EP2774733A1 - Appareil de travail manuel doté d'un dispositif de serrage pour une chaîne - Google Patents

Appareil de travail manuel doté d'un dispositif de serrage pour une chaîne Download PDF

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Publication number
EP2774733A1
EP2774733A1 EP14000735.2A EP14000735A EP2774733A1 EP 2774733 A1 EP2774733 A1 EP 2774733A1 EP 14000735 A EP14000735 A EP 14000735A EP 2774733 A1 EP2774733 A1 EP 2774733A1
Authority
EP
European Patent Office
Prior art keywords
tension spring
guide rail
spring
actuating
fastening
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.)
Withdrawn
Application number
EP14000735.2A
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German (de)
English (en)
Inventor
Helmut Zimmermann
Jonas Lank
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.)
Andreas Stihl AG and Co KG
Original Assignee
Andreas Stihl AG and Co KG
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 Andreas Stihl AG and Co KG filed Critical Andreas Stihl AG and Co KG
Publication of EP2774733A1 publication Critical patent/EP2774733A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
    • B27B—SAWS FOR WOOD OR SIMILAR MATERIAL; COMPONENTS OR ACCESSORIES THEREFOR
    • B27B17/00—Chain saws; Equipment therefor
    • B27B17/14—Arrangements for stretching the chain saw

