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1500 Points Raffle 1500 Points raffle :iconsealglompplz:How to join just fave this journal The raffle will end in 2 daysgoodluck :iconkissingplz:
[CLOSED+WINNER] Adopt Raffle 09 - MemoriesHi \;///v///;/ Thanks again for the support T////T I receive so many comments ;__; all so kind T////Tnnngh you have so wonderful idea for them ;__;Forgive again for the late Now I have the winner of the raffle \;//v//;/ <3 <3 <3This is :iconAzaikar: waaaah I'm so happy for you T////v////T <3 <3 <3 \;//v//;/Now Azaikar can choose her favorite in the batch and the others will be put on sale \;//v//;/ ( I'll make a poll before sell them ;u; <3 <3 )THANKS A LOT AGAIN TO EVERYONE *cries* ç__ç I feel very happy T////T <3 <3 <3HAVE A WONDERFUL DAY SEE YOU SOON IN THE NEXT RAFFLE Feel free to remove the journal from fav if you wish Waaah such a long time we didn't make a raffle >///v///< We really love doing that so this time we try with our new project "Memories" , Little Owl/penguin ( x°D )We hope you like them \;///v///;/
7 tips for the 21 year old me 7 TIPS FOR THE 21-YEAR-OLD ME by Bobby ChiuWhen I was a student in college working on my skills as a character designer, I'd had periods where I would sit at my desk working as hard as I could but having little to show for my efforts at the end of the day. I remember sitting there surrounded by blank pieces of paper, trying to come up with an amazing style that nobody had ever seen before. I would do one drawing and not be satisfied, so I would lay a new piece of paper over it, re-draw it with slight changes to features here and there. This would still not be good enough so I would put another piece of paper over my revision, make more minor adjustments trying to perfect this new style I was searching for. I did this for weeks on end, tweaking and polishing over and over, working hard every day. But in the end, did I come up with a brand new style, something amazing that
2500 Point Giveaway [OPEN] #5Hi guys! Just for anyone interested and/or that is really needed points, simply follow info.*and if you want help, please contribute a small or big donation, would be a great value! ♥ Enter in my profile page: ~~Help-donate-points~~ ---------- ----------I would like to thank the support of&
RAFFLE - TWO WINNERS. 3 DAYS LEFT!Hello~ /O/First, sorry for the inactivity. _(:'3_I haven't been at my house these months and I had trouble getting internet. But now I'm back and I hope that everything returns to normal. So I wanted to make a raffle to celebrate it. xD RULES:- Only watchers. u/v/u- Fav this journal to get a number. - Make a new journal entry linking to this raffle or make a poll about it! - Leave a comment here linking me to your journal entry/poll.THE RAFFLE ENDS SEPTEMBER 20th. Winners will be selected with ramdon.org.PRIZES: FIRST WINNER: Thigh-up or Chibi. SECOND WINNER:Chibi.THANK YOU AND GOOD LUCK! :'D
Your character in Missing Halloween! (RESULTS)MISSING HALLOWEENINTRODUCTIONIn August 21, "Your character in Missing Halloween!" mini-contest was announce.In September 1, a total of 313 character designs were submitted. Judging has begun.As the judge, there were 313 submissions, and only 32 to choose from. Trust me, it was haaaarrd! It still pains me that so many great designs didn't get in. (It's just that many) But I still did my best to judge them carefully.So here goes, the results!!!THE TOP 5 CANDY GIVERSAs mentioned, there will be 5 characters who will be featured as candy givers! (And their owners to be in the credits as "Additional Character Design")And here they are!!!:iconAndrea4You: Andrea4You's character: Akai:iconSkunkyfly: Skunkyfly's character: Amber:iconShiroXIX: ShiroXIX's character: Pydur:iconinkstainkat15: :d
halloween art exchange! since the holidays are coming up slowly but surely, and since a lot of exchange groups/ secret santas only accept "high quality art" or "only digital" and etc....i decided to do an exchange, and all art levels, mediums, and styles are accepted!:iconsecret-exchange-2014:and the theme of course is HALLOWEEN!how to enter (all steps are necessary)1. add this journal to your favorites, and if you want you can spread the word out with a journal or poll~!2. fill out this form in the comments section of this journal: username: *insert your username here*are you a digital, traditional, or mixed (you can do both) artist? : what skill level do you consider your art to be? : *be honest please, i will check your gallery and change your exchange group to a higher or lower level if necessary* *ex: very beginner, starter, rookie
CONTEST #2, MYO WATER DOG PRIZEHEYO IM BACK WHATS UP ALSO EXTENDING THIS TO SUNDAY (20TH)okay so contest two! This will last till next..Friday? ( Sept 19 ) yeahI've decided my contests will be themed kind of! SO this week all you gotta do is draw my sushi dogs! Any of them!http://sta.sh/216su5xtbmv6?edit=1 and my sushi cat lmao http://sta.sh/01p8dnnh413RULES-NO traced work or bases-any form of art is fine! traditional, digital, etc etc-you may humanize them/draw them anthro-you may NOT pair any of them up without asking me if it's okay! some of them are already shipped!-you may draw as many entries! you can do multiple characters in one picture as wellThe prize is a MYO Water Dog or 1500 points aaaand that's about it! if anyone needs it to be extended, just ask! have fun x)http://alfeddy.deviantart.com/favourites/61789831/D
CLOSED: 500 Watcher RaffleUpdate: Yay, I can finally edit journals again! Raffle is now closed!The winner was oreii Thank you for participating everyone! I just noticed I've reached over 500 watchers~ You guys are so awesome, thank you for all of the support, it means a whole lot to me! >///< To celebrate this happy occasion I'm hosting a raffle!♣ - Icon Raffle - ♣Deadline: Ends Monday, September 15th!Prizes: One lucky winner will win a Pixie icon!--• **But the icon will only have a basic blinking animation**♣ - How To Enter - ♣• - You must be a watcher! New watchers are also welcome~ (Please, only watch if you like my art)• - Please, favorite this journal, that will give you a entry number.• - For an extra chance of winning, you may writ
I'm really madHow many of you ever heard a racist comment that made you pissed? Well today I went Christmas shopping for my family and some random stranger called me something that angered me so much I was about to knock him out. I was in a store finding stuff for my mom and brother when I accidentally pump into this one guy I said sorry and excuse me for pumping you. He looked at me and crinkled his nose as if he some something descussing and said something I hate most of all he said " pff dirty native" ik it was not that bad but still it's the concept of someone thinking your dirty as if you never took a shower or that my place is awful but it's not I maybe Native American but I'm not uneducated I graduated with honors and I'm going to school to be a mechanical engineer so if some one is calling me dirty native is a reference that I'm stupid or that I am an awful race so if anyone says that to me again you better watch out I will give you a speech on how I'm not a dirty native....well no fighting
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The DeviantArt MMD
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|By Liz McMillan
Article Rating:
|July 28, 2014 11:30 AM EDT
@ThingsExpo Early Bird Savings here!
Almost everyone sees the potential of Internet of Things but how can businesses truly unlock that potential. The key will be in the ability to discover business insight in the midst of an ocean of Big Data generated from billions of embedded devices via Systems of Discover. Businesses will also need to ensure that they can sustain that insight by leveraging the cloud for global reach, scale and elasticity. Without bringing these three elements together via Systems of Discover you either end up with an Internet of somethings and/or a big mess of data.
In his session at @ThingsExpo, Mac Devine, a Distinguished Engineer at IBM, focused on how to ensure businesses have the right plans in place for Systems of Discovery for the Internet-of-Things world we are entering.
Click Here to View Mac Devine's Internet of @ThingsExpo Presentation Slides
Speaker Bio:
Mac Devine is a Distinguished Engineer at IBM. He has 24 years of experience with networking and virtualization.
The first 7 of those years were spent in mainframe software development where he served as chief programmer for several VTAM releases. Mac then moved to mainframe software design where he served as chief designer for several Communications Server releases and lead the design work for Sysplex and SNA over IP networking (aka Enterprise Extender).
In 2000, Mac went on temporary assignment for 2 years to assist the new networking alliance teams (IBM/Cisco, IBM/Nortel) in the role of lead solutions architect. Upon conclusion of this temporary assignment, he started the Linux Networking Solutions team within Enterprise Platform Software and served as its product director and chief architect.
In 2005, Mac started the Enterprise Platform Software Architecture Board and served as its chairman. The ESAB is the System z focus area for the SWGAB and is responsible for the architecture, design and strategy of solutions using IBM middleware on System z.
In 2007, Mac started the zCloud Innovation team and served as its chief architect. The zCloud Innovation team provided the architecture, design and development for several in-market experiments leveraging System z as a premier cloud platform. His innovative zCloud architecture and design resulted in him being named an IBM Master Inventor.
