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# Sugar Cane machine design MA3001

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This 30 page Bundle was uploaded by Ace Notetaker on Sunday September 27, 2015. The Bundle belongs to MA3001 at Nanyang Technological University taught by in Summer 2015. Since its upload, it has received 1323 views.

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Date Created: 09/27/15

N AN YAN G TECHNOLOGICAL UNIVERSITY SCHOOL OF MECHANICAL AND AEROSPACE ENGINEERING MA3001 MACHINE ELEMENT DESIGN PROJECT FINAL REPORT SUGAR CANE JUICE EXTRACTION MACHINE DONE BY TAN KE WEI U1120928E CHAN WEI SHENG ALVIN U1121167J TOH ZUAN MING U1121860L MA 3001 Machine Element Design Project Final Report TABLE OF CONTENTS 1 OVERVIEW 2 2 INDIVIDUAL COMPONENTS 4 21 MOTOR SELECTION 4 22 ROLLER SELECTION 4 23 GEAR DRIVE SELECTION 5 24 BELT DRIVE SELECTION 6 25 SHAFT DESIGN 8 3 FORCES ANALYSIS 9 31 BELT DRIVE 9 32 GEAR DRIVE 1 1 33 SHAFT DIAGRAMS AND DESIGN 11 34 BEARING SELECTION 15 35 KEY SELECTION 17 4 ASSEMBLY DRAWINGS AND PARTS LIST 19 APPENDIX 20 Page1 MA 3001 Machine Element Design Project Final Report 1 OVERVIEW The objective of the project is to design a sugar cane juice extraction machine including its power transmission drive based on a set of given requirements and ratings while keeping in line with engineering design requirements such as the effective use of components within the required parameters maintainability and availability of parts The transmission drive was to comprise of a combination of a spurhelical gear drive and a beltchain drive system The final product should be compact and have access to AC power supply Input Power 025 037 055 kW Input Speed 1420 rpm Desired Output Speed 25 35 45 55 rpm Maximum Dimensions 750 mm L by 750 mm B by 1300 mm H Our group has selected 025 kW as the input power and 55 rpm as the desired output speed for our project Smooth operation is assumed throughout the components of the sugar cane juice extraction machine designed Page2 MA 3001 Machine Element Design Project Final Report I39 i39 Page3 MA 3001 Machine Element Design Project Final Report 2 INDIVIDUAL COMPONENTS 21 MOTOR SELECTION The required motor output power and speed are 025 kW and 1420 rpm respectively Based on the requirements a commercially available general purpose aluminium motor product code of 3GVAO7lOOl CSB motor type M2VA 71 A by ABB was found to be suitable with the exact motor output power and speed The dimensions of the motor are as follows Motor Height 176 mm Motor Length 238 mm Motor Breadth 112 mm Height of Shaft from ground 71 mm Shaft Diameter 14 mm 22 ROLLER SELECTION Diameter of Rollers 100 mm Distance between Rollers 12 mm Diametrical Pitch of Gears R1 amp R2 112 mm DG m NG Using Module m 200 mm 112 Required no of teeth for Roller Gears NR1 NR2 2 00 2 56 TGUPNG TP wG NP SIIICC NR1 NR2 TR1 TRZ Tmax Nm Use heattreatable steel C45 or highstrength special steel ETGlOO From Load Diagram Z056 using Module m 200 mm no 0 f Teeth 22 S NR S 70 Page4 MA 3001 Machine Element Design Project Final Report Since the required NR 56 the selected gear material and conditions will be able to withstand the torque 23 GEAR DRIVE SELECTION The gear drive is used mainly for greatly reducing the rotating speed of the system It is the first