This document provides instructions for experiments on various turbomachines and pumps in the Mechanical Engineering Department of Aksum University. It includes procedures for determining the efficiency of a Pelton turbine, reaction turbine, axial turbine, and centrifugal pump. Formulas are provided for calculating mechanical power, hydraulic power, head, efficiency, and specific speed. Turbine tests involve varying the brake torque to obtain torque-speed characteristics while pumps are tested by varying the discharge.
Production Process 1 Mechanical Engineering Handwritten classes Notes (Study ...Khagendra Gautam
Production Process manufacturing technology
material science Mechanical Engineering Handwritten classes Notes (Study Materials) for IES PSUs GATE
Gate ME (Mechanical Engineering) Made Easy Handwritten coaching classes Notes (Study Materials) for IES PSUs GATE
1. A vehicle frame provides the main structure and supports all other vehicle components.
2. Frames can be classified as conventional, integral, or semi-integral depending on how the frame is constructed and integrated with the body.
3. Common frame types include ladder frames, backbone frames, X-frames, perimeter frames, platform frames, and unibody/unitized frames. Subframes are also used to isolate vibration.
This document discusses different types of hydraulic pumps, including their basic operating principles and comparisons. It provides equations to calculate pump parameters such as theoretical flow rate, volumetric displacement, efficiency, and torque. For example, it defines that positive displacement pumps capture and transfer fixed amounts of fluid, while centrifugal pumps impart velocity to fluid to create pressure. Gear pump displacement can be calculated based on gear dimensions. Pump efficiency is affected by factors like leakage and viscosity.
The document discusses the basics of how a carburetor works. It mixes air and fuel for combustion in internal combustion engines. A carburetor uses Bernoulli's principle - as the speed of the air moving through the venturi increases, the pressure decreases, drawing fuel into the air stream. It has several circuits that control fuel delivery at different engine speeds and throttle positions, including an idle circuit, main circuit, power valve, and accelerator pump. Carburetors rely on a float chamber to maintain the proper fuel level and supply fuel to the carburetor. While carburetors have largely been replaced by fuel injection, they are still commonly used on small engines.
Valve timing diagram is one of the most important topic about engine. This gives u the idea about how engine's valves should open and close. Knowing this u can make your engine more efficient and effective.
This document provides an overview of Computer Aided Process Planning (CAPP). It discusses the general steps in CAPP, including design input, material selection, and cost estimation. It describes two main approaches to CAPP: variant CAPP, which retrieves and modifies existing process plans; and generative CAPP, which generates new plans using decision logic and algorithms. The advantages of CAPP are reducing time/costs and increasing consistency and productivity. The disadvantages include difficulty maintaining consistency and accounting for all manufacturing factors in variant CAPP, and high initial costs compared to manual planning.
The document provides an overview of diesel power plant engineering. It discusses the key components of a diesel power plant including the diesel engine, starting system, fuel supply system, air intake system, lubrication system, cooling system, exhaust system, and governing system. It describes the basic four-stroke operating cycle of a diesel engine and highlights advantages such as simple design and ability to handle varying loads, as well as disadvantages like high operating costs.
Production Process 1 Mechanical Engineering Handwritten classes Notes (Study ...Khagendra Gautam
Production Process manufacturing technology
material science Mechanical Engineering Handwritten classes Notes (Study Materials) for IES PSUs GATE
Gate ME (Mechanical Engineering) Made Easy Handwritten coaching classes Notes (Study Materials) for IES PSUs GATE
1. A vehicle frame provides the main structure and supports all other vehicle components.
2. Frames can be classified as conventional, integral, or semi-integral depending on how the frame is constructed and integrated with the body.
3. Common frame types include ladder frames, backbone frames, X-frames, perimeter frames, platform frames, and unibody/unitized frames. Subframes are also used to isolate vibration.
This document discusses different types of hydraulic pumps, including their basic operating principles and comparisons. It provides equations to calculate pump parameters such as theoretical flow rate, volumetric displacement, efficiency, and torque. For example, it defines that positive displacement pumps capture and transfer fixed amounts of fluid, while centrifugal pumps impart velocity to fluid to create pressure. Gear pump displacement can be calculated based on gear dimensions. Pump efficiency is affected by factors like leakage and viscosity.
The document discusses the basics of how a carburetor works. It mixes air and fuel for combustion in internal combustion engines. A carburetor uses Bernoulli's principle - as the speed of the air moving through the venturi increases, the pressure decreases, drawing fuel into the air stream. It has several circuits that control fuel delivery at different engine speeds and throttle positions, including an idle circuit, main circuit, power valve, and accelerator pump. Carburetors rely on a float chamber to maintain the proper fuel level and supply fuel to the carburetor. While carburetors have largely been replaced by fuel injection, they are still commonly used on small engines.
Valve timing diagram is one of the most important topic about engine. This gives u the idea about how engine's valves should open and close. Knowing this u can make your engine more efficient and effective.
This document provides an overview of Computer Aided Process Planning (CAPP). It discusses the general steps in CAPP, including design input, material selection, and cost estimation. It describes two main approaches to CAPP: variant CAPP, which retrieves and modifies existing process plans; and generative CAPP, which generates new plans using decision logic and algorithms. The advantages of CAPP are reducing time/costs and increasing consistency and productivity. The disadvantages include difficulty maintaining consistency and accounting for all manufacturing factors in variant CAPP, and high initial costs compared to manual planning.
The document provides an overview of diesel power plant engineering. It discusses the key components of a diesel power plant including the diesel engine, starting system, fuel supply system, air intake system, lubrication system, cooling system, exhaust system, and governing system. It describes the basic four-stroke operating cycle of a diesel engine and highlights advantages such as simple design and ability to handle varying loads, as well as disadvantages like high operating costs.
The explanation of Performance parameters of IC engines is as follows.
1.Indicated power (I.P):
The total Power developed by the combustion of the fuel in the combustion chamber is called as Indicated power.
2.Break power (B.P):
The Power developed by an engine at the output shaft is called break power.
For more information, visit https://mechanicalstudents.com/ic-engines/
This document summarizes the testing and performance of diesel and petrol engines. It describes the key components and operating principles of diesel and petrol engines. It then discusses various performance characteristics of internal combustion engines that are used to evaluate engine performance, such as brake thermal efficiency, indicated thermal efficiency, specific fuel consumption, mechanical efficiency, volumetric efficiency, air fuel ratio, and mean effective pressure. The performance of engines is tested by measuring fuel consumption, brake power, and specific power output using various types of dynamometers.
The document discusses traction and tractive effort in vehicles. It defines traction as the friction between a drive wheel and the surface it moves upon. Tractive effort is the force available at the contact between drive wheel tires and the road. Traction control systems monitor each wheel and apply braking or torque to wheels that may be slipping to increase traction. Traction can be increased through methods like decreasing tire pressure, tread design, adding tracks/chains, additional weight, and dynamic weight transfer. Non-electric traction systems include steam and internal combustion engine drives, while electric traction uses diesel-electric or gas turbine electric drives.
1) Engine speed can be measured using a tachometer, counting revolutions, or using a magnetic pick-up with a pulse counter.
2) Fuel consumption is measured by determining the volume flow over time or measuring the time taken to consume a given mass.
3) Air consumption is difficult to measure due to pulsating flow but can be estimated using an orifice and measurements of pressure difference, temperature and flow velocity.
This document provides an overview of dynamics of machines including:
1. It defines force, applied force, constraint forces, and types of constrained motions like completely, incompletely, and successfully constrained motions.
2. It discusses static force analysis, dynamic force analysis, and conditions for static and dynamic equilibrium.
3. It covers concepts like inertia, inertia force, inertia torque, D'Alembert's principle, and principle of superposition.
4. It derives expressions for forces acting on the reciprocating parts of an engine while neglecting the weight of the connecting rod.
The document discusses combustion in spark-ignition (SI) engines. It defines combustion as a chemical reaction in which fuel combines with oxygen, liberating heat energy. In an SI engine, fuel and air are mixed and inducted into the cylinder where combustion is initiated by a spark at the spark plug near the end of the compression stroke. There are three stages of combustion: ignition lag, flame propagation, and after burning. Abnormal combustion phenomena like pre-ignition and knocking can occur if conditions are not suitable. Factors like turbulence, fuel-air ratio, temperature and pressure, compression ratio, and engine variables affect the flame speed and combustion process.
This document provides notes on dynamics of machines from a professor at Kalaignarkarunanidhi Institute of Technology in Coimbatore, India. It covers topics like vibratory motion, types of vibrations including free, forced and damped vibrations. It defines key terms used in vibratory motion like period, cycle, frequency. It describes different types of free vibrations such as longitudinal, transverse and torsional vibrations. Methods to determine the natural frequency of free longitudinal vibration including equilibrium method, energy method and Rayleigh's method are presented. The document also discusses the effect of inertia of constraints in longitudinal vibration and frequency of free damped vibrations. An example problem is given to determine frequency of longitudinal
Thermodynamic Cycles for CI engines
- Early CI engines injected fuel at top dead center, resulting in combustion during the expansion stroke. Modern engines inject fuel before top dead center, around 20 degrees.
- The combustion process in early CI engines approximates a constant pressure heat addition process, known as the Diesel cycle. Modern CI engines' combustion approximates a combination of constant volume and constant pressure processes, known as the Dual cycle.
- The air-standard Diesel cycle consists of four processes: isentropic compression, constant pressure heat addition, isentropic expansion, and constant volume heat rejection. Its thermal efficiency is lower than the Otto cycle for the same compression ratio due to the later fuel injection
Hydraulic accumulator is an accessory of a hydraulic system.
A hydraulic accumulator is a pressure storage reservoir in which a non-compressible hydraulic fluid is held under pressure by an external source.
The external source can be a spring, a raised weight, or a compressed gas. An accumulator enables a hydraulic system to cope with extremes of demand using a less powerful pump, to respond more quickly to a temporary demand, and to smooth out pulsations. It is a type of energy storage device.
Air Injection and Solid Injection SystemParthivpal17
This document summarizes different types of fuel injection systems used in diesel engines. It describes air injection systems which inject fuel along with compressed air, but are not commonly used today. It also discusses solid injection and airless injection systems, categorizing them as common rail, individual pump and injector, or distributor injection systems. The common rail system uses a single high-pressure pump to supply fuel to a header or rail that distributes fuel to each injector. Individual pump systems have a separate pump for each injector. Distributor systems use a central pump and distributor block to time fuel injection.
This presentation discusses reaction turbines. It defines a reaction turbine as a type of turbine that develops torque by reacting to the pressure or weight of a fluid based on Newton's third law of motion. The document outlines the working principle of reaction turbines and describes the main types - radial flow, axial flow, and mixed flow turbines. Examples of specific reaction turbines are provided, including the Francis, Kaplan, and propeller turbines. The advantages and disadvantages of reaction turbines are summarized. Key concepts like pressure compounding, turbine blade stages, and the pressure-velocity diagram for reaction blades are also explained briefly.
This presentation include the information about the different types of superchargers, advantages & disadvantages of superchargers and turbochargers. One case study of variable geometry turbocharger is included with literature review.
The document provides an overview of internal combustion engines. It discusses the basic classifications and cycles of internal combustion engines including two-stroke and four-stroke engines. It also covers the workings of spark ignition and compression ignition engines, as well as common engine components and systems such as carburetors and fuel injection systems. Key topics include the Otto, Diesel, and Carnot power cycles; combustion stages; valve timing diagrams; and scavenging, pre-ignition, detonation, lubrication, and emissions control.
