Investigation on the performance of the expansion water seal by using isogeometric analysis with variational inequalities for the frictional contact

Abstract: In this study, IGA is introduced into the performance analysis of the expansion water seal for an exact representation of its complex geometrical shape. Firstly, the incremental equilibrium equations used in the large deformation analysis are derived for the IGA discretization model based on the updated Lagrangian formulation. The contact forces are treated as a special kind of traction, which results in a simple expression of the equilibrium equations. Then, through the investigation of the contact conditions, the contact force is verified to be solution of two box-constrained variational inequalities with respect to the normal and tangential contact conditions, respectively. Furthermore, the incremental equilibrium equations for all components of the water seal system and the variational inequalities for all contacts between the components are assembled together and reformulated as a global variational inequality, which is resolved by using the Extra-gradient method. Ultimately, the new method is applied in the performance comparison of two optional expansion water seals, in which the capability and precision of the proposed method are investigated. Results verify that the proposed method is effective in the numerical simulation of the expansion water seal and has a higher precision than the traditional FEM under the same conditions.

Key words: expansion water seal; performance analysis; isogeometric analysis; frictional contact; variational inequality

1 Introduction

Developing clean energy plays an important role in pollution reduction and has been placed at the core of the environmental protection policy in a lot of countries. As a traditional clean energy, hydropower development has a long history, especially in China. The hydraulic steel gate is a key component in the hydropower station. Because the performance of the water seal directly determines the sealing effectiveness of the gate, reasonable and accurate evaluations of the performance of the water seal are essential in the hydraulic steel gate design. In the last two decades, a series of large hydropower stations, such as Wudongde, Baihetan, Xiluodu, and Xiajiaba projects, have been constructed in the downstream of the Jinsha River in China, which are typically featured with high pressure and large capacity. In this situation, the expansion water seal is verified to be more applicable than the conventional pre-compression water seal[1], thus it is extensively used in the gate now. As a consequence, the performance analysis of expansion water seal gained more attention in recent years.

Both model tests and numerical simulations were employed in the researches on the expansion water seal. To pursue a high reliability in terms of working performance of the expansion water seal, model tests were conducted for the hydraulic steel gate design in some large hydropower stations, e.g., Pubugou, Longtan and Laxiwa[2]. Although model tests have resolved the performance evaluation for these stations successfully, they are costly and time-consuming. Moreover, the results of a special model test may be wrong when the conditions change. Therefore, numerical simulations become more popular in performance analysis of expansion water seal recently.

Reasonability and reliability of numerical simulation come from the thorough knowledge on the mechanical properties of water seal material and the fundamental theories of numerical methods adopted. Expansion water seal is made of rubber, a typical hyperelastic material, which is marked by large deformation and incompressibility. An accurate constitutive model denoting the relation between the strain and stress in the expansion water seal is important to promise the precision of numerical results, which attracted many scholars’ devotion. Based on the test results of rubber material in laboratory, Mooney-Rivlin model[3] and Ogden model[4] were suggested for nonlinear analysis on expansion water seal, and the applicability of the two models were further investigated by Tan[5]. Considering that Mooney-Rivlin model is reliable to describe the stress-strain relation of rubber material, if the strain is no more than 1.50[6], it gains more popularity than Ogden model in previous researches[7, 8] due to its simple expression. When Mooney-Rivlin model is employed, increasing the number of parameters in the model will enhance the precision of stress-strain relation adopted, but damage the computational efficiency. The optimal number of parameters in model is investigated by Hu [9] to reach a balance between the precision and the computational efficiency, and Mooney-Rivlin model with three parameters is recommended ultimately. Generally speaking, scholars have profound acquaintance with the mechanical properties of water seal materials after abundant explorations.

Up to now, the finite element method (FEM) is commonly used in the existing numerical simulation of water seal, for the commercial FEM software is matured in simulating the material nonlinearity caused by the constitutive model of rubber material, the geometric nonlinearity caused by large deformation, and the nonlinear boundary conditions due to the contact between water seal and the steel plates[10]. However, the structure complexity of the expansion water seal leads the modeling to be complicated and time-consuming when using traditional FEM. More importantly, the geometry difference between FEM model and the actual water seal undoubtedly affects the accuracy of the results, albeit it is subtle. Therefore, a numerical method with more reliability and high efficiency is expected to replace the traditional FEM for a better analysis on the performance of water seal.

Isogeometric analysis (IGA), a novel numerical method proposed by Hughes et al.[11], originally aimed to bridge the gap between computer aided design (CAD) and finite element analysis (FEA). Because the nonuniform rational B-splines, which are widely used in most CAD tools, are adopted as basis functions, IGA is capable of representing the exact geometry of engineering structures. Moreover, the conventional FEM uses Lagrange polynomials feature C⁰ continuity at nodes regardless of their order, while IGA with spline functions of order p has the ability to provide C^p−1 continuity at all non-multiple knots. This means that IGA shows better robustness and accuracy compared to the conventional FEM for the same amount of degrees of freedom[12]. Owing to these significant advantages, IGA served as a hot topic in engineering analysis since its birth and were adopted in the resolution of diverse problems in structural mechanics, solid mechanics, and fluid mechanics. Developments of IGA theory and the related computer implementation until 2015 were reviewed by Nguyen et al.[13]. Meanwhile, numerous enhancements have been made to improve the ability of IGA to optimize the engineering structure, the progresses of which were reviewed by Wang et al.[14] in 2018 and Gao et al.[15] in 2020. IGA could play an important role in the performance analysis of water seal. On the one hand, the complex shape of the water seal can be represented exactly in IGA. On the other hand, the capacity of IGA to treat the incompressibility in case of large deformation had been fully developed[16]. Thus, IGA is employed in this article to investigate the performance of expansion water seal in diverse conditions.

However, as mentioned above, the contact between the water seal and the steel plates should be taken into account carefully when simulating the mechanical behavior of the water seal. A number of approaches, such as the interior method[17] and surface potentials method[18], had been proposed to model contact in IGA. These methods fall into two categories. The first type of method utilizes the classical penalty method to impose the contact conditions. In this case, the value of the penalty parameter is vital in the analyses but hard to be determined. While, the second type of method always adds the contact potential to the total potential analysis based on some assumptions, e.g., surface potentials and the third medium[19], in which the rationality of those assumptions should be further investigated. To avoid the demerit of the existing approaches, variational inequality (VI) theory[20] is introduced to formulate the contact conditions as variational inequalities, and the extra-gradient method[21] is used to solve the equations derived in the study. Considering that VI theory has been successfully used in the resolution of contact for a system of discrete bodies[22], the new approach is theoretical feasible to improve the ability of IGA in contact simulation.

