EP0037428B1 - Unbalanced-mass vibrator with switching clutch - Google Patents

Unbalanced-mass vibrator with switching clutch Download PDF

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Publication number
EP0037428B1
EP0037428B1 EP80101838A EP80101838A EP0037428B1 EP 0037428 B1 EP0037428 B1 EP 0037428B1 EP 80101838 A EP80101838 A EP 80101838A EP 80101838 A EP80101838 A EP 80101838A EP 0037428 B1 EP0037428 B1 EP 0037428B1
Authority
EP
European Patent Office
Prior art keywords
unbalance
gear
shaft
arm
lever
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
EP80101838A
Other languages
German (de)
French (fr)
Other versions
EP0037428A1 (en
Inventor
Hans-Georg Waschulewski
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 EP80101838A priority Critical patent/EP0037428B1/en
Priority to AT80101838T priority patent/ATE3452T1/en
Priority to DE8080101838T priority patent/DE3063259D1/en
Priority to US06/239,698 priority patent/US4440034A/en
Publication of EP0037428A1 publication Critical patent/EP0037428A1/en
Application granted granted Critical
Publication of EP0037428B1 publication Critical patent/EP0037428B1/en
Expired legal-status Critical Current

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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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
    • E02D3/074—Vibrating apparatus operating with systems involving rotary 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
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18344—Unbalanced weights

Definitions

  • An unbalance shaker of this type is known (DE-C-1 015275), in which a gearwheel provided with stops on the opposite end faces can be axially pushed back and forth between two disks seated on the unbalance shaft.
  • the gearwheel engages with another gearwheel which is firmly seated on an unbalanced shaft parallel to the former.
  • the disks carry drivers on the inner end faces facing the gearwheel, which come to rest against the stops either on one side or - offset at an angle - on the other side of the gearwheel. By switching the gear back and forth, the angle is adjusted step by step.
  • the unbalance shafts are adjusted in relation to one another and thus the direction of the vibrations caused by the counterbalance unbalance in steps by repeated switching back and forth.
  • the switching position of the switching element causing the displacement of the gear wheel therefore does not provide a clear indication of the respectively set angular position of the unbalanced shafts.
  • an unbalance shaker with clutch in which stops are provided in a gear housing located on the gear wheel.
  • the clutch includes an axially displaceable shift ring with a driver, which cooperate with two stops offset by 180 ° inside the shift housing and couple the gearwheel to the shaft.
  • inclined surfaces are arranged which interact with the cams of the switching ring.
  • the clutch is triggered by axially moving the shift ring and thus disengaging the driver from one stop.
  • the driven part now remains.
  • the switching ring is pushed back before passing the next stop, and the driver rests against the stop that is offset by 180 °.
  • the switching ring is moved back and forth with every switching operation. This back and forth movement increases wear.
  • the construction is complicated.
  • the switch position is not recognizable from the outside either.
  • the shifting ring may only be axially displaced for a short time and must be able to be pushed back freely for proper operation immediately after the clutch is disengaged. The power is transmitted to the side of the gear.
  • the invention has for its object to form a clutch of the type defined in such a way that the meshing gears can have the same width and an axial displacement of one gear against another meshing with it is avoided, the switching state is recognizable on the actuator and the impulse that occurs when the driving device strikes the lifting gear after the switching process is kept away from the switching mechanism.
  • the entrainment device is formed by a lever which is mounted on the unbalanced shaft so as to be pivotable about a pivot axis running transversely to the rotational axis of the unbalanced shaft.
  • the pivot lever is supported on the unbalanced shaft by means of the pivot bearing on a relatively long lever arm with respect to the transmitted torque.
  • This swivel bearing absorbs the impulse.
  • the switching mechanism acting in the plane of the pivoting movement is not influenced by the impact impulse.
  • the gears can be axially fixed and of the same width. The switching status is immediately recognizable on the actuator.
  • the stop can be provided directly on the gear and not far from its center plane. The entire arrangement can be made simple and space-saving.
  • 10 denotes a vibrator housing.
  • an unbalance 20 is supported by means of an unbalanced shaft 22 via roller bearings 16, 18, which in the exemplary embodiment shown is formed by two aligned shaft ends 24 and 26.
  • a similar unbalance (not shown) is mounted in the vibrator housing 10 with an unbalanced shaft 28 parallel to the unbalanced shaft 22.
  • gears 30 and 32 On the unbalanced shafts 22 and 28 there are gears 30 and 32, which are in engagement with each other.
  • the gear 30 is rotatably supported on the stub shaft 26 of the unbalanced shaft 22 via a slide bearing 34, while the gear 32 is fixedly connected to the unbalanced shaft 28.
  • the gear 30 can be coupled to the unbalanced shaft 22 via a clutch 36.
  • the clutch 36 includes a stop 38 which sits on the outer end face of the gear 30.
  • a double-armed lever 40 is mounted with a shaft 42 so as to be pivotable about a pivot axis 46 running transversely to the axis of rotation 44 of the unbalanced shaft 22.
  • the double-armed lever 40 is movable between two end positions. In the first end position, it comes to rest against the stop 38 with one arm 48 and in the second end position with the other arm 50.
  • the shaft 42 is mounted in bearing bushes 52 which are seated in bearing blocks 54, 56 which are fastened to the end face of the shaft end 26 by screws 58.
  • the unbalance shaft 22 is coupled to the gearwheel 30 in one position or in another position that is essentially offset by 180 ° . Since the gearwheel 30 engages with the gearwheel 32 on the other unbalanced shaft 28, the relative angular position of the counterbalanced unbalance changes and thus the resulting direction of oscillation.
  • one angular position corresponds to a forward movement of the device, while the other angular position leads to a backward movement.
  • the mass distribution of the double-armed lever 40 is so asymmetrical that the centrifugal force exerts a torque about the pivot axis 46 on the double-armed lever, which attempts to pivot the lever clockwise in FIG. 1 into a first position.
  • a switching device for actuating the clutch includes a Bowden cable 60, via which a force can be exerted on the double-armed lever 40 to generate a torque which counteracts the torque caused by the centrifugal force.
  • a rod 64 is axially displaceable in the shaft end 26 by means of a bearing bush 62. On the rod 64 sits a Z-shaped projection 66 which engages behind a nose 68 provided on the arm 48 of the double-armed lever 40 and at the same time can be placed against the inside of the arm 48 facing the gearwheel 30.
  • the latter is mounted in a housing 74 via an axially loadable ball bearing 72.
  • a pulling force can be exerted by the housing 74 onto the rod 64 from the housing 74 via a disk 76 which is seated on the rod 64 and which lies on the inside against the inner ring of the ball bearing 72 will.
  • the end wall 78 of the housing 74 opposite the ball bearing 74 is connected to the core 80 of the Bowden cable 60.
  • the Bowden cable 60 is passed through an axial bore 82 of the shaft end 24 and is supported there in a ball bearing 84. The non-rotating Bowden cable 60 is then guided out of the side of the vibrator housing 10.
  • the arm 50 In each end position of the double-armed lever 40, the arm lifted off the gearwheel 30, in the illustration of FIG. 1, the arm 50, with its rear side 86 facing away from the gearwheel 30, brakes against a brake surface 88 fixed to the housing.
  • a wedge-shaped cam 90 is provided on the end face of the gearwheel, by means of which, just before the arm 48 inclined towards the gearwheel 30 bears against the stop 38, this arm 48 can be pivoted back so far that the other arm 50 is lifted off the braking surface 88.
  • the double-armed lever 40 when the double-armed lever 40 is switched over, the arm 48 first comes into contact with the braking surface 88, before this arm is pivoted back shortly before the arm 50 abuts the stop 38 and the arm 48 is thus lifted off the braking surface.
  • the double-armed lever 40 preferably has a brake lining 92 on its rear side 86 facing away from the gearwheel 30.
  • This switching position advantageously corresponds to the direction of travel “forward” of a soil compactor provided with the unbalance shaker. This ensures that, in any case, even if the core 80 breaks, the unbalance shaker goes into the "forward" switch position.
  • the housing 74 is pulled to the left via the Bowden cable 60. This moves the rod 64 to the left. About the Z-shaped projection 66 and the nose 68, the double-armed lever 40 is pivoted counterclockwise, so that the arm 50 comes out of engagement with the stop 38 and, as shown in Fig. 1, the lever 48 in the path of the stop 38 arrives.
  • the brakes are temporarily braked via the brake lining 86 and the braking surface 88 until the arm 48 is pivoted back by the cam 90.
  • FIG. 3 A modified embodiment is shown in Fig. 3.
  • the basic structure of the unbalance vibrator and the switching device is the same as in the embodiment according to FIG. 1, and corresponding parts are provided with the same reference numerals as there.
  • the gearwheel 30 is fastened as a ring on the lateral surface of an annular, inwardly open housing 94 approximately in the central plane 96 thereof.
  • the housing 94 is in turn rotatably supported on the unbalanced shaft 22.
  • the housing 94 has axially and along the circumference angularly offset stops on the inside, and preferably more than two stops 98, 100, 102.
  • the lever here is a one-armed lever 104, which is pivotably mounted in a recess 106 in the unbalanced shaft 22 about a pivot axis 108 extending in the central plane 96 of the housing 94 perpendicular to the axis 44 of the unbalanced shaft 22 by means of a shaft 110.
  • the pivot lever 104 is connected to a radial shoulder 112 seated on the rod 64 via a link 114. With an axial movement of the rod 64 under the influence of the Bowden cable 60, the lever 104 is pivoted and successively comes into the path of the stops 102, 100 or 98, against which it comes into contact at different angular positions between the gear 30 and the shaft 22.
  • the switching device with the Bowden cable 60 preferably contains a number of latching positions corresponding to the number of stops 98, 100, 102, the lever 104 coming to rest on one of the stops in each latching position.
  • the arrangement described allows the setting of several relative angular positions between the gear 30 and the unbalanced shaft 22, which can correspond, for example, to the “forward”, “stand vibration” and “backward” operating modes.
  • the respective switching positions can be clearly recognized from the position of the switching mechanism.
  • the lever 104 engages closer to the center line 96 of the gearwheel 30, so that lower tilting moments become effective during the power transmission.

