UDC 621.833.1 : 621.753.1 DEUTSCHE NORMEN August 1978
System of Gear Fits
Back1 ash Tooth Thickness Allowances
Tooth Thickness Tolerances
Princbles
- - DIN
3967
Getriebe-Passystem; Flankenspiel, Zahndickenabmasse, Zahndickentoleranzen, Grundlagen
To facilitate use of this Standard, the calculation of tooth thickness allowances has been included as Appendix A.
Information on converting the allowances for the various measuring methods is add& in Appendix B.
The DIN backlash system of fits for gear pairs allows the limiting allowances of tooth thickness to be defined with
attention given to all effects occurring in the operation of a gear transmission, and to all deviations throughout the
gearing.
The system of fits therefore consists on the one hand of the allowances and tolerances of the gear teeth, referred to
their prevailing mounting arrangements, and on the other hand of the allowances and tolerances of all the other com
ponents of the gear transmission in so far as they determine the position of the teeth relative to one another. These
values defined for a reference temperature vary in operation through temperature changes in the upward or downward
direction, through elastic deformation under load and possibly through swelling or contraction.
The system of fits is defined as a tooth thickness system of fits in the normal section on the reference cylinder, i. e. all
allowances, tolerances and operationally induced alterations in the gear transmission are treated as tooth thickness
alterations and require to be converted to the nonnal section.
The normal section was chosen because the production effort, i. e. the necessary tooth thickness tolerance in the normal
section, is indëpendent of the helix angle. The normal section was also chosen for metrological reasons, since the normal
chordal tooth thickness and the base tangent length are measured in the normal section.
The calculation of the allowances however is made over the transverse section, since on the finished gear transmission
the backlash is measured as circumferential backlash (see Appendix A).
The system of f i ts provides for safeguarding the minimum backlash and limiting the maximum backlash.
The reference basis of the system of fits is the zero-play condition at the nominal centre distance, with nominal adden-
dum modification and with error-free components.
The necessary negative allowances of tooth thickness can be produced by an additional addendum modification in the
negative direction Ax. This however is not taken into account in the nominal addendum modification.
Whether the weakening of the tooth thickness needs to be taken into Consideration in calculations of IoadCarryng
capacity is something which has to be decided for the case concerned. In any event this should be done whenever
*sni > 0.005.
1 Other relevant Standards
DIN 3960 Definitions and parameters for cylindrical
gears and cylindrical gear pairs with involute
teeth
DIN 3961 Tolerances for cylindrical gear teeth;
principles
DIN 3962 Part 1 Tolerances for cylindrical gear teeth;
tolerances for deviations of individual para-
meters
DIN 3964 Centre distance allowances and shaft position
tolerances of housings for cylindrical gear
transm íssions
DIN 3999 Symbols for gear teeth
2 Backlash
The backlash value says nothing about the quality of the
gear teeth although, on the other hand, the different gear
tooth qualities demand given tooth thickness allowances
in order to ensure the requisite or permissible backlash.
The minimum backlash i s determined by the upper allow-
ances. However it does not correspond.to the sum of the
upper allowances because a whole series of factors alters
the backlash (see Appendix A).
The maximum backlash is determined by the lower tooth
thickness allowances which result from the upper allow-
ances and the tooth thickness tolerances. This also does
not correspond to the sum of the allowances because
here again a series of factors alters the backlash.
21 Theoretical backlash
The theoretical backlash it results from the tooth thick-
ness allowances converted to the transverse section and
from the converted allowances of the centre distance.
Continued on pages 2 to 23
Explanations on page 24
DIN3967 engL Preikgr. 7; !le sale rights of German Standards (DIN-Nonnen) are with Beuth Verlag GrnbH. Berlin 30
11.91 Verir.-Nr. O1 12
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Page 2 DIN 3967
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10
2.2 Acceptance backlash
The acceptance backlash is the backlash obtained with
the unloaded gear transmission a t reference temperature
when one of the gears is rotated against the other. It is
uwally smaller than the theoretical backlash, since the
backlash-reducing factors generally outweigh the factors
tending to increase the backlash. Backlash-reducing
factors are, for example, deviations in the gear teeth and
also form and position deviations, see Appendix A.
2.3 Working backlash
The working backlash is the backlash resulting when the
gear transmission i s operating. It i s not constant. During
the starting up of the gear transmikion in particular it is
possible for the more rapid temperature rise of the gears
compared with the housing to bring about larger changes
in the working backlash. It is generally larger than accept-
ance backlash when the linear coefficient of expansion of
10 - 100 - 85 - 70 - 58 - 48 - 40 - 33 - 22 - 10 - 5 O
50 - 1 3 5 - 1 1 0 - 9 5 - 7 5 - 6 5 - 5 4 - 4 4 - 3 0 - 1 4 - 7 O
the housing is greater than that of the gears. Shaft deflec-
tion and displacement also affect it.
