Calcul Reductor Winch

8/12/2019 Calcul Reductor Winch

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WINCH FORE

WIRE CAPACITY CALULATION OF WINCHDRUM Date: 06/06/14

Project/yardno:

Wire type:

INPUT:

Wire diameter (dw) = 40 mm Type:Drum diameter (D) = 406 mm 10.2 x dw

Drum length (L) = 500 mm 12.5 x dw

Extra space on drum (for stre = 100 mm 2.5 x dw

Pull 1st layer = 50.0 Ton (1) Ton (2)

Speed 1st layer = 10.0 m/min (1) m/min (2)

Hold.force 2nd layer = Ton rpm. speed 1: 7.14

Mom necesar toba= 111500 Nm

OUTPUT:

Layer Layer Store- ength Shield Pull Speed Pull Speed Holding Brake holding torq

diam. length n drm diameter (1) (1) (2) (2) force

wire Total Minimal

mm m m mm ton m/min ton m/min ton N*m

First 446 16 16 686 50.0 10.0 0.0

Second 515 19 35 755 43.3 11.6 0.0Third 585 21 56 825 38.1 13.1 0.0

Fourth 654 24 79 894 34.1 14.7 0.0

Fifth 723 26 106 963 30.8 16.2 0.0

Sixth 792 29 134 1032 28.1 17.8 0.0

Seventh 862 31 165 1102 25.9 19.3 0.0

Eighth 931 34 199 1171 24.0 20.9 0.0


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i= 151.22

h= 0.86

Q= 35 l/min 11.375 KW

Dp= 195.0 bar

Vg1= 19.6 cm3

hv= 0.95 n1= 1696 rpm N1ap= 11.22 rpm

hmh= 0.97 M1intrare= 59 Nm M1ap= 7677 Nm 15.72 m/min0.92 18.2 m/min

P= 10.49 Kw 20.6 m/min

23.0 m/min

25.5 m/min

27.9 m/min

30 m/min

33 m/min

With brake FL350

Mom fr. 89 Nm 89

V1


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e


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3.4 tons 34428 N

3.0 tons

2.6 tons

2.3 tons

2.1 tons

1.9 tons1.8 tons

1.6 tons

F1


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REDUCTION GEAR CALCULATION dwg.

1. Basic input parameters Pinion Wheel Pinion Wheel P

1.1 Transferred power P=

1.2 Rotational speed n2=n1/u n1(2)= 1696.4286 298.44577 298.44577 57.861934 57.

1.3 Torsional moment M1(2)=30000 P/(pn1(2)) M1(2)= 59.029728 335.5374 335.5374 1730.6666 173

1.4 Gear ratio (necessary) uneedful= 6.3759514 6.375951 5.3132928 5.313293 4

2. Options of material, loading conditions,operational and production parameters

Material Type

Normalized low carbon steels/ cast steels Wrought normalized low carbon steels

Cast steels

Cast iron materials Black malleable cast iron (perlitic structure)

Nodular cast iron (perlitic, bainitic, ferritic

Grey cast iron

Through-hardened wrought steels Carbon steels, alloy steels

Through-hardened cast steels Carbon steels, alloy steels

Case-hardened wrought steels

Flame or induction hardened wrought or cast steels

Nitrided wrought steels/ nitriding steels/ through-hardening steels, nitrided Nitriding steels

Through hardening steels

Wrought steels, nitrocarburized Through hardening steels

2.1 Material of the pinion

2.2 Treatment Pinion

2.3 Material of the wheel

2.4 Treatment Wheel

2.5 Tooth hardness -Side 52HRC 48HRC 52HRC 48HRC 5

2.6 Tooth hardness -Core HB= 240 220 260 240

2.7 Accuracy grade - ISO 1328

2.8 Coeffficient of one-off overloading Kas=

2.9 Nominal number of hours sevice hL=

2.10 Factor of safety from pittings SH=

2.11 Factor of safety from tooth breakage SF=

2.12 Application factor KA KA=

2.13 Load distribution factor Kg Kg=

3. Parameters of the cutting tool and tooth profile

St

GGG (perl., ba

GG

V

NV (nitr.

V (cast)

Step 1 Step 2

10.49 10.4866067

St (cast)

GTS (per

Abbreviati

1.4

Eh

IF

NT (nitr.)

