Bolt and Screw Compendium
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Transcript of Bolt and Screw Compendium
Bolt and Screw Compendium
Introduction
“Who invented the bolt, where, when and to what purpose it was invented, remainsentirely in the darkness of history” (S. Kellermann/Treue: “Die Kulturgeschichte derSchraube” (“The cultural history of bolts”); 2nd Ed. Munich, Bruckmann 1962).
“Today, in a slightly exaggerated sense, bolts hold together our entire civilization.Billions of bolts are manufactured throughout the year for the widest variety of uses.Hence it could be impulsively concluded that this omnipresent machine elementdoes not pose any problem to science and technology any more. But the fact that itis far from being so is shown by the abundance of works published on the subjectof bolts in the last two decades.”
This quote, from the introduction to the first Bolt and Screw Compendium, in thebeginning of the eighties, has not lost any of its relevance even today. Even thoughthe standard topics have been processed to the point of saturation, there are andhave always been new fields of requirement. In order to allow for the awareness inthe areas of materials and surface finishes as well as the changes in the computationalregulations, KAMAX has revised the Bolt and Screw Compendium, maintaining the usual compact form.
We hope that this booklet, like its predecessor is carried in numerous pockets, andis helpful to its user.
Troy, MI – September, 2006
Table of Contents
Page
1. Fastener Materials and Standards 6
2. Calculation of Bolted Joints 14
3. Self loosening of Bolted Joints 20
4. Tightening of Bolted Joints 23
5. Corrosion Protection and Lubrication 34
6. Durability-compatible Configuration 38
7. Miscellaneous 40
8. Formula Index 55
9. Literature 56
Bolt and Screw Compendium
Prop
erty
Cla
sses
Mec
hani
cal a
nd p
hysi
cal
3.6
4.6
4.8
5.6
5.8
6.8
8.8a
9.8b
10.9
12.9
char
acte
risti
csd≤
16m
mc
d>
16m
mc
Nom
inal
ten
sile
stre
ngth
Rm
nom
N/m
m2
300
400
500
600
800
800
900
1000
120
0
Min
imum
tens
ile st
reng
thR
m m
ind
eN
/mm
233
040
042
050
052
060
080
083
090
010
401
220
Vick
ers
hard
ness
HV
min
.95
120
130
155
160
190
250
255
290
320
385
F ≥
98 N
m
ax.
220f
250
320
335
360
380
435
Brin
ell h
ardn
ess
HB
min
.90
114
124
147
152
181
238
242
276
304
366
F =
30 (D
2 )m
ax.
209f
238
304
318
342
361
414
HRB
min
.52
6771
7982
89–
––
––
Rock
wel
l har
dnes
sH
RC m
in.
––
––
––
2223
2832
39
HRB
max
.95
.0f
99.5
––
––
–
HRC
max
.–
–32
3437
3944
Surf
ace
hard
ness
HV
0.3
––g
Low
er y
ield
str
ess
nom
inal
180
240
320
300
400
480
––
––
–
R eL
hin
N/m
m2
min
.19
024
034
030
042
048
0–
––
––
Stre
ss a
t 0.
2%
non
-pro
port
iona
l elo
ngat
ion
nom
inal
–64
064
072
090
010
80
R p 0
.2 i
in N
/mm
2m
in.
–64
066
072
094
011
00
Stre
ss u
nder
S p
/ReL
o. S
P/Rp
0.2
0.
940.
940.
910.
930.
900.
920.
910.
910.
900.
880.
88
proo
f lo
ad S
pN
/mm
218
022
531
028
038
044
058
060
065
083
097
0
Brea
king
tor
que
MB
Nm
min
.–
see
ISO
898
-7
1.Fa
sten
er M
ater
ials
and
Sta
ndar
ds
1.1
Mec
hani
cal a
nd p
hysi
cal c
hara
cter
isti
cs o
f fa
sten
ers
(at
room
tem
pera
ture
)(A
bstr
act
from
DIN
EN
ISO
898
-1; E
diti
on 1
1/99
)
6 – 7
Elon
gatio
n af
ter
frac
ture
A %
min
.25
22–
20–
–12
1210
98
Redu
ctio
n ar
ea a
fter
frac
ture
Z%
min
.–
5248
4844
Stre
ngth
und
er
The
valu
e fo
r th
e en
tire
bolt
(not
stu
d bo
lts) u
nder
bev
el t
ensi
le s
trai
n
wed
ge lo
adin
gm
ust
not
fall
belo
w t
he m
inim
um t
ensi
le s
tren
gths
giv
en a
bove
Impa
ct s
tren
gth,
KU
J m
in.
–25
–30
3025
2015
Hea
d so
undn
ess
No
rupt
ure
Min
imum
hei
ght
of
1 /2
H1
2 /3
H1
3 /4
H1
non-
deca
rb. t
hrea
d ar
ea E
Max
. dep
th o
f (c
ompl
ete
deca
rbur
izat
ion)
mm
–0.
015
Har
dnes
s af
ter
re-t
empe
ring
–M
ax. 2
0 H
V dr
op in
har
dnes
s
Surf
ace
inte
grity
In c
onfo
rman
ce w
ith IS
O 6
157-
1 or
ISO
615
7-3,
whe
reve
r ap
plic
able
aFo
r bo
lts o
f pr
oper
ty c
lass
8.8
in d
iam
eter
s d ≤
16 m
m, t
here
is a
n in
crea
sed
risk
of n
ut s
trip
ping
in t
he c
ase
of in
adve
rten
tov
er-t
ight
enin
g in
duci
ng a
load
exc
ess
of p
roof
load
. Ref
eren
ce t
o IS
O 8
98-2
is r
ecom
men
ded.
bAp
plie
s on
ly t
o no
min
al t
hrea
d di
amet
ers
d ≤
16 m
m.
cFo
r st
ruct
ural
bol
ting
the
limit
is 1
2 m
m.
dM
inim
um t
ensi
le p
rope
rtie
s ap
ply
to p
rodu
cts
of n
omin
al le
ngth
l ≥
2,5
d. M
inim
um h
ardn
ess
appl
ies
to p
rodu
cts
of le
ngth
l <
2,5
d an
d ot
her
prod
ucts
whi
ch c
anno
t be
ten
sile
-tes
ted
(e.g
. due
to
head
con
figur
atio
n).
eW
hen
test
ing
full-
size
bol
ts, s
crew
s an
d st
uds,
the
tens
ile lo
ads,
whi
ch a
re t
o be
app
lied
for
the
calc
ulat
ion
of R
msh
all m
eet
the
valu
es g
iven
in t
able
s 6
and
8.f
A ha
rdne
ss r
eact
ing
at t
he e
nd o
f bo
lts, s
crew
s an
d st
uds
shal
l be
250
HV,
283
HB
or 9
9.5
HRB
max
imum
.g
Surf
ace
hard
ness
sha
ll no
t be
mor
e th
an 3
0 Vi
cker
s po
ints
abo
ve t
he m
easu
red
core
har
dnes
s on
the
pro
duct
whe
n re
actin
gsof
bot
h su
rfac
e an
d co
re a
re c
arrie
d ou
t at
HV
0,3.
For
pro
pert
y cl
ass
10.9
, any
incr
ease
in h
ardn
ess
at t
he s
urfa
ce w
hich
indi
cate
s th
at t
he s
urfa
ce h
ardn
ess
exce
eds
390
HV
is n
ot a
ccep
tabl
e.h
In c
ases
whe
re t
he lo
wer
yie
ld s
tres
s R
eLca
nnot
be
dete
rmin
ed, i
t is
per
mis
sibl
e to
mea
sure
the
str
ess
at 0
.2%
non
-pr
opor
tiona
l elo
ngat
ion
Rp
0,2. F
or t
he p
rope
rty
clas
ses
4.8,
5.8
and
6.8
the
val
ues
for
ReL
are
giv
en f
or c
alcu
latio
n pu
rpos
eson
ly, t
hey
are
not
test
val
ues.
iTh
e yi
eld
stre
ss r
atio
acc
ordi
ng t
o th
e de
sign
atio
n of
the
pro
pert
y cl
ass
and
the
min
imum
str
ess
at 0
,2%
non
-pro
port
iopn
alel
onga
tion
Rp
0,2
appl
y to
mac
hine
d te
st s
peci
men
s. Th
ese
valu
es if
rec
eive
d fr
om t
est
of f
ull s
ize
bolts
and
scr
ews
will
var
ybe
caus
e of
pro
cess
ing
met
hod
and
size
eff
ects
.
Bolt and Screw Compendium
Prop
erty
M
ater
ials
and
Ch
emic
al C
ompo
siti
onTe
mpe
ring
Clas
ses
Trea
tmen
t(c
heck
ana
lysi
s)Te
mpe
ratu
re
CP
SBa
°Cm
in.
max
.m
ax.
max
.m
ax.
min
.3.
6b–
0.20
0.05
0.06
0.00
3–
4.6b
–0.
550.
050.
060.
003
–
4.8b
Carb
on s
teel
–0.
550.
050.
060.
003
–
5.6
0.13
0.55
0.05
0.06
0.00
3–
5.8b
–0.
550.
050.
060.
003
–
6.8b
–0.
550.
050.
060.
003
–
8.8c
Carb
on s
teel
with
add
itive
s (e
.g. B
oron
, Mn
or C
r)d 0.
15d
0.40
0.03
50.
035
0.00
342
5qu
ench
ed a
nd t
empe
red
Carb
on s
teel
, que
nche
d an
d te
mpe
red
0.25
0.55
0.03
50.
035
0.00
3
9.8
Carb
on s
teel
with
add
itive
s (e
.g. B
oron
, Mn
or C
r)d 0.
15d
0.35
0.03
50.
035
0.00
342
5qu
ench
ed a
nd t
empe
red
Carb
on s
teel
, que
nche
d an
d te
mpe
red
0.25
0.55
0.03
50.
035
0.00
3
10.9
ef
Carb
on s
teel
with
add
itive
s (e
.g. B
oron
, Mn
or C
r)d 0.
15d
0.35
0.03
50.
035
0.00
334
0qu
ench
ed a
nd t
empe
red
10.9
fCa
rbon
ste
el, q
uenc
hed
and
tem
pere
d0.
250.
550.
035
0.03
50.
003
Carb
on s
teel
with
add
itive
s (e
.g. B
oron
, Mn
or C
r)d 0.
20d
0.55
0.03
50.
035
0.00
342
5qu
ench
ed a
nd t
empe
red
Allo
yed
stee
l, qu
ench
ed a
nd t
empe
red
g0.
200.
550.
035
0.03
50.
003
12.9
fhi
Allo
yed
stee
l, qu
ench
ed a
nd t
empe
red
g0.
280.
500.
035
0.03
50.
003
380
1.2
Mat
eria
ls a
nd T
empe
ring
Tem
pera
ture
s fo
r Va
rious
Pro
pert
y Cl
asse
s of
fas
tene
rs.
(DIN
EN
ISO
898
-1; E
diti
on 1
1/99
)
8 – 9
aBo
ron
cont
ent
can
reac
h 0.
005
%, p
rovi
ded
that
non
-eff
ectiv
e bo
ron
is c
ontr
olle
d by
add
ition
of
titan
ium
and
/or
alum
iniu
m.
bFr
ee c
uttin
g st
eel i
s al
low
ed f
or t
hese
pro
pert
y cl
asse
s w
ith t
he f
ollo
win
g m
axim
um s
ulfu
r, ph
osph
orus
and
lead
con
tent
s:su
lfur:
0.34
%; p
hosp
horu
s: 0
.11%
; lea
d: 0
.35
%.
cFo
r no
min
al d
iam
eter
s ab
ove
20 m
m t
he s
teel
s sp
ecifi
ed f
or p
rope
rty
clas
ses
10.9
may
be
nece
ssar
y in
ord
er t
o ac
hiev
e su
ffic
ient
har
dena
bilit
y.d
In c
ase
of p
lain
car
bon
boro
n st
eel w
ith a
car
bon
cont
ent
belo
w 0
.25%
(lad
le a
naly
sis)
, the
min
imum
man
gane
se c
onte
ntsh
all b
e 0.
6% f
or p
rope
rty
clas
s 8.
8 an
d 0.
7% f
or 9
.8, 1
0.9
and
10.9
. e
Prod
ucts
sha
ll be
add
ition
ally
iden
tifie
d by
und
erlin
ing
the
sym
bol o
f th
e pr
oper
ty c
lass
(see
cla
use
9). A
ll pr
oper
ties
of 1
0.9
as s
peci
fied
in t
able
3 s
hall
be m
et b
y 1 0
.9, h
owev
er, i
ts lo
wer
tem
perin
g te
mpe
ratu
re g
ives
it d
iffer
ent
stre
ss r
elax
atio
n ch
arac
teris
tics
at e
leva
ted
tem
pera
ture
s (s
ee a
nnex
A).
fFo
r th
e m
ater
ials
of
thes
e pr
oper
ty c
lass
es, i
t is
inte
nded
tha
t th
ere
shou
ld b
e a
suff
icie
nt h
arde
nabi
lity
to e
nsur
e a
stru
ctur
eco
nsis
ting
of a
ppro
xim
atel
y 90
% m
arte
nsite
in t
he c
ore
of t
hrea
ded
sect
ions
for
the
fas
tene
rs in
the
“as
-har
dene
d“ c
ondi
tion
befo
re t
empe
ring.
gTh
is a
lloy
stee
l sha
ll co
ntai
n at
leas
t on
e of
the
fol
low
ing
elem
ents
in t
he m
inim
um q
uant
ity g
iven
: chr
omiu
m 0
.30%
, ni
ckel
0.3
0%, m
olyb
denu
m 0
.20%
, van
dium
0.1
0%. W
here
ele
men
ts a
re s
peci
fied
in c
ombi
natio
ns o
f tw
o, t
hree
or
four
and
have
allo
y co
nten
ts le
ss t
han
thos
e gi
ven
abov
e, t
he li
mit
valu
e to
be
appl
ied
for
clas
s de
term
inat
ion
is 7
0% o
f th
e su
m
of t
he in
divi
dual
lim
it va
lues
sho
wn
abov
e fo
r th
e tw
o, t
hree
or
four
ele
men
ts c
once
rned
.h
A m
etal
logr
aphi
cally
det
ecta
ble
whi
te p
hosp
horo
us e
nric
hed
laye
r is
not
per
mitt
ed f
or p
rope
rty
clas
s 12
.9 o
n su
rfac
es
subj
ecte
d to
ten
sile
str
ess.
iTh
e ch
emic
al c
ompo
sitio
n an
d te
mpe
ring
tem
pera
ture
are
und
er in
vest
igat
ion.
