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MECE E3430 Engineering Design
Spring 2013
Group 2
Ivett Ortega
Wole Oyelola
Claudia Vargas
Columbia University
Department of Mechanical Engineering
February 21, 2013
Executive Summary
In this paper the analysis and design of a magnetic bearing system consisting of both a passive
axial magnetic bearing and an active two-axis radial magnetic bearing is presented. The passive
magnetic bearing employs a set of permanent magnets to supply an axial position stiffness to
stabilize the rotor. The active two-axis radial magnetic bearing uses four electromagnets to
stabilize the rotor on the axes perpendicular to the rotation axis. The analysis of both bearings
used in this system was performed using Finite Element Method Magnetics. Furthermore, several
testing methods are described in order to validate the stability of the system, as well as assess the
response of the control system.
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TABLE OF CONTENTS
1. CONCEPT SELECTION ............................................................................................................................. 1
2. FINAL CONCEPT DESCRIPTION ........................................................................................................... 1
3. LITERATURE SEARCH RESULTS .......................................................................................................... 1
4. SPECIFICATIONS AND PARAMETER ANALYSIS .............................................................................. 3
4.1 Shaft Specifications .................................................................................................................................... 3
4.2 Shaft Analysis ............................................................................................................................................. 3
4.3 Active Magnetic Bearing Specifications .................................................................................................... 3
4.4 Passive Magnetic Bearing Specifications ................................................................................................... 6
4.5 Active and Passive Magnetic Bearing Analysis ......................................................................................... 6
5. FINAL DESIGN ............................................................................................................................................ 8
6. PLAN .............................................................................................................................................................. 9
7. PROBLEM ANALYSIS................................................................................................................................ 9
8. CONCLUSION ............................................................................................................................................ 10
9. REFERENCE LIST .................................................................................................................................... 11
1. APPENDICIES ............................................................................................................................................ 13
1.1 Appendix A: Creo Models & Dimensions ................................................................................................ 13
1.2 Appendix B: Calculations ......................................................................................................................... 34
1.3 Appendix C: FEMM and Creo Analysis .................................................................................................. 35
1.4 Appendix D: Manufacturer Specifications ............................................................................................... 37
1.5 Appendix E: Circuit Diagrams ................................................................................................................. 41
1.6 Appendix F: Budget ................................................................................................................................. 42
1.7 Appendix G: Gantt Chart .......................................................................................................................... 43
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LIST OF FIGURES
FIGURE 1: STATOR CROSS SECTION (ELECTROMAGNET SIDE) ......................................................... 4
FIGURE 2: STATOR CROSS SECTION (SENSOR SIDE) ......................................................................... 5
FIGURE 3: STATOR EXPLODED VIEW ............................................................................................... 5
FIGURE 4: PERMANENT MAGNETIC BEARING .................................................................................. 6
FIGURE 5: FEMM ANALYSIS, ACTIVE MAGNETIC BEARING ........................................................... 7
FIGURE 6: FEMM ANALYSIS, PERMANENT MAGNETIC BEARING .................................................... 8
FIGURE 7: COMPLETE ASSEMBLY .................................................................................................... 8
Appendix A
FIGURE A- 1: AMB STATOR FRONT VIEW WITH ELECTROMAGNET ............................................... 13
FIGURE A- 2: AMB STATOR BACK VIEW WITH PHOTOTRANSISTORS (NO BACK PLATE) .............. 13
FIGURE A- 3: AMB EXPLODED VIEW WITH FRONT AND BACK PLATES ......................................... 14
FIGURE A- 4: AMB CROSS-SECTIONAL VIEW WITH ELECTROMAGNET ......................................... 14
FIGURE A- 5: COMPLETE ASSEMBLY WITH TWO AMBS, PMB AND WATER WHEEL ...................... 15
