dfma stapler
TRANSCRIPT
DFMA as Applied to the Swingline® 747 Desktop Stapler.
Department of Mechanical Engineering, The University Of Utah, Salt Lake City, Utah.
Group Members
Xiaofan Xie, Vamsi Uppalapati, Charan R. Sarjapur Naveen Huilgol, Clief Castleton
Submitted 7 April 2003
To
Dr. A.K. Balaji
i
Table of Contents
List of Figures and Tables… … … … … … … … … … … … … … … … … … … … … … … .iv
Abstract…………………… … … … … … … … … … … … … … … … … … … … … … … .vi
1 I n t r o d u c t i o n … … … … … … … … … … … … … … … … … … … … … … … … .… … … … 1
1.1General Stapler Propert ies……………………………………………………..1
2 DFMA Paradigms and Analyses………………………………………… .… … … … 8
2.1Material Selection Paradigms………………………………………… … … … . 8
2.2 Material Selection of the Stapler…………………………………………….10
2.3 Recommended Changes………………………………………..… … … … … 11
2.4 Manufacturing Methods of the Stapler…………………………..… … … … . 11
2.4aSheet Metal Analyses … … … … … … … … … … … … … … … … … .…….13
2.4aiAnalysis for the Original Upper Staple Guide……………………13
2.4aii Analysis for the Changed Upper Staple Guide……… … … … … ..18
2.4a iii Abbreviated Analyses Results for Other Parts……… … … … … 23
2.5 Assembly Paradigms……………………………………… … … … … ..…….25
2.5a Assembly Times and Efficiency……………………………………….25
2.5b Guidelines for Manual Assembly…………………………………….. .26
2.5c Effects of Weight and Dimension…………………………………….. .26
2.5d C h a m f e r s … … … … … … … … … … … … … … … … … … … … … … … … 2 7
2.5e Miscellaneous Effects on Assembly Time……………………….…….28
2.5f Further Gui d e l i n e s … … … … … … … … … … … … … … … … … … … … . . 2 8
2.5g Assembly Layou t…………………………………………….… … ..…29
2.6 Assembly of the Stapler………………………………………….… … … ….30
2.6a Efficiency… … … … … … … … … … … … … … … … … … … … … … … . . . 3 1
2.6b C h a m f e r s … … … … … … … … … … … … … … … … … … … … … ...……31
2.7 Recommended Changes… … … … … … … … … … … … … … … … … … … … 3 1
3 D i s c u s s i o n … … … … … … … … … … … … … … … … … … … … … … … … … ..… … .32
4 C o n c l u s i o n … … … … … … … … … … … … … … … … … … … … … … .… … . … … … 33
ii
Appendix A: Material Selection Analyses………………………………………34
Appendix B: Manufacturing Process…………………………………………… 49
Appendix C: ProE© P a r t s D r a w i n g s … … … … … … … … … … … … … … … … … .51
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List of Figures and Tables
Figures
1. Rubber Pad… … … … … … … … … … … … … … … … … … … … … … … … … … … . . 2
2. Release Clip… … … … … … … … … … … … … … … … … … … … … … … … … … … . 3
3. Closed Stapler Function… … … … … … … … … … … … … … … … … … … … … … . . 3
4. Open Stapler Function… … … … … … … … … … … … … … … … … … … … … … … . 3
5. Lower Leaf Spring… … … … … … … … … … … … … … … … … … … … … … … … ...3
6. Anvil… … … … … … … … … … … … … … … … … … … … … … … … … … … … … … 4
7. Pinning vs. Stapling… … … … … … … … … … … … … … … … … … … … … … … … . 4
8. Base… … … … … … … … … … … … … … … … … … … … … … … … … … … … … … . 4
9. Anvil Actuator… … … … … … … … … … … … … … … … … … … … … … … … … … . 4
10. Spacer… … … … … … … … … … … … … … … … … … … … … … … … … … … … … . . 5
11. Spring… … … … … … … … … … … … … … … … … … … … … … … … … … … … … . . 5
12. Pin… … … … … … … … … … … … … … … … … … … … … … … … … … … … … … … 5
13. Staple Guide… … … … … … … … … … … … … … … … … … … … … … … … … … … 5
14. Staple Slide… … … … … … … … … … … … … … … … … … … … … … … … … … … . . 6
15. Upper Arm… … … … … … … … … … … … … … … … … … … … … … … … … … … . . . 6
16. Upper Staple Guide… … … … … … … … … … … … … … … … … … … … … … … … . 6
17. End Cap… … … … … … … … … … … … … … … … … … … … … … … … … … … … . . . 7
18. Upper Leaf Spring… … … … … … … … … … … … … … … … … … … … … … … … . . . 7
19. Upper Cover… … … … … … … … … … … … … … … … … … … … … … … … … … … 7
20. Plastic Cover… … … … … … … … … … … … … … … … … … … … … … … … … … … 8
21. Stress-Strain Plots… … … … … … … … … … … … … … … … … … … … … … … … … 9
22. General Trends… … … … … … … … … … … … … … … … … … … … … … … … … … 9
23. Bench Station… … … … … … … … … … … … … … … … … … … … … … … … … … 2 9
24. Multi-Station… … … … … … … … … … … … … … … … … … … … … … … … … … . 2 9
25. Modular Station… … … … … … … … … … … … … … … … … … … … … … … … … . 2 9
26. Custom Layout… … … … … … … … … … … … … … … … … … … … … … … … … . . 3 0
27. Flexible Layout… … … … … … … … … … … … … … … … … … … … … … … … … . . 3 0
v v
28. B a s e … … . . … … … … … … … … … … … … … … … … … … … … … … … … … … … .34
29. R e d e s i g n … … … … … … … … … … … … … … … … … … … … … … … … … … … … 34
Tables
1. Specifications of the Stapler… … … … … … … … … … … … … … … … … … … … … 1
2. Stapler Components… … … … … … … … … … … … … … … … … … … … … … … … . 2
3. Brief Overview Data… … … … … … … … … … … … … … … … … … … … … … … . . 11
4. Manufacturing Processes… … … … … … … … … … … … … … … … … … … … … . . . 1 2
5. Insertion Parameters… … … … … … … … … … … … … … … … … … … … … … … . . 2 7
6. Handling Times Data… … … … … … … … … … … … … … … … … … … … … … … . 3 0
7. Insertion Parameters fo r the Pin… … … … … … … … … … … … … … … … … … … 3 1
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ABSTRACT:
An analysis of the Swingline® Classic 747 desktop stapler is presented with a focus
on stapler components and their functions, materials, and other specifications. The
methods and paradigms used for analysis of manufacture, assembly, materials
selection, cost, times, and other factors follow those set forth by Boothroyd Dewhurst
Inc.’s Design for Manufacture and Assembly as found in Product Design for
Manufacture and Assembly, 2nd edition by Boothroyd, Dewhurst, and Knight.
DFMA as Applied to the Swingline® 747 Desktop Stapler
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1 Introduction As an introduction to DFMA paradigms and processes, the analysis of the Swingline®
Classic 747 stapler is presented. This full-strip desktop stapler has been on the market for
over 30 years. The stapler design is classic and therefore any part of the stapler could be
considered sufficient and require no change. However, the aim of this project was to
perform DFMA analyses on the components to determine if changes were possible and, if
needed, to have justified those changes. A materials selection analysis was run on all
parts except one. Manufacturing analyses were run for sheet metal operations for four
parts and the assembly sequence and time was derived based on certain plausible
assumptions. The DFMA paradigms applied to this project will be discussed as they are
used; viz. the paradigms for manufacturing are discussed prior to the presentation of
manufacturing methods for the stapler, etc. We begin with the stapler specifications,
functions, and capabilities.