Definitions

  • the invention relates to a hand-held implement with a tensioning device for a chain of the type specified in the preamble of claim 1.
  • a device for automatically tensioning a chain of a power saw is known.
  • the device has a coil spring which is supported at one end on the housing and at a second end to a Verstellnocken.
  • a separate locking cam must be operated to relax the saw chain.
  • the GB 2 481 038 A shows a tensioning device for a chain in which a locking device is provided, which keeps the tension spring tensioned when the sprocket cover is removed.
  • the invention has for its object to provide a hand-held implement with a tensioning device for a chain that allows easy tensioning and replacement of the chain.
  • the tension spring is tensioned in the fastening direction when the actuating device is actuated.
  • the mounting direction of the actuator is the direction in which the actuator is to operate to fix the guide rail. Accordingly, the tension spring is maximally tensioned when the fastening device fixes the guide rail.
  • the chain is tightened when mounting the guide rail, so when operating the actuator in the mounting direction. If the fastening device is released, for example for changing the chain or the guide rail, then the tension spring is advantageously at least partially relaxed. As a result, no additional facilities are necessary to interrupt the active connection between tension spring and guide rail and keep the tension spring in a tensioned state when changing the guide rail.
  • the implement has an inhibiting device which prevents a relaxation of the tension spring in partially dissolved actuator.
  • the inhibiting device advantageously comprises a friction belt which acts against a friction surface.
  • the friction belt can advantageously come into operative connection with the actuating device and with the tension spring.
  • the actuating device advantageously acts in the friction force-reducing direction on the friction belt. As a result, the frictional resistance, which the friction belt opposes to actuation in the actuating direction, that is to say the tightening of the actuating device, is reduced.
  • the tension spring acts advantageously in the frictional force increasing direction on the friction belt.
  • the tension spring is thereby prevented by the friction band from relaxing.
  • the actuating device acts in the frictional force increasing direction on the friction belt.
  • the actuating device also acts on the friction belt during the actuation in the release direction in the friction force-reducing direction.
  • the actuating device advantageously acts against a first end of the friction band and when actuated in the release direction against a second end of the friction band.
  • the friction band is formed integrally with the tension spring.
  • the tension spring is advantageously arranged in a separate spring housing.
  • the arrangement of the tension spring in a separate spring housing results in a simple assembly of the overall arrangement and good protection of the tension spring from contamination.
  • the spring housing is held in particular on the actuating device. This results in a compact design.
  • the spring housing is advantageously arranged at least partially in the actuating device.
  • the tension spring is relaxed when the fastening device is completely loosened.
  • the tension spring may be a coil spring.
  • Coil springs are usually arranged in a housing that receives the force exerted by the outer winding (s). Under a completely relaxed coil spring is understood in the present case a coil spring in which no spring force acts at the inner end. The outer turns can still be under tension, the force is absorbed by the spring housing.
  • a fully relaxed coil spring is a coil spring in which the inner end does not apply torque to the outer end.
  • the tensioning of the tension spring and the maximum actuating travel of the fastening device are matched to one another.
  • the maximum clamping travel of the tension spring is advantageously greater than the maximum actuation travel of the fastening device. This ensures that the tension spring when adjusting the actuator in the direction of actuation can not be stretched unduly wide.
  • the tension spring is a helical spring and the fastening device has a thread which is screwed onto a mating thread for unscrewing and loosening the guide rail or is unscrewed from the mating thread, it is advantageously provided that the permissible number of revolutions around which the ends of the tension spring when tightening the tension spring can be rotated against each other, is greater than the number of threads of the fastening device, in which the fastening device is screwed to the complete fixation of the guide rail.
  • the tension spring is advantageously a spiral spring, and the actuating device is rotatable in the actuating direction and in the release direction. This results in a simple, intuitive operation of the fastening device.
  • the actuator For fixing and tensioning of guide rail or chain only the actuator must be rotated in the direction of actuation. In the process, the tension spring is tensioned, which simultaneously tensions the chain.
  • the actuating device advantageously has a thread. The rotational movement of the actuator causes via the thread a movement of the actuator transversely to the plane of the guide rail.
  • the guide rail can be clamped transversely to the plane of the guide rail via the movement of the actuating device, and the clamping device can be tensioned via the rotary movement of the actuating device.
  • the actuator can advantageously be rotated so far until the guide rail is clamped held on the housing of the work device. To release the actuator is rotated in the release direction. At the same time the coil spring is relaxed, so that a simple replacement of the chain or the guide rail is possible.
  • the rotational movement of the actuator in the release direction causes via the thread at the same time a movement of the actuator transverse to the plane of the guide rail, whereby the clamping of the guide rail is released.
  • a simple structure results when the tension spring is arranged in an at least partially limited by the actuator interior.
  • the mounting region of the guide rail is covered by a sprocket cover, which has a receptacle for the tensioning device. This results in a simple, compact design. By replacing des.Kettenraddeckels the jig can be easily retrofitted to existing equipment.
