EP2140946A1 - Vibration creator - Google Patents

Vibration creator Download PDF

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Publication number
EP2140946A1
EP2140946A1 EP08011830A EP08011830A EP2140946A1 EP 2140946 A1 EP2140946 A1 EP 2140946A1 EP 08011830 A EP08011830 A EP 08011830A EP 08011830 A EP08011830 A EP 08011830A EP 2140946 A1 EP2140946 A1 EP 2140946A1
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EP
European Patent Office
Prior art keywords
piston
connecting rod
pin bearing
bearing
vibration generator
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.)
Granted
Application number
EP08011830A
Other languages
German (de)
French (fr)
Other versions
EP2140946B1 (en
Inventor
Christian Heichel
Albrecht Dr.-Ing. Kleibl
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.)
ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
Original Assignee
ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
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.)
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Application filed by ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH filed Critical ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
Priority to AT08011830T priority Critical patent/ATE481184T1/en
Priority to DE502008001334T priority patent/DE502008001334D1/en
Priority to EP08011830A priority patent/EP2140946B1/en
Priority to US12/456,842 priority patent/US8276471B2/en
Publication of EP2140946A1 publication Critical patent/EP2140946A1/en
Application granted granted Critical
Publication of EP2140946B1 publication Critical patent/EP2140946B1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/12—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving reciprocating 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
    • 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

