EN 13001-3-6:2018

SLOVENSKI STANDARD
01-julij-2018
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Cranes - General design - Part 3-6: Limit states and proof of competence of machinery -
Hydraulic cylinders
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Appareils de levage à charge suspendue - Conception générale - Partie 3-6 : États
limites et vérification d'aptitude des éléments de mécanismes - Vérins hydrauliques
Ta slovenski standard je istoveten z: EN 13001-3-6:2018
ICS:
23.100.20 +LGUDYOLþQLYDOML Cylinders
53.020.20 Dvigala Cranes
2003-01.Slovenski inštitut za standardizacijo. Razmnoževanje celote ali delov tega standarda ni dovoljeno.

EN 13001-3-6
EUROPEAN STANDARD
NORME EUROPÉENNE
February 2018
EUROPÄISCHE NORM
ICS 23.100.20; 53.020.20
English Version
Cranes - General design - Part 3-6: Limit states and proof
of competence of machinery - Hydraulic cylinders
Appareils de levage à charge suspendue - Conception Krane - Konstruktion allgemein - Teil 3-6:
générale - Partie 3-6 : États limites et vérification Grenzzustände und Sicherheitsnachweis von
d'aptitude des éléments de mécanismes - Vérins Maschinenbauteilen - Hydraulikzylinder
hydrauliques
This European Standard was approved by CEN on 13 November 2017.

CEN members are bound to comply with the CEN/CENELEC Internal Regulations which stipulate the conditions for giving this
European Standard the status of a national standard without any alteration. Up-to-date lists and bibliographical references
concerning such national standards may be obtained on application to the CEN-CENELEC Management Centre or to any CEN
member.
This European Standard exists in three official versions (English, French, German). A version in any other language made by
translation under the responsibility of a CEN member into its own language and notified to the CEN-CENELEC Management
Centre has the same status as the official versions.

CEN members are the national standards bodies of Austria, Belgium, Bulgaria, Croatia, Cyprus, Czech Republic, Denmark, Estonia,
Finland, Former Yugoslav Republic of Macedonia, France, Germany, Greece, Hungary, Iceland, Ireland, Italy, Latvia, Lithuania,
Luxembourg, Malta, Netherlands, Norway, Poland, Portugal, Romania, Serbia, Slovakia, Slovenia, Spain, Sweden, Switzerland,
Turkey and United Kingdom.
EUROPEAN COMMITTEE FOR STANDARDIZATION
COMITÉ EUROPÉEN DE NORMALISATION

EUROPÄISCHES KOMITEE FÜR NORMUNG

CEN-CENELEC Management Centre: Rue de la Science 23, B-1040 Brussels
© 2018 CEN All rights of exploitation in any form and by any means reserved Ref. No. EN 13001-3-6:2018 E
worldwide for CEN national Members.