FIGURE A- 6: SIDE VIEW OF COMPLETE ASSEMBLY ....................................................................... 15
FIGURE A- 7: WATER WHEEL ........................................................................................................ 16
Appendix C
FIGURE C- 1: CREO ANALYSIS FOR MATERIAL STRENGTH OF ROTOR AT 2000 RPM .................... 35
FIGURE C- 2: FEMM ANALYSIS OF AMB WITH MAGNETIC FIELD DENSITY ................................. 36
FIGURE C- 3: FEMM ANALYSIS OF PMB WITH MAGNETIC FIELD DENSITY .................................. 36
Appendix D
FIGURE D- 1: B666 PULL FORCE BETWEEN TWO MAGNETS AS A FUNCTION OF DISTANCE BETWEEN
MAGNETS (COURTESY OF K&J MAGNETICS, INC.) ................................................................. 38
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FIGURE D- 2: FEMM ANALYSIS OF B666 MAGNETIC FIELD DENSITY (COURTESY OF K&J
MAGNETICS, INC.) ................................................................................................................. 39
FIGURE D- 3: APW ELECTROMAGNET, GAUSSES AS A FUNCTION OF DISTANCE ........................... 40
Appendix E
FIGURE E- 1: QRD1114 SENSOR CIRCUIT ..................................................................................... 41
FIGURE E- 2: CONTROL COMPENSATOR CIRCUIT FOR ONE ELECTROMAGNET ............................... 41
Appendix G
FIGURE G- 1: GANTT CHART.......................................................................................................... 43
LIST OF TABLES
Appendix F
TABLE F- 1: BUDGET ..................................................................................................................... 42
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1. CONCEPT SELECTION
Initially, the focus was to design a single AMB using four electromagnets. One of the major
limitations to this design was the original $500 budget. Feedback from Design Review I
expressed concerns with axial movement of the shaft as well as inducing a rotation on the shaft
for testing. Based on this feedback the subsequent version of the design intended to use an axial
PMB and two AMBs, each containing three electromagnets. The decision to use three
electromagnets in each AMB was a result of the fact that more using more than six
electromagnets would have increased the project cost by requiring an Arduino with 8 PWM
inputs. One downside to this new design was that the control system for a three pole AMB
quickly becomes very complex, based on information from various journal articles. Ultimately,
the leading factor in the final design decision explained below was the increase in the budget to
$1,125.
2. FINAL CONCEPT DESCRIPTION
The final design employs two AMBs to stabilize the shaft in the z-direction along the entire
length of the shaft. A PMB is used to maintain a position in the axial direction, as little instability
will be present in this direction. Each AMB will contain four electromagnets and will be used to
control the x and y-axis, which are more prone to instability. All electromagnets will be
purchased in order to guarantee their functionality. Furthermore, the decision to purchase
electromagnets with north and south poles on the same face was made in order to provide a
substantial attractive force.
3. LITERATURE SEARCH RESULTS
Information collected from the literature review assisted in the decision to pursue the design of a
hybrid magnetic bearing. The advantage of a hybrid bearing to this project is that it has been
tested by many different people and groups before; therefore many journal articles and patents
related to the topic are available. Many of the journals deal with complex issues that stem from
magnetic bearing designs; however, they provide a substantial amount of information helpful to
this project.
Several articles showed that the majority of radial magnetic bearings utilize an eight-magnet, or
eight-pole, design. Due to budget constraints, this design employs a lesser number of poles. In
order to obtain an understanding of the physics behind a system utilizing fewer poles, “Optimal
design of a three-pole active magnetic bearing” by Chen and Chan-Tang was reviewed. This
paper outlines the importance of the orientation of the poles with respect to the center, the bias
current required to support the force balance condition between the rotor and the stator, and
helpful information regarding the calculation of the magnetic circuit and flux.
The text Magnetic Circuit: Electromagnetic Engineering by Karapetoff allowed for further
understanding of the concepts of magnetic circuits. The text “Introduction to Electrodynamics”
by Griffith was also consulted to review some necessary topics regarding electromagnetism. In
order to examine a more complete picture of the possible body friction losses due to eddy
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currents and hysteresis, the paper “Design and analysis of a novel low loss homopolar
electrodynamic bearing” by Lembke as also referenced.
The poles are each at a 90⁰ with respect to each other in our design. We made this decision after
reviewing the considerations in the paper by Chen. In this paper, the magnetic bearing analyzed
utilized three poles and had them in a “Y” orientation. This orientation minimized the hysteresis
losses by giving the two upper poles the same bias current. For our four pole design, rather than
modeling an analogous “X” orientation, we decided that a cross orientation. This way the rotor
will be aligned directly with the top pole, and the two horizontal poles will have the same bias
current. This will greatly simplify the control system.
