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The exam is closed book and closed notes.
1. Air discharge from a 2 in diameter nozzle and strikes a curved vane, which is in a vertical plane as shown in below figure. A stagnation tube connected to a water U-tube manometer is located in the free air jet. Determine the horizontal component of the force that the air jet exerts on the vane.
Neglect the weight of the air and all friction.
𝛾
𝑤𝑎𝑎𝑡𝑒𝑟: 62.4 𝑙𝑏/𝑓𝑡
3∑ 𝐹𝑥 = 𝑚̇𝑉 ⃗⃗⃗ − 𝑚̇𝑉
2⃗⃗⃗
12. The power P developed by a wind turbine is a function of turbine’s diameter D, air density ρ,
wind speed V, and rotation rate ω. Namely it can be written as P = f(D, ρ, V, ω). Viscosity effects
are negligible. Rewrite this relationship in dimensionless form.
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3. The viscous, incompressible flow between the parallel plates shown in Figure is caused by the motion of the bottom plate. Assuming pressure gradient along the 𝑥 direction is a constant and not a zero(
𝜕𝑃𝜕𝑥
≠ 0), steady, 2D, and parallel flow and using differential analysis: (a) Show that the flow is fully developed using continuity equation; (b) Find the velocity profile 𝑢(𝑦) using Navier- Stokes equations with appropriate boundary conditions; (c) Find wall shear stress at bottom wall;
and (d) Find the flow rate (hint: 𝑄 = ∫ 𝑉 ⋅ 𝑛 𝑑𝐴 and assume constant width w). Explicitly state all assumptions.
Incompressible Continuity Equation:
𝜕𝑢
𝜕𝑥+𝜕𝑣
𝜕𝑦+𝜕𝑤
𝜕𝑧 = 0
Incompressible Navier-Stokes Equations in Cartesian Coordinates:
𝜌𝑔𝑥−𝜕𝑝
𝜕𝑥+ 𝜇 (𝜕2𝑢
𝜕𝑥2+𝜕2𝑢
𝜕𝑦2+𝜕2𝑢
𝜕𝑧2) = 𝜌 (𝜕𝑢
𝜕𝑡+ 𝑢𝜕𝑢
𝜕𝑥+ 𝑣𝜕𝑢
𝜕𝑦+ 𝑤𝜕𝑢
𝜕𝑧) 𝜌𝑔𝑦−𝜕𝑝
𝜕𝑦+ 𝜇 (𝜕2𝑣
𝜕𝑥2+𝜕2𝑣
𝜕𝑦2+𝜕2𝑣
𝜕𝑧2) = 𝜌 (𝜕𝑣
𝜕𝑡+ 𝑢𝜕𝑣
𝜕𝑥+ 𝑣𝜕𝑣
𝜕𝑦+ 𝑤𝜕𝑣
𝜕𝑧) 𝜌𝑔𝑧−𝜕𝑝
𝜕𝑧+ 𝜇 (𝜕2𝑤
𝜕𝑥2+𝜕2𝑤
𝜕𝑦2+𝜕2𝑤
𝜕𝑧2) = 𝜌 (𝜕𝑤
𝜕𝑡+ 𝑢𝜕𝑤
𝜕𝑥+ 𝑣𝜕𝑤
𝜕𝑦+ 𝑤𝜕𝑤
𝜕𝑧) Shear stress (At free surface, shear stress is zero)
𝜏𝑥𝑦= 𝜏𝑦𝑥= 𝜇 (𝜕𝑢
𝜕𝑦+𝜕𝑣
𝜕𝑥) 𝜏𝑥𝑦= 𝜏𝑦𝑥= 𝜇 (𝜕𝑢
𝜕𝑦+𝜕𝑣
𝜕𝑥) 𝜏𝑥𝑦= 𝜏𝑦𝑥= 𝜇 (𝜕𝑢
𝜕𝑦+𝜕𝑣
𝜕𝑥)
---
Solution 1:
KNOWN: Inlet and outlet diameter, Outlet flow angle, manometer height.
