Mechanical striking mechanism, and hand-held tool machine

Abstract

To provide an improved mechanical striking mechanism for a hand-held tool machine.SOLUTION: A mechanical striking mechanism for striking drive of an insert tool of a hand-held tool machine comprises an intermediate shaft (101) which is rotatably supported, a striking member, and a driven shaft which is rotatably supported. Each of the intermediate shaft (101) and the striking member has at least one guide groove (111) for guiding at least one guide body, and a guide surface (117) of the guide groove (111) in the intermediate shaft (101) and / or a guide surface of the guide groove of the striking member is formed as a surface without any bend and / or ridge.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present invention relates to a mechanical impact mechanism for a handheld tool, and more particularly to a rotary impact driver. [Background technology]

[0002] In the prior art, mechanical striking mechanisms for rotary striking drivers are known. A known problem with these striking mechanisms, however, is the high mechanical loading of the components of the striking mechanism. Summary of the Invention [Problem to be solved by the invention]

[0003] The problem is to provide an improved mechanical striking mechanism for a hand tool machine. [Means for solving the problem]

[0004] This object is achieved by the striking mechanism of the independent claim. Advantageous configurations are the subject of the dependent claims.

[0005] According to one aspect, there is provided a mechanical striking mechanism for strikingly driving an insert tool of a hand-held tool machine, the mechanical striking mechanism comprising a rotatably supported intermediate shaft, an impacting body, and a rotatably supported driven shaft, wherein the intermediate shaft and the impacting body each have at least one guide groove that guides at least one guide body, and the guide surface of the guide groove of the intermediate shaft and / or the guide surface of the guide groove of the impacting body are formed as surfaces without bends and / or without ridges.

[0006] This can achieve the technical advantage that an improved impact mechanism can be provided. Due to the bend-free and / or edge-free guide surfaces of the guide groove, the guide body can be guided in the guide groove with relatively low energy losses. Furthermore, wear of the guide groove and the guide body can be reduced.

[0007] A guide groove, within the meaning of the present application, is a groove segment which defines the relative torsional and axial movement connection between the striking body and the intermediate shaft within the working area.

[0008] The guide surface of the guide groove is, within the meaning of the present application, the inner surface of the respective guide groove. When the guide body is guided in the guide groove, the guide body is arranged in the guide groove and rests on the guide surface of the guide groove. The guide surface is formed by a cutout in the guide groove and represents the part of the cutout on which the guide body rests.

[0009] Bend-free or ridge-free in the sense of the present application means that no bends or ridges are formed in the guide surface, in particular no ridges or bends are formed in the guide surface that cross the guide path of the guide body, which the guide body follows when guiding in the guide groove.

[0010] The striking body is also referred to in the prior art as a striking hammer or a rotary striking hammer.

[0011] According to one embodiment, the guide groove of the intermediate shaft and / or the striking body has an approximately parabolic extension.

[0012] This can achieve the technical advantage that, due to the parabolic extension of the guide groove, an energy-optimized guiding of the guide body can also be achieved.

[0013] The extension of the guide groove relates to the longitudinal direction of the guide groove. The extension of the guide groove defines the guide path followed by the guide body when it is guided by the guide groove. The extension is approximately parabolic. This means that deviations from an exact parabolic shape are possible.

[0014] According to one embodiment, the perimeter of the guide groove of the intermediate shaft and / or of the striking body is formed as a perimeter without any bends.

[0015] This allows the technical advantage to be achieved that the guide surface is designed as a smooth and bend-free or edge-free guide surface.

[0016] The perimeter of the guide groove represents the outer edge of the cutout that defines the guide groove.

[0017] According to one embodiment, the perimeter line and / or the guide surface of the guide groove of the intermediate shaft and / or the striking body can be mapped by a continuously differentiable function.

[0018] This can achieve the technical advantage that optimally bend-free and edge-free guide surfaces of the guide groove can be generated.

[0019] A continuously differentiable function is a mathematical function that is differentiable within a predetermined domain and whose derivative is a continuous function within the predefined domain.

[0020] According to one embodiment, the function is at least twice continuously differentiable.

[0021] This can achieve the technical advantage that optimally bend-free and edge-free guide surfaces of the guide groove can be generated.

[0022] According to one embodiment, the curvature of the guide groove is smaller than the curvature of the guide body.

