# MASTER DEGREE PROJECT

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1 MASTER DEGREE PROJECT Finite Element Analysis of a Washing Machine Cylinder Thesis in Applied Mechanics one year Master Degree Program Performed : Spring term, 2010 Level Author Supervisor s Examiner : 30 credits : Saidulu Gundeboina : Dr. Tobias Andersson : Prof. Ulf Stigh

2 Preface & Acknowledgments This is a Master of Science thesis in the master degree program Applied Mechanics. The thesis work was carried out for Asko Appliances at the school of technology and science, University of Skövde. I would like to thank all of the involved persons at the university and especially my supervisor s Tobias Andersson and Kent Salomonsson. I would also like to thank Alexander Eklind who has been helpful with ideas and suggestions in the course of this thesis work. Also many thanks are dedicated to the examiner Prof. Ulf Stigh. I would also like to thank Peder Bengtsson, Stefan Tholin and Markus Persson at Asko Appliances for their help and support during this thesis work. Saidulu Gundeboina Skövde, April ii

3 Abstract In this thesis a finite element model of a household washing machine cylinder is built and analysed in ABAQUS The aim is to help Asko appliances in conducting similar analysis for future manufacturing of high capacity cylinders by reducing experimentation. The analysis is mainly concerned with an evenly distributed load at a constant angular velocity. The load is applied with the help of lead plates instead of clothes. The cylinder is loaded with three thin (2 mm) lead plates weighing 2 kg each. The plates with dimensional 370x240x2 mm are mounted with one strip of double sided foam tape inside the cylinder. To estimate the behavior of the cylinder the strains are measured when the cylinder is rotating at 1620 and 2200 revolution per minute (rpm). To validate the model the numerical analyses are compared with experimental results. The results clearly show that the numerical strain values fit with experimental strain values. Keywords : Washing machine, Angular velocity, Cylinder. iii

4 Table of Contents Preface & Acknowledgments.. iv Abstract. iv 1 Introduction. 1 2 Today s Washing Technology Front loading washing machine Purpose The washing machine cylinder assembly The Cylinder Front side and rear side The paddles Material properties Finite element model Pressure loads Boundary condition Numerical results Experiment results Loading of the drum Results &validation Conclusions References iv

6 It is the consumer who is the final decision maker depending on his/her needs to choose the best type of machine which suits the requirements. 4. Purpose Figure 1. Front loading washing machine. The main purpose of developing a finite element model is to perform simulation instead of experiments thus reducing the cost in manufacturing a future cylinder. In the model the weight is applied by means of three lead plates weighing 2 kg each. A plate is shown in figure 2 (a). The numerical model is validated by comparing it to experimental results. Figure 2. (a) One lead plate on the inner surface of the cylinder. (b) 2 mm lead plate. 2

7 5. The washing machine cylinder assembly The final assembly of the cylinder is shown in figure 3. The main parts included in this washing machine are the cylinder, rear side, paddles and front side. Figure 3. Assembly of a washing machine cylinder. 5.1 The cylinder Asko Appliance uses a component in their washing machine called the cylinder. The cylinder is made of a 0.6 mm thick cold rolled stainless steel sheet and is assembled by three parts by folding its edges together. It is also punched and bent to create the perforated surface of the cylinder. 5.2 Front side and rear side The front and rear components are also made out of 0.6 mm thick stainless steel sheets. These parts are fixed to the front and rear sides of the cylinder. The front side edge is joined by folding as shown in figure 4 (a). The rear side is connected to the cylinder with three bolts as shown in figure 4 (b). 3

8 Figure 4. (a) Front side (b) Rear side. 5.3 The paddles Front loading washing machine has three paddles assembled on the inner surfaces of the cylinder. The paddles help the clothes to follow the rotation of the cylinder. The bottom surface of the paddle connected to the inner surface of the cylinder by means of six heels connection as shown in figure 5 (b). The paddles are made of a Polyethylene HDPE plastic material and has a complex solid geometry. Figure 5. (a) The paddle top surface and bottom surface. (b) Connection of heels. 4