The remainder of this study is organized as follows. Section 2 briefly explains how the expansion water seal works and presents the constitutive model of the expansion water seal. In Section 3, the basic theory of IGA is provided, and formulations for larger deformation problem are illustrated. In Section 4, VI theory is briefly given firstly, and then, the conditions regarding to the contacts between the expansion water seal and the steel plates are investigated, inducing two variational inequalities equivalent to the normal and tangential contact conditions, respectively. Section 5 presents how the proposed approach to be implemented. In Section 6, an engineering example is simulated by using the proposed method, including a comprehensive analysis on all focused properties and a comparative analysis for two optional shapes of the water seal head. Section 7 concludes the paper.

2 A brief description of the expansion water seal and its constitutive model

2.1 Introduction of the expansion water seal

In the case that the expansion water seal is employed, a typical composition of the water seal system in the hydraulic steel gate is illustrated in Fig.1. It is noticed that the gaps between the components are enlarged in Fig.1 for a clear demonstration. Water stop panel, pressing plates and bed plate are made of steel, while the water seal is usually made of rubber. Through regulating the magnitude of back pressure, the deformation of the expansion water seal and the contact between the water seal and water stop panel are adjusted to seal up the reservoir water. When the hydraulic steel gate is to be closed, the back pressure is exerted on the expansion water seal by using a specialized water or air pressure installation, and then the expansion water seal deforms and moves upward. Back pressure will increase until the water seal contacts the water stop panel with the expected length and stress, which stuffs up the gap between the water stop panel and the pressing plate. Finally, the reservoir water is sealed up. Conversely, if the hydraulic steel gate is to be open, the back pressure is discharged gradually and the expansion water seal backtracks. The gap emerges and the reservoir water flows in the gap freely, which means that the force offered by the hoisting device to open the gate can be small.

Figure 1, A schematic diagram for the expansion water seal and the related apparatus

The performance of the expansion water seal is always evaluated from the following aspects. At First, the back cavity formed by the expansion water seal and the bed plate is one critical section, the leakproofness of which directly impacts the operation of imposing a prescribed back pressure. Once the water seal system has been assembled, the stress magnitudes with regard to the contacts between the two water seal wings and the pressing plates and the bed plate are the key variables to estimate whether the leakproofness of the back cavity is satisfactory. Next, the stress magnitudes regarding to the contact between the water seal head and the water stop panel are the variables of the greatest importance to assess the effectiveness of the water seal to seal up the reservoir water, which varies with the width of the gap, the back pressure as well as the reservoir water pressure. Finally, the offset of the water seal head appears due to the singularity of the reservoir water flowing, which is always investigated for a better understanding on the wear of the water seal head. In summary, an expansion water seal should meet the specified requirements in case of prescribed back pressure and reservoir water pressure.

The expansion water seal has a much greater magnitude in the axis direction than on the cross section. Meanwhile, it suffers external loads having their directions parallel to its cross section and remaining unchanged in the axis direction. These mechanical features induce that the expansion water seal can be treated as a plane stress problem in numerical simulation.

2.2 The constitutive model for the expansion water seal

To simulate the performance of the expansion water seal reasonably, the constitutive model for the components of the water seal system should be determined in advance, in which the model for the water seal is a key point. Because the material of expansion water seal is rubber, Mooney-Rivlin model[23] gained more popularity in existing researches, which is retained in this study. Based on the assumption of phenomenological theory of continuum mechanics, the mechanical behavior of rubber is denoted by the strain energy per unit volume, due to its hyperelasticity and isotropy. And then, the derivations of the strain energy in terms of the strain components are the corresponding stress components. Here some fundamental formulations and notations are introduced briefly.

The strain energy W is always evaluated through Green strain invariants, I₁, I₂ and I₃. Green strain invariants are defined as.

$I_{1}={\lambda }_{1}^{2}+{\lambda }_{2}^{2}+{\lambda }_{3}^{2};{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}I_{2}=$${\lambda }_{1}^{2}{\lambda }_{2}^{2}+{\lambda }_{2}^{2}{\lambda }_{3}^{2}+$${\lambda }_{3}^{2}{\lambda }_{1}^{2};{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}I_{3}=$${\lambda }_{1}^{2}{\lambda }_{2}^{2}{\lambda }_{3}^{2}$

(1)

In Eq. (1), λ₁, λ₂ and λ₃ denote the elongation of a volume element along the three principle axes, respectively. It is noticed that I₃ identically equals to one for the incompressible material. Therefore, W is only calculated by using I₁ and I₂, that is

$W=W(I_{1},I_{2})$

(2)

Then, based on the definitions in Eq. (1), Eq. (2) can be reformulated as the following polynomial by using the power series expansion method.

$W=\sum _{i,j=0}^{n}C_{ij}{\left(I_{1}-3\right)}^{i}{\left(I_{2}-3\right)}^{j}$

(3)

where n is the order of polynomials, and C_ij is the material parameters. A different n adopted in Eq. (3) indicates a different polynomial. As mentioned in the introduction, Mooney-Rivlin models with three parameters[9] maybe a good choice accounting for the precision and computational efficiency, which actually sets n as one and has the formulation as follows.

$W=C_{10}(I_{1}-3)+C_{01}(I_{2}-3)+C_{11}(I_{1}-3)(I_{2}-3)$

(4)

Furthermore, a hyperelastic constitutive model representing the nonlinear stress-strain relationship of the expansion water seal can be expressed by using the following incremental formulation

${\mbox{d}}S_{ij}={\frac {{\partial }^{2}W}{\partial {\epsilon }_{ij}\partial {\epsilon }_{kl}}}d{\epsilon }_{kl}$

(5)

in which S_ij is the Kirchhoff stress tensor, ε_ijis the Green strain tensor.

Last but not least, the material parameters C_ijin Eq. (3) are usually determined by regression analysis on the experiment data of the uniaxial stress state test and pure shear test.

