EP1012404A1 - Working device with mass balancing on the crank mechanism - Google Patents

Working device with mass balancing on the crank mechanism

Info

Publication number
EP1012404A1
EP1012404A1 EP98951314A EP98951314A EP1012404A1 EP 1012404 A1 EP1012404 A1 EP 1012404A1 EP 98951314 A EP98951314 A EP 98951314A EP 98951314 A EP98951314 A EP 98951314A EP 1012404 A1 EP1012404 A1 EP 1012404A1
Authority
EP
European Patent Office
Prior art keywords
mass
crank
tool according
gravity
counter
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
EP98951314A
Other languages
German (de)
French (fr)
Other versions
EP1012404B1 (en
Inventor
Martin Greppmair
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.)
Wacker Construction Equipment AG
Original Assignee
Wacker Werke GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wacker Werke GmbH and Co KG filed Critical Wacker Werke GmbH and Co KG
Publication of EP1012404A1 publication Critical patent/EP1012404A1/en
Application granted granted Critical
Publication of EP1012404B1 publication Critical patent/EP1012404B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
    • E02D3/068—Vibrating apparatus operating with systems involving reciprocating masses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven
    • 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
    • Y10T74/18208—Crank, pitman, and slide
    • 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
    • Y10T74/21—Elements
    • Y10T74/2173—Cranks and wrist pins
    • Y10T74/2183—Counterbalanced
    • 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
    • Y10T74/21—Elements
    • Y10T74/2173—Cranks and wrist pins
    • Y10T74/2183—Counterbalanced
    • Y10T74/2184—Vibration dampers