The document discusses different types of engine cycles including ideal, fuel-air, and actual cycles. It provides details on:
- Air standard cycles which are idealized and assume a perfect gas, no mass change, reversible processes, and constant specific heats. Examples include Otto, Diesel, and Dual cycles.
- Fuel-air cycles which are more accurate by considering the actual cylinder gas composition, variable specific heats, incomplete fuel-air mixing at high temps, and dissociation effects.
- Actual engine cycles use even more accurate models of the processes and working fluid, taking into account variable properties and chemical reactions.
This document provides an overview of diesel engines, including their basic operation, components, and fuel injection systems. It describes how diesel engines ignite fuel via compression rather than a spark plug. Key points covered include the types of fuel injection systems (common rail, unit injection, etc.), injectors and nozzles, governors, and applications of diesel engines. The document concludes by comparing diesel engines to gasoline engines and discussing newer direct injection technologies.
Power assisted brakes use either hydraulic or vacuum pressure to reduce the amount of force needed to press the brake pedal. Hydraulic systems use pressure from the power steering pump or an air compressor, while vacuum systems use pressure from the intake manifold. Both types work by creating pressure on one side of a booster piston to multiply the force applied through the brake pedal to the master cylinder. When the pedal is pressed, it closes off the pressure source and applies hydraulic pressure to the brakes. Releasing the pedal vents the booster pressure and allows the pedal to return freely. Servo brakes provide additional braking power needed for heavier vehicles through mechanical, hydraulic, or vacuum assisted systems.
This document provides an overview of compressed air systems, including:
- The types of compressors and their characteristics such as reciprocating, rotary, centrifugal, and axial compressors.
- How compressors work using principles such as the ideal gas law and Bernoulli's equation.
- Factors that affect the energy consumption of compressed air systems such as inlet air conditions, pressure settings, piping layout and leaks.
- Methods for improving efficiency such as variable speed drives, capacity control, and detailed energy audits.
The document discusses compressed air systems in detail over 5 sections, covering the scope of work, types of compressors, selection criteria, performance comparisons, and system components.
This document summarizes key aspects of gasoline direct injection (GDI) engine technology. It discusses the timeline of fuel supply systems from carburetors to port injection to direct injection. The main components of a GDI system are described as the engine control unit, sensors, high pressure fuel pump, and fuel injector. GDI works by directly injecting pressurized fuel into the combustion chamber, allowing for improved efficiency and reduced emissions compared to port fuel injection. Benefits of GDI engines include increased power and torque, reduced fuel consumption and CO2 emissions, and ability to meet future emissions standards.
This document presents a project presentation by six students at Seacom Engineering College on the study and demonstration of the principles of a turbocharger. It includes definitions of a turbocharger and supercharger, explanations of why turbochargers are used instead of superchargers, diagrams of key turbocharger components like the turbine, compressor, shaft, and housing. It also covers the Brayton cycle that turbochargers are based on and comparisons of naturally aspirated versus supercharged engine P-V diagrams. Application areas and improvements in turbocharger performance over time are summarized as well.
PSG Design data book pages for rolling contact bearings designSagar Dhotare
PSG Design data book pages for rolling contact bearings design
This contains following points
Bearing type with application
Equivalent load formula
Dynamic capacity formula
Catalog of DGBB, Roller, Taper Roller Cylindrical or Spherical roller bearing, needle bearing.
This document provides an introduction and overview of notes on the design and analysis of machine elements for students at the University of Western Australia. It outlines the mechanical engineering design course, which introduces design concepts, reviews failure mechanisms, and considers the analysis and design of common machine elements. It explains that the notes are a resource for the entire design course, covering topics like springs, gears, shafts and more. The notes take a simple mathematical approach but emphasize that real-world engineering judgment is also needed. The goal is for students to demonstrate understanding of analysis approaches and ability to modify designs for new problems.
The document discusses the development of an electric car jack that can be automatically operated from inside the vehicle to make changing tires and performing repairs easier, especially for the elderly, disabled, and women. Current manual car jacks require significant physical effort and are difficult to use, while commercial lifts are too large and expensive for individual car owners. The proposed electric screw jack integrated into the vehicle aims to provide automatic and easy lifting of the car for repairs without much physical effort.
The explanation of Performance parameters of IC engines is as follows.
1.Indicated power (I.P):
The total Power developed by the combustion of the fuel in the combustion chamber is called as Indicated power.
2.Break power (B.P):
The Power developed by an engine at the output shaft is called break power.
For more information, visit https://mechanicalstudents.com/ic-engines/
This document summarizes the testing and performance of diesel and petrol engines. It describes the key components and operating principles of diesel and petrol engines. It then discusses various performance characteristics of internal combustion engines that are used to evaluate engine performance, such as brake thermal efficiency, indicated thermal efficiency, specific fuel consumption, mechanical efficiency, volumetric efficiency, air fuel ratio, and mean effective pressure. The performance of engines is tested by measuring fuel consumption, brake power, and specific power output using various types of dynamometers.
The document discusses traction and tractive effort in vehicles. It defines traction as the friction between a drive wheel and the surface it moves upon. Tractive effort is the force available at the contact between drive wheel tires and the road. Traction control systems monitor each wheel and apply braking or torque to wheels that may be slipping to increase traction. Traction can be increased through methods like decreasing tire pressure, tread design, adding tracks/chains, additional weight, and dynamic weight transfer. Non-electric traction systems include steam and internal combustion engine drives, while electric traction uses diesel-electric or gas turbine electric drives.
1) Engine speed can be measured using a tachometer, counting revolutions, or using a magnetic pick-up with a pulse counter.
2) Fuel consumption is measured by determining the volume flow over time or measuring the time taken to consume a given mass.
3) Air consumption is difficult to measure due to pulsating flow but can be estimated using an orifice and measurements of pressure difference, temperature and flow velocity.
This document provides an overview of dynamics of machines including:
1. It defines force, applied force, constraint forces, and types of constrained motions like completely, incompletely, and successfully constrained motions.
2. It discusses static force analysis, dynamic force analysis, and conditions for static and dynamic equilibrium.
3. It covers concepts like inertia, inertia force, inertia torque, D'Alembert's principle, and principle of superposition.
4. It derives expressions for forces acting on the reciprocating parts of an engine while neglecting the weight of the connecting rod.
The document discusses combustion in spark-ignition (SI) engines. It defines combustion as a chemical reaction in which fuel combines with oxygen, liberating heat energy. In an SI engine, fuel and air are mixed and inducted into the cylinder where combustion is initiated by a spark at the spark plug near the end of the compression stroke. There are three stages of combustion: ignition lag, flame propagation, and after burning. Abnormal combustion phenomena like pre-ignition and knocking can occur if conditions are not suitable. Factors like turbulence, fuel-air ratio, temperature and pressure, compression ratio, and engine variables affect the flame speed and combustion process.
This document provides notes on dynamics of machines from a professor at Kalaignarkarunanidhi Institute of Technology in Coimbatore, India. It covers topics like vibratory motion, types of vibrations including free, forced and damped vibrations. It defines key terms used in vibratory motion like period, cycle, frequency. It describes different types of free vibrations such as longitudinal, transverse and torsional vibrations. Methods to determine the natural frequency of free longitudinal vibration including equilibrium method, energy method and Rayleigh's method are presented. The document also discusses the effect of inertia of constraints in longitudinal vibration and frequency of free damped vibrations. An example problem is given to determine frequency of longitudinal
Thermodynamic Cycles for CI engines
- Early CI engines injected fuel at top dead center, resulting in combustion during the expansion stroke. Modern engines inject fuel before top dead center, around 20 degrees.
- The combustion process in early CI engines approximates a constant pressure heat addition process, known as the Diesel cycle. Modern CI engines' combustion approximates a combination of constant volume and constant pressure processes, known as the Dual cycle.
- The air-standard Diesel cycle consists of four processes: isentropic compression, constant pressure heat addition, isentropic expansion, and constant volume heat rejection. Its thermal efficiency is lower than the Otto cycle for the same compression ratio due to the later fuel injection
Hydraulic accumulator is an accessory of a hydraulic system.
A hydraulic accumulator is a pressure storage reservoir in which a non-compressible hydraulic fluid is held under pressure by an external source.
The external source can be a spring, a raised weight, or a compressed gas. An accumulator enables a hydraulic system to cope with extremes of demand using a less powerful pump, to respond more quickly to a temporary demand, and to smooth out pulsations. It is a type of energy storage device.
Air Injection and Solid Injection SystemParthivpal17
This document summarizes different types of fuel injection systems used in diesel engines. It describes air injection systems which inject fuel along with compressed air, but are not commonly used today. It also discusses solid injection and airless injection systems, categorizing them as common rail, individual pump and injector, or distributor injection systems. The common rail system uses a single high-pressure pump to supply fuel to a header or rail that distributes fuel to each injector. Individual pump systems have a separate pump for each injector. Distributor systems use a central pump and distributor block to time fuel injection.
This presentation discusses reaction turbines. It defines a reaction turbine as a type of turbine that develops torque by reacting to the pressure or weight of a fluid based on Newton's third law of motion. The document outlines the working principle of reaction turbines and describes the main types - radial flow, axial flow, and mixed flow turbines. Examples of specific reaction turbines are provided, including the Francis, Kaplan, and propeller turbines. The advantages and disadvantages of reaction turbines are summarized. Key concepts like pressure compounding, turbine blade stages, and the pressure-velocity diagram for reaction blades are also explained briefly.
This presentation include the information about the different types of superchargers, advantages & disadvantages of superchargers and turbochargers. One case study of variable geometry turbocharger is included with literature review.
The document provides an overview of internal combustion engines. It discusses the basic classifications and cycles of internal combustion engines including two-stroke and four-stroke engines. It also covers the workings of spark ignition and compression ignition engines, as well as common engine components and systems such as carburetors and fuel injection systems. Key topics include the Otto, Diesel, and Carnot power cycles; combustion stages; valve timing diagrams; and scavenging, pre-ignition, detonation, lubrication, and emissions control.
The document discusses different types of engine cycles including ideal, fuel-air, and actual cycles. It provides details on:
- Air standard cycles which are idealized and assume a perfect gas, no mass change, reversible processes, and constant specific heats. Examples include Otto, Diesel, and Dual cycles.
- Fuel-air cycles which are more accurate by considering the actual cylinder gas composition, variable specific heats, incomplete fuel-air mixing at high temps, and dissociation effects.
- Actual engine cycles use even more accurate models of the processes and working fluid, taking into account variable properties and chemical reactions.
This document provides an overview of diesel engines, including their basic operation, components, and fuel injection systems. It describes how diesel engines ignite fuel via compression rather than a spark plug. Key points covered include the types of fuel injection systems (common rail, unit injection, etc.), injectors and nozzles, governors, and applications of diesel engines. The document concludes by comparing diesel engines to gasoline engines and discussing newer direct injection technologies.
Power assisted brakes use either hydraulic or vacuum pressure to reduce the amount of force needed to press the brake pedal. Hydraulic systems use pressure from the power steering pump or an air compressor, while vacuum systems use pressure from the intake manifold. Both types work by creating pressure on one side of a booster piston to multiply the force applied through the brake pedal to the master cylinder. When the pedal is pressed, it closes off the pressure source and applies hydraulic pressure to the brakes. Releasing the pedal vents the booster pressure and allows the pedal to return freely. Servo brakes provide additional braking power needed for heavier vehicles through mechanical, hydraulic, or vacuum assisted systems.
This document provides an overview of compressed air systems, including:
- The types of compressors and their characteristics such as reciprocating, rotary, centrifugal, and axial compressors.
