ISO he Int ernational Org nization for Stan ardization is a worldwidefede ation of national s an ards b dies ISO membe b dies.. The work of pr p ring Int ernational Stan ards is normaly
Trang 1Plain bearing s — Hydrod ynamic plain
Part 2:
Paliers lisse s — B utée s h drody amique s à p tins g ométrie fixe
fnc tion a t en ré ime station aire —
Partie 2: Fo ctions p ur le calc ul de s b tée s à segment
S con edition
2 16-0 -1
Refer ence n mb r
Trang 2COPYRIGHT PROTECTED DOCUMENT
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written permis ion Permis ion c n be req esed from either ISO at the ad r es below or ISO’s member bod y in the c u try of
the r eq eser
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Tel + 12 7 9 011
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Trang 3F reword i v
Introduction v
1 Sc ope 1
2 Nor mati ve r eferenc es 1
3 F nctio s for the thr ust pad be ring 1
4 Efecti ve d ynamic visc osity of the lubricant , η ef , as a function of the efecti ve lubricant fi m temperature, T ef 7
Biblog raphy 10
Trang 4ISO (he Int ernational Org nization for Stan ardization) is a worldwidefede ation of national s an ards
b dies (ISO membe b dies) The work of pr p ring Int ernational Stan ards is normaly car ied out
through ISO t ech ical committ ees Each membe b dy int er st ed in a subje t for w hich a t ech ical
committ ee has be n es a lshed has the right t o be r pr sent ed on that committ ee Int ernational
org nizations, g ove nmental an non-g ove nmental, in laison with ISO, also take part in the work
ISO cola orat es closely with the Int ernational Ele trot ech ical C mmis ion (IEC) on al matt ers of
ele trot ech ical s an ardization
The proc d r s used t o develo this document an those int en ed for it furthe maint enanc ar
desc ibed in the ISO/IEC Dir ctives, Part 1 In p rticular the dife ent a pro al c it eria ne ded for the
dife ent ty es of ISO document should be not ed This document was draft ed in ac ordanc with the
edit orial rules of the ISO/IEC Dir ctives, Part 2 ( e www.iso.org dir ctives)
A tt ention is drawn t o the p s ibi ity that some of the element of this document ma be the subje t of
p t ent right ISO shal not be held r sponsible for identifying any or al such p t ent right Detais of
any p t ent right identified d ring the develo ment of the document wi be in the Introd ction an / r
on the ISO ls of p t ent de larations r c ived ( e www.iso.org p t ent )
Any trade name used in this document is information given for the convenienc of use s an does not
cons itut e an en orsement
For an ex lanation on the meaning of ISO spe ific t erms an ex r s ions r lated to conformity as es ment,
as wel as information a out ISO’s adhe enc to the Wor ld Trade Org nization (WTO) principles in the
Te h ical Bar ie s to Trade (TBT) se the folowing URL: www.iso.org/ iso/for word.html
The committ ee r sp nsible for thisdocument is ISO/TC1 3, Plain bearin s
This se on edition canc ls an r plac s the firs edition (ISO 1 1 1- 2:2 0 ), of w hich it cons itut es a
minor r vision
ISO 1 1 1 consis s of the folowing p rt , un e the g ene al title Plain bearin s — Hydrody namic plain
thrus t p d bearin s u de s teady-s tate c onditions:
— Part 1: Calc ulatio o thrus t p d bearin s
— Part 2 : Fu c tio s f r the c alc ulatio o thrus t p d bearin s
— Part 3 : Guide v lues f r the c alc ulatio o thrus t p d bearin s