powertransmitting system that we chose to work on for speed reduction Selecting Input Power 025 kW Desired Output Speed 55 rpm P T max 0min 025 x 1000 55 x 27 60 43406 Nm No additional adjustments to torque such as service and safety factors are required since the design power of 025 kW is sufficient to drive the machine Assume the use of 4 Spur Gears G1 G2 G3 and G4 Using heattreatable steel C45 or highstrength special steel ETG100 From Table B1 using Module m 200 mm No0f Teeth 22 S N54 S 70 Since maximum number of teeth for G4 is 70 NGZ NG4 70 are selected To ensure no interference and referring to Table B2 NG1 NG3 16 are selected T03 T04 X 16 43406 X 7 0 9921 Nm Checking against Table B1 using m 200 mm NG3 16 can be used T T x N 01 02 N02 16 21gtlt 22 N 99 70 68 m PagelS MA 3001 Machine Element Design Project Final Report Checking against Table B1 using m 200 mm NG1 16 can be used Therefore the speed ratios for Gm and G34 2 3 g 4375 24 BELT DRIVE SELECTION The VBelt was selected for its high tensile strength and exibility and its ability to allow transmission of high torques without slippage From Table A3 with design power 025 kW faster shaft speed 1420 rpm SPZ belt cross section was selected quotinput D32N02N04 Overall Speed Ratio 2 noutput D31N01N03 1420 rpm DBZ7070 equire pee a l0 55 rpm DBl1616 D Required Belt Drive Speed RatioD B2 1349 B1 From Table A4 sheave diameters D31 112 mm and D32 150 mm were selected to obtain a belt drive speed ratio nearest to the required speed ratio of 1349 D32 150 Obtained Belt Drwe Speed Ratio 2 1339 D31 112 DBlNGlNGB Obt dO t tS d aine u pu pee nmput DBZNGZNG4 1121616 1420 x 55394 1507070 mS 0394 rpm Percentage Difference in Output Speed 2 W x 100 0716 Since the percentage difference in output speed is 0716 which is relatively low and hence negligible the power transmission drive designed is acceptable Also since the obtained output speed is greater than 55 rpm the requirements for torque and range of teeth number are not affected Page6 MA 3001 Machine Element Design Project Final Report DBlel Belt Speed 121 2 112 x 1426OX21I 2 8327 ms Since 121 8327 ms S 33 ms which is the maximum belt speed before slippage occurs the smaller sheave diameters D31 112 mm is suitable Tentative Center Distance TCD 700 mm is selected Tentative Belt Len th TBL 2 x TCD ED D DBZ D312 g 39 2 32 Bl 4 x TCD 2 x 700 7T150 112 150 1122 1812 06 2 4 x 700 39 mm From Table A1 the nearest standard belt length L 1800 mm is selected Required Center Distance D32 lt C lt 3DBZ D31 Required Center Distance 150 lt C lt 786 B BZ 32D32 DB12 16 Actual Center Distance C where B 4L 21tDBZ D31 2 555381 555381 5553812 32150 1122 Actual Center Distance C 16 69397 mm o 1 D32 D31 Angle of Contact of Smaller Sheave931 180 2 SH T 180 2 39 1 150 112 176 4 5m 2 x 69397 39 From Table A5 the nearest arc of contact of 174 is selected With corresponding Correction Factor for Arc of Contact C9 099 From Table A6 under Profile SPZ L 1800 mm Belt Length Correction Factor C L 102 Fage7 MA 3001 Machine Element Design Project Final Report From Table A7 using double interpolation Speed Ratio RPM of Smaller Sheave 1200 1420 1450 1200 270 31136 317 D31 112 mm 1339 31496 1500 276 31912 325 Rated Power RP 3150 kWbelt Corrected Rated Power CRP C6 x CL x RP 099 X 102 X 3150 3181 kWbelt Design Power R 39 