Hoist Design Procedure for EOT crane…

THE DESIGN

We are concerned with the design of the hoisting arrangement of 2 tonne capacity of EOT crane ,which will lift the load up to a distance of 8 meters.
1.DESIGN OF HOOK


Selection of section : The section is trapezoidal
Selection of material : Mild steel
Load to lift : 2 tonne
Considering 50 % over loading.
So the design load = 2 tonne+50% of 2 tonne = 3tonne
Taking the help of (IS 3815-1969) for selection of material for 8 dimensions of crane hook.In IS 3815-1969 the nearest selection for 3.3 tonne is 3.2 tonne.
For load 3.2, proof load (P) is 6.4 tonne.
So C = 26.73√P = 26.73 x √6.4
= 67.62
≈ 68 mm
A = 2.75 C = 2.75 x 68 ≈ 187 mm
B = 1.31 C = 1.31 x 68 ≈ 89mm
D = 1.44 x C = 1.44 x 68 ≈ 98mm
E = 1.25C = 1.25 x 68 ≈ 85mm
F = C = 68mm
G = 35mm
G1 = M33, Pitch = 6mm (Coarse series)
H = 0.93 x C = 0.93 x 68 ≈ 63mm
J = 0.75 x C = 0.75 x 68 ≈ 51mm
K = 0.92 x C = 63mm
L = 0.7 x C = 0.7 x 68 ≈ 48mm
M = 0.6 x C = 0.6 x 68 ≈ 41mm
N = 1.2 x C = 82mm
P = 0.5 x C = 34mm ≈ 34mm
R = 0.5 x C = 0.5 x 68 ≈
U = 0.33 x C = 0.3 x 68≈20 mm
Checking for strength Area of the section = ½ x 63 x (41+8) = 1543.5 mm2
Centroid from ‘a’
= (.05 x 8 x 65) 63/3+(.5 x 41 x 63) x (2 x 63)/3
½ x 68 x (41+8)
= 38.571mm
= 38.6 mm= h2
So centroid from b = 63-38.6=24.4mm =h1
0 = 34 +24.4 = 58.4mm
r0 = A/(dA/u)
dA/u = [b2+r2/h (b1-b2)] ln r2/r1 – (b1-b2)
=28.65mm
r0 = A/(dA/u) = 1543.5 = 53.87  53.9 mm.
28.65
e= 0-r0 = 58.4 – 53.9 = 4.5mm

Moment
M = -P x 0
= -3 x 58.4
= – 175.2 (tonne x mm)
Stress due to bending is given by
b = M X 4
Ae r0-y
For point a
Y = -(e+h2)
= -(4.5+38.6)
= – 43.1 mm
For point b
Y = r0-r1
= 53.9 – 3.4
= 19.9 mm
Stress due to direct loading = P/A
= 3/1543.5
= 1.9436 x 10-3 Tonne/mm3
Stress due to curvature of ‘a’
ba = – (-175.2) x -43.1
1543.5 x 4.5 {53.99 – (-43.1)}
= 0.0112
So total tress at a
= – 0.0112 + 1.9436 x 10-3
= – 9.2642 x 10-3 Tonne/mm2
= – 9.2642 kg/mm2  -90.85 Mp
Stress due to curvature at b
bb = -(-175.2) x . 19.99 .
1543.5x 4.5 (53.9 – 19.9)
= 0.014763
So total stress at b
=bb + 1.9436 x10-3
=0.014763 + 1.9436 x 10-3
=0.0167 tonne/mm2
= 16.7 Kg/mm2  163.84 MPa
Let the material be class 4 carbon steel ( 55C 8)
Ultimate tensil strength I 710MPa
Design strength = Ultimate tensil strength
Factor of safety
 = 710/4
 = 177.5 MPa
163.84 > 177.5
So design is safe
Determination of length of threaded portion
Pitch = 6mm
Nominal dia of thread = 33 mm (G1) = d
Considering the screw and thread are of single safest & square mean diameter of screw =
dm = d- (p/2)
= 33 – (6/2)
= 30
tan  = 1/dm = 6/( x 30)
tan  = tan-1 { 6/( x 30)} = 3.640
Let the co-efficient of fraction be 0.15
So  = tan  = 0.15
= 8.530
Torque required to resist the load

