This article summarizes an experiment that investigated the effect of tube diameter and surface roughness on fluid flow friction factors. Three tubes were tested: a 1.14 mm diameter stainless steel tube, a 17 mm diameter smooth PVC tube, and a 15.5 mm diameter rough PVC tube coated internally with sand. The stainless steel tube results agreed with theoretical predictions. The 17 mm tube results deviated from theory likely due to the lack of a calming section. The rough 15.5 mm tube results showed friction factors were not significantly affected by Reynolds number in turbulent regimes and reasonably agreed with theoretical predictions, indicating diameter decrease has an insignificant effect on friction factor.
This document describes an experiment conducted to determine the friction factor of water flowing through a pipe. The experiment measured the volumetric flow rate, velocity, temperature, and pressure drop of water flowing through a pipe. These measurements were used to calculate the Reynolds number, theoretical friction factor based on equations, and experimental friction factor. The results showed that at higher Reynolds numbers, the friction factor was lower, following trends in friction factor charts. Sources of error included inaccurate measurements of pressure drop and flow time. The experiment demonstrated how friction factor depends inversely on Reynolds number for turbulent flow in a pipe.
This document summarizes an experiment on frictional head losses in pipes. The experiment measured pressure drops across different pipe sections and an orifice meter to calculate the Fanning friction factor, Reynolds number, and orifice meter discharge coefficient. Key findings included: 1) Fanning friction factor and Reynolds number trends matched expectations; 2) the calculated pipe roughness was much higher than expected, likely due to pressure measurement errors; and 3) the orifice meter coefficient of 0.75 was reasonable compared to the accepted range of 0.6-0.65. The document concluded the experiment achieved its objectives but noted areas for improvement.
,friction pipe ,friction loss along a pipe ,pipe ,along a ,loss along ,loss along a ,friction loss ,friction loss along a ,loss along a pipe ,along a pipe ,friction loss alon ,friction loss along a p ,loss along a pip
Head losses
Major Losses
Minor Losses
Definition • Dimensional Analysis • Types • Darcy Weisbech Equation • Major Losses • Minor Losses • Causes Head Losses
3. • Head loss is loss of energy per unit weight. • Head = Energy of Fluid / Weight • Head losses can be – Kinetic Head – Potential Head – Pressure Head 6/10/2015 4Danial Gondal Head Loss
4. • Kinetic Head – K.H. = kinetic energy / Weight = v² /2g • Potential Head – P.H = Potential Energy / Weight = mgz /mg = z • Pressure Head – P.H = P/ ρ g 6/10/2015 5
5. • (P/ ρ g) + (v² /2g ) + (z) = constant • (FL-2F-1L3LT-2L-1T2) + (L2T-2L1T2)+(L) = constant • (L) + (L) + (L) = constant • As L represent height so it is dimensionally L. 6/10/2015 6 Dimensional Analysis
6. • However the equation (P/ ρ g) + (v² /2g ) + (z) = constant Is valid for Bernoulli's Inviscid flow case. As we are studying viscous flow so (P1/ ρ g) + (v1² /2g ) + (z1) = EGL1(Energy Grade Line At point 1) (P2/ ρ g) + (v2² /2g ) + (z2) = EGL2(Energy Grade Line At point 2) 6/10/2015 7 Head Loss
7. • For Inviscid Flow EGL1 - EGL2= 0 • For Viscous Flow EGL1 - EGL2= Hf 6/10/2015 8 Head Loss
8. MAJOR LOSSES IN PIPES
9. •Friction loss is the loss of energy or “head” that occurs in pipe flow due to viscous effects generated by the surface of the pipe. • Friction Loss is considered as a "major loss" •In mechanical systems such as internal combustion engines, it refers to the power lost overcoming the friction between two moving surfaces. •This energy drop is dependent on the wall shear stress (τ) between the fluid and pipe surface. 6/10/2015 10 Friction Loss
10. •The shear stress of a flow is also dependent on whether the flow is turbulent or laminar. •For turbulent flow, the pressure drop is dependent on the roughness of the surface. •In laminar flow, the roughness effects of the wall are negligible because, in turbulent flow, a thin viscous layer is formed near the pipe surface that causes a loss in energy, while in laminar flow, this viscous layer is non-existent. 6/10/2015 11 Friction Loss
11. Frictional head losses are losses due to shear stress on the pipe walls. The general equation for head loss due to friction is the Darcy-Weisbach equation, which is where f = Darcy-Weisbach friction factor, L = length of pipe, D = pipe diameter, and V = cross sectional average flow velocity.
The document provides tables showing water flow rates through various types and diameters of pipes. It gives flow rates in cubic feet and gallons per minute for Type L and K copper tubing, Schedule 40 and 80 PVC pipes, and various diameter steel pipes. It also includes frequently asked questions about determining pipe types, guidelines for maximum water velocities in pipes, and equations for calculating flow rates and velocities.
CE6451 Fluid Mechanics and Machinery Unit 2P Manimaran
This document discusses boundary layer theory and flow through pipes. It defines boundary layer, boundary layer thickness, and the types of boundary layer thickness. It also discusses major and minor losses that occur in pipes due to friction or changes in flow direction or geometry. Pipes can be connected in series or parallel configurations. Moody's diagram is introduced to determine friction factor from Reynolds number and relative roughness.
When fluid flows through pipes, there are two types of losses - minor and major losses. Major losses are due to friction along the pipe walls and are quantified using the Darcy-Weisbach equation. The Darcy friction coefficient f depends on both the Reynolds number Re and the relative roughness κ/D. Plotting log f versus log Re for different pipes allows identification of the three sub-regions of turbulent flow - smooth, rough, and transitional - and how f varies in each sub-region.
This document summarizes an experiment that investigates the relationship between water pressure and flow rate. Water was flowed from a container through a small hole for timed intervals at varying water heights, and the resulting flow rate was measured. The data showed a proportional relationship between pressure difference and squared flow rate, supporting Bernoulli's equation. The slope of the line of best fit remained constant, as expected for this experimental setup. Limitations included the assumption of zero kinetic energy and challenges closing the hole precisely.
This document describes an experiment conducted to determine the friction factor of water flowing through a pipe. The experiment measured the volumetric flow rate, velocity, temperature, and pressure drop of water flowing through a pipe. These measurements were used to calculate the Reynolds number, theoretical friction factor based on equations, and experimental friction factor. The results showed that at higher Reynolds numbers, the friction factor was lower, following trends in friction factor charts. Sources of error included inaccurate measurements of pressure drop and flow time. The experiment demonstrated how friction factor depends inversely on Reynolds number for turbulent flow in a pipe.
This document summarizes an experiment on frictional head losses in pipes. The experiment measured pressure drops across different pipe sections and an orifice meter to calculate the Fanning friction factor, Reynolds number, and orifice meter discharge coefficient. Key findings included: 1) Fanning friction factor and Reynolds number trends matched expectations; 2) the calculated pipe roughness was much higher than expected, likely due to pressure measurement errors; and 3) the orifice meter coefficient of 0.75 was reasonable compared to the accepted range of 0.6-0.65. The document concluded the experiment achieved its objectives but noted areas for improvement.
,friction pipe ,friction loss along a pipe ,pipe ,along a ,loss along ,loss along a ,friction loss ,friction loss along a ,loss along a pipe ,along a pipe ,friction loss alon ,friction loss along a p ,loss along a pip
Head losses
Major Losses
Minor Losses
Definition • Dimensional Analysis • Types • Darcy Weisbech Equation • Major Losses • Minor Losses • Causes Head Losses
3. • Head loss is loss of energy per unit weight. • Head = Energy of Fluid / Weight • Head losses can be – Kinetic Head – Potential Head – Pressure Head 6/10/2015 4Danial Gondal Head Loss
4. • Kinetic Head – K.H. = kinetic energy / Weight = v² /2g • Potential Head – P.H = Potential Energy / Weight = mgz /mg = z • Pressure Head – P.H = P/ ρ g 6/10/2015 5
5. • (P/ ρ g) + (v² /2g ) + (z) = constant • (FL-2F-1L3LT-2L-1T2) + (L2T-2L1T2)+(L) = constant • (L) + (L) + (L) = constant • As L represent height so it is dimensionally L. 6/10/2015 6 Dimensional Analysis
6. • However the equation (P/ ρ g) + (v² /2g ) + (z) = constant Is valid for Bernoulli's Inviscid flow case. As we are studying viscous flow so (P1/ ρ g) + (v1² /2g ) + (z1) = EGL1(Energy Grade Line At point 1) (P2/ ρ g) + (v2² /2g ) + (z2) = EGL2(Energy Grade Line At point 2) 6/10/2015 7 Head Loss
7. • For Inviscid Flow EGL1 - EGL2= 0 • For Viscous Flow EGL1 - EGL2= Hf 6/10/2015 8 Head Loss
8. MAJOR LOSSES IN PIPES
9. •Friction loss is the loss of energy or “head” that occurs in pipe flow due to viscous effects generated by the surface of the pipe. • Friction Loss is considered as a "major loss" •In mechanical systems such as internal combustion engines, it refers to the power lost overcoming the friction between two moving surfaces. •This energy drop is dependent on the wall shear stress (τ) between the fluid and pipe surface. 6/10/2015 10 Friction Loss
10. •The shear stress of a flow is also dependent on whether the flow is turbulent or laminar. •For turbulent flow, the pressure drop is dependent on the roughness of the surface. •In laminar flow, the roughness effects of the wall are negligible because, in turbulent flow, a thin viscous layer is formed near the pipe surface that causes a loss in energy, while in laminar flow, this viscous layer is non-existent. 6/10/2015 11 Friction Loss
11. Frictional head losses are losses due to shear stress on the pipe walls. The general equation for head loss due to friction is the Darcy-Weisbach equation, which is where f = Darcy-Weisbach friction factor, L = length of pipe, D = pipe diameter, and V = cross sectional average flow velocity.
The document provides tables showing water flow rates through various types and diameters of pipes. It gives flow rates in cubic feet and gallons per minute for Type L and K copper tubing, Schedule 40 and 80 PVC pipes, and various diameter steel pipes. It also includes frequently asked questions about determining pipe types, guidelines for maximum water velocities in pipes, and equations for calculating flow rates and velocities.
CE6451 Fluid Mechanics and Machinery Unit 2P Manimaran
This document discusses boundary layer theory and flow through pipes. It defines boundary layer, boundary layer thickness, and the types of boundary layer thickness. It also discusses major and minor losses that occur in pipes due to friction or changes in flow direction or geometry. Pipes can be connected in series or parallel configurations. Moody's diagram is introduced to determine friction factor from Reynolds number and relative roughness.
