EP1725373B1 - Transmission a came oscillante - Google Patents

Transmission a came oscillante Download PDF

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Publication number
EP1725373B1
EP1725373B1 EP05715981A EP05715981A EP1725373B1 EP 1725373 B1 EP1725373 B1 EP 1725373B1 EP 05715981 A EP05715981 A EP 05715981A EP 05715981 A EP05715981 A EP 05715981A EP 1725373 B1 EP1725373 B1 EP 1725373B1
Authority
EP
European Patent Office
Prior art keywords
wobble
shaft
ring
drive
balancing
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.)
Not-in-force
Application number
EP05715981A
Other languages
German (de)
English (en)
Other versions
EP1725373B9 (fr
EP1725373A1 (fr
Inventor
Rudolf Berger
Wolfgang Schmid
Otto W. Stenzel
Michael Fischer
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 Construction Equipment AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wacker Construction Equipment AG filed Critical Wacker Construction Equipment AG
Publication of EP1725373A1 publication Critical patent/EP1725373A1/fr
Publication of EP1725373B1 publication Critical patent/EP1725373B1/fr
Application granted granted Critical
Publication of EP1725373B9 publication Critical patent/EP1725373B9/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/391—Use of weights; Weight properties of the tool
    • 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
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the invention relates to a wobble mechanism according to the preambles of claims 1 and 10.
  • wobble-type gear is understood to mean a device for converting a rotational movement into an oscillating translational movement.
  • a rotationally driven rotational element acts on a tumbling element in such a way that it is driven to reciprocate and thereby enable a further element to be translated into linear translation.
  • Such a wobble mechanism is z. B. from the DE 198 51 888 C1 known.
  • a wobble mechanism according to the preamble of claims 1 and 10 is known from DE 3427342 A1 known.
  • Fig. 1 shows an example of a known wobble mechanism for such a Luftfedertschtechnik.
  • a shaft 1 serving as a drive shaft is driven in rotation by a drive (not shown) (eg electric motor) via a gearwheel 2.
  • the shaft 1 is rotatably mounted on bearings 3 and 4 shown schematically. These bearings 3. 4 are usually rolling bearings, which are supported in a housing, not shown, as z. B. also in the DE 198 51 888 C1 is shown.
  • a pivot bearing 5 is fixed with an inner ring 5a.
  • the inner ring 5a must be connected to the shaft 1 z. B. rotatably connected via a press fit.
  • the shaft 1 and the inner ring 5a can be made in one piece.
  • the inner ring 5 a has an annular inner running surface 6 which lies in a plane which is not perpendicular to a rotation axis 7 of the shaft 1.
  • the angle ⁇ between the plane of the inner running surface and the plane perpendicular to the rotation axis 7 is approximately 30 °.
  • a wobble ring 8 Arranged around the inner ring 5a is a wobble ring 8, which has on its inner side an outer running surface 9 assigned to the inner running surface 6. Between the inner race 6 and the outer race 9 rolling elements 10 are arranged to be movable in a known manner.
  • the inner ring 5a with the inner race 6, the Taumelfingerring 8 with the outer race 9 and the rolling elements 10 together operatively form the pivot bearing 5, which is designed in the example shown as a rolling bearing.
  • other types of bearings such. B. plain bearings use.
  • a wobble finger 12 extends radially from an articulation point 11 to a central axis 13 of the wobble ring 8.
  • the shaft 1 is rotated together with the inner ring 5a. Due to the inclined inner race surface 6, the rolling elements 10 revolving therein and, with them, the wobble ring 8 are set in a tumbling motion, which can be converted into a linear reciprocating motion by the guidance of the piston pin 14 and the drive piston 15.
  • the wobble finger 12 is a significant imbalance mass which, with rapid movement (several hundred beats per minute), results in significant additional pendulum bearing loads acting on both the machine (bearings, housings) and the operator holding the machine.
  • the invention has for its object to reduce in a wobble gear generated by the movement of the wobble finger unbalance forces and thus prevent vibration unrest of the wobble mechanism.
  • At least one counterbalancing mass is formed on the shaft.
  • the balancing mass is to be provided in addition to the pivot bearing held by the shaft and an imbalance caused by its asymmetrical design.
  • the additional, constructively provided balancing mass generates an imbalance force on the shaft which, with appropriate dimensioning and design, can be superimposed on the imbalance force generated by the movement of the wobble finger in such a way that the imbalance forces at least partially cancel out or at least diminish in the resultant ,
  • the rotary bearing has a formed on the shaft inner ring, which is associated with a Taumelfingerring. Between the inner ring and the Taumelfingerring belonging to the rotary bearing rolling elements can rotate.
  • the balance mass can be created by adding mass elements to the shaft. Alternatively, it is also possible to produce a corresponding balancing mass by removing material elsewhere in the shaft.
  • the shaft is mounted on two bearings, each of the bearings is assigned a balancing mass.
  • balancing mass is to be understood abstractly.
  • a balancing mass can also be formed by a plurality of individual mass elements, which are to be arranged according to each other for generating a common mass effect.
  • each balancing mass at the bearing point assigned to it is able to selectively generate a counteracting the effect of the wobble finger counterforce, in order to reduce the resulting bearing force in this way.
