AU2000255634B2 - Independent multi output drive - Google Patents

Description

PCT/INOO/0005 1 WO 01/84016 Received 16 January 2002 Title: "INDEPENDENT MULTI OUTPUT DRIVE"' FIELD OF INVENTION: This invention relates to an "iINDEPENDE~NT MULTI OUTPUT

DRIVE"!

BACKGROUND OF THE INVENTION: While it is generally known that to draw power from a rotary equipment such as motor or engine or turbine, etc. (called as prime mover) and transmit the same to a receiver such as harvester, pump, alternator, conveyor belt, etc. The prime mover. is connected hitched to the receiver by means of coupling, clutch, belts, gear box, etc. for transfer of the rotary power.

While it is generally known that two or more receivers can draw power albeit, only alternatively from the same prime mover when prime mover power is more or less equal to each driven equipment.

While it is generally known that in the present art when two receivers of nearly equal ratings are to draw power from a prime mover as mentioned above.

a) belt transmission is used where to alternate the supply of power the prime mover is required to be shut and the transmission belt is required to be manually changed from one receiver to another. The fatult in this system lies with the manual removal of the transmission belt giving rise to extra human work and wear and tear on the belting caused by frequent change.

b) coupling or providing clutches for the receivers on either side of the prime mover thereby alternatively making use of the receivers. The fatult in the system lies in the fact that each receiver has to be compatible to prime mover in rpm and direction of rotation.

SUMMARY OF INVENTION: To overcome the above deficiency the invention seeks an independent multi output drive which allows transmission of power from one or more prime AMENDED SHEET 1 IPEA/AU PCT/IN00/00051 WO 01/84016 Received 16 January 2002 movers to receivers without the need to manually dismantle the receivers and allows flexibility in recievers' revolutions per minute and direction of rotation viz. a viz. the prime mover.

This invention relates to transmission of rotary power from just one end of prime mover(s) to two or more receivers alternatively simultaneously as required without manual dismantling of the receiver(s).

BRIEF DESCRIPTION OF DRAWINGS Figure A represents one arrangement of the drive.

Figure AA, Figure B and Figure BB represent the other arrangements of the drive Figure C1, C2 C2J represent the clutch faces (jaws).

Figure Dl, D1J D2 are developed views of the mating clutch faces. Figure E, Figure F, Figure G, Figure H, Figure I,Figure J, Figure K and Figure L represent the other arrangements of the drive.

DETAILED DESCRIPTION OF THE PREFERED EMBODIMENT: The invention can be explained by FIGURE A as under: The main shaft is coupled clutched connected, to a prime mover (PM).

For stability is supported on bearing(s) in pedestal or housing A set of bearings mounted on it upon which is mounted a free fixed pulley

(FFP).

"FFP" is for the purpose of transmitting rotary power or remaining stationary on The provision of grooves (integral or mounted) on "FFP" for Chain Belts /gear teeth, etc. on its outer diameter is to facilitate power transmission to another pulley. The provision of a clutch face (CF) integral or mounted on the face of the "FFP" away from the "PM" can assist in taking power from transmitting housing (TH) as and when required.

As indicated in the figure, straight splines or such other machined surface of length LA have been provided on the length of"M" after "FFP".

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Received 16 January 2002 WO 01/84016 For permanent rotary movement, a "TH" is mounted on LA and having on its internal diameter female straight splines or such other machined surface of suitable strength, length and design identical to those on On one side of facing "FFP", is a "CF" integral or mounted as required but matable with the "CF" of "FFP". On the other side of "TH" is also a mounted or integral and of desired type.

Further a groove is provided on the outside diameter of'"TH", a brass holding stirrup attached to a lever which when moved laterally makes the "TH" to move on the laterally.

A three position lever is then fixed on "TH" through the The three positions II, I or N indicate at which respective positions "TH" is mated to "FFP", rotary housing (RH) or is unmated.

The total length of'"TH" is less than LA.

After the LA are mounted on On is mounted a On one face of "RH" facing is a clutch face integral or mounted as required but matable with "CF" of"TH".

