Fasteners and Hardware Resource Guide - · PDF fileInch Bolt & Screw Nomenclature ... Fasteners and Hardware ... Table 1 includes a list of U.S. standard bolt and screw sizes along

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800.253.0421 www.ReidSupply.com Copyright©2008 Reid Supply Co. All Rights Reserved

CONTENTSReid Supply Resource Guides 1

Disclaimer 1

Terminology 1

Purpose of This Resource Guide 1

Design Considerations 2Fasteners 2

Inch Bolt & Screw Nomenclature 2Metric Bolt & Screw Nomenclature 5

Stress 9Tensile Force 17Shear Forces for Bolts, Screws, Pins or Rivets 20

Hardware 22

Environment 22Sanitation 22Security 22Space 22Vibration 22Aesthetics 22

Production Requirements 22Automation 23Quality 23Human Factors 23

Safety 23

Selecting the Correct Component 23Style 23

Screw Styles 23

Materials 26

Standards 29

Fasteners 30Screw vs. Bolt 31

Fastener Diameter 31

Vibration Proof Fasteners 32

Fastener Tools 32

Hardware 33

Custom Products 34

Summary 35For More Information 35

Glossary 37

References 37

LIST OF TABLESTable 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 Mechanical Properties for Steel Fasteners 11

Table 5: Mechanical Specifications for Carbon Steel Metric Fasteners with 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 Repairing Fasteners 32

Table 17: Types of Fasteners 33

Table 18: Recommended Documentation and Reference Manuals 35

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

LIST OF FIGURESFigure 1: Sample Bolt Head Markings 2

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

LIST OF EQUATIONSEq. 1A: Cross-sectional Area of Non-threaded Fastener 17

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

Eq. 1C: Cross-sectional 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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800.253.0421 www.ReidSupply.com 1

Copyright©2008 Reid Supply Co. All Rights Reserved

In our continuous effort to improve our offerings and meet customer needs, simplify effort and provide solutions, 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 12 categories. Each Resource Guide will include detailed application information, data and references to help our customers select the best product for their intended application.

Reid Supply welcomes your feedback and comments on any aspect of these Resource Guides. Please contact 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 is intended to assist in the selection of products sold by Reid Supply and its vendors. As Reid Supply and its vendors are not typically aware of or possess any expertise in the systems or processes for which products 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 impossible to 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 lack consistency.

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 related hardware have been around for many years and many reference and how-to manuals have been written. Information is also available online. To avoid confusion, a glossary of terms used in this document has been included at the end of the manual.

As Reid Supply purchases its products from several vendors, it is sometimes difficult to sort and categorize these differences. If you find yourself confused by terminology in the catalog or this document, 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 the Fasteners and Hardware of Reid Supply product offerings. The information included extends beyond the catalog to provide details, tables, charts and other information to further assist the customer in selecting the best Fasteners and Hardware for an application.

Much of the information presented and more, including this guide, can be found online. More detailed information 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 the text. References to text books and other documentation sold by Reid Supply are also referred to by number, e.g. {5} and listed in Table 18 at the end of this manual.

REID SUPPLY RESOURCE GUIDESREID SUPPLY RESOURCE GUIDES

DISCLAIMERDISCLAIMER

TERMINOLOGYTERMINOLOGY

PURPOSE OF THIS RESOURCE GUIDEPURPOSE OF THIS RESOURCE GUIDE


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2 800.253.0421 www.ReidSupply.com Copyright©2008 Reid Supply Co. All Rights Reserved

Although considerations for every and all applications is beyond the scope of this manual, some basic design considerations can be presented. The type of Fasteners and Hardware used in an application are based on what needs to be fastened to what and how. Hardware considerations are based on how things come together, even if they are not fastened. The remainder of this section discusses some basic considerations 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 later in this Resource Guide. There are two groups of fasteners shown Figure 1, inch and metric. Inch is primarily used in the U.S. while metric fasteners are used in Europe, Asia and the rest of the world. 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 and specifications 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 reference

for measuring a bolt or screw length is the surface plane for which the bolt or screw is inserted. For bolts, it is measured from the underside of the head and for screws, it depends on the screw type as shown in Table 7 later in this Resource Guide.

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

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

Machine Screw Size Number

of Threads Per Inch

Minor Diameter

Tap Drill Clearance Hole Drill

Aluminum, Brass & Plastics

Stainless Steel, Steels Iron All Materials

75% Thread 50% Thread Close Fit Free Fit

No. or Dia.

Major Dia. Drill Size

Decimal Equiv.

Drill Size

Decimal Equiv.

Drill Size

Decimal Equiv. Drill Size

Decimal Equiv.

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 CONSIDERATIONSDESIGN CONSIDERATIONS

FastenersFasteners

10.910.9

Inch Bolt & Screw NomenclatureInch Bolt & Screw Nomenclature

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of Threads Per Inch

Minor Diameter





No. or Dia.


Decimal Equiv.

Drill Size

Decimal Equiv.

Drill Size


Decimal Equiv.

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 0.1924 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


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No. or Dia.


Decimal Equiv.

Drill Size

Decimal Equiv.

Drill Size


Decimal Equiv.