1.1 General Stapler Properties The basic specifications of the stapler are given in Table 1. It should be stated that there
are various styles and capacities of staplers with various specifications. The 747, as with
other models, meets the required performance capacities.
Table 1. Specifications of the Stapler [1]
Stapling capability 20 sheet capacity
Staple type S.F.4 standard staples
Staple number 210
Jam-resistant Yes
Staple reload indicator
Yes
Height 60mm (2.36ins)
Width 45mm (1.77ins)
Length 200mm (7.88ins)
Weight 529g (1.167lbs)
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The stapler is designed to be used in three ways. The first two are dependent upon the
orientation of the anvil, which provides for stapling and pinning. The stapler can also be
opened to be used in tacking sheets to the wall. Table 2 shows the 17 components,
excluding fasteners, of the 747 and the material of which each is believed to be made.
There was a level of uncertainty in some cases, so an educated guess was made. A brief
description of each part and its function and properties follows with pictures of each part.
1. Rubber Pad:
Fig 1 Rubber Pad
The function of the rubber pad was identified as providing a good grip on the working
surface, protecting the surface, and covering the cavities on the bottom of the base. Due
to its material, it also provides a damping of vibrations while in use, which leads to better
ergonomic use of the stapler.
Component Name Actual Material
Rubber Pad Rubber
Release Clip Aluminum Alloy Lower Leaf Spring Spring Steel Anvil Alloy Steel Base Aluminum Alloy Anvil Actuator Aluminum Alloy Spacer Plastic Spring Spring Steel (Alloy Steel) Pin Alloy Steel Staple Slide Aluminum Alloy (Cu Coating) Bottom Staple Guide Aluminum Alloy Upper Arm Alloy Steel Upper Staple Guide Aluminum Alloy End Cap(747) Alloy Steel Upper Leaf Spring Spring Steel (Alloy Steel) Upper Cover Alloy Steel Plastic Cover Plastic
Table 2 – Stapler Components
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2. Release Clip
Fig 2 Release Clip
In order to facilitate tacking, when depressed the stapler base and cover assemblies can
open to 180 degrees. The unlocking mechanism allows the use of staples without
bending the ends. The clip also provides a locking mechanism between the base and the
upper arm when in desktop use. See figures 3 and 4. The release clip also provides a
springing action to the upper arm by means of connecting it with the lower leaf spring.
Fig 3 [2] When the release clip is in the locked position we have the ends of the staple bent by the anvil.
Fig 4 [2] When the release clip is in the unlocked position we have the ends of the staple go through the paper without being bent by the anvil.
3. Lower Leaf Spring
Fig 5 Lower Leaf
The lower leaf provides springing action for the anvil actuator which helps in rotating the
anvil and, along with the release clip , provides the restoring force to the upper arm,
allowing the stapler to return to initial orientation.
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4. Anvil
Fig 6 Anvil
The main function of the anvil is to provide a guiding mechanism for the staple ends.
Figure 7 shows the two stapling methods which can be achieved by rotating the anvil.
The left-hand figure shows that the anvil is set for conventional stapling, giving a more
secure hold, while the right-side figure shows a configuration providing a looser pinning
of the sheets that can easily be taken apart.
Fig 7 [2]
5. Base
Fig 8 Base
The base houses the rubber base, anvil, anvil actuator and lower leaf spring. Along with
the pin, it also provides the necessary hinging action between the upper and the lower
assemblies.
6. Anvil Actuator
Fig 9 Anvil Actuator The anvil actuator holds the anvil in place and also helps in rotating the anvil. Connected
to the lower leaf, it will automatically reset the anvil in its well when released.
Staple
Anvil
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7. Spacer
Fig 10 Spacer
The spacer supports the pin. It also holds the upper assembly and the lower assembly in
place. It is also believed to aid in the assembly of the upper and lower parts. (See
assembly section for further details.)
8. Spring
Fig 11 Spring
The spring along with the staple slide helps in pushing the staples forward, maintaining
adequate forward force on the staples, and when reloading removes the staple slide to the
rear.
9. Pin
Fig 12 Pin
It provides the necessary hinging action between the upper and the lower assemblies as
well as keeps the stapler together.
10. Bottom Staple Guide
Fig 13 Bottom Staple Guide The staple slide and staples rest on the bottom staple guide.
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11. Staple Slide
Fig 14 Staple Slide
The staple slide along with the spring helps in the feeding of the staples. The staple slide
moves along the staple guide. The copper coating helps in indicating the amount of
staples left in the stapler when viewed through the opening in the upper arm.
12. Upper Arm
Fig 15 Upper Arm
The upper arm houses the staple guide sub-assembly. It is an important component of the
upper assembly. Through a narrow opening at the distal end of the upper arm, the level of
remaining staples is visually indicated. It also keeps the cover secure while in use. The
upper leaf pushes out the staples through the gap in the front of the arm.
13. Upper Staple Guide
Fig 16 Upper Staple Guide The upper staple guide keeps the staples from coming off the lower guide and provides a
point of attachment for the spring as well as a turning point for the spring.
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14. End Cap
Fig 17 End Cap
The end cap helps in preventing the spreading out of the upper arm. It also serves as a
logo marquee.
15. Upper Leaf Spring
Fig 18 Upper Leaf Spring
The upper leaf spring provides the springing action between the upper arm and the upper
staple guide. It also serves the vital function of pushing out the staples.
16. Upper Cover
Fig 19 Upper Cover
The main function of the upper cover is to hold the upper assembly. The main
components held by the upper arm are the upper staple guide, upper leaf spring, and the
plastic cover.
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17. Plastic Cover
Fig 20 Plastic Cover
The plastic cover mainly serves as an advertising plate for Swingline®. It also covers the
holes in the upper cover.
2 DFMA Paradigms and Analyses
What follows is the discussion of DFMA paradigms and their application to three
areas; material selection, manufacturing, and assembly. In each area, the general
paradigms will be followed by their application to specific parts of the product.
2.1 Material Selection – General Paradigms
There are several factors which bear consideration while designing a product.
Among these are weight, strength, cost, durability, environment, aesthetics, etc. Each one
of these can affect the design both from the manufacture and assembly aspects. A part
that is designed for optimum manufacturability with a specific material may give rise to
assembly issues. The converse is also true. While still in the design phase, giving
thought to these factors will help reduce problems in the subsequent stages. With respect
to the mass of the material, and therefore the weight, some thoughts might go to whether
the product needs to be portable, if it will be manufactured on-site, what loads will be
placed on it, what are the costs involved, and so forth. Strength of the material selected is
also important primarily to prevent failure of the design. Figure 21 shows the stress-
strain plots for various materials. A DFMA analysis of a part might yield wood as the
best possible choice when considering cost and ease of manufacturability, as was the case
with one component of the stapler. However, functional analysis would identify that
material to be inadequate as it would fail under normal operating conditions. Figure 22
describes several general trends in relation to strength of materials.
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Fig 21 Stress Strain Plot for Various Materials [3]
n E (Young’s Modulus) is the slope of the stress-strain (σ−ε) curve. n Metals are stronger than other materials n Woods are stronger than some plastics but may break before much elongation. n Plastics have odd behavior but can be useful. n Rubbers are soft but can deform a great deal before failure. n Some materials do not have well defined yield stresses. If not given, use σT.