3 IGA for the large deformation problem

3.1 B-spline and NURBS basis functions

Although a series of new spline technologies ^[24-26] have been introduced into IGA, B-splines and nonuniform rational B-splines (NURBS) are still the most prevalent spline technologies in IGA at present. In B-splines, a knot vector Ξ ={ξ₁, ξ₂, …, ξ_m+p+1} is a sequence of nondecreasing real numbers in the parametric space, where m is the number of control points and p is the order of the spline curve. The interval [ξ₁, ξ_m+p+1) is denoted as a patch, and the interval [ξ_i, ξ_i+1) is denoted as a span. Once a knot vector is available, B-spline basis functions can be recursively defined as

$N_{i,0}(\xi )=\lbrace {\begin{array}{cc}1&{\mbox{if}}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\xi }_{i}\leq \xi <{\xi }_{i+1}\\0&{\mbox{otherwise}}\end{array}}$

(6)

and

$N_{i,p}(\xi )={\frac {\xi -{\xi }_{i}}{{\xi }_{i+p}-{\xi }_{i}}}N_{i,p-1}(\xi )+$${\frac {{\xi }_{i+p+1}-\xi }{{\xi }_{i+p+1}-{\xi }_{i+1}}}N_{i+1,p-1}(\xi ){\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}{\mbox{ }}(p\not =$$0){\mbox{ }}{\mbox{ }}$

(7)

It is noticed that a knot in Ξ is permitted to repeat by augmenting Eq. (6) and (7) with a definition

${\mbox{​}}{\frac {0}{0}}\doteq 0$

(8)

Denoting the multiplicity of the knots as k, the continuity of the B-spline basis functions between knot spans is C^p−k. For a better understanding, a quadratic example is presented in Figure 2 for the knot vector Ξ = {ξ₁, ξ₂, ξ₃, ξ₄, ξ₅, ξ₆, ξ₇, ξ₈, ξ₉, ξ₁₀, ξ₁₁} = {0, 0, 0, 1, 2, 3, 4, 4, 5, 5, 5}.

Figure 2, A quadratic example for the B-spline basis function

With the basis functions in hand, a B-spline curve can be constructed as their linear combination:

$C(\xi )=\sum _{i=1}^{m}N_{i,p}\left(\xi \right)P_{i}$

(9)

in which P _i∈R^d, i = 1, 2, …, m, are called as control points, and d is the dimension of the physical space.

B-spline surfaces and solids are the tensor product of univariate B-splines. Given a control net P _{i, j}∈R^d, i = 1, 2, …, m, j = 1, 2, …, n, polynomial orders p and q, and knot vectors Ξ ={ξ₁, ξ₂, …, ξ_m+p+1}, and Θ ={η₁, η₂, …, η_n+q+1}, a tensor product B-spline surface is generated by

$S\left(\xi ,\eta \right)=\sum _{i=1}^{m}\sum _{j=1}^{n}N_{i,p}\left(\xi \right)M_{j,q}\left(\eta \right)P_{i,j}$

(10)

where N_{i, p}(ξ) and M_{j, q}(η) are univariate B-spline basis functions of order p and q, corresponding to the knot vectors Ξ and Θ, respectively. Similar to B-spline surfaces, a tensor product B-spline solid can be defined if a control lattice P _{i, j, k}, three polynomial orders, and three knot vectors are given.

Based on univariate B-spline basis functions, univariate NURBS basis functions can be defined by pairing a positive weight w_iwith each basis function

$R_{i,p}(\xi )={\frac {N_{i,p}(\xi )w_{i}}{\sum _{{\overset {\mbox{ˆ}}{i}}=1}^{m}N_{{\overset {\mbox{ˆ}}{i}},p}(\xi )w_{\overset {\mbox{ˆ}}{i}}}}$

(11)

And a NURBS curve can be constructed as

$C(\xi )=\sum _{i=1}^{m}R_{i,p}\left(\xi \right)P_{i}$

(12)

Then, the bivariate NURBS basis functions are obtained as

$R_{ij,pq}\left(\xi ,\eta \right)={\frac {N_{i,p}\left(\xi \right)M_{j,q}\left(\eta \right)w_{ij}}{\sum _{{\overset {\mbox{ˆ}}{i}}=1}^{m}\sum _{{\overset {\mbox{ˆ}}{j}}=1}^{n}N_{{\overset {\mbox{ˆ}}{i}},p}\left(\xi \right)M_{{\overset {\mbox{ˆ}}{j}},q}\left(\eta \right)w_{{\overset {\mbox{ˆ}}{i}}{\overset {\mbox{ˆ}}{j}}}}}$

(13)

And a NURBS surface results from

$S\left(\xi ,\eta \right)=\sum _{i=1}^{m}\sum _{j=1}^{n}R_{ij,pq}\left(\xi ,\eta \right)P_{i,j}$

(14)

Finally, the extension of Eq. (13) and (14) to the 3D situation induces a NURBS solid. It is noticed that B-splines can be considered as a special case of NURBS where the weights are all equal.

A series of important properties of NURBS basis functions (likewise for B-spines) is illustrated by taking R_ij,pq(ξ, η) as an example. Firstly, throughout the patch [ξ₁, ξ_m+p+1)× [η₁, η_n+q+1), R_ij,pq(ξ, η) is nonnegative. The second is the partition of unity all over the patch. The third is the local support, which means that R_ij,pq(ξ, η) = 0 if (ξ, η) is outside the span domain of [ξ_i, ξ_i+p+1)× [η_j, η_j+q+1). The last one is the continuity that the interior of the knot span domain is continuous up to C^∞, while the continuity between knot spans are C^p−k and C^q−lin which k and l denote the multiplicity along two directions, respectively.

3.2 Large deformation analysis using IGA with updated Lagrangian formulation

Suffered from the back pressure and the reservoir water pressure, large deformation of the expansion water seal always happens. Total Lagrangian formulation and updated Lagrangian formulation were provided in the conventional FEM for large deformation analysis. Considering that the updated Lagrangian (U.L.) formulation is more applicable to the situation that the external loads vary with the body deformation, U.L. formulation is used for numerical analysis on the expansion water seal in this study. Thus, a large deformation analysis using IGA with U.L. formulation is demonstrated in this section.

The incremental analysis is essential for the large deformation problems, which means that all physical quantities at time t are assumed to be known, and the quantities at time t＋Δt are required to be solved. A pre-superscript is introduced to indicate the time when the physical quantities are measured, e.g., ^tu_k is the displacement measured at time t. The principle of virtual displacement equivalent to the equilibrium condition required for the body at time t＋Δt is formulated for the U.L. formulation as

${\int }_{V}S_{}{}_{ij}\delta {\epsilon }_{}{}_{ij}{\mbox{d}}V=$$Q_{}$

(15)

where ^tΔtS_ij and ^tΔtε_ij are the updated Kirchhoff stress tensor and the updated Green strain tensor, which are both defined referring to the configuration at time t. ^tΔtQ is the virtual work resulted by the external loads, which is calculated by

$Q_{}{\mbox{=}}{\int }_{S}t_{}{}_{k}\delta u_{}{}_{k}{\mbox{d}}S+$${\int }_{V}f_{}{}_{k}\delta u_{}{}_{k}{\mbox{d}}V$

(16)

in which t_k and f_k represent the tractions on the boundary of the element and the body force on the element. It is noticed that the contribution in terms of the contact is not expressed explicitly in Eq. (15) and (16). In this study, the contact force is treated as a special kind of traction, which results in the contribution of the contact to the equilibrium condition being settled as t_k.

