Tool device and method

Abstract

The invention relates to a tool device (1), in particular a saw device, comprising a stationary part (3), in particular a support part for supporting a workpiece, and a shifting part (7) which has a tool (4), in particular a saw blade, and which can be shifted relative to the stationary part (3) and in the process carries out a shifting movement (8) in order to set a position, in particular an angular position, of the tool (4) relative to the stationary part (3), further comprising a guide means (16) which is designed to guide the shifting part (7) relative to the stationary part (3) during the shifting movement (8), wherein the guide means (16) comprises a guide structure (18) that defines a movement path (17), and a guide part (20) that rests on a guide contour (19) of the guide structure (18) and that can be moved along the movement path (17) relative to the guide structure (18) in order to carry out the shifting movement (8). The tool device (1) comprises a pressing mechanism (21) which has a spring element (22) and which is designed to press, on the basis of a spring force (23) provided by the spring element (22), the guide part (20) against the guide structure (18) with a pressing force (24), in order to reduce or eliminate play between the guide part (20) and the guide structure (18) along the movement path (17).

Description

[0001] Festool GmbH , Wertstraße 20 , 73240 Wendlingen am Neckar

[0002] Tool device and method

[0003] The invention relates to a tool device, in particular a sawing device, comprising a stationary section, in particular a support section for supporting a workpiece, and an adjustment section having a tool, in particular a saw blade, which is adjustable by carrying out an adjustment movement relative to the stationary section in order to set a position, in particular an angular position, of the tool relative to the stationary section, further comprising a guide device which is designed to guide the adjustment section during the adjustment movement relative to the stationary section, wherein the guide device comprises a guide structure defining a movement path and a guide section which is in contact with a guide contour of the guide structure and which is movable relative to the guide structure along the movement path in order to carry out the adjustment movement.The adjustment movement is, for example, a swivel movement and the guide structure serves in particular to define a virtual swivel axis for the adjustment movement.

[0004] In conventional mobile or semi-stationary table saws, the angular position of the saw blade is usually set purely mechanically (i.e., in particular without an electric motor) via a user operation, for example, using a first control element. After setting the angular position, the user must clamp the saw blade in the set angular position via a further user operation, for example, using a second control element. Clamping generally also serves to reduce or eliminate any play that occurs in a radial direction of the angle setting. One such approach is explained in US2019366577A1.

[0005] One object of the invention is to provide an easy-to-use tool device that enables safe and precise machining of the workpiece.

[0006] The object is achieved by a tool device according to claim 1. The tool device comprises a pressing mechanism having a spring element, which is designed to press the guide section against the guide structure with a pressing force on the basis of a spring force provided by the spring element in order to reduce or eliminate play between the guide section and the guide structure, in particular the guide contour, along the movement path.

[0007] By reducing or eliminating the play, safe and precise machining of the workpiece can be made possible. The contact pressure is directed in particular in a radial direction in relation to the (in particular virtual) pivot axis of the adjustment movement, so that play in particular in this radial direction is reduced or eliminated. The contact pressure mechanism achieves the reduction or elimination of the play automatically - i.e. without any separate user operation (e.g. to trigger a clamping mechanism), as is often required with a conventional tool device. The tool device is therefore easy to operate. The tool is preferably fixed in the direction of the movement path by a self-locking drive device which serves to drive the adjustment section in order to set the adjustment section in the adjustment movement.

[0008] Preferably, therefore, no separate user action (for example to trigger a clamping mechanism) is required to fix the tool in the desired position, in particular the angular position.

[0009] Further exemplary details and exemplary embodiments are explained below with reference to the figures.

[0010] Figure 1 is a perspective view of a tool device designed as a sawing device,

[0011] Figure 2 is a block diagram of components of the tool device,

[0012] Figure 3 is a perspective view of an adjustment section, a guide device and a drive device of the tool device,

[0013] Figure 4 is a side view of a first end of the adjustment section,

[0014] Figure 5 is a perspective view of a guide section of the tool device,

[0015] Figure 6 shows a pressing arrangement of the tool device,

[0016] Figure 7 shows a lever element of the pressing arrangement, and Figure 8 shows a side view of a second end of the

[0017] adjustment section.

[0018] Reference is made below to the x-direction, y-direction, and z-direction shown in the figures, which are preferably aligned orthogonally to one another. The x-direction and the y-direction are (in a proper orientation of the tool device 1) horizontal directions. The z-direction is a vertical direction and, for example, points upwards.

[0019] Figure 1 shows a tool device 1 which is designed as an example as a sawing device, in particular as a table saw. The tool device 1 is designed in particular as a semi-stationary tool device 1. A semi-stationary tool device is a tool device which, during operation - that is to say when machining a workpiece - is stationary on a base, for example a workbench or a table, and which is designed in such a way (in particular with regard to its weight and / or its dimensions) that it can be carried by a single person. The tool device can also be designed as a hand-held circular saw or as a miter saw. Furthermore, the tool device can be designed as a tool device different from a sawing device, for example as a milling machine.

