Hammer mechanism

Abstract

A hammer mechanism having at least one impact-generation unit and a clamping chuck drive shaft is provided. The impact-generation unit includes a spur-gear transmission stage for translating a rotational speed of the clamping chuck drive shaft into a higher rotational speed for impact generation.

Claims

1. A hammer mechanism, comprising: at least one impact-generation unit including a hammer mechanism shaft; and a clamping chuck drive shaft, wherein the at least one impact-generation unit includes a spur-gear transmission stage adapted to translate a rotational speed of the clamping chuck drive shaft into a higher rotational speed of the hammer mechanism shaft for an impact generation.

2. The hammer mechanism as recited in claim 1, wherein: the at least one impact-generation unit includes a hammer mechanism shaft, and the hammer mechanism shaft includes an axis of rotation situated adjacent to the clamping chuck drive shaft in a radial direction.

3. The hammer mechanism as recited in claim 2, wherein the at least one impact-generation unit includes at least one bearing for mounting the hammer mechanism in an axially fixated manner.

4. The hammer mechanism as recited in claim 1, wherein the at least one impact-generation unit includes a hammer element mounted by the clamping chuck drive shaft in a manner allowing movement in a strike direction in at least one operating state.

5. The hammer mechanism as recited in claim 4, wherein the clamping chuck drive shaft penetrates the hammer element at least partially.

6. The hammer mechanism as recited in claim 4, further comprising: a coupling element connected to the clamping chuck drive shaft in a torsionally fixed manner and for driving the at least one impact-generation unit.

7. The hammer mechanism as recited in claim 1, further comprising: a bearing for mounting the clamping chuck drive shaft in an axially displaceable manner.

8. The hammer mechanism as recited in claim 1, further comprising: a planetary gearing for driving the clamping chuck drive shaft in at least one operating state.

9. The hammer mechanism as recited in claim 1, further comprising: a clamping chuck; and a snap die including a coupling element for transmitting a rotary motion to the clamping chuck.

10. A hammer mechanism, comprising: at least one impact-generation unit a clamping chuck; a clamping chuck drive shaft a snap die including a coupling element for transmitting a rotary motion to the clamping chuck; and an impact-generation deactivation unit including a blocking element for acting on the snap die parallel to at least one force of the clamping chuck drive shaft in at least a drilling operation, wherein the at least one impact-generation unit includes a spur-gear transmission stage adapted to translate a rotational speed of the clamping chuck drive shaft into a higher rotational speed of the hammer mechanism shaft for an impact generation.

11. A handheld tool, comprising: a hammer mechanism, comprising: at least one impact-generation unit including a hammer mechanism shaft, and a clamping chuck drive shaft, wherein the at least one impact-generation unit includes a spur-gear transmission stage adapted to translate a rotational speed of the clamping chuck drive shaft into a higher rotational speed of the hammer mechanism shaft for an impact generation.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 shows a handheld tool having a hammer mechanism according to the present invention, in a perspective view.

(2) FIG. 2 shows a section of the hammer mechanism of FIG. 1.

(3) FIG. 3 shows a coupling arrangement, clamping chuck drive shaft, snap die, and a portion of a clamping chuck of the hammer mechanism from FIG. 1, shown individually in a perspective view.

(4) FIG. 4 shows another part-sectional view of the hammer mechanism from FIG. 1, which shows an impact-generation deactivation unit of the hammer mechanism.

(5) FIG. 5 shows a first alternative exemplary embodiment of a snap die of the hammer mechanism from FIG. 1 in a schematic representation.

(6) FIG. 6 shows a second alternative exemplary embodiment of a snap die of the hammer mechanism from FIG. 1 in a schematic representation.

(7) FIG. 7 shows a third alternative exemplary embodiment of a snap die of the hammer mechanism from FIG. 1 in a sectional view.

(8) FIG. 8 shows the snap die from FIG. 7 in a first perspective view.

(9) FIG. 9 shows the snap die from FIG. 7 in a second perspective view.

(10) FIG. 10 shows a portion of a clamping chuck of the hammer mechanism of FIG. 7 in a perspective view.

(11) FIG. 11 shows a fourth alternative exemplary embodiment of a snap die of the hammer mechanism from FIG. 1 in a schematic representation.

