FEM2 131 2 132 Engl_Order_404705

Prévia do material em texto

SECTION I I 
DE LA FEDERATION EUROPEENNE DE L4 MANUTENTION 
Secretaire : Madame E. A. Codevelle 
39141, rue Louis Blanc, 92400 Courbevoie 
E3 92038 Paris-La Defense cedex, France 
tel. 33 (0)l 47 17 63 27 - telecopie 33 (0)t 47 17 63 30 
RULES FOR THE DESIGN 
OF MOBILE EQUIPMENT FOR 
CONTINUOUS HANDLING 
OF BULK MATERIALS 
DOCUMENT 2 131 1 2 132 
GENERAL SUMMARY 
chapter 1 Scope and field of application 
chapter 2 Classification and loading of structures 
and mechanisms 
chapter 3 Calculating the Stresses in structures 
chapter 4 Caiculation and choice of mechanisms 
components 
chapter 5 Safety requirements 
chapter 6 Tests and tolerantes 
edition 1997 
Copyright by FEM Section II -Also available in French and German 
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O FEM Section I1 
CHAPTER 1 
SCOPE AND FIELD OE APPLICATION 
CONTENTS 
Foreword and general contents 
Introduction 
Scope 0f the N ~ S 
Field of application 
List of maiii symbols and notations 
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O FEM Section I1 1-3 
1-1 FOREWORD AND GENERAL CONTENTS 
The rules for the design of mobile equipment for continuous handling of bulk materials developd hy tlie 
Technical Committee of FEM Section I1 have always been widely used in many countries throughout the 
world. 
It should be mentioned that, since its January 1978 edition, the document FEM 2 131 - 0111978 has been 
adopted as an ISO international standard under the reference ISO 504911. It shall be proposed for this ISO 
standard a revision to include the corresponding chapters of the present FEM edition. 
The revision done in 1997 does not bring fundamental changes to the 1992 edition. The important 
modifications deal with the following points : 
- fatigue calculation of mechanisms, 
- friction resistances to define drive mecbanisms and braking devices, 
- tables describing cases of notch effect for welded stmcture. 
In order to keep the histoiy of the evolution of these rules which apply to the machines defiiied below in 
the clause "Scope", it has been indicated below what are the adaed values of the 1992 editioii to the 
docurnents : 
a) FEM 2 131, edition January 1978 "Rules for the design of mobile continuous bulk handling 
equipment - chapter I Structures", 
b) FEM 2 132, edition June 1977 "Rules for the design of mobile continuous bulk handling 
equipment - chapter I1 Mechanisms". 
FEM Section I1 had decided to issue the 1992 edition of these design rules with a threefold objective : 
1) to make the periodical revision of the above rules to update them, 
2) to add chapters in pariicular on safety, tests and tolerances, 
3) to h m o n i z e them, as far as possible, with the third edition of the design iules issued by 
FEM Section I in 1988 f o ~ the design of lifting appliances. 
The following comments can be made on the three objectives which are at the origin of the 1992 edition : 
1) Revision of the rules FEM 2 131 - FEM 2 132 
The 1992 periodical revision did not involve fundamental changes, but was aii updating which 
essentially took into account the changes brought in othor standads with regard for exatnple to units, 
welding symbols, etc. 
2) Additions to the urevious edition 
The 1992 edition had been completed with two chapters covering : 
- safety requirements (chapter 5) 
- tests and tolerances (chapter 6) 
It was planned to add an "Electrical" chapter iii a next edition. 
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1-4 O FEM Section 11 
3) Harmonization with the 3rd edition of FEM Section I desisn rules for liftine apnliances 
Design depanments which have to design both handling equipment (FEM Section I1 r u h ) and lifting 
equipment (FEM Section I rules) have sometimes met difficulties due to a cenain lack of consisteiicy 
between the corresponding rules. 
While it should be pointed out that continuous handling equipment and lifting appliances are different 
with regard to the definition of loads and their combinations, it should be noted. on the other hand, that 
the method OS classification of the machines, of their mechanisms or components, and tlie calculaiioii 
of cenain elements, should be similar if not identical. 
The 1992 edition therefore tries to be in harmony with FEM Section I design rules lo the greatest 
possible extent. Sorne differences however remain : it may be possible to reduce them later when tlie 
results of many srudies currently in Progress (calculation for fatigue, definition of rail wheels. 
calculation o i wind effects, ... ) are known. 
4) Maior chanees in the documents FEM 2 131 and 2 132 editions of 1978 and I977 rcsnectivelq: 
It should be stressed that the 1992 version of the design rules for continuous bulk handhng equipment 
does not include any major changes in its coiitent compared 10 tlie previous edition which consisted of 
documents FEM 2 131 and 2 132. 
In particular, the definition of the loads applying on machines and the combination of loads Iiave beeil 
maintained for the most pan. 
The principal changes can be summarized as follows : 
- Classification of the machines. their mechanisms and components 
Groups have been created to facilitate dialogue between User and manufacturer. As far as the whole 
machine is concemed, these groups called A2 to A8 are directly based on the total desired duration 
of utilization. 
Mechanisms can be classified in eiglit groups called M1 to M8, each group being hased on a 
spectrum class on one hand and a class of utilization (i.e. on a total duratioti of utilization) on the 
other hand. 
Structural or mechanism components can be classified in eight groups named EI to E8, each of 
them being based, in the same way as mechanisms, on a class of load spectrum and a class of 
utilization. 
Loads to be taken into account in the calculation of structures 
Clarifications have been made regarding the definition of these loads, in pmicular on the subject of 
wind loads. A load case has been added for special situations which may occur for machincs during 
erection. 
Calculatinp the Stresses in structural comnonents 
A method for selecting the steel grade in relation to brittled fracture has been added : the choice is to 
be made between four quality groups which are distinguished by the impact strength of the 
corresponding steels. 
The cbapter on bolted joints has been reworked and completed. 
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O FEM Section I1 1-5 
The curves giving the permissible fatigue Stresses for structural components have beeil maintained 
and given in relation to the component classification group. 
Checkine and choice of mechanism components 
Wire ropes are chosen on the basis of a practical safety factor which depends on the mechanism 
classification group. The rope breaking strength takes into account the rope fill factor and spinning 
loss factor. 
Regarding the choice of rail wheels, the factor C2 is given in relation to the class of utilization of 
the mechanism and not the classification group, in order to keep the method used so far which is 
fully satisfactory. 
To conclude the Summary of the major changes introduced in 1992 to the previous edition (documents 
FEM 2 131 and 2 132), it is worthwhile noting thai the changes made dunng rhe elaboration of the 
standard ISO 504911 published in 1994 (which reproduced the FEM ~ l e s 2 131), have of Course been 
incorporated in the 1992 edition. 
1-2 INTRODUCTION 
To facilitate the use of these rules by the purchasers, manufacturers and safety organizations concemed, it is 
necessary to give some explanation in regard to the two following questions : 
- How should these rules be applied in practice to the different types of appliance whose construction they 
Cover ? 
- How should a purchaser usetbese rules to define liis requirements in relation to an appliance which he 
desires to order and what conditions should he specify in his enquiry to ensure that the manufacturers can 
submit a proposal in accordance with his requirements ? 
1) First of all, it is necessary to recognize the great variety of appliances which are covered by the design 
niles. It is obvious that a buckct-wheel reclaimer used for very high duty in a stockyard is not designed 
in the samemanner as a small stacker for infrequent duty. For the latter, it may not be necessary to 
make all the verifications which would appear to be requued from reading through the rules, because 
one would clearly finish with a volume of calculations which would be totally out of proportion to the 
objective in view. 
The manufacturer must therefore decide in eacb panicular case which p m s of the new machine, should 
be analysed and which pans can be accepted without calculation. This is not because the latter would 
contravene the requirements of the rules but because, on the contrary, due to experience, the designer is 
certain in advance, that the calculations for the latter would only confinn a favourable outcome. This 
may be because a standard component is being used which has been verified oiice and for all or because 
it has been established that some of the verifications imposed by the mles cannot, iri certain cases. 
bave an unfavourablc result and therefore serve no puipose. 
With the fatigue calculations, for example, it is very easy to see that cenain verifications are 
unnecessary for appliances of light or moderate duty because they always lead to the conclusion that 
the most unfavourable cases are those resulting from checking safety in relation to the elastic limit or 
to the breaking Stress. 
These considerations show that calculations, made in accordance with the rules, can take a veiy 
different form according to the type of appliance which is being considered, and may, in the case of 
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1-6 O FEM Section I1 
a simple machine or a machine embodying smdard components, be in the form of a brief Summary 
without prejudicing the compliance of the machine with the pnnciples set out by tbe design rules. 
2) As far as the second question is concemed. some explanation is first desirable for the purchaser, who 
may be somewhat bewildered by the extent of the document and confused when faced with the variety 
of choice which it presents, a variety which is, however, necessary if one wishes to take account of tlie 
great diversity of problems to be resolved. 
In fact, the only important matter for the purchaser is to define the duty which is to be expected from 
the appliance and if possible to give some indication of the duty of the various individual motions. 
As regards the service to be performed by the appliance, only one factor must be specified, i.e. the 
class of utilization, as defined in 2-1.2.2. This gives the group in which the appliance must be ranged. 
In order to obtain the number of hours which determines the class of utilization, the purciiaser may, for 
instance. find the product of : 
- the average number of hours which tlie appliance will be used each day, 
- the average number of days of use per year, 
- the number of years after which the appliance may be considered as baving to be replaced. 
In the case of mechanisms, the following should also be specified : 
- the class of utilization, as defined in 2-1.3.2, 
- the load spectrum, as defined in 2-1.3.3. 
