Kinetics Corporation

Features
1. Wide range of experiments
2. Forced and free vibrations
3. Experiments easily assembled
4. Covers requirements of most courses

Description
This apparatus enables a comprehensive range of vibration experiments to be conducted on a single basic framework. The experiments are specially designed for quick and easy assembly onto the framework. The frame is of extruded aluminum sectional frame which is installed on a rolling laboratory trolley with screw jacking for leveling. The working area of the frame is 900 mm wide by 700 mm height. Fastening elements are used for the formed grooves to obtain quick and accurate experimental set-up. The pendulum experiments set allows student to investigate several different types of pendulum, their characteristics and behavior.

The vibrator consists of a beam mounted in ball bearings at one end: a helical spring is hung on the other end of the beam. Force vibration is generated with an electric motor driven unbalance exciter.

The attachment of springs, the exciter and a damper to a perforated panel permits a wide range of different set-ups to be reproduced. The exciter frequency can be set on a control unit with digital display. The vibration can be damped using the adjustable viscosity damper. A mechanical drum and a polar diagram record the vibration.

The experiment also includes an amplitude contact with a TTL output, for triggering stroboscopes. The computerized data acquisition system is used to acquire through appropriate transducer and acquired data are analyzed and displayed graphically and numerically on the PC screen.

The application software for this is supplied and the software can be run on Microsoft Windows XP.

Range of experiments
1. Pendulum Experiments
- Simple Pendulums
One steel and one wooden ball of identical size (50 mm diameter) are supplied and each may be suspended on light cord from two pin vices on the sub-frame. The length of suspension can be altered by drawing the cord through the vices and hence the relationship between length and periodic time can be investigated.
- Compound Pendulums
Two compound pendulums are supplied. All pendulums are suspended on their knife-edge supports. The variation in periodic time may be investigated for different suspension positions in the case of the rod; and different mass positions in the case of the board. In both cases the experimentally determined radius of gyration can be compared with the theoretical value.

Additionally, a second knife-edge and a heavy adjustable steel mass are supplied. These can be fitted to the rods so that a reversible (or Kater) pendulum is obtained. The mass can be adjusted for any given distance between knife-edges until the periodic time is the same about each knife-edge. The measurement of periodic time is displayed digitally on the front panel of control box. The precise distance between knife-edges is then the length of an equivalent simple pendulum and the results can be used to determine an accurate value for the acceleration due to gravity.
- Bifilar Suspension
A uniform rectangular bar is suspended by strong cord from the pin vices of the sub-frame. It is drilled a regular intervals along its length to accept two 1800gm pegged masses. By measuring the periodic time of torsional vibration for various lengths of suspension, values for the radius of gyration of the bar assembly can be found and compared with the theoretical value. Similarly, other bodies could be bolted to the bar and their radius of gyration experimentally determined.
- Center of Percussion
The same wooden compound pendulum is used together with an adjustable heavy steel ball. The length of the simple pendulum is adjusted so that when allowed to swing and impact the compound pendulum, there is no lateral movement of the knife edge on the flat support. This is the point at which the length is equal to the equivalent length of the compound pendulum and is known as the center of percussion. At all other conditions there will be a noticeable reaction at the knife-edge support.
2. Mass-Spring System
Any one of three, different rate, open coil helical springs can be suspended from an upper adjustable assembly which is clamped to the top member of the basic frame. To the bottom of the spring is attached a rod and integral platform onto which ten 400g masses can be placed to load the spring.

The lower end of the rod passes through a guide bush. This ensures truly vertical vibrations of the assembly. A vernier depth gauge is supplied to measure deflections and this can be fitted to the upper assembly with its moveable stem. Each spring can thus be accurately calibrated before testing. For various applied masses, the spring can be freely vibrated and its periodic time measured.
3. Free and Forced Vibrations
A steel beam is clamped at one end into a bracket which can be fixed to the side of the basic frame. The beam is free to pivot in ball bearings in the bracket. The free end of the beam is supported by one of three tension springs (different stiffness) and uses the upper adjustable assembly. The assembly provides a handwheel adjustment so that the beam can be leveled before test.

A pen can be fitted to the free end of the test beam and continuously traces the vibrations onto a motor driven drum recorder. Amplitude and frequency measurements can be taken from the permanent trace. Using the linear transducer, the trace of vibration can be seen and recorded on the computer. The computer program can also analyze and displayed the amplitude and frequency.

