WO1997040943A1 - Apparatus and method for stabilizing a centrifuge rotor - Google Patents
Apparatus and method for stabilizing a centrifuge rotor Download PDFInfo
- Publication number
- WO1997040943A1 WO1997040943A1 PCT/US1997/006579 US9706579W WO9740943A1 WO 1997040943 A1 WO1997040943 A1 WO 1997040943A1 US 9706579 W US9706579 W US 9706579W WO 9740943 A1 WO9740943 A1 WO 9740943A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- disk
- rotor
- set forth
- vibrations
- centrifuge
- Prior art date
Links
Classifications
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
- B04B—CENTRIFUGES
- B04B9/00—Drives specially designed for centrifuges; Arrangement or disposition of transmission gearing; Suspending or balancing rotary bowls
- B04B9/12—Suspending rotary bowls ; Bearings; Packings for bearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
- B04B—CENTRIFUGES
- B04B9/00—Drives specially designed for centrifuges; Arrangement or disposition of transmission gearing; Suspending or balancing rotary bowls
- B04B9/14—Balancing rotary bowls ; Schrappers
- B04B9/146—Unbalance detection devices
-
- 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1485—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being unlimited with respect to driving means
- F16F15/1492—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being unlimited with respect to driving means with a dry-friction connection
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/30—Flywheels
- F16F15/305—Flywheels made of plastics, e.g. fibre-reinforced plastics [FRP], i.e. characterised by their special construction from such materials
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/30—Flywheels
- F16F15/315—Flywheels characterised by their supporting arrangement, e.g. mountings, cages, securing inertia member to shaft
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S29/00—Metal working
- Y10S29/901—Balancing method
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49002—Electrical device making
- Y10T29/49009—Dynamoelectric machine
- Y10T29/49012—Rotor
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2109—Balancing for drum, e.g., washing machine or arm-type structure, etc., centrifuge, etc.
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2121—Flywheel, motion smoothing-type
- Y10T74/2131—Damping by absorbing vibration force [via rubber, elastomeric material, etc.]
Definitions
- the present invention relates to a method and apparatus for accomodating rotating bodies, and, in particular, to a method and apparatus for reducing vibrations induced in centrifuge rotors during rotor acceleration and deceleration through the critical and slew speeds of the rotor.
- a centrifuge is an apparatus for subjecting a sample of a material to a centrifugal force in order to separate by density the sample into its constituent components.
- a common use for a centrifuge is in a clinical analytical laboratory where blood obtained from a patient is separated by centrifugal force into red cells and plasma components.
- the centrifuge includes a rotating member, or rotor, mounted for high speed rotational movement usually within a stationary, protective casing.
- the rotor may be outfitted with buckets or cavities which carry the sample to be separated during exposure to the centrifugal force.
- the rotor is part of a centrifuge system that includes a motor or other source of motive energy, a drive shaft, and a rotor mounting device disposed at the upper end of the drive shaft on which the rotor is received.
- a motor or other source of motive energy e.g., a motor or other source of motive energy
- a drive shaft e.g., a motor or other source of motive energy
- a rotor mounting device disposed at the upper end of the drive shaft on which the rotor is received.
- the rotor has certain natural frequencies of vibration which become apparent when the rotor is rotating at certain critical speeds.
- the rotor normally rotates about its geometric center of gravity. At critical speeds (resinant frequencies of the rotor) , the rotor tries to shift its axis of rotation laterally from that of the rotors geometric center to that of the rotors center of mass. This causes the rotor to vibrate.
- the centrifuge's rotor mount, or gyro, design is provided with some form of compliance mechanism which accomodates the forces generated by the system as the rotor's rotation approaches and traverses its critical speed.
- centrifuge rotor When an operator is loading a centrifuge rotor, important objective is achieving a weight-balanced, symmetrical sample distribution pattern about the drive shaft and instructions are normally provided to reach this objective. However, even reasonable balance is frequently not possible. For example, an emergency situation may require operating a centrifuge with only a partially filled rotor, or in an extreme situation, operating a centrifuge with only a single tube contained within the rotor. Thus a second important consideration in design of a centrifuge is reducing rotor vibrations arising from non-symmetrical sample loading conditions that may otherwise be capable of damaging the centrifuge. If not reduced or sufficiently dampened, the total imbalancing forces, arising from inherent rotor imbalances and/or sample loading patterns may result in premature failure of the centrifuge.
