EP0755756A2 - Perçeuse portative avec dispositif de commutation entre un mode de fonctionnement "forage" et un mode "forage à percussion" - Google Patents

Perçeuse portative avec dispositif de commutation entre un mode de fonctionnement "forage" et un mode "forage à percussion" Download PDF

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Publication number
EP0755756A2
EP0755756A2 EP96109456A EP96109456A EP0755756A2 EP 0755756 A2 EP0755756 A2 EP 0755756A2 EP 96109456 A EP96109456 A EP 96109456A EP 96109456 A EP96109456 A EP 96109456A EP 0755756 A2 EP0755756 A2 EP 0755756A2
Authority
EP
European Patent Office
Prior art keywords
drilling
intermediate wall
impact drill
axial
spindle
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
EP96109456A
Other languages
German (de)
English (en)
Other versions
EP0755756B1 (fr
EP0755756A3 (fr
Inventor
Günther Dipl.-Ing. Stark
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.)
Metabowerke GmbH and Co
Original Assignee
Metabowerke GmbH and Co
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 Metabowerke GmbH and Co filed Critical Metabowerke GmbH and Co
Publication of EP0755756A2 publication Critical patent/EP0755756A2/fr
Publication of EP0755756A3 publication Critical patent/EP0755756A3/fr
Application granted granted Critical
Publication of EP0755756B1 publication Critical patent/EP0755756B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/062—Cam-actuated impulse-driving mechanisms
    • B25D2211/064—Axial cams, e.g. two camming surfaces coaxial with drill spindle

