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ANSIIABMA Std. 7 - 1995 (Revision and redesignation of ANSUAFBMA Std. 7 - 1988)
AMERICAN NATIONAL STANDARD ABMA STANDARD SHAFT AND HOUSING FITS FOR METRIC RADIAL BALL AND ROLLER BEARINGS (EXCEPT TAPERED ROLLER BEARINGS) CONFORMING TO BASIC BOUNDARY PLAN
Copyright0 American Bearing Manufacturers Association, Inc. This reproduction made under license agreement by CSSinfo, (734) 930-9277. No part of the printed publication, nor any part of the electronic file may be reproduced or transmitted in any form, including transmittal by e-mail, by tile transfer protocol (FTP), or by being made part of a network-accessible system, without the prior written permission of the copyright owner.
Sponsored by American Bearing Manufacturers
Association,
Inc.
Approved October 27, 1995 American National Standards Institute,
Inc.
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AMERICAN
NATIONAL
STANDARD
Approval of an American National Standard requires verification by ANSI that the requirements for due process, consensus, and other criteria for approval have been met by the standards developer. Consensus is established when, in the judgment of the ANSI Board of Standards Review, substantial agreement has been reached by directly and materially affected interests. Substantial agreement means much more than a simple majority, but not necessarily unanimity. Consensus requires that all views and objections be considered, and that a concerned effort be made toward their resolution. The use of American National Standards is completely voluntary; their existence does not in any respect preclude anyone, whether he has approved the standards or not, from manufacturing, marketing, purchasing, or using products, processes, or procedures not conforming to the standards. The Ameri.can National Standards Institute does not develop standards and will in no circumstances give an interpretations of any American National Standard. Moreover, no person shall have the right or authority to issue an interpretations of an American National Standard in the name of the American National Standards Institute. Requests for interpretations should be addressed to the secretariat of sponsor whose name appears on the title page of this standard. CAUTION NOTICE: This American National Standard may be revised or withdrawn at any time. The procedures of the American National Standards Institute required that action be taken to reaffirm, revise, or withdraw this standard no later than five years from the date of approval. Purchasers of American National Standards may receive current information on all standards by calling or writing the American National Standards institute.
Published by American Bearing Manufacturers Association, Inc. (formerly Anti-Friction Bearing Manufacturers Association, Inc.) 1200 19th Street, N. W., Suite 300 Washington, D.C. 200362412
Q Copyright
1995 hy American Bearing Manufacturers
Association, Inc.
All rights reserved. No part of this publication may be reproduced in any form, in an electronic retrieval system or otherwise, without prior written permission of the publisher. Printed in the United States of America.
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FOREWORD
This foreword is not a part of ANSI/ABMA Standard7 - 1995, Shaft and Housing Fits for Metric Ball and Roller Bearings (Except Tapered Roller Bearings) Conforming to Basic Boundary Plan. This American National Standardprovides the general selection of shaft and housing fits for metric radial ball and roller bearings of tolerance classesABEC-1 and RBEC-1. Bearing type, loading and other design requirements influence the criteria for shaft and housing fits. The dimensions, tolerances and clearancesstatedin this standard are basedon metric units and are found in Part I of the various tables. A soft conversion to tJ.S. customary (inch-pound) units is provided in Part II of the various tables for the convenienceof the user. Suggestionsfor the improvement of this standardgained through experience with its use will be welcomed. These should be sent to the American National StandardsInstitute, Inc., 11 West 42nd Street, New York, NY 10036. The officers of Accredited StandardsCommittee B3 operating under the American National StandardsInstitute procedures and the organizations representedat the time this standardwas submitted are as follows: W.G. Looft, Chairman
G.T. Satterfield, Secretary
American Bearing Manufacturers Association Hydraulic Institute Association for Manufacturing Technology Society of Tribologists and Lubrication Engineers U.S. Departmentof Defense, DISC U .S. Departmentof the Navy