On tlie hasis of the class of utilization of the appliance as a whole, it is possible to determine a total 
number of working hours for eacli mechanism according to the average duration of a working cycle and 
the ratio between the operating time of the mechanism and the duration of the cotnplete cycle. An 
example of classification of an appliance, its mechanisms and elements is given in 2-1.5. 
As a generai rule, the purchaser need not supply any other information in connection with the design 
of the appliance, except in certain cases : e.g. the value of the out-of-service wind, where local 
conditions are considered to necessitate design for an out-of-service wind greater than that defined in 
2-2.3.6. 
1-3 SCOPE OF THE RULES 
Tbe purpose of these rules is to determine the loads and combinations of loads which must be taken into 
account when designing handling appliances, and also to establish the strength and stability conditions to 
be observed for the vaious load combinations. 
1-4 FIELD OF APPLICATION 
These rules are applicable to mobile equipment for continuous handling of bulk materials, especially to 
rail-mounted : 
- stackers 
- shiploaders 
- reclaimers 1 
- combined stackers and reclaimers / equipment fitted with bucket -wheels or hucket chains 
- continuous ship unloaders 1 
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O FEM Section I1 
For other equipment, such as : 
- excavators, 
- scrapers, 
- reclaimers with scraper chains, 
- tyre or crawler-mounted stackers andior reclaimers, 
the clauses in these design ~ l e s appropnate to each type of apparatus are applicable. 
Ir should be noted thar when a mobile machine includes one or several belt conveyors as conveying 
elements, the clauses of these design rules, insofar as they apply to the macliine in question, are applicable. 
The selection of the conveyors should be made in accordance with the standard ISO 5048 : "Continuous 
meclianical handling equipment - Belt conveyors with cmying idlers - Calculation of operating power aod 
tensile forces". 
On rhe other hand, belt conveyors whicli are not part of a mobile machine are excluded frorn tlie scope of 
these d e s i ~ n mles. 
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1-8 
1-5 LIST OF MAIN SYMBOLS AND NOTATIONS 
O FEM Section I1 
Symbol 
A 
A2 to A8 
Ae 
B 
BOtoB10 
b 
b 
C 
Cf 
C l , Clmax 
C2. C2max 
C , C' 
D 
D 
Dt 
d 
d2 
dt 
E 
E I to E8 
F 
F 0 
f 
Dimen- 
sion 
m2 
m2 
m 
m 
mm 
mm 
mm 
mm 
mm 
mm 
NImni2 
N 
N 
Designation - First mention chapter (...I 
Front area exposed to wind (2-2.2.1) 
Handling machine groups (2- 1.2) 
Enveloped area of lattice (2-2.2.1) 
Belt width of the conveyor (2-2.1.2) 
Classes of utilization of structural members (2-1.4.2) 
Width of the flow of material on the helt (2-2.1.2) 
Useful width of rail in wheel calculation (4-2.4.1) 
Coefficient used to calcuiate the tightening torque of holts (3-2.3) ; 
selection coefiicient for choice of running steel wire ropes (4-2.2.1) 
Shape coefficient in wind load calculation (2-2.2.1) 
Rotation speed coefficients for wheel calculation (4-2.4.1) 
Utilization class coefficient for wheel calculation (4-2.4.1) 
Factors characterising the slope of Wöhler curves (4-1.3.5) 
Symbol used in plate inspection for laniination defects (3-2.2.1) 
Rope winding diameter (4-2.3.1) ; wlieel diameter (4-2.4.1) 
Diameter of bolt holes (3-2.3) 
Nominal diaineter of rope (4-2.2.1) 
Bolt diameter at thread root (3-2.3) 
Nominal holt diameter (3-2.3) 
Elastic modulus (3-2.1.1) 
Groups of components (2-1.4) 
Wind force (2-2.2.1) ; compressive force on meinber in crippling 
calculation (3-3) 
Minimum breaking load of rope (4-2.2.1) 
Fill factor of rope (4-2.2.1) 
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O FEM Section I1 1-9 
Symbol 
S 
H 
Hy 
j 
K - K' . K" 
K' 
KO to K4 
2. 
KL 
k 
kd 
km 
ks 
ksp 
ku 
kuc 
L1 toL4 
1 
lk 
M 
M1 to M8 
Ma 
M s 
Mk 
m 
Dimen- 
sion 
m/s2 
N 
Nimm2 
mm 
mm 
Nm 
Nm 
Nm 
Nm 
Designation - First mention chapter (...) 
Acceleration due to gravity, according to ISO 9.80665 m/s? 
Coefficient depending on group for choice of rope dmnis and pulleys 
(4-2.3.1) 
Horizontalforce perpendiculat to rail axis (2-2.2.6) 
Group number in component groups EI to E8 (4-1.3.6) 
Safety coefficients for calculation of bolted joints (3-2.3) 
Empirical coefficient for detemining minimum breaking strengt11 of 
rope (4-2.2.1) 
Stress concentration classes for welded parts (3-4.5. I) 
Pressure of wheel on rail (4-2.4.2) 
Spinning loss coefficient for ropes (4-2.2.1) 
Size coefficient in fatigue veritication of mechanism parts (4-1.3.3) 
Spectmm factor for mechanisms 12-1.3.3) 
Shape coefficient in fatigue verification of mechanisni pans 
(4-1.3.3) 
Specmm factor for cornponents (2- I .4.3) 
Surface finish (machining) coefficient in fatigue verification of 
mechanism parts (4-1.3.3) 
Corrosion coefficient in fatigue verification of mecliaiiism paits 
(4-1.3.3) 
Spectrum classes for mechanisms (2-1.3.3) 
Overall width or rail head (4-2.4.1) 
Length of parts tightened in bolted joints (3-2.3) 
External moment in bolted joints (3-2.3.4.4) 
Mechanism groups (2- 1.3) 
Torque required to tighten bolts (3-2.3) 
Stabilizing moment for the machine (3-6.1) 
Overturning monient (3-6.1) 
Number of friction surfaces in boited joints (3-2.3.4.2) 
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1-10 O FEM Section I1 
Symbol 
N 
N 
Na 
n 
P 
P1 to P4 
PIO, PI00 
Pmean 1,11,III 
Pmin I, 11, 111 
Pmax I, 11, I11 
Pa 
PL 
4 
4 
R0 
r 
S 
S 
SG 
smean 
Smin 
smax I, 11,111 
s b 
s 
T 
Dimen- 
sion 
N 
kN 
N 
N 
N 
N 
mm 
Nimm2 
NImm2 
NImm2 
mm 
N 
m2 
N 
N 
N 
mm2 
m 
h 
Designation - First mention chapter (...) 
Number of stress cycles (2-1.4.2) 
Extemal force perpendicular to joint plane in holted joints 
(3-2.3.4.3) 
Pennissible additional tensile force for bolt (3-2.3.4.5) 
Number of stress cycles (4- 1.3.5) 
Load on wheel (4-2.4.2) 
Spectrum classes for components (2- 1.4.3) 
Symbols indicating welding tests (3-2.2.1) 
Mean load on wheel in loading cases I, I1 and 111 (4-2.4.1) 
Minimum load on wheel in loading cases I, 11 and 111 (4-2.4.1) 
Maximum load on wheel in loading cases I, I1 and 111 (4-2.4.1) 
Pitch of tliread (3-2.3) 
Limiting pressure in wheel calculation (4-2.4.1) 
Correction factor shape coefficient kS (4-1.3.1) 
Aerodynamic pressure of the wind (2-2.2.1) 
Minimum ultimate tensile strength of the wire of a rope (4-2.2.1) 
Radius of rope groove (4-2.3.2) ; radius of rail head (4-2.4.1) ; 
blending radius (4-1.3.1) 
Maximum tensile force in rope (4-2.2.1) 
Area of material on the conveyor belt (2-2.1.2) 
Center of gravity of dead loads (3-6.1) 
Mean load in beaing calculation (4-2.1.2) 
Minimum load in bearing calculation (4-2.1.2) 
Maximum load in load cases 1,11 or 111 (4-2.1.2) 
Root sectional area of holt (3-2.3.3) 
Span of handling appliance (6-2.2) 
Total duration of nse of handling appliance and its n~echanisms 
(2- 1.2.2) - (2- 1.3.2) 
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1-12 O FEM Sectioii I1 
> 
Designation - First mention chapter (...) 
