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7/23/2019 DESIGNING A BUCKET MECHANISM OF A BACKHOE LOADER
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DESIGNING A BUCKET MECHANISM OF
A BACKHOE LOADER
A PROJECT REPORT
Submitted by
MECHANICAL ENGINEERING DEPARTMENT
HACETTEPE UNIVERSITY
MAY2015
Alperen KALECantrk SANANFetihhan GRANM.Emre PAKSOY
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i
ABSTRACT
This is the final and third report of the stationary backhoe design project. This project is
combination of both design of systems and selection of systems. Design of systems includes
all the necessary calculations of a mechanical system, such as; static, dynamic, stress, fatigue
analysis so on and so forth. All of the calculations carried out with the help of Statics,
Dynamics, Strength of Materials, Design of Machine Elements and in particular Vehicle
Component Design courses. Selection of systems depends on online part selection tools of
firms and inspection of equivalent systems. These two main design processes combined
together to constitute the proper stationary backhoe for required work conditions with the
comprehensive effort of group members.
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ii
Table of Contents
I. Introduction ......................................................................................................................... 3
A. Problem Statement .......................................................................................................... 3
B. Motivation ....................................................................................................................... 3
C. Challenges and Goals ...................................................................................................... 3
D. Work Plan ........................................................................................................................ 4
II. LITERATURE SURVEY AND PRELIMINARY DESIGN ............................................. 5
A. Literature Survey ............................................................................................................. 5
B. Pugh Chart ....................................................................................................................... 6
C. Design Approach ............................................................................................................. 6D. Schematic Drawing ......................................................................................................... 7
III. DESIGN AND SIMULATION ....................................................................................... 9
A.Static Analysis .................................................................................................................. 10
B. Stress Analysis ................................................................................................................. 14
C. Dynamic Analysis ............................................................................................................ 21
D. Fatigue Analysis .............................................................................................................. 23
E. Machine Components Design ....................................................................................... 27
F. Simulation Results ............................................................................................................ 40
Mesh Information - Details ................................................................................................... 48
Mesh Control Information: ................................................................................................... 49
G. Cost Analysis ................................................................................................................... 55
H. 3D Drawings .................................................................................................................... 56
IV. CONCLUSION AND DISCUSSION ........................................................................... 62
A. Summary and Discussion of the Results ......................................................................... 62
B. Future Works ................................................................................................................... 62V. REFERENCES ................................................................................................................. 63
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iii
List of Tables
Table 1 - Task timetable ............................................................................................................. 4
Table 2 - Pugh Chart .................................................................................................................. 6
Table 3 - Cost Table ................................................................................................................. 55
List of Figures
Figure 1 - Free body diagram of the Bucket .............................................................................. 7
Figure 2 - Free body diagram of the Stick ................................................................................. 7
Figure 3 - Free body diagram of the Boom ................................................................................ 8
Figure 4 - Critical points of Factor of Safety ........................................................................... 53
Figure 5 - Critical points of Factor of Safety ........................................................................... 53
Figure 6 - Fatigue analysis and total life .................................................................................. 54Figure 7 - Static Factor of Safety Critical points ..................................................................... 54
Figure 8 - Side view technical drawing of closed position ..................................................... 56
Figure 9 - Top view technical drawing of closed position ....................................................... 56
Figure 10 - Front and back view technical drawing ................................................................ 57
Figure 11 - Top view technical drawing of opened position .................................................... 58
Figure 12 - Isometric view technical drawing of opened position ........................................... 58
Figure 13 - Isometric view technical drawing of closed position ........................................... 59
Figure 14 - CAD view 1 ........................................................................................................... 60
Figure 15 - CAD view 2 ........................................................................................................... 60
Figure 16 - CAD view 3 ........................................................................................................... 61
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Hacettepe University Department of Mechanical Engineering 3
I. Introduction
A.Problem Statement
Stationary backhoes are widely used in almost every mass production sector to carry
products from one place to another effectively. One can examine and find out that these
backhoes are mostly over safe and oversize for most applications. This projects aim is to
design a stationary backhoe which is safe enough, less cost and capable of performing the
duty without any restrictions.
B.
Motivation
The basic reason behind this project is to prevent large amount of energy losses which are
produced while the production of these oversize backhoes and during the operation of these
backhoes. Realizing that the most urgent problems of the World are the energy shortage and
the climate change which is directly affected by the energy production methods, even a small
amount of energy gain is very important.
C.
Challenges and Goals
Design of this project includes two main parts. The first one is designing a stationary
backhoe with the ability of lifting 500 kg load and the second one is designing necessary
components to run this stationary backhoe. Optimization of the geometry of the backhoe to
reach reasonable factor of safeties and reasonable sizes is the main difficulty, lots of iterations
needed. Another challenging is designation of driver components, there are billions of options
and most effective ones have to be chosen.
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D.Work Plan
1. Preparing first report and completing literature survey: 1st and 2nd weeks.
2. Completing hand calculations: 3
rd
and 4
th
week.3. Machine components design (Shafts and Bearings): 5th week.
4. Schematic drawings: 6th week.
5. Setting Second Report: 7th week.
6. CAD drawings and FEM analysis: 8th week.
7. Machine components design: 9th week.
8. Technical drawings- Parts list cost analysis: 10th week.
9. Setting final report- Preparing presentation: 11th
week.
Table 1 - Task timetable
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II. LITERATURE SURVEY AND PRELIMINARY DESIGN
A.
Literature Survey
At the beginning of this project the textbook has been exhaustively examined. A general
idea about for each component has gained by group members. Afterwards applications of
these component has been researched and compared with similar ones. These researches are
made via internet or speaking with the firms at phone.
Some of these sources;
1.
How Caterpillar Backhoe Loaders Work
http://science.howstuffworks.com/transport/engines-equipment/backhoe-loader1.htm
2.New Backhoe Loaders CAT 422F
http://www.cat.com/en_ZA/products/new/equipment/backhoeloaders/sideshift/18346265.html
3.CAT Backhoe Loader Brochure
http://s7d2.scene7.com/is/content/Caterpillar/C768535
4.Backhoe Loader
http://en.wikipedia.org/wiki/Backhoe_loader
5.Backhoe
http://opensourceecology.org/wiki/Backhoe
6. SKF Rolling Bearings
http://www.skf.com/binary/138-121486/SKF-rolling-bearings-catalogue.pdf
7. SKF Extra Power Belts
http://www.skf.com/binary/92-118145/Xtra-Power-belts---10552_3-EN.pdf
8. SKF Belt Drive Design Calculations Tool
http://www.skf.com/group/knowledge-centre/engineering-tools/belt-drive-design-
calcalutions-tool.html
9. Gamak 3 Phase Asynchronous Electric Motors
http://www.gamak.com/images/urun-pdf/standart_motorlar.pdf
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B.Pugh Chart
Table 2 - Pugh Chart
C.
