DETERMINATION OF POHJR REQUIREMENTS OF A SuIDSR-BED BJLT

CONVEYOR WITH VARIOUS LOADS, BELTS, AND BEDS

by

Jay igldman

A Thesis

Submitted to the School of Graduate Studies of Michigan
State College of Agriculture and Applied Science
in partial fulfillment of the requirements
for the degree of

Master of Science

Department of Mechanical Engineering

1951

THESIS

AB ’3 T RAG T

m

 

A conveyor is a mechanism which is used to move ob-
Jects from one location to another. The belt conveyor
fulfills this requirement by tranSportiog the various
items on a moving belt. Because of their low operating
costs and the ease of handling large volumes of materials,
the use of the belt conveyor spread from its early begin-
ning in the flour mills to other industries. However,
this growth was not without its problems of design and
construction. The main problems which had to be faced by
the design engineers were the proper selection of: belts,
belt tension, supporting surfaces, driving mechanisms,
Speed of flow, unit weights, angle of inclination and the
power required. Each of these problems is a variable
factor which in itself may change the performance of the
conveyor. This thesis concerns itself with the determin-
ation of the power requirements of a slider-bed belt con-
veyor by varying the loads, surfaces and the belts with
the other factors held constant.

The apparatus used for this test is a standard
slider-bed belt conveyor plus a Special dynamometer driv-
ing mechanism which was so constructed that the driving
force on the conveyor could be easily determined and the

power requirements computed. The surfaces which were

a!

ems

4
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.3;)

N

used in this test were as follows:

1. Enameled steel

2. Unpainted hot rolled steel

5. Type 502 stainless steel, #4 brush finish

4. Fir plywood .

5. Maple plywood

6. 61 ST aluminum
The belts which were used in this test are as follows:

1. Rough-top rubber

2. Smooth-top rubber

3. Neoprene rubber

4. Innerbound canvas

5. Impregnated canvas (Red Gandy 32)

6. Silver duck canvas top, rubber base

7. Chemigum

With the tension, speed, angle of inclination, and
the unit load held constant for each of the belts, the
test runs were made. The test consisted of taking scale
readings at zero, two hundred, four hundred, and six
hundred pound total loads with each belt on each surface.

The results of this test must be stated in a gen-
eral way since each belt acted somewhat differently on
the various surfaces. However it can be said that the
enameled steel surface required the most power to drive
the belts. The aluminum and stainless steel surfaces

required somewhat less power than did the enameled surface,

and the maple wood, fir wood, and unpainted hot rolled
steel surfaces required the least power. The belts which
required the most power to run over all of the surfaces
were the impregnated canvas, the innerbound canvas, and
the silver duck canvas. The neOprene, chemigum, smooth-
top rubber, and rough-top rubber belts required less
power than did the canvas belts.

Since none of the conveyor load vs. horsepower re-
quired curves start from the origin it is evident that
there is a certain amount of power required to drive the
conveyor at zero load which can be attributed to the
friction of the pulleys, the weight of the belt and the
bending of the belt, as well as an additional amount of
power required to drive the conveyor once a load has been
applied which is due to the additional frictional drag
plus the change in velocity to bring the load up to belt
speed.

It should be emphasized at this time that all of
the variable factors mentioned in this thesis play a very
important part in the performance of a conveyor. The
figures obtained in this study are the results of an
attempt to cancel out as many of the variables as possible
and varying the remaining factors under controlled con-

ditions, in order to make a comparison of a number of

belts and slider-beds. M/ g 2 .

War/(AME.

ACKNOHLEDGWENTS

 

 

The author wishes to express his deepest gratitude
and sincere thanks to Mr. J. M. Apple, under whose able
direction this investigation was conducted. He is also
greatly indebted to the Rapids-Standard Company and its
personnel for their support in furnishing the equipment
for this project, as well as all their helpful suggestions
and valuable assistance. Grateful acknowledgment is also
due to Mr. J. R. Barnes for his untiring help on this
thesis, and to all the others for their suggestions and

assistance in one way or another.

TABLE OF CONTENTS

PAGE

LIST CF GREXPHS o o o o o o o o o o o o o o o o o o 0
LIST CF FLIXTICS o o o o o o o o o o o o o o o o o o o

SLIDER-BED BELT CONVEYOR - FIGURE 1 . . . . . . . .

(1)qu

IKTRODUCTION . . . . . . . . . . . . . . . . . . . .
APPARATUS . . . . . . . . . . . . . . . . .
SLIDER-BED BELT CONVEYOR - FIGURE 2 . . . . . . . . ll
PROCEDURE . . . . . . . . . . . . . . . . . . . . . l4
CRADLE TYPE DYNAMCMETER - FIGURE 3 . . . . . . . . . 15
TENSION TAKE UP ADJUSTMENT ON SLIDfiR-EED BELT

CONVEYOR - FIGURE 4 . . . . . . . . . . . . . . . '17
DRIVING ESCHANISM CF SLIDER-BED BELT CONVEYOR -

FIGURE.5 . . . . . . . . . . . . . . . . . . . . . l9
RUNNING LOG OF POWER REQUIREBENTS OF SLIDER-BED

BELT CONVEYOR. . . . . . . . . . . . . . . . . . . 21-27
SAMPLE COMPUTATICNS. . . . . . . . . . . . . . . . . 28
RESULTS OF COLPUTATIONS OF POfiER REQUIHEKENTS OF

LIDER-BED BELT CONVEYOR . . . . . . . . . . . . 29-55

0)

A
SUKNEILARY M‘ID CCI‘JCLUSIC'NS o o o o o o o o o o o o o o 56

I‘LPPENDIX O O O O O O O O O O O 0 O O O O O O O O O O 4'0

CCNVL’ YCR LOAD VS.
TOP RUB3 ER BB 1LT
CONVEYOR LOAD VS.
TCP RUBJER BELT
CONVEYOR LOAD VS.
TOP RUBBLR BLLT
CONVEYOR LOAD VS.
TOP RUBBER BELT
CONVf1 LYOR LOAD VS.
TOP RUBBER ILLT
COIWV YCR LOAD VS
TCP RUBBLR ELLT
CONVEYOR LOAD VS.
TOP RUBBER BELT
(RECHECK . . .
CONVEYOR LOAD VS.
TOP RUBBL R BELT

CONVEYOR LOAD VS.