Friction coefficient in calculaiion of loads due to niotion (2-2.2.5) ; 
coefficient of friction in threads (3-2.3) 
Safety coefficient for calculation of stnictural rneinbers depending on 
case of loading (3-2.1.1) 
Safety coefficient for calculation of mecllanism parts depending on 
case of loading (4-1.1.2) 
Safety coefficient for verification of stability (3-6. I) 
Air density 
Calculated Stress in structures in general 
Apparent elastic limit (3-2.1.1) 
Ultimate tensile strength (3-2.1.1) 
n i e Euler stress (3-3.3) 
Permissible tensile stress for structural nlembers (3-2.1.1) 
Maximum permissible stress in welds (3-2.2.2) 
Compression stress in wheel and rail (4-2.4.2) 
Equivalent stress used in calculating structural members (3-2.1.3) 
Shear suess in general 
Permissible shear suess when calculating structural niembers 
(3-2.1.2) 
Maximum permissible shear stress in welds (3-2.2.2) 
Coefficient of eiongation for calculation of bolts (3-2.3.4.5) 
Slope of Wöhler curve (4-1.3.5) 
Ratio of Stresses at plate edges in buckling calculation (3-3.3) 
Crippling coefficieiit (3-3.1 . I ) 
Symbol 
W 
'JE 
VR 
VK 
P 
U 
"E 
OR 
E 
"R 
Ga 
Oaw 
"CE 
"CP 
T 
Ta 
Taw 
0 
9, 9' 
V 
W 
Dimen- 
sion 
keim' 
Nimm2 
Nimm2 
Nimm2 
Nimm2 
Nimm2 
Nimm2 
Nimm2 
Nimm2 
Nimm2 
Nimm2 
Nimm2 
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0 FEM Section 11 
CHAPTER 2 
CLASSIFICATION AND LOADING OF STRUCTURES AND MECHANISMS 
CONTENTS 
GROUP CLASSIFICATION OF MOBILE EQUIPMENT 
AND THEIR COMPONENTS 
- General plan olclassification 
- Classification of the coinplete handling niachine 
Classification system 
Classes of utilization = groups 
. Load specti-um 
- Classification of complete individual mechanisms 
. Classification systein 
. Classes of utilization 
Loading specirum factor 
Group classification of complete individuai mechanisms 
Guidance for group classification of complete individual meclianisnis 
- Classification of components 
Classification system 
Classes of utilization for coniponents 
, Stress spectrum 
Group classification of components 
- Hamioiiization of classification for the complete machiiie, complete 
mechanisms and components (suucture and niechanisins) 
Compiete machine 
Complete inechanisms 
Coinponents 
- Structural component groups 
- Mectianical component groups 
. An example of the classiiication of a machine aiid its componcnts 
LOADS ENTERING INTO THE DESIGN OE STRUCTURES 
- Main loads 
. Dead loads 
Material loads 
- Material load carried on the conveyors 
- Loads in the reclaiming devices 
- Material in the hoppers 
Incrustation 
Normal tangential and lateral diggiiig forces 
Forces on the conveyor(s) 
Permanent dynaniic effects 
Loads due to inclination of tlie working levei 
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- Additional loads 
Wind action 
- Aerodynamic wind pressure 
- in service wind 
- Wind load calcuiations 
- Shape and shieiding coefficients 
Snow and ice loads 
Temperature 
, Abnormal tangential and lateral digging forces 
Bearing friction and rolling resistances 
Reacrioii perpendiculai- to the rail duc io travelling of the appliance 
Non-permanent dynarnic effects 
- Special loads 
Clogging of chutes 
Resting of the reclaiming device or the boom 
Failure of load limiting devices as in paragrapli 2-2.1.2.1 
Blocking of travelling devices 
Lateral collision with the slope in case of bucket-wheel machines 
Wind load oii rnachines out of service 
Buffer effects 
. Loads due ro eanhquakes 
Loads during erection (or disniantling) of the macliine 
LOAD CASES FOR STRUCTURAL DESIGN 
- Table of load cases T.2-3.1 
LOADS ENTERING INTO THE DESIGN OF MECHANISMS 
- General information 
- Loads definition 
- Friction resistances 
LOAD CASES FOR THE DESIGN OF MECHANISMS 
- Tables of load cases T.2-5.1 (4 tables) 
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O FEM Section I1 2-3 
2-1 GROUP CLASSIFICATION OF MOBILE EQUIPMENT AND THEIR 
COMPONENTS 
2 - 1 .1 GENERAL PLAN OF CLASSIFICATION 
When designing a mobile appliance and its components for the continuous handling o i bulk materials. tiie 
service whicli they are to provide and their utilization should be taken into coiisideraiion. To thai end. a 
group classification is employed for : 
- tlie complete handling machine, 
- the complete individual mechanisms, 
- tlie components of stmcture and niechanisins 
This classification has been established of tlie base of two criteria : 
- tlie duration of use, 
- the load or stress svectrum 
2 - 1 . 2 CLASSIFICATION OF THE COMPLETE HANDLING MACHINE 
2 - 1 . 2 . 1 CLASSIFICATIONSYSTEM 
Complete handling machines are classified in seveii froups respectively designated by the syinhols 
A2, A3, ... A8 as defined in the table T.2-1.2.2 on the basis of seven classes of utilization. 
Imnortant note : The load spectrum which cliaracterizes all the Loads handled by the machine during 
its lifetime is not taken into account for tlie classificalion of tlie coniplete niacliine (see 2.1.2.3). 
2 -1 .2 .2 CLASSES OF UTILIZATION = GROUPS 
The utilization class of a machine depends on its total duratioii of use 
Tbe total duration o i use of a machine is defined as the nuinber of hours during wliicli the machine 
is actualiy in operation during its lifetime. 
The total duration of use is a calculated duration of use, coiisidered as a guide value, coiiiinencing 
when the appliance is put into service and ending when it is finally taken out of service. 
This duration, rneasured by a iiumber of hours of use T, depends on the desired service time in 
years, the average actual number of service days per year and tlie average actual number of service 
Iiours per day. 
On the base of tlie total duration of use, we have seven groups of liandling macliines, designed hy 
the syinbols A2, A3, ... A8. 
Tliey are defined in table T.2- 1.2.2. 
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2-4 O FEM Scctioii I1 
Complete inechaiiical handling machines are niost coniiiionly classified in groups A4 to A8. 
Table T.2-I .2.2 
GROUPS FOR HANDLING MACHINES 
2 - 1 . 2 . 3 LOAD SPECTRUM 
Total duration of usc T 
(h) 
T 5 1 600 
I 600 < T 5 3 200 
3 200 C T < 6 300 
6 300 C T - C 12 500 
12 500 C T - C 2.5 000 
25 000 C T - C 50 000 
50 000 < T 
Handling machines i i i operation are usually loaded close to tlie rated capacities whicli Iiave been 
taken into account in their diniensioning. 
GROUP Syiiibol 
A2 
A3 
A 4 
A 5 
A 6 
A 7 
A 8 
Additionally, the dead weight of the macliincs is usually iniportant conipared to tlie Iimdied loads. 
Thus, a handling machine will nomially be loaded close to thc maxiniuiii design \ d u e tliroughout 
its life. 
Tlie load spcclrum is therefore not taken into account for tlie classificatioii of coiiiplete handling 
machines. 
2 - 1 . 3 CLASSIFICATION OF COMPLETE INDIVIDUAL MECHANISMS 
2 - 1 . 3 . 1 CLASSIFICATION SYSTEM 
Individual complete mechanisms are classified in eight groups, designated respectively by tlie 
symbols M I , M2, ..., M8, on the hasis of ten classes of utilization (T0 to T9) and fourclasses 
of loading spectrum (L1 to L4). See 2-1.3.4. 
2 - 1 . 3 . 2 CLASS OF UTILIZATION 
Tlie class of utilization of a mechanism depends on its total duration of use. Tiiis is defined as tlie 
time during which the mechanism is actually in inotion during tlie life time of the rnacliine. 
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C FEM Sectioii I1 2-5 
The total duration of use of a mechanisni is a calculated duration considered as a guide \,alue and 
takes into account the fact that the mechanisni may be designed tobe replaced a nuinber o l tiines in 
the total life of the niachine. 
The total duration of use of a mechanism is expressed in terms of hours, T. cälculated on ihe basis 
of the average nuinber of service hourslday, the number of actual service daysiyeai aiid tlie required 
duration in tems of years before replacement. 
011 this basis, we liave teil classes of utilization. T0, T l , T2, . . , TY, rhe inost coninion classes 
being T3 to TY. Tliey are deiined in table T.2-1.3.2. 
Table T.2-I .3.2 
CLASSES OF UTILIZATION 
2- 1 .3 .3 LOADING SPECTRUM IIACTOH 
Utilization class 
symbol 
T0 
T1 
T2 
T 3 
T4 
T 5 
T 6 
T 7 
T 8 
T 9 
L 
The loading spectrum factor characterizes the magnitude of the loads acting on a inechaiiisni during 
its total duration of use. There is a distribution function, expressing tlie fractioii of the total 
duration of use (see table T.2-1.3.2) for which tlie inechanisni is subjccied to a load attaining a 
fractioii of the maximum rated load. 
Toräl duration of use T 
(11) 
T < 200 
200 < T S 400 
400 C T < 800 
8 0 0 C T - C 1 600 
1 600 < T - C 3 200 
3 200 < T - C 6 300 
6 300 < T - i J2 500 
12 500 < T - C 25 000 
25 000 < T - i 50 000 
50 000 < T 
An example of a loading spectruni is given in iigures 2-1.3.3.1 a and b. 
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Figure 2-1.3.3.1 a. Figure 2-1.3.3.1 b. 
S i = loading 
= maximum admissible load 
ti = duration for which the loading is at least equal to Si 
T = total duration of use 
Each spectrum is assigned a spectrum factor km, defined by : 
For the purposes of gtoup classification, exponent d is taken by convention as equal to 3. 
In many applications the function S(t) may be approximated by a function consisting of a certain 
number of steps r (see fig. 2-1.3.3.21, of respective durations t l , t2, ..., tr, for which the loadings 
may be considered as practically constant and equal to Si during the duration ti. If T represents the 
total duration of use and Smax the greatest of rhe loadings S I , S2, ..., S„ there exists a relation : 
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O FEM Section I1 2-7 
and in approximated form : 
3 3 
h m = ( ~ ) l . ~ + ( ~ ) i + , , , + ( ~ ) "lax Sm L .L= T 2 i = , (5) ,L 
mnx T 
- .5 t 
5 -. 
I,@ 
Q6 
o i 
02 
0 
I , I < I : , I I I , > > . ------ & ------ - T . 
/ I 1 
t r t z t a t r - 
T T T T 
Eig. 2-1.3.3.2 
Depending on its loading spectrum, a mechanism is placed in one of the four spectrum classes L I , 
L2, L3, L4, dehed in table T.2-1.3.3, the most common classes generally being L3 and L4 for 
the main mechanisms. 
Table T.2-1.3.3 
SPECTRUM CLASSES 
2- 1 .3 .4 GROUP CLASSIFICATION OF COMPLETE INDIVIDUAL 
MECHANISMS 
Spectrum class 
symbol 
L1 
L2 
L 3 
L 4 
Depending on their class of utilization and spectrum class, complete individual meclianisms are 
classified in one of the eight groups MI, M2, ..., M8, dehed in table T.2-1.3.4. The groups 
generally chosen for the main mechanisms are M4 to M8, a result of the commonly selected 
classes of utilization and spechum factors. 
