Friday, 17 August 2012

Design of flywheel


Design of a Flywheel

Introduction
A flywheel is an inertial energy-storage device. It absorbs mechanical energy and serves as a reservoir, storing energy during the period when the supply of energy is more than the requirement and releases it during the period when the requirement of energy is more than the supply.

Functions and Operation
The main function of a fly wheel is to smooth en out variations in the speed of a shaft caused by torque fluctuations. Flywheel absorbs mechanical energy by increasing its angular velocity and delivers the stored energy by decreasing its velocity

Design Approach
There are two stages to the design of a flywheel.
First, the amount of energy required for the desired degree of smoothing must be found and the (mass) moment of inertia needed to absorb that energy determined.
Then flywheel geometry must be defined that caters the required moment of inertia in a reasonably sized package and is safe against failure at the designed speeds of operation.

Design Parameters 
  •  Speed Fluctuation - This gives the range of speed
  • Coefficient of speed fluctuation - This gives a dimension-less ratio which is a normalized form obtained by dividing range by average
Geometry of Flywheel
The geometry of a flywheel may be as simple as a cylindrical disc of solid material, or may be of spoked construction like conventional wheels with a hub and rim connected by spokes or arms Small fly wheels are solid discs of hollow circular cross section. As the energy requirements and size of the flywheel increases the geometry changes to disc of central hub and peripheral rim connected by webs and to hollow wheels with multiple arms.

The latter arrangement is a more efficient of material especially for large flywheels, as it concentrates the bulk of its mass in the rim which is at the largest radius. Mass at largest radius contributes much more since the mass moment of inertia is proportional to mr2.

Stresses in Flywheel
Flywheel being a rotating disc, centrifugal stresses acts upon its distributed mass and attempts to pull it apart. Its effect is similar to those caused by an internally pressurized cylinder.
Analogous to a thick cylinder under internal pressure the tangential and radial stress in a solid disc flywheel as a function of its radius r is given by:
The point of most interest is the inside radius where the stress is a maximum. What causes failure in a flywheel is typically the tangential stress at that point from where fracture originated and upon fracture fragments can explode resulting extremely dangerous consequences, Since the forces causing the stresses are a function of the rotational speed also, instead of checking for stresses, the maximum speed at which the stresses reach the critical value can be determined and safe operating speed can be calculated or specified based on a safety factor.

Sunday, 12 August 2012

Work Measurement technique


A Survey of Work Measurement Techniques
    Dr. W. A. Woeber, PrEng, DSc(Tech), FIMechE, FIProdE

Seventy-five years have passed since Frederick Winslow Taylor presented his Paper on "A Piece-Rate System" to the American Society of Mechanical Engineers. It was he who adopted the term time-study and who set the pattern for the study of time elements and cycle times. Today, in operational research, we feel that indirect measures of fact are preferable to direct operational measures with the result that statistical and mathematical techniques have, in many instances, replaced the basic time study technique.
Although stopwatch time study and elemental time values are useful for measuring repetitive short cycle labour operations, most indirect activities are characterised by relatively long, irregular cycles requiring a work measurement technique based on statistical principles that allow generalisations about the entire time span to be made on the basis of a sample of that time interval.
Rating research:
                        The object of modern time study is to assess the work content of a specific task in terms of the time it should take a fully trained and experienced worker to carry out that task at "standard performance". This is achieved by comparing the performance of the worker with the observer's own concept of standard performance which is rated at 100 on the B.S. Scale. In addition to assessing the worker's rate of working, the time taken to complete the task is measured.
                 By multiplying the rating by the time taken, the Basic Minute Value (BMV) of the task is obtained. Certain relaxation allowances, which take into account the ergonomic and environmental conditions under which the task is performed, are added to the BMV to derive the Standard Minute Value (SMV).
                                                                             The random variations in performance times of a particular worker may be assumed to be normally distributed. The distribution will have a mean y. and a standard deviation a. The standard error will be equal to a divided by \/n, where n, the number of observations, represents the sample size. The actual size of the sample will be determined by the degree of accuracy which the analysis demands. To assess a "qualified" worker's rate of working raises the question of how the attributes of such a worker are to be defined.
                                              In the Westinghouse System the worker is evaluated in terms of four factors. These are skill, effort, consistency, and working conditions. Briefly, skill is defined as the proficiency at following a given method; effort, as the will to work; consistency, as the degree of variation in performance times; and conditions, as the characteristics of the physical environment which affect the worker, such as noise, light, heat and humidity.
                               Firstly, if normal working times (NWT) for the elements are available, a company can develop standard data for future use to describe a new job. Secondly, elemental time data permit making better estimates of the probable effect of method changes.  A variation and extension of effort rating was developed by Mundel5. He claims to have reduced the degree of subjective judgment to what he has called "objective rating". A modified version of the objective rating system has been proposed by Nadler6. Known as "pace rating", it follows the same procedure except that the rating of the worker's operating pace is obtained by selecting a speed, which is comparable, from a "step film". The film loop consists of a series of gradually increasing working paces of the performances of a simple job and each different pace is preceded by a symbol identifying the performance level. The pace rating system, like all the others, has its limitations; difficulties are encountered in selecting typical jobs and , judgment plays an inordinate role in their selection. An interesting research project was undertaken by Desmond who developed a method of analysis to measure three major defects in the techniques of work measurement, namely errors in the concept of normal performance, "flatness" of rating, or the inability to appreciate proportionate changes in speed, and residual inconsistency of rating, or the inability to recognize the same speed when seen on more than one occasion. A simplified graphical version of Desmond's "reciprate method", based on regression analysis, is shown in Fig. 1.

