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Guias e Dicas
Guias e Dicas

Catálogo de fabricante, Esquemas de Máquinas

Rolamentos de precisão para máquinas ferramentas

Tipologia: Esquemas

2022

Compartilhado em 20/10/2023

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PRECISION ROLLING BEARINGS
CATALOG NO.
2018.07.Z-ABE-ABE
The appearance and specifications may be changed without prior notice if req ired to improve per formance.
Ever y care has been taken to ensure the accuracy of the information contained in
this catalog but no liability can be accepted for any errors or omissions.
PRECISION ROLLING BEARINGS
B1031E-6
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Table of Contents

Precision Rolling Bearings

Technical Description Dimension T ables

Precision Rolling Bearing T ypes and Designs 42

7900C/7900AC Series 45

7000C/7000AC Series 47

7200C/7200AC Series 49

BNH Series 53

TAH Series 57

TBH Series 59

NN3000 Series 63

NNU4900 Series 65

XRN Series 69

XRG Series 69

TAB Series 73

TAU Series 77

TAF-X Series 81

XYS1 Series 85

W1 Series 89

Angular Contact Ball Bearings

Standard Type

High-speed Angular Contact

Ball Bearings

Thrust Load Angular Contact

Ball Bearings

Double row Cylindrical

Roller Bearings

Cross Tapered Roller Bearings

Ball Screw Support Bearings

1.Bearing Selection

2.Bearing Life

3.Bearing Tolerance

4.Bearing Arrangement

5.Preload and Rigidity

6.Lubrication

7.Limiting Speeds

8.Shaft and Housing Design

9.Bearing Handling

1-1 Bea ring Selection Procedure 5

1-2 Stu dy Bearing T ype 6

2-1 Basic Dynamic Load Rating and Rated Life 7

2-2 Dynamic Equivalent Load 7

2-3 Angular Contact Ball Bearing Load 8

2-4 Basic Static Load Rating and Static Equivalent Load 9

3-1 To lerances for Radial Bearings 10

3-2 To lerance for Thrust Load Angular Contact Ball Bearings (T AH/TBH Series) 12

3-3 To lerances for Cross T apered Roller Bearings 12

3-4 To lerances for Ball Screw Suppor t Bearing (T AB/T AU series) 13

3-5 To lerances for Ball Screw Suppor t Bearings (T AF-X series) 14

3-6 To lerances for T apered Bore Cylindrical Roller Bearings 14

4-1 Fea tures of Bearing Arrangement 15

4-2 Mounting and Mounting Symbols 16

4-3 Flush Ground Angular Contact Ball Bearings 16

5-1 Preload Objectives 17

5-2 Preload Methods 17

5-3 Measuring Preload 17

5-4 Preload Ef fect 18

5-5 Standard Preload and Axial Rigidity 19

6-1 Purpose of Lubrication 27

6-2 Lubrication Methods 27

7-1 Lim iting Speed Factors 31

8-1 Shaft and Housing Fits 32

8-2 Recommended Accuracy for Shaft and Housing 33

8-3 Chamfer Dimension Limits 34

9-1 Storing and T ranspor ting Bearings 35

9-2 Bea ring Installation 35

9-3 Running T est 39

9-4 Removing Bearings 39

5 Bearing Selection Bearing Selection 6

Technical Description

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

1.Bearing Selection

Figure 1.1 Bearing Selection Procedure

While it is not easy to select the optimum bearing type

and combination, it is no exaggeration to say that bearing

selection is essential in order to obtain the desired design

per formance and ser vice life.

While there is no “best” procedure for selecting the optimal

bearing, the designer should consider giving priority to

meeting the most critical requirement of the bearing.

Figure 1.1 provides an example of a procedure based on

the establishment of priorities for the required bearing

characteristics.

1-1 Bearing Selection Procedure

Factors Selection guidelines

Allowable space for bearings

● When designing a shaft system, the rigidity and strength of the shaft are important factors. The first step is to determine the shaft diameter, and the bore diameter. ● Figure 1.2 shows guidelines for the main precision rolling contact bearings types and sizes used in machine tools.

Load (type, direction, magnitude)

● Select the optimum bearing type in accordance with the magnitude of radial and axial load, direction of the load (either one or both directions), and level (vibration or shock). ● In general, a roller bearing has a greater load rating capacity than a ball bearing.

Rotating speed

● Select the bearing type in accordance with the maximum rotating speed specified for the machine where the bearing is used. ● The limiting speeds of bearings is largely depended on the magnitude of the load applied, running accuracy, cage material, and cage design. Therefore, careful consideration is necessary. ● In general, angular contact ball bearings or cylindrical roller bearings, which demonstrate minimal temperature rise, are used in high-speed applications.

Rigidity

● In order to improve the rigidity of rotational axis, the rigidity of the shaft and housing, as well as the bearing rigidity become important. ● In general, roller bearing rigidity is greater than a ball bearing. ● The rigidity of combination angular contact ball bearing is increased by applying a preload to the bearing. Mounting and dismounting ● Selecting a separable bearing increases work efficiency during mounting and dismounting for periodic inspection, etc.

79 Series NNU49 Series 70 Series BNH Series NN30 Series TAH Series 72 Series

Figure 1.2 Main Precision Rolling Bearings Used in Machine T ools

1-2 Study Bearing Type

Performance, operating conditions, and environmental conditions demanded of bearings

Study bearing arrangement and types

Determine fit

Required Dynamic Load Rating

Select the degree of accuracy

Determining Preload

Study shaft and housing accuracy

Study handling and installation

Study design from maintenance viewpoint

Selection of bearing

Selecting the lubrication method Grease lubrication Grease and Oil Iubrication Sealed bearings Open bearings

Select bearing dimensions.

Basic static load rating check

Review operating speed

Is size within design limits?

Is operating load smaller than static load rating?

Is speed within limits?

Yes

Yes

Yes

No

No

No

1-2 Study Bearing Type

8-1 Shaft and Housing Fit

2 Bearing Life

3 Bearing Tolerance

5 Preload and Rigidity

8-2 Recommended Accuracy for Shaft and Housing

9 Bearing Handling

6 Lubrication

① Change from ball bearings to roller bearings. ② Use multiple bearings. ③ Use alternate dimension.

Review lubrication method

2-4 Basic Static Load Rating and Static Equivalent Load

7 Limiting Speeds

P.

P.

P.

P.

P.

P.

P.

P.

P.

P.

① Load direction and size ② Speed ③ Noise and torque ④ Horizontal or vertical shaft

① Outer or inner ring rotation ② Stationary, rotational or impact loading ③ Shaft and housing materials

Calculate the required dynamic load ratings based on load, rotation speed, and desired service life.

① Shaft axial run-out ② Vibration from rotation ③ Rotating speed

If high rigidity is required increase the preload.

In order to maintain performance of the main spindle in a machine tool, the accuracy of shaft and housing must be equal or higher than bearing accuracy. The recommended shaft and housing accuracy and surface roughness are shown in Tables 8.4 to 8.7.

Consider how to protect bearings from damage and dirt in the work environment, and design installation tools.

If the bearing service life is the same as or greater than the machine service life, consider a design or lubrication that does not require maintenance.

Monitoring equipment can help in predicting service life through heat and vibration measurements.

If the bearing service life or grease life is shorter than the machine service life, create a design that allows easy bearing replacement or easy grease replenishment, and define the maintenance interval.

Value analysis (Can standard parts be used?)

⑤ Rigidity ⑥ Axial bearing arrangement ⑦ Installation and removal ⑧ Vibration, shock

■ Prevent dirt, water, and other foreign matter from getting inside the bearing. ■ Maintenance is not required, since grease cannot be removedor added.

■ Countermeasures to keep dirt out, and to prevent oil/grease from leaking. ■ Design that allows grease replenishment.

④ Fixed or expansion (free) ⑤ Inner ring expansion due to centrifugal force at high rotation speeds

Bearing Selection

7 Bearing Life Bearing Life 8

Technical Description

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

2.Bearing Life

Although the requirements of rolling contact bearings

var y somewhat with the individual application, the principal

requirements are:

● High load capabilities

● Low friction

● Smooth and quiet rotation

● High accuracy

● High rigidity

The reliability or durability requirement sets the time frame

over which all other requirements are to be maintained. The

reliability requirement (life in the broad sense) includes grease

and acoustic life, as well as fatigue life. Reliability is reduced by

various type of damage and degradation.

Though there are other damage such as breakage and seizure,

these are considered to be separate from bearing life. Improper

handling, mounting, lubrication, and fits are the major causes of

problems leading to lower -than-calculated bearing life.

Regardless of how well they are maintained or mounted or

handled, dynamic bearings will eventually fail from rolling fatigue

generated by the repetitive stress of bearing load. The ser vice

life of a bearing can be examined from two perspectives: 1)

If, from inspection, a trace of fatigue becomes noticeable, the

bearing should be deemed not suitable for fur ther use; or 2)

length of bearing life in hours or revolutions can be predefined

as a limit beyond which the bearing is automatically replaced.