The housing can be stationary, because of the provision of internal "B" mounted on when is rotating. Also this housing is supported by a "BP" on its outer diameter or its extended shaft. "RH" may also rotate with when it is mated to "TH".

In figure A, a coupling is shown mounted at the other end of An extended shaft can be mounted on "RH" at this end and the "BP" shifted from outer diameter of "RH" to its extended shaft. can then be mounted on the end of extended shaft. Thus "RH" in turn supports the shaft and so the entire assembly.

Output can be taken from at driven equipement I (DE I).

For the purpose of taking power from II "FFP", an auxillary shaft (AS) is mounted on "BP"s or some such support. On "AS" is mounted a fixed pulley(P) 3MENDED

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PCT/IN00/00051 WO 01/84016 Received 16 January 2002 with groves for belts or chain or a gear on its outer diameter to facilitate receiving of power from "FFP".

"AS" is mounted in such a way that receives power from "FFP". Ratio and sizes of "FFP and are adjusted according to the requirement. can also be mounted directly on input shaft of driven equipment II (DEII) in lieu of "AS".

The clutch faces on "FFP" and "RH" are jaw type and explained below.

Figure C1 shows the "FFP", more specifically its clutch face (CF) "VIEW

KK".

View at "AA" gives a cross section of one jaw, which is identical to all other jaws on "FFP".

Since the direction of rotation is known, the mating and relief side of each jaw is also known.

Side "ed" is mating side of jaw.

Angle "edc" is acute in lieu of right angle.

"cd" is parallel to root "ae".

"cba" is relief side of jaw.

Angle "bed" is obtuse angle.

Relief angle bed" and mating angle "edc" designed as per specific requirement but generally slope of "be" with reference to the vertical is more than slope of "ed" with reference to the Vertical, thus enabling stronger jaws within same clutch dimensions.

If direction of rotation is reverse, then even on the jaws, the mating and relief sides are interchanged.

Purpose of straight face "ab" is explained later.

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PCT/IN00/00051 WO 01/84016 Received 16 January 2002 Figure C2 shows more specifically its clutch faces.

"TH" has two clutch faces, one mating with "FFP" and with Figure C2 describes that "CF' "VIEW JJ", of "TH" which mates with the "CF' of "FFP". View at "BB" gives a cross section of one jaw which is identical to all other jaws on this face of"TH" which mates with "CF' of "FFP".

Since the direction of rotation is known, the mating and relief side of each jaw is also known.

"ml" is mating side of jaw.

Angle "lmn" is acute angle and equal to angle "cde" shown in figure C1.

Due to this angled mating, the jaws tend to pull towards each other and grip each other while rotating. The jaws thus have a positive clutching, a pull towards each other (a grip) as against the static (passive) clutching normally associated with straight faced jaws. In fact even lesser engagement of jaws along length "ed" and "lm" will pull the two jaw faces towards each other and the "TH" which is on splines will slide on shaft and ultimately full engagement can occur.

Relief obtuse angle helps in easier engagement and disengagement.

Length "mn" is jaw size and parallel to root "Ip".

"nop" is relief side of jaw.

Angle "opy" is obtuse angle.

"no" is straight face on relief side of jaw and mates with at time of accidental reversal of rotation or while shutting off when driver and driven roles get reversed, sometimes.

Angle "opy" is less than angle "bed" so that sloping surfaces of the relief side of jaws never meet, only the straight faces viz "ab" and "no" meet. Thus even while accidental reversal occurs, jaws do not disengage AMENDED

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1PEiVAU PCT/IN00/00051 WO 01/84016 Received 16 January 2002 If there is a specific requirement, straight faces "ab" and "no" can also have acute angles similar to "de" and "ml" for giving a grip (positive clutching) whenever reversal occurs.

Relief side of jaws can be plain straight or acute in lieu of obtuse angle i.e.

"abc" and "nop" shown in Cl and C2 can be straight lines. Thus mating sides are angled, as shown and serve the purpose of "grip" as described above.

