final project-of-exoskeleton-universiti-putra-malaysia-mechanical-student
TRANSCRIPT
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1 PROBLEM STATEMENT
Imagine spending days at a time hiking through the sweltering heat of the desert carrying heavy
backpacks and weaponry; Imagine loading two hundred pound missiles into aircraft and tanks
for hours. Exhaustion would quickly take over, diminishing the limits of the human body. These
are problems that military personnel face every day.
2 LITERATURE REVIEW
Military exoskeleton also known as powered exoskeleton, exoframe, or powered armor. The
main purposes of this exoskeleton are to support the wearer by increasing their endurance and
strength. This exoskeleton is controlled by using power motor system, hydraulic, pneumatics,
and electro-pneumatics. One of the main functions of military exoskeleton is to provide extra
support that enables a army to carry more weight. The military exoskeleton also can be used to
support firefighter and rescue squad in facing emergency situation. Nowadays, many big
countries in the world like United State (US), Germany, China and Japan try to develop the
military exoskeleton for their new power in military. For the example, the United State was
designed DARPA super-light exoskeleton and HULC exoskeleton.
The DARPA super-light exoskeleton was developed by Harvard’s Wyss Institute for Biological
Inspired Engineering, and received $2.9 million in development for DARPA. The HULC
exoskeleton is known as Lockheed Martin Human Universal Load Carrier/Berkeley Bionics. This
military exoskeleton could be a real benefit to the military field for the future.
The exoskeleton also designed for the medical use, heavy works in factory, and military use. For
the medical use, many exoskeletons was created like HAL (Hybrid Assistive Limb) the cyborg
robot from CYBERDYNE company to help people in the area of rehabilitation who suffer from
neuromuscular system, diseases of the brain, cerebrovascular diseases, traumatic brain injuries,
and spinal cord injuries, etc. The CYBERDYNE Company also manufactures HAL exoskeleton
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for non-medical use like welfare field, assistance for rescue activities on disasters site and heavy
work in factory.
The exoskeleton has limitations and design issues like a power supply, skeleton, actuators, and
power control and modulation. The exoskeleton was step up for walking, jumping and running
using more power supply. However, the power supply is one of the largest problem facing in
develop the exoskeleton. The power supply using nowadays is not sufficient energy density to
sustain a full-body powered exoskeleton for more than a few hours.
For the skeleton issues, before this the developers are commonly done using steel and aluminium
in exoskeleton project. But this material has a heavy weight and the exoskeleton must work harder
to overcome its own weight. Aluminium has light weight but it is easy to fail through fatigue. This
situation can give injury effect for the wearer. Some of the developers try to using other materials
like titanium to get some lightweight and strength but this material is more expensive to designed
exoskeleton.
3 OBJECTIVES
a) To create a soft and lightweight under-suit that protect wearers’ joint and helps increase
amount of weight a soldier can easily carry while using less energy and increase their
endurance.
b) To increase the strength and safety of the solder.
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4 MORPHOLOGY CHART
Table 1: Morphology chart
Option 1 Option 2 Option 3 Option 4 Option
5
1 Joint Movement
Method
Hydraulic Pneumatic electronic servomotor elastic
actuators
2 Joint
Connect/flexibiity
separate exterior
ball joint
hollow spherical
ball joint
A chain of external
ball joints
gasketed
hard shell
sections
joined with
free-
rotating
mechanical
bearings
suit
limbs
3 Suiting system Belt Sticky Clip Slider
4 Power source/energy
source
Internal
combustion
hydraulics engine
with electrical
system
Lithium ion
batteries
Electrochemical fuel
cells (SOFC: solid
oxide fuel cells)
Solar
5 Material (frame and
amour)
Titanium Carbon Fiber Steel Aluminum
6 Extra load picking
method/device
Back pack Clip/Hanger Clamp Waist pack
7 Exoskeleton balancer Gravity
balancing
Passive force
balancer
ZMP & CoP
9 Control system/ OS Based on
human
biological
signals
EMG
sEMG
PLC
PIC
Based on
human
non
biological
signals
Human
motion
using
sensor
Dynamic
model
Platform
independent
control
methods
Control
methods are
operates either
human
biological
signal or non-
biological
signal.
