EP1967292A2 - Oscillation exciter - Google Patents

Oscillation exciter Download PDF

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Publication number
EP1967292A2
EP1967292A2 EP07016396A EP07016396A EP1967292A2 EP 1967292 A2 EP1967292 A2 EP 1967292A2 EP 07016396 A EP07016396 A EP 07016396A EP 07016396 A EP07016396 A EP 07016396A EP 1967292 A2 EP1967292 A2 EP 1967292A2
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EP
European Patent Office
Prior art keywords
rotor shaft
stator housing
shaft
stator
locking
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
EP07016396A
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German (de)
French (fr)
Other versions
EP1967292B1 (en
EP1967292A3 (en
Inventor
Christian Heichel
Albrecht Dr. Ing. Kleibl
Rolf Winzen
Frank Hense
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ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
Original Assignee
ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
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Publication of EP1967292A3 publication Critical patent/EP1967292A3/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
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
    • E02D3/054—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil involving penetration of the soil, e.g. vibroflotation
    • 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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
    • E02D7/18—Placing by vibrating

Definitions

  • the invention relates to a vibration generator according to the preamble of claim 1.
  • the invention further relates to a pivot motor for use in a vibration exciter according to the preamble of claim. 7
  • 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.
  • the vibration is characterized by a linear movement and is generated by pairwise counter-rotating imbalances within a Vibratorgetriebes.
  • Vibration generators are characterized by the installed unbalance (referred to in the art as "static torque") and the maximum speed.
  • the amplitude, frequency or force direction of the vibrator In order to achieve optimal propulsion or good compaction depending on the pile material and soil properties, it is desirable to control the amplitude, frequency or force direction of the vibrator.
  • the Adjustment of the vibration is expediently via a change of the static torque or the phase position of the imbalances.
  • the vibration When starting the vibration exciter the natural frequency range of the soil is traversed. If the ground is excited in the resonance range, the amplitude of the floor vibration becomes very large, which can lead to damage to adjacent buildings. Therefore, it is necessary that act when starting the vibrator no imbalance.
  • the invention aims to remedy this situation.
  • the invention is based on the object to provide a vibration generator with a rotary vane pivot motor, in which the effective unbalance and thus the vibration is adjustable and in which moreover leaks over a longer period are avoided. According to the invention, this object is solved by the features of the characterizing part of patent claim 1.
  • a vibration exciter in which the effective unbalance and thus the vibration is adjustable and in which moreover leaks over a longer period of time are avoided.
  • the use of the rotary vane pivot motor allows a relative adjustment of the imbalance masses to each other, without the conversion of a linear movement is required in a rotary motion, whereby a compact design is achieved.
  • at least one shaft seal which is provided with a support member and which is hydraulically biased, external leaks are avoided at the shaft seals under an operating condition with low operating pressure.
  • the support member lifting of the sealing edge of the shaft seal is mechanically prevented at high speeds or vibrations.
  • the rotor shaft can be at least partially encapsulated inextricably with a sliding alloy.
  • the sliding alloy is a lead-bronze alloy.
  • the stator of the stator is formed on the rotor shaft side facing the gear.
  • the swivel motor comprises means for locking the stator housing with the rotor shaft.
  • a position change is avoided by internal leakage. Since in the locked state of the stator housing, the hydraulic pressure can be reduced, the seals are significantly less stressed, which has a lower wear of the seals result, since in the unpressurized state, the contact forces are significantly lower. Furthermore, an energy saving is effected because over the period of operation of the vibrator no adjustment or adjustment of the swing motor is required. Furthermore, the required control of the swing motor is simplified.
  • the means for locking is hydraulically actuated.
  • the brake system can be connected to the existing hydraulics.
  • the locking means is formed by a spring-loaded multi-disc brake.
  • Such multi-disc brakes require only a small space.
  • a swivel motor is provided for use in a vibration exciter, which in the operating mode of the vibration generator, a constant position of the imbalances at the same time. Prevention of leaks in the hydraulic system allows.
  • At least one shaft seal which is hydraulically biased and provided with a support member external leaks are avoided at the shaft seals under an operating condition with low operating pressure.
  • the support member lifting of the sealing edge of the shaft seal is mechanically prevented at high speeds or vibrations.
  • a thin-walled coating is achieved which, compared with pressed-in slide bearings, which tend to release under strong vibrations, is vibration-resistant.
  • the thin-walled coating is suitable to absorb the resulting from shaft deflection and inertia loads due to the high strength of the base material of the lid with good sliding properties.
  • the machinability of the bearing allows to be pressed against bearings a very small clearance, which in turn ensures a small relative movement between the shaft with rotor and housing with stator.
  • the low bearing clearance results in lower mass forces acting between shaft with rotor and housing with stator.
  • the rotor shaft can be at least partially encapsulated inextricably with a sliding alloy.
  • the sliding alloy is a lead-bronze alloy.
  • means for locking the stator housing are provided relative to the rotor shaft. As a result, a change in position due to internal leakage is further avoided. Since in the locked state of the stator housing, the hydraulic pressure can be reduced, the seals are significantly less stressed, which has a lower wear of the seals result, since in the unpressurized state, the contact forces are significantly lower.
  • the means for locking is hydraulically actuated. This allows the connection of the brake system to the existing hydraulics.
  • the means for locking is advantageously formed by a spring-loaded multi-disc brake. This allows a compact design.
  • a gear is arranged on the stator housing, which is formed on its inner side facing the rotor shaft as a stator with stator blades.
  • a possibly vibration-loaded separation point is avoided and the number of items is reduced.
  • the vibration generator chosen as the embodiment is designed as a vibrator gear (see. FIG. 1 ). It consists essentially of a housing 1, in which two with gears 31, 32, 33 and 51, 52, 53 provided shafts 3, 5 are rotatably mounted, and a pivot motor 6, the rotor shaft 61 with gears 613, 614 and its Stator housing 62 is provided with a gear 621.
  • the shaft 3 is rotatably mounted in bearings 11 of the housing 1.
  • an outer gear 31 is rotatably mounted, the opposite outer gear 33 is rotatably connected to the shaft 3.
  • the gears 31, 33 are each provided with imbalance masses 311, 331. Centered between the gears 31, 33, a gear 32 is further arranged rotatably mounted on the shaft 3. Also, the gear 32 is provided with an imbalance mass 321.
  • the shaft 3 is connected to a drive 2.
  • the shaft 3 opposite a shaft 5 is further rotatably supported by bearings 12 in the housing 1.
  • the shaft 5 is provided in the same way as the shaft 3 with three gears 51, 52, 53, to which imbalance masses 511, 521, 531 are attached.
  • the outer gears 51, 53 are rotatably connected to the shaft 5 on the shaft 5; the toothed wheel 51, 53 arranged gear 52 is rotatably mounted on the shaft 5.
  • the shaft 5 is connected to a drive 4.
  • a shaft 61 is rotatably supported by bearings 13 in the housing 1.
  • the shaft 61 is, as it were, the rotor shaft.
  • a pivoting motor 6 is arranged centrally on the shaft 6.
  • toothed wheels 613, 614 are rotatably mounted on the shaft 61.
  • the gears 613, 614 are positioned on the shaft 61 so as to be engaged with the gears 31, 51, 33, 53 of the shafts 3, 5, respectively.
  • a gear 621 is rotatably mounted on the stator housing 62 of the pivot motor 6.
  • the gear 621 is positioned on the stator housing 62 so as to be engaged with the gears 32, 52 of the shafts 3, 5.
  • the shaft 61 is further connected to a rotary feedthrough 615, which protrudes from the housing 1.
  • the pivoting motor 6 is essentially formed by the rotor shaft 61 and a surrounding stator housing 62, and two on both sides of the stator housing closure cap 63. Between the rotor shaft 61 and the stator housing 62, a gap formed by a integrally formed on the rotor shaft 61 rotor blade 611 and is divided by a molded on the stator housing 62 stator vanes 622, so that two working spaces 64a, 64b are formed.
  • the stator vane 622 is formed directly on the inside of the gear 621, so that the stator housing 62 with gear 621 and Statorwing 622 are integrally formed.
  • a shuttle valve 623 is arranged in the stator vanes 622 whose control channels open into the working spaces 64a, 64b on both sides of the stator vanes (cf. FIG. 6 ). Furthermore, 61 channels 612 for media supply of the working chambers and the multi-disc brake 65 are introduced longitudinally in the shaft through the hydraulic system.
  • the swivel motor is provided with a multi-disc brake 65.
  • the multi-disc brake 65 consists of a housing 630 fixed to the cover 63 of the stator housing 62, a hub 616 fixed to the shaft 61 and a clutch disc package 65.
  • the clutch discs meshing with the housing 630 are mechanically displaced by spring force (or alternatively hydraulically) against that with the rotor shaft 61 coupled hub meshing clutch discs pressed, a locking of the stator housing 62 is effected with the rotor shaft 61.
  • the stator housing 62 is sealed relative to the rotor shaft 61 by means of seals 631.
  • the seals 631 are mechanically biased hydraulically and with elastic elements and are pressed by the swivel motor integrated shuttle valve 623 upon pressurization of the working chambers 64a, 64b additionally with pressure to the corresponding mating surfaces.
  • a sliding alloy 633 is attached to the covers 63, which is cast permanently with the covers 63.
  • a thin-walled, vibration-resistant coating is formed which is suitable for absorbing the loads resulting from shaft deflection and inertial forces while at the same time providing good sliding properties.
  • the sliding alloy 633 is a lead-bronze alloy, which due to the thin-walled design combines the high mechanical properties of the base material of the cover 63 with the excellent lubricity of the alloy components.
  • the imbalance masses 311 and 331 are aligned relative to the imbalance mass 321 such that the resulting imbalance is equal to zero.
  • the gear 33 is driven via the shaft 3, which is in communication with the drive 2, and drives the gear 614 of the shaft 61, whereby the pivot motor 6 connected to the shaft 61 is rotated. Via the shaft 61, the gear 613 and likewise the gear 31 is driven.
  • the shaft 5 is set with the rotatably mounted on this gear 52 in rotation, which in turn is in engagement with the gear 621 of the stator housing 62.
  • the gear 32 of the shaft 3 is rotated, which is rotatably mounted on the shaft 3.
  • one of the working chambers 64a, 64b is subjected to overpressure via the hydraulic channels 612, controlled by an external directional control valve, so that the toothed wheel 621 rotates relative to the rotor shaft 61 and thus also to the toothed wheels 613, 614 connected in a rotationally fixed manner to the rotor shaft 61 becomes.
  • the gear wheels 62, 52 engaged with the gear 621 of the stator housing 62 are changed in their rotational position so that the unbalanced masses 321, 521 are brought out of equilibrium with the unbalanced masses 311, 331, 511, 531, resulting in a resulting imbalance is effected.
  • the degree of rotation of the gear 621 relative to the gears 613, 614 of the rotor shaft 61 the degree of vibration is infinitely adjustable.
  • the multi-disc brake 65 is mechanically activated by spring force when hydraulic pressure is released, whereby the stator housing 62 is locked to the rotor shaft 61. After locking, the further regulation of the position of the swivel motor via the hydraulic is no longer necessary, so that the pressurization can now be switched off, whereby the seals are relieved. Subsequently, the actual piling process can be performed.
  • FIGS. 2 to 4 To illustrate the unbalance control by means of rotary vane pivot motor according to the present invention are in the FIGS. 2 to 4 different wave and unbalance mass arrangements shown schematically.
  • the present invention is not limited to the exemplified arrangement.
  • FIG. 3 shows a possibility of adjusting the direction of force.
  • a direction of movement can be achieved in this way.
  • the pivot motor 6 via the gears 613 and 621, the angular position of the imbalances to each other.