The ratings are plotted against the times on specially prepared graph paper, in which the rating scale is proportional to the reciprocal of the rating. A rule is then placed through the origin and rotated until it produces the best fit. The time corresponding to the intersection of this line with the normal performance line is then the estimated normal time. The next step consists of drawing the study line by eye and measuring, on a linear scale, the height of its intersection with the original line through the origin. This distance is represented by the symbol E in Fig. 1. The height of the intersection of the study line with the rating axis is also measured and it is represented by the symbol D; this can be a negative quantity when the particular study is steep.
The ratio D/E is then the flatness of the study, and records of variation from study to study give a good indication of the ability to maintain a certain quality of rating with respect to this defect. Such records are conveniently kept as control charts, although calculation of control limits is subject to considerable difficulty.
                         The inconsistency of the study is determined graphically by means of the range of scatter about the estimated operation line. The plotted point is chosen which lies at a maximum vertical distance above the line, and this distance is represented by the symbol A. Similarly, the distance B represents the semi-range below the estimated operation line. Then the sum of these distances A + B = to is the range of reciprate scatter and can be used to estimate the standard deviation about the line. Desmond concluded his paper by stating that the method had been applied to the analysis of some 32 000 observations which had been collected during a nation-wide survey of time study rating accuracy.
Work sampling techniques:
                                   Work sampling is based upon statistical principles that allow generalisations about the entire time span to be made on the basis of a sample of that time interval. The technique, also described as the ratio-delay method, originated with L H. C. Tippett10of the Shirley Institute of the British Cotton Industry Research Association. The fundamental principle of work sampling may be stated thus: the number of observations is proportional to the amount of time spent in the working or idle state. The accuracy of the estimate depends on the number of random observations and on pre-set precision limits and confidence levels. The treatment of the data requires the setting up of a statistical model following a binomial distribution; statistical quality control methods can be used in analysis. Hence, from the simple formula for mean proportion:


and tables have been developed which give control limits. (Barnes). See Fig.
Quantitative approaches to the solution can be made by assuming that the nature of the service and arrival times follows a Poisson distribution. Essential to waiting-time analysis is the ratio of service time to between-service time. This ratio is defined as K. Work sampling provides a convenient means for the collection of the data.
If (in fractions)
m = machine time,
b = service time and
d = machine idle time,
then
m + b + d = 1
and
K = b/m
Once K is known, tables, such as those compiled by Docent Conny Palm, may be consulted to find the changes in the various times of idling, service, and operation with changes in number of machines per serviceman.
Another approach is Monte Carlo simulation. This method calls for estimating on the basis of past experience the probabilities of occurrence to be associated with the various possible service and arrival times.

Physiological work measurement:
                                          In physics and the engineering sciences "work" is defined as the scalar product of force and displacement. In
Physiology, however, the concept "work" has a more complex meaning. A physiologist sometimes speaks of "work", where it would be better to use the term "effort". "Energy" is the capacity for doing work. Physical working capacity, or the physiological limit for sustained work, is measured as the worker's maximum oxygen intake. Economy of effort in the performance of a task is expressed as the rate of oxygen in litres per minute, the physiologist's measure of energy expended to the work performed. Energy expenditure data are also stated in terms of calories per minute and heart rate data in beats per minute.

Relaxation allowance:
                             This is defined2 as "an addition to the basic time intended to provide the worker with the opportunity to recover from the physiological and psychological effects of carrying out specified work under specified conditions". To determine allowances for recovery from fatigue, the time study analyst uses tables which are based upon estimates of the physiological strain the worker is likely to experience as a result of the physical effort of the task and any environmental stresses which might add to the physical effort.
Physical effort is estimated from the metabolic activity of the worker, the air exhaled by him being collected in a Douglas bag. This is then quantitatively analysed and the rate of oxygen consumed per unit of time is computed.

