EP2527111A1 - Fraiseuse avec commande oscillante - Google Patents

Fraiseuse avec commande oscillante Download PDF

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Publication number
EP2527111A1
EP2527111A1 EP12003011A EP12003011A EP2527111A1 EP 2527111 A1 EP2527111 A1 EP 2527111A1 EP 12003011 A EP12003011 A EP 12003011A EP 12003011 A EP12003011 A EP 12003011A EP 2527111 A1 EP2527111 A1 EP 2527111A1
Authority
EP
European Patent Office
Prior art keywords
eccentric
pendulum
lever
milling machine
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12003011A
Other languages
German (de)
English (en)
Other versions
EP2527111B1 (fr
Inventor
Sibylle Rapp
Arne Holtz
Markus Stark
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Festool Group and Co KG
Original Assignee
Festool GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Festool GmbH filed Critical Festool GmbH
Publication of EP2527111A1 publication Critical patent/EP2527111A1/fr
Application granted granted Critical
Publication of EP2527111B1 publication Critical patent/EP2527111B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
    • B27F—DOVETAILED WORK; TENONS; SLOTTING MACHINES FOR WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES
    • B27F5/00—Slotted or mortised work
    • B27F5/02—Slotting or mortising machines tools therefor
    • B27F5/023—Portable plate joiners
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
    • B27F—DOVETAILED WORK; TENONS; SLOTTING MACHINES FOR WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES
    • B27F5/00—Slotted or mortised work
    • B27F5/02—Slotting or mortising machines tools therefor
    • B27F5/12—Slotting or mortising machines tools therefor for making holes designed for taking up fittings, e.g. in frames of doors, windows, furniture

Definitions

  • the invention relates to a milling machine, in particular a hand-milling machine, for milling slots in a workpiece, with a rotary drive to a rotary drive a tool holder for a milling tool and a pendulum drive for generating a rotation of the tool holder superimposed on a tool-receiving pendulum axis and pivoting tool holder oscillating movement of the tool holder for the milling tool, wherein the pendulum drive is a pendulum lever which can be driven by a pendulum lever oscillation swinging back and forth about an oscillating lever pivot axis, which is pivotally connected to the tool holder, and an adjusting device for adjusting a pendulum lever Amplitude of the pendulum lever oscillation movement, wherein the eccentric has a rotatable about an eccentric bearing axis and acting on the pendulum lever eccentric.
  • Such a milling machine with which long holes can be milled in a workpiece goes out DE 103 14 087 B3 out.
  • the known milling machine is compact.
  • the pendulum lever is housed in a short, but relatively wide gear housing.
  • a pivotally coupled with the tool holder driving pin is disposed between the eccentric and the pendulum lever axis.
  • the adjusting device is coupled in motion with the eccentric device for adjusting a relative position of the eccentric bearing axis to the pendulum lever pivot axis to adjust the pendulum lever amplitude.
  • a basic idea of the invention is that the eccentric device is adjustable relative to the pendulum lever, so that a large distance between the eccentric bearing axis and the pendulum lever pivot axis is present or adjustable. This allows high accuracy for adjusting the pendulum lever amplitude.
  • the pendulum lever expediently has a guide slot, in which engages the eccentric.
  • the eccentric device or its eccentric bearing axis along the guide slot is a total adjustable, so that the eccentric engages at different locations in the guide slot.
  • a pendulum lever longitudinal axis of the pendulum lever intersects the pendulum lever pivot axis.
  • the guide slot could have a curved course.
  • a preferred embodiment which is still clear in the drawing, however, provides that the guide slot comprises a particular linear extending slot whose longitudinal central axis extends along the pendulum lever longitudinal axis.
  • the eccentric bearing axis in this embodiment preferably adjustable along the pendulum lever longitudinal axis or the longitudinal center axis of the guide slot.
  • a with the eccentric rotatably coupled or rotatably coupled eccentric drive wheel with a eccentric driving, meshing with an eccentric drive shaft driven gear meshes.
  • the output gear, the eccentric drive wheel directly or - in the rotatable coupling - via other wheels and / or a flexible member (belt or the like) drive.
