Download GTU (Gujarat Technological University) BE/BTech (Bachelor of Engineering / Bachelor of Technology) 2019 Summer 5th Sem New 2152509 Machine Dynamics Previous Question Paper
Seat No.: ________ Enrolment No.___________
GUJARAT TECHNOLOGICAL UNIVERSITY
BE - SEMESTER ?V (NEW) EXAMINATION ? SUMMER 2019
Subject Code: 2152509 Date: 03/06/2019
Subject Name: Machine Dynamics
Time: 02:30 PM TO 05:00 PM Total Marks: 70
Instructions:
1. Attempt all questions.
2. Make suitable assumptions wherever necessary.
3. Figures to the right indicate full marks.
Q.1 (a) Define and explain the term: (i)Piston effort and (ii)Crank effort 03
(b) Briefly explain a dynamically equivalent system? 04
(c) A single cylinder vertical engine has a bore of 300 mm and stroke of 400mm. The
connecting rod is 1 m long. The mass of the reciprocating parts is 140 kg. On the expansion
stroke with the crank at 30? from the top dead centre the gas pressure is 0.7 Mpa. If the
engine runs at 250 rpm , determine :
(i) net force acting on cylinder
(ii) Resultant load on gudgeon pin
(iii) Thrust on sides of cylinder walls.
07
Q.2 (a) Derive an expression for the correction torque to be applied to a crank shaft if the
connecting rod of a reciprocating engine is replaced by two lumped masses at the piston pin
and crank pin respectively.
07
(b) Explain the procedure to partially balance the primary forces in single cylinder engine. 07
OR
(b) Reciprocating parts of an inside cylinder locomotive are having a mass of 300 kg. The
distance between the two cylinders is 600 mm. the cranks are at 90? and are 0.3 m long. The
driving wheels have diameter of 2m and are 1.5 m apart. Revolving balancing masses are
introduced to balance two third of the reciprocating parts. Find the variation in tractive
effort and the value of variation in wheel reaction, when the locomotive is running at 110
kmph.
07
Q.3 (a) What will be the harm if the rotating parts of a high speed engine are not properly balanced? 03
(b) Prove that the maximum variation of tractive force is obtained when ?= 135?or 315? 04
(c) A number of masses are attached to a shaft which is rotating at an angular speed of ?
rad/sec. if all the masses are in same plane, then describe the graphical method to balance
these masses by a single mass only.
07
OR
Q.3 (a) State the types of vibrations and give at least one application of each. 03
(b) Derive the expression of natural frequency of two rotor torsional vibratory system. 04
(c) A shaft is rotating at uniform angular speed. Four masses m1 ,m2, m3, and m4 of magnitudes
300kg, 450kg, 360kg and 390kg respectively are attached rigidly to the shaft. The masses
are rotating in the same plane. The corresponding radii of rotation are 200 mm, 150 mm,
250 mm and 300 mm respectively. The angles made by these masses with horizontal are 0?,
45?, 120? and 255? respectively. Find magnitude and position of balancing mass if its radius
of rotation is 200 mm.
07
Q.4 (a) Discuss the effect of inertia of a shaft on free longitudinal vibration. 07
(b) Find the equation of motion for the system shown in figure below. 07
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Seat No.: ________ Enrolment No.___________
GUJARAT TECHNOLOGICAL UNIVERSITY
BE - SEMESTER ?V (NEW) EXAMINATION ? SUMMER 2019
Subject Code: 2152509 Date: 03/06/2019
Subject Name: Machine Dynamics
Time: 02:30 PM TO 05:00 PM Total Marks: 70
Instructions:
1. Attempt all questions.
2. Make suitable assumptions wherever necessary.
3. Figures to the right indicate full marks.
Q.1 (a) Define and explain the term: (i)Piston effort and (ii)Crank effort 03
(b) Briefly explain a dynamically equivalent system? 04
(c) A single cylinder vertical engine has a bore of 300 mm and stroke of 400mm. The
connecting rod is 1 m long. The mass of the reciprocating parts is 140 kg. On the expansion
stroke with the crank at 30? from the top dead centre the gas pressure is 0.7 Mpa. If the
engine runs at 250 rpm , determine :
(i) net force acting on cylinder
(ii) Resultant load on gudgeon pin
(iii) Thrust on sides of cylinder walls.
07
Q.2 (a) Derive an expression for the correction torque to be applied to a crank shaft if the
connecting rod of a reciprocating engine is replaced by two lumped masses at the piston pin
and crank pin respectively.
07
(b) Explain the procedure to partially balance the primary forces in single cylinder engine. 07
OR
(b) Reciprocating parts of an inside cylinder locomotive are having a mass of 300 kg. The
distance between the two cylinders is 600 mm. the cranks are at 90? and are 0.3 m long. The
driving wheels have diameter of 2m and are 1.5 m apart. Revolving balancing masses are
introduced to balance two third of the reciprocating parts. Find the variation in tractive
effort and the value of variation in wheel reaction, when the locomotive is running at 110
kmph.
07
Q.3 (a) What will be the harm if the rotating parts of a high speed engine are not properly balanced? 03
(b) Prove that the maximum variation of tractive force is obtained when ?= 135?or 315? 04
(c) A number of masses are attached to a shaft which is rotating at an angular speed of ?
rad/sec. if all the masses are in same plane, then describe the graphical method to balance
these masses by a single mass only.
07
OR
Q.3 (a) State the types of vibrations and give at least one application of each. 03
(b) Derive the expression of natural frequency of two rotor torsional vibratory system. 04
(c) A shaft is rotating at uniform angular speed. Four masses m1 ,m2, m3, and m4 of magnitudes
300kg, 450kg, 360kg and 390kg respectively are attached rigidly to the shaft. The masses
are rotating in the same plane. The corresponding radii of rotation are 200 mm, 150 mm,
250 mm and 300 mm respectively. The angles made by these masses with horizontal are 0?,
45?, 120? and 255? respectively. Find magnitude and position of balancing mass if its radius
of rotation is 200 mm.
07
Q.4 (a) Discuss the effect of inertia of a shaft on free longitudinal vibration. 07
(b) Find the equation of motion for the system shown in figure below. 07
2
OR
Q.4 (a) Prove that the ratio of two successive amplitudes in case of under-damped system is
constant.
07
(b) A spring-mass damper system has a mass of 3.43 kg, stiffness K as 343N/m and damping
coefficient C as 34.3N-sec/m. Determine the
(i) Natural frequency of damped vibration.
(ii) Natural frequency of the system if instead of viscous damping, dry friction
damping is present.
07
Q.5 (a) Explain the term: (i) damping factor, (ii) Co-efficient of damping and (iii) damped
frequency of vibratory system.
03
(b) What is isochronism in governor? Prove that a porter governor cannot be isochronous. 04
(c) A loaded porter Governor has four links each 250 mm long, two revolving masses each of
3kg and central dead-weight of mass 20kg. All the links are attached to respective sleeves at
radial distance of 40 mm from the axis of rotation. The masses revolve at a radius of 150
mm at minimum speed and at a radius of 200 mm at maximum speed. Determine the range
of speed.
07
OR
Q.5 (a) Derive an equation of motion for a simple spring-mass system using energy method. 03
(b) Differentiate between Governor and Flywheel. 04
(c) Describe the function of a Proell governor with the help of neat sketch. Establish a relation
among various forces acting on the bent link.
07
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This post was last modified on 20 February 2020