This~pnoductionm&bycustQnnstandruds Services, SO2 Oakhnd Ave, Suite 5, Ann Arbor, MI 48104 (800) 699-9277, under myeky ,,qew& Nofutherreproduabnis~
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ABMA (formerly AFBMA) Standards for Ball and Roller Bearings 1 - Terminology for Anti-Friction Ball and Roller Bearings and Parts 4 - Tolerance Definitions and Gauging Practicesfor Ball and Roller Bearings 7 - Shaft and Housing Fits for Metric Radial Ball and Roller Bearings (Except Tapered Roller Bearings) Conforming to Basic Boundary Plan 8.1 - Mounting Accessories, Metric Design 8.2 - Mounting Accessories, Inch Design 9 - Load Ratings and Fatigue Life for Ball Bearings 10 - Metal Balls 11 - Load Ratings and Fatigue Life for Roller Bearings 12.1 - Instrument Ball Bearings, Metric Design 12.2 - Instrument Ball Bearings, Inch Design 13 - Rolling Bearing Vibration and Noise (Methods of Measuring) 14 - Housings for Bearings with Spherical Outside Surfaces 15 - Ball Bearings with Spherical Outside Surfacesand Extended Inner Ring Width (Includes Eccentric Locking Collars) 16.1 - Airframe Ball, Roller, and Needle Roller Bearings, Metric Design 16.2 - Airframe Ball, Roller, and Needle Roller Bearings, Inch Design 17 - Needle Rollers, Metric Design 18.1 - Needle Roller Bearings, Radial, Metric Design 18.2 - Needle Roller Bearings, Radial, Inch Design 19.1 - Tapered Roller Bearings, Radial, Metric Design 19.2 - Tapered Roller Bearings, Radial, Inch Design 20 - Radial Bearings of Ball, Cylinder Roller and Spherical Roller Types, Metric Design 21.1 - Thrust Needle Roller and Cage Assembliesand Thrust Washers, Metric Design 21.2 - Thrust Needle Roller and Cage Assembliesand Thrust Washers, Inch Design 22.1 - Spherical Plain Radial Bearings, Joint Type - Metric Design 22.2 - Spherical Plain Radial Bearings, Joint Type - Inch Design 23.2 - Thrust Bearings of Tapered Roller Type - Inch Design 24.1 - Thrust Bearings of Ball, Cylindrical Roller and Spherical Roller Types - Metric Design 24.2 - Thrust Bearings of Ball and Cylindrical Roller Types - Inch Design 25.2 - Rolling Bearings, Linear Motion, Recirculating Ball, Sleeve Type - Inch Series 26.2 - Thin Section Ball Bearings - Inch Design An ABMA Standard is intended as a guide to aid the manufacturer, the consumer, and the general public. The existenceof an ABMA Standarddoes not in any respectpreclude anyone, whether he has approved the standard or not, from manufacturing, marketing, purchasing, or using products, processes,or procedures not conforming to the standard. ABMA Standardsare subject to revision or withdrawal at any time and users who refer to an ABMA Standardshould satisfy themselvesthat they have the latest information from the Association.
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American National Standard ABMA Standard Shaft and Housing Fits for Metric Radial Ball and Roller Bearings (Except Tapered Roller Bearings) Conforming to Basic Boundary Plan CONTENTS Section
Page
1. 2. 3. 4.
..l
Scope .......................................................... Conformity with other ANSI Standards ...................................... Description of Shaft and Housing Tolerance Classifications ......................... Selection of Shaft and Housing Fits ......................................... 4.1 ShaftFi~ ................................................... 4.2 HousingFits .................................................... 5. Design and Installation Considerations ....................................... 5.1 Effect of Fit on Bearing Internal Clearance ................................ 5.2 Allowance for Axial Displacement ..................................... 5.3 Installation Techniques ............................................. 6. Symbols and Nomenclature ..............................................
1 1 4 ...4 . 5 5 5 5 6
LIST OF FIGURES Figure No.
Page
1. Graphical Representation of Shaft Fits ....................................... 2. Graphical Representation of Housing Fits ..................................... 3. Classification of Loads in Relation to Basic Radial Load Rating C, ....................
2 3 5
LIST OF TABLES TABLE No. 1. .Selection of Shaft Tolerance Classifications ................................... 2. Shaft Diameter Limits and Resultant Fits ..................................... 3. Selection of Housing Tolerance Classifications ................................ 4. Housing Bore Limits and Resultant Fits .....................................
