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Week 3 Specific Speed of Fluid Machineries

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Specific Speed
Turbomachinery speed is described by a specific speed 𝑁𝑠 .Dimensioned versions
are used in standard commercial and industrial procedures and are just as
useful. The suction specific speed is often defined by specific speed in pump
and turbine applications.
Derivation of Specific Speed:
Specific speed can be obtained by combination of dimensionless group (πœ‹)
Derivation of Pump Specific Speed
𝑄
𝑄
πœ™=
→𝑁=
3
𝑁𝐷
πœ™ 𝐷3
𝑔𝐻
πœ“= 2 2
𝑁 𝐷
1
𝑔𝐻 2
→𝑁=(
)
πœ“ 𝐷2
π‘πœ™ = π‘πœ“
1
𝑄
𝑔𝐻 2
=
(
)
πœ™ 𝐷3
πœ“ 𝐷2
1
1 𝑄
𝑔𝐻 2 1
=
(
)
(
)
𝐷3 πœ™
πœ“ 𝐷
𝑄
(πœ™ )
𝐷2 =
1
𝑔𝐻 2
(πœ“)
1
𝐷=
1
𝑄2πœ“4
1
1
→ π‘’π‘ž. 1
πœ™ 2 (𝑔𝐻)4
Going back to π‘πœ™
1
𝑄
𝑄 3
𝑁=
→ 𝐷 = ( ) → π‘’π‘ž. 2
3
πœ™π·
π‘πœ™
π‘’π‘ž. 1 π‘Žπ‘›π‘‘ π‘’π‘ž. 2
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1
1
1
𝑄2πœ“4
𝑄3
=
1
1
πœ™ 2 (𝑔𝐻)4
1
1
𝑁 3πœ™3
3
1
(𝑔𝐻)4 πœ™ 2
𝑁=
1 βˆ™ 3
𝑄2 πœ“4
1
1
𝑁𝑄 2
=
3
(𝑔𝐻)4
πœ™2
3
πœ“4
1
πœ‹5 =
πœ™2
3
πœ“4
1
𝑄 2
(
3)
πœ‹5 = 𝑁 𝐷 3
𝑔𝐻 4
( 2 2)
𝑁 𝐷
1
3
3
𝑄2𝑁 2𝐷2
πœ‹5 =
1
3
3
𝑁 2 𝐷 2 (𝑔𝐻)4
πœ‹5 =
𝑁√𝑄
3
(𝑔𝐻)4
𝑁√𝑄
3
(𝑔𝐻)4
𝑁𝑠 =
𝑁√𝑄
3
∝
𝑁√𝑄
3
𝐻4
→ 𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑆𝑝𝑒𝑒𝑑 π‘œπ‘“ π‘ƒπ‘’π‘šπ‘
𝐻4
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Derivation of Turbine Specific Speed
1
𝑃
𝑃 3
πœ‰=
→𝑁=( 5 )
3
5
πœŒπ‘ 𝐷
𝜌𝐷 πœ‰
𝑔𝐻
πœ“= 2 2
𝑁 𝐷
1
𝑔𝐻 2
→𝑁=(
)
πœ“ 𝐷2
π‘πœ‰ = π‘πœ“
1
1
𝑃 3
𝑔𝐻 2
( 5 ) = (
)
𝜌𝐷 πœ‰
πœ“ 𝐷2
1
1
𝐷
1
𝑃 3
𝑔𝐻 2 1
=
(
)
(
)
5 πœŒπœ‰
πœ“ 𝐷
3
1
2
𝐷3
1
𝑃3 πœ“2
=
1 1 1
(𝑔𝐻)2 𝜌3 πœ‰ 3
1
3
𝑃2 πœ“4
𝐷=
3
1
→ π‘’π‘ž. 1
1
(𝑔𝐻)4 𝜌2 πœ‰ 2
Going back to π‘πœ™
1
1
𝑔𝐻 2
𝑔𝐻 2
𝑁=(
) → 𝐷=(
) → π‘’π‘ž. 2
2
πœ“π·
πœ“ 𝑁2
π‘’π‘ž. 1 π‘Žπ‘›π‘‘ π‘’π‘ž. 2
1
1
𝑔𝐻 2
(
) =
πœ“ 𝑁2
1
(𝑔𝐻)2
1
π‘πœ“ 2
1
πœ‰2
1
πœ“2
3
πœ“4
3
1
1
(𝑔𝐻)4 𝜌2 πœ‰ 2
1
=
3
𝑃2 πœ“4
3
𝑃2 πœ“ 4
3