  • the invention relates to a vibration generator comprising a linearly guided piston, which is connected via a connecting rod with a crankshaft, wherein the piston is connected to the connecting rod via a piston pin bearing and the crankshaft with the connecting rod via a crank pin.
  • vibration generators such as vibrators, vibrators or vibratory bears are used to bring profiles into the soil or to pull or to compact soil material.
  • the soil is stimulated by vibration and thus reaches a "pseudo-liquid" state.
  • static load By static load the pile can then be pressed into the ground.
  • the vibration is characterized by a linear movement and is regularly generated by pairwise counter-rotating imbalances within a Vibratorgetriebes.
  • the rotating imbalance masses cause a force effect that describes a sinusoid over time.
  • Such a drive acts offset in time alternately in and against the direction of advance.
  • the propulsion direction is ultimately determined by static forces such as dead weight and static loads. Without the superposition of Vibration with static forces, the pile would not move forward, but only swing back and forth.
  • crank gear The directional operation of the crank gear is based on the fact that the connecting rod is designed to be small relative to the crank radius. On the other hand, however, the crank radius itself must be minimized in order to limit the reactive power which increases quadratically with the piston travel.
  • the connecting rod due to the geometry of the connecting rod is longer than the sum of the radii of crank pin and piston pin bearing perform. However, these bearings must be sized accordingly large due to the applied forces.
  • the connecting rod length and crank radius must be selected to be correspondingly large; The resulting large reactive power can be countered by a structurally large moment of inertia of the crankshaft.
  • a disadvantage of this approach is that the vibrator is large and heavy dimensions, resulting in unnecessarily high speeds and friction losses.
  • the invention aims to remedy this situation.
  • the invention has for its object to provide a vibration generator in the manner of a sliding-crank mechanism, which has a small size and in which, moreover, the achieved speeds and friction losses are reduced.
  • This object is achieved in that the crank pin bearing is disposed within the piston pin bearing.
  • a vibration generator in the manner of a sliding-crank mechanism which has a small size and in which the achieved speeds and friction losses are reduced.
  • the piston is designed such that the crankshaft is arranged centrally of the piston. Since the connecting rod forces in the middle of the piston attack, the bearing forces between the piston and the cylinder in which the piston is guided reduce.
  • the connecting rod is formed as a disc which is movably arranged in a sliding bearing.
  • the "connecting rod length" here is independent of the bearing diameters and is limited only by the crank radius.
  • crank pin bearings are arranged diametrically opposite each other within the piston pin bearing.
  • the piston pin bearing is slidably disposed within the crank pin bearing.
  • the connecting rod on means for relative change in position of the crank pin bearing.
  • the means for relative position change comprise at least one hydraulic cylinder arranged orthogonal to the crank pin in the connecting rod is. Through the hydraulic cylinder, the crank pin bearing in the connecting rod is displaceable.
  • At least one spring-mounted hammer is arranged within the piston.
  • the force is amplified at the lower reversal point of the piston and reduced at the upper reversal point.
  • the spring can be designed so that the striking piece reaches the piston housing and thus supported in the driving direction by hard impacts.
  • the vibration generator selected as an exemplary embodiment essentially comprises a piston 1 which receives a connecting rod 2 movably mounted in a slide bearing, in which a crankshaft 3 is arranged.
  • the piston 1 is designed as a substantially symmetrical body. At a substantially cuboid-shaped center piece 13 close on both sides cylindrically shaped end pieces 11, 12 at. Within the center piece 13, a piston pin bearing 14 is centrally introduced, which receives a circular connecting rod 2.
  • the cylindrical end pieces 11, 12 are solid in the embodiment.
  • the circular executed conrod 2 has a depth which corresponds substantially to the depth of the center piece 13 of the piston 1.
  • two crank pin positions 21 for receiving the crank pin 31 of the crankshaft 3 are introduced into the connecting rod disc diametrically opposite one another.
  • crankshaft 3 If the crankshaft 3 is set in rotation, so takes place via the connecting rod 2, an up and down movement of the linearly guided piston 1.
  • crankpin 31 of the crankshaft 3 is connected to the connecting rod 2 via a crankpin bearing 21;
  • piston 1 is connected to the connecting rod 2 via a piston pin, which is arranged in the piston pin bearing 14 of the connecting rod 2.
  • piston pin bearing 14 is enlarged so far that it goes beyond the crank pin bearing 21.
  • the piston is simultaneously extended so that the crankshaft is centered.
  • the connecting rod 2 Since the connecting rod forces act in the middle of the piston 1, the bearing forces between the piston 1 and the - not shown - cylinder in which the piston 1 is guided reduce.
  • the connecting rod 2 is formed as a disc which moves alternately in a sliding bearing. Due to the plain bearing virtually no noise takes place. Instead of the sliding bearing and roller bearings, such as needle roller bearings can be provided.
  • the connecting rod length is independent of the bearing diameters and is limited only by the crank radius. If the crankshaft is mounted in the lower crank pin bearing 21 of the connecting rod 2, a direction reversal of the working direction of the piston 1 is effected.
  • the end pieces 11, 12 of the piston 1 are hollow.
  • a cylindrically shaped mass piece 15 is arranged.
  • a hammer 16 is introduced, which is spring-mounted within the end piece 12 via a helical spring 17.
  • the hammer 16 is mushroom-shaped in the embodiment, wherein the mushroom head 161 rests on the coil spring 17, in which the stem 162 of the hammer 16 engages.
  • the spring 17 is formed such that the stem 162 of the striking piece 17 reaches the housing of the end piece 12 and supported in the driving direction by hard impacts.
  • crank pin bearing a slot in the connecting rod 2, in which a crank pin bearing receiving slider is arranged.
  • a crank pin bearing receiving slider On both sides of the slider hydraulic cylinders are provided, via which the slider is movable in the slot.
  • the crank pin bearing is displaceable in the respective end positions within the slot, whereby a reversal of direction of the working direction of the vibrator without further conversion measures can be achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Surgical Instruments (AREA)
  • Ultra Sonic Daignosis Equipment (AREA)
  • Transmission Devices (AREA)
  • Reciprocating Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Abstract

The generator has a piston (1) guided in a linear manner and connected with a crank shaft (3) via a connecting rod. The piston is connected with the connecting rod via a piston pin bearing. The crankshaft is connected with the connecting rod via a crank journal (31), and crank journal bearings (21) are movably arranged within the piston pin bearing. The connecting rod is designed as a connecting rod disk (2), which is movably arranged in a slide bearing. A resiliently mounted impact piece is arranged within the piston.

Description

Die Erfindung betrifft einen Schwingungserzeuger, umfassend einen linear geführten Kolben, der über ein Pleuel mit einer Kurbelwelle verbunden ist, wobei der Kolben mit dem Pleuel über ein Kolbenbolzenlager und die Kurbelwelle mit dem Pleuel über einen Kurbelzapfen verbunden ist.The invention relates to a vibration generator comprising a linearly guided piston, which is connected via a connecting rod with a crankshaft, wherein the piston is connected to the connecting rod via a piston pin bearing and the crankshaft with the connecting rod via a crank pin.

