EP0693324A2 - Vibrateur - Google Patents

Vibrateur Download PDF

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Publication number
EP0693324A2
EP0693324A2 EP95111391A EP95111391A EP0693324A2 EP 0693324 A2 EP0693324 A2 EP 0693324A2 EP 95111391 A EP95111391 A EP 95111391A EP 95111391 A EP95111391 A EP 95111391A EP 0693324 A2 EP0693324 A2 EP 0693324A2
Authority
EP
European Patent Office
Prior art keywords
shafts
parts
shaft
motor
vibration device
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.)
Withdrawn
Application number
EP95111391A
Other languages
German (de)
English (en)
Other versions
EP0693324A3 (fr
Inventor
Martin Sting
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.)
Aviteq Vibrationstechnik GmbH
Original Assignee
Licentia Patent Verwaltungs GmbH
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 Licentia Patent Verwaltungs GmbH filed Critical Licentia Patent Verwaltungs GmbH
Publication of EP0693324A2 publication Critical patent/EP0693324A2/fr
Publication of EP0693324A3 publication Critical patent/EP0693324A3/fr
Withdrawn legal-status Critical Current

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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

Definitions

  • the invention relates to a vibrating device with two parts which oscillate in approximately parallel directions of vibration in opposite directions to one another, each of which is set in vibration by a shaft rotating about its own longitudinal axis and equipped with an imbalance, the waves being rotated in the same direction of rotation by means of a mechanical device be forced and at least part of which is a conveyor element.
  • Such a vibrating device is described in document "Soviet Inventions Illustrated", (October 1962) Section H: MISCELLANEOUS under number 147443.
  • the vibrating device has two vibrating screens set in opposite directions to one another, horizontally in motion. The vibrating screens are suspended separately from each other so that they can vibrate.
  • An unbalanced shaft with a gear is rigidly attached to each vibrating screen. Both gears are rotated together by a third gear between them. This third gear is driven by a belt from a fixed motor.
  • the unbalances on the unbalanced shafts are offset by 180 ° to each other and move synchronously in the same direction of rotation due to the gear mechanism.
  • a vibrating linkage keeps the shafts of all three gears at the same distance from each other.
  • a vibrator with spring-coupled parts is from the attachment: Steinbrück, Klaus: Vibrating devices for conveyor and process engineering tasks known from the special print of AEG-TELEFUNKEN, vibration and welding technology, DK 621.867.52, page 3.
  • the special print is an extract from: TECHNICAL INFORMATION AEG-TELEFUNKEN 71 (1981) 3.
  • the vibrating device has a conveying element and a counter-vibrating frame located underneath.
  • the conveying element is fastened to the counter-oscillating frame via leaf springs.
  • the counter-oscillation frame is supported on springs on the foundation so that it can vibrate.
  • the vibrations are generated by an electromagnet attached to the counter-vibrating frame and an armature arranged on the conveyor floor.
  • a vibrating device, each with its own unbalance drive for the conveyor floor and counter-vibrating frame, is not mentioned.
  • a vibrating device with a resiliently mounted above the floor, horizontally movable conveyor element is known.
  • the conveying element is coupled via a leaf spring to a spring-mounted drive bracket, to which two unbalance motors are attached one above the other - above and below the leaf spring.
  • Both unbalance motors are driven separately in the same direction of rotation; they are not connected to one another by toothed belts or gears.
  • the two unbalances rotate by 180 ° to each other after a settling process has ended.
  • the vibration amplitude transmitted to the conveyor element reaches a minimum value. If different speeds are set on the unbalance motors, the vibration amplitude changes.
  • the vibrations of the conveying element are transmitted to the floor via the springs on which it is supported, so that considerable vibrations can possibly occur in a building.
  • the invention has for its object to provide a vibrator with two parts vibrating in approximately parallel directions of vibration opposite to each other, each of the two parts is set in motion with its own vibration drive and that Vibrating device works as quietly as possible, environmentally friendly and with only low mechanical stress on its elements.
  • the two parts which are mounted so that they can vibrate carry out oscillating movements. For example, if one part is moved to the right, the other part swings to the left. If the unbalanced shafts are arranged one above the other and the unbalances have the same weight, the upward and downward centrifugal forces always cancel each other out, the parts are then only set in motion by forces acting to the right and left. Due to the toothed belt (or a chain), the unbalanced shafts are always synchronized by force, even when the vibrator starts and brakes.
  • the vibrating device runs particularly smoothly, evenly and with little wear, and there is no "rocking" of the parts with increased vibrating amplitude, particularly when starting up.
  • the easy replacement in the event of wear of the toothed belt is favorable; the number of wearing parts is also limited.
  • the vibrator can be operated in a particularly environmentally friendly and low-maintenance manner.
  • the toothed belt emits less noise.
