EP0070344B1 - Directional vibrator - Google Patents

Directional vibrator Download PDF

Info

Publication number
EP0070344B1
EP0070344B1 EP81710026A EP81710026A EP0070344B1 EP 0070344 B1 EP0070344 B1 EP 0070344B1 EP 81710026 A EP81710026 A EP 81710026A EP 81710026 A EP81710026 A EP 81710026A EP 0070344 B1 EP0070344 B1 EP 0070344B1
Authority
EP
European Patent Office
Prior art keywords
flyweight
shaft
axis
gear
oscillating
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
Application number
EP81710026A
Other languages
German (de)
French (fr)
Other versions
EP0070344A1 (en
Inventor
Johannes Ing. grad. Bäumers
Werner Lisken
Heinz Ing. Grad. Lietzke
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.)
Losenhausen Maschinenbau AG and Co KG
Losenhausen Maschinenbau AG
Original Assignee
Losenhausen Maschinenbau AG and Co KG
Losenhausen Maschinenbau AG
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 Losenhausen Maschinenbau AG and Co KG, Losenhausen Maschinenbau AG filed Critical Losenhausen Maschinenbau AG and Co KG
Priority to DE8181710026T priority Critical patent/DE3169038D1/en
Priority to AT81710026T priority patent/ATE11879T1/en
Priority to EP81710026A priority patent/EP0070344B1/en
Priority to US06/394,717 priority patent/US4510815A/en
Publication of EP0070344A1 publication Critical patent/EP0070344A1/en
Application granted granted Critical
Publication of EP0070344B1 publication Critical patent/EP0070344B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • 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
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
    • 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
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18344—Unbalanced weights

Definitions

  • Such unbalanced vibrators designed as directional vibrators are used in particular in the case of self-moving vibratory plates in which the direction of movement of the vibratory plate can be changed by changing the direction of vibration.
  • two flyweights with imbalance shafts parallel to one another and mounted in a common housing rotate in opposite directions.
  • Each of the centrifugal weights generates a centrifugal force rotating with the drive speed. Due to the opposite rotation of the two centrifugal weights, the centrifugal force components cancel each other out in one plane, while they add up in the plane perpendicular to it. This creates a resulting vibration in one plane.
  • the position of this vibration level depends on the mutual phase relationship of the rotating centrifugal weights and can be changed by changing this phase relationship.
  • a known arrangement which allows a constant adjustment of the flyweights during the run, is that the unbalanced shafts are each provided with a gear.
  • the two gears are meshed with idler gears, the idler gears in turn meshing with each other.
  • the intermediate gears sit on rockers which are pivotable about the axes of the unbalanced shafts and are connected to one another by a link, so that they form a parallel link mechanism with this link.
  • One of the unbalanced shafts is driven.
  • the parallel link mechanism By swiveling the parallel link mechanism with the two rockers, the angular position of the other unbalanced shaft relative to the driven unbalanced shaft is changed and thus the position of the resulting vibration plane.
  • the invention is based on the object of relieving the displacement mechanism of such vibrations in an unbalance vibrator of the type defined at the outset.
  • Each of the rockers on the side opposite the idler gear with respect to the axis of the unbalanced shaft has a counterweight.
  • each of the rockers can be individually balanced, so that the resulting vibrations of the unbalance vibrator, even if they do not fall in the longitudinal direction of the rocker, do not exert any moments on the rocker about the axis of the unbalanced shaft.
  • Embodiments of the invention are the subject of the dependent claims.
  • the unbalanced mass vibration generator includes a Hous' se 10 in the housing 10, a first unbalanced shaft is mounted in bearings 14 12th
  • the first unbalanced shaft 12 carries a first flyweight 16. It is connected to a first gear 18.
