EP0047433B1 - Vibration device for compacting materials, especially for soil compaction - Google Patents

Vibration device for compacting materials, especially for soil compaction Download PDF

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Publication number
EP0047433B1
EP0047433B1 EP81106627A EP81106627A EP0047433B1 EP 0047433 B1 EP0047433 B1 EP 0047433B1 EP 81106627 A EP81106627 A EP 81106627A EP 81106627 A EP81106627 A EP 81106627A EP 0047433 B1 EP0047433 B1 EP 0047433B1
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EP
European Patent Office
Prior art keywords
clutch
unbalanced mass
unbalanced
drive shaft
axial direction
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
EP81106627A
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German (de)
French (fr)
Other versions
EP0047433A3 (en
EP0047433A2 (en
Inventor
Friedrich Kümmel
Ludwig Unrath
Rudolf Hennecke
Manfred Schubert
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Delmag Maschinenfabrik Reinhold Dornfeld GmbH and Co
Original Assignee
Delmag Maschinenfabrik Reinhold Dornfeld GmbH and Co
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Application filed by Delmag Maschinenfabrik Reinhold Dornfeld GmbH and Co filed Critical Delmag Maschinenfabrik Reinhold Dornfeld GmbH and Co
Priority to AT81106627T priority Critical patent/ATE16719T1/en
Publication of EP0047433A2 publication Critical patent/EP0047433A2/en
Publication of EP0047433A3 publication Critical patent/EP0047433A3/en
Application granted granted Critical
Publication of EP0047433B1 publication Critical patent/EP0047433B1/en
Expired legal-status Critical Current

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Classifications

    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight

Definitions

  • the invention relates to a vibration device for material compaction, in particular a soil compaction device, which has an unbalance system with two coaxial shafts that can be driven independently of one another, each of which is connected to an unbalanced mass and a first or a second gear element, as well as a drive shaft and at least one switchable clutch for optional drive of a third or fourth gear element which is in drive connection with the first or the second gear element.
  • the gear elements mentioned will usually be pulleys, gearwheels or the like, so that the drive connection is established by means of a V-belt or toothed belt, by direct meshing of the gearwheels with one another or by intermediate gears.
  • one of the two coaxial shafts is designed as a hollow shaft and it carries a half-shell-shaped unbalanced mass which overlaps the second unbalanced mass located on a core shaft, so that the two shafts together with the associated unbalanced masses are independent of one another can be driven.
  • This drive takes place via a drive shaft running parallel to the two coaxial shafts, which drives a switchable clutch with which two pulleys rotatably mounted on opposite end regions of the drive shaft can optionally be connected.
  • These drive one of the unbalanced masses via V-belts and pulleys attached to opposite end areas of the two coaxial shafts.
  • the known vibration device can be operated with two different frequencies as well as with two different unbalances, although there is a fixed association between frequency and unbalance.
  • the known vibration device has various disadvantages: In order not to endanger the operator, it must be prevented that the operator can reach into the V-belt transmission mentioned or that the operator's clothing can be caught by the V-belt transmission; Therefore, two housing-like covers on both sides of the unbalance system are required in the known vibration device. Furthermore, one of the two unbalanced masses is ineffective in each operating mode, so that it only increases the weight of the vibration device.
  • the present invention has now created a vibration device of the type mentioned at the outset, which is simpler in construction and can be built more compactly than the known vibration device described, namely according to the invention the four gear elements serving to drive the two unbalanced masses are all on one side of the unbalance system arranged and covered by a cover.
  • the vibration device according to the invention thus has a gearbox only on one side of the unbalance system, so that a cover is also required only on one side of the unbalance system. This not only makes the new vibration device cheaper to manufacture, it also makes it narrower and lighter.
  • the switchable clutch is therefore not used to change the frequency with which the unbalanced mass is operated, but rather to reverse the direction of rotation.
  • the vibration device according to DE-AS 2108106 also has all the disadvantages of the vibration device according to DE-OS 1 558869, and its unbalance system does not have a truly one-sided drive.
  • the construction according to the invention provides that the driven unbalanced mass always leads the unbalanced mass.
  • the unbalance system cannot change to the state of lowest total unbalance while continuously reducing the total unbalance, since a state would first have to be run through in which the total unbalance is greater than in the state in which the two unbalanced masses are at a smaller angular distance from one another and that driven unbalanced mass leads over the entrained unbalanced mass.
  • the vibrating device according to the invention thus allows the unbalance system to be operated with a large effective and with a small effective total unbalance when operating at a low frequency with a very simple structure. This is a great advantage for soil compaction equipment, since it is better to work hard soil with a high frequency and small amplitude in order to avoid damage to the vibrating device, whereas with soft soil such as clay, large jumps of the vibrating device at low frequency are desirable in order to get stuck of the vibrator on soft, damp floors.
  • a stop to take the unbalanced unbalanced mass per se would not be necessary at all, since the unbalance system endeavors to assume this state anyway if one of the two unbalanced masses is driven and the other can rotate freely.
  • a preferred embodiment of the vibration device according to the invention has a stop which takes the first unbalanced mass away from the angular position in which the unbalanced mass is at a greater angular distance from one another on.
  • the clutch for the connection of the two gear elements to the drive shaft should each have a clutch drum which are arranged next to one another in the axial direction and to which only a single switchable centrifugal weight clutch element which is non-rotatably connected to the drive shaft is assigned, and for switching over the Coupling, coupling element and coupling drums can be displaced relative to one another in the axial direction such that the coupling element can optionally be arranged within one of the coupling drums assigned to it.
  • switchable centrifugal clutches e.g. DE-OS 2 509 322
  • a centrifugal weight coupling element can be saved.
  • a particularly space-saving clutch is obtained when the clutch drums are rotatably connected to one of the gear elements to be coupled to the drive shaft, are arranged in the axial direction between them and are rotatably mounted together with them on the drive shaft.
  • a switching element which passes through the drive shaft in the axial direction is provided for the centrifugal weight coupling element which can be displaced along the drive shaft, so that the clutch drums can be made axially immovable.
  • an embodiment is shorter in the axial direction, in which the clutch drums are non-rotatable relative to the respectively assigned gear element, but are displaceable in the axial direction and can thus be arranged optionally above the centrifugal weight coupling element.
  • the shift path lies between the two gear elements to be coupled to the drive shaft, so that the embodiment is shorter in the axial direction by the shift path length than the embodiment described in the first place, in which as much space is required beyond the one gear element as that Movement of the switching element corresponds to the switching path length.
  • centrifugal clutch according to the invention essentially consists of series products available on the market len known centrifugal clutches and can therefore be manufactured inexpensively.
  • FIGS 1 and 2 show a soil compaction device designed according to the invention with a vibrating plate 10 on which an unbalance system 12 is attached. This is driven by an internal combustion engine 14 via a drive system 16. A tank in front of the engine was designated 18, a guide handle for the device attached to the vibrating plate 10 was designated 20.
  • the motor 14 drives one of two pulleys 24, 26 via a drive shaft 19 and a centrifugal clutch 22.
  • a clutch drum 28 or 30 is connected to each of the pulleys, within which is arranged an axially displaceable drive element 32, which is non-rotatably connected to the drive shaft 19 and which frictionally engages against that clutch drum 28 or, as the centrifugal weights increase, as the engine speed increases 30 creates within which it is currently located.
  • pulleys 38 and 40 are connected via V-belts 34 and 36 to pulleys 38 and 40, the first of which is connected in a rotationally fixed manner to a hollow shaft 42 and the second to a core shaft 44 which is concentric therewith.
  • the hollow shaft 42 carries a larger, the core shaft 44 a smaller unbalanced mass 46 or 48, so that the two shafts and the two unbalanced masses together form the unbalance system designated by 12 in FIGS. 1 and 2.
  • the unbalanced mass 46 or 48 connected to the respective non-driven shaft 42 or 44 could assume any rotational angle position relative to the driven unbalanced mass.
  • stops are now provided, which are arranged according to the invention in such a way that when the large unbalanced mass 46 is driven, the small unbalanced mass 48 is not taken along in any position, but in a position in which it lags slightly compared to the large unbalanced mass 46, as shown in FIG Figure 4a is shown.
  • the unbalanced masses 46 and 48 are driven at different speeds and the device runs at a low total frequency with a large total unbalance and at a high frequency with a small total unbalance.
  • FIGS. 5 and 6 show a preferred embodiment of the unbalance system 12 according to the invention, in which the hollow shaft 42 is mounted in a housing 60 with the aid of roller bearings 62, while slide bearings 64 serve to support the core shaft 44.
  • a stop bar 46a is attached to the large unbalanced mass 46 such that when the hollow shaft 42 is driven or the large unbalanced mass 46 is driven, the small unbalanced mass 48 which is carried along lags slightly in the direction of rotation, as is shown in FIG. 6 with solid lines.
  • a further stop bar 46b can be provided, through which the large unbalanced mass is driven when the core shaft 44 is driven so that it is diametrically opposed to the small unbalanced mass 48. This state is shown in dot-dash lines in FIG.
  • the two states with the largest and smallest total unbalance are brought about with the simplest means, so that complicated parts such as switchable couplings in the unbalance system itself can be dispensed with.
  • FIG. 7 shows a drive shaft 110 provided with a drive flange 112, on which two pulley bodies 116 and 118 are rotatably but axially non-displaceably mounted with ball bearings 114 held axially immovable.
  • Each of these pulley bodies forms a pulley 116a or 118a and a clutch drum 116b or 118b, the latter facing each other and having the same inside diameter according to the invention.
  • a switching axis 120 is held in the longitudinal direction; at its outer end it carries a shift lever 124 via a ball bearing 122 which is held immovably in the axial direction, while a tension pin 126 is fastened at its inner end, which extends through longitudinal slots 128 in the drive shaft 110 on both sides of the shift axis 120 and in one designated 130 as a whole Clutch disc protrudes.
  • This clutch disc is available as a whole part on the market, e.g. from the company Robert Scheuffele & Co., D-7120 Bietigheim-Bissingen.
  • the clutch disc 130 has a disc body 132 on which the flyweights 136 provided with clutch linings 134 are held with the aid of springs 138 pulling the flyweights against each other in such a way that they can only move outward in the radial direction relative to the disc body 132.
  • the clutch disc 130 By shifting the shift lever 124 in the axial direction, the clutch disc 130, which is non-rotatably connected to the drive shaft 110 via the dowel pin 126, can be shifted in the axial direction when the drive shaft 110 is at a standstill or only rotating at idling speed, and thus optionally within one of the clutch drums 116b and Arrange 118b so that when the speed of the drive shaft 110 increases, one of the two pulleys 116a or 118a is driven.
  • a clutch disk 130 ' is fixedly attached to a drive shaft 110', ie it rotates with the drive shaft and is immovable relative to the latter.
  • ball bearings 114 ' which are held immovably on the drive shaft 110'
  • two pulley bodies 116 ' and 118' are again rotatable on the drive shaft, but are mounted immovably relative to the latter and each form a pulley 116a 'and 118a'.
  • the clutch drums 116b 'and 118b' are not formed on the pulley bodies, but are formed as separate parts, which are connected in a rotationally fixed manner to the assigned pulley body via a ring of driving pins 150 'or driving wedges 152', but are opposed to it in Have it shifted axially.
  • a ball bearing 122 ' is fastened on each of the clutch drums 116b' and 118b ', a shift lever 124' was fastened on the outer rings of these ball bearings, so that one of the two clutch drums 116b 'and 118b' can be selectively positioned with its help over the clutch disc 130 'can be pushed.
  • the embodiment according to FIG. 9 is shorter in the axial direction than the embodiment according to FIG. 7.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Paleontology (AREA)
  • Soil Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Agronomy & Crop Science (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Road Paving Machines (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Soil Working Implements (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)

