Hand-held power tool

Abstract

A hand-held power tool, in particular an impact drill driver, has a gearbox assemblage, a hammer impact mechanism, and a tool spindle. The hammer impact mechanism includes a striker that at least partly surrounds the tool spindle in at least one plane.

Claims

1. A hand-held power tool, comprising: a gearbox assemblage; a hammer impact mechanism; and a tool spindle including a tool mounting device; wherein the hammer impact mechanism includes a linearly moveable striker that at least partly surrounds the tool spindle in at least one plane, wherein in at least one operating state, the striker impacts the tool spindle linearly, wherein in at least one operating state, the striker impacts a transfer element of the tool spindle linearly, wherein the transfer element is arranged as a thickening of the tool spindle, wherein the hammer impact mechanism has a drive rotation element having a rotation axis that is disposed coaxially with at least a part of the tool spindle, wherein the drive rotation element is arranged as an impact mechanism shaft that encases at least a region of the tool spindle and transfers a rotary motion to the striker to generate an impact.

2. The hand-held power tool of claim 1, wherein the hammer impact mechanism includes a resilient lever element, supported pivotably around a pivot axis, which is to drive the striker of the hammer impact mechanism in at least one operating state.

3. The hand-held power tool of claim 1, wherein in at least one operating state, the striker is freely movable in a principal working direction.

4. The hand-held power tool of claim 1, wherein the tool spindle includes a rotary entrainment contour which is for creating an axially displaceable and nonrotatable connection along a rotation axis.

5. The hand-held power tool of claim 4, wherein the rotary entrainment contour is configured to create an axially displaceable and non-rotatable connection with at least one gear stage element of the gearbox assemblage along a rotation axis for pickoff of a rotation speed of the tool spindle in at least one operating state.

6. The hand-held power tool of claim 5, wherein the rotary entrainment contour is embodied as an external tooth set of the tool spindle and an internal tooth set of the at least one gear stage element.

7. The hand-held power tool of claim 5, wherein the at least one gear stage element is embodied as a planet carrier.

8. The hand-held power tool of claim 1, wherein the gearbox assemblage includes at least one sun gear that, in at least one operating state, is connected nonrotatably to at least a part of the hammer impact mechanism.

9. The hand-held power tool of claim 8, wherein the at least one sun gear is connected nonrotatably to a drive rotation element of the hammer impact mechanism.

10. The hand-held power tool of claim 1, further comprising: an electric motor and a battery connector unit for supplying the electric motor with energy.

11. The hand-held power tool of claim 1, wherein the hammer impact mechanism includes a releasable clutch apparatus to transfer a rotary motion.

12. The hand-held power tool of claim 11, wherein the clutch apparatus is to be closed by a force transferred via the tool spindle.

13. The hand-held power tool of claim 11, wherein an operating element by way of which the clutch apparatus can be actuated.

14. The hand-held power tool of claim 11, wherein the clutch apparatus is configured to releasably nonrotatably connect in at least one operating state a drive rotation element of the hammer impact mechanism and at least one gear stage element of the gearbox assemblage.

15. The hand-held power tool of claim 11, wherein the clutch apparatus includes a spring element configured to close the clutch apparatus when the tool spindle is loaded with a force in an axial direction.

16. The hand-held power tool of claim 1, wherein a torque setting unit has a clutch apparatus that is for limiting, in at least one operating state, a maximum torque transferred via the tool spindle.

17. The hand-held power tool of claim 1, wherein the gearbox assemblage has at least one gear stage element to split a power flow so as to make available different rotation speeds for an impact mode and a rotation mode.

18. The hand-held power tool of claim 17, wherein the at least one gear stage element is embodied as a planet carrier.

19. The hand-held power tool of claim 1, wherein the gearbox assemblage includes at least one ring gear that is supported axially movably.

20. The hand-held power tool of claim 1, wherein the gearbox assemblage includes at least one gear stage to increase a rotation speed for an impact drive.