Im Bauwesen werden Schwingungserzeuger wie Vibratoren, Rüttler oder Vibrationsbären verwendet, um Profile in den Boden einzubringen oder zu ziehen oder auch um Bodenmaterial zu verdichten. Der Boden wird durch Vibration angeregt und erreicht so einen "pseudoflüssigen" Zustand. Durch statische Auflast kann das Rammgut dann in den Baugrund gedrückt werden. Die Vibration ist gekennzeichnet durch eine lineare Bewegung und wird regelmäßig durch paarweise gegenläufig rotierende Unwuchten innerhalb eines Vibratorgetriebes generiert. Die rotierenden Unwuchtmassen bewirken eine Kraftwirkung, die über der Zeit eine Sinuskurve beschreibt. Ein solcher Antrieb wirkt zeitlich versetzt abwechselnd in und entgegen der Vortriebsrichtung. Die Vortriebsrichtung wird letztlich durch statische Kräfte wie Eigengewicht und statische Auflasten bestimmt. Ohne die Überlagerung der Schwingung mit statischen Kräften würde sich das Rammgut nicht vorwärts bewegen, sondern nur vor- und zurückschwingen.In construction, vibration generators such as vibrators, vibrators or vibratory bears are used to bring profiles into the soil or to pull or to compact soil material. The soil is stimulated by vibration and thus reaches a "pseudo-liquid" state. By static load the pile can then be pressed into the ground. The vibration is characterized by a linear movement and is regularly generated by pairwise counter-rotating imbalances within a Vibratorgetriebes. The rotating imbalance masses cause a force effect that describes a sinusoid over time. Such a drive acts offset in time alternately in and against the direction of advance. The propulsion direction is ultimately determined by static forces such as dead weight and static loads. Without the superposition of Vibration with static forces, the pile would not move forward, but only swing back and forth.

Zur Überwindung der vorgenannten Nachteile wird in der DE 196 39 786 A1 vorgeschlagen, eine drehbar gelagerte Unwuchtmasse in Art eines Kurbelgetriebes senkrecht zu ihrer Antriebswelle um eine definierte Exzentrität versetzt anzuordnen. Aufgrund der Exzentrität führt die Unwuchtmasse bei konstanter Winkelgeschwindigkeit des Antriebs eine Rotation mit ungleichmäßiger Winkelgeschwindigkeit aus, so dass sich der Betrag der Fliehkraft in Abhängigkeit von deren Richtung verändert. Einen vergleichsweise einfacheren Aufbau zeigt das in der DE 196 39 787 A1 beschriebene Schubkurbelgetriebe. Derartige Schubkurbeigetriebe haben einen einfachen Aufbau und weisen zudem eine geringe Lärmentwicklung auf. Nachteilig an den vorbekannten Systemen ist jedoch, dass die geometrischen Verhältnisse sich als sehr problematisch erweisen. Die gerichtete Arbeitsweise des Schubkurbelgetriebes beruht darauf, dass die Pleuelstange relativ zum Kurbelradius klein ausgeführt ist. Dem gegenüber muss der Kurbelradius selbst jedoch minimiert werden, um die Blindleistung, die quadratisch mit dem Kolbenweg ansteigt, zu begrenzen. Darüber hinaus ist aufgrund der Geometrie der Pleuel länger als die Summe der Radien von Kurbelzapfen- und Kolbenbolzenlager auszuführen. Diese Lager müssen jedoch aufgrund der anliegenden Kräfte entsprechend groß dimensioniert werden. Zur Erfüllung der vorgenannten konträren Anforderungen sind Pleuellänge und Kurbelradius entsprechend groß zu wählen; der resultierend großen Blindleistung kann durch ein konstruktiv großes Massenträgheitsmoment der Kurbelwelle begegnet werden. Nachteilig an dieser Vorgehensweise ist, dass der Schwingungserzeuger groß und schwer dimensioniert ist, wobei sich unnötig große Geschwindigkeiten und Reibleistungen ergeben.To overcome the aforementioned disadvantages is in the DE 196 39 786 A1 proposed to arrange a rotatably mounted unbalanced mass in the manner of a crank mechanism perpendicular to its drive shaft offset by a defined eccentricity. Due to the eccentricity, the imbalance mass at constant angular velocity of the drive performs a rotation with uneven angular velocity, so that the amount of centrifugal force changes depending on their direction. A comparatively simpler structure shows that in the DE 196 39 787 A1 described crank mechanism. Such Schubkurbeigetriebe have a simple structure and also have a low noise. A disadvantage of the known systems, however, is that the geometric relationships prove to be very problematic. The directional operation of the crank gear is based on the fact that the connecting rod is designed to be small relative to the crank radius. On the other hand, however, the crank radius itself must be minimized in order to limit the reactive power which increases quadratically with the piston travel. In addition, due to the geometry of the connecting rod is longer than the sum of the radii of crank pin and piston pin bearing perform. However, these bearings must be sized accordingly large due to the applied forces. To meet the above-mentioned contrary requirements, the connecting rod length and crank radius must be selected to be correspondingly large; The resulting large reactive power can be countered by a structurally large moment of inertia of the crankshaft. A disadvantage of this approach is that the vibrator is large and heavy dimensions, resulting in unnecessarily high speeds and friction losses.

