Hand tool device

Abstract

Hand tool device with a percussion mechanism (22a; 22b; 22c) comprising a beater (44a) and a beater drive device (50a) designed to drive the beater (44a) at least in the direction of impact (54a) during a first direction of drill rotation, wherein the percussion mechanism (22a; 22b; 22c) comprises a percussion shut-off device (24a; 24b; 24c) designed to prevent the beater drive device (50a) from being driven during a second direction of drill rotation, characterized in that the percussion shut-off device (24a; 24b; 24c) is designed to automatically prevent the beater drive device (50a) from being driven during a counterclockwise direction of drill rotation, wherein the percussion shut-off device (24a; 24b; 24c) comprises a locking means (124a) that allows free rotation in at least one operating state.

Description

State of the art

[0001] In EP 1 690 642 A1, a hand tool device with a striking mechanism comprising a beater and a beater drive device, designed to drive the beater at least in the direction of impact during a first drilling rotation direction, has already been proposed.

[0002] DE 10 2004 018 084 B3 discloses a hammer drill comprising a tool spindle that can be driven in a clockwise and a counterclockwise direction, a single handle for setting a device function from pure drilling operation, pure hammer operation and hammer drill operation, and a switching device adjustable by the handle.

[0003] DE 28 20 125 A1 describes a hand-held machine tool with an electric drive motor by means of which a rotary sleeve with a tool holder actuated by it, in which a tool can be guided, can be driven rotaryally via a gearbox.

[0004] DE 100 37 808 A1 describes a hand-held machine tool with a tool holder that can be driven at least in a rotating manner via a drive motor and a drill spindle.

[0005] DE 199 44 294 A1 describes a rotary hammer with a tool insert attached to a front end of the rotary hammer, with a motor for driving the tool insert and with a switchable rotary transmission mechanism.

[0006] From EP 1 714 745 A2 a rotating power tool is known, having an operating mode selection mechanism for selecting between a striking operation and a drilling operation. Disclosure of the invention

[0007] The invention relates to a hand tool device with a striking mechanism comprising a beater and a beater drive device, which is designed to drive the beater at least in the direction of striking during a first drilling rotation direction.

[0008] It is proposed that the percussion mechanism include a percussion cut-off device designed to prevent the hammer drive mechanism from being driven, particularly independently, during a second direction of drill rotation. The term "percussion mechanism" is understood to mean, in particular, a device designed to generate a percussive impulse and, in particular, to transmit it in the direction of a tool. Preferably, the percussion mechanism transmits the percussive movement, at least during percussion drilling, advantageously via a tool spindle and / or, in particular, via a tool chuck of the hand tool attachment to the tool. The term "hammer" is understood to mean, in particular, a means that, at least during percussion drilling, is accelerated, especially translationally, and transmits an impulse received during acceleration as a percussive impulse in the direction of the tool.The term "hammer drive device" is understood to mean, in particular, a unit designed to convert a rotational movement into a percussive movement, especially a translational one. Preferably, the hammer drive device comprises an eccentric drive, a wobble bearing, and / or, more preferably, a cam guide. Specifically, "driving the hammer drive device" is understood to mean a process in which energy, provided in particular by a drive unit of the hand-held power tool, is mechanically transferred to the hammer drive device. Specifically, "drilling rotation direction" is understood to mean a direction of rotation in which the tool chuck is driven to rotate relative to a hand-held power tool housing, at least during one operation.Preferably, the hand tool device is designed to drive the insert tool with a counterclockwise drilling rotation direction and with a clockwise drilling rotation direction, at least in one drilling operation and / or advantageously at least in one screwdriving operation. A "stroke direction" is understood to be, in particular, a direction that runs parallel to an axis of rotation of the tool chuck and that is directed from the striker towards the tool chuck. In particular, a "stroke cut-off device" is understood to be a device that prevents at least one drive of the striker drive device in at least one operating state. Preferably, the stroke cut-off device prevents the drive of the striker drive device during operation in which the tool chuck is driven in the second drilling rotation direction.Alternatively or additionally, the impact cut-off device could prevent switching to impact drilling mode when the second drilling rotation direction is selected and / or prevent switching to the second drilling rotation direction when impact drilling mode is selected. "Provided for" is understood to mean specifically programmed, designed, and / or equipped. Specifically, "independent" is understood to mean that the impact cut-off device prevents and / or, in particular, shuts off the drive mechanism of the impact drive device in the second drilling rotation direction, at least independently of operator intervention. In this context, "prevent" is understood to mean that the impact cut-off device excludes simultaneous activation of the impact cut-off device and a drive in the second drilling rotation direction.The inventive design of the hand tool device allows for a particularly small, lightweight yet powerful impact mechanism to be provided and prevents damage to the impact mechanism from improper operation.

[0009] In a further embodiment, it is proposed that the hand tool device has a planetary gear stage, in particular a first stage, which drives the beater drive device in at least one operating state, thereby enabling a compact design. A "planetary gear stage" is understood to mean, in particular, a gear stage that has at least one planet gear connected to a planet carrier, which is coupled radially outwards to a ring gear and radially inwards to a sun gear.