7 9 11 13
. III
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SHAFT AND HOUSING FITS FOR METRIC RADIAL BALL AND ROLLER BEARINGS (EXCEPT TAPERED ROLLER BEARINGS) CONFORMING TO BASIC BOUNDARY PLAN
1. Scope This standard covers the general selection of shaft and housing fits for metric radial ball and roller bearings of tolerance classesABEC 1 RBEC 1 as influenced by the type and extent of bearing loading and other design requirements. Other tolerance classes are not covered by this standard.
2. Conformity Standards
Recommendations for the fitting practices of some particular types of ball and roller bearings are covered in other ANSI/ABMA standards. These include:
3. Description of Shaft and Housing Tolerance Classifications
ANSUABMA Std. No. 12.1 & 12.2 16.1 & 16.2 18.1 & 18.2 19.1 & 19.2 26.2
Instrument Ball Bearings Airframe Ball, Roller and Needle Roller Bearings Needle Roller Bearings Tapered Roller Bearings Thin Section Ball Bearings
This standard can also be used as a guide for determining shaft and housing dimensions for inch design ball and roller bearings by using the recommended shaft and housing fits for metric bearings and applying the appropriate bore and O.D. tolerances for the inch design bearings, except those bearings covered by ANSUABMA Standard 15.
with Other ANSI
In the size range O-2500 mm, the deviations used in this standard for shaft and housing seats conform to American National Standard ANSI B4.2, “Preferred Metric Limits and Fits”.
In the size range described in 2 above, the tolerance classifications are designated by a letter and a numeral. A lower case letter is used’for shafts and a capital letter is used for housings. Numerals indicate the degree of accuracy - the smaller numerals representing closer tolerances than the larger. The letters indicate the location of the shaft and housing limits relative to the inner ring bore and outer ring outside diameter tolerance ranges indicated in Figures 1 and 2 by the symbols KB and hB respectively. Figures 1 and 2 show graphically how the various tolerance classifications result in clearance or interference depending upon how the diameters of the mating parts interact in specific cases.
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A
INTERFERENCE
CLEARANCE
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OUTER RING 0.0. TOLERANCE RANGE
HoustNG
BORE
TOLERANCE
RANGES
Figure 2 Graphical representation of housing fits
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4. Selection of Shaft and Housing Fits To select the proper fits, it is necessary to consider the type and extent of the load, bearing type, and certain other design and performance requirements. The required shaft and housing fits are indicated in Tables 1 and 3. The terms “Light”, “Normal” and “Heavy” loads refer to radial loads that are generally related to C, as shown in Figure 3 (C,, being the Basic Dynamic Radial Load Rating computed in accordance with ANSI/ABMA Standards). 4.1 Shaft Fits. Table 1 indicates the initial approach to shaft fit selection. Note that for most normal applications where the shaft rotates and the radial load direction is constant, an interference fit should be used. Also, the heavier the load, the greater is the required interference. For stationary shaft conditions and constant radial load direction, the inner ring may be moderately loose on the shaft. Table 2 shows the shaft diameter deviations and resultant fits for the various tolerance classifications for bore sizes over 3 mm and up to 1250 mm. 4.2 Housing Fits. Table 3 indicates the initial approach to housing fit selection. Note that the use of clearance or interference fits is mainly dependent upon which bearing ring rotates in relation to the radial load. For indeterminate or varying load directions, avoid clearance fits. Clearance fits are preferred in axially split housings to avoid distorting bearing outer rings. The extent of the radial load also influences the choice of fit. Table 4 shows the housing bore deviations and resultant fits for the various tolerance classifications for outer diameter sizes over 10 mm and up to 2500 mm.
5. Design and Installation Considerations 5.1 Effect of Fit on Bearing Internal Clearance. Since interference fitting will reduce bearing radial internal clearance, it is recommended that prospective users consult bearing manufacturers to make certain that the required bearings are correctly specified to satisfy all mounting, environmental and other operating conditions and requirements. This is particularly necessary in those caseswhere heat sources in associatedparts may further diminish bearing clearances in operation. Standard values of radial internal clearances of radial bearings are listed in ANSUABMA Standard 20. 5.2 Allowance for Axial Displacement. Consideration should be given to axial displacement of bearing components due to thermal expansion or contraction of associated parts. Displacement may be accommodated either by the internal construction of the bearing or by allowing one of the bearing rings to be axially displaceable. For unusual applications consult bearing manufacturers. 5.3 Installation Techniques. Damage to internal bearing surfaces may result from the transmission of mounting forces through the rolling elements. Therefore, methods and tools should be used that apply these forces directly to the ring or rings being interference fitted. To facilitate the installation of bearings on their seatings with interference fits, bearings or housings, as the case requires, may be thermally expanded by heating under controlled conditions. Bearing temperatures should not be allowed to exceed 120°C (250°F) to avoid ‘reducing bearing hardness.
