Solenoid Operated Piston Pump Engineering Essay

Solenoid Operated Piston Pump Engineering Essay This project is aimed at analysing and designing a solenoid operated piston pump which is capable of delivering solution (this report assumes water) at a flow rate of 1 litre/min. However, the customer usage requires the flow rate to remain between 0.9 and 1.1 litre/min at an ambient pressure of about 1 bar. The operation mode of the piston pump is described below using the diagram: OscillPistonPump Fig 1.1 Solenoid Operated Piston Pump1 The solenoid coil (4) generates an electromagnetic field by the single wave diode rectified current flowing through the coil. Each current pulse moves the piston (5) against the pressure spring (3). This movement reduces the volume in the suction chamber causing an increase in pressure (P a 1/V), which opens the valve (6) in the piston, thereby allowing the liquid to run into the pressure side. When the current acting on the solenoid pulse is off, the pressure spring pushes back the piston toward the pressure side. The increase of pressure caused by the piston movement closes the piston valve (6) and the liquid flows through the valve (7) set in the pressure connection (8) and into the pressure pipe. The piston movement also simultaneously increases the volume in the suction chamber, thereby reducing the pressure below the chamber. The low pressure in the suction chamber opens the valve (2) set in the suction connection (1), and the liquid is sucked into the pump and the cycle starts again. The piston size and the length of its displacement define the flow rate. The pump will run without damage when the liquid flow is stopped momentarily1. This design concentrated on the piston, suction chamber and pressure springs design. Although references were made to the valves and solenoid force, engineering analysis were not carried out on them. CHAPTER 2 INITIAL ENGINEERING DESIGN ANALYSIS This section considered the engineering analysis of the operation of the piston pump to achieve the require specifications. The given specifications are; Flow rate Q = 1 Lit/min Frequency F = 60 cycles/sec Ambient Pressure = 1 bar Using the above specifications, the length of stroke of the piston, which is also termed as the â€Å"Swept Volume†, can be calculated using the relation below: Q = Volumetime=Volume Ãâ€"frequency = Ï€ d2 L4 Ãâ€"f ∠´L= 4QÏ€d2f Where: Q = Flow Rate =1 lit/min= 1.667 Ãâ€"104 mm3/sec f = Frequency (cycles/sec) L = Length of stroke/Swept volume (mm) d = Diameter of piston/suction chamber (mm) The diameter was varied from 1 to 20 mm and the corresponding lengths of stroke were obtained at different frequencies of 40, 45, 50, 55 and 60 cycles/sec. The results obtained were plotted (See appendix 1). After careful look, the frequency at 40 cycle/sec, so subsequent calculations would be based on this. It was also noticed that reasonable pair of dimensions of the diameter and length occurred around the diameters 5-10mm, therefore subsequent calculations were based on this range. 2.1 LOAD ANALYSIS The load analysis was carried out on each component designed as indicated below: A. Piston: The load analysis on the piston was done by isolating the piston and analysing the forces acting it. The different forces acting on the piston are as shown below: Force on piston causing acceleration Magnetic force from solenoid coil Resultant spring force Kinematic frictional force Gravitational force Resultant hydraulic force (including assumed viscous effect) This is assuming that atomic, initial static frictional force and temperature effects are negligible. The force analyses were carried out considering three different cases under which the pump operation can undergo. The intake and ejection strokes were also analysed separately to reduce complications. The difference between the intake and ejection stroke is that, the magnetic force from the solenoid is zero during ejection, because the solenoid is off: Case I: This is when the piston pump is used horizontally, that is, it is used to pump fluid on the same datum. This means that the gravitational effect and the height difference in the hydraulic force will be zero. The relationship between the forces will therefore be: Intake stroke: Force causing motion = Force from solenoid Resultant spring force Resultant hydraulic force Frictional force Ejection stroke: Force causing motion = Resultant spring force Resultant hydraulic force Frictional force Case II: This considered the case when the pump is used to transfer fluid from a higher level to a lower level. This means that the gravitational effect will favour the direction of flow therefore