CA1082000A - Epicyclic gear mechanism - Google Patents
Epicyclic gear mechanismInfo
- Publication number
- CA1082000A CA1082000A CA281,600A CA281600A CA1082000A CA 1082000 A CA1082000 A CA 1082000A CA 281600 A CA281600 A CA 281600A CA 1082000 A CA1082000 A CA 1082000A
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- Prior art keywords
- gear
- output
- input
- pinion
- epicyclic
- Prior art date
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Abstract
A B S T R A C T
An epicyclic gear mechanism having a series of gear trains each including a rotatable cage, a plurality of planet gears, a stationary gear pinion and an output gear, all of the gear trains being mounted about a fixed shaft. The output gear of one gear train is operably associated with the input gear of a succeeding gear train and is rotatable relative to its cage, and a final output means associated with the last gear train of the series.
An epicyclic gear mechanism having a series of gear trains each including a rotatable cage, a plurality of planet gears, a stationary gear pinion and an output gear, all of the gear trains being mounted about a fixed shaft. The output gear of one gear train is operably associated with the input gear of a succeeding gear train and is rotatable relative to its cage, and a final output means associated with the last gear train of the series.
Description
10~000 This invention concerns epicyclic gear mechanisms.
Gear mechanisms of the kind envisaged find application, for example, in load lifting equipment, such as travelling cranes, mobile cranes, tower cranes and the like. The mechaniqm may also be used as driving means for machines of various types in which high torque is required.
Thus according to the present invention there is provided an epicyclic gear mechanism characterised in that there i9 provided a series of gear trains on a fixed shaf-t, each gear train including a rotatable cage, at least two planet gears on the cage, and rotatable relative to the cage, a stationary gear pinion and an output gear rotatable relative to the cage, and connected to an input pinion, of a ~uccessive gear train, there being a stepwise increase in output speed of gear trains and a final output means in the form o~ an output pulley or gear rotatable on the stationary shaft.
The invention will now be described further, with re~erence to the accompanying drawings in which several alternative forms of gear mechanisms are illustrated somewhat schematically and by way o~ example only, of the many forms of gear mechanism that can be constructed in accordance with the invention.
Gear mechanisms of the kind envisaged find application, for example, in load lifting equipment, such as travelling cranes, mobile cranes, tower cranes and the like. The mechaniqm may also be used as driving means for machines of various types in which high torque is required.
Thus according to the present invention there is provided an epicyclic gear mechanism characterised in that there i9 provided a series of gear trains on a fixed shaf-t, each gear train including a rotatable cage, at least two planet gears on the cage, and rotatable relative to the cage, a stationary gear pinion and an output gear rotatable relative to the cage, and connected to an input pinion, of a ~uccessive gear train, there being a stepwise increase in output speed of gear trains and a final output means in the form o~ an output pulley or gear rotatable on the stationary shaft.
The invention will now be described further, with re~erence to the accompanying drawings in which several alternative forms of gear mechanisms are illustrated somewhat schematically and by way o~ example only, of the many forms of gear mechanism that can be constructed in accordance with the invention.
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In the drawings :
FIGS~ 1 to 9 illustrate different gear mechanisms made in accordance with the invention, FIGSolO to 12 illustrate schematically arrangements of gear trains and the manner in which loads can be moved, FIG.13 illustrates how separate units may be constructed and coupled together to form gear assemblies, FIGS.14 to 21 illustrate how the gear train assemblies may incorporate combination~ of the gear arrangements a~ in FIGS~ 1 to 9 FIGS. 22 to 27 illustrate arrangements for the application o~ centri~ugal ~orce balancing of the mechanisms, FIGS. 28 to 31 illustrate locations of rotary masses applied to the mechanisms, FIGS. 32 and 33 illustrate reverse rotation o~ the mechanisms, FIG.34 and FIG. 37 illustrates a mechanism a~sembly in an apparatus demonstrating balancing o~ masses, FIGS. 35 and 36 illustrates transport applications o~ the mechanism assemblies.
Re~erring now to the drawings, it will be seen that the mechanisms of FIGS. 1 to 9 are similarly composed, in that they each have a ~ixed centre shaft lO,supported at various , .
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0 !32000 points along its length, in carriers 11. Mounted on the shaft 10, at spaced intervals there-alcng, are a series of epicyclic gear assemblies 12, 13, 14. These are shown as being assembled together, and not as separate units, although separate units could be constructed, as in FIG.13 and subsequently coupled together. It is possible to couple together, all of the gear units shown in FIGS. 1 to y if desired, to give an extremely large input reduction.
On the fixed centre shaft 10, in each of the gear assemblies shown, is fixed for example, by a key or peg 66 an external gear A 30, about which the epicyclic gear !' as3emblies revolve, in addition to revolving about their own central axi~. In ~ome of the a~semblies, a fixed ; internal gear F 31, has been substituted for the fixed external gear A 30, (see FIGS. 3.4.5 and 6). As can also be seen, there are provided integral gears B 32 and C 33, and also a freely revolving centre internal gear FD 34 (see FIGS. 7.8.9) on the same axis as the fixed gear A 30, or fixed gear F31~ These gears are also marked, with either a minus or positive sign, and this minus or positive sign denotes whether one revolution is ~l to be ~ubtracted or added, to their obse~rved revolutions, and in the case of the centre gear D 35, or gear FD 34, whlch are shown in the assemblies as plus gears, this :~ ~ means that one revolu~ion ig to be added to their .." ~.:
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~082000 revolutions, which then become, observed and actual revoluticns, that is, in the case of centre freely revolving positive gear D 35, its observed and actual revolutio.ns are either, A x C + 1 or B ~ C ~ 1 and i.n the case of the centre freely revolving gear FD 34, its observed and actual revolutions would be ~ x F~ + 1 or F x C ~1.
B FD
Thus with reference to FI&~l. of the drawi.ngs, ~ith the fixed external centre gear A 30, of 1~ inches diameter, and the gear B 32, of ~ inches diameter, and gear C33, o~
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In the drawings :
FIGS~ 1 to 9 illustrate different gear mechanisms made in accordance with the invention, FIGSolO to 12 illustrate schematically arrangements of gear trains and the manner in which loads can be moved, FIG.13 illustrates how separate units may be constructed and coupled together to form gear assemblies, FIGS.14 to 21 illustrate how the gear train assemblies may incorporate combination~ of the gear arrangements a~ in FIGS~ 1 to 9 FIGS. 22 to 27 illustrate arrangements for the application o~ centri~ugal ~orce balancing of the mechanisms, FIGS. 28 to 31 illustrate locations of rotary masses applied to the mechanisms, FIGS. 32 and 33 illustrate reverse rotation o~ the mechanisms, FIG.34 and FIG. 37 illustrates a mechanism a~sembly in an apparatus demonstrating balancing o~ masses, FIGS. 35 and 36 illustrates transport applications o~ the mechanism assemblies.
Re~erring now to the drawings, it will be seen that the mechanisms of FIGS. 1 to 9 are similarly composed, in that they each have a ~ixed centre shaft lO,supported at various , .
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0 !32000 points along its length, in carriers 11. Mounted on the shaft 10, at spaced intervals there-alcng, are a series of epicyclic gear assemblies 12, 13, 14. These are shown as being assembled together, and not as separate units, although separate units could be constructed, as in FIG.13 and subsequently coupled together. It is possible to couple together, all of the gear units shown in FIGS. 1 to y if desired, to give an extremely large input reduction.
On the fixed centre shaft 10, in each of the gear assemblies shown, is fixed for example, by a key or peg 66 an external gear A 30, about which the epicyclic gear !' as3emblies revolve, in addition to revolving about their own central axi~. In ~ome of the a~semblies, a fixed ; internal gear F 31, has been substituted for the fixed external gear A 30, (see FIGS. 3.4.5 and 6). As can also be seen, there are provided integral gears B 32 and C 33, and also a freely revolving centre internal gear FD 34 (see FIGS. 7.8.9) on the same axis as the fixed gear A 30, or fixed gear F31~ These gears are also marked, with either a minus or positive sign, and this minus or positive sign denotes whether one revolution is ~l to be ~ubtracted or added, to their obse~rved revolutions, and in the case of the centre gear D 35, or gear FD 34, whlch are shown in the assemblies as plus gears, this :~ ~ means that one revolu~ion ig to be added to their .." ~.:
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~082000 revolutions, which then become, observed and actual revoluticns, that is, in the case of centre freely revolving positive gear D 35, its observed and actual revolutio.ns are either, A x C + 1 or B ~ C ~ 1 and i.n the case of the centre freely revolving gear FD 34, its observed and actual revolutions would be ~ x F~ + 1 or F x C ~1.
B FD
Thus with reference to FI&~l. of the drawi.ngs, ~ith the fixed external centre gear A 30, of 1~ inches diameter, and the gear B 32, of ~ inches diameter, and gear C33, o~
3 inches diameter, and centre gear D 35, of 1~ inches dia~eter then when one revolution o~ the input disc 36 which drives the integral gears B 32 and C 33, around the fixed external gear A 30, is considered, then the observed and actual revolutions of freely revolving centre gear D 35, are x 3 + 1 which is 2 ~ 2 + 1 which equals 5, but i.n the case of FIG.l, the input dlsc 36, makes 8 revolutions, so that the observed and actual revolutions o~ the first assembly would result in the external centre gear D 35, ... . .
revolving 8 x 5 revolutions, i.e. 40 revolutions, and these 40 observed and actual revolutions are transferred to the 1 second assembly, as the input.
i With the input disc 36, revolutions, for the ~econd . .
assembly being 40, and with the second a~sembly constructed in exactly the same manner a~ the first assembly~ in so -- .
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() far as ~ear sizes are concerned, the externai freely revolving 1~ inches diameter centre ~ear D ~5 9 in the second unit would make 40 x 5 revolutions~ i e, 200 revolutions, that is to say~ 200 revolutions actual and observed, and this becomes the input or disc 36, revolutions o~ the third assembly9 which again, assuming its gear ~izes to be like the gear sizes of the first two assemblies, the output would then be 200 ~ 5 or 1000 ~ revolutions actual and observedO
! With a pulley 37, attached to the output gear D 35 o~ the third assembly, by keys or pegs ~7, the latter would revolve at 1000 re~olutions per minute on the spindle 10, on which the three epicyclic gear units are revolving. As shown in the drawings, and in particular in ~IGol~ there sre provided a number of disc like fly-I wheel units, at the output end of the gear assembly, these ~ly-wheel units being indicated by the reference numerals 15. 16. 17. 18. 19 and 200 Aa shown, three o~ the fl~-wheel units, i.e. 15. 16 and 17 are ~ecured to the pulley 37, by screws and dowels 68 and 69, and the other three discs 1~. 19 and 20 are locatcd in ~1 inoperat$ve position adjacent to the pulley 37 on a stationary bush 70, these latter three units 18. 19 and 20, are not revolvi.n~, and are held stationary by belts and nuts 71 and 72 in the carrier 11 , - . . .
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:.' ' ,; . ~ , - ~ . , , ~0~32001) The purpose of providing the flywheel units, 18,19 and 20 or more if required, is to enable the effective weight of the revolving fly-wheel disc unif.s, 15, 16 and 17, to be varied, to ensure that the pulley 37 runs smoothly, these re~olving fly-wheel discs 15 9 16 and 17 being secured together by bolts and nuts 73 and 74 lhu, ~lywheel disc units ~an be added to, or removed from, the fixed pulley a~ desired. Similarly, at the input end of the as.~embly, are shown further fly-wheel disc unit~, 21 to 25, -these being attached to a hub 26, keyed or pegged to the worn,wheel 29, Rhaft, by keys or pegs 67 and revolving at the same speed a~ the first unit input discs 21 to 25, that is to say at 8 r.p.m.
; In order to drive the gear assembly, a 1440 rOp.m.
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motor 27 i~ provided, mounted on suitable framework 75, and fixed on a base plate or foundation base 76. Thus for a 1 inch diameter input pulley 38~ making 1440 r.p.m.
driving onto a 4~ inch diameter pulley 39, output from the latter would be ~20 rOpOm. which latter would be the epeed of the ~ingle pitch worm 28, which drives a 40 tooth wormwheel 29, mounted in a framework 77, attached to the ba~e plate or foundation 76, so that the output r~p.mO of the wormwheel 29 would be 34 i.eO 8 rOpOmO Although the apparatus illu~trated is not shown with any form of covering or oil bath lubrication, such equipment would be ' - . . . . . : , - . . . . .
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provided as required. Also intermediate gears 79 are shown in the epicyclic gear assemblies 12, 13 and 14 and the epicyclic gears framework, which acts a9 the input disc 36, is secured by tie bars 78. Also a hub 174 is al30 attache~ b~ screws 175 and dowels 176 to the input flywheel discs 21 to 250 Turning now to FIGo 20 it will be seen that the gear C 33, is larger than the comparable gear o~ FIGo 1 o in fact the gear C 33 i9 twice the diameter of ~TGolo that is to say it iB 6 inches diamete.r 80 that in this arrangement the ,.
observed and actual revolu~ions of the centre freely revolving gear D 35 of 1~ inches diameter, when one revolution of the input disc 36 is considered, would be A x C + 1 which i9 ~+1 which i8 2 ~ 4 + 1, i~eO .
9 r,p,m. ror centre gear D 35 ~ but in the case of this gear assembly, the input di~c 36 makes lo 35 revolutions, this resulting from a pulley 40, o~ 1~ inches diameter on the spindle of a 1440 rOpOmO motor 27 driving a 1 inch diameter pulley 41 attached to a worm 28 9 driving a wormwheel 29, so that the observed and actual revolutions of the tirst : a~sembly external centre gear D 35~ would be 1~35 ~ 9 which i~ 12.15 (~or convenience the rOpOmO l9 assumed to be 12), ~he~e 12 observed and actual revolutions are trans~erred to I the second unit 9 and become the input for that unit O
Assuming the second unit to have gears of the same size as -8- ;
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the first, then the centre gear D ~ 9 in the second unit assembly would make 12 x 9 iOeO 10~ observed and actual revolutiGns (si.nce the actual and observed revolutions of the f.-rst centre gear D 35~ are 12~15, the actual and observed revGlutions of tha ~econd gear D 35~ will be a~sume-l to be 109. The 109 revolutions of this unit become the input o~ the third assembly 9 SO that the actual and observed revolutions of the third as~embly would be 109 x 9 or 981, assuming the gears of the third assembly to be exactly t.he same as those of the preceding two as~emblies. A pulley 37~ attached to the output of the third assembly, therefore, would make ~81 rOpomo which of course would be the rate of revolution of those flywheel di~cs 15, 16 and 17, which are attached to the pulley 37 by screws 68 and dowels 69. As in the arrangement of FIG,l. there are further flywheel 18019 and 20 adjacent .
to the output pulley ~7, 80 that smooth running of the latter can be achieved, and ~imilarly there are a group of flywheel disos 21 to ~5, at the input trO the unit, the~e latter di~c~ being attached to the fir~t assembly hu~ 26, and input disc 36 and thus they would rotate at 1035 rOprm.