T = W x dm* tan ( + )
2
Where w is the weight of load is 3 tonne and the load of the hook itself.
The maximum weight of the hook is 50kg (from the use of the soft ware ‘Pro-Engineer’)
So
T = 3050x 30 x tan (3.61+ 8.53)
2
=9866.42 Kgmm

Stress induced in the screw
Direct tensible stress (allowable or design)
 =4w/ d02
d0 = core diameter of the screw.
dc = d-p = 33-6 = 27 mm
1 = 4x 3050
 272
= 5.326 kg/mm2  52.24MR

Torssional shear stress
 = 16T = 16×9866.42
 de3  x 273
= 2.5529 Kg/mm2 = 25MP

Maximum shear stress in the screw
max = ½  (2 + 4 2)
= ½ √ (52.242 + 4 x 252)
= max = 36.15Mpa

Height of the nut

a)Considering bearing action between the thread in engagement.
Let ‘n’ is no of thread in engagement with screw.
Considering bearing action between nut & screw.
Let the permissible bearing pressure =pi= 6 MR.
We know
Pi = 4W
 (d2-dc2) x n
So 6 = 4×3050 x 9.8
(332-272) x n

N = 4 x 3050 x 9.8
(332-272) x 6
 1.27 x 9.8
 12.5
So the height of the nut is = 2 x 12.5 = 25mm.
b) Considering shear failure of thread across root
Shear stress induced
 = . W .
dc(0.5xP) xn

= . 3050 x 9.8 .
 x 27 x (0.5 x 6) x n

= 117.46
n
= 0.5 x 177.5 = 117.46
n n
= 117.46
177.5 x0.5
= 1.32 = 2
So height is n x p = 2 x 6 =12mm
Tacking the highest value 25mm

Design of pin which will carry the dead load & the load of hook.
We have to determine the dimension of ‘t’.
n = M x Y
I
= M x (24)
I 2
Where “I” is moment of inertial about bh3 t x 243 x 2
12 12
Maximum bending moment for = M = ¼ x W x L
Let L = 70 mm
So M = ¼ x 3050 x 70 = 2 x 26687.5 Kgmm.
= 2 x 261.715 x 103 N-mm
 = 2x 261.715 x 103 x 24
1 t x 243 2
177.5 = 1363 x 2
t
t = 1363 x 2 = 7.8 x 2  15.2 MM
177.5
 16 mm
Taking 20 m for additional safety
Diameter of the projected portion

The projected position is undergo only shearing failure.
Design shear stress  = 0.5 x design tensive stress.
Force action on each side i.e. projected portion is
3050/2 =1525 kg  14.95 x 103
 15 KN
So the minimum value of the height of the projected portion is 15mm, taking n= 40mm for screwing arrangement.
 = 15 x 103
/4 x dk2
= 177.5 x 0.5 = 15 x 103
(/4) dk2
= dk2 = 15 x 103 x 4
177.5 x 0.5 x 
= dk2 = 15 x 103 x 4
177.5 x 0.5 x 
= 215.19
= 14.66
 15mm
Taking 20 mm for additional safety purpose.
So that it can be turned to thread in size ‘m20’.
Height of the projected portion
P * x * dk = w/2
Where p = bearing pressure or crushing stress.
Let p = 210 MPx
Allow crushing stress =210/4 =
210/4 x x x 20 = 3050 x 9.8
2
x = 3050 x 9.8 x 5
2 x 20 x 210
= 3.56 mm x 4
= 14.024 =15 mm
So the minimum value of the height of the projected portion is 15 mm, taking x = 40 mm for
screwing arrangement.

Design of link and the cover plate

coverplate

coverplate


Thickness of link and cover plate should not be minimum.

Let the material be (55C8).
a)Hole fopr placing the pin which will carry the hook will be ‘dk’ i.e. 20 mm.
zchecking for the failure of link & cover plate combindely(as they are of same material and undergone same condition of failure).