Since calculated fatigue life will var y with the size and type of

bearings used under identical load conditions, great care must

be taken in the analysis of the load conditions and the final

choice of bearings to satisfy the application requirements.

Fatigue lives of individual bearing are dispersed. When a group

of identical bearings operates under the same conditions, the

statistical phenomenon of dispersion will appear. Use of average

life is not an adequate criterion for selecting rolling contact

bearings. Instead, it is more appropriate to consider the limit

(hours or numbers of revolutions) which a large percentage of

the operating bearings can attain.

Accordingly , the rating life and basic dynamic load rating Cr or

Ca are defined using the following definitio

● Basic Rating Life

Total number of revolutions that 90% of a group of identical

bearings operated individually under equal conditions can

complete without suf fering material damage from rolling

fatigue.

● Basic Dynamic Load Rating (Cr or Ca)

Bearing load of constant direction and magnitude that ends

the bearing life after one million revolutions.

The rating life of bearings is calculated by Formula 2.1 and

Formula 2.2.

L=

P

C p^

── (Formula 2.1)

P

C p

Lh=

60n

─ (Formula 2.2)

L : Basic rating life (10 6 revolutions) Lh : Basic rating life (hours) C : Basic Dynamic Load Rating (N) (Cr for radial bearings, Ca for thrust bearings) P : Bearing Load (Dynamic Equivalent Load) (N) (Pr for radial bearings, Pa for thrust bearings) p : 3 (ball bearings), 10/3 (roller bearings) n : RPM: (min -1^ )

In case of multiple row ball bearing combinations, the basic

dynamic load rating is calculated using the factors provided

below.

2-row arrangement 3-row arrangement 4-row arrangement 1.62 2.16 2.

Bearing load P in Formula 2.1 and Formula 2.2 is the pure

radial load (pure axial load) of constant direction and magnitude.

Under actual operating conditions, there are many cases where

radial and axial loads are applied simultaneously. In such cases,

bearing life must be calculated by conver ting the radial and axial

loads into dynamic equivalent load.

Dynamic equivalent load is calculated using Formula 2.3.

Bearing load of constant direction and magnitude that ends the

bearing life after one million revolutions.

The rating life of bearings is calculated by Formula 2.1 and

Formula 2.2.

Pr=XFr +YFa or Pa=XFr +YFa ─^ (Formula 2.3)

Pr : Dynamic equivalent radial load (N) Pa : Dynamic equivalent axial load (N) Fr : Radial load (N) Pa : Axial load (N) X : Radial load factors (T able 2.1) Y : Axial load factors (T able 2.1)

2-1 Basic Dynamic Load Rating and Rated Life

2-2 Dynamic Equivalent Load

● Table 2.1 Load Factors Nominal contact angle

iFa/ Cor e

Single row and DT combination DB and DF combination

Fa/Fr >e Fa/Fr ≤e Fa/Fr >e

X Y X Y X Y

Radial ball bearings

15°

0.015 0.

1

0.029 0.40 1.40 1.57 2. 0.058 0.43 1.30 1.46 2. 0.087 0.46 1.23 1.38 2. 0.12 0.47 1.19 1.34 1. 0.17 0.50 1.12 1.26 1. 0.29 0.55 1.02 1.14 1. 0.44 0.56 1.00 1.12 1. 0.58 0.56 1.00 1.12 1. 25° − 0.68 0.41 0.87 0.92 0.67 1. 30° − 0.80 0.39 0.76 0.78 0.63 1. 40° − 1.14 0.35 0.57 0.55 0.57 0. Thrust ball bearings

50° − 1.49 0.73 1 1.37 0.57 0.73 1 55° − 1.79 0.81 1 1.60 0.56 0.81 1 60° − 2.17 0.92 1 1.90 0.55 0.92 1 (Note 1) i = 2 for DB and DF , i = 1 for single and DT.

(Note 2) For single and DT , use Pr=Fr when Fa/Fr ≤e.

(Note 3) When the nominal contact angle is 15°, use linear interpolation to determine X, Y , and e values of iFa/Cor that are not included in the table. (Note 4) For high-speed use (dmn value > 800,000), the centrifugal force of the roller must also be taken into consideration in addition to the external load. Please consult NACHI concerning such applications.

In the case of angular contact ball bearings, the points where

the extended contact lines within the bearing and the axis as

shown in Figure 2.1 must be used as the bearing suppor t

points (load centers).

Because of this, angular contact ball bearings are shown in

dimension tables with "a" dimensions indicating suppor t point

positions. This consideration is par ticularly impor tant when a

moment load is acting on a bearing series.

Axial component forces are generated when a radial load acts

on an angular contact ball bearing. Y ou can calculate the axial

component forces using Formula 2.4.

Fa'=

2Y

Fr ── (Formula 2.4)

Fa' : Induced axial load (N) Fr : Radial load (N) Y : Axial load factor

Due to these component forces, the axial load and dynamic

equivalent radial load acting on the bearing is as shown in

Table 2.2.

2-3 Angular Contact Ball Bearing Load

Figure 2.1 Induced Axial Load for Angular Contact Ball Bearings

Fr

Fa'

● Table 2.2 Axial Load and Dynamic Equivalent Load of Angula r Contact Ball Bearings

Bearing arrangement Load conditions Axial load Dynamic equivalent radial load

FrⅠ

Fa

FrⅡ

Fa ≥0.5( YⅠ− )

FrⅠ

YⅡ

FrⅡ FaⅠ=FaⅡ+Fa

FaⅡ=0.5 FrYⅡⅡ

PrⅠ=XⅠFrⅠ+YⅠ(FaⅡ+Fa )

PrⅡ=FrⅡ

FrⅠ

Fa

FrⅡ

Fa<0.5( YⅠ−^ )

FrⅠ

YⅡ

FrⅡ

FaⅡ=FaⅠ−Fa

FaⅠ=0.5 FrYⅠⅠ^ PrⅠ=FrⅠ

PrⅡ=XⅡFrⅡ+YⅡ(FaⅠ−Fa )

FrⅠ

Fa

FrⅡ

Fa ≥0.5( YⅡ−^ )

FrⅡ

YⅠ

FrⅠ

FaⅡ=FaⅠ+Fa

FaⅠ=0.5 FrYⅠⅠ^ PrⅠ=FrⅠ

PrⅡ=XⅡFrⅡ+YⅡ(FaⅠ+Fa )

FrⅠ

Fa

FrⅡ

Fa<0.5( YⅡ− )

FrⅡ

YⅠ

FrⅠ FaⅠ=FaⅡ−Fa

FaⅡ=0.5 FrYⅡⅡ

PrⅠ=XⅠFrⅠ+YⅠ(FaⅡ−Fa )

PrⅡ=FrⅡ

Fr Ⅰ, Fr Ⅱ : Radial load (N) applied to bearings I and II YⅠ, Y Ⅱ : Axial load factors of bearings I and II Pr Ⅰ, Pr Ⅱ : Dynamic equivalent radial load (N) of bearings I and II

Fa : External axial load (N) XⅠ, X Ⅱ : Radial load factors of bearings I and II

Bearing Life

11 Bearing T olerance Bearing T olerance 12

Technical Description

Bearing T olerance

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

● Table 3.2 T olerances of Outer Ring (JIS Class 5, Class 4, Class 2) (^) Unit: μm

Nominal bearing outside diameter

D (mm)

Single plane mean outside diameter variation of outer ring

ΔD mp

Outside diameter deviation

ΔD s

Outside diameter variation in a single radial plane (1)

VD sp

Mean outside diameter variation

VD mp

Class 5 Class 4 Class 2 Class 4 Class 2 Class 5 Class 4 Class 2 Class 5 Class 4 Class 2

Over Incl. Upper Lower Upper Lower Upper Lower

Diameter series Diameter series 0,2 9 0,2 9 0,2 0,2 max max max Upper Lower Upper Lower max max max max max 18 30 0 -6 0 -5 0 -4 0 -5 0 -4 6 5 5 4 4 3 2.5 2 30 50 0 -7 0 -6 0 -4 0 -6 0 -4 7 5 6 5 4 4 3 2 50 80 0 -9 0 -7 0 -4 0 -7 0 -4 9 7 7 5 4 5 3.5 2 80 120 0 -10 0 -8 0 -5 0 -8 0 -5 10 8 8 6 5 5 4 2. 120 150 0 -11 0 -9 0 -5 0 -9 0 -5 11 8 9 7 5 6 5 2. 150 180 0 -13 0 -10 0 -7 0 -10 0 -7 13 10 10 8 7 7 5 3. 180 250 0 -15 0 -11 0 -8 0 -11 0 -8 15 11 11 8 8 8 6 4 250 315 0 -18 0 -13 0 -8 0 -13 0 -8 18 14 13 10 8 9 7 4 315 400 0 -20 0 -15 0 -10 0 -15 0 -10 20 15 15 11 10 10 8 5

Unit: μm

Nominal bearing outside diameter

D (mm)

Outer ring radial runout of assembled bearing

K ea

Variation of outside surface generatrix inclination with outer ring reference

S D

Assembled bearing outer ring reference face runout with raceway (2)

S ea

Deviation of a single ring width

ΔC s

Outer ring width variation

VC s

Class 5 Class 4 Class 2 Class 5 Class 4 Class 2 Class 5 Class 4 Class 2 Class 5 Class 4 Class 2 Over Incl. max max max max max max max max max max max max 18 30 6 4 2.5 8 4 1.5 8 5 2.