1.2 1.2

NV (nitroca

1000 1000

7 7

1 1

1.1 1.1

1 1

1.4


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3.1 Basic rack tooth profiles for involute teeth of cylindrical gears according =>

3.2 Pressure angle a=

3.3 Addendum of tool ha0*= 1.25 1.25 1.25 1.25

3.4 Dedendum of tool hf0*= 1 1 1 1

3.5 Fillet radius of tool ra0*= 0.38 0.38 0.38 0.38

3.6 Root fillet radius of tool rf0*= 0.38 0.38 0.38 0.38

3.7 Chamfer of root cha*= 0 0 0 0

3.8 Chamfer of root chb*= 0 0 0 0

3.9 Protuberance hight d0*= 0 0 0 0

3.10 Unit head clearance anp*= 0 0 0 03.11 Addendum-Coefficient of the height of the tooth head ha*= 1 1 1 1

3.12 Unit head clearance c*= 0.25 0.25 0.25 0.25

4. Basic dimensions of gearing

4.1 Number of teeth Pinion z1= 19 19

4.2 Number of teeth Wheel z2= znec=121,1 108 znec=101 98 zn

4.3 Actual gear ratio u=z2/z1 u=

4.4 Module in normal section mn=

4.5 Addendum of basic rack of cylindrical gear haP=m ha* haP= 3 3.75 5 5

4.6 Dedendum of basic rack of cylindrical gear hfP=m (ha*+c*) hfP= 3.75 3.75 6.25 6.25

4.7 Normal pressure angle of the basic rack for cylindrical gear aPn= 20 20 20 20

4.8 Pressure angle in normal section an=4.9 Helix angle b=

4.10 Module in transverse section mt=mn/cos b mt=

4.11 Circular pitch p=p mn p=

4.9 Transverse circular pitch pt=p mt pt=

4.10 Base circular pitch ptb=pt cosat ptb=

4.11 Reference center distance a=[(z1+z2)/2]*[mn/cosb] a=

4.12 Production center distance av=

4.13 Working center distance aw=4.14 Pressure angle in transverse section at=arctg[tgan/cosb] at=

4.15 invat=tgat-at invat=

20 20

5

9.424777961 15.70796327

9.804591196

0

20 20

5.684210526 5.157894737

3

16

20.73857148 20

3.120898308 5

ISO/R 53-1974 ISO/R 53-1974

198.177 292.500

199.000 292.500

15.70796327

9.16931114 14.76065717

0.016681675 0.014904384


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4.16 Pressure angle at the pitch cylinder anw=

4.17 Transverse pressure angle at the pitch cylinder atw=arccos[(a/aw)*cosat] atw=

4.18 invatw=tgatw-atw invatw=

4.19 Base helix angle bb=arcsin(sinbcosan) bb=

4.20 bw=arctg[dw/d tgb] bw= 16.063022 16.063022 0 0

4.21 Addendum modification coefficient xS=[(invatw-invat)*(z2+z1)]/[2tgan] xS=

4.22 Sum of addendum modification coefficient x2=xS-x1 x1(2)= 0.2782384 0 0.25 -0.25

4.23 Pitch circle diameter d1(2)=mtz1(2) d1(2)= 59.29707 337.057 95 490

4.24 Work pitch diameter dw1(2)=2awz1(2)/[z2+z1] dw1(2)= 59.543307 338.45669 95 4904.25 Base circle diameter db1(2)=d1(2)cosat db1(2)= 55.454965 315.2177 89.270799 460.4493

4.26 Root circle diameter of gear wheel df1(2)=d1(2)-2mn(ha*+c*-x1(2)) df1(2)= 53.4665 329.557 85 475

4.27 Tooth depth without shortening href=[2ha*+c*]mn href=

4.28 Tooth depth shortened hsh=aw-0,5(df1+df2)-mnc* hsh= 6.7382424 6.7382424 11.25 11.25

4.29 Tooth shortening Dh=h-hsh Dh= 0.0117576 0.0117576 0 0

4.30 Tip diameter of gear wheel (without shortening of tooth) da ref1(2)=df1(2)+2href da ref1(2)= 66.966498 343.05702 107.5 497.5

4.31 Tip diameter of gear wheel (with shortening of tooth) da sh1(2)=df1(2)+2hsh da sh1(2)= 66.942983 343.0335 107.5 497.5

4.32 Tip diameter of gear wheel da1(2)= 66.94298 343.0335 107.5 497.5

4.33 Addendum ha1(2)=(da1(2)-d1(2))/2 ha= 3.8229575 2.9882424 6.25 3.75

4.34 Dedendum hf1(2)=(d1(2)-df1(2))/2 hf= 2.9152849 3.75 5 7.5

4.35 Width of Pinion/Wheel b1(2)= 56 52 64 60

4.36 Working face width bw=min(b1;b2) bw=

4.37 The ratio of the pinion width to its diameter yd=bw/d1(2) yd= 0.8769405 0.1542766 0.6315789 0.1224494.38 Face width ratio ya=bw/aw ya=