  • the eccentric device is preferably pivotably mounted with the adjusting device about the eccentric drive axis, so that a relative position of the eccentric bearing axis to the eccentric drive axis is adjustable in order to adjust the pendulum lever amplitude.
  • the eccentric bearing axis may be arranged at two different pendulum lever amplitudes once on a first side, the other time on a side opposite the first side of the driven wheel.
  • the eccentric drive wheel is, for example, arranged tangentially on the driven output gear and meshes therewith.
  • the eccentric is expediently mounted pivotably between a first pivot position and a second pivot position about the eccentric drive axle.
  • both pivot positions each have the same distance to a pivot axis, which is orthogonal to the pendulum lever longitudinal axis and / or a central axis of the pendulum lever oscillation movement and / or a central axis of the tool holder oscillation movement.
  • the center line of the pivoting movement, with which the eccentric device, for example a bearing part which supports the eccentric, pivots, preferably has the same spacing with respect to both pivot positions. This center line is expediently perpendicular to Pendulum lever longitudinal axis or to the pendulum lever center axis. This allows a high position accuracy and in particular also that the pendulum lever central axis is centrally centered at both pendulum lever amplitudes.
  • the center axis or center position of the milling tool is expediently the same even with different pendulum lever amplitudes.
  • this also facilitates the positioning of the milling tool or the milling machine relative to the workpiece to be machined, for example by means of an abutment device arranged on the milling machine.
  • the adjusting device has a first, a first pendulum lever amplitude associated stop and a second, a second pendulum lever amplitude associated stop.
  • proposes the adjustment of these attacks for example, to determine the aforementioned pivotal positions of the eccentric and the eccentric bearing axis.
  • the eccentric for example, the bearing part which supports the eccentric strikes a stop.
  • a stop it is also possible for a stop to be present on which the eccentric device abuts, another stop on which the adjusting device, for example an adjusting lever of the same, abuts, in order to determine the respective pendulum lever amplitudes and thus also the amplitude with which the milling tool commutes back and forth.
  • the first and the second stop for the adjusting device and / or the eccentric device are expediently arranged so that the tool-holder oscillating movement has the same central axis at both pendulum lever amplitudes.
  • both stops with respect to a housing of the milling machine, for example, a transmission housing for the Pendulum drive or the pendulum gear, are stationary. Thus, a high precision is possible. But it is also possible that one or both stops (it could also be provided more stops), with respect to a housing of the milling machine are adjustable. Thus, it is possible to set the pendulum lever amplitudes quasi dynamically.
  • a particularly synchronous and / or simultaneous adjusting movement of at least two stops preferably takes place along a linear axis, which is parallel to a pivot axis of the pendulum lever.
  • the attacks are individually individually or simultaneously motion coupled to each other or away from each other adjustable.
  • the adjusting device expediently has an actuating lever acting on the eccentric device or firmly connected thereto, which abuts in its end positions on the first or the second stop.
  • These two stops are preferably stationary.
  • one or both stops could also be movable relative to a housing of the Be milling machine.
  • the adjusting lever is expediently actuated by means of an actuating element, for example a lever, slide or the like.
  • a setting is present on the adjusting lever, in which engages a gate follower of the actuating element.
  • a backdrop could be present, in turn, a arranged on the adjusting lever of the eccentric link follower, for example, a projection engages.
  • the milling machine has a single drive motor, in particular an electric motor, which drives the rotary drive and the pendulum drive via a coupling gear. It is understood that of course also for the pendulum drive and the rotary drive each separate drive motors can be present. Then the rotational movement of the milling tool or the tool holder and the tool holder oscillation movement or oscillating movement of the tool holder can be driven particularly easily with mutually independent rotational speeds.
  • the coupling gear has, for example, a reduction gear.
  • a reduction gear in the pendulum gear is present that reduces a force acting on its drive shaft speed to its drive-coupled with the eccentric output down.
  • the eccentric drive wheel meshes with this output.
  • the tool holder is expediently rotatably mounted on a tool-bearing device, which is mounted pivotably about the tool-receiving pendulum axis.
  • a tool-bearing device which is mounted pivotably about the tool-receiving pendulum axis.
  • the Tool-bearing device on a bearing housing, which also receives the coupling gear.