  • the resilient coupling of the two parts creates an oscillation system with a very specific resonance frequency.
  • the drive frequency can be adjusted by means of the speed at which the unbalanced shafts are driven. With a drive frequency close to the resonance frequency of the vibration system, the vibration amplitude of the parts is particularly large. The vibration amplitude can thus be changed very easily via the speed of the unbalanced shafts.
  • the conveyor element can be, for example, a conveyor trough, a vibrating screen or a conveyor tube. So that bulk material located on the conveying element is moved in a known manner during the oscillating movements by micro-throws in a certain direction, the conveying element must oscillate with a slight inclination to its longitudinal movement. When using a vibrating screen, however, it may not be necessary to aim for a conveying movement of the bulk material in a longitudinal direction.
  • the coupling elements attached between the vibrating parts should guide the conveying element accordingly.
  • Leaf springs as link springs
  • sliding elements, rubber thrust elements or coil springs can also be attached to the two parts, they have to be attached in their longitudinal direction in the desired direction of vibration of the conveying element.
  • rigid link arms between the parts in addition to spring elements, wherein they are rotatably attached to the parts.
  • the link arms could be mounted parallel to leaf springs, whereby the distance of the vibrating parts in the longitudinal direction of the link arms remains unchanged.
  • two unbalance motors are used for the drive.
  • Unbalance motors are offered relatively cheaply as finished components; By using two unbalance motors, the vibrating device can be assembled from many available components. This contributes to cost savings. Since the toothed belt can transmit the rotary movement, only a single unbalance motor needs to be supplied with power. It is possible to drive one of the two shafts equipped with an unbalance by means of a fixed motor.
  • the shaft of this motor should be arranged parallel to the shaft to be driven.
  • the connecting line between the shaft of the motor and the shaft driven by it should run perpendicular to the direction of the vibrations. This ensures that the timing belt does not jump out of the associated toothed belt pulleys. At the same time, the load resulting from the vibrations does not have a tensile load on the toothed belt.
  • the counter-oscillation frame is used as a pure counterweight (and not as an element for conveying or sieving bulk material), the introduction of vibrations of the conveying element into the foundation (floor) can be reduced particularly effectively (by choosing a correspondingly high weight).
  • the counter-oscillation frame absorbs the pendulum movements of the support element. The load on the building (in terms of noise and vibrations) in which the vibrating device is installed is thereby kept low.
  • a shaft can be driven via a belt by an oscillating motor, for example fastened on the drive block.
  • the belt always has the same tension and cannot loosen during the pendulum movements.
  • a shaft from a fixedly mounted motor, an articulated shaft being attached between the shaft and the motor.
  • a transmission can be interposed between the drive shaft and the motor.
  • 1 has an elongated conveying element (1) which is designed as a conveying trough and is supported on an elongated counter-oscillating frame (3) with leaf springs (2) (link springs) arranged uniformly over its length.
  • leaf springs (2) link springs
  • Conveying element (1) and counter-oscillation frame (3) have the same length and are - parallel to each other - arranged one above the other.
  • the counter-oscillating frame (3) is supported on the bottom on spiral springs (4), which are attached to a foundation (5).
  • the leaf springs (2) are arranged at a slight incline and enable oscillating movements which mainly point in the longitudinal direction of the conveying element (1) and the counter-oscillating frame (3). Due to the inclined position of the leaf springs (2), however, there is also a vibration component in a direction perpendicular to it.
  • This vibration component enables micro-throws of bulk material located on the conveying element (1);
  • the micro-throws and the subsequent springing back of the conveying element (1) enable the bulk material to be transported in the conveying direction (direction A) in a manner known per se.
  • a drive block (6) On the end of the conveying element (1) and the counter-oscillating frame (3) opposite the conveying direction (direction A), a drive block (6) is arranged at a small distance, which is mounted on spiral springs (7). Between the conveying element (1) and the drive block (6) at the level of the lower edge of the conveying element (1) in the longitudinal direction there are two shock springs (8) (in the form of leaf springs) located next to each other at the same height, which provide a coupling between the conveying floor (1 ) and the drive block (6). Two additional shock springs (9) are attached in parallel under the shock springs (8) (next to each other at the same height), which couple the counter-oscillating frame (3) to the drive block (6).
  • the natural frequency of the partial vibration system which is formed by the leaf springs (2) supporting the conveyor floor (1), is greater than the natural frequency of the system formed by the spiral springs (4, 7).
  • a shaft (10) with an imbalance (11) is attached - approximately at the height of the shock springs (8).