Abstract

The vibrator, especially for a road surface tamping machine, has an adjustment mechanism to set the relative rotary positions of the out-of-balance masses (511,521,531). It has at least one rotary vane swing motor (6) with a rotor shaft (61) and a stator housing (62) with a variable rotary position in relation to the rotor shaft. The stator housing has at least one covering closure, coated durably at least partially with a sliding alloy for the radial and axial positioning of the rotor shaft. At least one shaft seal is between the rotor shaft and the stator housing, with a support unit and hydraulic tensioning.

Description

Die Erfindung betrifft einen Schwingungserreger nach dem Oberbegriff des Patentanspruchs 1. Die Erfindung betrifft weiterhin einen Schwenkmotor zum Einsatz in einem Schwingungserreger nach dem Oberbegriff des Patentanspruchs 7.The invention relates to a vibration generator according to the preamble of claim 1. The invention further relates to a pivot motor for use in a vibration exciter according to the preamble of claim. 7

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 durch paarweise gegenläufig rotierende Unwuchten innerhalb eines Vibratorgetriebes generiert. Schwingungserzeuger werden charakterisiert durch die installierte Unwucht (in Fachkreisen als "statisches Moment" bezeichnet) und die maximale Drehzahl.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 generated by pairwise counter-rotating imbalances within a Vibratorgetriebes. Vibration generators are characterized by the installed unbalance (referred to in the art as "static torque") and the maximum speed.

Um in Abhängigkeit von Rammgut und Bodeneigenschaften einen optimalen Vortrieb bzw. eine gute Verdichtung zu erreichen, ist es wünschenswert, Amplitude, Frequenz oder Kraftrichtung des Schwingungserzeugers zu regeln. Die Einstellung der Vibration erfolgt sinnvollerweise über eine Veränderung des statischen Moments oder der Phasenlage der Unwuchten. Beim Anfahren des Schwingungserregers wird der Eigenfrequenzbereich des Bodens durchfahren. Wird der Boden im Resonanzbereich angeregt, wird die Amplitude der Bodenschwingung sehr groß, was zu Schäden angrenzender Bebauung führen kann. Daher ist es erforderlich, das beim Anfahren des Schwingungserregers keine Unwuchten wirken.In order to achieve optimal propulsion or good compaction depending on the pile material and soil properties, it is desirable to control the amplitude, frequency or force direction of the vibrator. The Adjustment of the vibration is expediently via a change of the static torque or the phase position of the imbalances. When starting the vibration exciter the natural frequency range of the soil is traversed. If the ground is excited in the resonance range, the amplitude of the floor vibration becomes very large, which can lead to damage to adjacent buildings. Therefore, it is necessary that act when starting the vibrator no imbalance.