21. The hand-held power tool of claim 1, wherein the hand-held power tool is an impact drill driver.

22. The hand-held power tool of claim 1, wherein the tool spindle and the impact mechanism shaft rotate, in at least one operating state, at a different angular speed.

23. The hand-held power tool of claim 1, wherein the striker has an impact surface that is oriented substantially perpendicular relative to the tool spindle and the transfer element has an impact surface that is oriented substantially perpendicular relative to the tool spindle.

24. The hand-held power tool of claim 1, wherein the gearbox assemblage is embodied as a planetary gearbox assemblage.

25. The hand-held power tool of claim 24, wherein the planetary gearbox assemblage includes at least one gear stage adapted to reduce rotation speed of the tool spindle and at least one gear stage adapted to increase a rotation speed of a drive rotation element of the hammer impact mechanism for an impact drive.

26. The hand-held power tool of claim 25, wherein the at least one gear stage adapted to increase the rotation speed of the drive rotation element includes at least one sun gear that, in at least one operating state, is connectable nonrotatably to the drive rotation element.

27. The hand-held power tool of claim 24, wherein the planetary gearbox assemblage includes at least one planetary gear stage element which is adapted to increase the rotation speed of a drive rotation element of the hammer impact mechanism for an impact drive.

28. The hand-held power tool of claim 27, wherein the at least one planetary gear stage element is embodied as a planet carrier.

29. The hand-held power tool of claim 28, wherein the at least one planetary gear stage element is embodied as a common planet carrier of two planet gear stages.

30. A hand-held power tool, comprising: a gearbox assemblage; a hammer impact mechanism; and a tool spindle including a tool mounting device; wherein the hammer impact mechanism includes a linearly moveable striker that at least partly surrounds the tool spindle in at least one plane, wherein in at least one operating state, the striker impacts the tool spindle linearly, wherein the tool spindle includes a rotary entrainment contour which is for creating an axially displaceable and nonrotatable connection along a rotation axis, wherein the rotary entrainment contour is configured to create an axially displaceable and non-rotatable connection with at least one gear stage element of the gearbox assemblage along a rotation axis for pickoff of a rotation speed of the tool spindle in at least one operating state.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 shows a hand-held power tool according to the present invention having a schematically depicted drivetrain.

(2) FIG. 2 shows a functional sketch of the drivetrain of FIG. 1 having an electric motor, a gearbox assemblage, and a hammer impact mechanism.

(3) FIG. 3 shows a schematic partial section through the hammer impact mechanism of the hand-held power tool of FIG. 1.

(4) FIG. 4 shows a section through the hammer impact mechanism of FIG. 3.

(5) FIG. 5 shows a perspective depiction of a lever element of the hammer impact mechanism of FIG. 3.

(6) FIG. 6 shows a functional sketch of an alternative exemplifying embodiment of the drivetrain of FIG. 1.

DETAILED DESCRIPTION

(7) FIG. 1 is a partly schematic depiction of a hand-held power tool 10a that is embodied as a cordless impact drill driver. Hand-held power tool 10a has a torque setting unit 12a, a gearbox assemblage 14a, a hammer impact mechanism 16a, a tool spindle 18a, a battery connector unit 20a, a pistol-shaped hand-held power tool housing 22a, and an electric motor 24a disposed in hand-held power tool housing 22a. In a front region 28a of hand-held power tool 10a, viewed oppositely to a principal working direction 26a of hand-held power tool 10a, hand-held power tool 10a has a tool mounting apparatus 30a that is embodied as a tool chuck. Mounted in tool mounting apparatus 30a is an inserted tool 32a that, during operation of hand-held power tool 10a, rotates around a rotation axis 34a of tool spindle 18a that extends parallel to principal working direction 26a. Rotation axis 34a is embodied as a principal rotation axis, i.e. multiple elements of hand-held power tool 10a are rotatable about said rotation axis 34a.