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Heating of pre-lubricated bearings should be avoided to prevent deterioration of the lubricant. Alternatively, shafts or bearings may be chilled to provide sufficient contraction to facilitate installation. The bearing manufacturer should be contacted for information on low temperature limit and methods of cooling. Precautions should be observed to avoid corrosion through the creation of excessive atmospheric moisture condensation on bearings or other parts during this process.
6. Symbols and Nomenclature The following symbols and nomenclature are used in this standard. d = basic bore diameter D = basic outside diameter C, = basic dynamic radial load rating for a radial or angular contact ball bearing or for a radial roller bearing* P = equivalent radial load* * See ANSUABMA Standards 9 and 11 for additional information about how these values are determined.
BALL BEARINGS
CYLINDRICAL ROLLER BEARINGS
SPHERICAL ROLLER BEARINGS
P/C,
Figure 3 - Classification of Load (P) in Relation to Basic Load Rating (C,) l
l
Basic dynamicradial load rating C, basedon standard materials and one million revolutions
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TABLE 1 SELECTION OF SHAFT TOLERANCE CLASSIFICATIONS FOR METRIC RADIAL BALL AND ROLLER BEARINGS OF TOLERANCE CLASSES ABEC-1, RBEC-1 Ilt I
Dimensions in millimetres DESIGN &OPERATING CONDITIONS
Rotational Conditions
Inner Ring Axial
BALL BEARINGS
Radial 1 Loading Over
Diiplaceabillty
Inner Ring Rotating in relation to Load Direction
Light
’ 18
Normal
Or
Load Direction is Indeterminate
d
1:
Heavy
1:
Incl.
1 Tolerance Classification (1)
18 All
h5 j6 (2)
18 All
j5 k5
Loo All
k5 m5
1
CYLINDRICAL ROLLER BEARINGS d
Tolerance Classification (1)
T
SPHERICAL ROLLER BEARINGS
Over
Incl.
Tolerance Classification (1)
0 40 100 320 500
40 100 320 500 All
$32) W2) mW) n6 ~6
k5 m5 m6 n6 ~6 r6
0 40 65 100 140 280 500
40 65 100 140 280 500 All
k5 m5 m6 n6 ~6 r6 r7
m5 m6 n6 p6 r6 r7
0 40 65 100 140 200
40 65 100 140 200 All
m5 m6 n6 ~6 r6 r7
Over
Incl.
0 40 140 320 500
40 140 320 500 All
$X2) W2) W2)
0 40 100 140 320 500
40 100 140 320 500 All
0 40 65 140 200 500
40 65 140 200 500 All
z
d
Light Inner Ring StationaT in Relation to Load Direction
Inner Ring must be easily axially displaceable
Inner Ring need not be easily axially displaceable
Pure Thrust (Axial) Load
zerrn:’
/
All Sizes
1
g6
All Sizes
All Sizes
h6
All Sizes
86
All Sizes
h6
Consult Bearing Manufacturer
(1) Tolerance Classifications shown are for solid steel shaft.. Numerical values are listed in Table 2. For hollow or nonferrous shafts, tighter fits may be needed. (2) If greater accuracy is needed, substitute j5, k5 and m5 for j6, k6, and m6 respectively.
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TABLE 1 SELECTION OF SHAFT TOLERANCE CLASSIFICATIONS FOR METRIC RADIAL BALL AND ROLLER BEARINGS OF TOLERANCE CLASSES ABEC-1, RBEC-1 Dimensions in inches
Irt IT -Pa.__
BALL BEARINGS
DESIGN &OPERATING CONDITIONS Rotational Conditions
Inner Ring Axial Displaceabillty
Over
Light
Inner Rinrr-
d
Radial Loading
’ 0.71
Incl.
