EP1625374A1 - Method for the detection and quantitative evaluation of a balance error in a shaft-bearing system - Google Patents
Method for the detection and quantitative evaluation of a balance error in a shaft-bearing systemInfo
- Publication number
- EP1625374A1 EP1625374A1 EP04707876A EP04707876A EP1625374A1 EP 1625374 A1 EP1625374 A1 EP 1625374A1 EP 04707876 A EP04707876 A EP 04707876A EP 04707876 A EP04707876 A EP 04707876A EP 1625374 A1 EP1625374 A1 EP 1625374A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- value
- measurement signal
- bearing
- unbalance
- determined
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
- 238000000034 method Methods 0.000 title claims abstract description 43
- 238000001514 detection method Methods 0.000 title abstract description 5
- 238000011158 quantitative evaluation Methods 0.000 title abstract description 3
- 230000003068 static effect Effects 0.000 claims abstract description 15
- 238000005096 rolling process Methods 0.000 claims abstract description 13
- 230000008859 change Effects 0.000 claims abstract description 12
- 238000004458 analytical method Methods 0.000 claims abstract description 5
- 230000000737 periodic effect Effects 0.000 claims abstract description 4
- 238000005259 measurement Methods 0.000 claims description 59
- 230000006978 adaptation Effects 0.000 claims description 13
- 238000004364 calculation method Methods 0.000 claims description 13
- 238000011156 evaluation Methods 0.000 claims description 13
- 230000010355 oscillation Effects 0.000 claims description 9
- 238000010972 statistical evaluation Methods 0.000 claims description 3
- 238000012360 testing method Methods 0.000 abstract description 5
- 238000004519 manufacturing process Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 230000009466 transformation Effects 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 238000005070 sampling Methods 0.000 description 2
- 238000012935 Averaging Methods 0.000 description 1
- 239000006096 absorbing agent Substances 0.000 description 1
- 230000003044 adaptive effect Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000001066 destructive effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 238000007620 mathematical function Methods 0.000 description 1
- 230000003595 spectral effect Effects 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/14—Determining imbalance
- G01M1/16—Determining imbalance by oscillating or rotating the body to be tested
- G01M1/22—Determining imbalance by oscillating or rotating the body to be tested and converting vibrations due to imbalance into electric variables
- G01M1/225—Determining imbalance by oscillating or rotating the body to be tested and converting vibrations due to imbalance into electric variables for vehicle wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
- F16C19/522—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to load on the bearing, e.g. bearings with load sensors or means to protect the bearing against overload
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/14—Determining imbalance
- G01M1/16—Determining imbalance by oscillating or rotating the body to be tested
- G01M1/22—Determining imbalance by oscillating or rotating the body to be tested and converting vibrations due to imbalance into electric variables
Definitions
- the invention relates to a method for determining and for the quantitative evaluation of an imbalance occurring in a shaft-bearing system according to the preamble of claim 1.
- Such a method can be used advantageously where rotating bodies have imbalances that increase the life of a Component storage system must be eliminated.
- DE 27 46 937 A1 shows a force measuring bearing in which strain gauges are fastened in a circumferential groove of a fixed bearing outer ring and are connected to other electrical resistances in an electrical measuring bridge.
- Unbalance i.e. from the degree of mass misalignment and the speed, lead to permanent bearing damage more or less quickly, which can ultimately cause the total failure of a machine.
- the rotatable components are usually clamped into a balancing device at the end of their manufacturing process and checked there for the presence of imbalances. As soon as the location of the imbalance and its size have been determined, the imbalance can be eliminated, for example, by adding additional masses (also called absorber masses) or by removing the mass causing the imbalance.
- additional masses also called absorber masses
- unbalanced masses can also occur on rotatably mounted bodies during use.
- operational imbalances can arise from the fact that over time dirt collects at preferred locations on the shaft surface and an imbalance in the rotating masses occurs.
