US3770191A - Means for stabilizing high speed rotors - Google Patents

Means for stabilizing high speed rotors Download PDF

Info

Publication number
US3770191A
US3770191A US00157174A US3770191DA US3770191A US 3770191 A US3770191 A US 3770191A US 00157174 A US00157174 A US 00157174A US 3770191D A US3770191D A US 3770191DA US 3770191 A US3770191 A US 3770191A
Authority
US
United States
Prior art keywords
rotor
drive shaft
shaft
centrifuge
centrifuge according
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.)
Expired - Lifetime
Application number
US00157174A
Other languages
English (en)
Inventor
J Blum
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IVAN SORVALL INC US
SORVALL Inc IVAN
Original Assignee
SORVALL Inc IVAN
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by SORVALL Inc IVAN filed Critical SORVALL Inc IVAN
Application granted granted Critical
Publication of US3770191A publication Critical patent/US3770191A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • 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
    • B04B9/08—Arrangement or disposition of transmission gearing ; Couplings; Brakes
    • B04B2009/085—Locking means between drive shaft and rotor

Definitions

  • the problem is particularly acute during rotor deceleration after the materials have been centrifuged since any vibration occurring during deceleration may disturb or agitate the particles that have been centrifugally separated and, to varying degrees, put them back into at least partial suspension, thereby impairing the result of the experiment or test.
  • the invention herein constitutes an improvement over prior art centrifuges having vibration preventing or compensating means.
  • the present invention comprises a novel centrifuge drive system comprising a compound articulated mounting system for the rotor and for the rotor drive shaft.
  • the new system comprises a motor driven drive shaft and a rotor drive shaft pivotally articulated upon one end of said drive shaft, a universal joint upon which the rotor is mounted, and a slide block integrated with said universal joint and mounted on the motor driven drive shaft.
  • Said slide block is movable laterally to accommodate the movement of the geometric center of the spinning rotor to a position where its center of gravity becomes aligned with the axis of the centrifuge drive system and remains there during high speed centrifugation and deceleration through critical speeds until the rotor comes to a stop.
  • a novel feature of the invention is the provision of an articulated rotor shaft which notonly transmits rotational energy from the drive system of the centrifuge to the rotor, but also permits the lateral movement of the rotor whereby the geometric center thereof may be displaced so that its center of gravity becomes dynamically aligned with the axis of the drive system.
  • Another feature of the invention is the provision of a sliding block element integrated with a universal ball joint mounting of the rotor, said slide block being captive at the top of the centrifuge drive shaft. Said slide block is engaged by resilient damping friction means for controlling the lateral movement of said block relative to the centrifuge drive shaft when accommodating for the movement of the center of gravity of the rotor into alignment with the rotational axis of the centrifuge drive shaft. Said damping means assists in maintaining the stability of the drive system once it has achieved dynamic balance.
  • the centrifuge herein incorporates similar resilient bottom mountings for the centrifuge drive shaft and for the drive shaft housing, as disclosed in U. S. Pat. No. 2,827,229.
  • the resilient mounting at the bottom of the system is stronger than the initial friction of the sliding block provided by a ripple washer bearing thereon.
  • the centrifuge drive shaft and its bearing assembly as well as the rotor assembly including the sliding block have a tendency to establish an axial center by virtue of their own weights and of the resilient mounting at the bottom of the system.
  • the spinning rotor gradually finds its own center of gravity by virtue of the lateral movement of the sliding block relative to the established rotational axis of the drive system.
  • the spinning rotor After the spinning rotor has found its center of gravity which becomes axially aligned with the drive system, it remains in that position throughout the higher speeds of acceleration and throughout centrifuging speed and during the lowering speeds of deceleration until the rotor stops.
  • Centrifugal levers may also-be provided for extra security in automatically locking the slide block in a fixed position during high speed centrifuging rotation of the rotor, and for automatically releasing the slide block during deceleration of the rotor.
  • the slide block is free to move to permit corresponding dynamic free gradual movement of the geometric center of the rotor to shifting positions relative to the rotational axis of the centrifuge drive system whereby vibration of the rotor and of the rotor mount assembly and of the rotor shaft assembly are prevented.
  • a universal joint mounting is also provided for the rotor so that the latter maintains its horizontal center of gravity plane in position during the centrifuging procedure.