Abstract

An eccentric vibrating machine which includes parallel shafts each carrying an eccentric mass. A gear rotatably journalled on a first of the shafts is drivingly connected to the second shaft for mutual rotation of the gear and second shaft. A shifting coupling is mounted on the first shaft and is selectively engageable with the gear at multiple angular positions around the gear to couple the first shaft to the gear and thereby selectively vary the phase angle relationship of the eccentric masses carried on the two shafts. A manual shifting control device is carried on the first shaft, and can be manually actuated to selectively engage the shifting coupling with the gear.

Description

Die Erfindung betrifft einen Unwuchtrüttler, insbesondere für Bodenverdichter mit umsteuerbarer Marschrichtung, mit zwei gegenläufigen Unwuchtwellen, deren eine in ihrer Phasenlage gegenüber der anderen durch eine Schaltkupplung verstellbar ist, enthaltend eine erste Unwucht auf einer von einem Antriebsmotor angetriebenen Unwuchtwelle, eine zweite Unwucht auf einer zu dieser Unwuchtwelle parallelen Unwuchtwelle, ein erstes Zahnrad, das mit einer der Unwuchtwellen fest verbunden ist, ein zweites Zahnrad, das mit dem ersten Zahnrad in Eingriff und drehbar auf der anderen Unwuchtwelle gelagert ist und eine bei wenigstens zwei verschiedenen Winkellagen kuppelnde Schaltkupplung zwischen dem zweiten Zahnrad und der zugehörigen anderen Unwuchtwelle, wobei diese Schaltkupplung folgende Bauteile enthält:

  • Anschlagmittel an dem Zahnrad, eine mit der Unwuchtwelle umlaufende Mitnahmeeinrichtung, die zwischen einer ersten und einer zweiten Stellung beweglich ist und in der ersten Stellung bei einer Winkellage und in der zweiten Stellung bei einer anderen Winkellage mit den Anschlagmitteln zur Herstellung einer Antriebsverbindung zwischen Zahnrad und Unwuchtwelle zusammenwirkt, und eine Schaltvorrichtung durch welche die Mitnahmeeinrichtung zwischen der ersten und der zweiten Stellung schaltbar ist.
The invention relates to an unbalance shaker, in particular for soil compactors with a reversible direction of travel, with two counterbalance unbalanced shafts, one of which can be adjusted in phase with respect to the other by a clutch, containing a first unbalance on an unbalanced shaft driven by a drive motor and a second unbalance on one this unbalanced shaft parallel unbalanced shaft, a first gear which is fixedly connected to one of the unbalanced shafts, a second gear which is in engagement with the first gear and rotatably mounted on the other unbalanced shaft and a clutch which couples at least two different angular positions between the second gear and the associated other unbalanced shaft, this clutch includes the following components:
  • Sling means on the gear wheel, a driving device rotating with the unbalanced shaft, which is movable between a first and a second position and in the first position with an angular position and in the second position with a different angular position with the stop means for establishing a drive connection between the gear wheel and the unbalanced shaft cooperates, and a switching device through which the driver device can be switched between the first and the second position.