Hier will die Erfindung Abhilfe schaffen. Der Erfindung liegt die Aufgabe zugrunde, einen Schwingungserzeuger in Art eines Schubkurbelgetriebes zu schaffen, der eine geringe Baugröße aufweist und bei dem darüber hinaus die erzielten Geschwindigkeiten und Reibleistungen verringert sind. Gemäß der Erfindung wird diese Aufgabe dadurch gelöst, dass das Kurbelzapfenlager innerhalb des Kolbenbolzenlagers angeordnet ist.The invention aims to remedy this situation. The invention has for its object to provide a vibration generator in the manner of a sliding-crank mechanism, which has a small size and in which, moreover, the achieved speeds and friction losses are reduced. According to the invention This object is achieved in that the crank pin bearing is disposed within the piston pin bearing.

Mit der Erfindung ist ein Schwingungserzeuger in Art eines Schubkurbelgetriebes geschaffen, der eine geringe Baugröße aufweist und bei dem die erzielten Geschwindigkeiten und Reibleistungen verringert sind.With the invention, a vibration generator in the manner of a sliding-crank mechanism is provided, which has a small size and in which the achieved speeds and friction losses are reduced.

In Weiterbildung der Erfindung ist der Kolben derart ausgebildet, dass die Kurbelwelle mittig des Kolbens angeordnet ist. Da die Pleuelkräfte in der Mitte des Kolbens angreifen reduzieren sich die Lagerkräfte zwischen dem Kolben und dem Zylinder, in dem der Kolben geführt ist.In a further development of the invention, the piston is designed such that the crankshaft is arranged centrally of the piston. Since the connecting rod forces in the middle of the piston attack, the bearing forces between the piston and the cylinder in which the piston is guided reduce.

In Ausgestaltung der Erfindung ist das Pleuel als Scheibe ausgebildet, die in einem Gleitlager beweglich angeordnet ist. Die "Pleuellänge" ist hier unabhängig von den Lagerdurchmessern und wird nur vom Kurbelradius begrenzt.In an embodiment of the invention, the connecting rod is formed as a disc which is movably arranged in a sliding bearing. The "connecting rod length" here is independent of the bearing diameters and is limited only by the crank radius.

In weiterer Ausgestaltung der Erfindung sind innerhalb des Kolbenbolzenlagers zwei Kurbelzapfenlager diametral zueinander angeordnet. Durch Anordnung der Kurbelwelle in dem gegenüberliegenden Kurbelbolzenlager ist eine Richtungsumkehr des Schwingungserzeugers ermöglicht.In a further embodiment of the invention, two crank pin bearings are arranged diametrically opposite each other within the piston pin bearing. By arranging the crankshaft in the opposite crank pin bearing a reversal of the direction of the vibrator is possible.

