EP1725373A1 - Transmission a came oscillante - Google Patents

Transmission a came oscillante

Info

Publication number
EP1725373A1
EP1725373A1 EP05715981A EP05715981A EP1725373A1 EP 1725373 A1 EP1725373 A1 EP 1725373A1 EP 05715981 A EP05715981 A EP 05715981A EP 05715981 A EP05715981 A EP 05715981A EP 1725373 A1 EP1725373 A1 EP 1725373A1
Authority
EP
European Patent Office
Prior art keywords
wobble
ring
shaft
finger
wobble finger
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
EP05715981A
Other languages
German (de)
English (en)
Other versions
EP1725373B9 (fr
EP1725373B1 (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
Application granted granted Critical
Publication of EP1725373B1 publication Critical patent/EP1725373B1/fr
Publication of EP1725373B9 publication Critical patent/EP1725373B9/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 finger transmission according to the preambles of claims 1 and 10.
  • wobble finger gear means a device for converting a rotational movement into an oscillating translational movement.
  • a rotationally driven rotation element acts on a wobble element in such a way that it is driven back and forth and can thereby set another element in linear translation motion.
  • Such a wobble gear is such. B. from DE 198 51 888 C1.
  • Swash finger gears are - as described in DE 198 51 888 Cl - z. B. used in rotary or percussion hammers to convert the rotary movement of a drive into an oscillating translational movement, which can be used in a striking mechanism to apply impacts to a tool.
  • Fig. 1 shows an example of a known wobble finger transmission for such an air spring hammer mechanism.
  • a shaft 1 serving as a drive shaft is driven in rotation by a drive (not shown) (e.g. electric motor) via a gearwheel 2.
  • the shaft 1 is rotatably supported at schematically illustrated bearings 3 and 4.
  • These bearings 3, 4 are usually roller bearings that are supported in a housing, not shown, as z. B. is also shown in DE 198 51 888 C1.
  • a rotary bearing 5 is fastened with an inner ring 5a.
  • the inner ring 5a must with the shaft 1 z. B. be connected in a rotationally fixed manner via a press fit. If necessary, the shaft 1 and the inner ring 5a can also be produced in one piece.
  • the inner ring 5a has an annular inner tread 6, which in a
  • the angle ⁇ between the plane of the inner running surface and the plane perpendicular to the axis of rotation 7 is approximately 30 °.
  • a wobble finger ring 8 Arranged around the inner ring 5a is a wobble finger ring 8, which has an outer race surface 9 assigned to the inner race surface 6 on its inside.
  • Rolling elements 10 are arranged movably in a known manner between the inner running surface 6 and the outer running surface 9.
  • the inner ring 5a with the inner race 6, the wobble ring 8 with the outer race 9 and the rolling elements 10 together form the rotary bearing 5, which is designed as a rolling bearing in the example shown.
  • other types of storage such.
  • B. Use plain bearings.
  • a wobble 12 extends radially from a pivot point 11 to a central axis 13 of the wobble ring 8.
  • FIG. 1 a percussion piston 16 belonging to the air spring hammer mechanism is shown in FIG. 1.
  • Such air spring hammer mechanisms are known. However, since they do not relate to the subject matter of the invention, no further explanation is given.
  • the shaft 1 is rotated together with the inner ring 5a. Due to the inclined inner running surface 6, the rolling elements 10 rotating therein and with them the wobble finger ring 8 are set in a wobble movement, which can be converted into a linear reciprocating movement by guiding the piston pin 14 and the drive piston 15.
  • the wobble finger 12 represents a considerable unbalanced mass which, when moving rapidly (several hundred beats per minute), leads to considerable additional, oscillating bearing loads, both on the machine
  • the invention has for its object to reduce the imbalance forces generated by the movement of the wobble finger transmission and thus prevent vibration of the wobble transmission.
  • At least one balancing mass is formed on the shaft.
  • the balancing mass is to be provided in addition to the rotary bearing held by the shaft and an unbalance caused by its asymmetrical design.
  • the additional, structurally provided balancing mass generates an unbalance force on the shaft which, with appropriate dimensioning and design, can be superimposed on the unbalance force generated by the movement of the wobble finger in such a way that the unbalance forces are at least partially canceled out or at least reduced in the resultant - that.
  • the rotary bearing has an inner ring formed on the shaft, to which a wobble finger ring is assigned. Rolling elements belonging to the rotary bearing can circulate between the inner ring and the wobble ring.
  • the balancing mass can be generated by adding mass elements to the shaft. As an alternative to this, it is also possible to produce a corresponding balancing mass by removing material elsewhere on the shaft. In a particularly advantageous embodiment of the invention, the
  • balancing mass Shaft mounted on two bearings, each of which is assigned a balancing mass.
  • the term "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 corresponding to one another in order to produce a common mass effect.
  • each balancing mass at the bearing point assigned to it is able to specifically generate a counterforce superimposed on the effect of the wobble finger, in order to reduce the resulting bearing force in this way.
  • the axial distance between a bearing point and the balancing mass assigned to it is minimal. In this way, the effect of the balancing mass can be transferred particularly well to the bearing location assigned to it.
  • the balancing masses assigned to 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.
  • the two balancing masses generate a torque around the center of the shaft, which counteracts the wobble moment generated by the wobble finger.
  • the wobble finger ring is essentially rotationally symmetrical, with the exception of the region from which the wobble finger extends radially.
  • the wobble ring should be as light as possible in order to avoid additional wobble moments.
  • At least one balancing mass is provided on the wobble ring in an area which is neither at the articulation point nor, relative to the central axis of the wobble ring, opposite the articulation point at which the wobble finger extends radially from the wobble ring.
  • the inclined rotary bearing arranged between the shaft and the wobble ring can be realized by different bearing types, the rolling bearing being preferred because of the lower friction and high wear resistance.
  • balancing masses are provided which are arranged opposite one another on the wobble ring, based on the central axis of the wobble ring.
  • the balancing masses should be at the same angular distance, preferably at 90 ° with respect to the central axis of the wobble ring, relative to the articulation point of the wobble finger.
  • the wobble finger ring is essentially rotationally symmetrical, with the exception of the articulation point from which the wobble finger extends and the areas in which the additional balancing masses are provided. 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 unbalance forces and thus the vibrations.
  • the two solutions to the problem described separately above are combined with one another.
  • the wobble finger gear has a shaft on which additional balancing masses are attached, and secondly balancing masses are also provided on the wobble finger ring in the manner described above.
  • the combination of the balancing masses and the resulting total forces and moments result in a significant reduction in unwanted vibrations.
  • FIG. 1 shows a schematic section through a wobble finger transmission known from the prior art for an air spring hammer mechanism
  • FIG. 5 shows a diagram to explain the bearing loads in the event of imbalance on the shaft and on the wobble ring (third embodiment of the invention).
  • FIG. 3 takes up the essential components from FIG. 1, namely the shaft 1, the wobble finger ring 8 and the wobble finger 12. Furthermore, the
  • Bearing positions 3 and 4 are shown symbolically. The detailed technical implementation can, moreover, take place essentially according to FIG. 1.
  • balancing masses 20 and 21 are provided on the shaft 1, the balancing mass 20 being arranged as close as possible (based on the axial distance a) to the bearing point 3 and the balancing mass 21 as closely as possible to the bearing point 4. 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 wobble moment of the wobble finger 12.
  • the dimensioning of the balancing masses 20, 21, in particular their mass and their distance from the axis of rotation 7, can easily be determined by a person skilled in the art by experiments.
  • the distance a from the balancing mass 20 to the bearing point 3 and correspondingly the distance from the balancing mass 21 to the bearing point 4 should be as small as possible in order to develop the maximum effect of the balancing masses 20, 21. This results from the fact that the closer the balancing masses 20, 21 are to the bearing points 3, 4, the greater the moment about the X axis.
  • the balancing masses 20, 21 can, as shown in FIG. 3, be formed by attaching additional mass elements. Alternatively, material can also be removed from the shaft 1 on the opposite shaft side in order to generate the desired force. In general, the product of a balancing mass with the distance of its center of gravity from the axis of rotation 7 is referred to as the balance. With suitable dimensioning and arrangement of the balancing masses 20,
  • balancing masses 22 and 23 are attached to the wobble ring 8 (FIG. 3).
  • no balancing masses 20, 21 are formed on the shaft 1.
  • the balancing masses 22, 23 are arranged opposite one another in an area which is offset by 90 ° with respect 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 vertical (Y) and transverse directions (X) of the machine, as a result of which the effective bearing forces can be equalized. As was shown in FIG. 2, the bearing forces acting in the machine vertical axis (curve b) are greater than the forces in the machine transverse axis (curve a).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (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).
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 true EP1725373A1 (fr) 2006-11-29
EP1725373B1 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)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009007152A1 (fr) * 2007-07-06 2009-01-15 Robert Bosch Gmbh Machine-outil à main avec un support sur palier lisse intégré dans le palier d'entraînement de levage