[0023] This allows the technical advantage to be achieved that the guide body can be guided in the guide groove with the least possible friction.

[0024] The curvature of the guide groove is the curvature of the notch of the guide groove perpendicular to the extension of the guide groove.

[0025] According to one embodiment, the guide body is formed as a sphere.

[0026] This allows the technical advantage to be achieved that the guide body can be guided in the guide groove with the least possible friction.

[0027] According to one embodiment, the axial movement of the striking body along the extension of the guide groove is continuous and non-linear with respect to the relative angle between the striking body and the intermediate shaft.

[0028] This can achieve the technical advantage that the energy losses in the guiding of the guide body in the guide groove are minimized and that guiding of the guide body in the guide groove as energy-efficient as possible is achieved.

[0029] The concepts of continuous and non-linear must be understood mathematically: the extension of the guide groove is thus the extension of a mathematically continuous and non-linear function.

[0030] The relative angle indicates the angle of relative rotation between the intermediate shaft and the striking body.

[0031] The impact body then does not perform a purely axial movement, but always also has a pivoting movement, where axial movement means the axial component of the screw movement performed by the impact body.

[0032] According to one embodiment, the extension of the guide groove of the intermediate shaft and / or the striking body is mirror-symmetrical at the turning point.

[0033] This allows the technical advantage to be achieved that due to the symmetrical shape of the guide groove, a symmetrical guidance of the guide body in the guide groove is achieved, which is again energy efficient with as minimized energy losses as possible.

[0034] The turning point is then formed by the apex of the approximately parabolic extension.

[0035] According to one embodiment, the lengths of the guide grooves of the intermediate shaft and the striking body are the same or different.

[0036] This allows the technical advantage to be achieved that the guide groove is adapted to requirements: the length can then be adapted to the radius of the intermediate shaft and the striking body, so that as uniform as possible guidance of the guide body in the guide groove is made possible.

[0037] The length of the guide groove then extends between the end points of the guide groove, the length then extends along the extension of the guide groove, the end points being respectively defined by the perimeter of the guide groove.

[0038] According to one embodiment, the inclinations of extension of the guide grooves of the intermediate shaft and the striking body are the same as or different from each other.

[0039] This allows the technical advantage to be achieved that the extension of the guide groove can be adapted to the configuration of the intermediate shaft and the impact body, respectively, for example the radius of the intermediate shaft and the impact body, thereby achieving the most energy-efficient possible guidance of the guide body in the guide groove.

[0040] Slope, within the meaning of this application, is the mathematical slope of a mathematical function.

[0041] According to one embodiment, the inclination of the extension of the guide grooves of the intermediate shaft and the striking body, respectively, is constant or variable.

[0042] This allows the technical advantage to be achieved that the extension of the guide groove can be adapted to the configuration of the intermediate shaft and the impact body, respectively, for example the radius of the intermediate shaft and the impact body, thereby achieving the most energy-efficient possible guidance of the guide body in the guide groove.

[0043] A constant slope is the slope of a linear mathematical function. A variable slope is the non-constant slope of a non-linear function.

[0044] According to one embodiment, the striking mechanism is designed as a rotary striking mechanism.

[0045] This may achieve a technical advantage in that an improved rotary striking mechanism may be provided.

[0046] According to one aspect, there is provided a handheld tool machine comprising a mechanical striking mechanism according to any one of the above embodiments.

[0047] This allows for the technical advantage to be achieved that an improved handheld tool machine can be provided that includes an improved impact mechanism that provides the above-mentioned technical advantages.

[0048] According to one embodiment, the hand tool is configured as a rotary impact driver.

[0049] Thus, a technical advantage may be achieved in that an improved rotary impact driver may be provided.