- U.S. Pat. No. 4,846,773 discloses a vibration damper for a centrifuge in which the rotor drive shaft bearing has a frustoconical surface. Vibrations of the drive shaft traverse to its rotational axis and are transformed by means of the frustoconical surface into linear motion of a plunger concentrically mounted on the drive shaft. The plunger is mounted inside a solenoid and has its linear movement dampened by the solenoid.
- U.S. Pat. No. 4,236,426 (Meinke et al) relates to a damping system for a centrifuge rotor in which springs, dampers, weights and/or attenuators are coupled and uncoupled with respect to the rotor. This alters the flexural properties of the rotor as its rotational speed approaches critical speed. The effect of these damping devices is to alter the critical speed of the rotor. The devices are activated and deactivated to facilitate the rotors passage through critical speed.
- U.S. Pat. No. 4,098,457 (Gropper et al) relates to a floating stator pad attached to a stationary stator with means to increase the friction between the pad and the stator. Excessive vibrations of the rotor are transmitted by frictional contact to the stator pad. Gropper et al provide for increasing the frictional contact between the stator pad and stator so as to increase the efficiency of the stator pad in damping vibrations.
- U.S. Pat. No. 3,322,338 (Stallman et al) discloses a centrifuge having a movable bearing assembly carried by a frame that supports a rotatable member coaxially with the axis of rotation of the motor.
- the rotatable member is movable between advanced and retracted positions to release the rotor and to engage the rotor to hold it in a defined axis of rotation.
- the rotatable member is permitted to move laterally within predetermined limits, thereby damping lateral rotor movement at critical transition speeds.
- U.S. Pat. No. 2,961,277 discloses a bearing system in which a shaft has a frustoconical journal portion intermediate the ends of the shaft, which are supported on fixed bearings.
- a bearing is mounted on an adjustable support to be movable into or out of engagement with the frustoconical journal. The movable bearing is engaged with the journal before the shaft reaches the critical angular velocity and is disengaged from the shaft after the angular velocity is greater than the critical value.
- U.S. Pat. No. 2,951,731 discloses a centrifuge having damping means including two sets of concentric, spaced apart cylindrical sleeves. The sleeves are arranged to follow shaft vibrations and overlap with other sleeves that are fixed with respect to the shaft. A viscous liquid is retained between the overlapping sleeves to damp out shaft vibrations.
- U.S. Pat. No. 3,430,852 discloses a centrifuge rotor stabilizing device that frictionally contacts the rotor to provide stability at critical speeds.
- These prior art approaches generally rely upon mechanical contact and associated forces to constrain the movement of the rotor. This is generally accomplished by shifting the vibration from the rotor to another mechanical component. This mechanical contact usually involves frictional contact to provide dissipative energy losses.
- U.S. Pat. No. 3,902,659 (Brinkman et al. ) discloses a rotor stabilizing device having an upper bearing formed of a first axially polarized magnetic ring and a second ring including a ferrite material .
- One of the rings is secured to the rotor, and the other ring is held stationary relative to the rotor.
- the rings are positioned such that oscillations of the rotor cause eddy currents in the induction ring, which absorbs the energy of the vibrations.
- Brinkman et al . are seen to overcome some of the prior art problems associated with the use of friction to alleviate vibration occurring at critical speeds. Unfortunately, their solution of using a magnetic coupling does not accomodate large critical speed vibrations well.
- the present invention overcomes many of the difficulties associated with the complex dynamics of known damping systems including those that require movement of mechanical devices and/or high friction interactions to accomodate vibrations that are generated within rotating systems, particularly in the instance of highly non-symmetrically loaded rotors.
- the present invention relates to a method and apparatus for accomodating and/or restraining vibrations of a rotor used in a centrifuge instrument.
- the invention is an apparatus for accomodating vibrations in a centrifuge rotor comprising: a drive shaft having a vertical axis for mounting a centrifuge rotor for rotation about said axis, driving means for rotating said shaft, bearing means mounted on said shaft, a disk mounted on said bearing means, whereby the disk can rotate about said shaft, and restraining means to limit the vertical movement of said disk, thereby to allow the rotor to rotate about its center of mass.
- a desirable feature of the invention includes means to sense the radial displacement of said disk, and means responsive to the radial displacement exceeding a predetermined value to restrain the rotation of said disk, thereby to damp vibrations of the centrifuge rotor.
- the invention is seen to include a method for accomodating vibrations that occur in a body rotating about its geometric axis when the body passes through its critical speed, the body having a moment of inertia and a mass center, comprising the steps of: maintaining the movement of inertia of the body, and allowing the body to shift its rotational axis to that of its mass center.
