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7/30/2019 SECTION-13.pdf
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SECTION 13 BEVEL GEARS
Page 1 of 17
DESIGN PROBLEMS
751. Decide upon the pitch, face, gN , material, and heat treatment of a pair of straight
bevel gears to transmit continuously and indefinitely a uniform loading of 5 hp at
900 rpm of the pinion, reasonable operating temperature, high reliability;
75.1gm ; inDp 333.3 . Pinion overhangs, gear is straddle mounted.
Solution:
( )21
22
gp rrL +=
75.1
11tan ==
g
pm
o75.29=p
pp rL =sin
2333.375.29sin =L
inL 358.3=
lbv
hpF
m
t
000,33=
( )( )fpm
nDv
pp
m 4.78512
900333.3
12===
( )lbFt 210
4.785
5000,33==
( ) tmsfd FKNVFF =
( )56.1
50
4.78550
50
50 21
21
=+
=+
=mvVF
One gear straddle, one not
2.1=mK
Table 15.2, uniform
0.1=sfN
( )( )( )( ) lbFd 3932102.10.156.1 == Wear load
2
2
2
=
rt
lcd
pw CK
C
C
s
bIDFe
inDp 333.3=
( ) inLb 0.1358.33.03.0 === Temperature factor
0.1=tK , reasonable operating temperature
Life factor for wear
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SECTION 13 BEVEL GEARS
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0.1=lC for indefinite life
Reliability factor for wear
25.1=rC high reliability
Geometry factor for wear, Fig. 15.7
Assume 080.0=I
Elastic coefficient (Table 15.4)Steel on steel , 2800=eC
dw FF =
( )( )( )( )
( ) ( )( )393
25.10.1
0.1
280008.00.1333.3
2
2
2
=
cds
psiscd 370,134=
Table 15.3, use Steel, (300)
ksiscd 135=
Strength of bevel gears
rts
l
d
ds
KKK
K
P
bJsF =
Size factor, assume 71.0=sK
Life factor for strength
1=lK for indefinite life
Temperature factor,
1=tK good operating condition
Reliability factor
5.1=rK high reliability
Geometry factor for strength (Fig. 15.5)Assume 240.0=J
inb 0.1=
ds = design flexural stress
Min. BHN = 300
ksisd 19=
ds FF =
( )( )( )( )( )( )
3935.1171.0
1240.00.1000,19=
dP
11=dP
say 10=dP
so that inP
bd
0.110
1010===
( )( ) inmDD gpg 833.575.1333.3 ===
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SECTION 13 BEVEL GEARS
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( )( ) 33.58833.510 === gdg DPN
say 58=gN
Use 10=dP , inb 0.1= , 58=gN
Material = steel, min. Bhn = 300
752. A pair of steel Zerol bevel gears to transmit 25 hp at 600 rpm of the pinion;
3=gm ; let 20pN teeth; highest reliability; the pinion is overhung, the gear
straddle mounted. An electric motor drives a multi-cylinder pump. (a) Decideupon the pitch, face width, diameters, and steel (with treatment) for intermittent
service. (b) The same as (a) except that indefinite life is desired.
