US3822604A - Unbalanced vibrator for an oscillating conveyor or a vibrating screen - Google Patents

Unbalanced vibrator for an oscillating conveyor or a vibrating screen Download PDF

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Publication number
US3822604A
US3822604A US00258986A US25898672A US3822604A US 3822604 A US3822604 A US 3822604A US 00258986 A US00258986 A US 00258986A US 25898672 A US25898672 A US 25898672A US 3822604 A US3822604 A US 3822604A
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mass
motor
masses
speed
power unit
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Expired - Lifetime
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US00258986A
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K Grimmer
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/162—Making use of masses with adjustable amount of eccentricity
    • B06B1/164—Making use of masses with adjustable amount of eccentricity the amount of eccentricity being automatically variable as a function of the running condition, e.g. speed, direction
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G27/00—Jigging conveyors
    • B65G27/10—Applications of devices for generating or transmitting jigging movements
    • B65G27/16—Applications of devices for generating or transmitting jigging movements of vibrators, i.e. devices for producing movements of high frequency and small amplitude
    • B65G27/18—Mechanical devices
    • B65G27/20—Mechanical devices rotating unbalanced masses
    • 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
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight

Definitions

  • Appl. No.: 258,986 at least one pair of associated unbalanced masses disposed on the shaft of said motor, with the first mass of a pair of said unbalanced masses being rigidly fastened
  • the invention relates to an unbalanced vibrator for an oscillating conveyer or a vibrating screen connected in suitable manner to a conveyer or screen for impart- I ing vibrations thereto, and pertains particularly to vibratory power units driven by an asynchronous polyphase motor and provided with at least one pair of associated unbalanced masses disposed on the shaft of said motor, with the first mass of a pair of said unbalanced masses being rigidly fastened to said shaft and with said second mass of said pair being movably arranged relative to said first mass.
  • Vibratory power units of this type are known, in which the position of the movable mass or weight member is changeable by rotating it relative to the fixed mass.
  • a regulation of the centrifugal forces and, thus due to changes in the vibration amplitude a regulation of the conveying capacity between a maximum and a minimum value can be obtained.
  • Such regulation can, however, not be effected during operation but can be effected only when the unit is at rest. If the two masses of a pair or of each pair, if two pairs of masses are used, are of equal size, the conveying capacity can be adjusted between a maximum, when the two masses are directed equally with respect to the motor shaft, and zero, when the two masses are oppositely directed i and the generated centrifugal forces cancel each other.
  • Electro-magnetic vibrators do only operate on 50 Hz or 100 Hz frequencies. Such high frequencies permit, due to the natural frequencies in bending, only limited lengths for the conveyers and screens on which the units are used.
  • a further disadvantage is that at such high exciting frequencies the conveying speed and the conveying capacity is relatively low.
  • electromagnetic vibrating conveyers are noisy in operation and are also rather expensive.
  • a vibratory power unit for vibrating conveyers and screens comprises an asynchronous polyphase motor, at least one pair of associated unbalanced masses disposed on the shaft of said motor, with the first mass of a pair of said unbalanced masses being rigidly fastened to said shaft and with said second mass of said pair being movably arranged relative to said first mass, means for controlling and regulating the conveying rate during conveyer operation by varying the rotational speed of said motor between predetermined minimum and maximum values, said second mass being movably outwardly by centrifugal force against the pressure of spring means, said spring means being prestressed in such a manner that said second mass is, at rotational motor speeds lower than said minimum speed, held in its initial position, and at motor speeds between said lower and upper values in positions which are radially offset with respect to the axis of said motor to an extent depending on the value of said rotational motor speed.
  • the asynchronous polyphase motor is preferably a normal short circuit rotor motor, i.e., an extraordinarily sturdy and yet inexpensive: kindof motor.
  • control means for varying the rotational speed of this short circuit rotor motor there can for instance be used a controllable or regulatable compensating resistance or a transformer or a similar control means, by which the supply voltage of the motor can be reduced relative to its rated voltage in any desired manner.
  • a reduction of the supply voltage below a value corresponding to about percent of the rated motor speed is not desirable because the motor would stall, inasmuch as the torque produced by too low a voltage does not suffice anymore to overcome the forces resisting rotation.
