EP2448715B1 - Machine-outil portative - Google Patents

Machine-outil portative Download PDF

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Publication number
EP2448715B1
EP2448715B1 EP10720186.5A EP10720186A EP2448715B1 EP 2448715 B1 EP2448715 B1 EP 2448715B1 EP 10720186 A EP10720186 A EP 10720186A EP 2448715 B1 EP2448715 B1 EP 2448715B1
Authority
EP
European Patent Office
Prior art keywords
power tool
portable power
planetary gear
tool according
transmission stage
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.)
Active
Application number
EP10720186.5A
Other languages
German (de)
English (en)
Other versions
EP2448715A1 (fr
Inventor
Joachim Hecht
Heiko Roehm
Tobias Herr
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2448715A1 publication Critical patent/EP2448715A1/fr
Application granted granted Critical
Publication of EP2448715B1 publication Critical patent/EP2448715B1/fr
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
    • B25D11/062—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
    • 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
    • B25D16/003—Clutches specially adapted therefor
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/061—Swash-plate actuated impulse-driving mechanisms
    • 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
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • 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
    • B25D2250/241—Sliding impact heads, i.e. impact heads sliding inside a rod or around a shaft

Definitions

  • the invention relates to a hand tool according to the preamble of claim 1.
  • EP 1 690 642 A1 is a hand tool with a multi-stage planetary gear and a hammer blower, which is driven by the planetary gear.
  • the invention relates to a hand tool, in particular a ringbohhammer, with a gear assembly, a hammer mechanism and a tool spindle according to the independent claim 1.
  • the transmission arrangement on at least one gear stage element which is intended to divide a power flow to different speeds for a shock and to provide a rotary drive.
  • a "gear arrangement” is to be understood to mean an arrangement which has at least one gear stage.
  • the gear stage is designed as a bevel gear, as a bevel gear and / or as another, the expert appears appropriate gear stage.
  • the gear stage is designed as a planetary gear stage.
  • a "hammer impact mechanism” should be understood to mean a striking mechanism with at least one linearly moved racket.
  • the hammer blower moves the bat resiliently and / or pneumatically and / or hydraulically by means of a link device, by means of a wobble bearing and / or advantageously by means of an eccentric element.
  • the hammer mechanism is preferably designed as a sliding block, as a swash bearing impactor and / or as an eccentric percussion.
  • a sliding block is to be understood a hammer blower with a link device.
  • a linkage device generates a linear movement between at least two areas by elements that are movable on a mechanically limited endless track.
  • a “swash bearing impactor” is to be understood as meaning a bearing with a finger which is connected to a drive rotary element of the hammer impact mechanism and whose bearing plane deviates from a plane which is oriented perpendicular to the axis of rotation of the drive rotary element.
  • An “eccentric impact mechanism” is to be understood as a hammer impact mechanism which is intended to generate a linear movement perpendicular to the axis of rotation of the rotational movement from a rotational movement.
  • the eccentric percussion on an eccentric element which is rotatably connected to the drive rotary member.
  • a "hammer impact mechanism” should in particular not be understood as a detent impact mechanism in which a rotatable detent disc is permanently mechanically fixedly connected to the hand tool housing and in which the detent disc interacts with a detent disk mechanically mechanically connected to the tool spindle.
  • a "Rastentschtechnik” is a striking mechanism in which a punch-generating detent disc is driven in rotation. An axial toothing of the detent disc causes an axial movement of the tool spindle.
  • a “tool spindle” is to be understood as meaning a shaft of the handheld power tool which, in at least one operating state, transmits a rotational movement to a tool fastening device of the handheld power tool.
  • a rotation axis of the tool spindle lies on a rotation axis of an insertion tool and / or the tool fastening device.
  • the tool spindle transmits a rotational movement and a striking movement to the tool fastening device in at least one operating state.
  • at least part of the tool spindle is connected directly to the tool fastening device.
  • the tool spindle an attachment for the tool attachment device.
  • the tool spindle may be at least partially formed integrally with the tool fastening device.
  • the tool fastening device is advantageously designed as a tool chuck, as a hexagonal mount, as an SDS mount (special direct system from Robert Bosch GmbH) and / or as another tool fastener that appears expedient to the person skilled in the art.
  • a tool chuck is to be understood as meaning a sun gear, a ring gear, a planetary gear, another element of the gear arrangement which appears appropriate to a person skilled in the art, and / or in particular a planet carrier.
  • “divide” should be understood to mean that forces act on the gear stage element at at least three points which cause torques, such as in particular at least one input point and at least two output points.
  • a speed for a percussion drive can be optimized for a particularly effective stroke rate and thus a particularly large drilling progress can be achieved in a percussion drilling operation with small outer dimensions of the power tool.
  • the gear arrangement generates at least two output rotary movements in at least one operating state, which have an odd-numbered relationship to one another.
  • the gear assembly transmits one of the output rotational motions to the tool spindle and one of the output rotational motions to the hammer impact mechanism.
