Chapter 3. Mechanics of Deformable Bodies
Chapter 3. Mechanics of Deformable Bodies
Chapter 3. Mechanics of Deformable Bodies
Module
In
ES 107A
MECHANICS OF DEFORMABLE
BODIES
Module No. 3
Ryan A. Limco
Instructor II
Table of Contents
Content Page
Title Page 1
Table of Contents 2
Instruction to User 3
Introduction 4
Chapter 3
Torsion 5
Overview 5
Learning Outcomes 5
Pretest 6
Lesson 1: Torsion 7
Specific Learning Outcome 7
Time Allotment 7
Discussion 7
1.1 Torsion 7
1.2 Torsional Shearing Stress 8
1.3 Angle if Twist 9
1.4 Power Transmitted by the Shaft 9
Lesson 2: Helical Spring 13
Specific Learning Outcome 13
Time Allotment 13
Discussion 13
2.1 Helical Spring 13
2.2 Spring in Series 14
2.3 Spring in Parallel 15
Activities/Exercises 20
References 21
INTRODUCTION
Chapter 3
Torsion
A. Overview
Module 3 covers Torsion. The module includes one lesson: Lesson 1 – Torsion,
and Lesson 2 – Helical Springs.
B. Learning Outcomes
Lesson 1
Torsion
C. Discussion
1.1 Torsion
Consider a bar to be rigidly attached at one end and twisted at the other end by a torque
or twisting moment T equivalent to F × d, which is applied perpendicular to the axis
of the bar, as shown in the figure. Such a bar is said to be in torsion.
𝑇 = 𝐹𝑑
𝜏= and 𝜏 =
where J is the polar moment of inertia of the section and r is the outer radius.
For solid circular shaft:
𝜏𝑟
𝜏 =
𝐽
Since 𝐽 = and 𝑟 =
𝟏𝟔𝑻
𝝉𝒎𝒂𝒙 =
𝝅𝑫𝟑
𝟏𝟔𝑻𝑫
𝝉𝒎𝒂𝒙 =
𝝅(𝑫𝟒 − 𝒅𝟒 )
1.3 Angle of Twist
The angle θ through which the bar length L will twist is
𝜃= in radians
Where: T is the torque in N·mm, L is the length of shaft in mm, G is shear modulus in
MPa, J is the polar moment of inertia in mm4, D and d are diameter in mm, and r is
the radius in mm.
answer
answer
Problem 2. What is the minimum diameter of a solid steel shaft that will not twist
through more than 3° in a 6-m length when subjected to a torque of 12 kN·m? What
maximum shearing stress is developed? Use G = 83 GPa.
Solution:
answer
answer
Solution:
Based on maximum shearing stress, τmax = 16T / πd3:
Steel
Aluminum
𝑃 4.5 𝑥 10 𝑊
𝑇= =
2𝜋𝑓 2𝜋(3 𝐻𝑧)
𝑇 = 238,732.41 𝑁 ∙ 𝑚
𝑑 = 289.71 𝑚𝑚
𝜋 (238,732.41𝑥10 𝑁 ∙ 𝑚𝑚)(26𝑑)
1° =
180° 1
𝜋𝑑 (83𝑥10 𝑀𝑃𝑎)
32
𝑑 = 352.08 𝑚𝑚
Lesson 2
Helical Spring
C. Discussion
The maximum shearing stress is the sum of the direct shearing stress 𝜏 = 𝑃/𝐴 and
the torsional shearing stress 𝜏 = 𝑇𝑟/𝐽, with 𝑇 = 𝑃𝑅.
𝜏=𝜏 +𝜏
𝑃 𝑇𝑟
𝜏= +
𝐴 𝐽
𝑃 16𝑃𝑅
𝜏= +
𝜋𝑑 /4 𝜋𝑑
𝟏𝟔𝑷𝑹 𝒅
𝝉= 𝟏 +
𝝅𝒅𝟑 𝟒𝑹
Note: This formula neglects the curvature of the spring. This is used for light spring
where the ratio is small.
For heavy springs and considering the curvature of the spring, R. A. M. Wahl
formula, a which is more precise, is used. It is given by:
𝟏𝟔𝑷𝑹 𝟒𝒎 − 𝟏 𝟎. 𝟔𝟏𝟓
𝜏= +
𝝅𝒅𝟑 𝟒𝒎 − 𝟒 𝒎
𝐷
𝑚=
𝑑
The elongation is
𝟔𝟒𝑷𝑹𝟑 𝒏
𝜹=
𝑮𝒅𝟒
Notice that the deformation 𝛿 is directly proportional to the applied load P. The ratio
P to 𝛿 is called the spring constant, k and is equal to
𝑷 𝑮𝒅𝟒
𝒌= = 𝑵/𝒎𝒎
𝜹 𝟔𝟒𝑹𝟑 𝒏
2.2 Spring in Series
For two or more springs with spring laid in series, the resulting spring constant k is
given by
𝟏 𝟏 𝟏
= + +⋯
𝒌 𝒌𝟏 𝒌𝟐
Where 𝑘 , 𝑘 , … are the spring constants for different spring.