Design Approach
The basic design approach of this project rely on the motivation of this project. The
sufficient and necessary design method for less energy loss is downsizing. Cost of the project
is another issue that has to be minimized, avoiding from over safe parts will result less energy
loss and less cost. The reliability of this stationary backhoe must be satisfactory so an
optimization is essential between downsizing approach and safety. Such an optimization has
been considered through whole project.
0
0
0
0
Reference Design 1 Reference Design 2 Our Design
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D.Schematic Drawing
1. Free Body Diagram of the Bucket
Figure 1 - Free body diagram of the Bucket
2. Free Body Diagram of the Stick
Figure 2 - Free body diagram of the Stick
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3. Free Body Diagram of the Boom
Figure 3 - Free body diagram of the Boom
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III. DESIGN AND SIMULATION
In this part static analysis, dynamic analysis have been made by hand calculations. Also
stress and fatigue analysis have been completed by hand calculations. Assumptions needed to
make analysis are decided after an intense literature survey. A rough sketch of boom, stick
and bucket is completed.
Decision and design of back parts of the system such as electirc motor, shafts and
bearings are made according to necessary power to carry a 500 kg load. The static analysis for
bucket is made in this part.
To begin with, the mass of bucket is assumed as 200 kg and a factor of safety is
considered as 4. The factor of safety is used at the begining of static analysis instead of using
at the end of the stress values consideration.
The desired maximum load is 500 kg. The calculations are made due to this approach,
and therefore the maximum load is taken as 2000 kg. According to this value, the piston
forces and the reactions forces are determined. The formulas and calculations are shown
below.
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A. Statc Analyss
1. Bucket:
Bucket mass mbucket 200 kgkgkgkg
Mass carred by bucket mload 500 kgkgkgkg
Bucket length Lbucket 130 cmcmcmcm
Bucket to pston rod angle bucket 70
Bucket max. closed angle b.closed 30
Bucket to pston dstance db.p 45 cmcmcmcm
Bucket jont dstance db.j 20 cmcmcmcm
Stck to ground angle s.g 0
Factor of Safety FoSbucket 4
Pston 1 Force:
FP1
+mload FoSbucket mbucket gggg Lbucket
2 cos b.closed
db.p sin bucket db.j
=FP1 54.494 kNkNkNkN
Force balance for ont 1 at y axs:
R1y +mload FoSbucket mbucket gggg
=R1y 21.575 kNkNkNkN
Force balance for ont 1 at x axs:
R1x FP1
=R1x 54.494 kNkNkNkN
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2.Stck:
The mass of stck, lengths and angles are assumed and gven below. Due to these
values, the reactons and pston forces are determned.
Stck Length Lstick 2.6 mmmm
Stck Mass mstick 200 kgkgkgkg
Dstance between stck and pston 1 ds.p1 25 cmcmcmcm
Pston to ground angle p2.g 30
Stck arm !ont to !ont " dstance ds.j2.j3 60 cmcmcmcm
Pston #orce$
FP2
+Lstick
2 mstick gggg R1y Lstick FP1 ds.p1
sin p2.g ds.j2.j3
=FP2 150.067 kNkNkNkN
#orce balance for %ont at & a&s$
R2x +R1x FP2 cos p2.g FP1
=R2x 129.962 kNkNkNkN
#orce balance for %ont at ' a&s$
R2y ++R1y mstick gggg FP2 sin p2.g
=R2y 98.57 kNkNkNkN
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3.Boom:
The mass of boom, shape, lengths and angles are assumed and gven below. Due to
these values, the reactons and pston forces are determned.
Boom length 1 Lb1 1.5 mmmm
Boom length 2 Lb2 1.7 mmmm
Mass of boom mboom 350 kgkgkgkg
Pston 3 to groung angle p3.g 60
Pston 2 perpendcular dstance to ont 3 dp2.j3 +Lb2 sin p3.g ds.j2.j3 sin p2.g
=dp2.j3 1.772 mmmm
!ont 2 to ont 3 hor"ontal dstance dj2.j3x +Lb2 cos p3.g Lb1 cos p2.g
=dj2.j3x 2.149 mmmm
!ont 2 to ont 3 vertcal dstance dj2.j3y +Lb2 sin p3.g Lb1 sin p2.g
=dj2.j3y 2.222 mmmm
#o$ of Boom to ont 3
perpendcular dstance
dcogb.j3 Lb2 cos p3.g
=dcogb.j3 0.85 mmmm
Pston 3 to ont 3
perpendcular dstance
dp3.j3 ds.j2.j3 sin p2.g
=dp3.j3 0.3 mmmm
Moment balance for boom%
Mj3 0
FP3 ++mboom gggg dcogb.j3 R2y dj2.j3x R2x dj2.j3y FP2 dp2.j3
dp3.j3
=FP3 639.652 kNkNkNkN
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&orce balance for !ont 3 at ' a(s
R3y ++R2y mboom gggg FP3 sin p3.g FP2 sin p2.g
=R3y 580.923 kNkNkNkN
&orce balance for !ont 3 at ( a(s
R3x +R2x FP3 cos p3.g FP2 cos p2.g
=R3x 319.826 kNkNkNkN
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B. Stress Analyss
1.Bucket:
Wdth of bucket Wbucket 70 cmcmcmcm
Abucket Lbucket Wbucket 1.5 =Abucket 1.365 mmmm2
bucket mload FoSbucket
Abucketgggg =bucket 14.369 kPakPakPakPa
Snce the total stress s too small the stress analyss s not necessary. The bucket
wll not fal.
2. Stck:
The lengths (wdth, heght and wall thckness) of stck and ts profle are assumed and
gven below. Due to these values, the stress analyss s done and the results are shown.
