Title | Thermo Final Equation Sheet |
---|---|
Author | Chance Jerry |
Course | Thermodynamics |
Institution | The Pennsylvania State University |
Pages | 3 |
File Size | 133.4 KB |
File Type | |
Total Downloads | 67 |
Total Views | 151 |
Final exam formula sheet, covers from work and power to thermodynamic cycles. ...
Interpolation
x −x a ) y = y a +( y b− y a)( x b− x a Work and Power
V2 W e =VI =I R= R W m =Fd W s =T ∅ ´ m =Fv ´ W W s =Tω 2
Energy
1 2 P 1 2 e mch= + v +gz = ρv + v +gz ρ 2 2 P 1 2 e mchflow =u+ + v + gz ρ 2 1 2 e mchflow =u+ ρv + v + gz 2 Efficiency
Desired Required ηtot =η1+ η2+⋯ η=
Energy and Heat Transfer
m ´ =ρ V´ = ρAV Q out =−¿ Q ¿ =+ ¿ Phase Descriptions
V T sat → SHV Pressure at Known Temperature
P> Psat → SCL P< Psat → SHV Quality
m vap m tot V −V f X= V f −V g X=
Enthalpy
h=u+ pv H=U + PV h ≈ hf @T +v f @ t ( Psys + Psat @ t ) Pressure |¿|−P sys
Patm =P¿ sys+ P atm P¿
|¿|=P
Energy Balance
∆ E=∑ E¿ −∑ E out
∆ u+ ∆ KE+∆ PE=Q ¿ +W ¿ + m´ ¿ e Ideal Gas Law
PV =mRT Pv = RT
Conservation of Mass
V´ ´ =ρ V avg A c =ρ V´ = m v ´ =V avg A c V
Isobaric (P=constant)
V1 T1
=
V2 T2
One Inlet One Exit
ρ 1 V 1 A1 = ρ 2 V 2 A 2 V 1 A1 V 2 A2 = v1 v2
Isothermal (T=cons)
P1 V 1=P 2 V 2 Isochoric (V=cons)
P1 P2 = T1 T 2
Turbines, Compressors, Pumps, and Fans
Compressibility Factor
Pv RT P Pr = Pcr Z=
Pv =ZRT T r=
T T cr
Using Ideal Gas Law
Pr ≪1 IGL T r >2∧Pr ≯1 T r >2∧Pr ≯3 T r ≈ 1∧P r ≈ 1
IGL Comp Chart Property Tables
Specific Heats
∆ u=CVavg ∆ T ∆ h =C Pavg ∆ T C p =C v =C h=u+ P ∆ v ∆ h=C Vavg ∆ T +v ∆ P Boundary Work
W B =Fds= PAds =P ∆ V Polytropic
P 2 V 2−P1 V 1
1−n n n P1 V 1 =P2 V 2 mR ( T 2−T 1) 1−n
Conservation of Energy for Steady Flow
( (
)
´ −W´ =m´out h− 1 v 2−gz Q 2 out 1 2 −m´ ¿ h− v +gz 2 ¿ V 1 A1 V 2 A 2 = m´ 1=m´2= v2 v1
)
[
1 2 2 ( v −v ) 2 1 2 1 2 2 If Q=0 :h2 −h1= ( v 1−v 2 ) 2 IF Q=0∧Ideal Gas : 1 2 2 C p (T 2−T 1) = (V 1 −V 2) 2 Q out=m ( h 1−h2 )+
]
Heat Engines (Power Plants)
W out Q out QL =1− =1− Q¿ Q¿ QH Q ¿ +W ¿=Q out −W out W output =Q ¿ −Q out ηth=
Ideal Gas
WB=
Turb :W out =+¿ Comp , P , F :W ¿=−¿ ´ W´ =m Q= ´ ( ∆ h +∆ KE + ∆ PE ) ∆ h=open sys ∆ u=closed sys
Energy Balance for Nozzles and Diffusers
Solids and Liquids
WB=
∆ U + P ∆ V =Q−W other ∆ H=Q−W other
where n ≠ 1
Isothermal Ideal Gas where n=1
v W B =mRT ln ( 2 ) v1 First Law for Closed Systems
∆ E =∆ U + ∆ KE + ∆ PE ∆ E=Q ¿ +W ¿ −Q out −W out Isochoric (V=constant)
∆ U =Q−W other Isobaric (P=constant)
∆ U =Q− P ∆ V −W other First Law Energy Balance
∆ U =Q− P ∆ V −W other
Refrigerators (Air Conditioners)
[
QL Q H Q −1= H −1 = W¿ W ¿ QL Q H =W ¿ +Q L CO PR =
]
−1
Heat Pump
[
Q Q Q CO P HP= H =1+ L = 1− L W¿ W¿ QH
−1
]
Carnot Cycle (most efficient) Four totally reversible processes
1→ 2 ¿ Isothermal heat addition (T 1 = 2→ 3 ¿ Isentropic expansion(S2 =S 3)
3 → 4 ¿ Isothermal heat rejection (T 4 → 1 ¿ Is entropic compression(S 4= W T ηth = net =1− L Q¿ TH Carnot Heat Pump
[ ] [ ]
Q T CO P HP= H = 1 − L W¿ TH Carnot Refrigerator
CO PR =
QL T H = −1 W¿ T L
−1
−1
Approximate Analysis (constant specific heats) A-1/A-2
T2 v2 +R ln T1 v1
( ) ( ( ) (
∆ s=s 2−s1 ≈C vavg ln
T P ∆ s=s 2−s1 ≈C pavg ln 2 −R ln P T1 Guess T 2 , find Cvavg ∨C pavg , calcula Exact Analysis (variable specific heats) A-17 o
o
∆ s=s 2−s1= s2 −s1 −R ln
( ) P2 P1
∑ m´ ¿ h=∑ m´out h where Q=0 Single Fluid System
Q=∑ m´out h−∑ m´ ¿ h Q B → A=m ( h A 2−h A 1 )
Throttling Valve (Decrease Pressure)
h1=h2 If ideal gas :h1=h2 ∧T 1=T 2 Mixing Chamber
m 1 h1 + m 2 h2=m 3 h3 m 1+ m2 =m3 ∑ m¿ =∑ mout Entropy 2
∆ s=s 2−s2=∫ 1
∆ s=
dQ T
Q To
Q +s T o gen ∆ s>0 irreversible ∆ s=0 isentropic ∆ s...