This document contains a formula book for fluid mechanics and machinery prepared by three professors at R.M.K College of Engineering and Technology. It includes formulas for fluid properties like density, specific volume, specific weight, viscosity, and surface tension. Formulas are also provided for continuity equation, Bernoulli's equation, and coefficient of discharge. The book is intended as a reference for students in the Department of Mechanical Engineering taking the course CE6451 - Fluid Mechanics and Machinery.
Every material has certain strength, expressed in terms of stress or strain, beyond which it
fractures or fails to carry the load. Failure Criterion: A criterion used to hypothesize the failure.
Failure Theory: A Theory behind a failure criterion.
Need of Failure Theories:
(a) To design structural components and calculate margin of safety.
(b) To guide in materials development.
(c) To determine weak and strong directions.
Every material has certain strength, expressed in terms of stress or strain, beyond which it
fractures or fails to carry the load. Failure Criterion: A criterion used to hypothesize the failure.
Failure Theory: A Theory behind a failure criterion.
Need of Failure Theories:
(a) To design structural components and calculate margin of safety.
(b) To guide in materials development.
(c) To determine weak and strong directions.
The various forces acts on the reciprocating parts of an engine.
The resultant of all the forces acting on the body of the engine due to inertia forces only is known as unbalanced force or shaking force.
Springs - DESIGN OF MACHINE ELEMENTS-IIDr. L K Bhagi
Introduction to springs, Types and terminology of springs, Stress and deflection equations, Series and parallel connection, Design of helical springs, Design against fluctuating load, Concentric springs, Helical torsion springs, Spiral springs, Multi-leaf springs, Optimum design of helical spring
This presentation gives the information about 'vibration measuring instruments' covering syllabus of Unit-5 of Theory of vibrations or mechanical vibrations for BE course under VTU, Belgaum. This presentation is prepared by Hareesha N G, Asst. Prof, Dept of Aerospace, DSCE, B'Lore-78.
single degree of freedom systems forced vibrations KESHAV
SDOF, Forced vibration
includes following content
Forced vibrations of longitudinal and torsional systems,
Frequency Response to harmonic excitation,
excitation due to rotating and reciprocating unbalance,
base excitation, magnification factor,
Force and Motion transmissibility,
Quality Factor.
Half power bandwidth method,
Critical speed of shaft having single rotor of undamped systems.
,friction pipe ,friction loss along a pipe ,pipe ,along a ,loss along ,loss along a ,friction loss ,friction loss along a ,loss along a pipe ,along a pipe ,friction loss alon ,friction loss along a p ,loss along a pip
This document gives the class notes of Unit 2 stresses in composite sections. Subject: Mechanics of materials.
Syllabus contest is as per VTU, Belagavi, India.
Notes Compiled By: Hareesha N Gowda, Assistant Professor, DSCE, Bengaluru-78.
The various forces acts on the reciprocating parts of an engine.
The resultant of all the forces acting on the body of the engine due to inertia forces only is known as unbalanced force or shaking force.
Springs - DESIGN OF MACHINE ELEMENTS-IIDr. L K Bhagi
Introduction to springs, Types and terminology of springs, Stress and deflection equations, Series and parallel connection, Design of helical springs, Design against fluctuating load, Concentric springs, Helical torsion springs, Spiral springs, Multi-leaf springs, Optimum design of helical spring
This presentation gives the information about 'vibration measuring instruments' covering syllabus of Unit-5 of Theory of vibrations or mechanical vibrations for BE course under VTU, Belgaum. This presentation is prepared by Hareesha N G, Asst. Prof, Dept of Aerospace, DSCE, B'Lore-78.
single degree of freedom systems forced vibrations KESHAV
SDOF, Forced vibration
includes following content
Forced vibrations of longitudinal and torsional systems,
Frequency Response to harmonic excitation,
excitation due to rotating and reciprocating unbalance,
base excitation, magnification factor,
Force and Motion transmissibility,
Quality Factor.
Half power bandwidth method,
Critical speed of shaft having single rotor of undamped systems.
,friction pipe ,friction loss along a pipe ,pipe ,along a ,loss along ,loss along a ,friction loss ,friction loss along a ,loss along a pipe ,along a pipe ,friction loss alon ,friction loss along a p ,loss along a pip
This document gives the class notes of Unit 2 stresses in composite sections. Subject: Mechanics of materials.
Syllabus contest is as per VTU, Belagavi, India.
Notes Compiled By: Hareesha N Gowda, Assistant Professor, DSCE, Bengaluru-78.
NUMERICAL SIMULATION AND ENHANCEMENT OF HEAT TRANSFER USING CUO/WATER NANO-FL...IAEME Publication
Heat transfer enhancement using nano-fluids has gained significant attention over the past few years. Nano-fluids are potentially applicable as alternative coolants for many areas such as electronics, automotive, air conditioning, power generation and nuclear applications. Several published researches have concluded that the use of nano-fluid effectively improved the fluid thermal conductivity which consequently enhanced heat transfer performance.
The Micro-Heat exchangers are heat exchangers in which fluids flows in very confined area such as tubes or small cavities whose dimensions are below 1mm in size. They also go by others name as Micro scale heat exchangers, micro channel heat exchangers, micro structure heat exchanger. They comprises of numerous parallel but relatively short micro channels for the passage of fluid flow. Their ability to handle high heat flux densities to control precise chemical reactions or cool the high-end computer processors is becoming more and more relevant to their efficient and safe operation.The Micro-Heat exchangers are heat exchangers in which fluids flows in very confined area such as tubes or small cavities whose dimensions are below 1mm in size. They also go by others name as Micro scale heat exchangers, micro channel heat exchangers, micro structure heat exchanger. They comprises of numerous parallel but relatively short micro channels for the passage of fluid flow. Their ability to handle high heat flux densities to control precise chemical reactions or cool the high-end computer processors is becoming more and more relevant to their efficient and safe operation.
Pressure distribution around a circular cylinder bodies | Fluid Laboratory Saif al-din ali
SAIF ALDIN ALI MADIN
سيف الدين علي ماضي
S96aif@gmail.com
A cylinder in a closed circuit wind tunnel will be experimented upon
to gather the pressure distribution acting on it
Laminar flow is defined when a fluid flows in parallel layers, with no
disruption between the layers. In comparison to this Turbulent flow
has a much more disorganized pattern, it is characterized by
mixing of the fluid by eddies of varying size within the flow.
The Reynolds number (Re), gives the measure for laminar and
turbulent flows. Laminar flow takes place when Reynolds number
is lower than 104, and for Turbulent flow the Re must be greater
than 3Ã-105.
The pressure is measured using the manometer, and then
therefore the pressure at the tapping must be the same as the
pressure head.
The cylinder being experimented on is placed in the wind tunnel.
The pressure upstream of the cylinder is sensed by a taping on the
tunnel wall and is connected to one of the tubes.
Pressure distribution along convergent- divergent NozzleSaif al-din ali
SAIF ALDIN ALI MADIN
سيف الدين علي ماضي
S96aif@gmail.com
This aim of this practical was to investigate compressible flow in a
convergent-divergent nozzle. Different flow patterns that influence
the results of the investigation are also explored. The different
pressure distributions that occur at varying lengths in the nozzle
were also recorded and analyzed
Flow analysis of centrifugal pump using CFX solver and remedies for cavitatio...IJERA Editor
In this scholarly thesis pertinent to the working of centrifugal pump, a CFD solver namely CFX is employed in order to simulate fluid flow characteristics with well-defined constraints and boundary conditions defining the problem. Stringent solid model is meticulously prepared encompassing the present day usage and constructional features of a centrifugal pump and is constrained with various boundary conditions having fixed domain in order to evaluate plots and results. To spearhead and facilitate this analysis program a numerical approximation tool with high degree of convergence rate called ANSYS 15.0 software is used. The ASNYS software avoids tedious calculations presumably impending in the design procedure and uses ultimate numerical tool to approximate the solution of the partial differential equations associated with continuity, momentum and energy phases of a flow problem in a 3-D model. This exquisite feature of ANSYS enables designer to optimize the design procedure in an iterative manner based on the final plots of post-processing phase. In addition, the scholarly writing also constitutes the appraisal of the most debilitating and painstaking problem retarding the efficiency of the centrifugal pump known as cavitation. Possible remedies for overcoming this problem will be indirectly inferred from the various plots and figures derived from the post-processing phase of the design process.
Aerodynamic Study about an Automotive Vehicle with Capacity for Only One Occu...IJERA Editor
The presented study describes the aerodynamic behavior of a compact, single occupant, automotive vehicle. To
optimize the aerodynamic characteristics of this vehicle, a flow dynamics study was conducted using a virtual
model. The outer surfaces of the vehicle body were designed using Computer Aided Design (CAD) tools and its
aerodynamic performance simulated virtually using Computational Fluid Dynamics (CFD) software. Parameters
such as pressure coefficient (Cp), coefficient of friction (Cf) and graphical analysis of the streamlines were used
to understand the flow dynamics and propose recommendations aimed at improving the coefficient of drag (Cd).
The identification of interaction points between the fluid and the flow structure was the primary focus of study to
develop these propositions. The study of phenomena linked to the characteristics of the model presented here,
allowed the identification of design features that should be avoided to generate improved aerodynamic
performance.
Experimental Investigations and Computational Analysis on Subsonic Wind Tunnelijtsrd
This paper disclose the entire approach to design an open circuit subsonic wind tunnel which will be used to consider the wind impact on the airfoil. The current rules and discoveries of the past research works were sought after for plan figuring of different segments of the wind tunnel. Wind speed of 26 m s have been practiced at the test territory. The wind qualities over a symmetrical airfoil are viewed as probably in a low speed wind tunnel. Tests were finished by moving the approach, from 0 to 5 degree. The stream attributes over a symmetrical airfoil are examined tentatively. The pressure distribution on the airfoil area was estimated, lift and drag force were estimated and velocity profiles were acquired. Rishabh Kumar Sahu | Saurabh Sharma | Vivek Swaroop | Vishal Kumar ""Experimental Investigations and Computational Analysis on Subsonic Wind Tunnel"" Published in International Journal of Trend in Scientific Research and Development (ijtsrd), ISSN: 2456-6470, Volume-3 | Issue-3 , April 2019, URL: https://www.ijtsrd.com/papers/ijtsrd23511.pdf
Paper URL: https://www.ijtsrd.com/engineering/mechanical-engineering/23511/experimental-investigations-and-computational-analysis-on-subsonic-wind-tunnel/rishabh-kumar-sahu
DYNAMIC BEHAVIOUR OF HYDRAULIC PRESSURE RELIEF VALVEIAEME Publication
This paper discusses the influence of the radial clearance of the poppet of the direct spring operated pressure relief valve type DPRS06K315 on the dynamic behaviour of the valve. The
mathematical model of the valve has been developed; these mathematical terms have been represented in Matlab/SIMULINK. The results obtained by a simulation describe dynamic behaviour of the valve and its influence on the system dynamic with respect to the poppet clearance
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Welcome to WIPAC Monthly the magazine brought to you by the LinkedIn Group Water Industry Process Automation & Control.
In this month's edition, along with this month's industry news to celebrate the 13 years since the group was created we have articles including
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Student information management system project report ii.pdfKamal Acharya
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About
Indigenized remote control interface card suitable for MAFI system CCR equipment. Compatible for IDM8000 CCR. Backplane mounted serial and TCP/Ethernet communication module for CCR remote access. IDM 8000 CCR remote control on serial and TCP protocol.
• Remote control: Parallel or serial interface.
• Compatible with MAFI CCR system.
• Compatible with IDM8000 CCR.
• Compatible with Backplane mount serial communication.
• Compatible with commercial and Defence aviation CCR system.
• Remote control system for accessing CCR and allied system over serial or TCP.
• Indigenized local Support/presence in India.
• Easy in configuration using DIP switches.
Technical Specifications
Indigenized remote control interface card suitable for MAFI system CCR equipment. Compatible for IDM8000 CCR. Backplane mounted serial and TCP/Ethernet communication module for CCR remote access. IDM 8000 CCR remote control on serial and TCP protocol.
Key Features
Indigenized remote control interface card suitable for MAFI system CCR equipment. Compatible for IDM8000 CCR. Backplane mounted serial and TCP/Ethernet communication module for CCR remote access. IDM 8000 CCR remote control on serial and TCP protocol.
• Remote control: Parallel or serial interface
• Compatible with MAFI CCR system
• Copatiable with IDM8000 CCR
• Compatible with Backplane mount serial communication.
• Compatible with commercial and Defence aviation CCR system.
• Remote control system for accessing CCR and allied system over serial or TCP.
• Indigenized local Support/presence in India.
Application
• Remote control: Parallel or serial interface.
• Compatible with MAFI CCR system.
• Compatible with IDM8000 CCR.
• Compatible with Backplane mount serial communication.
• Compatible with commercial and Defence aviation CCR system.
• Remote control system for accessing CCR and allied system over serial or TCP.
• Indigenized local Support/presence in India.
• Easy in configuration using DIP switches.