The non mating sides can be straight or similarly angled (acute angle) as in mating side as per specific requirement.

The jaws of clutch face are narrower at ID but wider at OD. One thus gets lower cross section at the ID of each jaw.

In figure Cl "view -SS" gives a cross sectional view of one jaw, which is identical to all other jaws on "FFP".

"ji" is the side of the jaw on the OD.

"hgf" is the side of the jaw on the ID.

Instead of a regular straight line "hgf" the jaw is strengthened by a chamfer at the ID resulting in "fgf".

The cross section "fgf" reinforces the jaw at the ID.

Although the jaw meets on the face "jihgf", point is not a corer as in conventional case, resulting in stronger jaw at ID.

In figure C2 "view -TT" gives a cross sectional view of one jaw which is identical to all other jaws on "TH".

"vu" is the side of the jaw on the OD. "tsr'" is the side of the jaw on the ID.

Instead of a regular straight line "tsr'" the jaw is strengthened by chamfer at the ID resulting in "rsr'".

The cross section "rsr"' reinforces the jaw at the ID.

Although the jaw meets on the face "vutsr"' only, the point is not a corner as in conventional case, resulting in stronger jaw at ID.

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PCT/INO000o 51 WO 01/84016 Reoa ed 16 h09b2 Angle A 1" is always less than A 2" so that during reversal the jaws never meet at angled surface but only at straight face. Hence accidental unmating is avoided (above para is explained by figure Dl which is a developed view of jaws at outer diameter).

This same principle can be used in other such engagement devices and more specifically on clutch faces between "RH" "TH" "TH" "FFP".

Although angles A "A etc. are shown dimensions and angles of jaws are arrived at by determining all the angles with reference to the centre line of the clutch.

In all the jaws on one clutch face (CF2) the straight side "ab" is at root whereas in all jaws on the opposite clutch face (CF1) the straight side "no" is at neck.

The same clutching mechanism can be used by reversing only one or more of these straight faces in such a way that the jaws completely mate at predetermined position(s) on the clutch face only (shown in figure D 2) to achieve positional clutching.

In all jaws the sharp corers and edges are finely rounded off or chamfered in a way that the corers edges do not meet.

Figure C2J shows an isometric view of one jaw of the "TH" clutch face which is similar to all other jaws on While mating, all the jaw faces do not completely meet each other as the clutch face material is basically stiff (viz. iron, steel). Invariably some jaw teeth portions are loaded more than the others.

So on the mating face a thin pad (but equal in size to the jaw face, sans the chamfer at the root or ID) of "rubber" (neoprene, viton, etc.) or any such compressible material (CP) is stuck. On this another thin wear plate (of iron, etc.) (WP) of same size is stuck (which may be integral with the compressible pad).

AMENDED SHEET -7 IPENAU PCT/INOO/0005 1 WO 01/84016 Received 16 January 2002 The jaws now meet on 'the wear plate (WP) only, but because of the compressibility of the sandwiched pad all the jaw faces (plates) meeet each other more equally, and power transmission takes place more evenly, these also absorb the impact shock loads. Each jaw tooth is now more equally loaded as compared to straight metal to metal contact without the sandwiched compressible material pad Periodic change of compressible material pad (CP) and wear plate (WP) is cheaper than changing entire clutch face.

Although because of above the jaw teeth become thinner to accomodate the plates (metal and compressible), it is more than compensated because of even loading of the jaw teeth.

Only without the can also be stuck on to the mating jaw faces.

Thus the metallic wear plate protect the jaw faces.

The above can be done on both the mating clutch faces or only on one, as desired (shown in C2J). The mating faces (the wear and (or) rubber plates can still be at accute angle with reference to each other to facilitate the grip as explained earlier and shown in figure D1J which is a developed view of the j aws at outer diameter using the wear and rubber plates.

The basic configuration remaining same following extra provisions can be made.

I1. More outputs can be taken from II i.e. "FEP" by adding extra grooves on "FFP" and mounting two outputs on "AS" or even having another shaft on other side to give multiple outputs at I.

