This document provides an overview and tutorial on ISO 1940/1, an international standard for selecting balance quality requirements for rigid rotors. It discusses key terms, how to determine permissible residual unbalance (Uper) for a rotor based on its balance quality grade and specifications, and how to allocate Uper between correction planes depending on the rotor's configuration, such as whether it is symmetrical, narrow, or overhung. The document aims to simplify the practical application of the standard.
Project - Upgrade and Design an access platform that would be attached to an A-Frame. All Designs and Drawings were created by me. Created in Solidworks.
Bevel gears are used to transmit motion between two intersecting shafts at any angle. The design procedure involves selecting materials, tooth profiles, and module based on requirements and strength calculations. Bevel gears are then designed with the proper diameters, cone distance, and face width. Design is checked for surface and bending stresses. Bevel gears are commonly used in differentials and hand drills to change the direction of rotation. They allow transmission of power between non-parallel shafts but require precise mounting and bearings.
The gears are a type of mechanical element whose teeth are cut around a cylindrical or conical surface with the same space. It is used for the rotation and transmission of force from the drive shaft to the driven shaft when coupling a pair of elements. The gears can be classified into spiral, cycloid and trochoidal gears according to their shape. It can also be classified as parallel shaft gear, transverse shaft gear and non-parallel and non-transverse shaft gear depending on the position of the shaft.
lecture 4 (design procedure of journal bearing)ashish7185
This document provides information about the design procedure for sliding contact bearings. It defines key terms used in hydrodynamic journal bearings such as diametral clearance, radial clearance, eccentricity, minimum oil film thickness, and short/long bearings. It discusses bearing characteristic number and bearing modulus, and how they relate to the coefficient of friction. Equations are provided for critical pressure, heat generated in bearings, and heat dissipated by bearings. The design procedure involves selecting bearing dimensions, material properties, operating parameters, and verifying thermal equilibrium conditions.
This document provides an overview of machinery alignment. It defines alignment as arranging the centerlines of rotating shafts in a straight line when machines are at operating temperature. Misalignment occurs when shaft centerlines do not match up and can be radial or angular. The document discusses types of misalignment, methods of alignment including straight edge, rim and face, and laser, symptoms of misalignment, tools used, and importance of precision alignment. It provides guidance on pre-alignment checks like foundation, piping, shims, and indicates alignment tolerances are required for proper machinery function.
Power transmission involves moving energy from where it is generated to where it is applied. Power is defined as units of energy per unit time. Gears are used to transmit power between rotating or linear shafts by means of teeth that progressively engage. There are different types of gears that transmit motion between parallel shafts, intersecting shafts, and non-parallel shafts. Gear drives are commonly used for power transmission due to their ability to transmit high power and torque over a wide range of speed ratios in a compact package.
This document provides an overview of different types of gears including their key components and terminology. It discusses common gear types like spur gears, helical gears, bevel gears, and worm gears. For each type it provides examples of advantages and disadvantages as well as typical applications. The document also discusses gear materials and common modes of gear failure such as scoring, wear, pitting, plastic flow, and tooth fracture.
Project - Upgrade and Design an access platform that would be attached to an A-Frame. All Designs and Drawings were created by me. Created in Solidworks.
Bevel gears are used to transmit motion between two intersecting shafts at any angle. The design procedure involves selecting materials, tooth profiles, and module based on requirements and strength calculations. Bevel gears are then designed with the proper diameters, cone distance, and face width. Design is checked for surface and bending stresses. Bevel gears are commonly used in differentials and hand drills to change the direction of rotation. They allow transmission of power between non-parallel shafts but require precise mounting and bearings.
The gears are a type of mechanical element whose teeth are cut around a cylindrical or conical surface with the same space. It is used for the rotation and transmission of force from the drive shaft to the driven shaft when coupling a pair of elements. The gears can be classified into spiral, cycloid and trochoidal gears according to their shape. It can also be classified as parallel shaft gear, transverse shaft gear and non-parallel and non-transverse shaft gear depending on the position of the shaft.
lecture 4 (design procedure of journal bearing)ashish7185
This document provides information about the design procedure for sliding contact bearings. It defines key terms used in hydrodynamic journal bearings such as diametral clearance, radial clearance, eccentricity, minimum oil film thickness, and short/long bearings. It discusses bearing characteristic number and bearing modulus, and how they relate to the coefficient of friction. Equations are provided for critical pressure, heat generated in bearings, and heat dissipated by bearings. The design procedure involves selecting bearing dimensions, material properties, operating parameters, and verifying thermal equilibrium conditions.
This document provides an overview of machinery alignment. It defines alignment as arranging the centerlines of rotating shafts in a straight line when machines are at operating temperature. Misalignment occurs when shaft centerlines do not match up and can be radial or angular. The document discusses types of misalignment, methods of alignment including straight edge, rim and face, and laser, symptoms of misalignment, tools used, and importance of precision alignment. It provides guidance on pre-alignment checks like foundation, piping, shims, and indicates alignment tolerances are required for proper machinery function.
Power transmission involves moving energy from where it is generated to where it is applied. Power is defined as units of energy per unit time. Gears are used to transmit power between rotating or linear shafts by means of teeth that progressively engage. There are different types of gears that transmit motion between parallel shafts, intersecting shafts, and non-parallel shafts. Gear drives are commonly used for power transmission due to their ability to transmit high power and torque over a wide range of speed ratios in a compact package.
This document provides an overview of different types of gears including their key components and terminology. It discusses common gear types like spur gears, helical gears, bevel gears, and worm gears. For each type it provides examples of advantages and disadvantages as well as typical applications. The document also discusses gear materials and common modes of gear failure such as scoring, wear, pitting, plastic flow, and tooth fracture.
Pre-alignment is important to save time and money during shaft alignment. It involves observing the system for any issues like soft foot, thermal growth potential, or worn components. The alignment target or tolerance should be determined based on factors like coupling type and speed. Soft foot must be corrected by shimming feet to be level before alignment. Shaft alignment is done in four steps - correcting angular misalignment vertically, then parallel offset vertically, then angular misalignment horizontally, then parallel offset horizontally. Backlash and vibration need to be controlled during measurement.
The document discusses fatigue failure and fatigue analysis. It begins by explaining that fatigue failure starts with a crack, usually at a stress concentration, which then propagates until sudden fracture. It then provides examples of fatigue failures and discusses different fatigue analysis methods. The key points are:
- Fatigue failure results from repeated or fluctuating stresses that are lower than the material's ultimate strength.