Corresponds to the

values of ΔB s of

the inner ring being matched with it.

(Note 1) Applies to open type bearings. (Note 2) Applies to ball bearings. Remark: The low outside diameter deviation of bearings in T able 3.2 does not apply within a distance from the ring face of 1.2 x r max of the chamfer.

Except for the outside diameter of outer ring outside diameter , accuracy of angular contact ball bearings for thrust loads

conforms to JIS Class 4. Outside diameter of outer ring tolerances is as shown in T able 3.3.

Tolerances for cross tapered roller bearings is shown in T able 3.4 and T able 3.5.

3-2 Tolerance for Thrust Load Angular Contact Ball

Bearings (TAH/TBH Series)

3-3 Tolerances for Cross Tapered Roller Bearings

● Table 3.3 T olerance of Outside Diameter (^) Unit: μm Nominal bearing outside diameter

D (mm)

Outside diameter deviation

ΔD s

Over Incl. Upper Lower 50 80 -30 - 80 120 -36 - 120 180 -43 - 180 250 -50 - 250 315 -56 -

● Table 3.4 XRN Series Inner Ring and Outer Ring tolerances (^) Unit: μm

Bearing No.

Single plane mean bore diameter variation

Δd mp

Single plane mean outside diameter variation of outer ring

ΔD mp

Variation of assembled height T s Outer ring run-out max

Upper Lower Upper Lower Upper Lower Radial run-out Sideface runout 150XRN23 0 -13 0 -15 +350 -250 7 7 200XRN28 0 -15 0 -18 +350 -250 7 7 250XRN33 0 -15 0 -18 +350 -250 7 7 250XRN35 0 -10 0 -13 +350 -250 9 9 300XRN40 0 -13 0 -15 +350 -250 7 7 310XRN42 0 -13 0 -15 +350 -250 7 7 0330XRN045 +25 0 +25 0 +350 -250 8 8 350XRN47 0 -13 0 -15 +350 -250 9 9 375XRN49 0 -13 0 -15 +350 -250 7 7 400XRN55 0 -13 0 -18 +350 -250 9 9 0457XRN060 +25 0 +25 0 +380 -380 9 9 580XRN76 +25 0 +38 0 +406 -406 10 10 0685XRN091 +38 0 +38 0 +508 -508 12 12 950XRN117 0 -75 0 -75 +750 -750 14 14

● Table 3.5 XRG (XRGV) Series Inner Ring and Outer Ring T olerances (^) Unit: μm

Bearing No.

Single plane mean bore diameter variation

Δd mp

Single plane mean outside diameter variation of outer ring

ΔD mp

Variation of assembled height T s Inner ring run-out max

Upper Lower Upper Lower Upper Lower Radial run-out Sideface runout 130XRG23 0 -10 0 -15 +350 -250 6 7 140XRGV20 0 -13 0 -15 +350 -350 5 5 150XRG23 0 -13 0 -15 +350 -250 6 7 200XRGV028 0 -15 0 -18 +350 -350 7 7 320XRG43 0 -13 0 -15 +350 -250 7 7 480XRGV66 0 -45 -70 -100 +450 -450 11 11

ToleranceBearing

13 Bearing T olerance Bearing T olerance 14

Technical Description

Bearing T olerance

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

Tolerances for ball screw suppor t (T AB/T AU Series) is shown in T able 3.6 and T able 3.7.

For T AB flush ground type, P4 , tighter tolerances of outside and bore diameter , are available as option to minimize

dimensional dif ference within combination bearings.

3-4 Tolerances for Ball Screw Support Bearing (TAB/TAU series)

● Table 3.6 Tolerances for Inner Ring (Including Outer Ring W idth and Outer Ring Sideface Runout Reference to Raceway) (^) Unit: μm

Nominal bearing bore diameter

d (mm)

Single plane mean bore and bore variation

Δd mp, Δd s

Bore diameter variation in a single radial plane

Vd p

Mean bore diameter variation

Vd mp

Deviation of a single inner ring width (or a single outer ring width)

ΔB s, ΔC s

Width deviation of Inner ring

VB s

Radial runout of assembled bearing inner ring

K ia

Side face

runout S d with

reference to bore

Side face runout with reference to raceway of assembled bearing

inner ring S ia and of

assembled bearing

outer ring S ea

Class 5 Class 4 Class 5 Class 4 Class 5 Class 4 Class 5/Class 4 Class 5 Class 4 Class 5 Class 4 Class 5 Class 4 Class 5 Class 4 Over Incl. Upper Lower Upper Lower max max max max Upper Lower max max max max max max max max 10 18 0 -5 0 -4 4 3 3 2 0 -80 5 2.5 4 2.5 7 3 4 2 18 30 0 -6 0 -5 5 4 3 2.5 0 -120 5 2.5 4 3 8 4 5 2. 30 50 0 -8 0 -6 6 5 4 3 0 -120 5 3 5 4 8 4 6 2. 50 80 0 -9 0 -7 7 5 5 3.5 0 -150 6 4 5 4 8 5 7 2.

● Table 3.7 T olerances for Outer Ring (^) Unit: μm

Nominal bearing outside diameter

D (mm)

Single plane mean outside diameter variation of outer ring

ΔD mp, ΔD s

Outside diameter variation in a single radial plane

VD p

Mean outside diameter variation

VD mp

Outer ring width variation

VC s

Outer ring radial runout of assembled bearing

K ea

Variation of outside surface generatrix inclination with outer ring reference

S D

Class 5 Class 4 Class 5 Class 4 Class 5 Class 4 Class 5 Class 4 Class 5 Class 4 Class 5 Class 4 Over Incl. Upper Lower Upper Lower max max max max max max max max max max 30 50 0 -7 0 -6 5 5 4 3 5 2.5 7 5 8 4 50 80 0 -9 0 -7 7 5 5 3.5 6 3 8 5 8 4 80 120 0 -10 0 -8 8 6 5 4 8 4 10 6 9 5

● Table 3.8 Tolerances for Bore Diameter of Inner Ring (P4F) (^) Unit: μm Nominal bearing bore diameter

d (mm)

Single plane mean bore diameter variation

Δd mp, Δd s

Class 4 flush ground Over Incl. Upper Lower 10 18 0 - 18 30 0 - 30 50 0 - 50 80 0 - Tolerances for other than bore diameter conforms to Class 4 in T able 3.6.

● Table 3.9 Tolerance for Outside Diameter of Outer Ring (P4F) (^) Unit: μm Nominal bearing outside diameter

D (mm)

Single plane mean outside diameter variation of outer ring

ΔD mp, ΔD s

Class 4 flush ground Over Incl. Upper Lower 30 50 0 - 50 80 0 - 80 120 0 - Tolerances for other than outside diameter conforms to Class 4 in T able 3.7.

Tolerances for ball screw suppor t (T AF-X Series) is shown in T able 3.10 and T able 3.11.

Tolerances for tapered bores (Cylindrical roller bearings) is specified by JIS. Since JIS tolerances are rather broad, NACHI

defines its own narrower range for precision bearings

3-5 Tolerances for Ball Screw Support Bearings (TAF-X series)

3-6 Tolerances for Tapered Bore Cylindrical Roller Bearings

● Table 3.10 T olerances for Inner Ring (Including Outer Ring W idth, Equivalent JIS Class 5) (^) Unit: μm

Nominal bearing bore diameter

d (mm)

Single plane mean bore diameter variation

Δd mp

Bore diameter variation in a single radial plane

Vd p

Mean bore diameter variation

Vd mp

Outer and inner ring width variation

ΔB s, ΔC s

Width deviation VBS of Inner Ring

VB s

Radial runout of assembled bearing inner ring

K ia

Side face runout with reference to bore

S d

Side face runout with reference to raceway of assembled bearing inner ring

S ia

Over Incl. Upper Lower max max Upper Lower max max max max 18 30 0 -6 5 3 0 -120 5 4 8 8 30 50 0 -8 6 4 0 -120 5 5 8 8 50 80 0 -9 7 5 0 -150 6 5 8 8 80 120 0 -10 8 5 0 -200 7 6 9 9

● Table 3.11 T olerances for Outer Ring (Equivalent JIS Class 5) (^) Unit: μm

Nominal bearing outside diameter

D (mm)