2. One or more fixed pulley(s) can also be mounted on "RH" main body or on its extended shaft as per design for taking of more outputs to other driven equipments at I (points are explained by figure AA).

3. A bearing mounted in a housing can be used to- replace the stirrup for the same effect on "TH".

8 AMENDED SHEET PCTLNOO/0005 1 WO 01/84016 Received 16 January 2002 4. Transmitting housing can be split radially and each "TH" can then have a stirrup bearing in a housing on their respective outer diameters. This would facilitate both I and II to give outputs simultaneously or alternatively as desired by user. These two "TH" can have positions I and N and or II and N respectively to mate independently with I or (and) 11 or (and) remain neutral.

With this change both I and 11 can be used to give outputs simultaneously or alternately as required, only constraint that for simultaneous use the prime mover power should be greater than or equal to power output. at I plus power output at IIL Spline length LB is greater than total length of "TH I" "TH II".

(This is explained by figure B).

Transmitting Housing "TH II" can be shifted and brought immediately after "BP" on main shaft Also splines or such other machined surface of suitable strength, design and straight length "L II" are provided immediately after "BY" Onl to accommodate "TH II". Thus we have positions Neutral and II immediately after then "FFP", then splines or some such machined surface of Length "L I" to accommodate "TH 1I^ and then "RH" on shaft This is explained by Figure BB.

Basically, figure BB is not different from figure B except that here "TH I" and "TH 11" are away from each other and there are two splines or some such machined surface of suitable length, strength and design cut on the shaft to accommodate the two "TH"s mounted separately as against just one length of splines or some such machined surface but longer in Figure B where both the "TH I" and "TH 11" are mounted together and near each other.

6. Additional independent outputs can be taken from shaft by mounting the set of "FFP", its bearings, "TH" and having splines or some such machined surface, on the shaft to accommodate respective "TH" This is explained in Figure E Figure F.

Thus one can have multiple indendent outputs by way of mounting above sets AMENDED SHEET PCT/IN00/00051 WO 01/84016 Received 16 January 2002 on shaft Shaft can be supported by additional bearing(s) in housing or pedestal (BP) in between the "FFP"s or between "FFP" "RH" as determined by loading patterns.

7. The clutching system which is jaw type can be replaced by a hydraulic frictional electromegnetic pin bush clutch splines, etc.

Clutch engagement comprising the levers, etc. can be changed as per specific application requirement.

8. Unit can also be simplified by doing away with "FFP", its bearings and clutch face on "FFP" side of Thus one has only 2 options N I. One thus has independent output only at "DE I".

A fixed pulley (FP) can also be mounted on Thus fixed outputs can be taken from "DE II", "DE III", etc. by mounting the respective "FP"s directly on as desired.

Thus one has fixed outputs at "DE II", "DE III", etc. but independent output at "DE This is explained by figure G. Similarly by removing "TH "RH", its bearings, etc. and mounting "BP" on main shaft in lieu of one has independent outputs from via the various "FFP"s only alongwith a fixed output at "DE F' as desired. This is explained by figure H.

9. In specific cases a simple push pull mechanism can be used in lieu of stirrup bearing in a housing to move the "TH" when the clutch faces are acute angled jaw type as mentioned above.

The clutch faces being acute angled jaw type no force will be required to hold the "TH" in place at time of power transmission and hence no holding mechanism required.

Brakes can be incorporated on "FFP", etc. as required to bring unit to a halt quickly.

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PCT/IN00/00051 WO 01/84016 Received 16 January 2002 11. Additional "PM"s can be incorporated into the system (by connecting the same through the "FFP"s shown in A, B, BB, E, F, etc. in lieu of the "DE"s) to supply power to the various driven equipments alternately as required.

Thus one may have more than one "PM" to supply power alternately as required to the driven equipments which may also be one or more in number.

A single driven equipment can be connected to the unit in lieu of the "PM" (shown in figure A, B BB) and two prime movers in place of"DE r' "DE II" respectively can be used to supply power alternately/ as required (shown in figure I).