- It can be analyzed using stress-life, strain-life, or fracture mechanics methods, with stress-life most common for high-cycle fatigue.
- The stress-life approach estimates fatigue strength (Sf) based on stress levels and uses modifying factors to account for real-world differences from test specimens.
The document discusses various case studies of gearbox diagnosis from different industries using different vibration analysis techniques. These include a misaligned gearbox diagnosed using time waveform analysis showing directional forces, a cracked tooth problem in a cement mill gear diagnosed using high crest factor readings indicating sharp peaks, and a flexible gearbox support structure causing shaft failures diagnosed using operational deflection shapes analysis. The case studies demonstrate the need to use multiple analysis tools to effectively diagnose different types of gearbox faults.
This document provides details on the manufacturing process for a hand vice. It includes lists of the basic parts of a hand vice including the base, jaws, pin, screw, and handle. It describes the operations used to make each part such as measuring, cutting, milling, drilling, and threading. The materials used include mild steel for the main components and tools such as hacksaws, milling cutters, and lathes. Manufacturing each part involves multiple steps to cut, shape, and finish the materials according to design specifications.
The document discusses helical gears. Some key points:
- Helical gears have teeth cut at an angle (helix angle) ranging usually between 15-30 degrees, compared to spur gears which have straight teeth parallel to the shaft axis.
- Helical gears can be parallel, crossed, or herringbone. Herringbone gears cancel thrust loads by using two sets of teeth with opposite hands.
- Helical gears carry more load than equivalent spur gears because the teeth act over a larger effective area due to the helix angle. However, efficiency is lower for helical gears due to increased sliding contact.
- Additional geometry considerations are required for helical gears, including normal and transverse pit
Tolerances of Form(Form Errors) for a Hydraulic valveSilvester S.M
Four types of Form errors must be within a restricted limit in hydraulic valve parts. The circularity, straightness and cylindricity are very critical to quality in spool and spool bore in valve body. The flatness is very important to the faces of valve body sections in a sectional DC valve.
Gears are used to transfer motion and torque between rotating shafts. They work by engaging teeth along the edge of one gear with another gear. This allows for speed and torque conversions between driving and driven components. There are several types of gears including spur gears, helical gears, bevel gears, and worm gears which can transmit power at 90 degree angles. Gear ratios are calculated based on the number of teeth and are used to increase torque or reduce speed between connected rotating parts like motors and pumps.
The worm gears are widely used for transmitting power at high velocity ratios between non-intersecting shafts that are generally, but not necessarily, at right angles.
It can give velocity ratios as high as 300 : 1 or more in a single step in a minimum of space, but it has a lower efficiency.
1. Leaf springs are used in automobile suspension and consist of flat plates or leaves assembled together. Stress and deflection equations can be derived by modeling the leaves as beams.
2. To make the spring more compact, the original plate can be cut into strips and stacked together. Stress and deflection are calculated by replacing the plate width with the total width of strips.
3. Semi-elliptical leaf springs are the most common type. They consist of a master leaf and graduated leaves held together with clips. The stress and deflection equations treat the master and graduated leaves as a beam and extra full length leaves as another beam.
MET 304 Mechanical joints riveted_jointshotman1991
Riveting was commonly used to join metal parts before welding but is now less common. Rivets are cylindrical shafts inserted through holes in materials to be joined and formed into heads on both ends. Riveted joints can fail due to bending, shearing of rivets, crushing of rivets or plates, or tearing of materials. The document provides equations to calculate load capacities of riveted joints based on factors like rivet material properties, number of rivets, and whether rivets are in single or double shear. Design of riveted joints involves selecting rivet size, number and layout to optimize strength and load distribution.
This document summarizes information about journal bearings. It defines a journal bearing as a block of cast iron with a hole for supporting a rotating shaft. It describes how lubricating oil is fed into the bearing and dragged by the shaft, creating hydrodynamic lift and resisting shaft motion. There are three types of journal bearings: dry, hydrodynamic, and hydrostatic. The document discusses the pressure distribution in a journal bearing due to the flow of viscous fluid in a converging channel, and defines the eccentricity ratio as the ratio of eccentricity to radial clearance. It concludes with discussing the study of bearing functions and types, and viewing the pressure distribution curve of a journal bearing.
Sliding Contact Bearing Theory Prof. Sagar DhotareSagar Dhotare
In present ppt covers following points:
Introduction of Sliding Contact Bearings
Classification
Applications
Different lubrications systems
Hydrodynamic bearing concept and working
Comparison between sliding and rolling contact bearings
PETROFF’S EQUATION For Hydrodynamic Journal Bearing
Dimensionless Parameters used in SCB
Design procedure for Hydrodynamic Journal Bearing
Coupling is used to transmit power from one shaft to another and make permanent or semi-permanent connections between shafts. There are two main types of couplings: rigid couplings which do not allow relative rotation between shafts and must be perfectly aligned, and flexible couplings which allow for some misalignment and protect from vibrations. Examples of flexible couplings include bush pin flange couplings using rubber or leather bushes over pins to absorb shocks, and universal couplings used to join intersecting shafts where the angle may vary.
Bearings are used to support rotating shafts and come in different types depending on whether they are designed to withstand axial thrusts, radial loads, or both. The main bearing types are ball bearings, which use spheres, and cylindrical roller bearings, which use cylinders, with each type having different capacities for loads and misalignment. Deep groove ball bearings can withstand both radial and axial loads, while angular contact ball bearings have increased axial load capacity and self-aligning ball bearings are very tolerant of misalignment.
The document discusses key terminology related to limits and fits including:
- Basic size, zero line, shaft, hole, deviations, tolerance, fits, and grades of tolerance.
- It defines types of fits like clearance fit, transition fit, interference fit.
- It explains hole basis and shaft basis systems for defining fits and provides an example designation.
- The document also discusses endurance limit, fatigue limit, and notch sensitivity factor which is a measure of how sensitive materials are to stress concentrations from notches or geometric irregularities.
This document discusses the design of journal bearings. It begins by introducing journal bearings and how they operate by allowing sliding along a circular surface to handle radial loads. It then describes the different types of journal bearings according to their angle of contact and lubricating layer thickness. The document outlines the materials commonly used for journal bearings and defines important terms in hydrodynamic journal bearings. It presents two main design methods - the M.D. Hersey method and the A.A. Raimondi and J. Boyd method - and provides overviews of the steps and considerations involved in each.