  • a pulley 20 is seated on the first unbalanced shaft 12, via which the first unbalanced shaft 12 can be driven by a motor (not shown).
  • a second unbalanced shaft 22 is mounted in the housing 10 in parallel to the first unbalanced shaft 12 in bearings 24 and 26. It carries a second flyweight 28, which is formed here by two part weights 28A and 28B arranged symmetrically on both sides of the flyweight 16.
  • a second gear 30 is connected to the second unbalanced shaft 22. The two gears 18 and 30 are not in engagement with each other.
  • a first rocker 32 is pivotally mounted about the axis 33 of the first unbalanced shaft 12.
  • a second rocker 34 is pivotally mounted about the axis 36 of the second unbalanced shaft 22.
  • the rocker 34 consists of two halves 34A and 34B which are mounted on the second shaft 22 via ball bearings 38 and 40 on both sides of the gearwheel 30 and by a pin 42 at a distance from the second shaft 22 are connected.
  • the rocker arm 32 is mounted on the first shaft 12 in a similar manner.
  • a link 44 is articulated on the first and second rocker arms 32 and 34.
  • a bolt 46 extends between the two parts 34A and 34B of the rocker 34.
  • the link 44 is articulated between these parts 34A and 34B via a needle bearing 48 in one end.
  • the link 44 is articulated on the rocker 32.
  • the distance of the axis 50 about which the link 44 is pivotally articulated on the rocker 34 from the axis 36 of the second shaft 22 is the same as the distance of the axis 52 about which the link 44 is pivotally articulated on the first rocker 32, from the axis 33 of the first unbalanced shaft 12.
  • the effective length of the link 44 i. H. the distance between the axes 50 and 52 is equal to the distance between the axes 33 and 36 of the unbalanced shafts 12 and 22, respectively. It is thereby achieved that the axes 33, 36, 50 and 52 always form the corners of a parallelogram and the rockers 32 and 34 always run parallel to one another.
  • a first intermediate gear 54 is rotatably mounted on the first rocker 32 at a distance from the axis 33 of the first unbalanced shaft 12.
  • the first idler gear 54 is engaged with the first gear 18.
  • a second idler gear 56 is rotatably supported on the second rocker 34 at the same distance from the axis 36 of the second imbalance shaft 22 that the first idler gear 54 is from the axis 33 of the first imbalance shaft 12 has.
  • the second intermediate gear 56 is rotatably mounted on the pin 42 via a needle bearing 58.
  • the first intermediate gear 54 is mounted on the rocker 32 in the same way.
  • the second intermediate gear 54 is engaged with the second gear 30. 1, it is also in engagement with the first intermediate gear 54.
  • the second unbalanced shaft 22 is driven by the first unbalanced shaft 12 via the gear 18, the first intermediate gear 54, the second gear 56 and the second gear 30, in opposite directions to the unbalanced shaft 12.
  • the two rockers 32 and 34 can be pivoted by means of an adjusting mechanism 60, which will be described later.
  • each of the rockers 32 and 34 has a counterweight 62 and 64 on the side opposite the intermediate gear 54 and 56 with respect to the axis 33 and 36 of the unbalanced shaft 12 and 22, respectively. Due to the counterweights, each of the rockers 32 and 34 is' balanced with respect to its pivot axis, namely the axes 33 and 36, respectively.
  • the link 44 is articulated on the rocker arms 32 and 34 on the side opposite the intermediate gears 54 and 56 with respect to the axes 33 and 36 of the unbalanced shafts 12 and 22, respectively.
  • the adjustment mechanism 60 includes a toothed segment 66 that is attached to one of the rockers, in the preferred embodiment shown, to the second rocker 34.
  • the toothed segment 66 is curved about the axis 36 of the associated unbalanced shaft 22.
  • a toothed rack 68 is guided in longitudinally displaceable fashion in bushings 70, 72 and engages with the toothed segment 66.
  • the rack 68 is adjustable by means of movement transmission means, which in the preferred exemplary embodiment shown are formed by a Bowden cable 74.
  • a relatively light adjustment mechanism with a Bowden cable 74 can be used for the adjustment.