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5 CONCEPT GENERATION & CONCEPT SELECTION
5.1 EXOSKELETON BALANCER
Concept
A B C
Gravity
Balancing
Passive Force
Balancer
Zero Moment Point (ZMP) & Center of Pressure
(CoP)
Concept A and B are the concept to reduce weight of body acting on the wearer legs; Concept C
is avoid the wearer to fall down due to unbalance extra load carried.
Reference Model – Moon Walker
Figure 1: Moon Walker - a Lower Limb Exoskeleton able to Sustain Bodyweight using a Passive
Force Balancer
10 Sensors Force
sensor
Pressure
sensor
Ground
contact
sensor.
Muscle
sensor
fabric
bend
sensor
Angle
sensor
Gyroscope
sensor
Accelerometers
Bio electric
signal sensor.
5
Concept Screening
Table 2: Concept Screening for Exoskeleton Balancer
Concept Variants
Selection Criteria A B C Ref.
Ease of controlling - 0 + 0
Ease balancing - + + 0
Ease of safety + 0 0 0
System reliability - + + 0
Passivity + 0 - 0
Ease of
maintenance
+ 0 - 0
Ease of power
consumption
+ + 0 0
Pluses 4 3 3
Sames 0 4 2
Minuses 3 0 2
Net 1 4 1
Rank 3 1 2
Continue? No Yes Yes
No concept scoring required for the chosen Concept A and B because both concepts can balance
the exoskeleton from different aspect. Concept B is to balance the wearer weight with a constant
spring so that the body weight acting on both legs of the wearer can be reduce. Concept C is to
balance the whole exoskeleton (with wearer), so that it will not easy fall down sue to unbalance
from extra loading. As a result, implement both together can make the exoskeleton better.
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5.2 Exoskeleton Lower Part
The design of our exoskeleton suit is based on a few criteria. As for joint movement method,
joint connectivity, suiting system and the material used,the selection of the best option is by
using screening process. Table bellows the option of specification
Table 3: Morphology chart
Option 1 Option 2 Option 3 Option 4
1 Joint Movement
Method
Hydraulic Pneumatic electronic servomotor elastic actuators
2 Joint
Connectivity
separate exterior
ball joint
hollow spherical
ball joint
A chain of external ball
joints
gasketed hard
shell sections
joined with free-
rotating
mechanical
bearings
3 Suiting system Belt Sticky Clip Slider
4 Material (frame
and amour)
Titanium Carbon Fibre Steel Aluminium
Based on the morphology chart, we had combine the option then make four options of design’s
spefication
Design 1
Option 1 Option 2 Option 3 Option 4
1 Joint Movement
Method
Hydraulic Pneumatic electronic servomotor elastic actuators
2 Joint
Connect/flexibiity
separate exterior
ball joint
hollow spherical
ball joint
A chain of external ball
joints
gasketed hard
shell sections
joined with free-
rotating
mechanical
bearings
3 Suiting system Belt Sticky Clip Slider
4 Material (frame
and amour)
Titanium Carbon Fibre Steel Aluminium
Specification of Design 1
7
Design 2
Option 1 Option 2 Option 3 Option 4
1 Joint Movement
Method
Hydraulic Pneumatic electronic servomotor elastic actuators
2 Joint
Connect/flexibiity
separate exterior
ball joint
hollow spherical
ball joint
A chain of external ball
joints
gasketed hard
shell sections
joined with free-
rotating
mechanical
bearings
3 Suiting system Belt Sticky Clip Slider
4 Material (frame
and amour)
Titanium Carbon Fibre Steel Aluminium
Specification of Design 2
Design 3
Option 1 Option 2 Option 3 Option 4
1 Joint Movement
Method
Hydraulic Pneumatic electronic servomotor Elastic Actuator
2 Joint
Connect/flexibiity
separate exterior