In alternativer Ausgestaltung der Erfindung ist das Kolbenbolzenlager innerhalb des Kurbelzapfenlagers verschiebbar angeordnet. Hierdurch ist eine Veränderung der relativen Position zum Mittelpunkt der Pleuelscheibe ermöglicht, wodurch wiederum eine Richtungsumkehr des Schwingungserzeugers erzielbar ist.In an alternative embodiment of the invention, the piston pin bearing is slidably disposed within the crank pin bearing. As a result, a change in the relative position to the center of the connecting rod is possible, which in turn a reversal of direction of the vibrator can be achieved.

In Weiterbildung der Erfindung weist die Pleuelscheibe Mittel zur relativen Lageänderung des Kurbelbolzenlagers auf. Hierdurch ist eine einfache Richtungsumkehr sowie eine Einstellung der Amplitude des Schwingungserzeugers erzielbar.In development of the invention, the connecting rod on means for relative change in position of the crank pin bearing. As a result, a simple reversal of direction and an adjustment of the amplitude of the vibrator can be achieved.

Bevorzugt umfassen die Mittel zur relativen Lageänderung wenigstens einen Hydraulikzylinder, der orthogonal zum Kurbelzapfen in der Pleuelscheibe angeordnet ist. Durch den Hydraulikzylinder ist das Kurbelzapfenlager in der Pleuelscheibe verschiebbar.Preferably, the means for relative position change comprise at least one hydraulic cylinder arranged orthogonal to the crank pin in the connecting rod is. Through the hydraulic cylinder, the crank pin bearing in the connecting rod is displaceable.

In weiterer Ausgestaltung der Erfindung ist innerhalb des Kolbens wenigstens ein federnd gelagertes Schlagstück angeordnet. Hierdurch wird die Kraftwirkung am unteren Umkehrpunkt des Kolbens verstärkt und am oberen Umkehrpunkt reduziert. Die Feder kann dabei so ausgebildet sein, dass das Schlagstück das Kolbengehäuse erreicht und so in Rammrichtung durch harte Schläge unterstützt.In a further embodiment of the invention, at least one spring-mounted hammer is arranged within the piston. As a result, the force is amplified at the lower reversal point of the piston and reduced at the upper reversal point. The spring can be designed so that the striking piece reaches the piston housing and thus supported in the driving direction by hard impacts.

Andere Weiterbildungen und Ausgestaltungen der Erfindung sind in den übrigen Unteransprüchen angegeben. Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen dargestellt und wird nachfolgend im Einzelnen beschrieben. Es zeigen:

Figur 1
die dreidimensionale Darstellung eines Schwingungserzeugers;
Figur 2
die Darstellung eines Schwingungserzeugers in einer weiteren Ausführungsform und
Figur 3
die schematische Darstellung eines Schubkurbelgetriebes (Stand der Technik).
Other developments and refinements of the invention are specified in the remaining subclaims. An embodiment of the invention is illustrated in the drawings and will be described in detail below. Show it:
FIG. 1
the three-dimensional representation of a vibrator;
FIG. 2
the representation of a vibrator in a further embodiment and
FIG. 3
the schematic representation of a sliding-crank mechanism (prior art).

Der als Ausführungsbeispiel gewählte Schwingungserzeuger umfasst im Wesentlichen einen Kolben 1, der eine in einem Gleitlager beweglich gelagerte Pleuelscheibe 2 aufnimmt, in der wiederum eine Kurbelwelle 3 angeordnet ist.The vibration generator selected as an exemplary embodiment essentially comprises a piston 1 which receives a connecting rod 2 movably mounted in a slide bearing, in which a crankshaft 3 is arranged.

