Control System Engineering Study Guide

CSE

Study

Guide

Table of Contents

1. Common Conversion Factors / Equations ... 9

1.1 Conversion Factors: ... 9 1.1.1 Common Factors: ... 9 1.1.2 Distance Factors:... 9 1.1.3 Volume Factors: ... 9 1.1.4 Mass Factors: ... 9 1.1.5 Force Factors: ... 9 1.1.6 Energy Factors: ... 9 1.1.7 Temperature Factors: ... 10 1.1.8 Pressure Factors: ... 10 1.1.9 Viscosity... 10 1.2 Equations: ... 11 1.2.1 General ... 11 1.2.1.1 Angles ... 11 1.2.2 Pressure: ... 11 1.2.3 Boyle’s Law ... 11 1.2.4 Charles’s Law ... 11 1.2.5 Gay-Lussac's Law ... 12

1.2.6 Ideal Gas Law... 12

1.2.7 Pascal’s Law... 12

1.2.8 Bernoulli’s ... 12

1.2.9 Flow: ... 12

1.2.10 Darcy’s Formula (general formula for pressure drop): ... 12

1.2.11 Velocity of Exiting Fluid: ... 13

1.2.12 Convert ACFM to SCFM:... 13

1.2.13 Joule–Thomson (Kelvin) coefficient: ... 13

1.2.14 Differentiation: ... 13 1.2.15 Integration:... 14 1.2.16 Logarithms: ... 14 1.2.17 Parabola Equation: ... 15 1.2.18 Hyperbola Equation: ... 15 1.2.19 Laplace Transforms:... 15 1.2.20 Electrical Equations: ... 16 1.2.21 Wheatstone Bridge: ... 18

1.2.22 Mass Flow – Gas Equations:... 20

1.2.23 Volume Formulas: ... 20

1.2.24 Surface Area Formulas:... 20

2. Sizing Calculations ... 21

2.1 Orifice Plate Sizing: ... 21

2.2 Venturi Sizing (liquid): ... 22

2.3 V-Cone Sizing: ... 22

2.4 Elbow Flowmeter Sizing:... 22

2.5 Pitot / Annubar Sizing:... 23

2.6 Magmeter Sizing: ... 23

2.7 Weir Sizing: ... 23

2.8 Control Valve Sizing: ... 24

2.8.1 Liquid (Turbulent Flow):... 24

2.8.2 Steam: ... 25

2.8.2.1 Saturated Steam: ... 25

2.8.3 Gas (Compressible Fluid):... 26

2.7 Pressure Relief Valve Sizing:... 27

2.7.1 Gas & Vapor Service: ... 27

2.7.2 Steam Service: ... 27

2.7.3 Liquid Service: ... 28

2.8 Rupture Disk Sizing:... 29

2.9 Pressure Regulator Sizing: ... 29

2.9.1 Steam or Gas: ... 29

2.9.1.2 Predict flow for perfect or non-perfect gas sizing applications ... 29

2.9.1.3 Predict flow for either high or low recovery valves: ... 30

2.9.1.4 Very low pressure drop:... 30

2.9.1.5 Determine critical flow capacity: ... 30

2.9.2 Liquid: ... 30

2.9.2.1 Basic liquid sizing equation:... 30

2.10 Voltage Drop: ... 31

2.10.1 DC... 31

2.10.2 AC... 31

3 Periodic Table of Elements:... 33

4 Networks ... 34 4.1 OSI Model: ... 34 4.1.1 Acronyms / Definitions... 35 4.2 Network Hardware: ... 36 4.2.1 Switches: ... 36 4.2.2 Router: ... 37 4.2.3 Hub: ... 38 4.2.4 Server: ... 39

4.2.5 RAID (Redundant Array of Independent Disks): ... 39

4.3 Network Communications: ... 44 4.3.1 RS232 ... 44 4.3.2 RS485... 45 4.3.3 RS422... 46 4.3.4 ModBus... 46 4.3.5 DH+ ... 49 4.3.6 HART: ... 50 4.3.7 AS-I:... 51 4.3.8 Profibus:... 51 4.3.9 Foundation Fieldbus: ... 52 4.3.10 ARCNET: ... 53 4.3.11 BACnet: ... 53 4.3.12 CAN Bus: ... 53 4.3.13 DeviceNet: ... 54 4.3.14 OPC ... 54

4.3.15 Common Ethernet Variations (e.g. 10Base5, etc)... 55

5. Bus Topology ... 56 Star: ... 56 Bus: ... 56 Ring: ... 56 Tree: ... 56 Mesh:... 57 6. Fiber Optics ... 58 Multimode:... 58 Singlemode: ... 58 Bandwidth:... 59 7. Copper Cabling ... 60 Twisted Pair... 60 Cable Shielding ... 60 Cable Terminators... 61 8. Cable Tray... 64 9. Wireless ... 66 10. Flow Measurement... 67

10.1 Flow Meter Evaluation Table... 67

10.2 Reynolds Number... 69

10.3 D/P Producers ... 69

10.3.1 Orifice Plate ... 69

10.3.1.1 Orifice Plate Types... 69

10.3.1.2 Orifice Tap Types... 71

10.3.2 Venturi Flowmeter ... 74

10.3.3 V-Cone Flowmeter:... 74

10.3.4 Flow Nozzle: ... 74

10.3.5 Elbow Flowmeter: ... 75

10.3.6 Pitot Tube / Annubar:... 75

10.3.7 Variable Area / Rotameter: ... 76

10.3.8 Target Meter: ... 76 10.4 Electronic Flowmeters:... 76 10.4.1 Vortex Shedder:... 76 10.4.2 Magmeter: ... 77 10.4.3 Ultrasonic Flowmeter:... 77 10.5 Mass Flowmeters: ... 78 10.5.1 Coriolis:... 78 10.5.2 Thermal Mass: ... 79 10.5.3 Hot-Wire Anemometer:... 79 10.6 Mechanical Flowmeters: ... 80 10.6.1 Turbine Meter: ... 80 10.6.2 Positive-Displacement Meter:... 80 10.6.3 Metering Pumps: ... 82

10.7 Open Channel Flow: ... 84

10.7.1 Weir: ... 84

10.7.2 Flume:... 84

11 Temperature Measurement ... 85

11.1 Temperature Sensor Comparison:... 85

11.2 Thermocouple: ... 85

11.2.1 Thermocouple Junctions: ... 85

11.2.2 Thermocouple Types:... 86

11.2.3 Thermocouple RASS Rule: ... 87

11.3 RTD: ... 87 11.3.1 RTD Standards:... 87 11.3.2 RTD Wiring Configuration:... 88 11.3.3 RTD Accuracy: ... 88 11.3.4 RTD Types: ... 89 11.4 Thermistor: ... 89 11.5 Thermowell:... 89 11.6 Infra-Red: ... 90 12 Pressure Measurement ... 93 12.1 Sensing Elements: ... 93 12.1.1 Manometers:... 93