[0010] Furthermore, it is proposed that the impact cut-off device act on a ring gear of the planetary gear stage, thus enabling particularly simple assembly and a short overall length in the impact direction. A "ring gear" is understood to be, in particular, a ring-shaped gear with internal teeth.

[0011] Furthermore, it is proposed that the impact cut-off device act on a planet carrier of the planetary gear stage, thereby achieving a particularly slim design. Specifically, a "planet carrier" is understood to be a component of a planetary gear stage that guides a planet gear rotatably on a circular path.

[0012] Furthermore, it is proposed that the striking mechanism shut-off device acts on a striking mechanism spindle, thereby enabling a particularly slim design. A "striking mechanism spindle" is understood to be, in particular, a shaft that transmits a rotational motion from the planetary gear stage to the striking mechanism. Preferably, the striking mechanism spindle is designed as a hollow shaft.

[0013] Furthermore, it is proposed that the impact cut-off device be designed to automatically prevent the hammer drive mechanism from operating in a counterclockwise direction of drill rotation. This would allow for advantageous operation of a standardized impact drill bit in a clockwise direction of drill rotation. Specifically, "counterclockwise drill rotation" is defined as a rotation of the tool chuck in which, viewed from the impact direction, the chuck rotates counterclockwise. Conversely, "clockwise drill rotation" is defined as a rotation of the tool chuck in which, viewed from the impact direction, the chuck rotates clockwise.

[0014] In an advantageous embodiment of the invention, it is proposed that the impact shut-off device be designed to shut off the impact drive device, particularly automatically, during a second drilling rotation direction. This allows the operator to conveniently switch from a clockwise to a counterclockwise drilling rotation direction without deactivating an impact drilling mode. Specifically, the term "shut-off" is understood to mean that the impact shut-off device interrupts the drive of the impact drive device, particularly automatically, during a drive of the tool chuck in the second drilling rotation direction.

[0015] In a further embodiment, it is proposed that the impact shut-off device includes a locking element that allows freewheeling in at least one operating state, thereby achieving a simple and advantageous shut-off in the counterclockwise direction of drill rotation. A "locking element" is understood to mean, in particular, any means that would appear suitable to a person skilled in the art, preferably at least a clamping roller, a clamping element, a pawl, a toothed disc, and / or a coil spring. Specifically, the term "freewheeling element" is understood to mean that, in one direction of rotation of a component, for example, the ring gear, the locking element allows rotation of the component relative to another component, for example, the hand tool housing, and prevents rotation of the component relative to the other component in a different direction of rotation.

[0016] Furthermore, it is proposed that the striker drive device has a cam guide that drives the striker, at least during impact drilling operation, thus providing a particularly small, lightweight, yet powerful striking mechanism. In particular, a wobble bearing or rocker arm can be advantageously omitted. Specifically, a "cam guide" is understood to be a device that converts rotational energy for striking into linear kinetic energy of the striker, at least by means of a specially shaped guide surface along which a connecting element runs, at least during impact drilling operation. Preferably, the striking mechanism has a striking spring that stores the linear kinetic energy of the striker for striking. Preferably, the specially shaped surface is a surface that defines a guide curve of the cam guide.In this context, "propelling" should be understood in particular as the curve transferring energy to the racket for generating a hit.

[0017] Furthermore, it is proposed that the cam guide incorporate an impact relief zone, thereby achieving high impact energy and advantageously low wear with a short overall length. An "impact relief zone" is understood to be, in particular, a section of the cam guide's cam where the connecting element is located when the impact spring accelerates the striker in the direction of impact. Preferably, the impact relief zone is wide enough to allow the connecting element to traverse it along different paths. Preferably, the impact relief zone exerts no force on the striker, at least during impact drilling operation.

[0018] Furthermore, the invention relates to a hand tool with a hand tool device according to the invention. Preferably, the hand tool is designed to drive the insert tool in a screw mode, in a drill mode, in a screw-drill mode, and particularly in a chisel mode. drawing

[0019] Further advantages become apparent from the following description of the drawings. The drawings illustrate five exemplary embodiments of the invention. The drawings, the description, and the claims contain numerous features in combination. A person skilled in the art will expediently consider the features individually and combine them into meaningful further combinations.