When fluid flows through pipes, there are two types of losses - minor and major losses. Major losses are due to friction along the pipe walls and are quantified using the Darcy-Weisbach equation. The Darcy friction coefficient f depends on both the Reynolds number Re and the relative roughness κ/D. Plotting log f versus log Re for different pipes allows identification of the three sub-regions of turbulent flow - smooth, rough, and transitional - and how f varies in each sub-region.
This document summarizes an experiment that investigates the relationship between water pressure and flow rate. Water was flowed from a container through a small hole for timed intervals at varying water heights, and the resulting flow rate was measured. The data showed a proportional relationship between pressure difference and squared flow rate, supporting Bernoulli's equation. The slope of the line of best fit remained constant, as expected for this experimental setup. Limitations included the assumption of zero kinetic energy and challenges closing the hole precisely.
This document provides guidance on designing irrigation systems. It discusses key concepts like water flow in pipes, hydrostatic pressure, head loss, and lateral pipe characteristics. The document presents examples calculating water velocity, flow rate, pipe diameter, and pressure under different system configurations. It also examines alternatives for designing manifolds and subplots. The overall aim is to provide practical methods for laying out any pressure irrigation system based on hydraulic principles.
Fluid Mechanics-Shear stress ,Shear stress distribution,Velocity profile,Flow Of Viscous Fluid Through The circular pipe ,Velocity profile for turbulent flow Boundary layer buildup in pipe,Velocity Distributions
8. fm 9 flow in pipes major loses co 3 copyZaza Eureka
This document provides an overview of fluid mechanics concepts related to flow in pipes over 3 weeks. It discusses laminar and turbulent flow, identifies the types of flow using the Reynolds number, and explains major and minor losses for flow in pipes. The key points are:
- There are two types of flow - internal (in pipes) and external (over bodies). Internal flow examples include water pipes, blood flow, and HVAC systems.
- Flow can be laminar, turbulent, or in transition as determined by the Reynolds number. The continuity, Bernoulli, and momentum equations govern pipe flow.
- Major losses are pressure/head losses due solely to pipe friction. They can be calculated using the Darcy-
This document discusses flow through pipes, including:
- Laminar and turbulent flow characteristics defined by Reynolds number
- Head losses calculated using Darcy-Weisbach and minor loss equations
- Friction factors determined from Moody diagrams for laminar and turbulent flows
- Total head loss in a pipe system equals major losses in pipe sections plus minor losses from fittings
This document provides an introduction and overview of a thesis investigating minor water loss and head loss coefficients in locally available PVC pipes with 90-degree bends of different dimensions. It discusses the purpose of determining minor loss coefficients for local pipes, which are not currently available. The document outlines previous related works and the structure of the thesis, which will present experimental results and findings to help establish more convenient use of local pipes in local industries.
This experiment aimed to determine the Reynolds number (NRe) as a function of flow rate for liquid flowing through a circular pipe. NRe was calculated for 6 trials with increasing flow rates. All trials had NRe below 2100, indicating laminar flow as observed by the smooth movement of dye in the pipe. As flow rate increased, NRe also increased but remained in the laminar flow regime. The results show that flow type depends on NRe, with laminar flow occurring at low velocities (NRe < 2100).
This document provides an overview of fluid mechanics concepts related to flow through pipes. It discusses different types of head losses that can occur through pipes including major losses due to friction and minor losses due to fittings. It also covers topics such as hydraulic grade line, pipes in series and parallel, syphons, power transmission through pipes, flow through nozzles, and water hammer effects in pipes.
This document discusses fluid flow in pipes and provides examples of applying Bernoulli's equation to solve fluid mechanics problems involving pipe flow. It begins by introducing key concepts of pipe flow, such as average velocity, laminar flow profiles, and the use of circular pipes to withstand pressure differences. Several example problems are then presented and solved using Bernoulli's equation to determine velocities, pressure changes, and discharge rates for incompressible, steady pipe flows.
Calculation of Flowrate and Pressure Drop Relationship for Laminar Flow using...Usman Shah
This document discusses the relationships between flow rate, pressure drop, and shear stress for laminar flow in pipes. It provides equations to calculate flow rate from shear stress and pressure drop data. The key relationships are:
1) Pressure drop is directly proportional to flow rate for laminar flow.
2) Shear stress at the wall is related to pressure drop by an equation involving pipe diameter and length.
3) Shear stress decreases linearly from the wall to the center of the pipe in laminar flow.
4) The flow rate can be calculated from experimentally measured shear stress and pressure drop data using integration methods like Simpson's rule.
Pipe Flow Friction factor in fluid mechanicsUsman Shah
This slide will explain you the chemical engineering terms .Al about the basics of this slide are explain in it. The basics of fluid mechanics, heat transfer, chemical engineering thermodynamics, fluid motions, newtonian fluids, are explain in this process. ,education ,chemical engineerin ,chemical engineering ,fluid mechanics ,heat transfer ,chemical process principles ,macdonald ,kfc ,mazeo ,chemicals ,engineers ,cv formatin ,law ,laptop.
Basics of two phase flow (gas-liquid) line sizingVikram Sharma
This document discusses two-phase flow line sizing for liquid-gas flows in piping systems. It describes the different flow regimes that can occur using Baker's flow regime map. The key steps outlined are: 1) determining the flow regime based on fluid properties and flow rates, 2) calculating pressure drops for the liquid and gas phases separately using correlations, 3) using a multiplier to determine the two-phase pressure drop based on the flow regime, and 4) summing pressure drops from friction, elevation changes, and fittings to obtain the total pressure drop. Care must be taken to size each pipe segment separately as properties and regimes can change along the line.
The document discusses laminar and turbulent pipe flow. It states that the transition from laminar to turbulent flow depends on the dimensionless Reynolds number. It also discusses head losses due to friction in pipes and defines head loss as the equivalent height that the fluid needs to be raised to overcome frictional losses. Finally, it explains the water hammer phenomenon that can occur in pipes due to sudden changes in flow rate, describing how it generates pressure waves that travel through the pipe and can damage pipe walls.
This document discusses concepts related to fluid flow through circular conduits including:
- Laminar flow through pipes and boundary layer concepts such as boundary layer thickness.
- The Darcy-Weisbach equation for calculating head loss and how it relates to friction factor.
- The Moody diagram which plots friction factor against Reynolds number for different relative pipe roughnesses.
- Commercial pipes and how piping systems are used to transport fluids with considerations for energy loss due to friction.
This document discusses various flow measurement techniques including venturimeters, orifices, mouthpieces, pitot tubes, weirs and notches. It provides detailed explanations and equations for venturimeters and orifices. Venturimeters use the Bernoulli's equation to relate the pressure difference between two sections to the flow rate. Orifices use the relationship between head loss and flow rate. The document also defines various coefficients used in flow measurements like coefficient of contraction, velocity, and discharge. It discusses types of venturimeters and orifices based on their orientation and geometry.
The document discusses turbulent flow in pipes. It defines turbulent flow and laminar flow, and explains that the shear stress in turbulent flow is defined using eddy viscosity, which depends on the turbulence of the flow. The total shear stress in turbulent flow is the sum of the laminar shear stress and turbulent shear stress. It also discusses the viscous sublayer that exists near the wall in turbulent flow, where viscosity effects are dominant over turbulent effects. The velocity profile in fully developed turbulent pipe flow can be described by the Prandtl universal velocity distribution equation.
The document discusses fluid dynamics and Bernoulli's equation. It provides:
1) Objectives of understanding measurements of fluids in motion and applying Bernoulli's equation to calculate energy in pipes, venturi meters, and orifices.
2) An explanation of Bernoulli's equation and its components of potential, pressure, and kinetic energy.
3) Examples of applying the equation to calculate discharge in a horizontal venturi meter using measurements of pressure and height differences.
This document provides information about pipe flow and head losses in civil engineering. It discusses:
1. Types of pipe flow including steady/unsteady, uniform/non-uniform, laminar/turbulent.
2. Forces in pipe flow including pressure, gravity, inertia. Conservation equations for mass and momentum are presented.
3. Energy head in pipe flow including kinetic, pressure, and potential (elevation) heads. The Bernoulli equation relating these is derived.
Major and minor head losses are also summarized. Darcy-Weisbach equation for calculating major head losses due to pipe friction is presented.
The document is a technical report summarizing the design, construction, and testing of a microchannel heat exchanger flow loop. A flow loop was built that circulates coolant through a microchannel heat exchanger to remove heat at a rate of 100 W/cm^2, simulating a modern integrated circuit. Testing showed the measured friction factor and Nusselt number were close to theoretical predictions for developing laminar flow. The completed flow loop was approved by the advisor to serve as an experimental tool for students.
This document provides instructions and guidelines for conducting experiments in a fluid mechanics laboratory. It begins with an overview of course learning outcomes, safety procedures, and expectations for cleaning the lab space. It then discusses proper experimental methodology, including defining hypotheses, designing experiments to test hypotheses, collecting accurate and precise measurements, and analyzing results. The document emphasizes minimizing errors and uncertainties in measurements. It provides definitions for key terms like error, uncertainty, accuracy, and precision when evaluating experimental data. Finally, it outlines the content and procedures for 20 specific fluid mechanics experiments that will be conducted.
This document provides guidance on designing irrigation systems. It discusses key concepts like water flow in pipes, hydrostatic pressure, head loss, and lateral pipe characteristics. The document presents examples calculating water velocity, flow rate, pipe diameter, and pressure under different system configurations. It also examines alternatives for designing manifolds and subplots. The overall aim is to provide practical methods for laying out any pressure irrigation system based on hydraulic principles.
Fluid Mechanics-Shear stress ,Shear stress distribution,Velocity profile,Flow Of Viscous Fluid Through The circular pipe ,Velocity profile for turbulent flow Boundary layer buildup in pipe,Velocity Distributions
8. fm 9 flow in pipes major loses co 3 copyZaza Eureka
This document provides an overview of fluid mechanics concepts related to flow in pipes over 3 weeks. It discusses laminar and turbulent flow, identifies the types of flow using the Reynolds number, and explains major and minor losses for flow in pipes. The key points are:
- There are two types of flow - internal (in pipes) and external (over bodies). Internal flow examples include water pipes, blood flow, and HVAC systems.
- Flow can be laminar, turbulent, or in transition as determined by the Reynolds number. The continuity, Bernoulli, and momentum equations govern pipe flow.