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 1

8 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

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

M# x P - TPgTCg

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 TPg = Tolerance grade of thread pitch diameter (Typically not used) TCg = 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 pass through holes.

Table 2: Recommended Hole and Drill Sizes for Metric Screws

Machine Screw Size Tapping Drills Clearance Drills

Nom. Dia. PitchSeries

Drill Size Close Fit Free Fit

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

Decimal Equiv.

Drill Size

Decimal Equiv. Drill Size Decimal

Equiv.

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 0.07870.35 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 NomenclatureMetric Bolt & Screw Nomenclature


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Decimal Equiv.

Drill Size


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 0.59051.25 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

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Decimal Equiv.

Drill Size


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 1.49612 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


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Decimal Equiv.

Drill Size


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

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Decimal Equiv.

Drill Size


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 be understood to maintain the integrity of the joint. Depending on the type of joint, the ability for the fastener 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 nut or other similar fastener. The fastener may have to resist joint separation in one or both directions as indicated. An eye bolt mounting a pulley opposes axial forces of tension. While the fastener holding the 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 in the Clamps and Working or Tooling Components Resource Guides.

NOTE: Equations Eq. 1, thru Eq. 3 are for estimating torque. For critical applications, refer to more detailed and accurate calculations included in references listed in Table 18: {3} Machinery’s Handbook under Torque and Tension in Fasteners, {6} Mark’s Standard Handbook for Mechanical Engineers under Design of Bolted Joints and {7} Standard Handbook of Machine Design chapter 22.

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

StressStress

ST = Ultimate Tensile Strength

SY = Yield Strength

SP = Proof Strength

ST = Ultimate Tensile Strength

SY = Yield Strength

SP = Proof Strength

Tens

ion

(Stre

ss)

Tens

ion

(Stre

ss)

Bolt Elongation (Strain)Bolt Elongation (Strain)

STST

SYSY

FractureFracture

Plastic RegionPlastic Region

YieldYield

00

Elas

tic R

egio

nEl

astic

Reg

ion

SPSP

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Table 3: Mechanical Properties of Various Materials

Material1Yield Strength Ultimate Stress Elongation Elastic Modulus Shear Modulus Poisson’s

Ratio(ksi) (MPa) (ksi) (MPa) (%) (ksi) (GPa) (ksi) (GPa)

Aluminum [Al] 2.9 20 10.2 70 60 10200 70 3770 26 0.33

Aluminum Alloy 5 - 72 35 - 500 15 - 80 100 - 550 1 - 45 10200 - 11500 70 - 79 3770 - 4350 26 - 30 0.33

Brass 10 - 72 70 - 550 29 - 90 200 - 620 4 - 60 13900 - 16000 96 - 110 5220 - 5950 36 - 41 0.34

Brass; Noval 25 - 60 170 - 410 60 - 85 410 - 590 15 - 50 14500 100 5660 39 0.34

Brass; Red (80% Cu, 20% Zn) 13 - 68 90 - 470 44 - 85 300 - 590 4 - 50 14500 100 5660 39 0.34

Brick (Compression) - - 1 - 10 7.0 - 70 - 1450 - 3480 10 - 24 - - -

Bronze; Regular 12 - 100 82 - 690 29 - 120 200 - 830 5 - 60 13900 - 17400 96 - 120 5220 - 6380 36 - 44 0.34

Bronze; Manganese 25 - 65 170 - 450 65 - 90 450 - 620 10 - 35 14500 100 5660 39 0.34

Carbon [C] 1000 6.9 - - -

Ceramic 43500 - 58000 300 - 400 - - -

Concrete (Compression) - - 1.45 - 10 10 - 70 - 2610 - 4350 18 - 30 - - 0.1 - 0.2

Copper [Cu] 8 - 48 55 - 330 33 - 55 230 - 380 10 - 50 16000 - 17400 110 - 120 5800 - 6820 40 - 47 0.33 - 0.36

Copper Alloy 110 760 120 830 4 17400 120 6820 47 -

Cork - - - - 0

Glass - - 4.4 - 145 30 - 1000 - 6960 - 12000 48 - 83 2760 - 4930 19 - 34 0.2 - 0.27

Gold 12000 83 - - 0.44

Iron (Cast) 18 - 42 120 - 290 10 - 70 69 - 480 0 - 1 12000 - 24700 83 - 170 4640 - 10000 32 - 69 0.2 - 0.3

Iron (Wrought) 30 210 49 340 35 27600 190 10900 75 0.3

Magnesium [Mg] 2.9 - 10 20 - 70 15 - 25 100 - 170 5 - 15 5950 41 2180 15 0.35

Magnesium Alloy 12 - 40 80 - 280 20 - 49 140 - 340 2 - 20 6530 45 2470 17 0.35

Monel (67% Ni, 30% Cu) 25 - 160 170 - 1100 65 - 174 450 - 1200 2 - 50 24700 170 9570 66 0.32

Nickel [Ni] 20 - 90 140 - 620 45 - 110 310 - 760 2 - 50 30500 210 11600 80 0.31

Nylon; Polyamide - - 6 - 10 40 - 70 50 305 - 406 2.1 - 2.8 - - 0.4

Platinum [Pt] 21000 145 - - 0.38

Rubber 0.15 - 1 1.0 - 7.0 1 - 2.9 7.0 - 20 100 - 800 0.102 - 0.580 7.0 × 10-4 - 4.0 × 10-3