d B It equlre no of e S Corrected Rated Power 03925 00786 3181 39 Since the next largest real number is 1 the number of belts required 1 25 SHAFT DESIGN Before beginning the shaft design a material has to be selected based on its material properties From Table B5 A181 1050 Colddrawn carbon steel was chosen and its material properties are Sy 690 MPa Su 579 MPa Next by using Table B6 the endurance strength Sn is estimated to be 263 MPa for a tensile strength Su 579 MPa Also by designing a desired reliability of 50 the reliability factor CR is 075 Next assuming the shaft size is to be reasonably large an estimate of C3 075 is utilised From the modified endurance strength equation S n Sle Cs XCR 263075075 165 MPa For the placement of various components on the first shaft the vbelt taper lock pulley A is placed on the outermost left on its right there is a bearing B a spur gear C and lastly a second bearing D The bearings do not experience any torque at all thus the components that consist of torque are the spur gear and the vbelt taper lock pulley As we are able to calculate the rotational speed of the driven sheave which is identical to that of the spur gear the rotational speed is 10605 rpm With that the torque T can be calculated to be PagelB MA 3001 Machine Element Design Project Final Report P 025 x 103 Z a Z 21t10605 23925 Nm 60 3 FORCES ANALYSIS 31 BELT DRIVE The belt tensions F1 and F2 would be calculated first Allowing for centrifugal force due to the inertia effect of the belt the belt tension ratio can be obtained from 91f I F1FC sm e F2Fc Em Where F1 tension on tight side N F2 tension on slack side N FC centrifugal force inertia effect of belt N m belt mass per unit length 0070kgm from Table A8 12 belt velocity 8327 ms PC mm 0070kgm x 83272 4854 N f coefficient of friction on belt sheave 91 angle of contact on the small sheave radian 3087 radian B half the included angle on the sheave groove 19 f Sin 3 f e effective coefficient of friction 040 from Table A8 PagelQ MA 3001 Machine Element Design Project Final Report 39 Driven 1 T1 1 T2 1 D1 2 D2 91f sm Where y 6 From Which we get F1 4719 N and F2 1717N Shaft loads are necessary in order to calculate the required shaft diameter The forces acting on the shafts F1 and F2 can be resolved in thee axes parallel and perpendicular to the centreline of the drive Thus giving the relations ZFX 0 FX F1 F2 cos 0i ZFy 0 Fy F1 F2 sin or FX F1 F2 cos OL 4719 1717 cos 15690 6434 N Fy F1 F2 sin or 4119 1717 sin 1569quot 0822N PagellO MA 3001 Machine Element Design Project Final Report 3 2 GEAR DRIVE The commonly used gear forces tangential load Wt and radial load Wr are the components of Wu The tangential component is the transmitted load and the one that is useful While the radial component does no useful work but tends to push the gears apart Wt TR 2TD 22250032 1407N Wr Wt tan I Where I pressure angle 20 5121N Wn Wt cos I 14973N 33 SHAFT DIAGRAMS AND DESIGN For XZ axis Loading Diagram A RC2 14069N D l RBZ 4261 N l RAZ 0822 N I RDZ 9891 N Page11 MA 3001 Machine Element Design Project Final Report Shear Force Diagram 41784 0 I 0822 9891 Bending Moment Diagram 262 A B C D 0019 For YZ axis Loading diagram RAy 396433 N RCy 5121 N l B D Ray 9627 N RDy 1927 N Page12 MA 3001 Machine Element Design Project Final Report Shear Force Diagram 