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EP2873488A1 - Manual tool machine - Google Patents

Manual tool machine Download PDF

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Publication number
EP2873488A1
EP2873488A1 EP20130192765 EP13192765A EP2873488A1 EP 2873488 A1 EP2873488 A1 EP 2873488A1 EP 20130192765 EP20130192765 EP 20130192765 EP 13192765 A EP13192765 A EP 13192765A EP 2873488 A1 EP2873488 A1 EP 2873488A1
Authority
EP
European Patent Office
Prior art keywords
shell
housing
bearing
axial distance
shaft
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
EP20130192765
Other languages
German (de)
French (fr)
Other versions
EP2873488B1 (en
Inventor
Bernhard Liebert
Stefan Schmid
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.)
Hilti AG
Original Assignee
Hilti 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 Hilti AG filed Critical Hilti AG
Priority to EP13192765.9A priority Critical patent/EP2873488B1/en
Publication of EP2873488A1 publication Critical patent/EP2873488A1/en
Application granted granted Critical
Publication of EP2873488B1 publication Critical patent/EP2873488B1/en
Active 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
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/02—Construction of casings, bodies or handles
    • 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
    • B25D2250/065—Details regarding assembling of the tool
    • 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
    • B25D2250/121—Housing details
    • 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
    • B25D2250/331—Use of bearings
    • 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
    • B25D2250/331—Use of bearings
    • B25D2250/335—Supports therefor