50
125
3 Tooth thickness allowances
Normally the tooth thickness allowances and tooth thick-
ness tolerances can be found directly from Tables 1 and 2
on the basis of existing experience, such that, as a rule,
the upper allowances for each gear should be at least as
large (numerical value) as the lower allowance of the
housing centre distance (without converting). If no
empirical values are available for backlash and tooth
thickness allowances, these must be calculated. A guide
for this purpose will be found in Appendix A. The cal-
culated values are usually rounded and then likewise
taken from Tables 1 and 2. I f exceptionally small amounts
of backlash are necessary for functional reasons, calcula-
tion is indispensable.
and tooth thickness tolerances
125 - 180 - 150 - 125 - 105 - 85 - 70 - 60 - 40 - 19 - 9 O
280 - 250 - 200 - 170 - 140 -115 - 95 - 80 - 56 - 26 - 12 O
Table 1. Upper tooth thickness allowances A , in pn
t I I
280
560
Reference diameter I imm)
560 - 330 - 280 - 230 - 190 -155 -130 -110 - 75 - 35 - 17 O
1000 - 450 - 370 - 310 - 260 -210 -175 -145 -100 - 48 - 22 O
Allowance series
1000
1600
1600 - 600 - 500 - 420 - 340 -290 -240 -200 -135 - 64 - 30 O
2500 - 820 - 680 - 560 - 460 -390 -320 -270 -180 - 85 - 41 O
2500
4000
4000 -1100 - 920 - 760 - 620 -520 -430 -360 -250 -115 - 56 O
6300 -1500 -1250 -1020 - 840 -700 -5m -480 -330 -155 - 75 O
over up to
- 10
10 50
21 22 23 24 25 26 27 28 29 I 30
3 5 8 12 20 30 50 80 130 200
5 8 1 12 20 30 50 80 330 200 300
1 6300 I 10000 ~ - 2 0 0 0 ~ - 1 6 5 0 ~ - 1 3 5 0 ~ - 1 1 5 0 ~ -940 1-780 1-640 1-450 1-210 1-100 1 O 1
280
560
1000
Table 2. Tooth thickness tolerances TSn in pm
I I i
560 10 16 25 40 60 100 160 250 400 600
1 000 12 20 30 50 80 130 200 300 500 800
1600 16 25 40 60 100 160 250 400 600 1000
Reference diameter I (mm)
1600
2500
4000
Tolerance series
2 500 20 30 50 80 130 200 300 500 800 1300
4 000 25 40 60 100 160 250 400 600 1000 1600
6 300 30 50 80 130 200 300 500 800 1300 2000
I 50 1 125 I 6 I 10 1 16 I 25 I 40 I 60 I 100 I 160 I 250 I 400 I
I I loooo I 40 I 60 I I 160 I 250 I 400 I 600 I lm I 1600 r2400 I
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DIN 3967 Page 3
3.1 Upper allowances
The upper allowances are to be taken from Table 1
independently of the reference diameter and the allow-
ance series. Their choice is largely independent of the
gear tooth quality. As a rule for transmissions of the
same kind it is possible to choose the upper allowance
for pinion and gear in all cases from a single allowance
series; it is also permissible however to select values from
different allowance series.
3.2 Lower allowances
The lower allowances are obtained by combining the
upper allowances with the tooth thickness tolerances.
Since the upper and lower allowances are always nega-
tive the amount of the tolerance has to be deducted
from the upper allowance.
3.3 Tooth thickness tolerances
The tooth thickness tolerances are to be found from
Table 2. Their choice is largely independent of the gear
tooth quality and should be governed by the manufactur-
ing facilities, although it should be borne in mind that
the tooth thickness tolerance must be at least twice as
large as the permissible tooth thickness fluctuation R,
according to DIN 3962 Patt 1. I f a maximum backlash
has to be watched for functional reasons, calculation
according to Appendix A will be necessary. Quite
generally it should be noted that small tooth thickness
tolerances unfavourably affect the maintaining of gear
tooth quality, since they unnecessarily limit the correc-
tion possibilities during manufacture (see, for example,
VDINDE 2608).
In order to distinguish them clearly from the gear tooth
qualities, the tolerance series have been given the num-
bers 21 to 30. The preferred series are 24 to 27.
3.4 Information in drawings
The limiting allowances can be indicated in the drawing
either directly or by means of an code designation, see
DIN 3966 Part 1. The symbol consists of the number of
the tooth thickness tolerance series and the letter symbol
of the series for the upper tooth thickness allowance.
Example: 27cd; this designation yields, ford = 100 rnm
for example, the limiting allowances A , = - 70 pm and
A,, = - 170 pm.