In 2008, Mac was appointed as an IBM Distinguished Engineer and became the WebSphere CTO for Cloud Computing. His innovations in this role resulted in him being appointed as a member of IBM's prestigious Academy of Technology in July 2009.
In 2009, Mac went on temporary assignment for 2 years with the IBM Corporate Strategy team where he served as the CTO for Cloud Partnerships and Client Innovations. During this time, he co-authored the Springer's Handbook of Cloud Computing which is used by many Colleges and Universities. Upon conclusion of this temporary assignement, he joined the IBM Global Technology Services team and served as its Director and CTO for the Cloud Portfolio. In this role, he led the technical due diligence for the SoftLayer acquisition and the creation of IBM's new Cloud Services Division. Mac currently serves as the Director of CloudFirst Innovation and CTO for the IBM Cloud Services Division.
Mac is a 1988 Clemson University graduate with an MS in Mathematical Sciences.
A Rock Star Faculty, Top Keynotes, Sessions, and Top Delegates!
Internet of @ThingsExpo 2014 Silicon Valley, November 4-6, at the Santa Clara Convention Center in Santa Clara, CA, will feature technical sessions from a rock star conference faculty and the leading IoT industry players in the world.
The growth and success of Internet of Things will be on display at the upcoming Internet of @ThingsExpo conference and exhibition in Santa Clara, CA, November 4-6, 2014.
All main layers of the IoT ecosystem will be represented at the Internet of @ThingsExpo - the infrastructure players, the platform providers, and those offering applications, and they'll all be here to speak, sponsor, exhibit and network.
Sponsorship Opportunities
for Internet of @ThingsExpo 2014 Silicon Valley
Internet of @ThingsExpo 2014 Silicon Valley "show prospectus" has shipped. Sponsorship, exhibit, and keynote opportunities can be obtained from Carmen Gonzalez by email at events (at) sys-con.com, or by phone 201 802-3021.
Early Bird Registration Options
for Internet of @ThingsExpo 2014 Silicon Valley
Internet of @ThingsExpo delegates can pre-register for Internet of @ThingsExpo with Early Bird Savings here.
About SYS-CON Media & Events
SYS-CON Media (www.sys-con.com) has since 1994 been connecting technology companies and customers through a comprehensive content stream at www.sys-con.com - featuring over forty focused subject areas, from Cloud Computing to Web Security - interwoven with market-leading full-scale conferences produced by SYS-CON Events. The company's internationally recognized brands include among others Cloud Expo® (www.CloudComputingExpo.com), Big Data Expo (http://BigDataExpo.net), Virtualization Conference & Expo (www.VirtualizationConference.com), DevOps Summit (http://DevOpsSummit.sys-con.com), Internet of @ThingsExpo (http://www.ThingsExpo.com), SDDC Expo (http://SDDCExpo.sys-con.com), WebRTC Summit (http://WebRTCSummit.net), Government IT Conference & Expo (www.GovITExpo.com), Cloud Computing Bootcamp (www.CloudComputingBootcamp.com), and UlitzerLive! New Media Conference & Expo (http://events.sys-con.com).
Predicted by Gartner to add $1.9 trillion to the global economy by 2020, the Internet of Everything (IoE) is based on the idea that devices, systems and services will connect in simple, transparent ways, enabling seamless interactions among devices across brands and sectors. As this vision unfolds, it is clear that no single company can accomplish the level of interoperability required to support the horizontal aspects of the IoE. The AllSeen Alliance, announced in December 2013, was formed wi...
Sep. 19, 2014 11:45 PM EDT Reads: 1,089
There's Big Data, then there's really Big Data from the Internet of Things. IoT is evolving to include many data possibilities like new types of event, log and network data. The volumes are enormous, generating tens of billions of logs per day, which raise data challenges. Early IoT deployments are relying heavily on both the cloud and managed service providers to navigate these challenges. In her session at 6th Big Data Expo®, Hannah Smalltree, Director at Treasure Data, to discuss how IoT, B...
Sep. 19, 2014 07:45 PM EDT Reads: 1,055
SYS-CON Events announced today that Connected Data, the creator of Transporter, the world's first peer-to-peer private cloud storage device, will exhibit at SYS-CON's 15th International Cloud Expo®, which will take place on November 4–6, 2014, at the Santa Clara Convention Center in Santa Clara, CA. Connected Data is the creator of Transporter, the world's first peer-to-peer private cloud storage device. Connected Data is focused on providing elegantly designed solutions for consumers, professi...
Sep. 19, 2014 06:00 PM EDT Reads: 828
Goodness there is a lot of talk about cloud computing. This 'talk and chatter' is part of the problem, i.e., we look at it, we prod it and we might even test it out – but do we get down to practical implementation, deployment and (if you happen to be a fan of the term) actual cloud 'rollout' today? Cloud offers the promise of a new era they say – and a new style of IT at that. But this again is the problem and we know that cloud can only deliver on the promises it makes if it is part of a well...
Sep. 19, 2014 12:00 PM EDT Reads: 670
Cisco on Wedesday announced its intent to acquire privately held Metacloud. Based in Pasadena, Calif., Metacloud deploys and operates private clouds for global organizations with a unique OpenStack-as-a-Service model that delivers and remotely operates production-ready private clouds in a customer's data center. Metacloud's OpenStack-based cloud platform will accelerate Cisco's strategy to build the world's largest global Intercloud, a network of clouds, together with key partners to address cu...
Sep. 18, 2014 01:00 PM EDT Reads: 1,285
I write and study often on the subject of digital transformation - the digital transformation of industries, markets, products, business models, etc. In brief, digital transformation is about the impact that collected and analyzed data can have when used to enhance business processes and workflows. If Amazon knows your preferences for particular books and films based upon captured data, then they can apply analytics to predict related books and films that you may like. This improves sales. T...
Sep. 18, 2014 11:00 AM EDT Reads: 910
Technology is enabling a new approach to collecting and using data. This approach, commonly referred to as the "Internet of Things" (IoT), enables businesses to use real-time data from all sorts of things including machines, devices and sensors to make better decisions, improve customer service, and lower the risk in the creation of new revenue opportunities. In his session at Internet of @ThingsExpo, Dave Wagstaff, Vice President and Chief Architect at BSQUARE Corporation, will discuss the real...
Sep. 18, 2014 11:00 AM EDT Reads: 1,590
IoT is still a vague buzzword for many people. In his session at Internet of @ThingsExpo, Mike Kavis, Vice President & Principal Cloud Architect at Cloud Technology Partners, will discuss the business value of IoT that goes far beyond the general public's perception that IoT is all about wearables and home consumer services. The presentation will also discuss how IoT is perceived by investors and how venture capitalist access this space. Other topics to discuss are barriers to success, what is n...
Sep. 18, 2014 07:15 AM EDT Reads: 1,330
When one expects instantaneous response from video generated on the internet, lots of invisible problems have to be overcome. In his session at 6th Big Data Expo®, Tom Paquin, EVP and Chief Technology Officer at OnLive, to discuss how to overcome these problems. A Silicon Valley veteran, Tom Paquin provides vision, expertise and leadership to the technology research and development effort at OnLive as EVP and Chief Technology Officer. With more than 20 years of management experience at lead...
Sep. 18, 2014 05:30 AM EDT Reads: 861
BlueData aims to "democratize Big Data" with its launch of EPIC Enterprise, which it calls "the industry's first Big Data software to enable enterprises to create a self-service cloud experience on premise." This self-service private cloud allows enterprises to create 100-node Hadoop and Spark clusters in less than 10 minutes. The company is also offering a Community Edition via free download. We had a few questions for BlueData CEO Kumar Sreekanti about all this, and here's what he had to s...
Sep. 18, 2014 04:00 AM EDT Reads: 990
- ARM Server to Transform Cloud and Big Data to "Internet of Things"
- Using Docker For a Complex "Internet of Things" Application
- Innodisk | Efficiencies for Cloud Hardware at Cloud Expo New York
- Docker + Stackato: The Perfect Workload Portability Solution
- What DevOps Can Do About Cloud's Predictable Provisioning Problem
- Rise of the Thing - Internet of Things
- Disruptive Innovations in Cloud Computing
- Interview: Enterprise Internet of Things with Red Hat
- WebRTC Summit Names Peter Dunkley "Summit Chair" At @ThingsExpo
- My Journey to #DevOps Enlightenment
- 'Internet Of Things' and Identity
- CA Keynote At DevOps Summit New York
- ARM Server to Transform Cloud and Big Data to "Internet of Things"
- Using Docker For a Complex "Internet of Things" Application
- Innodisk | Efficiencies for Cloud Hardware at Cloud Expo New York
- WSTA Named "Association Sponsor" of Cloud Expo Silicon Valley
- Docker + Stackato: The Perfect Workload Portability Solution
- What DevOps Can Do About Cloud's Predictable Provisioning Problem
- New Relic Announces General Availability of Real-Time Analytics Platform New Relic Insights
- Rise of the Thing - Internet of Things
- SaaS Represents the Commoditization of Business Function
- Disruptive Innovations in Cloud Computing
- Interview: Enterprise Internet of Things with Red Hat
- WebRTC Summit Names Peter Dunkley "Summit Chair" At @ThingsExpo
- Cloud Expo New York: Best CIO Practices Shared from SHI's Customers
- How Platfora Is Transforming Hadoop
- Meal Management System ISOBAG™ Offers 10% Off Coupon To Spur Holiday Season Shopping in 2013
- Cloud Computing and Big Data in 2013: What's Coming Next?