LIST OF GRAPES

HORSEPONLR REQUIRED FOR ROUGH
ON SNAISLSU STELL SURFACE . .
HORSSPONSR HSQUI~LU FOR HOUCH
CN STAIN LSS ISL SURFACE. .
HORSBPCUER REQUIRLD FCH HCUOH
CN ALLI INUN SUP FACE . . . . .
HORSSPOUSH REQUIRED FCR ROUGH
ON UNPAINTLD STEEL SURFACE. .
RCRSLPCsLR REQUIRED FOR ROUGH
ON FIR wooo SURFACE . . . . .
HCRSSPCNSS REQUIRED FOR ROUGH
ON NAPLS “GOD SURFACE . . . .
HORSLrOvLR RE HUI SD FOR ROUGH

ON ENALELED STEEL SURFACE

HO: LLPO.LR RE HUI‘L D FOR ROUGH
OI} [LLL SURFACES o o 0 o o o o

BCRSEPOULI REOUIRED FOR INIL.

BOUND CANVAS BELT ON LPLB LLED STEEL SURFACE .

CONVEYOR LOAD VS.

HORSL PO JER REQUIRED FOR INNLI—

BOUND CANVAS BELT ON STAINLESS STEEL SURFACE.

PAGE

41

42

45

44

45

46

47

4a

49

50

 

B||l|ll|ll|l|lllill|i.i

PAGE

CONVLYOR LOAD VS. NORSEFOUER REQUIRED FOR INNER-
SOUND CANVAS BELT ON ALUNINUN SURFA CE . . . . . 51
CONVEYOR LOAD VS. HOICSFO.ER REgUIRED FOR INNLI-
SOUND CANVAS BELT CN UNFAIN TED ST”? SURFACE. . 52
CONVEYOR LOAD VS. HORSEPCNE; REQUIRED FOR INNER-
SOUND CANVAS BELT ON FIR WOOD SURFACE . . . . . 55
CONVEYOR LCAD VS. HORSSIOVC REQUIRED FOR INNER-
SOUND CANVAS BELT ON RIFLE WOOD SURFACE . . . . 54
CONVEYOR LOAD VS. RORS SI CHER REQUIRED FOR INNER-
SOUND CANVAS BELT ON EIAIJLED STEEL SURFACE
(RBCIILCK) . . . . . . . . . . . . . . . . . . 55
CONVEYOR LOAD VS. HORSSFONER REQUIRED FOR INNLR-
tOUND CANVAS BELT ON STAINLLSSS "T EL SURFACE
(RECRECK) . . . . . . . . . . . . . . . . . . . 56
CONVEYOR LOAD VS. HORSEFOIER REQUIRED FOR INNER-
SOUND CANVAS BELT ON ALL SURFACES . . . . . . . 57
CONVEYOR LOAD VS. RORSSFOSER REQUIRED FOR SNOOTH
TOP RUBBER BLLT ON ENANELED STEEL SURFACE . . . 58
CONVEYOR LOAD VS. BCRSEPCLEB REQUIRED FOR SI: COT:
TOP RUBBER SILT ON STAI\L§SS S33SLS SURFACE. . . 59
COL V‘YGR LOAD VS. HCRSLPCVJR RSIUIISD FOR SI COTH
TOP {ULRII SSLT ON ALUAINUN SURFACE . . . . . . SO
CORVJYOR LOID VS. ACR331SHSR {LL} ES 363 SNOOTH

TOP RUBBJR BLL ON UN IAIV’PZD STEL'

6].

1
U)
C:
LU
'11
n, 3
(3
OH
O
O
O

CCLV‘YO{ LOAD VS.
TOP RUBBSH BELT
C(NJ' Ici CAD VS.
TOP RUBSSR ESL.
CCNVEYOP LCAD VS.
TOP RUBBER BSLT
CCU‘SYCR LOAD VS.
TOP RUBBSR LSLT

CONVIS‘LCR LLIJLD VS.

DUCK CAP-WAS ESL”

CONVEYOR LOAD VS.
DUCK CANVAS BEL
CON EYCN LOAD VS.
DUCK CEVAS ESL

CONVEYOR LOAD VS.

PAGE

RORSSFOIER NSIUIRSD FOR SLCOTR
ON FIN NOOD SURFACE . . . . . . 62
RONSEFOIER RC‘UIILJ FOL SRCCTH
ON EARLS UCOD SURFACE . .‘. . . 63

PCSSCPOXL? RS';;UIABD FOR SMOOTH

CV ALUIIN’IC SURF.”CE (ASCTS C) . 64

HORSE? OJSR MR QUIRSD FOR SMOOTH

2N EIMA SLED 8T3 SUE FACE. o o 66

RORSSFOVER HSQUILED FOR SILVER

T ON STAINLHSS \EPEEL SURFACE o o 67

HOAS‘UOJS. REQUIASD FOR SILVER

I. 01‘] JELLUJVAT .L Di TUJI': SULRLUACE O O O O O 6 8

H ROE 0J3: REIUIRSD FOR SILVER

DUCK CAH'AS BELT OM UNPAINTSD W’SSL SURF CE . . 69

CONVEYOR LOAD VS.

HO SEFONER REQUINED FOR SILVER

DUCK thm A3 .BSLT ON F13 HGC‘D SUELFACE o o o o 0 7O

CONVEYOR LOAD VS.

CR3 IROASR ISIUIISD FC R SIL ER

DUCK C‘UJAD BELT ON NZAPLEE 'fiIO-OD SURFACE. . . . . 71

CCUVJYOR LOAD VS.

HOR33POJER REQUIRED FOR SILVER

DUCK CANVAS BELT ON SNIISLED TSSL 3U TFACE

(RECHECI.) . . .

O O O O O O O O O O O O O O O O 72

P303

CANVJYCR LOAD vs. :0333p 0;33 AJQUIAJD 303 s: M
DUCK CAUVAs BJLT 03 ALULINUH ""3bACu 33 m) .
00 :V3303 LOAD vs. 303s3p0333 33’3 333 303 31L V33
DUCK AUV33 - LU ON A3L SURE A033 . . . . . . . .
cc:IV3Uc3 LOAD vs. 033390 33 33;U 3* FOR IUP333-
33333 CA3*As B3LT 03 3NAm3L ) 53333 3U3FAC3. . .
CONVEYOR LOAD vs. 30333U0333 iucUI33J 303 133:33—