  • FIG. 1 is an elevation of the centrifuge of the present invention, partly broken away and partly in section, showing mainly the exterior of the rotor and the exterior of the rotor mounting hub and of the drive assembly, as well as a fragmentary portion of the support frame of the apparatus, some parts being omitted;
  • FIG. 2 is an enlarged vertical central section view of the apparatus shown in FIG. 1, omitting the rotor, some parts being shown in elevation and some parts being shown in dotted outline, said Figure illustrating the positions of the respective parts when the drive shaft and the rotor shaft are axially aligned.
  • FIG. 3 is a still further enlarged plan view of insert elements at the top and bottom of the pivoting rotor drive shaft shown in FIG. 2;
  • FIG. 4 is a view taken on line 44 of FIG. 2, some parts being omitted;
  • FIG. 5 is a greatly enlarged view, similar to FIG. 2, showing the location of the rotor hub and the pvioting action of the rotor drive shaft when the geometric center of the spinning rotor has moved to a position where the center of gravity of the rotor is axially aligned with the axis of the drive shaft;
  • FIG. 6 is an enlarged perspective view of one of two ripple spring washers located in the centrifuge assembly.
  • FIG. 7 is a greatly enlarged perspective view of the pivoting rotor drive shaft.
  • the apparatus herein comprises a motor or power shaft 11, the lower end of which is connected to an electric motor or the like, not shown, and which is used to power the apparatus.
  • power shaft 11 may be rotatcd by means other than an electric motor, namely, by a pulley drive, turbine drive, gear drive, or the like.
  • the apparatus herein is mounted on a frame 12, a fragmentary portion of which is shown in FIG. 1, and which may comprise a circular ring mounted upon a plurality of downwardly extending legs in circular array in a manner comparable to that shown in Blum, U. S. Pat. No. 2,827,229, said frame and legs also supporting the electric motor or the like.
  • a tubular bearing housing 16 is located centrally and extends upwardly of mounting ring 13. Formed integrally at a short distance from the lower end of bearing housing 16 is an annular flange 17. See FIG. 2. Spaced downwardly from flange 17 near the lower end of bearing housing 16, is a removable ring 18 which is secured in position by means of a lock washer l9 fitting into a suitable annular recess near the lower end of housing 16.
  • the outside diameters of flange 17 and of ring 18 are substantially the same.
  • annular resilient mounting cushion 21 Located between flange 17 and ring 13 is an annular resilient mounting cushion 21 made of rubber or the like.
  • Mounting cushion 21 has an annular recess intermediate its upper and lower surfaces which accommodates with a snug fit the inner annular portion of mounting ring 13 whereby the lower end of bearing housing 16 is resiliently coupled thereto.
  • the removability of lock washer 19 and of ring 18 permits the removal of annular cushion 21 from the lower end of housing 16 so that the apparatus can be disassembled and subsequently re-assembled with these replaceable parts.
  • a circular coupling housing 24 Connected by means of set screw 23 to the upper end of motor shaft 11 is a circular coupling housing 24, the upper portion of which is integrally formed in an upwardly extending tubular coupling collar 26.
  • the outside diameter of coupling housing 24 and of tubular coupling collar 26 is somewhat smaller than the inside diameter of stationary bearing housing 16 whereby the former rotate freely within the lower end portion of the latter.
  • a resilient coupling ring 27 Located within tubular coupling collar 26 is a resilient coupling ring 27 made of rubber or the like, said coupling ring being either uniform in annular crosssection or being lobed to form a plurality of radially spaced apart elements for enhanced resiliency.
  • a metallic adapter element 28 mounted fast within central aperture of ring 27 is a metallic adapter element 28 which, in turn, has a central square aperture which removably accommodates with a close sliding fit the square-shaped stub 31 of a bearing drive shaft 32 which extends axially upwardly through housing 16. The lower end of stub 31 is spaced apart from the upper end of motor shaft 11.
  • Resilient coupling ring 27 and adapter element 28 are enclosed and retained within housing collar 26 by means of cap 33 secured by means of an integrally formed downwardly extending collar on said housing with a press fit.
  • Cap 33 has a top, central aperture through which stub 31 freely extends.
  • the rotation of power shaft 1 1 causes the rotation of drive shaft 32 by way of coupling 24, couping ring 27, and adapter element 28.
  • the resilient mounting formed by cushion 21 is approximately in the same plane as the resilient coupling formed by ring 27 between motor shaft 11 and drive shaft 31.
  • bearing housing 16 Mounted within bearing housing 16 are upper and lower spaced apart bearings 34, the inner races of which surround drive shaft 32 and the outer races of which abut the inner wall of housing 16. Bearings 34 are maintained in their spaced apart relationship by means of spacer sleeve 36 surrounding shaft 32, while said bearings are maintained in position within housing 16 by means of tru-arc rings 37, or the like.