- Cloud Expo New York: How to Use Google Apps Script
- Think You Heard It All About The Best of the Best from CES? Well, Think Again ... My eHome® -- the Gotta-Have-It Multi-Play Solution -- Targeted for Launch in First Quarter 2014
- Examining the True Cost of Big Data
- Don't forget to register for FOSE 2013
- Small Cancers, Big Data, and a Life Examined
- ARM Server to Transform Cloud and Big Data to "Internet of Things"
- Cloud Expo New York: Cloud Is Changing the Economics of Business
- Best Practices: The Role of API Management

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A method and apparatus quickly and reliably reduce the weight critical flexural amplitude of a flexible rotor having an anisotropic flexural stiffness. Rotor data including the midpoint deflection of a vibration at twice the rotational frequency are measured on the rotating rotor, and a mathematical model is developed, using the measured rotor data, to represent the rotor. Parameters in the dynamic equation of motion in the mathematical model are evaluated in connection with the actual measured data, and thereby the stiffness anisotropy of the rotor is determined by minimizing the difference between the model values and the actual measured values, for example by using the least squares method. Based on the determined anisotropy, compensating data such as machining data for machining the rotor in order to reduce the stiffness anisotropy are calculated. The rotor is machined in accordance with the compensating data, by boring blind holes or continuous through-going holes parallel to the rotational axis and intersecting the soft axis of the rotor. By providing symmetrically arranged pairs of bored holes, the rotational weight balance of the rotor is maintained while the flexural stiffness anisotropy is reduced.
1. A method for reducing the weight critical flexing amplitude of a flexible rotor having a flexural stiffness anisotropy, comprising the following steps:
a) rotating said rotor about a central axis thereof and measuring a rotor deflection of said rotor during said rotating to provide measured values of rotor deflection,
b) forming a mathematical model for representing said rotor, wherein said mathematical model comprises an equation of motion including model values of rotor deflection;
c) evaluating said model values of rotor deflection in connection with said measured values of rotor deflection so as to minimize a difference between said model values and said measured values;
d) defining said flexural stiffness anisotropy of said rotor by using said evaluated model values of rotor deflection in said mathematical model;
e) calculating compensation data that reduce said defined flexural stiffness anisotropy in said mathematical model; and
f) adjusting a configuration of said rotor in accordance with said compensation data to reduce said flexural stiffness anisotropy of said rotor.
2. The method of claim 1, wherein said minimizing of said difference in said step c) is carried out according to the least squares method.
3. The method of claim 1, wherein said compensation data are calculated in said step e) using a general stiffness characteristic of said rotor.
4. The method of claim 1, wherein said compensation data are calculated in said step e) using the mechanics law of work.
5. The method of claim 1, wherein said mathematical model is a mathematical representation of an isotropically rotatably supported non-circular flexible Laval shaft with external damping.
6. The method, of claim 1, wherein said mathematical model is a mathematical representation of a modally analyzed continuous rotor.
7. The method of claim 6, wherein said continuous rotor is analyzed by means of finite element analysis.
8. The method of claim 1, wherein said step a) further comprises sensing a rotational angular position of said rotor to provide rotational angle data correlating with said measured values of said rotor deflection, wherein said defining of said flexural stiffness anisotropy of said rotor in said step d) comprises determining a degree of flexural stiffness over a range of angular position and determining a respective angular position of at least one of a soft axis of said rotor having a lower flexural stiffness and a stiff axis of said rotor having a greater flexural stiffness by using said rotational angle data together with said evaluated model values of rotor deflection in said mathematical model, and wherein said compensation data calculated in said step e) includes said respective angular position of at least one of said soft axis and said stiff axis.
9. The method of claim 8, wherein said step of determining said degree of flexural stiffness over said range of angular position in said step d) comprises forming a Nyquist amplitude-phase diagram of an amplitude of said measured values of rotor deflection or said evaluated model values of rotor deflection relative to said rotational angle data.
10. The method of claim 8, wherein said compensation data comprises material addition data defining an addition of material to said rotor on a stiff plane defined by said stiff axis and said central axis, and wherein said adjusting of said configuration of said rotor in said step f) comprises adding additional material to said rotor on said stiff plane in accordance with said material addition data.
11. The method of claim 10, wherein said additional material has a rod shape.
12. The method of claim 10, wherein said additional material is added to said rotor at two rotationally symmetrical positions.
13. The method of claim 10, wherein said rotor has a hollow space therein, and wherein said additional material is added onto an interior wall of said rotor bounding said hollow space.
14. The method of claim 10, wherein said compensation data further comprises material removal data defining a removal of material from said rotor on a soft plane defined by said soft axis and said central axis, and wherein said adjusting of said configuration of said rotor in said step f) further comprises removing material from said rotor on said soft plane in accordance with said material removal data.
15. The method of claim 8, wherein said compensation data comprises material removal data defining a removal of material from said rotor on a soft plane defined by said soft axis and said central axis, and wherein said adjusting of said configuration of said rotor in said step f) comprises removing material from said rotor on said soft plane in accordance with said material removal data.
16. The method of claim 15, wherein said removing of material from said rotor comprises boring at least two continuous through-going holes in said rotor on said soft plane parallel to and equidistant from said central axis.
17. The method of claim 16, wherein said material removal data comprises respective data defining said angular position of said soft axis, a bore diameter of said holes, and a radial spacing of said holes relative to said central axis.
18. The method of claim 15, therein said removing of material from said rotor comprises boring at least two terminating blind holes in at least one end face of said rotor on said soft plane parallel to and equidistant from said central axis.
19. The method of claim 18, wherein said material removal data comprises respective-data defining said angular position of said soft axis, a bore diameter of said holes, a radial spacing of said holes relative to said central axis, and an axial length of said holes.
20. The method of claim 1, comprising carrying out each of said steps a), b), c), d), e) and f) only a single time and excluding repetitive iterations of said steps a)r b), c), d), e) and f) for reducing said flexural stiffness anisotropy of said rotor below an acceptable threshold.
21. The method of claim 1, wherein said adjusting of said configuration of said rotor in said step f) comprises boring at least two holes in an end face of said rotor on said soft plane parallel to and equidistant from said central axis.
22. The method of claim 1, wherein said step f) is carried out automatically by a computer numerically controlled machining apparatus responsively to said compensation data.
23. The method of claim 1, wherein said step a) comprises rotating said, rotor over a range of rotational speeds and measuring said rotor deflection respectively over said range of rotational speeds.
24. The method of claim 23, wherein said range of rotational speeds includes a speed of approximately one of the first critical bending speed of the rotor, and wherein said step of measuring said rotor deflection comprises measuring a resonant vibrating rotor deflection having a frequency twice the rotational frequency of the rotor.
This application is based on and claims the priority under 35 U.S.C. �119 of German Patent Application 197 08 409.5, filed on Mar. 3, 1997. The entire disclosure of German Patent Application 197 08 409.5 is incorporated herein by reference.
The invention relates to a method for reducing the weight critical amplitude of flexural vibrations of a rotating rotor that has an anisotropic flexural stiffness. The invention further relates to an apparatus for carrying out such a method.
The trend in modern machine manufacturing is to achieve ever higher capacity and output of the machines, which generally calls for higher rotational speeds and an optimum utilization of materials in the machines. As a result, dynamic problems in the operation of the machines, which have previously only been considered of secondary importance, have now come into the foreground. For these reasons, it is now especially important to consider vibration and oscillation processes, such as imbalance vibrations and flexural bending vibrations, in the construction of shafts, rolls and other rotors that are intended to operate at high rotational speeds.
While mass imbalances have been addressed in the prior art, the occurrence of flexural bending vibrations due to anisotropy in the flexural stiffness characteristic of a rotating member have not been adequately taken into account. Such flexural bending vibrations are especially critical in shafts or other rotating members that are to be operated at a speed approaching the first critical bending speed or especially more than half of that critical speed. An example is represented by the calendar rolls and other rolls used in paper manufacturing, which are characterized as elastic shafts, i.e. the roll or shaft cannot be regarded as rigid but rather is elastically flexible over its length. If such a shaft or roll has even a slight anisotropy in its flexural stiffness, it will undergo a very strong vibration having a frequency of twice (2f) the rotational frequency, once the rotational speed of the shaft or roll reaches about one half of the first critical bending speed. In the field of rotor dynamics, this phenomenon is known as a so-called weight critical resonance or weight critical behavior.