[0050] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to the following drawings. [Brief description of the drawings]

[0051] [Figure 1] 1 is a schematic diagram of a handheld tool equipped with a mechanical impact mechanism according to one embodiment; [Diagram 2] 1 is a schematic diagram of a mechanical impact mechanism for a handheld tool machine according to one embodiment; [Diagram 3] FIG. 2 is a schematic diagram of an intermediate shaft of a mechanical striking mechanism according to one embodiment. [Figure 4] FIG. 2 is a schematic diagram of an impact body of a striking mechanism according to one embodiment. [Diagram 5] FIG. 13 is another schematic diagram of an impacting body of the impact mechanism according to one embodiment. [Figure 6] 1 is a schematic diagram of a guide groove of an intermediate shaft and / or a striking body of a striking mechanism of the prior art; [Figure 7] 1 is a graphical plot of the lifting and impact behavior of a prior art impact mechanism and a striking mechanism according to the present invention; [Figure 8]1 is a graphical plot of the lifting and impact behavior of a prior art impact mechanism and a striking mechanism according to the present invention; [Figure 9] 1 is a graphical plot of the lifting and impact behavior of a prior art impact mechanism and a striking mechanism according to the present invention; DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0052] FIG. 1 shows a schematic diagram of a handheld tool machine 200 with a mechanical striking mechanism 100 according to one embodiment.

[0053] In the illustrated embodiment, the handheld tool machine comprises a drive motor 205, a motor shaft 207, a transmission unit 209 and a tool receiving part 203 with a tool insert 201. The handheld tool machine further comprises a striking mechanism 100 according to the invention, the striking mechanism 100 comprising an intermediate shaft 101, a driven shaft 105 and a striking body 103. The striking mechanism 100 is arranged between the transmission unit 209 and the tool receiving part 203. Via the transmission unit 209, the striking mechanism 100 is rotatable via the drive motor 205, and via the rotation of the striking mechanism 100, the tool insert 201 arranged in the tool receiving part 203 is rotatably driven. The tool receiving part can be a plug-in receiving part and / or a slip-on receiving part.

[0054] According to one embodiment, the impact mechanism 100 is configured as a rotary impact mechanism. The handheld machine tool 200 is correspondingly configured as a rotary impact driver.

[0055] FIG. 2 shows a schematic diagram of a mechanical striking mechanism 100 for a handheld tool 200 according to one embodiment.

[0056] FIG. 2 shows, in schematic form, the interaction of the striking mechanism 100 with the power train unit 209 and tool receiver 203 of the hand tool machine 200 shown in FIG.

[0057] In the illustrated embodiment, the striking mechanism 100 comprises an intermediate shaft 101. The intermediate shaft 101 has a cylinder body 149. At least one guide groove 111 is formed in an outer surface 147 of the cylinder body 149. A spherical guide body 115 is slidably disposed in the guide groove 111.

[0058] The striking mechanism 100 further includes a striking body 103. The striking body 103 has a ring body 155, which has an axial through-guide opening 153. One end face 157 of the ring body 155 is formed with two drive cams 107.

[0059] The impact mechanism 100 further includes a driven shaft 105. The driven shaft 105 has a cylinder body 161 and a base element 159 formed at one free end of the cylinder body 161. The base element 159 has two driven cams 109 formed thereon.

[0060] In the prior art, the driven shaft 105 with the driven cam 109 is also called the anvil. The striking body 103 with the driving cam 107 is also called the hammer in this case. During the striking operation, the driving cam 107 of the hammer 103 thereby strikes the driven cam 109 of the anvil 105.

[0061] In the illustrated embodiment, the striking mechanism further comprises a bearing unit 133 and a spring element 135 .

[0062] The intermediate shaft 101 can be connected to the power train unit 209 via corresponding gears. The cylinder body 149 of the intermediate shaft 101 can be guided by the bearing unit 133 and the spring element 135 by the guide opening 153 of the striking body 103.

[0063] According to the present invention, at least one guide groove 113 (not shown in FIG. 2) is formed on the inner surface 151 of the through-guide opening 153 of the impacting body 103. A guide body 115 can be rotatably arranged in the guide groove 113. When the intermediate shaft 101 is guided through the through-guide opening 153 of the impacting body 103, the intermediate shaft 101 can be rotatably connected to the driven shaft 105. The driven shaft 105 can be rotatably introduced into the tool receiving part 203.