Bolt and Screw Compendium
1.3 Material for high-tensile bolts (DIN EN ISO 898-1)
Tensile Strength Classes Material
8.8 19 MnB 4 / 23MnB 328 B 2 / 35 B 2
10.9 19 MnB 4 / 23MnB 328 B 2
32 CrB 4
12.9 32 CrB 434 CrMo 4
Working Temperature* Tensile Strength Rm Material Head Marking
≤ 500 °C 1040 –1200 N/mm2 40 CrMoV 4-7 GB
≤ 540 °C 800 –1000 N/mm2 21 CrMoV 5-7 GA
≤ 580 °C 800 –1050 N/mm2 X 22 CrMoV 12-1 V(for Rp0,2 ≥ 600 MPa)
≤ 650 °C 900 –1150 N/mm2 X6NiCrTiMo SDVB25-15-2 / A 286
≤ 700 °C 1000 –1300 N/mm2 Nimonic 80 A SB
* Unit Temperature
1.4 Material for high temperature resistant bolts (DIN EN 10269)
Tensile Strength Rm Type of Steel* Material Material-No
> 700 N/mm2 A2 – 70 X 5 CrNi 18 12 1.4303
> 800 N/mm2 A2– 80
> 700 N/mm2 A4 – 70 X 5 CrNiMo 17 12 2 1.4401
> 800 N/mm2 A4 – 80
* as per DIN EN ISO 3506-1
1.5 Material for corrosion resistant fasteners
10 – 11
1.6 Materials for high-tensile bolts without heat treatment after cold forming
Tensile Strength Rm Material Annotation
800 –1000 N/mm2 10 MnSi 7 Micro-alloyed Tensile Strength Classes 800K 17 MnV 7 Steels
800 –1000 N/mm2 34 Cr 4 Pre heat treatedmaterial
1.7 Materials for Fasteners made from Aluminum Alloys
Tensile Strength Rm Material Field of Application
Rm > 320 N/mm2 EN AW 6082 Magnesium boltingRp0,2 > 290N/mm2 AlSi1MgMn Temperature load <100 °C
Without heat treatment High corrosion loadafter cold working
Rm > 380 N/mm2 EN AW 6056 Magnesium boltingRp0.2 > 350 N/mm2 AlSi6MgCuMn Aluminum bolting
With heat treatment EN AW 6013 Temperature load <150 °Cafter cold working AlMg1Si0,8CuMn High corrosion load
Type of Bolt Product Standard
Hexagon bolt DIN EN ISO 4014 Hexagon head boltsDIN EN ISO 4017 Hexagon head screwsDIN EN ISO 8676 Hexagon head screws,
with fine pitch threadDIN EN ISO 8765 Hexagon head bolts with
fine pitch threads
Hexagon bolt DIN EN 1662 Hexagon bolt with flange – small with flange DIN EN 1665 Hexagon bolt with flange – large
ISO 4162 Hexagon flange bolts – small
Hexalobular bolt KN 7210 Kamax Spec. KARUND – with flange external drive
DIN 34 800 Hexalobular bolts with small flange
DIN 34 801 Hexalobular bolts with large flange
Hexalobular KN 7230 Kamax Spec. KARUND – with internal drive socket cap screws
KN 7240 Cylindrical bolt for overelastic tightening with large KARUND
DIN EN ISO 14 579 (Fig.) Hexalobular socket head cap screws
DIN EN ISO 14 580 (Fig.) Hexalobular socket cheese head screws
DIN 34 802 Hexalobular bolts with large internal drive
Bolt and Screw Compendium
1.8 Types of Bolts and Associated Product Standards
12 – 13
Type of Bolt Product Standard
Hexagon socket head screws DIN EN ISO 4762 Hexagon socket head cap screwsDIN 6912 Hexagon socket thin head cap screws
with pilot recessDIN 7984 Hexagon socket thin head cap screws
Internal multipoint socket KN 7300 Kamax Spec. for internal drive – multipoint socket head
KN 7310 Cylindrical bolts for overelastic tightening with internal multipointsocket head
Bolt and Screw Compendium
2. Calculation of Bolted Joints
Generally a load carrying bolted joint is designed so that:
• the forces occurring during tightening and operation of the joint do not overstrain the components of the joint
• a minimal clamping force will be maintained during service which will guarantee the function of the joint regarding the necessary sealing force or a prevention of the opening of the joint
• the fatigue strength of the bolt will be exceeded by the cyclic load
without over sizing of the joint.
During assembly, in principle, the bolts are elongated (fSM) and the bolted parts are compressed (fPM). The load of both partners is equal in magnitude (action = reaction = FM = FSM = FPM), but the elongation/comression of the bolts and bolted components are dependent on the stiffness, and thus unequal.
Fig. 2.1 Elongation/CompressionComponents of a bolted joint before and after loading
The basic relations of load and elongation alterations of a bolted joint are clearlyshown in the joint diagram.
2.1 Joint Diagram
The classical form of the joint diagram, originally introduced by Roetscher, will beused here. However, through various modifications, it can also be applied to complex joints.
Fig. 2.2 Joint Diagram
The relationship between the assemblypreload and the elongation of the boltis shown in the bolt curve, which isnone other than the spring characteristicof the bolt. This analogy is valid for the joint components which experiencea compression. The slope of the curve is dependent on the material and geometry. The typicaljoint diagram is now developed byreflecting the component displacementcurve on the same coordinate system asthe bolt elongation curve and bringingthe two curves to the point of intersec-tion of the clamp load. When a work load is applied to thejoint the internal load balance will bealtered.
The load on the bolt increases, that on the components decreases. The bolt is thusfurther elongated, and the components somewhat expand because of the release. Itshould be noted that the alteration of the displacement for the bolt and the jointcomponent is the same, whereas depending on the relation of the slope (equals the
14 – 15
Clamped plates
Elongation + f
Bolt
Compression – f
+ F
– F
Change in length
Change in length
Bolt and Screw Compendium
ratio of the stiffness) of the curves the work load will be carried unequally. Therequirement of a minimal clamp load during operation therefore borders the bearable work load as well as the upper limit of the load capacity of the bolt.
2.2 Mechanics of Calculation
The fundamental pre-requisites for the calculation of a bolted joint according to the nominal diameter and tensile strength (PC) are:• External forces and torques• Stiffness and load introduction conditions• Minimal clamping force• Embedding• Tightening factors
First, the diameter of the bolt is estimated from tables and approximate formulae,and from these estimated measures the actual calculation in carried out. If theresults do not lie within the permissible range of stress, the diameter should bechanged and the calculation should be carried out all over again.The systematic of calculation given below refers exclusively to the linear calculationapproach according to VDI2230 (10/2001).The core point of the calculation is the principle dimensioning formula (calculationstep 6) which is shown graphically as well as a formula in the force-elongation diagram below:
Fig. 2.3Principle dimensioning formula
Basis formula:
Elongation f
Load
F
f
f f
SA
FPA
PASA
fSM fPM
F
Verf
FV
F KR
F
Mm
inF
Mm
inF
Mm
axF
Mm
axF
Sm
axF
Ker
fF
ZF
MF
AF
AF
–
�
Step 0At the beginning of the calculation, the required bolt diameter d and the propertyclass as well as the applicability of the calculation rules for eccentrically deformedand/or loaded joints has to be evaluated on the basis of tables or simple formula.
Step 1A tightening method should be determined. Its accuracy is reflected through the factor �A attributed to it. The method of assembly has huge influence on theassembly preload and consequently the designing of the bolted joint.
Step 2A minimal clamping force of the joint FKerf , not to be under-run at any time duringoperation is to be estimated from the working conditions. This can be deduced from the requirements regarding the sealing force of the joint, the friction, or theprevention of an opening under work load.
Step 3The load ratio � is to be calculated in order to determine the distribution of axialworking load FA between the bolt and the joint components. Smaller the ratio �, lesser additional force will be carried by the bolt. Thus � defines itself from theelastic resilience of the bolt �S and the joint parts �P, as well as the load introduction level (denoted by the factor n) and the eccentricities of the jointand work load. In general, the value of � decreases with the increase in the resilience of the bolt, as opposed to that of the deformed parts. The factor n isdependent on the given geometry, the level of load introduction level and the typeof joint. It can be defined according to VDI2230 or from a table.
Step 4Through the embedment of surfaces, the system looses partly its elastic deformati-on. This is reducing the assembly preload. Under consideration of the stiffness FZ ,the loss of preload as a result of the embedding, will be determined and used forthe calculation. Furthermore a change in the preload FVth will occur under thermalload when the components of the bolted joint do have different thermal expansioncoefficients.
16 – 17
Bolt and Screw Compendium
Steps 5 and 6By using the main dimensioning formula FMax = �A* [FKerf + (1- �)* FA + FZ + FVth],the maximum assembly preload as well the minimum required assembly preloadFMin = FMax / �A of the bolted joint will be calculated.
Step 7The result is to be compared against the table values for the bolt stress (FM) ) at a utilisation of the yield strength of 90% and the given friction factors. The condition FMzul ≥ FMmax or FMTab ≥ FMmax , must be fulfilled. The reference valuemust be calculated for specially designed bolts.Should the result lead to a necessary change in the bolt geometry or the ratio ofgrip length, the calculation is to be repeated right from step 2.
Step 8It should be calculated whether the allowable bolt load during operation is notexceeded through the total bolt load of FSmax = FMzul + �en* FAmax - �FVth. Thecondition �red , B < Rp0.2min should be fulfilled, where �red, B represents the compa-rative stress from maximum tensile stress and torsional stress obtained from thesmallest cross-sectional area of the bolt. The simplified formula FSmax ≤ Rp0.2min* A0is acceptable for torsion-free joints. Furthermore, a safety factor can be incorporatedfor �red, B < Rp0.2min / SF.
Step 9The acceptable alternating stress �A is relatively low for bolts as compared to theunthreaded wire. In case there is continious alternating stress, the joint should bechecked for the condition �a ≤ �AS where �AS depends on whether the bolt hashad thread rolling before or after heat treatment. The existing alternating stress �a isdetermined with respect to the tensile stress area of the bolt.
Step 10In general, the surface pressure in the joints should not exceed the allowable surfa-ce pressure of the components concerned in either the assembly state pMmax orduring operation pBmax in order to avoid a decrease in the preload by creep processes.A safety factor can be included for pG ≥ pM, Bmax .
Step 11The length of full thread engagement available has to be determined in order toavoid stripping of the thread(s). Related to nominal diameter and strength the minimum values can be gathered from the VDI 2230 standard.
Step 12The transverse loads working in the joint are generally transmitted by static frictionin the interfaces of the preloaded joint. Considering the number of interfaces andthe friction coefficients of the interfaces, a comparison has to be carried out betweenthe minimal residual clamp load FKRmin and the clamp load required for the trans-mission of the transverse loads FKQerf . A safety factor FKQerf < FKRmin / SF may alsobe included. If it comes to overloading of the joint, or also for the use of fittingbolts, one should avoid shearing the bolt. For that, �max = FQmax / A� ≤ �B should be valid.
Step 13The assembly torque required for the tightening of the bolts can be read from corresponding tables for 90 % bolt utilization, or can be calculated through MA = FMzul* [0.16* P + 0.58* d2* µGmin + DKm / 2* µKmin]. Additional moments in case connecting elements are used to prevent slacking and loosening have to be considered.
18 – 19
Bolt and Screw Compendium
3. Self loosening of bolted joints
A bolted joint with a mechanically sound design and reliable assembly does notneed a locking device in most cases. In these cases, the applied clamping forcesobstruct relative movements on the bolted joint over the entire life.
But under certain conditions, initial stress in the bolted joints can be broken down,reduced for a short time, or nullified.
1. Relaxation of bolted joint through loss of preload as a result of compression or permanent elongations, e.g. creep.
2. Dynamic load normal to the bolt axis can result in complete self-loosening of a bolt. This begins under a full preload when transverse shearing deformationoccurs as relative movement between joint components.