  • the axial distance between a bearing and the respectively associated therewith balancing mass is minimal. In this way, the effect of the balancing mass can be transferred particularly well to its associated bearing point.
  • the balancing masses associated with the two bearing points are arranged opposite one another with respect to the axis of rotation of the shaft. This means that the centrifugal forces generated by the balancing masses are offset by 180 ° to each other. In addition, the two balancing masses generate a torque about the center of the shaft, which counteracts the wobble generated by the wobble finger.
  • the wobble ring is essentially rotationally symmetrical, with the exception of the region from which the wobble finger extends radially.
  • the Taumelfingerring should have the lowest possible weight to avoid the emergence of additional tumbling moments.
  • underlying object is provided on the wobble ring at least one balancing mass in a range that neither at the articulation point, still, based on the center axis of the wobble ring, opposite of the articulation point at the the wobble finger extends radially from the wobble ring is located.
  • the arranged between the shaft and the Taumelfingerring, obliquely rotating bearings can be realized by different types of bearings, the rolling bearing is preferable due to the lower friction and high wear resistance.
  • two balancing masses are provided which are arranged opposite one another on the wobble ring, relative to the central axis of the wobble ring.
  • the balancing masses with the same angular distance, preferably with 90 ° relative to the center axis of the wobble ring, relative to the pivot point of the wobble finger.
  • the wobble ring with the exception of the point of articulation, from which the wobble finger extends, and the areas in which the additional balance masses are provided, is substantially rotationally symmetrical. It has been found that the arrangement of balancing masses in areas other than those defined above does not lead to an improvement in the vibration situation, but rather to an increase in the imbalance forces and thus the vibrations.
  • the two solutions of the problem described above separately from each other are combined.
  • the wobble gear on the one hand has a shaft to which additional balancing masses are attached, and on the other hand also on the wobble ring balancing masses are provided in the manner described above.
  • the combination of balancing masses and the resulting total forces and moments cause a significant reduction in unwanted vibrations.
  • Fig. 1 In the known wobble mechanism of Fig. 1 occur at the bearings 3, 4 bearing loads, which are plotted in Fig. 2 by way of example over time.
  • the curve a represents the bearing forces in the direction of a transverse axis (horizontal plane), while the curve b corresponds to the bearing load in the direction of the machine vertical axis. It is assumed that the wobble finger 12 is directed substantially vertically, ie in the direction of the machine vertical axis.
  • Fig. 3 accesses from Fig. 1, the essential components, namely the shaft 1, the Taumelfingerring 8 and the wobble finger 12. Furthermore, the bearings 3 and 4 are shown symbolically. Incidentally, the detailed technical embodiment can essentially be carried out according to FIG. 1.
  • balancing masses 20 and 21 are provided on the shaft 1, wherein the balancing mass 20 as close as possible (relative to the axial distance a) to the bearing point 3 and the balancing mass 21 are arranged as close as possible to the bearing point 4. Furthermore, it can be seen in FIG. 3 that the balancing masses 20 and 21 are arranged opposite one another with respect to the axis of rotation 7 of the shaft. As a result, the balancing masses 20 and 21 generate a torque about the axis X, which is opposite to the tumbling moment of the wobble finger 12.
  • the distance a of the balancing mass 20 to the bearing 3 and according to the distance from the balancing mass 21 to the bearing 4 should be as low as possible in order to develop a maximum effect of the balancing masses 20, 21. This results from the fact that the closer the balancing weights 20, 21 are to the bearing points 3, 4, the greater the momentum around the X axis.
  • the balancing masses 20, 21 may, as shown in Fig. 3, be formed by attaching additional mass elements. Alternatively, it is also possible to remove material from the shaft 1 in each case on the opposite shaft side in order to produce the desired force. As a force, the product of a balancing mass is generally referred to with the distance of its center of gravity from the axis of rotation 7.
  • the total bearing load c shown in FIG. 2 can be reduced.
  • the curve c of Fig. 2 is taken.
  • the curve d corresponds to the course of the total bearing load when the balancing masses 20, 21 are provided on the shaft 1. The resulting significant reduction of the total storage loads can be seen directly in Fig. 4.
  • the balancing masses 22, 23 are arranged opposite each other in a region which is offset in each case by 90 ° relative to the articulation point 11 of the wobble finger 12.
  • the balancing masses 22, 23 lead to an alignment of the maximum bearing forces in the high (Y) and transverse (X) directions of the machine, whereby the effective bearing forces can be made uniform. As was shown in FIG. 2, the bearing forces acting in the machine vertical axis (curve b) are greater than the forces in the transverse machine axis (curve a).
  • the first and second embodiments in themselves already bring a significant improvement to the reduction of unwanted vibration forces.
  • the combination of the first and second embodiments to the third embodiment allows even further vibration reduction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • Transmission Devices (AREA)

