Drive shafts for steel production/industrial equipment

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CAT.NO.UA002EN-1MY,,
Printed in Japan 23.03（ 16.1）

CAT.NO.UA002EN-1MY

CONTENTS

Drive shafts for steel production/industrial equipment■ Drive shaft overview and configuration■ Composition of drive shaft numbers

03
05■ Measures to improve service life and strength
Application of different diameter rollers for cross & bearing 06

Preface

Ball burnishing on cross shaft

Throughout the manufacturing industry the pursuit of greater power output at higher efficiency is a priority. Under such circumstances, highly sophisticated and economical drive
shafts that fit in a limited space are in great demand for use in various equipment andmachines.
Drive shaft lineup is certain to satisfy your requirements in various applications, including
iron manufacturing machines, rolling mills, construction machines, and rolling stock.
We thank you in advance for your support of our drive shafts.

06

Thermal spraying coat of tungsten carbide (WC) on bearing cup key 07
Application of form rolling to bearing set bolt

07

Development of a high-sealing oil seal08

■ Maintenance and inspection method of drive shaft■ Cases of failures09
11■ Technical data

General characteristics of universal joint

13

Drive shaft selection

15

Balance quality of drive shaft

17

Torque wrench set for bolt tightening18■ Specifications
D series

19

U series

21

T series

23■ Product introduction
Drive shaft with roll phase adjustment device for bar and rod mill 25
Hyper coupling27■ Attached tables
Recommended tightening torque for flange bolts

31

Shape and dimensions of parallel key and keyway (JIS B 1301) 32■ Drive shaft selection sheet■ Hyper coupling selection sheet

33
34

U series
D series
T series

01

02

Drive shaft overview and configuration
Drive shaft configuration
Functions
Bearing set bolts

A drive shaft is a revolving shaft used to transmit thepower of a motor to a machine.

Cross & bearing

Since it is installed in a limited space, the axes are

Retainer washers
Weld yoke
Spline sleeve

Bearing cup
Thrust washer

Yoke

Rollers
Roller guideseldom aligned.

Oil seal

However, by using a universal joint, the input axis and the

SlingerCross

output axis can be flexibly connected even in a limited

Yoke

space, enabling smooth torque transmission.

Retainer ring

Felt seal

Fitting yoke
(Oval bore yoke)

Each universal joint has four rolling bearings (cross &bearing), realizing low friction and minimizing torquelosses.

Fitting yoke
(Cylindricalbore yoke)
Cross & bearing
Weld yoke
Propeller tube

Universal joint(Cross-type universal joint)

Spline shaft

Features(1) Used forextra-heavy duty
applications.
(2) High dust
resistance makesthese series
optimal for use
under severe
operatingconditions suchas in rolling mills.

Characteristics(1) Swing diameter(mm) :
160 - 1230
(2) Torque(kN・m) :10.9 - 8970
(3) Torque(kN・m) :34.1 - 18800(4) Maximum operating
angle ( °) : 4 - 15

・ refers to the reference torque used as the criterion
for evaluation of resistance to the maximum torqueunder normal operating conditions.
・ refers to the reference torque used as the criterion
for evaluation of resistance to the breaking torqueunder emergency conditions.

Configuration of parts
1) Cross & bearings
The cross & bearings are the most criticalcomponents of a drive shaft.
A cross & bearing has a cross-shaped shaft andfour rolling bearings that individually support eachend of the shaft.
2) Bearing set bolt
Used to connect the cross & bearing and its
mating part.
3) Spline sleeve/shaft
There are a spline hole and shaft and the attaching
length is adjustable.
4) Spline cover
Used to improve the dustproof and waterproof
properties if the ambient environment is not good.
5) Flange yoke
The flange yoke is commonly used to connect a drive unit

5) Flange yoke

2) Bearing set bolt

(such as a motor). A variety of joints are available to suitspecifically desired applications.

1) Cross & bearing4) Spline cover6) Fitting yoke
Used mainly for connection with the machine and the motor.

6) Fitting yoke3) Spline sleeve/shaft

Various types of coupling arrangements are provided according to the application.

03

04

Composition of drive shaft numbers

Measures to improve service life and strength

Below are optional specifications for use under severe conditions in which further strength and/or longer life are required.

Model No.

5 6

1 0 0

1 2 3

4

C M
Fitting code

Configuration code
Design serial No.
Swing diameter No.
BRG No.

*When model numbers are different
on the right and left

T60120 D56100(Model No.)

(Model No.)

Series code

234
Design serialNo.

The two model numbers are
written side by side
If the rotation diameters are thesame, the model numbers are
written in order of T, D, and U
If the rotation diameters aredifferent, the model number
with larger rotation diameter iswritten first

U : U series

Cross
Effect of rollers different in diameter

Load
distribution

T : T series

Ceramic ballWork piece rotation■ Configuration code : Decided according to the configuration of the drive shaft■ Fitting code : The following shape codes are added to the left, then to the right, according to the shape of the attaching parts at both ends.

Hardness, HV

B : Cross & bearing

T : Tapered bore

1.4-fold(1) The hardness of the surface becomes higher than that of the carburized original material.
(2) Residual compressive stress at subsurface is larger than in the case of carburizing, and it can be applied deeply.
(3) Raceway roughness of the machined surface is improved. And no further finishing process is required after ball burnishing process.
(4) As the ball burnishing fixture can be used by attaching to lathe or other machine, there is actually no limitation in size of workpieces.

■ Design serial No. : Represented in three digits for each model number (001 - 999)

M : Oval bore

Conventional type

Approx.

■ Swing diameter No. : The value is swing diameter of cross & bearing / 5 and is represented in three digits (e.g.: φ450 ㎜ → 090, φ900 ㎜ → 180)

F : Flange【Improved flaking life】

Equal loads

Feeding
Liquid pressure■ BRG. No. : The raceway diameters of the cross are represented in two digits in order of size (e.g.: 56, 63)

C : Cylindrical bore

(Torque load)

Load
distribution

The flaking life can be improved by the ball burnishing on cross raceway. This process is a type of plastic working process, which
is applied by rolling contact of super-hard ball backed up hydraulically on the cross raceway surface.

Supplementary explanation of items
D : D series

Unequal loads

Ball burnishing on cross shaft

Features■ Series code

Bearing cup
Rollers

Because the cross is an elastic cantilever beam and the bearing has someradial clearance, the load on the crossgenerally becomes heavier toward to
the end of the cross.
In order to improve this phenomenon,load on the roller is made uniform bydesigning the roller to have a minutely
smaller diameter at the very close end,
which would improve flaking life.
(figure on the right).
It is required that the detailed investigation takes into account multitude of
JTEKT records and the technology oftheoretical analysis by FEM, when thiswould be applied.
(Rollers with different diameters can beused in a three-row structure.)

Ball burnishedAs carburized

Residual compressive stress, MPa

D

Application of different diameter rollers for cross & bearing

Ball burnishedAs carburized
Depth from the surface, μm
Measurement result of residual compressive stress【Improved flaking life】
Conventional type

Depth from the surface, μm

Approx.