[0020] They show: Fig. 1 a cut of a hand tool with a hand tool device according to the invention, Fig. 2 a partially isolated section through a percussion mechanism and a planetary gear of the hand tool device Fig. 1, Fig. 3 a first cutting surface A of the impact mechanism of the hand tool device made of Fig. 1, Fig. 4 a second cutting surface B of the impact mechanism of the hand tool device made of Fig. 1, Fig. 5 a perspective view of a striking mechanism spindle of the striking mechanism of the hand tool device from Fig. 1, Fig. 6 a perspective view of a beater of the striking mechanism of the hand tool device made of Fig. 1, Fig. 7 a cross-sectional area C of a first planetary gear stage and a first impact cut-off device of the hand tool device Fig. 1, Fig. 8 a cross-sectional area D of a control element and a second impact shut-off device of the hand tool device Fig. 1, Fig. 9 a perspective sectional view of part of the hand tool device made of Fig. 1, Fig. 10 a cutting surface E of a spindle locking device of the hand tool device made of Fig. 1, Fig. 11 a cross-sectional area F through blocking means of the spindle blocking device of the hand tool device Fig. 1, Fig. 12 a cutting surface G of a second planetary gear stage of the hand tool device made of Fig. 1, Fig. 13 a cutting surface H of a third planetary gear stage of the hand tool device made of Fig. 1, Fig. 14 a cross-sectional surface I of a fourth planetary gear stage of the hand tool device made of Fig. 1, Fig. 15 a schematic representation of an operating device and a protective device of the hand tool device made of Fig. 1 , Fig. 16 an alternative embodiment of a first impact shut-off device of a hand tool device according to the invention, Fig. 17 a further embodiment of a first impact shut-off device of a hand tool device according to the invention, Fig. 18 an alternative embodiment of an impact switching spring of a hand tool device according to the invention and Fig. 19 an alternative embodiment of an operating device and a protective device of a hand tool device according to the invention. Description of the exemplary implementations

[0021] Fig. Figure 1 shows a hand tool 10a. The hand tool 10a is designed as an impact drill / driver. The hand tool 10a comprises a hand tool device 12a according to the invention, a hand tool housing 14a, and a battery interface 16a. The battery interface 16a is designed to supply the hand tool device 12a with electrical energy from a hand tool battery (not shown in detail here). The hand tool housing 14a is pistol-shaped. The hand tool housing 14a is multi-part. It includes a handle 18a, by means of which an operator holds the hand tool 10a during a work operation. The hand tool device 12a comprises a tool guidance unit 20a, an impact mechanism 22a, a first impact shut-off device 24a, a second impact shut-off device 26a, a planetary gear 28a, a drive unit 30a, an operating device 32a, and a torque limiting unit 34a.

[0022] The tool guidance unit 20a comprises a tool chuck 36a and a tool spindle 38a. During a machining operation, the tool chuck 36a secures an insert tool (not shown), for example, a drill bit or a screwdriver bit. The tool chuck 36a secures the insert tool by friction. The tool chuck 36a has three clamping jaws that can be moved by an operator and which secure the insert tool during a machining operation. Furthermore, the tool chuck 36a secures the insert tool axially immovably relative to the tool chuck 36a and, in particular, the tool spindle 38a during a machining operation. A portion of the tool chuck 36a and the tool spindle 38a are connected to each other in a way that prevents movement relative to one another. Here, the tool chuck 36a and the tool spindle 38a are bolted together. The hand tool device 12a has a bearing means 40a which supports the tool spindle 38a on a side facing the tool chuck 36a.The bearing element 40a supports the tool spindle 38a so that it is axially displaceable. The bearing element 40a is axially fixed to the tool spindle 38a. The bearing element 40a is axially movable within the hand tool housing 14a. The hand tool device 12a has a further bearing element 41a, which supports the tool spindle 38a on a side facing the planetary gear 28a. The bearing element 41a is designed as a rolling bearing, in this case a needle bearing, which allows for low-backlash mounting. The bearing element 41a supports the tool spindle 38a so that it is axially displaceable. The bearing element 41a surrounds a percussion spindle 46a. The bearing element 41a is operatively located between the tool spindle 38a and the percussion spindle 46a.

[0023] The tool spindle 38a includes a striking surface 42a, against which a striker 44a of the impact mechanism 22a strikes during impact drilling operation. The striker 44a has a mass that is at most two-thirds the mass of the tool guide unit 20a. Here, the mass of the striker 44a is less than half the mass of the tool guide unit 20a. The mass of the striker 44a is approximately 45% of the mass of the tool guide unit 20a.

[0024] In the Fig. Figure 2 shows the striking mechanism 22a and the planetary gear 28a in more detail. The striking mechanism 22a comprises the striker 44a, the striking spindle 46a, a striking spring 48a, a striker drive device 50a, and a striker guide 52a. The striker 44a is mounted so that it can move translationally in the striking direction 54a. The striking direction 54a is aligned parallel to an axial direction of the striking spindle 46a.

[0025] The Fig. 3 and Fig. Figure 4 shows a cross-sectional surface A and a cross-sectional surface B of the striking mechanism 22a. The striker guide 52a mounts the striker 44a relative to the hand tool housing 14a in a rotationally fixed manner. The striker guide 52a has three guide rods 56a on which the striker 44a slides. The guide rods 56a are arranged regularly around the striker 44a. The striker 44a has sliding surfaces 58a that enclose the guide rods 56a by 180 degrees on a plane perpendicular to the striking direction 54a. The striker 44a encloses the striking mechanism spindle 46a by 360 degrees on a plane oriented perpendicular to the striking direction 54a. Furthermore, the striker 44a encloses the tool spindle 38a by 360 degrees on this plane. Additionally, the striking mechanism spindle 46a encloses the tool spindle 38a by 360 degrees on this plane. The impact spindle 46a is arranged coaxially to the tool spindle 38a.