Definitions

  • the invention relates to a working device according to the preamble of claim 1.
  • the invention relates to a ramming device for soil compaction or a hammer.
  • Known ramming devices of this type are constructed in such a way that an upper mass, which accommodates a motor and a crank mechanism, is connected via a spring set to a working mass which essentially forms a work or compression plate.
  • the rotary movement generated by the engine is converted by the crank mechanism into an oscillating axial movement, which is transferred to the worktop for soil compaction via the spring set.
  • the upper mass comprises approximately two thirds and the striking working mass a third of the total tamping mass, while the distances traveled by the upper mass and the working mass are in inverse relation to each other.
  • the upper mass is of the order of 25 to 30 mm.
  • vibrations of the upper mass are transmitted via a guide bracket to the person guiding the implement, which is very uncomfortable, especially when working for long periods. Vibrations in the horizontal or lateral direction are particularly stressful for the operator. In contrast, vibrations in the vertical direction are required for the rammer to work efficiently.
  • Fig. 2 shows such a known rammer.
  • a drive shaft 1 of the tamper is driven by a motor (not shown), which drives a crank disk 3, which is mounted in the tamper housing and provided with external teeth, via a pinion 2.
  • a crank pin 4 is attached to the crank disk 3, on which a connecting rod 5 is rotatably mounted.
  • the connecting rod 5 is rotatably connected at its other end to a guide piston 7 by means of a piston pin 6.
  • the guide piston 7 carries a piston guide 9 formed by a steel disk and fastened by a nut 8.
  • the guide piston 7 can be moved axially back and forth with the piston guide 9 within a guide tube 10 belonging to the undersize.
  • This axial direction device corresponds to a vertical or working direction of the device during its use.
  • a spring set 11 consisting of several springs is arranged on both sides of the piston guide 9, the springs being supported on their side facing away from the piston guide 9 against spring plates 12 fastened to the guide tube 10.
  • the guide tube 10 with the spring plates 12 belongs to the working or undersize of the rammer.
  • a ramming foot (not shown in FIG. 2) can be attached to the lower mass and is used for soil compaction.
  • the upper mass and the lower mass are connected by an elastic bellows 13.
  • the rotary movement of the engine is converted into an oscillating axial movement of the guide piston 7 by the crank mechanism consisting of the crank disk 3, the crank pin 4 and the connecting rod 5.
  • This axial movement is transmitted via the spring sets 11 to the guide tube 10 and thus to the lower mass and can be used for soil compaction.
  • a tamper is known in which the drive power of the engine is distributed to two crank drives which simultaneously apply a working mass via spring sets. Counter masses are attached to the counter-rotating crank drives, the centrifugal forces of which balance each other out in the horizontal direction, while they add up in the vertical direction, as a result of which the vibration amplitude of the tamper housing is reduced.
  • horizontal vibrations that are stressful for the operator also occur with this device.
  • the invention is therefore based on the object of specifying an implement in which horizontal vibrations of the upper mass can be reduced as they arise.
  • crank mechanism taken on its own, generates considerable vibrations, which, however, overlap and essentially compensate for the vibrations generated by the subordinate components, namely in particular the guide piston and the spring assemblies.
  • the superimposition of the vibrations leads to a considerable calming of the upper mass, especially in the horizontal direction.
  • the mass and the angular offset of the counter mass can be adjusted depending on the properties of the spring set in such a way that the vibrations which are not directed in the working or vertical direction of the implement are minimal. This is possible, for example, during the manufacture or assembly of the crank disk, with an appropriate angular arrangement of the gearboxes depending on the spring set used. gene mass can be provided with a suitable mass.
  • the counter mass is formed in one piece with the crank disk. This leads to simplification of assembly and manufacture.
  • a suitable mold can be used when casting the crank disk or a corresponding die when forging the crank disk.
  • the counter mass can be attached to the crank disk. It is particularly advantageous if the counter mass can be fastened at different points on the crank disk relative to the crank pin at an angle about the axis of rotation of the crank disk. This has the advantage that fine adjustments can be made during assembly, which lead to a further reduction in the horizontal vibrations of the upper mass. It is also possible, without changing the shapes or dies used in the manufacture, to individually coordinate the crank disk and the counterweight when installing different spring assemblies.
  • the difference between the offset angle and 180 ° is at least 10 °.
  • the angle between the center of gravity of the counterweight and the center of gravity of the crank pin with respect to the axis of rotation of the crank disk is approximately 90 °.
  • the mass of the counter mass is larger, preferably even considerably larger than that of the crank pin. This allows the moving masses of the connecting rod, the guide piston and the piston guide to be balanced out by the counter mass.
  • Fig. 1 shows a part of a ramming device according to the invention in
  • FIG. 2 shows a partial section of a known ramming device.
  • crank disk 3 carries a counter mass 14 in the invention.
  • the center of gravity of the counter mass 14 is not arranged with respect to an axis of rotation 15 of the crank disk 3 opposite the crank pin 4, which would correspond to an offset angle of 180 °, but by an angle not equal to 180 °.
  • the offset angle should deviate by at least 10 ° from 180 °, ie be less than 170 ° or greater than 190 °.
  • the center of gravity of the counter mass 14 and the crank pin 4 and the axis of rotation 15 are therefore not on a straight line.
  • the counter mass 14 is produced in one piece with the crank disk 3, for example by forging.
  • the crank pin 4 is also integrally connected to the crank disk 3 and machined to produce a bearing seat.
  • the crank disk 3 essentially has three elements: an essentially balanced carrier disk which carries the axis of rotation 15 and is optionally provided with external teeth, the crank pin 4 and the counter mass 14.
  • the counter mass 14 can, for example, also consist of several individual masses, which are attached to the support plate at different points.
  • the crank disk 3 is designed as in the prior art, but has an attachment option for the counter mass 14.
  • the counter mass 14 can be attached in different angular positions and radii and with different masses depending on the vibration properties of the overall device.
  • a tamper for soil compaction has been described as an example of an implement according to the invention.
  • the invention can also be advantageously used with a hammer, in particular a percussion hammer.
  • a percussion hammer usually has an air spring hammer mechanism instead of the steel springs forming the spring set 11 in the tamper.
  • the generation of the directional vibration by means of a crank mechanism takes place essentially as described above.

Landscapes

  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Soil Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Agronomy & Crop Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Road Paving Machines (AREA)

Abstract

A working device, especially a ramming device for compacting soil, or a hammer, has a crank mechanism (3, 4, 5) for producing a controlled vibration. Said crank mechanism (3, 4, 5) is coupled with a set of springs (11). According to the invention, the crank disk (3) belonging to the crank mechanism is provided with a counter-mass (14) whose centre of gravity is shifted around an angle not equal to 1800 from the centre of gravity of a crank pin (4) on the crank disk (3), in relation to the axis of rotation (15) of the crank disk. This prevents vibrations which would be unpleasant for the person operating the device from occurring.