1.7-fold

Measurement result of hardness

05

06

Measures to improve service life and strength
Development of a high-sealing oil seal
Thermal spraying coat of tungsten
carbide (WC) on bearing cup key

Operating environment

Movement of oil seal during operation

Rolling mill water＋
Scale

Rotational oscillating motion＋
Axial oscillating motion

Permanent elongation of each lip portion(residual deformation)

Low sealing performance of the side lips

To avoid corrosion on the side face of bearing cup key applying carburizing heat treatment, one possible method is to apply
thermal spraying coat of tungsten carbide (WC) on these surfaces.

Bearing cup (carburized steel)
Reduction in oil seal sealing performance(

Yoke(Quenched and tempered)Effects

Without WC coat
Corrosion wear after
13 months use)(

WC coated productNo corrosion wear after
20 months use)

Effect of thermal spraying coat of tungsten carbide (WC)The following effects are expected in case the generation ofclearance due to corrosion at the key area is restrained.
(1) The bending stress of bolt can be alleviated, which leads to
the restraint of strength reduction.
(2) The heavier load on raceways at the end of the cross can be
restrained, which expects longer fatigue life for cross & bearing.

1 Improved sealing performance through material change

Features・By changing from nitrile rubber to high nitrile rubber,permanent elongation under rolling mill water and hightemperature (90°C) environment is reduced by 50%
compared to conventional products.

【Improved corrosion resistance】
Conventional type

Approx.

1.5-fold50

The thread of the bearing set bolt has conventionally been machined
after heat treatment. However, by switching this process to form
rolling, allowable fatigue stress at the bottom radii of the threadincreases significantly.
Features

Permanent elongation ratio

Conventional product(Machined)

Developed product(Rolled)(Actual product)(1) Fiber flow is formed along the shape of the thread.
(figure on the right)(2) Residual compressive stress at subsurface beneath thebottom radius of the thread increases. (figure below)

1.0％

reduction

0.8
0.6
0.4
0.2
0

Conventional
products

Developed
products

2 Improved sealing performance through shape change

・By changing from side lip seal thrust contact to radialcontact, sealing performance relative to axial
oscillating motion has improved
・Reduced decline in lip tension by 80% compared toconventional
・Reduced intrusion of rolling mill water by 80%
compared to conventional products②【Confirmation of lip tension】①【Confirmation of permanent elongation】
1.2

Application of form rolling to bearing set bolt

2 Shape changes

1 Material change

1.2
1.0

80

％

reduction

0.8
0.6
0.4
0.2
0

③【Confirmation of sealing performance】
Water content ratio after bench test

WC thermal spraying coated(bearing cup side)
SUS welding(yoke side)

Tension reduction ratio after bench test

Bearing set bolt

1.2
1.0

80

％

reduction

0.8
0.6
0.4
0.2
0

Conventional Developed
products
products

Conventional Developed
products
products

These changes suppress sudden damage to the cross bearing caused by deterioration in lubricating ability,
thus contributing to reduced maintenance costs and improved productivity for customers.

Depth from the surface, μm

Residual compressive stress, MPa

Bearing cup
Roller guide

Fiber flow of rolled thread

Oil seal

Rolled thread
Machined thread

Slinger【Improved fatigue strength】

Cross
Conventional type

Approx.

1.9-foldRollers
Thrust washer

Residual compressive stress distribution of rolled thread

07

08

Maintenance and inspection method of drive shaft

To use drive shafts safely for a long time, periodic inspection is required. Below is the periodic inspection procedure.
We can repair JTEKT products with a swing diameter of 500 mm or more as a guide. Please do not hesitate to contact JTEKT if you needmore information.
<Examples of repair>- Repair by grinding of raceway surfaces of cross and bearing cup- Repair by overlay welding of yoke key way and oval bore
- Repair of slight wear and removal of rust

Overhaul■ As a rule, conduct overhaul of the major parts every year after the start of operation.
■ Cross & bearing- Check for brinelling, wear, flaking, seizure, cracks, nicks, or rusting, etc. of the cross and the bearing cup.

Bearing cup

Periodic inspection
Checks(1) Greasing

Thrust washer

The greasing amount varies depending on the sizes of the cross & bearing and spline part.
Apply the amount of grease specified by JTEKT.
■ Greasing positions
Apply grease in the positions shown in the figure below.

①Cross & bearing②Spline partRollers
Roller guide①Cross & bearing(bearing cup part or cross body)

Checks

Cross

Oil seal

Bearing cup

Cross
Slinger
Bearing set bolts■ Bearing set bolt
■ Cycles of periodic greasing- Hot strip mills: Once a month- Cold strip mills: Once a month- Others: Every 3 months

Check(2) Tightening torque of bolts

Check

The tightening torque of bolts is set according to the bolt size.
If the bolts are not tightened with the proper tightening torque, it may lead to their early damage.
Refer to the tightening torque of the bolts specified in the drawing.
In addition, a dimension table of torque wrenches is provided on page 18.
To crane■ Periodic inspection of bolts
Conduct initial inspection of the bolts one week and one month after
operation.
After that, conduct periodic inspection every six months.
Inspection of the bolts includes the following.
- Check for looseness or damage of the whirl-stop- Check the elongation by hammering or looking

Yoke- Check for bending, looseness, cracks, or rusting of the bolt.

＊Be sure to apply grease with correct intervals and amount.
The grease to be applied should be the one specified in the drawing.
Use of insufficient or different grease may lead to early damage.

■ Yoke- Check for cracks, nicks, or rusting, etc. of each part.
- Especially, check the cross & bearing attaching part and the flange

Tensiometer

Check
Checksattaching part for signs of the above.
■ Others- Check for wear, scuffing, or cracking, etc. of the oval bore and spline.

Check＊Consult with JTEKT about the inspection result.

Wrench＊The next page shows some examples of failures of each part.

Reaction
receiver

Whirl-stop with one bolt

■ How to loosen/tighten the bolts of the cross & bearing(1) As shown in the figure on the right, tighten the drive shaft witha jig such as chain tongs.
(2) Before tightening, apply a small amount of grease to the thread
section and the head seat of the bolt.
(3) Tighten to the specified torque by using a wrench, tensiometer, etc.

09

Management/storage

Whirl-stop with three bolts
Chain tongs■ When storing the product for a long period of time, take measures to prevent rusting.
■ Before using a product stored for a long period of time, reapply grease to the cross & bearing, spline, etc.

10Cases of failures

Here are some examples of failure cases of drive shaft parts.

