US3692236A - Self-balancing centrifuge method and apparatus - Google Patents

Self-balancing centrifuge method and apparatus Download PDF

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Publication number
US3692236A
US3692236A US85348A US3692236DA US3692236A US 3692236 A US3692236 A US 3692236A US 85348 A US85348 A US 85348A US 3692236D A US3692236D A US 3692236DA US 3692236 A US3692236 A US 3692236A
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United States
Prior art keywords
centrifuge
wheel
shaft
annular chamber
cups
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Expired - Lifetime
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US85348A
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English (en)
Inventor
Stanley L Livshitz
Robert Alan Mayo
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Bayer Corp
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Technicon Instruments Corp
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    • 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
    • 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.

Definitions

  • ABSTRACT A centrifuge of the type used for a number of individual test samples in separate sample containers is dynamically balanced automatically by means of a counterbalancing mass contained in an annular chamber within the centrifuge wheel.
  • the centrifuge wheel is mounted as an inverted pendulum about a fixed pivot and spring biased to the vertical position.
  • the counterbalancing mass which is at the same vertical level as the sample containers, automatically moves angularly to the counter-balancing position at speeds above the speed corresponding to the natural vibration frequency of the pendulum system.
  • This invention relates to improved centrifuges of the type which are particularly useful for separating small sample quantities of chemical or biological fluids such as blood samples, the samples being contained in a plurality of small tubes which are carried at the periphery of a centrifuge wheel.
  • the present invention may be carried out for balancing a centrifuge of the type having a plurality of separate cups arranged around the periphery of the centrifuge wheel for the purpose of holding containers of liquids to be centrifuged by providing an annular chamber within the wheel, pivotally mounting the centrifuge at its axis as a pendulum, spring biasing the centrifuge to a substantially vertical axis position, placing at least two balancing weight bodies loosely within the annular chamber for free movement therein, and then operating the centrifuge at a speed substantially in excess of that corresponding to the natural frequency of the spring biased pendulum system to cause the balancing weight bodies to move within the annular chamber to positions compensating for any unbalanced condition in the loading of the centrifuge cups.
  • FIG. 1 is a side view, partially in section, illustrating a preferred embodiment of the invention.
  • FIG. 2 is a partial schematic sectional top view, taken at section 2-2 of FIG. 1, and serving to illustrate features of the dynamic operation of the embodiment of FIG. 1.
  • a centrifuge wheel 10 including a removable upper wheel portion 12, sometimes referred to hereinafter as a tray arranged for holding a number of sample tubes 14 of liquid to be separated by centrifugal action.
  • the wheel 10 also includes a lower, non-removable, portion 16 which is attached for rotation upon a shaft 18.
  • Shaft 18 is an extension of the shaft of a drive motor 20 by means of which the wheel 10 is rotated.
  • the mounting plate 22 is spring biased to a substantially horizontal position by means of a series of springs 28 spaced around the peripheral edges of the plate. By means of this spring biasing, the shaft 18 of the centrifuge is spring biased to a substantially vertical position.
  • the pivot 24 is concentric with the center line of theshaft 18.
  • the pivotal mounting of the centrifuge, with its spring bias to the vertical position may be appropriately described as an inverted pendulum mounting and the pendulum possesses a natural oscillation or a vibration frequency about the pivot 24 which is determined by the physical dimensions and characteristics of the system, and particularly by the mass of the wheel 10 and the spring rate of the springs 28.
  • the lower portion 16 of the wheel 10 defines an annular chamber 30 containing a counterweight mass 32 which automatically shifts within the cavity to counterbalance for any unbalance in the loading of the sample tubes 14. This automatic counterbalancing operation will be described in more detail below.
  • the tray portion 12 of the wheel 10 includes holders 34 and 34A for the sample tubes 14, and the holders 34 and 34A are pivotally mounted, as at 36, to the peripheral edges of the tray wheel portion 12, so that they may freely swing radially outwardly when the centrifuge wheel is spinning.