  • the upper end of drive shaft 32 terminates in an integrally formed circular crown 41 of enlarged diameter, said crown extending above and spaced apart from bearing housing 16.
  • integrally formed at the upper portion of crown 41 is an upwardly extending annular skirt 42 defining a slide block chamber 43. See FIG. 5.
  • a circular clamp ring 44 Threadably connected to crown 41 and enclosing skirt 42 is a circular clamp ring 44, the upper end of said ring having an integrally formed and inwardly extending annular flange 45.
  • annular recess 46 Located axially in the top of crown 41 is an annular recess 46 in which is secured fast an annular insert 47 made of bronze or steel and having a square-shaped central aperture 48. (See FIGS. 2, 3 and 5) Aperture 48 pivotally accommodates the lower square ball end 51 of rotor drive shaft 52, the upper end of which terminates in a square ball end 53 similar to ball end 51.
  • a support ring 54 made of hardened metal or the like, and upon which rests a ball thrust bearing 56.
  • an annular slide block 57 Movably resting upon thrust bearing 56 is an annular slide block 57, said block being movable in all directions in a horizontal plane on said bearing 56 relative to the axis of shaft 32 and crown 41.
  • an annular friction ring 58 Positioned on the top surface of slide block 57 is an annular friction ring 58, on top of which is located an annular ripple spring washer or pressure spring 59.
  • the dimension between the floor of chamber 43 and the bottom surface of flange 45 is such that said captive ripple spring washer 59 exerts just sufficient downward pressure upon sliding block 57 to prevent undue free movement of the latter without preventing suitable and necessary movement of said block in all lateral directions in its function of accommodating and responding to centrifugal forces, as will be explained hereinafter.
  • clamp ring 44 may optionally be provided with a plurality of radially spaced apart vertical slots 61 within each of which are freely pivotally movable centrifugal locking levers 62 mounted on pins 63 at the upper portion of said clamp ring. See also FIG. 4.
  • the upper portion of each centrifugal lock lever 62 has an inwardly and downwardly extending finger 64 which, when the apparatus is spinning at certain predetermined speeds, bears down upon friction ring 58 to cause the latter to lock sliding block 57 into an immovable position.
  • the weight ofall of the locking levers 62 is determined by empirical or computer means to respond at a particular rate of rotation of the spinning apparatus for causing fingers 64 simultaneously to lock sliding block 57 in a fixed position.
  • centrifugal locking levers 62 release sliding block 57 during deceleration of the centrifuge at a predetermined speed. Accordingly, centrifugal locking levers 62 cause sliding block 57 to be locked in position only above a certain predetermined centrifuging speed. Below such predetermined speed, the sliding block 57 is free to move horizontally in respect of the geometric axis of the centrifuge apparatus for reasons that will be explained hereinafter.
  • the centrifuge rotor 71 of the apparatus is mounted by means of a bolt 72 or the like to a rotor hub 73 shaped in this embodiment in the form of a truncated cone.
  • Hub 73 has an axial recess 74 in which is firmly secured an annular insert 76, similar to annular insert 47 (FIG. 3), the central square aperture 76A of which pivotally accommodates square ball end 53.
  • a somewhat larger adjacent axial recess 77 in hub 73 accommodates an annular bearing block 78, the interior of which has a pair of adjacent annular bearing surfaces '79 and 81 positioned at an angle relative to each other.
  • Bearing block 78 is retained in position within recess 77 by means of the upper circular edge of annular clamp ring 82 threadably inserted in the central aperture of hub 73 and secured in position by means of set screw 33 extending laterally through the wall of hub 73.
  • the bottom portion of clamp ring 82 has an integrally formed, inwardly extending annular flange 84 upon which rests a ripple spring washer or pressure spring 86 which, in turn, supports annular friction ring 87.
  • the central aperture of friction ring 87 is shaped in the form of a curved annular seat 88 which is slidably engaged by a universal hollow ball joint 89 which also slidably engages annular surfaces 79 and 81 of block 78.
  • rotor hub 73 is pivotably movable relative to universal ball joint 89 by virtue of the sliding engagement between block 78 and ball joint 89.
  • Spring ripple washer 86 has sufficient biasing action between flange 84 and ring 87 to cause friction ring 87 to exert the requisite amount of pressure against ball joint 89 to provide the requisite frictional engagement between said ball joint and block 78 in order to prevent undue excessive pivoting action between hub 73 and said ball joint while, at the same time, said spring is sufficiently yieldable to permit the necessary adjustment pivoting action that takes place to a limited degree while rotor 71 is spinning under various centrifuging conditions.
  • ball joint 89 At the bottom of ball joint 89 is an integrally formed, downwardly extending sleeve 91 whose external annular sloping surface mates with the internal annular sloping surface of an upwardly extending collar 92 formed integrally with slide block 57.