Der Kolben 1 ist als im Wesentlichen symmetrischer Körper ausgebildet. An ein im Wesentlichen quaderförmig ausgebildetes Mittelstück 13 schließen sich beidseitig zylinderförmig ausgebildete Endstücke 11, 12 an. Innerhalb des Mittelstücks 13 ist zentrisch ein Kolbenbolzenlager 14 eingebracht, das eine kreisrunde Pleuelscheibe 2 aufnimmt. Die zylinderförmigen Endstücke 11, 12 sind im Ausführungsbeispiel massiv ausgebildet.The piston 1 is designed as a substantially symmetrical body. At a substantially cuboid-shaped center piece 13 close on both sides cylindrically shaped end pieces 11, 12 at. Within the center piece 13, a piston pin bearing 14 is centrally introduced, which receives a circular connecting rod 2. The cylindrical end pieces 11, 12 are solid in the embodiment.

Die kreisrund ausgeführte Pleuelscheibe 2 weist eine Tiefe auf, die im Wesentlichen der Tiefe des Mittelstücks 13 des Kolbens 1 entspricht. Exzentrisch sind in die Pleuelscheibe diametral zueinander zwei Kurbelzapfenlagen 21 zur Aufnahme des Kurbelzapfens 31 der Kurbelwelle 3 eingebracht.The circular executed conrod 2 has a depth which corresponds substantially to the depth of the center piece 13 of the piston 1. Eccentrically, two crank pin positions 21 for receiving the crank pin 31 of the crankshaft 3 are introduced into the connecting rod disc diametrically opposite one another.

Die Funktionsweise des Schwingungserzeugers gemäß Figur 1 wird nachfolgend in Gegenüberstellung eines aus dem Stand der Technik bekannten Schubkurbelgetriebes gemäß Figur 3 erläutert: Wird die Kurbelwelle 3 in Rotation versetzt, so erfolgt über das Pleuel 2 eine Auf- und Abbewegung des linear geführten Kolbens 1. Im Stand der Technik gemäß Figur 3 ist der Kurbelzapfen 31 der Kurbelwelle 3 über ein Kurbelzapfenlager 21 mit dem Pleuel 2 verbunden; der Kolben 1 ist über einen Kolbenbolzen, der in dem Kolbenbolzenlager 14 des Pleuels 2 angeordnet ist, mit dem Pleuel 2 verbunden. Im Ausführungsbeispiel gemäß Figur 1 ist das Kolbenbolzenlager 14 soweit vergrößert, dass es über das Kurbelzapfenlager 21 hinausgeht. Der Kolben ist gleichzeitig so verlängert, dass die Kurbelwelle mittig angeordnet ist. Da die Pleuelkräfte in der Mitte des Kolbens 1 angreifen, reduzieren sich die Lagerkräfte zwischen dem Kolben 1 und dem - nicht dargestellten - Zylinder, in dem der Kolben 1 geführt ist. Der Pleuel 2 ist dabei als Scheibe ausgebildet, die sich in einem Gleitlager alternierend bewegt. Durch das Gleitlager findet praktisch keine Geräuschentwicklung statt. Anstelle des Gleitlagers können auch Wälzlager, beispielsweise Nadellager vorgesehen sein. Die Pleuellänge ist unabhängig von den Lagerdurchmessern und wird nur vom Kurbelradius begrenzt. Wird die Kurbelwelle in dem unteren Kurbelzapfenlager 21 der Pleuelscheibe 2 gelagert, ist eine Richtungsumkehr der Arbeitsrichtung des Kolbens 1 bewirkt.The operation of the vibrator according to FIG. 1 is subsequently in comparison of a known from the prior art crank gear according to FIG. 3 explains: If the crankshaft 3 is set in rotation, so takes place via the connecting rod 2, an up and down movement of the linearly guided piston 1. In the prior art according to FIG. 3 the crankpin 31 of the crankshaft 3 is connected to the connecting rod 2 via a crankpin bearing 21; the piston 1 is connected to the connecting rod 2 via a piston pin, which is arranged in the piston pin bearing 14 of the connecting rod 2. In the embodiment according to FIG. 1 the piston pin bearing 14 is enlarged so far that it goes beyond the crank pin bearing 21. The piston is simultaneously extended so that the crankshaft is centered. Since the connecting rod forces act in the middle of the piston 1, the bearing forces between the piston 1 and the - not shown - cylinder in which the piston 1 is guided reduce. The connecting rod 2 is formed as a disc which moves alternately in a sliding bearing. Due to the plain bearing virtually no noise takes place. Instead of the sliding bearing and roller bearings, such as needle roller bearings can be provided. The connecting rod length is independent of the bearing diameters and is limited only by the crank radius. If the crankshaft is mounted in the lower crank pin bearing 21 of the connecting rod 2, a direction reversal of the working direction of the piston 1 is effected.

