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Influence of composite material laying parameters on the load-carrying capacity of type IV hydrogen storage vessel

  • Qian Zhang EMAIL logo , Wenchun Jiang , Jiupeng Yan , Jiangkun Bai , Hui Fan and Bingying Wang
Published/Copyright: December 2, 2024
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Science and Engineering of Composite Materials
From the journal Science and Engineering of Composite Materials Volume 31 Issue 1

Abstract

The composite material laying parameters are important factors affecting the carrying capacity and quality of the type Ⅳ hydrogen storage vessel. In this article, the composite laying scheme is designed and analyzed by the finite element method. Through 100 groups of laying schemes, the influence laws of circumferential winding layers, spiral winding layers, spiral winding angle, and laying sequence are summarized. The results show that, when the number of spiral winding layers and the number of circumferential winding layers exceed 35 and 25 respectively, the bearing capacity of the hydrogen storage vessel cannot be significantly improved with the increase of the layer number. With the increase in the spiral winding angles, the maximum S11 decreases first and then increases, while the maximum S22 stabilizes first and then increases. But, for different numbers of spiral layers, the turning point of stress rise is different, and the best winding angle is between 55° and 65°. It is found that performing circumferential winding first and then spiral winding is the best winding sequence.

Keywords: hydrogen storage pressure vessel; composite material laying parameters; Influence law; finite element analysis; carrying capacity

1 Introduction

Since the Paris Agreement, new energy vehicles have been developed worldwide. The transportation sector has formulated the strategy of using hydrogen fuel cell electric vehicles [1,2]. Hydrogen is increasingly regarded as a multifunctional future energy carrier, which releases greenhouse gas and air pollutant emissions close to zero and can fill different roles in the energy system [3,4]. However, due to the gas nature of hydrogen, it faces many challenging storage problems. Hydrogen can be stored by various physical and chemical methods [5,6,7], among which the hydrogen storage vessels have become the mainstream storage method due to their simple process and convenience [8]. At present, the most concerned product is the IV-type composite hydrogen storage vessel, which consists of the plastic liner and the carbon fiber layer fully wrapped around the plastic liner [9,10,11]. Due to the complexity of composite strength and failure modes [12,13], the design and manufacture of IV-type hydrogen storage vessels still face many problems, which are also concerned by researchers.

The internal pressure of the IV-type hydrogen storage vessel is mainly borne by the composite winding layer, which seriously affects the mechanical properties of the final hydrogen vessels. Therefore, the design of the carbon fiber winding layer is the key point. Experimental and theoretical studies show that the laying sequence and winding angle have important effects on the quality and mechanical properties of the vessel [14,15,16,17,18]. Park et al. [19] carried out geometric nonlinear finite element analysis to quantify the amount of winding angle change through the thickness direction. Various design parameters including winding thickness and spiral winding angle were considered during the analysis. They found that the winding angle difference near the opening of the first layer and last layer is 18°, and it is important to consider that the winding angle changes to predict the stress distribution of the dome and opening correctly. Rosenow [20] obtained that the optimal winding angle of a cylindrical thin-walled composite pressure vessel with a 0.5 ratio of axial stress to circumferential stress is 55° by taking different values of the filament winding angle between 15° and 85°. Kim et al. [21] studied the influence of the fiber winding direction and the fiber winding mode on gas vessels by comparing various optimization algorithms, including semi-geodesic path algorithm, progressive failure analysis, and genetic algorithm, and put forward their optimization suggestion. The performance of the optimized vessels improved by 23.5% based on their suggestions. Hu et al. [22] used the user-defined material subroutine based on the Hashin progressive damage model to predict the burst pressure and burst mode of the vessel and found that the fiber stress of the head affects the burst mode. The smaller the winding angle of the head, the better the reinforcement effect. The head reinforcement technology can transfer the maximum stress to the cylinder part of the vessel, and then the risk of blasting failure is reduced. Si et al. [23] studied the key mechanical and electrical properties of glass fiber wound tubes with winding angles of 40°, 45°, 50°, 55°, 60°, and 65°. The results show that in practical engineering applications, it is more appropriate to control the winding angle at 50°–60°, and multiangle composite winding can also be used. Ramirez et al. [24] simulated the bursting pressure and bursting mode of type IV high-pressure hydrogen storage vessel. The complex wound composite geometry and orientation were simulated using a specific ABAQUS plug-in named wound composite modeler (WCM). Sharma et al. [25] designed a type Ⅲ composite hydrogen storage vessel to store hydrogen fuel under working pressure of 35 MPa. The finite element model was verified by the test of a similar vessel. At the same time, the weight of the vessel was reduced by adjusting the winding angle, sequence, and thickness.