Bekannte Lösungen wie Planetengetriebe oder schwenkbare Räderzüge erfordern viel Platz, sind für hohe Drehzahlen wenig geeignet und erzeugen auf Grund zusätzlicher Zahnräder einen hohen Lärmpegel.Known solutions such as planetary or pivoting gear trains require a lot of space, are not very suitable for high speeds and generate due to additional gears a high noise level.

Zur Lösung dieser Problematik wurde in der DE 41 188 069 C2 vorgeschlagen, eine Drehkolben-Verstelleinrichtung zur Ausrichtung von Unwuchtmassen einzusetzen. Hierbei hat sich jedoch gezeigt, dass derartige Einrichtungen, wie beispielsweise ein Drehflügelschwenkmotor, bei den erforderlichen hohen Hydraulikdrücken, die über einen langen Zeitraum zu gewährleisten sind, es bereits nach kurzer Zeit zu Leckagen kommt, welche aufwendige Steuer- und Regeleinrichtungen erforderlich machen, um die relative Position der Unwuchtmassen konstant zu halten.To solve this problem was in the DE 41 188 069 C2 proposed to use a rotary piston adjusting device for aligning imbalance masses. It has been found, however, that such devices, such as a rotary vane swivel motor, at the required high hydraulic pressures, which are to be ensured over a long period, it comes to leaks after a short time, which require complex control and regulating devices to the to keep the relative position of the imbalance masses constant.

Hier will die Erfindung Abhilfe schaffen. Der Erfindung liegt die Aufgabe zu Grunde, einen Schwingungserreger mit einem Drehflügelschwenkmotor zu schaffen, bei dem die wirksame Unwucht und damit die Vibration einstellbar ist und bei dem darüber hinaus Leckagen auch über einen längeren Zeitraum vermieden sind. Gemäß der Erfindung wird diese Aufgabe durch die Merkmale des kennzeichnenden Teils des Patentanspruchs 1 gelöst.The invention aims to remedy this situation. The invention is based on the object to provide a vibration generator with a rotary vane pivot motor, in which the effective unbalance and thus the vibration is adjustable and in which moreover leaks over a longer period are avoided. According to the invention, this object is solved by the features of the characterizing part of patent claim 1.

Mit der Erfindung ist ein Schwingungserreger geschaffen, bei dem die wirksame Unwucht und damit die Vibration einstellbar ist und bei dem darüber hinaus Leckagen auch über einen längeren Zeitraum vermieden sind. Der Einsatz des Drehflügelschwenkmotors ermöglicht eine relative Verstellung der Unwuchtmassen zueinander, ohne das eine Umwandlung einer linearen Bewegung in eine Drehbewegung erforderlich ist, wodurch eine kompakte Bauweise erzielt ist. Durch die zwischen Rotorwelle und Statorgehäuse angeordnete wenigstens eine Wellendichtung, die mit einem Stützelement versehen ist und die hydraulisch vorgespannt ist, werden externe Undichtigkeiten an den Wellendichtungen unter einem Betriebszustand mit niedrigem Betriebsdruck vermieden. Durch das Stützelement wird ein Abheben der Dichtkante der Wellendichtung bei hohen Drehzahlen bzw. Vibrationen mechanisch verhindert.With the invention, a vibration exciter is provided in which the effective unbalance and thus the vibration is adjustable and in which moreover leaks over a longer period of time are avoided. The use of the rotary vane pivot motor allows a relative adjustment of the imbalance masses to each other, without the conversion of a linear movement is required in a rotary motion, whereby a compact design is achieved. By arranged between the rotor shaft and the stator housing at least one shaft seal, which is provided with a support member and which is hydraulically biased, external leaks are avoided at the shaft seals under an operating condition with low operating pressure. By the support member lifting of the sealing edge of the shaft seal is mechanically prevented at high speeds or vibrations.

Durch die an wenigstens einem Verschlussdeckel aufgebrachte Gleitlegierung zur radialen und axialen Lagerung des Statorgehäuses gegenüber der Rotorwelle ist eine dünnwandige Beschichtung erzielt, die gegenüber eingepressten Gleitlagern, die unter starken Vibrationen zum Lösen neigen, vibrationsbeständig ist. Alternativ oder ergänzend kann zur Erzielung dieses Vorteils die Rotorwelle zumindest partiell mit einer Gleitlegierung unlösbar vergossen sein. Vorteilhaft ist die Gleitlegierung eine Blei-Bronze-Legierung.By applied to at least one closure cover sliding alloy for radial and axial mounting of the stator housing relative to the rotor shaft a thin-walled coating is achieved, which is resistant to vibration against pressed sliding bearings that tend to release under strong vibrations. Alternatively or additionally, to achieve this advantage, the rotor shaft can be at least partially encapsulated inextricably with a sliding alloy. Advantageously, the sliding alloy is a lead-bronze alloy.

In Weiterbildung der Erfindung ist der Statorflügel des Statorgehäuses an der der Rotorwelle zugewandten Seite des Zahnrades angeformt. Hierdurch ist eine effektivere Ausnutzung des Bauraums erzielt. Weiterhin kann unter Ausnutzung des Zahnradkörpers bei gleichem Achsabstand das Drehmoment des Schwenkmotors gesteigert werden. Eine vibrationsbelastete Trennstelle wird vermieden, die Anzahl der Einzelteile reduziert.In a further development of the invention, the stator of the stator is formed on the rotor shaft side facing the gear. As a result, a more effective use of space is achieved. Furthermore, by utilizing the gear body at the same axial distance, the torque of the swing motor can be increased. A vibration-loaded separation point is avoided, reduces the number of items.

In Ausgestaltung der Erfindung weist der Schwenkmotor Mittel zur Arretierung des Statorgehäuses mit der Rotorwelle auf. Hierdurch wird eine Positionsveränderung durch interne Leckage vermieden. Da im arretierten Zustand des Statorgehäuses der Hydraulikdruck gesenkt werden kann, werden die Dichtungen deutlich weniger beansprucht, was einen geringeren Verschleiß der Dichtungen zur Folge hat, da im drucklosen Zustand die Anpresskräfte deutlich geringer sind. Weiterhin wird eine Energieeinsparung bewirkt, da über den Zeitraum des Betriebs des Vibrators keine Verstellung bzw. Nachstellung des Schwenkmotors erforderlich ist. Weiterhin ist die erforderliche Regelung des Schwenkmotors vereinfacht.In an embodiment of the invention, the swivel motor comprises means for locking the stator housing with the rotor shaft. As a result, a position change is avoided by internal leakage. Since in the locked state of the stator housing, the hydraulic pressure can be reduced, the seals are significantly less stressed, which has a lower wear of the seals result, since in the unpressurized state, the contact forces are significantly lower. Furthermore, an energy saving is effected because over the period of operation of the vibrator no adjustment or adjustment of the swing motor is required. Furthermore, the required control of the swing motor is simplified.

