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The design method of rubber-metallic expansion joint

  • Przemysław Jaszak , Janusz Skrzypacz and Konrad Adamek EMAIL logo
Published/Copyright: December 26, 2018
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Open Engineering
From the journal Open Engineering Volume 8 Issue 1

Abstract

The paper present the method of designing a rubber expansion joints, intended for operation in the pressure class 25 bar. During the design used a numerical analysis,which based on the finite element method (FEM). The results from experimental test were used to correctly modeled the rubber or polyamide reinforcement. Basis on the obtained results, the hyperelastic model of the rubber was prepared, then the design of the rubber expansion joint was tested in different load case, i.e tensile or compressive deflection and pressurization.

Keywords: rubber; modeling; hyperelastic; FEM; design

1 Introduction

The rubber expansion joint is an elastic element of the pipeline system whose main task is to minimize the thermal and mechanical deflections as well as dampening of the noises and vibrations [1]. The main part of the expansion joint is elastic diaphragm made of rubber and a reinforcing layer. Usually the diaphragm is embedded in the metal flanges used for joining with the pipeline system – Fig. 1.

Figure 1 Rubber expansion joint with metallic loose flanges
Figure 1

Rubber expansion joint with metallic loose flanges

The elastic diaphragm consists of several layers; internal, reinforced and external – Fig. 2. The internal layer plays the protective role for subsequent reinforcing layers. The reinforcing layer is usually made from polyamide or aramid fiber. There is an important element since its quality influences the durability and strength of the expansion joint. The last layer, that is, the external one is protection against atmospheric agents as well as it binds the all elements into one composite piece.

Figure 2 The design of elastic diaphragm: 1-internal layer; 2-reinforcing layer; 3-external layer; 4-metallic wire
Figure 2

The design of elastic diaphragm: 1-internal layer; 2-reinforcing layer; 3-external layer; 4-metallic wire

The adequate selection of the rubber onto each layer of the expansion joint provides its resistance against different aggressive media. Table No 1 presents the main application of expansion joint depending on type of rubber used as the internal layer.

It is worth to mention that the rubber expansion joint is not a supporting element of the pipeline system. The proper scheme of its installation is presented in Fig. 3, where expansion joint is located between two fixed supports.

Figure 3 Scheme of the installation of the expansion joint in pipeline system
Figure 3

Scheme of the installation of the expansion joint in pipeline system

The displacements of the pipeline which are mitigated by means of the expansion joint could be distinguished into three basic groups:

Figure 4 The displacement of the expansion joint: a) compressive; b) tensile; c) lateral; d) angular
Figure 4

The displacement of the expansion joint: a) compressive; b) tensile; c) lateral; d) angular

Table 1

Application of the expansion joint depending on the rubber.

Internal layerThe most widely used
NRAbrasive materials, sewages, sea water
CRCold water, sea water, cold air
NBROil, gasoline, gas, compressed air
NBR/PVCPetrol, hydraulic oil
EPDMHot water, cooling water, acids, diluted chlorine solutions
CSMAcids and alkaline solutions
IIRHot compressed air, alkalines
HNBRHot oil 120 ∘C, mixtures of oil and water
PTFEExtremelly agressive agents

Guidelines for tests conditions of the rubber expansion joint are included in [1]. The main procedures are:

  • – Internal pressure test at room temperature (the compensator should be withstand the test pressure equals 20 bar, for 1 hour)

  • – Internal pressure test at 100∘ C temperature (the compensator should be withstand the test pressure equals 20 bar, for 1 hour)

  • – Flexibility test (at room and 100∘ C temperature with internal pressure 10 bar)

  • – Ageing test (at 100∘C and pressure 10 bar).

The rubber expansion joints are widely available on the market, their are mainly dedicated to the maximum pressure class PN16, i.e. the maximum working pressure is 16 bar. However, there are installations where higher pressure is required, therefore, special solutions are necessary. In this paper the design method of such an expansion joint was presented.

2 The design method of expansion joint in numerical way

To design such structures as elastic composite diaphragm is very complex since the elements made of rubber exhibit strongly non-linearity between the stress and strain relationship. In this case the best solution is to use numerical methods. One of them is a finite element method FEM. Modeling of the hyperplastic material like rubber in FEM includes adequate reflect of the real material by constitutive model.

For this reason, it is necessary to carry out experimental tests of the rubber in a multidirectional state of stress and strain. Then, based on the experimental data, the material constants of the constitutive hyperelastic model are

determined. The whole process of designing rubber expansion joint in FEM can be divided into a few basic steps:

  • – Testing of rubber materials,

  • – Adapting of the hyperelastic mathematical model,

  • – Preparation of the geometrical model,

  • – Setting the boundary conditions,

  • – Analyzing of the results obtained from the calculations.