In summary, composite material laying parameters including laying sequence, winding angle, and number of winding layers have great effects on the quality of hydrogen storage vessel. These parameters are the key to improve bearing capacity, realize lightweight design, and reduce cost. However, the current research lacks comprehensiveness. Only individual composite material laying parameters were analyzed. In this article, the influence of composite material laying parameters on the bearing capacity is studied in detail, and different laying modes are designed and analyzed for comparison.

2 Finite element method

2.1 Structures and materials

The hydrogen storage vessel studied in this article consists of plastic liner, carbon fiber spiral wound layer, and carbon fiber circumferential wound layer. Figure 1 shows the structural diagram of the plastic liner of 237 L hydrogen storage vessel. The carbon fiber laying parameters are the number of spiral wound layers, the number of circumferential wounded layers, spiral wound angles, and the winding sequence.

Figure 1 Configurations of the liner (unit: mm).
Figure 1

Configurations of the liner (unit: mm).

The plastic liner is made of high-density polyethylene (HDPE), and the composite layer is wound by T700 carbon-fiber/epoxy. Table 1 shows the mechanical properties of HDPE, and Table 2 shows the mechanical properties of T700 carbon-fiber/epoxy. These material parameters are provided by the gas cylinder production company (Shandong Auyan New Energy Technology Co., Ltd., China).

Table 1

Mechanical properties of HDPE

Property Elasticity modulus (GPa) Poisson’s ratio Elongation
HDPE 0.9 0.41 ≥20%
Table 2

Mechanical property of T700 carbon-fiber/epoxy

E x (MPa) E y (MPa) E z (MPa) V xy V yz V xz G xy (MPa) G yz (MPa) G xz (MPa)
154,100 11,410 11,410 0.33 0.49 0.49 7,092 3,792 7,092

2.2 Models and verification

The finite element (FE) model of the hydrogen storage vessel is established by ABAQUS software combined with the WCM plug-in. The thickness and width of the used T700 carbon-fiber/epoxy tape are 0.35 and 14 mm, respectively. As the hydrogen storage vessel is rotationally symmetric, for the convenience of calculation, 1/36 or 1/4 models are adopted. The outer surface of the plastic liner is bound to the inner surface of the spiral wound layers, and at the same time, periodic boundary conditions are applied. To prevent rigid displacement of the vessel, a completely fixed constraint is imposed on the pole hole of the vessel. The FE models are meshed by C3D8R.

To ensure the reliability of the FE model, hydraulic testing of type Ⅳ hydrogen storage vessel was carried out at room temperature. A glass fiber protective layer has been added to the outermost part of the hydrogen storage vessel. According to the standard GB/T 15385-2022, the pressure increased at a rate of 0.5 MPa/s until the explosion. The type Ⅳ hydrogen storage vessel model for FE analysis has the same size parameters and laying methods as the tested hydrogen storage vessel. As shown in Figure 2(a), the simulation results of the 1/36 FE model show that the maximum S11 appears at the cylinder near the head, and the burst pressure is 60.5 MPa. Figure 2(b) shows that the type Ⅳ hydrogen storage vessel under hydraulic testing is damaged at the upper section of the cylinder, and the bursting pressure is 55.2 MPa. The error between the simulation and the experiment is only 9.6%. It indicates that the FE model and the simulation method are reliable.

Figure 2 The failure mode of the type Ⅳ hydrogen storage vessel: (a) simulation and (b) experiment.
Figure 2

The failure mode of the type Ⅳ hydrogen storage vessel: (a) simulation and (b) experiment.

In the first part, to study the influence of the number of spiral winding layers, the 1/36 hydrogen storage vessel model is established. The winding angle is set as 10°, and a total of seven groups, namely 7, 14, 21, 28, 35, 42, and 50 layers, are set. Taking a seven-layer model as an example, after element-independent checking, the element number of the plastic liner is 14,364, and the element number of spiral wound layers is 24,990, as shown in Figure 3.

Figure 3 Mesh and boundary conditions of the 1/36 hydrogen storage vessel FE model.
Figure 3

Mesh and boundary conditions of the 1/36 hydrogen storage vessel FE model.