.
4 Converting the tooth thickness allowances
for the different test methods
The system of f i t s is referred to a theoretical value. This
i s the tooth thickness in the normal section which, how-
ever, i s not directly measurable. Therefore indirect meas-
urements are made by various methods, see DIN 3960.
For an error-free gear there are mathematical relation-
ships connecting the different measured quantities. How-
ever, since the individual measured quantities are affected
differently by the individual deviations of the gear teeth
a purely mathematical conversion of the tooth thickness
allowances does not necessarily guarantee the required
backlash. Where adequate experience i s available (e. g. in
the case of tooth thickness tolerance zone 26e or coarser)
the tooth thickness allowances can be converted directly
into given test dimension allowances (e. g. base tangent
length allowances) and these used for acceptance testing
the gear. It may then happen, however, that acceptance
testing by a different measuring method (e. g. pin dimen-
sion measurement) will show that the tolerance is not
fully complied with.
With the closer tolerance zones it is therefore recommend-
able when calculating different test dimensions and their
allowances to apply appropriate corrections which take
account of the influence of the individual deviations on
these test dimensions empirically (statistically). Guidance
on determining correction values is given in Appendix B.
For calculating the allowance factors according to
DIN 3960, October 1976 edition, Sections 4.1.3 and 5,
the mean generating addendum modification coefficient
xh, corresponding to the mean allowance should always
be used.
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Page 4 DIN 3967
Standard basic Gear teeth
rack tooth profile Tool
5 Example
Length dimensions in mrn
~ ~~ ~
DIN 867
DIN 3972
Helical gears
Helix angle ß
Flank direction
External
Pinion I Gear
9? 53? 49? DIN 3978
Left Right
I Normal module rn, I 5 I
Gear tooth quality
Facewidth b
I Number of teeth 2 1 20 I 97
I
6 7
70
Housing centre distance a
Housing width
~~
300 is 7
200
I Reference diameter d 1 101.517 1- 492.326
x 1 +0,4000 1 +O2389 I Addendum modification 1 coefficient to DIN 3992
Pinion 16 MnCr 5
Gear 42 CrMo 4V
Material
I Housing material I GG 22 I
Pinion hardened and ground, gear heat-treated and milled.
It is assumed that it is known from experience that the
upper allowan,cesof tooth thickness of series cd are
appropriate for this type of transmission.
According to Table 1 the upper allowances are selected
as A,, = - 70 pm for the pinion and A,, = - 130 pm
for the gear.
(These values are algebraically smaller than the lower
allowance - 26 pn of the centre distance.)
For the particular application concerned, the observance
of a functionally imposed maximum backlash is not
necessary. To cater for hardening distortion, and also to
keep the grinding COR low, the tolerance for the pinion
is made comparatively large. For series 27 Table 2 gives
T, = 1 O0 pm and hence
A , = - 70 pm = - 0,070 mm
A , = - 170 pn = - 0,170 mm
(lower allowance = upper allowance minus tolerance).
Since the gear is milled, a tolerance of 1 O0 p n (Table 2
series 26) i s adequate. Consequently
A , 2 = - 130 pm = - 0,130 mm
Apii2 =-230pm=-0,230mm
The adoption of these tolerance zones, which meet the
manufacturing requirements, means that the tooth thick.
nesses are not unacceptably weakened
Since the tooth thickness fluctuation according to
DIN 3962 Part 1 i s allowed to be 14 pm for the pinion
and 25 pm for the gear, the tolerances are correctly
selected in this respect also (see Section 3.3).
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DIN3967 Page5
Number of teeth z
Sn nenn
20 97
9.3099 8,7235
Tooth thidcness I 9,2399 sn mittel 9.1 899 8,5935 8,5435
Sn min
I I I . I ~ I . . . . .
9,1399 8.1935
+ 0,4000
I Xmin I +O9533 I +0,1757
+ 0,2389
The above result in the following test dimensions with their allowances:
+ 0,3808
+ 0,3670 maenaum moaiTicarion I
+ 0,2032
+ 0.1 894
177,485 f 0,047
507,604 f 0,126 i-'. 507,670 f 0,126 Base taqent length W Measured number of teeth K Allowance factor A& Dimension over balls MdK Dimension over rollers MdR
Ball and roller diameter D M
Allowance factor AMa
39,619 f 0,047
3
0,940
1 17,472 f 0,099
9,297 = 9
1,988
Working distance with master gear
Number of teeth of master gear
(DIN 3970) 1)
Allowance factor A;"
a"
ZL
129,314f0.061 323,962 f 0,066
30 30
1,218 1,325
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Page 6 DIN 3967
The calculated allowances of the measured values are shown in Fig. 1: these are values for ideal geometry. For use in
practical measurements they may need to be corrected, see Section 4 and Appendix B (Fig. B.l and 8.3).
