Patent Application
20220288760
The present invention relates to a rotary drive for driving a tool fitting of a hand-held power tool, in particular of a combination hammer or hammer drill. The rotary drive is configured, with respect to a working axis of the tool fitting, to convert a thrust input movement into a rotary output movement.
A rotary drive of this kind is known for example from EP 3 181 302 A1.
It is an object of the present invention to provide a comparatively compact and robust rotary drive. A further object of the present invention is to specify a hand-held power tool having such a rotary drive.
The present invention provides a rotary drive in the form of a slotted-link mechanism with a freewheel-mounted track body and a ball cage arranged coaxially with the track body, wherein, when the ball cage is subjected to the thrust input movement, at least one ball of the ball cage slides along in an endless track contour formed on an outer surface of the track body and thus brings about a rotation of the freewheel-mounted track body. The ball cage can have one or more balls. In particular, the ball, as a coupling element between the track body and the ball cage, is not connected fixedly to the track body or to the ball cage.
The invention incorporates the finding that when the drilling tool (striking and rotating tool) is varied, different drill bit diameters or drill bit types sometimes require a slower rotational speed of the tool fitting for the best possible drilling performance. This makes a step-down gear mechanism with a comparatively stronger reducing action necessary, this—at least in the hand-held power tools of the prior art—disadvantageously increasing the space requirement, the costs, the number of components, the complexity and the weight of these tools.
In the rotary drive of the invention, which is preferably incorporated in a hand-held power tool in the form of a hammer drill or combination hammer, use is made of a slotted-link mechanism. This is instead of spur gears and/or bevel gears, which are exclusively or at least predominantly used in hand-held power tools of the prior art. As a result, a comparatively compact and robust rotary drive can be provided.
In a particularly preferred configuration, the endless track contour is formed in an undulating and/or continuous manner. Particularly preferably, the endless track contour is free of track portions that are oriented parallel to the working axis of the tool fitting.
It has been found to be advantageous for the rotary drive to have a sleeve carrying the ball cage, wherein the sleeve engages at least partially around the track body. In a particularly preferred configuration, the track body is freewheel-mounted by way of a form-fitting or force-fitting freewheel. This makes it possible to ensure that the rotary output movement is executed only in one direction of rotation. Preferably, the track body has only one degree of freedom, preferably only one degree of rotational freedom about the working axis.
It has been found to be advantageous for the rotary drive in the form of a slotted-link drive to have a transmission ratio of 1:25.
In a particularly preferred configuration, the track body consists of plastic or exhibits such a plastic. The rotary drive may be free of metal gearwheels.
As regards the hand-held power tool, the present invention provides a hand-held power tool, in particular a hammer drill or combination hammer, having a tool fitting for holding a striking and rotating tool on a working axis, and having an electric motor. The hand-held power tool is equipped with a rotary drive of the above-described type, wherein the electric motor, for generating the thrust input movement, is coupled to the rotary drive and the rotary drive is arranged so as to drive a spindle carrying the tool fitting in rotation about the working axis.
In a particularly preferred configuration, the hand-held power tool is equipped with an impact mechanism that has a striker moved periodically along the working axis, wherein the electric motor is coupled to the impact mechanism. Particularly preferably, the electric motor is coupled to the impact mechanism via a transmission component that may have an impact-mechanism eccentric wheel or a wobble plate.
It has been found to be advantageous for the impact mechanism to be arranged at least partially within the track body and/or within the sleeve carrying the ball cage. In this way, the hand-held power tool can be embodied in a particularly compact manner.
In a particularly preferred configuration, the spindle, at a constant rotational speed of the electric motor, executes an irregular, pulsating rotary output movement. In particular, an oscillating movement and a rotary movement of the tool fitting can be phase offset, for example with a phase offset of 180 degrees.
Further advantages will become apparent from the following description of the figures. Various exemplary embodiments of the present invention are illustrated in the figures. The figures, the description and the claims contain numerous features in combination. A person skilled in the art will expediently also consider the features individually and combine them to form useful further combinations.