- How compressors work using principles such as the ideal gas law and Bernoulli's equation.
- Factors that affect the energy consumption of compressed air systems such as inlet air conditions, pressure settings, piping layout and leaks.
- Methods for improving efficiency such as variable speed drives, capacity control, and detailed energy audits.
The document discusses compressed air systems in detail over 5 sections, covering the scope of work, types of compressors, selection criteria, performance comparisons, and system components.
This document summarizes key aspects of gasoline direct injection (GDI) engine technology. It discusses the timeline of fuel supply systems from carburetors to port injection to direct injection. The main components of a GDI system are described as the engine control unit, sensors, high pressure fuel pump, and fuel injector. GDI works by directly injecting pressurized fuel into the combustion chamber, allowing for improved efficiency and reduced emissions compared to port fuel injection. Benefits of GDI engines include increased power and torque, reduced fuel consumption and CO2 emissions, and ability to meet future emissions standards.
This document presents a project presentation by six students at Seacom Engineering College on the study and demonstration of the principles of a turbocharger. It includes definitions of a turbocharger and supercharger, explanations of why turbochargers are used instead of superchargers, diagrams of key turbocharger components like the turbine, compressor, shaft, and housing. It also covers the Brayton cycle that turbochargers are based on and comparisons of naturally aspirated versus supercharged engine P-V diagrams. Application areas and improvements in turbocharger performance over time are summarized as well.
PSG Design data book pages for rolling contact bearings designSagar Dhotare
PSG Design data book pages for rolling contact bearings design
This contains following points
Bearing type with application
Equivalent load formula
Dynamic capacity formula
Catalog of DGBB, Roller, Taper Roller Cylindrical or Spherical roller bearing, needle bearing.
This document provides an introduction and overview of notes on the design and analysis of machine elements for students at the University of Western Australia. It outlines the mechanical engineering design course, which introduces design concepts, reviews failure mechanisms, and considers the analysis and design of common machine elements. It explains that the notes are a resource for the entire design course, covering topics like springs, gears, shafts and more. The notes take a simple mathematical approach but emphasize that real-world engineering judgment is also needed. The goal is for students to demonstrate understanding of analysis approaches and ability to modify designs for new problems.
The document discusses the development of an electric car jack that can be automatically operated from inside the vehicle to make changing tires and performing repairs easier, especially for the elderly, disabled, and women. Current manual car jacks require significant physical effort and are difficult to use, while commercial lifts are too large and expensive for individual car owners. The proposed electric screw jack integrated into the vehicle aims to provide automatic and easy lifting of the car for repairs without much physical effort.
This document summarizes a student's final project report on improving the design of a car jack. The student conducted research on existing car jack designs and identified key issues like them requiring significant strength and energy to operate. The objective of the project was to redesign the car jack to be more functional and consider human factors. The student followed a process flow chart that included problem analysis, literature review, concept creation, testing, and conclusion. The scope was to design a 3-ton hydraulic car jack that optimizes human power usage by replacing the long arm with a foot pedal for easier operation. CAD drawings and testing of the new design were also part of the project scope.
DESIGN AND FABRICATION OF A POWER SCISSOR JACKsasank babu
The document describes the design and fabrication of a power scissor jack. It provides background on screw jacks used in World War II vehicles and discusses various types of lifting devices such as levers, screws, and gears. The document is a project report submitted to fulfill the requirements for a Bachelor of Technology degree in Mechanical Engineering. It includes chapters on power screws, design of the scissor jack components, drawings, manufacturing methods, fabrication, and conclusions.
This document discusses building a SaaS startup using the Django and Angular frameworks. It describes the architecture as having a client-side web interface built with Angular that communicates with the backend built using Django. The backend includes components like a task queue using Celery, app monitoring with New Relic, code versioning with BitBucket, and error tracking with Sentry. The document advocates this technical stack can be used to develop a complete product by a single developer within 3 months.
This document provides information about an assignment for an MBA course on Employee Relations Management. It includes 6 questions related to topics like enterprise risk management, organizational conflict, discipline procedures, grievance handling, trade unions, and workplace compensation and rewards. Students can submit their answers to the assignment questions to subjects4u@gmail.com or contact 09882243490 to get the assignment solved at a nominal price of Rs. 125 per question.
This document provides information about an MBA research methodology assignment that can be purchased for Rs. 125 per solved question. It includes 6 questions related to defining business research, descriptive research designs, measurement scales, sampling methods, coding questions, and the structure of a research report. Students are to answer each question in 300-400 words. Contact information is provided to purchase the solved assignments.
Integrated Treatment for ARLD: Making it happen, 2 February 2017, Presentatio...Health Innovation Wessex
The Clinical Research Network Wessex (CRN Wessex) provides study support services across six divisions to facilitate NIHR portfolio research. CRN Wessex is part of the NIHR family of organizations and works to support clinical research studies through resources like research nurses, clinical trials assistants, study coordinators, and support services in pharmacy, pathology, and radiology. For more information, contact the CRN Wessex study support team.
This document provides information about an assignment for an MBA course in International Financial Management. It includes 6 questions related to goals of international financial management, functions of the money market, counter-trade examples, managing transaction and operating exposure, capital budgeting techniques, and definitions of American Depository Receipts and portfolios. Students are to answer each question in 300-400 words for a total of 60 marks. Contact information is provided to obtain solved assignments for Rs. 125 each.
This document provides details of an MBA assignment related to security analysis and portfolio management. It includes 6 questions asking to define key terms, explain concepts like the investment process, primary markets, technical indicators, the assumptions of the Markowitz and CAPM models, and the structure and types of mutual funds. Students are instructed to answer each question in 300-400 words for a total of 60 marks. They are provided contact information to get solved assignments for Rs. 125 each.
Three New draft guidances related to compounding of human drugsDr. Reena Malik
FDA has issued three new draft guidance documents related to compounding of human drugs:
1) Addressing prescription requirements for compounded drugs under Section 503A.
2) Defining outsourcing facilities under Section 503B as facilities that compound sterile drugs and have elected to register with FDA.
3) Explaining that hospitals can compound drugs under Section 503A based on individual prescriptions or for limited quantities in advance, but FDA will not take action if certain conditions are met for distribution within affiliated facilities within a 1 mile radius.
El documento presenta información sobre la juventud y su desarrollo desde varias perspectivas. La ONU define a la juventud como el periodo entre los 15 y 25 años. Se discuten temas como las tribus urbanas, los tres tipos de desarrollo durante la juventud (orgánico, social y espiritual), y los retos actuales como vicios a temprana edad y la delincuencia juvenil. El documento concluye resaltando la importancia de que los jóvenes aprovechen las oportunidades y tecnologías disponibles para crecer sabi
El documento presenta las actividades realizadas por Miguel Ramírez en la materia de autómatas en lenguaje formal de la carrera de ingeniería en computación en la Universidad Fermín Toro. Estas actividades incluyen videos explicativos, información en un canal de televisión, una nube de palabras con conceptos clave, una historieta interactiva y blogs que brindan información adicional sobre los temas de la materia.
Performance of a_centrifugal_pump_autosavedDickens Mimisa
The document summarizes an experimental analysis of a centrifugal pump performed by a student. Key findings include:
- The experiment investigated the relationship between head, discharge, input power, and efficiency of a centrifugal pump under different revolution speeds.
- Data was collected manually and analyzed to determine the pump's characteristic curve and efficiency at varying flow rates.
- Results show efficiency increases with flow rate until peak efficiency is reached, then decreases as flow rate continues to rise.
Unit-1 Basics of Hydraulics and Pumps.pptxHARIBALAJIMECH
Basics of Hydraulics – Pascal’s Law – Principles of flow - Friction loss – Work, Power and Torque Problems, Sources of Hydraulic power : Pumping Theory – Pump Classification – Construction, Working, Design, Advantages, Disadvantages, Performance, Selection criteria of Linear and Rotary – Fixed and Variable displacement pumps – Problems.
This report gives basic knowledge about overhauling of Turbine, erection, commissioning.
For more information visit@supratheek Turbo Engineering Services
The document discusses performance assessment of compressors through field testing. It describes methods to measure free air delivery, isothermal power, volumetric efficiency and specific power requirement. The nozzle method and pump up method are explained to measure free air delivery. Calculations are provided as examples to determine isothermal efficiency, specific power consumption and compare actual performance to design values to assess energy efficiency.
The document discusses performance assessment of compressors through field testing. It describes methods to measure free air delivery, isothermal power, volumetric efficiency and specific power requirement. The nozzle method and pump up method are explained to measure free air delivery. Calculations are provided as examples to determine isothermal efficiency and specific power consumption. Periodic performance assessment is important to minimize compressed air costs and improve system efficiencies.
Energy efficiency in pumps and fans pptD.Pawan Kumar
The document discusses assessing the energy efficiency of pumps and fans through on-site performance testing. Key parameters that are measured for pumps include flow rate, head, power, and efficiency. Various methods for measuring flow are described, such as the tracer method, ultrasonic meters, tank filling, and installing an online flow meter. Opportunities to improve pumping system efficiency include operating at the best efficiency point, minimizing restrictions, and proper maintenance. Performance testing of fans similarly determines flow, power input, and pressure rise. Generic opportunities to improve fan efficiency also focus on operating conditions and maintenance.
This document provides instructions for laboratory experiments on hydraulic machines and systems, including determining the coefficient of impact of jets on different vanes, studying the characteristic curves of a Pelton wheel turbine and Francis turbine at constant head conditions, and studying the characteristic curves of a Kaplan turbine at constant head condition. Key details include objectives, required apparatus, relevant formulas, procedures, expected observations and results for each experiment. The experiments aim to analyze forces on vanes from fluid jets, efficiency of different turbine types, and develop characteristic curves under constant head.
Generally Pumps classification done on the basis of its mechanical configurat...ShriPrakash33
Pumps simplify the transportation of water and other fluids, making them very useful in all types of buildings - residential, commercial, and industrial. For example, fire pumps provide a pressurized water supply for firefighters and automatic sprinklers, water booster pumps deliver potable water to upper floors in tall buildings, and hydronic pumps are used in HVAC systems that use water to deliver space heating and cooling.
TYPES OF PUMPS AND THEIR WORKING PRINCIPLES
Generally Pumps classification done on the basis of its mechanical configuration and their working principle. Classification of pumps mainly divided into two major categories:
Dynamic pumps / Kinetic pumps
Dynamic pumps impart velocity and pressure to the fluid as it moves past or through the pump impeller and, subsequently, convert some of that velocity into additional pressure. It is also called Kinetic pumps Kinetic pumps are subdivided into two major groups and they are centrifugal pumps and positive displacement pumps.
Classification of Dynamic Pumps
1.1 Centrifugal Pumps
A centrifugal pump is a rotating machine in which flow and pressure are generated dynamically. The energy changes occur by virtue of two main parts of the pump, the impeller and the volute or casing. The function of the casing is to collect the liquid discharged by the impeller and to convert some of the kinetic (velocity) energy into pressure energy.
1.2 Vertical Pumps
Vertical pumps were originally developed for well pumping. The bore size of the well limits the outside diameter of the pump and so controls the overall pump design.2.) Displacement Pumps / Positive displacement pumps
2. Displacement Pumps / Positive displacement pumps
Positive displacement pumps, the moving element (piston, plunger, rotor, lobe, or gear) displaces the liquid from the pump casing (or cylinder) and, at the same time, raises the pressure of the liquid. So displacement pump does not develop pressure; it only produces a flow of fluid.