  • An "odd-numbered relationship” should be understood in particular as meaning a ratio that lies outside a natural set of numbers.
  • the ratio is outside the natural number of numbers between 2 and 6.
  • initial rotational movement should be understood in particular a rotational movement, which leads a power out of the gear assembly out. Due to the ungranted ratio between the two output rotational movements, an advantageous impact pattern can be achieved, which enables a particularly effective percussion drilling operation.
  • the gear arrangement has at least one ring gear, which is mounted axially movable.
  • axially movably mounted should be understood to be movable in particular in a direction parallel to a rotational axis of the ring gear.
  • the ring gear relative to a hand tool housing, compared with at least one planetary gear of the same gear stage and / or against at least one planetary gear of another gear stage movable.
  • the ring gear is movable so that it is coupled with at least one planetary gear two different gear stages simultaneously and / or successively. Due to the axially movably mounted ring gear structurally simple, space-saving and cost-effective a Kochrastkupplung and / or a blowout can be realized.
  • the hand tool machine has a spring element which exerts a force on the axially movable ring gear in at least one operating state, whereby the ring gear is advantageously automatically moved in at least one direction and so a structurally simple structure is possible.
  • the transmission arrangement has at least one gear stage, which is intended to increase a speed for a percussion drive, whereby an advantageously high impact rate and thus an effective Schlagbohrvorgang can be achieved.
  • the hammer impact mechanism has a spring-elastic, about a pivot axis pivotally mounted lever member which is intended to drive a racket of the hammer impact mechanism in at least one operating condition.
  • a "lever element” is to be understood in particular a movable element, act on the at least two torques at a distance, advantageously at a different distance to the pivot axis.
  • the lever element is pivotable about a pivot axis which is aligned perpendicular to the axis of rotation of the tool spindle.
  • the lever element is configured rotationally asymmetric and / or can be moved about an axis of rotation by less than 360 °.
  • lever element is at least partially made of spring steel.
  • to drive should be understood in particular accelerating.
  • the racket is freely movable in at least one operating state in a main working direction.
  • the racket is movable by the lever element.
  • freely movable is to be understood in this context, in particular, that the racket over at least a distance in the main working direction of components, with the exception of a sliding and / or rolling friction in a guide, is decoupled.
  • a “main working direction” should be understood to mean a direction of impact of the hammer impact mechanism.
  • the tool spindle has a rotational engagement contour, which is provided to produce along an axis of rotation an axially displaceable and rotationally fixed connection.
  • the rotary driving contour advantageously transmits primarily, particularly advantageously exclusively, rotational forces.
  • the rotational engagement contour is designed as a rotational engagement contour that appears appropriate to the person skilled in the art, such as, in particular, a splined shaft profile and / or advantageously like a gearing.
  • the tool spindle is formed in two parts and the rotary driving contour connects the two parts of the tool spindle with each other.
  • a ratio between racket and spindle mass can advantageously be optimally selected and the tool spindle can be decoupled axially from the gear arrangement, as a result of which wear, in particular on a planet carrier of the gear arrangement, can be minimized.
  • the gear arrangement has at least one sun gear which, in at least one operating state, is non-rotatable, in particular directly, i.e. without intermediary further components, rotatably connected to at least a portion of the hammer impact mechanism, whereby a structurally particularly simple and space-saving design is possible.
  • the sun gear is rotatably connected to a drive rotary element of the hammer impact mechanism.
  • an electric motor and a Akkuan gleichiser proposed, which is intended to provide the electric motor with energy.
  • the battery connecting unit is preferably connected to a battery unit in an operational state of operation.
  • a “battery connection unit” should be understood in particular to mean a unit which is intended to make contact with the battery unit.
  • the Akkuan gleichiser produces an electrical and a mechanical contact.
  • a “rechargeable battery unit” is to be understood in particular as a device having at least one rechargeable battery, which is intended to supply the portable power tool with power independently of the mains.
  • the hand tool can also be operated with another motor that appears appropriate to a person skilled in the art, such as, in particular, an electric motor having a mains connection or a compressed-air motor.
  • the gear arrangement has a gear stage, which is designed as a planetary gear stage.
  • the planetary gear stage has at least one sun gear, a ring gear, at least one planetary gear and / or a planet carrier. Due to the planetary gear stage can be achieved in a particularly space-saving advantageous reduction.
  • the hammer impact mechanism has a releasable, in particular mechanically releasable coupling device, which is intended to transmit a rotational movement.
  • the coupling device rotatably connects a striking mechanism shaft of the hammer impact mechanism and at least a part of the transmission assembly.
  • a "releasable coupling device” is to be understood in particular a coupling device which transmits a rotational movement in at least one operating state and which interrupts transmission of the rotational movement in at least one operating state.
  • Transmit a rotary motion is to be understood in particular a speed and / or torque forward. Due to the releasable coupling device, the hammer impact mechanism can advantageously be switched off, and thus an advantageously usable as a screwdriver hand tool can be achieved.
  • the coupling device is intended to be closed by a force transmitted via the tool spindle.