0.029 - 0.145

2.0 × 10-4 - 1.0 × 10-3 0.45 - 0.5

Silver [Ag] 11000 76 - - -

Solder; Tin-Lead - - 1.7 - 7.8 12 - 54 55 - 30 2610 - 5080 18 - 35 - - -

Steel 40 - 232 280 - 1600 49 - 276 340 - 1900 3 - 40 27600 - 30500 190 - 210 10900 - 11600 75 - 80 0.27 - 0.3

Stone; Granite (Compression) - - 10 - 40 70 - 280 - 5800 - 10200 40 - 70 - - 0.2 - 0.3

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Material1Yield Strength Ultimate Stress Elongation Elastic Modulus Shear Modulus Poisson’s

Ratio(ksi) (MPa) (ksi) (MPa) (%) (ksi) (GPa) (ksi) (GPa)

Stone; Limestone (Compression) - - 2.9 - 29 20 - 200 - 2900 - 10200 20 - 70 - - 0.2 - 0.3

Stone; Marble (Compression) - - 7.25 - 26 50 - 180 - 7250 - 14500 50 - 100 - - 0.2 - 0.3

Tin [Sn] 6090 42 - - 0.36

Titanium [Ti] - - 72.5 500 25 16000 110 5800 40 0.33

Titanium Alloy - - 131 - 141 900 - 970 10 16000 - 17400 110 - 120 5660 - 6380 39 - 44 0.33

Tungsten [W] - - 203 - 580 1400 - 4000 0 - 4

Wood; Ash (Bending) 6 - 10 40 - 70 7.25 - 14.5 50 - 100 - 1450 - 1600 10 - 11 - - -

Wood; Douglas Fir (Bending) 4.4 - 7.25 30 - 50 7.25 - 12 50 - 80 - 1600 - 1890 11 - 13 - - -

Wood; Oak (Bending) 6 - 8.7 40 - 60 7.25 - 14.5 50 - 100 - 1600 - 1740 11 - 12 - - -

Wood; Southern Pine (Bending) 6 - 8.7 40 - 60 7.25 - 14.5 50 - 100 - 1600 - 2030 11 - 14 - - -

Zinc [Zn} - - - - 0.25

NOTE 1) More exact values can be found in the reference material listed in Table 18.

Table 4: ASTM, SAE and ISO Grade Markings and Mechanical Properties for Steel Fasteners