The damper, which is provided, can be located three positions along the test beam to alter the degree of damping. The damping can be adjusted between 5 and 15 N-s / m. Forced vibration tests can be conducted using the Exciter Motor and Control Unit. The exciter motor is 24 volt 30 W DC motor and the speed is controlled in the range of 0 to 3000 rev/min. The motor and its lower belt-driven shaft assembly can be transversely clamped onto the beam in any convenient position relative to the pivot. The slow speed (driven) shaft rotates at approximately one third motor speed and carries an unbalanced disc each end. A plain circular piece of paper can be attached to the light smooth plate which is clamped to the front unbalanced disc.

Its tip can be brought into contact with the disc to make a circular trace of the beam vibration. Analysis of a simple paper trace will reveal both the amplitude of vibration and the phase difference between the beam and the unbalanced force. Using the optical sensor and linear transducer, both the amplitude of vibration and the phase difference between the beam and the unbalanced force are analyzed and displayed on the computer.

A wide range of masses (10 numbers of 400 gm) can be clamped beneath the motor assembly to increase the inertia of the system. These are common to both this experiment and Mass- Spring System experiment.

To prevent the damage or injury during resonant conditions, a safety stop is provided to limit the amplitude of the vibrations. This can be clamped to the top member of the basic frame.
4. Lateral Vibrations
A steel beam is supported at one end by the pivot bracket and at the other end by a similar bracket designed to allow free lateral movement of the beam during test. The same Exciter Motor and Control Unit are used for lateral vibration experiments. The basic motor can be clamped anywhere along the beam and loaded underneath with the range of masses.

This experiment also includes an amplitude contact with a TTL output, for triggering stroboscopes. The micrometer/contactor arrangement is used to measure both the amplitude of vibration and the phase difference between the vibration beam and the unbalanced rotating force.

The optical sensor provide the phase information to computer. The amplitude and frequency of vibration are measured with the linear transducer . The computer software can display the amplitude and frequency of vibration and the phase difference between the vibrating beam and the unbalanced rotating force.
5. Undamped Vibration Absorber
This is an attachment for clamping to the underneath of the basic motor unit of experiment. It consists of a central block carrying two spring steel cantilevers onto which steel masses are clamped. During vibration of the beam, these masses can be adjusted along the cantilevers until the system is correctly tuned. At this point, all the vibrations are transmitted to the absorber and the beam and motor unit remain stationary.
6. Free Torsional Vibrations
For experiments on undamped torsional vibrations of shafts, the vibrating inertia is provided by a heavy steel flywheel of 254 mm diameter x 50 mm thick. Three steel test shafts are supplied: different diameters and same length of 965 mm.

The compound rotor system consisted of 180 mm diameter flywheel, two pairs of steel arms bolted to sides of the flywheel and two pairs of masses of 100 mm diameter x 50 mm thick attached to both ends of arms.

Both flywheels can be freely rotate on the bearing support units attached to the side frames. One end of the steel test shaft is joined to the flywheel by a chuck and at the other end or at certain distances from other end the shaft is fixed by a collet and support system. By this way flywheel can oscillate torsionally. The torsional stiffness of the shaft can be varied by changing the distance between the fixed collet and the flywheel. The amount of inertia can be changed by using a heavy flywheel and compound rotor system with and without extension masses.

A double flywheel system having fixed test span, can be obtained by removing collet and support system and mount flywheels, one at each end.
7. Damped Torsional Vibration
A heavy steel flywheel is suspended from a chuck which is contained in a bracket. This bracket can be clamped to the top member of the frame so that the chuck hangs over the side of the frame. The length of the shaft between chuck and flywheel can be varied. The test shaft passes through a removable nylon guide bush which is fitted to a bracket carried on the side of the frame. The conical aluminum base of the flywheel is lightly grooved at equal intervals on its surface and can, therefore, be precisely immersed in the oil reservoir beneath. The oil is contained in a large Perspex cylinder having an open top. This is supported on a bracket on the frame and can easily be adjusted vertically on a screw thread to increase or decrease the depth of immersion of the cone and hence the amount of damping.

A drum recorder is fitted to the flywheel to allow a permanent amplitude/time chart of the vibration obtained. A pen is again used to trace the vibrations onto a piece of paper wrapped around the drum. This pen is supported from a piston which can be allowed to freely descend on a close fitting cylinder filled with oil. This is specially designed to provide a constant rate of descent and provide time base for analyzing the trace.