[0064] During the impact operation of the handheld tool machine 200, the intermediate shaft 101 lifts the impacting body 103. At that time, the impacting body 103 moves toward the intermediate shaft 101 in the axial direction, and at this time, rotates toward the intermediate shaft 101 in the circumferential direction. During the lifting, the impacting body 103 rotates with respect to the intermediate shaft 101 at a slightly changed rotational speed and also moves in the axial direction. When the impacting body 103 is being lifted, the impacting body 103 performs a rotational impacting motion, during which the impacting body 103 is moved in the axial direction and in the circumferential direction. At this time, the impacting body 103 is moved toward the tool receiving portion 203, and at this time, performs a rotational motion along the circumferential direction. At this time, the driving cam 107 of the impacting body 103 comes into contact with the driven cam 109 of the driven shaft 105, which causes the driven shaft 105 to rotate so as to strike. As a result, the insert tool 201 is rotated so as to strike in the same manner, thereby causing the hand-held tool machine 200 to perform a striking operation.

[0065] In the embodiment shown, the striking mechanism 100 further comprises a further bearing unit 137 which is arranged between the driven shaft 105 and the tool receiving part 203 .

[0066] FIG. 3 shows a schematic diagram of an intermediate shaft 101 of a mechanical striking mechanism 100 according to one embodiment.

[0067] According to the invention, the intermediate shaft 101 has at least one guide groove 111 which guides at least one guide body 115. The guide groove 111 has a guide surface 117. The guide surface is formed by the inner surface of a cutout which forms the guide groove 111. The guide surface 117 of the guide groove 111 of the intermediate shaft 101 is formed according to the invention as a surface without bends and / or without ridges.

[0068] In the embodiment shown, the guide groove 111 has a substantially parabolic extension 121. The extension 121 represents a line extending along the longitudinal direction of the guide groove 111. The extension 121 is located in the cylindrical body 149 of the intermediate shaft 101. This can be seen in FIG. b). The extension 121 extends at the lowest point of the cutout of the guide groove 111.

[0069] A bendless or ridgeless guide surface 117 has no ridges or bends across the written extension 121 of the guide surface 117, as shown in figures a) and b).

[0070] In the illustrated embodiment, the guide groove 111 further has a perimeter 125. The perimeter 125 represents the outer edge of the cutout forming the guide groove 111. In the illustrated embodiment, the perimeter 125 of the guide groove 111 is formed as a perimeter 125 without bends. As shown in views a) and b), the perimeter 125 does not have bends. The perimeter 125 can instead be represented by a continuously differentiable mathematical function, which is continuously differentiable everywhere about the perimeter 125.

[0071] The same is true for guide surface 117. Since guide surface 117 also has no bends or edges anywhere, guide surface 117 can be represented by a two-dimensional mathematical function that is continuously differentiable everywhere in its domain.

[0072] According to one embodiment, the mathematical function describing the perimeter 125 of the guide groove 111 or the guide surface 117 is continuously differentiable at least twice.

[0073] According to one embodiment, the curvature of the guide groove 111 is smaller than the curvature of the spherical guide body 115. Due to the smaller curvature of the guide groove 111, the guide body 115 (not shown in FIG. 3) can be slidably positioned within the guide groove 111.

[0074] In the embodiment shown, the guide surface 117 or the extension 121 of the guide groove 111 is mirror-symmetrical at the turning point 129. The turning point 129 is located at the lowest point of the cutout of the guide groove 111 on the guide surface 117 and represents the apex of the guide groove 111 which is formed as an approximately parabola.

[0075] Due to the generally parabolic shape of the extension 121 of the guide groove 111, the slope of the extension 121 can vary and is therefore not constant.

[0076] FIG. b) shows an enlarged view of the intermediate shaft 101 of FIG. a), in which the intermediate shaft 101 is rotated about the longitudinal axis L of the intermediate shaft 101. As shown diagrammatically in FIG. b), the intermediate shaft 101 has two guide grooves 111, which are formed in the outer surface 147 of the cylinder body 149, respectively.

[0077] According to one embodiment, both guide grooves 111 of the intermediate shaft 101 are formed to have the same structure.

[0078] FIG. 4 shows a schematic diagram of the striking body 103 of the striking mechanism 100 according to one embodiment.

[0079] Fig. b) shows an enlarged view of the guide groove 113 formed on the inner surface 151 of the through-guide opening 153 of the ring body 155 of the striking body 103. The illustration shown in Fig. b) shows the guide groove 113 along the cutting plane A in Fig. a).

[0080] According to the invention, the guide groove 113 has a guide surface 119, which is formed as a surface without bends or edges. Like the guide surface 117 of the guide groove 111 of the intermediate shaft 101, the guide surface 119 has an approximately parabolic extension 123 in the embodiment shown. The extension 123 is located in the ring body 155 of the striking body 103.