In the second part, to study the influence of the number of circumferential wound layers, the 1/4 model is used for calculation convenience. Since the carrying capacity of the plastic liner can be ignored compared with the composite layers, only the carbon fiber circumferential wound layers are established for simulation. A total of 16 groups of circumferential winding method, namely, 5, 10, 15, 20, 25, 30, 35, 40, 45, 50, 55, 60, 65, 70, 75, and 80 layers, are analyzed. Taking a ten-layer model as an example, as shown in Figure 4, after element-independent checking, the FE model of circumferential wound layers is meshed by 5,270 elements.

Figure 4 Mesh and boundary conditions of ten-layer circumferential winding layer FE model.
Figure 4

Mesh and boundary conditions of ten-layer circumferential winding layer FE model.

In the third part, to study the influence of different spiral winding angles, a total of 75 groups of spiral winding methods are studied. The winding angles are set as 10°, 15°, 20°, 25°, 30°, 35°, 40°, 45°, 50°, 55°, 60°, 65°, 70°, 75°, and 80°, and the number of winding layers are 7, 14, 21, 28, and 35. In this part, the modeling method and constraints are the same as those of the first part.

In the fourth part, the influence of different winding sequences of spiral and circumferential layers are studied. The modeling method and constraints are the same as those of the first part. The spiral winding angle is set as 50° here. A total of three groups of winding methods are carried out. The winding method of the first group is 14 layers of spiral winding inside and 21 layers of circumferential winding outside. The second group is 21 layers of circumferential winding inside and 14 layers of spiral winding outside. The third group is 7 layers of spiral winding inside and 21 layers of circumferential winding in the middle and 7 layers of spiral winding outside.

The applied internal pressure of the four simulations above is 20 MPa.

3 Results and discussion

3.1 Influence of the number of the spiral winding layers

Taking the model of 28-layer spiral winding as an example, the stress along the fiber direction S11 and the stress perpendicular to the fiber direction S22 of the storage vessel are shown in Figures 5 and 6, respectively. It shows that the maximum stress S11 locates at the transition between the head and the cylinder, with the maximum value 975.9 MPa. Ignoring the stress at the fixed position, the maximum stress S22 occurs at the cylinder, with the maximum value of 45.9 MPa.

Figure 5 The stress along the fiber direction S11 of the 28-layer spiral winding model.
Figure 5

The stress along the fiber direction S11 of the 28-layer spiral winding model.

Figure 6 The stress perpendicular to the fiber direction S22 of the 28-layer spiral winding model.
Figure 6

The stress perpendicular to the fiber direction S22 of the 28-layer spiral winding model.

Tables 3 and 4 show the stress analysis results of different numbers of spiral winding layers. It can be seen that, for all winding methods, the maximum S11 always appears at the transition between the head and the cylinder, and the maximum S22 always appears at the middle section of the cylinder.

Table 3

Maximum value and position of S11 of different number of spiral winding layers

Number of layers Maximum S11 (MPa)
Value Position
7 2,169 Transition between head and cylinder
14 1,661 Transition between head and cylinder
21 1,261 Transition between head and cylinder
28 975.9 Transition between head and cylinder
35 781.3 Transition between head and cylinder
42 640.3 Transition between head and cylinder
50 548.1 Transition between head and cylinder
Table 4

Maximum value and position of S22 of different number of spiral winding layers

Number of layers Maximum S22 (MPa)
Value Position
7 193.7 Cylinder
14 91.7 Cylinder
21 60.9 Cylinder
28 45.9 Cylinder
35 36.9 Cylinder
42 29.5 Cylinder
50 26.0 Cylinder

Figure 7 shows the maximum S11 and S22 variation curves with the number of spiral winding layers increasing. It is found that with the increase of the number of spiral winding layers, the stress along the fiber direction S11 and that perpendicular to the fiber direction S22 decrease gradually. At the beginning, the stress decreases greatly. When the number of winding layers reaches 35, the stress decreases more gently.

Figure 7 The maximum S11 and S22 variation curves with the number of spiral winding layers increasing.
Figure 7

The maximum S11 and S22 variation curves with the number of spiral winding layers increasing.

The stress distribution along the thickness direction of the storage vessel is basically the same for different numbers of spiral winding layers, taking 28-layer spiral winding as an example. Figure 8 shows the S11 and S22 variation along the thickness direction of the 28-layer spiral winding. It shows that the maximum S11 appears at the innermost layer of the spiral winding layers. From the inside to the outside, the S11 first decreases and then increases. The turning point is in the middle of the spiral winding layers. The maximum S22 appears at the innermost layer of the spiral winding layers. It decreases from the inside to the outside layer by layer, but the stress change amplitude is small.