Contents Page
European foreword . 4
Introduction . 5
1 Scope . 6
2 Normative references . 6
3 Terms, definitions and symbols . 7
3.1 Terms and definitions . 7
3.2 Symbols an abbreviations . 7
3.3 Terminology . 10
4 General . 12
4.1 Documentation . 12
4.2 Materials for hydraulic cylinders . 12
4.2.1 General requirements . 12
4.2.2 Grades and qualities . 13
5 Proof of static strength . 13
5.1 General . 13
5.2 Limit design stresses . 15
5.2.1 General . 15
5.2.2 Limit design stress in structural members . 15
5.2.3 Limit design stresses in welded connections . 16
5.3 Linear stress analysis . 16
5.3.1 General . 16
5.3.2 Typical load cases and boundary conditions . 16
5.3.3 Cylinder tube . 18
5.3.4 Cylinder bottom . 19
5.3.5 Piston rod welds . 20
5.3.6 Cylinder head . 21
5.3.7 Cylinder tube and piston rod threads . 21
5.3.8 Thread undercuts and locking wire grooves . 21
5.3.9 Oil connector welds . 22
5.3.10 Connecting interfaces to crane structure . 22
5.4 Nonlinear stress analysis . 23
5.4.1 General . 23
5.4.2 Standard cylinder with end moments . 23
5.4.3 Support leg . 23
5.5 Execution of the proof . 24
5.5.1 Proof for load bearing components . 24
5.5.2 Proof for bolted connections . 24
5.5.3 Proof for welded connections . 25
6 Proof of fatigue strength . 25
6.1 General . 25
6.2 Stress histories . 25
6.3 Execution of the proof . 27
6.4 Limit design stress range . 27
6.5 Details for consideration . 27
6.5.1 General . 27
6.5.2 Bottom weld. 28
6.5.3 Notch stress at oil connectors . 30
6.5.4 Cylinder head . 31
6.5.5 Piston rod . 33
6.5.6 Cylinder head bolts . 35
6.5.7 Cylinder head flange weld . 35
6.5.8 Mechanical interfaces . 37
7 Proof of elastic stability . 37
7.1 General . 37
7.2 Critical buckling load . 37
7.3 Limit compressive design force . 39
7.4 Execution of the proof . 40
Annex A (informative) Critical buckling load for common buckling cases . 41
A.1 General . 41
A.2 Buckling case A . 42
A.3 Buckling case B . 42
A.4 Buckling case C . 43
A.5 Buckling case D . 43
A.6 Buckling case E . 43
A.7 Buckling case F . 43
A.8 Buckling case G . 44
Annex B (informative) Second order analysis of two important cases . 45
B.1 Compressed cylinder with end moments and angular misalignment . 45
B.2 Compressed cylinder with lateral end force and angular misalignment . 46
B.3 Axial stresses for cases in B.1 and B.2 . 47
Annex C (informative) Shell section forces and moments for cylinder bottom . 48
Annex D (informative) Fatigue analysis of bottom weld for more complex cases . 51
Annex E (informative) Selection of a suitable set of crane standards for a given application . 54
Annex ZA (informative) Relationship between this European Standard and the essential
requirements of Directive 2006/42/EC aimed to be covered . 56
Bibliography . 57
European foreword
This document (EN 13001-3-6:2018) has been prepared by Technical Committee CEN/TC 147 “Cranes
— Safety”, the secretariat of which is held by BSI.
This European Standard shall be given the status of a national standard, either by publication of an
identical text or by endorsement, at the latest by August 2018, and conflicting national standards shall
be withdrawn at the latest by August 2018.
Attention is drawn to the possibility that some of the elements of this document may be the subject of
patent rights. CEN shall not be held responsible for identifying any or all such patent rights.
This document has been prepared under a mandate given to CEN by the European Commission and the
European Free Trade Association, and supports essential requirements of EU Directive(s).
For relationship with EU Directive(s), see informative Annex ZA, which is an integral part of this
document.
According to the CEN-CENELEC Internal Regulations, the national standards organisations of the
following countries are bound to implement this European Standard: Austria, Belgium, Bulgaria,
Croatia, Cyprus, Czech Republic, Denmark, Estonia, Finland, Former Yugoslav Republic of Macedonia,
France, Germany, Greece, Hungary, Iceland, Ireland, Italy, Latvia, Lithuania, Luxembourg, Malta,
Netherlands, Norway, Poland, Portugal, Romania, Serbia, Slovakia, Slovenia, Spain, Sweden, Switzerland,
Turkey and the United Kingdom.
Introduction