- material can be removed from the surface of the drive shaft at a certain point over time, for example by an object that is periodically abraded on the drive shaft, which likewise leads to an imbalance in the rotating masses and thus to an imbalance.
- a measurement signal generated by strain gauges on the bearing run through a frequency filter which separates a carrier frequency from a modulation frequency of the measurement signal.
- the undisturbed sinusoidal measurement signal oscillation caused by the periodic rolling over of the rolling elements is regarded as the carrier frequency, while the forces acting on the sensors of the bearing due to the imbalance are referred to as the modulation frequency.
- a disadvantage of this known method is that when the modulation frequency changes, for example by changing the component speed, the frequency filter must also be adjusted accordingly with regard to its filter properties. This can only be practiced in the case of digitally operating frequency filters, but is associated with a considerable and therefore time-consuming computing effort. So-called “observers” are often adaptively tracked for this, which are based on special mathematical functions. However, with regard to the analysis method used there, care must be taken to determine which plausible results can also be achieved while tracking such frequency filters. This is generally made more difficult that such digital filters have a transient response that the
- Another method for determining the unbalance of a rotatably mounted body is also based on the aforementioned amplitude-modulated measurement signal, in which the unbalance magnitude frequency response is determined by means of a Fourier transformation.
- a Fourier transform is one Averaging process includes, with a rapid change in the component speed, the assignment of spectral components that indicate an imbalance is difficult to carry out.
- the resolution of the magnitude spectrum is determined by the length of the time interval that can be used for the transformation. Measuring signal analyzes for unbalance determination using the Fourier transformation can generally only be carried out offline, ie only with a time delay, due to the necessary calculation steps. This is disadvantageous above all in the case of imbalances arising from operation, since these occur completely unexpectedly and can build up quickly with a destructive effect.
- the object of the invention is to present a method with which the occurrence and presence of unbalanced bodies which can be rotated can be determined easily, quickly and without direct inspection, so that, for example, operational imbalances can be eliminated quickly and in a targeted manner and bearing damage avoided can be.
- the invention is based on the knowledge that the measurement signal of a measurement bearing known per se with sensors which change their electrical resistance in a pressure-sensitive manner can also be used to determine the presence of an unbalance and the rotational frequency of the unbalance of a component carried in the bearing.
- a component generates a load in the bearing, which also has a dynamic component from a static component and, in the presence of an imbalance.
- Both load components are contained in the measurement signal, the signal component of the static load being superimposed on the dynamic load component and thus leading to amplitude modulation of the sensor signal.
- the dynamic changes in amplitude are examined in more detail.
- the period or frequency of the vibration generated by an unbalance in the measurement signal and its variance are determined from it. This variance is then compared with a predefined variance threshold value, a drop below the threshold value being evaluated as an indication of a significant imbalance in the bearing.
- the invention relates to a method for determining and quantitatively determining an unbalance of a component mounted in a roller bearing, in which the static and dynamic forces acting on the bearing are measured using sensors arranged on the roller bearing and changing their electrical resistance in a pressure-dependent manner and in the form of both Forces common periodic measurement signal is provided to a computer for analyzing the signal curve.
- the following method steps are preferably provided in this method:
- This process sequence can also be used with a comparatively small one
- An evaluation device ie a microcomputer, detects an imbalance in real time, which acts on the component accommodated in a bearing.
- the formation of very small imbalances on rotatably mounted components can therefore be determined very early and very cost-effectively. This is particularly advantageous if the unbalance occurs suddenly and as a result of the operation. In such cases in particular, impending bearing damage can be recognized very quickly and efficiently and avoided by shutting down the rotating component. In this way, considerable costs can be saved, which would arise from a warehouse failure with subsequent bearing exchange and any production downtime. Instead, it will be sufficient in most practical cases, for example, to continuously or suddenly remove auxiliary materials or product components from a shaft that are adhering to this shaft when the machine is at a standstill.