An angular transducer of resolution less than 1 degree is also attached by a belt drive to flywheel and can record the amplitude time trace on the PC and frequency and logarithmic decrement are analyzed and displayed on the computer.
8. The application software The optical sensor provides frequency of vibration on the digital display.
- Using the optical sensor the frequency of oscillation of pendulums and spring-mass system can be seen on digital display as well as on computer.
- Using the optical sensor, the frequency of excitation can be obtained on the display and on computer.
- Using the linear displacement transducer, the vibration trace can be obtained on the computer, from which amplitude of force vibration, logarithmic decrement of amplitude in free vibration, natural frequency of free vibration and frequency of force vibration can be obtained on the application software.
- Using the angular displacement transducer, angular vibration trace of single rotor free torsional oscillation and single rotor damped free vibration, from which amplitude of force vibration, logarithmic decrement of amplitude in free vibration and natural frequency of free vibration can be obtained on the application software.
9. Instruction Manual
A full technical manual is supplied with the apparatus. This describes the equipment and separately details each experiment. Typical test results are shown. The manual includes photographs of each experiment with all the component parts labeled to assist assembly.

Features
1. simple and compound gear trains
2. acceleration of geared system
3. mechanical efficiency of geared system
4. mass moment of inertia of geared system
5. Includes a dynamometer and comprehensive control and instrumentation unit

Description
Comprehensive range of experiments on geared systems can be done on this apparatus. Students can study the simple and compound gear trains. Using the acceleration of geared system, the comparison of theoretical and experimentally determined mass moments of inertia can be made. The mechanical efficiency of geared systems can be determined

The apparatus consists of a gear box with three shafts supporting the gears. A variable speed motor with electronic control and display unit operates as a variable speed drive. An electronic load cell measures input torque. A simple prone brake loads the gear unit and measures the output torque. To accelerate the system, a falling mass is used. A sensor measures the center shaft position, velocity and acceleration. The appara tus includes interlocks and guards for safet

The unit can operate stand alone without computer as well as with computer software. With a PC, the software can display the data and record the data in sequence and can display graph of gear acceleration.

Range of Experiments
1. Mechanical Efficiency of a Geared System: simple and compound trains
2. The Effect of Speed on the Mechanical Losses and Efficiency of a Geared System
3. Acceleration of a Gear System
4. Inertias of a Geared System

Features

Demonstrates relationship between gyroscopic torque, disk speed and rate of precession

Disk speed is variable and reversible

Portable and suitable for classroom demonstrations as well as use by students in the laboratory

Moment of inertia of the gyroscope disk and motor armature determined experimentally

Operates from safe low voltage supply; low voltage DC motor

Description
The Gyroscope TM05 is well designed to demonstrate the phenomena of gyroscope. The gyroscope consists of a disk that can be rotated by a DC motor and its speed is adjustable and reversible. A movable counter weight balances the disk. The small counter weight is used to make fine adjustments to the balance. An add-on-mass can be easily placed on the end of the shaft to cause a torque and precession. The rotational inertia of the disk is easily obtained by accelerating the disk using a string around the pulley that is attached to the disk.

Range of Experiments
1. Determination of the relationship between gyroscopic torque, rotational speed and rate of precession for a rotating mass of given polar moments of inertia.
2. Demonstration of Precession
3. Demonstration of Nutations

Description
The TM05A Model Gyroscope has an open design that makes all the parts easily accessible to the student. The gyroscope consists of a disk that can be rotated by hand or by pulling a string that is wrapped around the pulley. A movable counterweight balances the disk. The small counterweight is used to make fine adjustments to the balance. An add-on mass can be easily placed on the end of the shaft to cause a torque and precession. The rotational inertia of the disk is easily obtained by accelerating the disk using a string around the pulley that is attached to the disk. All basic gyroscopic phenomena can be demonstrated convincingly with this simple equipment.

A complete instruction manual is provided describing the apparatus, its application, experimental procedure and typical test results.

Experiments
To demonstrate visually precession and stability of a gyroscope, and to assess the effect of direction of spin and speed of rotation

Features
1. Demonstrate the working principle of different centrifugal force governors.
2. Determination of the characteristic curves of different centrifugal force governors

Description
A motor drive is used to rotate the governor provided and speed is controlled through the electronic controller with digital tachometer. Masses and sleeve forces can be varied with the accessories provided in a tool box.

The stroke can be measured using the marks on the governor shaft. When in operation, a transparent protective lid covers the rotating centrifugal governor. The unit can only be placed in operation if the lid is correctly fitted. The apparatus is designed with the following
specifications and features:
1. 3 types of governor provided.
- Porter Governor – 1 unit
- Proell Governor – 1 unit
- Hartnell Governor – 1 unit
2. DC drive motor 40W, 24V
3. Rotational Speed: 60 to 400 rpm, electronic control with digital display

Experiments
1. Determination of characteristic curves of sleeve position against speed of rotation.
2. Derivation of actual controlling force curve from its characteristics and comparison with theoretically predicted controlling force curve.
3. Comparison of governor types (Porter governor, Proell governor and Hartnell governor) in terms of sensitivity, stability and governing effort.