Single plane mean outside diameter variation of outer ring

ΔD mp

Outside diameter variation in a single radial plane

VD p

Mean outside diameter variation

VD mp

Outer ring width variation

VC s

Outer ring radial runout of assembled bearing

K ea

Variation of outside surface generatrix inclination with outer ring reference

S D

Assembled bearing outer ring reference face runout with raceway

S ea

Over Incl. Upper Lower max max max max max max 50 80 0 -9 7 5 6 8 8 10 80 120 0 -10 8 5 8 10 9 11 120 150 0 -11 8 6 8 11 10 13 150 180 0 -13 10 7 8 13 10 14 180 250 0 -15 11 8 10 15 11 15 250 315 0 -18 14 9 11 18 13 18

● Table 3.12 T olerances for T apered Bores (Cylindrical Roller Bearings) (^) Unit: μm

Nominal bearing bore diameter

d (mm)

Mean bore diameter deviation at theoretical small end of a tapered bore Bore diameter variation in asingle plane radial plane

Δd mp Δd 1mp - Δd mp Vd p

Class 5 Class 4 Class 5 Class 4 Class 5 Class 4 Over Incl. Upper Lower Upper Lower Upper Lower Upper Lower max max 18 30 +10 0 +6 0 +5 0 +3 0 3 3 30 50 +12 0 +8 0 +5 0 +4 0 4 3 50 80 +15 0 +9 0 +6 0 +4 0 5 4 80 120 +20 0 +10 0 +7 0 +5 0 5 4 120 180 +25 0 +13 0 +10 0 +7 0 7 5 180 250 +30 0 +15 0 +12 0 +9 0 8 6 250 315 +35 0 +18 0 +15 0 +11 0 9 9 315 400 +40 0 +23 0 +16 0 +12 0 12 12

d : Nominal bearing bore diameter

d 1 : Basic diameter at theoretical large end of tapered bore

d 1 = d + 121 B

Δd mp : Mean bore diameter deviation at theoretical small end of tapered bore

Δd 1mp : Mean bore diameter deviation at theoretical large end of tapered bore

B : Nominal bearing inner ring width

α : Nominal taper angle (half of cone angle)

Figure 3.1 Tapered Bores of Cylindrical Roller Bearings

Theoretical tapered bore Tapered bore with actual mean diameters at their deviations

φ d

α

B B

α

φ d

1 φ(

d + Δd

)mp

φ(

d^1 +

Δd 1mp

Δd 1mp- Δd 1mp 2

ToleranceBearing

17 Preload and Rigidity Preload and Rigidity 18

Technical Description

5.Preload and Rigidity

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

Rolling contact bearings generally have internal clearance

suitable for operating conditions, angular contact

ball bearings also may be installed with appropriate

predetermined negative clearance (axial preload).

This is known as "preload". Care is required when

determining preloads. An improper preload can increase

friction torque, raise temperature, cause abnormal sounds,

shor ten bearing life, and cause other problems.

The following is a list of what can be achieved by preloading.

● Reduced axial displacement due to external force and

greater axial rigidity

● Prevention of vibration and noise and increased speed

due to greater axial rigidity

● Less chance of fretting due to external vibration

● Smooth rolling rotation

● Lower noise and less heat due to ball centrifugal force

and gyro-moment

Gyro-moment

The balls of an angular contact ball bearing spin around

rotational axes while they revolve around an orbital axis (axis

line). An angle is per formed between the rotational axis

and orbital axis, and a moment is generated when a ball

attempts to revolve on the center of the two dif ferent axes.

This is called a "gyro-moment" (Figure 5.1).

The size of the gyro-moment is propor tional to rotational

angular velocity and orbital angular velocity. Gyro-moment

is small enough to be ignored at low-speed rotation, but

heat generation due to slipping caused by gyro-motion in the

high-speed rotation range cannot be ignored. In order to

suppress slipping caused by gyro-motion, friction (ball load x

coefficient of friction) between the balls and raceway su face

must be maintained. This means that there are times when

minimal preload can be chosen.

Ball rotation

Gyro-moment

Figure 5.1 Gyro-moment

5-1 Preload Objectives

Axial load measurement method

For spring preloading (fixed-pressure preload), the preload

is known if the spring displacement is known.

For nut preloading (fixed-position preload), the preload

can be determined based on the relationship between

nut tightening torque and tightening force. However , that

caution is required because there is wide variation in the

relationship between nut tightening torque and tightening

force due to accuracy and roughness of the threaded

por tion.

Axial displacement measurement method

The preload can be determined based on the relationship

between the axial load on the bearing and axial

displacement.

Bearing starting friction torque measurement method

To per form this measurement, your first need to create a

graph of the load and star ting torque of the bearing itself.

However , caution is required because of variation due to

bearing type, lubrication conditions, etc.

5-3 Measuring Preload

Preloading combination bearings is broadly divided between

fixed-position preload and fixed-pressure preloa

Table 5.1 (P. 18) shows graphic examples and describes

the characteristics of each type of preloading.

A cylindrical roller bearing with tapered bore also may be

used with radial preload (negative radial clearance) applied.

However , caution is required because radial preload that is

too large dramatically reduces ser vice life (Figure 5.2).

5-2 Preload Methods

Figure 5.2 Cylindrical Roller Bearing (NN3020) Radial Clearance and Ser vice Life

0

-0.020 0 0.020 0.040 0. Radial clearance (mm)

Radial Load: 4710N (3% of dynamic load rating)

● Table 5.1 Preload Methods Preload methods Design example Features

Fixed-position preload

Method using either a duplex bearing with pre-adjusted preload or a dimension adjusted spacer

● Since bearing spread is used, the prescribed preload can be obtained simply by tightening a nut. ● Fit causes preload inconsistency. ● Heat generation causes preload inconsistency. ● Applying an axial load that is too great can cause loss of preload.

Preload adjustment method using nut tightening

● Uniform preload, even if fit is inconsistent ● Further tightening possible ● Heat generation causes preload inconsistency. ● Applying an axial load that is too great can cause loss of preload.

Fixed-pressure preload

Method using spring

● Constant uniform preload while running ● No loss of preload ● Suitable for high speeds ● In principle, one-direction axial load can be applied ● Inferior rigidity compared to fixed-position preload of the same preload

Graphic analysis of load distribution and axial displacement

on two bearings when preload is applied with an external

load, as shown in Figure 5.3, is per formed as described

below.

① Graph the Axial Load T - Axial Deflection δa cur ve for

bearing A.

② Locating preload Tp on the T -axis, determine the point

of intersection for bearing A cur ve, and then graph the

T - δa cur ve for Bearing B point P.

③ Link the above two cur ves horizontally along the T -axis

for a length that corresponds to the external load value

Tw.

④ Loads T a and Tb, which correspond to the points of

intersection of the lines, are the loads of each bearing

under external load conditions.

⑤ Axial displacement is given as bearing B displacement

δw. (Bearing B displacement is the displacement for Tp

subtracted from the displacement for Tb.)

The reason for this is that the displacements of two

preloaded bearings are not uniform within the range that

the preload does not become zero due to outside load.

(Figure 5.3 is uniform). In other words, bearing A is

displaced only as much as bearing B is displaced by the

external load.

After external load becomes great and preload is eliminated,

bearing B load Tb becomes the same as external load

Tw, and bearing A load is eliminated. The size of the

external load when this preload is eliminated is indicated in

Figure 5.3 as Tpo.

5-4 Preload Effect

Figure 5.3 Fixed-position Preload

Bearing A Bearing B

Tw (^) O

Applied load Tw

Axial load

Ta

T-^ δ^ a curve of bearing A

T- δ a curve of bearing B

Tp Tb

P

Tpo

O’

δ w

Preload and

Rigidity

(Life=1 when radial clearance=0)

Life ratio

Axial elastic displacement amount

δ a

19 Preload and Rigidity Preload and Rigidity 20

Technical Description

Preload and Rigidity

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

5.5.1 Angular Contact Ball Bearing

Preloads and axial rigidity for face-to-face and back-to-back

duplex mounting are shown in T able 5.3 1 to 6

(P. 19 through 21). Preloads for multiple-row arrangements

can be obtained by multiplying by the coefficients in

Table 5.2.

● Table 5.2 Preload Factors for Multiple-row Arrangements 3-row arrangement 4-row arrangement FFB ・BFF FFFB ・BFFF FFBB ・BBFF 1.36 1.57 2

5-5 Standard Preload and Axial Rigidity

● Table 5.