Description

Arbeitsgerät mit Massenausgleich am Kurbeltrieb Tool with mass balance on the crank mechanism
Die Erfindung betrifft ein Arbeitsgerät gemäß dem Oberbegriff von Patentanspruch 1. Insbesondere betrifft die Erfindung ein Stampfgerät zur Boden- Verdichtung oder einen Hammer.The invention relates to a working device according to the preamble of claim 1. In particular, the invention relates to a ramming device for soil compaction or a hammer.
Bekannte Stampfgeräte dieser Art sind so aufgebaut, da_3 eine einen Motor und einen Kurbeltrieb aufnehmende Obermasse über einen Federsatz mit einer im wesentlichen eine Arbeits- bzw. Verdichtungsplatte bildenden Ar- beitsmasse verbunden ist. Die vom Motor erzeugte Drehbewegung wird durch den Kurbeltrieb in eine oszillierende Axialbewegung gewandelt, die über den Federsatz auf die Arbeitsplatte zur Bodenverdichtung übertragen wird. Die Obermasse umfa_3t etwa zwei Drittel und die schlagende Arbeitsmasse ein Drittel der gesamten Stampfermasse, während die von der Ober- masse und der Arbeitsmasse jeweils zurückgelegten Wege in umgekehrtem Verhältnis zueinander stehen. Dabei bewegt sich die Obermasse in einer Größenordnung von 25 bis 30 mm.Known ramming devices of this type are constructed in such a way that an upper mass, which accommodates a motor and a crank mechanism, is connected via a spring set to a working mass which essentially forms a work or compression plate. The rotary movement generated by the engine is converted by the crank mechanism into an oscillating axial movement, which is transferred to the worktop for soil compaction via the spring set. The upper mass comprises approximately two thirds and the striking working mass a third of the total tamping mass, while the distances traveled by the upper mass and the working mass are in inverse relation to each other. The upper mass is of the order of 25 to 30 mm.
Die Schwingungen der Obermasse werden über einen Führungsbügel auf die das Arbeitsgerät führende Person übertragen, was insbesondere bei längerem Arbeiten sehr unangenehm ist. Besonders belastend sind für den Bediener dabei Schwingungen in Horizontal- bzw. Seitenrichtung. Schwingungen in Vertikalrichtung sind dagegen für ein leistungsfähiges Arbeiten des Stampfers erforderlich.The vibrations of the upper mass are transmitted via a guide bracket to the person guiding the implement, which is very uncomfortable, especially when working for long periods. Vibrations in the horizontal or lateral direction are particularly stressful for the operator. In contrast, vibrations in the vertical direction are required for the rammer to work efficiently.
Fig. 2 zeigt einen derartigen bekannten Stampfer.Fig. 2 shows such a known rammer.
Gemäß Fig. 2 wird von einem nicht dargestellten Motor eine Antriebswelle 1 des Stampfers angetrieben, die über ein Ritzel 2 eine in dem Stampfergehäu- se gelagerte und mit einer Außenverzahnung versehene Kurbelscheibe 3 antreibt. An der Kurbelscheibe 3 ist ein Hubzapfen 4 angebracht, auf den ein Pleuel 5 drehbeweglich aufgesetzt ist. Das Pleuel 5 ist an seinem anderen Ende mittels eines Kolbenbolzens 6 drehbeweglich mit einem Führungskolben 7 verbunden. Der Führungskolben 7 trägt eine durch eine Stahlscheibe gebildete und durch eine Mutter 8 befestigte Kolbenführung 9. Der Führungskolben 7 ist mit der Kolbenführung 9 innerhalb eines zur Untermasse gehörenden Führungsrohrs 10 axial hin- und herbeweglich. Diese Axialrich- tung entspricht einer Vertikal- bzw. Arbeitsrichtung des Geräts während seines Einsatzes.According to FIG. 2, a drive shaft 1 of the tamper is driven by a motor (not shown), which drives a crank disk 3, which is mounted in the tamper housing and provided with external teeth, via a pinion 2. A crank pin 4 is attached to the crank disk 3, on which a connecting rod 5 is rotatably mounted. The connecting rod 5 is rotatably connected at its other end to a guide piston 7 by means of a piston pin 6. The guide piston 7 carries a piston guide 9 formed by a steel disk and fastened by a nut 8. The guide piston 7 can be moved axially back and forth with the piston guide 9 within a guide tube 10 belonging to the undersize. This axial direction device corresponds to a vertical or working direction of the device during its use.
Auf beiden Seiten der Kolbenführung 9 ist ein aus mehreren Federn beste- hender Federsatz 1 1 angeordnet, wobei die Federn jeweils auf ihren von der Kolbenführung 9 abgewandten Seite gegen am Führungsrohr 10 befestigte Federplatten 12 abgestützt sind.A spring set 11 consisting of several springs is arranged on both sides of the piston guide 9, the springs being supported on their side facing away from the piston guide 9 against spring plates 12 fastened to the guide tube 10.