Again a 1440 rOp.mO motor 27, is utilised, mounted on suitable framework 177 and Irixed on a base plate or foundation 118. So that with a 1~ diameter inch pulley 40, on the output shaft o~ the motor 27, dri~ing a 1 inch :
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~0~2~00 diameter pulley 41 which serves as the input, via a worm drive 28 and 29 mounted in a framework 112, attached to the base plate or f'oundation base 178, to the gear assemblies 9 the 1 inch diameter pulley 41 would De revolving at 2160 rO~OmO to drive a single pitch worm 28 and 40 tooth wor~wheel 2g, so that the latter would ~e rotating at 2160 divided by 40, iOeO 54 rOpOmO In the particular arrangement being described, a second single pitch worm 28 is provided and driven ~'rom the fir~t worm-wheel 29, so that its rate of revolution would be 54 r.p.m.
and assuming this drives a second 40 tooth wormwheel 29, the output rOp.mO o~ the motor 27 is reduced again to provide the lo'S5 r.p.mO input speed for the first gear assembly. Also intermediate gears 8~ and 81 and 82 are shown in the epicyclic gear assemblies 120 13 and 14 and the epicyclic gears ~ramework, which acts a~ the input disc ~6 i3 secured by tie bars 78. Also a hu~ 174 is also attached by screws 175 and dowels 176 to the input flywheel di~c~ 21 to 25. l'he assembly in other respect~
coniorms to that previously de~cribedO
Referring now to ~'IG.30 it will be seen that this di~ers ~rom the arrangements o~ FIGS o 1 and 2 in that the fixed gear in this arrangement i9 of 9 inches internal' diameter ~ixed gear ~' 31, secured to base plate or ~ound-ation base 179 ~y screws 180. ln thi~ arrangement, the . .
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` ~ ~o~ v gears B 32 and C 33, and the centre freely revolving centre gear D 35 are the same as in FIG~lo that is to say the gear B 32 is of ~ inch d-ameter and the gear C 33 and D 35~ are respectively ~ inches and 1~ inches diameter.
In tnis arrangement the observed and actual revoluticns of the centre freely revolving 1~ lnches diameter centre gear 0 35, for each one revolution of the input di~c 36, would be $ x D + 1 which i9 ~ ~ + 1 which is -12 x 2 + 1 io eO 25 rOp ~mO
However in this particular arrangement, the input disc 36 make~ 00072~ revolutions, 80 that the observed and actual revolutions of the first asqembly external centre gear D 359 would be 000726 ~ 25 that is 1.815 r.p.mr and these actual and observed revolution~ are transferred to the second assemblY, that is, the 1.815 rOp~mO becomes the input Yor the second assembly which latter being of e~actly the same construction, in so Yar as gear ~izes are concerned, as the first assembly, will result in the output centre gear D 35 of that assembly making 10~l5 X 25 revolutions, that i~
to say, the output r.p mO o~ the second unit would be 450375 rOpOmO observed and actual revolutions, and of course, this becomes the input f~r the third unit, which again, since it has ~he same ~ear ~izes and construction as the preceding two, would result in an output o~ 45,~75 x 25 which i~ 1134 rO pOmo observed and actual revolutions, and it is thi~ 1134 rOpOmq which is applied to the pulley ~7 and its . ~ '.
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' ~ '' . ' ' ~ ' ' ' ' ~ ' ' ' attached flywheel discs 5 15 a 16 and 170 As in the previous arrangements9 additional flywheel discs 180 19 and 20 are provided in order that the effective weight of the revol~ing flywheel 150 16 and 17 can be modified as desi~ed 9 to ensure smooth rotation of the pulley 370 Al 30 as in the previous arrangements, a plurality of flywheel di~cs 21 to 25 are provided at the input end of the gear assembly and between the input disc 36 and the worm drive arran~ement to that disc.
In the arrangement of ~IG.3~ the input rOpOm~ of 0,0726 i~ derived from a 1440 rOpOmO motor 27, mounted on the base plate or foundation base 179 by the use of a 1~ inch diameter pulley 42 on the output shaft of the motor 27, driving a 15~ inch diameter pulley 43 to reduce the rOpOmO of the second pulley shaft to 116 which is the ~peed of rotation of the firæt single pitch worm 28, mounted in a framework 113 9 attached to the ba~e plate or ioundation base 179 which drive~ a 40 toothed wormwheel 29.
So that the reduction in ~peed from 1440 rOpOmO at the first wormwheel 29 i6 to 209 rOpOmO which is utili~ed as the rate oi rotation of the second worm 28 which dri~es a second 40 toothed wormwheel 29, to further reduce the speed from 2.9 to 000726 rOpOmO Also ~ntermediate gear~ 83 and 84 are shown in the epicyclic gear assemblie~ 120 13 and 14 and the epicyclic gear framework, which acts as the input di~c 36, -12- .
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o~ o is secured by tie bars 780 Also a hub 174 is also attached, by screws 175 and do~lels 176 to the input flywheel discs 21 to 25. The assembly in other respects conforms to that previously describedO
The arrangement of FIGo 4O is to some extent similar to that of FIGu 3o the primary exception being, that the gear C 33 of FIGo4a is 0~ ~ inch diameter whereas in FIGo 3O the ~ear C 33 has a 3 inch dia~eter~ In the arrangement of FIGo 40 the ob~erved and actual revolutions of the 1~ inoh diameter9 freely reYolvi.ng centre gear D 35 will be B x D + 1 that is ~ x ~ + 1 which i8 12 x 4 + 1 which is 49 rOpOmO for the centre gear D 35.
Thu~ 49 rOpOmO would be the input speed for the input o*
the second assemblyv and thus the output observed and actual revolutions of the second gear unit assembly would be 49 ~ 49 namely, 2401 r.pOmO which become the : input revolution~ for the input of the third assembly, the output from which would be 2401 x 49~
Such a high speed output would find little practical -application and thus to bring down this output speed to an output of the order of 1000 rOpOmO an extremely large worm-whee~ 44 or a number of smaller worm or wormwheels, driven by worms 28, mounted in a framework 114 attached to the base piate, or roundaticn base 181, are required at the input i ' .
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end of the gear trainO These assemblies are not shown since the principle of reducing the output speed of the p~ime mover, by the use of wormwheels and worm drive3 iæ illustrated in FIGSo 1 to 3 referred to pre~iously~ Also intermediate gears 85 and 86 are shown in the epi~yclic gear a~semblies 120 13 and 14 and the epicyclic gears Lramework which acts as the input di~c 36 i~ ~ecured by tie bars 780 Also a hub 174 is al~Qo attached, by screws 175 and dowels 176 to the input ~lywheel discs 21 to 250 The assembly in other re~pects conforms to that previously describedO
Re~erring now to FIG~ 50 of the drawings the gear unit there illustrated i9 ~ in ~act, a combination of one of the gear a~semblies of FIGo 30 and two of the units of FIG.l. arranged such, that the gear unit o~ the kind illustrated in FIGo 30 becomes the first unit of the mechanismO Thus when considering one revolution of the input to the ~ir~t gear unit it wlll be observed that the actual and ob~erved revolutions o~ the freely revolving centre gear D 35 which in this case is 1~ inches diameter would be B x C + 1 io eO ~ ~ ~ + 1 io eO 25 re~olutions which become~ the input speed o~ the input of .
the second unitO
The observed and actual revolution~ of the second unit which again haæ a freely revolving 1~ inch diameter centre ~
A C 1~ ~ 3 gear D 35 would be B ~ D + 1 iOeo ~ x 1~ +
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which i~ 5 revolutions. So that the output revolutionsof the second unit would be 125 9 and this becomes the input to the third unit which, ~ince its gear train i3 exactly the same as that of the second unit, results in an output of 5 ~ 125 r~p~m~ which is 625 rOpOmO
Now, if at the output end, a 1~40 rOpOmO drive motor 27 mounted on suitable ~ramework 182 and fixed on a base plate cr foundation base 183 is provided with a 1~ inch diameter pulley 45 driving a 15~ inch diameter pulley 46 the latter would have 140 rOpOmO which would be the same rate of revolution, as a 1~ inch diameter pulley 47 mounted on the same shaft as the 15~ inch diameter pulley 46, thus if the drive from the 1~ inch diameter pulley 47 is now taken to a 3 inch ~iameter puïley 48, the revolutions of this latter pulley 48 wpuld be 70, and .
thio pulley 48 is adapted to drive a worm 28, meshing with a 40 toothed wormwheel 29~ mounted in a framework 115, attached to the base plate or foundation ba8e 183, which gear is attached to the input o~ the ~irst gear assembly, via the *lywheel discs 21 to 250 So that the input would be 40 r,p.m.
namely 1075 rOpOm~ and this gives 43075 rOpomo observed and actual revolutions of the first unit ~reely revolving centre gear D 35, this rate of revolution being the same as the input revolutions of the second gear unit~ So that the observed and actual revolutions of the second unit would be l .
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43.75 2 5 namely 218~75 which becomes the input revolutions of the third unit, the output of which becomes the input revolutions of the third unit, the output of which becomes 21~.75 x 5 namely 1094 r~pOm.
which is the rate nf revolution of the pulley 37,attached to the output flywheel discs 150 16 and 17 by screws 68 and dowel3 69 9 as the latter would also be revolving at 1094 rDpOmO on the spindle. As in the previous arrangements, additional ~lywheel di3cs 180 19 and 20 are provided on a non-rotar~ extension of the spindle 70, so that the weight of the revolving flywheel di.scæ 15, 16 and 17 can be varied as requiredO Also intermediate gears 87 and 88 and 89 are shown in the epicyclic gear assemblies 120 13 and 14 and the epicyclic gears ~ramework, which acts as :
the input disc 36 is secured by tie bars 78. Also a hub 174 i9 also attached by screws 175 and dowels 176 to the input ilywheel discs 21 to 250 The assembly in other respects conform~ to that previously described.
Referring now to FIG 6. it will be seen that the arrangement is somewhat ~imllar to that of FIG.50 It should be noted,however, that the fixed gear A 30, in this particular ca~e of the centre gear as~embly, is of 3 inch diameter, whereas in the FIGo 50 arrangement it was of 1~
I inch dlameterO It will also be noted, that the third gear I assembly o~ the FIG~ 6 arrangement, i~ like that of the FIG.5 .
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arrangement, with th~ ~ixed gear A 30, of 1~ inch diameter, and thus taklng the gear tr~in as a whole, and assuming, one revoluticn of ~he input disc 36, then in the first assembly, the observed and actual revolutions of the freely revolving centre gear D 35, which is of li inch diameter would be :~ x D + 1 namely i.e. 12 x 2 + 1 namely 25 rOp.m. 'l'his of course becomes the in~ut revolutions of the second gear assembly, in which the observed ~ld actual revoluticns o~ the ~reely revolving 1~ inch diameter centre gear D 35, would be B x D l 1 that i9 to say ~ x ~ + 1 namely 4 x 2 + 1 iOeO 9 r.p.m.
thus the output becomes 225 r.p.mO namely 9 x 25 observed and actual revolutionsO The input revolutions therefore, of the third assembly, becomes 225 and the output rate of revolution of the ~reely revolving centre gear D 35,which i8 o~ 1~ inch diameter would be 225 x 5 namely 1125 rOp.mO
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and this would be derived from B x D + 1 that is to ~ay ~F x 1~ + 1 which i9 2 x 2 + 1 which is 50 If one now applies an input drive to the ~irst gear unit derived ~rom a 1440 rOpOmO motor 27, mounted on suitable framework 184, attached to the base plate or foundation base 185, driving a 40 toothed wormwheel 29, mounted in a framework 116, attached to the base plate or foundation base 185, to give 36 rOpOmO drive to a second worm 28y also driving a 40 toothed wormwheel 29, which applies drive to : : - . - . - .
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~ 10~
the first gear assembly, then the drive to this assembly would be 40 namely 009 rOpOmO So that the actual and observed revoluticns o~ the 1-'- inch diameter freely revolving centre gear D 35 of the first unit, would be 2205. The output re~olutions of the second unit wo~ld be 2205 x 9 namely 202c5 and the third unit assembly would have an output of 20205 x 5 namely 101205 rOpOmO This in practice would be the rate of revolution of the pulley 37 9 attached to the flywheel discs 150 16 and 17 by screws 68 and dowels 69 and also of course the rate of revolution of the flywheel discs 150 16 and 17. As in the previous arrangements additional flywheel discs 180 19 and 20 may be mounted on a non-rGtating flywheel bush 70 adjacent to the flywheel discs 15. 16 and 170 80 that its effective woight may be varied to suit requirementsO As in all previously described assemblies, there would be a sump for lubricant, and of course, the mechanisms would be enclosed within a suitable casing. A190 ~ intermediate gears 90-91-92-93-94 and 95 are shown in the epicyclic gear a~semblies, 12, 1~ and 14 and the epicyclic gears framework, ~which acts a~ the input disc 36 is secured by tie bars 780 Also a hub 174, i9 also attached by screw~ 175 and dowel~ 176 to the input flywheel discs 21 to 250 The assembly in other respects conforms to that previously describedO
S
' .: .
. .
~ :, - . ~ . , - - . . ~. ..
. .. . . : :
~6~82~
Referring now to FIGo7 it will be seen, that the arrangement is similar to that of I~IG o 1~ but in this particular case, an intern.~ 9 inch diameter gear FD 34 haæ been substituted for the 1~ inch diameter external centre gear D 35, of FIGo 1 o Additionall~, the gear C 33 in the arrangement of FIG~7 is made 3~ inch diameter, and thus when one revolution of the in~ut disc 36 i9 considered, then in the fir~t gear assembly, the observed and actùal revolutions of the freely revolving gear FD 34 will be A x C + 1 nc~melY~ ~ 9 +
that ia to say lo 5/6ths observed and actual revolutionsO
~his becomes the input revolutions for the second assembly, which is exactly the same in construction as the first as~embly, so that the observed and actual revolutions of the second assembly will be 105/6ths x 105/6ths, that is appro~imately 3036 rOpOm~ which becomes the input for the third aesembly, which is exactly the same, in construction, as the previouRly de~cribed as~emblie~. ~o that the revolution~ at the output of this assembly, will be 3.~6 x 105/6ths which is appro~imately 6016 observed and actual revolutions.
Now if one applies a 1440 rOp~m. prime mover 27,mounted on the base plate or foundation base 186, to supply the input power, for the gear train, and assuming that this has a 1~ inch diameter pulley 49~ driving a 6~ inch diameter - .. . . . ~
- . . . .. .
pulley 50, the output rOpOmO would be 332, which is applied to a 1~ inch diameter pulley 51, carried on the same shaft as the 6~ inch diameter pulley 50, mounted in a framework 117~ attached to the base plate or foundation baæe 186 ~nd this serves to drive a 3 inch diameter pulley 52, attaçhed to a hub 174, whieh is attached to input ~lywh~el di~cs 21 to 25; by screws 175 and do~el~ 176 of the gear assembly~ The input therefore.to the gear assembly would be 166 rOpOmO so that the output from the ~irst gear unit would be 304 r~p~mO of the second unit 558 r.p.m.
and oi the third unit 1013 rO pO mO Thus the speed of a pulley 37, at the output end of the gear assembly is 1013 rOpOmO
which iæ the same rate of revolution as the flywheel discs 15. 16. and 17, attached to the pulley 37, by screws 68 and dowels 69, attached to a driving hub 188, which flywheel disc~, as can be seen, is o~ a similar form to that described in the preceding arrangement 9 namely, it is capable o~ having its mass either increased or decreased by the addition or removal of disc like ~lywheel element8 180 19 and 20. As in the previous arrangements a number of such elements are provided on a non-rotary bush 70 t adjacent to the flywheel discs 15. 16 and 17~ Al~o intermediate gear~ 96 and 97 are shown in the epicyclic gear assemblies 120 13 and 14 and the epicyclic gears ~ramework, which acts as the input disc 36, i9 secured by tie bars 780 Also a hub 174, is also ' .