The document discusses fits and tolerances between mating parts. It defines tolerance as the total amount a dimension is permitted to vary between its maximum and minimum limits. There are four main types of fits between parts: clearance fits which always leave space between parts, interference fits which create actual interference or contact between parts, transition fits which can result in either clearance or interference, and line fits where contact or clearance can result during assembly. The document also discusses hole and shaft basis systems for specifying fits using tolerances and deviations from a basic size.
1. Gears transmit power between two shafts by meshing teeth without slip. The smaller gear is called the pinion and the larger is called the gear.
2. Gears can be classified based on tooth shape and disposition, including spur, helical, bevel, and worm gears. Spur gears have parallel teeth and transmit power between parallel shafts.
3. Involute tooth profiles satisfy the law of gearing by allowing the contact point between meshing teeth to move smoothly along a common tangent, transmitting motion efficiently. Involute profiles are commonly used in gear design.
presentation on CENTRE DISTANCE VARIATION,MINIMUM NUMBER OF TEETH,CONTACT RAT...STAVAN MACWAN
This document discusses various topics related to gears, including:
1. Center distance variation in gears can affect time-varying mesh stiffness and gear vibration. A new kinematic model is proposed to evaluate actual contact positions under varying center distances.
2. The minimum number of teeth for gears without undercutting is typically 17, though gears with fewer can be used if strength and contact ratio allow.
3. Contact ratio measures the average number of teeth in contact during engagement, and is typically 1.3-1.4 for machine tool components depending on the application's precision requirements.
4. Spur gears have straight, parallel teeth but produce high stresses and noise. Helical gears generate thrust but allow
This document provides an overview and tutorial on ISO 1940/1, an international standard for selecting balance quality requirements for rigid rotors. It outlines the standard's methodology for determining permissible residual unbalance (Uper) based on rotor type, weight, and maximum operating speed. The document simplifies the calculations for Uper and provides guidance on allocating Uper between correction planes for different rotor configurations, such as symmetrical, overhung, and narrow rotors. It also compares ISO 1940/1 balance quality grades to those specified by other standards like MIL-STD-167-1 and API.
This document discusses dynamics of rotating machinery with an emphasis on balancing. It covers balancing fundamentals, critical speeds and vibratory modes, damping, bearings and support structures. Case studies on balancing of a 115 MW generator rotor are presented, showing vibration measurements before and after balancing. Details of the generator rotor, balancing planes and trial weights used are provided. Common vibratory modes like rocking, conical and bending modes are explained. The document also discusses turbo machinery damping mechanisms and hydrodynamic bearings.
Pre-alignment is important to save time and money during shaft alignment. It involves observing the system for any issues like soft foot, thermal growth potential, or worn components. The alignment target or tolerance should be determined based on factors like coupling type and speed. Soft foot must be corrected by shimming feet to be level before alignment. Shaft alignment is done in four steps - correcting angular misalignment vertically, then parallel offset vertically, then angular misalignment horizontally, then parallel offset horizontally. Backlash and vibration need to be controlled during measurement.
The document discusses fatigue failure and fatigue analysis. It begins by explaining that fatigue failure starts with a crack, usually at a stress concentration, which then propagates until sudden fracture. It then provides examples of fatigue failures and discusses different fatigue analysis methods. The key points are:
- Fatigue failure results from repeated or fluctuating stresses that are lower than the material's ultimate strength.
- It can be analyzed using stress-life, strain-life, or fracture mechanics methods, with stress-life most common for high-cycle fatigue.
- The stress-life approach estimates fatigue strength (Sf) based on stress levels and uses modifying factors to account for real-world differences from test specimens.
The document discusses various case studies of gearbox diagnosis from different industries using different vibration analysis techniques. These include a misaligned gearbox diagnosed using time waveform analysis showing directional forces, a cracked tooth problem in a cement mill gear diagnosed using high crest factor readings indicating sharp peaks, and a flexible gearbox support structure causing shaft failures diagnosed using operational deflection shapes analysis. The case studies demonstrate the need to use multiple analysis tools to effectively diagnose different types of gearbox faults.
This document provides details on the manufacturing process for a hand vice. It includes lists of the basic parts of a hand vice including the base, jaws, pin, screw, and handle. It describes the operations used to make each part such as measuring, cutting, milling, drilling, and threading. The materials used include mild steel for the main components and tools such as hacksaws, milling cutters, and lathes. Manufacturing each part involves multiple steps to cut, shape, and finish the materials according to design specifications.
The document discusses helical gears. Some key points:
- Helical gears have teeth cut at an angle (helix angle) ranging usually between 15-30 degrees, compared to spur gears which have straight teeth parallel to the shaft axis.
- Helical gears can be parallel, crossed, or herringbone. Herringbone gears cancel thrust loads by using two sets of teeth with opposite hands.
- Helical gears carry more load than equivalent spur gears because the teeth act over a larger effective area due to the helix angle. However, efficiency is lower for helical gears due to increased sliding contact.
- Additional geometry considerations are required for helical gears, including normal and transverse pit
Tolerances of Form(Form Errors) for a Hydraulic valveSilvester S.M
Four types of Form errors must be within a restricted limit in hydraulic valve parts. The circularity, straightness and cylindricity are very critical to quality in spool and spool bore in valve body. The flatness is very important to the faces of valve body sections in a sectional DC valve.
Gears are used to transfer motion and torque between rotating shafts. They work by engaging teeth along the edge of one gear with another gear. This allows for speed and torque conversions between driving and driven components. There are several types of gears including spur gears, helical gears, bevel gears, and worm gears which can transmit power at 90 degree angles. Gear ratios are calculated based on the number of teeth and are used to increase torque or reduce speed between connected rotating parts like motors and pumps.
The worm gears are widely used for transmitting power at high velocity ratios between non-intersecting shafts that are generally, but not necessarily, at right angles.
It can give velocity ratios as high as 300 : 1 or more in a single step in a minimum of space, but it has a lower efficiency.
1. Leaf springs are used in automobile suspension and consist of flat plates or leaves assembled together. Stress and deflection equations can be derived by modeling the leaves as beams.
2. To make the spring more compact, the original plate can be cut into strips and stacked together. Stress and deflection are calculated by replacing the plate width with the total width of strips.
3. Semi-elliptical leaf springs are the most common type. They consist of a master leaf and graduated leaves held together with clips. The stress and deflection equations treat the master and graduated leaves as a beam and extra full length leaves as another beam.