Using the patent search engine available to the United States Patent and Trademark Office
website, www.uspto.gov, we were able to find the patent US6664680, by searching the
keywords, “Active Magnetic Bearing Flywheel”. This patent is entitled Flywheel Device with
Active Magnetic Bearings. Upon reviewing the patent, we learned more about using flywheels as
a practical application of magnetic bearings. This patent argues the use of permanent magnets
rather than electromagnets to decrease power consumption, reduce cost, and increase reliability.
This patent also provides an inclusive control system block diagram.
From this patent we were able to obtain the following parameter to be used for a category search
in the USPTO databases.
310/90.5
o This subclass is indented under subclass 90. Subject matter wherein the bearing
has an induction field.
Because this category is so specific, we were able to find several patents that addressed our exact
project.
The first most relevant patent is titled “Magnetic bearing control device having a three-phase
converter, and use of a three-phase converter for controlling a magnetic bearing” (US8294314)
and provides an in-depth discussion on the control system used for the magnetic bearings. More
specifically, it addresses the hardware components needed to complete the task.
“Magnetic axial bearing and a spindle motor having this kind of magnetic axial bearing”
(US8212444) also provides a substantial amount of information related to our project. Although
it is important to note that this patent focuses on a rotating axial bearing, the methods of
employing permanent magnets and flux guide elements are still applicable to our project.
“Method and systems for operating magnetic bearings and bearingless drives” (US8115358)
focuses on the circuitry used to generate a signal for energizing the windings of the magnetic
bearing element. This addresses the issues of detecting the radial position of the element within
the bearing. According to this patent, this is a low-cost and efficient means for dynamically
suspending the rotor of the rotary device.
“Large gap horizontal field magnetic levitator” (US8169114) this last patent addresses magnetic
levitation conducted over large gaps. It is important to note that this patent discusses cases with
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two types of magnets, permanent magnets and electromagnets. In order to control the levitating
object the employment of a servomechanism is discussed.
All the patent searches provided very in-depth information on the details of magnetic bearings,
such as part arrangements, control system options, and control system components.
4. SPECIFICATIONS AND PARAMETER ANALYSIS
The specifications of this design are based on the optimal distance at which the electromagnets,
permanent magnet, and proximity sensors can function to levitate the intended mass.
4.1 Shaft Specifications
The design began with the selection of the shaft and shaft mass. A ¾ inch shaft was selected as
the levitation mass to present a reasonable distance between electromagnets in order to avoid any
interference between them. Unhardened steel was chosen as the shaft material for its strength,
machinability, and ferromagnetic properties. These ferromagnetic properties allow the shaft to be
levitated by the electromagnets; therefore the shaft will serve as the rotor for the AMB. A key
slot will be machined into the shaft for a key size of 0.1875 inches by 0.1875 inches, in order to
attach rotating parts.
In order to address the issue of rotating the shaft during testing as well as adding a rotating mass,
a water wheel has been added to the shaft. The water wheel will be secured using a key a ¾ inch
collar, acquired through Stock Drive, on either side. By applying compressed air to the water
wheel, rotation will be induced, and the effect on the control system will be tested. The speed of
the water wheel will be monitored using a tachometer to measure the RPM. Due to the shape, the
water wheel will be manufactured using the 3D printer.
4.2 Shaft Analysis
Using finite element method analysis on Creo, the strength of the shaft was tested to ensure the
material would not deform at high rotational speeds. Speeds of up to 2000 RPM were tested, and
it was found the shaft saw a maximum shear stress of 55,000 lbm/(in·s2). Unhardened steel can
withstand stresses up to approximately 13,000,000 lbm/(in·s2), thus material shearing is not a
concern.
4.3 Active Magnetic Bearing Specifications
The most critical portion of this design is that of the AMB stator. Each stator will include four
electromagnets, each at 90 degrees from each other, in order to fully constrain the x and y-axis.
The stator will also house the proximity sensors that detect the position of the shaft.