- Major losses are pressure/head losses due solely to pipe friction. They can be calculated using the Darcy-
This document discusses flow through pipes, including:
- Laminar and turbulent flow characteristics defined by Reynolds number
- Head losses calculated using Darcy-Weisbach and minor loss equations
- Friction factors determined from Moody diagrams for laminar and turbulent flows
- Total head loss in a pipe system equals major losses in pipe sections plus minor losses from fittings
This document provides an introduction and overview of a thesis investigating minor water loss and head loss coefficients in locally available PVC pipes with 90-degree bends of different dimensions. It discusses the purpose of determining minor loss coefficients for local pipes, which are not currently available. The document outlines previous related works and the structure of the thesis, which will present experimental results and findings to help establish more convenient use of local pipes in local industries.
This experiment aimed to determine the Reynolds number (NRe) as a function of flow rate for liquid flowing through a circular pipe. NRe was calculated for 6 trials with increasing flow rates. All trials had NRe below 2100, indicating laminar flow as observed by the smooth movement of dye in the pipe. As flow rate increased, NRe also increased but remained in the laminar flow regime. The results show that flow type depends on NRe, with laminar flow occurring at low velocities (NRe < 2100).
This document provides an overview of fluid mechanics concepts related to flow through pipes. It discusses different types of head losses that can occur through pipes including major losses due to friction and minor losses due to fittings. It also covers topics such as hydraulic grade line, pipes in series and parallel, syphons, power transmission through pipes, flow through nozzles, and water hammer effects in pipes.
This document discusses fluid flow in pipes and provides examples of applying Bernoulli's equation to solve fluid mechanics problems involving pipe flow. It begins by introducing key concepts of pipe flow, such as average velocity, laminar flow profiles, and the use of circular pipes to withstand pressure differences. Several example problems are then presented and solved using Bernoulli's equation to determine velocities, pressure changes, and discharge rates for incompressible, steady pipe flows.
Calculation of Flowrate and Pressure Drop Relationship for Laminar Flow using...Usman Shah
This document discusses the relationships between flow rate, pressure drop, and shear stress for laminar flow in pipes. It provides equations to calculate flow rate from shear stress and pressure drop data. The key relationships are:
1) Pressure drop is directly proportional to flow rate for laminar flow.
2) Shear stress at the wall is related to pressure drop by an equation involving pipe diameter and length.
3) Shear stress decreases linearly from the wall to the center of the pipe in laminar flow.
4) The flow rate can be calculated from experimentally measured shear stress and pressure drop data using integration methods like Simpson's rule.
Pipe Flow Friction factor in fluid mechanicsUsman Shah
This slide will explain you the chemical engineering terms .Al about the basics of this slide are explain in it. The basics of fluid mechanics, heat transfer, chemical engineering thermodynamics, fluid motions, newtonian fluids, are explain in this process. ,education ,chemical engineerin ,chemical engineering ,fluid mechanics ,heat transfer ,chemical process principles ,macdonald ,kfc ,mazeo ,chemicals ,engineers ,cv formatin ,law ,laptop.
Basics of two phase flow (gas-liquid) line sizingVikram Sharma
This document discusses two-phase flow line sizing for liquid-gas flows in piping systems. It describes the different flow regimes that can occur using Baker's flow regime map. The key steps outlined are: 1) determining the flow regime based on fluid properties and flow rates, 2) calculating pressure drops for the liquid and gas phases separately using correlations, 3) using a multiplier to determine the two-phase pressure drop based on the flow regime, and 4) summing pressure drops from friction, elevation changes, and fittings to obtain the total pressure drop. Care must be taken to size each pipe segment separately as properties and regimes can change along the line.
The document discusses laminar and turbulent pipe flow. It states that the transition from laminar to turbulent flow depends on the dimensionless Reynolds number. It also discusses head losses due to friction in pipes and defines head loss as the equivalent height that the fluid needs to be raised to overcome frictional losses. Finally, it explains the water hammer phenomenon that can occur in pipes due to sudden changes in flow rate, describing how it generates pressure waves that travel through the pipe and can damage pipe walls.
This document discusses concepts related to fluid flow through circular conduits including:
- Laminar flow through pipes and boundary layer concepts such as boundary layer thickness.
- The Darcy-Weisbach equation for calculating head loss and how it relates to friction factor.
- The Moody diagram which plots friction factor against Reynolds number for different relative pipe roughnesses.
- Commercial pipes and how piping systems are used to transport fluids with considerations for energy loss due to friction.
This document discusses various flow measurement techniques including venturimeters, orifices, mouthpieces, pitot tubes, weirs and notches. It provides detailed explanations and equations for venturimeters and orifices. Venturimeters use the Bernoulli's equation to relate the pressure difference between two sections to the flow rate. Orifices use the relationship between head loss and flow rate. The document also defines various coefficients used in flow measurements like coefficient of contraction, velocity, and discharge. It discusses types of venturimeters and orifices based on their orientation and geometry.
The document discusses turbulent flow in pipes. It defines turbulent flow and laminar flow, and explains that the shear stress in turbulent flow is defined using eddy viscosity, which depends on the turbulence of the flow. The total shear stress in turbulent flow is the sum of the laminar shear stress and turbulent shear stress. It also discusses the viscous sublayer that exists near the wall in turbulent flow, where viscosity effects are dominant over turbulent effects. The velocity profile in fully developed turbulent pipe flow can be described by the Prandtl universal velocity distribution equation.
The document discusses fluid dynamics and Bernoulli's equation. It provides:
1) Objectives of understanding measurements of fluids in motion and applying Bernoulli's equation to calculate energy in pipes, venturi meters, and orifices.
2) An explanation of Bernoulli's equation and its components of potential, pressure, and kinetic energy.
3) Examples of applying the equation to calculate discharge in a horizontal venturi meter using measurements of pressure and height differences.
This document provides information about pipe flow and head losses in civil engineering. It discusses:
1. Types of pipe flow including steady/unsteady, uniform/non-uniform, laminar/turbulent.
2. Forces in pipe flow including pressure, gravity, inertia. Conservation equations for mass and momentum are presented.
3. Energy head in pipe flow including kinetic, pressure, and potential (elevation) heads. The Bernoulli equation relating these is derived.
Major and minor head losses are also summarized. Darcy-Weisbach equation for calculating major head losses due to pipe friction is presented.
The document is a technical report summarizing the design, construction, and testing of a microchannel heat exchanger flow loop. A flow loop was built that circulates coolant through a microchannel heat exchanger to remove heat at a rate of 100 W/cm^2, simulating a modern integrated circuit. Testing showed the measured friction factor and Nusselt number were close to theoretical predictions for developing laminar flow. The completed flow loop was approved by the advisor to serve as an experimental tool for students.
This document provides instructions and guidelines for conducting experiments in a fluid mechanics laboratory. It begins with an overview of course learning outcomes, safety procedures, and expectations for cleaning the lab space. It then discusses proper experimental methodology, including defining hypotheses, designing experiments to test hypotheses, collecting accurate and precise measurements, and analyzing results. The document emphasizes minimizing errors and uncertainties in measurements. It provides definitions for key terms like error, uncertainty, accuracy, and precision when evaluating experimental data. Finally, it outlines the content and procedures for 20 specific fluid mechanics experiments that will be conducted.
This document provides an overview of a process to produce 5000 barrels per day of biodiesel from microalgae. It describes cultivating the microalgae Chlorella vulgaris in 209 closed raceway ponds using flue gas from a coal power plant for CO2 and agricultural waste water. The algae biomass produced would then undergo pretreatment including dewatering before oil extraction and transesterification to produce biodiesel. Safety, sustainability, and economic considerations are also discussed at a high level. Diagrams and calculations are provided in the appendices to support the proposed design.
This document provides a design for an oil storage terminal in Gdansk, Poland. It includes the design of an input gathering pipeline and storage tank. For the storage tank, it discusses the type of tank (fixed roof), tank dimensions optimized for volume and surface area, maintaining internal conditions through temperature control coils, materials of construction (steel-reinforced concrete), and safety concerns. The gathering pipeline design addresses parameters, factors on the suction and discharge sides, pump selection, and preventing heat loss.
This document provides diagrams and descriptions of 8 pieces of equipment in the Fluid Mechanics Laboratory at the University of Gujrat's Department of Chemical Engineering. The equipment is used to demonstrate various fluid mechanics principles and phenomena, including Bernoulli's principle, losses in bends and fittings, orifice and jet velocity, Osborn Reynolds demonstration, pipe friction, pipe networks, hydrostatic pressure, and particle drag coefficients. For each apparatus, the main components are listed, with a brief 1 sentence description provided for some of the equipment.
This document describes 7 fluid mechanics laboratory equipment, including their components, technical descriptions, and applications. The equipment measure phenomena like Bernoulli's principle, pressure losses, jet velocity, laminar and turbulent flow visualization, pipe friction losses, pipe networks, and particle drag coefficients. Objectives of the experiments include demonstrating fluid dynamics concepts and measuring flow properties.
This document discusses techniques for analyzing energy losses in pipeline systems that contain components like valves, fittings, and changes in pipe size. It begins by introducing the concept of minor losses, which are energy losses caused by components other than pipe friction. Methods are provided for calculating the energy loss associated with specific minor loss elements like sudden pipe enlargements using resistance coefficients. The document lists learning objectives and provides examples of calculating minor losses for water flowing through a pipe enlargement.
This document describes an experiment to characterize a centrifugal pump by measuring its performance characteristics at constant speed. Key parameters such as discharge, head, input and output power are measured across a range of operating conditions created by throttling the delivery valve. The measurements are used to calculate efficiency and draw characteristic curves showing relationships between discharge, head, power and efficiency over the pump's operating range.
IRJET- Experimental Analysis of Circular Perforated Fin Arrays by Forced Conv...IRJET Journal
This document summarizes an experimental analysis of heat transfer from circular perforated fin arrays under forced convection using a wind tunnel. Trapezoidal microfin arrays with circular perforations were selected and designed using Taguchi Method. Experiments were conducted in a wind tunnel on three test specimens - a solid rectangular fin array and two trapezoidal perforated fin arrays with different perforation pitches. The perforated fin arrays showed higher overall efficiency and effectiveness compared to the solid fin array. Maximum overall efficiency was obtained for the array with 5mm perforation pitch at an air velocity of 2m/s and heat input of 150W. Optimum effectiveness was obtained for the array with 7mm pitch at 2m/s and 120W input
International Journal of Engineering Research and Applications (IJERA) is an open access online peer reviewed international journal that publishes research and review articles in the fields of Computer Science, Neural Networks, Electrical Engineering, Software Engineering, Information Technology, Mechanical Engineering, Chemical Engineering, Plastic Engineering, Food Technology, Textile Engineering, Nano Technology & science, Power Electronics, Electronics & Communication Engineering, Computational mathematics, Image processing, Civil Engineering, Structural Engineering, Environmental Engineering, VLSI Testing & Low Power VLSI Design etc.
