HAND TOOL MACHINE

Description

[0001] The invention relates to a hand-held power tool with a drive motor, a gearbox, and a tool holder, wherein a motor output of the drive motor is rotationally coupled to a gearbox drive of the gearbox, and a gearbox output of the gearbox, which is rotatable about a rotational axis, is rotationally coupled to the tool holder. The gearbox has a first switching gearbox element and a second switching gearbox element, which are each linearly adjustable between a first setting position and a second setting position with respect to a gearbox housing by means of an actuating device. The actuating device is coupled to the switching gearbox elements and has an actuating member which is pivotally mounted about an actuating pivot axis with respect to a machine housing of the hand-held power tool and which can be manually actuated by an operator of the hand-held power tool.wherein the first gearshift element is adjustable linearly along its adjustment axis by means of a deflection gear by means of a pivoting movement of the actuating member about the actuating pivot axis, wherein the deflection gear comprises a driving ring extending annularly around the gear housing and mounted rotatably about the actuating pivot axis, which driving ring is coupled to the first gearshift element for its linear adjustment by means of a first coupling element.

[0002] Such a hand-held power tool is described, for example, in EP 1 886 769 A1. The hand-held power tool has a four-speed transmission with two ring gears as selectable transmission elements. Each ring gear or selectable transmission element can be engaged by an actuating device on the hand-held power tool, with both ring gears being adjusted linearly in the transmission housing. A complex actuating device is required for individual actuation of the ring gears.

[0003] EP 2 551 063 A1 discloses a hand-held power tool according to the preamble of claim 1 with a four-speed transmission. The four-speed transmission is shiftable by an actuating device that is rotatably and linearly adjustable. A deflection gear is required to convert a rotary movement of the actuating device into a linear movement of a shift transmission element. Both shift transmission elements must be controlled individually by the actuating device.

[0004] It is therefore the object of the present invention to provide a hand-held machine tool with an improved operating concept.

[0005] To solve the problem, a hand-held machine tool according to the technical teaching of claim 1 is provided.

[0006] The basic idea is that the drive ring essentially forms a rotating body or pivot bearing for the actuating element. The actuating element can thus pivot around the transmission housing with the drive ring to engage the first shifting transmission element. The actuating element, in turn, is mounted on this drive ring for linear displacement, allowing it to directly execute the linear movement required to adjust the second shifting transmission element. An additional slide or support for the actuating element or the second coupling element is not necessary.In addition, with this arrangement it is possible to carry out the two actuating movements, namely around the actuating longitudinal axis and around the actuating pivot axis, which can run parallel to one another, in a superimposed manner, so that the first switching transmission element and the second switching transmission element can be switched simultaneously and the transmission can be switched, for example, from a first switching position or a first gear directly into a third gear or a third switching position, without the second or an intermediate switching position or an intermediate gear having to be controlled beforehand.

[0007] Compared to the embodiment of a transmission according to EP 1 886 769 A1 mentioned at the beginning, operation is therefore easier.

[0008] With regard to EP 2 551 063 B1, the actuating device and the coupling between the actuating device and the shift transmission elements are constructed more simply. In particular, only a single coupling element, the second coupling element, is sufficient between the actuating element and the second shift transmission element. This coupling element can even be integrally formed on the actuating element if a corresponding degree of rotational freedom exists between the second coupling element and the second shift transmission element.

[0009] A spring arrangement is expediently arranged between the actuating member and the first gearshift element or the second gearshift element, or both. During and / or after actuation of the actuating member, the spring arrangement loads the gearshift element into its respective set position or a set position associated with the position of the actuating member. If the gearshift element cannot reach its set position, for example, because its teeth are not aligned with the teeth of a gear wheel interacting with the gearshift element, the spring load ensures that the two components can engage with each other in a positive-locking manner during a relative rotational adjustment of the gearshift element and the gear wheel.

[0010] The spring arrangement between the second shift transmission element and the actuating member can be provided in particular by the second coupling element, for example, exclusively by the second coupling element. However, it is also possible for a separate spring or spring arrangement to be provided. Furthermore, a spring arrangement and the resilient coupling element can be provided. However, the spring arrangement between the first shift transmission element and the actuating member can also easily be provided by the first coupling element.

[0011] The first coupling element or the second coupling element, or both, can comprise or be a spring element, for example. A spring clip or the like is particularly suitable as a resilient, flexible coupling element, e.g., as described in EP 1 886 769 B1.

[0012] The first coupling element and / or the second coupling element expediently comprises or is formed by a spring clip. The spring clip expediently extends in a ring shape around the first manual transmission element or the second manual transmission element. The spring clip can, for example, have clip arms that are resiliently flexible. The spring clip expediently engages with its longitudinal end regions in corresponding receptacles, for example, bores, grooves, guides, in particular longitudinal guides or the like, on the respective first or second manual transmission element.

[0013] A favorable and simple embodiment provides for the actuating element to be coupled to the second gearshift element exclusively by the second coupling element or by a single component. Therefore, no additional component is required between the gearshift element and the actuating element. The aforementioned spring clip is particularly suitable as the second coupling element, which, as a single component, is sufficient to realize the coupling between the actuating element and the second gearshift element.

[0014] According to the invention, a transmission member, for example annular, rod-shaped or similarly designed, is arranged between the driving ring and the first coupling element, which transmission member can be carried along by the driving ring about the actuating pivot axis. The transmission member and the driving ring are movable relative to one another, for example rotatable and / or displaceable relative to one another. Between the transmission member and the driving ring, there is arranged a spring arrangement which can be actuated by a relative movement of the transmission member and the driving ring and which spring-loads the first actuating gear element into at least one switching position. Thus, the driving ring can already reach a rotational end position, while the transmission member has not yet reached this end position and is loaded into the end position by the spring element or the spring arrangement.When the first actuating gear element has a suitable position in relation to a component to be switched, for example a gear wheel, it is pressed or adjusted into this end position by the spring arrangement.

[0015] At least one guide slot is advantageously arranged on the drive ring or on a transmission element that can be moved along by the drive ring around the actuating pivot axis, for example, the aforementioned transmission element that is adjustable relative to the drive ring. For example, the first coupling element or a body connected to it or coupled thereto engages in the guide slot. Preferably, two guide slots are provided, which are arranged on opposite sides of the transmission housing or the transmission support structure.

[0016] The second coupling element is expediently mounted so that it can pivot and / or slide relative to the gear housing. Thus, it is possible for the second coupling element, which is linearly adjusted, to transmit the linear movement to the second actuating gear element due to a displacement relative to the gear housing. However, a pivot bearing or a combined pivot bearing and sliding bearing of the second coupling element is also possible.

[0017] The second coupling element is expediently pivotally mounted on a pivot bearing provided on the gearbox housing, for example a bearing pin protruding in front of a peripheral wall of the gearbox housing or a bearing receptacle arranged in the peripheral wall of the gearbox housing. Alternatively or additionally, the second coupling element can also be pivotally mounted on the actuating member. The bearing receptacle can be implemented, for example, by a longitudinal groove. This longitudinal groove can also be the arcuate guide receptacle described below. If bearing pins or bearing receptacles are provided on the gearbox housing, they are expediently provided on opposite sides of the gearbox housing and / or in a region of the largest circumference of the gearbox housing. Thus, the bearing pins protrude, for example, radially in front of the peripheral wall of the gearbox housing.

[0018] The actuating member expediently has a guide receptacle extending in an arc around the actuating pivot axis, into which the second coupling element engages. In particular, the second coupling element has a linear or arcuate section that engages the aforementioned guide receptacle. It is also possible for the guide receptacle to be sufficiently deep to provide an arcuate free space for movement into which the second coupling element can engage when pivoting about the actuating pivot axis.

[0019] Preferably, a locking arrangement is provided which serves to lock the actuating member in at least one actuating position. The locking arrangement has, for example, one locking receptacle or an arrangement of several locking receptacles on the actuating member. The locking arrangement is preferably arranged in a concealed manner. The locking arrangement is preferably provided on an underside of the actuating member and / or arranged between the actuating member and the gear housing. For example, one or more locking receptacles can be provided on the actuating member, into which a locking member, in particular a spring-loaded or resilient locking member, which is arranged on the gear housing engages. However, the resilient locking member can also be arranged on the actuating member and engage in locking receptacles on the gear housing.Thus, the actuating member can be locked in an actuating position associated with a respective switching position of the transmission, for example in the respective longitudinal end positions with respect to the actuating longitudinal axis and / or a pivoting position with respect to the actuating pivoting axis.