(3) Excessive load

⑧

⑨

⑥

①

②

⑤、⑦

(1) Insufficient greasing① Flaking of crossraceway surface<Part>
Cross<Cause>- Flaking occurred at the bottom of the crossdue to insufficient lubrication<Measure>- Periodic greasing<Treatment>- Repair by re-grinding

11② Flaking of bearing cup
raceway surface<Part>
Bearing cup<Cause>- Flaking occurred on the bearing cup inlet
side due to insufficient lubrication<Measure>- Periodic greasing<Treatment>- Repair by re-grinding③、④④ Breakage of bolt

<Part>
Bearing set bolt
<Cause>- An excessive bending stress acted on the
bolt<Measures>- Review the usage conditions- Apply an appropriate load
- Reduce the bending stress acting on thebolt<Treatment>- Replace with a new part

<Part>
Bearing set bolt
<Cause>- Flat fracture shape because the axial force
did not act on the bolt
<Measures>- Tighten with the proper tightening torque- Maintenance of the attaching surfaces of
the cup and yoke
<Treatment>- Replace with a new part

⑥ Dent deformation of key<Part>
Cross<Cause>- An excessive load acted on the raceway
surface<Measures>- Review the usage conditions- Apply an appropriate load
<Treatment>- Repair by re-grinding<Part>
Yoke key way<Cause>- An excessive load acted on the key way<Measures>- Review the usage conditions- Apply an appropriate load
<Treatment>- Repair by weld overlaying(4) Life(2) Insufficient tightening torque③ Breakage of bolt

⑤ Brinelling on
raceway surface⑦ Flaking of raceway
surface<Part>
Cross<Cause>- Flaking occurred at the cross end due tolong-term use<Treatment>- Repair by re-grinding- Replace with a new part

⑧ Spline wear

<Part>
Spline sleeve<Cause>- Wear of the torque transmission surface
due to long-term use<Treatment>- Reusable in the case of slight wear
- Replace with a new part in the case ofserious wear
(Repair by weld overlaying is impossible)⑨ Oval bore wear

<Part>
Oval bore yoke
<Causes>- Doglegged surface pressure- Clearance of the torque transmission
surface- Wear of the torque transmission surface
due to long-term use<Treatment>-Repair by weld overlaying

12Technical data (1)Double universal joints

General characteristics of universal joint (Cross-type universal joint)

Universal joints are usually installed in pairs. When assembled as shown in Fig. 4, that is,(1) With equal operating angles in both joints

Single universal joints(2) Yokes connected to the same shaft in line
(3) Central lines of all three shafts (driving shaft, intermediate

Driven shaft

The driving shaft and driven shaft intermediated by a universal
joint has the following relationship between their rotational
angles:

tan
where

cos

shaft, and driven shaft) in the same plane, the driven shaft
rotates exactly in the same way as the driving shaft.

Shaft
operating angleθ

Therefore, they should be attached as shown in the figure on

…(1)

tan

the right as far as possible.

: Rotational angle of driving shaft: Rotational angle of driven shaft: Shaft operating angle (Fig. 1)

This means that, even if the rotational speed and torque of thedriving shaft are constant, the driven shaft is subject to fluctu-

Fig. 1 Single universal joint

ation in rotational speed and torque.

Fig. 4 Installation of double universal joints

Driving shaft

The speed ratio between the driving shaft and driven shaft can beobtained by differentiating equation (1) with respect to time ( t ),
·

and

by

cos
1-sin2
where

sin2

·

Secondary couple:…(2)
It is often necessary to consider the secondary couples: Rotational angular velocity of driving shaft (rad/s): Rotational angular velocity of driven shaft (rad/s): Angular velocity ratio

Equation (2) can be expressed in diagram form as shown in
Fig. 2. The maximum value and minimum value of the angularvelocity ratio can be expressed as follows:

1 / cos
cos

max.
min.

imposed by universal joints operating at an angle;
especially under high angle or large torque.

min.

cos

planes of the yoke. These couples are about the intersection of the shaft axis. They impose a load on the bearings
and a bending stress in the shaft connecting the joints,
and they fluctuate from maximum to zero every 90° of
shaft revolution. The broken lines in Fig. 5 indicate theeffect of these secondary couples on the shafts andRotation angle of driving shaft
Fig. 2 Angular velocity fluctuation

The equation for maximum secondary couple is asfollows:

cos

max.
max.

minimum value can be obtained as shown below, respectively:: Input torque: Output torque: Torque ratio

where

0°
90°

tan
sin

(for driving shaft)

Drivenshaft(for driven shaft): Secondary couple on driving shaft (N･m): Secondary couple on driven shaft (N･m): Driving torque (N･m)

Torque ratio

where: Shaft operating angle
The ratio of the secondary couple to the driving torque isshown in Fig. 6.

Rotation angle of driving shaft
Fig. 3 Torque fluctuation

13

Maximum secondary couple is producedon the driving side yoke and the driven side yoke alternately
at every rotation of 90°
Fig. 5 Effect of secondary couple

bearings.

by the diagram shown in Fig. 3. The maximum value and

cos
cos

Direction of
secondary couple

Rotated 90°

The secondary couples in the universal joints are in the

The torque ratio between input and output can be expressed

max.
min.

Directionof torqueThese

shafts and supporting bearings.

The maximum fluctuation rate of angular velocity in a universal

max.

Direction of
secondary couple

couples must be taken into account in designing the

90°0°

joint can be expressed by the following equation:

Directionof torque

The secondary coupleandmultiplying

by the driving torqueor

can be obtained by.

Ratio of secondary couple

is byAngular velocity ratio

where

Drivingshaft

Rotation angle of driving shaft
Fig. 6 Fluctuation of secondary couple to driving torque14

Technical data (2)Drive shaft selection
A drive shaft should be selected so as to satisfy the required strength, service life, operating angle and dimensions necessitated by its purpose.
Especially, a drive shaft can be selected if it meets conditions of both strength and life of cross & bearings, except for special cases.

Load torque of drive shaft

Strength of drive shaft

Critical number of rotation

To decide the size of the drive shaft, it is necessary to grasp

A drive shaft should be selected so that the normal maximum

When the rotation speed approaches the critical number of rotations of a drive shaft (bending natural frequency), the powertrain

the load torque first.

torque shall not exceed the "may be affected by resonance, and thus when a drive shaft is designed, the rotational flexural rigidity of the drive shaft needs toA maximum torque including an impact torque and a mean

to determine the true maximum torque, and the engine capacity

be considered.

torque should be known, and it is essential for selecting an

or motor capacity is used as the maximum torque in many cases.

If you need to increase the rotation speed through equipment alteration etc., please contact JTEKT.

appropriate drive shaft to understand the correct maximum

In consideration of the torque amplification factor (TAF) of thetorque and mean torque.

drive shaft and various imponderables, the safety factor (torque." However, it is difficult) ofno less than 1.5 should be considered as the most desirable.
Maximum torque:
Value to determine if the strength of each part is sufficient.
Mean torque:
Value necessary to calculate the service life=

/maximum torque under normal operating conditions > 1.5

Evaluation/analysis

To obtain the load torque of a drive shaft, there is a method to

JTEKT conducts FEM analysis as one of the evaluation/analy-

calculate the torque from the motor output. The following is

sis approaches to utilize for selection of a drive shaft.

