries a bevelled gear 12 which meshes with the pinion gears 15a. First output βhaft la iβ arranged concentrically in the output βhaft 2 and carries a pinion gear 13 which also meshes with the gears 15. The shaft 2 iβ hollow to accommodate the intermediate βhaft la. The shaft la has an extension lb which iβ accommodated rotatably within the input βhaft 1 βo the βhaftβ 1, la and 2 can rotate relative to one another. As in the earlier embodiments, the yoke 10 carries the moveable cluster 9 which has teeth 9a in intermeshing engagement with the tranβfer gear 5 which in turn meshes with teeth 8b of fixed cluster 8. The moveable cluster 9 also meshes with gear 4 as in the previous embodiment. In the embodiment of Figure 2, the yoke 10 iβ designed so that it site over the cage 15 βo that the yoke 10 can be pivoted on the βhaftβ 1 and 2 relative to the βhaftβ la and 2 and cage 15. When the input shaft 1 is rotated, cage 15 is also rotated to cause the pinion gears 14 to rotate the gears 12 and 13 βo that the output shaft 2 is rotated. The phase relationship bet- e the output shaft la and output shaft 2 is adjusted by S- aply pivoting or fully rotating the yoke 10 to cause the spur gear 9 to rotate about gears 4 and 5 to cause the gear 4 and therefore the bevel gear 12 to advance or regress relative to the gear 3 carried by cage 15 and therefore the bevel gear 13. Thus, the phase relationship between the output shaft la and output βhaft 2 can again be adjusted by rotating the yoke 10. The amount of phase change upon a predetermined amount of pivoting of the yoke 10 is set by the gear ratio between the teeth 9a and 9b on the cluster 9. Thus, the ratio between the teeth 9a and 9b can be set to provide a large amount of phase shift between the βhaftβ 1 and 2 upon a predetermined amount of pivoting of the yoke 10 or a email amount of phase shift with the same amount of rotation of the yoke 10. The arrangement described with reference to Figure 2 reduces the reaction back to the moveable yoke 10 thereby making the moveable yoke 10 more easy to move particularly if manual adjustment of the yoke 10 is desired. The transfer gear 5 in this embodiment also forms a transfer gear which operates in a similar manner to the transfer gear 5 described with reference to Figure 1. A third embodiment of the invention is shown in Figure 3. Once again, like reference numerals indicate like parts to those described with reference to Figures 1 and 2. In this embodiment of the invention, the input shaft 1 carries a moveable circular cage lc. Arranged in cage lc are planet shaftβ Id upon which two βetβ of planet gearβ 18 and 18' are arranged. One set of planet gears 18 mesh with first gear 3 connected to first output shaft la and the other set 18' mesheβ with gear 4 coupled to second output shaft 2. A fixed orbit gear 16 mesheβ with the planet gearβ 18' and a moveable orbit gear 17 meshes with the planet gears 18. The moveable orbit gear 17 can have a handle 19 to facilitate its rotation relative to gear 16. When the input βhaft 1 iβ rotated, the cage lc is also rotated to thereby rotate the planet gearβ 18 and 18'. This causes the gears 3 and 4 to rotate in unison. If the moveable orbit gear 17 is rotated, it will alter the phase relationship between the gears 3 and 4 and therefore between the output la and output 2. In Figure 3, the orbit gearβ 16 and 17 form tranβfer gearβ which perform the same function as the gears 5 described with reference to Figures 1 and 2. In this embodiment, as explained above, the gear 17 iβ moveable relative to the gear 16. Figure 4 showβ a further embodiment of the invention which iβ adapted for use in outboard motors for controlling the pitch of a propeller. In this embodiment, the phase control mechanism has an input βhaft 50 which carries a first bevel gear 52 and a second bevel gear 54 which are arranged in back to back relationship as seen in Figure 4. The first bevel gear 52 mesheβ with a plurality of bevel gearβ 56 which are arranged on axles 58 coupled to an inner cage 60. The inner cage 60 forms part of an output shaft 61 and the output βhaft 61 also includes an integral output βhaft portion 62. The second bevel gear 54 mesheβ with a plurality of bevel gearβ 64 which are mounted on axles 66 coupled to an outer cage 68. The outer cage 68 has a front cover plate 70 and forme part of a βecond concentric output βhaft 71 which also includes an integral second output βhaft portion 72. The cover plate 70 is bolted to a flange 72 of the cage 68 by bolts or screws 74. As can be seen in Figure 4, the first output shaft 62 iβ concentric with the βhaft 72 and arranged within the βhaft 72. The βhaft 72 iβ obviously hollow to accommodate the sha t 62. The input shaft 50 iβ hollow and a first control rod 80 is arranged within the input shaft 50 for rotation relative to shaft 50 and passes through the bevel gears 54 and 