In vorteilhafter Ausgestaltung ist das Mittel zu Arretierung hydraulisch betätigbar. Hierdurch ist das Bremssystem an die bestehende Hydraulik anschließbar.In an advantageous embodiment, the means for locking is hydraulically actuated. As a result, the brake system can be connected to the existing hydraulics.

Bevorzugt ist das Mittel zur Arretierung durch eine Federdruck-Lamellenbremse gebildet. Derartige Lamellenbremsen beanspruchen lediglich einen geringen Bauraum.Preferably, the locking means is formed by a spring-loaded multi-disc brake. Such multi-disc brakes require only a small space.

Der Erfindung liegt weiterhin die Aufgabe zu Grunde, einen Schwenkmotor zum Einsatz in einem Schwingungserreger zu schaffen, der im Arbeitsbetrieb des Schwingungserregers eine konstante Stellung der Unwuchten bei gleichzeitiger Vermeidung von Leckagen des Hydrauliksystems ermöglicht. Gemäß der Erfindung wird diese Aufgabe durch den kennzeichnenden Teil des Patentanspruchs 7 gelöst.The invention is further based on the object to provide a swivel motor for use in a vibration exciter, which allows a constant position of the imbalances while avoiding leaks in the hydraulic system during operation of the vibrator. According to the invention, this object is achieved by the characterizing part of claim 7.

Mit der Erfindung ist ein Schwenkmotor zum Einsatz in einem Schwingungserreger geschaffen, der im Arbeitsbetrieb des Schwingungserregers eine konstante Stellung der Unwuchten bei gleichzeitiger. Vermeidung von Leckagen des Hydrauliksystems ermöglicht.With the invention, a swivel motor is provided for use in a vibration exciter, which in the operating mode of the vibration generator, a constant position of the imbalances at the same time. Prevention of leaks in the hydraulic system allows.

Durch die zwischen Rotorwelle und Statorgehäuse angeordnete wenigstens eine Wellendichtung, die hydraulisch vorgespannt und mit einem Stützelement versehen ist werden externe Undichtigkeiten an den Wellendichtungen unter einem Betriebszustand mit niedrigem Betriebsdruck vermieden. Durch das Stützelement wird ein Abheben der Dichtkante der Wellendichtung bei hohen Drehzahlen bzw. Vibrationen mechanisch verhindert.By arranged between the rotor shaft and the stator housing at least one shaft seal, which is hydraulically biased and provided with a support member external leaks are avoided at the shaft seals under an operating condition with low operating pressure. By the support member lifting of the sealing edge of the shaft seal is mechanically prevented at high speeds or vibrations.

Durch die an wenigstens einem Verschlussdeckel aufgebrachte Gleitlegierung zur radialen und axialen Lagerung des Statorgehäuses gegenüber der Rotorwelle ist eine dünnwandige Beschichtung erzielt, die gegenüber eingepressten Gleitlagern, die unter starken Vibrationen zum Lösen neigen, vibrationsbeständig ist. Zudem ist die dünnwandige Beschichtung geeignet, die aus Wellendurchbiegung und Massekräften resultierenden Belastungen auf Grund der hohen Festigkeit des Grundmaterials des Deckels bei gleichzeitig guten Gleiteigenschaften aufzunehmen. Die Bearbeitbarkeit der Lagerstelle ermöglicht gegenüber einzupressenden Lagern ein sehr geringes Lagerspiel, was wiederum eine geringe Relativbewegung zwischen Welle mit Rotor und Gehäuse mit Stator gewährleistet. Aus dem geringen Lagerspiel resultieren geringere Massenkräfte, die zwischen Welle mit Rotor und Gehäuse mit Stator wirken.Due to the sliding alloy applied to at least one closure cover for the radial and axial mounting of the stator housing with respect to the rotor shaft, a thin-walled coating is achieved which, compared with pressed-in slide bearings, which tend to release under strong vibrations, is vibration-resistant. In addition, the thin-walled coating is suitable to absorb the resulting from shaft deflection and inertia loads due to the high strength of the base material of the lid with good sliding properties. The machinability of the bearing allows to be pressed against bearings a very small clearance, which in turn ensures a small relative movement between the shaft with rotor and housing with stator. The low bearing clearance results in lower mass forces acting between shaft with rotor and housing with stator.

Alternativ oder ergänzend kann die Rotorwelle zumindest partiell mit einer Gleitlegierung unlösbar vergossen sein. Vorteilhaft ist die Gleitlegierung eine Blei-Bronze-Legierung.Alternatively or additionally, the rotor shaft can be at least partially encapsulated inextricably with a sliding alloy. Advantageously, the sliding alloy is a lead-bronze alloy.

In Weiterbildung der Erfindung sind Mittel zur Arretierung des Statorgehäuses relativ zur Rotorwelle vorgesehen. Hierdurch wird eine Positionsveränderung durch interne Leckage weiter vermieden. Da im arretierten Zustand des Statorgehäuses der Hydraulikdruck gesenkt werden kann, werden die Dichtungen deutlich weniger beansprucht, was einen geringeren Verschleiß der Dichtungen zur Folge hat, da im drucklosen Zustand die Anpresskräfte deutlich geringer sind.In development of the invention, means for locking the stator housing are provided relative to the rotor shaft. As a result, a change in position due to internal leakage is further avoided. Since in the locked state of the stator housing, the hydraulic pressure can be reduced, the seals are significantly less stressed, which has a lower wear of the seals result, since in the unpressurized state, the contact forces are significantly lower.

Bevorzugt ist das Mittel zur Arretierung hydraulisch betätigbar. Hierdurch ist der Anschluss des Bremssystems an die bestehende Hydraulik ermöglicht.Preferably, the means for locking is hydraulically actuated. This allows the connection of the brake system to the existing hydraulics.

Vorteilhaft ist das Mittel zur Arretierung durch eine Federdruck-Lamellenbremse gebildet. Hierdurch ist eine kompakte Bauweise ermöglicht.The means for locking is advantageously formed by a spring-loaded multi-disc brake. This allows a compact design.

In Ausgestaltung der Erfindung ist auf dem Statorgehäuse ein Zahnrad angeordnet, das auf seiner der Rotorwelle zugewandten Innenseite als Stator mit Statorflügel ausgebildet ist. Hierdurch wird eine effektive Ausnutzung des Bauraums bewirkt. Darüber hinaus kann unter Ausnutzung des Zahnradkörpers bei gleichem Achsabstand das Drehmoment des Schwenkmotors gesteigert werden.In an embodiment of the invention, a gear is arranged on the stator housing, which is formed on its inner side facing the rotor shaft as a stator with stator blades. As a result, effective utilization of the installation space is effected. In addition, the torque of the swing motor can be increased by utilizing the gear body at the same center distance.