[0026] The striking spring 48a accelerates the striker 44a in the direction of impact 54a before striking. For this purpose, the tool housing 14a supports the striking spring 48a on a side facing away from the striker 44a. The striking spring 48a presses directly against the striker 44a. The striker 44a has a spring mounting 60a. The spring mounting 60a is designed as an annular recess. Fig. Figure 5 shows the percussion spindle 46a in a perspective view. Fig. Figure 6 shows the striker 44a in a perspective view. The striker drive device 50a has a first cam guide 62a and a second first cam guide 64a. The cam guides 62a, 64a each comprise a guide cam 66a, 68a and a connecting element 70a, 72a. The connecting elements 70a, 72a are spherical. The striker 44a mounts the connecting elements 70a, 72a in a fixed position relative to the striker 44a. The striker 44a has hemispherical mounting recesses 74a. During impact drilling, the connecting elements 70a, 72a slide in the guide cam 66a, 68a. The impact spindle 46a has a portion of the cam guides 62a, 64a, namely the guide cam 66a, 68a. The impact spindle 46a defines a space in which the connecting elements 70a, 72a move during impact drilling operation.

[0027] The impact spindle 46a is designed as a hollow shaft. The planetary gear 28a drives the impact spindle 46a. For this purpose, the impact spindle 46a has a toothed section 76a on the side facing away from the tool chuck 36a. The guide cams 66a and 68a each have an impact freewheeling section 78a and 80a, an impact winding section 82a and 84a, and a mounting recess 86a and 88a. During assembly, the connecting elements 70a and 72a are inserted through the mounting recesses 86a and 88a into the mounting recesses 74a of the hammer 44a. During impact drilling, the impact spindle 46a rotates clockwise in the impact direction 54a. The impact winding sections 82a and 84a are spirally shaped. They extend 180 degrees around a rotational axis 90a of the impact spindle 46a. The impact winding sections 82a, 84a move the connecting elements 70a, 72a and thus the hammer 44a in the impact drilling operation against the impact direction 54a.Thus, the striking mechanism 22a has the connecting means 70a, 72a which, in at least one operating state, transmit a movement from the striking mechanism spindle 46a to the beater 44a.

[0028] The impact relief sections 78a, 80a each connect two ends 92a, 94a, 96a, 98a of the impact winding sections 82a, 84a. The impact relief sections 78a, 80a extend 180 degrees around a rotation axis 90a of the impact spindle 46a. The impact relief sections 78a, 80a each have an impact flank 100a, 102a which, starting from an end 94a, 96a of the impact winding section 82a facing the planetary gear 28a, runs approximately parallel to the impact direction 54a. After the connecting elements 70a, 72a enter the striking free-running areas 78a, 80a, the striking spring 48a accelerates the beater 44a and the connecting elements 70a, 72a in the striking direction 54a. During this movement, the connecting elements 70a, 72a pass through the striking free-running areas 78a, 80a without experiencing an axial force until the beater 44a strikes the striking surface 42a. The cam guides 62a, 64a are arranged offset by 180 degrees around the axis of rotation 90a.The curve guides 62a, 64a are arranged one behind the other in the axial direction.

[0029] The planetary gear 28a has the first planetary gear stage 104a, a second planetary gear stage 106a, a third planetary gear stage 108a and a fourth planetary gear stage 110a. Fig. Figure 7 shows a cross-sectional area C of the first planetary gear stage 104a. The in the Fig. 7, Fig. 12, Fig. 13 and Fig. The 15 planetary gear stages 104a, 106a, 108a, 110a depicted have gears with a number of teeth that would be considered reasonable by a person skilled in the art. The gears of the planetary gear stages 104a, 106a, 108a, 110a mesh with each other, although this is not always shown in the illustration. The first planetary gear stage 104a increases the initial rotational speed of the second planetary gear stage 106a to drive the impact mechanism 22a. The second planetary gear stage 106a drives the tool spindle 38a with this initial rotational speed. The toothing 76a of the impact mechanism spindle 46a forms a sun gear of the first planetary gear stage 104a. The toothing 76a meshes with planet gears 112a of the first planetary gear stage 104a, which are guided by a planet carrier 114a of the first planetary gear stage 104a. A ring gear 116a of the first planetary gear stage 104a meshes with the planet gears 112a of the first planetary gear stage 104a.