The acceptance backlash may turn out to be smaller than the sum of t h e upper allowances, as dictated by the tolerance
for the housing and other effects. It may, however, also turn out to be larger than the sum of the lower allowances, as
dictated by the slope of the tooth and the housing tolerance, and further effects (see Appendix A).
Figure 1. Tolerance zones of test dimensions after ideal-geometry conversion'of tooth thickness tolerance zone
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DIN 3967 Page 7
Appendix A
Calculation of tooth thickness allowances or backlash
A.l General
A.l.l Symbols and designations
A.1.2 Connection between backlash and allowances
A.2 Backlash-modifying effects
A.2.1 Temperature rise
A.2.2 Centre distance tolerance of the housing
A 2 3 Non-parallelism of bore axes in the housing
A.2.4 Gear tooth individual deviations
A.2.5 Swelling or contraction
A.2.6 Position, form a n d dimension deviations of
components
A.2.7 Elasticity
A.3 Action of the backlash-modifying effects
A.4 Calculation of the backlashmodifying effects
A.4.1 Backlash modification through temperature
rise Aje
A4.2 Backlash modification through centre distance
tolerance Aja
A.4.3 Backlash modification through non-parallelism
of bore axes Aics
A.4.4 Backlash modification through gear tooth
individual deviations AiF
A.4.5 Backlash modification through swelling or con-
traction AiQ
A.4.6 Backlash modification through position, form
and dimension deviations of components AiB
A.4.7 Backlash modification through elasticity AiE
Contents
A.1 General
Al .1 Symbols and designations
U
b
d
fD
fZß
it
it,
it,
Centre distance
Facewidth
Reference diameter
Individual pitch deviation
Axial skew over length LG
Theoretical backlash
Acceptance backlash
Working backlash
Maximum circumferential backlash
Minimum circumferential backlash
Module
Relative water absorption (relative volume
expansion)
Addendum modification coefficient with
mean tooth thickness allowance
A , Centre distance allowance
A , Upper centre distance allowance
A.5 Calculation of sum of upper allowances ZA*
from minimum backlash jtmb and the badclash-
modifying effects
A.5.1 Determining the upper allowances of tooth thick-
ness in the normal section
A.6 Calculation of sum of lower allowances ZA&
from maximum backlash it msx and the backlash-
modifying effects
A.6.1 Definitions
A.6.2 Maximum backlash jt mu
A.6.3 Calculation
A.6.4 Determining the lower allowances of tooth thick-
ness in the normal section
A.7 Calculation of backlash from the tooth thickness
allowances and the badclash-modifying effects
A.8 Allowance diagram of tooth thickness in the
normal section
A.9 Example for determining tooth thickness
allowances
A9.1 Upper allowances
A.9.2 Lower allowances
A.9.3 Lower allowances without a specified maximum
backlash
A.9.4 Allowances under modified conditions
A.9.5 Acceptance backlash
A.10 Example for determining the backlash
to be expected
A.lO.l Determining the theoretical backlash
A.102 Acceptance backlash
A , Lower centre distance allowance
A,,
Asm
Upper allowance of tooth thickness' in normal
section
Lower allowance of tooth thickness in normal
section
Upper allowance of tooth thickness in trans-
verse section
Lower allowance of tooth thickness in trans-
verse section
Total profile deviation 1) .
Pitch span deviation over k pitches
Concentricity deviation
Tooth trace total deviation 1 )
Separation of bearing centres of a shaft
Swelling of housing
Swelling of gears
1) Measured according to DIN 3960 in the transverse
section tangential to the base cylinder.
DIN 3967
Tooth thickness fluctuation
Tolerance
Tolerance of two-flank working distance
Tolerance of normal chordal tooth thickness
fluctuation
Tooth thickness tolerance in the normal section
Tolerance of diametral two-ball or two-roller
measurement
Tolerance of radial single-ball or single-roller
measurement
Base tangent length tolerance
Pressure angle
Normal pressure angle
Transverse pressure angle
Linear coefficient of expansion of housing
Linear coefficient of expansion of gears or
gear rings
Helix angle
Backlash modification through centre
distance tolerance
Backlash modification through form and
dimension deviations of the components
Backlash modification through elasticity
Backlash modification through gear tooth
ind ividual deviations
Backlash modification through swelling or
contraction
Backlash modification through temperature rise
Backlash mcdif ication through non-parallelism
of bore axes
Temperature difference of housing relative
to 20°C
Temperature difference of gears relative to
20 "c
Sum of upper allowances of tooth thickness
of gear pair in the normal section
Sum of lower allowances of tooth thickness
of gear pair in the n
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