Since this phenomenon is caused by the anisotropic flexural stiffness characteristic, it can occur even if the shaft or roll appears to be perfectly "round" and properly mass balanced. In other words, the weight critical resonance is caused by the resonant oscillation of the weight-induced sag or bending of the rotor, at twice the shaft rotation frequency. As an example, this phenomenon can be clearly understood in connection with a board that has a rectangular cross-section and that rotates about its lengthwise axis. Such a board will have a greater weight-induced sag when its major cross-sectional dimension is horizontal, and a lesser sag when its major cross-sectional dimension is vertical (i.e. when the board is upright on edge). Thus, if the sag is measured at the longitudinal midpoint of the board as the board rotates through one revolution, the midpoint sag will be smaller when the board is at angular positions 0� and 180� (board upright on edge) and greater when the board is at angular positions of 90� and 270�. As a result, the sagging or bending of the board will cause a bending vibration having a frequency of twice the rotational frequency.
Differences or anisotropies in the flexural stiffness of a rotor can arise due to any deviation from a perfectly round cross-section of the rotor, for example due to the presence of keyways, spline grooves, or other grooves or notches. This is true even if such grooves do not effect the rotational mass balancing of the rotor. In hollow shafts or other rotors, an anisotropy can also result if any area of the inner diameter is not perfectly concentric with the outer diameter, thus causing areas of lesser and greater relative rigidity. Anisotropies in the flexural stiffness can also arise in certain regions of a cast rotor due to the presence of different grain characteristics and thus different moduli of stiffness or elasticity in these regions, as may be caused by locally different cooling velocity during the production of shafts or rolls by casting. Generally, anisotropy in the overall flexural stiffness or rigidity of the rotor can arise from any source of deviations in the flexural strength and rigidity of the rotor in one plane relative to another plane.
PCT International Publication WO 95/33143 discloses a method for reducing the flexural rigidity fluctuation and the semi-critical disturbance occurring during the operation of a roll or cylinder, whereby the measured or calculated flexural rigidity fluctuation or imbalance is compensated by forming additional grooves or pockets or by changing the size of previously machined grooves or pockets. The grooves or pockets are to be so arranged that the combined effect thereof diminishes or at least does not increase the imbalance and/or the flexural rigidity fluctuation in the roll or cylinder. This reference suggests that the required measurements can be determined by measuring the motion of the center of the roll at the midsection thereof, or by measuring the circularity profile or the diametral fluctuation after carrying out the machining operation. However, the reference does not provide any teachings regarding how and under what conditions the measurements are to be carried out, nor any teachings regarding how any measurement results are related to or used for determining compensating steps that must be carried out. Since the reference provides no direct link between measurement results and the required compensating or corrective steps, it appears that an iterative process would be required, in which repeated measurements are carried out after repeated machining steps, in a trial and error manner, to finally hopefully achieve an acceptable compensation of the flexural rigidity fluctuation.
In view of the above it is the aim of the invention to provide a method and an apparatus for improving the dynamic behavior of a rotor by carrying out measurements on the rotor and then directly determining corrective or compensating steps that are required based on the measurements, and by carrying out those corrective or compensating steps to quickly and reliably reduce the anisotropy of the flexural stiffness of the rotor and thereby reduce the vibrations thereof having a frequency double the rotational frequency (so-called "2f vibrations"). The invention further aims to avoid or overcome the disadvantages of the prior art and to achieve additional advantages, as apparent from the present description.
The above objects have been achieved in a method for reducing the weight critical flexural amplitude of a rotor according to the invention, wherein pertinent rotor data are determined and a mathematical model is used in connection with the rotor data to characterize or define the rotatably supported rotor. Values or parameters in the equation of motion of the mathematical model are evaluated in connection with specific measured values of rotor deflection, and thereby the anisotropy of the rotor is determined and defined, preferably using the least squares method of data fitting. Once the anisotropy has been determined in this manner, then compensation date (e.g. machining data) are calculated based on either the known stiffness characteristics of the material of the rotor or the law of mechanics defining work. The machining data are then used, for example by a computer numerical controlled machining tool, to carry out a corrective or compensating machining of the rotor in order to reduce its stiffness anisotropy and thereby reduce the weight critical flexural amplitude of the rotor as it rotates. It should be understood that reduction of the anisotropy and the flexural amplitude should so to zero, i.e. complete elimination. This method can be carried out quickly and reliably, preferably as one direct procedure from the measurements to the final corrective machining, without requiring repetitive iterations of re-measuring and re-machining.
The above objects have further been achieved in an apparatus for reducing the weight critical flexural amplitude of a rotor according to the invention, including a sensor head for sensing a rotor index mark, a displacement pick-up or transducer for detecting and measuring the midpoint deflection of the rotor, a computer unit, and a measured value acquisition device having inputs connected to the sensor head and the displacement pick-up and having an output connected to the computer unit. The apparatus further includes a data unit for providing rotor specific data, which are supplied to an input of the computer unit. The computer unit outputs data that can be further processed or directly used by a computer controlled machining tool or the like to carry out a corrective compensation of the stiffness anisotropy of the rotor. The apparatus may include an axial boring tool connected directly to the computer unit.
Since a mathematical model is used to define the rotatably mounted rotor, and the values obtained through the mathematical model are combined and evaluated in connection with actual measured values of the rotor midpoint deflection, it is possible to determine the rotor anisotropy with only a single measuring run over various rotational speeds, and to generate machining data for correcting the anisotropy in a single machining operation directly from the measured data determined by such a single measuring run. Thus, as a major advantage of the invention, it is unnecessary to carry out an iterative sequence of plural measuring runs and corrective steps to reduce the anisotropy in successive intermittent partial steps by trial and error, as was carried out in the prior art.
Accordingly, the method according to the invention makes it possible to achieve a rapid and especially an exact compensation or correction of the stiffness anisotropy, whereby the double frequency (2f) midpoint deflections of the rotor can be held within a prescribed tolerance range using only a single measurement and single corrective machining step. This means that the rotor may be operated without any limitations on its rotational speed due to the weight critical resonance problem, which in turn means that the rotor, such as a roll used for paper, film or foil production, may be operated at a higher rotational speed and thereby achieve a higher production output, while simultaneously achieving a higher product quality due to the reduced vibrations of the roll.
Advantageously, the mathematical model to be used according to the invention may simply be based on an isotropically supported non-circular flexible Laval shaft with external damping. It has been determined by the inventors that even this simple model is adequate to achieve a substantially exact compensation or correction of the flexural stiffness anisotropy. The accuracy and the adaptability to various configurations of rotors are further improved according to the invention, if the model is based on a continuous rotor with modal analysis. In this context, the rotationally supported rotor is calculated by means of the finite element method, whereby the continuous rotor is modeled by a consecutive row of adjacent disks, in contrast to the Laval model of the rotor which includes a single disk. In connection with a modular decoupling, equations of motion are determined for the individual characteristic unit forms, of which the first characteristic unit form is preferably taken into consideration. The generalized stiffness characteristic of the rotor is a result value that is essential to the invention. The specific process steps that are valid for carrying out the inventive method in connection with the Laval model, principally also pertain for carrying out the method using the more detailed or fine-tuned model based on the continuous rotor.
A particularly simple method for determining the axes of greater and smaller flexural stiffness, i.e. the stiff axis and the soft axis, is the evaluation of an amplitude-phase diagram such as a Nyquist diagram. This can be carried out manually from a plotted diagram or may be carried out in a computer supported manner based on stored data values representing the diagram.
The final corrective or compensating step can be achieved by removing material or by adding material to the rotor, depending on the particular rotor type. It is also possible that both of these techniques can be used on a single rotor for correcting or compensating the anisotropy. Material removal is conveniently carried out by a machining operation such as boring, while material addition is conveniently carried out by attaching rod-shaped members by welding, soldering or the like, or any other known method of adding or building-up material. In any event, the material removal or material addition are carried out to correct or compensate the anisotropy of the flexural stiffness, while also maintaining the rotational mass balance of the rotor. In other words, the material removal and/or material addition must be carried out to correct the stiffness anisotropy.
More specifically, rotor material is to be removed in the plane of lower flexural stiffness (i.e. in a plane defined by the central axis and the soft axis), while material is to be added in the plane of greater flexural stiffness (i.e. the plane defined by the central axis and the stiff axis). The removal of material preferably comprises forming through-going continuous bores or closed blind bores equidistant from and parallel to the axis of the rotor in the plane of the smaller bending stiffness. The addition of material preferably comprises applying rod-shaped materials, onto the outer surface of the rotor or the inner surface of a hollow rotor, rotationally symmetrically in the plane of greater bending stiffness.