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2119536B1 (fr) 2003-03-21 2017-08-23 Black & Decker Inc. Outil électrique incorporant un appareil de réduction de vibration
JP4756474B2 (ja) * 2006-07-20 2011-08-24 日立工機株式会社 電動工具
DE102007061716A1 (de) * 2007-12-19 2009-06-25 Robert Bosch Gmbh Taumelantrieb einer Handwerkzeugmaschine
DE102008000687A1 (de) * 2008-03-14 2009-09-17 Robert Bosch Gmbh Handwerkzeugmaschine für schlagend angetriebene Einsatzwerkzeuge
EP2163355A1 (fr) * 2008-09-12 2010-03-17 AEG Electric Tools GmbH Outil électrique comprenant un entraînement oscillant ou vilebrequin ayant une masse réduite
CN102802876B (zh) * 2009-06-25 2015-03-25 阿特拉斯科普柯建筑设备有限公司 手持式拆除工具
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
JP6325360B2 (ja) * 2014-06-12 2018-05-16 株式会社マキタ 打撃工具
DE102015203487A1 (de) * 2015-02-26 2016-09-01 Ecoroll Ag Werkzeugtechnik Festhammervorrichtung zum Beeinflussen von Werkstücken und zugehöriges Verfahren
DE102020212425A1 (de) * 2020-10-01 2022-04-07 Robert Bosch Gesellschaft mit beschränkter Haftung Lagerflansch für ein Antriebssystem einer Handwerkzeugmaschine, sowie Bohrhammer mit einem Schlagwerk und einem Lagerflansch

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009007152A1 (fr) * 2007-07-06 2009-01-15 Robert Bosch Gmbh Machine-outil à main avec un support sur palier lisse intégré dans le palier d'entraînement de levage

Also Published As

Publication number Publication date
EP1725373B9 (fr) 2007-10-24
WO2005092575A1 (fr) 2005-10-06
ES2286799T3 (es) 2007-12-01
DE502005000984D1 (de) 2007-08-16
US20070163370A1 (en) 2007-07-19
JP2007529696A (ja) 2007-10-25
EP1725373B1 (fr) 2007-07-04
CN1898066A (zh) 2007-01-17
DE102004012820B3 (de) 2005-11-17

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