Immunizing Image Classifiers Against Localized Adversary Attacksgerogepatton
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When combined with 3D convolution and deep curriculum learning optimization (CLO), itsignificantly improves
the immunity of models against localized universal attacks by up to 40%. We evaluate our proposed approach
using contemporary CNN architectures and the modified Canadian Institute for Advanced Research (CIFAR-10
and CIFAR-100) and ImageNet Large Scale Visual Recognition Challenge (ILSVRC12) datasets, showcasing
accuracy improvements over previous techniques. The results indicate that the combination of the volumetric
input and curriculum learning holds significant promise for mitigating adversarial attacks without necessitating
adversary training.
Hierarchical Digital Twin of a Naval Power SystemKerry Sado
A hierarchical digital twin of a Naval DC power system has been developed and experimentally verified. Similar to other state-of-the-art digital twins, this technology creates a digital replica of the physical system executed in real-time or faster, which can modify hardware controls. However, its advantage stems from distributing computational efforts by utilizing a hierarchical structure composed of lower-level digital twin blocks and a higher-level system digital twin. Each digital twin block is associated with a physical subsystem of the hardware and communicates with a singular system digital twin, which creates a system-level response. By extracting information from each level of the hierarchy, power system controls of the hardware were reconfigured autonomously. This hierarchical digital twin development offers several advantages over other digital twins, particularly in the field of naval power systems. The hierarchical structure allows for greater computational efficiency and scalability while the ability to autonomously reconfigure hardware controls offers increased flexibility and responsiveness. The hierarchical decomposition and models utilized were well aligned with the physical twin, as indicated by the maximum deviations between the developed digital twin hierarchy and the hardware.
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FLUID MECHANICS AND MACHINERY FORMULA BOOK
1. R.M.K COLLEGE OF ENGINEERING
AND TECHNOLOGY
RSM NAGAR, PUDUVOYAL-601206
DEPARTMENT OF MECHANICAL ENGINEERING
CE6451 – FLUID MECHANICS & MACHINERY
III SEM MECHANICAL ENGINEERING
Regulation 2013
FORMULA BOOK
PREPARED BY
C.BIBIN / R.ASHOK KUMAR / N.SADASIVAN
2. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
CE6451 – FLUID MECHANICS AND MACHINERY FORMULA BOOK
Prepared By BIBIN.C / ASHOK KUMAR.R / SADASIVAN . N (AP / Mech) 2
PROPERTIES OF FLUID:
MASS DESNITY (ρ):
𝜌 =
𝑚
𝑉
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
m Mass Kg
V Volume m3
SPECIFIC VOLUME (v):
𝑣 =
𝑉
𝑚
=
1
𝜌
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
m Mass Kg
V Volume m3
𝑣 Specific Volume 𝑚3
𝑘𝑔⁄
SPECIFIC WEIGTH or WEIGTH DENSITY (w):
𝑤 =
𝑊
𝑉
=
𝑚𝑔
𝑉
= 𝜌𝑔
𝑆𝑖𝑛𝑐𝑒 𝑊 = 𝑚𝑔 𝑎𝑛𝑑 𝜌 = 𝑚
𝑉⁄
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
m Mass Kg
V Volume m3
UNIT – I – FLUID PROPERTIES AND FLOW
CHARACTERISTICS
3. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
CE6451 – FLUID MECHANICS AND MACHINERY FORMULA BOOK
Prepared By BIBIN.C / ASHOK KUMAR.R / SADASIVAN . N (AP / Mech) 3
𝑤 Specific Weight 𝑁
𝑚3⁄
g Acceleration due to gravity 𝑚
𝑠2⁄
SPECIFIC GRAVITY (S):
𝑆 =
𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑊𝑒𝑖𝑔ℎ𝑡 𝑜𝑓 𝑔𝑖𝑣𝑒𝑛 𝑓𝑙𝑢𝑖𝑑
𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑊𝑒𝑖𝑔ℎ𝑡 𝑜𝑓 𝑠𝑡𝑎𝑛𝑑𝑎𝑟𝑑 𝑓𝑙𝑢𝑖𝑑
𝑆 =
𝑀𝑎𝑠𝑠 𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑔𝑖𝑣𝑒𝑛 𝑓𝑙𝑢𝑖𝑑
𝑀𝑎𝑠𝑠 𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑠𝑡𝑎𝑛𝑑𝑎𝑟𝑑 𝑓𝑙𝑢𝑖𝑑
Symbol Description Unit
𝑆 Specific Gravity No unit
𝜌 Density or Mass Density 𝑘𝑔
𝑚3⁄
𝑤 Specific Weight 𝑁
𝑚3⁄
𝑤 𝑤𝑎𝑡𝑒𝑟
Specific Weight of
Standard Fluid (Water) =
9.81
𝑁
𝑚3⁄
𝜌 𝑤𝑎𝑡𝑒𝑟
Mass Density of Standard
Fluid (Water) = 1000
𝑘𝑔
𝑚3⁄
VISCOSITY (μ):
𝜏 𝛼
𝑑𝑢
𝑑𝑦
𝜏 = 𝜇
𝑑𝑢
𝑑𝑦
Symbol Description Unit
𝜏 Shear Stress 𝑁
𝑚2⁄
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
𝑑𝑢 Change in Velocity 𝑚
𝑠⁄
𝑑𝑦 Change in Distance 𝑚
4. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
CE6451 – FLUID MECHANICS AND MACHINERY FORMULA BOOK
Prepared By BIBIN.C / ASHOK KUMAR.R / SADASIVAN . N (AP / Mech) 4
DYNAMIC VISCOSITY (μ):
𝜇 =
𝜏
𝑑𝑢
𝑑𝑦⁄
Symbol Description Unit
𝜏 Shear Stress 𝑁
𝑚2⁄
𝜇 Dynamic Viscosity 𝑁 − 𝑠
𝑚2⁄
𝑑𝑢 Change in Velocity 𝑚
𝑠⁄
𝑑𝑦 Change in Distance 𝑚
𝑑𝑢
𝑑𝑦⁄ Rate of Shear Strain 1
𝑠⁄
Unit Conversion:
1
𝑁𝑠
𝑚2
= 10 𝑝𝑜𝑖𝑠𝑒
1 𝐶𝑒𝑛𝑡𝑖𝑝𝑜𝑖𝑠𝑒 =
1
100
𝑝𝑜𝑖𝑠𝑒
1 𝑝𝑜𝑖𝑠𝑒 = 0.1
𝑁𝑠
𝑚2
KINEMATIC VISCOSITY (γ):
𝛾 =
𝜇
𝜌
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝜇 Dynamic Viscosity 𝑁 − 𝑠
𝑚2⁄
γ Kinematic Viscosity 𝑚2
𝑠⁄
Unit Conversion:
1 𝑠𝑡𝑜𝑘𝑒 = 10−4 𝑚2
𝑠⁄
5. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
CE6451 – FLUID MECHANICS AND MACHINERY FORMULA BOOK
Prepared By BIBIN.C / ASHOK KUMAR.R / SADASIVAN . N (AP / Mech) 5
1 𝐶𝑒𝑛𝑡𝑖𝑠𝑡𝑜𝑘𝑒 =
1
100
𝑠𝑡𝑜𝑘𝑒
VISCOSITY PROBLEMS FOR PLATE TYPE:
FORCE (F):
𝜏 =
𝐹
𝐴
Symbol Description Unit
𝜏 Shear Stress 𝑁
𝑚2⁄
F Force N
A Area of the plate 𝑚2
POWER (P):
𝑃 = 𝐹 ∗ 𝑑𝑢
Symbol Description Unit
𝑃 Power 𝑊
F Force N
𝑑𝑢 Change in Velocity 𝑚
𝑠⁄
VISCOSITY PROBLEMS FOR SHAFT TYPE:
VELOCITY OF SHAFT (u):
𝑢 =
𝜋𝐷𝑁
60
Symbol Description Unit
𝐷 Diameter of Shaft 𝑚
N Speed of Shaft Rpm
𝑢 Velocity 𝑚
𝑠⁄
6. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
CE6451 – FLUID MECHANICS AND MACHINERY FORMULA BOOK
Prepared By BIBIN.C / ASHOK KUMAR.R / SADASIVAN . N (AP / Mech) 6
FORCE (F):
𝜏 =
𝐹
𝐴
𝜏 = 𝜋𝐷𝐿
Symbol Description Unit
𝜏 Shear Stress 𝑁
𝑚2⁄
F Force N
A Circumference of Shaft 𝑚2
𝐷 Diameter of Shaft 𝑚
𝐿 Length of Shaft 𝑚
TORQUE ON SHAFT (T):
𝑇 = 𝐹 ∗
𝐷
2
Symbol Description Unit
𝑇 Torque 𝑁 − 𝑚
F Force N
𝐷 Diameter of Shaft 𝑚
POWER ON SHAFT (P):
𝑃 =
2𝜋𝑁𝑇
60
Symbol Description Unit
𝑃 Power 𝑊
𝑇 Torque 𝑁 − 𝑚
N Speed of Shaft Rpm
7. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
CE6451 – FLUID MECHANICS AND MACHINERY FORMULA BOOK
Prepared By BIBIN.C / ASHOK KUMAR.R / SADASIVAN . N (AP / Mech) 7
VISCOSITY PROBLEMS FOR CONICAL BEARING:
ANGULAR VELOCITY (ω):
𝜔 =
2𝜋𝑁
60
Symbol Description Unit
𝜔 Angular Velocity 𝑟𝑎𝑑
𝑠𝑒𝑐⁄
N Speed of Shaft Rpm
ANGLE (θ):
𝑡𝑎𝑛𝜃 =
𝑟1 − 𝑟2
𝐻
Symbol Description Unit
𝑟1 Outer Radius 𝑚
𝑟2 Inner Radius 𝑚
𝐻 Height 𝑚
POWER (P):
𝑃 =
2𝜋𝑁𝑇
60
Symbol Description Unit
𝑃 Power 𝑊
𝑇 Torque 𝑁 − 𝑚
8. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
CE6451 – FLUID MECHANICS AND MACHINERY FORMULA BOOK
Prepared By BIBIN.C / ASHOK KUMAR.R / SADASIVAN . N (AP / Mech) 8
N Speed of Shaft Rpm
THICKNESS OF OIL (h):
𝑇 =
𝜋𝜇𝜔
2ℎ𝑠𝑖𝑛𝜃
( 𝑟1
4
− 𝑟2
4)
Symbol Description Unit
𝜇 Dynamic Viscosity 𝑁 − 𝑠
𝑚2⁄
𝑇 Torque 𝑁 − 𝑚
𝜔 Angular Velocity 𝑟𝑎𝑑
𝑠𝑒𝑐⁄
ℎ Thickness of Oil 𝑚
𝑟1 Outer Radius 𝑚
𝑟2 Inner Radius 𝑚
CAPILLARITY:
HEIGHT OF LIQUID IN TUBE (h):
ℎ =
4𝜎𝑐𝑜𝑠𝜃
𝜌𝑔𝑑
Symbol Description Unit
ℎ Height of Liquid in Tube 𝑚
𝜎 Surface Tension 𝑁
𝑚⁄
𝜃
Angle of Contact between
Liquid and Tube
𝑟𝑎𝑑
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
𝑑 Diameter of Tube 𝑚