13.12-41.) CIL-i [Rx-S P3134]? (LJ STAIN N333 STEEL :JTTTD'ACC o o

CCNVNYCN LCAD VS. HCASCP CHS'R NA‘UAALJ FCR 1.1333NAT JD

‘CJ

CANVAS 3LT CN ALULINUM SURFACE . . . . . . . .
CCNVEYCN LCAD VS. JCE”'3 "3 {"CUI{L3 FOR IAPREG-
NATBD CANVAS BNLT C} NPAINTE STEEL SURFACE . .
CCN JYCH LCAD VS. {CASLPCHS ASCUIRED FOR INPNZC-
HATED CANVfl - BCLT CN FIN WCCD SURFACE . . . . .
CCGI JEZOR LCAD VS. HCRSE‘C.JSR‘1JQUIAED FCR IAQflNG-
ifiATA D CAUV.lS EBLT ON MAPLE WCCD SURFACE. . . . .
CC IJEYCR LCAD VS. HORSEPCNER REQUINED FOR IiPREG-
NATED C;.IA3 BJLT CN ALL SURFACES. . . . . . . .
CONVEYCN LCAD VS. AC?”CPC 3'3 RS;UIREJ FCR CHBNIGUM
RUBBER BELT C} ENAUELSD STEEL SURFACE. . . . . .
CCNVJYC. LCAD VS. HCRSEPCIE; ACZUIKSD FCR CH3“IGUM
EKUB333 BNLT CN STAINLECS CTBJL SURFACE . . . . .
CC V‘YC fl CAD T\S. HCRSEPCJSK R'.JI.SD FC1 CLBZ GCM

ELLE CN .[TUK-I-NUIUA ST RF‘A‘SCE o o o o o o c o o o o o

75

74

76

77

78

79

80

81

82

‘P
o;

(D
sh

CONVEYOfl
RUBBSR
CCNVSYCfl
ENJBUUL
CONVEYOR
RUBBER
CONVMYOR
RUBBER
CONVEYOR
RUBBjd
CONVEYOfi
RUBBER
CCNJEYCL
hU BSR
CC”V KC d
RUBBER
CCU‘EYCR
RUBBER
CONVEYCR
% BB3

CCTV: '1 rn1
JJXUL

RUBBSR

LCAD
BELT

Tbs

.LJ'Jn
BELT
LOAD

BflLT

101311011 N1WJIK U Fc1 011.13*~
SURBACB . . . . .
vs. 1013110111 11gUI11U 101 CHE1IGUM
01 111 1030 SURFAC‘S . . . . . . . .
0,11 11 UI1EU 101 CHEgIGUd
1011190111 11 UI11D 101 C”ZLIGUV

011 ALL 1U2111013 . . . ... . . . . .
vs. 101319011:

Vrrfl .\ l-‘hI‘U‘
{' - '4
lduvl'i {nu

REQUIRED 101

ON ENJLILJ Eu) DST}: 3L SURFI‘.CEQ o o o o 0

VS. HORSEPOJER RflgUIfljD FOR

N‘OPHZNB

cm STAINLESS .TE SURFACE . . . .

LEJ
0

VS. LLOLUJJLIDONZ Ltlj QUILIJJ-‘H F021 I‘JLJC'p 913::

ON ALURIN

WU ?
in Q 11.1.13qu 0 o o o o o o o

uul‘l" J

.J

013‘] [U‘JP:1IL‘I ‘JD ST 33L SURFIJ'ACE o o o o 0

VS. H RSEPCXER REZUIRSD F3 3 NBC :ENE
CTN FI.I ‘U'V'CCD SW FULCE o o o o o o o o

173. H0 333 Carla. 31.33132) F23. IIDCPIHHJJ

UI

CM KAPLE WCCD SURFACE. . . . . . . .

VS. UCRSZPCJS;

1'15 prfir‘Dm-fiug
-1413 JTILLQD FOR Lulu.“ .‘L..JL'u‘.J

CU

[XI-1L 3U? F‘XCES O O O O O O O O O O

85

0)
.q

88

(I)
£0

90

95

'11
a"
L)
DJ

CONVBYCR LOAD V3. ”u3331CiL- 3’1UIR3D FOR AL BjLTS
ON EN MELE T33L SURWPA E . . . . . . . . . . . . 96
J3VOR LOAD VS. HCR;fi EPGn3R 33;UI&3D FOR ALL BELTS
ON SEAIN LE 33 STEGL SURE ACE. . . .'. . . . . . . . 97

COlfiVJYCR LCAD V3. HOROUIOiAR REQUIRED FOR ALL B3LTS

CCKVJflCR LCA' V3. HORSEPCJEP RGTUIE% FOR ALL EBLTS
CI‘I IL‘:P.1ILJEC:D IS'EEIQL SLrL-EFZ'LCIEO o o o o o o o o o D 0 99

CCN'EYOR LCAD V3. HORSE} C.33 REQUIiBD CR ALL JJLTS
C L‘vr F: 3 "I JCCD SURIPIEACE o o O o o 0 o o A. o o o O O O 10:)
CC CJE‘ CR 'CA‘ 3. HCCSJPOHLR RL“UI “D FCR ALL EELTS

CN mgpLa wocn STEFACB . . . . . . . . . .w. . . . 101

WWI-J

4:-

LIST OF PLATES

.SLIJER-E’EI) BESLT CCY-JVSYCR . . . . .
SLIDSR-B:3D BELT CCLIVZ‘ECEL . . . . .

,- “ 7'1 Try .4‘ rN-vrrr ; '1 yr‘ygu—‘n 1'
CYIKDLL‘J 114.51.) U \LHA‘iL‘qu'un 1.3 o o O o O

([1 .‘T‘? 3“ 'I’ “I .\ 771 f 7" 1

‘ r‘ . ‘ . 9—H} .'T T m
.L.-_J;\LJ.L L‘ .L-ML‘:‘J [JP :30!) T3123}:.biu C'DJ Sulijb' '-

p
‘

DRIVING ILLJCHAIIFI‘JI CF SLIJSR-BEJ BQZL‘.

COM” EYOR o o o o o o o o o o o o

7r .. -.-,,-_ , ,

 

m0>w>zoo ._.1_mm ommumwojm
_ Mano:

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H ‘

9"Fnun

o
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o
...

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Mr

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INTRCDUCTION

 

A conveyor is a mechanism which is used to move ob-
jects from one location to another. The belt conveyor,
which transports various items on a moving belt or band,
is simply one means of accomplishing this requirement.
These conveyors have been used in this country for the
past one hundred and fifty years. Noving belts were first
used in the processing of flour, because this type of
conveyor seemed to be the best for handling the bulky
products of the mills. With the develOpment of the large
grain elevators, the problem of materials handling be-
came more intensified and the elevator operators were in-
terested in better and more efficient designs which
would solve their problems. It follows that since the
leading eXponent of belt conveyors was the flour industry,
the early research, development and testing were under-
taken with this one type'of product in mind.

Because of the low Operating costs and the ease of
handlirg a large volume of materials, the use of belt
conveyors gradually spread to other industries. Due to
this growth, many new problems arose which demanded changes
in design of both the conveyor and its auxiliary equip-
ment. These problems consisted mainly of the proper

selection of: belts, belt tension, supporting surfaces,

 

III I ! i, I. III I! l I I II I II. «III‘ till.

9
driving mechanisms, speed of flow, unit weights, angle of
inclination, and the power required.