Wdth of stck wstick 200 mmmmmmmm
eght of stck hstick 150 mmmmmmmm
Wall thckness of stck sstick 10 mmmmmmmm
!ont dameter Djoint 50 mmmmmmmm
Stress concentraton factor Kt.stick 2
"rea of stck#
Astick hstick wstick hstick 2 sstick wstick 2 sstick 2 Djoint sstick
=Astick 0.006 mmmm2
"rea moment of nerta of stck#
Istick hstick
3wstick wstick 2 sstick hstick 2 sstick
3
12
=Istick 2.33 105
mmmm4
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Axal Stresses:
a.stick +FP1 R1x R2x
Astick
=a.stick 23.208 MPaMPaMPaMPa
Bendng Stresses:
b.stick +
mstick gggg Lstick
2
hstick
2
Istick
R1y Lstick hstick
2
Istick
FP1 ds.p1 hstick
2
Istick
=b.stick 144.946 MPaMPaMPaMPa
Total Stresses:
tot.stick +a.stick b.stick Kt.stick
=tot.stick 243.477 MPaMPaMPaMPa
3. Boom:
The lengths (wdth, heght and wall thckness) of stck and ts profle are assumed and
gven below !ue to these values, the stress anal"ss s done and the results are shown
#dth of Boom wboom 350 mmmmmmmm
$eght of Boom hboom 300 mmmmmmmm
#all thckness of Boom sboom 30 mmmmmmmm
Stress concentraton factor Kt.boom 1.5
Area of Boom
Aboom hboom wboom hboom 2 sboom wboom 2 sboom
=Aboom 0.035 mmmm2
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Area moment of nerta of boom:
Iboom hboom
3wboom wboom 2 sboom hboom 2 sboom
3
12
=Iboom 4.534 104
mmmm4
Axal Stresses:
a.boom +FP2 R2x FP3 cos p3.g
Aboom
cos p3.g
=a.boom 4.801 MPaMPaMPaMPa
Bendng Stresses:
b.boom Kt.boom hboom
2
+++
FP3 dp3.j3Iboom
FP2 dp2.j3
Iboom
mboom gggg dcogb.j3Iboom
R2y dj2.j3x
Iboom
=b.boom 143.314 MPaMPaMPaMPa
4. Jont between bucket and stck
Materal IS2062
Stress lmt for bucket pn
jont
max.bpj 205 MPaMPaMPaMPa
Allowable sear stress bpj 42 MPaMPaMPaMPa
Maxmum bearng pressure Pbpj 40 MPaMPaMPaMPa
!ameter of bucket pn jont dbpj 50 mmmmmmmm
"engt of bucket pn jont Lbpj 300 mmmmmmmm
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Effectve length of pn jont Lbpje 225 mmmmmmmm
Ymax.bpj dbpj2
=Ymax.bpj 25 mmmmmmmm
R1xy+R1y
2R1x
2=R1xy 58.61 kNkNkNkN
Bearng Force of bucket pn
jontPbpj1
R1xy
dbpj Lbpje
=Pbpj1 5.21 MPaMPaMPaMPa
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Maxmum bendng stress
developped n the bucket pnbpj
Mbpj Ymax.bpjIbpj
=bpj 134.324 MPaMPaMPaMPa
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Shear force actng on bucket spj1 R2xy
Aspj
=spj1 18.461 MPaMPaMPaMPa
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Effectve length of pn jont Lbopje 285 mmmmmmmm
Ymax.bopj dbopj
2 =Ymax.bopj 60 mmmmmmmm
R3xy+R3y
2R3x
2=R3xy 663.144 kNkNkNkN
Bearng Force of bucket pn
jont
Pbopj1 R3xy
dbopj Lbopje
=Pbopj1 19.39 MPaMPaMPaMPa
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Maxmum bendng stress
developped n the bucket pn
bopjbopj max.bopj
Ibopj=bopj 139.258 MPaMPaMPaMPa
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The angular velocty gven below s the angular velocty of the stck at z axs.
stick
4
radradradrad
ssss
Accordng to ths angular velocty, dynamc force analyss has been evaluated:
Fsmax.x +mcombined stick2
Lstick R1x
=Fsmax.x 58.183 kNkNkNkN
Fsmin.x R1x
=Fsmin.x 54.494 kNkNkNkN
Boom Analyss
Same approach whc has been used for stck dynamc analyss s also used for
boom analyss.
mcombined.b +++mstick mbucket 4 mload mboom
2
=mcombined.b 2575 kgkgkgkg
The acceleraton gven below s angular acceleraton of the boom on z axs.
boom.z
8
radradradrad
ssss2
Accordng to ths acceleraton, dynamc force analyss has been evaluated:
Lboom 3.09 mmmm
Fbmax.y +mcombined.b boom.z Lboom sin 25 R3y
=Fbmax.y 580.51 kNkNkNkN
Fbmin.y mcombined.b boom.z Lboom sin 25 R3y
=Fbmin.y 581.337 kNkNkNkN
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The angular velocty gven below s the angular velocty of the boom at z axs.
boom
4
radradradrad
ssss
Accordng to ths angular velocty, dynamc force analyss has been evaluated:
Fbmax.x +mcombined.b boom2
Lboom R3x
=Fbmax.x 324.734 kNkNkNkN
Fbmin.x R3x
=Fbmin.x 319.826 kNkNkNkN
D. Fatgue Analyss
The selected materal for ths backhoe applcaton s AR !" #teel.