- the rotor By providing a sliding support for a freely rotating disk mounted on the drive shaft of the rotor, the rotor is permitted to shift its spin axis to that of the center of mass.
- the invention thus adds radial mass to the rotor but not moment of inertia as do the prior art systems. This reduces the tendency of the rotor to vibrate even at critical speeds and does not slow the rotor speed to reduce vibrations even at critical speed as does much of the prior art.
- the rotor is peripherically gripped by sliding bearings to dampen by means of the disk such vibration. No elastomeric materials are used, hence oscillations due to spring constants are not precipitated.
- the apparatus of the invention is simple and does not require the use of complex rotating type dampeners.
- Figure 1 is a perspective view of a centrifuge which uses a method and apparatus for reducing vibrations in the centrifuge rotor:
- Figure 2 is an exploded view of the gyro for the centrifuge depicted in Fig. 1:
- Figure 3 is a cutaway elevation view of the gyro of Fig. 2:
- FIG. 4 is a block diagram of a vibration sensor used with the centrifuge accomodating apparatus of Fig. 1.
- FIG. 1 a rotating body vibration accomodating apparatus constructed in accordance with this invention.
- the apparatus illustrated is a gyro for a centrifuge rotor.
- the gyro includes an upper drive shaft 11 for driving and positioning or mounting the rotor (Fig. 3) .
- a knob 12 is provided for securing such a rotor on the gyro.
- the vibration accomodating apparatus of this invention includes a housing 10 having a cap 16 secured thereto as by screws 18.
- the drive pulley 17 which may be attached to a suitable motor (not shown) for rotating the upper drive shaft 11.
- a rotor 13 which may be of a conventional type mounted to the upper shaft 11 and secured by the knob 12.
- the gyro is formed of two shafts, the upper shaft 11, as noted, and a lower drive shaft 20, the shafts bearing coupled together by a flexible coupling 22 which permits relative lateral motion (perpendicular to the axis of rotation of the shafts) between the two shafts.
- the flexible coupling 22 may be any suitable coupling of this type, one suitable coupling being that manufactured by Servometer Corporation.
- the flexible coupling 22 has upper and lower end cap mounts 24 and 26, respectively.
- the lower end cap mount 26 has a dowpin 28 mounted therein which is used as a flag for sensing the home position of the rotor (shafts) . This position is sensed by a suitable transducer 30 which observes the position of the flag 28 and may be used in a known manner to control the position of the rotor.
- the lower drive shaft 20 is secured by suitable ball bearings 32 positioned within a bearing housing 38 by appropriate washers and retaining rings 34.
- the ball bearings 32 are separated by a suitable spacer bearing 36.
- the bearing housing 38 is secured to the lower end of the housing 10 by suitable screws.
- the upper drive shaft 11 is in the form of a stub, the lower end of which is secured in the upper end cap mount 24 and is positioned within disk bearings 42 which are housed by a bearing housing in the form of a hub 46 to which a disk 40 is integrally formed.
- the disk 40 preferably is formed of stainless steel and is positioned within the housing 10 whos upper end is generally cup-shaped and covered by the cap 16.
- the housing 14 has a counterbore in which is positioned a plastic boss 50 which acts as a bumper to stop radial movement of the upper drive shaft 11 (and of course) .
- the disk bearings 42 are secured at either end of the housing 46 by suitable washers and retaining rings 52.
- a plurality of restraining means preferably in the form of lower support sliding bearings 60 are positioned under the disk 40 to support its rotation in a horizontal plane.
- These lower support bearings 60 are positioned in recesses 62 formed in the lower portioned of the cap shaped portion of the housing 10 preferably at equally spaced circumferential positions (6 are shown) .
- three upper sliding bearings 64 are positioned in recesses 66, formed in the cap 16, which are positioned axially above the, equally spaced, corresponding lower support bearings 60.
- the upper restraining bearings 64 are positioned, circumferentially spaced, only above three of the lower support bearings 60 allowing room for damping means in the form of solenoid activated sliding bearings 68, which are positioned directly above the remaining, equally circumferentially spaced, support bearings 60.
- the solenoid actuated bearings 68 are actuated by three solenoids 70 which is countersunk in the cap 16 and operate to actuate a solenoid shaft 72 which is attached to the damping bearings 68.
- the bearings 68 may be formed of a suitable material such as VespelTM with graphite having low sliding friction.
