C h a p t e r 5 Spatial Buckling of Struts

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1 C h a p t e r 5 Spatial Buckling of Struts

2 5.1. Lateral-Torsional Buckling of Columns
[Halasz, 1965] [Wagner, 1936] [Kappus, 1937] [Goodier, 1941] [Bleich, 1952] [Timoshenko, Gere, 1961] [Vlasov, 1961] [Murray, 1984]

3 5.1.1 Equilibrium Method for General Open Cross-section Column

4 (a) Displacements of the cross-section
Centroid C (y=z=0):

5 (b) Equilibrium equations
Bending moments:

6 There are two factors which contribute further torque components.
The first component is due to the fact that P retains its original direction. In the y-x plane, therefore, P has a component P*du/dx which acts through the centroid. Together with component of P in the z-x plane the column has thus a twisting moment about the shear centre.

7 The second component contribution to MT is caused by the fact that two cross-sections dz apart will warp with respect to each other, and therefore the stress element sdA is inclined by the angle a to the axis x. The component of the stress element is And it causes a twist about the shear centre. Moment of polar inertia for the shear centre Radius of gyration for the shear centre

8 (c) Solution of equilibrium equations
Saint-Venant torsion: (c) Solution of equilibrium equations Non-uniform torsion: Equilibrium: Boundary conditions:

9 Substitution of the deflections and their derivatives into the DE gives three homogeneous simultaneous equations. The vanishing of the determinant formed by the coefficients C1, C2 and C3 gives the following buckling conditions: Non-trivial solution:

10 Third-order algebraic equation:
The critical value of P is always less than either Pez, Pey and Pw, and must therefore be computed!

11 (d) Plane or spatial buckling load is minimum?
We can prove this as follows. Then: (a) (b) (c) (d) Let us call the left side of det. F(P) and assume arbitrarily that:. (e)

12 Critical loads belonging to in-plane and spatial buckling

13 5.1.2 Energy Method for General Open Cross-section Column
(a) Strain energy of torsion [Galambos, 1968] [Chajes, 1974] St. Venant torsion: Warping torsion:

14 (b) Total strain energy
(c) The potential energy of external loads From the Pythagorean theorem the length ds of the deformed element is:

15 The total displacements of the fibre at (y,z) are therefore:
To simplify this expression, we make use of the following relations: The potential energy of external loads:

16 (d) Simple supported column
Boundary conditions: Assumed buckling shape: Strain energy:

17 Potential energy of the external load:
Total potential energy: Stationary value  all the derivatives vanish:

18 5.1.3 Double-Symmetric Open Cross-section
Mono-Symmetric Open Cross-section

19 Two possibilities considered:
(a) Euler-type flexural in-plane buckling in x-z plane: (b) Flexural-torsional buckling: and [Gerard, Becker, 1957] [Chajes, Winter, 1965]

20 Limit curves to separate plane and spatial buckling
Parameters to be used: Limit curves to separate plane and spatial buckling

21 (Values of r coefficient are shown in the next slide)
Design process: Ideal slenderness (Values of r coefficient are shown in the next slide)

22 Values of r coefficient for spatial (flexural-torsional) buckling

23 5.1.5 Column with Closed Cross-section
[Hunyadi, 1962]

24

25 5.1.6 Lateral-Torsional Buckling of Columns with Imperfections
[Hunyadi, 1962] [Iványi, Hunyadi, 1988] External moments: Equilibrium equation:

26 Solution: Open cross-section: Closed cross-section:

27 5.2. Lateral-Torsional Buckling of Beams
[Prandtl, 1899] [Mitchell, 1899] [Timoshenko, 1910] [Lee, 1960] [Nethercot, 1983] [Trahair, Bradford, 1988]

28 5.2.1 Equilibrium Method for Beams in Pure Bending
(a) Rectangular Cross-section [Chen, Lui, 1987] Boundary conditions: Bending and torsion:

29 For rectangular cross-section it is supposed:
Substitution of the expressions in DE, leads to the following equations: Moment components:

30 Non-trivial solution:
For rectangular cross-section: Boundary conditions:

31 (b) “I” Cross-section [Timoshenko, 1910]
Initial assumptions and boundary conditions are the same as for rectangular section, but:

32 Non-trivial solution:
Boundary conditions:

33 If: If: If:

34 5.2.2 Energy Method for Beams in Bending
(a) “I” Cross-section Simple Supported Beams in Pure Bending [Chajes, 1974] [Allen, Bulson, 1980] [Chen, Lui, 1987] Strain energy:

35 Potential energy of external loads:

36 Boundary conditions:

37 (b) Fixed Ends Beam in Pure Bending
Boundary conditions:

38 (c) Uniform Bending – The Ends Free to Rotate About Horizontal and Vertical Axis, but Fully Restrained Against the Warping of End Cross-section Boundary conditions: This value is 3.3% more than the “exact” result

39 5.2.3 Lateral-Torsional Buckling of Beams with Initial Imperfections
[Hunyadi, 1962]

40 – for open cross-section
– for closed cross-section

41 5.2.4 Design Method: Fundamental Solutions
Two components of vector of bending moments M : Bending moments: Bimoment: Superpose: Stresses:

42 (a) Mono-Symmetric “I” Cross-section
Open cross-section: Closed cross-section: [Hunyadi, Ivanyi, 1991] Equilibrium DE:

43 Critical moment: At the beginning of buckling:

44 Safety factor:

45 For double-symmetric cross-section it can be supposed:
In the previous figure: Thus: At lateral-torsional buckling:

46 (b) Ayrton-Perry Formula
[Costa Ferreira, Rondal, 1987] Initial imperfection:

47 Suggestion for the formula:
(i) Costa Ferreira and Rondal I. Cross-section a Welded Rolled (ii) Costa Ferreira and Rondal II. Cross-section a Welded Rolled [Barta, 1972]

48 (c) Rankine-Merchant Formula
In elastic state: In plastic state:

49 Fukumoto and Kubo Suggestion
Result: Expression: In general: Fukumoto and Kubo Suggestion n=2.5 for rolled cross-sections n=2.0 for welded cross-sections

50 (d) Experimental Tests and Hungarian Standard (MSZ)

51 Experimental results for welded cross-sections:
Experimental results for hot-rolled cross-sections: Hungarian Standard (MSZ) regulation:

52 (e) Effect of the Shape of Cross-section
[Trahair, 1993]

53

54 5.2.5 Design Method: General Solution
[Clark, Hill, 1961] Total potential energy: From the equilibrium: Transversal load: Transformation: Bending Moments

55 (Eurocode 3) Equivalent bending moment parameter

56 5.3. Lateral-Torsional Buckling of Beam-Columns
Stability Requirements. Experimental Results General remarks

57 5.3.1.2 Bracing requirements for continuous beams

58 5.3.1.3 Bracing requirements for beam-columns
(a) Requirements in the ECCS Recommendations (b) Proposals of British authors

59

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61 5.3.1.4 Test Results [Halász, Iványi, 1979]
(a) Effect of lateral buckling of beam-columns (b) Effects of change in geometry  Rankine-Merchant formula:

62 5.3.2 Draft of Hungarian Specifications for Plastic Design
[Halász, Iványi, 1979]

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