The updated Kirchhoff stress ^tΔtS_ij is the summation of and the updated Kirchhoff stress increment ΔS_ij and the known Cauchy stress ^tτ_ij, that is

$S_{}{}_{ij}{\mbox{=}}\Delta S_{ij}{\mbox{+}}{\tau }_{}{}_{ij}$

(17)

Considering that ^tε_ij is known, δ^tΔtε_ij is only determined by the updated Green stain increment Δε_ij. Δε_ij is the sum of the linear part Δε_ij^L and the nonlinear part Δε_ij^N, which can be computed as

$\Delta {\epsilon }_{ij}{\mbox{=}}\Delta {\epsilon }_{ij}{}^{L}{\mbox{+}}\Delta {\epsilon }_{ij}{}^{N}{\mbox{=}}{\frac {1}{2}}\left(\Delta u_{i,j}+\right.$$\left.\Delta u_{j,i}\right)+{\frac {1}{2}}\left(\Delta u_{k,i}\Delta u_{k,j}\right)$

(18)

in which Δu_k represents the incremental displacement during the time interval Δt. Substituting Eq. (17) and (18) into Eq. (15), we have

${\int }_{V}\Delta S_{ij}\delta \left(\Delta {\epsilon }_{ij}\right){\mbox{d}}V{\mbox{+}}{\int }_{V}{\tau }_{}{}_{ij}\delta \left(\Delta {\epsilon }_{ij}{}^{N}\right){\mbox{d}}V=$$Q_{}-{\int }_{V}{\tau }_{}{}_{ij}\delta \left(\Delta {\epsilon }_{ij}{}^{L}\right){\mbox{d}}V$

(19)

Based on Eq. (5), the incremental stress-strain relation is written as

$\Delta S_{ij}{\mbox{=}}D_{ijkl}\Delta {\epsilon }_{kl}$ ,

(20)

in which D_ijkl is the tensor denoting the constitutive relation. By ignoring the contribution of high-order terms, Eq. (19) can be further expressed as

${\int }_{V}D_{ijkl}\left(\Delta {\epsilon }_{kl}{}^{L}\right)\delta \left(\Delta {\epsilon }_{ij}{}^{L}\right){\mbox{d}}V{\mbox{+}}{\int }_{V}{\tau }_{}{}_{ij}\delta \left(\Delta {\epsilon }_{ij}{}^{N}\right){\mbox{d}}V=$$Q_{}-{\int }_{V}{\tau }_{}{}_{ij}\delta \left(\Delta {\epsilon }_{ij}{}^{L}\right){\mbox{d}}V$

(21)

The domain of the expansion water seal ΩR² can be discretized into a set of elements, that is, Ω =∪Ω^e. NURBS functions in Eq. (13) are used for the approximation of the displacement field ^t u ^e, the displacement increment Δu ^e, and the coordinates x ^e within each element as

${\boldsymbol {u}}_{}{}^{e}={\boldsymbol {R}}\left(\xi ,\eta \right)u_{}{}^{e},\Delta {\boldsymbol {u}}^{e}=$${\boldsymbol {R}}\left(\xi ,\eta \right)\Delta u^{e},{\boldsymbol {x}}_{}{}^{e}=$${\boldsymbol {R}}\left(\xi ,\eta \right)x_{}{}^{e}{\mbox{    }}\forall \left(\xi ,\eta \right)\in {\Omega }^{e}$

(22)

in which, ^t u ^e and ^t x ^e are the arrays containing the displacements and the coordinates of n^e number of control points in an element at time t,Δu ^e is the array containing the displacement incremental of control points in an element within the time interval Δt. R(ξ, η) = [R₁(ξ, η)I, R₂(ξ, η)I, …, R_ne(ξ, η)I] is a matrix of size 2 × 2n^e with identity matrix I in R². Here, R (ξ, η) is a simplified notation of R_ij,pq(ξ, η) in Eq. (13), and n^e denotes the total number of control points whose R (ξ, η) has local support in an element Ω^e.

Combined Eq. (21) and (22), a matrix expression of the equilibrium equation can be obtained for an element Ω^e as the following formulation.

$\left({\boldsymbol {K}}_{L}+{\boldsymbol {K}}_{NL}\right)\Delta u=$${\boldsymbol {Q}}-{\boldsymbol {F}}$

(23)

in which

${\boldsymbol {K}}_{L}{\mbox{=}}{\int }_{V}{\boldsymbol {B}}_{L}^{T}{\boldsymbol {D}}{\boldsymbol {B}}_{L}{\mbox{d}}V$

(24)

${\boldsymbol {K}}_{NL}{\mbox{=}}{\int }_{V}{\boldsymbol {B}}_{NL}^{T}{\boldsymbol {\tau }}{\boldsymbol {B}}_{NL}{\mbox{d}}V$

(25)

${\boldsymbol {F}}{\mbox{=}}{\int }_{V}{\boldsymbol {B}}_{L}^{T}{\boldsymbol {{\tau }^{'}}}{\mbox{d}}V$

(26)

B _L and B _NL are given by

(27)

${\boldsymbol {B}}_{NL}=\left[{\begin{array}{ccccccc}{\frac {\partial R_{1}}{\partial x}}&0&{\frac {\partial R_{2}}{\partial x}}&0&\cdots &{\frac {\partial R_{n^{e}}}{\partial x}}&0\\{\frac {\partial R_{1}}{\partial y}}&0&{\frac {\partial R_{2}}{\partial y}}&0&\cdots &{\frac {\partial R_{n^{e}}}{\partial y}}&0\\0&{\frac {\partial R_{1}}{\partial x}}&0&{\frac {\partial R_{2}}{\partial x}}&\cdots &0&{\frac {\partial R_{n^{e}}}{\partial x}}\\0&{\frac {\partial R_{1}}{\partial y}}&0&{\frac {\partial R_{2}}{\partial y}}&\cdots &0&{\frac {\partial R_{n^{e}}}{\partial y}}\end{array}}\right]$