  • the individual sample containers 14 may be filled to various levels, and individual tube holders 34 may remain empty. These two factors may cause the centrifuge to be rather seriously unbalanced. This causes the centrifuge to wobble as it rotates so that the shaft 18 defines a rotating cone of revolution. Thecenter of the pivotal motion is the ball pivot structure 24. The wobbling motion is resisted by the springs 28. The wobbling motion may be referred to hereinafter as rotational vibration, or simply as vibration.
  • the unbalanced condition is illustrated in FIG. 1 by the presence of a sample tube 14 within the holder 34, and the absence of a sample tube within the holder 34A.
  • the counterbalancing mass 32 tends to move within the cavity 30 to the unbalanced side of the centrifugal wheel so that it does not accomplish a compensating function.
  • the speed of rotation of the centrifuge wheel exceeds the natural frequency of the pendulum system, there is a phase reversal of the forces upon the compensating mass 32 and it is caused to shift within the cavity 30 towards the lightly loaded side of the centrifuge wheel to compensate for the unbalanced forces.
  • the compensating mass 32 may consist of a liquid, in the preferred form of the invention it consists of at least two solid bodies which are capable of sliding or rolling within the cavity 30 to accomplish the compensation effect.
  • the centrifuge of the present invention may also include a hydraulic energy absorption device 38 having a piston plunger 40.
  • Device 38 provides energy absorption to prevent a drastic build-up of vibration as the natural resonant frequency of the system of the inverted pendulum is approached.
  • the energy absorber 38 may be of the hydraulic fluid type in which fluid is forced through an orifice.
  • the device 38 may be rigidly mounted by means of a threaded boss into a suitable threaded hole within the plate 22.
  • the plunger 40 may simply be provided with a spherical bottom surface which rests against the base 26 and is normally biased onto contact therewith by an internal spring.
  • a number of the energy absorber devices 38 may be provided and may be interspersed between adjacent springs 28 around the periphery of the plate 7.
  • the energy absorber 38 may be a small hydraulic shock absorber of the type which is commercially available, for instance, under model number designations having the prefix SI-I" from the Special Products Division of Integrated Dynamics Inc. of 2206 Elmwood Avenue, Buffalo, New York 14216.
  • Other similar hydraulic damper structures may be employed such as rotary dampers which may be coupled between plate 22 and base members 26 by means of rotary operating arms and connecting rods. It is also possible to provide for some energy absorption by substituting rubber springs for the springs 28 since the rubber absorbs additional energy as it is deformed.
  • FIG. 2 is a partial schematic sctional top view taken at section 2-2 in FIG. 1.
  • the mass 32 preferably consists of at least two solid bodies 32A and 32B,which are preferably cylinders or spheres having a circular profile when viewed from above. These bodies are rotatably slidable to compensating positions such as illustrated at 32A and 328.
  • the cylindrical form of the bodies 32A and 32B is preferred because the slight frictional restraint caused by the requirement that the cylinders must slide on the bottom Y surface of the chamber 30 provides somewhat greater stability at low speeds and provides quieter operation.
  • the centrifugal forces upon the bodies 32A and 32B are so much greater than the downward gravity force that the sliding friction is not a serious restraining force. It has been determined that the frictional restraint of the cylinders on the bottom surface of the chamber 30 is often sufficient to keep the cylinders in the dynamic balance position when the centrifuge is turned off and slowed down at the end of an operating cycle. Thus the centrifuge remains balanced as it slows through the speed corresponding to the natural vibration frequency of the system.
  • the frictional resistance of the cylinders on the bottom surface of the chamber is also advantageous in restraining movement of the cylinders to the unbalanced side of the centrifuge during the acceleration phase of the operating cycle.
  • non-skid surfaces on the bottom surface of the changer, or the bottom surface of the cylinders, or both.
  • This non-skid feature may be implemented in many ways, including, for instance, roughened surfaces which provide an interlock effect.
  • the counterbalancing mass 32 is referred to generically in FIG. 1, it is represented as a cylinder, such as the cylindrical body 32A, since that is the preferred form for the mass.