[0030] The first impact shut-off device 24a fixes the ring gear 116a of the first planetary gear stage 104a immovably relative to the hand tool housing 14a during impact drilling operation. The first impact shut-off device 24a is designed to engage the hammer drive device 50a during a first, clockwise drilling rotation and to automatically disengage the hammer drive device 50a during a second, counterclockwise drilling rotation. The first impact shut-off device 24a acts on the ring gear 116a of the first planetary gear stage 104a. The first impact shut-off device 24a blocks the ring gear 116a of the first planetary gear stage 104a during the first, clockwise drilling rotation. The first impact shut-off device 24a releases the ring gear 116a of the first planetary gear stage 104a during the second, counterclockwise drilling rotation, allowing it to rotate.The first impact shut-off device 24a has three clamping mechanisms 122a. Each clamping mechanism 122a comprises a locking element 124a, a first clamping surface 126a, a second clamping surface 128a, and free-running surfaces 130a. The locking element 124a is designed as a roller. The first clamping surface 126a forms an outer area of ​​a surface of the ring gear 116a of the first planetary gear stage 104a. The second clamping surface 128a is fixed relative to the hand tool housing 14a. During operation in the first, clockwise direction of drill rotation, the locking elements 124a clamp between the first clamping surfaces 126a and the second clamping surface 128a. During operation in the second, counterclockwise direction of drill rotation, the free-running surfaces 130a guide the locking elements 124a and prevent jamming.

[0031] Furthermore, the Fig. 7 A connecting element 118a that connects the tool spindle 38a and a planet carrier 120a of the second planetary gear stage 106a in a rotationally fixed manner. The connecting element 118a connects the tool spindle 38a and the planet carrier 120a of the second planetary gear stage 106a in an axially displaceable manner in this case.

[0032] Furthermore, the Fig. 3, Fig. 4 and Fig. 7 three first transmission means 132a of the second shock-stop device 26a. The transmission means 132a are designed as rods. Fig. Figure 8 shows a cross-sectional area D through a control element 134a of the hand tool device 12a. Fig. Figure 9 shows the second impact shut-off device 26a in a perspective sectional view. The control element 134a supports the tool guidance unit 20a in a position within the Fig. 1, Fig. 8 and Fig. 9, shown screw mode and in a drilling mode in a direction opposite to the impact direction 54a. A force applied to the tool guide unit 20a acts via the bearing means 40a, a second transmission means 136a of the second impact shut-off device 26a and the first transmission means 132a on support surfaces 138a of the control element 134a. The control element 134a has three recesses 140a. In a Fig. In the 2 shown impact drilling mode, the first transmission means 132a can be inserted into the recesses 140a, making the tool guide unit 20a axially movable.

[0033] The second impact cut-off device 26a has an impact cut-off clutch 142a. The impact cut-off clutch 142a is partially formed integrally with the planetary gear 28a. The impact cut-off clutch 142a is arranged between the first planetary gear stage 104a and the second planetary gear stage 106a. The impact cut-off clutch 142a has a first clutch element 144a, which is rotationally fixed to a planet carrier 114a of the first planetary gear stage 104a. The impact cut-off clutch 142a has a second clutch element 146a, which is rotationally fixed to a planet carrier 120a of the second planetary gear stage 106a. In the illustrated screwing mode and drilling mode, the impact cut-off clutch 142a is open. During a percussion drilling operation, the tool spindle 38a transmits an axial clutch force to the impact shut-off clutch 142a when the operator presses a tool against a workpiece.The clutch force closes the impact cut-off clutch 142a. In the . Fig. Figure 2 shows the impact shut-off clutch 142a in the closed position. When the operator removes the tool from the workpiece, an impact switching spring 148a of the hand tool device 12a opens the impact shut-off clutch 142a.

[0034] The planet carrier 120a of the second planetary gear stage 106a is designed in two parts. A first part 150a of the planet carrier 120a of the second planetary gear stage 106a is rotationally fixed to the tool spindle 38a. The first part 150a of the planet carrier 120a is axially displaceable from the tool spindle 38a, so that the planet carrier 120a remains rotationally coupled to the tool spindle 38a even in the event of an impact. Thus, the first part 150a is permanently connected to the tool spindle 38a. The first part 150a of the planet carrier 120a is axially displaceable relative to the impact switching spring 148a. A second part 152a of the planet carrier 120a of the second planetary gear stage 106a is rotationally fixed to the first part 150a of the planet carrier 120a. The first part 150a and the second part 152a of the planet carrier 120a are connected in a way that allows axial displacement relative to each other.The first part 150a and the second part 152a of the planet carrier 120a are permanently connected in a rotationally fixed manner.

[0035] Fig. Figure 10 shows a cross-sectional area of ​​a spindle locking device 154a of the hand tool device 12a. The spindle locking device 154a is designed to connect the tool spindle 38a to the hand tool housing 14a in a rotationally fixed manner when a tool torque is applied to the tool chuck 36a, for example, when clamping a tool insert into the tool chuck 36a. The spindle locking device 154a is partially formed integrally with the planet carrier 120a of the second planetary gear stage 106a. The spindle locking device 154a has locking means 156a, first clamping surfaces 158a, a second clamping surface 160a, and free-running surfaces 162a. The locking means 156a are cylindrical. The first clamping surfaces 158a are formed as areas of a surface of the first part 150a of the planet carrier 120a of the second planetary gear stage 106a. The first clamping surfaces 158a are flat.The second clamping surface 160a is formed as an inner surface of a clamping ring 164a of the spindle locking device 154a. The clamping ring 164a is rotationally fixed to the hand tool housing 14a. The free-running surfaces 162a are formed as areas of a surface of the second part 152a of the planet carrier 120a of the second planetary gear stage 106a. When a tool torque is applied to the tool chuck 36a, the locking means 156a clamp between the first clamping surfaces 158a and the second clamping surface 160a. When the drive unit 30a is driven, the free-running surfaces 162a guide the locking means 156a in a circular path and prevent clamping. The first part 150a and the second part 152a of the planet carrier 120a are meshed with each other with backlash.

