EP0050192B2 - Perceuse à percussion - Google Patents

Perceuse à percussion Download PDF

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Publication number
EP0050192B2
EP0050192B2 EP81105591A EP81105591A EP0050192B2 EP 0050192 B2 EP0050192 B2 EP 0050192B2 EP 81105591 A EP81105591 A EP 81105591A EP 81105591 A EP81105591 A EP 81105591A EP 0050192 B2 EP0050192 B2 EP 0050192B2
Authority
EP
European Patent Office
Prior art keywords
intermediate shaft
hammer drill
drill according
hub member
hammer
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.)
Expired
Application number
EP81105591A
Other languages
German (de)
English (en)
Other versions
EP0050192A1 (fr
EP0050192B1 (fr
Inventor
Manfred Bleicher
Manfred Dipl.-Ing. Buck
Jörg Fälchle
Karl Dr.-Ing. Wanner
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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
Family has litigation
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Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0050192A1 publication Critical patent/EP0050192A1/fr
Application granted granted Critical
Publication of EP0050192B1 publication Critical patent/EP0050192B1/fr
Publication of EP0050192B2 publication Critical patent/EP0050192B2/fr
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/006—Mode changers; Mechanisms connected thereto
    • 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

Definitions

  • the invention relates to a hammer drill of the type of the main claim (DE-OS-2 449 191).
  • a hammer drill has already become known, in which the striking mechanism was automatically put into operation when the tool held in the tool holder of the hammer drill was attached to the workpiece to be machined. This is done by a longitudinal movement of the tool holder, wherein a clutch that sets the striking mechanism in motion is actuated. To keep the clutch in its engaged position, the operator must always overcome the force of a spring that attempts to disengage the clutch. Pure drilling without axial loading of the tool is not possible with the known hammer drill.
  • the hammer drill according to the invention with the characterizing features of the main claim has the advantage that in the - by the operator intentionally set - percussion drilling, the clutch, via which the swash plate drive is set in motion, is held in engagement by a clutch. This significantly simplifies the handling of the rotary hammer.
  • This hammer drill also offers the option of being used as a drilling machine. This opens up the possibility of creating a light hand drill, which is therefore suitable for DIY use, but which can still be used with the highly effective air cushion hammer mechanism that was previously reserved for relatively heavy handicraft machines.
  • FIG. 3 contains two partial sections rotated about the axis of the intermediate shaft in the plane of the drawing.
  • the viewing directions are labeled III 'and III' in FIG. 3; the corresponding areas are numbered the same in FIG. 2.
  • the hammer drill shown in Fig. 1 of the drawing has a metal gear housing 1, which is arranged in an outer plastic shell 2. At its front end, the plastic shell merges into a cylindrical housing extension 3, which is designed, for example, for clamping additional devices - here a handle 4. At the front end of the housing extension 3, a tool holder 5 is arranged on the hammer drill, which is used to hold tools (not shown) - here a drill 6.
  • a pistol handle 7 is molded onto the plastic housing shell 2 at the rear end facing away from the tool holder 5.
  • a switch is provided with a pusher 8, via which the hammer drill can be put into operation.
  • a power supply cable 9 is inserted through an elastic grommet.
  • the gear housing essentially consists of a transverse wall 10, in which a bearing seat 11 for a front laser of an armature shaft 13 of an electric motor designed as a ball bearing 12 is arranged approximately in the center.
  • the electric motor of which essentially only the front part of the armature shaft 13 is shown in the drawing, thus lies on the side of the transverse wall 10 of the transmission housing 1 facing away from the tool holder 5.
  • the transverse wall 10 carries a tubular extension 14 on the side facing away from the electric motor , in which a cylindrical sleeve 16 for an air cushion hammer mechanism 15 is arranged.
  • the extension 14 carries a flange 17 which, in a tubular fitting 18 in the interior of the housing shell 2, supports the gear housing 1 on its front side.
  • the gear housing 1 is supported on the other side with the transverse wall 10 on the inner surface of the housing shell 2.
  • an O-ring 19 is inserted in an annular groove on the outer edge of the transverse wall 10, which contacts the inner wall of the housing shell 2 with a slight prestress.
  • the transverse wall 10 is supported on stops 20 formed by thickening the wall of the housing shell 2.
  • Fig. 2 of the drawing it can be seen that the extension 14 and the bearing seat 11, in which The armature shaft 13 is guided concentrically, are arranged in the longitudinal center plane 21 of the hammer.
  • the end of the armature shaft 13 which is mounted in the ball bearing 12 carries a motor pinion 22.
  • the motor pinion 22 in turn meshes with a gearwheel 23 which is seated on an intermediate shaft 24 in a rotationally fixed manner.
  • the intermediate shaft 24, which is arranged laterally offset to the longitudinal center plane 21, has an outer spline toothing 25 over its entire length and is held in a deep groove ball bearing 26 with its end facing the transverse wall 10.
