Resource Guide Fastener Hardware

8/2/2019 Resource Guide Fastener Hardware

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Fasteners and HardwareQuick Release Pins

Thread Inserts

Fasteners

Latches, Catches, Hingesand Slides

800.253.0421 www.ReidSupply.com

Copyright©2008 Reid Supply Co. All Rights Reserved

CONTENTS

Reid Supply Resource Guides 1

Disclaimer 1

Terminology 1

Purpose of This Resource Guide 1

Design Considerations 2

Fasteners 2

Inch Bolt & Screw Nomenclature 2

Metric Bolt & Screw Nomenclature 5

Stress 9

Tensile Force 17

Shear Forces for Bolts, Screws, Pins or Rivets 20

Hardware 22

Environment 22

Sanitation 22

Security 22

Space 22Vibration 22

Aesthetics 22

Production Requirements 22

Automation 23

Quality 23

Human Factors 23

Safety 23

Selecting the Correct Component 23

Style 23

Screw Styles 23

Materials 26

Standards 29

Fasteners 30

Screw vs. Bolt 31

Fastener Diameter 31

Vibration Proof Fasteners 32

Fastener Tools 32

Hardware 33

Custom Products 34

Summary 35

For More Information 35

Glossary 37

References 37

LIST OF TABLES

Table 1: Recommended Hole and Drill Sizes for U.S. Screws 2

Table 2: Recommended Hole and Drill Sizes for Metric Screws 5

Table 3: Mechanical Properties of Various Materials 10

Table 4: ASTM, SAE and ISO Grade Markings and MechanicalProperties for Steel Fasteners 11

Table 5: Mechanical Specifications for Carbon Steel Metric Fastenerswith External Threads 16

Table 6: Torque Coefficients ( K ) for Typical Fastener Materials 18

Table 7: ASA Screw Thread Types 24

Table 8: Screw Head Styles 25

Table 9: Materials Used to Manufacture Fasteners and Hardware 27

Table 10: Material Specifications - Metals 28

Table 11: Material Specifications - Nylon 29

Table 12: Standards 29

Table 13: Types of Fasteners 30

Table 14: Vibration Proof Fasteners 32

Table 15: Special Tools for Installing Fasteners 32

Table 16: Special Tools for Removing or Repair ing Fasteners 32

Table 17: Types of Fasteners 33Table 18: Recommended Documentation and Reference Manuals 35

Table 19: Reference Manual Content Relative to This Guide. 36

LIST OF FIGURES

Figure 1: Sample Bolt Head Markings 2

Figure 2: Shear vs. Tension Forces in Bolted Joint 9

LIST OF EQUATIONS

Eq. 1A: Cross-sectional Area of Non-threaded Fastener 17

Eq. 1B: Cross-sectional Area of Threaded Fastener - Inch 17

Eq. 1C: Cross-sect ional Area of Threaded Fastener - Metric 17

Eq. 2A: Determining Fastener Preload, Method 1 18

Eq. 2B: Estimating Fastener Preload, Method 2 18

Eq. 3: Estimating Fastener Torque 19

Eq. 4: Estimating Shear Stress Within a Bolt, Screw 20

Eq. 5: Estimating Shear Stress on a Rivet 20

Eq. 6: Estimating Minimum Fastener Diameter 31



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Fasteners and Hardware

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In our continuous effort to improve our offerings and meet customer needs, simplify effort and providesolutions, Reid Supply has separated our products into 12 easy-to-identify categories:

Manual Controls - Blue

Clamps and Workholding - Red

Tooling Components - Gold

Fasteners and Hardware - Blue Green

Leveling Devices and Vibration Control - Orange

Material Handling - Purple

Bearings and Power Transmission - Blue Gray

Metalworking - Brown

Maintenance, Repair and Operations - Aqua

Pneumatics and Hydraulics - Dark Red

Structural Systems - Yellow Green

Safety - Orange Yellow

Fasteners and Hardware is the fourth of a series of Resource Guides relative to each of the 12categories. Each Resource Guide will include detailed application information, data and references tohelp our customers select the best product for their intended application.

Reid Supply welcomes your feedback and comments on any aspect of these Resource Guides. Pleasecontact Customer Service at the number listed below or email us at [email protected].

It should be noted that this Resource Guide is for reference only . The information provided isintended to assist in the selection of products sold by Reid Supply and its vendors. As Reid Supply andits vendors are not typically aware of or possess any expertise in the systems or processes for whichproducts are being applied, we cannot accept any responsibility or liability for the outcome thereof.

Furthermore, with new and old technologies continually expanding and changing, it is impossibleto address all systems, processes and applications for which Reid Supply products are purchased.Reid Supply also has little control over materials and processes from which our products are produced.

In addition, due to the nature of some materials; colors, textures, shapes and sizes may lackconsistency.

Reid Supply reserves the right to modify, update and otherwise maintain this document and its content.

Terms used to define products are typically determined by the vendor. However, fasteners and relatedhardware have been around for many years and many reference and how-to manuals have been writtenInformation is also available online. To avoid confusion, a glossary of terms used in this document hasbeen included at the end of the manual.

As Reid Supply purchases its products from several vendors, it is sometimes difficult to sort andcategorize these differences. If you find yourself confused by terminology in the catalog or thisdocument, try shopping online using the web site listed below.

If a product consists of assembled parts, there is a very good chance Fasteners and Hardware are used

to hold the parts together. The purpose of this manual is to aid customers in the proper selection of theFasteners and Hardware of Reid Supply product offerings. The information included extends beyond thecatalog to provide details, tables, charts and other information to further assist the customer in selectingthe best Fasteners and Hardware for an application.

Much of the information presented and more, including this guide, can be found online. More detailedinformation can be found in the references manuals listed in Table 18 at the end of the guide.

NOTE: References used are listed at the end of this manual and referred to by number, e.g. [1,2], in thetext. References to text books and other documentation sold by Reid Supply are also referredto by number, e.g. {5} and listed in Table 18 at the end of this manual.

REID SUPPLY RESOURCE GUIDES

REID SUPPLY RESOURCE GUIDES

DISCLAIMERDISCLAIMER

TERMINOLOGYTERMINOLOGY

PURPOSE OF THIS RESOURCE GUIDEPURPOSE OF THIS RESOURCE GUIDE




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Although considerations for every and all applications is beyond the scope of this manual, some basicdesign considerations can be presented. The type of Fasteners and Hardware used in an applicationare based on what needs to be fastened to what and how. Hardware considerations are based on howthings come together, even if they are not fastened. The remainder of this section discusses some basicconsiderations which should be understood when applying fasteners and related hardware.

The most common fasteners are bolts and screws. Other fastener types are listed in Table 13 laterin this Resource Guide. There are two groups of fasteners shown Figure 1, inch and metric. Inchis primarily used in the U.S. while metric fasteners are used in Europe, Asia and the rest of theworld. Because of globalization in world markets, the U.S. is slowly converting to the metric system.Reid Supply offers an increasing selection of metric fasteners.

Figure 1 shows sample markings for inch and metric systems. A more detailed list of markings andspecifications can be found in Table 4.

Figure 1: Sample Bolt Head Markings

Inch Metric

U.S. bolts and screws are generally identified by diameter and threads per inch as shown below.

D x N x L

Where: D = Nominal diameter of fastener

N = Thread per inch

L = Length, this is a secondary value that is not always specified. The referencefor measuring a bolt or screw length is the surface plane for which the bolt orscrew is inserted. For bolts, it is measured from the underside of the headand for screws, it depends on the screw type as shown in Table 7 later in thisResource Guide.

Table 1 includes a list of U.S. standard bolt and screw sizes along with recommended drill sizes for tapor pass through holes.

Table 1: Recommended Hole and Drill Sizes for U.S. Screws

Machine ScrewSize

Numberof

ThreadsPer Inch

MinorDiameter

Tap Drill Clearance Hole Drill

Aluminum, Brass& Plastics

Stainless Steel,Steels Iron All Materials

75% Thread 50% Thread Close Fit Free Fit

No. orDia.

MajorDia. Drill Size

DecimalEquiv.

DrillSize

DecimalEquiv.

DrillSize

DecimalEquiv. Drill Size

DecimalEquiv.

0 0.06 80 0.0447 23437 0.0469 55 0.052 52 0.0635 50 0.07

1 0.07364 0.0538 53 0.0595 1/16 0.0625

48 0.076 46 0.08172 0.056 53 0.0595 52 0.0635

2 0.08656 0.0641 50 0.07 49 0.073

43 0.089 41 0.09664 0.0668 50 0.07 48 0.076

3 0.09948 0.0734 47 0.0785 44 0.086

37 0.104 35 0.1156 0.0771 45 0.082 43 0.089

DESIGN CONSIDERATIONS

DESIGN CONSIDERATIONS

FastenersFasteners

10.9 10.9

Inch Bolt & Screw Nomenclature Inch Bolt & Screw Nomenclature



Quick Release Pins

Thread Inserts

Fasteners





Machine Screw

Size

Number

ofThreadsPer Inch

MinorDiameter




75% Thread 50% Thread Close Fit Free FitNo. orDia.


DecimalEquiv.

DrillSize

DecimalEquiv.

DrillSize


DecimalEquiv.

4 0.11240 0.0813 43 0.089 41 0.096

32 0.116 30 0.128548 0.0864 42 0.0935 40 0.098

5 0.12540 0.0943 38 0.1015 23559 0.1094

30 0.1285 29 0.13644 0.0971 37 0.104 35 0.11

6 0.13832 0.0997 36 0.1065 32 0.116

27 0.144 25 0.149540 0.1073 33 0.113 31 0.12

8 0.16432 0.1257 29 0.136 27 0.144

18 0.1695 16 0.17736 0.1299 29 0.136 26 0.147

10 0.19 24 0.1389 25 0.1495 20 0.161 9 0.196 7 0.20132 0.1517 21 0.159 18 0.1695

12 0.216

24 0.1649 16 0.177 12 0.189

2 0.221 1 0.22828 0.1722 14 0.182 10 0.1935

32 0.1777 13 0.185 9 0.196

1/4 0.25

20 0.1887 7 0.201 11871 0.2188

F 0.257 H 0.26628 0.2062 3 0.213 1 0.228

32 0.2117 7/32 0.2188 1 0.228

5/16 0.3125

18 0.2443 F 0.257 J 0.277

P 0.323 Q 0.33224 0.2614 I 0.272 9/32 0.2812

32 0.2742 9/32 0.2812 L 0.29

3/8 0.375

16 0.2983 5/16 0.3125 Q 0.332

W 0.386 X 0.39724 0.3239 Q 0.332 S 0.348

32 0.3367 11/32 0.3438 T 0.358

7/16 0.4375

14 0.3499 U 0.368 25/64 0.3906

29/64 0.4531 15/32 0.468720 0.3762 25/64 0.3906 13/32 0.4062

28 0.3937 Y 0.404 Z 0.413

1/2 0.5

13 0.4056 27/64 0.4219 29/64 0.4531

33/64 0.5156 17/32 0.531220 0.4387 29/64 0.4531 15/32 0.4688

28 0.4562 15/32 0.4688 15/32 0.4688

9/16 0.5625

12 0.4603 31/64 0.4844 33/64 0.5156

37/64 0.5781 19/32 0.593818 0.4943 33/64 0.5156 17/32 0.5312

24 0.5114 33/64 0.5156 17/32 0.5312

5/8 0.625

11 0.5135 17/32 0.5312 9/16 0.5625

41/64 0.6406 21/32 0.656218 0.5568 37/64 0.5781 19/32 0.5938

24 0.5739 37/64 0.5781 19/32 0.5938

11/16 0.6875 24 0.6364 41/64 0.6406 21/32 0.6562 45/64 0.7031 23/32 0.6562




Thread Inserts

Fasteners




Machine Screw

Size

Number

ofThreadsPer Inch

MinorDiameter




75% Thread 50% Thread Close Fit Free FitNo. orDia.


DecimalEquiv.

DrillSize

DecimalEquiv.

DrillSize


DecimalEquiv.