Eine möglicherweise vibrationsbelastete Trennstelle wird vermieden und die Anzahl der Einzelteile wird reduziert.A possibly vibration-loaded separation point is avoided and the number of items is reduced.

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:

Fig. 1
die Darstellung eines Vibratorgetriebes im Längsschnitt;
Fig. 2
eine Prinzipdarstellung einer schwenkmotorindizierten Unwuchtverstellung mit einer unwuchtbelasteten Achse;
Fig. 3
eine Prinzipdarstellung einer schwenkmotorindizierten Unwuchtverstellung mit zwei unwuchtbelasteten Achsen zur Einstellung der Kraftrichtung;
Fig. 4
die Prinzipdarstellung einer schwenkmotorindizierten Unwuchtverstellung mit paarweise angeordneten unwuchtbelasteten Wellen;
Fig. 5
die Darstellung eines Drehflügelschwenkmotors mit Federdruck-Lamellenbremse im Längsschnitt;
Fig. 6
die Darstellung des Schwenkmotors aus Figur 5 im Querschnitt entlang der Linie VI-VI und
Fig. 7
die Detailansicht des Ausschnitts VII aus Figur 5.
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 representation of a vibrator in longitudinal section;
Fig. 2
a schematic diagram of a Schwenkmotorindizierten imbalance adjustment with a unbalanced load axis;
Fig. 3
a schematic diagram of a Schwenkmotorindizierten imbalance adjustment with two unbalanced loaded axes for adjusting the direction of force;
Fig. 4
the schematic diagram of a Schwenkmotorindizierten imbalance adjustment with paired unbalanced waves loaded;
Fig. 5
the representation of a rotary vane with spring-loaded multi-disc brake in longitudinal section;
Fig. 6
the representation of the swing motor FIG. 5 in cross section along the line VI-VI and
Fig. 7
the detailed view of section VII off FIG. 5 ,

Der als Ausführungsbeispiel gewählte Schwingungserzeuger ist als Vibratorgetriebe ausgeführt (vgl. Figur 1). Er besteht im Wesentlichen aus einem Gehäuse 1, in dem zwei mit Zahnrädern 31, 32, 33 bzw. 51, 52, 53 versehene Wellen 3, 5 drehbar gelagert sind, sowie einem Schwenkmotor 6, dessen Rotorwelle 61 mit Zahnrädern 613, 614 und dessen Statorgehäuse 62 mit einem Zahnrad 621versehen ist.The vibration generator chosen as the embodiment is designed as a vibrator gear (see. FIG. 1 ). It consists essentially of a housing 1, in which two with gears 31, 32, 33 and 51, 52, 53 provided shafts 3, 5 are rotatably mounted, and a pivot motor 6, the rotor shaft 61 with gears 613, 614 and its Stator housing 62 is provided with a gear 621.

Die Welle 3 ist in Lagern 11 des Gehäuses 1 drehbar gelagert. Auf der Welle 3 ist ein äußeres Zahnrad 31 drehbar gelagert angeordnet, das gegenüberliegende äußere Zahnrad 33 ist drehfest mit der Welle 3 verbunden. Die Zahnräder 31, 33 sind jeweils mit Unwuchtmassen 311, 331 versehen. Mittig zwischen den Zahnrädern 31, 33 ist weiterhin ein Zahnrad 32 auf der Welle 3 drehbar gelagert angeordnet. Auch das Zahnrad 32 ist mit einer Unwuchtmasse 321 versehen. Im Ausführungsbeispiel ist die Welle 3 mit einem Antrieb 2 verbunden.The shaft 3 is rotatably mounted in bearings 11 of the housing 1. On the shaft 3, an outer gear 31 is rotatably mounted, the opposite outer gear 33 is rotatably connected to the shaft 3. The gears 31, 33 are each provided with imbalance masses 311, 331. Centered between the gears 31, 33, a gear 32 is further arranged rotatably mounted on the shaft 3. Also, the gear 32 is provided with an imbalance mass 321. In the exemplary embodiment, the shaft 3 is connected to a drive 2.

Der Welle 3 gegenüberliegend ist in dem Gehäuse 1 weiterhin eine Welle 5 mittels Lagern 12 drehbar gelagert. Die Welle 5 ist in gleicher Weise wie die Welle 3 mit drei Zahnrädern 51, 52, 53 versehen, an denen Unwuchtmassen 511, 521, 531 befestigt sind. Im Gegensatz zur Welle 3 sind an der Welle 5 jedoch die äußeren Zahnräder 51, 53 drehbar mit der Welle 5 verbunden; das zwischen den Zahnrädern 51, 53 angeordnete Zahnrad 52 ist drehfest an der Welle 5 befestigt. Im Ausführungsbeispiel ist die Welle 5 mit einem Antrieb 4 verbunden.The shaft 3 opposite a shaft 5 is further rotatably supported by bearings 12 in the housing 1. The shaft 5 is provided in the same way as the shaft 3 with three gears 51, 52, 53, to which imbalance masses 511, 521, 531 are attached. In contrast to the shaft 3, however, the outer gears 51, 53 are rotatably connected to the shaft 5 on the shaft 5; the toothed wheel 51, 53 arranged gear 52 is rotatably mounted on the shaft 5. In the exemplary embodiment, the shaft 5 is connected to a drive 4.

Zwischen den Wellen 3, 5 ist eine Welle 61 über Lager 13 in dem Gehäuse 1 drehbar gelagert. Die Welle 61 ist gleichsam die Rotorwelle.eines mittig auf dieser angeordneten Schwenkmotors 6. Beidseitig des Schwenkmotors 6 sind auf der Welle 61 Zahnräder 613, 614 drehfest angeordnet. Die Zahnräder 613, 614 sind derart auf der Welle 61 positioniert, dass sie mit den Zahnrädern 31, 51 bzw. 33, 53 der Wellen 3, 5 im Eingriff sind. Weiterhin ist an dem Statorgehäuse 62 des Schwenkmotors 6 ein Zahnrad 621 drehfest angeordnet. Das Zahnrad 621 ist derart auf dem Statorgehäuse 62 positioniert, dass es mit den Zahnrädern 32, 52 der Wellen 3, 5 im Eingriff steht. Die Welle 61 ist weiterhin mit einer Drehdurchführung 615 verbunden, die aus dem Gehäuse 1 hinausragt.Between the shafts 3, 5, a shaft 61 is rotatably supported by bearings 13 in the housing 1. The shaft 61 is, as it were, the rotor shaft. A pivoting motor 6 is arranged centrally on the shaft 6. On both sides of the pivoting motor 6, toothed wheels 613, 614 are rotatably mounted on the shaft 61. The gears 613, 614 are positioned on the shaft 61 so as to be engaged with the gears 31, 51, 33, 53 of the shafts 3, 5, respectively. Furthermore, a gear 621 is rotatably mounted on the stator housing 62 of the pivot motor 6. The gear 621 is positioned on the stator housing 62 so as to be engaged with the gears 32, 52 of the shafts 3, 5. The shaft 61 is further connected to a rotary feedthrough 615, which protrudes from the housing 1.