Abstract

A material compacting vibration machine provided with an imbalanced system having coaxial first and second independently rotatable shafts carrying first and second drive elements and a pair of unbalanced masses having third and fourth drive elements secured thereto with driving connections between the first and third drive elements and between the second and fourth drive elements, and a drive shaft selectively coupled to the first and second drive elements, wherein the four drive elements all are disposed on one side of the imbalanced system and are shielded by a cover.

Description

Die Erfindung betrifft ein Vibrationsgerät zur Materialverdichtung, insbesondere ein Bodenverdichtungsgerät, welches ein Unwuchtsystem mit zwei unabhängig voneinander antreibbaren koaxialen Wellen aufweist, deren jede mit einer Unwuchtmasse und einem ersten bzw. einem zweiten Getriebeelement verbunden ist, sowie mit einer Antriebswelle und mindestens einer schaltbaren Kupplung zum wahlweisen Antrieb eines dritten bzw. vierten Getriebeelements, welches mit dem ersten bzw. dem zweiten Getriebeelement in Triebverbindung steht. Bei den erwähnten Getriebeelementen wird es sich üblicherweise um Riemenscheiben, Zahnräder oder dergleichen handeln, so dass die Triebverbindung durch einen Keil- oder Zahnriemen, durch unmittelbares Kämmen der Zahnräder miteinander oder durch Zwischenräder hergestellt wird.The invention relates to a vibration device for material compaction, in particular a soil compaction device, which has an unbalance system with two coaxial shafts that can be driven independently of one another, each of which is connected to an unbalanced mass and a first or a second gear element, as well as a drive shaft and at least one switchable clutch for optional drive of a third or fourth gear element which is in drive connection with the first or the second gear element. The gear elements mentioned will usually be pulleys, gearwheels or the like, so that the drive connection is established by means of a V-belt or toothed belt, by direct meshing of the gearwheels with one another or by intermediate gears.