Under ideal conditions, if
£ = total energy expenditure per minute,
r = rate of working,
n = energy expenditure per minute due to normal metabolism, and
m = energy expenditure per minute not due to normal metabolism,
then
£ = mr + n,
or
m= (E - n)/r
Summing up, it can be stated that where physical effort is involved in an operation, information can be obtained by means of energy expenditure measurements, the physiological strain involved and the time necessary for circular respiratory recovery.

Conclusion
As a result of increased mechanisation in industry, the muscle load on the worker will be reduced. The man machine system will give him less and less to do with his legs, arms and trunk, and more to do with his eyes and his fingers in the way of watching and manipulating controls, pointers and switches. This is the change of the work load from the more physiological elements to the psychological aspects of man. The physical load is diminished and the perceptual load increased.

Gas Turbine as a prime mover

THE GAS TURBINE AS A PRIME MOVER
FOR STANDBY POWER APPLICATIONS
Bernt Marcussen, Kongsberg Dresser Power A/S
P.O. Box 173
3601 Kongsberg,Norway

Introduction:
Many think that a gas turbine, as the expression implies, solely burns gaseous fuels. This is not correct. It is true that gaseous fuels of different qualities are excellent for a gas turbine; however, the machine runs equally welt on liquid fuel.
Gas turbines on standby duty in most cases operate on liquid fuel, either a light diesel fuel or kerosene.

Principle of operation:
Gas turbines are normally classified in two groups, single shaft and two shaft engines. The compressor and turbine sections can be either of the axial or radial type. The principle of a single shaft gas turbine is shown schematically in Figure 1. Air at atmospheric conditions is drawn into the compressor and delivered from the compressor to the combustion chamber at an elevated pressure. Fuel supplied to the engine supports the continuous burning in the combustion chamber. The hot combustion gases pass through the guide vanes to the turbine
wheel where energy is released from the hot gases. The turbine wheel drives the compressor which is positioned on the turbine wheel shaft (single shaft concept).
The net power which is the difference between the power generated by the turbine wheel and the power absorbed by the compressor is transmitted through a reduction gear to the output shaft where a generator may be connected.

Single shaft gas turbines typically have very high rotational speed stability. However, the torque transmitted is at its maximum at rated speed and decreases rapidly with decreasing speed. Single shaft turbines are therefore ideal in constant speed applications such as generator drives.
In applications where operation over a wide speed range is required a two shaft engine may be the best choice. A two shaft engine consists of a gas generator section and a power turbine section. The gas generator section is in principle the same as a single shaft turbine, where the turbine wheel is designed to develop just enough power to drive the compressor. The residual energy in the gas generator exhaust drives the power turbine positioned on a separate shaft which is also the output shaft. With the dual shaft concept, high torques may be transmitted at low speeds, making the dual shaft gas turbine ideal for compressor drives, pump drives etc.
Figure 2 shows the principle of a dual shaft gas turbine.

General features:
Weight and volume Gas turbines are much lighter and much smaller than comparable diesel engines. The reason is that in a gas turbine the compression, ignition and expansion are continuous processes and in addition the rotating speed is considerably higher. The rotating elements in a gas turbine are in complete balance and therefore only a High engine frame structure is required. In the lower horsepower range the
difference in weight and size between the two engine types is not very apparent, but in the higher range the difference is significant. The low weight of a gas turbine and the fact that vibrations are almost non-existent mean that the foundation requirements are minimal. The force transmitted to the foundation is for all practical purposes equal to the static weight of the machine and there are virtually no forces transmitted due to vibration. It is fully acceptable to install a gas turbine generating set on a building floor dimensioned for the static
weight of the set.
A typical 1500 kW generating set has the following weights (KDP KG2):
Gas turbine and gear
2.5 tons
Generator
5.0 tons
Common base frame and auxiliary equipment
1.0 tons
Total
8.5 tons
Length: approx. 4 meters (12 ft).

Cooling:
The cooling of a gas turbine engine is simple. Only the heat generated in the rotor bearings and in the reduction gear needs to be dissipated. This can easily be achieved in small oil to air cooler or oil to water cooler, depending on the facilities available at the installation site.
It is customary to choose oil to air cooler for a standby generating set, since experience has shown that the water supply is often cut off at the same time a blackout occurs. The heat which needs to be dissipated normally amounts to about 5% of the rated power of the generating set, which calls for an oil cooler quite moderate in size. The ejector principal may be applied to eliminate the need for motor driven fans. This increases the potential for maintaining a high level of reliability. In a diesel engine the heat to be dissipated is of the same order of magnitude as the rated power of the engine. In a gas turbine the principal part of the heat loss is concentrated in the exhaust gases, which leave the engine at a relatively high temperature and at a high rate of flow.