3/4 0.75

10 0.6273 21/32 0.6562 11/16 0.6875

49/64 0.7656 25/32

0.7812

16 0.6733 11/16 0.6875 45/64 0.7031

20 0.6887 45/64 0.7031 23/32 0.7188

13/16 0.8125 20 0.7512 49/64 0.7656 25/32 0.7812 53/64 0.8281 27/32 0.8438

7/8 0.875

9 0.7387 49/64 0.7656 51/64 0.7969

57/64 0.8906 29/32 0.906214 0.7874 13/16 0.8125 53/64 0.8281

20 0.8137 53/64 0.8281 27/32 0.8438

15/16 0.9375 20 0.8762 57/64 0.8906 29/32 0.9062 61/64 0.9531 31/32 0.9688

1 18 0.8466 7/8 0.875 59/64 0.9219

1-1/64 1.0156 1-1/32 1.031312 0.8978 15/16 0.9375 61/64 0.9531

20 0.9387 61/64 0.9531 31/32 0.9688

1-1/16 1.0625 18 0.9943 1.000 1.000 1-1/64 1.0156 1-5/64 1.0781 1-3/32 1.0938

1-1/8 1.125

7 0.9497 63/64 0.9844 1-1/32 1.0313

1-9/64 1.1406 1-5/32 1.156212 1.0228 1-3/64 1.0469 1-5/64 1.0781

18 1.0568 1-1/16 1.0625 1-5/64 1.0781

1-3/16 1.1875 18 1.1193 1-1/8 1.125 1-9/64 1.1406 1-13/64 1.2031 1-7/32 1.2188

1-1/4 1.25

7 1.0747 1-7/64 1.1094 1-5/8 1.1562

1-17/64 1.2656 1-9/32 1.281212 1.1478 1-11/64 1.1719 1-13/64 1.2031

18 1.1818 1-3/16 1.1875 1-13/64 1.2031

1-5/16 1.3125 18 1.2443 1-1/4 1.25 1-17/64 1.2656 1-21/64 1.3281 1-11/32 1.3438

1-3/8 1.375

6 1.1705 1-7/32 1.2187 1-17/64 1.2656

1-25/64 1.3906 1-13/32 1.406212 1.2728 1-19/64 1.2969 1-21/64 1.3281

18 1.3068 1-5/16 1.3125 1-21/64 1.3281

1-7/16 1.4375 18 1.3693 1-3/8 1.375 1-25/64 1.3906 1-29/64 1.4531 1-15/32 1.4688

1-1/2 1.5

6 1.2955 1-11/32 1.3437 1-25/64 1.3906

1-33/64 1.5156 1-17/32 1.531212 1.3978 1-27/64 1.4219 1-7/16 1.4375

18 1.4318 1-7/16 1.4375 1-29/64 1.4531

1-9/16 1.5625 18 1.4943 1-1/2 1.5 1-33/64 1.5156 1-37/64 1.5781 1-19/32 1.5938

1-5/8 1.625 18 1.5568 1-9/16 1.5625 1-37/64 1.5781 1-41/64 1.6406 1-21/32 1.6562

1-11/16 1.6875 18 1.6193 1-5/8 1.625 1-41/64 1.6406 1-45/64 1.7031 1-23/32 1.7188

1-3/4 1.75 5 1.5046 1-9/16 1.5625 1-5/8 1.625 1-49/64 1.7659 1-25/32 1.7812



Quick Release Pins

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Fasteners





The identification for ISO threads are similar to U.S. sizes and specifies diameter. The threads areidentified by pitch as shown below.

M# x P - T P gT

C g

Where: M = Symbol for SI fastener

# = Diameter in millimeters

P = Thread pitch in millimeters, P = 1/ n (n = # threads per inch) for U.S. sizes

T P g = Tolerance grade of thread pitch diameter (Typically not used)

T C g = Tolerance grade of thread crest diameter (Typically not used)

Table 2 includes metric sizes from 1 mm to 56 mm along with recommended drill sizes for tap or passthrough holes.

Table 2: Recommended Hole and Drill Sizes for Metric Screws

Machine Screw Size Tapping Drills Clearance Drills

Nom. Dia. Pitch

Series

Drill Size Close Fit Free Fit

(mm) (mm) (65-75%thread)

DecimalEquiv.

DrillSize

DecimalEquiv.

Drill Size DecimalEquiv.

10.2 Fine 0.8 0.0315

1.05 0.0413 1.2 0.04720.25 Coarse 0.75 0.0295

1.10.2 Fine 0.9 0.0354

1.15 0.0453 1.3 0.05120.25 Coarse 0.85 0.0335

1.20.2 Fine 1 0.0394

1.3 0.0512 1.5 0.0590.25 Coarse 0.95 0.0374

1.40.2 Fine 1.2 0.0472

1.5 0.0591 1.7 0.06690.3 Coarse 1.1 0.0433

1.60.2 Fine 1.4 0.0551

1.7 0.0669 2 0.0787

0.35 Coarse 1.25 0.0492

1.80.2 Fine 1.6 0.063

1.9 0.0748 2.2 0.08660.35 Coarse 1.45 0.0571

20.25 Fine 1.75 0.0689

2.2 0.0866 2.6 0.10240.4 Coarse 1.6 0.063

2.20.25 Fine 1.95 0.0768

2.4 0.0945 2.8 0.11020.45 Coarse 1.75 0.0689

2.50.35 Fine 2.15 0.0846

2.7 0.1063 3.1 0.1220.45 Coarse 2.05 0.0807

30.35 Fine 2.65 0.1043

3.2 0.126 3.6 0.14170.5 Coarse 2.5 0.0984

3.50.35 Fine 3.15 0.124

3.7 0.1457 4.2 0.16530.6 Coarse 2.9 0.1142

40.5 Fine 3.5 0.1378

4.3 0.1693 4.8 0.1890.7 Coarse 3.3 0.1299

4.50.5 Fine 4 0.1575

4.8 0.189 5.3 0.20870.75 Coarse 3.7 0.1457

Metric Bolt & Screw

Nomenclature

Metric Bolt & Screw

Nomenclature




Thread Inserts

Fasteners





Nom. Dia. PitchSeries


(mm) (mm)(65-75%

thread)

Decimal

Equiv.

Drill

Size

Decimal

Equiv.

Drill SizeDecimal

Equiv.

50.5 Fine 4.5 0.1772

5.3 0.2087 5.8 0.22830.8 Coarse 4.2 0.1654

60.75 Fine 5.25 0.2067

6.4 0.252 7 0.27561 Coarse 5 0.1969

70.75 Fine 6.25 0.2461

7.4 0.2913 8 0.3151 Coarse 6 0.2362

8

0.75 Fine 7.25 0.2854

8.4 0.3307 10 0.39371 Fine 7.5 0.2953

1.25 Coarse 6.8 0.2677

9

0.75 Fine 8.25 0.3248

9.5 0.374 10.5 0.41341 Fine 8 0.315

1.25 Coarse 7.8 0.3071

10

0.75 Fine 9.25 0.3642

10.5 0.4134 12 0.47241 Fine 9 0.3543

1.25 Fine 8.8 0.3465

1.5 Coarse 8.5 0.3346

11

0.75 Fine 10.25 0.4035

12 0.4724 13 0.51181 Fine 10 0.3937

1.5 Coarse 9.5 0.374

12

1 Fine 11 0.4331

13 0.5118 15 0.5905

1.25 Fine 10.75 0.4232

1.5 Fine 10.5 0.4134

1.75 Coarse 10.2 0.4016

14

1 Fine 13 0.5118

15 0.5905 17 0.66931.25 Fine 12.8 0.5039

1.5 Fine 12.5 0.4921

2 Coarse 12 0.4724

151 Fine 14 0.5512

16 0.6299 18 0.70871.5 Fine 13.5 0.5315

16

1 Fine 15 0.5906

17 0.6693 19 0.7481.5 Fine 14.5 0.5709

2 Coarse 14 0.5512

171 Fine 16 0.6299

18 0.7087 20 0.78741.5 Fine 15.5 0.6103

18

1 Fine 17 0.6693

19 0.748 21 0.82681.5 Fine 16.5 0.6496

2 Fine 16 0.6299

2.5 Coarse 15.5 0.6102



Quick Release Pins

Thread Inserts

Fasteners








(mm) (mm)(65-75%

thread)

Decimal

Equiv.

Drill

Size

Decimal

Equiv.

Drill SizeDecimal

Equiv.

20

1 Fine 19 0.748

21 0.8268 24 0.94491.5 Fine 18.5 0.7283

2 Fine 18 0.7087

2.5 Coarse 17.5 0.689

22

1 Fine 21 0.8268

23 0.9055 26 1.02361.5 Fine 20.5 0.8071

2 Fine 20 0.7874

2.5 Coarse 19.5 0.7677

24

1 Fine 23 0.9055

25 0.9842 28 1.10241.5 Fine 22.5 0.8858

2 Fine 22 0.8661

3 Coarse 21 0.8268

25

1 Fine 24 0.9449

26 1.0236 30 1.18111.5 Fine 23.5 0.9252

2 Fine 23 0.9055

26 1.5 Fine 24.5 0.9646

27

1 Fine 26 1.0236

28 1.1024 32 1.25981.5 Fine 25.5 1.0039

2 Fine 25 0.9843

3 Coarse 24 0.9449

28

1 Fine 27 1.063

1.5 Fine 26.5 1.0433

2 Fine 26 1.0236

30

1 Fine 29 1.1417

31 1.2205 35 1.3779

1.5 Fine 28.5 1.122

2 Fine 28 1.1024

3 Fine 27 1.063

3.5 Coarse 26.5 1.0433

321.5 Fine 30.5 1.2008

2 Fine 30 1.1811

33

1.5 Fine 31.5 1.2402

34 1.3386 38 1.4961

2 Fine 31 1.2205

3 Fine 30 1.1811

3.5 Coarse 29.5 1.1614

351.5 Fine 33.5 1.3189

2 Fine 33 1.2992




Thread Inserts

Fasteners







(mm) (mm)(65-75%

thread)

Decimal

Equiv.

Drill

Size

Decimal

Equiv.

Drill SizeDecimal

Equiv.

36

1.5 Fine 34.5 1.3583

37 1.4567 42 1.65352 Fine 34 1.3386

3 Fine 33 1.2992

4 Coarse 32 1.2598

39

1.5 Fine 37.5 1.4764

40 1.5748 45 1.77162 Fine 37 1.4567

3 Fine 36 1.4173

4 Coarse 35 1.378

40

1.5 Fine 38.5 1.5157

2 Fine 38 1.4961

3 Fine 37 1.4567

42

1.5 Fine 40.5 1.5945

43 1.6929 48 1.8898

2 Fine 40 1.5748

3 Fine 39 1.5354

4 Fine 38 1.4961

4.5 Coarse 37.5 1.4764

45

1.5 Fine 43.5 1.7126

46 1.811 52 2.0472

2 Fine 43 1.6929

3 Fine 42 1.6535

4 Fine 41 1.6142

4.5 Coarse 40.5 1.5945

48

1.5 Fine 46.5 1.8307

50 1.9685 56 2.2047

2 Fine 46 1.811

3 Fine 45 1.7717

4 Fine 44 1.7323

5 Coarse 43 1.6929

50

1.5 Fine 48.5 1.9094

2 Fine 48 1.8898

3 Fine 47 1.8504

52

1.5 Fine 50.5 1.9882

54 2.126 62 2.4409

2 Fine 50 1.9685

3 Fine 49 1.9291

4 Fine 48 1.8898

5 Coarse 47 1.8504

55

1.5 Fine 53.5 2.1063

2 Fine 53 2.0866

3 Fine 52 2.0472

4 Fine 51 2.0079



Quick Release Pins

Thread Inserts

Fasteners








(mm) (mm)(65-75%

thread)

Decimal

Equiv.

Drill

Size

Decimal

Equiv.

Drill SizeDecimal

Equiv.

56

1.5 Fine 54.5 2.1457

58 2.2835 66 2.5984

2 Fine 54 2.126

3 Fine 53 2.0866

4 Fine 52 2.0472

5.5 Coarse 50.5 1.9882

Any time two or more parts are assembled with a fastener, the strength of the fastener must beunderstood to maintain the integrity of the joint. Depending on the type of joint, the ability for thefastener to oppose external forces depends on the fastener material and size.

Figure 2: Shear vs. Tension Forces in Bolted Joint

Figure 2 illustrates two forces that exists in a typical compression joint of two parts using a bolt and nutor other similar fastener. The fastener may have to resist joint separation in one or both directions asindicated. An eye bolt mounting a pulley opposes axial forces of tension. While the fastener holdingthe pulley together resists stress in the mostly lateral direction as the rope or cable passes through it.Bolting the base of a robotic arm may have to resist external forces in both directions.

NOTE: More information on clamping forces used to hold two or more parts together can be found inthe Clamps and Working or Tooling Components Resource Guides.

NOTE: Equations Eq. 1, thru Eq. 3 are for estimating torque. For critical applications, refer to moredetailed and accurate calculations included in references listed in Table 18: {3} Machinery’sHandbook under Torque and Tension in Fasteners, {6} Mark’s Standard Handbook for MechanicalEngineers under Design of Bolted Joints and {7} Standard Handbook of Machine Design chapter22.

Values shown in Figure 2 vary with material type. Table 3 includes the mechanical properties illustratedin the chart by material type. Table 4 includes mechanical properties for various fasteners by gradeand class. For fasteners which do not have a grade or class designation, use Table 3 or refer to thereference material listed in Table 18 for more material properties and formulas. The values can also befound on the Internet. Product details can also be obtained by contacting Reid Customer Service at thetoll-free number listed at the bottom of the page or online at ReidSupply.com.

