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Bolted joints are one of the most common elements in construction and machine design. They consist of cap screws or studs that capture and join other parts, and are secured with the mating of screw threads.
There are two main types of bolted joint designs. In one method the bolt is tightened to a calculated torque, producing a clamp load. The joint will be designed such that the clamp load is never overcome by the forces acting on the joint (and therefore the joined parts see no relative motion).
The other type of bolted joint does not have a designed clamp load but relies on the shear strength of the bolt shaft. This may include clevis linkages, joints that can move, and joints that rely on locking mechanism (like lock washers, thread adhesives, and lock nuts).
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The clamp load, also called preload, of a cap screw is created when a torque is applied, and is generally a percentage of the cap screw\'s proof strength. Cap screws are manufactured to various standards that define, among other things, their strength and clamp load. Torque charts are available that identify the required torque for cap screws based on their property class.
When a cap screw is tightened it is stretched, and the parts that are captured are compressed. The result is a spring-like assembly. External forces are designed to act on the parts that have been compressed, and not on the cap screw.
The result is a non-intuitive distribution of strain; in this engineering model, as long as the forces acting on the compressed parts do not exceed the clamp load, the cap screw doesn\'t see any increased load. This model is only valid when the members under compression are much stiffer than the capscrew.
This is a simplified model. In reality the bolt will see a small fraction of the external load prior to it exceeding the clamp load, depending on the compressed parts\' stiffness with respect to the hardware\'s stiffness.
The results of this type of joint design are:
In the case of the compressed member being less stiff than the hardware (soft, compressed gaskets for example) this analogy doesn\'t hold true. The load seen by the hardware is the preload plus the external load.
Nut threads are designed to support the rated clamp load of their respective bolts. If tapped threads are used instead of a nut, then their strength needs to be calculated. Steel hardware into tapped steel threads requires a depth of 1.5× thread diameter to support the full clamp load.
If an appropriate depth of threads is not available, or the threads are in a weaker material than the cap screw, then the clamp load (and torque) needs to be derated appropriately.
Threads are usually created on a thread rolling machine. They may also be cut with a lathe, tap or die. Rolled threads are about 40% stronger than cut threads.
Engineered joints require the torque to be accurately set. The clamp load produced during tightening is about 75% of the fastener\'s proof load. Over tightening will damage threads and stretch the bolt, ruining the joint\'s strength; see Hooke\'s law.
If the hardware is Cadmium-plated or lubricated (or both), the torque is reduced by 15 – 25% to achieve the same clamp load. Specialty coatings exist that allow a reduction of 50% in torque (compared to non-plated, non-lubricated hardware) to achieve the designed clamp load. Cadmium-plated fasteners are no longer produced due to the toxicity of the metal.
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This article or section may contain original research or unverified claims. Please improve the article by adding references. See the talk page for details. (February 2008) |
Torquing the bolt is notoriously inaccurate. Even with a calibrated torque wrench large errors are caused by dirt, surface finish, lubrication, etc. The turn of the nut method is more accurate, but requires additional calculations and tests for each application.[citation needed]
There are more expensive tools for accurate torque setting, like ultrasonic meters, but they are out of reach of most shops.
There are many different property classes (grades) of bolts and nuts. The most common are listed below. Note that each nut property class listed can support the bolt proof strength load of the bolt it is listed beside without stripping. The first number in the bolt property class indicates the nominal tensile strength, and the second number the yield stress as a proportion of the tensile strength. In other words class 8.8 means tensile strength of 800 MPa and proof stress of 0.8 x 800 MPa = 640 MPa.The Southern African Institute of Steel Construction, The Blue Book: Structural Steel Tables, The Southern African Institute of Steel Construction, p. 3.1, ISBN 97806230380614
| Bolt property class | Material | Proof strength | Tensile yield strength, min. | Tensile ultimate strength, min. | Bolt marking | Nut marking | Nut class |
|---|---|---|---|---|---|---|---|
| ISO, per ISO 898-1 | |||||||
| 5.8 | Low or med. carbon steel | 380 MPa (55 ksi) | 420 MPa (61 ksi) | 520 MPa (75 ksi) | 
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| 5 |
| 8.8 | Med. carbon steel Q&T | 580 MPa (84 ksi) | 640 MPa (93 ksi) | 800 MPa (116 ksi) | 
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| 8 |
| 10.9 | Alloy steel Q&T | 830 MPa (120 ksi) | 940 MPa (136 ksi) | 1040 MPa (151 ksi) | 
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| 10 |
| SAE, per SAE J429 | |||||||
| 2 | Low or med. carbon steel | 55 ksi (379 MPa) | 57 ksi (393 MPa) | 74 ksi (510 MPa) | 
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| 2 |
| 5 | Med. carbon steel Q&T | 85 ksi (586 MPa) | 92 ksi (634 MPa) | 120 ksi (827 MPa) | 
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| 5 |
| 8 | Alloy steel Q&T | 120 ksi (827 MPa) | 130 ksi (896 MPa) | 150 ksi (1034 MPa) | 
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| 8 |
Bolted joint |
Screw joint |
Pin joint |
The most common mode of failure is overloading. Operating forces of the application produce loads that exceed the clamp load and the joint works itself loose, or fails catastrophically. Something that is not considered structural failure, but nevertheless is becoming a modern annoyance in new buildings is bolt banging.
Over torquing will cause failure by damaging the threads and deforming the hardware, the failure might not occur until long afterwards. Under torquing can cause failures by allowing a joint to come loose. It may also allow the joint to flex and thus fail under fatigue.
Brinelling may occur with poor quality washers, leading to a loss of clamp load and failure of the joint.
Corrosion, embedment and exceeding the shear stress limit are other modes of failure.
Bolted joints in an automobile wheel. Here the outer four screws are studs that project through the brake drum and wheel, while nuts with conical locating surfaces secure the wheel. The central nut (with cotter key) secures the wheel bearing to the steering spindle. Other configurations use a bolt into threaded holes in the axle end or brake drum.
Locking mechanisms keep bolted joints from coming loose. They are required when vibration or joint movement will cause loss of clamp load and joint failure, and in equipment where the security of bolted joints is essential.
The torque is applied by means of suspending the weights on one end of the rope and other end is wound around the head of the bolt and tied to the projection. The amount of load is increased gradually till the bolt starts rotating. The applied load is then calculated by adding up the weights. This is the load that is required to overcome the friction between the threads. Similarly the net applied torque is calculated by multiplying the resultant load by bolt head radius.
In another method the torque is applied to the nut by an electromagnetic force.A specially designed gripper is used to grip the nut. A bar magnet is mounted on two sides of the gripper. Externally a coil is wound in which AC (alternating current) current is passed. As the magnetic field from the permanent magnet interacts with the field created by the coil, a torque is generated which would try to rotate the magnet, thus rotating the nut. This is quite similar to the construction of the motor, and hence a motor can be directly used to provide the torque. Stepper motor can be used so that the torque is provided in steps, as desired, each time giving a small angular displacement. The torque provided by the motor can be known at each discrete angular displacement of Δθ. The process is repeated till the nut has traversed to the desired length of the bolt. The discrete torques can be added to get the net torque consumed in displacing the nut from one end of the bolt to the desirable point. This is the torque that is required to overcome the friction between the threads.
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