20 – 21
Mat
rix f
or S
ecur
ing
Elem
ents
for
Bol
ted
Join
tsM
echa
nica
l Saf
ety
Elem
ents
Nam
eW
orki
ngSa
fety
Har
dnes
sIn
stal
lati
onRe
cycl
e
Lubr
icat
ion
Surf
ace
of
Shel
f-lif
e
tem
p.fo
r dy
n.of
coun
t of
bol
t/be
arin
gof
pro
duct
°Clo
adbe
arin
gbe
arin
gsu
rfac
esu
rfac
esu
rfac
e
Karip
p®U
pto
yes
Mus
t be
La
rger
m
ultip
leAn
y
Min
or
unlim
ited
star
ting
less
tha
n fla
nge
lubr
icat
ion
dam
age,
te
mp.
the
tens
iledi
amet
erpo
ssib
le
not
for
st
reng
than
d sp
ace
lacq
uer
of t
he b
olt
requ
irem
ent
Kalo
k®se
rrat
ion
Upt
oye
sM
ust
be le
ssLa
rger
mul
tiple
Any
Maj
orun
limite
dst
artin
gth
an th
e te
n-fla
nge
lubr
icat
ion
dam
age,
tem
p.si
le s
tren
gth
diam
eter
poss
ible
not
for
of t
he b
olt:
and
spac
ela
cque
rm
ax. 4
0 HR
Cre
quire
men
t
Kalo
k II®
Upt
oye
sM
ust
be le
ssle
ss s
pace
mul
tiple
Any
Maj
orun
limite
dst
artin
gth
an th
e te
n-re
quire
men
tlu
bric
atio
nda
mag
e,te
mp.
sile
str
engt
hpo
ssib
leno
t fo
rof
the
bol
t:
lacq
uer
max
. 40
HRC
Plas
tic
lock
ing
-56
cond
ition
alAl
l le
ss s
pace
mul
tiple
no4
Year
sPa
tch
coat
ins
bis
hard
ness
esre
quire
men
tsda
mag
ePA
1112
0
Trilo
bula
rlo
ckin
g fe
atur
e of
U
pto
cond
ition
alTe
nsile
stre
ngth
Lock
ing
mul
tiple
Any
noun
limite
dTh
read
sth
read
form
ing
area
in
star
ting
of t
he d
rill
effe
ct o
nly
lubr
icat
ion
dam
age
conn
ectio
n w
ithte
mp.
mus
t be
less
in b
lind
poss
ible
fem
ale
thre
adth
an t
heho
le b
orin
gste
nsile
stre
ngth
of t
he b
olt
Bolt and Screw Compendium
Mat
rix f
or S
ecur
ing
Elem
ents
for
Bol
ted
Join
tsM
echa
nica
l Saf
ety
Elem
ents
Man
ufac
ture
r,W
orki
ngSa
fety
for
H
ardn
ess
of
Inst
alla
tion
Recy
cle
Lubr
icat
ion
Surf
ace
of
Shel
f-lif
e tr
adem
ark
tem
p.dy
n. L
oad
seal
ing
run
coun
tbo
lt/
seal
ing
run
of°C
seal
ing
run
prod
uct
MVK
,O
mni
-U
pto
150
yes
All
No
easy
secu
ring
N
o 2
–4
year
s,
red
Tech
nik
hard
ness
esad
ditio
nal
MVK
not
dam
age
less
er a
t
Prec
ote
80sp
ace
with
SM
; hi
gh
requ
irem
ents
nut
thre
ad
hum
idity
oilfr
ee
MVK
,3M
Upt
o 11
0ye
sAl
l N
oea
syse
curin
g N
o2
–4
year
s,
blue
Scot
ch g
ripha
rdne
sses
addi
tiona
lM
VK n
ot
dam
age
less
er a
t
2353
spac
ew
ith S
M;
high
requ
irem
ents
nut
thre
adhu
mid
ityoi
lfree
MVK
,O
mni
-U
pto
170
yes
All
No
easy
secu
ring
No
2–
4 ye
ars,
turq
uois
eTe
chni
kha
rdne
sses
addi
tiona
lM
VK n
ot
dam
age
less
er a
t
Prec
ote
85sp
ace
with
SM
;hi
gh
requ
irem
ents
nut
thre
adhu
mid
ityoi
lfree
Liqu
idye
sAl
so s
uita
ble
No
easy
No
adhe
sive
for
high
ad
ditio
nal
dam
age
hard
ness
essp
ace
requ
irem
ents
22
4. Tightening joints
The tightening methods used today are not able to measure the assembly preloaddirectly, but only as a function of the tightening torque, the elastic elongation, the tightening angle or the determination of the yield point of the bolt. The variationof the friction coefficients and the inaccuracy of the tightening methods do lead to a need for over dimensioning of the bolted joint, which is expressed by the tightening factor
�A = Fvmax / Fvmin
4.1 Torque Controlled Tightening
By tightening tests on original components, the friction coefficients are first determined,and the required torque is subsequently specified. This torque must be assigned in such a way that the elastic limit of the bolt is not exceeded even in adverse conditions e.g. low friction factor, etc. Pic 4.1. For hexagon bolts acc. DIN EN 24014and similar, the torque values are shown on table 4.1. These are valid for a stress inthe shank of 90 % of the standard minimum yield strenght according to VDI code2230. The table values represent the maximal torque values. For deviant head-geometry, the initial torque is calculated by
MA = FM(0.16*P+0.58*d2*µG+(DKm/2)*µK)
For torque-driven tightening, the designing of bolts is based on a �A of 1.8 .
Monitoring the final angle of rotation along with a given torque is recommendedfor the control of the assembly process. The tolerance range of the final angle ofrotation must be in a defined zone (window), which is established through tests. In case the final angle of rotation lies outside of this window, the driver indicates a failure.
– 23
Bolt and Screw Compendium
Fig. 4.1 Scatter of �FM for torque controlled tightening of bolted joints
4.2 Angle Controlled Tightening
First the joint is loaded with a snug torque until all interfaces are completely closed. Subsequently a defined angle �A will be applied, which is measured fromthe point the snug torque is achieved, with which the bolt will be tightened to or beyond the yield point.
For the control of the tightening process a tolerance range for the final torque hasto be specified. The final torque must be in this range. The big advantage of this tightening process versus torque controlled tightening is that the elongation of the bolt in the plastic area is defined over thegiven angle. The cut off torque preferably lies above the yield point. The bolt willthus be used to the full. It therefore underlies a tightening factor �A = 1.0 .
150
100
50 50
100
150
50 50
MA
max
MA
max
MK
MG
A m
ax
MG
A m
in
FF
min
FF
min
FM
max
FM
maxF [kN]M
� = 0G
�= 0,10
G
�=
0,16
G
�=
0,10
ges
�=
0,10
ges
�=
0,17
1ge
s
�=
0,17
1ge
s
�=
0,10
;
G
�=
0,10
K
�=
0,10
;
G
�=
0,10
K
�=
0,16
;G
�=
0,18
K
�=
0,16
;G
�=
0,18
K
F [kN]M
MA
min
MA
min
FM FM
MA
MGA
MA
,MK
MA
MAMA
[Nm]
MA
[Nm]
v = 0,9 v=1v = 0,9 v=1
1
23
4
Fig. 4.2Angle controlled tightening of bolted connections
4.3 Yield Controlled Tightening
Similar to angle controlled tightening, a snug torque will be applied until all inter-faces are completely closed. From this point, the angle and the attained torque aredynamically measured, and the respective differential ratio
�Ma/��
is calculated. This differential ratio is constant in the elastic region, and diminishesas it approaches the elastic limit of the bolt; the torque does not increase in proportion to the angle of rotation any more. When the value of the differentialratio declines to a pre determined value,
e.g. 0.5*(�Ma/��)
the assembly machine will be cut off and the tightening process is completed.
24 – 25
Angle �
Snugpoint
Pre
load
FM
50
50
100
kN
100 150grd
��A
�F
M
�F
M
FF
Rp 0,2 -Punkt
��A
�A
�F�p 0,2
Bolt and Screw Compendium
Fig. 4.3Yield controlled tighteningof bolted connections
The position of the cut-off in the diagram Ma/� is essentially determined throughthe tensile strength of the bolt and the friction. The assembly preload varies withthe elastic limit of the bolt and thread friction (Fig. 4.4).
Fig. 4.4Scatter of clampload due to variances of thread friction andyield point of fastener materialduring yield controlled tighteningof bolted joints
Rp 0,2 -point
Angle �D
iffer
entia
l quo
tiant
�MA
max��
�M
A�
�
�MA
max��
�MA��
�MA��
�MA
�M
A
�M
A
MF
max��
��
��
Cut-off point
= 0,5
= f (�)
Pre
load
MA
�F
Snugpoint
Snu
gtor
que
Snugangle
1
2
3150
150
100
100
50
50
Nm
grd
�=
0,14
ges
�=
0,10
ges
�= 0,10
G
� = 0G
�= 0,
12
G
�=
0,14
G
FM
MG
A
R p 0,2 = 1100 N/mm2
FM [kN]
MGA ,MA
[Nm]
R p 0,2 = 940 N/mm2
1
2
3
4
150
100
100
50
50
�AFMmax
66,684,1 1,26
FMmin
= = =
For the control of the tightening, the min. and max. values of tightening torque androtating angle of tightening are calculated, or established through tests. Recordedin diagram Ma/�, these values define a right angle, which is usually indicated by agreen window (Fig. 4.5). If the cut-off points lie within this range, the tighteningprocess is deemed OK.
Fig 4.5 “green window“ for yield controlled tightening of bolted joints
As compared to the angle control, there is the advantage that the bolts undergo a smaller plastic elongation; of course the assembly preload level is somewhatlower.
The required torque and the attained assembly preload can be estimated through multiplication of values from Table 4.1 with the following conversion factors:
FM bzw. MA = 1.1-1.3* Table value
26 – 27
MAmax
(Rp 0,2 =1100 N/mm2; �G=�K=0,14)
(Rp 0,2 =1100 N/mm2; �G=�K=0,12)
(Rp 0,2 =940 N/mm2; �G=�K=0,12)
(Rp 0,2 =940 N/mm2; �G=�K=0,10)
MAmax
MAmin
MAmin
�m
in (R
p 0,
2 =
940
N/m
m2 ; �
G=
�K=
0,14
)
�m
in (R
p 0,
2 =
940
N/m
m2 ; �
G=
�K=
0,12
)
�m
ax (R
p 0,
2 =
110
0 N
/mm
2 ; �G=
�K=
0,12
)
�m
ax (R
p 0,
2 =
110
0 N
/mm
2 ; �G=
�K=
0,10
)
Angle �
Tigh
teni
ng to
rque
MA
Snu
gtor
que
Snugangle
MF
�F
150
100
50
50 100 grd
Nm
bc
a
A'A
A''
Point Rp0.2 F mG mK
[N/mm2] [kN]
A 1020 75.3 0.120 0.120A' 960 70.2 0.125 0.134A" 1080 82.7 0.100 0.114a 870 65.4 0.110 0.130b 1200 85.2 0.140 0.100c 1000 87.2 0.080 0.140
Bolt and Screw Compendium
Thre
ad S
ize
Prop
erty
Asse
mbl
y Pr
eloa
d F M
[kN
] fo
r µ g
Tigh
teni
ng T
orqu
e M
A[N
m]
for
µ k=
µ gCl
ass
0.08
0.10
0.12
0.16
0.20
0.08
0.10
0.12
0.16
0.20
M6
8.8
10.7
10.4
10.2
09.6
09.0
07.7
09.0
10.1
12.3
14.1
AS=
20.1
mm
210
.915
.715
.314
.914
.113
.211
.313
.214
.918
.020
.712
.918
.417
.917
.516
.515
.513
.215
.417
.421
.124
.2M
78.
815
.515
.114
.814
.013
.112
.614
.816
.820
.523
.6A
S=
28.9
mm
210
.922
.722
.521
.720
.519
.318
.521
.724
.730
.134
.712
.926
.626
.025
.424
.022
.621
.625
.428
.935
.240
.6M
8 x
1.0
8.8
21.2
20.7
20.2
19.2
18.1
19.3
22.8
26.1
32.0
37.0
AS=
39.2
mm
210
.931
.130
.429
.728
.126
.528
.433
.538
.347
.054
.312
.936
.435
.634
.732
.931
.033
.239
.244
.955
.063
.6M
8 x
1.25
8.8
19.5
19.1
18.6
17.6
16.5
18.5
21.6
24.6
29.8
34.3
AS=3
6.6
mm
210
.928
.728
.027
.325
.824
.327
.231
.836
.143
.850
.312
.933
.632
.832
.030
.228
.431
.837
.242
.251
.258
.9M
9 x
1.0
8.8
27.7
27.2
26.5
25.2
23.7
28.0
33.2
38.1
46.9
54.4
AS=
51.0
mm
210
.940
.739
.939
.037
.034
.941
.148
.855
.968
.879
.812
.947
.746
.745
.643
.340
.848
.157
.065
.480
.693
.4M
10 x
1.0
8.8
35.2
34.5
33.7
32.0
30.2
39.0
46.0
53.0
66.0
76.0
AS=
64.5
mm
210
.951
.750
.649
.547
.044
.457
.068
.078
.097
.011
2.0
12.9
60.4
59.2
57.9
55.0
51.9
69.0
80.0
91.0
113.
013
1.0
M10
x 1
.25
8.8
33.1
32.4
31.6
29.9
28.2
38.0
44.0
51.0
62.0
72.0
AS=
61.2
mm
210
.948
.647
.546
.444
.041
.455
.065
.075
.092
.010
6.0
12.9
56.8
55.6
54.3
51.4
48.5
65.0
76.0
87.0
107.
012
4.0
4.1
Clam
p Lo
ads
and
tigh
teni
ng t
orqu
es f
or b
olts
wit
h m
etric
thr
ead
acc
DIN
13 a
ndhe
ad c
onfi
gura
tion
acc
D/E
/I 4
014
for
�=
0.9
28 – 29
M10
x 1
.58.