  • the clamping device has a sliding link, wherein each rotational position of the sliding link is assigned a position of the guide rail.
  • the sliding link is in particular a spiral guide, in which a pin is guided.
  • the pitch angle of the spiral guide is designed so that the sliding link is not self-locking in the opposite direction of the clamping direction. This ensures that the tension in the chain does not exceed the tension provided by the tensioning device.
  • the sliding link is advantageous in operative connection with the tension spring.
  • the clamping device has a securing device which secures the rotational position of the sliding link in a form-fitting manner.
  • the securing device is advantageously designed so that it acts only immediately before reaching the fully fixed position of the actuating device, so that the actuation and release of the actuating device is not complicated by the securing device.
  • the implement has a fixation for the actuator, which secures the actuator positively against a housing part.
  • a fixation for the actuator which secures the actuator positively against a housing part.
  • the actuator has a pivotable bracket which is rotatably connected in a mounting position with the housing part and in an operating position allows actuation of the actuator.
  • the pivotable bracket must be pivoted into the operating position. Subsequently, the actuating device can be actuated, for example rotated.
  • Fig. 1 shows as an exemplary embodiment of a hand-held implement a power saw 1.
  • the power saw 1 has a housing 2 to which a guide rail 8 is fixed via a fastening device 12.
  • a chain 9 is guided circumferentially, which is driven by a sprocket 10.
  • the chain 9 is formed as a saw chain.
  • the implement may also be a rock cutter, in which on the guide rail 8 designed as a cutting chain chain 9 is arranged for cutting rock.
  • the guide rail 8 is opposite to the Housing 2 moves in a clamping direction 15, which is directed from the housing 2 in the direction of the free, projecting away from the housing 2 end of the guide rail 8.
  • the region of the guide rail 8, which is fixed to the housing 2, as well as the sprocket 10 is covered by a sprocket 11.
  • a rear handle 3 is arranged on the housing 2, on which a throttle lever 4 and a throttle lever lock 5 are pivotally mounted.
  • a drive motor 150 arranged in the housing 2 is to be operated.
  • the drive motor 150 is designed as an internal combustion engine.
  • the drive motor 150 may also be an electric motor which is connected via a connecting cable to a power supply or which is powered by a battery or a battery with energy.
  • the power saw 1 has a handle tube 6, which engages over the housing 2 of the power saw 1, and a hand guard 7, which extends to the guide rail 8 facing side of the handle tube 6.
  • the hand guard 7 is advantageously used to trigger a braking device, not shown, for the chain. 9
  • the fastening device 12 is to be actuated via an actuating device 19, which is formed in the embodiment as a rotary.
  • actuating device 19 In the in Fig. 1 shown, non-actuated state of the actuator 19 closes the actuator 19 approximately flush with the outside of the sprocket 11 from.
  • a bracket 26 of the actuator 19 To actuate the actuator 19, a bracket 26 of the actuator 19 must be folded outward. So that the operator can grip the bracket 26 well, a recessed grip 56 is provided on the bracket 26.
  • the actuator 19 is rotated in a release direction 77, which runs counterclockwise in the embodiment in the direction of rotation in the embodiment.
  • the actuating device is rotated in a fastening direction 76.
  • the attachment direction 76 is aligned in the exemplary embodiment in a clockwise direction.
  • a rotary movement of the actuator 19 may also be another Movement of the actuator 19, for example, a linear movement along the sprocket 11 may be provided.
  • the chainsaw 1 has an in Fig. 4 shown tensioning device 13.
  • the tensioning device 13 comprises an in Fig. 4 shown tension spring 14 which is formed in the embodiment as a spiral spring.
  • the tension spring 14 acts on a later described in more detail Verschiebekulisse, which is also part of the tensioning device 13 and the rotational movement of the tension spring 14 in a longitudinal movement of the guide rail 8 in the in Figures 1 and 2 shown clamping direction 15 converts.
  • Fig. 2 shows a part of the clamping device 13 in an exploded view.
  • the arranged in the actuator 19 part of the clamping device 13 is not visible in this illustration.
  • the sprocket 11 has a receptacle 20 whose bottom 89 has an opening 91.
  • the opening 91 extends over a large part of the front side of the receptacle 20, so that the bottom 89 is essentially formed by a peripheral edge.
  • the bottom 89 has a tooth contour 27, whose function will be explained in more detail below.
  • the friction belt 17 is disposed on the outer periphery of the actuator 19 between the actuator 19 and the friction surface 18.
  • the friction belt 17 forms with the friction surface 18 an inhibiting device 16, the function of which will be described in more detail below.
  • the tensioning device 13 comprises a rotary element 29 and a displacement element 30, which are arranged on the inside of the sprocket cover 11 facing the housing 2.
  • a driver 28 is rotatably held, the rotationally fixed connection with one end of the tension spring 14 (FIG. FIGS. 3 and 4 ) serves, as will be described in more detail below.
  • the rotary member 29 As a sliding link, the rotary member 29 a spiral guide 21. In the spiral guide 21, a pin 31 of the displacement element 30 is arranged.
  • the displacement element 30 protrudes with in Fig. 3 retaining lugs 50 shown in openings 23 of the guide rail 8 and is thereby rotatably connected to the guide rail 8.
  • a fastening bolt 24 and a guide pin 25 are fixed, each having a collar 32 for abutment of the guide rail 8.
  • the fastening bolt 24 and the guide pin 25 project through a longitudinal groove 22 of the guide rail 8.
  • the fastening bolt 24 and the guide pin 25 also protrude through a Fig. 5
  • the displacement element 30 and the guide rail 8 can only move in the clamping direction 15, which is aligned in the direction of the longitudinal groove 22 and the longitudinal slot 41, and in the opposite direction relative to the housing 2.
  • a rotation of the rotary member 29 about the rotation axis 92 causes a movement of the pin 31 in the spiral guide 21. This changes the distance of the pin 31 to the rotational axis 92 of the rotary member 29.
