Plate Buckling ref. Hughes Chapter 12
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1 Plate Buckling ref. Hughes Chapter 1 Buckling of a plate simply supported on loaded edges treated as a wide column results in similar Euler stress, with EI replaced byd*(b): dividing by area (b*t): π Db π Et 3 eqn 9.1.5, 1/b D D := P e := σ e := a a 1( 1 ν t ) implied Buckling of a simply supported plate. i.e. simply supported on all four sides deflected shape is represented by sine waves in x and y: wx, y) := C m and n are the number of half waves in ( mn m n π a D m + n argument in text for minimum stress a b can specify n = 1, but m not clear σ acr := tm with n = 1, can express in form where k is buckling coefficient in equation eqn σ acr := k π D N.B. shift to plate width b in denominator b t m := 1.. n := 1.. a_over_b := 0.5, k(a_over_b, m) := m + a_over_b eqn sin mπx sin nπy, a b deflection eqn k(a_over_b, 1) k min (a_over_b) := min k(a_over_b, ) k(a_over_b, 3) k(a_over_b, 4) 6 a_over_b m k min (a_over_b) 5 therefore for long plates, simply supported on loaded ends k = 4 4 σ acr := 4 π D b t a_over_b very wide i.e. a/b -> 0, approaches Euler as a<<b σ acr (a_over_b) := k min (a_over_b) π D k -> b a + = b + a -> b b t a b ab a 1 notes_9_plate_buckling.mcd
2 a square column meets these boundary conditions hence will buckle with each edge forming half sine wave deflection in half sine waves approaching square for large a/b; long plate loaded on end simply supported on all sides Plate loaded on all four sides; σ ax in a direction, σ ay in b direction Again taking two half wave sine series using energy methods, results in combination expression for both stresses, again taking minimum of straight lines from: critical m σ ax + n σ ay 1 = m + n σ acr := 4 π D stress with α σ axcr1 σ axcr1 b t 4 α only σ ax σ axcr1 := σ acr σ σ ymn, ( ay ( ax, α), α) := α := a := xmn, σ axcr1 σ axcr1 b 1 y 1 ( xm,, n, α ) := m + n m x 4n α nα x := 1.5, fig 9.5 in T&G y 1 ( xm,, n, α ), y1 ( xm,, n, α ), (y 1 ( xm,, n, α )), y 1 ( xm,, n, α ), y1 ( xm,, n, α ), y1 ( xm,, n, α ) y 1 (x1,, 1, 1) 4 y 1 (x,, 1, 1) ( y 1 (x1,,, 1) ) y 1 (x,,, 1) y 1 (x3,, 1, 1) 0 y 1 (x1,, 3, 1) x notes_9_plate_buckling.mcd
3 Buckling stresses of biaxially loaded simply supported plates only taking m=n=4 terms. Effect of higher terms would be seen in lower right corner asymptote. x := 1, y 1 ( x1,, 1, α ) y1 ( x1,,, α ) y1 ( x1,, 3, α ) y1 ( x1,, 4, α ) y ( 1 ( x,, 1, α ) y1 ( x,,, α ) y1 ( x,, 3, α ) y1 ( x,, 4, α ) yx, α) := min y 1 ( x3,, 1, α ) y1 ( x3,,, α ) y1 ( x3,, 3, α ) y1 ( x3,, 4, α ) y1 ( x4,, 1, α ) y1 ( x4,,, α ) y1 ( x4,, 3, α ) y1 ( x4,, 4, α ) 4 3 y(x, 0.5) y(x, 0.75) yx (, 1) yx (, ) yx (, 3) x 3 notes_9_plate_buckling.mcd