  • the tool holder pendulum axis and the pendulum lever pivot axis are expediently identical. Thus, so the tool holder pivots about the pendulum lever pivot axis. But it is also possible that between the pendulum lever and the tool holder or the aforementioned tool-bearing device, a transmission gear is present, so that the pendulum lever is coupled via a transmission gear with the tool holder. Possible, for example, a toothing on the head of the pendulum lever, which meshes with a counter toothing on the aforementioned bearing housing or the tool-bearing device which rotatably supports the tool holder, a coupling rod or the like. Further, between the tool holder or the tool-bearing device and the pendulum lever instead of a toothed gear and a belt transmission, cable transmission or the like may be provided.
  • the eccentric is directly coupled to an actuator or coupled in a further preferred manner via a rocker arm assembly.
  • the eccentric In the respective end position of the rocker arm assembly, the eccentric assumes a stable position.
  • the eccentric adjusting lever can of course also have a stable position due to self-locking, latching, holding by a clamp or other holder, for example in the abovementioned, respectively defined amplitudes defining pivot positions when the eccentric pivot lever its respective end position occupies.
  • a milling machine 10 has a drive motor 11 which drives a milling tool 13 directly or via a gear 12.
  • the milling tool 13 is a milling cutter.
  • the drive motor 11 is arranged in a drive housing 14 of a drive part 15.
  • the milling machine 10 is an electrical milling machine, which is supplied with electrical energy, for example via an electrical supply cable, not shown, or by an energy storage component, for example a battery pack, located on the milling machine 10.
  • the drive housing 14 has a handle 16 which can be grasped by an operator. From the handle 16 from a drive switch 17 can be actuated, for example, with the thumb, with which the drive motor 11 is switched on.
  • the drive motor 11 is arranged in a lower housing region 18 of the drive housing 14, for example below the handle 16.
  • the gear 12 is located in a handle 16 upstream upper housing portion 19 of the drive housing 14.
  • the milling tool 13 is frontally below in front of the drive housing 14 before.
  • the milling tool 13 is driven by the drive motor 11 or motor.
  • the transmission 12 includes a pendulum transmission such that the milling tool 13 is an oscillating reciprocating motion P passes through to mill in a schematically illustrated workpiece W recesses, such as slots. In such a recess, for example, a dowel, a fitting or the like can be used.
  • a suitably adjustable on the transmission 12 pivoting range of the reciprocating motion P defines a transverse length of the workpiece recess, while a diameter of the milling tool 13 determines a transverse width of the recess.
  • a stop device 20 is used to abut the milling machine 10 on the workpiece W.
  • the stop device 20 has a front stop surface 21 which is provided for abutment with a front side F of the workpiece W.
  • the stop device 20 has even more stop surfaces, for example, to bear on the workpiece W.
  • a bottom surface 22 of the stopper 20 is, for example, angled, in particular perpendicular, to the front stop surface 21.
  • the stop device 20 can be placed with the bottom surface 22, for example, on a workpiece W upstream surface become.
  • An angular abutment plate 23 provides an angular abutment surface 24, which in the in FIG. 1 shown position of the angular contact plate with the front stop surface 21 is aligned.
  • the angle stop surface 24 is pivotable about a pivot axis 29 with respect to the front stop surface 21.
  • a respective angular position of the angle plate 23 relative to the front stop surface 21 can be fixed with a pivot adjustment device 25.
  • the angular contact plate 23 is also adjustable in height, so that their distance from the bottom surface 22 is adjustable.
  • the stop device 20 has for grasping by an operator still a handle 26, which preferably upwards the stopper 20 protrude ergonomically favorable. Furthermore, a dust removal port 27 is still provided on the stop device 20, can be sucked through the in the processing of the workpiece W accumulating dust or chips.
  • the stop device 20 is relative to the drive member 15, linearly here, along a Tiefenverstellwegs T adjustable.
  • a guide arrangement 30 is provided which guides the stop device 20 linearly with respect to the drive part 15.
  • the drive part 15 is guided relative to the stop device 20, namely that the drive part 15 for processing the workpiece W toward this, i. is moved to the stopper 20, so that the milling tool 13 penetrates into the workpiece W.
  • the stopper 20 is positioned relative to the workpiece W, for example, with the front stop surface 21 applied to the workpiece front side F.