IRJET- Heat Transfer Studies of Corrugated Plate Heat Exchanger using OilIRJET Journal
This document presents a study on heat transfer in corrugated plate heat exchangers using oil as the heat transfer fluid. Three corrugated plate heat exchangers with angles of 30°, 40°, and 50° were experimentally tested and compared to a flat plate heat exchanger. The heat transfer coefficient and Nusselt number increased with increasing Reynolds number and corrugation angle. The 50° corrugation angle achieved the highest heat transfer rates, representing a 40% increase over the 30° angle. Using oil as the fluid resulted in slightly higher heat transfer compared to previous studies using water. The experimental results agreed with previous CFD analyses showing improved performance of corrugated plates over flat plates.
Experimental Investigation of Heat Transfer Enhancement by Using Clockwise an...ijiert bestjournal
Present Experimental work shows result obtain from experimentation of heat transfer enhancement in
circular horizontal tube by using clockwise and counterclockwise corrugated twisted tape inserts with
working fluid is air. Experiments conducted on plain circular tube with or without c-cc corrugated
twisted tube. During experiment constant heat flux and different mass flow rate condition. The c-cc
corrugated twisted tape are of same pitch and twist ratio but three different angle of rotation in
clockwise and counter clockwise direction as 30˚, 60˚, 90˚ respectively. The Reynolds no. varied from
4000 to 10000. Heat transfer coefficient and pressure drop are calculated and results are compared with
the plain tube without inserts. Finally heat transfer enhances with clockwise and counterclockwise
corrugated twisted tape inserts as compared to plain tube varied from 8 % to 44 % for various inserts.
Plain twisted tape results are also compared with the same results.
IRJET- Study of Heat Transfer Characteristics for the Flow of Air over a Heat...IRJET Journal
This document summarizes a study that used computational fluid dynamics (CFD) to analyze heat transfer from circular and diamond-shaped tubes. The study found that the diamond shape performed better than the circular shape. Specifically:
1) Temperature distribution results showed higher surface temperatures on the circular tube compared to the diamond tube. Higher Reynolds numbers also reduced surface temperatures for both shapes.
2) Nusselt number, a measure of heat transfer, increased with Reynolds number for both shapes. However, the diamond shape had higher Nusselt numbers, indicating better heat transfer performance compared to the circular shape.
3) Tube shape was found to significantly impact heat transfer characteristics, with the diamond shape offering better heat
This document provides details of a project to analyze thermo-mechanical stresses in a tube sheet heat exchanger using finite element analysis software ANSYS. It includes details of the guiding staff, the research area of solar dryers, identified problems regarding stresses leading to failures, and a literature review summarizing previous related research on stress analysis of tube sheets. The work plan for phase 1 is to learn finite element methods and ANSYS to determine stresses, study factors influencing stresses, and conduct further literature review to aid the stress analysis, with ANSYS training planned for December 2013.
This document summarizes a study on improving heat transfer in tubes by using different types of twisted tape inserts. Experiments were conducted to assess heat transfer and pressure drop in a tube fitted with alternating clockwise and counter-clockwise twisted tapes (C-CC tapes) as well as serrated twisted tapes (STT). For C-CC tapes, heat transfer increased with higher twist ratios and lower twist angles. For STT, heat transfer increased with higher serration depth ratios but decreased with higher serration width ratios. Thermal performance factors above unity indicated STT provided advantages over plain tubes or twisted tapes. Correlations for Nusselt number and friction factor were determined for both C-CC and STT.
IRJET-Numerical Investigation of Heat Performance Enhancement for a Double-Pi...IRJET Journal
This document presents a numerical investigation of heat transfer enhancement in a double-pipe heat exchanger with continuous helical baffles in the annulus and either water or alumina nanofluid as the working fluid. The study varies baffle spacing, mass flow rate, and nanofluid concentration to analyze their effects on heat transfer rate, pressure drop, and thermal performance. Results show that adding helical baffles increases the fluid flow path and turbulence, enhancing heat transfer. Replacing water with nanofluid further improves heat transfer while also increasing pressure drop. Graphs comparing the different configurations are presented and agree with previous research findings. The goal is to optimize baffle design and nanofluid parameters to maximize heat transfer rate and performance for practical
This document summarizes a study on the hydrodynamic characteristics of a swirling fluidized bed with a four duct plenum chamber. Large Geldart D-type particles (coffee beans and black pepper) were used. Numerical simulations were conducted using CFD software to validate experimental results. Key parameters like distributor pressure drop, minimum fluidization velocity, bed pressure drop, and radial/tangential velocities were analyzed experimentally and through simulations. The results show that a swirling fluidized bed can effectively fluidize large particles that are difficult to fluidize in a conventional bed. Pressure drops and velocities varied as expected with changes in air flow rates.
Analysis of Heat Generation in Double Pipe Heat Exchanger: An Experimental Ev...IRJET Journal
This document summarizes research on analyzing heat generation in a double pipe heat exchanger with an elliptical fin surface contact. An experiment was conducted to compare the heat transfer rate of an elliptical fin to other fin types (tube-tube, rectangular, annular, spiral rod). The results showed the elliptical fin had a higher heat transfer rate. The document reviews several other studies analyzing different fin geometries, heat transfer optimization techniques, and computational fluid dynamics simulations of heat exchangers. It provides background on analyzing heat exchangers using methods like logarithmic mean temperature difference and effectiveness-NTU and discusses prior work optimizing dimensions, materials, and flow conditions to improve heat transfer performance.
Heat transfer enhancement through different circular diametrical dimple surfa...eSAT Journals
Abstract The prime objective of present work is to study experimentally the heat transfer enhancement through different circular diametrical dimple surfaces in longitudinal and lateral directions. In this paper horizontal rectangular plates of Stainless Steel and Galvanised Iron with different circular diametrical dimples (like 11mm , 14mm ) for in-line arrangements were studied in forced convection with varying laminar external flow condition. The various parameters considered for study are Reynolds Number, Nusselt number, Prandtl Number, Co-efficient of Friction, Heat transfer coefficient and heat transfer rate for a constant Prandtl number (0.698) It has been found that the heat transfer coefficient and heat transfer rate increases for various dimple surfaces as compared to plane surface. It has been also found that the heat transfer coefficient and heat transfer rate increases along longitudinal direction as compared to lateral direction. And it is seen that heat transfer rate is maximum for larger diameter (14mm) of dimple. For circular dimples, heat transfer enhancements (relative to a flat plate) were observed for Reynolds number range from 350 to 550. Index Terms: Dimple plates, Forced Convection, Heat transfer Enhancement
Developing Flow Pressure Drop and Friction Factor of Water in Copper Microcha...Mirmanto
Experiments were conducted to measure the pressure drop and friction factor of water flowing through three copper microchannels of varying widths (0.5 mm, 1.0 mm, and 1.71 mm) but constant depth (0.39 mm) and length (62 mm). The water temperature was varied from 30-90°C for adiabatic tests and was 30°C with a heat flux of 147 kW/m2 for non-adiabatic tests of the 0.635 mm channel. The friction factors obtained were generally in agreement with conventional developing flow theory and were not significantly affected by temperature. However, pressure drop decreased with increasing inlet temperature.
Defeloping flow and pressure drop in microchannelsMirmanto
Experiments were conducted to measure the pressure drop and friction factor of water flowing through three copper microchannels of different widths (0.5 mm, 1.0 mm, and 1.71 mm) but the same depth (0.39 mm) and length (62 mm). The experiments covered a Reynolds number range of 234 to 3,430. Pressure drop decreased with increasing inlet temperature, while friction factors showed little difference across test sections. Friction factors agreed reasonably well with conventional developing flow theory. Heat flux had a negligible effect on friction factor.
IRJET-Enhancement of Heat Transfer through Pipe with the Help of Various Type...IRJET Journal
This document reviews research on enhancing heat transfer through pipes using various types of turbulators. It begins with an abstract discussing using active or passive techniques to increase heat transfer rates in heat exchangers. The paper then discusses using modified baffled twisted tape inserts to change heat transfer rates. It provides equations for heat transfer and reviews several studies that experimentally analyzed heat transfer and pressure drop when using twisted tapes, baffled twisted tapes, and other turbulator inserts in pipes. The studies found that inserts can increase heat transfer by inducing swirl and disrupting boundary layers, but also increase pressure drop. The level of increased heat transfer and pressure drop depended on turbulator design and fluid properties like Reynolds number.
IRJET- Thermal Analysis on Solar Air Heater DuctIRJET Journal
This document summarizes a numerical study on the effects of transverse rectangular ribs on heat transfer properties in a solar air heater duct. Computational fluid dynamics (CFD) simulations were performed to analyze thin and square ribs arranged in single, staggered, and inline patterns. The simulations found that introducing ribs significantly increased heat transfer compared to a smooth duct. Thin ribs performed better than square ribs. Inline thin ribs produced a 1.83 times higher heat transfer coefficient than the smooth duct. Reynolds number increases led to higher Nusselt numbers for all cases. Staggered ribs had lower heat transfer than inline ribs. The study provides conclusions on rib effects and turbulence model selection for predicting solar air heater performance.
In compact heat exchangers, thermal resistance is generally dominant on the air-side and may
account for 80% or more of the total thermal resistance. The air-side heat transfer surface area is 8 to
10 times larger than the water-side. Any improvement in the heat transfer on air-side therefore
improves the overall performance of the heat exchanger. Due to the high thermal resistance on the
air-side, the optimization of such fins is essential to increase the performance of the heat exchangers
which results in thermal systems enhancement. This helps to reduce CO2 emissions through a
reduction of mass and fuel consumption.
Optimization of louvered fin geometry in such heat exchangers is essential to increase the
heat transfer performance and reduce weight, packaging, and cost requirements. In this study deals
with Computational Fluid Dynamics (CFD) studies of the interactions between the air flow and
louvered fins which equipped the automotive heat exchangers is carried out. 3D numerical
simulation results is obtained by using the ANSYS Fluent 14.0 code and compared with
experimental data. Finally the effect of louver angle and louver pitch geometrical parameters, on
overall thermal hydraulic performances of louvered fins is studied.
