MODEL QUESTION PAPER (CIE) | MACHINE DESIGN | V- Semester Diploma Examination | DIPLOMA 5th and 6th Semester



 MACHINE DESIGN

 

 

V- Semester Diploma Examination

MACHINE DESIGN

Time: 3 Hours]

Note: Answer all questions

[Max Marks: 100

PART-A

1

List the general Considerations in machine design

5

2

Explain man-machine joint system

5

3

List with examples five basic forms for shape of product

5

 

PART-B

 

4- a

List the different types of riveted joints and rivets.

5

B

Two plates of 10 mm thickness each are to be joined by means of a single

 

 

riveted   double    strap butt joint. Determine the rivet diameter; rivet pitch,

15

 

strap thickness and efficiency of the joint. Take the working stresses in

 

 

tension and shearing as 80 MPa and 60 MPa respectively.

 

 

OR

 

4- a

b

Discuss the stresses induced in the Screw fasteners when it is subjected to static loading.

The cylinder head of a steam engine is subjected to a steam pressure of 0.7 N/mm2. It is held in position by means of 12 bolts. A soft copper gasket is

5

 

15

 

used to make the joint leak-proof. The effective diameter of cylinder is

 

 

300 mm. Find the size of the bolts so that the stress in the bolts is not to

 

 

exceed 100 MPa.

 

5- a

Explain the effect of keyway cut into the shaft.

Select the diameter of a solid steel shaft to transmit 20kw at 200 rpm. The ultimate shear stress for the steel may be taken as 360mpa and factor of safety as 8. If a hallow shaft is to be used in place of solid shaft , finds the inside and outside diameter when the ratio of inside to outside is 0.5.

OR

Explain how the shafts are designed when it is subjected to twisting moment only on stiffness/strength basis.

Select the diameter of a solid steel shaft for a pair of wheels of a railway wagon carries a load of 50KN on each axle box acting at a distance of 100mm outside the wheel base. The gauge of the rails is 1.4 m ,if the  stress is not to exceed 100Mpa.

5

b

 

 

15

 

5- a

b

 

 

5

 

15

6- a

Explain the applications of spring

Design a close coiled helical compression spring for a service load ranging from 2250 N to 2750 N. The axial deflection of the spring for the load range is 6 mm. Assume a spring index of 5. The permissible shear stress intensity is 420 MPa and modulus of rigidity, G = 84 kN/mm2. Neglect the effect of stress concentration.

OR

Classify the springs.

5

b

 

 

15

 

6- a

 

 

5

 

 

Design the spring for the buffers of a rail wagon of mass 20 tonnes is

8


b

moving with a velocity of 2 m/s. It is brought to rest by two buffers with springs of 300 mm diameter. The maximum deflection of springs is 250 mm. The allowable shear stress in the spring material is 600 MPa.

15

PART C

7

Design a knuckle joint to connect two mild steel bars under a tensile load of 25 kN. The allowable stresses are 65 MPa in tension, 50 MPa in shear and 83 MPa in crushing.

.

OR

Design a rigid flange coupling to transmit a the torque of 250 N-m between two coaxial shafts. The shaft is made of alloy steel, flanges out of cast iron and bolts out of steel. Four bolts are used to couple the flanges. The shafts are keyed to the flange hub. The permissible stresses are given below: Shear stress on shaft =100 MPa

Bearing or crushing stress on shaft =250 MPa Shear stress on keys =100 MPa

Bearing stress on keys =250 MPa Shearing stress on cast iron =200 MPa Shear stress on bolts =100 MPa

25

 

 

8

 

 

25

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 



 

 

 

 

Text Box: MODEL QUESTION BANK

V- Semester Diploma Examination

 MACHINE DESIGN

 

Note: The paper setter is of liberty to set the questions on his/her desecration based on cognitive levels notified for that unit. They have to follow only blue print of SEE question paper format. The model question bank is only for reference to students/course coordinator to initiate the process of teaching-learning only.

Text Box: CO-1: Understand the concept of design and behavior of material under varying load conditions, Use of design data books while designing machine components

 

Text Box: Remember

1)  Define machine Design.

2)  List out the classification of machine design.