.
.
. - ' ~ ~ .-. -: . ' ,. .. .
: - : -: .. : -, :
.: . ,,, -:
: :-- :: .:
- . , - - . - ~
.
-. . .
attached by screws 175 and dowels 176 to the input flywheel discs 21 to 25 and to the pulley 520 The assembly in other respects con~orms to that previously describedO
In the arrangement according to FIG ~ 8~ the gear assembly is somewhat similar to that just described 9 in that the first and middle and last gear assemblies are similar to those shown in FIGo 7 but in this particular case a 1-~ inch diameter centre gear D gear 53 which is freely revolving on the f.ixed shaft 10, has been added to the last gear as,sembly. This latter centre gear, D gear 53 is driven by ordinarily revolving gears 54 and 55 running on spindles l9G secured in framework 191 ~rom the inaide gear perimeter of the output gear FD 34 o~ the last o~ the gear assemblies, namely a 9 inch diameter internally toothed gear FD 340 So that when one revolution of the input disc 36 is considered in the first gear unit assembly, the observed and actual revolutions o~ the 9 inch internal diameter gear FD 34 would be ~ x C ~ 1 namely ~ x ~ + 1 which~ as in the arrangement of FIG.7 gives an output of observed and actual revolutions of 1 ~nd 5/6ths which becomes the input to the second unit, which since it is of e~actly the same construction as the first will ha~e an output 3036 rOpOmO
and the third unit will have an output of 6 o 16 actual and observed revolutionsO
' : . : . -.. .
: . ~ . : . , ,: :
2~
In this particular case however, the 1440 rOpomo prime mover 27 mounted on the base plate or foundation base 189 is provided with a 1~ inch diameter pulley 56 to drive a 15~ inch diameter pulley 57 to give a 140 rOp.mO at the pulley and 140 rOpOmO of a 1~ inch diameter pulley 58, mounted on the same shaft as the 15~ inch diameter pulley 57, mounted in a frameworX 118, attached to the base plate or found~tion base 189~ ~his latter pulley 58, itsel~
drives a 7~ inch diameter pulley 59 to give 28 r~pOmO which is the input speed of the first gear asæembly 9 and of course the flywheel disc~ 21 to 25 ~ at the input end o~ the machine~ -Thus the output rOp~m~ of the first gear unit will be 28 x 1~ 5/6ths that is approximately 51 rOpOmO The output from the second assembly would be 51 x lo 5/6ths, which gives approximately 94 r.p.mO and thus the output from the third assembly is 94 x 1.5/6th~ which is appro~imately 172 o 33 rOpOmO ~hus 172.33 rOp.mO is applied, by ordinary revolving gears, 54 and 55, running on spindles 190, secured in framework 191, to the l~ inch diameter freely revolving centre ~ear D gear 53 to result in the output speed of 1034 rOpomo namely x 9. The speed of the drive pulley 37 ~ attached to ~lywheel discs 150 16 ~ld 17 by screws 68 and dowels 69 and the speed of flywheel di~cs 150 16 and 17 at the output end o~ the gear arran~ement is thu~ 1034 rO pOmo As in the prevlous arrangements, adjustable mass flywheel di~cs . .
.. . . . . . . .
:. ' ' ' ' . , - ~
, ~ : - ~. . .
.
18. 19 and 20 are provided J as of course is a sump, for lubricant and a cover for the mechanismO Also intermediate gear~ 98 and 99 are shown in the epicyclic gear a~semblies 120 13 and 14 and the epicyclic gears framework ~hich acts a~ the input di~c 36 9 iS ~ecured by tie bars 7~O A180 a hub 174 is also attached by screws 175 and dowe]s 176 to the input flywheel discs 21 to 25 and to the pulley 59O ~he assembly in other respects conforms to that previously describedO
Turning now to FlGo9 it will be seen that there is an arrangement in which the gear assembly i8 similar to that just described in that a 1~ inch diameter centre mounted ireely revolving centre gear D gear 53 is provided at the output oi the third gear assemblyO It will be noted,however, that a similar ireely revolving centre gear D gear 53 has been provided at the output of each o~ the other two gear assemblies, and thus assuming in each case that the output ~ear o~ the gear a~8ernbli.ee i8 a 9 inch dlameter internal gear FD 34 and that in each case this drives a 1~ inch diameter freely revolving gear D gear 53 by means o~ ordinary re~olving gears 54 and 55, running on spindles 190, secured in *r~ework 191, then the ~ituation when one considerc one re~olution of the input disc 36, i~ that, in the first gear asseMbly the ob~erved and actual revolutions oi the ireely revolving 9 inch intérnal :~
diameter gear FD 34 will be A x F~ ~ 1 namely ~ ~ ~ + 1 ~.
i.e, 1.5/6ths revolutions actual and observedO This 1O5/6ths ~ r.p.m. oi the ~ear FD 34 i~ now transierred to the 1~ inch .l -23-! . . .
.. . .
;. , ' '' ' ' ' : ':
: . ,: . .: , ' : , ': ' : ' . . . - ' 2C~90 di2meter freely revolving centre gear D gear 53 by means of two fixed spindle 9 or fixed axis gears 54 and 55 9 previously described as ordinary revolving gears 9 so that the speed of the 1~ inch diameter revolving gear D gear 53 would be 105/6ths x g divided by 1~, that is approximately 11 rOpOmO It follows that 11 rOpOmO is the input e~eed ~or the second gear assembly so that~ since it is identical in construction to the first assembly9 the output will be 11 x 105/6ths that is approximately 200163 rOpOm.
at the 9 inch internal diameter revolving gear FD 349 thus the speed of the 1~ inch diameter freely revolvirlg centre gear D gear 53 of this assembly is 200163 x 9 divided by 1~ that is app~oximately 121 rOpOmO As can ~e seen from the drawing, the drive tO the second centre gear D gear 53 : is via two ~ixed centre, or fixed axis gears, 54 and 55 described as ordinary revolving gears 54 and 55, the first of' which is driven, by the internal 9 inch diameter gear FD 34. In this gear train 121 rOpomo i9 the input speed of the third gear assembly 9 wh.ich being identical in oonstruction to the previous two assemblies, gives an output o~ 121 x 105/6ths iOeO 222 rO~OmO at the 9 inch diameter gear ~D 34, 80 that the speed of the third 1-~ inch diameter f'reely revolving centre gear D gear 53 will be 222 x 9 divided by 1~ which is 1~32 rOpOmO
' , ~ -24-. . . ~ , .
-- ~ ' , , .
. ~ : . , - - . . ::
o~c)o~
If, at the input end of the gear assembly there is provided a 1440 rOpOmO prime mover 27 mounted on the base plate or foundation base 192 with a 1-~ inch diameter pulley 60 on its output shaft, dri~ing a 1~ inch diameter pulley 61 the speed of the latter pulley 61 will be 1234 r~0m.
and i~ this pulley 61 drives a worm 28 that in turn drives a 40 toothed wormwheel 29 mounted in a framework 119, attached to the base plat~ or foundation base 192, this first wormwheel will have 30085 rOpOmO This rate of revolution will be the same as that of a second wor~ 2~
upon which the first wormwheel 29 i8 mounted, and if the second worm 28 drives a 40 toothed wormwheel 29 the output r.p.m. will be 0~77 namely 40 Thus in this assembly the input speed of the first assembly would be OD77 rOp0m0 and the speed of the first 9 inch diameter gear FD 34 would be 0077 x 105/6ths that is 1.4116 rOp.mO with the output speed of the gear FD 349 at 104116 the freely revolving centre ~ear D gear 53 wlll b~ rotating at 8045 I _.4116 x ~
,I r.p.m. that i8 1~ and thus 80 47 becomes the input speed for the input of the second assembly0 The output of this second assembly is that the speed of the gear FD 34 I will be 8047 x 105/6ths that is 150528 rOp0m. and thuq j the freely revolving centre gear D gear 53 of this assembly 15O52~ x 9 will be 1~ to gi~e 93D17 rOp.m0 as the input speed . I . ~
of the third assembly, and thus the output speed of the gear FD 34, of this assembly, will be 93017 ~ 1.5/6ths, namely , ~, .
I' -25-: ~ , , . .. ~, .. . .
- .: . : ..
-.
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, ~ . ' '. ' . . '' ' . ' ~o~z~
17008 rOp~mO The output from the third freely 170 8 x .
revolving centre gear D gear 53 will therefore be -1 that is 1024 rOp~mO ~he output pulley ~7 secured b~
screws 68 and dowels 69 to the variable mass flywheels 15. 16 and 17 attached thereto will therefore have a speed o~ lG24 rcp.mO Also intermediate gears 100 and 101 are shown in the epicyclic gear as~emblies 12~ 13 and 14 and the epicyclic gears framework, which acts. as the input disc 35 is secured by tie bars 780 Also a hub 174 is also attached by screws 175 and dowels 176 to the input flywheels 21 to 25 and to the second wor~wheel 290 ~he as~embly in other respects conforms to that previously describedO
~ he arrangement~ ~hown in FIGSo 1 to 9 previou~ly described~ all illustrate three sets of gear assembly units and clearly these could be built as separate unitæ 9 ehown in FIGo 1~ or as a complete assembly. By increasing the number of gear assemblies, for example, by coupling together one or more o~ the gear trains described, it is possible to pro~ide an arrangement in which an extremely low input drive speed can be applied, thereby enabling the gear a~sembly to be utilised, ~or example9 for weight lifting, in for example cranes or the like, or in weight balanGirlg mQchines or apparatusO In this latter case1 the apparatus can be adapted to operate in such a way that ~or one , -26~
.
, :, , . . . - , . ~
.-~ , ,. :
: - - . : : . -: - :
c f~ 2()~o revolution of the input of the first ~,ear assembly and also one revolution at the output of a similar gear a~sembly 9 one can have the situation in which a small diamet2r central output ~ear D 35 or a gear D gear 53 - as in FIG~10 is making *or example 1000 r~ p O mO to result in one re.volution of an extremely large gear 62 in mesh therewith 9 thi~ large gear 62 making one revolution in compari~on to one revolution of the input (the output en~ o~ such a gear train i~ shown in FIGolO)o However an extremely large gear wheel may result in design dif~iculties and thus it ls envisaged that the same re~ult could be obtained by substituting for the very large gear, a compound reduction gear of the kind shown in FIG~ Alternatively as shown in FIG~12 worm and wormwheel reduction means.may be employed with bevel wheels 193 aubstituted for the gear D gear 53~ these bevel wheels 193 driving a worm 28 and wormwheel 290 ., : Al~o it would be noted that previou~ly the FIG~. from 1 to 9 concern an external ~ixed gear A 30 and an internal -~ixed gear F 31 and a centre revolving gear D 35 or internal revolving gear FD 34 driven by integral epicyclic gears 32 and C 33, these integral gears B 32 and C 33 being o~
di~erent diametersO
: 1 .
Now in FIG~ 14 and FIG~15 examples are shown, with a . -27-,.. :,. , .
., . , . . :
- : ~
~ ' ' ' . - . ' ' : ' ' ' . ':
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.
fixed internal gear F 31 utilised with a freely revolving internal gear FD 34 with the integral gears B 32 and C 33 now being of equal diameters with intermediate gears 102 in ~esh with gear C 33 and freely re.volv.i~g.gear FD 340 ~o that the observed and actual revolutions of the ~reely revclving gear FD 34 would be B x FD + 1 and when F=9, B=3, C=3 and FDL9 then 3 x 9 + 1 -- 1+1 _ 2 actual and observed revolutions of internal gear FD 34~
FIG~15 i~ similar to FIGol4 but in FIGol5 a series oi ordinary revolving ~ears 540 55 and 63 running on spindles 190 securéd in a framework 191 are in mesh with the internal revolving gear FD 34 and a centre gear D
gear 53 say for example of 1,'- inch diameter. Also are shown the fixed spindle 10 with carrier 11 and the input disc 36 and flywheel discs 21 to 25 ahd securing screws 1800 Also when a fixed internal diameter gear F 31 1 utilised with integral gears B 32 ~nd a 33 of equal diameter as shown in FIGo 16 then in this case the gear C 33 .can be omitted and the assembly would then be as in FIG 17 . ., with the gears B 32 in me~h with a centre ~reely revolving gear D 35, the gears B 32 running on spindle~ 103 secured in the input discs 360 So that when F~9, B=3, C-3 and D=3 then the actual and observed revolutions of centre gear D 35 would be B x D + 1 which is 3 x 3 ~ 1 = 3 + 1 = 4 !
~!
. .. . . . . . . . ~ . .
.. ...
2~
and when C ~3 is omitted9 then the actual and observed F omitted C same size as B
revolutions D 35 wo~ld be B x D
+ 1 or actual and observed revolutions of D 35, are F x B ~ 1 so that F=9, B=3, B=3 and D=3 then B x D~ + 1-3+l=4~ Also are shown the fixed spindle lG, with carrier 11 and the input disc 36 and flywheel disc 21 to 25 and securing screws 18C~
Also as in FIGD 18 an external fixed gear A 30 could ~-be utilised with an external freely revclving gear D 35 with equal diameter integrc~ gears B 32 and C 33 and intermediate gears 104. So that the observed and actu~1 revolutions of the freely revolvi~g external gear D 35 would be B x D I 1 and when A=3, B=~, C=3, DL9, then ~ ~ I
3 x 9 ~ 1 = 1 x ~ + 1 = 1-~ actual and observed revolutions j o~ external gear D 350 ~ IG. 19 is similar to FIG~ 18 but in FIGo 19 ordinary revolving gears 54 and. intermediate gears 104 and 105 are in mesh with the external revolving gear D 35 and al~o with a centre gear D gear 53 the ordinary revolving gears 54 running on a spindle 190 in a ~ramework 191 attached to the baseO Also are æh~wll the fixed spindle lO,with carrier 11 and the input disc 36 and ~lywheel di~cs 21 to 25, Also in FIG. 20 is shown an external fixed gear A 30 utilised with an internal ~reely revolving gear FD 34 with .. . .~ . . : . :
. .
, , ~ , .
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~ 10~0~
equal diameter integral gears B 32 and ~ ~3 so that the observed and actual revolutions of the freely revolving A C
internal gear ~D 34 would be B x ~'D + 1 and when A=3, B=3, C=3 and FD=9 then 3 x 9 ~ 1 = 1 x ~ + 1 = 1~
actual and observed revolutions of internal gear FD ~4O
FIG~ 21 is similar to FIGo 20 but in FIG~ 21 the gear C 33 has been om~tted and the gears B 32 ~un on spindles 103 in the input discs 36 and the actual and observed reYolution~ of internal gear FD 34 l~ould be B x ed C same size as B
h'D -~ ~ 1 or actual and observed revolutions of internal gear ~D 34 = B x FD + 1 A B
So that when A=3,B=~,BL3,and FD=9 then B x ~D + 1 =
x ~ + 1 = 1 x ~ + 1 = 1~ actual and observed revolutions of internal gear ~D 340 Also are shown the fixed spindle 10 with carrier 11 and the input discs 36 and flywheel dlscs 21 to 250 Also as in ~IGSo 22 to 27 when the gears, other than the gears with their axi~ on the centre fixed shaft 10 are revolving epicyclicly round the axis of the centre ~ixed shaft 10, then the centrifugal force of these orbiting gears would be taken into ccnsideration and to neutralise the ei~ect of the centrifugal force so caused 9 rollers as in FIGS. 22 to 27 could be attached to the orbiting assemblies, a~d these rollers 64 would run upon a metal ring or rings 65 - ~
,, . . , - . . . . . . . ..