StressStress

S T

= Ultimate Tensile Strength

S Y

= Yield Strength

S P

= Proof Strength

S T

= Ultimate Tensile Strength

S Y

= Yield Strength

S P

= Proof Strength

T e n s i o n ( S t r e s s )

T e n s i o n ( S t r e s s )

Bolt Elongation (Strain)Bolt Elongation (Strain)

S T

S T

S Y

S Y

FractureFracture

Plastic RegionPlastic Region

YieldYield

00 E l a s t i c R e g i o n

E l a s t i c R e g i o n

S P

S P




Thread Inserts

Fasteners




T a b l e 3 : M e c h a n i c a l P r o p e r t i e s o f V a r i o u s M a t e r i a l s

M a t e r i a l 1

Y i e l d S t r e n g t h

U l t i m a t e S t r e s s

E l o n g a t i o n

E l a s t i c M

o d u l u s

S h e a r M o d u l u s

P o i s s o n ’ s

R a t i o

( k s i )

( M P a )

( k s i )

( M P a )

( % )

( k s i )

( G P a )

( k s i )

( G P a )

A l u m i n u m [ A l ]

2 . 9

2 0

1 0 . 2

7 0

6 0

1 0 2 0 0

7 0

3 7 7 0

2 6

0 . 3 3

A l u m i n u m A l l o y

5 - 7 2

3 5 - 5 0 0

1 5 - 8 0

1 0 0 - 5 5 0

1 - 4 5

1 0 2 0 0 - 1 1 5 0 0

7 0 - 7 9

3 7 7 0 - 4 3 5 0

2 6 - 3 0

0 . 3 3

B r a s s

1 0 - 7 2

7 0 - 5 5 0

2 9 - 9 0

2 0 0 - 6 2 0

4 - 6 0

1 3 9 0 0 - 1 6 0 0 0

9 6 - 1 1 0

5 2 2 0 - 5 9 5 0

3 6 - 4 1

0 . 3 4

B r a s s ; N o v a l

2 5 - 6 0

1 7 0 - 4 1 0

6 0 - 8 5

4 1 0 - 5 9 0

1 5 - 5 0

1 4 5 0 0

1 0 0

5 6 6 0

3 9

0 . 3 4

B r a s s ; R e d ( 8 0 % C u , 2 0 %

Z n )

1 3 - 6 8

9 0 - 4 7 0

4 4 - 8 5

3 0 0 - 5 9 0

4 - 5 0

1 4 5 0 0

1 0 0

5 6 6 0

3 9

0 . 3 4

B r i c k ( C o m p r e s s i o n )

-

-

1 - 1 0

7 . 0 - 7 0

-

1 4 5 0 - 3 4 8 0

1 0 - 2 4

-

-

-

B r o n z e ; R e g u l a r

1 2 - 1 0 0

8 2 - 6 9 0

2 9 - 1 2 0

2 0 0 - 8 3 0

5 - 6 0

1 3 9 0 0 - 1 7 4 0 0

9 6 - 1 2 0

5 2 2 0 - 6 3 8 0

3 6 - 4 4

0 . 3 4

B r o n z e ; M a n g a n e s e

2 5 - 6 5

1 7 0 - 4 5 0

6 5 - 9 0

4 5 0 - 6 2 0

1 0 - 3 5

1 4 5 0 0

1 0 0

5 6 6 0

3 9

0 . 3 4

C a r b o n [ C ]

1 0 0 0

6 . 9

-

-

-

C e r a m i c

4 3 5 0 0 - 5 8 0 0 0

3 0 0 - 4 0 0

-

-

-

C o n c r e t e ( C o m p r e s s i o n )

-

-

1 . 4 5 - 1 0

1 0 - 7 0

-

2 6 1 0 - 4 3 5 0

1 8 - 3 0

-

-

0 . 1 - 0 . 2

C o p p e r [ C u ]

8 - 4 8

5 5 - 3 3 0

3 3 - 5 5

2 3 0 - 3 8 0

1 0 - 5 0

1 6 0 0 0 - 1 7 4 0 0

1 1 0 - 1 2 0

5 8 0 0 - 6 8 2 0

4 0 - 4 7

0 . 3 3 - 0 . 3 6

C o p p e r A l l o y

1 1 0

7 6 0

1 2 0

8 3 0

4

1 7 4 0 0

1 2 0

6 8 2 0

4 7

-

C o r k

-

-

-

-

0

G l a s s

-

-

4 . 4 - 1 4 5

3 0 - 1 0 0 0

-

6 9 6 0 - 1 2 0 0 0

4 8 - 8 3

2 7 6 0 - 4 9 3 0

1 9 - 3 4

0 . 2 - 0 . 2 7

G o l d

1 2 0 0 0

8 3

-

-

0 . 4 4

I r o n ( C a s t )

1 8 - 4 2

1 2 0 - 2 9 0

1 0 - 7 0

6 9 - 4 8 0

0 - 1

1 2 0 0 0 - 2 4 7 0 0

8 3 - 1 7 0

4 6 4 0 -

1 0 0 0 0

3 2 - 6 9

0 . 2 - 0 . 3

I r o n ( W r o u g h t )

3 0

2 1 0

4 9

3 4 0

3 5

2 7 6 0 0

1 9 0

1 0 9 0 0

7 5

0 . 3

M a g n e s i u m [ M g ]

2 . 9 - 1 0

2 0 - 7 0

1 5 - 2 5

1 0 0 - 1 7 0

5 - 1 5

5 9 5 0

4 1

2 1 8 0

1 5

0 . 3 5

M a g n e s i u m A l l o y

1 2 - 4 0

8 0 - 2 8 0

2 0 - 4 9

1 4 0 - 3 4 0

2 - 2 0

6 5 3 0

4 5

2 4 7 0

1 7

0 . 3 5

M o n e l ( 6 7 % N i , 3 0 % C u )

2 5 - 1 6 0

1 7 0 - 1 1 0 0

6 5 - 1 7 4

4

5 0 - 1 2 0 0

2 - 5 0

2 4 7 0 0

1 7 0

9 5 7 0

6 6

0 . 3 2

N i c k e l [ N i ]

2 0 - 9 0

1 4 0 - 6 2 0

4 5 - 1 1 0

3 1 0 - 7 6 0

2 - 5 0

3 0 5 0 0

2 1 0

1 1 6 0 0

8 0

0 . 3 1

N y l o n ; P o l y a m i d e

-

-

6 - 1 0

4 0 - 7 0

5 0

3 0 5 - 4 0 6

2 . 1 - 2 . 8

-

-

0 . 4

P l a t i n u m [ P t ]

2 1 0 0 0

1 4 5

-

-

0 . 3 8

R u b b e r

0 . 1 5 - 1

1 . 0 - 7 . 0

1 - 2 . 9

7 . 0 - 2 0

1 0 0 - 8 0 0

0 . 1 0 2 - 0 . 5 8 0

7 . 0 × 1 0 - 4

- 4 . 0 × 1 0 - 3

0 . 0 2 9

- 0 . 1 4 5

2 . 0 × 1 0 - 4

- 1 . 0 × 1 0 - 3

0 . 4 5 - 0 . 5

S i l v e r [ A g ]

1 1 0 0 0

7 6

-

-

-

S o l d e r ; T i n - L e a d

-

-

1 . 7 - 7 . 8

1 2 - 5 4

5 5 - 3 0

2 6 1 0 - 5 0 8 0

1 8 - 3 5

-

-

-

S t e e l

4 0 - 2 3 2

2 8 0 - 1 6 0 0

4 9 - 2 7 6

3

4 0 - 1 9 0 0

3 - 4 0

2 7 6 0 0 - 3 0 5 0 0

1 9 0 - 2 1 0

1 0 9 0 0

- 1 1 6 0 0

7 5 - 8 0

0 . 2 7 - 0 . 3

S t o n e ; G r a n i t e

( C o m p r e s s i o n )

-

-

1 0 - 4 0

7 0 - 2 8 0

-

5 8 0 0 - 1 0 2 0 0

4 0 - 7 0

-

-

0 . 2 - 0 . 3



Quick Release Pins

Thread Inserts

Fasteners





M a t e r i a l 1

Y i e l d S t r e n g t h

U l t i m a t e S t r e s s

E l o n g a t i o n

E l a s t i c M

o d u l u s

S h e a r M o d u l u s

P o i s s o n ’ s

R a t i o

( k s i )

( M P a )

( k s i )

( M P a )

( % )

( k s i )

( G P a )

( k s i )

( G P a )

S t o n e ; L i m e s t o n e


-

-

2 . 9 - 2 9

2 0 - 2 0 0

-

2 9 0 0 - 1 0 2 0 0

2 0 - 7 0

-

-

0 . 2 - 0 . 3

S t o n e ; M a r b l e


-

-

7 . 2 5 - 2 6

5 0 - 1 8 0

-

7 2 5 0 - 1 4 5 0 0

5 0 - 1 0 0

-

-

0 . 2 - 0 . 3

T i n [ S n ]

6 0 9 0

4 2

-

-

0 . 3 6

T i t a n i u m [ T i ]

-

-

7 2 . 5

5 0 0

2 5

1 6 0 0 0

1 1 0

5 8 0 0

4 0

0 . 3 3

T i t a n i u m A l l o y

-

-

1 3 1 - 1 4 1

9 0 0 - 9 7 0

1 0

1 6 0 0 0 - 1 7 4 0 0

1 1 0 - 1 2 0

5 6 6 0 - 6 3 8 0

3 9 - 4 4

0 . 3 3

T u n g s t e n [ W ]

-

-

2 0 3 - 5 8 0

1 4 0 0 - 4 0 0 0

0 - 4

W o o d ; A s h ( B e n d i n g )

6 - 1 0

4 0 - 7 0

7 . 2 5 - 1 4 . 5

5 0 - 1 0 0

-

1 4 5 0 - 1 6 0 0

1 0 - 1 1

-

-

-

W o o d ; D o u g l a s F i r

( B e n d i n g )

4 . 4 - 7 . 2 5

3 0 - 5 0

7 . 2 5 - 1 2

5 0 - 8 0

-

1 6 0 0 - 1 8 9 0

1 1 - 1 3

-

-

-

W o o d ; O a k ( B e n d i n g )

6 - 8 . 7

4 0 - 6 0

7 . 2 5 - 1 4 . 5

5 0 - 1 0 0

-

1 6 0 0 - 1 7 4 0

1 1 - 1 2

-

-

-

W o o d ; S o u t h e r n P i n e

( B e n d i n g )

6 - 8 . 7

4 0 - 6 0

7 . 2 5 - 1 4 . 5

5 0 - 1 0 0

-

1 6 0 0 - 2 0 3 0

1 1 - 1 4

-

-

-

Z i n c [ Z n }

-

-

-

-

0 . 2 5

N O T E

1 )

M o r e e x a c

t v a l u e s c a n b e f o u n d i n t h e r e f e r e n c e m a t e r i a l l i s

t e d i n T a b l e 1 8 .

T a b l e 4 : A S T M ,

S A E a n d I S O G r a d e M a r k i n g s a n d M e c h a n i c a l P

r o p e r t i e s f o r S t e e l F a s t e n e r s

G r a d e 1

o r

C l a s s

I D M a r k

S p e c i fi c a t i o n

F a s t e n e r

T y p e

M a t e r i a l

N o m i n a l

S i z e R a n g e

M e c h a n i c a l P r o p e r t i e s

P r o o f L o a d 2

Y i e l d S t r e n g t h M i n

T e n s i l e S t r e n g t h M i n

i n .

p s i

M P a

p s i

M P a

p s i

M P a

N o G r a d e

M a r k

S A E J 4 2 9

G r a d e 1

B o l t s ,

S c r e w s ,

S t u d s

L o w o r M e d i u m C a r b o n S

t e e l

1 / 4 t h r u 1 - 1 / 2

3 3 , 0 0 0

2 2 8

3 6 , 0 0 0

2 4 8

6 0 , 0 0 0

2 2 8

A S T M A 3 0 7

G r a d e s A & B

L o w C a r b o n S t e e l

1 / 4 t h r u 4

- -

- -

- -

- -

S A E J 4 2 9

G r a d e 2


t e e l

1 / 4 t h r u 3 / 4

5 5 , 0 0 0

3 7 9

5 7 , 0 0 0

3 9 3

7 4 , 0 0 0

5 1 0

O v e r 3 / 4 t o

1 - 1 / 2

3 3 , 0 0 0

2 2 8

3 6 , 0 0 0

2 4 8

6 0 , 0 0 0

4 1 4

N o G r a d e

M a r k

S A E J 4 2 9

G r a d e 4

S t u d s

M e d i u m C a r b o n C o l d D r a w n

S t e e l

1 / 4 t h r u 1 - 1 / 2

- -

- -

1 0 0 , 0 0 0

6 8 9

1 1 5 , 0 0 0

7 9 3




Thread Inserts

Fasteners




G r a d e 1

o r

C l a s s

I D M a r k


F a s t e n e r

T y p e

M a t e r i a l

N o m i n a l

S i z e R a n g e


P r o o f L o a d 2



i n .

p s i

M P a

p s i

M P a

p s i

M P a

B 5

A S T M A 1 9 3

G r a d e B 5

A I S I 5 0 1

1 / 4 T h r u 4

- -

- -

8 0 , 0 0 0

5 5 2

1 0 0 , 0 0 0

6 8 9

B 6

A S T M A 1 9 3

G r a d e B 6

A I S I 4 1 0

- -

- -

8 5 , 0 0 0

5 8 6

1 1 0 , 0 0 0

7 5 8

B 7

A S T M A 1 9 3

G r a d e B 7

A I S I 4 1 4 0 , 4 1 4 2 , o r 4 1 0

5

1 / 4 t h r u 2 - 1 / 2

O v e r 2 - 1 / 2

t h r u 4

O v e r 4 t h r u 7

- -

- -

1 0 5 , 0 0 0

7 2 4

1 2 5 , 0 0 0

8 6 2

9 5 , 0 0 0

6 5 5

1 1 5 , 0 0 0

7 9 3

7 5 , 0 0 0

5 1 7

1 0 0 , 0 0 0

6 8 9

B 1 6

A S T M A 1 9 3

G r a d e B 1 6

C r M o V a A l l o y S t e e l

- -

- -

1 0 5 , 0 0 0

7 2 4

1 2 5 , 0 0 0

8 6 2

9 5 , 0 0 0

6 5 5

1 1 5 , 0 0 0

7 9 3

8 5 , 0 0 0

5 8 6

1 0 0 , 0 0 0

6 8 9

B 8

A S T M A 1 9 3

G r a d e B 8

A I S I 3 0 4

1 / 4 a n d l a r g e r

- -

- -

3 0 , 0 0 0

2 0 7

7 5 , 0 0 0

5 1 7

B 8 C

A S T M A 1 9 3

G r a d e B 8 C

A I S I 3 4 7

B 8 M

A S T M A 1 9 3

G r a d e B 8 M

A I S I 3 1 6

B 8 T

A S T M A 1 9 3

G r a d e B 8 T

B o l t s ,

S c r e w s ,

S t u d s f o r

H i g h - T e m p .