Definitions

  • the present invention relates to a hand tool, in particular a hammer drill or a chisel hammer with a motor-driven pneumatic hammer mechanism.
  • the hand tool of the invention has a tool holder for receiving a tool.
  • a shaft couples a motor to a unit driving the tool.
  • the driving unit is an example of a pneumatic striking mechanism.
  • the shaft is stored in two rolling bearings.
  • the first rolling bearing has an outer bearing shell, an inner bearing shell and arranged between the outer bearing shell and the inner bearing shell rolling elements.
  • the second rolling bearing has an outer bearing shell, an inner bearing shell and between the outer bearing shell and the inner bearing shell arranged rolling elements.
  • the inner bearing shells of the rolling bearings are offset from one another in a first axial distance placed on the shaft.
  • a housing has a second housing shell connected to a first housing shell by a non-positive connection.
  • the outer bearing shell of the first rolling bearing is in the first housing shell and the outer bearing shell of the second rolling bearing is inserted into the second housing shell.
  • the outer bearing shells are at a second axial distance.
  • the first axial distance is compared to the second axial distance, is selected such that the first housing shell and the second housing shell are braced by the frictional connection parallel to the shaft.
  • the tension is partially transferred to the rolling bearings, preferably ball bearings.
  • the shaft in particular for an eccentric, can be exposed to high radial forces. It proves advantageous to preload the ball bearings axially in order to increase the service life.
  • the structure of the invention achieves the bias in a compact and reliable manner.
  • One embodiment provides that the outer bearing shells, along the axis immovably in the housing shells used, and the inner bearing shells, immovably mounted on the shaft along the axis.
  • the outer and inner bearing shells each have a tight fit.
  • the smaller axial distance between the outer bearing shells compensate the housing shells by deforming.
  • the outer bearing shells can move slightly relative to the inner bearing shells, compared to the rolling bearings without axial load.
  • An embodiment provides that the first housing shell a contact surface and the second housing shell have a contact surface, which touch each other by the non-positive connection, and dissolved in non-positive connection, the outer bearing shell a third axial distance to the contact surface of the first housing shell and the outer bearing shell a fourth axial distance to the contact surface of the second housing shell, and the first axial distance is greater than the sum of the third and fourth axial distance is.
  • One embodiment provides that the shaft is part of an eccentric is coupled with a pneumatic percussion.
  • An embodiment provides that a transmission is arranged in the housing oil-tight.
  • Fig. 1 shows as an example of a chiseling hand tool machine schematically a hammer drill 1.
  • the hammer drill 1 has a tool holder 2, in which a shank end 3 of a tool, for example one of the drill 4, can be used.
  • a primary drive of the hammer drill 1 is a motor 5, which drives a striking mechanism 6 and an output shaft 7 .
  • a battery pack 8 or a power line supplies the motor 5 with power.
  • a user can guide the hammer drill 1 by means of a handle 9 and be by means of a system switch 10 to the hammer drill 1 is in operation.
  • the hammer drill 1 rotates the drill 4 continuously about a working axis 11 and can beat the drill 4 in the direction of impact 12 along the working axis 11 in a substrate.
  • the percussion 6 is a pneumatic percussion 6.
  • An exciter piston 13 and a racket 14 are movably guided in a guide tube 15 in the striking mechanism 6 along the working axis 11 .
  • the excitation piston 13 is coupled via an eccentric 16 to the motor 5 and forced to a periodic, linear movement.
  • a connecting rod 17 connects the eccentric 16 with the excitation piston 13.
  • An air spring formed by a pneumatic chamber 18 between the excitation piston 13 and the racket 14 couples a movement of the racket 14 to the movement of the exciter piston 13 .
  • the racket 14 can strike directly on a rear end of the drill 4 or indirectly transmit a portion of its pulse to the drill 4 via a substantially resting intermediate racket 19 .
  • the striking mechanism 6 and preferably the further drive components are arranged within a machine housing 20 .
  • Fig. 2 and Fig. 3 show a gear assembly 21 and the eccentric 16.
  • the eccentric 16 has a shaft 22 which is rotatably mounted about an axis 23 .
  • a finger 24 is arranged eccentrically to the axis 23 on the shaft 22 .
  • the connecting rod 17 connects the finger 24 with the exciter piston 13.
  • a gear 25 of the gear 21 is rotatably, for example, with a press fit, placed on the shaft 22 .
  • a gear 25 meshing gear 26 of the transmission 21 may be arranged for example on the motor shaft 27 of the motor 5 .
  • the single-stage gear 21 and multi-stage transmission can be provided.
  • the eccentric 16 is mounted in a two-part housing 28 .
  • Fig. 3 illustrates the two-part housing before its two housing shells 29, 30 are connected together.
  • the housing 28 is preferably an encapsulating transmission housing 28 which encloses the gear assembly 21 oil-tightly.
  • the upper housing shell 29 has a contact surface 31 which comes mounted on a contact surface 32 of the lower housing shell 30 to rest.
  • the exemplary contact surfaces 31, 32 are closed in an annular manner, preferably provided with an additional sealing ring, in order to provide an oil-tight encapsulation to reach.
  • the contact surfaces 31, 32 are complementary to each other, therefore expediently flat and perpendicular to the axis 23 of the eccentric 16, but may also be stepped or inclined to the axis 23 .
  • the two housing shells 29, 30 are connected to each other by screws 33 .
  • the screws 33 are preferably oriented parallel to the axis 23 and arranged radially offset from the shaft 22 through the contact surfaces 31, 32 extending.
  • the shaft 22 of the eccentric 16 is mounted in two rolling bearings 34, 35 , which are arranged offset from one another along the axis 23 .
  • the bearings 34 may be a deep groove ball bearing, or an angular contact ball bearing, as shown.
  • the gear 25 is preferably disposed between the rolling bearings 34, 35 .
  • the upper rolling bearing 34 closer to the finger 24 is preferably larger than the lower rolling bearing 35.
  • the upper rolling bearing 34 intercepts the radial transverse forces introduced via the finger 24 onto the eccentric 16 .
  • the upper roller bearing 34 has a radially outer bearing shell 36 and a radially inner bearing shell 37.
  • the outer bearing shell 36 encloses annularly the inner bearing shell 37.
  • the axial dimensions of the outer bearing shell 36 and the inner bearing shell 37 are the same, for example.
  • the two bearing shells 36, 37 have facing radially oriented running surfaces 38, 39, in which rolling elements 40, preferably balls, are guided. Both treads 38 are concavely curved.
  • the rolling elements 40 are parallel to the axis 23 and in the radial direction, ie perpendicular to the axis 23, forcibly guided.
  • the rolling elements 41 ie their centers of gravity, lie in a direction perpendicular to the axis 23 guide plane 42.
  • the lower roller bearing 35 has substantially the same structure as the upper roller bearing 34.
  • Wälz Archives 41 preferably balls, are by radially aligned, concave treads 43, 44 of an outer bearing shell 45 and an inner bearing shell 46 forcibly guided in a guide plane 47 .
  • the shaft 22 is inserted into the two inner bearing shells 37, 46 .
  • the inner bearing shells 37, 46 are immovable along the axis 23 to the shaft 22 and thus immovable to one another.
  • An axial distance 48 between the two inner bearing shells 37, 46 is fixed.
  • the axial distance 48 is related, for example, to the guide planes 42, 47 of the roller bearings 34, 35 , which have the roller bearings 34, 35 axially unloaded in the arrangement of the inner bearing shells 37, 46 .
  • the inner bearing shells 37, 46 are fastened to the shaft 22 , for example by means of an interference fit.
  • the exemplary shaft 22 has a smaller diameter at the lower roller bearing 35 . Adjacent to the lower roller bearing 35 , the diameter of the shaft 22 is larger.
  • the lower roller bearing 35 may be positively supported on the diameter jump, to prevent displacement of the lower roller bearing 35 in the direction of the upper roller bearing 34 .
  • the outer bearing shell 36 of the upper roller bearing 34 is seated in a seat 49 in the upper housing shell 29, and the outer bearing shell 45 of the lower roller bearing 35 is seated in a seat 50 in the lower housing shell 30 .
  • the two outer bearing shells 36, 45 are immovable in the respective housing shells 29, 30 , in particular immovably fixed along the axis 23 .
  • the upper, outer bearing shell 36 has to the contact surface 31 of the upper housing shell 29 at an axial distance 51 (upper distance 51) .
  • the lower, outer bearing shell 45 has an axial distance 52 (lower distance 52) to the contact surface 32 of the lower housing shell 30 . If the contact surfaces 31, 32 are inclined or stepped, the axial distances 51, 52 are determined at touching portions, eg at the same screw in each case.
  • the axial distances 51, 52 are determined analogously to the inner bearing shells, for example on the basis of the guide planes 42, 47 , which results for axially unloaded roller bearings 34, 35 in the arrangement of the outer bearing shells 36 .
  • the sum of the upper distance 51 and the lower distance 52 for the outer bearing shells 36, 45 is less than the axial distance 48 of the inner bearing shells 37, 46.
  • the difference is preferably in the range of 0.2 mm to 3 mm.
  • the outer bearing shells 36, 45 are slightly offset from the inner bearing shells 37, 46 , compared to axially unloaded bearings.
  • Fig. 2 is the relative offset of the inner bearing shells 37, 46 with respect to the outer bearing shells 36, 46 shown oversubscribed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Drilling And Boring (AREA)