  • the outer spline toothing 25 has been turned in the area of the deep groove ball bearing 26, it is supported on the inner ring of the deep groove ball bearing 26 with the shoulder that arises.
  • the outer ring of the deep groove ball bearing 26 is held in a correspondingly designed receptacle 26 'which is molded onto the transverse wall 10 (FIG. 3).
  • the outer ring of the deep groove ball bearing 26 is supported on the base of the receptacle 26 'in such a way that axial forces transmitted by the intermediate shaft 24 can be introduced into the transverse wall 10.
  • a bore 27 is coaxially made, in which a spring 28 is arranged.
  • a shaft part 29 extends from the free end of the bore 27 and can be inserted telescopically against the force of the spring 28 into the bore 28.
  • the free end of the shaft part 29 is in turn held in a needle bearing 30. With its end face, the shaft part 29 is held axially by the spring 28 against a plate 32 arranged in the base of a bearing seat 31 for the needle bearing 30.
  • the bearing receptacle 31 is integrally formed on the housing shell 2, which may consist of a glass fiber reinforced plastic.
  • a hub body 33 of a swash plate drive for the air cushion hammer mechanism 15 is rotatably arranged on the intermediate shaft 24.
  • the hub body 33 On its outside, the hub body 33 has a single groove 34 for balls 35, which is closed in itself in a ring shape and is inclined in one plane to the axis of the hub body 33.
  • the hub body 33 is connected to the intermediate shaft 24 by means of a positive coupling element.
  • the outer spline teeth 25 of the intermediate shaft 24 serve as coupling elements, in which an annular inner spline teeth 36 engages in the bore of the hub body 33.
  • an undercut 37 is located axially on the side facing the deep groove ball bearing 26 next to the internal spline toothing 36, the axial width of which is greater than the width of the annular internal spline toothing 36 of the hub body 33.
  • the drive gear 23 provided with a corresponding internal spline connection sits on the intermediate shaft 24 in a rotationally fixed but axially displaceable manner , in which the hub body 33 and the drive gear 23 are arranged on the intermediate shaft 24, a tooth height which is reduced in relation to the tooth height in the remaining partial region of the intermediate shaft 24.
  • the transition 38 from the reduced to the undiminished tooth height forms an axial stop for the hub body 33 on its end face facing away from the drive gear 23.
  • the bore in the hub body 33 is adapted at least in the area of the ring-shaped internal spline teeth 36 to the reduced tooth height of the external teeth 25 of the intermediate shaft 24.
  • the hub body 33 is supported on the one hand with the annular internal spline 36 on the intermediate shaft 24.
  • the hub body 33 is supported on an axially projecting collar 39 of the drive gear 23.
  • the spring 28 In the position shown in FIG. 3, in which the coupling elements 25 (external spline teeth) of the intermediate shaft 24 are engaged with the mating coupling elements 36 (internal spline teeth) of the hub body 33, the spring 28 ultimately braces the intermediate shaft with the axial stop (transition 38) against the Hub body 33.
  • This in turn is supported axially on the drive gear 23, which rests on the inner ring of the deep groove ball bearing 26.
  • the external spline toothing 25 of the intermediate shaft 24 has the form of a toothing suitable for the transmission of rotary movements, in this case, for example, an involute toothing. Therefore, the front part of the spline toothing facing away from the deep groove ball bearing 26 and having the undiminished tooth height can form the output pinion 40 of the intermediate shaft 24.
  • This output pinion 40 meshes with a gear 41, which ultimately sets the tool held in the tool holder 5 - the drill 6 - in rotation.
  • the hub body 33 In the position shown in FIG. 3, the hub body 33 is in the engaged position, in which it is set in rotation by the intermediate shaft 24.
  • the intermediate shaft In order to interrupt the rotary connection between the intermediate shaft 24 and the hub body 33, ie ultimately to put the air cushion hammer mechanism 15 out of operation, the intermediate shaft must be moved forward in the direction of the tool holder 5.
  • switching means that can be actuated from the outside have been arranged, which enable this disengagement of the striking mechanism.
  • These switching means are designed as eccentrics 42 on a switching shaft 43.
  • the selector shaft is guided in an associated bearing bore 44 which is formed in the transverse wall 10. In the operating position of the rotary hammer, the axis of the control shaft 43 and thus also the bearing bore 44 lie horizontally.
  • the selector shaft 43 carries an actuation button 45 (FIGS. 2 and 3).
  • the switching eccentric 42 is designed such that it touches the rear, from the deep groove ball bearing 26 outstanding, crowned end 46 of the intermediate shaft 24 in the position in which the striking mechanism is switched on. Only by turning the actuating button 45 from the position shown in FIG. 3 by 180 ° does the outer surface of the switching shaft 43 come into contact with the crowned end 46 of the two-shaft 24 so that it is finally moved forward against the force of the spring 28. The above-mentioned axial bracing of the hub body 33 is finally released via the gear 23 against the housing of the hammer drill.
  • the front end face of the hub body 33 comes into contact with a stop 47 formed by part of the machine housing, as a result of which it is limited in its axial movement.
