design summary
TRANSCRIPT
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GEAR DRIVE DESIGN JONATHAN BUNIE
APRIL 26 2012
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PROJECT SUMMARY
This gear drive was designed for Titan Industries for the purpose of powering coal
transfer conveyers. As requested, it was designed using a Baldor CEM3769T-5 three phase
electric motor rated at 7.5 horse power at 3525 rpm. The drive consists of three shafts, two
pinions, two gears, three different types of bearings, and other support accessories as well.
The motor is mounted directly to the gear housing with the shaft entering the housing
through the back. The shaft must be reduced to a ¾ inch diameter due to the small size of the
pinion. The motor’s shaft is supported by a bearing to resist stress resulting from bending
moment. The input pinion is mounted directly to the motor shaft using a key to transmit torque
and a retaining ring for pinion positioning on the shaft. There are also three identical spacers
located in a row between the inner bearing race and the pinion also for the purpose of axial
location on the shaft.
The intermediate shaft has a nominal diameter of 1.25 inches but has and enlarged
diameter section located against the inner race of the rear bearing and is used for resisting
thrust loads on the shaft thus maintaining shaft position. The rear intermediate gear is placed
against the opposite side of the enlarged section and is constrained using a key for
transmitting torque followed by a spacer to separate the gear and the pinion on the same
shaft. The rear end of the shaft is threaded to receive a nut which secures the shaft to the
bearing. The front of the shaft contains a retaining ring and groove before entering the bearing.
This combination prevents any axial shaft translation.
The output shaft is slightly longer than the intermediate shaft for the acceptance of the
chain sprocket however they share the same nominal diameter. Similar to the intermediate
shaft, there is also a section of the output shaft with a larger diameter to prevent axial
movement of the gears. The rear end is threaded for fixation to the bearing. The gear is
constrained using a key for torque transfer as well as a retaining ring to prevent axial
APRIL 26 2012
GEAR DRIVE DESIGN
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APRIL 26 2012
PROJECT SUMMARY (CONT.)
movement. The front end of the output shaft is splined and threaded in order to attach the
chain sprocket using a large nut. All shafts are manufactured using 1040 cold drawn steel
incorporating a safety factor of four.
The housing is constructed using quarter inch thick 1040 cold drawn steel. All joints are
welded with the exception of the cover plate which is secured using bolts. The cover plate
provides easy access for assembly and disassembly and provides support for the shaft and
bearings.
The following standard parts were incorporated into the design: Four high load, double
sealed bearings for 1.25 inch shaft diameter and one high load, double sealed bearing for ¾
inch shaft diameter, one #6799K26 Stainless steel machinable-bore sprocket for #80 roller
chain, several various size stainless steel shims, aluminum washers, and ½-13 grade 8 steel
hex nuts and 1.75 inch bolts. The retaining rings used are external type rings with a black
finish. Finally, Buna-N O-ring cord stock must be used as an oil seal between the cover plate
and housing.
Using the provided fill ports, add 5.25 US Quarts of API GL-3 Gear oil for proper gear
lubrication.
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APRIL 26 2012
GEAR DESIGN
MOTOR SHAFT
The motor shaft contains one pinion with a key to transmit torque. The pinion is constrained axially with a retaining ring and a spacer to separate the pinion from the bearing. The pinion has a diametral pitch of 8 and with a 2.25 inch diameter, the number of teeth total 18. The pinion is manufactured using .20 carbon steel giving an allowable bending stress of 20000lb. The total bending stress was calculated to be 12151 lb. The pinion was designed to slide freely onto the shaft with an RC1 tolerance. All gears in the unit were designed with a 1 inch face width.
INTERMEDIATE SHAFT
Contains two gears, one receiving power from the motor
pinion, and one transmitting power to the output shaft.
Both gears transmit torque with a 1 inch long by .25 inch
square key.
Both have a diametral pitch of 8. The larger gear has a
diameter of 8.28 inches and has 66 teeth. The smaller
pinion has a diameter of 2.25 inches and has 18 teeth.
Both gears are designed to slide freely over the shaft
using an RC1 tolerance.
The two gears are constrained between the enlarged
diameter shaft section and a retaining ring before the front
bearing. One spacer separates the gear from the pinion.
The gear and pinion are manufactured using .20 carbon
steel giving an allowable bending stress of 20000lb. The
total bending stress was calculated to be 12151 lb for the
gear and 19452.7 lb for the pinion
OUTPUT SHAFT
Contains one gear receiving power from the intermediate
shaft.
The gear has a diametral pitch of 8. It has a diameter of
8.28 inches and has 66 teeth.
It transmits torque through a 1 inch long by .25 inch
square key.