Abstract

Two flyweight shafts 12,22 are coupled by means of gears 18,30 each attached to one flyweight shaft 12,22 and two intermediate gears 54,56 each engaging one of these gears 18,30 and mesh with each other. Each of the intermediate gears 54, 56 is mounted on one of the oscillating cranks 32, 34 pivotably mounted on the associated flyweight shaft 12 and 22, respectively. The oscillating cranks 32 and 34 are held parallel to each other and can be pivoted to effect a relative phase displacement of the flyweight shafts 12, 22. The oscillating cranks 32,34 are provided with counterweights 62,64 and are thereby mass balanced to prevent oscillations from becoming effective on the oscillating cranks 32,34 and thus on the adjusting mechanism 60 during vibratory operation due to intertial forces.

Description

Die Erfindung betrifft einen als Richtschwinger ausgebildeten Unwuchtrüttler mit verstellbarer Schwingungsrichtung, enthaltend

  • (a) ein Gehäuse
  • (b) eine erste Unwuchtwelle, die
    • (b1) in dem Gehäuse gelagert ist,
    • (b2) ein erstes Fliehgewicht trägt,
    • (b3) mit einem ersten Zahnrad verbunden ist und
    • (b4) durch einen Motor antreibbar ist
  • (c) eine zweite Unwuchtwelle, die
    • (C1) in dem Gehäuse parallel zu der ersten Unwuchtwelle gelagert ist,
    • (c2) ein zweites Fliehgewicht trägt und
    • (c3) mit einem zweiten Zahnrad verbunden ist,
  • (d) eine erste Schwinge, die um die Achse der ersten Unwuchtwelle schwenkbar gelagert ist,
  • (e) eine zweite Schwinge, die um die Achse der zweiten Unwuchtwelle schwenkbar gelagert ist,
  • (f) einen Lenker,
    • (f1) der an der ersten und der zweiten Schwinge in gleichen Abständen von den Achsen der zugehörigen Unwuchtwellen angelenkt ist und
    • (f2) dessen effektive Länge gleich dem Abstand dieser Achsen voneinander ist,
  • (g) ein erstes Zwischenzahnrad, das
    • (gi) an der ersten Schwinge im Abstand von der Achse der ersten Unwuchtwelle drehbar gelagert ist und
    • (g2) mit dem ersten Zahnrad in Eingriff ist,
  • (h) ein zweites Zwischenzahnrad, das
    • (h1) an der zweiten Schwinge in den gleichen Abstand von der Achse der zweiten Unwuchtwelle drehbar gelagert ist, den das erste Zwischenzahnrad von der Achse der ersten Unwuchtwelle hat,
    • (ho mit dem zweiten Zahnrad in Eingriff ist und
    • (h3) mit dem ersten Zwischenzahnrad in Eingriff ist und
  • (i) einen Verstellmechanismus, durch den die beiden Schwingen verschwenkbar sind.
The invention relates to an imbalance shaker designed as a directional vibrator with an adjustable direction of vibration, comprising
  • (a) a housing
  • (b) a first unbalance shaft, the
    • (b 1 ) is stored in the housing,
    • (b 2 ) carries a first flyweight,
    • (b 3 ) is connected to a first gear and
    • (b 4 ) can be driven by a motor
  • (c) a second unbalance shaft, the
    • ( C1 ) is mounted in the housing parallel to the first unbalanced shaft,
    • (c 2 ) carries a second flyweight and
    • (c 3 ) is connected to a second gear,
  • (d) a first rocker which is pivotally mounted about the axis of the first unbalanced shaft,
  • (e) a second rocker which is pivotally mounted about the axis of the second unbalanced shaft,
  • (f) a handlebar,
    • (f 1 ) which is articulated on the first and second rockers at equal distances from the axes of the associated unbalanced shafts and
    • (f2) whose effective length is equal to the distance between these axes,
  • (g) a first idler gear that
    • (g i ) is rotatably mounted on the first rocker at a distance from the axis of the first unbalanced shaft and
    • (g2) is engaged with the first gear,
  • (h) a second idler gear that
    • (h 1 ) is rotatably mounted on the second rocker at the same distance from the axis of the second unbalanced shaft that the first intermediate gear has from the axis of the first unbalanced shaft,
    • (ho is engaged with the second gear and
    • (h 3 ) is engaged with the first idler gear and
  • (i) an adjustment mechanism by means of which the two rockers can be pivoted.

Solche als Richtschwinger ausgebildete Unwuchtrüttler werden insbesondere bei selbstbeweglichen Rüttelplatten verwendet, bei denen durch Veränderung der Schwingungsrichtung die Bewegungsrichtung der Rüttelplatte veränderbar ist. Bei solchen Unwuchtrüttlern laufen zwei Fliehgewichte mit zueinander parallelen, in einem gemeinsamen Gehäuse gelagerten Unwuchtwellen gegensinnig um. Jedes der Fliehgewichte erzeugt eine mit der Antriebsdrehzahl umlaufende Fliehkraft. Durch den gegensinnigen Umlauf der beiden Fliehgewichte heben sich die Fliehkraftkomponenten in einer Ebene auf, während sie sich in der dazu senkrechten Ebene addieren. Es entsteht so eine resultierende Schwingung in einer Ebene. Die Lage dieser Schwingungsebene hängt von der gegenseitigen Phasenbeziehung der umlaufenden Fliehgewichte ab und kann durch Veränderung dieser Phasenbeziehung verändert werden.Such unbalanced vibrators designed as directional vibrators are used in particular in the case of self-moving vibratory plates in which the direction of movement of the vibratory plate can be changed by changing the direction of vibration. In the case of such imbalance shakers, two flyweights with imbalance shafts parallel to one another and mounted in a common housing rotate in opposite directions. Each of the centrifugal weights generates a centrifugal force rotating with the drive speed. Due to the opposite rotation of the two centrifugal weights, the centrifugal force components cancel each other out in one plane, while they add up in the plane perpendicular to it. This creates a resulting vibration in one plane. The position of this vibration level depends on the mutual phase relationship of the rotating centrifugal weights and can be changed by changing this phase relationship.

Diese Veränderung der gegenseitigen Phasenbeziehung der Fliehgewichte muß während des Laufs des Unwuchtrüttlers stattfinden und sollte vorzugsweise stetig erfolgen.This change in the mutual phase relationship of the flyweights must take place during the run of the unbalance shaker and should preferably take place continuously.