... . , . . -. . ,- .
- . : . . : - . - . -. - . ,. . : . . ~ : ., , : -- --:
'. -' . '' ' ', ~ ~ , - ~ ., - , . ~ . , . .. :
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recessed into the housing or casing and secured with screws 106 and dowels 1070 These rings 65 could be solid~ or ~or larger assemblies a ring constructed of segments could be utilised 9 bolted and dowelled in position, to the hou3ing or casing, ~nd al90 the rollers 6~ and centrifug~l pressure rings 65 could be hardened and ground ~or enduranceO Alsop oil filler plugs 108 and sealing rings 109 would be incorporated in the housings or casings 9 for oil filling and drai.ning purposes, and the fixed internal gears 31 could also be secured to the housings or casings with screws 110 and dowel8 lll o Also in FIGo 28~ FIG~ 29 and FIG. 30 are shown flywheels at the input and output ends of the unit - i mechanism assemblies and also in between each unit, -in the mechanism assemblies and also with no input flywheels and none between each unit, in the mechanism assemblies but ju~t with the final output flywheels or flywheel mass only as in FIGo310 So that when considering FIGo 28 and when the flywheels are all of similar diameter~ then flywheel 120 would be say of mass 19 revolving say at 8 rOpOmO and flywheel 121 would be revolving 5 times as fast at 40 rOpOmO and would be 3 mass in comparison to flywheel 1200 Similarly ' .
' ' -~ ' ' .,-'.- , :
, . . . , ' ~ , , - ' , : ~ . ', ' ' . .
. . .
.
; ' '' ' ' ' ' . ~ `
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~lywheel 122 revolving at 200 rOpOmO that is 5 times faster than flywheel 121 would be 25 mass by comparison to flywheel 120 and flywheel 1210 Similarly flywheel 123 revoJ-~ing at 1000 rOpOmO that is 5 times ~aster than flywheel 122 would be 125 mass by comparison to ~lywhesls 120, 121 and 1220 So that the momentums of each mass flywheel would be say9 1 x 8 _ 8 and 5 x 40 = 8 and 25 x 200 = 8 and 125 x 1000 =
8 and the kinetic energy o~ the flywheel masses would be say 1 x 8 - 64 and 5 x 40 = 320 and 25 x 200 = 1600 and 125 x 1000 _ 8000 iOeO rising in multiples of 50 .
When now the flywheel masses are reduced in diameter as in FIG~ 29 as 1240 1250 126 and 127 so that they are all of equal mass and their rotary velocity is also equal,0 then this would be as FIGo 290 80 that in FIG~ 29 the momentum o~ each mass would be equal, as in the previous FIGo 28 and now in FIG. 29 the kinetic energy o~ the mas~e~ would also be equal and masses 125 and 126 could be omitted, leaving ~;
mass 124 and 127 or masses 124~ 125 and 126 could be o~itted leavlng mass 127 alone as shown in FIG~ 310 .
When now in the gear arrangements as shown in FIGol I I
then ~or 1 revolution of the input disc ~6 the revolutions o~ the gear D ~5 are as B x D ~ 1 or ~ x which i~ 5 re~olutions. So that, when considering say one , : .
.
-~2-.
- , . . . - . - . .
-- . ; : ., ., ~ -. . . ~ .
: -~ ~O~Q~@~
unit, then when the input revoluticns and the output revolutions are made the same, say ~or example, 1 input revoluti.cn and 1 o~tput revolution, then the m~sses balanced~ would ~e as the ratio is of gear B 32 is to gear C 33 and in this case of FIGo 1~ this is ~ is to 3, namely a ratio of 4. So that considering the pre~ious FIG, 28 when the di.ameters al~ relative masses o~ the wheels were ~imilar, then the follGwing as in FIG~30 would apply, namely mass 128 would be say of mas~ 1 re~olving at say 8 rOpOm. and mass 129 would ~e of mas~ 4, revo].ving at 8 rOpomo and mass 130 would be of mass 16 revolving at 8 r.p.mO and mass 131 would be of mass 64 revolving at 8 rOpOmO
and this making the input and output revolutions equal, could ij be achieved by inserting reduction gearing between each unit, ..
a~ shown in ~IG.300 That is say the output gear D gear 53 of the fir~t unit i9 1~ inches diameter and meshing with the inch diameter gear D gear 53 is a gear 132 Gf 7~ inch diameter integral with which iR the ~ear 133 of 1~ inch diameter and meshing with thi~ 1~ inch diameter gear 133 is an intermediate gear 134 which meshes with the input gear 135 o~ 1~ i.nch diameter which i~ the input gear of tha second unit. So that the mass flywheel 129 i3 slowed b~ a ratio o~ 5, and ;-this arrangement i~ s~own applied to.the other units, and it would be noted that, if the intermediate gear 134 of the la8t output unit was made into 2 gearg ~ then reverse rotation. .
oi the mass 131 would occurO
~33 .. ~ .
.' ' `' : , ,' ' ~8 2~
Figo 31 is similar to ~IGJ30 but now the masses 128 129 and 130 have been omitted leaving mass 136 alone at the output endO So that now, when the input revolutions are multiplied by 125 to give 1000 rO~,mO input revolutions then the ~ollowing as in FIG. 31 would apply~ In FIG~ 31 the prime mover is a 1440 rOp~mO motor 27 on the shaft of which is a pulley 137 of lo 042 inch diameter driving an input pulley 138 of 1~ inch diameterO So that the input re~olucions to the first unit would be 1000 rOpOmO As the gears in the Pirst unit are as in FIGo 1 ~ then the output gear D gear 53 of the first unit would make 5000 r~pOmo and this 5000 rOpomo gear D gear 53 is in mesh with a 7 inch diameter gear 132 integral with which is the gear 133 of 1~ inch diameterO So that the revolutions of the 7~ inch diameter gear 132 and 1~ inch diameter gear 133 would be 1000 r.p.m. This 1000 rOpOmO gear 133 is in mesh with an intermediate gear 134 which in turn i9 in mesh with 1~
inch diameter input gear 135 of the second unit. So that the input speed of' the second unit is 1000 rOp~m. similar to the input speed o~ the first unit. Similar conditions would apply to the third unitO '~he units are supported on a channel 140, also supported on the framework 139 housing the reduction gears 53, 132 ~ 133, 134 and 135 these being mounted as shown in FIGo 31 on a base plate or foundation base~
FIG. 32 shows a centre gear D gear 53 being in mesh with intermediate gears 55 and 54 mounted in a bracket 191 and the intermediate gear 54 i1 in mesh with a ~reely revolving internal diameter gear FD 340 -- .- . : ~ , .. , . .. . - . - ~ -.
, , . . - . . . ~ ' ., , . - ~ . , : ~
.. , , . , . .~ ~ .. .
~0~2~00 ~ IGo 33 shows a similar arrangemen-t to FIG~ 32 but ~ow in FIGo 33 the rotation of the centre gear D gear 53 would be opposite to that in FIGo 32 o In FIGo34 and also if re~erence is made to ~IGol~
then when a similar gear assembly~ as that in FIGolo is uti.lised, as i.n the arrangement shown in ~IG. ~4 then when also re~erence i3 made to FIGo 30 then the gear arrangement as in FIGo 1 could be arranged as in FIG.34. That i~, fixed gear A 143 is 1~ inch diameter and gears B 144 are ~ inch diameter and gears C 145 are 3 inch diameter and gear D 146 i9 1~ inch diameterO So that the output revolutions of the gear D 146 would bs A x C + 1 which i8 ~ x ~ ~ 1 which is 2 x 2 + 1 which i8 5 revolutionsO So that the gear D 146 at 1~ ' -inch diameter would make 5 revolutions, and this gear D 146 o~ l~ inch diameter, making 5 revolution~ would al80 cau~e a gear D gear 142 also o~ 1~ inch diameter which is.
an e~tension o~ the gear D 146 to aleo make 5 revolution~.
~his 1~ lnch diameter gear D gear 142 making 5 revolutions now meshes with a 7~ inch diameter gear 141, ~o that this 7~ inch diameter gear 141 would make 1 revolutionO
Me~hing wi.th the fixed gear A 143 of 1~ inch diameter and the gears B 144 o~ ~inch diameter are the intermediate gear~
i47 of lt inch diameter and i~ the intermediate gears 147 were made into two ~eparate gears 9 then rever~e rotation of the assembly gears would take placeO
-35- .
.: . '~ , 1 -~ . .
'' - ' ' ~ . .
.: ' .
.. . . . .
ze~o~
~he gear A 143 is fixed, but the intermediate gears 147 and the gears B 144 and the gears C 145 which are integral and the gear D 146 are free to revolve5 and are located in frame bars 153 secured by tie bar~ 1580 These frame bars 153 being pivotted about a centre spindle 148 ~he 7~ inch diameter gear 1~1 is fixed to a bar 154 by screws 194 and dowels 195 and thi.~ bar 154 is free to pivot abont the ~pindle 14-9. The spindle 148 secured t~ - -bearing bracket~ 155~ by pegs 156 ~d spindle 149 are supported in the bearing brackets 155 9 the bases of whi~h would be secured to a bench or baseD In the frame bars 153 and 154 are ~ixed, spindles or studs 152, of equal length~ ~
; snd diameters, the centre pivotting distances of these stud~ s or spindles 152 being equidistant ~rom the pivotting centres 148 and 149. So that it could be said, that when the ~rame ~:.
bars 153 and bar 154 being equal in length are in horizontal parallel position as shown in FI~.34 then the mechanism assembly would be in bal~lce. So that now it could be ~aid that, when 1 re~olution of the frame bars 153 18 made, say in an anti-clockwise direction, round the fixed gear A 143 ~ecured to the ~pindle 148 by pegs 157 then this would cause the gesr assembly to revolve epicyclically round ~he flxed gear A 143 and 80 cau3e bar 154 to which is attached .
the 7~ inch diameter gear 141 to revolve al~o in an anti~
clockwise directionO
. ~ _ .
... . ' ' ~ :
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., . , . . : .. , :,.: ... . : -: . .. . . . :
:: . -:: - .
.. ... , . . . : . ~ .. ,. , ,. .: ~ . . .. ~. , .. -. . ... . . . . . .. ... . .. .. . . . ... .
When now, a mass weight 159 of say mass one is placed on the left hand spindle or stud 152 in the frame bars 1531 then this would fall in an anti~
clockwise manner and so eause the b~r 154 to revolve 9 also in an anti-clockwise mannerO When now, a mass weight 160 is placed on the right hand side spindle or stud 152 on the bar 154 then thi.s mass weight 160 would oppose the falling of the mass weight 159 of mass one9placed on the left hand side spindle or stud 152 in the framie bars 1530 Pre~iously it is stated that the integral gears B 144 and C 145 are ~ inch diamieter and 3 inch diameter respectively~ and this ratio of ~ is to 3, is a ratio o~ to 40 So that with the epicyclic gear assembly shown in FIGo 34 then a mass weight 159 o~ mass one placed on the spindle or stud 152 would balance a mass weight 160 of mass 4 (or just slightly less than 4) placed with care on a spindle or stud 152 on the opposite side to that of the mass one 159. So that their masse~ are opposed ; and al80 the frame bars would still be in a hiorizontal balanced position~ So that it would be noted that when say the mass weight 160 is remo~ed from the assembly, then the mass weight ].59 would drop with ain acceleration, due to gravityO Similarly when say the mass weight 159 is removed ~rom the assembly, then the mass weight 160 would drop with an acceleration, due to gravityO When now, the mass weight 160 a~d the mass weight 159 are replaced with the frame bars , ... . .
,.. . . ~ . . , , . ~ :
- . . . - . . : .
~` ~.(1~2~
15~ and 1.54 in the horizontal position as shown in FIG. 34 then when movement of the mass weight 159 occurs then this would callse the balanced mass weight 160 ~ so to move in a corresponding manner and this movement o~ the balanced masses would be a movement of velocity, and not accelerationO So that, say, for examplep the balanced masses 159 and 160 move with a velocity of one, due to both masses being placed, equidistant, from the centre pivot then the mass weight 15g would move with a mass of one and a velocity of one, whereas the ma~s weight 160 would move with a mass of 4 and a velocity of one.
So that when now, mass weight 159 of mass one, is placed on a fi~ed spindle or as the sasne fixed spindle 10, in the previous FIGS, on which the gear A 30, i8 fixed, and when the ma~s weight 160 of mass 4 is placed also on the same fixed spindle 10, these ma~ses I being at the input and output ends o~ the epicyclic gear as~embly, then the mechanism shown in the FIGo 34 assesnbly could become as the FIGo 30~ SO that when referring now to ~IG~ 34 the e~ual centre pivotting distances of the masa weight 159 and the ma.ss weight 160 could be regarded as the radius of gi~ation of revolving circular discs.
So the momentum of mass weight 159 of mass one, moving at say a velocity of one, would have a momentum of one, .
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and the momentum of the balancecl mass weight 160 of mass 4 moving at say a velocity o~ one, would have a momentum of 4O Similarly the kinetic energy of the balanced revolving masses revolving at a velocity o~
one, would be for mass weight 159, mass one times a velocity o~ one 9 times one, which is one, and the kinetic energy of mass weight 160, would be, mass 4 times a velocity of one time~ one, which is 40 So that by comparison, mass weight 160 would possess 4 times the momentum and 4 times the kinetic energy of mass w~ight 159.
Al~o a~ stated in FIG,34 when the frame bars 153 tend to make one re~Glution, then the bar 154 also tends to make one revolution and when the mass weight 159 and mass weight 160 are placed 9 with inertia borne in mind9 in po8ition with care, a~ in FIG~ 34 then the assembly would be in balance and no movement would occurO It i~ to be noted that the ma~s weight 159 and ma~s weight 160 are placed diametrically opposite with their tendency to motion opposed, and thls could also be arranged, i~ required9 in the gear a~emblie~ shown, in the previous FIGSo by the in~ertion oi an additional intermediate gear which would not be detrimental to the mechanical efficiency oi the arrangement~0 It i~ with renown, that large reduction gear unit !
~ g _ , ., -, , . -- . .. .
. - . .. .. . . . .- ... - . - - :
. ~ . - , . . , -~ o~
assemblies are utilised, in modern arrangements for s~ip propulsion. So that in the assemblies shown, such as say in FIG. 30 when comparatively low output revolutions are required~ the reduction gearing drives between the units could be by suitable worm and wheel reduction gearing, and if re~uired, input and output masses could be utilised in the la~t unit, with the input and output masses omitted in other unitsO Also in arrangements when the reduc-tion gearing between the units is large 9 with any comparative low output revolutions, then such arrangements could be adaptable ~or and applied to ship propulsion and it would be apparent that to have high output revolutions ror ship prop~.sion would be a repulse for high revolutions due to the high inertia of the very heavy mass o~ the ships.
So that when reduction gearing is utilised, between the gear units, as stated, then oil filler and drainage plugs and seal~ could be incorporated in the hood, or cover, o~ the assemblies, to facilitate functioning of the m~chani8m assemblies.
Further practical applications o~ the gear unit as~emblies could be utilised as in ~IG. 35 and FIG.36.
~IG.35 8hows 3 gear units 161,162 and 163 such as those I ùtilised in the previou~ ~IGS, and the~e gear units are assembled in a vertical manner, so that the input gear 164 and output gears 165 are opposite on each unit~ So that a prime mover 168, secured on a bridge 173, would drive the _ -40 , .. , . , . . .. , ~,:
:
:, - . , .