In order that the invention may be clearly understood, it will now be described, in connection with an example embodiment of the invention, with reference to the drawings, wherein:
FIG. 1 is a schematic cross-section of a portion of a rotor in the form of a hollow roll that was manufactured by casting;
FIGS. 2A and 2B are schematic diagrams representing a mathematical model for characterizing the rotor of FIG. 1;
FIG. 3 is a diagram showing the progression of the weight-induced double frequency vibration amplitudes relative to the reference rotational speed of the shaft with external damping;
FIG. 4 is a Bode diagram showing measured values and a fitted or approximated curve of the midpoint deflection of the rotor relative to the rotational speed of the rotor;
FIG. 5 is a Nyquist diagram showing measured data points for determining the axes of greater bending stiffness and lower bending stiffness;
FIG. 6A is a side view of a rotor, partially broken open in section, showing through-going bored holes for compensating the anisotropy according to the invention;
FIG. 6B is a side view of a rotor, partially broken open in section, showing blind bored holes extending inwardly from the ends of the rotor for compensating the anisotropy according to the invention;
FIG. 6C is a schematic end view diagram figuratively demonstrating the soft axis and the stiff axis of the rotors of FIGS. 6A and 6B;
FIGS. 7A and 7B are two schematic side views of a rotor, illustrating examples of calculating the anisotropy reduction according to the invention;
FIG. 8 is a schematic block diagram illustrating the apparatus and the sequence of steps for carrying out the method according to the invention; and
FIG. 9 is a diagram of the double frequency midpoint deflection of the rotor relative to the rotational speed before and after carrying out the anisotropy correction according to the invention.
FIG. 1 schematically shows an example of a rotor in the form of a lengthwise extending hollow shaft 1, which has regions of differing grain characteristics resulting from the casting process by which the hollow shaft 1 was manufactured. This lengthwise extending hollow shaft 1 represents that part of a roll, such as a roll of a paper manufacturing plant, which primarily causes the flexural stiffness anisotropy of the roll. More specifically, the hollow shaft 1 is provided with end caps and bearing support studs or shaft stubs at both ends to form the complete roll.
As mentioned above, the hollow shaft 1 is formed by casting, and particularly by casting in a vertically standing orientation in an appropriate mold. During the casting process, the melt is caused to rotate in the mold as the mold is filled from bottom to top. Due to different rates of cooling of the melt, three different grain layers are formed, namely an outer chill cast or white cast layer 2 comprising cementite, an inner gray cast layer 3, and a transition layer 4 having a cementite content that increases from the inside to the outside, located between the outer layer 2 and the inner layer 3. Due to their different material compositions, these layers 2, 3 and 4 have respective different densities and moduli of elasticity. These layers also have varying thicknesses over the length of the shaft 1.
Moreover, the shaft 1 may become curved or deformed during its cooling and solidification, whereafter the shaft is machined by turning or the like on its inner and outer surfaces to form the finished shaft 1. This procedure can even further amplify the varying thickness of the three different layers 2, 3 and 4 along the length of the finished shaft 1. Thus, even the finished, turned hollow shaft 1 still has an anisotropy of its characteristics relative to the rotational axis A. If a hollow shaft or pipe is formed by deep drawing rather than by casting, anisotropies still result due to the varying wall thicknesses around the circumference and along the length of the finished pipe or shaft. Similarly, for carbon or glass fiber reinforced composite rotors, the processing of the material also leads to anisotropies in the finished rotor.
Since the anisotropy in the hollow shaft 1 shown in FIG. 1 arises due to the varying moduli of elasticity in the different layers 2, 3 and 4, the flexural stiffness and therewith the dynamic behavior of the finished hollow shaft 1 will also be anisotropic. In order to be able to correct such anisotropy and thus improve the dynamic behavior of the hollow shaft 1 according to the invention, the shaft and its dynamic behavior must first be modeled and mathematically described according to the method of the invention, as shown in an overview in FIG. 8, which will be described in detail below.
Particularly, equations of motion for the hollow shaft must be derived from the mathematical model. In the present example, for simplicity, a single-disk massless non-circular Laval shaft 10 is used as the mathematical model, as represented in FIGS. 2A and 2B. It should be understood, however, that other mathematical models can be used according to the invention, for example a continuous rotor analyzed in a modal manner. In that case, the rotatably supported rotor is calculated or analyzed by means of finite element analysis, whereby the continuous rotor is modeled by a sequence of disks, in contrast to the single disk of the Laval rotor model. For a modular decoupling, equations of motion are determined for the individual characteristic unit forms, of which the first characteristic form is preferably taken into consideration. The generalized stiffness characteristic of the rotor or shaft is a result value essential to the invention. The process steps and considerations pertaining to an evaluation of the Laval model principally also pertain for the more detailed or fine-tuned model based on a continuous rotor. For the sake of simplicity, the process steps for carrying out an evaluation using the Laval model will now be described in detail.
As shown in FIG. 2A, the Laval model shaft 10 includes a massless shaft 10A and a rotor disk 10B having the mass m attached rigidly and eccentrically to the shaft 10A. The rotor disk 10B has a center of mass S, while the shaft 10A passes through the disk 10B at a shaft connection point W offset from the center of mass S to define the eccentricity. The non-circular shaft 10A has two perpendicular principle axes of inertia that respectively have two different flexural stiffness coefficients c1 and c2 associated therewith, so that the Laval shaft 10 has a flexural stiffness anisotropy μ that is defined as described below. The evaluation is carried out for a stationary rotational condition, namely the rotational condition with constant angular velocity Ω. In order to simplify the mathematical analysis in the complex plane, two coordinate systems will be used, namely a space-fixed coordinate system yz lying in the central plane of the rotor disk, and a rotor-fixed coordinate system ηζ which rotates together with the rotor. The shaft connection point w at which the undeformed shaft 10A would pass through the disk 10B, i.e. the true axis of rotation, is chosen as the origin, as shown in the schematic of FIG. 2A and in the enlarged space diagram of FIG. 2B. For simplicity, FIG. 2B simply shows a cross-section through the shaft 10A at the point w of its intersection with the disk 10B.
The axes η' and ζ' represent the principle inertial axes, which generally do not coincide with the rotor-fixed reference system. Instead, considered generally, the system of perpendicular principle inertial axes η' and ζ' is shifted by an angle of β from the rotor-fixed reference coordinate system ηζ. Moreover, the center of gravity S of the rotor disk 10B is offset or rotated by an angle δ relative to the rotor-fixed, i.e. rotating, reference coordinate system ηζ. For simplicity of calculation, the rotor-fixed reference coordinate system ηζ can be assigned so that it corresponds to the principle inertial axes η' and ζ'.
The first step of the analysis will be to define and evaluate the deflection of the Laval shaft 10 from its undeformed axis, i.e. the x axis of the coordinate system. The vectors of the deflections in the yz plane and in the ηζ plane respectively are given by:
r=y+j z Eq. (1)
ρ=η+j�ζ Eq. (2)
with the transformation conditions
r=ρ�ejΩt Eq. (3)
ρ=r�e-jΩt Eq. (4)
The corresponding differential equation is derived according to the d'Alembertian principle (requiring equilibrium between the kinetic or inertial forces and the external applied forces):
m�r=Ff +G Eq. (5)
Ff =elastic return force in the fixed system; and
B=the self weight.
When transformed into the rotating coordinate system, the result is:
m(ρ+2jΩp-Ω2 ρ)=Frot -j�m�g�e-jΩt Eq. (6)
Frot =-c1 η-jc2 ζ; and
c1, c2 =flexural stiffness coefficients.
By applying certain substitutions or abbreviations, namely ##EQU1## wherein ω1, ω2 =characteristic or Eigenfrequencies of the shaft,
ω0 =average Eigenfrequency of a shaft having an average flexural stiffness coefficient, and by further substituting, simplifying, and transforming, the equation of motion is represented in the following form for describing the resultant translational motion of the rotor disk 10B due to its own weight: ##EQU2## wherein ##EQU3## From this, the complex amplitudes ρ1 and ρ2 are given as follows: ##EQU4## Under the influence of an externally applied damping D, the complex amplitudes ρ1 and ρ2 are thus given as follows: ##EQU5## wherein
Δg =(1-μ2 -4η2)2 +16D2.sub.η2Eq. (11)
The contributions of the complex amplitudes ρ1 and ρ2 over the reference rotational speed are shown in FIG. 3, whereby ρ1 is the amplitude of the circular motion having a doubled frequency (2f) relative to the rotational frequency, and ρ2 is the amplitude of the vertical sag or deflection. The variation in the sag or deflection ρ2 upon reaching the weight critical rotational speed results from a superposition of the constant weight-induced sagging deflection and the flexing vibration or oscillation of the non-circular rotating shaft. The amplitude ρ1 of the double frequency (2f) circular motion has a maximum value at a rotational speed corresponding approximately to one half of the first critical bending speed.