[0020] By way of example, the tool device 1 has a support structure 2, with the underside 5 of which the tool device 1 can be conveniently placed on the base. The support structure 2 has, for example, a substantially cuboidal basic shape. The support structure 2 expediently comprises the outer housing (or at least part of the outer housing) of the tool device 1.

[0021] The tool device 1 comprises a stationary section 3, which is designed, for example, as a support section for supporting a workpiece. The support section is, for example, a support table and in particular has a preferably horizontally aligned support surface. The support section serves to support the workpiece while it is being machined with a tool 4 of the tool device 1. The stationary section 3 is, for example, part of the support structure 2. For example, the stationary section 3, in particular the support section, is formed by the upper side of the support structure 2. In a state in which the tool device 1 is placed stationary on a base, the stationary section 3 is expediently stationary with respect to the base.

[0022] The tool 4 is designed, for example, as a saw blade, in particular as a circular saw blade. For example, an opening 6 is provided in the support section, through which the tool 4 extends, in particular from inside the support structure 2 through the opening 6 to the outside of the support structure 2, for example upwards over the support section. The opening 6 is provided, for example, in a panel 11. The tool 4 is arranged in the region of the support section, so that a workpiece placed on the support section can be machined with the tool 4.

[0023] The tool 4 expediently defines a feed direction 10 in which the workpiece is to be moved toward the tool 4 (for example, manually by a user) in order to machine the workpiece with the tool 4. The feed direction 10 expediently runs parallel to the saw blade plane and / or parallel to the support surface. The feed direction 10 is oriented, for example, parallel to the x-direction.

[0024] The tool device 1 expediently comprises an operating device 25, which is arranged, for example, on the outside of the support structure 2, in particular on a front side of the support structure 2. The operating device 25 preferably comprises an input unit 26 and / or a display unit 27. The input unit 26 can, for example, comprise a rotary knob, in particular a rotary push button. The input unit 26 serves, in particular, to set a position, in particular an angular position, of the tool 4 relative to the stationary section 3, for example by inputting (by the user) a position value representing the position. The angular position, in particular the position value, is, for example, an angle of inclination or miter angle of the tool 4. The display unit 27 is, for example, designed as a graphic display and is designed, in particular, to display the position, for example the position value.

[0025] Figure 2 shows a block diagram of a drive arrangement 28 of the tool device 1. The drive arrangement 28 comprises the operating device 25, a control unit 29, designed for example as a microcontroller, a drive unit 15 and / or a drive device 30. The control unit 29 is expediently communicatively connected to the operating device 25, the drive unit 15 and / or the drive device 30. The control unit 29 is expediently designed to control the drive unit 15 and / or the drive device 30, in particular in accordance with an input made by a user via the operating device. The control unit 29, the drive unit 15 and / or the drive device 30 is expediently arranged within the outer housing of the tool device 1.The drive unit 15 expediently comprises a first electric motor and serves, in particular, to set the tool 4 in a machining movement in which the workpiece can be machined, for example, sawn, by the tool. The drive device 30 expediently comprises a second electric motor and serves, in particular, to set the tool 4 in an adjusting movement 8 in order to thereby adjust the position, in particular the angular position, of the tool 4 relative to the stationary section 3.

[0026] The tool device 1 expediently comprises an adjustment section 7 and / or a guide device 16. Figure 3 shows a perspective view of a structure comprising the adjustment section 7, the guide device 16, and the drive device 30. By way of example, the adjustment section 7 is aligned with its longitudinal axis in the x-direction.

[0027] The adjustment section 7 expediently comprises the tool 4. By way of example, the adjustment section 7 further comprises a riving knife 9, which is expediently arranged behind the tool 4 in the feed direction 10. The adjustment section 7 further expediently comprises a saw blade cover 12, which is arranged in particular below the panel 11 and serves to cover the part of the saw blade located in the support structure 2. The saw blade cover 12 is, for example, a cassette for receiving the saw blade. By way of example, the saw blade can be moved within the cassette in a vertical direction, in particular in the z-direction, in order to adjust a height of the saw blade.By way of example, the adjustment section 7 further comprises a suction channel 13, which can expediently be subjected to a negative pressure (for example, by connecting the tool device 1 to a suction unit) in order to extract particles generated by machining carried out with the tool 4. The suction channel 13 is expediently in fluid communication with an interior of the saw blade cover 12 and is arranged, by way of example, at the bottom of the saw blade cover 12.

[0028] Preferably, the adjustment section 7 further comprises a drive shaft 14 coupled to the tool 4, via which the tool 4 can be driven to perform the machining movement. The machining movement is, for example, a rotary movement about an axis of rotation running perpendicular to the feed direction 10, in particular the axis of rotation of the drive shaft 14. Preferably, the adjustment section 7 further comprises the drive unit 15, which serves to set the tool 4 in the machining movement, in particular via the drive shaft 14.

