Influence of Cord Parameters on the Load Characteristics of Airbags

Abstract

To accurately characterize the large deformation and nonlinear characteristics of airbags, the influence of cord parameters on vertical force characteristics was studied, and a finite-element simulation model of airbags based on gas-solid coupling was established. First, uniaxial tension and compression experiments with airbag under different initial pressures were carried out to analyse the effects of the initial pressure and working height on the mechanical properties of the airbag. Second, the validity of the model was verified by the test data of the vertical force and cavity pressure of the airbag. Finally, based on the gas-solid coupling model proposed, the influence of the cord parameters on the vertical force characteristics was studied. The results show that the vertical force characteristics of an airbag are different between compression and tension and the nonlinear characteristic of the airbag becomes more obvious with the increase in the displacement in compression. After comparing the effects of cord parameters on the vertical force of the airbag, we can conclude that the number of cord layers has the most significant effect on the vertical force, followed by the cord diameter, while other cord parameters have a general effect. Under the same compression and tension displacements (d = ±80 mm), the effective area of 1 cord layer is 2.56 times as much as the effective area of 6 cord layers and the vertical force of the airbag with a cord diameter of 0.25 mm is 7.28 times greater than that of the corresponding vertical force with a cord diameter of 1.0 mm. The airbag with different cord angles shows differences in the working state of compression and tension, especially in compression. The force of the airbag at 90° cord angle gradually exceeds the force at other angles with an increase in displacement. The difference in the load at different working states of compression and tension is useful.

This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

1. Introduction

Air springs are composite materials composed of cord and rubber that have strong material nonlinearity, geometric nonlinearity, and contact nonlinearity in a typical airbag. Owing to its variable stiffness, low natural frequency, and as an excellent vibration isolator, air springs have been widely used in railway vehicles, luxury buses, intercity buses, and commercial vehicles [1–5]. In addition, air springs have been applied in ejection impact and other fields and show excellent performance [6].

A series of studies have been carried out to establish an analytical model of the nonlinear characteristics of air springs. For example, Zargar et al. [7] established a nonlinear theoretical model and verified the correctness of its mathematical model through experiments. Quaglia et al. [8] theoretically deduced the expression of the stiffness of the air spring of a capsule-type revolution body and analysed the variation in the effective area in detail using the graphical method [9]. de Melo and Chang and other scholars have carried out a series of studies on the dynamic characteristics of air springs based on vehicle suspension by means of numerical analysis, model simplification, and mechanical model establishment [10, 11]. Fachinetti et al. [4] compared two modelling methods of two-stage air spring suspension and evaluated its influence on the accuracy of multibody simulation of rail vehicle dynamics. Zhang et al. [12] proposed an air spring model with a variable orifice in an auxiliary chamber and optimized the parameters of the air spring with an auxiliary chamber, which improved the basic performance of semiactive control. Zhu et al. [13, 14] studied the nonlinear dynamic response of an air spring mechanical model under large-amplitude excitation and different precompression and pretension conditions and verified that the proposed model can predict the dynamic characteristics of an air spring through a bench test.

Some scholars apply thermodynamic theory to the air spring model to improve the calculation accuracy of the model. For example, Lee [15] established a mathematical model based on thermodynamics and believed that the stiffness of the air spring was affected by volume, heat transfer, and effective area. Okorn and Nagode [16] applied thermodynamics, heat transfer, and hydrodynamics to the model and developed a more accurate air spring suspension system model by combining these effects. Investigating the influence of an additional air chamber on the performance of an air spring, Li et al. [17] found that the shape and material characteristics of the air spring, the volume of the additional air chamber, and the diameter of the orifice are the main factors affecting the performance of the air spring. Chen et al. [18] took the air spring with orifice and additional air chamber as the research objects, established the nonlinear model, and studied the influence of the mechanical characteristics of the rubber on the dynamic characteristics of the whole air spring. Tang et al. [19] studied the influence of a single-chamber cross-section on the stiffness characteristics of membrane air spring and obtained that under the condition of determining the basic structure size, the variation of piston cone angle and piston height are the main factors affecting the single-cavity variable-section air spring.