[0020] The actuating member is expediently mounted for linear displacement on a linear guide of the driving ring. Thus, the driving ring has a linear guide that has one or more guide grooves or other similar linear guide elements. Linear guide projections can also be provided, for example, longitudinal ribs or the like, which protrude from the driving ring and engage in corresponding longitudinal guide grooves of the actuating member. Thus, linear guide components are present on the driving ring and the actuating member.

[0021] Another embodiment provides for the actuating member to be guided on a machine housing of the handheld power tool. For example, a wall of the machine housing has a recess or cutout in which the actuating member is arranged. Guide receptacles, in particular guide grooves, pockets, or the like, can be provided at one or more edge regions of the cutout for guiding the actuating member.

[0022] The second coupling element advantageously engages in a recess in the linear guide. For example, the linear guide has linear guide sections between which the recess is arranged. The linear guide sections are advantageously connected by connecting sections. The second coupling element engages between the connecting sections and the actuating member.

[0023] The linear guide advantageously comprises two linear guide sections arranged at an angular distance from one another with respect to the actuating pivot axis. Thus, the actuating member can be guided along two or more linear guide sections, which may also be interrupted, for example, due to the aforementioned recess.

[0024] The actuating member advantageously has at least one support section for support on the transmission housing. Thus, the actuating member is supported on the one hand by the drive ring and on the other hand by the transmission housing.

[0025] It is preferred if the actuating member has an arched or barrel-shaped wall shape. It is therefore advantageous if the actuating member covers the components it is intended to actuate and / or the locking arrangement.

[0026] A further embodiment may provide for the actuating member to connect spaced-apart longitudinal end regions of the driving ring. The driving ring thus has a distance between its longitudinal end regions, which is bridged by the actuating member. For example, the actuating member engages linear guide sections arranged at the longitudinal end region, so that these are connected to one another with respect to the actuating pivot axis. The actuating member, so to speak, closes the driving ring.

[0027] At this point, it should be noted that the drive ring can be a closed ring, meaning it completely encloses the transmission housing. However, it is also possible for the drive ring to be only a partial ring. Thus, the drive ring can be designed as a ring segment. The drive ring preferably extends around at least half of the outer circumference of the transmission housing, i.e., at least 180 degrees. It is preferred if the drive ring extends around at least 270 to 300 degrees of the outer circumference of the transmission housing.

[0028] An advantageous embodiment provides that the transmission is switchable between at least two switching positions in which speed ratios between the transmission input and the transmission output are different from one another, wherein the transmission comprises a first gear arrangement and at least one second gear arrangement, each having at least one gear and a switching transmission element, one of which is the switching actuator and the other the switching transmission element switchable by the switching actuator,wherein in both gear wheel arrangements, the at least one gear wheel can roll on the switching transmission element of the gear wheel arrangement and / or the switching transmission element can roll on the at least one gear wheel of the gear wheel arrangement, and the respective switching transmission element is mounted on the transmission support structure so as to be locally adjustable between at least two setting positions for setting the switching positions of the transmission and / or is adjustable with respect to the transmission support structure between an immovable position and a movable position, and that for switching the transmission between at least two of the switching positions, the switching transmission element of the first gear wheel arrangement forms a switching actuator for the second gear wheel arrangement, which is switchable between a first setting position and at least one second setting position,in which a mobility of the switching transmission element of the second gear arrangement with respect to the transmission support structure is different and / or the switching actuator is disengaged and engaged with the at least one gear of the second gear arrangement.,

[0029] The basic idea here is that the shift transmission element of the first gear arrangement, on the one hand, acts as a shift element directly for the first gear arrangement, but on the other hand also directly or indirectly influences the rotational behavior of the second gear arrangement, which can in itself be shifted by its own shift transmission element. The shift actuator can engage directly with one or more gears of the second gear arrangement, for example, firmly couple or couple a planetary gear set with the second gear arrangement with a planetary gear set of the first gear arrangement, which forms or comprises the at least one gear of the first gear arrangement. The planetary gear sets are then no longer rotatable relative to one another and are rotationally fixedly coupled to one another by the shift transmission element, for example a ring gear.

[0030] Another or additional possible embodiment provides that the shift actuator, i.e., the shift transmission element of the first gear arrangement, influences the shift transmission element of the second gear arrangement in the first setting position, so that, for example, it can no longer rotate relative to the transmission housing. However, in the second setting position of the shift transmission element, the shift transmission element of the second gear arrangement is rotatable relative to the transmission housing. Thus, the second shift transmission element can, for example, form a rolling base for the at least one gear of the second gear arrangement, which can roll accordingly on the second shift transmission element.

[0031] Preferably, the switching transmission elements and the gear wheels of the gear wheel arrangements are gears. Of course, the invention would also be readily applicable to a roller gear or friction gear.

[0032] In any case, the invention makes it possible for only the shift transmission element of the first gear arrangement to be adjusted in order to shift not only the first gear arrangement but also the second gear arrangement. This makes operation significantly simpler. For example, an actuating device is easier to construct that only needs to be coupled to the shift transmission element of the first gear arrangement or controls it in order to act not only on the first gear arrangement but also on the second gear arrangement. For example, this eliminates the need for a housing opening in a transmission housing of the transmission, which would otherwise be necessary for controlling or actuating the shift transmission element of the second gear arrangement.

[0033] One configuration can provide that the shift transmission element of the second gear arrangement is rotationally fixed relative to the transmission support structure, for example, the transmission housing, in the first setting position of the shift actuator, and rotatable relative to the transmission support structure in the second setting position. In the rotationally fixed position of the shift transmission element of the second gear arrangement, planetary gears, for example, i.e., the at least one gear of the second gear arrangement, can roll on the shift transmission element. In the rotatable position of the shift transmission element of the second gear arrangement, the at least one gear, for example, a planetary gear, of the second gear arrangement can drive the shift transmission element or rotate it.

[0034] The manual transmission element of the second gear arrangement advantageously has, for rotationally fixed attachment relative to the transmission support structure, for example, the transmission housing, at least one anti-rotation contour for engagement with a positive-locking mating contour of the transmission support structure and / or the manual transmission element forming the shift actuator. The anti-rotation contour and the positive-locking mating contour can, for example, be a pairing of teeth and tooth spaces or tooth receptacles, a pairing of anti-rotation projection and anti-rotation receptacle, a groove structure, or the like. It is possible for the manual transmission element of the second transmission arrangement to have multiple anti-rotation contours or anti-rotation contours located on different sides, so that it can be positively attached to multiple components, for example, to a positive-locking mating contour of the transmission housing fixed to the housing and / or to the shift actuator.

[0035] For example, the anti-rotation contour is arranged on a radial outer circumference, on one end face, or on both sides of the gearshift element that can be switched by the shift actuator. Tooth structures can be provided there, for example.

[0036] The shift transmission element forming the shift actuator can have an arcuate toothing on its inner circumference as a positive-locking counter-contour. In the first setting position, the anti-rotation contour of the shift transmission element shiftable by the shift actuator engages with this toothing. In the second setting position, at least one gear wheel of the first gear wheel arrangement, for example, its radial outer toothing, engages with this toothing. For example, this gear wheel meshes with the shift transmission element or shift actuator.

[0037] In the first setting position, it is advantageous if the shift transmission element forming the shift actuator is completely disengaged from the at least one gear wheel of the first gear wheel arrangement, in particular, disengaged from direct engagement with the at least one gear wheel of the first gear wheel arrangement or all gear wheels of the first gear wheel arrangement. Thus, the shift transmission element only fulfills the function of a shift actuator for the other shift transmission element, the shift transmission element of the second gear wheel arrangement.

[0038] However, a configuration is also possible in which the shift transmission element of the first gear arrangement engages with at least one gear of the first gear arrangement, for example, a planetary gear set or at least two planetary gears of the first gear arrangement, when the shift actuator assumes the first shift position. This is a possible configuration, for example, in a coupling of planetary gear sets that form components of the first gear arrangement and the second gear arrangement.

[0039] In the second setting position of the shift transmission element forming the shift actuator, the shift transmission element of the at least one second gear arrangement, i.e., the engaged shift transmission element, is rotatable relative to the transmission support structure, so that it can be carried along by the at least one gear of the at least one second gear arrangement. Thus, the shift transmission element of the second gear arrangement can rotate in the second setting position of the shift actuator and thus be carried along by the one or more gears of the second gear arrangement.