FIG. 4 is a Bode diagram illustrating or exemplifying the process for identifying the parameters used according to the present invention, as will be described in detail below. Specifically, FIG. 4 is a diagram showing the midpoint deflection of the rotor over a range of rotational speeds, by means of actual measured data points as well as an approximated or fitted curve based on those measured data points. The following points pertain in general to the estimation or evaluation and identification of the parameters. The rotor system is a particularly dynamic system from which measured values are acquired to characterize the system behavior, on the one hand. Furthermore, on the other hand, the inventive method provides a mathematical model of the system, in which one or more parameters are unknown or known only approximately with a large degree of possible error.
According to the invention, the measured values are compared to, and used to evaluate, corresponding results provided by the mathematical model. Differences between the computationally determined values and the actually measured values are taken into account as estimation errors. The unknown parameters are to be determined in such a manner that the estimation errors are minimized. In order to determine whether a minimum in the estimation errors has been achieved, a control or optimality criterion must be selected and applied. In the present example, the sum of least squares method is used as the optimality criterion, whereby the sum of squares of the estimation errors is to be minimized. The mathematical model provides a general parameter dependent function F(x,α,β, . . .) of the parameters (α,β, . . .), which is to approximate the initial value f. The measured values f1, xi of the function f describing the system are acquired by measurement techniques, whereby i=1, . . .k indicates the respective one of a number k of measured data points.
The sum of the squares of the errors is then given by ##EQU6## which is to be minimized.
The following text describes one possible solution in which the values or magnitudes of the anisotropy and of the damping are determined. The above described optimization problem can be solved using any one of a number of commercially available software products, such as "MATHCAD"� or "MATHLAB" or others for carrying out mathematical calculations or optimizations. Such commercially available software products can determine additional values as well.
By inserting or substituting: ##EQU7## into the above recited Equation (10) for ρ1, for the mathematical model selected according to the invention, one obtains the following function W that is dependent on the parameters μ and D as shown in FIG. 4: ##EQU8## as well as the equation or relationship that is to be optimized: ##EQU9## wherein wi indicates the measured amplitudes at the respective associated rotational speeds ni, as indicated by the squares in FIG. 4.
Thus, stated simply, both the damping D and the coefficient of anisotropy μ of a rotor are identified or determined according to the invention by combining and evaluating the values provided by a mathematical model (a Laval shaft model in the selected example) in connection with measured values determined from the actual physical rotor, by using the above described method of parameter estimation. Instead of using the above described method, it is alternatively possible to solve the optimization problem by means of the complex measured values, in other words by using the values plotted in the Nyquist diagram of FIG. 5 rather than the Bode diagram of FIG. 4.
Once the anisotropy of the rotor has been determined as described above, the remaining step is to compensate or correct that determined anisotropy. Namely, proper manipulations or adjustments on the hollow shaft 1 or other rotor must be carried out in order to significantly reduce or remove the determined anisotropy. More specifically, the determined anisotropy is reduced or removed by altering the flexural stiffness characteristics of the rotor 1 by introducing an inverse or counteracting anisotropy. To achieve this, it is most effective to manipulate the rotor, i.e. to remove material from or add material to the rotor, along the principle inertial axes thereof.
A simple method for achieving this is to bore through-going holes 5 through the rotor 1 on or intersecting the soft axis Asoft so that the stiffness of the rotor 1 about the stiff axis Astiff is reduced to such an extent that it matches the stiffness of the rotor 1 about the soft axis Asoft, as shown in FIGS. 6A and 6C. Alternatively, non-through-going or blind bored holes 6 can be provided extending parallel to the rotational axis A from one end face or preferably both end faces of the rotor 1, respectively on lines intersecting the soft axis Asoft at a spacing r away from the stiff axis Astiff, as shown in FIGS. 6B and 6C. It should be noted that the bored holes 5 or 6 are always provided in rotationally symmetrically arranged pairs to maintain the rotational mass balance of the rotor 1. It should further be noted that the rectangular end view shown in FIG. 6C is merely a schematic representation to more clearly demonstrate the concept of the soft axis Asoft and the stiff axis Astiff, while the rotor 1 actually has an essentially circular cross-section with different stiffness characteristics along the soft axis and stiff axis as described above in connection with FIG. 1.
Instead of providing bored holes 5 or 6, it is alternatively possible to remove material from the outer surface of the rotor 1, such as by machining grooves therein, on the soft axis Asoft. As a further alternative, instead of removing material, it is possible to apply additional material in the form of a rod or bead, either on the outer surface or the inner surface of the hollow shaft rotor 1, in parallel to the shaft axis A and on the stiff axis Astiff, in order to reduce the stiffness anisotropy by increasing the stiffness about the soft axis Asoft. Such a rod-shaped additional material 7 is indicated schematically in FIG. 6C.
The angular positions of the stiff axis Astiff and the soft axis Asoft the hollow rotor shaft 1 may, for example, be determined by means of an amplitude-phase diagram, e.g. a Nyquist diagram, representing the measurement values of the double frequency (2f) midpoint deflections of the hollow rotor shaft 1 rotating at about one half of the first critical bending speed. FIG. 5 is such a Nyquist diagram showing a plurality of measured data points respectively representing the amplitude of the deflection relative the angular phase around one full rotation, with a maximum deflection range of 500 μm. In order to determine the angular position of the stiff axis, first the phase direction of the initial drifting or deviation of the hollow shaft 1 from its true circular rotation is read from the phase diagram. The deflection of the hollow shaft 1 in this angular direction indicates that the primary stiff axis of the hollow shaft lies in this direction, because the shaft is bending about the soft axis which is perpendicular to the stiff axis.
In the present example as seen in FIG. 5, the direction of this initial deflection, represented by the first fifty measurement points, is at about 120� it must further be taken into account that the determined angular value must be divided by two, to result in an angular position of the stiff axis at 60�, since this evaluation involves double frequency (2f) measured values that correspondingly have a frequency double that of the rotational frequency. Accordingly, it has been determined that the stiff axis lies at a position of 60�, while the soft as lies at a position of 150�, i.e. perpendicularly to the stiff axis. These angular positions are determined relative to an index position or index mark on the shaft, as will be described below in connection with FIG. 8.
Once the angular positions of the stiff axis and of the soft axis and the amount of anisotropy have been determined, the next step is to determine the proper bore diameter DB, a radial spacing r of the bored holes relative to the stiff axis Astiff, and the proper bore depth or length L in the case of blind bores 6. This determination will now be briefly discussed with regard to a rotor that is symmetrical about its center plane and also symmetrically rotatably supported, wish reference to FIG. 7. This determination is, for example, based on evaluation of the Laval shaft model in view of the general mechanics law or definition of work. In order to carry this out, the data values of thickness and moduli of elasticity of the rotor are taken into account, as listed under the point "geometry" in the method diagram of FIG. 8. The sagging deflection S is calculated by means of the mechanical definition of work. As schematically represented in FIGS. 7A and 7B, a force F or virtual force 1 is applied at the midpoint of the shaft 1 between the two bearings 1'. As a result, the moment distributions M(x) and M(x) indicated schematically in FIGS. 7A and 7B arise along the shaft 1, whereby the sagging deflection S can be calculated using the so-called work integral: ##EQU10## wherein M(x)=moment due to force F
M(x)=moment due to force 1
E(x)=average modulus of elasticity
I(x)=surface moment of inertia in the respective principle action direction.
Next, for M(x)=M(x)F, the stiffness C is calculated as: ##EQU11## If the rotor is made up of several elements, for example various regions or portions having different diameters, then the denominator of the above Equation 17 must be replaced by the sum of the work integrals of the various rotor elements.
The products of the respective modulus of elasticity and surface moment of inertia in the case in which the rotor element does not include bored holes, are equal for both principle axis directions and are given as follows: ##EQU12## wherein Da is the outer diameter and Di is the inner diameter. If a rotor element is provided with bored holes 6 as shown in FIGS. 7A and 7B, then two different products of the respective modulus of elasticity and the surface moment of inertia will apply for the two principle axis directions, and namely, according to Steiner: ##EQU13## wherein: DB=bore diameter
r=radial spacing between bore axis and rotor center
EB =modulus of elasticity of the material in which the bores are provided.