The maximum torque that may occur in an emergency should bedetermined using "torque." The safety factor () of no lessthan 1.5 should be considered as desirable in this case as well.

=/breaking torque under emergency conditions > 1.5

To select a drive shaft based on a safety factor of 1.5 or less,

Mean torque

Torque calculation from motor output

consult JTEKT as close examination is required in considerationof previous performance records.

the calculation equation.
Horsepower → Torque (N･m)

HP･7122 (N･m) ……(1)
T＝N

However, in the case of PS (CV in French) horsepower,
the following equation is applied.

It is apparent that all kinds of machines are not operating
thoroughly by their maximum torque. Therefore, if a driveLife of drive shaft

shaft is selected according to a service life calculated fromthe maximum torque, it results in being uneconomically larger
than necessary.
So, it is reasonable to set up a longer expected service life, if
the application condition are severe; and shorter, if the conditions are easy.
If, for instance, a job is expressed as in the table below,
Drive stage
TorqueThere is no global standard for the method of calculating the service
life of cross & bearings, and this method is based on the results ofresearch performed by each manufacturer.
JTEKT employs the following empirical equation based on
extensive experimentation (conforming to SAE).
The service life
is defined as the expected number of operating
hours before a flaking occurs on the rolling contact surface of the
bearing. The use of the bearings over the service life
may bepractical on a low speed machine such as a rolling mill.

Rotational
speedTime ratio

Where,

the cube root of mean torque (rotational speed () and the arithmetical mean of) are yielded from the following equations.

: Average calculated bearing life (h)PS･7024 (N･m) ……(2)T＝NNote) Check if the horsepower specified in the drawing
provided means HP horsepower or PS horsepower.

kW → Torque (N･m)kW･9552 (N･m) ……(3)T＝N
In equations (1) to (3) above,

T : Torque (N･m)
N : Rotational speed (min-1)
HP : Horsepower(English horsepower)

PS : Horsepower(French horse power)

kW : Kilowatt
Example of FEM analysis: Material factor = 1 to 3
: Rated torque (N･m): Mean torque (N･m): Speed factor = 10.2/: Angle factor = 1.46/: Rotational speed = (min-1): Shaft operating angle (°)Note) A drive shaft should be selected by considering thetype of the machine, peripheral equipment, particular
operating conditions, and other factors. The method
outlined in this catalog is a common rough guide. It is
recommended to consult JTEKT for details.

15

16

Technical data (3)Balance quality of drive shaft

Torque wrench set for bolt tightening

If a rotating drive shaft is unbalanced, it may adversely influence the equipment and ambient conditions, thus posing a problem.

JTEKT provides torque wrench sets suitable for bolt tightening of the drive shaft.

JTEKT designs and manufactures drive shafts to satisfy the balance quality requirements specified in JIS B 0905.

The following are torque wrenches and related tools and their specifications. For details, contact JTEKT.

Expression of balance quality

Balance quality grades

The balance quality is expressed by the following equation:

The JIS specifies the balance quality grades from G0.4 toG4000. Generally, the three grades described in Table 1
below are commonly used.
We apply grade G16 to high speed drive shafts unlessotherwise specified.

Balance quality =orBalance quality =
where

/9.55

Torque wrench

TensiometerL(Effective length)

No.
TM500

L

: Amount of specific unbalance (mm)of a rigid rotor by the rotor mass. The amount isequal to the deviation of the center of the rotor(kN)
5

TM100010TM200020TM300030(Effective length)

Correction of the unbalance of drive shaftsThis amount is the quotient of the static unbalance

Weighing

JTEKT corrects the unbalance of drive shafts to the optimalmass from the center line of the shaft.

value by the two plane balancing method, using the latest: Maximum service angular velocity of the rotor (rad/s)balance system.

: Rotational speed (min-1)

To correct the balance of a drive shaft, it is critical to correct
the balance between two planes each near the two individual universal joints, instead of by the one plane balancing as
used to balance car wheels.

No.

L (mm)

TW4200750

TW8500Scale range (same on the right and left) Minimum scale
(N・m)

(N・m)

1310

100〜85020

TW280001240

300〜2800

50

TW42000

1400

400〜4200

100

70〜42010Especially in the case of a long drive shaft, this two planebalancing method is the only way to acquire good results.

Sockets

Wrenches

Table 1 Recommended balance quality grades (excerpt from JIS B 0905)
Upper limit value ofBalancebalance quality
quality grade(1) Ring head

Recommended applicable machines

L

Car wheels, wheel rims, wheel sets and drive shafts
Crankshaft systems of elastically mounted high speed four stroke engines (gasoline or diesel) withsix or more cylinders
Crankshaft systems of the engines of automobiles, trucks and rolling stock
Drive shafts with special requirements (propeller shafts and diesel shafts)
Components of crushing machines
Components of agricultural machinesW

No.
HR17X4200

L Width across ﬂat(mm) W (mm)100

17

HR19X4200

100

19

HR22X4200

100

22

HR24X8500

160

24

HR27X8500

160

27

HR30X8500

160

30

HR32X8500

160

32

HR36X8500

160

36

HR41X8500

16041(1) Ring wrench
W
L

Components of the engines of automobiles, trucks and rolling stock (gasoline or diesel)
Crankshaft systems with six or more cylinders with special requirements
Devices of processing plants
Ship engine turbine gears (for merchant ships)
Centrifugal drums
Papermaking rolls and printing rolls
Fans
Assembled aerial gas turbine rollers
Flywheels
Pump impellers
Components of machine tools and general industrial machines
Medium or large electric armatures (of electric motors having at least 80 mm in the shaft center
height) without special requirements
Small electric armatures used in vibration insensitive applications and/or provided with vibration
insulation (mainly mass produced models)Components of engines with special requirements

17(2) Socket wrenchW

No.
WR32X500
WR36X500
WR41X500
WR46X500
WR50X500
WR50X500A
WR55X500
WR55X500A
WR60X500
WR60X800A
WR65X800
WR70X800
WR75X800
WR80X800
WR85X800
WR90X800
WR95X1000No.
WB36X500

L

L Width across ﬂat(mm) W (mm)
500
500
500
500
500
500
500
500
500
800
800
800
800
800
800
800
1000

32
36
41
46
50
50
55
55
60
60
65
70
75
80
85
90
95

L Width across ﬂat(mm) W (mm)500

36

WB41X500

50041

WB46X500

500

46

WB50X500

500

50

WB55X500

500

55

WB60X800

80060

WB65X800

800

65

WB70X800

80070

WB75X800

800

75

18

Specifications

D series■ Features
This series is suitable for use under severe conditions, such as in driving rolling mill rolls.
Based on standardized cross & bearings, this series can be designed to suit a wide range ofdimensions and a wide variety of fitting configurations.

Telescoping type (with propeller tube): Propeller tube dia.
: Spline dia.
: Allowable telescoping stroke

＊

＊

＊

＊

■ Designs available to order
The fixed type can be designed to order, assemblingcomponents shown on the right.
For more details on these designs, consult JTEKT.