FIND:
- Force 𝑅
𝑥that requires to hold the plate stationary ASSUMPTIONS:
Neglect weight of air Neglect friction loss
∑ 𝐹𝑥 = −𝑅
𝑥= 𝑚̇𝑉
2− 𝑚̇𝑉
1𝑅
𝑥= 𝑚̇𝑉
1− 𝑚̇𝑉
2Diameter of section
①and
②is same
∴ |𝑉
1| = |𝑉
2|
𝑉
2Direction is negative 𝑥 and has cos (30
𝑜)
∴ 𝑅
𝑥= 𝑚̇𝑉
1− 𝑚̇(−𝑉
1𝑐𝑜𝑠30
𝑜) 𝑅
𝑥= 𝑚̇𝑉
1(1 + 𝑐𝑜𝑠30
𝑜)
Calculate 𝑉
1using Bernoulli equation (Apply stagnation point and section
①) 𝑃
𝑠𝑡𝑎𝑔𝜌
𝑎𝑖𝑟+ 𝑉
𝑠𝑡𝑎𝑔22 = 𝑃
1𝜌
𝑎𝑖𝑟+ 𝑉
122
𝑃
𝑠𝑡𝑎𝑔𝜌
𝑎𝑖𝑟= 𝑃
1𝜌
𝑎𝑖𝑟+ 𝑉
122 From the manometer,
𝑃
𝑠𝑡𝑎𝑔= 𝑃
𝑎𝑡𝑚+ ℎ𝛾
𝑤𝑎𝑡𝑒𝑟𝑃
1= 𝑃
𝑎𝑡𝑚𝑃
𝑎𝑡𝑚+ ℎ𝛾
𝑤𝑎𝑡𝑒𝑟𝜌
𝑎𝑖𝑟= 𝑃
𝑎𝑡𝑚𝜌
𝑎𝑖𝑟+ 𝑉
122
∴ 𝑉
122 = ℎ𝛾
𝑤𝑎𝑡𝑒𝑟𝜌
𝑎𝑖𝑟, 𝑉
1= √2ℎ 𝛾
𝑤𝑎𝑡𝑒𝑟𝜌
𝑎𝑖𝑟(1)
(1)
(2)
(2)
(2)
---
Plug in 𝑉
1to the 𝑅
𝑥𝑅
𝑥= 𝑚̇𝑉
1(1 + 𝑐𝑜𝑠30
𝑜) = 𝜌
𝑎𝑖𝑟𝜋 4 ( 2
12 )
2
𝑉
12(1 + 𝑐𝑜𝑠30
𝑜)
𝑅
𝑥= 𝜌
𝑎𝑖𝑟𝜋 4 ( 2
12 )
2
2ℎ 𝛾
𝑤𝑎𝑡𝑒𝑟𝜌
𝑎𝑖𝑟(1 + 𝑐𝑜𝑠30
𝑜) 𝑅
𝑥= 𝜋ℎ
2 ( 2 12 )
2
𝛾
𝑤𝑎𝑡𝑒𝑟(1 + 𝑐𝑜𝑠30
𝑜)
𝑅
𝑥= 𝜋(7/12) 2 ( 2
12 )
2
62.4(1 + 𝑐𝑜𝑠30
𝑜)
𝑅
𝑥= 2.963 𝑙𝑏
(2)---
Solution 2:
ASSUMPTIONS: the problem is only a function of the above dimensional variables ANALYSIS:
P = f(D, ρ, V, ω).
𝑛 = 5
𝑃 = {𝑀𝐿2𝑇3 } , 𝐷 = {𝐿}, 𝜌 = {𝑀
𝐿3} , 𝑉 = {𝐿
𝑇} ,
𝜔
= {1 𝑇}𝑗 = 3 → 𝑘 = 𝑛 − 𝑗 = 5 − 3 = 2 The repeating variables are 𝐷, 𝜌, 𝑉
Calculate first non-dimension variable
Π0 = 𝑃𝐷𝑎𝜌𝑏𝑉𝑐
𝑢𝑛𝑖𝑡 [Π0] → {𝑀𝐿2
𝑇3 } {𝐿𝑎} {𝑀𝑏 𝐿3𝑏} {𝐿𝑐
𝑇𝑐}
Above one should be non-dimension
[𝑀] → 1 + 𝑏 = 0 [𝐿] → 2 + 𝑎 − 3𝑏 + 𝑐 = 0
[𝑇] → −3 − 𝑐 = 0
∴ 𝑏 = −1, 𝑐 = −3, 𝑎 = −2
∴ Π0= 𝑃𝐷−2𝜌−1𝑉−3= 𝑃 𝜌𝐷2𝑉3
Calculate second non-dimension variable
