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WO1998001733A1 - Procede de reduction de l'amplitude d'une vibration dans des systemes rotatifs - Google Patents

Procede de reduction de l'amplitude d'une vibration dans des systemes rotatifs Download PDF

Info

Publication number
WO1998001733A1
WO1998001733A1 PCT/SE1997/001216 SE9701216W WO9801733A1 WO 1998001733 A1 WO1998001733 A1 WO 1998001733A1 SE 9701216 W SE9701216 W SE 9701216W WO 9801733 A1 WO9801733 A1 WO 9801733A1
Authority
WO
WIPO (PCT)
Prior art keywords
imbalance
rotary
mass
rotary system
vibration amplitude
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.)
Ceased
Application number
PCT/SE1997/001216
Other languages
English (en)
Inventor
Jonas NILSAGÅRD
Peter Kinde
Lars NORDSTRÖM
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.)
SKF AB
Original Assignee
SKF AB
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 SKF AB filed Critical SKF AB
Priority to AU36382/97A priority Critical patent/AU3638297A/en
Publication of WO1998001733A1 publication Critical patent/WO1998001733A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24D—TOOLS FOR GRINDING, BUFFING OR SHARPENING
    • B24D5/00—Bonded abrasive wheels, or wheels with inserted abrasive blocks, designed for acting only by their periphery; Bushings or mountings therefor
    • B24D5/16—Bushings; Mountings
    • B24D5/165—Balancing means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
    • B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B41/00—Component parts such as frames, beds, carriages, headstocks
    • B24B41/04—Headstocks; Working-spindles; Features relating thereto
    • B24B41/042—Balancing mechanisms
    • 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
    • F16F15/32—Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels
    • F16F15/36—Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels operating automatically, i.e. where, for a given amount of imbalance, there is movement of masses until balance is achieved
    • F16F15/363—Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels operating automatically, i.e. where, for a given amount of imbalance, there is movement of masses until balance is achieved using rolling bodies, e.g. balls free to move in a circumferential direction
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M1/00—Testing static or dynamic balance of machines or structures
    • G01M1/30—Compensating imbalance
    • G01M1/36—Compensating imbalance by adjusting position of masses built-in the body to be tested