12. Two main shafts as explained above with their various connections can be mounted alongside.

Prime mover X and Prime mover Y [PM connected to each.

This is explained by figure J. One can thus have free and independent transfer of power from the to the driven equipments of i.e. "DE I "DE etc. and vice versa via the "FFP" of each shaft.

Thus "PM can also be used to drive the "DE II(Y)" or "DE I or both as required and vice versa. Only constraint that when "PM [or is powering the driven equipments of"PM [or "PM [or "PM needs to be free of its main shaft [or or capable of rotating with [or "M without any damage or power loss.

One can have additional "PM"s or "DE"s connected to any of the main shafts as required, by "FFP" "FP" One can even delete relocate one or more of the "DE" as desired.

13. Rotary housings "RH" (with or without their extension shaft) alongwith internal bearings, can be mounted on both sides of the Main shaft These can in turn be supported by "BP"s on their outside diameters (or extended shafts). Subsequently, their respective "TH" with their internal splines or such SAMENDED

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PCT/IN00/00051 WO 01/84016 Received 16 January 2002 other machined surface on their internal diameter can be mounted on the main shaft having splines or such other machined surface on its outside diameter of suitable length, strength and design.

The clutch faces of the "RH" and respective 'TH" face each other. The main shaft is now independent of both the "PM" or "DE" on one end and the "DE" or "PM" on other end.

Other "PM" "DE" can be connected via the "FFP"s/ "FP"s/ "P"s to the main shaft. One can delete relocate one or more of the "PM" as desired.

Thus one has independent multi output multi input(s) from the unit.

This is explained by figure K.

"PM I" is connected via the "RH IV" and "TH IV" combination on one end and "DE I" by the "RH I" and "TH I" combination on other end of the shaft.

"DE II" is connected to the main shaft via the "FFP II" "P II" combination and "PMII" is connected to the main shaft via the "FFP III" "P rI" combination.

Thus the various "TH" will mate independently or remain neutral and one can have the prime mover(s) to independently power the driven equipment(s) simultaneously or alternately as required.

Here because the shafts are independent of both ends, connection or disconnection of "PM I" and "DE I" is possible, as desired.

14. Two main shafts (having "RH" mounted on both sides) can be mounted alongside. Prime mover X and prime mover Y connected to each main shaft and respectively. This is explained by figure L.

One can thus have free and independent transfer of power from the to the driven equipments of i.e. "DE I "DE II etc. and vice versa via the "FFP" of each shaft.

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PCT/IN00/00051 WO 01/84016 Received 16 January 2002 Thus "PM can also be used to drive the "DE II(Y)" or "DE I or both as required and vice versa.

Here because the shafts are independent of both ends connection or disconnection of"PM(X)" and is possible, as desired.

One can have additional "PM"s or DE's connected to any of the main shafts as required by "FFP" "FP" One can even delete relocate one or more of the "DE" as desired.

Although couplings, fasteners, sleeves, pedestals, keys, washers, etc. are used to fasten the bearings, pulleys, shafts, couplings, etc. the same are not shown on the drawings to avoid confusion or making the drawings too complicated.

16. In the drawings the driven equipments and prime movers associated with the various "FFP"s are shown connected on one/particular side of the main shaft.

These driven equipments can be shifted and mounted on either side based on site and specific requirement.

17. In the drawings a coupling is shown bolted on to the fag end of "RH".

However, this can also be keyed on to the outer diameter of"RH", as required.

18. Wherever one or two bearings are shown in the drawing, they can be one or many as required by design.

19. Full clutch faces can be coated with rubber to give compressibility to all-metal mating jaw faces to ensure maximum contact between mating jaws.

Only drawback being that periodic recoating after wear and tear, is relatively more expensive proposition viza viz pads.

The word rubber is used to denote any compressible material like neoprene, viton, nitrile, etc. etc.

21. Certain equipments are able to take the required load of When such equipments are used to connect to the first support of viz. "BP" can AMENDED SHEET 13 A P e IPENAU Page PCT/IN00/0005T Received 16 January 2002 WO 01/84016 be done away with. is supported by the equipment at this end, being connected directly or by a rigid coupling to it.