Figure 22 General Trends [3]
In order to achieve optimal overall costs, which is vital in a competitive market, the costs
of manufacture and assembly of the product must be considered early. DFMA provides
several methods which can be carried out by hand or computer that will analyze designs
based on projected costs. The specifics not used in our analysis are available in the text
by Boothroyd, Dewhurst, and Knight or in the DFMA software. A final product which is
too costly as a result of poor planning and inefficient methods will be priced out of the
market. Other factors also should contribute in the initial design phases. The product
should be durable and aesthetic, given toda y’s consumer-driven market. Also,
environmental issues in manufacture, governed by political climates, must also be dealt
with, as well as problems that may be caused by the environment in which the product
Metals
Plastics
Rubbers
Woods
σ
ε
σu
σy
DFMA as Applied to the Swingline® 747 Desktop Stapler
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will be used. Weather, temperature, soil acidity, and a host of other factors may affect
the lifetime of the product, which in turn can also affect the design. As was mentioned,
the optimal design for one aspect might be the least desirable for another.
One of the key material selection paradigms in DFMA is the derived parameter
ranking. This enables the designers to rank each material depending on the desired
property or ratios of related properties. According to the resulting data, proper selection
of material can be better made.
2.2 Material Selection – Stapler
The full material selection data obtained by using DFMA equations is available in
appendix A. Appendix B gives the selection criterion for DFMA. Table 3 gives a limited
overview of the materials selection for each of the 17 primary parts of the 747 stapler. It
is a brief presentation of what material DFMA suggests should be used for each part
based on different criteria. Some parts were not analyzed due to their apparent adequacy,
i.e. no materials change was deemed necessary. The column labeled analysis run
indicates the criteria desired. The three subsequent columns give the material best suited
for those criteria under certain conditions. For example, the release clip analysis was run
to obtain the strongest beam. The material yielding the maximum performance is alloy
steel. The minimum weight is achieved with aluminum. The minimum cost material is
cast iron. The variance of materials offered by the analysis is indicative of the subjective
nature of DFMA; sometimes a decision must be made when the data present conflicting
results. The last column of Table 3 indicates what is believed to be the actual material of
which the part is made.
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Table 3 - Brief overview data on material selection for 747 stapler parts. Note: The detailed results for the above analysis have been attached (Appendix A).
2.3 Recommended Changes
While an analysis was run on each of the parts that was believed to require change,
the DFMA analysis revealed that the presumed actual materials already were properly
chosen. Therefore, no recommended changes to the materials used in the Swingline ® 747
stapler can be made. While change was considered for the cover and base from metal to
plastic, it was decided to leave them metal due to strength and durability issues.
2.4 Manufacturing Method of Stapler
Table 4 shows the various parts of the stapler along with the various
manufacturing processes along with the sub-operations. Thereafter is given the sheet
metal analysis for several stapler components. Guidelines for design for manufacturing
are given in Appendix C. The specific equations and numerical analysis is given in
No. Component Name Analysis Run Maximum Performance Minimum Weight Minimum Cost Actual Material
1 Rubber Pad NA NA NA NA Rubber
2 Release Clip Strongest beam Alloy steel Aluminum Cast Iron Aluminum
3 Lower Leaf Spring Best Diaphragm Spring Beryllium copper Beryllium copper Ductile iron Spring Steel
4 Anvil Strongest plate Beryllium copper Aluminum Cast Iron Steel
5 Base Strongest plate Beryllium copper Aluminum alloy Cast Iron Aluminum
6 Anvil Actuator Strongest Ten Member Alloy steel Alloy steel Ductile iron Aluminum
7 Spacer NA NA NA NA Plastic
8 Spring Best Coil Spring Beryllium copper Alloy steel Ductile iron Spring Steel
9 The Pin Strongest beam Alloy steel Aluminum alloy Ductile iron Alloy Steel
10 Staple Slide Strongest Comp Member Alloy steel Alloy steel Gray cast iron Al (Cu Coating)
11 Bottom Staple Guide Light Weight NA NA NA Aluminum
12 The Upper Arm Strongest beam Alloy steel Aluminum alloy Ductile iron Steel
13 Top Staple Guide Light Weight NA NA NA Aluminum
14 End Cap(747) Strongest Plate Alloy steel Aluminum alloy Ductile iron Steel
15 Upper Leaf Spring Best Diaphragm Spring Beryllium copper Beryllium copper Ductile iron Spring Steel
16 Upper Cover Strongest beam Alloy steel Aluminum alloy Ductile iron Alloy Steel
17 Plastic Cover NA NA NA NA Plastic
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whole for the upper staple guide. The analyses for the other parts, while completed fully,
have been limited in this paper to the presentation of the results. This was done for
brevity. The information in the last columns of Table 4 is not given in order of process
sequence.
Table 4 – Manufacturing Processes
No Component Name Manufacturing Processes Operations
1 Rubber Pad Molding NA
2 Release Clip Sheet Metal working Part-off, Punching, Bending
3 Lower Leaf Spring Sheet Metal working Part-off, Punching, Bending, Plating
4 Anvil Sheet Metal working Blanking, Punching, Bending
5 Base Die casting Painting
6 Anvil Actuator Die casting Painting
7 Spacer Injection Molding NA
8 Spring Coiling Coiling, Bending, Plating
9 Pin Casting Turning, Knurling, Copper Coating
10 Staple Slide Sheet Metal working Blanking, Punching, Bending
11 Bottom Staple Guide Sheet Metal working Blanking, Punching, Bending
12 Upper Arm Sheet Metal working Blanking, Punching, Bending, Plating, Embossing
13 Upper Staple Guide
Sheet Metal working Blanking, Punching, Bending, Embossing
14 End Cap(747) Sheet Metal working Part-off, Bending, Embossing, Plating
15 Upper Leaf Spring Sheet Metal working Part-off, Punching, Bending, Plating
16 Upper Cover Sheet Metal Forming Drawing, Ironing
17 Plastic Cover Injection Molding Printing
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2.4a Sheet Metal Analyses
Equations and tables used for the following calculations are from [4].
2.4a.i Upper Staple Guide
Material: - Aluminum Gauge Number: -20 Thickness: - 1.02 mm Ultimate tensile strength: - 90 MN/m2
Cost of blanking die:
Taking 50 mm tolerances on four sides
Usable area = Au = 25.5*14.6 = 372.3 cm2
Cost of die set = Cds = 120 +0.36*Au = $ 255.