[0040] The shift transmission element, which can be shifted by the shift actuator, is expediently mounted rotatably with respect to the transmission support structure. It can also be mounted linearly immovably on or in the transmission support structure, either additionally or alternatively. It is particularly advantageous if the shift transmission element of the second gear arrangement is immovable with respect to a rotational axis of the transmission output of the transmission or its own rotational axis.

[0041] For the rotatable mounting of the shift transmission element of the second gear arrangement, which can be switched by the shift actuator, a bearing arranged on the transmission housing or the transmission support structure can be provided, for example, a bearing, for example a bearing groove and a bearing projection, a rolling bearing, in particular a nail bearing, ball bearing, or the like. Preferably, for example, a support body is arranged stationary with respect to the transmission support structure, on the outer circumference and / or inner circumference of which the shift transmission element of the second gear arrangement is rotatably mounted. However, at least one gear wheel of the second gear wheel arrangement can also be provided for the rotatable mounting of the shift transmission element. Thus, the shift transmission element of the second gear wheel arrangement can be rotatably mounted on one or more gear wheels of the second gear wheel arrangement or by means of the gear wheels.This is possible, for example, if the switching transmission element of the second gear arrangement is designed as a ring gear, which surrounds a planetary gear set in a ring shape and is mounted on the planetary gear set.

[0042] Furthermore, it is advantageous if the shift transmission element of the second gear arrangement can only be switched or actuated by the shift transmission element or the shift transmission element of the first gear arrangement forming the shift actuator. An actuating device that can be actuated, for example, directly by the operator from an outside of the machine housing is thus coupled to the shift transmission element of the second gear arrangement only via the shift transmission element of the first gear arrangement and / or not directly.

[0043] The shift transmission element forming the shift actuator is expediently mounted linearly with respect to the transmission support structure, for example, parallel to a rotational axis of the transmission input and / or output, or its own rotational axis, between the first setting position and the second setting position. The shift transmission element forming the shift actuator is expediently a pivot point in one, two, or more, particularly setting positions, with respect to the transmission support structure. It is possible for the shift transmission element of the first gear arrangement to be rotatable in a setting position, for example, in an intermediate setting position located between two further setting positions.The operator can therefore move the switching actuator from a rotationally fixed position to a rotatable position with respect to the gearbox housing or the gearbox support structure, for example by adjusting it linearly, rotating it or the like.

[0044] Furthermore, it is advantageous if one or more, in particular all, of the shift transmission elements are spring-loaded into a respective shift position. For example, the shift transmission element of the second gear arrangement can be spring-loaded into one or both of the first and second setting positions by a spring arrangement. Thus, if the teeth of one of the shift transmission elements, for example, do not match the respective gear of the first or second gear arrangement to be shifted or mesh with it, the spring loading ensures that the respective teeth slide into each other when the teeth fit together.

[0045] The gears of the first gear arrangement and the at least one second gear arrangement that are in or can be brought into rolling engagement with the gearshift elements are expediently different in terms of their diameter and / or have different rolling circumferences for rolling engagement with the respective associated gearshift element. This allows for advantageously setting of different speed ratios between the gear drive and the gear drive output.

[0046] It is expediently provided that a radial outer circumference of the shift transmission element of the second gear arrangement is aligned with the radial outer circumference of the at least one gear of the first gear arrangement, so that the shift transmission element forming the shift actuator is linearly adjustable between the outer circumferences of the shift transmission element of the second gear arrangement and the at least one gear of the first gear arrangement, in particular parallel to a rotational axis of the gear. The shift transmission element of the second gear arrangement therefore does not project radially outward in front of the at least one gear of the first gear arrangement, but is aligned with it.However, this alignment is to be understood in such a way that an angular offset may well be present between the form-fitting contours, for example toothings, of the switching transmission element to be linearly adjusted and the switching transmission element of the second gear wheel arrangement or the at least one gear wheel of the first gear wheel arrangement, which, however, is canceled out upon further movement of the transmission in such a way that the linear adjustment of the switching transmission element is possible.For example, the switching transmission element of the second gear arrangement is a ring gear which is arranged on the outer circumference of one or more planetary gears of the second gear arrangement and has a toothing on its outer circumference which has the same tooth geometry as the at least one gear, in particular planetary gear, of the first gear arrangement, and is aligned with the gear of the first gear arrangement, so that the switching transmission element designed as a ring gear and serving as a switching actuator is linearly adjustable between the outer circumferences of the ring gear of the second gear arrangement and the at least one gear of the first gear arrangement.

[0047] The gears of the first gear arrangement and the at least one second gear arrangement that are in or can be brought into rolling engagement with the transmission elements are, for example, connected to one another in a rotationally fixed manner or are integrally formed. They can also form stepped gears or stepped planetary gears.

[0048] Furthermore, it is possible that the gear wheels of the first gear wheel arrangement and the at least one second gear wheel arrangement which are in rolling engagement or can be brought into rolling engagement with the gearbox elements are separated from one another, but are arranged on a common planetary gear carrier or web.

[0049] A further embodiment of the invention provides that the gear drive is rotationally fixedly connected or rotationally coupled to a sun gear, which is in rolling engagement with the at least one gear of the first gear arrangement. However, it would also be conceivable for the sun gear to mesh with one or more gears, for example, planetary gears, of the second gear arrangement.

[0050] The gear wheels of the first gear wheel arrangement and the second gear wheel arrangement can be arranged on a common planetary gear carrier or web, but also on separate planetary gear carriers or webs, in particular those that are rotatable relative to one another or movable relative to one another.

[0051] The first gear arrangement and the second gear arrangement expediently form a first gear stage, wherein the transmission has at least one second gear stage, for example, a planetary gear stage. The first gear stage is arranged upstream or downstream of the second gear stage with respect to the transmission output. In particular, the gear stages are arranged sequentially one behind the other.

[0052] The second gear stage can be a gear stage providing a fixed speed ratio, i.e., it can be merely a speed-reducing or speed-increasing gear stage that is not shiftable. However, a shiftable configuration is preferred. The second gear stage can expediently be shifted between at least two shift positions in which a speed ratio between an input of the second gear stage and an output of the second gear stage differs. For example, a four-speed transmission can be realized in this way.

[0053] The gear system is preferably a planetary gear system. However, other gear designs are also readily possible.

[0054] The first and / or the second actuating gear element expediently comprises a ring gear or is formed by a ring gear.

[0055] The embodiment of the invention, described in more detail below in the drawing, shows a screwing machine or drilling machine. Naturally, the invention is also applicable to other hand-held power tools, such as milling machines, cutting machines, saws, grinding machines, polishing machines, or the like. However, the gear mechanism and / or the actuating device according to the invention can also be used, for example, in hand-held power tools that have an oscillatory-driven, for example, linearly reciprocating tool holder.

[0056] The hand-held power tool expediently has a tool holder for a working tool and / or a working tool, for example a drilling tool, screwing tool, or the like. However, a cutting tool, milling tool, or the like can also be provided.

[0057] The gearbox output is preferably directly coupled to a tool holder of the hand-held power tool. For example, a holder for a screwdriver bit, a drill chuck, a screw chuck, or a similar tool holder can be provided. Furthermore, it is advantageous if an impact mechanism, such as an axial impact mechanism, is also arranged on the gearbox output.

[0058] Furthermore, it is possible that a deflection gear is present between the gearbox and a tool holder of the hand-held power tool, for example an angular gear or a conversion gear, which converts the rotating output movement of the gearbox output into an oscillatory linear movement or a hypercycloid and / or eccentric movement of the tool holder.