  • the lower end of sleeve 91 extends below slide block 57 and threadably accommodates a nut 93 which secures sleeve 91 firmly into collar 92.
  • the universal hollow ball 89 and block 57 form an integrated unit whereby any lateral movement of ball joint 89 in any horizontal direction is accompanied by a corresponding movement of collar 92 and slide block 57.
  • Ball joint 89 and sleeve 91 have a common axial aperture 94 within which rotor drive shaft 52 freely extends and within which said shaft is pivotally movable without touching any portion of ball joint 89 or sleeve 91. Since rotor shaft 52 is pivotally articulated on the upper end portion of drive shaft 32, and rotor 71 is pivotally articulated at universal ball joint 89, said rotor is given the freedom of movement of its geometric center away from the axis of the drive system comprising drive shaft 32 in order to permit the center of gravity of said rotor to become aligned with the drive system axis.
  • slide block 57 also becomes axially displaced from the axial center of the drive system in accordance with the extent to which the geometric centers of rotor 71 and of rotor hub 73 becomes displaced from said drive system axial center.
  • Slide block 57 is free to shift its position in order to accommodate to the departure of the geometric center of rotor 71 from the axial center of the drive system, but said sliding action is controlled to prevent erratic action thereof by a modicum of frictional pressure applied to block 57 by means of friction ring 58 being urged downwardly upon block 57 by means of yieldable spring washer 59.
  • spring washer 59 exerts a modicum of pressure, it is sufficiently yieldable to permit the gradual adjusting movement of slide block 57 to the adjusting deviation of the geometric center of rotor 71 from the axial center of the drive system after the rotor has accelerated through the critical speeds.
  • pivoting lock levers 62 may be dispensed with in some embodiments, they may nevertheless be found useful for locking slide block 57 in a particular location after rotor 71 has achieved a predetermined speed upon acceleration as, for example, to resist any shock tending to disrupt dynamic rotation. Accordingly, the size and weights of levers 62 may be determined as to be operative by centrifugal forces whereby their outward movement causes fingers 64 to bear downwardly upon friction ring 58 with sufficient force to lock slide block 57 securely between said friction fring and bearing 56.
  • centrifugal locking system comprising levers 62
  • the operation of the centrifugal locking system comprising levers 62 is limited to centrifuging speeds above the critical range of speeds in the course of which the center of gravity of rotor 71 becomes aligned with the axial center of the drive system comprising drive shaft 32.
  • clamp ring 44 will be of sufficient magnitude to permit the lateral movement of slide block 57 in any horizontal direction to the extent that may be expected or required in accommodating for deviation of the center of gravity of rotor 71 from the axial center of the centrifuge drive system.
  • the relative dimensions of the various component parts may be determined by suitable empirical means.
  • rotor 71 In the absence of the adjustment mechanism herein comprising slide block 57, rotor shaft 52, and universal ball joint 89, rotor 71 would vibrate during acceleration and deceleration during the aforementioned critical range of speeds, as is characteristic of centrifuge operation. Although vibration during the critical range of speeds during acceleration may be tolerated for the reason that the materials in the centrifuge have not as yet been subjected to centrifuging action, it is most important that vibration be eliminated during deceleration in order to prevent any agitation of the centrifuged materials in the rotor that would otherwise impair the integrity of said materials and possibly destroy the experiment or test intended to be made by the centrifugation process.
  • a centrifuge comprising a frame, a drive shaft on said frame, a rotor shaft, one end of said rotor shaft being pivotally connected to an end portion of said drive shaft and rotated thereby, a rotor operably and pivotally connected to the other end of said rotor shaft, an articulating connection between said rotor and said drive shaft, said articulating connection being movable perpendicularly relative to the axis of said drive shaft when said rotor shaft moves pivotally relative to said drive shaft, and a hub in said rotor being connected by a universal mounting on said articulating connection.
  • a centrifuge according to claim 1 wherein said articulating connection comprises a tubular member surrounding and spaced apart from said rotor shaft, the upper end portion of said member forming a ball joint with the interior of said hub, and an outwardly extending annular, slide slide block at the other end portion of said member, said block being slidably engaged at the upper end of said first shaft for movement in all lateral directions relative to the axis of said first shaft.
  • a centrifuge according to claim 2 wherein said first means comprises a ring resting upon said slide block and said second means comprises a plurality of spaced apart, freely pivotally mounted elements in circular array on the upper portion of said drive shaft, and integrally formed fingers on said elements which, when said drive shaft reaches a predetermined minimum speed of rotation, exert pressure upon said ring to cause the latter to lock said slide block into a fixed position relative to said drive shaft.