  • the coupling device is provided to be closed by a force acting in the axial direction of the tool spindle force.
  • the handheld power tool has a torque setting unit with a coupling device which is provided to limit a maximum torque transmitted via the tool spindle in at least one operating state.
  • the coupling device is detachable.
  • the "maximum torque" is preferably a torque which the tool spindle can transmit to an insert tool in operation, in particular before a coupling device opens automatically.
  • the coupling device is designed as a device with spring-loaded or spring-loaded locking elements, in particular balls. In principle, however, other devices which appear reasonable to the person skilled in the art are also conceivable.
  • the locking elements can be loaded in an axial and / or preferably in a radial direction with a spring force. By limiting the maximum torque undesirable high torques can be prevented.
  • the handheld power tool has an operating element by means of which the coupling device can be actuated.
  • the operator can operate the coupling device by means of the operating element and / or by means of the tool spindle.
  • a sensor unit and an actuating unit can actuate the coupling device at least partially automatically based on material properties of a workpiece.
  • actuate should be understood in particular open and / or close the coupling device, whereby the impact operation can be switched on and off comfortably by the operator and in particular the coupling device of Drehmomenteinstellhow can be permanently closed in a drilling operation.
  • the hammer impact mechanism has a drive rotation element with an axis of rotation which is arranged coaxially to at least a part of the tool spindle.
  • a “drive rotation element” is to be understood, in particular, as an element which carries out a rotational movement in at least one operating state and which moves at least one further element of the hammer impact mechanism.
  • the drive rotation element is designed as a shaft, particularly advantageously as a hollow shaft.
  • coaxial is to be understood in particular that at least a part of the tool spindle and the drive rotation element are driven in rotation in at least one operating state about a common axis of rotation.
  • the tool spindle and the drive rotation element are rotatable about the same axis of rotation relative to each other.
  • the power tool is formed undulating.
  • inter-shaft is to be understood in particular that all waves of the power tool, which transmit rotational movement at least in a drilling operation, have a common axis of rotation, which advantageously coincide with the axis of rotation of the tool spindle.
  • at least a portion of the tool spindle is meant in particular a region of the tool spindle, which is connected directly to the tool fastening device.
  • the drive rotary element is designed as a striking mechanism shaft, which surrounds at least a portion of the tool spindle.
  • An "impactor shaft” is to be understood in particular as meaning a shaft which transmits a rotational movement to at least one further element of the hammer impact mechanism for generating a shock.
  • the tool spindle and the percussion shaft rotate in at least one operating state with a different angular velocity.
  • envelope is to be understood in particular that the percussion shaft, the tool spindle in at least one plane for the most part, advantageously encloses 360 °.
  • this plane is oriented perpendicular to the axis of rotation of the drive rotation element.
  • the hammer impact mechanism has an eccentric element, whereby structurally simple a mechanically low-wear and a powerful hand tool can be provided.
  • the eccentric element has an axis of rotation which coincides with an axis of rotation of the tool spindle.
  • the term "coincide” is to be understood in particular that the eccentric element is mounted for rotation about a same axis of rotation as the tool spindle.
  • the eccentric element and at least a portion of the tool spindle are rotatably connected to each other. This can advantageously be dispensed with an intermediate shaft and it can be a special handy and lightweight hand tool can be achieved.
  • a powerful hand tool with a weight including a battery less than 5kg, advantageously less than 2kg, particularly advantageously less than 1.5kg can be achieved.
  • the hammer impact mechanism has a racket which at least partially surrounds the tool spindle in at least one plane.
  • the tool spindle advantageously at least partially passes through the racket in the direction of the axis of rotation of the tool spindle.
  • the tool spindle passes completely through the racket.
  • the racket encloses the tool spindle in at least one plane by 360 °.
  • the phrase "encircling 360 ° in at least one plane" should be understood in particular to mean that the racket radially surrounds at least one point of the tool spindle in at least one plane.
  • the racket strike the tool spindle in at least one operating state.
  • the racket transmits a shock pulse to at least a portion of the tool spindle, wherein the tool spindle advantageously transmits the impact pulse to a tool fastening device of the power tool.
  • the tool attachment device preferably transmits the impact pulse to an insert tool.
  • the racket strikes a shock transmission device, such as an anvil, or directly on an insert tool of the power tool.
  • the impact transmission device transmits a striking motion directly to an insert tool.
  • the impact transmission device is arranged, for example, at least partially coaxially within the tool spindle.
  • the tool spindle can advantageously combine a striking movement and a rotary movement to be transferred to a tool fastening device, thereby advantageously producing an inexpensive, universally applicable one and structurally simple tool fastening device used and again space can be saved.
  • FIG. 1 shows a hand tool 10a, which is designed as a cordless combi drill, in a partially schematic representation.
  • the hand tool 10a has a Drehmomenteinstellech 12a, a Gear assembly 14a, a hammer mechanism 16a, a tool spindle 18a, a Akkuan gleich 20a, a pistol-shaped portable power tool housing 22a and arranged in the hand tool housing 22a electric motor 24a.