Figure 8 The S11 and S22 variation curves along the thickness direction of the 28-layer spiral winding.
Figure 8

The S11 and S22 variation curves along the thickness direction of the 28-layer spiral winding.

3.2 Influence of the number of the circumferential winding layers

Taking the model of 30-layer circumferential winding as an example, the stress along the fiber direction S11 and the stress perpendicular to the fiber direction S22 of the storage vessel are shown in Figure 9. It can be seen that the maximum S11 is at the outermost of the circumferential winding layer, and the maximum S22 is at the innermost of the circumferential winding layer.

Figure 9 The stress contour of the 30-layer circumferential winding model: (a) S11 and (b) S22.
Figure 9

The stress contour of the 30-layer circumferential winding model: (a) S11 and (b) S22.

Table 5 shows the stress analysis results of different numbers of circumferential winding layers. It can be seen that for all of the circumferential winding methods, the maximum S11 appears at the outermost layer, and the maximum S22 appears at the innermost layer.

Table 5

Stress analysis results of different numbers of circumferential winding layers

Number of layers Maximum S11 (MPa) Maximum S22 (MPa)
Value Position Value Position
5 2,607 Outermost layer 259.9 Innermost layer
10 1,431 Outermost layer 129.8 Innermost layer
15 976.1 Outermost layer 86.5 Innermost layer
20 743.6 Outermost layer 64.9 Innermost layer
25 601.6 Outermost layer 52.0 Innermost layer
30 504.6 Outermost layer 43.3 Innermost layer
35 433.7 Outermost layer 37.2 Innermost layer
40 379.1 Outermost layer 32.6 Innermost layer
45 336.3 Outermost layer 29.0 Innermost layer
50 305.2 Outermost layer 26.1 Innermost layer
55 277.3 Outermost layer 23.9 Innermost layer
60 255.4 Outermost layer 22.0 Innermost layer
65 236.1 Outermost layer 20.4 Innermost layer
70 220 Outermost layer 19.1 Innermost layer
75 206 Outermost layer 17.9 Innermost layer
80 193.7 Outermost layer 16.9 Innermost layer

Figure 10 shows the maximum S11 and S22 variation curves with the number of circumferential winding layers increasing. It is found that with the increase of the number of circumferential winding layers, the maximum S11 and maximum S22 decrease gradually. At the beginning, the stress decreases greatly. When the number of winding layers reaches 25, the stress decreases more gently.

Figure 10 The maximum S11 and S22 variation curves with the number of circumferential winding layers increasing.
Figure 10

The maximum S11 and S22 variation curves with the number of circumferential winding layers increasing.

As the stress distribution is the same for different numbers of circumferential winding layers, take 30-layer circumferential winding as an example. Figure 11 shows the stress distribution along the thickness direction of a 30-layer circumferential winding model. It shows that the maximum S11 appears at the outermost layer. With the increase in the number of circumferential winding layers, the maximum S11 first keeps stable and then increases, and the turning point is at the middle layer. The maximum S22 appears at the innermost layer, and the change amplitude of S22 from inside to outside is small.

Figure 11 The S11 and S22 variation curve along the thickness direction of the 30-layer circumferential winding.
Figure 11

The S11 and S22 variation curve along the thickness direction of the 30-layer circumferential winding.

3.3 Influence of the spiral winding angles

Table 6 shows the stress analysis results of 28-layer models with different spiral winding angles. It can be seen that, with the increase of the winding angles, the position of the maximum S11 changes from the transition between the head and the cylinder to the middle section of the head, while the position of the maximum S22 changes from the cylinder to the middle section of the head.