Bei einem bekannten derartigen Vibrationsgerät (DE-OS 1 558869) ist eine der beiden koaxialen Wellen als Hohlwelle ausgebildet und sie trägt eine halbschalenförmige Unwuchtmasse, die die zweite, auf einer Kernwelle sitzende Unwuchtmasse überfängt, so dass die beiden Wellen samt den zugehörigen Unwuchtmassen unabhängig voneinander angetrieben werden können. Dieser Antrieb erfolgt über eine parallel zu den beiden koaxialen Wellen verlaufende Antriebswelle, die eine schaltbare Kupplung antreibt, mit der wahlweise zwei auf einander gegenüberliegenden Endbereichen der Antriebswelle drehbar gelagerte Riemenscheiben verbunden werden können. Diese treiben über Keilriemen und auf einander entgegengesetzten Endbereichen der beiden koaxialen Wellen befestigte Riemenscheiben jeweils eine der Unwuchtmassen an. Da die Übersetzungsverhältnisse der beiden Riemenscheibengetriebe ebenso wie die Unwuchten der beiden Unwuchtmassen unterschiedlich gewählt wurden, kann das bekannte Vibrationsgerät sowohl mit zwei verschiedenen Frequenzen als auch mit zwei verschiedenen Unwuchten betrieben werden, wobei allerdings eine feste Zuordnung zwischen Frequenz und Unwucht besteht.In a known vibration device of this type (DE-OS 1 558869), one of the two coaxial shafts is designed as a hollow shaft and it carries a half-shell-shaped unbalanced mass which overlaps the second unbalanced mass located on a core shaft, so that the two shafts together with the associated unbalanced masses are independent of one another can be driven. This drive takes place via a drive shaft running parallel to the two coaxial shafts, which drives a switchable clutch with which two pulleys rotatably mounted on opposite end regions of the drive shaft can optionally be connected. These drive one of the unbalanced masses via V-belts and pulleys attached to opposite end areas of the two coaxial shafts. Since the transmission ratios of the two pulley gears and the unbalance of the two unbalanced masses were chosen differently, the known vibration device can be operated with two different frequencies as well as with two different unbalances, although there is a fixed association between frequency and unbalance.

Das bekannte Vibrationsgerät hat verschiedene Nachteile: Um die Bedienungsperson nicht zu gefährden, muss verhindert werden, dass die Bedienungsperson in die erwähnten Keilriemengetriebe hineinfassen kann oder Kleidungsstücke der Bedienungsperson von den Keilriemengetrieben erfasst werden können; deshalb sind bei dem bekannten Vibrationsgerät zwei gehäuseartige Abdeckungen zu beiden Seiten des Unwuchtsystems erforderlich. Ferner ist bei jeder Betriebsart eine der beiden Unwuchtmassen unwirksam, so dass sie nur das Gewicht des Vibrationsgeräts erhöht.The known vibration device has various disadvantages: In order not to endanger the operator, it must be prevented that the operator can reach into the V-belt transmission mentioned or that the operator's clothing can be caught by the V-belt transmission; Therefore, two housing-like covers on both sides of the unbalance system are required in the known vibration device. Furthermore, one of the two unbalanced masses is ineffective in each operating mode, so that it only increases the weight of the vibration device.

Durch die vorliegende Erfindung wurde nun ein Vibrationsgerät der eingangs erwähnten Art geschaffen, das einfacher in seinem Aufbau ist und kompakter gebaut werden kann als das geschilderte bekannte Vibrationsgerät, indem nämlich erfindungsgemäss die vier, dem Antrieb der beiden Unwuchtmassen dienenden Getriebeelemente sämtlich auf einer Seite des Unwuchtsystems angeordnet und durch eine Abdeckung überfangen werden. Das erfindungsgemässe Vibrationsgerät weist also nur auf einer Seite des Unwuchtsystems ein Getriebe auf, so dass auch nur auf einer Seite des Unwuchtsystems eine Abdeckung erforderlich ist. Dadurch lässt sich das neue Vibrationsgerät nicht nur billiger herstellen, sondern es baut auch schmäler und leichter.The present invention has now created a vibration device of the type mentioned at the outset, which is simpler in construction and can be built more compactly than the known vibration device described, namely according to the invention the four gear elements serving to drive the two unbalanced masses are all on one side of the unbalance system arranged and covered by a cover. The vibration device according to the invention thus has a gearbox only on one side of the unbalance system, so that a cover is also required only on one side of the unbalance system. This not only makes the new vibration device cheaper to manufacture, it also makes it narrower and lighter.

Bei Vibrations-Bodenverdichtungsgeräten ist es zwar schon bekannt (DE-AS 2108106), an einer Antriebswelle nur auf einer Seite eines Unwuchtsystems sowohl zwei Getriebeelemente in Form von Riemenscheiben als auch eine schaltbare Kupplung anzuordnen, mit deren Hilfe wahlweise eine der beiden Riemenscheiben mit der Antriebswelle verbunden werden kann, jedoch sind auch bei dieser bekannten Konstruktion zu beiden Seiten des nur eine einzige Unwuchtmasse und demzufolge nur eine einzige Welle aufweisenden Unwuchtsystems Getriebeelemente angeordnet, und zwar zwei an den voneinander abgekehrten Enden der Unwuchtmasse-Welle befestigte Riemenscheiben und zwei ebenfalls an den voneinander abgewandten Enden einer Zwischenwelle angebrachte Riemenscheiben, wobei sich diese Zwischenwelle über die ganze Breite des Unwuchtsystems erstreckt und dazu dient, die Unwuchtmasse in zur normalen Drehrichtung entgegengesetzten Richtung antreiben zu können. Bei diesem bekannten Vibrationsgerät dient die schaltbare Kupplung also nicht der Änderung der Frequenz, mit der die Unwuchtmasse betrieben wird, sondern der Umkehr der Drehrichtung. Auch das Vibrationsgerät nach der DE-AS 2108106 weist also sämtliche Nachteile des Vibrationsgeräts nach der DE-OS 1 558869 auf, und sein Unwuchtsystem besitzt keinen echt einseitigen Antrieb.In the case of vibratory soil compacting devices, it is already known (DE-AS 2108106) to arrange both gear elements in the form of pulleys and a switchable clutch on a drive shaft only on one side of an unbalance system, with the aid of which either one of the two pulleys with the drive shaft can be selected can be connected, but also in this known construction on both sides of the only one unbalanced mass and consequently only a single shaft unbalance system gear elements are arranged, namely two pulleys attached to the opposite ends of the unbalanced mass shaft and two also on the one another Pulleys attached to the opposite ends of an intermediate shaft, this intermediate shaft extending over the entire width of the unbalance system and serving to be able to drive the unbalanced mass in the direction opposite to the normal direction of rotation. In this known vibration device, the switchable clutch is therefore not used to change the frequency with which the unbalanced mass is operated, but rather to reverse the direction of rotation. The vibration device according to DE-AS 2108106 also has all the disadvantages of the vibration device according to DE-OS 1 558869, and its unbalance system does not have a truly one-sided drive.

Bei Vibrationsgeräten mit einem zwei Unwuchtmassen aufweisenden Unwuchtsystem ist es auch schon bekannt (DE-OS 2738794), unterschiedliche Gesamtunwuchten dadurch einzustellen, dass sich die Unwuchtmassen mittels einer Kupplung in verschiedenen Winkelstellungen relativ zueinander anordnen und fixieren lassen.In vibration devices with an unbalance system having two unbalanced masses, it is also known (DE-OS 2738794) to set different total unbalances in such a way that the unbalanced masses can be arranged and fixed relative to one another in different angular positions by means of a coupling.