DETAILED DESCRIPTION

(12) FIG. 1 shows a handheld tool 10a, which is developed as impact drill screwer. Handheld tool 10a has a pistol-shaped housing 12a. A drive motor 14a of handheld tool 10a is situated inside housing 12a. Housing 12a has a handle region 16a and a battery coupling means 18a, which is disposed at an end of handle region 16a facing away from drive motor 14a. Battery coupling means 18a links a handheld tool battery 20a in a manner that allows an operator to sever the link electrically or mechanically. Handheld tool battery 20a has an operating voltage of 10.8 Volt, but could also have a different, especially higher, operating voltage. Furthermore, handheld tool 10a has a hammer mechanism 22a according to the present invention, which includes a clamping chuck 24a disposed on the outside, and operating elements 26a, 28a.

(13) FIG. 2 shows hammer mechanism 22a in a sectional view. Hammer mechanism 22a also includes a planetary gearing 30a and a clamping chuck drive shaft 32a. When in operation, planetary gearing 30a drives clamping chuck drive shaft 32a to execute rotary motions about an axis of rotation. To do so, planetary gearing 30a has three planetary gear stages 34a, 36a, 38a. An operator is able to adjust a transmission ratio of planetary gearing 30a between a rotor 40a of drive motor 14a and clamping chuck drive shaft 32a in at least two stages. As an alternative, a transmission ratio between drive motor 14a and clamping chuck drive shaft 32a could also be designed not to be adjustable.

(14) Hammer mechanism 22a has a torque restriction device 42a. Torque restriction device 42a keeps a ring gear 44a of planetary gearing 30a fixated during a working process. Toward this end, torque restriction device 42a includes fixation balls 46a, which engage with recesses of ring gear 44a. A spring 48a of torque restriction device 42a exerts a force on fixation balls 46a in the direction of ring gear 44a in the process. An operator is able to move an end of spring 48a facing fixation balls 46a in the direction of fixation balls 46a by means of one of operating elements 26a. Operating element 26a is provided with an eccentric element for this purpose. Thus, the force acting on fixation balls 46a is adjustable. If a particular maximum torque has been reached, fixation balls 46a are pressed out of the recesses, and ring gear 44a runs freely, so that a force transmission between rotor 40a and clamping chuck drive shaft 32a is interrupted. Torque restriction device 42a thus is provided to restrict a maximum torque transmittable via clamping chuck drive shaft 32a.

(15) Hammer mechanism 22a has an impact-generation unit 50a and a first coupling means 52a. First coupling means 52a is connected to clamping chuck drive shaft 32a in torsionally fixed manner, first coupling means 52a and clamping chuck drive shaft 32a being formed in one piece, in particular. Impact-generation unit 50a includes a second coupling means 54a, which is connected to first coupling means 52a in torsionally fixed manner during a drilling and/or impact drilling mode. As shown in FIG. 3 as well, first coupling means 52a is developed in the form of premolded shapes and second coupling means 54a as recesses. When the drilling mode is activated, first coupling means 52a dips into second coupling means 54a, i.e., to the full extent. As a result, the coupling between first coupling means 52a and second coupling means 54a is reversible by axial shifting of clamping chuck drive shaft 32a in the direction of clamping chuck 24a. A spring 56a of hammer mechanism 22a is situated between first coupling means 52a and second coupling means 54a. Spring 56a presses clamping chuck drive shaft 32a in the direction of clamping chuck 24a. When impact-generation unit 50a is deactivated, it opens the linkage between first coupling means 52a and second coupling means 54a.

(16) Hammer mechanism 22a has a first bearing 58a, which fixates second coupling means 54a relative to housing 12a in the axial direction and rotationally mounts it in coaxial manner with respect to clamping chuck drive shaft 32a. Furthermore, hammer mechanism 22a has a second bearing 60a, which rotationally mounts clamping chuck drive shaft 32a on a side facing drive motor 14a, such that it is able to rotate about the axis of rotation. Second bearing 60a is integrally formed with one of the three planetary gear stages. Clamping chuck drive shaft 32a includes a coupling means 62a, which connects it to a planet carrier 64a of this planetary gear stage 38a in axially displaceable and torsionally fixed manner. As a result, planetary gear stage 38a is provided to support clamping chuck drive shaft 32 in axially displaceable manner. On a side facing clamping chuck 24a, clamping chuck drive shaft 32a together with clamping chuck 24a is rotationally mounted by a clamping chuck bearing 70a. Clamping chuck bearing 70a has a rear bearing element, which is pressed onto clamping chuck 24a in axially fixated manner. In addition, clamping chuck bearing 70a has a front bearing element which supports clamping chuck 24a inside housing 12a in axially displaceable manner.