Abstract

Eine Handwerkzeugmaschine hat eine Welle (22), die einen Motor (5) mit einer das Werkzeug antreibenden Einheit (6) koppelt. Die Welle (22) ist in zwei Wälzlagern (34, 35) gelagert. Die inneren Lagerschalen (37, 46) der Wälzlager sind in einem ersten axialen Abstand (48) zueinander versetzt auf die Welle (22) aufgesetzt. Ein Gehäuse (28) hat eine mit einer ersten Gehäuseschale (29) durch eine kraftschlüssige Verbindung verbundene zweite Gehäuseschale (30). Die äußere Lagerschale (36) des ersten Wälzlagers ist in die erste Gehäuseschale und die äußere Lagerschale (45) des zweiten Wälzlagers ist in die zweite Gehäuseschale eingesetzt. Die äußeren Lagerschalen sind in einem zweiten axialen Abstand (51, 52). Der erste axiale Abstand ist gegenüber dem zweiten axialen Abstand, derart gewählt ist, dass die erste Gehäuseschale und die zweite Gehäuseschale durch die die kraftschlüssige Verbindung parallel zu der Welle verspannt sind.A handheld power tool has a shaft (22) coupling a motor (5) to a tool driving unit (6). The shaft (22) is mounted in two rolling bearings (34, 35). The inner bearing shells (37, 46) of the roller bearings are offset relative to one another on the shaft (22) at a first axial distance (48). A housing (28) has a second housing shell (30) connected to a first housing shell (29) by a non-positive connection. The outer bearing shell (36) of the first rolling bearing is in the first housing shell and the outer bearing shell (45) of the second rolling bearing is inserted into the second housing shell. The outer bearing shells are at a second axial distance (51, 52). The first axial distance is compared to the second axial distance, is selected such that the first housing shell and the second housing shell are braced by the frictional connection parallel to the shaft.

Description

GEBIET DER ERFINDUNGFIELD OF THE INVENTION

Die vorliegende Erfindung betrifft eine Handwerkzeugmaschine, insbesondere eine Bohrhammer oder einen Meißelhammer mit einem motorgetriebenen pneumatischen Schlagwerk.The present invention relates to a hand tool, in particular a hammer drill or a chisel hammer with a motor-driven pneumatic hammer mechanism.

OFFENBARUNG DER ERFINDUNGDISCLOSURE OF THE INVENTION

Die erfindungsgemäße Handwerkzeugmaschine hat einen Werkzeughalter zum Aufnehmen eines Werkzeugs. Eine Welle koppelt einen Motor mit einer das Werkzeug antreibenden Einheit. Die antreibende Einheit ist beispielhaft ein pneumatisches Schlagwerk. Die Welle ist in zwei Wälzlagern gelagert. Das erste Wälzlager hat eine äußere Lagerschale, eine innere Lagerschale und zwischen der äußeren Lagerschale und der inneren Lagerschale angeordnete Wälzkörper. Das zweite Wälzlager hat eine äußere Lagerschale, eine innere Lagerschale und zwischen der äußeren Lagerschale und der inneren Lagerschale angeordnete Wälzkörper. Die inneren Lagerschalen der Wälzlager sind in einem ersten axialen Abstand zueinander versetzt auf die Welle aufgesetzt. Ein Gehäuse hat eine mit einer ersten Gehäuseschale durch eine kraftschlüssige Verbindung verbundene zweite Gehäuseschale. Die äußere Lagerschale des ersten Wälzlagers ist in die erste Gehäuseschale und die äußere Lagerschale des zweiten Wälzlagers ist in die zweite Gehäuseschale eingesetzt. Die äußeren Lagerschalen sind in einem zweiten axialen Abstand,. Der erste axiale Abstand ist gegenüber dem zweiten axialen Abstand, derart gewählt ist, dass die erste Gehäuseschale und die zweite Gehäuseschale durch die die kraftschlüssige Verbindung parallel zu der Welle verspannt sind. Die Verspannung überträgt sich teilweise in die Wälzlager, vorzugsweise Kugellager. Die Welle, insbesondere für einen Exzenter, kann hohen radialen Kräften ausgesetzt sein. Hierbei erweist es sich vorteilhaft, die Kugellager axial vorzubelasten, um die Lebensdauer zu erhöhen. Der erfindungsgemäße Aufbau erreicht die Vorspannung in kompakter und zuverlässiger Weise.The hand tool of the invention has a tool holder for receiving a tool. A shaft couples a motor to a unit driving the tool. The driving unit is an example of a pneumatic striking mechanism. The shaft is stored in two rolling bearings. The first rolling bearing has an outer bearing shell, an inner bearing shell and arranged between the outer bearing shell and the inner bearing shell rolling elements. The second rolling bearing has an outer bearing shell, an inner bearing shell and between the outer bearing shell and the inner bearing shell arranged rolling elements. The inner bearing shells of the rolling bearings are offset from one another in a first axial distance placed on the shaft. A housing has a second housing shell connected to a first housing shell by a non-positive connection. The outer bearing shell of the first rolling bearing is in the first housing shell and the outer bearing shell of the second rolling bearing is inserted into the second housing shell. The outer bearing shells are at a second axial distance. The first axial distance is compared to the second axial distance, is selected such that the first housing shell and the second housing shell are braced by the frictional connection parallel to the shaft. The tension is partially transferred to the rolling bearings, preferably ball bearings. The shaft, in particular for an eccentric, can be exposed to high radial forces. It proves advantageous to preload the ball bearings axially in order to increase the service life. The structure of the invention achieves the bias in a compact and reliable manner.