12.1.2 C / Spiral / Helical Bourdon Tube: ... 93

12.1.3 Capsule / Diaphragm:... 94

12.1.4 LVDT:... 95

12.1.5 Optical:... 95

12.1.6 Pressure Installation Details: ... 96

12.1.6.1 Steam / Liquid Service... 96

12.1.6.2 Gas Service ... 96

12.2 Pressure Regulators: ... 97

12.2.1 Pressure Reducing Regulator: ... 97

12.2.2 Back Pressure Regulator:... 98

12.2.3 Pressure Loaded Regulator:... 98

12.2.4 Vacuum Regulators & Breakers: ... 98

12.2.5 Applying Regulators: ... 99

12.2.6 Regulator Droop: ... 99

12.2.7 Regulator w/External Control Line:... 100

12.2.8 Regulator Casing Vent: ... 100

12.2.9 Regulator Hunting:... 100

13 Level Measurement... 101

13.1 Level Device Evaluation Table:... 101

13.2.1 Zero Elevation / Suppression ... 102 13.2.2 Installation Details: ... 103 13.2.2.1 Close Coupled: ... 103 13.3 Bubbler Level: ... 104 13.3.1 Installation Details: ... 104 13.4 Capacitance Level:... 105 13.4.1 Installation Details: ... 105 13.5 Conductivity Level: ... 105 13.6 Displacer Level:... 106 13.7 Float Level:... 106 13.8 Laser Level:... 107

13.9 Level Gauge / Magnetic Flag Indicator: ... 107

13.10 Optical Level: ... 109

13.11 Magnetostrictive Level: ... 109

13.12 Nuclear Level: ... 109

13.13 Rotating Paddle: ... 110

13.14 Thermal Level Switch:... 110

13.15 Ultrasonic: ... 111

13.16 Vibratory:... 111

13.17 TDR/PDS: ... 111

14 Analytical Measurement... 113

14.1 Analyzer Selection for Specific Substances... 113

14.2 Analyzer Technologies... 115

14.2.1 Combustible Gas Analyzers: ... 115

14.2.2 Moisture / Dew Point Analyzers: ... 116

14.2.3 Conductivity Analyzers: ... 116

14.2.4 pH / ORP Analyzers: ... 117

14.2.5 Infrared Adsorption Analyzers (NIR / MIR / FTIR):... 117

14.2.6 UV Absorption Analyzers:... 118

14.2.7 Gas Chromatographic Analyzers: ... 119

14.2.8 Liquid Chromatographic Analyzers: ... 119

14.2.9 Oxygen Content (in Gas) Analyzers:... 120

14.2.10 Dissolved Oxygen Analyzers: ... 121

14.2.11 Mass Spectrometric Analyzers:... 121

14.2.12 Turbidity Analyzers:... 122

14.2.13 Load Cells: ... 122

15 Final Control Elements... 123

15.1 Control Valves ... 123

15.1.1 Selection Guide ... 123

15.1.2 Control Valve Characteristics ... 125

15.1.3 Control Valve Plug Guiding ... 125

15.1.4 Control Valve Packing ... 127

15.1.5 Control Valve Bonnets... 128

15.1.6 Control Valve Shutoff Classifications: ... 129

15.1.7 Control Valve Flashing / Cavitation: ... 129

15.1.7.1 Control Valve Noise: ... 129

15.1.8 Control Valve Types: ... 132

15.1.8.1 Sliding Stem:... 132

15.1.8.2 Rotary Valves:... 133

15.1.8.3 Special Purpose Valves:... 134

15.1.8.4 Actuators:... 135

15.2 Variable Frequency Drives / Motors:... 138

15.2.1 Types of Variable Frequency Drives (AC): ... 138

15.2.2 Types of Motors: ... 139

15.2.2.1 DC Motors... 139

15.2.2.2 AC Induction Motors ... 140

15.2.2.3 Synchronous Motors ... 142

15.2.2.4 TWO Speed Motors... 142

15.2.4 Motor NEMA Insulation Classes: ... 143

15.2.5 Motor Feeder Sizes:... 144

16 Relief Valves... 145

16.1 Selection of Pressure Relief Devices ... 145

16.2 Types of Pressure Relief Devices ... 146

16.3 Types of Rupture Disks:... 148

16.4 Pressure Relief Sizing Contingencies: ... 150

16.5 Pressure Relief Terms: ... 151

17 Control System Analysis... 153

17.1 Control System Types: ... 153

17.1.1 Programmable Logic Controller (PLC): ... 153

17.1.2 Distributed Control System (DCS):... 154

17.1.3 Supervisory Control & Data Acquisition (SCADA):... 155

17.1.4 DCS vs PLC: ... 156

17.2 Controller Actions: ... 157

17.3 S88 Batch Control: ... 160

17.3.1 Automation Pyramid: ... 160

17.3.2 Procedural Model: ... 161

17.3.3 Process Cell Level:... 161

17.3.4 Unit: ... 161

17.3.5 Equipment & Control Modules:... 162

17.3.6 Phases:... 162

17.3.7 Sequential Function Chart: ... 162

17.4 Alarm Management: ... 163

17.5 Fuzzy Logic: ... 164

17.6 Model Predictive Control: ... 165

17.7 Artificial Neural Networks (ANN) ... 166

17.8 Example Boiler Control: ... 167

17.9 Example Distillation Column Control:... 168

17.10 Example Compressor Control:... 169

17.11 Example Burner Combustion Control: ... 171

18 Loop Tuning ... 173

18.1 Description of PID Units: ... 173

18.2 Description of Processes: ... 174

18.2.1 Fast Loops (Flow & Pressure) ... 174

18.2.2 Slow Loops (Temperature) ... 174

18.2.3 Integrating (Level & Insulated Temperature)... 174

18.2.4 Noisy Loops (where PV is constantly changing) ... 174

18.3 Manual Tuning:... 175

18.3.1 Trial & Error Method (closed loop): ... 175

18.4 Tuning Map – Gain & Reset:... 176

18.5 Open Loop Testing:... 176

18.5.1 Potential Problems with Open Loop Tuning: ... 176

18.6 Closed Loop Testing: ... 176

18.6.1 Potential Problems with Closed Loop Tuning:... 176

18.6.2 Potential Problems with Closed Loop Tuning:... 176

18.7 Z-N Tuning: ... 177

18.7.1 Open Loop Method:... 177

18.7.2 Closed Loop Method: ... 177

18.8 Tuning Rules of Thumb:... 177

18.9 Statistics: ... 178

18.10 Damping Ratio: ... 179

18.11 Nyquist Stability Criterion:... 180

19 S95 (MES) ... 183 20 Enclosure Ratings ... 185 20.1 NEMA ... 185 20.2 IP ... 186 21 Hazardous Areas: ... 187 21.1 NEC Classes (500)... 187

21.2 NEC Zones (505) ... 188

21.3 FM Approvals ... 190

21.3.1 Protection Concepts ... 190

21.3.2 Ex Markings ... 192

21.3.3 Temperature Classifications ... 192

21.4 Purged & Pressurized Systems ... 193

21.4.1 Type X Purge... 193 21.4.2 Type Y Purge... 193 21.4.3 Type Z Purge... 194 21.5 Wiring Methods ... 194 21.5.1 Class I, Division I ... 194 21.5.2 Class I, Division II ... 195 21.5.3 Installation Details ... 196