(8) An operating element 36a of torque setting unit 12a is disposed annularly around rotation axis 34a of tool spindle 18a, between hand-held power tool housing 22a and tool mounting apparatus 30a. Disposed on an upper side 38a, i.e. a side facing away from battery connector unit 20a, of hand-held power tool 10a is an operating element 40a that enables an operator (not further depicted) to change over between a drilling or screwing mode and a hammer drilling mode.

(9) Electric motor 24a is disposed in a rear region 42a, i.e. a region facing away from tool mounting apparatus 30a, of hand-held power tool housing 22a. A stator (not further depicted) of electric motor 24a is connected nonrotatably to hand-held power tool housing 22a. Gearbox assemblage 14a is disposed in a tubular upper region 44a, disposed axially with respect to rotation axis 34a, of the pistol-shaped hand-held power tool housing 22a. A lower region 46a of hand-held power tool housing 22a, which adjoins upper region 44a approximately at right angles, forms a handle 48a. Battery connector unit 20a is disposed at a lower end of lower region 46a. In a ready-to-operate state (as shown), a battery unit 50a is connected to battery connector unit 20a. During operation, battery unit 50a supplies electric motor 24a with energy.

(10) As FIGS. 2 and 3 show, hammer impact mechanism 16a has a drive rotation element 52a having a rotation axis 34a that is disposed coaxially with respect to tool spindle 18a. Drive rotation element 52a is embodied as an impact mechanism shaft 54a. Impact mechanism shaft 54a encases a region of tool spindle 18a that faces toward gearbox assemblage 14a. Rotation axis 34a of impact mechanism shaft 54a is oriented parallel to principal working direction 26a of hand-held power tool 10a. Tool spindle 18a connects tool mounting apparatus 30a to gearbox assemblage 14a along rotation axis 34a nonrotatably, and is embodied for the most part as a solid shaft.

(11) Hammer impact mechanism 16a is embodied as an eccentric impact mechanism that has an eccentric element 56a. As shown by the section (A-A) depicted in FIG. 4, eccentric element 56a has a rotation axis that coincides with rotation axis 34a of tool spindle 18a. Eccentric element 56a is constituted by a sleeve whose wall thickness 58a continuously increases and then decreases over a 360-degree circuit around rotation axis 34a. Eccentric element 56a is connected nonrotatably to impact mechanism shaft 54a, and is penetrated by the latter in an axial direction. Hammer impact mechanism 16a has an eccentric outer element 60a that is moved by eccentric element 56a during a hammer drilling mode. Eccentric outer element 60a is embodied as an approximately elliptical disk. It has a round orifice 62a that is disposed in a region 64a, facing away from handle 48a, of eccentric outer element 60a. Eccentric element 56a is supported in orifice 62a, movably relative to eccentric outer element 60a, by way of a bearing (not further depicted). Eccentric outer element 60a further has an aperture 80a that is disposed in a region, facing toward handle 48a, of eccentric outer element 60a. Aperture 80a is penetrated by a resilient lever element 66a. Lever element 66a prevents a rotation of eccentric outer element 60a in a circumferential direction relative to hand-held power tool housing 22a.

(12) Hammer impact mechanism 16a has a striker 68a. Lever element 66a drives striker 68a during a hammer drilling mode. Lever element 66a is embodied as a bracket, L-shaped in a side view, made of spring steel. As FIG. 5 shows, lever element 66a has a horseshoe-shaped region 70a that is penetrated by tool spindle 18a. Hammer impact mechanism 16a has a housing-mounted pivot shaft 72a around which lever element 66a is tiltable. Housing-mounted pivot shaft 72a is oriented perpendicular to rotation axis 34a of tool spindle 18a.