The current research on the parameters of airbag cords focuses mainly on the modification of the tensile formula of cord rubber material parameters and the theoretical derivation of numerical models and simplified models [20–22]. Hao and Jaecheon [23] carried out a series of static and dynamic tests to measure the dynamic and static stiffness of an air spring. The research focuses mainly on the simplified model verification and dynamic characteristics of pneumatic suspension air springs. However, research on the vertical load characteristics of airbags due to changes in cord parameters is still insufficient. This paper takes the airbag as the research object, and it is effectively compounded by cord reinforcement phase and rubber matrix. The pressure load of the internal chamber is mainly carried by the cord of airbag, which has complex anisotropy and nonlinear characteristics. In this paper, the thermodynamic theory is introduced, and a simulation model of the airbag based on gas-solid coupling is established. The correctness of the model is verified based on the uniaxial tensile and compression experiment of the airbag, and on this basis, a detailed analysis is performed. The influence of cord parameters on the vertical load characteristics of the airbag is further discussed. The load characteristics of the airbag are composed mainly of vertical force, cavity pressure, cavity volume, and effective area.

2. Airbag Model

2.1. Fluid Cavity Model

The load characteristics of airbags depend not only on the geometric nonlinearity, material nonlinearity, and contact nonlinearity but also on the variation in cavity pressure. Each cavity has a unique reference point and a single degree of freedom to refer to the change in cavity pressure. The fluid element can be used to simulate various gas-filled cavities under pneumatic conditions. According to the augmented virtual work principle, the ideal gas equation is used to determine the closed gas boundary conditions, and the virtual work equation of the structure is obtained through the gas boundary conditions [14, 16, 24, 25].

Fluid volume is a function of fluid pressure, temperature, and mass. The volume of the fluid cavity $\overline{V}$ is obtained by the fluid pressure $p$ and gas temperature $\theta$, which is equal to the actual volume $V$. As the pressures of all elements in the chamber are the same, the augmented virtual work expression can be written as the sum of the expressions for individual elements. The augmented virtual work expression of the structure is realized by the following constraint equation [6, 26]:$$\begin{array}{}\text{(1)}& \delta {\Pi }^{\ast }={\displaystyle \sum }_e\delta {\Pi }^e-p\delta V^e-\delta p{V}^e-{\overline{V}}^e,\end{array}$$where $\delta {\mathrm{\Pi }}^{\ast }$ is the augmented virtual work expression and $\delta \mathrm{\Pi }$ is the virtual work expression for the structure without fluid. As the temperature is the same for all elements in the cavity, the fluid volume can be calculated for each element as$$\begin{array}{}\text{(2)}& {\overline{V}}^e=\overline{V}p,\theta ,m^e,\end{array}$$where $m^e$ is the element mass and $V$ can be obtained by equation (2).$$\begin{array}{}\text{(3)}& V=\sqrt[e]{\overline{V}P,\theta ,m^e}.\end{array}$$

As the mass of the gas flowing into the cavity of airbag is equal to the total mass of all the fluid elements, the fluid density can be obtained as$$\begin{array}{}\text{(4)}& pP,\theta =p_R\frac{{\theta }_R-{\theta }_{A}P+P_A}{\theta -{\theta }_A{P}_R+P_A},\end{array}$$where $T_R$ is the temperature at the reference point $P_R$, and the unit of temperature is K. $P_R$ is the pressure at the reference point $P_R$, and the unit of pressure is Pa. ${\theta }_A$ is the ambient temperature, and $P_A$ is the ambient pressure.