Solution:
dd
p
pPP
ND
20==
( )fpm
P
PnDv
d
dpp
m
1000
12
60020
12=
==
LetdP
b10
=
Dynamic load
( ) tmsfd FKNVFF =
lbv
hpF
m
t
000,33=
( ) d
d
t P
P
F 6.2621000
25000,33 =
=
dd
dm
PP
PvVF
121.11
121.11
50
100050
50
502
1
21
21
+=+=
+
=+
=
Table 15.2, electric motor drives a multi-cylinder pump
Service factor, 25.1=sfN
One gear straddle, one not, 2.1=mK
( )( )( )
+=
+=
d
dd
d
dP
PPP
F121.1
13946.2622.125.1121.1
1
(a) Strength of Bevel Gears
rts
l
d
ds
KKK
K
P
bJsF =
Size factor, assume 71.0=sK
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SECTION 13 BEVEL GEARS
Page 4 of 17
Life factor for strength
Intermittent service, use 6.4=lK
Temperature factor, say 0.1=tK
Reliability factor, highest reliability
0.3=rK
Geometry factor for strength
p
g
gN
Nm =
20=pN
( ) 60203 ==pN
Fig. 15.5, 205.0=J
dPb
10=
Design flexural stress, steel
Assume ksisd 15=
ds FF =
( ) ( )( )
( )( )( )
+=
d
d
d
d
PP
P
P 121.11394
30.171.0
6.4205.010
000,15
+=
d
d
d PP
P
121.11394
408,662
814.4=dP
say 5=dP
inP
bd
0.25
1010===
Wear load for bevel gears2
2
2
=
rt
lcdpw
CK
C
C
sbIDF
e
inP
ND
d
p
p 45
20===
0.1=tK
Life factor for wear, intermittent service
5.1=lC
Reliability factor for wear, highest reliability
25.1=rC
Geometry factor for wear, Fig. 15.7
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SECTION 13 BEVEL GEARS
Page 5 of 17
20=pN , 60=gN
083.0=I
Elastic coefficient, steel on steel (Table 15.4)
2800=eC
5=d
P
dw FF =
( )( )( )( ) ( )( )
( )
+=
5
121.115394
25.10.1
5.1
2800083.024
2
2
2
cds
psiscd 730,155=
Table 15.3
Use steel, min. BHN = 360, ksiscd 160=
5=dP
inb 2=
inDp 4=
( )( ) inDmD pgg 1243 ===
steel, min. BHN = 360
(b) For indefinite life,
0.1=lK , life factor for strength
0.1=lC , life factor for wear
Strength:
rts
l
d
ds
KKK
K
P
bJsF =
ds FF =
( ) ( )( )
( )( )( )
+=
d
d
d
d
PP
P
P 121.11394
30.171.0
0.1205.010
000,15
+=
d
d
d PP
P
121.11394
437,142
799.2=dP say 3=dP
inP
bd
33.33
1010===
Wear load
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SECTION 13 BEVEL GEARS
Page 6 of 17
2
2
2
=
rt
lcdpw
CK
C
C
sbIDF
e
inP
ND
d
p
p 67.63
20===
dw FF =
( )( )( )( ) ( )( )
( )
+=
3
121.113394
25.10.1
0.1
2800083.033.367.6
2
2
2
cds
psiscd 744,113=
Table 15.3
Use steel, min. BHN = 240, ksiscd 115=
3=dP
inb 33.3=
inDp 67.6=
( )( ) inDmD pgg 2067.63 ===
steel, min. BHN = 240
753. Decide upon the pitch, face, and number of teeth for two spiral-bevel gears for a
speed reducer. The input to the pinion is 20 hp at 1750 rpm; 9.1gm ; pinion
overhung, gear-straddle mounted. It is hoped not to exceed a maximum pD of 4
3/8-in.; steel gears with minimum 245 BHN on pinion and 210 BHN on gear.The gear is motor-driven, subject to miscellaneous drives involving moderate
shock; indefinite life against breakage and wear with high reliability. If the gears
designed for the foregoing data are to be subjected to intermittent service only,how much power could they be expected to transmit?