Abstract

La présente invention concerne une transmission à came oscillante, dans laquelle un arbre (1) porte, par l'intermédiaire d'un palier de pivotement (5), un anneau à came oscillante (8) duquel part une came oscillante (12). Afin de limiter les oscillations qui résultent du mouvement de la came oscillante (12), au moins une masse d'équilibrage (20, 21) est montée sur l'arbre (1). De façon alternative ou en complément, au moins une masse d'équilibrage (22, 23) peut être montée sur l'anneau à came oscillante (8). Cela permet d'équilibrer les oscillations produites naturellement par le mouvement de la came oscillante (12).

Claims (18)

  1. Transmission à came oscillante, comprenant
    - un arbre (1);
    - un palier de rotation (5) disposé sur l'arbre (1) et incliné par rapport à un axe de rotation (7) de l'arbre (1);
    - une came oscillante (12) s'étendant à partir de l'axe de rotation (7) de l'arbre (1) et maintenue par le palier de rotation (5),
    caractérisée en ce qu'au moins une masse d'équilibrage (20, 21) est réalisée sur l'arbre (1).
  2. Transmission à came oscillante selon la revendication 1, caractérisée en ce que la masse d'équilibrage (20, 21) est disposée sur l'arbre (1) de telle sorte qu'elle s'oppose au déséquilibre dû à la conception de la transmission à came oscillante.
  3. Transmission à came oscillante selon la revendication 1 ou 2, caractérisée en ce que
    - le palier tournant (5) présente une bague intérieure (5a) réalisée sur l'arbre (1), avec une surface de roulement intérieure (6) de forme annulaire pour des corps de roulement (10), la surface de roulement intérieure (6) étant disposée dans un plan qui n'est pas perpendiculaire à l'axe de rotation (7) de l'arbre (1) ;
    - au palier tournant (5) est attribuée une bague de came oscillante (8) disposée autour de la bague intérieure (5a), avec une surface de roulement extérieure (9) de forme annulaire, et attribuée à la surface de roulement intérieure (6) pour les corps de roulement (10); et en ce que
    - la came oscillante (12) s'étend à partir de la bague de came oscillante (8) radialement vers un axe médian (13) de la bague de came oscillante (8).
  4. Transmission à came oscillante selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la masse d'équilibrage (20, 21) peut être fabriquée par enlèvement de matériau de l'arbre (1).
  5. Transmission à came oscillante selon l'une quelconque des revendications 1 à 4, caractérisée en ce que
    - l'arbre (1) est logé sur au moins deux points de palier (3, 4);
    - au moins une masse d'équilibrage (20, 21) est attribuée au moins à l'un des points de palier (3, 4).
  6. Transmission à came oscillante selon la revendication 5, caractérisée en ce que
    - l'arbre (1) est logé sur deux points de palier (3, 4) et en ce que
    - une masse d'équilibrage (20, 21) est attribuée à chacun des points de palier (3, 4).
  7. Transmission à came oscillante selon la revendication 6, caractérisée en ce que la distance axiale (a) entre un point de palier (3) et la masse d'équilibrage (20) qui lui est attribuée est minimale.
  8. Transmission à came oscillante selon la revendication 6 ou 7, caractérisée en ce que les masses d'équilibrage (20, 21) attribuées aux deux points de palier (3, 4) sont disposées en face de l'arbre (1) par rapport à l'axe de rotation (7).
  9. Transmission à came oscillante selon l'une quelconque des revendications 1 à 8, caractérisée en ce que la bague de came oscillante (8) est sensiblement symétrique en rotation à l'exception de la zone à partir de laquelle s'étend la came oscillante (12).
  10. Transmission à came oscillante, comprenant
    - un arbre (1) ;
    - un palier de rotation (5) disposé sur l'arbre (1) et incliné par rapport à un axe de rotation (7) de l'arbre (1) ;