1 7900C Series, Contact Angle 15°

Bore diameter number

E preload (extra-light preload) L preload (light preload) M preload (medium preload) Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm) 00 5 10 15 15 30 20 01 7 12 20 18 40 24 02 8 13 25 21 50 28 03 8 13 25 21 50 28 04 15 19 40 27 80 36 05 15 19 50 33 100 43 06 15 21 50 36 100 48 07 25 28 70 41 140 56 08 25 28 80 44 155 60 09 35 35 100 53 195 70 10 35 35 100 56 195 72

2 7900AC Series, Contact Angle 25°

Bore diameter number

L preload (light preload) M preload (medium preload) H preload (heavy preload) Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm) 00 20 33 88 59 196 82 01 20 33 98 65 216 90 02 29 42 108 67 235 94 03 29 42 118 74 255 102 04 59 65 235 107 490 149 05 69 69 265 120 560 169 06 78 78 294 134 628 190 07 88 88 323 147 785 212 08 88 98 412 165 1,000 244 09 98 109 470 188 1,040 260 10 118 118 520 208 1,140 284

3 7000C Series, Contact Angle 15°

Bore diameter number

E preload (extra-light preload) L preload (light preload) M preload (medium preload) H preload (heavy preload) Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm) 00 20 13 50 20 100 29 145 37 01 20 14 50 21 100 31 145 39 02 20 15 50 23 100 34 145 42 03 20 16 50 25 100 35 145 43 04 50 23 100 33 195 48 295 59 05 50 26 100 36 195 50 295 63 06 50 27 100 38 195 53 390 75 07 70 33 145 46 295 64 390 75 08 70 34 145 49 295 68 590 98 09 70 34 145 49 295 68 590 98 10 70 36 145 51 295 70 590 100 11 100 43 195 56 390 78 785 112 12 100 43 195 58 390 82 785 115 13 100 47 195 61 390 85 785 123 14 145 57 295 75 590 105 1,170 149 15 145 57 295 77 590 107 1,170 153 16 145 57 295 75 590 105 1,170 149 17 195 65 390 89 785 125 1,470 171 18 195 65 390 87 785 121 1,470 165 19 195 68 390 91 785 125 1,470 171 20 195 70 390 93 785 127 1,470 173

4 7000AC Series, Contact Angle 25°

Bore diameter number

L preload (light preload) M preload (medium preload) H preload (heavy preload) Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm)

Preload (N)

Axial rigidity (N/μm) 00 39 39 118 62 314 95 01 39 44 127 67 343 104 02 49 49 157 83 353 118 03 59 59 216 98 520 144 04 59 59 274 110 608 152 05 108 83 392 140 804 187 06 118 91 441 158 892 208 07 127 98 539 174 1,156 236 08 147 113 617 193 1,176 256 09 216 135 745 213 1,646 300 10 225 141 784 224 1,744 317 11 314 157 1,040 254 2,078 341 12 333 167 1,098 268 2,205 362 13 363 191 1,225 299 2,450 402 14 392 196 1,460 332 3,010 443 15 412 206 1,530 348 3,155 464 16 529 230 1,900 373 3,880 504 17 549 239 1,990 390 4,080 530 18 676 260 2,185 405 4,600 555 19 706 272 2,300 427 4,810 580 20 745 287 2,400 445 5,050 608

Preload and

Rigidity

23 Preload and Rigidity Preload and Rigidity 24

Technical Description

Preload and Rigidity

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

5.5.4 Ball Screw Support Bearings

● Table 5.

1 T AB Series, Contact Angle 60°, L preload (light preload)

Bearing No.

2-row arrangement 3-row arrangement 4-row arrangement DB/DF FFB/BFF FFBB/BBFF FFFB/BFFF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 15TAB04 1,080 540 10 1,470 800 11 2,160 1,080 16 1,700 1,020 12 17TAB04 1,080 540 10 1,470 800 11 2,160 1,080 16 1,700 1,020 12 20TAB04 1,080 540 10 1,470 800 11 2,160 1,080 16 1,700 1,020 12 25TAB06 1,665 757 15 2,260 1,130 20 3,330 1,510 30 2,610 1,430 23 30TAB06 1,665 757 15 2,260 1,130 20 3,330 1,510 30 2,610 1,430 23 35TAB07 1,960 933 20 2,670 1,390 27 3,920 1,870 40 3,080 1,760 31 40TAB07 1,960 933 20 2,670 1,390 27 3,920 1,870 40 3,080 1,760 31 40TAB09 2,600 1,000 30 3,540 1,490 41 5,200 2,000 60 4,080 1,890 47 45TAB07 2,060 981 20 2,800 1,460 27 4,120 1,960 40 3,230 1,850 31 45TAB10 2,990 1,107 35 4,070 1,650 47 5,980 2,210 70 4,690 2,090 54 50TAB10 3,140 1,163 40 4,270 1,730 54 6,280 2,330 80 4,930 2,200 62 55TAB10 3,140 1,163 40 4,270 1,730 54 6,280 2,330 80 4,930 2,200 62 55TAB12 3,530 1,358 45 4,800 2,020 61 7,060 2,720 90 5,540 2,570 70 60TAB12 3,530 1,358 45 4,800 2,020 61 7,060 2,720 90 5,540 2,570 70

2 T AB Series, Contact Angle 60°, M preload (medium preload)

Bearing No.

2-row arrangement 3-row arrangement 4-row arrangement DB/DF FFB/BFF FFBB/BBFF FFFB/BFFF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 15TAB04 2,160 735 15 2,940 1,080 20 4,310 1,470 30 3,430 1,320 25 17TAB04 2,160 735 15 2,940 1,080 20 4,310 1,470 30 3,430 1,320 25 20TAB04 2,160 735 15 2,940 1,080 20 4,310 1,470 30 3,430 1,320 25 25TAB06 3,330 981 20 4,510 1,470 27 6,670 1,960 40 5,200 1,910 30 30TAB06 3,330 981 20 4,510 1,470 27 6,670 1,960 40 5,200 1,910 30 35TAB07 3,920 1,230 25 5,300 1,770 35 7,840 2,350 50 6,180 2,300 40 40TAB07 3,920 1,230 25 5,300 1,770 35 7,840 2,350 50 6,180 2,300 40 40TAB09 5,200 1,320 50 7,060 1,910 68 10,400 2,550 100 8,140 2,500 80 45TAB07 4,120 1,270 30 5,590 1,910 40 8,240 2,550 60 6,470 2,500 45 45TAB10 5,980 1,470 60 8,140 2,160 82 12,000 2,890 120 9,410 2,790 95 50TAB10 6,280 1,520 65 8,530 2,260 88 12,600 3,040 130 9,810 2,940 100 55TAB10 6,280 1,520 65 8,530 2,260 88 12,600 3,040 130 9,810 2,940 100 55TAB12 7,060 1,770 70 9,610 2,550 95 14,100 3,480 140 11,100 3,380 110 60TAB12 7,060 1,770 70 9,610 2,550 95 14,100 3,480 140 11,100 3,380 110

3 TAU Series, Contact Angle 60°, M preload (medium preload)

Bearing No. Preload (N)^ Axial rigidity (N/μm)^ Starting torque (N ・cm) 15TAU06F 1,000 400 5 17TAU06F 1,180 450 5 20TAU06F 2,160 650 10 25TAU07F 2,350 750 15 30TAU08F 2,550 850 15 30TAU10F 4,310 950 30 35TAU09F 2,550 900 15 40TAU10F 3,230 1,000 20 40TAU11F 7,200 1,200 60 50TAU11F 4,210 1,250 30 50TAU14F 7,850 1,400 70 60TAU14F 4,980 1,300 40

4 T AF-X Series, Contact Angle 55°, E preload (extra-light preload)

Bearing No.

2-row arrangement 3-row arrangement 4-row arrangement DB/DF FFB/BFF FFBB/BBFF FFFB/BFFF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 25TAF05X 80 240 0.4 110 360 0.5 160 480 0.8 130 450 0. 25TAF06X 120 255 0.7 160 380 0.9 240 510 1.4 190 480 1 30TAF07X 180 345 1 240 510 2 360 690 2 280 650 1. 35TAF09X 270 410 2 370 610 3 540 820 4 420 770 3 40TAF09X 270 410 2 370 610 3 540 820 4 420 770 3 40TAF11X 410 510 3 560 760 4 820 1,020 6 640 960 4 45TAF10X 320 450 3 440 670 3 640 900 6 500 850 4 45TAF11X 410 510 3 560 760 4 820 1,020 6 640 960 4 50TAF11X 410 510 3 560 760 4 820 1,020 6 640 960 4 50TAF13X 550 600 5 750 890 7 1,100 1,200 10 860 1,130 8 60TAF13X 550 600 5 750 890 7 1,100 1,200 10 860 1,130 8 60TAF17X 890 780 10 1,210 1,160 13 1,780 1,560 20 1,400 1,470 15 80TAF17X 890 780 10 1,210 1,160 13 1,780 1,560 20 1,400 1,470 15 80TAF21X 1,390 930 20 1,890 1,390 25 2,780 1,860 40 2,180 1,760 30 100TAF21X 1,390 930 20 1,890 1,390 25 2,780 1,860 40 2,180 1,760 30 100TAF26X 1,960 1,000 30 2,670 1,490 40 3,920 2,000 60 3,080 1,890 50 120TAF26X 1,960 1,000 30 2,670 1,490 40 3,920 2,000 60 3,080 1,890 50

5 T AF-X Series, Contact Angle 55°, L preload (light preload)

Bearing No.