- the solenoids 70 are retained by an appropriate set screw 80.
- the upper restraining bearings 64 may be formed of a suitable material such as ErtalyteTM polyester which has a low sliding friction.
- the sliding bearings may be formed of any suitable material which provides a low sliding friction, such as are: teflon, nylon, delrin, to name but a few.
- the upper bearings 64 and 68 are positioned so that they either do not contact or lightly contact the upper side of the disk 40.
- Control for the solenoid is provided by a mechanism such as that depicted in Fig. 4.
- the disk is illustrated as having a light emitting diode (LED) positioned close to the periphery and overlapping the outer radial limits of the disk 40.
- the LED 40 is directed downwardly to ward a suitable detector 102.
- a lateral movement of the disk 40 would vary the amount of light reaching the detector 102, signifying a greater or lesser degree of vibrations of the disk.
- the output of the detector 102 is coupled to a suitable, conventional controller 104 to control or activate the solenoid 70 to a greater or lesser degree, depending upon the amplitude of the vibrations of the disk 40 sensed by the detector 102.
- the solenoid as described, directs the damping bearings 68 against the top face of the disk 40.
- any imbalance forces generated by the rotation of the rotor as it accelerates or decelerates through critical speed manifest themselves as vibration.
- the flexible coupling 22, such as that provided by ServoMeter Company, Cedar Grove, N.J. , permits the lateral motion of the upper shaft 11 relative to the lower shaft 20.
- the vibrations also manifest themselves in radial movement of the disk 40.
- the disk 40 is free to move perpendicular to the axis of the rotation of the upper shaft 11.
- the entire assembly including the drive shaft and any rotors mounted, is allowed to shift laterally, i.e., manner perpendicular to the axis of rotation of the drive shaft 11, and thus accomodate such vibrations.
- the apparatus of this invention adds radial mass but does not add moment of inertia because although the disk 40 is freely rotating because of the low friction of the rolling bearings 42, the disk does not rotate with the velocity of the rotor because of the friction of the sliding bearings 60.
- the restraining bearings 60 merely support the disk and impose little or no friction on it. Hence, there is little or no change in moment of inertia (the ratio of angular torque to angular acceleration produced) .
- moment of inertia the ratio of angular torque to angular acceleration produced
- solenoids 70 are activated causing the solenoid activated bearings 68 to be applied to the upper side of the disk 16, thereby damping further movement by the application of a sliding friction to the disk and limiting its ability to move in either the vertical or radial directions.
- the use of the disk 40 first accomodates vibration of the gyro and rotor and then, if such vibrations are excessive, further accomodates such vibrations by the activating the solenoid bearings 68 to engage the side of the disk 40.
- the disk by resisting vertical motion restrains oscillation which try to reposition the disk out of its plane of rotation.
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP53897197A JP4045466B2 (en) | 1996-04-30 | 1997-04-21 | Apparatus and method for stabilizing a centrifuge rotor |
EP97918750A EP0848649B1 (en) | 1996-04-30 | 1997-04-21 | Apparatus and method for stabilizing a centrifuge rotor |
DE69710166T DE69710166T2 (en) | 1996-04-30 | 1997-04-21 | DEVICE AND METHOD FOR STABILIZING A CENTRIFUGAL ROTOR |
AT97918750T ATE212566T1 (en) | 1996-04-30 | 1997-04-21 | DEVICE AND METHOD FOR STABILIZING A CENTRIFUGE ROTOR |
AU26778/97A AU714988B2 (en) | 1996-04-30 | 1997-04-21 | Apparatus and method for stabilizing a centrifuge rotor |