Zur Erzielung desselben Effekts, ohne dass jedoch komplizierte Bauteile wie Kupplungen benötigt werden, wird nun erfindungsgemäss vorgeschlagen, das Unwuchtsystem so auszubilden, dass mindestens in der einen Winkelstellung der beiden Unwuchtmassen relativ zueinander die nicht mit der Antriebswelle gekuppelte Unwuchtmasse von der anderen Unwuchtmasse mitgenommen wird und dass für diejenige Winkelstellung, in der die Unwuchtmassen den kleineren Winkelabstand voneinander aufweisen, zusammen mit der angetriebenen ersten Unwuchtmasse ein die andere, zweite Unwuchtmasse mitnehmender Anschlag umläuft, welcher so angeordnet ist, dass die erste Unwuchtmasse gegenüber der zweiten Unwuchtmasse voreilt. In diesem Zusammenhang muss auf folgendes hingewiesen werden: Es würde nicht ausreichen, einfach zusammen mit der jeweils angetriebenen Unwuchtmasse einen Anschlag für die jeweils andere Unwuchtmasse mitlaufenzulassen; würde nämlich im Zustand grösster Gesamtunwucht, d.h. bei im wesentlichen ohne Winkelabstand miteinander umlaufenden Unwuchtmassen, die grössere Unwuchtmasse mit dem Antrieb gekuppelt und die kleinere Unwuchtmasse durch einen zusammen mit der grösseren Unwuchtmasse umlaufenden Anschlag so mitgenommen werden, dass sie in Drehrichtung vor der sie mitnehmenden grossen Unwuchtmasse liegt, was an sich das Naheliegendste wäre, so hätte dies zur Folge, dass die mitgenommene Unwuchtmasse alsbald eine Winkelstellung einnehmen würde, in der sie der angetriebenen Unwuchtmasse ungefähr gegenüberliegt - ein solches Unwuchtsystem hat stets das Bestreben, den Zustand geringster Gesamtunwucht einzunehmen, und beim Aufschlagen eines solchen Vibrationsgeräts auf dem Boden würde die mitgenommene, kleinere Unwuchtmasse gegenüber der grösseren, mit dem Antrieb gekuppelten Unwuchtmasse voreilen können. Deshalb sieht die erfindungsgemässe Konstruktion vor, dass die angetriebene Unwuchtmasse gegenüber der mitgenommenen Unwuchtmasse stets voreilt. In diesem Fall kann das Unwuchtsystem nicht unter stetiger Verringerung der Gesamtunwucht in den Zustand geringster Gesamtunwucht übergehen, da zunächst ein Zustand durchlaufen werden müsste, in dem die Gesamtunwucht grösser ist als in dem Zustand, in dem die beiden Unwuchtmassen einen kleineren Winkelabstand voneinander aufweisen und die angetriebene Unwuchtmasse gegenüber der mitgenommenen Unwuchtmasse voreilt.To achieve the same effect, but without requiring complicated components such as couplings, it is now proposed according to the invention to design the unbalance system in such a way that the unbalanced mass not coupled to the drive shaft is carried along by the other unbalanced mass at least in one angular position of the two unbalanced masses and that for the angular position in which the unbalanced masses have the smaller angular distance from one another, together with the driven first unbalanced mass, a stop which carries the other, second unbalanced mass and which is arranged such that the first unbalanced mass is opposite leads the second unbalanced mass. In this connection, the following must be pointed out: It would not be sufficient simply to allow a stop for the other unbalanced mass to run along with the driven unbalanced mass; namely, in the state of greatest total unbalance, i.e. with substantially unbalanced masses of unbalanced mass, the larger unbalanced mass would be coupled to the drive and the smaller unbalanced mass would be taken along by a stop rotating together with the larger unbalanced mass such that they would rotate in the direction of rotation before the large one Imbalance mass, which would be the most obvious in itself, would have the consequence that the unbalanced mass taken would soon assume an angular position in which it is roughly opposite the driven unbalanced mass - such an unbalance system always endeavors to assume the state of lowest total unbalance, and When such a vibrating device strikes the ground, the smaller, unbalanced mass taken along would lead the larger unbalanced mass coupled to the drive. Therefore, the construction according to the invention provides that the driven unbalanced mass always leads the unbalanced mass. In this case, the unbalance system cannot change to the state of lowest total unbalance while continuously reducing the total unbalance, since a state would first have to be run through in which the total unbalance is greater than in the state in which the two unbalanced masses are at a smaller angular distance from one another and that driven unbalanced mass leads over the entrained unbalanced mass.

Das erfindungsgemässe Vibrationsgerät erlaubt es also bei einfachstem Aufbau, das Unwuchtsystem bei einem Betrieb mit niedriger Frequenz mit einer grossen und bei hoher Frequenz mit einer kleinen wirksamen Gesamtunwucht zu betreiben. Dies ist bei Bodenverdichtungsgeräten ein grosser Vorteil, da man einen harten Boden besser mit hoher Frequenz und kleiner Amplitude bearbeitet, um Beschädigungen des Vibrationsgeräts zu vermeiden, während bei einem weichen Boden wie beispielsweise Lehm grosse Sprünge des Vibrationsgeräts bei kleiner Frequenz erwünscht sind, um ein Festsaugen des Vibrationsgeräts am weichen, feuchten Boden zu verhindern.The vibrating device according to the invention thus allows the unbalance system to be operated with a large effective and with a small effective total unbalance when operating at a low frequency with a very simple structure. This is a great advantage for soil compaction equipment, since it is better to work hard soil with a high frequency and small amplitude in order to avoid damage to the vibrating device, whereas with soft soil such as clay, large jumps of the vibrating device at low frequency are desirable in order to get stuck of the vibrator on soft, damp floors.

Für den Zustand kleinster Gesamtunwucht wäre ein Anschlag zum Mitnehmen der nicht angetriebenen Unwuchtmasse an sich gar nicht erforderlich, da das Unwuchtsystem ohnehin bestrebt ist, diesen Zustand einzunehmen, wenn eine der beiden Unwuchtmassen angetrieben wird und sich die andere frei drehen kann. Damit jedoch bei einem Antrieb der dem Zustand kleinster Gesamtunwucht zugeordneten Welle des Unwuchtsystems der Zustand kleinster Gesamtunwucht rasch eingenommen wird, weist eine bevorzugte Ausführungsform des erfindungsgemässen Vibrationsgeräts für diejenige Winkelstellung, in der sich die Unwuchtmasse im grösseren Winkelabstand voneinander befinden, einen die erste Unwuchtmasse mitnehmenden Anschlag auf.For the state of smallest total unbalance, a stop to take the unbalanced unbalanced mass per se would not be necessary at all, since the unbalance system endeavors to assume this state anyway if one of the two unbalanced masses is driven and the other can rotate freely. However, so that when the shaft of the unbalance system assigned to the state of the smallest total unbalance is driven, the state of the smallest total unbalance is quickly assumed, a preferred embodiment of the vibration device according to the invention has a stop which takes the first unbalanced mass away from the angular position in which the unbalanced mass is at a greater angular distance from one another on.