(28)

Matrices τ and τ′ associated with the Cauchy stress tensor ^t τ _ij are given by

${\boldsymbol {\tau }}=\left[{\begin{array}{cccc}{\tau }_{}{}_{11}&{\tau }_{}{}_{12}&0&0\\{\tau }_{}{}_{21}&{\tau }_{}{}_{22}&0&0\\0&0&{\tau }_{}{}_{11}&{\tau }_{}{}_{12}\\0&0&{\tau }_{}{}_{21}&{\tau }_{}{}_{22}\end{array}}\right]$

(29)

${\boldsymbol {{\tau }^{'}}}={\left[{\begin{array}{ccc}{\tau }_{}{}_{11}&{\tau }_{}{}_{22}&{\tau }_{}{}_{12}\end{array}}\right]}^{T}$

(30)

Finally, the contributions of the loads to the equilibrium equation constitute Q, that is

${\boldsymbol {Q}}{\mbox{=}}{\int }_{S}{\boldsymbol {R}}{\left({\boldsymbol {\xi }}\right)}^{T}{\boldsymbol {t}}{\mbox{d}}S{\mbox{+}}{\int }_{V}{\boldsymbol {R}}{\left({\boldsymbol {\xi }}\right)}^{T}{\boldsymbol {f}}{\mbox{d}}V$

(31)

in which, t = [t_x, t_y]^T and f = [f_x, f_y]^T are the vector expressions for t_k and f_k, respectively. There is no barrier to obtain the value of the body force f. But, the value of the traction force t is difficult to be determined for the contact force is considered as a special kind of traction. This issue is figured out by introducing VI theory, which will be demonstrated in the next section.

Besides the expansion water seal, the entire water seal system comprises the water stop panel, the left and right pressing plate as well as the bed plate. These components are made of steel and their deformation is usually restrained in the elastic stage. Considering that elastic analysis is a fundamental application of IGA ^[12], the detailer derivation of the formulations and matrix equations in terms of these steel plates are left out in this study. The equilibrium equation for an element Ω^e in these steel plates can be expressed as the following matrix formulation after the IGA discretization.

${\boldsymbol {K}}^{\mbox{I}}\Delta u^{\mbox{I}}={\boldsymbol {Q}}^{\mbox{I}}-$${\boldsymbol {F}}^{\mbox{I}}{\mbox{ (I}}={\mbox{A,B,C,D)}}$

(32)

in which K^I is the stiffness matrix for steel plate I in the water seal system to be computed as K _L in Eq. (24), Δu^I is the array containing the displacement incremental of control points in steel plate I, Q^I is the load vector and F^I is the vector denoting the contribution of the existing stress to the equation. F^I and Q^I can be calculated by using Eq. (26) and (31). A, B, C, and D in Eq. (32) refer to the water stop panel, the left and right pressing plates, and the bed plate, respectively.

It is noticed that the contact forces acting on these steel plates are also considered as a special kind of traction in the solution of Eq. (32). Therefore, the positions and forces regarded to the contacts between the water seal and these steel plates are the critical quantities to be determined in the numerical simulation for the performance of the water seal system.

4 Variational inequalities for estimating the traction on the expansion water seal

4.1 Basic conception of VI theory

For convenience, a brief introduction to VI theory is given in this section; the details can be found in the monograph ^[20] by Facchinei and Pang. A variational inequality is formally defined below.

Definition 1 (VI) Given a subset K of the n-dimensional Euclidean space Rⁿ and a mapping F: K→Rⁿ, the variational inequality, denoted by VI(K, F), is to find a vector x∈K such that

${\left({\boldsymbol {y}}-{\boldsymbol {x}}\right)}^{T}{\boldsymbol {F}}\left({\boldsymbol {x}}\right)\geq 0,\forall {\boldsymbol {y}}\in K$

(33)

Here, means “for any” and ∈ “belonging to”.

Definition 2 (Box constrained VI), The box constrained VI(K, F) is such that the set K is a closed rectangle given by

$K\equiv \left\{{\boldsymbol {x}}\in R^{n}:a_{i}\leq x_{i}\leq b_{i},i=\right.$$\left.1,\cdots ,n\right\}$

(34)

Here, a_i and b_i are possibly infinite scalars satisfying ${\mbox{-}}\infty \leq a_{i}\leq b_{i}\leq {\mbox{+}}\infty$ .

Box constrained VI(K, F) is an important linearly constrained variational inequality and has some familiar degenerate forms. A point x∈K is a solution to the box constrained VI(K, F) if and only if for every i,

${\begin{array}{c}x_{i}=a_{i}\Rightarrow F_{i}\left(x\right)\geq 0\\a_{i}<x_{i}<b_{i}\Rightarrow F_{i}\left(x\right)=0\\x_{i}=b_{i}\Rightarrow F_{i}\left(x\right)\leq 0\end{array}}$

(35)

In the subsequent analysis, Eq. (35) is used to transform the contact conditions into VI.

4.2 VI for normal contact conditions

Figure 3 plots two elastic bodies coming into contact and undergoing deformation, one of which is called as the slave body Ω^s, and another one is called as Ω^m, referring to the monograph ^[27] by Wriggers. Compared with the expansion water seal, the deformation of the steel plate is small. Therefore, the water seal is directly assigned as the master body, while the steel plate is assigned as the slave body. ^t x^m represents the coordinates of a control point located on the boundary of the expansion water seal at time t, and its projection point ^t x^s is determined based on the minimum distance criterion ^[28]. The two points constitute a typical contact pair. Then, a framework (n_c, τ_c) to identify the normal and tangential directions regarding to the contact pair is defined, where n_c is specified as the inner normal direction of the expansion water seal boundary at ^t x^m.

File:Draft Hou 413412225-image39-c.png Figure 3, A schematic illustration of the contact restraints for a typical contact pair

Within a small time interval Δt, both the master and slave bodies deform, which induces a change in the configuration of the contact pair at the end of this time step. The normal distance d _n and the tangential relative displacement d _τ can be calculated for given Δu ^m and Δu ^s. Here, Δu ^m and Δu ^s are the increment displacements of the master and slave bodies within the time interval, respectively. Then, the tractions on ^t+Δt x^m and ^t+Δt x^s can be estimated based on VI theory, which finally induces two VIs as important augments to the equilibrium equations for both the master and slave bodies.