22. Certain equipments are able to take the required load of When such equipments are used to connect to the "BP" on "RH" (or its extended shaft) can be done away with. The "RH" is connected directly or by a rigid coupling to the equipment. The "RH" being supported by the equipment supports the shaft and so the entire assembly, at this end.

Note: From point 4 onwards above, unless specifically mentioned 1) 'TH "TH II", etc. include brass bronze stirrup or bearing in a housing with its lover attachment and 2) "FFP", etc. include the clutch faces "CF'.

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Claims (31)

1. In an attachment of prime mover(s) to two or more receiver(s), by way of an "Independent Multi Output Multi input Drive" the arrangement comprising: of a main shaft, for stability, supported on a set of at least one bearing in pedestal or housing, a second set of at least one bearing mounted on the main shaft upon which is mounted a free fixed pulley for the purpose of transmitting rotary power or remaining stationery even when the shaft rotates; the provision of grooves integral or mounted on outside diameter of the free fixed pulley for belts gear teeth chain, etc. for power transmission to a driven equipment, the second via a fixed pulley; the provision of a clutch face (friction/ electromagnetic spline jaw pin bush type, etc. as required integral or mounted on the face of the free fixed pulley but facing a transmitting housing; provision of straight splines or such other machined surface on the length (of length LA) of the shaft with the transmitting housing mounted on the shaft and having identical femrale straight splines or such other machined surface on its internal diameter, for its permanent rotary movement with respect to the main shaft, total length of the machined surface on the inside diameter of the transmitting housing less than LA; the provision of a similar clutch face on one side of the transmitting housing and facing the free fixed pulley, to mate the transmitting housing with the free fixed pulley, the provision of stirrup of brass /bronze such other material on outside diameter of the transmitting housing, a clutch face (friction electromagnetic spline /jaw pin bush type, etc. as required) on the other side of transmitting housing to mate with the rotary housing; the provision of a lever mechanism attached to the stirrup for the purpose of moving the transmitting housing on main shaft and mating transmitting housing with the free fixed pulley or the rotary housing or unmating and also maintaining position of clutch faces with respect to each other; provision of similar clutch face (integral or mounted) on the side of rotary housing facing the transmitting housing and matable with the clutch face of transmitting housing; the support of the main shaft by means of at least one bearings inside a rotary housing at the end of the shaft and provision of bearing in a pedestal or housing on the outside diameter of the rotary housing for supporting the entire system, the provision of a coupling clutch, etc. at other end of rotary housing for power transmission to a driven equipment the first, the provision of a fixed pulley having on its outside diameter grooves for belts gear teeth chain, etc. for the purpose of receiving power from the free fixed pulley, the fixed pulley itself is mounted on shaft of the second driven equipment or on an auxiliary shaft, supported on at least one set of bearing in pedestal coupled clutched connected to the second driven equipment, the arrangement facilitates trasmission of rotary power from the prime mover to either of the two driven equipments or for each equipment to be independently run when lever is in neutral position.

2. Combination of claim 1 wherein jaw type clutch faces are provided on at least one pair of clutch faces of the free fixed pulley, transmitting housing rotary housing.

3. Combination of claim 2 wherein mating sides of jaw type clutch faces are acute angled to avoid disengagement during operation and facilitate full engagement in running.

4. Combination of claim 2 3 wherein relief sides of the jaw type clutch faces are acute angled to facilitate the grip even while reverse running occurs.

Combination of claim 2 3 wherein for ease of mating, extra strength to each jaw and avoiding accidental disengagement due to reversal, etc. providing a combination of relief angle (obtuse angle) and straight portion (acute angled portion) respectively on non mating side of each jaw in such a way that only the straight portions (or acute angled portions) meet while reversal i.e. on non mating side of each jaw on one clutch face (called clutch face 1 for simplicity) the straight portion (or acute angled portion) is at the neck and on the non mating side of each jaw on the mating clutch face (called clutch face 2 for simplicity) the straight portion (or acute angled portion) is at the root, also adjusting the relief angles (obtuse angles) on the non mating side of jaws of mating clutch faces so that only the straight portions (or acute angled portions) meet and not the obtuse angled portion, when reversal occurs and jaws do not disengage accidentally i.e. the obtuse angle on the jaws of one clutch face (clutch face 2) is more than the obtuse angle on the jaws of other clutch face (clutch face 1).