[0059] An embodiment of the invention is explained below with reference to the drawings. They show: Figure 1a front view of a hand-held power tool according to the hand-held power tool shown in Figure 2 in cross-section along a section line AA in Figure 1 is shown, Figure 3 is an exploded view of a gearbox of the hand-held power tool according to the preceding figures, Figure 4 is an exploded view of a drive train of the hand-held power tool including the gearbox and with a drill chuck, Figure 5 is an exploded view of an actuating device for the gearbox, Figure 6 is a bottom view of an actuating member of the actuating device according to Figure 5 , Figure 7 a plan view of the actuator according to Figure 6 when installed in the housing of the hand-held power tool, Figure 8 shows a side view of the gearbox, according to Figure 3 , Figure 9 a sectional view of the gearbox according to Figure 8 along a section line BB in Figure 8, Figure 10 a front view of the gearbox according to the preceding figures, approximately in the direction of view corresponding Figure 1 in a first and second switching position of the transmission, Figure 11 the view according to Figure 10 but in a third and fourth switching position of the transmission, Figure 12 the transmission according to the preceding figures in a sectional view according to a section line CC in Figure 10 in a first switching position, Figure 13 the transmission according to Figure 12 , but in a second switching position, Figure 14 a cross-sectional view of the transmission according to the preceding figures in a third switching position, approximately corresponding to a section line FF in Figure 11 and Figure 15 a cross-sectional view of the gearbox approximately corresponding Figure 14 , but in a fourth switching position.

[0060] A handheld power tool 10, for example, a screwdriver, has a machine housing 11, which is preferably pistol-shaped. An operator can grasp the machine housing 11 and thus the handheld power tool 10 by a handle portion 12, which protrudes from a motor portion 13 of the machine housing 11. An energy storage interface 14 is provided at a base area or at the free end area of ​​the handle portion 12 remote from the motor portion 13, to which an energy storage device 25, for example, a battery pack, can be attached. Thus, the handheld power tool 10 can be operated independently and wirelessly, although this is not essential.A hand-held power tool with a mains connection 14B for an alternating current network, in particular a connecting cable with a plug and / or a socket for a connecting cable, in particular a mains cable, or a hand-held power tool with an energy storage interface and mains connection, would also be possible without further ado.

[0061] The energy storage interface 14 supplies a power supply device 15 with electrical energy. The power supply device 15 can be actuated by means of a switch 16, which is preferably arranged on the handle section 12, to supply power to a drive motor 17, which is accommodated in the motor section 13 of the machine housing 11, in particular to adjust its speed and / or torque.

[0062] The drive motor 17 has a motor shaft 18 extending in the longitudinal direction of the motor section 13. The motor shaft 18 is rotatably mounted on motor bearings 19. The drive motor 17 has, for example, an excitation coil arrangement 20 through which the motor shaft 18 passes and in which a rotor, in particular a permanent magnet rotor, a squirrel-cage rotor, or the like, is rotatably mounted.

[0063] The drive motor 17 is fixedly mounted in the machine housing 11. Its motor shaft 18 extends from a rear wall 21 toward an end face 22 of the motor section 13. A top wall 23 of the machine housing 11 is provided on the side of the motor section 13 facing away from the handle section 12. A rotation direction switch 24 is preferably arranged between the handle section 12 and the motor section 13, with which the rotation direction of the drive motor 17 can be adjusted or switched.

[0064] Preferably, a hook element 26 is provided at a free end region or other location of the machine housing 11 in order to hang the hand-held power tool 10, for example on the belt of a user.

[0065] A motor output 27 of the drive motor 17 drives a gear 40 of the hand-held power tool 10.

[0066] The transmission 40 has a transmission drive 41, which is designed, for example, as a drive wheel and / or drive shaft or has a drive wheel and / or a drive shaft, which is connected in a rotationally fixed manner to the motor output 27.

[0067] A gear output 42 of the gear 40 drives, for example, a tool shaft 28 which projects in front of the end face 22 of the machine housing 11.

[0068] The tool shaft 28 has, for example, a tool holder 29 for a working tool 30, for example, a drilling tool, screwing tool, or the like. The tool shaft 28 is rotatably mounted on the machine housing 11, for example, by means of a bearing 31. However, the tool shaft 28 can also be mounted directly by the gear 40 or on the gear 40, for example, by means of a bearing 43.

[0069] Furthermore, it is advantageous if, in a hand-held power tool according to the invention, a percussion mechanism, for example an axial percussion mechanism and / or a rotary percussion mechanism, is arranged at the output of the gearbox. Such a percussion mechanism can also be easily integrated into the gearbox. In the specific embodiment, a percussion mechanism 200 is provided.

[0070] An impact body 201 of the impact mechanism 200 is formed, for example, by the tool shaft 28 or is firmly connected to it. The impact body 201 is, for example, a ring through which the tool shaft 28 passes and which is connected to the tool shaft 28 in a rotationally fixed and axially fixed manner.

[0071] The impact body 201 is subjected to force by a spring 202 in a direction SW1 forward, ie towards the tool holder 29.

[0072] The percussion mechanism 200 can be switched between a percussion mode described and a non-percussion mode, for example, by actuating an actuating element 206 that can be grasped by the operator. The actuating element 206 comprises, for example, a slide or a rotary element. The actuating element 206 can move an actuating body 207 between the position shown in Figure 2illustrated and associated with impact operation, in which the tool shaft 28 including the bearing 31 is linearly displaceable with respect to the rotational axis D, i.e., has longitudinal play, and thus gears 203, 204 can engage with one another, and a further switching position, not illustrated in the drawing, which represents non-impact operation and in which the gears 203, 204 are held out of engagement. The bearing 31 is held on the adjusting body 207. The tool shaft 28 is mounted displaceably with respect to the rotational axis D on the bearing 43.

[0073] The toothing 203 is arranged on an abutment body 205, which is arranged between the bearing 43 and the impact body 201 in a fixed position (rotationally and axially displaceably fixed) with respect to the machine housing 11. The toothing 203 is opposite the toothing 204, which is arranged on the impact body 201. The toothings 203, 204 are arranged on the respective end faces of the abutment body 205 and the impact body 201. The toothings 203, 204 are preferably helical toothings. The toothings 203, 204 preferably extend in a ring-shaped or partially ring-shaped manner around the rotational axis D of the tool shaft 28.

[0074] When pressure is applied in a force direction SW2 to the tool shaft 28, for example when the working tool 30 is loaded by a screw or a workpiece toward the machine housing 11, the gears 203, 204 slide along one another, adjusting the impact body 201 in the force direction SW2, so that a spring 202 is loaded and tensioned by a force direction SW1. When the gears 203, 204 are rotated further from one tooth pair to the next, they can suddenly engage one another under the load of the spring 202, so that an impact with the force direction SW1 is executed on the tool shaft 28 and thus the tool holder 29.

[0075] One in Figure 4 The only partially indicated embodiment provides, instead of the tool shaft 28, a chuck 32, for example a drill chuck, which is suitable for holding, for example, the working tool 30.

[0076] The transmission 40 is a four-speed transmission. The transmission 40 can therefore be switched between four gears or shift positions S1, S2, S3 and S4, which are Figures 12, 13, 14 and 15 are shown.

[0077] The gearbox is housed in a gearbox housing 44. The gearbox housing 44 has a peripheral wall 45 that defines a substantially cylindrical interior space in which the gearbox components, pinions, and the like, of the gearbox 40 are essentially accommodated. The gearbox housing 44 is covered at its front end by end walls 46, 47, for example, covers. The end walls 46, 47 have through-openings 48 through which the motor output 27 can be connected to the gearbox drive 41 and the tool shaft 28 or the chuck 32 can be connected to the gearbox output 42 of the gearbox 40. The through-openings 48 are, for example, push-through openings.

[0078] The gear housing 44 is accommodated in a rotationally fixed manner in the machine housing 11 of the hand-held power tool 10, for which purpose, for example, a toothing 49 and / or an anti-rotation projection 49A are provided on the end wall 47 facing the tool holder 29 and / or a circumferential contour 50 designed in the manner of an anti-rotation device on the end wall 46 facing the drive motor 17.

[0079] Thus, the gear housing 44 (the peripheral wall 45), which forms a basic gear housing, as well as the end walls 46, 47 forming the cover, essentially tightly house the gear components of the gear 40 explained below, for which sealing elements, in particular textile seals, plastic seals, O-rings, labyrinth seals, etc., can be provided.

[0080] The transmission 40 has a first gear stage G1 and a second gear stage G2. The first gear stage G1 forms an input gear stage and is driven by the transmission drive 41. The second gear stage G2 forms an output gear stage and drives the transmission output 42 of the transmission 40.

[0081] Gear stages G1 and G2 are planetary gear stages. Overall, gear unit 40 is designed as a planetary gear.