  • the axis of rotation 92 is the axis of rotation of the actuator 19.
  • the displacement element 30 is in Clamping direction 15 shifted when the distance between the pin 31 and the rotation axis 92 is reduced.
  • Fig. 3 shows, the driver 28, the rotary member 29 and the displacement element 30 in the direction of the axis of rotation 92 are firmly connected.
  • a rivet sleeve 37 and a plate spring 38 To secure the connection serve a rivet sleeve 37 and a plate spring 38.
  • the plate spring 38 causes when tightening the actuator 19 in a structurally predetermined angle range a steadily increasing torque. This gives the operator a feedback that the screw is fixed and the guide rail 8 is kept clamped.
  • the structurally predetermined angle range can be, for example, from about 90 ° to about 360 °, in particular about 180 °.
  • the angular range can also extend over more than 360 °.
  • a fastening screw 36 may be provided, which is screwed into a retaining lug 50.
  • a bead 49 is formed on the spiral guide 21.
  • the rotary member 29 is advantageously made of a thick sheet, in which the spiral guide 21 is impressed. When embossing the spiral guide 21, the bead 49 is formed.
  • the sheet can, for example have a thickness of more than 1 mm. As a result, sufficient mechanical stability of the rotary element 29 is ensured even at high forces acting on the rotary element 29.
  • the tension spring 14 of the tensioning device 13 is disposed in an inner space 34 of the actuator 19.
  • the actuating device 19 has a main body 39 which limits the interior space 34.
  • a threaded sleeve 33 is held on the main body 39.
  • the threaded sleeve 33 can be positively connected to the base body 39 and / or be injected into the base body 39, which is advantageously a plastic part.
  • the threaded sleeve 33 serves to screw the fastening device 12 on the fastening bolt 24, such as Fig. 4 shows.
  • the tension spring 14 is disposed in a spring housing 40, which closes the interior 34 of the actuator 19 to the inside of the sprocket 11 towards. As a result, the tension spring 14 is protected from contamination.
  • a driver 35 is rotatably mounted on the main body 39.
  • the driver 35 has at least one driving lug 58. In the embodiment, two opposing driving lugs 58 are provided, of which in Fig. 3 one is shown. Each entrainment approach 58 protrudes between Fig.
  • FIG. 5 shown driving lugs 43 of the driver 28 and thus provides a rotationally fixed connection between the inner end of the tension spring 14 and the driver 28 ago.
  • the driver 28 is about in Fig. 5 shown recess 44 and a pin 45 on the rotary member 29 rotatably connected to the rotary member 29.
  • the spring force of the tension spring 14 acts on the rotary element 29.
  • the threaded sleeve 33 acts on the plate spring 38, the driver 28, the rotary member 29 and the displacement element 30 against the guide rail 8 and thereby presses the guide rail 8 against the collar 32 and in Fig. 4 schematically drawn housing 2 of the power saw 1.
  • the threaded sleeve 33, the plate spring 38, the driver 28, the rotary member 29th and the displacement element 30 made of metal, so that a good fixation of the guide rail 8 results.
  • the main body 39 of the actuator 19 has on its front side an edge 83 which presses against the bottom 89 of the receptacle 20 and thereby presses the sprocket 11 against the housing 2, so that the sprocket 11 is well fixed.
  • the base body 39 is designed so that the clamping force for fixing the sprocket 11 is introduced directly into the bottom 89 of the receptacle 20 of the sprocket 11, without further elements such as the spring housing 40 are arranged in the power flow. This can be achieved by appropriate design of the tolerances or training according to defined contact surfaces.
  • the FIGS. 5 to 7 show the structure of the tensioning device 13 in detail.
  • the tensioning device 13 comprises a rivet sleeve 37 which projects through the longitudinal slot 41 of the displacement element 30, through an opening 51 in the rotary element 29, through an opening 42 in the driver 28 and through the plate spring 38.
  • the rivet sleeve 37 causes an axially fixed, but rotatable connection of said elements together.
  • the rotationally fixed connection of the driver 28 with the rotary member 29 is achieved via the recess 44 on the driver 28 and the pin 45 on the rotary member 29.
  • the rotary member 29 has two driving openings 46, which are aligned so that the driving lugs 58 of the driver 35 (FIG. Fig. 3 ) can engage in the driving openings 46.
  • Fig. 6 shows the rotary member 29 with the rivet sleeve 37 and the plate spring 38 without the between disc spring 38 and rotary member 29 to be arranged driver 28 to illustrate the structure.
  • the actual arrangement in which the driver 28 is disposed between the plate spring 38 and the rotary member 29 is in Fig. 7 shown.
  • a securing contour 48 is formed adjacent to the pin 31 on the displacement element 30, adjacent to the pin 31 on the displacement element 30, adjacent to the pin 31 on the displacement element 30, a securing contour 48 is formed.
  • the securing contour 48 is arranged on the side of the journal 31 facing away from the longitudinal slot 41.
  • the rotary element 29 has a securing contour 47 into which the securing contour 48 engages when the fastening device 12 is completely fixed. As a result, a positive connection of rotary member 29 and displacement element 30 is achieved.
  • the securing contours 47 and 48 form a securing device 59 (FIG. Fig. 6 ), which prevents the rotary member 29 rotate in operation relative to the displacement element 30 and thus change the tension of the chain 9, in particular the chain 9 can loosen.
  • the spiral guide 21 extends by less than one revolution about the rotation axis 92.
  • the angle which encloses the spiral guide 21 with the circumferential direction is thereby comparatively large.
  • the guide rail 8, the sliding element 30 against the force of the tension spring 14 move against the clamping direction 15 when the chain tension significantly exceeds the force of the tension spring 14. This may be the case, for example, when the chain 9 is tensioned in the warm state and the tensioning device 13 is then fixed. Upon cooling, the chain 9 shrinks, which significantly increases the chain tension. If necessary, the chain 9 can no longer be moved manually over the guide rail 8.
  • the tension spring 14 is formed as a spiral spring.