5. Chek dimensions of gearing

5.1 Pressure angle ax1(2)from the measuring point of thelength over teeth (on the cilinder of diameter dx1(2)=d1(2)+2x1(2)mn)

cosax1(2)=z1(2)cosat/[z1(2)+2x1(2)cosb] ax1(2)= 24.550232 20.738571 23.709215 19.176435.2 Theoretical number of measured teeth

Nc1(2)=(tgax1(2)/cos2bb-2x1(2)tgan/z1(2)-invat) z1(2)/p Nc1(2)= 2.7958935 13.379207 2.5079296 10.44163

5.3 Number of measured teeth N1(2)=INTEGER (Nc1(2)+0,5) N1(2)= 3 14 3 11

5.4 Base tangent length Wn1(2)=mn[p(N1(2)-0,5)+2 x1(2)tgan+z1(2)invat] cosan Wn1(2)= 23.605476 124.64023 39.08722 160.99455.5 Minimum face width needful for measuring bw nec=Wn1(2)sinbb bw nec= 6.1141581 32.283614 0 0

6. Supplement parameters of gearing

6.1 Virtual number of teeth of a helical gear zn1 2 =z1 2/[cos2bbcosb] zn1(2)= 21.187099 120.43193 19 98

6.2 Virtual reference diameter dn1 2 =d1 2/ cos2

bb dn1(2)= 63.561 361.296 95.000 490.0006.3 Virtual tip diameter dan1(2)=dn1(2)+da1(2)-d1(2) dan1(2)= 71.207 367.272 107.500 497.500

6.4 Virtual base diameter dbn1(2)=dn1(2)cosan dbn1(2)= 59.728 339.507 89.271 460.449

7. Qualitative indices of gearing

6.750 11.250

0.018276486 0.014904384

15.01158754 0

21.35559052 20

0.261306533 0.205128205

0.278238369 0

52 60


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7.1 Transverse contact ratio ea={[(da12-db1

2)1/2

+(da22-db2

2)1/2

]-2awsinatw}/[2pmtcosat] ea=

7.2 Overlap ratio eb=bwsinb/[pmn] eb=

7.3 Total contact ratio eg=ea+eb eg=

7.4 Virtual transverse contact ratio ean=ea/cos2bb ean=

7.5 Single pitch deviation acc. ISO 1328-1:1995 fpt= 12 14 13 16

7.6 Total cumulative pitch deviation acc. ISO 1328-1:1995 Fp= 38 65 39 66

7.7 Total profile deviation acc. ISO 1328-1:1995 Fa= 16 21 19 24

7.8 Total helix deviation acc. ISO 1328-1:1996 Fb= 20 22 20 22

Profile form deviation, acc. ISO 1328-1:1996 f fa= 12 16 15 18Profile slope deviation, acc. ISO 1328-1:1997 fHa= 10 13 12 15