Das Führungsrohr 10 mit den Federplatten 12 gehört zur Arbeits- bzw. Un- termasse des Stampfers. An der Untermasse kann ein in Fig. 2 nicht gezeigter Stampffuß angebracht werden, der zur Bodenverdichtung dient. Um das Eindringen von Feuchtigkeit und Schmutz zu vermeiden, sind die Obermasse und die Untermasse durch einen elastischen Balg 13 verbunden.The guide tube 10 with the spring plates 12 belongs to the working or undersize of the rammer. A ramming foot (not shown in FIG. 2) can be attached to the lower mass and is used for soil compaction. In order to prevent the ingress of moisture and dirt, the upper mass and the lower mass are connected by an elastic bellows 13.
Wie aus Fig. 2 erkennbar, wird die Drehbewegung des Motors durch den aus der Kurbelscheibe 3, dem Hubzapfen 4 und dem Pleuel 5 bestehenden Kurbeltrieb in eine oszillierende Axialbewegung des Führungskolbens 7 gewandelt. Diese Axialbewegung wird über die Federsätze 1 1 auf das Führungsrohr 10 und damit auf die Untermasse übertragen und kann zur Bodenver- dichtung genutzt werden.As can be seen from FIG. 2, the rotary movement of the engine is converted into an oscillating axial movement of the guide piston 7 by the crank mechanism consisting of the crank disk 3, the crank pin 4 and the connecting rod 5. This axial movement is transmitted via the spring sets 11 to the guide tube 10 and thus to the lower mass and can be used for soil compaction.
Zur Dämpfung der auf den Bediener wirkenden Schwingungen war es bisher bekannt, den Führungbügel gegenüber der Obermasse mittels Gummielementen mechanisch zu entkoppeln. Der angebaute Antriebsmotor bleibt da- bei aber weiter hohen Schwingungsbelastungen ausgesetzt. Eine Verbesserung der Schwingungsdämpfung kann hierbei nur durch hohen baulichen Aufwand erzielt werden.To dampen the vibrations acting on the operator, it was previously known to mechanically decouple the guide bracket from the upper mass by means of rubber elements. The attached drive motor remains exposed to high vibration loads. An improvement in vibration damping can only be achieved here with high structural expenditure.
Wünschenswert ist es daher, das Entstehen von Schwingungen der Ober- masse von vornherein zu vermeiden.It is therefore desirable to avoid vibrations of the upper mass from the outset.
Aus der DE-OS 19 25 870 ist ein Stampfer bekannt, bei dem die Antriebsleistung des Motors auf zwei Kurbeltriebe verteilt wird, die gleichzeitig eine Arbeitsmasse über Federsätze beaufschlagen. An den sich gegenläufig drehen- den Kurbeltrieben sind Gegenmassen befestigt, deren Fliehkräfte einander in horizontaler Richtung ausgleichen, während sie sich in Vertikalrichtung summieren, wodurch die Schwingungsamplitude des Stampfergehäuses ver- mindert wird. Auch bei diesem Gerät treten jedoch für den Bediener belastenden Horizontalschwingungen auf.From DE-OS 19 25 870 a tamper is known in which the drive power of the engine is distributed to two crank drives which simultaneously apply a working mass via spring sets. Counter masses are attached to the counter-rotating crank drives, the centrifugal forces of which balance each other out in the horizontal direction, while they add up in the vertical direction, as a result of which the vibration amplitude of the tamper housing is reduced. However, horizontal vibrations that are stressful for the operator also occur with this device.
Der Erfindung liegt daher die Aufgabe zugrunde, ein Arbeitsgerät anzugeben, bei dem Horizontalschwingungen der Obermasse bereits im Entstehen verringert werden können.The invention is therefore based on the object of specifying an implement in which horizontal vibrations of the upper mass can be reduced as they arise.
Erfindungsgemäß wird die Aufgabe durch ein Arbeitsgerät mit den Merkmalen von Patentanspruch 1 gelöst.According to the invention the object is achieved by an implement having the features of claim 1.