  • the tension spring 14 has an outer end 53 which is fixed in a receptacle 55 of the spring housing 40.
  • the tension spring 14 has an inner end 52 which is hooked to a receptacle 54 on the driver 35.
  • the actuator 19 is rotatably connected to the spring housing 40. Rotation of the actuating device 19 in the fastening direction 76 causes the outer end 53 to move in the fastening direction 76 relative to the inner end 52 of the tension spring 14. As a result, the tension spring 14 is tensioned.
  • the bracket 26 is pivotable about a pivot axis 57 relative to the base body 39 of the actuator 19.
  • bearing pin 61 is provided.
  • the bearing pin 61 pivotally supports the bracket 26 on the base body 39.
  • the bracket 26 is biased by a spring 62 in the direction of its folded into the receptacle 20 position.
  • the bracket 26 has at least one fixing pin 60, which is approximately parallel to the axis of rotation 92 when the bracket 26 is folded in ( Fig. 4 ).
  • the bracket 26 is in the folded state adjacent to a wall 67 of the body 39. Wie Fig. 4 shows, the wall 67 also limits the interior 34, so that the tension spring 14 is protected from contamination.
  • the wall 67 has a recess 66 through which the fixing pin 60 protrudes.
  • the fixing pin 60 engages in the in the Figures 2 and 3 shown tooth contour 27 at the bottom 89 of the receptacle 20 and thereby fixes the actuator 19 positively against rotation on the sprocket 11.
  • the tooth contour 27 is open to the interior of the sprocket 11. Dirt that has accumulated in the region of the tooth contour 27 is thereby pressed by the fixing pin 60 into the interior of the sprocket 11 and passes from there to the environment. A clogging of the tooth contour 27 is prevented.
  • the base body 39 has a toothing 64, in which a toothing 65 of the threaded sleeve 33 engages.
  • the threaded sleeve 33 is positively held on the base body 39.
  • the teeth 64 and 65 are made separately from each other and the threaded sleeve 33 is pressed into the body 39.
  • the threaded sleeve 33 with the toothing 65 can also be encapsulated by the base body 39, wherein the toothing 64 is formed.
  • the spring housing 40 has an opening 86 through which the driver 35 protrudes.
  • the driver 35 has an outwardly projecting, circumferential edge 87 which abuts adjacent to the opening 86 on the spring housing 40 and the driver 35 axially secures.
  • the spring housing 40 has adjacent to the opening 86 a nozzle 88 which surrounds the region of the edge 87 of the driver 35.
  • the entrainment approach 58 protrudes beyond the neck 88.
  • the entrainment approach 58 has a slope 71, which serves as a guide slope when attaching the driver 35 to the driver 28 and the plugging easier.
  • the edge 83 of the base body 39 has a recess 69, into which a formed on the edge 81 of the spring housing nose 68 protrudes.
  • the spring housing 40 and the base body 39 are rotatably connected to each other.
  • the base body 39 has support ribs 82, which support the spring housing 40, which may be formed, for example, as a thin plastic injection molded part, and prevent deformation of the spring housing 40.
  • the spring housing 40 has an actuating web 70th Fig. 10
  • the friction belt 17 has a first end 74 and a second end 75.
  • the first end 74 projects between the actuating web 70 and a spring housing 40 formed on the first stop surface 78.
  • the stop surface 78 is in Fig. 11 shown and in Fig. 10 schematically drawn.
  • the second end 75 projects between a wall 80 of the base body 39 and a wall 93 on the bracket 26. This is in Fig. 11 shown schematically.
  • the tension spring 14 is relaxed. If the actuating device 19 is rotated in the fastening direction 76, that is to say in the illustration in FIG Fig. 10 in the clockwise direction, the base body 39 of the actuator 19 and the spring housing 40 move relative to the friction belt 17 until the first stop surface 78 comes into contact with the first end 74 of the friction belt 17. The second end 75 then still has a distance from the wall 93. The stop surface 78 takes the friction belt 17 and thereby reduces the diameter of the friction belt 17th slightly. This results in a low frictional resistance between friction belt 17 and friction surface 18, and the actuator 19 can be easily operated.
  • the inner end 52 of the tension spring 14 is rotatably connected to the rotary member 29. Due to the frictional resistance between the guide rail 8, the fastening bolt 24, the guide pin 25 and the housing 2 (FIG. Fig. 4 ), the inner end 52 is held stationary with a relaxed tension spring 14. As a result, the tension spring 14 is tensioned when the actuating device 19 is actuated in the fastening direction 76. As soon as the force of the tension spring 14 exceeds the frictional forces acting on the rotary element 29, the displacement element 30 and the guide rail 8, the rotary element 29 is rotated and the displacement element 30 is displaced with the guide rail 8 and the chain 9 is tensioned.
  • the maximum clamping force of the tension spring 14 is achieved significantly before the complete fixing of the clamping device 13, so that a tensioning of the chain 9 is ensured with the desired clamping force.
  • the threaded sleeve 33 and the fastening bolt 24 are matched to the tension spring 14 so that the tension spring 14 is not fully tensioned when the fastening device 12 is completely fixed.
  • the maximum tension of the tension spring 14, so the number of revolutions by which the tension spring 14 can be maximally tensioned, is greater than the maximum actuation travel of the fastening device 12, that is, the number of threads by which the actuator 19 are screwed onto the mounting bolt 24 can until the guide rail 8 is clamped between the displacement element 30 and the fastening bolt 24.
  • the threaded sleeve 33 is screwed onto the fastening bolt 24 and thereby fixed the guide rail 8.
  • the tension spring 14 is tensioned.
  • the tensioning spring 14 tensions the chain 9 by displacing the guide rail 8 in the tensioning direction 15.
  • the tensioning of the chain 9 takes place until the chain 9 is completely in contact with the guide rail 8.
  • the securing contours 47 and 48 engage one another positively Engagement, so that the rotating member 19 and the displacement member 30 can no longer rotate against each other. If the actuator 19 is further rotated in the attachment direction 76, the guide rail 8 is clamped and thereby fixed.