With
propeller tube

With
coupling yoke＊

7）

Swing Torque capacity (kN･m)

Dimensions marked with an asterisk (＊) need to be determined to suit existing equipment.
Please provide the specifications of your equipment when placing an inquiry.

Model dia.
No.
(mm)

Boundary dimensions (mm)Torque Wrench No.
Nominal Width Tightening
6）
Socket No.
torquethread across
Q ty Type Tensiometer No.
ﬂats
size
(N･m)
Wrench No.

(°)(min.)(min.)

Tightening
torque(N･m)Torque Wrench No.
6）
Socket No.
Q ty Type Tensiometer No.
Wrench No.

D66150

1730

3870

2090

M72×4

20400±500

B

TM3000WR90×800

D68160

2090

4600

2225

M76×4

24500±500

B

TM3000
WR95×1000

D22032

10.9

34.1

9

M16×1.5185± 20A

TW4200
HR17×4200

D71170

3720

6200

2337

M48×2

5590±200

C

TM2000
WB50×500

D26038

22.5

54.7

9.5

M18×1.5285± 20A

TW4200
HR19×4200

D72180

4070

6610

2445

M48×2

5590±200

C

TM2000
WB50×500

D3004435.3

73.1 10M20×2

370± 20A

TW4200
HR22×4200

D7E184

4360

8050

2495

M52×2

7350±300

C

TM2000
WB50×500

D34052

56.2

140

7.5

M24×2

645± 30A

TW8500
HR27×8500

D74190

3900

9250

2564

M56×3

9120±300

C

TM2000
WB60×800

D38060

22.7

89.9

260

8

M30×2

1180± 50

B

TM500
WR32×500

D75194

4600

10400

2594

M56×3

9120±300

C

TM2000
WB60×800

D44070

38.3

144

384

9

M33×2

1720± 70

B

TM500
WR36×500

D76204 1020

4540

8050

2654

M52×3

7650±300

C

TM2000
WB55×500

D48080

213

560

8

M39×3

3040±200

B

TM1000WR50×500

D7J216 1080

1040

6780

13500

C

TM2000
WB65×800

D50085

264

708

8

M42×3

4020±200

B

TM1000WR50×500

D81220 1100

1100

7970

13300

2970

M64×3

14200±300

C

TM2000
WB65×800

D54090

333

739

8

M42×3

4020±200

B

TM1000WR50×500

D8B226 1130

1210

7550

15200

3070

M68×3

17100±500

C

TM3000
WB70×800

D56100

500

1060

8

M48×3

5980±300

B

TM2000WR60×500

D8E246 1230

1540

8970

18800

3165

M72×4

20400±500

C

TM3000
WB75×800

D58110

747

1460

6

M52×3

7650±300

B

TM2000WR65×800

D60118

590

191

939

1990

4.5 1730

125

490

325

235

M58×3

70

10300±300

8BTM2000WR70×800

D60126

630

209

993

2180

15

1776

125

490

325

235

M58×3

70

10300±300

8BTM2000WR70×800

D62134

670

260

1170

2640

9

1859

136

530

350

250

M62×3

75

12700±300

8BTM2000WR75×800

1510

3370

6

B

TM3000WR85×800

D6414019

Recommended wrench set(bearing set bolt)

Bearing set bolts

Recommended wrench set(bearing set bolt)

Bearing set bolts
Nominal Widththread acrosssize ﬂats(°)

7）

Swing Torque capacity (kN･m) Max.
operatingModel dia.
angle
No.
(mm)

Max.
operatingangle

Boundary dimensions (mm)M68×3

17100±500[Notes]

6

2890

230

890

1030

600

400

M64×3

65

14200±300

24

1)
2)

refers to the rated torque used for service life calculation (refer to page 15). The material factor
is supposed to be 3 in this calculation.
refers to the reference torque used as the criterion for evaluation of resistance to the maximum torque under normal operating conditions.
divided by the maximum torque should preferably be greater than 1.5.
3)
refers to the reference torque used as the criterion for evaluation of resistance to the breaking torque under emergency conditions.
divided by the breaking torque should preferably be greater than 1.5.
4)refers to the minimum dimension when the shaft has neither propeller tube nor welded connection.
5) The parenthesized values refer to the involute spline diameter.
6) Represents the bolt quantity used for one kit of cross & bearing.
7) The types of wrench set are as follows. For details, refer to “Torque wrench set for bolt tightening” on page 18.
Type A: Torque wrench + Ring headType B: Tensiometer + Ring wrenchType C: Tensiometer + Socket wrench[Remarks] 1) The values with ※ mark are reference values.
2) Thevalues in the table are the values with alternating load. For the values with pulsating load, contact JTEKT.
20Specifications

U series
Telescoping type (with propeller tube): Propeller tube dia.
: Spline dia.
: Allowable telescoping stroke

＊

＊

＊

＊

■ Features
The U Series is mainly intended for non reversing mills,
such as the finishing stand of a hot strip mill.
■ Designs available to order
The fixed type can be designed to order, assemblingcomponents are shown on the right.
For more details on these designs, consult JTEKT.

＊

With
propeller tube

With
coupling yoke
Dimensions marked with an asterisk (＊) need to be determined to suit existing equipment.
Please provide the specifications of your equipment when placing an inquiry.
7）

Swing Torque capacity (kN･m)

Model dia.
No.
(mm)

Max.
operatingangle

Boundary dimensions (mm)(°)

Torque Wrench No.
Nominal Width Tightening
6）
Socket No.
torquethread across
Q ty Type Tensiometer No.
ﬂats
size
(N･m)
Wrench No.

5）(min.)

21

Recommended wrench set(bearing set bolt)

Bearing set bolts

7）

Swing Torque capacity (kN･m)

Model dia.
No.
(mm)

(°)

285

19.6

115

230

4

943

57

244.5

177.8
(160)

135

M30×2

32

1320± 50

8

B

TM500
WR32×500

U65146

U38059

295

20.8

121

244

4

975

60

244.5

177.8
(160)

135

M32×2

32

1470± 70

8

B

TM500
WR32×500

U43069

345

34.5

217

430

4

1155

70

339.7

225
(200)

165

M36×2

41

2550±1508BU45073

45.5

284

497

1185

U4H078

53.3

313

745

U4908462.7

414

U5308877.1

U5E095M48×2

5590±200

C

TM2000
WB50×500

M52×2

7650±300

C

TM2000
WB55×500

2195

M45×2

TM1000
WR41×500

U6J156

3770

5700

2235

4360

6650

2357

B

TM1000
WR41×500

U69168

1240

M42×2

3820±200

B

TM1000
WR46×500[Notes]