MET 304 Mechanical joints riveted_jointshotman1991
Riveting was commonly used to join metal parts before welding but is now less common. Rivets are cylindrical shafts inserted through holes in materials to be joined and formed into heads on both ends. Riveted joints can fail due to bending, shearing of rivets, crushing of rivets or plates, or tearing of materials. The document provides equations to calculate load capacities of riveted joints based on factors like rivet material properties, number of rivets, and whether rivets are in single or double shear. Design of riveted joints involves selecting rivet size, number and layout to optimize strength and load distribution.
This document summarizes information about journal bearings. It defines a journal bearing as a block of cast iron with a hole for supporting a rotating shaft. It describes how lubricating oil is fed into the bearing and dragged by the shaft, creating hydrodynamic lift and resisting shaft motion. There are three types of journal bearings: dry, hydrodynamic, and hydrostatic. The document discusses the pressure distribution in a journal bearing due to the flow of viscous fluid in a converging channel, and defines the eccentricity ratio as the ratio of eccentricity to radial clearance. It concludes with discussing the study of bearing functions and types, and viewing the pressure distribution curve of a journal bearing.
Sliding Contact Bearing Theory Prof. Sagar DhotareSagar Dhotare
In present ppt covers following points:
Introduction of Sliding Contact Bearings
Classification
Applications
Different lubrications systems
Hydrodynamic bearing concept and working
Comparison between sliding and rolling contact bearings
PETROFF’S EQUATION For Hydrodynamic Journal Bearing
Dimensionless Parameters used in SCB
Design procedure for Hydrodynamic Journal Bearing
Coupling is used to transmit power from one shaft to another and make permanent or semi-permanent connections between shafts. There are two main types of couplings: rigid couplings which do not allow relative rotation between shafts and must be perfectly aligned, and flexible couplings which allow for some misalignment and protect from vibrations. Examples of flexible couplings include bush pin flange couplings using rubber or leather bushes over pins to absorb shocks, and universal couplings used to join intersecting shafts where the angle may vary.
Bearings are used to support rotating shafts and come in different types depending on whether they are designed to withstand axial thrusts, radial loads, or both. The main bearing types are ball bearings, which use spheres, and cylindrical roller bearings, which use cylinders, with each type having different capacities for loads and misalignment. Deep groove ball bearings can withstand both radial and axial loads, while angular contact ball bearings have increased axial load capacity and self-aligning ball bearings are very tolerant of misalignment.
The document discusses key terminology related to limits and fits including:
- Basic size, zero line, shaft, hole, deviations, tolerance, fits, and grades of tolerance.
- It defines types of fits like clearance fit, transition fit, interference fit.
- It explains hole basis and shaft basis systems for defining fits and provides an example designation.
- The document also discusses endurance limit, fatigue limit, and notch sensitivity factor which is a measure of how sensitive materials are to stress concentrations from notches or geometric irregularities.
This document discusses the design of journal bearings. It begins by introducing journal bearings and how they operate by allowing sliding along a circular surface to handle radial loads. It then describes the different types of journal bearings according to their angle of contact and lubricating layer thickness. The document outlines the materials commonly used for journal bearings and defines important terms in hydrodynamic journal bearings. It presents two main design methods - the M.D. Hersey method and the A.A. Raimondi and J. Boyd method - and provides overviews of the steps and considerations involved in each.
The document discusses fits and tolerances between mating parts. It defines tolerance as the total amount a dimension is permitted to vary between its maximum and minimum limits. There are four main types of fits between parts: clearance fits which always leave space between parts, interference fits which create actual interference or contact between parts, transition fits which can result in either clearance or interference, and line fits where contact or clearance can result during assembly. The document also discusses hole and shaft basis systems for specifying fits using tolerances and deviations from a basic size.
1. Gears transmit power between two shafts by meshing teeth without slip. The smaller gear is called the pinion and the larger is called the gear.
2. Gears can be classified based on tooth shape and disposition, including spur, helical, bevel, and worm gears. Spur gears have parallel teeth and transmit power between parallel shafts.
3. Involute tooth profiles satisfy the law of gearing by allowing the contact point between meshing teeth to move smoothly along a common tangent, transmitting motion efficiently. Involute profiles are commonly used in gear design.
presentation on CENTRE DISTANCE VARIATION,MINIMUM NUMBER OF TEETH,CONTACT RAT...STAVAN MACWAN
This document discusses various topics related to gears, including:
1. Center distance variation in gears can affect time-varying mesh stiffness and gear vibration. A new kinematic model is proposed to evaluate actual contact positions under varying center distances.
2. The minimum number of teeth for gears without undercutting is typically 17, though gears with fewer can be used if strength and contact ratio allow.
3. Contact ratio measures the average number of teeth in contact during engagement, and is typically 1.3-1.4 for machine tool components depending on the application's precision requirements.
4. Spur gears have straight, parallel teeth but produce high stresses and noise. Helical gears generate thrust but allow
This document provides an overview and tutorial on ISO 1940/1, an international standard for selecting balance quality requirements for rigid rotors. It outlines the standard's methodology for determining permissible residual unbalance (Uper) based on rotor type, weight, and maximum operating speed. The document simplifies the calculations for Uper and provides guidance on allocating Uper between correction planes for different rotor configurations, such as symmetrical, overhung, and narrow rotors. It also compares ISO 1940/1 balance quality grades to those specified by other standards like MIL-STD-167-1 and API.
This document discusses dynamics of rotating machinery with an emphasis on balancing. It covers balancing fundamentals, critical speeds and vibratory modes, damping, bearings and support structures. Case studies on balancing of a 115 MW generator rotor are presented, showing vibration measurements before and after balancing. Details of the generator rotor, balancing planes and trial weights used are provided. Common vibratory modes like rocking, conical and bending modes are explained. The document also discusses turbo machinery damping mechanisms and hydrodynamic bearings.
This document discusses balancing of rotating members. It defines balancing as restoring a rotor with unbalance to a balanced state by adjusting its mass distribution about its axis of rotation. Balancing is necessary for quiet and high-speed operation, as well as long bearing life. It describes static and dynamic balancing. Static balancing involves balancing in a single plane, while dynamic balancing accounts for masses in multiple planes. Graphical methods using force and couple polygons are presented for determining balancing masses and their positions to achieve dynamic balance. An example problem demonstrates using these methods to balance a shaft with masses in four planes.