Much eXperimental work has been done on each of the
above problems by the various manufacturers of conveyor
equipment. These concerns have tried to incorporate new
develOpments in materials, construction, and driving
mechanisms in to their designs. However, it should be
realized that each problem is a variable factor and that
any one may change the performance of a conveyor. For
any given set of circumstances or requirements, each of
the problems must be considered in the design of the con-
veyor.

This thesis concerns itself with the determination
of the power requirements of a slider-bed belt conveyor
by varying the loads, surfaces, and the belts with the

other factors held constant.

APPARATUS

A belt conveyor consists of an endless belt, a
driving pulley, a take up pulley, a belt supporting unit,
and accessory devices for loading, unloading, and maintain—
ing proper tension in the belt. The conveyor which was
used in this investigation was a slider-bed model FVB-Bl-
16-5/4 Floor-Veyor Jr. which was manufactured by the
Rapids Standard Company of Grand Rapids, Michigan. The
bed was twenty-one feet long from center to center of
the pulleys and carried a belt sixteen inches wide. The
diameter of the drive pulley was eight inches and that
of the take up pulley was four inches. The slider-bed
was equipped with special lugs so that sheets of different
types of materials could be fastened on the bed to simu-
late various bed surfaces.

The power to drive the belt was furnished by a
cradle type dynamometer which had a one horsepower, four
hundred and forty volt, three phase, sixty cycle right
hand gear head motor revolving at fifty-nine revolutions
per minute. The thirteen tooth RC-SO sproket on the
motor drove the thirty-five tooth sprocket on the drive
pulley through an eight foot length of RC-SO coupling
link chain. The conveyor belt speed with this drive was

forty-six feet per minute.

 

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,5;

1’,fa§ J at! Ifl‘filii

 

12

In order to allow the load to run on and off the
conveyor, two ten-foot feeder sections of lZ-BR-lO wheel
conveyor complete with case stops were attached to both
ends of the conveyor. The load consisted of a number of
steel tote pans, into which enough lead weights were
placed to give a total weight of fifty pounds per pan.
The area of each pan in contact with the belt was exactly
one hundred and twenty square inches. Thus the load was
distributed in such a way that the unit load on the belt
was exactly sixty pounds per square foot.

The surfaces which were used in this test were as
follows:

1. Enameled steel

2. Unpainted hot rolled steel

3. Type 502 stainless steel, #4 brush finish

4. Fir plywood .

5. Maple plywood

6. 61 ST aluminum
With the exception of the enameled steel, which was the
actual slider bed surface, each of the other surfaces were
bed cover sheets twenty feet long and twenty inches wide.

The following belts, each cut to exactly forty-
four feet and two inches long and sixteen inches wide,
were used in the test:

1. Rough-top rubber

 

Smooth-top rubber

Neoprene rubber

Innerbound canvas

Impregnated canvas (Red Gandy 32)
Silver duck canvas top, rubber base

Chemigum

13

PROCEDURE

When the conveyor arrived it was assembled, mounted
on cast iron legs, and leveled so that the bed was hori-
zontal. Therefore the angle of inclination mentioned in
the introduction was held constant for all belts and sur-
faces. The sections of wheel conveyor were then attached
to both ends of the belt conveyor and the case stops
placed in position.

The cradle dynamometer with its motor and gear
reducing mechanism was mounted in its frame and the
coupling link chain was attached between the dynamometer
and the drive pulley. It was realized that the torque
on the dynamometer would be very high when the belt was
loaded and therefore the dynamometer frame was bolted and
clamped to the slider-bed and its supports. The tension
in the driving chain was adjusted before the dynamometer
was secured into place.

This cradle type dynamometer was designed especially
for this type of power determination test. The motor and
gear reducing mechanism were welded into the cradle up-
side down with its weight pivoting around the drive shaft.
On the Opposite end of the cradle enough weights were
welded into place so as to counterbalance the weight of

the motor. Therefore the cradle was in equilibrium and

 

?
é
a
3,
7.

 

 

FIG us is ‘3
CRADLE TYPF’YM “OMETER

 

16
the weight of the motor was automatically canceled out.
To one end of the cradle at a distance of ten inches
from the drive shaft was placed a hook and directly above
this on the frame, another hook was placed. A scale was
then hung between these hooks so that any turning moment
of the cradle in the proper direction registered on the
scale.

The principle upon which the dynamometer operated
was a very simple one. The motor was mounted longitudinally
in the cradle and by using a right-hand worm- riven gear-
head reduction unit, the output drive shaft was perpen-
dicular to the drive shaft of the motor. Through this
type of arrangement it was possible to pivot the motor
around the output drive shaft. When the motor was running
and there was no load on the drive shaft, the motor stayed
in equilibrium or in a horizontal position.- As soon as
a load was applied to the drive shaft, the normal tendency
was to slow the motor down, but since the motor was free
to pivot it produced an equal and opposite reaction to
the load. Since the motor was welded to the cradle, the
entire cradle rotated and in so doing registered the
amount of the force on the scale. From this scale read-
ing, the horsepower applied to the drive chain was deter-
mined. This was the actual horsepower required to drive

the belt and not the motor horsepower. The difference

 

 

 

FIGURE 4
TENSION TAKE UP ADJUSTMENT

ON SLI D E R-BE D'BE LT CONVEYOR

18
between these readings and the motor horsepower was the
losses in the motor and gear reducing mechanism.

Each belt was then placed on the conveyor and the
tension take up was adjusted to the point where the belts
would pull the maximum load of six hundred pounds with-
out any noticeable slippage. It was decided that the
tension to use in the test would be that which would move
the load on the belt with the highest coefficient of
friction. This tension amounted to exactly a two and one-
half inch extension on the take up screws. Throughout
the test this tension was held constant for each belt.

It was felt that by using this constant take up gap and
by having all of the belts cut to exactly the same length,
the problem of belt tension would be held fairly constant
for all of the belts. It should be realized however that
the stretch characteristics of each belt were different,
but it was felt that the slight amount of change in belt
tension due to the difference in stretch characteristics
would be a very small part of the total power required to
move the belt, eSpecially under load. This fact became
evident when a test was made in which the tension gap was
doubled and the resulting increase in power required to
drive the belt was negligible.

Before starting the actual test run each belt was

run on all of the surfaces for three or four hours. Also

m0>m>zoo ...Jmm owmnmwojm m0... 2w_z<Iom:2 oz_>_mo

 

20
the Speed of the belt was checked and found to be forty-
six feet per minute. This speed was held constant through-
out the test. Conversion tables can be used if it is
necessary to know the power requirements at different
speeds.