  • the conveying capacity is to be gradually changed during operation betweenthe maximum value and practically zero, it is of advantage to have, when said second mass is disposed in its initial position, the center of gravity of the system, which comprises said first and second unbalanced masses and said spring means, located on the axis of the motor shaft. in this position the two masses of a pair are balanced with respect to the rotational axis of the motor. Thus no centrifugal forces are generated up to the time the lower limit of the control resp. regulating range has been reached and the vibration amplitude and therefore the conveying capacity is zero up to this lower limit.
  • the spring or resilient means comprise at least one spring and preferably four prestressed helical springs which are interposed between the two masses.
  • the restoring force caused by the prestressing already exists when the unit is at rest and is, up to the time the minimum speed is reached, so large that the mass remains in its initial position.
  • the centrifugal force acting on the movable second mass will be of such magnitude that it surpasses the restoring force exerted by the prestressing of the springs, so that the second mass is lifted from the first mass.
  • the second mass can for instance be guided on the free end of a pin the other end of which is rigidly fastened to the first mass.
  • a pin Preferably two such pins and for masses of relatively large width four such pins are provided. This construction is also expedient, because the fixed end of the pin resp. pins can simultaneously act as holding or centering means for the helical spring or springs.
  • the system In order to obtain always the same position for the second mass at any specific motor speed between minimum and rated speed, the system should be designed in such a way that radial movement of the center of gravity of the second mass is a function of the motor speed resp. of the corresponding angular velocity.
  • the overall spring constant c of the spring means is to be at least equal but preferably greater than the product of the mass m of the second unbalanced mass and the square of the angular velocity w corresponding to the rated motor speed.
  • the dis tance which the center of gravity of the second mass has in the initial position thereof relative to the rotational axis of the motor, is unequal and preferably larger than the amount of linear prestressing of the spring means.
  • a vibratory unit according to the invention is preferably provided with two pairs of unbalanced masses arranged on the free ends of the motor shaft in overhung position.
  • a further advantage of the vibratory unit according to the invention resides in the fact that in the new device the centrifugal force does continuously decrease to a marked extent. As a result a stable synchronisation is also obtained in the lower region of the regulation range, if two contrarotating vibrationexciting units are arranged on the vibrating conveyer or screen.
  • FIG. 1 shows in section and in elevation seen in the direction of the motor shaft a pair of associated unbalance masses and the spring means interposed there between with the second mass being shown in its initial position;
  • FIG. 2 shows a similar view as FIG. 1 of the vibratory unit with the second mass in a position corresponding to a motor speed intermediate the minimum speed and the rated or maximum speed;
  • FIG. 3 is a semi-schematic representation of an asynchronous polyphase motor having a pair of associated unbalanced masses adjacent each end of the motor shaft and speed regulator for controlling the speed of the motor.
  • mass 1 When mass 1 has been properly positioned by pulling it on the shaft its two portions separated by slot 7 are tightly drawn together by a screw 8 thereby firmly fastening mass3 on the shaft.
  • the other or second mass 4 is arranged in such a way that it is relatively movable to mass 3 resp. to axis 1 from its initially occupied position shown in FIG. 1 in the direction of arrow 9.
  • the regulation means designated speed regulator in FIG. 3, is a transformer with which the supply voltage of the motoris regulated.
  • the regulation means is of known type and therefore details thereof need not be shown.
  • the spring means interposed between the two unbalanced masses comprises four prestressed helical compression springs 11 of which only two are shown in the drawing. The other two springs are disposed in back of the two springs shown.
  • the center of gravity of the system comprising the masses 3, 4 and the springs 11 is, if the second mass is in its initial position, located on axis 1. This position of the center of gravity is obtained by balancing the system.
  • the system is so devised that the restoring force of the springs 11 which forces the two masses 3, 4 into mutual engagement is, owing to the selected prestressing of the springs, of such magnitude that at a motor speed It between zero and a predetermined minimum speed ri the second mass 4 is held in its initial position (FIG. ll), inasmuch as the centrifugal force acting on mass 4 does not sufiice to overcome the restoring force.
  • the predetermined motor speed ri corresponds to that motor speed at which the motor torque just suffices to overcome the forces resisting a rotation of the motor, for instance frictional resistance. If the speed is reduced below ri the motor will stall.
  • the speed n is also the lower speed limit of the regulation range.
  • the defined outward movement of the second mass 4 at a specific speed within the regulation range is preferably obtained by making the total spring constant c of the spring means larger than the product of the mass m of the second unbalanced mass and the square of the angular velocity w corresponding to the rated speed rz