This document discusses a numerical investigation of the geometry of louvered fins in automotive radiator compact heat exchangers. Computational fluid dynamics simulations were performed using ANSYS Fluent to analyze the interactions between air flow and louvered fins. The effects of louver angle and pitch on thermal hydraulic performance were studied. The results were compared to experimental data to validate the simulations. Optimization of louvered fin geometry can increase heat transfer performance while reducing weight and cost requirements.
Analysis of cross flow induced vibration in an inline and staggered configura...eSAT Journals
Abstract
In many engineering applications like heat exchanger, radiator, evaporator, nuclear power plant and thermal power plant, arrangement of tubes is very crucial. Fluid elastic instability forms the basis for deciding the type of arrangement and tube spacing but the phenomenon of vortex induced vibration is random in nature. Tube spacing also plays a critical role in different types of arrangement. Different type of application requires different tube spacing and the range of tube spacing vary from 1 to 6. Vortex Induced Vibration in cross flow around the inline and staggered arrangement of the tube arrays is experimentally studied for varying P/d (tube spacing) ratio. It is observed that with the increase in the velocity, the amplitude displacement increases. As the amplitude displacement of the tube reduces, the pitch over diameter ratio is increased from 2 to 4. It is also observed that between inline and staggered arrangement, the amplitude displacement of staggered arrangement is more compared to inline arrangement for same tube spacing.
Keywords: Vortex Induced Vibration, Inline Arrangement, Staggered Arrangement, Regression Analysis
Numerical Investigation of Heat Transfer from Two Different Cylinders in Tand...IJERA Editor
A two dimensional technique has been studied numerically to predict the heat transfer from two different cylinders
in tandem arrangement (one is circular and the other is elliptical) using finite element technique with RNG k-ε turbulent
model, taking into consideration the effect of gap ratio (L/Deq ) and Reynolds number , where the distance between
the centers of cylinders is L (L=30 mm and 37 mm), the equivalent diameter of cylinder is Deq=22.5mm and
the range of Reynolds number is 2x103
< Reeq < 21x103 .The commercial CFD software FLUENT was used to get
the thermofluid characteristics (temperature, velocity, kinetic energy and pressure contours ,coefficient of friction ,
heat transfer coefficient , Stanton number …… etc) of the flow around cylinders. The dependency of the heat transfer
coefficient, Stanton number (Sta), pressure drop, and friction factor for circular and elliptical cylinders on the gap
ratio is clear from the results. Results show that, for circular cross section, the heat transfer coefficient is increased as
velocity, and gap ratio increase. On the other hand Sta decreased as velocity increase. The pressure drop and hence
the friction factor increase for circular cylinder as gap ratio increases. For elliptical tube the heat transfer and Sta are
relatively equal to that for circular one at the same gap ratio, but the overall power consumption and friction factor
for elliptical tube is lower than that of circular one. As the elliptical cylinder fixed on the second position the heat
transfer and Sta
increase, on the other hand the pressure drop and hence the friction factor decreases. For all studied
arrangements the highest heat transfer is observed for the arrangement of circular-first and elliptical-second cylinder
and the minimum pressure drop and hence the friction factor are for the elliptical one
Improved Thermal Performance of Solar Air Heater Using V-Rib with Symmetrical...IJERA Editor
This document summarizes an experimental investigation of the thermal performance of a solar air heater duct with an absorber plate containing V-shaped ribs with symmetrical gaps and staggered ribs. Experiments were conducted for a Reynolds number range of 3000-14000 with various rib parameters. Results showed that the heat transfer coefficient and Nusselt number were higher for the roughened plate compared to a smooth plate, indicating enhanced heat transfer. The efficiency was also higher for the roughened plate configuration compared to the smooth plate due to the increased heat transfer. The V-rib with symmetrical gap and staggered rib geometry increased secondary flows and accelerated the air flow, improving thermal performance compared to a smooth plate.
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10 karakteristik sifat mekanik komposit serat bambu resin polyester tak jenuh...Mirmanto
Studi ini menguji pengaruh fraksi volume partikel sekam padi (0%, 10%, 20%, 30%) terhadap sifat mekanik komposit serat bambu-resin polyester tak jenuh. Hasil uji tarik menunjukkan kekuatan tarik konstan sampai 20% fraksi sekam kemudian menurun. Uji bending menunjukkan kekuatan naik sampai 20% fraksi sekam lalu menurun, sedangkan modulus bending tidak dipengaruhi. Kekuatan impak juga tidak dipengaruhi fra
9 potensi pasir lokal tanjung bintang pada aluminium sand casting terhadap po...Mirmanto
Green sand is one of the most important components in the process of metal casting. The sand in Indonesia region is varied level of subtlety, size of sand, and shape of sand. Green sand used in the process of metal casting is possible can affect the quality of casting product. This aims to determine the potential of Tanjung Bintang sand as green sand and the quality of the product in terms of porosity defects. The research was conducted by varying sand river from Tanjung Bintang and sand from Maringgai. Composition made varying is 100%,75%, 50%, and 25% Tanjung Bintang sand compared Maringgai sand with bentonit and water is 10% and 5% constantly .The Examine of the green sand by SNI 15-0312-1989 among other water content, clay content, Grain Finnest Number (GFN), Shape of grain. The result said aluminium casting product with 50% Tanjung Bintang sand has the lowest value of porosity, 5.08% and the higher value with 75% composition of Tanjung Bintang sand, 6.98%.
8 studi kelayakan penggunaan mesin diesel dengan metode break even point (bep...Mirmanto
Studi ini bertujuan untuk menganalisis kelayakan penggunaan mesin diesel PLTD Ampenan dengan metode break even point dan analisis sensitivitas. Ada beberapa alternatif harga jual listrik ke masyarakat yang dianalisis, yaitu Rp800, Rp900, dan Rp1000 per kWh beserta besaran subsidi yang berbeda. Analisis sensitivitas dilakukan dengan mengubah nilai investasi awal dan pendapatan. Hasilnya menunjukkan PLTD masih layak beroperasi walaupun
7 analisis perilaku aliran terhadap kinerja roda air arus bawah untuk pembang...Mirmanto
Dokumen tersebut merupakan analisis perilaku aliran air terhadap kinerja roda air untuk pembangkit listrik skala pikohidro. Penelitian ini menganalisis kecepatan aliran, putaran, torsi, dan daya roda air serta kecepatan relatif air terhadap sudu roda air dengan variasi kecepatan aliran. Hasil pengukuran awal menunjukkan kecepatan rata-rata air 2,50 m/s, putaran poros 79,78 rpm, torsi r
6 optimasi parameter permesinan terhadap waktu proses pada pemrograman cnc mi...Mirmanto
Dokumen ini membahas optimasi parameter permesinan terhadap waktu proses pada pemrograman CNC milling dengan berbasis CAD/CAM. Parameter permesinan yang dioptimalkan meliputi kecepatan potong, kecepatan pemakanan, dan kedalaman pemotongan. Penelitian ini bertujuan untuk mengetahui pengaruh ketiga parameter tersebut terhadap waktu proses pada CNC milling."
5 pengaruh absorsi gas co2 dan h2 s dalam biogas menggunakan pasta batu apung...Mirmanto
Dokumen ini membahas pengaruh pemurnian biogas menggunakan pasta batu apung terhadap peningkatan kinerja mesin bakar. Biogas yang dihasilkan dari fermentasi kotoran kuda mengandung kontaminan seperti CO2 dan H2S yang perlu dihilangkan. Pemurnian dilakukan dengan mengalirkan biogas melalui pasta batu apung dengan variasi laju aliran. Hasil pengujian menunjukkan kinerja terbaik pada putaran 4500 rpm dan laju aliran 2 L
4 pengaruh ketinggian lubang udara pada tungku pembakaran biomassa terhadap u...Mirmanto
Alternative energies, e.g. biomassa, can be utilized using combustion processes in a stove. Nevertheless, traditional stoves that are available in the market or have been used by the community for years are not effective and efficient. One thing that may affect their efficiency and effectiveness is a distance between the combustion chamber and air hole. Therefore, this research investigates experimentally the effect of the distance.The tested stoves had identical combustion room and air hole diameters, but the distance between the combustion chamber and air hole was varied 10 cm, 20 cm, 30 cm, 40 cm. The combustion chamber diameter was 13 cm and the top diameter of the stove was 19 cm. The fuel employed was coconut shell with various size of 2-4 cm and 5-10 cm. One traditional stove was also tested as a comparison. The test were conducted by heating the water in a 18 cm diameter pan from the ambient temperature to the boiling temperature (1000C). Investigated parameters showing the stove performance were boiling time, FCR, heat input, heat output, heat losses and efficiency.The results show that the fastest boiling time (472 s) and the highest FCR (0,9407 Kg/h) were resulted in the stove with the air hole distance of 40 cm and coconut shell size of 5-10 cm. In this stove, the highest heat input, heat output, heat losses occurred too. On the other hand, the highest efficiency (15,62 %) was achieved in the stove with the air hole distance of 10 cm.
2 karakterstik serapan suara komposit polyesterMirmanto
The purpose of this study is to investigate of sound absorption of coconut filter fiber composites. The research material made with coconut filter fiber as reinforcement and matrix resin unsaturated polyester (UPRs) type Yukalac BQTN 157 with 1% hardener types MEKPO (Methyl Ethyl Ketone Peroxide) and fiber treatment by 0,5% KMnO4. Production methods is poltrusion and the variations of fiber volume fraction are 20, 25 and 30% and fiber length are 5, 10 and 15 mm. Testing of sound absorption frequency are 250, 500, 1000, 2000 and 4000 Hz. The results of research show that the highest value of sound absorption coefficient is on the composites with composition of 10 mm fiber length and 30% fiber volume fraction, that is 0.550828. The values are included in the class “Sound Absorption Coefficient Class D (Extremely absorbing)” with the range 0.40 – 0.60 based on ISO standard 11654:1997.