(17) Impact-generation unit 50a includes a spur-gear transmission stage 72a, which translates a rotational speed of clamping chuck drive shaft 32a into a higher rotational speed for impact generation. A first toothed wheel 74a of spur-gear transmission stage 72a is integrally formed with second coupling means 54a. In an impact drilling operation, it is driven by clamping chuck drive shaft 32a. A second toothed wheel 76a of spur-gear transmission stage 72a is integrally formed with a hammer mechanism shaft 78a. An axis of rotation of hammer mechanism shaft 78a is disposed next to the axis of rotation of clamping chuck drive shaft 32a in the radial direction. Impact-generation unit 50a has two bearings 80a, which mount hammer mechanism shaft 78a in axially fixed and rotatable manner. Impact-generation unit 50a is provided with a drive means 82a, which translates a rotary motion of impact mechanism shaft 78a into a linear motion. An eccentric element 84a of drive means 82a is integrally formed with impact mechanism shaft 78a. Using a needle roller bearing, an eccentric sleeve 86a of drive means 82a is rotationally mounted on eccentric element 84a so as to be rotatable relative to eccentric element 84a. Eccentric sleeve 86a has a recess 88a, which encloses a rocker lever 90a of impact-generation unit 50a.

(18) Rocker lever 90a is mounted in pivotable manner on a pivot axle 92a of impact-generation unit 50a, that is to say, it is pivotable about an axis that runs perpendicularly to the axis of rotation of clamping chuck drive shaft 32a. An end of rocker lever 90a facing away from drive means 82a partially encloses a hammer means 94a of hammer mechanism 22a. The rocker lever engages with a recess 96a of hammer means 94a in the process. Recess 96a is developed in the form of a ring. When operated as impact drill, rocker lever 90a exerts a force on hammer means 94a, which accelerates the hammer means. Rocker lever 90a is moved in a sinusoidal pattern during operation. Rocker lever 90a has a flexible design. It has a spring constant between eccentric sleeve 86a and hammer 90a that is less than 100 N/mm and greater than 10 N/mm. In this exemplary embodiment, rocker lever 98a has a spring constant of approximately 30 N/mm.

(19) Clamping chuck drive shaft 32a mounts hammer means 94a in a manner that allows it to move in strike direction 98a. To do so, hammer means 94a delimits a recess 100a. Clamping chuck drive shaft 32a penetrates hammer means 94a through recess 100a. In the process, hammer means 94a encloses recess 100a in a plane perpendicular to recess 100a to 360 degrees. When operated, hammer means 94a strikes a snap die 102a of hammer mechanism 22a. Snap die 102a is situated between an inserted tool 104a and hammer means 94a. In an operative state, inserted tool 104a is fixed in place in clamping chuck 24a. Clamping chuck 24a mounts snap die 102a so as to allow movement parallel to strike direction 98a. In an impact drilling operation, snap die 102a transmits hammer pulses originating from hammer means 94a to inserted tool 104a.

(20) Clamping chuck drive shaft 32a is connected to snap die 102a in axially movable and torsionally fixed manner. Snap die 102a delimits a recess 106a for this purpose. When in an operative state, clamping chuck drive shaft 32a is partially situated in recess 106a of snap die 102a. Clamping chuck drive shaft 32a is rotationally mounted via snap die 102a, clamping chuck 24a, and clamping chuck bearing 70a. Clamping chuck 24a is rotationally driven via snap die 102a. For this purpose, clamping chuck 24a and snap die 102a each include coupling means 108a, 110a, which are provided to transmit the rotary motion to clamping chuck 24a. Coupling means 108a of snap die 102a is developed as groove, whose main extension is situated parallel to strike direction 98a. Coupling means 108a extends along a radially outward-lying surface area of snap die 102a. Coupling means 110a of clamping chuck 24a thus is developed as a raised region that fits the groove.