  • a centrifuge comprising a frame, a bearing housing mounted on and extending upwardly from said frame, a rotatable drive shaft within said housing, a rotor shaft, the lower end of said rotor shaft being pivotally connected to the upper end of and rotated by said drive shaft, a rotor operatively pivotally connected to the upper end of said rotor shaft and rotated thereby, a tubular sleeve located coaxially around and spaced apart from said rotor shaft, the upper portion of said sleeve forming a universal joint with the interior of said rotor, a radially extending annular slide block mounted on the lower portion of said sleeve, said slide block being slidably mounted and held captive at the top portion of said drive shaft and being movable laterally in all radial directions to permit the pivoting action of said rotor drive shaft.
  • a centrifuge comprising a frame, a rotating drive system on said frame, a rotor, a rotor shaft, one end of said rotor shaft being pivotally connected to and rotated by said drive system, the other end of said rotor shaft being operably pivotally connected to and rotating said rotor, an articulating connection between said drive system and said rotor separate from said rotor I shaft, said connection being operative to bring about movement of the rotor in a horizontal plane and the axial alignment of the center of gravity of the spinning rotor dynamically with the rotational axis of said drive system.
  • a centrifuge according to claim 16 in which said drive system comprises a drive shaft and a bearing housing surrounding said drive shaft, said centrifuge further comprising rotational power means on said frame for rotating said drive shaft, a resilient coupling between said drive shaft and said power means, and a second independent resilient mounting between said housing and said frame.
  • a centrifuge comprising a frame, a rotatable drive shaft on said frame, a rotor, a rotor shaft, one end portion of said rotor shaft being pivotally connected to said drive shaft and rotated thereby, the other end portion of said rotor shaft being operably pivotally connected to said rotor, and an articulating connection means between said rotor and said drive shaft, said articulating connection means being movable in a horizontal plane relative to the vertical axis of said drive shaft when said rotor shaft moves pivotally and the center of gravity of the spinning rotor moves in a horizontal plane to become aligned with the axis of rotation of said drive shaft.
  • said articulating connection means comprising an articulating connection (5731) between said rotor and said drive shaft, a first universal yieldable friction mounting (86,87) between said articulating connection and said rotor, and a second yieldable friction mounting (59) between said articulating connection and said drive shaft, said second yieldable friction mounting being movable horizontally in all directions relative to said drive shaft.
  • a centrifuge according to claim 22 wherein the pivotal connection between the rotor shaft and the rotor comprises a square shaped recess in said rotor and a square ball end on said rotor shaft accommodated by said recess and movable pivotably in all directions relative thereto, said square ball end moving in an arcuate path during the movement of said rotor in a horizontal plane.
  • a centrifuge according to claim 22 wherein said articulating connection comprises an annular slide block surrounding and spaced apart from said rotor shaft and mounted for horizontal movement on said drive shaft, a ball joint in said rotor surrounding and spaced apart from said rotor shaft, a tubular connection between said ball joint and said slide block, said rotor and said slide block being movable in a horizontal plane only relative to said drive shaft while said rotor shaft moves pivotally between said drive shaft and said rotor.
  • a centrifuge comprising a frame, a vertical rotatable drive shaft on said frame, a rotor shaft, a pivot connection between said rotor shaft and said drive shaft, a pivot connection between said rotor shaft and said rotor, means connected between said rotor and said drive shaft and movable in a horizontal plane relative to said drive shaft and means on the pivot connection between the rotor shaft and the rotor within which the end of said rotor shaft moves in an arcuate path when the rotor moves in a horizontal plane.
  • a centrifuge comprising a frame, a rotatable drive shaft on said frame, a rotor mounted on said drive shaft and movable in all directions restricted in a perpendicular plane relative to the axis of said drive shaft, and a rotor shaft, one end of said rotor shaft being pivotally connected to said drive shaft, the other end of said rotor shaft pivotally engaging the interior of said rotor, said other end of said rotor shaft moving in an arcuate path when said rotor moves in said perpendicular plane.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Centrifugal Separators (AREA)
  • Vibration Prevention Devices (AREA)
US00157174A 1971-06-28 1971-06-28 Means for stabilizing high speed rotors Expired - Lifetime US3770191A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US15717471A 1971-06-28 1971-06-28