[0082] The gear stage G1 comprises a sun gear 51, which is arranged on the drive gear or gear drive 41 or is integral with the gear drive 41. The sun gear 51 meshes with planet gears 52, which are rotatably mounted on a web or planet gear carrier 53. For example, the planet gears 52 are rotatably mounted on axle elements 55 projecting in front of a carrier body 54. The planet gears 52 can be mounted directly on the axle elements 55 or, as in the exemplary embodiment, preferably by means of rolling bearings 56, in particular ball bearings or needle bearings, which improves the rotatability and mounting. Protruding from the carrier body 54 on opposite sides are, on the one hand, the axle elements 55, and on the other hand, an output 57, which forms a sun gear 58 for the second gear stage G2. A toothing 59 is provided on a radial outer circumference of the planet gear carrier 53 or carrier body 54.

[0083] The planetary gears 52 form a planetary gear set 60, to which a first ring gear 61 and a second ring gear 62 are assigned.

[0084] The planetary gears 52 are, so to speak, stepped planetary gears. The planetary gears 52 have rolling circumferences 63, 64 with different diameters, which are assigned to the first and second ring gears 61, 62 or mesh with them when a corresponding shift position of the transmission 40 is set.

[0085] The ring gear 61 is rotatable in the gear housing 44, but is axially immovable.

[0086] In the embodiment, the ring gear 61 is sandwiched between the end wall 46 and the steps 65 of the planet gears 52.

[0087] The ring gear 61 is supported, for example, with its opposite end faces, on the one hand directly or indirectly on the end wall 46, and on the other end face, on a step 65 provided between the rolling circumferences 63, 64. Between the ring gear 61 and the end wall 46, a bearing plate 66 is preferably provided, which is rotatable or preferably non-rotatable in the interior of the circumferential wall 45, as in Figure 4 indicated by corresponding outer circumferential contours or rotary form-locking contours. It is also possible for the ring gear 61 to be held immovably relative to a rotational axis D of the transmission output 42 of the transmission 40 by other measures, for example by annular contours engaging with a support body 61, which will be described in more detail later. For example, an annular projection can protrude radially outward from the support body 61 and engage in an annular groove on the inner circumference of the ring gear 61.

[0088] In the interest of stabilization and a mechanically resilient structure, the axle elements 55 are supported on their free sides facing away from the carrier body 54 on a support body 67. The support body 67 has receptacles 68 for at least one of the axle elements 55. In addition, support projections 69 are provided, which, so to speak, delimit receiving chambers or receiving spaces for the planet gears 52. It is possible, but not absolutely necessary, for some of the axle elements 55, in particular axle elements 55 not carrying planet gears, to engage positively in the support projections 69, for which the support projections 69 have, for example, receptacle 69A. Thus, the planet gears 52 are, so to speak, sandwiched between the planet gear carrier 53 and the support body 57 and are rotatably mounted on the planet gear carrier 53, namely its axle elements 55.

[0089] It is understood that the support body 67 and the carrier body 54 can also be formed in one piece. Furthermore, the support body 67 represents an option, ie, the carrier body 54 would also be sufficient to rotatably support the planetary gears 52, so that the support body 67 is not required in this case.

[0090] While the first ring gear 61 is rotatably but immovably mounted in the gear housing 44, the second ring gear 62 is mounted in the gear housing 40 so that it can move relative to an adjusting axis SA, but cannot rotate. Anti-rotation projections 70 are provided on the radial outer circumference of the second ring gear 62 and engage in anti-rotation receptacles 71 of the gear housing 44. The anti-rotation projections 70 are designed, for example, in the manner of sliding blocks, link followers, or the like. They engage in the anti-rotation receptacles 71. The anti-rotation receptacles 71 are designed, for example, as longitudinal grooves 72 that run parallel to the adjusting axis SA. The anti-rotation receptacles 71 or longitudinal grooves 72 extend, for example, on the inside or on the inner circumference of the peripheral wall 45.The anti-rotation projections 70 and / or the anti-rotation receptacles 71 can have different cross-sectional contours, for example, they can be wider or narrower in the circumferential direction. This is not important in detail to ensure the basic functionality, namely that the ring gear 62 is adjustable along the adjustment axis SA or parallel to the adjustment axis SA on the transmission housing 40 and / or relative to the planetary gear set 60.

[0091] In the Figure 12 and Figure 14In the switching position shown, namely the first switching position S1 and the third switching position S3, the second ring gear 62 is in a setting position P1 with respect to the setting axis SA, in which the second ring gear 62 holds the first ring gear 61 in a rotationally fixed manner in the gear housing 40, so that the planet gears 52 mesh with their smaller rolling circumferences 63 with an internal toothing 75 of the first ring gear 61 and roll on the internal toothing 75. The second ring gear 62, which is received in a rotationally fixed manner in the gear housing 64, has anti-rotation contours on its inner circumference for the rotationally fixed holding of the first ring gear 61, which has corresponding complementary rotationally positive locking contours on its outer circumference. These rotary form-locking contours and complementary rotary form-locking contours are provided by an internal toothing 73 of the second ring gear 62 and an external toothing 74 of the first ring gear 61, which can mesh with each other in a form-fitting manner.Therefore, the internal toothing 73 of the second ring gear 62 has, on the one hand, the function of allowing the planetary gears 52 to roll on it, and, on the other hand, the function of holding the first ring gear 61 rotationally fixed with respect to the gear housing 44 and thus also the machine housing 11 of the hand-held power tool 10.

[0092] If the second ring gear 62 takes the Figures 13 and 15 shown setting position P2 with respect to the setting axis SA, the first ring gear 61 is released from rotation. Therefore, the planetary gears 52 or the planetary gear set 60 can drive the first ring gear 61 in rotation and experience little or no resistance from the ring gear 61. In this situation, the planetary gears 52 roll with their larger rolling circumferences 64 on the inner circumference, thus the internal toothing 73, of the second ring gear 62, which is responsible for the Figures 13 and 15illustrated switching position, the second switching position S2 and the fourth switching position S4, of the transmission 40. The output 57 of the first gear stage G1 rotates in the second and fourth switching positions at a higher speed and a lower torque than in the first and third switching positions S1, S3.

[0093] The gear stage G2 comprises planetary gears 76 of a planetary gear set 77, which mesh on the one hand with the sun gear 58, i.e., the output 57 of the first gear stage G1, and on the other hand with a third ring gear 78. The third ring gear 78 is movably accommodated in the gear housing 44 along an adjusting axis SB. The adjusting axis SA can be coaxial with the adjusting axis SB or parallel thereto. The adjusting axes SA, SB are in the Figures 12 and 13 shown as an example.

[0094] The adjustment axes SA, SB can also be coaxial or coincide, for example, with a rotational axis D of the gearbox 40 and / or the gearbox input 41 and / or the gearbox output 42. The rotational axis D of the gearbox 40 is simultaneously the rotational axis of the drive motor 17, so that the gearbox 40, the drive motor 17, and the gearbox output 42 are ultimately coaxial. The tool holder 23 also rotates about the rotational axis D.

[0095] The planet gears 76 are rotatably mounted on a planet gear carrier 79, i.e., a web. The planet gear carrier 79 has a carrier body 80, of which axle elements 81, on the one hand, and the transmission output 42, on the other hand, are arranged on opposite sides. The axle elements 81 project toward the sun gear 58, thus the output 57 of the first gear stage G1, so that the planet gears 76, which are rotatably mounted on the axle elements 81 or rotatably mounted by the axle elements 81, engage with the output 57 or can be driven by it. The planet gears 76 can be rotatably mounted directly on the axle elements 81 or indirectly, for example, via rolling bearings (not shown), in particular needle bearings.

[0096] For example, planetary gear set 77 comprises four planetary gears 76, while planetary gear set 60 comprises three planetary gears 52. However, these numbers are not to be understood as limiting. Thus, a planetary gear set can also have two planetary gears, five planetary gears, or any other number of planetary gears.

[0097] The ring gear 78 has anti-rotation projections 83 on its radial outer circumference, which can be brought into engagement with anti-rotation receptacles 84 of the gear housing 44, for example on the cover or the end wall 47. In the Figures 12 and 13 In the switching positions S1 and S2 of the transmission 40 shown, the third ring gear 78 assumes a setting position P3 relative to the setting axis SB, in which the third ring gear 78 is fixed in a rotationally fixed manner relative to the rotational axis D or the transmission housing 44. The anti-rotation projections 83 then engage the anti-rotation receptacles 84.

[0098] In a setting position P4 with respect to the setting axis SB, however, the anti-rotation projections 83 of the third ring gear 78 are released from the anti-rotation receptacles 84 or are arranged apart from them, so that the ring gear 78 can rotate about the rotation axis D.