[0029] The adjustment section 7 is adjustable by carrying out the adjustment movement 8 relative to the stationary section 3 in order to set the position, in particular the angular position, of the tool 4 relative to the stationary section 3. Expediently, the angle of inclination or miter angle of the tool 4 can be adjusted via the adjustment movement 8. Preferably, during the adjustment movement 8 of the adjustment section 7, all components of the adjustment section 7 - that is to say in particular the tool 4, the riving knife 9, the saw blade cover 12, the extraction channel 13, the drive shaft 14 and / or the drive unit 15 - carry out the adjustment movement 8. The adjustment movement 8 is expediently a rotary movement, in particular a pivoting movement, preferably in a y-z plane. The adjustment movement expediently takes place about a (in particular virtual) pivot axis, which expediently runs parallel to the feed direction 10.The pivot axis expediently runs parallel to the sawblade plane and / or parallel to the support surface. Preferably, the (in particular virtual) pivot axis is aligned in the x-direction. The term "virtual pivot axis" refers to an imaginary pivot axis. The pivot axis is expediently defined by the guide device 16. The angular position to be set is, in particular, the angular position of the sawblade plane relative to the support surface.

[0030] The drive device 30 is designed, for example, as a linear drive, in particular as a spindle drive. The drive device 30 is designed, in particular, to be self-locking. For example, the drive device 30 comprises a rotary drive 31 (in particular the aforementioned second electric motor) and a spindle 32 which can be driven via the rotary drive 31. The drive device 30 further comprises a drive element 33, for example a spindle nut, arranged on the spindle 32. The drive element 33 is coupled to the adjustment section 7, in particular fastened thereto, so that the adjustment section 7 can be set into the adjustment movement 8 by a movement (brought about by the rotary drive 31), in particular a linear movement, of the drive element 33. The linear movement expediently takes place in a y-z plane. The rotary drive 31 is expediently fastened to the stationary section 3.Figure 4 shows a side view of the adjustment section.

[0031] 7 , the guide device 16 and the drive device 30 .

[0032] The guide device 16 is designed to guide the adjustment section 7 during the adjustment movement 8 relative to the stationary section 3. The guide device 16 comprises a guide structure 18 which defines a movement path 17. By way of example, the movement path is in the shape of a circular arc. The guide device 16 further comprises a guide section 20 which bears against a guide contour 19 of the guide structure 18 and which can be moved along the movement path 17 relative to the guide structure 18 in order to carry out the adjustment movement 8. The movement path 17 expediently lies in a y-z plane; the movement path 17 therefore expediently has no x component. The movement path 17 is defined in particular by the guide contour 19.

[0033] During the adjustment movement 8, the guide section 20 moves relative to the guide structure 18, specifically along the movement path 17. The guide section 20 preferably carries out the adjustment movement 8. The guide section 20 is preferably part of the adjustment section 7 or is fastened to the adjustment section 7, so that the guide section 20 carries out the adjustment movement 8 as part of the adjustment section 7 or together with the adjustment section 7. The guide structure 18 is preferably part of the stationary section 3 or is fastened to the stationary section 3, for example a housing of the tool device 1, in particular the outer housing. By way of example, the guide structure 18 is stationary relative to the stationary section 3 during the adjustment movement 8. According to an alternative embodiment (not shown in the figures), the guide structure is part of the adjustment section and the guide section is part of the stationary section.In this embodiment, too, a relative movement of the guide section relative to the guide structure along the movement path takes place in order to carry out the adjustment movement; in this case, the guide structure carries out the adjustment movement 8 and not the guide section.

[0034] The tool device 1 further comprises a pressing mechanism 21 which has a spring element 22 which is exemplified as a helical spring. The pressing mechanism 21 is designed, on the basis of a spring force 23 provided by the spring element 22, to press the guide section 20 against the guide structure 18 with a pressing force 24 in order to expediently reduce or eliminate play between the guide section 20 and the guide structure 18 along the movement path 17, in particular during the adjustment movement 8 and / or during the machining movement - that is to say in particular during the machining of the workpiece with the tool 4.

[0035] The play to be eliminated or reduced includes, in particular, play in the radial direction with respect to the movement path 17. The radial direction expediently lies in a y-z plane and is oriented radially with respect to the (in particular virtual) pivot axis of the adjustment movement 8. Expediently, the radial direction crosses the (in particular virtual) pivot axis.

[0036] The pressing mechanism 21 serves in particular to ensure that the guide section 20 rests against the guide structure 18, in particular the guide contour 19, along the movement path 17 - in particular along the entire movement path 17 - in particular permanently, preferably with a constant frictional force. The pressing mechanism 21 preferably ensures that the guide section 20 rests constantly against the guide structure 18 in every possible position along the entire movement path 17, so that there is no play between the guide section 20 and the guide structure 18, in particular in the radial direction with respect to the movement path 17. The pressing force 24 is preferably aligned in the radial direction with respect to the adjustment movement 8 and / or the movement path 17. By way of example, the pressing force 24 is directed in the radial direction away from the (in particular virtual) pivot axis of the adjustment movement 8.The contact force 24 is oriented in particular perpendicular to the pivot axis and / or the feed direction 10. The direction of the contact force 24 is expediently in the same plane as the adjustment movement 8.