Eine Ausgestaltung sieht vor, dass die äußeren Lagerschalen, längs der Achse jeweils unbeweglich in den Gehäuseschalen, eingesetzt und die inneren Lagerschalen, längs der Achse unbeweglich auf der Welle aufgesetzt sind. Die äußeren und inneren Lagerschalen haben jeweils einen festen Sitz. Den beispielsweise geringeren axialen Abstand zwischen den äußeren Lagerschalen kompensieren die Gehäuseschalen, indem sie sich verformen. Die äußeren Lagerschalen können sich gegenüber den inneren Lagerschalen etwas verschieben, verglichen zu den Wälzlagern ohne axiale Belastung.One embodiment provides that the outer bearing shells, along the axis immovably in the housing shells used, and the inner bearing shells, immovably mounted on the shaft along the axis. The outer and inner bearing shells each have a tight fit. For example, the smaller axial distance between the outer bearing shells compensate the housing shells by deforming. The outer bearing shells can move slightly relative to the inner bearing shells, compared to the rolling bearings without axial load.

Eine Ausgestaltung sieht vor, dass die erste Gehäuseschale eine Kontaktfläche und die zweite Gehäuseschale eine Kontaktfläche aufweisen, die durch die kraftschlüssige Verbindung einander berühren, und bei gelöster kraftschlüssiger Verbindung die äußere Lagerschale einen dritten axialen Abstand zu der Kontaktfläche der ersten Gehäuseschale und die äußere Lagerschale einen vierten axialen Abstand zu der Kontaktfläche der zweiten Gehäuseschale aufweisen, und der erste axiale Abstand größer als die Summe des dritten und vierten axialen Abstands, ist.An embodiment provides that the first housing shell a contact surface and the second housing shell have a contact surface, which touch each other by the non-positive connection, and dissolved in non-positive connection, the outer bearing shell a third axial distance to the contact surface of the first housing shell and the outer bearing shell a fourth axial distance to the contact surface of the second housing shell, and the first axial distance is greater than the sum of the third and fourth axial distance is.

Eine Ausgestaltung sieht vor, dass die Welle Teil eines Exzenters ist, mit einem pneumatischen Schlagwerk gekoppelt ist.One embodiment provides that the shaft is part of an eccentric is coupled with a pneumatic percussion.

Eine Ausgestaltung sieht vor, dass ein Getriebe in dem Gehäuse öldicht angeordnet ist.An embodiment provides that a transmission is arranged in the housing oil-tight.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Die nachfolgende Beschreibung erläutert die Erfindung anhand von exemplarischen Ausführungsformen und Figuren. In den Figuren zeigen:

  • Fig. 1 einen Bohrhammer
  • Fig. 2 eine Getriebeeinheit in einem Gehäuse
  • Fig. 3 die Getriebeinheit, bevor das Gehäuse verschraubt ist
The following description explains the invention with reference to exemplary embodiments and figures. In the figures show:
  • Fig. 1 a hammer drill
  • Fig. 2 a gear unit in a housing
  • Fig. 3 the gear unit before the housing is bolted

Gleiche oder funktionsgleiche Elemente werden durch gleiche Bezugszeichen in den Figuren indiziert, soweit nicht anders angegeben.Identical or functionally identical elements are indicated by the same reference numerals in the figures, unless stated otherwise.

AUSFÜHRUNGSFORMEN DER ERFINDUNGEMBODIMENTS OF THE INVENTION

Fig. 1 zeigt als Beispiel einer meißelnden Handwerkzeugmaschine schematisch einen Bohrhammer 1. Der Bohrhammer 1 hat eine Werkzeughalter 2, in welche ein Schaftende 3 eines Werkzeug, z.B. eines des Bohrers 4, eingesetzt werden kann. Einen primären Antrieb des Bohrhammers 1 bildet ein Motor 5, welcher ein Schlagwerk 6 und eine Abtriebswelle 7 antreibt. Ein Batteriepaket 8 oder eine Netzleitung versorgt den Motor 5 mit Strom. Ein Anwender kann den Bohrhammer 1 mittels eines Handgriffs 9 führen und mittels eines Systemschalters 10 den Bohrhammer 1 in Betrieb nehmen. Im Betrieb dreht der Bohrhammer 1 den Bohrer 4 kontinuierlich um eine Arbeitsachse 11 und kann dabei den Bohrer 4 in Schlagrichtung 12 längs der Arbeitsachse 11 in einen Untergrund schlagen. Fig. 1 shows as an example of a chiseling hand tool machine schematically a hammer drill 1. The hammer drill 1 has a tool holder 2, in which a shank end 3 of a tool, for example one of the drill 4, can be used. A primary drive of the hammer drill 1 is a motor 5, which drives a striking mechanism 6 and an output shaft 7 . A battery pack 8 or a power line supplies the motor 5 with power. A user can guide the hammer drill 1 by means of a handle 9 and be by means of a system switch 10 to the hammer drill 1 is in operation. In operation, the hammer drill 1 rotates the drill 4 continuously about a working axis 11 and can beat the drill 4 in the direction of impact 12 along the working axis 11 in a substrate.