3194 1927 6433 Bending Moment Diagram 449 Torque Diagram 225 Nm Page13 Shaft Diameter Calculation 2 32N kfb M 7t 3 3ltT 4 3y MA 3001 Machine Element Design Project Final Report 13 13 at 2 kfbM gt SnCSCR 3 4 3y 0008338 m 8338 mm gt Where Design Factor N 3 Typical industrial conditions Moment M V26232 44872 5197Nm Point C Where there is highest moment amp torque Stress Concentration Factor kfb 15 well rounded fillets Endurance Strength Sn 2 263 X 106 Pa From Figure Table B6 D 011 Slze Factor C5 762mmltDlt50mm Reliability Factor C R 075 From Table 51 desired reliability 0999 Torque T 2251Nm Yield Strength sy 579 x 106Pa Table B5 selected 1050 Colddrawn Point Item K M Nm erl n D 111211124 DIlnzlll6 Left ofA 15 0 225 47 0 0 A Bearing 15 0 225 47 6433 14 Right ofA 15 0 225 47 6433 14 Left of B 15 1480 225 58 6433 14 B Belt 15 1480 225 58 5259 13 Right ofB 15 1480 225 58 5259 13 Left of C 15 520 225 83 5259 13 C Gear 15 520 225 83 10077 18 Right of C 15 520 0 83 10077 18 Left of D 15 0 0 0 10077 18 D Bearing 15 0 0 0 0 0 Right of D 15 0 0 0 0 O Fage14 MA 3001 Machine Element Design Project Final Report 34 BEARING SELECTION We chose to use Deep Grove Ball Bearings for our machine design largely because they are the most common type of bearings It is also mainly used for pure radial loads which is similar to our design project Other advantages of Deep Grove Ball Bearing include its durability low coefficient of friction low cost and also it does not require regular maintenance On the shaft the components that contribute to the reactive forces on the bearings are the spur gear and vbelt taper lock pulley There will be no axial forces as well due to the use of spur gears thus all forces on the shaft are radial forces that act toward the centre of the bearings Hence we have to calculate the resultant radial forces acting on the bearings at points B and D and use them to find the dynamic load at these points Fradiaw 08222643272 6433 N FmdialD J1406942512082 14972 N The equation to be used to find the dynamic load is Pd VXFr YFa Where Pd equivalent radial or dynamic load Fr applied radial load Fa applied axial load V rotation factor 10 for innerring rotation X radial factor Y thrust factor In our design project there is no axial load hence Fa 0 thus the equation can be simplified to Pd VXFr 10 x10 x Fr PdFr Thus the dynamic loads acting on the bearings at points B and D are 6433 N and 14972 N respectively PagellS MA 3001 Machine Element Design Project Final Report After calculating the dynamic loads the life equation can be used to find the basic dynamic load rating We have chosen the design life L10 from Table B11 to be 12 X 103 hours as the sugar cane juice machine is assumed to be used intermittently and is also highly dependent on reliability 1 Using the dynamic load rating equation C Pd 719k k 3 for ball bearings we can find the ratings at points B and D 1 1 3 CB Pd B 6433 1473 N 1 1 3 CD Pd D 14972 3428 N The basic dynamic load ratings for the bearings at points B and D are calculated to be 1473N and 3428N After obtaining the basic dynamic load rating of 1473N at point B minimum bore diameters for both gear and belt sheave and finally referring to the catalogue bearing 6002 was chosen The properties of bearing number 6002 include Bore Diameter d mm 15 Outside Diameter D mm 32 Width