SURFACE TENSION:
PRESSURE IN LIQUID DROPLET (P):
𝑃 =
4𝜎
𝑑
9. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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Symbol Description Unit
𝑃 Pressure 𝑁
𝑚2⁄
𝜎 Surface Tension 𝑁
𝑚⁄
𝑑 Diameter of Droplet 𝑚
PRESSURE IN BUBBLE (P):
𝑃 =
8𝜎
𝑑
Symbol Description Unit
𝑃 Pressure 𝑁
𝑚2⁄
𝜎 Surface Tension 𝑁
𝑚⁄
𝑑 Diameter of Bubble 𝑚
PRESSURE IN LIQUID JET (P):
𝑃 =
2𝜎
𝑑
Symbol Description Unit
𝑃 Pressure 𝑁
𝑚2⁄
𝜎 Surface Tension 𝑁
𝑚⁄
𝑑 Diameter of Jet 𝑚
CONTINUITY EQUATION:
𝜕𝑢
𝜕𝑥
+
𝜕𝑣
𝜕𝑦
+
𝜕𝑤
𝜕𝑧
= 0 [ 𝐹𝑜𝑟 3 − 𝐷 𝑓𝑙𝑜𝑤]
𝜕𝑢
𝜕𝑥
+
𝜕𝑣
𝜕𝑦
+ = 0 [ 𝐹𝑜𝑟 2 − 𝐷 𝑓𝑙𝑜𝑤]
𝜕
𝜕𝑟
( 𝑟𝑢 𝑟) +
𝜕
𝜕𝜃
( 𝑢 𝜃) = 0[ 𝐹𝑜𝑟 𝑝𝑜𝑙𝑎𝑟 𝑐𝑜𝑜𝑟𝑑𝑖𝑛𝑎𝑡𝑒𝑠]
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BERNOULLI’S EQUATION:
𝜕𝑃
𝜌
+ 𝑣. 𝑑𝑣 + 𝑔. 𝑑𝑧 = 0
𝑃1
𝜌𝑔
+
𝑣1
2
2𝑔
+ 𝑧1 =
𝑃2
𝜌𝑔
+
𝑣2
2
2𝑔
+ 𝑧2 + ℎ 𝑓
Symbol Description Unit
𝑃1 & 𝑃2 Pressure at Section 1 & 2 𝑁
𝑚2⁄
𝑣1 & 𝑣2 Velocity at Section 1 & 2 𝑚
𝑠⁄
𝑧1 & 𝑧2
Datum Head at Section 1 &
2
𝑚
ℎ 𝑓 Head Loss 𝑚
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
COEFFICIENT OF DISCHARGE:
𝐶 𝑑 =
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙
COEFFICIENT OF VELOCITY:
𝐶𝑣 =
𝑣 𝐴𝑐𝑡𝑢𝑎𝑙
𝑣 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙
DISCHARGE OF VENTURIMETER AND ORIFICEMETER:
𝑄 = 𝐶 𝑑
𝑎1 𝑎2
√( 𝑎1
2 − 𝑎1
2)
√2𝑔ℎ
Symbol Description Unit
𝑎1 & 𝑎2 Area at Section 1 & 2 𝑚2
ℎ
Pressure Difference
between Section 1 & 2
(
𝑃1− 𝑃2
𝜌𝑔
)
𝑚
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𝐶 𝑑 Coefficient of Discharge
𝑥
Difference in Mercury
Level
𝑚
ℎ = 𝑥 (1 −
𝑆 𝑚
𝑆
) [ 𝑤ℎ𝑒𝑛 𝑆 > 𝑆 𝑚]
ℎ = 𝑥 (
𝑆 𝑚
𝑆
− 1) [ 𝑤ℎ𝑒𝑛 𝑆 𝑚 > 𝑆]
ℎ = (
𝑃1
𝜌𝑔
+ 𝑍1) − (
𝑃2
𝜌𝑔
+ 𝑍2) [ 𝐼𝑛𝑐𝑙𝑖𝑛𝑒𝑑 𝑉𝑒𝑛𝑡𝑢𝑟𝑖𝑚𝑒𝑡𝑒𝑟]
MOMENTUM EQUATION:
𝐹 =
𝑑 (𝑚𝑣)
𝑑𝑡
FORCE ACTING IN X – DIRECTION:
𝐹𝑥 = 𝜌𝑄 ( 𝑣1 − 𝑣2 𝑐𝑜𝑠𝜃) + 𝑃1 𝐴1 − 𝑃2 𝐴2 𝑐𝑜𝑠𝜃
FORCE ACTING IN Y – DIRECTION:
𝐹𝑦 = 𝜌𝑄 (− 𝑣2 𝑠𝑖𝑛𝜃) − 𝑃2 𝐴2 𝑠𝑖𝑛𝜃
Symbol Description Unit
𝑃1 & 𝑃2 Pressure at Section 1 & 2 𝑁
𝑚2⁄
𝑣1 & 𝑣2 Velocity at Section 1 & 2 𝑚
𝑠⁄
𝐴1 & 𝐴2 Area at Section 1 & 2 𝑚
𝜃 Angle of the Bend 𝐷𝑒𝑔𝑟𝑒𝑒
𝑄 Discharge 𝑚3
𝑠⁄
RESULTANT FORCE:
𝐹𝑅 = √𝐹𝑥
2
+ 𝐹𝑦
2
12. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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ANGLE MADE BY RESULTANT FORCE:
𝑡𝑎𝑛𝜃 =
𝐹𝑦
𝐹𝑥
MOMENT OF MOMENTUM EQUATION:
𝑇 = 𝜌𝑄 ( 𝑣2 𝑟2 − 𝑣1 𝑟1)
Symbol Description Unit
𝑇 Torque 𝑁 − 𝑚
𝑣1 & 𝑣2 Velocity at Section 1 & 2 𝑚
𝑠⁄
𝑟1 & 𝑟2
Radius of Curvature at
Section 1 & 2
𝑚
𝑄 Discharge 𝑚3
𝑠⁄
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
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TOTAL ENERGY LINE (TEL):
𝑇𝐸𝐿 = 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝐻𝑒𝑎𝑑 + 𝐾𝑖𝑛𝑒𝑡𝑖𝑐 𝐻𝑒𝑎𝑑 + 𝐷𝑎𝑡𝑢𝑚 𝐻𝑒𝑎𝑑
𝑇𝐸𝐿 =
𝑃
𝜌𝑔
+
𝑣2
2𝑔
+ 𝑍
Symbol Description Unit
𝑃 Pressure 𝑁
𝑚2⁄
𝑣 Velocity 𝑚
𝑠⁄
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝑍 Datum Head 𝑚
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
HYDRAULIC ENERGY LINE (HEL):
𝐻𝐸𝐿 = 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝐻𝑒𝑎𝑑 + 𝐷𝑎𝑡𝑢𝑚 𝐻𝑒𝑎𝑑
𝑇𝐸𝐿 =
𝑃
𝜌𝑔
+ 𝑍
HAGEN POISEUILLE’S EQUATION:
SHEAR STRESS:
𝜏 = −
𝜕𝑝
𝜕𝑥
∗
𝑟
2
Symbol Description Unit
𝜏 Shear Stress 𝑁
𝑚2⁄
𝜕𝑝
𝜕𝑥
Pressure Gradient 𝑁
𝑚3⁄
𝑟 Radius of pipe 𝑚
UNIT – II – FLOW THROUGH CIRCULAR CONDUITS
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VELOCITY:
𝑢 = −
1
4𝜇
∗
𝜕𝑝
𝜕𝑥
∗ (𝑅2
− 𝑟2
)
Symbol Description Unit
𝑢 Velocity of Fluid in Pipe 𝑚
𝑠⁄
𝜕𝑝
𝜕𝑥
Pressure Gradient 𝑁
𝑚3⁄
𝑟 Radius of pipe 𝑚
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
MAXIMUM VELOCITY:
𝑢 = −
1
4𝜇
∗
𝜕𝑝
𝜕𝑥
∗ (𝑅2
)
Symbol Description Unit
𝑢 Velocity of Fluid in Pipe 𝑚
𝑠⁄
𝜕𝑝
𝜕𝑥
Pressure Gradient 𝑁
𝑚3⁄
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
AVERAGE VELOCITY:
𝑢̅ = −
1
4𝜇
∗
𝜕𝑝
𝜕𝑥
∗ (𝑅2
)
Symbol Description Unit
𝑢̅
Average Velocity of Fluid
in Pipe
𝑚
𝑠⁄
𝜕𝑝
𝜕𝑥
Pressure Gradient 𝑁
𝑚3⁄
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
RATIO BETWEEN MAXIMUM VELOCITY AND AVERAGE VELOCITY:
𝑢 𝑚𝑎𝑥
𝑢̅
= 2
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DISCHARGE:
𝑢 = −
1
8𝜇
∗
𝜕𝑝
𝜕𝑥
∗ 𝜋 ∗ 𝑅4
Symbol Description Unit
𝑢 Velocity of Fluid in Pipe 𝑚
𝑠⁄
𝜕𝑝
𝜕𝑥
Pressure Gradient 𝑁
𝑚3⁄
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
PRESSURE DIFFERENCE:
𝑃1 − 𝑃2 =
32𝜇𝑢̅𝐿
𝐷2
Symbol Description Unit
𝑢̅
Average Velocity of Fluid
in Pipe
𝑚
𝑠⁄
𝐿 Length of Pipe 𝑚
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
𝐷 Diameter of Pipe 𝑚
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
LOSS OF HEAD:
ℎ 𝑓 =
𝑃1 − 𝑃2
𝜌𝑔
=
32𝜇𝑢̅𝐿
𝜌𝑔𝐷2
[ 𝑓𝑜𝑟 𝐿𝑎𝑚𝑖𝑛𝑎𝑟 𝑓𝑙𝑜𝑤]
DARCY WEISBACH EQUATION:
ℎ 𝑓 =
𝑃1 − 𝑃2
𝜌𝑔
=
4𝑓𝐿𝑣2
2𝑔𝑑
[ 𝑓𝑜𝑟 𝑇𝑢𝑟𝑏𝑢𝑙𝑒𝑛𝑡 𝑓𝑙𝑜𝑤]
Symbol Description Unit
𝑣 Velocity of Fluid in Pipe 𝑚
𝑠⁄
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𝐿 Length of Pipe 𝑚
𝑓 Friction Factor
𝑑 Diameter of Pipe 𝑚
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
REYNOLD’S NUMBER:
𝑅 𝑒 =
𝜌𝑣𝑑
𝜇
𝑓 =
0.079
𝑅 𝑒
0.25
[ 𝐹𝑜𝑟 𝑇𝑢𝑟𝑏𝑢𝑙𝑒𝑛𝑡 𝐹𝑙𝑜𝑤]
𝑓 =
16
𝑅 𝑒
[ 𝐹𝑜𝑟 𝐿𝑎𝑚𝑖𝑛𝑎𝑟 𝐹𝑙𝑜𝑤]
𝑅 𝑒 < 2000 𝑇ℎ𝑒𝑛 𝑡ℎ𝑒 𝐹𝑙𝑜𝑤 𝑖𝑠 𝐿𝑎𝑚𝑖𝑛𝑎𝑟
𝑅 𝑒 > 2000 𝑇ℎ𝑒𝑛 𝑡ℎ𝑒 𝐹𝑙𝑜𝑤 𝑖𝑠 𝑇𝑢𝑟𝑏𝑢𝑙𝑒𝑛𝑡
Symbol Description Unit
𝑣 Velocity of Fluid in Pipe 𝑚
𝑠⁄
𝑑 Diameter of Pipe 𝑚
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
MAJOR LOSS IN PIPES:
ℎ 𝑓 =
32𝜇𝑢̅𝐿
𝜌𝑔𝑑2
[ 𝑓𝑜𝑟 𝐿𝑎𝑚𝑖𝑛𝑎𝑟 𝑓𝑙𝑜𝑤]
ℎ 𝑓 =
4𝑓𝐿𝑣2
2𝑔𝑑
[ 𝑓𝑜𝑟 𝑇𝑢𝑟𝑏𝑢𝑙𝑒𝑛𝑡 𝑓𝑙𝑜𝑤]
17. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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Symbol Description Unit
𝑢̅ & 𝑣 Velocity of Fluid in Pipe 𝑚
𝑠⁄
𝑑 Diameter of Pipe 𝑚
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
𝑙 Length of Pipe 𝑚
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
𝑓 Friction Factor
MINOR LOSS IN PIPES:
LOSS DUE TO SUDDEN ENLARGEMENT:
ℎ 𝑒 =
( 𝑣1 − 𝑣2)2
2𝑔
Symbol Description Unit
𝑣1 & 𝑣2
Velocity of Fluid in Pipe at
Inlet and Outlet
𝑚
𝑠⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
LOSS DUE TO SUDDEN CONTRACTION:
ℎ 𝑐 =
𝐾𝑣2
2𝑔
𝐾 = (
1
𝐶𝑐
− 1)
2
ℎ 𝑐 =
0.5𝑣2
2𝑔
[ 𝐼𝑓 𝐶𝑐 𝑛𝑜𝑡 𝑔𝑖𝑣𝑒𝑛]
Symbol Description Unit
𝑣 Velocity of Fluid at Outlet 𝑚
𝑠⁄
𝐶𝑐
Coefficient of Contraction
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𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
LOSS AT ENTRANCE OF PIPE:
ℎ𝑖 =
0.5𝑣2
2𝑔
Symbol Description Unit
𝑣 Velocity of Fluid at Inlet 𝑚
𝑠⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
LOSS AT EXIT OF PIPE:
ℎ 𝑜 =
𝑣2
2𝑔
Symbol Description Unit
𝑣 Velocity of Fluid at Outlet 𝑚
𝑠⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
LOSS DUE TO GRADUAL CONTRACTION:
ℎ 𝑒 =
𝐾( 𝑣1 − 𝑣2)2
2𝑔
Symbol Description Unit
𝑣1 & 𝑣2
Velocity of Fluid in Pipe at
Inlet and Outlet
𝑚
𝑠⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
𝐾 Coefficient of Contraction
LOSS AT BEND OF PIPE:
ℎ 𝑏 =
𝐾𝑣2
2𝑔
19. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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Symbol Description Unit
𝑣 Velocity of Flow 𝑚
𝑠⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
𝐾 Coefficient of Bend
LOSS AT DUE TO VARIOUS FITTINGS:
ℎ 𝑣 =
𝐾𝑣2
2𝑔
Symbol Description Unit
𝑣 Velocity of Flow 𝑚
𝑠⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
𝐾 Coefficient of Fittings
LOSS AT DUE TO OBSTRUCTION:
ℎ 𝑣 =
𝑣2
2𝑔
(
𝐴
𝐶𝑐 ( 𝐴 − 𝑎)
− 1)
𝐶𝑐 =
𝐴 𝑐
( 𝐴 − 𝑎)
Symbol Description Unit
𝑣 Velocity of Flow 𝑚
𝑠⁄
𝐴 Area of Pipe 𝑚2
𝑎 Area of Obstruction 𝑚2
𝐴 𝑐