Table 6

The stress analysis results of 28-layer models with different spiral winding angles

Winding angle (°) Maximum S11 (MPa) Maximum S22 (MPa)
Value Position Value Position
10 975.9 Transition between head and cylinder 45.9 Cylinder
15 951.2 Transition between head and cylinder 45.8 Cylinder
20 917.1 Transition between head and cylinder 45.8 Cylinder
25 873.2 Transition between head and cylinder 45.8 Cylinder
30 819.4 Transition between head and cylinder 46.4 Cylinder
35 755.6 Transition between head and cylinder 47.2 Cylinder
40 682.7 Transition between head and cylinder 47.8 Cylinder
45 603.6 Transition between head and cylinder 48.3 Cylinder
50 523.6 Transition between head and cylinder 48.3 Cylinder
55 450.6 Transition between head and cylinder 47.8 Cylinder
60 397 Transition between head and cylinder 50.9 Middle of head
65 349.9 Transition between head and cylinder 59.8 Middle of head
70 347.9 Middle of head 70.7 Middle of head
75 407.9 Middle of head 73.7 Middle of head
80 539.8 Middle of head 103.9 Middle of head

Figure 12 shows the maximum S11 and S22 variation with the increase of the spiral winding angle under different numbers of layers. For all of the number of winding layers, with the increase in the winding angle, the maximum S11 decreases first and then increases, but the turning point gradually changes from 60° to 70°. With the increase in the spiral winding angle, the maximum S22 stabilizes first and then increases. With the number of winding layers increasing, the turning point gradually changes from 70° to 55°.

Figure 12 The maximum S11 and S22 variation with the increase of the spiral winding angle: (a) 7-layer winding model, (b) 14-layer winding model, (c) 21-layer winding model, (d) 28-layer winding model, and (e) 35-layer winding model.
Figure 12

The maximum S11 and S22 variation with the increase of the spiral winding angle: (a) 7-layer winding model, (b) 14-layer winding model, (c) 21-layer winding model, (d) 28-layer winding model, and (e) 35-layer winding model.

3.4 Influence of different winding sequences

The stress analysis results of the three winding methods are summarized in Tables 7 and 8. Table 7 lists the maximum S11 and S22 of the spiral winding layers. It shows that, for the three winding sequences, the maximum S11 always appears at the transition between the head and the cylinder, and the maximum S22 always appears at the middle section of the head. Table 8 lists the maximum S11 and S22 of the circumferential winding layers. For the winding method of 21-layer circumferential winding + 14-layer spiral winding, the maximum S11 appears at the cylinder, while that of the other two winding methods appear at the end of the cylinder. The maximum S22 all appears at the cylinder. Comparing the stress results of the three winding sequences, the S11 and S22 of the method with 21-layer circumferential winding + 14-layer spiral winding are the smallest. It will be seen that performing circumferential winding inside and then spiral winding outside is the best winding sequence.

Table 7

Stress analysis results of spiral winding

Winding sequence Spiral winding layers
Maximum S11 (MPa) Position Maximum S22 (MPa) Position
14 + 21 753.9 Transition between head and cylinder 57.5 Middle section of head
21 + 14 713.8 Transition between head and cylinder 56.5 Middle section of head
7 + 21 + 7 717.1 Transition between head and cylinder 57.0 Middle section of head
Table 8

Stress analysis results of circumferential winding

Winding sequence Circumferential winding layers
Maximum S11 (MPa) Position Maximum S22 (MPa) Position
14 + 21 238.3 End of cylinder 40.5 Cylinder
21 + 14 85.8 Cylinder 36.8 Cylinder
7 + 21 + 7 115.8 End of cylinder 40.0 Cylinder

3.5 Discussion

According to the previous analysis, with the increase in the number of spiral winding layers, the maximum S11 and maximum S22 decrease quickly first. But when the number of winding layers reaches about 35, the stress decreases significantly slowly. Besides, with the increase in the number of circumferential winding layers, the maximum S11 and maximum S22 decrease quickly first. But when the number of winding layers reaches about 25, the stress decreases significantly slowly. It indicates that it is better if the number of spiral winding layers and the number of circumferential winding layers are not the more. When the number of winding layers exceeds a certain value, the bearing capacity of the storage vessel will not be improved significantly, but the manufacturing cost will increase.

According to the 75 groups of winding methods with different winding layers and different winding angles, it is found that with the increase of the winding angles, the maximum S11 decreases first and then increases, while the maximum S22 stabilizes first and then increases. For different numbers of winding layers, the turning point of stress rise is different. Considering the values of maximum S11 and maximum S22, the best winding angle is between 55° and 65°. The simulations of different composite material laying parameters provide a certain foundation for the production, manufacturing, and structural optimization of hydrogen storage vessel.

4 Conclusions

The influence of composite material laying parameters on the load-carrying capacity of Ⅳ-type hydrogen storage vessel was investigated, and the following conclusions can be obtained.