reducing the force needed to drive the piston. The relationship between the forces will therefore be: Intake stroke: Force causing motion = Force from solenoid Resultant spring force Resultant hydraulic force Frictional force Gravitational force Ejection stroke: Force causing motion = Resultant spring force Resultant hydraulic force Frictional force + Gravitational force Case III: This considered the case when the piston pump is used to deliver fluid from a lower level to a higher level. The difference between this case and case II is in the gravitational effect and the datum difference in the hydraulic effect. The design load analysis was done under this circumstance because pumps are usually used for this particular purpose. Even with this design concept, the pump can still be used for other cases, but it might deliver fluid at a higher flow rate, which could still be in the boundaries of the given tolerance of the flow rate. The relationship between the forces will therefore be: Intake stroke: Force causing motion = Force from solenoid Resultant spring force Resultant hydraulic force Frictional force + Gravitational force Ejection stroke: Force causing motion = Resultant spring force Resultant hydraulic force Frictional force Gravitational force. The different forces were calculated as follows using the free body diagram of the piston shown below: Figure 2.1 Boundary conditions of intake and ejection strokes Force from solenoid coil= Fs Force on piston causing motion = Mpa Where Mp = mass of piston kg and a = acceleration of piston (mm/s2) Mp= Ï  Ãâ€"V Ï  = Density of material (Stainless steel) =8Ãâ€"10-6 (kg/mm3) V=Volume of fluid displced in one stroke mm3= Q Ãâ€"t= Qf where f=45 cycles/sec=90 strokes/sec (2 strokes=1 cycle) Mp= Ï  Ãâ€" Qf=8Ãâ€"10-6 Ãâ€" 1.667 Ãâ€"10490=1.482Ãâ€"10-3 From law of motion; v2= u2+ 2aS u = 0 ∠´a=v22S Also v= St= S Ãâ€"f v=Velocity (mm/s) and S= L=Length of stroke (mm) ∠´a=L Ãâ€"f22L= L Ãâ€" f22= L Ãâ€" 9022 The length was varied from 5 to 10 mm, and different accelerations were obtained (See appendix 2). Resultant spring force = K2∆x- K1∆x= ∆xK2- K1= ∆x∆K Where K1 and K2=Stiffness of springs 1 and 2 respectively (N/mm) ∆x=L=Stoke length (mm) Kinematic frictional force = ÃŽ ¼kÃâ€"N= ÃŽ ¼kÃâ€"Mpg Where ÃŽ ¼k=Coefficient of kinematic friction N=Normal force= Mpg g=acceleration due to gravity=9810 mm/s2 Gravitational force = Mpg Hydraulic force = Total Change in Pressure ∆P (N/mm2)Surface Area of Piston A (mm2) From Bernoulllis equation   P1Ï g+ V122g+ Z1= P2Ï g+ V222g+ Z2 ∆P= P1-P2=Ï V22-V122+ ∆ZÏ g Q= A1V1= A2V2 ,   then V2= QA2= A1V1A2 and V1= QA1 ∆P= Ï A1V1A22-V122+ ∆ZÏ g= V12Ï 2 A1A22- 1+ ∆ZÏ g ∆P= Ï  Q22A12A1A22- 1+ ∆ZÏ g Where Q= Flow rate (mm3/s) , Ï  =density of water =1Ãâ€"10-6 (kg/mm3) A1and A2=Area mm2   and V1 and V2=Velocity (m/s) ∆Z=L=Length of Stroke mm Including the discharge coefficient C = 0.98 to account for viscous effect, ∆P therefore becomes: ∆P= Ï  Q22C2A12A1A22- 1+ LÏ g ∠´ Hydraulic force = Ï  Q22C2A12A1A22- 1+ LÏ gSurface Area of Piston A mm2 = Ï  Q22C2A12A1A22- 1+ LÏ gA2- A1 The forces were algebraically added according the ejection stroke equation developed above (case III) to obtain ?K at different diameter of pistons, fixing inner diameter of Piston D2 (corresponding to A2) = 0.5, 1, 1.5, 2 and 2.5mm (See appendix 3). Force causing motion = Resultant spring force Resultant hydraulic force Frictional force Gravitational force. Mpa= L ∆K- Ï  Q22C2A12A1A22- 1+ LÏ gA2- A1- ÃŽ ¼kMpg- Mpg ∆K= 1LMpa+ ÃŽ ¼kg+g+ Ï  Q22C2A12A1A22- 1+ LÏ gA2- A1 The hydraulic effect is due to the fluid forced out from the suction chamber into the outlet. Therefore the A1 and A2 will be the area of the piston and the outlet, corresponding to diameters D1 and D2 respectively. Also the outlet diameter was assumed to be equal to the inner diameter of the piston. The results obtained for difference in stiffness ?K above, were used to obtain the force from solenoid coil Fs using the injection stroke equation above. Also different diameter of piston were used while varying the inner diameter of piston D2 (corresponding to A2) = 0.5, 1, 1.5, 2 and 2.5mm (See appendix 4). Considering the intake stroke equation for case III: Force causing motion = Force from solenoid Resultant spring force Resultant hydraulic force Frictional force + Gravitational force Mpa= Fs-L∆K- Ï  Q22C2A12A1A22- 1+ LÏ gA1- ÃŽ ¼kMpg+ Mpg Fs= Mpa+ ÃŽ ¼kg-g+L∆K+ Ï  Q22C2A12A1A22- 1+ LÏ g A1 The hydraulic effect is due to the change in pressure as the fluid passes through the piston, because of the reduction in area. Therefore the A1 and A2 will be the area of the piston outer and inner diameter, corresponding