Helix form deviation, acc. ISO 1328-1:1996 f fb= 14 16 14 16

Helix slope deviation, acc. ISO 1328-1:1997 f Hb= 14 16 14 16

7.6 Limit deviation of axis parallelity f x=Fb2 fx=

7.7 Limit deviation of axis parallelity f y=0,5 Fb2 fy=

7.9 Base pitch deviation of pinion, wheel f pb=fptcos at fpb= 11 13 12 15

7.10 Efficiency of the gearing ha=1-[pmaea/(fcosb)][1/z1+1/z2] ma= f= ha=

8. Force conditions ( forces acting on the toothing)

8.1 Torsional moment M1(2)=30000 P/(pn1(2)) M1(2)= 59.029728 335.5374 335.5374 1730.6666

8.2 Maximum torque Mmax1(2)=M1(2)Kas Mmax1(2)= 59.029728 335.5374 335.5374 1730.6666

8.3 Nominal transverse force Ft=M12000/d1 Ft=

8.4 Nominal axial force Fa=Fttgbw Fa=

8.5 Nominal radial force Fr=Fttgan/cosbw Fr=8.6 Peripheral speed on the pitch diameter v1=pd1n1/ 60000 v=

8.7 Number of cycles NHE1(2)=60hLn1(2) NHE1(2)= 101785714 17906746 17906746 3471716.1

9. Parameters of the chosen material

9.1 Density of pinion, wheel materials r1,2= 7850 7850 7850 7850

9.2 Young's modulus of elasticity E1(2)= 206000 206000 206000 206000

9.3 Poisson's ratio n1(2)= 0.3 0.3 0.3 0.3

9.4 Endurance limit for Hertzian contact stress sHlim b1(2)= 1181.5 1139 1181.5 1139

9.5 Endurance limit for bending stress sFE1(2)= 700 700 700 700

9.6 Static number of load cycles in contact NHst= 100000 100000 100000 100000

9.7 Base number of load cycles in contact NHB= 5.00E+07 5.00E+07 5.00E+07 5.00E+07

9.8 Wohler curve exponent for contact qH= 10 10 10 10

9.9 Static number of load cycles in bending NFst= 1000 1000 1000 1000

9.10 Base number of load cycles in bending NFB= 3.00E+06 3.00E+06 3.00E+06 3.00E+069.11 Wohler curve exponent for bending qF= 6 6 6 6

9.12 Nominal kinematic viscosity of the oil at 40 n40=

1.520184625 1.632867967

1.629505638 1.632867967

3.040978277 1.632867967

1.520793653 0

0.1 2 0.984625502 0.983883263

22 22

11 11

1990.983041 7063.945316

573.2759625 0

778.4780603 2571.0658325.267049735 1.484525464

150 150


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10. Coeficient for safety calculation

10.1 Mesh stiffness, cga cga=c'(0,75ea+0,25) cga=

10.1 Mesh stiffness, cgb cgb=0,85cga cgb=

10.2 Stiffness of a tooth pair c '=c'thCMCRCBcosb c'=

10.3 Theoretical stiffness of a tooth pair c'th=1/q' c'th=

10.4 Minimum value for the flexibility of a pair of teeth q'=0,04723+0,15551/zn1+0,25791/zn2 -

-0,00635xn1-0,11654xn1/zn1-0,00193xn2-0,24188xn2/zn2+0,00529xn12+0,00182xn2

2 q'=

10.5 Correction factor CM=

10.6 Gear blank factor CR=1+ln(bs/b)/[5e(sR/(5mn))] CR= 0.9431119 0.929415

Web thickness bs= 56 24 64 30 The real value for bs/b bs/b= 1 0.4615385 1 0.5 The adopted value for bs/b

If bs/b1,2 use 1,2 for bs/b bs/b= 1 0.4615385 1 0.5

The internal diameter of rim di1,2= 0 299.55702 0 441.25 Rim thickness SR1(2)=(df1(2)-di1(2))/2 SR1(2)= 26.733249 15 42.5 16.875 The real value for SR/mn SR/mn= 8.911083 5 8.5 3.375 The adopted value for SR/mn If sR/mn


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Cv5=0,47 Cv5= Cv6=0,47 for eg2 and Cv6=0,12/[eg-1,74] for eg>2 Cv6=

Cv7=0,75 for 1


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Material & treatment Relation Restrictions

-for St, St(cast), V, -for v5 m/s no restriction

V(cast), GTS(perl.) Y b=320 Fbx/sHlim -for 5 m/s10 m/s

ybmax=12800/sHlim

-for Eh, IF, NT(nitr.) for all velocities but with

and NV(nitrocar) Y b=0,15 Fbx the restriction

ybmax=6 Yb1(2)= 0.8483148 0.8483148 0.8854298 0.885429

10.11 Face load factor (root stress) KF KF =POWER{KH ;(b/h)2/[1+b/h+(b/h)2]}where b/h=min(b1/h1;b2/h2) KF=

10.12 Transverse load factor (contact stress) KHKHa=(eg/2)[0,9+0,4 cga(fpb-ya) b/(FtKAKvKHb)] for eg2 1

KHa=0,9+0,4[2(eg-1)/eg]1/2

cga(fpb-ya) b/(FtKAKvKHb) for eg>2 temporar 2.1624171 1.280378

when KHaeg/(eaZe2), use KHa=eg/(eaZe

2) KH=

10.13 Transverse load factor (root stress) KFKFa=KHa if KFaeg/(0,25ea+0,75) KFa=eg/(0,25ea+0,75) KF=

10.14 Single pair mesh factor for pinion If eb=0 ZB=max{M1;1}

If 0


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Determination of factor CZV for sHlimCZV=0,85