725

1309

M45×2

4900±200

B

TM2000WR50×500A

504

855

1388

275

M45×2

5050±200

B

TM2000
WR55×500

94.1

650

1170

1465

275

M48×2

5880±200

B

TM2000
WR55×500A

U55098

108

755

1252

1503

275

M52×2

7350±300

B

TM2000WR60×800A

U5G105

127

859

1410

1630

M52×3

7650±300

B

TM2000WR65×800

U57108

140

1160

1780

1674

M56×2

9120±300

B

TM2000WR60×800A

U59118

180

1500

2270

1775

M36×2

2350±100

C

TM1000
WB36×500

U63128

229

2120

2920

1899

M39×2

2940±150

C

TM1000
WB36×500

U6S132

255

2230

3030

1963

M39×2

2940±150

C

TM1000
WB36×500

U6D138

285

2660

3710

2049

M42×2

4270±200

C

TM1000
WB41×500

670

450

305

24

TM2000
WB46×500

4840

155

4900±200

C

3440

2160

(N･m)

4900±200

U67152

4

Torque Wrench No.
6）
Socket No.
Q ty Type Tensiometer No.
Wrench No.
TM2000
WR46×500

5050

2840±150

344

Tightening
torque

C

2920

M39×2

730

Recommended wrench set(bearing set bolt)

Bearing set bolts
Nominal Widththread acrosssize ﬂats

5）(min.)

U36057(200)

Max.
operatingangle

Boundary dimensions (mm)

M45×2

46

1)
2)

refers to the rated torque used for service life calculation (refer to page 15). The material factor
is supposed to be 3 in this calculation.
refers to the reference torque used as the criterion for evaluation of resistance to the maximum torque under normal operating conditions.
divided by the maximum torque should preferably be greater than 1.5.
3)
refers to the reference torque used as the criterion for evaluation of resistance to the breaking torque under emergency conditions.
divided by the breaking torque should preferably be greater than 1.5.
4)refers to the minimum dimension when the shaft has neither propeller tube nor welded connection.
5) The value within parentheses indicates the spline diameter of the involute splines.
6) Represents the bolt quantity used for one kit of cross & bearing.
7) The types of wrench set are as follows. For details, refer to “Torque wrench set for bolt tightening” on page 18.
Type A: Torque wrench + Ring headType B: Tensiometer + Ring wrenchType C: Tensiometer + Socket wrench[Remarks] 1) The
values in the table are values with pulsating load.

22

Specifications

T series: Spline dia.
: Allowable telescoping stroke

＊

＊

＊

＊

■ Features
The T Series is intended for such applications where telescoping function is required in a small space.
Because one of the cross & bearings needs to be hollow to enable the required stroke, this series isapplicable in such cases where the swing diameter has a given allowance on either the driving side or
driven side.

＊

Dimensions marked with an asterisk (＊) need to be determined to suit existing equipment.
Please provide the specifications of your equipment when placing an inquiry.

Model
No.

Swing
dia.

Torque capacity (kN･m)Max.
operating
angle

(mm)
(

(°)

)

6）

Boundary dimensions (mm)4）(min.)()

Recommended wrench set(bearing set bolt)

Bearing set bolts
Nominalthreadsize

Widthacrossﬂats

Tightening
torque(N･m)

5）

QuantityType

Torque Wrench No.
Socket No.
Tensiometer No.
Wrench No.

M24×2

645± 30

A

TM500
HR27×8500

M30×2

1180± 50

B

TM500
WR32×500

969

M33×2

1720± 70

B

TM500
WR36×500

560

1080

M39×3

3030±200

B

TM1000WR50×500

333

739

1196

M42×3

4020±200

B

TM1000WR50×500

T60120(D56100)

500

1060

1319

M48×3

5980±300

B

TM2000WR60×500

T62130(D58110)

747

1460

1414

M52×3

7650±300

B

TM2000WR65×800

T66150(D62130)

1140

2520

1617

M62×3

12700±300

B

TM2000WR75×800

T42065(D30044)

35.3

73.1

T48080(D38060)

89.9

260

8

T54090(D44070)

144

384

9

TZ56100(D48080)

213

T58110(D54090)[Notes]refers to the rated torque used for service life calculation (refer to page 15). The material factor
is supposed to be 3 in this calculation.
refers to the reference torque used as the criterion for evaluation of resistance to the maximum torque under normal operating conditions.
divided by the maximum torque should preferably be greater than 1.5.
3)
refers to the reference torque used as the criterion for evaluation of resistance to the breaking torque under emergency conditions.
divided by the breaking torque should preferably be greater than 1.5.
4)refers to the minimum dimension when the shaft has neither propeller tube nor welded connection.
5) Represents the bolt quantity used for one kit of cross & bearing.
6) The types of wrench set are as follows. For details, refer to “Torque wrench set for bolt tightening” on page 18.
Type A: Torque wrench + Ring headType B: Tensiometer + Ring wrenchType C: Tensiometer + Socket wrenchvalues in the table are the values with alternating load. For the values with pulsating load, contact JTEKT.
[Remarks] 1) The
2) Specifications in parentheses are recommended model numbers and dimensions for combination.

23

1)
2)

24

Product introduction
Drive shaft with roll phase adjustment device for bar and rod millWork procedure
S : Adjustment
amount(1) Phase adjustment work should be conducted with the rolls of the rolling

Applications

mill inserted to the drive shaft. First, measure the adjustment amount.
(2) Decide the number of adjustment scales from the following equation.

Used to adjust the rotation direction phase of the upper and lower rolling mill rolls

N＝arbitrarily when forming a continuous thread shape in manufacturing of bar and rod
steel for building material (screw reinforcing bar) in bar and rod mills.

18･P ･S
D ･L ･tan

N : Number of adjustment scales
P : Helical spline PCD＊S : Adjustment amount (mm) (Measure the dimension
in the figure on the right)

Reasons for increase of needs of screw reinforcing bar

D : Roll diameter (mm) (customer dimension)
L : Adjustment nut pitch＊(1) To simplify operations, the connection method of bar steel was increasingly changed

Fixing nut

Phase adjustment nut: Helical spline helix angle＊

from previous “welding method” to “screw connection method.”

For items with ＊, contact JTEKT.

(2) By forming continuous convex in the periphery of bar steel, adhesion with concrete isincreased.

(3) Loosen the fixing nuts in three positions so that the adjustment nut

Necessity of phase adjustment of rotation direction of rolls(4) Proceed with adjustment by rotating the phase adjustment nut.

should be able to rotate.
When the adjustment nut is rotated, the helical spline slides.

For roll forming of continuous convex screw thread on the surface of bar steel, theWith sliding of the helical spline, the rolls rotate slightly. Adjust themrotation direction phase of the upper and lower rolls with concavity spiral groove formed

to an arbitrary phase.
(5) When the work is complete, tighten the fixing nuts for whirl-stop so thatshould be adjusted to an arbitrary position.

the adjustment unit should not move. It is fixed to this phase.

Features

For design of phase adjustment device(1) The rotation phase can be adjusted almost steplessly, which improves
the accuracy of products.
(2) The phase can be adjusted in a short time, which improves theefficiency of the work.
(3) With its unique configuration, the space can be saved in the directionsof diameter and shaft.