Eine bekannte Anordnung, die eine stetige Verstellung der Fliehgewichte während des Laufes gestattet, besteht darin, daß die Unwuchtwellen mit je einem Zahnrad versehen sind. Die beiden Zahnräder sind mit Zwischenzahnrädern in Eingriff, wobei die Zwischenzahnräder ihrerseits miteinander in Eingriff sind. Die Zwischenzahnräder sitzen auf Schwingen, die um die Achsen der Unwuchtwellen verschwenkbar und durch einen Lenker miteinander verbunden sind, so daß sie mit diesem Lenker ein Parallellenkergetriebe bilden. Eine der Unwuchtwellen wird angetrieben. Durch Verschwenkung des Parallellenkergetriebes mit den beiden Schwingen wird die Winkellage der anderen Unwuchtwelle gegenüber der angetriebenen Unwuchtwelle verändert und damit die Lage der resultierenden Schwingungsebene.A known arrangement, which allows a constant adjustment of the flyweights during the run, is that the unbalanced shafts are each provided with a gear. The two gears are meshed with idler gears, the idler gears in turn meshing with each other. The intermediate gears sit on rockers which are pivotable about the axes of the unbalanced shafts and are connected to one another by a link, so that they form a parallel link mechanism with this link. One of the unbalanced shafts is driven. By swiveling the parallel link mechanism with the two rockers, the angular position of the other unbalanced shaft relative to the driven unbalanced shaft is changed and thus the position of the resulting vibration plane.

Bei den bekannten Unwuchtrüttlern dieser Art ergaben sich Probleme dann, wenn die resultierende Schwingungsebene nicht parallel zur Längsrichtung der Schwingen verläuft, also parallel zu den Ebenen, die durch die Achsen der Unwuchtwellen und die Achsen der Zwischenzahnräder gehen. Dann wirken nämlich auf die Zwischenzahnräder infolge der Schwingungen Trägheitskräfte, welche die Schwingen periodisch hin- und herzubewegen trachten. Diese Trägheitskräfte werden an dem Verstellmechanismus wirksam und müssen von diesem aufgenommen werden. Die bekannten Unwuchtrüttler dieser Art enthielten daher aufwendige Verstellmechanismen z. B. in Form eines Schneckentriebs.In the case of the known unbalance vibrators of this type, problems arose when the resulting vibration plane is not parallel to the longitudinal direction of the rockers, that is to say parallel to the planes which pass through the axes of the unbalance shafts and the axes of the intermediate gearwheels. Then, because of the vibrations, inertial forces act on the intermediate gears, which periodically move the rockers back and forth. These inertial forces act on the adjustment mechanism and must be absorbed by it. The known unbalance vibrators of this type therefore contained complex adjustment mechanisms such. B. in the form of a worm gear.

Der Erfindung liegt die Aufgabe zu grunde, bei einem Unwuchtrüttler der eingangs definierten Art den Verstellmechanismus von solchen Schwingungen zu entlasten.The invention is based on the object of relieving the displacement mechanism of such vibrations in an unbalance vibrator of the type defined at the outset.

Erfindungsgemäß wird diese Aufgabe dadurch gelöst, daßAccording to the invention, this object is achieved in that

(j) jede der Schwingen auf der dem Zwischenzahnrad in Bezug auf die Achse der Unwuchtwelle gegenüberliegenden Seite ein Gegengewicht aufweist.(j) Each of the rockers on the side opposite the idler gear with respect to the axis of the unbalanced shaft has a counterweight.

Auf diese Weise kann jede der Schwingen für sich masseausgeglichen werden, so daß die resultierenden Schwingungen des Unwuchtrüttlers, auch wenn sie nicht in die Längsrichtung der Schwinge fallen, keine Momente auf die Schwinge um die Achse der Umwuchtwelle ausüben.In this way, each of the rockers can be individually balanced, so that the resulting vibrations of the unbalance vibrator, even if they do not fall in the longitudinal direction of the rocker, do not exert any moments on the rocker about the axis of the unbalanced shaft.

Ausgestaltungen der Erfindung sind Gegenstand der Unteransprüche.Embodiments of the invention are the subject of the dependent claims.

Ein Ausführungsbeispiel der Erfindung ist nachstehend unter Bezugnahme auf die zugehörigen Zeichnungen näher erläutert :

  • Figur 1 ist eine Seitenansicht, teilweise im Schnitt, eines als Richtschwinger ausgebildeten Unwuchtrüttler.
  • Figur 2 zeigt eine Endansicht des Unwuchtrüttlers, ebenfalls teilweise im Schnitt.
  • Figur 3 zeigt eine Draufsicht des Unwuchtrüttlers ebenfalls teilweise im Schnitt.
An embodiment of the invention is explained in more detail below with reference to the accompanying drawings:
  • FIG. 1 is a side view, partly in section, of an unbalance shaker designed as a directional vibrator.
  • Figure 2 shows an end view of the unbalance shaker, also partially in section.
  • Figure 3 shows a top view of the unbalance vibrator, also partially in section.