[0099] In the setting position P3, the rotationally fixed position of the third ring gear 78, the planetary gears 78 roll with their outer circumferences on an internal toothing 85 of the ring gear 78. The second gear stage G2 thereby causes a speed reduction and thus an increase in torque from its input side to its output side or from its input to the transmission output 42.

[0100] In the setting position P4 of the ring gear 78, however, the gears 76 continue to mesh with the internal toothing 85. However, the ring gear 78 continues to mesh with its internal toothing 85 with the outer or radially outer toothing 59 of the planet gear carrier 53. Thus, the ring gear 78 is fixed in a rotationally fixed manner with respect to the planet gear carrier 73. In addition, the planet gears 76 are mounted in a rotationally fixed manner between the toothing of the sun gear 78 and the internal toothing 85 of the third ring gear 78. Thus, in this situation, the second gear stage D2 has a speed ratio of i = 1 between its input side and its output side, thus causing neither a change in speed nor a change in torque.

[0101] The transmission output 42 is provided on the planetary gear carrier 79. The planetary gear carrier 79 has support projections 86 projecting from the carrier body 80, between which, for example, the tool shaft 28 can be arranged or by which the tool shaft 28 can be held. For example, the tool shaft 28 is held by support elements 87, which in turn are supported on the support projections 86.

[0102] The gear drive 41, which can also be referred to as a drive shaft, is mounted on a rotary bearing 88, in particular a roller bearing, in the Figures 12 to 14 The pivot bearing 88 is supported on an inner circumference of a through-opening of the support body 67 and is axially secured relative to the rotational axis D, for example, by a snap ring 89.

[0103] In the Figure 15In the illustrated bearing concept, however, the support body 67 is rotatably mounted on the cover or end wall 46 of the gear housing 44 by means of a pivot bearing 90. The pivot bearing 90, for example a ball bearing, needle bearing, or other rolling bearing (a plain bearing is also possible), is arranged and supported, for example, in the passage opening 48.

[0104] An actuating device 100 is used to shift and operate the transmission 40. The actuating device 100 allows the ring gear 78 to be linearly adjusted between the setting positions P3 and P4. The ring gear 78 forms a first shift transmission element 101. The ring gear 62 can also be linearly adjusted between the setting positions P1 and P2 by the actuating device 100 and is coupled to the actuating device 100 for this purpose. The ring gear 62 forms a second shift transmission element 102.

[0105] A third shift transmission element 103 is not switched directly by the actuating device 100, but rather by the shift transmission element 102 which is, so to speak, interposed. The shift transmission element 103 is provided by the ring gear 78.

[0106] The planetary gear set 60 forms a component of a first and a second gear arrangement 104, 105, see Figure 14The first gear arrangement 104 is assigned to the first manual transmission element 102 and includes, for example, the rolling circumferences 64 of the planetary gears 52. The second gear arrangement 105 is, so to speak, rigidly coupled or connected to the first gear arrangement 104, at least with respect to the planetary gears 52. Each planetary gear 52 has different rolling circumferences 63, 64 and thus forms, so to speak, two partial planetary gears. The partial planetary gear with the rolling circumference 63 is assigned to the ring gear 61 and thus to the manual transmission element 103 and the gear arrangement 105 as a gear 105A. The partial planetary gear with the rolling circumference 64 is assigned to the ring gear 62 and thus to the manual transmission element 102 and the gear arrangement 104 as a gear 104A. Due to their design as stepped planetary gears, the partial planetary gears are integrally or firmly coupled to one another.However, it is easy to imagine that the partial planetary gears can also be individual planetary gears that are connected to each other in a rotationally fixed manner or, in another embodiment, can be rotated relative to each other.

[0107] The shift transmission element 102 acts, on the one hand, as an active shift element with respect to the gear arrangement 104, namely, in the setting position P2, it is directly engaged with the larger rolling circumferences 64 of the planetary gears 52. In the setting position P1, however, the ring gear 62 is shifted away from the planetary gears 52, i.e., the internal toothing 73 no longer meshes with the rolling circumferences 64.

[0108] In the setting position P1, however, the ring gear 62 is a shift actuator for the other ring gear 61, which is held rotationally fixed by the ring gear 62 or the shift transmission element 102 with respect to the transmission housing 44 forming a transmission support structure 44A by means of the intermeshing toothings, namely the external toothing 74 and thus an anti-rotation contour 93, and the internal toothing 73 and thus a positive-locking counter-contour 94. Thus, the shift transmission element 103 is shifted, so to speak, by the shift transmission element 102.

[0109] At this point, it should be mentioned that the toothing between the gearshift elements 102, 103 or ring gears 61, 62 is not absolutely necessary. For example, the gearshift element 102 can adjust the gearshift element 103 merely in the direction of a housing-fixed or stationary positive-locking counter-contour 91, in particular on the end wall 46, so that an anti-rotation contour 92 of the gearshift element 103 can adjust the positive-locking counter-contour 91 into an engagement that holds the gearshift element 103 in a rotationally secure manner with respect to the transmission support structure, i.e., the transmission housing 44 ( Figure 13 ). The anti-rotation contour 92 is, for example, a positive-lock projection running parallel to the adjusting axis SA, and the positive-lock counter-contour 91 is a corresponding positive-lock receptacle, for example, a blind hole. However, toothing as anti-rotation contours or positive-lock counter-contours is advantageous.

[0110] Thus, no direct coupling is required between the actuating device 100, and in particular its actuating member 110, and the shift transmission element 103 in order to shift the gear arrangement 105. This simplifies the design of the actuating device 100. The transmission 40 is shorter. Furthermore, this results in simple and convenient handling of the actuating device 100, which will become clearer below.

[0111] The actuating device 100 comprises the actuating member 110 with an actuating handle 111. The actuating handle 111 is arranged in an opening 33 on a top wall 34 of the housing 11 of the hand-held power tool 10 and is thus easily accessible to an operator.

[0112] On the housing 11, for example, at the edge areas of the opening 33, numbers 1, 2, 3 and 4 or other markings 35 can be arranged, which are assigned to the respective switching positions S1, S2, S3 and S4. The actuating handle 111 is displaceable and / or pivotable within the opening 33. The actuating handle 111 can be adjusted into the area of ​​a respective marking 35, in this case into respective corner areas of the opening 33, in order to set the switching positions S1, S2, S3 and S4. It is possible to directly switch or set the actuating handle 111 from any of the switching positions S1, S2, S3 and S4 to any other of the switching positions S1, S2, S3 and S4, without setting an intermediate switching position. For example, the transmission 40 can be switched directly from the switching position S1 (actuating handle 111 is in Figure 7 shown in dashed lines) into the switching position S4 (operating handle 111 is in Figure 7shown in solid lines) without moving to one of the intermediate switching positions S2 or S3.

[0113] The actuating handle 110 is provided on an upper side 114 of a particularly barrel-shaped or curved wall body 112, the underside 113 of which faces the gear housing 44. A curvature of the wall body 112 approximately corresponds to a curvature of the peripheral wall 45 of the gear housing 44, so that the wall body 112 is movable along the peripheral wall 45 in the manner of a cover or cover part or wall section.

[0114] The actuating member 110 is arranged on a drive ring 120, which in turn is pivotably or rotatably mounted on the transmission housing 44, in particular on the outer circumference of the peripheral wall 45, about a pivot axis MA, which preferably coincides with the rotational axis D of the transmission output 42. As a result, the actuating member 110 can pivot about the pivot axis MA and thus an actuating pivot axis BS between actuating positions D1 and D2.

[0115] The driving ring 120 has an annular body 121, which is rotatably mounted in an annular guide 145 of the gear housing 44. The annular body 121 is guided on its narrow sides, for example, by circumferential projections 146 that protrude in front of the circumferential wall 45.

[0116] A linear guide 123 for the actuating member 110 is provided at free longitudinal end regions 122 of the driving ring 120, so that the latter is displaceably mounted on the driving ring 120 along an actuating longitudinal axis BL between actuating positions L1 and L2.

[0117] The linear guide 123 comprises linear guide sections 124 arranged directly at the longitudinal end regions 122, which are angularly spaced from one another according to the angular distance between the longitudinal end regions 122. Thus, the actuating member 110 is, so to speak, a connecting member or link that connects the longitudinal end regions 122 of the driving ring 120 to one another.