[0037] The pressing mechanism 21 is preferably designed to press the guide section 20 against the guide structure 18 along the entire movement path 17 with the pressing force 24 in order to reduce or eliminate play between the guide section 20 and the guide structure 18 along the entire movement path 17. The maximum approachable movement path 17 of the guide section 20 relative to the guide structure 18 is referred to as the entire movement path 17. The pressing mechanism 21 is preferably designed to provide a substantially constant pressing force 24 along the movement path 17, in particular the entire movement path 17.

[0038] By way of example, the guide structure 18 comprises a plate-shaped section which is expediently aligned with its plate plane normal to the x-direction, i.e. by way of example normal to the (in particular virtual) pivot axis of the adjustment movement 8 and / or normal to the feed direction 10. By way of example, the guide structure 18, in particular the plate-shaped section, comprises a recess 35, in particular in the shape of a circular arc. The guide section 20 is expediently guided in the recess 35. The recess 35 has an inner edge and / or inner surface, in particular a lower inner edge and / or lower inner surface, which expediently forms the guide contour 19 against which the guide section 20 is pressed with the contact force 24.

[0039] The pressing mechanism 21 preferably comprises a pressing section 34 which bears against a counter-contour 36 of the guide structure 18. The counter-contour 36 is expediently formed by an outer edge and / or outer surface, in particular a lower outer edge and / or lower outer surface, of the guide structure 18, in particular of the plate-shaped section. The counter-contour 36 is expediently circular-arc-shaped and in particular concentric to the guide contour 19. The pressing section 34 is pressed against the counter-contour 36 by a counter-force 42 caused by the spring force 23.

[0040] The guide structure 18 comprises a structural section 37, in particular one which is in the shape of a circular arc and which has the guide contour 19 and / or the counter-contour 36. By way of example, the guide contour 19 is arranged on a first side - by way of example the upper side - of the structural section 37 and the counter-contour 36 is arranged on a second side opposite the first side - by way of example the lower side - of the structural section 37. The pressing section 34 is resiliently coupled to the guide section 20 by means of the spring element 22, so that due to the spring force 23 the pressing section 34 is pressed against the counter-contour 36 and the guide section 20 (due to the spring force 23) is pressed against the guide contour 19. The spring force 23 expediently causes the structural section 37 to be clamped between the guide section 20 and the pressing section 34, in particular in the radial direction with respect to the adjustment movement 8.The spring force 23 forces the guide section 20 and the pressing section 34 toward one another, thereby pressing each against the structural section 37 located between the guide section 20 and the pressing section 34. Preferably, the pressing section 34 is prestressed against the guide contour 19 by the spring element 22, whereby the guide section 20 is prestressed against the counter contour 36.

[0041] By way of example, the pressing mechanism 21 comprises a pressing arrangement 38 which comprises the pressing section 34. The spring element 22 is arranged between a supporting section 39 of the pressing arrangement 38 and a supporting point of a coupling section 40. In particular, the spring element 22 is supported at one end on the supporting section 39 and at the supporting point with the other end, so that the spring element 22 presses the supporting section 39 and the supporting point away from one another - in particular in opposite directions - with its spring force 23. The coupling section 40 is connected to the guide section 20. The coupling section 40 is preferably part of the adjusting section 7. The guide section 20 is expediently pressed against the guide structure 18, in particular against the guide contour 19, via the coupling section 40 by the spring force 23.The spring element 22 is exemplary on the second side - i.e. exemplary the lower side - of the structural section.

[0042] 37. The guide section 20 is arranged, for example, on the first side - that is, for example, the upper side - of the structural section 37. The coupling section 40 runs from the spring element 22 - in particular from the end of the spring element 22 facing away from the structural section 37 - towards the guide section 20, in particular vertically upwards, preferably past the structural section 37, in particular horizontally offset past the structural section 37.

[0043] Preferably, the pressing arrangement 38, in particular the pressing section 34, has a roller 41 which bears against the counter-contour 36 and can roll on this. By way of example, the pressing section 34 is designed as the roller 41. The roller 41 rolls on the counter-contour 36 during the adjustment movement 8. The roller 41 is pressed against the counter-contour 36 with the counter-force 42. The roller 41 comprises, for example, a ball bearing and / or is rotatably mounted via a ball bearing, for example on a lever element 43 of the pressing arrangement

[0044] 38 .

[0045] Optionally, the pressing arrangement, in particular the pressing section, comprises at least one stripping section (not shown in the figures) which rests against the counter-contour in order to remove impurities from the counter-contour. For example, stripping sections can be attached in front of and behind the roller (in the direction of the movement path), in particular on the lever element of the pressing arrangement. During the adjusting movement, the stripping sections free a rolling surface of the counter-contour of impurities (for example sawdust). In this way, the freedom of movement of the angular adjustment - that is to say the freedom of movement of the adjusting section 7 during the adjusting movement 8 - can be improved.