The test run consisted of taking scale readings at
zero, two hundred, four hundred, and six hundred pound
loads with each belt on each surface. The conveyor was
allowed to run freely and the loads were applied at in-
tervals. The scale was read only while the load was mov-
ing towards the drive pulley. It was found that during
the run the scale had a tendency to waver from one-fourth
to one-half of a pound from the average readings. This
shows that the load does not move smoothly across the sur-
face but tends to start and stop all the way across.

Also the initial effect of placing the load on the moving
belt caused a very high scale reading. Because of this,
the dynamometer had to be dampened by hand until the
scale readings were fairly constant.

After each belt was completely tested, it was re-
run over the same surfaces and rechecked until the read-
ings coincided with those taken during the first run. The
results of these rechecks were also plotted in the graph
section. During the test run the enameled surface had to

be repainted several times to assure accuracy of results.

PCULR PL UIhLL’ LJNTS CF SLIDLR-ELD BELT CCNVEYCB
TYiL 0F BLLT--RCUGH TCP RUBLl-ZR

Observer - Mr. Goldman Revolutions per Ninute of
lotor - 59
July 50, 1951 Lever Arm to Scale - 10"
LCAD in Pounds LCAD in Pounds
0 200 400 600 O 200 400 600
Enameled Steel Surface- Fir Wood Surface-
1. 4.0 19.0 55.0 46.0 1. 5.75 15.25 22.5 55.25
2. 4.25 18.5 55.25 47.0 2. 5.5 19.5 22.75 55.0
5. 43.0 21.0 36.0 46’05 5. 400 15.5 22.75 39.5
4. 4.25 20.0 54.0 47.0 4. 5.75 15.75 25.0 53.25
Stainless Steel Surface- waple Wood Surface-
1. 4.0 17.5 51.75 47.0 1. 5.75 14.0 24.75 55.25
2. 5.75 18.0 1.0 47.25 2. 4.0 14.0 24.75 55.25
5. 4.25 17.75 52.0 45.0 5. 5.75 14.25 24.75 55.5
4:. 4.0 18.0 32.25 47.0 4‘. 5075 14025 25.0 35.0
Aluminum Surface- Recheck - Enameled Steel Surfa ce—

1. 4.0 16. 5 28. 5 40.5 1. 4.0 15.0 24.5 3»4. 0
2. 4.5 17.0 29.0 40.0 2. 5.75 15.75 24.75 54.5
5. 4.25 17. 25 29.25 59.75 5. 4.25 15.25 25.5 56.5
4. 4.25 17.0 29.0 59.75 4. 4.0 15.5 25.25 56.25

mQZchmw Mbbom

Unpainted Steel Surface-
1. 5.25 14.5 25.5 54.0
2. 5.25 15.5 24.5 54.5
5. 5.5 14.0 25.0 55.0
4. 5.25 14.0 24.5 54.5

5&4

f

wiltsc 0k:

PCT: IERP tUIl—{LM LJIVTS CP‘
TYPE

Observer - Mr. Goldman

()3

July 1, 1951
LCAD in Pounds
O 200 400 600

Enameled Steel Surface-

S 1. 4.0 18.0 54.0 46.0
C 2. 5.75 18.25 54.25 46.25
A. 5. 4.25 18.25 54.0 45.5
L 4. 4.0 18.5 54.0 46.0
E
Stainless Steel Surface-

R 1. 4.5 21.0 55.5 50.0
E 2. 4.25 21.25 55.75 48.5
A 5. 4.5 21.0 56.0 49.0
D 4. 4.5 21.25 55.5 49.0
I
N Aluminum Surface-
0 1. 5. 0 18.5 51.5 44.0
S 2. 5.25 18.75 51.25 44.25

5. 5.5 18.75 51.0 44.25
i 4. 5. 25 19.0 51.0 44.5
n

Unpainted Steel Surface-
1. 4.5 14.5 25.5 52.5
2. 4.25 14.25 25.25 52.25
5. 4.75 14.25 25.25 5 .5
4. 4.5 14.25 25.5 52.75

wiltSޢ323

CF FLLT-—INNBRBCUND Ci

(‘3
{\D

SLIDER BED EELT CCKVEYCR

QJVAS

LCAD in Pounds

0 200 400 600

Fir Hood Surface-

1. 4.75 16. 26.5 57.0

2. 4.75 16.05 26.75 56.75

5. 5.0 16.5 27.0 57.25

4. 4.5 16.5 26.75 57.0
Maple Wood Surface-

1. 4.5 17.5 50.0 42.5
2. 4.75 17.75 50.25 42.75

5. 5.0 18.0 50.25 45.0

4. 4.75 ‘18.0 50.5 45.0

Reeheck-Enameled Steel Surface-

1. 4.0 15.0 21.75 51.75
2. 5.75 15.25 22.0 51.5
5. 4.25 15.5 22.5 52.0
4. 4.0 15.5 25.0 51.75

Stainless Steel Surface-

1. 4.5 18.25 50.5 41.0
2. 4.25 15.75 50.25 40.75
5. 4.75 18.75 50.75 40.75
4. 4.5 19.0 50.25 41.0

Observer - Mr.

Angus

mQZHcpmm Mbbom

tn»

0105:1053

PCULR REQUIRLJfiKTS F
TYPE CF BSLT—-S

Goldman

t l, 1951

LCAD in Pounds

0 200 400 600
Enameled Steel Surface-

10 4.5 19.0 35.0 46.75

2. 4.25 19.5 55.5 46.25

5. 4.0 19.25 52.75 46.5
4. 4.25 19.25 55.0 47.0
Stain 19 MS Steel Surface—

1. 4.0 16.0 27.0 58.0
2. 5.75 16.25 27.0 58.25
5. 4.25 16.0 27.25 57.75
4. 4.0 16.0 27.0 58.0
Aluminum Surface-

1. 4.0 14.25 25.0 54.75
2. 5.75 14.5 25.25 55.0
5. 4.25 14.75 25.25 54.5
4. 4.0 14.75 25.0 54.75
Unpainted Steel Surface-

1. 5.75 14.25 25.75 55.25
2. 5.5 15.75 25.5 55.5
4'. 3.5 15:75 23: 75 33.25

XCCTH TC?