Area of Vena Contraction 𝑚2
WHEN PIPES ARE CONNECTED IN SERIES:
DISCHARGE:
𝑄 = 𝑄1 = 𝑄2
𝑄 = 𝐴1 𝑣1 = 𝐴2 𝑣2
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HEAD LOSS:
ℎ 𝑓 = ℎ 𝑓1 + ℎ 𝑓2
ℎ 𝑓 =
4𝑓𝑙1 𝑣1
2
2𝑔𝑑1
+
4𝑓𝑙2 𝑣2
2
2𝑔𝑑2
Symbol Description Unit
𝑣1 & 𝑣2
Velocity of Flow at Pipe 1
& 2
𝑚
𝑠⁄
𝐴1& 𝐴2 Area of Pipe 1 & 2 𝑚2
𝑑1& 𝑑2 Diameter of Pipe 1 & 2 𝑚
𝑙1& 𝑙2 Length of Pipe 1 & 2 𝑚
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
𝑓 Friction Factor
WHEN PIPES ARE CONNECTED IN PARALLEL:
DISCHARGE:
𝑄 = 𝑄1 + 𝑄2
𝑄 = 𝐴1 𝑣1 + 𝐴2 𝑣2
HEAD LOSS:
ℎ 𝑓 = ℎ 𝑓1 = ℎ 𝑓2
ℎ 𝑓 =
4𝑓𝑙1 𝑣1
2
2𝑔𝑑1
=
4𝑓𝑙2 𝑣2
2
2𝑔𝑑2
Symbol Description Unit
𝑣1 & 𝑣2
Velocity of Flow at Pipe 1
& 2
𝑚
𝑠⁄
𝐴1& 𝐴2 Area of Pipe 1 & 2 𝑚2
𝑑1& 𝑑2 Diameter of Pipe 1 & 2 𝑚
𝑙1& 𝑙2 Length of Pipe 1 & 2 𝑚
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𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
𝑓 Friction Factor
EQUIVALENT PIPE:
𝐿
𝐷5
=
𝐿1
𝐷1
5 +
𝐿2
𝐷2
5 +
𝐿3
𝐷3
5 + ⋯ +
𝐿 𝑛
𝐷 𝑛
5
Symbol Description Unit
𝐷 Diameter of Pipe 𝑚
𝐿 Length of Pipe 𝑚
BOUNDARY LAYER:
DISPLACEMENT THICKNESS:
𝛿∗
= ∫ (1 −
𝑢
𝑈
)
𝛿
0
𝑑𝑦
MOMENTUM THICKNESS:
𝜃 = ∫
𝑢
𝑈
(1 −
𝑢
𝑈
)
𝛿
0
𝑑𝑦
MOMENTUM THICKNESS:
𝛿∗∗
= ∫
𝑢
𝑈
(1 −
𝑢2
𝑈2
)
𝛿
0
𝑑𝑦
Symbol Description Unit
𝑢
𝑈
Velocity Distribution
𝛿 Boundary layer thickness
SHEAR STRESS:
𝜏0
𝜌𝑈2
=
𝜕𝜃
𝜕𝑥
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𝜃 = ∫
𝑢
𝑈
(1 −
𝑢
𝑈
)
𝛿
0
𝑑𝑦
DRAG FORCE:
𝐹 𝐷 = ∫ 𝑆ℎ𝑒𝑎𝑟 𝑆𝑡𝑟𝑒𝑠𝑠 ∗ 𝐴𝑟𝑒𝑎
𝐿
0
𝐹 𝐷 = ∫ 𝜏0 ∗ 𝑏 ∗ 𝑑𝑥
𝐿
0
LOCAL COEFFICIENT OF DRAG:
𝐶 𝐷
∗
=
𝜏0
1
2
𝜌𝑈2
AVERAGE COEFFICIENT OF DRAG:
𝐶 𝐷 =
𝐹 𝐷
1
2
𝜌𝐴𝑈2
Symbol Description Unit
𝜏0 Shear Stress 𝑁
𝑚2⁄
𝑏 Width of Plate 𝑚
𝑈 Free Stream Velocity 𝑚
𝑠⁄
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝐴 Area 𝑚2
𝐹 𝐷 Drag Force 𝑁
BLASIUS’S SOLUTION:
BOUNDARY LAYER THICKNESS:
𝛿 =
4.91𝑥
√ 𝑅 𝑒𝑥
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LOCAL COEFFICIENT OF DRAG:
𝐶 𝐷
∗
=
0.664
√ 𝑅 𝑒𝑥
AVERAGE COEFFICIENT OF DRAG:
𝐶 𝐷 =
1.328
√ 𝑅 𝑒𝐿
Symbol Description Unit
𝑅 𝑒𝑥
Reynold’s Number at
distance x
𝑅 𝑒𝐿
Reynold’s Number at
distance L
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UNITS:
Physical Quantity Symbol Unit Dimensions
Length L m L
Mass M Kg M
Time T Sec T
Area A m2
L2
Volume V m3
L3
Diameter D m L
Head H m L
Roughness k M L
Velocity v m/s LT-1
Angular Velocity ω rad/sec T-1
Acceleration a m/s2
LT-2
Angular Acceleration α rad/sec2
T-2
Speed N Rpm T-1
Discharge Q m3
/s L3
T-1
Kinematic Viscosity γ cm2
/s L2
T-1
Dynamic Viscosity μ N-s/m2
ML-1
T-1
Force F N MLT-2
Weight W N MLT-2
Thrust T N MLT-2
Density ρ Kg/ m3
ML-3
Pressure P N/m2
ML-1
T-2
UNIT – III – DIMENSIONAL ANALYSIS
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Physical Quantity Symbol Unit Dimensions
Specific Weight w N/m3
ML-2
T-2
Young’s Modulus E N/m2
ML-1
T-2
Bulk Modulus K N/m2
ML-1
T-2
Shear Stress τ N/m2
ML-1
T-2
Surface Tension σ N/m MT-2
Energy / Work W/E J = N-m ML2
T-2
Torque T N-m ML-2
T-2
Power P W=J/s ML-2
T-3
Momentum M Kg m/s MLT-1
Efficiency η No Unit Dimensionless
SIMILARITY:
GEOMETRIC SIMILARITY:
𝐿 𝑝
𝐿 𝑚
=
𝑏 𝑝
𝑏 𝑚
=
𝐷 𝑝
𝐷 𝑚
= 𝐿 𝑟
𝐴 𝑝
𝐴 𝑚
=
𝐿 𝑝
𝐿 𝑚
∗
𝑏 𝑝
𝑏 𝑚
= 𝐿 𝑟 ∗ 𝐿 𝑟 = 𝐿 𝑟
2
𝑉𝑝
𝑉𝑚
=
𝐿 𝑝
𝐿 𝑚
∗
𝑏 𝑝
𝑏 𝑚
∗
𝑡 𝑝
𝑡 𝑚
= 𝐿 𝑟 ∗ 𝐿 𝑟 ∗ 𝐿 𝑟 = 𝐿 𝑟
3
Symbol Description Unit
𝐿 𝑝&𝐿 𝑚
Length of Prototype &
Model
𝑚
𝑏 𝑝&𝑏 𝑚
Breadth of Prototype &
Model
𝑚
𝐷 𝑝&𝐷 𝑚
Diameter of Prototype &
Model
𝑚
𝑡 𝑝&𝑡 𝑚
Thickness of Prototype &
Model
𝑚
𝐴 𝑝&𝐴 𝑚 Area of Prototype & Model 𝑚2
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𝑉𝑝&𝑉𝑚
Volume of Prototype &
Model
𝑚3
𝐿 𝑟 Length Ratio
KINEMATIC SIMILARITY:
𝑣 𝑝
𝑣 𝑚
= 𝑣𝑟
𝑎 𝑝
𝑎 𝑚
= 𝑎 𝑟
Symbol Description Unit
𝑣 𝑝&𝑣 𝑚
Velocity of Prototype &
Model
𝑚
𝑠⁄
𝑎 𝑝&𝑎 𝑚
Acceleration of Prototype
& Model
𝑚
𝑠2⁄
𝑣𝑟 Velocity Ratio
𝑎 𝑟 Acceleration Ratio
DYNAMIC SIMILARITY:
( 𝐹𝑖) 𝑝
( 𝐹𝑖) 𝑚
=
( 𝐹𝑣) 𝑝
( 𝐹𝑣) 𝑚
=
(𝐹𝑔)
𝑝
(𝐹𝑔)
𝑚
= 𝐹𝑟
Symbol Description Unit
( 𝐹𝑖) 𝑝& ( 𝐹𝑖) 𝑚
Inertia Force of Prototype
& Model
𝑁
( 𝐹𝑣) 𝑝& ( 𝐹𝑣) 𝑚
Viscous Force of Prototype
& Model
𝑁
(𝐹𝑔)
𝑝
& (𝐹𝑔)
𝑚
Gravity Force of Prototype
& Model
𝑁
𝐹𝑟 Force Ratio
DIMENSIONLESS NUMBER:
REYNOLD’S NUMBER:
𝑅 𝑒 =
𝜌𝑣𝐷
𝜇
(𝑜𝑟)
𝜌𝑣𝐿
𝜇
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Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑣 Velocity 𝑚
𝑠⁄
𝜇 Viscosity 𝑁 − 𝑠
𝑚2⁄
𝐷 Diameter 𝑚
𝐿 Length 𝑚
FROUDE’S NUMBER:
𝐹𝑒 =
𝑣
√ 𝐿𝑔
Symbol Description Unit
𝑣 Velocity 𝑚
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐿 Length 𝑚
FROUDE’S NUMBER:
𝐹𝑒 =
𝑣
√ 𝐿𝑔
Symbol Description Unit
𝑣 Velocity 𝑚
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐿 Length 𝑚
EULER’S NUMBER:
𝐸 𝑢 =
𝑣
√ 𝑝
𝜌⁄
Symbol Description Unit
𝑣 Velocity 𝑚
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
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𝑝 Pressure 𝑁
𝑚2⁄
WEBER’S NUMBER:
𝑊𝑒 =
𝑣
√ 𝜎
𝜌𝐿⁄
Symbol Description Unit
𝑣 Velocity 𝑚
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
𝐿 Length 𝑚
𝜎 Surface Tension 𝑁
𝑚⁄
MACH’S NUMBER:
𝑊𝑒 =
𝑣
√ 𝐾
𝜌⁄
Symbol Description Unit
𝑣 Velocity 𝑚
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
𝐾 Elastic Stress 𝑁
𝑚2⁄
REYNOLD’S MODEL LAW:
TIME RATIO:
𝐹𝑟 = 𝑚 𝑟 𝑎 𝑟
𝐹𝑟 = 𝑚 𝑟
𝑣𝑟
𝑇𝑟
DISCHARGE RATIO:
𝑄 𝑟 = 𝜌𝑟 𝐿 𝑟
2
𝑣𝑟
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Symbol Description Unit
𝐹𝑟 Force Ratio
𝑚 𝑟 Mass Ratio
𝑣𝑟 Velocity Ratio
𝑇𝑟 Time Ratio
𝐿 𝑟 Length Ratio
𝜌𝑟 Density Ratio
FROUDE’S MODEL LAW:
TIME RATIO:
𝑇𝑟 = √ 𝐿 𝑟
ACCELERATION RATIO:
𝑎 𝑟 = 1
DISCHARGE RATIO:
𝑄 𝑟 = ( 𝐿 𝑟)
5
2⁄
FORCE RATIO:
𝐹𝑟 = ( 𝐿 𝑟)3
PRESSURE RATIO:
𝐹𝑟 = 𝐿 𝑟
ENERGY RATIO:
𝐸𝑟 = ( 𝐿 𝑟)4
MOMENTUM RATIO:
𝑀𝑟 = ( 𝐿 𝑟)3
∗ √ 𝐿 𝑟
TORQUE RATIO:
𝑇𝑟 = ( 𝐿 𝑟)4
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POWER RATIO:
𝑃𝑟 = ( 𝐿 𝑟)
7
2⁄
Symbol Description Unit
𝐿 𝑟 Length Ratio
DISTORTED MODELS:
( 𝐿 𝑟) 𝐻 =
𝐿𝑖𝑛𝑒𝑎𝑟 𝐻𝑜𝑟𝑖𝑧𝑜𝑛𝑡𝑎𝑙 𝐷𝑖𝑚𝑒𝑛𝑠𝑖𝑜𝑛𝑠 𝑜𝑓 𝑃𝑟𝑜𝑡𝑜𝑡𝑦𝑝𝑒
𝐿𝑖𝑛𝑒𝑎𝑟 𝐻𝑜𝑟𝑖𝑧𝑜𝑛𝑡𝑎𝑙 𝐷𝑖𝑚𝑒𝑛𝑠𝑖𝑜𝑛𝑠 𝑜𝑓 𝑀𝑜𝑑𝑒𝑙
( 𝐿 𝑟) 𝐻 =
𝐿 𝑝
𝐿 𝑚
=
𝐵𝑝
𝐵 𝑚
( 𝐿 𝑟) 𝑉 =
𝐿𝑖𝑛𝑒𝑎𝑟 𝑉𝑒𝑟𝑡𝑖𝑐𝑎𝑙 𝐷𝑖𝑚𝑒𝑛𝑠𝑖𝑜𝑛𝑠 𝑜𝑓 𝑃𝑟𝑜𝑡𝑜𝑡𝑦𝑝𝑒
𝐿𝑖𝑛𝑒𝑎𝑟 𝑉𝑒𝑟𝑡𝑖𝑐𝑎𝑙 𝐷𝑖𝑚𝑒𝑛𝑠𝑖𝑜𝑛𝑠 𝑜𝑓 𝑀𝑜𝑑𝑒𝑙
( 𝐿 𝑟) 𝑉 =
ℎ 𝑝
ℎ 𝑚
VELOCITY RATIO:
𝑣𝑟 = √(𝐿 𝑟) 𝑉
AREA RATIO:
𝐴 𝑟 = ( 𝐿 𝑟) 𝐻 ∗ ( 𝐿 𝑟) 𝑉
DISCAHRGE RATIO:
𝑄 𝑟 = ( 𝐿 𝑟) 𝐻 ∗ [( 𝐿 𝑟) 𝑉]
3
2⁄
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CENTRIFUGAL PUMP:
VELOCITY TRIANGLE DIAGRAM:
Symbol Description Unit
𝑢1&𝑢2
Tangential Velocity of
Impeller at Inlet & Outlet
𝑚
𝑠⁄
𝑣 𝑟1&𝑣 𝑟2
Relative Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑣1&𝑣2
Absolute Velocity at Inlet
& Outlet
𝑚
𝑠⁄
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
UNIT – IV – PUMPS
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𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝛽
Angle made by Absolute
Velocity at Outlet with the
Direction of Motion of
Vane
Degree
𝜙
Angle made by Relative
Velocity at Outlet with the
Direction of Motion of
Vane
Degree
TANGENTIAL VELOCITY AT INLET:
𝑢1 =
𝜋𝑑1 𝑁
60
Symbol Description Unit
𝑑1
Inlet (or) Internal Diameter
of Impeller
𝑚
𝑁 Speed of Impeller 𝑟𝑝𝑚
TANGENTIAL VELOCITY AT OUTLET:
𝑢2 =
𝜋𝑑2 𝑁
60
Symbol Description Unit
𝑑2
Oulet (or) External
Diameter of Impeller
𝑚
𝑁 Speed of Impeller 𝑟𝑝𝑚
FROM INLET VELOCITY TRIANGLE DIAGRAM:
𝑡𝑎𝑛𝜃 =
𝑣𝑓1
𝑢1
Symbol Description Unit
𝑢1
Tangential Velocity of
Impeller at Inlet
𝑚
𝑠⁄
𝑣1 Absolute Velocity at Inlet 𝑚
𝑠⁄