Es hat sich überraschenderweise gezeigt, daß ein Auswuchten des Kurbeltriebs, d.h. ein Versehen der den Hubzapfen tragenden Kurbelscheibe mit einer die Masse des Kurbelzapfens ausgleichenden Gegenmasse nicht die gewünschte Verbesserung hinsichtlich einer Reduktion der Horizontalschwin- gungen der Obermasse führt. Vielmehr wurde völlig überraschend herausgefunden, daß die Horizontalschwingungen nur dann wirksam vermindert werden können, wenn der Schwerpunkt des Hubzapfens, die Drehachse der Kurbelscheibe und der Schwerpunkt der Gegenmasse nicht auf einer Geraden liegen und somit die Schwerpunkte bezüglich der Drehachse der Kurbel- scheibe um 180° versetzt sind, sondern wenn der Schwerpunkt der Gegenmasse zum Schwerpunkt des Hubzapfens bezüglich der Drehachse der Kurbelscheibe um einen Winkel ungleich 180° versetzt angeordnet ist.Surprisingly, it has been shown that balancing the crank mechanism, i.e. Providing the crank disk carrying the crank pin with a counter mass that compensates for the mass of the crank pin does not lead to the desired improvement with regard to a reduction in the horizontal vibrations of the upper mass. Rather, it was found completely surprisingly that the horizontal vibrations can only be effectively reduced if the center of gravity of the crank pin, the axis of rotation of the crank disk and the center of gravity of the counter mass are not on a straight line and thus the centers of gravity with respect to the axis of rotation of the crank disk by 180 ° are offset, but if the center of gravity of the counter mass is offset from the center of gravity of the crank pin with respect to the axis of rotation of the crank disk by an angle not equal to 180 °.
Dies bedeutet zwar, daß der Kurbeltrieb, für sich alleine genommen, erhebli- ehe Schwingungen erzeugt, die sich jedoch mit den durch die nachgeordne- ten Bauelemente, nämlich insbesondere den Führungskolben und den Federpaketen erzeugten Schwingungen überlagern und im wesentlichen kompensieren. Im Ergebnis führt das Überlagern der Schwingungen zu einer beträchtlichen Beruhigung der Obermasse, insbesondere in Horizontalrich- tung.This means that the crank mechanism, taken on its own, generates considerable vibrations, which, however, overlap and essentially compensate for the vibrations generated by the subordinate components, namely in particular the guide piston and the spring assemblies. As a result, the superimposition of the vibrations leads to a considerable calming of the upper mass, especially in the horizontal direction.
Bei einer bevorzugten Ausführungsform sind die Masse und der Winkelversatz der Gegenmasse in Abhängigkeit von den Eigenschaften des Federsatzes derart einstellbar, daß die nicht in Arbeits- bzw. Vertikalrichtung des Ar- beitsgeräts gerichteten Schwingungen minimal sind. Dies ist z.B. bei der Fertigung oder der Montage der Kurbelscheibe möglich, wobei je nach verwendetem Federsatz eine entsprechende winkelmäßige Anordnung der Ge- genmasse mit geeigneter Masse vorgesehen werden kann.In a preferred embodiment, the mass and the angular offset of the counter mass can be adjusted depending on the properties of the spring set in such a way that the vibrations which are not directed in the working or vertical direction of the implement are minimal. This is possible, for example, during the manufacture or assembly of the crank disk, with an appropriate angular arrangement of the gearboxes depending on the spring set used. gene mass can be provided with a suitable mass.
Bei einer besonders bevorzugten Ausführungsform ist die Gegenmasse mit der Kurbelscheibe einstückig ausgebildet. Dies führt zu einer Vereinfachung der Montage und der Herstellung. Je nach Herstellungsverfahren kann beim Gießen der Kurbelscheibe eine entsprechende Gießform bzw. beim Schmieden der Kurbelscheibe ein entsprechendes Gesenk verwendet werden.In a particularly preferred embodiment, the counter mass is formed in one piece with the crank disk. This leads to simplification of assembly and manufacture. Depending on the manufacturing process, a suitable mold can be used when casting the crank disk or a corresponding die when forging the crank disk.
Bei einer anderen bevorzugten Ausführungsform ist die Gegenmasse an der Kurbelscheibe befestigbar. Besonders vorteilhaft ist es dabei, wenn die Gegenmasse relativ zu dem Kurbelzapfen winkelmäßig um die Drehachse der Kurbelscheibe an verschiedenen Stellen auf der Kurbelscheibe befestigbar ist. Dies hat den Vorteil, daß bei der Montage Feinabstimmungen vorgenommen werden können, die zu einer weiteren Verminderung der horizontalen Obermassenschwingungen führen. Ebenfalls ist es möglich, ohne Änderung der bei der Herstellung verwendeten Formen oder Gesenke die Kurbelscheibe und die Gegenmasse bei Einbau verschiedener Federpakete jeweils individuell aufeinander abzustimmen.In another preferred embodiment, the counter mass can be attached to the crank disk. It is particularly advantageous if the counter mass can be fastened at different points on the crank disk relative to the crank pin at an angle about the axis of rotation of the crank disk. This has the advantage that fine adjustments can be made during assembly, which lead to a further reduction in the horizontal vibrations of the upper mass. It is also possible, without changing the shapes or dies used in the manufacture, to individually coordinate the crank disk and the counterweight when installing different spring assemblies.