(0
()1

SLILJER LIED BELT CCIILIN VCR

P. TEIEIL‘R

LCAD in Pounds

O 200 400 600

Fir Wood Surface-

1. 4. O 14.75 24.0 54.25
2. 5.75 14.5 24.5 54.25
5. 4.25 14.75 24. 25 54.0
4. 4.0 14. 5 24. 5 54.0
haple HOOd Surface-

1. 5.75 14.25 25.75 55.75
2. 5.5 14.0 24.0 54.5
5. 4.0 15.75 24.0 55.75
4. 5.75 14.0 25.75 55.75
Recheck—Aluminum Surface-

1. 5.5 15.25 22.75 52.75
2. 5.75 15.25 25.25 52.75
5. 5.5 15.5 25.5 52.75
4. 5.75 15.25 25.25 52.75

PCNER

'71
-.4

IHL'jimS CF SLIDEB BE ‘ ESLT CCEVEYCR
TYPE OF BELT-~SILVER DUCK CA WAS TOP, FUEB SR BASE
Observer - Mr. Goldman

August 5, 1951

LCAD in Pounds LCAD in Pounds
0 200 400 600 0 200 400 600
Enameled Steel Surfs ce- Fir Wood Surface-
5 1. 5.0 26.75 40. 25 56.0 1. 5. 75 17.5 50.5 42.5
C 2. 4.75 27.75 40.0 56.25 2. 6.0 17.75 30.25 42.25
A 5. 5.25 27.5 40.5 55.5 5. 5.5 17.75 50.25 42.25
L 4. 5.5 27.5 40.25 56.0 4. 5. 75 15.0 50.25 42.5
E
Stainless Steel Surface- Maple 'hood Surface-
R 1. 5. 50 19.5 51.5 45.25 1. 5.5 17.75 51.75 44.0
E 2. 5.25 19. 25 51.75 45.5 2. 5.25 18.0 51.5 45.75
A 5. 5.75 19. 25 52.0 44.25 5. 5.75 18. 25 51.5 45.75
D 4. 5.5 19. 5 51.75 45.75 4. 5.5 15. 25 51.5 44.0
I
N Aluminum Surface- Recheck-Enameled Steel Surface-
G 1. 5.0 15.75 51.5 44.0 1. 5.0 21.5 59.75 55.5
S 2. 5.25 5.75 51.25 44.25 2. 4.75 22.0 59.5 56. O
5. 4.75 19.25 51.75 44.25 5. 5.5 22.I 59.5 56.25
i 4. 5.25 19.0 51.75 44.0 4. 5.25 22.0 59.75 56.0
n
Unpainte‘ Steel Surface- Aluminum Surface-

0

.25 17.25 28.0 40.5 1. 5.0 16.75 27.5 40.0
.5 17.5 28.5 40.5 2. 4.75 16.25 28.0 40.25
.75 17.5 28.75 40.75 5. 4.5 16.5 27.75 40.75
.5 17.75 28.75 40.75 4. 4.75 16.5 28.0 40.5

mtltscfiowj
5’

PCRLR REQUIREMENTS CF SLIDER BED BELT CONVEYOR

TYPE

Cbserver

CF BELT-~IKPREGNATED CANVAS (RAD GAEDY 32)

- Mr.

Goldman

August 6, 1951

LCAD in Pounds

0 200 400 600
Enameled Steel S rface-
S 1. 8.75 57.0 60.0 85.25
C 2. 9.0 56.5 59.25 85.0
A 5. 8.75 56.25 59.5 85.25
L 4. 9.0 58.5 59.5 85.25
E
Stainless Steel Surface-
2 1. 7.5 22.75 55.75 45.0
E 2. 7.25 22.5 55.75 44.75
A 5. 7.75 22.5 55.5 44.5
D 4. 7.5 21.5 55.25 44.75
I
N Aluminum Surface-
G l. 8.0 20.75 51.5 44.25
S 2. 7.75 20.5 51.75 44.5
5. 7.75 20.5 52.0 44.0
i 4. 7.5 20.75 51.75 44.25
n
Unpainted Steel Surface-
p 1. 8.0 20.5 50.0 40.5
o 2. 7.75 19.75 29.75 41.0
u 5. 7.5 20.25 50.25 41.5
n 4. 8.0 20.0 50.0 41.0
d
s

.LQAQ in Pounds

0 200 400

Fir Wood Surface-

1. 7.5 20.5 51.0
2. 7.75 19.75 51.5
5. 7.25 20.25 51.0
4. 7.5 19.75 51.5
Kaple Wood Surface-

1. 7.25 20.75 52.0
2. 7.5 20.25 51.25
5. 7.5 23.5 51.25
4. 7.75 20.75 52.0

Recheck C. K.-

600

42.5
42.0
41.75
41.75

42.5
42.75
2.5

45.0

POWER REgUIREkBNTS CF SLIDER BED BELT CONVEYOR
TYPE CF BELT-—CHENIGUM
Cbserver - Mr. Goldman

August 7, 1951

LOAD in Pounds LCAD in Pounds
0 200 400 600 0 200 400 600
Enameled Steel Surface- Fir Wood Surface-
s 1. 5.0 20.0 55.75 47.0 1. 5.0 15.25 25.75 55.5
C 2. 5.25 20.25 54.0 47.25 2. 5.25 15.5 25. 55.0
A 5. 4.75 19.75 54.25 47.0 5. 5.5 15.5 25.25 55.25
L 4. 5.0 19.75 54.25 46.75 4. 5.25 15.25 25.0 54.75
E
Stainless Steel Surface- Maple Wood Surface-

R 1. 4.75 16.5 27.75 59.75 1. 5.0 15.25 24.75 54.5
E 2. 4.5 16.25 27.5 59.75 2. 5.25 14.75 25.0 54.75
A 5. 5.0 16.75 27.5 57.75 5. 4.75 15.0 25.0 54.75
D 4. 4.75 16.5 27.75 57.75 4. 5.0 15.25 24.75 55.0
I
N Aluminum Surface- Recheck C. K.-
G l. 4.75 15.75 25.0 56.25
S 2. 5.0 15.0 25.25 55.25

5. 5.24 15.25 25.5 56.0
i 4. 5.0 15.5 25.5 56.25
n

Unpainted Steel Surface-

. 4.75 15.0 24.75 54.75
. 5.0 15.0 25.0 54.5
. 5.0 14.75 24.75 55.0

. 4.75 15.0 25.0 54.75

msztsc10ws
pawl-4*"

Cbserver - 1r

August 9,

COOZHU3='t’JID WITHr’OUJ

5+4

mQUCO'U

PCZ

333 RE

;UIBENDNTS CFS

TYPE CF BELT-~11 ‘CP 31L} E

. Goldman

1951

LCéQ in Pounds

0 200 400
Enameled Steel Surface-
1. 4.25 22.5 59.5
2. 4.0 2.75 40. 0
5. 4.5 22.5 40. 75
4. 4.25 22.5 40. 25

Stainless
1. 4.0
2. 5.75
5. 4.0
4. 5.75

600

(f! 0'1

(.OQUJQ
o o o o
O'KTYU’JI

01 (I! (I1 ()1

Steel Surface-

15. 75 27.0 58.0

Aluminum Surface-

1. 4.25
2. 4.0
5. 4.5
4.