Mode of failure
Tearing of cover plate & link at the edge.
Crushing of cover plate and link.
Breaking at the lowest cross section.
i).Considering tearing of cover plate & link at the edge

Experiments from the riveted joints have shown that if the distance between the centre of rivet
and the edge is 1.5 times the diameter of the rivet.The element will not undergo the failure of tearing at the edge.
The same condition is also applicable in our case.
But for more safety reasons taking the distance between the centre of the projected element and the edge of the cover plate & linkis 2 times the dia of the projected element.
So Z = 2 x dk
= 2 x 20 = 40 mm
Considering tensile failure at the lower cross section
So σd = w/2
A
177.5 = 3050 x 9.8/2
2 x x x 30

x = 3050 x 9.8/2
2 x 30 x 177.5

= 28/2 mm ≈ 1.4 mm

Considering crushing failure
Force = σcrushing(d) x projected area
3050 x 9.8 = σcrushing(d) x (20 x x)
FOS
= 3050 x 9.8 x 4 = 14.24 mm ≈ 15 mm
2 x 210 x 20
So taking maximum of x i.e 15 mm, So x = 15 mm

cover-plate-auto-cad

cover-plate-auto-cad


AutoCAD drawing Of Cover plate

auto_link Auto CAD

auto_link Auto CAD

AutoCAD Drawing Of Link

Design of shaft carrying the pulley

shaft to carry pully

shaft to carry pully

Pulley

Pulley


The weight of each cover plate is 2.5 kg.
Weights of each link weigh 2 kg.
So weight of 2 covers plate & 2 link
Is 2 x 2.5 + 2 x 2 = 9 kg.
So the total weight which the shafts carry is 3050 + 9 = 3059 ≈ 3060
Each Side subjected to a load of 3060/2 = 1530 kg.
The shaft is only subjected to
Crushing failure (at the cover plate and link).
Shear failure.
Crushing failure (at the pulley)
Considering shear failure
 = f/a
 = allowable shear stress
= 0.5 x 177.5 = 0 .5 x 177.5 = 22.2 MR
FOS 4
Stress induced = 1530 x 9.8 = 150042
π/4 x 302 π/4 x 302
= 21.22 MPa
As induced stress is less than that allowable stress, the design is safe

Considering crushing failure at the cover plate
Crushing stress = Force/Protected area
Allowable stress = 240/4 = 60MPa

Induced Crushing stress = Force
Projected area
= 3060 x 9.8
70 x 40
As allowable induced stress 60.86 KN. The selection is feasible.

Design of Sheave

sheave

sheave

a = 40mm
b = 30mm
c = 7mm
d = 18mm
e = 1mm
l = 10mm
r = 12mm
r4 = 8mm
h = 25mm
r1 = 4mm
r2 = 3mm
r3 = 12mm
Material is caste iron
Let dia of the sheave = 20 x d
= 20 x 14
= 240mm
The reference is made from Rudenko,N.’Materials Handling Equipment ‘,Mir Publishers, Moscow(1969).
P .86,Table 16.

Drum design
Drum grove size

Referring to Redenko,N “Materials Handing Equipment”,Mir publishers,Moscow (1969),P.No.90 table 17.
Considering standard groove of drum, for, diameter of wire 15 mm as it is nearest to 14mm.
Drum diameter = sheeve diameter = 240 mm.
r 1 = 0.53 x d (d ≈15) = 9mm
s1 = 1.15d = 17mm
C1 = 0.25 d = 5mm
No. of turn on each side of drum
Z = (hi/πd) + 2 =
Where
H = Lifting Height.
I = Ratio of the pulley system.
D = Drum diameter ≈ 45 x 14 = 630
So Z = ( 8.00 x 2) + 2
Π x63
Z = 10
Full lenth of drum for one rope.
L = (2HI + 7)Si (I = 2 assumed)
πD
=(2 x 800 x 2 + 7)1.5
=34.75
≈35 cm
The drum is made up of IS grade = SG 80/2
With stress = 480Mpa
W = 0.02 x 630 = 10
= 22.6
≈ 23 mm
Outside dia of the drum Do = D + 6d
= 630 + 6 x 14 = 714mm
Inside dia of the drum = Di = D – 2W
= 630 – 2 x 25
= 584 mm
Checking of strength
Bending Stress in drum

σbend = 8WLD
π(D4 – Di4)
= 8 x 6200 x 9.8 x 35 x 630
Π x (6304 – 5844)
= 0.0828MP

Maximun Torque
Tmax = W (D + d)
2
= 6200 x 9.8 (630 + 14)
2
= 19.564 x 106
Maximum Shear Stress
 = 16 Tmax D
π(D4 – Di4)
= 16 x 19.56 x 106 x 630
π x (6304 – 5844)
≈ 1.523 MPx
Direct Compressive Stress
= W = σc
wSi
= 6200 x 9.8
23 x 17
= 155.4MPx

Maximum Stress in the Drum
σ = √σbend2 + σc2 + 4max2
= (0.08282 +155.42 = 4 x 1.5232)1/2

σ < 480 MPx, S the Design is safe.