(21) Clamping chuck 24a has an inserted-tool coupling region 112a, in which inserted tool 104a is fixed in strike direction 98a during a drilling a screw-drilling operation, or in which region it is mounted in movable manner in strike direction 98a during an impact-drilling operation. In addition, the clamping chuck has a tapered region 114a, which delimits a movement range of snap die 102a in strike direction 98a. Furthermore, clamping chuck 24a includes a mounting ring 116a, which delimits a movement range of snap die 102a counter to strike direction 98a.

(22) During an impact drilling operation, an operator presses inserted tool 104a against a workpiece (not shown further). The operator thereby shifts inserted tool 104a, snap die 102a and clamping chuck drive shaft 32a relative to housing 12a, in a direction opposite to the strike direction 98a, i.e., in the direction of drive motor 14a. In so doing, the operator compresses spring 56a of hammer mechanism 22a. First coupling means 52a dips into second coupling means 54a, so that clamping chuck drive shaft 32a begins to drive impact-generation unit 50a. When the operator stops pressing inserted tool 104a against the workpiece, spring 56a shifts clamping chuck drive shaft 32a, snap die 102a and inserted tool 104a in strike direction 98a. This opens a torsionally fixed connection between first coupling means 52a and second coupling means 54a, so that impact-generation unit 50a is switched off.

(23) Hammer mechanism 22a has an impact-generation deactivation unit 118a including a blocking element 120a, a sliding block guide 122a, and operating element 28a. In a drilling or screwing mode, blocking element 120a exerts a force on snap die 102a, which acts on snap die 102 parallel to at least one force of clamping chuck drive shaft 32a. The force of blocking element 120a acts on snap die 102a via clamping chuck bearing 70a, via clamping chuck 24a, and via mounting ring 116a. The force of blocking element 120a prevents an axial displacement of snap die 102a and clamping chuck drive shaft 32a during a drilling and screwing mode, and thus prevents an activation of impact-generation unit 50a. The force of clamping chuck drive shaft 32a has a functionally parallel component which drives snap die 102a in rotating fashion during operation. In addition, the force has a functionally and directionally parallel component which is brought to bear on snap die 102a by spring 56a by way of clamping chuck drive shaft 32a.

(24) FIG. 4 shows a section that runs perpendicularly to the section of FIG. 2 and parallel to strike direction 98a, operating element 28a being disposed in two different positions in the sections of FIGS. 2 and 4. Operating element 28a is developed in the shape of a ring. It coaxially encloses the axis of rotation of clamping chuck drive shaft 32a. Operating element 28a is mounted so as to allow a rotation. It is connected to sliding block guide 122a in torsionally fixed manner. Sliding block guide 122a is likewise developed in the form of a ring. Sliding block guide 122a includes a bevel 124a. Bevel 124a joins two surfaces 126a, 128a of sliding block guide 122a. Surfaces 126a, 128a are aligned perpendicularly to strike direction 98a. Surfaces 126a, 128a are disposed on different planes in strike direction 98a.

(25) In an impact drilling mode, blocking element 120a is situated in a recess 130a, which, for one, is delimited by bevel 124a and one of surfaces 126a. This surface 126a is situated closer to drive motor 14a than the other surface 128a. Housing 12a includes a housing element 132a, which mounts the blocking element in torsionally fixed manner and allows it to be displaced in strike direction 98a. At the beginning of an impact-drilling operation, blocking element 120a, together with clamping chuck 24a, is therefore able to be pressed in a direction counter to strike direction 98a. Blocking element 120a does not exert any blocking force on clamping chuck 24a in an impact-drilling operation. When operating element 28a of impact-generation deactivation unit 118a is rotated, blocking element 120a is moved through bevel 124a in strike direction 98a. In the drilling or screwing mode, blocking element 120a is kept in this frontal position. Blocking element 120a thereby prevents axial shifting of clamping chuck drive shaft 32a in the drilling or screwing mode.