52. A bevel gear 82 iβ fixed to the βhaft 80 and mesheβ with the bevel gearβ 56 which are coupled to the inner cage 60. The βhaft 62 haβ a recess 84 for accommodating the end of the control rod 80. The control rod 80 is not coupled in the recess 84 so that the control rod 80 can rotate relative to the shaft 62. A second control rod 86 is provided with a bore 88 and is arranged on the input shaft 50 and controller rod 80 as shown in Figure 4 for location relative to the βhaft 50 and rod 80. The second control rod 86 has a bevel gear 90 which meshes with the bevel gears 64 coupled to the outer cage 68. The control rod 80 is provided with a bevel gear 92 and the control rod 86 is provided with a bevel gear 94. The bevel gear 92 engages with a bevel gear 96 which is coupled to a drive rod 98 which in turn can be driven by a motor 100. The bevel gear 94 engages with a bevel gear 102 which is mounted on a drive rod 104 which in turn can be rotated by a motor 102. In order to provide output drive to the shaftβ 62 and 72, the input βhaft 50 iβ driven by a power supply (not shown) such as the outboard motor (not shown) with which the phase control mechanism shown in Figure 4 can be used. Rotation of the input shaft 50 will rotate the bevel gears 52 and 54 which in turn will drive the bevel gearβ 56 and 66 βo that the inner cage 60 and outer cage 68 are rotated about the longitudinal axis of the input shaft 50 to in turn rotate the output shaftβ 72 and 62 to provide output power. In order to adjust the phase of the shaft 62 with respect to the shaft 72 to, for example, alter the pitch of a propeller driven by the outboard motor, (not shown) either the control rod 80 or control rod 86 iβ rotated or, indeed, both control rode 80 and 86 can be rotated. Rotation of the control rod 80 will rotate the bevel gear 82 which will cause the bevel gearβ 56 to advance or regress relative to the bevel gears 64 to in turn cause the inner cage 60 to rotate relative to the outer cage 68 to thereby change the phase relationship between the shaftβ 72 and 62. Similarly, if the βecond control rod 86 is rotated, the bevel gear 90 will be rotated to cause the bevel gearβ 64 to advance or regress relative to the bevel gears 56 to also cause the cage 68 to rotate relative to the cage 60 to thereby change the phase relationship between the shaftβ 62 and 72. Thus, the phase relationship between the shaftβ 62 and 72 can be altered by rotation of the control rod 80, or rotation of the control rod 86 or rotation of both control rode 86 and 80. The control rode 80 and 86 are preferably controlled by motors 100 and 102 which are preferably electric motors which can be actuated by an electric supply (not shown) . Actuation of the motors 100 and 102 will rotate drive shaftβ 98 and 104 to in turn rotate bevel gearβ 96 and 102 βo that the bevel gearβ 92 and 94 are driven to rotate the control rod 80 or control rod 86 about their reβpective longitudinal axes. Thus, in the case of an outboard motor, the motors 102 and 100 can be actuated to selectively shift the phase of the rods 62 and 72 relative to one another to place a propeller (not shown) at a predetermined pitch suitable for take-off so that the outboard motor need not be highly revved in order to propel the boat from a stationary position. As the boat picks up speed, the pitch of the propeller can be altered accordingly by adjustment of the control rods 80 or 86 under the influence of motors 100 and 102 to set the pitch of the propellers for continued propulsion as the boat continues to move. In Figure 4, the bevel gearβ 52 and 54, which are effectively integral with one another being provided on the input shaft 50, form transfer gears which operate in the same manner as the gearβ 5 described with reference to Figures 1 and 2. The phase control mechanism of Figure 4 may be positioned beneath water level so it is water cooled and appropriate seals may be included to ensure that the mechanism iβ water-tight. A bearing 106 may be disposed between the control rod 86 and the cage 68 for supporting relative rotation of the cage 68 with respect to the control rod 86. In the preferred embodiments of the invention described above, the phase relationship between two output βhaftβ iβ adjusted. It would also be possible to alter the phase relationship between more than two output shaftβ by adding additional output βhaftβ concentric with the output βhaftβ la and 2 and duplicating the mechanism described above so that there would be a series of yokes 10 or moveable orbit gearβ 17 which can be adjusted to alter the phase relationship between three or more βhaftβ. Since modifications within the spirit and scope of the invention may readily be effected by persons skilled within the art, it is to be understood that this invention is not limited to the particular embodiment described by way of example hereinabove.