(13) FIGS. 2 and 3 further show that striker 68a of hammer impact mechanism 16a is freely movable in principal working direction 26a during a free-flight phase. The free-flight phase is a time period that begins with the end of an acceleration of striker 68a by lever element 66a, and ends immediately before an impact. Upon impact, striker 68a transfers an impact pulse to tool spindle 18a. For this, striker 68a impacts a transfer element 74a of tool spindle 18a. Transfer element 74a is embodied as a thickening of tool spindle 18a that has a surface 76a on the side facing toward striker 68a. Surface 76a is oriented parallel to an impact surface 78a of striker 68a. Striker 68a surrounds tool spindle 18a over 360 in planes that are oriented perpendicular to rotation axis 34a of tool spindle 18a. Striker 68a is guided on tool spindle 18a and is supported rotatably, with respect to hand-held power tool housing 22a, around rotation axis 34a of tool spindle 18a. Alternatively, the striker can also be guided at its outer contour and/or can be rotationally secured with respect to the hand-held power tool housing.

(14) Upon a rotation of eccentric element 56a, eccentric outer element 60a moves perpendicular to rotation axis 34a of tool spindle 18a. As a result of a motion of eccentric outer element 60a, an end 82a, disposed tiltably in aperture 80a of eccentric outer element 60a, of lever element 66a is moved, and lever element 66a is thereby tilted. Lever element 66a thereby accelerates striker 68a out of an initial position, facing toward gearbox assemblage 14a, in the direction of principal working direction 26a, by the fact that a driving end 84a of lever element 66a presses against a first bracing surface 86a of striker 68a. After acceleration, striker 68a moves in principal working direction 26a into the free-flight phase, in which driving end 84a of lever element 66a is disposed in a free region 88a of striker 68a and is thus decoupled from striker 68a in principal working direction 26a. At the end of this free-flight phase, striker 68a strikes transfer element 74a of tool spindle 18a and transfers its momentum to tool spindle 18a. Lever element 66a then moves striker 68a back into the initial position by the fact that driving end 84a of lever element 66a exerts a force on a second bracing surface 90a of striker 68a, said surface being disposed, with reference to first bracing surface 86a, on a different side of free region 88a. As a result of the resilient configuration of lever element 66a, smooth profiles are achieved for the forces that act between lever element 66a and striker 68a.

(15) Gearbox assemblage 14a has four gear stages, which are embodied as planet wheel gear stages 92a, 94a, 96a, 98a. The four planet wheel gear stages 92a, 94a, 96a, 98a are disposed behind one another along rotation axis 34a of tool spindle 18a. The four planet wheel 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 planet wheels 124a, 126a, 128a, 130a, only two of which are depicted in each case. Planet wheels 124a of first planet wheel gear stage 92a mesh with sun gear 108a of first planet wheel gear stage 92a and with ring gear 100a of first planet wheel gear stage 92a, and are supported rotatably on planet carrier 116a of first planet wheel gear stage 92a. Planet carrier 116a of first planet wheel gear stage 92a guides planet wheels 124a of first planet wheel gear stage 92a on a circular path around rotation axis 34a of tool spindle 18a. Second planet wheel gear stage 94a, third planet wheel gear stage 96a, and fourth planet wheel gear stage 98a are constructed correspondingly thereto.

(16) Sun gear 108a of first planet wheel gear stage 92a is connected nonrotatably to electric motor 24a and is disposed next to electric motor 24a in principal working direction 26a, between tool mounting apparatus 30a and electric motor 24a. Ring gear 100a of first planet wheel gear stage 92a is connected nonrotatably to hand-held power tool housing 22a. Planet carrier 116a of first planet wheel gear stage 92a is connected nonrotatably to sun gear 110a of second planet wheel gear stage 94a, ring gear 102a of which is likewise connected to hand-held power tool housing 22a. Planet carrier 118a of second planet wheel gear stage 94a is connected nonrotatably to sun gear 112a of third planet wheel gear stage 96a. Ring gear 104a of third planet wheel gear stage 96a is likewise connected nonrotatably to hand-held power tool housing 22a during a drilling, screwdriving, or hammer drilling procedure. The first, the second, and the third planet wheel gear stage 92a, 94a, 96a thus each bring about a gear reduction in the direction of tool mounting apparatus 30a. A gear reduction thus likewise occurs between sun gear 108a of first planet wheel gear stage 92a and planet carrier 120a of third planet wheel gear stage 96a. A ratio of this gear reduction between a rotation speed of electric motor 24a and a rotation speed of tool spindle 18a is equal to approximately 60:1.