831
.030
.329
.627
.926
.336
.043
.048
.059
.068
.0A
S=
58.0
mm
210
.945
.644
.543
.441
.038
.653
.063
.071
.087
.010
0.0
12.9
53.3
52.1
50.8
48.0
45.2
62.0
73.0
83.0
101.
011
6.0
M12
x 1
.25
8.8
50.1
49.1
48.0
45.6
43.0
66.0
79.0
90.0
111.
012
9.0
AS=
92.1
mm
210
.973
.672
.170
.566
.963
.297
.011
6.0
133.
016
4.0
190.
012
.986
.284
.482
.578
.373
.911
4.0
135.
015
5.0
192.
022
2.0
M12
x 1
.58.
847
.646
.645
.543
.140
.664
.076
.087
.010
7.0
123.
0A
S=
88.1
mm
210
.970
.068
.566
.863
.359
.795
.011
2.0
128.
015
7.0
181.
012
.981
.980
.178
.274
.169
.811
1.0
131.
015
0.0
183.
021
2.0
M12
x 1
.75
8.8
45.2
44.1
43.0
40.7
38.3
63.0
73.0
84.0
102.
011
7.0
AS=
84.3
mm
210
.966
.364
.863
.259
.856
.392
.010
8.0
123.
014
9.0
172.
012
.977
.675
.974
.070
.065
.810
8.0
126.
014
4.0
175.
020
1.0
M14
x 1
.58.
867
.866
.464
.861
.558
.110
4.0
124.
014
2.0
175.
020
3.0
AS=
125
mm
210
.999
.597
.595
.290
.485
.315
3.0
182.
020
9.0
257.
029
9.0
12.9
116.
511
4.1
111.
410
5.8
99.8
179.
021
3.0
244.
030
1.0
349.
0M
14 x
2.0
8.8
62.0
60.6
59.1
55.9
52.6
100.
011
7.0
133.
016
2.0
187.
0A
S=
115
mm
210
.991
.088
.986
.782
.177
.214
6.0
172.
019
5.0
238.
027
4.0
12.9
106.
510
4.1
101.
596
.090
.417
1.0
201.
022
9.0
279.
032
1.0
M16
x 1
.58.
891
.489
.687
.683
.278
.615
9.0
189.
021
8.0
269.
031
4.0
AS=
167
mm
210
.913
4.2
131.
612
8.7
122.
311
5.5
233.
027
8.0
320.
039
6.0
461.
012
.915
7.1
154.
015
0.6
143.
113
5.1
273.
032
5.0
374.
046
3.0
539.
0M
16 x
2.0
8.8
84.7
82.9
80.9
76.6
72.2
153.
018
0.0
206.
025
2.0
291.
0A
S=
157
mm
210
.912
4.4
121.
711
8.8
112.
610
6.1
224.
026
4.0
302.
037
0.0
428.
012
.914
5.5
142.
413
9.0
131.
712
4.1
262.
030
9.0
354.
043
3.0
501.
0M
18 x
1.5
8.8
122.
012
0.0
117.
011
2.0
105.
023
7.0
283.
032
7.0
406.
047
3.0
AS=
216
mm
210
.917
4.0
171.
016
7.0
159.
015
0.0
337.
040
3.0
465.
057
8.0
674.
012
.920
4.0
200.
019
6.0
186.
017
6.0
394.
047
2.0
544.
067
6.0
789.
0
Bolt and Screw Compendium
Thre
ad S
ize
Prop
erty
Asse
mbl
y Pr
eloa
d F M
[kN
] fo
r µ g
Tigh
teni
ng T
orqu
e M
A[N
m]
for
µ k=
µ gCl
ass
0.08
0.10
0.12
0.16
0.20
0.08
0.10
0.12
0.16
0.20
M18
x 2
.08.
811
4.0
112.
010
9.0
104.
098
.022
9.0
271.
031
1.0
383.
044
4.0
AS=
204
mm
210
.916
3.0
160.
015
6.0
148.
013
9.0
326.
038
6.0
443.
054
5.0
632.
012
.919
1.0
187.
018
2.0
173.
016
3.0
381.
045
2.0
519.
063
8.0
740.
0M
18 x
2.5
8.8
107.
010
4.0
102.
096
.091
.022
0.0
259.
029
5.0
360.
041
5.0
AS=
193
mm
210
.915
2.0
149.
014
5.0
137.
012
9.0
314.
036
9.0
421.
051
3.0
592.
012
.917
8.0
174.
017
0.0
160.
015
1.0
367.
043
2.0
492.
060
1.0
692.
0M
20 x
1.5
8.8
154.
015
1.0
148.
014
1.0
133.
032
7.0
392.
045
4.0
565.
066
0.0
AS=
272
mm
210
.921
9.0
215.
021
1.0
200.
019
0.0
466.
055
8.0
646.
080
4.0
90.0
12.9
257.
025
2.0
246.
023
4.0
222.
054
5.0
653.
075
6.0
941.
011
00.0
M20
x 2
.58.
813
6.0
134.
013
0.0
123.
011
6.0
308.
036
3.0
415.
050
9.0
588.
0A
S=
245
mm
210
.919
4.0
190.
018
6.0
176.
016
6.0
438.
051
7.0
592.
072
5.0
838.
012
.922
7.0
223.
021
7.0
206.
019
4.0
513.
060
5.0
692.
084
8.0
980.
0M
22 x
1.5
8.8
189.
018
6.0
182.
017
3.0
164.
044
0.0
529.
061
3.0
765.
089
6.0
AS=
333
mm
210
.926
9.0
264.
025
9.0
247.
023
3.0
627.
075
4.0
873.
010
90.0
1276
.012
.931
5.0
309.
030
3.0
289.
027
3.0
734.
088
2.0
1022
.012
75.0
1493
.0M
22 x
2.5
8.8
170.
016
6.0
162.
015
4.0
145.
041
7.0
495.
056
7.0
697.
080
8.0
AS=
303
mm
210
.924
2.0
237.
023
1.0
213.
020
7.0
595.
070
4.0
807.
099
3.0
1151
.012
.928
3.0
277.
027
1.0
257.
024
2.0
696.
082
4.0
945.
011
62.0
1347
.0M
24 x
1.5
8.8
228.
022
4.0
219.
020
9.0
198.
057
0.0
686.
076
9.0
995.
011
66.0
AS=
401
mm
210
.932
5.0
319.
031
2.0
298.
028
2.0
811.
097
7.0
1133
.014
17.0
1661
.012
.938
0.0
373.
036
6.0
347.
033
0.0
949.
011
43.0
1326
.016
58.0
1943
.0M
24 x
2.0
8.8
217.
021
0.0
209.
019
8.0
187.
055
7.0
666.
076
9.0
955.
011
14.0
AS=
384
mm
210
.931
0.0
304.
029
7.0
282.
026
7.0
793.
094
9.0
1095
.013
60.0
1586
.012
.936
2.0
355.
034
8.0
331.
031
2.0
928.
011
10.0
1282
.015
91.0
1856
.0
30 – 31
M24
x 3
.08.
819
6.0
192.
018
8.0
178.
016
8.0
529.
062
5.0
714.
087
5.0
1011
.0A
S=
353
mm
210
.928
0.0
274.
026
7.0
253.
023
9.0
754.
089
0.0
1017
.012
46.0
1440
.012
.932
7.0
320.
031
3.0
296.
027
9.0
882.
010
41.0
1190
.014
58.0
1685
.0M
27 x
1.5
8.8
293.
028
8.0
282.
026
9.0
255.
082
2.0
992.
011
53.0
1445
.016
97.0
AS=
514
mm
210
.941
8.0
410.
040
2.0
383.
036
3.0
1171
.014
13.0
1643
.020
59.0
2417
.012
.948
9.0
480.
047
0.0
448.
042
5.0
1370
.016
54.0
1922
.024
09.0
2828
.0M
27 x
2.0
8.8
281.
027
6.0
270.
025
7.0
243.
080
6.0
967.
011
19.0
1394
.016
30.0
AS=
496m
m2
10.9
400.
039
3.0
384.
036
6.0
346.
011
49.0
1378
.015
94.0
1986
.023
22.0
12.9
468.
046
0.0
450.
042
8.0
405.
013
44.0
1612
.018
66.0
2324
.027
17.0
M27
x 3
.08.
825
7.0
252.
024
6.0
234.
022
0.0
772.
091
5.0
1050
.012
92.0
1498
.0A
S=
459
mm
210
.936
7.0
359.
035
1.0
333.
031
4.0
1100
.013
04.0
1496
.018
40.0
2134
.012
.942
9.0
420.
041
0.0
389.
036
7.0
1287
.015
26.0
1750
.021
53.0
2497
.0
Bolt and Screw Compendium
4.5 Tightening Torques for bolt assembly beyond yield point
The snug torques and angles of rotation in the following table are valid for bolt grip lengths from 1d to 4d which are assembled beyond yield (angle controlled and yield controlled tightening). For smaller and larger grip length,the required angle of rotation is to be determined by test on original components.In such cases, by keeping the same initial torques, rotation angles of 45° or 180°should be considered. The reusability of these bolted joints is limited.
Thread Property Initial Preload Force Tightening Torque Class Torque [kN] [Nm]
[Nm] + overelastic angle overelastic angle Rotation controlled tightening controlled tighteningAngle 90°
FMmin FMmax MAmin MAmax
8.8 8 10.5 14.5 10.0 17M 6 10.9 10 15.5 20 14.5 23.5
12.9 10 18.5 22.5 17.0 26.58.8 20 19.5 26 24.0 41
M 8 10.9 20 29 36 35.5 5712.9 20 34 41.5 41.5 658.8 40 31 41.5 47.5 81
M 10 10.9 50 45.5 57 70 11012.9 50 54 66 81 1308.8 60 48 64 85 154
M 12 x 1.5 10.9 90 71 88 125 20012.9 90 83 100 145 2308.8 100 69 91 140 240
M 14 x 1.5 10.9 150 100 125 205 33512.9 150 115 145 235 3808.8 120 95 125 215 380
M 16 x 1.5 10.9 180 135 170 310 51012.9 180 160 195 360 5858.8 140 125 165 315 555
M 18 x 1.5 10.9 210 175 220 450 74512.9 210 205 250 525 855
32 – 33
4.6 Recommended Values for Tightening Factors
4.7 Recommended Minimum Length of Thread Engagement for Blind-hole Threads (VDI 2230)
Tightening process Tightening factors �a Remarks
Yield point controlled, 1.18motorized or manual
Angle of rotation controlled, 1.18 Snug torque (pre-tightening) and motorized or manual angle of rotation determined
through experimentation
Elongation measurement of 1.2calibrated bolt
Hydraulic tightening 1.2 to 1.6 Long bolts: lower valuesShort bolts: higher values Established through measurement of elongation length and applied pressure
Torque controlled, 1.4 to 1.6 Determination of required torque with torque wrench or through measurement of FM on precision screwdriver with the jointdynamic torque control 1.6 to 1.8 Nominal torque determined with
the estimated friction coefficient of the particular case
Torque controlled, 1.7 to 2.5 Pre-setting of power screwdriver with mechanical screwdriver with post torque, which isImpulse controlled, 2.5 to 4,0 established from the requiredwith impact wrench torque plus post torque