As all elements in the chamber have the same temperature, the fluid volume for each element is as follows:$$\begin{array}{}\text{(5)}& {\overline{V}}^e=\overline{V}p,\theta ,m^e.\end{array}$$

The volume of fluid can be expressed as$$\begin{array}{}\text{(6)}& V={\displaystyle \sum _e{\overline{V}}^e}={\displaystyle \sum _e\overline{V}p,\theta ,m^e}=\frac{m}{\rho P,\theta }.\end{array}$$

The volume of the fluid of the flexible per pressure is$$\begin{array}{}\text{(7)}& \frac{\text{d}V}{\text{d}p}=-\frac{m\text{d}\rho }{{\rho }^2\text{d}p}=-\frac{m}{{\rho }_R}\frac{{\theta }_R-{\theta }_{A}P+P_A}{\theta -{\theta }_A{P_R+P_A}^2}.\end{array}$$

2.2. Mechanical Model of Airbags

The ideal model of the airbag is shown in Figure 1, with the fix wall fixed and the axial force $F_e$ acting on the move wall, and the contact area between the move wall and the airbag is $A_e$. Under the different pressure states on the move wall, the effective contact area between the airbag and the move wall is dynamic. $P$ and $P_a$ are the absolute pressure and atmospheric pressure of the chamber, respectively; $T$ is the temperature of the chamber; $F_e$ is the axial force along the Y direction; and $V$ is the volume of the chamber.

[figure omitted; refer to PDF]

The airbag allows deflection and force transmission in three directions [27]. The stiffness of the airbag was obtained based on the original ejection model, and the nonlinear stiffness of the airbag can be derived as the following equation [6]:$$\begin{array}{}\text{(8)}& K_e=\frac{\text{d}F}{\text{d}x}=-\frac{nP{A}_e}{V}\frac{\text{d}V}{\text{d}x}+P-P_a\frac{\text{d}{A}_e}{\text{d}x}.\end{array}$$

The temperature change in the airbag chamber is uniform, and the energy in and out of the system can be described by the first law of thermodynamics:$$\begin{array}{}\text{(9)}& W=\Delta E+Q.\end{array}$$where $W$ is the work done by the outside on the fluid in the cavity of the airbag, $\mathrm{\Delta }E$ is the increased internal energy of the fluid in the cavity, and $Q$ is the heat transferred from the gas in the chamber to the flexible airbag material.

The work done on the fluid can be described as$$\begin{array}{}\text{(10)}& W=Fx-\Delta E{}^{\prime }.\end{array}$$where $F$ is the external load exerted on the airbag by the outside, $x$ is the deformation of the airbag, and $\mathrm{\Delta }E$ is the internal energy stored in the deformation of the airbag.

By combining equations (9) and (10), the increment of internal energy in the airbag chamber can be obtained as follows:$$\begin{array}{}\text{(11)}& \Delta E=Fx-\Delta E{}^{\prime }-Q.\end{array}$$

Assuming that the fluid is an ideal gas, the relationship between temperature and energy increment is as follows:$$\begin{array}{}\text{(12)}& \Delta E=m{C}_v\Delta T,\end{array}$$where $\mathrm{\Delta }T$ is the temperature change in the chamber and $C_v$ is the constant volume-specific heat of the fluid.

From equations (11) and (12), it can be concluded that$$\begin{array}{}\text{(13)}& \Delta T=\frac{Fx-\Delta E{}^{\prime }-Q}{m{C}_v}.\end{array}$$

$Q$ is expressed as$$\begin{array}{}\text{(14)}& Q=\beta T-T{}^{\prime }.\end{array}$$where $\beta$ is the heat transfer coefficient between the gas in the chamber and the flexible air bag, $T$ is the fluid temperature, $T{}^{\prime }$ is the material temperature of the airbag, and t is the time of heat transfer.

3. Experimental Test of the Airbag

3.1. Working State Description

To study the influence of different initial pressures and working heights on the load characteristics of airbag, a uniaxial tension-compression test of airbag was carried out based on a measure testing simulation (MTS), as shown in Figure 2.

[figure omitted; refer to PDF]

The initial working height (H) of the airbag is 300 mm, and the initial working height is defined as d = 0 mm. The actuator of the MTS testing machine compresses the airbag upward (the upward displacement is positive) and stretches the airbag downward (the downward displacement is negative). The maximum compression and tension displacements are +80 and −140 mm, respectively. The experimental equipment used was an MTS 809.25 testing machine, the axial load range was ±250 kN, and the accuracy of the force sensor and displacement sensor was 0.5. The measurement of pressure is realized through the installation of an intelligent pressure transmitter. The pressure measurement range is −0.1 ∼ + 60 MPa.