6. Combination of claim 2 and 5 wherein for ease of machining, only straight mating faces are used but on non mating side a combination of relief angle (obtuse angle) and straight portion (or acute angled portion) as explained above is used for ease of mating, extra strength to each jaw and avoiding accidental disengagement due to reversal etc., respectively.

7. Combination of claim 2 4 and 5 wherein on mating side a combination of relief angle (obtuse angle) and straight portion (or acute angled portion) is used for ease of mating and extra strength to each jaw.

8. Combination of claim 2, 5, 6 and 7 wherein reversing the straight portion (or acute angled portion) with the obtuse angled portion on predetermined jaw(s) between any two mating clutch faces to achieve positional clutching.

9. Combination of claim 2, 3, 4,5,6,7 and 8 wherein the jaws have chamfer at the inside diameter, for additional strength to jaws at inside diameter.

Combination of claim 2, 3, 4, 5, 6, 7, 8&9 wherein the clutch faces are coated by a layer of compressible material like nitrile, viton, etc. to ensure even loading of the jaw faces.

11. Combination of claim 2, 3, 4, 5, 6, 7, 8, 9&10 wherein wear plates (metal/other material) are stuck attached to the jaw faces to protect them from wear tear.

12. Combination of claim 2, 3, 4, 5, 6, 7, 8, 9& 1 wherein pad of any suitable compressible material is sandwiched stuck/attached between the wear plate jaw for ensuring more even loading of the jaws at the time of power transmission absorbing shock/impact loading.

13. Combination of claim 12 wherein the wear plate is integral with or is a part of the compressible material pad.

14. Combination of claim 1 where a bearing in housing with a lever attached is used in lieu of brass bronze such other material stirrup.

Combination of claim 1 where an extended shaft is mounted on fag end of the rotary housing and a bearing in a pedestal or housing is mounted on rotary housing outside diameter or the extended shaft for supporting the entire system.

16. Combination of claim 1 and 15 where at least one pulley is mounted on rotary housing main body or its extension shaft to provide extra outputs through the system via the rotary housing, provision of extra outputs through the system via the free fixed pulley by mounting extra grooves on the free fixed pulley and taking extra outputs through two mountings on the auxiliary shaft or even having another shaft on other side of prime mover to get extra outputs through one more auxiliary shaft.

17. Combination of claim 1, 14, 15 and 16 wherein two transmitting housings, transmitting housing II transmitting housing I with just one clutch face on each (in lieu of just one transmitting housing with two clutch faces) and on the 'outer diameter' of each a set of bearing in a housing with a lever attached, are provided immediately next to each other on a machined surface of length "LB" of main shaft, capable of independently mating with free fixed pulley and rotary housing, respectively or remaining unmated, thus making it possible for transmission of power from one prime mover to two or more driven equipment individually or together or remaining neutral.

18. Combination of claim 1, 14, 15, 16 and 17 wherein the following arrangement is provided; provision of the splines or such other machined surface of length "L II" on the main shaft immediately after the bearing pedestal support to accommodate transmitting housing II with its clutch face and on its outer diameter a bearing in a housing with a lever attached, on the main shaft, then free fixed pulley, with its associated bearings compatible clutch face, then splines or such machined surface of length "L on the main shaft to accommodate transmitting housing I with its clutch face and on its outer diameter a bearing in a housing with a lever attached, then rotary housing with its associated bearings compatible clutch face etc. on the main shaft in that order, here again transmitting housing II and transmitting housing I are capable of independently mating with free fixed pulley rotary housing respectively or remaining unmated, thus making it possible for a different arrangement in position of the transmitting housings and their respective levers.