21.5.3.1 Class I, Division I Lighting:... 196

21.5.3.2 Class I, Division I Power: ... 197

21.5.3.3 Class I, Division II Power & Lighting: ... 198

21.6 Hazardous Substances Used in Industry ... 199

22 Safety Instrumented Systems (SIS) ... 205

22.1 Determining PFD (Probability of Failure on Demand):... 208

23 Codes Standards & Regulations ... 209

24 System Documentation ... 211

24.1 ISA:... 211

24.1.1 Identification Letters ... 211

24.1.2 Instrument Line Symbols ... 212

24.1.3 Instrument & Function Symbols ... 213

24.1.4 Function Blocks – Function Designations ... 214

24.2 SAMA ... 216

24.3 Block Diagram: ... 217

25 Miscellaneous Tables / Information ... 219

25.1 Wet Bulb / Dry Bulb ... 219

25.2 Psychometric Chart ... 221

25.3 Mollier Steam Diagram... 222

25.3.1 How To Read Mollier Diagram ... 222

25.3.2 Properties of Saturated Steam: ... 223

25.4 Viscosity Nomograph: ... 224 25.5 RTD Resistance Table ... 225 25.5.1 100Ω Platinum in °C ... 225 25.5.2 10Ω Copper RTD in °F ... 229 25.5.3 120Ω Nickel RTD in °F ... 230 25.5.4 120Ω Nickel-Iron (Balco) RTD in °F ... 231

25.6 Copper Resistance Table:... 233

25.7 Boolean Logic Operations:... 235

25.8 Instrument Air Quality:... 236

25.9 Derivative Tables:... 236

25.10 Integral Tables: ... 237

25.11 Laplace Tables:... 240

1.

Common Conversion Factors / Equations

1.1 Conversion

Factors:

1.1.1 Common Factors: Unit = Unit Gallon 8.34 Lbs Water @ 60°F Density of Water 62.4 Lbs/Ft3 Density of Air 0.07649 Lbs/Ft3 SG Water @ 60°F 1 MW of Air 29 SG of Liquid MW of Liquid / 18.02 SG of Gas MW of Gas / 29 1.1.2 Distance Factors: Multiply By To Obtain Inch 2.54 Centimeters Centimeter 0.3937 Inch Foot 0.3048 Meter Meter 3.28083 Foot 1.1.3 Volume Factors: Multiply By To Obtain Gallon 0.13368 FT3 Gallon 0.003754 M3 Gallon 3.7853 Liter Liter 0.2642 Gallon Liter 0.03531 FT3 Liter 0.001 M3 FT3 7.481 Gallon FT3 28.3205 Liter FT3 0.028317 M3 M3 35.3147 FT3 M3 3.28083 Gallon M3 1000 Liter 1.1.4 Mass Factors: Multiply By To Obtain Pound 0.4536 Kilogram Kilogram 2.2046 Pound 1.1.5 Force Factors: Multiply By To Obtain Newton 0.22481 Pound-Force Pound-Force 4.4482 Newton 1.1.6 Energy Factors: Multiply By To Obtain BTU 778.17 Ft-Lbf BTU 1.055 KJoules BTU/Hr 0.293 Watt HP 0.7457 Kilowatt HP 2545 BTU/Hr

1.1.7 Temperature Factors:

Unit Use Equation To Obtain Unit

°F (°F – 32)*1.8 °C °F (°F + 459.67) / 1.8 °K °F (°F + 459.67) °R °C (°C × 1.8) + 32 °F °C °C + 273.15 °K °C (°C × 1.8) + 32 + 459.67 °R °K (°K × 1.8) – 459.67 °F °K °K - 273.15 °C °K °K × 1.8 °R °R °R – 459.67 °F °R (°R – 32 – 459.67) / 1.8 °C °R °R / 1.8 °K 1.1.8 Pressure Factors: Multiply By To Obtain Atm 1.01295 Bar Atm 29.9213 “Hg Atm 760 mm Hg Atm 406.86 “WC Atm 14.696 PSI Atm 1.01295 x 105 N/M2 or Pa Bar 0.9872 Atm Bar 29.54 “ Hg Bar 750.2838 mm Hg Bar 401.65 “WC “WC 0.03612 PSI “WC 0.07354 “Hg “WC 1868.1 mm Hg “WC 248.9 N/M2 or Pa “WC 0.001868 Micron or mtorr PSI 27.68 “WC PSI 2.036 “Hg PSI 51.71 mm Hg PSI 0.068046 Atm PSI 0.068948 Bar PSI 6892.7 N/M2 or Pa Micron or mtorr 0.0005353 “WC N/M2 or Pa 0.004018 “WC N/M2 or Pa 0.00014508 PSI 1.1.9 Viscosity Multiply By To Obtain cs 0.999g/cm3 cp cp 1 / 0.999g/ cm3 cs

1.2 Equations:

1.2.1 General 1.2.1.1 Angles rees x r r deg 180 360 2     57.3 180 1  radian c a hypotenuse opposite A  sin A a c opposite hypotenuse A sin 1 csc    c b hypotenuse adjacent A  cos A b c adjacent hypotenuse A cos 1 sec    A A b a adjacent opposite A cos sin tan    A A a b opposite adjacent A sin cos cot    1.2.2 Pressure:

A

F

P



F = Force applied A = Area 1.2.3 Boyle’s Law 2 2 1 1

V

P

V

P



Boyle’s law states that at constant temperature, the absolute pressure and the volume of a gas are inversely proportional. The law can also be stated in a slightly different manner, that the product of absolute pressure and volume is always constant P = Pressure in PSIA V = Volume in FT3 1.2.4 Charles’s Law 2 2 1 1

T

V

T

V 

OR

V

₁

T

₂



V

₂

T

₁

Charles’ law states that at constant pressure, the volume of a given mass of an ideal gas increases or decreases by the same factor as its temperature on the absolute temperature scale (i.e. the gas expands as the temperature increases).

T = Temperature in °R V = Volume in FT3

1.2.5 Gay-Lussac's Law 2 2 1 1 T P TP  OR P₁T₂ P₂T₁

The pressure of a fixed mass and fixed volume of a gas is directly proportional to the gas's temperature.

T = Temperature in °R P = Pressure in PSIA

1.2.6 Ideal Gas Law

(for compressibles):

RT PV 

R = Gas Constant (Value = 1544 / MW) P = Pressure in PSIA

V = Volume in FT3 T = Temperature in °R

1.2.7 Pascal’s Law

(a change in the pressure of an enclosed incompressible fluid is conveyed undiminished to every part of the fluid and to the surfaces of its container)

)

( h

g

P









ΔP = Hydrostatic pressure ρ = Mass Density g= Gravitation constant

Δh = Difference in elevation between the two points within the fluid column

1.2.8 Bernoulli’s

(states that as the speed of a moving fluid increases, the pressure within the fluid decreases): 2 2 2 1 1 1

T

V

P

T

V

P



P + ½ ρv2 _{+ ρgh = Constant} P = Pressure in PSIA ρ = Mass Density g = Gravitation constant

h = Height above reference level v = Velocity

1.2.9 Flow:

AV

Q



Q(gpm) = 3.12 A(sq in) x V(ft/sec) Make sure units match

Q = Volumetric Flow Rate

A = Cross Sectional Area of the Pipe V = Velocity of the Fluid

1.2.10 Darcy’s Formula (general formula for pressure drop):

Dg

fLV

h

2

2



h = Pressure drop in feet of fluid L = Length of pipe

V = Velocity of the fluid

g = acceleration of gravity (32.2 ft/sec2) D = Pipe ID

1.2.11 Velocity of Exiting Fluid:

gh

V



2

Q



A

2

gh

V = Velocity of the Fluid g = Gravitation constant

h = Height above reference level (in feet) A = Area of opening (in sq ft)

1.2.12 Convert ACFM to SCFM:

















520

7

.