  • a tool fastening device 30a which is designed as a tool chuck.
  • the rotation axis 34a is formed as a main rotation axis, that is, a plurality of elements of the power tool 10a are rotatable about this rotation axis 34a.
  • An operating element 36a of the torque setting unit 12a is arranged in an annular manner about the rotation axis 34a of the tool spindle 18a, between the hand-held power tool housing 22a and the tool fastening device 30a.
  • a control element 40a is arranged, which allows an operator not shown a change between a drilling or screwing operation and a percussion drilling operation.
  • the electric motor 24a is arranged in a rear, that is the tool fastening device 30a remote from region 42a of the power tool housing 22a.
  • a not-shown stator of the electric motor 24a is rotatably connected to the power tool housing 22a.
  • the gear arrangement 14a is arranged in a tubular, upper region 44a of the pistol-shaped hand-held power tool housing 22a arranged axially to the rotation axis 34a.
  • the gear arrangement 14a is arranged in a tubular, upper region 44a of the pistol-shaped hand-held power tool housing 22a arranged axially to the rotation axis 34a.
  • a lower portion 46a of the power tool housing 22a which connects approximately at right angles to the upper portion 44a, forms a handle 48a.
  • the battery terminal unit 20a is disposed.
  • a battery unit 50a connected to the battery terminal unit 20a is in a shown ready state, a battery unit 50a connected.
  • the battery unit 50a supplies the electric motor 24a with power during
  • the drive rotation member 52a is formed as a hammer shaft 54a.
  • the percussion shaft 54a encloses a portion of the tool spindle 18a, which faces the gear assembly 14a.
  • the axis of rotation 34a of the impactor shaft 54a is aligned parallel to the main working direction 26a of the hand tool 10a.
  • the tool spindle 18a rotatably connects the tool attachment device 30a to the gear assembly 14a along the rotation axis 34a, and is largely formed as a solid shaft.
  • the hammer mechanism 16a is formed as an eccentric impactor having an eccentric 56a.
  • the eccentric 56a has an axis of rotation which coincides with the axis of rotation 34a of the tool spindle 18a.
  • the eccentric element 56a is formed by a sleeve, whose wall thickness 58a increases and decreases continuously in the course of 360 ° about the axis of rotation 34a.
  • the eccentric 56a is rotatably connected to the percussion shaft 54a and is penetrated by this in the axial direction.
  • Hammer impactor 16a has an eccentric outer member 60a that is moved by eccentric member 56a during a percussion drilling operation.
  • the eccentric outer element 60a is designed as an approximately elliptical disk.
  • the eccentric outer element 60a has a round bore 62a, which is arranged in a region remote from the handle 48a region 64a of the eccentric outer element 60a.
  • the eccentric element 56a is mounted movably relative to the eccentric outer element 60a by means of a bearing not shown in detail.
  • the eccentric outer element 60a has an opening 80a, which is arranged in a region of the eccentric outer element 60a facing the handle 48a.
  • the opening 80a is penetrated by a resilient lever element 66a.
  • the lever member 66a prevents rotation of the eccentric outer member 60a in the circumferential direction relative to the power tool housing 22a.
  • the hammer mechanism 16a has a racket 68a.
  • the lever member 66a drives the racket 68a during a percussion drilling operation.
  • the lever member 66a is formed as a, in a side view, L-shaped bracket made of spring steel. As FIG. 5 shows, the lever member 66a a horseshoe-shaped portion 70a, which is penetrated by the tool spindle 18a.
  • the hammer mechanism 16a has a housing-fixed pivot axis 72a, about which the lever element 66a is tiltable.
  • the housing-fixed pivot axis 72a is aligned perpendicular to the rotational axis 34a of the tool spindle 18a.
  • the beater 68a of the hammer impact mechanism 16a is freely movable during a free-flying phase in the main working direction 26a.
  • the free-flying phase is a period beginning with an end of acceleration of the beater 68a by the lever member 66a and ending immediately before a bounce.
  • the beater 68a transmits a shock pulse to the tool spindle 18a.
  • the racket 68a strikes a transmission element 74a of the tool spindle 18a.
  • the transmission element 74a is formed as a thickening of the tool spindle 18a, which has a surface 76a on a side facing the racket 68a.
  • the surface 76a is aligned parallel to a striking surface 78a of the racket 68a.
  • the racket 68a encloses the tool spindle 18a in planes aligned perpendicular to the axis of rotation 34a of the tool spindle 18a by 360 °.
  • the racket 68a is guided on the tool spindle 18a and is mounted rotatably about the rotation axis 34a of the tool spindle 18a relative to the hand tool housing 22a.
  • the racket can also be guided on its outer contour and / or rotationally secured relative to the hand tool housing.
  • the eccentric outer 60a moves perpendicular to the axis of rotation 34a of the tool spindle 18a.
  • an end 82a of the lever element 66a which is tiltably arranged in the opening 80a of the eccentric outer element 60a is moved and thereby the lever element 66a is tilted.