1
1
(𝑔𝐻)4 𝜌2 πœ‰ 2
1
=
𝑁 𝑃2
1
3
1
(𝑔𝐻)2 (𝑔𝐻)4 𝜌2
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1
πœ‰2
5
πœ“4
1
=
𝑁 𝑃2
1
3
(𝑔𝐻)2 (𝑔𝐻)4
→ π·π‘–π‘šπ‘’π‘›π‘ π‘–π‘œπ‘›π‘™π‘’π‘ π‘ 
1
𝜌2
1
πœ‹6 =
πœ‰2
5
πœ“4
1
πœ‹5 =
2
𝑃
(
)
3
5
πœŒπ‘ 𝐷
5
𝑔𝐻 4
( 2 2)
𝑁 𝐷
πœ‹5 =
1
5
3
5
5
𝑃2 𝑁 2 𝐷 2
1
5
𝜌2 𝑁 2 𝐷 2 (𝑔𝐻)4
πœ‹5 =
𝑁 √𝑃
5
(𝑔𝐻)4
𝑁 √𝑃
5
(𝑔𝐻)4
𝑁𝑠 =
𝑁 √𝑃
5
∝
𝑁 √𝑃
5
𝐻4
→ 𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑆𝑝𝑒𝑒𝑑 π‘œπ‘“ π‘‡π‘’π‘Ÿπ‘π‘–π‘›π‘’
𝐻4
Were,
𝑄 𝑖𝑠 𝑖𝑛 π’ˆπ’‘π’Ž
𝑃 𝑖𝑠 𝑖𝑛 𝒉𝒑
𝐻 𝑖𝑠 𝑖𝑛 𝒇𝒕
𝑁 𝑖𝑠 𝑖𝑛 π’“π’‘π’Ž
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Speed Factor or overall head coefficient (Peripheral Coefficient)
πœ™=
√2π‘”π»π‘Ž
𝑣
𝑣 = πœ‹π·π‘
Example:
A pump delivers 0.300
π‘š3
𝑠
against a head of 200 π‘š with a rotative speed of
2000 π‘Ÿπ‘π‘š. Find the specific speed.
Solution:
𝑁𝑠 =
𝑁√𝑄
3
𝐻4
(2000 π‘Ÿπ‘π‘š)√(0.300
𝑁𝑠 =
π‘š3 1000 𝐿 1 π‘”π‘Žπ‘™
60𝑠
π‘₯
π‘₯
π‘₯
)
3
𝑠
1π‘šπ‘–π‘›
3.785
𝐿
1π‘š
3
3.28 4
(200 π‘šπ‘₯ 1π‘š )
𝑁𝑠 = 1064.03 π‘Ÿπ‘π‘š
Example:
Select the specific speed of the pump or pumps required to lift 5835 π‘”π‘π‘š
of water 350 ft through 9400 𝑓𝑑 of 2.5 𝑓𝑑 − π‘‘π‘–π‘Žπ‘šπ‘’π‘‘π‘’π‘Ÿ pipe (𝑓 = 0.022). The pump
rotative speed is to be 1700 π‘Ÿπ‘π‘š. Consider the following cases:
Single Pump
Two Pumps is Series
Two Pumps in Parallel
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Given:
𝑄 = 5835 π‘”π‘π‘š
𝐿 = 9400 𝑓𝑑
𝐷 = 2.5 𝑓𝑑
𝑓 = 0.022
𝑁 = 1700 π‘Ÿπ‘π‘š
Solution
For Single Pump
𝑁𝑠 =
𝑁√𝑄
3
𝐻4
𝐻 𝑖𝑠 π‘‘β„Žπ‘’ π‘‘π‘œπ‘‘π‘Žπ‘™ β„Žπ‘’π‘Žπ‘‘
𝐻𝑇 = β„Ž + β„Žπ‘“πΏ
β„Žπ‘“πΏ =
𝑓𝐿𝑣 2
2𝑔𝐷
For velocity 𝑣,
𝑣=
𝑄
𝐴
π‘”π‘Žπ‘™ 3.785 πΏπ‘–π‘‘π‘’π‘Ÿπ‘  1 π‘š3 (3.28 𝑓𝑑)3 1π‘šπ‘–π‘›
5835 π‘šπ‘–π‘› π‘₯
π‘₯ 1000 𝐿 π‘₯
π‘₯ 60 𝑠𝑒𝑐
1 π‘”π‘Žπ‘™
1 π‘š3
𝑣=
πœ‹
(2.5 𝑓𝑑)2
4
𝑣 = 2.65
β„Žπ‘“πΏ =
𝑓𝑑
𝑠
𝑓𝐿𝑣 2
2𝑔𝐷
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(0.022)(9400 𝑓𝑑) (2.65
β„Žπ‘“πΏ =
2 (32.2
𝑓𝑑 2
𝑠)
𝑓𝑑