for 850sHlim1200[N/mm2] => CZV=0,85+0,08 (sHlim-850)/350

for sHlim>1200[N/mm2] => CZV=0,93 CZV=

10.23 Roughness factor ZR=[3 / RZ10]CZR

ZR=

RZ10=RZ[10/rred]1/3

RZ10=

Teeth roughness R Z=0,5 (RZ1+RZ2) RZ=

Teeth roughness R Z1(2)= 6.3 6.3 12.5 12.5

Relative radius of curvature rred=r1r2/(r1+r2) rred=

Radius of curvature r1(2)=0,5 db1(2)tgatw r1(2)= 10.841497 61.625352 16.245957 83.7949 Determination of factor CZR for sHlimCZR=0,15

for 850sHlim1200[N/mm2] => CZR=0,32-sHlim/5000

for sHlim>1200[N/mm2] => CZR=0,08 CZR=

10.24 Hardness ratio factor care duritate side sau core?for HB 130 =>ZW=1,2for 130ZW=1 ZW=10.25 Size factor ZX=

10.26 Tooth form factor YFa=[6(hF/mn)cosaFen]/[(sFn/mn)2cosan] YFa1(2)= 1.2236289 1.3033323 1.2696992 1.39601

ean=ea/cos2bb ean=

den1(2)=(2zn1(2)/z1(2)){{[(dan1(2)/2)2-(dbn1(2)/2)

2]1/2

-[(pd1(2)cosbcosan)/z1(2)](ean-1)}2+(dbn1(2)/2)

2}

1/2 den1(2)= 65.804466 363.16562 98.322919 490.729

Pressure angle at the highest point of single tooth contact

aen1(2)

=arccos(dbn1(2)

/den1(2)

) aen1(2)

= 24.816042 20.795358 24.778502 20.2328

ge1(2)=[(1/zn1(2))(p/2+2x1(2)tgan)+invan-invaen1(2)](180/p) ge1(2)= 3.9717588 0.6373131 4.4698072 0.7807 Angle for application of load at the highest point of single tooth contact

aFen1(2)=aen1(2)-ge1(2) aFen1(2)= 20.8443 20.1580 20.3087 19.452

Tip radius of tool ra0=mnra0* ra0= 1.14 1.14 1.9 1.9

Basic rack addendum of tool ha0=mnha0* ha0= 3.75 3.75 6.25 6.25

Determination of factor G G=ra0/mn-ha0/mn+x1(2) G1(2)= -0.591762 -0.87 -0.62 -1.12

Protuberance of tool d0=mnd0* d0= 0 0 0 0

Material allowances for finish machining q= 0 0 0 0

Residual undercut left by protuberance Spr=d0-q Spr= 0 0 0 0

Determination of factor E E=(p/4)mn-ha0tgan+Spr/cosan-(1-sinan)ra0/cosan E= 0.1930695 0.1930695 0.3217825 0.32178

Determination of factor H H=(2/zn)(p/2-E/mn)-p/3 H1(2)= -0.904994 -1.02218 -0.888625 -1.0164

Determination of factor n n=(2G/zn)tgn-H n1(2)= 0.8423755 0.999694 0.8188435 0.98221

hF=(mn/2)[(cosge-singetgaFen)(den/mn)-zncos(p/3-n)-G/cosn+ra0/mn] hF1(2)= 2.7425672 3.3701871 4.5462857 5.67184 sFn=mnznsin(p/3-n)+3

1/2(G/cosn-rao/mn) sFn1(2)= 6.3342997 6.8189379 10.354024 11.059

rF=mn{ra0/mn+2G2/[cosn (zncos

2n-2G)]} rF1(2)= 1.4385341 1.3674874 2.4569082 2.59635

10.27 Stress concentration factor YS1(2)=(1,2+0,13L1(2))qs1(2)1/[1,21+2,3/L1(2)]

YS1(2)= 2.1455901 2.1593481 2.0929827 1.99438

L1(2)=sFn1(2)/hF1(2) L1(2)= 2.3096242 2.0233113 2.2774689 1.94983

0.916057141 0.916057141

6.47297781 11.28014919

0.931551307

1 1

1 1

1.629505638 1.632867967

0.885048662

0.092200002 0.092200002

9.219540866 13.60772451

6.3 12.5


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GL STAS

kW]

min-]

Nm]

150

HV= 545 484.2857 545 484.2857 545 484

12.5

1

h] 1 GL 1181.5 1139 1181.5 1139 1182 1139

2 ISO-ML 1005.3 960.37142 1005.3 960.3714 1005 960

3 ISO-MQ 1176.845 1143.9986 1176.845 1143.999 1177 ###

4 ISO-ME 1288.225 1257.5643 1288.225 1257.564 1288 ###

1

1 B

2 D


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17/41

]