~ ~Qi~
input gear 164 of the unit 161 through motor driving gear 166 and intermediate gear 1670 So that the input gear 164 on the first unit 161 driving through the unit 161 would cause the output gear 165 of the first unit 161 to revolve, and this output gear 165 of the first unit 161 would now drive, through intermediate gear 167, the input gear 164 of the second unit 162 which would cause the output gear 165 of the second unit 162 to revolve, and so drive, through the intermediate gear 167 the input gear 164 of the third unit 163 which in turn would cause the output gear 165 of the third unit 16~ to revolve and this revolving output gear 165 of the third unit 163 would through intermediate gear (or gears) 169 drive a gear 171, this gear 171 being integral and part o~ a railway bogie waggon wheel 1700 These wheels 170 running on railway lines, or other tracksO
~he whole assembly would be supported on a frame or bridge 173 which would be part o~ the railway bogie assembly and through which passes the spindle or spindles 172. So that when the prime mover, or say an electric motor 168, i~ energised with power from say an overhead pantagraph, or by means o~ central rail ground power supply, the gear unit assemblies would transmit the power to the locomotive ~aggon or bogie wheels and so propel the complete assembly along the rails or track, the speed and distance propelled being relative to the gear unit assemblies utilisedO
1, ~
.~ . , . .......... . . . . - - :
- .
FIGo 36 is similar to FIG~ 35 but in FIGo 36 the gear unit assemblies are arranged horizontallyO
These arrangements could also be adapted to other forms of locomotion other than tracked vehicles and whil~3t t~iese arrangements are adaptable to tracked ~ehicles they could also be utilised for other forms of locomotionO
In FIGo 37 is shown an arrangement of how the mechani~m assembly in the apparatus demonstrating balancing of mas,ses as in FIGo 34 could be adapted to be ~imilar to say a conventional pair of scales, and it would be noted that the centre of gravity of the masses 90 balanced would be similarO The reference numerals are as in FIGo 34 o !~
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-
revolving 8 x 5 revolutions, i.e. 40 revolutions, and these 40 observed and actual revolutions are transferred to the 1 second assembly, as the input.
i With the input disc 36, revolutions, for the ~econd . .
assembly being 40, and with the second a~sembly constructed in exactly the same manner a~ the first assembly~ in so -- .
- . . : - . . . - :
. - - , . , - : .
~` :
() far as ~ear sizes are concerned, the externai freely revolving 1~ inches diameter centre ~ear D ~5 9 in the second unit would make 40 x 5 revolutions~ i e, 200 revolutions, that is to say~ 200 revolutions actual and observed, and this becomes the input or disc 36, revolutions o~ the third assembly9 which again, assuming its gear ~izes to be like the gear sizes of the first two assemblies, the output would then be 200 ~ 5 or 1000 ~ revolutions actual and observedO
! With a pulley 37, attached to the output gear D 35 o~ the third assembly, by keys or pegs ~7, the latter would revolve at 1000 re~olutions per minute on the spindle 10, on which the three epicyclic gear units are revolving. As shown in the drawings, and in particular in ~IGol~ there sre provided a number of disc like fly-I wheel units, at the output end of the gear assembly, these ~ly-wheel units being indicated by the reference numerals 15. 16. 17. 18. 19 and 200 Aa shown, three o~ the fl~-wheel units, i.e. 15. 16 and 17 are ~ecured to the pulley 37, by screws and dowels 68 and 69, and the other three discs 1~. 19 and 20 are locatcd in ~1 inoperat$ve position adjacent to the pulley 37 on a stationary bush 70, these latter three units 18. 19 and 20, are not revolvi.n~, and are held stationary by belts and nuts 71 and 72 in the carrier 11 , - . . .
.
.. . . , - . . ~ . , ~ .
:.' ' ,; . ~ , - ~ . , , ~0~32001) The purpose of providing the flywheel units, 18,19 and 20 or more if required, is to enable the effective weight of the revolving fly-wheel disc unif.s, 15, 16 and 17, to be varied, to ensure that the pulley 37 runs smoothly, these re~olving fly-wheel discs 15 9 16 and 17 being secured together by bolts and nuts 73 and 74 lhu, ~lywheel disc units ~an be added to, or removed from, the fixed pulley a~ desired. Similarly, at the input end of the as.~embly, are shown further fly-wheel disc unit~, 21 to 25, -these being attached to a hub 26, keyed or pegged to the worn,wheel 29, Rhaft, by keys or pegs 67 and revolving at the same speed a~ the first unit input discs 21 to 25, that is to say at 8 r.p.m.
; In order to drive the gear assembly, a 1440 rOp.m.
"
motor 27 i~ provided, mounted on suitable framework 75, and fixed on a base plate or foundation base 76. Thus for a 1 inch diameter input pulley 38~ making 1440 r.p.m.
driving onto a 4~ inch diameter pulley 39, output from the latter would be ~20 rOpOm. which latter would be the epeed of the ~ingle pitch worm 28, which drives a 40 tooth wormwheel 29, mounted in a framework 77, attached to the ba~e plate or foundation 76, so that the output r~p.mO of the wormwheel 29 would be 34 i.eO 8 rOpOmO Although the apparatus illu~trated is not shown with any form of covering or oil bath lubrication, such equipment would be ' - . . . . . : , - . . . . .
. .
~zooo : ~
provided as required. Also intermediate gears 79 are shown in the epicyclic gear assemblies 12, 13 and 14 and the epicyclic gears framework, which acts a9 the input disc 36, is secured by tie bars 78. Also a hub 174 is al30 attache~ b~ screws 175 and dowels 176 to the input flywheel discs 21 to 250 Turning now to FIGo 20 it will be seen that the gear C 33, is larger than the comparable gear o~ FIGo 1 o in fact the gear C 33 i9 twice the diameter of ~TGolo that is to say it iB 6 inches diamete.r 80 that in this arrangement the ,.
observed and actual revolu~ions of the centre freely revolving gear D 35 of 1~ inches diameter, when one revolution of the input disc 36 is considered, would be A x C + 1 which i9 ~+1 which i8 2 ~ 4 + 1, i~eO .
9 r,p,m. ror centre gear D 35 ~ but in the case of this gear assembly, the input di~c 36 makes lo 35 revolutions, this resulting from a pulley 40, o~ 1~ inches diameter on the spindle of a 1440 rOpOmO motor 27 driving a 1 inch diameter pulley 41 attached to a worm 28 9 driving a wormwheel 29, so that the observed and actual revolutions of the tirst : a~sembly external centre gear D 35~ would be 1~35 ~ 9 which i~ 12.15 (~or convenience the rOpOmO l9 assumed to be 12), ~he~e 12 observed and actual revolutions are trans~erred to I the second unit 9 and become the input for that unit O
Assuming the second unit to have gears of the same size as -8- ;
!
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. . .
. . .
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.
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. .
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the first, then the centre gear D ~ 9 in the second unit assembly would make 12 x 9 iOeO 10~ observed and actual revolutiGns (si.nce the actual and observed revolutions of the f.-rst centre gear D 35~ are 12~15, the actual and observed revGlutions of tha ~econd gear D 35~ will be a~sume-l to be 109. The 109 revolutions of this unit become the input o~ the third assembly 9 SO that the actual and observed revolutions of the third as~embly would be 109 x 9 or 981, assuming the gears of the third assembly to be exactly t.he same as those of the preceding two as~emblies. A pulley 37~ attached to the output of the third assembly, therefore, would make ~81 rOpomo which of course would be the rate of revolution of those flywheel di~cs 15, 16 and 17, which are attached to the pulley 37 by screws 68 and dowels 69. As in the arrangement of FIG,l. there are further flywheel 18019 and 20 adjacent .
to the output pulley ~7, 80 that smooth running of the latter can be achieved, and ~imilarly there are a group of flywheel disos 21 to ~5, at the input trO the unit, the~e latter di~c~ being attached to the fir~t assembly hu~ 26, and input disc 36 and thus they would rotate at 1035 rOprm.
Again a 1440 rOp.mO motor 27, is utilised, mounted on suitable framework 177 and Irixed on a base plate or foundation 118. So that with a 1~ diameter inch pulley 40, on the output shaft o~ the motor 27, dri~ing a 1 inch :
:, _9, .~
. .
.. . . . .
., . . : ::
: . . . .
.. .. . .
~0~2~00 diameter pulley 41 which serves as the input, via a worm drive 28 and 29 mounted in a framework 112, attached to the base plate or f'oundation base 178, to the gear assemblies 9 the 1 inch diameter pulley 41 would De revolving at 2160 rO~OmO to drive a single pitch worm 28 and 40 tooth wor~wheel 2g, so that the latter would ~e rotating at 2160 divided by 40, iOeO 54 rOpOmO In the particular arrangement being described, a second single pitch worm 28 is provided and driven ~'rom the fir~t worm-wheel 29, so that its rate of revolution would be 54 r.p.m.
and assuming this drives a second 40 tooth wormwheel 29, the output rOp.mO o~ the motor 27 is reduced again to provide the lo'S5 r.p.mO input speed for the first gear assembly. Also intermediate gears 8~ and 81 and 82 are shown in the epicyclic gear assemblies 120 13 and 14 and the epicyclic gears ~ramework, which acts a~ the input disc ~6 i3 secured by tie bars 78. Also a hu~ 174 is also attached by screws 175 and dowels 176 to the input flywheel di~c~ 21 to 25. l'he assembly in other respect~
coniorms to that previously de~cribedO
Referring now to ~'IG.30 it will be seen that this di~ers ~rom the arrangements o~ FIGS o 1 and 2 in that the fixed gear in this arrangement i9 of 9 inches internal' diameter ~ixed gear ~' 31, secured to base plate or ~ound-ation base 179 ~y screws 180. ln thi~ arrangement, the . .
, . . .. . . .
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: , . ' - . .. . . ~ :
. ;. . . ~ : .
:. . . . .
:~ . . . - :
` ~ ~o~ v gears B 32 and C 33, and the centre freely revolving centre gear D 35 are the same as in FIG~lo that is to say the gear B 32 is of ~ inch d-ameter and the gear C 33 and D 35~ are respectively ~ inches and 1~ inches diameter.
In tnis arrangement the observed and actual revoluticns of the centre freely revolving 1~ lnches diameter centre gear 0 35, for each one revolution of the input di~c 36, would be $ x D + 1 which i9 ~ ~ + 1 which is -12 x 2 + 1 io eO 25 rOp ~mO
However in this particular arrangement, the input disc 36 make~ 00072~ revolutions, 80 that the observed and actual revolutions of the first asqembly external centre gear D 359 would be 000726 ~ 25 that is 1.815 r.p.mr and these actual and observed revolution~ are transferred to the second assemblY, that is, the 1.815 rOp~mO becomes the input Yor the second assembly which latter being of e~actly the same construction, in so Yar as gear ~izes are concerned, as the first assembly, will result in the output centre gear D 35 of that assembly making 10~l5 X 25 revolutions, that i~
to say, the output r.p mO o~ the second unit would be 450375 rOpOmO observed and actual revolutions, and of course, this becomes the input f~r the third unit, which again, since it has ~he same ~ear ~izes and construction as the preceding two, would result in an output o~ 45,~75 x 25 which i~ 1134 rO pOmo observed and actual revolutions, and it is thi~ 1134 rOpOmq which is applied to the pulley ~7 and its . ~ '.
, 1 .
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' ~ '' . ' ' ~ ' ' ' ' ~ ' ' ' attached flywheel discs 5 15 a 16 and 170 As in the previous arrangements9 additional flywheel discs 180 19 and 20 are provided in order that the effective weight of the revol~ing flywheel 150 16 and 17 can be modified as desi~ed 9 to ensure smooth rotation of the pulley 370 Al 30 as in the previous arrangements, a plurality of flywheel di~cs 21 to 25 are provided at the input end of the gear assembly and between the input disc 36 and the worm drive arran~ement to that disc.
In the arrangement of ~IG.3~ the input rOpOm~ of 0,0726 i~ derived from a 1440 rOpOmO motor 27, mounted on the base plate or foundation base 179 by the use of a 1~ inch diameter pulley 42 on the output shaft of the motor 27, driving a 15~ inch diameter pulley 43 to reduce the rOpOmO of the second pulley shaft to 116 which is the ~peed of rotation of the firæt single pitch worm 28, mounted in a framework 113 9 attached to the ba~e plate or ioundation base 179 which drive~ a 40 toothed wormwheel 29.
So that the reduction in ~peed from 1440 rOpOmO at the first wormwheel 29 i6 to 209 rOpOmO which is utili~ed as the rate oi rotation of the second worm 28 which dri~es a second 40 toothed wormwheel 29, to further reduce the speed from 2.9 to 000726 rOpOmO Also ~ntermediate gear~ 83 and 84 are shown in the epicyclic gear assemblie~ 120 13 and 14 and the epicyclic gear framework, which acts as the input di~c 36, -12- .
. ~
., :
.
- ~ ~ '` ' ' ' ' .
o~ o is secured by tie bars 780 Also a hub 174 is also attached, by screws 175 and do~lels 176 to the input flywheel discs 21 to 25. The assembly in other respects conforms to that previously describedO
The arrangement of FIGo 4O is to some extent similar to that of FIGu 3o the primary exception being, that the gear C 33 of FIGo4a is 0~ ~ inch diameter whereas in FIGo 3O the ~ear C 33 has a 3 inch dia~eter~ In the arrangement of FIGo 40 the ob~erved and actual revolutions of the 1~ inoh diameter9 freely reYolvi.ng centre gear D 35 will be B x D + 1 that is ~ x ~ + 1 which i8 12 x 4 + 1 which is 49 rOpOmO for the centre gear D 35.
Thu~ 49 rOpOmO would be the input speed for the input o*
the second assemblyv and thus the output observed and actual revolutions of the second gear unit assembly would be 49 ~ 49 namely, 2401 r.pOmO which become the : input revolution~ for the input of the third assembly, the output from which would be 2401 x 49~
Such a high speed output would find little practical -application and thus to bring down this output speed to an output of the order of 1000 rOpOmO an extremely large worm-whee~ 44 or a number of smaller worm or wormwheels, driven by worms 28, mounted in a framework 114 attached to the base piate, or roundaticn base 181, are required at the input i ' .
':' ' ' , ' ' ' , .' ', ' . ' " ' ' . " ' . ~ " ' ' ' , "' '' . ', ' '" . '" ~ ~ ' .
,.
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end of the gear trainO These assemblies are not shown since the principle of reducing the output speed of the p~ime mover, by the use of wormwheels and worm drive3 iæ illustrated in FIGSo 1 to 3 referred to pre~iously~ Also intermediate gears 85 and 86 are shown in the epi~yclic gear a~semblies 120 13 and 14 and the epicyclic gears Lramework which acts as the input di~c 36 i~ ~ecured by tie bars 780 Also a hub 174 is al~Qo attached, by screws 175 and dowels 176 to the input ~lywheel discs 21 to 250 The assembly in other re~pects conforms to that previously describedO
Re~erring now to FIG~ 50 of the drawings the gear unit there illustrated i9 ~ in ~act, a combination of one of the gear a~semblies of FIGo 30 and two of the units of FIG.l. arranged such, that the gear unit o~ the kind illustrated in FIGo 30 becomes the first unit of the mechanismO Thus when considering one revolution of the input to the ~ir~t gear unit it wlll be observed that the actual and ob~erved revolutions o~ the freely revolving centre gear D 35 which in this case is 1~ inches diameter would be B x C + 1 io eO ~ ~ ~ + 1 io eO 25 re~olutions which become~ the input speed o~ the input of .
the second unitO
The observed and actual revolution~ of the second unit which again haæ a freely revolving 1~ inch diameter centre ~
A C 1~ ~ 3 gear D 35 would be B ~ D + 1 iOeo ~ x 1~ +
.~
.