to diameters D1 and D2 respectively. B. Pressure Springs: The load analysis of the spring was also done by isolating the spring and analysing the forces acting it. Considering the ejection stroke of upper spring (spring 1), the different forces acting on the spring are as shown below: Force on piston causing acceleration Spring force Resultant hydraulic force (including assumed viscous effect) This is assuming that the frictional force on spring is negligible because the surface area contacting the wall is small. Force causing motion = Spring force + Resultant hydraulic force Mpa= LÃâ€"K1+ Ï  Q22C2A12A1A22- 1+ LÏ g A1 K1=1LMpa- Ï  Q22C2A12A1A22- 1+ LÏ g A1 ∠´K2=K1+∆K Where Force on springs Fsk=KÃâ€"Length of stroke The values of stiffness of springs 1 and 2 were calculated using the relationships above at different outer and inner diameters of the piston. The graphs were plotted to see the variations (See appendix 5 and 6). C. Inlet Valve and Spring: Considering also the inlet valves and analysing the forces acting it, the injection stroke is caused by an increase in volume of the suction chamber, causing a corresponding decrease in pressure. Therefore the different forces acting on the inlet valve are given below: Inlet spring force at compression Resultant hydraulic force (including assumed viscous effect) This is assuming that the frictional force and gravitational force on the valve is negligible because the valve is light. Resultant Pressure Change= ?P From Gas Law: P1V1= P2V2 P1 and P2 are the initial and final pressures of both the inlet and suction chamber respectively (N/mm2). The initial pressure P1 is assumed to be equal to the external pressure which is given to be equal to the atmospheric pressure Pa = 1 bar = 0.1 N/mm2. That is why fluid is not flowing because there is no pressure difference, or P1 was higher than Pa P2= P1V1V2= PaV1V2 where V2=V1+Vs and Vs=Swept Volume per stoke Vs=Flow rateFrequency in stroke/sec=1.667Ãâ€"10490 =185.22 mm2/stroke P2= P1V1V1+Vs ∆P1=Change in pressure due to swept volume= Pa-P2 ∆P1=Pa-PaV1V1+Vs=Pa V1+Vs-PaV1 V1+Vs=PaV1-PaV1+PaVsV1+Vs=PaVsV1+Vs Where V1 = VT and it is the total volume of the inlet spring area, suction chamber and the inner space of the piston. ∆P2=Pressure Change due to area changes ∆P2=Ï  Q22C2A12A1A22- 1+ LÏ g The above pressure change is the sum of the pressure changes from the inlet through suction chamber and into pistons inner diameter. This is negligible because the pressure drops as it enters the suction chamber and increases as it enters the inner diameter of piston, thereby almost cancelling out. ∆P=∆P1=PaVsVT+Vs Hydraulic force=spring force at compression ∆P1A3=PaVsA3VT+Vs= K3x3 PaVs=K3x3A3VT+ K3x3A3Vs VT=PaVs- K3x3A3VsK3x3A3 Where A3=Inlet area mm2, K3=Inlet Spring Stiffness (N/mm) and x3=Spring movement=Valve lifting mm The values the total internal volume VT was obtained at different values of the diameter of the inlet D3 (corresponding to A3). The value of the spring force K3x3 was varied from 0.01 to 0.05 N and the variations were plotted to see an appropriate one (See appendix 7). 2.2 Component Design and Selection The component design has been carried out along with the load analysis shown above. The desired dimensions for different components were then selected after a careful study and analysis of the graphs plotted. The dimensions were selected based on those that satisfy the required specifications, reasonably able to be manufactured and can be selected from the manufacturers catalogue as in the case of the springs2. Below are the component dimensions: Solenoid: Solenoid Frequency: 45cycles/sec = 90 strokes/sec Force from solenoid coil: 108.8N Length of stroke: 7.367 mm Piston: Piston outer diameter: 8 mm Piston inner diameter: 2 mm Springs: Pressure spring 1 rate = 5.771 N/mm Force on spring 1 = Rate * length of stroke = 5.771 * 7.367 = 42.515 N Pressure spring 2 rate = 14.683 N/mm Force on spring 1 = Rate * length of stroke = 14.683 * 7.367 = 108.17 N From the above calculations and estimated values of the spring rates, the most accurate spring chosen from the compression spring catalogue are (see appendix 8 and 9): Spring 1: C6609150 Wire diameter: 1.02 mm Outer Diameter: 7.62 mm Free length: 15.88 mm Rate: 5.81 N/mm Spring 2: D22110 Wire diameter: 1.25 mm Outer Diameter: 7.55mm Free length: 17mm Rate: 15.03 N/mm Inlet: Inlet spring stiffness = 0.02 N/mm Inlet spring length = 9.804 mm Inlet diameter = 1.78 mm 2.3 Stress Analysis The stress analysis was carried out on just two components as shown below. This was because these are the two components whose failure affects the pump operation most. A. Piston: The two