Definitions

  • the present invention refers to a method for controlling vibration imparted on different types of rotary systems following imbalance in said systems. For minimizing such imbalance tendencies it has since long been provided mechanisms, which automatically outbalance the vibrations and allow the system to operate at a substantially reduced vibration level. This is achieved by means of rolling bodies freely movable in paths concentric with the axis of the rotary system, which rolling bodies at rotation of the system automatically will find their appropriate angular positions along the path to compensate for the inherent imbalance of the system. Such mechanisms are commonly referred to as auto-balancing units, and the method itself is called auto-balancing.
  • the purpose of the present invention is to provide a solution of this problem and to suggest a method for controlling vibration amplitude in rotary systems, whereby is obtained a rapid and appropriate automatic positioning of the balancing rolling bodies in their path, and this is achieved with the features defined in the accompanying claim 1.
  • Fig. 1 a diagrammatical illustration over a mechanical system appropriate for being equipped with an autobalancing unit.
  • Fig. 2 is a diagram showing the vibrational characteristics for a discrete system with initial eccentricity ⁇ .
  • FIG. 3 illustrates in a schematical side view an autobalancing unit in out-balanced position.
  • Fig.s 4a and 4b illustrate schematically the forces acting upon a rolling body in an autobalancing unit at different amplitudes
  • Fig. 5 illustrates schematically an autobalancing unit provided with an artificial imbalance in accordance with the present invention.
  • FIG. 1 which very schematically shows a housing 1, being resiliently connected to a base 2, as illustrated with a symbolic spring 3, and being provided with a shaft 4 having a rotating mass 5.
  • the stationary vibration level i.e. the vibration level resulting after a long time and at different rotational speeds, for the rotating mass, (continuous line), and for the machinery housing (dash-line), when the rotating mass has an eccentricity ⁇ relative to its shafting point.
  • Fig. 3 is schematically illustrated in a side view an autobalancing unit, intended to be connected concentric to the rotary shaft or the like, which shall be outbalanced, and comprising an inner ring 6, an outer race ring 7 positioned about the inner ring 6 and concentric thereabout and a number of rolling bodies 8, preferably balls, but being of such a number that they occupy only a part of the volume contained between the two 0 rings 6 and 7.
  • rolling bodies 8 preferably balls, but being of such a number that they occupy only a part of the volume contained between the two 0 rings 6 and 7.
  • the space between the rings 6, 7 is closed off externally by means of not shown end plates, and the free volume between rings and endplates, not occupied by the rolling bodies 8 is usually filled with a medium, e.g. oil exerting a dampening and pulling-along effect on the rolling bodies.
  • a medium e.g. oil exerting a dampening and pulling-along effect on the rolling bodies.
  • the unit in this figure is shown in out-balanced condition, whereby an out-off-balance effect is illustrated in the upper right hand quadrant of the outer race ring at OOB.
  • the rolling bodies 8 here have taken up spaced apart positions along the outer race ring distributed about the position opposite to the position for the OOB, and thereby the disturbing out- off-balance OOB is compensated, and the centrifugal force F c acting on the rolling body and the normal force F N acting perpendicularly towards the race track are equal and directed in opposite directions and through the centre of rotation RC and the geometrical centre GC, which thereby coincide. Therefore there is no resulting force causing imbalance when the system is running.
  • the out-off-balance symbol OOB is illustrated as a rather small area, representing a comparatively small mass, and the rolling bodies 8 thereby are distributed over quite a long portion of the race track. If the size of the OOB and/or the distance between the position for OOB and the geometrical centre GC should increase, then the rolling bodies of course should become more concentrated opposite to the position for OOB, until they finally should be positioned close to each other.
  • the autobalancing principle requires that there is about 180° phase shift between the centre of gravity of the rotating mass and its deflection, i.e. when the centre of gravity of the rotating body 5 is pointing upwards on the body, then its shaft centre is in its lowermost position.
  • This phase difference can be seen in the Fig. 2 diagram, as a "negative amplitude", i.e. the continuous line is in the appropriate area situated below the axis representing the rotational speed.
  • the rotational speed is generally in the intermediate area, i.e. on the plateau of the continuous line in Fig. 2.
  • the balancing bodies are influenced in a manner so as to help them initially to start finding their correct balancing positions, and this is done by intentionally increas- 10 ing the forced vibration amplitude U f .
  • this can be achieved by increasing the ratio between the rotating imbalance m.-,, * ⁇ and the total mass m Iot , which last mentioned is m rot + m h , i.e. the rotating mass together with the mass of the housing supporting the rotating mass.
  • FIG. 4a With reference to Fig.s 4a and 4b it is schematically shown that at a system with imbalance there is a distance between the geometrical centre GC and the rotating centre RC, and this distance causes a resulting force F R .
  • Fig. 4a is shown how a small distance al _- causes a small resulting force F R
  • a larger distance a2 shown in Fig. 4b causes a bigger force F R .
  • the difference between heavy and light systems can be found in the size of the vibration amplitude.
  • the resulting force F R causing the balancing bodies (balls) in the balancing — unit to change their positions can be considered to be proportional to the vibration amplitude. This is shown to be lower for heavy machines, such as floor-anchored grinding machines, as compared to light machines, e.g. hand-held angular grinders.
  • the balls thus will experience a lower resulting force at lower vibration amplitude, and if this is too low the balls will not be able to overcome the internal resistance of the system, such as moment of inertia, resistance from the oil provided in the housing of the autobalancing unit as a medium dampening the motion of the balls and carrying them along, and this means that the balls will not move to try to find their optimum positions from a balancing point of view.
  • the internal resistance of the system such as moment of inertia, resistance from the oil provided in the housing of the autobalancing unit as a medium dampening the motion of the balls and carrying them along, and this means that the balls will not move to try to find their optimum positions from a balancing point of view.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Testing Of Balance (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

Procédé de réduction de l'amplitude d'une vibration se produisant dans différents types de systèmes rotatifs à la suite d'un déséquilibre dans ces systèmes, utilisant d'une manière connue en soi une unité auto-équilibrante comprenant une piste annulaire encaissée (7) montée dans le système et comportant un certain nombre d'éléments roulants (8) pouvant de déplacer librement le long de la piste de manière à compenser le déséquilibre du système rotatif, par l'application intentionnelle à l'unité auto-équilibrante d'une amplitude supplémentaire de vibration forcée accrue (uf).
PCT/SE1997/001216 1996-07-09 1997-07-04 Procede de reduction de l'amplitude d'une vibration dans des systemes rotatifs Ceased WO1998001733A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU36382/97A AU3638297A (en) 1996-07-09 1997-07-04 A method for controlling vibration amplitude in rotary systems