  • the linear amount of prestressing of springs 11 is smaller than the distance a of the center of gravity 8., of the second mass 4 as shown in FIG. 1, with said second mass in its initial position.
  • pins 12 which constitute the free ends of the shafts of bolts 13 threadedly connected to a flange 14 of first mass 3. These pins 12 extend into guiding bores 16 provided in the second mass. Of these bolts only two are shown, as the other two are disposed in the drawing in back of those shown. The heads of the bolts 13 serve as supporting or centering means for springs ll.
  • an elastic buffering layer 17 which is fixedly connected as by bonding to flange 14 at its side 19 facing the second mass.
  • This buffering layer 17 which may consist for instance of polyethylene or a suitable rubber prevents chattering of the power unit.
  • a corresponding buffering layer 21 is also provided on the stop faces of stops 22, in order to prevent chattering, when the maximum speed resp. rated speed n has been reached.
  • the stops 22 are parts of bolts threadedly connected to mass 4. These bolts, which are adjustable by means of nuts 23, also serve for centering and supporting the springs 11. Although it would be possible to do without such stops, inasmuch as the largest outward movement of mass 4 is prescribed by the rated speed, the provision of such stops is preferred for reason of safety.
  • the mass system can be so devised that the center of gravity of the entire system is, when the device is in its position of rest shown in FIG. 1, not located on the motor axis, but is shifted outwardly in the direction of arrow 9 in accordance with the desired minimum conveying capacity in the lower region of the regulation range.
  • the restoring force of the spring means is so selected that the second mass 4- moves away from the motor axis at the lower speed n
  • the short circuit rotor motor has a rated speed 11,, 1,470 revolutions/min, which owing to the decreasing centrifugal force at de creased motor speedscontrary to known resonant unbalanced power units cannot only be reduced to a value of n 1,270 revolutions/min but, by lowering of the voltage, to a value for ri 900 1,000 revolutions/min. This results in a. considerably larger regulation range and also in stable synchronised operation at any speed.
  • FIG. 2 the device of FIG. 1 is shown when operating at a motor speed between minimum speed n and the maximum speed n
  • the second mass 4 has now moved away from the first mass 3 in the direction of arrow 9 with parts 13 and 21 being still out of engagement, as the rated speed n,,,,-,, has not been reached as yet.
  • the axis of symmetry is indicated by the reference numeral 24.
  • a vibratory power unit comprising a pair of associated unbalanced masses adapted to be carried by the rotatable drive shaft of a prime mover, the first of said masses being of generally T-shape in transverse cross section and adapted to be rigidly fastened to such a drive shaft, the second mass of said masses having a generally U-shaped portion in transverse cross section, and a portion connecting the free ends of said U- shaped portion, said second mass being movable radially outwardly relative to said first mass, said connecting portion having an opening therein of a size to receive the leg portion of said T-shaped mass with the cross portions of the latter disposed within said U- shaped portion, elongated guide means carried by said cross portions disposed in respective bores in the intermediate part of said U-shaped portion, and spring means disposed between the respective cross portions and said connecting portion, operative to normally maintain said second mass in its inward position, said spring means being compressible during rotation of the unit in response to centrifugal forces acting on said second mass, whereby the latter may assume
  • Vibratory power unit according to claim 1 wherein the center of gravity of the system comprising said first and second unbalanced masses and said spring means is disposed, when said second mass is in its initial position, at the rotational axis of said motor shaft and on the axis of symmetry of said masses.
  • Vibratory power unit according to claim 2 wherein the difference in length of the spring means in its normal and its prestressed state is greater than the distance between the axis of said motor shaft and the center of gravity of said second mass, when said mass is disposed in its initial position.
  • Vibratory power unit according to claim 1 wherein the spring constant of said spring means is unequal to the product of the mass of said second unbalanced mass and the square of the angular velocity corresponding to the rated rotational speed of said motor.
  • Vibratory power unit according to claim 1 wherein stop means are provided between said masses for limiting relative movement of the masses away from each other when said motor rotates at its rated rotational speed.
  • Vibratory power unit according to claim 5 wherein means for supporting the free ends of said spring means are so configurated that they also act as stop means.
  • Vibratory power unit according to claim 6 wherein at least one of the abutting faces of said stop means is covered by a layer of resilient material.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Jigging Conveyors (AREA)
US00258986A 1971-06-03 1972-06-02 Unbalanced vibrator for an oscillating conveyor or a vibrating screen Expired - Lifetime US3822604A (en)