14

a a

T

P

SCFM

ACFM

equivalent to 2 2 2 1 1 1

T

V

P

T

V

P

_

Pa = Actual pressure (PSIA)

Ts = Standard temperature (520°R) NOTE: °R =60°F+460

Ta = Actual temperature (°R)

1.2.13 Joule–Thomson (Kelvin) coefficient:

The rate of change of temperature T with respect to pressure P in a Joule–Thomson process (that is, at constant enthalpy H) is the Joule–Thomson (Kelvin) coefficient μJT.

This coefficient can be expressed in terms of the gas's volume V, its heat capacity at constant pressure Cp, and its coefficient of thermal expansion α as:





1























T

C

V

P

T

P H JT





The value of μJT is typically expressed in °C/bar (SI units: K/Pa)

In practice, the Joule–Thomson effect is achieved by allowing the gas to expand through a throttling device (usually a valve) which must be very well insulated to prevent any heat transfer to or from the gas. No external work is extracted from the gas during the

expansion (the gas must not be expanded through a turbine, for example)

In a gas expansion the pressure decreases, so the sign δP of is always negative. With that in mind, the following table explains when the Joule–Thomson effect cools or warms a real gas:

1.2.14 Differentiation:

Method to compute the rate at which a dependent output y changes with respect to the change in the independent input x. This rate of change is called the derivative of y with respect to x. In more precise language, the dependence of y upon x means that y is a function of x. If x and y are real numbers, and if the graph of y is plotted against x, the derivative measures the slope of this graph at each point. This functional relationship is often denoted y = ƒ(x), where ƒ denotes the function.

The simplest case is when y is a linear function of x, meaning that the graph of y against x is a straight line. In this case, y = ƒ(x) = m x + c, for real numbers m and c, and the slope m is given by:

x y x in change y in change m    

The idea is to compute the rate of change as the limiting value of the ratio of the differences Δy / Δx as Δx becomes infinitely small. In Leibniz's notation, such an infinitesimal change in x is denoted by dx, and the derivative of y with respect to x is written:

dx dy

Differentiation Rules:

o Constant rule: if ƒ(x) is constant, then f’ = 0

o Sum rule: for all functions ƒ and g and all real numbers a and b. (af + bg)’ = af’ +bg’

o Product rule: for all functions ƒ and g. (fg)’ = f’g + fg’

o Quotient rule: for all functions ƒ and g where g ≠ 0. 2 ' ' ' g fg g f g f _       

o

Chain rule: If f(x) = h(g(x)), then

F’(x) = h’(g(x)) * g’(x)

For Differential tables Reference Section 25.10

Example computation The derivative of 7 ) ln( ) sin( ) (x x4 x2  x ex  f is: 0 ) ( ln ) (ln ) cos( ) ( 4 ) ( ' 2 2 ) 1 4 ( _{   }   dx e d x e dx x d x dx x d x x f x x _{simplified is:} x x _{x e} e x x x x x f'( )_4 3_2 cos( 2)_1 _ln( ) 1.2.15 Integration:

Defined informally to be the net signed area of the region in the xy-plane bounded by the graph of ƒ, the x-axis, and the vertical lines x = a and x = b.

The term integral may also refer to the notion of antiderivative, a function F whose derivative is the given function ƒ.



b  

af(x)dx F(b) F(a)

For Integral tables Reference Section 25.11

1.2.16 Logarithms:

The logarithm of x to the base b is written logb(x) or, if the base is implicit, as log(x). So,

for a number x, a base b and an exponent y, If x = by, then y = logb(x)

An important feature of logarithms is that they reduce multiplication to addition, by the formula:

Log(xy) = log x + log y That is, the logarithm of the product of two numbers

o The exponential equation 43 = 64 could be written in terms of a logarithmic equation as log4(64) = 3.

o The exponential equation 5-2 = 1 / 25 can be written as the logarithmic equation log5(1/25) = –2.

The antilogarithm function antilogb(y) is the inverse function of the logarithm function logb(x); it

1.2.17 Parabola Equation:



yk



24a



xh)



1.2.18 Hyperbola Equation: 1 2 2 2 2   b y a x

1.2.19 Laplace Transforms: LaPlace Transforms:

The Laplace transform is very useful in the area of circuit analysis. It is often easier to analyze the circuit in its Laplace form, than to form differential equations.

The techniques of Laplace transform are not only used in circuit analysis, but also in o Proportional-Integral-Derivative (PID) controllers

o DC motor speed control systems o DC motor position control systems

o Second order systems of differential equations (underdamped, overdamped and critically damped)

Inverse of Laplace Transforms:

If G(s) = {g(t)}, then the inverse transform of G(s) is defined as: -1G(s) = g(t)

Some Properties of the Inverse Laplace Transform

Property 1: Linearity Property

-1

{a G1(s) + b G2(s)} = a g1(t) + b g2(t)

Property 2: Shifting Property

If -1G(s) = g(t), then -1G(s - a) = eatg(t)

Property 3

If -1G(s) = g(t), then

Property 4

If -1G(s) = g(t), then -1{e-asG(s)} = u(t - a) • g(t - a)

For Laplace tables Reference Section 25.12

1.2.20 Electrical Equations: o Ohm’s Law (DC): E = I x R  Resistors in parallel: 1 1 3 1 2 1 1 1     _{  }  N T R R R R R

o Ohm’s Law (AC): ERMS = IRMS x Z

 Inductive Reactance: XLL2fL  Inductive Capacitance: fC C XC _{ } 2 1 1  

This depicts the phasor diagrams and complex impedance expressions for RL and RC circuits in polar form. They can also be expressed in cartesian form.

o Polar to Rectangular Conversion:

Rectangular coordinates are in the form (x,y), where 'x' and 'y' are the horizontal and

vertical distances from the origin:

Polar coordinates are in the form: (r,q), where 'r' is the distance from the origin to the

point, and 'q' is the angle measured from the positive 'x' axis to the point:

To convert between polar and rectangular coordinates, make a right triangle to the

point (x,y), like shown on next page:

Polar to Rectangular:

From the diagram above, these formulas convert polar coordinates to rectangular coordinates:

x = r cosθ, y = r sinθ

So the polar point: (r,q) can be converted to rectangular coordinates like this: ( r cosθ, r sinθ )  (x, y)