stresses acting on the piston are normal and shear stresses which is given as. Stress (N/mm2) sij= Force (N)Area (mm2) The notation is to differentiate between the direction and plane of action, where the first digit represents the plane of action and the second digit represents the direction of force. When the notations are different, it signifies shear stress and when the notations are the same it means normal stress. The force on the piston varies as the piston goes through the cycle, therefore the different forces and principal stresses were calculated as the spring compresses and stretches. This was shown in appendix 10 and 11, but the calculations of the maximum and minimum principal stresses at the springs peak are shown below. The principal stresses were calculated because they are the cause of fracture in a component3. Considering the piston and spring 1: Fig 2.2: Stresses acting on piston from spring 1 and wall3 s11= 0 because there is no horizontal force in that direction s12= Force from SolenoidSurface area of piston= Fsp Do Lp= 108.8pÃâ€"8Ãâ€"15=0.2886 N/mm2 Where D0=Outer diameter of piston mm, Lp=Length of Piston (mm) s22= Force from spring 1Outer Area-Inner Area= K1Lp4 Do2- Di2 s22=5.771 Ãâ€"7.367p4 82- 22= 42.51547.1239=0.9022 N/mm2 s21= 0 because there is no horizontal force in that direction Considering the piston and spring 2: s11= 0 because there is no horizontal force in that direction s12= Force from SolenoidSurface area of piston= Fsp Do Lp= 108.8pÃâ€"8Ãâ€"15=0.2886 N/mm2 Where D0=Outer diameter of piston mm, Lp=Length of Piston (mm) s22= Force from spring 2Outer Area-Inner Area= K2Lp4 Do2- Di2 s22=14.638 Ãâ€"7.367p4 82- 22= 107.838147.1239=2.2884 N/mm2 s21= 0 because there is no horizontal force in that direction The total principal stress which is the usual cause of fracture was calculated using the total normal stresses from the springs and the shear stress from solenoid. Total shear stresses: Ts12=s12 from Spring 1+ s12 from Sprig 2=0.2886+0.2886= 0.5772 Total normal stresses: Ts22=s22 from Spring 1+ s22 from Sprig 2=0.9022+2.2954= 3.1976 Therefore the principal stresses: s11s22- s(s11+s22)+s2-s122=0 0Ãâ€"3.1976- s(0+3.1976)+s2-0.57722=0 s2-3.1976s-0.3331=0 Principal stresses; smin=-0.101 N/mm2, smax=3.2986 N/mm2 B. Pressure Springs: The major stress acting on the spring is shear stress acting on the coils. The force and consequentially the shear stress on the springs vary as the piston deflection (i.e. length of stroke) increases and decreases. The various forces and shear stresses were calculated and the graph plotted (see appendix 12). But the calculation of the maximum shear stress, which occurs at the full deflection is shown below4: Fig 2.4: Force acting on spring4 Shear stress tmax= 8FDWpd3 Where F=Force on spring N D=Mean outer diameter of spring mm d=diameter of spring coil mm W = Wahl Correction Factor which accounts for shear stress resulting from the springs curvature W=4C-14C-4+0.615C C=Dd Considering Spring 1 Fmax= K1Ãâ€"Length of stroke=5.771Ãâ€"7.367=42.515 N/mm2 D=7.62 mm and d=1.02 mm ?C=Dd= 7.621.02=7.4705 W=4C-14C-4+0.615C= 4Ãâ€"7.4705-14Ãâ€"7.4705-4+0.6157.4705=1.1982 tmax= 8FmaxDWpd3= 8Ãâ€"42.515 Ãâ€"7.62Ãâ€"1.1982pÃâ€"1.023=931.113 N/mm2 Considering Spring 2 Fmax= K1Ãâ€"Length of stroke=14.638Ãâ€"7.367=108.17 N/mm2 D=7.55 mm and d=1.25 mm ?C=Dd= 7.551.25=6.04 W=4C-14C-4+0.615C= 4Ãâ€"6.04-14Ãâ€"6.04-4+0.6156.04=1.2506 tmax= 8FmaxDWpd3= 8Ãâ€"108.17 Ãâ€"7.55Ãâ€"1.2506pÃâ€"1.253=1331.119 N/mm2 CHAPTER 3 INITIAL MANUFACTURING DESIGN ANALYSIS 3.1 Dimensions The dimensions of all the main components; piston, springs, cylinder and valves had been obtained from the calculations and graphical analysis made above. However, the detailed dimensions of all components namely; pump body (left and right side), cylinder and liners, piston, springs and valves are shown in the CAD drawing in appendix 13. 3.2 Tolerances Tolerance for Stroke Length The statistical tolerance of the stoke length was calculated using integral method, which is much more effective than an additional tolerance. Given the tolerance of the flow rate as  ± 0.1litres/min, the tolerance of the frequency was assumed to be  ± 5 cycles/sec under normal distribution condition. The tolerance of the stroke length was calculated as follows: Standard deviation s=Tolerance3 Ãâ€"Cp where Cp=process capability index In general manufacturing industry, a process capability index (Cp) of 1.33is considered acceptable. Therefore Cp Flow rateQ=1  ±0.1 lit/min= 1.667 Ãâ€"104  ±1.667 Ãâ€"103mm3/sec   Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚     Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚   ÏÆ'Q=3.33 Ãâ€"1033 Ãâ€"1.33=8.356 Ãâ€"102 Frequency F= 45  ±5 cycles/sec (Assuming a Normal distributed variable)   Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚     Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚   ÏÆ'f=103 Ãâ€"1.33=2.506 Therefore the flow rate and frequency could be written as; Q ~ N 1.667 Ãâ€"104 , 8.356 Ãâ€"102 mm3/sec f ~ N 45 , 2.506 cycles/sec Q = Volumetime=Volume Ãâ€"frequency = Ï€ d2 L4 Ãâ€"f ∠´L= 4QÏ€d2f Using differential tolerance: ÏÆ'∅2= i=1n∂∅∂xi2 ÏÆ'xi2 ÏÆ'L2= ∂L∂Q2ÏÆ'Q2+ ∂L∂f2ÏÆ'f2+ ∂L∂d22ÏÆ'd2 ÏÆ'L2= 4Ï€ 1ÃŽ ¼d2 Ãâ€"ÃŽ ¼f2ÏÆ'Q2+ ÃŽ ¼QÃŽ ¼d2 Ãâ€"ÃŽ ¼f22ÏÆ'f2+ ÃŽ ¼QÃŽ ¼d3 Ãâ€"ÃŽ ¼f2ÏÆ'd2 Ãâ€"2 ∠´Tolerance=ÏÆ'3 Ãâ€"Cp The standard deviations and tolerances of the stoke length were calculated using the above equations, while varying the diameter from 1 to 20 mm, and the results were plotted out (see appendix 14). Tolerance for Piston Principal Stress Assuming a normally distributed around the maximum principal stress acting on the piston, the standard deviation and the tolerance of the maximum principal stress was calculated using the load distribution obtained in appendix 11. ∠´3ÏÆ'=3.2918-0.5772=2.7146 Tolerance=CpÃâ€"3ÏÆ'=1.33Ãâ€"2.7146=3.6104 N/mm2 Upper and lower limit=3.61042= ± 1.8052 N/mm2 Tolerance for Springs Shear Stress Also assuming a normally distributed around the maximum shear stress acting on the springs, the standard deviation and the tolerance of the maximum shear stress was calculated using the load distribution obtained in appendix 12. For spring 1: ∠´3ÏÆ'=931.113-0=931.113 Tolerance=CpÃâ€"3ÏÆ'=1.33Ãâ€"931.113=1238.38 N/mm2 Upper and lower limit=1238.382= ± 619.19 N/mm2 For spring 2: ∠´3ÏÆ'=1331.119-0=1331.119 Tolerance=CpÃâ€"3ÏÆ'=1.33Ãâ€"1331.119=1770.39 N/mm2 Upper and lower limit=1770.392= ± 885.195 N/mm2 3.3 Fits The components that are fitted into the cylinder, namely; cylinder liner, piston springs 1 and 2 are almost of equal diameter. But because of the consideration of the fits and limits to give some allowance a transition fit was chosen from â€Å"Data Sheet 4500A British Standard selected ISO Fits-Hole Basis†. Since it fell in between the nominal size of 0 6 mm, the transition fit selected was H700.015 for the hole and k60-0.009 for the shaft5. 3.4 Material Selection Piston and Cylinder The piston and the cylinder are to be made of stainless steel grade 431. This is due to the prevention of fracture which could be caused by principal stress. From the maximum principal stress obtained for the piston above (3.2986 N/mm2 = 3.2986 MPa), it is sure that the material which has a yield strength of 655 MPa will be able to prevent failure. Also the other reason for choosing this material is because of its high resistance to corrosion6. Since the piston and cylinder interacts with the fluid, which increases the tendency for corrosion to occur, it is quite safe to use a highly corrosion resistance material like this. It is also very easily machined in annealed condition. The properties of the stainless steel grade 431are shown in appendix 156. Springs The springs are to be made of stainless steel grade 316. This is also due to the strength of the grade in preventing fracture, breakage and buckling of the spring due to the shear stress acting on it. From the maximum shear stress calculated above (1331.119 N/mm2 = 1.331 GPa), it is sure that this grade of stainless steel with an elastic modulus of 193 GPa will be able to withstand the compression. The material is also highly corrosion resistant and relatively easy to machine. The other properties of the stainless steel grade 316 are shown in appendix 156. Valves The valves are to be made of polytetrafluoroethylene PTFE, which is a thermoplastic. This was chosen because the material has to be light and can easily float. Also, it has very low coefficient of friction, which reduces the fluid drag force and wears on the piston and spring. 3.5 Surface Finish The surface finishing chosen for the manufacturing of the parts was to be 0.8  µm Ra. This is to reduce friction and rate of wear, because there are lots of parts moving against each other. The grinding process requires a very great accuracy because it is a relatively delicate manufacturing process. 