Grade1 or

Class ID Mark

Specification Fastener Type Material

Nominal Size Range

Mechanical Properties

Proof Load2 Yield Strength Min Tensile Strength Minin. psi MPa psi MPa psi MPa

No Grade Mark

SAE J429 Grade 1

Bolts, Screws, Studs

Low or Medium Carbon Steel 1/4 thru 1-1/2 33,000 228 36,000 248

60,000 228ASTM A307 Grades A&B Low Carbon Steel 1/4 thru 4 -- -- -- --

SAE J429 Grade 2

Low or Medium Carbon Steel 1/4 thru 3/4 55,000 379 57,000 393 74,000 510

Over 3/4 to 1-1/2 33,000 228 36,000 248 60,000 414

No Grade Mark

SAE J429 Grade 4 Studs Medium Carbon Cold Drawn

Steel 1/4 thru 1-1/2 -- -- 100,000 689 115,000 793


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Grade1 or

Class ID Mark


Nominal Size Range



B5 ASTM A193 Grade B5 AISI 501 1/4 Thru 4 -- -- 80,000 552 100,000 689

B6 ASTM A193 Grade B6 AISI 410 -- -- 85,000 586 110,000 758

B7 ASTM A193 Grade B7 AISI 4140, 4142, or 4105

1/4 thru 2-1/2 Over 2-1/2

thru 4 Over 4 thru 7

-- --

105,000 724 125,000 862

95,000 655 115,000 793

75,000 517 100,000 689

B16 ASTM A193 Grade B16 CrMoVa Alloy Steel -- --

105,000 724 125,000 862

95,000 655 115,000 793

85,000 586 100,000 689

B8 ASTM A193 Grade B8 AISI 304

1/4 and larger -- -- 30,000 207 75,000 517B8C ASTM A193 Grade B8C AISI 347

B8M ASTM A193 Grade B8M AISI 316

B8T ASTM A193 Grade B8T

Bolts, Screws, Studs for

High-Temp. Service

AISI 321 1/4 and larger -- -- 30,000 207 75,000 517

B8 ASTM A193 Grade B8

AISI 304 Strain Hardened

1/4 thru 3/4 Over 3/4 thru 1

Over 1 thru 1-1/4

Over 1-1/4 thru 1-1/2

-- --

100,000 689 125,000 862

B8C ASTM A193 Grade B8C

AISI 347 Strain Hardened

80,000 552 115,000 793

65,000 448 105,000 724

50,000 345 100,000 689

B8M ASTM A193 Grade B8M


High-Temp. Service

AISI 316 Strain Hardened 1/4 thru 3/4

Over 3/4 thru 1 Over 1 thru

1-1/4 Over 1-1/4 thru

1-1/2

-- --

95,000 655 110,000 758

80,000 552 100,000 689

65,000 448 95,000 655

50,000 345 90,000 621

B8T ASTM A193 Grade B8T

AISI 321 Strain Hardened -- --

100,000 689 125,000 862

80,000 552 115,000 793

65,000 448 105,000 724

50,000 345 100,000 689

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Grade1 or

Class ID Mark


Nominal Size Range



L7 ASTM A320 Grade L7


Low-Temp. Service

AISI 4140, 4142 or 4145

1/4 thru 2-1/2 -- -- 105,000 724 125,000 862

L7A ASTM A320 Grade L7A AISI 4037

L7B ASTM A320 Grade L7B AISI 4137

L7C ASTM A320 Grade LC7 AISI 8740

L43 ASTM A320 Grade L43 AISI 4340 1/4 thru 4 -- -- 105,000 724 125,000 862

B8 ASTM A320 Grade B8 AISI 304

1/4 and larger -- -- 30,000 724 75,000 724

B8C ASTM A320 Grade B8C AISI 347

B8T ASTM A320 Grade B8T AISI 321

B8F ASTM A320 Grade B8F

AISI 303 or 303Se

B8M ASTM A320 Grade B8M AISI 316

B8 ASTM A320 Grade B8 AISI 304 1/4 thru 3/4 -- -- 100,000 689 100,000 689

B8C ASTM A320 Grade B8C AISI 347 Over 3/4 thru 1 -- -- 80,000 552 80,000 552

B8F ASTM A320 Grade B8F

AISI 303 or 303Se

Over 1 thru 1-1/4 -- -- 65,000 448 65,000 448

B8M ASTM A320 Grade B8M AISI 316 Over 1-1/4 thru

1-1/2 -- -- 50,000 345 50,000 345

B8T ASTM A320 Grade B8T AISI 321

SAE J429 Grade 5


Medium Carbon Steel, Quenched and Tempered

1/4 thru 1 85,000 586 92,000 634 120,000 827

Over 1 to 1-1/2 74,000 510 81,000 558 105,000 724

ASTM A449

1/4 thru 1 85,000 586 92,000 634 120,000 827

Over 1 to 1-1/2 74,000 510 81,000 558 105,000 724

Over 1-1/2 thru 3 55,000 379 58,000 400 90,000 621

SAE J429 Grade 5.1 Sems Low or Medium Carbon Steel,

Quenched and Tempered No. 6 thru 3/8 85,000 586 -- -- 120,000 827


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Grade1 or

Class ID Mark


Nominal Size Range



SAE J429 Grade 5.2


Low Carbon Martensitic Steel, Quenched and

Tempered1/4 thru 1 85,000 586 92,000 634 120,000 827

A325 ASTM A325 Type 1

High Strength Structural

Bolts


1/2 thru 1 85,000 586 92,000 634 120,000 827

1-1/8 thru 1-1/2 74,000 510 81,000 558 105,000 724

A325

ASTM A325 Type 2

Low Carbon Martensitic Steel, Quenched and

Tempered1/2 thru 1 85,000 586 92,000 634 120,000 827

A325 ASTM A325 Type 3

Atmospheric Corrosion Resisting Steel, Quenched

and Tempered

1/2 thru 1 85,000 586 92,000 634 120,000 827

1-1/8 thru 1-1/2 74,000 510 81,000 558 105,000 724

BB

ASTM A354 Grade BB

Bolts, Studs

Alloy Steel, Quenched and Tempered

1/4 thru 2-1/2 2-3/4 thru 4

80,000 552 83,000 572 105,000 724

75,000 517 78,000 538 100,000 689

BC

ASTM A354 Grade BC

105,000 724 109,000 752 125,000 862

95,000 655 99,000 683 115,000 793

SAE J429 Grade 7

Bolts, Screws

Medium Carbon Alloy Steel, Quenched and Tempered 4 1/4 thru 1-1/2 105,000 724 115,000 793 133,000 917

SAE J429 Grade 8 Bolts,

Screws, Studs

Medium Carbon Alloy Steel, Quenched and Tempered

1/4 thru 1-1/2 120,000 827 130,000 896 150,000 1,034ASTM A354 Grade BD

Alloy Steel, Quenched and Tempered 4

No Grade Mark

SAE J429 Grade 8.1 Studs

Medium Carbon Alloy or SAE 1041 Modified Elevated

Temperature Drawn Steel1/4 thru 1-1/2 120,000 827 130,000 896 150,000 1,034

A490 ASTM A490

High Strength Structural

Bolts

Alloy Steel, Quenched and Tempered 1/2 thru 1-1/2 120,000 827 130,000 896 150,000 min

170,000 max1,034 min 1,170 max

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Grade1 or

Class ID Mark


Nominal Size Range



No Grade Mark

ISO R898 Class 4.6



All Sizes thru 40 mm

32,633 225 29,588 204 58,015 400

No Grade Mark

ISO R898 Class 5.8 55,114 380 60,916 420 75,420 520

8.8 or 88 ISO R898 Class 8.8 Alloy Steel, Quenched and

Tempered

87,023 600 92,824 640 120,381 830

10.9 or 109

ISO R898 Class 10.9 120,381 830 136,335 940 150,839 1,040

NOTES: 1) Only sample hex heads are included with specific markings. Otherwise heads will be blank.