Fastening Of Rope With The Drum
For 14 mm dia
Locating Dimension
Pitch of screw = 53 mm
T = 43 mm
Screw size
Lo = 18 mm
L = 50 mm

Plate
C = 7 mm
No. of fastenings = 1

Selection of Motor
W = 3100 kg x 9.8 m/s2
V = 0.2m/sec
So power required = 3100 x 9.8 x 0.2
= 6080.123Nm/sec
= 6.08 Kwatt
Taking 11 Kwatt 3 phase induction motor (flange type) of 11 KW (nearest to 6.08KW)
Frame No. 132 M
Flange designation F265B
The speed is 1000 RPM
By using gear box the speed can be reduced to 300 RPM

GearBox Calculation
Gearbox ratio = (Input RPM x π x rope drum dia)
(speed x no. of falls /2)
= ( 980 x π x .714) = 183.54
(3.00 x 4 )

Brake calculation
Required Brake Torque = 1.5 x 716.2 x mech H.P.
Motor RPM
= 1.5 x 716.2 x 50.12
300
= 53.84 Nm
Design of wormset
Power = P = 6.08 Kwatt
RPM of Worm = Nw = V x 60
πd
= 0.2 x 60
π x 0.63
RPM of Worm Gear NG = 300 RPM
So R = NG
Nw
= 300
6
Let Ф = 14.5o
Let the centre distance = C = 300 mm =0.3m
Pitch circle diameter of the worm
Dw = C.8750 = 3Pc
3.48
Dw = 3.8750 = 0.10020m
3.48

≈ 100mm
Dw = 3Pc = 3Pa = 3 x π x ma
So ma = Dw/3π = 100.2/3π
= 10.63 mm ≈ 11mm

Pitch circle dia of the gear Dg = 2C – Dw = 2x 300 – 100 = 500 mm
Velocity ratio = Ng/Nw = 50
Ng/Nw = Dg /(ma x Nw)
50 = Dg/(11 x Nw)
Dg = 50 x 11 x Nw

Taking Ng = 1 , because Dw is closer to the calculated.
So, Dg = 550
Dw = 2C – Dg
= 2 x 300 -500
= 50mm
Face width of the gear
b = 0.73 x Dw
= 0.73 x 50
= 36.5
= 40 mm
Static strength of Bronze
σd = 90MPa
In worm drive irrespective of materials of worm and worm ger,the gear is weak.
So design should be based on gear.

Tangential load on the gear :
Ft = σ π mn y b
= (σd x Cv)π mn y b
Velocity factor Cv = 6 .
6 + Vg
Vg = π x Dg x Ng
60
= 8.69
Cv = 6 = 0.41
6 + 8.69
Form factor
Y = 0.124 – 0.684
Ng
= 0.11132
Tan λ = m x Nw
Dw

= 11 x 1
50
λ = tan-1 (.22) = 12.4o

Nominal Module = m (ma) x cos λ
= 11 x cos 12.4
= 10.743 mm
Ft = 90 x .41 x π x 1o.743 x .11132 x 40
= 5545.47 N
= 5.55 KN
Power Capacity = P1 = Ft x Vg
= 5.55 x 103 x 8.69
= 48.19 K watt
Which is greater than capacity so the design is safe.
Powe capacity of drive from wear point of view

P2 = Dg x b x W x Vg
= 550 x 40 x W x 8.64
W = .550 = Material combination factor.
For worm and worm gear made up of hardened steel and phosphor bronze
So, P2 = (550 / 1000) x 40 x .55 x 8.64
= 104.4 Kwatt
Power capacityof the drive, from the heat dissipation point of view is given by :
P3 = 3650 x C17
R + 5
= 3650 x 300 17
50 + 5
= 361.99K watt
So The safe power capacity is minimum i.e P1 = 48.19 Kw

CONCLUSION : The design of the hoist of EOT crane is done Numerically .We can implement the design practically in industries for various lifting jobs.
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78 Responses

  1. Dear sir.
    I need to a reference for designing and producing hoists in E.O.T.. Specially I need to the restricting data of the design criteria. I mean some useful coefficients and also factor of safeties which should be mentioned.
    I really appreciate it if you help me or inform me about a useful references.
    Best regards

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  2. Design of Gear Box, Hoist ,Pully Etc

  3. DEAR SIR,

    I WANT TWO SAMPLE DESIGN CALCULATIONS FOR COMPLETE EOT CRANES . CAN YOU GIVE ME THAT .