Publications (1)

Publication Number Publication Date
US3770191A true US3770191A (en) 1973-11-06

Family

ID=22562631

Family Applications (1)

Application Number Title Priority Date Filing Date
US00157174A Expired - Lifetime US3770191A (en) 1971-06-28 1971-06-28 Means for stabilizing high speed rotors

Country Status (6)

Country Link
US (1) US3770191A (enrdf_load_stackoverflow)
JP (1) JPS513585B1 (enrdf_load_stackoverflow)
CA (1) CA947735A (enrdf_load_stackoverflow)
DE (1) DE2217611C3 (enrdf_load_stackoverflow)
FR (1) FR2143679B1 (enrdf_load_stackoverflow)
GB (1) GB1387045A (enrdf_load_stackoverflow)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1980001470A1 (en) * 1979-01-22 1980-07-24 Haemonetics Corp Apparatus for separating blood into components thereof
US4890947A (en) * 1988-10-26 1990-01-02 E. I. Du Pont De Nemours And Company Mounting adapter having locking taper removal arrangement
US5026341A (en) * 1987-05-22 1991-06-25 Robert Giebeler Low speed disengageable damper
US5342282A (en) * 1992-08-04 1994-08-30 Jouan Centrifuge including a rotor driveshaft with an elastic damping seal and corresponding shaft
US5683341A (en) * 1996-03-14 1997-11-04 Piramoon Technologies, Inc. Quill shaft suspension for centrifuge rotor having central stator
US5827168A (en) * 1996-04-30 1998-10-27 Dade Behring Inc. Apparatus for stabilizing a centrifuge rotor
US6149571A (en) * 1997-07-25 2000-11-21 Tomy Seiko Co., Ltd. Centrifuge having a rotor with convex surface matching concave surface of nut for securing rotor on drive shaft
WO2000078465A1 (en) 1999-06-17 2000-12-28 Kendro Laboratory Products, L.P. Centrifuge gyro diaphragm capable of maintaining motor shaft concentricity
US6183408B1 (en) * 1999-05-03 2001-02-06 Beckman Coulter, Inc. Rotor shaft assembly having non-linear stiffness
US20030075929A1 (en) * 2001-08-22 2003-04-24 Roland Weitkamp Wind power plant
US20040138041A1 (en) * 2001-04-20 2004-07-15 Tatsuya Konno Centrifuge
US6776752B2 (en) * 2002-04-12 2004-08-17 Wagner Development, Inc. Automatic tube bowl centrifuge for centrifugal separation of liquids and solids with solids discharge using a scraper or piston
US20050233883A1 (en) * 2004-04-14 2005-10-20 Wagner Development, Inc. Conical piston solids discharge and pumping centrifugal separator
US20050233882A1 (en) * 2004-04-14 2005-10-20 Wagner Development, Inc. Conical piston solids discharge centrifugal separator
US20070049479A1 (en) * 2005-09-01 2007-03-01 Carr Robert B Gas driven solids discharge and pumping piston for a centrifugal separator
US20070114161A1 (en) * 2005-09-01 2007-05-24 Carr Robert B Solids recovery using cross-flow microfilter and automatic piston discharge centrifuge
US20100167899A1 (en) * 2008-12-29 2010-07-01 Carr Robert B Solids discharge centrifugal separator with disposable contact elements
US20140242678A1 (en) * 2011-07-27 2014-08-28 Andreas Boos Apparatus and method for a lysis of a sample, in particular for an automated and/or controlled lysis of a sample
US20190084178A1 (en) * 2017-09-15 2019-03-21 Pilot Pastoral Co. Pty. Ltd. Portable Sawmill
US10677312B2 (en) * 2018-02-15 2020-06-09 General Electric Company Friction shaft damper for axial vibration mode
WO2024025771A1 (en) * 2022-07-28 2024-02-01 Fiberlite Centrifuge Llc Interlocking cones system for attaching a rotor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5375081A (en) * 1976-12-06 1978-07-04 Kiyouhei Majima Apparatus for automatic feed supply
JPS5454685U (enrdf_load_stackoverflow) * 1977-09-22 1979-04-16
JPS5551174U (enrdf_load_stackoverflow) * 1978-10-03 1980-04-04
SE1150826A1 (sv) * 2011-09-13 2012-12-11 3Nine Ab Centrifugalsepareringsanordning