2) Also known as Proof Strength or Proof Load Stress.


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Table 5: Mechanical Specifications for Carbon Steel Metric Fasteners with External Threads

Property Class

Designation

Nominal Size of Product Material and Treatment

Mechanical Requirements

Property Class Ident.

Marking

Proof Load

Stress

Min. Yield

Strength

Min. Tensile

Ultimate Strength

Prod. Hardness, Rockwell

Surface Core

MPa MPa MPa Max. Min. Max.

4.6 M5-M100 low or medium carbon steel 225 240 400 -- B67 B95 4.6

4.8 M1.6-M16low or medium carbon steel, fully or partially annealed

310 340 420 -- B71 B95 4.8

5.8 M5-M24 low or medium carbon steel, cold worked 380 420 520 -- B82 B95 5.8

8.8 M16-M72 medium carbon steel, quenched and tempered 600 640 830 30N56 C23 C34 8.8

A325M Type 1 M16-M36 A325M 8S

8.8 M16-M36 low carbon boron steel, quenched and tempered 600 640 830 30N56 C23 C34 8.8

A325M Type 2 A325M 8S

A325M Type 3 M16-M36atmospheric corrosion resistant steel, quenched and tempered

600 640 830 30N56 C23 C34 A325M 8S3

9.8 M1.6-M16 medium carbon steel, quenched and tempered 650 720 900 30N58 C27 C36 9.8

9.8 M1.6-M16 low carbon boron steel, quenched and tempered 650 720 900 30N58 C27 C36 9.8

10.9 M5-M20 medium carbon steel, quenched and tempered 830 940 1040 30N59 C33 C39 10.9

10.9 M5-M100 medium carbon alloy steel, quenched and tempered 830 940 1040 30N59 C33 C39 10.9

A490M Type 1 M12-M36 A490M 10S

10.9 M5-M36 low carbon boron steel, quenched and tempered 830 940 1040 30N59 C33 C39 10.9

A490M Type 2 M12-M36 A490M 10S

A490M Type 3 M12-M36atmospheric corrosion resistant steel, quenched and tempered

830 940 1040 30N59 C33 C39 A490M 10S3

12.9 M1.6-M100

alloy steel, quenched and tempered 970 1100 1220 30N63 C38 C44 12.9

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In Figure 2, tensile forces continuously work against the joint axially in an attempt to pull it apart. At the same time, shearing forces may work against each other due to motion or vibration in the joint. Tensile forces are necessary to take advantage of friction and generate enough clamping force to maintain joint integrity. Anytime a fastener is used, forces are built up and stored in the joint that continuously work to both 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 be used.

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

At the Yield point, continued rotation stretches the elongated bolt to the point of no return (Plastic Region in Figure 2 graph) and any relaxation of the tension will not return the elongated bolt to its previous length or the threads to their original state. This point is known as the Yield Strength (SY) of the fastener. Continued tension in the axial direction eventually stretches the fastener to the Ultimate Tensile Strength (ST) where it weakens and finally fractures. Proof Load (SP) 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 the Reid Supply catalog and in many of the reference manuals listed in Table 18. These specifications include Yield Strength, Ultimate Tensile Strength and Proof Load for fasteners by grade and class. These values are used in design considerations to estimate Stress ( ) and Torque (T) for bolts, screws and rivets.

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

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

22

2

42ddrAB

(Standard formula for area of a circle)

Where: AB = 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

29743.04 n

dAS

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

29382.04

PdAS

Where: AS = Cross sectional area of fastener d = Fastener nominal diameter n = Number of threads per inch P = Thread pitch = 1/n

Tensile ForceTensile Force


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Use Eq. 2A {6} to determine the current preload (clamping force) of a fastener relative to a change in fastener length. The formula is only valid if the fastener is within the Elastic Region of Figure 2. Eq. 2B can be used to estimate the Preload Force (FP ) referenced to Proof Load (SP).

Eq. 2A: Determining Fastener Preload, Method 1

lAEeFP

Where: FP = Preload force A = Cross-sectional area (for a circle, A= r2) of fastener (accepted values can be

found in MIL-S-8879C) E = Modulus of elasticity for fastener material found in references listed in

Table 18 e = To measure elongation, must be accessible from both ends l = Original length of bolt

Eq. 2B: Estimating Fastener Preload, Method 2

FP = SPAS

Where: FP = Preload force SP = Proof Load by grade or class found in Table 4, Table 5 or references listed in

Table 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. The equation allows estimation of the amount of torque to obtain the Proof Load, but that would not allow for external forces which may add to existing preload and compromise joint integrity. Adding a safety factor allows for any external forces. If the joint is static, a safety factor of 90% is typical. For dynamic joints, a 75% safety factor is acceptable.