According to ISO 1940/1:
- ISO 1940/1 defines balance quality grades (G values) that represent the maximum permissible vibration caused by unbalance at operating speeds. Lower G values indicate better balance quality requirements.
- Specific unbalance is the product of the rotor's center of gravity displacement and angular velocity. It is measured in units like mm/s.
- Maximum permissible residual unbalance (Uper) is calculated based on factors like specific unbalance, rotor weight, balancing radius, and rotor geometry. Formulas are provided to calculate Uper for general, symmetrical, overhung, and narrow rotors.
- Motors supply the force and torque needed for robots to move through wheels, arms, etc. The speed of a robot is determined by the wheel diameter and motor RPM.
- Factors like motor torque, robot weight, acceleration, and wheel diameter must be balanced to achieve proper velocity. The robot motor factor (RMF) can be used to quickly calculate torque requirements.
- For robot arms, the torque required at each joint must be calculated based on the load weight and distance from the pivot point to select the appropriate motor. Gears can be used to exchange torque and velocity.
The document provides service information for Honda CBR250FOUR and CBR250R motorcycles. It includes specifications, diagrams, and maintenance procedures for the engine, frame, electrical systems, and other parts. The document emphasizes following procedures carefully, using proper tools and materials, and ensuring safety during maintenance work. Individual sections cover inspection and repair of specific systems like the engine, suspension, brakes, and electrical components.
The document introduces the RCP4 series of actuators and their new Power CON 150 controller. Key points include:
1. The Power CON 150 controller allows speeds up to 1.5 times and payloads up to double previous models, significantly boosting productivity.
2. The RCP4 series now includes side-mounted motor and cleanroom specifications. Various slider and rod models are available.
3. New functions like total movement/travel counters and smart tuning allow easier maintenance and optimal setup of operating conditions.
This document provides information about balancing high speed rotors. It defines balancing as correcting the mass distribution of a rotor so that vibration forces and displacements are within specified limits when the rotor is rotating. It discusses the different types of unbalance that can occur, including static, couple, quasi-static and dynamic unbalance. The causes of unbalance are described as design errors, material faults, and machining/assembly errors. The balancing procedure and standards followed at BHEL Hyderabad are outlined, including low and high speed balancing of flexible rotors using modal and influence coefficient methods.
This document provides information about balancing high speed rotors. It defines balancing as correcting the mass distribution of a rotor so that vibration forces are within limits. There are four main types of unbalance: static, couple, quasi-static, and dynamic. Unbalance is caused by design errors, material faults, and machining errors. Flexible rotors require balancing at multiple speeds approaching critical speeds to account for deflection. Standards specify limits for vibration amplitudes and bearing forces for acceptance of balancing quality.
This document discusses flywheels and balancing of rotating masses. It defines a flywheel as an energy storage device that acts to smooth power transmission. Flywheels store excess energy from a motor and deliver it when needed. The kinetic energy of a flywheel depends on its moment of inertia and angular velocity. Flywheels are used to reduce torque fluctuations in machines like punch presses. The document also discusses balancing rotating masses to reduce vibrations by ensuring the system's center of gravity is at the axis of rotation.
The document discusses considerations for switching from air cylinders to electric cylinders (ROBO Cylinders). It covers key differences to consider like installation space needs, the need for home return operations, and different maintenance requirements. The document also provides details on allowable dynamic moment calculations and how moment loads impact service life. Installation orientation limitations are shown in a table for different ROBO Cylinder models.
The document summarizes the optimization of engine cycles for two different vehicles - a commercial airliner and long-range missile - at various flight conditions. For the airliner, a turbofan design provided the best performance, while a turbojet was best for the missile. The turbofan and turbojet designs were then optimized. For the turbofan, increasing the bypass ratio improved efficiency. For the turbojet, bleed ratio and compressor ratio were optimized to minimize fuel consumption while maintaining required thrust. Ramjet and turbojet performance were also compared, showing ramjets are better at high speeds and turbojets at low speeds.
This document provides steps to calculate the torque required for the drive wheel motors of a mobile vehicle. It describes calculating: (1) rolling resistance, grade resistance, and acceleration force to determine total tractive effort; (2) wheel torque based on tractive effort and wheel radius; and (3) maximum tractive torque a wheel can transmit to verify wheel torque can be achieved without slipping. An example calculation is shown for a 35lb vehicle traveling at 1.5ft/s on a 2 degree incline to determine a total wheel torque of 14lb-in is required.
This document provides guidance on calculating bearing life for railway applications. It discusses calculation principles, basic rating life calculations according to ISO 281, and more advanced SKF rating life calculations. It also provides example calculations for typical symmetrical and link arm axlebox designs, showing how to determine static and dynamic bearing loads based on vehicle specifications in order to calculate the basic or SKF rating life in millions of revolutions or kilometers.
Hyster r005 (h4.5 ft6 europe) forklift service repair manualfujsekfksmemer
This document provides specifications for service and repair of Hyster lift truck models H4.0FT5 through H5.5FT, including:
- Lifting capacities ranging from 3,629 to 5,443 kg
- Counterweight weights ranging from 2,172 to 3,294 kg
- Tire sizes for drive and steer tires
- Fuel, engine oil, coolant, hydraulic oil, and other fluid capacities
- Electrical system specifications like battery voltage and alternator output
- Transmission and hydraulic system relief pressures
Hyster r005 (h4.0 ft6 europe) forklift service repair manualfujsekfksmemer
This document provides specifications for service and repair of Hyster lift truck models H4.0FT5 through H5.5FT, including:
- Lifting capacities ranging from 3,629 to 5,443 kg
- Counterweight weights ranging from 2,172 to 3,294 kg
- Tire sizes for drive and steer tires
- Fuel, engine oil, coolant, hydraulic oil, and other fluid capacities
- Electrical system specifications like battery voltage and alternator output
- Transmission and hydraulic system relief pressures
Hyster r005 (h4.5 fts5 europe) forklift service repair manualfikdkksmmd
This document provides specifications for service and repair of Hyster lift truck models H4.0FT5 through H5.5FT, including:
- Lifting capacities ranging from 3,629 to 5,443 kg
- Counterweight weights ranging from 2,172 to 3,294 kg
- Tire sizes for drive and steer tires
- Fuel, engine oil, coolant, hydraulic oil, and other fluid capacities
- Electrical system specifications like battery voltage and alternator output
- Transmission and hydraulic system relief pressures
Hyster r005 (h5.0 ft europe) forklift service repair manualfujsekfksmemer
This document provides specifications for service and repair of Hyster lift truck models H4.0FT5 through H5.5FT, including:
- Lifting capacities ranging from 3,629 to 5,443 kg
- Counterweight weights ranging from 2,172 to 3,294 kg
- Tire sizes for drive and steer tires
- Fuel, engine oil, coolant, hydraulic oil, and other fluid capacities
- Electrical system specifications like battery voltage and alternator output
- Transmission and hydraulic system relief pressures
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Balance quality requirements_of_rigid_rotors
1. IRD Balancing Technical Paper 1
World’s Leading Supplier of Soft Bearing
Balancing Machines & Instruments
Balance Quality Requirements
of Rigid Rotors
The Practical Application of ISO 1940/1
2. ABSTRACT
International Standard ISO 1940/1 is a widely-
accepted reference for selecting rigid rotor
balance quality. This paper is presented as a
tutorial and user's reference of the standard and
its practical applications.