2-row arrangement 3row arrangement 4-row arrangement DB/DF FFB/BFF FFBB/BBFF FFFB/BFFF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 25TAF05X 310 385 1.5 420 570 2 620 770 3 490 730 2 25TAF06X 460 390 3 630 580 4 920 780 6 720 740 5 30TAF07X 660 490 5 900 730 6 1,320 980 10 1,040 930 7 35TAF09X 1,000 495 10 1,360 740 10 2,000 990 20 1,570 940 15 40TAF09X 1,000 495 10 1,360 740 10 2,000 990 20 1,570 940 15 40TAF11X 1,550 795 15 2,110 1,180 20 3,100 1,590 30 2,430 1,500 25 45TAF10X 1,200 680 10 1,630 1,010 15 2,400 1,360 20 1,890 1,290 15 45TAF11X 1,550 795 15 2,110 1,180 20 3,100 1,590 30 2,430 1,500 25 50TAF11X 1,550 795 15 2,110 1,180 20 3,100 1,590 30 2,430 1,500 25 50TAF13X 2,070 920 25 2,820 1,370 30 4,140 1,840 50 3,250 1,740 35 60TAF13X 2,070 920 25 2,820 1,370 30 4,140 1,840 50 3,250 1,740 35 60TAF17X 3,350 1,180 45 4,560 1,760 65 6,700 2,360 90 5,260 2,230 70 80TAF17X 3,350 1,180 45 4,560 1,760 65 6,700 2,360 90 5,260 2,230 70 80TAF21X 5,200 1,030 90 7,070 1,530 120 10,400 2,060 180 8,160 1,950 140 100TAF21X 5,200 1,030 90 7,070 1,530 120 10,400 2,060 180 8,160 1,950 140 100TAF26X 7,500 1,800 150 10,200 2,680 250 15,000 3,600 300 11,800 3,400 235 120TAF26X 7,500 1,800 150 10,200 2,680 250 15,000 3,600 300 11,800 3,400 235

6 T AF-X Series, Contact Angle 55°, M preload (medium preload)

Bearing No.

2-row arrangement 3-row arrangement 4-row arrangement DB/DF FFB/BFF FFBB/BBFF FFFB/BFFF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm)

Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 25TAF05X 780 550 4 1,060 820 6 1,560 1,100 8 1,220 1,040 6 25TAF06X 1,160 535 8 1,580 780 11 2,320 1,070 16 1,820 1,010 12 30TAF07X 1,660 650 15 2,260 970 17 3,320 1,300 30 2,600 1,230 20 35TAF09X 2,530 870 25 3,440 1,300 31 5,060 1,740 50 3,970 1,640 36 40TAF09X 2,530 870 25 3,440 1,300 31 5,060 1,740 50 3,970 1,640 36 40TAF11X 3,900 1,080 45 5,300 1,610 60 7,800 2,160 90 6,120 2,040 68 45TAF10X 3,050 975 30 4,150 1,450 40 6,100 1,950 60 4,790 1,840 47 45TAF11X 3,900 1,080 45 5,300 1,610 60 7,800 2,160 90 6,120 2,040 68 50TAF11X 3,900 1,080 45 5,300 1,610 60 7,800 2,160 90 6,120 2,040 68 50TAF13X 5,200 1,270 70 7,070 1,890 90 10,400 2,540 140 8,160 2,400 110 60TAF13X 5,200 1,270 70 7,070 1,890 90 10,400 2,540 140 8,160 2,400 110 60TAF17X 8,400 1,580 140 11,400 2,350 190 16,800 3,160 280 13,200 2,990 220 80TAF17X 8,400 1,580 140 11,400 2,350 190 16,800 3,160 280 13,200 2,990 220

Preload and

Rigidity

25 Preload and Rigidity Preload and Rigidity 26

Technical Description

Preload and Rigidity

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

7 7000XYS1 Series, Contact Angle 30°, M preload

(medium preload)

Bearing No.

2-row arrangement DB/DF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 7000XYS1 147 92 0. 7001XYS1 147 98 0. 7002XYS1 147 98 0. 7003XYS1 147 105 0. 7004XYS1 294 147 1.

9 7000W1 Series, Contact Angle 30°, M preload

(medium preload)

Bearing No.

2-row arrangement DF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 7000W1Y 147 77 0. 7001W1Y 147 86 0. 7002W1Y 147 98 0. 7003W1Y 294 128 0. 7004W1Y 294 134 0. 7005W1Y 490 175 1.

8 7200XYS1 Series, Contact Angle 30°, M preload

(medium preload)

Bearing No.

2-row arrangement DB/DF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 7203XYS1 294 140 1. 7204XYS1 490 169 3. 7205XYS1 490 188 3. 7206XYS1 490 196 4.

 7200W1 Series, Contact Angle 30°, M preload

(medium preload)

Bearing No.

2-row arrangement DF Preload (N)

Axial rigidity (N/μm)

Starting torque (N ・cm) 7200W1Y 147 82 0. 7201W1Y 147 82 0. 7202W1Y 294 118 0. 7203W1Y 294 118 0. 7204W1Y 490 153 1. 7205W1Y 490 169 1.

5.5.5 Radial Internal Clearance for Double row

Cylindrical Roller Bearings

The radial internal clearance for double row cylindrical

roller bearings is specified by JIS, NACHI defines its ow

narrower range in order to maximize rotation accuracy.

The radial internal clearances for cylindrical bore bearings

and tapered bore bearings are shown in T able 5.7. Also,

caution is required when handling and installing bearings

with non-interchangeable clearances, because there is no

interchangeability with another bearing's outer ring or inner

ring.

● Table 5.

1 Cylindrical Bore Bearing Non-interchangeable Clearance Unit: μm

Nominal bearing bore diameter d (mm)

Cylindrical bore bearing clearance (non-interchangeable) C1na C2na Cna C3na Over Incl. min max min max min max min max 24 30 0 10 10 25 25 35 40 50 30 40 0 12 12 25 25 40 45 55 40 50 0 15 15 30 30 45 50 65 50 65 0 15 15 35 35 50 55 75 65 80 0 20 20 40 40 60 70 90 80 100 0 25 25 45 45 70 80 105 100 120 0 25 25 50 50 80 95 120 120 140 0 30 30 60 60 90 105 135 140 160 0 35 35 65 65 100 115 150 160 180 0 35 35 75 75 110 125 165 180 200 0 40 40 80 80 120 140 180 200 225 0 45 45 90 90 135 155 200 225 250 0 50 50 100 100 150 170 215 250 280 0 55 55 110 110 165 185 240 280 315 0 60 60 120 120 180 205 265 315 355 0 65 65 135 135 200 225 295

2 Tapered Bore Bearing Non-interchangeable Clearance Unit: μm

Nominal bearing bore diameter d (mm)

Tapered bore bearing clearance (non-interchangeable) C9na C1na C2na Over Incl. min max min max min max 24 30 5 10 15 25 25 35 30 40 5 12 15 25 25 40 40 50 5 15 17 30 30 45 50 65 5 15 20 35 35 50 65 80 10 20 25 40 40 60 80 100 10 25 35 55 45 70 100 120 10 25 40 60 50 80 120 140 15 30 45 70 60 90 140 160 15 35 50 75 65 100 160 180 15 35 55 85 75 110 180 200 20 40 60 90 80 120 200 225 20 45 60 95 90 135 225 250 25 50 65 100 100 150 250 280 25 55 75 110 110 165 280 315 30 60 80 120 120 180 315 355 30 65 90 135 135 200

Preload and

Rigidity

29 Lubrication Lubrication 30

Technical Description

Lubrication

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

● Table 6.2 Bearing Internal Space V olume

1 Internal space volume of angular contact ball bearings and cylindrical roller bearings Unit: cc/each

Bore diameter number

Bore diameter (mm)

Series 7900C 7900AC

7000C

7000AC

7200C

7200AC BNH^

TA H

TBH NN3000^ NNU

2 Ball Screw Suppor t Bearings (T AB Series) Internal Space

Volume

Bearing No. Internal space volume [cc/ each] 15TAB04 3. 17TAB04 3. 20TAB04 3. 25TAB06 4. 30TAB06 4. 35TAB07 5. 40TAB07 5. 40TAB09 14 45TAB07 6. 45TAB10 15 50TAB10 16 55TAB10 16 55TAB12 19 60TAB12 19

3 Ball Screw Suppor t Bearings (T AF-X Series) Internal

Space V olume

Bearing No. Internal space volume [cc/ each] 25TAF05X 5. 25TAF06X 9. 30TAF07X 14 35TAF09X 26 40TAF09X 26 40TAF11X 44 45TAF10X 31 45TAF11X 44 50TAF11X 44 50TAF13X 70 60TAF13X 70 60TAF17X 149 80TAF17X 149 80TAF21X 285 100TAF21X 285 100TAF26X 488 120TAF26X 488

4 Ball Screw Suppor t Bearings (7001XYS1 Series) Internal

Space V olume

Bearing No. Internal space volume [cc/ each] 7000XYS1 0. 7001XYS1 0. 7002XYS1 1. 7003XYS1 1. 7004XYS1 2.

