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Plastic deformation

Storyboard

For small deformations, the material only undergoes elastic deformation, meaning that upon removing the load, it returns to its original shape. For larger deformations, atoms may experience greater displacements, leading to a permanent change in structure. In such cases, we refer to it as plastic deformation.

>Model

ID:(324, 0)



Mechanisms

Iframe

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Code
Concept
Application to fracture
Bending with one Fixed Point
Bending with two Fixed Points
Bone deformation due to torsion
Bone structure
Buckling
Elastic deformation of the Solido Structure
Impact fracture
Permanent Deformation explained with Atoms
Plastic deformation in the Solido Structure
The bone
The dynamics

Mechanisms

Application to fractureBending with one Fixed PointBending with two Fixed PointsBone deformation due to torsionBone structureBucklingElastic deformation of the Solido StructureImpact fracturePermanent Deformation explained with AtomsPlastic deformation in the Solido StructureThe boneThe dynamics

ID:(15576, 0)



Bone structure

Concept

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The bone can be modeled as a hollow cylinder since the material inside it is not capable of bearing a significant load. Therefore, it is geometrically modeled as a cylinder with properties the body length (L), the inside radio (R_1), and the outdoor radio (R_2):

None



Therefore, the effective radius (R) is

R^2=R_1^2+R_2^2



the body Section (S) is

S = \pi ( R_2 ^2- R_1 ^2)



and the moment of inertia of surface (I_s) is

I_s =\displaystyle\frac{ \pi }{2}( R_2 ^4- R_1 ^4)

ID:(1915, 0)



Application to fracture

Description

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In the case of bone, there are different situations that lead to the generation of extreme tensions that result in fracture.

One situation is when the bone is fixed at one end and is being flexed from the other:



An example is a person falling and leaning on a point, creating a fixed point through friction while the center of mass continues to move due to inertia, flexing the bone until it fractures.

Another scenario is when it is fixed at both ends and receives a perpendicular force at some intermediate position:



A typical example of this is when a soccer player places their foot (a fixed point) and the mass of their body, due to inertia, retains the second point, which can be considered fixed, while another player impacts their leg with their foot.

Lastly, there is the situation where the bone collapses due to axial pressure.



In this case, there are two situations. On the one hand, the structure of the bone itself can collapse and fracture due to compression. On the other hand, there may be buckling, meaning that due to some inhomogeneity, the bone flexes and ends up deflecting extremely, leading to fracture.

These are the basic mechanisms that can subsequently, in reality, initiate the process, compromising other bones or extending within the same bone, resulting in a more complex fracture.

ID:(222, 0)



Bending with one Fixed Point

Concept

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One situation that may arise is when a deformation force with a fixed point (F_1) acts on a bone with properties a body length (L), the modulus of Elasticity (E), and the moment of inertia of surface (I_s), which is fixed at one end.

None



the strain energy with a fixed point (W_1), storing the structure against a stress to deformation with a fixed point (\sigma_1), is defined by

W_1 =\displaystyle\frac{3 E I_s }{2 L ^3} u_1 ^2



the deformation force with a fixed point (F_1), the applied force, leads to a stress to deformation with a fixed point (\sigma_1) as per

F_1 =\displaystyle\frac{3 E I_s }{ L ^3} u_1



and the stress to deformation with a fixed point (\sigma_1), which depends on the outdoor radio (R_2), is given by

\sigma_1 =\displaystyle\frac{2 R_2 L }{3 I_s } F_1

ID:(739, 0)



Bending with two Fixed Points

Concept

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One possible scenario is that a deformation force with two fixed points (F_2) acts on a bone with properties a body length (L), the modulus of Elasticity (E), and the moment of inertia of surface (I_s), which is fixed at both ends:

None



the strain energy with two fixed points (W_2), storing the structure against a movement in flexion with two fixed points (u_2), is given by

W_2 =\displaystyle\frac{24 E I_s }{ L ^3} u_2 ^2



the deformation force with two fixed points (F_2), the applied force, leads to a movement in flexion with two fixed points (u_2) as per