Tensile Strength of Bolt 8.8 8.8 10.9 10.9Fineness of thread d/P < 9 ≥ 9 < 9 ≥ 9
AlCuMg1 F 40 1.1 d 1.4 d –
GG 22 1.0 d 1.2 d 1.4 d
St 37 1.0 d 1.25 d 1.4 d
St 50 0.9 d 1.0 d 1.2 d
C 45 V 0.8 d 0.9 d 1.0 d
Bolt and Screw Compendium
5. Corrosion Protection and Lubrication
5.1 Surface Coating System (Optional)Specifications as known at the time of printing.
Symbol (abbr.) Basecoat Passivation Topcoat / Sealing
Surfaces containing Cr(VI)
Zn yellow Galv. Zinc Yellow -
Zn + Metex LM Galv. Zinc (acid) Yellow Metex® LM
ZnFe black Galv. Zinc-Iron Black -
ZnNi transparent Galv. Zinc-Nickel Transparent -
ZnNi black Galv. Zinc-Nickel Black- -
DAC 320 DACROMET® 320 -
DAC 500 DACROMET® 500 -
DAC 320 + Plus L DACROMET® 320 Plus® L
Cr(VI)-free Surfaces
op thin Zinc phosphate - -
Zn transp. / Zn Thin III Galv. Zinc Thin layer Cr(III) -
Zn Thin III + V Galv. Zinc Thin layer Cr(III) Sealing
Zn Thick III Galv. Zinc Thick layer Cr(III) -
Zn Thick III + V Galv. Zinc Thick layer Cr(III) Sealing
ZnFe Pass III Galv. Zinc-Iron Containing Cr(III) -
ZnFe Pass III + V Galv. Zinc-Iron Containing Cr(III), if black Sealing if black
ZnNi Pass III Galv. Zinc-Nickel Containing Cr(III) -
ZnNi Pass III + V Galv. Zinc-Nickel Containing Cr(III), if black Sealing if black
DS (GZ) - DELTA®-Seal (GZ)
GEO 500 GEOMET® 500 -
DT/DP 100 (+ SM) DELTA®-Tone / DELTA®-Protekt KL 100 -
GEOMET + V GEOMET® 321 e.g. DACROLUB x
DT / DP 100 + DS GZ DELTA®-Tone / DELTA®-Protekt KL 100 DELTA®-Seal GZ
DT / DP 100 + Klevercol DELTA®-Tone / DELTA®-Protekt KL 100 Klevercol®
GEOBLACK GEOMET® 500 Plus ML black
DP 100 + DP 30x DELTA®-Protekt KL 100 DELTA®-Protekt VH 30x
GEO + Plus VL GEOMET® 321 Plus® VL
GEOMET + Plus x GEOMET® 321 Plus® 10 / L / ML / M
B 46 + B 18 x MAGNI B 46 MAGNI B 18 x
1 Reference values for parts in new condition (head and thread ends) to be examined individually /these values can be reduced through subsequent handling operation
34 – 35
Optical characteristics Layer Additional NaCl-Test Resistance to thickness lubricant DIN 50 021 chemicals 1, 2
[µm] treatment RR (WR) 1, 2 (Rim-cleanser)
Yellow ≥ 8 Necessary 144h (72h) -
Yellowish ≥ 15 TTF 600h (192h) -
Black ≥ 8 Necessary 360h (48h) -
Silver ≥ 8 Necessary 480h (240h) -
Black ≥ 8 Necessary 480h (120h) -
Silver ≥ 5 / ≥ 8 Necessary 480h / 720h No
Silver ≥ 5 / ≥ 8 - (Possible) 480h / 720h No
Silver ≥ 5 - (Possible) 720h (Yes)
Dark / black 1 - 4 Oiled 8h No
Silver ≥ 8 Necessary 96h (6h) -
Silver ≥ 8 If necessary 144h (48h) -
Silver (iridescent) ≥ 8 Necessary 168h (72h) -
Silver ≥ 8 If necessary 240h (96h) -
(Silver) ≥ 8 Necessary 240h (24h) -
Silver / black ≥ 8 If necessary 480h (120h) -
(Silver) ≥ 8 Necessary 480h (120h) -
Silver / black ≥ 8 If necessary 720h (240h) -
Silver / black ≥ 10 If necessary 120h Yes
Silver ≥ 12 - (Possible) 480 / 720h No
Silver ≥ 8 / ≥ 12 If necessary 240h / 480h No
Silver ≥ 8 / ≥ 12 - (Possible) 480h conditional
Silver / black ≥ 12 - (Possible) 480h (120h) Yes
Black ≥ 12 - (Possible) 480h (240h) Yes
Black ≥ 12 - (Possible) 720h (120h) (Yes)
Silver ≥ 12 - (Possible) 480 / 720h (Yes)
Silver-gray ≥ 12 - (Possible) 480 / 720h (Yes)
Silver-gray ≥ 12 - (Possible) 480 / 720h (Yes)
Silver-gray ≥ 12 - (Possible) 480 / 720h Yes
2 With Cr(VI)-free surfaces, a considerably stronger scaling should be accounted for, compared to surfaces containing with Cr(VI), as there's no self-healing effect
Bolt and Screw Compendium
5.2 Lubrication
The primary task of lubricants is to set up a defined and constant coefficient offriction. Along with this task, lubricants can also fulfill other functions (e.g. Anti-corrosion, chemical resistance, optical characteristics etc.) where applicable.
Specifications VDA 235-101/ DIN 946 / DIN EN ISO 16047According to VDA 235-101, a total friction coefficient µtot of 0.09 – 0.14 is requiredfor lubricated bolts (partial friction coefficients µK and µG between 0.08 and 0.16).The determination of the friction coefficients generally is performed according toDIN 946 and DIN EN ISO 16047 respectively.
Influencing Factors(To be considered while choosing a suitable lubricant)The friction coefficients and their range, in practice, are greatly dependant on the following factors:
• Coating system of the bolt: Type of coating, thickness of layer etc.• Bearing plates: hard (e.g. hardened steel), middle (e.g. auto-body sheet steel),
soft (e.g. Al), uncoated / KTL-coated)• Geometry of the bolt-head: Convex / Concave bearing surface,
flange diameter, etc. • Nut thread: un-coated / coated (type of coating), crimped nut, etc.• End conditions: Temperature, dampness, tightening speed,
multiple surfaces etc.
NotesThe friction-coefficient window defined in the VDA test sheet 235-101 can generally beobtained by proper lubrication. The process-safe compliance in the serial productionwith acceptable range of distribution can still be problematic (» Influencing factors).In principle, integrated lubricants are best suited for majority applications. If required, friction coefficients over 0.14 can be reached through proper lubricanttreatment or through a single coating system without additional lubricant treatment.The spread of friction coefficients increases with increase in the coefficients. Friction coefficients under 0.08 are technically quite difficult to set, and are notdesired due to the required safety against self loosening of a joint.
Standard Lubricants with usual areas application (Example)
36 – 37
Product name Friction Coefficients Area of application(DIN 946)
Subsequently-applied LubricantsGardorol CP 8006 or similar 0.08 – 0.14 Phosphated bolts
(Motor bolts)
Torque N Tension Fluid 0.09 – 0.14 Zinc-plated coats /galv. surface
microGLEIT DF911 / 921 0.09 – 0.14 Zinc-plated coats /galv. surface
Gleitmo® 605 0.07 – 0.14 Galvanic surfaces
Gleitmo® 2332 V 0.09 – 0.14 Application withhigh temperatures
OKS® 1700 0.09 – 0.14 Aluminum bolts /thread-forming bolts
OKS® 1765 0.08 – 0.14 Thread-forming bolts
Gleitmo® 627 0.09 – 0.14 Austenitic bolts
Integrated LubricantsTorque N Tension 11 / 15 0.08 – 0.14 / 0.12 – 0.18 Galvanic surfacesmicroGLEIT DCP 9000 0.09 – 0.14 Zinc-plated coats /
galv. surface
DACROLUB® 10 / 15 0.10 – 0.14 / 0.15 – 0.20 DACROMET® 320 /GEOMET® 321
Geomet® 500 0.12 – 0.18 -
Plus® VL 0.09 – 0.14 GEOMET® 321
Plus® L / ML / M 0.08 – 0.14 / 0.10 – 0.16 / DACROMET® 320 / 0.15 – 0.20 GEOMET® 321
DELTA®-Seal GZ 0.10 – 0.16 DELTA®-Tone / DELTA®-Protekt KL 100
DP VH 301 GZ / VH 302 GZ 0.09 – 0.14 / 0.10 – 0.16 DELTA®-Tone / DELTA®-Protekt KL 100
B 18 / B 18 N / B 18 T 0.12 – 0.18 / 0.15 – 0.21 / MAGNI B 460.18 – 0.24
Bolt and Screw Compendium
6. Durability-compatible Configuration
The fatigue limit of a bolted connection can be raised through the following measures:
a) Rolling of threads after heat treatment; Please note: Disassembly of residual stress occurs during a temperature load.Hence it is important to note the working temperature and thermal load duringthe coating process.
b) Cold worked bolts from annealed raw material or tensile strength class 800 K.
c) The geometery of bolts constructed according to the largest possible elastic resilience. e.g. fully threaded parts, parts, waisted shank or reduced shank, hollow shaft option of the largest possible grip length.
d) Observance of the thermal expansion of bolted parts and fastener. Choosing materials with similar coefficients of expansion if possible.
e) Usage of MJ thread with enlarged core-radius according to DIN ISO 5855 sections 1-3.
f) Equal load distribution in threads:1.) Nut materials of smaller E-modules (e.g. cast iron, Aluminum, Titanium)2.) Nut materials of lower tensile strength (Note depth of thread!)3.) Nuts designed as tensile-nuts
g) Bolt head designed for fatigue endurance (e.g. bigger radius in head-shaft transition).Avoiding metal-cutting process, especially under the bolt head.
h) Reduction of setting amount through:1.) Reduction of joint faces/clamped parts2.) Avoiding over-loading of bearing faces.
(Note surface pressure!)3.) Usage of the smoothest possible bearing areas
6.1 Estimation of fatigue limits (reference value)
a) Heat treated after thread rolling
�ASV = 0.75 (180/d + 52)
b) Heat treated before thread rolling
�ASG = (2 - FV / F0.2) �ASV
38 – 39
+-
+-
Bolt and Screw Compendium
7. Miscellaneous
7.1 Conversion tables for hardness and tensile strength
Hardness test and Conversion Cold forming material and Punching in untempered Condition
HB, HV, HRc and Tensile Strength(according to DIN 50150 Table A.1 – Oct. 2000) – values partly interpolated
Brinell Conversion∅ 2.5 [mm] ∅ 5 [mm] ∅ 10 [mm] HB HV HRc Rm1.839 [kN] 7.355 [kN] 29.42 [kN] [N/mm2]
0.750 1.50 3.00 415 436 44.0 1407
0.760 1.52 3.04 404 424 43.1 1367
0.770 1.54 3.08 393 413 42.1 1331
0.780 1.56 3.12 383 402 41.0 1295
0.790 1.58 3.16 373 392 40.0 1262
0.800 1.60 3.20 363 381 38.9 1225
0.810 1.62 3.24 354 372 37.9 1195
0.820 1.64 3.28 345 362 36.8 1163
0.830 1.66 3.32 337 354 35.9 1137
0.840 1.68 3.36 329 346 34.9 1111
0.850 1.70 3.40 321 337 34.2 1082
0.860 1.72 3.44 313 329 33.3 1056
0.870 1.74 3.48 306 321 32.4 1031
0.880 1.76 3.52 298 313 31.5 1005
0.890 1.78 3.56 292 307 30.6 986
0.900 1.80 3.60 285 299 29.8 960
0.910 1.82 3.64 278 292 28.9 937
0.920 1.84 3.68 272 286 27.9 918
0.930 1.86 3.72 266 279 27.1 895
0.940 1.88 3.76 260 273 26.2 876
0.950 1.90 3.80 255 268 25.2 860
0.960 1.92 3.84 249 261 24.5 837
0.970 1.94 3.88 244 256 23.4 821
40 – 41
Brinell Conversion∅ 2.5 [mm] ∅ 5 [mm] ∅ 10 [mm] HB HV HRc Rm1.839 [kN] 7.355 [kN] 29.42 [kN] [N/mm2]
0.980 1.96 3.92 239 251 – 805
0.990 1.98 3.96 234 246 – 789
1.000 2.00 4.00 229 240 – 770
1.010 2.02 4.04 224 235 – 754
1.020 2.04 4.08 219 230 – 738
1.030 2.06 4.12 215 226 – 725
1.040 2.08 4.16 211 222 – 712
1.050 2.10 4.20 207 217 – 696
1.060 2.12 4.24 202 212 – 680
1.070 2.14 4.28 198 208 – 667
1.080 2.16 4.32 195 205 – 657
1.090 2.18 4.36 191 201 – 644
1.100 2.20 4.40 187 196 – 631
1.110 2.22 4.44 184 193 – 621
1.120 2.24 4.48 180 189 – 607
1.130 2.26 4.52 177 186 – 597
1.140 2.28 4.56 174 183 – 587
1.150 2.30 4.60 170 179 – 573
1.160 2.32 4.64 167 175 – 563
1.170 2.34 4.68 164 172 – 553
1.180 2.36 4.72 161 169 – 543
1.190 2.38 4.76 158 166 – 533
1.200 2.40 4.80 156 164 – 526
1.210 2.42 4.84 153 161 – 516
1.220 2.44 4.88 150 158 – 506
Bolt and Screw Compendium
Hardness test and Conversion Cold forming material and Punching in tempered Condition
HB, HV, HRc and Tensile Strength(according to DIN 50150 Table B.2 – Oct. 2000) – values partly interpolated
Brinell Conversion∅ 2.5 [mm] ∅ 5 [mm] ∅ 10 [mm] HBW HV HRc Rm1.839 [kN] 7.355 [kN] 29.42 [kN] [N/mm2]0.720 1.44 2.88 451 458 46.2 1424
0.725 1.45 2.90 444 450 45.7 1401
0.730 1.46 2.92 438 444 45.4 1390
0.735 1.47 2.94 432 438 44.7 1365
0.740 1.48 2.96 426 432 44.3 1347
0.745 1.49 2.98 420 426 43.7 1328
0.750 1.50 3.00 415 421 43.3 1317
0.755 1.51 3.02 409 414 43.0 1294
0.760 1.52 3.04 404 409 42.4 1281
0.765 1.53 3.06 398 403 41.8 1260
0.770 1.54 3.08 393 398 41.3 1244
0.775 1.55 3.10 388 393 40.8 1238
0.780 1.56 3.12 383 388 40.4 1214
0.785 1.57 3.14 378 383 39.9 1198
0.790 1.58 3.16 373 378 39.4 1185
0.795 1.59 3.18 368 373 38.9 1168
0.800 1.60 3.20 363 368 38.4 1152
0.805 1.61 3.22 359 364 38.0 1140
0.810 1.62 3.24 354 359 37.5 1125
0.815 1.63 3.26 350 355 37.1 1113
0.820 1.64 3.28 345 350 36.5 1097
0.825 1.65 3.30 341 346 36.0 1085
0.830 1.66 3.32 337 341 35.5 1073
0.835 1.67 3.34 333 337 35.1 1060
0.840 1.68 3.36 329 333 34.6 1046
0.845 1.69 3.38 325 329 34.2 1033
42 – 43
Brinell Conversion∅ 2.5 [mm] ∅ 5 [mm] ∅ 10 [mm] HB HV HRc Rm1.839 [kN] 7.355 [kN] 29.42 [kN] [N/mm2]0.850 1.70 3.40 321 325 33.7 1020
0.855 1.71 3.42 317 321 33.2 1006
0.860 1.72 3.44 313 317 32.7 994
0.865 1.73 3.46 309 313 32.2 981
0.870 1.74 3.48 306 310 31.8 972
0.875 1.75 3.50 302 306 31.3 959
0.880 1.76 3.52 298 302 30.8 946
0.885 1.77 3.54 295 299 30.4 937
0.890 1.78 3.56 292 296 29.9 925
0.895 1.79 3.58 288 292 29.3 915
0.900 1.80 3.60 285 289 28.9 906
0.905 1.81 3.62 282 286 28.5 896
0.910 1.82 3.64 278 282 28.0 883
0.915 1.83 3.66 275 279 27.6 874
0.920 1.84 3.68 272 276 27.1 864
0.925 1.85 3.70 269 273 26.7 852
0.930 1.86 3.72 266 270 26.2 845
0.935 1.87 3.74 263 268 26.0 842
0.940 1.88 3.76 260 266 25.6 832
0.945 1.89 3.78 257 262 24.9 819
0.950 1.90 3.80 255 260 24.6 813
0.955 1.91 3.82 252 257 24.1 803
Bolt and Screw Compendium
7.2 Size limit for regular (standard) and fine threads Metric ISO-threads, size limits for regular threads, DIN 13 Part 20, Oct 1983
Sym
bol
max
.m
in.
min
.m
ax.
min
.m
in.
max
.m
in.
min
.4h
- 6
h4h
6h4g
-6g
4g6g
4e-6
e4e
6e
oute
rØ=d
3.00
02.