1 pengaruh debit terhadap unjuk kerja alat penukar kalor dan penurunan suhu r...Mirmanto
Due to population growth, industry advance and rapid development, fresh and comfortable air may be difficult to get. Conditioning the air to get comfort environment may be a basic demand for people, but the prices of the device and its operation for this purpose are expensive. This research tries to solve this problem but it is just only to know the capability of the heat exchanger to transfer/ absorb heat and is not to cool the room to be below the ambient temperature. The working fluid used was clean water and the heat exchangers employed were parallel and serpentine which were made of copper pipes with a diameter of 1/4 inch and 1/2 inch (for the header). The volumetric flow rates used were 300 ml/minutes, 400 ml/minutes and 500 ml/minutes. While the heat that should be absorbed by the water from the room is 50 W, 100 W and 150 W. The results show that the effect of volumetric flow rate on heat exchanger performance and room temperature is insignificant. From the pressure drop results, the parallel pipe heat exchanger has lower pressure drops while the serpentine has higher pressure drops.
3 rancangan ruang pengering berbasis ergonomi menurunkan keluhan muskuloskele...Mirmanto
With traditional fish drying process, most possible can cause an unhealthy working posture , such as a squatting action. As a consequence , worker will suffer a musculoskeletal disorders because of not ergonomic tools and bad working posture. Without ergonomics working procedures was found that the average of musculoskeletal complaints after working is 52.25 ± 1.03. To solve this ccomplaints, a drying chamber based ergonomics design was built in order to reduce musculoskeletal disorders. Dimensions of the drying chamber were based on anthropometric data of fish craftsmen and the material of drying chamber was by the participatory method. Test was performed on 20 samples and the result showed that the mean rate of musculoskeletal complaints after working is 38.30 ± 1.30. The ergonomic based design for drying camber application can reduce the musculoskeletal complaints up to 26.7%.
Prediction and measurement of pressure drop in microchannelsMirmanto
The document discusses the benefits of exercise for mental health. Regular physical activity can help reduce anxiety and depression and improve mood and cognitive functioning. Exercise boosts blood flow and levels of neurotransmitters and endorphins which elevate and stabilize mood.
Heat transfer coefficient in microchannelsMirmanto
This article compares two methods for calculating local flow boiling heat transfer coefficients in microchannels: using a linear pressure gradient assumption and direct pressure gradient measurement. An experiment was conducted for boiling water in three single microchannels of varying widths and depths. The local heat transfer coefficients determined by the two methods were found to be significantly different at high heat fluxes. The linear pressure distribution assumption may only be used with caution when the heat flux is below a certain threshold value that depends on the channel size.
Effect of boiling in the upatream loop on instability of flow boiling in a mi...Mirmanto
The document discusses an experiment that measured pressure fluctuations and flow reversals during flow boiling in a single microchannel. Four pressure sensors were inserted into the copper channel to measure pressure fluctuations. Tests were conducted with and without boiling occurring in the upstream loop before the test section. Results showed that pressure fluctuations and flow reversals were caused by bubble activity inside the channel. Boiling in the upstream loop was found to cause unstable flow. Flow reversal could occur when bubbles generated a temporary pressure higher than the inlet pressure. The upstream boiling affected the magnitude and duration of pressure fluctuations and flow reversals.
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Harness the power of AI-backed reports, benchmarking and data analysis to predict trends and detect anomalies in your marketing efforts.
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Watch the video recording at https://youtu.be/5vjwGfPN9lw
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https://ml.dssconf.pl/user.html#!/lecture/DSSML24-041a/rate
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Timothy Spann
https://www.youtube.com/@FLaNK-Stack
https://medium.com/@tspann
https://www.datainmotion.dev/
milvus, unstructured data, vector database, zilliz, cloud, vectors, python, deep learning, generative ai, genai, nifi, kafka, flink, streaming, iot, edge
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A quick poll on agility in changing pipelines from end to end indicated a huge span in capabilities. For the question "How long time does it take for all downstream pipelines to be adapted to an upstream change," the median response was 6 months, but some respondents could do it in less than a day. When quantitative data engineering differences between the best and worst are measured, the span is often 100x-1000x, sometimes even more.
A long time ago, we suffered at Spotify from fear of changing pipelines due to not knowing what the impact might be downstream. We made plans for a technical solution to test pipelines end-to-end to mitigate that fear, but the effort failed for cultural reasons. We eventually solved this challenge, but in a different context. In this presentation we will describe how we test full pipelines effectively by manipulating workflow orchestration, which enables us to make changes in pipelines without fear of breaking downstream.
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STATATHON: Unleashing the Power of Statistics in a 48-Hour Knowledge Extravag...
Effect of tube diameter and surface roughness on fluid flow friction factor dinamika teknik mesin
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Volume 4. Nomor 2. Edisi Juli-Desember 2014
JURNAL KEILMUAIT DAI[ TERAPAN TEKNIK MESIN
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DAFTAR ISI
Effect of Tube Diameter and Surface Roughness on
Fluid Flow Friction Factor
Mirmanto, I GI[K Yudhyadi, Emmy Dyah S. 62 -70
Control Of The Two Dof Inverted Pendulum
7t -77Muhammad Fajar
Karakteristik Sifat Tarik Dan Mode Patahan Komposit Polyester Berpenguat Serat Tapis Kelapa
I Made Astika,I Gusti Komang Dwijana 78 -82
Analisa Unjuk Kerja N{otor Bakar Berbahan Bakar Biogas
Termurnikan Berbasis Absorber Fezot
Rudy Sutanto, Ida Bagus Alit, Nurchayati 83 - 87
Aplikasi Break Even PointPada Sistem Operasional Kapal Motor
Penyeberangan Roditha PT. Asdp Indonesia Ferry
(Persero) Cabang Lembar
Made Wijana, A.A.AIit Triadi, Firza Febriandi 88 - 95
Pengaruh Kadar Air Awal Kayu Jati Dan Suhu Curing Perekat
Pada Kekuatan Geser Sambungan Kayu Jati (Tectona Grandis)
Secara Perekatan
Sugiman, Abdul Hayyi Nu'man, Emmy Dyah Sulistyowati 96 - 102
Pengaruh Variasi Jumlah Blade Terhadap Aerodinamik Performan
Pada Rancangan Kincir Angin 300 Watt
I Made Adi Sayoga,I Kade Wiratama, Made Mara, Agus Dwi Catur 103 - 109
Pengaruh Jumlah Blade Dan Variasi Panjang Chord Terhadap
Performansi Turbin Angin Sumbu Horizontal (Tash)
I Kade Wiratama,I Made MararL. Edsona Furqan Prina. 110 - 116
Analisa Nilai Kalor Dan Laju Pembakaran Pada Briket Campuran
B ij i Nyamplung (Caloplryllm Inopltyllum) Dan Abu Sekam Padi
M. Afif Almu, Syahrul,Yesung Allo Padang lL1 -122
4. lr*e -**.llesrr. Volume 4 No. 2 Juli 201 4
s* lE&x
Mirmanto, Yudhyadi, Emmy: Effed Of Tube Dianeter
EFFECT OF TUBE DIAMETER AND SURFACE ROUGHNESS ON FLUID
FLOW FRICTION FACTOR
Mirmanto*, I GNK Yudhyadi, Emmy Dyah S.
Mechanical Engineering Department, Mataram University, Jl. Majapahit No. 62,
Mataram, NTB, 83125, lndonesia
*E-mail: mmlrmanto@gmall.com
Abstract
Experiments have been performed to investigate the effect of channel roughness and
:ameter on fluid friction. Three different diameters and roughness of tubes were used to
eramine the friction factor. The first tube made of stainless steel with an inner diameter of 1.14
-rn was investigated at Brunel University, whilst the others made of PVC with diameters of 17
-.r and 15.5 mm rough were tested at Mataram University. The stainless steelwas equipped
^fi a 200 mm calmihg section and smooth one. The 15.5 mm diameter tube was coated
-:emally with sand that had an average grain size of 0.5 mm so that the tube had a relative
:.Jghness of 0.032. The last tube with a diameter of 17 mm was smooth as explained in the
-e38 Fluid Friction Experimental Apparatus manual.
The results indicate that the llow in the stainless steel tube still obeys the theory and in
:e '7 mm tube shows a deviation in friction factor with the theory. However, this was due to no
= -:ng section installed in the test rig. Flow in the rough tube (15.5 mm diameter)
:eronitrates that the Reynolds number does not affect the friction factor in turbulent regimes
=-,: the experimental friction faclors were reasonably in a good agreement with the theory or
uoody diagram. Hence, the effect of decreasing in diameter of channels on friction fuctor is
-sgnificant.
(eyr,vords: ft iction faclor, 1
surface roughness, fl u id friction theory.
1. Background
Friction factors are important
parameters in a process that utilizes fluid
flow. This can cause high pressure drops
s,hich further cause high demands of
cumping energy. Processes that use small
:ubes/channels need carefully pressure drop
calculations because in smaller tubes, the
pressure drop becomes signi{icantly higher
than in bigger tubes. Even, in microchannels
the pressure drop is one of the major
problems that must be solved or eliminated
correctty and still being a concemed problem
in this field study. Researches on this field
are still challenging the microchannel
communities.
Still there are many contradictory
conclusions on the definition of
microchannels. Previous studies used flow
oehaviour as criteria to define microchannels,
e.g. Brauner and Moalem-Maron [1], Kew
and Comwell [2], and Peng and Wang [3].
Cn the other hand, some studies used a
dimension of channel3-to differ microchannel
tom macrochannel. Mehendale et al. [4]
dassified heat exchangers in general, in
terms of D6:
(a) Micro heat exchanger: D1, = 1 - 100
Fm.
(b) Meso heat exchanger: D1 = 100 pm - 1
mm.
(c) CompacUmacro heat exchange( Dh =
1 -6 mm.
(d) Conventional heat exchanger: Da > 6m.
Finally, based on engineering practice and
application areas, such as refrigeration
industry in small tonnage units, compact
evaporators, cryogenic industries, cooling
elements of microelectronics and micro
electro mechanical systems (MEMS)'
Kandlikar [5] subdivided channels into three
groups in terms of D6, as follows:
(a) Conventional channels: Dr, > 3 mm.
(b) Minichannels: D6 = 200 Pm - 3 mm.
(c) Microchannels: D6 = 10 - 200 Prn.
Research results published in the open
literatures are seem different each other.
Some previous studies stated that ftic'tion
factors in large diameter tubes difiered fom
those in small/micro tubes. Some indicated
higher friction factors, e.g. Urbanek et al' [6],
Pipautsky et al. [], Ptund et al. [8], Shen et
al. [9]. Other studies showed no distinclion
between experimental friction factors and
theory, e.g. Silverio and Moreira [11]' Akbari
5. Dinamika Teknik Mesin, Votume 4 No. Z Juti 2014
ISSN:2088488X Mirmanto, Yudhyadt Emny if* Cf Tube Diameter
.-
-
-
et al. [12], Mirmanto et at. [13]. However,
several studies presented friction factors that
are lower than the theory, e.g. Jiang et al.