  • the inner spline toothing 36 of the hub body 33 is disengaged from the outer spline toothing 25 of the intermediate shaft 24 and moved into the undercut 37:
  • the rotary connection between the intermediate shaft and the hub body 33 of the swash plate drive has thus been interrupted.
  • the further rotating intermediate shaft continues to set the gear 41 in rotation, so that pure drilling operation with the hammer drill is possible.
  • the switching eccentric 42 is thus loaded by the spring 28 in the axial direction only when the air cushion percussion mechanism is switched off, in which no stresses are placed on the machine.
  • the switching eccentric 42 When the striking mechanism is switched on, the switching eccentric 42 is completely relieved of the force of the spring 28.
  • the spring force is fully available to eliminate the axial play of the hub body 33. In this way, minimal noise is achieved on the one hand.
  • the elastic bracing of the hub body 33 against the housing of the hammer drill guarantees complete freedom from axial play - both due to manufacturing tolerances and the occurrence of wear.
  • the groove 34 on the hub body 33 is assigned an outer groove 49 cut into the inside of a ring 48, between which the balls 35 are guided. In order to keep the balls at a defined distance, they are guided in a cage 50 known from ball bearings.
  • a wobble finger 51 which drives the air cushion percussion mechanism 15 of the rotary hammer back and forth, is integrally formed on the ring 48.
  • the hammer mechanism of the rotary hammer is arranged in the interior of the fixed bushing 16 which is attached in the extension 14. It consists of a cup piston 52 which is tightly and slidably guided in the liner 16 and in the cylindrical bore 53 of which a club 54 designed as a free-flying piston is also arranged in a tight and sliding manner.
  • the rear end of the pot piston 52 facing away from the tool holder 5 is fork-shaped and carries a pivot pin 55.
  • a cross hole is arranged in the center of the pivot pin 55, in which the wobble finger 51 engages with little movement play. As a result, the wobble finger 51 can move slightly in the axial direction in the transverse bore.
  • an intermediate striker 56 extends into the front end region of the bore 53 which is modified from the wobble finger 51.
  • the intermediate striker is guided in an axially movable manner in a support sleeve 57.
  • the intermediate striker touches with its front end in a manner known per se and therefore not shown in the drawing, the inner end of the drill 6 axially displaceable but non-rotatably held in the tool holder 5.
  • the support sleeve 57 is in turn fastened inside a rotary sleeve 58 which is rotatably guided in the housing extension 3 in a manner not shown.
  • the rear end of the rotary sleeve 58 is supported by an axial needle bearing 59 on the flange 17 of the extension 14 of the transverse wall 10. In the radial direction, the rotary sleeve is guided in its rear region facing the needle bearing 59 on the end of the sleeve 16 protruding from the extension 15.
  • the gear 41 which meshes with the intermediate shaft 24, is rotatably guided on the cylindrical outer wall of the rotary sleeve 58.
  • the body of the gearwheel 41 which has clutch claws on its end face on the engine, is held in engagement with associated clutch claws on the rear flange 62 of the rotary sleeve 58 via a compression spring 61 which is supported on a snap ring 60 which is inserted into an associated groove of the rotary sleeve 58 .
  • the strength of the compression spring 61 is dimensioned such that the gear 41 is held in engagement with the rear flange of the rotary sleeve at normal drilling torques via the coupling claws.
  • the rotary connection between the gear 41 and the rotary sleeve 58 is only interrupted when a response torque is reached.
  • a rotary movement of the hub body 33 produces, as can be easily seen, a reciprocating movement of the pot piston 52.
  • the racket is also moved in an axial direction via the air cushion which forms between the piston 52 and the racket 54 and acts as an energy store. and moving around.
  • the striker 54 releases its energy, which finally acts as an axial stroke on the tool held in the tool holder 5.
  • the tool - the drill 6 - is set in rotation via the above-described safety coupling consisting of gear 41 and rear flange 62 of the rotating sleeve 58.
  • the striking mechanism By actuating the eccentric 42 arranged on the control shaft 43, the striking mechanism can be deactivated in the manner described above. Since the air cushion hammer mechanism is completely stationary in this case, an absolutely vibration-free run is achieved in impact stop operation, i.e. in drilling operation. It has shown that the swash plate drive can be switched in any operating state of the rotary hammer.
  • the second exemplary embodiment of an intermediate shaft 24 shown in FIG. 5 differs from the first exemplary embodiment in that the tooth height of the external spline toothing 25 is of the same height over the entire length of the intermediate shaft 24.
  • the axial stop required for the axial displacement of the hub body 33 or for the axial bracing of the hub body 33 in the engaged state, which in the first embodiment is formed by the transition 38 from the reduced to the undiminished tooth height of the external spline teeth 25, in this embodiment from one to at least one Recess of the intermediate shaft 24 inserted round ring 68 is formed.
  • the recess consists of parts of an annular groove cut into each tooth of the external spline toothing 24. Of course, if the annular groove were cut deeper, the recess could extend into the core of the intermediate shaft 24.