The normal direction is investigated in the first place. Because the master and slave bodies cannot be penetrated into each other, the normal distance d _n should be nonnegative, that is,

$d_{\boldsymbol {n}}={\boldsymbol {n}}_{c}{}^{T}\left({\boldsymbol {x}}_{}{}^{m}-\right.$$\left.{\boldsymbol {x}}_{}{}^{s}\right)={\boldsymbol {n}}_{c}{}^{T}\left({\boldsymbol {x}}_{}{}^{m}-\right.$$\left.{\boldsymbol {x}}_{}{}^{s}+\Delta {\boldsymbol {u}}^{m}\left({\boldsymbol {x}}^{m}\right)-\right.$$\left.\Delta {\boldsymbol {u}}^{s}\left({\boldsymbol {x}}^{s}\right)\right)\geq 0$

(36)

The normal contact force p _n is directly related to the normal distance d _n. The expansion water seal suffers the back pressure on the back and the reservoir water pressure on the head, which both have specified magnitudes. If the expansion water seal contacts the steel plate tightly, in other words, d _n=0, p _n is certainly greater than the normal force p ′_n induced by the back pressure or the water pressure. Otherwise, if d _n＞0, the traction acting on ^t+Δt x^m is p ′_n. The above conditions can be expressed as

${\begin{array}{c}p_{\boldsymbol {n}}={p^{'}}_{\boldsymbol {n}}\Rightarrow d_{\boldsymbol {n}}>0{\mbox{ }}\\p_{\boldsymbol {n}}>{p^{'}}_{\boldsymbol {n}}\Rightarrow d_{\boldsymbol {n}}{\mbox{=}}0{\mbox{  }}\end{array}}$

(37)

Comparing Eq. (37) with (35), (37) is equivalent to a box-constrained variational inequality with a_i = p ′_n and b_i = +∞; thus, the normal contact force must be the solution of the following VI

$VI\left(K^{\boldsymbol {n}},{\boldsymbol {F}}^{\boldsymbol {n}}\right),{\mbox{ with }}K^{\boldsymbol {n}}=$$\left[{p^{'}}_{\boldsymbol {n}},+\infty \right),{\mbox{ and }}{\boldsymbol {F}}^{\boldsymbol {n}}=$$d_{\boldsymbol {n}}$

(38)

4.3 VI for tangential contact conditions

As shown in Fig. 3, if d _n＞0 the normal contact force is p ′_n, and the tangential force must be zero considering that the properties of water pressure and air pressure. However, if d _n=0, the expansion water seal contacts the steel plate tightly, the tangential contact force must be taken into account. In this case, a contact pair might be in one of two contact states: the sticky state and the sliding state. The tangential relative displacement d _τ can be computed as

$d_{\boldsymbol {\tau }}={\boldsymbol {\tau }}_{c}{}^{T}\left({\boldsymbol {x}}_{}{}^{m}-\right.$$\left.{\boldsymbol {x}}_{}{}^{s}\right)={\boldsymbol {\tau }}_{c}{}^{T}\left({\boldsymbol {x}}_{}{}^{m}-\right.$$\left.{\boldsymbol {x}}_{}{}^{s}+\Delta {\boldsymbol {u}}^{m}\left({\boldsymbol {x}}^{m}\right)-\right.$$\left.\Delta {\boldsymbol {u}}^{s}\left({\boldsymbol {x}}^{s}\right)\right)$

(39)

The relative tangential movement in terms of a contact pair is dominated by the Coulomb friction law. Considering that the direction of the friction acting on the slave body Ω^s is in agreement with the tangential relative movement, it is denoted as p _τ. If a relative displacement happens, that is, d _τ≠0, the magnitude of p _τ will arrive at the maximum value μp _n allowed by the Coulomb friction law, in which μ denotes the Coulomb friction coefficient. Otherwise, if d _τ＝0, the magnitude of p _τ is certainly smaller than μp _n, but its direction is undetermined.

Based on the above analysis, for the sticky state, we have

${\begin{array}{c}p_{\boldsymbol {\tau }}=-\mu p_{\boldsymbol {n}}\Rightarrow -d_{\boldsymbol {\tau }}>0\\p_{\boldsymbol {\tau }}=\mu p_{\boldsymbol {n}}\Rightarrow -d_{\boldsymbol {\tau }}<0{\mbox{ }}\end{array}}$

(40)

The conditions about the tangential relative movement in Eq. (40) are written as a formulation of d _τ with the opposite sign, which aims to provide an intuitive form for the subsequent analysis.

For the sliding state, we have

$-\mu p_{\boldsymbol {n}}\leq p_{\boldsymbol {\tau }}\leq \mu p_{\boldsymbol {n}}\Rightarrow -$$d_{\boldsymbol {\tau }}=0$

(41)

Comparing Eq. (40) and (41) with Eq. (35), the two conditions can be considered as another box-constrained variational inequality with a_i =－μp _n and b_i = μp _n; therefore, p _τ must be the solution of the following VI

$VI\left(K^{\boldsymbol {\tau }},{\boldsymbol {F}}^{\boldsymbol {\tau }}\right),{\mbox{ with }}K^{\boldsymbol {\tau }}=$$\left[-\mu p_{\boldsymbol {n}},\mu p_{\boldsymbol {n}}\right],{\mbox{ and }}{\boldsymbol {F}}^{\boldsymbol {\tau }}=$$-d_{\boldsymbol {\tau }}$

(42)

For each control point located on the boundary of the expansion water seal at time t, the normal and tangential contact forces must be the solutions of Eq. (38) and (42), which are the supplement equations for Eq. (23) and Eq. (32) to estimate the traction on the expansion water seal.

5 Solution Strategy

Up to now, a set of formulations, including Eq. (23), (32), (38), and (42), are derived to simulate the entire water seal system, which can be resolved by various approaches. Actually, each equation is a degenerated VI in the framework of VI theory. Thus, gathering the formulations together will induce a total VI, and then, Path Newton Method based on the merit function ^[22] can be employed to solve it. However, this way may be inefficient because it doesn’t take full advantage of the structural features of the formulations. The structural feature is analyzed as follows.

To begin with, the tractions in the formulations fall into two categories: the known tractions where no possible contact occurs and the unknown contact forces where a possible contact pair occurs, because the contact force is treated as a special kind of traction. Once the unknown contact forces are given, there is no difficulty to solve Eq. (23) and (32) based on the classical FEM theory. And then, the normal distance d _n and the tangential relative displacement d _τ can be regarded as functions in terms of the unknown contact forces. Finally, the relations between the unknown contact forces and d _n and d _τ are expressed as Eq. (38) and (42). Therefore, selecting the unknown contact forces as the unknown quantity may be an advisable choice, which means that the increment displacements of all components of the water seal system are considered as the intermediate variables.