The chain sprocket located outside the gearbox receives
torque through the splines and is constrained between the
bearing and a large nut.
The gear and pinion are manufactured using .20 carbon
steel giving an allowable bending stress of 20000lb. The
total bending stress was calculated to be 19452.7 lb.
The gears and chain sprocket designed to slide freely
over the shaft using an RC1 tolerance.
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APRIL 26 2012
SHAFT DESIGN
MOTOR SHAFT
The motor is manufactured with a shaft with a 1.375 inch diameter. The shaft needs to be reduced to a 0.75 inch diameter to receive the pinion. The keyway on the motor shaft is designed to be 0.19 inch in width and height by 0.945 inch long. Directly after the keyway is a retaining ring groove with a 0.7 inch diameter and a 0.046 inch width. This shaft enters the gearbox through a bearing using a force fit class FN2.
INTERMEDIATE SHAFT Rear threaded end to accept large constraint nut.
Nominal diameter is 1.25 inches with a .188 inch long
section of diameter 1.55 inches.
2 gear keyways separated by a spacer. Recommended
key length of .239 inches was adjusted to 1 inch.
Designed to accept .25 inch square key.
Retaining ring groove immediately following keyways
toward front of shaft. Accepts 1/8’’ thick type 316
stainless steel external retaining rings.
The overall length is 4.056 inches with a chamfer on the
back end and a fillet on the front end.
Both ends are supported by bearings using a force fit
class FN2.
OUTPUT SHAFT Threaded on both ends to accept a large shaft constraint
nut as well as to constrain the chain sprocket to the shaft.
Rear threaded end to accept large constraint nut.
Nominal diameter is 1.25 inches with a 1.313 inch long
section of diameter 1.55 inches.
1 gear keyway immediately after enlarged shaft section.
Recommended key length of .881 inches was adjusted to
1 inch. Designed to accept .25 inch square key.
Retaining ring groove immediately following keyway
toward front of shaft. Accepts 1/8’’ thick type 316
stainless steel external retaining rings.
The overall length is 6.256 inches with a chamfer on both
ends.
Both ends are supported by bearings using a force fit
class FN2.
Torque is transmitted from the chain sprocket through 8
splines. The sprocket is separated from the bearing using
3 identical spacers and is secured axially with a large nut.
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company
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ACCESSORIES
The gears transmit torque in the shaft through the use of keys and keyways. The standard size is .25 inch
square of the intermediate and output shafts and 0.188 inch quare for the motor shaft. They have design
lengths of .881 inches of the output shaft, .239 inches for the intermediate shaft, and .087 inches for the motor
shaft.
The shafts are supported by high load, double sealed bearing and use a class 2 force fit for the shaft mount
and a class 1 clearance fit for the bearings mounted to the housing. All bearing have a maximum of 5000 rpm
and are design for 20000 hr of life.
The 6799K26 Chain Sprocket is a stainless steel machinable bore sprocket for ANSI #80 Roller Chain. The
hub has a 4 inch diameter and the overall width is 1.5 inches. The overall diameter is 5.95 inches with a tooth
pitch of 1 inch. The bore needs to be 1.25 inches with class 1 clearance fit and 8 splines .05x.1 inches.
The shaft components consist of spacers and retaining rings. The spacers are 1/8 inch thick stainless steel
shims for a 1.25 inch and ¾ inch diameters. The
retaining rings are black finish, magnetic, external
retaining rings. The motor shaft receives a .042 inch
thick ring for ¾ inch diameter. The drive shafts receive
a .05 inch thick ring for 1.25 inch diameter.
A large nut is used on the back of the intermediate
shaft and on both ends of the output shaft. It is a 1.75
inch hexagonal nut with 1 ¼ - 7 threads.
Housing
The housing is composed of .25 inch carbon steel
with welded seams.
To assist in maintenance, an access cover was
added for easy assembly and disassembly.
The bearings rest on the access cover and rear of the
housing and are constrained between extruded
portions in the face of the housing.
The access cover is held in place using 16 bolts and
washer assemblies. The bolts are 1.75 inches long
and have ½ - 13 threads and a head width of ¾
inches. The washers are .05 inch thick lightweight
aluminum for a bolt diameter of .5 inches.
The access cover is oil sealed with Buna-N 1/8 inch
O-ring cord stock. The O-ring stock fits into a groove
behind the access cover.
Drain and fill ports were added on the top and left
side for easy maintenance.
A filler cap is manufactured using 1.5 inch hexagonal
stock and is bored with 1 ¼ - 7 threads that are .5
inches deep.
For added strength, the base of the housing
supporting the electric motor is manufactured using ½
inch thick steel.
APRIL 26 2012