(17) In addition, one skilled in the art is familiar with possibilities for switching to an alternative conversion ratio between a rotation speed of electric motor 24a and a rotation speed of tool spindle 18a. For example, ring gear 102a of second planet wheel gear stage 94a can be nonrotatably connectable, alternatively to hand-held power tool housing 22a, to planet carrier 116a of first planet wheel gear stage 92a by way of a clutch apparatus (not further depicted). The alternative conversion ratio between the rotation speed of a motor speed and the rotation speed of tool spindle 18a is equal to approximately 15:1.

(18) Gearbox assemblage 14a has a gear stage element 132a that splits a power flow. Gear stage element 132a is embodied as a common planet carrier 120a, 122a of the third and the fourth planet wheel gear stage 96a, 98a. Tool spindle 18a has a rotary entrainment contour 134a that creates, along rotation axis 34a, an axially displaceable and nonrotatable connection to gearbox assemblage 14a, more precisely to gear stage element 132a. A pickoff of a rotation speed of tool spindle 18a accordingly occurs at planet wheel 120a of third planet wheel gear stage 96a.

(19) In this example, rotary entrainment contour 134a is embodied as an internal tooth set 136a of gear stage element 132a and an external tooth set 138a of tool spindle 18a. Alternatively, pickoff could occur at the ring gear of third planet wheel gear stage 96a.

(20) Alternatively or in addition to rotary entrainment contour 134a shown in FIG. 2 and previously described, a rotary entrainment contour 140a can, as shown in FIG. 3, divide tool spindle 18a axially into two parts 142a, 144a. The one part 142a of tool spindle 18a is connected directly to gearbox assemblage 14a. The other part 144a of tool spindle 18a is connected directly to tool mounting apparatus 30a. The previously described rotary entrainment contour 134a can be omitted. Part 142a of tool spindle 18a that is connected directly to gearbox assemblage 14a can then be connected fixedly in an axial direction to gear stage element 132a. As a result, a mass of the axially movable part 144a of tool spindle 18a can be reduced.

(21) Sun gear 114a of fourth planet wheel gear stage 98a is connected, during a hammer drilling mode, nonrotatably to drive rotation element 52a. Sun gear 114a of fourth planet wheel gear stage 98a is thus, in the context of a hammer drilling procedure, connected nonrotatably to eccentric element 56a of hammer impact mechanism 16a. Alternatively, ring gear 106a of fourth planet wheel gear stage 98a could also be connected nonrotatably to drive rotation element 52a.

(22) Ring gear 106a of fourth planet wheel gear stage 98a is supported axially movably. Gearbox assemblage 14a has a coupling element 146a that connects ring gear 106a of fourth planet wheel gear stage 98a nonrotatably and axially displaceably to hand-held power tool housing 22a. As a result of this disposition, gearbox assemblage 14amore precisely fourth planet wheel gear stage 98agenerates from the two power flows of the common planet carrier 120a, 122a of the third and the fourth planet wheel gear stage 96a, 98a, during a hammer drilling mode, output rotary motions that have a non-integer ratio to one another. In addition, fourth planet wheel gear stage 98a increases a rotation speed for an impact drive, i.e. a rotation speed of impact mechanism shaft 54a or of drive rotation element 52a is higher than a rotation speed of tool spindle 18a. Gearbox assemblage 14amore precisely gear stage element 132athus makes available different rotation speeds for an impact drive and a rotary drive.