]

]

]

mm]

mm]

mm]

mm]

mm]

mm]

mm]

mm]

mm]

mm]

mm]

mm]

mm]

mm]

]

mm]

mm]

mm]

mm]

mm]


18/41

mm]

mm]

mm]

mm]

mm]mm]

mm]

mm]

mm]

mm]

mm]

Nm]

Nm]

N]

N]

N]m/s]

kg/m ]

N/mm ]

N/mm ]

N/mm ]

cycles]

cycles] 1159

cycles]

cycles]

mm /s]


19/41

N/mm-mm] 1-80 c '=0,8 cosbCBSCR/q'

q'=(0,04723+0,15551/zn1+0,25791/zn2 -0,00635xn1-0,11654xn1/zn1-0,00193xn2-0,24188xn2/zn2+0,00

mm]

mm] 299.557 441.25 618

kg/mm] 1-30

mm] 1-311-32

r.p.m.] 1-6

1-9

alege

1-13

1-14

tb4/pg27

tb4/pg27

tb4/pg27

tb4/pg27


20/41

tb4/pg27

tb4/pg27

tb4/pg27

1-15

mm] 1-18

mm] 1-78

1-75

1-77mm intra si la k ha temporar

1-16

mm] 1-19

mm]

mm]

1-17

mm]

mm]mm] tb4/pg27

7 pg39

1-39 1.845703

1-40

N] 0.8516549

mm] 1-43

mm] 1-52 0.0714945

mm] 1-56 8 500

mm-mm/N] 100 110

mm] -0.48

mm] 1-50 1.075167 -17.9229 18.2229 19.59266


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1-44

1-48mm]

1-69

1-70

1-71

1-72

1-73

1-74

2-17

2-18

2-16

2-19 300

2-25 3E+09

2-26 11.299416 11.29942 10.33699 10.3

2-36 0.2388668 0.238867 0.261106 0.26

0.0885001 0.0885 0.09674 0.1

1.3491032 1.57338 1.641193 1.92

2-37

2-39

2-38

2-40

2-42


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2-48

2-45

mm] 2-44

mm]

mm] 2-46

mm] 2-47

2-50

2-49

2-51 RZH= 7.9959346 21.19029

HB~HV~U/3,6 unalloyed steel

HB~HV~U/34 alloyed steel

]

]

]

mm]

mm]

mm]

mm]

mm]

mm]


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intra la khalfa

1.2990465

1.2990465

0.635714

#### ### # #

#### ### # #

#### ### # #

#### ### # #


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strunjire Rmax= 40-100 strunjire grosolana

10-40 strunjire mijlocie

2,5-10 strunjire fina

R1max= 100R2max= 100

Strangerea maxima si minima a ajustajului ales

ametru 400 arbore 0.471 0.435 Ajustaje recomandate

etare alezaj 0.057 0 -ajustaje cu strangeri mari H6/s5 H7/s6 H8/s

7/u6 -ajustaje cu strangeri foarte mari H6/t5 H7/t6

Smax= 0.471 BUN -ajustaje cu strangeri extrem de mari H6/u5 H7/u6 H8/u

Smin= 0.378

Presiunile critice de contact

pcr1= 38.672 [N/mm]

pcr2= 79.986 [N/mm]

OL52 sc1= 330[N/mm]34Cr Mo4 sc2= 550[N/mm]

Strangerile critice

Scr1= 1.1828571

Scr2= 2.1901385 BUN

strangere extrem de mare

2d

21d2d

c1

2

1cr1

p

=

22

d

2d22

d

c2

2

1cr2

p

=

nSpcr1p

Scr1

S =

nSpcr2

pS

cr2S =


27/41

Incarcare numai cu moment de torsiune 0.04 686 27.44 610.12

4 0.08 686 54.88 555.24

ate: Momentul necesar de transmis Mt= 35706.385 [Nm]

Diametrul exterior al coroanei d2= 665 [mm] 15.75 35.438 594.13 47.5 coroa

Lungimea suprafetei de fretare l= 80 [mm] 39.375 586.25 30 obad

Diametrul de fretare d= 570 [mm]

Diametrul interior al obezii d1= 510 [mm]

Coeficientul de frecare m= 0.14Modulul de elasticitate

- pentru coroana E1= 2200000 [daN/cm2]

- pentru obada E2= 2200000 [daN/cm2]

Coeficientul Poisson al materialului

- pentru coroana n1= 0.3

- pentru obada n2= 0.3

Presiunea de strangere necesara

p= 6.2468 [N/mm2]