This European Standard has been prepared to be a harmonized standard to provide one means for the
mechanical design and theoretical verification of cranes to conform with the essential health and safety
requirements of the Machinery Directive, as amended. This standard also establishes interfaces
between the user (purchaser) and the designer, as well as between the designer and the component
manufacturer, in order to form a basis for selecting cranes and components.
This European Standard is a type C standard as stated in EN ISO 12100:2010.
The machinery concerned and the extent to which hazards, hazardous situations and events are
covered are indicated in the scope of this standard.
When provisions of this type C standard are different from those which are stated in type A or B
standards, the provisions of this type C standard take precedence over the provisions of the other
standards, for machines that have been designed and built according to the provisions of this type C
standard.
1 Scope
This European Standard is to be used together with EN 13001-1, EN 13001-2 and EN 13001-3-1 as well
as pertinent crane type product EN standards, and as such they specify general conditions,
requirements and methods to, by design and theoretical verification, prevent mechanical hazards of
hydraulic cylinders that are part of the load carrying structures of cranes. Hydraulic piping, hoses and
connectors used with the cylinders, as well as cylinders made from other material than carbon steel, are
not within the scope of this standard.
The following are significant hazardous situations and hazardous events that could result in risks to
persons during intended use and reasonably foreseeable misuse. Clauses 4 to 7 of this standard are
necessary to reduce or eliminate risks associated with the following hazards:
a) exceeding the limits of strength (yield, ultimate, fatigue);
b) elastic instability (column buckling).
NOTE EN 13001–3–6 deals only with the limit state method in accordance with EN 13001–1.
2 Normative references
The following documents are referred to in the text in such a way that some or all of their content
constitutes requirements of this document. For dated references, only the edition cited applies. For
undated references, the latest edition of the referenced document (including any amendments) applies.
EN 10083-2:2006, Steels for quenching and tempering — Part 2: Technical delivery conditions for non
alloy steels
EN 10210-2:2006, Hot finished structural hollow sections of non-alloy and fine grain steels — Part 2:
Tolerances, dimensions and sectional properties
EN 10216-3:2013, Seamless steel tubes for pressure purposes — Technical delivery conditions — Part 3:
Alloy fine grain steel tubes
EN 10277-2:2008, Bright steel products — Technical delivery conditions — Part 2: Steels for general
engineering purposes
EN 10305-1:2016, Steel tubes for precision applications — Technical delivery conditions — Part 1:
Seamless cold drawn tubes
EN 10305-2:2016, Steel tubes for precision applications — Technical delivery conditions — Part 2:
Welded cold drawn tubes
EN 13001-1, Cranes — General design — Part 1: General principles and requirements
EN 13001-2, Crane safety — General design — Part 2: Load actions
EN 13001-3-1, Cranes — General Design — Part 3-1: Limit States and proof competence of steel structure
EN 13445-2:2014, Unfired pressure vessels — Part 2: Materials
EN ISO 148-1:2016, Metallic materials — Charpy pendulum impact test — Part 1: Test method (ISO 148-
1:2016)
EN ISO 5817:2014, Welding — Fusion-welded joints in steel, nickel, titanium and their alloys (beam
welding excluded) — Quality levels for imperfections (ISO 5817:2014)
EN ISO 8492:2013, Metallic materials — Tube — Flattening test (ISO 8492:2013)
EN ISO 12100:2010, Safety of machinery — General principles for design — Risk assessment and risk
reduction (ISO 12100:2010)
ISO 724:1993, ISO general-purpose metric screw threads — Basic dimensions
3 Terms, definitions and symbols
3.1 Terms and definitions
For the purposes of this document, the terms and definitions given in EN ISO 12100:2010 apply.
ISO and IEC maintain terminological databases for use in standardization at the following addresses:
— IEC Electropedia: available at http://www.electropedia.org/