Claims (15)

1. Perforateur comportant un mécanisme de percussion à coussin d'air (15) qui comporte un percuteur (54), celui-ci étant entraîné par un organe d'entraînement (52) par l'intermédiaire du coussin d'air, et dont l'organe de fonctionnement est entraîné alternativement, axialement, par l'intermédiaire d'un entraînement à disque de nutation (51) susceptible d'être débrayé, et monté sur l'axe intermédiaire (24) entraîné par le pignon (22) d'un moteur électrique, caractérisé en ce que les éléments d'accouplement (25) ne faisant qu'une seule pièce avec l'axe intermédiaire (24) peuvent être mis hors de prise de forme par rapport aux éléments d'accouplement opposés (36) sur le corps de moyeu (33) à mouvement axial limité de l'entraînement à disque de nutation par un moyen de commutation (42) susceptible d'être actionné de l'extérieur, contre la force d'un ressort (28).
2. Perforateur selon la revendication 1, caractérisé en ce que le corps de moyeu (33) s'appuie en direction axiale sur des parties (27, 47) du carter (2, 10) du perforateur.
3. Perforateur selon la revendication 1, caractérisé en ce que l'axe intermédiaire (24) comporte une partie d'axe (29) susceptible d'être coulissée télescopiquement dans un perçage coaxial (27) contre la force d'un ressort (28) logé également dans le perçage (27).
4. Perforateur selon l'une des revendications précédentes caractérisé en ce que les moyens de commutation sont constitués par un excentrique (42) qui touche l'axe intermédiaire (24, 46) uniquement en position débrayée.
5. Perforateur selon la revendication 1, caractérisé en ce que les éléments d'accouplement opposés sur le corps de moyeu (33) sont constitués par une denture cannelée intérieure (36) et lés éléments d'accouplement de l'axe intermédiaire (24) sont constitués par une denture cannelée extérieure (25).
6. Perforateur selon la revendication 5, caractérisé en ce que la denture cannelée extérieure (25) s'étend sur toute la longueur de l'axe intermédiaire (24) et comporte un dégagement par raînure (37) dont la largeur axiale est adaptée à la largeur de la denture de cannelure intérieure annulaire (36) du corps de moyeu (33).
7. Perforateur selon l'une des revendications précédentes, caractérisé en ce qu'un pignon denté d'entraînement (23) est monté solidaire en rotation mais coulissant axialement sur l'axe intermédiaire (24) à l'aide d'une liaison à cannelure, pignon qui engrène avec le pignon (22) du moteur.
8. Perforateur selon l'une des revendications précédentes, caractérisé en ce que la denture cannelée extérieure (25) de l'axe intermédiaire (24) est une denture convenant pour la transmission de mouvement de rotation par exemple une denture en enveloppante qui forme le pignon de sortie (40) de l'axe intermédiaire (24) qui engrène en particulier avec le pignon (41) entraînant en rotation l'outil (6).
9. Perforateur selon les revendications 6 et 7, caractérisé en ce que le corps de moyeu (33) s'appuie d'une part en direction radiale par la denture cannelée intérieure annulaire (36) sur l'axe intermédiaire (24) et d'autre part sur un collet (39) du pignon d'entraînement (23), en salle axialement.
10. Perforateur selon l'une des revendications précédentes, caractérisé en ce qu'en position embrayée, le ressort (28) serre l'axe intermédiaire (24) avec une butée axiale (38, 68) contre le corps de moyeu (33) qui s'appuie à son tour, axialement contre le pignon denté d'entraînement (33) qui s'appuie sur la bague intérieure d'un palier (26) de préférence d'un palier à billes à raînure recevant l'axe intermédiaire (24).
11. Perforateur selon la revendication 10, caractérisé en ce que la butée axiale est formée par au moins un anneau torique (68) logé dans une cavité de l'axe intermédiaire (24).
12. Perforateur selon l'une des revendications 8 et 10, caractérisé en ce que les dents de la denture cannelée extérieure (25) présentent dans la zone dans laquelle se trouvent le corps de moyeu (33) et le pignon denté de sortie (23) sur l'axe intermédiaire (24), une hauteur de dents réduite par rapport à la hauteur de dents de la partie restante de l'axe intermédiaire (24) et la transition (38) de la hauteur de dents réduite à la hauteur de dents non réduite forme la butée axiale pour le corps de moyeu (33) qui présente un alésage de diamètre réduit de façon correspondante avec une denture cannelée intérieure (36).
13. Perforateur selon l'une des revendications précédentes, caractérisé en ce que le corps de moyeu (33) comporte sur son côté extérieur une seule raînure de roulement (34) annulaire, fermée, inclinée par rapport à l'axe du corps de moyeu (33), raînure à laquelle est associée une bague (48) avec une raînure de roulement extérieure (49) prévue sur sa face intérieure et en ce que des billes (35) sont guidées dans les deux raînures de roulement (4, 49) le cas échéant dans une cage (50).
14. Perforateur selon la revendication 13, caractérisé en ce qu'un doigt de nutation (51) est réalisé en une seule pièce sur la bague (48), ce doigt venant dans un perçage transversal d'un goujon de rotation (55) de l'organe d'entraînement (5) constitué par un piston (52) en forme de pot.
15. Perforateur selon l'une des revendications précédentes, caractérisé en ce que l'axe géométrique de l'axe intermédiaire (24) (dans la position d'utilisation normale du perforateur) se trouve en-dessous et décalé latéralement par rapport à l'axe du mécanisme de percussion (15) qui se trouve de préférence dans le plan médian longitudinal du perforateur.
EP81105591A 1980-10-21 1981-07-16 Perceuse à percussion Expired EP0050192B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803039669 DE3039669A1 (de) 1980-10-21 1980-10-21 Bohrhammer
DE3039669 1980-10-21