[0081] This is shown diagrammatically in figures b) and 5b). The extension 123 extends at the lowest point of the cutout of the guide groove 111. The guide surface 119 does not have any edges or bends crossing the extension 123.

[0082] In the illustrated embodiment, the guide groove 113 further has a perimeter line 127. The perimeter line 127 is also formed without any bends.

[0083] In the illustrated embodiment, the guide surface 119 and the perimeter 127 of the guide groove 113 can each be represented by a continuously differentiable mathematical function.

[0084] According to one embodiment, a continuously differentiable mathematical function is continuously differentiable at least twice everywhere in its domain.

[0085] According to one embodiment, the curvature of the guide groove 113 of the striking body 103 is smaller than the curvature of the guide body 115 which is formed in a spherical shape.

[0086] Similar to the guide groove 111 of the intermediate shaft 101, the extension 123 of the guide groove 113 of the impacting body 103 is mirror-symmetrical at the turning point 131. The turning point 131 is located at the lowest point of the cutout of the guide groove 113 on the guide surface 119 and represents the apex of the guide groove 113 which is formed as an approximately parabolic shape.

[0087] The guide groove 111 of the intermediate shaft 101 and the guide groove 113 of the impacting body 103 may be formed to have the same structure as each other. In this case, the guide grooves 111, 113 may have the same length. The length of the guide grooves 111, 113 extends between the end points 143, 145 along the extensions 121, 123. The end points 143, 145 of the guide grooves 111, 113 represent the ends of the respective guide grooves 111, 113. The guide groove 111 of the intermediate shaft 101 has two end points 143, and the intermediate shaft 113 of the impacting body 103 similarly has two end points 145. The guide body 115 can be guided in the guide grooves 111, 113 between the end points 143, 145 at most. Furthermore, the extensions 121, 123 of the guide grooves 111, 113 may have the same inclination.

[0088] In the illustrated embodiment, the slope of the extension 123 is variable, i.e., not constant, based on the generally parabolic shape of the extension 123 .

[0089] As shown diagrammatically in FIG. a), the striking body 103 has two guide grooves 113, which are respectively arranged on the inner surface 151 of the through-guide opening 153 of the ring body 155. When the intermediate shaft 101 is introduced through the through-guide opening 153, each spherical guide body 115 is guided by the guide groove 111 of the intermediate shaft 101 and the guide groove 113 of the striking body 103, respectively. Due to the guidance of the spherical guide bodies 115 in the approximately parabolic guide grooves 111, 113, the intermediate shaft 101 and the striking body 103 can rotate relative to each other about the longitudinal axis L and can move along the longitudinal axis L.

[0090] According to one embodiment, the guide groove 113 has a smaller curvature than the spherical guide body 115. Thus, the spherical guide body 115 is slidably or rollably disposed in the guide groove 113 of the impact body 103.

[0091] According to one embodiment, the axial movement of the striker 103 along the extension 123 of the guide groove 113 is continuous and non-linear with respect to the relative angle α between the intermediate shaft 101 and the striker 103. The relative angle α represents, at this time, the relative twist of the intermediate shaft 101 with respect to the striker 103.

[0092] FIG. 5 shows another schematic view of the striker 103 of the striking mechanism 100 according to one embodiment.

[0093] FIGS. a) and b) show cross-sectional views of the striker 103 of FIG. 4. The guide grooves 113 are respectively grooved in the inner surface 151 of the through guide opening 153.

[0094] FIG. 6 shows a schematic view of the guide groove 101A of the intermediate shaft 101A and / or the striker 103A of a prior art striking mechanism.

[0095] In the prior art, guide surfaces 117A, 119A are provided in the guide grooves 111A, 113A formed in both the intermediate shaft and the striker of a known striking mechanism in the prior art, and the guide surfaces 117A, 119A are not formed without bending or ridges. Instead, the guide grooves 111A, 113A, which are representatively shown for the known guide grooves in the prior art in FIG. 6, have three ridges 139A that meet at one bending point 147A.