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𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
∵ 𝛼 = 90°
𝑣1 = 𝑣𝑓1
FROM OUTLET VELOCITY TRIANGLE DIAGRAM:
𝑡𝑎𝑛𝜙 =
𝑣𝑓2
𝑢2 − 𝑣 𝑤2
𝑣2 = √𝑣𝑓2
2 + 𝑣 𝑤2
2
𝑡𝑎𝑛𝛽 =
𝑣𝑓2
𝑣 𝑤2
Symbol Description Unit
𝑢2
Tangential Velocity of
Impeller at Outlet
𝑚
𝑠⁄
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑣2 Absolute Velocity at Outlet 𝑚
𝑠⁄
𝑣𝑓2 Flow Velocity at Outlet 𝑚
𝑠⁄
𝜙
Angle made by Relative
Velocity at Outlet with the
Direction of Motion of
Vane
Degree
𝛽
Angle made by Absolute
Velocity at Outlet with the
Degree
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Direction of Motion of
Vane
DISCHARGE:
𝑄 = 𝜋𝑑1 𝑏1 𝑣𝑓1 = 𝜋𝑑2 𝑏2 𝑣𝑓2
Symbol Description Unit
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑑1&𝑑2
Diameter of Impeller at
Inlet & Outlet
𝑚
𝑏1&𝑏2
Width of Impeller at Inlet
& Outlet
𝑚
𝑄 Discharge 𝑚3
𝑠⁄
WORK DONE BY AN IMPELLER PER SECOND:
𝑊 =
𝜌𝑔𝑄
𝑔
𝑣 𝑤2 𝑢2
Symbol Description Unit
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑢2
Tangential Velocity at
Outlet
𝑚
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
WORK DONE BY AN IMPELLER PER UNIT WEIGHT OF WATER:
𝑊 =
𝑣 𝑤2 𝑢2
𝑔
Symbol Description Unit
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑢2
Tangential Velocity at
Outlet
𝑚
𝑠⁄
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𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
MANOMETRIC EFFICIENCY:
𝜂 𝑚 =
𝑔𝐻
𝑣 𝑤2 𝑢2
Symbol Description Unit
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑢2
Tangential Velocity at
Outlet
𝑚
𝑠⁄
𝐻 Manometric Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
POWER REQUIRED BY THE PUMP:
𝑃 = 𝜌𝑄𝑣 𝑤2 𝑢2
Symbol Description Unit
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑢2
Tangential Velocity at
Outlet
𝑚
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑃 Power 𝑘𝑊
MINIMUM SPEED TO START THE PUMP:
𝑁 𝑚𝑖𝑛 =
120 ∗ 𝜂 𝑚 ∗ 𝑣 𝑤2 ∗ 𝑑2
𝜋 (𝑑2
2
− 𝑑1
2
)
Symbol Description Unit
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑑1&𝑑2
Diameter of Impeller at
Inlet & Outlet
𝑚
𝜂 𝑚 Manometric Efficiency
36. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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OVERALL EFFICIENCY:
𝜂 𝑜 =
𝐼𝑚𝑝𝑒𝑙𝑙𝑒𝑟 𝑃𝑜𝑤𝑒𝑟
𝑆ℎ𝑎𝑓𝑡 𝑃𝑜𝑤𝑒𝑟
=
𝜌𝑔𝑄𝐻
𝑆. 𝑃
𝜂 𝑜 = 𝜂 𝑚𝑎𝑛𝑜 ∗ 𝜂 𝑚𝑒𝑐ℎ ∗ 𝜂 𝑣𝑜𝑙
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝐻 Manometric Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
MECHANICAL EFFICIENCY:
𝜂 𝑚𝑒𝑐ℎ =
𝜌𝑔𝑄𝐻
𝑆. 𝑃
∗
𝑣 𝑤2 𝑢2
𝑔𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝐻 Manometric Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝑆. 𝑃 Shaft Power 𝑊
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑢2
Tangential Velocity at
Outlet
𝑚
𝑠⁄
POWER OF PUMP:
𝑃 = 𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
37. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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𝐻 Manometric Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
HYDRAULIC EFFICIENCY:
𝜂ℎ𝑦𝑑 =
𝐴𝑐𝑡𝑢𝑎𝑙 𝐿𝑖𝑓𝑡
𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 𝐿𝑖𝑓𝑡
=
𝐴𝑐𝑡𝑢𝑎𝑙 𝐻𝑒𝑎𝑑
𝐼𝑑𝑒𝑎𝑙 𝐻𝑒𝑎𝑑
IDEAL HEAD:
𝑃𝐼 = 𝜌𝑔(𝑄 + 𝑞)𝐻𝑖
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝑞 Leakage of Water 𝑚3
𝑠⁄
𝐻𝑖 Ideal Head 𝑚
𝑃𝐼 Power at Input 𝑊
TORQUE EXERTED BY IMPELLER:
𝑇 =
𝜌𝑔𝑄
𝑔
∗ 𝑣 𝑤2 ∗ 𝑅2
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑅2
Radius of Impeller at
Outlet
𝑚
38. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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SPECIFIC SPEED:
𝑁𝑠 =
𝑁√ 𝑄
𝐻
3
4⁄
𝑁𝑠 =
𝑁√ 𝑃
𝐻
5
4⁄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝐻 Head 𝑚
𝑃 Power 𝑘𝑊
𝑁 Speed 𝑟𝑝𝑚
𝑁𝑠 Specific Speed
SPEED RATIO:
𝐾 𝑢 =
𝑢2
√2𝑔𝐻
𝐾 𝑢 = 0.95 − 1.25
Symbol Description Unit
𝑢2
Tangential Velocity at
Outlet
𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾 𝑢 Speed Ratio
FLOW RATIO:
𝐾𝑓 =
𝑣𝑓2
√2𝑔𝐻
𝐾𝑓 = 0.1 − 0.25
39. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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Symbol Description Unit
𝑣𝑓2 Flow Velocity at Outlet 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾𝑓 Flow Ratio
RECIPROCATING PUMP:
DISCHARGE:
𝑄 =
𝐴𝐿𝑁
60
𝐴 =
𝜋
4
𝐷2 [ 𝐹𝑜𝑟 𝑆𝑖𝑛𝑔𝑙𝑒 𝐴𝑐𝑡𝑖𝑛𝑔 𝑃𝑢𝑚𝑝]
𝐴 = [
𝜋
4
𝐷2
+
𝜋
4
( 𝐷2
− 𝑑2)] [ 𝐹𝑜𝑟 𝐷𝑜𝑢𝑏𝑙𝑒 𝐴𝑐𝑡𝑖𝑛𝑔 𝑃𝑢𝑚𝑝]
Symbol Description Unit
𝐴 Area of Cylinder 𝑚2
𝐿 Stroke Length 𝑚
𝑁 Speed 𝑟𝑝𝑚
𝐷
Diameter of Cylinder or
Bore
𝑚
𝑑 Diameter of Piston Rod 𝑚
WEIGHT OF THE WATER DELIVERED PER SECOND:
𝑊 = 𝜌𝑔𝑄
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝑊 Weight of Water 𝑁
𝑠⁄
40. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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WORK DONE BY RECIPROCATING PUMP:
𝑊 = 𝜌𝑔𝑄𝐻
𝐻 = ℎ 𝑠 + ℎ 𝑑
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
𝑊 Work Done 𝑊
ℎ 𝑠 Suction Head 𝑚
ℎ 𝑑 Delivery Head 𝑚
POWER DEVELOPED BY RECIPROCATING PUMP:
𝑃 = 𝜌𝑔𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 Actual Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
POWER REQUIRED TO DRIVE THE PUMP:
𝑃 = 𝜌𝑔𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 Theoretical Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
41. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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SLIP OF RECIPROCATING PUMP:
𝑆 = 𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 − 𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙
Symbol Description Unit
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 Actual Discharge 𝑚3
𝑠⁄
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 Theoretical Discharge 𝑚3
𝑠⁄
COEFFICENT OF DISCHARGE:
𝐶 𝑑 =
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙
Symbol Description Unit
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 Actual Discharge 𝑚3
𝑠⁄
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 Theoretical Discharge 𝑚3
𝑠⁄
PERCENTAGE OF SLIP IN RECIPROCATING PUMP:
% 𝑜𝑓 𝑆𝑙𝑖𝑝 =
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 − 𝑄 𝐴𝑐𝑡𝑢𝑎𝑙
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙
% 𝑜𝑓 𝑆𝑙𝑖𝑝 = 1 − 𝐶 𝑑
Symbol Description Unit
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 Actual Discharge 𝑚3
𝑠⁄
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 Theoretical Discharge 𝑚3
𝑠⁄
𝐶 𝑑 Coefficient of Discharge
VOLUMETRIC EFFICIENCY:
𝜂 𝑉𝑜𝑙 =
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙
= 𝐶 𝑑
Symbol Description Unit
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 Actual Discharge 𝑚3
𝑠⁄
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙
Theoretical Discharge 𝑚3
𝑠⁄
𝐶 𝑑
Coefficient of Discharge
42. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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MECHANICAL EFFICIENCY:
𝜂 𝑚𝑒𝑐ℎ =
𝑃𝑜𝑤𝑒𝑟 𝐷𝑒𝑣𝑒𝑙𝑜𝑝𝑒𝑑 𝑏𝑦 𝑃𝑢𝑚𝑝
𝑃𝑜𝑤𝑒𝑟 𝑅𝑒𝑞𝑢𝑖𝑟𝑒𝑑 𝑡𝑜 𝐷𝑟𝑖𝑣𝑒 𝑡ℎ𝑒 𝑃𝑢𝑚𝑝
𝜂 𝑚𝑒𝑐ℎ =
𝑃𝑜𝑤𝑒𝑟 𝑜𝑓 𝑃𝑢𝑚𝑝
𝑃𝑜𝑤𝑒𝑟 𝑜𝑓 𝑀𝑜𝑡𝑜𝑟
𝜂 𝑚𝑒𝑐ℎ =
𝜌𝑔𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 𝐻
𝜌𝑔𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 𝐴𝑐𝑡𝑢𝑎𝑙 Actual Discharge 𝑚3
𝑠⁄
𝑄 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 Theoretical Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
ACCELERATION HEAD:
ℎ 𝑎𝑠 =
𝑙 𝑠
𝑔
∗
𝐴
𝑎 𝑠
∗ 𝜔2
∗ 𝑟 ∗ 𝑐𝑜𝑠𝜃 [ 𝐴𝑡 𝑆𝑢𝑐𝑡𝑖𝑜𝑛 𝑆𝑡𝑟𝑜𝑘𝑒]
ℎ 𝑑𝑠 =
𝑙 𝑑
𝑔
∗
𝐴
𝑎 𝑑
∗ 𝜔2
∗ 𝑟 ∗ 𝑐𝑜𝑠𝜃 [ 𝐴𝑡 𝐷𝑒𝑙𝑖𝑣𝑒𝑟𝑦 𝑆𝑡𝑟𝑜𝑘𝑒]
𝐴 =