[0046] The pressing mechanism 21, in particular the pressing arrangement 38, preferably has a lever element 43, by means of which the spring force 23 is converted into the pressing force 24, in particular in such a way that the pressing force 24 is greater than the spring force 23, in particular in terms of amount. By way of example, the lever element 43 comprises the support section 39. The pressing section 34 is expediently attached to the lever element 43. Alternatively, the pressing section can be part of the lever element. By way of example, the roller 41 is rotatably mounted on the lever element 43. The lever element 43 is expediently pivotably mounted on the coupling section 40, in particular about a lever element pivot axis aligned parallel to the x-direction.

[0047] By way of example, the pressing section 34 is coupled to the spring element 22 via the lever element 43. The lever element 43 represents a physical lever whose pivot point is formed by the mounting of the lever element 43 on the coupling section and which expediently converts the spring force 23 into the counterforce 42. By way of example, the lever element 43 represents a one-sided lever, so that the spring force 23 and the counterforce 42 are located on the same side of the pivot point of the lever element 43. The counterforce 42 is expediently arranged closer to the pivot point than the spring force 23. By means of the lever provided by the lever element 43, the spring force 23 is converted into the counterforce 42 in such a way that the counterforce 42 is greater than the spring force 23, in particular in terms of amount.

[0048] By coupling the pressing section 34 with the

[0049] Guide section 20 (exemplarily via the lever element 43, the spring element 22 and the coupling section 40) guides the increased counterforce 42 to the increased contact force 24, so that the lever element 43 also causes the increased contact force 24 (compared to the spring force 23).

[0050] Advantageously, the preload of the spring element 22 is independent of the position, in particular the angular position, of the tool 4, so that a frictional force between the guide section 20 and the guide contour 19 is preferably constant.

[0051] Preferably, the pressing mechanism 21 is part of the adjustment section 7 and accordingly performs the adjustment movement 8 as part of the adjustment section 7. In particular (during the adjustment movement 8 of the adjustment section 7), the guide section 20, the coupling section 40, the spring element 22, the lever element and / or the roller 41 perform the adjustment movement 8, in particular together with the tool 4.

[0052] The drive device 30 is designed to drive the adjustment section 7 relative to the stationary section 3 in order to set the adjustment section 7 in the adjustment movement 8. The drive device 30 is preferably designed to fix the adjustment section 7 in a fixed state relative to the stationary section 3, so that the guide section 20 is fixed in the direction of the movement path 17 relative to the guide structure 18. The fixed state is expediently always present when the adjustment section 7 is not driven by the drive device 30 (in the direction of the movement path 17). The drive device 30 is expediently designed to be self-locking, so that the adjustment section 7 is always automatically fixed relative to the stationary section (in the direction of the movement path 17) by the drive device 30 when the drive device 30 does not provide a drive for the adjustment section 7 (in the direction of the movement path 17).

[0053] In addition or alternatively to the drive device 30, the tool device 1 can have a particularly manually operable, preferably non-electrical, mechanism for adjusting the position, in particular the angular position, of the tool 4. For example, the adjustment section 7 can be moved by manual actuation in order to perform the adjustment movement 8.

[0054] Preferably, in the fixing state in the direction of the movement path 17, there is no fixing of the guide section 20 relative to the guide structure 18 by means of frictional engagement between the guide section 20 and the guide structure 18. This means that the fixing of the guide section 20 provided in the fixing state is not brought about by a frictional engagement between the guide section 20 and the guide structure 18. Instead, as explained above, this fixing is achieved by the drive device 30, in particular the self-locking design of the drive device 30. Expediently, the drive device 30 provides a fixing force in the fixing state which fixes the guide section 20 relative to the guide structure 18 and which is many times greater than a frictional force present between the guide section 20 and the guide structure 18 in the fixing state.

[0055] Figure 5 shows an exemplary embodiment of the guide section 20. The guide section 20 is designed as a single piece. The guide section 20 is made, for example, from polyoxymethylene with aramid fibers and polytetrafluoroethylene. Good sliding properties and low wear can be achieved with this material. The guide section 20 expediently comprises a guide section body 44, which is designed, for example, in the form of a plate. The guide section body 44 is preferably aligned with its plate plane normal to the x-direction. The guide section body 44 is preferably curved, so that its basic shape is in the shape of a circular arc. The curvature of the guide section body 44 is expediently equal to the curvature of the movement path 17.

[0056] Preferably, the guide section 20 has a first contact projection 45 and a second contact projection 46 spaced apart from the first contact projection 45. The distance between the two contact projections 45, 46 in the longitudinal direction of the guide section 20 and / or in the direction of the movement path 17 is expediently greater than 30%, greater than 40%, or greater than 50% of the longitudinal direction of the guide section 20 and / or the extent of the guide section 20 in the direction of the movement path 17.

[0057] By way of example, the first contact projection 45 and the second contact projection 46 protrude perpendicularly from the plate plane of the guide section body 44, by way of example in the negative x-direction. The first contact projection 45 and the second contact projection 46 each expediently have a cuboid basic shape. The first contact projection 45 and the second contact projection 46 each have a contact surface 47 with which they bear against the guide contour 19. The contact surfaces 47 are expediently curved in accordance with the guide contour 19. Normals of the contact surfaces 47 are aligned radially with respect to the pivot axis. Conveniently, one contact surface 47 is arranged at a first end of the guide section 20 and the other contact surface 47 is arranged at another end of the guide section 20.