— ISO Online browsing platform: available at http://www.iso.org/obp
3.2 Symbols an abbreviations
The essential symbols and abbreviations are given in Table 1.
Table 1 — Symbols and abbreviations
Symbols Description
A% Percentage elongation at fracture
a Weld throat thickness
A , B , C , D
Constants
i i i i
A
Stress area
s
D Piston diameter
d Rod diameter
D
Diameter of axles
a,i
D
Pressure affected diameter
p
D
Weld diameter
w
E Modulus of elasticity
F Compressive force
F
Compressive force
A
FE Finite Elements
f
Limit design stress
Rd
f
Limit design stress, normal
Rdσ
Symbols Description
f
Limit design stress, shear
Rdτ
F
Lateral force
S
F
External design force
Sd
f
Ultimate strength
u
f
Limit design weld stress
w,Rd
f
Yield strength
y
h thickness of the cylinder bottom
I Moment of inertia, generic
I
Moment of inertia of the tube
I
Moment of inertia of the rod
L Overall length of the cylinder
L
Length of the cylinder tube
L
Length of the cylinder rod
m Slope of the log Δσ – log N curve
Shell section bending moment, acting at the intersection between tube and
M
bottom
MB Bending moment
N Compressive force
N
Critical buckling load
k
N
Limit compressive design force
Rd
N
Compressive design force
Sd
p
Maximum pressure in piston side chamber
i1
p
Maximum pressure in rod side chamber
i2
p
Outer pressure
o
p
Design pressure
Sd
Middle radius of the tube (R = R + t/2)
R
i
r
Inner radius of the tube
i
R
Inner radius of the tube
i
r
Outer radius of the tube
o
r
Outer radius of the piston rod
r
Symbols Description
s
Stress history parameter (see EN 13001–3-1)
t Wall thickness of the tube
Shell section transverse force, acting at the intersection between tube and
T
bottom
x, y Longitudinal and lateral coordinates
α Angular misalignment, radians
γ General resistance factor (γ = 1,1, see EN 13001–2)
m m
γ
Fatigue strength specific resistance factor (see EN 13001–3-1)
mf
γ Total resistance factor (γ = γ · γ )
R R m s
γ
Specific resistance factor
s
Δσ Stress range
Δσ
Bending stress range in the tube
b
Δσ
Characteristic fatigue strength
c
Δσ
Membrane stress range in the tube (axial)
m
Δσ
Limit design stress range
Rd
Δσ
Design stress range
Sd
Δp
Design pressure range on piston side
Sd
δ
Maximum displacement
max
κ Reduction factor for buckling
λ Slenderness
λ
Friction parameters
i
μ
Friction factors
i
ν Poisson’s ratio (ν = 0,3 for steel)
σ
Axial stress in the tube
a
σ
Lower extreme value of a stress range
b
σ
Radial stress in the tube
r
σ
Design stress, normal
Sd
σ
Tangential stress in the tube (hoop stress)
t
σ
Upper extreme value of a stress range
u
σ
Weld design stress, normal
w,Sd
Symbols Description
τ
Design stress, shear
Sd
τ
Weld design stress, shear
w,Sd
3.3 Terminology
Terms which are used in this European Standard for the main parts of hydraulic cylinder are indicated
in Figure 1 to Figure 3.
Key
1 bushing
2 rod head
3 cylinder head
4 oil connector
5 piston rod
6 cylinder tube
7 spacer
8 piston
9 nut
10 cylinder bottom
11 grease nipple
12 piston side chamber
13 rod side chamber
Figure 1 — Complete cylinder
Key
1 wiper
2 O-ring
3 secondary seal
4 guide ring (2 × )
5 primary seal
6 backup ring
7 O-ring
Figure 2 — Cylinder head
Key
1 seal
2 pressure element
3 guide ring (2 × )
Figure 3 — Piston
The figures above show some specific design features in order to exemplify the terminology. Other
designs may be used.
4 General
4.1 Documentation
The documentation of the proof of competence shall include:
— design assumptions including calculation models;
— applicable loads and load combinations;
— material grades and qualities;
— weld quality levels, in accordance with EN ISO 5817:2014 and EN 13001-3-1;
— relevant limit states;
— results of the proof of competence calculation, and tests when applicable.
4.2 Materials for hydraulic cylinders
4.2.1 General requirements
The materials for tubes and rods that are subjected to internal pressure shall fulfil the following
requirements:
— The impact toughness in the transversal direction shall be tested in accordance with EN ISO 148-1
and shall meet the requirements stated in EN 13001-3-1. Samples shall be cut out in the transversal
direction and prepared such that the axis of the notch is perpendicular to the surface of the tube.