Definitions

  • the invention relates to an impact drill with an intermediate wall on the motor side, in particular only radial mounting of a drilling spindle, and with an adjusting member for axially adjusting the drilling spindle between an impact drilling operating position and a rotary drilling operating position and with an axial bearing supporting the drilling spindle in the rotary drilling operating position.
  • the drilling spindle executes axial movements in the hammer drilling operating position, which are generated by a hammer mechanism which is generally formed by indexing disks.
  • the one acting on the drilling spindle Axial force is transferred to the machine housing via the striking mechanism.
  • the hammer mechanism is switched off in rotary drilling mode and the drilling spindle performs a pure rotary movement. If the striking mechanism is formed by indexing disks, the axial movement is prevented by disengaging the indexing disks and holding them in this position, which is achieved by an axial displacement of the drilling spindle.
  • the axial force in the drilling spindle caused by the pressing of the drilling machine against the workpiece in the rotary drilling mode is then absorbed by an axial bearing mentioned above.
  • this axial bearing is formed by the end face of the drilling spindle being supported on a housing section, an intermediate wall or a similar component of the machine.
  • Generic impact drills of this type are described, for example, in DE 27 15 682 C3 and in EP 0 399 714 A2. With such an axial bearing of the drilling spindle in rotary drilling operation, however, high surface pressures and thus high temperatures occur due to the small contact surface, and a correspondingly high level of wear occurs.
  • Impact drills have also become known in which roller bearings are used as axial bearings for the drilling spindle.
  • the DT 23 28 462 A1 shows an impact drill in which the drilling spindle is supported with one shoulder on an axial roller bearing in rotary drilling operation.
  • This Axial roller bearing is in turn supported on a longitudinally displaceable bearing bush which radially supports the drilling spindle on the motor side and is in turn guided in a housing section.
  • a bolt running perpendicular to the drilling spindle which has a manually operated rotary knob and an eccentric cam.
  • the eccentric cam presses on the longitudinally displaceable bearing bush and pushes the drilling spindle forward so that the hammer mechanism is switched off.
  • the axial force flow goes from the spindle via the axial bearing, the bearing bush, the eccentric cam to the bolt and from there to the machine housing.
  • the eccentric cam and the bolt must therefore be designed for these loads, which is problematic and expensive.
  • the known impact drill has the problem that the rear spindle bearing is imprecise due to the axial displaceability of the bearing bush.
  • the front spindle bearing is designed as a shoulder bearing, one shoulder of which can be axially displaced by means of a manually operated adjusting ring in the front area of the machine housing.
  • This version requires many individual parts and is therefore complex and expensive. Furthermore, the axial force flow over these many individual parts, which increases wear and susceptibility to failure.
  • a hammer drill of the type described in the introduction in that the axial bearing is a roller bearing and the adjusting element acts on the drill spindle via this roller bearing and is provided between the intermediate wall and a drive wheel arranged on the drill spindle.
  • the invention therefore proposes to arrange a lifting device formed by the adjusting member and the axial roller bearing cooperating therewith between the motor-side intermediate wall and the gear wheel driving the drilling spindle.
  • a hammer drill designed in this way is distinguished by the advantages of using an axial roller bearing and by a relatively short axial force flow from the drilling spindle via the axial roller bearing and the like Adjusting member on the partition without going over the rear radial bearing of the drilling spindle, as is the case with the impact drill known from DE 23 28 462 A1, in which no partition according to the application is provided for the storage of the drilling spindle.
  • the intermediate wall can also be produced inexpensively as a stamped part made of sheet metal or as a sintered part.
  • the adjusting member or the intermediate wall has one component that extends in the axial direction and the other component facing projection, which cooperates with a recess in the other component.
  • the adjusting member can be formed by an adjusting lever which can be pivoted transversely to the drilling spindle, so that the projection can be brought into engagement with the recess or out of engagement with the recess by pivoting the lever and thus an axial displacement of the adjusting lever which can be transferred to the drilling spindle can be achieved.
  • a fixed locking disk is provided between the intermediate wall and the drive wheel arranged on the drilling spindle and is held by the intermediate wall.
  • the force shocks acting in the axial direction can be absorbed by the stable intermediate wall, which is preferably supported over a large part of its circumference on the machine housing.
  • the operative connection between the adjusting member and the drilling spindle could be designed in such a way that the axial bearing is supported on a shoulder or a collar of the drilling spindle; however, the axial roller bearing is preferably supported against the drive wheel seated on the drilling spindle, so that the adjusting element acts on the drive wheel via the axial roller bearing.
  • the axial roller bearing can be formed by this drive wheel, by rolling elements and a bearing shell adjacent to the adjusting element. It can also prove to be advantageous if a thrust washer is provided between the drive wheel and the adjusting element. In an advantageous embodiment of the invention, it is further provided that the adjusting member lies flat against the intermediate wall, so that no high surface pressure and thus no wear occurs when the force acting in the axial direction is transmitted.
  • FIG. 1 shows an impact drill marked overall with reference number 2, the part of the impact drill not affected by the invention being omitted.
  • the hammer drill 2 comprises a drill spindle 4, the is supported radially at its rear end by an intermediate wall 6 inserted in two housing shells by a needle bearing 8. In the front area of the drilling machine, the spindle 4 is additionally supported radially by a deep groove ball bearing 10.
  • a radial ball bearing 12 is also held in the intermediate wall 6, through which an armature shaft 14 is guided and supported.
  • the armature shaft 14 extends through the intermediate wall 6 and has at its front end a pinion 16 which meshes with a drive wheel 18 which is seated on the drilling spindle 4 and is fixed in terms of rotation.
  • An impact mechanism 20 of the impact drill 2 is accommodated between the intermediate wall 6 and the drive wheel 18.
  • the striking mechanism 20 comprises a fixed locking disk 22 which is supported against the intermediate wall 6 and is held thereon.
  • the detent disk 22 has on its end face facing the drive wheel 18 detent teeth 24 which, in percussion drilling operation of the machine, cooperate with detent teeth 26 on the end face of the drive wheel 18 in a manner known per se.
  • adjusting member 30 in the Form of a pivotable in a plane perpendicular to the drilling spindle 4 adjusting lever 32 housed.
  • the adjusting lever 32 has a projection 34 which faces the intermediate wall 6 and which can be latched into a recess 36 formed in the intermediate wall 6.
  • the impact drill 2 is in the impact drilling operating position, in which the ratchet teeth 24 and 26 are engaged. If the adjusting lever 32 is pivoted into a second position perpendicular to the plane of the drawing in FIGS. 1 and 2, the projection 34 slides out of the recess 36 and thereby displaces the adjusting lever 32 to the front.
  • the adjusting lever 32 presses on a thrust washer 38.
  • the thrust washer 38 forms the rear bearing shell 40 of an axial roller bearing 42.
  • the axial roller bearing 42 is formed in the illustrated case by the thrust washer 38, by spherical rolling elements 44 and by the drive wheel 18 forming a front bearing shell.
  • the axial offset of the adjusting lever 32 when pivoting from the percussion drilling operating position into the rotary drilling operating position is thus transmitted directly via the axial roller bearing 42 to the drive wheel 18 and thus to the drilling spindle 4, whereby this is also shifted forward and the locking teeth 24 of the locking disk 22 and the locking teeth 26 of the drive wheel 18 are disengaged.
  • the axial load occurring during drilling operation from the drilling spindle 4 or the drive wheel 18 is via the Axial roller bearing 42, transmitted to the intermediate wall 6 via the adjusting lever 32.
  • a spring 46 is arranged between the adjusting lever 32 and the thrust roller bearing 42, which presses the adjusting lever 32 into the recess 36 in the intermediate wall 6, but also presses the drive wheel 18 and thus the drilling spindle 4 forward in the percussion drilling operating position in such a way that the ratchet teeth 24 and 26 remain out of engagement until the drill spindle is pressed against a workpiece.
  • FIGS. 3 and 5 show a section running perpendicular to the longitudinal axis of the drilling spindle 4 and through the axial roller bearing 42.
  • the impact drill is in the impact drilling operating position; the projections 34 of the adjusting lever 32 are snapped into the recesses 34 in the intermediate wall 6, and the arrangement of adjusting lever 32, axial roller bearing 42 and drive wheel 18 or drilling spindle 4 is in the lower position shown in FIG. 1.
  • the locking disk 22 which can be seen in FIGS. 3 and 5 is shown as an individual part in FIG. It has two feet 48 with which it is centered and held in recesses in the intermediate wall 6. In this case, the catch disk 22 is supported with its surface 50 on the intermediate wall 6 from.
  • the ratchet teeth 24 are located on the opposite side.
  • FIG. 5 shows the adjusting lever 32 in its other swivel position, in which the drilling machine is in the rotary drilling operating position.
  • the projections 34 of the adjusting lever 32 facing the intermediate wall 6 are out of engagement with the recesses 36 of the intermediate wall 6, and the adjusting lever 32 is in the upper position in FIG. 1 and presses the drive wheel 18 and thus the drilling spindle via the axial roller bearing 42 4 forward.
  • the axial load occurring is transmitted via the axial roller bearing 42 to the adjusting lever 32 and from there via the three projections 34 to the intermediate wall 6.
  • FIG. 6 shows a further embodiment of the impact drill according to the invention, which differs from the previously described embodiment in that an intermediate wall 6 'and a detent disk 22' are designed as a one-piece component.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Drilling And Boring (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP96109456A 1995-07-25 1996-06-13 Perçeuse portative avec dispositif de commutation entre un mode de fonctionnement "forage" et un mode "forage à percussion" Expired - Lifetime EP0755756B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19527117A DE19527117C2 (de) 1995-07-25 1995-07-25 Handbohrmaschine mit Einrichtung zum Umschalten der Betriebsarten "Bohren" und "Schlagbohren"
DE19527117 1995-07-25