3.2. Experimental Methods

The working principle of the airbag compression and tensile experiment is shown in Figure 3. The experiment test system consists of an air compressor, MTS testing machine, airbag, intelligent pressure transmitter, three-way valve, intake pipe, load-displacement sensor, and air compressor. First, the airbag was fixed on the MTS testing machine by fixture, then the working height of the airbag was adjusted to 300 mm by the MTS testing machine control system. The actuator was locked at this position, and the gas was injected into the cavity of the airbag through an air compressor and air inlet pipe, and the air inlet valve was closed when the pressure reached 0.204 MPa to keep the cavity pressure stable. Finally, the compression and tensile displacement functions of the airbag were set by the MTS testing machine control system, and the speed of the actuator was 70 mm/min.

[figure omitted; refer to PDF]

The cord rebar model of the airbag is shown in Figure 7 including the cord layer, cord angle, cord spacing, cord diameter, and cord centre distance. The thickness of the airbag is 6 mm, which is vulcanized by inner rubber, outer rubber, and cord, as shown in Figure 6. The cord is generally distributed symmetrically in two layers. The first cord layer is arranged in a 50° arrangement, and the second cord layer is arranged in a 50° arrangement. The cord diameter is 0.2 mm, and the cord centre distance and cord spacing are both 1 mm.

[figure omitted; refer to PDF]

The cord layer of the airbag can be represented as a rebar element in the cord rebar model without increasing the degree of freedom, which is effective in dealing with geometric nonlinearity and physical nonlinearity [29, 30]. In the cord rebar model, the internal potential energy of cord rebar is the sum of the internal potential energy of rubber and cord.$$\begin{array}{}\text{(15)}& \tilde{U}={\tilde{U}}_1+{\tilde{U}}_2,\end{array}$$where $\tilde{U}$ is the total internal potential energy. ${\tilde{U}}_1$ is the based internal potential energy. ${\tilde{U}}_2$ is the internal potential energy of the cord rebar.

By introducing the solid part associated with the cord to modify, and distinguishing the different functions of single cord and cord layer, the $\tilde{U}$ can be expressed as$$\begin{array}{}\text{(16)}& \tilde{U}={\displaystyle \int V_e{W}_b\widehat{E}+\tilde{E}-S_b:\tilde{E}}\text{d}V-{\displaystyle \int V_s{W}_b\widehat{E}+\tilde{E}-S_b:\tilde{E}\text{d}V}-{\displaystyle \int V_r{W}_b\widehat{E}+\tilde{E}-S_b:\tilde{E}}\text{d}V+{\displaystyle \int {\displaystyle \int V_s{W}_b\widehat{E}+\tilde{E}-S_s:\tilde{E}}}V+{\displaystyle \int V_r{W}_b\widehat{E}+\tilde{E}-S_r:\tilde{E}}\text{d}V,\end{array}$$where $V_e$ is the strain energy density of matrix material, J/m³; $\widehat{E}$ is Green Lagrange strain tensor; $\tilde{E}$ is the enhanced strain tensor; $S_b$ is the fundamental stress tensor; $W_s$ is strain energy density of single cord, J/m³; $W_r$ is the strain energy density of cord layer, J/m³; $S_r$ is the stress tensor of cord layer, Pa; $S_s$ is the single-cord stress tensor, Pa; $V_e$ is the element volume, m³; $V_s$ is the volume of single cord, m³; and $V_r$ is the volume of cord layer, m³.