Das Schlagwerk 6 ist ein pneumatisches Schlagwerk 6. Ein Erregerkolben 13 und ein Schläger 14 sind in einem Führungsrohr 15 in dem Schlagwerk 6 längs der Arbeitsachse 11 beweglich geführt. Der Erregerkolben 13 ist über einen Exzenter 16 an den Motor 5 angekoppelt und zu einer periodischen, linearen Bewegung gezwungen. Ein Pleuel 17 verbindet den Exzenter 16 mit dem Erregerkolben 13. Eine Luftfeder gebildet durch eine pneumatische Kammer 18 zwischen dem Erregerkolben 13 und dem Schläger 14 koppelt eine Bewegung des Schlägers 14 an die Bewegung des Erregerkolbens 13 an. Der Schläger 14 kann direkt auf ein hinteres Ende des Bohrers 4 aufschlagen oder mittelbar über einen im Wesentlichen ruhenden Zwischenschläger 19 einen Teil seines Impuls auf den Bohrer 4 übertragen. Das Schlagwerk 6 und vorzugsweise die weiteren Antriebskomponenten sind innerhalb eines Maschinengehäuses 20 angeordnet.The percussion 6 is a pneumatic percussion 6. An exciter piston 13 and a racket 14 are movably guided in a guide tube 15 in the striking mechanism 6 along the working axis 11 . The excitation piston 13 is coupled via an eccentric 16 to the motor 5 and forced to a periodic, linear movement. A connecting rod 17 connects the eccentric 16 with the excitation piston 13. An air spring formed by a pneumatic chamber 18 between the excitation piston 13 and the racket 14 couples a movement of the racket 14 to the movement of the exciter piston 13 . The racket 14 can strike directly on a rear end of the drill 4 or indirectly transmit a portion of its pulse to the drill 4 via a substantially resting intermediate racket 19 . The striking mechanism 6 and preferably the further drive components are arranged within a machine housing 20 .

Fig. 2 und Fig. 3 zeigen eine Getriebeanordnung 21 und den Exzenter 16. Der Exzenter 16 hat eine Welle 22, die um eine Achse 23 drehbar gelagert ist. Ein Finger 24 ist zu der Achse 23 exzentrisch auf der Welle 22 angeordnet. Das Pleuel 17 verbindet den Finger 24 mit dem Erregerkolben 13. Ein Zahnrad 25 des Getriebes 21 ist drehfest, z.B. mit einem Presssitz, auf die Welle 22 aufgesetzt. Ein das Zahnrad 25 kämmendes Zahnrad 26 des Getriebes 21 kann beispielsweise auf der Motorwelle 27 des Motors 5 angeordnet sein. Anstelle des einstufigen Getriebes 21 können auch mehrstufige Getriebe vorgesehen sein. Fig. 2 and Fig. 3 show a gear assembly 21 and the eccentric 16. The eccentric 16 has a shaft 22 which is rotatably mounted about an axis 23 . A finger 24 is arranged eccentrically to the axis 23 on the shaft 22 . The connecting rod 17 connects the finger 24 with the exciter piston 13. A gear 25 of the gear 21 is rotatably, for example, with a press fit, placed on the shaft 22 . A gear 25 meshing gear 26 of the transmission 21 may be arranged for example on the motor shaft 27 of the motor 5 . Instead of the single-stage gear 21 and multi-stage transmission can be provided.

Der Exzenter 16 ist in einem zweiteiligen Gehäuse 28 gelagert. Fig. 3 illustriert das zweitteilige Gehäuse, bevor dessen zwei Gehäuseschalen 29, 30 miteinander verbunden sind. Das Gehäuse 28 ist vorzugsweise ein kapselndes Getriebegehäuse 28, das die Getriebeanordnung 21 öldicht umschließt. Die obere Gehäuseschale 29 hat eine Kontaktfläche 31, die montiert auf einer Kontaktfläche 32 der unteren Gehäuseschale 30 zum Aufliegen kommt. Die beispielhaften Kontaktflächen 31, 32 sind ringförmig geschlossen, vorzugsweise mit einem zusätzlichen Dichtring versehen, um eine öldichte Kapselung zu erreichen. Die Kontaktflächen 31, 32 sind zueinander komplementär, daher zweckmäßiger Weise eben und senkrecht zu der Achse 23 des Exzenters 16, können aber auch gestuft oder geneigt zu der Achse 23 sein. Die beiden Gehäuseschalen 29, 30 sind miteinander durch Schrauben 33 verbunden. Die Schrauben 33 sind vorzugsweise parallel zu der Achse 23 orientiert und radial versetzt zu der Welle 22 durch die Kontaktflächen 31, 32 verlaufend angeordnet.The eccentric 16 is mounted in a two-part housing 28 . Fig. 3 illustrates the two-part housing before its two housing shells 29, 30 are connected together. The housing 28 is preferably an encapsulating transmission housing 28 which encloses the gear assembly 21 oil-tightly. The upper housing shell 29 has a contact surface 31 which comes mounted on a contact surface 32 of the lower housing shell 30 to rest. The exemplary contact surfaces 31, 32 are closed in an annular manner, preferably provided with an additional sealing ring, in order to provide an oil-tight encapsulation to reach. The contact surfaces 31, 32 are complementary to each other, therefore expediently flat and perpendicular to the axis 23 of the eccentric 16, but may also be stepped or inclined to the axis 23 . The two housing shells 29, 30 are connected to each other by screws 33 . The screws 33 are preferably oriented parallel to the axis 23 and arranged radially offset from the shaft 22 through the contact surfaces 31, 32 extending.