  • the milling tool 13 projects in front of the front stop surface 21. Through a recess 28 on the front stop surface 21, the milling tool 13 in the processing of the workpiece W in front of the front stop surface 21 are available.
  • the guide assembly 30 includes fixed to the stopper 20 guide members 31, which are in front of the stopper 20 in the direction of the drive member 15 and the drive housing 14.
  • the guide elements 31 are slidably received in guide receivers 34, 35 of the drive member 15.
  • the guide receptacles 34, 35 form linear guides for the guide elements 31.
  • the guide receptacles 34, 35 are arranged for example laterally on the drive housing 14, so that the gear 12 and / or the drive motor 11 between the guide receptacles 34, 35 is located.
  • the drive part 15 and the stopper 20 are acted upon by a spring arrangement in a sense away from one another.
  • the front in the drawing guide member 31 and the guide receptacle 35 cooperate with a depth stop assembly 40 which includes a depth stop body 41 which is mounted on a depth stop bearing means 42 along a setting path 43 linearly movable.
  • the adjustment 43 extends parallel or in axial extension to Tiefenverstellweg T.
  • the guide member 31, which penetrates the guide receptacle 35, projects into a recess 47 of the depth stop bearing means 42, at least when the drive member 15 is adjusted to the stopper 20, and strikes against the depth stop body 41, which thus determines the penetration depth of the milling tool 13 into the workpiece W.
  • the depth stop assembly 40 has index bodies 44 which are also movably supported on the depth stop bearing means 42, namely parallel to the depth adjustment path T and the adjustment path 43.
  • the index bodies 44 are disposed on opposite sides of the depth stop body 41 and can be adjusted along the adjustment path 43 limit.
  • the depth stop body 41 can be reciprocated between the index bodies 44.
  • the depth stop body 41 is guided on a guide slot 45, and the index bodies 44 are guided on a guide slot 46 of the depth stop bearing device 42.
  • the front stop surface 21 is arranged on a base body 37 of the stop device 20.
  • the main body 37 has an angular shape and provides on the one hand the bottom surface 22, on the other hand the front abutment surface 21 ready.
  • the angular contact plate 23 is pivotally mounted on the base body 37.
  • the stop device 20 For adjusting transverse distances of the recess to be milled in the workpiece W to a side surface of the workpiece W, ie to a workpiece lateral side Q, the stop device 20 has a plurality of adjusting stops 38 on its front side, i. in the area of the front stop surface 21.
  • the adjustment stops 38 have with respect to a central axis M of the milling tool 13 in its pendulum motion P or - relative to the stopper 20 - with respect to the recess 28 different transverse distances and are in front of the front stop surface 21 in a stop position and behind this back, in Shooting 39 into a rest or non-use position adjustable.
  • the transmission 12 includes a rotary gear 48, which provides a rotary drive for the milling tool 13, a coupling gear 49, which couples the drive motor 11 with the rotary gear 48, and a likewise coupled via the coupling gear 49 to the drive motor 11 pendulum 50.
  • the pendulum 50 sets a pendulum drive 51 ready for a tool holder 52, in which the milling tool 13 rotatably arranged, for example, pluggable, screwed or the like, is.
  • An output shaft 53 of the drive motor 11 drives a helical gear 55 via a bevel gear 54.
  • a bevel gear 56 is arranged on the output shaft 53, which meshes with a further bevel gear 57 of the bevel gear 54.
  • the bevel gear 57 and a crown wheel 58 of the spur gear 55 are connected to each other rotatably connected.
  • the crown wheel 58 drives a tool shaft 59, at the front, free end of the tool holder 52 is arranged.
  • the tool shaft 59 is rotatably connected to a gear or circumferentially has a toothing, with the crown wheel 58 meshes.
  • the tool shaft 59 is rotatably supported by pivot bearings 60 in a tool-bearing device 61.
  • the tool-bearing device comprises a lower part 62, which has an end-side opening 63, on which the tool holder 52 is arranged.
  • the lower part 62 further has a bearing receptacle 64, in which a arranged between the bevel gear 57 and the crown wheel 58 pivot bearing 66 is supported.
  • the bearing receiver 64 and the opening 63 are expediently rectangular, this being an option.
  • the bevel gear 54 is received in the tool-bearing device 61.