Key
1 sample cut out in longitudinal direction
2 sample cut out in transversal direction
Figure 4 — Sample for impact toughness testing
— If the material thickness or tube dimensions do not allow samples to be cut out, the tube material
shall pass a flattening test in accordance with EN ISO 8492. For welded tubes two test are required,
one with the weld aligned with the press direction and one where the weld is placed 90 degrees
from the press direction. The tube section shall be flattened down to a height H given by:
1,07⋅ t
H=
t
0,07+
D
o
where
D is the outer diameter of the tube;
o
t is the wall thickness of the tube.
Material used in other parts shall meet the requirements stated in EN 13001-3-1.
4.2.2 Grades and qualities
European Standards specify materials and specific values. This standard gives a preferred selection.
Steels in accordance with the following European Standards shall be used as tube material:
— EN 10083-2;
— EN 10210-2;
— EN 10216-3;
— EN 10277-2;
— EN 10305-1;
— EN 10305-2;
— EN 13445-2.
Alternatively, other steel grades and qualities than those listed in this clause may be used as tube
material provided that they comply with the following requirements:
— the design value of f is limited to f /1,1 for materials with f /f < 1,1;
y u u y
— the percentage elongation at fracture A % ≥ 14 % on a gauge length LS5,65× (where S is
0 0
the original cross-sectional area);
Grades and qualities of materials used in other parts of cylinders or mounting interfaces of cylinders
shall be selected in accordance with EN 13001-3-1.
5 Proof of static strength
5.1 General
A proof of static strength by calculation is intended to prevent excessive deformations due to yielding of
the material, elastic instability and fracture of structural members or connections. Dynamic factors
given in EN 13001-2 or relevant product standards are used to produce equivalent static loads to
simulate dynamic effects. Also, load increasing effects due to deformation shall be considered. The use
of the theory of plasticity for calculation of ultimate load bearing capacity is not considered acceptable
within the terms of this standard. The proof shall be carried out for structural members and
connections while taking into account the most unfavourable load effects from the load combinations A,
B or C in accordance with EN 13001-2 or relevant product standards.
=
The cylinders are either active or passive. Active cylinders are moving and thereby increasing the
potential energy of the crane. Passive cylinders are either not moving or moving thereby decreasing the
potential energy of the crane. As the forces applied to the cylinder by the crane structure are computed
in accordance with EN 13001-2, they are already increased by the partial safety factors γ and relevant
p
dynamic factors. Formulae (1) and (2) give design pressures p caused by forces acting on the cylinder
Sd
from the crane structure. In addition, additional pressures p caused by internal phenomena in the
Sde
hydraulic circuit shall be considered and added to the design pressures p . Such internally generated
Sd
pressures can be caused e.g. by regenerative connections, pressure drop in return lines or cushioning.
In case a cylinder is intended to be tested as a component at higher pressure than the design pressure
p , this load case shall also be taken into account in the proof of static strength, and in which case the
Sd
test pressure shall be multiplied by a partial safety factor γ equal to 1,05.
p
The design pressure p in the piston side chamber or in the rod side chamber shall be computed from
Sd
the design force F taking into account the force direction and the cylinder efficiency η due to friction.
Sd
An efficiency factor Ψ is used to handle the effect of cylinder friction. For active cylinders Ψ has the
value of 1/η and for passive cylinders Ψ has the value of η.
For the piston side chamber, the design pressure is given by:
4⋅ F
Sd
p ⋅Ψ (1)
Sd
π⋅ D
where
F is the external design force;
Sd
D is the piston diameter.
Ψ is set to η for passive cylinders and to 1/η for active cylinders.
For the rod side chamber the design pressure is given by:
4⋅ F
Sd
pp⋅Ψ+ (2)
Sd Sde
π⋅ Dd−
( )
where
F is the external design force;
Sd
D is the piston diameter;
d is the rod diameter;
Ψ is set to η for passive cylinders and to 1/η for active cylinders;
p is additional pressure caused by internal phenomena.
Sde
Unless justified information for the value of η is used, the value 1,1 shall be assigned to Ψ.
This standard is based on nominal stresses, i.e. stresses calculated using traditional elastic strength of
materials theory which in general neglect localized stress non-uniformities. When more accurate
alternative methods of stress calculation are used, such as finite element analysis, using those stresses
for the proof given in this standard may yield inordinately conservative results.
=
=
5.2 Limit design stresses
5.2.1 General
The limit design stresses shall be calculated from:
(3)
Limit desing stresses ff= function ,γ
( )
Rd k R
where
f is the characteristic values (or nominal value);
k
γ is the total resistance factor ;
γ γγ⋅
R
R m s
γ is the general resistance factor (see EN 13001-2);
γ = 1,1
m
m
γ is the specific resistance factor applicable to specific structural components as given in the
s
clauses below.
NOTE f is equivalent to R /γ in EN 13001–1.
Rd d m
5.2.2 Limit design stress in structural members
The limit design stress f , used for the design of structural members, shall be calculated from:
Rd
f
y
(4)
f = for normal stresses
Rdσ
γ
Rm
f
y
f = for shear stresses (5)
Rdτ
γ ⋅ 3
Rm
with
γ γγ⋅
Rm m sm
where
f is the minimum value of the yield stress of the material;
y
γ is the specific resistance factor for material.
sm
for steels according to standards listed in 4.2.2;
γ = 0, 95
sm
for other steels.
γ = 10,
sm
For tensile stresses perpendicular to the plane of rolling (see Figure 5), the material shall be suitable for
carrying perpendicular loads and be free of lamellar defects. EN 13001-3-1 specifies the values of γ
sm
for material loaded perpendicular to the rolling plane.
Example from cylinder tube bottom, where plate steel is used (eye is welded). The figure shows a
tensile load perpendicular to plane of rolling where:
=
=
Key
1 is the plane of rolling
2 is the direction of stress/load
Figure 5 — Tensile load perpendicular to plane of rolling
5.2.3 Limit design stresses in welded connections
The limit design weld stress f used for the design of a welded connection shall be in accordance
w,Rd
with EN 13001-3-1.
5.3 Linear stress analysis
5.3.1 General
5.3 comprises typical details for consideration that are relevant for the proof of static strength. Details
that are only relevant for fatigue analysis (e.g. shell bending of tube) are not dealt with in 5.3. In cases or
conditions not covered here, other recognized sources or static pressure/force testing shall be used.
5.3.2 Typical load cases and boundary conditions
Before executing calculations, boundary conditions and loading shall be investigated. Typical conditions
to be determined are:
— external forces and directions;
— type of cylinder;
— cylinder tube and rod mounting to the machine;
— forces/stresses due to thread pre-tightening;
— direction of gravity.
Different load cases shall be considered when calculating static strength for cylinders.
Typical load cases are shown in Figure 6 to Figure 10 here below.
Figure 6 — Pushing cylinder with supported bottom