Der Schwenkmotor 6 ist im Wesentlichen gebildet durch die Rotorwelle 61 und ein diese umgebendes Statorgehäuse 62, sowie zwei beidseitig des Statorgehäuses angeordnete Verschlussdeckel 63. Zwischen der Rotorwelle 61 und dem Statorgehäuse 62 ist ein Zwischenraum gebildet, der durch einen an der Rotorwelle 61 angeformten Rotorflügel 611 sowie durch einen an dem Statorgehäuse 62 angeformten Statorflügel 622 unterteilt ist, so dass zwei Arbeitsräume 64a, 64b gebildet sind. Im Ausführungsbeispiel ist der Statorflügel 622 direkt auf der Innenseite des Zahnrades 621 angeformt, so dass das Statorgehäuse 62 mit Zahnrad 621 und Statorflügel 622 einstückig ausgebildet sind. Zur Realisierung einer druckabhängigen Vorspannkraft der inneren Dichtungen 631 des Schwenkmotors 6 ist in dem Statorflügel 622 ein Wechselventil 623 angeordnet, dessen Steuerkanäle beidseitig des Statorflügels in die Arbeitsräume 64a, 64b münden (vgl. Figur 6). Weiterhin sind längs in der Welle 61 Kanäle 612 zur Medienversorgung der Arbeitskammern und der Lamellenbremse 65 durch das Hydrauliksystem eingebracht.The pivoting motor 6 is essentially formed by the rotor shaft 61 and a surrounding stator housing 62, and two on both sides of the stator housing closure cap 63. Between the rotor shaft 61 and the stator housing 62, a gap formed by a integrally formed on the rotor shaft 61 rotor blade 611 and is divided by a molded on the stator housing 62 stator vanes 622, so that two working spaces 64a, 64b are formed. In the exemplary embodiment, the stator vane 622 is formed directly on the inside of the gear 621, so that the stator housing 62 with gear 621 and Statorwing 622 are integrally formed. In order to realize a pressure-dependent prestressing force of the inner seals 631 of the swivel motor 6, a shuttle valve 623 is arranged in the stator vanes 622 whose control channels open into the working spaces 64a, 64b on both sides of the stator vanes (cf. FIG. 6 ). Furthermore, 61 channels 612 for media supply of the working chambers and the multi-disc brake 65 are introduced longitudinally in the shaft through the hydraulic system.

Im Ausführungsbeispiel gemäß Figur 5 ist der Schwenkmotor mit einer Lamellenbremse 65 versehen. Die Lamellenbremse 65 besteht aus einem am Deckel 63 des Statorgehäuses 62 befestigten Gehäuse 630, einer an der Welle 61 befestigten Nabe 616 und einem Kupplungsscheibenpaket 65. Werden die mit dem Gehäuse 630 kämmenden Kupplungsscheiben mechanisch durch Federkraft (oder alternativ hydraulisch) gegen die mit der Rotorwelle 61 verbundenen Nabe kämmenden Kupplungsscheiben gepresst, so ist eine Arretierung des Statorgehäuses 62 mit der Rotorwelle 61 bewirkt.In the embodiment according to FIG. 5 the swivel motor is provided with a multi-disc brake 65. The multi-disc brake 65 consists of a housing 630 fixed to the cover 63 of the stator housing 62, a hub 616 fixed to the shaft 61 and a clutch disc package 65. The clutch discs meshing with the housing 630 are mechanically displaced by spring force (or alternatively hydraulically) against that with the rotor shaft 61 coupled hub meshing clutch discs pressed, a locking of the stator housing 62 is effected with the rotor shaft 61.

Das Statorgehäuse 62 ist gegenüber der Rotorwelle 61 mittels Dichtungen 631 abgedichtet. Die Dichtungen 631 sind hydraulisch sowie mit elastischen Elementen mechanisch vorgespannt und werden durch das im Schwenkmotor integrierte Wechselventil 623 bei Druckbeaufschlagung der Arbeitskammern 64a, 64b zusätzlich mit Druck an die entsprechenden Gegenlaufflächen gepresst. Somit wird über den Zeitraum der Verstellung, das heißt im druckbeaufschlagten Zustand, eine hohe Dichtheit und somit ein hoher volumetrischer Wirkungsgrad erzielt. Im drucklosen Zustand entfällt die hydraulische Anpresskraft vollständig mit dem Vorteil einer Verschleißreduzierung.The stator housing 62 is sealed relative to the rotor shaft 61 by means of seals 631. The seals 631 are mechanically biased hydraulically and with elastic elements and are pressed by the swivel motor integrated shuttle valve 623 upon pressurization of the working chambers 64a, 64b additionally with pressure to the corresponding mating surfaces. Thus, over the period of adjustment, that is in the pressurized state, a high density and thus a high volumetric efficiency is achieved. In the pressureless state, the hydraulic contact pressure completely eliminated with the advantage of a reduction in wear.

Zur Vermeidung von externen Undichtigkeiten an den Wellendichtungen 631 unter einem Betriebszustand mit niedrigem Betriebsdruck sind diese zusätzlich mit einem Stützelement 632 versehen. Das Stützelement 632 verhindert ein Abheben der Dichtkante bei hohen Drehzahlen. Zur Unterstützung der Dichtwirkung der Dichtungen 631 sind in dem Deckel 63 Hydraulikkanäle 634 eingebracht.To avoid external leaks at the shaft seals 631 under an operating condition with low operating pressure, these are additionally provided with a support element 632. The support member 632 prevents lifting of the sealing edge at high speeds. To support the sealing effect of the seals 631 63 hydraulic channels 634 are introduced in the lid.

Zur axialen und radialen Lagerung der Rotorwelle in den Deckeln 63 des Statorgehäuses 62 ist an den Deckeln 63 eine Gleitlegierung 633 angebracht, die mit den Deckeln 63 unlösbar vergossen ist. Hierdurch ist eine dünnwandige, vibrationsbeständige Beschichtung gebildet, die geeignet ist, die aus Wellendurchbiegung und Massenkräften resultierenden Belastungen bei gleichzeitig guten Gleiteigenschaften aufzunehmen. Im Ausführungsbeispiel ist die Gleitlegierung 633 eine Blei-Bronze-Legierung, die aufgrund der dünnwandigen Ausführung die hohen mechanischen Eigenschaften des Grundmaterials des Deckels 63 mit der hervorragenden Gleitfähigkeit der Legierungskomponenten vereint.For axial and radial mounting of the rotor shaft in the covers 63 of the stator housing 62, a sliding alloy 633 is attached to the covers 63, which is cast permanently with the covers 63. As a result, a thin-walled, vibration-resistant coating is formed which is suitable for absorbing the loads resulting from shaft deflection and inertial forces while at the same time providing good sliding properties. In the exemplary embodiment, the sliding alloy 633 is a lead-bronze alloy, which due to the thin-walled design combines the high mechanical properties of the base material of the cover 63 with the excellent lubricity of the alloy components.