F_2 =\displaystyle\frac{48 E I_s }{ L ^3} u_2



and the stress to deformation with two fixed points (\sigma_2), which depends on the outdoor radio (R_2), is expressed as

\sigma_2 =\displaystyle\frac{ R_2 L }{3 I_s } F_2

ID:(740, 0)



Buckling

Condition

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One possible scenario is that a deformation force in buckling condition (F_p) acts along the axis of the bone with properties a body length (L), the modulus of Elasticity (E), the buckling factor (K), the effective radius (R), and the moment of inertia of surface (I_s), inducing buckling:

None



the strain energy in buckling condition (W_p), is defined as

W_p =\displaystyle\frac{ \pi ^4 E I_s }{2 K ^4 L ^3} R ^2



the deformation force in buckling condition (F_p), the applied force, according to

F_p =\displaystyle\frac{ \pi ^2 E I_s }{ K ^2 L ^2}



and the stress to deformation in the case of buckling (\sigma_p), which depends on the outdoor radio (R_2), is expressed as

\sigma_p =\displaystyle\frac{ \pi ^2 E I_s }{ K ^2 L ^2 S }

ID:(741, 0)



Bone deformation due to torsion

Concept

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One way to cause a fracture is through bone torsion, which involves applying opposite torques at the ends:

ID:(1916, 0)



Elastic deformation of the Solido Structure

Concept

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Microscopic elastic deformation corresponds to a modification in the distance between atoms under an external force, without any rearrangement of these atoms.

None

In general, it's a deformation where the distance changes proportionally to the applied force, referred to as elastic deformation.

ID:(1685, 0)



Permanent Deformation explained with Atoms

Concept

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Plastic deformation means that if the applied stress is reduced, the material decreases its deformation but ends up with a permanent deformation.

None

Therefore, if it's subjected to stress again, it generally returns to its elastic form, but due to the new shape, it can't recover its original form.

ID:(1911, 0)



Plastic deformation in the Solido Structure

Concept

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Plastic deformation involves atoms rearranging themselves, dissociating from existing structures, and forming new bonds that are inherently stable. However, such deformation typically entails a modification in the shape of the material.

None

Plastic deformation can ultimately lead to changes that may include catastrophic ruptures, which are permanent.

ID:(1686, 0)



The bone

Image

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We will work with a bone and with the fall and impact scenarios. The bone parameters and material properties are summarized here:

Geometry and elasticity

ID:(1556, 0)



Impact fracture

Image

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If a player is impacted in the middle of the bone, considering the foot due to friction and the body due to inertia as fixed points, it results in a load that flexes the bone.

None

Question of interest: What are the energy, stress, force, displacement, and jump height at which buckling would occur? (W_{tv}, \sigma_{tv}, F_{tv}, u_{tv}, v).

ID:(1560, 0)



The dynamics

Image

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Two situations are considered, fall (break due to buckling, compression or flexion) and impact on the central part of the bone (break due to flexion).

ID:(1557, 0)



Model

Top

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Parameters

Symbol
Text
Variable
Value
Units
Calculate
MKS Value
MKS Units
L
L
Body length
m
S
S
Body Section
m^2
K
K
Buckling factor
-
R
R
Effective radius
m
R_1
R_1
Inside radio
m
E
E
Modulus of Elasticity
Pa
I_s
I_s
Moment of inertia of surface
R_2
R_2
Outdoor radio
m
\pi
pi
Pi
rad

Variables

Symbol
Text
Variable
Value
Units
Calculate
MKS Value
MKS Units
F_p
F_p
Deformation force in buckling condition
N
F_1
F_1
Deformation force with a fixed point
N
F_2
F_2
Deformation force with two fixed points
N
u_1
u_1
Flexion displacement with a fixed point
m
u_2
u_2
Movement in flexion with two fixed points
m
W_p
W_p
Strain energy in buckling condition
J
W_1
W_1
Strain energy with a fixed point
J
W_2
W_2
Strain energy with two fixed points
J
\sigma_p
sigma_p
Stress to deformation in the case of buckling
Pa
\sigma_1
sigma_1
Stress to deformation with a fixed point
Pa
\sigma_2
sigma_2
Stress to deformation with two fixed points
Pa