- this measurement signal is freed of its offset value before the first process step enumerated. This is preferably done by an adaptive-recursive mean value estimation.
- Another embodiment of the method according to the invention also provides for the course of the minimum and maximum measurement signal strokes to be freed from the proportion of the static force acting on the bearing (method step b) likewise by means of adaptive-recursive mean value estimation.
- the equation for the estimated mean is preferably used to carry out this adaptive-recursive mean value estimation
- E ⁇ X r (k + 1) the expected value for the weighted arithmetic mean and E indicates the current expected value of a weighted arithmetic mean x
- k for the run variable, x stand for a digital sample value of the measurement signal or the measurement signal strokes and c for an adaptation constant.
- EX 2 r (k + 1) EX 2 r (k) + c x 2 [x 2 (k + 1) - EX 2 f (k)] [Eq. 2]
- E i X 2 r (k + 1) stands for the expected value of the weighted arithmetic mean value of the second order and E ⁇ x 2 ⁇ (k) for the current expected value of the second order, while k is a run variable, x is a value for the determined period of the unbalance and c represent an adaptation constant.
- the location of the unbalance on the component rotatably mounted in the roller bearing can be determined with the method according to the invention in that, with a known spatial arrangement of the sensor on the roller bearing, the time of occurrence of a dynamic measurement signal amplitude caused by the unbalance is the location of the unbalance at the Component marked.
- FIG. 1 shows a schematic cross section through a measuring bearing with an unbalanced component stored therein
- FIG. 2 shows the course of a measurement signal from the sensors of the bearing according to FIG. 1
- FIG. 3 shows the course of the measurement signal after it has been freed from the offset portion of the measurement system
- FIG. 4 shows the course of the measurement signal strokes for each period of the measurement signal in accordance with FIG. 3,
- FIG. 5 shows an oscillation period curve adjusted for the static portion of the measurement signal strokes according to FIG. 4,
- FIG. 6 shows an oscillation period course according to FIG. 5 after interpolation in the time direction
- FIG. 7 shows a statistical representation of unbalance periods determined by five sensors A to E in a so-called box plot.
- FIG. 1 accordingly shows a measuring bearing 1, which comprises a fixed outer ring 2 and a rotatable inner ring 3, between which rolling elements 4 are arranged. While the inner ring 3 receives and supports a cylindrical component 5, 2 sensors are attached to the outside of the bearing outer ring in measuring bridges 6, 7, 8, 9, which change their electrical resistance depending on the pressure.
- the sensors of the measuring bridges 6, 7, 8, 9 are strain-dependent resistors which are connected to one another in a manner known per se.
- piezoelectric pressure transducers can also be used sensibly.
- the arrangement of the measuring bridges of FIG. 1 is an exemplary embodiment and can be varied as desired and / or the number of measuring bridges can be changed.
- the output signal of the measuring bridges 6, 7, 8 or 9 is forwarded to an evaluation device 10, which is preferably designed as a microcomputer attached to the bearing outer ring 3.
- the evaluation device 10 determines values from the output signal of the measuring bridges 6, 7, 8, 9 in each case in detail in real time, the occurrence or existence of an imbalance on the rotatably mounted component 5 can be concluded.
- the evaluation device 10 it is also possible for the evaluation device 10 to carry out only part of the calculation work and to send intermediate values in this regard to a more powerful computer 11 which is arranged outside the bearing 1 and is connected to the evaluation device 10 via data lines.
- the evaluation device or devices 10, 11 can use the method according to the invention to determine and display an imbalance in the rotatably mounted component 5.
- the measuring bridges 6, 7, 8 or 9, which are preferably arranged on the fixed outer bearing ring 3, generate an essentially sinusoidal measuring signal when their mounting locations roll over, the characteristic change of which over time in the event of a static force F s of 10 kN is shown in this figure. Since an imbalance acts on the component 5, the signal curve also shows that the amplitudes do not all reach the same maximum or minimum value. The respective difference between the minimum and maximum amplitude values is due to the fact that the force Fu arising from the unbalance in this example is 0.25 kN via the bearing inner ring 3 and the
- Rolling element 4 is passed on to the bearing outer ring 2.