A simplified method is shown for determining
permissible residual unbalance for various rotor
classifications. Emphasis is given to allocating
permissible residual unbalance to appropriate
correction planes for rotor configurations, such
as unsymmetrical, narrow and overhung rotors.
Finally, a comparison of various balance quality
grades is made with MIL-STD-167-1 and API
balance limits.
INTRODUCTION
The International Standards Organization, ISO,
published Standard 1940/1 "Balance Quality
Requirements of Rigid Rotors," which has been
adopted by the American National Standards
Institute, ANSI, as S2.19-1975, "Balance Quality
Requirements of Rotating Rigid Bodies." It has
also been adopted by BRITISH Standards as BS
6861: Part 1 and by GERMAN Standards as VDI
2060.
ISO 1940/1 requires an understanding of
balancing and its terminology if the standard is
to be understood and used properly. The
reader is directed to the paper's "Balance
Terminology" section for a summary of terms
used in this paper.
USING THE STANDARD
The use of the standard involves the following
steps:
1. Select a balance quality grade "G number"
from Table 1 based on rotor type.
2. Use the Figure 1 (A or B) graph to determine
the permissible residual specific unbalance
value, eper for the rotor's maximum operating
speed and the selected "G number." Then
multiply eper by rotor weight to obtain the
permissible residual unbalance, Uper.
3. Allocate Uper to the balancing correction
planes based on rotor configuration.
Performing step 1 simply requires the user to
find the rotor type that most nearly describes
the one to be balanced.
Step 2 is more involved as it requires using the
graph in Figure 1 to find the permissible specific
unbalance, followed by multiplying by rotor
weight and then a constant to convert Uper to
proper units (gram-millimeters or ounce-inches).
This step can be simplified by using some
simple equations to calculate Uper directly.
Step 3, allocating Uper, is often not performed
because it is not easily understood.
Therefore, the following pages provide a
simplified method for step 2 and describe the
procedures for step 3.
1
Balance Quality Requirements of Rigid Rotors
The Practical Application of ISO 1940/1
3. 2
Table 1 Balance quality grades for various groups of representative rigid rotors
(From ISO 1940/1)
Balance
Quality
Grade
Product of the
Relationship
(eper x ) (1) (2)
mm/s
Rotor Types - General Examples
G 4 000
G 1 600
G 630
G 250
G 100
G 40
G 16
G 6.3
G 2.5
G 1
G 0.4
4 000
1 600
630
250
100
40
16
6.3
2.5
1
0.4
Crankshaft/drives(3)
of rigidly mounted slow marine diesel engines with uneven number of cylinders(4)
Crankshaft/drives of rigidly mounted large two-cycle engines
Crankshaft/drives of rigidly mounted large four-cycle engines
Crankshaft/drives of elastically mounted marine diesel engines
Crankshaft/drives of rigidly mounted fast four-cylinder diesel engines(4)
Crankshaft/drives of fast diesel engines with six or more cylinders(4)
Complete engines (gasoline or diesel) for cars, trucks and locomotives(5)
Car wheels, wheel rims, wheel sets, drive shafts
Crankshaft/drives of elastically mounted fast four-cycle engines with six or more cylinders(4)
Crankshaft/drives of engines of cars, trucks and locomotives
Drive shafts (propeller shafts, cardan shafts) with special requirements
Parts of crushing machines
Parts of agricultural machinery
Individual components of engines (gasoline or diesel) for cars, trucks and locomotives
Crankshaft/drives of engines with six or more cylinders under special requirements
Parts of process plant machines
Marine main turbine gears (merchant service)
Centrifuge drums
Paper machinery rolls; print rolls
Fans
Assembled aircraft gas turbine rotors
Flywheels
Pump impellers
Machine-tool and general machinery parts
Medium and large electric armatures (of electric motors having at least 80 mm shaft height) without
special requirements
Small electric armatures, often mass produced, in vibration insensitive applications and/or with
vibration-isolating mountings
Individual components of engines under special requirements
Gas and steam turbines, including marine main turbines (merchant service)
Rigid turbo-generator rotors
Computer memory drums and discs
Turbo-compressors
Machine-tool drives
Medium and large electric armatures with special requirements
Small electric armatures not qualifying for one or both of the conditions specified for small electric
armatures of balance quality grade G 6.3
Turbine-driven pumps
Tape recorder and phonograph (gramophone) drives
Grinding-machine drives
Small electric armatures with special requirements
Spindles, discs and armatures of precision grinders
Gyroscopes
1) = 2πn/60 ≈ n/10, if n is measured in revolutions per minute and in radians per second.
2) For allocating the permissible residual unbalance to correction planes, refer to "AIIocation of Uper to correction planes."
3) A crankshaft/drive is an assembly which includes a crankshaft, flywheel, clutch, pulley, vibration damper, rotating portion of connecting rod, etc.
4) For the purposes of this part of ISO 1940/1, slow diesel engines are those with a piston velocity of less than 9 m/s; fast diesel engines are those
with a piston velocity of greater than 9 m/s.
5) In complete engines, the rotor mass comprises the sum of all masses belonging to the crankshaft/drive described in note 3 above.