The selected electromagnets are designed with the north and south poles both present on the top
face. Note that as a result each electromagnet provides an attractive magnetic force. The
maximum holding force specified by the manufacturer is 25 lbf. (See Appendix A, APW
Company Drawing) The relationship between distance and electromagnetic gauss are also given
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by the manufacturer (see Appendix D, Figure D-3). This relationship was used to determine the
intended gap between the electromagnet and the shaft.
The electromagnets must be close enough to the rotor to induce a magnetic field strong enough
to levitate the shaft weight. The shaft and waterwheel have a combined weight of only 1.90 lbs.
The design will be capable of levitating 5 lbs, thus ensuring a 2.5 factor of safety. Based on these
parameters, the design allows for a 0.3 inch gap when the system is active and a 0.6 inch gap
when the system is inactive (see Appendix B).
In order to provide stability, each electromagnet will sit on a flat base within the stator which
includes a tapped hole to secure the electromagnet using a screw supplied by the manufacturer. A
channel will be machined from the electromagnet to the bottom of the stator in order to lead the
wiring to the control system without interfering with the other magnets, as shown in Figure 1.
Figure 1: Stator Cross Section (Electromagnet Side)
The housing for the proximity sensors must somewhat mirror that of the electromagnetic stator in
order to provide an appropriate measuring point to be fed back through the control system. To
avoid the need for two stators, the sensor housing is designed to sit on the other side of a thin
wall within the same stator as the electromagnet, see Figure 2. A sensor will be located next to
each of the electromagnets used such that each magnet can be independently and simultaneously
controlled based on the position of the shaft.
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Figure 2: Stator Cross Section (Sensor Side)
Each sensor is designed to detect distances between 0 and 0.78 inches (0 cm to 2 cm) (See
Appendix A). As a safety measure the sensor is designed to detect the shaft at a maximum
distance of 0.689 inches (1.75 cm), which occurs when the electromagnets are turned off and the
shaft is as far away from the top sensor as possible. When the AMB is active, the sensor will be
about 0.425 inches (~1 cm) from the shaft.
Each sensor includes four electrical leads; therefore this side of the stator also includes a channel
to lead the wiring out of the stator. One area of concern regarding the phototransistors is the
effect of light interference from the environment. In order to address this each sensor will sit
within a second wall in order to create a dark trench (See Appendix A, Figure A-4). Due to this
layout, the sensors will be secured to each wall using epoxy.
Figure 3: Stator Exploded View
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Based on these parameters, the final stator design is about 2.5 inches wide, 4.75 inches tall and
1.25 inches thick (See Appendix A, Drawing 4). Aluminum was selected as the material of the
stator and its plates due to its ease of machinability and ability to withstand a sudden drop of the
stator. The stator will be machined in three parts, as shown in Figure 3. The central portion of the
stator will be machined on both sides: one containing the electromagnet housing and the other
containing the proximity sensor housing. Two plates, each with a different interior diameter, will
be machined and secured to each side of the stator using four screws. It is important to note that
at no point in time will the rotor be sitting on an electromagnet. Due to the size of the inner
diameter of the sensor side plate, the shaft will sit on the sensor side of the stator when the
electromagnets are not active.
4.4 Passive Magnetic Bearing Specifications
In order to account for axial instability, a PMB is placed toward the end of the shaft. A set of
neodymium magnets are oriented with poles opposing each other to provide repulsive forces that
prevent axial movement. An acrylic ring mounted with eight neodymium magnets is attached to
the shaft via a key, and two stands each containing four appropriately oriented magnets are used
to repel these magnets from each side. The north poles of the magnets face each other on one
side, and the south sides of the magnets face each other on the other, as seen in Figure 4. At a
distance of 0.2 inches the magnets create a repulsion force of approximately 2 lbf – higher than
any axial force expected to be exerted on the shaft. See Appendix D for the pull force and
illustration of the magnetic field of the B666 neodymium magnet used.
Figure 4: Permanent Magnetic Bearing
4.5 Active and Passive Magnetic Bearing Analysis
The magnetic fields induced by the AMB and PMB were modeled using Finite Element Method
Magnetics or FEMM software. FEMM is a freeware package that utilizes finite element analysis
to solve electrodynamic problems. This program features meshing applications that operate
quickly in comparison to other programs of its kind. Unfortunately, FEMM has the drawback of
having only 2D capabilities and relatively weak drafting dexterity.