0.71 All
Tolerance Classification (1) h5 j6 (2)
Rotating in relation to Load Direction Normal
or
&& Direction is Indeterminate
Heavy
0 0.71
0.71 3.94
0.71 All
3.94 All
j5 k5
k5 m5
CYLINDRICAL ROLLER BEARINGS d Over
Incl.
Tolerance Classification (1)
SPHERICAL ROLLER BEARINGS d
Tolerance Classification (1)
Over
Incl.
0 1.57 3.94 12.6 19.7
1.57 3.94 12.6 19.7 All
$32) W2) m6(2) n6 ~6
12.6 19.7
19.7 All
j6(2) WV mG9 n6 ~6
0 1.57 3.94 5.51 12.6 19.7
1.57 3.94 5.51 12.6 19.7 All
k5 m5 m6 n6 ~6 r6
0 1.57 2.56 3.94 5.51 11.0 19.7
1.57 2.56 3.94 5.51 11.0 19.7 All
k5 m5 m6 n6 ~6 r6 r7
0 1.57 2.56 5.51 7.87 19.7
1.57 2.56 5.51 7.87 19.7 All
m5 m6 n6 ~6 r6 r7
0 1.57 2.56 3.94 5.51 7.87
1.57 2.56 3.94 5.51 7.87 All
m5 m6 n6 ~6 r6 r7
0 1.57 5.51
1.57 5.51 12.6
Light
Inner Ring Stationary in Relation to Load Direction
Inner Ring must be easily axially displaceable
Normal
All Sizes
86
All Sizes
All Sizes
h6
All Sizes
All Sizes
j6
All Sizes
g6
All Sizes
h6
Heavy Inner Ring need not be easily axially displaceable
Pure Thrust (Axial) Load
Light Normal
h6
Heavy Consult Bearing Manufacturer
(1) Tolerance Classifications shown are for solid steel shaft.. Numerical values are listed in Table 2. For hollow or nonferrous shafts, tighter fits may be needed. (2) If greater accuracy is needed, substitute j5, k5 and m5 for j6, k6, and m6 respectively.
7
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TABLE 2 SHAFI’ FIlTING PRACTICE FOR METRIC RADIAL BALL AND ROLLER BEARINGS OF TOLERANCE CLASSES ABEC-1, RBEC-1 Part I
r
I
d
Shaft Lkvistion
Deviation 131
1
-8
-5 -14
14L 3T
-6 -17 -7 -20 -9 -25 -10 -29
17L 2T 2OL 3T 25L 3T 29L ST
0 -13 1 0 -16
80
0 -8 0 -10 0 -14 0 -15
-19
IIL ST l3L IOT 16L l2T l9L 15T
120
0 -20
-12 -34
34L 8T
0 -22
I80
0 -25
-14 -39
39L IIT
1 2W
0 1 -30
1
-I5 ~44 1
1 225
1 0 i -30
1 1
225
1 1 250
1 0 1 -30
250
1 1 280
-:
2L 12T
+7 -2
2L IST
+7 +I
0 -8
8L 8T
+5 -3 t5 -4 +6 -5 t6 -1
3L l3T 4L IST 5L I8T 7L 2lT
t8 -3 t9 -4 tll -5 t12 -7
3L l6T 4L l9T 5L 23T 7L 27-T
+9 +I fll t2 +13 t2 +I5 t2
22L 2OT
+6 -9
9L 26T
t13 -9
3:;
+I8 +3
0 -25
25L 25T
t7 -II
IIL 32T
t14 -II
IIL 39T
t21 +3
44L 15T I
0 -29 ,
29L 30T 1
l3L VT,
+I6 -I3
l3L 46T1 -.
t24 +4
-15 1 -44 1
44L 1 IST 1
0 1 -29 1
.~.