  • the bodies 32A and 32B move from the position shown in FIG. 2 to the position indicated at 32A and 328', they move in a coordinated manner on both sides of the chamber 30 until a balanced position is achieved.
  • the bodies When compensating for a maximum unbalanced condition, the bodies would proceed to the extreme position opposite to the original position until they touched in the bottom most position in FIG. 2. In the event the centrifuge wheel is actually balanced (independent of bodies 32A and 323), then the bodies 32A and 328 end up in positions diametrically opposite to one another. For any intermediate unbalanced condition, the bodies are positioned at some intermediate position such as shown in the drawing at 32A and 32B.
  • the upper tray portion 12 of the wheel is easily removable from the remainder of the centrifuge by simply lifting it vertically upward by means of the central handle which is provided on the tray 12.
  • This provides quick removal of the tray and all of the loaded cups 34 and quick transfer of the entire tray and all the samples for a combination with automatic sample analysis apparatus.
  • the balancing mass 32 is supported within the chamber 30 in a vertical position which is in substantial horizontal alignment with the unbalanced loadsof the cups 34. While this perfect horizontal alignment is not entirely apparent from the static picture given by FIG. 1, when the centrifuge is in operation, the cups 34, whether they are filled or empty, swing radially outwardly about the pivots 36 so that the center of gravity of each cup 34 is effectively raised to be substantially horizontally in line with the mass 32. This feature is important because it provides a more perfect balancing condition when the ultimate balancing is achieved, a condition in which force couples are absent.
  • the entire vertical support of the apparatus is provided through the springs 28 and the energy absorption devices 38.
  • a pivoting or rocking action of the plate 22 is achieved about a pivot point in response to unbalanced conditions.
  • the fixed pivot construction employing the spherical ball point pivot 24 is preferred as it provides vertical stability for the apparatus. It will be understood that other universal pivot structures may be employed as alternatives to the spherical bearing shown.
  • the speed corresponding to the resonant vibration frequency is less than ten percent of the full operating speed of the device.
  • the speed corresponding to the resonant vibration frequency is about revolutions per minute, and the full operating speed is at least 1,500 revolutions per minute, and more typically about 2,250 revolutions per minute, or higher.
  • a method of balancing a centrifuge of the type having a plurality of separate cups arranged around the periphery of a centrifuge wheel for the purpose of holding containers of liquids to be centrifuged comprising providing an annular chamber within the wheel,
  • a cenmfuge as .clalmed m claim 4 when! cups, the balancing weight bodies being positioned sald naimral vlbratlon. frequency corresponds to 8 within the annular chamber at substantially the centrifuge speed which less than ten pelicem of same level as the centrifuge cups during the rotathe fun operaimg sPeed the i tion ofthe centrifuge lo 11.
  • said supporting means comprises a fixed supporting base mounting and supporting said ball swivel bearing
  • the force i the spimgs biasmg i c.enmfuge to a said mounting plate being fixed with respect to the substantially vertical axis position is selected to 15 provide a natural vibration fre uenc of the cenaxialposm-on sa-ld shaft 3 y d h and said spring biasing means comprising compresi correspon mg to a can 1 uge spec w sion springs arranged between said supporting is less than ten percent of the normal full operating base member and said plate and spring biasing said speed ofthe cfmmfugei plate to a position substantially parallel to said 4.
  • a self-balancing centrifuge comprising a rotatable base member shaft 12.
  • Sald Suppomng meanP f Spnng basmg said rotatable shaft being connected to and forming mealls arranged to fi 531d f' an extension of the shaft of said drive motor and stantially vertical position aboutsald pivot point, being supported upon and directly driven thereby a motor connected to mate Said Shaft 13.
  • said wheel about said pivot point, said annular 15.
  • chamber being formed to allow the shift of said said energy absorption means comprises a plurality counterbalance mass to a position which is at subof hydraulic shock absorber devices.
  • a centrifuge as l i d i l i 4 h i operable when the vibration excursion exceeds a said counterbalance mass comprises a plurality of p g t h g if g lf fia spring Solid i rate an o t ere y imit u er v1 ration am- 6.