S e r v i c e

A I S I 3 2 1

1 / 4 a n d l a r g e r

- -

- -

3 0 , 0 0 0

2 0 7

7 5 , 0 0 0

5 1 7

B 8

A S T M A 1 9 3

G r a d e B 8

A I S I 3 0 4

S t r a i n H a r d e n e d

1 / 4 t h r u 3 / 4

O v e r 3 / 4 t h r u 1

O v e r 1 t h r u

1 - 1 / 4

O v e r 1 - 1 / 4 t h r u

1 - 1 / 2

- -

- -

1 0 0 , 0 0 0

6 8 9

1 2 5 , 0 0 0

8 6 2

B 8 C

A S T M A 1 9 3

G r a d e B 8 C

A I S I 3 4 7


8 0 , 0 0 0

5 5 2

1 1 5 , 0 0 0

7 9 3

6 5 , 0 0 0

4 4 8

1 0 5 , 0 0 0

7 2 4

5 0 , 0 0 0

3 4 5

1 0 0 , 0 0 0

6 8 9

B 8 M

A S T M A 1 9 3

G r a d e B 8 M

B o l t s ,

S c r e w s ,

S t u d s f o r

H i g h - T e m p .

S e r v i c e

A I S I 3 1 6


1 / 4 t h r u 3 / 4

O v e r 3 / 4 t h r u 1

O v e r 1 t h r u

1 - 1 / 4

O v e r 1 - 1 / 4 t h r u

1 - 1 / 2

- -

- -

9 5 , 0 0 0

6 5 5

1 1 0 , 0 0 0

7 5 8

8 0 , 0 0 0

5 5 2

1 0 0 , 0 0 0

6 8 9

6 5 , 0 0 0

4 4 8

9 5 , 0 0 0

6 5 5

5 0 , 0 0 0

3 4 5

9 0 , 0 0 0

6 2 1

B 8 T

A S T M A 1 9 3

G r a d e B 8 T

A I S I 3 2 1


- -

- -

1 0 0 , 0 0 0

6 8 9

1 2 5 , 0 0 0

8 6 2

8 0 , 0 0 0

5 5 2

1 1 5 , 0 0 0

7 9 3

6 5 , 0 0 0

4 4 8

1 0 5 , 0 0 0

7 2 4

5 0 , 0 0 0

3 4 5

1 0 0 , 0 0 0

6 8 9



Quick Release Pins

Thread Inserts

Fasteners





G r a d e 1

o r

C l a s s

I D M a r k


F a s t e n e r

T y p e

M a t e r i a l

N o m i n a l

S i z e R a n g e


P r o o f L o a d 2



i n .

p s i

M P a

p s i

M P a

p s i

M P a

L 7

A S T M A 3 2 0

G r a d e L 7

B o l t s ,

S c r e w s ,

S t u d s f o r

L o w - T e m p .

S e r v i c e

A I S I 4 1 4 0 ,

4 1 4 2 o r 4 1 4 5

1 / 4 t h r u 2 - 1 / 2

- -

- -

1 0 5 , 0 0 0

7 2 4

1 2 5 , 0 0 0

8 6 2

L 7 A

A S T M A 3 2 0

G r a d e L 7 A

A I S I 4 0 3 7

L 7 B

A S T M A 3 2 0

G r a d e L 7 B

A I S I 4 1 3 7

L 7 C

A S T M A 3 2 0

G r a d e L C 7

A I S I 8 7 4 0

L 4 3

A S T M A 3 2 0

G r a d e L 4 3

A I S I 4 3 4 0

1 / 4 t h r u 4

- -

- -

1 0 5 , 0 0 0

7 2 4

1 2 5 , 0 0 0

8 6 2

B 8

A S T M A 3 2 0

G r a d e B 8

A I S I 3 0 4

1 / 4 a n d l a r g e r

- -

- -

3 0 , 0 0 0

7 2 4

7 5 , 0 0 0

7 2 4

B 8 C

A S T M A 3 2 0

G r a d e B 8 C

A I S I 3 4 7

B 8 T

A S T M A 3 2 0

G r a d e B 8 T

A I S I 3 2 1

B 8 F

A S T M A 3 2 0

G r a d e B 8 F

A I S I 3 0 3

o r 3 0 3 S e

B 8 M

A S T M A 3 2 0

G r a d e B 8 M

A I S I 3 1 6

B 8

A S T M A 3 2 0

G r a d e B 8

A I S I 3 0 4

1 / 4 t h r u 3 / 4

- -

- -

1 0 0 , 0 0 0

6 8 9

1 0 0 , 0 0 0

6 8 9

B 8 C

A S T M A 3 2 0

G r a d e B 8 C

A I S I 3 4 7

O v e r 3 / 4 t h r u 1

- -

- -

8 0 , 0 0 0

5 5 2

8 0 , 0 0 0

5 5 2

B 8 F

A S T M A 3 2 0

G r a d e B 8 F

A I S I 3 0 3

o r 3 0 3 S e

O v e r 1 t h r u

1 - 1 / 4

- -

- -

6 5 , 0 0 0

4 4 8

6 5 , 0 0 0

4 4 8

B 8 M

A S T M A 3 2 0

G r a d e B 8 M

A I S I 3 1 6

O v e r 1 - 1 / 4 t h r u

1 - 1 / 2

- -

- -

5 0 , 0 0 0

3 4 5

5 0 , 0 0 0

3 4 5

B 8 T

A S T M A 3 2 0

G r a d e B 8 T

A I S I 3 2 1

S A E J 4 2 9

G r a d e 5

B o l t s ,

S c r e w s ,

S t u d s

M e d i u m C a r b o n S t e e l ,

Q u e n c h e d a n d T e m p e r e d

1 / 4 t h r u 1

8 5 , 0 0 0

5 8 6

9 2 , 0 0 0

6 3 4

1 2 0 , 0 0 0

8 2 7

O v e r 1 t o 1 - 1 / 2

7 4 , 0 0 0

5 1 0

8 1 , 0 0 0

5 5 8

1 0 5 , 0 0 0

7 2 4

A S T M A 4 4 9

1 / 4 t h r u 1

8 5 , 0 0 0

5 8 6

9 2 , 0 0 0

6 3 4

1 2 0 , 0 0 0

8 2 7

O v e r 1 t o 1 - 1 / 2

7 4 , 0 0 0

5 1 0

8 1 , 0 0 0

5 5 8

1 0 5 , 0 0 0

7 2 4

O v e r 1 - 1 / 2

t h r u 3

5 5 , 0 0 0

3 7 9

5 8 , 0 0 0

4 0 0

9 0 , 0 0 0

6 2 1

S A E J 4 2 9

G r a d e 5 . 1

S e m s


t e e l ,


N o . 6 t h r u 3 / 8

8 5 , 0 0 0

5 8 6

- -

- -

1 2 0 , 0 0 0

8 2 7




Thread Inserts

Fasteners




G r a d e 1

o r

C l a s s

I D M a r k


F a s t e n e r

T y p e

M a t e r i a l

N o m i n a l

S i z e R a n g e


P r o o f L o a d 2



i n .

p s i

M P a

p s i

M P a

p s i

M P a

S A E J 4 2 9

G r a d e 5 . 2

B o l t s ,

S c r e w s ,

S t u d s

L o w C a r b o n M a r t e n s i t i c

S t e e l , Q u e n c h e d a n d

T e m p e r e d

1 / 4 t h r u 1

8 5 , 0 0 0

5 8 6

9 2 , 0 0 0

6 3 4

1 2 0 , 0 0 0

8 2 7

A 3 2 5

A S T M A 3 2 5

T y p e 1

H i g h

S t r e n g t h

S t r u c t u r a l

B o l t s



1 / 2 t h r u 1

8 5 , 0 0 0

5 8 6

9 2 , 0 0 0

6 3 4

1 2 0 , 0 0 0

8 2 7

1 - 1 / 8 t h r u 1 - 1 / 2

7 4 , 0 0 0

5 1 0

8 1 , 0 0 0

5 5 8

1 0 5 , 0 0 0

7 2 4

A 3 2 5

A S T M A 3 2 5

T y p e 2

L o w C a r b o n M a r t e n s i t i c

S t e e l , Q u e n c h e d a n d

T e m p e r e d

1 / 2 t h r u 1

8 5 , 0 0 0

5 8 6

9 2 , 0 0 0

6 3 4

1 2 0 , 0 0 0

8 2 7

A 3 2 5

A S T M A 3 2 5

T y p e 3

A t m o s p h e r i c C o r r o s i o n

R e s i s t i n g S t e e l , Q u e n c h

e d

a n d T e m p e r e d

1 / 2 t h r u 1

8 5 , 0 0 0

5 8 6

9 2 , 0 0 0

6 3 4

1 2 0 , 0 0 0

8 2 7

1 - 1 / 8 t h r u 1 - 1 / 2

7 4 , 0 0 0

5 1 0

8 1 , 0 0 0

5 5 8

1 0 5 , 0 0 0

7 2 4

B B

A S T M A 3 5 4

G r a d e B B

B o l t s ,

S t u d s

A l l o y S t e e l , Q u e n c h e d a

n d

T e m p e r e d

1 / 4 t h r u 2 - 1 / 2

2 - 3 / 4 t h r u 4

8 0 , 0 0 0

5 5 2

8 3 , 0 0 0

5 7 2

1 0 5 , 0 0 0

7 2 4

7 5 , 0 0 0

5 1 7

7 8 , 0 0 0

5 3 8

1 0 0 , 0 0 0

6 8 9

B C

A S T M A 3 5 4

G r a d e B C

1 0 5 , 0 0 0

7 2 4

1 0 9 , 0 0 0

7 5 2

1 2 5 , 0 0 0

8 6 2

9 5 , 0 0 0

6 5 5

9 9 , 0 0 0

6 8 3

1 1 5 , 0 0 0

7 9 3

S A E J 4 2 9

G r a d e 7

B o l t s ,

S c r e w s

M e d i u m C a r b o n A l l o y S t e e l ,

Q u e n c h e d a n d T e m p e r e d 4

1 / 4 t h r u 1 - 1 / 2

1 0 5 , 0 0 0

7 2 4

1 1 5 , 0 0 0

7 9 3

1 3 3 , 0 0 0

9 1 7

S A E J 4 2 9

G r a d e 8

B o l t s ,

S c r e w s ,

S t u d s

M e d i u m C a r b o n A l l o y S t e e l ,


1 / 4 t h r u 1 - 1 / 2

1 2 0 , 0 0 0

8 2 7

1 3 0 , 0 0 0

8 9 6

1 5 0 , 0 0 0

1 , 0 3 4

A S T M A 3 5 4

G r a d e B D


n d

T e m p e r e d 4

N o G r a d e

M a r k

S A E J 4 2 9

G r a d e 8 . 1

S t u d s

M e d i u m C a r b o n A l l o y o

r

S A E 1 0 4 1 M o d i fi e d E l e v a

t e d

T e m p e r a t u r e D r a w n S t e

e l

1 / 4 t h r u 1 - 1 / 2

1 2 0 , 0 0 0

8 2 7

1 3 0 , 0 0 0

8 9 6

1 5 0 , 0 0 0

1 , 0 3 4

A 4 9 0

A S T M A 4 9 0

H i g h

S t r e n g t h

S t r u c t u r a l

B o l t s


n d

T e m p e r e d

1 / 2 t h r u 1 - 1 / 2

1 2 0 , 0 0 0

8 2 7

1 3 0 , 0 0 0

8 9 6

1 5 0 , 0 0 0 m i n

1 7 0 , 0 0 0 m a x

1 , 0 3 4 m i n

1 , 1 7 0 m a x



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Thread Inserts

Fasteners





G r a d e 1

o r

C l a s s

I D M a r k


F a s t e n e r

T y p e

M a t e r i a l

N o m i n a l

S i z e R a n g e


P r o o f L o a d 2



i n .

p s i

M P a

p s i

M P a

p s i

M P a

N o G r a d e

M a r k

I S O R 8 9 8

C l a s s 4 . 6

B o l t s ,

S c r e w s ,

S t u d s



A l l S i z e s t h r u 4 0

m m

3 2 , 6 3 3

2 2 5

2 9 , 5 8 8

2 0 4

5 8 , 0 1 5

4 0 0

N o G r a d e

M a r k

I S O R 8 9 8

C l a s s 5 . 8

5 5 , 1 1 4

3 8 0

6 0 , 9 1 6

4 2 0

7 5 , 4 2 0

5 2 0

8 . 8 o r 8 8

I S O R 8 9 8

C l a s s 8 . 8


n d

T e m p e r e d

8 7 , 0 2 3

6 0 0

9 2 , 8 2 4

6 4 0

1 2 0 , 3 8 1

8 3 0

1 0 . 9 o r

1 0 9

I S O R 8 9 8

C l a s s 1 0 . 9

1 2 0 , 3 8 1

8 3 0

1 3 6 , 3 3 5

9 4 0

1 5 0 , 8 3 9

1 , 0 4 0

N O T E S :

1 )

O n l y s a m p l e h e x h e a d s a r e i n c l u d e d w i t h s p e c i fi c m a r k i n g s . O t h e r w i s e h e a d s w i l l b e b l a n k .