Claims: CLAIMS : 1. A phase control mechanism including: an input for supplying input rotary power; a plurality of outputs each for providing output rotary power; a plurality of first gear members each coupled to a corresponding output of the plurality of outputs; drive means for transmitting rotary power from the input to the outputs βo that when the input iβ driven, power iβ supplied to the outputs for driving the outputs; a phase adjusting means for causing the first gear members to advance or regress relative to one another; and means for actuating the phase adjusting means to thereby cause the first gear members to advance or regress relative to one another to change the phase relationship between the outputs. 2. The phase control mechanism of claim 1 wherein the input is integral with a first of the output shaftβ and a second of the output shafts is mounted concentrically on the first output shaft, the drive means comprises: in respect of the first output, the integral coupling of that output to the input, and in respect of the second output comprises; (a) a fixed spur gear having a first set of teeth which mesh with teeth of the first gear member on the first output, the fixed spur gear having a second set of teeth which mesh with teeth on an idler gear rotatable relative to the outputs; a second spur gear which haβ a first set of teeth meshing with the idler gear and a second set of teeth meshing with the first gear member coupled to the βecond output; and wherein said βecond spur gear is mounted in a yoke pivotal relative to the outputs and wherein the βecond spur gear forms said phase adjusting means and the yoke forms said actuating meanβ βo that when the yoke iβ pivoted relative to the input and output, the βecond βpur gear iβ driven around the firβt gear on the βecond output and the idler gear to cause the first gear on the second output to regreββ or advance relative to the firβt gear on the firβt output to alter the phase relationship between the input and output. 3. The phase control mechanism of claim 1 wherein the input has a cage which supports at least one pinion gear, the pinion gear engaging a first bevel gear mounted on firβt output and a βecond bevel gear mounted on a βecond output; wherein said pinion gear and said first and second bevel gears form said drive means; said firβt gear member coupled to the firβt output being arranged on said cage and being coupled to the first output by the cage, the pinion gear and the first bevel gear, the first gear member on the cage engaging a first set of teeth of a fixed spur gear, the fixed spur gear having a second set of teeth for engaging an idler gear rotatable relative to the outputs, a βecond βpur gear mounted in a yoke pivotable relative to the outputs, the βecond βpur gear having a first set of teeth engaging said idler gear and a βecond βet of teeth engaging said first gear member coupled to the second shaft; and wherein said second spur gear forms the phase adjusting means and wherein the yoke forms the actuating means so that upon pivoting movement of the yoke, the second spur gear iβ rotated around the idler gear and the firβt gear member on the second output to thereby cause the second gear member on the second output and the second bevel gear to advance or regreββ relative to the firβt gear member on the cage and the firβt bevel gear on the firβt output to thereby alter the phase relationship between the outputs. 4. The phase control mechanism of claim 1 wherein the drive meanβ compriβes a cage coupled to the input which carries at least one planet shaft, the planet shaft carrying a firβt planet gear which meshes with the firβt gear fixed to the first output, the planet βhaft also carrying a second planet gear which meβheβ with the first gear mounted on the second output; a first orbit gear arranged for rotation relative to the outputs and meshing with the first planet gear and a second orbit gear arranged for rotation relative to the outputs and engaging the βecond planet gear, one of the firβt or second orbit gears being fixed and the other of the first or βecond orbit gears being moveable relative to the said one of the orbit