  1. The number of winding layers is not the more the better, there is an optimal number of winding layers. The best spiral winding angle is between 55° and 65°. Performing circumferential winding layers inside and spiral winding layers outside is the best winding sequence.

  2. With the increase of the number of the spiral and circumferential winding layers, both of the maximum stress along the fiber direction S11 and perpendicular to the fiber direction S22 decrease gradually. But, for spiral winding layers, the maximum S11 and S22 appears at the innermost layer, while the maximum S11 occurs at the outermost layer and the maximum S22 occurs at the innermost layer for the circumferential winding layers.

  3. When the number of spiral winding layers and the number of circumferential winding layers exceed 35 and 25, respectively, the bearing capacity of the storage vessel is not significantly improved.

  4. With the increase in the spiral winding angles, the maximum S11 decreases first and then increases, while the maximum S22 is stable first and then increases. But, for different numbers of winding layers, the turning point of stress rise is different.

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Acknowledgments

The study was supported by the National Natural Science Foundation of China (52205175), Taishan Scholar Foundation for Young People of Shandong Province (tsqnz20240827), the Natural Science Foundation of Shandong Province (ZR2021QE099), the Key R&D Program of Shandong Province (2021CXGC011302), and Science & Technology Support Project for Young People in Colleges of Shandong Province (2023KJ120).

  1. Funding information: The authors state no funding involved.

  2. Author contributions: All authors have accepted responsibility for the entire content of this manuscript and consented to its submission to the journal, reviewed all the results, and approved the final version of the manuscript. QZ: methodology, logical structure; WJ: software, validation; JY: data curation, writing-original draft preparation; JB: writing – reviewing and editing; HF: experiments, data analysis of the experiment; BW: investigation and analysis of the influence law.

  3. Conflict of interest: Authors J.B. and H.F. are employees of Shandong Auyan New Energy Technology Co., Ltd. The authors declare no other conflict of interest.

  4. Data availability statement: The datasets generated during and/or analyzed during the current study are available from the corresponding author on reasonable request.

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Received: 2024-06-28
Revised: 2024-09-09
Accepted: 2024-10-02
Published Online: 2024-12-02

© 2024 the author(s), published by De Gruyter

This work is licensed under the Creative Commons Attribution 4.0 International License.

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  15. Roles of corn starch and gellan gum in changing of unconfined compressive strength of Shanghai alluvial clay
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  17. Experimental investigation of the performances of thick CFRP, GFRP, and KFRP composite plates under ballistic impact
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  26. Research on uniaxial compression performance and constitutive relationship of RBP-UHPC after high temperature
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  42. Investigation on acoustic properties of metal hollow sphere A356 aluminum matrix composites
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  53. Thermo-mechanical coupling behavior of needle-punched carbon/carbon composites
  54. Influence of composite material laying parameters on the load-carrying capacity of type IV hydrogen storage vessel
  55. Review Articles
  56. Effect of carbon nanotubes on mechanical properties of aluminum matrix composites: A review
  57. On in-house developed feedstock filament of polymer and polymeric composites and their recycling process – A comprehensive review
  58. Research progress on freeze–thaw constitutive model of concrete based on damage mechanics
  59. A bibliometric and content analysis of research trends in paver blocks: Mapping the scientific landscape
  60. Bibliometric analysis of stone column research trends: A Web of Science perspective
https://doi.org/10.1515/secm-2024-0046
Keywords for this article
hydrogen storage pressure vessel; composite material laying parameters; Influence law; finite element analysis; carrying capacity
Creative Commons
BY 4.0