Profile complexity = Xp = P2/LW
L = 155 mm = 15.5 cm W = 46 mm = 4.6cm P = 432.5 mm = 43.25 cm
Therefore, Xp = 26.23
Total die manufacturing points:
Basic manufacturing points poM
From Fig. 9.9 poM = 33
Plan area = 71.3 cm2
Plan area correction factor wf1 from Fig. 9.10 wf1 = 1.75
Assuming number of parts to be produced as 500,000 hd = 21.31 mm from Equation (9.3)
Now considering hd = 25 mm
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Die plate thickness correction factor from Equation (9.5) is fd = 0.5 +0.02* hd = 1
Thus, total die manufacturing points are therefore Mp = fd*f1w*Mpo = 1*1.75*33 = 57.75
The estimated blanking die cost, assuming $40/hr for die making, is = Cds + Mp*40 = 255 + 57.75*40 = $2565. Scrap percent:
Area of each part is
Ap =19.5 + 6.875 + 4878 + 190 + 57.5 + 130 = 52.82 cm2
Area of sheet used for each part is
As = (15.5 + 0.204)*(4.6 + 0.204) = 75.44 cm2
Scrap % = (As – Ap)/As = .30 = 30 % Cost of piercing die: Cds = $255, L = 138.75 mm = 13.875 cm, W = 39.5 mm = 3.95 cm
The base manufacturing score from eq. (9.7) is
Mpo = 23 + 0.03 LW = 24.64
The number of hours required to manufacture the custom-punching element for the non-standard aperture is, from eq. (9.8)
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Pp = 112 mm = 11.2 cm, Np = 2 Mpc = 8 + 0.6 * Pp + 3 Np = 20.72
The equipment manufacturing time for punches, die plate inserts is, from eq. (9.9) Round holes K = 2, Np = 4, Nd = 1 Mps = K*Np + 0.4 Nd = 8.4
Rectangular holes K = 3.5, Np = 2, Nd = 2 Mps = K*Np + 0.4 Nd = 7.8 Total Mps = 16.2
The estimated piercing die cost, assuming $40/h for die making, is = Cds + ( Mpo + Mpc + Mps )*40 = $2720 Cost of bending die: Cds = $255, L = 155 mm = 15.5 cm, W = 46 mm = 4.6 cm, D = 1.7 cm
Basic die manufacturing score for bending Mpo = (18 + 0.023LW)*(0.9 + 0.02 D) = 18.34
Additional point for bend length and multiple bends Lb = 28.525 cm, Nb = 7 Mpn = 0.68 Lb + 5.8 Nb = 60
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The estimated bending die cost, assuming $40/h for die making, is = Cds + ( Mpo + Mpn) * 40 = $3390 Cost of embossing die: Cds = $255, L = 80 mm = 8 cm, W = 26 mm = 2.6 cm, Mpx = 0.13 Nsp Mpo = 23 + 0.03 LW Mpc = 8 + 0.6 Pp + 3 Np
Therefore, Mpo = 23.624
Rectangular embossing Mpx = 4 *(0.13*3) = 1.56
Circular embossing Mpx = 2 * (0.13 * 1) = 0.26
Total Mpx = 1.82 Mpc = 8 + 0.6 * 7.8 + 3 * 6 = 30.68
Cost of embossing die is, = Cds + ( Mpo + Mpc + Mpx) * 40 = $2500 Cost of progressive die: Cd = 2 Cid
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Where
Cid = 2565 + 2720 + 3390 + 2500 = $11175 Cd = $22350 Cycle time for each part: U = 90*103KN/m2 h = 1.02 mm = 1.02 * 10-3 m
Force for Blanking: Fblanking = 0.5UhLs
Where Ls = length to be sheared = 43.45 cm = 0.4325 m Fblanking = 19.85 KN
Force for Punching: Fpunching = 0.5UhLs
Where Ls = 260 mm = 0.26m
Fpunching = 11.93 KN
Force for Embossing:
For one embossing Fembossing = UhLsSinθ = 5.06 since Ls = 0.078m Total Fembossing = 6 * 5.06 (As they are six embossing effects) = 30.38 KN
Force for Bending: Fbendung = 0.08UhLb
Where Lb = Length of bend = 28.525 cm = .28525 m Fbendung = 2.094 KN
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So, Total force required = Fblanking + Fpunching + Fembossing + Fbendung = 64.25 KN = 65 KN
From Table 9.3 The space required for 4 die stations is, 4*14.6 = 58.4
From Table 9.8 Appropriate press for 58.4 is 500 KN press force, $76/hr operating cost and
speed of 90 strokes/min.
The estimated cycle time per part is, t = 60/90 =0.67 sec
Processing cost per part is Cp = (0.67/3600)*76*100 = 1.4 cents. 2.4aii Sheet metal analysis for changed part: Cost of blanking die:
Taking 50 mm tolerances on four sides
Usable area = Au = 25.5*14.6 = 372.3 cm2
Cost of die set = Cds = 120 +0.36*Au = $ 255.
Profile complexity = Xp = P2/LW
L = 155 mm = 15.5 cm W = 46 mm = 4.6cm P = 395.5 mm = 39.55 cm
Therefore, Xp = 21.93
Total die manufacturing points
Basic manufacturing points poM
From Fig. 9.9 poM = 32
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Plan area = 71.3 cm2
Plan area correction factor wf1 from Fig. 9.10
wf1 = 1.75
Assuming number of parts to be produced as 500,000 hd = 21.31 mm from Equation (9.3)
Now considering hd = 25 mm
Die plate thickness correction factor from Equation (9.5) is fd = 0.5 +0.02* hd = 1
Thus, total die manufacturing points are therefore Mp = fd*f1w*Mpo = 1*1.75*32 = 56
The estimated blanking die cost, assuming $40/hr for die making, is = Cds + Mp*40 = 255 + 56*40 = $2495. Scrap percent:
Area of each part is Ap = 51.52 cm2
Area of sheet used for each part is As = (15.5 + 0.204)*(4.6 + 0.204) = 75.44 cm2
Scrap % = (As – Ap)/As = .32 = 32 %
DFMA as Applied to the Swingline® 747 Desktop Stapler
20
Cost of piercing die: Cds = $255, L = 138.75 mm = 13.875 cm, W = 39.5 mm = 3.95 cm
The base manufacturing score from eq. (9.7) is
Mpo = 23 + 0.03 LW = 24.64
The number of hours required to manufacture the custom-punching element for the nonstandard aperture is, from Eq. (9.8)
Pp = 150.5 mm = 15.05 cm, Np = 3 Mpc = 8 + 0.6 * Pp + 3 Np = 26.03
The equipment manufacturing time for punches, die plate inserts is, from Eq. (9.9) Round holes K = 2, Np = 4, Nd = 1 Mps = K*Np + 0.4 Nd = 8.4
The estimated piercing die cost, assuming $40/h for die making, is = Cds + ( Mpo + Mpc + Mps )*40 = $2617.8 = $2620 Cost of bending die: Cds = $255, L = 155 mm = 15.5 cm, W = 46 mm = 4.6 cm, D = 1.7 cm
Basic die manufacturing score for bending Mpo = (18 + 0.023LW)*(0.9 + 0.02 D) = 18.34
Additional point for bend length and multiple bends Lb = 26.225 cm, Nb = 3 Mpn = 0.68 Lb + 5.8 Nb
DFMA as Applied to the Swingline® 747 Desktop Stapler
21
= 35.233
The estimated bending die cost, assuming $40/h for die making, is = Cds + ( Mpo + Mpn) * 40 = $2397.92 = $2400 Cost of embossing die: Cds = $255, L = 80 mm = 8 cm, W = 26 mm = 2.6 cm, Mpx = 0.13 Nsp Mpo = 23 + 0.03 LW Mpc = 8 + 0.6 Pp + 3 Np
Therefore, Mpo = 23.624
Rectangular embossing Mpx = 4 *(0.13*3) = 1.56
Circular embossing Mpx = 2 * (0.13 * 1) = 0.26
Total Mpx = 1.82 Mpc = 8 + 0.6 * 7.8 + 3 * 6 = 30.68
Cost of embossing die is,
= Cds + ( Mpo + Mpc + Mpx) * 40 = $2500
DFMA as Applied to the Swingline® 747 Desktop Stapler
22
Cost of progressive die: Cd = 2 Cid
Where Cid = 2495 + 2620 + 2400 + 2500 = $10015 Cd = $20030 Cycle time for each part: U = 90*103KN/m2 h = 1.02 mm = 1.02 * 10-3 m
Force for Blanking: Fblanking = 0.5UhLs
Where Ls = length to be sheared = 39.55 cm = 0.3955 m Fblanking = 18.15 KN
Force for Punching: Fpunching = 0.5UhLs
Where Ls = 210 mm = 0.21m Fpunching = 9.65 KN
Force for Embossing:
For one embossing Fembossing = UhLsSinθ = 5.06 since Ls = 0.078m Total Fembossing = 6 * 5.06 (As they are six embossing effects) = 30.38 KN
Force for Bending: Fbendung = 0.08UhLb
Where Lb = Length of bend = 26.225 cm = .26225 m
DFMA as Applied to the Swingline® 747 Desktop Stapler
23
Fbendung = 1.92 KN
So, Total force required = Fblanking + Fpunching + Fembossing + Fbendung = 60 KN
From Table 9.3 The space required for 4 die stations is, 4*14.6 = 58.4
From Table 9.8 Appropriate press for 58.4 is 500 KN press force, $76/hr operating cost and
speed of 90 strokes/min.
