Download PDF - Gear Technology magazine
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DESCRIBING NONSTANDARD GEARS ..<br />
(continued from page 20)<br />
Derivation of Equation 5:<br />
p'<br />
p'<br />
011 (tbl - inv¢') + 01 2<br />
(. th2. - inve') +B'<br />
ObI 0"2.<br />
p' tbl ..., 0'2 tb2 D'2 . , B'<br />
-----mv¢ +-----mv¢ +-<br />
0'1 Dbl D'l ~1 OIl D'l<br />
L_Ph<br />
D\ ObI<br />
0'2 Db2<br />
----<br />
Crossed<br />
Conditions:<br />
Axis <strong>Gear</strong>s<br />
• Axis are in parallel<br />
planes.<br />
• N ormal operating circular pitches are equal<br />
• Normal operating pressure angles are equal.<br />
• Sum of normal operating tooth thicknesses plus normal<br />
circular backlash equals operating normal circular pitch.<br />
Derivation of Equation 12:<br />
Given: tOnI' tbn2' a, N1, Nz, PN, Px1 and Px2<br />
Note that axial pitches are different fo,r the two gears.<br />
OIl Dj,1<br />
Note: B~is transverse backlash at 0 1 ,<br />
B is transverse backlash in plane of action.<br />
for<br />
each gear:<br />
j<br />
1I'D<br />
N<br />
t'n -<br />
t't coS¢'<br />
ttb _ 'I' tnb<br />
OJ,<br />
NPN<br />
_ N p'n..<br />
O'COSlP'<br />
'IT<br />
D'lCOS¥/'l<br />
, ;, ., 11' tnhl '.' . ..' r tnbz. ,<br />
Pn-DICOSlPl(•.- -mv¢tl)+D2c.oSlPz(-.--mv¢t2)+B n<br />
N1Pn.<br />
NzPn<br />
., _, (tnbI+tnb2) Pn'N<br />
I,<br />
,'N<br />
A.' P.n-2._ A.' +·B<br />
Pn-Pn - -. - --mv"'·t1 - --mv"'t2 ·n<br />
PN PN 11' 11'<br />
, tnbl tnb2 Nl.. j N2. , B n<br />
l---+----Invcf> n--InvrP t2+-<br />
PN PN 11' 11' p'n<br />
NI<br />
N!!.I!'U! you r ,!!,ppUc:atlonl<br />
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(Bn_BN)<br />
p'n<br />
Pn<br />
TINI +T2N2+'l: BN<br />
PN<br />
tbl tb2 BN<br />
or . -=NIL )+N 2 (- .. -+ 11' (-)- 'II'<br />
ObI Db2 PN<br />
(22)<br />
(12)<br />
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CIRCLEA-4 ON READER,REPLYCARD<br />
Tooth Thickness (See Fig. 8.)<br />
Derivation of Equation 13:<br />
Rl is the radius<br />
where:<br />
"t" - tooth thickness is equal to "s" - tooth space.<br />
¢1 is the pressure angle at that radius.<br />
~ is the base circle radius.<br />
22 <strong>Gear</strong> Technol.ogy