Example: A point has polar coordinates: (5, 30º). Convert to rectangular coordinates. Solution: (x,y) = (5cos30º, 5sin30º) = (4.3301, 2.5)

Rectangular to Polar:

Again, from the diagram above, these formulas convert rectangular coordinates to

polar coordinates:

By the rule of Pythagoras:

r



x

2



y

2 and

x

y





tan

so 

















x

y

q

_tan

1

So the rectangular point: (x,y) can be converted to polar coordinates like shown on the next page:





























x

y

y

x

2 2

,

tan

1

 (r,

θ)

Example: A point has rectangular coordinates: (3, 4). Convert to polar coordinates. Solution: r = square root of (3² + 4²) = 5, q = tan-1(4/3) = 53.13º

so (r,q) = (5, 53.13º) 1.2.21 Wheatstone Bridge:

The wheatstone bridge is an instrument used to measure electrical resistance by means of balancing a bridge circuit. The bridge circuit contains two legs, one of which contains the unknown resistance. Variations in wheatstone bridge can be employed to measure inductance, capacitance, and impedance also

In its basic application, a dc voltage (E) is applied to the Wheatstone Bridge, and a galvanometer (G) is used to monitor the balance condition. The values of R1 and R3 are precisely known, but do not have to be identical. R2 is a calibrated variable resistance, whose current value may be read from a dial or scale.

An unknown resistor, RX, is connected as the fourth side of the circuit, and power is applied. R2 is

adjusted until the galvanometer, G, reads zero current. At this point, RX = R2 × R3/R1.

This circuit is most sensitive when all four resistors have similar resistance values. However, the circuit works quite well in any event. If R2 can be varied over a 10:1 resistance range and R1 is of a similar value, we can switch decade values of R3 into and out of the circuit according to the range of value we expect from RX. Using this method, we can accurately measure any value of

RX by moving one multiple-position switch and adjusting one precision potentiometer.

Voltage Divider Rule:

Simple linear circuit that produces an output voltage (Vout) that is a fraction of its input

voltage (Vin). Voltage division refers to the partitioning of a voltage among the

components of the divider.

A simple example of a voltage divider consists of two resistors in series or a

potentiometer. It is commonly used to create a reference voltage, and may also be used as a signal attenuator at low frequencies.

Voltage Divider Resistive Voltage Divider IN OUT V Z Z Z V    2 1 2 IN OUT V R R R V    2 1 2

A resistive divider is a special case where both impedances, Z1 and Z2, are purely resistive

Proof (Ohm’s Law) Substitute Z1 = R1 and Z2 = R2 into the

previous expression:



Z1 Z2



I VIN   2 Z I VOUT   2 1 Z Z V I IN    IN IN OUT Z Z Z V V 2 1 2   _

Low-pass RC filter:

Consider a divider consisting of a resistor and capacitor as shown above. Comparing with the general case, we see Z1 = R and Z2 is the impedance of the

capacitor, given by:

fC j C j jX Z C   2 1 1 2    XC = Capacitive Reactance

C = is the capacitance of the capacitor

j = the imaginary unit

ω = (omega) is the radian frequency of the input voltage.

This divider will then have the voltage ratio:

RC j R C j C j Z Z Z V V IN OUT







     1 1 1 1 2 1 2

The product of τ (tau) = RC is called the time constant of the circuit. The ratio then depends on frequency, in this case decreasing as frequency increases. This circuit is, in fact, a basic (first-order) lowpass filter. The ratio contains an imaginary number, and actually contains both the amplitude and phase shift information of the filter. To extract just the amplitude ratio, calculate the magnitude of the ratio, that is:





2 1 1 RC V V IN OUT    Inductive divider:

Inductive dividers split DC input according to resistive divider rules above. Inductive dividers split AC input according to inductance:

2 1 2 L L L V V_{OUT IN}   

The above equation is for ideal conditions. In the real world the amount of mutual inductance will alter the results.

Capacitive divider:

Capacitive dividers do not pass DC input. For an AC input a simple capacitive equation is:

2 1 2 C C C V V_{OUT IN}   

Capacitive dividers are limited in current by the capacitance of the elements used. This effect is opposite to resistive division and inductive division.

1.2.22 Mass Flow – Gas Equations:

Substitute Q for V/t: Substitute for Q:





























T

p

t

V

R

M

t

m

w

₃

10















T

p

R

MQ

w

₃

10

R

Mk

k

D

k

Q

₃f

10

;





Simplified:















T

p

D

k

w

w = Mass flow rate (kg/sec) Q = Volume flow rate (m3/sec) p = Absolute pressure (pascal) T = Absolute temperature (Kelvin) M = MW (g/mol)

R = Universal gas constant = 8.314 J  (K x mol) D = Flowmeter D/P (pascal)

k = Mass flow proportionality constant kf = Flowmeter proportionality constant

AV

M





M = Mass flow rate (lbs/sec) A = Cross sectional area (ft2) ρ = Fluid density (lbs/ft3

) V = Velocity (ft/sec)

Density will vary in reverse proportion to temperature, and in direct proportion to pressure. 1.2.23 Volume Formulas: o Sphere: 3 3 4 r 

o Right Circular Cone:

r

2

h

3

1

_

o Right Circular Cylinder:



r

2

h

o Pyramid:

A



h

3

1

(A = Area of base)

1.2.24 Surface Area Formulas:

o Sphere: 2

4 r

o Right Circular Cone:



r

2





rs

o Right Circular Cylinder:

2



rh



2



r

2

2. Sizing

Calculations

2.1 Orifice Plate Sizing:

Beta Ratio (β): d / D

o Liquid Orifice (LK Spink) Ratios

M F b M

h

G

ND

G

Q

S

2

*



1 2 1 2

P

P

F

F







2 2 1 1 2















F

F

P

P

2 2 1 1

V

A

V

A



Basic Equation: F M M

G

h

SD

Q



₅

_.

₆₆₇

2 QM = Maximum flow in GPM

Gb = Base S.G. [(S.G. of liquid @ 60°F (Water @ 60°F = 1)]

N = 5.667 for GPM D = Pipe ID in inches

GF = Flowing SG of liquid @ flowing temperature (see Crane A-6)

hM = Meter differential in “WC

S = Orifice ratio (reference Spink pg. 167 Table 12 for corresponding β) o Liquid Orifice (Cameron Hydraulic Book)

4 2 1 2 1 1 1 636 . 19         d d h Cd Q Where d1  d2 > 0.3 h Cd Q 19.636 12 Where d1  d2 < 0.3 Q = Flow (in GPM)

d1 = Diameter of orifice or nozzle opening (in inches) d2 = Diameter of pipe in which orifice is placed (in inches) h = Differential head at orifice (in FEET of liquid)

C = Discharge coefficient (typical values below for water)(Ref. Cameron Book pg 2-8): Sharp Edge: C = 0.61

Square Edge: C = 0.61 Well Rounded: C = 0.98

o Steam or Gas Orifice (LK Spink)

M W h S D W S 2 * 359 

Basic Equation Steam  Basic Equation Gas W m hr lbs

SD

h

S

W

/



359

2 f f f m abs abs scfh G T P h P T SD Q 218.4 2 Tf = Tabs in °R Pabs = 14.7 SGgas=MW29 W = Flow in lbs / hr

SW = Specific Weight of vapor in lbs/ft

3 _{= 1  Specific Volume}

For Steam, reference Crane A12 thru A18 (use 1/specific volume) For Gas, reference Crane A-8, column rho ‘ρ’)

hM = Meter differential in “WC

D = Pipe ID in inches

S = Orifice ratio (reference Spink pg. 167 Table 12 for corresponding β)

A rule of thumb to use in gas flow is that critical flow is reached when the downstream pipe tap registers an absolute pressure to approximately 50% or less than the upstream pipe tap.