Features
Computerized static and dynamic balancing apparatus can gain students the experiences with 5 types of balancing, namely:
1. Static balancing
2. Single transverse plane dynamic balancing
3. Single axial plane dynamic balancing
4. Single axial plane unbalance couple dynamic balancing
5. Multiple transverse and axial planes dynamic balancing
6. Static Couple Method for balancing of unknown unbalance (real case)

Description
The static and dynamic balancing apparatus has been designed to provide means for accurate experimental work in the balancing of rigid rotors. The design of the apparatus adheres to industrial practice and the apparatus can be used to balance real rotors of up to 200 mm diameter and 200 mm long in addition to four disc rotor provided.

The main feature of the apparatus is that the cradle, in which the rotor to be balanced is supported, has only one degree of freedom at two bearing supports. The magnitude of the out-of-balance force and/or moment are obtained from the amplitude and phase at two bearings.

In an experiment the four-disc rotor is used with an arbitrary but known out-of-balance system of masses added to the center two discs and the results for the balancing masses required on the outer two discs are compared with those obtained theoretically.

The static couple method used in the industrial balancing machine has been employed graphically to solve the real case of unknown unbalance. For the rotor to be balanced the location and magnitude of unbalance mass is unknown. Making the runs with trail weights and then the required balance weights and location of balance weights have been found graphically by plotting the vectors. By repeating this procedure, the rotor is finally balanced to the required grade.

Using the velocity transducer instead of acceleration transducer, the grade of unbalance is obtained directly. The four-disc rotor is balanced to balancing grade 2.5 before shipment.

Range of Experiments
1. Static balancing of single plane unbalance and multi-plane unbalance
2. Dynamic balancing of single transverse plane unbalance
3. Dynamic balancing of single axial plane unbalance
4. Dynamic balancing of statically balanced rotor with unbalance dynamic couple
5. Dynamic balancing of multiple transverse and multiple axial planes unbalance
6. Static couple method: explains by vectors on graph the way industrial balancing machine works

Features
Centrifugal Force Apparatus is designed to verify that centrifugal force varies with the square of the speed, the rotating mass. A unique feature is that all two variables can be set and the centrifugal force directly read from the load cell displayed on the (ontrol and Display board or on the computer display. (Computer not shown in the picture) Also speed is also displayed on the (ontrol and Display board as well as on the computer.

Descriptions
The apparatus consists of a turntable carrying two pairs of masses mounted on radius rods and linkage so that the centripetal force is measured using load cell under the turntable. A similar pair of radius rods beneath the turntable compensate for any force due to the rods themselves. For experimental work the mass, radius of gyration and speed can be varied. The masses, which may be separated to show the effect of equivalent mass, can be fixed at any radius from 25 to 125 mm along the graduated radius rods. The centrifugal force and speed can be read directly on the Control and Display Box or can be read on the computer display.

Range of Experiments
1. To verify that the centrifugal force on a rotating mass is proportional to the:
- square ofthe speed
- mass
2. To compare the experimental results with those calculated from theory

Features
Demonstration the relationship between load and deformation on tension springs and compression spring

Description
The wall unit enables the changes in the length of springs to be determined for varying loads. The unit consists of a base plate to which a holder for springs is fitted. Each of the tension springs can be loaded using a hook with the aid of a weight. Compression springs are checked using a compression bar. The change in length is read at a pointer running along a millimeter scale.

Range of Experiments
1. Tension spring characteristic curve
2. Compression spring characteristic curve
3. Determination of the spring stiffness

Features
Journal bearing friction
Different bearing materials
Comparison with roller bearing friction

Description
The apparatus allows determination of friction moments in journal and roller bearings. Friction moments can be measured and comparisons made between different bearing designs. It is also possible to perform experiments on the dynamics of rotation. A roller bearing pair is also provided as an alternative mounting.

Range of Experiments
1. Determining the friction moments on journal bearings
2. Determining the friction moment on a roller bearing
3. Comparison between journal and roller bearings
4. Experiments on the fundamentals of rotational dynamics

Description
A steel disc 250 mm diameter and 30 mm thick is mounted on a shaft running in ball bearings housed on a substantial wall bracket. A mark on the flywheel and a pointer on the bracket enable the revolutions to be counted and timed with the stop watch supplied. A cord, load hanger and set of weights are provided. The moment of inertia can be altered by the addition of a disc and a ring of similar masses. A vibrating arm provides an accurate means of measuring acceleration, drawing a simple harmonic curve at a frequency of 5Hz onto a strip of paper attached to the flywheel periphery. This is actuated automatically as the flywheel starts to rotate.