Der Unwuchtrüttler enthält ein Gehä 'se 10. In dem Gehäuse 10 ist eine erste Unwuchtwelle 12 in Lagern 14 gelagert. Die erste Unwuchtwelle 12 trägt ein erstes Fliehgewicht 16. Sie ist mit einem ersten Zahnrad 18 verbunden. Auf der ersten Unwuchtwelle 12 sitzt eine Riemenscheibe 20, über die die erste Unwuchtwelle 12 von einem (nicht dargestellten) Motor antreibbar ist. Eine zweite Unwuchtwelle 22 ist in dem Gehäuse 10 parallel zu der ersten Unwuchtwelle 12 in Lagern 24 und 26 gelagert. Sie trägt ein zweites Fliehgewicht 28, das hier von zwei symmetrisch beiderseits des Fliehgewichts 16 angeordneten Teilgewichten 28A und 28B gebildet ist. Mit der zweiten Unwuchtwelle 22 ist ein zweites Zahnrad 30 verbunden. Die beiden Zahnräder 18 und 30 stehen nicht miteinander in Eingriff.The unbalanced mass vibration generator includes a Hous' se 10 in the housing 10, a first unbalanced shaft is mounted in bearings 14 12th The first unbalanced shaft 12 carries a first flyweight 16. It is connected to a first gear 18. A pulley 20 is seated on the first unbalanced shaft 12, via which the first unbalanced shaft 12 can be driven by a motor (not shown). A second unbalanced shaft 22 is mounted in the housing 10 in parallel to the first unbalanced shaft 12 in bearings 24 and 26. It carries a second flyweight 28, which is formed here by two part weights 28A and 28B arranged symmetrically on both sides of the flyweight 16. A second gear 30 is connected to the second unbalanced shaft 22. The two gears 18 and 30 are not in engagement with each other.

Eine erste Schwinge 32 ist um die Achse 33 der ersten Unwuchtwelle 12 schwenkbar gelagert. Eine zweite Schwinge 34 ist um die Achse 36 der zweiten Unwuchtwelle 22 schwenkbar gelagert. Wie aus Fig. 2 am besten ersichtlich ist, besteht die Schwinge 34 aus zwei Hälften 34A und 34B, die über Kugellager 38 und 40 beiderseits des Zahnrads 30 auf der zweiten Welle 22 gelagert und durch einen Zapfen 42 im Abstand von der zweiten Welle 22 miteinander verbunden sind. In ähnlicher Weise ist die Schwinge 32 auf der ersten Welle 12 gelagert. An der ersten und der zweiten Schwinge 32 und 34 ist ein Lenker 44 angelenkt. Ein Bolzen 46 erstreckt sich zwischen den beiden Teilen 34A und 34B der Schwinge 34. Auf diesem Bolzen 46 ist zwischen diesen Teilen 34A und 34B der Lenker 44 über ein Nadellager 48 in einem Ende angelenkt. In gleicher Weise ist der Lenker 44 an der Schwinge 32 angelenkt. Der Abstand der Achse 50 um welche der Lenker 44 an der Schwinge 34 schwenkbar angelenkt ist, von der Achse 36 der zweiten Welle 22 ist der gleiche wie der Abstand der Achse 52, um die der Lenker 44 an der ersten Schwinge 32 schwenkbar angelenkt ist, von der Achse 33 der ersten Unwuchtwelle 12. Die effektive Länge des Lenkers 44, d. h. der Abstand der Achsen 50 und 52 ist gleich dem Abstand der Achsen 33 und 36 der Unwuchtwellen 12 bzw. 22 voneinander. Dadurch wird erreicht, daß die Achsen 33, 36, 50 und 52 stets die Ecken eines Parallelogramms bilden und die Schwingen 32 und 34 immer zueinander parallel verlaufen.A first rocker 32 is pivotally mounted about the axis 33 of the first unbalanced shaft 12. A second rocker 34 is pivotally mounted about the axis 36 of the second unbalanced shaft 22. As can best be seen from FIG. 2, the rocker 34 consists of two halves 34A and 34B which are mounted on the second shaft 22 via ball bearings 38 and 40 on both sides of the gearwheel 30 and by a pin 42 at a distance from the second shaft 22 are connected. The rocker arm 32 is mounted on the first shaft 12 in a similar manner. A link 44 is articulated on the first and second rocker arms 32 and 34. A bolt 46 extends between the two parts 34A and 34B of the rocker 34. On this bolt 46, the link 44 is articulated between these parts 34A and 34B via a needle bearing 48 in one end. In the same way, the link 44 is articulated on the rocker 32. The distance of the axis 50 about which the link 44 is pivotally articulated on the rocker 34 from the axis 36 of the second shaft 22 is the same as the distance of the axis 52 about which the link 44 is pivotally articulated on the first rocker 32, from the axis 33 of the first unbalanced shaft 12. The effective length of the link 44, i. H. the distance between the axes 50 and 52 is equal to the distance between the axes 33 and 36 of the unbalanced shafts 12 and 22, respectively. It is thereby achieved that the axes 33, 36, 50 and 52 always form the corners of a parallelogram and the rockers 32 and 34 always run parallel to one another.