3)  List general considerations in machine design.

4)  Define the following terms a) Load b) Stress c) strain

6)   Define factor of safety.

7)   Recall the equation for bending.

8)   Recall the equation for Torsion.

9)   List the various factors to be considered in deciding the factor of safety.

10)   Label the salient features of stress- strain diagram for mild steel.

11)   List the different types of failure theories.

Text Box: CO-2: Design of bolts, nuts, and riveted joints subjected to direct stresses and analyze the type of stresses induced under different load conditions

 

Text Box: Remember

1.  Define fastener.

2.  Define Riveted joint.

3.  List the different types of riveted joints and rivets.

4. 

Text Box: Understanding

Define efficiency of riveted joint.

1.  Classify the fasteners.

2.  Compare Bolt, stud and Nut.

3.  Explain bolt of uniform strength. Where it is preferably used.

4.  Explain the stresses induced in the Screw fasteners when it is subjected to static loading.

5.  Interpret the reasons for “Initial tightening of bolts is essential”.

6.  Interpret the reasons for “Excessive tightening of bolts is avoided”.

7.  Explain the necessity of riveted joint.


8.  List the applications of riveted joint in modern equipments.

9.   Explain the types of failures in riveted joint with sketch.

 


 

1.               A steam engine cylinder has an effective diameter of 350 mm and the maximum steam pressure acting on the cylinder cover is 1.25 N/mm2. Calculate the number and size of studs required to fix the cylinder cover, assuming the permissible stress in the studs as 33 MPa.

 

2.                    A mild steel cover plate is to be designed for an inspection hole in the shell of a pressure vessel. The hole is 120 mm in diameter and the pressure inside the vessel is 6 N/mm2. Design the cover plate along with the bolts. Assume allowable tensile stress for mild steel as 60 MPa and for bolt material as 40 MPa.

 

3.              The cylinder head of a steam engine is subjected to a steam pressure of 0.7 N/mm2. It is held in position by means of 12 bolts. A soft copper gasket is used to make the joint leak- proof. The effective diameter of cylinder is 300 mm. Find the size of the bolts so that the stress in the bolts is not to exceed 100 MPa.

 

4.            An eye bolt is to be used for lifting a load of 60 kN. Find the nominal diameter of the bolt, if the tensile stress is not to exceed 100 MPa. Assume coarse threads.

 

5.             Determine the safe tensile load for bolts of M 20 and M 36. Assume that the bolts are not initially stressed and take the safe tensile stress as 200 MPa.

 

6.             An eye bolt carries a tensile load of 20 kN. Find the size of the bolt, if the tensile stress is not to exceed 100 MPa..

 

7.               An engine cylinder is 300 mm in diameter and the steam pressure is 0.7 N/mm2. If the cylinder head is held by 12 studs, find the size. Assume safe tensile stress as 28 MPa.

Text Box: B. Problems on rivets Applications/evaluating/creating

 

1.  A double riveted lap joint with zig-zag riveting is to be designed for 13 mm thick plates. Assume σt = 80 MPa ; τ = 60 MPa ; and σc = 120 MPa. State how the joint will fail and find the efficiency of the joint.

 

2.  Two plates of 10 mm thickness each are to be joined by means of a single riveted double strap butt joint. Determine the rivet diameter; rivet pitch, strap thickness and efficiency of the joint. Take the working stresses in tension and shearing as 80 MPa and 60 MPa respectively.


3.   Design a double riveted butt joint with two cover plates for the longitudinal seam of a boiler shell 1.5 m in diameter subjected to a steam pressure of 0.95 N/mm2. Assume joint efficiency as 75%, allowable tensile stress in the plate 90 MPa ; compressive stress 140 MPa

; and shear stress in the rivet 56 MPa.

 

4.   A single riveted lap joint is made in 15 mm thick plates with 20 mm diameter rivets. Determine the strength of the joint, if the pitch of rivets is 60 mm. Take σt = 120 MPa; τ = 90 MPa and σc = 160 MPa.