Publications (3)

Publication Number Publication Date
EP0755756A2 true EP0755756A2 (fr) 1997-01-29
EP0755756A3 EP0755756A3 (fr) 1998-01-28
EP0755756B1 EP0755756B1 (fr) 2000-01-05

Family

ID=7767719

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96109456A Expired - Lifetime EP0755756B1 (fr) 1995-07-25 1996-06-13 Perçeuse portative avec dispositif de commutation entre un mode de fonctionnement "forage" et un mode "forage à percussion"

Country Status (2)

Country Link
EP (1) EP0755756B1 (fr)
DE (2) DE19527117C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1834736A1 (fr) * 2006-03-18 2007-09-19 Metabowerke GmbH Outil à main électrique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2555533A1 (fr) * 2006-08-08 2008-02-08 Fern Beauchamp Accessoire de mandrin de trepan de marteau perforateur

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1346537A (en) * 1971-08-09 1974-02-13 Metabowerke Kg Electrically-powered multi-purpose tools usable as rotary-percussive drills
FR2192894A1 (fr) * 1972-07-13 1974-02-15 Black & Decker Mfg Co
DE2715682A1 (de) * 1977-04-07 1978-10-19 Metabowerke Kg Schlagbohrmaschine mit gehaeusefest angeordneten rasten
EP0399714A2 (fr) * 1989-05-25 1990-11-28 Black & Decker Inc. Machines à forer

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2328462C2 (de) * 1973-06-05 1985-08-29 Robert Bosch Gmbh, 7000 Stuttgart Schlagbohrmaschine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1346537A (en) * 1971-08-09 1974-02-13 Metabowerke Kg Electrically-powered multi-purpose tools usable as rotary-percussive drills
FR2192894A1 (fr) * 1972-07-13 1974-02-15 Black & Decker Mfg Co
DE2715682A1 (de) * 1977-04-07 1978-10-19 Metabowerke Kg Schlagbohrmaschine mit gehaeusefest angeordneten rasten
EP0399714A2 (fr) * 1989-05-25 1990-11-28 Black & Decker Inc. Machines à forer

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1834736A1 (fr) * 2006-03-18 2007-09-19 Metabowerke GmbH Outil à main électrique

Also Published As

Publication number Publication date
DE19527117C2 (de) 2000-05-31
DE59604090D1 (de) 2000-02-10
EP0755756B1 (fr) 2000-01-05
EP0755756A3 (fr) 1998-01-28
DE19527117A1 (de) 1997-01-30

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