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  3. Structural optimization of trays in bolt support systems
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  6. The application of epoxy resin polymers by laser induction technologies
  7. Analysis of water absorption on the efficiency of bonded composite repair of aluminum alloy panels
  8. Experimental research on bonding mechanical performance of the interface between cementitious layers
  9. A study on the effect of microspheres on the freeze–thaw resistance of EPS concrete
  10. Influence of Ti2SnC content on arc erosion resistance in Ag–Ti2SnC composites
  11. Cement-based composites with ZIF-8@TiO2-coated activated carbon fiber for efficient removal of formaldehyde
  12. Microstructure and chloride transport of aeolian sand concrete under long-term natural immersion
  13. Simulation study on basic road performance and modification mechanism of red mud modified asphalt mixture
  14. Extraction and characterization of nano-silica particles to enhance mechanical properties of general-purpose unsaturated polyester resin
  15. Roles of corn starch and gellan gum in changing of unconfined compressive strength of Shanghai alluvial clay
  16. A review on innovative approaches to expansive soil stabilization: Focussing on EPS beads, sand, and jute
  17. Experimental investigation of the performances of thick CFRP, GFRP, and KFRP composite plates under ballistic impact
  18. Preparation and characterization of titanium gypsum artificial aggregate
  19. Characteristics of bulletproof plate made from silkworm cocoon waste: Hybrid silkworm cocoon waste-reinforced epoxy/UHMWPE composite
  20. Experimental research on influence of curing environment on mechanical properties of coal gangue cementation
  21. Multi-objective optimization of machining variables for wire-EDM of LM6/fly ash composite materials using grey relational analysis
  22. Synthesis and characterization of Ag@Ni co-axial nanocables and their fluorescent and catalytic properties
  23. Beneficial effect of 4% Ta addition on the corrosion mitigation of Ti–12% Zr alloy after different immersion times in 3.5% NaCl solutions
  24. Study on electrical conductive mechanism of mayenite derivative C12A7:C
  25. Fast prediction of concrete equivalent modulus based on the random aggregate model and image quadtree SBFEM
  26. Research on uniaxial compression performance and constitutive relationship of RBP-UHPC after high temperature
  27. Experimental analysis of frost resistance and failure models in engineered cementitious composites with the integration of Yellow River sand
  28. Influence of tin additions on the corrosion passivation of TiZrTa alloy in sodium chloride solutions
  29. Microstructure and finite element analysis of Mo2C-diamond/Cu composites by spark plasma sintering
  30. Low-velocity impact response optimization of the foam-cored sandwich panels with CFRP skins for electric aircraft fuselage skin application
  31. Research on the carbonation resistance and improvement technology of fully recycled aggregate concrete
  32. Study on the basic properties of iron tailings powder-desulfurization ash mine filling cementitious material
  33. Preparation and mechanical properties of the 2.5D carbon glass hybrid woven composite materials
  34. Improvement on interfacial properties of CuW and CuCr bimetallic materials with high-entropy alloy interlayers via infiltration method
  35. Investigation properties of ultra-high performance concrete incorporating pond ash
  36. Effects of binder paste-to-aggregate ratio and polypropylene fiber content on the performance of high-flowability steel fiber-reinforced concrete for slab/deck overlays
  37. Interfacial bonding characteristics of multi-walled carbon nanotube/ultralight foamed concrete
  38. Classification of damping properties of fabric-reinforced flat beam-like specimens by a degree of ondulation implying a mesomechanic kinematic
  39. Influence of mica paper surface modification on the water resistance of mica paper/organic silicone resin composites
  40. Impact of cooling methods on the corrosion behavior of AA6063 aluminum alloy in a chloride solution
  41. Wear mechanism analysis of internal chip removal drill for CFRP drilling
  42. Investigation on acoustic properties of metal hollow sphere A356 aluminum matrix composites
  43. Uniaxial compression stress–strain relationship of fully aeolian sand concrete at low temperatures
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  45. Intelligent sportswear design: Innovative applications based on conjugated nanomaterials
  46. Research on the equivalent stretching mechanical properties of Nomex honeycomb core considering the effect of resin coating
  47. Numerical analysis and experimental research on the vibration performance of concrete vibration table in PC components
  48. Assessment of mechanical and biological properties of Ti–31Nb–7.7Zr alloy for spinal surgery implant
  49. Theoretical research on load distribution of composite pre-tightened teeth connections embedded with soft layers
  50. Coupling design features of material surface treatment for ceramic products based on ResNet
  51. Optimizing superelastic shape-memory alloy fibers for enhancing the pullout performance in engineered cementitious composites
  52. Multi-scale finite element simulation of needle-punched quartz fiber reinforced composites
  53. Thermo-mechanical coupling behavior of needle-punched carbon/carbon composites
  54. Influence of composite material laying parameters on the load-carrying capacity of type IV hydrogen storage vessel
  55. Review Articles
  56. Effect of carbon nanotubes on mechanical properties of aluminum matrix composites: A review
  57. On in-house developed feedstock filament of polymer and polymeric composites and their recycling process – A comprehensive review
  58. Research progress on freeze–thaw constitutive model of concrete based on damage mechanics
  59. A bibliometric and content analysis of research trends in paver blocks: Mapping the scientific landscape
  60. Bibliometric analysis of stone column research trends: A Web of Science perspective
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