3.6 Geometric Tolerance In obtaining the tolerance of the components, since algebraic addition of tolerances is very unrealistic and will not be efficient, the tolerances of components that fit into each other were taken from the â€Å"Data Sheet 4500A British Standard selected ISO Fits-Hole Basis†5. These are show below S/No Parts Dimensions (mm) Tolerances (mm) Drawings 1 Cylinder 11.00 + 0.015 2 Cylinder liner 8.00 0.009 3 Piston 2.00 0.006 4 Spring 1 17.00  ± 0.0015 3.7 Process Selection The manufacturing processes of the various parts of the pump will be very important aspects of the design.The parts to be manufactured are pump body, cylinder liners and piston. It will take a great deal of accuracy in carrying out the process, because the geometry of the parts is very delicate. Any wrong dimension will affect the output or operation of the pump. There are three steps in manufacturing the components mentioned above. Firstly, all the components would be manufactured by casting, which would probably not give the accurate dimensions. Then a turning/boring process can then be carried out, using a CNC or lathe machines, to achieve better dimension. The last process is the surface finish, which gives a smoother and precise dimension. It is relatively easier to manufacture the components by this method because of the intricacies of the geometry and dimensions, and also the materials chosen are easily machined. The manufacturing process of the springs would not be considered in this report because they are provided by suppliers. CHAPTER 4 DESIGN OPTIMISATION 4.1 Component Manufacturing Risk Assessment Component Name Pump Body (Left Right Side) Calculation of qm Drawing number 001 mp = 1 Ãâ€" 1.6 = 1.6 gp = 1.7 Ãâ€" 1 Ãâ€" 1 Ãâ€" 1 Ãâ€" 1.1 Ãâ€" 1.1 = 2.057 Ajustable tol= Design tolmpÃâ€"gp = + 0.0151.6 Ãâ€"2.057=+0.00455 tp = 1.7Ãâ€"1 = 1.7 sp = 1 Ãâ€" 1.3 = 1.3 qm = 1.7 Ãâ€" 1.3 = 2.21 Manufacturing variability risk, qm = 2.21 Material 431 Stainless Steel Manufacturing Process Turning/Boring Characteristic Description Holes at centre to edge Characteristic Dimension 8 mm Design Tolerance + 0.015 Surface Roughness 0.8 µm Ra Component Name Piston Calculation of qm Drawing number 005 mp = 1 Ãâ€" 1.6 = 1.6 gp = 1 Ãâ€" 1 Ãâ€" 1 Ãâ€" 1 Ãâ€" 1 Ãâ€" 1.1 = 1.1 Ajustable tol= Design tolmpÃâ€"gp = 0.0061.6 Ãâ€"1.1=0.0034 tp = 1.7Ãâ€"1 = 1.7 sp = 1 Ãâ€" 1 = 1 qm = 1.7 Ãâ€" 1 = 1.7 Manufacturing variability risk, qm =1.7 Material 431 Stainless Steel Manufacturing Process Turning/Boring Characteristic Description Holes at centre to edge Characteristic Dimension 2 mm Design Tolerance 0.002, -0.008 Surface Roughness 0.8 µm Ra  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚  Ã‚   The values of the component manufacturing risk analysis obtained above are considerably with a low risk. This shows that the processes chosen for the manufacturing of the components are acceptable. 4.2 Failure Mode and Effects Analysis (FMEA) The failure mode and effects analysis (FMEA) is an analytical technique performed to ensure that all possible failure modes of the piston pump have being identified and address. Below are the predicted failure modes of each components of the piston pump, the caused, effects and the suggested solutions: It can be seen from the FMEA above that the spring breakage has the greatest severity, but the wear on all the components has the greatest risk priority number. This is because wear would be experience by the customer over time of use which made the risk priority number very high. Therefore, while desig

INFLUENZA Essay -- essays research papers fc

Influenza, also known as â€Å"the flu,† is a virus that infects the respiratory tract. Although Influenza is not as severe as many viral infections it's almost the worst for viral infections of the respiratory tract. Typically, when someone is infected with influenza they experience fever (usually 100 ° to 103 °F in adults, but even higher in children) and causes a cough, sore throat, runny or stuffy nose, and also headaches, muscle aches, and usually extreme tiredness. There are sometimes other symptoms such as nausea, vomiting and diarrhea but usually only in rare cases with young children. One other note: The term â€Å"Stomach flu† isn’t really caused by the influenza virus. The average recovery time from the flu is about 1-2 weeks, although some patients do develop more severe complications such as pneumonia, which are capable of being life threatening. On average, influenza is associated with more than 20,000 deaths nationwide and more than 100,000 hospitalizations. These are usually from patients who develop complications and they are usually children or the elderly, although complications can develop at any age. There are three types of influenza viruses, Groups A, B, and C. Only Groups A and B are responsible for causing the epidemics of flu that occur almost every year. Influenza C is different in several ways because it causes mild to no symptoms and doesn’t cause the yearly epidemics. Scientists put out most of their effort to control influenza A and B because of their huge impact on the nation and the world. Influenza type A viruses have two proteins that determine their specific type. Take Influenza A(H1N1) the H stands for hemagglutinin and the N stands for neuraminidase. The current types of Influenza A are A(H1N1) and A(H3N2). Influenza A(H1N1), A(H3N2), and Influenza B strains are included in each year’s vaccines. Influenza A viruses are very hard to control because they undergo changes, making it harder for human’s immune systems to detect them. There are two types of changes. The first is a series of mutations that occur over time and cause a gradual change in the virus. This is called antigenic â€Å"drift.