Should the joint include a gasket, over-torquing the fastener can compress and damage the gasket. Proof Load (SP) 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 from coefficient of friction between materials and other factors. This value is discussed in detail in reference material found in Table 18 where formulas are given to more accurately calculate this value. Table 6 includes 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 = KDFPSF

Where: T = Estimated torque K = Torque coefficient from Table 6 D = Fastener nominal diameter FP = Preload force calculated from Eq. 2A or Eq. 2B SF = Safety factor, typical values are 1.0 if not required, 0.9 for a static joint and

0.75 for a dynamic joint

NOTE: Adding lubrication will decrease the friction between threads and the surface of the fastener body. 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 using the 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 joint with a bushing. Referring to one of the reference documents in Table 18 or the Reid Supply catalog, we see Grade 5 bolts and screws have a Proof Load (SP) of 85,000 psi, Tensile Strength (ST) of 120,000 psi and a Yield Strength (SY) of 92,000 psi.

Using Eq. 1B, the Stress Area is:

226.0119743.0625.07854.09743.0

4

22

ndAS in2

Applying Eq. 2B, Preload Force is:

FP = SPAS = 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, the torque is (A Safety Factor of 75% is used for a dynamic joint):

T = KDFPSF = 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 a container. Referring to one of the reference documents in Table 18 or the Reid Supply catalog, we see Class 8.8 bolts and screws have a Proof Load (SP) of 600 MPa, Tensile Strength (ST) of 830 MPa and a Yield Strength (SY) of 660 MPa.

Using Eq. 1C, the Stress Area is:

29382.04

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

Applying Eq. 2B, Preload Force is:

FP = SPAS = 600 MPa x 58 mm2 = 34,800 N.


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

T = KDFPSF = 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% SF is applied. Depending on the materials being held, this value may generate more clamping force than is needed for the application.

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

All fasteners are the same type and sizeJoint 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 (ST) of the fastener, it will likely fail. For critical applications, refer to references listed in Table 18 for more details and accurate formulas.

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

STBBr AmAmF

AF (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 all

fasteners in the joint system mB = 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 AB = Sum of cross-sectional area where joint crosses threaded section of all

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

in the joint system

Eq. 5: Estimating Shear Stress on a Rivet

rbmAF

(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 the

same 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 M10 x 1.0 Class 8.8 bolts. It is estimated the maximum force applied to the yoke will be 10,000 lbs. What is the 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

4dAS = 0.7854 x 0.52 = 0.196 in2

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

0196.0110000

xAmAmF

AF

STBBr = 50.9 ksi = 351 MPa

NOTE: Because the tension of the cable on the yoke is equally divided and distributed to each end of the ball lock pin, the above result reflects the total shear stress on the ball lock pin which has four joint planes passing through it, two on the inside of the yoke and two on the outside. It could be argued that because the ends of the pin are not secured, the two inside joint planes absorb 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:

196.01210000

xxbmAF

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 work fine 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 bolt threads):

29382.04

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

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

5.642044500

xAmAmF

AF

STBBr

= 345 MPa = 50 ksi

345 MPa is the Shear Stress for the plate being held by two bolts bolts with 172.5 MPa each. From Table 4, the Yield Strength for a Class 8.8 metric bolt is 640 MPa, which puts the bolts well within the estimated 172.5 MPa each in this example. Like the ball lock pin in Part A, the bolts are stronger than required 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 pieces in an application. A wide variety of industrial hardware is available from Reid Supply. Hardware ranges from non-threaded fasteners to most any hardware required for cabinets to seals and gaskets. Refer to Table 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 some latches list a grip strength. Eq. 5 can be used for most any fastener to determine minimum load bearing sizes.

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 (SY) 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:

011.013000

xAmAmF

AF

STBBr = 27,272.7 psi = 188 MPa

11.0113000

xxbmAF

r

= 27,272.7 psi = 188 MPa

Environment can be an important concern when designing any equipment. Metal cutting equipment typically uses coolants; medical and food processing systems are concerned with sanitation. All of these 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 by containing internal or excluding external influences. Neoprene washers also have environmental application.

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 and building of enclosures. Latches with locks or built-in sensors, hidden hinges, drawer slides and other components are available which support secure enclosures that can be locked or otherwise made secure. Heavy duty hardware resists intrusion.

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

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

Least important from a practical point of view is aesthetics. However, it can be very important if the design 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 relative to the production process. Fasteners and Hardware are used in the assembly and production of many products. Production requirements may include automation, quality and human factors.

HardwareHardware

EnvironmentEnvironment

SanitationSanitation

SecuritySecurity

SpaceSpace

VibrationVibration

AestheticsAesthetics

Production RequirementsProduction Requirements

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Automation involves the use of equipment and processes which partially or completely automate a production line with minimal human intervention. Automation can be applied to storage and delivery systems and include the actual assembly of the product; in part or to completion. Automating storage and movement of components is not too difficult. However, when designing an automated assembly system, 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 determine the 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 encourage any and all feedback from its customers. If there are any issues, positive or negative, with products purchased from Reid Supply, contact Customer Service at the toll-free number listed at the bottom of the 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 for Fasteners and Hardware are similar to that of Manual Controls and Clamps and Workholding. Refer to the 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. The integrity of any application and design can be compromised by:

Improper design - anytime a fastener or other hardware is employed in a design, forces exist within 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 to give 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 a bridge swaying in the wind to a machine driving a tool through a piece of steel to a child dropping a toy. It is up to the designer to anticipate these conditions and select the best fastener or piece of hardware that will be strong enough and resilient enough to last.Operator neglect - many aspects of human behavior are both surprising and unpredictable. For those that are predictable, there are Fasteners and Hardware which can be purchased to protect both 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 design considerations for the application. Tables and other information have been included that allow the comparison of similar products.