  • the bevel gear 54 forms part of the linkage 49.
  • a shaft 67 is rotatably connected, so that a rotation of the bevel gear 57 is transmitted to the shaft 67.
  • the shaft 67 is rotatably mounted on the tool-bearing device 61 via the pivot bearing 66 and a pivot bearing 68, which is arranged in the region of its front, in front of the bevel gear 57 projecting longitudinal end.
  • the pivot bearing 68 is received in a bearing receptacle on a bearing portion 69 of an upper part 70 of the tool-bearing device 61.
  • the top 70 is substantially cylindrical.
  • the upper part 70 and the lower part 62 are firmly connected to each other, for example screwed, glued or welded. An integral construction of a tool-bearing device is alternatively possible.
  • the tool-bearing device 61 in turn is rotatably received by means of rotary bearings 71 in a bearing portion 72 of a gear housing 73 of the transmission 12.
  • the tool-bearing device 61 pivots as a whole about a tool-receiving pendulum axis 74.
  • the milling tool 13 can pivot about the pendulum axis 74, while it can simultaneously rotate about an axis of rotation 65 of the tool shaft 59.
  • the bearing portion 72 is approximately cylindrical overall.
  • the bearing portion 72 has expediently a bearing receptacle with approximately hollow cylindrical shape, to receive the cylindrical in its upper portion cylindrical tool-bearing device 61 rotatably.
  • the depth stop bearing device 42 On the gear housing 73, for example, the depth stop bearing device 42, in particular the guide slot 45 is arranged.
  • the depth stop bearing device 42 is laterally from the bearing portion 72 from.
  • the guide receptacles 34, 35 are integral with the gear housing 73, for example, are arranged laterally below the bearing portion 72.
  • the pendulum gear 50 drives the tool-bearing device 61 to the oscillating, oscillating back and forth pivotal movement P, so therefore to an oscillatory motion about the tool holder pendulum axis 74.
  • the pendulum gear 50 drives the tool-bearing device 61 to the oscillating, oscillating back and forth pivotal movement P, so therefore to an oscillatory motion about the tool holder pendulum axis 74.
  • a driven gear 75 is arranged, for example, next to the pivot bearing 68.
  • the output gear 75 is up in front of the tool-bearing device 61, at least the upper part 70 before.
  • the output gear 75 drives the pendulum gear 50 via a transmission gear.
  • the transmission gear has a reduction gear 76, which reduces the relatively high speed of the output gear 75 via a plurality of intermeshing wheels 77-80 up to a driven gear 82.
  • the wheel 77 meshes with the driven gear 75 on the shaft 67, so it is driven by this.
  • the wheel 77 is disposed on an axle 83.
  • the wheel 77 in turn drives the wheel 78, which is non-rotatably arranged with the wheel 79 on an axle element 84.
  • the wheel 79 in turn drives the wheel 80, which is rotatably mounted on a shaft member 85.
  • the wheel 80 and the output gear 82 are rotatably connected to each other.
  • the axle elements 83, 84 and 85 are formed for example by axle pieces or comprise axle pieces.
  • the axle elements 83, 84 and 85 are e.g. in bearing receivers 86 on the gear housing 73 and / or a cover 87 which closes an interior 88 of the gear housing 73, rotatably mounted.
  • the axle 85 not only supports the wheels 80, 82 but also a bearing member 89 of an eccentric 90.
  • the eccentric 90 includes an eccentric drive wheel 91 which is driven by the output gear 82.
  • An eccentric 92 is rotatably connected to the eccentric drive wheel 91, so that the eccentric drive wheel 91 drives the eccentric 92.
  • the bearing element 89 is rotatably mounted with a bearing portion 93 on the axle 85.
  • the eccentric 92 and the eccentric drive gear 91 are rotatably received in a bearing portion 94 of the bearing member 89.
  • the two bearing portions 93, 94 are for example approximately cylindrical and expediently arranged next to one another.
  • a control lever 95 From the bearing portion 94 is a control lever 95, with which the eccentric 90 can be adjusted as a whole.
  • the adjusting lever 95 and the bearing portion 93 are disposed on opposite sides of the bearing portion 94.
  • the eccentric device 90 pivots about an eccentric drive axle 96 defined by the axle element 85.