Strangerea necesara

S= 0.2519 [mm]

K1= 8.7278

K2= 6.8385

Strangerea corectata

Sc= 0.4919

Sn= 0.24

l2d

tM2

p

m410d2

E2

K

1E1

KpS =

22d22

d

2d22

d

2K n

=

121d2d

21d2d

1K n

=

26

26

26

/101,11

/106,12,1

/102,21,2

cmdaNbronz

cmdaNfonta

cmdaNotel

=

=

=

nSScS =

=2max

R1max

R1,2nS


28/41

strunjire Rmax= 40-100 strunjire grosolana

10-40 strunjire mijlocie

2,5-10 strunjire fina

R1max= 100R2max= 100

Strangerea maxima si minima a ajustajului ales

ametru 570 arbore 0.704 0.660 Ajustaje recomandate

etare alezaj 0.070 0 -ajustaje cu strangeri mari H6/s5 H7/s6 H8/s

7/u6 -ajustaje cu strangeri foarte mari H6/t5 H7/t6

Smax= 0.704 BUN -ajustaje cu strangeri extrem de mari H6/u5 H7/u6 H8/u

Smin= 0.590

Presiunile critice de contact

pcr1= 32.909 [N/mm]

pcr2= 72.959 [N/mm]

OL52 sc1= 330[N/mm]34Cr Mo4 sc2= 550[N/mm]

Strangerile critice

Scr1= 1.5672267

Scr2= 3.1824957 BUN

strangere extrem de mare

2d

21d2d

c1

2

1cr1

p

=

22

d

2d22

d

c2

2

1cr2

p

=

nSpcr1p

Scr1

S =

nSpcr2

pS

cr2S =


29/41

2 C45

s= 340 [N/mm2]

taf= 129.2 [N/mm2]

z= 6 nr stifturi

l= 20 lungime stiftdsitft= 8 mm

2*Mt/dfre*dstift*l*z

tf= 4.3013 BUN

M= 735 Nm

Dia= 356 mm

3C45

s= 340 [N/mm2]

taf= 129.2 [N/mm2]

z= 6 nr stifturi

l= 20 lungime stift

dsitft= 8 mm

2*Mt/dfre*dstift*l*z

tf= 17.563 BUN

M= 3920 Nm

Dia= 465 mm


30/41

GL

Diametru interior arbore 0 [mm] 1

Diametru exterior arbore 85 [mm]

Puterea transmisa 10.49 [kW]

Turatia 11.21813 [r.p.m.]

Coeficient F 100 DIAMETRUL MINIMRupere material 750 [N/mm

2] 95.64264

Factor de material Cw 0.6154

Coeficient k (1,1-la pinion; 1,15 arb) 1.15

GL

Diametru interior arbore 0 [mm] 1

Diametru exterior arbore 85 [mm]

Puterea transmisa 10.48661 [kW]