(4) The lineup of equipment has been enriched to suit
most of the bar steel sizes.
(5) On-line work can be conducted without removing
the drive shaft.

Provide JTEKT with the following information for design of the optimal phase adjustment device.
Provide them along with the selection sheet of the drive shaft.
- Stand status (horizontal stand or vertical stand)- Roll diameter (disposal diameter)- Roll rotation direction (seen from the pinion stand)- Pinion PCD- Pitch in the case of screw reinforcing bar and intercalary dimension in the case of deformed steel bar.

Installation examples
The phase adjustment device can be attached to both horizontal stand and vertical stand.
The figures below and on the right are installation examples.

Phase adjustment device

For horizontal stand (installed in intermediate part)For vertical stand25

For horizontal stand (installed in cylindrical bore yoke part)26

Product introduction
Hyper coupling (1)Features(1) The recovery time after operation (oil pressure release) is(4) High durability performance.
significantly shortened.
- A high degree of free independen rotation performance after(2) High operation accuracy.
the release of the oil pressure is secured by utilizing our- The operation torque accuracy is high. The variation of theknow-how as a bearing manufacturer.
operation torque is within ±10 %.
- Special surface treatment is applied to the operating surface to- The operation torque is validated by using a large-sized
improve durability.
torsion testing machine to improve reliability.
- The oil pressure release-performance is improved byestablishing an analysis method of the oil pressure release time.
(3) The operation torque can be easily set.

Applications
Used to protect peripheral devices of rolling mills against excessive torque.

Drive shafts

Work rolls

Structure and working principle
The hydraulic expansion type torque limiter transmits torque by the friction
between the shaft components and the welded coupling assemble, whichis generated by the bore shrinkage of the welded coupling assemble when
oil is filled and pressurized in the hydraulic expansion chamber.
The torque can be set in proportion to hydraulic pressure, which is simultaneously released by the decompression of oil, thanks to the breakage ofthe shear valve coming concurrently with slipping of torque transmission
surface, if the excessive torque beyond set value is generated.
The following illustration shows an example of the hydraulic expansion
type torque limiter applied to a rolling mill.

Hyper coupling
Pinion stand

Motor

A

Operating principle

A hydraulic expansion chamber is provided
in the outer cylinder part for expansion by theoil pressure, so that torque should be transmitted
to the shaft part by friction connection.

Installation on this side
can be also considered
Hydraulic expansion
chamber

Shear valve

Torque transmission

Support bearing
Shaft part

Outer cylindrical part

1

4

3

RecoveryWork rollRolling accident(Multiple jam of rolled material)2

Oil pressure release

Free independent rotation

Sudden stop of work roll
Excessive torque (moment of inertia )Imposes on drive shaft

Supportbearing

Cover tube
Female coupler

Static damage

Torque transmission surface and sliding surface

View A (Example of abnormal rolling)

The shear valve is replaced by matching
the phases of the outer cylindrical partand shaft part. When oil pressure fromthe female coupler is applied again,
recovery is completed.

Installation position and structure of hyper coupling

When excessive torque occurs, thetorque transmission surface slides
relatively. At the same time, the shear
valve is broken by the cover tube andthe oil pressure is released instantly.
The outer cylindrical part and the shaft part are free torotate independently and smoothly on the bearings that
support both ends of the torque transmission surface.

Comparison of Conventional ProductAt the Replacement
part
time ofrecovery Ratio of required

man-hours forpart replacement

At the regularinspection time

◆Shear pin : 4 pieces◆Nut: 4 pieces: 8 pieces◆BusheHyper coupling◆Shear valves : 4 pieces

1
Periodic replacement of shear
pins is required due toaccumulated fatigue

Merits of Hyper coupling27

1/4
Periodic replacementof shear valvesis not required

4 Shear pins
8 Bushings(Torquetransmission)

At normal

4 NutsHyper coupling
Hydraulicexpansionchamber(Oil pressure
charged)4 Shear valves(With oil pressure
retained)

Torque transmission surface(Connection by friction)

4 Shear pins

Shearing

Hydraulicexpansionchamber(Oil pressure
released)

Operation torque4 Shear valves

Shearing

＋10％
­10％

Operation torque, kN・mShear pin typeShear pin type

At excessive torqueThe shear pin type torque limiter has been used as the implement torelease torque, however, the maintenance of surrounding parts of theshear pin is required in case the shear pin is broken, which leads to a lotof time consuming for replacement. Furthermore, the pin needs to beperiodically replaced in the overhaul in order to prevent the accumulated
metal fatigue of the pin. Compared with the share pin type torque limiter,
the hydraulic expansion type torque limiter requires only share valve
replacement for repair. Since it is not required to replace the shear valvesduring periodical inspection, it will improve the overhaul time.

Before shipping, a large-sized torsion testing machine is usedwith the actual machine to calculate the relationship between
each oil pressure and operation torque.
We set the oil pressure value for the requested operation torque.
The accuracy of the operation torque with each oil pressure
value is high: within ±10 %.

Oil pressure, MPa
Sliding surface(Clearance)

Oil pressure-operation torque diagram (image)The setting of operation torque can be changed easily byadjusting the oil pressure value.

Large-sized torsion testing machine28

Product introduction
Hyper coupling (2)Recovery method after operation

Phase fixing pin(1) After the drive system (drive shaft) is stopped completely,

Dimension tables

Shear valve

clean its surroundings.
(2) Match the phases of the outer cylinder part and shaft part

Female coupler

and fix the cover tube and the outer cylinder part by usingLthe phase fixing pin.
Remove the shear valve that has been cut off and replacewith a new shear valve after cleaning.
(figure on the upper right)(3) Insert the connection hose of the hydraulic pump with aHydraulic pumpconnection hosemale coupler to the female coupler and fill the hydraulicexpansion chamber with oil and pressurize to the set

FD

pressure. (figure on the middle right)

F

Male coupler(4) The oil pressure is retained by tightening the shear valve
with specified torque. (figure on the lower right)
Highper
coupling
No.

Operation torque(kN・m)

Full length

L (mm)

Outside Flange outsidedia.
diameter

D (mm)F (mm)

Corresponding model No.
D series(5) Check for oil leakage of the shear valve.

U series

Torque wrench(6) After removing the residual pressure of the hydraulic pump,

TL070

80〜 150

550

420

330

D34052−

TL088

160〜 280

650

510

430

D44070−

TL104

200〜 510

750

590

525

D50085

U49084For details, refer to the operation manual attached to the

TL120

400〜 800

850

670

610

D56100U53088product to conduct work.

TL134

600〜1100

950

740

675

D58110U5G105

TL148

800〜1300

1000

810

735

D60120

U57108TL160

1000〜1800

1100

870

800

D62130

U59118

TL176

1400〜2300

1200

950

860

D64140

U6S132

TL188

2100〜2900

1300

1010

920

D66150

U6D138

TL204

2500〜3600

1400

1090

980

D68160U67152

TL218

3200〜4300

1500

1160

1050

D71170

U69168

remove the connection hose. The recovery is completed.