$ropertes of AR !":
%eld strength y.235 482.6 MPaMPaMPaMPa
Tensle strength u.235 792.89 MPaMPaMPaMPa
&ndurance lmt S'e 396.45 MPaMPaMPaMPa
&ndurance lmt correlaton factors are set as :
#urface condton modfcaton factor
for machned steel
ka 0.88
#ze factor for bendng kb 0.667
'orkng condtons are always at
reasonable temperatures. #o the
temperature factor
kd 1
Relablty factor for (() ke 0.814
*scellaneous effects factor kf 1
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Corrected endurance lmt:
Se ka kb kd ke kf S'e =Se 189.418 MPaMPaMPaMPa
1. Stck Analyss
a.stick.max +FP1 Fsmax.x R2x
Astick=a.stick.max 22.549 MPaMPaMPaMPa
b.stick.max
+
mstick gggg Lstick
2 h
stick
2
Istick
Fsmax.y Lstick hstick
2
Istick
FP1 ds.p1 hstick
2
Istick
Kt.stick
=b.stick.max 329.207 MPaMPaMPaMPa
stick.max +b.stick.max a.stick.max =stick.max 306.658 MPaMPaMPaMPa
a.stick.min+FP1 Fsmin.x R2x
Astick=a.stick.min 23.208 MPaMPaMPaMPa
b.stick.min
+
mstick gggg Lstick
2
hstick
2
Istick
Fsmin.y Lstick hstick
2
Istick
FP1 ds.p1 hstick
2
Istick
Kt.stick
=b.stick.min 250.576 MPaMPaMPaMPa
stick.min +b.stick.min a.stick.min =stick.min 227.369 MPaMPaMPaMPa
Alternatng stress of crtcal pont of stck:
stick.alt stick.max stick.min2
=stick.alt 39.645 MPaMPaMPaMPa
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Mean stress of crtcal pont of stck:
stick.mean +stick.max stick.min2
=stick.mean 267.013 MPaMPaMPaMPa
Soderberg Falure Crteran:
Fatgue factor of Safety for stck
nstick.f Se y.235
+stick.alt y.235 Se stick.mean
=nstick.f 1.311
2. Boom Analyss
a.boom.max Kt.boom +FP2 R2x FP3 cos p3.g
Aboom
cos p3.g
=a.boom.max 0.843 MPaMPaMPaMPa
Kt.boom 0.41
b.boom.max Kt.boomhboom
2
+++
FP3 dp3.j3Iboom
FP2 dp2.j3
Iboom
mboom gggg dcogb.j3Iboom
Fbmax.y dj2.j3x
Iboom
=b.boom.max 179.652 MPaMPaMPaMPa
boom.max +b.boom.max a.boom.max =boom.max 178.809 MPaMPaMPaMPa
a.boom.min ++FP1 Fbmin.x R2x
Astick=a.boom.min 70.588 MPaMPaMPaMPa
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b.boom.min Kt.boomhboom
2
+++
FP3 dp3.j3Iboom
FP2 dp2.j3
Iboom
mboom gggg dcogb.j3Iboom
Fbmin.y dj2.j3x
Iboom
=b.boom.min 159.011 MPaMPaMPaMPa
boom.min +b.boom.min a.boom.min =boom.min 88.423 MPaMPaMPaMPa
Alternatng stress of crtcal pont of stck:
boom.altboom.max boom.min2
=boom.alt 133.616 MPaMPaMPaMPa
Mean stress of crtcal pont of stck:
boom.mean+boom.max boom.min
2
=boom.mean 45.193 MPaMPaMPaMPa
Soderberg Falure Crteran:
Fatgue factor of Safety for stck
nboom.f
Se y.235+boom.alt y.235 Se boom.mean
=nboom.f 1.251
NOTE: All the factor of safetes are actually 4 tmes of ther values snce at the
begnnng of the analyss load has taken to be 2000 kg nstead of 500 kg
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E. Machne Components Desgn
Assumptons:
Time for liftng the bucket to 5m
y 5 mmmm
tlift 4 ssss Vy y
tlift=Vy 1.25
mmmm
ssss
Power Caluculatons:
Requred power n drecton
of y asPy +
+mload mbucket gggg y
tlift
mstick gggg y
2
tlift
=Py 9.807 kWkWkWkW
The dstance between the Co! of the bucket and "ont #:
rbucket.x ++Lb1 sin p3.g Lb2 cos p3.g Lstick Lbucket cos b.closed
rbucket.y +Lb1 cos p3.g Lb2 sin p3.g Lbucket sin b.closed
rbucket+rbucket.x
2rbucket.y
2
=rbucket 3.95 mmmm
The dstance between the Co! of the stck and "ont #:
rstick.x ++Lb1 sin p3.g Lb2 cos p3.g
Lstick
2
rstick.y +Lb1 cos p3.g Lb2 sin p3.g
rstick+rstick.x
2rstick.y
2
=rstick 4.103 mmmm
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The dstance between the CoG of the boom and Jont 3:
rboom.x Lb1 sin p3.g
rboom.y Lb1 cos p3.g
rboom+rboom.x
2rboom.y
2
=rboom 1.5 mmmm
Angular velocty:
w
4
radradradrad
ssss
Angular acceleraton:
8
radradradrad
ssss2
Moment of Inertas:
Ibucket.p +mbucket mload rbucket2
=Ibucket.p 1.092 104
kgkgkgkg mmmm2
Istick.p mstick rstick2
=Istick.p 3.367 103
kgkgkgkg mmmm2
Iboom.p mboom rboom2
=Iboom.p 787.5 kgkgkgkg mmmm2
Actng toqrue:
++Iboom.p Istick.p Ibucket.p
= 5919.562 NNNN mmmm
equred !ower to rotate the system n drecton of " a#s:
Pz w
=Pz 4.649 kWkWkWkW
Total requred !ower:
Pdet +Py Pz
=Pdet 14.456 kWkWkWkW
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Effcences:
mechanical 0.9
hydraulic 0.7
Power of hydraulc motor:
P Pdet
hydraulic mechanical
=P 22.946 kWkWkWkW
Electric motor efficiency and gearbox efficiency
el.motor 0.91
gb 0.9
Pel.motor P
el.motor gb
=Pel.motor 28.017 kWkWkWkW
It s assumed that, the backhoe s workng at a fxed poston wth AC electrcty
Consderng rough calculatons, the speed of electrc motor s found low !o t s
con"enent to use AC motor wth # poles
Power of electric motor $ %& kw choosen
Propertes of electrc motor:
MARATHON 404 TTFS8102 % phases, '& (), %&k*, +'& rpm, -+. eff
P 30 kWkWkWkW
N 750 rpmrpmrpmrpm
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1. Shaft Desgn:
When desgnng the shaft, smlar applcatons are researched. Theconvenent materal for ths shaft s determned as AISI 440 C steel.