9 Stress [MPa] 5.4 Material properties The cylinder is made of stainless steel. Material data are obtained from tensile tests [2]. Depending upon these properties we can define whether the material is in the elastic region, MPa, or in the plastic region, MPa. The stress-strain relationship is shown in figure Material law steel Strain Figure 6. Stress strain curve. Material properties for cylinder, front side and rear side values are shown in table 1. S.No. Property Value 1 Modulus of elasticity 210 GPa 2 Mass density 7800 kg/m 3 3 Poisson s ratio Yield tensile strength 300 MPa Table 1. Material properties of stainless steel. Material properties for polyethylene HDPE are given in table 2. S.No. Property Value 1 Modulus of elasticity 800 MPa 2 Mass density 1400 kg/m 3 3 Poisson s ratio Table 2. Material properties of the HDPE. 5

10 Material properties of the lead plates are given in table 3. S.No. Property Value 1 Modulus of elasticity 14 GPa 2 Mass density kg/m 3 3 Poisson s ratio Table 3. Material properties of lead. 6. Finite element model The development of the FE-model starts by importing the CAD model of the washing machine cylinder assembly into Pro/Engineer 4.0 software(pro-e). The assembly only consider the cylinder, front, rear sides and peddles as shown in figure 7. The assembled Pro-E model is then exported to Abaqus using the.igs format. Figure 7. The geometric model is shown in the various views. The washing machine cylinder is meshed based on a 3D geometry model. The cylinder, front side, rear side and lead plates are meshed with 3-noded shell elements (S3) with an average size of 1.5 mm. Each shell element have 6 degree of freedom per node and 5 integration points through the thickness are used. The paddles have a complicated geometry are meshed using 3D solid 4-node elements (C3D4). To calculate the strains at positions 1, 2, 3 and 4 shown in figure 8, 4-noded shell elements (S4) are used. 6

11 Figure 8. Finite element model of assembly. The element type and various material properties and thickness assigned for the components are given table 4, 5 and 6. Element type Young s modulus : 3-node shell elements (S3) and 4-node shell elements ( S4). : 210 GPa Mass density : 7800 kg/m 3 Poisson s ratio : Plastic region : MPa, see [2] Shell thickness : 0.6 mm Table 4. Material properties of stainless steel. Element type : 3-node shell elements (S3). Young s modulus : 14 GPa Mass density : kg/m 3 Poisson s ratio : Shell thickness : 2 mm Table 5. Material properties of lead 7

12 Element type : 4-node solid elements (C3D4). Young s modulus : 800 MPa Mass density : 1400 kg/m 3 Poisson s ratio : Table 6. Material properties of HDPE. Contact conditions are applied between the cylinder - paddle and between cylinder - lead plates. The friction between the paddles (plastic), cylinder (stainless steel) and lead plates are assumed to be low and as a result the friction is set to zero. Also, tie constraints are applied between the paddle heels and the outer surface of the cylinder as shown in figure 9 (b). Figure 9. (a) The box shown represents the contact zone between the paddle and the cylinder. (b) Position of ties constraints. The lead plates are mounted on the inner surface of the cylinder by means of a double sided foam tape as shown in figure 10 (a). In the numerical model tie constraints are applied in the middle of the lead plate as shown in figure 10 (b). 8

13 Figure 10. (a) Position of the double sided foam tape. (b) Position of tie constraints. To define the stresses in the cylinder we consider a cylindrical pressure vessel with radius r and wall thickness t subjected to an internal gage pressure p. There are two kind of stresses when a pressure is subjected a cylinder. One is the longitudinal stress (or axial stress) (σl) which acts along the length of the cylinder as shown in figure (a). The other is called the hoop stress (σh) which acts along the circumference of the cylinder as shown in figure 13(b). Figure 13. (a) longitudinal stress (σl). (b) circumference stress (σh). 9

15 The angular velocity is known and it has to be converted to acceleration to find out the force and finally the pressure load. The acceleration is radius times the square of angular velocity. (3) Since the pressure load due to the rotation only acts on the cylinder walls, only the circumference of the cylinder is considered. (4) where r is the cylinder radius and h is the cylinder height. Here the total cylinder mass is 3 kg, r = m and h = m. Using equation (1) to (4) the pressure is calculated to pcylinder = 64 kpa. We also, calculate the pressure load due to the lead plates. The mathematical calculations are similar to the steps above where pressure on the lead plates is considered. The area of the plate is considered as ( 5 ) where l is the length of the lead plate and b is the width. Here the total plate mass is 2 kg, l = m and b = m. Using equation (1) to (3) and 5 the pressure is calculated to pplate = 118 kpa. 11

