EP0582696A1 - Outil a moteur commande a la main - Google Patents

Outil a moteur commande a la main

Info

Publication number
EP0582696A1
EP0582696A1 EP19930904011 EP93904011A EP0582696A1 EP 0582696 A1 EP0582696 A1 EP 0582696A1 EP 19930904011 EP19930904011 EP 19930904011 EP 93904011 A EP93904011 A EP 93904011A EP 0582696 A1 EP0582696 A1 EP 0582696A1
Authority
EP
European Patent Office
Prior art keywords
machine tool
tool according
cage
clamping
clamping bodies
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Withdrawn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
EP19930904011
Other languages
German (de)
English (en)
Inventor
Alfred SCHÄR
Mihail Stefanopulos
Benedikt Barbisch
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.)
Scintilla AG
Original Assignee
Scintilla AG
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 Scintilla AG filed Critical Scintilla AG
Publication of EP0582696A1 publication Critical patent/EP0582696A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/069—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags
    • F16D41/07—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags between two cylindrical surfaces
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01G—HORTICULTURE; CULTIVATION OF VEGETABLES, FLOWERS, RICE, FRUIT, VINES, HOPS OR SEAWEED; FORESTRY; WATERING
    • A01G3/00—Cutting implements specially adapted for horticultural purposes; Delimbing standing trees
    • A01G3/04—Apparatus for trimming hedges, e.g. hedge shears
    • A01G3/047—Apparatus for trimming hedges, e.g. hedge shears portable
    • A01G3/053—Apparatus for trimming hedges, e.g. hedge shears portable motor-driven