Figure 7 — Pushing cylinder, flange mounted with unsupported bottom

Figure 8 — Pulling cylinder or pushing cylinder with pressurized rod chamber

Figure 9 — Pushing cylinder at end of stroke

Figure 10 — Pulling cylinder at end of stroke
The worst load condition or combination shall be used when calculating stresses σ or σ for a
Sd w,Sd
feature.
5.3.3 Cylinder tube
Cylinder tube stresses shall be computed from three components. For calculation of each component,
forces and pressures shall be determined in accordance with 5.3.2.

Figure 11 — Stresses in cylinder tube
The tangential stress (hoop stress) is given by:
 
r 
r
o i
 
+ 1  + 1
  
r r
  
(6)
σ rp= ⋅ + p⋅
( )
ti o
   
r
r
o i
   
−−1 1
   
rr
 io  
For cylindrical shells such as tubes or hollow rods that are also loaded by an outer pressure, the
combination of inner and outer pressure that gives the largest absolute value of the tangential (hoop)
stress shall be used.
Maximum radial stress magnitude in the tube occurs at the inner radius r or the at the outer radius r
i o
and is given by:
σ =−p orσ =−p (7)
r i r o
For the cylinder arrangement shown in Figure 6, maximum axial stress in the tube is given by:
4⋅ r
o
σ M⋅ (8)
ab
π⋅ r − r
( )
oi
For the cylinder arrangements shown in Figure 8 and Figure 10, maximum axial stress in the tube is
given by:
2 2
p ⋅−r r
)
i2 ( i r 4⋅ r
o
(9)
σ +⋅M
ab
2 2
r − r
π⋅ r − r
oi ( )
oi
=
=
For the cylinder arrangement shown in Figure 7 and Figure 9, maximum axial stress in the tube is given
by:
p ⋅ r 4⋅ r
i1 i o
σ +⋅M (10)
ab
2 2
r − r
π⋅ r − r
oi ( )
oi
where
r is an arbitrary radius of the tube;
r is the inner radius of the tube;
i
r is the outer radius of the tube;
o
r is the outer radius of the piston rod;
r
p is the inner pressure;
i
p is the inner maximum pressure in piston side chamber;
i1
p is the inner maximum pressure in rod side chamber;
i2
p is the outer pressure;
o
M is any bending moment acting on the cylinder tube (e.g. dead weight).
b
The von Mises equivalent stress shall be computed for the location having the most severe stress as:
σ σ++−σ σ σσ−σσ−σ σ (11)
Sd t r a t a t r r a
5.3.4 Cylinder bottom
5.3.4.1 Bottom plate
The stress in an unsupported bottom plate, in a cylinder with the ratio outer diameter to inner diameter
in the range 1,07 to 1,24, shall be calculated as:


341 3 D+⋅2 tD
σ = p⋅ −⋅ ⋅ (12)


Sd i
350 7 D h



where
p is the inner pressure;
i
D is the inner diameter;
t is the tube thickness;
h is the bottom thickness.
=
=
Figure 12 — Stresses in unsupported cylinder bottom
5.3.4.2 Bottom weld
Bottom welds shall be calculated for different load cases in accordance with 5.3.2.

Figure 13 — Bottom weld
The bottom weld is loaded by the axial force in the tube, caused by internal pressure (Figure 7 and
Figure 8) or by pushing cylinder coming to end of stroke (Figure 9).
F
Sdt
σ = (13)
w,Sd
2⋅π⋅ R⋅ a
where
F is the design axial force acting in the tube;
Sdt
a is the effective thickness of the weld;
R is the middle radius of the weld.
5.3.5 Piston rod welds
Piston rod welds shall be calculated for different load cases according to 5.3.2, in the same way as the
calculation of bottom welds.
F
Sdw
σ = (14)
w,Sd
2⋅π⋅ R⋅ a
where
F is the maximum design force acting in the rod;
Sdw
a is the effective thickness of the weld;
R is the middle radius of the weld.
5.3.6 Cylinder head
Depending on the design, the cylinder head has a governing stress area A , which is the smallest area