ball joint
hollow spherical
ball joint
A chain of external ball
joints
gasketed hard
shell sections
joined with free-
rotating
mechanical
bearings
3 Suiting system Belt Sticky Clip Slider
4 Material (frame
and amour)
Titanium Carbon Fibre Steel Aluminium
Specification of Design 3
8
Design 4
Option 1 Option 2 Option 3 Option 4
1 Joint Movement
Method
Hydraulic Pneumatic electronic servomotor elastic actuators
2 Joint
Connect/flexibiity
separate exterior
ball joint
hollow spherical
ball joint
A chain of external ball
joints
gasketed hard
shell sections
joined with free-
rotating
mechanical
bearings
3 Suiting system Belt Sticky Clip Slider
4 Material (frame
and amour)
Titanium Carbon Fibre Steel Aluminium
Specification of Design 4
Table 4 : Screening
Selection
Criteria
Concepts Design
Design 1 Design 2 Design 3 Design 4
Ease of
Handling
Ease of Use
Mobility
Durability
Costing
Weight
Maintenance
Power saving
Efficiency
0
0
0
0
0
0
0
0
0
0
-
-
0
0
-
0
+
+
0
0
0
0
+
-
+
+
+
0
0
+
-
0
-
0
+
0
-
+
+
-
Sum of +’s
Sum of 0’s
Sum of –‘s
0
7
0
2
5
3
5
4
1
3
3
4
Net Score
Rank
0 -1 4 -1
*Design 1 been set as parameter
Therefore, by using screening concept we have decided that Design 3 is selected as the best
options.
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6 EXOSKELETON CONCEPT SKETCHES
Figure 2: Exoskeleton concept sketch 1
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Figure 3: Exoskeleton concept sketch 2
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Figure 4: Exoskeleton concept sketch 3
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Figure 5: Exoskeleton final concept sketch
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7 MATERIAL SELECTION
The method use to select the main materials is by comparing few materials using CES
EduPack and then using scoring concept based on their performance index. Material is selected
based on the required criteria. The criteria for body materials should be low in density, high in
young modulus, high in yield strength and low in price. The reference material is Cast iron, nodular
graphite, EN GJS 450 10.
Table 5: List of properties of reference material and selected materials for crankshaft
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Figure 6: Graph of Young’s Modulus VS Density
Figure above shows 8 of the materials that have been filtered out based on the required criteria.
Table 6: formula for performance index
Young Modulus, E Shear Modulus, G Yield Strength, σ
Performance
Index
calculation
Mass Price Mass Price Mass Price
𝐸12
𝜌
𝐸12
𝜌𝐶
𝐺12
𝜌
𝐺12
𝜌𝐶
𝜎23
𝜌
𝜎23
𝜌𝐶
Where,
𝐸 = 𝑀𝑜𝑑𝑢𝑙𝑢𝑠 𝑜𝑓 𝐸𝑙𝑎𝑠𝑡𝑖𝑐𝑖𝑡𝑦 (N/𝑚2)
𝐺 = 𝑀𝑜𝑑𝑢𝑙𝑢𝑠 𝑜𝑓 𝑅𝑖𝑔𝑖𝑑𝑖𝑡𝑦 (𝑃𝑎)
𝜌 = 𝑑𝑒𝑛𝑠𝑖𝑡𝑦 (𝑘𝑔
𝑚3)
𝑐 = 𝑚𝑎𝑡𝑒𝑟𝑖𝑎𝑙 𝑐𝑜𝑠𝑡 (𝑅𝑀
𝐾𝑔)
Density (kg/m^3)2000 5000 10000
Yo
un
g's
mo
du
lus
(GP
a)
10
20
50
100
200
500
Cast iron, nodular graphite, EN GJS 450 10
Titanium, alpha-beta alloy, Ti-6Al-2Sn-4Zr-6Mo (6-2-4-6)
Titanium, alpha alloy, Ti-8Al-1Mo-1V, solution treated & stabilized
Aluminum, 8019, rapid solidification
Beryllium-aluminum alloy, Beralcast 310, cast
Beryllium, Standard Grade, hot pressed
Aluminum, 6061, wrought, T6
Aluminum, 7075, wrought, T6
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Table 7: Performance index Scoring for Exoskeleton materials
Results shows that Berylium is the best performance material that we can use. Since the price of
Berylium is too expensive, so we had choose the second best material, which is Titanium alpha-
beta. Therefore, here is the mechanical properties of the materials.