933
2.89
42.
980
2.91
32.
874
2.95
02.
883
2.84
4M
3 x
0.5
flank
Ø=d
22.
675
2.62
72.
600
2.65
52.
607
2.58
02.
625
2.57
72.
550
core
Ø=d
32.
387
2.32
02.
293
2.36
72.
299
2.27
32.
337
2.27
02.
243
oute
rØ=d
4.00
03.
910
3.86
03.
978
3.88
83.
838
3.94
43.
854
3.80
4M
4 x
0.7
flank
Ø=d
23.
545
3.48
93.
455
3.52
33.
467
3.43
33.
489
3.43
33.
399
core
Ø=d
33.
141
3.05
83.
024
3.11
93.
036
3.00
23.
085
3.00
22.
968
oute
rØ=d
5.00
04.
905
4.85
04.
976
4.88
14.
826
4.94
04.
845
4.79
0M
5 x
0.8
flank
Ø=d
24.
480
4.42
04.
385
4.45
64.
396
4.36
14.
420
4.36
04.
325
core
Ø=d
34.
019
3.92
83.
893
3.99
53.
903
3.86
93.
959
3.86
83.
833
oute
rØ=d
6.00
05.
888
5.82
05.
974
5.86
25.
794
5.94
05.
828
5.76
0M
6 x
1.0
flank
Ø=d
25.
350
5.27
95.
238
5.32
45.
253
5.21
25.
290
5.21
95.
178
core
Ø=d
34.
773
4.66
34.
622
4.74
74.
637
4.59
64.
713
4.60
34.
562
oute
rØ=d
7.00
06.
888
6.82
06.
974
6.86
26.
794
6.94
06.
828
6.76
0M
7 x
1.0
flank
Ø=d
26.
350
6.27
96.
238
6.32
46.
253
6.21
26.
290
6.21
96.
178
core
Ø=d
35.
773
5.66
35.
622
5.74
75.
637
5.59
65.
713
5.60
35.
562
oute
rØ=d
8.00
07.
868
7.78
87.
972
7.84
07.
760
7.93
77.
805
7.72
5M
8 x
1.25
flank
Ø=d
27.
188
7.11
37.
070
7.16
07.
085
7.04
27.
125
7.05
07.
007
core
Ø=d
36.
466
6.34
36.
300
6.43
86.
315
6.27
26.
403
6.28
06.
237
oute
rØ=d
9.00
08.
868
8.78
88.
972
8.84
08.
760
8.93
78.
805
8.72
5M
9 x
1.25
flank
Ø=d
28.
188
8.11
38.
070
8.16
08.
085
8.04
28.
125
8.05
08.
007
core
Ø=d
37.
466
7.34
37.
300
7.43
87.
315
7.27
27.
403
7.28
07.
237
oute
rØ=d
10.0
009.
850
9.76
49.
968
9.81
89.
732
9.93
39.
783
9.69
7M
10 x
1.5
flank
Ø=d
29.
026
8.94
18.
894
8.99
48.
909
8.86
28.
959
8.87
48.
827
core
Ø=d
38.
160
8.01
77.
970
8.12
87.
985
7.93
88.
093
7.95
07.
903
oute
rØ=d
11.0
0010
.850
10.7
6410
.968
10.8
1810
.732
10.9
3310
.783
10.6
97M
11 x
1.5
flank
Ø=d
210
.026
9.94
19.
894
9.99
49.
909
9.86
29.
959
9.87
49.
827
core
Ø=d
39.
160
9.01
78.
970
9.12
88.
985
8.93
89.
093
8.95
08.
903
44
Metric ISO-threads, size limits for regular threads, DIN 13 Part 20, Oct 1983
– 45
Sym
bol
max
.m
in.
min
.m
ax.
min
.m
in.
max
.m
in.
min
.4h
- 6
h4h
6h4g
-6g
4g6g
4e-6
e4e
6e
oute
rØ=d
12.0
0011
.830
11.7
3511
.966
11.7
9611
.701
11.9
2911
.759
11.6
64M
12 x
1.7
5fla
nkØ
=d2
10.8
6310
.768
10.7
1310
.829
10.7
3410
.679
10.7
9210
.697
10.6
42co
reØ
=d3
9.85
39.
691
9.63
59.
819
9.65
69.
602
9.78
29.
619
9.56
5
oute
rØ=d
14.0
0013
.820
13.7
2013
.962
13.7
8213
.682
13.9
2913
.749
13.6
49M
14 x
2.0
flank
Ø=d
212
.701
12.6
0112
.541
12.6
6312
.563
12.5
0312
.630
12.5
3012
.470
core
Ø=d
311
.546
11.3
6911
.309
11.5
0811
.331
11.2
7111
.475
11.2
9811
.238
oute
rØ=d
16.0
0015
.820
15.7
2015
.962
15.7
8215
.682
15.9
2915
.749
15.6
49M
16 x
2.0
flank
Ø=d
214
.701
14.6
0114
.541
14.6
6314
.563
14.5
0314
.630
14.5
3014
.470
core
Ø=d
313
.546
13.3
6913
.309
13.5
0813
.331
13.2
7113
.475
13.2
9813
.238
oute
rØ=d
18.0
0017
.788
17.6
6517
.958
17.7
4617
.623
17.9
2017
.708
17.5
85M
18 x
2.5
flank
Ø=d
216
.376
16.2
7016
.206
16.3
3416
.228
16.1
6416
.296
16.1
9016
.126
core
Ø=d
314
.933
14.7
3114
.666
14.8
9114
.688
14.6
2514
.853
14.6
5014
.587
oute
rØ=d
20.0
0019
.788
19.6
6519
.958
19.7
4619
.623
19.9
2019
.708
19.5
85M
20 x
2.5
flank
Ø=d
218
.376
18.2
7018
.206
18.3
3418
.228
18.1
6418
.296
18.1
9018
.126
core
Ø=d
316
.933
16.7
3116
.666
16.8
9116
.688
16.6
2516
.853
16.6
5016
.587
oute
rØ=d
22.0
0021
.788
21.6
6521
.958
21.7
4621
.623
21.9
2021
.708
21.5
85M
22 x
2.5
flank
Ø=d
220
.376
20.2
7020
.206
20.3
3420
.228
20.1
6420
.296
20.1
9020
.126
core
Ø=d
318
.933
18.7
3118
.666
18.8
9118
.688
18.6
2518
.853
18.6
5018
.587
oute
rØ=d
24.0
0023
.764
23.6
2523
.952
23.7
1623
.577
23.9
1523
.679
23.5
40M
24 x
3.0
flank
Ø=d
222
.051
21.9
2621
.851
22.0
0321
.878
21.8
0321
.966
21.8
4121
.766
core
Ø=d
320
.319
20.0
7820
.003
20.2
7120
.030
19.9
5520
.234
19.9
9319
.918
oute
rØ=d
27.0
0026
.764
26.6
2526
.952
26.7
1626
.577
26.9
1526
.679
26.5
40M
27 x
3.0
flank
Ø=d
225
.051
24.9
2624
.851
25.0
0324
.878
24.8
0324
.966
24.8
4124
.766
core
Ø=d
323
.319
23.0
7823
.003
23.2
7123
.030
22.9
5523
.234
22.9
9322
.918
oute
rØ=d
30.0
0029
.735
20.5
7529
.947
29.6
8229
.522
29.9
1029
.645
29.4
85M
30 x
3.5
flank
Ø=d
227
.727
27.5
9527
.515
27.6
7427
.542
27.4
6227
.637
27.5
0527
.425
core
Ø=d
325
.706
25.4
3925
.359
25.6
5325
.386
25.3
0625
.616
25.3
4925
.269
Bolt and Screw Compendium
Sym
bol
max
.m
in.
min
.m
ax.
min
.m
in.
max
.m
in.
min
.4h
- 6
h4h
6h4g
-6g
4g6g
4e-6
e4e
6e
oute
rØ=d
8.00
07.
910
7.86
07.
978
7.88
87.
838
7.94
47.
854
7.80
4M
8 x
0.75
flank
Ø=d
27.
513
7.45
07.
413
7.49
17.
428
7.39
17.
457
7.39
47.
357
core
Ø=d
37.
080
6.98
86.
951
7.05
86.
968
6.92
97.
024
6.93
26.
895
oute
rØ=d
8.00
07.
888
7.82
07.
974
7.86
27.
794
7.94
07.
828
7.76
0M
8 x
1.0
flank
Ø=d
27.
350
7.27
97.
238
7.32
47.
253
7.21
27.
290
7.21
97.
178
core
Ø=d
36.
773
6.66
36.
622
6.74
76.
637
6.59
66.
713
6.60
36.
562
oute
rØ=d
9.00
08.
888
8.82
08.
974
8.86
28.
794
8.94
08.
828
8.76
0M
9 x
1.0
flank
Ø=d
28.
350
8.27
98.
238
8.32
48.
253
8.21
28.
290
8.21
98.
178
core
Ø=d
37.
773
7.66
37.
622
7.74
77.
637
7.59
67.
713
7.60
37.
562
oute
rØ=d
10.0
009.
888
9.82
09.
974
9.86
29.
794
9.94
09.
828
9.76
0M
10 x
1.0
flank
Ø=d
29.
350
9.27
99.
238
9.32
49.
253
9.21
29.
290
9.21
99.
178
core
Ø=d
38.
773
8.66
38.
622
8.74
78.
637
8.59
68.
713
8.60
38.
562
oute
rØ=d
10.0
009.
868
9.78
89.
982
9.84
09.
760
9.93
79.
805
9.72
5M
10 x
1.2
5fla
nkØ
=d2
9.18
89.
113
9.07
09.
160
9.08
59.
042
9.12
59.
050
9.00
7co
reØ
=d3
8.46
68.
343
8.30
08.
438
8.31
58.
272
8.40
38.
280
8.23
7
oute
rØ=d
12.0
0011
.888
11.8
2011
.974
11.8
6211
.794
11.9
4011
.828
11.7
60M
12 x
1.0
flank
Ø=d
211
.350
11.2
7511
.232
11.3
2411
.249
11.2
0611
.290
11.2
1511
.172
core
Ø=d
310
.773
10.6
5910
.616
10.7
4710
.633
10.5
9010
.713
10.5
9910
.556
oute
rØ=d
12.0
0011
.868
11.7
8811
.972
11.8
4011
.760
11.9
3711
.805
11.7
25M
12 x
1.2
5fla
nkØ
=d2
11.1
8811
.103
11.0
5611
.160
11.0
7511
.028
11.1
2511
.040
10.9
93co
reØ
=d3
10.4
6610
.333
10.2
8610
.438
10.3
0510
.258
10.4
0310
.270
10.2
23
oute
rØ=d
12.0
0011
.850
11.7
6411
.968
11.8
1811
.732
11.9
3311
.783
11.6
97M
12 x
1.5
flank
Ø=d
211
.026
10.9
3610
.886
10.9
9410
.904
10.8
5410
.959
10.8
6910
.819
core
Ø=d
310
.160
10.0
129.
962
10.1
289.
980
9.93
010
.093
9.94
59.