In der Anlaufphase des Vibrators sind die Unwuchtmassen 311 und 331 gegenüber der Unwuchtmasse 321 derart ausgerichtet, dass die resultierende Unwucht gleich Null ist. Das Zahnrad 33 wird über die Welle 3, die mit dem Antrieb 2 in Verbindung steht, angetrieben und treibt das Zahnrad 614 der Welle 61 an, wodurch der mit der Welle 61 verbundene Schwenkmotor 6 rotiert wird. Über die Welle 61 wird das Zahnrad 613 und gleichermaßen das Zahnrad 31 angetrieben.In the start-up phase of the vibrator, the imbalance masses 311 and 331 are aligned relative to the imbalance mass 321 such that the resulting imbalance is equal to zero. The gear 33 is driven via the shaft 3, which is in communication with the drive 2, and drives the gear 614 of the shaft 61, whereby the pivot motor 6 connected to the shaft 61 is rotated. Via the shaft 61, the gear 613 and likewise the gear 31 is driven.

Über den - synchrongesteuerten - Antrieb 4 wird die Welle 5 mit dem auf dieser drehfest angeordneten Zahnrad 52 in Rotation versetzt, welches wiederum mit dem Zahnrad 621 des Statorgehäuses 62 im Eingriff steht. Über das Zahnrad 621 des Statorgehäuses 62 wird das Zahnrad 32 der Welle 3 rotiert, welches auf der Welle 3 drehbar gelagert ist. Am Ende der Anlaufphase wird eine der Arbeitskammern 64a, 64b über die Hydraulikkanäle 612, geregelt über ein externes Wegeventil mit Überdruck beaufschlagt, so dass das Zahnrad 621 relativ zur Rotorwelle 61 und somit auch zu den mit der Rotorwelle 61 drehfest verbundenen Zahnrädern 613, 614 verdreht wird.About the - synchronous controlled - drive 4, the shaft 5 is set with the rotatably mounted on this gear 52 in rotation, which in turn is in engagement with the gear 621 of the stator housing 62. About the gear 621 of the stator housing 62, the gear 32 of the shaft 3 is rotated, which is rotatably mounted on the shaft 3. At the end of the start-up phase, one of the working chambers 64a, 64b is subjected to overpressure via the hydraulic channels 612, controlled by an external directional control valve, so that the toothed wheel 621 rotates relative to the rotor shaft 61 and thus also to the toothed wheels 613, 614 connected in a rotationally fixed manner to the rotor shaft 61 becomes.

Gleichermaßen werden die mit dem Zahnrad 621 des Statorgehäuses 62 im Eingriff stehenden Zahnräder 32, 52 in ihrer Drehposition verändert, so dass die Unwuchtmassen 321, 521 gegenüber den Unwuchtmassen 311, 331, 511, 531 außer Gleichgewicht gebracht werden, wodurch eine resultierende Unwucht bewirkt ist. Durch den Grad der Verdrehung des Zahnrads 621 gegenüber den Zahnrädern 613, 614 der Rotorwelle 61 ist der Grad der Vibration stufenlos einstellbar.Similarly, the gear wheels 62, 52 engaged with the gear 621 of the stator housing 62 are changed in their rotational position so that the unbalanced masses 321, 521 are brought out of equilibrium with the unbalanced masses 311, 331, 511, 531, resulting in a resulting imbalance is effected. By the degree of rotation of the gear 621 relative to the gears 613, 614 of the rotor shaft 61, the degree of vibration is infinitely adjustable.

Ist der gewünschte Vibrationsgrad erreicht, wird die Lamellenbremse 65 bei hydraulischer Druckentlastung mechanisch durch Federkraft aktiviert, wodurch das Statorgehäuse 62 mit der Rotorwelle 61 arretiert wird. Nach Arretierung ist die weitere Regelung der Position des Schwenkmotors über die Hydraulik nicht mehr erforderlich, so dass die Druckbeaufschlagung nunmehr abgeschaltet werden kann, wodurch die Dichtungen entlastet werden. Nachfolgend kann der eigentliche Rammvorgang durchgeführt werden.Once the desired degree of vibration is achieved, the multi-disc brake 65 is mechanically activated by spring force when hydraulic pressure is released, whereby the stator housing 62 is locked to the rotor shaft 61. After locking, the further regulation of the position of the swivel motor via the hydraulic is no longer necessary, so that the pressurization can now be switched off, whereby the seals are relieved. Subsequently, the actual piling process can be performed.

Da der Schwenkmotor 6 nunmehr nur noch im lastfreien Zustand des Vibrators betrieben wird und durch die Arretierung mittels der Lamellenbremse 65 während des Rammprozesses entlastet ist, ist eine deutlich geringere Baugröße des Schwenkmotors ermöglicht.Since the pivot motor 6 is now operated only in the load-free state of the vibrator and is relieved by the locking means of the multi-disc brake 65 during the ramming process, a significantly smaller size of the swing motor is possible.

Zur Verdeutlichung der Unwuchtregelung mittels Drehflügelschwenkmotor gemäß vorliegender Erfindung sind in den Figuren 2 bis 4 unterschiedliche Wellen- und Unwuchtmasseanordnungen schematisch dargestellt. Selbstverständlich ist die vorliegende Erfindung nicht auf die beispielhaft dargestellte Anordnung beschränkt.To illustrate the unbalance control by means of rotary vane pivot motor according to the present invention are in the FIGS. 2 to 4 different wave and unbalance mass arrangements shown schematically. Of course, the present invention is not limited to the exemplified arrangement.

Figur 3 zeigt eine Möglichkeit der Verstellung der Kraftrichtung. Bei Bodenverdichtern, beispielsweise Rüttelplatten, kann auf diese Weise eine Bewegungsrichtung erzielt werden. Dabei verändert der Schwenkmotor 6 über die Zahnräder 613 und 621 die Winkelstellung der Unwuchten zueinander. FIG. 3 shows a possibility of adjusting the direction of force. In soil compactors, such as vibrating plates, a direction of movement can be achieved in this way. In this case, the pivot motor 6 via the gears 613 and 621, the angular position of the imbalances to each other.