Es ist ein Unwuchtrüttler dieser Art bekannt (DE-C-1 015275), bei welchem ein auf den gegenüberliegenden Stirnseiten mit Anschlägen versehenes Zahnrad zwischen zwei auf der Unwuchtwelle sitzenden Scheiben axial hin- und herverschiebbar ist. Das Zahnrad ist mit einem weiteren Zahnrad in Eingriff, das fest auf einer zu der ersteren parallele Unwuchtwelle sitzt. Die Scheiben tragen auf den inneren, dem Zahnrad zugewandten Stirnflächen Mitnehmer, die an den Anschlägen entweder auf der einen oder - winkelversetzt - auf der anderen Seite des Zahnrads zur Anlage kommen. Durch Hin- und Herschalten des Zahnrads erfolgt eine schrittweise Winkelverstellung.An unbalance shaker of this type is known (DE-C-1 015275), in which a gearwheel provided with stops on the opposite end faces can be axially pushed back and forth between two disks seated on the unbalance shaft. The gearwheel engages with another gearwheel which is firmly seated on an unbalanced shaft parallel to the former. The disks carry drivers on the inner end faces facing the gearwheel, which come to rest against the stops either on one side or - offset at an angle - on the other side of the gearwheel. By switching the gear back and forth, the angle is adjusted step by step.

Diese bekannte Anordnung hat verschiedene Nachteile:This known arrangement has several disadvantages:

Die Verstellung der Unwuchtwellen zueinander und damit der Richtung der durch die gegenläufigen Unwuchten hervorgerufenen Schwingungen erfolgt in Schritten durch wiederholtes Hin- und Herschalten. Die Schaltstellung des die Verschiebung des Zahnrads bewirkenden Schaltgliedes liefert daher keine eindeutige Anzeige für die jeweils eingestellte Winkelstellung der Unwuchtwellen.The unbalance shafts are adjusted in relation to one another and thus the direction of the vibrations caused by the counterbalance unbalance in steps by repeated switching back and forth. The switching position of the switching element causing the displacement of the gear wheel therefore does not provide a clear indication of the respectively set angular position of the unbalanced shafts.

Es ist weiterhin erforderlich, ein drehmoment- übertragendes Zahnrad axial hin- und herzuschieben. Dabei muss das mit dem verschiebbaren Zahnrad in Eingriff stehende Zahnrad auf der anderen Welle eine die Verschiebung zulassende Breite besitzen. Beiderseits des verschiebbaren Zahnrads sitzen auf der Unwuchtwelle die Scheiben mit den Mitnehmern. Hierdurch wird die Schaltkupplung aufwendig und die axialen Abmessungen der Schaltkupplung werden unerwünscht gross.It is also necessary to move a torque-transmitting gear axially back and forth. The gearwheel which is in engagement with the displaceable gearwheel on the other shaft must have a width which permits the displacement. The disks with the drivers sit on both sides of the sliding gear on the unbalanced shaft. As a result, the clutch is complex and the axial dimensions of the clutch are undesirably large.

Bei einem nach dem Prinzip der DE-C-1 015 275 arbeitenden, offenkundig vorbenutzten Bodenverdichter (Losenhausen ATN 2000) sind nur zwei Winkelstellungen vorgesehen, bei denen das Zahnrad entweder mit der einen oder mit der anderen Scheibe kuppelt. Damit ist jeder Winkelstellung «Vorwärts» oder «Rückwärts» eine eindeutige Axiallage des verschiebbaren Zahnrads und damit eine eindeutige Schaltstellung des die Verschiebung des Zahnrads bewirkenden Schaltmechanismus zugeordnet. Aus der Stellung des Schaltmechanismus kann daher eindeutig auf die Schwingungsrichtung geschlossen werden. Bei diesem bekannten Gerät entfällt daher der eine Nachteil der Anordnung nach DE-C-1 015275. Die übrigen vorstehend diskutierten Nachteile dieser Anordnung bleiben jedoch bestehen.In a obviously pre-used soil compactor (Losenhausen ATN 2000) which works according to the principle of DE-C-1 015 275, only two angular positions are provided in which the gearwheel couples either with one or the other disk. Each angular position "forward" or "backward" is thus assigned a unique axial position of the displaceable gearwheel and thus a unique switching position of the switching mechanism which effects the displacement of the gearwheel. From the position of the switching mechanism, the direction of vibration can therefore be clearly concluded. In this known device there is therefore no disadvantage of the arrangement according to DE-C-1 015275. However, the other disadvantages of this arrangement discussed above remain.

Durch die DE-C-1 484588 ist ein Unwuchtrüttler mit Schaltkupplung bekannt, bei welchem in einem an dem Zahnrad sitzenden Schaltgehäuse Anschläge vorgesehen sind. Die Schaltkupplung enthält einen axial auf der Welle verschiebbaren Schaltring mit einem Mitnehmer, die mit zwei um 180° versetzten Anschlägen im Inneren des Schaltgehäuses zusammenwirken und das Zahnrad mit der Welle kuppeln. Auf der den Anschlägen gegenüberliegenden Stirnfläche des Zahnrads sind Schrägflächen angeordnet, die mit Auflaufnocken des Schaltrings zusammenwirken.From DE-C-1 484588 an unbalance shaker with clutch is known, in which stops are provided in a gear housing located on the gear wheel. The clutch includes an axially displaceable shift ring with a driver, which cooperate with two stops offset by 180 ° inside the shift housing and couple the gearwheel to the shaft. On the end face of the gearwheel opposite the stops, inclined surfaces are arranged which interact with the cams of the switching ring.

Die Schaltkupplung wird ausgelöst, indem der Schaltring axial bewegt und damit der Mitnehmer ausser Eingriff mit dem einen Anschlag gebracht wird. Der getriebene Teil bleibt jetzt zurück. Bei Erreichen der Schrägflächen wird der Schaltring vor Passieren des nächsten Anschlags zurückgeschoben, und der Mitnehmer legt sich an den um 180° versetzten Anschlag an.The clutch is triggered by axially moving the shift ring and thus disengaging the driver from one stop. The driven part now remains. When the inclined surfaces are reached, the switching ring is pushed back before passing the next stop, and the driver rests against the stop that is offset by 180 °.