2.2 Venturi

Sizing

(liquid):

4

1

2









CA

P

Q

throat m





m v

Q

Q



A = Area of Throat C = Coefficient of Discharge ΔP = Differential Pressure Qm = Mass Flow Rate Qv = Volumetric Flow Rate Ρ = Density

(From Cameron Hydraulic Book):

4 2 1 2 1 1 1 05 . 19         d d H d

Q for any Venturi Tube

H d

Q 19.17 12 for Venturi Tube in which d1 = 0.33d2

Q = Flow (in GPM)

d1 = Diameter of Venturi Throat (in inches)

d2 = Diameter of Main Pipe (in inches)

H = Diff. in head between upstream end and throat (in feet)

2.3 V-Cone

Sizing:

D

d

D

2



2





k

G

_C

D

C

_F 4 2 2 1

1

2

576

_

_









P

k

ACFS



₁

5

.

197



B = V-Cone Beta Ratio

K1 = Flow Constant

CG = Gravitational Constant

D = Pipe ID d = Cone Diameter

CF = Flowmeter Coefficient (use 1 if unknown)

2.4 Elbow Flowmeter Sizing:

D

r

S



₀

_.

₆₈

b w l f a n

h

G

G

F

SND

Q



2 OR 2



















f a l n w

G

SNDF

G

Q

h

S = Elbow ratio (reference Spink pg. 180 Table 14 for corresponding S) rb = Radius to the center of mass of the fluid flowing in the elbow from

the center of curvature of the bend. D = Elbow ID

N = Constant (reference Spink pg. 154 Table 4 for corresponding N) Fa = Ratio to correct for thermal expansion of elbow (reference Spink

pg. 156 Table 7) Gf = S.G. at flowing temperature

Cl = S.G. at base temperature

Hw = Operating D/P in “WC

2.5 Pitot / Annubar Sizing:

Liquid:

14

.

32

4 2 2

D

K

S

Q

P



f



ΔP = D/P in “WC Q = Flowrate in GPM. Sf = S.G. at flowing conditions

K = Flow Coefficient (use 1 if unknown) D = Pipe ID Steam or Gas:

128900

)

/

(

4 2 2



D

K

hr

lb

Q

P





or

16590

)

(

4 2 2

P

D

K

T

S

scfm

Q

P



s R



ΔP = D/P in “WC Ss = S.G. at 60°F

K = Flow Coefficient (use 1 if unknown) D = Pipe ID

ρ = Density (in lb/ft3

)

P = Static Line Pressure (in PSIA) TR = Temperature in °R

2.6 Magmeter

Sizing:

A

L

B

U

A

v

Q

e V







_



QV = Flowrate in GPM. v = Flow velocity

Ue = Induced Measuring Voltage

A = Pipe Cross-sectional Area B = Magnetic Field Strength L = Distance Between Electodes

2.7 Weir

Sizing:

(From Cameron Hydraulic Book):

Weir (Rectangular Notch):





1.5 2 . 0 33 . 13 L H H

Q   Francis Formula (Ref Cameron Book pg 2-10)

Q = FT3 of water flowing per second

L = Length of weir opening in feet (should be 4 to 8 times H) H = Head on weir in feet (to be measured 6ft back of weir opening)

Weir (V - Notch):

gH

H

L

C

Q





0

.

2667





2

Thompson Formula (Ref Cameron Book pg 2-11) Q = Flow of water in FT3/second

L = Width of notch in feet at H distance above apex H = Head of water above apex of notch (in feet)

2.8 Control Valve Sizing:

2.8.1 Liquid (Turbulent Flow):

Volumetric Flow Rate: (From Fisher Control Valve handbook)

2 1 1

P

P

G

F

N

Q

C

f P V





OR f V P

G

P

P

C

F

N

Q

1 1 2





Mass Flow Rate:



1 2



1 6

F

P

P



N

w

C

P v





OR

w



N

₆

F

P

C

V



P

₁



P

₂





₁ General Equation:

P

G

Q

C

_V





Q in GPM; G = SG

Q = Volumetric Flow Rate w = Weight or Mass Flow Rate Gf = Liquid Specific Gravity

P1 = Inlet Pressure in PSIA

P2 = Outlet Pressure in PSIA

N = Numerical Constants of Units of Measure Used (Ref. Table below) γ1 = Specific Weight (upstream conditions)

d = Nominal Valve Size D = Pipe ID

FP = Piping Geometry Factor

























₄

1

2 2

d

N

C

K

F

P V

Inlet Reducer Only:

2 2 2 1

0

.

5

1

















D

d

K

Outlet Reducer Only:

2 2 2 2

1

.

0

1

















D

d

K

When Inlet & Outlet Reducers are same size:

2 2 2 2 1

1

.

5

1



















D

d

K

K

Numerical Constants N for Liquid Flow:

Constant Units Used in Equations

N w Q P1ΔP d,D γ1 v 0.0865 m3/h kPa 0.865 m3/h Bar N1 1.00 gpm psia 0.00214 mm N2 _{890 in} 76000 m3/h mm Centistokes* N4 _{17300 gpm in Centistokes*} 2.73 kg/h kPa kg/m3 2.73 kg/h Bar kg/m3 N6 63.3 lb/h psia lb/ft3

* To convert m2/s to centistokes multiply by 106 To convert centipoise to centistokes, divide by Gf

Chocked Flow & Noise:

o Valves in flashing service can be recognized using the comparison below: When P2 < PV and ΔP(choked) < ΔP(actual) = Flashing Service

o Valves in cavitation service can be recognized using the comparison below: When P2 > PV and ΔP(choked) < ΔP(actual) = Cavitation Service

Check for critical flow by calculating the allowable ΔP



F V



L

allow

F

P

F

P

P







2 ₁

FL = Pressure Recovery Coefficient (globe ~ 0.85; ball ~ 0.6)

P1 = Inlet Pressure in PSIA

PV = Liquid Vapor Pressure in PSIA

PC = Pressure at Thermodynamic Critical Point (in PSIA)(eg Wtr = 3206)

FF = Liquid Critical Pressure Ratio Factor

C V F

P

P

F



0

.

96



0

.

28

If ΔP > ΔPallow then use this equation: V

F F L V

P

F

P

G

F

Q

C





1

2.8.2 Steam:

2.8.2.1 Saturated Steam: Basic equation W V

S

XP

Y

W

C

1

3

.