Ein erstes Zwischenzahnrad 54 ist an der ersten Schwinge 32 im Abstand von der Achse 33 der ersten Unwuchtwelle 12 drehbar gelagert. Das erste Zwischenzahnrad 54 ist in Eingriff mit dem ersten Zahnrad 18. Ein zweites Zwischenzahnrad 56 ist an der zweiten Schwinge 34 in dem gleichen Abstand von der Achse 36 der zweiten Unwuchtwelle 22 drehbar gelagert, den das erste Zwischenzahnrad 54 von der Achse 33 der ersten Unwuchtwelle 12 hat. Wie aus Figur 2 ersichtlich ist, ist das zweite Zwischenzahnrad 56 auf dem Zapfen 42 über ein Nadellager 58 drehbar gelagert. Das erste Zwischenzahnrad 54 ist in gleicher Weise an der Schwinge 32 gelagert. Das zweite Zwischenzahnrad 54 ist mit dem zweiten Zahnrad 30 in Eingriff. Es ist außerdem, wie aus Figur 1 ersichtlich ist, mit dem ersten Zwischenzahnrad 54 in Eingriff. Dadurch wird die zweite Unwuchtwelle 22 von der ersten Unwuchtwelle 12 über das Zahnrad 18, erste Zwischenzahnrad 54, das zweite Zahnrad 56 und das zweite Zahnrad 30 angetrieben, und zwar gegensinnig zu der Unwuchtwelle 12.A first intermediate gear 54 is rotatably mounted on the first rocker 32 at a distance from the axis 33 of the first unbalanced shaft 12. The first idler gear 54 is engaged with the first gear 18. A second idler gear 56 is rotatably supported on the second rocker 34 at the same distance from the axis 36 of the second imbalance shaft 22 that the first idler gear 54 is from the axis 33 of the first imbalance shaft 12 has. As can be seen from Figure 2, the second intermediate gear 56 is rotatably mounted on the pin 42 via a needle bearing 58. The first intermediate gear 54 is mounted on the rocker 32 in the same way. The second intermediate gear 54 is engaged with the second gear 30. 1, it is also in engagement with the first intermediate gear 54. As a result, the second unbalanced shaft 22 is driven by the first unbalanced shaft 12 via the gear 18, the first intermediate gear 54, the second gear 56 and the second gear 30, in opposite directions to the unbalanced shaft 12.

Durch einen noch zu beschreibenden Verstellmechanismus 60 sind die beiden Schwingen 32 und 34 verschwenkbar.The two rockers 32 and 34 can be pivoted by means of an adjusting mechanism 60, which will be described later.

Wie aus Figur 1 und 2 ersichtlich ist, weist jede der Schwingen 32 und 34 auf der dem Zwischenzahnrad 54 bzw. 56 in bezug auf die Achse 33 bzw. 36 der Unwuchtwelle 12 bzw. 22 gegenüberliegenden Seite ein Gegengewicht 62 bzw. 64 auf. Durch die Gegengewichte ist jede der Schwingen 32 und 34 in' bezug auf ihre Schwenkachse, nämlich die Achse 33 bzw. 36 masseausgeglichen.As can be seen from FIGS. 1 and 2, each of the rockers 32 and 34 has a counterweight 62 and 64 on the side opposite the intermediate gear 54 and 56 with respect to the axis 33 and 36 of the unbalanced shaft 12 and 22, respectively. Due to the counterweights, each of the rockers 32 and 34 is' balanced with respect to its pivot axis, namely the axes 33 and 36, respectively.

Bei der dargestellten Ausführung ist der Lenker 44 auf der den Zwischenzahnrädern 54 und 56 in bezug auf die Achsen 33 bzw. 36 der Unwuchtwellen 12 bzw. 22 gegenüberliegenden Seite an den Schwingen 32 bzw. 34 angelenkt.In the embodiment shown, the link 44 is articulated on the rocker arms 32 and 34 on the side opposite the intermediate gears 54 and 56 with respect to the axes 33 and 36 of the unbalanced shafts 12 and 22, respectively.

Der Verstellmechanismus 60 enthält ein Zahnsegment 66, daß an einer der Schwingen, bei dem dargestellten, bevorzugten Ausführungsbeispiel an der zweiten Schwinge 34 angebracht ist. Das Zahnsegment 66 ist um die Achse 36 der zugehörigen Unwuchtwelle 22 gekrümmt. Eine Zahnstange 68 ist in Buchsen 70, 72 im Gehäuse 10 längsverschiebbar geführt und mit dem Zahnsegment 66 in Eingriff. Die Zahnstange 68 ist durch Bewegungsübertragungsmittel verstellbar, die bei dem dargestellten, bevorzugten Ausführungsbeispiel von einem Bowdenzug 74 gebildet werden.The adjustment mechanism 60 includes a toothed segment 66 that is attached to one of the rockers, in the preferred embodiment shown, to the second rocker 34. The toothed segment 66 is curved about the axis 36 of the associated unbalanced shaft 22. A toothed rack 68 is guided in longitudinally displaceable fashion in bushings 70, 72 and engages with the toothed segment 66. The rack 68 is adjustable by means of movement transmission means, which in the preferred exemplary embodiment shown are formed by a Bowden cable 74.