The estimated cycle time per part is, t = 60/90 =0.67 sec
Processing cost per part is Cp = (0.67/3600)*76*100 = 1.4 cents. 2.4aiii For the remaining parts, the analysis is abbreviated: Staple slide:
Cost for progressive die = $9120 Cycle time = 0.6 sec Processing cost per part = Cp = 0.91 cents
Redesigned staple slide:
Cost for progressive die = $8500.00 Cycle time = 0.6 sec Processing cost per part = Cp = 0.91 cents
Anvil:
Cost for progressive die = $7590 Cycle time = 0.6 sec Processing cost per part = Cp = 0.91 cents
DFMA as Applied to the Swingline® 747 Desktop Stapler
24
Redesigned Anvil:
Cost for progressive die = $7050 Cycle time = 0.6 sec
Processing cost per part = Cp = 0.91 cents Upper Arm:
Cost for progressive die = $22,220 Cycle time = 0.67 sec
Processing cost per part = Cp = 1.4 cents Redesigned Upper Arm:
Cost for progressive die = $22,060 Cycle time = 0.67 sec
Processing cost per part = Cp = 1.4 cents Unmodified parts: Upper leaf spring:
Cost for progressive die = $9760.00 Cycle time = 0.6 sec Processing cost per part = Cp = 0.91 cents
Bottom Staple Guide:
Cost for progressive die = $9130.00 Cycle time = 0.6 sec Processing cost per part = Cp = 0.91 cents
End Cap:
Cost for progressive die = $5250.00 Cycle time = 0.6 sec Processing cost per part = Cp = 0.91 cents
DFMA as Applied to the Swingline® 747 Desktop Stapler
25
2.5 Assembly Paradigms
When designing for assembly, there are many varied considerations. As has been
the precedent, a brief discussion of the DFMA paradigms will be followed by application
of relevant paradigms to the Swingline 747 classic stapler. The object of design for
assembly is to provide the designers a tool for effective assembly considerations, to guide
the designers to simplicity, to provide information from experienced engineers early in
the process that will help less experienced designers, and to establish a database of
assembly times and cost factors. Most of the following information is taken from Product
DFMA, 2nd ed., hereafter referred to as PDFMA, by Boothroyd, Dewhurst, and Knight.
While there are tools and equations to be used for both manual and automated (robotic,
high-speed) assembly, the focus will remain on manual assembly since it is most
pertinent to the case at hand. Briefly, the main advantage for automation is the reduced
errors in assembly that lead to quality issues. The authors state, “… it is becoming widely
accepted that faulty assembly steps, rather than defective components, are more often the
reason for production quality problems.” For more information on automated assembly,
the interested reader is referred to the text. For manual assembly, there are several issues
to be considered.
2.5a Assembly Times and Efficiency
Assembly efficiency, also known as the DFA index, is vital to proper assembly
design. Two main factors that influence efficiency are the number of parts and the ease
of handling, inserting, and fastening those parts. To calculate the efficiency, Ema, the
following equation is given:
Ema = Nminta/tma
where Nmin is the theoretical minimum number of parts, ta is the basic assembly time for
one part, which is about 3 s, and tma is the estimated time to complete the assembly of the
entire product.
There are three time systems that can be used to estimate assembly times. One of
these, MOST, is used for very large parts which cannot be carried by workers. A lifting
device must be employed. Since this is beyond the scope of the example, it is not
discussed here. The other two systems, methods time measurement (MTM) and work
DFMA as Applied to the Swingline® 747 Desktop Stapler
26
factor (WF) are useful. Both of these use part symmetry in their assessment of assembly
times. The symmetry of a part can be regarded about two axes; the insertion axis and any
axis perpendicular to insertion. The angle associated with the former is known as the
beta angle, the angle around the latter is alpha. These both have reference to the
maximum number of degrees by which a part that has been grasped needs to be rotated to
repeat its orientation. The total symmetry of a part is given by adding these two angles.
The MTM system uses the maximum possible orientation, given by 0.5β. The WF uses a
combination of both in the form β/α .
2.5b Guidelines for Manual Assembly
Handling and insertion/fastening are the two main areas of assembly. Some
design guidelines for handling and insertion/fastening are:
• Symmetrical design. • Prevent jamming. • Prevent tangling. • Avoid hazardous parts (sharps, slippery, etc). • Minimize resistance to insertion. • Standardize. • Employ pyramid assembly. • Part location prior to release. • Simplify fastening. • Avoid repositioning.
When dealing with these guidelines, it is safe to assume that not all may be able to be
incorporated simultaneously. The benefits and costs of each attribute must be weighed
against the over-all picture.
2.5c Effects of Weight and Dimensions
It is considered that a part whose thickness is less than 2mm will be difficult to
grasp and require the use of tweezers or other implement, thus adding to the assembly
time. The size of a part, which is the longest non-diagonal length, is also a factor. The
weight of a part is also a consideration, not only for assembly, but also for ergonomic
concerns. Generally, weight causes parts to be categorized as being able to be lifted with
DFMA as Applied to the Swingline® 747 Desktop Stapler
27
one hand, two hands, two people, or by machine. Each of these has a different effect on
assembly time.
2.5d Chamfers
When dealing with insertion, chamfers will provide many benefits such as
reduced assembly time and incidents of jamming. Several parameters used to describe
attributes of both the pin and hole are listed in Table 5.
Table 5 – Insertion Parameters
The clearance c of the insertion is given by (D – d)/D and is dimensionless. PDFMA
presents the following conclusions regarding chamfer properties:
• For a given clearance, the insertion time for two different chamfer designs is constant.
• A chamfer on the peg is more effective than one on the hole. • The maximum effective chamfer width w is 0.1D. • The most effective conical chamfer design has chamfers on both hole and peg
with the widths equal to 0.1D and angles less than 45°. • Manual insertion time is not sensitive to angle changes from 10° to 50°. • For small c, round or conical chamfers can be more effective.
As the clearance decreases, the insertion time increases at various rates, depending on
whether there are chamfers on one or both parts involved or none. Another consideration
is when parts to be inserted jam. This is caused by one or more points of contact during
insertion. Different chamfer designs can alleviate this problem and reduce insertion time.
Insertion time can be estimated by the following equations:
D Diameter of hole. d Diameter of peg. L Length of insertion. w1 Width of peg
chamfer. w2 Width of hole
chamfer. θ1 Angle of peg
chamfer. θ2 Angle of hole
chamfer.