Schliesslich wird auch noch ein besonders einfacher Aufbau für die Kupplung des Vibrationsgeräts vorgeschlagen; gemäss diesem Vorschlag soll die Kupplung für die Verbindung der beiden Getriebeelemente mit der Antriebswelle jeweils eine Kupplungstrommel aufweisen, die in axialer Richtung nebeneinander angeordnet sind und denen nur ein einziges, mit der Antriebswelle drehfest verbundenes, schaltbares Fliehgewicht-Kupplungselement zugeordnet ist, und zum Umschalten der Kupplung sind Kupplungselement und Kupplungstrommeln in axialer Richtung derart relativ zueinander verschiebbar, dass das Kupplungselement wahlweise innerhalb einer der ihm zugeordneten Kupplungstrommeln angeordnet werden kann. Gegenüber bekannten schaltbaren Fliehkraftkupplungen (z.B. DE-OS 2 509 322) lässt sich so ein Fliehgewicht-Kupplungselement einsparen.Finally, a particularly simple structure for the coupling of the vibration device is also proposed; According to this proposal, the clutch for the connection of the two gear elements to the drive shaft should each have a clutch drum which are arranged next to one another in the axial direction and to which only a single switchable centrifugal weight clutch element which is non-rotatably connected to the drive shaft is assigned, and for switching over the Coupling, coupling element and coupling drums can be displaced relative to one another in the axial direction such that the coupling element can optionally be arranged within one of the coupling drums assigned to it. Compared to known switchable centrifugal clutches (e.g. DE-OS 2 509 322), a centrifugal weight coupling element can be saved.

Eine besonders raumsparende Kupplung ergibt sich dann, wenn die Kupplungstrommeln mit jeweils einem der mit der Antriebswelle zu kuppelnden Getriebeelemente drehfest verbunden, in axialer Richtung zwischen diesen angeordnet und zusammen mit diesen auf der Antriebswelle drehbar gelagert sind.A particularly space-saving clutch is obtained when the clutch drums are rotatably connected to one of the gear elements to be coupled to the drive shaft, are arranged in the axial direction between them and are rotatably mounted together with them on the drive shaft.

Bei einer vorteilhaften Ausführungsform der erfindungsgemässen Kupplung ist ein die Antriebswelle in axialer Richtung durchsetzendes Schaltelement für das längs der Antriebswelle verschiebbare Fliehgewicht-Kupplungselement vorgesehen, so dass die Kupplungstrommeln axial unverschiebbar gestaltet werden können. In axialer Richtung kürzer baut jedoch eine Ausführungsform, bei der die Kupplungstrommeln relativ zu dem jeweils zugeordneten Getriebeelement unverdrehbar, jedoch in axialer Richtung verschiebbar sind und sich so wahlweise über dem Fliehgewicht-Kupplungselement anordnen lassen. Bei dieser Ausführungsform liegt der Schaltweg zwischen den beiden mit der Antriebswelle zu kuppelnden Getriebeelementen, so dass die Ausführungsform in axialer Richtung um die Schaltweglänge kürzer baut als die an erster Stelle beschriebene Ausführungsform, bei der jenseits des einen Getriebeelements soviel Platz benötigt wird, als dies der Bewegung des Schaltelements um die Schaltweglänge entspricht.In an advantageous embodiment of the clutch according to the invention, a switching element which passes through the drive shaft in the axial direction is provided for the centrifugal weight coupling element which can be displaced along the drive shaft, so that the clutch drums can be made axially immovable. However, an embodiment is shorter in the axial direction, in which the clutch drums are non-rotatable relative to the respectively assigned gear element, but are displaceable in the axial direction and can thus be arranged optionally above the centrifugal weight coupling element. In this embodiment, the shift path lies between the two gear elements to be coupled to the drive shaft, so that the embodiment is shorter in the axial direction by the shift path length than the embodiment described in the first place, in which as much space is required beyond the one gear element as that Movement of the switching element corresponds to the switching path length.

Bei der zweiten, vorstehend beschriebenen Ausführungsform ist es schliesslich zweckmässig, auf den Kupplungstrommeln ein mit diesen in axialer Richtung fest verbundenes Schaltelement drehbar zu lagern, um mit einem stillstehenden Schaltelement die Kupplungstrommeln hin- und herschieben zu können.In the second embodiment described above, it is finally expedient to rotatably mount a switching element firmly connected to the latter in the axial direction on the clutch drums, in order to be able to push the clutch drums back and forth with a stationary switching element.

Ein besonderer Vorteil der erfindungsgemässen Fliehkraftkupplung ist es, dass sie im wesentlichen aus auf dem Markt erhältlichen Serienteilen bekannter Fliehkraftkupplungen und daher kostengünstig hergestellt werden kann.A particular advantage of the centrifugal clutch according to the invention is that it essentially consists of series products available on the market len known centrifugal clutches and can therefore be manufactured inexpensively.

Weitere Merkmale, Vorteile und Einzelheiten der Erfindung ergeben sich aus den beigefügten Ansprüchen und/oder aus der beiliegenden zeichnerischen Darstellung und der nachfolgenden Beschreibung bevorzugter Ausführungsformen eines erfindungsgemässen Vibrationsgeräts, eines erfindungsgemässen Unwuchtsystems und einer erfindungsgemässen Fliehkraftkupplung; in der beiliegenden Zeichnung zeigen:

  • Fig. 1 eine Seitenansicht des als Bodenverdichtungsgerät ausgebildeten Vibrationsgeräts;
  • Fig. 2 eine Frontansicht dieses Bodenverdichtungsgeräts;
  • Fig. 3 eine schematische Darstellung des Unwuchtsystems und seines Antriebs bei Verwendung in dem Bodenverdichtungsgerät gemäss den Figuren 1 und 2;
  • Fig. 4a
  • Fig. 4b die Zustände grösster und kleinster Gesamtunwucht des Unwuchtsystems in einer schematischen Seitenansicht;
  • Fig. 5 einen Axialschnitt durch das Unwuchtsystem gemäss der Linie 5-5 in Figur 1;
  • Fig. 6 einen Querschnitt durch das Unwuchtsystem nach der Linie 6-6 in Figur 5;
  • Fig. 7 einen Axialschnitt durch eine erste Ausführungsform einer erfindungsgemässen Fliehkraftkupplung;
  • Fig. 8 einen Schnitt nach der Linie 8-8 in Figur 7, wobei jedoch nur das Fliehgewicht-Kupplungselement dargestellt wurde, und
  • Fig. 9 einen Axialschnitt durch eine zweite Ausführungsform der erfindungsgemässen Fliehkraftkupplung.
Further features, advantages and details of the invention emerge from the appended claims and / or from the attached drawing and the following description of preferred embodiments of a vibration device according to the invention, an unbalance system according to the invention and a centrifugal clutch according to the invention; in the attached drawing show:
  • 1 shows a side view of the vibration device designed as a soil compaction device;
  • Fig. 2 is a front view of this soil compacting device;
  • 3 shows a schematic illustration of the unbalance system and its drive when used in the soil compacting device according to FIGS. 1 and 2;
  • Fig. 4a
  • 4b shows the states of largest and smallest total unbalance of the unbalance system in a schematic side view;
  • 5 shows an axial section through the unbalance system along the line 5-5 in FIG. 1;
  • 6 shows a cross section through the unbalance system along the line 6-6 in FIG. 5;
  • 7 shows an axial section through a first embodiment of a centrifugal clutch according to the invention;
  • Fig. 8 is a section along the line 8-8 in Figure 7, but only the flyweight coupling element has been shown, and
  • Fig. 9 shows an axial section through a second embodiment of the centrifugal clutch according to the invention.