Die Welle 22 des Exzenters 16 ist in zwei Wälzlagern 34, 35 gelagert, die längs der Achse 23 versetzt zueinander angeordnet sind. Die Wälzlager 34 können wie dargestellt ein Rillenkugellager, oder ein Schrägkugellager sein. Das Zahnrad 25 ist vorzugsweise zwischen den Wälzlagern 34, 35 angeordnet. Das dem Finger 24 nähere obere Wälzlager 34 ist vorzugsweise größer als das untere Wälzlager 35. Das obere Wälzlager 34 fängt die über den Finger 24 eingeleiteten radialen Querkräfte auf den Exzenter 16 ab. Das obere Wälzlager 34 hat eine radial äußere Lagerschale 36 und eine radial innere Lagerschale 37. Die äußere Lagerschale 36 umschließt ringförmig die innere Lagerschale 37. Die axialen Abmessungen der äußeren Lagerschale 36 und der inneren Lagerschale 37 sind beispielsweise gleich. Die beiden Lagerschalen 36, 37 haben einander zugewandte radial ausgerichtete Laufflächen 38, 39, in welchen Wälzkörper 40, vorzugsweise Kugeln, geführt sind. Beide Laufflächen 38 sind konkav gekrümmt. Die Wälzkörper 40 sind parallel zu der Achse 23 und in radialer Richtung, d.h. senkrecht zu der Achse 23, zwangsgeführt. Die Wälzkörper 41, d.h. ihre Schwerpunkte, liegen in einer zu der Achse 23 senkrechten Führungsebene 42. Das untere Wälzlager 35 hat im Wesentlichen den gleichen Aufbau wie das obere Wälzlager 34. Wälzkörper 41, vorzugsweise Kugeln, sind durch radial ausgerichtete, konkave Laufflächen 43, 44 einer äußeren Lagerschale 45 und einer inneren Lagerschale 46 in einer Führungsebene 47 zwangsgeführt.The shaft 22 of the eccentric 16 is mounted in two rolling bearings 34, 35 , which are arranged offset from one another along the axis 23 . The bearings 34 may be a deep groove ball bearing, or an angular contact ball bearing, as shown. The gear 25 is preferably disposed between the rolling bearings 34, 35 . The upper rolling bearing 34 closer to the finger 24 is preferably larger than the lower rolling bearing 35. The upper rolling bearing 34 intercepts the radial transverse forces introduced via the finger 24 onto the eccentric 16 . The upper roller bearing 34 has a radially outer bearing shell 36 and a radially inner bearing shell 37. The outer bearing shell 36 encloses annularly the inner bearing shell 37. The axial dimensions of the outer bearing shell 36 and the inner bearing shell 37 are the same, for example. The two bearing shells 36, 37 have facing radially oriented running surfaces 38, 39, in which rolling elements 40, preferably balls, are guided. Both treads 38 are concavely curved. The rolling elements 40 are parallel to the axis 23 and in the radial direction, ie perpendicular to the axis 23, forcibly guided. The rolling elements 41, ie their centers of gravity, lie in a direction perpendicular to the axis 23 guide plane 42. The lower roller bearing 35 has substantially the same structure as the upper roller bearing 34. Wälzkörper 41, preferably balls, are by radially aligned, concave treads 43, 44 of an outer bearing shell 45 and an inner bearing shell 46 forcibly guided in a guide plane 47 .

Die Welle 22 ist in die beiden inneren Lagerschalen 37, 46 eingesetzt. Die inneren Lagerschalen 37, 46 sind längs der Achse 23 unbeweglich zu der Welle 22 und damit auch zueinander unbeweglich. Ein axialer Abstand 48 zwischen den beiden inneren Lagerschalen 37, 46 ist fest. Der axiale Abstand 48 wird beispielsweise auf die Führungsebenen 42, 47 der Wälzlager 34, 35 bezogen, welche die Wälzlager 34, 35 axial unbelastet bei der Anordnung der inneren Lagerschalen 37, 46 aufweisen. Die inneren Lagerschalen 37, 46 sind beispielsweise mittels eines Presssitzes auf der Welle 22 befestigt. Die beispielhafte Welle 22 weist einen geringeren Durchmesser an dem unteren Wälzlager 35 auf. Angrenzend an das untere Wälzlager 35 ist der Durchmesser der Welle 22 größer. Das untere Wälzlager 35 kann an dem Durchmessersprung formschlüssig abgestützt sein, um ein Verschieben des unteren Wälzlagers 35 in Richtung zu dem oberen Wälzlagers 34 zu unterbinden.The shaft 22 is inserted into the two inner bearing shells 37, 46 . The inner bearing shells 37, 46 are immovable along the axis 23 to the shaft 22 and thus immovable to one another. An axial distance 48 between the two inner bearing shells 37, 46 is fixed. The axial distance 48 is related, for example, to the guide planes 42, 47 of the roller bearings 34, 35 , which have the roller bearings 34, 35 axially unloaded in the arrangement of the inner bearing shells 37, 46 . The inner bearing shells 37, 46 are fastened to the shaft 22 , for example by means of an interference fit. The exemplary shaft 22 has a smaller diameter at the lower roller bearing 35 . Adjacent to the lower roller bearing 35 , the diameter of the shaft 22 is larger. The lower roller bearing 35 may be positively supported on the diameter jump, to prevent displacement of the lower roller bearing 35 in the direction of the upper roller bearing 34 .