[0096] The ridges 139A are formed in the guide surfaces 117A, 119A and cross the extensions 121A, 123A of the guide grooves 111A, 113A. Due to the ridges 139A, the guide surfaces 117A, 119A cannot be represented by a continuously differentiable mathematical function. This is because the mathematical function is not differentiable within the ridges 139A. The same applies to the extensions 121A, 123A, which are also not differentiable at the ridges 139A.

[0097] The perimeters 125A, 127A of the guide grooves 111A, 113A also have a bend 141A, which means that the perimeters 125A, 127A also cannot be represented by a continuously differentiable mathematical function in the prior art. Due to the edges 139A of the guide surfaces 117A, 119A, the guiding of the spherical guide body in the guide grooves 111A, 113A is not uniform, as it is in the guide grooves 111, 113 of the present invention.

[0098] Instead, the spherical guide body 115 moves in a jumping manner at the height of the edge 139A of the guide surfaces 117A, 119A, whereby uniform guiding of the guide body 115 is not possible, causing increased material load and increased material wear of the guide body 115 and the guide grooves 111A, 113A.

[0099] 7-9 show graphical graphs of the lifting and impact behavior of a prior art impact mechanism and the impact mechanism 100 according to the present invention.

[0100] 7A to 7D show plots of the axial position AL of the intermediate shaft 101 and the impacting body 103 relative to the relative angle α between the intermediate shaft 101 and the impacting body 103.

[0101] In the figures a) and b) the start-up phase of the impact operation from 0 to 0.1 seconds is shown. In the figures c) and d) the impact operation after the start-up phase for 3.6 to 3.7 seconds is shown. The figures a) and c) show the results for an impact mechanism with guide grooves 111A, 113A known in the prior art and shown in figure 6. The figures b) and d) show the results for an impact mechanism 100 with guide grooves 111, 113 according to the invention.

[0102] In figures a) to d) the curves for the lift 141 and the strike 139 between the driven shaft 105 and the striker 103 are shown respectively.

[0103] As can be seen from figures b) and d), the curves in figures b) and d), i.e. the axial position AL in relation to the relative angle α, progress in a much more orderly and symmetrical manner than those shown in figures a) and c) of the percussion mechanisms known from the prior art.

[0104] FIG. 8 shows, in a) to d), the axial velocity V a is plotted.

[0105] Figures a) and b) again show the rise phase for a time period between 0.0 and 0.1 seconds. Figures c) and d) show the results for an impact run for a time period between 3.6 and 3.7 seconds after the rise phase.

[0106] Figures a) and c) again show the results for a striking mechanism known from the prior art, while figures b) and d) show the results for the striking mechanism 100 according to the invention.

[0107] In figures a) to d) the curves for the lift 141 and the strike 139 between the driven shaft 105 and the striker 103 are shown respectively.

[0108] As can be seen from figures b) and d), the relative axial velocity V for the striking mechanism 100 according to the invention with respect to the relative angle α a shows a much more symmetrical and uniform extension than that shown in the striking mechanisms known in the prior art, such as those shown in figures a) and c).

[0109] FIG. 9 shows, in a) to d), the tangential velocity V t is plotted.

[0110] Figures a) and b) again show the tangential velocity V during the rise phase from 0.0 to 0.1 seconds. t is shown relative to the relative angle α.

[0111] In figures a) to d) the curves for the lift 141 and the strike 139 between the driven shaft 105 and the striker 103 are shown respectively.

[0112] Figures c) and d) show the tangential velocity V for the impact operation at 3.6 to 3.7 seconds after the start-up phase. t Figures a) and c) show the results for a striking mechanism known from the prior art, while figures b) and d) show the results for the striking mechanism 100 according to the invention.

[0113] As can be seen from figures b) and d), the tangential velocity V relative to the relative angle α for the striking mechanism 100 according to the invention is t shows a much more symmetrical and uniform extension than the striking mechanisms known in the prior art, as can be seen from figures a) and c).

