Stress in a hole due to pin force

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Discussion Overview

The discussion revolves around determining the compression stress in a plate with a hole for a lifting shackle pin, particularly when the hole diameter is significantly larger than the pin diameter. Participants explore the theoretical implications of stress concentration and the appropriate areas to consider for calculations.

Discussion Character

  • Technical explanation
  • Mathematical reasoning
  • Debate/contested

Main Points Raised

  • Guideon questions what area should be used to determine compression stress in a pin-hole scenario, emphasizing that the hole diameter is much larger than the pin diameter.
  • Some participants suggest that the calculations may relate to bearing stress, with one participant providing a formula for maximum compressive stress involving load per unit length and material properties.
  • Another participant introduces a formula for stress in a plate with an elliptical hole, noting that for a circular hole, the stress increases by a factor of three compared to the compressive stress.
  • Concerns are raised about the applicability of stress concentration formulas derived for uniaxial tension in this context, suggesting that traction forces may alter the stress distribution around the hole.
  • Guideon seeks clarification on whether the stress equations depend on the units used and whether the dimensionless factor in the provided equation is indeed dimensionless.
  • Responses indicate that engineering formulas should be dimensionally consistent and confirm that the factor in question is dimensionless.

Areas of Agreement / Disagreement

Participants express varying interpretations of the stress equations and their applicability. While some agree on the need for clarification regarding the equations and their assumptions, no consensus is reached on the best approach to calculate the compression stress in this specific scenario.

Contextual Notes

Participants note that the stress concentration formulas may not apply directly due to the nature of the contact stress problem and the geometry of the hole. There is also uncertainty regarding the relationship between different stress calculations and the conditions under which they are derived.

Who May Find This Useful

This discussion may be useful for engineers and students interested in stress analysis, particularly in applications involving holes in structural components and the effects of geometry on stress distribution.

guideonl
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Hi everyone,

What is the area should be taken to determine the compression stress of pin-hole in tention force (i.e plate with known thickness having a hole for lifting shakle pin) where the hole diameter is greater than the pin diameter (> x3) (theoretically, it is not an area just line of contact between the hole and the pin, which is the thickness of the plate).
Thank you, Guideon
 
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guideonl said:
Hi everyone,

What is the area should be taken to determine the compression stress of pin-hole in tention force (i.e plate with known thickness having a hole for lifting shakle pin) where the hole diameter is greater than the pin diameter (> x3) (theoretically, it is not an area just line of contact between the hole and the pin, which is the thickness of the plate).
Thank you, Guideon

Hey man, I would like to help you, but I don't quite understand your description. A diagram would be really helpful here.
 
Thank you,
Hereby a sketch attached to clarify the question, I hope it would explain it better.

Guideon
 

Attachments

  • pin acting in a hole 001.jpg
    pin acting in a hole 001.jpg
    7.8 KB · Views: 1,970
guideonl said:
Thank you,
Hereby a sketch attached to clarify the question, I hope it would explain it better.

Guideon

Oh wow, that's great, thanks for the clarification. When I get home from work today I'll hook you up. Do you have numbers? I could also run a FE solution for you.
 
guideonl said:
Hi everyone,

What is the area should be taken to determine the compression stress of pin-hole in tention force (i.e plate with known thickness having a hole for lifting shakle pin) where the hole diameter is greater than the pin diameter (> x3) (theoretically, it is not an area just line of contact between the hole and the pin, which is the thickness of the plate).
Thank you, Guideon

Your attachment calcs look like you're trying to solve for bearing stress. However, since the pin is much smaller than the socket, the max compressive stress is actually given by:

\sigma c_{max} = 0.798 \cdot \sqrt{\frac{p}{K_D \cdot C_E}}

Where,

p = load per unit length
E1 = modulus of elasticity of bottom socket
E2 = modulus of elasticity of pin
v1 = poisson's ratio of bottom socket
v2 = poisson's ratio of pin

K_D = \frac{D_2 \cdot D_1}{D_1 - D_2}

C_E = \frac{1- \nu_1^2}{E_1} + \frac{1- \nu_2^2}{E_2}

CS
 

Attachments

  • CompressiveStressCyl.JPG
    CompressiveStressCyl.JPG
    2.1 KB · Views: 1,021
I agree with Stewart, though I would also add that the stress in your plate increases due to the hole.

For an elliptical center hole,

\sigma_{A} = \sigma_{c}\left(1+\frac{2a}{b}\right)

Since your hole is circular, a = b = r, thus

\sigma_{A} = 3\sigma_{c}

where

\sigma_{c} is compressive stress
\sigma_{A} is the actual stress, taking into account the geometry of the hole
2a is the major axis
2b is the minor axis
r is the radius of your circular hole

Source: Anderson, T.L., Fracture Mechanics Fundamentals and Applications, 3rd Ed., CRC / Taylor and Francis, 2005, p27.
 
Unit91Actual said:
I agree with Stewart, though I would also add that the stress in your plate increases due to the hole.

For an elliptical center hole,

\sigma_{A} = \sigma_{c}\left(1+\frac{2a}{b}\right)

Since your hole is circular, a = b = r, thus

\sigma_{A} = 3\sigma_{c}

where

\sigma_{c} is compressive stress
\sigma_{A} is the actual stress, taking into account the geometry of the hole
2a is the major axis
2b is the minor axis
r is the radius of your circular hole

Source: Anderson, T.L., Fracture Mechanics Fundamentals and Applications, 3rd Ed., CRC / Taylor and Francis, 2005, p27.

The stress concentration formula you're talking about was derived for uniaxial tension. I don't think those boundary conditions apply in this case. Also, since this is a contact stress problem, the stresses will be altered because traction forces are applied to the hole.
 
Thank you all, you are great
I just want to be sure that I undersdand your answers:
stewartcs,
a) Is the stress equation you sent depends on the units you use in the equation (SI/american)?
b) The 0.798 factor is dimensionless?
Unit91Actual
a) Is the compressive stress you used in the equation for an elliptical center hole is the result of the max compressive stress equation in stewartcs reply? If not, how can I calculate this sress? that was my original question.
b) According to your important note, actually, the major stress is not where the pin force acts, but at 90 degrees right/left from the hole center (3 times the compressive stress)?

Thank you all again, Guideon
 
guideonl said:
Thank you all, you are great
I just want to be sure that I undersdand your answers:
stewartcs,
a) Is the stress equation you sent depends on the units you use in the equation (SI/american)?
b) The 0.798 factor is dimensionless?
Unit91Actual

As with all engineering formulas, the equation should be dimensionally consistent.

The 0.798 is a dimensionless factor.

CS
 

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