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8 PARAMETERS DESIGN AND CALCULATIONS
Figure 7: Average body dimension
𝐴𝑣𝑒𝑟𝑎𝑔𝑒 𝑚𝑎𝑠𝑠 𝑜𝑓 𝑔𝑟𝑜𝑢𝑝 𝑚𝑒𝑚𝑏𝑒𝑟 =50 + 67 + 58 + 58 + 55
5= 57.6𝑘𝑔
𝑇ℎ𝑒 𝑏𝑜𝑑𝑦 𝑤𝑒𝑖𝑔ℎ𝑡 𝑎𝑐𝑡𝑖𝑛𝑔 𝑜𝑛 𝑡ℎ𝑒 𝑒𝑥𝑜𝑠𝑘𝑒𝑙𝑒𝑡𝑜𝑛 = 57.6𝑘𝑔 × 9.81𝑚𝑠−2 = 565.06𝑁
The exoskeleton should carry extra payload which is twice of the body weight,
So,
𝑃𝑎𝑦𝑙𝑜𝑎𝑑 = 2 × 𝑏𝑜𝑑𝑦 𝑤𝑒𝑖𝑔ℎ𝑡 = 2 × 565.06𝑁 = 1130.112𝑁 ≈ 1131𝑁
8.1 STATIC ANALYSIS
The final sketch is then simplified into free body diagram. Then, from the free body diagram, the
internal load and the direction of load in each member is determined as below.
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Figure 8: The free body diagram of Exoskeleton
The static analysis is done separately of Part 1, Part 2 and Part 3 with Assumptions:
The weight of each rigid member is negligible.
Part 1
Part 2
Part 3
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8.1.1 STATIC ANALYSIS OF PART 1 (TRUNK & HIP)
Figure 9: Free body diagram of part 1 – trunk and hip
Part 1, determine responding force, FA and FB:
∑ 𝑀𝐵 = 0, +𝐶𝑊:
80𝐹𝐴 − 1131(125 + 80) = 0
𝑭𝑨 = 𝟐𝟖𝟗𝟖. 𝟏𝟗𝑵 𝒇𝒐𝒓𝒄𝒆 𝒖𝒑𝒘𝒂𝒓𝒅
∑ 𝑀𝐴 = 0, +𝐶𝑊:
564.04(80) − 1131(125) − 𝐹𝐵(80) = 0
𝑭𝑩 = −𝟏𝟐𝟎𝟑. 𝟏𝟓𝑵 = 𝟏𝟐𝟎𝟑. 𝟏𝟓𝑵 𝒇𝒐𝒓𝒄𝒆 𝒖𝒑𝒘𝒂𝒓𝒅
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Part 1, Joint A,
∑ 𝐹𝑦 = 0, +𝑢𝑝𝑤𝑎𝑟𝑑 ∶
−2898.19 + 𝐹2 𝑠𝑖𝑛 28.68 = 0
𝑭𝟐 = 𝟔𝟎𝟑𝟖. 𝟗𝟒𝑵 (𝑪)
∑ 𝐹𝑥 = 0, +𝑡𝑜 𝑟𝑖𝑔ℎ𝑡 ∶
𝐹1 − 𝐹2 cos 28.68 = 0
𝑭𝟏 = 𝟓𝟐𝟗𝟖. 𝟎𝟒𝑵 (𝑻)
Part 1, Joint B,
∑ 𝐹𝑥 = 0, +𝑡𝑜 𝑟𝑖𝑔ℎ𝑡 ∶
−5298.04 + 𝐹3 sin 45 = 0
𝑭𝟑 = 𝟕𝟒𝟗𝟐. 𝟓𝟔𝑵 (𝑪)
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∑ 𝐹𝑦 = 0, +𝑢𝑝𝑤𝑎𝑟𝑑 ∶
1203.15 + 7492.56 sin 45 − 𝐹5 = 0
𝑭𝟓 = 𝟔𝟓𝟎𝟏. 𝟏𝟗𝑵 (𝑻)
Part 1, Joint C,