Rotational speed stability:
Single shaft gas turbines have very high rotational speed stability. This is the result of a large mass rotating at high speed. Speed variations due to load changes are suppressed by the substantial amount of kinetic energy stored in the rotating elements.

Fuel consumption:
The fuel consumption of small and medium size gas turbines is normally about double the consumption of comparable diesel engines. The fuel consumption may be reduced considerably through adopting  recuperate for preheating which preheats the air before it enters the combustion chamber. However, this is expensive and increases the installation cost significantly. Standby generators would normally accumulate very few hours of operation and the fuel consumption is of minor importance.

Noise:
Because of its cousin the jet engine, gas turbine engines have a quite adverse reputation for being potential noise generators. The design philosophy of aircraft jet engines is entirely different and there is a very significant difference in the sound pressure levels of the two engine types. This is not to say that the gas turbine engine needs no silencing - some is required for all types of rotating power machinery. The noise emitted from a gas turbine is air borne and at high frequency, and the silencing is therefore quite simple.

Start-up time:
Start-up of a gas turbine implies that the heavy rotor mass must be accelerated to a high speed level. A gas turbine would therefore normally require a longer starting time than a comparable diesel engine. On the other hand a gas turbine may be loaded to 100% immediately upon reaching rated speed, while diesel engines often require loading in steps. Experience shows that a start-up time of 40-50 seconds is fully acceptable for large standby generating sets provided full load can be accepted immediately, when the engine reaches 100% speed.

Controls and supervisory systems:
By-an-large gas turbines require the same supervisory system and controls as other prime movers. Normally this implies alarm and shutdown in case of excessive levels of rotating speed, lube oil temperature and exhaust gas temperature. Whether the design engineer specifies alarm or shutdown depends on the nature of the specific installation in question.

Emissions:
Gas turbines operate with an air/fuel ratio high above the stoichiometric level. This secures an almost complete combustion and results in an invisible exhaust containing very small quantities of undesirable components. Figure shows an exhaust gas analysis of a Kongsberg Dresser Power KG2 gas turbine operating at approx. 1500 kW.

The extremely low content of CO is a result of the high air/fuel ratio (approx.4:1) while the very low NOx-numbers is the result of a combustion at low pressure and rapid cool-down of the flame front.

Lube oil system:
We mentioned earlier that a gas turbine generating set requires a supply of lube oil to the rotor bearings and to the reduction gear. Common mineral oils are normally specified however synthetic oils are equally suitable. In the Kongsberg Dresser Power KG2 turbine the two rotor bearings of hydrodynamic type are both positioned in the cold section of the machine. This means that the oil cannot be contaminated by the exhaust gas, nor will there be any loss of oil to the combustion chamber. The consumption of lubricating oil in the KG2 gas turbine is therefore very small.

Auxiliary power requirement:
While on standby a gas turbine generating set has some need for the supply of auxiliary power. For a KG2 generating set in the 1300-1700 kW power range the power demand is limited to the following:
Charger for control system batteries (24V) : 2 kW
Charger for start batteries (48V) : 7 kW
Lube oil reservoir heater : 2 kW
Heater inside generating casing : 0.4 kW

Reliability:
The starting and operating reliability is probably the most important feature required in a standby generating set. The single shaft gas turbine with a single stage radial compressor and a single stage radial inflow turbine is probably the simplest prime mover in existence today and it has the potential for being the most reliable. The single shaft gas turbine is in principle identical to a turbocharger except that the gas turbine has its own combustion section and an output shaft.

Applications of the gas turbine:
In principle gas turbines may be installed wherever there is a need for standby power, except in cases where an extremely short start-up time is essential. Experience shows that gas turbines are more competitive in applications above 1000 kW than in the lower power range. This has to do with the pricing structure. The price of gas turbines per kW increases with decreasing engine size, while it is the opposite for diesel engines. The explanation lies in the difference in production volume for the respective prime movers. The larger the power requirement, the more competitive the gas turbine, particularly when the low installation and maintenance costs are taken into consideration. Gas turbines often represent the only alternative, particularly in cases where standby generating sets are engineered into existing facilities and where it is difficult to supply the necessary amount of cooling air for a diesel engine. For roof top installations the gas turbine is often the only realistic alternative.