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Application Number Priority Date Filing Date Title
US05/473,061 US4114462A (en) 1972-06-02 1974-05-24 Unbalanced vibrator for an oscillating conveyor or a vibrating screen

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19712127433 DE2127433B2 (de) 1971-06-03 1971-06-03 Unwuchterreger zum antrieb einer schwingrinne oder eines schwingsiebes

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US05/473,061 Division US4114462A (en) 1972-06-02 1974-05-24 Unbalanced vibrator for an oscillating conveyor or a vibrating screen

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US (1) US3822604A (de)
DE (1) DE2127433B2 (de)
FR (1) FR2140233B3 (de)
GB (1) GB1346726A (de)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4341126A (en) * 1977-02-25 1982-07-27 Thomas Hubert E Variable amplitude vibratory apparatus
US4342523A (en) * 1981-02-24 1982-08-03 Koehring Company High-low force amplitude device
US4348912A (en) * 1979-08-21 1982-09-14 Thomas Hubert E Variable amplitude vibrator apparatus
US4367054A (en) * 1981-02-24 1983-01-04 The Koehring Company Vibratory roller
US4461122A (en) * 1981-08-03 1984-07-24 Roto-Finish Company, Inc. Finishing apparatus with automatically-variable vibrogyratory intensity and/or direction
US4580456A (en) * 1983-04-14 1986-04-08 Kikumithus Takano Balance weight transfer device for a vibrator
US4759659A (en) * 1987-07-01 1988-07-26 Fernand Copie Variable vibrator system
DE3716664A1 (de) * 1987-05-19 1988-12-01 Buehler Miag Gmbh Auslesemaschine fuer koerniges gut
US4830534A (en) * 1987-10-21 1989-05-16 Hyster Company Dual amplitude vibration generator for compaction apparatus
US5054606A (en) * 1988-05-11 1991-10-08 General Kinematics Corporation Control system for vibratory apparatus
US6224293B1 (en) * 1999-04-19 2001-05-01 Compaction America, Inc. Variable amplitude vibration generator for compaction machine
WO2002000359A1 (de) * 2000-06-29 2002-01-03 Riedl, Franz Vibrationserreger mit amplitudenverstellung
US6401933B1 (en) * 2000-11-01 2002-06-11 Ohio Central Steel Company An Ohio Corporation Displaceable eccentric for vibratory screen
US6516679B2 (en) 2001-01-29 2003-02-11 Ingersoll-Rand Company Eccentric assembly with eccentric weights that have a speed dependent phased relationship
US6585450B2 (en) * 2001-07-10 2003-07-01 Ingersoll-Rand Company Speed controlled eccentric assembly
US6669026B2 (en) * 2000-11-01 2003-12-30 Ohio Central Steel Company Portable screening plant with displaceable eccentric
US20080027694A1 (en) * 2006-07-12 2008-01-31 Yury Michael Gitman Heartbeat Simulation Method And Apparatus
US20110013990A1 (en) * 2007-10-16 2011-01-20 Uwe Richter Device for producing vibrations
US20110158745A1 (en) * 2009-12-31 2011-06-30 Caterpillar Paving Products Inc. Vibratory system for a compactor
US10227737B1 (en) * 2017-11-03 2019-03-12 Caterpillar Inc. Compaction machine

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4040303A (en) * 1975-09-05 1977-08-09 Fmc Corporation Two mass vibratory material handling apparatus and methods of manufacturing and fine tuning the same
DE2727958C2 (de) * 1977-06-22 1983-01-13 Klöckner-Humboldt-Deutz AG, 5000 Köln Resonanzfördervorrichtung, insbesondere für den Bunkerabzug
DE2935739A1 (de) * 1979-09-05 1981-03-26 Klöckner-Humboldt-Deutz AG, 51063 Köln Verfahren und vorrichtung zur steuerung einer resonanzschwingrinne
DE20008496U1 (de) 2000-05-11 2000-09-21 Rammax Maschinenbau GmbH, 72555 Metzingen Vorrichtung zur Verdichtung
DE102010015950B4 (de) * 2010-03-12 2012-12-13 RAVI Baugeräte GmbH Handrüttelgerät zur Verdichtung von Materialien im Straßen-, Gleis- und Erdbau