4. 3
Figure 1-A Maximum permissible residual unbalance, eper
(Imperial values adapted from ISO 1940/1)
PERMISSIBLERESIDUALUNBALANCEeperinlb-in/lbofrotorweight
or
CENTEROFGRAVITYDISPLACEMENT,eperininches
MAXIMUM SERVICE SPEED IN RPM
5. 4
Figure 1-B Maximum permissible residual unbalance, eper
(From ISO 1940/1)
PERMISSIBLERESIDUALUNBALANCE,epering-mm/kgofrotorweight
OR
CENTEROFGRAVITYDISPLACEMENT,eperinµm
MAXIMUM SERVICE SPEED IN RPM
6. BALANCE QUALITY GRADES
Table 1 shows the balance quality grades for a
variety of rotor types. The "G" number is the
product of specific unbalance and the angular
velocity of the rotor at maximum operating speed
and is a constant for rotors of the same type.
G = e x = constant
This is based on the fact that geometrically similar
rotors running at the same speed will have similar
stresses in the rotor and its bearings.
Balance quality grades are separated by a factor
of 2.5. However, G numbers of intermediate value
may be used to satisfy special requirements. For
example, a standard pump impeller has a
suggested balance quality grade of G 6.3. Special
conditions may require a better balance quality of
G 4.0 to satisfy installation in an area with low
structure-borne noise limits.
DETERMINING PERMISSIBLE
RESIDUAL UNBALANCE - Uper
Uper = eper x m
(m = rotor mass)
Permissible residual unbalance is a function of G
number, rotor weight and maximum service speed
of rotation. Instead of using the graph to look up
the "specific unbalance" value for a given G
number and service RPM and then multiplying by
rotor weight (taking care to use proper units), Uper
can be calculated by using one of the following
formulae:
Uper (oz-in) = 6.015 x G x W/N (W in Ib)
Uper (g-in) = 170.5 x G x W/N (W in Ib)
Uper (g-mm) = 9549 x G x W/N (W in kg)
G = Balance quality grade from Table 1
W = Rotor weight
N = Maximum service RPM
A slide rule that calculates Uper is also available
from some balancing machine manufacturers.
ALLOCATION OF Uper
TO CORRECTION PLANES
Uper is the total permissible residual unbalance
and must be allocated to the balancing correction
planes used based on rotor dimensions and
configuration.
For rotors balanced in a single correction plane,
all of the Uper applies to that correction plane.
For rotors balanced in two correction planes, Uper
must be allocated to each correction plane based
on rotor configuration and dimensions.
SYMMETRICAL ROTORS
Rules for symmetrical rotors. (See Figure 2.)
1. Correction planes are between bearings.
2. Distance "b" is greater than 1/3 "d."
3. Correction planes are equidistant from the
center of gravity.
Uper left = Uper right = Uper/2
When correction planes are NOT equidistant from
the center of gravity, then -
Uper left = Uper (hR/b)
Uper right = Uper (hL/b)
The Uper left or Uper right should not be less than
30% or more than 70% Uper. If they are, then
use rules for narrow rotors.
5
Figure 2 Symmetrical rotors
7. ROTORS WITH OUTBOARD
CORRECTION PLANES
Rules for rotors with correction planes outside the
bearings. This is often referred to as a "dumb-
bell" rotor configuration. (See Figure 3)
Both correction planes are outboard of the
bearings.
b > d
Adjust Uper by ratio of d/b. (Reduces Uper)
Uper = Uper (d/b) Uper = Adjusted value
When correction planes are not equidistant from
the center of gravity, calculate Uper left and right
as follows:
Uper left = Uper (hR/b) Uper right = Uper (hL/b)
OVERHUNG AND NARROW ROTORS
Rules for overhung and narrow rotors.
(See Figures 4 and 5).
1. Distance between correction planes is less than
1/3 the distance between bearings. b < 0.33 d.
2. Assumes equal permissible dynamic bearing
loads.
3. Couple corrections are made 180° apart in their
respective planes.
4. The plane for static corrections may be a third
plane or either of the planes used for couple
corrections.
5. Allocate Uper as static and couple residual
unbalance as follows:
Uper static = Uper/2 x d/2c
Uper couple = Uper/2 x 3d/4b
Permissible unbalance allocations for overhung
and narrow rotors require that two plane
unbalance corrections be divided into static and
couple unbalance equivalents. This can be done
graphically by plotting the two plane balance
solution vectors UL and UR as shown in Figure 6.
Connect vectors UL and UR as shown. The vector
from the origin to the mid-point of vector CL-CR is
one-half the rotor's static unbalance. Vectors CL
and CR are the couple unbalance.
6
Figure 3 Rotor with outboard planes
Figure 4 Overhung rotors
Figure 5 Narrow rotors
Figure 6 Static-couple graphical derivation
8. 7
Figure 7 Comparision of API, ISO & MIL-STD-167-1 balance tolerances
MAXIMUM CONTINUOUS OPERATING RPM
1 in = 25.4 mm
1 mm = .0394 in
1 lb = 454 g
1 kg = 2.2 lb
1 mil = 25.4 µm
1 µm = .0394 mil
1 oz = 28.35 g
1 g = .0353 oz
1 oz in = 720 g mm
1 g mm = .00139 oz in
Useful Conversions
COMPARING API, ISO & MIL-STD-167-1
BALANCE TOLERANCES
Uper = Permissible residual unbalance FOR EACH CORRECTION PLANE in ounce inches. (oz-in)
W = Rotor Weight In Pounds. W = 1000 lbs. for all examples shown.
N = Maximum Continuous Operating RPM.
G = ISO Balance Quality Grade Number, i.e. 6.3, 2.5, 1.0 etc.
Fc
< 10% Journal Static Load Uper = 56.347 x (Journal Static Load W/2)
ISO Uper = G x 6.015 x W/2
N2
N
MIL-STD-167-1 Uper = 0.177 W (0 to 150 RPM)
= 4000 W / N2
(150 to 1000 RPM)
= 4 W / N (Above 1000 RPM)
W = Total Rotor Weight
API Uper = 4 W / N (W = Journal static Load)
Fc
= 1.77 (RPM/1000)2
(oz-in) [Centrifugal Force]
150
500
1000
2000
3000
4000
5000
6000
7000
177
16
4
2
1.33
1.0
.8
.67
.57
7
7
7
14
21
28
35
43
49
126.0
38.0
19.0
9.5
6.3
4.7
3.8
3.2
2.7
5
17
34
67
100
133
168
201
234
50.0
15.0
7.5
3.8
2.5
1.9
1.5
1.3
1.1
2.0
6.6
13.3
26.6
39.8
53.8
66.4
79.7
92.8
20.0
6.0
3.0
1.5
1.0
.8
.6
.5
.4
0.8
2.7
5.3
10.6
15.9
21.2
26.6
31.9
37.3
13.3
4.0
2.0
1.0
0.6
0.5
0.4
0.3
0.3
0.5
1.8
3.5
7.1
9.6
14.2
17.7
19.1
26.0
1252.0
113.0
28.0
7.0
3.1
1.8
1.1
0.8
0.6
50
50
50
50
50
50
50
50
50
N
Uper
oz-in
Centr.