[0036] The Fig. 1, Fig. 2, Fig. 9 and Fig. Figure 10 shows the torque limiting unit 34a. The torque limiting unit 34a is designed to limit the maximum tool torque delivered by the tool chuck 36a in a screwdriving mode. The torque limiting unit 34a comprises an operating element 166a, an adjusting element 168a, limiting springs 170a, transmission means (not shown), first stop surfaces 172a, a second stop surface 174a, and limiting means 176a. The operating element 166a is ring-shaped. It connects to the tool chuck 36a in the direction of the planetary gear 28a. The operating element 166a has an adjusting thread 178a, which is coupled to an adjusting thread 180a of the adjusting element 168a. The adjusting element 168a is mounted to be rotationally fixed and axially displaceable. A rotation of the control element 166a moves the adjusting element 168a in an axial direction. The limiting springs 170a are supported on one side of the adjusting element 168a.The limiting springs 170a are supported on another side via the transmission means against a stop element 182a of the torque limiting unit 34a. One surface of the stop element 182a has the first stop surface 172a. The stop element 182a is mounted in the screw configuration so as to be axially movable against the limiting springs 170a. The second stop surface 174a is formed as a region of a surface of a ring gear 184a of the second planetary gear stage 106a. The second stop surface 174a has trough-shaped recesses 186a. The limiting elements 176a are spherical. The limiting elements 176a are mounted in tubular recesses 188a so as to be slidably displaceable in the direction of impact 54a. Fig. Figure 11 shows a cross-sectional area F of the torque limiting unit 34a. During a screwing operation, the limiting means 176a are arranged in the trough-shaped recesses 186a. The limiting means 176a secure the ring gear 184a of the second planetary gear stage 106a against rotation. When the set maximum tool torque is reached, the limiting means 176a push the stop means 182a away against the limiting springs 170a. The limiting means 176a then spring into the next of the trough-shaped recesses 186a. This causes the ring gear 184a of the second planetary gear stage 106a to rotate, thus interrupting the screwing operation.

[0037] The control element 134a of the hand tool device 12a has support means 190a which, at least during drilling operation, prevent axial movement of the stop means 182a. For this purpose, the support means 190a support the stop means 182a in the axial direction. The stop means 182a has screw recesses 192a into which the stop means 182a are inserted, particularly during drilling operation. Fig. The support means 190a are arranged accordingly when the control element 134a is in a screw position, as shown in Figure 9, and when the maximum tool torque is reached. During impact drilling, the support means 190a also prevent axial movement of the stop means 182a and thus prevent the torque limiting unit 34a from being activated. Alternatively, during impact drilling, the stop means could also be arranged so that they can be inserted into screw recesses. In this case, a torque limiting unit would be active during impact drilling.

[0038] Fig. Figure 12 shows a cross-sectional surface G of the second planetary gear stage 106a. The ring gear 184a of the second planetary gear stage 106a is secured against complete rotation, at least during drilling operation, by being mounted in the hand tool housing 14a. Planet gears 194a of the second planetary gear stage 106a mesh with the ring gear 184a and a sun gear 196a of the second planetary gear stage 106a.

[0039] Fig. Figure 13 shows a cross-sectional area H of the third planetary gear stage 108a. The sun gear 196a of the second planetary gear stage 106a is non-rotatably connected to a planet carrier 198a of the third planetary gear stage 108a. Planet gears 200a of the third planetary gear stage 108a mesh with a sun gear 202a and a ring gear 204a of the third planetary gear stage 108a. The ring gear 204a of the third planetary gear stage 108a has a tooth 206a that non-rotatably connects the ring gear 204a of the third planetary gear stage 108a to the hand tool housing 14a in a first gear ratio.

[0040] Fig. Figure 14 shows a cross-sectional area I of the third planetary gear stage 108a. The sun gear 202a of the third planetary gear stage 108a is non-rotatably connected to a planet carrier 208a of the fourth planetary gear stage 110a. Planet gears 210a of the fourth planetary gear stage 110a mesh with a sun gear 212a and a ring gear 214a of the fourth planetary gear stage 110a. The ring gear 214a is non-rotatably connected to the hand tool housing 14a. The sun gear 212a of the fourth planetary gear stage 110a is non-rotatably connected to a rotor 216a of the drive unit 30a.