Trang 5As uming hydrodynamic con itions with ful lubrication, the fu ctions of the ty e co e ed b this p rt
of ISO 1 1 1 ar ne es ary for the calculation of oi -lubricat ed p d thrus bearings in ac ordanc with
ISO 1 1 1-1 They ar b sed on the pr mises an b un ary con itions spe if ied The v lues ne es ary
for the calculation can be det ermined b means ofthe given formulae, as wel as from dia rams an
ta les The formulae in thisp rt of ISO 1 1 1ar a pro imations of the n me icaly det ermined v lues
trac d as curves ac ording t o R efe enc [2] The ex lanation of the symb ls, as wel as ex mples for the
calculation, ar inclu ed in ISO 1 1 1-1
Trang 7Plain bearing s — Hydrod ynamic plain thrust pad bearing s
Part 2:
This p rt of ISO 1 1 1 spe ifies fu ctions for thrus p d bearings It also co e s the efe t of dynamic
viscosity on lubricant film t empe atur
2 Normati ve r eferences
The folowing document , in w hole or in p rt, ar normatively r fe enc d in this document an ar
in ispensa le for it a pl cation F or dat ed r fe enc s, only the edition cit ed a pl es F or u dat ed
r fe enc s, the lat es edition of the r fe enc d document ( inclu ing any amen ment )a pl es
ISO 1 1 1-1, Plain bearin s — Hydrody namic plain thrus t bearin s u de s teady-s tate c onditio s —
Part 1: Calc ulatio o thrus t p d bearin s
3 Functions for the thrust pad bearing
3.1 Char acte is ic v lue of lo d car ying ca acity,
B
*
F , as a fu ction of the r elative bearing leng th, B /L,
and the r elative minimum lubricant fi m thicknes , h
min /C
ed
Ap ro imation of the curves of Figur 1 (rang e of a plcation: 0,1 ≤
h
C min
w ed
≤ 1 )
F
l
L
h
C
B
w ed min
w ed
min w ed
min
*
ln
/
/
= ×
×
× +
5
1
w
w ed
w ed
min w ed
w ed w ed
+
− ×
× × l
l
L
l
L 1
/
h
l
l
L
l
min
wed
w ed
w ed
+ × −
+ × −
×
3 1
4 2 4 3
1
min w ed
w ed
min w ed
l
+ × −
×
4 1
1 2
×
C
B
L
1
1
1
1
1
2
α
×
−2
2
1
min w ed /
α =
h
C
h
C
h
C 1
1 + 2
min
w ed
min
w ed
min
w ed 2
2
2
×
×
+
− ×
+
+
1 2
2
min
w ed
min
w ed h
C
h
C
×
1
ln +
min
w ed
min h
C
h /
/
w ed
min w ed
C
−
2
Trang 8A
B
L
B
L
2
×
− ,0 15 4
3
×
B
L
*
B
B
L
B
L
0 2 634 0 3 114 0 1 95
2
0,0 86 3
3
×
B
L
*
C
B
L
B
L
0 0 07 5 0 0 93 01 0 0 27 27
2
×
+ 0,0 01 446
3
B
L
Figure 1 — Characteristic value of load car ying capacity for thrust pad be rings,
B
*
F , as a
functio of the relative be ring width, B/L, and the relative minimum lubricant fi m thicknes ,
h
min /C
w ed , for l
w ed /L = 0, 75
Trang 9Table 1 — Values to Figure 1 w here
B
*
F
= f( B/ L, h
min /C
w ed , l
w ed /L = 0,7 )
h
min
/C
w ed
B/ L
3.2 Char acte is ic v lue of friction for thrus p d bearing s, f
B
*
, as a fu ction of the r elative bearing
width, B /L, an the r elative minimum lubricant fim thick es , h
min /C
ed
Ap ro imation of the curves of Figur 2 (rang e of a plcation: 0,1 ≤
h
C min
w ed
≤ 1 )
f
l
L h
C
l
L B
w ed min
w ed
min w ed
min w ed
w ed
*
ln
/
/
+
4
1
1
−
×
2
l
L h
C
h
C
l
L
w ed min
w ed
min
w ed
w ed
h
C
l
L h
C
l
L min
w ed
w ed min
w ed
w ed
2
×
−
6
5
1
1 2
B
L
A
B α
*
min
*
/
w ed
α =
h
C
h
C
h
C 1
1 + 2
min
w ed
min
w ed
min
w ed 2
×
2 2
2
2
+
1
min
w ed
min
w ed h
C
h
C
×
1+ /
min
w ed
min w ed
m ln h
C
in w ed
/
−
2
A
B
L
B
L
B
L
*
2
3
F or
min
w ed
is
*
F or
min
w ed
is
B
L
*
,
−
01 9 9
Trang 10Figure 2 — Characteristic value of frictio for pad thrust be rings,
B
*
f , as a functio of the