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The AMB was modeled as a frontal cross-section, showing effects in the x and y-axis. Each
electromagnet was assigned aluminum casing, coils of 26 AWG wire and 260 coil loops each, as
specified by the manufacturer. The cross section of the electromagnetic side of the stator
required that two rectangles be the model for the electromagnetic coils; one denoting current
entering the page, the other denoting current exiting the page. By the right-hand rule, the
magnetic field points either upward or downward in the y-direction, based on the direction of the
current loops.
The PMB was modeled including all three components (two stands and the ring on the stator)
from the side view, as it is designed to control the z-axis. The stands contained three squares
each, and the rotor contained six squares, each square representing a permanent magnet. Each
permanent magnet was assigned the material NdFeB, grade N42, as specified by the
manufacturer. The location of the north and south poles were then assigned for each magnet such
that they would have a repulsive alignment with respect to each of the three components.
Based on the design of the stator, the magnetization vector M is related to the vector potential, A.
By taking the integral twice, two boundary conditions were determined. These were used by the
program to map out finite element method meshes for both cases. These meshes were then used
to plot the magnetic field density for both the AMB and PMB.
Figure 5: FEMM Analysis, Active Magnetic Bearing
From the magnetic field density plot it is shown that the majority of the current must go through
the electromagnet at the top of the bearing. By integrating the area of the rotor, pictured in the
center, the magnetic flux through the rotor can be determined. The force applied on the rotor is
proportional to the magnetic flux squared. Using this information, the current required to lift the
rotor can be calculated.
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Figure 6: FEMM Analysis, Permanent Magnetic Bearing
As shown in the magnetic field density plot of the PMB, it is evident that the magnetic field lines
are less dense in between each cube magnet. This shows that the attractive magnetic forces will
not only be weak between each component, but in fact, the components will repel each other. As
the components get closer to each other the repulsive forces will increase, thus negating axial
fluctuations in the rotor.
5. FINAL DESIGN
The complete design of the system is shown in Figure 7. It consists of a 16 inch long ¾ inch steel
shaft that functions as the electromagnet bearing rotor, with active magnetic bearings as
stabilizers in the x and y-direction, permanent magnets for axial stability and a wheel that will be
used to rotate the shaft with compressed air. The complete assembly is 16 inches by 4 inches and
4.75 inches high. The wheel measures 4 inches in diameter and is 1 inch wide, and has angled
slots to allow air flow into it and induce a rotation.
Figure 7: Complete Assembly
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A QRD1114 sensor, which combines an infrared emitted diode with an infrared phototransistor
to detect the reflected infrared signal will be used to detect the distance from the sensor to the
shaft. The sensor will provide the circuit the information needed to determine how much current
to draw through each magnet, and therefore how much pulling force each magnet will exert. A
sensor will be located next to each of the electromagnets such that each magnet can be
independently and simultaneously controlled based on the position of the shaft. See Appendix E
for the sensor circuit diagram.
The current running through each magnet will be controlled using an Arduino Mega 2560 R3,
which has a clock speed fast enough to quickly adjust for the position of the shaft based on the
data obtained by the sensor. A preliminary circuit diagram for the AMB controller can be found
in Appendix E.
Appendix A contains dimensioned drawings of major components of the assembly, including
holes for screws and keys. Finally, a complete list of parts with vendors, part numbers, and costs
can be found in the budget in Appendix F.
6. PLAN
The next step in the project process is to complete a prototype using one electromagnet.
Prototyping is set to begin after receiving feedback from Design Review II. The Arduino,
proximity sensors and one electromagnet have been purchased and received. In addition, a
prototype stator has been 3D printed. This first test will consist of one magnet levitating a ¼ inch
steel rod. This will test the sensitivity of the phototransistor to light, the accuracy of our FEMM
analysis, and will help complete the final circuit used in the control system. In addition the shaft
will be spun manually to determine whether the control system can compensate for stability
induced by rotation.
Once the control system is working properly and the magnet and sensors have been tested, the
remaining parts will be ordered and assembly will begin. Manufacturing will begin the first week
of March, and all parts are to be completed by the end of that week. The complete assembly is
expected to be completed by April 1st (see Gantt chart in Appendix G for a complete schedule).