Π1=
𝜔
𝐷𝑎𝜌𝑏𝑉𝑐 𝑢𝑛𝑖𝑡 [Π1] → {1𝑇} {𝐿𝑎} {𝑀𝑏 𝐿3𝑏} {𝐿𝑐
𝑇𝑐} [𝑀] → 𝑏 = 0
[𝐿] → 𝑎 − 3𝑏 + 𝑐 = 0 [𝑇] → −1 − 𝑐 = 0
∴ 𝑏 = 0, 𝑐 = −1, 𝑎 = 1
∴ Π1=
𝜔
𝐷1𝜌0𝑉−1=𝜔𝐷
𝑉 As a result,Π0= 𝑓𝑛𝑐(Π1) → 𝑃
𝜌𝐷2𝑉3= 𝑓𝑛𝑐 (
𝜔𝐷
𝑉 )(4)
(1) (1)
(2) (2)
---
Solution 3:
KNOWN: Flow condition, Boundary condition FIND:
- Show that the flow is fully developed - velocity profile 𝑢(𝑦)
- Find wall shear stress at bottom wall - Find the flow rate
ASSUMPTIONS:
- steady:
𝜕𝜕𝑡
= 0 - 2D flow: 𝑤 = 0;
𝜕𝜕𝑧
= 0 - Parallel flow: 𝑣 = 𝑤 = 0 -
𝜕𝑝𝜕𝑥
= constant
ANALYSIS:
(a) Continuity
𝜕𝑢
𝜕𝑥 + 𝜕𝑣
𝜕𝑦 + 𝜕𝑤
𝜕𝑧 = 0
𝜕𝑢
𝜕𝑥 + 0 + 0 = 0 → 𝜕𝑢
𝜕𝑥 = 0 → 𝑓𝑢𝑙𝑙𝑦 𝑑𝑒𝑣𝑒𝑙𝑜𝑝𝑒𝑑
(b) x-momentum equation 𝜌 ( 𝜕𝑢
𝜕𝑡 + 𝑢 𝜕𝑢
𝜕𝑥 + 𝑣 𝜕𝑢
𝜕𝑦 + 𝑤 𝜕𝑢
𝜕𝑧 ) = 𝜌𝑔
𝑥− 𝜕𝑝
𝜕𝑥 + 𝜇 ( 𝜕
2𝑢
𝜕𝑥
2+ 𝜕
2𝑢
𝜕𝑦
2+ 𝜕
2𝑢
𝜕𝑧
2)
0 = − 𝜕𝑃
𝜕𝑥 + 𝜇 𝜕
2𝑢
𝜕𝑦
2𝜕
2𝑢
𝜕𝑦
2= 1 𝜇
𝜕𝑝
𝜕𝑥
Integrate twice
𝑢(𝑦) = 1 2𝜇
𝜕𝑝
𝜕𝑥 𝑦
2+ 𝑐
1𝑦 + 𝑐
2 (1)(1)
(1.5)
(1.5)
---
Apply boundary conditions
𝑦 = 0 → 𝑢 = 𝑈 → 𝑐
2= 𝑈
𝑦 = 𝑏 → 𝜏 = 0 → 𝜇 ( 𝜕𝑢
𝜕𝑦 ) = 0 → 𝜇 ( 1 𝜇 ( 𝜕𝑝
𝜕𝑥 ) 𝑏 + 𝑐
1) = 0
𝑐
1= − 1 𝜇 ( 𝜕𝑝
𝜕𝑥 ) 𝑏
Therefore,
𝑢(𝑦) = 1 2𝜇
𝜕𝑝
𝜕𝑥 𝑦
2− 𝑏 𝜇 ( 𝜕𝑝
𝜕𝑥 ) 𝑦 + 𝑈
𝑢(𝑦) = 1 2𝜇 ( 𝜕𝑝
𝜕𝑥 ) (𝑦
2− 2𝑏𝑦) + 𝑈
(c) Shear stress at bottom wall 𝜏 = 𝜇 𝑑𝑢
𝑑𝑦 = 𝜇 { 1 2𝜇 ( 𝜕𝑝
𝜕𝑥 ) (2𝑦 − 2𝑏)} = ( 𝜕𝑝
𝜕𝑥 ) (𝑦 − 𝑏)
𝜏
𝑤𝑎𝑙𝑙= 𝜏(0) = −𝑏 ( 𝜕𝑝
𝜕𝑥 )
(d) Flow rate
𝑄 = ∫ 𝑉 ⋅ 𝑛 𝑑𝐴 = 𝑤 ∫ 𝑢(𝑦)𝑑𝑦
𝑏 0
= 𝑤 2𝜇 ( 𝜕𝑝
𝜕𝑥 ) ( 1
3 𝑦
3− 𝑏𝑦
2)
0 𝑏
+ 𝑤𝑈(𝑦)
0𝑏𝑄 = 𝑤 2𝜇 ( 𝜕𝑝
𝜕𝑥 ) ( 1
3 𝑏
3− 𝑏
3) + 𝑤𝑈𝑏 = − 𝑤𝑏
33𝜇 ( 𝜕𝑝
𝜕𝑥 ) + 𝑤𝑈𝑏
(2)
(1.5)
(1.5)