4.2. Finite-Element Simulation Model

The S4R element is used to establish the airbag simulation model with an element size of 4 mm. The number of elements is 36,034, and the number of nodes is 36,037, including the reference points of the cavity. The thickness of airbag is shown in Figure 7. The airbag was inflated with gas until the total (absolute) pressure reached 0.204 MPa. When the specified pressure was reached, the gas flowing into the airbag chamber was stopped, and the airbag was compressed upward by 80 mm. The finite-element simulation model and constraint load of the airbag are shown in Figure 8. The finite-element simulation model is a three-dimensional solid model and the geometric structure of the airbag is axisymmetric. So, the reference point of fluid cavity coincides with the center of symmetry of airbag. The end of the airbag is fully constrained, and the displacement load along the Y-direction is set at the other end.

[figure omitted; refer to PDF]

4.3. Model Validation

Based on the gas-solid coupling airbag simulation model, the changes in the vertical force and cavity pressure with the working height under different initial pressures (0.204, 0.408, and 0.605 MPa) were calculated. Different from the explicit algorithm used in the dynamic ejection model, the implicit algorithm is used in the quasi-static calculation of airbag. The simulation results (Sim) compared with the experimental data (Exp) are shown in Figure 9.

[figures omitted; refer to PDF]

The comparison results in Figure 9 show that the variation of cavity pressure obtained by simulation calculation is close to the experimental value, and the variation trend is the same. Since the force is related to not only the cavity pressure but also the effective contact area of the airbag, there is a certain error in the simulation calculation of the load, but within the acceptable range. With increasing compression displacement, the vertical force and cavity pressure also change nonlinearly. The simulation results are close to the experimental results, and the experimental results verify the correctness of the finite-element simulation model.

Based on the simulation model verification, the influence of cord parameters on the vertical force, cavity pressure, cavity volume, and effective area of the airbag were investigated. The following research on cord parameters is based on an initial pressure of 0.204 MPa and a displacement of 80 mm in compression and tensile testing.

5. Results and Discussion

5.1. Influence of Different Cord Layers on the Characteristics of Airbags

The cord layer of the airbag is usually arranged in two layers. Based on the established finite-element simulation model of a gas-solid coupling airbag, the distribution of different cord layers was investigated. The influence of cord layers on the vertical force, cavity pressure, cavity volume, and effective area is obtained, as shown in Figure 10.

[figures omitted; refer to PDF]

As Figure 10(a) shows, the vertical force of the airbag increases with the increase in the number of cord layers in both the compression and tensile states and is significantly increased, which indicates that the vertical force can be significantly improved by increasing the number of cord layers. For the airbag with 1 and 2 cord layers, the force difference is small when the airbag is compressed, while the force difference is obvious in tensile testing, indicating that the force characteristics are not completely consistent when the cord has only one or two layers, and there are differences.

Figure 10(b) shows that the cavity pressure increases with increasing compression displacement. The effect of cord layers on cavity pressure becomes obvious with increasing displacement when the airbag is in compression. When stretching, the airbag was stretched by the actuator, the effect of cord layers on cavity pressure is very small, and the cavity pressure of different cord layers remains the same. With increasing tensile displacement, the cavity pressure gradually decreases. For the pressure change trend, when the tensile displacement reaches a certain value, the final cavity pressure will tend to a constant value. This shows that the initial tensile displacement has a significant effect on the cavity pressure, but when the tensile displacement is large, the pressure will not change.

For the change in cavity volume in Figure 10(c), the volume decreases with increasing compression displacement and increases with increasing tensile displacement. At the same working height, with the increase in the number of cord layers, the cavity volume of the airbag will decrease, while the extent of reduction will decrease with the increase in the number of cord layers. After reaching a certain number of cord layers, the cavity volume will remain the same, and the change in the number of cord layers will have no influence on the volume.

The change trend in the effective area in Figure 10(d) is consistent with the change trend in the force. The effective area increases with the increase in the number of cord layers, regardless of compression or tensile. At the same compression and tensile displacement (d = +80 mm and d = −80 mm), the effective area difference of the 1 cord layer and 6 cord layers is 35,143 and 13,705 mm², respectively. The difference of 2.56 times indicates that the number of cord layers has a significant effect on the effective area, which shows that the effect of the cord layer number on the effective area when the airbag is in the tensile is much greater than the compression.