Classification of Displacement Pumps
2.1 Reciprocating pumps
In a reciprocating pump, a piston or plunger moves up and down. During the suction stroke, the pump cylinder fills with fresh liquid, and the discharge stroke displaces it through a check valve into the discharge line. Reciprocating pumps can develop very high pressures. Plunger, piston and diaphragm pumps are under these type of pumps.
2.2 Rotary Type Pumps
The pump rotor of rotary pumps displaces the liquid either by rotating or by a rotating and orbiting motion. The rotary pump mechanisms consisting of a casing with closely fitted cams, lobes, or vanes, that provide a means for conveying a fluid. Vane, gear, and lobe pumps are positive displacement rotary pumps.
2.3 Pneumatic Pumps
Compressed air is used to move the liquid in pneumatic pumps. In pneumatic ejectors, compressed air displaces the liquid from a gravity-fed pressure vessel through a check valve into the discharge line in a series of surges spaced by the time required.
This document provides instructions for conducting an experiment to determine the jet diameter and coefficient of discharge of an orifice. It describes the necessary apparatus, including an orifice discharge setup, collecting tank fitted with a piezometer, stopwatch and meter scale. Formulas are given for calculating the radius of the jet, jet contraction coefficient, velocity coefficient, and discharge coefficient based on measurements taken. The procedure explains how to adjust the orifice setup and take measurements using a micrometer to determine the jet radius.
ABSTRACTA pelton wheel is considered as an impulse turbin.docxransayo
ABSTRACT
A pelton wheel is considered as an impulse turbine, a turbine that converts pressure head into velocity head. This lab will use this mechanism along with a prony brake to calculate the input power, output power, and efficiency of the turbine. The team will be provided with measuring devices such as a stroboscope to measure the turbine speed as well as a hydraulic bench to control the flow rate of the liquid flowing through the turbine [1].
The experiment will consist of two separate trials with two different water heads. This experiment will neglect all frictional forces for the theoretical calculations. The hydraulic bench will be calibrated to have a water head of 8m H2O and 12m H2O. The team will record the needed data for the experiment: turbine inlet pressure, flow rate, turbine speed, and the net spring forces. For the first trial, 8m H2O, the Prony brake net spring force will be set to have a net force of 10N and will be adjusted to decrease by 1N until the net force reaches 4N, having 7 data points for the first trial. The experiment will then be repeated for a water head of 12m H2O with the Prony brake net force set to 12N and adjusted to decrease by 2N until the net force reaches 2N, having 6 data points. The volume of the flow will be recorded at every other data point to ensure that flow rate remains constant.
The team concluded that the efficiency of the turbine increases as the angular velocity increases. The percent error between experimental and theoretical calculations were relatively high. Which were expected because the theoretical calculations did not account for any frictional losses.
INTRODUCTION
1. The main objectives of this lab experiment are following
i. Observe flow through a mini Pelton Turbine
ii. Calculate input power, output power, and efficiency for readings taken at a constant nozzle inlet pressure.
iii. Calculate the efficiency of the turbine and compare it to the theoretical efficiency value.
2. The purpose of this lab work is to study Pelton wheel turbine which make us able to understand the working of the turbine, design of the turbine and factors which effect the efficiencies.
3. The experiment will be done to check the effect of angular velocity on the efficiency, it is expected that increase in angular velocity will result in increase in the efficiency
4. List of Equations [1]:
· Gage Pressure:
(1)
Where
= Density of water
g = Gravitational Acceleration
h = Head of water
· Work Input:
(2)
Where
Q = Flow rate of water
= change in pressure
· Work Output:
(3)
Where
F = Force of water
r = distance measured from the axis of rotation to where the force is applied
= Dynamometer Angular velocity
· Work Theoretical:
(4)
Where
= Force of water in x direction
r = distance measured from the axis of rotation to where the force is applied
= .
This document describes experiments conducted to determine the characteristics of different types of hydraulic turbines under constant head conditions. The experiments measure parameters such as speed, power output, flow rate, and efficiency at varying loads. Formulas are provided to calculate hydraulic power input, brake horsepower, unit quantities, and turbine efficiency. Graphs of unit speed vs. unit power, unit discharge and efficiency are used to obtain the constant head characteristic curves and determine the maximum efficiency for each turbine type. Turbines tested include Pelton wheel, Francis, and Kaplan turbines. Precautions and sample calculations are also outlined.
This document discusses how to optimize energy usage in pumps through condition monitoring techniques. Pumps use 25% of the world's motor-driven electricity, or around 6.5% of global electricity production. Condition monitoring can detect degradation in bearings, casing wear, misalignment, and internal wear in impellers and seals. Performance analysis by measuring head-flow curves is particularly useful for detecting internal wear and optimizing the timing of pump overhauls to balance repair costs and wasted energy. The document provides examples of using performance analysis on boiler feed pumps to schedule optimal overhaul times that minimize total costs.
This document is a vocational training project report submitted by JINENDRA NINAMA about their training at the NTPC SIPAT coal fired steam power plant from June 2-28, 2014. The report includes declarations by the student, acknowledgments, and details about the Sipat Thermal Power Plant. It also includes simplified diagrams and descriptions of the key components of the coal fired steam power plant, including the cooling tower, transmission lines, generator, steam turbine, condenser, feedwater pumps, control valves, deaerator, feedwater heaters, pulverizer, boiler steam drum, superheater, and economizer.
This document discusses various topics related to hydraulic turbines, including:
1. Classification, selection, and design of impulse turbines like the Pelton wheel and reaction turbines like the Francis and Kaplan turbines.
2. Components like the draft tube, surge tanks, and governing systems.
3. Concepts like unit speed, unit discharge, unit power, and characteristic curves used to analyze turbine performance.
4. Cavitation in hydraulic turbines.
This document describes a design project for the impulse stage of a steam turbine. The goal is to calculate the number of blades and their lengths needed to operate the impulse stage. Key calculations involve determining the blade velocity, angles of the steam, and dimensions of the blades. The results show the design meets criteria like the axial cord being less than the blade spacing and a loading factor below 3. The design was found to need 248 blades of 0.4696 inches axial cord length.
The document describes the methodology and experimental procedure for testing a Pelton turbine. Key points:
1) Calculations will be performed using appropriate equations to determine parameters like absolute velocity, hydraulic power, mechanical power, effective height, and turbine efficiency. Characteristic curves will then be graphed.
2) Testing procedures involve measuring pressures, flow rates, torque, and rpm. Calculations will then be done to find load, speed, power, and efficiency.
3) Test results are presented in a table with values for flow rate, rpm, pressure, torque, and other parameters. Calculations are shown for one test point to determine velocity, height, hydraulic power, mechanical power, and efficiency.
Performance studies on a direct drive turbine for wave power generation in a ...Deepak Prasad
This document describes a study using computational fluid dynamics (CFD) to simulate wave power generation from a direct drive turbine in a numerical wave tank (NWT). The CFD model is validated against experimental data and shows good agreement. Flow characteristics through the front guide nozzle, augmentation channel, and turbine stages are examined. Peak turbine power and efficiency occur at 35 rotations per minute, matching experimental results closely.
This document summarizes Uphaar Prasad's two-week vocational training project at the NTPC Sipat coal fired steam power plant. It includes a declaration by the student, acknowledgements, and a simplified diagram explaining the main components of the power plant, including the cooling tower, transmission lines and transformer, electric generator, steam turbine, condenser, boiler feedwater pump, control valves, and boiler. The power plant has a total installed capacity of 2980 MW divided between units of 660 MW and 500 MW.
Improving Energy Efficiency of Pumps and Fanseecfncci
Pumps and Fans are energy consuming equipment that can be found in almost all Industries. Therefore, it is important to check if they are running efficiently. This presentation give an overview about energy saving opportunities in pump and fan equipment. It was prepared in the context of energy auditor training in Nepal in the context of GIZ/NEEP programme. For further information go to EEC webpage: http://eec-fncci.org/
1) The document describes the modeling of a flash vaporizer unit that separates a binary mixture of water and ethanol. Both stationary and dynamic models are developed.
2) For the stationary model, component balances, equilibrium equations, summation equations, and an energy balance are applied. The Wilson activity coefficient model is used.
3) Controller equations for level, pressure, and temperature are developed for the dynamic model. Degree of freedom analysis is performed.
1. 1
AKSUM UNIVERSITY
COLLEGE OF ENGINEERING AND TECHNOLOGY
DEPARTMENT OF MECHANICAL ENGINEERING
TURBO MACHINES & MACHINES LAB MANUAL
Compiled by
A.Syed Bava Bakrudeen,
Associate Professor,
Mechanical Department
Aksum University, Ethiopia
LIST OF EXPERIMENTS
1. Pelton turbine
2. Reaction turbine (Efficiency Test)
3. Axial turbine
4. Reaction turbine (Velocity Test)
5. Centrifugal pump
6. Piston pump
7. Gear pump
8. Axial fan
9. Radial fan
10. Tubular heat exchanger (Parallel flow)
11. Tubular heat exchanger (Counter flow)
12. Air compressor
13. Multipurpose air duct.
2. 2
1. PELTON TURBINE
THEORY: Pelton wheel turbine is an impulse turbine, which is used to act on
high loads and for generating electricity. All the available heads are classified in to
velocity energy by means of spear and nozzle arrangement. Position of the jet
strikes the knife-edge of the buckets with least relative resistances and shocks.
While passing along the buckets the velocity of the water is reduced and hence an
impulse force is supplied to the cups which in turn are moved and hence shaft is
rotated.
AIM:
To determine the efficiency of the given pelton turbine using constant
volume method.
APPARATUS REQUIRED:
1. Pelton turbine setup.
2. Collecting tank
3. Stop watch
4. Meter scale
FORMULA:
1. Mechanical Power = Pmech = Mω = Mx 2xπxn/60
M=Moment in N/m.
n = Speed in rpm.
2. Hydraulic Efficiency = Phyd = pxV
p = Pressure in N/m2
.
V= Volume flow rate in m3
/Sec (Discharge)
(1liter =1000 cm3
= 0.001 m3
) (1bar = 1x105
N/m2
)
(1liter/min =16.67x10-6
m3
/Sec) (1liter = 1kg)
3. Efficiency η = Pmech x100/ Phyd
PROCEDURE:
1. Tare values in the system diagram
2. Select "Measurement Diagram" in the program.
3. 3
3. Enable new series of measurements. Make settings for the measurements file.
4. Open the brake fully with the adjusting screw(8).
5. Open valve (4) fully to create the maximum volume flow.
6. Change the pump to "Pressure Control" and specify a control pressure. This
corresponds to the constant height difference of a real turbine to the storage
lake. With the pumps used it is possible to achieve pressures up to about 3.8 bar
with the needle nozzle fully opened. Higher pressures are only possible by
throttling the volume flow. We recommend using this pressure range. The
measured values obtained by GUNT reach 4 bar.
7. Wait until the operating point is reached. In this case the observation of the
water jet from the blade is particularly relevant for the subsequent explanation.
Then record measurements (the current measurement data set is written to the
measurements file). The program is now ready for the next measurement.
8. a) Use the adjusting screw on the brake (8) to increase the brake torque. The
turbine's rotational speed and torque change. The change depends on the desired
number of measurement points. Meaningful characteristics are often obtained
with 5 to 6 measurement points.
b) The volume flow can still be varied at each braking position. To do this, the
nozzle is closed gradually from the initial fully open position.
9. Repeat steps 7 and 8 as often as needed until the turbine's rotational speed has
fallen to zero and tabulate the value.