(23) Hand-held power tool 10a has a first releasable clutch apparatus 148a that transfers a rotary motion during a hammer drilling mode. First clutch apparatus 148a is embodied as a claw clutch, and remains closed in the context of an axial motion of tool spindle 18a caused by an impact. In a hammer drilling mode, first clutch apparatus 148a connects hammer impact mechanism 16a to sun gear 114a of fourth planet wheel gear stage 98a.

(24) First clutch apparatus 148a furthermore has a spring element 150a that is embodied as a spiral spring. Spring element 150a opens first clutch apparatus 148a when tool spindle 18a is unloaded oppositely to principal working direction 26a. In this case hammer impact mechanism 16a is deactivated. First clutch apparatus 148a is closed during a hammer drill mode by a force transferred via tool spindle 18a in an axial direction and proceeding from inserted tool 32a. When tool spindle 18a is loaded with a force, as a result of a force generated by the operator onto a workpiece (not further depicted) via an inserted tool 32a mounted in tool mounting apparatus 30a, spring element 150a is compressed and first clutch apparatus 148a is closed. The force is applied in an axial direction in the context of a hammer drilling mode, via a shaped element 152a that is connected to tool spindle 18a, onto impact mechanism shaft 54a and thus onto first clutch apparatus 148a.

(25) In addition, hand-held power tool 10a has operating element 40a with which the operator can actuate first clutch apparatus 148a by uninterruptedly opening first clutch apparatus 148a. Hammer impact mechanism 16a is thus deactivated in this operating state. This operating element 40a thus enables a manual changeover between a drilling or screwdriving mode and a hammer drilling mode, and drilling and screwdriving can be performed with hand-held power tool 10a without an impact pulse. Operating element 40a is embodied as a slide switch.

(26) Torque setting unit 12a has a clutch apparatus 154a that limits a transferable torque. A maximum torque is settable by way of torque setting unit 12a. This further, second clutch apparatus 154a is disposed between ring gear 104a of third planet wheel gear stage 96a and ring gear 106a of fourth planet wheel gear stage 98a. Second clutch apparatus 154a opens automatically at a settable maximum torque that acts on tool spindle 18a. When second clutch apparatus 154a is open, ring gear 104a of third planet wheel gear stage 96a is axially secured and rotationally movable. Second clutch apparatus 154a is embodied as an overload clutch, known to one skilled in the art, the response torque of which is modifiable by way of an axial force on second clutch apparatus 154a. For example, second clutch apparatus 154a is embodied as a shaped-element clutch having oblique surfaces, or as a friction clutch. Alternatively, ring gear 106a of fourth planet wheel gear stage 98a serves as a shaped element, by the fact that it meshes simultaneously with planet wheels 128a, 130a of third planet wheel gear stage 96a and of fourth planet wheel gear stage 98a and, when the maximum torque is exceeded, becomes displaced in principal working direction 26a and releases planet wheels 128a of third planet wheel gear stage 96a. For this purpose, ring gear 106a of fourth planet wheel gear stage 98a may be embodied to be wider than planet wheels 128a, 130a of the third and/or the fourth planet wheel gear stage 96a, 98a.

(27) Hand-held power tool 10a has a spring element 156a that, during a working procedure, exerts a force on the axially movable ring gear 106a of fourth planet wheel gear stage 98a and thus on second clutch apparatus 154a, and thus closes second clutch apparatus 154a. By way of operating element 36a of torque setting unit 12a, second clutch apparatus 154a can be shifted by the operator, i.e. a force on the axially movable ring gear 106a can be set. This is done by way of an axial motion of a contact point 158a of spring element 156a. When the maximum torque of tool spindle 18a is exceeded and clutch apparatus 154a is not uninterruptedly closed manually, second clutch apparatus 154a produces a counterforce and compresses spring element 156a, and clutch apparatus 154a opens. Operating element 36a of torque setting unit 12a is embodied as a ring rotatable by the operator.