Examples of main tools (attached)(4) Male coupler
Attached to the end of the hose attached to the(1) Hydraulic pump(3) Phase fixing pin

hydraulic pump.

Used to fill the hydraulic

Used for whirl-stop at the time of

It is inserted to the female coupler of the hyper

expansion chamber with oil

recovery of the hyper coupling.

coupling to pressurize and depressurize theand pressurize.

hydraulic expansion chamber.

(2) Torque wrench
Used to attach and remove
the shear valve assembly,
coupler assembly, and phasefixing pin.

29

30

Attached tables

Recommended tightening torque for flange bolts
Shape and dimensions of parallel key and keyway (JIS B 1301)

Designation

Fine
screw
thread

Pitch

(mm)

Width across ﬂats

(mm)

(N･m)

Tightening force

(N)

12±1
29±2
59±5
98±5

11500
21100
33500
47400

155±10245±20345±20480±30645±4065400
91800
114000144000179000825±501230±701670±1002260±1502840±150

2070002760003340004170004790003730±200
4610±300
5790±300
6960±400
9020±500

5820006650007830008760001060000

11300±600
13700±700
16700±900
20100±1000

1240000
1410000
1610000
1840000

Tightening torque(N･m)Sectionof keySectionof keyway

unit : mm
Dimension of key
Nominalsize
of keyTolerance(h9)

Informativenote

Dimension of keyway

Tolerance

Tightening force(N)

Sliding type

Normal type Fastening type
andTolerance Tolerance Tolerance Tolerance Tolerance（ H 9 ）（ D 1 0 ）（ N 9 ）（ J S 9 ） （ P 9 ）
0.025
0

0.060
0.020

0.030
0

0.078
0.030

0.036
0

0.098
0.040

14±1
31±2
64±5
105±5
105±5

12900
23000
37200
54400
52800

0.043
0

0.120
0.050

175±10265±20360±20500±30675±4075400
102000123000153000191000

0.052
0

0.149
0.065

900±501320±70
1810±1002450±150
3040±150

233000305000378000468000523000

0.062
0

0.180
0.080

3920±200
5000±300
6180±300
7550±400
9610±500

6240007400008550009790001160000

12300±700
14700±800
18100±1000
21600±1000

1380000
1560000
1810000
2040000

0.074
0

0.220
0.100

0.087
0

0.260
0.120

and

Toleranceof andCoarsescrew
threadTightening torque

Basic dimensionofBasic dimension
of

(mm)

Basic dimensionof andWidth across ﬂats

Basicdimension

Pitch

(mm)

Basic
dimension

Designation

Applicable
shaft
dia.

90 360[Notes][Remarks] 1）The recommended values are applicable to the following bolts.
Hexagon head bolts of JIS strength class 10.9 (bolt holes is JIS class 1)
Non treated (including blackening), grease lubrication ( = 0.125 to 0.14)
2）The values are also applicable to class 2 bolt holes and reamer bolt holes as well ashexagon socket head cap screws as far as the designation and pitch are identical.

311）Dimension shall be selected among the following within the range given in Table.
The dimensional tolerance on shall be generally h12 in JIS B0401.
6 , 8 , 10 , 12 , 14 , 16 , 18 , 20 , 22 , 25 , 28 , 32 , 36 , 40 , 45 , 50 , 56 , 63 , 70 , 80 , 90 , 100 , 110 , 125 , 140 , 160 , 180 , 200 ,
220 , 250 , 280 , 320 , 360 , 4002）The applicable shaft diameter is appropriate to the torque corresponding to the strength of the key.
[Remark] The nominal sizes given in parentheses should be avoided from use, as possible.
[Reference] Where the key of the smaller tolerance than that specified in this standard is needed, the tolerance on width of the key shall be h7.
In this case, the tolerance on height shall be h7 for the key 7× 7 or less in nominal size and h11 for the key of 8 × 7 or more.

32

Drive shaft selection sheet

Item

Hyper coupling selection sheet

Necessity

Description

Remarks

Name of the machine

Necessity

Item

Description

Name of the machine

Location of installation(1) Rated motor output(2) Motor speed○

Location of installation

（kW）

○

（min-1）○（kW）(1) Rated motor output

Max.

Min.

○

(3) Reduction ratio
Drive shaft○(2) Motor speed○(3) Reduction ratio○

Existing overload prevention device○(4) Number of drive shafts per motor（kN・m）(5) Torque transmission(6) Rotational speed（min-1）(7) Direction(s) of rotation(Circle one of the two listed on the right.)○

NormalNormal max.

(4) Installation position (refer to (11))

Emergency max.
Unnecessary if (2) and (3)are filled in

○

Min.

Max.

○

Non reversing

Reversing（mm）△(9) Required stroke

（mm）

○

(10) Pinion PCD

（mm）

△

(11) Roll minimum dia.

（mm）

△

Enter when the shaft isused for reduction rolls
as an example.

△

Black if not specified(12) Paint color（℃）△
Water, steam, etc.
○：Must be filled in.
△：Should be filled in as appropriate.

(15) Installation dimensions (Must be ﬁlled out.)

Driving side

Distance between shaft ends

Offset(5) Type

No

A

B

Shear pin

Installation position (refer to (11))○(6) (1) - (7) in the ﬁgure below○

Driven side

Distance between shaft ends（mm）
Oﬀset
Horizontal（mm）Vertical（mm）

HydraulicA

OthersB（kN・m）

Transmission torque△(14) Special environmental conditions

Yes

If Yes(8) Limit swing dia.

(13) Ambient temperature

Remarks(7) Normal○(8) Max.

○(9) Emergency max.

○(10) Operation torque○

Rotational speed（min-1）○（℃）△

Paint color
Ambient temperature△Special environmental conditions○：Must be filled in.
△：Should be filled in as appropriate.

(11) Installation dimensions (Must be ﬁlled out.)（6）

Fit
Driving side
Driven side

＊In the case of
cylindrical shaft

Driven side

＊In the case ofoval shaft(1) Flange outside diameter（mm）(2) Mounting hole PCD x quantity

（mm）
（mm）
（mm）
（mm）

w（mm）
（mm）

(3) Flange outside diameter

Hyper
coupling
Motor（2） （1）（5）(4) Mounting hole PCD x quantity（3） （4）

Pinionstand(5) Hyper coupling outside diameter(6) Full length

A. When installed between the motor and the pinion stand（6）(1) Flange outside diameter(2) Mounting hole PCD x quantity

Hypercoupling
Pinionstandw
In the case of oval shaft

33（2）（1） （5）(3) Flange outside diameter（3） （4）

Drive shaft(4) Mounting hole PCD x quantity(5) Hyper coupling outside diameter(6) Full length（7）(7) Pinion PCD

B. When installed between the pinion stand and the drive shaft

34