Future tests on the complete system will include spinning the shaft at several RPM and adding
additional weight to test the response of the control system.
7. PROBLEM ANALYSIS
In performing the material strength analysis of the shaft on Creo, the calculations were limited by
the types of analysis available on Creo. The structural integrity of the shaft was tested assuming
the ends were constrained, so there was no displacement in the z-direction, because there is no
option available for the centrifugal effects of rotation on a free-floating shaft. The results showed
that the maximum shear stress on the shaft was approximately 55,000 lbm/( in·s2) and steel can
withstand stresses of up to 13,000,000 lbm/( in·s2) . Therefore the analysis proves that even with
constraints at the ends of the shaft the maximum shear stress will not be reached. One of the risks
of using the FEMM software is that is only capable of models in two dimensions.
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8. CONCLUSION
The hybrid magnetic bearing design uses a combination of active magnetic bearings and a
passive magnetic bearing to levitate and stabilize a steel shaft while it rotates. A controller using
a phototransistor as a proximity sensor will adjust the amount of current going through each
electromagnet as needed to provide the correct amount of magnetic force needed to maintain
levitation of the shaft. A passive magnetic bearing at the end of the shaft will provide axial
stability to prevent the shaft from moving in the z-direction. Using a water wheel in the center,
compressed air will be used to rotate the shaft in order to show that the control compensator can
account for instability induced by shaft rotation.
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9. REFERENCE LIST
B. Shafai, S. Beale, P. LaRocca, and E Cusson, "Magnetic bearing control systems and adaptive
forced balancing," IEEE Contr. Syst. Mug., vol. 14, no. 2, pp. 4-13, Apr. 1994
Budig, P.-K.; , "On the theory and application of magnetic bearings," Systems, Signals and
Devices (SSD), 2012 9th International Multi-Conference on , vol., no., pp.1-9, 20-23
March 2012 doi: 10.1109/SSD.2012.6198013
http://ieeexplore.ieee.org/stamp/stamp.jsp?tp=&arnumber=6198013&isnumber=6197898
B. V. Jayawant, Electromagnetic Levitation and Suspension Techniques. UK: Edward Arnold,
1981.
Chen, Shyh-Leh, and Chan-Tang Hsu. "Optimal design of a three-pole active magnetic bearing."
Magnetics, IEEE Transactions on 38.5 (2002): 3458-3466.
Denk, Kopken, Stoiber, Wedel (2007) US8294314 Magnetic bearing control device having a
three-phase converter, and use of a three-phase converter for controlling a magnetic
bearing
F. Matsumura et al., “Fundamental equation of horizontal shaft magnetic bearing and its control
system,” Trans. JIEE, vol. 101-C, pp.
Gabrys (2001) US6664680 Flywheel Device with Active Magnetic Bearings
Griffiths, David J. Introduction to Electrodynamics. 3rd ed. Upper Saddle River, NJ: Prentice
Hall, 1999. Print.
Karapetoff, Vladimir. Magnetic Circuit: Electromagnetic Engineering. Palm Springs: Wexford
College, 2003. Print.
Lembke, Torbjörn A. Design and analysis of a novel low loss homopolar electrodynamic
bearing. Diss. KTH, 2005.
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M. S. de Queiroz and D. M. Dawson. Nonlinear control of active magnetic bearings: A
backstepping approach. IEEE Transactions on Control System Technology, 4(5):545-
552,
1996.
Popov, Bauer, Schmid, Schwamberger (2008) US8212444 Magnetic axial bearing and a spindle
motor having this kind of magnetic axial bearing
Rakov (2009) US8115358 Method and systems for operating magnetic bearings and bearingless
drives
Samanta, P.; Hirani, H.; , "Magnetic Bearing Configurations: Theoretical and Experimental
Studies," Magnetics, IEEE Transactions on , vol.44, no.2, pp.292-300, Feb. 2008 doi:
10.1109/TMAG.2007.912854
URL:
http://ieeexplore.ieee.org/stamp/stamp.jsp?tp=&arnumber=4432699&isnumber=4432685
Schweitzer, G. "Active Magnetic Bearings - Chances and Limitations." International Centre for
Magnetic Bearings, n.d. Web. 11 Nov. 2012. http://www.mcgs.ch/web-content/AMB-
chances_and_limit.pdf
Setiawan, Joga D., Ranjan Mukherjee, and Eric H. Maslen. "Adaptive Compensation of Sensor
Runout for Magnetic Bearings With Uncertain Parameters: Theory and Experiments."