Specmm factor km 
km 5 0.125 
0.125 < km < 0.250 
0.250 < k , 5 0 .500 
0 . 5 0 0 < km < 1 .000 
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Table T.2- 1.3.4 
MECHANISM GROUPS 
2- 1 .3 .5 GUIDANCE FOR GROUP CLASSIFlCATION OF COMPLETE 
INDIVIDUAL MECHANISMS 
Class of load 
specvuni 
L1 
L2 
L 3 
L 4 
Since appliances of tlie saine type niay be used in a wide variety of ways, accordiiig to tlie nietliod 
of working foi. instance, i i is not really possible to pre-determine ilie group of a i~iecliuiiisiii 
exactly. 
The classification possibilities are panicularly wide for niechanisnis wliicli caii bc eitlier working 
rnechanisins or only positioning mechanisms. 
Class of utilizatioii 
Further discussion relating to the Iiarmonization of classcs and groups is givcn i n cliapter 2-1.5, 
along with a typical example of classification of a niacliine and its components. 
T0 
M1 
M1 
M1 
M2 
2 - 1 . 4 CLASSIFICATION OF COMPONENTS 
2- 1 . 4 . 1 CLASSIFICATION SYSTEM 
Coniponents, both siructurai and inechanical, are classified i n eight groups, desigiied irspecii\,ely 
by the symbols EI, E2, ..., E8, on the basis of eleven classes of utilizatioii B0 to ß I0 and 
Cour classes of stress spectruin P1 to P4. 
TI 
MI 
M1 
M2 
M3 
2- 1 . 4 . 2 CLASSES OF UTILIZATION FOR COMPONENTS 
T 3 
M? 
M3 
M 4 
M 5 
T2 
MI 
M2 
M3 
M4 
The class of utilization of a cotnponent depends on its total duration of usc, wliicli is defined as tlie 
number of stress cycles 10 which the component is subjected during the lifetime of tlie iiiacliine. 
A stress cycle is a complete sei ofsuccessive Stresses, commencing at the moment wlicii the stress 
underconsideration exceeds the stress om defined in fig. 2-1.4.3 and ending at the nioineiit when 
this stress is, for the first tiine, about to exceed again 0, in the saine dircctioii. Fig. 2- 1.4.3 
therefore represenu tlie fluctuations of tlie stress o over a duration of use equal to five stress 
cycles. 
T 4 
M3 
M4 
M 5 
M 6 
The total duration of use of a component is a calculated duration, considered as a guide value a?d 
taking into account thc fact tliat the coinponent may be designed to be replaced a nun~ber OE tiiiies 
in the total life of the machine. 
T 5 
M4 
M5 
M 6 
M 7 
T 6 
M5 
M6 
M 7 
M 8 
T 7 
M6 
M7 
M 8 
M 8 
T 8 
M7 
M8 
M 8 
M 8 
T 9 
M8 
M8 
M 8 
M 8 
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O FEM Sectioii I1 2-9 
In tlie case of structural components the number of Stress cycles is proportioiial to thc nuiiiher of 
typical Iiandiing sequences. Certain components inay be subjected to se\,eral stress cycles duriiip a 
typical sequence depending on their position in tlie structure. Hense tlie ratio in question nia? difCer 
iroiii one component io another. Once tliis ratio is known. tlie total duration of use for the 
component is derived from the total duration of use determined by tlie dass of utilization of tiic 
appliance. 
For mechanical components, the total duration of usc is derived froni tlie total duratioii of usc of the 
mechanism to which that pmicular component belongs taking into account its speed of rotation 
andlor otiier circumstances affecting its operation. 
Based on this total duration of usc. we liave eleven classes of utilization, desipiiated respccti\,ely hy 
the symbols RO, BI. ..., BIO. They are defined iii tahle T.?-1.4.2. Tlie inost usual classes arc B5 
to B10 for the main components. 
Table T.?-I .4.2 
CLASSES OF IJTILIZATION 
Uiilization class 
symbol Total duration a i use iiieasured by numhcr N of stress cycics 
B 9 
B I O 
2- 1 . 4 . 3 STRESS SPECTRUM 
The stress spectmm characterizes the magnitude of the loads acting on tlie conipoiient duritig its 
total duration of use. There is a distribution fuiiction, expressing tlie fraction of the total duration of 
use (see 2-l.4.2), during which the component is subjected to a stress attainirig at least a iiactioii of 
the inaximuni stress. 
Each stress spectrum is assigned a spectruin factor ksp defined by : 
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Wherein the exponent C is dependant on tlie propenies o i tlie material concerned. the sliape and size 
ofthe component, its surface roughness and its depree ofexposure to corrosion. 
- For strucuiral comnoncnts : unless otherwise specified, the valuc of C sliould norrnally he takcn 
as 3 for welded parts. Higher values for some configurations may be used i n soine 
circumstances, but these should be used with care. 
- For mechanical comnonents : tlie calculation of C values is given in cliaptcr 4-1.3.5 aiid 
Annex A.4- I .3. 
In many applications the function o(n) may be. approximated hy a function consisting of a cenain 
number r of steps, comprising respectively n ] , n2, ..., n, siress cycles ; the stress ff iiiay k 
considered as praciically constant and equal to ffi during iii cycles. 1 fN represeiits the total number 
of cycles and omax the greatest of the Stresses 0 1 , 02, ..., f f , , there exists a relation : 
we gei an approximated form : 
in which summation is tnincated for the first ni 2 2.106. Tliis ni is taken as 11,. and repiaced by 
nr = 2.10%ycles. 
Depending on its stress spectrum, a componcnt is placed in one of the spectruiii classes P I , P2, 
P3, P4, defined in table T.?-1.4.3, ihe iiiost usual classes being P3 arid P4 for niain coriiponents. 
Table T.2-I .4.3 
Spectruni class Spectrutn iactor ksp 
synibol 
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O FEM Section I1 2-11 
For structursl components, the stresses to be taken into consideration for determination of the 
spectrum factor are the differentes osup - G m between the upper stresses and the average 
stress crm, these concepts being defined by fi;. 2-1.4.3 representin; the variation of the stress 
over time during five stress cycles. 
Fig. 2-1.4.3 - Variation of stress as a function of time during five stress cycles 
osup = upper suess 
oup max = maximum upper stress 
owp min = "nimum upper stress 
oinf = lower stress 
Gm = arithmetic mean of all upper and lower stresses dunng the total duration of use 
- In the case of mechanical components, om can be assumed to be Zero and the suesses inücduced 
into the calculation of the spectrum factor are then the total stresses occumng in the relevant 
section of the component. 
Note : Stress changes with values less than 10 % of the maximum stress are not to be considered 
for the calculation of the spectrum factor for structural or mechanical components. 
These small stress changes, as proved by experience, have no noticeable effect on the working life. 
2 - 1.4 .4 GROUP CLASSIFICATION OF COMPONENTS 
On die basis of their class of utilization and their suess spectrum class, components are classified 
in one of the eight groups E l , E2, ..., E8, defined in table T.2-1.4.4. 
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Considering the most common classes of utiiization and stress spcciruiii classcs. thc groups 
generally used ior rnain cornponents are E5 to E8. 
Tabie T.2-1.4.4 
COMPONENT GROUPS 
2 - 1 .5 HARMONIZATION OF CLASSIFICATION FOR THE COMPLETE 
MACHINE, COMPLETE MECHANISMS AND COMPONENTS 
(STRUCTURE AND MECHANISMS) 
Stress 
spectrum 
class 
P1 
P2 
P 3 
P4 
2 - 1 .5 .1 COMPLETE MACHINE 
The classification of the various mechanisiiis or components (of structurc or iiiechanisriis) 01' a 
given handliiig rnachine is denved irom tlie expected TOTAL DURATION OF USE (expressed in 
hours) of the macliine during its IiSetime whicli defines its GROUP. 
Class oS utilization 
The total duration of use (expressed i n hours) of the coinplete iiiachitie is tlic product of the threc 
following estirnated factors : 
- averagc number of actual service hours per day, 
- average number of actual service days per year, 
- number oidesired service years. 
B0 
EI 
E1 
EI 
EI 
2 - 1 .5 .2 COMPLETE MECHANISMS 
B2 
EI 
EI 
E2 
E3 
B1 
EI 
E1 
Ei 
E2 
From the total duration of use o i the machine the duration of use o i eacli complctc inechanisin is 
deiennined. This duration obviously depends on the operating iiiodc o i tlie macliinc aiid of tlie 
mechanism involved, and coi~esponds to a class ~Sutilization (T0 to T9). The conihination o i this 
class of utilization with tlie load spectrum class (L1 to L4) defines the niechanisiii group (MI 
to M8). The most commonly used groups will nornially be M4 to M8 ior tnain iiieclianisiiis. 
2 - 1 .5 .3 COMPONENTS 
B3 
EI 
E2 
E3 
E4 
The groups for structural or mechanical cornponents are dctermined as follows : 
B4 
E2 
E3 
E4 
E5 
B 5 
E3 
E4 
E 5 
E 6 
B 6 
E4 
E5 
E 6 
E 7 
B 7 
E5 
E6 
E 7 
E 8 
B 8 
E6 
E7 
E 8 
E 8 
B 9 
E7 
E8 
E 8 
E 8 
B I O 
E8 
ER 
E 8 
E 8 
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O FEM Section I1 2-13 
2-1.5.3.1 STRUCTURAL COMPONENT GROUPS 
On the basis of the frequency o i operating cycles (and tlierefore of rcpetition cycles) aiid tlic total 
duration of use of the machine, it is possible to calculate tlie total iiuinber o i tlie stress repetiiion 
cycles expected in the lifetinie of tiie machine and therefore to classify tlic structural coiiiponeiit iii 
one of the classes o i utilizaiion (B0 10 B 10). This is used. along with the spectruiii class (PI 
to P4) to select rhe component group(EI to Es). 