Assuming the number of contact pairs is m_c during the current time step, the normal contact force p _n and the tangential contact force p _τ in terms of m_c contact pairs constitute two arrays p_n and p_τ, respectively. The normal distance d ⁿ and the tangential relative displacement d ^τ constitute two arrays dⁿ and d^τ, respectively. Then, the formulations including Eq. (23), (32), (38), and (42) can be expressed as the following VI. Let the subset K^G= Kⁿ×K^τ, the mapping

${\boldsymbol {F}}^{G}:K^{G}\mapsto R^{2m_{c}}\equiv \left({\begin{array}{c}\\\end{array}}{\boldsymbol {d}}^{\boldsymbol {n}}-{\boldsymbol {d}}^{\boldsymbol {\tau }}\right)$

(43)

then (p_n, p_τ) is the solution of VI(K^G, F^G). Kⁿ and K^τ is composed of K ⁿ in Eq. (37) and K ^τ in Eq. (41) regarding to m_c contact pairs, respectively. Eq. (23) and (32) are used to calculated dⁿ and d^τ for a given (p_n, p_τ). Eq. (43) is called as the global variational inequality for the problem, which is resolved by using the Extra-gradient method ultimately. The details of the Extra-gradient method can be referred to the monograph ^[20] by Facchinei and Pang and the article ^[21] by Jiang et al.

6 Performance analysis for the expansion water seal using the proposed method

According to the requirements of the steel gate design for a planned hydropower station located in the downstream of the Jinsha River in southwest China, the performance analysis is implemented for two optional expansion water seals. The models of the two options are illustrated in Fig. 4 after the IGA discretization. It can be observed that the main difference between the two options is the shape of their seal heads. The proposed method is employed in the simulation of the deformation of the two options. Performance comparison is executed in terms of the leakproofness of the back cavity, the contact between the seal head and the stop panel as well as the offset of the seal head. Finally, a better option is recommended after a comprehensive consideration.

(a) Option A, (b) Option B

Figure 4, The IGA discretization for two optional expansion water seals

The two options are both made of LD-19 rubber, which is commonly used for the expansion water seal in hydraulic power stations such as Three Gorges Project. Their values of C₁₀, C₀₁, and C₁₁ in Eq. (4) have been measured by Liu et al. ^[3], which are 1.1505, -0.3286 and 0.0816, respectively. The steel plates have physical properties: Young’s modulus E = 2.07×10⁵ MPa, Poisson’s ratio ν = 0.3. Referring to the design code, the friction coefficient μ is taken as 0.60 for the contact between the water seal and the steel plate.

6.1 The free expansion of the water seal head

The free expansion of the water seal head, that is, the upward movement of the seal head without the effect of the water stop panel and the reservoir water pressure, is an important reference value in determining the width of the gap between the pressing plate and the water stop panel. By using the proposed method, the deformations of the two optional expansion water seals only suffered, when the back pressures are investigated, and the upward movements of the water seal head are measured. To verify the validity of the proposed method, the resulted movements are compared with the results of the laboratory model experiments ^[7] and the results of traditional FEM. The traditional FEM analysis is accomplished by ANSYS, and the established model in ANSYS has an equal number of elements to the IGA model in Fig.4 for an objective comparison. The upward movements of the water seal head resulted by the proposed method, ANSYS, and the laboratory model experiments are all plotted in Fig.5.

(a) Results for Option A (b) Results for Option B

Figure 5 Free expansion results for two optional expansion water seals

As Fig.5 shows, the variation tendencies of the upward movements on the back pressure resulted by the proposed method and ANSYS are consistent with the results of the model experiments. The gap between the experiment results and the numerical simulation results becomes larger with the back pressure increasing. However, the result of the proposed method are more close to the experiment results than that of ANSYS. The peak value of the difference between the experiment results and the results of the proposed method is smaller than 0.50 mm, while the peak value of the difference between the experiment results and the results of ANSYS exceeds 1.00 mm. Therefore, the new method proposed in this study is effective in the numerical simulation of the expansion water seal and has a higher precision than the traditional FEM.

When the two options are suffering the same back pressure, a little difference between their results appears, indicating that the shape of the water seal head imposes no influence on the free expansion of the water seal head. Upward movement of the water seal head increases with an increasing back pressure, which apparently presents a nonlinear feature and can be described as the following four stages. In the first stage, the back pressure is less than 0.01 MPa and the upward movements are near zero. In the second stage, the back pressure rises from 0.02 MPa to 0.14 MPa and the upward movements appear to be increased dramatically. The upward movements at the end of the second stage arrive at 65.60% and 65.36% of the total upward movements for Option A and Option B, respectively. In the third stage, the back pressure rises from 0.15 MPa to 0.18 MPa and the slopes of the upward movement curves are becoming smaller, which can be considered as a transition stage. In the fourth stage, the back pressure is greater than 0.18 MPa and the upward movements present a linear increase with a gentle slope.

Additionally, the upward movement where the third stage begins is always treated as a reference to determine the width of the gap between the pressing plate and the water stop panel. According to the upward movement curves, the gap width is temporarily assumed to be 25 mm for both optional expansion water seals.

6.2 The leakproofness of the back cavity

After the assembly of the water seal system, the leakproofness of the back cavity is dominated by the contacts between the two water seal wings and the pressing plates and the bed plate. If the contact stress is greater than the back pressure, the back cavity is considered to have a satisfactory leakproofness. According to the engineering design scheme, the reservoir water pressure acting on the expansion water seal is 0.2 MPa, which means that the steel gate suffers the hydraulic head of 20 m. The working back pressure is 0.4 MPa. The width of gap between the pressing plate and the water stop panel has been set as 25 mm. The deformations of two optional expansion water seals under the above conditions are investigated by using the proposed method, and the results of deformations and stresses are plotted in Fig.6.

(a) Configuration and principal stress σ₁ for Option A, (b) Configuration and principal stress σ₁ for Option B

(c) Contact stress at the boundary of Option A, (d) Contact stress at the boundary of Option B

Figure 6 results of deformations and stresses for two optional expansion water seals

Option A is investigated in the first place. Under the prescribed working conditions, the peak value of the principal stress σ₁ is 1.73 MPa, far less than LD-19 rubber’s break strength 7.64 MPa. Regarding the contact between the water seal wings and the adjacent plates, the peak value of the stress is 2.03 MPa, and the average value is about 1.08 MPa, which is far more than the working back pressure 0.40 MPa. Thus, the leakproofness of the back cavity is satisfied by Option A.