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US85348A 1970-10-30 1970-10-30 Self-balancing centrifuge method and apparatus Expired - Lifetime US3692236A (en)

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US8534870A 1970-10-30 1970-10-30

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US (1) US3692236A (OSRAM)
BE (1) BE773364A (OSRAM)
CA (1) CA936506A (OSRAM)
CH (1) CH542658A (OSRAM)
DE (1) DE2152840A1 (OSRAM)
FR (1) FR2110116A5 (OSRAM)
GB (1) GB1346115A (OSRAM)
IT (1) IT938889B (OSRAM)
NL (1) NL7114176A (OSRAM)
SU (1) SU463254A3 (OSRAM)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4804355A (en) * 1987-11-17 1989-02-14 Utah Bioresearch, Inc. Apparatus and method for ultrasound enhancement of sedimentation during centrifugation
US4865810A (en) * 1986-09-25 1989-09-12 Kis Photo Industrie Centrifuge for performing medical analyses
US5207634A (en) * 1991-01-23 1993-05-04 Biotope, Inc. Self-balancing apparatus and method for a centrifuge device
US5823068A (en) * 1996-08-27 1998-10-20 Comair Rotron, Inc. Rotating system with reduced transference of vibration and acoustics and method for reducing same
WO2000029122A1 (en) * 1998-11-12 2000-05-25 Genevac Limited Automatic balancing in centrifuges
WO2000014493A3 (en) * 1998-09-05 2000-06-08 Michael Cole Control of weight during evaporation of samples
US6132354A (en) * 1996-11-08 2000-10-17 Hitachi Koki Co., Ltd. Automatic ball balancer for rotating machine
WO2001066212A1 (en) * 2000-03-03 2001-09-13 Genevac Ltd. Balancing device in combination with centrifugal evaporator
US6651527B2 (en) * 2000-07-19 2003-11-25 INA-Wälzlager Schaeffler oHG Self-balancing device
US20040018927A1 (en) * 2001-04-02 2004-01-29 Dou-Ha Baik Automatic balance adjusting centrifugal apparatus
US20040142808A1 (en) * 2001-05-26 2004-07-22 Wilfried Mackel Centrifugal separator
US20050026765A1 (en) * 2003-07-29 2005-02-03 Diagyr Process to balance a rotatable plate of a centrifuge and centrifuge using the process
US20070225143A1 (en) * 2006-03-23 2007-09-27 Korea Institute Of Machinery & Materials Balancer for vertical rotor and centrifuge using the same
US20100009835A1 (en) * 2008-07-09 2010-01-14 Hanlab Corporation Automatic balancing centrifuge using balancer
US20100009833A1 (en) * 2008-07-10 2010-01-14 Hanlab Corporation Automatic balance adjusting centrifuge and the control method thereof
US20100069216A1 (en) * 2008-09-16 2010-03-18 Hanlab Corporation Control method of automatic balancing centrifuge using balancer
US20100160138A1 (en) * 2008-12-18 2010-06-24 Thermo Electron Led Gmbh Mounting Means For Mounting A Device With A Rotor
US8375826B1 (en) * 2011-12-15 2013-02-19 Cnh America Llc Self balancing chopping or threshing rotor
US20130263659A1 (en) * 2012-04-04 2013-10-10 Elliott Company Passive dynamic inertial rotor balance system for turbomachinery
US10337943B2 (en) * 2014-11-12 2019-07-02 Andreas Hettich Gmbh & Co. Kg Centrifuge and method for sensing imbalances in the centrifuge
US10335804B2 (en) * 2014-02-25 2019-07-02 Andreas Hettich Gmbh & Co. Kg Centrifuge with damping elements
CN113304896A (zh) * 2021-04-16 2021-08-27 中国联合工程有限公司 土工离心机转子系统在线动态不平衡调节装置及调节方法
US11292014B2 (en) 2015-04-05 2022-04-05 Arteriocyte Medical Systems, Inc. Centrifuge counterbalance with adjustable center of gravity and methods for using the same
CN116673135A (zh) * 2023-05-30 2023-09-01 武汉兰丁云医学检验实验室有限公司 可切换配重的内部补偿式细胞组织离心装置
CN118236732A (zh) * 2024-05-28 2024-06-25 广州市朗坤环境科技有限公司 一种酶法生物柴油中甘油分离装置及其分离方法
CN118705324A (zh) * 2024-08-29 2024-09-27 中科南京生命健康高等研究院 一种用于生物试验的多功能酶标仪