895
oute
rØ=d
14.0
0013
.888
13.8
2013
.974
13.8
6213
.794
13.9
4013
.828
13.7
60M
14 x
1.0
flank
Ø=d
213
.350
13.2
7513
.232
13.3
2413
.249
13.2
0613
.290
13.2
1513
.172
core
Ø=d
312
.773
12.6
5912
.616
12.7
4712
.633
12.5
9012
.713
12.5
9912
.556
oute
rØ=d
14.0
0013
.850
13.7
6413
.968
13.8
1813
.732
13.9
3313
.783
13.6
97M
14 x
1.5
flank
Ø=d
213
.026
12.9
3612
.886
12.9
9412
.904
12.8
5412
.959
12.8
6912
.819
core
Ø=d
312
.160
12.0
1211
.962
12.1
2811
.980
11.9
3012
.093
11.9
4511
.895
Metric ISO-threads, size limits for fine pitch threads, DIN 13 Part 21, Oct 1983
46
Sym
bol
max
.m
in.
min
.m
ax.
min
.m
in.
max
.m
in.
min
.4h
- 6
h4h
6h4g
-6g
4g6g
4e-6
e4e
6e
oute
rØ=d
16.0
0015
.888
15.8
2015
.974
15.8
6215
.794
15.9
4015
.828
15.7
60M
16 x
1.0
flank
Ø=d
215
.350
15.2
7515
.232
15.3
2415
.249
15.2
0615
.290
15.2
1515
.172
core
Ø=d
314
.773
14.6
5914
.616
14.7
4714
.633
14.5
9014
.713
14.5
9914
.556
oute
rØ=d
16.0
0015
.850
15.7
6415
.968
15.8
1815
.732
15.9
3315
.783
15.6
97M
16 x
1.5
flank
Ø=d
215
.026
14.9
3614
.886
14.9
9414
.904
14.8
5414
.959
14.8
6914
.819
core
Ø=d
314
.160
14.0
1213
.962
14.1
2813
.980
13.9
3014
.093
13.9
4513
.895
oute
rØ=d
18.0
0017
.850
17.7
6417
.968
17.8
1817
.732
17.9
3317
.783
17.6
97M
18 x
1.5
flank
Ø=d
217
.026
16.9
3616
.886
16.9
9416
.904
16.8
5416
.959
16.8
6916
.819
core
Ø=d
316
.160
16.0
1215
.962
16.1
2815
.980
15.9
3016
.093
15.9
4515
.895
oute
rØ=d
18.0
0017
.820
17.7
2017
.962
17.7
8217
.682
17.9
2917
.749
17.6
49M
18 x
2.0
flank
Ø=d
216
.701
16.6
0116
.541
16.6
6316
.563
16.5
0316
.630
16.5
3016
.470
core
Ø=d
315
.546
15.3
6915
.309
15.5
0815
.331
15.2
7115
.475
15.2
9815
.238
oute
rØ=d
20.0
0019
.850
19.7
6419
.968
19.8
1819
.732
19.9
3319
.783
19.6
97M
20 x
1.5
flank
Ø=d
219
.026
18.9
3618
.886
18.9
9418
.904
18.8
5418
.959
18.8
6918
.819
core
Ø=d
318
.160
18.0
1217
.962
18.1
2817
.980
17.9
3018
.093
17.9
4517
.895
oute
rØ=d
20.0
0019
.820
19.7
2019
.962
19.7
8219
.682
19.9
2919
.749
19.6
49M
20 x
2.0
flank
Ø=d
218
.701
18.6
0118
.541
18.6
6318
.563
18.5
0318
.630
18.5
3018
.470
core
Ø=d
317
.546
17.3
6917
.309
17.5
0817
.331
17.2
7117
.475
17.2
9817
.238
oute
rØ=d
22.0
0021
.850
21.7
6421
.968
21.8
1821
.732
21.9
9321
.783
21.6
97M
22 x
1.5
flank
Ø=d
221
.026
20.9
3620
.886
20.9
9420
.904
20.8
5420
.959
20.8
6920
.819
core
Ø=d
320
.160
20.0
1219
.962
20.1
2819
.980
19.9
3020
.093
19.9
4519
.895
oute
rØ=d
22.0
0021
.820
21.7
2021
.962
21.7
8221
.682
21.9
2921
.749
21.6
49M
22 x
2.0
flank
Ø=d
220
.701
20.6
0120
.541
20.6
6320
.563
20.5
0320
.630
20.5
3020
.470
core
Ø=d
319
.546
19.3
6919
.309
19.5
0819
.331
19.2
7119
.475
19.2
9819
.238
oute
rØ=d
24.0
0023
.850
23.7
6423
.968
23.8
1823
.732
23.9
3323
.783
23.6
97M
24 x
1.5
flank
Ø=d
223
.026
22.9
3122
.876
22.9
9422
.899
22.8
4422
.959
22.8
6422
.809
core
Ø=d
322
.160
22.0
0721
.952
22.1
2821
.975
21.9
2022
.093
21.9
4021
.885
oute
rØ=d
24.0
0023
.820
23.7
2023
.962
23.7
8223
.682
23.9
2923
.749
23.6
49M
24 x
2.0
flank
Ø=d
222
.701
22.5
9522
.531
22.6
6322
.557
22.4
9322
.630
22.5
2422
.460
core
Ø=d
321
.546
21.3
6321
.299
21.5
0821
.325
21.2
6121
.475
21.2
9221
.228
Metric ISO-threads, size limits for fine pitch threads, DIN 13 Part 21, Oct 1983
– 47
Bolt and Screw Compendium
7.3 GO Screw ring gage measurement acc. DIN/ISO 1502 edition 01/12.96th
read
sm
in.
Flan
k-Ø
Flan
k-Ø
Tigh
teni
ngco
re-Ø
oute
r-Ø
(tol
eran
cew
ear
limit
torq
ue
ball
cont
act
Test
dim
ensi
on
Test
Dim
ensi
on
(tol
eran
cein
µm
)N
m m
ax.
M (t
ol. i
n µm
)M
wor
n ou
tin
µm
)
M6
-6h
6.08
15.
348
±7
5.36
40.
220.
620
5.59
2 ±
75.
608
4.91
7±
7M
8-6
h8.
099
7.18
6±
77.
202
0.51
0.72
57.
5416
±
77.
5576
6.64
7±
7M
8 x
1.0
-6h
8.08
17.
348
±7
7.36
40.
510.
620
7.59
3 ±
77.
609
6.91
7±
7M
10-6
h10
.119
59.
018
±9
9.03
91.
00.
837
9.47
8 ±
99.
499
8.37
6±
9M
10 x
1.0
-6h
10.0
819.
348
±7
9.36
41.
00.
620
9.59
34 ±
79.
6094
8.91
7±
7M
10 x
1.2
5-6
h10
.099
9.18
6±
79.
202
1.0
0.72
59.
5424
±7
9.55
848.
647
±7
M12
-6h
12.1
375
10.8
55±
910
.876
1.73
1.10
11.2
68
±9
11.2
8910
.106
±9
M12
x 1
.0-6
h12
.081
11.3
48±
711
.364
1.73
0.62
011
.593
6±
711
.609
610
.917
±7
M12
x 1
.25
-6h
12.1
0111
.180
±9
11.2
011.
730.
725
11.5
368
±9
11.5
578
10.6
47±
9M
12 x
1.5
-6h
12.1
195
11.0
18±
911
.039
1.73
0.83
711
.478
7±
911
.499
710
.376
±9
M14
-6h
14.1
555
12.6
93±
912
.714
2.7
1.11
213
.310
7±
913
.331
711
.835
±9
M14
x 1
.0-6
h14
.081
13.3
48±
713
.364
2.7
0.62
013
.593
7±
713
.609
712
.917
±7
M14
x 1
.5-6
h14
.119
513
.018
±9
13.0
392.
70.
837
12.4
791
±9
13.5
001
12.3
76±
9M
16-6
h16
.155
514
.693
±9
14.7
144.
11.
112
15.3
113
±9
15.3
323
13.8
35±
9M
16 x
1.0
-6h
16.0
8115
.348
±7
15.3
644.
10.
620
15.5
938
±7
15.6
098
14.9
17±
7M
16 x
1.5
-6h
16.1
195
15.0
18±
915
.039
4.1
0.83
715
.479
4±
915
.500
414
.376
±9
M18
-6h
18.1
915
16.3
68±
916
.389
5.8
1.35
017
.180
4±
917
.201
415
.294
±9
M18
x 1
.5-6
h18
.119
517
.018
±9
17.0
395.
80.
837
17.4
795
±9
17.5
005
16.3
76±
9M
18 x
2.0
-6h
18.1
555
16.6
93±
916
.714
5.8
1.11
217
.311
7±
917
.332
715
.835
±9
M20
-6h
20.1
915
18.3
68±
918
.389
81.
3519
.181
±9
19.2
0217
.294
±9
M20
x 1
.5-6
h20
.119
519
.018
±9
19.0
398
0.83
719
.479
6±
919
.500
618
.376
±9
M20
x 2
.0-6
h20
.155
518
.693
±9
18.7
148
1.11
219
.312
±9
19.3
3317
.835
±9
M22
-6h
22.1
915
20.3
68±
920
.389
10.6
1.35
21.1
814
±9
21.2
024
19.2
94±
9M
22 x
1.5
-6h
22.1
195
21.0
18±
921
.039
10.6
0.83
721
.479
7±
921
.500
720
.376
±9
M22
x 2
.0-6
h22
.155
520
.693
±9
20.7
1410
.61.
112
21.3
122
±9
21.3
332
19.8
35±
9M
24-6
h24
.227
522
.043
±9
22.0
6413
.81.
773
22.8
653
±9
22.8
863
20.7
52±
9M
24 x
1.5
-6h
24.1
195
23.0
18±
923
.039
13.8
0.83
723
.479
8±
923
.500
822
.376
±9
M24
x 2
.0-6
h24
.155
522
.693
±9
22.7
1413
.81.
112
23.3
123
±9
23.3
333
21.8
35±
9
Test
dim
ensi
ons
for
wea
r-lim
its
48
thre
ads
min
.Fl
ank-
ØFl
ank-
ØTi
ghte
ning
Kern
-Øou
ter-
Ø(t
oler
ance
wea
r lim
itto
rque
ball
cont
act
Test
dim
ensi
onTe
st D
imen
sion
(Tol
eran
zin
µm
)N
m m
ax.
M (t
ol. i
n µm
)M
wor
n ou
tin
µm
)
M6
-6g
6.05
55.
322
±7
5.33
80.
220.
620
5.56
6±
75.
582
4.89
1±
7M
8-6
g8.
071
7.15
8±
77.
174
0.51
0.72
57.
5136
±7
7.52
966.
619
±7
M8
x 1.
0-6
g8.
055
7.32
2±
77.
338
0.51
0.62
07.
567
±7
7.58
36.
891
±7
M10
-6g
10.0
875
8.98
6±
99.
007
1.0
0.83
79.
446
±9
9.46
78.
344
±9
M10
x 1
.0-6
g10
.055
9.32
2±
79.
338
1.0
0.62
09.
5674
±7
9.58
348.
891
±7
M10
x 1
.25
-6g
10.0
719.
158
±7
9.17
41.
00.
725
9.51
44±
79.
5304
8.61
9±
7M
12-6
g12
.103
510
.821
±9
10.8
421.
731.
1011
.233
9±
911
.254
910
.072
±9
M12
x 1
.0-6
g12
.055
11.3
22±
711
.338
1.73
0.62
011
.567
6±
711
.583
610
.891
±7
M12
x 1
.25
-6g
12.0
7311
.152
±9
11.1
731.
730.
725
11.5
088
±9
11.5
298
10.6
19±
9M
12 x
1.5
-6g
12.0
875
10.9
86±
911
.007
1.73
0.83
711
.446
7±
911
.467
710
.344
±9
M14
-6g
14.1
175
12.6
55±
912
.676
2.7
1.11
213
.272
7±
913
.293
711
.797
±9
M14
x 1
.0-6
g14
.055
13.3
22±
713
.338
2.7
0620
13.5
677
±7
13.5
837
12.8
71±
7M
14 x
1.5
-6g
14.0
875
12.9
86±
913
.007
2.7
0.83
713
.447
1±
913
.468
114
.344
±9
M16
-6g
16.1
175
14.6
55±
914
.676
4.1
1.11
215
.273
3±
915
.294
313
.797
±9
M16
x 1
.0-6
g16
.055
15.3
22±
715
.338
4.1
0.62
015
.567
8±
715
.583
814
.891
±7
M16
x 1
.5-6
g16
.087
514
.986
±9
15.0
074.
10.
837
15.4
471
±9
15.4
681
12.3
44±
9M
18-6
g18
.149
516
.326
±9
16.3
475.
81.
350
17.1
384
±9
17.1
594
15.2
52±
9M
18 x
1.5
-6g
18.0
875
16.9
86±
917
.007
5.8
0.83
717
.447
5±
917
.468
516
.344
±9
M18
x 2
.0-6
g18
.117
516
.655
±9
16.6
765.
81.
112
17.2
737
±9
17.2
947
15.7
97±
9M
20-6
g20
.149
518
.326
±9
18.3
478
1.35
19.1
39±
919
.160
17.2
52±
9M
20 x
1.5
-6g
20.0
875
18.9
86±
919
.007
80.
837
19.4
476
±9
19.4
686
18.3
44±
9M
20 x
2.0
-6g
20.1
175
18.6
55±
918
.676
81.
112
19.2
74±
919
.295
17.7
97±
9M
22-6
g22
.149
520
.326
±9
20.3
4710
.61.
3521
.139
4±
921
.160
419
.252
±9
M22
x 1
.5-6
g22
.087
520
.986
±9
21.0
0710
.60.
837
21.4
47±
921
.468
720
.344
±9
M22
x 2
.0-6
g22
.117
520
.655
±9
20.6
7610
.61.
112
21.2
742
±9
21.2
952
19.7
97±
9M
24-6
g24
.179
521
.995
±9
22.0
1613
.81.
776
22.8
172
±9
22.8
382
20.7
04±
9M
24 x
1.5
-6g
24.0
875
22.9
86±
923
.007
13.8
0.83
723
.447
8±
923
.468
822
.344
±9
M24
x 2
.0-6
g24
.117
522
.655
±9
22.6
7613
.81.
112
23.2
743
±9
23.2
953
21.7
97±
9
Test
dim
ensi
ons
for
wea
r-lim
its
– 49
Bolt and Screw Compendium
7.4 Tolerance symbols and toleranced propertiesTo
lera
nces
for
for
m a
nd p
osit
ion
(Sum
mar
y of
IN IS
O 1
101)
Tole
ranc
e sy
mbo
l and
Ex
ampl
es f
or a
pplic
atio
nto
lera
nced
cha
ract
eris
tic
Tole
ranc
e zo
neDi
agra
m s
peci
ficat
ions
Expl
anat
ion
Stra
ight
ness
of a
line
Ever
y ge
nera
trix
mus
t lie
at
adi
stan
ce o
f t
= 0.