c
that carries the axial load. Axial force can be caused by internal pressure, external force or pre-
tightening. The stresses in the cylinder head shall be calculated for the different load cases in
accordance with 5.3.2. The design stress shall be computed as:
F
Sdh
σ = (15)
Sd
A
c
where
F is the maximum axial design force acting on the head;
Sdh
A is the critical stress area for the axial force holding the cylinder head.
c
5.3.7 Cylinder tube and piston rod threads
Stresses in cylinder tube threads and piston rod threads shall be calculated for the different load cases
in accordance with 5.3.2. The design stress shall be computed as:
F
Sdr
σ = (16)
Sd
A
s
2⋅ F
Sdr
τ = (17)
Sd
π⋅ Ld⋅
where
F is the maximum design force acting on the cylinder head or the piston rod head;
Sdr
A is the stress area of the threaded cylinder tube or piston rod (equivalent to stress area of
s
bolt or nut);
L is the effective thread length, maximum 0,9 · d ;
d is the pitch diameter of the thread in accordance to ISO 724.
It should be considered that the tube diameter can increase due to the internal pressure and thus
decrease the shear area in Formula (17).
5.3.8 Thread undercuts and locking wire grooves
Stresses in thread undercuts or locking wire grooves shall be calculated for the different load cases in
accordance with 5.3.2.
The design stress shall be computed as:
F
Sdu
σ = (18)
Sd
A
c
where
F is the maximum design force acting at the undercut;
Sdu
A is the critical stress area at the undercut or locking wire groove.
c
Figure 14 — Undercuts at thread run out
5.3.9 Oil connector welds
This clause considers oil connectors welded to the tube. The design stress σ shall be computed as:
w,Sd
F
Sdo
σ = (19)
w,Sd
A
with
A=π⋅ D ⋅ a (20)
w
and
pD⋅π⋅
Sd p
F = (21)
Sdo
where
p is the design pressure for chamber side;
Sd
D is the pressure affected diameter;
p
a is the effective thickness of the weld;
D is the effective weld diameter.
w
Figure 15 — Welded oil connector
5.3.10 Connecting interfaces to crane structure
The design stresses in parts connecting the cylinder to the crane structure shall be calculated in
accordance with EN 13001-3-1.
5.4 Nonlinear stress analysis
5.4.1 General
Nonlinear stress analysis takes into account the force balance in the deformed shape of the cylinder and
can be governing when the compressive force acts together with bending moment or lateral force, or
due to the angular misalignment α between rod and tube caused by the play at the guide rings.
Nonlinear stress analysis may be omitted if lateral forces and bending moments are negligible, and if
the maximum displacement δ due to the angular misalignment α is smaller than L/600, where L is
max
the overall length of the cylinder. If the misalignment is unknown, δ shall be set to L/300. The
max
omission of a second order analysis shall be justified.
In particular the cases described in 5.4.2 and 5.4.3 might require nonlinear stress analysis. The
nonlinear stress analyses may either be made with FE-analysis or by the analytical equations given in
Annex B.
5.4.2 Standard cylinder with end moments
Standard cylinder with the same configuration as in buckling case D (see 7.2), loaded by a compressive
force F and by moments M and M caused by axle frictions acting at the bushings at the cylinder’s
1 2
ends, and with an angular misalignment α between the cylinder tube and the piston rod caused by play
at guide rings, see Figure 16.