(26) FIGS. 5 through 11 show additional exemplary embodiments of the present invention. The following descriptions and the drawing are essentially limited to the differences between the exemplary embodiments. Regarding components that are designated in the same way, particularly regarding components provided with identical reference numerals, it is basically also possible to refer to the drawing and/or the description of the other exemplary embodiments, especially of FIGS. 1 through 4. In order to distinguish the exemplary embodiments, the letter a has been added after the reference numerals of the exemplary embodiment in FIGS. 1 through 4. In the exemplary embodiments of FIGS. 5 through 11, the letter a has been replaced by the letter b or by the letters b through e.

(27) FIG. 5 shows a portion of a hammer mechanism 22b. A hammer means 94b of an impact-generation unit 50b of hammer mechanism 22b is mounted in movable manner on a clamping chuck drive shaft 32b of hammer mechanism 22b. Clamping chuck drive shaft 32b is joined to a snap die 102b of hammer mechanism 22b in torsionally fixed and axially displaceable manner. Snap die 102b includes a coupling means 108b, which forms a torsionally fixed connection to a clamping chuck 24b of hammer mechanism 22b in at least one operating state. Coupling means 108b is situated on a side that is facing a tapered region 114b of clamping chuck 24b. Coupling means 108b is developed as teething. A sealing region 134b of the snap die is resting against clamping chuck 24b without teeth and advantageously prevents dust from entering impact-generation unit 50b.

(28) FIG. 6, like FIG. 5, schematically illustrates a portion of hammer mechanism 22c. A hammer means 94b of an impact-generation unit 50c of hammer mechanism 22c is mounted in movable manner on a clamping chuck drive shaft 32c of hammer mechanism 22c. Clamping chuck drive shaft 32c is joined to a snap die 102b of hammer mechanism 22c in torsionally fixed and axially displaceable manner. Snap die 102c includes a coupling means 108c, which forms a torsionally fixed connection to a clamping chuck 24c of hammer mechanism 22c in at least one operating state. Clamping chuck 24c has an inserted-tool coupling region 112c, in which coupling means 108c of snap die 102c engages at least partially. Inserted-tool coupling region 112c is provided to produce forces on an inserted tool in the peripheral direction during operation. In an operative state, coupling means 108c is at least partially disposed inside a tapered region 114c of clamping chuck 24c. Coupling means 108c is developed as an external hexagon. The dimensions of external hexagon correspond to the usual dimensions of a bit for screw-fitting operations. A sealing region 134c of the snap die 102c is resting against clamping chuck 24c without teeth and advantageously prevents dust from entering impact-generation unit 50b in a manner that is able to be produced in a cost-effective way. Especially fat loss is able to be minimized.

(29) FIGS. 7 through 10 show a portion of a hammer mechanism 22d, also as a section and in a perspective view. A hammer means 94d of an impact-generation unit 50d of hammer mechanism 22d is movably mounted on a clamping chuck drive shaft 32d of hammer mechanism 22d. Clamping chuck drive shaft 32d is joined to a snap die 102d of hammer mechanism 22d in torsionally fixed and axially displaceable manner. Snap die 102d has a coupling means 108d which forms a torsionally fixed connection to a clamping chuck 24d of hammer mechanism 22d in at least one operating state. In an operative state, coupling means 108d is at least partially disposed inside a tapered region 114d of clamping chuck 24d.

(30) Coupling means 108d is developed as teething with two coupling ribs that lie opposite each other in relation to the axis of rotation. Coupling means 108d has the same form and the same dimensions as a coupling means for coupling with an inserted tool. The form and the dimensions correspond to those of the SDS Quick standard. A sealing region 134d of snap die 102d is resting against clamping chuck 24d without teething.

(31) FIG. 11, like FIG. 5, schematically illustrates a portion of hammer mechanism 22e. A hammer means 94e of an impact-generation unit 50e of hammer mechanism 22e is mounted in movable manner on a clamping chuck drive shaft 32e of hammer mechanism 22e. Clamping chuck drive shaft 32e is joined to a snap die 102e of hammer mechanism 22e in torsionally and axially fixed manner. Clamping chuck drive shaft 32e and snap die 102e are developed in one piece. In a strike, hammer means 94e moves both clamping chuck drive shaft 32e and snap die 102e in strike direction 98e. By way of a coupling means 62e, clamping chuck drive shaft 32e is connected in axially displaceable and torsionally fixed manner to a planetary-gear stage described in the exemplary embodiment of FIGS. 1 through 4.