[0058] The guide section 20 expediently rests with the first contact projection 45 and the second contact projection 46 on the guide contour 19, in particular exclusively with the first contact projection 45 and the second contact projection 46. Preferably, the contact surfaces 47 in the common x-region of the guide section 20 and the guide contour 19 represent the points of the guide section 20 that are closest to the guide contour 19. Expediently, the guide section 20 only touches the guide contour 19 with the contact surfaces 47. Purely optionally, the contact projections 45, 46 are connected to one another via a connecting structure 48. The connecting structure 48 is curved in accordance with the curvature of the movement path 17. The connecting structure 48 does not rest on the guide contour 19.By way of example, the connecting structure 49 has two connecting webs 49 running parallel to one another, which are in particular curved, expediently in the shape of a circular arc.

[0059] The pressing section 34 is preferably arranged in the direction of the movement path 17 (in particular centrally) between the first contact projection 45 and the second contact projection 46. This is shown in Figure 4. In this way, a uniform load on the two contact surfaces 47 can be achieved. The spring-loaded pressing section 34 preloads the guide section 20 against the counter contour 36 in such a way that the guide section 20 rests with its two contact surfaces 47 on the guide contour 19 and is preloaded against it with a constant preload force which is independent of the angular position of the tool 4 - the pressing force 24.

[0060] Figures 6 and 7 show an exemplary embodiment of the pressing arrangement 38. The pressing arrangement 38 comprises the lever element 43 and the roller 41. The lever element 43 is elongated and, for example, is aligned with its longitudinal axis substantially in the y-direction. The lever element 43 has an elongated main section 50. At a first end in the longitudinal direction of the lever element 43, the lever element 43 has the support section 39 for supporting the spring element 22. The support section 39 has a pin 51 protruding from the main section 50, onto which the spring element 22 is placed (as shown, for example, in Figure 4). The pin 51 protrudes, for example, in the negative z-direction from the main section 50.At a second end in the longitudinal direction of the lever element 43, the lifting element 43 has a pivot axis section 52, via which the lever element 43 is pivotally mounted on the coupling section 40 and which is expediently cylindrical. The pivot axis section 52 protrudes from the main section 50, for example in the positive x-direction.

[0061] Figure 7 shows the pressing arrangement 38 without the roller 41. By way of example, the lever element 43 has a rotation axis section 53 on which the roller 41 is rotatably mounted. The rotation axis section 53 projects from the main section 50, in particular in the opposite direction to the pivot axis section 52, for example in the negative x-direction. By way of example, the rotation axis section 53 and the pivot axis section 52 are arranged on opposite sides of the main section 50. In the longitudinal direction of the lever element 43, the rotation axis section 53 is expediently arranged between the support section 39 and the pivot axis section 52, preferably in the longitudinal direction closer to the pivot axis section 52 than to the support section 39, by way of example (in the longitudinal direction) directly next to the pivot axis section 52.

[0062] The guide device 16 can also be referred to as the first guide device, the guide structure 18 as the first guide structure, the movement path 17 as the first movement path and the guide section 20 as the first guide section.

[0063] The tool device 1 expediently also has a second guide device 16.2. Figure 8 shows an exemplary embodiment of the second guide device 16.2.

[0064] By way of example, the first guide device 16 and the second guide device 16.2 are arranged spaced apart from one another in the x-direction. A respective guide device 16, 16.2 is expediently arranged at each end in the longitudinal direction of the adjustment section 7.

[0065] The second guide device 16.2 is preferably designed like the first guide device 16, so that the above explanations relating to the first guide device 16 expediently apply correspondingly to the second guide device 16.2. The components of the second guide device 16.2 explained below are expediently designed like the corresponding components of the first guide device 16.2 explained above. The second guide device 16.2 comprises a second guide structure 18.2 defining a second movement path 17.2, as well as a second guide section 20.2 resting against a second guide contour 19.2 of the second guide structure 18.2, which is movable relative to the second guide structure 18.2 along the second movement path 17.2 to carry out the adjustment movement 8. The second movement path 17.2 preferably runs parallel to the first movement path 17.By way of example, the second guide structure 18.2 has a second structural section 37.2, which defines a second counter contour 36.2.

[0066] The pressing mechanism 21 explained above can also be referred to as the first pressing mechanism, the spring element 22 as the first spring element, the spring force 23 as the first spring force and the pressing force 24 as the first pressing force.

[0067] The tool device 1 expediently also has a second pressing mechanism 21.2. Figure 8 shows an exemplary embodiment of the second pressing mechanism 21.2.

[0068] By way of example, the first pressing mechanism 21 and the second pressing mechanism 21.2 are arranged spaced apart from one another in the x-direction. A respective pressing mechanism 21, 21.2 is expediently arranged at each end in the longitudinal direction of the adjustment section 7.