- the dynamic unbalance force Fu and the static bearing force F s overlap, the latter acting on the bearing 1 and thus on the measuring bridge 8 even with a balanced component 5 or non-rotating component 5 because of the gravitational force directed vertically downwards.
- This superposition of forces F s + Fu is therefore generally detectable and can be evaluated using measurement technology.
- the measurement signal shown in FIG. 2 is first digitized, in order to then gradually subject a digital measurement signal value to an adaptive-recursive mean value estimate online.
- the applied digital value is weighted with an average value obtained from later digital values.
- adaptive-recursive mean value estimation means that result values of the first mean value calculation are included in the calculation of the next mean value. This enables the signal amplitude to be estimated consistently on the basis of only one new sample value in each case, without a large storage and computing capacity having to be kept available in an electronic evaluation device 10, 11.
- the weighted arithmetic mean is therefore determined using the recursive basic equation
- E iXr (k) indicates the instantaneous expected value of the weighted arithmetic mean x, while k stands for a run variable, x for a digital sample of the measurement signal and c for an adaptation constant.
- the estimated instantaneous average value E ⁇ Xr (k) is subtracted from the current sample value of the sensor signal at each sampling time, so that an offset-free measurement signal curve shown in FIG. 3 is produced.
- the adaptation constant c is a value that is less than one and greater than zero and from the equation for the so-called adaptation speed
- the so-called signal strokes that is to say the maximum and minimum amplitude value of the measurement signal per period for an oscillation period, are then determined.
- the current sample value of the measurement signal is compared with the previous sample value.
- a register max_wert for storing the maximum value of a period is set to zero in the evaluation device.
- the new sample value is stored in this register max_wert. In this way, the register content for the maximum value is renewed with increasing positive amplitude values until a new one
- the measurement signal changes from plus to minus. At this point in time, the maximum of the positive half-wave is reliably determined one period of the measured signal.
- the minimum value min_value of the now following negative half-wave of the measurement signal is then determined in the same way.
- the difference in the stored maximum and minimum values is used to calculate the signal swing of the examined period and thus the total force at the measuring point, which is composed of the dynamic component Fu and the static component F s caused by the unbalance.
- This offset compensation process continues over time. In this way, the signal strokes or the amplitudes of the total force F s + Fu for each period of the measurement signal are determined, which are shown by way of example in FIG. 4.
- the portion of the static force F s which is to be regarded here as the second offset value is removed from the offset-free signal stroke curve according to FIG. 4.
- this second offset value is approximately at a value of 1 ⁇ V, around which the dynamic signal swing values fluctuate. If these unbalanced measurement signal stroke values are released by means of a new adaptive-recursive mean value calculation in accordance with the above-mentioned equation [Eq. 1] from this second offset value, the curve of an oscillation around the zero point shown in FIG. 5 is obtained, the period of which correlates with the rotational speed of the rotatably mounted component 5 in the presence of an imbalance.
- the peaks of the sample values according to FIG. 5 describe a continuous curve, from the points of intersection with the abscissa or with the zero line of which three-point calculation from the amplitude values and the time values of the last positive Sampling value before a crossing point and after this crossing point the period is calculated.
- E ⁇ X 2 r (k + 1) stands for the expected value of the weighted arithmetic mean value of the second order and E ⁇ X 2 r (k) for the current expected value of the second order, while k is a run variable, x a current determined value of the period of the unbalance and c represent an adaptation constant.
- FIG. 7 shows the calculated period average values of the measurement signals from five different sensors A to F, which were used in five different unbalance detection tests. The imbalances found in these tests are of varying degrees of strength, but they are still below an unbalance threshold determined empirically beforehand.