The propertes of shaft are gven below:
ength of shaft L 2 mmmm
!eld strength y 450 MPaMPaMPaMPa
Shear mod"l"s G 77.2 GPaGPaGPaGPa
#lasc mod"l"s E 210 GPaGPaGPaGPa
$enst% 7800kgkgkgkg
mmmm3
Shear %eld strength y 0.5
The cl"tch ma% ca"se mpacts on the shaft so&
'actor of safet% n 2.4
Allowable shear stress:
all
n
=all 93.75 MPaMPaMPaMPa
(a)m"m tor*"e appled on the shaft:
T P
N
=T 381.972 NNNN mmmm
Shaft dameter calc"latons:
$ameter
d3
T 16
all
=d 2.748 cmcmcmcm
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The shaft dameter s assumed as 3 cm;
d 3 cmcmcmcm
Mass of shaft
m d
2
4 L
=m 11.027 kgkgkgkg
Weght of shaft W m gggg
=W 108.138 NNNN
Weght dstrbuton wdistW
L
Polar moment of nerta J d
4
32 =J 7.952 10
8mmmm
4
Area moment of nerta I
64 d
4=I 3.976 10
8mmmm
4
Angular deflecton
t T L
J G360
2
=t 7.13
Bendng deflecton
max5 wdist L
4
384 E I
=max 1.349 103
mmmm
Maxmum speed
Nmax 0.75
gggg
max
=Nmax 610.628 rpmrpmrpmrpm
The maxmum speed s lower than requred speed of shaft. o the new
dameter s selected as ! cm
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"ameter of shaft d 4 cmcmcmcm
Mass of shaftm
d2
4 L
=m 19.604 kgkgkgkg
Weght of shaft W m gggg
=W 192.245 NNNN
Weght dstrbuton wdistW
L
Polar moment of nerta J d
4
32 =J 2.513 10
7mmmm
4
Area moment of nerta I
64 d
4=I 1.257 10
7mmmm
4
Angular deflecton
t T LJ G
3602
=t 2.256
Bendng deflecton
max 5 wdist L
4
384 E I
=max 7.588 104
mmmm
Maxmum speed
Nmax 0.75
gggg
max
=Nmax 814.171 rpmrpmrpmrpm
Maxmum speed s hgher than the requred speed. o t can be used.
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2. Bearng Selecton
Lfe assumpton:
It s assumed that the backhoe wll work 30 years,
9 month per year and 8 hour per day
Life 750 30 270 8 60
106
=Life 2.916 103
mllon cycle
ka 1.1 because of clutch impactmay occur
kr 1 90% reliability is enouh
FbW
2 a 3
C a
Life ka Fb =C 1.511 kNkNkNkN
!earin selection
"eep roo#e ball bearin is choosen because of low radial forces
$& '(808 s choosen
d " ! ) )0
$& *+plorer bearin
0 -. / ,9 3,- .'000 ('000
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3. Gear and Belt
Np 5500 rpmrpmrpmrpm
Nem 750 rpmrpmrpmrpm Electrc motors speed s low because of shafts vbratonrestrcton.
Reducton rato
RR Np
Nem=RR 7.333
Desgn Crteron
Gear part of the reducton s set to be 5; RRG 5
So the belt part s;
RRB7.333
RRG=RRB 1.467
Nmain Nem =Nmain 750 rpmrpmrpmrpm
Npinion Nmain RRG =Npinion 3.75 103
rpmrpmrpmrpm
P 30 kWkWkWkW
L 100 106
50 HRC
m 4 mmmmmmmm Assumpton
zpinion 20
dpinion m zpinion =dpinion 80 mmmmmmmm
dmain Npinion
Nmaindpinion =dmain 400 mmmmmmmm
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b 10 m =b 40 mmmmmmmm Assumption between 9m-14m
Spur Gear-Tooth Bending Stress (AGMA)
FO !"#"O#
V Npinion dpinion
2 =V 15.708
mmmm
ssssTpinion
P
Npinion
=Tpinion 76.394 NNNN mmmmFt
Tpinion
dpinion=Ft 0.955 kNkNkNkN
J 0.35 From graph
Kv1
0.6From graph Ko 1.25 From Tab$e
Km 1.3 From Tab$e %&4 (sma$$ bearing '$earan'es)
pinion Ft
b m JKv Ko Km =pinion 46.183 MPaMPaMPaMPa
Assume ast "ron grade * as materia$ o+ both gear
sf 482 MPaMPaMPaMPa ut 240 MPaMPaMPaMPa 'e 97 MPaMPaMPaMPa
kL 1 kV 1 ks 0.8 kr 0.814 (,99) kt 1 kf 1
km 1.33
e 'e kL kV ks kr kt kf km =e 84.011 MPaMPaMPaMPa
B#."#G FO MA"# GA
V Nmain dmain
2 =V 15.708
mmmm
ssssTmain
P
Nmain
=Tmain 381.972 NNNN mmmmFt
Tmain
dmain=Ft 0.955 kNkNkNkN
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J 0.35 From graph
Kv 1
0.6From graph Ko 1.25 From Table
Km 1.3 From Table 7.4 (small bearing clearances)
main Ft
b m JKv Ko Km =main 46.183 MPaMPaMPaMPa
this values are same with
pinion
Assume Cast Iron grade 3 as material o! both gear
'sf 482 MPaMPaMPaMPa ut 240 MPaMPaMPaMPa
"ith hardening # $%C assumed
ut 1665 MPaMPaMPaMPa 'e =ut
2 832.5 MPaMPaMPaMPa
kL 1 kV 1 ks 0.8 kr 0.814 (&'') kt 1 kf 1
km 1.33
e 'e kL kV ks kr kt kf km =e 721.025 MPaMPaMPaMPa
I sin 20 cos 20
2
5
6
Cp 149 MPaMPaMPaMPa0.5
H Cp
Ft
b dpinion IKv Ko Km =H 339.983 MPaMPaMPaMPa
KL 0.9 KT 1 KR 1
sf 'sf KL KR KT =sf 433.8 MPaMPaMPaMPa
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4. Hydraulic Calculations for Hydraiulic Pump Selection
To calculate piston volumetric flow rate, piston rods speeds are needed. That
speed is directly depend on speed of bucket , stick and boom. That's why relationbetween these speeds must be defined. These relation basically ratio of length piston
arms and parts length (bucket,stick,boom). On this assumption effect of angle
between parts are ignored to easier calculations.
Analysis have been made by pi! ma"imum lifting for boom and stick. #ut on a
combine movement these speeds will limited to pi$ for each.
%ovement on rotat&onal a"&s' &s not calculated because of these mot&ons w&ll
reduce each other on comb&ne movement to decrease forces that act&ng on arms and
s&e of pump.