Then, Option B is investigated. The peak value of the principal stress σ₁ is 1.56 MPa in the water seal under the same working conditions. The peak value of the contact stress is 2.01 MPa, and the mean value is about 1.09 MPa. In this case, the expansion water seal will not be broken and the leakproofness of the back cavity is also satisfied.

In short, both Option A and Option B can satisfy the leakproofness of the back cavity. Moreover, there is a little difference in stresses regarding to the contacts between their wings and the adjacent plates, which can be attributed to the fact that the water seal wings of the two options are identical.

6.3 The effectiveness to seal up the reservoir water

The stress in terms of the contact between the water seal head and the water stop panel is a critical quantity to assess the effectiveness of the water seal to seal up the reservoir water. In general, the back pressure required for successfully sealing up the reservoir water should be determined under an assumed gap width.

First of all, taking the back pressure and the reservoir water into account, the contact between the seal head and the stop panel is investigated for a given gap width. To reveal the variation law of the contact stress and width, it is assumed that the back pressure varies from 0.10 MPa to 0.60 MPa, and the water pressure varies from 0.05 MPa to 0.30 MPa. The deformation of the expansion water seal is simulated, and the stress and width of contact between the seal head and the stop panel are recorded. Take Option A with a 10 mm gap width as an example, the mean value of contact stress and the contact width vary as Fig.7 shows.

(a) Contact stress, (b) Contact width

Figure 7, The variation of the contact stress and width with the back pressure and the reservoir water pressure

Both the mean value of contact stress and the contact width rise with an increasing back pressure when the reservoir water pressure is fixed. While, they both decrease with an increasing reservoir water pressure, when the back pressure remains unchanged. In case that the water seal head contacts the water stop panel, the results comparison verifies that the back pressure has a more significant effect on the contact stress and the contact width than the reservoir water pressure.

Although the effect of the reservoir water pressure on the stress and width of contact is relatively small, the reservoir water pressure is a key quantity in determining the threshold value required for the back pressure. If the reservoir water pressure increases, a larger threshold value is required for the back pressure to seal up the reservoir water. Once the water seal head contacts the stop panel, the contact stress will be greater than the reservoir water pressure and be mainly dominated by the back pressure. Therefore, the threshold value required for the back pressure should be determined based on the reservoir water pressure.

A general criterion that the contact between the water seal head and the water stop panel results in the contact stress greater than the reservoir water pressure is used to determine the threshold value required for the back pressure. Through numerical simulation, the threshold values required for the back pressure are acquired for different combinations of gap width and reservoir water pressure, which are plotted in Fig.8.

Figure 8 threshold values of the back pressure required for the two options

Results show that the threshold values of the back pressure required for the two options are almost indistinguishable under the same reservoir water pressure and gap width. Both the increase of the reservoir water pressure and the gap width result in a rising threshold value of the required back pressure. However, when the gap width arrives at 30 mm, the threshold value of the back pressure will be greater than the prescribed working back pressure 0.40 MPa. Under a gap width of 25 mm, the threshold value of the back pressure are less than the prescribed working back pressure, even if the reservoir water pressure increases to 0.30 MPa. Thus, it is reasonable to prescribe the gap width as 25 mm. In conclusion, there is little difference between the two optional expansion water seals in their ability to seal up the reservoir water, and both of them can work efficiently by using the prescribed gap width.

6.4 The offset of the water seal head

Due to the singularity of the reservoir water flowing, the offset of the water seal head is inevitable. In case of an excessive offset, the deformation recovery of the water seal head maybe difficult at the time that the back pressure is cancelled, and then the working life will be shortened. Therefore, the offset should be inspected for estimating the deformation recovery capacity and the working life of the expansion water seal. In this study, the horizontal displacement of the water seal head at the highest point of the upper curved boundary is taken as a reference value for the offset.

Figure 9, Horizontal displacement of the water seal head for the two options

The horizontal displacements at the reference point are recorded for the two options and plotted in Fig.9 in case that the gap width takes the prescribed value 25 mm. To reveal the variation of the offset, the reservoir water pressure is assumed to vary from 0.20 MPa to 0.30 MPa, and the back pressure varies from the corresponding threshold value to the prescribed working back pressure 0.40 MPa. Increasing reservoir water pressure induces a larger horizontal displacement, while the increase of the back pressure results in a smaller horizontal displacement. In case of the same back pressure and the same reservoir water pressure, the horizontal displacement at the reference point of Option A are about 1 mm less than that of Option B. Considering that the maximum value of the horizontal displacement in Fig.9 is about 7 mm, the difference is considerable. Thus, a conclusion can be drawn that Option A is better than Option B in terms of the deformation recovery capacity and working life.

6.5 The recommended option

Up to now, the back cavity leakproofness, the effectiveness on sealing up the reservoir water, and the seal head offset have been comprehensively investigated for the two optional expansion water seals. Both options are capable to satisfy the back cavity leakproofness and are effective in sealing up the reservoir water by using the prescribed gap width and the prescribed working back pressure. The main difference between the two options is the offset of the seal head. Under the same conditions, the seal head offset of Option A is smaller than Option B, indicating that Option A may have a better deformation recovery capacity and a longer working life than Option B. Thus, Option A is recommended for the hydraulic steel gate design finally.

7 Conclusions

The work presented in this article aims at developing an effective and accurate method based on IGA analysis to investigate the performance of the expansion water seal in the hydraulic steel gate. The proposed method has the following advantages:

(1) The complex geometrical shape of the expansion water seal can be represented more exactly by using IGA analysis than by the traditional FEM method.

(2) The estimation of the contact force is accomplished by solving the variational inequality in terms of the contact conditions, which avoids the demerits of the existing approaches and simplifies the incremental equilibrium equations.

(3) The proposed method is effective in the numerical simulation of the expansion water seal and has a higher precision than the traditional FEM under the same conditions.

Data Availability

The data used to support the findings of this study are available from the corresponding author upon request.

Conflicts of Interest

The authors declare that there are no conflicts of interest regarding the publication of this article.

Authors’ Contributions

Conceptualization, Zhou Yida; Formal analysis, Hu Kejian; Methodology, Hu Taoyong; Resources, Shi Shoujin; Software, Han Yifeng; Validation, Wang Jinkun; Visualization, Lou Yidan; Writing – original draft, Hou Tao.

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