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Testing Of Balance (AREA)
- Measurement Of Mechanical Vibrations Or Ultrasonic Waves (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10305067A DE10305067A1 (en) | 2003-02-07 | 2003-02-07 | Method for determining and quantitatively evaluating an imbalance in a shaft-bearing system |
PCT/DE2004/000183 WO2004070340A1 (en) | 2003-02-07 | 2004-02-04 | Method for the detection and quantitative evaluation of a balance error in a shaft-bearing system |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1625374A1 true EP1625374A1 (en) | 2006-02-15 |
Family
ID=32730868
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04707876A Withdrawn EP1625374A1 (en) | 2003-02-07 | 2004-02-04 | Method for the detection and quantitative evaluation of a balance error in a shaft-bearing system |
Country Status (5)
Country | Link |
---|---|
US (1) | US7650254B2 (en) |
EP (1) | EP1625374A1 (en) |
JP (1) | JP4379816B2 (en) |
DE (1) | DE10305067A1 (en) |
WO (1) | WO2004070340A1 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004027800B4 (en) | 2004-06-08 | 2006-04-06 | Fag Kugelfischer Ag & Co. Ohg | Method and computer program for determining operating parameters in a rolling bearing and evaluable rolling bearing hereby |
DE102004048095A1 (en) * | 2004-09-30 | 2006-04-06 | Carl Zeiss Industrielle Messtechnik Gmbh | Stylus and stylus replacement holder for a coordinate measuring machine |
US8136405B2 (en) * | 2005-08-31 | 2012-03-20 | Siemens Aktiengesellschaft | Method and device for monitoring the dynamic behavior of a rotating shaft, in particular of a gas or steam turbine |
DE102010012915A1 (en) * | 2010-03-26 | 2011-09-29 | Schaeffler Technologies Gmbh & Co. Kg | Device and method for determining a damage state of a wheel bearing |
US10684193B2 (en) | 2015-06-08 | 2020-06-16 | Pioneer Engineering Company | Strain based systems and methods for performance measurement and/or malfunction detection of rotating machinery |
US9841329B2 (en) | 2015-06-08 | 2017-12-12 | Pioner Engineering Company | Strain gage based system and method for failure detection of a fluid film bearing |
DE102017223628A1 (en) * | 2017-12-21 | 2019-06-27 | Aktiebolaget Skf | condition monitoring |
EP3489650B1 (en) * | 2017-11-22 | 2020-06-17 | ALSTOM Transport Technologies | System and method for measuring motor bearings consumption of railway vehicles |
CN117288383B (en) * | 2023-11-23 | 2024-05-10 | 南通进宝机械制造有限公司 | Machine static and dynamic balance optimization test method based on data analysis |
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US3697841A (en) * | 1971-04-16 | 1972-10-10 | Whirlpool Co | Induction motor structure and reversing circuit therefor |
JPS5925167B2 (en) * | 1975-03-25 | 1984-06-15 | 三菱重工業株式会社 | How to inspect rotating shaft systems by measuring bearing reaction force |
US4027539A (en) * | 1976-04-09 | 1977-06-07 | Halloran John D | Apparatus for, and method of, measuring dynamic forces |
US4060003A (en) * | 1976-10-18 | 1977-11-29 | Ransburg Corporation | Imbalance determining apparatus and method |
DE2746937C2 (en) * | 1977-10-17 | 1986-11-06 | Gerhard Dr.-Ing. 1000 Berlin Lechler | Force measuring device |
US4666315A (en) * | 1981-06-12 | 1987-05-19 | International Business Machines Corporation | Planar and cylindrical oscillating pneumatodynamic bearings |