2.3 Spring in Parallel
For two or more springs in parallel, the resulting spring constant is
𝒌 = 𝒌𝟏 + 𝒌𝟐 + ⋯
Where 𝑘 , 𝑘 , … are the spring constants for different spring.
𝑃𝐿
𝛿 =
𝐴𝐸
50,000 𝑁(500𝑚𝑚)
50𝑚𝑚 =
𝐴𝐸
𝐴𝐸 = 500,000 𝑁
𝑃𝐿
𝛿 =
𝐴𝐸
50,000 𝑁(250𝑚𝑚)
𝛿 =
500,000 𝑁
𝜹𝟐 = 𝟐𝟓 𝒎𝒎
16𝑃𝑅 𝑑
𝜏= 1+
𝜋𝑑 4𝑅
16𝑃 (75𝑚𝑚) 20 𝑚𝑚
140 = 1+
𝜋(20𝑚𝑚) 4(75𝑚𝑚)
𝑷𝟏 = 𝟐𝟕𝟒𝟗 𝑵
b. Load carried by outer spring:
16𝑃𝑅 𝑑
𝜏= 1+
𝜋𝑑 4𝑅
16𝑃 (100𝑚𝑚) 30 𝑚𝑚
140 = 1+
𝜋(30𝑚𝑚) 4(100𝑚𝑚)
𝑷𝟏 = 𝟔𝟗𝟎𝟒 𝑵
c. Maximum load that the spring could carry.
64𝑃𝑅 𝑛
𝛿=
𝐺𝑑
𝛿 =𝛿
Solution:
a. Maximum value of P.
16𝑃𝑅 4𝑚 − 1 0.615
𝜏= +
𝜋𝑑 4𝑚 − 4 𝑚
For the upper spring:
𝐷 200
𝑚= = =8
𝑑 25
16𝑃 (100) 4(8) 0.615
200 = +
𝜋(25) 4(8) − 4 8
𝑃 = 5182.29 𝑁
For the lower spring:
𝐷 150
𝑚= = = 7.5
𝑑 20
16𝑃 (75) 4(7.5) 0.615
200 = +
𝜋(20) 4(7.5) − 4 8
𝑃 = 3498.28 𝑁
Use 𝑷 = 𝟑𝟒𝟗𝟖. 𝟐𝟖 𝑵
b. Total Elongation
64𝑃𝑅 𝑛
𝛿=
𝐺𝑑
For the upper spring:
64𝑃𝑅 𝑛 64(3498.28)(100) (12)
𝛿 = = = 82.87 𝑚𝑚
𝐺𝑑 (83000)(25)
Problem 2.4 A Rigid plate of negligible mass rests on a central spring which is 20 mm
higher than the symmetrically loaded outer springs. Each of the outer springs consists
of 18 turns of 10 mm wire on a mean diameter of 100 mm. The central spring has 24
turns of 20 mm wire on a mean diameter of 150 mm. If a load P = 5 kN is now applied
to the plate, use G=83 GN/m2.
a. Determine the load carried by the central spring.
b. Determine the shearing stress of the central spring.
c. Determine the shearing stress of the outer spring.
Solution:
a. Load carried by the central spring:
𝛿 = 𝛿 + 20
64𝑃 𝑅 𝑛 64𝑃 𝑅 𝑛
= + 20
𝐺𝑑 𝐺𝑑
0.0488𝑃 = 0.1735𝑃 + 20
𝑃 = 826 𝑁
𝑃 + 2(826) = 5000
𝑷𝟏 = 𝟑𝟑𝟒𝟖 𝑵
16𝑃𝑅 𝑑
𝜏= 1+
𝜋𝑑 4𝑅
16(3348)(75) 30
140 = 1+
𝜋(20) 4(75)
𝑷𝟏 = 𝟏𝟕𝟎. 𝟓 𝑵
16𝑃𝑅 𝑑
𝜏= 1+
𝜋𝑑 4𝑅
16(826)(50) 10
140 = 1+
𝜋(10) 4(50)
𝑷𝟏 = 𝟐𝟐𝟎. 𝟗 𝑵
D. Activities/Exercises
Exercise 1:
Direction: Design a compound shaft attached to rigid support using bronze with G=35
GPa and allowable shear stress of 60 MPa, and Steel with G = 200 GPa and allowable
shear stress of 80 MPa. Assume different values of diameter for Bronze and Steel.
Compute for the ratio of the length of Steel to the length of Bronze so that each
material will be stressed to its maximum permissible limit. Give the reaction at the
supports, maximum torque carried by each material, and the maximum angle of twist.
Exercise 2:
Using 2 springs of different spring constants, wire diameter, mean radius, Modulus of
Rigidity, and turns, compute the maximum value of load and total deformation using
the following conditions: Concentric (Activity 2A), Series (Activity 2B) and Parallel
(Activity 2C). Note that each material has Constant values for Modulus of Rigidity.
F. References
Student’s Information
Name:
Program:
Year and Section:
Contact No.:
E-mail address:
Facebook Account:
Messenger Account:
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WPU-QSF-ACAD-82A Rev.
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