Im Ausführungsbeispiel gemäß Figur 2 sind die Endstücke 11, 12 des Kolbens 1 hohl ausgebildet. Innerhalb des Endstücks 11 ist ein zylindrisch ausgebildetes Massestück 15 angeordnet. Innerhalb des gegenüberliegend angeordneten Endstücks 13 des Kolbens 1 ist ein Schlagstück 16 eingebracht, welches über eine Schraubenfeder 17 innerhalb des Endstücks 12 federnd gelagert ist. Das Schlagstück 16 ist im Ausführungsbeispiel pilzartig ausgebildet, wobei der Pilzkopf 161 auf der Schraubenfeder 17 aufliegt, in welche der Stengel 162 des Schlagstücks 16 eingreift. Die Feder 17 ist derart ausgebildet, dass der Stengel 162 des Schlagstücks 17 das Gehäuse des Endstücks 12 erreicht und in Rammrichtung durch harte Schläge unterstützt.In the embodiment according to FIG. 2 the end pieces 11, 12 of the piston 1 are hollow. Within the end piece 11, a cylindrically shaped mass piece 15 is arranged. Within the oppositely disposed end piece 13 of the piston 1, a hammer 16 is introduced, which is spring-mounted within the end piece 12 via a helical spring 17. The hammer 16 is mushroom-shaped in the embodiment, wherein the mushroom head 161 rests on the coil spring 17, in which the stem 162 of the hammer 16 engages. The spring 17 is formed such that the stem 162 of the striking piece 17 reaches the housing of the end piece 12 and supported in the driving direction by hard impacts.

In einer - nicht dargestellten - weiteren Ausgestaltung der Erfindung ist es auch denkbar, anstelle mehrerer Kurbelzapfenlager ein Langloch in die Pleuelscheibe 2 einzubringen, in dem ein ein Kurbelzapfenlager aufnehmendes Gleitstück angeordnet ist. Beidseitig des Gleitstücks sind Hydraulikzylinder vorgesehen, über welche das Gleitstück in dem Langloch bewegbar ist. Über die Hydraulikzylinder ist das Kurbelzapfenlager in die jeweiligen Endlagen innerhalb des Langlochs verschiebbar, wodurch eine Richtungsumkehr der Arbeitsrichtung des Schwingungserzeugers ohne weitere Umbaumaßnahmen erzielbar ist.In a - not shown - further embodiment of the invention, it is also conceivable to introduce instead of several crank pin bearing a slot in the connecting rod 2, in which a crank pin bearing receiving slider is arranged. On both sides of the slider hydraulic cylinders are provided, via which the slider is movable in the slot. About the hydraulic cylinder, the crank pin bearing is displaceable in the respective end positions within the slot, whereby a reversal of direction of the working direction of the vibrator without further conversion measures can be achieved.

Claims (8)