5.2. Influence of Cord Layer Spacing on the Characteristics of the Airbag

The cord layer spacings of the airbag are 1.5, 2.0, 2.5, and 3.0 mm. When the initial pressure is 0.204 MPa and the compression and tensile displacement are both 80 mm, the influence of cord layer spacing on the vertical force, cavity pressure, cavity volume, and effective contact area was studied. The calculation result based on the finite-element simulation model of a gas-solid coupling airbag is shown in Figure 11.

[figures omitted; refer to PDF]

Figure 11(a) shows that the vertical force decreases with increasing cord spacing. Especially when the airbag was stretched by the actuator, the difference in the vertical force was more obvious. The difference in vertical force is very small when the airbag is in the compression, indicating that the cord spacing has a significant effect on the vertical force when airbag is in the tension.

As shown in Figure 11(b), the cavity pressure of the airbag is almost the same at the different cord spacings, regardless of whether the airbag is in the compression or tensile, showing that the cord spacing has little effect on the cavity pressure.

For the change in cavity volume under different cord spacings in Figure 11(c), the cavity volume increases with increasing cord spacing at the same working height, but the increase is small. The cavity volume does not change because the airbag is in the compression and tension states.

Figure 11(d) shows that the change trend of the effective area of the airbag is consistent with the change in the load, and the effective area is different when the airbag is compressed and stretched. The effective area decreases with increasing cord spacing in the tensile state, showing that the vertical force difference with different cord spacings is caused mainly by the change in effective area.

5.3. Influence of Cord Diameter on the Characteristics of Airbags

The influence of cord diameter on the vertical force characteristics of airbag was investigated by changing the cord diameter (0.25, 0.5, 0.75, and 1.0 mm). The result is shown in Figure 12.

[figures omitted; refer to PDF]

As shown in Figure 12(a), the vertical force of the airbag increases with increasing cord diameter regardless of compression or tensile testing. Especially when it is tensile, the cord diameter has a more obvious effect on the vertical force of the airbag. When the tensile displacement is −80 mm, the vertical force difference of the airbag corresponding to cord diameters of 0.25 mm and 1.0 mm is 3029 N, which is 7.28 times the vertical force difference when the compression displacement is 80 mm, showing that the cord diameter is more sensitive to the vertical force of the airbag in the tensile test.

Figure 12(b) shows that the cavity pressure of airbag with different cord diameters increases with increasing displacement under compression. However, the cavity pressure decreases with increasing displacement when it is tensile. In compression, the cavity pressure increases with increasing cord diameter. In the tensile test, the cord diameter has little effect on the cavity pressure. When the cord diameter is greater than 0.25 mm, the load values of different cord diameters are similar, and there is no increase with increasing cord diameter.

Figure 12(c) shows that under different cord diameters, the volume of the airbag chamber decreases with increasing compression displacement. Under the same displacement, the volume of the airbag chamber decreases with increasing cord diameter, but the reduction amplitude decreases. When the cord diameter reaches 0.75 mm or above, the volumes of the airbag chamber are close to each other.

Figure 13(d) shows the variation in the effective area of the airbag with different values. When it is pulled down, the effective area of the airbag increases with increasing cord diameter. The difference in effective area between the 0.25 mm cord diameter and 1.0 mm cord diameter is 17,223 and 2589 mm, respectively. The effective area is 6.65 times different. Especially from tensile to compression, the effective area of the airbag changes through two different phases. In Phase 1, with increasing compression displacement, the effective area difference of airbag with different cord diameters increases. However, in Phase 2, when the compression displacement is greater than 33.3 mm, the effective area difference of airbag with different cord diameters decreases significantly.

5.4. Influence of Cord Angle on the Characteristics of Airbags

The cord angles were 10°, 20°, 30°, 40°, 50°, 60°, 70°, 80°, and 90°. The effects of the vertical force, cavity pressure, cavity volume, and effective area of the airbag were studied by changing the cord angle. The results are shown in Figure 13.