63





W



N

₁

N

₆

F

_P

C

_V

Y

xP

₁

S

_W W P V

S

xP

Y

F

N

N

W

C

1 6 1



N1 = Always = 1 for PSIA

N6 = 63.3

W = Flow Rate in lbs/hr P1 = Inlet Pressure in PSIA

Sw = Specific Weight in lbs/ft 3

(1/specific volume) (See Crane A12 thru 15 and use the inverse of specific volume)

Y = Expansion Factor T

X

x

Y

3

1





x = Pressure Drop Ratio

1

P

P

x





XT = 0.85FL 2

(FL depends on valve style: globe = 0.85; ball = 0.060)

If ΔP/P1 < 0.1 the equation above can be simplified to:



1 2



1

.

2

P

P

P

W

C

V







The flow coefficient must be corrected for superheated steam flow:







1 2



1

.

2

0007

.

0

1

P

P

P

T

W

C

V SH







2.8.3 Gas (Compressible Fluid):

For Volumetric Flow Rate Units:

S.G. of Gas Known: MW of Gas Known:

Z

T

C

x

Y

P

F

N

Q

C

g P V 1 1 7



Z

MT

x

Y

P

F

N

Q

C

P V 1 1 9



For Mass Flow Rate Units:

Specific Weight of Gas Known: MW of Gas Known:

1 1 6

F

Y

xP



N

w

C

P v



Z

T

xM

Y

P

F

N

w

C

P V 1 1 8



Aerodynamic Noise Prediction: T V

g

C

X

C

 40



Q = Volumetric Flow Rate w = Weight or Mass Flow Rate M = Molecular Weight (MW of air = Cg = SG of Gas Cg = MW  29

P1 = Inlet Pressure in PSIA

T1 = Inlet Temperature in °R

N = Numerical Constants of Units of Measure Used (Ref. Table on next page) γ1 = Specific Weight (upstream conditions)

FK = Ratio of Specific Heats (use 1 if unknown)

Z = Compressibility Factor (1.0 for pressures less than 100 psia – ideal gas) d = Nominal Valve Size

D = Pipe ID

Y = Expansion Factor X = Pressure Drop Ratio

1

P

P

X





XT = 0.85FL 2

(FL depends on valve style: globe = 0.85; ball = 0.060)

FP = Piping Geometry Factor

























₄

1

2 2

d

N

C

K

F

P V

Inlet Reducer Only:

2 2 2 1

0

.

5

1

















D

d

K

Outlet Reducer Only:

2 2 2 2

1

.

0

1

















D

d

K

When Inlet & Outlet Reducers are same size:

2 2 2 2 1

1

.

5

1



















D

d

K

K

Numerical Constants N for Gas Flow:

Constant Units Used in Equations

N w Q P1ΔP d,D γ1 T1 0.00241 mm N5 1000 in 2.73 kg/h kPa kg/m3 27.3 kg/h Bar kg/m3 N2 63.3 lb/h psia lb/ft3 4.17 m3/h kPa °K 417 m3/h Bar °K N7 1360 scfh psia °R 0.948 kg/h kPa °K 94.8 kg/h Bar °K N8 19.3 lb/h psia °R 22.5 m3/h kPa °K 2250 m3/h Bar °K N9 7320 scfh psia °R

2.7 Pressure Relief Valve Sizing:

2.7.1 Gas & Vapor Service:

10% Over-Pressure (lb/hr) ASME VIII Code Equation

) ( 1 / CCF M K CKP TZ W A b hr lb  TZ M CKAP K W  b 1 1 1

1

2

520

 

















k k

k

k

C

Combination derating factor when used in conjunction with rupture disk = 0.9

A = Minimum required orifice area, in2 W = Required relieving rate, lb/hr T = Relieving temperature, °R

Z = Compressibility factor (use 1 if unknown) M = Molecular weight

C = Gas constant = a function of (Cp / Cv) (use 315 if unknown)(see equation above) Cp = specific heat at constant pressure (consistent units)

Cv = specific heat at constant volume (consistent units) k = Specific heats ratio

K = Coefficient of discharge, (0.975)

Kb = Backpressure correction factor, (use 1.0 for atmospheric)

P1 = Relief pressure + allowable accumulation, psia

CCF = Combination De-Rating Factor (1 if not combination, otherwise 0.9)

10% Over-Pressure (scfm)

)

(

175

.

1

CKP

₁

K

CCF

TGZ

W

A

b scfm



G = S.G. of the gas or vapor

2.7.2 Steam Service: 10% Over-Pressure (lb/hr) b n SH hr lb

K

K

K

KP

W

A

1 /

5

.

51



Kn = Correction factor for dry saturated steam

= 1.0 where P1 < 1515 psia 1061 2292 . 0 1000 1906 . 0 1 1   P

P _{Where P1 > 1515 psia and ≤ 3215 psia}

K = Coefficient of Discharge (0.975)

Kb = Vapor gas correction for constant backpressure above critical pressure

Superheat Correct Factor (KSH) Table:

2.7.3 Liquid Service:

Spring Loaded: Pilot Operated: Basic Equation

 

P K K G Q A W U g   14 . 28

 

P

K

G

Q

A

U g





81

.

36

)

(

2

.

27

_{P U W} g

K

K

K

G

P

Q

A





Qg = Relieving rate in GPM

G = S.G. of liquid at flowing conditions

ΔP = Set pressure (psig) + over pressure – back pressure (PSID) Kp = Overpressure correction for liquid = 0.60

Kw = (Bellows Seal Valves Only) Variable or constant backpressure factor

KU = Correction factor due to viscosity at flowing conditions

2.8 Rupture Disk Sizing:

Vapor: Sonic Flow Subsonic Flow

ZT

M

C

V

A



₉

_.

₀₂

A W _{Volume-actual} 1 1 1 2 520         k k k k C                           k k k P P P P k k C 1 1 2 2 1 2 1 735

T

ZM

CP

V

A

W S 1

92

.

3



Volume-standard Liquid:

P

Q

A



186



Volume



P

W

A

1492



Mass Steam: 1

5

.

51 KP

W

A





















1061

2292

.

0

1000

1906

.

0

5

.

51

1 1

P

P

W

A

1

)

012

.

0

1

(

KP

X

W

A









Dry Sat ≤1500psig 1500 < Dry Sat < 3200psig Wet Steam

 = density in lbs/ft3 _{(to use SG instead of : SG x 62.37)}

C = Gas Constant (function of ratio of specific heat) Z = Compressibility Factor

A = Area in square inches W = Lbs/hour

MW = Molecular Weight

P1 = Inlet Pressure PSIA

Q = Relieving Rate (in GPM) SG = Liquid SG, where water = 1.0 T = Relieving Temperature (in °R) K = 0.62 per ASME code

k = Ratio of Specific Heats ΔX = (100 - % steam quality)

2.9 Pressure Regulator Sizing:

2.9.1 Steam or Gas:

2.9.1.1 Steam flows when P1 is < 1000 psig:

Deg

P

P

C

SIN

T

P

C

Q

SH S hr lb























































1 1 1 /

3417

00065

.