2 )

A l s o k n o w

n a s P r o o f S t r e n g t h o r P r o o f L o a d S t r e s s .




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T a b l e 5 : M e c h a n i c a l S p e c i fi c a t i o n s f o r C a r b o n S t e e l M e t r i c F a s t e

n e r s w i t h E x t e r n a l T h r e a d s

P r o p e r t y

C l a s s

D e s i g n a t i o n

N o m i n a l

S i z e o f

P r o d u c t

M a t e r i a l a n d T r e a t m e n t

M e c h a n i c a l R e q u i r e m e n t s

P r o p e r t y

C l a s s

I d e n t .

M a r k i n g

P r o o f

L o a d

S t r e s s

M i n .

Y i e l d

S t r e n g t h

M i n .

T e n s i l e

U l t i m a t e

S t r e n g t h

P r o d .

H a r d n e s s ,

R o c k w e l l

S u r f a c e

C o r e

M P a

M P a

M P a

M a x .

M i n .

M a x .

4 . 6

M 5 - M 1 0 0

l o w o r m e d i u m c a r b o n s t e e l

2 2 5

2 4 0

4 0 0

- -

B 6 7

B 9 5

4 . 6

4 . 8

M 1 . 6 - M 1 6

l o w o r m e d i u m c a r b o n

s t e e l , f u l l y o r p a r t i a l l y

a n n e a l e d

3 1 0

3 4 0

4 2 0

- -

B 7 1

B 9 5

4 . 8

5 . 8

M 5 - M 2 4

l o w o r m e d i u m c a r b o n

s t e e l , c o l d w o r k e d

3 8 0

4 2 0

5 2 0

- -

B 8 2

B 9 5

5 . 8

8 . 8

M 1 6 - M 7 2

m e d i u m c a r b o n s t e e l ,

q u e n c h e d a n d t e m p e r e d

6 0 0

6 4 0

8 3 0

3 0 N 5 6

C 2 3

C 3 4

8 . 8

A 3 2 5 M T y p e 1

M 1 6 - M 3 6

A 3 2 5 M

8 S

8 . 8

M 1 6 - M 3 6

l o w c a r b o n b o r o n s t e e l ,


6 0 0

6 4 0

8 3 0

3 0 N 5 6

C 2 3

C 3 4

8 . 8

A 3 2 5 M T y p e 2

A 3 2 5 M

8 S

A 3 2 5 M T y p e 3

M 1 6 - M 3 6

a t m o s p h e r i c c o r r o s i o n

r e s i s t a n t s t e e l , q u e n c h e d

a n d t e m p e r e d

6 0 0

6 4 0

8 3 0

3 0 N 5 6

C 2 3

C 3 4

A 3 2 5 M

8 S 3

9 . 8

M 1 . 6 - M 1 6



6 5 0

7 2 0

9 0 0

3 0 N 5 8

C 2 7

C 3 6

9 . 8

9 . 8

M 1 . 6 - M 1 6



6 5 0

7 2 0

9 0 0

3 0 N 5 8

C 2 7

C 3 6

9 . 8

1 0 . 9

M 5 - M 2 0



8 3 0

9 4 0

1 0 4 0

3 0 N 5 9

C 3 3

C 3 9

1 0 . 9

1 0 . 9

M 5 - M 1 0 0

m e d i u m c a r b o n a l l o y s t e e l ,


8 3 0

9 4 0

1 0 4 0

3 0 N 5 9

C 3 3

C 3 9

1 0 . 9

A 4 9 0 M T y p e 1

M 1 2 - M 3 6

A 4 9 0 M

1 0 S

1 0 . 9

M 5 - M 3 6



8 3 0

9 4 0

1 0 4 0

3 0 N 5 9

C 3 3

C 3 9

1 0 . 9

A 4 9 0 M T y p e 2

M 1 2 - M 3 6

A 4 9 0 M

1 0 S

A 4 9 0 M T y p e 3

M 1 2 - M 3 6

a t m o s p h e r i c c o r r o s i o n

r e s i s t a n t s t e e l , q u e n c h e d

a n d t e m p e r e d

8 3 0

9 4 0

1 0 4 0

3 0 N 5 9

C 3 3

C 3 9

A 4 9 0 M

1 0 S 3

1 2 . 9

M 1 . 6 -

M 1 0 0

a l l o y s t e e l , q u e n c h e d a n d

t e m p e r e d

9 7 0

1 1 0 0

1 2 2 0

3 0 N 6 3

C 3 8

C 4 4

1 2 . 9



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In Figure 2, tensile forces continuously work against the joint axially in an attempt to pull it apart. At thesame time, shearing forces may work against each other due to motion or vibration in the joint. Tensileforces are necessary to take advantage of friction and generate enough clamping force to maintain jointintegrity. Anytime a fastener is used, forces are built up and stored in the joint that continuously work toboth hold and pull the joint apart. External forces like vibration or rotation in the joint can allow the nut

or bolt to turn and loosen the joint. To prevent joint separation, vibration proof washers or nuts can beused.

During assembly, as the joint is tightened (refer to Figure 2 graph), contact is made between allcomponents in the joint. At this point (0 in the graph), a preload builds within the bolt body. Astightening continues, friction builds between the threads and assembled components. A clamping forceis generated that compresses all components between the bolt head and nut and the bolt stretches inopposition to the pressure. The torque necessary to continue turning the nut increases as the tensionbuilds. While bolt elongation remains in the Elastic Region of Figure 2, the bolt length will return tonormal as tension is decreased.

At the Yield point, continued rotation stretches the elongated bolt to the point of no return (PlasticRegion in Figure 2 graph) and any relaxation of the tension will not return the elongated bolt to itsprevious length or the threads to their original state. This point is known as the Yield Strength (S

Y ) of the

fastener. Continued tension in the axial direction eventually stretches the fastener to the Ultimate TensileStrength (S

T ) where it weakens and finally fractures. Proof Load (S

P ) is a value slightly lower than Yield

Strength before a fastener transitions into the Plastic Region, Figure 2.

Table 3 includes specifications for metric fasteners. Specifications for inch fasteners are listed in theReid Supply catalog and in many of the reference manuals listed in Table 18. These specificationsinclude Yield Strength, Ultimate Tensile Strength and Proof Load for fasteners by grade and class. Thesevalues are used in design considerations to estimate Stress () and Torque (T ) for bolts, screws andrivets.

To estimate Stress and Torque, cross-sectional area must be determined for the fastener. If the fastenerdoes not contain threads, the cross-sectional area is calculated using Eq. 1 {7} (more detailed formulasare included in the Machinery’s Handbook {3}):

Eq. 1A: Cross-sectional Area of Non-threaded Fastener

2

2

2

42

d d

r A B

(Standard formula for area of a circle)

Where: A B

= Cross sectional area of fastener body with no threads

d = Fastener body diameter

r = Fastener radius = d / 2

If the fastener is threaded, the cross-sectional area becomes:

Eq. 1B: Cross-sectional Area of Threaded Fastener - Inch

2

9743.0

4

nd A

S

Eq. 1C: Cross-sectional Area of Threaded Fastener - Metric

29382.04

P d AS

Where: AS

= Cross sectional area of fastener

d = Fastener nominal diameter

n = Number of threads per inch

P = Thread pitch = 1/n

Tensile Force Tensile Force




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Use Eq. 2A {6} to determine the current preload (clamping force) of a fastener relative to a change infastener length. The formula is only valid if the fastener is within the Elastic Region of Figure 2. Eq. 2Bcan be used to estimate the Preload Force ( F

P ) referenced to Proof Load (S

P ).

Eq. 2A: Determining Fastener Preload, Method 1

l

AEe F P

Where: F P

= Preload force

A = Cross-sectional area (for a circle, A=r 2) of fastener (accepted values can befound in MIL-S-8879C)

E = Modulus of elasticity for fastener material found in references listed inTable 18

e = To measure elongation, must be accessible from both ends

l = Original length of bolt

Eq. 2B: Estimating Fastener Preload, Method 2

F P

= S P A

S

Where: F P

= Preload force

S P

= Proof Load by grade or class found in Table 4, Table 5 or references listed inTable 19

AS

= Stress Area of threaded fastener from Eq. 2; if unthreaded, use Eq. 1

With a Preload established, the Torque required to obtain this preload can be estimated using Eq. 3. Theequation allows estimation of the amount of torque to obtain the Proof Load, but that would not allow forexternal forces which may add to existing preload and compromise joint integrity. Adding a safety factorallows for any external forces. If the joint is static, a safety factor of 90% is typical. For dynamic joints, a75% safety factor is acceptable.

Should the joint include a gasket, over-torquing the fastener can compress and damage the gasket.Proof Load (S P ) may be substituted with a lesser predetermined preload or clamping force to better match

the application. Vibration proof washers or nuts can also be used, if necessary.

For Eq. 3, a Torque Coefficient ( K ) is used which represents an experimental value derived fromcoefficient of friction between materials and other factors. This value is discussed in detail in referencematerial found in Table 18 where formulas are given to more accurately calculate this value. Table 6includes some typical values of K .

Table 6: Torque Coefficients ( K ) for Typical Fastener Materials

Material Size Range K *

Cadmium-plated 1/4 - 1 0.16

Lubricated 1/4 - 1 0.18

Mild Steel 1/4 - 1 0.2

Non-plated Black Finish 1/4 - 1 0.3

Zinc-plated 1/4 - 1 0.2

* Torque coefficient specified by bolt, nut or lubricant manufacturer. K -values for lubricants are

listed in the Metalworking Resource Guide.



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Eq. 3: Estimating Fastener Torque

T = KDF P S

F

Where: T = Estimated torque K = Torque coefficient from Table 6

D = Fastener nominal diameter

F P

= Preload force calculated from Eq. 2A or Eq. 2B

S F

= Safety factor, typical values are 1.0 if not required, 0.9 for a static joint and0.75 for a dynamic joint

NOTE: Adding lubrication will decrease the friction between threads and the surface of the fastenerbody. If the wrong value for K can result in over-torquing of the fastener according to Eq. 3.

Eq. 3 is only valid for the linear Elastic Region shown in Figure 2.

If there is any uncertainty about formulas and the results, contact Reid Customer Service usingthe toll-free number at the bottom of the page or online at ReidSupply.com.

Example 1: Estimating Torque for Inch Fastener:

Estimating torque for a 5/8 (0.625) x 11 hex bolt x 2 inch long, Grade 5 that is used to fasten a pivot joinwith a bushing. Referring to one of the reference documents in Table 18 or the Reid Supply catalog, wesee Grade 5 bolts and screws have a Proof Load (S

P ) of 85,000 psi, Tensile Strength (S

T ) of 120,000 psi

and a Yield Strength (S Y ) of 92,000 psi.

Using Eq. 1B, the Stress Area is:

226.011

9743.0625.07854.0

9743.0

4

22

nd A

S

in2

Applying Eq. 2B, Preload Force is:

F P

= S P A

S = 85,000 psi x 0.226 in2 = 19,210 lbs.

Using Eq. 3, torque can be calculated. Coefficient of friction = 0.2 for non lubricated mild steel, thetorque is (A Safety Factor of 75% is used for a dynamic joint):

T = KDF P S

F = 0.2 x 0.625 in x 19210 lbs x 75% = 1800 in-lbs = 150 ft-lbs

Example 2: Estimating Torque for Metric Fastener

Estimating torque for an M10 x 1.5 hex bolts, Class 8.8 that are used to fasten a square lid on acontainer. Referring to one of the reference documents in Table 18 or the Reid Supply catalog, we seeClass 8.8 bolts and screws have a Proof Load (S

P ) of 600 MPa, Tensile Strength (S

T ) of 830 MPa and a

Yield Strength (S Y ) of 660 MPa.

Using Eq. 1C, the Stress Area is:

29382.04

P d AS

= 0.7854(10-0.9382 x 1.5)2 = 58 mm2

Applying Eq. 2B, Preload Force is:

F P

= S P A

S = 600 MPa x 58 mm2 = 34,800 N.




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Fasteners




Using Eq. 3, torque can be calculated. Coefficient of friction = 0.2 for non lubricated mild steel, thetorque is (a Safety Factor of 90% is used for a static joint):

T = KDF P S

F = 0.2 x 10 mm x 34,800 N x 90% = 62,640 N•mm = 62.6 N•m

NOTE: Eq. 3 can produce a maximum allowed fastener torque if 100% S F

is applied. Depending onthe materials being held, this value may generate more clamping force than is needed for theapplication.

Stress reflects a bolt’s ability to resist shear forces illustrated in Figure 2. Shear forces work laterallyagainst the sides of the fastener and the friction between the parts in a joint. If the Yield Strength isexceeded, the fastener will shear and the joint will fail. Shear Stress is expressed in terms of the forceapplied and the cross-sectional area of the fastener or fasteners used. Eq. 4 assumes:

All fasteners are the same type and size

Joint planes pass through all fasteners equally at body and threaded section.

The coefficient of friction between joints is zero.

CAUTION: If the resulting value of Eq. 4 exceeds the rated Tensile Strength (S T ) of the fastener, it will

likely fail. For critical applications, refer to references listed in Table 18 for more detailsand accurate formulas.