    KIND REGARDS

    RKROY

  4. Can you give me design calculation for EOT Cranes . I want to learn EOT crane design.

    Kind Regards

    R K ROY

  5. Please give the EOTcrane design of double girder

  6. PL GIVE ME A SAMPLE DESIGN CALCULATION FOR FOLLOWING EOT CRANES VARIANTS

    20TON SWL X 20 M SPAN X 8 MTRS LIFT
    20TON SWL X 30 M SPAN X 10 MTRS LIFT
    50TON SWL X 20 M SPAN X 10 MTRS LIFT
    50TONS / 10 TONS SWL X 20 M SPAN X 10 M LIFT

    • 20TON SWL X 20 M SPAN X 8 MTRS LIFT
      20TON SWL X 30 M SPAN X 10 MTRS LIFT
      50TON SWL X 20 M SPAN X 10 MTRS LIFT
      50TONS / 10 TONS SWL X 20 M SPAN X 10 M LIFT

      pl give me a design calculation for above E.O.T. Cranes.

  7. Sir i need how to design a worm shaft of EOT crane is this any procedure if yes then pls send me some information about it

  8. th eliterature is superb.
    but, it is not clearly readable as symbols used in this artical gets discarded.
    can u please send me it in *.doc format??
    can u send me the design if the loading capacity is higher, for multiple bend of rope???

  9. that’s fantastic

    can get the IS 3815-1969 data
    reagarding design of hoisting equipments.

  10. software for eot crane calculation

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  11. kindly guide me for the failure of pinion of the gearbox used in E.o.t cranes.

  12. dear sir,

    can you give me, any components system in electric wire rope hoist
    and complete design with their pitcure…
    thanx…

    kind regards

  13. This is the first time I visited this site. I really need design of trolley design on design of 10 Ton double girder eot crane

  14. Dear Sir,
    can u please give me the Design procedure for following capacities?
    5 TON EOT, 12 m span
    10 TON EOT, 12 m span
    15 TON EOT, 12 m span
    20 TON EOT, 12 m span

  15. Sir,
    M Design Er. in crane industry. I shall need your help. A Request to provide me your mail i d & contact details.

    Regards,
    Deepakk

  16. sir,

    pls can u give me the sample calculation of hoist manufacturing ….

  17. need to design a crab for EOT span 15mts, double girder. capacity 25 m.t.

  18. Sir, can you please e-mail me the design procedure and manufacturing considerations of 5 ton E.O.T hoist crane

  19. Dear Sir,

    I need assitance for the selection of bearings for a sheave block for a deck crane (36 tons SWL), could you contact me by email ???

    thanks,

    Antonio Gonzalo
    Spain

  20. I am interested in mechanical engg topics like the hoist design. Kindly send me further details. thank you

  21. Good Useful Information.

  22. thank you sir for the design. really appreciated it. However if you don’t mind i need some information as to where i can get a 2d drawing of an EOT CRANE and also travelling mechanism design.

  23. The calculations are superb .. but it is not clearly readable as some of the symbols are not supported . can you send me the .doc copy of the calculations ?

  24. really good article,

    can you provide me wire rope selection procedure? in EOT cranes …..

  25. Dear sir,

    I want completed Eot crane design having 30T main and 5T auxiliary crane with 25 meter span

  26. Design calculation of hook are appreciable, i am in the business of crane design
    you are requested to send me the design calculation for crane design please take the data as under
    Load 5T, Span 20 mts , lift 10 mts ,class II, indoor application
    Speed MH 5MPM, CT 10MPM, LT 20 MPM
    Regards
    DDSharma

  27. Dear sirm
    can you please send me the design procedure of EOT cranes of 5 ton, 10, ton, 12 ton with 50 meter span,
    It is very urgent
    regards
    sanjay

  28. the website
    thanks much

  29. Sir, can you please e-mail me the design procedure and manufacturing considerations of 10 ton E.O.T hoist crane
    double girder (full design calculation)

  30. can you give me the detail calculation of eot crane design for industrial cranes
    Thanks
    T.Raju

  31. Dear sir,
    Can you mail me the 5 Ton SGEOT Crane,25 m Span design calculation,Hoist selection procedure with details consideration