𝜋
4
𝐷2
𝑎 𝑠 =
𝜋
4
𝑑 𝑠
2
𝑎 𝑑 =
𝜋
4
𝑑 𝑑
2
𝜔 =
2𝜋𝑁
60
43. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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𝑟 =
𝐿
2
Symbol Description Unit
𝑙 𝑠 Length of Suction Pipe 𝑚
𝑙 𝑑 Length of Delivery Pipe 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐴 Area of Cylinder 𝑚2
𝑎 𝑠 Area of Suction Pipe 𝑚2
𝑎 𝑑 Area of Delivery Pipe 𝑚2
𝜔 Angular Speed 𝑟𝑎𝑑
𝑠⁄
𝑟 Radius of Crank 𝑚
𝜃 Angle of Crank 𝑑𝑒𝑔𝑟𝑒𝑒
𝐷
Diameter of Cylinder or
Bore
𝑚
𝑑 𝑠 Diameter of Suction Pipe 𝑚
𝑑 𝑑 Diameter of Delivery Pipe 𝑚
𝑁 Speed of Crank 𝑟𝑝𝑚
𝐿 Stroke Length 𝑚
PRESSURE HEAD:
𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝐻𝑒𝑎𝑑 = ℎ 𝑠 + ℎ 𝑎𝑠 [ 𝐹𝑜𝑟 𝑆𝑢𝑐𝑡𝑖𝑜𝑛 𝑆𝑡𝑟𝑜𝑘𝑒]
𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝐻𝑒𝑎𝑑 = ℎ 𝑑 + ℎ 𝑎𝑑 [ 𝐹𝑜𝑟 𝐷𝑒𝑙𝑖𝑣𝑒𝑟𝑦 𝑆𝑡𝑟𝑜𝑘𝑒]
Symbol Description Unit
ℎ 𝑠 Suction Head 𝑚
ℎ 𝑑 Delivery Head 𝑚
ℎ 𝑎𝑠
Acceleration Head at
Suction
𝑚
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ℎ 𝑎𝑑
Acceleration Head at
Delivery
𝑚
ABSOLUTE PRESSURE HEAD:
𝐴𝑏𝑠𝑜𝑙𝑢𝑡𝑒 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝐻𝑒𝑎𝑑
= 𝐻 𝑎𝑡𝑚 − (ℎ 𝑠 + ℎ 𝑎𝑠) [ 𝐹𝑜𝑟 𝑆𝑢𝑐𝑡𝑖𝑜𝑛 𝑆𝑡𝑟𝑜𝑘𝑒]
𝐴𝑏𝑠𝑜𝑙𝑢𝑡𝑒 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝐻𝑒𝑎𝑑
= 𝐻 𝑎𝑡𝑚 + (ℎ 𝑑 + ℎ 𝑎𝑑 ) [ 𝐹𝑜𝑟 𝐷𝑒𝑙𝑖𝑣𝑒𝑟𝑦 𝑆𝑡𝑟𝑜𝑘𝑒]
Symbol Description Unit
ℎ 𝑠 Suction Head 𝑚
ℎ 𝑑 Delivery Head 𝑚
ℎ 𝑎𝑠
Acceleration Head at
Suction
𝑚
ℎ 𝑎𝑑
Acceleration Head at
Delivery
𝑚
𝐻 𝑎𝑡𝑚
Atmospheric Pressure
Head
𝑚
SEPARATION HEAD:
𝑃𝑠𝑒𝑝 = 𝜌𝑔ℎ 𝑆𝑒𝑝
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
ℎ 𝑠𝑒𝑝 Separation Head 𝑚
𝑃𝑠𝑒𝑝 Separation Pressure 𝑁
𝑚2⁄
HEAD LOSS WITHOUT AIR VESSEL:
ℎ 𝑓𝑊𝑂𝐴 =
4𝑓𝑙 𝑑 𝑣2
2𝑔𝑑 𝑑
Symbol Description Unit
𝑓 Friction Factor
𝑙 𝑑 Length of Delivery Pipe 𝑚
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𝑣
Velocity without Air
Vessel
𝑚
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝑑 𝑑 Diameter of Delivery Pipe 𝑚
VELOCITY WITHOUT AIR VESSEL:
𝑣 =
𝐴
𝑎 𝑑
∗ 𝜔 ∗ 𝑟
𝐴 =
𝜋
4
𝐷2
𝑎 𝑑 =
𝜋
4
𝑑 𝑑
2
𝜔 =
2𝜋𝑁
60
𝑟 =
𝐿
2
Symbol Description Unit
𝐴 Area of Cylinder 𝑚2
𝑎 𝑑 Area of Delivery Pipe 𝑚2
𝜔 Angular Speed 𝑟𝑎𝑑
𝑠⁄
𝑟 Radius of Crank 𝑚
𝐷
Diameter of Cylinder or
Bore
𝑚
𝑑 𝑑 Diameter of Delivery Pipe 𝑚
𝑁 Speed of Crank 𝑟𝑝𝑚
𝐿 Stroke Length 𝑚
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HEAD LOSS WITH AIR VESSEL:
ℎ 𝑓𝑊𝐴 =
4𝑓𝑙 𝑑 𝑣2
2𝑔𝑑 𝑑
Symbol Description Unit
𝑓 Friction Factor
𝑙 𝑑 Length of Delivery Pipe 𝑚
𝑣 Velocity with Air Vessel 𝑚
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝑑 𝑑 Diameter of Delivery Pipe 𝑚
VELOCITY WITH AIR VESSEL:
𝑣 =
𝐴
𝑎 𝑑
∗ 𝜔 ∗
𝑟
𝜋
𝐴 =
𝜋
4
𝐷2
𝑎 𝑑 =
𝜋
4
𝑑 𝑑
2
𝜔 =
2𝜋𝑁
60
𝑟 =
𝐿
2
Symbol Description Unit
𝐴 Area of Cylinder 𝑚2
𝑎 𝑑 Area of Delivery Pipe 𝑚2
𝜔 Angular Speed 𝑟𝑎𝑑
𝑠⁄
𝑟 Radius of Crank 𝑚
𝐷
Diameter of Cylinder or
Bore
𝑚
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𝑑 𝑑 Diameter of Delivery Pipe 𝑚
𝑁 Speed of Crank 𝑟𝑝𝑚
𝐿 Stroke Length 𝑚
POWER SAVED BY AIR VESSEL:
𝑃 = 𝜌𝑔𝑄 (
2
3
ℎ 𝑓𝑊𝑂𝐴 − ℎ 𝑓𝑊𝐴)
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
ℎ 𝑓𝑊𝑂𝐴
Head Loss Without Air
Vessel
𝑚
ℎ 𝑓𝑊𝐴 Head Loss With Air Vessel 𝑚
POWER REQUIRED TO DRIVE THE PUMP:
𝑃 = 𝜌𝑔𝑄 (ℎ 𝑠 + ℎ 𝑑 +
2
3
ℎ 𝑓𝑠𝑊𝑂𝐴 + ℎ 𝑓𝑑𝑊𝐴)
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
ℎ 𝑠 Suction Head 𝑚
ℎ 𝑑 Delivery Head 𝑚
ℎ 𝑓𝑠𝑊𝑂𝐴
Head Loss Without Air
Vessel at Suction
𝑚
ℎ 𝑓𝑑𝑊𝐴
Head Loss With Air Vessel
at Delivery
𝑚
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PELTON WHEEL:
Symbol Description Unit
𝑢1&𝑢2
Tangential Velocity of
Runner at Inlet & Outlet
𝑚
𝑠⁄
𝑣 𝑟1&𝑣 𝑟2
Relative Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑉1&𝑉2
Absolute Velocity at Inlet
& Outlet
𝑚
𝑠⁄
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝛽
Angle made by Absolute
Velocity at Outlet with the
Direction of Motion of
Vane
Degree
𝜙
Angle made by Relative
Velocity at Outlet with the
Direction of Motion of
Vane
Degree
UNIT – V – TURBINES
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TANGENTIAL VELOCITY AT INLET AND OUTLET (OR) VELOCITY OF
WHEEL:
𝑢 =
𝜋𝐷𝑁
60
Symbol Description Unit
𝐷 Diameter of Runner 𝑚
𝑁 Speed of Impeller 𝑟𝑝𝑚
VELOCITY OF JET:
𝑉1 = 𝐶𝑣√2𝑔𝐻
𝐶𝑣 = 0.97 − 0.99
Symbol Description Unit
𝐶𝑣 Coefficient of Velocity
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
VELOCITY OF WHEEL:
𝑢 = 𝑘 𝑢√2𝑔𝐻
𝑘 𝑢 = 0.43 − 0.45
Symbol Description Unit
𝑘 𝑢 Speed Ratio
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
FROM INLET VELOCITY TRIANGLE DIAGRAM:
𝑉 𝑤1 = 𝑉1
𝑉 𝑤1 = 𝑢1 + 𝑉𝑟1
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Symbol Description Unit
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑉1 Absolute Velocity at Inlet 𝑚
𝑠⁄
FROM OUTLET VELOCITY TRIANGLE DIAGRAM:
cos 𝜙 =
𝑢2 + 𝑣 𝑤2
𝑣 𝑟2
tan 𝜙 =
𝑣𝑓2
𝑢2 + 𝑣 𝑤2
sin 𝜙 =
𝑣𝑓2
𝑣 𝑟2
tan 𝛽 =
𝑣𝑓2
𝑣 𝑤2
Symbol Description Unit
𝑢2
Tangential Velocity of
Runner at Outlet
𝑚
𝑠⁄
𝑣 𝑟2 Relative Velocity at Outlet 𝑚
𝑠⁄
𝑣 𝑤2 Whirl Velocity at Outlet 𝑚
𝑠⁄
𝑣𝑓2 Flow Velocity at Outlet 𝑚
𝑠⁄
WORK DONE BY JET PER SECOND:
𝑊 = 𝜌𝑄 [ 𝑣 𝑤1 + 𝑣 𝑤2] 𝑢
Symbol Description Unit
𝑢
Tangential Velocity of
Runner
𝑚
𝑠⁄
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
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HYDRAULIC EFFICIENCY:
𝜂ℎ𝑦𝑑 =
2[ 𝑣 𝑤1 + 𝑣 𝑤2] 𝑢
𝑉1
2
Symbol Description Unit
𝑢
Tangential Velocity of
Runner
𝑚
𝑠⁄
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑉1 Absolute Velocity at Inlet 𝑚
𝑠⁄
OVERALL EFFICIENCY:
𝜂 𝑜 =
𝑆ℎ𝑎𝑓𝑡 𝑃𝑜𝑤𝑒𝑟
𝐼𝑛𝑝𝑢𝑡 𝑃𝑜𝑤𝑒𝑟
𝜂 𝑜 =
𝑆. 𝑃
𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
𝑆. 𝑃 Shaft Power 𝑊
DISCHARGE OF SINGLE JET:
𝑞 =
𝜋
4
∗ 𝑑2
∗ 𝑉1
Symbol Description Unit
𝑑 Diameter of Jet 𝑚
𝑉1 Absolute Velocity at Inlet 𝑚
𝑠⁄
𝑞 Discharge of Single Jet 𝑚3
𝑠⁄
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NUMBER OF JET:
𝑛 =
𝑄
𝑞
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝑞 Discharge of Single Jet 𝑚3
𝑠⁄
NUMBER OF BUCKET:
𝑍 = 15 +
𝐷
2𝑑
Symbol Description Unit
𝑑 Diameter of Jet 𝑚
𝐷 Diameter of Runner 𝑚
DIMENSIONS OF BUCKET:
𝐴𝑥𝑖𝑎𝑙 𝑊𝑖𝑑𝑡ℎ 𝐵 = 4.5𝑑
𝑅𝑎𝑑𝑖𝑎𝑙 𝐿𝑒𝑛𝑔𝑡ℎ 𝐿 = 2.5𝑑
𝐷𝑒𝑝𝑡ℎ 𝑜𝑓 𝐵𝑢𝑐𝑘𝑒𝑡 𝑇 = 𝑑
Symbol Description Unit
𝑑 Diameter of Jet 𝑚
KINETIC ENERGY OF JET:
𝐾. 𝐸 𝑜𝑓 𝐽𝑒𝑡 =
1
2
𝑚 𝑉1
2
𝑆𝑖𝑛𝑐𝑒 𝑚 = 𝜌𝐴𝑉
𝑇ℎ𝑒𝑟𝑒𝑓𝑜𝑟𝑒 𝐾. 𝐸 𝑜𝑓 𝐽𝑒𝑡 =
1
2
𝜌 ∗ 𝐴 ∗ 𝑉1 ∗ 𝑉1
2
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𝑆𝑖𝑛𝑐𝑒 𝑄 = 𝐴𝑉
𝑇ℎ𝑒𝑟𝑒𝑓𝑜𝑟𝑒 𝐾. 𝐸 𝑜𝑓 𝐽𝑒𝑡 =
1
2
𝜌 ∗ 𝑄 ∗ 𝑉1
2
POWER LOST IN NOZZLE:
𝐼𝑛𝑝𝑢𝑡 𝑃𝑜𝑤𝑒𝑟 = 𝐾𝑖𝑛𝑒𝑡𝑖𝑐 𝐸𝑛𝑒𝑟𝑔𝑦 + 𝑃𝑜𝑤𝑒𝑟 𝐿𝑜𝑠𝑡 𝑖𝑛 𝑁𝑜𝑧𝑧𝑙𝑒
POWER LOST IN RUNNER:
𝐼𝑛𝑝𝑢𝑡 𝑃𝑜𝑤𝑒𝑟
= 𝑃𝑜𝑤𝑒𝑟 𝑜𝑓 𝑆ℎ𝑎𝑓𝑡 + 𝑃𝑜𝑤𝑒𝑟 𝐿𝑜𝑠𝑡 𝑖𝑛 𝑁𝑜𝑧𝑧𝑙𝑒
+ 𝑃𝑜𝑤𝑒𝑟 𝐿𝑜𝑠𝑡 𝑖𝑛 𝑅𝑢𝑛𝑛𝑒𝑟
+ 𝑃𝑜𝑤𝑒𝑟 𝐿𝑜𝑠𝑡 𝐷𝑢𝑒 𝑡𝑜 𝑀𝑒𝑐ℎ𝑎𝑛𝑖𝑐𝑎𝑙 𝑅𝑒𝑠𝑖𝑠𝑡𝑎𝑛𝑐𝑒
RESULTANT FORCE ON BUCKET:
𝐹 = 𝜌𝑄 [ 𝑣 𝑤1 + 𝑣 𝑤2]
Symbol Description Unit
𝐹 Resultant Force on Bucket 𝑁
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
TORQUE:
𝑇 = 𝐹 ∗
𝐷
2
Symbol Description Unit
𝐹 Resultant Force on Bucket 𝑁
𝐷 Diameter of Runner 𝑚
𝑇 Torque 𝑁 − 𝑚
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POWER:
𝑃 =
2𝜋𝑁𝑇
60
Symbol Description Unit
𝑃 Power 𝑊
𝑇 Torque 𝑁 − 𝑚
N Speed of Shaft Rpm
SPECIFIC SPEED:
𝑁𝑠 =
𝑁√ 𝑄
𝐻
3
4⁄
𝑁𝑠 =
𝑁√ 𝑃
𝐻
5
4⁄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝐻 Head 𝑚
𝑃 Power 𝑘𝑊
𝑁 Speed 𝑟𝑝𝑚
𝑁𝑠 Specific Speed
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REACTION TURBINE:
INWARD FLOW REACTION TURBINE:
Symbol Description Unit
𝑢1&𝑢2
Tangential Velocity of