BR9702288A BR9702288A (en) | 1996-04-30 | 1997-04-21 | Apparatus and process for stabilizing a machine rotor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US64039196A | 1996-04-30 | 1996-04-30 | |
US08/640,391 | 1996-04-30 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997040943A1 true WO1997040943A1 (en) | 1997-11-06 |
Family
ID=24568054
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1997/006579 WO1997040943A1 (en) | 1996-04-30 | 1997-04-21 | Apparatus and method for stabilizing a centrifuge rotor |
Country Status (9)
Country | Link |
---|---|
US (2) | US5921148A (en) |
EP (1) | EP0848649B1 (en) |
JP (1) | JP4045466B2 (en) |
CN (1) | CN1196691A (en) |
AT (1) | ATE212566T1 (en) |
AU (1) | AU714988B2 (en) |
BR (1) | BR9702288A (en) |
DE (1) | DE69710166T2 (en) |
WO (1) | WO1997040943A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20210031215A1 (en) * | 2017-11-27 | 2021-02-04 | Gea Mechanical Equipment Gmbh | Separator |
Families Citing this family (37)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19910276A1 (en) * | 1999-03-09 | 2000-09-14 | Schlafhorst & Co W | Spinning rotor for open-end spinning machines and method for producing the spinning rotor |
US6183408B1 (en) * | 1999-05-03 | 2001-02-06 | Beckman Coulter, Inc. | Rotor shaft assembly having non-linear stiffness |
US6354988B1 (en) | 1999-06-17 | 2002-03-12 | Kendro Laboratory Products, Llp | Centrifuge gyro diaphragm capable of maintaining motor shaft concentricity |
FR2799547B1 (en) * | 1999-10-06 | 2002-05-24 | Gradient Ass | DISC TRIBOMETER FOR MEASURING TRIBOLOGICAL PHENOMENES |
US6635007B2 (en) * | 2000-07-17 | 2003-10-21 | Thermo Iec, Inc. | Method and apparatus for detecting and controlling imbalance conditions in a centrifuge system |
US6507799B2 (en) | 2001-02-26 | 2003-01-14 | Honeywell International Inc. | Method and apparatus for reducing microprocessor speed requirements in data acquisition applications |
KR100470068B1 (en) * | 2001-04-02 | 2005-02-05 | 주식회사 한랩 | automatic balance adjusting centrifuge apparatus |
US6532422B1 (en) | 2001-06-29 | 2003-03-11 | Honeywell International, Inc. | Simultaneous injection method and system for a self-balancing rotatable apparatus |
DE10141098A1 (en) * | 2001-08-22 | 2003-03-06 | Gen Electric | Wind turbine |
US6701561B2 (en) | 2001-09-10 | 2004-03-09 | Honeywell International Inc. | Method and system for detecting fluid injection from stationary to rotating members |
US6665625B2 (en) | 2001-09-10 | 2003-12-16 | Honeywell International Inc | Energy-based thresholds applied dynamic balancing |
US6622105B2 (en) | 2001-09-10 | 2003-09-16 | Honeywell International Inc. | Dynamic correlation extension for a self-balancing rotatable apparatus |
US6687572B2 (en) | 2001-11-15 | 2004-02-03 | Honeywell International Inc. | Supervisory method and system for improved control model updates applied to dynamic balancing |
US6795792B2 (en) * | 2001-11-15 | 2004-09-21 | Honeywell International Inc. | Continuous flow method and system for placement of balancing fluid on a rotating device requiring dynamic balancing |
US6662682B2 (en) | 2001-11-15 | 2003-12-16 | Honeywell International Inc. | Dynamic balancing application mass placement |
US6647790B2 (en) | 2001-11-15 | 2003-11-18 | Honeywell International Inc. | Fixed-bandwidth correlation window method and system for a self-balancing rotatable apparatus |
US6681430B2 (en) | 2001-11-15 | 2004-01-27 | Honeywell International Inc. | Method and system for mechanizing simultaneous multi-actuator actions applied to dynamic balancing |
US6775870B2 (en) | 2001-11-15 | 2004-08-17 | Honeywell International Inc. | Data manipulation method and system for a self-balancing rotatable apparatus |
US6546354B1 (en) | 2001-11-15 | 2003-04-08 | Honeywell International, Inc. | Resonance identification extension for a self-balancing rotatable apparatus |
US6764438B2 (en) * | 2002-04-22 | 2004-07-20 | Kendro Laboratory Products, Lp | Cover attachment apparatus |