Force
Uper
oz-in
Centr.
Force
Uper
oz-in
Centr.
Force
Uper
oz-in
Centr.
Force
Uper
oz-in
Centr.
Force
Uper
oz-in
Centr.
Force
MIL-STD-167 ISO G 6.3 ISO G 2.5 ISO G 1.0 API FC = 10%W/2
Copyright 1999 IRD Balancing
DATA TABULATION
9. STANDARDS COMPARISON
A frequent question is, "How do the ISO 1940/1
quality grades compare with other balancing
standards, such as API and MIL-STD-167-1?"
A comparison graph and data tabulation appears
in Figure 7. Three ISO grades (6.3, 2.5 and 1.0),
MIL-STD-167-1 and API balance quality standards
are compared in tabular and graphical form.
In addition, Uper was calculated for a constant
centrifugal force of 50 pounds (10% of static
journal load). A symmetrical 1000 pound rotor
with the C.G. midway between bearings and
correction planes was used. Static load at each
journal is 500 pounds and centrifugal force was
calculated for each Uper.
To more clearly show the relationship, a
summary of balance quality standards and their
corresponding centrifugal forces are shown in
Table 2 as a percentage of journal static loading
for 900, 1200, 1800 and 3600 RPM.
Table 2 Centrifugal force as a percent
of journal static load
Uper = Permissible residual unbalance for each correction plane
F = Centrifugal force due to residual unbalance
L = Journal static load L = W/2 W = 1000 lbs.
From the graph and Table 2, it is easy to see
that the API standard demands a low residual
unbalance level and with a smaller unbalance
force load on the rotor's bearings. However,
the effort to achieve this result may not always
be cost effective.
Published balance tolerances provide everyone
with a common reference for communicating
balance quality expectations, as well as what
the provider promises. Proper interpretation
and application of each is needed to realize
satisfaction for everyone.
BALANCE TERMINOLOGY
BALANCE QUALITY GRADE - GXXX - for rigid
rotors, G, is the product of specific unbalance, e,
and rotor maximum service angular velocity.
Service angular velocity is service RPM expressed
in radians per second.
G = e x = constant
CENTER OF GRAVITY - the point in a body through
which the resultant of the weights of its
component particles passes for all orientations of
the body with respect to a gravitational field C.G.
CORRECTION (BALANCING) PLANE - plane
perpendicular to the shaft axis of a rotor in which
correction for unbalance is made.
COUPLE UNBALANCE - that condition of
unbalance for which the central principal axis
intersects the shaft axis at the center of gravity.
CRITICAL SPEED - speed at which a system
resonance is excited. The resonance may be of
the journal supports (rigid mode) or flexure of the
rotor (flexural mode).
DYNAMIC UNBALANCE - that condition of
unbalance for which the central principal axis is not
parallel to and does not intersect the shaft axis.
8
Balance
Quality
Std.
900 RPM 1200 RPM 1800 RPM 3600 RPM
Uper
oz-in
Uper
oz-in
Uper
oz-in
Uper
oz-in
F/L % F/L % F/L % F/L %
ISO G6.3
ISO G2.5
MIL-STD
ISO G1.0
API
21
8.3
4.4
3.3
2.2
6.0%
2.4%
1.3%
0.9%
0.6%
15.8
6.3
3.3
2.5
1.7
8.1%
3.2%
1.7%
1.3%
0.8%
10.5
4.2
2.2
1.7
1.1
12.0%
4.8%
2.5%
1.90%
1.3%
5.3
2.1
1.1
0.8
0.6
24.1%
9.6%
5.1%
3.7%
2.6%
10. Note: Dynamic unbalance is equivalent to two
unbalance vectors in two specified planes which
completely represent the total unbalance of the
rotor.
Note: Dynamic unbalance may also be resolved
into static and couple unbalance vectors whose
vector sum is also equal to the total unbalance of
the rotor.
FLEXIBLE ROTOR - a rotor that does not satisfy the
rigid rotor definition because of elastic deflection.
PERMISSIBLE RESIDUAL UNBALANCE Uper - the
maximum residual unbalance permitted for a
rotor or in a correction plane.
Uper = eper x m
where m = rotor mass
PRINCIPAL INERTIA AXIS - the coordinate
directions corresponding to the principal moments
of inertia. In balancing, the term principal inertia
axis is used to designate the central principal axis
most nearly coincident with the shaft axis of the
rotor.
RESIDUAL (FINAL) UNBALANCE - the unbalance
of any kind that remains after balancing.
RIGID ROTOR - a rotor is considered rigid if its
unbalance can be corrected in any two correction
planes. After the correction, the residual
unbalance does not change significantly at any
speed up to the maximum service speed.
ROTOR - a body capable of rotation which
generally has journals supported by bearings.
STATIC UNBALANCE - that condition of unbalance
for which the central principal axis is displaced
only parallel to the shaft axis.
SPECIFIC UNBALANCE - static unbalance U
divided by rotor mass m (i.e., mass eccentricity).
Note: In the case of a rotor with two correction
planes, specific unbalance may refer to the
unbalance in one plane divided by rotor mass
allocated to that plane.
REFERENCES
1. ISO 1940/1, "Balance Quality Requirements of
Rigid Rotors." International Organization for
Standardization.
2. ANSI S2. 19-1975, "Balance Quality
Requirements of Rotating Rigid Bodies."
American National Standards Institute.
3. BS 6861: Part 1, "Balance Quality Requirements
of Rigid Rotors." British Standards Institution.
4. VDI 2060, "Balance Quality Requirements of
Rigid Rotors." German Standards Institution.
5. Standard Paragraphs, API Subcommittee on
Mechanical Equipment, Revision 19, September
1991. American Petroleum Institute.
6. MIL-STD-167-1 (SHIPS), 1 May 1974,
"Mechanical Vibrations of Shipboard
Equipment." Department of the Navy,
Naval Ship Systems Command.
7. "DYNAMIC BALANCING HANDBOOK,"
October 1990, IRD Mechanalysis Inc.
8. ISO 1925, “Balancing Vocabulary.”
International Organization for Standardization.
9