2.1 Test of materials

To perform the elastic diaphragm the EPDM and NBR rubber were selected. Those materials are commonly used to the production of the elastic diaphragm of the expansion joint which are utilized in the industry. The both materials meet general requirement of the maximum operating temperature for the rubber expansion joint which equals 130∘C. The other kind of rubbers are rather dedicated in special cases, for instance in a higher operating temperatures or in applications where an aggressive media are transported. The hardness of both materials was 65 Shore. First, the tests of uniaxial tension were carried out in line with [2, 3]. The experiment was conducted by means of Instron test rig presented in Fig. 5.

Figure 5 Test rig Instron model 5944
Figure 5

Test rig Instron model 5944

The aim of the test was to determine the stress (σ) and strain (ϵ) relationship in uniaxial state of deformation. The exemplary characteristic of uniaxial tension of the NBR rubber was shown in Fig. 6.

Figure 6 Uniaxial tension of the NBR 65∘ Sha
Figure 6

Uniaxial tension of the NBR 65∘ Sha

The second test was equibiaxial tension. Due to lack of the proper standards in this test the bubble inflation method was used in accordance with [4, 5, 6, 7, 8, 9].

This method consisted of pressurization of the rubber disc located between two metallic flanges – Fig. 7a and recording its deformation under increasing nitrogen pressure – Fig. 7b. The scheme of the test rig was presented in Figure 7c. The exemplary registered pictures of the deformed mode of the rubber sample were shown in Fig. 8.

Figure 7 Test rig to biaxial stretch of rubber by means of bubble inflated method a) flange joint, b) view of inflated diaphragm, c) scheme of the test rig 1- reservoir, 2-regulating valve, 3-milimetric scale, 4- rubber sample, 5-flange joint, 6-manometer, 7-camera, 8-tablle
Figure 7

Test rig to biaxial stretch of rubber by means of bubble inflated method a) flange joint, b) view of inflated diaphragm, c) scheme of the test rig 1- reservoir, 2-regulating valve, 3-milimetric scale, 4- rubber sample, 5-flange joint, 6-manometer, 7-camera, 8-tablle

Figure 8 The deflection of the rubber samples under increasing pressure.
Figure 8

The deflection of the rubber samples under increasing pressure.

The engineering strain in the bubble pole were estimated by means of the following formula [4]:

(1)ϵx=ϵy=−1ϵz=−12lntt0=ln1+hR2

where: ϵx, ϵy, ϵz – directional strain respectively in axis x,y,z; t0 – nominal thickness of the rubber sample; t– thickness under deflection; h –hight of the bubble ; R– radius of the flange’s hole.

The engineering stress in the bubble pole was calculated by means of the following formula [4]:

(2)σx=σy=pR2t0

Applying the formulas (1) and (2) in the function of the pressure, the stress – strain relationship could be plotted as a biaxial characteristic presented in Fig. 9. The mechanical strength of the rubber under biaxial deflection is prominently lower than uniaxial because rupturing took place at twice lower stress and strain.

Figure 9 Biaxial tension of the NBR 65∘ Sha
Figure 9

Biaxial tension of the NBR 65∘ Sha

2.2 The hyperelastic model of the rubber

To reflect the rubber behaviour the tri-parameric hiperelastic model proposed by Mooneya–Rivlina (M-R) was used [10, 11, 12, 13]. The density of the elastic strain energy is described by formula (3):

(3)W=C10I¯1−3+C01I¯2−3+C11I¯1−3I¯2−3

where: C10, C01, C11 – material constants, I1, I2 –Couchy-Green strain invariants.

The values of the constants C10, C01, C11 were determined based on uniaxial and biaxial tests. In Fig. 10 the fitting curves of the M-R model to the experimental data were presented.

Figure 10 Fitting curves of the M-R model to experimental data: 1 – approximation of the uniaxial tensile ; 2 – approximation of the biaxial tensile; 3 approximation of the uniaxial shear –; 4 – experimental data set of the uniaxial tensile; 5 – experimental data set of the biaxial tensile
Figure 10

Fitting curves of the M-R model to experimental data: 1 – approximation of the uniaxial tensile ; 2 – approximation of the biaxial tensile; 3 approximation of the uniaxial shear –; 4 – experimental data set of the uniaxial tensile; 5 – experimental data set of the biaxial tensile

2.3 Geometrical model and boundary conditions

Based on geometrical model of the elastic diaphragm (Fig. 11a) the numerical model (Fig. 11b)was prepared. The discretization of the geometry was performed by hexagon elements with a higher shape function. The contact between two element (polyamide layer and rubber layer) was set as a bonded. It reflected a real behavior of this structure because during the curing process the both materials were stuck together. The steady state of structural analysis was set.

Figure 11 a) geometrical model: 1 – external layer, 2 – reinforcement, 3 – mid layer, 4 – wire, 5 – internal layer; b) discretized model
Figure 11

a) geometrical model: 1 – external layer, 2 – reinforcement, 3 – mid layer, 4 – wire, 5 – internal layer; b) discretized model

In the Fig. 12 the boundary condition of the numerical model was presented.