19. Combination of claim 1, 14, 15, 16, 17 and 18 wherein additional independent outputs from the drive can be obtained by providing the additional set of free fixed pulley, its associated bearings, its associated transmitting housing, and splines or some such machined surface on the main shaft, corresponding machined surface on internal diameter of respective transmitting housing, their associated clutch faces etc. for more independent outputs from the shaft.

Combination of claim 16, 17, 18 and 19 wherein provision of additional supports to the main shaft by at least one bearing pedestal units in between the free fixed pulley or in between free fixed pulley rotary housing as determined by loading patterns for extra stability to the drive.

21. Combination of claim 1, 14, 16, 17, 18, 19 and 20 wherein the main shaft is supported at the end by a bearing pedestal unit only i.e. not providing the rotary housing with or without its extended shaft, its associated bearings, its associated transmitting housing, splines, etc. thus having independent outputs from drive via the various free fixed pulleys only.

22. Combination of claim 1, 14, 15, 16, 17 and 18 where not providing any free fixed pulley, its associated bearings, its associated transmitting housing, Splines, etc. thus having independent output only via rotary housing i.e. rotary housing main body or its extended shaft if provided.

23. Combination of claim 1, 14, 15, 16, 17, 18, 19, 20, 21 and 22 wherein at least one fixed pulley is mounted on main shaft to give fixed output from the drive via the various fixed pulleys also.

24. Combination of claim 1, 14, 15, 16, 17, 18, 19, 21, 22 and 23 wherein the brass holding stirrup with its lever attachment or bearing in housing and its lever attachment is not provided thus, for shifting the various transmitting housing a simple push pull mechanism can replace the stirrup with lever attachment or bearing in housing with lever attachment.

Combination of claim 1, 14, 15, 16, 17, 18, 19, 21, 23 and 24 wherein positive slipless timing belts are used on free fixed pulley, fixed pulley, pulley, etc. to transmit power.

26. Combination of claim 1, 14, 15, 16, 17, 18 and 20 where the prime mover is replaced by a driven equipment and the driven equipment I, driven equipment II by prime movers to simultaneously alternately supply power to the driven equipment.

27. Combination of claim 1, 14, 15, 16, 17, 18, 19, 20, 21, 23, 24, 25 and 26 where at least one additional prime mover is attached to the drive in lieu of driven equipment II, driven equipment III, etc. to simultaneously alternately drive one or more driven equipments together or alternately.

28. Combination of claim 1, 14, 15, 16, 17, 18,19, 20, 22, 23 ,24, 25, 26 and 27 where the main shaft is supported on both ends by means of rotary housing, their associated internal bearing, their associated external bearing with housing, etc. then having their associated transmitting housings, splines, etc. on the main shaft; the various free fixed pulley with their associated bearings, transmitting housings, splines, etc. mounted in between, on the main shaft; to facilitate free and independent exchange of power between the prime movers and driven equipments.

29. Combination of claim 1, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27 and 28 where two or more main shafts are aligned near to each other and interconnected for free and independent exchange of power between the prime movers and driven equipments.

Combination of claim 1, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27, 28 and 29 where in cases when the equipment associated with main shaft is able to take the required load of the main shaft, the first support of the main shaft viz. bearing pedestal unit is done away with, to reduce the overall length and cost of the drive, the main shaft is supported by the equipment at this end, being connected directly or by a rigid coupling to it or is a part of the equipment at this end.

31. Combination of claim 1, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27, 28, 29 and 30 where in cases when the equipment associated with a rotary housing is able to take the required load of the rotary housing, bearing pedestal unit on rotary housing (or its extended shaft) is done away with the rotary housing so main shaft etc. are supported by the equipment at this end, the rotary housing (or its extended shaft) being connected directly or by a rigid coupling to it or is a part of the equipment at this end. Note: Claim 12 onwards unless specifically mentioned 1) Transmitting housing, transmitting housing I, transmitting housing II, etc. include brass bronze stirrup or bearing in a housing with its lever attachment and 2) Transmitting housing, free fixed pulley, rotary housing, etc. include the clutch faces.