Dadurch, daß die Schwingen 32 und 34 masseausgeglichen sind und dadurch die geschilderten Schwingungen vermieden werden, kann für die Verstellung ein relativ leichter Verstellmechanismus mit einem Bowdenzug 74 verwendet werden.Because the rockers 32 and 34 are balanced and the described vibrations are avoided, a relatively light adjustment mechanism with a Bowden cable 74 can be used for the adjustment.

Claims (4)

1. Flyweight vibrator designed as directional vibrator with the direction of oscillation being adjustable, comprising
(a) a housing (10)
(b) a first flyweight shaft (12), which
(b1) is mounted in the housing (10),
(b2) carries a first flyweight (16),
(b3) is connected to a first gear (18) and
(b4) is adapted to be driven by a motor,
(c) a second flyweight shaft (22), which
(c1) is mounted in the housing (10) parallel to the first flyweight shaft (12),
(C2) carries a second flyweight (28) and
(C3) is connected to a second gear (30),
(d) a first oscillating crank (32) pivotably mounted about the axis (33) of the first flyweight shaft (12),
(e) a second oscillating crank (34) mounted for pivoting about the axis (36) of the second flyweight shaft (22),
(f) a connecting rod (44)
(f1) which is coupled to the first and the second oscillating crank (32, 34) at equal distances from the axes (33, 36) of the associated flyweight shafts (12, 22) and
(f2) the effective length of which is equal to the distance of these axes (33, 36) from each other,
(g) a first intermediate gear (54), which
(g1) is mounted for rotation on the first oscillating crank (32) at a distance from the axis (33) of the first flyweight shaft (12) and
(g2) meshes with the first gear (18),
(h) a second intermediate gear (56), which
(hj) is mounted for rotation on the second oscillating crank (34) at a distances from the axis (36) of the second flyweight shaft (22) equal to the distance of the first intermediate gear (54) from the axis (33) of the first flyweight shaft (12),
(h2) meshes with the second gear (30) and
(h3) meshes with the first intermediate gear (54) and
(i) a shifting mechanism (60) arranged to rotate the two oscillating cranks characterized in that
(j) each of the oscillating cranks (32, 34) has a counterweight (62, 64) on the side opposite the intermediate gear (54, 56) with respect to the axis (33, 36) of the flyweight shaft (12, 22).
2. Flyweight vibrator as set forth in claim 1, characterized in that the connecting rod (44) is mounted on the oscillating cranks on the side opposite the intermediate gears (54, 56) with respect to the axes (33, 36) of the flyweight shafts (12, 22).
3. Flyweight vibrator as set forth in claim 1 or 2, characterized in that the shifting mechanism (60)
(a) comprises a toothed segment (66)
(a1) attached to one of the oscillating cranks (34) and
(a2) curved about the axis (36) of the associated flyweight shaft (22), as well as
(b) a rack (68), which
(b1) is longitudinally movably guided in the housing (10) and
(b2) engages the toothed segment (66) and
(c) motion transfer means (74) by means of which the rack (68) is adjustable.
4. Flyweight vibrator as set forth in claim 3, characterized in that the motion transfer means (74) are formed by a Bowden cable.
EP81710026A 1981-07-18 1981-07-18 Directional vibrator Expired EP0070344B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE8181710026T DE3169038D1 (en) 1981-07-18 1981-07-18 Directional vibrator
AT81710026T ATE11879T1 (en) 1981-07-18 1981-07-18 IMBALANCE VIBRATOR TRAINED AS AN ANGLER.
EP81710026A EP0070344B1 (en) 1981-07-18 1981-07-18 Directional vibrator
US06/394,717 US4510815A (en) 1981-07-18 1982-07-02 Flyweight vibrator designed as directional vibrator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81710026A EP0070344B1 (en) 1981-07-18 1981-07-18 Directional vibrator

Publications (2)

Publication Number Publication Date
EP0070344A1 EP0070344A1 (en) 1983-01-26
EP0070344B1 true EP0070344B1 (en) 1985-02-20

Family

ID=8188619

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81710026A Expired EP0070344B1 (en) 1981-07-18 1981-07-18 Directional vibrator

Country Status (4)

Country Link
US (1) US4510815A (en)
EP (1) EP0070344B1 (en)
AT (1) ATE11879T1 (en)
DE (1) DE3169038D1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3709112C1 (en) * 1986-08-27 1988-01-28 Knauer Maschf Gmbh Vibrating device for a concrete block molding machine

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3639803A1 (en) * 1986-11-21 1988-05-26 Kloeckner Humboldt Deutz Ag Two-roller machine, in particular roller press having two rotatably mounted, contra-rotating rollers
US5064053A (en) * 1990-10-24 1991-11-12 Carrier Vibrating Equipment, Inc. Vibratory drive system for a vibratory conveyor apparatus and a conveyor apparatus having same
US5584375A (en) * 1994-12-21 1996-12-17 Food Engineering Corporation Single drive vibrational conveyor with vibrational motion altering phase control and method of determining optimal conveyance speeds therewith
US6837648B1 (en) * 2004-05-27 2005-01-04 Theodore S. Wadensten Portable roller-type compactor apparatus having a combined means for the vibrating and the reversible propelling thereof
EP2257674B1 (en) * 2008-02-29 2017-07-26 Tennant Company Filter shaker assembly for sweeping machine
US9038236B2 (en) 2012-04-25 2015-05-26 Shop Vac Corporation Filter shaker