Several product lines fall under the Fasteners and Hardware category of the Reid Supply catalog. Each product line offers a variety of styles to choose from. Refer to the many tables listed from this point on in 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 by the material being fastened to and its properties.

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

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•

AutomationAutomation

QualityQuality

Human FactorsHuman Factors

SafetySafety

SELECTING THE CORRECT COMPONENTSELECTING THE CORRECT COMPONENT

StyleStyle

Screw StylesScrew Styles


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Table 7: ASA Screw Thread Types

Thread Type Self Drill

Self Start

Self Tap

Description

CONE POINT 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 desired contour to fit your particular requirements.

CUPPED POINT

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

DIE POINT

One of the least expensive pointing operations applied at the time of heading. This operation provides an end chamfer starting with a diameter smaller than the root diameter of the thread. The minimum reduction of the point is approximately 10% below the 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 diameter of 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 slightly squared surface. Used for impinging or locking against wood or other soft material. Other degrees of included angle and sharpness also available.

PINCH POINT

(ROUNDED)

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

ROLLED POINT

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

ROUND POINT

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

SELF-DRILLING X X

With special drilling points – lengths – diameters that will drill through ¼ in. metal. Eliminates all hole preparation – drills faster than a drill. No punching, drilling or tapping required. 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 mated threads increase strip and back out pressures.

TYPE 17 POINT X

For wood with a coarse tapping screw thread and a special long sharp point fluted to capture chips.

TYPE A POINT X

This sheet metal screw for use in thin metal .015 to .050 thick. It is best to start with a drilled, punched or nested hole in sheet metal, resin impregnated plywood, asbestos combinations, among others. Not recommended for new design.

TYPE B POINT X

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

TYPE C POINT X

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

TYPE D POINT X X

Blunt tapered point thread with single flute for cutting an approximate fine standard machine screw thread. For low strength metals and plastics or high strength brittle metals and for rethreading clogged pretapped holes.

TYPE F POINT X

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

TYPE G POINT X

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

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Thread Type Self Drill

Self Start

Self Tap

Description

TYPE T POINT X

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

TYPE U POINT X

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

TYPE AB POINT X

Combining Type A and B features, it includes a Type A locating point with Type B thread size and pitch. Normal limitations of Type B apply.

TYPE BF POINT X

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

TYPE BT POINT X

Similar to Type T point except with coarse Type B thread. For plastics and other soft materials with large chip clearing and cutting edges.

Screw head styles are selected for aesthetics and practical reasons. Practical reasons include strength and space. In some cases a low profile is required due to mechanical motion, while others require a strong head to hold down a part. Table 8 lists some common head styles and drive types. More drive types 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 HEAD Straight 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 head with 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 a correspondingly deeper slot. The smaller diameter head increases the pressure applied on the smaller area and can be assembled close to flanges and raised surfaces. Headed in counterbored dies 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 of the countersunk portion removed to facilitate production of extremely short lengths. As illustrated, it will 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 require a flush fastening unit. The countersunk portion offers good centering possibilities. This style takes full advantage of the self-centering feature of the countersunk portion and provides a smooth, flush outer surface.

FLAT HEAD

100’ Countersunk

This special Flat Head screw has been developed for applications requiring flush surfaces and is recommended 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 corners trimmed to close tolerances. Recommended for general applications. It is available in all standard patterns and in all thread diameters.

INDENTED HEXAGON

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


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Head Style Description

INDENTED HEXAGON

WASHER HEAD

Produced in the same manner as the standard indented hexagon head but with a washer section at the 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 with a standard screw driver. Manufactured with amazing economy in productive quantities, this simple design can frequently solve costly assembly problems.

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

PAN HEAD

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

PHILLIPS FINISHING

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

ROUND HEAD Not recommended for new design (see Pan Head). This head was the most universally used design in the past.

SQUARE SHOULDER

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

TRUSS HEAD

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

Type “T”

OverlugFor applications requiring smooth, finished outer surfaces. Under surface of head is designed for perfect electrode contact.

WASHER HEAD

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

WELDING HEAD

Type U (Underlug)

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

Type U is for general application. Assembles easily into pre-located holes and fully utilizes head strength. 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 the reference documents listed in Table 18. [1,3]

Material considerations include:

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

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

Corrosion Should the material used have an adverse reaction to chemicals or temperature or both, it may not perform well. Corrosion, mold and mildew are concerns of the food and medical industry along with a material’s reaction to cleaning solutions. Table 12 of the Manual Controls 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 some hardware. 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 a concern, 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-critical applications.

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

Refer to Table 9 to help decide on a material to be used for your application based on material properties. [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 or have 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 can be 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 for many 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 and corrosion.Tensile strength is a maximum of 500 MPa (72,500 psi).Stronger than aluminum.

•

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•

•

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 the nose 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 strong chemicals.

•

Stainless Steel

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

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 wear resistance.Passivated to resist corrosion with zinc or black oxide.Impact resistant.Less expensive than stainless.

•

•

••

Can corrode or rust if protective coating is compromised.