[0118] On the underside 113 of the actuating member 110, linear guide projections 115 are provided which engage in the linear guide sections 124.

[0119] In principle, the longitudinal end regions 122 of the driving ring 120 already have such a width or length with respect to the longitudinal actuating axis BL that they are sufficient for linear guidance of the actuating member 110. Furthermore, the actuating member 110 can be guided in guide recesses, for example grooves, on the outer circumference, for example, the longitudinal sides and / or transverse sides, of the recess or opening 33 of the top wall 34.

[0120] However, additional and improved support is provided by support projections 129, which protrude in front of the longitudinal end regions 122 of the driving ring 120 with respect to the longitudinal actuation axis BL or the rotational axis D. Further linear guide sections 125 are provided on the support projections 122, into which the linear guide projections 115 engage and through which the linear guide projections 115 are guided with respect to the longitudinal actuation axis BL. The linear guide sections 124, 125 are, for example, longitudinal grooves whose transverse width with respect to the longitudinal actuation axis BL approximately corresponds to a transverse width of the linear guide projections 115.

[0121] Now, an embodiment could provide that guide slots in the manner of the guide slots 133 explained below are provided on the longitudinal end regions 122 of the driving ring 120, with which a first coupling element 140, which in turn is connected to the switching transmission element 101 and thus to the ring gear 78, can be driven.

[0122] However, the guide slots 133 are provided on a transmission member 130, which in turn is rotatable relative to the actuating pivot axis BS or a rotational axis of the drive ring 120. The transmission member 130 has an annular body 131, whose longitudinal end regions 132 are configured, for example, in the manner of plate bodies. Between the longitudinal end regions, an annular recess 137 is provided on the annular body 131, i.e., a space between annular sections 138 extending between the longitudinal end regions 132.

[0123] The transmission member 130 is arranged in an interior space of the driving ring 120. A driver 136 projects in front of a radial outer circumference of the annular body 132 and is motionally coupled to a driver 126 of the driving ring 120. A fixed coupling would also be possible here. However, the driver 126 is mounted displaceably or pivotably on the driving ring 120. The driver 126 is movably mounted in a slotted guide 127 of the driving ring 120. The slotted guide 127 extends annularly on the driving ring 120. It is provided on the annular body 121. The driver 126 projects radially inward in front of the annular body 121 so that it can engage with the driver 136. For example, a plug-in connection is provided between the drivers 126, 136. The link 127 is therefore arcuate or ring-shaped and extends around the pivot axis MA of the driving ring 120, around which the driving ring 120 pivots with respect to the gear housing 44.

[0124] The driver 126 is spring-loaded by a spring arrangement 128, for example, a helical spring. Thus, when the driver ring 120 is pivoted about the pivot axis MA, the driver 126 is moved along with it, so that, supported by the spring arrangement 128, this rotational movement or rotational force is transmitted to the transmission member 130, which ultimately converts the rotational movement into a linear movement for the coupling element 140 and the shift transmission element 101.

[0125] The coupling element 140 is formed, for example, by a spring clip 141. Longitudinal ends 142 of the coupling element 140 protrude radially outward in front of an annular portion of the coupling element 140 and engage, like guide followers, in the guide guides 133. The guide guides 133 are, for example, inclined guides. A coupling element receptacle 143, for example, an annular groove, is provided radially on the outside of the manual transmission element 101, into which the coupling element 140 engages, particularly with the annular portion 144. The resilient longitudinal ends 142 of the coupling element 140 also provide a certain spring property, so that the spring arrangement 128 could ultimately be omitted. On the ring guide 145, into which the ring body 131 and thus the transmission member 130 also engage, a recess 147 can be provided for the longitudinal end regions 132 of the transmission member 130, which represents a certain locking effect.

[0126] The longitudinal ends 142 of the coupling element 140, which is arranged in the interior of the gear housing 44, protrude through recesses or longitudinal grooves 72 in front of the peripheral wall 45 and engage in the guide slots 133. Thus, when the actuating member 110 pivots about the actuating pivot axis BS, the driving ring 120 also pivots simultaneously about the pivot axis MA, wherein this pivoting movement is deflected by a deflection gear 135, which includes, among other things, the guide slots 133 and the coupling element 140 and in particular its longitudinal ends 142, into a linear actuating movement for the actuating element 101 between the actuating positions P3 and P4.

[0127] Unlike in the exemplary embodiment, the transmission of the linear movement of the transmission element 110 relative to the longitudinal actuation axis BL could, in principle, be directly transferred into a linear actuation movement of a second coupling element 150, which is arranged between the actuation element 110 and the shift transmission element 102. In the present case, however, the coupling element 150 is pivotally mounted about a pivot axis S, so that a linear adjustment of the actuation element 110 along the longitudinal actuation axis BL in one direction is redirected into a linear adjustment of the actuating transmission element 102 in an opposite direction.

[0128] The coupling element 150 comprises a spring clip 159. The coupling element 150 comprises an actuating portion 151, which engages in a guide receptacle 116 on the underside 113 of the actuating member 110. Furthermore, the actuating portion 151 is received in a recess 124A between the linear guide portions 124, 125 of the drive ring 120.

[0129] The spring clip 159 or the coupling element 150 is pivotally mounted on the gear housing 44 about the pivot axis S. The pivot axis S is located between the actuating section 151 and driving projections 154 at the free end regions of the coupling element 150. Between the driving projections 154, bearing receptacles 157 are formed on the coupling element 150, into which bearing pins 156 engage, which project radially outward in front of the gear housing 44 or the peripheral wall 45. The bearing receptacles 157 are located between actuating sections 152 and driving sections 153 of the coupling element 150. The actuating sections 152, 153 are, so to speak, lever arms that protrude from the pivot axis S.

[0130] The driving projections 154, which are, for example, thin wire ends, engage in driving recesses 155 of the gearshift element 102, thus of the ring gear 62. For example, bores or, as in the exemplary embodiment, grooves are provided as driving recesses 155.

[0131] The second coupling element 150 extends arcuately around the manual transmission element 102, but is only in contact with the manual transmission element 102 in the region of the driving projections 154. In contrast, the coupling element 140 is annular due to its ring section 144 and engages with the manual transmission element 101 over a greater length.

[0132] In contrast to the coupling element 140, the coupling element 150 is arranged outside the transmission housing 44. Its driving projections 154 extend radially inward relative to the actuating pivot axis BS or the pivot axis MA in front of the driving sections 153 and penetrate recesses 158 on the transmission housing 44 or peripheral wall 45, so that they engage with the driving recesses 155 of the ring gear 62 or the switching transmission element 102.

[0133] The actuating device 100 can also be locked by a locking arrangement 160. The locking arrangement 160 comprises a locking member 161, which can engage in locking recesses 164 on the actuating member 110, for example, on the underside 113 of the wall body 112. The locking member 161 is spring-loaded by a spring 162 into its locking position engaging in the locking recesses 164. The spring 162 and preferably also the locking member 161 are received and / or guided in a receptacle or on a receptacle 163 of the transmission housing 44, for example, a cylindrical receptacle. Each locking recess 164 is assigned to one of the switching positions S1, S2, S3, and S4 of the transmission 40.

[0134] The operator can move the actuating element 110 into the actuating position associated with the respective switching positions S1 - S4 with respect to the actuating longitudinal axis BL and the actuating pivot axis BS, in which position a locking action is advantageously possible. The actuating element 110 can, for example, be locked and / or positioned in the actuating positions L1, D1 for setting the switching position S1, in the actuating positions L2, D2 for setting the switching position S2, in the actuating positions L1, D2 for setting the switching position S3, and finally in the actuating positions D2, L2 for setting the switching position S4.

[0135] The drive ring 120 follows the movement of the actuating member 110 about the actuating pivot axis BS. The spring arrangement 128 decouples the actuating movement from the actual actuating movement.

[0136] However, a springing action is also provided with respect to the coupling element 150. For example, the driving sections 153 can be springy or resiliently yielding with respect to the actuating sections 151 and / or 152. This is achieved, on the one hand, by the design of the coupling element 150 as a spring clip 159. However, it is also further facilitated or improved by the fact that the bearing receptacle 157 is formed by a winding of the spring clip 159, so that the driving sections 153 are springy relative to the driving actuating sections 152 with respect to the pivot axis S.