  • the displacement element 30 is along the in Fig. 5 shown line 63 slightly away from the rotary member 29 and bent to the guide rail 8 out.
  • the securing contours 47 and 48 are not engaged with each other. Only when the displacement element 30 comes to bear against the guide rail 8 during tightening of the arrangement and the region 31 of the displacement element 30 is bent toward the rotary element 29, the securing contours 47 and 48 come into engagement with each other.
  • the actuating web 70 comes to rest on the first end 74 of the friction belt 17.
  • the second end 75 of the friction belt 17 is not in contact with the wall 80. Due to the movement of the actuating web 70 in the release direction 77, the friction belt 17 is slightly widened and pressed against the friction surface 18.
  • the operator In order to actuate the actuating device in the release direction 77, the operator must additionally overcome the frictional resistance between the friction belt 17 and the friction surface 18.
  • the tension spring 14 also acts in the release direction 77 on the spring housing 40 and the actuator 19.
  • the base body 19 adjacent to the actuating web 70 has a support rib 85, on which the actuating web 70 is supported.
  • the central axis 72 of the tension spring 14 is arranged at a small distance from the axis of rotation 92 of the actuator 19. As a result, there is sufficient space for the Fixerzapfen 60 available. Characterized in that the tension spring 14 is arranged with axial offset to the axis of rotation 92, a large outer periphery of the tension spring 14 can be achieved at the same time.
  • the central axis 72 is the geometric center of the outer turn of the tension spring 14.
  • Fig. 11 also shows the suspension of the inner end 52 on the driver 35th Wie Fig. 11 Also shows, an area 84 of the spring housing 40 abuts against the support ribs 85.
  • FIGS. 12 to 15 show two fixing pins 60 are provided in the embodiment. Also, a different number of fixing pins 60, for example one or three or more fixing pins 60 may be advantageous. Does a fixing pin 60 when folding the bracket 26 not on a gap, but a ridge of the tooth contour 27, this can lead to the breaking out of the tooth contour 27. In order to reduce the forces acting on the tooth contour 27 forces and avoid the breaking of the tooth contour 27, a plurality of fixing pins 60 are advantageous. At least one fixing pin 60 advantageously consists of metal or has a metallic coating. As a result, the wear on the fixing pin 60 can be reduced.
  • Fig. 13 shows the arrangement of the portion 84 of the spring housing 40 on the support webs 82. Wie Fig.
  • the base body 39 engages positively in the spring housing 40 a.
  • webs 73 are formed on the base body 39, which are part of the edge 83 and against the bottom 89 of the receptacle 20 (FIG. Fig. 2 ) Act.
  • the webs 73 partially cover the tooth contour 27. This complicates that dirt from the interior of the sprocket 11 can pass through the tooth contour 27 to the friction belt 17.
  • FIGS. 13 and 14 also show the two driving lugs 58 of the driver 35, which are arranged opposite to each other.
  • Fig. 15 shows the first end 74 between the stop surface 78 and the actuating bar 70.
  • the distances to the stop surface 78 and the actuating bar 70 are significantly smaller than that of the second end 75 to the wall 80 or the wall 93. This ensures that the second end 75 can not come into contact with the wall 80 or the wall 93.
  • the wall 93 is formed in the exemplary embodiment on a fixing pin 60.
  • the second end 75 has no function during operation. Due to the symmetrical design of the friction belt 17, an incorrect installation of the friction belt 17 is not possible.
  • FIGS. 16 to 19 show a further embodiment of an actuator 19 and a clamping device 13.
  • the same reference numerals designate corresponding elements as in the preceding figures, reference being made to the description of the preceding figures.
  • the actuator 19 off Fig. 16 has a bracket 26, which has an outwardly projecting fixing pin 90.
  • a tooth contour 97 is formed on the receptacle 20, which is designed to be closed to the interior of the sprocket 11.
  • the tensioning device 13 has a spring element 94, which comprises a tension spring 95 and an integrally formed on the tension spring 95 friction belt 96.
  • the friction belt 96 engages around the tension spring 95 in the opposite direction to the winding direction of the tension spring 95.
  • an outer end 103 of the tension spring 95 connects.
  • An inner end 102 of the tension spring 95 is designed for attachment to a driver 105.
  • the driver 105 has for this purpose a receptacle 54.
  • the driver 105 is annular and has on its inner circumference a total of four driving lugs 106. Each driving lug 106 has a slope 107 which extends over the entire end face of the driving lug 106.
  • the tensioning device 13 comprises a rotary element 99, to which a driver 108 is integrally formed.
  • the driver 108 may also be formed as a separate component and fixed rotatably on the rotary member 99.
  • the driver 108 has on its outer circumference a total of four driving lugs 109, which have bevels 110 on their end facing the driver 105 side.
  • the bevels 107 and 110 form guide slopes and facilitate the mating of the drivers 105 and 108th
  • the rotary element 99 has a spiral guide 111 which extends over more than two revolutions about the axis of rotation 92 (FIG. Fig. 17 ).
  • the spiral guide 111 acts self-locking.
  • a force acting on the guide rail 8 and on the displacement element 30 can not rotate the rotary element 99.
  • the operator must manually move the rotating member 99.
  • the tension spring 95 is arranged in a spring housing 100.
  • a cover 98 is arranged, which covers the spring housing 100 to the interior of the sprocket 11 towards.
  • the cover 98 is advantageously fixed to the sprocket 11, for example screwed or clipped.
  • the spring housing 100 is designed to be substantially closed to the interior 34 in the exemplary embodiment.
  • the driver 105 is disposed between the bottom of the spring housing 100 and the cover 98.
  • the driver 108 engages in the driver 105, whereby the driving lugs 106 and 109 come into engagement with each other.
  • the friction belt 96 surrounds the edge 83 of the body 39 and is adjacent to a friction surface 18 of the receptacle 20 is arranged.
  • the friction belt 96 forms the inhibiting device 16 with the friction surface 18.
  • Fig. 18 shows the structure of the spring element 94 in detail.