5.75 14.25

15. 75 26. 75
16.0 26.75
16.0 27.0
14.25 24.0
15.75 25.75
14.0 25.75

25.75

57. 75

4‘ T‘\
55.0

57.75

55.75

54.0
54.0
55.75

Unpainted Steel Surface-

1. 4.0 14.25 26.25
2. 5.75 14.5 26.5
5. 5.75 14.75 26.5
4. 4.0 15.0 26.25

LIDIR 31D BLLT CChVLYCR

IC D in Pounds

0 200 400

Fir Wood Surface-

1. 4.25 15.0 25.0

2. 4.0 14.75 25.25

5. 4.5 14.75 24.25
4. 4.25 15.0 24.75
1ap1e flood Surfaoe-

l. 4.2514.75 25.25

2. 4.5 14.5 25.25
5. 4.0 14.75 25.0
4. 4.25 14.75 25.25
Recheck C. K.-

27

600

OOQO
0'1

ongfioa
(nohkcn

(fl

ouwcnoa
01010101
0 0
53500153
(DUI

SJJCPLE CC 1 } UTATICI’Q

 

1. Average Scale -- (Rough tOp rubber belt on enameled
steel surface)

Av. Scale = Read: n9 1 - 2 - Reading 5 - Read ing_4

1
er f30f Readings

:1 m
co

= 19 - 18.5 — 21 - 20 / 4

19.6 Pounds

 

2. Horsepower to Chain

H.P. = 2 T N /ss,000

where N — Revolutions per minute of motor

59 ROPOIV“.
T = Torque on motor in foot pounds

= (Average Scale)(Lever Arm to scale)

= (19.6)§102
12

= 16.33 FtoLbo

H.P. = 2 (isigsggse)
35,000

0.5155IL

 

29

resume CF CCL‘PU’I‘ATISI‘JS CF PC'E 2113;013:515:sz CF 03110133

BED BELT CCRVEYCR CH RCUGH TCP RUBBLR BELT

Observer - 1r. Goldman Revolutions per Minute of
KOtOP - 59
July 50, 1951 Lever Arm to Scale - 10"

LCéQ in Pounds

0 200 400 600

Enameled Steel Surface-

Av. Scale 4.15 19.6 55.06 46.6

Horsepower .3587 .1855 .5282 .4562 .
Stainless Steel Surface-

Av. Scale 4.0 17.81 51.75 46.44

Horsepower _ .0575 .1667 .2972 .4547
Aluminum Surface-

Av. Scale 4.25 16.94 28.94 40.0

Horsepower .0598 .1586 .2709 .5745
Unpainted Steel Surface-

Av. Scale 5.51 14.0 24.4 54.5

Horsepower .0510 .1511 .2284 .5250
Fir Wood Surface-

Av. Scale 5.75 15.5 22.5 55.0

Porsepower .0551 .1264 .2106 .5090
Maple Wood Surface-

Av. Scale 4.0 15.57 20.0 55.51

Horsepower .0574 . 251 .2540 .5506
Recheck

Enameled Steel Surface-
Av. Scale 4.0 15.57 25.0 55.51
Horsepower .0574 .1251 .2540 .5506

 

 

 

' GL1: JET—{‘2' ' 'c

\-

 

fr!
ms...

RESULTS CF CCMPUTATIONS CF PCEER HEQJIRSNBNTS

BED BELT CONVEYCR CN INNER BCUND CANVAS

Observer - Hr. Goldman

Av. Scale
Horsepower

Stainless Steel Surface-

Av. Scale
Horsepower

Aluminum Surface-

AV. Scale
Horsepower

Unpainted Steel Surface-

Av. Scale
Horsepower

Fir Wood Surface-

Av. Scale
Horsepower

Maple Wood Surface-

Av. Scale
Horsepower

Recheck
Enameled Steel Surface

Av. Scale
Horsepower

Stainless Steel Surface-

Av. Scale
Horsepower

BELT

CF SLIDER

July 31, 1951

LOAD in Pounds

0

4.0
.0575

4.44
.0416

4.5

.04215

200

18.25
.1709

21.15
.1979

18.75
.1755

14.51
.1540

16.44
.1559

17.81
.1667

15.51
.1246

18.69
.1750

400

54.06
.5159

55.69
.5541

25.26
.2150

26.75
..504

50.25
.2852

° 73")
0303
(OF-4

(3) ()4

50.44
.2850

600

52.25
.5020

57.0
.5464

42.81
.4008

40.9

.5829

RESULTS OF CCEPUTATICIJS 0F PCVER RugUITQRJL 8 CF SLIDER

BED BHLT CONVEYOR CN

Observer - Mr. Goldman

Enameled Steel Surface-

Av. Scale
Horsepower

Stainless Steel Surface-

Av. Scale
{orsepower

Aluminum Surface-

Av. Scale
Horsepower

Unpainted Steel Surface-

Av. Scale
Horsepower

Fir Wood Surface-

Av. Scale
Horsepower

Maple Wood Surface-

Av. Scale
Horsepower

Recheck
Aluminum Surface-

Av. Scale
Horsepower

SLZCCTH TCP

4.25
.0598

4.0
.0575

.0575

5.75
.0551

5.65
.0540

T -1
2081;.

CAD in Pounds

200

19.25
.1802

16.06
.1505

14.56
.1565

15.94
.1505

14.65
.1570

BSLT

400

55.06
.5094

27.06
.2555

25.13
.2555

25.19
.2171

August 1, 1951

600

46.65
.4565

ocx

Odco

OH
(HO

54.75
.5255

55.58
.5215

54.51
.5195

55.94
.5177

52.69
.5060

01

RESULTS OF COSPUTATIGHS

CF 130.4233 HEJQUIHHILEI‘JTS

BED BELT CCN‘EYCR CN SILVER DUCK CANVAS BELT

Observer - Mr. Goldman

LCAD in Pounds

August 5,

0 200 400

Enameled Steel Surface-

Av. Scale 5.12 27.57 40.25

Horsepower .0479 .2562 .5768
Stainless Steel Surface-

Av. Scale 5.5 19.58 51.75

Horsepower .0515 .1814 .2972
Aluminum Surface-

Av. Scale 5.06 18.94 51.56

Horsepower .0474 .1775 .2955
Unpainted Steel Surface-

Av. Scale 5.5 17.5 28.5

Horsepower .0515 .1658 .2668
Fir Wood Surface-

Av. Scale 5.75 17.75 50.51

Horsepower .0558 .1662 .2857
Maple Wood Surface-

Av. Scale 5.5 18.06 51.56

Horsepower .0515 .1691 .2955
Recheck

Enameled Steel Surface-
Horsepower .0479 .2160 .5710
Aluninum Surface-
Av. Scale 4.75 16.5 27.81
Horsepower .0445 .1545 .2605