Publications (3)

Publication Number Publication Date
EP0050192A1 EP0050192A1 (fr) 1982-04-28
EP0050192B1 EP0050192B1 (fr) 1984-02-22
EP0050192B2 true EP0050192B2 (fr) 1989-10-04

Family

ID=6114858

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81105591A Expired EP0050192B2 (fr) 1980-10-21 1981-07-16 Perceuse à percussion

Country Status (4)

Country Link
US (1) US4446931A (fr)
EP (1) EP0050192B2 (fr)
JP (1) JPS57102779A (fr)
DE (2) DE3039669A1 (fr)

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US9630307B2 (en) 2012-08-22 2017-04-25 Milwaukee Electric Tool Corporation Rotary hammer
CN102975174B (zh) * 2012-12-11 2015-07-08 浙江奔宇工具有限公司 电锤的传动切换装置
JP6070826B2 (ja) * 2013-03-26 2017-02-01 日立工機株式会社 電動工具
JP6325360B2 (ja) * 2014-06-12 2018-05-16 株式会社マキタ 打撃工具
JP6479570B2 (ja) * 2015-05-19 2019-03-06 株式会社マキタ 作業工具

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Also Published As

Publication number Publication date
DE3039669A1 (de) 1982-05-27
JPS6351828B2 (fr) 1988-10-17
EP0050192A1 (fr) 1982-04-28
US4446931A (en) 1984-05-08
JPS57102779A (en) 1982-06-25
EP0050192B1 (fr) 1984-02-22
DE3162371D1 (en) 1984-03-29

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