  • the lever element 66a thereby accelerates the racket 68a from an initial position facing the gear arrangement 14a in the direction of the main working direction 26a, by a driving end 84a of the lever element 66a being pressed against a first support surface 86a of the racket 68a presses.
  • the striker 68a moves in the main working direction 26a into the free-flight phase, in which the driving end 84a of the lever element 66a is arranged in a free region 88a of the striker 68a and thus decoupled from the striker 68a in the main working direction 26a.
  • the racket 68a hits the transmission element 74a of the tool spindle 18a and transmits its pulse to the tool spindle 18a.
  • the lever member 66a returns the racket 68a to the home position by the driving end 84a of the lever member 66a exerting a force on a second support surface 90a of the rack 68a disposed on another side of the free area 88a with respect to the first support surface 86a. Due to the resilient design of the lever member 66a jump-free courses of the forces acting between the lever member 66a and the racket 68a, achieved.
  • the gear assembly 14a has four gear stages, which are formed as planetary gear stages 92a, 94a, 96a, 98a.
  • the four planetary gear stages 92a, 94a, 96a, 98a are arranged one behind the other along the rotational axis 34a of the tool spindle 18a.
  • the four planetary gear stages 92a, 94a, 96a, 98a each have a ring gear 100a, 102a, 104a, 106a, a sun gear 108a, 110a, 112a, 114a, a planet carrier 116a, 118a, 120a, 122a and four planetary gears 124a, 126a, 128a, 130a, of which only two are shown.
  • the planet gears 124a of the first planetary gear stage 92a mesh with the sun gear 108a of the first planetary gear stage 92a and the ring gear 100a of the first planetary gear stage 92a, and are rotatably supported on the planet carrier 116a of the first planetary gear stage 92a.
  • the planet carrier 116a of the first planetary gear stage 92a guides the planetary gears 124a of the first planetary gear stage 92a in a circular path about the rotation axis 34a of the tool spindle 18a.
  • the second planetary gear 94a, the third planetary gear 96a and the fourth planetary gear 98a are constructed accordingly.
  • the sun gear 108a of the first planetary gear stage 92a is rotatably connected to the electric motor 24a and disposed in the main operating direction 26a adjacent to the electric motor 24a, between the tool mounting device 30a and the electric motor 24a.
  • the ring gear 100a of the first planetary gear stage 92a is rotatably connected to the power tool housing 22a.
  • the planet carrier 116a of the first planetary gear stage 92a is non-rotatably connected to the sun gear 110a of the second planetary gear 94a, the ring gear 102a is also connected to the power tool housing 22a.
  • the planet carrier 118a of the second planetary gear stage 94a is rotatably connected to the sun gear 112a of the third planetary gear stage 96a.
  • the ring gear 104a of the third planetary gear stage 96a is also rotatably connected to the power tool housing 22a during a drilling, screwing or hammering operation.
  • the first, second and third planetary gear stages 92a, 94a, 96a each cause a reduction in the direction of the tool attachment device 30a.
  • a ratio of this reduction between a rotational speed of the electric motor 24a and a rotational speed of the tool spindle 18a is approximately 60: 1.
  • the person skilled in the possibilities for switching an alternative transmission ratio between a rotational speed of the electric motor 24a and a rotational speed of the tool spindle 18a known.
  • the ring gear 102a of the second planetary gear 94a may be rotatably connected by means of a coupling device, not shown, alternatively to the power tool housing 22a with the planet 116a of the first planetary gear stage 92a.
  • the alternative ratio between the speed of a motor speed and the speed of the tool spindle 18a is approximately 15: 1.
  • the gear assembly 14a includes a gear stage member 132a that divides a power flow.
  • the gear stage member 132a is formed as a common planet carrier 120a, 122a of the third and fourth planetary gear stages 96a, 98a.
  • the tool spindle 18a has a rotational engagement contour 134a, which produces an axially displaceable and rotationally fixed connection with the gear arrangement 14a, more precisely with the gear stage element 132a, along the rotational axis 34a. Accordingly, there is a tap of a speed of the tool spindle 18a on the planet carrier 120a of the third planetary gear stage 96a.
  • the rotational engagement contour 134a is formed as an internal toothing 136a of the gear step element 132a and an outer toothing 138a of the tool spindle 18a.
  • the tap could be made on the ring gear of the third planetary gear stage 96a.
  • the rotational engagement contour 134a may be as shown in FIG. 3 A rotary drive contour 140a axially divides the tool spindle 18a into two parts 142a, 144a.
  • the one part 142a of the tool spindle 18a is directly connected to the gear assembly 14a.
  • the other part 144a of the tool spindle 18a is directly connected to the tool attachment device 30a.
  • the rotational drive contour 134a described above can be dispensed with.
  • the portion 142a of the tool spindle 18a, which is directly connected to the gear assembly 14a may then be fixedly connected in the axial direction with the gear stage member 132a. Thereby, a mass of the axially movable part 144a of the tool spindle 18a can be reduced.