CF SLIDBR

1951

600

° 01
0101
one
~14>

{‘00

40.58
.5780

55

*SULTS CF CChPUTATIONS CF POKER REQUIHEAENTS CF SLIDER
BSD BELT COEVEYGR CH ILPHHGNATED CANVAS (BSD GANDY 52) EHLT
Cbserver - Hr. Goldman August 6, 1951

LOAD in Pounds

0 200 400 600

Enameled Steel Surface-

Av. Scale 8.88 56.56 59.65 85.06

Horsepower .0851 .5425 .5582 .7776
Stainless Steel Surface-

Av. Scale 7.5 22.51 55.56 44.75

Horsepower .0702 . 089 .5142 .4189
Aluminum Surface-

Horsepower .0758 .1951 .2972 .4142
Unpainted Steel Surface-

AV. scale 7081 (001:5 50.0 4100

Horsepower .0751 .188 .2808 .5858
Fir Wood Surface-

Av. Scale 7.5 20.06 51.25 42.0

Horsepower .0702 .1878 .2925 '.5952
Maple Wood Surface-

Av. Scale 7.5 20.56 51.65 42.69

Horsepower .0702 .1925 .2961 .5996

Recheck -— O. K.

54

RESULTS CF COHPUTATICHS CF POKER HEQUIHSHEHTS CF SLIDBR
BSD BELT CCHVSYCH CH HEHIS'H BELT
Cbserver - Hr. Goldman August 7, 1951

LCAD in Pounds

*-

0 200 400 600

Enameled Steel Surface-

Av. Scale 5.0 19.94 54.06 47.0

Horsepower .0468 .1867 .5189 .4400
Stainless Steel Surface-

Av. Scale 4.75 16.5 27.65 59.75

Horsepower .0445 .1545 .2587 .5721
Aluminum Surface-

Av. Scale 5.0 15.58 25.51 55.94

Horsepower .0468 .1440 .2569 .5565
Unpainted Steel Surface-

Av. Scale 4.88 14.94 24.88 54.75

Horsepower .0457 .1599 .2529 .5255
Fir Wood Surface-

Av. Scale 5.25 15.58 25.58 55.19

Horsepower .0492 .1440 .2576 .5294
Maple WOOd Surface-

Av. Scale 5.0 15.06 24.88 54.75

Horsepower .0468 .1411 .2529 .5255

Recheck -- 0. K)

()3

RESULTS CF CCEPUTATICNS CF POLAR REQUIHEALNTS CF SLIDCR
LSD BSLT CCHVEYCR CH HJCPRLHE BHLT
Cbserver - Hr. Goldman August 9, 1951

LCAD in Pounds

0 200 400 600

Enameled Steel Surface-

Av. Scale 4.25 22.56 43.15 57.88

Horsepower .0598 .2119 .5757 .5418
Stainless Steel Surface-

AVO scale 3.88 15.38 26.33 37088

Horsepower .0565 .1487 .2516 .5546
Aluminum Surface-

Av. Scale 4.15 14.06 25.81 55.88

Horsepower .0587 .1516 .2229 .5172
Unpainted Steel Surface-

Av. Scale 5.88 14.65 26.58 56.88

Horsepower .0565 .1570 .2470 .5455
Fir Wood Surface-

Av. Scale 4.2 14.88 24.94 54.94

Horsepower .0598 .1595 .2555 .5271
Maple Wood Surface-

Av. Scale 4.25 14.69 25.19 55.44

Horsepower .0598 .1575 .2558 .5518

Recheck -— O. H.

3111::st AHD pcwcmsmw

 

It is difficult to make any difirite statements as
to the power required to run the various belts because
each belt had its own characteristics which made it act
differently on the different surfaces. However certain
generalizations can be made regarding the belts which re-
quired the least power, as well as the comparative quali-

ties of the surfaces.

Running_surfaces. With the exception of the inner-
bound canvas belt on the stainless steel surface, all of
the belts required more power on the enameled steel sur-
face. The stainless steel and aluminum surfaces were
very close together and required just a little less power
than the enameled steel surface. The running surfaces
requiring the least power seemed to be the maple wood,
the fir wood, and the unpainted hot rolled steel.

During the testing of the first three belts, the
enameled surface was used as the initial surface tested.
It was found that after all of the surfaces had been
tested and a recheck make of the enamel, the power re-
quired to drive the belt was quite a bit lower than the
original readings. The first eXplanation of this was

that the tension in the belt had changed. However, after

57
reversing the order of the surfaces it was proven that
this marked difference could only be due to the wearing
away of the enamel during the run. As the enamel wore
thin, the unpainted metal of the slider-bed became ex-
posed. The belts running on this unpainted steel naturally
gave a lower power reading. The curves of the rechecks
were included mainly to show that after a short period of
running, the enamel disappears and that it is of little

value to paint the slider-bed originally.

Egltg. The belts which required the most power to
run over all of the surfaces were the impreganted canvas,
the innerbound canvas, and the silver duck canvas. The
neoprene, chemigum, smooth-top rubber, and rough-top
rubber belts required less power than did the canvas belts.
However, each of these belts performed differently on the
different surfaces and no definite order of least to most

power could be established.

Power. These generalizations were made on the
basis of the conveyor load vs. horsepower required curves
found in the appendix of this thesis. These curves Show
that there was a straight line relationship between the
power required to drive the conveyor belts and the load
which the conveyor carried. It was also noted that none

of these curves started from the origin at the zero load.

58
Thus it is evident that the power required to drive the
conveyor was broken down into two components: first was
the power required to drive the belt when there was no
load on it; and the second was the power required to drive
the load from one location to another.

The power required to drive the belt at zero load
could be further broken down into the power required to
overcome the friction of the pulleys, to pull the unloaded
belt across the slider-bed and to make the belt bend to
conform to the design of the conveyor. When the belt we
loaded, each of these factors was increased and to them
was added the increased frictional drag due to the weight
of the load, plus the power required to bring the load
from its initial contact up to the Speed of the moving
belt. This last power requirement accounted for the in-
crease in torque on the dynamometer when the load was

added to the belt.

General. In conclusion, it should be remembered
that this test was conducted using one specific make of
conveyor with definite brands of belts and under the con-
ditions present in the laboratory. The results of such
a test may or may not coincide with results obtained under
any other given set of conditions. It should be empha-

sized at this time that all of the variable factors

mentioned in this thesis play a Very important part in
the performance of a conveyor. The figures obtained in
this study are the results of an attempt to cancel out

as many of the variables as possible and varying remain-
ing factors under controlled conditions, in order to make

a comparison of a number of belts and slider-beds.

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