.
~ ~ . . ' ' , ' ~
~ .
-01~2~
which i~ 5 revolutions. So that the output revolutionsof the second unit would be 125 9 and this becomes the input to the third unit which, ~ince its gear train i3 exactly the same as that of the second unit, results in an output of 5 ~ 125 r~p~m~ which is 625 rOpOmO
Now, if at the output end, a 1~40 rOpOmO drive motor 27 mounted on suitable ~ramework 182 and fixed on a base plate cr foundation base 183 is provided with a 1~ inch diameter pulley 45 driving a 15~ inch diameter pulley 46 the latter would have 140 rOpOmO which would be the same rate of revolution, as a 1~ inch diameter pulley 47 mounted on the same shaft as the 15~ inch diameter pulley 46, thus if the drive from the 1~ inch diameter pulley 47 is now taken to a 3 inch ~iameter puïley 48, the revolutions of this latter pulley 48 wpuld be 70, and .
thio pulley 48 is adapted to drive a worm 28, meshing with a 40 toothed wormwheel 29~ mounted in a framework 115, attached to the base plate or foundation ba8e 183, which gear is attached to the input o~ the ~irst gear assembly, via the *lywheel discs 21 to 250 So that the input would be 40 r,p.m.
namely 1075 rOpOm~ and this gives 43075 rOpomo observed and actual revolutions of the first unit ~reely revolving centre gear D 35, this rate of revolution being the same as the input revolutions of the second gear unit~ So that the observed and actual revolutions of the second unit would be l .
!
: ~ 15- :
... .. .. . , -1~ ~01~2~0~
. . .
43.75 2 5 namely 218~75 which becomes the input revolutions of the third unit, the output of which becomes the input revolutions of the third unit, the output of which becomes 21~.75 x 5 namely 1094 r~pOm.
which is the rate nf revolution of the pulley 37,attached to the output flywheel discs 150 16 and 17 by screws 68 and dowel3 69 9 as the latter would also be revolving at 1094 rDpOmO on the spindle. As in the previous arrangements, additional ~lywheel di3cs 180 19 and 20 are provided on a non-rotar~ extension of the spindle 70, so that the weight of the revolving flywheel di.scæ 15, 16 and 17 can be varied as requiredO Also intermediate gears 87 and 88 and 89 are shown in the epicyclic gear assemblies 120 13 and 14 and the epicyclic gears ~ramework, which acts as :
the input disc 36 is secured by tie bars 78. Also a hub 174 i9 also attached by screws 175 and dowels 176 to the input ilywheel discs 21 to 250 The assembly in other respects conform~ to that previously described.
Referring now to FIG 6. it will be seen that the arrangement is somewhat ~imllar to that of FIG.50 It should be noted,however, that the fixed gear A 30, in this particular ca~e of the centre gear as~embly, is of 3 inch diameter, whereas in the FIGo 50 arrangement it was of 1~
I inch dlameterO It will also be noted, that the third gear I assembly o~ the FIG~ 6 arrangement, i~ like that of the FIG.5 .
.
; , . , . : - ~
- .
.. . . . . .. . .
... , . .. . .. . ~ , .. . .. . .
. . - : - . .
arrangement, with th~ ~ixed gear A 30, of 1~ inch diameter, and thus taklng the gear tr~in as a whole, and assuming, one revoluticn of ~he input disc 36, then in the first assembly, the observed and actual revolutions of the freely revolving centre gear D 35, which is of li inch diameter would be :~ x D + 1 namely i.e. 12 x 2 + 1 namely 25 rOp.m. 'l'his of course becomes the in~ut revolutions of the second gear assembly, in which the observed ~ld actual revoluticns o~ the ~reely revolving 1~ inch diameter centre gear D 35, would be B x D l 1 that i9 to say ~ x ~ + 1 namely 4 x 2 + 1 iOeO 9 r.p.m.
thus the output becomes 225 r.p.mO namely 9 x 25 observed and actual revolutionsO The input revolutions therefore, of the third assembly, becomes 225 and the output rate of revolution of the ~reely revolving centre gear D 35,which i8 o~ 1~ inch diameter would be 225 x 5 namely 1125 rOp.mO
; h C ..
and this would be derived from B x D + 1 that is to ~ay ~F x 1~ + 1 which i9 2 x 2 + 1 which is 50 If one now applies an input drive to the ~irst gear unit derived ~rom a 1440 rOpOmO motor 27, mounted on suitable framework 184, attached to the base plate or foundation base 185, driving a 40 toothed wormwheel 29, mounted in a framework 116, attached to the base plate or foundation base 185, to give 36 rOpOmO drive to a second worm 28y also driving a 40 toothed wormwheel 29, which applies drive to : : - . - . - .
:. , . .: .. . .. ,, , - , . . .:
. ,, ,., . " , . - , , . ,~
., .. ~ . . . .
~ 10~
the first gear assembly, then the drive to this assembly would be 40 namely 009 rOpOmO So that the actual and observed revoluticns o~ the 1-'- inch diameter freely revolving centre gear D 35 of the first unit, would be 2205. The output re~olutions of the second unit wo~ld be 2205 x 9 namely 202c5 and the third unit assembly would have an output of 20205 x 5 namely 101205 rOpOmO This in practice would be the rate of revolution of the pulley 37 9 attached to the flywheel discs 150 16 and 17 by screws 68 and dowels 69 and also of course the rate of revolution of the flywheel discs 150 16 and 17. As in the previous arrangements additional flywheel discs 180 19 and 20 may be mounted on a non-rGtating flywheel bush 70 adjacent to the flywheel discs 15. 16 and 170 80 that its effective woight may be varied to suit requirementsO As in all previously described assemblies, there would be a sump for lubricant, and of course, the mechanisms would be enclosed within a suitable casing. A190 ~ intermediate gears 90-91-92-93-94 and 95 are shown in the epicyclic gear a~semblies, 12, 1~ and 14 and the epicyclic gears framework, ~which acts a~ the input disc 36 is secured by tie bars 780 Also a hub 174, i9 also attached by screw~ 175 and dowel~ 176 to the input flywheel discs 21 to 250 The assembly in other respects conforms to that previously describedO
S
' .: .
. .
~ :, - . ~ . , - - . . ~. ..
. .. . . : :
~6~82~
Referring now to FIGo7 it will be seen, that the arrangement is similar to that of I~IG o 1~ but in this particular case, an intern.~ 9 inch diameter gear FD 34 haæ been substituted for the 1~ inch diameter external centre gear D 35, of FIGo 1 o Additionall~, the gear C 33 in the arrangement of FIG~7 is made 3~ inch diameter, and thus when one revolution of the in~ut disc 36 i9 considered, then in the fir~t gear assembly, the observed and actùal revolutions of the freely revolving gear FD 34 will be A x C + 1 nc~melY~ ~ 9 +
that ia to say lo 5/6ths observed and actual revolutionsO
~his becomes the input revolutions for the second assembly, which is exactly the same in construction as the first as~embly, so that the observed and actual revolutions of the second assembly will be 105/6ths x 105/6ths, that is appro~imately 3036 rOpOm~ which becomes the input for the third aesembly, which is exactly the same, in construction, as the previouRly de~cribed as~emblie~. ~o that the revolution~ at the output of this assembly, will be 3.~6 x 105/6ths which is appro~imately 6016 observed and actual revolutions.
Now if one applies a 1440 rOp~m. prime mover 27,mounted on the base plate or foundation base 186, to supply the input power, for the gear train, and assuming that this has a 1~ inch diameter pulley 49~ driving a 6~ inch diameter - .. . . . ~
- . . . .. .
pulley 50, the output rOpOmO would be 332, which is applied to a 1~ inch diameter pulley 51, carried on the same shaft as the 6~ inch diameter pulley 50, mounted in a framework 117~ attached to the base plate or foundation baæe 186 ~nd this serves to drive a 3 inch diameter pulley 52, attaçhed to a hub 174, whieh is attached to input ~lywh~el di~cs 21 to 25; by screws 175 and do~el~ 176 of the gear assembly~ The input therefore.to the gear assembly would be 166 rOpOmO so that the output from the ~irst gear unit would be 304 r~p~mO of the second unit 558 r.p.m.
and oi the third unit 1013 rO pO mO Thus the speed of a pulley 37, at the output end of the gear assembly is 1013 rOpOmO
which iæ the same rate of revolution as the flywheel discs 15. 16. and 17, attached to the pulley 37, by screws 68 and dowels 69, attached to a driving hub 188, which flywheel disc~, as can be seen, is o~ a similar form to that described in the preceding arrangement 9 namely, it is capable o~ having its mass either increased or decreased by the addition or removal of disc like ~lywheel element8 180 19 and 20. As in the previous arrangements a number of such elements are provided on a non-rotary bush 70 t adjacent to the flywheel discs 15. 16 and 17~ Al~o intermediate gear~ 96 and 97 are shown in the epicyclic gear assemblies 120 13 and 14 and the epicyclic gears ~ramework, which acts as the input disc 36, i9 secured by tie bars 780 Also a hub 174, is also ' .
.
.
. - ' ~ ~ .-. -: . ' ,. .. .
: - : -: .. : -, :
.: . ,,, -:
: :-- :: .:
- . , - - . - ~
.
-. . .
attached by screws 175 and dowels 176 to the input flywheel discs 21 to 25 and to the pulley 520 The assembly in other respects con~orms to that previously describedO
In the arrangement according to FIG ~ 8~ the gear assembly is somewhat similar to that just described 9 in that the first and middle and last gear assemblies are similar to those shown in FIGo 7 but in this particular case a 1-~ inch diameter centre gear D gear 53 which is freely revolving on the f.ixed shaft 10, has been added to the last gear as,sembly. This latter centre gear, D gear 53 is driven by ordinarily revolving gears 54 and 55 running on spindles l9G secured in framework 191 ~rom the inaide gear perimeter of the output gear FD 34 o~ the last o~ the gear assemblies, namely a 9 inch diameter internally toothed gear FD 340 So that when one revolution of the input disc 36 is considered in the first gear unit assembly, the observed and actual revolutions o~ the 9 inch internal diameter gear FD 34 would be ~ x C ~ 1 namely ~ x ~ + 1 which~ as in the arrangement of FIG.7 gives an output of observed and actual revolutions of 1 ~nd 5/6ths which becomes the input to the second unit, which since it is of e~actly the same construction as the first will ha~e an output 3036 rOpOmO
and the third unit will have an output of 6 o 16 actual and observed revolutionsO
' : . : . -.. .
: . ~ . : . , ,: :
2~
In this particular case however, the 1440 rOpomo prime mover 27 mounted on the base plate or foundation base 189 is provided with a 1~ inch diameter pulley 56 to drive a 15~ inch diameter pulley 57 to give a 140 rOp.mO at the pulley and 140 rOpOmO of a 1~ inch diameter pulley 58, mounted on the same shaft as the 15~ inch diameter pulley 57, mounted in a frameworX 118, attached to the base plate or found~tion base 189~ ~his latter pulley 58, itsel~
drives a 7~ inch diameter pulley 59 to give 28 r~pOmO which is the input speed of the first gear asæembly 9 and of course the flywheel disc~ 21 to 25 ~ at the input end o~ the machine~ -Thus the output rOp~m~ of the first gear unit will be 28 x 1~ 5/6ths that is approximately 51 rOpOmO The output from the second assembly would be 51 x lo 5/6ths, which gives approximately 94 r.p.mO and thus the output from the third assembly is 94 x 1.5/6th~ which is appro~imately 172 o 33 rOpOmO ~hus 172.33 rOp.mO is applied, by ordinary revolving gears, 54 and 55, running on spindles 190, secured in framework 191, to the l~ inch diameter freely revolving centre ~ear D gear 53 to result in the output speed of 1034 rOpomo namely x 9. The speed of the drive pulley 37 ~ attached to ~lywheel discs 150 16 ~ld 17 by screws 68 and dowels 69 and the speed of flywheel di~cs 150 16 and 17 at the output end o~ the gear arran~ement is thu~ 1034 rO pOmo As in the prevlous arrangements, adjustable mass flywheel di~cs . .
.. . . . . . . .
:. ' ' ' ' . , - ~
, ~ : - ~. . .
.
18. 19 and 20 are provided J as of course is a sump, for lubricant and a cover for the mechanismO Also intermediate gear~ 98 and 99 are shown in the epicyclic gear a~semblies 120 13 and 14 and the epicyclic gears framework ~hich acts a~ the input di~c 36 9 iS ~ecured by tie bars 7~O A180 a hub 174 is also attached by screws 175 and dowe]s 176 to the input flywheel discs 21 to 25 and to the pulley 59O ~he assembly in other respects conforms to that previously describedO
Turning now to FlGo9 it will be seen that there is an arrangement in which the gear assembly i8 similar to that just described in that a 1~ inch diameter centre mounted ireely revolving centre gear D gear 53 is provided at the output oi the third gear assemblyO It will be noted,however, that a similar ireely revolving centre gear D gear 53 has been provided at the output of each o~ the other two gear assemblies, and thus assuming in each case that the output ~ear o~ the gear a~8ernbli.ee i8 a 9 inch dlameter internal gear FD 34 and that in each case this drives a 1~ inch diameter freely revolving gear D gear 53 by means o~ ordinary re~olving gears 54 and 55, running on spindles 190, secured in *r~ework 191, then the ~ituation when one considerc one re~olution of the input disc 36, i~ that, in the first gear asseMbly the ob~erved and actual revolutions oi the ireely revolving 9 inch intérnal :~
diameter gear FD 34 will be A x F~ ~ 1 namely ~ ~ ~ + 1 ~.
i.e, 1.5/6ths revolutions actual and observedO This 1O5/6ths ~ r.p.m. oi the ~ear FD 34 i~ now transierred to the 1~ inch .l -23-! . . .
.. . .
;. , ' '' ' ' ' : ':
: . ,: . .: , ' : , ': ' : ' . . . - ' 2C~90 di2meter freely revolving centre gear D gear 53 by means of two fixed spindle 9 or fixed axis gears 54 and 55 9 previously described as ordinary revolving gears 9 so that the speed of the 1~ inch diameter revolving gear D gear 53 would be 105/6ths x g divided by 1~, that is approximately 11 rOpOmO It follows that 11 rOpOmO is the input e~eed ~or the second gear assembly so that~ since it is identical in construction to the first assembly9 the output will be 11 x 105/6ths that is approximately 200163 rOpOm.
at the 9 inch internal diameter revolving gear FD 349 thus the speed of the 1~ inch diameter freely revolvirlg centre gear D gear 53 of this assembly is 200163 x 9 divided by 1~ that is app~oximately 121 rOpOmO As can ~e seen from the drawing, the drive tO the second centre gear D gear 53 : is via two ~ixed centre, or fixed axis gears, 54 and 55 described as ordinary revolving gears 54 and 55, the first of' which is driven, by the internal 9 inch diameter gear FD 34. In this gear train 121 rOpomo i9 the input speed of the third gear assembly 9 wh.ich being identical in oonstruction to the previous two assemblies, gives an output o~ 121 x 105/6ths iOeO 222 rO~OmO at the 9 inch diameter gear ~D 34, 80 that the speed of the third 1-~ inch diameter f'reely revolving centre gear D gear 53 will be 222 x 9 divided by 1~ which is 1~32 rOpOmO
' , ~ -24-. . . ~ , .