Distance between stick and piston 1 dp1 25 cmcmcmcm
Distance between boom and piston 2 dp2 30 cmcmcmcm
Distance between boom and piston 3 dp3 30 cmcmcmcm
Bucket rotational velocity for lifting motion wbucket
2 radradradrad
ssss
Stick rotational velocity for lifting motion wstick
4
radradradrad
ssss
Boom rotational velocity for lifting motion wboom
8 radradradrad
ssss
Typical pressure for pistons are 300 bar but piston type pumps can reach
420 bar so 400 bar is selected and forces on pistons are already known
from report 2 than;
Hydraulic pressure for pistons P 400 barbarbarbar
Forces acting on piston 1 Fp.1 54.494 kNkNkNkN
Forces acting on piston 2 Fp.2 150.067 kNkNkNkN
Forces acting on piston 3 Fp.3 639.652 kNkNkNkN
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Area and bore of pistons are ;
Area of piston 1 Ap.1 Fp.1
P
=Ap.1 1.362 103mmmmmmmm
2
Dp.1
4 Ap.11
=Dp.1 41.649 mmmmmmmm
to standardization Dp.1 45 mmmmmmmm
Ap.1 Dp.1
2
4
Area of piston 2 Ap.2Fp.2
P
=Ap.2 3.752 103mmmmmmmm
2
Dp.2 4 Ap.21
=Dp.2 69.114 mmmmmmmm
Dp.2 70 mmmmmmmm
Ap.2 Dp.2
2
4
Area of piston 3 Ap.3Fp.3
P
=Ap.3 159.913 cmcmcmcm2
Dp.3
4 Ap.31
=Dp.3 142.691 mmmmmmmm
Dp.3 145 mmmmmmmm
Ap.3 Dp.3
2
4
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Speed and volumetric flow rate of piston rods are ;
Speed of piston rod 1 vp.1 dp1 wbucket
Volumetric flow rate of piston 1 Qp.1 vp.1 Ap.1
=Qp.1 0.625 LLLL
ssss
Speed of piston rod 2 vp.2 dp2 wstick
=vp.2 0.236 mmmm
ssss
Volumetric flow rate of piston 2 Qp.2 vp.2 Ap.2
=Qp.2 0.907 LLLL
ssss
Speed of piston rod 3 vp.3 dp3 wboom
Volumetric flow rate of piston 3 Qp.3 vp.3 Ap.3
=Qp.3 1.945 LLLL
ssss
Speed of piston 4 (for rotating)
Needed volumetric flow rate for pump selection;
Q ++Qp.1 Qp.2 Qp.3
=Q 208.603LLLL
minminminmin
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Hacettepe University Department of Mechanical Engineering 40
F. Simulation Results
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Hacettepe University Department of Mechanical Engineering 41
Model name: Gen.V2
Current Configuration: Varsaylan
Solid Bodies
Document Name and
ReferenceTreated As Volumetric Properties
Document Path/Date
Modified
Fillet4
Solid Body
Mass:115.931 kg
Volume:0.0147683 m^3
Density:7850 kg/m^3
Weight:1136.12 N
D:\Gen.V2\hyd.cyl\1.SL
DPRT
May 20 01:00:14 2015
Fillet3
Solid Body
Mass:71.1489 kg
Volume:0.00906355 m^3
Density:7850 kg/m^3
Weight:697.259 N
D:\Gen.V2\hyd.cyl\1.SL
DPRT
May 20 01:00:14 2015
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Hacettepe University Department of Mechanical Engineering 42
Fillet3
Solid Body
Mass:28.0339 kg
Volume:0.0035712 m^3
Density:7850 kg/m^3
Weight:274.733 N
D:\Gen.V2\hyd.cyl\1.SL
DPRT
May 20 01:00:14 2015
Fillet1
Solid Body
Mass:13.5738 kg
Volume:0.00172914 m^3
Density:7850 kg/m^3
Weight:133.023 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:2.01023 kg
Volume:0.00025608 m^3
Density:7850 kg/m^3
Weight:19.7002 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:7.78129 kg
Volume:0.000991247 m^3Density:7850 kg/m^3
Weight:76.2566 N
D:\Gen.V2\boompin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:1.27543 kg
Volume:0.000162475 m^3
Density:7850 kg/m^3
Weight:12.4992 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:5.92278 kg
Volume:0.000754494 m^3
Density:7850 kg/m^3
Weight:58.0432 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
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Hacettepe University Department of Mechanical Engineering 43
Fillet1
Solid Body
Mass:2.01527 kg
Volume:0.000256723 m^3
Density:7850 kg/m^3
Weight:19.7497 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:5.92278 kg
Volume:0.000754494 m^3
Density:7850 kg/m^3
Weight:58.0432 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:2.27422 kg
Volume:0.000289709 m^3
Density:7850 kg/m^3
Weight:22.2873 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:5.36096 kg
Volume:0.000682924 m^3Density:7850 kg/m^3
Weight:52.5374 N
D:\Gen.V2\boompin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:2.49617 kg
Volume:0.000317984 m^3
Density:7850 kg/m^3
Weight:24.4625 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
Fillet1
Solid Body
Mass:6.29235 kg
Volume:0.000801573 m^3
Density:7850 kg/m^3
Weight:61.665 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
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Hacettepe University Department of Mechanical Engineering 44
Fillet1
Solid Body
Mass:7.78129 kg
Volume:0.000991247 m^3
Density:7850 kg/m^3
Weight:76.2566 N
D:\Gen.V2\boom
pin_V2.SLDPRT
May 20 00:39:04 2015
Fillet27
Solid Body
Mass:253.134 kg
Volume:0.0322463 m^3
Density:7850 kg/m^3
Weight:2480.71 N
D:\Gen.V2\boom
rev1_V2.sldprt
May 20 00:39:00 2015
Fillet25
Solid Body
Mass:479.509 kg
Volume:0.0610839 m^3
Density:7850 kg/m^3
Weight:4699.18 N
D:\Gen.V2\boom_V2.SL
DPRT
May 19 17:27:25 2015
Fillet5
Solid Body
Mass:38.6272 kg
Volume:0.00492066 m^3Density:7850 kg/m^3
Weight:378.546 N
D:\Gen.V2\bucketlink1_V2.SLDPRT
May 20 00:36:35 2015
Fillet1
Solid Body
Mass:12.1638 kg
Volume:0.00154952 m^3
Density:7850 kg/m^3
Weight:119.205 N
D:\Gen.V2\bucketlink2_
V2.SLDPRT
May 20 00:36:07 2015
Fillet4
Solid Body
Mass:74.7706 kg
Volume:0.00952495 m^3
Density:7849.98 kg/m^3
Weight:732.752 N
D:\Gen.V2\bucketlink3_