2-1.5.3.2 MECHANICAL COMPONENT GROUPS 
Dependant on tlie class o i uiilization of a coiiiplete mechanisiii to wliich a particulür coiiiponent 
belongs, the total number of stress cycles to whicli this componcni will he suhjccted iii tlie 
duration oiuse of tlie ineclianism caii be deteniiiiied. 
1t is iiot possible to give a general method ior detenniniiig tlie nuiiiher of stress cycles F ior a 
incchanical component, as the nuinber of stress cycles greatly depends upon tlie type o i load 2nd tlie 
fuiiction of tlie coiiiponent in a given ineclianisin. 
This applies to mechanism elements whicli. for eacli operating cycle. underpo stress variations 
corresponding to a cenain inultiple of the operatiiig cycle, ior exaiiipie. cai~iage wlieel axlcs, 
slewing hearings for rotating parts of tlie unit. 
In this case the nuniber of cycles per hour is : 
where : 
S p = nuniber of working cycles per opcrating hour 
ka = the iactor by which the number of operating cycles is multiplied wlien tlie meclianisiii 
element is subjected to several stress cycles for each operating cycle. 
Ex-mple : carriage wheel axle of a reclaiming uni1 where one working cycle includes tlie iollowing - 
rnovenients : 
I - iorward inoveiiient o i tlie uni1 with wheel load 
2 - slewing the booni 
3 - forward moveiiient of the unit with altered wheel load 
4 - boom return. 
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2-14 C FEM Section 11 
In this case : ka = 2, for a fixed axlc as tlie stress ciianpes only when the booin is slewed 
This group contains all rotating mechanism parts whicli are stressed by rotatiiig-bendiiig and 
shearing Stresses. l t also applies ro the bending and Hertzian siresses on toothcd geai-s. 
In rhese cases : 
Fh = ka . nill . 60 
where : 
nm = number of revolutions per niinute 
For tlie Hertzian stress of toothed gears, whose flanks are used oii botli sides. C.:. undcr-cariiages oi- 
slewing iiieclianisrns, it shall be coiisidered : 
From the nurnber of stress cycles to whicli tlie tnechanical coniponeiit will be subjected, a class of 
utilization (B0 to B10) can be deterniined. This is used, along with the speciruni class (PI to P4), 
to seleci thc component group (EI to E8). 
In this manner, all components or sets of coniponeiits are classilied in CROUPS repi-esenting the 
anticipaied service to be provided by ihose components. 
2-1 .5 .4 AN EXAMPLE OF THE CLASSIFICATION OF A MACHINE AND 
ITS COMPONENTS 
The classiiication and values given in this chapter niust only be considered as aii example. 
Tlie assumptions relating to particular design requireiiieiits and operating inethods are specific to 
Chis example and will vary according to the detailed design of tlie iiiacliinc, site cotiditions, working 
method, etc. 
This example is based on a combined stackeribucket-wheei reclaimcr for tlie handling o i ore aiid 
coal. 
Stacking capacity : 
Reclaiming capacity : 
Ore handling : 
Coal handling : 
3000 1/11 of ore - 2000 tlh «f coal 
2000 Uh of'ore - 1000 tih of coal 
213 of total tonnagc 
113 o i total tonnage 
Desired duratioii of use : 50,000 Iiours, i.e. CROUP A7 for the inachine as a wliolc 
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O FEM Sectioii I1 2-15 
Fron1 these parameters i t can be calculated that the niacliine will be used in the followiiig way : 
- Ore stacking = 10,500 Ii approx. (31.5 Mt) 
- Coal stacking = 7,900 h approx. (15.8 Mt) 
- Ore reclaiminf = 15.800 Ii approx. (31.5 Mt) 
- Coal reclaiming = 15.800 h approx. (15.8 Mt) 
= 50.000 h 
EXAMPLE OF GROUP CLASSIFICATION OF MECHANISMS AS A WHOLE 
*(I) Assuming : 31,600 Ii for reclaiming operation 
+ 1,900 h during 10 C/o of stacking operati«n 
*(2) Assuiniiig : 7,900 h continuous travel during coal stacking to ensure preliminary 
blending 
1,100 h travel during 10 C/o of stackiiip operation (iron ore) 
3,200 h travel during 10 70 of reclaim operation (5-6 secondslminute 
for advance) 
TOTAL : 12,200 h 
rounded to 12,500 21. 
*(3) Spectrum factors must be calculated on rhe basis of tlie loads applied during tlie wliole or 
relevant parts of the four rnain Service phases, i.e. ore stacking, coal stackiiif, ore reclaiming, 
coal reclaiming. 
Class oS 
utilization 
T8 
T8 
T8 
T5 
T6 
Spectrum 
Sactor 
I<,,] * (3) 
i.e. 0.76 
i.e. 0.45 
i.e. 0.80 
i.e. 1 
i.e. I 
Mechanism 
Reclaiming 
unit 
Booin 
conveyor 
Slewing 
Lifiing 
Travelling 
Total duration 
of use 
(11) 
3 1,600 
50,000 
33,500 
*(I) 
5,000 
12.500 
* (2) 
Spectruiii 
dass 
L4 
L3 *(4) 
L4 
L4 
L4 
GROUP 
M8 
M8 
M8 
M7 
M8 
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2-16 O FEhl Sectioii 11 
For the reclaiming unit for instance, if the loads created by coal reclaiming ariiount to 80 C/c 
of the loads created by ore reclaiming (corresponding to a maximurn load) for equal servicc 
times for ore and coal, factor km will be 0.5 + 0.8' . 0.5 = 0.76 approx. 
It shouid be noted that the most common spectrum class for these appiiances is ciass L4. 
*(4) Assuming a reversible boom conveyor, thc different duration of utilizatioii in rclatioii to thc 
total duration of utilization of the machine will be as follows : 
Storage o i iron ore = 0.21 out of a total of 
storage of coal = 0.158 1 50,000 Iiours of 
reclaiming ofiron ore = 0.316 1 scheduled utilization 
reclaiming of coal = 0.316 j 
If we consider that the mechanisin will be loaded at the niaximum valiie of I for tiie storage 
of iron ore, the ioads on the mechanism for the three otlier operations are for instance : 
0.74 for storage ofcoal and reclaiming OE iron ore 
0.53 for rcclaiming coal at the capacity o i 1000 tlh 
we have tlierefore : 
kn, = 0.449 and spectruin class L3 
It must be noted that, for a booin conveyor with a variable inclinatioii i t would be possible, 
for eacli of the four kiiids of utilizatioii, to calculate an average load for the driving 
niechanism as ii is obvious tliat the maximuiii loadiiig wlien staking material is supported 
only when the elevation of the handled product is inaximurii, i.e. witii tiie boom i n the 
highest position. 
Nevertheless, the. iiiteresr of this study appears only if it is possible to g« froni a stress lactor 
spectrum to a sinaller one, which is not the case for the exarnple above. 
When cliosing some components of the inechanism sucli as the gear box reducer. 
cotisideration may be given to the fact that tlie boom convcyor is reversible, whicli nieans 
that the reducer will be used 18,400 hours driving in one dircction and 31,600 hours in the 
opposite direction. 
CLASSIFICATION OF STRUCTURAL AND MECHANICAL COMPONENTS 
For structural coinponents it is necessaiy to detemiine tlic nuinber OE stress cycles to wliicli a givcn 
component will be subjected during the 50,000 h use of tiie machiiie. 
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O FEM Section I1 2-17 
A stmctural component will therefore belong to a group (generally E5 to E8) depending esscntially 
on its position in the machine. 
As regards mechanical components, it is also necessary to determine the number of stress cycles to 
which each part will be subjecred during the use of the mechanism as a whole, e.g. thc sleu, drive 
pinion can be classified as follows : 
- given rotating speed 2 rpm, hence F = 112 . 2 . 60 = 6011i 
number of hours of utilization = 33,500 
hense expected stress cycles = 33,500. 60 = 2.01 . 10" 
class of utilization = B8 
spectrum class = P4 
(according to spectrum factor of approx. 0.8, siiiiilar to spectruiii factor OS slewitig iiiechaiiisiii) 
hense group classification EX. 
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2-18 G FEM Section I1 
2-2 LOADS ENTERING INTO THE DESIGN OF STRUCTURES 
Tliestructural calculations shall be undenaken to determine tlie Stresses developed i n an appliance duriiig 
its operation or when out of ser~rice witii maximuni wind conditions. These strcsscs shall he calculated oii 
tlie basis o i the loads defined below. 
Dependinf on their frequency, the loads are divided into three difierent load catcgories : iuain loads. 
additional loads and special loads. 
a) The main loads include all the pemianent loads which occur wlien tlie equipment is used under iioriiial 
operating conditions. 
They mainly are : 
- dcad ioads, 
- material loads, 
- incrustation, 
- iiorinal tangential and lateral digging forces, 
- iorces on tlie conveyor(s), 
- peniiatient dynamic effects, 
- inclination of the working level. 
h) n i e additional Ioads are loads [hat can occur intermittently durinp operation OS tlic equipiueiit oi- wlieti tlie 
equipment is not working ; these loads can either replace certain inain loads or he additional io tlie iiiain 
loads. 
They are. among othcr : 
- wind load for inachine in service, 1 
- snow and ice loads, 1 climatic efiects 
- temperature eifects, J 
- abnonnal tangential and lateral diggiiig forces, 
- bearing iriction and rolling resistances, 
- reactions pependicular to the rail due to uavelling (skewing efiect), 
- non pernianent dynaniic effects. 
c) The special loads comprise those loads which should not occur during and outside tlie operatioti o i the 
equipinent but the occurence of whicii is not to be excluded. 