DFMA as Applied to the Swingline® 747 Desktop Stapler
28
ti = 1.4L + 15 ms or
ti = -70 ln c + f(chamfers) + 3.7L + 0.75d ms
whichever is larger and where f(chamfers) = -100 (no chamfer) -220 (chamfer on hole) -250 (chamfer on peg) -370 (chamfer on both) 2.5e Miscellaneous Effects on Assembly Time
When designing parts to be assembled, obstructed views and access should be
considered. The effects of an obstructed view or obstructed access are that time for
assembly is increased and there is also a risk of harm to the worker. The inability to see
the parts can lead to fumbling, dropping or other time penalties, and obstruction may
force the worker to slow down, cause repeated small motions in awkward positions (i.e.
ulnar-deviated wrists while turning a wrench). The cost of time and ergonomics then
becomes an issue. Manual clamping also has a deleterious effect on time and has
ergonomic considerations. There are many parameters, born both empirically and by
experience, which bear consideration while designing for manual assembly. However,
the data presented are averages and therefore should not be taken to be cumulative. In
some cases, the times are overestimated, in others it is underestimated. Also, in the
situation where the assembly requires various different parts, care should be taken not to
accumulate times caused by different features. Only when large quantities of similar
parts are used should these results be consulted.
2.5f Further Guidelines
The minimum parts criteria also give the following guidelines:
• Avoid connections by placing parts to be connected at the same location. • Design so that assembly access is not restricted. • Avoid adjustments. • Use kinematic design principles to avoid over-constrained designs.
Also, for large assemblies with large numbers of parts, the differences in assembly time
generated by different parts will generally cancel each other out.
DFMA as Applied to the Swingline® 747 Desktop Stapler
29
2.5g Assembly Layout
Depending on the size of the largest parts in an assembly, the layout of the assembly area
will differ. For small parts that can be placed within easy reach of the worker, the bench
or multi-station assembly methods are recommended (figs. 23 and 24). This layout
eliminates major body motion of the worker, reducing part retrieval time and cumulative
trauma disorders. For parts weighing more than 5 lbs but less than 30 lbs, or are longer
than 12 in. but less than 35 in., the modular assembly center is recommended (fig. 25).
There are three categories that determine which modular layout to use. These are based
upon the largest part being less than 15 in., between 15 and 25 in., and between 25 and 35
in. Larger parts will best be assembled in a custom assembly layout or a flexible
assembly layout (figs. 26 and 27). Other layouts do exist, such as on-site (i.e. for an
elevator), in clean rooms (microprocessors), modular assembly for very large parts
(automobiles), etc.
Figure 23 – Bench Station [4] Figure 24 – Multi-Station [4]
Figure 25 – Modular Station [4]
DFMA as Applied to the Swingline® 747 Desktop Stapler
30
2.6 Assembly Methods – Stapler
Table 6 gives the alpha, beta, and handling times data for the various parts. This
data is derived from Tables 3.15 to 3.17 in PDFMA. A bench station assembly layout is
assumed.
Table 6 – Handling Times Data
No. Component or
Operation
Alpha Angle α
Beta Angle β
Symm. Angle
(α+β)
No. of
Items RP
Hand- ling
Time TH
Tool Acquire
Time TA
Inser- tion
Time TI
Time (s) TA+RP* (TH+TI)
Steps
1 Base 360 360 720 1 1.95 0 1.5 2.45 Place on Worksurface
2 Release Clip 360 360 720 1 3.34 0 3.0 6.34 Add
3 Lower Leaf Spring 360 360 720 1 2.25 2.9 2.6 7.75 Add Fasten
4 Anvil Actuator 360 0 360 1 1.13 2.9 2.6 6.63 Add Hold
5 Reorientation - - - 1 - - 4.5 4.5 Reorient
6 Anvil 360 180 540 1 2.36 2.9 2.6 7.86 Rivet
7 Set Aside - - - 1 - - 1.0 1.0 Special
8 Top Staple Guide 360 360 720 1 3.06 0 1.5 4.56 Place on Worksurface
9 Spring 180 0 180 1 2.25 0 5.2 7.45 Add
10 Staple Slide 360 360 720 1 2.73 0 1.5 4.23 Add
11 Bottom Staple Guide 360 360 720 1 3.06 0 1.5 4.56 Add
12 Upper Arm 360 360 720 1 1.95 2.9 4.5 9.35 Add
13 Set Aside - - - 1 - - 1.0 1.0 Special
14 Upper Cover 360 360 720 1 1.95 0 1.5 3.45 Place on Worksurface
15 Upper Leaf Spring 360 360 720 1 2.51 2.9 2.6 8.01 Add Fasten
16 Reorientation - - - 1 - - 4.5 4.5 Special
17 Pin 360 0 360 1 1.8 2.9 2.6 7.3 Add
18 Add Subassembly - - - 1 - - 4.5 4.5 Special
19 Spacer 360 180 540 1 2.36 0 1.8 4.16 Add
20 Plastic Cover 360 360 720 1 2.51 0 1.8 4.31 Add
21 Rubber Pad 360 360 720 1 1.95 0 3.0 4.95 Add
Figure 27 – Flexible Layout [4] Figure 26 – Custom Layout [4]
DFMA as Applied to the Swingline® 747 Desktop Stapler
31
The total assembly time can therefore be derived from Table 6 to be 108.86 seconds.
2.6a Efficiency
Using Nmin = 19 (two fasteners), ta = 3 seconds, and tma = 108.86 seconds from
Table 6, the efficiency for assembling t he stapler is then 53%.
2.6b Chamfers The insertion of the pin and the anvil actuator are subjects for chamfer analysis.
We present the analysis for the pin only. Table 7 gives the chamfer dimensions for the
pin.
Table 7 – Insertion Parameters for the Pin
There is no chamfer around the insertion point. The pin has a rounded chamfer, therefore
no angle or chamfer width is given. From these data, we can calculate the clearance c
between the pin and the base to be 0.016 in. Since the clearance is so small, the pin uses
a rounded chamfer. The insertion time is 44.2 ms using ti = -70 ln c + f(chamfers) + 3.7L
+ 0.75d where f(chamfers) is -250. Despite the fact that insertion into the base, cover,
and subassemblies is progressive, we consider the diameters D to be the same and the
length L to be the entire width of the base along the insertion axis. As the pin is inserted
and parts through which it travels added, the stability of the pin increases. There is also
the draft on the base to consider. Since the clearance is such that the pin is inserted rather
easily, the draft need not be a concern.
2.7 Recommended Changes
A few changes in the manufacturing process led directly to changes in assembly.
For instance, if the spring is halved and the upper staple guide is redesigned, the spring
D 0.189
d 0.186 L 1.253
w2 0 θ2 0
DFMA as Applied to the Swingline® 747 Desktop Stapler
32
no longer has to be threaded through the guide, saving on handling time. The time to set
the guide aside, insert the staple slide, and then later reacquire the guide is also reduced.
These have the effect of cutting the total assembly time from 108.86 to 97.86 and
increasing the efficiency from 53% to 58%. All other processes and methods were
believed to be adequate and therefore left unchanged.
3 Discussions
Due to numerical analyses performed on changes that were suggested, it was
determined that the overall design of the 747 stapler is adequate. The manufacturing cost
savings of $3650.00 for re-tooling, die costs, etc. and the assembly time savings of only
11 seconds do not justify implementation of those changes. For example, the time
savings only yields a 6-cent per unit saving. One such manufacturing change that DFM
suggested was to change the anvil manufacture method from blanking to cut off. This
would result in a savings in cost through die, reduced scrap, and cycle time. However,
DFA showed that it should not be implemented due to the sharp corners that would be a
safety issue both in the assembly and daily use of the product. Also, strength analysis
revealed residual stresses at the corners. Another change implemented was to create a
two-part foot pad. DFM recommended this change based on saving in time, cost and die
manufacture and reduced cycle time. Again, DFA showed this change to be unwarranted.