Die Figuren 1 und 2 zeigen ein erfindungsgemäss ausgebildetes Bodenverdichtungsgerät mit einer Rüttelplatte 10, auf der ein Unwuchtsystem 12 befestigt ist. Dieses wird von einem Verbrennungsmotor 14 über ein Antriebssystem 16 angetrieben. Ein vor dem Motor liegender Tank wurde mit 18 bezeichnet, ein an der Rüttelplatte 10 angebrachter Führungsgriff für das Gerät mit 20.Figures 1 and 2 show a soil compaction device designed according to the invention with a vibrating plate 10 on which an unbalance system 12 is attached. This is driven by an internal combustion engine 14 via a drive system 16. A tank in front of the engine was designated 18, a guide handle for the device attached to the vibrating plate 10 was designated 20.

Wie die Figur 3 erkennen lässt, treibt der Motor 14 über eine Antriebswelle 19 und eine Fliehkraftkupplung 22 wahlweise eine von zwei Riemenscheiben 24, 26 an. Zu diesem Zweck ist mit jeder der Riemenscheiben eine Kupplungstrommel 28 bzw. 30 verbunden, innerhalb welcher ein axial verschiebliches, mit der Antriebswelle 19 jedoch drehfest verbundenes Antriebselement 32 angeordnet ist, das sich bei Erhöhung der Motordrehzahl nach Art von Fliehgewichten reibungsschlüssig gegen diejenige Kupplungstrommel 28 bzw. 30 anlegt, innerhalb welcher es sich gerade befindet. Durch Verschieben des Antriebselements 32 lässt sich also vorwählen, welche der Kupplungstrommeln und damit welche der Riemenscheiben 24,26 angetrieben wird.As can be seen in FIG. 3, the motor 14 drives one of two pulleys 24, 26 via a drive shaft 19 and a centrifugal clutch 22. For this purpose, a clutch drum 28 or 30 is connected to each of the pulleys, within which is arranged an axially displaceable drive element 32, which is non-rotatably connected to the drive shaft 19 and which frictionally engages against that clutch drum 28 or, as the centrifugal weights increase, as the engine speed increases 30 creates within which it is currently located. By moving the drive element 32, it is thus possible to select which of the clutch drums and thus which of the pulleys 24, 26 is to be driven.

Diese Riemenscheiben sind über Keilriemen 34 bzw. 36 mit Riemenscheiben 38 und 40 verbunden, von denen die erste mit einer Hohlwelle 42 und die zweite mit einer hierzu konzentrischen Kernwelle 44 drehfest verbunden ist.These pulleys are connected via V-belts 34 and 36 to pulleys 38 and 40, the first of which is connected in a rotationally fixed manner to a hollow shaft 42 and the second to a core shaft 44 which is concentric therewith.

Die Hohlwelle 42 trägt eine grössere, die Kernwelle 44 eine kleinere Unwuchtmasse 46 bzw. 48, so dass die beiden Wellen und die beiden Unwuchtmassen zusammen das in den Figuren 1 und 2 mit 12 bezeichnete Unwuchtsystem bilden.The hollow shaft 42 carries a larger, the core shaft 44 a smaller unbalanced mass 46 or 48, so that the two shafts and the two unbalanced masses together form the unbalance system designated by 12 in FIGS. 1 and 2.

Da sich stets eine der beiden Kupplungstrommeln 28, 30 frei drehen kann, könnte an sich die mit der jeweils nicht angetriebenen Welle 42 bzw. 44 verbundene Unwuchtmasse 46 bzw. 48 jede beliebige Drehwinkelstellung gegenüber der jeweils angetriebenen Unwuchtmasse einnehmen. Nun sind jedoch Anschläge vorgesehen, die erfindungsgemäss so angeordnet sind, dass beim Antrieb der grossen Unwuchtmasse 46 die kleine Unwuchtmasse 48 nicht in irgendeiner beliebigen Stellung mitgenommen wird, sondern in einer Stellung, in der sie gegenüber der grossen Unwuchtmasse 46 geringfügig nacheilt, wie dies in Figur 4a dargestellt ist. Andererseits ist auch für den Zustand kleinster effektiver Gesamtunwucht, bei dem die kleine Unwuchtmasse 48 angetrieben wird, ein die grosse Unwuchtmasse 46 mitnehmender Anschlag vorgesehen, um zu erreichen, dass die grössere Unwuchtmasse 46 von Anfang an in derjenigen Stellung mitgenommen wird, in der sie der kleineren Unwuchtmasse 48 ungefähr diametral gegenüberliegt, wie dies in Figur 4b dargestellt wurde.Since one of the two clutch drums 28, 30 can always rotate freely, the unbalanced mass 46 or 48 connected to the respective non-driven shaft 42 or 44 could assume any rotational angle position relative to the driven unbalanced mass. However, stops are now provided, which are arranged according to the invention in such a way that when the large unbalanced mass 46 is driven, the small unbalanced mass 48 is not taken along in any position, but in a position in which it lags slightly compared to the large unbalanced mass 46, as shown in FIG Figure 4a is shown. On the other hand, even for the state of the smallest effective total unbalance, in which the small unbalanced mass 48 is driven, a stop carrying the large unbalanced mass 46 is provided, in order to ensure that the larger unbalanced mass 46 is carried in the position in which it was moved from the beginning smaller unbalanced mass 48 is approximately diametrically opposite, as was shown in Figure 4b.

Durch entsprechende Wahl der Durchmesser der Riemenscheiben 24, 26, 38, 40 kann erreicht werden, dass die Unwuchtmassen 46 und 48 mit unterschiedlichen Drehzahlen angetrieben werden und das Gerät bei grosser Gesamtunwucht mit niedriger Frequenz und bei kleiner Gesamtunwucht mit hoher Frequenz läuft.By appropriate selection of the diameters of the pulleys 24, 26, 38, 40 it can be achieved that the unbalanced masses 46 and 48 are driven at different speeds and the device runs at a low total frequency with a large total unbalance and at a high frequency with a small total unbalance.

Da sich erfindungsgemäss das ganze Getriebe 24, 26, 38, 40, 34, 36 auf einer Seite des Unwuchtsystems 12 befindet, wird auch nur eine einzige gehäuseartige Abdeckung benötigt, welche in den Figuren 1 und 2 mit 50 bezeichnet worden ist.Since, according to the invention, the entire transmission 24, 26, 38, 40, 34, 36 is located on one side of the unbalance system 12, only a single housing-like cover, which has been designated 50 in FIGS. 1 and 2, is required.