  • Both the shaft (10) and the motor shaft of the unbalance motor (12) are arranged perpendicular to the longitudinal direction of the conveyor element (1) and counter-oscillating frame (3). Both shafts (shaft 10, motor shaft) are equipped with unbalances (11, 13). The unbalances (11, 13) on both shafts have the same weight and are offset by 180 ° to each other; So that the staggered arrangement is maintained during operation, the shaft (10) and the motor shaft are coupled to each other via a toothed belt (14) (forced synchronization).
  • the imbalances (11, 13) are as centrifugal disks educated. The centrifugal disks are attached to both ends of the associated shafts (shaft 10, motor shaft).
  • the conveying element (1) and the counter-oscillating frame (3) oscillate in a pendulum-shaped manner, i.e. H. when the conveyor element (1) moves to the right, the counter-oscillating frame (3) simultaneously moves to the left and vice versa.
  • the drive bracket (6) oscillates around an inner pivot point (not shown) in the directions of the arrows (A) and (B).
  • FIG. 2 shows a vibrating device constructed similarly to FIG. 1;
  • two shafts (15, 16) are attached to the drive block (6), each of which, as described in connection with FIG. 1, has unbalances (17, 18) at the shaft ends, the unbalances (17, 18) are arranged offset by 180 ° as in the embodiment according to FIG. 1 in comparison of the two shafts (15, 16).
  • the shafts (15, 16) are attached in the same way as the shaft (10) and the motor shaft of the unbalance motor (12) in Fig. 1.
  • the shaft (16) is driven by a fixed, non-resonating motor (19), the transmits the rotary motion to the shaft (16) via a cardan shaft (20).
  • the shafts (15, 16) are coupled via a toothed belt (21).
  • FIG. 3 shows a further embodiment of the vibrating device.
  • two shafts (15, 16) with unbalances (17, 18) are fastened to the drive block (6); the upper shaft (15) is driven by a motor (23) via a toothed belt (22) which is held in toothed belt pulleys.
  • the lower shaft (16) is coupled to the upper one via a toothed belt (21).
  • the motor (23) is on top of the Drive bracket (6) attached and can have a different favorable speed than the speed of the shaft (15) (when using differently sized toothed belt pulleys).
  • the shaft (10) with the unbalance (11) according to FIG. 1 is replaced by a further unbalance motor (24); however, this unbalance motor (24) does not need to be connected to the mains.
  • this unbalance motor (24) does not need to be connected to the mains.
  • the shaft (10) in FIG. 1 it is set in motion via a toothed belt (14 ') by the unbalance motor (12') arranged below it.
  • the toothed belt (14 ') could also be omitted if both unbalance motors (12' and 24) were connected to the mains.
  • the load on the coil springs (7) then increases sharply in the start-up and in the outlet, and the deflection of the shock springs (8, 9) then requires a greater degree of freedom.
  • the embodiment according to FIG. 5 is largely identical to that in FIG.
  • the vibration drive also has a stationary motor (19 ') which drives the lower of the two shafts (15, 16) of the drive block (6) equipped with unbalances (17, 18).
  • a gear (25) is connected between the motor (19 ') and the lower shaft (16) and is driven by the motor (19') via a clutch (26).
  • an articulated shaft (27) is attached to the transmission (25), which transmits the rotary movement to the shaft (16) similarly as in FIG. 2.
  • the gear (15) can optionally be an actuating gear.
  • the motor (19 ') expediently has a higher speed than the shaft (16).
  • FIG. 6 shows a vibrating device similar to that described in FIG. 1, but the vibrating device according to FIG. 6 has no drive block (6).
  • the oscillating movement is generated by an unbalance motor (12 ') and a shaft (10') driven by the latter via a toothed belt (14 ') and equipped with an unbalance (11') (instead of the shaft 10 'with unbalance 11' a second unbalance motor could also be installed);
  • the shaft (10 ') is attached to the bottom of the conveyor floor (1) and the unbalance motor (12') is spatially offset below it on the counter-oscillating frame (3).
  • the unbalance (11 ', 13') of the unbalance motor (12 ') and shaft (10') are arranged offset by 180 ° to each other.
  • leaf springs (2) (as link springs) which prevent the toothed belt (14') from being subjected to any forces in its longitudinal direction during the oscillatory movements is.
  • the arrangement of the leaf springs (2) creates a pendulum movement.
  • Handlebar rods (28) are arranged in a sprung manner parallel to the leaf springs (2), which are adjacent to the unbalance motor (12 ') and which, in addition to other leaf springs (2), hold the conveyor floor (1).
  • shock springs (8) and (9) can also be replaced by swivel joints, which practically only transmit forces in the longitudinal direction (i.e. in the direction of vibration), but not in a direction perpendicular to it.
  • Swivel joints the articulated arms of which can only be moved in one plane ("degrees of freedom" only in one plane) should be mounted between the drive bracket (6) and the conveyor element (1) or the counter-oscillating frame (3) in such a way that this plane is perpendicular to the Waves with the unbalance runs.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jigging Conveyors (AREA)
EP95111391A 1994-07-20 1995-07-20 Vibrateur Withdrawn EP0693324A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19944425646 DE4425646C2 (de) 1994-07-20 1994-07-20 Schwinggerät
DE4425646 1994-07-20