[0041] The ring gear 204a of the third planetary gear stage 108a is as in Fig. Figure 2 shows the components mounted to be axially displaceable. In the first gear ratio, the ring gear 204a of the third planetary gear stage 108a is rotationally fixed to the hand tool housing 14a. In the second gear ratio, the ring gear 204a of the third planetary gear stage 108a is rotationally fixed to the planet carrier 208a of the fourth planetary gear stage 110a and is rotatably mounted relative to the hand tool housing 14a. This results in a reduction ratio in the first gear ratio between the rotor 216a of the drive unit 30a and the planet carrier 198a of the third planetary gear stage 108a that is greater than the reduction ratio in the second gear ratio.

[0042] The operating device 32a comprises a first operating element 218a and a second operating element 220a. The first operating element 218a is arranged on a side of the hand tool housing 14a facing away from the handle 18a. It is mounted so as to be movable parallel to the axial direction of the planetary gear 28a. The first operating element 218a is connected axially to the ring gear 204a of the third planetary gear stage 108a via an adjusting element 222a of the operating device 32a. The ring gear 204a of the third planetary gear stage 108a has a groove 224a into which the adjusting element 222a engages. Thus, the ring gear 204a of the third planetary gear stage 108a is connected to the adjusting element 222a in an axially rotatable manner relative to the adjusting element 222a. The adjusting means 222a is spring-loaded, which allows the ratio to be adjusted independently of the rotational position of the ring gear 204a of the third planetary gear stage 108a.When the first control element 218a is pushed towards the tool chuck 36a, the first gear ratio is set. When the second control element 220a is pushed away from the tool chuck 36a, the second gear ratio is set.

[0043] The second control element 220a is located on the side of the hand tool housing 14a facing away from the handle 18a. The second control element 220a is slidably mounted about an axis that is aligned parallel to the axial direction of the planetary gear 28a. The second control element 220a is rotationally fixed to the control element 134a of the hand tool device 12a. The screwdriving mode, the drilling mode, and the impact drilling mode can be set using the second control element 220a. When the second control element 220a is moved to the left (viewed in the direction of impact 54a), the impact drilling mode is set. When the second control element 220a is moved to the right (viewed in the direction of impact 54a), the screwdriving mode is set. When the second control element 220a is positioned in the center (viewed in the direction of impact 54a), the drilling mode is set.

[0044] Fig. Figure 15 schematically shows a protective device 226a of the hand tool device 12a, which prevents operation in the first gear ratio in the impact drilling mode. Fig. The first gear ratio and the drilling mode are set. The protective device 226a is partially formed integrally with the operating device 32a. A first locking element 228a of the protective device 226a is integrally formed with the first operating element 218a. A second locking element 230a of the protective device 226a is integrally formed with the second operating element 220a. The locking elements 228a are each tongue-shaped. The first locking element 228a extends towards the second operating element 220a. The second locking element 230a extends towards the first operating element 218a. The protective device 226a prevents switching to the impact drilling mode when the first gear ratio is set. The protective device 226a prevents switching to the first gear ratio when the impact drilling mode is set.

[0045] The drive unit 30a is designed as an electric motor. The drive unit 30a has a maximum torque that results in a maximum tool torque of more than 15 Nm in the first gear ratio and less than 15 Nm in the second gear ratio. The maximum tool torque in the first gear ratio is 30 Nm. The maximum tool torque in the second gear ratio is 10 Nm. The tool torque is to be determined according to the standard DIN EN 60745.

[0046] The impact switching spring 148a of the hand tool device 12a opens the impact shut-off clutch 142a during impact drilling operation when the operator lifts the tool from the workpiece. The impact switching spring 148a is arranged coaxially with the planetary gear stages 104a, 106a, 108a, 110a of the planetary gear 28a. The second planetary gear stage 106a and the third planetary gear stage 108a each enclose the impact switching spring 148a on at least one plane that is oriented perpendicular to the axial direction of the planetary gear 28a. The second planetary gear stage 106a and the third planetary gear stage 108a are each operatively arranged between at least two further planetary gear stages 104a, 106a, 108a, 110a of the planetary gear 28a. The planet carrier 120a of the second planetary gear stage 106a supports the impact switching spring 148a on a side facing away from the tool chuck 36a.

[0047] In the Fig. 16, Fig. 17, Fig. 18 to Fig. Figure 19 shows further embodiments of the invention. The following descriptions and drawings are essentially limited to the differences between the embodiments, whereby, with regard to identically designated components, in particular components with the same reference numerals, reference is also generally made to the drawings and / or the description of the other embodiments, in particular the Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Fig. 10, Fig. 11, Fig. 12, Fig. 13, Fig. 14 to Fig. 15, reference can be made. To distinguish the embodiments, the letter a is the reference numeral of the embodiment in the Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Fig. 10, Fig. 11, Fig. 12, Fig. 13, Fig. 14 to Fig. 15 appended. In the exemplary embodiments of the Fig. 16, Fig. 17, Fig. 18 to Fig. In 19, the letter a is replaced by the letters b to e.