A complete instruction manual is provided describing the apparatus, its application, experimental procedure and typical test results

Experiments
- To verify the second law of motion applied to a flywheel, ie the relationship between torque and angular accerleration
- To compare experimental and calculated moments of inertia of a disc
- To study the energy transformations and to demonstrate that a flywheel can be used to store energy
- To observe the effect of a change in moment of inertia

DescriptionDetail
Much of the design of parts in mechanical and civil engineering is complicated by there being biaxial or triaxial stresses for which some failure state has to be determined. Obvious examples are high pressure cylinders containing liquids or gases and concrete hinges for large bridge bearings. For more than a century, physicists, mathematicians and engineers have been proposing various theories of failure. Some theories have been attempts to explain observed failures while a few have tried to base a mechanism on fundamental properties of materials.

It is evident that there is a considerable difference between the behaviour of ductile and brittle materials. That apart, it is quite difficult to determine failure with sufficient accuracy in experiments designed to show which failure theory is most applicable. Hence, it is frequently found that codes of practice lay down what appears to be a somewhat empirical design method which experience has proved to be workable.

This simple machine uses inexpensive test specimens made from round bar. The specimen is clamped at one end to the base bracket and at the other to a counterbalanced circular loading plate. This plate is graduated in 15° intervals. A special hanger enables pure bending, pure torque or combined loads to be applied depending on the position of the plate. The specimen deflection is measured by a dial gauge mounted diametrically opposite the load point. In the event of a specimen failure safety is ensured by set screws.

A complete instruction manual is provided describing the apparatus, its application, experimental procedure and typical test results.

Experiments

To determine elastic failure of a specimen subjected to several ratios of bending and torsion simultaneously

To compare the results with the established theories of failure

Description
The apparatus shows the relationship between crank shaft rotation and piston displacement, for a fixed "cylinder". The crank length is adjustable,and the connecting rod length can be varied. Crankshaft rotation is measured by a rotating protractor scale and piston displacement is shown on asliding scale.

The equipment may be mounted vertically for demonstration purposes, or flat on the bench for experimental use. A complete instruction manual is provided describing the apparatus, its application, experimental procedure and typical test results.

Experiments
- To determine the relationship between crank angle and stroke
- To study the effect of changing the a) crank radius b) connecting rod length
- To investigate by graphical differentation the relationship between angular and linear speeds and accelerations of the mechanism
- To construct velocity and acceleration diagrams for the mechanism
- Comparison of experimental results with theoretical predictions

Features
Demonstration of moment equilibrium

Description
The apparatus demonstrates the laws on the formation of an equilibrium of moments in static systems. Two pulleys made of anodized aluminum with different radii are fitted to a steel shaft mounted on ball bearings. Easy to change weight discs can be hung on cords placed around the pulleys. In this way it is possible to make changes to the peripheral force on the pulleys. The anodized aluminum base plate is intended for wall mounting.

Range of Experiments
The equilibrium of moments

Description
This TM30 Noise Control Demonstration Unit let us perform experiment on noise and vibration control such as attenuation of a mechanical or aerodynamic noise source. The TM 30 consist of a glass reinforce plastic instrument panel and control panel are attached on the same baseboard. There are two noise sensor ;(i) a motor and gearbox (ii) a dc fan. Both a motor and gearbox with detachable eccentric rotor and a12 v dc fan may be fixed to resilient mounts attached to the baseboard. Resilient mounting and mount by pass equipment allows experiment of modes of vibration at various frequencies and transmission of noise through solids. A rigid glass reinforced plastic enclosure may be placed over either of the noise sourced both with and without an absorbent acoustic lining.

Range of experiment
1. Attenuation of a mechanical or aerodynamic noise source using a rigid enclosure and combining this with a sound absorber lining.
2. The rapid degeneration in effectiveness of the above enclosure method due to minor imperfections in construction
3. The transmission of noise along duct and method of attenuation using sound absorber linings.
4. The transmission of noise along solid paths and the method of reduction by isolation.
5. The effect of the noise frequency on the effectiveness of attenuation methods
6. Rigid body modes of vibration of a resiliently mounted source and the effects of mass variation on the resonant frequencies and modes of vibration