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1970377A (en) * 1933-01-28 1934-08-14 Gen Electric Centrifugal machine
US2580435A (en) * 1947-01-29 1952-01-01 Apex Electrical Mfg Co Washing machine
US2797569A (en) * 1951-06-09 1957-07-02 Apex Electrical Mfg Co Clothes washing machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1970377A (en) * 1933-01-28 1934-08-14 Gen Electric Centrifugal machine
US2580435A (en) * 1947-01-29 1952-01-01 Apex Electrical Mfg Co Washing machine
US2797569A (en) * 1951-06-09 1957-07-02 Apex Electrical Mfg Co Clothes washing machine

Cited By (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55501133A (enrdf_load_stackoverflow) * 1979-01-22 1980-12-18
US4303193A (en) * 1979-01-22 1981-12-01 Haemonetics Corporation Apparatus for separating blood into components thereof
WO1980001470A1 (en) * 1979-01-22 1980-07-24 Haemonetics Corp Apparatus for separating blood into components thereof
US5026341A (en) * 1987-05-22 1991-06-25 Robert Giebeler Low speed disengageable damper
US4890947A (en) * 1988-10-26 1990-01-02 E. I. Du Pont De Nemours And Company Mounting adapter having locking taper removal arrangement
US5342282A (en) * 1992-08-04 1994-08-30 Jouan Centrifuge including a rotor driveshaft with an elastic damping seal and corresponding shaft
US5683341A (en) * 1996-03-14 1997-11-04 Piramoon Technologies, Inc. Quill shaft suspension for centrifuge rotor having central stator
US5827168A (en) * 1996-04-30 1998-10-27 Dade Behring Inc. Apparatus for stabilizing a centrifuge rotor
US5921148A (en) * 1996-04-30 1999-07-13 Dade Behring Inc. Method for stabilizing a centrifuge rotor
US6149571A (en) * 1997-07-25 2000-11-21 Tomy Seiko Co., Ltd. Centrifuge having a rotor with convex surface matching concave surface of nut for securing rotor on drive shaft
US6183408B1 (en) * 1999-05-03 2001-02-06 Beckman Coulter, Inc. Rotor shaft assembly having non-linear stiffness
EP2292335A1 (en) 1999-06-17 2011-03-09 Thermo Fisher Scientific (Asheville) LLC Centrifuge with shaft-coupling capable of maintaining motor shaft concentricity
US6638203B2 (en) 1999-06-17 2003-10-28 Kendro Laboratory Products, Lp Centrifuge rotor shaft vertical displacement restriction device with angular deflection capability
WO2000078465A1 (en) 1999-06-17 2000-12-28 Kendro Laboratory Products, L.P. Centrifuge gyro diaphragm capable of maintaining motor shaft concentricity
EP1214152A4 (en) * 1999-06-17 2006-04-12 Kendro Lab Prod Lp GYROSCOPIC CENTRIFUGE DIAPHRAGM FOR MAINTAINING THE CONCENTRICITY OF A MOTOR SHAFT
US7108651B2 (en) * 2001-04-20 2006-09-19 Hitachi Koko Co., Ltd. Centrifuge having multiple rotors
US20040138041A1 (en) * 2001-04-20 2004-07-15 Tatsuya Konno Centrifuge
US6870281B2 (en) * 2001-08-22 2005-03-22 General Electric Company Wind power plant stabilization
US20030075929A1 (en) * 2001-08-22 2003-04-24 Roland Weitkamp Wind power plant
US6776752B2 (en) * 2002-04-12 2004-08-17 Wagner Development, Inc. Automatic tube bowl centrifuge for centrifugal separation of liquids and solids with solids discharge using a scraper or piston
US20050009681A1 (en) * 2002-04-12 2005-01-13 Wagner Development, Inc. Centrifuge for separation of liquids and solids with solids discharge using a piston or scraper
US6986734B2 (en) 2002-04-12 2006-01-17 Wagner Development, Inc. Centrifugal separator with scraper or piston for discharging solids
US7261683B2 (en) 2004-04-14 2007-08-28 Wagner Development, Inc. Conical piston solids discharge and pumping centrifugal separator
US20050233882A1 (en) * 2004-04-14 2005-10-20 Wagner Development, Inc. Conical piston solids discharge centrifugal separator
US7052451B2 (en) 2004-04-14 2006-05-30 Wagner Development, Inc. Conical piston solids discharge centrifugal separator
US20050233883A1 (en) * 2004-04-14 2005-10-20 Wagner Development, Inc. Conical piston solids discharge and pumping centrifugal separator
US7935042B2 (en) 2005-09-01 2011-05-03 Wagner Development, Inc. Gas driven solids discharge and pumping piston for a centrifugal separator
US7618361B2 (en) 2005-09-01 2009-11-17 Wagner Development, Inc. Gas driven solids discharge and pumping piston for a centrifugal separator
US7628749B2 (en) 2005-09-01 2009-12-08 Wagner Development Inc. Solids recovery using cross-flow microfilter and automatic piston discharge centrifuge
US20070114161A1 (en) * 2005-09-01 2007-05-24 Carr Robert B Solids recovery using cross-flow microfilter and automatic piston discharge centrifuge
US20070049479A1 (en) * 2005-09-01 2007-03-01 Carr Robert B Gas driven solids discharge and pumping piston for a centrifugal separator
US20100167899A1 (en) * 2008-12-29 2010-07-01 Carr Robert B Solids discharge centrifugal separator with disposable contact elements
US8475352B2 (en) 2008-12-29 2013-07-02 Wagner Development, Inc. Solids discharge centrifugal separator with disposable contact elements
US20140242678A1 (en) * 2011-07-27 2014-08-28 Andreas Boos Apparatus and method for a lysis of a sample, in particular for an automated and/or controlled lysis of a sample
US9963670B2 (en) * 2011-07-27 2018-05-08 Curetis Gmbh Apparatus and method for a lysis of a sample, in particular for an automated and/or controlled lysis of a sample
US11447737B2 (en) 2011-07-27 2022-09-20 Curetis Gmbh Apparatus and method for a lysis of a sample, in particular for an automated and/or controlled lysis of a sample
US20190084178A1 (en) * 2017-09-15 2019-03-21 Pilot Pastoral Co. Pty. Ltd. Portable Sawmill
US10751904B2 (en) * 2017-09-15 2020-08-25 Pilot Pastoral Co. Pty. Ltd. Portable sawmill
US10677312B2 (en) * 2018-02-15 2020-06-09 General Electric Company Friction shaft damper for axial vibration mode
WO2024025771A1 (en) * 2022-07-28 2024-02-01 Fiberlite Centrifuge Llc Interlocking cones system for attaching a rotor