Die äußere Lagerschale 36 des oberen Wälzlagers 34 ist in einem Sitz 49 in der oberen Gehäuseschale 29 und die äußere Lagerschale 45 des unteren Wälzlagers 35 ist in einem Sitz 50 in der unteren Gehäuseschale 30 eingesetzt. Die beiden äußeren Lagerschalen 36, 45 sind in den jeweiligen Gehäuseschalen 29, 30 unbeweglich, insbesondere längs der Achse 23 unbeweglich, fixiert. Die obere, äußere Lagerschale 36 weist zu der Kontaktfläche 31 der oberen Gehäuseschale 29 einen axialen Abstand 51 (oberer Abstand 51) auf. Die untere, äußere Lagerschale 45 weist zu der Kontaktfläche 32 der unteren Gehäuseschale 30 einen axialen Abstand 52 (unterer Abstand 52) auf. Sofern die Kontaktflächen 31, 32 geneigt oder gestuft sind, werden die axialen Abstände 51, 52 an sich berührenden Abschnitten, z.B. bei der jeweils gleichen Schraube, bestimmt. Die axialen Abstände 51, 52 werden, analog zu den inneren Lagerschalen, beispielsweise anhand der Führungsebenen 42, 47 bestimmt, welche sich für axial unbelastete Wälzlager 34, 35 bei der Anordnung der äußeren Lagerschalen 36 ergibt. Die Summe des oberen Abstandes 51 und des unteren Abstandes 52 für die äußeren Lagerschalen 36, 45 ist geringer als der axiale Abstand 48 der inneren Lagerschalen 37, 46. Der Unterschied liegt vorzugsweise im Bereich von 0,2 mm bis 3 mm. Vor dem Anziehen der Schrauben 33 zeigt sich der Unterschied in einem Spalt 53 zwischen den Gehäuseschalen 29, 30, insbesondere den Kontaktflächen 31, 32. Nach dem Anziehen der Schrauben 33 ergibt sich eine Verspannung der Gehäuseschalen 29, 30, welche sich daraufhin verformen. Die axiale Vorspannung wirkt in die Wälzlager 34, 35 ein. Die äußeren Lagerschalen 36, 45 sind etwas gegenüber den inneren Lagerschalen 37, 46 versetzt, verglichen zu axial unbelasteten Wälzlagern. In Fig. 2 ist der relative Versatz der inneren Lagerschalen 37, 46 gegenüber den äußeren Lagerschalen 36, 46 überzeichnet dargestellt.The outer bearing shell 36 of the upper roller bearing 34 is seated in a seat 49 in the upper housing shell 29, and the outer bearing shell 45 of the lower roller bearing 35 is seated in a seat 50 in the lower housing shell 30 . The two outer bearing shells 36, 45 are immovable in the respective housing shells 29, 30 , in particular immovably fixed along the axis 23 . The upper, outer bearing shell 36 has to the contact surface 31 of the upper housing shell 29 at an axial distance 51 (upper distance 51) . The lower, outer bearing shell 45 has an axial distance 52 (lower distance 52) to the contact surface 32 of the lower housing shell 30 . If the contact surfaces 31, 32 are inclined or stepped, the axial distances 51, 52 are determined at touching portions, eg at the same screw in each case. The axial distances 51, 52 are determined analogously to the inner bearing shells, for example on the basis of the guide planes 42, 47 , which results for axially unloaded roller bearings 34, 35 in the arrangement of the outer bearing shells 36 . The sum of the upper distance 51 and the lower distance 52 for the outer bearing shells 36, 45 is less than the axial distance 48 of the inner bearing shells 37, 46. The difference is preferably in the range of 0.2 mm to 3 mm. Before tightening the screws 33 , the difference in a gap 53 between the housing shells 29, 30, in particular the contact surfaces 31, 32. After tightening the screws 33 results in a distortion of the housing shells 29, 30, which then deform. The axial bias acts in the rolling bearings 34, 35 a. The outer bearing shells 36, 45 are slightly offset from the inner bearing shells 37, 46 , compared to axially unloaded bearings. In Fig. 2 is the relative offset of the inner bearing shells 37, 46 with respect to the outer bearing shells 36, 46 shown oversubscribed.

Claims (5)