Calculations


First, select the equation: to , then, select the variable: to
F_1 = 3* E * I_s * u_1 / L ^3 F_2 = 48* E * I_s * u_2 / L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) I_s = pi *( R_2^4 - R_1 ^4)/2 S = pi *( R_2 ^2- R_1 ^2) sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) sigma_2 = R_2 * L * F_2 /(3* I_s ) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) W_2 =24* E * I_s * u_2 ^2/ L ^3 W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

Calculations

Symbol
Equation
Solved
Translated

Calculations

Symbol
Equation
Solved
Translated

Variable Given Calculate Target : Equation To be used
F_1 = 3* E * I_s * u_1 / L ^3 F_2 = 48* E * I_s * u_2 / L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) I_s = pi *( R_2^4 - R_1 ^4)/2 S = pi *( R_2 ^2- R_1 ^2) sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) sigma_2 = R_2 * L * F_2 /(3* I_s ) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) W_2 =24* E * I_s * u_2 ^2/ L ^3 W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2




Equations

#
Equation

F_1 =\displaystyle\frac{3 E I_s }{ L ^3} u_1

F_1 = 3* E * I_s * u_1 / L ^3


F_2 =\displaystyle\frac{48 E I_s }{ L ^3} u_2

F_2 = 48* E * I_s * u_2 / L ^3


F_p =\displaystyle\frac{ \pi ^2 E I_s }{ K ^2 L ^2}

F_p = pi ^2* E * I_s /( K ^2* L ^2)


I_s =\displaystyle\frac{ \pi }{2}( R_2 ^4- R_1 ^4)

I_s = pi *( R_2^4 - R_1 ^4)/2


S = \pi ( R_2 ^2- R_1 ^2)

S = pi *( R_2 ^2- R_1 ^2)


\sigma_1 =\displaystyle\frac{2 R_2 L }{3 I_s } F_1

sigma_1 = 2* R_2 * L * F_1 /(3* I_s )


\sigma_2 =\displaystyle\frac{ R_2 L }{3 I_s } F_2

sigma_2 = R_2 * L * F_2 /(3* I_s )


\sigma_p =\displaystyle\frac{ \pi ^2 E I_s }{ K ^2 L ^2 S }

sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S )


W_1 =\displaystyle\frac{3 E I_s }{2 L ^3} u_1 ^2

W_1 =3* E * I_s * u_1 ^2/(2* L ^3)


W_2 =\displaystyle\frac{24 E I_s }{ L ^3} u_2 ^2

W_2 =24* E * I_s * u_2 ^2/ L ^3


W_p =\displaystyle\frac{ \pi ^4 E I_s }{2 K ^4 L ^3} R ^2

W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3)


R^2=R_1^2+R_2^2

R^2=R_1^2+R_2^2

ID:(15579, 0)



Effective radius

Equation

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The integration over the section with the inside radio (R_1) and the outdoor radio (R_2) leads to the introduction of the effective radius (R), defined by:

R^2=R_1^2+R_2^2

R
Effective radius
m
7700
R_1
Inside radio
m
5378
R_2
Outdoor radio
m
5377
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(7972, 0)



Section

Equation

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With the outdoor radio (R_2) and the inside radio (R_1), the body Section (S) is defined as

S = \pi ( R_2 ^2- R_1 ^2)

S
Body Section
m^2
5352
R_1
Inside radio
m
5378
R_2
Outdoor radio
m
5377
\pi
Pi
3.1415927
rad
5057
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(3784, 0)



Moment of Surface Inertia

Equation

>Top, >Model


The moment of inertia of surface (I_s) is calculated in the case of a cylinder with the outdoor radio (R_2) and the inside radio (R_1) through