∑ 𝐹𝑦 = 0, +𝑢𝑝𝑤𝑎𝑟𝑑 ∶
𝐹4 cos 7.44 − 6038.9 sin 28.68 − 7492.56 sin 45 = 0
𝑭𝟒 = 𝟖𝟐𝟔𝟓. 𝟖𝑵 (𝑪)
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Part 1, Joint D,
∑ 𝐹𝑦 = 0, +𝑢𝑝𝑤𝑎𝑟𝑑 ∶
𝐹6 + 6501.19 − 8265 cos 7.44 = 0
𝑭𝟔 = 𝟏𝟔𝟗𝟓. 𝟎𝟐𝑵 (𝑪)
8.1.2 STATIC ANALYSIS OF PART 2 (CALF)
Figure 10: Free body diagram of part 2 – calf
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Part 2, Joint A,
∑ 𝐹𝑥 = 0, +𝑡𝑜 𝑟𝑖𝑔ℎ𝑡 ∶
𝐹1 sin 45 = 0
𝑭𝟏 = 𝟎 𝑵
∑ 𝐹𝑦 = 0, +𝑢𝑝𝑤𝑎𝑟𝑑 ∶
𝐹2 + 𝐹1 cos 14.64 − 1695.02 = 0
𝑭𝟐 = 𝟏𝟔𝟗𝟓. 𝟎𝟐𝑵 (𝑪)
Part 2, Joint C,
∑ 𝐹𝑥 = 0, +𝑡𝑜 𝑟𝑖𝑔ℎ𝑡 ∶
𝑭𝟑 = 𝟎 𝑵
∑ 𝐹𝑦 = 0, +𝑢𝑝𝑤𝑎𝑟𝑑 ∶
𝑭𝟓 = 𝟏𝟔𝟗𝟓. 𝟎𝟐𝑵 (𝑪)
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Part 2, Joint D,
∑ 𝐹𝑥 = 0, +𝑡𝑜 𝑟𝑖𝑔ℎ𝑡 ∶
𝑭𝟒 = 𝟎 𝑵
∑ 𝐹𝑦 = 0, +𝑢𝑝𝑤𝑎𝑟𝑑 ∶
𝑭𝟔 = 𝟏𝟔𝟗𝟓. 𝟎𝟐𝑵 (𝑪)
8.1.3 STATIC ANALYSIS OF PART 3 (FOOT)
Figure 11: Free body diagram of part 3 – foot
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𝑭𝟏 = 𝑭𝟐 = 𝑭𝟔 = 𝑭𝟕 = 𝟏𝟔𝟗𝟓. 𝟎𝟐𝑵 (𝑪)
𝑭𝟑 = 𝑭𝟒 = 𝑭𝟓 = 𝟎 𝑵
8.2 MEMBER THICKNESS IDENTIFICATION
From the above calculation, maximum compression and tensile force in the member have been
detected, as shown below,
Table 8: The maximum tensile and compression load in the member
Maximum force Location
Compression 8265.8 N Part 1, Joint B
Tensile 6501.19 N Part 1, Joint C
These 2 maximum force is then used to determine the suitable dimension for hip, calf, and foot.
By using the material buckling and tensile equation, the dimension of exoskeleton can be
determined.
Compression force can cause a member to buck. By inverse calculation, substitute the maximum
compression force of 8265.8N into equation of buckling to determine the right dimension to
prevent buckling of member.