relative be ring width, B/ L, an the relative minimum lubricant fim thicknes , h
min /C
w ed , for
l
w ed /L = 0, 75
Table 2— Values to Figure 2 w here f
B
*
= f( B/L, h
min /C
w ed , l
w ed /L = 0,7 )
h
min
/C
w ed
B/ L
Trang 113.3 Relative lubricant flow r ates,
1
*
Q an
3
*
Q , as a fu ction of the r elative bearing w idth, B /L, an the
relative minimum lubricant im thick es , h
min /C
ed
Ap ro imation of the curves of Figur s 3 an 4 (rang e of a plcation: 0,1 ≤
h
C min
w ed
≤1 )
i
min
w ed
w ed min
w ed
*
=
Q
h
C
l
L h
C
+ ×
+
/
min w ed
min
h
1
1
1 2
w
w ed
w ed min
w ed
min
w ed C
l
L h
C
h
C +
2
1
w ed l
L
with cons ant A
i
an B
i
for
i
*
1
*
= :
B
L
B
L i
1
2
1,7 55 0,5 42 0,1 80
B
L
B
L i
1
2
1,0 48 0,7 88 0,1 35
for
i
*
3
*
= :
B
L
B
L i
3
2
2 0,4348 0,3 82 0,0 95
B
L
B
L i
3
2
2 0,47 4 0,3 56 0,0 21
Trang 12Figure 3— Relative lubricant flow rate,
1
*
Q , as a functio of the relative be ring width, B/L, and
the relative minimum lubricant fi m thicknes , h
min /C
w ed , for l
w ed /L = 0, 75
Table 3 — Values to Figure 3 w here Q
1
*
= f( B/L, h
min /C
w ed , l
w ed /L = 0,7 )
h
min
/C
w ed
B/ L
Trang 13Figure 4 — Relative lubricant flow rate,
3
*
Q , as a functio of the relative be ring width, B/L, and
the relative minimum lubricant fi m thicknes , h
min /C
w ed , for l
w ed /L = 0, 75
Table 4 — Values to Figure 4 w here Q
3
*
= ×(B/L, h
min /C
w ed , l
w ed /L = 0,7 )
h
min
/C
w ed
B/ L
4 Efecti ve d ynamic visc osity ofthe lubr icant , η
ef , as a function ofthe efecti ve
lubricant fi m temperature, T
ef
F or lq id lubricant , the Vog el formula is g ene aly a plca le
[3]
+
K
K
I
ex p
2
3
Trang 14R efe enc [2] show s the o e ational viscosity, η, for mine al oi s can also be calculat ed dir ctly from
the ISO VG
W ith density, ρ, in kg m
3
, it gives:
ln
C
ln
V G
x
x η
η
ρ
η
=
−
×
×
×
1 9 5
9
0 1 19 3
1 6 ,
,
T
In this formula, η
x
Pas
−
3
, , an is a cons ant coefficient
Theviscosity of ISO-complant oi s is given for a mean density ρ = 9 0 kg m
3
Engine an gear b x ois for ro d vehicles ar s an ardiz d ac ording t o inte national viscosity
clas es SAE
The SAE clas ification of these lubricant can only be comp r d incomplet ely with the ISO VG
clas if ication The clas ification is inac urat e that for espe ial y pr cise calculations, the sup le is
r q est ed t o sup ly viscosity data
As compar d with pur mine al ois, multi-grade oi s ha e mor even viscosity-t empe atur beha iour
Synthetic ois ve y oft en r ach such con itions without intrinsicaly viscous ad itives as r q ir d for
mine al oi s
Trang 15Figure 5 — Efective dy amic vis osity, η
ef ,as a functio of the efective lu ricant fim
temperature, T
ef , at a density ρ = 900 kg/ m
3
Trang 16Bibl og raphy
[1] ISO 1 1 1-3, Plain bearin s — Hydrody namic plain thrus t p d bearin s u de s teady-s tate
c onditio s — Part 3 : Guide v lues fr the c alc ulatio o thrus t p d bearin s
[2] Rodermu d H B er ch u g de Tempe atura h n igkeit de Vi skos ität v n Mine alölen a s dem
Vi skos itäts grad (C lculation of t empe atur depen enc of mine al oi viscosity b sed on the
viscosity grade) S hmie t ech ik u d Trib lo ie2/ 19 8, p 5 -5
[3] Vo el H Das Tempe atura h n igkeits ges etz de V kos ität v n Flüs s igkeiten (The t empe atur
dependenc law for viscosity of fluids) Ph s Z 1 2 , 2 p 645– 46
[4 ] Camer on A The Princ iples o L bric atio L ngmans, Lon on, 1 66
Trang 18ICS 21.100.10
Pric based on 10 pag es