1 1
-15 1 -44 1
44L 1 IST 1
1 0 1 -35
1 1
-17 1 -49 1
1
1
1
-17 1
50 80 I20
280
0
0 -II
01
_._
0 1 -29 1
29L I 3OT i
I 1
1
1
t7 1 -13 I
l3L, 37Tl
+I6 -I3
1
I
l3L I 46Tl
t24 +4
1 1
4T i 5ATl
49L 1 l8T 1
0 1 -32 1
32L 1 35T 1
I
1 1
t7 I -16 1
l6L 1 +I6 42T 1 -I6
I 1
l6L 1 t27 5IT 1 +4
f 1
49L 1
0 1
1
+7 -16
I6L 42T
+I6 -16
l6L SIT
t27 t4
36L 4oT
t7 -I8
I8L 47T
+I8 -18
l8L 58T
t29 t4
36L 40T
+7 -I8
I8L 47T
+I8 -18
l8L 58T
t29 t4
+7 -20
2OL 52T
+20 -20
2OL 65T
t32 t5
t7 -20
2OL 52T
t20 -20
2OL 65T
t32 t5
22L 58T
t22 -22
22L 72T
t30
-.
-60
2ST
-40
SM)
-22 -6.5
66L 28T
0 -44
44L SOT
0 -50 0 -75
-22 -66 -24 -74
66L 28T 74L SIT
0 -44 0 -50
44L SOT SOL 75T
0
-24
74L
0
5OL
-70 -26 .I -82 -26 -82
-.’ 1x1 -CAnI
.
1..
+37l
I..
l7Tl
.
,“,
+4nl
“..
I
+4flI
I
I
I7 Resultan, Fit
Shaft Deviation
Raultant Fit
..I
1
37-r 79-r, ~~~
I
43T 1 +!Xl 93T 1 t65
, 65T, 1 I I5T I
27T, t68 77T 1 +43
1 i
31T 1 +79 9iJT 1 t50
1 SOT, tlC.5 1 lO9T 1 t77
I
I I I I
I I I
I
1 77T I I 1361 I
+mI
,“.
20T 1 t57
t59 +37, --
,-,
17rl
,~,
7”T I
1
+.M
+23
95T
.“I t68
““. l53T
, ,,tl32
l32T 217T
+I95 +I32
I321 2401
t56 +26
26T IO6T
+122 t7.5
7ar l72T
+194 +I50
ISOT 244T
t220 tl50
l5Ul 27o1
i-56 +26 -CM +30 +fx
26T lO6T UIT, l4OT %IT I
t122 +7cl
78-r l72T
t199 +I55
l55T 249T
+225 +I55
IS5 I 275’1.
I S-Y t&8
YYI 213T
IL>> +I85
102,’ 3lOT
+265 +I85
1851. 340 I
+74 +34
34T l74T
+I56 +Wl .--
IOOT lwi--_.
t266 +,tn .-._
,c4.T _“I.
2lOT
t3GU A,,” ,c,”
“,YYl -L”,,
+74 +34
34T l74T
t 156 +IM)
IM)T 256T
t276 t220
220T 376T
t310 +??O
l 7,111.
1 :fff / -. . . ::t::--I 1 IZOT 1 t326 I 3llTI t260
__. , I 2MT 1 45lT)
+260
,
-- I --. I -_’ +Gi1 14OT
:::
I 2::
.I. l25T
t40
I
I
I I I
I
I I
I
I I
I I
I I
1
1
I
t461 0, 0 1 l7lT 1
ShnR tkviation
2:: RI2%
?L I .. t40 +I5
.
Raultant Fit
I
I--l. IST 58T
.
Shaft Dtriation
I
I --.-..
D ,_ +33 +15
.
I
I
r6
p6 Redtan, M
I
1 +43
I
--47 I1 -----.
Shaft Lkvistinn
3: IIT 39T
.
0
-ii 1 IOOT( t28 28L -28 l2liT t28 28L -28 l28T 1 I::::
_.. 54T
7TT.
t22 22L 22L t30 -22 72T 0 58T 25L 1 t25 1 25L 1 +35 I 85T 1 -251 IcuTl 01 25L ~~~ 1 t25 I 25L I t35 I
t13 1 33L 1 +-:: -33 l38T I
.-.
.-. 3T 53T
n6
Redtsnt m
6T 2OT
+20 t9 +74
4T
t241 +4 i
-.
2T 30T 2T
.” t28 t3
l3LI 46T I
-45
710
-1. 3T 46T
+I61 -13 I
SW
710
+I8 t2 t21
l3Ll 37T I
1
1I
Shaft DeviSO””
. . .