Figure 12 Boundary condition of the elastic diaphragm: 1 –the surface where the internal pressure was applied; 2 – the plane where fixed support was applied; 3 – the plane where displacements were applied.
Figure 12

Boundary condition of the elastic diaphragm: 1 –the surface where the internal pressure was applied; 2 – the plane where fixed support was applied; 3 – the plane where displacements were applied.

The following load cases of the elastic diaphragm were analyzed.

  • – Internal pressure in range from 10 to 25 bar,

  • – compression/tension deflection up to 20 mm,

  • – lateral deflection up to 20 mm,

  • – angular deflection up to 20∘.

The M-R model (3) was prepared in two configurations for EPDM and NBR rubber for which the material constants equal C10EPDM = 0,554, C01EPDM = 0,003, C11EPDM = 0,012 and C10NBR = 0,964, C01NBR = -0,273, C11NBR = 0,066 respectively. In accordance whit the standardized construction of the elastic diaphragm its reinforcing layer (in the form of crossed braided mesh) is an circumferentially wound inside the structure. So, some fibers of the polyamide layer are parallel to the axis of the diaphragm and the other are oriented in perpendicular way. Therefore, the orthotropic model of the polyamide was used. The material properties of the polyamide model were compiled in Table 2.

Table 2

Mechanical properties of the polyamide fiber of 1 mm thickness [14]

Longitudional deformation moduleForm deformation modulePoisson ratio
Axis directionValue [MPa]PlaneValue [MPa]PlaneValue [–]
X1 200XY400XY0,43
Y1 200YZ400YZ0,43
Z500XZ200XZ0,35

3 Results

The main aim of the numerical calculation was to determine the allowable displacement of the elastic diaphragm in defined directions at constant pressure. The Figures 13 and 14 depict the exemplary maps of von Misses stress distribution of the elastic diaphragm in a selected deformation mode.

Based on these maps in the Fig. 13b and 14b it was observed that the highest stress occurs in the reinforcing layer. The exemplary chart of the stress in the reinforcing layer in the function of deformation increase was shown in Fig. 15. The allowable stress of this material is 110 MPa. Therefore, exceedance of this value determined the maximum displacement of the elastic diaphragm in particular direction. These maximum displacements for all deflecting mode were compiled in Table 3.

Figure 13 The deflection and von Misses stress distribution of the elastic diaphragm made of EPDM rubber. Load case: angular deflection at 15 deg. and internal pressure 20 bar, a) generalized deflection, b) von Mises stress distribution
Figure 13

The deflection and von Misses stress distribution of the elastic diaphragm made of EPDM rubber. Load case: angular deflection at 15 deg. and internal pressure 20 bar, a) generalized deflection, b) von Mises stress distribution

Figure 14 The deflection and von Misses stress distribution of the elastic diaphragm made of EPDM rubber. Load case: compressive deflection at 15 deg. and internal pressure 20 bar, a) generalized deflection, b) von Mises stress distribution
Figure 14

The deflection and von Misses stress distribution of the elastic diaphragm made of EPDM rubber. Load case: compressive deflection at 15 deg. and internal pressure 20 bar, a) generalized deflection, b) von Mises stress distribution

Figure 15 The von Misses stress in reinforcing layer depending on axial tensile displacement and internal pressure 25 bar for elastic diaphragm made of EPDM rubber.
Figure 15

The von Misses stress in reinforcing layer depending on axial tensile displacement and internal pressure 25 bar for elastic diaphragm made of EPDM rubber.

Table 3

The maximum displacement of the elastic diaphragm depending on internal pressure

RubberPressure [bar]Displacement
Compression clim [mm]Tension alim [mm]Lateral rlim [mm]Angular αlim [∘]
EPDM101310158
15138157
20127157
25106125
NBR10138158
15126158
20126158
25105125

4 Summary

The finite element method is a helpful tool at designing and analyzing components made of rubber, especially in case a large deformation, since the rubber material exhibits a strong nonlinearity between strain and stress relationship. Using this method for designing of the rubber expansion joint enabled to checked how are the permissible deflection of the elastic diaphragm in particular directions, providing its failure-free work. It turn out that the maximum stress in the elastic diaphragm occurred in reinforcing layer regardless of kind of rubber used for internal and external layers.

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Received: 2018-07-06
Accepted: 2018-10-01
Published Online: 2018-12-26

© 2018 P. Jaszak et al., published by De Gruyter

This work is licensed under the Creative Commons Attribution-NonCommercial-NoDerivatives 4.0 License.

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https://doi.org/10.1515/eng-2018-0065
Keywords for this article
rubber; modeling; hyperelastic; FEM; design
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BY-NC-ND 4.0

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