Journal of Dynamic Systems, Measurement, and Control 123.2 (2001): 211. Print.
Simon (2010) US8169114 Large gap horizontal field magnetic levitator
T. Lembke (2005). PhD Thesis "Design and Analysis of a Novel Low Loss Homopolar
Electrodynamic Bearing". Stockholm: Universitetsservice US AB. ISBN 91-7178-032-7
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1. APPENDICIES
1.1 Appendix A: Creo Models & Dimensions
Figure A- 1: AMB Stator Front View with Electromagnet
Figure A- 2: AMB Stator Back View with Phototransistors (No Back Plate)
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Figure A- 3: AMB Exploded View with Front and Back Plates
Figure A- 4: AMB Cross-Sectional View with Electromagnet
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Figure A- 5: Complete Assembly with Two AMBs, PMB and water wheel
Figure A- 6: Side View of Complete Assembly
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Figure A- 7: Water Wheel
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1.2 Appendix B: Calculations
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1.3 Appendix C: FEMM and Creo Analysis
Figure C- 1: Creo Analysis for Material Strength of Rotor at 2000 RPM
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Figure C- 2: FEMM Analysis of AMB with Magnetic Field Density
Figure C- 3: FEMM Analysis of PMB with Magnetic Field Density
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1.4 Appendix D: Manufacturer Specifications
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Figure D- 1: B666 Pull Force between Two Magnets as a Function of Distance between Magnets
(courtesy of K&J Magnetics, Inc.)
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Figure D- 2: FEMM Analysis of B666 Magnetic Field Density (courtesy of K&J Magnetics,
Inc.)
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Figure D- 3: APW Electromagnet, Gausses as a Function of Distance
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1.5 Appendix E: Circuit Diagrams
Figure E- 1: QRD1114 Sensor Circuit
Figure E- 2: Control Compensator Circuit for One Electromagnet
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1.6 Appendix F: Budget
Table F- 1: Budget
Part Supplier Part Number Quantity Cost/Unit Subtotal Free Parts
1.0" Diameter
Round
Electromagnet
APW Company EM100-3H-
222
8 $29.95 $239.60
Phototransistor
QRD1114
SparkFun SEN-00246 10 $1.18 $11.80
Arduino Mega
2560 R3
SparkFun DEV-11061 1 $58.95 $58.95
Permanent Magnets K&J Magnetics,
Inc.
B666 16 $1.78 $28.48
Power Supply Marlin P. Jones
& Assoc.
(13.8V 20A) 1 $20.00 $20.00
Circuit
Components
Digi-Key 1 $10.00 $10.00
Protoboard SparkFun 1 $5.00 $5.00
Waterwheel MECE Lab (3D Print) $0.00 $0.00
Steel Shaft 3/4"
OD, 24" L
McMaster 1346K32 1 $22.91 $22.91
Key Stock Drive A 9C39-0632 1 $0.81 $0.00 $0.81
Collar Stock Drive A 7X 2-14024 2 $0.00 $0.00 $20.58
Race McMaster 8975K324 1 $52.69 $52.69
Race Plates McMaster 8975K425 1 $11.77 $11.77
Angle Plates McMaster 1556A24 12 $0.37 $4.44
JB Weld McMaster 7605A11 1 $6.17 $6.17
Acrylic MECE Lab $0.00 $0.00
Tachometer IR Kit SparkFun KIT-10732 1 $2.95 $2.95
Tachometer
Phototransistor
SparkFun 1 $1.13 $1.13
Display SparkFun COM-11629 1 $12.95 $12.95
Poster 1 $50.00 $50.00
Total: $538.84 $560.23
Budget: $1,125.00 $1,125.00
Money Left: $586.16 $564.77
MECE E3430 Engineering Design 43 2/21/2013
1.7 Appendix G: Gantt Chart
Figure G- 1: Gantt Chart