US4464935A (en) * | 1983-05-09 | 1984-08-14 | General Electric Company | Shaft vibration evaluation |
JPS60148944U (en) * | 1984-03-14 | 1985-10-03 | 新日本製鐵株式会社 | Bearing for radial load measurement |
US4700117A (en) * | 1985-05-31 | 1987-10-13 | Beckman Instruments, Inc. | Centrifuge overspeed protection and imbalance detection system |
JPH065193B2 (en) * | 1987-04-28 | 1994-01-19 | 光洋精工株式会社 | Bearing remaining life prediction device |
US4941105A (en) * | 1988-09-29 | 1990-07-10 | University Of Pittsburgh | Method and apparatus for measuring dynamic bearing force |
US5140849A (en) * | 1990-07-30 | 1992-08-25 | Agency Of Industrial Science And Technology | Rolling bearing with a sensor unit |
JPH0711473B2 (en) * | 1990-10-25 | 1995-02-08 | 旭化成工業株式会社 | Abnormality detection method and device |
JPH063215A (en) * | 1992-06-19 | 1994-01-11 | Kao Corp | Diagnostic method and diagnosing device for rotary equipment |
DE19522543A1 (en) * | 1994-08-01 | 1996-02-08 | Ntn Toyo Bearing Co Ltd | Piezoelectric measuring sensor system for roller bearings |
US5747953A (en) * | 1996-03-29 | 1998-05-05 | Stryker Corporation | Cordless, battery operated surical tool |
US5905212A (en) * | 1997-06-04 | 1999-05-18 | Continental Emsco Company | Load and deflection measurement system for elastomeric bearings |
DE19828498C2 (en) * | 1998-06-26 | 2001-07-05 | Fraunhofer Ges Forschung | Method for measuring unbalance of rotating bodies and device for carrying out the method |
US6490935B1 (en) * | 1999-09-28 | 2002-12-10 | The Timken Company | System for monitoring the operating conditions of a bearing |
JP2001200841A (en) * | 2000-01-19 | 2001-07-27 | Ntn Corp | Bearing abnormality detecting device in bearing device |
US6687623B2 (en) * | 2000-05-17 | 2004-02-03 | Ntn Corporation | Real time bearing load sensing |
FR2812356B1 (en) * | 2000-07-28 | 2002-12-06 | Roulements Soc Nouvelle | BEARING COMPRISING AT LEAST ONE ELASTIC DEFORMATION ZONE AND BRAKING ASSEMBLY COMPRISING SAME |
JP3530474B2 (en) * | 2000-09-22 | 2004-05-24 | 三菱重工業株式会社 | Wing vibration measurement method and wing vibration monitoring system using the same |
US6766697B1 (en) * | 2000-12-06 | 2004-07-27 | Bearings Plus, Inc. | Hydrodynamic bearings having strain sensors |
US6879126B2 (en) * | 2001-06-29 | 2005-04-12 | Medquest Products, Inc | Method and system for positioning a movable body in a magnetic bearing system |
JP4093392B2 (en) * | 2001-08-01 | 2008-06-04 | 大日本コンサルタント株式会社 | Self-supporting network measurement system |
-
2003
- 2003-02-07 DE DE10305067A patent/DE10305067A1/en not_active Withdrawn
-
2004
- 2004-02-04 JP JP2006501488A patent/JP4379816B2/en not_active Expired - Fee Related
- 2004-02-04 EP EP04707876A patent/EP1625374A1/en not_active Withdrawn
- 2004-02-04 US US10/544,507 patent/US7650254B2/en not_active Expired - Fee Related
- 2004-02-04 WO PCT/DE2004/000183 patent/WO2004070340A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2004070340A1 * |
Also Published As
Publication number | Publication date |
---|---|
JP2006516726A (en) | 2006-07-06 |
WO2004070340A1 (en) | 2004-08-19 |
US7650254B2 (en) | 2010-01-19 |
US20060235628A1 (en) | 2006-10-19 |
JP4379816B2 (en) | 2009-12-09 |
DE10305067A1 (en) | 2004-08-19 |
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