They include : 
- clogging of chutes, 
- resting of the reclaiming device or the boom, 
- iailure oiload limiting devices (see 2-2.1.2. I), 
- hlocking of travelling devices, 
- lateral collision of the buckei-wheel with the slope, 
- wind load on niachines out of service, 
- huifer effects, 
- loads due to earthquakes, 
- loads during erection (or dismantling) of tlie machine. 
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O FEM Section I1 
2 - 2 . 1 MAIN LOADS 
2 - 2 . 1 . 1 DEAD LOADS 
Dead loads coiisist of all loads of constant niagnitude and position on the inacliine. wliicli aci 
pcmanently on the siructure or memher heing designed. 
N«le : It sliould be noted tliat stairs. platforms aiid gangways on whicii equipiiient caii he placed 
inust he calculated to bear 3 kN of "patch load" (on an assuminf area of 0.5 x 0.5 m). Access and 
garigways only used as passage ior people are calculated to bear 1.5 hNIiii, and tIie railinfs and 
guards to stand 0.3 kN of liorizontal load. 
When higher loads are to be supponed temporarily by platforiiis, the latter niust bc designed aiid 
sized accordingly. Platforms of large size niust be vcrified with a load o i at least I hNini2. 
Dead loads inciude tlie structure of stairs, gangways, ctc, but exclude loads «n stairs, gangways, etc. 
wliich are to bc considered as local loads for tlie dcsipn OS tlicse stairs. gangways, etc. but no lor 
the desipn of tlie structure as a wliole. 
2 - 2 . 1 . 2 MATERIAL LOADS 
Tlie material loads camied on con\,eyors aiid reclaiiiiing deviccs are to bc considered as follows : 
2-2.1.2.1 MATERIAL LOAD CARRIED ON THE CONVEYORS 
These loads a e detennined from the design capacity (iii~lli) and tiie iiiaxiniurn corresponding bulh 
density specified by the custoiner. 
I) Units with no hiiilt-in reclaimine device 
a) Wliere the belt load is limited by autoniatic devices, tlie load on tlie conveyor \r,ill be assuined to be 
that which results froiii the capacity thus iimilcd. 
b) Where there is no capacity limiter, the design capacity is tliat resulting froiii the iiiaxiinum 
equivalent cross sectional area of the material oii tlie conveyor multipiied by thc conveyiiig Speed. 
Uiiless otherwise specified in the contract, this cross sectional m a sliall be detemiined assuming a 
surcharge angle 8 = 20' and considering a surcliarge a e a according to 1SO 5048 "Continuous 
mechanical handling equipment - Belt conveyors witli canying idlers - Calculatioii of operating 
power and tensile forces". 
The diagrams 2-2.1.2.1 Iiereafier give the cross sectional a e a to be considered for dilTerent belt 
conveyor designs. 
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Fig. 2-2.1.2.1 - Belt convevor cross-sections 
a ) With one carryiny idier 
b) With two carryiny idiers 
i_ 13 J 
C ) With three carrying idiers 
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O FEM Section I1 2-21 
c) Where tlie design capacity resulting from b) on tlie upstream units is lower tlian tliat of 
downsiream units, the downstream units may have the sanie capacity as the upstream iinits. 
2) Units fitted with bucket-wheel or buckei chain as reclaimino device 
a) Where there is no capacity limiter, the design volumetric capacity shall be takeii as I .5 tiiiies tlie 
iiominal filling capacity of the buckeis niultiplied hy tlie maximuiii nunibcr of discliarges. 111 tlie 
case of bucket-wheels, the factor 1.5 (wliich takes into account tlie volumes wliicli ca i~ he filled i n 
additioii to the buckets), can be replaced by taking into account the actual fill value additioiial to ilie 
bucket volurne. 
b) Where there are automatic capacity limiters, the design capacity shall be ihe capacity tlius liiiiited. 
Where the uni1 is to be used to convey materials OE different bulk densities (1.01 exaiiiple coal anti 
ore) safcty devices shall be provided to ensure that thc calculated loads will 1101 be exceeded witli the 
heavier material. 
3) Dvnamic load factor 
To account for the dynainic loads with can be appiied to tlie conveyor iii transporting the material. 
the material loads defined above must he multiplied by tlie factor 1 .I 
2-2.1.2.2 LOADS IN THE RECLAIMING DEVICES 
To take into account the weight of the n~aterial to be conveyed i n ihe reclaiiiiing de\,ices i t can be 
assumed tliat, typically : 
a) for hucket-wheels : 
- 114 of all availahle buckets are full ai 100 %, 
b) for bucket-chains : 
- 113 of alt the buckets in contact with the Sace are 33.3 5% full, 
- 113 of all the buckets in contact with the Sace are 66.7 '% Sull, 
- all other buckets up to the sprocket are I00 '% full. 
2-2.1.2.3 MATERIAL IN THE HOPPERS 
The weight of the material iii hoppers is obtained hy rnultiplying thc bulk density of thc inatcriai 
by the volume (filled to the brim). 
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2-22 O FEM Sect~oii 11 
Wliere the weiglit of the niateriai is limited by reliablc aulornatic controls; deviation froiii the 
above-mentioned vaiue is pemissible. 
2 - 2 . 1 . 3 INCKUSTATION 
The d e g w of incrustation (din accumulaiion) depends on the specific iiiaterial aiid operating 
conditions prevailing in each given case. 
The data which follow are to be takeii as a guide. and are generally applicablc t« stockyards 
machines. 
For cxcavating equipmenr they ai'e to be taken as iiiinimuni values. 
Unless experience in particular cases or customer's requirenicnts specify otlierwise. tlic loads due to 
dirt accumulaiion that should be taken into account are : 
a) on the conveying dcvices 10 % ofthe material load calculated according to 2-2.1.2, 
b) for bucket-wlieels the equivalent weiglit of a 5 cni thick layer of inaierial o i iiiaxiniuiii specified 
bulk density on the centre of the bucket-wheel considered as a solid disc up to the curtiiig circle, 
c) for bucket-cliaiiis 10 W of the design material load calculated accordin~ to 2-2.1.2, uniforiiily 
distributed over the total lengtli ofthe ladder. 
2 - 2 . 1 . 4 NORMAL TANGENTIAL AND LATERAL DIGGING FORCES 
Tliese forces are to bc calculated as concencated loads, i.e. on bucket-whcels as acting at tlie most 
uniavourable point of tlie cutting circle, on bucket-cliains as actiiig at a point oiie-third «f tlie way 
along the part of tlie ladder in contactwith the face. 
a) Normal tangential digging force 
For excavators and, in general, for machines for which the digging efiort is largely uncertain, the 
normal digging forcc acting tangentially to the wheel cutting circle or in tlic direction of tiie 
bucket-chain is obtained from the nominal rating of the drive rnotor, the efficieiicy of tlie 
transniission gear, the circumferential speed of the cutting edge, and the power iiecessai-y to lift 
the material, and in the case of bucket-ladders from tlie power iiecessar)' to iiiove tlie loaded 
bucket-chain. 
To calculate the lifting power, thc figures indicated in 2-2.1.2.2 inust be used 
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O FEM Section I1 2-23 
For Storage yard applications, tlie above method of calculation inay be ignored if tlie digpiiig 
resistance of the material is accurately known as a result of tests and if it caii be guaianteed that 
this digging resistance will not be exceeded during normal operation. 
b) Normal lateral digging force 
Unless otherwise specified. the normal lateral digging force can be assumed as 0.3 tiiiies tlie values 
of tlie nonnal tangential digging force. 
2 - 2 . 1 . 5 FORCES ON THE CONVEYOR(S) 
Belt tensions, cliain tensions, etc. must be taken iiito consideration for tlie calculatioii as Par as tliey 
Iiave aii effect oii the structures. 
2 - 2 . 1 . 6 PERMANENT DYNAMIC EFFECTS 
a) In generai tlie dynamic effect of the digging rcsistances. tlic falliiig iiiasses at thc transfcr poiiits. tlie 
rotating pans of machinery, the vibratinp feeders, etc. need only be considered as aciiiig locally. 
h) The inertia forces due to acceleration and braking of rnoving structural parts must bc takeii into 
account. These can be neglected for appliances workiiig outdoors if tlie acccleratioii and deceleration 
are < 0.2 mis'. 
If possible tlie drive iiiotors and brakes must be designed in sucli a way tliat tliis acceleration value 
0.2 mis? is not exceeded. 
If the number of load cycles caused by inertia forces due to acceleration and braking is lower tlian 
2 x IO'during tlie lifetime of the machine the effects sliouid be coiisidercd as additional loads (sec 
2-2.2.7). 
2 - 2 . 1 . 7 LOADS DUES T 0 INCLINATION OE WORKING LEVEL 
Iii cases where the working level is inclined, dead loads acting vertically sliould be resoived into 
components aciing perpendicularly aiid parallel to tlie working plane. 
The slope related loads should be determined for the maxiiiium slopc contractually defined and rlieii 
increased by 20 % for the calculation purposes. 
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2 - 2 . 2 ADDITIONAL LOADS 
2 - 2 . 2 . 1 WIND ACTION 
This clause relates to wind loads on the structure of handling machines 
11 gives a siniplified method of calculation and assumes tliat the wind can hlow horizontaliv fiom 
aiiy direction, that the wind blows at a constani velocity and that thcre is a static rcaction to tlic 
Ioadings it applies io the cran structure. 
Tlie wind effects shall be considered for the macliine in service (sec 2-2.2.1.2) aiid for tlic iiiacliinc 
out of servicc (2-2.3.6). Uniess otherwise specified due to local c«iid~ti«iis. tfie dcsign wind s~xed 
given in tliese chapters should he used. 
