Bolt and Screw Compendium
description
Transcript of Bolt and Screw Compendium
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Bolt and Screw Compendium
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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
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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
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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
csd1
6m
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 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
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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 bolting
Rp0,2 > 290N/mm2 AlSi1MgMn Temperature load 380 N/mm2 EN AW 6056 Magnesium bolting
Rp0.2 > 350 N/mm2 AlSi6MgCuMn Aluminum bolting
With heat treatment EN AW 6013 Temperature load
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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
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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
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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.
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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
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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
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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
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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* Gmin + DKm / 2* Kmin]. Additional moments in case connecting elements are used to prevent slacking and loosening have to be considered.
18 19
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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.
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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
pU
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
kse
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
ofC
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*G+(DKm/2)*K)
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
MGAMA
,MK
MAMAMA
[Nm]
MA[Nm]
v = 0,9 v=1 v = 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
AA
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
MAmax
M
A
MAmax
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/mm
2; 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 g
Tigh
teni
ng T
orqu
e M
A[N
m]
for
k=
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 g
Tigh
teni
ng T
orqu
e M
A[N
m]
for
k=
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 180should 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 MAmax8.8 8 10.5 14.5 10.0 17
M 6 10.9 10 15.5 20 14.5 23.512.9 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
[m] 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 NoSilver 5 / 8 - (Possible) 480h / 720h NoSilver 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 YesSilver 12 - (Possible) 480 / 720h NoSilver 8 / 12 If necessary 240h / 480h NoSilver 8 / 12 - (Possible) 480h conditionalSilver / black 12 - (Possible) 480h (120h) YesBlack 12 - (Possible) 480h (240h) YesBlack 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 tot of 0.09 0.14 is requiredfor lubricated bolts (partial friction coefficients K and G 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
r=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
=d
22.
675
2.62
72.
600
2.65
52.
607
2.58
02.
625
2.57
72.
550
core
=d
32.
387
2.32
02.
293
2.36
72.
299
2.27
32.
337
2.27
02.
243
oute
r=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
=d
23.
545
3.48
93.
455
3.52
33.
467
3.43
33.
489
3.43
33.
399
core
=d
33.
141
3.05
83.
024
3.11
93.
036
3.00
23.
085
3.00
22.
968
oute
r=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
=d
24.
480
4.42
04.
385
4.45
64.
396
4.36
14.
420
4.36
04.
325
core
=d
34.
019
3.92
83.
893
3.99
53.
903
3.86
93.
959
3.86
83.
833
oute
r=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
=d
25.
350
5.27
95.
238
5.32
45.
253
5.21
25.
290
5.21
95.
178
core
=d
34.
773
4.66
34.
622
4.74
74.
637
4.59
64.
713
4.60
34.
562
oute
r=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
=d
26.
350
6.27
96.
238
6.32
46.
253
6.21
26.
290
6.21
96.
178
core
=d
35.
773
5.66
35.
622
5.74
75.
637
5.59
65.
713
5.60
35.
562
oute
r=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
=d
27.
188
7.11
37.
070
7.16
07.
085
7.04
27.
125
7.05
07.
007
core
=d
36.
466
6.34
36.
300
6.43
86.
315
6.27
26.
403
6.28
06.
237
oute
r=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
=d
28.
188
8.11
38.
070
8.16
08.
085
8.04
28.
125
8.05
08.
007
core
=d
37.
466
7.34
37.
300
7.43
87.
315
7.27
27.
403
7.28
07.
237
oute
r=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
=d
29.
026
8.94
18.
894
8.99
48.
909
8.86
28.
959
8.87
48.
827
core
=d
38.
160
8.01
77.
970
8.12
87.
985
7.93
88.
093
7.95
07.
903
oute
r=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
=d
210
.026
9.94
19.
894
9.99
49.
909
9.86
29.
959
9.87
49.
827
core
=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
r=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
nk
=d2
10.8
6310
.768
10.7
1310
.829
10.7
3410
.679
10.7
9210
.697
10.6
42co
re
=d3
9.85
39.
691
9.63
59.
819
9.65
69.
602
9.78
29.
619
9.56
5
oute
r=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
=d
212
.701
12.6
0112
.541
12.6
6312
.563
12.5
0312
.630
12.5
3012
.470
core
=d
311
.546
11.3
6911
.309
11.5
0811
.331
11.2
7111
.475
11.2
9811
.238
oute
r=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
=d
214
.701
14.6
0114
.541
14.6
6314
.563
14.5
0314
.630
14.5
3014
.470
core
=d
313
.546
13.3
6913
.309
13.5
0813
.331
13.2
7113
.475
13.2
9813
.238
oute
r=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
=d
216
.376
16.2
7016
.206
16.3
3416
.228
16.1
6416
.296
16.1
9016
.126
core
=d
314
.933
14.7
3114
.666
14.8
9114
.688
14.6
2514
.853
14.6
5014
.587
oute
r=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
=d
218
.376
18.2
7018
.206
18.3
3418
.228
18.1
6418
.296
18.1
9018
.126
core
=d
316
.933
16.7
3116
.666
16.8
9116
.688
16.6
2516
.853
16.6
5016
.587
oute
r=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
=d
220
.376
20.2
7020
.206
20.3
3420
.228
20.1
6420
.296
20.1
9020
.126
core
=d
318
.933
18.7
3118
.666
18.8
9118
.688
18.6
2518
.853
18.6
5018
.587
oute
r=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
=d
222
.051
21.9
2621
.851
22.0
0321
.878
21.8
0321
.966
21.8
4121
.766
core
=d
320
.319
20.0
7820
.003
20.2
7120
.030
19.9
5520
.234
19.9
9319
.918
oute
r=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
=d
225
.051
24.9
2624
.851
25.0
0324
.878
24.8
0324
.966
24.8
4124
.766
core
=d
323
.319
23.0
7823
.003
23.2
7123
.030
22.9
5523
.234
22.9
9322
.918
oute
r=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
=d
227
.727
27.5
9527
.515
27.6
7427
.542
27.4
6227
.637
27.5
0527
.425
core
=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
r=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
=d
27.