Figure 16 — Cylinder with end moments from axle frictions and angular misalignment
5.4.3 Support leg
Support leg cylinder loaded by a compressive force F and by a lateral force F , and with an angular
A S
misalignment α between the cylinder tube and the piston rod caused by play at guide rings, see
Figure 17.
Figure 17 — Support leg cylinder with lateral force and angular misalignment
5.5 Execution of the proof
5.5.1 Proof for load bearing components
For the load bearing components (e.g. tube, rod, lugs) it shall be proven that:
σ ≤ f and τ ≤ f (22)
Sd Rdσ Sd Rdτ
where
σ is the design normal stress or the von Mises equivalent stress;
Sd
τ is the design shear stress;
Sd
f , f are the corresponding limit design stresses in accordance with 5.2.2.
Rdσ Rdτ
5.5.2 Proof for bolted connections
Bolted connections shall be proofed in accordance with EN 13001-3-1.
5.5.3 Proof for welded connections
For the weld it shall be proven that:
σ ≤ f (23)
w,Sd w,Rd
where
σ is the design weld stress;
w,Sd
f is the limit design weld stress in accordance with EN 13001-3-1.
w,Rd
6 Proof of fatigue strength
6.1 General
The proof of fatigue strength is intended to prevent risk of failure due to formation and propagation of
critical cracks in load carrying part of a hydraulic cylinder under cyclic loading.
For the execution of the proof of fatigue strength, the cumulative damages caused by variable stress
cycles shall be calculated. In this European Standard, Palmgren-Miner’s rule of cumulative damage is
reflected by use of the stress history parameters (see EN 13001-3-1).
The fatigue strength specific resistance factor γ is as defined in EN 13001-3-1.
mf
The limit design stress of a constructional detail is characterized by the value of the characteristic
fatigue strength ∆σ , which represents the fatigue strength at 2·10 cycles under constant stress range
c
loading and with a probability of survival equal to P 97,7 % (see EN 13001-3-1).
S
∆σ -values depend on the quality level of the weld. Quality levels shall be in accordance with
c
EN ISO 5817:2014, Annex C.
Fatigue testing may be used to establish ∆σ -values for details deviating from those given here below,
c
or to prove higher ∆σ -values than those given here. Such fatigue testing shall be done in accordance
c
with EN 13001-3-1.
6.2 Stress histories
The stress history is a numerical presentation of all stress variations that are
...