  • the eccentric drive axle 96 i. the axis of rotation of the output gear 82, and the pivot axis of the bearing element 89 and the eccentric 90 are therefore identical.
  • the eccentric 90 is pivoted on the axle member 85, the driven gear 82 and the eccentric drive gear 91 remain engaged.
  • the eccentric 92 engages in a guide slot 97 on a pendulum lever 98 a.
  • the guide slot 97 is designed as a slot.
  • the guide slot 97 extends along a pendulum lever longitudinal axis 99.
  • the pendulum lever longitudinal axis 99 extends through the pendulum lever pivot axis 100 about which the pendulum lever 98 is pivotally mounted.
  • the pendulum lever pivot axis 100 advantageously corresponds to the tool-receiving pendulum axis 74.
  • the pendulum lever 98 is in fact non-rotatably connected with its front portion 101 with the tool-bearing device 61.
  • a passage opening 102 is provided, through which the shaft 67, expediently also the bearing portion 69 of the tool-bearing device 61 protrudes upward in front of the pendulum lever 98.
  • the output gear 75 is arranged.
  • a plurality of screws are provided, which are screwed into the upper end wall of the upper part 70 of the tool-bearing device 61.
  • the region 101 of the oscillating lever 98 rests substantially flat or positively against this end wall of the upper part 70.
  • This measure and / or the following described advantageous geometric construction of the pendulum gear 50 contribute to the high precision of the oscillating movement of the milling tool 13, whose amplitude is also precisely adjustable, for which, among other things, the lever 95 is provided.
  • the pendulum lever 98 includes a lever arm 103, on which the guide slot 97 extends.
  • the lever arm 103 protrudes from the front portion 101.
  • the pendulum lever 98 is loaded by springs 104 in the direction of a middle position.
  • the springs 104 are supported on the one hand on inner walls of the interior 88 of the gear housing 73, on the other hand on the pendulum lever 98, for example, the lever arm 103rd
  • the adjusting lever 95 is used to adjust the amplitudes with which the pendulum lever 98 can pivot back and forth, thus thus also the amplitudes with which the milling tool 13 and the tool holder 52 oscillates back and forth.
  • the adjusting lever 95 is adjustable between two pivoting end positions, which are defined by stops 105, 106.
  • the stops 105, 106 comprise pins or other projections on which the adjusting lever 95 can strike laterally.
  • the stops 105, 106 are fixedly connected to the gear housing 73 so that they have a defined position with respect to the same. This measure contributes among other things to the fact that the pendulum stroke or the pendulum amplitude of the pendulum lever 98 and thus of the tool holder 52 and the milling tool 13 are adjustable with high precision.
  • a variant not realized in the exemplary embodiment could provide that the adjusting lever 95 protrudes outwards in front of the drive housing 14, so that it can be grasped and adjusted there by an operator. It is understood that fixed or adjustable stops for this "extended" lever 95 may be provided outside the drive housing. Of the Lever could be latched, clamped or the like otherwise be fixed in its respective pivot position.
  • the adjusting lever 95 and thus the eccentric 90 by means of an adjusting device 107 is adjustable.
  • the adjusting device 107 which may optionally also include the adjusting lever 95 or which could be formed by the described "extended" actuating lever 95, comprises an actuating element 108, e.g. an actuating lever which is pivotally mounted by means of a pivot bearing 109 on the drive housing 14, preferably the transmission housing 73.
  • the actuator 108 is disposed on an axle 110 which is pivotally received in a bearing receptacle 111 of the gear housing 73 and forms together with this the pivot bearing 109.
  • the actuating element 108 is arranged, for example, laterally on the transmission housing 73, so that it can be easily grasped.
  • the adjusting device 107 is preferably designed so that it holds the adjusting lever 95 and / or the eccentric 90 stably on the respective stop 105 or 106. This could be done, for example, by a latching in which, for example, the adjusting lever 95 and / or the actuating element 108 and / or a component coupled thereto in a stationary manner latched. Even a self-locking would be possible. In the present case, however, a rocker arm assembly is realized.
  • the actuating element 108 is coupled by means of a driver 112 with the adjusting lever 95.
  • the driver 112 engages in a link 113 on the lever 95.