[figures omitted; refer to PDF]

Figure 13(a) shows that the vertical force of the airbag has obvious differences in compression and tensile strength. In the tensile test, the vertical force has the maximum tensile load when the cord angle is 20°. When the cord angle is 90° and the compression displacement is 80 mm, the vertical force reaches its maximum, which indicates that the cord angle has a significant difference at different working heights. However, the change of cord angle has little influence on the dynamic ejection velocity of the airbag [6]. Different from dynamic ejection, the airbag under static load shows obvious differences, which is of great significance to the application of airbags under different states.

Figure 13(b) shows that different cord angles have a certain influence on the cavity pressure of the airbag, especially when the cord angle is 20°. The cavity pressure is the lowest, and when the cord angle is 90°, the cavity pressure is the highest. When d < 0, the effect of the cord angle on the cavity pressure becomes increasingly obvious with increasing tensile displacement.

As shown in Figure 13(c), the cavity volume decreases with increasing compression displacement, and the cavity volume of the airbag has different variation rules under different cord angles. When the tensile displacement is more than 30 mm, the cavity volume of the airbag at the cord angle of 30° and below obviously begins to change. Finally, with the increase in the displacement, the cavity volume is larger than the cavity volume at other angles, which is also the main reason for the decrease in the cavity pressure of the airbag at cord angles of 30° and below.

Figure 13(d) shows that the effective area of the airbag has certain differences under different compression and tensile stresses. When the airbag is tensile, the effective area is the largest when the cord angle is 20°. However, in compression, with increasing compression displacement, the effective area of the airbag with cord angles of 90°, 80°, and 70° gradually exceeds the effective area at other angles.

5.5. Influence of Centre Distance on the Characteristics of Airbags

The centre distances of the cord are 1.0, 1.5, 2.0, and 2.5 mm. By changing the centre distance, the change rules of the force, cavity pressure, cavity volume, and effective area of the airbag were studied, and the results are shown in Figure 14.

[figures omitted; refer to PDF]

Figures 14(a) and 14(d) shows that the vertical force and effective area of the airbag increase with increasing centre distance when it is in compression, but there is no obvious difference in the change in the vertical force and effective area for the tensile airbag. Figures 14(b) and 14(c) show that different cord centre distances have almost no effect on the cavity pressure and cavity volume, which increase with increasing compression displacement and decrease with increasing tensile displacement, with almost the same change value.

6. Conclusion

Based on the MTS testing machine, a uniaxial tensile-compression experimental test of the airbag was performed. The vertical force nonlinearity of the airbag became more obvious with increasing displacement when the airbag was in compression. The vertical force of the airbag at different initial pressures tended to be gradually consistent when in tensile testing. Finally, the airbag changed from the state of compression to the tensile state with increasing tensile displacement, and the airbag with the lowest initial pressure first reached the tensile state. In the tensile state, different initial pressures tended to a constant value and no longer changed with increasing tensile displacement.

Based on the finite-element model proposed, the effect of cord parameters on airbag was studied. The comparison results showed that the number of cord layers and cord diameter have obvious influences on the load characteristics of airbag, while the cord angle, cord spacing, and cord centre distance have less influence, among which the cord layer has the most significant influence. In addition, the more cord layers there are, the greater the vertical force, due mainly to the increase in the cord layers leading to the effective area of the airbag.

The results show that the cord layer spacing has a significant effect on the vertical force of the airbag in the tensile state, but the cord layer spacing has little effect on the compression. Therefore, the vertical force of the airbag can be improved by increasing the cord layer spacing. The vertical forces of the airbag at different cord angles are different, which shows differences in the tensile state and the state of compression. The cord centre distance has a significant effect on the vertical force in the state of compression, but it has little effect in the tensile state.

Acknowledgments

This research was supported by the National Natural Science Foundation Project (grant no. 52175123), Sichuan Science and Technology Foundation Project (grant nos. 2020JDRC0080 and 2019YJ0216), and Science and Technology Research and Development Program of China Railway Group Co. Ltd. (grant no. P2020J024).

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