    Thanks & Regards
    Raja

  32. PL GIVE ME A SAMPLE DESIGN CALCULATION FOR FOLLOWING EOT CRANES

    20TON SWL X 20 M SPAN X 8 MTRS LIFT
    20TON SWL X 30 M SPAN X 10 MTRS LIFT

  33. DEAR SIR,
    I WANT TWO SAMPLE DESIGN CALCULATIONS FOR COMPLETE EOT CRANES . CAN YOU GIVE ME THAT .

    KIND REGARDS

    KIRAN

  34. i want electric wire rope hoist with electric trolley design calculation with genaral arrangement drawing software

  35. dearsir, i want to sample design calculation e o t crane soft ware complet e

  36. Dear sir ,

    , software for eot crane calculation with drawing as is 3177

    ,

  37. i want design caculation with drawing….. as per IS 3177 girder, trolly, endcarriage.
    1. CT Wheel
    a. Design of Wheel Diameter
    b. Motor Selection
    c. Input & Output Coupling Selection
    d. Brake Selection
    e. Design of Shaft Diameter
    f. Bearing Selection
    g. Wheel Adhesion Calculation
    h. Wheel Tearing Calculation
    2. LT Wheel
    a. Design of Wheel Diameter
    b. Motor Selection
    c. Input & Output Coupling Selection
    d. Brake Selection
    e. Design of Shaft Diameter
    f. Bearing Selection
    g. Wheel Adhesion Calculation
    h. Wheel Tearing Calculation
    3. Rope Drum
    a. Wire Rope selection
    b. Rope Drum calculations
    i. Diameter of Rope Drum
    ii. No. of Grooves required
    iii. Length of Rope Drum
    iv. Rope Drum Pipe
    c. Motor Selection
    d. Gear Box Selection
    e. Coupling Selection
    f. Brake Selection
    g. Design of Shaft Diameter
    h. Bearing Selection
    4. Bottom Block and Top Block (4 Fall / 6 Fall / 8 Fall)
    a. Design of Top Block Shaft Diameter
    b. Design of Top Block Sheave / Pulley Bearing
    c. Design of Top Block Pulley Diameter
    d. Design of Bottom Block Shaft
    e. Design of Sheave/Pulley Bearing of Bottom Block Shaft
    f. Design of Bottom Block Pulley
    g. Design of Equalizing Pulley and Shaft
    h. Design of Hook & Hook Nut
    i. Design of Thrust Bearing
    i want design caculation with drawing…..

  38. dear sir

    plaease give me the camplete e.o.t. overhead crane design procedure

    i m very greatfull toy ou

    also give me your canctact no and addrees

    regards

    bhavin patel
    vapi

  39. Can you give me design calculation for EOT Cranesand specially gantry cranes. Sir please can you give us some design procedure above mentioned ffied.

    Regards,

    Firoz Pawaskar
    Reckon Engineers
    India

  40. We require 40 MT (Main Hoist)+ 10 MT (Auxillary Hoist)EOT Crane. Please advise weight of Pillars and other Structural material and please design the load bearing pillars.Please advise mfg. and fabricators and any second sale dealers of used cranes too.

  41. Our span is 60 ft. and grade II

  42. nice design. it is very helpfull to make a design.

  43. Sir,
    your design is very nice and very help to make a design.

    Regards,
    Er. Hemant kumar
    Ph: +919887076580

  44. PL GIVE ME A SAMPLE DESIGN CALCULATION FOR FOLLOWING EOT CRANES VARIANTS

    6.3TON (2X3.2) SWL X 25 M SPAN X 8 MTRS LIFT

    Many Thanks & Kind Regards,

  45. i need to modify an existing trolley hoisting arrangement used for cane offloading so that the hoist drums are independently driven.the safe working load should be 15t.it has a travel span of 32m and a lifting height of 18m.trolley wheel base is 4m wide and pitch of 3.3m.i would appreciate assistance in determining the necessary specs for the motor,gearboxes and brakes for the hoists and the cross travel .

  46. Hello,
    Can you provide me the EOT crane Hoisting motor and other travel motor KW calculation examples with Formulas?

    kind Regards,
    S.Rao

  47. I need assistance for details regarding physical parameters to be measured and monitored in a Security System for static EOT cranes used in building construction

  48. Dear Mr. Rajendra,

    Thank you for the calculation kindly provide a design of typical EOT crane.

    Regards,

    Avinash

  49. your design of hoist is excellent .
    ropesheave of hoist detail is good.