Publications (2)

Publication Number Publication Date
EP0693324A2 true EP0693324A2 (fr) 1996-01-24
EP0693324A3 EP0693324A3 (fr) 1997-05-21

Family

ID=6523657

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EP95111391A Withdrawn EP0693324A3 (fr) 1994-07-20 1995-07-20 Vibrateur

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DE (1) DE4425646C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002024347A1 (fr) * 2000-09-19 2002-03-28 Kertesz Andras Mecanisme pendulaire equilibre

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10325033B3 (de) * 2003-06-02 2005-02-03 Fritz Sperber Gmbh & Co. Antriebseinheit für eine Materialfördereinrichtung, insbesondere für ein Grasaufnahmefahrzeug
DE102012205153B4 (de) * 2012-03-29 2013-10-17 Repower Systems Se Prüfvorrichtung und Schwingmassenanordnung für ein Rotorblatt einer Windenergieanlage

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU147443A1 (ru) 1959-07-24 1961-11-30 А.Я. Лейкин Механический вибратор
US3053379A (en) 1956-06-21 1962-09-11 Schenck Gmbh Carl Material handling vibrating machine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE648127C (de) * 1933-11-24 1937-07-22 Carl Schenck Eisengiesserei Foerderrinne zur Foerderung von Massengut mittels schneller, vornehmlich ellipsenfoermig verlaufender Schwingungen von kleinem Ausmasse
US3630357A (en) * 1969-06-17 1971-12-28 Simpson Co Orville Stop motion screening appartus and method
US3750866A (en) * 1971-06-15 1973-08-07 Gen Kinematics Corp Vibratory conveyor with counterpoise
US5056652A (en) * 1979-07-02 1991-10-15 General Kinematics Corporation Vibratory conveyor

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3053379A (en) 1956-06-21 1962-09-11 Schenck Gmbh Carl Material handling vibrating machine
SU147443A1 (ru) 1959-07-24 1961-11-30 А.Я. Лейкин Механический вибратор

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
TECHNISCHE MITTEILUNGEN AEG-TELEFUNKEN, vol. 71, 1981, pages 3

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002024347A1 (fr) * 2000-09-19 2002-03-28 Kertesz Andras Mecanisme pendulaire equilibre

Also Published As

Publication number Publication date
DE4425646C2 (de) 1997-06-19
DE4425646A1 (de) 1996-01-25
EP0693324A3 (fr) 1997-05-21

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