Diese bekannte Anordnung hat ebenfalls verschiedene Nachteile:This known arrangement also has several disadvantages:

Der Schaltring wird bei jedem Schaltvorgang hin- und herbewegt. Diese Hin- und Herbewegung erhöht den Verschleiss. Die Konstruktion ist kompliziert. Auch dort ist die Schaltstellung von aussen nicht erkennbar. Der Schaltring darf nur kurzzeitig axial verschoben und muss für eine einwandfreie Arbeitsweise sofort nach dem Ausrücken der Kupplung wieder frei zurückschiebbar sein. Die Kraftübertragung erfolgt stark seitlich von dem Zahnrad.The switching ring is moved back and forth with every switching operation. This back and forth movement increases wear. The construction is complicated. The switch position is not recognizable from the outside either. The shifting ring may only be axially displaced for a short time and must be able to be pushed back freely for proper operation immediately after the clutch is disengaged. The power is transmitted to the side of the gear.

Durch die DE-A-2008055 oder die DE-A-2802648 ist ein Unwuchtrüttler mit Schaltkupplung bekannt, bei welchem an dem Zahnrad in einem seitlich davon angeordneten und mit dem Zahnrad verbundenen Schaltgehäuse axial gegeneinander versetzte Anschläge angeordnet sind. Ein radialer Mitnehmer sitzt an einem in der Welle geführten Schaltbolzen und ragt durch ein Fenster der Welle. Dieser Mitnehmer wird entweder in die Ebene des einen oder des anderen Anschlags bewegt.From DE-A-2008055 or DE-A-2802648 an unbalance shaker with clutch is known, in which axially offset stops are arranged on the gearwheel in a switch housing arranged laterally and connected to the gearwheel. A radial driver sits on a switching pin guided in the shaft and protrudes through a window of the shaft. This driver will either that moves into the plane of one or the other stop.

Bei dieser Anordnung wird der nach dem Ausrücken der Kupplung beim Auftreffen des radialen Mitnehmers an dem nächsten Anschlag auftretende Auftreffimpuls unmittelbar an dem Schaltmechanismus, nämlich dem Schaltbolzen wirksam.With this arrangement, the impact pulse occurring after the clutch disengages when the radial driver hits the next stop acts directly on the switching mechanism, namely the switching pin.

Der Erfindung liegt die Aufgabe zugrunde, eine Schaltkupplung der eingangs definierten Art so auszubilden, dass die in Eingriff befindlichen Zahnräder gleiche Breite haben können und eine Axialverschiebung eines Zahnrades gegen ein damit kämmendes anderes vermieden wird, der Schaltzustand am Stellglied erkennbar ist und der Auftreffimpuls, der beim Anschlagen der Mitnahmeeinrichtung an das Anschlagmittel nach dem Schaltvorgang auftritt, von dem Schaltmechanismus ferngehalten ist.The invention has for its object to form a clutch of the type defined in such a way that the meshing gears can have the same width and an axial displacement of one gear against another meshing with it is avoided, the switching state is recognizable on the actuator and the impulse that occurs when the driving device strikes the lifting gear after the switching process is kept away from the switching mechanism.

Erfindungsgemäss wird diese Aufgabe dadurch gelöst, dass die Mitnahmeeinrichtung von einem Hebel gebildet ist, der an der Unwuchtwelle um eine quer zur Umlaufachse der Unwuchtwelle verlaufende Schwenkachse schwenkbar gelagert ist.According to the invention, this object is achieved in that the entrainment device is formed by a lever which is mounted on the unbalanced shaft so as to be pivotable about a pivot axis running transversely to the rotational axis of the unbalanced shaft.

Bei einer solchen Anordnung wird der Schwenkhebel an der Unwuchtwelle über die Schwenklagerung an einem relativ langen Hebelarm gegenüber dem übertragenen Drehmoment abgestützt. Diese Schwenklagerung nimmt den Auftreffimpuls auf. Der in der Ebene der Schwenkbewegung angreifende Schaltmechanismus wird von dem Auftreffimpuls nicht beeinflusst. Die Zahnräder können axial festliegend und von gleicher Breite sein. Der Schaltzustand ist an dem Stellglied unmittelbar erkennbar. Der Anschlag kann unmittelbar am Zahnrad und nicht weit von dessen Mittelebene vorgesehen werden. Die gesamte Anordnung kann einfach und raumsparend ausgebildet werden.In such an arrangement, the pivot lever is supported on the unbalanced shaft by means of the pivot bearing on a relatively long lever arm with respect to the transmitted torque. This swivel bearing absorbs the impulse. The switching mechanism acting in the plane of the pivoting movement is not influenced by the impact impulse. The gears can be axially fixed and of the same width. The switching status is immediately recognizable on the actuator. The stop can be provided directly on the gear and not far from its center plane. The entire arrangement can be made simple and space-saving.

Weitere Ausgestaltungen der Erfindung sind Gegenstand der Unteransprüche.Further embodiments of the invention are the subject of the dependent claims.

Die Erfindung ist nachstehend an zwei Ausführungsbeispielen unter Bezugnahme auf die zugehörigen Zeichnungen näher erläutert:

  • Fig. 1 zeigt einen Schnitt durch einen Unwuchtrüttler längs einer die Umlaufachse der einen Unwucht enthaltenden Ebene.
  • Fig. 2 zeigt (teilweise im Schnitt) eine Axialansicht des Unwuchtrüttlers bei abgenommenem Deckel.
  • Fig. 3 zeigt in einer Darstellung ähnlich Fig. 1 eine abgewandelte Ausführungsform des Unwuchtrüttlers.
The invention is explained in more detail below using two exemplary embodiments with reference to the accompanying drawings:
  • Fig. 1 shows a section through an unbalance shaker along a plane containing the axis of rotation of an unbalance.
  • Fig. 2 shows (partly in section) an axial view of the unbalance vibrator with the cover removed.
  • Fig. 3 shows a representation similar to Fig. 1 shows a modified embodiment of the unbalance vibrator.