𝑆𝐹 × 𝑃𝑐𝑟 =𝜋2𝐸𝐼
(𝐾𝐿)2
Where,
𝑆𝐹 = 𝑠𝑎𝑓𝑒𝑡𝑦 𝑓𝑎𝑐𝑡𝑜𝑟 = 3 (𝑓𝑜𝑟 𝑑𝑦𝑛𝑎𝑚𝑖𝑐 𝑖𝑚𝑝𝑎𝑐𝑡)
𝑃𝑐𝑟 = 𝑡ℎ𝑒 𝑐𝑟𝑖𝑡𝑖𝑐𝑎𝑙 𝑐𝑜𝑚𝑝𝑟𝑒𝑠𝑠𝑖𝑜𝑛 𝑙𝑜𝑎𝑑 = 8265.8𝑁
𝐸 = 𝑡ℎ𝑒 𝑦𝑜𝑢𝑛𝑔′𝑠 𝑚𝑜𝑑𝑢𝑙𝑢𝑠 𝑜𝑓 𝑚𝑎𝑡𝑒𝑟𝑖𝑎𝑙 = 28𝐺𝑃𝑎 𝑓𝑜𝑟 𝑡𝑖𝑡𝑎𝑛𝑖𝑢𝑚
𝐼 = 𝑚𝑜𝑚𝑒𝑛𝑡 𝑜𝑓 𝑖𝑛𝑒𝑟𝑡𝑖𝑎
𝐾 = 𝑑𝑒𝑠𝑖𝑔𝑛 𝑓𝑎𝑐𝑡𝑜𝑟 𝑏𝑎𝑠𝑒𝑑 𝑜𝑛 ℎ𝑜𝑤 𝑡ℎ𝑒 𝑚𝑒𝑚𝑏𝑒𝑟 𝑏𝑒𝑒𝑛 𝑓𝑖𝑥𝑒𝑑 𝑎𝑡 𝑏𝑜𝑡ℎ 𝑒𝑛𝑑
= 1 𝑓𝑜𝑟 𝑏𝑜𝑡ℎ 𝑝𝑖𝑛𝑛𝑒𝑑 𝑒𝑛𝑑
𝐿 = 𝑡ℎ𝑒 𝑙𝑒𝑛𝑔𝑡ℎ 𝑜𝑓 𝑚𝑒𝑚𝑏𝑒𝑟
25
Rearrange the equation to I as subject,
𝐼 =𝑆𝐹 × 𝑃𝑐𝑟 × (𝐾𝐿)2
𝜋2𝐸
So,
𝐼 =(24797.4)(0.2186)2
𝜋2(113 × 109)
𝐼 = 1.0625 × 10−4 𝑚4
Taking width, b = 60mm = 0.06m
𝐼 =(𝑤𝑖𝑑𝑡ℎ, 𝑏) × (𝑡ℎ𝑐𝑖𝑘𝑛𝑒𝑠𝑠, ℎ)3
12+ 𝐴𝑑𝑥
Rearrange the equation to h as subject,
ℎ = √12𝐼𝑦𝑦
𝑏
3
= √12 ×1.0625 × 10−9
0.06
3
= 4.61 × 10−4𝑚 = 𝟎. 𝟒𝟔𝟏𝒎𝒎
Furthermore, tensile force can cause a member to fracture. By inverse calculation, substitute the
maximum tensile force of 6501.19 N into equation of axial tensile to determine the right dimension
to prevent tensile failure of members.