US6802803B2 (en) * | 2002-04-22 | 2004-10-12 | Kendro Laboratory Products, Inc. | Cover attachment apparatus |
DE60310917T2 (en) * | 2002-05-22 | 2007-10-11 | Dyson Technology Ltd., Malmesbury | AUTOMATIC BALANCING DEVICE |
DE20310654U1 (en) * | 2003-07-11 | 2003-09-18 | Retsch Gmbh & Co Kg | Laboratory device with slide foot mounting |
FR2858251B1 (en) * | 2003-07-29 | 2005-10-28 | Diagyr | METHOD FOR BALANCING A ROTARY TRAY OF A CENTRIFUGE AND CENTRIFUGE EMPLOYING THE PROCESS |
KR100606264B1 (en) * | 2004-11-19 | 2006-07-31 | 주식회사 한랩 | centrifugal apparatus of automatic balancing type by fluid compensation |
KR100756231B1 (en) * | 2006-02-24 | 2007-09-06 | 주식회사 한랩 | Automatic balance adjusting rotor for centrifuge apparatus |
JP4569778B2 (en) * | 2006-09-01 | 2010-10-27 | 日立工機株式会社 | Centrifuge |
DE102007015634A1 (en) * | 2007-03-31 | 2008-10-02 | Schaeffler Kg | Damping device for transverse vibrations of shaft is in form of disc mounted by rotation bearing on shaft transversely to shaft axis and connected indirectly to housing |
US7806820B2 (en) * | 2007-05-02 | 2010-10-05 | Gary Wayne Howell | Automatic balancing device and system for centrifuge rotors |
SE533089C2 (en) * | 2008-05-13 | 2010-06-22 | Alfa Laval Corp Ab | centrifugal |
CN103687638B (en) * | 2011-07-13 | 2017-05-10 | 费雪派克医疗保健有限公司 | Impeller and motor assembly |
CN103091118A (en) * | 2011-11-01 | 2013-05-08 | 中国航空工业集团公司北京航空精密机械研究所 | Test board for testing overload composite environment |
CN106902990A (en) * | 2017-02-28 | 2017-06-30 | 唐凌霄 | Driven centrifugal unit and its solid-liquid separating equipment |
US11472540B2 (en) * | 2017-06-27 | 2022-10-18 | Moog Inc. | Variable rotary pendulous mass vibration suppression system |
US10634152B2 (en) | 2018-08-17 | 2020-04-28 | Itt Manufacturing Enterprises Llc | Multi-bearing design for shaft stabilization |
CN108927297B (en) * | 2018-09-07 | 2023-12-22 | 黄泽浩 | Automatic balancing device of laboratory centrifuge and control circuit thereof |
US11692585B2 (en) * | 2019-01-15 | 2023-07-04 | Goodrich Corporation | Composite shaft with outer periphery ring |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1419237A (en) * | 1964-12-29 | 1965-11-26 | Method for stabilizing the center of gravity of a suspended apparatus driven in rotation, as well as devices and apparatus, in particular centrifuges, for carrying out the present method or similar method | |
GB1111362A (en) * | 1966-01-24 | 1968-04-24 | Commissariat Energie Atomique | A damping centering bearing for a rotating shaft |
DE1632298A1 (en) * | 1967-12-13 | 1970-12-23 | Heinrich Hinz Fa | Device for damping the pendulum movements of centrifuge drums |
DE2112834A1 (en) * | 1970-03-17 | 1971-10-07 | Fives Lille Cail | Machine with pendulum suspended rotor with vertical axis |
EP0070157A2 (en) * | 1981-07-09 | 1983-01-19 | HAEMONETICS CORPORATION(a Massachusetts Corporation) | Improvements in centrifuges |
Family Cites Families (37)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1501187A (en) * | 1921-09-03 | 1924-07-15 | Charles L Rayfield | Flexible coupling |
US1752106A (en) * | 1927-12-19 | 1930-03-25 | Cook Electric Co | Flexible coupling |
US2951731A (en) * | 1944-09-25 | 1960-09-06 | Frank C Rushing | Centrifuges |
US2961277A (en) * | 1957-12-23 | 1960-11-22 | Gen Electric | Functional bearings |
US3232076A (en) * | 1962-12-31 | 1966-02-01 | Edward V Sundt | Flexible coupling for rotating shafts |
US3322338A (en) * | 1963-04-15 | 1967-05-30 | Beckman Instruments Inc | Centrifuge stabilizing assembly with heat probe |
US3455013A (en) * | 1964-10-28 | 1969-07-15 | Alden G Rayburn | Method of manufacture of flexible couplings |
US3430852A (en) * | 1967-06-08 | 1969-03-04 | Beckman Instruments Inc | Rotor stabilizer |
US3524332A (en) * | 1968-09-06 | 1970-08-18 | Rex Chainbelt Inc | Elastomer coupling |