Bei der Ausführungsform nach Fig. 1 und 2 ist mit 10 ein Rüttlergehäuse bezeichnet. In Lagerschilden 12, 14 ist über Wälzlager 16, 18 eine Unwucht 20 mittels einer Unwuchtwelle 22 gelagert, die bei dem dargestellten Ausführungsbeispiel von zwei fluchtenden Wellenstümpfen 24 und 26 gebildet ist. Eine ähnliche (nicht dargestellte) Unwucht ist mit einer zu der Unwuchtwelle 22 parallelen Unwuchtwelle 28 im Rüttlergehäuse 10 gelagert. Auf den Unwuchtwellen 22 und 28 sitzen Zahnräder 30 bzw. 32, die miteinander in Eingriff sind. Das Zahnrad 30 ist über ein Gleitlager 34 drehbeweglich auf dem Wellenstumpf 26 der Unwuchtwelle 22 gelagert, während das Zahnrad 32 fest mit der Unwuchtwelle 28 verbunden ist. Das Zahnrad 30 ist mit der Unwuchtwelle 22 über eine Schaltkupplung 36 kuppelbar.In the embodiment according to FIGS. 1 and 2, 10 denotes a vibrator housing. In end shields 12, 14, an unbalance 20 is supported by means of an unbalanced shaft 22 via roller bearings 16, 18, which in the exemplary embodiment shown is formed by two aligned shaft ends 24 and 26. A similar unbalance (not shown) is mounted in the vibrator housing 10 with an unbalanced shaft 28 parallel to the unbalanced shaft 22. On the unbalanced shafts 22 and 28 there are gears 30 and 32, which are in engagement with each other. The gear 30 is rotatably supported on the stub shaft 26 of the unbalanced shaft 22 via a slide bearing 34, while the gear 32 is fixedly connected to the unbalanced shaft 28. The gear 30 can be coupled to the unbalanced shaft 22 via a clutch 36.

Die Schaltkupplung 36 enthält einen Anschlag 38, der auf der äusseren Stirnfläche des Zahnrads 30 sitzt. Ein doppelarmiger Hebel 40 ist mit einer Welle 42 um eine quer zur Umlaufachse 44 der Unwuchtwelle 22 verlaufende Schwenkachse 46 schwenkbar gelagert. Der doppelarmige Hebel 40 ist zwischen zwei Endstellungen bewegbar. In der ersten Endstellung kommt er mit einem Arm 48 und in der zweiten Endstellung mit dem anderen Arm 50 an dem Anschlag 38 zur Anlage.The clutch 36 includes a stop 38 which sits on the outer end face of the gear 30. A double-armed lever 40 is mounted with a shaft 42 so as to be pivotable about a pivot axis 46 running transversely to the axis of rotation 44 of the unbalanced shaft 22. The double-armed lever 40 is movable between two end positions. In the first end position, it comes to rest against the stop 38 with one arm 48 and in the second end position with the other arm 50.

Wie aus Fig. 2 ersichtlich ist, ist die Welle 42 in Lagerbuchsen 52 gelagert, die in Lagerböcken 54, 56 sitzen, welche durch Schrauben 58 an der Stirnfläche des Wellenstumpfes 26 befestigt sind.As can be seen from FIG. 2, the shaft 42 is mounted in bearing bushes 52 which are seated in bearing blocks 54, 56 which are fastened to the end face of the shaft end 26 by screws 58.

Je nachdem, ob der doppelarmige Hebel 40 in der in Fig. 1 dargestellten Lage ist oder im Uhrzeigersinn in die andere Lage verschwenkt ist, ist die Unwuchtwelle 22 in der einen oder einer dagegen im wesentlichen um 180° winkelversetzten anderen Lage mit dem Zahnrad 30 gekuppelt. Da das Zahnrad 30 mit dem Zahnrad 32 auf der anderen Unwuchtwelle 28 in Eingriff ist, verändert sich die relative Winkellage der gegensinnig umlaufenden Unwuchten und damit die resultierende Schwingungsrichtung.Depending on whether the double-armed lever 40 is in the position shown in FIG. 1 or is pivoted clockwise into the other position, the unbalance shaft 22 is coupled to the gearwheel 30 in one position or in another position that is essentially offset by 180 ° . Since the gearwheel 30 engages with the gearwheel 32 on the other unbalanced shaft 28, the relative angular position of the counterbalanced unbalance changes and thus the resulting direction of oscillation.

Bei Anwendung an einem Plattenrüttler für die Bodenverdichtung entspricht die eine Winkellage einer Vorwärtsbewegung des Geräts, während die andere Winkellage zu einer Rückwärtsbewegung führt.When used on a plate compactor for soil compaction, one angular position corresponds to a forward movement of the device, while the other angular position leads to a backward movement.

Bei der dargestellten Ausführungsform ist die Masseverteilung des doppelarmigen Hebels 40 so unsymmetrisch, dass die Fliehkraft auf den doppelarmigen Hebel ein Drehmoment um die Schwenkachse 46 ausübt, welches den Hebel im Uhrzeigersinn in Fig. 1 in eine erste Stellung zu schwenken sucht. Eine Schaltvorrichtung zur Betätigung der Schaltkupplung enthält einen Bowdenzug 60, über welchen auf den doppelarmigen Hebel 40 eine Kraft zur Erzeugung eines Drehmoments ausübbar ist, das dem von der Fliehkraft hervorgerufenen Drehmoment entgegenwirkt. Im einzelnen ist in dem Wellenstumpf 26 mittels einer Lagerbuchse 62 eine Stange 64 axial verschiebbar. An der Stange 64 sitzt ein Z-förmiger Ansatz 66, der hinter eine an dem Arm 48 des doppelarmigen Hebels 40 vorgesehene Nase 68 greift und gleichzeitig an die dem Zahnrad 30 zugewandte Innenseite des Arms 48 anlegbar ist.In the illustrated embodiment, the mass distribution of the double-armed lever 40 is so asymmetrical that the centrifugal force exerts a torque about the pivot axis 46 on the double-armed lever, which attempts to pivot the lever clockwise in FIG. 1 into a first position. A switching device for actuating the clutch includes a Bowden cable 60, via which a force can be exerted on the double-armed lever 40 to generate a torque which counteracts the torque caused by the centrifugal force. In particular, a rod 64 is axially displaceable in the shaft end 26 by means of a bearing bush 62. On the rod 64 sits a Z-shaped projection 66 which engages behind a nose 68 provided on the arm 48 of the double-armed lever 40 and at the same time can be placed against the inside of the arm 48 facing the gearwheel 30.