 

5.  Two plates 16 mm thick are joined by a double riveted lap joint. The pitch of each row of rivets is 90mm. The rivets are 25 mm in diameter. The permissible stresses are as +follows: σt = 140 MPa ; τ = 110 MPa and σc = 240 MPa Find the efficiency of the joint.

 

6.   A single riveted double cover butt joint is made in 10 mm thick plates with 20 mm diameter rivets

with a pitch of 60 mm. Calculate the efficiency of the joint, if σt = 100 MPa ; τ = 80 MPa and σc = 160 MPa.

 

7.   A double riveted double cover butt joint is made in 12 mm thick plates with 18 mm diameter rivets. Find the efficiency of the joint for a pitch of 80 mm, if σt = 115 MPa ; τ = 80 MPa and σc = 160 MPa.


1)  Explain the effect of keyway cut into the shaft.

2)  List the reasons for rectangular keys are preferred over square keys.

3)  Explain how the shafts are designed when it is subjected to twisting moment only on stiffness/strength basis.

4)  Explain how the shafts are designed when it is subjected to Bending moment only on stiffness/strength basis.

5)  Explain how the shafts are designed when it is subjected to combined twisting moment and bending moment on stiffness/strength basis.

6)  List the properties of materials used for shafts.

7)  Classify Sunk keys.

8)  List he standard sizes of Transmission shafts.

9)  Explain how the shafts are designed on Rigidity basis.

 


 

1)  Select the diameter of the shaft for a mild steel rotating at 200 rpm, transmiting  20kW with a allowable shear stress of 42MPa.


2)  Select the diameter of the shaft for a mild steel rotating at 240rpm, is transmitting 1 MW The maximum torque transmitted exceeds the mean torque by 20%. The allowable shear stress as 60mpa.

3)  Select the diameter of a solid steel shaft to transmit 20kw at 200 rpm. The ultimate shear stress for the steel may be taken as 360mpa and factor of safety as 8. If a hallow shaft is to be used in place of solid shaft , finds the inside and outside diameter when the ratio of inside to outside is 0.5.

4)  Select the diameter of a solid steel shaft for a pair of wheels of a railway wagon carries a load of 50KN on each axle box acting at a distance of 100mm outside the wheel base. The gauge of the rails is 1.4 m ,if the stress is not to exceed 100Mpa.

5)  Select the diameter of a solid steel shaft is subjected to bending moment of 3000N-m and  a torque of 10000N-m. The shaft is made of 45 c 8 steel having ultimate tensile stress of 700Mpa and Ultimate shear stress of 500Mpa. Assuming factor of safety as 6.

6)  Select the diameter of a solid steel shaft made of mild steel is required to transmit 100 kW at 300 r.p.m. The supported length of the shaft is 3 metres. It carries two pulleys each weighing 1500 N supported at a distance of 1 metre from the ends respectively. Assuming the safe value of stresses

7)  Select the diameter of a solid steel shaft by considering two different theories of failure made of steel of yield strength 700 MPa is subjected to static loads consisting of a bending moment of 10 kN-m and a torsional moment of 30 kN-m. and assuming a factor of safety of 2.

8)    Choose the outside and inside diameter of a hollow steel shaft transmits 600 kW at 500

r.p.m. The maximum shear stress is 62.4 MPa. The outer diameter is twice of inside diameter, assuming that the maximum torque is 20% greater than the mean torque.


1)   Recommend the rectangular key for a shaft of 50 mm diameter. The shearing and

crushing stresses for the key material are 42 MPa and 70 MPa.

 

2)    Recommend the required length of key, if the shaft is loaded to transmit the maximum permissible torque. Use maximum shear stress theory and assume a factor of safety of 2 for a 45 mm diameter shaft is made of steel with a yield strength of 400 MPa. A parallel key of size 14 mm wide and 9 mm thick made of steel with a yield strength of 340 MPa is to be used.

3)   A 15 kW, 960 r.p.m. motor has a mild steel shaft of 40 mm diameter and the extension being 75 mm. The permissible shear and crushing stresses for the mild steel key are 56 MPa and 112 MPa. Design the keyway in the motor shaft extension. Check the shear strength of the key against the normal strength of the shaft.