-- ~ ' , , .
. ~ : . , - - . . ::
o~c)o~
If, at the input end of the gear assembly there is provided a 1440 rOpOmO prime mover 27 mounted on the base plate or foundation base 192 with a 1-~ inch diameter pulley 60 on its output shaft, dri~ing a 1~ inch diameter pulley 61 the speed of the latter pulley 61 will be 1234 r~0m.
and i~ this pulley 61 drives a worm 28 that in turn drives a 40 toothed wormwheel 29 mounted in a framework 119, attached to the base plat~ or foundation base 192, this first wormwheel will have 30085 rOpOmO This rate of revolution will be the same as that of a second wor~ 2~
upon which the first wormwheel 29 i8 mounted, and if the second worm 28 drives a 40 toothed wormwheel 29 the output r.p.m. will be 0~77 namely 40 Thus in this assembly the input speed of the first assembly would be OD77 rOp0m0 and the speed of the first 9 inch diameter gear FD 34 would be 0077 x 105/6ths that is 1.4116 rOp.mO with the output speed of the gear FD 349 at 104116 the freely revolving centre ~ear D gear 53 wlll b~ rotating at 8045 I _.4116 x ~
,I r.p.m. that i8 1~ and thus 80 47 becomes the input speed for the input of the second assembly0 The output of this second assembly is that the speed of the gear FD 34 I will be 8047 x 105/6ths that is 150528 rOp0m. and thuq j the freely revolving centre gear D gear 53 of this assembly 15O52~ x 9 will be 1~ to gi~e 93D17 rOp.m0 as the input speed . I . ~
of the third assembly, and thus the output speed of the gear FD 34, of this assembly, will be 93017 ~ 1.5/6ths, namely , ~, .
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- .: . : ..
-.
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, ~ . ' '. ' . . '' ' . ' ~o~z~
17008 rOp~mO The output from the third freely 170 8 x .
revolving centre gear D gear 53 will therefore be -1 that is 1024 rOp~mO ~he output pulley ~7 secured b~
screws 68 and dowels 69 to the variable mass flywheels 15. 16 and 17 attached thereto will therefore have a speed o~ lG24 rcp.mO Also intermediate gears 100 and 101 are shown in the epicyclic gear as~emblies 12~ 13 and 14 and the epicyclic gears framework, which acts. as the input disc 35 is secured by tie bars 780 Also a hub 174 is also attached by screws 175 and dowels 176 to the input flywheels 21 to 25 and to the second wor~wheel 290 ~he as~embly in other respects conforms to that previously describedO
~ he arrangement~ ~hown in FIGSo 1 to 9 previou~ly described~ all illustrate three sets of gear assembly units and clearly these could be built as separate unitæ 9 ehown in FIGo 1~ or as a complete assembly. By increasing the number of gear assemblies, for example, by coupling together one or more o~ the gear trains described, it is possible to pro~ide an arrangement in which an extremely low input drive speed can be applied, thereby enabling the gear a~sembly to be utilised, ~or example9 for weight lifting, in for example cranes or the like, or in weight balanGirlg mQchines or apparatusO In this latter case1 the apparatus can be adapted to operate in such a way that ~or one , -26~
.
, :, , . . . - , . ~
.-~ , ,. :
: - - . : : . -: - :
c f~ 2()~o revolution of the input of the first ~,ear assembly and also one revolution at the output of a similar gear a~sembly 9 one can have the situation in which a small diamet2r central output ~ear D 35 or a gear D gear 53 - as in FIG~10 is making *or example 1000 r~ p O mO to result in one re.volution of an extremely large gear 62 in mesh therewith 9 thi~ large gear 62 making one revolution in compari~on to one revolution of the input (the output en~ o~ such a gear train i~ shown in FIGolO)o However an extremely large gear wheel may result in design dif~iculties and thus it ls envisaged that the same re~ult could be obtained by substituting for the very large gear, a compound reduction gear of the kind shown in FIG~ Alternatively as shown in FIG~12 worm and wormwheel reduction means.may be employed with bevel wheels 193 aubstituted for the gear D gear 53~ these bevel wheels 193 driving a worm 28 and wormwheel 290 ., : Al~o it would be noted that previou~ly the FIG~. from 1 to 9 concern an external ~ixed gear A 30 and an internal -~ixed gear F 31 and a centre revolving gear D 35 or internal revolving gear FD 34 driven by integral epicyclic gears 32 and C 33, these integral gears B 32 and C 33 being o~
di~erent diametersO
: 1 .
Now in FIG~ 14 and FIG~15 examples are shown, with a . -27-,.. :,. , .
., . , . . :
- : ~
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.
fixed internal gear F 31 utilised with a freely revolving internal gear FD 34 with the integral gears B 32 and C 33 now being of equal diameters with intermediate gears 102 in ~esh with gear C 33 and freely re.volv.i~g.gear FD 340 ~o that the observed and actual revolutions of the ~reely revclving gear FD 34 would be B x FD + 1 and when F=9, B=3, C=3 and FDL9 then 3 x 9 + 1 -- 1+1 _ 2 actual and observed revolutions of internal gear FD 34~
FIG~15 i~ similar to FIGol4 but in FIGol5 a series oi ordinary revolving ~ears 540 55 and 63 running on spindles 190 securéd in a framework 191 are in mesh with the internal revolving gear FD 34 and a centre gear D
gear 53 say for example of 1,'- inch diameter. Also are shown the fixed spindle 10 with carrier 11 and the input disc 36 and flywheel discs 21 to 25 ahd securing screws 1800 Also when a fixed internal diameter gear F 31 1 utilised with integral gears B 32 ~nd a 33 of equal diameter as shown in FIGo 16 then in this case the gear C 33 .can be omitted and the assembly would then be as in FIG 17 . ., with the gears B 32 in me~h with a centre ~reely revolving gear D 35, the gears B 32 running on spindle~ 103 secured in the input discs 360 So that when F~9, B=3, C-3 and D=3 then the actual and observed revolutions of centre gear D 35 would be B x D + 1 which is 3 x 3 ~ 1 = 3 + 1 = 4 !
~!
. .. . . . . . . . ~ . .
.. ...
2~
and when C ~3 is omitted9 then the actual and observed F omitted C same size as B
revolutions D 35 wo~ld be B x D
+ 1 or actual and observed revolutions of D 35, are F x B ~ 1 so that F=9, B=3, B=3 and D=3 then B x D~ + 1-3+l=4~ Also are shown the fixed spindle lG, with carrier 11 and the input disc 36 and flywheel disc 21 to 25 and securing screws 18C~
Also as in FIGD 18 an external fixed gear A 30 could ~-be utilised with an external freely revclving gear D 35 with equal diameter integrc~ gears B 32 and C 33 and intermediate gears 104. So that the observed and actu~1 revolutions of the freely revolvi~g external gear D 35 would be B x D I 1 and when A=3, B=~, C=3, DL9, then ~ ~ I
3 x 9 ~ 1 = 1 x ~ + 1 = 1-~ actual and observed revolutions j o~ external gear D 350 ~ IG. 19 is similar to FIG~ 18 but in FIGo 19 ordinary revolving gears 54 and. intermediate gears 104 and 105 are in mesh with the external revolving gear D 35 and al~o with a centre gear D gear 53 the ordinary revolving gears 54 running on a spindle 190 in a ~ramework 191 attached to the baseO Also are æh~wll the fixed spindle lO,with carrier 11 and the input disc 36 and ~lywheel di~cs 21 to 25, Also in FIG. 20 is shown an external fixed gear A 30 utilised with an internal ~reely revolving gear FD 34 with .. . .~ . . : . :
. .
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equal diameter integral gears B 32 and ~ ~3 so that the observed and actual revolutions of the freely revolving A C
internal gear ~D 34 would be B x ~'D + 1 and when A=3, B=3, C=3 and FD=9 then 3 x 9 ~ 1 = 1 x ~ + 1 = 1~
actual and observed revolutions of internal gear FD ~4O
FIG~ 21 is similar to FIGo 20 but in FIG~ 21 the gear C 33 has been om~tted and the gears B 32 ~un on spindles 103 in the input discs 36 and the actual and observed reYolution~ of internal gear FD 34 l~ould be B x ed C same size as B
h'D -~ ~ 1 or actual and observed revolutions of internal gear ~D 34 = B x FD + 1 A B
So that when A=3,B=~,BL3,and FD=9 then B x ~D + 1 =
x ~ + 1 = 1 x ~ + 1 = 1~ actual and observed revolutions of internal gear ~D 340 Also are shown the fixed spindle 10 with carrier 11 and the input discs 36 and flywheel dlscs 21 to 250 Also as in ~IGSo 22 to 27 when the gears, other than the gears with their axi~ on the centre fixed shaft 10 are revolving epicyclicly round the axis of the centre ~ixed shaft 10, then the centrifugal force of these orbiting gears would be taken into ccnsideration and to neutralise the ei~ect of the centrifugal force so caused 9 rollers as in FIGS. 22 to 27 could be attached to the orbiting assemblies, a~d these rollers 64 would run upon a metal ring or rings 65 - ~
,, . . , - . . . . . . . ..
... . , . . -. . ,- .
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recessed into the housing or casing and secured with screws 106 and dowels 1070 These rings 65 could be solid~ or ~or larger assemblies a ring constructed of segments could be utilised 9 bolted and dowelled in position, to the hou3ing or casing, ~nd al90 the rollers 6~ and centrifug~l pressure rings 65 could be hardened and ground ~or enduranceO Alsop oil filler plugs 108 and sealing rings 109 would be incorporated in the housings or casings 9 for oil filling and drai.ning purposes, and the fixed internal gears 31 could also be secured to the housings or casings with screws 110 and dowel8 lll o Also in FIGo 28~ FIG~ 29 and FIG. 30 are shown flywheels at the input and output ends of the unit - i mechanism assemblies and also in between each unit, -in the mechanism assemblies and also with no input flywheels and none between each unit, in the mechanism assemblies but ju~t with the final output flywheels or flywheel mass only as in FIGo310 So that when considering FIGo 28 and when the flywheels are all of similar diameter~ then flywheel 120 would be say of mass 19 revolving say at 8 rOpOmO and flywheel 121 would be revolving 5 times as fast at 40 rOpOmO and would be 3 mass in comparison to flywheel 1200 Similarly ' .
' ' -~ ' ' .,-'.- , :
, . . . , ' ~ , , - ' , : ~ . ', ' ' . .
. . .
.
; ' '' ' ' ' ' . ~ `
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~lywheel 122 revolving at 200 rOpOmO that is 5 times faster than flywheel 121 would be 25 mass by comparison to flywheel 120 and flywheel 1210 Similarly flywheel 123 revoJ-~ing at 1000 rOpOmO that is 5 times ~aster than flywheel 122 would be 125 mass by comparison to ~lywhesls 120, 121 and 1220 So that the momentums of each mass flywheel would be say9 1 x 8 _ 8 and 5 x 40 = 8 and 25 x 200 = 8 and 125 x 1000 =
8 and the kinetic energy o~ the flywheel masses would be say 1 x 8 - 64 and 5 x 40 = 320 and 25 x 200 = 1600 and 125 x 1000 _ 8000 iOeO rising in multiples of 50 .
When now the flywheel masses are reduced in diameter as in FIG~ 29 as 1240 1250 126 and 127 so that they are all of equal mass and their rotary velocity is also equal,0 then this would be as FIGo 290 80 that in FIG~ 29 the momentum o~ each mass would be equal, as in the previous FIGo 28 and now in FIG. 29 the kinetic energy o~ the mas~e~ would also be equal and masses 125 and 126 could be omitted, leaving ~;
mass 124 and 127 or masses 124~ 125 and 126 could be o~itted leavlng mass 127 alone as shown in FIG~ 310 .
When now in the gear arrangements as shown in FIGol I I
then ~or 1 revolution of the input disc ~6 the revolutions o~ the gear D ~5 are as B x D ~ 1 or ~ x which i~ 5 re~olutions. So that, when considering say one , : .
.
-~2-.
- , . . . - . - . .
-- . ; : ., ., ~ -. . . ~ .
: -~ ~O~Q~@~
unit, then when the input revoluticns and the output revolutions are made the same, say ~or example, 1 input revoluti.cn and 1 o~tput revolution, then the m~sses balanced~ would ~e as the ratio is of gear B 32 is to gear C 33 and in this case of FIGo 1~ this is ~ is to 3, namely a ratio of 4. So that considering the pre~ious FIG, 28 when the di.ameters al~ relative masses o~ the wheels were ~imilar, then the follGwing as in FIG~30 would apply, namely mass 128 would be say of mas~ 1 re~olving at say 8 rOpOm. and mass 129 would ~e of mas~ 4, revo].ving at 8 rOpomo and mass 130 would be of mass 16 revolving at 8 r.p.mO and mass 131 would be of mass 64 revolving at 8 rOpOmO
and this making the input and output revolutions equal, could ij be achieved by inserting reduction gearing between each unit, ..
a~ shown in ~IG.300 That is say the output gear D gear 53 of the fir~t unit i9 1~ inches diameter and meshing with the inch diameter gear D gear 53 is a gear 132 Gf 7~ inch diameter integral with which iR the ~ear 133 of 1~ inch diameter and meshing with thi~ 1~ inch diameter gear 133 is an intermediate gear 134 which meshes with the input gear 135 o~ 1~ i.nch diameter which i~ the input gear of tha second unit. So that the mass flywheel 129 i3 slowed b~ a ratio o~ 5, and ;-this arrangement i~ s~own applied to.the other units, and it would be noted that, if the intermediate gear 134 of the la8t output unit was made into 2 gearg ~ then reverse rotation. .
oi the mass 131 would occurO
~33 .. ~ .
.' ' `' : , ,' ' ~8 2~
Figo 31 is similar to ~IGJ30 but now the masses 128 129 and 130 have been omitted leaving mass 136 alone at the output endO So that now, when the input revolutions are multiplied by 125 to give 1000 rO~,mO input revolutions then the ~ollowing as in FIG. 31 would apply~ In FIG~ 31 the prime mover is a 1440 rOp~mO motor 27 on the shaft of which is a pulley 137 of lo 042 inch diameter driving an input pulley 138 of 1~ inch diameterO So that the input re~olucions to the first unit would be 1000 rOpOmO As the gears in the Pirst unit are as in FIGo 1 ~ then the output gear D gear 53 of the first unit would make 5000 r~pOmo and this 5000 rOpomo gear D gear 53 is in mesh with a 7 inch diameter gear 132 integral with which is the gear 133 of 1~ inch diameterO So that the revolutions of the 7~ inch diameter gear 132 and 1~ inch diameter gear 133 would be 1000 r.p.m. This 1000 rOpOmO gear 133 is in mesh with an intermediate gear 134 which in turn i9 in mesh with 1~
inch diameter input gear 135 of the second unit. So that the input speed of' the second unit is 1000 rOp~m. similar to the input speed o~ the first unit. Similar conditions would apply to the third unitO '~he units are supported on a channel 140, also supported on the framework 139 housing the reduction gears 53, 132 ~ 133, 134 and 135 these being mounted as shown in FIGo 31 on a base plate or foundation base~
FIG. 32 shows a centre gear D gear 53 being in mesh with intermediate gears 55 and 54 mounted in a bracket 191 and the intermediate gear 54 i1 in mesh with a ~reely revolving internal diameter gear FD 340 -- .- . : ~ , .. , . .. . - . - ~ -.