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US948047A (en) * 1906-06-18 1910-02-01 John Fraser Gyratory machine.
US952565A (en) * 1908-10-30 1910-03-22 John Fraser Gyratory machine.
US1128729A (en) * 1914-08-26 1915-02-16 Salem Foundry And Machine Works Gyratory sifter.
US1207847A (en) * 1915-12-20 1916-12-12 Nordyke & Marmon Company Self-balancing sifter.
US2989869A (en) * 1957-02-25 1961-06-27 Continental Oil Co Constant force variable speed vibrator
US3342075A (en) * 1965-02-23 1967-09-19 Missouri Rogers Corp Vibrating mechanism

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US948047A (en) * 1906-06-18 1910-02-01 John Fraser Gyratory machine.
US952565A (en) * 1908-10-30 1910-03-22 John Fraser Gyratory machine.
US1128729A (en) * 1914-08-26 1915-02-16 Salem Foundry And Machine Works Gyratory sifter.
US1207847A (en) * 1915-12-20 1916-12-12 Nordyke & Marmon Company Self-balancing sifter.
US2989869A (en) * 1957-02-25 1961-06-27 Continental Oil Co Constant force variable speed vibrator
US3342075A (en) * 1965-02-23 1967-09-19 Missouri Rogers Corp Vibrating mechanism

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4341126A (en) * 1977-02-25 1982-07-27 Thomas Hubert E Variable amplitude vibratory apparatus
US4348912A (en) * 1979-08-21 1982-09-14 Thomas Hubert E Variable amplitude vibrator apparatus
US4342523A (en) * 1981-02-24 1982-08-03 Koehring Company High-low force amplitude device
US4367054A (en) * 1981-02-24 1983-01-04 The Koehring Company Vibratory roller
US4461122A (en) * 1981-08-03 1984-07-24 Roto-Finish Company, Inc. Finishing apparatus with automatically-variable vibrogyratory intensity and/or direction
US4580456A (en) * 1983-04-14 1986-04-08 Kikumithus Takano Balance weight transfer device for a vibrator
DE3716664A1 (de) * 1987-05-19 1988-12-01 Buehler Miag Gmbh Auslesemaschine fuer koerniges gut
US4978011A (en) * 1987-05-19 1990-12-18 Buhler Gmbh Sorting machine for grained products
US4759659A (en) * 1987-07-01 1988-07-26 Fernand Copie Variable vibrator system
US4830534A (en) * 1987-10-21 1989-05-16 Hyster Company Dual amplitude vibration generator for compaction apparatus
US5054606A (en) * 1988-05-11 1991-10-08 General Kinematics Corporation Control system for vibratory apparatus
US6224293B1 (en) * 1999-04-19 2001-05-01 Compaction America, Inc. Variable amplitude vibration generator for compaction machine
WO2002000359A1 (de) * 2000-06-29 2002-01-03 Riedl, Franz Vibrationserreger mit amplitudenverstellung
US6401933B1 (en) * 2000-11-01 2002-06-11 Ohio Central Steel Company An Ohio Corporation Displaceable eccentric for vibratory screen
US6669026B2 (en) * 2000-11-01 2003-12-30 Ohio Central Steel Company Portable screening plant with displaceable eccentric
US6516679B2 (en) 2001-01-29 2003-02-11 Ingersoll-Rand Company Eccentric assembly with eccentric weights that have a speed dependent phased relationship
US6585450B2 (en) * 2001-07-10 2003-07-01 Ingersoll-Rand Company Speed controlled eccentric assembly
US20080027694A1 (en) * 2006-07-12 2008-01-31 Yury Michael Gitman Heartbeat Simulation Method And Apparatus
US20110013990A1 (en) * 2007-10-16 2011-01-20 Uwe Richter Device for producing vibrations
US8226329B2 (en) * 2007-10-16 2012-07-24 Thyssenkrupp Gft Tiefbautechnik Gmbh Device for producing vibrations
US20110158745A1 (en) * 2009-12-31 2011-06-30 Caterpillar Paving Products Inc. Vibratory system for a compactor
US10227737B1 (en) * 2017-11-03 2019-03-12 Caterpillar Inc. Compaction machine

Also Published As

Publication number Publication date
DE2127433B2 (de) 1973-05-30
FR2140233A1 (de) 1973-01-12
DE2127433A1 (de) 1972-12-21
GB1346726A (en) 1974-02-13
FR2140233B3 (de) 1975-08-08

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