[0069] The second pressing mechanism 21.2 is preferably designed like the first pressing mechanism 21, except for the differences explained below, so that the above explanations relating to the first pressing mechanism 21 expediently apply correspondingly to the second pressing mechanism 21.2. The components of the second pressing mechanism 21.2 explained below are expediently designed like the corresponding components of the first pressing mechanism 21 explained above.

[0070] The second pressing mechanism 21.2 comprises a second spring element 22.2 and is designed, on the basis of a second spring force 23.2 provided by the second spring element 22.2, to press the second guide section 20.2 with a second pressing force 24.2 against the second guide structure

[0071] 18.2 in order to reduce or eliminate play between the second guide section 20.2 and the second guide structure 18.2 along the second movement path 17.2, in particular in the radial direction with respect to the (in particular virtual) pivot axis of the adjustment movement 8. The second spring element 22.2 is exemplarily connected to the second guide section via a second coupling section 40.2

[0072] 20.2. The second pressing mechanism 21.2 has, for example, a second pressing section 34.2, which is designed as a second roller 41.2 and rests against the second counter contour 36.2. The second pressing section

[0073] 34.2 is pressed against the second counter contour 36.2 by a second counter force 42.2 caused by the second spring force 23.2.

[0074] The second pressing mechanism 21.2 differs from the first pressing mechanism 21 in that the second spring force 23.2 is oriented in a different direction than the first spring force 23. For example, the second spring force 23.2 is oriented orthogonally to the first spring force 23. Preferably, the first spring force 23 is oriented parallel to the saw blade plane and / or the second spring force 23.2 is oriented normal to the saw blade plane. Preferably, the second pressing mechanism 21.2 comprises a second pressing arrangement 38.2 with a second lever element 43.2, which is expediently oriented with its longitudinal axis orthogonal to the longitudinal axis of the first lever element 43.2.

[0075] The first contact force 24 and the second contact force 24.2 are expediently both oriented in the radial direction with respect to the (in particular virtual) pivot axis of the adjustment movement 8. Furthermore, the first counterforce 42 and the second counterforce 42.2 are expediently both oriented in the radial direction with respect to the (in particular virtual) pivot axis of the adjustment movement 8. Expediently, the first counterforce 42 and the second counterforce 42.2 are both oriented in the same direction and / or in the same radial plane through the (in particular virtual) pivot axis, as shown, for example, by comparing Figs. 4 and 8.

[0076] Alternatively, the second pressing mechanism 21.2 can also be designed the same as the first pressing mechanism 21 or mirrored (in particular on a yz mirror plane) to the first pressing mechanism 21.

[0077] The following describes a method for operating the tool device 1. Optionally, the method begins with a user carrying the tool device 1 to a place of use and placing it on a base there. The user then expediently enters a desired position, in particular a desired angular position, of the tool 4 relative to the stationary section 3 via the operating device 25. The tool device 1 then sets the position of the tool 4 in accordance with the position entered by the user. For this purpose, the tool device 1 carries out the adjusting movement 8. By means of the pressing mechanism 21 (and the optionally present second pressing mechanism 21 .2 ), the tool 4 is constantly - i.e. in particular before, during and after the adjustment movement 8 - mounted free of play relative to the stationary section 3, in particular in the radial direction with respect to the (in particular virtual) pivot axis about which the adjustment movement 8 takes place. The user expediently activates the drive unit 15 (for example by actuating an on switch of the tool device 1) in order to cause the tool 4 to be set in the machining movement. The user places a workpiece on the support surface and guides the workpiece in the feed direction 10 towards the tool 4 in order to machine the workpiece with the tool 4, specifically in the previously set position, in particular the previously set angular position. By means of the pressure mechanism 21 (and the optionally present second pressure mechanism 21 .2), the tool 4 is mounted free of play relative to the stationary section 3 even during machining of the workpiece, in particular in the radial direction with respect to the (in particular virtual) pivot axis of the adjustment movement 8. Consequently, after the completion of the adjustment movement 8 and / or before machining the workpiece, the user does not have to perform any separate user action (for example, triggering a clamping mechanism) in order to fix the adjustment section 7 relative to the stationary section 3 and / or to achieve the play-free mounting; expediently, the user does not perform any such separate user action between the completion of the adjustment movement 8 and the start of machining the workpiece. The fixing of the adjustment section 7 is achieved automatically by the self-locking drive device 30 and the play-free mounting is achieved automatically by the first and / or second pressure mechanism 21, 21.2 is achieved, so no user action is required and does not occur.

Claims

Claims 1. Tool device (1), in particular a saw device, comprising a stationary section (3), in particular a support section for supporting a workpiece, and an adjustment section (7) comprising a tool (4), in particular a saw blade, which is adjustable relative to the stationary section (3) by performing an adjustment movement (8) in order to set a position, in particular an angular position, of the tool (4) relative to the stationary section (3), further comprising a guide device (16) configured to guide the adjustment section (7) during the adjustment movement (8) relative to the stationary section (3), wherein the guide device (16) comprises a guide structure (18) defining a path of movement (17) and a guide section (20) abutting a guide contour (19) of the guide structure (18), which is movable along the path of movement (17) relative to the guide structure (18) for carrying out the adjustment movement (8).characterized by a pressure mechanism (21) comprising a spring element (22), which is configured to press the guide section (20) against the guide structure (18) with a pressure force (24) on the basis of a spring force (23) provided by the spring element (22), in order to reduce or eliminate play between the guide section (20) and the guide structure (18) along the path of movement (17).