Solution:
(a)( )( )
fpmnD
vpp
m 200012
1750375.4
12===
( )lb
v
hpF
m
t 3302000
20000,33000,33===
Dynamic load
( ) tmsfd FKNVFF =
One gear straddle, one not2.1=mK
Table 15.2Motor-driven, moderate shock
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SECTION 13 BEVEL GEARS
Page 7 of 17
25.1=sfN
21
21
70
70
+=
mvVF , spiral
( )254.170
2000702
1
21
=
+=VF
( )( )( )( ) lbFd 6213302.125.1254.1 ==
Wear load2
2
2
=
rt
lcdpw
CK
C
C
sbIDF
e
inDp 375.4=
Temperature Factor, 0.1=tK
Design contact stresses,245=BHN , pinion
ksiscd 116=
Life factor for wear
0.1=lC , indefinite life
Reliability factor for wear
25.1=rC , high reliability
Geometry factor for wear, Fig. 15.8
Assume 12.0=I
Elastic coefficient, steel on steel (Table 15.4)
2800=eC
( )( )( )( )
( ) ( )( )bbFw 721
25.10.1
0.1
2800
000,11612.0375.4
2
2
2
=
=
dw FF =
621721 =b
inb 8613.0=
say ininb 875.08
7==
Strength of gear
rts
l
d
ds
KKK
K
P
bJsF =
ds = design flexural stress
min. BHN = 210
ksisd 4.15=
Size factor, assume 71.0=sK
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SECTION 13 BEVEL GEARS
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Life factor for strength
1=lK for indefinite life
Temperature factor,
1=tK
Reliability factor
5.1=rK high reliability
Geometry factor Fig. 15.6
Assume 28.0=J
( )( )( )( )( )( ) dd
sPP
F3543
5.1171.0
128.0875.0400,15=
=
ds FF =
6213543
=
dP
7.5=dP
say 6=dP
Then, 6=dP , inb8
7= , ( )( ) 266375.4 === dpp PDN
( )( ) 50269.1 === pwg NmN
(b) Intermittent service onlyStrength
rts
l
d
ds
KKK
K
P
bJsF =
psisd
400,15= (Gear)
For 6=dP , 64.0=sK
For indefinite service, 6.4=lK
0.1=tK , 5.1=rK
Geometry factor, Fig. 15.6, 26=pN , 50=gN
292.0=J
( )( )( )( )( )( )
lbFs 31425.1171.0
6.4
6
292.0875.0400,15=
=
Wear load2
2
2
=
rt
lcdpw
CKC
CsbIDF
e
inDp 375.4=
0.1=tK
ksiscd 116=
2800=eC
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SECTION 13 BEVEL GEARS
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5.1=lC intermittent service
25.1=rC
Geometry factor for wear, Fig. 15.8
26=pN , 50=gN
116.0=
I
( )( )( )( )
( ) ( )( )lbFw 1098
25.10.1
5.1
2800
000,116116.0875.0375.4
2
2
2
=
=
use dw FF =
( ) tmsfd FKNVFF =
( )( )( ) tF2.1125254.11098 =
lbFt 584=
( )( )hp
vFhp mt 35
000,33
2000584
000,33===
CHECK PROBLEMS
755. A pair of straight-bevel gears are to transmit a smooth load of 45 hp at 500 rpm
of the pinion; 3=gm . A proposed design is .15 inDg = , .8
32 inb = , 4=dP .
Teeth are carburized AISI 8620, SOQT 450 F. The pinion overhangs, the gear is
straddle-mounted. Would these gears be expected to perform with high reliabilityin continuous service? If not would you expect more than 1 failure in 100?
Solution:
inm
DD
g
g
p 53
15===
( )( )fpm
nDv
pp
m 65512
5005
12===
( )lb
v
hpF
m
t 2267655
45000,33000,33===
Dynamic load
( ) tmsfd FKNVFF =
( )512.150
65550
50
50 21
21
=+
=+
=mv
VF
One gear straddle, one not
2.1=mK
Smooth load, 0.1=sfN
( )( )( )( ) lbFd 411322672.10.1512.1 ==
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SECTION 13 BEVEL GEARS
Page 10 of 17
Strength of bevel gears
rts
l
d
ds
KKK
K
P
bJsF =
Size factor, for 4=dP ,
71.0=s
K
Life factor for strength
1=lK
Temperature factor,
1=tK
Geometry factor for strength (Fig. 15.5)
( )( ) 2054 === pdp DPN
( )( ) 60154 === gdg DPN
205.0=J
ksisd 30= (55 63 Rc) for carburized teeth
( )( )( )( )( )( ) rr
sKK
F5143
171.0
1
4
205.0375.2000,30=
=
ds FF =
41135143
=
rK
5.125.1
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SECTION 13 BEVEL GEARS
Page 11 of 17
41136364
2=
rC
25.1244.1 =rC , high reliability
Since 5.1