V2.SLDPRT
May 20 00:35:41 2015
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Hacettepe University Department of Mechanical Engineering 45
Fillet7
Solid Body
Mass:241.524 kg
Volume:0.0307674 m^3
Density:7850 kg/m^3
Weight:2366.93 N
D:\Gen.V2\myownbucket
2_V2.SLDPRT
May 19 15:47:21 2015
Fillet2Solid Body
Mass:1.21139 kg
Volume:0.000154317 m^3
Density:7850 kg/m^3
Weight:11.8716 N
D:\Gen.V2\hyd.cyl\Holde
r.SLDPRT
May 20 00:16:58 2015
Cut-Revolve2Solid Body
Mass:44.2107 kg
Volume:0.00563194 m^3
Density:7850 kg/m^3
Weight:433.265 N
D:\Gen.V2\hyd.cyl\Rod.S
LDPRT
May 20 00:24:40 2015
Fillet2Solid Body
Mass:1.21139 kg
Volume:0.000154317 m^3
Density:7850 kg/m^3
Weight:11.8716 N
D:\Gen.V2\hyd.cyl\Holde
r.SLDPRT
May 20 00:16:58 2015
Cut-Revolve2Solid Body
Mass:25.345 kg
Volume:0.00322866 m^3
Density:7850 kg/m^3
Weight:248.381 N
D:\Gen.V2\hyd.cyl\Rod.S
LDPRT
May 20 00:24:40 2015
Fillet2Solid Body
Mass:1.21139 kg
Volume:0.000154317 m^3
Density:7850 kg/m^3
Weight:11.8716 N
D:\Gen.V2\hyd.cyl\Holde
r.SLDPRT
May 20 00:16:58 2015
Cut-Revolve2Solid Body
Mass:7.32229 kg
Volume:0.000932776 m^3
Density:7850 kg/m^3
Weight:71.7584 N
D:\Gen.V2\hyd.cyl\Rod.S
LDPRT
May 20 00:24:40 2015
Fillet16
Solid Body
Mass:349.622 kg
Volume:0.0445379 m^3
Density:7850 kg/m^3
Weight:3426.3 N
D:\Gen.V2\stick
v2_V2.SLDPRT
May 20 00:24:39 2015
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Hacettepe University Department of Mechanical Engineering 46
1. Study Properties
Study name dinamik
Analysis type Static
Mesh type Solid Mesh
Thermal Effect: On
Thermal option Include temperature loads
Zero strain temperature 298 Kelvin
Include fluid pressure effects fromSolidWorks Flow Simulation
Off
Solver type FFEPlus
Inplane Effect: Off
Soft Sprin: Off
Inertial !elief: Off
Incompati"le "ondin options Automatic
#are displacement Off
$ompute free "ody forces On
Friction Off
%se Adaptive Method: Off
!esult folder Solidorks document !d"#temp$
%nit system: SI !MKS$
#enth&'isplacement mm
Temperature Kelvin
Anular velocity %ad&sec
(ressure&Stress '&mm(2 !MPa$
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Hacettepe University Department of Mechanical Engineering 47
2. Loads and Fixtures
Fi)ture name Fi)ture Ima*e Fi)ture +etails
Fi)ed,-
Entities: ) face*s+
Type: Fi,ed -eometry
%esultant Forces
$omponents . / Z !esultant
!eaction force*0+ 1112)13 )443325 61112437 )445425
!eaction Moment*02m+ 8 8 8 8
.oad name .oad Ima*e .oad +etails
Force,-
Entities: 3 face*s+!eference: Ede9 3
Type: Apply force;alues: 666< 666< 38888 0
/ravit0,-
!eference: =st '>?lem;alues: 8 8 61273
%nits: SI
Force,2
Entities: 3 face*s+!eference: Ede9 3
Type: Apply force;alues: 666< 666< 3888 0
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Hacettepe University Department of Mechanical Engineering 48
Force,1
Entities: 3 face*s+!eference: Ede9 3
Type: Apply force;alues: 666< 666< 3888 0
3. Mesh Information
Mesh type Solid Mesh
Mesher %sed: urvature 3ased mesh
@aco"ian points 4 Points
Ma,imum element si?e 2596247 mm
Minimum element si?e 4-68494 mm
Mesh uality i*h
!emesh failed parts with incompati"le mesh Off
Mesh Information - Details
Total 0odes 18715
Total Elements 22894
Ma,imum Aspect !atio 216-
B of elements with Aspect !atio 9 C ::6:
B of elements with Aspect !atio 38 164
B of distorted elements*@aco"ian+ 5
Time to complete mesh*hhDmmDss+: 55"55"29
$omputer name: A.PE%E',P
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Hacettepe University Department of Mechanical Engineering 49
Mesh Control Information:
Mesh ontrol 'ame Mesh ontrol Ima*e Mesh ontrol +etails
ontrol,-
Entities: 3 Solid ody *s+
%nits: mmSi?e: 5528131
!atio: 32
ontrol,2
Entities: C Solid ody *s+%nits: mm
Si?e: 3428337!atio: 32
ontrol,1
Entities: 7 Solid ody *s+%nits: mm
Si?e: C4217G1!atio: 32
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Hacettepe University Department of Mechanical Engineering 50
ontrol,4
Entities: 3G Solid ody *s+%nits: mm
Si?e: C2131!atio: 32
3. Study Results
0ame Type Min Ma,
Stress- ;O'" von Mises Stress 16-7521e,55 '&mm(2
!MPa$
'ode" 119287
45:6858 '&mm(2 !MPa$
'ode" 4971
/en6;2,dinamik,Stress,Stress-
0ame Type Min Ma,
+isplacement-
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Hacettepe University Department of Mechanical Engineering 51
/en6;2,dinamik,+isplacement,+isplacement-
0ame Type Min Ma,
Strain- ES=%'" E>uivalent Strain -6:29-2e,5-5
Element" :758
5655-:949
Element" 2454
/en6;2,dinamik,Strain,Strain-
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Hacettepe University Department of Mechanical Engineering 52
0ame Type Min Ma,
Factor of Safet0- Automatic -6-14
'ode" 4971
-64824e?557
'ode" 119287
/en6;2,dinamik,Factor of Safet0,Factor of Safet0-
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Hacettepe University Department of Mechanical Engineering 53
Figure 4 - Critical points of Factor of Safety
Figure 5 - Critical points of Factor of Safety
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Hacettepe University Department of Mechanical Engineering 54
Figure 7 - Static Factor of Safety Critical points
Figure 6 - Fatigue analysis and total life
This is the critical point of the first work. In order to avoid this huge stress concentration, the sizeof joints are made bigger and stronger.