  • the sun gear 114a of the fourth planetary gear stage 98a is rotatably connected to the drive rotation member 52a during a percussion drilling operation.
  • the sun gear 114a of the fourth planetary gear stage 98a is rotatably connected to the eccentric element 56a of the hammer impact mechanism 16a during a percussion drilling operation.
  • the ring gear 106a of the fourth planetary gear stage 98a could also be connected in a rotationally fixed manner to the drive rotation element 52a.
  • the ring gear 106a of the fourth planetary gear stage 98a is mounted axially movable.
  • the gear arrangement 14a has a coupling element 146a which connects the ring gear 106a of the fourth planetary gear stage 98a in a rotationally fixed and axially displaceable manner to the handheld power tool housing 22a.
  • the gear assembly 14a more specifically, the fourth planetary gear stage 98a, generates during a percussion drilling operation the two power fluxes of the common planet carrier 120a, 122a of the third and the fourth Planetenradgetriebecut 96a, 98a output rotational movements, which have an odd-numbered relationship to each other.
  • the fourth planetary gear stage 98a increases a rotational speed for a percussion drive, that is, a rotational speed of the percussion shaft 54a and the drive rotational element 52a is higher than a rotational speed of the tool spindle 18a.
  • the gear assembly 14a more specifically the gear stage member 132a, provides different speeds for a percussion and a rotary drive.
  • the hand tool 10a has a first releasable coupling device 148a, which transmits a rotational movement during a percussion drilling operation.
  • the first coupling device 148a is formed as a dog clutch and remains closed during an axial movement of the tool spindle 18a caused by a shock. In a percussion drilling operation, the first coupling device 148a connects the hammer hammer 16a to the sun gear 114a of the fourth planetary gear set 98a.
  • the first coupling device 148a has a spring element 150a, which is designed as a spiral spring.
  • the spring element 150a opens the first coupling device 148a when the tool spindle 18a is relieved against the main working direction 26a. In this case, the hammer mechanism 16a is deactivated.
  • the first coupling device 148a is closed by a force transmitted through the tool spindle 18a in the axial direction, by the insert tool 32a, during a percussion drilling operation.
  • the spring element 150a is compressed and the first coupling device 148a is closed.
  • the force is applied in the axial direction in a percussion drilling operation via a shaping element 152a, which is connected to the tool spindle 18a, on the striking mechanism shaft 54a and thus on the first coupling device 148a.
  • the hand tool 10a has the operating element 40a, by means of which the operator can actuate the first coupling device 148a by permanently opening the first coupling device 148a. That's it Hammer impact mechanism 16a deactivated in this operating state.
  • this operating element 40a allows a manual change between a drilling or screwing operation and a percussion drilling operation and it can be drilled and screwed with the hand tool 10a without impact pulse.
  • the operating element 40a is designed as a slide switch.
  • the torque adjusting unit 12a has a coupling device 154a that limits a transmittable torque.
  • a maximum torque is adjustable by means of Drehmomenteinstellech 12a.
  • second coupling device 154a is arranged between the ring gear 104a of the third planetary gear stage 96a and the ring gear 106a of the fourth planetary gear stage 98a.
  • the second clutch device 154a opens automatically from an adjustable maximum torque acting on the tool spindle 18a. When the second clutch device 154a is opened, the ring gear 104a of the third planetary gear train stage 96a is axially secured and rotatably movable.
  • the second clutch device 154a is designed as an overload clutch known to the person skilled in the art, the response torque of which can be changed by an axial force on the second clutch device 154a.
  • the second coupling device 154a is formed as a form element coupling with inclined surfaces or as a friction clutch.
  • the ring gear 106a of the fourth planetary gear stage 98a serves as a form element by simultaneously meshing with the planetary gears 128a, 130a of the third planetary gear stage 96a and the fourth planetary gear stage 98a and displaced when the maximum torque is exceeded in the main working direction 26a and the planet gears 128a of the third planetary gear stage 96a releases.
  • the ring gear 106a of the fourth planetary gear stage 98a is preferably wider than the planet gears 128a, 130a of the third and / or the fourth planetary gear stage 96a, 98a.
  • the portable power tool 10a has a spring element 156a, which exerts a force on the axially movable ring gear 106a of the fourth planetary gear stage 98a and thus on the second clutch device 154a during operation, thus closing the second clutch device 154a.
  • the second coupling device 154a can be adjusted by the operator, that is, a force on the axially movable ring gear 106a can be adjusted. This is done by an axial movement of an abutment point 158a of the spring element 156a.
  • the operating member 36a of the torque adjusting unit 12a is formed as a ring rotatable by the operator.
  • the operating element 36a has a mold element, which is not shown in more detail, which is provided to manually permanently close the second coupling device 154a. This is done by a corresponding adjustment of the operating element 36a by the operator. As a result, opening of the second clutch device 154a during a drilling operation can be prevented at all torques transmitted via the tool spindle 18a that do not exceed a safety torque.
  • the gear arrangement 14a has two bearing elements 160a, 162a which radially support the tool spindle 18a.