4 Biaxial loading all edges clamped: σ ax is relative to π *D/(b *t) α + σ ax ( α, σay_over_σax ) := ( α eqn in T&G form α σay_over_σax) tbl. 1-3 σ ax (1., 0) = σ ax (1, ) = , 0 σ ax (11), = σ ax (1, 0.5) = , 8.80 per T&G good for shape close to square, data does not compare well with Hughes tbl. 1.3 or T&G tbl 9-15 plate buckling due to pure shear: simply supported on four sides: T&G article 9.7, page 379ff τ cr := π π D 1 σ ref := π D h = thickness = t 3 b h λ b h from five equations := 1, = a/b π ( ) := π D 3 ( ) b h λ τ cr 1 ( ) := λ ( ) k in τ cr := k π D π 1 becomes k ( ) := close for = <, no good elsewhere ( ) b 3 λ h it's probably ok by T&G, for few equations 4 compare with simple curve fit k 1 ( ) := exact solution for very long plates = a/b -. is k = At = 1 k = 9.34 exact. k1 ( ) 1 = less than 1% difference more complexity doesn't buy anything 9.34 k (b_over_a) := b_over_a := 0., π b_over_a 1 3 λ 1 k 1a (b_over_a) := b_over_a b_over_a k (b_over_a) 8 k 1a (b_over_a) 6 k ( ) k 1 ( ) b_over_a, b_over_a 4 notes_9_plate_buckling.mcd
5 table 9-10 in T&G page 38; values of k in τ cr := k π D from the results of the solution by determinants = 0. b h tbl_9_10 := i := k3 i := tbl_9_10 1i, b_over_a 3i := tbl_9_10 0i 1, 10 k (b_over_a) k 1a (b_over_a) k clamped on four sides critical shear stress b_over_a, b_over_a, b_over_a 3 T & G only provides infinitely long value of τ cr 8.98 π D := and then plots combination b h 5 notes_9_plate_buckling.mcd
6 Interaction formula for combination of shear stress and axial load from ref 10 (in AA library) when a/b > 1, problem is one of axial stress, and parabola is good model. When a/b is less than one, it is the equivalent of a transverse stress with shear. Parabola is not a good fit. Hence Hughes model based on a/b. R c (R s, α) := if 1 R s α > 1, 1 R s, if R s > 3 ( 1 α ), 8 ( α ) 1.6, 1 eqn R s := 0, fr ( s, α) := 1 R s α := 0.5 looks a transverse stress with a/b = 4. since α <1, parabola doesn't fit well with Rc(Rs,α). Curve lays on top when α>1, (by definition) R s R s R c ( R s, α), f( R s, α ) 6 notes_9_plate_buckling.mcd
7 Ultimate strength of plates: ( ) := := ξ Es_over_E ( ) := ξ ( ) ( ) 10.4 ξ b t σ Y σr_over_σy := 0.0 for curve in text: set this parameter to 0.1 σau_overσy ( ) ( ) ξ ( ) 10.4 := 0.5 4σr_over_σy + ξ Faulkner 1 E with reduction σr_over_σy = 0 σau_over_σy F ( ) := if < 1, 1, Ets_over_E ( ) := if < 1, 0, if >.5, 1, ( 1) to correct for residual stress σau_overσy E ( ) := 3.6 for reference := 0.01, σau_overσy ( ) σau_over_σy F ( ) 0.6 σau_overσy E ( ) similar to fig 1.5 in text 7 notes_9_plate_buckling.mcd
8 bringing in some other standards: AISI and UK (new) from Professor Wirrzbicki's Manual for Crash Wothiness Engineering Feb 1989 CTS MIT and in handout validation of plate buckling note: be/b is another way of representing peak load b e σ Y = bσ cr σ cr_over_σy ( ) := 1.9 σ Y_over_σcr ( ) := 1.9 C ( ) := if > 1.5,.5 1.5, 1 ABS Alaa σau_overσy E ( ) := if > 1.9, 3.6, 1 for reference 1 := ( ) := if > 1, 1 14( ( ) 0.35) 4, 1 be_over_b uk + σ Y_over_σcr be_over_b aisi ( ) := if > 1, σ cr_over_σy ( ) ( σ cr_over_σy ( )), 1 := 0.5, σau_overσy ( ) σau_over_σy F ( ) σau_overσy E ( ) C ( ) be_over_b uk ( ) 0.4 be_over_b aisi ( ) notes_9_plate_buckling.mcd
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