A basic principle of DFA was violated; reduce part numbers.
Thought was given into changing the materials in the manufacture of the stapler.
The DFM material selection analyses run according to Boothroyd-Dewhurst [4] revealed
that the material selected were already DFM compliant. However, consideration was
given to the use of plastics, particularly for the cover and the base. These changes were
ultimately rejected due to durability factors, cyclic loads, and severe impact safety factors.
Also, Swingline® makes different models made with plastic. Had the recommendations
to change the 747 to plastic been implemented, there would have been a reduction in the
variety offered to the consumer.
DFMA as Applied to the Swingline® 747 Desktop Stapler
33
4 Conclusions
In general, a strict application of DFMA paradigms may give rise to contradictory
recommended changes in the design of a project. For the Swingline® 747 desktop stapler
such contradictions were evident. Some recommendations can also be made which are
wholly unsuitable for the task at hand. In any case, applying DFMA can and does reduce,
at least in part, the costs associated with the bringing to market of a product. Those costs
can be associated with manufacture, assembly, material selection, etc. or any combination
of these.
With regards to the stapler at hand, the overall results of our DFMA application
yielded some worthwhile recommendations. Five parts were redesigned from a
manufacture point of view which reduced the time and cost of manufacture. An added
bonus to those changes was a time and cost saving at the assembly stage. However, most
of the components, from the point of view of both material selection and manufacture,
and of assumed assembly methods of the stapler, proved to be very acceptable. It is, after
all, the Swingline® Classic™ stapler.
34
NOTE: The best and the worst materials obtained after running the DFMA
analysis for all the parts are represented by bold characters in the
Tables.
Part 1. Rubber Base.
No analysis was run. It could be recommended that the rubber base be
eliminated and instead have two foot pads at each one of the ends. This would in
turn save money which otherwise would be needed for the molding of rubber
base. This also reduces assembly time.
Fig A -1 Base Fig A-2 Alternate
The figures seen above are the two different designs discussed previously. Part 2: Release Clip:
The release clip is made of aluminum alloy.
Analysis Run for Strongest Beam and Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 43 Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88
APPENDIX A
35
Copper, hard 24
Analysis Run for Strongest Beam and Minimum Weight, Their Respective Index
Values:
Gray cast iron 20 Ductile iron 44 Malleable iron 26 Mild steel 7 Alloy steel 93 Stainless steel 0 Aluminum alloy 100 Beryllium copper 76 Copper, hard 0
Analysis Run for Strongest Beam and Minimum Cost, Their Respective Index
Values:
Gray cast iron 100 Ductile iron 100 Malleable iron 92 Mild steel 68 Alloy steel 45 Stainless steel 44 Aluminum alloy 50 Beryllium copper 0 Copper, hard 43
Part 3: Lower Leaf Spring:
The lower leaf spring is made of alloy steel.
Analysis Run for Best Diaphragm Spring and Max Performance, Their
Respective Index Values:
Gray cast iron 23 Ductile iron 39 Malleable iron 26 Mild steel 0 Alloy steel 95
36
Stainless steel 0 Aluminum alloy 24 Beryllium copper 100 Copper, hard 32
Analysis Run for Best Diaphragm Spring and Minimum Weight , Their Respective
Index Values:
Gray cast iron 28 Ductile iron 44 Malleable iron 29 Mild steel 2 Alloy steel 97 Stainless steel 0 Aluminum alloy 65 Beryllium copper 100 Copper, hard 28
Analysis Run for Best Diaphragm Spring and Minimum Cost, Their Respective
Index Values:
Gray cast iron 93 Ductile iron 100 Malleable iron 82 Mild steel 34 Alloy steel 54 Stainless steel 1 Aluminum alloy 33 Beryllium copper 0 Copper, hard 22
Part 4: Anvil:
The anvi l is made of alloy steel.
Analysis Run for Strongest Beam and Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 43
37
Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88 Copper, hard 24
Analysis Run for Strongest Beam and Minimum Weight, Their Respective Index
Values: Gray cast iron 20 Ductile iron 44 Malleable iron 26 Mild steel 7 Alloy steel 93 Stainless steel 0 Aluminum alloy 100 Beryllium copper 76 Copper, hard 0
Analysis Run for Strongest Beam and Minimum Cost, Their Respective Index
Values:
Gray cast iron 100 Ductile iron 100 Malleable iron 92 Mild steel 68 Alloy steel 45 Stainless steel 44 Aluminum alloy 50 Beryllium copper 0 Copper, hard 43
Part 5: Base:
The Base is made of aluminum alloy.
38
Analysis Run for Strongest Beam and Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 43 Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88 Copper, hard 24
Analysis Run for Strongest Beam and Minimum Weight, Their Respective Index
Values:
Gray cast iron 20 Ductile iron 44 Malleable iron 26 Mild steel 7 Alloy steel 93 Stainless steel 0 Aluminum alloy 100 Beryllium copper 76 Copper, hard 0
Analysis Run for Strongest Beam and Minimum Cost, Their Respective Index
Values:
Gray cast iron 100 Ductile iron 100 Malleable iron 92 Mild steel 68 Alloy steel 45 Stainless steel 44 Aluminum alloy 50 Beryllium copper 0 Copper, hard 43
39
Part 6: Anvil Actuator:
The anvil actuator is made of aluminum alloy.
Analysis Run for Strongest Beam and Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 43 Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88 Copper, hard 24
Analysis Run for Strongest Beam and Minimum Weight, Their Respective Index
Values:
Gray cast iron 16 Ductile iron 41 Malleable iron 24 Mild steel 5 Alloy steel 100 Stainless steel 0 Aluminum alloy 47 Beryllium copper 84 Copper, hard 7
Analysis Run for Strongest Beam and Minimum Cost, Their Respective Index
Values:
Gray cast iron 94 Ductile iron 100 Malleable iron 88 Mild steel 58
40
Alloy steel 54 Stainless steel 30 Aluminum alloy 34 Beryllium copper 0 Copper, hard 32
Part 7: Spacer:
Remarks:
Made of plastic. No analysis was run for the spacer.
Part 8: Spring:
The spring is made of alloy steel (spring steel).
Analysis Run for Best Coil Spring and Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 40 Malleable iron 25 Mild steel 1 Alloy steel 99 Stainless steel 0 Aluminum alloy 15 Beryllium copper 100 Copper, hard 28
Analysis Run for Best Coil Spring and Minimum Weight, Their Respective Index
Values:
Gray cast iron 24 Ductile iron 43 Malleable iron 28 Mild steel 2 Alloy steel 100 Stainless steel 0
41
Aluminum alloy 46 Beryllium copper 99 Copper, hard 25
Analysis Run for Best Coil Spring and Minimum Cost, Their Respective Index
Values:
Gray cast iron 87 Ductile iron 100 Malleable iron 80 Mild steel 31 Alloy steel 73 Stainless steel 0 Aluminum alloy 26 Beryllium copper 21 Copper, hard 23
Part 9: Pin:
The pin is made of alloy steel.
