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Research Papers

Origami Crash Boxes Subjected to Dynamic Oblique Loading

[+] Author and Article Information
Caihua Zhou, Xiangjun Bi

State Key Laboratory of Structural Analysis
for Industrial Equipment,
Department of Engineering Mechanics,
Dalian University of Technology,
Dalian 116024, China

Liangliang Jiang

Beijing Institute of Astronautical
Systems Engineering,
Beijing 100076, China

Kuo Tian

State Key Laboratory of Structural
Analysis for Industrial Equipment,
Department of Engineering Mechanics,
Dalian University of Technology,
Dalian 116024, China

Bo Wang

State Key Laboratory of Structural Analysis
for Industrial Equipment,
Department of Engineering Mechanics,
Dalian University of Technology,
Dalian 116024, China
e-mail: wangbo@dlut.edu.cn

1Corresponding author.

Contributed by the Applied Mechanics Division of ASME for publication in the JOURNAL OF APPLIED MECHANICS. Manuscript received May 5, 2017; final manuscript received June 23, 2017; published online July 12, 2017. Assoc. Editor: Weinong Chen.

J. Appl. Mech 84(9), 091006 (Jul 12, 2017) (11 pages) Paper No: JAM-17-1236; doi: 10.1115/1.4037160 History: Received May 05, 2017; Revised June 23, 2017

The energy absorption capacity of origami crash boxes (OCB) subjected to oblique loading is investigated in the present study. A conventional square tube (CST) with identical weight is employed as benchmark. The comparative study reveals that the origami crash box is more desirable than the conventional square tube in most of the range of load angle. A parameter study is performed to assess the effect of geometry parameters on the energy absorption characteristics. The geometry parameters are tube length L, tube width b, module length l, and width of folded lobe c. Considering that bamboo with large slenderness ratio could effectively resist wind load, a bulkhead-reinforced origami crash box is proposed as a high-performance energy absorption device. And an optimum structure designed based on the parameter study is investigated. The result suggests that the proposed tube performs much better than the original design.

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References

Figures

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Fig. 1

(a) A module of the OCB; (b) a module of the origami pattern for origami crash box; (c) an OCB assembled by five modules

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Fig. 2

Representative finite element model (note that the origami crash box with M = 5, L = 300 mm, b = 60 mm, l = 60 mm, c = 30 mm, t = 1 mm is potted here)

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Fig. 3

Engineering stress–strain curve

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Fig. 4

Mesh sensitivity study on OCB. (Note that the tube O0 subjected to oblique loading with α=7deg is investigated).

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Fig. 5

Deformed profiles of OCB from (a) experiment (T16 in Ref. [26]) and (b) FE simulation

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Fig. 6

Deformed profiles of CST from (a) experiment (T59 in Ref. [26]) and (b) FE simulation

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Fig. 7

The comparison between experimental and numerical results using force versus displacement curves of (a) OCB and (b) CST

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Fig. 8

Crushing force versus displacement curves for (a) O0 and (b) C0

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Fig. 9

Specific energy absorption (SEA) versus the load angle curves for (a) O0 and (b) C0

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Fig. 10

(a) Normalized SEA versus load angle curve and (b) normalized Pmax versus load angle curve

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Fig. 11

(a) Models of L_120 to L_420 and (b) SEA and Pmax versus L/t curves

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Fig. 12

(a) Models B_40 to B_100 and (b) SEA and Pmax versus b/t curves

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Fig. 13

Crushed configuration of B_40 and B_80

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Fig. 14

(a) Models l_15 to l_100 and (b) SEA and Pmax versus l/t curves

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Fig. 15

Crushed configurations of l_15, l_20, and l_25

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Fig. 16

(a) Models C_12 to C_30 and (b) SEA and Pmax versus c/l curves

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Fig. 17

(a) The bulkhead origami crash box and (b) SEA and Pmax versus t1/t curves

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Fig. 18

Crushed configurations of T_6 and T_8

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Fig. 19

(a) Normalized SEAα versus load angle curves and (b) normalized Pmax versus load angle curves

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