Also Published As

Publication number Publication date
GB1387045A (en) 1975-03-12
FR2143679A1 (enrdf_load_stackoverflow) 1973-02-09
FR2143679B1 (enrdf_load_stackoverflow) 1974-07-26
DE2217611C3 (de) 1975-09-25
CA947735A (en) 1974-05-21
DE2217611A1 (de) 1973-01-25
JPS513585B1 (enrdf_load_stackoverflow) 1976-02-04
DE2217611B2 (de) 1975-02-20

Similar Documents

Publication Publication Date Title
US3770191A (en) Means for stabilizing high speed rotors
US6132354A (en) Automatic ball balancer for rotating machine
JP4361785B2 (ja) 回転部材用平衡アセンブリ
KR0168893B1 (ko) 불평형 보정 방법 및 장치
US5256037A (en) Self balancing motor
US6974362B2 (en) System and method for automatically compensating for unbalanced resistance forces
US5356367A (en) Centrifugal separator with flexibly suspended restrainable bowl
EP0848649B1 (en) Apparatus and method for stabilizing a centrifuge rotor
US7435211B2 (en) Ball balancer for vertical rotor and centrifuge
US2799445A (en) High speed rotor
JP4040875B2 (ja) モータ軸の同心性を維持することができる遠心機ジャイロダイヤフラム
JPS5817858A (ja) 流体を処理する遠心分離機
JPS6250189B2 (enrdf_load_stackoverflow)
US4897075A (en) Centrifuge drive hub
EP4547405A1 (en) Radial locking system for attaching a rotor
JPH0249789B2 (enrdf_load_stackoverflow)
US2238989A (en) Self-balancing dynamic system
US6183408B1 (en) Rotor shaft assembly having non-linear stiffness
US4224165A (en) Cyclical centrifugal machine
KR20220146653A (ko) 원심 분리기
US1743753A (en) Centrifugal machine
CN213726149U (zh) 一种涡旋混合器
KR100579078B1 (ko) 상부 지지형 로터리 테이블 장치
WO2024025771A1 (en) Interlocking cones system for attaching a rotor
EP4558278A1 (en) Rotational locking system for attaching a rotor