AT301963B (en) * | 1969-06-11 | 1972-09-25 | Stromag Maschf | Elastic shaft coupling |
BE755911A (en) * | 1969-09-15 | 1971-02-15 | Stromag Maschf | ELASTIC COUPLING |
FR2112824A5 (en) * | 1970-11-10 | 1972-06-23 | Glaenzer Spicer Sa | |
US3727429A (en) * | 1971-06-10 | 1973-04-17 | Reliance Electric Co | Shaft coupling |
US3770191A (en) * | 1971-06-28 | 1973-11-06 | Sorvall Inc Ivan | Means for stabilizing high speed rotors |
US3902659A (en) * | 1971-12-15 | 1975-09-02 | Kernverfahrenstechnik Gmbh | Device for stabilizing the rotor of high-speed centrifuges |
US3888093A (en) * | 1974-02-21 | 1975-06-10 | Reliance Electric Co | Flexible shaft coupling |
US3955377A (en) * | 1975-05-06 | 1976-05-11 | Bendall Wilfrid H | Flexible couplings |
DE2632586C2 (en) * | 1976-07-20 | 1983-05-19 | Gesellschaft für Kernverfahrenstechnik mbH, 5170 Jülich | Method and device for running through critical speeds of elongated rotors |
DE2711065C3 (en) * | 1977-03-14 | 1982-05-19 | Gesellschaft für Kernverfahrenstechnik mbH, 5170 Jülich | Radially damped backup bearing for supercritically running rotors |
US4098457A (en) * | 1977-03-28 | 1978-07-04 | Beckman Instruments, Inc. | Friction producing stator pad for an air driven centrifuge |
US4201066A (en) * | 1978-03-29 | 1980-05-06 | Damon Corporation | Flexible shaft construction for a high inertia centrifuge |
JPS59500006U (en) * | 1982-05-19 | 1984-05-17 | ||
US4540906A (en) * | 1984-03-09 | 1985-09-10 | Synektron Corporation | Stator assembly for permanent magnet rotary device |
US4536170A (en) * | 1984-05-25 | 1985-08-20 | Reliance Electric Company | Elastomeric shear shaft coupling |
US4568324A (en) * | 1984-11-09 | 1986-02-04 | E. I. Du Pont De Nemours And Company | Rotor shaft having damper member mounted thereon |
JPS61116632A (en) * | 1984-11-10 | 1986-06-04 | Toshiba Corp | Rotary balance adjustor |
US4846773A (en) * | 1985-05-13 | 1989-07-11 | Beckman Instruments, Inc. | Rotating system critical speed whirl damper |
US5206988A (en) * | 1986-09-10 | 1993-05-04 | Beckman Instruments, Inc. | Hybrid ultra-centrifuge rotor with balancing ring and method of manufacture |
KR930005345B1 (en) * | 1986-10-23 | 1993-06-17 | 후지덴기 가부시기가이샤 | Stator housing and rotor of mini-motor |
US5026341A (en) * | 1987-05-22 | 1991-06-25 | Robert Giebeler | Low speed disengageable damper |
FI89737C (en) * | 1991-12-05 | 1993-11-10 | Valmet Paper Machinery Inc | FAESTMETOD FOER ETT AEMNE SOM ANVAENDS VID BALANSERING AV EN VALS OCH CONSTRUCTION SOM ANVAENDS VID BALANSERING AV EN VALS |
FR2694509B1 (en) * | 1992-08-04 | 1994-10-07 | Jouan | Centrifuge comprising a rotor drive shaft with elastic damping seal and corresponding shaft. |
JP3782466B2 (en) * | 1992-10-07 | 2006-06-07 | ジヤトコ株式会社 | Rotating body balancing method |
JPH0777242A (en) * | 1993-07-14 | 1995-03-20 | Niyuusutain:Kk | Rotator and machine therewith |
JP3286406B2 (en) * | 1993-07-27 | 2002-05-27 | 株式会社ブリヂストン | How to correct weight imbalance of rim-mounted tires |
US5555144A (en) * | 1995-01-12 | 1996-09-10 | Seagate Technology, Inc. | Balancing system for a disc drive disc assembly |
DE19508792C2 (en) * | 1995-03-14 | 1997-07-17 | Heraeus Instr Gmbh | Device for automatically compensating an imbalance in a rotor rotatable about an axis of rotation |
-
1997
- 1997-04-21 JP JP53897197A patent/JP4045466B2/en not_active Expired - Fee Related
- 1997-04-21 EP EP97918750A patent/EP0848649B1/en not_active Expired - Lifetime
- 1997-04-21 WO PCT/US1997/006579 patent/WO1997040943A1/en active IP Right Grant
- 1997-04-21 AU AU26778/97A patent/AU714988B2/en not_active Ceased
- 1997-04-21 BR BR9702288A patent/BR9702288A/en not_active Application Discontinuation
- 1997-04-21 CN CN97190753A patent/CN1196691A/en active Pending
- 1997-04-21 AT AT97918750T patent/ATE212566T1/en not_active IP Right Cessation
- 1997-04-21 DE DE69710166T patent/DE69710166T2/en not_active Expired - Lifetime