  • the tension spring 95 has a sufficient number of turns, which may correspond, for example, the number of turns in the first embodiment. For a better overview, only three of the turns of the tension spring 95 are shown in the figures.
  • the first end 74 of the friction belt 96 connects.
  • the spring housing 100 is arranged coaxially with the axis of rotation 92.
  • the spring housing 100 has a passage opening 101 through which the first end 74 of the friction belt 96 protrudes. Adjacent to the first end 74 of the friction belt 96 is on the base body 39 of the actuator 19 a stop surface 78 is formed. If the actuator 19 is moved in the fastening direction 76, so the stop surface 78 takes the friction belt 96 at the first end 74 and thereby reduces the friction between the friction belt 96 and friction surface 18. At the same time, the outer end 103 of the tension spring 95 is taken over the first end 74 and thereby tensioned the tension spring 95. When you release the actuator 19, the tension spring 95 tries to relax.
  • FIGS. 20 to 27 show a further embodiment of a clamping device 13, wherein the same reference numerals as in the preceding figures denote the same elements.
  • a driver 118 is held.
  • the driver 118 has, as Fig. 21 shows three driving lugs 120.
  • the driving lugs 120 protrude through openings 117 in the main body 39 of the actuator 19 and are thereby in the circumferential direction, ie in the fastening direction 76 and in the release direction 77, positively connected to the body 39.
  • the driver 118 may also be encapsulated by the base body 39 of the actuator 19 and thereby held on the actuator 19.
  • On bracket 26 a total of three fixing pins 60 are formed, which engage in the folded contour of the bracket 26 in the tooth contour 27 on the sprocket 11 and thereby secure the actuator 19 positively against rotation relative to the sprocket 11.
  • the tensioning device 13 comprises, as Fig. 20 shows a spring housing 119, on which a spiral guide 111 is formed.
  • the spiral guide 111 corresponds to the in Fig. 16 shown spiral guide 111 and is self-locking.
  • the tensioning device 13 comprises a spring element 124 arranged in the spring housing 119.
  • the spring housing 119 for the spring element 124 forms the rotary element of the tensioning device 13 Fig. 21 also shows, is adjacent to the spiral guide 111 formed on the spring housing 119 has a securing contour 47, which is designed as a fine toothing and with the in Fig. 23 shown fuse contour 48 on the displacement element 30 cooperates.
  • the tensioning device 13 comprises a driver 121, which has driving lugs 122. Overall, three driving approaches 122 are provided. The distance between the driving lugs 122 is selected so that the driving lugs 120 of the driver 118 can intervene between the driving lugs 122.
  • the tensioning device 13 also includes a sleeve 123 having an opening 127. At the opening 127 two flats 128 are formed, which are arranged opposite to each other.
  • Fig. 22 shows the arrangement of the spring element 124 in the spring housing 119th Wie Fig. 22 shows, the spring housing 119 has an edge 136 which surrounds the spring element 124.
  • a rivet sleeve 129 is provided for connecting spring housing 119 and displacement element 30.
  • the rivet sleeve 129 has opposing flats 132, which come into abutment in the mounted state on the flats 128 of the sleeve 123 and the sleeve 123 rotatably connect with the rivet sleeve 129.
  • the flats 132 are also dimensioned so that they secure the rivet sleeve 129 rotationally fixed in the displacement element 30. As a result, a rotationally fixed connection of the sleeve 132 with the displacement element 30 is achieved.
  • the sleeve 123 protrudes through an opening 130 in the spring housing 119 and through a plate spring 131, which is advantageously arranged on the side facing away from the displacement element 30 of the sleeve 123.
  • the spring element 124 comprises a tension spring 125 and a friction belt 126.
  • the friction belt 126 is integrally formed on the inner end 134 of the tension spring 125.
  • the friction belt 126 engages around the sleeve 123.
  • On the outer circumference of the sleeve 123 a friction surface 137 is formed, with which the friction belt 126 cooperates.
  • the inner end 134 of the tension spring 125 rotatably connected to the displacement element 30 can be connected.
  • the driver 121 engages over the sleeve 123 and the friction belt 126th
  • the main body 39 of the actuator 19 has an edge 140.
  • the edge 136 of the spring housing 119 is adjacent to the edge 140, but has to this a distance.
  • the main body 39 and the spring housing 119 define an interior space 34 in which the spring element 124 is arranged. Over the gap formed between the edges 136 and 140 and over the gap formed between the edge 136 and the sprocket 11, the interior 34 is open to the interior of the sprocket 11.
  • Fig. 26 shows a section through the spring housing 119.
  • the tension spring 125 has an outer end 133 which is mounted on a receptacle 135 of the spring housing 116.
  • the receptacle 135 is formed by two slots in the edge 136 of the spring housing 119.
  • the friction belt 126 has a first end 138, which is integrally formed on the inner end 134 of the tension spring 125, and a second end 139.
  • the two ends 138 and 139 are arranged on both sides of a driving lug 120 of the driver 118.
  • a driving projection 120 acts against the first end 138 of the friction belt 126 and widens the friction belt 126 thereby, so that the friction between the friction belt 126 and the friction surface 137 of the sleeve 123 (FIGS. Fig. 24 ) is reduced.
  • About the first end 138 of the friction band 126 of the driving lug 120 acts on an adjacent driving lug 122 of the driver 121.
  • the tension spring 125 pulls the first end 138 of the friction belt 126 in the direction of the entrainment approach 120 and thereby pulls the friction belt 126 tightly around the sleeve 123. Because of the rotationally fixed connection of the sleeve 123 with the rivet sleeve 129 and the displacement element 30 prevents the tension spring 125 can relax.
  • the friction belt 126 forms an inhibiting device 16 with the friction surface 137.
  • the driving lug 120 moves against the second end 139 of the friction belt 126, such as Fig. 27 shows.
  • the brake band 126 is lifted slightly off the sleeve 123, and the friction on the friction surface 137 (FIG. Fig. 24 ) is reduced.
  • the operating force in the release direction 77 is only small.