Am anderen, inneren Ende der Stange 64 ist diese über ein axial belastbares Kugellager 72 in einem Gehäuse 74 gelagert. Über eine an der Stange 64 sitzende Scheibe 76, die auf der Innenseite an dem Innenring des Kugellagers 72 anliegt, kann von dem Gehäuse 74 eine Zugkraft nach links in Fig. 1 auf die Stange 64 ausgeübt werden. Die dem Kugellager 74 gegenüberliegende Stirnwand 78 des Gehäuses 74 ist mit der Seele 80 des Bowdenzugs 60 verbunden. Der Bowdenzug 60 ist durch eine Axialbohrung 82 des Wellenstumpfes 24 hindurchgeführt und dort in einem Kugellager 84 gelagert. Der nicht-umlaufende Bowdenzug 60 ist dann seitlich aus dem Rüttlergehäuse 10 herausgeführt.At the other, inner end of the rod 64, the latter is mounted in a housing 74 via an axially loadable ball bearing 72. A pulling force can be exerted by the housing 74 onto the rod 64 from the housing 74 via a disk 76 which is seated on the rod 64 and which lies on the inside against the inner ring of the ball bearing 72 will. The end wall 78 of the housing 74 opposite the ball bearing 74 is connected to the core 80 of the Bowden cable 60. The Bowden cable 60 is passed through an axial bore 82 of the shaft end 24 and is supported there in a ball bearing 84. The non-rotating Bowden cable 60 is then guided out of the side of the vibrator housing 10.

in jeder Endstellung des doppelarmigen Hebels 40 liegt der jeweils von dem Zahnrad 30 abgehobene Arm, in der Darstellung von Fig. 1 der Arm 50, mit seiner im Zahnrad 30 abgewandten Rückseite 86 bremsend an einer gehäusefesten Bremsfläche 88 an. An der Stirnfläche des Zahnrads ist ein keilförmiger Nocken 90 vorgesehen, durch welchen kurz vor Anlage des zum Zahnrad 30 hingeneigten Armes 48 an dem Anschlag 38 dieser Arm 48 soweit zurückschwenkbar ist, dass der andere Arm 50 von der Bremsfläche 88 abgehoben wird. In ähnlicher Weise erfolgt bei einer Umschaltung des doppelarmigen Hebels 40 zunächst eine Anlage des Armes 48 an der Bremsfläche 88, bevor kurz vor Anlage des Armes 50 an dem Anschlag 38 dieser Arm zurückgeschwenkt und damit der Arm 48 von der Bremsfläche abgehoben wird. Der doppelarmige Hebel 40 weist vorzugsweise auf seiner dem Zahnrad 30 abgewandten Rückseite 86 einen Bremsbelag 92 auf.In each end position of the double-armed lever 40, the arm lifted off the gearwheel 30, in the illustration of FIG. 1, the arm 50, with its rear side 86 facing away from the gearwheel 30, brakes against a brake surface 88 fixed to the housing. A wedge-shaped cam 90 is provided on the end face of the gearwheel, by means of which, just before the arm 48 inclined towards the gearwheel 30 bears against the stop 38, this arm 48 can be pivoted back so far that the other arm 50 is lifted off the braking surface 88. Similarly, when the double-armed lever 40 is switched over, the arm 48 first comes into contact with the braking surface 88, before this arm is pivoted back shortly before the arm 50 abuts the stop 38 and the arm 48 is thus lifted off the braking surface. The double-armed lever 40 preferably has a brake lining 92 on its rear side 86 facing away from the gearwheel 30.

Die Wirkungsweise der beschriebenen Anordnung ist wie folgt:

  • Wenn keine Zugkraft auf den Bowdenzug 60 ausgeübt wird, bewegt sich die Stange 64 nach rechts in Fig. 1 unter dem Einfluss des von der Fliehkraft im Uhrzeigersinn auf den doppelarmigen Hebel 40 ausgeübten Drehmomentes und verschwenkt den doppelarmigen Hebel 40 im Uhrzeigersinn, so dass der Arm 48 ausser Eingriff mit dem Anschlag 38 kommt und der Arm 50 in die Bahn des Anschlags 38 bewegt wird. In der Endstellung des doppelarmigen Hebels 40 kommt der Arm 50 mit dem Bremsbelag 92 an der Bremsfläche 88 zur Anlage. Hierdurch wird die Unwuchtwelle 22 und die Unwucht 20 abgebremst, so dass sie dem über das Zahnrad 32 angetriebenen Zahnrad 30 nacheilt, solange bis der Anschlag 38 an dem Arm 50 zur Anlage kommt. Kurz bevor dies geschieht, wird der Arm 50 durch den Nocken 90 etwas zurückgeschwenkt, so dass der Arm 48 von der Bremsfläche 88 wieder abhebt.
The arrangement works as follows:
  • When no pulling force is applied to the Bowden cable 60, the rod 64 moves to the right in FIG. 1 under the influence of the torque exerted by the centrifugal force on the double-armed lever 40 and pivots the double-armed lever 40 clockwise so that the arm 48 comes out of engagement with the stop 38 and the arm 50 is moved into the path of the stop 38. In the end position of the double-armed lever 40, the arm 50 with the brake lining 92 comes to rest on the braking surface 88. As a result, the unbalance shaft 22 and the unbalance 20 are braked so that they lag behind the gear 30 driven by the gear 32 until the stop 38 comes to bear on the arm 50. Shortly before this happens, the arm 50 is pivoted back somewhat by the cam 90, so that the arm 48 lifts off the braking surface 88 again.

Diese Schaltstellung entspricht vorteilhafterweise der Fahrtrichtung «Vorwärts» eines mit dem Unwuchtrüttler versehenen Bodenverdichters. Es wird so sichergestellt, dass auf jeden Fall, auch beispielsweise bei Bruch der Seele 80, der Unwuchtrüttler in die Schaltstellung «Vorwärts» geht.This switching position advantageously corresponds to the direction of travel “forward” of a soil compactor provided with the unbalance shaker. This ensures that, in any case, even if the core 80 breaks, the unbalance shaker goes into the "forward" switch position.

Zum Umschalten des Unwuchtrüttlers in die in Fig. 1 dargestellte Schaltstellung wird das Gehäuse 74 über den Bowdenzug 60 nach links gezogen. Damit wird die Stange 64 nach links bewegt. Über den Z-förmigen Ansatz 66 und die Nase 68 wird der doppelarmige Hebel 40 entgegen dem Uhrzeigersinn verschwenkt, so dass der Arm 50 ausser Eingriff mit dem Anschlag 38 kommt und, wie in Fig. 1 dargestellt, der Hebel 48 in die Bahn des Anschlags 38 gelangt. Auch hier erfolgt eine zwischenzeitliche Abbremsung über den Bremsbelag 86 und die Bremsfläche 88, bis der Arm 48 durch den Nocken 90 zurückgeschwenkt wird.To switch the unbalance shaker into the switch position shown in FIG. 1, the housing 74 is pulled to the left via the Bowden cable 60. This moves the rod 64 to the left. About the Z-shaped projection 66 and the nose 68, the double-armed lever 40 is pivoted counterclockwise, so that the arm 50 comes out of engagement with the stop 38 and, as shown in Fig. 1, the lever 48 in the path of the stop 38 arrives. Here, too, the brakes are temporarily braked via the brake lining 86 and the braking surface 88 until the arm 48 is pivoted back by the cam 90.