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA708737A (en) * 1965-05-04 Pavlovich Tatarnikov Boris Vibrating machine for sinking piles, thin-walled cylindrical casings and plates
US1145445A (en) * 1915-03-16 1915-07-06 Henry M Stewart Mechanical movement.
US2144382A (en) * 1936-04-09 1939-01-17 Allis Chalmers Mfg Co Low head vibrating screen
CH241986A (en) * 1942-05-01 1946-04-15 Goditiabois Auguste Vibration generator device.
US2512304A (en) * 1945-03-15 1950-06-20 Calver Cyril Maurice Grahame Vibrating table
US2445175A (en) * 1947-06-13 1948-07-13 Jeffrey Mfg Co Variable throw vibratory head for screens, conveyers, and the like
US2677995A (en) * 1948-11-05 1954-05-11 Clyde W Wood Vibratory earthworking roller
US3056306A (en) * 1959-04-25 1962-10-02 Muller Ludwig Exciter assembly for vibratory devices
US3280924A (en) * 1961-03-13 1966-10-25 Pavlovich Tatarnikov Boris Vibrating machine for plunging piles, thin-walled clindrical casings and plates
DE1291152B (en) * 1967-05-27 1969-03-20 Delmag Maschinenfabrik Device for changing the phase position of two unbalances
FR1565988A (en) * 1967-05-27 1969-05-02
US3433311A (en) * 1967-05-31 1969-03-18 Lebelle Jean L Pile driver and extractor with rotating eccentric masses of variable weights
US4033193A (en) * 1974-03-04 1977-07-05 International Combustion Australia Limited Vibratory drive unit
SU620284A1 (en) * 1975-11-24 1978-08-25 Предприятие П/Я М-5703 Inertia vibrator
JPS5584706A (en) * 1978-12-15 1980-06-26 Shinko Electric Co Ltd Vibration conveyor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3709112C1 (en) * 1986-08-27 1988-01-28 Knauer Maschf Gmbh Vibrating device for a concrete block molding machine

Also Published As

Publication number Publication date
ATE11879T1 (en) 1985-03-15
DE3169038D1 (en) 1985-03-28
EP0070344A1 (en) 1983-01-26
US4510815A (en) 1985-04-16

Similar Documents

Publication Publication Date Title
DE19631849C1 (en) Vibration drive for a screening machine
DE2512012A1 (en) DEVICE FOR CONVERTING A ROTATING MOTION INTO A BACK AND BACK MOTION, IN PARTICULAR KNIFE DRIVE FOR A MAWING PLANT
EP0070344B1 (en) Directional vibrator
DE1652192C3 (en) Device for generating a pivoting movement of the workpiece or tool holder of a spectacle lens grinding machine
CH677202A5 (en)
DE2829587A1 (en) DRIVE DEVICE FOR GENERATING AN ELLIPTICAL VIBRATION
DE1758226A1 (en) Unbalance rioters
EP2363212B1 (en) Continuously adjustable vibration generator
DE3418268A1 (en) VIBRATION DEVICE, ESPECIALLY FOR SOIL COMPRESSION DEVICES
DE4108131C2 (en) Cutting head
DE3026841C2 (en) Tamping device for a track tamping machine
DE3226942A1 (en) Vibrating machine
DE4430201C2 (en) Mechanical press
DE3206710C2 (en) Vibration plate for compacting the soil
DE2648950C2 (en) Readout device for granular material
DE1930078A1 (en) Vibration generator
DE868100C (en) Drive device for the knife gate valve
DE2251814B2 (en) RIBBON FOR THE PROCESSING OF SCHUETTGUT
DE2809111C2 (en) Self-propelled vibratory compactor
DE2927241C2 (en) Mechanical vibrator with directional effect
DE3727742C1 (en) Schuettelbock
DE837389C (en) Road roller
DE4138476C1 (en) Mass equaliser for flat screening machines - has eccentric drive firmly coupled to main frame, or foundation, also contg. equalising weight
EP0582872A1 (en) Belt gear
EP0070342A1 (en) Vibrator

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT DE SE

RBV Designated contracting states (corrected)

Designated state(s): AT DE SE

17P Request for examination filed

Effective date: 19830406

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT DE SE

REF Corresponds to:

Ref document number: 11879

Country of ref document: AT

Date of ref document: 19850315

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3169038

Country of ref document: DE

Date of ref document: 19850328

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19860714

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19880718

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19940731

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19940922

Year of fee payment: 14

EAL Se: european patent in force in sweden

Ref document number: 81710026.6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19950719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19960402

EUG Se: european patent has lapsed

Ref document number: 81710026.6