Landscapes

  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Wood Science & Technology (AREA)
  • Forests & Forestry (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Sawing (AREA)
  • Portable Power Tools In General (AREA)
EP14000735.2A 2013-03-06 2014-03-01 Appareil de travail manuel doté d'un dispositif de serrage pour une chaîne Withdrawn EP2774733A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013003850.2A DE102013003850A1 (de) 2013-03-06 2013-03-06 Handgeführtes Arbeitsgerät mit einer Spannvorrichtung für eine Kette

Publications (1)

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EP2774733A1 true EP2774733A1 (fr) 2014-09-10

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EP14000735.2A Withdrawn EP2774733A1 (fr) 2013-03-06 2014-03-01 Appareil de travail manuel doté d'un dispositif de serrage pour une chaîne

Country Status (7)

Country Link
US (1) US9713881B2 (fr)
EP (1) EP2774733A1 (fr)
JP (1) JP2014172397A (fr)
CN (1) CN104308261B (fr)
BR (1) BR102014003710A2 (fr)
DE (1) DE102013003850A1 (fr)
RU (1) RU2014107353A (fr)

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EP3385045A1 (fr) * 2017-04-04 2018-10-10 Andreas Stihl AG & Co. KG Tronçonneuse à chaîne

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WO2014142722A1 (fr) * 2013-03-15 2014-09-18 Husqvarna Ab Scie à chaîne comprenant ensemble de molette auto-verrouillant
JP6132626B2 (ja) * 2013-03-29 2017-05-24 株式会社マキタ 携帯作業機
JP6026943B2 (ja) * 2013-03-29 2016-11-16 株式会社マキタ チェンソーのガイドバー締結装置
JP6360658B2 (ja) * 2013-03-29 2018-07-18 株式会社マキタ チェンソーのチェーン張力調整装置
DE102014007878A1 (de) 2014-05-24 2015-11-26 Andreas Stihl Ag & Co. Kg Handgeführtes Arbeitsgerät
US11685034B2 (en) 2014-05-24 2023-06-27 Andreas Stihl Ag & Co. Kg Handheld work apparatus
WO2018141105A1 (fr) * 2017-02-06 2018-08-09 南京德朔实业有限公司 Scie à chaîne

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US20140250702A1 (en) * 2013-03-06 2014-09-11 Andreas Stihl Ag & Co. Kg Handheld work apparatus having a tensioning device for a chain
US9713881B2 (en) * 2013-03-06 2017-07-25 Andreas Stihl Ag & Co. Kg Handheld work apparatus having a tensioning device for a chain
EP3385045A1 (fr) * 2017-04-04 2018-10-10 Andreas Stihl AG & Co. KG Tronçonneuse à chaîne
US10814518B2 (en) 2017-04-04 2020-10-27 Andreas Stihl Ag & Co. Kg Chainsaw

Also Published As

Publication number Publication date
DE102013003850A1 (de) 2014-09-25
US9713881B2 (en) 2017-07-25
JP2014172397A (ja) 2014-09-22
CN104308261B (zh) 2018-01-02
BR102014003710A2 (pt) 2014-12-30
US20140250702A1 (en) 2014-09-11
RU2014107353A (ru) 2015-09-10
CN104308261A (zh) 2015-01-28

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