  50. dear sir i want design for eot, hot ,gantry&zib crane sample design s . please can u give me the sample calculation of hoist manufacturing. thnx 2 u

  51. SIR, plz send me G.A drawing of 3 ton double girder E.O.T crane

  52. sir,
    plz send me G.A drawing of 3 ton double girder E.O.T hoist

  53. Dear Sir,
    I want 30 MT EOT class III hoist Gear Box, I want to know the hoist gear box ratio. i am having data as follows:
    Hoisting Speed – 3 Mtr / Min
    Electric Motor – 30 HP
    Electric Motor rpm – 1440
    Rope drum diameter – 450 mm
    No. of falls – 8

    Please let me know.

    Thanks

    Nikhil Arora
    9737047207

  54. Dear Sir

    Can you please send me a portal crane design procedure, of capacity of 10 ton, respectively.

  55. dear sir,
    will you provide me soft copy for design calculation for monorail hoist or excel sheet for the same.

  56. I want to design 7.5 ton Single girder box type EOT crane.pl.guide me for calculation or design.

  57. can you please send me the selection procedure of eot and specifications of all types eot designing structure

  58. Dear sir, i will be greatful if you could send me full dimension and construction detail for 5 Tons and 10 tons E.O.T CRANES, Span 24 meters, lift 8 meters

  59. dear sir,
    ur explanation is superb,i have just completed my engineering & joined as design engineer,the problem is that the firm is newly started,so MY kind request to U IS TO send the design procedure of crane assembly (EOT,HOT,JIB.GOLIATH). I just beg of u and also ready to pay.ANYBODY FRM ABOVE PLZ HELP.
    CONTACT:09665621417.
    MAIL harish7878@rediff.com

  60. dear sir,
    your explanation is superb,i have just completed my engineering & joined as design engineer,the problem is that the firm is newly started,so MY kind request to U IS TO send the design procedure of crane assembly (EOT,HOT,JIB.GOLIATH). I just beg of u and also ready to pay.ANYBODY FRM ABOVE PLZ HELP.
    CONTACT:09665621417.
    MAIL harish7878@rediff.com

  61. Dear Mr. Parmanik,
    Could you please suggest a reference book for these calculations?
    Thank you.

  62. dear sir

    can u give me various housing drawing of gear box use in crane company please

  63. There is beam of cross section I, we know the span and section modulus (Z) then how will i calculate the lifting capacity of EOT crane?

  64. Dear sir,
    Its nice to see the design of hoists. can you help us in design of eot cran,
    jib crane and grab buckets. we are manufacturers of these.we look forward
    to a fruitful business co-operation.
    with regards,
    shivaswamy,
    General Manager

  65. PL GIVE ME A SAMPLE DESIGN CALCULATION FOR FOLLOWING EOT CRANES VARIANTS
    10T cap EOT crane Double girder. Span 27mtrs,height of the lift 8mtrs
    Gantry crane 5T cap Span 12mtrs Heighte of the lift 5mtrs
    Gib crane 5t Fixed location 180degree 4mtrs C.T,5mtrs heighte
    Please send Design with formulas

  66. CAN ANYBODY TELL ME THE APPROX WEIGHT OF E0T CRANE OF 70 T CAPACITY OF 12 M SPAN

  67. Hello all, if anybody wants to know the design results of your required crane, send me your eot crane requirement data sheet, I can design it for you.

    Only double girder eot cranes from 10 Tons to 300 Tons.

    eotcranedesigner@gmail.com

  68. you may also visit eotcranedesigner.wordpress.com and request ur design.

  69. Good post. I learn something totally new and challenging on websites I stumbleupon on a daily basis. It’s always useful to read through content from other writers and practice something from other websites.

  70. Hello, can anyone give me a book reference of what to consider in designing a girder to column connection for a hoist crane having 12.5T capacity…
    Thank you…

  71. Dear Sir,
    I request you to e-mail me the complte design procedure and manufacturing considerations of EOT Crane.
    1. Design of trolley structure.
    2. Design of main girder.
    3. Design of side truss.
    4. Design horizontal truss.
    5. Design of members.
    6. Design of gantry girder and column.
    7. Design of mechanical components, rope, pulley, drum.
    8. Design of crane hooks, brakes, drives etc.
    Regards
    Sanjay

  72. I want to design 250 kg wire rope hoist ,2.5 mpm speed.pl.guide me for calculation or design.

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