[141
The reasons of being higher than the
theoy are u-sually due to enirance effect,
roughness effecl, dimension errors and flow
measurements. eu et al. [15] demonstrated
retativety high friction factors from
conventional theory when they measured
pressure drops for water flowing in
trapezoidal silicon microchannels with
hydrautic diameters ranging from ii pm to
169 pm. Their friction taitois *er" iUo-ui'ayo
to .l_879 hisher than theory. Xo*erei-inevjustified the deviation as bling iii"-r".uii or
the high retative roughness (i.S% rc-s.7,,/;).
Jiang et al. [16], who used L mfrocnann"l
IIh "
hydraulic diameter of 30O frr, "nOX,aqo]ilar et at. [17J, who emptoyeJ airr"Lr"
or 1.06 mm and 0.62 mm tubes elucidated
that because of the roughness their
-friction
|:^1:t wele.hjg!-er tnai tneory. Ho*"rur,
Kandtikar et al. [17] specified thaftne effect of
:rl1f roughness (retative roughness of
gj36yo) was significant onty to, tn-u
"rJfu"tdiameter test section (0.62 mm). Stren ei al.
tgl studied flow and treat
'trinsiei'tor
deionized water in rough-walled cooDer
microchannels assembled- in a ZO-.n"['n"r
.?I1v -I1"1:ctansutar
channets *"r" eOO J,yye and 800 pm deep. They apptied rhiee
different inlet temperatures; 3'0"i,' SO;C'
"na70oC and their iteynotos num-ueiJ ,"ilaftom 162 to 1257. They found tiiin"
"JiL"tgl.lurface roughness (ielative ,orghn"r-" i _
6%) on taminar flow was significait inO-tn"t
higher inlet temperatures- O"crers"O jnu
pressure drop. However, they did not exptiin
the effect of fluid temperature on the triitlon
fuctor.
ln this study, experimental friction
raoors obtained from flow in different
diameters of the tube are compared each
:I"-r :19 also.compared with ineot.-i;;arms are to see if there are any differerices of
investigated friction factors id;J i;;;"1
lube at the same Reynotdi
-
ilil;.Furthermore, as the test seciions ,r"O in ini.research were not equipped with ;lm-i;sectaons, pressure drop'predictions
-in
iiiE
inlet and.ouflet plenums are analped and
presented in the forms of graph.
2. Experimental Facility and Test Sections
.. Experiments using the 1.14 mm
diameter tube were perfoimed using the test
rig at Brunet Universrty, United Kinglom, see
Fig. 1 in Mirmanto ei at. [13]. Tn-e test ng
used in this work consisted of a reservoir
made of SS316, micropump (modet
Micropump GA-723, PF'SB),' iorioris
!o-1v119ter (model Micromotion
- -
Erit"
CMF0.10), preheaters and tesi- sections.
Deionized water was used as the working
fiuid that was set at 30"C. ttre water
temperature was measured using K type
the.rmomuple with an uncertainty 6f tO.i X
calibrated against the platinum precis-ion
Thermometer with an accuracy of t0.025 K.
To obtain pressure drops,
'two pr"r.rru
transducers modet Honeyweil 26piCO *itn
an uncertainty of t0.2 kpa were installed in
the inlet and ouflet and were ."[oirt"o
against the deadweight tester for n,gn
pressures and the water manometer for low
?le:sl1es The experiments using 15.S mm
and 17 mm tubes were conducted at
Mataram g.nry9rgity, lndonesia. ffre test rrg
used was H40B Fluid Friction Apparatus-isee
fig. t) and the test section *"re irort".i"lilv
TecQuipment Ltd, [10J.
The lengths of the test sections were
200 mm for the 1S.5 mm tuOe- Oiimeie,
(tapping 30 and 31) and g12 mm roiin" izmm tube diameter (tapping 7 and g). The'ro.5 mm tube was roughen using sand orain
with.an average size of o.s mi, girinili"
relative roughness of 0.032, see fi[. i."fn"pressure drop was measured usin--q closed
manometer with a resolution of t mm:
Three test sections employed were (i)
a stainless steel tube with an'inner OiamltJr
of
. 1.14 mm (measured using , iSinmicroscope with an accuracy ofit prm, see
Fig. 3),.200 mm tong, equipped *itn ZOfi m,tong calming sections placed before and after
Ine test section, (ii) a pVC tube with an inner
dpmeter of 17 mm and a length of 912 mm
without a calming section, (iiD-a pVC iouof,
tube with an effective diamet,er of f S.S-m'#
and.a length of 200 mm without ,
"rlringsection.
63
6. )re.1ika Teknik Masin, Volume 4 No.2 Juli 2014
SSfl;2O88{88X
Mimanto, Yudhyadi, Emmy: Effed Of Tube Ciandq
--+
15
rm
]st
'ig
rir
€l
lis
te
s.
rg
€
K
n
h
n
t
1
V
t
I
)
I
Ccr$qadPdil!
lntemal
diamettl
=17 mm
tur
$dcnE$$ion *mcrfi6'lnnEc
Itfti0ulE&r
3rrdrqtrrf,2rrDitr
Figure 1. Experimental schematic diagram ['10]
Grains sf Send
lltriln 8.rd
lmfinEird
Figure 2. Rough PiPe test section
lil) rrnSatd
PIF*datiltlOfioi,
fi*ntilrnffiqt,
lxrrrdtdm,Are(hi*
l***frmriirusl#
ft'.*ffirrftSf*tlt
FlErcrlm*i1nriboGl'F
Sdtttlity
5rCfirr0trrff*l'sfth4.
Mrflfl,eBnmfut
7. Dinamika Teknik Mesin, Volume 4 No' 2 Juli 2014
,SSrr;2088-O88X
Miniqltc '-t1a Zar', Z@Of TubeDiameter
0.562
-0.a27
0.000
Figure 3. Stainless steel test section measured using a TSER microscope
I
!-{
-.1
-{
I
--{-raI
--tI
{
I<
J
t
I
-el--d I
g!-1
ril :I
-:5r1#-
*tt
=aB4
7@f
s =/
-za
.t*
t
I
I
I
li'
3. Data Reduction
ln this studY, the inlet and outlet
pressures were measured directly, therefore,
the pressure drop is obtained by subtracting
the outlet pressure from the inlet pressure
and called as total Pressure droP,
Lp, = p,- p. (1)
where p, is the measured inlet pressure and
po is the measured outlet pressure. The
channel pressure drop is then determined
using Eq. (3), however, for the test section
that ls equipped with a calming section, the
channel pressure drop is the same as the
total pressure droP, Eq. (2).
Lp* = Lp, (2)
LPo = LP, - LP, - LP" (3)
the inlet and outlet pressLlre drops are due to the
differences between iniet and outlet tube
diameters and channel diameter- Meanwhile, in
the outlet" there is a pressure recovery due to the
deceleration of the fluid. The inlet and outlet
pressure drops can be estimated as follows:
Lp, = Lp, + Lp" = p!t,v: l2 @
+ pv.:fr-Q,, r ,l')rz a,,
Lp. = Lp, - Lp, =
4,(r,,-v")'
tz ,r,L
- pv,:l - (,n"0 t .n,)' )r 2
where dp; is the static pressure drop, dp, is
the pressure drop due to ffuid acceleration
and Ap6 is the pressure recovery due to fluid
deceleration. A"; is the channel cross
sectional area, Aiis the inlet plenum cross
sectional area and Ao is the outlet plenum
cross sectional area. V"6 is the average
channel fluid velocity and %is the average
outlet plenum fluid velocity. & is the loss
coefficient that is equal to 'l for Eq. (5) and
dependent on the ratio of channel diameter
and inlet plenum diameter for Eq. (4)' see
Table 1, whilst p is the fluid density'
The experimental friclion factor, f, is
calculated using Eq. (6), whicft is given by
f =2Lp",D_* (6)
r - pLV:
where L is the channel length and D"n is the
channel diameler. The friction factor theory in
this study is the Darcy-Weisbach equation for
laminarwhich is given bY
.-e=
:,:FJe
-'tfr
=iE-tz
.r.E
Sr*
2|trt
3-€
f,
T=t.L
u
, -R.
65
(7)
8. lra-ra Teknik Mesin, Volume 4 No. 2 Juli 20i4
ssr 2068-088X
Mirmanto, Yudhyacli, Emmy: EtforI Of Tub Eiamder
z-c lar turbulent liow in the smooth pipe, the
-.=on factor equation used is' Alasius
3t-ation which is expressed as
,f = o.316Re{.25 (g)
*-rilst for turbulent flow in a rough channel,
::e friction factor formula sitecteO ii3olebrook-White equation or Moody diagram
,rhich is written as [18]:
where k is the channel absolute roughness
and Re is the Reynolds number.
The goodness of data is analyzed
using_enor analysis proposed by Coleman
and Steele [19]. ln this study the errors
consist of bias/systematic and random erors.
Systematic erors can be minimized with a
calibration whilst random erors cannot.
Following Coleman and Steete [19J, the
random uncertainty of a measured-variable,
X, is estimated as the standard deviation, S,,
of a sample of N measurements of the
variable, X, calculated as follows:
i--l -,^i
-J: =.1-- I(-Xt - X'
Y N-1,=l
lil
X=-ZX,
Ni=l I
where Xis the mean value of the sample
population. By contrast, the systematic
uncertainty of a measured variabie, X is
calculated as the root sum (RSS) given by
Eq. (12).
a, ' ,,, , ( a, ' .,,
^--luvtl-lUvdx, ) At
l)X, ) A1
rt _
(14)
(L.
fi=r.to_osoer,f
Dis.z
I *,
(.*E)
!.qqat!9n
(14) gives the absotute uncertainty,
Ur, in the result.
Table 1. k1 , loss coefficient for the sudden
contraclion
Drl",i D, k,
0
a2
0rl
0.6
08
r0
0.*ct
043
fi aA
0.:t8
014
0
(12)
Where (8,) is the Jh of the etementat
systematic uncertainties (8,)r, (Br)z
(81)r. . ... (Br)u, estimated from, for example
calibration data and instrument specifications
given by the manufacturers. The combined
erot uc is then given by Eq. (13) and the
propagated errer can be estimated using Eq.
(14).