GRAPHS:
i Torque (M) Vs Speed (n) (Ordinary Graph)
RESULT:
1. Maximum efficiency of the turbine = ……………………… %
2. Speed corresponding to maximum efficiency = ………….. rpm
3. Power corresponding to maximum efficiency = …………..W.
4. Discharge corresponding to maximum efficiency = ………….. L/min.
5. 5
2. REACTION TURBINE (EFFICIENCY TEST)
THEORY: Reaction turbines are acted on by water, which changes pressure as it
moves through the turbine and gives up its energy. They must be encased to
contain the water pressure (or suction), or they must be fully submerged in the
water flow. Newton's third law describes the transfer of energy for reaction
turbines.Most water turbines in use are reaction turbines and are used in low
(<30 m or 100 ft) and medium (30–300 m or 100–1,000 ft) head applications. In
reaction turbine pressure drop occurs in both fixed and moving blades. It is largely
used in dam and large power plants
AIM:
To determine the efficiency of the given reaction turbine under constant
pressure condition.
APPARATUS REQUIRED:
1. Francis turbine setup.
2. Collecting tank
3. Stop watch
4. Meter scale
FORMULA:
1. Mechanical Power = Pmech = Mω = Mx 2xπxn
M=Moment in N/m.
n = Speed in rpm.
(1liter =1000 cm3
= 0.001 m3
) and (1bar = 1x105
N/m2
)
2. Hydraulic Efficiency = Phyd = pxV
p = Pressure in N/m2
.
V= Volume flow rate in m3
/Sec (Discharge)
3. Efficiency = Pmech x100/ Phyd
PROCEDURE:
1. Tare values in the system diagram
2. Select "Measurement Diagram" in the program.
3. Enable new series of measurements. Make settings for the measurements file.
6. 6
4. Open the brake fully with the adjusting screw(8).
5. Open valve (4) fully to create the maximum volume flow.
6. Change the pump to "Pressure Control" and specify a control pressure. Pressure
up to about 3 bar can be achieved with the pump used. Higher pressure cannot
be maintained over the entire operating range due to increasing the volume
flow.
7. Wait until the operating point is reached. Then record measurements (the
current measurement data set is written to the measurements file). The program
is now ready for the next measurement.
8. The brake torque is increased via the adjusting screw (7). The torque is varied
depend up on the desired number of measurement points. Meaningful
characteristics are often obtained with 10 measurement points.
9. Repeat steps 7 and 8 as often as needed until the turbine's rotational speed has
fallen to zero and tabulate the value.
GRAPHS:
i Torque (M) Vs Speed (n) (Ordinary Graph)
RESULT:
1. Maximum efficiency of the turbine = ……………………… %
2. Speed corresponding to maximum efficiency = ………….. rpm
3. Power corresponding to maximum efficiency = …………..W.
4. Discharge corresponding to maximum efficiency = ………….. L/min.
8. 8
3. AXIAL TURBINE
THEORY: If the water flows parallel to the axis of the rotation of the shaft, the
turbine is known as axial flow turbine. If the head at the inlet of the turbine is the
sum of pressure energy and kinetic energy and during the flow of water through
runner a part of pressure energy is converted into kinetic energy, the turbine is
known as reaction turbine.
AIM:
To determine the efficiency of the given axial flow axial turbine under
constant speed and pressure.
APPARATUS REQUIRED:
1. Kaplan turbine setup.
2. Collecting tank
3. Stop watch
4. Meter scale
FORMULA:
1. Mechanical Power = Pmech = Mω = Mx 2xπxn
M=Moment in N/m.
n = Speed in rpm.
(1 Millibar = 0.001 bar)
2. Hydraulic Efficiency = Phyd = pxV
p = Pressure in N/m2
.
V= Volume flow rate in m3
/Sec (Discharge)
3. Efficiency = Pmech x100/ Phyd
PROCEDURE:
1. Tare values in the system diagram
2. Select "Measurement Diagram" in the program.
3. Enable new series of measurements. Make settings for the measurements file.
4. Open the brake fully with the adjusting screw.
5. Open control valve V1 to obtain maximum upstream pressure
6. Switch on the pump.
9. 9
7. Wait until the operating point is established. Then record the measuring values
(the current measurement data set is written to the measurement file). The
program is now ready for next measurement.
8. Increase the turbine torque using the adjusting screw. The torque variation is
depending on the number of measuring points chosen. Meaningful
characteristics are often obtained with 5 to 6 measuring points.
10.Repeat steps 7 and 8 as often as needed until the adjusting screw is at the stop.
11. Save the measurement file.
12.Alternatively, further series of measurement can be recorded at reduced
upstream pressure. To do so, reduce the pressure at control valve V1 and repeat
the measurement from step 6 onwards.
GRAPHS:
i Torque (M) Vs Speed (n) (Ordinary Graph)
RESULT:
1. Maximum efficiency of the turbine = ……………………… %
2. Speed corresponding to maximum efficiency = ………….. rpm
3. Power corresponding to maximum efficiency = …………..W.
4. Discharge corresponding to maximum efficiency = ………….. L/min.
10. 10
TABULATION:
S.
N
o
Torque (M)
(Ncm)
Pressure
(p)
(mbar)
Speed
(n)
(1/min)
Volume
Flow (V)
( L/min)
Mechanical
Power
(Pmech) (W)
Hydraulic
Power
(Phyd) (W)
Efficiency
(η) (%)
1. 34.8 890 3490 125 127.2 185.42 68.6
MODEL CALCULATIONS:
1. Phyd = pxV = 0.89x105
x125x0.001/60 = 185.42 W
2. Pmech = Mω = Mx 2xπxn/60 = 34.8x10-2
x2xπx3490/60 = 127.2 W.
3. η = Pmechx100/ Phyd = (127.2 /185.42)x100 =68.6%
Guided Wheel Impeller
Fig3. Axial Turbine
11. 11
4. REACTION TURBINE ( VELOCITY TEST)
THEORY:
Absolute velocity (c): The velocity that the water jet has at the outlet from the
turbine compared to the environment.
Circumferential velocity (u): The velocity of the impeller. Since this depends on
the flow of the exiting water jet, it is the velocity at the diameter of the outlet
nozzle.
Relative velocity (w): It is the velocity corresponds to the velocity of the flow
relative to the nozzle. It is calculated by adding circumferential velocity (u) and
absolute velocity (c).
AIM:
To find the relative velocity and circumferential velocity of the francis
turbine and determine the correlation between relative velocity and volume flow
rate of the given turbine.
APPARATUS REQUIRED:
1. Francis turbine setup.
2. Collecting tank
3. Stop watch
4. Meter scale
FORMULA:
1. Circumferential Velocity = u2 = πdn/60
d= Diameter of nozzle = 52 mm.
n = Speed in rpm.
2. Relative velocity = W2 = √(((Pux2)/ρ)+ u2
2
)
pu = Net Pressure in N/m2
.
ρ = Density of water = 1000 kg/m3
.
PROCEDURE:
1. Tare values in the system diagram
2. Select "Measurement Diagram" in the program.
3. Enable new series of measurements. Make settings for the measurements file.
4. Loosen off adjusting screw to open the brake.
12. 12
5. Let the pump run to100% power (This ensures that air in the flow section does
not affect the measured values).
6. Wait until the operating point is reached. Then record measurements (the
current measurement data set is written to the measurements file). The program
is now ready for the next measurement.
7. The capacity of the pump is retracted one step. The power is varied depending
on the desired number of measurement points. Meaningful characteristics are
often obtained with 5 to 6 measurement points
8. Repeat steps 6 and 7 as many times as needed until there is no more rotational
speed at the turbine.
9. Save the measurements file.
GRAPHS:
i Relative Velocity Vs Volume flow.
OBSERVATION: Diameter of nozzle (d) = 52 mm.
RESULT:
1. The maximum relative velocity = ________________ m/s.
2. Net pressure at inlet = _____N/m2
at maximum relative velocity
3. The relative velocity is directly proportional to volume flow rate.
13. 13
TABULATION:
S.
No
Pressu
re (p)
bar
Speed
(n)
1/min
Volume
Flow (V)
L/min
Circumferential Velocity
(u2) (m/s)
Relative velocity
(W2)
(m/s)
1 3.18 19894 46.7 54.16 59.8
MODEL CALCULATIONS:
1. u2 = πdn = πx0.052x19894/60 = 54.16 m/s
2. W2 = √(((Pux2)/ρ)+ u2
2
) = √(((3.18x105
x2)/1000)+ 54.22
)= 59.8 m/s
W
C
u2
Fig 4. Velocities in reaction turbine
C- Absolute velocity at outlet (m/s)
W= Relative velocity (m/s)
u2= Circumferential velocity (m/s)
14. 14
5. CENTRIFUGAL PUMP
THEORY: Centrifugal pumps are a sub-class of dynamic axisymmetric work-
absorbing turbomachinery. Centrifugal pumps are used to transport fluids by the
conversion of rotational kinetic energy to the hydrodynamic energy of the fluid
flow. The rotational energy typically comes from an engine or electric motor. The
fluid enters the pump impeller along or near to the rotating axis and is accelerated
by the impeller, flowing radially outward into a diffuser or volute chamber
(casing), from where it exits.
AIM:
To determine the characteristics of a centrifugal pump under constant speed
and varying the discharge method.
APPARATUS REQUIRED:
1. Centrifugal pump setup.
2. Collecting tank
3. Stop watch
4. Meter scale
FORMULA:
1. Hydrualic Power Phyd= ∆P xV in Watts.
∆P = P2-P1=Difference in pressure in N/m2
.
V = Volume flow rate (Discharge or Actual discharge) in m3
/sec.
(1L/min = 0.001 m3
/min) (1 min = 60 sec) (1 L/min = 16.66x10-6
m3
/sec)
(1bar = 1x105
N/mm2
)
2. Head H = ∆P/ ρxg in meter
ρ= Density of water=1000 kg/m3
.
g = Specific gravity =9.81 m/s2
.
(1L/min = 0.001 m3
/min)
3. Efficiency = Phyd/Pel.
Phyd = Hydrualic Power in W
Pel = Electrical Power in W
4. Specific speed Ns = n√V/ (H)3/4
(unitless)
15. 15
PROCEDURE:
1. Bleed the pump demonstrator.
2. Open valve V2 fully.
3. Use the Tare button to calibrate to zero.
4. Leave pump to turn to n=_________ rev/min.
5. Record measuring values of the suction pressure (P1), the pump outlet
pressure (P2), hydraulic and electrical power and volume flow (V).
6. Reduce the volume flow bit by bit by gradually closing valve V2 and take
the measurements according to point 5.
7. Repeat steps 5 and 6 until the volume flow is completely throttled.
8. Additional curves can be recorded with different rotational speed.
GRAPHS:
i Volume flow rate (V2) Vs Hydraulic Power (Phyd)
ii. Volume flow rate (V2) Vs Electrical Power (Pel)
iii. Volume flow rate (V2) Vs Efficiency (η)
RESULT:
1. Maximum efficiency of the pump = ……………………… %
2. Discharge corresponding to maximum efficiency = ………….. m3
/Sec.
3. Input power corresponding to maximum efficiency = …………..W.
4. Head corresponding to maximum efficiency = ………….. meter.
16. 16
TABULATION:
S
.