  • the backdrop 113 is a Longitudinal groove, the driver 112, which represents a gate follower insofar, for example, is designed as a projection.
  • the driver 112 is disposed on an actuating arm 114 which projects radially from the axle 110.
  • the actuator 108 and the actuator arm 114 preferably protrude on opposite sides in front of the axle 110.
  • a spring 115 loads the adjusting device 107 in its respective end position, in which the eccentric 90 strikes one of the two stops 105 or 106.
  • the spring 115 acts for example on the actuating arm 114, in particular on a projection 116 on the actuating arm 114.
  • the spring 115 is supported on a not visible in the drawing abutment in the interior 88 of the gear housing 73 or the bearing member 89 from.
  • the spring 115 loads the actuating arm 114 in the direction of the respective end position in which the driver 112 presses the adjusting lever 95 in the direction of the stop 105 or the stop 106, so that the adjusting lever 95 and thus the eccentric 90 assumes a stable position.
  • An index part 117 comprises an axle element 118, which is pivotably mounted on the drive housing 14 and / or on the transmission housing 73 and / or on the cover 87.
  • the corresponding bearing support or bore is not shown in the drawing.
  • the index member 117 is taken from the lever 95 when it is adjusted between its end positions. It is understood that a rotational drive of an index part, for example, via an eccentric easily would be possible.
  • a driving projection 119 is arranged, which abuts laterally on the adjusting lever 95, for example. It is possible that the index member 117 is taken only in one direction by the adjusting lever 95 and is acted upon in the opposite direction, for example by a spring. A bi-directional entrainment is of course possible.
  • an index projection 120 is further provided, which projects outwardly in front of the drive housing 14.
  • the drive housing 14 has a display recess 121, for example a recess in which at least a front, free region of the index projection 120 is visible.
  • the index projection 120 is shown in the display recess 121 on a scale 122.
  • the scale 122 includes, for example, numbers or symbols or both, which make visible the set pendulum lever amplitude.
  • the eccentric 90 pivots between a first pivot position 123 associated with the stop 105 and a second pivot position 124 associated with the stop 106. Between the pivot positions 123, 124, as by the eccentric drive shaft 96 and the axis of rotation of the eccentric drive axle 96 extending lines are shown in the drawing, a pivot axis 125 extends.
  • pivot center axis 125 as in the embodiment is orthogonal to a central axis of the tool holder oscillation movement or orthogonal to a central axis of the pendulum lever oscillation movement.
  • These two central axes preferably coincide in the embodiment or are identical. They are designated M in the drawing.
  • the distance of the eccentric 92 from the tool-receiving pendulum axis 74 or the pendulum lever pivot axis 100 is relatively large, so that a larger pendulum lever amplitude A1, which is associated with the stop 105, and a smaller, the stop 106 associated pendulum lever -Amplitude A2 are respected each with great precision.
  • the amplitudes A1 and A2 are shown exaggerated for better visibility.
  • the stops 105, 106 may preferably be mounted so as to be displaceable simultaneously parallel (arrow 127) to the pivot center axis 125, for example, when they are arranged on a corresponding slide or schematically indicated actuating body 126, in order to open this way to set further amplitudes of the pendulum lever oscillation movement.
  • stops 105, 106 could be synchronously via a gear (not shown) to each other or away from each other adjustable, in particular linear or along a curved path.
  • the springs 104 ensure that the pendulum lever 98 and the eccentric 92 always remain in contact. This is also the case when the eccentric 92 is located, for example, in expanded or wider areas of the guide slot 97 at their respective longitudinal ends.
  • the tool holder pendulum axis 74 and the pendulum lever pivot axis 100 are identical in the present case.
  • This in itself represents an independent concept according to the invention, ie it does not matter in this respect that the eccentric device 90 pivots about the eccentric drive axle 96 and moreover does not insist that the eccentric 92 acts directly on the pendulum lever 98, in particular the guide slot 97 is added.
  • a crank drive which is actuated by the output gear 82 and acts on the pendulum lever 98 via a connecting rod.
  • the pendulum lever longitudinal axis 99 and the axis of rotation 65 of the tool holder 52 and the longitudinal axis of the tool shaft 59 in the middle position of the pendulum lever 98 and tool holder 52, corresponding to the central axis M, in the same plane so are parallel and aligned.