•

Table 10: Material Specifications - Metals

Metals1

Service Temp2

Hardness2

Coefficient of Friction3

Tensile Strength2

Yield Strength2

Typical Elongation2

°C/°F static and drysliding and dry

MPa ksi

MPa ksi %

Aluminum 260/500 80 - 125 Brinnell

1.05

1.4

0.22-0.276

0.032-0.040<1 - 3.5

Brass 905/1660 65 - 80 Brinnell

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 1093/2000 137 - 223 Brinnell

0.74

0.57

462 - 772

67 - 11214 - 25

Stainless Steel 343/650 200 - 445 Brinnell -

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

Service Temp Rockwell

Hardness

Coefficient of Friction

Tensile Strength

Notched Izod Impact

Tensile Elongation

Flexural Modulus

°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. These standards are used by the designer to determine the best component to purchase and how to apply them. This is especially true for fasteners.

Table 12: Standards

Standard1 Number2 FunctionANSI American National Standards 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 of Mechanical 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

ASTM American Society for Testing 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, General Use

A581/A581M-95B

Standard Specification for Free-Machining Stainless Steel Wire and Wire 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 and Metric Series

IFI

Industrial Fasteners Institute

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

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

ISO

International Organization for Standardization

www.iso.org

ISBN 92-67-10344-X

ISO Standards Handbook, Fasteners and Screw Threads

Volume 1: Terminology and nomenclature, General reference standards

ISBN 92-67-10345-8

ISO Standards Handbook, Fasteners and Screw Threads

Volume 2: Product Standards

StandardsStandards


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Standard1 Number2 FunctionSAE

Society of Automobile Engineers

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, and Studs

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 a bolt 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

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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 end by 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 used like a bolt, but the head is something other than a hex head. However, a hex-washer head screw is an 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 directly or 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 with research 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

SFPd7854.0

9382.0

Where: d = Estimated Diameter of fastener P = Thread Pitch, set to zero for non-threaded fastener FP = Preload Force ST = Proof Load by grade or class for threaded fastener (Table 4 and Table 5, for

non-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 (SP) for Yield Strength (SY) 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.

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32 800.253.0421 www.ReidSupply.comCopyright©2008 Reid Supply Co. All Rights Reserved

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. 640 MPa was obtained from Table 4 as the Yield Strength (SY) for Class 8.8 metric bolt and is substituted for SP in Eq. 6:

6407854.0222500

7854.09382.0

xSFPd

P

P = 6.65 mm

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

Vibration is always a concern with threaded and non-threaded fasteners. Reid Supply offers a variety of solutions 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 Proof FastenersVibration Proof Fasteners

FASTENER TOOLSFASTENER TOOLS

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The word “fastener” has a much broader meaning than many people are aware. The most common is a bolt or screw. Table 17 categorizes fasteners available at Reid Supply.

Table 17: Types of Fasteners

1/4 Turn Latch Adjustable Latch Door Holder Draw Latch

Draw Pull Catch Explosion Proof Latch Grabber Catch Grip Latch

Key Latch L-Handle Latching Handle Magnetic Catch

Panel Latch Paddle LatchReplacement Key

(For lockable latches) Roller Catch

Slam Lock T-Handle Tension Latch Toggle Latch

Cover Stay Door Stop Lid Support Rod Assembly

Door Edge Protection

Push On Trim Seals

Weather Stripping Window Seal

Acrylic Hinge Bolt On Hinge Butt Hinge Concealed Hinge

Continuous Hinge Flush Mount Butt Hinge Latch Hinge Lift-Off Hinge

HARDWAREHARDWARE


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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

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CUSTOM PRODUCTSCUSTOM PRODUCTS

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The use of this Resource Guide should help select the best Fasteners and Hardware for a wide variety of applications. Use the included tables, equations and related information as a tool to assist in the design 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 easy to find. Reid Supply online resources include other Resource Guides, Ask an Expert and reference manuals found in the Reid Supply catalog. These reference manuals are listed in Table 18. Table 19 list topics within each manual relative to Fasteners and Hardware. This Resource Guide can also be downloaded 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

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Table 19: Reference Manual Content Relative to This Guide.

Information Type DR-5

C DR

-CD

DR-5

T DR

-5J

DR-1

1

DR-1

2

DR-1

7

DR-1

8

DR-2

6

DR-3

7

DR-5

2

DR-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 2,5

Dowel 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 DefinitionAxial Parallel to and along a given axis. Usually referenced to the direction of motion

or force vectors.

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

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

Proof Load (SP) Proof load is a tension-applied load that the fastener must support without evidence of permanent deformation. Proof load is an absolute value, not a maximum or minimum. Proof loads are established at approximately 90 to 93 percent 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 an external 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 and in line with the applied forces creating stress.

Tensile Strength (ST) 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 without permanently 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 resulting radial force (F) applied over a radial distance (R) at, and normal to, the pivot point (P). The equation: T = FR

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

Yield Strength (SY) The minimum amount of lateral force exerted against a fastener before breaking. If exceeded, the fastener integrity could be compromised and distort or 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 12Reference manuals listed in Table 18www.matweb.com

1]2]3]

GLOSSARYGLOSSARY

FFRR

PP

REFERENCESREFERENCES

8-02-05-04

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