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2605108B1 (fr) * 1986-09-25 1988-11-25 Kis Photo Ind Dispositif automatique pour la realisation d'analyses notamment biologiques et medicales
DE50001202D1 (de) * 1999-08-03 2003-03-13 Eppendorf Ag Unwuchtsaugleichsvorrichtung für zentrifugen
RU2199394C2 (ru) * 2000-11-14 2003-02-27 Научно-производственное республиканское унитарное предприятие "НПО "Центр", г.Минск Центробежная установка
RU2408432C1 (ru) * 2009-07-31 2011-01-10 Общество с ограниченной ответственностью "Новые технологии-инжиниринг" Роторный механизм для центробежной установки
CN112834413B (zh) * 2021-03-04 2025-05-30 常州必达科生物科技有限公司 全自动流式细胞仪

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4865810A (en) * 1986-09-25 1989-09-12 Kis Photo Industrie Centrifuge for performing medical analyses
US4804355A (en) * 1987-11-17 1989-02-14 Utah Bioresearch, Inc. Apparatus and method for ultrasound enhancement of sedimentation during centrifugation
US5207634A (en) * 1991-01-23 1993-05-04 Biotope, Inc. Self-balancing apparatus and method for a centrifuge device
US5376063A (en) * 1991-01-23 1994-12-27 Boehringer Mannheim Corporation Self-balancing apparatus and method for a centrifuge device
US5823068A (en) * 1996-08-27 1998-10-20 Comair Rotron, Inc. Rotating system with reduced transference of vibration and acoustics and method for reducing same
US5983750A (en) * 1996-08-27 1999-11-16 Comair Rotron, Inc. Rotating system with reduced transference of vibration and acoustics and method for reducing same
US6132354A (en) * 1996-11-08 2000-10-17 Hitachi Koki Co., Ltd. Automatic ball balancer for rotating machine
WO2000014493A3 (en) * 1998-09-05 2000-06-08 Michael Cole Control of weight during evaporation of samples
WO2000029122A1 (en) * 1998-11-12 2000-05-25 Genevac Limited Automatic balancing in centrifuges
WO2001066212A1 (en) * 2000-03-03 2001-09-13 Genevac Ltd. Balancing device in combination with centrifugal evaporator
US6651527B2 (en) * 2000-07-19 2003-11-25 INA-Wälzlager Schaeffler oHG Self-balancing device
US20040018927A1 (en) * 2001-04-02 2004-01-29 Dou-Ha Baik Automatic balance adjusting centrifugal apparatus
US6949063B2 (en) * 2001-04-02 2005-09-27 Hanlab Corporation Automatic balance adjusting centrifugal apparatus
US20040142808A1 (en) * 2001-05-26 2004-07-22 Wilfried Mackel Centrifugal separator
US6960158B2 (en) * 2001-05-26 2005-11-01 Westfalia Separator Ag Centrifugal separator
US20050026765A1 (en) * 2003-07-29 2005-02-03 Diagyr Process to balance a rotatable plate of a centrifuge and centrifuge using the process
US7025714B2 (en) * 2003-07-29 2006-04-11 Diagyr Process to balance a rotatable plate of a centrifuge and centrifuge using the process
US7435211B2 (en) * 2006-03-23 2008-10-14 Korea Institute Of Machinery & Materials Ball balancer for vertical rotor and centrifuge