0

1

C1 = CG / CV

CS = Steam sizing coefficient CG / 20

CG = Gas sizing coefficient

TH = Degrees of superheat, °F

P1 = Inlet Pressure

Qlb/hr = Steam or vapor flow rate, pounds per hour

2.9.1.2 Predict flow for perfect or non-perfect gas sizing applications

For any vapor including steam, at any service condition when fluid density is known: Deg P P C SIN C P d Qlb hr G 1 1 1 1 / 3417 06 . 1 _        

d1 = Density of steam or vapor at inlet, lb/ft 3

2.9.1.3 Predict flow for either high or low recovery valves:

for any gas adhering to the perfect gas lows, and under any service conditions:

Universal Gas Sizing Equations

Rad

P

P

C

SIN

P

C

GT

Q

_{SCFH G}

_











_















1 1 1

64

.

59

520

OR

Deg

P

P

C

SIN

P

C

GT

Q

_{SCFH G}

_











_















1 1 1

3417

520

C1 = CG / CV

CG = Gas sizing coefficient

T = Absolute temperature of gas at inlet, °R P1 = Inlet Pressure

G = S.G. at flowing conditions QSCFH = Gas flow rate, SCFH

2.9.1.4 Very low pressure drop:

(ΔP/P1) ratios of 0.02 or less:

GT

P

P

P

C

Q

_SCFH

59

.

64

_V

520

1 1







P1 = Inlet Pressure

CV = Liquid sizing coefficient

G = S.G. at flowing conditions T = Temperature in °R

2.9.1.5 Determine critical flow capacity:

at a given inlet pressure

GT

P

C

Q

_CRIT



_{G 1}

520

CG = Gas sizing coefficient

T = Absolute temperature of gas at inlet, °R P1 = Inlet Pressure

G = S.G. at flowing conditions QCRIT = Critical flow rate, SCFH

2.9.2 Liquid:

2.9.2.1 Basic liquid sizing equation:

G

P

C

Q



_V



OR

P

G

Q

C

_V





CV = Valve sizing coefficient

P1 = Inlet Pressure

P2 = Outlet Pressure

ΔP = P1 – P2

G = S.G. at flowing conditions Q = Liquid flow rate, GPM

2.10 Voltage

Drop:

2.10.1 DC

R

I

L

V

d















 



1000

2

2.10.2 AC Single Phase: e d

I

Z

L

V















 



1000

2

(Note: Ze with PF = 100% is equal to dc Resistance)

Three Phase: e d

I

Z

L

V

_























1000

3

(Note: Ze with PF = 100% is equal to dc Resistance)

Cable Sizing: Single Phase:





















d

V

k

I

L

cm

2

Three Phase:

















_

_

_



d

V

k

I

L

cm

3

4 Networks

4.1 OSI

Model:

 Open System Interconnection

 In its most basic form, it divides network architecture into seven layers

 Layer 7 (Application Layer): This layer supports application and end-user processes. Communication partners are identified, quality of service is identified, user authentication and privacy are considered, and any constraints on data syntax are identified. Everything at this layer is application-specific. This layer provides application services for file

transfers, e-mail, and other network software services. Telnet and FTP are applications that exist entirely in the application level. Tiered application architectures are part of this layer.

 Layer 6 (Presentation Layer): This layer provides independence from differences in

data representation (e.g., encryption) by translating from application to network format, and vice versa. The presentation layer works to transform data into the form that the application layer can accept. This layer formats and encrypts data to be sent across a network, providing freedom from compatibility problems. It is sometimes called the syntax

layer.

 Layer 5 (Session Layer): This layer establishes, manages and terminates connections between applications. The session layer sets up, coordinates, and terminates

conversations, exchanges, and dialogues between the applications at each end. It deals with session and connection coordination.

 Layer 4 (Transport Layer): This layer provides transparent transfer of data between end systems, or hosts, and is responsible for end-to-end error recovery and flow control. It ensures complete data transfer. Layer 4 data units are also called packets, but when you're talking about specific protocols, like TCP, they're "segments" or "datagrams" in UDP (User Datagram Protocol). This layer is responsible for getting the entire message, so it must keep track of fragmentation, out-of-order packets, and other perils. Another way to think of layer 4 is that it provides end-to-end management of communication. Some protocols, like TCP, do a very good job of making sure the communication is reliable. Some don't really care if a few packets are lost--UDP is the prime example.  Layer 3 (Network Layer): This layer provides switching and routing technologies,

creating logical paths, known as virtual circuits, for transmitting data from node to node. Routing and forwarding are functions of this layer, as well as addressing, internetworking, error handling, congestion control and packet sequencing. If you're talking about an IP address, you're dealing with layer 3 and "packets" instead of layer 2's "frames." IP is part

of layer 3, along with some routing protocols, and ARP (Address Resolution Protocol). Everything about routing is handled in layer 3. Addressing and routing is the main goal of this layer.

 Layer 2 (Data Link Layer): At this layer, data packets are encoded and decoded into bits. It furnishes transmission protocol knowledge and management and handles errors in the physical layer, flow control and frame synchronization. The data link layer is divided into two sub layers: The Media Access Control (MAC) layer and the Logical Link Control (LLC) layer. The MAC sub layer controls how a computer on the network gains access to the data and permission to transmit it. The LLC layer controls frame synchronization, flow control and error checking. Layer two is Ethernet, among other protocols. Switches, as they're called nowadays, are bridges. They all operate at layer 2, paying attention only to MAC addresses on Ethernet networks. If you're talking about MAC address, switches, or network cards and drivers, you're in the land of layer 2. Hubs live in layer 1 land, since they are simply electronic devices with zero layer 2 knowledge.

 Layer 1 (Physical Layer): This layer conveys the bit stream - electrical impulse, light or radio signal -- through the network at the electrical and mechanical level. It provides the hardware means of sending and receiving data on a carrier, including defining cables, cards and physical aspects. Fast Ethernet, RS232, and ATM are protocols with physical layer components. Layer one is simply wiring, fiber, network cards, and anything else that is used to make two network devices communicate.

4.1.1 Acronyms / Definitions

Acronym Definition

ATM Asynchronous Transfer Mode

In electronic digital data transmission systems, the network protocol Asynchronous Transfer Mode (ATM) encodes data traffic into small fixed-sized cells. The standards for ATM were first developed in the mid 1980s. The goal was to design a single networking strategy that could transport real-time video and audio as well as image files, text and email. Two groups, the

International Telecommunications Union and the ATM Forum were involved in the creation of the standards.

ATM, as a connection-oriented technology, establishes a virtual circuit between the two endpoints before the actual data exchange begins. ATM is a cell relay, packet switching protocol which provides data link layer services that run over Layer 1 links. This differs from other technologies based on packet-switched networks (such as the Internet Protocol or Ethernet), in which variable sized packets (known as frames when referencing Layer 2) are used. ATM exposes properties from both circuit- and packet switched networking, making it suitable for wide area data networking as well as real-time media transport. It is a core protocol used in the SONET/SDH backbone of the public switched telephone network.

FTP File Transfer Protocol

File Transfer Protocol (FTP) is a network protocol used to transfer data from one computer to another through a network such as the Internet.

FTP is a file transfer protocol for exchanging and manipulating files over a TCP computer network. An FTP client may connect to an FTP server to manipulate files on that server.