[0114] 7 to 9 show that the guide grooves 111, 113 according to the present invention, which have guide surfaces 117, 119 without ridges or bends, allow a much more uniform guiding of the guide body 115 and the impacting body 103. This is because the intermediate shaft 101 and the impacting body 103 have essentially more uniform extensions relative to each other in terms of the axial position AL and the tangential velocity V t and axial velocity V a This allows for an inherently more energy-efficient and material-friendly operation of the impact mechanism 100 according to the invention, which can be triggered both in the start-up phase and in the impact operation. [Explanation of symbols]

[0115] 100 Striking mechanism 101 Intermediate shaft 101A intermediate shaft 103 Impact body, hammer 103A Impactor 105 Driven shaft, anvil 107 Drive Cam 109 Driven Cam 111 Guide groove 111A Guide groove 113 Guide groove 113A Guide groove 115 Guide body 117 Guide surface 117A Guide surface 119 Guide surface 119A Guide surface 121 Extend 121A Extension 123 Extend 123A Extension 125 Perimeter 125A Periphery line 127 Perimeter 127A Perimeter Line 129 Turning Point 131 Turning Point 133 Bearing unit 135 Spring elements 137 Another bearing unit 139 Strike 139A Ridge 141 Raise 141A Bend 143 End Point 145 End Point 147 Exterior 147A Bend Point 149 Cylinder body 151 Inside 153 Through guide opening 155 Ring body 157 End face 159 Base Elements 161 Cylinder body 200 Hand-held tool machine 201 Insert tool 203 Tool holder 205 Drive motor 207 Motor shaft 209 Powertrain Unit A cutting plane AL Axial Position L Longitudinal axis Va Axial Velocity V t tangential velocity α Relative angle

Claims

1. A mechanical striking mechanism (100) for strikingly driving an insert tool (201) of a hand-held tool machine (200), comprising: A rotatably supported intermediate shaft (101); An impact body (103); A rotatably supported driven shaft (105); Equipped with The intermediate shaft (101) and the striking body (103) each have at least one guide groove (111, 113) that guides at least one guide body (115); and the guide surface (117) of the guide groove (111) of the intermediate shaft (101) and / or the guide surface (119) of the guide groove (113) of the striking body (103) are formed as surfaces without bends and / or edges; A mechanical striking mechanism (100).

2. 2. The striking mechanism (100) according to claim 1, wherein the guide grooves (111, 113) of the intermediate shaft (101) and / or of the striking body (103) have an approximately parabolic extension (121, 123).

3. 3. The striking mechanism (100) according to claim 1 or 2, wherein the perimeter (125, 127) of the intermediate shaft (101) and / or the guide groove (111, 113) of the striking body (103) is formed as a perimeter (125, 127) without a bend.

4. 4. The striking mechanism (100) according to claim 3, wherein the circumferential line (125, 127) of the intermediate shaft (101) and / or the guide groove (111, 113) of the striking body (103) and / or the guide surface (117, 119) can be mapped by a continuously differentiable function.

5. The striking mechanism (100) of claim 4, wherein the function is continuously differentiable at least twice.

6. The striking mechanism (100) according to any one of claims 1 to 5, wherein the curvature of the guide grooves (111, 113) is smaller than the curvature of the guide body (115).

7. The striking mechanism (100) according to any one of the preceding claims, wherein the guide body (115) is formed as a sphere.

8. 8. The striking mechanism (100) according to claim 2, wherein the axial movement of the striking body (103) along the extension (121, 123) of the guide groove (111, 113) is continuous and non-linear with respect to the relative angle between the intermediate axis (101) and the striking body (103).

9. 9. The striking mechanism (100) according to claim 2, wherein the extension (121, 123) of the intermediate shaft (101) and / or the guide groove (111, 113) of the striking body (103) is mirror-symmetrical at a turning point (129, 131).

10. 10. The striking mechanism (100) according to any one of the preceding claims, wherein the lengths of the guide grooves (111, 113) of the intermediate shaft (101) and the striking body (103) are the same or different.

11. 11. The striking mechanism (100) according to claim 2, wherein the inclinations of extension of the guide grooves (111, 113) of the intermediate shaft (101) and the striking body (103) are identical to one another or differ from one another.

12. 12. The striking mechanism (100) according to any one of claims 2 to 11, wherein the inclination of the extension of the guide grooves (111, 113) of the intermediate shaft (101) and the striking body (103), respectively, is constant or variable.

13. The striking mechanism (100) according to any one of claims 1 to 12, wherein the striking mechanism (100) is formed as a rotary striking mechanism.

14. A hand-held tool (200) comprising a mechanical impact mechanism (100) according to any one of claims 1 to 13.

15. The handheld machine (200) of claim 14, wherein the handheld machine (200) is configured as a rotary impact driver.

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