Eine abgewandelte Ausführungsform ist in Fig. 3 dargestellt. Der Grundaufbau des Unwuchtrüttlers und der Schalteinrichtung ist der gleiche wie bei der Ausführungsform nach Fig. 1, und entsprechende Teile sind mit den gleichen Bezugszeichen versehen wie dort.A modified embodiment is shown in Fig. 3. The basic structure of the unbalance vibrator and the switching device is the same as in the embodiment according to FIG. 1, and corresponding parts are provided with the same reference numerals as there.

Bei der Ausführungsform nach Fig. 3 ist das Zahnrad 30 als Ring auf der Mantelfläche eines ringförmigen, nach innen offenen Gehäuses 94 etwa in der Mittelebene 96 desselben befestigt. Das Gehäuse 94 ist seinerseits auf der Unwuchtwelle 22 drehbar gelagert. Das Gehäuse 94 weist auf der Innenseite axial und längs des Umfangs winkelversetzte Anschläge, und zwar vorzugsweise mehr als zwei Anschläge 98, 100, 102 auf. Der Hebel ist hier ein einarmiger Hebel 104, der in einer Ausnehmung 106 der Unwuchtwelle 22 um eine in der Mittelebene 96 des Gehäuses 94 senkrecht zur Achse 44 der Unwuchtwelle 22 verlaufenden Schwenkachse 108 mittels einer Welle 110 verschwenkbar gelagert ist. Der Schwenkhebel 104 ist mit einem an der Stange 64 sitzenden radialen Ansatz 112 über einen Lenker 114 verbunden. Bei einer axialen Bewegung der Stange 64 unter Einfluss des Bowdenzugs 60 wird der Hebel 104 verschwenkt und gelangt nacheinander in die Bahn der Anschläge 102, 100 oder 98, an denen er bei verschiedenen Winkellagen zwischen Zahnrad 30 und Welle 22 zur Anlage kommt. Vorzugsweise enthält die Schaltvorrichtung mit dem Bowdenzug 60 eine der Anzahl der Anschläge 98, 100, 102 entsprechende Zahl von Raststellungen, wobei der Hebel 104 in jeder Raststellung an jeweils einem der Anschläge zur Anlage kommt.In the embodiment according to FIG. 3, the gearwheel 30 is fastened as a ring on the lateral surface of an annular, inwardly open housing 94 approximately in the central plane 96 thereof. The housing 94 is in turn rotatably supported on the unbalanced shaft 22. The housing 94 has axially and along the circumference angularly offset stops on the inside, and preferably more than two stops 98, 100, 102. The lever here is a one-armed lever 104, which is pivotably mounted in a recess 106 in the unbalanced shaft 22 about a pivot axis 108 extending in the central plane 96 of the housing 94 perpendicular to the axis 44 of the unbalanced shaft 22 by means of a shaft 110. The pivot lever 104 is connected to a radial shoulder 112 seated on the rod 64 via a link 114. With an axial movement of the rod 64 under the influence of the Bowden cable 60, the lever 104 is pivoted and successively comes into the path of the stops 102, 100 or 98, against which it comes into contact at different angular positions between the gear 30 and the shaft 22. The switching device with the Bowden cable 60 preferably contains a number of latching positions corresponding to the number of stops 98, 100, 102, the lever 104 coming to rest on one of the stops in each latching position.

Die beschriebene Anordnung gestattet die Einstellung mehrerer relativer Winkelstellungen zwischen Zahnrad 30 und Unwuchtwelle 22, die beispielsweise den Betriebsweisen «Vorwärts», «Standrüttlung» und «Rückwärts» entsprechen können. Im Gegensatz zu der DE-C-1 015 275 sind die jeweiligen Schaltstellungen aus der Stellung des Schaltmechanismus eindeutig erkennbar. Im Vergleich zu der DE-A-2008055 ergibt sich ein kompakterer Aufbau. Der Hebel 104 greift näher an der Mittellinie 96 des Zahnrads 30 an, so dass bei der Kraftübertragung geringere Kippmomente wirksam werden.The arrangement described allows the setting of several relative angular positions between the gear 30 and the unbalanced shaft 22, which can correspond, for example, to the “forward”, “stand vibration” and “backward” operating modes. In contrast to DE-C-1 015 275, the respective switching positions can be clearly recognized from the position of the switching mechanism. In comparison to DE-A-2008055 there is a more compact structure. The lever 104 engages closer to the center line 96 of the gearwheel 30, so that lower tilting moments become effective during the power transmission.

Claims (7)

1. Unbalance vibrator, in particular for soil compactors with reversible direction of propulsion, having two unbalance shafts (22, 28) rotating in opposite directions, the phase angle of one of said shafts being adjustable relative to the other shaft by means of a shift coupling comprising
a first unbalance on an unbalance shaft driven by a drive motor
a second unbalance on an unbalance shaft parallel to this unbalance shaft,
a first gear (32), which is fixedly connected to one of the unbalance shafts,
a second gear (30), which meshes with the first gear (32) and is rotatably mounted on the other unbalance shaft (22), and
a shift coupling (36) between the second gear (30) and the associated other unbalance shaft (22) which coupling couples in, at least, two different angular positions, said shift coupling (36) comprising the following components:
stop means (38) on the gear (30),
an engaging device rotating with the unbalance shaft (22), said device being movable between a first and a second position and cooperating with the stop means to establish drive connection between gear (30) and unbalance shaft (22) at one angular position, in said first position, and at another angular position, in said second position, and
a shifting device which is arranged to shift the engaging device between said first and second positions,