US20070225143A1 (en) * 2006-03-23 2007-09-27 Korea Institute Of Machinery & Materials Balancer for vertical rotor and centrifuge using the same
US20100009835A1 (en) * 2008-07-09 2010-01-14 Hanlab Corporation Automatic balancing centrifuge using balancer
US7942801B2 (en) * 2008-07-09 2011-05-17 Hanlab Corporation Automatic balancing centrifuge using balancer
US20100009833A1 (en) * 2008-07-10 2010-01-14 Hanlab Corporation Automatic balance adjusting centrifuge and the control method thereof
US8251883B2 (en) * 2008-07-10 2012-08-28 Hanlab Corporation Automatic balance adjusting centrifuge and the control method thereof
US20100069216A1 (en) * 2008-09-16 2010-03-18 Hanlab Corporation Control method of automatic balancing centrifuge using balancer
US8292793B2 (en) * 2008-09-16 2012-10-23 Hanlab Corporation Control method of automatic balancing centrifuge using balancer
US20100160138A1 (en) * 2008-12-18 2010-06-24 Thermo Electron Led Gmbh Mounting Means For Mounting A Device With A Rotor
US8517904B2 (en) * 2008-12-18 2013-08-27 Thermo Electron Led Gmbh Mounting structure having direction-dependent resilient properties for mounting a device with a rotor
US8375826B1 (en) * 2011-12-15 2013-02-19 Cnh America Llc Self balancing chopping or threshing rotor
US20130263659A1 (en) * 2012-04-04 2013-10-10 Elliott Company Passive dynamic inertial rotor balance system for turbomachinery
US8984940B2 (en) * 2012-04-04 2015-03-24 Elliot Company Passive dynamic inertial rotor balance system for turbomachinery
US10335804B2 (en) * 2014-02-25 2019-07-02 Andreas Hettich Gmbh & Co. Kg Centrifuge with damping elements
US10337943B2 (en) * 2014-11-12 2019-07-02 Andreas Hettich Gmbh & Co. Kg Centrifuge and method for sensing imbalances in the centrifuge
US11292014B2 (en) 2015-04-05 2022-04-05 Arteriocyte Medical Systems, Inc. Centrifuge counterbalance with adjustable center of gravity and methods for using the same
CN113304896A (zh) * 2021-04-16 2021-08-27 中国联合工程有限公司 土工离心机转子系统在线动态不平衡调节装置及调节方法
CN116673135A (zh) * 2023-05-30 2023-09-01 武汉兰丁云医学检验实验室有限公司 可切换配重的内部补偿式细胞组织离心装置
CN116673135B (zh) * 2023-05-30 2025-10-31 武汉兰丁云医学检验实验室有限公司 可切换配重的内部补偿式细胞组织离心装置
CN118236732A (zh) * 2024-05-28 2024-06-25 广州市朗坤环境科技有限公司 一种酶法生物柴油中甘油分离装置及其分离方法
CN118705324A (zh) * 2024-08-29 2024-09-27 中科南京生命健康高等研究院 一种用于生物试验的多功能酶标仪

Also Published As

Publication number Publication date
DE2152840A1 (de) 1972-05-31
SU463254A3 (ru) 1975-03-05
BE773364A (fr) 1972-03-30
CA936506A (en) 1973-11-06
NL7114176A (OSRAM) 1972-05-03
FR2110116A5 (OSRAM) 1972-05-26
GB1346115A (en) 1974-02-06
AU3333171A (en) 1973-03-15
IT938889B (it) 1973-02-10
CH542658A (de) 1973-10-15

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Effective date: 19871231