Es hat sich als zweckmäßig erwiesen, wenn die Differenz zwischen dem Versatzwinkel und 180° wenigstens 10° beträgt.It has proven to be expedient if the difference between the offset angle and 180 ° is at least 10 °.
Bei einer besonders vorteilhaften Ausführungsform der Erfindung beträgt der Winkel zwischen dem Schwerpunkt der Gegenmasse und dem Schwer- punkt des Hubzapfens bezüglich der Drehachse der Kurbelscheibe ungefähr 90°.In a particularly advantageous embodiment of the invention, the angle between the center of gravity of the counterweight and the center of gravity of the crank pin with respect to the axis of rotation of the crank disk is approximately 90 °.
Ebenso hat es sich als zweckmäßig herausgestellt, wenn die Masse der Gegenmasse im wesentlichen gleich der Masse des Hubzapfens ist.It has also been found to be expedient if the mass of the counter mass is substantially equal to the mass of the crank pin.
Bei einer anderen Ausführungsform der Erfindung ist die Masse der Gegenmasse größer, vorzugsweise sogar erheblich größer als die des Hubzapfens. Dies ermöglicht es, durch die Gegenmasse auch die sich bewegenden Massen des Pleuels, des Führungskolbens und der Kolbenführung auszuglei- chen. Diese und weitere Merkmale der Erfindung werden nachfolgend unter Zuhilfenahme der Figuren näher erläutert.In another embodiment of the invention, the mass of the counter mass is larger, preferably even considerably larger than that of the crank pin. This allows the moving masses of the connecting rod, the guide piston and the piston guide to be balanced out by the counter mass. These and other features of the invention are explained in more detail below with the aid of the figures.
Es zeigen:Show it:
Fig. 1 einen Teil eines erfindungsgemäßen Stampfgeräts inFig. 1 shows a part of a ramming device according to the invention in
Schnittdarstellung; Fig. 2 einen Teilschnitt eines bekannten Stampfgeräts.Sectional view; Fig. 2 shows a partial section of a known ramming device.
Da wesentliche Bauelemente des erfindungsgemäßen, in Fig. 1 gezeigten Stampfgeräts den bereits in Zusammenhang mit Fig. 2 beschriebenen, bekannten Elementen entsprechen, wird auf eine erneute Beschreibung verzichtet. Zur Vereinfachung werden in den Figuren für gleiche Bauteile auch gleiche Bezugszeichen verwendet.Since essential components of the tamping device according to the invention shown in FIG. 1 correspond to the known elements already described in connection with FIG. 2, a new description is dispensed with. For simplification, the same reference numerals are used in the figures for the same components.
Der wesentliche Unterschied zwischen dem in Fig. 2 gezeigten, bekannten Stampfer und dem erfindungsgemäßen Stampfer aus Fig. 1 besteht darin, daß die Kurbelscheibe 3 bei der Erfindung eine Gegenmasse 14 trägt. Obwohl dies in Fig. 1 nicht ohne weiteres erkennbar ist, ist der Schwerpunkt der Gegenmasse 14 nicht bezüglich einer Drehachse 15 der Kurbelscheibe 3 gegenüber von dem Hubzapfen 4 angeordnet, was einem Versatzwinkel von 180° entsprechen würde, sondern um einen Winkel ungleich 180°. Je nach Ausführungsform sollte der Versatzwinkel um mindestens 10° von 180° abweichen, d.h. kleiner als 170° oder größer als 190° sein. Die Schwerpunkte der Gegenmasse 14 und des Hubzapfens 4 sowie die Drehachse 15 liegen somit nicht auf einer Geraden. Als besonders zweckmäßiger Winkel hat sich dabei ein Winkelversatz der beiden Schwerpunkte von 90° herausgestellt. In dem Fall ist die Phasenlage einer bei Drehung der Kurbelscheibe 3 durch die Masse des Hubzapfens 4 erzeugten Fliehkraft und einer durch die Gegen- masse 14 erzeugten Fliehkraft um einen Winkel von 90° versetzt, wodurch sich die Fliehkräfte nicht gegenseitig aufheben, was bei einem Winkelversatz von 180° und entsprechend gleicher Masse der Fall wäre. Vielmehr wird daher eine resultierende Kraft durch den Kurbeltrieb erzeugt, die sich mit anderen, im wesentlichen durch das Pleuel 5, den Führungskolben 7 und die Federsätze 1 1 erzeugten