Die Figuren 5 und 6 zeigen eine bevorzugte Ausführungsform des erfindungsgemässen Unwuchtsystems 12, bei der die Hohlwelle 42 mit Hilfe von Rollenlagern 62 in einem Gehäuse 60 gelagert ist, während der Lagerung der Kernwelle 44 Gleitlager 64 dienen.FIGS. 5 and 6 show a preferred embodiment of the unbalance system 12 according to the invention, in which the hollow shaft 42 is mounted in a housing 60 with the aid of roller bearings 62, while slide bearings 64 serve to support the core shaft 44.

Erfindungsgemäss ist an der grossen Unwuchtmasse 46 eine Anschlagleiste 46a so angebracht, dass bei angetriebener Hohlwelle 42 bzw. angetriebener grosser Unwuchtmasse 46 die mitgenommene kleine Unwuchtmasse 48 in Drehrichtung geringfügig nacheilt, wie dies in Figur 6 mit ausgezogenen Linien dargestellt ist.According to the invention, a stop bar 46a is attached to the large unbalanced mass 46 such that when the hollow shaft 42 is driven or the large unbalanced mass 46 is driven, the small unbalanced mass 48 which is carried along lags slightly in the direction of rotation, as is shown in FIG. 6 with solid lines.

Ferner kann an einer der beiden Unwuchtmassen, bei der dargestellten Ausführungsform gleichfalls an der grossen Unwuchtmasse 46, eine weitere Anschlagleiste 46b vorgesehen sein, durch die die grosse Unwuchtmasse bei angetriebener Kernwelle 44 so mitgenommen wird, dass sie der kleinen Unwuchtmasse 48 diametral gegenübersteht. Dieser Zustand ist in Figur 6 strichpunktiert dargestellt.Furthermore, on one of the two unbalanced masses, in the illustrated embodiment also on the large unbalanced mass 46, a further stop bar 46b can be provided, through which the large unbalanced mass is driven when the core shaft 44 is driven so that it is diametrically opposed to the small unbalanced mass 48. This state is shown in dot-dash lines in FIG.

Bei dem erfindungsgemässen Vibrationsgerät werden also die beiden Zustände mit grösster und kleinster Gesamtunwucht mit einfachsten Mitteln herbeigeführt, so dass auf komplizierte Teile wie schaltbare Kupplungen im Unwuchtsystem selbst verzichtet werden kann.In the vibration device according to the invention the two states with the largest and smallest total unbalance are brought about with the simplest means, so that complicated parts such as switchable couplings in the unbalance system itself can be dispensed with.

Die Figur 7 zeigt eine mit einem Antriebsflansch 112 versehene Antriebswelle 110, auf der mit axial unverschiebbar gehaltenen Kugellagern 114 zwei Riemenscheibenkörper 116 und 118 drehbar, jedoch in axialer Richtung unverschiebbar gelagert sind. Jeder dieser Riemenscheibenkörper bildet eine Riemenscheibe 116a bzw. 118a und eine Kupplungstrommel 116b bzw. 118b, wobei die letzteren einander zugekehrt sind und erfindungsgemäss gleiche Innendurchmesser aufweisen.FIG. 7 shows a drive shaft 110 provided with a drive flange 112, on which two pulley bodies 116 and 118 are rotatably but axially non-displaceably mounted with ball bearings 114 held axially immovable. Each of these pulley bodies forms a pulley 116a or 118a and a clutch drum 116b or 118b, the latter facing each other and having the same inside diameter according to the invention.

In der Antriebswelle 110 ist eine Schaltachse 120 in Längsrichtung verschiebbar gehalten; sie trägt an ihrem äusseren Ende über ein in axialer Richtung unverschiebbar gehaltenes Kugellager 122 einen Schalthebel 124, während an ihrem inneren Ende ein Spannstift 126 befestigt ist, der beidseits der Schaltachse 120 Längsschlitze 128 in der Antriebswelle 110 durchgreift und in eine als ganzes mit 130 bezeichnete Kupplungsscheibe hineinragt. Diese Kupplungsscheibe ist als ganzes Teil auf dem Markt erhältlich, z.B. von der Firma Robert Scheuffele & Co., D-7120 Bietigheim-Bissingen.In the drive shaft 110, a switching axis 120 is held in the longitudinal direction; at its outer end it carries a shift lever 124 via a ball bearing 122 which is held immovably in the axial direction, while a tension pin 126 is fastened at its inner end, which extends through longitudinal slots 128 in the drive shaft 110 on both sides of the shift axis 120 and in one designated 130 as a whole Clutch disc protrudes. This clutch disc is available as a whole part on the market, e.g. from the company Robert Scheuffele & Co., D-7120 Bietigheim-Bissingen.

Die Kupplungsscheibe 130 besitzt einen Scheibenkörper 132, auf dem mit Kupplungsbelägen 134 versehene Fliehgewichte 136 mit Hilfe von die Fliehgewichte gegeneinander ziehenden Federn 138 so gehalten sind, dass sie sich relativ zum Scheibenkörper 132 nur in radialer Richtung nach aussen bewegen können.The clutch disc 130 has a disc body 132 on which the flyweights 136 provided with clutch linings 134 are held with the aid of springs 138 pulling the flyweights against each other in such a way that they can only move outward in the radial direction relative to the disc body 132.

Durch Verschieben des Schalthebels 124 in axialer Richtung lässt sich bei stehender oder sich nur mit Lehrlaufdrehzahl drehender Antriebswelle 110 die Kupplungsscheibe 130, die über den Spannstift 126 mit der Antriebswelle 110 drehfest verbunden ist, in axialer Richtung verschieben und so wahlweise innerhalb einer der Kupplungstrommeln 116b und 118b anordnen, so dass bei Erhöhung der Drehzahl der Antriebswelle 110 wahlweise eine der beiden Riemenscheiben 116a bzw. 118a angetrieben wird.By shifting the shift lever 124 in the axial direction, the clutch disc 130, which is non-rotatably connected to the drive shaft 110 via the dowel pin 126, can be shifted in the axial direction when the drive shaft 110 is at a standstill or only rotating at idling speed, and thus optionally within one of the clutch drums 116b and Arrange 118b so that when the speed of the drive shaft 110 increases, one of the two pulleys 116a or 118a is driven.

Bei der Variante der erfindungsgemässen Fliehkraftkupplung nach Figur 9 ist auf einer Antriebswelle 110' eine Kupplungsscheibe 130' fest angebracht, d.h. sie dreht sich mit der Antriebswelle und ist relativ zu dieser unverschiebbar. Mit Hilfe von auf der Antriebswelle 110' unverschiebbar gehaltenen Kugellagern 114' sind wieder zwei Riemenscheibenkörper 116' und 118' auf der Antriebswelle drehbar, gegenüber dieser jedoch unverschiebbar gelagert und sie bilden jeweils eine Riemenscheibe 116a' bzw. 118a'.In the variant of the centrifugal clutch according to the invention according to FIG. 9, a clutch disk 130 'is fixedly attached to a drive shaft 110', ie it rotates with the drive shaft and is immovable relative to the latter. With the aid of ball bearings 114 'which are held immovably on the drive shaft 110', two pulley bodies 116 ' and 118' are again rotatable on the drive shaft, but are mounted immovably relative to the latter and each form a pulley 116a 'and 118a'.