Due to the different products of the modulus of elasticity and the surface moment of inertia, this will result in different coefficients of stiffness c1 and c2 in the two principle axis directions so that the shaft would be made anisotropic due to the provision of the bored holes (assuming that the initial condition was isotropic), whereby the above mentioned relationship between the anisotropy μ and the coefficients of stiffness c1 and c2 applies (see the definitions in connection with Equation 7 above).
Thus, the desired proper bore diameter is directly connected to the identified anisotropy of the rotor. In other words, the proper diameter DB must simply be selected so that the anisotropy caused by providing the bored holes counteracts or cancels out the anisotropy that originally existed in the anisotropic rotor. This bore diameter DB is calculated in the computer unit shown in FIG. 8, using the above described calculations and methods. Additionally, the radial spacing distance r at which the bored holes 6 are to be provided must also be determined. By positioning the bored holes 6 on the soft axis Asoft at a spacing r away from the stiff axis Astiff in an anisotropic shaft, then the stiff axis will be weakened to a greater extent than is the soft axis, so that the previously existing anisotropy of the shaft can be cancelled out or compensated by the newly caused anisotropy by properly selecting the bore diameter DB and the radial spacing r.
FIG. 8 provides a schematic overview of the components of an apparatus for carrying out the present method, as well as a flow diagram of the steps involved in carrying out the method. The rotor 1 is rotatably supported on two bearing stands 27 and 28. A data acquisition unit 20 is provided for acquiring, obtaining or determining the geometrical data pertaining to the geometry of the rotor 1, and specifically containing the dimensions of the rotor 1 as well as the associated moduli of elasticity and thicknesses of the layers 2, 3 and 4 in the structure of the rotor 1. These values are provided to a computer unit 21, which forms a mathematical model of the rotatably supported rotor 1. These values could alternatively be manually determined and input into the computer unit 21.
A deflection measuring device 22 is provided to measure the rotational speed, phase angle, and 2f or double frequency midpoint deflection of the rotor 1, and to provide corresponding measured values to a measured value acquisition device 23 connected to the output of the device 22. Appropriate filtering may be used to isolate the 2f deflection values. The device 23 provides corresponding measured values for the rotational speed, phase angle, and double frequency or 2f midpoint deflection to the computer unit 21, which in turn determines the axis positions of the rotor 1, and the complex anisotropy μ in terms of its magnitude and phase, among other things, by carrying out the above described process of parameter identification.
Next, taking into account the geometric data provided by the data acquisition unit 20, the computer unit 21 finally determines and indicates the specific material removal or addition that must be carried out in order to compensate or reduce the anisotropy that is initially present in the rotor 1. For example, the computer unit indicates or outputs data defining the bore diameter DB and radial spacing r of through-going bore holes 5 or additionally the bore hole depth or length of blind bore holes 6. The computer unit 21 provides the above described output signals to a display unit 35 and optionally also directly to a computer controlled machining station, for example including an axial boring machine 45.
The deflection measuring device 22 comprises a contact-less displacement pick-up or transducer 25, preferably using an eddy current sensor, for detecting the vertical midpoint deflection of the rotor 1, as well as a sensor head 24 for sensing a rotor index mark 26 provided on the rotor 1. Thus, the sensor head 24 provides information regarding the rotational or angular position and the rotational speed of the rotor 1. The output signals of the sensor head 24 and the displacement pick-up 25 are provided to the deflection measuring device 22 proper, which in turn therefrom determines rotational speed dependent measured values of the amplitude of the 2f midpoint deflection of the rotor 1 relative to the rotational angular position, which are then passed on to the measured value acquisition device 23, whereupon all of this information is conveyed on to the computer unit 21 for its use.
FIG. 9 shows the double frequency midpoint deflection of a test rotor relative to its rotational speed, both before and after carrying out the method according to the invention for compensating the rotor anisotropy. As can be seen, the usable range of rotational speeds has been considerably enlarged, because excessive vibrating deflection at or about one half the first critical bending speed has been avoided. Thus, for example in the operation of a paper, film or foil manufacturing plant, the respective rolls can be operated at a higher rotational speed so as to increase the production output. Moreover, the product quality can be improved by the reduction of vibrational deflection of the rolls. If the acceptable 2f midpoint deflection is 10 μm in the example of FIG. 9, then there is absolutely no limit on the rotational speed of the roll with regard to the weight critical resonance or weight critical rotational speed.
Although the invention has been described with reference to specific example embodiments, it will be appreciated that it is intended to cover all modifications and equivalents within the scope of the appended claims. It should also be understood that the present disclosure includes all possible combinations of any individual features recited in any of the appended claims.
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Metcalf & Associates Launches On-line Innovative Leadership Development Program
The initial online leadership development program will focus on emerging leaders and managers by applying the methods and philosophy of the Innovative Leadership Workbook for Emerging Leaders and Managers as its foundation, and will deliver weekly e-mail with leadership development exercises. Additionally, participants have the option to take part in webinars and can also select a coaching to accompany the online development process for an additional fee. This model will provide a range of options for emerging leaders to enhance their skills and build their careers. See sample series posted on Metcalf & Associates blog as a series from December 5, 2012 through January 21, 2013.
"Leadership needs innovation the way innovation demands leadership. By combining them, you improve your capacity to deliver results and your organization's capacity to affect change," says Metcalf. The Innovative Leadership Workbook for Emerging Leaders and Managers, designed specifically for busy people, includes field-tested processes and worksheets for innovating how you lead, transforming your organization, and creating sustainability. The workbook takes readers on their own leadership journey through a series of development activities while providing insight into the thought processes of two different and highly successful emerging leaders whose unique challenges provide invaluable insight into how a leader develops and incorporates innovation both personally and professionally.
About Author
- Watch: BEAUTIFUL's Jessie Mueller Performs GILMORE GIRLS Theme
- TV and Modern Art to Collide in 'REVOLUTION OF THE EYE' Exhibition, Opening May 2015 at The Jewish Museum
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- BET Networks Announces Breast Cancer Awareness Month Activities
- New Blake Shelton Album Comes to Prime Music on Release Day
- Rock Legend Gene Simmons Set for Dan Rather's THE BIG INTERVIEW Tonight
- Tony-Winner Laura Benanti Signs with Deraney Public Relations


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|IEC 60684-3-100 ed2.0 withdrawn corrigendum
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Let it rip! Amanda Seyfried dresses down in torn jeans for lunch in fancy Hollywood restaurant
Les Miserables actress Amanda Seyfried wore ripped jeans and a casual loose fitting T-shirt for a lunch date at Cecconi's on Thursday.
The casually dressed star stepped out into the LA sunshine with her friend, and looked relaxed as they said their goodbyes after the meal.
Amanda, who burst onto our screens in the musical Mama Mia in 2008, is reported to be joining her Les Miserables costars on stage at the Academy Awards to perform some hits from the movie.
Rip it up: Amanda Seyfriend wore a casual outfit for lunch at Ceccioni's in West Hollywood on Thursday
Amanda and her castmates Hugh Jackman, Anne Hathaway, Eddie Redmayne and Samantha Barks are in talks to perform a medley of songs from the the Oscar nominated film.
Scruffy: The actress's jeans were torn at the knee
Les Miserables picked up three awards at the Golden Globes on Sunday, and Amanda has spoken of the strict regime she took on to land a role in the movie.
The actress, 27, was so determined to be involved in the production that she changed her lifestyle, giving up caffeine, dairy and alcohol.
Amanda said that landing a part in Les Miserables was a dream come true, as she has been obsessed with the musical since she was a child.
She said: 'I was only 11 when I first saw it, and ever since I've been hoping and wanting to be a part of it. Playing Cosette is proof that life has a way of making things come full circle if you want something badly enough.'
Amanda started training with a voice coach in August 2011 in preparation for the role, and said,'I wanted the role more than anything I've ever wanted in my life.'
Her upcoming role in Deep Throat is a far cry from the pure and virginal character she portrays in Les Miserables.
She plays American porn star Linda Lovelace in the biopic, which costars Sarah Jessica Parker, Sharon Stone, Chloe Sevigny, Chris Noth and Hank Azaria. James Franco plays a young Hugh Hefner in the movie.
Kate Hudson was originally asked to play Linda, until it was announced last November that Seyfried was up for the role.
Fed up? The 27-year-old holds her stomach as she waits for the valet outside the restaurant, and her friend texts on his cell phone
A farewell peck: Amanda kisses her friend goodbye as they leave the West Hollywood restaurant
- Man being brutally detained by West Virginia Police
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- Nicole Kidman arrives back in Sydney with husband Keith
- A baby bear performs a circus act at a golf course
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- 'Damaged but not down and out': Greg Norman nearly loses his...
- Bride-to-be whose fiancé died just days before their wedding...


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1. Preheat oven to 375 degrees Fahrenheit.