 

4)   Select the length of a 20 mm wide key required to mount a pulley on the shaft so that the stress in the key does not exceed 42MPa. A shaft 80 mm diameter transmits power at maximum shear stress of 63 MPa.


5)   Select the dimensions of the key so that A shaft 30 mm diameter is transmitting power at a maximum shear stress of 80 MPa. If a pulley is connected to the shaft by means of a key, the stress in the key is not to exceed 50 MPa and length of the key is 4 times the width.

 

6)   Select a suitable key for the gear having a steel shaft has a diameter of 25 mm. The shaft rotates at a speed of 600 r.p.m. and transmits 30 kW through a gear. The tensile and yield strength of the material of shaft are 650 MPa and 353 MPa respectively. Take a factor of safety 3. Assume that the key and shaft are made of the same material.

Text Box: CO-4: Design of machine element like Solid Muff Coupling- flange coupling subjected to direct and twisting moments and Knuckle joint-Cotter joint subjected to direct stress and analyze the various modes of failure(with numeric examples)

 

 Apply/ Analysis                                                                                                     

 

 

  Muff coupling                                                                                                     

 

1)  Design a muff coupling which is used to connect two steel shafts transmitting 40 kW at 350 r.p.m. The material for the shafts and key is plain carbon steel for which allowable shear and crushing stresses may be taken as 40 MPa and 80 MPa respectively. The material for the muff is cast iron for which the allowable shear stress may be assumed as 15 MPa.

2)   Design a muff coupling to connect two shafts transmitting 40 kW at 120 r.p.m. The permissible shear and crushing stress for the shaft and key material (mild steel) are 30 MPa and 80 MPa respectively. The material of muff is cast iron with permissible shear stress of 15 MPa. Assume that the maximum torque transmitted is 25 per cent greater than the mean torque.

 

1)   Design a cast iron protective type flange coupling to transmit 15 kW at 900

r.p.m. from an electric motor to a compressor. The service factor may be assumed as 1.35. The

Following permissible stresses may be used :

Shear stress for shaft, bolt and key material = 40 MPa Crushing stress for bolt and key = 80 MPa

Shear stress for cast iron = 8 MPa

2)   Design a protective type of cast iron flange coupling for a steel shaft

transmitting 15 kW at 200 r.p.m. and having an allowable shear stress of 40 MPa. The working stress in the bolts should not exceed 30 MPa. Assume that the same material is used for shaft and key and that the crushing stress is twice the value of its shear stress. The maximum torque is 25% greater than the full load torque. The shear stress for cast iron is 14 MPa.


3)   Design a cast iron flange coupling for a mild steel shaft transmitting 90 kW at 250 r.p.m. The allowable shear stress in the shaft is 40 MPa and the angle of twist is not to exceed 1° in a length of 20 diameters. The allowable shear stress in the coupling bolts is 30 MPa.

4)    Design a rigid flange coupling to transmit a torque of 250 N-m between two coaxial shafts. The shaft is made of alloy steel, flanges out of cast iron and bolts out of steel. Four bolts are used to couple the flanges. The shafts are keyed to the flange hub. The permissible stresses are given below:

Shear stress on shaft =100 MPa

Bearing or crushing stress on shaft =250 MPa Shear stress on keys =100 MPa

Bearing stress on keys =250 MPa Shearing stress on cast iron =200 MPa Shear stress on bolts =100 MPa

 

5)   Two 35 mm shafts are connected by a flanged coupling. The flanges are fitted with 6 bolts on 125 mm bolt circle. The shafts transmit a torque of 800 N-m at 350 r.p.m. For the safe stresses mentioned below, calculate 1. diameter of bolts ; 2. thickness of flanges ; 3. key dimensions ;4. hub length; and 5. power transmitted.

Safe shear stress for shaft material = 63 MPa Safe stress for bolt material = 56 MPa

Safe stress for cast iron coupling = 10 MPa Safe stress for key material = 46 MPa


 

 

1.   Design a cotter joint to connect two mild steel rods for a pull of 30 kN. The maximum permissible stresses are 55 MPa in tension; 40 MPa in shear and 70 MPa in crushing. Draw a neat sketch of the joint designed.