  • An inclination between the two central axes or longitudinal axes of the tool holder and the pendulum lever is readily possible, so that, for example, the pendulum lever could be inclined in its central position to the longitudinal axis of the milling tool. This alternative is not shown in the drawing.

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  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Wood Science & Technology (AREA)
  • Mechanical Engineering (AREA)
  • Forests & Forestry (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
EP20120003011 2011-05-24 2012-04-28 Fraiseuse avec commande oscillante Active EP2527111B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201110103014 DE102011103014B4 (de) 2011-05-24 2011-05-24 Fräsmaschine mit einem Pendelgetriebe

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Cited By (2)

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CN109352041A (zh) * 2018-12-26 2019-02-19 罗甸县金泰模具机械制造有限公司 铣头360度旋转定位水平移动万向铣钻装置
CN109482946A (zh) * 2018-12-26 2019-03-19 罗甸县金泰模具机械制造有限公司 铣头360度旋转定位电动万向铣钻装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102024101338A1 (de) * 2024-01-17 2025-07-17 Festool Gmbh Handgehaltenes Elektrowerkzeug und Verfahren zum Betreiben eines handgehaltenen Elektrowerkzeugs

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US843322A (en) * 1905-01-26 1907-02-05 Peter Bontenakels Groove-cutting machine.
US1415790A (en) * 1920-12-30 1922-05-09 George W Campbell Mortising machine
US1469170A (en) * 1921-07-13 1923-09-25 George E Norris Mortising machine
US1698069A (en) * 1924-08-21 1929-01-08 Perfection Mortiser Company Mortising machine
CH237664A (de) * 1940-10-22 1945-05-15 Mueller & Cie Maschinenfabrik Stemmaschine.
CH284155A (de) * 1950-09-27 1952-07-15 Imhof Hugo Stemmvorrichtung für Kettenfräsmaschinen.
US2895516A (en) * 1956-01-05 1959-07-21 Mayer Max Oscillating adjustable stroke mortising machine
SU715321A1 (ru) * 1978-08-23 1980-02-15 Специальное Конструкторско-Технологическое Бюро По Автоматике И Нестандартному Оборудованию Главмоспромстройматериалов Долбежна головка к станку дл образовани пазов в древесине
DE10314087B3 (de) 2003-03-28 2004-11-11 Festool Gmbh Fräsmaschine
DE102005036213B3 (de) * 2005-08-02 2006-10-05 Festool Gmbh Fräsmaschine

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Publication number Priority date Publication date Assignee Title
US843322A (en) * 1905-01-26 1907-02-05 Peter Bontenakels Groove-cutting machine.
US1415790A (en) * 1920-12-30 1922-05-09 George W Campbell Mortising machine
US1469170A (en) * 1921-07-13 1923-09-25 George E Norris Mortising machine
US1698069A (en) * 1924-08-21 1929-01-08 Perfection Mortiser Company Mortising machine
CH237664A (de) * 1940-10-22 1945-05-15 Mueller & Cie Maschinenfabrik Stemmaschine.
CH284155A (de) * 1950-09-27 1952-07-15 Imhof Hugo Stemmvorrichtung für Kettenfräsmaschinen.
US2895516A (en) * 1956-01-05 1959-07-21 Mayer Max Oscillating adjustable stroke mortising machine
SU715321A1 (ru) * 1978-08-23 1980-02-15 Специальное Конструкторско-Технологическое Бюро По Автоматике И Нестандартному Оборудованию Главмоспромстройматериалов Долбежна головка к станку дл образовани пазов в древесине
DE10314087B3 (de) 2003-03-28 2004-11-11 Festool Gmbh Fräsmaschine
DE102005036213B3 (de) * 2005-08-02 2006-10-05 Festool Gmbh Fräsmaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109352041A (zh) * 2018-12-26 2019-02-19 罗甸县金泰模具机械制造有限公司 铣头360度旋转定位水平移动万向铣钻装置
CN109482946A (zh) * 2018-12-26 2019-03-19 罗甸县金泰模具机械制造有限公司 铣头360度旋转定位电动万向铣钻装置

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EP2527111B1 (fr) 2013-06-19
DE102011103014A1 (de) 2012-11-29

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