N
o
Rotation
al speed
(n) (Rev
/ min)
Volume
flow
(V)
(L/min)
Suction
Pressure
(P1) (bar)
Discharg
e
Pressure
(P2) (bar)
Temp
eratu
re (T)
(0
C)
Electric
al
Power(
Pel)
(W)
Pressure
Differen
ce (∆P)
(bar)
Head
(H)
(M)
Hydrau
lic
Power
(Phyd)
(W)
Efficien
cy (η)
(%)
Specifi
c speed
(Ns)
-
1 3300 25.2 -0.0056 0.865 25 343 0.8706 8.875 36.56 10.66 13.15
MODEL CALCULATIONS:
1. Phyd= ∆P xV = 0.8706X105
x 25.2x0.001/60 = 36.56
2. Head H = ∆P/ ρxg = 0.8706X105
/(1000X9.81) = 8.875
3. Efficiency = Phydx100/Pel = 36.56x100/343=10.66%.
4. Specific speed Ns = n√V/ (H)3/4
= 3300 x √(25.2x0.001/60 )/ (8.875)3/4
= 13.15
Fig6. Schematic diagram of centrifugal pump
EI1 Energy input Pel of the pump B1 Water tank
FI1 Volume flow P1 Centrifugal pump
PI1 Pressure p1 upstream of the pump V1 Valve to throttle the suction side
PI2 Pressure p2 downstream of the pump V2 Valve to throttle the pressure side
TI1 Water temperature V3 Outlet valve
17. 17
6. PISTON PUMP
THEORY: Reciprocating is a positive displacement pump in which the liquid is
sucked and then it is actually pushed or displaced due to the thrust exerted on it by
a moving member, which results in lifting the liquid to the required height These
pumps usually have one or more chambers which are alternatively filled with the
liquid to be pumped and then emptied again As such the discharge of liquid
pumped by these pumps almost wholly depends on the speed of the pump. It is
widely used in Automobile Service Stations and Chemical Industries.
AIM:
To conduct the performance test on piston pump
APPARATUS REQUIRED:
1. Piston pump setup.
2. Collecting tank
3. Stop watch
4. Meter scale
FORMULA:
1. Hydrualic Power Phyd= ∆P xV in Watts.
∆P = P2-P1=Difference in pressure in N/m2
.
V = Volume flow rate (Discharge or Actual discharge) in m3
/sec.
(1L/min = 0.001 m3
/min) (1 min = 60 sec) (1 L/min = 16.66x10-6
m3
/sec)
(1bar = 1x105
N/mm2
.)
2. Indexed Work Pind = Wind x60 / n
Pind = Indexed work in joules.
3. Head H = ∆P/ ρxg in meter
ρ= Density of water=1000 kg/m3
.
g = Specific gravity =9.81 m/s2
.
4. Efficiency = Phyd/Pel.
Phyd = Hydrualic Power in W
Pel = Electrical Power in W
5. Qt = Theoretical discharge = 2xLxAxn/60 in m3
/sec
18. 18
Where Area of the piston A= (π/4) x d2
in m2
.
d= diameter of the piston =32mm
L= Stroke length of the piston = 15mm
n = Motor speed in rpm.
6. Percentage of slip = (Qt – V)x100/Qt.
PROCEDURE:
1. Open the throttle valve and suction-side throttle valve fully.
2. Check whether the air cushion in the air vessel fills approx. half the useable
volume.
3. Tare values in the system diagram.
4. Set overflow valve to maximum set point.
5. Switch on the piston pump, set speed to 100min-1
.
6. Gradually close the throttle valve (7) until the supply pressure p2 is approx.
2 bars.
7. Save a screenshot of the system diagram in a file.
GRAPHS:
i Volume flow rate (V2) Vs Hydraulic Power (Phyd)
ii. Volume flow rate (V2) Vs Electrical Power (Pel)
iii. Volume flow rate (V2) Vs Efficiency (η)
OBSERVATIONS: d= diameter of the piston =32mm
L= Stroke length of the piston = 15mm
RESULT:
1. Maximum efficiency of the pump = ……………………… %
2. Discharge corresponding to maximum efficiency = ………….. m3
/Sec.
3. Input power corresponding to maximum efficiency = …………..W.
4. Head corresponding to maximum efficiency = ………….. meter.
5. Percentage of slip corresponding to maximum efficiency=………..
19. 19
TABULATION:
S
.
N
o
Rotat
ional
speed
(n)
(Rev
/ min)
Volume
flow
(V)
(L/min)
Suctio
n
Pressu
re (P1)
(N/m2
)
Disch
arge
Pressu
re (P2)
(N/m2
)
Elect
rical
Powe
r (Pel)
(W)
Index
ed
powe
r (Pin)
(W)
Index
work
in (J)
Wind
Pressur
e
Differe
nce
(∆P)
(bar)
Hea
d
(H)
(M)
Hydrau
lic
Power
(Phyd)(
W)
Effic
ienc
y (η)
(%)
Theoretica
l
Discharge
(Qt) (m3
/s)
% of
Slip
1 94 1.03 -0.08 1.93 55.2 3.6 2.23 2.01 20.5 3.45 6.25 3.8 x10-5
53.4
MODEL CALCULATIONS:
1. Phyd= ∆P xV = 2.01x105
x1.03x0.001/60 =3.45 W
2. Wind = Pind x60 / n = 3.6x60/94=2.23 J
3. H = ∆P/ (ρxg) =2.01x105
/ (1000x9.81) = 20.5 m
4. η=Phyd x100/Pel = 3.45x100/55.2 = 6.25%
5. Qt = 2xLxAxn/60 = 2x 0.015 x(π/4)x 0.0322
x 94/60 = 3.8 x10-5
m3
/Sec.
6. % slip = (Qt – V)x100/Qt.
= (3.8x10-5
– (1.03x16.67x10-6
))x100/ 3.8x10-5
= 53.46%
Fig 6. Piston pump
20. 20
7. GEAR PUMP
THEORY: A rotary gear pump consists essentially of two intermeshing spur gears
which are identical and which are surrounded by a closely fitting casing. One of
the pinions is driven directly by the prime mover while the other is allowed to
rotate freely. The fluid enters the spaces between the teeth and the casing and
moves with the teeth along the outer periphery until it reaches the outlet where it is
expelled from the pump. Each tooth of the gear acts like a piston or plunger of on
reciprocating pump and hence the pump can be termed a positive displacement
pump. Gear pump is widely used for cooling water and pressure oil to be supplied
for lubrication to motors, turbine, machine tools etc.
AIM:
To determine the characteristics of a gear pump under constant speed and
varying the discharge and obtain the best-driven conditions by drawing the
performance curves.
APPARATUS REQUIRED:
1. Gear pump setup.
2. Collecting tank
3. Stop watch
4. Meter scale
FORMULA:
1. Hydrualic Power Phyd= HxV in Watts.
∆P = P2-P1=Difference in pressure in N/m2
.
V = Volume flow rate (Discharge or Actual discharge) in m3
/sec.
(1L/min = 0.001 m3
/min) (1 min = 60 sec) (1 L/min = 16.66x10-6
m3
/sec)
(1bar = 1x105
N/mm2
)
2. Head H = ∆P/ ρxg in meter
ρ= Density of water=1000 kg/m3
.
g = Specific gravity =9.81 m/s2
.
3. Efficiency = Phyd/Pel.
Phyd = Hydrualic Power in W
Pel = Electrical Power in W
21. 21
4. Specific speed Ns = n√V/ (H)3/4
(unit less)
PROCEDURE:
1. Bleed the pump demonstrator.
2. Open valve V2 fully.
3. Use the Tare button to calibrate to zero.
4. Leave pump to turn to n=_________ rev/min.
5. Record measuring values of the suction pressure (P1), the pump outlet
pressure (P2), hydraulic and electrical power and volume flow (V).
6. Reduce the volume flow bit by bit by gradually closing valve V2 and take
the measurements according to point 5.
7. Repeat steps 5 and 6 until the volume flow is completely throttled.
8. Additional curves can be recorded with different rotational speed.
GRAPHS:
i Volume flow rate (V2) Vs Hydraulic Power (Phyd)
ii. Volume flow rate (V2) Vs Electrical Power (Pel)
iii. Volume flow rate (V2) Vs Efficiency (η)
RESULT:
1. Maximum efficiency of the pump = ……………………… %
2. Discharge corresponding to maximum efficiency = ………….. m3
/Sec.
3. Input power corresponding to maximum efficiency = …………..W.
4. Head corresponding to maximum efficiency = ………….. meter.
5. Specific speed corresponding to the flow =……………………
22. 22
TABULATION:
S
.
N
o
Rotati
onal
speed
n
(Rev
/ min)
Volu
me
flow
V
(L/mi
n)
Suctio
n
Pressu
re (P1)
(N/m2
)
Discha
rge
Pressu
re (P2 )
(N/m2
)
Temp
eratu
re
(T1)
(0
C)
Electr
ical
Power
(Pel)
(W)
Pressure
Differen
ce (∆P)
(bar)
Head
(H)
(M)
Hydraulic
Power
(Phyd) (W)
Effici
ency
(η)
(%)
Speci
fic
speed
(Ns)
-
1 600 8.7 -0.09 0.98 23.9 147 1.07 17.33 15.515 10.55 0.85
MODEL CALCULATIONS:
1. Phyd= ∆PxV = 1.07x105
x 8.7x0.001/60 =15.515 W
2. H = ∆P/ (ρxg) = 1.07x105
/(1000x9.81) = 17.33m
3. Efficiency = Phyd x100/Pel = 15.515x100/147= 10.55%
4. Specific speed Ns = n√V/ (H)3/4
= 600 x √(8.7x16.67x10-6
)/ (17.33)3/4
= 0.85
Figure. 7 Gear Oil Pump
23. 23
8. AXIAL FAN
THEORY: An axial fan is a type of a compressor that increases the pressure of the
air flowing through it. The blades of the axial flow fans force air to
move parallel to the shaft about which the blades rotate. In other words, the flow is
axially in and axially out, linearly, hence their name. The design priorities in an
axial fan revolve around the design of the propeller that creates
the pressure difference and hence the suction force that retains the flow across the
fan. The main components that need to be studied in the designing of the propeller
include the number of blades and the design of each blade. Their applications
include propellers in aircraft, helicopters, hovercrafts, ships and hydrofoils. They
are also used in wind tunnels and cooling towers.
AIM:
To identifying characteristics data, to investigate of typical dependencies
and recording the fan characteristics are three aims of our experiment
APPARATUS REQUIRED:
1. Axial fan apparatus setup.
2. Computer system.
FORMULA:
1. ρ =ρ0 x (T0/T1)x(pamb/p0)
ρ0 = 1.293 kg/m3
is air density at reference temperature at T0 = 273.15 K.
p0= 1,013 mbar,in
T1= Temperature of intake air in Kelvin. (1K = X0
C +273.15)
2. Air velocity c = √((2/ρ) x dpN) in m/sec.
dpN = Dynamic pressure in N/m2
.
3. Suction volume flow Vs = c x A in m3
/sec.
A = Area of the intake pipe in m2
.
A= (π/4) x d2
where d = diameter of intake pipe = 110 mm.
4. Power hydraulic Phyd = dpF x Vs in Watts
5. Efficiency = Phydx100/Pel.
Phyd = Hydrualic Power in W
Pel = Electrical Power in W
24. 24
PROCEDURE:
1. Tare values and enter the ambient pressure in the system diagram.
2. Select ‘Measurement Diagram’ in the program.
3. Enable new series of measurements. Make any setting for the measurement
file.
4. Switch on radial fan, select speed of ____ %
5. For the first measurement, close the throttle valve completely.
6. Wait until the displayed measurement stable. Then record measurements
(the current measurement data set is written to the measurement file). The
program is now ready for the next measurement.
7. Open the throttle valve a little bit. The position of the throttle valve is
dependent on the desired number of measurement points. Meaningful
characteristics are often obtained with 5 to 6 measurement points.