2. Tool device according to claim 1, wherein the adjustment movement is a rotary movement and / or the path of movement is arc-shaped.

3. Tool device (1) according to claim 1 or 2, wherein the contact force (24) is aligned radially with respect to the adjustment movement (8) and / or the movement path (17).

4. Tool device (1) according to a preceding claim, wherein the pressing mechanism (21) is configured to guide the guide section (20) along the entire path of movement. (17) with the contact force (24) against the guide structure (18) to press in order to reduce or eliminate play between the guide section (20) and the guide structure (18) along the entire path of movement (17).

5. Tool device (1) according to a preceding claim, wherein the pressing mechanism (21) is configured to provide the pressing force (24) as a substantially constant pressing force along the path of movement (17).

6. Tool device (1) according to a preceding claim, wherein the pressing mechanism (21) comprises a pressing section (34) which bears against a counter contour (36) of the guide structure (18) and is resiliently coupled to the guide section (20) by means of the spring element (22), so that, due to the spring force (23), the pressing section (34) is pressed against the counter contour (36) and the guide section (20) against the guide contour (19) is pressed.

7. Tool device (1) according to claim 6, wherein the Leading contour (19) on a first page of a structural section (37) of the management structure (18) arranged is and the counter contour (36) is arranged on a second side of the structural section (37) opposite the first side.

8. Tool device (1) according to claim 6 or 7, wherein the pressure section (34) has a roller (41) that rests against the counter contour (36) and can roll on it.

9. Tool device according to claim 8, wherein the pressure section comprises at least one scraper section abutting the counter contour in order to remove contaminants from the counter contour.

10. Tool device (1) according to a preceding claim, wherein the pressing mechanism (21) has a lever element (43) by means of which the spring force (23) is converted into the pressing force (24) such that the pressing force (24) is greater than the spring force (23).

11. Tool device (1) according to claim 10 in combination with one of claims 6 to 9, wherein the pressure section (34) is coupled to the spring element (22) via the lever element (43).

12. Tool device (1) according to a preceding claim, wherein the guide section (20) has a first contact projection (45) and a second contact projection (46) spaced apart from the first contact projection (45) and bears against the guide contour (19) with the first contact projection (45) and the second contact projection (46).

13. Tool device (1) according to claim 12 in combination with one of claims 6 to 9, wherein the pressure section (34) is arranged in the direction of the movement path (17) between the first contact protrusion (45) and the second contact protrusion (46).

14. Tool device (1) according to a preceding claim, comprising a drive device (30) configured to drive the adjusting section (7) relative to the stationary section (3) in order to move the adjusting section (7) into the adjusting movement (8), and further configured to fix the adjusting section (7) in a fixed state relative to the stationary section (3) so that the guide section (20) is fixed in the direction of the movement path (17) relative to the guide structure (18).

15. Tool device (1) according to claim 14, wherein in the fixing state the fixing of the guide section (20) relative to the guide structure (18) in the direction of the movement path (17) is not achieved by means of frictional engagement between the guide section (20) and the guide structure (18).

16. Tool device (1) according to a preceding claim, wherein the guide device (16) is a first guide device, the guide structure (18) is a first guide structure, the path of movement (17) is a first path of movement, and the guide section (20) is a first guide section, and wherein the tool device (1) further comprises a second guide device (16.2) spaced apart from the first guide device (16), which comprises a second guide structure (18.2) defining a second path of movement (17.2) and a second guide section (20.2) abutting a second guide contour (19.2) of the second guide structure (18.2), which is for the execution of the adjustment movement (8) along the second movement path (17.2) relative to the second guide structure (18.2) is movable, wherein the clamping mechanism (21) is a first clamping mechanism, the spring element (22) is a first spring element, the spring force (23) is a first spring force, and the clamping force (24) is a first clamping force, and wherein the tool device (1) further comprises a second clamping mechanism (21.2) having a second spring element (22.2), which is configured to clamp the second guide section (20.2) with a second clamping force based on a second spring force (23.2) provided by the second spring element (22.2). (24.2) to push against the second guidance structure (18.2) in order to reduce or eliminate play between the second guidance section (20.2) and the second guidance structure (18.2) along the second movement path (17.2).

17. Tool device (1) according to claim 16, wherein the second path of movement (17.2) runs parallel to the first path of movement (17).

18. Tool device (1) according to claim 16 or 17, wherein the second spring force (23.2) is oriented in a different direction than the first spring force (23), wherein the first contact force (24) and the second contact force (24.2) are advantageously oriented radially with respect to the adjustment movement (8) and / or the movement path (17).

19. Method for operating a tool device (1) according to one of claims 1 to 18, comprising the step: performing the adjustment movement (8) .

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