W m 9 Fillet radius r mm 03 Basic Dynamic Load Rating C kN 585 Basic Static Load Rating C0 kN 285 Fatigue Load Limit kN 012 Limit Speed with on 103 rpm 32 Mass kg 003 Page16 MA 3001 Machine Element Design Project Final Report The properties above are based on 1 million revolutions and 90 reliability Bearing number 6002 was chosen because it satisfies all requirements for points B and D where the minimum diameters are 14mm and 12mm respectively Based on the catalogue and also the calculated dynamic load rating CD 3428 N it is confirmed that bearing number 6002 meets the criteria and hence it can be selected for the bearing at point D 35 KEY SELECTION The powertransmitting elements in our design which are the spur gears and the pulley are mounted on rotating shafts It is important to transmit the full torque from the shaft to gear hence the usage of a key is vital to prevent relative motion between the shaft and the connected machine elements The key is then placed at the interface between a shaft and the hub of a powertransmitting element gearpulley for transmitting torque It is also intended for safety purposes as it will shear before the shaft or machine element fails when there is a drastic increase in loading From earlier calculations and also referring to Table B10 we chose a key with groove width W of 5 mm and a key height H of 5 mm which is a square key We also chose the key to be made from A181 1040 Hotrolled steel with Sy 290MPa From previous shaft design calculations design factor N 3 and the torque in the shaft is 225Nm As for the shaft diameters for vbelt sheave and the spur gear they are 14mm and 12mm In order to determine the required key length we use two equations to calculate it The two equations are 4TN LS which is based on shear of the key and DWSy 4TN LC 2 Wthh 1s based on bear1ng stress DH sy For the bearing at point B where D 0014m 4TN 42253 DWsy 00140005290 x 106 LS B 133mm LcB Page17 MA 3001 Machine Element Design Project Final Report For the bearing at point D Where D 0012m 4TN 42253 DWSy 00120005 290 x 106 LS D 155mm 2 LCD Both LS values and LC are identical since the key is square hence H equals to W From the calculations above the required key lengths for points B and D are 133mm and 155mm respectively The larger of the two computed lengths governs the design hence we have to choose 155mm Referring to Table B9 the key lengths to be used for points B and D should b 14mm and 16mm PagellB MA 3001 Machine Element Design Project Final Report 4 ASSEMBLY DRAWINGS AND PARTS LIST Part No Description Qty Symbol O M2VA71A AC Motor 1 A 1610 14mm Bore Tapered Bush 2 B SPZ 112mm Belt Sheave 1 C SPZ 1800mm VBelt 1 D SPZ 150mm Belt Sheave 1 E 6002 15mm Bore Deep Grooved Bearing 8 F 1050 ColdDrawn Shaft 4 G SG 2016 16T Gear 2 H SG 2070 70T Gear 2 J Roller 2 K SG 2056 56T Gear 2 L Page19 5 Appendix A Table A1 APPENDIX MA 3001 Machine Element Design Project Final Report hs Cross Section Dirncnsnons and Belt Len 5quot z339 11123522 quot1225 SP2 97 B SPA 127 x 10 SP3 133 x 3 g 35 SP0 22 x 15 P 19 186 x 15 Standard Pitch Length SPA SP8 SPC SPA 800 SPA 850 SPA 900 SPA 950 SPA 1000 SPA 1060 SPA 1120 SPA 1180 SPA 1250 SP8 1250 SPA 1320 SP8 1320 SPA 1400 SP8 1400 SPA 1500 SP8 1500 SPA 1600 SP8 1600 SPA 1700 SP8 1700 SPA 1800 SPB 1800 SPA 1900 SP8 1900 SPA 2000 SP8 2000 