[0137] In Figure 15It is indicated that the switching transmission element 102 can also, in principle, serve to non-rotatably couple the gear wheel assemblies 104 and 105 to one another. For example, in a setting position P2B, the switching transmission element 102 is simultaneously non-rotatably engaged with both gear wheel assemblies 104 and 105 and can rotate within the transmission support structure 44A or the transmission housing 44. Thus, the switching transmission element 102 forming the switching actuator is simultaneously engaged with both gear wheel assemblies 104 and 105. To ensure the rotational freedom of the switching transmission element 102, an annular groove or similar other recess can be provided in the transmission housing 44, for example.

[0138] The spring clip 159 or the coupling element 150 is pivotally mounted on the transmission housing 44 about the pivot axis S, so that a respective sliding actuation of the actuating member 110 in a first direction is redirected into an opposite linear movement of the manual transmission element 102. However, it would be possible, for example, for the coupling element 150 to be rigidly coupled to the actuating member 110, so that the aforementioned reversal of movement does not occur, or, in other words, for the movement directions of the actuating member 110, the coupling element 150, and the manual transmission element 102 to run in the same direction.

[0139] It is possible that with the same setting positions of the actuating member 110 the same gear ratios are possible as in the configuration described above, if the gear 40 is configured, for example, as follows and in Figure 14schematically indicated modified. In this configuration, for example, the planet gears 52 are arranged on the planet gear carrier 53 such that the smaller rolling circumference 63 is closer to the carrier body 54 than the larger rolling circumference 64. This is indicated by a planet gear 52B, which is arranged on the planet gear carrier 53 rotated by 180°, so to speak, like the planet gear 52. If the radially inner ring gear 61 meshing with the smaller rolling circumference 63 is also arranged closer to the carrier body 54 (which is the case with a ring gear 61B in Figure 14 indicated), the gear ratios that can be adjusted by linearly adjusting the ring gear 62 between the setting positions P1 and P2 are exactly the opposite of those in the embodiment described above.

Claims

1. Manual machine tool having a drive motor, a gearbox and a tool holder, wherein a motor drive of the drive motor with a gearbox drive of the gearbox and a gearbox of the drive that is rotatable about an axis of rotation are coupled to the tool holder in a manner which permits rotation, wherein the gearbox has a first switching gear element (101) and a second switching gear element (102), which can be adjusted in a linear manner by means of an actuating device (100) in each case between a first setting position and a second setting position relative to a gearbox housing, wherein the actuating device (100) is coupled to the switching gear elements and has an actuating part (110) which is pivotably mounted relative to a machine housing of the manual machine tool about an actuating pivot axis and can be actuated manually by an operator of the manual machine tool, wherein the first switching gear element (101) can be adjusted in a linear manner along its setting axis by means of a pivot movement of the actuating part (110) about the actuating pivot axis using a deflecting gear (135), wherein the deflecting gear (135) comprises a carrier element (120) which extends in a ring-shaped manner around the gearbox housing and is rotatably mounted about the actuating pivot axis, which carrier element is coupled to the first switching gear element (101) to enable the linear adjustment of this by means of a first coupling element (140), wherein the actuating part (110) is mounted in a manner which permits the linear displacement on the carrier element (120) along an actuating longitudinal axis and is coupled to the at least one second switching gear element (102) by means of a second coupling element (150) to enable the linear displacement of the second switching gear element (102), charcaterised in that the carrier element (120) is a carrier ring (120) and that between the carrier ring (120) and the first coupling element (140) an, in particular ring-shaped, transmission part (130) that can moved together with the carrier ring (120) about the actuating pivot axis, is arranged, wherein the transmission part (130) and the carrier ring (120) can be moved relative to one another and between the transmission part (130) and the carrier ring (120) a spring arrangement (128) actuable by a relative movement of the transmission part (130) and the carrier ring (120) is arranged for spring loading of the first setting gear element in at least one switch position.

2. Manual machine tool according to any one of the preceding claims, characterised in that at least one spring arrangement (128) is arranged between the actuating part (110) and the first switching gear element (101) and / or the second switching gear element (102), wherein it is advantageously provided that the spring arrangement between the second switching gear element (102) and the actuating part (110) is in particular exclusively provided by the second coupling element.

3. Manual machine tool according to any one of the preceding claims, characterised in that the first coupling element (140) and / or the second coupling element (150) is or comprises a spring element.

4. Manual machine tool according to any one of the preceding claims, characterised in that the first coupling element (140) and / or the second coupling element (150) is a spring bow (141, 159) or comprises a spring bow (141, 159), wherein the spring bow (141, 159) extends in a ring-shaped manner about the first switching gear element (101) or the second switching gear element (102).

5. Manual machine tool according to any one of the preceding claims, characterised in that the actuating part (110) is coupled to the second switching gear element (102) exclusively by means of the second coupling element (150) and / or by means of a single component.

6. Manual machine tool according to any one of the preceding claims, charcaterised in that at least one guide cam is arranged on the carrier ring (120) or a transmission part (130) that can be moved together with the carrier ring (120) about the actuating pivot axis, in which the first coupling element (140) engages in order to deflect the movement of the actuating part (110) about the actuating pivot axis into a linear movement of the first setting gear element.

7. Manual machine tool according to any one of the preceding claims, characterised in that the second coupling element (150) is pivotably and / or displaceably mounted relative to the gearbox housing.

8. Manual machine tool according to any one of the preceding claims, characterised in that the second coupling element (150) is pivotably mounted on a pivot bearing provided on a gearbox housing, in particular a bearing pin which protrudes from a circumference wall of the gearbox housing or a bearing recess arranged in the circumference wall of the gearbox housing, and / or on the actuating part (110).

9. Manual machine tool according to any one of the preceding claims, characterised in that the second coupling element (150) engages in a guide recess of the actuating part (110) extending in an arc-shape about the actuating pivot axis and / or arranged at a distance about the actuating pivot axis.

10. Manual machine tool according to any one of the preceding claims, characterised in that it has a locking arrangement (160) for locking the actuating part (110) in at least one actuating position.

11. Manual machine tool according to any one of the preceding claims, characterised in that the actuating part (110) is mounted linearly dispaceably on a linear guide (123) of the carrier ring (120) and / or a machine housing of the manual machine tool, wherein it is advantageously provided that the second coupling element (150) is received in a slot (124A) of the linear guide (123) and / or that the linear guide (123) comprises at least two linear guide sections (123) arranged at an angular distance from one another relative to the actuating pivot axis.

12. Manual machine tool according to any one of the preceding claims, characterised in that the actuating part (110) connects longitudinal end areas of the carrier ring (120) that are at a distance from one another to one another.

13. Manual machine tool according to any one of the preceding claims, characterised in that the actuating part (110) has an arch-shaped or barrel-shaped wall design and / or the actuating part (110) connects longitudinal end areas of the carrier ring (120) that are at a distance from one another to one another14. Manual machine tool according to any one of the preceding claims, characterised in that the gearbox is a planetary gear and / or the first and / or second setting gear element is or comprises a hollow wheel (61, 62, 78).

15. Manual machine tool according to any one of the preceding claims, characterised in that the gearbox can be switched between at least two switch positions (S1, S2, S3, S4) in which the speed ratios between the gearbox drive and the gearbox output are different to one another, wherein the gearbox comprises a first gear wheel arrangement (104) and at least a second gear wheel arrangement (105), each of which has at least one gear wheel and a switching gear element, of which one is a switch actuator and the other the switching gear element that can be switched by the switch actuator, wherein the two gear wheel arrangements (104, 105) can roll the at least one gear wheel on the switching gear element of the gear wheel arrangement (104, 105) and / or the switching gear element on the at least one gear wheel of the gear wheel arrangement (104, 105) and the respective switching gear element is mounted in a locally adjustable manner between at least two setting positions in order to adjust the switch positions (S1, S2, S3, S4) of the gearbox on the gearbox holding structure (44A) and / or is adjustable between an immobile position and a mobile position relative to the gearbox holding structure (44A), and in order to switch the gearbox between at least two of the switch positions (S1, S2, S3, S4) the switching gear element (102) of the first gear wheel arrangement (104) forms a switch actuator for the second gear wheel arrangement (105) which can be switched between a first setting position and at least a second setting position, in which a movement of the switching gear element (103) of the second gear wheel arrangement (105) is different relative to the gearbox holding structure and / or the switch actuator is disengaged and engaged with the at least one gear wheel (105A) of the second gear wheel arrangement (105).