8. Repeat the steps until throttle valve is fully open.
9. Repeat the steps with the newly selected speed of 100%, save the
measurements and plot the characteristics curve using system.
OBSERVATION:
Diameter of intake pipe ……110…….. mm
GRAPHS:
Fan speed Vs Efficiency
RESULT:
1. Maximum efficiency of the pump = ……………………… %
2. Hydraulic power corresponding to maximum efficiency = …………..W.
3. Electrical power corresponding to maximum efficiency = …………..W
4. Air velocity corresponding to maximum efficiency = …………..m/s
5. Suction volume flow corresponding to maximum efficiency = …….. m3
/Sec
25. 25
TABULATION:
S.
N
o
Fan
speed
(n)
(Rev/
min)
Differe
ntial
Pressu
re flow
(dpN)
(N/m2
)
Pressu
re
increas
e (dpF )
(N/m2
)
Tempe
rature
of
intake
air (T1)
(0
C)
Elect
rical
Powe
r (Pel)
(W)
Ambie
nt
pressur
e (pamb)
(mbar)
Density
of
intake
air (ρ)
(Kg/m3
)
Air
Velo
city
(c)
(m/
sec)
Suction
volume
flow
(Vc)
(m3
/
sec)
Power
hydru
alic
(Phyd)
(W)
Effic
ienc
y (η)
(%)
1 9602 364 394 20.4 78.4 1013 1.203 7.8 0.7412 29.2 37.2
MODEL CALCULATIONS:
1. ρ =ρ0 x (T0/T1)(pamb/p0) = 1.293x (273.15/293.55)x(1013/1013) =1.203kg/m3
.
2. c = √((2/ρ) x dpN) = √((2/1.203) x 36.4) =7.8 m/s
3. Vs = c x A =7.8 x (π/4) x 0.112
=0.07412 m3
/s = 266.8 m3
/hr .
4. Phyd = dpF x Vs = 394x0.07412 =29.2 W
5. Efficiency = Phydx100/Pel = 29.2/78.4 = 37.2%
Main components
M = Drive motor dpF = Differential pressure, radial fan
V-R = Axial fan dpN = Differential pressure, inflow
V1 = Throttle valve n = Speed
Pel = Electrical power of the drive motor T1= Temperature of the intake air
26. 26
9. RADIAL FAN
THEORY: A mine fan (or radial flow fan) in which the air enters along the axis
parallel to the shaft and is turned through a right angle by the blades and
discharged radially. There are three main types with (1) backwardly inclined
blades; (2) radial blades; and (3) forward curved blades. In (2) and (3) the blades
are made of sheet steel, while in (1) the present tendency is to replace curved
sheet-steel blades by blades of aerofoil cross section. The aerofoil bladed radial-
flow fan has an efficiency of about 90%.
AIM:
To determine the efficiency of the radial fan in constant speed condition and
plot the necessary chart.
APPARATUS REQUIRED:
3. Radial fan apparatus setup.
4. Computer system.
FORMULA:
1. Density of intake air ρ =ρ0 x (T0/T1)x(pamb/p0)
ρ0 = 1,293 kg/m3
is air density at reference temperature at T0 = 273.15 K.
p0= 1,013 mbar.
T1= Temperature of intake air in Kelvin. (1K = X0
C +273.15)
2. Air velocity c = √((2/ρ) x dpN) in m/sec.
dpN = Dynamic pressure in N/m2
.
3. Suction volume flow Vs = c x A in m3
/sec.
A = Area of the intake pipe in m2
.
A= (π/4) x d2
where d = diameter of intake pipe = 90 mm.
4. Power hydraulic Phyd = dpF x Vs in Watts
5. Efficiency = Phyd/Pel.
Phyd = Hydrualic Power in W
Pel = Electrical Power in W
27. 27
PROCEDURE:
1. Tare values and enter the ambient pressure in the system diagram.
2. Select ‘Measurement Diagram’ in the program.
3. Enable new series of measurements. Make any setting for the measurement
file.
4. Switch on radial fan, select speed of ____ %
5. For the first measurement, close the throttle valve completely.
6. Wait until the displayed measurement stable. Then record measurements
(the current measurement data set is written to the measurement file). The
program is now ready for the next measurement.
7. Open the throttle valve a little bit. The position of the throttle valve is
dependent on the desired number of measurement points. Meaningful
characteristics are often obtained with 5 to 6 measurement points.
8. Repeat the steps until throttle valve is fully open.
9. Repeat the steps with the newly selected speed of 100%, save the
measurements and plot the characteristics curve using system.
GRAPHS:
Speed in rpm Vs suction volume.
OBSERVATION: Diameter of intake pipe (d) = ……90…….. mm
RESULT:
1. Maximum efficiency of the pump = ……………………… %
2. Hydraulic power corresponding to maximum efficiency = …………..W.
3. Electrical power corresponding to maximum efficiency = …………..W
4. Air velocity corresponding to maximum efficiency = …………..m/s
5. Suction volume flow corresponding to maximum efficiency = …….. m3
/Sec
28. 28
TABULATION:
S.
N
o
Fan
speed
(n)
(Rev/
min)
Differe
ntial
Pressu
re flow
(dpN)
(N/m2
)
Pressur
e
increas
e (dpF )
(N/m2
)
Tempe
rature
of
intake
air (T1)
(0
C)
Elect
rical
Powe
r (Pel)
(W)
Ambie
nt
pressur
e (pamb)
(mbar)
Density
of intake
air (ρ)
(Kg/m3
)
Air
Velo
city
(c)
(m/
sec)
Suction
volume
flow
(Vc)
(m3
/
sec)
Power
hydru
alic
(Phyd)
(W)
Effici
ency
(η)
(%)
1 2640 22.2 250 25 55.1 1013 1.184 6.12 0.04 10 18.15
MODEL CALCULATIONS:
1. ρ =ρ0 x (T0/T1)(pamb/p0) = 1.293x (273.15/298.15)x(1013/1013) =1.184kg/m3
.
2. c = √((2/ρ) x dpN) = √((2/1.184) x 22.2) =6.12 m/s
3. Vs = c x A =6.12 x (π/4) x 0.092
=0.04 m3
/s = 140.16 m3
/hr .
4. Phyd = dpF x Vs = 250x0.04 =10 W
5. Efficiency = Phydx100/Pel = 10x100/55.1 = 18.15%.
Figure 9. Radial fan
Main components
M = Drive motor dpF = Differential pressure, radial fan
V-R = Radial fan dpN = Differential pressure, inflow
V1 = Throttle valve n = Speed
Pel = Electrical power of the drive motor T1= Temperature of the intake air
29. 29
10. TUBULAR HEAT EXCHANGER (PARRALLEL FLOW)
THEORY: A heat exchanger is a device used to transfer heat between one or more
fluids. The fluids may be separated by a solid wall to prevent mixing or they may
be in direct contact.[1]
They are widely used in space heating, refrigeration, air
conditioning, power stations, chemical plants, petrochemical plants, petroleum
refineries, natural-gas processing, and sewage treatment. The classic example of a
heat exchanger is found in an internal combustion engine in which a circulating
fluid known as engine coolant flows through radiator coils and air flows past the
coils, which cools the coolant and heats the incoming air. There are several types
heat exchanger shell and tube heat exchanger and plate type heat exchanger etc.
AIM: Parameter determination of the tubular heat exchanger in parallel flow of
water.
APPARATUS REQUIRED:
1. Tubular heat exchanger setup.
2. Water tank.
FORMULA:
1. LMTD = Logarithmic Mean Temperature Difference.
LMTD = [Thi –Tci]- [Tho – Tco] / {ln [(Thi- Tci)/(Tho- Tco)]}
Where Tci = T6 = Entry temperature of cold fluid in Kelvin.
Thi = T1 = Entry temperature of hot fluid in Kelvin.
Tco = T4 = Exit temperature of cold fluid in Kelvin.
Tho = T3 = Exit temperature of hot fluid in Kelvin.
2. Qh = Heat transfer rate from hot water in KJ = mh x Cph [Thi – Tho]
Where mh = Mass flow rate of hot water [Kg/s]
Cph = Specific heat of hot water [KJ/KgK] = 4.187 KJ/KgK
3. Qc = Heat Transfer rate to the cold water = mc x Cpc [Tco- Tci]
Where mc = Mass flow rate of cold water [Kg/s]
Cpc = Specific heat of cold water [KJ/KgK] =4.187 KJ/KgK
4. Q = Heat transfer rate in Watts = [Qh + Qc] / 2
5. U = Overall Heat transfer co-efficient W/m2K = Q/(A x[ΔT]M)
30. 30
Where [ΔT]M = LMTD
A = Area = πdl
6. Cr = Cmin/ Cmax
Ch = Cph x mh
Cc = Cpc x mc
In Cc , Ch which is minimum called Cmin and which is maximum called Cmax.
7. NTU = No of transfer units = Ux A/ Cmin
1- exp [ - NTU x (1+ Cr)]
8. Effectiveness E = ------------------------------------
1+ Cr
PROCEDURE:
1. Give the necessary connection to the set up.
2. Heat the water in the setup using heater.
3. Give the flow of hot water and cold water using the valve according to the
diagram. Note down the flow rate of hot and cold water.
4. Now the change in temperatures take place, note down the temperatures
after the change in temperatures reaches a steady value
5. Repeat the process of for other flow rates.
6. Tabulate the value and plot the graph.
GRAPHS: Heat transfer rate Vs Effectiveness.
Observation:
Overall length (L) = ……..560…….. mm.
Diameter (D) = ………..7…….. mm.
RESULT:
1. Heat transfer rate (Q)= _______________ W
2. Overall heat transfer coefficient (U)= _____________ W/m2
k.
3. Effectiveness (E) = ___________ .
31. 31
TABULATION:
S
.
N
o
Flow rate
of Hot
water
Flow rate
of Cold
water
Inlet
temp of
hot
water
(Thi)
(T1)
outlet
temp of
hot water
(Tho) (T3)
Inlet
temp of
cold
water
(Tci)
(T6)
Outlet
temp of
hot water
(Tco)
(T4) LMT
D
Hea
t
tran
sfer
rate
(Q)
Ove
r all
heat
tran
sfer
coef
ficie
nt
(U)
Effe
ctiv
enes
s
(E)
L/hr Kg /s
L/mi
n
Kg /s 0
C K 0
C K 0
C K 0
C K
1 144 .04 120 .0333 56 329 45 318 34 307 39 312 12.31 1.27 8.4 .403
MODEL CALCULATIONS:
LMTD = [Thi – Tci] - [Tho – Tco] / ln [Thi – Tci/Tho – Tco]
= [329 – 307] – [318 – 312] / ln [(329 – 307) / (318 – 312)]= 12.31 K.
Qh = mh x Cph [Thi – Tho] = 0.04 x 4.187 x [329 – 318] = 1.842 KJ/sec.
Qc = mc x cpc [Tco –Tci]= 0.0333 x 4.187 [312 – 307] = 0.691 KJ/sec.
Q = [Qh + Qc] / 2 = [1.842 + 0.691] / 2 = 1.27 KJ/sec.
A = π x D x L= π x 0.007 x 0.56= 0.0123 m2
.
U = Q/(A x[ΔT]M)= 1.27 / (0.0123 x 12.31)= 8.4 W/m2
K.