† This process allows the virus to make a more stable change yet still evade the immune system. The second type of change is an abrupt change in the hemagglutinin and/or the neuraminidase proteins. This is called antigenic "shift.† It isn’t as s... ...uenza vaccines, since the vaccine is prepared from influenza grown in eggs. The most common side effect is mild soreness at the injection site. Serious side effects such as such as life-threatening allergic reactions or Guilain-Barre syndrome are rare (fewer than 1to 2 cases per million vaccine recipients). Although the virus will continue to change and we will continue to try to defeat it, we never will. Just in the past three years two new strains have been discovered but were isolated and wiped out quickly. Maybe next time we won’t be so lucky but maybe we will. After all, it’s only the flu and humans didn’t get this far by worrying about it. Works Cited (I did it in MLA Format so be happy):P References: â€Å"Influenza A(H5N1).† Who.gov. Online. January, 1998. â€Å"Isolation of Avian Influenza A(H5N10 Viruses from Humans.† CDC.Gov. Online. Hong Kong, May-December, 1997. Larson, Erik. â€Å"The Flu Hunters.† TIME. February 23, 1998. Britannica.com. Simao, Paul. â€Å"Flu Season.† Rueters. Thursday March 22, 2001. Britannica.com. Stannard, Linda M. â€Å"Influenza Virus.† 1995. Uct.ac.za. By Grant Wade April 22, 2001 Fayetteville, Arkansas Email me at Buzbom99@aol.com if you use this paper please.

Re-Branding Sunsilk Back Into the UK Hair Market Essay

Originally launched in the Netherlands in 1956, Sunsilk provides haircare solutions in 80 countries around the globe. No matter the hair type or problem, we have the products and the know how to make your hair feel and look beautiful. Our passion in life is to help women celebrate looking beautiful everyday, anywhere. Bad hair days are history Take on life with confidence and consign bad hair days to the bin with Sunsilk. Our range of products incorporates various natural ingredients and extracts with their own specific properties; chamomile for cleansing without limpness, ginseng extract for strength and more for any and all requirements. Get great advice and tips on hair care from us too. Key facts * Number 1 in Asia, Latin America and the Middle East * Sales of more than â‚ ¬1 billion a year * Sells in 80 countries * Also sold as Elidor, Hazeline, Seda and Sedal * Recent awards: Holds the Guinness world record for the most heads of hair washed and styled in one day Sunsilk is a hair care brand, primarily aimed at women, produced by the Unilever group, which is now considered the world’s leading company in hair conditioning and the second largest in shampoo[1]. Sunsilk is Unilever’s leading hair care brand, and ranks as one of the Anglo-Dutch conglomerate’s â€Å"billion dollar brands†. Sunsilk shampoos, conditioners and other hair care products are sold in 69 countries worldwide. Sunsilk is sold under a variety of different names in markets around the world including Elidor, Seda and Sedal. The brand is strongest in Asia, Latin America and the Middle East and is the number one hair care brand in India, Brazil, Argentina, Bolivia, Bangladesh, Sri Lanka and Thailand. * 1954 – Sunsilk first launched in the UK.  * 1955 – First advertisement of Sunsilk appeared on TV. * 1964 – Launch of Sunsilk hair spray. * 1968 – Sunsilk shampoo re-packaged in PVC bottles. * 1971 – Launch of Sunsilk conditioner. * 1975 – Sunsilk became the biggest name in hair care. * 2003 – Sunsilk glossy magazine launched in Argentina. * 2008 – Social networking site Gang of Girls was introduced in India. First advertising Sunsilk began advertising in 1955 with a campaign that focused on specific hair â€Å"issues†. In the UK, the campaign focused on shiny hair. During the 1960s, a television commercial of Sunsilk featured a tune composed by John Barry, â€Å"The girl with the sun in her hair†, which proved so popular that it was subsequently released as a pop single. Sunsilk radio commercials were aired in 1969 featuring