Definitions

  • the invention relates to a hand-held, power-driven machine tool according to the preamble of claim 1.
  • DE-OS 40 05 133 discloses a generic hedge trimmer in which a switchable freewheel clutch in combination with a wrap spring causes entrainment or standstill of the hedge trimmer blade between the drive and the tool.
  • the actual task of the known solution, to prevent the hedge trimmer blades from running after switching off with as little delay as possible, is only achieved with a certain inertia under certain conditions. A complete decoupling of the drive area from the output area is not possible quickly enough.
  • the machine tool according to the invention with the characteristic features Painting claim 1 has the advantage that the connection between the drive train and the output is released when the machine tool is switched off with an unprecedentedly short reaction time.
  • the one-way clutch consists of only a small number of very light individual parts which can be produced at low cost and can be assembled in a short amount of time.
  • the machine tool according to the invention has a lower overall volume and weight and is therefore more manageable than the known machine tools.
  • the wrap spring in the known solution is more expensive to manufacture than the cage switching sleeve used in the invention.
  • the clamping bodies designed according to the invention as clamping levers are smaller in volume than clamping rollers and moreover have a larger friction surface than rollers, which is why more clamping levers than rolling bodies can be accommodated on the circumference of the surfaces to be coupled. Because of the smaller volume, smaller mass forces are required to move the clamping bodies than to move the rollers. This leads to reduced reaction time as well as the fact that the clamping bodies only have to be tilted in order to be brought into the coupling or uncoupling position, while the rollers have to be rolled over a relatively long way in order to get out of the clamping position.
  • the clamping bodies according to the invention run between two smooth cylinder walls, while in the known solution the rollers in the outer cylinder make curved path-like recesses necessary, the manufacture of which requires great effort.
  • FIG. 1 shows the side view of a hedge trimmer
  • FIG. 2 shows the sectional view of a section of the hedge trimmer according to the invention
  • FIG. 3 shows the enlargement of a detail from FIG. 2 with the area of the drive and output
  • FIG. 4 shows the view of a switching sleeve according to the invention
  • the figures 5 and 6 show a schematic illustration of the one-way clutch when coupling and when uncoupling.
  • FIG. 1 shows the structure of a hedge trimmer 1, which consists of a housing 3 with a first handle 5 and a second handle 7.
  • the housing 3 accommodates a motor, not shown, with an output shaft and power transmission system, which are coupled to hedge trimmer blades 31, 33.
  • the hedge trimmer 1 according to the invention shown in section in FIG. 2 shows the housing 3 with the first and the second handle 5, 7, which receives a motor 11 with an output shaft 13. At the free end of the output shaft 13 there is a pinion 15 which meshes with a ring gear 17 which is rotatably mounted about an axis 19.
  • the ring gear 17 is non-positively connected to a drive sleeve 23 via a slip clutch 21 and rotatably mounted on a crankshaft 25 concentrically with the axis 19.
  • a first and a second eccentric disk 27, 29 are arranged on the crankshaft 25 in a rotationally fixed manner, which are coupled in the manner of a crank pin to a hedge trimmer knife 31, 33 and convert the rotating movement into an oscillating movement.
  • a one-way clutch Arranged between the drive sleeve 23 and the crankshaft 25 is a one-way clutch which consists of clamping bodies 37 which are captively arranged in a cage sleeve 35 and which are held in the cage sleeve 35 by means of a band-like elastic means 39. Except the clamping body 37 engages radially with its outer end a switching sleeve 41 arranged in a cage.
  • the switching sleeve 41 is connected on its front side on the machine side to a disk 43 with radial cams 45.
  • a shifting pin 47 which is displaceable parallel to the axis 19, can engage in the cams 45.
  • the switching bolt 47 is arranged on a leaf spring-like bolt carrier 49, which is shifted into the blocking position shown in FIG. In the blocking position, the switching pin 47 engages in the cams 45 and thus holds the disk 43 with the switching sleeve 41 in place.
  • the enlarged section according to FIG. 3 in the area of the freewheel clutch of the hedge trimmer 1 shows, in accordance with FIG. 33.
  • the one-way clutch shows the clamping bodies 37, which are captively arranged in the cage sleeve 35 and are held in the cage sleeve 35 via the band-like elastic means 39.
  • the clamping bodies 37 penetrate radially through the cage-like switching sleeve 41.
  • the switching sleeve 41 is connected to the disk 43 on one end face.
  • the switching pin 47 can engage in their cams 45.
  • the slip clutch 21 from FIG. 2 is not shown.
  • a friction-reducing needle bearing 51 is arranged between the ring gear 17 and the crankshaft 25.
  • the switching pin 47 is disengaged from the cams 45 of the disc 43.
  • the switching sleeve 41 rotates, so that the clamping bodies 37 assume a position in which they are due to the tensioning force of the band-like means 39 support in an inclined position between the crankshaft 25 and the drive sleeve 23.
  • the ring gear 17 which is integral with the drive sleeve 23 seeks to straighten the clamping bodies 37 out of their shifting position. This results in high support forces between the clamping bodies 37 and the parts to be coupled during canting, so that rotational entrainment between these parts is ensured.
  • the principle of the sprag freewheel is that the sprags 37 straighten up when coupling, as happens with the individual hairs of a fur when brushing against the grain.
  • the switching pin 47 moves into the engagement position with the disk 43, so that the latter is braked suddenly.
  • the switching sleeve 41 is held together with the disk 43. The latter tries to reinforce the inclined position of the clamping bodies 37, which is supported by a torque difference between the crankshaft 25 and the ring gear 17.
  • the frictional connection between the ring gear 17 and the crankshaft 25 is separated.
  • the output shaft 13 and the toothed ring 17 can rotate freely with respect to the drive train consisting of the crankshaft 25 and the pair of knives 31, 33, the drive train coming to a standstill quickly due to the friction between the reciprocating hedge trimmer knives 31, 33.
  • FIG. 4 shows the individual switching sleeve 41, which carries the clamping bodies 37 here alone, without a separate cage sleeve, these of a thin spiral spring, the elastic holding means 39, is gripped radially and held in the switching sleeve 41.
  • the Klemmkorper 37 are provided with a central, open longitudinal groove, which center the engaging band-like elastic means 39.
  • the clamping bodies 37 enter the switching sleeve 41 through slots 42, through which they cannot fall due to their wide head area.
  • the disc 43 can be seen particularly clearly with one of the propeller-wing-like switching cams 45.
  • FIGS. 5 and 6 show once the end position uncoupling and once the end position take away.
  • a separate clamp body cage was also dispensed with in this exemplary embodiment. Its function is also perceived by the switching sleeve 41 and leads to a simplified, functionally reliable and lighter construction.
  • the clamping bodies 37 each assume an oblique position with respect to a radial line 44 drawn through dash-dot lines through the crankshaft axis. This oblique position is brought about by the switching sleeve 41 being brought to a standstill from the outside.
  • the switching sleeve 41 By holding the switching sleeve 41 under the assumption that the crankshaft 25 and the ring gear 17 move counterclockwise, the clamping bodies 37 tilt out of their cant In the position shown below in FIG. 6 and in this stop position on the switching sleeve 41, it is no longer possible to return to its tilted position coupling between the crankshaft 25 and the ring gear 17.
  • FIG. 6 shows how the clamping bodies 37 tilt between the crankshaft 25 and the ring gear 1.7.
  • the position of the clamping bodies 37 which is essentially parallel with respect to the radial lines 44, is evident from this. In this upright position, the coupling between the input and output, i.e. switched between ring gear 17 and crankshaft 25.
  • the cage sleeve for the clamping bodies is produced from a sheet metal strip which has three transverse slots with the same spacing over its length for receiving the clamping bodies and which is pressed to form a sleeve via a flanged connection.
  • the clamping bodies here have a circumferential slot / recess into which a thin tension spring wrapping around the cage can fully enter and is supported on the clamping bodies in such a way that they are captively held in a stable position in the cage sleeve.
  • the stable position is more of an inclined position than an upright position parallel with respect to an imaginary radial.
  • the switching sleeve is also connected via a flange connection to a thick-walled sheet-metal disk which carries three cams pointing radially outward in the manner of a propeller wing.
  • the clamping bodies are designed as rotary wedges which can couple together rotating parts which are axially contested.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Biodiversity & Conservation Biology (AREA)
  • Ecology (AREA)
  • Forests & Forestry (AREA)
  • Environmental Sciences (AREA)
  • Harvester Elements (AREA)
  • Scissors And Nippers (AREA)