Kräften überlagert, was insgesamt zu einer Beruhigung der Obermasse führt. Bei der in Fig. 1 gezeigten Ausführungsform ist die Gegenmasse 14 einstük- kig mit der Kurbelscheibe 3 beispielsweise durch Schmieden hergestellt. Der Hubzapfen 4 ist ebenfalls einstückig mit der Kurbelscheibe 3 verbunden und zur Erzeugung eines Lagersitzes bearbeitet worden. Zur begrifflichen Klärung sei darauf hingewiesen, daß die Kurbelscheibe 3 im wesentlichen drei Elemente aufweist: eine im wesentlichen ausgewuchtete Trägerscheibe, die die Drehachse 15 trägt und gegebenenfalls mit einer Außenverzahnung versehen ist, den Hubzapfen 4 und die Gegenmasse 14. Die Gegenmasse 14 kann z.B. auch aus mehreren Einzelmassen bestehen, die an verschiedenen Stellen auf der Trägerscheibe befestigt sind.The essential difference between the known tamper shown in FIG. 2 and the tamper according to the invention from FIG. 1 is that the crank disk 3 carries a counter mass 14 in the invention. 1, the center of gravity of the counter mass 14 is not arranged with respect to an axis of rotation 15 of the crank disk 3 opposite the crank pin 4, which would correspond to an offset angle of 180 °, but by an angle not equal to 180 °. Depending on the embodiment, the offset angle should deviate by at least 10 ° from 180 °, ie be less than 170 ° or greater than 190 °. The center of gravity of the counter mass 14 and the crank pin 4 and the axis of rotation 15 are therefore not on a straight line. An angle offset of 90 ° between the two centers of gravity has proven to be a particularly useful angle. In this case, the phase position of a centrifugal force generated by the mass of the crank pin 4 when the crank disk 3 rotates and a centrifugal force generated by the counter mass 14 are offset by an angle of 90 °, as a result of which the centrifugal forces do not cancel each other out, which is the case with an angular offset of 180 ° and correspondingly the same mass would be the case. Rather, a resulting force is therefore generated by the crank mechanism, which is superimposed on other forces essentially generated by the connecting rod 5, the guide piston 7 and the spring sets 11, which leads to a calming of the upper mass. In the embodiment shown in FIG. 1, the counter mass 14 is produced in one piece with the crank disk 3, for example by forging. The crank pin 4 is also integrally connected to the crank disk 3 and machined to produce a bearing seat. To clarify the concept, it should be pointed out that the crank disk 3 essentially has three elements: an essentially balanced carrier disk which carries the axis of rotation 15 and is optionally provided with external teeth, the crank pin 4 and the counter mass 14. The counter mass 14 can, for example, also consist of several individual masses, which are attached to the support plate at different points.
Bei einer nicht dargestellten Ausführungsform der Erfindung ist die Kurbelscheibe 3 wie beim Stand der Technik ausgebildet, weist jedoch eine Befestigungsmöglichkeit für die Gegenmasse 14 auf. Die Gegenmasse 14 kann je nach Anwendungsfall in verschiedenen Winkelstellungen und Radien sowie mit unterschiedlicher Masse je nach Schwingungseigenschaften des Gesamtgeräts angebracht werden.In an embodiment of the invention, not shown, the crank disk 3 is designed as in the prior art, but has an attachment option for the counter mass 14. Depending on the application, the counter mass 14 can be attached in different angular positions and radii and with different masses depending on the vibration properties of the overall device.
Bisher wurde als Beispiel für ein erfindungsgemäßes Arbeitsgerät ein Stamp- fer zur Bodenverdichtung beschrieben. Die Erfindung kann jedoch auch bei einem Hammer, insbesondere einem Schlaghammer, vorteilhaft angewendet werden. Ein Schlaghammer weist üblicherweise statt der bei dem Stampfer den Federsatz 1 1 bildenden Stahlfedern ein Luftfederschlagwerk auf. Die Erzeugung der gerichteten Schwingung mittels eines Kurbeltriebs erfolgt aber im wesentlichen genauso wie oben beschrieben. So far, a tamper for soil compaction has been described as an example of an implement according to the invention. However, the invention can also be advantageously used with a hammer, in particular a percussion hammer. A percussion hammer usually has an air spring hammer mechanism instead of the steel springs forming the spring set 11 in the tamper. However, the generation of the directional vibration by means of a crank mechanism takes place essentially as described above.