Eq. 4: Estimating Shear Stress Within a Bolt, Screw

S T B Br Am Am

F

A

F

(For round fastener)

Where: = Shear stress

F = Lateral force applied to joint system

AT

= Total cross-sectional area = the sum of the cross-sectional area of allfasteners in the joint system

m B

= Number of fasteners where joint plane passes through fastener body(assumes: all fasteners are the same type and size), set = 0 if none

mT = Number of fasteners where joint plane passes through threads (assumes:all fasteners are the same type and size), set = 0 if none

A B

= Sum of cross-sectional area where joint crosses threaded section of allbolts in the joint system

AS

= Sum of cross-sectional area where joint crosses body of all bolts or rivetsin the joint system

Eq. 5: Estimating Shear Stress on a Rivet

r bmA

F (For round fastener)

Where: = Shear stress

F = Lateral force applied to joint system b = Number of shear planes or surfaces passing through rivets (assumes: all

fasteners are the same type and size)

m = Number of fasteners joint plane passes through

Ar

= Cross-sectional area of fasteners in the joint system, assumes all are thesame type and size

•

•

•

Shear Forces for

Bolts, Screws, Pins or Rivets

Shear Forces for

Bolts, Screws, Pins or Rivets



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Example 3: Estimating Shear Stress for Cable Connected to a Frame

A half inch ball lock pin is used to secure a yoke to a steel plate that is secured to a frame by two M10x 1.0 Class 8.8 bolts. It is estimated the maximum force applied to the yoke will be 10,000 lbs. What isthe Shear Stress on the ball lock pin and each bolt?

Part A: The Yoke and Ball Lock Pin

Calculating the Stress Area ( AS ) for the ball lock pin using Eq. 1A:

2

4d A

S

= 0.7854 x 0.52 = 0.196 in2

The resulting Shear Stress, from Eq. 4, will be:

0196.01

10000

x Am Am

F

A

F

S T B Br

= 50.9 ksi = 351 MPa

NOTE: Because the tension of the cable on the yoke is equally divided and distributed to each end ofthe ball lock pin, the above result reflects the total shear stress on the ball lock pin which hasfour joint planes passing through it, two on the inside of the yoke and two on the outside. Itcould be argued that because the ends of the pin are not secured, the two inside joint planesabsorb the majority of the stress. The Shear Stress at each joint plane is 50.9/2 or 25.45 ksi.

Estimating the Shear Stress using Eq. 5:

196.012

10000

x xbmA

F

r

= 25.5 ksi = 176 MPa

The Yield Strength listed in Table 3 for steel is 40 ksi - 232 ksi, This would imply the design will workfine and a smaller ball lock pin and yoke may be used.

Part B: Plate Mounting

Calculating the Stress Area for each metric bolt using Eq. 1C (the joint plane passes through the boltthreads):

2

9382.04

P d AS

0.7854(10-0.9382*1.0)2 = 64.5 mm2 = 0.1 in2

The Shear Stress at the plate is (Eq. 4):

5.6420

44500

x Am Am

F

A

F

S T B Br

= 345 MPa = 50 ksi

345 MPa is the Shear Stress for the plate being held by two bolts bolts with 172.5 MPa each. FromTable 4, the Yield Strength for a Class 8.8 metric bolt is 640 MPa, which puts the bolts well within theestimated 172.5 MPa each in this example. Like the ball lock pin in Part A, the bolts are stronger thanrequired for this application.

10,000 lbs = 44500 N10,000 lbs = 44500 N




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In this case, hardware refers to any component which can be used in the joining of two or more piecesin an application. A wide variety of industrial hardware is available from Reid Supply. Hardware rangesfrom non-threaded fasteners to most any hardware required for cabinets to seals and gaskets. Refer toTable 17 for a summary of industrial hardware.

Where applicable, the most important design consideration for hardware is strength. For instance,specifications for drawer slides include Rated Load. Some hinges include a working load and somelatches list a grip strength. Eq. 5 can be used for most any fastener to determine minimum load bearingsizes.

CAUTION: When determining load bearing capacities of any fastener, estimate based on the weakest joint of the fastener or hardware component. If uncertain, contact Reid Customer Service at the toll-free number listed at the bottom of the page or online at ReidSupply.com.

Example 4: Estimating the shear stress for a 3/8 inch clevis pin made with 1010 steel. The Yield Strength (S Y )

is 44.2 ksi. The maximum load is determined to be 3000 lbs.

If the pin is used to align and hold two plates only one shear plane exists and either Eq. 4 or Eq. 5:

011.01

3000

x Am Am

F

A

F

S T B Br

= 27,272.7 psi = 188 MPa

11.011

3000

x xbmA

F

r

= 27,272.7 psi = 188 MPa

Environment can be an important concern when designing any equipment. Metal cutting equipmenttypically uses coolants; medical and food processing systems are concerned with sanitation. All ofthese systems use fasteners and related hardware to hold them together and attach components.Explosion proof hinges are available, if needed.

Weather is also an issue. Seals, gaskets and weather proofing hardware can protect contents bycontaining internal or excluding external influences. Neoprene washers also have environmentalapplication.

As previously mention, food and medical industries are concerned with biological contaminants.Some materials listed in Table 9 and Table 10 are biologically friendly and should be used for these

applications.

Much of the hardware included in Fasteners and Hardware is used in the design, construction andbuilding of enclosures. Latches with locks or built-in sensors, hidden hinges, drawer slides and othercomponents are available which support secure enclosures that can be locked or otherwise madesecure. Heavy duty hardware resists intrusion.

In some instances, space is a premium. The use of thread inserts eliminates the need for external nutsand saves space. Screws can be countersunk or have flat heads which allow movable devices to passover them. Low profile and recessed latches and hinges are also available that conserve space andstreamline the design.

Just the mention of fastener in any design raises concerns of vibration or any influence which candiminish or defeat the purpose of the joint. Several options are available to choose from and are listedin Table 14.

Least important from a practical point of view is aesthetics. However, it can be very important if thedesign is to have a lot of human exposure.

When any component is to be used in a production setting, there are many things to consider relativeto the production process. Fasteners and Hardware are used in the assembly and production of manyproducts. Production requirements may include automation, quality and human factors.

HardwareHardware

EnvironmentEnvironment

Sanitation Sanitation

Security Security

Space Space

Vibration Vibration

Aesthetics Aesthetics

ProductionRequirementsProductionRequirements



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Automation involves the use of equipment and processes which par tially or completely automate aproduction line with minimal human intervention. Automation can be applied to storage and deliverysystems and include the actual assembly of the product; in part or to completion. Automating storageand movement of components is not too difficult. However, when designing an automated assemblysystem, the first step is an attempt to eliminate or reduce the need for fasteners. This is because many

fasteners can be difficult to mechanically handle and install automatically. The designer must determinethe best fastener and hardware which can be used in an automated design.

Reid Supply is proud of its effort to ensure only quality products are found in its catalog and encourageany and all feedback from its customers. If there are any issues, positive or negative, with productspurchased from Reid Supply, contact Customer Service at the toll-free number listed at the bottom ofthe page, online at ReidSupply.com or by email at [email protected].

Any time an operator is part of the process, human factors must be considered. Human factors forFasteners and Hardware are similar to that of Manual Controls and Clamps and Workholding. Refer tothe Manual Controls or Clamps and Workholding Resource Guide for details.

Of course, safety is a high priority for any application; especially when human interface is required. Theintegrity of any application and design can be compromised by:

Improper design - anytime a fastener or other hardware is employed in a design, forces existwithin the joint where the fastener is used. Reid Supply offers many choices for the designer.Specifications for proper implementation of its products is available:

In the catalog - the information in this Resource Guide goes beyond the catalog and attempts togive customers more detailed information to implement Fasteners and Hardware.

As part of U.S. and ISO engineering standards governing dimensions and tolerances, material,production processes and product testing.

A degraded or failed joint - all joints held by fasteners are subject to external influences, from abridge swaying in the wind to a machine driving a tool through a piece of steel to a child droppinga toy. It is up to the designer to anticipate these conditions and select the best fastener or piece ofhardware that will be strong enough and resilient enough to last.

Operator neglect - many aspects of human behavior are both surprising and unpredictable. Forthose that are predictable, there are Fasteners and Hardware which can be purchased to protectboth the human and the product.

The previously discussed design considerations lead to a selection of a fastener or relative hardware.Use this section of the Resource Guide to help determine the product which best meets the designconsiderations for the application. Tables and other information have been included that allow thecomparison of similar products.

Several product lines fall under the Fasteners and Hardware category of the Reid Supply catalog. Eachproduct line offers a variety of styles to choose from. Refer to the many tables listed from this point onin the Resource Guide to help select the best style of Fasteners and Hardware.

While bolts have standard hex head, are straight shanked and have a limited selection of thread types,screws have a variety of heads, shanks, driver types and threads. The type of thread is determined bythe material being fastened to and its properties.

Table 7 lists screw thread types, while Table 8 illustrates different head types. Table 8 also shows thereference point from which screw length is measured. {3,6,7}

•

−

−

•

•

Automation Automation

Quality Quality

Human Factors Human Factors

SafetySafety

SELECTING THE CORRECT COMPONENT

SELECTING THE CORRECT COMPONENT

StyleStyle

Screw StylesScrew Styles




Thread Inserts

Fasteners




Table 7: ASA Screw Thread Types

Thread TypeSelfDrill

SelfStart

SelfTap

Description

CONEPOINT X

A precision forming operation to provide any required included angle. Offers a smooth

surface, accurate length, and a sharp point which can be produced to any desiredcontour to fit your particular requirements.

CUPPEDPOINT

A special cup section supplied on the end of the threaded screw having a depression inthe end to reduce the area in contact with the surface which increases its holding andlocking power under pressure.

DIE POINT

One of the least expensive pointing operations applied at the time of heading. Thisoperation provides an end chamfer starting with a diameter smaller than the rootdiameter of the thread. The minimum reduction of the point is approximately 10% belowthe maximum minor diameter with an included angle of 40 to 50 degrees.

DOG POINT

Includes a straight pointed section reduced in diameter slightly below the root diameterof the thread, usually extending in length about two-thirds the diameter of the thread.Recommended for ease in starting, to insure against stripping fine threaded products,and to increase efficiency along production lines.

NAIL POINT

(PINCHED)

Usually supplied with an approximate 45° included angle having a sharp point and slightlysquared surface. Used for impinging or locking against wood or other soft material. Otherdegrees of included angle and sharpness also available.

PINCHPOINT

(ROUNDED)

An inexpensive method of applying a 40°, 60° or 90° lead-in point having a slightlyrounded contour but with pinch-off marks on its surface. Used for aligning several sheetsor assembling several parts requiring pilot action.

ROLLEDPOINT

An efficient method of producing pointed long studs or long screws with an end chamfersimilar to the Die Point. The last thread and a half is slightly cupped by the thread roll-over operation.

ROUNDPOINT

A dome-like rounded surface applied to the end of a threaded screw in order to offerpressure without disfigurement. Used for adjusting screws where friction without cuttingaction is desirable.

SELF-DRILLING

X XWith special drilling points – lengths – diameters that will drill through ¼ in. metal.Eliminates all hole preparation – dr ills faster than a drill. No punching, drilling or tappingrequired. Reduces die costs.

SELF-DRILLING

X X

Produces more secure sheet metal assemblies faster. Used as self-drilling screw or

driving thru pre-punched holes. Can be used with or without pilot holes. Positive rake“forward cutting edge” drills straight thru sheet metal at peak speed. Perfectly matedthreads increase strip and back out pressures.

TYPE 17POINT

XFor wood with a coarse tapping screw thread and a special long sharp point fluted tocapture chips.

TYPE APOINT

XThis sheet metal screw for use in thin metal .015 to .050 thick. It is best to start with adrilled, punched or nested hole in sheet metal, resin impregnated plywood, asbestoscombinations, among others. Not recommended for new design.

TYPE BPOINT

XFor use in heavier metal .050 to .200 thick. It has a larger root diameter with finerthread pitch for light and heavy sheet metal, non-ferrous castings, plastics, impregnatedplywoods, asbestos combinations, and other materials.

TYPE CPOINT

X

Includes a blunt tapered point and approximates either coarse or fine pitch machinescrew thread. Makes a chip-free assembly and permits replacement with standardscrew in the field. Requires a higher driving torque. Usable in heavy sheet metal and die

castings.

TYPE DPOINT

X XBlunt tapered point thread with single flute for cutting an approximate fine standardmachine screw thread. For low strength metals and plastics or high strength brittlemetals and for rethreading clogged pretapped holes.

TYPE FPOINT

XSimilar to Type D point, but having multi-cutting edges and chip cavities. For use in heavygauge sheet metal, aluminum, zinc and lead die castings, cast iron, brass and plastic.

TYPE GPOINT

XBlunt die point with a single through slot to form two cutting edges. Machine screwthreads. Same general use as Type C, but where less driving torque is required. Usedfor low strength metals and plastics.



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Thread TypeSelfDrill

SelfStart

SelfTap

Description

TYPE TPOINT

XThe fine thread series offers maximum thread cutting area and excellent chip clearing,with minimum tightening torques.

TYPE UPOINT

XHas multiple high Helix threads for driving or hammering into sheet metal, castings, fiberor plastics for permanent, quick assemblies. Should not be used in materials less thanone screw diameter thick.

TYPE ABPOINT

XCombining Type A and B features, it includes a Type A locating point with Type B threadsize and pitch. Normal limitations of Type B apply.