03m
m b
etw
een
two
para
llel p
lane
s.
Even
ness
of a
n ar
eaTh
e to
lera
nced
are
a m
ust
lie a
t a
dist
ance
of
0.05
mm
bet
wee
n tw
opa
ralle
l pla
nes.
Roun
dnes
s of
the
circ
umfe
renc
e of
a c
ylin
der,
The
tole
ranc
ed c
ircum
fere
ntia
l lin
e of
eve
ry
disc
, con
e et
c.cr
oss-
sect
ion
perp
endi
cula
r to
the
axi
s m
ust
lie a
t a
radi
al d
ista
nce
of t
- 0
.02m
m b
etw
een
two
conc
entr
ic c
ircle
s.
Cylin
dric
al f
orm
The
tole
ranc
ed c
ylin
der
shel
l mus
t lie
be
twee
n tw
o co
axia
l cyl
inde
rs t
hat
have
a
radi
al d
ista
nce
of t
= 0
.05.
Form
50 – 51
Tole
ranc
e sy
mbo
l and
Ex
ampl
es f
or a
pplic
atio
nto
lera
nced
cha
ract
eris
tic
Tole
ranc
e zo
neDi
agra
m s
peci
ficat
ions
Expl
anat
ion
The
tole
ranc
ed p
rofil
e m
ust,
in e
very
sec
tion
plan
e pa
ralle
l to
the
draw
ing
plan
e (in
whi
chth
e pr
ofile
is t
oler
ance
d), l
ie b
etw
een
two
clad
ding
line
s w
hose
dis
tanc
e th
roug
h th
eci
rcle
is li
mite
d by
the
dia
met
er t
= 0
.08
mm
.Th
e ce
nter
s of
the
se c
ircle
s lie
on
the
geo-
met
rical
ly p
erfe
ct a
rea.
Line
for
mof
an
arbi
trar
y lin
e (p
rofil
e)
Form
Area
for
mof
an
arbi
trar
y su
rfac
e ar
ea
The
tole
ranc
ed p
rofil
e m
ust,
in e
very
sec
tion
plan
e pa
ralle
l to
the
draw
ing
plan
e (in
whi
chth
e pr
ofile
is t
oler
ance
d) b
etw
een
two
clad
ding
line
s w
hose
dis
tanc
e th
roug
h th
eci
rcle
is li
mite
d by
the
dia
met
er t
= 0
.01
to0.
05 m
m. T
he c
ente
rs o
f th
ese
circ
les
lie o
nth
e ge
omet
rical
ly p
erfe
ct a
rea.
The
tole
ranc
ed a
rea
mus
t lie
bet
wee
n tw
ocl
addi
ng a
reas
, who
se d
ista
nce
thro
ugh
the
sphe
re is
lim
ited
by th
e di
amet
er t
= 0.
03 m
m.
The
cent
ers
of t
hese
sph
eres
lie
on t
he g
eo-
met
rical
ly p
erfe
ct a
rea.
Ref.
arro
w
tole
ranc
ed
elem
ent
ref.
lett
er
(if n
eces
sary
)
Refe
renc
e le
tter
Ref.
tria
ngle
Ref.
elem
ent
Tole
ranc
e sy
mbo
l
Tole
ranc
e va
lue
(t)
Sym
bol f
orm
ax. m
ater
ial
cond
ition
Theo
retic
ally
exac
t m
ass.
Ref.
to a
xis
and
cent
er p
lane
Ref.
to li
ne
Bolt and Screw Compendium
Tole
ranc
e sy
mbo
l and
Ex
ampl
es f
or a
pplic
atio
nto
lera
nced
cha
ract
eris
tic
Tole
ranc
e zo
neDi
agra
m s
peci
ficat
ions
Expl
anat
ion
Para
llelis
mof
a li
ne (a
xis)
to
The
tole
ranc
ed u
pper
bor
e ax
is m
ust
lie
a re
fere
nce
line
(axi
s)w
ithin
a c
ylin
der
para
llel t
o th
e re
fere
nce
axis
A, o
f di
amet
er t
= 0
.1 m
m.
Perp
endi
cula
rity
of a
n ar
ea t
o a
refe
renc
e ar
ea
The
tole
ranc
ed a
rea
mus
t lie
bet
wee
n tw
o (o
f a li
ne …
acc
ordi
ng t
o th
e ex
ampl
epl
anes
whi
ch a
re p
aral
lel t
o ea
ch o
ther
and
fo
r „i
nclin
atio
n“)
perp
endi
cula
r to
the
ref
eren
ce a
rea
„A“,
at a
dis
tanc
e of
t =
0.0
8mm
.
Incl
inat
ion
(Ang
ular
ity)
of a
line
(axi
s) t
o a
refe
renc
e ar
ea
The
tole
ranc
ed b
ore
axis
mus
t lie
at a
dist
ance
(of
a re
fere
nce
area
....a
ccor
ding
to
of o
f t =
0.1
mm
bet
wee
n tw
o pl
anes
par
alle
lth
e ex
ampl
e fo
r 'p
erpe
ndic
ular
ity')
to e
ach
othe
r and
incl
ined
at
a ge
omet
rical
lype
rfec
t an
gle
of 6
0˚ t
o th
e re
fere
nce
area
A.
of a
n ar
ea t
o a
refe
renc
e ar
eaTh
e to
lera
nced
are
a m
ust
lie b
etw
een
two
plan
es p
aral
lel t
o th
e re
fere
nce
area
at
a di
stan
ce o
f t
= 0.
01 m
m.
PositionDirection
52 – 53
Tole
ranc
e sy
mbo
l and
Ex
ampl
es f
or a
pplic
atio
nto
lera
nced
cha
ract
eris
tic
Tole
ranc
e zo
neDi
agra
m s
peci
ficat
ions
Expl
anat
ion
Posi
tion
Th
e to
lera
nced
axi
s of
the
hole
mus
t lie
with
inof
line
s (a
xes)
cro
ss-c
onne
cted
a
cylin
der o
f dia
met
er t
= 0.
05m
m, w
hose
axi
sw
ith e
ach
othe
r or
to
one
or m
ore
lies
on t
he g
eom
etric
ally
per
fect
pos
ition
refe
renc
e el
emen
ts(w
ith f
ram
ed d
imen
sion
s).
Axia
l Run
-out
Th
e to
lera
nced
axi
s of
the
rig
ht c
ylin
der
(con
cent
ricity
) of
an a
xis
to a
of
the
sha
ft m
ust
lie w
ithin
a c
ylin
der
of
refe
renc
e ax
isdi
amet
er t
= 0
.03
mm
, coa
xial
to
a re
fere
nce
axis
Axia
l Run
-out
Fo
r ro
tatio
n ar
ound
the
ref
eren
ce a
xis
A,
the
late
ral r
un-o
ut m
ay n
ot e
xcee
d th
e va
lue
of t
= 0
.02
mm
, mea
sure
d pa
ralle
l an
d at
an
arbi
trar
y di
stan
ce f
rom
the
re
fere
nce
axis
A.
Radi
al R
un-o
utFo
r ro
tatio
n ar
ound
the
ref
eren
ce a
xis
A-B,
of a
cyl
inde
r sh
ell t
o a
the
tole
ranc
ed c
ircum
fere
ntia
l lin
e of
eve
ry
(ref
eren
ce) p
ivot
perp
endi
cula
r cr
oss-
sect
ion
of t
he s
haft
's m
iddl
e cy
linde
r mus
t lie
bet
wee
n tw
o co
ncen
tric
circ
les
at a
rad
ial d
ista
nce
of t
= 0
.1 m
m.
Sym
met
ry
The
tole
ranc
ed c
ente
r pla
ne o
f the
nut
mus
t
of a
cen
ter
plan
e to
alie
bet
wee
n tw
o pa
ralle
l pla
nes
whi
ch h
ave
refe
renc
e ce
nter
pla
nea
dist
ance
of
t =
0.08
mm
, and
are
ord
ered
sy
mm
etric
ally
to
the
refe
renc
e ce
nter
pla
neA
of b
oth
the
oute
r ar
eas.
Place Run-outPosition
Bolt and Screw Compendium
Lengths1 mm = 0.03937014 inches (Zoll) 1 inch = 25.399956 mm1 m = 3.280851 feet (Fuß) 1 foot = 12 inch = 304.799472 mm1 m = 1.093616 yards 1 yard = 3 feet = 0.914398 m1 km = 0.621372 engl. Meile 1 mile = 1760 yards = 1.609341 km1 km = 0.539614 Seemeile 1 nautc. mile = 1.853178 kmAreas1 mm2 = 0.00155001 sq. in. (Zoll) 1 sq. inch = 6.451578 cm2
1 m2 = 19.76398328 sq. feet 1 sq. foot = 144 sq. inch = 929.0272 cm2
1 m2 = 1.19599596 sq. yards 1 sq. yard = 9 sq. feet = 8361.2448 cm2
1 a = 100 m_ = 0.024711 arces 1 arces = 4840 sq. yards = 40.4684 a1 ha = 100 a = 2.471063 arces1 km2 = 100 ha = 0.3861 sq. miles 1 sq mile = 640 arces = 2.59 km2
Volumes1 cm3 = 0.061024 cubic inch 1 cubic inch = 16.386979 cm3
1 dm3 = 0.035315 cubic feet 1 cubic foot = 28.3167 dm3
1 m3 = 1.307957 cubic yard 1 cubic yard = 0.764551 m3
1 m3 = 0.353148 Register tons 1 register ton = 100 cubic feet = 2.83167 m3
1 l = 0.220097 gallons (UK) 1 gallon (US) = 0.83268 gal (UK)1 l = 0.264323 gallons (US) 1 gallon (US) = 3.78324 l1 hl = 100 lForces Masses1 kg = 2.20462 lbs (pounds) 1 lb = 0.453592 kg1 kp = 9.80665 N 1 lbf = 4.44822 N1 N = 0.224809 lbf 1 fi lb = 1.35582 J1 J = 0.737561 ft lb 1 btu = 1.05506 kJOther dimensions1 Nm = 1 Joule = 0.737456 ft-lbs 1 ft-lb = 1.35582 Nm1 Nm = 8.8495 lbs-in 1 lb-in = 0.113 Nm1 N/mm2 = 1 MPa = 0.0069 psi1 atm = 1.01325 bar1 l/100 km = 235.1 miles/gallon (US) 100 miles/gallon (US) = 0.4254 l/100 km
7.5 Conversion of German and English Units of Measurements
54
8. Formula Index
At Shearing area at lateral loadA0 Smallest applicable cross-sectional area of the boltd Diameter of boltd2 Thread diameter of boltFA Axial forceFKerf Clamping force required for fulfillment of the functionFKR Residual clamping force at working jointFM Assembly preloadFMmin Minimum required assembly preloadFMmax Maximum assembly preloadFMTab Tabular value of assembly pre loadFMzul Acceptable assembly preloadFPA Fraction of the axial force which alters the load of the deformed partsfPA Elastic deformation of parts through FPA
fPM Elastic deformation of parts through FM
FPM Assembly preload in deformed partsFQ Radial / Shearing forceFS Bolt forceFSA Additional axial bolt forcefSA Elongation of bolt through FSA
fSM Elongation of bolt through FM
FSM Assembly pre-stressing load in the boltFVth Change in preload due to temperatureFZ Loss in preload due to activationHB Brinell hardnessHRc Rockwell hardnessHV Vickers hardnessMA Initial torque at assembly to achieve FM
MG Part of initial torque operative in threadMK Moment of friction in the head or nut bearingn Force transmission factorP PitchpB Surface pressure in working statepG Marginal surface pressurepM Surface pressure in mounting stateRm Ultimate tensile strength of the bolt
– 55
RP0.2min 0.2%-Yield point of boltSF Safety factorsred,B Equivalent stress under working load�P Elastic resilience of joined components�S Elastic resilience of the bolt� Utilisation factor of yield pointa Alternating cyclic stress of boltA Tightening factorAS Stress amplitude of the endurance limit related to AS
Torsional stressB Shearing strength�G Coefficient of friction of the thread surface�K Coefficient of friction of the underhead bearing surface� Ratio of force �en Ratio of force during centric tension and eccentric
force transmission � Angle of rotation
9. Literature
Systematisch Berechnung hochbeanspruchter Schraubenverbindungen, VDI-Richtlinie 2230, (October 2001)
Kübler, K.H. und Mages, W.: Handbuch der hochfesten Schrauben. 1. Auflage,Giradet Buchverlag 1986
Westphal, Knut, „Keine Patentlösung in Sicht – Neue Cr(VI) – freie Zinklamellen-systeme für Verbindungselemente der Automobilindustrie, MO – Metalloberfläche5/2002, S. 20 – 23
Wiegand, Kloos, Thomala: Schraubenverbindungen, Springer Verlag, 4. Auflage 1988
Kayser, Klaus: High tensile bolted joints, Verlag Moderne Industrie, 1993
DIN EN ISO 898-1; Mechanische Eigenschaften von Verbindungselementen ausKohlenstoffstahl und legiertem Stahl, (November 1999)
DIN 50150, Umwerten von Härtewerten, (October 2000)
Bolt and Screw Compendium
56 – 57
Note
Note
KAMAX-WerkeRudolf Kellermann GmbH & Co. KG
Dr. Rudolf-Kellermann-Straße 2D-35315 Homberg/Ohm
Telefon +49 (0) 66 33/79-4 11Fax +49 (0) 66 33/79-4 13
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