    - une bague à came oscillante (8) maintenue par le palier de rotation (5) ;
    - une came oscillante (12) s'étendant sur un point d'articulation (11) à partir de la bague de came oscillante (8) radialement par rapport à un axe médian (13) de la bague de came oscillante (8) ;
    caractérisée en ce que sur la bague de came oscillante (8) est prévue au moins une masse d'équilibrage (22, 23) dans une zone qui est située ni sur le point d'articulation (11) ni, par rapport à l'axe médian (13) de la bague de came oscillante (8), en face du point d'articulation (11).
  11. Transmission à came oscillante selon la revendication 10, caractérisée en ce que
    - le palier de rotation (5) présente une bague intérieure (5a) réalisée sur l'arbre (1), avec une surface de roulement intérieure (6) de forme annulaire pour des corps de roulement (10), la surface de roulement intérieure (6) étant disposée dans un plan qui n'est pas perpendiculaire à l'axe de rotation (7) de l'arbre (1), et en ce que
    - la bague de came oscillante (8) est attribuée à la bague intérieure (5a) et présente une surface de roulement extérieure (9) de forme annulaire, associée à la surface de roulement intérieure (6) pour les corps de roulement (10).
  12. Transmission à came oscillante selon la revendication 10 ou 11, caractérisée en ce que deux masses d'équilibrage (22, 23) sont prévues, lesquelles sont disposées sur la bague de came oscillante (8) en face l'une de l'autre par rapport à l'axe médian (13) de la bague de came oscillante (8).
  13. Transmission à came oscillante selon l'une quelconque des revendications 10 à 12, caractérisée en ce que deux masses d'équilibrage (22, 23) sont prévues, et en ce que le point d'articulation (11) est à une distance d'angle identique aux deux masses d'équilibrage (22, 23) par rapport à l'axe médian (13) de la bague de came oscillante (8).
  14. Transmission à came oscillante selon l'une quelconque des revendications 10 à 13, caractérisée en ce que
    - une masse d'équilibrage (22) est disposée dans une zone de la bague de came oscillante (8), qui est décalée par rapport au point d'articulation (11) de la came oscillante (12) de +90° par rapport à l'axe médian (13) de la bague de came oscillante (8), et en ce que
    - l'autre masse d'équilibrage (23) est disposée dans une zone de la bague de came oscillante (8) qui est décalée par rapport au point d'articulation (11) de la came oscillante (8) de -90° par rapport à l'axe médian (13) de la bague de came oscillante (8).
  15. Transmission à came oscillante selon l'une quelconque des revendications 10 à 14, caractérisée en ce que la bague de came oscillante (8) est sensiblement symétrique en rotation à l'exception du point d'articulation (11), à partir duquel s'étend la came oscillante (12), et les zones dans lesquelles les masses d'équilibrage (22, 23) sont prévues.
  16. Transmission à came oscillante selon l'une quelconque des revendications 10 à 15, caractérisée en ce que la masse d'équilibrage (22, 23) peut être fabriquée par enlèvement de matériau de la bague de came oscillante (8).
  17. Transmission à came oscillante selon au moins l'une quelconque des revendications 1 à 9 et au moins l'une des revendications 10 à 16.
  18. Transmission à came oscillante selon l'une quelconque des revendications 1 à 17, caractérisée en ce qu'une masse d'équilibrage (20, 21, 22, 23) est formée de plusieurs éléments de masse d'équilibrage.
EP05715981A 2004-03-16 2005-03-11 Transmission a came oscillante Not-in-force EP1725373B9 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004012820A DE102004012820B3 (de) 2004-03-16 2004-03-16 Taumelfingergetriebe
PCT/EP2005/002620 WO2005092575A1 (fr) 2004-03-16 2005-03-11 Transmission a came oscillante