+I5 t7 +17. +8
I
+71 -13 I
4OL 45T 4OL 45T
630
IT 17-r 2T 21T 2T 25T 2T
1 1
-ir
630
1::
r
+9
Iiillnl._
m6
Redtant Fit
+12 t6
I
.-
I1
1
I
1
Shah DAhm ------
I1
ITI I4Tl
29L 1 3OT 1
-.
1
mS Raultant M
-..
+7 -I3
400
SKI
I I
I
Shnfi Deviation
1
355
500
k6 Redtsnt FR
,
315
--Roll
Shaft DWIation
t4 -2
50
1
Rest& tan, Fit
6L 8T
30
200
Shaft Devistion
t6 +I
30
180
Red*a”, Fit
2L1 I4T1
I8
.i
9L 8T
16
Shaft Derlnilon
+6 1 -2 1
I8
8LI WI
Red,.“, Fll
2Li IITI
0
0 1 -8 1
ShnR Dwistion
+3 I -21
IO
I
Raul*ant Fit
CLASSIFICATIONS
ks
5L1 ST 1
IO
1
Shaft Devistion
.js
0 1 -5 t
6
1
1 1
Rwultan, Fit
h5
I2L 1 4T 1
I61
0 -8
h6
-4 , -12 1
1
1
TOLERANCE
16
i +86 1 +40
1 40T 1 1 2llT)
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I :I:: .-1 +I86 I +I20
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TABLE 2 SHAFT FITTING PRACTICE FOR METRIC RADIAL BALL AND ROLLER BEARINGS OF TOLERANCE CLASSES ABEC-1, RBEC-1 Dimensions m lnclws and Fits in O.ooOl lncl~s
Deviakmsr
I
d
TOLERANCE
g6 Deviario”
Shaft Deviation
Redtan, nt
Shaft Deviatian
Rest& tnnt Fit
I
Shaft Deviatlon
Raultani Fit
Shaft &viation
Redtant Fit
Shaft lkvistion
Redtnnt Fit
Shaft Lkviation
ms
Redtmt Fn
Shaft &viation
n6
m6
Redtan, Fit
Shaft Devintion
Rsultant Fit
i
Shaft lkvistion
3L 3T
-i
2L 3T
+I -I
IL 4T
+2 -I
IL 5T
+2 0
OT ST
+4 +2
2T -IT
-2 -6
6L IT
0 -4
4L 3T
0 -2
t2 -I
IL ST
+3 -I
IL 6T
t3
:::
0
OT 6T
t5 +2
2T 8T
-2 -7
7L IT
0 -4
4L 3T
3L 3T
t2 -I
IL ST
t3 -I
IL 6T
t4
.;
0
OT 7T
+6 +3
-3 -8
8L IT
0 -5
t2 -2
2L 6T
+4 -2
2L 8T
+4 +I
:$
t7 +3
3T IIT
0 -4.5
-4 -10
IOL 0.5T
0 -6
6L 4.5T
+S +4
4T l2.5T
+10 t4
4T l4.5T
.i:
IIL 2T
0 -7
I:;
t9 +4
4T IST
+I2 +4
I::
t15 t8
0 -8
-5 -13
13L 3T
.i
7L 6T 9L ST
t5 +I +6 +I
Il.:%
0 -6
8.::: 3L IIT
+2 -4
4L IOT
t5 -4
4L l3T
t7 +I
IT IST
+I0 +I
IT l8T
+ll +5
ST l9T
+I4 t5
2::
+I8 +9
0 -IO
-6 -I5
l5L 4T
0 -10
IOL IOT
+3 -4
4L l3T
+6 -4
4L l6T
t8 +I
IT I8T
tll +I
1T 21T
IIL
t3 -5 I
5L IST I
+6 -5 I
5L l8T1
t9 t2
2T 2lT1
+24 +I2
+3 1 -5
5Lt IST
+6 1 -5
5Li I8Tj
+9 +2
t3 -5 +3 -6
5L IST 6L l7T
+6 -5 t6 -6
1::: 6L 2OT
+9 t2 +II +2
1 1
+3 1 -61
6L1 I7Tl
t6
1
6L1
tll
I I
t3 -71
I
7L I IWI
+7
I
7Ll
+I1
1
t3
1
7Li l9TI
+7 1 -7 1
8L 21T
+8 -8
8L 26T
+I3 +2
2;;
+8 -8
8L 26T
+I3 +2
9L 23T
t9-9
9L 29T
+126
3:; 0 I 3iT
3;T
0
-6 -17 i
l7L hT i -.