2. For the Cornbread: In a large bowl add together melted butter and sugar and combine.
3. In a separate bowl mix together buttermilk and baking soda.
4. Once combined add to the butter, sugar mixture and stir well.
5. Next add in remaining ingredients and mix until very few lumps remain.
6. On a sheet pan with parchment paper and non-stick spray pour corn bread batter and spread evenly.
7. Bake at 375 degrees for 30-40 minutes.
8. Once the corn bread is cooked, slice into thick chunks and place in a very large bowl.
9. For the Chorizo: In a large saute pan on high heat with 2 tablespoons of olive oil, caramelize the sweet onion, celery stalks, carrots and garlic.
10. Once brown, add in the chorizo and saute for 3 to 4 minutes.
11. Finish with green onions, salt and pepper and add it to the large bowl with cornbread.
12. Mix thoroughly and transfer to a souffle dish.
13. In a separate bowl, whisk together chicken stock and eggs and pour over the mixed cornbread, vegetables and chorizo.
14. Place the souffle dish in the oven on 375° for 20 ro 30 minutes.
15. Once cooked, remove from the heat and serve.


text:
The Zero Theorem
Terry Gilliam's first science fiction film since "12 Monkeys" is an inventively designed but oddly inert satire on technology, God and the future of humankind.
Terry Gilliam's first science fiction film since "12 Monkeys" is an inventively designed but oddly inert satire on technology, God and the future of humankind.
It's not surprising that Smith's characterizations and dialogue lack subtlety given the type of broad comedy that Smith has practically made his brand. But somehow,…
"The Ballad of Narayama" is a Japanese film of great beauty and elegant artifice, telling a story of startling cruelty. What a space it opens…
Patrice Leconte's "Monsieur Hire" is a tragedy about loneliness and erotomania, told about two solitary people who have nothing else in common. It involves a…
"Life Itself" is set to debut in London as part of the Dogwoof Weekender.
"Life Itself" opens at many more venues, including the Gene Siskel Film Center.
An FFC reviews the gentle, sweet "The Lunchbox."
An FFC comments on domestic violence in film and her life.
An FFC reviews the gentle, sweet "The Lunchbox."
An FFC comments on domestic violence in film and her life.
A TV review of ABC's "How to Get Away with Murder" and "Black-ish".
An interview with legendary film critic David Thomson about the latest edition of "The New Biographical Dictionary of Film."
Named after the David Cronenberg film, this is the blog of former RogerEbert.com editor Jim Emerson, where he has chronicled his enthusiasms and indulged his whims since 2005. Favorite subjects include evidence-based movie criticism, cinematic form and style, comedy, logical reasoning, language, journalism, technology, epistemology and fun. No topic is off-limits, but critical thinking is required.
"It is not enough to like a film. One must like it for the right reasons." -- Pierre Rissient
This is entirely coincidental, so consider it a fortuitous double-bill. Just as I posted the item below ("The sins of the critic"), Roger Ebert posted a blog essay on the subject: "'Critic' is a four-letter word." Here's a taste:
Too many simply absorb. They are depositories for input. They can hardly be expected to be critical of their own tastes, can they? Of course they can. It is not enough simply to be a "Cubs fan," although I confess I am one. It is necessary to feel the philosophy, the history, and even the poetry about the activity called "baseball." It is helpful to step outside a little, and see that sports teams are surrogates for our own desires to conquer, and expressions of our xenophobia. For some, they are even the best way ever invented to drink beer outdoors. If you are only a Cubs fan, you are a willing automaton in a business venture. Join me in being a Cubs fan, but know why you do it. What is my most fundamental reason? I am a fan because they are always the underdogs. That may be why I bought a Studebaker 30 years after the company went out of business.
Read the entire piece here.
Next Article: Underdogs: The dogs below the title (Part 1) Previous Article: The sins of the critics
As we mourn Abrams' macho Star Trek obliteration, it's a good time to revisit that most Star Trek-ian of accomplishme...
This message came to me from a reader named Peter Svensland. He and a fr...
Part ten in Scout Tafoya's The Unloved series tackles "The Village."
A photo gallery offering snapshots from The Ebert Dinner at the 2014 Toronto International Film Festival.


text: May 7, 2012 News Hey y'all, Its getting to be that time of the lunar cycle once again! Get your lights, and glowsticks ready and be at Thorpe Saturday, May 19th at 8pm, tee off at 830!!! A/B pool, CTP prizes etc, etc, etc. We had 16 show up last time, lets see if we can get 25!?!??!? -Josh Share this Post Tweet Like Plus one Pin It Share Related Posts League Results 4/1/14 No foolin, there was some serious wind happening on the course. Roy Lopez was the… League Results 9/17/13 The weather is changing as we had windy conditions in the beginning then as the… Saturday League Today we will play handicap at noon on the NAU course. Bring rain gear!


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Mountain Sage Community School is a tuition free, arts-integrated school inspired by Waldorf education, that integrates sustainable living practices into student life. Read about our whole child approach to education, our mission to Cultivate the Creative Mind, and our vision, here. Located in beautiful Fort Collins, Colorado, Mountain Sage Community School will grow by one grade each year, becoming a K-8 school by the 2016-2017 academic year.
Now accepting K-6 Intent to Enroll forms for the 2014-15 and 2015-16 school years. Submit yours today!
Pictures of Mountain Sage generously provided by Rambling Roots Art
Monthly school tours are currently held on the first Wednesday of each month from 9:30-10:30 am. Email firstname.lastname@example.com, or call 970-568-5456 for scheduling.
School News
Seeking Kindergarten Teacher- We are currently seeking a long-term substitute to serve as lead kindergarten teacher. Learn more here.
Harvest Festival is October 4th! Each enrolled family should have received information from your teacher or class parent about your class' responsibilities for this school community festival. Remember to BYODW (bring your own dishware) to support our zero waste events. See you this Saturday!
October 8th is International Bike and Walk to School Day. Gear up for this special day by joining the Walking School Bus or using the remote park and walk locations. Learn more here.
Amazon Smile added to the fundraising options for MSCS. If you buy anything on Amazon.com, use Amazon Smile and the school earns 5% of your purchase at no cost to you! Learn more here.


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Trafalgar Square
My second and last entry for the Association of Illustrators Prize for Illustration 2015.
Tatiana greeting her fans (◕‿◕✿)
(Source: genetically-identical)
(Source: jakeparalta)
Random thoughts recently. Yes. I tweeted most of these. Whatever.
- This American Girl episode of Project Runway makes me think of the store in Chicago and how my family went when I was younger.
- I'm still annoyed Little Mix canceled their tour in PHX
- Friendships that organically grow apart still are sad.
- I enjoy being called a feminist as an insult. Particularly when it involves the NFL. Because I'm a girl who doesn't know football. DUH.
- I'm also being nostalgic for the most random things lately.
Always a good day when I'm with my sisters #DeLosPantalones Love these amazing women @amberrosetamblyn @blakelively @alexisbledelofficial
(Source: teamamericaferrera)
I am so using this line
(Source: skinsluver)
(Source: jakeparalta)
(Source: de4thstarr)
Funny and Cute Illustrations by Jaco Haasbroek
(Source: clonespiracy)


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Home improvement and appliance retailer The Home Depot(R), declared a first-quarter cash dividend of U.S. $0.10 per share. The board also authorized an additional $1 billion to repurchase outstanding shares, bringing the total authorized share repurchase program to $10 billion. Over the past 4 years, the company has repurchased $8.1 billion of its outstanding shares.
"Our solid first quarter results reflect the hard work and dedication of our 325,000 associates," said Bob Nardelli, chairman, president, and CEO. "The company's relentless focus on our strategy has enabled us to effectively manage our business, serve our customers and produce sustainable financial results. The board's decision today supports our commitment of reinvesting in the business for growth and returning cash to our shareholders."
In the past 4 years, the company said it has returned over 55 percent of its cumulative earnings to the company's shareholders in the form of dividends and share repurchases. The retailer also said it showed a return on invested capital of 22 percent at the end of the first quarter of 2005.
The dividend is payable on June 23, 2005, to shareholders of record on the close of business on June 9, 2005.
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Sep 19, 2014: Builder confidence at highest level since Nov. 2005
Sep 19, 2014: Builders Show, Kitchen/Bath Show, and 3 other events converge for 2015 Design & Construction Week
Sep 19, 2014: GE Appliances supporting Susan G. Komen
Sep 18, 2014: AHRI at White House unveils $5 billion refrigerant R&D plan
Sep 18, 2014: Solar microinverter market could break $1 billion by 2018
Daily News>>
March 2014: Market Research - 62nd Annual U.S. Appliance Industry Forecast
February 2014: Appliance Magazine Market Insight: December 2013
January 2014: Market Research - Appliance Historical Statistical Review: 1954-2012
January 2014: Appliance Magazine Market Insight: November 2013