Publications (3)

Publication Number Publication Date
EP1725373A1 EP1725373A1 (fr) 2006-11-29
EP1725373B1 true EP1725373B1 (fr) 2007-07-04
EP1725373B9 EP1725373B9 (fr) 2007-10-24

Family

ID=34961358

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05715981A Not-in-force EP1725373B9 (fr) 2004-03-16 2005-03-11 Transmission a came oscillante

Country Status (7)

Country Link
US (1) US20070163370A1 (fr)
EP (1) EP1725373B9 (fr)
JP (1) JP2007529696A (fr)
CN (1) CN1898066A (fr)
DE (2) DE102004012820B3 (fr)
ES (1) ES2286799T3 (fr)
WO (1) WO2005092575A1 (fr)

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EP1818141A3 (fr) * 2003-03-21 2007-11-28 Black & Decker, Inc. Système limitant les vibrations pour outil électrique, et outil électrique incorporant ce système

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EP2163355A1 (fr) * 2008-09-12 2010-03-17 AEG Electric Tools GmbH Outil électrique comprenant un entraînement oscillant ou vilebrequin ayant une masse réduite
AU2010263293B2 (en) * 2009-06-25 2015-11-26 Atlas Copco Airpower, Naamloze Venootschap Hand-held demolition tool
DE102009044934A1 (de) * 2009-09-24 2011-03-31 Robert Bosch Gmbh Pleuelantrieb mit Zusatzschwinger
EP2543808B1 (fr) * 2011-07-05 2020-03-04 U-Shin Deutschland Zugangssysteme GmbH Dispositif d'actionneur pour l'activation automatique de la porte d'un véhicule motorisé
DE102012005864A1 (de) 2011-10-22 2013-04-25 Wolfgang Schmid Taumelwelle mit integrierter Sicherheitskupplung und Verriegelung
DE102013212554B4 (de) * 2013-06-28 2023-12-14 Robert Bosch Gmbh Handwerkzeugmaschinenantriebsvorrichtung
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1818141A3 (fr) * 2003-03-21 2007-11-28 Black & Decker, Inc. Système limitant les vibrations pour outil électrique, et outil électrique incorporant ce système

Also Published As

Publication number Publication date
CN1898066A (zh) 2007-01-17
JP2007529696A (ja) 2007-10-25
EP1725373B9 (fr) 2007-10-24
US20070163370A1 (en) 2007-07-19
EP1725373A1 (fr) 2006-11-29
WO2005092575A1 (fr) 2005-10-06
DE502005000984D1 (de) 2007-08-16
ES2286799T3 (es) 2007-12-01
DE102004012820B3 (de) 2005-11-17

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