-,I
-6 1 -17
l7L i 6T
-II
-6 -17 -7 -10
l7L 6T 19L lT
I
I
-7 I -10 , I
-16 1
I
-7 I -9, _. 1
I
-7 I -1; 1
I 0 I 77 I -II._ I 2lLl 01 .li. I QT _. I 2lL I 0I OTI .I; I
1
,
0 -I2
1
0 -I? 0 -1.4 1. .,4
.,
-16 1
‘-
-1;
-3
_.
-8 -24
0 1
l2T1 .-.
1
I
0 I
IILI l2T
I
1
0
IIL l2T l3L IAT
-II 0 -11
-
l9L
,.
24L IOT
.
t2 -2 +2 -3
.
0 -16
I IdT . .I
13L l4LI
I.w I 14L I IfiT I ._.
.“.
I I I aI I I
I
-8 I
I6L l&T
+3 -8 +3 -8
I
+I3 t6
6T 23T
t16 +6
+I5 1 +7
1
7T 27Tl
+I8 t7
I
?T 30T I
1 +I5 1 +7
I 1
7T I +I8 27T1 +7
1 1
7T I t24 30T 1 +I2
I
i
7L1 +II 23T 1 +Z -
-2;
-Ii ”
I6L IST 171 iar
0 -20
-2
26L IIT
0 -17
l7L 2oT
t3 -9
2::
+9 -9
9L 29T
+12 0
29L
0
2OL 1 30T
+4 -IO
IOL 34T
+I0 -10
IOL 40T
+I4
2OL MT
t4 -IO
IOL 34T
+10 -10
IOL 40T
t14
22L 39T
IIL 44T
+I1 -II
IIL 5crT
+I6
-::
22L
+5
IIL
tll
IIL
+I6
-9
2TI 21T
I
2T 21T 2T 25T
.
24L IOT 7hl ;iT
I
1
+7 +I
+I5 +7
7-I’ 27-r
+I8 t7
+17
8T
+20
1 +I7 I 1 +R 1 ._
-8 -24 -9 -26
t3 -9
9.:T
I
0 -I8 n
0
0 -16
.
+4 -2
6.:::
_.
I 1
2T1 77l’I
_..
I I
+I8
II +R ._ I -I-18 I -CR ._
$20 +9
3:;
I
+29
1
I 1
l2T 1 +3l 36T1 +20
I 1
2UT1 43T1
t43 t3l
I I
2l-n 43T
t44 +33
267 45T 30T 54T
33T S6T
+5l +33
33’1 hTl
t29 +I5
IST ACT
+39 &,A
9r 38T
l6T 49T
t43 t27
2TT 6lT
+65 t50
JUI 83T
T,., +50
,I,, 92-r
t31 +I6
16T 49T
t43 +27 +AR ._ 1 +3l
27T 6lT 1IT . 68T
t68 +52 +7h t59
52T 86T WT 96-k
t77 +52 +I77 +$I
52’1 95’1 COT _‘. 1071
+48 +31
3lT 68T
t78 t6l
61T 98T
t89 t6l
61’1 109.1
35T +89 P”T I ILCI “7. I”,
69T ll9T
+I00 t69
69T l3OJ
35T 84T
t93 +73
73T I23T
+I04 t73
73T l34T
1 t6l 1 +39
1 39T It105 1 IOOT I +83
83T 144T
+I18 +83
83T 1571.
1 +6l
1
8TT
+I22
871
I
I
Redtant Fit
t31 +I6
I
I+131
Shaft Devintion
ST -SAT
I
1 t29
Redtan, Fit
_..
I
I
I
15T 1 -I ACTI +,A
l2T 56T
0 55T
I
I I
I I
0
I
+42 t30
ST I 1RTl
I I
t26 +I2
+35 +26
20T 43TI
l3T 1 -I 4Crl-1I
12T