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Arbeitsgerät, insbesondere Stampfgerät zur Bodenverdichtung oder Hammer, mit einer von einem zu einer Obermasse gehörenden Motor über einen einzigen Kurbeltrieb (3, 4, 5) und einen Federsatz (1 1) linear hin- und hertreibbaren Arbeitsmasse, wobei der Kurbeltrieb eine von dem Motor angetriebene Kurbelscheibe (3) aufweist, die exzentrisch zu ihrer Drehachse (15) einen mit einem Pleuel (5) gekoppelten Hubzapfen (4) sowie eine Gegenmasse (14) trägt, und der Schwerpunkt der Gegenmasse (14) bezüglich der Dreh- achse (15) der Kurbelscheibe (3) um einen Winkel ungleich 180° versetzt zum Schwerpunkt des Hubzapfens (4) angeordnet ist.1. Working device, in particular ramming device for soil compaction or hammer, with a working mass belonging to a motor belonging to an upper mass via a single crank mechanism (3, 4, 5) and a spring set (1 1), the crank mechanism being one of the motor-driven crank disc (3), which eccentrically to its axis of rotation (15) carries a crank pin (4) coupled to a connecting rod (5) and a counter mass (14), and the center of gravity of the counter mass (14) with respect to the axis of rotation (15) of the crank disc (3) is offset by an angle not equal to 180 ° to the center of gravity of the crank pin (4).
2. Arbeitsgerät nach Anspruch 1 , dadurch gekennzeichnet, daß die2. Tool according to claim 1, characterized in that the
Masse und der Winkelversatz der Gegenmasse (14) in Abhängigkeit von den Eigenschaften des Federsatzes (1 1) derart einstellbar sind, daß die nicht in eine Arbeitsrichtung des Arbeitsgeräts gerichteten Schwingungen minimal sind.The mass and the angular offset of the counter mass (14) can be adjusted in dependence on the properties of the spring set (11) in such a way that the vibrations which are not directed in one working direction of the implement are minimal.
3. Arbeitsgerät nach einem der vorstehenden Ansprüche, dadurch ge- kennzeichnet, daß die Gegenmasse (14) mit der Kurbelscheibe (3) einstük- kig ausgebildet ist.3. Tool according to one of the preceding claims, characterized in that the counter mass (14) with the crank disc (3) is formed in one piece.
4. Arbeitsgerät nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Gegenmasse ( 14) an der Kurbelscheibe (3) befestigbar ist.4. Tool according to claim 1 or 2, characterized in that the counter mass (14) on the crank disc (3) can be fastened.
5. Arbeitsgerät nach Anspruch 4, dadurch gekennzeichnet, daß die Gegenmasse (14) relativ zu dem Kurbelzapfen (4) winkelmäßig um die Drehachse (15) an verschiedenen Stellen auf der Kurbelscheibe (3) befestigbar ist.5. Tool according to claim 4, characterized in that the counter mass (14) relative to the crank pin (4) angularly about the axis of rotation (15) at different locations on the crank disc (3) can be attached.
6. Arbeitsgerät nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Differenz zwischen dem Versatzwinkel und 180° wenigstens 10° beträgt.6. Tool according to one of the preceding claims, characterized in that the difference between the offset angle and 180 ° is at least 10 °.
7. Arbeitsgerät nach einem der vorstehenden Ansprüche, dadurch ge- kennzeichnet, daß der Winkel zwischen dem Schwerpunkt der Gegenmasse ( 14) und dem Schwerpunkt des Hubzapfens (4) bezüglich der Drehachse ( 15) der Kurbelscheibe (3) ungefähr 90° beträgt. 7. Tool according to one of the preceding claims, character- ized in that the angle between the center of gravity of the counterweight (14) and the center of gravity of the crank pin (4) with respect to the axis of rotation (15) of the crank disc (3) is approximately 90 °.
8. Arbeitsgerät nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Masse der Gegenmasse (14) im wesentlichen gleich der Masse des Hubzapfens (4) ist.8. Tool according to one of the preceding claims, characterized in that the mass of the counterweight (14) is substantially equal to the mass of the crank pin (4).
9. Arbeitsgerät nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Masse der Gegenmasse (14) größer ist als die Masse des Hubzapfens (4). 9. Tool according to one of claims 1 to 7, characterized in that the mass of the counterweight (14) is greater than the mass of the crank pin (4).
EP98951314A 1997-09-10 1998-08-25 Working device with mass balancing on the crank mechanism Expired - Lifetime EP1012404B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19739742 1997-09-10
DE19739742A DE19739742C2 (en) 1997-09-10 1997-09-10 Tool with mass balance on the crank mechanism
PCT/EP1998/005391 WO1999013165A1 (en) 1997-09-10 1998-08-25 Working device with mass balancing on the crank mechanism

Publications (2)

Publication Number Publication Date
EP1012404A1 true EP1012404A1 (en) 2000-06-28
EP1012404B1 EP1012404B1 (en) 2002-04-10

Family

ID=7841878

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98951314A Expired - Lifetime EP1012404B1 (en) 1997-09-10 1998-08-25 Working device with mass balancing on the crank mechanism

Country Status (5)

Country Link
US (1) US6352004B1 (en)
EP (1) EP1012404B1 (en)
JP (1) JP3851083B2 (en)
DE (2) DE19739742C2 (en)
WO (1) WO1999013165A1 (en)

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Also Published As

Publication number Publication date
JP3851083B2 (en) 2006-11-29
DE19739742A1 (en) 1999-03-18
DE19739742C2 (en) 1999-10-21
EP1012404B1 (en) 2002-04-10
WO1999013165A1 (en) 1999-03-18
JP2001515975A (en) 2001-09-25
US6352004B1 (en) 2002-03-05
DE59803762D1 (en) 2002-05-16

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