characterized in that
the engaging device is a lever (40, 104) which is pivotably mounted on the unbalance shaft (22) about a pivot axis (46, 108) extending transversely to the axis of rotation (44) of the unbalance shaft (22).
2. Unbalance vibrator as claimed in claim 1 characterized in that
(a) the stop means are formed by a stop (38) which is located on one end face of the gear (30), and
(b) the lever of the engaging device is a two-armed lever (40), which, in its first position, engages the stop (38) with one arm and, in its second position, engages the stop with the other arm (48).
3. Unbalance vibrator as claimed in claim 2, characterized in that
(a) in each end position of the two-armed lever (40) the respective arm (48, 50) liftet from the gear (30) brakingly engages a housing-fixed braking surface (88) with its rear surface (86) and
(b) a cam (90) is provided on the end face of the gear (30) and is arranged such that, shortly before the arm (48) tilted towards the gear (30) engages the stop (90), it rotates this arm (48) back to such an extent that the other arm (50) is lifted from the braking surface (88).
4. Unbalance vibrator as claimed in claim 3, characterized in that the two-armed lever (40) carries a brake lining (92) on its rear surface (86) remote from the gear (30).
5. Unbalance vibrator as claimed in anyone of the claims 2 to 4, characterized in that
(a) the mass distribution of the two-armed lever (40) is unsymmetric such that the centrifugal force exerts a torque on the two-armed lever (40) about the pivot axis (46), which torque tends to rotate the lever (40) into a first position, and
(b) the shifting device comprises a Bowden cable (60) which is arranged to exert a traction force on the two-armed lever to generate a torque which counteracts the torque caused by the centrifugal force.
6. Unbalance vibrator as claimed in claim 1, characterized in that
(a) the gear (30) is a ring on the peripheral surface of an annular housing (94) open towards the inside and is affixed substantially in the center plane (96) thereof, said housing, in turn, being mounted for rotation on the unbalance shaft (22),
(b) the housing (94) has axially and, along its circumference, angulary spaced stops (98, 100, 102), on its inner surface, and
(c) the lever is a single-armed lever (104) which is pivotably mounted in a recess (106) of the unbalance shaft (22) about a privot axis (108) located in said center plane (96) and normal to the unbalance shaft (22).
7. Unbalance vibrator as claimed in claim 6, characterized in that
(a) more than two axially and angulary spaced stops (98, 100, 102) are provided in the housing (94) and
(b) the shifting device has a plurality of detent positions corresponding to the number of these stops, the lever (104) engaging a respective one of the stops (98, 100, 102) in each of said detent positions.
EP80101838A 1980-04-05 1980-04-05 Unbalanced-mass vibrator with switching clutch Expired EP0037428B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP80101838A EP0037428B1 (en) 1980-04-05 1980-04-05 Unbalanced-mass vibrator with switching clutch
AT80101838T ATE3452T1 (en) 1980-04-05 1980-04-05 UNBALANCE VIBRATOR WITH SHIFT CLUTCH.
DE8080101838T DE3063259D1 (en) 1980-04-05 1980-04-05 Unbalanced-mass vibrator with switching clutch
US06/239,698 US4440034A (en) 1980-04-05 1981-03-02 Eccentric vibrator with shifting coupling

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP80101838A EP0037428B1 (en) 1980-04-05 1980-04-05 Unbalanced-mass vibrator with switching clutch

Publications (2)

Publication Number Publication Date
EP0037428A1 EP0037428A1 (en) 1981-10-14
EP0037428B1 true EP0037428B1 (en) 1983-05-18

Family

ID=8186652

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80101838A Expired EP0037428B1 (en) 1980-04-05 1980-04-05 Unbalanced-mass vibrator with switching clutch

Country Status (4)

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US (1) US4440034A (en)
EP (1) EP0037428B1 (en)
AT (1) ATE3452T1 (en)
DE (1) DE3063259D1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE443591B (en) * 1981-10-28 1986-03-03 Dynapac Ab DEVICE FOR CONTINUOUS REVOLUTION OF THE VIBRATION AMPLIANCE WITH A ROTABLE EXCENTER ELEMENT
DE3248474A1 (en) * 1982-12-29 1984-07-12 Weber Maschinentechnik Gmbh, 5928 Laasphe ACTUATING DEVICE FOR THE SWITCHING COUPLING SWITCHABLE VIBRATORS OF GROUND COMPRESSORS
DE19913074C2 (en) * 1999-03-23 2001-07-26 Wacker Werke Kg Soil compacting device with servo control
US6234718B1 (en) * 1999-03-26 2001-05-22 Case Corporation Vibratory apparatus
JP3447993B2 (en) * 1999-11-19 2003-09-16 三笠産業株式会社 Oil lubrication mechanism of vibrator
CN113386243A (en) * 2021-06-09 2021-09-14 福建群峰机械有限公司 Vibrating box

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1057274A (en) * 1963-02-09 1967-02-01 Wacker Hermann Improvements in ground-tamping apparatus incorporating a device for altering the direction of vibration
DE1634477A1 (en) * 1966-03-24 1970-08-06 Buckau Wolf Maschf R Switching device for a vibrating compressor
DE2802648A1 (en) * 1978-01-21 1979-07-26 Guenther Weber Herstellung Und RUETTEL PLATE REVERSIBLE IN THE MARCHING DIRECTION

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1015275B (en) * 1954-03-29 1957-09-05 Losenhausenwerk Duesseldorfer Coupling for the gradual relative rotation of two rotating shafts by means of a gear drive
IT561054A (en) * 1955-10-24
AT220651B (en) * 1959-03-09 1962-04-10 Schenkir Dipl Ing Ludwig Soil compactor with rotating imbalances
DE1253177B (en) * 1964-07-17 1967-10-26 Wacker Hermann Device for achieving a forward or reverse flow in soil compaction plates
NL6818522A (en) * 1968-01-15 1969-07-17
US3505885A (en) * 1968-03-12 1970-04-14 Losenhausen Maschinenbau Ag Vibration generators
DE2008055C3 (en) * 1970-02-21 1978-06-15 Guenther Weber Herstellung Und Vertrieb Von Baumaschinen, 5929 Rueckershausen Unbalance vibrators, in particular for soil compactors
DE2052036B1 (en) * 1970-10-23 1971-11-25 Maschinenfabrik Buckau R Wolf Ag Unbalance gear with switching device
US4193309A (en) * 1975-08-01 1980-03-18 Shimano Industrial Company Limited Speed-changing device for bicycle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1057274A (en) * 1963-02-09 1967-02-01 Wacker Hermann Improvements in ground-tamping apparatus incorporating a device for altering the direction of vibration
DE1634477A1 (en) * 1966-03-24 1970-08-06 Buckau Wolf Maschf R Switching device for a vibrating compressor
DE2802648A1 (en) * 1978-01-21 1979-07-26 Guenther Weber Herstellung Und RUETTEL PLATE REVERSIBLE IN THE MARCHING DIRECTION

Also Published As

Publication number Publication date
EP0037428A1 (en) 1981-10-14
ATE3452T1 (en) 1983-06-15
DE3063259D1 (en) 1983-07-07
US4440034A (en) 1984-04-03

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