5 Ball Screw Suppor t Bearings (7200XYS1 Series) Internal

Space V olume

Bearing No. Internal space volume [cc/ each] 7203XYS1 2. 7204XYS1 4. 7205XYS1 5. 7206XYS1 7.

6.2.3 Grease Life

Grease life is af fected by operating temperature, grease type,

rotation speed, load, and other factors. Grease life approximate

estimates for a rolling contact bearing, which is used as a

representative example, can be calculated using Formula 5.1.

log L= −2.3 + 273 +T−0.301 ×(S G+S N+S W )

2450 ─ (Formula 5.1)

L : Grease life (hours) T : Bearing temperature (°C) S G : Life reduction factor based on grease type

Grease type S G

Long life petroleum grease and silicon grease 0 Conventional petroleum grease 1. Diester and and low temperature grease 2.

S N =0.

(dn )L

d・n

S N : Life reduction factor based on rotation speed d : Nominal bearing bore diameter (mm) n : Bearing speed (min -1^ ) (dn) L : Bearing type-specific speed facto

Bearing type (dn) L Angular contact ball bearings 400, Cylindrical roller bearings 200,

S W =2.714 C 2

n・d・w

S W : Load-specific life reduction facto C : Basic dynamic load rating (N) w : Bearing load (N)

Lubrication

31 Limiting Speeds Shaft and Housing Design 32

Technical Description

7.Limiting Speeds 8.Shaft and Housing Design

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

Using a bearing at high speed that exceed its limit

generates frictional heat inside the bearing, which can

cause temperatures to rise to levels that will not suppor t

bearing per formance. The limit on the empirical rotation

speed that avoids these problems is called the "Limiting

Speed".

The Limiting Speed depends on the bearing type,

dimensions, lubricating method, load, etc. The Limiting

Speed of a contact seal bearing is limited by the

circumferential speed of the contact sections of the seal

and raceway ring. The dimension tables in this catalog show

Limiting Speed for grease lubrication and oil lubrication,

but these values all assume light load, horizontal shaft

operation, and proper lubrication.

Though normally two or more pre-loaded angular contact

ball bearings are used, the rotation speed is limited in so it

is necessar y to multiply the speeds in the dimension tables

by the correction factors shown in T able 7.1.

When using a bearing at 75% or more of its Limiting

Speed, select the correct required grease type and amount

or the correct lubrication oil and method.

7-1 Limiting Speed Factors

● Table 7.1 Limiting Speed Factors for Multiple Row Ball Be aring Combinations No. of bearings in set E preload (extra-light preload) L preload (light preload) M preload (medium preload) H preload (heavy preload) 2 rows 0.83 0.78 0.63 0. 3 rows 0.73 0.68 0.54 0. 4 rows 0.78 0.73 0.59 0.

Appropriate inner ring and shaft fit, and outer ring and

housing fit is required in order to get the most pe formance

out of a bearing.

Loose fit su faces can result in rotation of the raceway rings

on the shaft or in the housing.

This is called "creep." When it occurs creep can cause

premature failure, vibration, and other trouble due to

abnormal heat and wear , from debris getting into the

bearing. An inter ference fit is a good way of preventing

creep. For convenient installation the inter ference fit in on

the inner ring and shaft or on the outer ring and housing

(not both).

However , this cannot be done under cer tain conditions

so bearing fitting needs to be determined after carefully

considering the relationship between the shaft and housing

and other factors.

Recommended fits for general operating conditions (inner

ring rotation) of precision bearings used for machine tools

are shown in T ables 8.1 through 8.3.

8-1 Shaft and Housing Fits

● Table 8.1 Shafts and Recommended Fits (^) Unit: μm

Bearing type

Shaft diameter (mm)

Bearing accuracy class Class 5 Class 4/Class 2 Over Incl. Desired fit Shaft tolerance Desired fit Shaft tolerance

Angular contact ball bearings

10 18 0~2T h4 0~2T h 18 50 0~2.5T h4 0~2.5T h 50 80 0~3T h4 0~3T h 80 150 0~4T js4 0~4T js 150 200 0~5T js4 0~5T js

Cylindrical roller bearings (cylindrical bore)

25 40 − js4 − js 40 140 − k4 − k 140 200 − k4 − k Main spindle thrust bearing For all shaft diameters^ 0~6L^ h4^ 0~6L^ h Ball screw support bearings For all shaft diameters^ 0~10L^ h5^ 0~10L^ h

● Table 8.2 Housings and Recommended Fits (Fixed Side) (^) Unit: μm

Bearing type

Housing bore diameter (mm)

Bearing accuracy class Class 5 Class 4/Class 2 Over Incl. Desired fit Housing bore tolerance Desired fit Housing bore tolerance

Angular contact ball bearings

18 50 0~3L JS4 0~3L JS

50 120 0~4L JS4 0~4L JS

120 180 0~5L JS4 0~5L JS

180 250 0~6L JS4 0~6L JS

Cylindrical roller bearings Overall housing bore ± 0 K5 ± 0 K Main spindle thrust bearing Overall housing bore^ 30L~40L^ K5^ 30L~40L^ K Ball screw support bearings Overall housing bore^ 10L~20L^ H6^ 10L~20L^ H

● Table 8.3 Housings and Recommended Fits (Free Side) (^) Unit: μm

Bearing type

Housing bore diameter (mm)

Bearing accuracy class Class 5 Class 4/Class 2 Over Incl. Desired fit Housing bore tolerance Desired fit Housing bore tolerance

Angular contact ball bearings

18 50 6L~10L H4 6L~10L H

50 120 8L~13L H4 8L~13L H

120 180 12L~18L H4 12L~18L H

180 250 15L~22L H4 15L~22L H

Cylindrical roller bearings Overall housing bore ± 0 K5 ± 0 K Ball screw support bearings Overall housing bore^ 10L~20L^ H6^ 10L~20L^ H (Note) In T ables 8.1 through 8.3, "L" following a value indicates loose or clearance fit, while "T" indicates tight or inte ference fit

Limiting Speeds

Shaft and

Housing Design

35 Bearing Handling Bearing Handling 36

Technical Description

9.Bearing Handling

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

Rolling contact bearings are precision components. It is

impor tant to handle them with care to avoid damage due to

impact. Rolling contact bearings also are susceptible to dir t and

rust, so care is required during storage and transpor t.

● When storing bearings, select a cool, dr y location that is

not exposed to direct sunlight or humidity.

● Do not leave bearings on the floo. Store them at a height

of at least 30 cm, and avoid exposure to dust.

● First-in, first-out storage should always be used for bearing

inventor y management. Arrange bearings so those with the

oldest packing date can be used first

● Take care bearings being transpor ted are not crushed or

dropped, etc., protect them from damage and deformation

due to impact, and ensure they do not become soiled due

to broken packing materials.

Press fits

W ith this method, a tool is placed on the inner ring side sur face

and a jack or press is used to press fit (Figure 9.4). When

press fitting the inner ring on a shaft do not apply force to

the outer ring or cage. In the case of an angular contact ball

bearing, application of force in the opposite direction of the

contact angle direction should be avoided because it will damage

the raceway shoulder (Figure 9.5).

Figure 9.4 Inner Ring Press Fitting

Risk of ball damage

Figure 9.5 Angular Contact Ball Bearing Assembly Direction

Reference: Maximum radial run-out locations

The maximum radial run-out locations of the inner ring and

outer ring are indicated by " ○" marks on the ring face. Axial

run-out can be minimized by aligning the minimum radial run-out

location of the axis with the " ○" mark on the inner ring. The

outer ring also should be assembled so its " ○" mark is aligned

with the minimum run-out locations of the housing.

Note that there is no relationship between the outside ring

"○" mark position and the outside diameter " <" mounting mark

position.

Maximum radial run-out surface

Figure 9.6 Maximum Radial Run-out Locations

Reference: Press fit force and removal force

Though the force required to press fit a bearing inner ring

to and removing it from the shaft depends on inter ference

amounts and the shaft sur face finish, general values can be

obtained using Formula 9.1.

Ka=fk・Δde・B・{ 1 (− )

2

di^ }

d ─ (Formula 9.1)

Ka : Press fit force (removal force) (kN fk : Installation/removal condition coefficient ( able 9.1) Δde : Effective inter ference (mm) B : Nominal inner ring width (mm) d : Nominal bearing bore diameter (mm) di : Inner ring mean outside diameter (mm) Cylindrical roller bearing di=(D+3d)/ Other bearings di=(3D+7d)/ Here, D = Nominal bearing outside diameter (mm)

● Table 9.1 Installation/Removal Condition Coefficien Conditions fk (mean value) Inner ring press fit to cylindrical solid shaft 39 Inner ring removal from cylindrical solid shaft 59 (Note) V alues when shaft bore and shaft are thinly coated with oil.