2-2.2.1.1 AERODYNAMIC WIND PRESSURE 
Tiie aerodynamic wind pressure q, in relation wiih tlie air derisity and ilie wind specd Vs. is giveii 
hy tlie forinula : 
q = the aerodynamic pressure Nini' 
Vs = the design wind speed in ids . used for tlie calculation and depending oii tlie load case 
p = air density in kglm, 
Uiider normal conditions, will) p = 1.225 kplnfi tlie forriiula becoines : 
2-2.2.1.2 IN SERVICE WIND 
a) Maximum in service wind 
Tliis is the maximum wind in which the inachinc is desifned to operate. Tlie wind loads m 
assunied to be applied in the least fa\rourable direciion in conibination with tlie appropriate service 
loads. 
For calculation and unless specified otherwisc, a inaximum desigii wind speed 
V, = 20inIs = 72 knilh (coiistant over the heighi of the machine) shall be assumed for ihe 
machine in operation. 
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O FEM Section 11 2-25 
Tlie corresponding pressure q is 250 Nimi ( 1 j 
b) Eauivalent averaoe iii service wind 
For wear or fatigue calculations on mechanisnis for exaniple, an aerodynamic wind pressure equal to 
of the maximum working aerodynamic pressure should be assuiiied. 
This equivalent aerodynaniic pressure is assunied to he applied during the wliole design lifetiiiie of 
thc mechanisni and to cause the sainc wear or fatigue effects as the actual effects of service vr~irids 
whose aerodynamic pressures will v a v between 0 and the maxiinum workins acrodynaiiic 
pressure. 
It should be noted that tliis equivalent aerodynamic prcssure for wear calculations corrcspoiids to a 
wind speed equal to approximately 60 Cn of the design maximum peniiissible spced of tlic service 
wind. 
C) Start-up must always be possible agairist maximuin in service wiiid, but it is assuiiied thai tlie 
operating speeds aiid nominal accelerations are not necessarily reaclied under rnaxiiiiuiii in seivicc 
wind conditions. 
dj Under certain circumstances, an appliance niay Iiave to go back, uiiloaded. to "out of service" 
anclioring positions. In such cases, travelling meclianisms should be diriiensioned in relation to tlie 
maximuni permissible aerodynamic wind pressures defined in thc specifications for tliis load case, 
and dependant on the niacliiiie surface exposed to the wind, tlie inacliine niay need to bc placed in a 
configuration designed ior such transfer. 
2-2.2.1.3 WIND LOAD CALCULATIONS 
a) The nlane of tlie exnosed parts nlaced nemendicularlv to tlie wind direction 
For most coinplete or part structures, md individual riieinhers uscd iii structurcs, tlie wind load is 
calculated from : 
F = A . q . C r 
for a wind blowing perpendicularly to the exposed plane ofthc componeiits. 
( 1 ) Where a wind speed measuring device is to be attacbed to an appliance, it sliall normally he pkaced 
at the niaximuni height. In cases where tlie wiiid speed at a different levcl is more significant to tlie 
safety of the appliance, the iiianufacturer shall state tlie heigt at which tlie device shall be placed. 
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where : 
F is the wind load in N 
A is the effective frontal area of the part under consideration in m' 
q is the aerodynamic wind pressure corresponding to the appropriate design condition in N/m2 
Cf is the shape coefficient for the part under consideration. 
Note : shape coefficient is differently named in some docurnents, 
The total wind load on die structure is taken as the sum of the loads on its component pans 
In determining strength of the appliance and safety requirements against ovenurning and drifting the 
total wind load shall be considered (see 3-6 and 3-7). 
b) n e plane of the exnosed parts ~ laced non perpendicularlv to the wind direction (inclined boom for 
m&c& 
Where the wind blows at an angle 0 to the longitudinal axis of a member (see fig. 2-2.2.1.3) : 
The load in the duection of wind is : 
F = A . q . C f . s i n 2 0 
- The load in the diiection perpendicular to the wind diiection is : 
F 1 = A . q . C f , sin 0 . cos 0 
The load in the direction perpendicular to the longitudinal axis of the member is the resultant of 
F and F 1 and is : 
fig. 2-2.2.1.3 
wind 
__f 
A' = L.b or L.D 
L = lenght 
b = width 
D = diameter 
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2-28 6 FEM Seciioii I1 
Tlie wind load on single lattice girders iiiay be calculatedon tlie basis of the coefficients for the 
individual members given in the top part of table T.2-2.2.1.4.1. In this case thc acrodyriaiiiic 
slendemess of each inernber shall be takeii into account. Alternatively the overall coeficients for 
latrice girders constructed of flat sided and circular sections givcn i n ilie iniddle part of tlie table iiiay 
bc used. 
Wliere a lattice girder is niade up of flat-sided or circular sections. or of circular scctioiis iii botli 
flow regimes (D . V s < 6 mils and D . V s 2 6mlis) tlie appropriate sliapc cocificieiits 
applied to the ci~rrespoiiding frontal areas. 
Wliere gusset plates oE normal size are uscd in weldcd latticc construction no allowaiice Tor tlic 
additional area prcsenred by thc plates is necessmy, provided the iengths of indi\,idual iiienibeis an: 
taken between the ccntres of iiode points. 
Shape coefficients obtained from wind-tunnel or full-scalc tests iuay also be used. 
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T.2-2.2.1.4.1 
SHAPE COEFFICIENTS 
* see figure 2-2.2.1.4.2 
Type Description 
Rolied sections J ] 
Rectangular hollow 
sectioiis up to 356 mrn 
Square 
and 254 X 457 min 
rectans!ulai. 
Single 
lattice 
güders 
Machinery 
houses 
etc. 
Aerodvnamic slenderness Ilb or IID * 
< 5 
1.15 
1.4 
1.05 
Flat-sided sections 
Circular sections where 
D.Vs < 6 m2/s 
D.VS 2 6 in2/s 
Closed rectangular 
structures 
I .60 
1.10 
0.80 
1.30 
10 
1.15 
1.45 
1.05 
20 
1.3 
1.5 
1.2 
30 
1.4 
1.55 
1.3 
40 
1.45 
1.55 
1.4 
I 
50 
1.5 
1.55 
1.5 
>SO 
1.60 
1.6 
1.6 
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2-30 O FEM Section I1 
Figure 2-2.2.1.4.2 
DEFINITIONS : AERODYNAMIC SLENDERNESS SOLIDITY RATIO SPACING RATIO 
AND SECTION RATIO 
(I) Aerodynamic slendemess = 
lenpth of member 1 - - * I 
breadth of section across wind front - b 
or - * 
D 
* In lattice construction the lengths of individual members are taken between the centres of 
adjacent node points. See diagram below. 
area of solid pans A 
(U) Solidity ratio = 
enclosed area A, , 
(111) Spacing ratio = 
distance between facing sides a - - a 
breadth of members across wind front - b Or B 
for "a" take the smallest possible value in the geometry of the exposed face. 
(N) Section ratio = breadth of section across wind front b - - 
depth of section parallel to wind flow - d 
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O FEM Section I1 2-31 
b) Sliieldins factors for multiple eirders or inemhers 
Where parallel girders or memhers are positioned so tliat shielding takes place, tlie wind loads on 
the windward girder or member, and on the unsheltered pans of those behind it. are calculated usiiig 
the appropriate force coefficients. The wind load oii the sheltered parts is multiplied by a shieidiiig 
factor q given in table T.2-2.2.1.4.3. Values of q vaty witli the solidiiy and spacinf ratios as 
defined in figures 2-2.2.1.4.2. 
Tahle T.2-2.2.1.4.3 
SHIELDING COEFFlCIENTS q 
Wliere a number of identical girders or members ase spaced equidistantly beliind each otlier in such a 
way that each girder shields those beliind it, the shiediing effect is assumed to iiicrease up to tlie 
ninth girder and to remain constant thereafter. Tlie wind loads ase calculated as follows : 
Spacing ratio 
ab 
0.5 
1 .0 
2.0 
4.0 
5.0 
6.0 
On the Ist. girder F ] = A.q.Cf 
On the 2nd. girder F2 = q.A.q.C{ 
Solidity ratio A/Ae 
On the nth girder FI1 = q ( ] i - l ) . ~ . ~ . C ~ 
(where n is from 3 to 8) 
0. I 
0.75 
0.92 
0.95 
1 
1 
1 
On the 9th and 
suhsequent girders Fg = q!A.q.Cf 
The total wind load is thus : 
0.2 
0.4 
0.75 
0.8 
0.88 
0.95 
1 
Where there are up to 9 girders Ftotal = [ l + q + q b q 3 + +.. + ] A.q.Cf 
= A.~.C~*) 
1 - ? 
in N 
0.3 
0.32 
0.59 
0.63 
0.76 
0.88 
I 
0.4 
0.21 
0.43 
0.5 
0.66 
0.81 
1 
0.5 
0.15 
0.25 
0.33 
0.55 
0.75 
1 
2 0.6 
0. I 
0. I 
0 .2 
0.45 
0.68 
1 
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2-32 O FEM Section I1 
Where tliere are more ihan 9 girders Ftotal = [I + + q' + q3 + ... + V % (11 - 9)11" 1.q.Cf 
= ~ . q . ~ f [ @ ) i ( n - 9 ) q ~ ] in N 
1 - r l 
Note : - 
The lern] used in the above formula is assumed to have a iou~es limit o i 0.10. 11 is tahen as 0.10 
when ever 
I.attice towers 
For calculating the "face-on" wind load on square towers in the abscnce of a detailed calculatioii. tlie 
solid area of the wiiidward face is iiiultiplied by the following overall Force coefficient : 
For towers composed of flat sided sections l.7.(1 tq) 
For towers composcd of circular sections 
where D.Vs < 6 m21s l . l . ( l + q ) 
where D.Vs 2 6 m21s I .4 
The value of q is takeii from tablc T.2-2.2.1.4.3 ior alb = 1 according to the soiidity ratio of tlic 
windward face. 