Analysis Run for Strongest Beam and Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 43 Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88 Copper, hard 24
Analysis Run for Strongest Beam and Minimum Weight, Their Respective Index
Values:
Gray cast iron 20 Ductile iron 44
42
Malleable iron 26 Mild steel 7 Alloy steel 93 Stainless steel 0 Aluminum alloy 100 Beryllium copper 76 Copper, hard 0
Analysis Run for Strongest Beam and Minimum Cost, Their Respective Index
Values:
Gray cast iron 100 Ductile iron 100 Malleable iron 92 Mild steel 68 Alloy steel 45 Stainless steel 44 Aluminum alloy 50 Beryllium copper 0 Copper, hard 43
Part 10: Staple Slide:
The staple slide is made of alloy steel.
Analysis Run for Strongest Compression Member and Max Performance, Their
Respective Index Values:
Gray cast iron 21 Ductile iron 24 Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88 Copper, hard 24
43
Analysis Run for Strongest Compression Member and Minimum Weight, Their
Respective Index Values:
Gray cast iron 16 Ductile iron 20 Malleable iron 24 Mild steel 5 Alloy steel 100 Stainless steel 0 Aluminum alloy 47 Beryllium copper 84 Copper, hard 7
Analysis Run for Strongest Compression Member and Minimum Cost, Their
Respective Index Values:
Gray cast iron 100 Ductile iron 96 Malleable iron 94 Mild steel 62 Alloy steel 57 Stainless steel 32 Aluminum alloy 36 Beryllium copper 0 Copper, hard 34
Part 11: Bottom Staple Guide:
The staple bottom guide is made of aluminum alloy. No analysis was carried out
for the bottom s taple guide.
Part 12: Upper Arm:
The upper arm is made of alloy steel.
44
Analysis Run for Strongest Beam and Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 43 Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88 Copper, hard 24
Analysis Run for Strongest Beam and Minimum Weight, Their Respective Index
Values:
Gray cast iron 20 Ductile iron 44 Malleable iron 26 Mild steel 7 Alloy steel 93 Stainless steel 0 Aluminum alloy 100 Beryllium copper 76 Copper, hard 0
Analysis Run for Strongest Beam and Minimum Cost, Their Respective Index
Values:
Gray cast iron 100 Ductile iron 100 Malleable iron 92 Mild steel 68 Alloy steel 45 Stainless steel 44 Aluminum alloy 50 Beryllium copper 0 Copper, hard 43
45
Part 13: Top Staple Guide:
The top staple guide is made of aluminum alloy. No analysis carried out for the
top staple guide.
Part 14: The End Cap (747):
The end cap is made of alloy steel.
Analysis Run for Strongest Beam Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 43 Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88 Copper, hard 24
Analysis Run for Strongest Beam and Minimum Weight, Their Respective Index
Values:
Gray cast iron 20 Ductile iron 44 Malleable iron 26 Mild steel 7 Alloy steel 93 Stainless steel 0 Aluminum alloy 100 Beryllium copper 76 Copper, hard 0
46
Analysis Run for Strongest Beam and Minimum Cost, Their Respective Index
Values:
Gray cast iron 100 Ductile iron 100 Malleable iron 92 Mild steel 68 Alloy steel 45 Stainless steel 44 Aluminum alloy 50 Beryllium copper 0 Copper, hard 43
Part 15: Upper Leaf Spring:
The upper leaf spring is made of alloy steel.
Analysis Run for Best Diaphragm Spring and Max Performance, Their
Respective Index Values:
Gray cast iron 23 Ductile iron 39 Malleable iron 26 Mild steel 0 Alloy steel 95 Stainless steel 0 Aluminum alloy 24 Beryllium copper 100 Copper, hard 32
Analysis Run for Best Diaphragm Spring and Minimum Weight , Their Respective
Index Values:
Gray cast iron 28 Ductile iron 44 Malleable iron 29 Mild steel 2 Alloy steel 97
47
Stainless steel 0 Aluminum alloy 65 Beryllium copper 100 Copper, hard 28
Analysis Run for Best Diaphragm Spring and Minimum Cost, Their Respective Index Values: Gray cast iron 93 Ductile iron 100 Malleable iron 82 Mild steel 34 Alloy steel 54 Stainless steel 1 Aluminum alloy 33 Beryllium copper 0 Copper, hard 22
Part 16: Upper Cover:
The upper cover is made of aluminum alloy.
Analysis Run for Strongest Beam and Max Performance, Their Respective Index
Values:
Gray cast iron 21 Ductile iron 43 Malleable iron 30 Mild steel 16 Alloy steel 100 Stainless steel 13 Aluminum alloy 0 Beryllium copper 88 Copper, hard 24
48
Analysis Run for Strongest Beam and Minimum Weight, Their Respective Index
Values:
Gray cast iron 20 Ductile iron 44 Malleable iron 26 Mild steel 7 Alloy steel 93 Stainless steel 0 Aluminum alloy 100 Beryllium copper 76 Copper, hard 0
Analysis Run for Strongest Beam and Minimum Cost, Their Respective Index
Values: Gray cast iron 100 Ductile iron 100 Malleable iron 92 Mild steel 68 Alloy steel 45 Stainless steel 44 Aluminum alloy 50 Beryllium copper 0 Copper, hard 43
Part 17. Plastic Cap.
Remarks: Made of plastic. No analysis was run for the plastic cap.
49
Manufacturing Process
The appendix C is meant to illustrate the various Manufacturing steps involved in
the making of the Upper Arm. At attempt using Pro – E to show the various steps
has been made.
Step 1
The first step would be to blank the outline of the part and then pierce out the
holes in the part. The assumption in making this part is to use a progressive die.
APPENDIX B
50
Step 2 The 2nd step as seen in the above figure is to bring in the initial bends to as
indicated by the circles.
Step 3 Finally in step 3 we bring in the side bends which gives us the final shape of the
part.
We have similarly simulated the manufacturing processes of all the parts.
However the Pro-E drawings were made only for a few parts.
51
The Pro-E part sketches of following parts have been attached. The parts being,
Sl No Part Name 1 Lower leaf Spring 2 Base 3 Spacer 4 Staple Slide ( Old Design) 5 Staple Slide ( New Design) 6 Bottom Staple Guide 7 Upper Arm ( Old Design) 8 Upper Arm ( New Design) 9 Upper Staple Guide (Old Design) 10 Upper Staple Guide (New Design) 11 End Cap 12 Upper Leaf Spring 13 Upper Cover 14 Plastic Cap
Note: The Pro-E drawings for the parts mentioned in the above table have been attached.
APPENDIX C
1. www.swingline.com
2. www.page.sannet.ne.jp/ gaho1300/proe/ practical_guide /hd90013/index_hd90013.html
3. www.materials.eng.com.ac.uk/mpsite
4. Boothroyd, G., 1988, Dewhurst, P., Product Design for Manufacture and Assembly.
5. http://www-ec.njit.edu/~das/1-1-2.html
6. http://www.tm.tue.nl/race/ce/dfma_2.html
7. A. U. Alvi and A. W. Labib, ‘Selecting Next-generation Manufacturing Paradigms - An Analytic Hierarchy Process-based Criticality Analysis’ Proc Instn Mech Engrs Vol 215 Part B , 2001 Pg. 1773-1786
8. Tomiyama, T. A manufacturing paradigm towards the 21st century. Integrated Computer Aided Engg, 1997, 4, 159-178.
9. http://www.dfma.com/news/dfmcost_news.html
10. Stoll, H.W., 1986, Design for Manufacture: An overview 11. http://www.scs.unr.edu/mecheng/me151/dfm/sld005.htm
References