gears; wherein the phase adjusting means comprises the moveable orbit gear which, upon rotation relative to the fixed orbit gear, causes the first gear fixed to the firβt output to advance or regress relative to the firβt gear fixed to the βecond output to in turn cause the phaβe relationship between the outputs to change; and wherein the actuating means comprises a handle on the moveable orbit gear for moving the moveable orbit gear relative to the fixed orbit gear. 5. The phase control mechanism of claim 1 wherein a first of the output shaftβ includes a first cage and a βecond of the output shafts includes a concentric second cage: the plurality of first gear members comprising a plurality of firβt bevel gearβ and a plurality of βecond bevel gearβ; the firβt plurality of bevel gearβ being mounted on the firβt cage, and the βecond plurality of bevel gearβ being mounted on the βecond cage; the input having a firβt bevel gear for engaging the first plurality of bevel gears on the first cage for driving the first cage to in turn rotate the first output βhaft ; the input having a βecond bevel gear for engaging the βecond plurality of bevel gears on the second cage for rotating the βecond cage to in turn rotate the βecond output βhaft; the drive meanβ comprising the first and second bevel gears of the input and the first and βecond plurality of bevel gearβ mounted on the firβt cage and the βecond cage. 6. The phase control mechanism of claim 5 wherein the phase adjusting means comprises at least one control rod having a bevel gear thereon for engaging the first plurality of bevel gearβ or the βecond plurality of bevel gears so that upon rotation of the control rod, the bevel gear on the control rod is rotated to causes the first plurality of bevel gears to advance or regress relative to the second plurality of bevel gears to thereby change the phase relationship between the first and second output shaftβ. 7. The phase control mechanism of claim 6 wherein the means for actuating the phase adjusting means comprises a bevel gear mounted on the control rod and a motor for driving the bevel gear on the control rod to in turn rotate the control rod. 8. The phase control mechanism of claim 5 wherein firβt and βecond control rode are included each carrying firβt and βecond bevel gearβ for engaging respectively the first plurality of bevel gears on the inner cage and the second plurality of bevel gears on the outer cage and preferably first and second motors and firβt and βecond bevel gear arrangemente are arranged for rotating the firβt and βecond control rode to cauβe the firβt plurality of bevel gearβ on the inner cage to advance or regreββ relative to the βecond plurality of bevel gearβ on the outer cage to thereby change the phaβe relationβhip between the firβt and βecond output βhaftβ. 9. A phaβe control mechaniβm, including: an input for supplying input rotary power; a plurality of outputs, each for providing output rotary power; a plurality of first gear members each coupled to a corresponding output of the plurality of outputs; drive means for transmitting rotary power from the inputs to the outputs βo that when the input is driven, power ie supplied to the outputs for driving the outputs; a tranβfer gear for rotation or operation independently of the input, the tranβfer gear being meβhingly coupled to the first gear members for allowing rotary motion to be transferred between the first gear members; and phase adjusting means for causing the first gear members to advance or regress relative to one another to change the phaβe relationβhip between the outputs. 10. The phaβe control mechaniβm of claim 9 wherein the tranβfer gear iβ meβhingly coupled with the firβt gear members by being enmeshed with ancillary gears fixedly attached to the first gear members. 11. The phase control mechanism of claim 9 wherein the tranβfer gear is mounted on the input.

Inventors: WILLMOT ERIC PAUL, WILLMOT, ERIC, PAUL
Applicants: AIMBRIDGE PTY LTD, WILLMOT ERIC PAUL, AIMBRIDGE PTY. LTD., WILLMOT, ERIC, PAUL
Application year: 1996
Main classification: B23B31
IPC codes: B23B31, B63H5, B64C11, B64C27, B64D31, F01L1, F03D7, F03D11, F16H35, F16H37