SP6 2000 SPA 2120 SP8 2120 SP0 2120 SPA 2240 SP8 2240 SP6 2240 SPA 2360 SPB 2360 SP0 2360 SPA 2500 SP8 2500 SP0 25cc SPA 2550 39 SP8 2550 SP0 2550 SPA 2800 SPB 2800 SPC 2800 SPA 3000 SP8 3000 SP0 3000 SPA 3150 SPB 3150 mm 3150 SPA 3350 SP8 3350 SP0 3350 SPA 3550 SPB 3550 SP0 3550 SPA 3750 SP8 3750 SM 3750 SPA 4000 SP8 4000 SPc 4000 SPA 4250 SPB 4250 SP0 4250 SPA 4500 98 4500 SP6 4500 SP8 4750 SPc 4750 SP8 5000 SP6 5000 SP8 5300 SP0 5300 SP8 5600 SPc 5600 SP8 6000 SP6 6000 SP8 6300 SP0 6300 SPB 5700 SP0 6700 SP8 7100 SP0 7100 SPB 7500 SP0 39 7500 SP8 8000 SP0 8000 SP8 8500 SP0 8500 SPB 9000 SP0 9000 SP0 9500 90 10000 SPC 10600 SPc 11200 SP0 1 1800 SPC 12500 Pagelzo MA 3001 Machine Element Design Project Final Report Table A3 Choice of Cross Section F aster shaft rpm 063 10 16 25 40 63 10 16 25 40 63 100 160 250 400 Design Power Drive Pon39cr 3 Service Factor kW Table A4 Standard Sheave Diameters mm SPUSV 83 71 75 00 90 100 112 125 132 110 150 160 180 200 224 250 280 315 355 400 500 630 i SPNW 90 95 100 108 112 118 125 132 140 150 160 180 200 224 250 280 815 355 400 450 500 560 630 710 300 SPBISV 140 150 160 170 180 200 22 250 280 315 355400 450 500 580 600 710 750 800 900 1000 1120 EP CITV 224 236 250 265 280 300 315 335 355 400 450 500 560 600 630 710750 800 900 1000 1120 1250 1400 1600 2000 Page21 MA 3001 Machine Element Design Project Final Report Table A5 Correction Factor tor Arc of Contact CG Nucleoan woo o M 915111911511115119 174 Wquot 153 1571 151 145 139 133 127 120 113 105 99 911 C 1 P I 6 00 099 097 096 094 093 091 099 097 095 092 079 077 013 070 Table A 39 6 Standard Belt Length L mm and Belt Length Correction Factor CL i 1 Profile 39 82 Prollle SPA 4 Pr0 le SP8 Profile SPC i L quot1quot 2121 Correction Correction Correct 39 Mm factor L mm actor L mm do 630 o no 900 091 1250 093 2000 093 800 cg 900 093 1400 095 2240 085 9 1000 095 1900 097 2500 097 w 100 090 1 120 097 1900 099 2900 099 1 20 092 gt 1250 099 2000 090 3150 090 034 1400 090 2240 092 3550 092 150 099 1900 093 2500 094 4000 094 16 099 1900 094 2900 099 4500 099 100 2000 099 9150 099 5000 099 1900 102 2240 099 0550 100 5900 100 2000 104 2500 100 4000 102 9900 102 2240 109 2900 102 4500 104 7100 104 2500 109 3150 104 5000 109 9000 1 09 2900 110 3550 106 5900 109 9000 109 43150 112 4000 109 9300 110 10000 110 3550 114 4500 110 7100 912 11200 112 9000 114 12500 114 Standard boll lengths acc to ISO 4148 Arman dud b r Table A8 TAPER LOCK PULLEY quot ultoyo contoun to I 20 352193199991425 Dulgnod tor on with both Wedge narrow and V classical Vbetts 3Fn1ZE m 71 n N 0 Grooves A quot9 Dimensions in mitllrnetres y 7 7 m A A W E u lh tco mm 0m 2 L E V F c H 39Frk onJc Siquotz 80 g 8 3 9539 939 12 200 11 j SPA gt 118 5 1 8 g 11 1o 15 39 275 1375 g g see gt 190 g 9 3 14 125 19 350 1750 j J 59c gt 315 g 3 5 g 19 17 255 43 24 gij Page22 MA 3001 Machine Element Design Project Final Report Appendix B Table B1 Torque M Nm 3000 2000 7quot 1 O 00 800 quot 600 b 500 400 200 100 80 60 50 3O mammoo Number 2 of teeth 2 1O 20 3O 4O 50 60 70 80 90 100110 120 Table B2 Table 3 Number of pinion teeth to ensure no interference For a 20 fulldepth For a pinion meshing with a rack pinion meshing with a gear Minimum number Number of Maximum number Tooth form of teeth pinion teeth of gear teeth 145 involute fulldepth 32 1a In nite 20 