Bei dieser Ausführungsform sind jedoch die Kupplungstrommeln 116b' und 118b'nicht an die Riemenscheibenkörper angeformt, sondern als separate Teile ausgebildet, die über jeweils einen Kranz von Mitnehmerstiften 150' oder Mitnehmerkeilen 152' mit dem zugeordneten Riemenscheibenkörper drehfest verbunden sind, sich diesem gegenüber jedoch in axialer Richtung verschieben lassen.In this embodiment, however, the clutch drums 116b 'and 118b' are not formed on the pulley bodies, but are formed as separate parts, which are connected in a rotationally fixed manner to the assigned pulley body via a ring of driving pins 150 'or driving wedges 152', but are opposed to it in Have it shifted axially.

Auf jeder der Kupplungstrommeln 116b' bzw. 118b' ist ein Kugellager 122' befestigt, auf den Aussenringen dieser Kugellager wurde ein Schalthebel 124' befestigt, so dass sich mit seiner Hilfe wahlweise eine der beiden Kupplungstrommeln 116b' bzw. 118b' über die Kupplungsscheibe 130' schieben lässt.A ball bearing 122 'is fastened on each of the clutch drums 116b' and 118b ', a shift lever 124' was fastened on the outer rings of these ball bearings, so that one of the two clutch drums 116b 'and 118b' can be selectively positioned with its help over the clutch disc 130 'can be pushed.

Für vorstehend nicht beschriebene Teile der Ausführungsform nach Figur 9 wurden dieselben Bezugszeichen wie in den Figuren 7 und 8 verwendet, jedoch unter Beifügung eines Apostrophs.The same reference numerals as in FIGS. 7 and 8 were used for parts of the embodiment according to FIG. 9 not described above, but with the addition of an apostrophe.

Da bei der zweiten Ausführungsform der von den beiden Kupplungstrommeln in axialer Richtung benötigte Raum zwischen den beiden Riemenscheiben für die Unterbringung des Schaltwegs verwendet wird, baut die Ausführungsform nach Figur 9 in axialer Richtung kürzer als die Ausführungsform nach Figur 7.Since in the second embodiment the space between the two pulleys required by the two clutch drums in the axial direction is used to accommodate the shifting path, the embodiment according to FIG. 9 is shorter in the axial direction than the embodiment according to FIG. 7.

Claims (9)

1. A vibration machine for compacting materials, in particular an earth compacting machine; comprising an imbalance system (12) with two coaxial shafts (42, 44) drivable independently of each other, each of said shafts being connected with an unbalanced mass (46, 48) and a first or second gear element (38 or 40), also comprising a drive shaft (19) and at least one actuatable clutch (22) for selective driving of a third or fourth gear element (24 or 26), these elements being in drive connection with either the first or second gear element (38 or 40), respectively, characterized in that the four gear elements (24, 26, 38, 40) are all disposed on one side of the imbalance system (12) and shielded by a cover (50).
2. Vibration machine according to claim 1, characterized in that the unbalanced masses (46, 48) are adjacent to each other in axial direction and are disposable in at least two angular positions relative to each other to achieve different total imbalances, the unbalanced mass not coupled with the drive shaft being taken along by the other unbalanced mass in at least one of said angular positions, and that for the angular position, in which the unbalanced masses (46,48) have the smaller angular space between them, a stop (46a) taking along the second unbalanced mass (48) rotates together with the first, driven unbalanced mass (46), this stop being disposed such that the first unbalanced mass (46) is ahead of the second unbalanced mass (48).
3. Vibration machine according to claim 2, the unbalanced masses of which have different imbalance momentums, characterized in that the first unbalanced mass (46) has the greater imbalance momentum.
4. Vibration machine according to claims 2 or 3, characterized in that a stop (46b) taking along the first unbalanced mass (46) is provided for the angular position, in which the unbalanced masses have the greater angular distance between them.
5. Vibration machine according to any or several of the preceding claims, characterized in that the clutch for the third and fourth gear elements (24, 26 or 116a, 118a or 116a', 118a') has a clutch cylinder (16b, 18b or 116b', 118b') for each of said gear elements, these cylinders being disposed next to each other in axial direction and having only one single, actuatable flyweight clutch element (130 or 130') associated with them, this flyweight clutch element being secured to the drive shaft (19 or 110) such that they do not rotate relative to each other, and that for changing the clutch clutch element (130; 130') and clutch cylinders (116b, 118b; 116b', 118b') are movable relative to each other in axial direction such that the clutch element is selectively disposable inside one of the clutch cylinders associated with it.
6. Vibration machine according to claim 5, characterized in that the clutch cylinders (116b, 118b) are each secured to a gear element (116a, 118a) such that they do not rotate relative to each other, are disposed between these elements in axial direction and rotatably mounted together with these elements on the drive shaft (110).
7. Vibration machine according to claims 5 and 6, characterized in that an actuating element (120) penetrating the drive shaft (110) in axial direction is provided for the clutch element (130) displaceable along the drive shaft.
8. Vibration machine according to claim 6, characterized in that the clutch cylinders (116b', 118b') are not rotatable relative to the gear element (116a', 118a') associated with each cylinder, are displaceable in axial direction and disposable alternatingly over the clutch element (130').
9. Vibration machine according to claim 8, characterized in that an actuating element (124') is rotatably mounted on the clutch cylinders (116b', 118b') and rigidly connected with these in axial direction.
EP81106627A 1980-09-05 1981-08-26 Vibration device for compacting materials, especially for soil compaction Expired EP0047433B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81106627T ATE16719T1 (en) 1980-09-05 1981-08-26 VIBRATION DEVICE FOR MATERIAL COMPACTION, ESPECIALLY SOIL COMPACTION DEVICE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3033476A DE3033476C2 (en) 1980-09-05 1980-09-05 Vibration device for material compaction
DE3033476 1980-09-05

Publications (3)

Publication Number Publication Date
EP0047433A2 EP0047433A2 (en) 1982-03-17
EP0047433A3 EP0047433A3 (en) 1982-12-29
EP0047433B1 true EP0047433B1 (en) 1985-11-27

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EP81106627A Expired EP0047433B1 (en) 1980-09-05 1981-08-26 Vibration device for compacting materials, especially for soil compaction

Country Status (5)

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US (1) US4412757A (en)
EP (1) EP0047433B1 (en)
JP (1) JPS57119011A (en)
AT (1) ATE16719T1 (en)
DE (2) DE3033476C2 (en)

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Also Published As

Publication number Publication date
DE3033476A1 (en) 1982-03-25
US4412757A (en) 1983-11-01
EP0047433A3 (en) 1982-12-29
DE3173067D1 (en) 1986-01-09
EP0047433A2 (en) 1982-03-17
DE3033476C2 (en) 1985-03-21
JPS57119011A (en) 1982-07-24
ATE16719T1 (en) 1985-12-15

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