16 Case 2: 1620 rpm The pressure in case 2 is calculated similar to the pressure calculated in case 1. The major difference is the constant rotational velocity which is 1620 rpm in this case. By using equation (1) to (4) the pressure is calculated to pcylinder = 42 kpa on the inner surface of the cylinder. The pressure loads on the lead plates are calculated using equation (1) to (3) and 5 to be pplate = 77 kpa. Finally, calculated pressures are shown in table 5. Case 1: 2200 rpm pcylinder = 64 kpa Case 2: 1620 rpm pcylinder = 118 kpa pplate = 42 kpa pplate = 77 kpa Table 5. Applied pressure loads. 8. Boundary conditions The rear side is connected to a very stiff external component at 3 places shown in figure 12. These places are assumed to be fully constrained. Figure 12. The postion of the boundry conditions. 12

17 9. Numerical results. Two simulations are carried out using Abaqus at two different velocities where the von Mises stresses are plotted in figure 14 and 15. Figure 14. Maximum von Mises stress plots. For case 1 resulting the maximum von Misses stress is determined to 549 MPa which is in the plastic region. Figure 15. Maximum von Misses stress plots. For case 2 stress according to von Misses becomes 300 MPa. The numerical model is compared to the experiments to validate the numerical model. The numerical and experimental results are explained in detail. The cylinder undergo strains when a pressure load is applied. High strains are located at position 2 and 3 which are located in the middle of the cylinder as shown in figure 16. Lower strains are located at position 1 and 4 which are located near to the 13

18 front and the rear side of the cylinder as shown in figure 16. These strains give a clear idea of the deformation of the cylinder at high rotational speeds. Figure 16. Numerical model of the cylinder where position 1-4 indicates the position of the strain gauges. Strain results from the numerical model are shown in table 6 and 7. RPM Strain 1 [ppm] Strain 2 [ppm] Strain 3 [ppm] Strain 4 [ppm] Table 6. Average strain in one element from case 1. RPM Strain 1 [ppm] Strain 2 [ppm] Strain 3 [ppm] Strain 4 [ppm] Note: the unit ppm is the same as micro strain, micro meter/meter Table 7. Average strain in one element from case 2. 14

19 10. Experiment results Measurements with strain gauges on the outside of the drum are performed by ASKO. The strain gauges are positioned as shown in figure 17 with the measuring direction shown by the arrow. Figure 17. Strain gauges positioned at four places. 11. Loading of the drum The drum is loaded with three thin (2mm) lead plates weighing 2.0 kg each. The plates measure 370x240x2 mm and are placed on the cylinder inner surface with double sided foam tap. The tape strip is just strong enough to keep the lead plate from falling down before the spinning of the drum begins. When the drum spins the centrifugal force keeps it in place. Strain results from the experimental model are shown in table 8. RPM Strain 1 [ppm] Strain 2 [ppm] Strain 3 [ppm] Strain 4 [ppm] note: the unit ppm is the same as micro strain, micro meter/meter Table 8. Summary of the strain experiment results. 15

20 12. Results & validation The graphs plotted between the two cases results clearly show that the numerical strain values in both cases fit with experimental strains. Case 1:2200 rpm Strain Gage Analysis Experiment % Error Graph 1 16

21 Case 2 : 1620 rpm Strain Gage Analysis Experiment % Error Graph Conclusions From the above results it can be concluded that : 1. The numerical analysis results and the experimental real time results obtained at Asko Appliance have been carefully observed at two different speeds of 2200 and 1620 rpm. The graphs plotted between the two cases results clearly show that the numerical strain values in both cases fit with experimental strains. The maximum error is calculated is 17 %. 2. The analysis methodology can be applied to enhanced capacities of washing machines, reducing the experiments for each model. 17

22 14. References [1] machine works. [2] A. Eklind (2010) Structural analysis of a washer machine cylinder. Master thesis, University of Skövde, Sweden. 18

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