Design And Thermal Analysis of Thermal Expansion Joint in Industrial Application

Size: px

Start display at page:

Download "Design And Thermal Analysis of Thermal Expansion Joint in Industrial Application"

Lucas Miller
5 years ago
Views:

IJIRST International Journal for Innovative Research in Science & Technology Volume 2 Issue 1 June 2015 ISSN (online): 2349-6010 Design And Thermal Analysis of Thermal Expansion Joint in Industrial

Khunt Assistant Professor Department of Mechanical Engineering Nar Narayan Sastri Institute of Technology, Jetalpur Abstract Present study covers different types of expansion joints used in industry.

1 IJIRST International Journal for Innovative Research in Science & Technology Volume 2 Issue 1 June 2015 ISSN (online): Design And Thermal Analysis of Thermal Expansion Joint in Industrial Application Rakesh. P. Prajapati M.E Student Department of Thermal Engineering Nar Narayan Sastri Institute of Technology, Jetalpur Prof. Jayesh. B. Khunt Assistant Professor Department of Mechanical Engineering Nar Narayan Sastri Institute of Technology, Jetalpur Abstract Present study covers different types of expansion joints used in industry. The expansion joints are used to dissipate the energy during contraction or expansion in pipes. Different types of expansion joints are widely used in piping industries. This covers detailed calculation from EJMA (Expansion Joint Manufacturers association), Design, Modelling, and Thermal and Structural analysis of axial type expansion joint. All design process will be performed with aid of FE analysis using ANSYS software. Keywords: ANSYS, FE I. INTRODUCTION An Externally Pressurized Expansion Joint takes pressure from the outside of the bellows element relatively than on the inside as in a conventional expansion joint. In conventional type of expansion joints with internally pressurized bellows it is not possible to contain large axial movements due to the squirm connected with the higher bellows length. Fig. 1: Thermal Expansion Bellows The stabilizing effect of the external pressure increases the bellows capacity to absorb high axial movements without twist making the externally pressurized expansion joints the best explanation for applications involving very high axial movements. The construction of an externally pressurized expansion joint consists of a heavy outer pipe which contains the pressure and serves as a covering to protect the bellows and also functions as pipe-guide. The outer pipe in externally pressurized expansion joints contain the full pressure of the system and if bellows disappointment occurs the medium does not run away radially outwards, thus protecting the personnel working in the surrounding area. The internal pipe of the externally pressurized expansion joint act as liner and maintains fluid flow external to the bellows so that the flowing medium does not collect inside the bellows convolutions and hence do not show aggression the bellows element if the flowing medium is corrosive. Drain and vent links can be easily provided to remove any deposit or remains that collects inside the outer cover. The externally pressurized expansion joint is really easy to insulate and steam tracing can be used to sustain the temperature of the medium flowing through it. Another important advantage of this type of expansion joint is that in the occasion of anchor failure the bellows get compressed and act as a shock absorber to keep up the overall system constancy. All rights reserved by 39

II. GEOMETRY A. LOAD CASE-1: The Geometry for the FEA consists of Assembly of all the main components of the Expansion Joint i.e. Bellows, Collars, Tee Pipe, End Pipes, Centre Pipe, Blind Flange, Tie Rods, Tie Rod Gussets, Back-up Bars and Stiffeners.

2 LOAD CASE-2: The Geometry for the FEA consists of Assembly of all the main Structural Components of the Expansion Joint i.e. Tee Pipe, End Pipes, Blind Flange, Tie Rods, Tie Rod Gussets, Back-up Bars and Stiffeners.

2 II. GEOMETRY A. LOAD CASE-1: The Geometry for the FEA consists of Assembly of all the main components of the Expansion Joint i.e. Bellows, Collars, Tee Pipe, End Pipes, Centre Pipe, Blind Flange, Tie Rods, Tie Rod Gussets, Back-up Bars and Stiffeners. The 3D model used for FEA is as shown in image be Fig. 2: 3D Model used for FEA Fig. 3: Geometry for FEA for Load Case-1 B. ss6.4.2 LOAD CASE-2: The Geometry for the FEA consists of Assembly of all the main Structural Components of the Expansion Joint i.e. Tee Pipe, End Pipes, Blind Flange, Tie Rods, Tie Rod Gussets, Back-up Bars and Stiffeners. The 3D model used for FEA is as shown in image below: All rights reserved by 40

Load Case: 3 Pressure Thrust due to bellow applied on pipe piece Nominal Case Fig.