The maximum wind load on a Square tower occurs when tlie wind blows on to a corner. In tlie 
absence of a detailed calculation, this load caii be considercd as I .? tiilies tliat dcvelopd uritli 
"face-oii" wind on one side. 
2-2.2.2 SNOW AND ICE LOADS 
For teinperate areas, normal snow and ice loads can be assunied to have been included in tlie 
allowances for incrustation calculated in section 2-2.1.3. 
For niachines in a rea with severe cliiiiatic coiidiiioiis, or whese specified by ihe purchaser, 
consideration should be given to the additional loads arising fiom snow arid ice. 
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O FEM Section I1 2-32 
2 - 2 . 2 . 3 TEMPERATURE 
Temperature effects need only by considered in special cases, e.g. for areas with extreme climatic 
conditions or when using matedals with different expansion coefficients witliiii tlie sanie 
component that are not free to expand or contract separateiy. 
2 - 2 . 2 . 4 ABNORMAL TANGENTIAL AND LATERAL DIGGING FORCES 
The abnormal digging force acting tangentially to tiie bucket-wlieel or in tlie direction of the 
bucket-cliain, is calculated from thc staning torque of the drive motor or from the cut-off torque of 
the built i n safety coupling taking into account tlie more unfavourable of the two cases listed 
below : 
a) If the wheel or chain is not loaded : 
In this case no account is taken of the power necessary to liil andlor niove rlie material and tiie load 
due to the staniiig or cut-off torque of 1Iie motor is coiisidered as a digging load. 
b) If the whcel 01 chain is loaded according to 2-2.1.2.2, in this case tiie digging power caii be ieduced 
hy the power required to lift andlor move the material. 
The abnormal lateral digging force is calculated as in 2-2.1.4.2 (b) thereby coiisidering a load of 
0.3 times tlie abnomial tangential digging force. 
If appropriate, this load can be calculated from tlie working lorque of aii existing cut-out device of 
the slewing or travelling mechanism and which should bc at least equal to 1 . I times the suin of the 
torques due to the inclination of the macliine (see 2-2.1.7) and to wind load for machiiies in 
operation (see 2-2.2.1.2). 
Where a torque limit device is installed on the slewing inechanism; the iiieclianisni niust bc 
equipped with a locking device preventing the slewing pari rotating when out of service (due to 
wind force) if this rotation is dangerous. 
2 - 2 . 2 . 5 BEARING FRICTION AND ROLLING RESISTANCES 
a) Frictional forces need only to be calculated where they influence tlie size of structural coinponents. 
Foilowing friction coefficient can be used in default of inore precise vaiues bascd oii suppliers' 
specifications : 
- for pivots aiid ball bearings 
- for structural pans with sliding frictioii 
- on wheels of rail-mounted machines 
- on wheels of crawler-mounted macliines 
- hetween plate base and ground (crawler, shiftable conveyors) 
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2 - 2 . 2 . 6 REACTION PERPENDICULAR T 0 THE RAIL DUE T 0 
TRAVELLING OF THE APPLIANCE (LOAD CAUSED B Y 
SKEWING) 
For appliances oii rails account must be takeii of tlie reactioiis resulting froiii tlie traveliiiig 
movement of the unit under a skewin: angle, giving rise io a Iioriz«ntal guidc Force H! directcd 
perpcndicularl)~ lo tlie rail. 
The force Hy caii act on any guidin; device (flange O E wlieei oi- scpzate guiding wlieel) aiid is ii i 
equilibriuni witli the horizontal friction forces acting heiween u~heels aiid rails. 
To calculate the force Hy tlie relevant systein propcrties sliall he iahen into account (see ISO 8686 
clause 6.2.2 and annex F). 
If no accuratc calculaiioii can be effected tlie force Hy sliould be takeii as : 
wliere Vy is tlie inaxiinum vertical load O E the wheel or bogie 
2 - 2 .2 .7 NON-PERMANENT DYNAMIC EFFECTS 
Inertia forces (due to tlie acceleration and braking of moving structural paits) w,liicli «ccur less tlian 
2 . 10' titnes during the lifetime OS the appliance should he cliecked as additional loads. Tlicy triay 
be disregarded if tlieir effect is less tlian the wind force during operation as defiiied i n 2-2.2. I 
If the inertia forces arc sucli tliat they have 10 bc takeii iiito account, tlic wind effect caii Ix 
disregarded. 
Note : As these f«rces are, in practice, present at tlie same tiine as tlie wind effects, it inust be - 
noted that actual accelerating and braking times are not tlie saine as whcti still conditiotis prevail. 
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O FEM Section I1 
2 - 2 . 3 SPECIAL LOADS 
2 - 2 . 3 . 1 CLOGGING OF CHUTES 
The weight of material due to clogging should be calcuiated using a load wliich is equivalcnt to the 
capacity of the chute in question, with due reference to the angle of repose. The actual bulk dcnsity 
inust be taken for calculation. 
2 - 2 . 3 . 2 RESTING OE THE RECLAIMING DEVICE OR THE BOOM 
Where safety devices arc installed such as a siack rope detector for rope suspensions or pressurc 
switches for hydraulic Iioists, wliich prevent the full weight o i tlie reclainiiiig device or the booiii 
from coming to rest, the permissible resting force is to he calculared as a special load at 1.10 times 
the value sei by the safety device. 
Where such saiety devices ai.e not provided, the special load is to be calculatcd witli tlic full resting 
weight. 
2 - 2 . 3 . 3 FAILURE OF LOAD LIMITING DEVICES AS IN PARAGRAPH 
2 - 2 . 1 . 2 . 1 
In tlie case of iailure on thc part o i an auioinatic load liinitiiig to liinit tiie useful loads on tlic 
conveyors, the output can be calculated as follows : 
a) iii the case o i appiiances withoui reclaiming device according 10 paragrapli I) (61, of iteiii 
2.2.1.2.1, 
b) in the case of appliances witli built-iii reclaitning device according ia paragrapli 2) (a), of iteiii 
2-2.1.2.1. 
For this purpose account need not be taken of the dynaiiiic iactor 1.1 
2 - 2 . 3 . 4 BLOCKING OF TRAVELLING DEVICES 
The design of rail-mounted equipment must take into accouiit the likelihood of bogies being 
blocked, e.g. by derailment or rail fracture. For tlie loads occurring under such conditions, tlie 
coefficient of friction between driven wheels and rails should be calculated as = 0.20 provided 
that the drive motors can generate sufiicient torque. 
For equipment mounted on fixed rails, a wheel can be considered as blocked which cannot rotate but 
slides on the rail. 
For equipment mounted on relocatable rails, blocking of a canying wlieel or bogie should bc 
assumed as resulting froin derailment or rail fracturc. The maximum motive force is then 
determined by tlie non blocked wheels aiid it cannot exceed tlie force transferable by raivwheel 
friction. 
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O FEM Section I1 2-37 
The calculation procedure is detailed in chapter 2-2.2. I. I (in service wind) 
Where machines are to be permanently installed or used for extended penods in areas wliere wind 
conditions are exceptionally severe, the above figures may be niodified by agreement between the 
manufacturer and purchaser in the light of local meteorological data. 
2 -2 .3 .7 BUFFER EFFECTS 
For horizontal speeds below 0.7 mis no account sliall bc taken of buffer effects. For speeds i n 
excess of0.7 ni/s account must be taken of the reaction on tlie structure by collisions witli buffers. 
when buffering is not made impossible by special devices. 
It shail be assuined that the buffers are capable of absorbing tiie kiiietic energy of the machine with 
operating load up to a certain fraction of tlie rated traveliing speed V, ; this fraction is iixed at 
minimum 0.7 V,. 
The resulting loads on the structure sliall be calculated iii tertns of the deceleratioii itnparted to tlie 
macliine by the buffer in use. 
2 -2 .3 .8 LOADS DUE T 0 EARTHQUAKES 
In general tlie süuctures of handiing appliances do not have tobe cliecked for seisniic effects. 
However, if local regulations or particular specificatioiis so prcscribe, special rules oi 
recommendations must be applied in areas subject to earthquakes. 
The supplier shall be advised of this requiremeiit by the User of the iiistallation who shall also 
provide the corresponding seis~nic spectra. 
2 -2 .3 .9 LOADS DURING ERECTION (OR DISMANTLING) OF THE 
MACHINE 
In general, the loads during erection are less than tbey will be For the iiiaciiine in operation 
Nevertheless, in some particular situations, according to the erection process, it can be iiecessary to 
check some structural (or mechanical) parts for a cenain stage of the erectioti. 
The checking is made by taking into account the actual supporting conditions and the eventual 
anchorages of the given structural pari. 
The permissible Stresses are : 
- stress allowed in case I for no wind condition 
- stress allowed in case 111 for out of service wind condition 
File is licenced for VALE S/A - Order-no: 404705 - 1License(s)
http://www.vdma-verlag.com/home/
2-38 0 FEM Section 11 
2-3 LOAD CASES FOR STRUCTURAL DESIGN 
Tiie inain, additional and special loads mentioned in chapter 2-2 niusi be combined in load cases I. I1 üiid 
I11 according to table T.2-3.1 hereaiter. 
Loads should only be combined that can occur simultaneously to piovide the higliest rcsultaiii siresscs. 
We shall retain for case I11 the most unfavourable combination. 
2 - 3 . 1 TABLE OF LOAD CASES 
(see table on iollowing page). 
File is licenced for VALE S/A - Order-no: 404705 - 1License(s)
http://www.vdma-verlag.com/home/
T
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