) (2.5𝑓𝑑)
𝑠2
β„Žπ‘“πΏ = 9 𝑓𝑑
𝐻𝑇 = β„Ž + β„Žπ‘“πΏ
𝐻𝑇 = 350𝑓𝑑 + 9 𝑓𝑑
𝐻𝑇 = 359 𝑓𝑑
𝑁𝑠 =
(1700 π‘Ÿπ‘π‘š)√5835 π‘”π‘π‘š
3
(359 𝑓𝑑)4
𝑁𝑠 = 1574.5 π‘Ÿπ‘π‘š
For Two Pumps in Series,
𝐻𝑇 = 359 𝑓𝑑 = 𝐻𝑇1 + 𝐻𝑇2
𝐻𝑇 = 𝐻𝑇1 + 𝐻𝑇2 ; 𝐻𝑇1 = 𝐻𝑇2
π»π‘‡π‘“π‘œπ‘Ÿ π‘Ž 𝑠𝑖𝑛𝑔𝑙𝑒 π‘π‘’π‘šπ‘ =
π»π‘‡π‘“π‘œπ‘Ÿ π‘Ž 𝑠𝑖𝑛𝑔𝑙𝑒 π‘π‘’π‘šπ‘ =
𝐻𝑇
2
359 𝑓𝑑
2
π»π‘‡π‘“π‘œπ‘Ÿ π‘Ž 𝑠𝑖𝑛𝑔𝑙𝑒 π‘π‘’π‘šπ‘ = 179.5 𝑓𝑑
𝑁𝑠 =
(1700 π‘Ÿπ‘π‘š)√5835 π‘”π‘π‘š
3
(179.5 𝑓𝑑)4
𝑁𝑠 = 2648.02 π‘Ÿπ‘π‘š
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For Parallel Pumps
π‘„π‘‡π‘œπ‘‘π‘Žπ‘™ = 𝑄1 + 𝑄2 ; 𝑄1 = 𝑄2
π‘„π‘‡π‘“π‘œπ‘Ÿ π‘Ž 𝑠𝑖𝑛𝑔𝑙𝑒 π‘π‘’π‘šπ‘ =
π‘„π‘‡π‘“π‘œπ‘Ÿ π‘Ž 𝑠𝑖𝑛𝑔𝑙𝑒 π‘π‘’π‘šπ‘ =
𝑄𝑇
2
5835 π‘”π‘π‘š
2
𝑄 = 2917.5 π‘”π‘π‘š
𝑁𝑠 =
(1700 π‘Ÿπ‘π‘š)√2917.5 π‘”π‘π‘š
3
(359 𝑓𝑑)4
𝑁𝑠 = 1113.35 π‘Ÿπ‘π‘š
Example:
A double-overhung impulse-turbine installation is to develop 20,000 β„Žπ‘ at
275 π‘Ÿπ‘π‘š under a net head of 1100 𝑓𝑑. Determine the Specific Speed.
Given:
𝑃 = 20,000 β„Žπ‘
𝑁 = 275 π‘Ÿπ‘π‘š
𝐻 = 1100 𝑓𝑑
Solution:
𝑁𝑠 =
𝑁 √𝑃
5
𝐻4
𝑁𝑠 =
(275 π‘Ÿπ‘π‘š)√20,000 β„Žπ‘
5
(1100 𝑓𝑑)4
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𝑁𝑠 = 6.14 π‘Ÿπ‘π‘š
Seatwork:
A pump is driven by a two-speed motor having speeds of 1750 π‘Ÿπ‘π‘š and
1185 π‘Ÿπ‘π‘š. At 1750 π‘Ÿπ‘π‘š, the flow is 𝑄 = 45 π‘”π‘π‘š, the head is 𝐻 = 90 𝑓𝑑, and the
total efficiency is πœ‚ = 0.60. The pump impeller has a diameter of 10 π‘–π‘›π‘β„Žπ‘’π‘ .
(a) What values of 𝑄, and 𝐻 are obtained if the pump runs at 1185 rpm'?
(b) Find the specific speed of the pump (at 1750 rpm).
A small centrifugal pump is tested at 𝑁 = 2875 π‘Ÿπ‘π‘š in water. It delivers
0.15 π‘š3/𝑠 at 42 π‘š of head at its best efficiency point ( πœ‚ = 0.86).
(a) Determine the specific speed of the pump.
(b) Compute the required input power.
(c) Estimate the impeller diameter.
(d) Calculate the Reynolds Number.
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