Handwerkzeugmaschine (1) mit
einem Werkzeughalter (2) zum Aufnehmen eines Werkzeugs (4),
einem Motor (5),
einer Welle (22), die den Motor (5) mit einer das Werkzeug (4) antreibenden Einheit (6, 7) koppelt,
einem ersten Wälzlager (34), das eine äußere Lagerschale (36), eine innere Lagerschale (37) und zwischen der äußeren Lagerschale (36) und der inneren Lagerschale (37) angeordnete Wälzkörper (40) aufweist, einem zweiten Wälzlager (35), das eine äußere Lagerschale (45), eine innere Lagerschale (46) und zwischen der äußeren Lagerschale (45) und der inneren Lagerschale (46) angeordnete Wälzkörper (41) aufweist, wobei die innere Lagerschale (37) des ersten Wälzlagers (34) und die innere Lagerschale (46) des zweiten Wälzlagers (35) in einem ersten axialen Abstand (48) zueinander auf die Welle (22) aufgesetzt sind,
einem Gehäuse (28), das eine mit einer ersten Gehäuseschale (29) durch eine kraftschlüssige Verbindung (33) verbundene zweite Gehäuseschale (30) aufweist, wobei die äußere Lagerschale (36) des ersten Wälzlagers (34) in die erste Gehäuseschale (29) und die äußere Lagerschale (45) des zweiten Wälzlagers (35) in die zweite Gehäuseschale (30) eingesetzt sind und die äußere Lagerschale (36) des ersten Wälzlagers (34) zu der äußeren Lagerschale (45) des zweiten Wälzlagers (35) einen zweiten axialen Abstand (51, 52) aufweist, und
wobei der erste axiale Abstand (48) gegenüber dem zweiten axialen Abstand (51, 52) derart gewählt ist, dass die erste Gehäuseschale (29) und die zweite Gehäuseschale (30) durch die die kraftschlüssige Verbindung (33) parallel zu der Welle (22) verspannt sind.Hand tool (1) with
a tool holder (2) for receiving a tool (4),
a motor (5),
a shaft (22) coupling the motor (5) to a unit (6, 7) driving the tool (4),
a first roller bearing (34) having an outer bearing shell (36), an inner bearing shell (37) and between the outer bearing shell (36) and the inner bearing shell (37) arranged rolling elements (40), a second rolling bearing (35), an outer bearing shell (45), an inner bearing shell (46) and arranged between the outer bearing shell (45) and the inner bearing shell (46) rolling elements (41), wherein the inner bearing shell (37) of the first rolling bearing (34) and the inner bearing shell (46) of the second rolling bearing (35) is placed on the shaft (22) at a first axial distance (48) from one another,
a housing (28) having a second housing shell (30) connected to a first housing shell (29) by a non-positive connection (33), the outer bearing shell (36) of the first rolling bearing (34) being inserted into the first housing shell (29) and the outer bearing shell (45) of the second rolling bearing (35) in the second housing shell (30) are inserted and the outer bearing shell (36) of the first rolling bearing (34) to the outer bearing shell (45) of the second rolling bearing (35) has a second axial distance (51, 52), and
wherein the first axial distance (48) relative to the second axial distance (51, 52) is selected such that the first housing shell (29) and the second housing shell (30) through which the frictional connection (33) parallel to the shaft (22 ) are braced. Handwerkzeugmaschine (1) nach Anspruch 1, dadurch gekennzeichnet, dass die äußeren Lagerschalen (36, 45) längs der Achse (23) unbeweglich in den Gehäuseschalen (29, 30) eingesetzt und die inneren Lagerschalen (37, 46) längs der Achse (23) unbeweglich auf der Welle (22) aufgesetzt sind.Hand machine tool (1) according to claim 1, characterized in that the outer bearing shells (36, 45) along the axis (23) immovably in the housing shells (29, 30) used and the inner bearing shells (37, 46) along the axis (23 ) immovably on the shaft (22) are placed. Handwerkzeugmaschine (1) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die erste Gehäuseschale (29) eine Kontaktfläche (31) und die zweite Gehäuseschale (30) eine Kontaktfläche (32) aufweisen, die durch die kraftschlüssige Verbindung (33) einander berühren, und bei gelöster kraftschlüssiger Verbindung (33) die äußere Lagerschale (36) einen dritten axialen Abstand (51) zu der Kontaktfläche (31) der ersten Gehäuseschale (29) und die äußere Lagerschale (45) einen vierten axialen Abstand (52) zu der Kontaktfläche (32) der zweiten Gehäuseschale (30) aufweisen, und der erste axiale Abstand (48) größer als die Summe des dritten und vierten axialen Abstands (51, 52) ist.Hand tool (1) according to claim 1 or 2, characterized in that the first housing shell (29) has a contact surface (31) and the second housing shell (30) has a contact surface (32) which by the non-positive connection (33) touch each other, and when the force-locking connection (33) is released, the outer bearing shell (36) has a third axial distance (51) from the contact surface (31) of the first Housing shell (29) and the outer bearing shell (45) have a fourth axial distance (52) to the contact surface (32) of the second housing shell (30), and the first axial distance (48) greater than the sum of the third and fourth axial distance (51, 52). Handwerkzeugmaschine (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Welle (22) Teil eines Exzenters (16) ist, mit einem pneumatischen Schlagwerk (6) gekoppelt ist.Powered hand tool (1) according to one of the preceding claims, characterized in that the shaft (22) is part of an eccentric (16), with a pneumatic percussion (6) is coupled. Handwerkzeugmaschine (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ein Getriebe (21) in dem Gehäuse (28) öldicht angeordnet ist.Hand tool (1) according to one of the preceding claims, characterized in that a transmission (21) in the housing (28) is arranged oil-tight.
EP13192765.9A 2013-11-13 2013-11-13 Manual tool machine Active EP2873488B1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3901498A1 (en) * 2020-04-21 2021-10-27 Hilti Aktiengesellschaft Electro-pneumatic percussion mechanism

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3114423A (en) * 1960-03-30 1963-12-17 Skil Corp Rotary-hammer device
US20030083186A1 (en) * 2001-09-17 2003-05-01 Hetcher Jason D. Rotary hammer
EP1604785A2 (en) * 2004-06-08 2005-12-14 Hitachi Koki Co., Ltd. Striking tool

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3114423A (en) * 1960-03-30 1963-12-17 Skil Corp Rotary-hammer device
US20030083186A1 (en) * 2001-09-17 2003-05-01 Hetcher Jason D. Rotary hammer
EP1604785A2 (en) * 2004-06-08 2005-12-14 Hitachi Koki Co., Ltd. Striking tool

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3901498A1 (en) * 2020-04-21 2021-10-27 Hilti Aktiengesellschaft Electro-pneumatic percussion mechanism
WO2021213804A1 (en) * 2020-04-21 2021-10-28 Hilti Aktiengesellschaft Electropneumatic percussion mechanism
CN115398130A (en) * 2020-04-21 2022-11-25 喜利得股份公司 Electropneumatic Shock Mechanism

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