513
7.45
07.
413
7.49
17.
428
7.39
17.
457
7.39
47.
357
core
=d
37.
080
6.98
86.
951
7.05
86.
968
6.92
97.
024
6.93
26.
895
oute
r=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
=d
27.
350
7.27
97.
238
7.32
47.
253
7.21
27.
290
7.21
97.
178
core
=d
36.
773
6.66
36.
622
6.74
76.
637
6.59
66.
713
6.60
36.
562
oute
r=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
=d
28.
350
8.27
98.
238
8.32
48.
253
8.21
28.
290
8.21
98.
178
core
=d
37.
773
7.66
37.
622
7.74
77.
637
7.59
67.
713
7.60
37.
562
oute
r=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
=d
29.
350
9.27
99.
238
9.32
49.
253
9.21
29.
290
9.21
99.
178
core
=d
38.
773
8.66
38.
622
8.74
78.
637
8.59
68.
713
8.60
38.
562
oute
r=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
nk
=d2
9.18
89.
113
9.07
09.
160
9.08
59.
042
9.12
59.
050
9.00
7co
re
=d3
8.46
68.
343
8.30
08.
438
8.31
58.
272
8.40
38.
280
8.23
7
oute
r=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
=d
211
.350
11.2
7511
.232
11.3
2411
.249
11.2
0611
.290
11.2
1511
.172
core
=d
310
.773
10.6
5910
.616
10.7
4710
.633
10.5
9010
.713
10.5
9910
.556
oute
r=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
nk
=d2
11.1
8811
.103
11.0
5611
.160
11.0
7511
.028
11.1
2511
.040
10.9
93co
re
=d3
10.4
6610
.333
10.2
8610
.438
10.3
0510
.258
10.4
0310
.270
10.2
23
oute
r=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
=d
211
.026
10.9
3610
.886
10.9
9410
.904
10.8
5410
.959
10.8
6910
.819
core
=d
310
.160
10.0
129.
962
10.1
289.
980
9.93
010
.093
9.94
59.
895
oute
r=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
=d
213
.350
13.2
7513
.232
13.3
2413
.249
13.2
0613
.290
13.2
1513
.172
core
=d
312
.773
12.6
5912
.616
12.7
4712
.633
12.5
9012
.713
12.5
9912
.556
oute
r=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
=d
213
.026
12.9
3612
.886
12.9
9412
.904
12.8
5412
.959
12.8
6912
.819
core
=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
r=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
=d
215
.350
15.2
7515
.232
15.3
2415
.249
15.2
0615
.290
15.2
1515
.172
core
=d
314
.773
14.6
5914
.616
14.7
4714
.633
14.5
9014
.713
14.5
9914
.556
oute
r=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
=d
215
.026
14.9
3614
.886
14.9
9414
.904
14.8
5414
.959
14.8
6914
.819
core
=d
314
.160
14.0
1213
.962
14.1
2813
.980
13.9
3014
.093
13.9
4513
.895
oute
r=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
=d
217
.026
16.9
3616
.886
16.9
9416
.904
16.8
5416
.959
16.8
6916
.819
core
=d
316
.160
16.0
1215
.962
16.1
2815
.980
15.9
3016
.093
15.9
4515
.895
oute
r=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
=d
216
.701
16.6
0116
.541
16.6
6316
.563
16.5
0316
.630
16.5
3016
.470
core
=d
315
.546
15.3
6915
.309
15.5
0815
.331
15.2
7115
.475
15.2
9815
.238
oute
r=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
=d
219
.026
18.9
3618
.886
18.9
9418
.904
18.8
5418
.959
18.8
6918
.819
core
=d
318
.160
18.0
1217
.962
18.1
2817
.980
17.9
3018
.093
17.9
4517
.895
oute
r=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
=d
218
.701
18.6
0118
.541
18.6
6318
.563
18.5
0318
.630
18.5
3018
.470
core
=d
317
.546
17.3
6917
.309
17.5
0817
.331
17.2
7117
.475
17.2
9817
.238
oute
r=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
=d
221
.026
20.9
3620
.886
20.9
9420
.904
20.8
5420
.959
20.8
6920
.819
core
=d
320
.160
20.0
1219
.962
20.1
2819
.980
19.9
3020
.093
19.9
4519
.895
oute
r=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
=d
220
.701
20.6
0120
.541
20.6
6320
.563
20.5
0320
.630
20.5
3020
.470
core
=d
319
.546
19.3
6919
.309
19.5
0819
.331
19.2
7119
.475
19.2
9819
.238
oute
r=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
=d
223
.026
22.9
3122
.876
22.9
9422
.899
22.8
4422
.959
22.8
6422
.809
core
=d
322
.160
22.0
0721
.952
22.1
2821
.975
21.9
2022
.093
21.9
4021
.885
oute
r=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
=d
222
.701
22.5
9522
.531
22.6
6322
.557
22.4
9322
.630
22.5
2422
.460
core
=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-
Flan
k-
Tigh
teni
ngco
re-
oute
r-
(tol
eran
cew
ear
limit
torq
ue
ball
cont
act
Test
dim
ensi
on
Test
Dim
ensi
on
(tol
eran
cein
m
)N
m m
ax.
M (t
ol. i
n m
)M
wor
n ou
tin
m
)
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