- 1997-07-09 US US08/891,420 patent/US5921148A/en not_active Expired - Lifetime
- 1997-10-01 US US08/944,062 patent/US5827168A/en not_active Expired - Lifetime
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1419237A (en) * | 1964-12-29 | 1965-11-26 | Method for stabilizing the center of gravity of a suspended apparatus driven in rotation, as well as devices and apparatus, in particular centrifuges, for carrying out the present method or similar method | |
GB1111362A (en) * | 1966-01-24 | 1968-04-24 | Commissariat Energie Atomique | A damping centering bearing for a rotating shaft |
DE1632298A1 (en) * | 1967-12-13 | 1970-12-23 | Heinrich Hinz Fa | Device for damping the pendulum movements of centrifuge drums |
DE2112834A1 (en) * | 1970-03-17 | 1971-10-07 | Fives Lille Cail | Machine with pendulum suspended rotor with vertical axis |
EP0070157A2 (en) * | 1981-07-09 | 1983-01-19 | HAEMONETICS CORPORATION(a Massachusetts Corporation) | Improvements in centrifuges |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20210031215A1 (en) * | 2017-11-27 | 2021-02-04 | Gea Mechanical Equipment Gmbh | Separator |
US11596954B2 (en) * | 2017-11-27 | 2023-03-07 | Gea Mechanical Equipment Gmbh | Separator |
Also Published As
Publication number | Publication date |
---|---|
DE69710166T2 (en) | 2002-09-26 |
BR9702288A (en) | 1999-07-20 |
JP2000504993A (en) | 2000-04-25 |
DE69710166D1 (en) | 2002-03-14 |
EP0848649B1 (en) | 2002-01-30 |
JP4045466B2 (en) | 2008-02-13 |
AU714988B2 (en) | 2000-01-13 |
EP0848649A1 (en) | 1998-06-24 |
US5827168A (en) | 1998-10-27 |
CN1196691A (en) | 1998-10-21 |
AU2677897A (en) | 1997-11-19 |
ATE212566T1 (en) | 2002-02-15 |
US5921148A (en) | 1999-07-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US5827168A (en) | Apparatus for stabilizing a centrifuge rotor | |
CA1087874A (en) | Method and device for passing through critical speeds of elongate rotors | |
US7883456B2 (en) | Centrifugal machine having a vibration preventing mechanism | |
US5679992A (en) | Bearing unit | |
US4412831A (en) | Two plane self-balancing centrifuge | |
EP1214152B1 (en) | Centrifuge gyro diaphragm capable of maintaining motor shaft concentricity | |
US6960158B2 (en) | Centrifugal separator | |
US7806820B2 (en) | Automatic balancing device and system for centrifuge rotors | |
EP1545788B1 (en) | Decanting centrifuge with vibration isolation | |
CA1330214C (en) | Low speed disengageable vibration damper for centrifuge | |
EP0109410A1 (en) | Centrifuge stabilizing bearing | |
US6183408B1 (en) | Rotor shaft assembly having non-linear stiffness | |
KR100285523B1 (en) | Automatic balancing device of rotor | |
KR100565181B1 (en) | Balancing device of disc tachometer | |
KR102515354B1 (en) | Orthogonal robot | |
SU874336A1 (en) | Portable motor saw | |
RU2052300C1 (en) | Centrifuge drive | |
RU2114702C1 (en) | Gas centrifuge | |
JPH0582490B2 (en) | ||
JPS6341076Y2 (en) | ||
RU1771893C (en) | Mill | |
Bild et al. | A Simple High-Speed Air Spinner for Centrifugal Testing of Small Mechanical Devices | |
RU98101719A (en) | DEVICE AND METHOD FOR STABILIZING A CENTRIFUGE ROTOR | |
JPH0389018A (en) | Vibrationproofing type rotation axis support system | |
RU93012594A (en) | CONE INERTIAL CRUSHER |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 97190753.6 Country of ref document: CN |
|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AU BR CN JP RU |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LU MC NL PT SE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1997918750 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref document number: 1997 538971 Country of ref document: JP Kind code of ref document: A |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWP | Wipo information: published in national office |
Ref document number: 1997918750 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 1997918750 Country of ref document: EP |