Cr = Cmin/ Cmax = 0.14/0.167= 0.8383
Ch = Cph x mh = 4.187 x 0.04= 0.167 = Cmax
Cc = Cpc x mc = 4.187 x 0,0333= 0.140 = Cmin
33. 33
11. TUBULAR HEAT EXCHANGER (COUNTER FLOW)
THEORY: A heat exchangers are classified parallel flow and counter flow based
on the direction of both the fluids flow. In parallel flow heat exchanger both the
fluids (hot and cold) are flowing in the same direction. But in counter flow heat
exchanger both the fluids are flowing in the opposite direction.
AIM: Parameter determination of the tubular heat exchanger in counter flow of
water.
APPARATUS REQUIRED:
1. Tubular heat exchanger setup.
2. Water tank.
FORMULA:
1. LMTD = Logarithmic Mean Temperature Difference.
LMTD = [Thi –Tci]- [Tho – Tco] / {ln [(Thi- Tci)/(Tho- Tco)]}
Where Tci = T4 = Entry temperature of cold fluid in Kelvin.
Thi = T1 = Entry temperature of hot fluid in Kelvin.
Tco = T6 = Exit temperature of cold fluid in Kelvin.
Tho = T3 = Exit temperature of hot fluid in Kelvin.
2. Qh = Heat transfer rate from hot water in KJ = mh x Cph [Thi – Tho]
Where mh = Mass flow rate of hot water [Kg/s]
Cph = Specific heat of hot water [KJ/KgK] = 4.187 KJ/KgK
3. Qc = Heat Transfer rate to the cold water = mc x Cpc [Tco- Tci]
Where mc = Mass flow rate of cold water [Kg/s]
Cpc = Specific heat of cold water [KJ/KgK] =4.187 KJ/KgK
4. Q = Heat transfer rate in Watts = [Qh + Qc] / 2
5. U = Overall Heat transfer co-efficient W/m2K = Q/(A x[ΔT]M)
Where [ΔT]M = LMTD
A = Area = πdl
6. Cr = Cmin/ Cmax
Ch = Cph x mh
34. 34
Cc = Cpc x mc
In Cc , Ch which is minimum called Cmin and which is maximum called Cmax.
7. NTU = No of transfer units = Ux A/ Cmin
1- exp [ - NTU x (1- Cr)]
8. Effectiveness E = -------------------------------------------
1- {Cr xexp [ - NTU x (1- Cr)]}
PROCEDURE:
1. Give the necessary connection to the set up.
2. Heat the water in the setup using heater.
3. Give the flow of hot water and cold water using the valve according to the
diagram. Note down the flow rate of hot and cold water.
4. Now the change in temperatures take place, note down the temperatures
after the change in temperatures reaches a steady value
5. Repeat the process of for other flow rates.
6. Tabulate the value and plot the graph.
GRAPHS: Heat transfer rate Vs Effectiveness.
Observation:
Overall length (L) = ……..560…….. mm.
Diameter (D) = ………..7…….. mm.
RESULT:
1. Heat transfer rate (Q)= _______________ W
2. Overall heat transfer coefficient (U)= _____________ W/m2
k.
3. Effectiveness (E) = ___________ .
35. 35
TABULATION:
S.
N
o
Flow rate
of Hot
water
Flow rate
of Cold
water
Inlet
temp of
hot
water
(Thi)
(T1)
outlet
temp of
hot
water
(Tho)
(T3)
Inlet
temp of
cold
water
(Tci)
(T4)
Outlet
temp of
hot
water
(Tco)
(T6)
LMT
D
Hea
t
tran
sfer
rate
(Q)
Over
all
heat
trans
fer
coeff
icien
t (U)
Effe
ctiv
enes
s
L/h
r
Kg /s L/hr Kg /s 0
C K 0
C K 0
C K 0
C K
1 288 .08 191 .053 82 355 57 330 35 308 51 324 26.24 5.95 18.43 0.44
MODEL CALCULATIONS:
LMTD = [Thi – Tci] - [Tho – Tco] / ln [Thi – Tci/Tho – Tco]
= [355 – 324] – [330 – 308] / ln [(355 – 324) / (330 – 308)]= 26.24 K.
Qh = mh x Cph [Thi – Tho] = 800 x 10-4
x 4.187 x [355 – 330] = 8.347 KJ/sec.
Qc = mc x cpc [Tco –Tci]= 0.053 x 10-4
x 4.187 [32 4 – 308] = 3.551 KJ/sec.
Q = [Qh + Qc] / 2 = [8.347 + 3.551] / 2 = 5.95 KJ/sec.
A = π x D x L= π x 0.007 x 0.56= 0.0123 m2
.
U = Q/(A x[ΔT]M)= 5.95 / (0.0123 x 26.24)= 18.4352 W/m2
K.
Cr = Cmin/ Cmax = 0.335/0.222 = 1.51
Ch = Cph x mh = 4.187 x 0.08 = 0.335 = Cmax
Cc = Cpc x mc = 4.187 x 0.053 = 0.222 = Cmin
NTU = Ux A/ Cmin = 18.4352x0.0123/ 0.222 = 1.02.
36. 36
1- exp [ - NTU x (1- Cr)] 1- exp [- 1.02 x -0.51]
E = -------------------------------------- = -------------------------------------- = 0.44
1- {Cr xexp [ - NTU x (1- Cr)]} 1- {1.51xexp [- 1.02 x -0.51]}
Fig 13. Counter Flow Tubular Heat Exchanger
37. 37
12. AIR COMPRESSOR
THEORY: An air compressor is a device that converts power (using an electric
motor, diesel or gasoline engine, etc.) into potential energy stored in pressurized air
(i.e., compressed air). This air compressor is a two stage reciprocating type. The air
is sucked from atmosphere and compressed in the first cylinder. The compressed
air then passes through an inter cooler into the second stage cylinder, where it is
further compressed. The compressed air then goes to a reservoir through a safety
valve. This valve operates an electrical switch that shuts off the motor when the
pressure exceeds the set limit.
AIM: To conduct a performance test on a two stage air compressor and determine
its volumetric efficiency.
APPARATUS REQUIRED:
1.Two stage air compressor apparatus.
2. Stop watch
FORMULA:
1. Volume V0 = Ad x√(2x∆p/ρ) ) in m3
.
Ad = Area of the duct= 1.131x10-4
m2
.
ρ = Density of air =1.293 kg/m3
.
(1bar = 1x105
N/m2
) (1mbar = 1x10-3
bar) (1Pa = 1N/m2
)
2. Isothermal power Piso = p1V0 ln (p4/p1)
3. Efficiency = Piso/Pel.
Pel = Electrical Power in W
1 p1 - Inlet pressure
2 T1 - Inlet temperature
3 p2 - Pressure after 1st compressor stage
4 T2-Temperature after 1st compressor stage
5 p4-Pressure vessel pressure
6 T3-Temperature before 2nd compressor stage
7 ∆p-Differential pressure across Venturi nozzle
8 T4-Temperature after 2nd compressor stage
38. 38
PROCEDURE:
1. Close the outlet valve.
2. Switch on compressor (see Section 2.4) If it does not start up, it is possible
that the over-current protection switch may have cut out directly on the
motor - restart.
3. Allow the system to run, until a constant pressure p3 has built up, set the
desired final pressure with the bleeder valve and record the measured values.
4. Tabulate the value and plot the graph.
GRAPHS:
Pressure Vs Volume
OBSERVATION: Area of duct inlet= ……1.131x10-4
m2
…….
RESULT:
1. Maximum efficiency of the compressor = ……………………… %
2. Isothermal power corresponding to maximum efficiency = …………..W.
3. Electrical power corresponding to maximum efficiency = …………..W
4. Volume flow rate V0
at maximum efficiency = …………………l/min
39. 39
TABULATION:
S.
No
p1 T1 p2 T2 T3 p4 T4 ∆p V0
Pelec Tim
e
Piso η
Un
it
bar 0
C bar 0
C 0
C bar 0
C mba
r
m3
/ Sec W min W %
1 0.99 23 3.4 127.1 58.8 11.7 151.6 7.4 38.26x10-4
2550 3 935.43 36.7
MODEL CALCULATIONS:
1. V0 = Ad x√(2x∆p/ρ) ) = 1.131X10-4
x(√(2x7.4/1.293) ) = 38.26x10-4
m3
/s.
2. Piso = p1V0 ln (p4/p1) = 0.99x105
x38.26x10-4
xln(11.7x105
/0.99x105
) =935.43W
3. η = Pisox100/Pel = 935.43x100/2550 =36.7%.
Fig 12 Air compressor
40. 40
13. MULTI PURPOSE AIRDUCT
THEORY: There are various forms of heat transport: Convection is the transport
of heat by a moving fluid. Example: In forced convection, a conveying unit (pump,
blower) moves the fluid to be heated or cooled along the surfaces of a heat
exchanger. Thermal radiation is energy emitted by electromagnetic waves.
Example: Thermal radiation from the sun. Conduction is kinetic energy being
transported between two neighboring atoms or molecules. Example: A refrigerator
is insulated to prevent conduction.
Convective heat transfer takes part in heat exchangers and plays a large role in
many areas of industry. There are many different forms of heat exchangers which
transfer heat from one medium to another. Convective heat transfer in heat
exchangers can take place according to different principles: Parallel flow,
Counterflow, Cross-flow.
The Multipurpose Air Duct and Heat Transfer Unit WL 312 offers an excellent
supplement for calculations. It can be used to determine convective heat transfer on
an experimental basis. It provides a view of industrial applications with the
possibility of installing different types of heat exchangers with different heat
transfer media.
AIM: To determine the flow velocity and volume flow rate in multipurpose air
duct.
APPARATUS REQUIRED:
1. Air duct compressor apparatus.
2. Stop watch
FORMULA:
1. Velocity c = √(2xpdyn/ρ) ) in m/sec.
pdyn = Differential pressure between the ambient air and air duct (PD1) in mbar.
ρ = Density of air =1.293 kg/m3
.
(1bar = 1x105
N/m2
) (1mbar = 1x10-3
bar) (1Pa = 1N/m2
)
2. Volume flow rate V = c xAd in m3
/sec.
Ad= Area of duct inlet in m2
= hdx bd.
hd = Height of the duct in mm.
bd = Width of the duct in mm.
41. 41
PROCEDURE:
1. Place the throttle valve in a position that is vertical (90°) to the air flow. This
ensures that the maximum possible flow rate of the fan is achieved, since the
resistance is at its lowest level on the pressure side.
2. Switch on the fan.
3. Read the dynamic pressure (which is a proportion of the flow velocity in the air
duct) on the digital display with the differential pressure sign (flow).
4. Change the position of the throttle valve in order to obtain a different dynamic
pressure (flow rate).
GRAPHS:
Pressure Vs Velocity
OBSERVATION: hd = Height of the duct …290…. mm.
bd = Width of the duct …150…mm.
RESULT:
1. Maximum Velocity of air in duct = ……………. m/s
2. Maximum flow rate of air in duct=……………... m3
/s
3. Angle of opening of throttle valve at Maximum flow rate of air in
duct=……………... 0
42. 42
TABULATION:
S.No Throttle valve
Position in °
Dynamic
pressure
pdyn
in mbar
Flow velocity
c
in m/s
Flow rate
V in m³/Sec
1 90 0.873 12.1 0.505
MODEL CALCULATIONS:
4. Ad = hdx bd = 0.29x0.15= 0.0435 m2
.
5. c = √(2xpdyn/ρ) ) = (√(2x0.873x105
x10-3
/1.293) ) = 11.62 m/s.
6. V = c xAd = 11.62x0.0435=0.505 m3
/sec.
Switch Cabin Test section
Throttle valve Fig 13. Air duct Air inlet