In the figures, identical and similar components are denoted by the same reference signs. In the figures:
A first preferred exemplary embodiment of a rotary drive 70 is illustrated in
The rotary drive 70 is in the form of a slotted-link mechanism 71 with a freewheel-mounted track body 75 and a ball cage 77 arranged coaxially with the track body, wherein, when the ball cage 77 is subjected to the thrust input movement SE, at least one ball 76 of the ball cage 77 slides along in an endless track contour 78 formed on an outer surface OF of the track body 75 and thus brings about a rotation of the freewheel-mounted track body 75 about the working axis 3.
As can be gathered from
On that side of the rotary drive 70 that faces the tool fitting 2, the track body 75 is freewheel-mounted in a freewheel 72 configured in this case for example in a form-fitting manner. By way of the freewheel 72, it is possible to ensure that the rotary output movement DA is executed only in one direction of rotation (indicated by the arrow tip at DA). Preferably, the rotary drive 70 has an anti-rotation safeguard 73 for the sleeve 79, in this case for example in the form of a slot/pin pairing 73′. In the direction of the working axis 3, the track body 75 is mounted immovably with respect to the machine housing 10, in this case for example by means of a fixed bearing 69.
A preferred track body 75 will now be described with reference to
As a result of the track geometry shown, the ball always slides and/or rolls in the same track direction BR. As mentioned above, the endless track contour 78 is arranged in the circumferential direction U on an outer surface OF of the cylindrical track body 75. The only remaining degree of freedom of the cylindrical track body 75 is the rotary output movement DA about the cylinder axis, which in this case coincides with the working axis 3. The endless track contour 78 is designed such that the ball 76 can always move freely. The corners of the track contour always reliably passed through by the ball 76 of the ball cage 77 in the same track direction BR. Since the track body 75 can rotate as a single degree of freedom (rotation about the working axis 3) and the ball 76 is moved cyclically in translation along the working axis 3, a rotary output movement DA is produced by the endless track contour 78. The rotary output movement DA takes place upon each forward stroke (arrows LR oriented toward the left) and rearward stroke (arrows PR oriented toward the right) equally. The speed VDA of the rotary output movement DA is irregular as a physical result of the track contour (similar to a pulsating behavior).
As a result of the comparatively large helix angle SW (for example greater than 60 degrees here) in the respective corner regions EB of the endless track contour 78, the ball 76 is located significantly beneath a singular point SP of the endless track contour 78 at its turning points UP and, upon the return movement (arrows PR oriented toward the right), is captured reliably by the collecting funnel FT, i.e. a relative widening of the endless track contour 78, which makes it easier to “catch” the ball 76. It has been found that when the driven tool 4 (cf.
Finally, in the lower region of
A preferred exemplary embodiment of a hand-held power tool 100 according to the invention having a rotary drive 70 is illustrated in
The impact mechanism 50 and the rotary drive 70 are arranged in a machine housing 10. A handle 11 is typically arranged on a side of the machine housing 10 that faces away from the tool fitting 2. The user can hold and guide the hammer drill 101 by means of the handle 11 during operation. An additional auxiliary handle can be fastened close to the tool fitting 2. Arranged on or in the vicinity of the handle 11 is an operating button 12, which the user can actuate preferably with the holding hand. The electric motor 8 is switched on by the actuation of the operating button 12. Typically, the electric motor 8 rotates for as long as the operating button 12 is kept pressed.
The tool 4 is movable along the working axis 3 in the tool fitting 2. For example, the tool 4 has an elongate groove, in which a blocking ball 5 or some other blocking body of the tool fitting 2 engages. The user holds the tool 4 in a working position in that the user presses the tool 4 indirectly against a substrate by way of the hammer drill 101.
The tool fitting 2 is fastened to a spindle 13 of the rotary drive 70, wherein the spindle 13 is in this case formed integrally with the track body 75 of the rotary drive. The tool fitting 2 can rotate about the working axis 3 with respect to the machine housing 10. At least one claw 1 or other suitable means in the tool fitting 2 transmits a torque from the tool fitting 2 to the tool 4.