TYPE BFPOINT

XWith a blunt tapered point and multi-cutting edges and chip cavities, this thread can beused for plastics, die castings, metal clad and resin impregnated plywoods, and asbestos.

TYPE BTPOINT

XSimilar to Type T point except with coarse Type B thread. For plastics and other softmaterials with large chip clearing and cutting edges.

Screw head styles are selected for aesthetics and practical reasons. Practical reasons include strengthand space. In some cases a low profile is required due to mechanical motion, while others require astrong head to hold down a part. Table 8 lists some common head styles and drive types. More drivetypes can be found in the Maintenance, Repair and Operations Resource Guide.

Table 8: Screw Head Styles

Head Style Description

ACORN HEAD

Full UndercutA very neat appearing trim screw for appliance application-excellent wrench surfaces.

BINDING HEADStraight Side

Generally used in electrical and radio work because of its identifying undercut beneath the head,which binds and eliminates fraying of stranded wire. Offers an attractively designed, medium-low headwith ordinarily sufficient bearing surface. Not ordinarily recommended as a Phillips Recessed Head-see Pan Head for better functional design.

FILLISTER HEAD

The standard oval fillister head has a smaller diameter than the round head, but is higher with acorrespondingly deeper slot. The smaller diameter head increases the pressure applied on thesmaller area and can be assembled close to flanges and raised surfaces. Headed in counterboreddies to insure concentricity, they may be used successfully in counterbored holes.

FLAT AND OVAL

Heads Undercut

This is the standard flat or oval head 80° to 82° countersunk screw which has the lower one-third ofthe countersunk portion removed to facilitate production of extremely short lengths. As illustrated, itwill fit a standard counterbored hole and is particularly adaptable to flush assemblies in thin stock.

FLAT HEAD

Supplied to standard dimensions with an 80° to 82° angle to be used where finished surfaces requirea flush fastening unit. The countersunk portion offers good centering possibilities. This style takes fulladvantage of the self-centering feature of the countersunk portion and provides a smooth, flush outersurface.

FLAT HEAD

100’ Countersunk

This special Flat Head screw has been developed for applications requiring flush surfaces and isrecommended for use in soft materials to distribute pressure over a larger and less angular surface.Very well adapted for use with thin aluminum, soft plastics, etc.

HEXAGON HEAD

Trimmed

This is the standard type of wrench-applied hexagon head, characterized by clean, sharp cornerstrimmed to close tolerances. Recommended for general applications. It is available in all standardpatterns and in all thread diameters.

INDENTEDHEXAGON

An inexpensive wrench head fastener made to standard hexagon head dimensions. The hex iscompletely cold upset in a counterbored die and possesses an identifying depression in the topsurface of the head.




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Head Style Description

INDENTEDHEXAGON

WASHER HEAD

Produced in the same manner as the standard indented hexagon head but with a washer section atthe base of the head to protect the finish of the assembly from wrench disfigurement.

ONE-WAY HEADThis ingenious, tamper-proof type of head, once assembled cannot be removed, yet is driven witha standard screw driver. Manufactured with amazing economy in productive quantities, this simpledesign can frequently solve costly assembly problems.

OVAL HEADFully specified as “oval countersunk”, this head is identical to the standard flat head, but possesses arounded, neat appearing upper surface for attractiveness of design.

PAN HEAD

Recommended for new designs to replace round, truss and binding heads. Provides a low largediameter head, but with characteristically high outer edge along the-outer periphery of the headwhere driving action is most effective for high tightening torques. Slightly different head contour wheresupplied with recessed head.

PHILLIPSFINISHING

WASHER HEADDesigned as a neat appearance product for the electronic and appliance trade with all threaded styles.

ROUND HEADNot recommended for new design (see Pan Head). This head was the most universally used designin the past.

SQUARESHOULDER

An adaptation of the standard carriage bolt design. Possesses a truss head on a square shank whichresists rotation when located or driven into place. This square shoulder may also be staked into placeas a permanent fastener. A great many varieties in all screw diameters are available in productivequantities.

TRUSS HEAD

Also known as Oven Head, Stove Head, and Oval Binding Head. A low, neat appearing, largediameter head having excellent design qualities, and as illustrated can be used to cover largerdiameter clearance holes in sheet metal when additional play in assembly tolerance is required.Suggest Pan Head as a substitute.

Type “T”

Overlug

For applications requiring smooth, finished outer surfaces. Under surface of head is designed forperfect electrode contact.

WASHER HEAD

This design has the finished appearance of a conventional round head plus washer and was originallycreated to provide extra large bearing surface under the head. The modern “truss” head (carriedin stock) normally answers this purpose. When a larger diameter is required this washer head isrecommended.

WELDING HEAD

Type U(Underlug)

The welding screw has been developed to provide a strong permanent threaded fastener whichbecomes an integral part of the assembly. It utilizes the principle of projection welding by means ofmultiple lugs applied to various head surfaces.

Type U is for general application. Assembles easily into pre-located holes and fully utilizes headstrength. Top surfaces of head designed for efficient welding anode contact.

As discussed previously, materials must be considered when selecting fasteners and related hardware.Table 9 lists some common materials used for Fasteners and Hardware. Table 10 and Table 11 list

basic properties of metals and plastics. More details on material properties can be found in some of thereference documents listed in Table 18. [1,3]

Material considerations include:

Properties The properties of materials used to produce fasteners are governed by standards andlisted by Grade or Class. Material properties can be found in tables within this ResourceGuide, in reference material listed in Table 18 and on the Internet.

Stress Material stress and fatigue can also be an issue if the material selected will not hold up tothe applied forces and bend or brake. This can be a function of both internal and external

MaterialsMaterials



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forces applied and for how long. Equations and tables provided in this Resource Guide, inreference material listed in Table 18 and on the Internet can be used to estimate strengthof materials use for fasteners and related hardware.

Most all fasteners and some hardware components list strength factors as previously

stated.

Strength Much of the information provided previously in Design Considerations is related to strengthof materials.

WARNING: Selecting a fastener or hardware that is too weak for any application will compromise itsintegrity and lead to equipment damage, personal injury or worse.

Corrosion Should the material used have an adverse reaction to chemicals or temperature or both, itmay not perform well. Corrosion, mold and mildew are concerns of the food and medicalindustry along with a material’s reaction to cleaning solutions. Table 12 of the ManualControls Resource Guide lists chemical properties of common plastics.

Weight Weight may be an issue that would favor plastics, but aluminum is also an option for somehardware. In the case of fasteners, less weight usually means less strength.

Friction Anytime parts come together and lateral forces exist, friction is generated. Friction is

an important factor for critical joints and calculations used to design them. If wear is aconcern, friction must be considered in the selection of fasteners and related hardware.It may be neglected for estimating and selecting Fasteners and Hardware for non-criticalapplications.

Other Conductivity, thermal properties, hardness, wear resistance, plasticity, and more. If theseand other considerations are required when selecting Fasteners and Hardware, refer toreference material listed in Table 18 or contact Reid Customer Service at the toll-freenumber posted at the bottom of the page, online at ReidSupply.com or email Reid atmail @ReidSupply.com.

Refer to Table 9 to help decide on a material to be used for your application based on materialproperties. [1,3]

Table 9: Materials Used to Manufacture Fasteners and Hardware

Material Pros Cons

Aluminum

Standoffs, screws, rivets, hinges, handles, and other hardware are made of aluminum orhave aluminum parts.

Lightweight.

Less corrosive than steel.

Non magnetic.

•

•

•

Soft, harder to machine than steel.•

Brass

Bushing, threaded inserts, screws, nuts, hinges, tips for set screws and other hardware canbe made of brass or have brass components.

Low wear factor.

Low coefficient of friction.

•

•

Softer than steel.•

Mild Steel

The most common form of steel that provides material properties that are acceptable formany applications. Used to manufacture most Fasteners and Hardware components.

Low carbon content (up to 0.3%) that is neither

extremely brittle nor ductile.Usually with black oxide finish to resist rust andcorrosion.

Tensile strength is a maximum of 500 MPa(72,500 psi).

Stronger than aluminum.

•

•

•

•

Can rust or corrode if not protected.

Heavier than aluminum or brass.

•

•




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Material Pros Cons

Nylon

Used in lock nuts and other fasteners as the locking element in threads. Also used for thenose for some set screws. See Vibration Proof Fasteners.

Long wear.

Will not mar soft metals or other material.

Self lubricating.

•

•

•

Sensitive to heat.•

Plastic

Typically used as handle material for some fasteners. Some hardware is made of plastic.

Softer and less expensive than metal.

Moldable to most any shape.

Lightweight, but strong.

•

•

•

Sensitive to heat and some strongchemicals.

•

Stainless Steel

Most fasteners are either steel or stainless steel. Many hardware components are stainlesssteel.

Corrosive resistant.

Impact resistant.

Non-magnetic.

Can be case hardened for better wear resistance.

•

•

•

•

Steel

A majority of fasteners and hardware components are made of steel.Typically case hardened for better wearresistance.

Passivated to resist corrosion with zinc or blackoxide.

Impact resistant.

Less expensive than stainless.

•

•

•

•

Can corrode or rust if protectivecoating is compromised.

•

Table 10: Material Specifications - Metals

Metals1

ServiceTemp2

Hardness2

Coefficient ofFriction3

TensileStrength2

YieldStrength2

TypicalElongation2

°C/°Fstatic and dry

sliding and dryMPaksi

MPaksi

%

Aluminum 260/500 80 - 125Brinnell

1.051.4

0.22-0.2760.032-0.040

<1 - 3.5

Brass 905/166065 - 80Brinnell

0.51 (on steel)

0.44 (on steel)

317-883

46-128

97-427

14-6265

Hard Steel 1093/20000.78

0.42

621 - 758

90 - 11011 - 30

Mild Steel 1093/2000137 - 223Brinnell

0.74

0.57

462 - 772

67 - 11214 - 25

Stainless Steel 343/650200 - 445Brinnell

-413 - 689

60 - 10010 - 40

NOTES: 1) Materials and specifications are for comparison purposes only and may differ from those used by OEM.

2) Values will vary with material property and temperature. More details can be found in references listed

in Table 18. [1,3]. If exact values are required for the desired tooling component, contact Reid Supply Customer Service at the toll-free number listed at the bottom of this page.

3) On like metal.



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Table 11: Material Specifications - Nylon

Plastics

ServiceTemp Rockwell

Hardness

Coefficientof Friction

TensileStrength

Notched IzodImpact

TensileElongation

FlexuralModulus

°C / °F

on steel

dry / wet

MPa

psi

J/m

ft-lb/in %

MPa

ksi

Nylon 6 82 / 180 101 to 123 0.4 / 0.1520.13-106.9

2920 - 15500

16.0 - 1.33E+31

0.300 - 2.50E+290.50 - 100

2.00 - 3130

0.290 - 453

Many industrial components are built around a set of national or international standards. Thesestandards are used by the designer to determine the best component to purchase and how to applythem. This is especially true for fasteners.

Table 12: Standards

Standard1 Number2 Function

ANSIAmerican NationalStandards Institute

www.ansi.org

B18.2.1 1996 Square and Hex Bolts and Screws, Inch Series

B18.2.2K 1987 Square and Hex Nuts

B18.2.3.1M 1986 Socket Head Cap Screws (Metric Series)

B18.2.3.4M 1986 Hexagon Socket Button Head Cap Screws (Metric Series)

B18.2.4.1M 2002 Metric Hex Nuts, Style 1

B18.3 2003 Socket Cap, Shoulder, and Set Screws, Hex and Spline Keys(Inch Series)

B18.6.3 2003 Machine Screws and Machine Screw Nuts

B18.17 1968 Nuts and Wing Nuts - Cold Forged

B18.21.1 1999 Lock Washers (Inch Series)

B18.22.1 1965 Plain Washers

ASME

American Society ofMechanical Engineers

www.asme.org

B18.2.1 Same as ANSI

B18.2.3.1M Same as ANSI

B18.6.3 Same as ANSI

B18.17 Same as ANSI

ASTMAmerican Society forTesting and Materials

www.astm.org

A449-07b Standard Specification for Hex Cap Screws, Bolts and Studs, Steel,Heat Treated, 120/105/90 ksi Minimum Tensile Strength, GeneralUse

A581/ A581M-95B

Standard Specification for Free-Machining Stainless Steel Wire andWire Rods

A582/ A582M-05

Standard Specification for Free-Machining Stainless Steel Bars

F436-07a Standard Specification for Hardened Steel Washers

F812/ F812M-07

Standard Specification for Surface Discontinuities of Nuts, Inch andMetric Series

IFI

Industrial FastenersInstitute

100/107 2002 Prevailing Torque Steel Hex and Hex Flange Nuts

101 Torque Tension Requirements for Prevailing-Torque Type Steel Hexand Hex Flange Nuts

ISO

InternationalOrganization forStandardization

www.iso.org

ISBN 92-67-10344-X

ISO Standards Handbook, Fasteners and Screw Threads

Volume 1: Terminology and nomenclature, General referencestandards

ISBN 92-67-10345-8

ISO Standards Handbook, Fasteners and Screw Threads

Volume 2: Product Standards

StandardsStandards




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Standard1 Number2 Function

SAE

Society of AutomobileEngineers

www.sae.org

J119 Fiberboard Crease Bending Test

J122A Surface Discontinuities on Nuts

J489 Lock Washers (Cancelled Jan 1990, Superseded by ANSI/ASME/ B18.21)

J995 Mechanical and Material Requirements for Steel Nuts

J1061 Surface Discontinuities on General Application Bolts, Screws, andStuds

NOTES: 1) More about standards can be found on the Internet and in the reference material listed in Table 18.