  • the first bearing element 160a is arranged on the side of the tool spindle 18a facing the tool fastening device 30a.
  • the first bearing element 160a is axially fixedly connected to the tool spindle 18a and is axially displaceably mounted in the portable power tool housing 22a.
  • the first bearing element can also be axially fixedly connected to the portable power tool housing and axially displaceably mounted on the tool spindle.
  • the second bearing element 162a is arranged, which supports the tool spindle 18a within the sun gear 114a of the fourth planetary gear stage 98a.
  • the tool spindle 18a can be supported by means of the common planet carrier 120a, 122a of the third and fourth planetary gear stage 96a, 98a.
  • FIG. 6 a further embodiment of the invention is shown.
  • the letter a in the reference numerals of the embodiment in the FIGS. 1 to 5 by the letter b in the reference numerals of the embodiment in the FIG. 6 replaced.
  • the following Description is limited essentially to the differences from the embodiment in the FIGS. 1 to 5 , wherein with respect to the same components, features and functions on the description of the embodiment in the FIGS. 1 to 5 can be referenced.
  • various arrangements and combinations of the coupling device described are conceivable.
  • FIG. 6 shows how FIG. 2 Specifically, a torque adjusting unit 12b, a gear assembly 14b, a hammer hammer 16b, and a tool spindle 18b.
  • the Drehmomenteinstellech 12b has locking elements 164b, which are formed as balls.
  • the locking elements 164b are mounted in non-illustrated form elements and are disposed between a ring gear 104b of a third planetary gear stage 96b and a power tool housing 22b.
  • the latching elements 164b are spring-loaded by a spring element 156b of the torque setting unit 12b with a force that can be adjusted by the operator radially to a rotation axis 34b of the tool spindle 18b. If a torque transmitted via the tool spindle 18b exceeds a set maximum torque, the latching elements 164b push the shaped elements apart against a force of the spring element 156b.
  • the ring gear 104b of the third planetary gear stage 96b rotates relative to the portable power tool housing 22b, and the tool spindle 18b does not transmit torque at this time.
  • the ring gear 104b of the third planetary gear stage 96b and a ring gear 106b of a fourth planetary gear stage 98b are non-rotatably connected to one another by means of a coupling device 148b.
  • the coupling device 148b is opened, the ring gear 106b of the fourth planetary gear stage 98b is freely rotatable about the rotation axis 34b and thus the hammer blower 16b is switched off for a drilling and screwing operation.
  • the coupling device 148b is closed by means of two mold elements 152b, 168b.
  • the first mold element 152b transmits a force in the axial direction from the tool spindle 18b to a percussion shaft 54b.
  • This mold element 152b is axially mechanically fixed to the tool spindle 18b.
  • the second mold member 166b is connected to the percussion shaft 54b in the axial direction. It transmits the force in the axial direction via a bearing 168b to the ring gear 106b of the fourth planetary gear stage 98b. The force closes the coupling device 148b during a drilling and screwing operation. Alternatively, a transmission of the force via the fourth planetary gear 98b is possible.
  • the coupling device 148b is opened by a spring element 150b, which applies a axial force aligned with a tool fastening device 30b to the striking mechanism shaft 54b via a bearing 170b.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Drilling And Boring (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (17)

  1. Outil manuel motorisé, en particulier foreuse à percussion, présentant
    un ensemble de transmission (14a; 14b),
    un mécanisme de percussion (16a; 16b) et
    une broche (18a; 18b) à outil,
    l'ensemble de transmission (14a; 14b) présentant au moins un étage de transmission configuré comme étage de transmission (92a, 94a, 96a; 92b, 94b, 96b) à roues planétaires et ayant pour effet un soutien et au moins un étage de transmission (98a; 98b) disposé en aval de l'étage de transmission (92a, 94a, 96a; 92b, 94b, 96b) à roues planétaires et configuré comme étage de transmission à roues planétaires,
    l'étage de transmission (98a; 98b) aval présentant au moins un élément (132a; 132b) d'étage de transmission prévu pour répartir un flux de force de manière à délivrer des vitesses de rotation différentes en entraînement de percussion et en entraînement de rotation,
    caractérisé en ce que
    l'étage de transmission aval (98a; 98b) est prévu pour augmenter la vitesse de rotation de l'entraînement de percussion par rapport à l'étage ou aux étages de transmission amont.
  2. Outil manuel motorisé selon la revendication 1, caractérisé en ce que l'élément (132a; 132b) d'étage de transmission est configuré comme porte-roues planétaires.
  3. Outil manuel motorisé selon les revendications 1 ou 2, caractérisé en ce que dans au moins un état de fonctionnement, l'ensemble de transmission (14a; 14b) forme au moins deux déplacements de rotation de sortie qui présentent l'un par rapport à l'autre un rapport non entier.
  4. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé en ce que l'ensemble de transmission (14a; 14b) présente au moins une roue creuse (106a; 106b) montée à déplacement axial.
  5. Outil manuel motorisé selon la revendication 4, caractérisé par un élément élastique (156a; 156b) qui, au moins dans un état de fonctionnement, exerce une force sur la roue creuse (106a; 106b) mobile axialement.