According to the invention, the rotary drive 70 is in the form of a slotted-link mechanism 71 with a freewheel-mounted 75 track body and a ball cage 77 arranged coaxially with the track body 75. If the ball cage 77 is subjected to the thrust input movement SE, one ball 76 of the ball cage 77 slides along in an endless track contour 78 formed on an outer surface of the track body 75, with the result that a rotation (about the working axis 3 in the arrow direction of the rotary output movement DA) of the freewheel-mounted (for example by a form-fitting freewheel 72 in this case) track body 75 is brought about.
The pneumatic impact mechanism 50 has, in the striking direction 6, an exciter 14, a striker 15 and an anvil 16. The exciter 14 is forced to execute a periodic movement along the working axis 3 by means of the electric motor 8. The exciter 14 is attached via a transmission component 17 for converting the rotary movement of the electric motor 8 into a periodic movement in translation along the working axis 3. An example of a transmission component 17 contains an impact-mechanism eccentric wheel 21 or a wobble plate. A period of the movement in translation of the exciter 14 is defined by the rotational speed of the electric motor 8 and optionally by a reduction ratio in the transmission component 17. The connecting rod 7, which is fastened to a sleeve 79 of the rotary drive 70 by means of a connecting pin 80, is readily apparent. It is readily apparent that the sleeve 79 carries the ball cage 76 and the sleeve 79 engages partially around the track body, i.e. engages around in particular in the region of the ball cage 76. Via the transmission component 17, both the rotary drive 70 and the impact mechanism 50 are coupled to the electric motor of the hand-held power tool 100. As can be gathered from
The striker 15 couples to the movement of the exciter 14 via a pneumatic spring. The pneumatic spring is formed by a pneumatic chamber 18 closed off between the exciter 14 and the striker 15. The striker 15 moves in the striking direction 6 until the striker 15 strikes the anvil 16. The anvil 16 bears against the tool 4 in the striking direction 6 and transmits the impact to the tool 4. The period of the movement of the striker 15 is identical to the period of the movement of the exciter 14. The striker 15 thus strikes with a striking rate that is identical to the inverse of the period. The optimal striking rate is defined by the mass of the striker 15 and the geometric dimensions of the pneumatic chamber 18. An optimal striking rate may lie in the range between 25 Hz and 100 Hz.
The example of an impact mechanism 50 has a piston-like exciter 14 and a piston-like striker 15, which are guided along the working axis 3 by a guide tube 19. The exciter 14 and the striker 15 bear with their lateral surfaces against the inner surface of the guide tube 19. The pneumatic chamber 18 is closed off along the working axis 3 by the exciter 14 and the striker 15 and in a radial direction by the guide tube 19. Sealing rings in the lateral surfaces of the exciter 14 and striker 15 can improve the airtight closing off of the pneumatic chamber 18.
The rotary drive 70 contains the spindle 13, which is arranged coaxially with the working axis 3. The spindle 13 is for example hollow, and the impact mechanism 50 is arranged within the spindle. The tool fitting 2 is fitted on the spindle 13. The tool fitting 2 can be connected releasably or permanently to the spindle 13 via a closing mechanism.
The spindle 13 rotates preferably periodically. Preferably, the spindle 13 is rotated continuously but with a speed (caused by the rotary drive 70 in the form of a slotted-link mechanism 71) that is dependent on rotational position. Thus, the spindle 13, at a constant rotational speed of the electric motor 8, executes an irregular, pulsating rotary output movement DA. The rotary drive 70 is synchronized with the impact mechanism 50, wherein the striking movement and rotary movement can be phase offset, for example through 180 degrees.
| Number | Date | Country | Kind |
|---|---|---|---|
| 19195363.7 | Sep 2019 | EP | regional |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2020/073621 | 8/24/2020 | WO |