2) An “M” at the end of all standard numbers signifies Metric standard.

Other standards organizations listed in the catalog, but not listed in Table 12.

DIN Deutsches Institut fuer Normung (German National Standards Institution) www.din.de

The word “fastener” has a much broader meaning than many people are aware. The most common is abolt or screw. Table 13 includes a sample selection of fasteners available at Reid Supply.

Table 13: Types of Fasteners

Bolt Carriage Bolt Shoulder Screw Socket Head Cap Screw

Lag Screw Machine Screw Self Drilling Screw Sheet Metal Screw

Captive Panel Screw Captive Screw Set Screw Thumb Screw

Finishing Washer Flat Washer Lock Washer Machinery Bushing

Hex Nut Locknut Wing Nut Stud

Spacers Standoffs Gauge Yoke

Clevis Pin Pull Dowel Spring Pin Taper Pin

Click Pin Cotter Pin Hitch Pin Lynch Pin

Ball Lock Pin Quick Release Pin Flanged Receptacle Lanyard

FASTENERSFASTENERS



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Toggle Bolt U-Bolt Fastener Kits Fastener Storage

HeliCoil ® Rivet Nut Threaded Insert Thread Insert for Plastic

Aluminum Drive Rivet 1/4 Turn Fastener Receptacle Retainer

Standards offer no clear definition between a screw and a bolt. Generally speaking:

A bolt shank is 1/4 inch or more in diameter with straight threads and is always held on the other endby a nut or threaded hole in a block or other structure.

Bolt heads are typically limited to hex type and have threads that meet a specification such as M,MJ, UN, UNR or UNJ.

Bolts are grouped by grade for inch or class for metric sizes.

Screws:

Have a 1/4 inch or smaller shank with either straight or tapered threads. Straight threads are usedlike a bolt, but the head is something other than a hex head. However, a hex-washer head screw isan exception. Socket head cap screws are also an exception.

Can have tapered threads that are self tapping and intended to be driven into a substrate directlyor follow a pilot hole. The style of tapered thread determines the intended substrate: wood, plastic,cement, etc.

Determining the best fastener to use for any applications requires some engineering. Along withresearch for material types and fastener styles, some calculations are necessary. Eq. 3 and Eq 4 can

be transposed to get a minimum diameter:

Eq. 6: Estimating Minimum Fastener Diameter

P

P

S

F P d

7854.09382.0

Where: d = Estimated Diameter of fastener

P = Thread Pitch, set to zero for non-threaded fastener

F P

= Preload Force

S T

= Proof Load by grade or class for threaded fastener (Table 4 and Table 5, fornon-threaded fastener

NOTE: 1) Eq. 6 was derived from transposing Eq. 1C and Eq. 2B Although Eq. 1C is for metric fasteners, it can be

used to estimate both inch and metric diameters (see note 3).2) For non-threaded fasteners, set P = 0 and substitute Proof Load (S

P ) for Yield Strength (S

Y ) by material

found in Table 3 or from references listed in Table 18.

3) A safety factor should be included when selecting the best diameter fastener for the application.

•

•

•

•

•

Screw vs. BoltScrew vs. Bolt

Fastener DiameterFastener Diameter




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Example 5: Estimated the minimum bolt diameter for Example 3, Part B.

Assuming the force is evenly divided between the two bolts, 10,000 / 2 or 5,000 lbs or 22250 N. 640MPa was obtained from Table 4 as the Yield Strength (S

Y ) for Class 8.8 metric bolt and is substituted for

S P

in Eq. 6:

6407854.0

222500

7854.09382.0

xS

F P d

P

P = 6.65 mm

According to the above calculation, two Class 8.8, 8 mm bolts would have been sufficient to hold theplate on the frame.

Vibration is always a concern with threaded and non-threaded fasteners. Reid Supply offers a variety ofsolutions for this problem.

Table 14: Vibration Proof Fasteners

Jam Nut

Keps Nut Locknut Serrated Flange Locknut

Slotted Hex Nut Spinner Grip™ Flange Nut Nylon Locking Screw

Tooth Lock Washer

Lock Washer Nord-Lock™ Washer Serrated Safety Washer Spring Washer

The most typical tools for installation and removal of fasteners is a wrench or screwdriver. However,some fasteners are not typical and require special tools. Table 15 and Table 16 list recommended tools

designed for installation and removal of specific fasteners.

Table 15: Special Tools for Installing Fasteners

Air Hydraulic Thread-Setter Hand Thread-Setters

Hand Thread-SetterLow Volume Thread Insert Power Drive

HeliCoil ® Hand Insert Tool HeliCoil ® Production ToolHeliCoil ® Tang Break-Off

Tool Thread Taps

Table 16: Special Tools for Removing or Repairing Fasteners

HeliCoil ® Extracting Tool E-Z LOK™ Repair Kits Stud Repair Set Thread Repair Tools Thread Repair Kits

Vibration ProofFastenersVibration ProofFasteners

FASTENER TOOLSFASTENER TOOLS






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Light Duty Hinge Spring Hinge Spring Release Hinge Strap Hinge

Weld On Hinge Drawer Slide Lazy Susan CRT/TV Swivel Slide

Reid Does More Than You Think…..

We have over 52,000 products in 12 color-coded categories

Whether you call our friendly customer service reps or visit our new web site, ReidSupply.com,we have what you need. Take advantage of Reid’s 60 years of sales and product managementexperience.

Can’t find what you are looking for in our catalog?

Reid’s Rapid Response team is trained to find products that you can’t find. We will source theproduct for you.

Need technical support?“Ask an Expert” is a free service available on the Reid SupplyLine e-newsletter. Once registered, anyquestion submitted is passed to experienced team of professionals who provide a quick response.

Do you need help customizing a standard product?

TQM, Total Quality Machining, is our manufacturing and modification tooling company. We can takevirtually any standard part and customize it to meet your needs.

Just call the toll-free number listed at the bottom of the page or online at ReidSupply.com.

•

•

•

•

CUSTOM PRODUCTSCUSTOM PRODUCTS



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The use of this Resource Guide should help select the best Fasteners and Hardware for a wide varietyof applications. Use the included tables, equations and related information as a tool to assist in thedesign and purchase of Fasteners and Hardware.

For comments on the contents of this Resource Guide, contact the Reid Customer Service department

using the toll-free number listed at the bottom of the page or by email at mail @ReidSupply.com (enter“Resource Guide” in the subject line).

Although the Internet offers a vast wealth of information, it may not always be readily available or easyto find. Reid Supply online resources include other Resource Guides, Ask an Expert and referencemanuals found in the Reid Supply catalog. These reference manuals are listed in Table 18. Table 19list topics within each manual relative to Fasteners and Hardware. This Resource Guide can also bedownloaded and/or printed as needed.

Table 18: Recommended Documentation and Reference Manuals

Ref # Title Cat. No.

1 Machinery’s Handbook Pocket Companion DR-11

2 Machinery’s Handbook Guide

DR-12

DR-5CD

DR-5C

3 Machinery’s HandbookDR-5T

DR-5J

4 Basic Machining Reference Handbook DR-17

5 Machinist’s Ready Reference DR-18

6 Mark’s Standard Handbook for Mechanical Engineers DR-26

7 Standard Handbook of Machine Design DR-37

8 Materials Handbook DR-52

9 Engineer’s Black Book DR-95

NOTE: Refer to Table 19 for details on content relative to this Resource Guide.

SUMMARYSUMMARY

For MoreInformationFor MoreInformation




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Table 19: Reference Manual Content Relative to This Guide.

Information Type D R - 5 C

D R - C D

D R - 5 T

D R - 5 J

D R - 1 1

D R - 1 2

D R - 1 7

D R - 1 8

D R - 2 6

D R - 3 7

D R - 5 2

D R - 9 5

AISI classification of aluminum 2,4,7 2,4 2,7 2,4 2,4,7 5 2 2

AISI classification of tool steel 2,4,7 2,4 2,7 2,4 2,4,7 5 2 2

Bolt classification 1,2,3,4,7 1,2,4 2 1,2,3, 1,2,4,5 1,2

Bolt identification 1,2,4,7 1,2 2 1,2,6 1,2,5 1,2

Bolt specifications 1,2,7 1,2,5 2 1,2,5 1,2,5

Bolt and fastener strength values 2,4,6 3,6,8 2,4 1,2,4,7 1,2,3,7,8 2

Clamping forces for fasteners 3,6 3,6 3,7,8

Coefficient of Friction for materials 2,3,7 6 2,3,7 2,5

Conversion factors 2,3,7 2 2 2 1,2,3,5 2 2

Coordinates for locating holes on circle 1,2,6,8

Cotter and Clevis Pins 1,2,7 2,5Dowel pin data 1,2,7 1,2,5 2,3,6

Drill specifications 1,2,3,7,8 1,2,6 2,7 1,2,3 1,2 2

Driver types for nuts, bolts and screws 1,2

GD&T 2,4,7,8 2,4,5 2,6 2

Geometric shapes 3,7,8 3,5 3,7,8 3 3,4,7 3 3,5

Hardness 2,4,7 2,4 7 2,4,7 2,4,7 4,7 2

Head types for bolts and screws 1,2,7 1,2,5 2,5 1,2

Human dimensions 2,3,4,7 2

ISO/ANSI classes of carbide 2,7 2,4 5 2,6 2,4,6 2,5

Nut types 1,2,7 1,2,5 1,2,5 1,2

Properties of metals 2,4,7 2,5 3,6,8 6 2,4 2,4,7 2,3,4,7 7 2,5

Properties of non-metals 2,4,6 2,4,5 2,4,7 5

Rivets 1,2,7 2,4 1,2,3,4,7

Screw heads and types 1,2,7 2 1,2,5 1,2,3,6 2

Screw specifications 1,2,7 1,2,5 1,2,6 1,2,5

Set screw types and specifications 1,2,7 2,5 1,2 2,5

Shear strength for bolts and rivets 1,2,3,7,8 3,6,8 1,2,3,7,8 1,2,3,7,8

Stainless steel type 2,4,7 2,4 6 2,4,7 7 2

Standards for limits and fits 1,2,3,7 1,2,4,5 7,8 1,2,6 1,2,3,7 1,2,3,7 2

Standards listed in Table 12 1,2,4,6 2,5 2,4 1,2,4,6 2

Surface coatings 2,6 5

Thread types 1,2,3,4,7 1,2,3,7,8 6,8 6,8 1,2,3 1,2,4,6 1,2,3,6 1,2

Tolerances 1,2,3,4,7 1,2,4,6 3,7,8 1,2,6 1,2,6 1,2,3,6 1,2

Torque requirements for fasteners 1,2,3,7,8 1,2,3,7,8

Torque conversion 1,2,3,4,7 3,7,8 1,2,3,4 1,2,4

Washer specifications 1,2,5,8 2, 2,6

Wrench clearance 2,5 2,5



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Notes: 1) Imperial and metric systems

2) Data/specification charts and tables

3) Formulas

4) Comparison information

5) Some discussion

6) Basics discussion

7) Detailed discussion

8) How-to information

Below is a list of terms used in this document.

Term Definition

Axial Parallel to and along a given axis. Usually referenced to the direction of motionor force vectors.

Lateral Perpendicular to a given axis. Usually referenced to a sideways direction ofmotion or force vectors.

Preload ( P ) The amount of axial force added to a fastener to form a predeterminedclamping force. It is applied by torquing down a fastener or crimping arivet. If this value is exceeded by external forces, the joint integrity could becompromised.

Proof Load (S P ) Proof load is a tension-applied load that the fastener must support withoutevidence of permanent deformation. Proof load is an absolute value, not amaximum or minimum. Proof loads are established at approximately 90 to 93percent of the expected minimum yield strength of the fastener material.

Shear Stress The application of lateral forces, Figure 2, to a fastener and joint.

Strain () To pull, draw or stretch beyond the proper or legitimate limit. To apply anexternal force to the point of deformity.

Stress An applied force or system of forces that tends to strain or deform a body.

Stress Area The cross-sectional area of an object measured within a plane parallel to andin line with the applied forces creating stress.

Tensile Strength (S T ) Illustrated in Figure 2, Tensile strength (minimum value is usually given) for

fasteners is the amount of axial force that can be applied to a fastener withoutpermanently changing its shape. Forces exceeding this value can permanently

elongate or break the fastener.Torque (T )

Measured in N·m (Newton meter) or ft-lbs (foot-pounds), Torque is the resultingradial force ( F ) applied over a radial distance ( R) at, and normal to, the pivotpoint ( P ). The equation: T = FR

For example: if a force ( F ) of 50 N is applied 300 mm ( R) from the center of thepivot point ( P ), the resulting torque would be 15 N·m; or: 50 N x .3 m = 15 N·m.

Yield Strength (S Y ) The minimum amount of lateral force exerted against a fastener before

breaking. If exceeded, the fastener integrity could be compromised and distortor break the fastener and joint.

The following is a list of referenced used in to create this document. They are referred to by number,e.g. [3], in the text where applicable.

Standards listed in Table 12

Reference manuals listed in Table 18www.matweb.com

1]

2]3]

GLOSSARYGLOSSARY

FF

RR

PP

REFERENCESREFERENCES



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Resource Guide Fastener Hardware