𝜎𝑠𝑦 =𝑆𝐹 × 𝑃
𝐴=
𝑆𝐹 × 𝑃
𝑏ℎ
Where,
𝜎𝑠𝑦 = 𝑦𝑖𝑒𝑙𝑑 𝑠𝑡𝑟𝑒𝑛𝑔𝑡ℎ 𝑜𝑓 𝑡𝑖𝑡𝑎𝑛𝑖𝑢𝑚 = 1120𝑀𝑃𝑎
𝑃 = 𝑡ℎ𝑒 max 𝑡𝑒𝑛𝑠𝑖𝑙𝑒 𝑙𝑜𝑎𝑑 𝑎𝑐𝑡𝑖𝑛𝑔 𝑜𝑛 𝑡ℎ𝑒 𝑚𝑒𝑚𝑏𝑒𝑟 = 6501.19𝑁
𝑆𝐹 = 𝑠𝑎𝑓𝑒𝑡𝑦 𝑓𝑎𝑐𝑡𝑜𝑟 = 3 (𝑓𝑜𝑟 𝑑𝑦𝑛𝑎𝑚𝑖𝑐 𝑖𝑚𝑝𝑎𝑐𝑡)
𝑏 = 𝑤𝑖𝑑𝑡ℎ 𝑜𝑓 𝑡ℎ𝑒 𝑚𝑒𝑚𝑏𝑒𝑟
ℎ = 𝑡ℎ𝑖𝑐𝑘𝑛𝑒𝑠𝑠 𝑜𝑓 𝑡ℎ𝑒 𝑚𝑒𝑚𝑏𝑒𝑟
Take width, b = 60mm = 0.06m, rearrange the equation to find thickness, h,
26
ℎ =𝑆𝐹 × 𝑃
𝑏 × 𝜎𝑠𝑦=
3 × 6501.19
0.06 × 1120 × 106= 2.9 × 10−4 = 𝟎. 𝟐𝟗𝒎𝒎
As a comparison, the minimum thickness of the member to withstand compression and tension
force are 0.461mm and 0.29mm respectively. To be safe, the thickest of the member must be bigger
the 0.461mm
8.3 BOLT DIAMETER IDENTIFICATION
From the previous static analysis, the maximum load acting on the member is shown in tale below:
Table 9: The maximum tensile and compression load in the member
Maximum force Location
Compression 8265.8 N Part 1, Joint B
Tensile 6501.19 N Part 1, Joint C
Following is the calculation to determine the suitable bolt diameter, d with 8265.8 N
compression force.
𝑆ℎ𝑒𝑎𝑟 𝑆𝑡𝑟𝑒𝑠𝑠 𝑜𝑓 𝑡𝑖𝑡𝑎𝑛𝑖𝑢𝑚, 𝜏 =𝑆𝐹 × 𝐹𝑜𝑟𝑐𝑒, 𝐹
𝐴𝑟𝑒𝑎, 𝐴=
𝑆𝐹 × 𝐹 × 4
𝜋𝑑2
Rearrange the equation to bolt diameter, d as subject,
𝑏𝑜𝑙𝑡 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟, 𝑑 = √𝑆𝐹 × 𝐹 × 4
𝜋 × 𝜏= √
3 × 8265.8 × 4
𝜋 × 1120 × 106= 5.31 × 10−3𝑚 = 𝟓. 𝟑𝟏𝒎𝒎
To achieve minimum SF of 3, both diameter should be equal or bigger than 5.31mm, but the bigger
and available bolt diameter in the industry is 5.5mm. So, 5.5mm bolt diameter is chosen.
27
9 FINAL DESIGN
Figure 12: Front isometric view of Exoskeleton
Foot
Payload Shoulder
Spline
Hip
Calf
Trunk
28
Figure 13: Back isometric view of Exoskeleton
The detail dimension for every parts are shown in Attachment.
10 ANALYSIS AND SIMULATION
The overall image of the Exoskeleton is shown in the figures below. Simple FEM are to be done
in static condition. The body weight and payload are applied on the trunk, the result is observed.
The important parameter need to be observe in from the result are:
Maximum Von Mises stress
Maximum displacement
Minimum safety factor
29
Figure 14: Applied weight of 565.04N and payload of 1131N
As shown in Figure above, body weight (565.04N) and payload (1131N) are applied to the main
trunk. At the same time, fix constraint is applied to both foot base of Exoskeleton. Finally,
frictionless constraint applied to the back of Exoskeleton to avoid it falling backward and
forward during simulation.