, , . . - . . . ~ ' ., , . - ~ . , : ~
.. , , . , . .~ ~ .. .
~0~2~00 ~ IGo 33 shows a similar arrangemen-t to FIG~ 32 but ~ow in FIGo 33 the rotation of the centre gear D gear 53 would be opposite to that in FIGo 32 o In FIGo34 and also if re~erence is made to ~IGol~
then when a similar gear assembly~ as that in FIGolo is uti.lised, as i.n the arrangement shown in ~IG. ~4 then when also re~erence i3 made to FIGo 30 then the gear arrangement as in FIGo 1 could be arranged as in FIG.34. That i~, fixed gear A 143 is 1~ inch diameter and gears B 144 are ~ inch diameter and gears C 145 are 3 inch diameter and gear D 146 i9 1~ inch diameterO So that the output revolutions of the gear D 146 would bs A x C + 1 which i8 ~ x ~ ~ 1 which is 2 x 2 + 1 which i8 5 revolutionsO So that the gear D 146 at 1~ ' -inch diameter would make 5 revolutions, and this gear D 146 o~ l~ inch diameter, making 5 revolution~ would al80 cau~e a gear D gear 142 also o~ 1~ inch diameter which is.
an e~tension o~ the gear D 146 to aleo make 5 revolution~.
~his 1~ lnch diameter gear D gear 142 making 5 revolutions now meshes with a 7~ inch diameter gear 141, ~o that this 7~ inch diameter gear 141 would make 1 revolutionO
Me~hing wi.th the fixed gear A 143 of 1~ inch diameter and the gears B 144 o~ ~inch diameter are the intermediate gear~
i47 of lt inch diameter and i~ the intermediate gears 147 were made into two ~eparate gears 9 then rever~e rotation of the assembly gears would take placeO
-35- .
.: . '~ , 1 -~ . .
'' - ' ' ~ . .
.: ' .
.. . . . .
ze~o~
~he gear A 143 is fixed, but the intermediate gears 147 and the gears B 144 and the gears C 145 which are integral and the gear D 146 are free to revolve5 and are located in frame bars 153 secured by tie bar~ 1580 These frame bars 153 being pivotted about a centre spindle 148 ~he 7~ inch diameter gear 1~1 is fixed to a bar 154 by screws 194 and dowels 195 and thi.~ bar 154 is free to pivot abont the ~pindle 14-9. The spindle 148 secured t~ - -bearing bracket~ 155~ by pegs 156 ~d spindle 149 are supported in the bearing brackets 155 9 the bases of whi~h would be secured to a bench or baseD In the frame bars 153 and 154 are ~ixed, spindles or studs 152, of equal length~ ~
; snd diameters, the centre pivotting distances of these stud~ s or spindles 152 being equidistant ~rom the pivotting centres 148 and 149. So that it could be said, that when the ~rame ~:.
bars 153 and bar 154 being equal in length are in horizontal parallel position as shown in FI~.34 then the mechanism assembly would be in bal~lce. So that now it could be ~aid that, when 1 re~olution of the frame bars 153 18 made, say in an anti-clockwise direction, round the fixed gear A 143 ~ecured to the ~pindle 148 by pegs 157 then this would cause the gesr assembly to revolve epicyclically round ~he flxed gear A 143 and 80 cau3e bar 154 to which is attached .
the 7~ inch diameter gear 141 to revolve al~o in an anti~
clockwise directionO
. ~ _ .
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., . , . . : .. , :,.: ... . : -: . .. . . . :
:: . -:: - .
.. ... , . . . : . ~ .. ,. , ,. .: ~ . . .. ~. , .. -. . ... . . . . . .. ... . .. .. . . . ... .
When now, a mass weight 159 of say mass one is placed on the left hand spindle or stud 152 in the frame bars 1531 then this would fall in an anti~
clockwise manner and so eause the b~r 154 to revolve 9 also in an anti-clockwise mannerO When now, a mass weight 160 is placed on the right hand side spindle or stud 152 on the bar 154 then thi.s mass weight 160 would oppose the falling of the mass weight 159 of mass one9placed on the left hand side spindle or stud 152 in the framie bars 1530 Pre~iously it is stated that the integral gears B 144 and C 145 are ~ inch diamieter and 3 inch diameter respectively~ and this ratio of ~ is to 3, is a ratio o~ to 40 So that with the epicyclic gear assembly shown in FIGo 34 then a mass weight 159 o~ mass one placed on the spindle or stud 152 would balance a mass weight 160 of mass 4 (or just slightly less than 4) placed with care on a spindle or stud 152 on the opposite side to that of the mass one 159. So that their masse~ are opposed ; and al80 the frame bars would still be in a hiorizontal balanced position~ So that it would be noted that when say the mass weight 160 is remo~ed from the assembly, then the mass weight ].59 would drop with ain acceleration, due to gravityO Similarly when say the mass weight 159 is removed ~rom the assembly, then the mass weight 160 would drop with an acceleration, due to gravityO When now, the mass weight 160 a~d the mass weight 159 are replaced with the frame bars , ... . .
,.. . . ~ . . , , . ~ :
- . . . - . . : .
~` ~.(1~2~
15~ and 1.54 in the horizontal position as shown in FIG. 34 then when movement of the mass weight 159 occurs then this would callse the balanced mass weight 160 ~ so to move in a corresponding manner and this movement o~ the balanced masses would be a movement of velocity, and not accelerationO So that, say, for examplep the balanced masses 159 and 160 move with a velocity of one, due to both masses being placed, equidistant, from the centre pivot then the mass weight 15g would move with a mass of one and a velocity of one, whereas the ma~s weight 160 would move with a mass of 4 and a velocity of one.
So that when now, mass weight 159 of mass one, is placed on a fi~ed spindle or as the sasne fixed spindle 10, in the previous FIGS, on which the gear A 30, i8 fixed, and when the ma~s weight 160 of mass 4 is placed also on the same fixed spindle 10, these ma~ses I being at the input and output ends o~ the epicyclic gear as~embly, then the mechanism shown in the FIGo 34 assesnbly could become as the FIGo 30~ SO that when referring now to ~IG~ 34 the e~ual centre pivotting distances of the masa weight 159 and the ma.ss weight 160 could be regarded as the radius of gi~ation of revolving circular discs.
So the momentum of mass weight 159 of mass one, moving at say a velocity of one, would have a momentum of one, .
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. . . -.. -. . . . . ~ , . .
2~
and the momentum of the balancecl mass weight 160 of mass 4 moving at say a velocity o~ one, would have a momentum of 4O Similarly the kinetic energy of the balanced revolving masses revolving at a velocity o~
one, would be for mass weight 159, mass one times a velocity o~ one 9 times one, which is one, and the kinetic energy of mass weight 160, would be, mass 4 times a velocity of one time~ one, which is 40 So that by comparison, mass weight 160 would possess 4 times the momentum and 4 times the kinetic energy of mass w~ight 159.
Al~o a~ stated in FIG,34 when the frame bars 153 tend to make one re~Glution, then the bar 154 also tends to make one revolution and when the mass weight 159 and mass weight 160 are placed 9 with inertia borne in mind9 in po8ition with care, a~ in FIG~ 34 then the assembly would be in balance and no movement would occurO It i~ to be noted that the ma~s weight 159 and ma~s weight 160 are placed diametrically opposite with their tendency to motion opposed, and thls could also be arranged, i~ required9 in the gear a~emblie~ shown, in the previous FIGSo by the in~ertion oi an additional intermediate gear which would not be detrimental to the mechanical efficiency oi the arrangement~0 It i~ with renown, that large reduction gear unit !
~ g _ , ., -, , . -- . .. .
. - . .. .. . . . .- ... - . - - :
. ~ . - , . . , -~ o~
assemblies are utilised, in modern arrangements for s~ip propulsion. So that in the assemblies shown, such as say in FIG. 30 when comparatively low output revolutions are required~ the reduction gearing drives between the units could be by suitable worm and wheel reduction gearing, and if re~uired, input and output masses could be utilised in the la~t unit, with the input and output masses omitted in other unitsO Also in arrangements when the reduc-tion gearing between the units is large 9 with any comparative low output revolutions, then such arrangements could be adaptable ~or and applied to ship propulsion and it would be apparent that to have high output revolutions ror ship prop~.sion would be a repulse for high revolutions due to the high inertia of the very heavy mass o~ the ships.
So that when reduction gearing is utilised, between the gear units, as stated, then oil filler and drainage plugs and seal~ could be incorporated in the hood, or cover, o~ the assemblies, to facilitate functioning of the m~chani8m assemblies.
Further practical applications o~ the gear unit as~emblies could be utilised as in ~IG. 35 and FIG.36.
~IG.35 8hows 3 gear units 161,162 and 163 such as those I ùtilised in the previou~ ~IGS, and the~e gear units are assembled in a vertical manner, so that the input gear 164 and output gears 165 are opposite on each unit~ So that a prime mover 168, secured on a bridge 173, would drive the _ -40 , .. , . , . . .. , ~,:
:
:, - . , .
~ ~Qi~
input gear 164 of the unit 161 through motor driving gear 166 and intermediate gear 1670 So that the input gear 164 on the first unit 161 driving through the unit 161 would cause the output gear 165 of the first unit 161 to revolve, and this output gear 165 of the first unit 161 would now drive, through intermediate gear 167, the input gear 164 of the second unit 162 which would cause the output gear 165 of the second unit 162 to revolve, and so drive, through the intermediate gear 167 the input gear 164 of the third unit 163 which in turn would cause the output gear 165 of the third unit 16~ to revolve and this revolving output gear 165 of the third unit 163 would through intermediate gear (or gears) 169 drive a gear 171, this gear 171 being integral and part o~ a railway bogie waggon wheel 1700 These wheels 170 running on railway lines, or other tracksO
~he whole assembly would be supported on a frame or bridge 173 which would be part o~ the railway bogie assembly and through which passes the spindle or spindles 172. So that when the prime mover, or say an electric motor 168, i~ energised with power from say an overhead pantagraph, or by means o~ central rail ground power supply, the gear unit assemblies would transmit the power to the locomotive ~aggon or bogie wheels and so propel the complete assembly along the rails or track, the speed and distance propelled being relative to the gear unit assemblies utilisedO
1, ~
.~ . , . .......... . . . . - - :
- .
FIGo 36 is similar to FIG~ 35 but in FIGo 36 the gear unit assemblies are arranged horizontallyO
These arrangements could also be adapted to other forms of locomotion other than tracked vehicles and whil~3t t~iese arrangements are adaptable to tracked ~ehicles they could also be utilised for other forms of locomotionO
In FIGo 37 is shown an arrangement of how the mechani~m assembly in the apparatus demonstrating balancing of mas,ses as in FIGo 34 could be adapted to be ~imilar to say a conventional pair of scales, and it would be noted that the centre of gravity of the masses 90 balanced would be similarO The reference numerals are as in FIGo 34 o !~
, .`
~, : .
' . ' , ' : - '' , . -- ., ; , : ..
., . - ~ ' . . . . . . .
~: , ~ ,. .. ; ... . ~ i , , , ,' ' ` ~ . ' :. .- , .
-
Claims (13)
1. An epicyclic gear mechanism characterised in that there is provided a series of gear trains on a fixed shaft, each gear train including a rotatable cage J at least two planet gears on the cage and rotatable relative to the cage, a stationary gear pinion and an output gear rotatable relative to the cage and connected to an input pinion of a successive gear train, there being a stepwise increase in output speed of the gear train and a final output means in the form of an output pulley or gear rotatable on the stationary shaft.
2. An epicyclic gear mechanism as claimed in CLAIM 1 in which there are four planet gears on an input side of the cage, the latter consisting of a pair of spaced-apart disc like elements connected together for simultaneous rotation.
3. An epicyclic gear mechanism as claimed in CLAIM 1 in which the stationary gear pinion is a sun pinion fixed to the stationary shaft and in which input to the gear train is through the case to the planet pinions,the latter being of compound form and being mounted one on the inputside of the cage and one on the output side, the output gear being also in the form of a sun pinion rotatable on the stationary shaft and connected to the input pinion of a successive gear train.
4. An epicyclic gear mechanism as claimed in Claim 3 in which the connection of the output sun gear of the first and successive gear trains is connected to the input pinion of the successive gear trains, with the exception of the output sun pinion of the last gear train, through the cage, the input pinions of the successive gear trains being planet gears.
5. An epicyclic gear mechanism as claimed in claim 1 or 2 in which an intermediate pinion is located between the stationary sun pinion and input planet pinions at the input side of the cage, there being an intermediate pinion between the rotatable sun pinion and each of the planet pinions at the output side of the cage.
6. An epicyclic gear mechanism as claimed in claims 1 or 2 in which the output sun pinion of the last gear train is connected to an output pulley or gear on the stationary shaft.
7. An epicyclic gear mechanism as claimed in CLAIM 1 in which the stationary gear pinion of each gear train is in the form of a gear ring extending around and enmeshed with the planet pinions at the input side of the cage, the planet pinions of the output side of the cage being connected to an output sun pinion rotatable around the stationary shaft and connected to the input planet pinions of a successive gear train through the input side of the cage.
8. An epicyclic gear mechanism as claimed in CLAIM 7 in which the final output gear is in the form of a sun pinion rotatable around the stationary shaft and connected to an output gear or pulley also rotatable on the stationary shaft.
9. An epicyclic gear mechanism as claimed in claims 1 or 2 in which a flywheel is provided between the first gear train and a prime mover, there being a further flywheel attached to the final output pulley or gear.
10. An epicyclic gear mechanism as claimed in CLAIM 1 in which some of the gear trains have a stationary gear pinion in the form of a sun gear mounted on the stationary shaft and other gear trains have a stationary gear pinion in the form of a gear ring surrounding and enmeshed with the planet pinions at the input side of the gear train.
11. An epicyclic gear mechanism as claimed in claims 1 or 2 in which a reduction gear system is provided between a prime mover and the input gear of the first gear train.
12. An epicyclic gear mechanism as claimed in CLAIM 1 in which the stationary gear is in the form of a gear ring extending around and enmeshed with the planet pinions of the first gear train, there being a drive connection between the planet pinions of the first gear train and a free gear ring of a subsequent gear train which includes a sun gear the latter being the output year of the subsequent gear train.
13. An epicyclic gear mechanism as claimed in CLAIM 1 in which the stationary gear is in the form of a sun gear on the fixed shaft, said sun gear meshing with a series of intermediate gears including planet gears adapted to drive a free gear ring of a subsequent gear train which includes a sun gear the latter being the output gear of the subsequent gear train.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA281,600A CA1082000A (en) | 1977-06-28 | 1977-06-28 | Epicyclic gear mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA281,600A CA1082000A (en) | 1977-06-28 | 1977-06-28 | Epicyclic gear mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1082000A true CA1082000A (en) | 1980-07-22 |
Family
ID=4108993
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA281,600A Expired CA1082000A (en) | 1977-06-28 | 1977-06-28 | Epicyclic gear mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1082000A (en) |
-
1977
- 1977-06-28 CA CA281,600A patent/CA1082000A/en not_active Expired
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Legal Events
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|---|---|---|---|
| MKEX | Expiry | ||
| MKEX | Expiry |
Effective date: 19970722 |