Turatia 11.21813 [r.p.m.]Coeficient F 100 DIAMETRUL MINIM

Rupere material 750 [N/mm2] 614125.00 874892.4

Factor de material Cw 0.6154

Coeficient k (1,1-la pinion; 1,15 arb) 1.15


31/41


32/41

Ft2p= 7063.9 N

roata R2a= 1884.4 N

pinion R2b= 5185.5 N

roata Mi2a= 98.0 Nxm

pinion Mi2b= 342.2 Nxm

roata Mred2a= 589.4 Nxm

pinion Mred2b= 674.5 Nxm

TREAPTA 2 Pinion Mt21= 335.5 Nxm

n21= 298.4 rot/min

Roata Mt22= 1730.7 Nxm

n22= 57.9 rot/min

carcasa a2= 79.5 mm

r - p c2= 92.5 mm

carcasa b2= 68 mm

roata Fr3r= 2571.1 N ar3=

Ft3r= -7063.9 N

arborele 3 pinion Fr3p= 9472.3 N ap3=

Ft3p= 26025.1 N

pinion R3a= 19007.2 N

roata R3b= 11417.2 N

pinion Mi3a= 1511.1 Nxm

roata Mi3b= 776.4 Nxm

pinion Mred3a= 3356.9 Nxm

roata Mred3b= 3096.5 Nxm

TREAPTA 3 Pinion Mt31= 1730.7 Nxm

n31= 57.9 rot/min

Roata Mt32= 8926.6 Nxm

n32= 11.2 rot/min

arborele 4 (A.P.) motor a4= 75 mm

carcasa b4= 155 mm


33/41

roata Fr4r= 9472.3 N ar4=

Ft4r= 26025.06 N

R4a= 18664.2 N

R4b= 9031.1 N

Mi4= 1399.8 Nxm

Mred4= 15524.6 Nxm

F1p= 27695.3 N


34/41

(8


35/41

Sinap2= 0.77

V2r= -1876.1 N H2r= 1024.8 N

V2P= 6510.2 N H2P= 3758.6 N

V2a= 357.9 N H2a= 1850.1 N

V2b= 4276.1 N H2b= 2933.3 N

C45 +QT sai= 111 N/mm2

tat= 66.6 N/mm

Teoretic d12min= 40 mm

Predimensionare Registru d12min= #REF! mm


tat= 66.6N/mm



50 o Cosar3= 0.64

Sinar3= 0.77

-10 o Cosap3= 0.98

Sinap3= -0.17

V3r= -2571.1 N H3r= -7063.9 N

V3P= 23984.8 N H3P= -13847.6 N

V3a= 15311.4 N H3a= -11262.1 N

V3b= 6102.4 N H3b= -9649.5 N


tat= 66.6 N/mm



42CrMo4 sai= 165 N/mm2

tat= 99N/mm




36/41

-10 o Cosar4= 0.98

Sinar4= -0.17

V4r= 23984.8 N H4r= -13847.6 N

V4a= 16163.7 N H4a= -9332.1 N

V4b= 7821.1 N H4b= -4515.5 N


37/41

(60


38/41

D3pana= 67 mm

Pana b= 20 mm

h= 12 mm

l= 60 mm

Pc2= 143.5 N/mm2 Pca2= 129.5 N/mm

2

t2= 43.1 N/mm2 ta2= 129.5 N/mm2

D4pana= 112 mm

Panab= 32 mmh= 18 mm

l= 88 mm

Pc2= 201.3 N/mm2 Pca2= 129.5 N/mm

2

t2= 56.6 N/mm2 ta2= 129.5 N/mm2


39/41

Aw Abatere X Abatere Y Abatere alfa x=270.000 266.000 46.303 52.914

270.100 0.100 266.090 0.090 46.369 0.066 0.923524 0.060301 0.06

269.900 -0.100 265.910 -0.090 46.237 -0.066

232.000 150.000 176.986 30.631

232.090 0.090 150.050 0.050 177.061 0.076 0.534612 0.077442 0.08

231.910 -0.090 149.950 -0.050 176.910 -0.076

199.000 128.000 152.371 9.184

199.090 0.090 128.050 0.050 152.447 0.076 0.160291 0.088846 0.09

198.910 -0.090 127.950 -0.050 152.296 -0.076

258.000 203.000 159.233 38.111

258.100 0.100 203.080 0.080 159.293 0.060 0.665162 0.078682 0.08

257.900 -0.100 202.920 -0.080 159.172 -0.060

191.647 21.432 190.445 83.579

191.737 0.090 21.442 0.010 190.534 0.089 1.458729 0.010065 0.01

191.557 -0.090 21.422 -0.010 190.355 -0.089


40/41

Coeficientul de siguranta c= 2.5

Arbore principal CUPLAJ 1.75

Momentul de transmis M= xxxx [Nm]

Diametrul arborelui D= xxxx [mm]

Latimea penei b= xxxx [mm]Inaltimea penei h= xxxx [mm]

Rezistenta materialului s= 340 [N/mm2]

Presiunea admisibila Pa= 323 [N/mm2]

taf= 129.2 [N/mm2]

Lungime pana (strivire) l> #VALUE! [mm] #####

(forfecare) l> #VALUE! [mm]


Arbore principal ROATA

Momentul de transmis M= 8926.60 [Nm]

Diametrul arborelui D= 110 [mm]

Latimea penei b= 28 [mm]

Inaltimea penei h= 16 [mm]

Rezistenta materialului s= 340 [N/mm2]

Presiunea admisibila Pa= 323 [N/mm2]

taf= 129.2 [N/mm2]

Lungime pana (strivire) l> 157.026 [mm] 78.51 80(forfecare) l> 112.161 [mm]


Arbore 2

Momentul de transmis M= 1730.67 [Nm]

Diametrul arborelui D= 102 [mm]

Latimea penei b= 28 [mm]

Inaltimea penei h= 16 [mm]

Rezistenta materialului s= 340 [N/mm2]Presiunea admisibila Pa= 323 [N/mm2]

taf= 129.2 [N/mm2]

Lungime pana (strivire) l> 32.8315 [mm] 16.42 35

(forfecare) l> 23.4511 [mm]



41/41

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