I_s =\displaystyle\frac{ \pi }{2}( R_2 ^4- R_1 ^4)

R_1
Inside radio
m
5378
I_s
Moment of inertia of surface
m^4
5376
R_2
Outdoor radio
m
5377
\pi
Pi
3.1415927
rad
5057
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(3774, 0)



Bending with two Fixed Points, Energy

Equation

>Top, >Model


The relationship between the strain energy with two fixed points (W_2) and the movement in flexion with two fixed points (u_2) in a bending with two fixed points depends on the modulus of Elasticity (E), the body length (L), and the moment of inertia of surface (I_s) is

W_2 =\displaystyle\frac{24 E I_s }{ L ^3} u_2 ^2

L
Body length
m
5355
E
Modulus of Elasticity
Pa
5357
I_s
Moment of inertia of surface
m^4
5376
u_2
Movement in flexion with two fixed points
m
10340
W_2
Strain energy with two fixed points
J
10337
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(3780, 0)



Bending with two fixed points, force

Equation

>Top, >Model


The relationship between the deformation force with two fixed points (F_2) and the movement in flexion with two fixed points (u_2) in a bending with two fixed points depends on the modulus of Elasticity (E), the body length (L), and the moment of inertia of surface (I_s). In this context,

F_2 =\displaystyle\frac{48 E I_s }{ L ^3} u_2

L
Body length
m
5355
F_2
Deformation force with two fixed points
N
10346
E
Modulus of Elasticity
Pa
5357
I_s
Moment of inertia of surface
m^4
5376
u_2
Movement in flexion with two fixed points
m
10340
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(3778, 0)



Bending with two fixed points, stress

Equation

>Top, >Model


The relationship between the stress to deformation with two fixed points (\sigma_2) and the deformation force with two fixed points (F_2) in a bending with two fixed points depends on the outdoor radio (R_2), the body length (L), and the moment of inertia of surface (I_s). In this context,

\sigma_2 =\displaystyle\frac{ R_2 L }{3 I_s } F_2

L
Body length
m
5355
F_2
Deformation force with two fixed points
N
10346
I_s
Moment of inertia of surface
m^4
5376
R_2
Outdoor radio
m
5377
\sigma_2
Stress to deformation with two fixed points
Pa
10343
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(3779, 0)



Bending with a fixed point, energy

Equation

>Top, >Model


The relationship between the strain energy with a fixed point (W_1) and the flexion displacement with a fixed point (u_1) in a bending with a fixed point depends on the modulus of Elasticity (E), the body length (L), and the moment of inertia of surface (I_s) is:

W_1 =\displaystyle\frac{3 E I_s }{2 L ^3} u_1 ^2

L
Body length
m
5355
u_1
Flexion displacement with a fixed point
m
10341
E
Modulus of Elasticity
Pa
5357
I_s
Moment of inertia of surface
m^4
5376
W_1
Strain energy with a fixed point
J
10338
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(3777, 0)



Bending with a fixed point, force

Equation

>Top, >Model


The relationship between the deformation force with a fixed point (F_1) and the flexion displacement with a fixed point (u_1) in a bending with a fixed point depends on the modulus of Elasticity (E), the body length (L), and the moment of inertia of surface (I_s) is:

F_1 =\displaystyle\frac{3 E I_s }{ L ^3} u_1

L
Body length
m
5355
F_1
Deformation force with a fixed point
N
10347
u_1
Flexion displacement with a fixed point
m
10341
E
Modulus of Elasticity
Pa
5357
I_s
Moment of inertia of surface
m^4
5376
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(3775, 0)



Bending with a fixed point, stress

Equation

>Top, >Model


The relationship between the stress to deformation with a fixed point (\sigma_1) and the deformation force with a fixed point (F_1) in a bending with a fixed point depends on the outdoor radio (R_2), the body length (L), and the moment of inertia of surface (I_s) is