Derek Nimmo to support the new Sunsilk Herb shampoo for problem hair called â€Å"Hairy Tales†. In the early 1970s, Sunsilk was advertised with the slogan â€Å"All you need is Sunsilk†. Celebrity associations Madonna, Shakira, Marilyn Monroe, and Marian Rivera all featured in Sunsilk’s 2008 advertising campaign â€Å"Life Can’t Wait†[3] which launched with a Super Bowl XLII spot. The philosophy behind the campaign was about girls taking positive steps to gain better control of their lives â€Å"Hair On = Life On†. Actress and former Miss World Priyanka Chopra is the brand ambassador for Sunsilk in India. [4] In 2009, singer Delta Goodrem was announced as the â€Å"face of Sunsilk† in Australia. The singer and her music have since featured in several Sunsilk adverts.[5] In 2007, British girlband Girls Aloud launched a campaign for Sunsilk after securing a sponsorship deal worth over  £1,000,000.[6] Members Nicola Roberts, Nadine Coyle, Cheryl Cole, Kimberly Walsh and Sarah Harding all represented the brand, which included shooting a television commercial. Sunsilk also sponsored their following tour. Magazine In 2003, Sunsilk (Sedal) launched the first hair only glossy magazine in Argentina aiming to communicate to the professional hair industry. More than 800,000 copies are published each month. The magazine focuses on hair, fashion and beauty issues as well as showcasing hairdressers’ work. It is sold locally on news stands and distributed to hair salons. Gang of Girls In 2008, Sunsilk India launched a social networking site called Gang of Girls [7], which offered its users access to a variety of local and global experts to address various hair care needs through its content, blogs and live chat room. The site includes rich content of hair care and fashion, and users can also take part in interactive games and quizzes.In 2011, Sunsilk was listed in The Brand Trust Report published by Trust Research Advisory. Co-Creation collaboration From 2009 Sunsilk started working with a number of professional hair â€Å"experts† to develop new and improved products. Each hair â€Å"issue† variant links to an â€Å"expert† with the relevant specialist hair knowledge. For example, Dr Francesca Fusco, a New York dermatologist, co-created a â€Å"hairfall† variant for the brand. The line up also includes: Jamal Hammadi for Black Shine, Rita Hazan for Vibrant Colour, Teddy Charles for Plumped Up Volume, Thomas Taw for Damage Reconstruction, Ouidad for Defined Curls and Yuko Yamashita – inventor of Japanese hair straightening process ‘YUKO’ – for Perfect Straight. Availability Sunsilk is available in over 60 countries worldwide. However Sunsilk products seem to be no longer available in the United States. The Sunsilk website has a list of countries where their products are sold, the USA is not one of them.

Why Freedom And Equality Is An Artificial Creation Created...

The aim of this essay is to explore whether freedom and equality is founded on natural moral principle or whether it is to an extent an artificial creation created by the political institution. To an extent, I do agree that freedom and equality are based on natural moral principles because during the state of nature human beings are able to enjoy freedom and equality as these seem are the rights that humans are borned along with. Therefore, it is sufficient to say that they exist in respect of the nature and with the intention from the God. This idea is further supported by many different philosophers such as John Locke and Thomas Aquinas. However, to a certain extent, I believe that political intitution such as law is an artificial tool to help restore freedom and equality in a society so that people can still enjoy these rights. Through the theory of social contract, it clearly shows that law plays an important role in enforcing the instead of the artificial creator of these right s. To find out whether freedom and equality are rest on natural moral principles, one has to ask is what the principle means. One of the basic moral principles is to follow what the nature intends and that is known as the natural law, by making decisions in respects of the nature of things . In terms of Natural law, it is to follow what is natural for human beings and the rest of creation. Therefore, I will examine the freedom and equality during the state of nature in order to prove that theyShow MoreRelatedIn The Second Treatise Of Government, John Locke Offers1637 Words   |  7 PagesInequality, Rousseau argues that â€Å"private property is an artificial creation and the source of crimes, wars, miseries, and horrors† (Rousseau. p. 62). 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