2. Two rod ends of a pump are joined by means of a cotter and spigot and socket at the ends. Design the joint for an axial load of 100 kN which alternately changes from tensile to compressive. The allowable stresses for the material used are 50 MPa in tension, 40 MPa in shear and 100 MPa in crushing.

 

3.  Two mild steel rods 40 mm diameter are to be connected by a cotter joint. The thickness of the cotter is 12 mm. Calculate the dimensions of the joint, if the maximum permissible stresses are: 46 MPa in tension ; 35 MPa in shear and 70 MPa in crushing.

 

4.   Design a cotter joint to support a load varying from 30 kN in compression to 30 kN in tension. The material used is carbon steel for which the following allowable stresses may be used. The load is applied statically. Tensile stress = compressive stress 50 MPa ; shear stress 35 MPa and crushing stress= 90 MPa.


 

1.  Design a knuckle joint to transmit 150 kN. The design stresses may be taken as 75 MPa in tension, 60 MPa in shear and 150 MPa in compression.

2.  Design a knuckle joint for a tie rod of a circular section to sustain a maximum pull of 70 kN. The ultimate strength of the material of the rod against tearing is 420 MPa. The ultimate tensile and shearing strength of the pin material are 510 MPa and 396 MPa respectively. Determine the tie rod section and pin section. Take factor of safety = 6.

3.  Design a knuckle joint to connect two mild steel bars under a tensile load of 25 kN. The allowable stresses are 65 MPa in tension, 50 MPa in shear and 83 MPa in crushing.

4.   A knuckle joint is required to withstand a tensile load of 25 kN. Design the joint if the permissible stresses are :σt = 56 MPa ; τ = 40 MPa and σc = 70 MPa.

Text Box: CO-5: Design procedure of machine elements subjected to twisting moment and analyzes the type of stresses induced in them

 

  Remember                                                                                                     

1) List the applications of spring

3)  List materials used in Springs.

4)  Define the terms used in springs.

5)  Name the springs used in a) Spring balance b)Ball Pen c) Door Hinges d) Truck Chassis e)Clock

  Understand                                                                                                     

1)  Classify the springs.

2)  Explain the significance of Whal’s factor

3)  Expline the applications of spring

4)  List the materials used in Springs.

 

 Problems on springs

 

 Apply/ Analysis                                                                                                     

 

1)      Design a close coiled helical compression spring for a service load ranging from 2250 N to 2750 N. The axial deflection of the spring for the load range is 6 mm. Assume a spring index of 5. The permissible shear stress intensity is 420 MPa and the modulus of rigidity, G = 84 kN/mm2. Neglect the effect of stress concentration.

 

2)      Design and draw a valve spring of a petrol engine for the following operating conditions: Spring load when the valve is open = 400 N

Spring load when the valve is closed = 250 N Maximum inside diameter of spring = 25 mm Length of the spring when the valve is open= 40 mm

Length of the spring when the valve is closed= 50 mm Maximum permissible shear stress = 400 MPa

 

3)      Design the spring for the buffers of a rail wagon of mass 20 tonnes is moving with a velocity of 2 m/s. It is brought to rest by two buffers with springs of 300 mm diameter. The


maximum deflection of springs is 250 mm. The allowable shear stress in the spring material is 600 MPa.

4)      Design a helical compression spring for a maximum load of 1000 N for a deflection of 25 mm using the value of spring index as 5. The maximum permissible shear stress for spring wire is 420 MPa and modulus of rigidity is 84 kN/mm2,with considering whal’s factor.

Text Box: CO-6: Know the Principles of design as per ergonomic, and Environmental considerations

 

 

  Remember                                                                                                     

 

1)             Define Ergonomics.

2)             List with examples five basic forms for the shape of the Product.

3)             List the types of controls.

4)             List the types of Display.

  Understand                                                                                                     

1)   Explain the relationship between functional requirements and the external appearance of the Product.

2)   Explain the scope of ergonomics in product design.

3)   Explain the meaning of different colors as per the morgan’s code.

4)   Explain the man-machine joint system.

5) Explain the ergonomics considerations in the design of controls.

6)   Explain the ergonomics considerations in the design of the Display.


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