\sigma_1 =\displaystyle\frac{2 R_2 L }{3 I_s } F_1

L
Body length
m
5355
F_1
Deformation force with a fixed point
N
10347
I_s
Moment of inertia of surface
m^4
5376
R_2
Outdoor radio
m
5377
\sigma_1
Stress to deformation with a fixed point
Pa
10344
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2

ID:(3776, 0)



Buckling, energy

Equation

>Top, >Model


The strain energy in buckling condition (W_p) in buckling depends on the modulus of Elasticity (E), the body length (L), the moment of inertia of surface (I_s), the effective radius (R), and the buckling factor (K) is

W_p =\displaystyle\frac{ \pi ^4 E I_s }{2 K ^4 L ^3} R ^2

L
Body length
m
5355
K
Buckling factor
-
5379
R
Effective radius
m
7700
E
Modulus of Elasticity
Pa
5357
I_s
Moment of inertia of surface
m^4
5376
\pi
Pi
3.1415927
rad
5057
W_p
Strain energy in buckling condition
J
10339
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2



The value of the buckling factor (K) is:

• 0.5 if both edges are fixed,

• 1.0 if both can rotate,

• 0.7 if one is fixed and the other can rotate, and

• 2.0 if both are free.

ID:(3783, 0)



Buckling force

Equation

>Top, >Model


The deformation force in buckling condition (F_p) in buckling depends on the modulus of Elasticity (E), the body length (L), the moment of inertia of surface (I_s), and the buckling factor (K).

F_p =\displaystyle\frac{ \pi ^2 E I_s }{ K ^2 L ^2}

L
Body length
m
5355
K
Buckling factor
-
5379
F_p
Deformation force in buckling condition
N
10348
E
Modulus of Elasticity
Pa
5357
I_s
Moment of inertia of surface
m^4
5376
\pi
Pi
3.1415927
rad
5057
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2



The value of the buckling factor (K) is:

• 0.5 if both edges are fixed,

• 1.0 if both can rotate,

• 0.7 if one is fixed and the other can rotate, and

• 2.0 if both are free.

ID:(3781, 0)



Buckling, stress

Equation

>Top, >Model


The stress to deformation in the case of buckling (\sigma_p) in buckling depends on the modulus of Elasticity (E), the body length (L), the moment of inertia of surface (I_s), the body Section (S), and the buckling factor (K).

\sigma_p =\displaystyle\frac{ \pi ^2 E I_s }{ K ^2 L ^2 S }

L
Body length
m
5355
S
Body Section
m^2
5352
K
Buckling factor
-
5379
E
Modulus of Elasticity
Pa
5357
I_s
Moment of inertia of surface
m^4
5376
\pi
Pi
3.1415927
rad
5057
\sigma_p
Stress to deformation in the case of buckling
Pa
10345
I_s = pi *( R_2^4 - R_1 ^4)/2 F_1 = 3* E * I_s * u_1 / L ^3 sigma_1 = 2* R_2 * L * F_1 /(3* I_s ) W_1 =3* E * I_s * u_1 ^2/(2* L ^3) F_2 = 48* E * I_s * u_2 / L ^3 sigma_2 = R_2 * L * F_2 /(3* I_s ) W_2 =24* E * I_s * u_2 ^2/ L ^3 F_p = pi ^2* E * I_s /( K ^2* L ^2) sigma_p = pi ^2* E * I_s /( K ^2* L ^2* S ) W_p = pi ^4* E * I_s * R ^2/(2* K ^4 * L ^3) S = pi *( R_2 ^2- R_1 ^2)R^2=R_1^2+R_2^2LSKF_pF_1F_2Ru_1R_1EI_su_2R_2piW_pW_1W_2sigma_psigma_1sigma_2



The value of the buckling factor (K) is:

0.5 if both edges are fixed,

1.0 if both can rotate,

0.7 if one is fixed and the other can rotate, and

2.0 if both are free.

ID:(3782, 0)