invoiute fulldepth 18 17 1 309 25 involute fulldepth 12 16 101 15 45 14 26 13 i6 Page23 MA 3001 Machine Element Design Project Final Report Table B3 Tea TAPER Lock PULLEYS s 1 111 so 1 1000 20 0 10 2o 10 17 00 0 10 1 1010 42 1 10 20 11 02 1111 2 00 26 D 20 20 27 40 00 0 2 1010 3 3 20 77 39JI IA 7 0 0 3 I010 2 3 l0 7 10 96 a LS 56 1 006 3 0 3 9 39 00 0396 4 1010 42 2 02 77 27 20 12 2 1100 20 O 20 30 37 39 6 2012 60 3 04 I 37 32 L v 6 00 2 0 so I 22 n on 02 0 2012 60 3 l I 4 12 10 a 1 0 2 O 2 3 27 4 04 01 quot m w W quotquot 2 1 1010 42 1 10 20 0 02 10 63 1 I100 28 1 IO 22 0 00 09 2 1010 I 3 20 31 3 26 1393 2 1 100 20 1 20 17 0 22 03 0 201 2 00 1 4o 02 0 12 13 1 1100 20 1 40 17 10 22 01 4 2012 00 1 02 01 20 12 15 0 2012 00 1 04 01 12 12 1 a 1 1100 20 1 1o 2239 0 00 020 67 2 no 2 a u M o 23 o 0 2012 00 1 70 01 44 12 19 40 10 10 22 00 390 1100 20 3 1 8 1 1010 42 1 10 20 0 02 00 71 1 1100 20 1 10 22 o 00 02 2 1010 42 1 20 00 n L a 1100 20 1 20 42 0 22 04 1 201 2 00 1 40 00 0 12 10 1 1100 20 1 40 42 10 22 00 4 2012 00 1 02 011 20 12 1 0 2012 00 a 4 75 quot quot 2 39 39 quot 22 o 0 2017 00 1 0 3 3 quota 2 1210 32 1 2O 3 26 OJ 20 1 1210 12 1 4o 40 10 20 00 125 no a m 26 o 02 Lo 80 1 1210 12 1 10 200 100 70 00 2 0 3 3 26 00 a 20 14 2 1210 32 a 20 a 2 0 00 3 2012 DO 2 4o 00 12 0 10 1 1210 12 1 40 01 10 20 07 3 5 2 62 90 33 20 22 4 1210 12 a 02 01 27 2o 00 5 20 5 3 04 00 32 12 23 0 2017 00 1 70 00 a1 40 20 85 1 1210 12 1 10 20 0 01 00 4 2 1010 42 1 20 1 20 00 132 1 1010 42 1 10 211 39 11 02 11 1 1010 42 1 4o 00 10 25 00 2 1010 42 1 20 11 1 20 10 4 1010 42 3 62 00 27 26 00 3 2012 so 2 4o 1 1 1 a a cg a 1010 42 39 1 04 60 30 20 10 4 2012 00 2 02 1 11 12 20 20 90 1 1210 12 1 10 200 105 111 07 2 21 2 391 1 quot 2 1010 42 1 20 1 20 0 07 quot 39 2 2 2 3 5 5 quot 239 14 1 1010 42 1 10 20 11 02 12 5 39 2 3 52 27 2 39 39 39 39 2 1010 42 2 20 111 20 1 17 1010 42 1 64 01 39 25 3 1 2012 00 2 3940 111 2 0 20 95 I 1210 32 1 10 205 100 01 07 4 2012 00 2 02 111 12 20 20 2 103 2 3 2 3 25 o 039 5 25 M 2 64 quot 6 0 32 3 1010 2 3 0 0 6 25 09 C 2517 M 2 7 11 46 3 36 O 100 2 a 52 6 27 26 quotl o 3639 6 l m 1 276 5 270 0 a 3 3 3quot 2 quot3 15 1 1010 42 1 10 20 0 02 12 1 0 2 0 32 0 25 o 83 00 2 2 2 w 2 a 336 35 3 20 3 1010 42 3 2 71 3 25 39oo 3 2012 30 2 4O 12 32 ll 31 1 1010 42 1 4o 71 15 2s 11 4 2017 00 2 02 121 40 7 2 1010 2 1 52 71 27 20 11 6 2017 06 2 04 121 40 1o 6 2012 00 1 04 71 32 12 13 0 quot 7 3 n 239 quot 5 m 39 39 4 100 121 2711 411 270 01 30quot 50 1 70 71 44 12 14 0 2017 00 Pulioy dlmton given 070 In mllilmoton Table B4 Page24 MA 3001 Machine Element Design Project Final Report METRIC Bores39and Keyways mm 5 raw 0 o 3 o o s o o w m 7 o 5 8 7 7 o 5 8 7 7 333mm 3 3 3 3 3 3 m 13 m m 1 h m a o 4 4 31m 33333 33333 33333 33333 3333333 3333333 333333 33333343 433333343 34333 mmmmz w mam 11221 112231 12233 22333 2233333 22333344 3333444 333444554 334445565 4445 m h 82 6802582 02582 1 34568 34568 56 5 258 2468025 m 3 33333 333mm 333 333333 33331 333333 111133333 1133333 33333 b 5 55505 02625 026258 26202 62082 620 2 0 6208205 082 555 820555550 205555505 555550 11122 111222 11233 12334 123 4w5 1233455w334w567 345567890 4556789Hn 56789nn 789nm 91404 91504 1408 50850 408505 08508 850 0 508 0 1 08 00 o 1122 1122 1122 12234 122344 22344 234w m7 344 m7ww 44 78 mmwmwm mmwwm m 9 49 95 4952 952 952 5 52 5 