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9602706-5 1996-07-09
SE9602706A SE510266C2 (sv) 1996-07-09 1996-07-09 Metod för styrning av vibrationsamplitud i roterande system

Publications (1)

Publication Number Publication Date
WO1998001733A1 true WO1998001733A1 (fr) 1998-01-15

Family

ID=20403330

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1997/001216 Ceased WO1998001733A1 (fr) 1996-07-09 1997-07-04 Procede de reduction de l'amplitude d'une vibration dans des systemes rotatifs

Country Status (3)

Country Link
AU (1) AU3638297A (fr)
SE (1) SE510266C2 (fr)
WO (1) WO1998001733A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2341811A (en) * 1998-09-05 2000-03-29 Michael Cole Centrifugal evaporator with load sensor
GB2345655A (en) * 1998-11-12 2000-07-19 Michael Cole Centrufugal evaporator
DE10320974B4 (de) * 2003-05-09 2005-12-01 Siemens Ag Verfahren zur Verminderung einer Unwucht und Verwendung einer elektro-rheologischen Flüssigkeit zur Verminderung einer Unwucht
DE10320973B4 (de) * 2003-05-09 2006-04-27 Siemens Ag Bildgebendes Tomographie-Gerät und Verfahren zur Verminderung einer Unwucht an einem Tomographie-Gerät
DE102006050207B3 (de) * 2006-10-25 2008-05-29 Ab Skf Fahr- oder Flugzeugmodell oder -spielzeug
DE102007034382A1 (de) 2007-07-24 2009-01-29 Schaeffler Kg Autobalancing-Einrichtung zur Unwuchtkompensation in Separatoren bzw. Zentrifugen sowie Separator bzw. Zentrifuge mit einer solchen Autobalancing-Einrichtung
US20100069216A1 (en) * 2008-09-16 2010-03-18 Hanlab Corporation Control method of automatic balancing centrifuge using balancer
US7942801B2 (en) * 2008-07-09 2011-05-17 Hanlab Corporation Automatic balancing centrifuge using balancer
US10818450B2 (en) 2017-06-14 2020-10-27 Black & Decker Inc. Paddle switch

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4075909A (en) * 1976-01-29 1978-02-28 Deakin James E Automatic shaft balancer

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4075909A (en) * 1976-01-29 1978-02-28 Deakin James E Automatic shaft balancer

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2341811A (en) * 1998-09-05 2000-03-29 Michael Cole Centrifugal evaporator with load sensor
GB2341811B (en) * 1998-09-05 2002-04-17 Michael Cole Control of weight during evaporation of samples
GB2345655A (en) * 1998-11-12 2000-07-19 Michael Cole Centrufugal evaporator
DE10320974B4 (de) * 2003-05-09 2005-12-01 Siemens Ag Verfahren zur Verminderung einer Unwucht und Verwendung einer elektro-rheologischen Flüssigkeit zur Verminderung einer Unwucht
DE10320973B4 (de) * 2003-05-09 2006-04-27 Siemens Ag Bildgebendes Tomographie-Gerät und Verfahren zur Verminderung einer Unwucht an einem Tomographie-Gerät
DE102006050207B3 (de) * 2006-10-25 2008-05-29 Ab Skf Fahr- oder Flugzeugmodell oder -spielzeug
DE102007034382A1 (de) 2007-07-24 2009-01-29 Schaeffler Kg Autobalancing-Einrichtung zur Unwuchtkompensation in Separatoren bzw. Zentrifugen sowie Separator bzw. Zentrifuge mit einer solchen Autobalancing-Einrichtung
US7942801B2 (en) * 2008-07-09 2011-05-17 Hanlab Corporation Automatic balancing centrifuge using balancer
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
US10818450B2 (en) 2017-06-14 2020-10-27 Black & Decker Inc. Paddle switch

Also Published As

Publication number Publication date
SE510266C2 (sv) 1999-05-03
AU3638297A (en) 1998-02-02
SE9602706L (sv) 1998-01-10
SE9602706D0 (sv) 1996-07-09

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