Runner at Inlet & Outlet
𝑚
𝑠⁄
𝑣 𝑟1&𝑣 𝑟2
Relative Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑉1&𝑉2
Absolute Velocity at Inlet
& Outlet
𝑚
𝑠⁄
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜙
Angle made by Relative
Velocity at Outlet with the
Degree
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Direction of Motion of
Vane
TANGENTIAL VELOCITY AT INLET:
𝑢1 =
𝜋𝑑1 𝑁
60
Symbol Description Unit
𝑑1
Inlet (or) External
Diameter
𝑚
𝑁 Speed of Turbine 𝑟𝑝𝑚
TANGENTIAL VELOCITY AT OUTLET:
𝑢2 =
𝜋𝑑2 𝑁
60
Symbol Description Unit
𝑑2
Outlet (or) Internal
Diameter
𝑚
𝑁 Speed of Turbine 𝑟𝑝𝑚
FROM INLET VELOCITY TRIANGLE DIAGRAM:
sin 𝛼 =
𝑣𝑓1
𝑉1
cos 𝛼 =
𝑣 𝑤1
𝑉1
tan 𝛼 =
𝑣𝑓1
𝑣 𝑤1
sin 𝜃 =
𝑣𝑓1
𝑣 𝑟1
cos 𝜃 =
𝑣 𝑤1 − 𝑢1
𝑣 𝑟1
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tan 𝜃 =
𝑣𝑓1
𝑣 𝑤1 − 𝑢1
Symbol Description Unit
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑉1 Absolute Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
RELATIVE VELOCITY AT INLET:
𝑣 𝑟1 = √ 𝑣𝑓1
2 + ( 𝑣 𝑤1 − 𝑢1)2
Symbol Description Unit
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
DISCHARGE:
𝑄 = 𝜋𝑑1 𝑏1 𝑣𝑓1 = 𝜋𝑑2 𝑏2 𝑣𝑓2
𝑄 = 𝐴𝑣𝑓1 = 𝐴𝑣𝑓2 = 𝐴 𝑓1 𝑣𝑓1 = 𝐴 𝑓2 𝑣𝑓2
Symbol Description Unit
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𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑑1&𝑑2
Diameter of Impeller at
Inlet & Outlet
𝑚
𝑏1&𝑏2
Width of Impeller at Inlet
& Outlet
𝑚
𝑄 Discharge 𝑚3
𝑠⁄
𝐴 Area of Runner 𝑚2
𝐴 𝑓1&𝐴 𝑓2
Area of Flow at Inlet &
Outlet
𝑚
𝑠⁄
MASS OF WATER FLOWING THROUGH THE RUNNER:
𝑚 = 𝜌 𝑄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
HEAD AT INLET OF TURBINE:
𝐻 =
1
𝑔
∗ 𝑣 𝑤1 ∗ 𝑢1 +
𝑣𝑓1
2
2𝑔
Symbol Description Unit
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
INPUT POWER TO TURBINE (OR) POWER GIVEN TO TURBINE:
𝑃 = 𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
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𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
POWER DEVELOPED BY TURBINE:
𝑃 = 𝜌 ∗ 𝑄 ∗ 𝑣 𝑤1 ∗ 𝑢1
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
HYDRAULIC EFFICIENCY:
𝜂ℎ𝑦𝑑 =
𝑣 𝑤1 𝑢1
𝑔𝐻
𝜂ℎ𝑦𝑑 =
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡 − 𝐻𝑒𝑎𝑑 𝐿𝑜𝑠𝑠
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡
Symbol Description Unit
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
OVERALL EFFICIENCY:
𝜂 𝑜 =
𝑆ℎ𝑎𝑓𝑡 𝑃𝑜𝑤𝑒𝑟
𝐼𝑛𝑝𝑢𝑡 𝑃𝑜𝑤𝑒𝑟
𝜂 𝑜 =
𝑆. 𝑃
𝜌𝑔𝑄𝐻
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Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
𝑆. 𝑃 Shaft Power 𝑊
SPEED RATIO:
𝐾 𝑢 =
𝑢
√2𝑔𝐻
𝐾 𝑢 = 0.6 − 0.9
Symbol Description Unit
𝑢 Tangential Velocity 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾 𝑢 Speed Ratio
FLOW RATIO:
𝐾𝑓 =
𝑣𝑓1
√2𝑔𝐻
𝐾𝑓 = 0.15 − 0.3
Symbol Description Unit
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾𝑓 Flow Ratio
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SPECIFIC SPEED:
𝑁𝑠 =
𝑁√ 𝑄
𝐻
3
4⁄
𝑁𝑠 =
𝑁√ 𝑃
𝐻
5
4⁄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝐻 Head 𝑚
𝑃 Power 𝑘𝑊
𝑁 Speed 𝑟𝑝𝑚
𝑁𝑠 Specific Speed
OUTWARD FLOW REACTION TURBINE:
Symbol Description Unit
𝑢1&𝑢2
Tangential Velocity of
Runner at Inlet & Outlet
𝑚
𝑠⁄
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𝑣 𝑟1&𝑣 𝑟2
Relative Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑉1&𝑉2
Absolute Velocity at Inlet
& Outlet
𝑚
𝑠⁄
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜙
Angle made by Relative
Velocity at Outlet with the
Direction of Motion of
Vane
Degree
TANGENTIAL VELOCITY AT INLET:
𝑢1 =
𝜋𝑑1 𝑁
60
Symbol Description Unit
𝑑1 Inlet (or) Internal Diameter 𝑚
𝑁 Speed of Turbine 𝑟𝑝𝑚
TANGENTIAL VELOCITY AT OUTLET:
𝑢2 =
𝜋𝑑2 𝑁
60
Symbol Description Unit
𝑑2
Outlet (or) External
Diameter
𝑚
𝑁 Speed of Turbine 𝑟𝑝𝑚
FROM INLET VELOCITY TRIANGLE DIAGRAM:
63. R.M.K COLLEGE OF ENGG AND TECH / AQ / R2013/ CE6451 / III / MECH / JUNE 2017 – NOV 2017
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sin 𝛼 =
𝑣𝑓1
𝑉1
cos 𝛼 =
𝑣 𝑤1
𝑉1
tan 𝛼 =
𝑣𝑓1
𝑣 𝑤1
sin 𝜃 =
𝑣𝑓1
𝑣 𝑟1
cos 𝜃 =
𝑣 𝑤1 − 𝑢1
𝑣 𝑟1
tan 𝜃 =
𝑣𝑓1
𝑣 𝑤1 − 𝑢1
Symbol
Description Unit
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑉1 Absolute Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
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RELATIVE VELOCITY AT INLET:
𝑣 𝑟1 = √ 𝑣𝑓1
2 + ( 𝑣 𝑤1 − 𝑢1)2
Symbol Description Unit
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
DISCHARGE:
𝑄 = 𝜋𝑑1 𝑏1 𝑣𝑓1 = 𝜋𝑑2 𝑏2 𝑣𝑓2
𝑄 = 𝐴𝑣𝑓1 = 𝐴𝑣𝑓2 = 𝐴 𝑓1 𝑣𝑓1 = 𝐴 𝑓2 𝑣𝑓2
Symbol Description Unit
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑑1&𝑑2
Diameter of Impeller at
Inlet & Outlet
𝑚
𝑏1&𝑏2
Width of Impeller at Inlet
& Outlet
𝑚
𝑄 Discharge 𝑚3
𝑠⁄
𝐴 Area of Runner 𝑚2
𝐴 𝑓1&𝐴 𝑓2
Area of Flow at Inlet &
Outlet
𝑚
𝑠⁄
MASS OF WATER FLOWING THROUGH THE RUNNER:
𝑚 = 𝜌 𝑄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
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INPUT POWER TO TURBINE (OR) POWER GIVEN TO TURBINE:
𝑃 = 𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
POWER DEVELOPED BY TURBINE:
𝑃 = 𝜌 ∗ 𝑄 ∗ 𝑣 𝑤1 ∗ 𝑢1
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
HYDRAULIC EFFICIENCY:
𝜂ℎ𝑦𝑑 =
𝑣 𝑤1 𝑢1
𝑔𝐻
𝜂ℎ𝑦𝑑 =
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡 − 𝐻𝑒𝑎𝑑 𝐿𝑜𝑠𝑠
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡
Symbol Description Unit
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
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OVERALL EFFICIENCY:
𝜂 𝑜 =
𝑆ℎ𝑎𝑓𝑡 𝑃𝑜𝑤𝑒𝑟
𝐼𝑛𝑝𝑢𝑡 𝑃𝑜𝑤𝑒𝑟
𝜂 𝑜 =
𝑆. 𝑃
𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
𝑆. 𝑃 Shaft Power 𝑊
SPEED RATIO:
𝐾 𝑢 =
𝑢
√2𝑔𝐻
𝐾 𝑢 = 0.6 − 0.9
Symbol Description Unit
𝑢 Tangential Velocity 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾 𝑢 Speed Ratio
FLOW RATIO:
𝐾𝑓 =
𝑣𝑓1
√2𝑔𝐻
𝐾𝑓 = 0.15 − 0.3
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Symbol Description Unit
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾𝑓 Flow Ratio
SPECIFIC SPEED:
𝑁𝑠 =
𝑁√ 𝑄
𝐻
3
4⁄
𝑁𝑠 =
𝑁√ 𝑃
𝐻
5
4⁄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝐻 Head 𝑚
𝑃 Power 𝑘𝑊
𝑁 Speed 𝑟𝑝𝑚
𝑁𝑠 Specific Speed
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FRANCIS TURBINE:
Symbol Description Unit
𝑢1&𝑢2
Tangential Velocity of
Runner at Inlet & Outlet
𝑚
𝑠⁄
𝑣 𝑟1&𝑣 𝑟2
Relative Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑉1&𝑉2
Absolute Velocity at Inlet
& Outlet
𝑚
𝑠⁄
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜙
Angle made by Relative
Velocity at Outlet with the
Direction of Motion of
Vane
Degree
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TANGENTIAL VELOCITY AT INLET:
𝑢1 =
𝜋𝑑1 𝑁
60
Symbol Description Unit
𝑑1
Inlet (or) External
Diameter
𝑚
𝑁 Speed of Turbine 𝑟𝑝𝑚
TANGENTIAL VELOCITY AT OUTLET:
𝑢2 =
𝜋𝑑2 𝑁
60
Symbol Description Unit
𝑑2
Outlet (or) Internal
Diameter
𝑚
𝑁 Speed of Turbine 𝑟𝑝𝑚
FROM INLET VELOCITY TRIANGLE DIAGRAM:
sin 𝛼 =
𝑣𝑓1
𝑉1
cos 𝛼 =
𝑣 𝑤1
𝑉1
tan 𝛼 =
𝑣𝑓1
𝑣 𝑤1
sin 𝜃 =
𝑣𝑓1
𝑣 𝑟1
cos 𝜃 =
𝑣 𝑤1 − 𝑢1
𝑣 𝑟1
tan 𝜃 =
𝑣𝑓1
𝑣 𝑤1 − 𝑢1
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Symbol Description Unit
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑉1 Absolute Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
RELATIVE VELOCITY AT INLET:
𝑣 𝑟1 = √ 𝑣𝑓1
2 + ( 𝑣 𝑤1 − 𝑢1)2
Symbol Description Unit