[0048] In the Fig. Figure 16 schematically illustrates another, alternative embodiment of a first impact shut-off device 24b. A planet carrier 114b of a first planetary gear stage 104b is designed in two parts. A first part 232b of the planet carrier 114b guides planet gears 112b of the first planetary gear stage 104b. A second part 234b of the planet carrier 114b is rotaryally coupled to a second planetary gear stage 106b. A first impact shut-off device 24b of an impact mechanism 22b has a freewheel 236b, which appears advantageous to those skilled in the art, and which connects the first part 232b and the second part 234b of the planet carrier 114b in a rotationally fixed manner when the drill is rotating clockwise, and disconnects them when the drill is rotating counterclockwise. A ring gear 116b of the first planetary gear stage 104b is permanently and rotationally fixed to a hand tool housing.

[0049] In the Fig. Figure 17 schematically illustrates a further embodiment of a first impact shut-off device 24c. An impact spindle 46c of an impact mechanism 22c is designed in two parts. A first part 238c of the impact spindle 46c is connected to a striker drive device. A second part 240c of the impact spindle 46c is connected to a second planetary gear stage 106c. The first impact shut-off device 24c has a freewheel 242c, which appears advantageous to those skilled in the art, and which connects the first part 238b and the second part 240c of the impact spindle 46c in a rotationally fixed manner during clockwise drilling and separates them during counterclockwise drilling. A ring gear 116c of the first planetary gear stage 104c is permanently and rotationally fixed to a hand tool housing.

[0050] In the Fig. Figure 18 shows a further embodiment of an impact switching spring 148d. A second planetary gear stage 106d supports the impact switching spring 148d on a side facing a tool chuck. A drive unit 30d supports the impact switching spring 148d on a side facing away from a tool chuck. The second planetary gear stage 106d, a third planetary gear stage 108d, and a fourth planetary gear stage 110d each enclose the impact switching spring 148d on at least one plane that is oriented perpendicular to an axial direction of the planetary gear stages 106d, 108d, and 110d, respectively. The drive unit 30d is rotationally fixed to a part of the planetary gear stage 110d.

[0051] Fig.Figure 19 shows an alternative embodiment of the operating device 32e and a protective device 226e. The operating device 32e has a first operating element 218e and a second operating element 220e. The operating elements 218e and 220e are pivotally mounted about pivot axes 244e and 246e, respectively. The operating elements 218e and 220e have a disc-shaped base. The first operating element 218e (not shown in detail) is connected to a planetary gear via a mechanism that would appear useful to a person skilled in the art. A first gear ratio and a second gear ratio can be set using the first operating element 218e. The second operating element 220e (not shown in detail) is connected to a control element via a mechanism that would appear useful to a person skilled in the art. A screwdriving mode, a drilling mode, and a percussion drilling mode can be set using the second operating element 220e. A chiseling mode could also be set.

[0052] The guard 226e has a freewheeling range 248e limited by the first control element 218e. The guard 226e has a freewheeling range 250e limited by the second control element 220e. The freewheeling range 248e of the first control element 218e allows the screwdriving mode, the drilling mode, and the impact drilling mode to be set when a second gear ratio is selected. The freewheeling range 250e of the second control element 220e allows the screwdriving mode and the drilling mode to be set when a first gear ratio is selected. In impact drilling mode, the guard 226e prevents the first gear ratio from being selected. When the first gear ratio is selected, the guard 226e prevents the impact drilling mode from being selected.

Claims

[1] Hand tool device with a percussion mechanism (22a; 22b; 22c) comprising a beater (44a) and a beater drive device (50a) designed to drive the beater (44a) at least in the direction of impact (54a) during a first direction of drill rotation, wherein the percussion mechanism (22a; 22b; 22c) comprises a beater shut-off device (24a; 24b; 24c) designed to prevent the beater drive device (50a) from being driven during a second direction of drill rotation, characterized by , that the impact shut-off device (24a; 24b; 24c) is designed to prevent the drive of the beater drive device (50a) independently in a counterclockwise direction of drilling rotation, wherein the impact shut-off device (24a; 24b; 24c) has a blocking means (124a) which allows free rotation in at least one operating state. [2] Hand tool device according to claim 1, characterized bya planetary gear stage (104a; 104b; 104c) that drives the beater drive device (50a) in at least one operating state. [3] Hand tool device according to claim 1 or 2, characterized by , that the impact cut-off device (24a) acts on a ring gear (116a) of the planetary gear stage (104a). [4] Hand tool device according to claim 1 or 2, characterized by , that the impact cut-off device (24b) acts on a planet carrier (114b) of the planetary gear stage (104b). [5] Hand tool device according to claim 1 or 2, characterized by , that the impact cut-off device (24c) acts on an impact spindle (46c) of the impact mechanism (22c). [6] Hand tool device according to one of the preceding claims, characterized by , that the impact shut-off device (24a; 24b; 24c) is designed to shut off the beater drive device (50a) in a second drilling rotation direction. [7] Hand tool device according to one of the preceding claims, characterized by , that the beater drive device (50a) has a cam guide (62a, 64a) which drives the beater (44a) at least during impact drilling operation. [8] Hand tool device according to claim 7, characterized by , that the curve (62a, 64a) has a free-running area (78a, 80a). [9] Hand tool with a hand tool device (12a) according to one of the preceding claims.

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