3 Fig. 4: Geometry C. Load Case: 3 Pressure Thrust due to bellow applied on pipe piece Nominal Case: 1) Boundary Condition: Fig.2.4. Load Case: 3 Pressure Thrust due to bellow applied on pipe piece Nominal Case Fig. 5: Load Case -3 Table 1 Location of Loads SR. NO PROB POINT LOCATION LOAD (N) 1 A Left Side Sleeve B Towards T joint C Towards T joint D Right Side Sleeve All rights reserved by 41

4 D. 1) Load Case: 4 Pressure Thrust due to bellow applied on pipe piece TestPressure Case: Boundary Condition Fig. 6: Load Case: 4 Pressure Thrust Due To Bellow Applied On Pipe Piece Test Pressure Table 2: Location of Load SR. NO PROB POINT LOCATION LOAD (N) 1 A Left Side Sleeve B Towards T joint C Towards T joint D Right Side Sleeve E. Optimization of Ply Thickness of Corrugated Bellow Assembly at Different No. Of Plies: As shown in below figure here we are taking 0.2 mm ply thickness at 5 number of plies. 1) ply thickness = 0.2 mm 2) No. of plies = 5 1) Total Deformation: Fig7.:- Analysis for evaluating the Total deformation at 0.2 mm ply thickness Fig. 7: Optimization of Bellows Here we are reduce the ply thickness from 0.5 to 0.2 mm at 5 no. of plies and the generated result data shows that the total deformation is 3.5 mm and generated equivalent stress is Mpa as in the figure All rights reserved by 42

Fig. 8: Optimization Of 0.2 Mm Thickness F. Equivalent Stress Fig. 9: Analysis For Evaluating The Total Deformation At 0.4 Mm Ply Thickness Analysis for evaluating the Equivalent stress at 0.

Of Plies = 4 3) Total Deformation: Here we are reduce the ply thickness from 0.5 to 0.4 mm at 4 no. of plies and the generated result data shows that the total deformation is 2.

5 Fig. 8: Optimization Of 0.2 Mm Thickness F. Equivalent Stress Fig. 9: Analysis For Evaluating The Total Deformation At 0.4 Mm Ply Thickness Analysis for evaluating the Equivalent stress at 0.2 mm ply thickness 2) As shown in below figure here we are taking 0.4 mm ply thickness at 4 number of plies. 1) Ply Thickness = 0.4mm 2) No. Of Plies = 4 3) Total Deformation: Here we are reduce the ply thickness from 0.5 to 0.4 mm at 4 no. of plies and the generated result data shows that the total deformation is mm and generated equivalent stress is 197 Mpa as shown in the above figure. G. Optimization Result: Table - 3 Optimization Result Table VARIABLE PARAMETERS CASE-1 CASE-2 CASE-3 PLY THICKNESS DEFLECTION 1.3 mm 2.6 mm 3.5 mm STRESS 118Mpa 197Mpa 315.6Mpa All rights reserved by 43

6 Fig. 10: Optimization Result Graph III. CONCLUSION A. Case - 1: The Load Case simulates only the effect of External Pressure on Bellow. The Results obtained are satisfactory and the allowable stresses are less than those considered in Design calculations. B. Case -2: The Load Case simulates only the effect of Direct External Pressure on Blind Flange and Pipe Sections. As can be seen considering the Allowable stresses of 140 MPa, the maximum stresses coming on the Structure are around 126 MPa, However, taking into considering the Direction of the Loading i.e. the External Pressure coming on the Blind Flange, the stresses are Compressive in nature and occurring on the Pipe End. C. Case -3: The Load Case simulates the effect of thrust forces produced due to bellow contraction at nominal pressure. The stresses are well below the allowable limit. D. Case -4: The Load Case simulates the effect of thrust forces produced due to bellow contraction at Test pressure. The stresses are well below the allowable limit. REFERENCES [1] Bijayani Panda, M. Sujata, M. Madan, S.K. Bhaumik; Stress corrosion cracking in 316L stainless steel bellows of a pressure safety valve.volume: 36 ELSEVIER(2014) [2] Brijesh M. Patel1, B.D.Patel2, V.M.Prajapati3 A Critical Review on Metal Expansion Bellows. (IJESIT) Volume 2, Issue 2, March 2013, ISSN: Pgs: [3] H. T. Akshatha, A. Rinku, M. L. Shankar and PrashanthBanakara, Design, Development, Simulation And Realization of Expansion Joints In Ecs Engine Bleed System ForA Typical Light Transport Aircraft. ISSN Vol. 9, No. 5, May 2014.Pgs.: [4] D. E. Newland, Buckling Of Double Bellows Expansion Joints Under Internal Pressure. Issue 3, Vol , ISSN Pgs: [5] Brijeshkumar. M. Patel, Design, Manufacturing and Analysis of Metal Expansion Bellows(IJESIT) Volume 2, ISSN: XIssue 3, May 2013.Pgs [6] Gaurav R. Mohite1, A. P. Edlabadkar2,Analysis Of Expansion Joint In Heat Exchanger Using Finite Element IJPRET 2014; Volume 2 (9): [7] Gh. Faraji, M. MosaviMashhadi, V. Norouzifard,Evaluation of effective parameters in metal bellowsforming process journal of materials processing technology 209 (2009) All rights reserved by 44

FEA BASED STATIC STRUCTURAL ANALYSIS OF UNCORRODED EXPANSION BELLOW BASED ON ASME AND RCB 8 CODE

FEA BASED STATIC STRUCTURAL ANALYSIS OF UNCORRODED EXPANSION BELLOW BASED ON ASME AND RCB 8 CODE A.R.Pimple 1, Prof. G. E. Kondhalkar 2 1 PG Student, Mechanical Design Engineering, APCOER, Pune 2 Professor,