Source [10]
4. Results and Discussions
The inlet and ouflet pressures have
been measured and the total pressure drop
obtained from the three test section is
presented in Fig. 4. The test section #1 is the
smooth test section with a diameter of 1.14
mm equipped with calming sections installed
before and after the test section, therefore,
the total pressure drop is the same as the
channel pressure drop and the associated
flow is fully developed i?ow. The test section
#2 is the smooth test section with a diameter
of 17 mm and without a calming section and
the test #3 is the rough test section with an
average diameter of ,t5.5 mm (the actual
diameter is 17 mm and the effective diameter
is 15.5 mm) and without a calming section.
From Fig. 4, it is clear that decreasing in
diameter increases the pressure drop
significantly. For example, the decrease in
diameter ftom 17 mm to 1S.5 mm, the
pressure drop deviates of about 400% of the
pressure drop obtained in the 17 mm tube
diameter at the same Reynolds number of
20000, whilst ftom 17 mm to 1.14 mm the
qlessure drop deviates of approximately
1665670/o of the pressure drop-lained in the
17 mm tube diameter at the same Reynolds
number of 3000. This is becoming a serious
problem in the use of small to micro
channels.
ln Fig. 4, the pressure drops were
measured in the test section with diameters
of 15.5 mm and 17 mm and without a calming
(10)
(1 1)
Eb.x
Bj +sjuc= (13)
66
9. ISSN: 20884t88X ' '
rv'
' ru't zu71 Mimanto, yudhyadi,
Emmy: Efied Of TubeDiametar
m
OA
9.r.". zris the mass flow rate. For the i7
ffi:FIl1rj'j# Y.ql
-ro
;il';'i, E;:
,t?l;';::r. 1'-1r:, it"ji"i-,; i';: I #,'*
Hl"*1m:1"j31"_^_isr"i.ir,,i'iiiJ!,liiiJ?mm tube diameter. rii_
-._., .,,voE ril .ne 1t
llte sr rrfaaa ,^, r_L- ^ , s was obviously due tothe. surface rougrrness-
'rqc e.,vreusty oue to
?nft chanaar .r;^_^^- or rough channel walland channetoiimetli.
e '0',}
!ln
co tr.
.f = 12.55Re{.e2
-f*ard".dld.r
-!r&
-L{I&trrO ll=U4r
r 0=l7r
r D=EJrril
Ifr.i@I3)
yction, unless for the 1.14 mm tube
!11fg. Therefore, to obtain t"""r,"ri"Tr
lf_T"".dr:n Eo. (3) to rsl-rr,orii"'ol
.9rqpy"d The cross'sectiodi,"h;;;Lr;
Lhr"ir:i.:hi!i:"1rn'j"ixl1fl ]jorameter is O.OOO22z ,., tt"i"mi": ;ffivetocities in the channet can-be-i,illrii#E}S:
bc
! ,.,
I
b
(15)
::fl,ol:TY: droP
.becaus. t l-'i,eianJ
[T,t1?i"3,::!i?I' Eq (4) ,;; (o;"; i; l0o rt.o rele 100000
,?l,rij,fl::1i311q""t-i, ffi il-",:ffi
".::
tr
Frgure 5. Experimental friction factorsl3;j:*:jjq1"i"i, *!,;, ii,. il: EI",H
;;l",*, "j:*,j-ii ;;: [: j,
:""Jffi
"TI:l*,.t1,,: *f : 1 .
y r
-'r,;il='"il;:iJ;"'T,:
-r, ;li5
',,
F
.,=il-qr
"i,f,/
Figure 4. Total on
ooia ineo irorn' ;;^IrT:fi ,.i:K l:l,fr?",
. As there are m
rn experiments 6rPnlf-onttdictory
results
gggli i;i
"in,J'"l.ijS,;,ilr:?,#i:?
r.rctton factors are o
flt$fiHffilt'3,ffifrHtr
ffi #*,*iffiifql}',"H,:!'ffi r?tr
1si, o +sti ,ii' ffi #T ,ffrTffiffi:fll":
,HT[?",},,T;";::lJ:"'"'J?;ffi ffi 'ft,l;
rts ln the Fio_ 5, the experimental frictionre factors are in Iq. Ia"" il-" ii,"i"fl"B'"f,n!::T:,,Hrr
#m tube diameter ol
i tn =;;i; Tff $i
Meodv,:lXr#i,T
o subtracted from I
il deviati;il;il;1",i,5'3;::ffi
i',,:f lljchannel pressur
roe,z". rJriil"'f, fflf *t1, :i#"lg,"lil
g*:::r:x"fl:ff:-".: *eir witr' dr'"ill p,t
r s. s *iii l,ii' ii' lffioLlJl";H,:[:,H,'*?experiments coutd- not b. p#;;;,i.j" ,otheir lengths. if thr
*'"n in ilmin; ti:T$?"Hi"iffi,.1"f"?could be read. Adr
obtiained in tt" rinlolally'
the friction factor
h,gili ;a;' t;,i
"lL'r,*T, ?f"", i,ffi:?^,trs not due ro ttre
!1ae aiai"iur',[,]i
,tnu
roughness. Meanwrril- -;;:,=.=:-
":: ..
?rypo".d ov
^a#r'#1",?0,
Slr rr?JHfH:clata, because the corelation was created fordeveloping florv cr
,:;lrii]t#r:;H"ks,ij#n?ii
ffi:lil$*Tr'x3l^ 1'- "'tt"n- ilffi on,
19
",,*iJ ;^"ji',",]'JT,f#,ff 1fl1,"[*agree with the theon
:::, .""rv.[";Iy; "' ";fj "?1[:,,..U:cxamples of excel anatvsic ;;; :--I] ']::T"i
are described f^ll.s't
and eror analysis
experimentar data .i?l?- ,
consider ir,"
ru6e oiamef,r,;;o":1:lled in the 17 mm
regression), 6" .;o;,6"IT-l -analysis
(ANQvA
".,i.,
p","a ffi
-iy;
i'ffi: f"i:'. r.il:il,f
"?:
rs no deviation betw
results ;il;"1f1- the exPerimental
nooitionarri,-
"r- sTry- ?"? Tab{e 2.
s"[",T: ill ffi;,;: Ti+,,*j,;$:(16)
67
10. I
l
n0
}* Tdotik Mesin, Volume 4 No. 2 Juli 2014
g*N4'EEX
Mirmanto, Yudhyadi, Emnry EMOf Tube Aanxf,er
ar*r. The first point with big enor bars
rffing the furthers point, still coverc the
bius [21] correlation, henc,e, the data are
n a good agreement with the theory. The
error bars for the experimental ftiction factor
sfu,Yn in Fig. 6 are given by:
The uncertainty of the pressure drop,
diameter, tube length and fluid velocity are
known from the experiments, hence, the
relative error of friction factors can be found
and shown in Fig. 6.
-Eir
r l)=l?r
lrt
tt
lHS
Figure 6. Enor analysis for data obtained for
the 17 mm tube diameter
0
I
Iur0
Ita
rfffl.ffi'.)" (16,
t0
Table 2. Excelanalysis using ANOVA regression
s{JMnL^tRT &IIPLTT
E.trdss{rx ,*6err.5
Mr{tiple R it64487317
Rsqrraa 0-930235785
.{djDsrdB.
Sqrrac $914869307
SnodardError fi.ffi0?9)979
Ob*rr*io6s 15
.{NOy.{
q
Regrcssion I
Rcridrnl 11
Ss lA ? swnLtue.F
1-49809E-95 14988-05 1?1.v195 6.8X)13E{9
I 12351E46 8i42E48
Tsr2l 14 l-61044E45
-
ldcr€ar fin{,2fig9)78 0-0m361599 7.4&$n 4fiif46 0.l)01918091 030348el65 0-$01918091 018348&165
0-1i27819 8 0-fi11ffi)31 13.165919 632E.ig 0-127772102 0.1T}851575 0.ATJ72592 9.777851575
5. Conclusion
Experiments to see the difference of
friction factors obtained for flow in several
different diameter tubes have been
performed. For the 1.14 tube diameter, the
experiments were conducted at the Brunel
Univareity, whilst for other test sections were
performed at the Mataram University. The
results show that, for both experiments
conducted in different locations, the
experimental friction factors are not
influenced by the size ofthe tubes but by the
condition of the entrance and surface
roughness, and they obey the theory very
well. However, as the size of the tubes
reduces, the pressure drop increases
drastieally.
Acknowledgement
The first author would like to
acknowledge the lndonesia Higher Educatiqn
for the funding, and the Brund Unlversity antl
Mataram University fur the facilities.
11. r uunyaoL Emmy: Effed Of Tube Diameter
Nomenclature
R
Re
&
uc
U,
v
X
X
A
B,
D
df
f
k
kt
L
M
m
N
Cross sectional area [m2]
Systematic uncertain;
Diameter
Degree of freedom
Friction factor
) fl P..r^"_l
r.,rent sysrematic uncerrai nty
Aosorute rouglmess [m]
Losses coefficient
Tube length [m]
Maximum number of element systematic
uncertainty
l4ass flow rate [kgls]
Number of measurements
,leasured pressure [pa]
Keglesslon
Re,rnolds nurnber
Standard deviation
Combined error
Propagated error ofr function
Channel average velocity [m/s]
Measured variable
Average of measured variable
Subscript
ch Channel
i Intet
o Outlet
, Total
Greek symbol
lp Pressure drop [pa]
p Fluid density tkg;rl
I
I
I
Refercnces
t1] Brauner, N.
.&..Moalem-Maron, D.,1992, ,,tdentification
"i ii,"'l_ri" ""r
smail diameter co.nduits *O"ii,rgtwo-phase flow panem tr"n.liloi.j,Internationat Commu nicaiiin; ;;riMass Transfer vor. rg, zg _-i- ' 'qc
I2l Kew, p.A. a_ comw+ r]] rgsz"Conetations for the pr.oiltion-ii
boiting heat transfer i, .irrrr j""#"tJ,
channets", Apptiei iiii,i."i,,
13, F!i!:w f,
'iiJ:;],,a??-t
i;"Forced convection-' ,ni', #;";characteristics in ,roo"r,"].,-#rlproc. of llt HTc, 1, l6d,i;1=,1390.
t41 llrtahendate, S.S., Jacobi, A.M. &Shah, R.K., 2000, ,,Ftuid
no* ii,r,"ritran-sfer at micro and messo s;;i;;thapprication to heat
"r"n"ng"i
dliii;:,
lpy1lra Mechanics C"riJr",'.,V[1.
53(7),175 _ 193.
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