(28) Operating element 36a further has a shaped element (not further depicted) which is provided in order to manually close second clutch apparatus 154a uninterruptedly. This is done by way of a corresponding setting, by the operator, of operating element 36a. Opening of second clutch apparatus 154a in the context of a drilling mode can thereby be prevented at all torques that are transferred via tool spindle 18a and do not exceed a safety torque.

(29) Gearbox assemblage 14a has two bearing elements 160a, 162a that radially support tool spindle 18a. First bearing element 160a is disposed on the side of tool spindle 18a facing toward tool mounting apparatus 30a. First bearing element 160a is connected axially fixedly to tool spindle 18a, and is supported axially displaceably in hand-held power tool housing 22a. Alternatively, the first bearing element can also be connected axially fixedly to the hand-held power tool housing, and supported axially displaceably on the tool spindle. Disposed on the side of tool spindle 18a facing away from tool mounting apparatus 30a is second bearing element 162a, which supports tool spindle 18a inside sun gear 114a of fourth planet wheel gear stage 98a. Alternatively, tool spindle 18a can be supported by way of the common planet carrier 120a, 122a of the third and the fourth planet wheel gear stage 96a, 98a.

(30) FIG. 6 shows a further exemplifying embodiment of the present invention. To differentiate the exemplifying embodiments, the letter a in the reference characters of the exemplifying embodiment in FIGS. 1 to 5 is replaced by letters b in the reference characters of the exemplifying embodiment in FIG. 6. The description that follows is limited substantially to the differences with regard to the exemplifying embodiment in FIGS. 1 to 5; reference may be made to the description of the exemplifying embodiment in FIGS. 1 to 5 with regard to components, features and functions that remain the same. In particular, different dispositions and combinations of the above-described clutch apparatus are conceivable.

(31) FIG. 6, like FIG. 2, shows in particular a torque setting unit 12b, a gearbox assemblage 14b, a hammer impact mechanism 16b, and a tool spindle 18b.

(32) Torque setting unit 12b has latching elements 164b that are embodied as balls. Latching elements 164b are supported in shaped elements (not further depicted) and are disposed between a ring gear 104b of a third planet wheel gear stage 96b and a hand-held power tool housing 22b. Latching elements 164b are spring-loaded radially to a rotation axis 34b of tool spindle 18b, by a spring element 156b of torque setting unit 12b, with a force that is settable by the operator. If a torque transferred via tool spindle 18b exceeds a set maximum torque, latching elements 164b push the shaped elements apart against a force of spring element 156b. Ring gear 104b of third planet wheel gear stage 96b thus rotates relative to hand-held power tool housing 22b, and tool spindle 18b transfers no torque at that time.

(33) Ring gear 104b of third planet wheel gear stage 96b and a ring gear 106b of a fourth planet wheel gear stage 98b are nonrotatably connected to one another by way of a clutch apparatus 148b. When clutch apparatus 148b is opened, ring gear 106b of fourth planet wheel gear stage 98b is freely rotatable around rotation axis 34b, and hammer impact mechanism 16b is thus disengaged for a drilling and screwdriving mode.

(34) Clutch apparatus 148b is closed by way of two shaped elements 152b, 168b. First shaped element 152b transfers a force in an axial direction from tool spindle 18b onto an impact mechanism shaft 54b. This shaped element 152b is axially mechanically connected fixedly to tool spindle 18b.

(35) Second shaped element 166b is connected in an axial direction to impact mechanism shaft 54b. Said element transfers force in an axial direction via a bearing 168b to ring gear 106b of fourth planet wheel gear stage 98b. The force closes clutch apparatus 148b in the context of a drilling and screwdriving mode. Alternatively, a transfer of force via fourth planet wheel gear stage 98b is possible. Clutch apparatus 148b is opened by a spring element 150b that applies axial force, directed onto a tool mounting apparatus 30b, onto impact mechanism shaft 54b via a bearing 170b.