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
DISCHARGE:
𝑄 = 𝜋𝑑1 𝑏1 𝑣𝑓1 = 𝜋𝑑2 𝑏2 𝑣𝑓2
𝑄 = 𝐴𝑣𝑓1 = 𝐴𝑣𝑓2 = 𝐴 𝑓1 𝑣𝑓1 = 𝐴 𝑓2 𝑣𝑓2
Symbol Description Unit
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑑1&𝑑2
Diameter of Impeller at
Inlet & Outlet
𝑚
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𝑏1&𝑏2
Width of Impeller at Inlet
& Outlet
𝑚
𝑄 Discharge 𝑚3
𝑠⁄
𝐴 Area of Runner 𝑚2
𝐴 𝑓1&𝐴 𝑓2
Area of Flow at Inlet &
Outlet
𝑚
𝑠⁄
CIRCUMFERENTIAL AREA OF RUNNER:
𝐴 = 𝜋𝑑1 𝑏1 = 𝜋𝑑2 𝑏2
Symbol Description Unit
𝑑1&𝑑2
Diameter of Impeller at
Inlet & Outlet
𝑚
𝑏1&𝑏2
Width of Impeller at Inlet
& Outlet
𝑚
𝐴
Circumferential Area of
Runner
𝑚2
MASS OF WATER FLOWING THROUGH THE RUNNER:
𝑚 = 𝜌 𝑄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
INPUT POWER TO TURBINE (OR) POWER GIVEN TO TURBINE:
𝑃 = 𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
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POWER DEVELOPED BY TURBINE:
𝑃 = 𝜌 ∗ 𝑄 ∗ 𝑣 𝑤1 ∗ 𝑢1
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
HYDRAULIC EFFICIENCY:
𝜂ℎ𝑦𝑑 =
𝑣 𝑤1 𝑢1
𝑔𝐻
𝜂ℎ𝑦𝑑 =
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡 − 𝐻𝑒𝑎𝑑 𝐿𝑜𝑠𝑠
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡
Symbol Description Unit
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
OVERALL EFFICIENCY:
𝜂 𝑜 =
𝑆ℎ𝑎𝑓𝑡 𝑃𝑜𝑤𝑒𝑟
𝐼𝑛𝑝𝑢𝑡 𝑃𝑜𝑤𝑒𝑟
𝜂 𝑜 =
𝑆. 𝑃
𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
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𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
𝑆. 𝑃 Shaft Power 𝑊
SPEED RATIO:
𝐾 𝑢 =
𝑢
√2𝑔𝐻
𝐾 𝑢 = 0.6 − 0.9
Symbol Description Unit
𝑢 Tangential Velocity 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾 𝑢 Speed Ratio
FLOW RATIO:
𝐾𝑓 =
𝑣𝑓1
√2𝑔𝐻
𝐾𝑓 = 0.15 − 0.3
Symbol Description Unit
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾𝑓 Flow Ratio
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BREADTH RATIO:
𝑛 =
𝑏1
𝑑1
𝑛 = 0.1 − 0.4
Symbol Description Unit
𝑏1 Width of Runner at Inlet 𝑚
𝑑1 Diameter of Runner at Inlet 𝑚
𝑛 Breadth Ratio
SPECIFIC SPEED:
𝑁𝑠 =
𝑁√ 𝑄
𝐻
3
4⁄
𝑁𝑠 =
𝑁√ 𝑃
𝐻
5
4⁄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝐻 Head 𝑚
𝑃 Power 𝑘𝑊
𝑁 Speed 𝑟𝑝𝑚
𝑁𝑠 Specific Speed
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KAPLAN TURBINE:
Symbol Description Unit
𝑢1&𝑢2
Tangential Velocity of
Runner at Inlet & Outlet
𝑚
𝑠⁄
𝑣 𝑟1&𝑣 𝑟2
Relative Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑣 𝑤1&𝑣 𝑤2
Whirl Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝑉1&𝑉2
Absolute Velocity at Inlet
& Outlet
𝑚
𝑠⁄
𝑣𝑓1&𝑣𝑓2
Flow Velocity at Inlet &
Outlet
𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜙
Angle made by Relative
Velocity at Outlet with the
Direction of Motion of
Vane
Degree
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TANGENTIAL VELOCITY AT INLET:
𝑢1 =
𝜋𝐷 𝑜 𝑁
60
Symbol Description Unit
𝐷 𝑜
Inlet (or) External
Diameter
𝑚
𝑁 Speed of Turbine 𝑟𝑝𝑚
TANGENTIAL VELOCITY AT OUTLET:
𝑢2 =
𝜋𝐷 𝑏 𝑁
60
=
𝜋𝐷ℎ 𝑁
60
Symbol Description Unit
𝐷 𝑏 𝑜𝑟 𝐷ℎ
Outlet (or) Boss (or) Hub
Diameter
𝑚
𝑁 Speed of Turbine 𝑟𝑝𝑚
FROM INLET VELOCITY TRIANGLE DIAGRAM:
sin 𝛼 =
𝑣𝑓1
𝑉1
cos 𝛼 =
𝑣 𝑤1
𝑉1
tan 𝛼 =
𝑣𝑓1
𝑣 𝑤1
sin 𝜃 =
𝑣𝑓1
𝑣 𝑟1
cos 𝜃 =
𝑣 𝑤1 − 𝑢1
𝑣 𝑟1
tan 𝜃 =
𝑣𝑓1
𝑣 𝑤1 − 𝑢1
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Symbol Description Unit
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑉1 Absolute Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝛼
Angle made by Absolute
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
𝜃
Angle made by Relative
Velocity at Inlet with the
Direction of Motion of
Vane
Degree
RELATIVE VELOCITY AT INLET:
𝑣 𝑟1 = √ 𝑣𝑓1
2 + ( 𝑣 𝑤1 − 𝑢1)2
Symbol Description Unit
𝑣 𝑟1 Relative Velocity at Inlet 𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
DISCHARGE:
𝑄 =
𝜋
4
[𝐷0
2
− 𝐷 𝑏
2
]𝑣𝑓1
Symbol Description Unit
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝐷0
Inlet (or) External
Diameter
𝑚
𝐷 𝑏 𝑜𝑟 𝐷ℎ
Outlet (or) Boss (or) Hub
Diameter
𝑚
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𝑄 Discharge 𝑚3
𝑠⁄
CIRCUMFERENTIAL AREA OF RUNNER:
𝐴 =
𝜋
4
[𝐷0
2
− 𝐷 𝑏
2
]
Symbol Description Unit
𝐷0
Inlet (or) External
Diameter
𝑚
𝐷 𝑏 𝑜𝑟 𝐷ℎ
Outlet (or) Boss (or) Hub
Diameter
𝑚
𝐴
Circumferential Area of
Runner
𝑚2
MASS OF WATER FLOWING THROUGH THE RUNNER:
𝑚 = 𝜌 𝑄
Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝜌 Density 𝑘𝑔
𝑚3⁄
INPUT POWER TO TURBINE (OR) POWER GIVEN TO TURBINE:
𝑃 = 𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
POWER DEVELOPED BY TURBINE:
𝑃 = 𝜌 ∗ 𝑄 ∗ 𝑣 𝑤1 ∗ 𝑢1
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
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𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
HYDRAULIC EFFICIENCY:
𝜂ℎ𝑦𝑑 =
𝑣 𝑤1 𝑢1
𝑔𝐻
𝜂ℎ𝑦𝑑 =
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡 − 𝐻𝑒𝑎𝑑 𝐿𝑜𝑠𝑠
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡
Symbol Description Unit
𝑢1
Tangential Velocity of
Runner at Inlet
𝑚
𝑠⁄
𝑣 𝑤1 Whirl Velocity at Inlet 𝑚
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
OVERALL EFFICIENCY:
𝜂 𝑜 =
𝑆ℎ𝑎𝑓𝑡 𝑃𝑜𝑤𝑒𝑟
𝐼𝑛𝑝𝑢𝑡 𝑃𝑜𝑤𝑒𝑟
𝜂 𝑜 =
𝑆. 𝑃
𝜌𝑔𝑄𝐻
Symbol Description Unit
𝜌 Density 𝑘𝑔
𝑚3⁄
𝑄 Discharge 𝑚3
𝑠⁄
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐻 Head 𝑚
𝑆. 𝑃 Shaft Power 𝑊
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SPEED RATIO:
𝐾 𝑢 =
𝑢
√2𝑔𝐻
𝐾 𝑢 = 0.6 − 0.9
Symbol Description Unit
𝑢 Tangential Velocity 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾 𝑢 Speed Ratio
FLOW RATIO:
𝐾𝑓 =
𝑣𝑓1
√2𝑔𝐻
𝐾𝑓 = 0.15 − 0.3
Symbol Description Unit
𝑣𝑓1 Flow Velocity at Inlet 𝑚
𝑠⁄
𝐻 Head 𝑚
𝑔
Acceleration due to
Gravity
𝑚
𝑠2⁄
𝐾𝑓 Flow Ratio
SPECIFIC SPEED:
𝑁𝑠 =
𝑁√ 𝑄
𝐻
3
4⁄
𝑁𝑠 =
𝑁√ 𝑃
𝐻
5
4⁄
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Symbol Description Unit
𝑄 Discharge 𝑚3
𝑠⁄
𝐻 Head 𝑚
𝑃 Power 𝑘𝑊
𝑁 Speed 𝑟𝑝𝑚
𝑁𝑠 Specific Speed
DRAFT TUBE:
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Symbol Description Unit
𝑉1&𝑉2 Velocity at Inlet & Outlet 𝑚
𝑠⁄
𝐻𝑠
Vertical Height of Draft
Tube Above Tail Race
𝑚
𝑦
Distance of Bottom of
Draft Tube from Tail Race
𝑚
FROM BERNOULLI’S EQUATION:
𝑃1
𝜌𝑔
+
𝑉1
2
2𝑔
+ 𝑧1 =
𝑃2
𝜌𝑔
+
𝑉2
2
2𝑔
+ 𝑧2 + ℎ 𝑓
Symbol Description Unit
𝑃1 & 𝑃2
Pressure at Inlet & Outlet
of Draft Tube
𝑁
𝑚2⁄
𝑉1 & 𝑉2
Velocity at Inlet & Outlet
of Draft Tube
𝑚
𝑠⁄
𝑧1 & 𝑧2
Datum Head Inlet & Outlet
of Draft Tube
𝑚
ℎ 𝑓 Head Loss 𝑚
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
LENGTH OF DRAFT TUBE:
𝐿 = 𝐻𝑠 + 𝑦
Symbol Description Unit
𝐿 Length of Draft Tube 𝑚
𝐻𝑠
Vertical Height of Draft
Tube Above Tail Race
𝑚
𝑦
Distance of Bottom of
Draft Tube from Tail Race
𝑚
EFFICIENCY OF DRAFT TUBE:
𝜂 𝑑 =
(
𝑉1
2
2𝑔
−
𝑉2
2
2𝑔
) − ℎ 𝑓
𝑉1
2
2𝑔
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Symbol Description Unit
𝑉1 & 𝑉2
Velocity at Inlet & Outlet
of Draft Tube
𝑚
𝑠⁄
ℎ 𝑓 Head Loss 𝑚
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄
HYDRAULIC EFFICIENCY OF DRAFT TUBE:
𝜂ℎ𝑦𝑑 =
𝐻𝑒𝑎𝑑 𝑈𝑡𝑖𝑙𝑖𝑧𝑒𝑑 𝑏𝑦 𝑇𝑢𝑟𝑏𝑖𝑛𝑒
𝐻𝑒𝑎𝑑 𝐼𝑛𝑙𝑒𝑡 𝑜𝑓 𝑇𝑢𝑟𝑏𝑖𝑛𝑒
𝜂ℎ𝑦𝑑 =
𝐻 − ℎ 𝑓𝑡 − ℎ 𝑓𝑑 −
𝑉2
2
2𝑔
𝑃1
𝜌𝑔
+
𝑉1
2
2𝑔
+ 𝑧1
Symbol Description Unit
𝑃1
Pressure at Inlet of Draft
Tube
𝑁
𝑚2⁄
𝑉1 & 𝑉2
Velocity at Inlet & Outlet
of Draft Tube
𝑚
𝑠⁄
𝑧1
Datum Head Inlet of Draft
Tube
𝑚
ℎ 𝑓 Head Loss 𝑚
𝜌 Density of Liquid 𝑘𝑔
𝑚3⁄
𝑔 Acceleration due to gravity 𝑚
𝑠2⁄