  6. Outil manuel motorisé selon les revendications 4 ou 5, caractérisé en ce que l'ensemble de transmission (14a) présente un élément d'accouplement (146a) qui relie la roue creuse (106a) de l'étage de transmission (98a) à roues planétaires à rotation solidaire et à coulissement axial à un boîtier (22a) de l'outil manuel motorisé.
  7. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé en ce que la broche (18b; 18b) à outil présente un contour (134a, 140a; 134b) d'entraînement en rotation prévu pour établir le long d'un axe de rotation (34a; 34b) une liaison à rotation solidaire et coulissant axialement.
  8. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé en ce que l'étage de transmission aval de l'ensemble de transmission (14a; 14b) présente au moins une roue solaire (114a; 114b) qui, dans au moins un état de fonctionnement, est reliée à rotation solidaire à au moins une partie du mécanisme de percussion (16a; 16b).
  9. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé par une unité (12a; 12b) de réglage du couple de rotation qui présente un ensemble d'accouplement (154a; 154b) prévu pour, dans au moins un état de fonctionnement, limiter à une valeur maximale le couple de rotation transmis par l'intermédiaire de la broche (18a; 18b) à outil.
  10. Outil manuel motorisé selon la revendication 9, caractérisé par un élément d'actionnement (36a, 40a; 36b, 40b) au moyen duquel l'ensemble d'accouplement (148a, 154a; 148b, 154b) peut être actionné.
  11. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé en ce que le mécanisme de percussion (16a; 16b) présente un élément (52a; 52b) d'entraînement en rotation doté d'un axe de rotation (34a; 34b) disposé coaxialement par rapport à au moins une partie de la broche (18a; 18b) à outil.
  12. Outil manuel motorisé selon la revendication 11, caractérisé en ce que l'élément (52a; 52b) de rotation d'entraînement est configuré comme arbre de percussion (54a; 54b) qui entoure au moins une partie de la broche (18a; 18b) à outil.
  13. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé en ce que le mécanisme de percussion (16a; 16b) présente un élément excentrique (56a; 56b).
  14. Outil manuel motorisé selon la revendication 13, caractérisé en ce que l'élément excentrique (56a; 56b) présente un axe de rotation (34a; 34b) qui correspond à l'axe de rotation (34a; 34b) de la broche (18a; 18b) à outil.
  15. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé en ce que le mécanisme de percussion (16a; 16b) présente un percuteur (68a; 68b) qui entoure la broche (18a; 18b) à outil au moins en partie dans au moins un plan.
  16. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé en ce que l'ensemble de transmission (14a; 14b) présente quatre étages de transmission configurés comme étages de transmission (92a, 94a, 96a, 98a, 92b, 94b, 96b, 98b) à roues planétaires, le premier, le deuxième et le troisième étage de transmission (92a, 94a, 96a, 92b, 94b, 96b) à roues planétaires ayant chacun pour effet une diminution du rapport de transmission dans la direction d'un ensemble (30a) de fixation d'outil, le quatrième étage (98a; 98b) de la transmission à roues planétaires étant prévu pour augmenter la vitesse de rotation d'un entraînement de percussion par rapport au troisième étage de transmission (96a, 96b) à roues planétaires.
  17. Outil manuel motorisé selon l'une des revendications précédentes, caractérisé en ce que l'élément (132a; 132b) d'étage de transmission est configuré comme support commun (120a, 122a, 120b, 122b) de roue planétaire du ou des étages de transmission (92a, 94a, 96a; 92b, 94b, 96b) à roues planétaires et du ou des étages de transmission (98a; 98b).
EP10720186.5A 2009-07-03 2010-06-01 Machine-outil portative Active EP2448715B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009027442A DE102009027442A1 (de) 2009-07-03 2009-07-03 Handwerkzeugmaschine
PCT/EP2010/057658 WO2011000654A1 (fr) 2009-07-03 2010-06-01 Machine-outil portative

Publications (2)

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EP2448715A1 EP2448715A1 (fr) 2012-05-09
EP2448715B1 true EP2448715B1 (fr) 2017-09-06

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US (1) US9415497B2 (fr)
EP (1) EP2448715B1 (fr)
JP (2) JP5514904B2 (fr)
CN (1) CN102470521B (fr)
DE (1) DE102009027442A1 (fr)
WO (1) WO2011000654A1 (fr)

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Publication number Publication date
WO2011000654A1 (fr) 2011-01-06
JP2012531323A (ja) 2012-12-10
JP2014121787A (ja) 2014-07-03
CN102470521B (zh) 2015-12-16
DE102009027442A1 (de) 2011-01-05
CN102470521A (zh) 2012-05-23
US20120175140A1 (en) 2012-07-12
US9415497B2 (en) 2016-08-16
JP5514904B2 (ja) 2014-06-04
EP2448715A1 (fr) 2012-05-09
JP5837121B2 (ja) 2015-12-24

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