Category Archives: Mechanical elements

DIN STANDARD PARTS

DIN STANDARD PARTS

McMaster (U.S,)

OPAC (Spanish)

WIKIPEDIA (List of standards)

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Safety factor

Safety factor

Nductile ≥ max(N1, N2, N3) ; based on yield strength

Nbrittle ≥ max(N1, N2, N3) ; based on ultimate strength

N = N1 . N2

N1 = f(A, B, C), from the first table

N2 = f(D, E) , from the second table

Parameters:

A             Quality of materials, workmanship, maintenance and inspection

B             Control over applied loads

C             Accuracy of stress analysis, experimental data, or experience with similar parts

D             Danger to people

E             Economic impact

The transition from engineering model to reality is usually facilitated by including a factor of safety in the design to accommodate uncertainly in material properties and the design process, the consequences of failure, risk to people and degree of characterization of and control over the service environment.

Safety factor is a simple ratio that is intended to be greater than 1.

N=frac{capacity}{load}=frac{strength}{stress}> 1

Safety factors for ductile materials are based on yield strength. Safety factors for brittle materials are based on ultimate strength and are twice the recommended values for ductile materials. Safety factors for primarily cyclic loading are based on endurance limit. Impact loads require a safety factor of at least 2 multiplied by an impact factor from 1.1 to 2.

The factor safety is often specified in a design code or standard.

Factor safety is affected by:

  1. Material strength basis: Brittle materials use ultimate strength and ductile use yield strength.
  2. Manner of loading: Static applied slowly, repeated; fatigue failure may occur; impact; high initial stresses develop.
  3. Possible misuse: Designer must consider any reasonable foreseeable use of misuse of product.
  4. Complexity of stress analysis.
  5. Environment: Temperature, weather, radiation, quimical…
  6. Hazard of failure; What happens if the parts fail?
  7. Cost.
  8. Market segment: Different safety factor for different markets (aerospace, health…)

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Bolt axial force vs torque

Bolt axial force vs torque

The torque required to tighten the bolt:

T=Kcdot Fcdot d

Where:

T:            Torque (N.m)

K:            Torque coefficient

F:            Axial preload force (N)

d:            Nominal bolt diameter (mm)

The torque coefficient:

K=0.5cdot left ( frac{lcdot cosalpha +pi cdot dcdot mu }{pi cdot dcdot cosalpha -lcdot mu } right )+0.625 cdot mu _{c}

Where:

l:             Lead (mm)

α:           Half angle of the screw thread (°)

d:            Nominal bolt diameter (mm)

µ:            Thread friction coefficient

µc:          Collar friction coefficient

Common torque coefficient values for µ=µc=0.15:

Bolt condition    K
Non plated black finish steel bolts 0.3
Mild steel bolts 0.2
Zinc plated steel bolts 0.2
Lubricated steel bolts 0.18
Cadmium plated steel bolts 0.16
With bowman anti-seize 0.12
With bowman-grip nuts 0.09

 

It is estimated that roughly 90% of the input energy is lost in overcoming the mating friction under the head (collar) and between the thread or nut and its mating threads.  Consequently only the remaining 10% of input energy is turned into bolt stretch.

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Cantilever snap joint

Cantilever snap joint

Bayer – Snap-Fit joints for plastics

 

 

This calculation is for a snap-fitting hook of rectangular cross section.There are two types which can be choosen for the calculation. Type 1 is a snap-fitting hook of a constant rectangular cross section and Type 2 is a snap-fitting hook of rectangular cross section with a constant decrease in thickness from h at the root to h/2 at the end of the hook. Young modulus and Yield strength of the material have to be choosen. The Deflection Force is the force required to bend the arm the value of the introduced deflection (y). Introducing the friction coefficient of the material and the angle of the arm according with the shape represented in picture, the mating force is calculated. This is the force required for introducing the snap-fitting hook. The calculus allows to ensure that the yield strength of the material won’t be exceeded as long as the safety coeficient is higher that 1. This calculation is an approximation because of we are only taking into account the shear due to bending.

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Thread identification guide

Thread identification guide

STEP 1

Determine if the thread is tapered or parallel/straight.

Measure the thread with a caliper at the beginning and the end. If the diameters increase for a male end or decrease for a female end, the thread is tapered. If it is the same value the thread is straight/parallel.

STEP 2

Determine the thread size and type. Imperial sizes are normally common fractions ¼”=0.25”.

Measure the outside diameter OD for male and inside ID for female threads.

If the thread is tapered measure the diameter of 4th or 5th full thread.

The diameter measurement obtained in this step may not be exactly the same as the listed nominal size for the given thread. This variation is due to manufacturing tolerances.

STEP 3

Determine the pitch for metric or the amount of threads per inch (T.P.I) for imperial sizes.

In both cases Thread pitch gauges can be used.

TPI 28 27 24 20 19 18  16  14  12 11.5 11 8
Thread pitch (mm) 0.91 0.94 1.06 1.27  1.34  1.4  1.59  1.81  2.12 2.21 2.31 3.18

Check for any markings on fitting or equipment which may be a clue to thread type. Country of origin may provide a clue.

Europe (DIN,BSP), America (NPT, JIC, UNO, ORFS), UK/Australia (BSP), Japan (JIS).

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Thread types

Thread types

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