Schwingungserzeuger, umfassend einen linear geführten Kolben, der über ein Pleuel mit einer Kurbelwelle verbunden ist, wobei der Kolben mit dem Pleuel über ein Kolbenbolzenlager und die Kurbelwelle mit dem Pleuel über einen Kurbelzapfen verbunden ist, dadurch gekennzeichnet, dass das Kurbelzapfenlager (21) innerhalb des Kolbenbolzenlagers (14) angeordnet ist.A vibration generator, comprising a linearly guided piston, which is connected via a connecting rod with a crankshaft, wherein the piston is connected to the connecting rod via a piston pin bearing and the crankshaft with the connecting rod via a crank pin, characterized in that the crank pin bearing (21) within the Piston pin bearing (14) is arranged. Schwingungserzeuger nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass der Kolben (1) derart ausgebildet ist, dass die Kurbelwelle (3) mittig des Kolbens (1) angeordnet ist.Vibration generator according to one of the preceding claims, characterized in that the piston (1) is designed such that the crankshaft (3) is arranged centrally of the piston (1). Schwingungserzeuger nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Pleuel (2) als Scheibe ausgebildet ist, die in einem Gleitlager beweglich angeordnet ist.Vibration generator according to claim 1 or 2, characterized in that the connecting rod (2) is designed as a disc which is movably arranged in a slide bearing. Schwingungserzeuger nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass innerhalb des Kolbenbolzenlagers (14) zwei Kurbelzapfenlager (21) diametral zueinander angeordnet sind.Vibration generator according to one of claims 1 to 3, characterized in that within the piston pin bearing (14) two crankpin bearings (21) are arranged diametrically opposite each other. Schwingungserzeuger nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass das Kurbelzapfenlager (31) innerhalb des Kolbenbolzenlagers (14) verschiebbar angeordnet ist.Vibration generator according to one of claims 1 to 3, characterized in that the crank pin bearing (31) within the piston pin bearing (14) is arranged displaceably. Schwingungserzeuger nach Anspruch 5, dadurch gekennzeichnet, dass das Pleuel (2) Mittel zur relativen Lageänderung des Kurbelzapfenlagers (21) aufweist.Vibration generator according to claim 5, characterized in that the connecting rod (2) has means for relative change in position of the crank pin bearing (21). Schwingungserzeuger nach Anspruch 6, dadurch gekennzeichnet, dass die Mittel zur relativen Lageänderung einen Hydraulikzylinder umfassen, der orthogonal zum Kurbelzapfen (31) angeordnet ist.Vibration generator according to claim 6, characterized in that the means for relative position change comprise a hydraulic cylinder which is arranged orthogonal to the crank pin (31). Schwingungserzeuger nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass innerhalb des Kolbens (1) ein federnd gelagertes Schlagstück angeordnet ist.Vibration generator according to one of the preceding claims, characterized in that within the piston (1) a spring-mounted hammer is arranged.
EP08011830A 2008-07-01 2008-07-01 Vibration creator Not-in-force EP2140946B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AT08011830T ATE481184T1 (en) 2008-07-01 2008-07-01 VIBRATION GENERATOR
DE502008001334T DE502008001334D1 (en) 2008-07-01 2008-07-01 vibrator
EP08011830A EP2140946B1 (en) 2008-07-01 2008-07-01 Vibration creator
US12/456,842 US8276471B2 (en) 2008-07-01 2009-06-23 Vibration generator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08011830A EP2140946B1 (en) 2008-07-01 2008-07-01 Vibration creator

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EP2140946A1 true EP2140946A1 (en) 2010-01-06
EP2140946B1 EP2140946B1 (en) 2010-09-15

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EP08011830A Not-in-force EP2140946B1 (en) 2008-07-01 2008-07-01 Vibration creator

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DE102010010037B4 (en) * 2010-03-03 2019-10-31 Bomag Gmbh Continuously adjustable vibration exciter

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DE29707017U1 (en) * 1997-04-18 1997-07-10 Wacker-Werke Gmbh & Co Kg, 85084 Reichertshofen Ramming device for soil compaction
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DE19639786A1 (en) 1996-09-27 1998-04-02 Univ Freiberg Bergakademie Mechanical vibration system with rotating unbalanced masses

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US4607980A (en) * 1984-12-06 1986-08-26 Spetsialnoe Konstruktorskoe Bjuro "Stroimekhanizatsia" Apparatus for compacting soil, concrete and like materials
DE19639787A1 (en) 1996-09-27 1998-04-02 Univ Freiberg Bergakademie Vibration system with mechanically moved unbalanced mass
DE19639786A1 (en) 1996-09-27 1998-04-02 Univ Freiberg Bergakademie Mechanical vibration system with rotating unbalanced masses
DE29707017U1 (en) * 1997-04-18 1997-07-10 Wacker-Werke Gmbh & Co Kg, 85084 Reichertshofen Ramming device for soil compaction

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US8276471B2 (en) 2012-10-02
ATE481184T1 (en) 2010-10-15
EP2140946B1 (en) 2010-09-15
US20100000351A1 (en) 2010-01-07
DE502008001334D1 (en) 2010-10-28

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