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G. Cost Analysis
From,@rand Properties
Price of
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H. 3D Drawings
Figure 8 - Side view technical drawing of closed position
Figure 9 - Top view technical drawing of closed position
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Figure 10 - Front and back view technical drawing
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Figure 11 - Top view technical drawing of opened position
Figure 12 - Isometric view technical drawing of opened position
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Figure 13 - Isometric view technical drawing of closed position
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Figure 14 - CAD view 1
Figure 15 - CAD view 2
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Figure 16 - CAD view 3
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IV. CONCLUSION AND DISCUSSION
A. Summary and Discussion of the Results
After the implementation of each subsystems to the system, analysis carried out and
results obtained. These results are evaluated and according to them methods has been
developed. The developed methods are depend on the motivation and design approach of this
project. Results are discussed whether the system provides requirements and whether the
system is over safe. If the system turned out to be over safe, downsizing has considered and
applied according to the amount of excess factor of safeties. For the present this system is safe
enough and reliable to perform a lifting of 500 kg.
B. Future Works
In our project the main approach was making the most optimal backhoe with high
speed and low cost. The cost depends on the material. In the future there will be more safer
materials with higher speed ability and lower cost. Also the manufacturing will cost less
because the technology will improve and that will cause decrease in cost. In other projects our
aim will be design a machine with longer life time, with safer material and high ability to
desired approach.
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V. REFERENCES
1. How Caterpillar Backhoe Loaders Work
http://science.howstuffworks.com/transport/engines-equipment/backhoe-loader1.htm
2. New Backhoe Loaders CAT 422F
http://www.cat.com/en_ZA/products/new/equipment/backhoeloaders/sideshift/18346265.html
3. CAT Backhoe Loader Brochure
http://s7d2.scene7.com/is/content/Caterpillar/C768535
4. Backhoe Loader
http://en.wikipedia.org/wiki/Backhoe_loader
5. Backhoe
http://opensourceecology.org/wiki/Backhoe
6. SKF Rolling Bearings
http://www.skf.com/binary/138-121486/SKF-rolling-bearings-catalogue.pdf
7. SKF Extra Power Belts
http://www.skf.com/binary/92-118145/Xtra-Power-belts---10552_3-EN.pdf
8. SKF Belt Drive Design Calculations Tool
http://www.skf.com/group/knowledge-centre/engineering-tools/belt-drive-design-
calcalutions-tool.html
9. Gamak 3 Phase Asynchronous Electric Motors
http://www.gamak.com/images/urun-pdf/standart_motorlar.pdf
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Engineering Skills
Firstly this project has improved the engineering skills of all of the group members.
All of the theoretical informations were used in order to get something perceptible. The most
important processes were the problems. Sometimes there was huge problems and it was hard
to solve them. Beacuse of these problems the project did not go easily straight forward. But at
this point all of the group members tried to create a way out and the brain stormings, which
are made during these problems were very important. During this continuum a lot of shiny
idea are took shape and the problems were solved. Besides the problems the technical drawing
and alaysis skills were improved.
This project was a good first step and a great experience for our engineering career.
Its sure that all of us will use these experiences and informations in the future.
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1
A. Sample Cost Analysis
Shaft Manufacturing Analysis
Model ad: Long ShaftRapor tarih ve zaman: 5/20/2015 10:50:37 AM
Malzeme: lain !ar"on Steel
#retim $%re&i: Ma'ineleme
(amamlanm) par*a a+rl+: 55,03 l"
Sto' tipi: -lo&'
-lo&' Size: 1,57.1,57.7,7 in
Malzeme malieti/a+rl+: 1,1 S/l"
Shop Rate: 30,00 S
#retile&e' Mi'tar(oplam par*a $a$: 100
Lot "%%'l%+%: 100
ar*a "a)na 4ng4r%lenmaliet:
88.85 USD
6llanlan maliet )a"lon6:ma&hiningtemplatedefa6lt8engli$h$tandard9,$ld&tm
6llanlan maliet mod6: Man6fa&t6ring ro&e$$ Re&ognition
ar)la)trma:
Maliet a+lmMalzeme: 77,5 S 7;
#retim: 11,27 S 13;
Mar'6p 0,00 S 0;
ar*a "a)na 4ng4r%len$%re:
00:22:31
6r6l6mlar: 00:05:35
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2
Maliyet Raporu
Model Ad: art1 Malzeme: lain !ar"onSteel
Malzeme malieti: 77,5 S (oplam maliet/par*a:
88.85 USD
#retim malieti: 11,27 S (oplam $%re/par*a: 00:22:31
Mar'6p 0,00 S
retim Maliyet Dalm
lem Ayarlar ama! "##:$$:##% Maliyet "USD%
Setup &peratio! 1 00:00:3= 0,30
'oplam 00:00:3( 0.30
)urulumlar *+,le -e )al$r ama! "##:$$:##% Maliyet "USD%Setup &peratio! 1 00:05:00 2,50
'oplam 00:05:00 2.50
re/e lemi*+/eyila#
,arla! aim"i!43%
ama!"##:$$:##%
Maliyet"USD%
Aletlee,ille!$ir
me
aima!aMaliyet
"USD6i!43%
7olume 1 Ro6ghing 10, 00:0:13 2,12>lat ?nd
Mill@/A
7olume 2 Ro6ghing 10, 00:0:13 2,12>lat ?nd
Mill@/A
7olume 3 Ro6ghing 10, 00:0:13 2,12>lat ?nd
Mill@/A
7olume Ro6ghing 10, 00:0:13 2,12>lat ?nd
Mill@/A
'oplam 1.91 00:1(:55 8.
)urulum lemleri1. Setup &peratio! 1
a. 7olume . 7olume 2. 7olume 3$. 7olume 1
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B. Belt Specifications
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