The quality of bearing installation influences precision, se vice

life, per formance, and other factors, so care is required. The

following is the procedure for assembly work.

① Shaft and housing inspection

② Unpacking and cleaning

③ Assembly

④ Post assembly check

9.2.1 Shaft and Housing Inspection

● Clean the shaft and housing thoroughly and remove any dir t

and debris. Also, confirm there are no burrs

● Confirm that the shaft and housing are finished i

accordance with the drawings, and check and record

dimensions, shoulder squareness, and the corner radius.

As shown in Figure 9.1, measure the shaft diameter and

housing bore at two locations in the axial direction and four

locations radially.

A B

A B

Figure 9.1 Shaft Diameter and Housing Diameter Measurement Locations

9.2.2 Unpacking and Cleaning

● Do not unpack a bearing until just before you are ready

to use it. Be sure to wear vinyl gloves when unpacking a

bearing. Unpacking a bearing with bear hands or while

wearing fabric gloves creates the risk of rust or lint

intrusion.

● Apply anti-rust oil to the sur face of the unpacked bearing.

Wash the bearing with white kerosene. For washing,

prepare either a filtered shower or two containers with

raised wire mesh bottoms, one for basic washing and one

for finish washing

● After washing, shake the oil from the bearing and then

cover it. Do not rotate a bearing that has been degreased.

9.2.3 Mounting

Generally the majority of bearings assembled into machine tools

use inter ference shaft fits and loose housings fits. The method

used for mounting bearings to shafts are the shrink and press

fits

Shrink fits

W ith this mounting method, the bearing is heated until it

expands larger than the shaft and the inner ring can be slipped

onto the shaft.

An electromagnetic heater with degausser (Figure 9.2) avoids

undue stress to the inner ring, while an oven helps to shor ten

process time.

Heating temperature must be no greater than 120°C.

Temperatures greater than 120°C can decrease bearing

hardness and shor tens its ser vice life.

After a heated bearing is installed on a shaft, it contracts axially

as it cools, which can cause a gap between the inner ring and

shaft shoulder (Figure 9.3), so positioning is achieved using a

nut, etc.

Figure 9.2 Induction Heater

Figure 9.3 Shaft Shoulder Gap After Cooling

9-1 Storing and Transporting Bearings

9-2 Bearing Installation

Handling Bearing

37 Bearing Handling Bearing Handling 38

Technical Description

Bearing Handling

Bearing Selection

Bearing Life

ToleranceBearing

Bearing

Arrangement

Preload and

Rigidity

Lubrication

Limiting Speeds

Shaft and

Housing Design

HandlingBearing

Mounting on a shaft

Normally a shaft nut is used to secure the inner ring of the

bearing to the shaft.

It is necessar y to ensure that the shaft nut side sur face is at

the proper angle relative to the thread. If the sur faces are not

square tightening of the shaft nut can result in bending of the

shaft.

Also, adjustment of the shaft nut is required when tightening

it because of edge contact due to a gap in the mating sur face

between the shaft nut and the shaft.

Tightening with the shaft nut makes it possible to apply a

specific tightening force by controlling the tightening torque.

Though there is a discrepancy in the relationship between

shaft nut tightening torque and the tightening force due to the

accuracy and roughness of each threaded por tion, it can be

expressed as Formula 9.2.

The recommended mounting force for each bearing bore is

shown in T able 9.2.

F≈

Mn

─ (Formula 9.2)

tan(β+ρ)+ ・mμ

d 2

d n

F : Tightening force (N) Mn : Tightening torque (N·mm) d 2 : Thread nominal diameter (mm) β : Lead angle tan β = P πd 2 P : Pitch (mm) ρ : Thread sur face friction angle tan ρ = (^) cosμ α α : Half-angle of thread d n : Mean diameter of nut bearing sur face (mm)

μm : Coefficient of friction of nut bearing sur face ( ≈0.15)

μ : Coefficient of friction of thread sur face ( ≈0.15)

● Table 9.2 Recommended Shaft Nut T ightening Force V alues Nominal bearing bore diameter (mm)

Shaft nut tightening force (N)

Nominal bearing bore diameter (mm)

Shaft nut tightening force (N) 10 1,500 80 19, 12 2,500 85 19, 15 2,500 90 19, 17 2,500 95 19, 20 4,900 100 19, 25 4,900 105 19, 30 4,900 110 19, 35 4,900 120 19, 40 9,800 130 19, 45 9,800 140 29, 50 9,800 150 29, 55 14,700 160 29, 60 14,700 170 29, 65 14,700 180 29, 70 14,700 190 29, 75 14,700 200 29,

Mounting on a housing

In order to secure the outer ring of a bearing in the axial

direction, clearing normally is maintained between the press-fit

cover and housing and a bolt is used for tightening. Caution is

required because outer ring misalignment and deformation can

occur bolts are not tightened correctly or uniformly (Figure 9.7).

Generally an Outer Ring Clearance Reduction Gap D of 0.010 to

0.020 is recommended. Recommended Clearance Reduction

Gap V alues for a face-to-face ball suppor t bearing (T AB Series,

TAF-X Series) are shown in T ables 9.3 and 9.4.

Housing

2A clearance

Press-fit cover A A

Δ+ 2A

Δ=0.010mm Δ=0.050mm Figure 9.7 Example of Raceway Deflection Depending on Outer Ring Clearance Reduction Gap

● Table 9.3 Recommended Clearance Reduction Gap V alues for Ball Screw Suppor t Bearings (T AB Series) Bearing No. (^) External ring clearance reduction gap Δ (mm) 15TAB04 DF 17TAB04 DF 0.010 ~ 0. 20TAB04 DF 25TAB06 DF 0.010 ~ 0.

30TAB06 DF

35TAB07 DF

40TAB07 DF

40TAB09 DF

45TAB07 DF

45TAB10 DF

50TAB10 DF

55TAB10 DF

55TAB12 DF

60TAB12 DF 0.020 ~ 0.

● Table 9.4 Recommended Clearance Reduction Gap V alues for Ball Screw Suppor t Bearings (T AF-X Series) Bearing No. External ring clearance reduction gap Δ (mm) 25TAF06X DF 0. 30TAF07X DF 35TAF09X DF 0. 40TAF09X DF 40TAF11X DF

45TAF11X DF

50TAF11X DF

60TAF13X DF

60TAF17X DF

80TAF17X DF 0.

100TAF21X DF

120TAF03X DF

Tapered bore cylindrical roller bearing clearance adjustment

The internal clearance of a tapered bore cylindrical roller

bearing can be adjusted by the spacer width using the

procedure below.

① Check the shaft taper. Coat the taper with a thin layer of

bluing; 80% or more contact is required.

② Lightly place the inner sub-unit onto the shaft taper

(Figure 9.8).

③ Place the outer ring and fix the shaft horizontall.

④ Touch the center the outer ring with a dual gauge probe.

⑤ Pressing down on the outer ring from above, rotate it left

and right a few times so it fits well, and then zero set the dial

gauge.

⑥ Push the outer ring straight up 180° from its position of

symmetr y (directly below), and rotate it slightly left and right

to take a reading of its maximum value (Figure 9.9).

⑦ Change the position of the shaft at steps of approximately

30°, measure the axial displacement, and calculate the

average of the readings as the value of D R.

⑧ Use a block gauge to measure the length to the inner ring

edges sur face and shaft shoulder (Figure 9.10).

⑨ Change the position and use the average of five or six

locations as the value for L'.

⑩ Use Formula 9.3 to determine the wide dimension of the

required spacer.

L=L ’− 12 (ΔR−Δ−λe・δ)──^ (Formula 9.3)

L’ : Average spacer width obtained in step ⑨ ΔR : Measured radial clearance Δ : Desired post-assembly radial clearance λe : External ring contraction ratio

λe (^) = DeD − 1 −( (^) DD^ eh ) 2

1 −( (^) DD h ) 2

D : Inner ring outside diameter (mm) D e : Inner ring bore (mm) D h : Housing bore (mm) δ : Outer ring inter ference

⑪ Correct the spacer width dimension.

⑫ Remove the inner sub-unit from the shaft. This time avoid

striking the inner ring with strong force. Use of a special

removal tool to make ring removal easy.

⑬ Install the spacer and bearing onto the shaft.

⑭ Again, measure the radial clearance and confirm that the

desired radial clearance is provided (Figure 9.11).

9.2.4 Post Assembly Check

Use the procedure under "5-3 Measuring Preload" (P. 17) to

confirm that the prescribed preload is being applied

Figure 9.8 Inner Sub-unit T emporar y T ightening

Figure 9.9 Radial Clearance Measurement

Figure 9.10 Spacer T emporar y W idth Dimension Measurement

Block gauge

Figure 9.11 Final Assembly Radial Clearance Check

HandlingBearing