Claims (12)

Schwingungserreger, insbesondere für eine Vibrationsramme, umfassend wenigstens zwei parallel zueinander angeordnete Achsen, sowie wenigstens zwei Unwuchtmassen, die auf einer oder auf mehreren der Achsen befestigt sind, wobei Mittel zur Verstellung der relativen Drehposition der Unwuchtmassen zueinander vorgesehen sind, dadurch gekennzeichnet, dass die Mittel mindestens einen Drehflügelschwenkmotor (6) mit einer Rotorwelle (61) und einem Statorgehäuse (62) umfassen, wobei die Rotorwelle (61) Bestandteil einer der Achsen ist und die Drehstellung des Statorgehäuses (62) relativ zur Rotorwelle (61) veränderbar ist, dass das Statorgehäuse (62) wenigstens einen Verschlussdeckel (63) aufweist, der zur radialen und axialen Lagerung der Rotorwelle (61) zumindest partiell mit einer Gleitlegierung (633) unlösbar beschichtet ist und dass zwischen Rotorwelle (61) und Statorgehäuse (62) wenigstens eine Wellendichtung (631) angeordnet ist, die hydraulisch vorgespannt und mit einem Stützelement versehen ist.Vibration generator, in particular for a vibration ram, comprising at least two axes arranged parallel to one another and at least two imbalance masses which are mounted on one or more of the axes, wherein means for adjusting the relative rotational position of the imbalance masses are provided to one another, characterized in that the means at least one rotary vane (6) with a rotor shaft (61) and a stator housing (62), wherein the rotor shaft (61) is part of one of the axes and the rotational position of the stator housing (62) relative to the rotor shaft (61) is variable, that Stator housing (62) has at least one closure cover (63) which is at least partially non-detachably coated for radial and axial mounting of the rotor shaft (61) with a sliding alloy (633) and that between the rotor shaft (61) and stator housing (62) at least one shaft seal ( 631) is arranged, which is hydraulically biased and with a Stützele ment is provided. Schwingungserreger nach Anspruch 1, dadurch gekennzeichnet, dass die Rotorwelle (61) zusätzlich zu oder anstelle der Beschichtung des wenigstens einen Verschlussdeckels zumindest partiell mit einer Gleitlegierung (633) unlösbar beschichtet ist.Vibration generator according to claim 1, characterized in that the rotor shaft (61) in addition to or instead of the coating of the at least one closure cap is at least partially permanently coated with a sliding alloy (633). Schwingungserreger nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass auf dem Statorgehäuse 62 ein Zahnrad 621 angeordnet ist, das auf seiner der Rotorwelle (61) zugewandten Innenseite als Stator mit mindestens einem Statorflügel (622) ausgebildet ist.Vibration generator according to one of the preceding claims, characterized in that on the stator housing 62, a gear 621 is arranged, which on its the rotor shaft (61) facing the inside as a stator with at least one stator (622) is formed. Schwingungserreger nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass der Schwenkmotor (6) Mittel (65) zur Arretierung des Statorgehäuses (62) mit der Rotorwelle (61) aufweist.Vibration generator according to one of the preceding claims, characterized in that the swivel motor (6) has means (65) for locking the stator housing (62) to the rotor shaft (61). Schwingungserreger nach Anspruch 4, dadurch gekennzeichnet, dass das Mittel (65) zur Arretierung hydraulisch betätigbar ist.Vibration generator according to claim 4, characterized in that the means (65) for locking is hydraulically actuated. Schwingungserreger nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass das Mittel zur Arretierung durch eine Federdruck-Lamellenbremse (65, 616, 630) gebildet ist.Vibration generator according to claim 4 or 5, characterized in that the means for locking by a spring-loaded multi-disc brake (65, 616, 630) is formed. Schwenkmotor, geeignet zum Einsatz in einem Schwingungserreger nach einem der vorgenannten Ansprüche, umfassend eine Rotorwelle (61) und ein Statorgehäuse (62), zwischen denen Arbeitskammern (64a, 64b) gebildet sind, wobei das Statorgehäuse (62) um die Rotorachse (61) drehbar ist, dadurch gekennzeichnet, dass das Statorgehäuse (62) wenigstens einen Verschlussdeckel (63) aufweist, der zur radialen und axialen Lagerung der Rotorwelle (61) zumindest partiell mit einer Gleitlegierung (633) unlösbar beschichtet ist und dass zwischen Rotorwelle (61) und Statorgehäuse (62) wenigstens eine Wellendichtung (631) angeordnet ist, die hydraulisch vorgespannt und mit einem Stützelement versehen ist.Pivoting motor suitable for use in a vibration generator according to one of the preceding claims, comprising a rotor shaft (61) and a stator housing (62), between which working chambers (64a, 64b) are formed, the stator housing (62) being wound around the rotor axis (61). is rotatable, characterized in that the stator housing (62) has at least one closure cover (63), which is at least partially permanently coated for radial and axial mounting of the rotor shaft (61) with a sliding alloy (633) and that between rotor shaft (61) and Stator housing (62) at least one shaft seal (631) is arranged, which is hydraulically biased and provided with a support member. Schwenkmotor nach Anspruch 7, dadurch gekennzeichnet, dass die Rotorwelle (61) zur radialen und axialen Lagerung des Statorgehäuses (62) gegenüber der Rotorwelle (61) zusätzlich zu oder anstelle der Beschichtung des wenigstens einen Verschlussdeckels zumindest partiell mit einer Gleitlegierung (633) unlösbar vergossen ist.Pivoting motor according to claim 7, characterized in that the rotor shaft (61) for the radial and axial mounting of the stator housing (62) relative to the rotor shaft (61) in addition to or instead of the coating the at least one closure cap is at least partially cast non-detachably with a sliding alloy (633). Schwenkmotor nach einem der Ansprüche 7 und 8, dadurch gekennzeichnet, dass Mittel (65) zur Arretierung des Statorgehäuses (62) relativ zur Rotorwelle (61) vorgesehen sind.Pivoting motor according to one of claims 7 and 8, characterized in that means (65) for locking the stator housing (62) relative to the rotor shaft (61) are provided. Schwenkmotor nach Anspruch 9, dadurch gekennzeichnet, dass das Mittel zur Arretierung hydraulisch betätigbar ist.Pivoting motor according to claim 9, characterized in that the means for locking is hydraulically actuated. Schwenkmotor nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass das Mittel zur Arretierung durch eine Federdruck-Lamellenbremse (65, 616, 630) gebildet ist.Swivel motor according to claim 9 or 10, characterized in that the means for locking by a spring-loaded multi-disc brake (65, 616, 630) is formed. Schwenkmotor nach einem der Ansprüche 9 bis 11, dadurch gekennzeichnet, dass auf dem Statorgehäuse (62) eine Zahnrad (621) angeordnet ist, das auf seiner der Rotorwelle (61) zugewandten Innenseite als Stator mit Statorflügeln (622) ausgebildet ist.Pivoting motor according to one of claims 9 to 11, characterized in that on the stator housing (62) a gear (621) is arranged, which on its the rotor shaft (61) facing the inside as a stator with stator vanes (622) is formed.
EP07016396.9A 2007-03-07 2007-08-22 Vibration generator Active EP1967292B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202007003532U DE202007003532U1 (en) 2007-03-07 2007-03-07 Vibrator, for a road surface tamping machine, has a rotary vane swing motor to adjust the relative positions of the out-of-balance masses

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EP1967292A2 true EP1967292A2 (en) 2008-09-10
EP1967292A3 EP1967292A3 (en) 2013-11-13
EP1967292B1 EP1967292B1 (en) 2014-10-29

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Also Published As

Publication number Publication date
EP1967292B1 (en) 2014-10-29
EP1967292A3 (en) 2013-11-13
US20080219085A1 (en) 2008-09-11
DE202007003532U1 (en) 2007-07-05
US8070352B2 (en) 2011-12-06

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