30
Figure 15: Mesh view of Exoskeleton
Then, Auto Mesh is applied to the whole Exoskeleton geometry.
31
Figure 16: Result of Von Mises Stress
The maximum Von Mises Stress is 38.04 MPa and it happen at the knee joint. 38.04 MPa is
lower than yield strength of titanium which is 1120 MPa. Therefore, the material is operate under
safe region.
32
Figure 17: Result of displacement
Due to the loading, the maximum displacement happen at the knee again. The value of maximum
displacement is 0.07405mm, which is a not visible displacement. And, it is a very acceptable
displacement.
33
Figure 18: Result of safety factor
Finally and the most important result is the minimum safety factor. The minimum safety factor
that shows from the result is 8.16. Safety factor of 8.16 is more than what expected. In short, the
Exoskeleton passed the static load test.
34
11 COST ESTIMATION
The total weight of the frame is 71.59kg
Material used : Titanium, alpha-beta alloy, Ti-6Al-2Sn-4Zr-6Mo(6-2-4-6)
Table 10: Cost item
Cost Item Price
(RM)
Quantity Total
Cost
Raw material 85.20 71.590 6099
Battery (Lithium polymer) 500 1 500
Actuator 90 4 360
Equipment 10 1 10
Manufacturing 300 1 300
Summary 7269
Since no allocation budget:
Estimated hours: 670 Planned hours: 720 Imputed hours: 470 Hour rate: RM2.50/h
Table 11: Total cost
Category Estimated Planned Hour
cost
Total cost
Coordination 40 40 40 100
Analysis 100 100 100 250
Design 120 140 130 325
Draft 40 40 40 100
Template 40 60 40 100
Apply design 40 40 40 100
Development 190 200 195 487.5
Product Management 50 50 50 125
Testing 50 50 50 125
Summary RM 1712.5
Estimated cost summary=7269+1712.5= RM8981.5
35
12 REFERENCES
http://en.wikipedia.org/wiki/Powered_exoskeleton
http://www.digitaltrends.com/cool-tech/darpa-invests-super-light-exoskeleton-soldiers/
http://www.defensereview.com/lockheed-martin-hulc-human-universal-load-carrier-
anthropomorphic-exoskeleton-for-future-military-special-operations-forces-sof-warfare-at-sofic-
2012-video/
http://www.kurzweilai.net/book-review-science-fiction-bots-becoming-fact
36
13 ATTACHMENT
37
Contents
1 PROBLEM STATEMENT ...................................................................................................... 1
2 LITERATURE REVIEW ........................................................................................................ 1
3 OBJECTIVES .......................................................................................................................... 2
4 MORPHOLOGY CHART ...................................................................................................... 3
5 CONCEPT GENERATION & CONCEPT SELECTION ...................................................... 4
5.1 EXOSKELETON BALANCER ...................................................................................... 4
5.2 Exoskeleton Lower Part ................................................................................................... 6
6 EXOSKELETON CONCEPT SKETCHES ............................................................................ 9
7 MATERIAL SELECTION .................................................................................................... 13
8 PARAMETERS DESIGN AND CALCULATIONS ............................................................ 16
8.1 STATIC ANALYSIS ..................................................................................................... 16
8.1.1 STATIC ANALYSIS OF PART 1 (TRUNK & HIP) ............................................ 18
8.1.2 STATIC ANALYSIS OF PART 2 (CALF)............................................................ 21
8.1.3 STATIC ANALYSIS OF PART 3 (FOOT) ........................................................... 23
8.2 MEMBER THICKNESS IDENTIFICATION .............................................................. 24
8.3 BOLT DIAMETER IDENTIFICATION ....................................................................... 26
9 FINAL DESIGN .................................................................................................................... 27
10 ANALYSIS AND SIMULATION .................................................................................... 28
11 COST ESTIMATION ........................................................................................................ 34
12 REFERENCES .................................................................................................................. 35
13 ATTACHMENT ................................................................................................................ 36