5 5 1 11 11 8 8 84 84 84 84 o 1 1 3 1 12 12 12 12 1 1 11 PagelZS MA 3001 Machine Element Design Project Final Report Table B5 Shaft Material 39l39rrutmrnt nl raw 11111139139i11lr Dummy Bn39ncll I Mulmal l 39l 1 r1u1111zl l 39l39msilr 51111114111 5 Yield strength 3 I amquot mum 10111110011 mm hardness 0 W P MP P9 1319113811071 HB mumm in 5 cm or 2m 1m 111311161151quot 319 as F 207 l 30 i 25 I I J Wmquot 115513giggllyu 61 1 352 I 51 l 15 l 122 J 15275 39 7 113Iamquot 115 60 l 29039 l 43 l 33 l 121 J 1040quotquot junkyavm W252 0 1 490 l 71 l 12 l 160 U l m OU39ITWMP I 42 I 6 I 5quotquotquot1076quot quot 111r51105 Wit2 3 600 l 8 l 9 2 656 quotri61r111at 19390 90 333 l 4quot 5 80 tiMWEBiB yam 090 100 579 l 84 10 200 m 162 96 42 6 30 192 newmflmm wag135 I 9 W039 I 1 43 l 753 1 10 10 321 H 37quotquot nnIiiimimua 697w 38 I 331 48 15 176 I 7539011 3316 676 93 l 565 82 10 196 ninjaw QQT39LWQJ mgng l 37 l 414 60 23 174 llv3r39quot 0131400 1033 l 157 l 933 136 5 352 Table B6 Tensile or ultimate strength 3930 MP 1200 1400 600 800 1000 5 600 A 395 80 Polished v 500 a a i g 60 400 D g Machined 3 g 300 8 s 40 1 3 g 3 m 200 L5 20 100 0 18039 200 220 100 120 140 160 Tensile or ultimate strength 5 ksi Page26 MA 3001 Machine Element Design Project Final Report Table B7 Qesired39 reliability vs Reliability factor Reliability DCSiredfeliab ity 4 CR factor normal 050 1 00 distribution 090 090 099 081 0999 075 1 0 Table B8 Size factor C S O 0 00 so 1 100 125 150 175 200 225 25039 Shaft diameter mm 06 A 39 39 39 0 25 5390 75 Page27 Preferable basic sizes for machine parts and a compOnents I Dimension of Rectangular Keys with respect to the shaft diameter MA 3001 Machine Element Design Project Final Report Table B9 Nominal size 1 mm j First choice 39 Second quot Choice 39 First choice quot39 1 535 quot1439 60 16 18 8O 55f 55 20 100 22 120 Table B10 ISO Standard mm Imperial Standard inches Groove Key width height Sha diameter Groove Key width height Sha diameter W H gt s W H ooIA 14 12 18 18 12 34 316 316 34 1 14 14 12 17 1 1 14 516 14 17 22 1 14 1 12 38 14 2 3 10 12 4 5 6 8 22 30 1 12 134 716 516 303 38 10 1 34 2 12 516 38 44 h 12 2 2 12 58 716 OOOOOQONUiADJN 44 50 14 2 12 3 34 12 u I O p a O 50 58 39 3 3 12 78 58 H H 58 65 18 3 12 4 1 34 d N 65 75 20 1 14 78 PagelZB MA 3001 Machine Element Design Project Final Report Table B11 Bearing Bore 0016166 W1dih 1711161 Basic 3661c Fatigue Mass 111611 rumba diam etc diameter 19 mm radius1 dynamic static load kg speed damn D mm rmm load 1666 1116113 06111 ratings ratings P m 011 CkN chm lO tpm 6 00 10 26 3 03 475 196 0033 0019 40 600 30 9 39 06 54 236 010 0032 34 6300 35 11 06 352 340 0143 0053 32 5003 15 32 9 03 535 235 012 003 32 6202 35 11 06 306 375 016 0045 23 6302 12 13 1 1 19 540 0223 0032 24 6004 20 39 42 12 06 995 5 0212 0069 24 6206 a 14 1 135 655 023 011 20 6304 52 15 1 163 73 0335 014 19 5005 25 47 12 06 391 19 655 0275 0 03 20 6205 52 15 1 143 73 0335 013 13 630 62 17 1 234 116 049 023 16 6006 30 55 13 1 133 33 0335 012 17 6206 6392 16 1 203 11 2 0475 02 15 6306 72 19 1 296 16 067 035 13 6007 35 62 14 1 168 102 064 016 15 6207 72 17 1 27 153 0655 029 13 630 30 21 15 351 19 0315 046 12 6003 40 63 15 1 173 116 049 019 14 6203 30 13 1 325 19 03 037 1 1 6303 90 23 15 423 A 24 102 0 63 11 Page29

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