Abstract

Outil commandé à la main, notamment entraîné électriquement, comme un taille-haies (1), une meuleuse d'angle et autre outil de ce type, dans lequel un embrayage à roue libre commutable agit entre l'entraînement et l'outil, avec des corps de serrage (37) pour entraîner l'outil et le mettre en roue libre. Pour ce type de dispositif, on obtient une séparation encore plus rapide de l'arbre d'entraînement et de l'arbre de sortie pour un arrêt à faible décélération des couteaux de taille-haies, lorsque seul un arrêt de blocage par friction (35, 37, 39, 41, 43), notamment des cliquets de roue libre, sert d'embrayage à roue libre.
EP19930904011 1992-02-29 1993-02-24 Outil a moteur commande a la main Withdrawn EP0582696A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19924206438 DE4206438A1 (de) 1992-02-29 1992-02-29 Handgefuehrte, kraftgetriebene werkzeugmaschine
DE4206438 1992-02-29

Publications (1)

Publication Number Publication Date
EP0582696A1 true EP0582696A1 (fr) 1994-02-16

Family

ID=6452966

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930904011 Withdrawn EP0582696A1 (fr) 1992-02-29 1993-02-24 Outil a moteur commande a la main

Country Status (4)

Country Link
EP (1) EP0582696A1 (fr)
JP (1) JPH06507317A (fr)
DE (1) DE4206438A1 (fr)
WO (1) WO1993016585A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4418102C2 (de) * 1994-05-24 1996-03-21 Mogatec Moderne Gartentechnik Motorisch angetriebene Heckenschere mit gegenläufigen Scherblättern
JP4251441B2 (ja) 2003-03-11 2009-04-08 株式会社ニッカリ 刈取機の安全装置
WO2012135942A1 (fr) 2011-04-04 2012-10-11 Litens Automotive Partnership Mécanisme d'embrayage et dispositif de découplage comprenant celui-ci
JP5995558B2 (ja) 2012-07-04 2016-09-21 株式会社マキタ 園芸用バリカン
US10655689B2 (en) 2013-11-14 2020-05-19 Litens Automotive Partnership Decoupler with overrunning and belt-start capability with simplified construction
WO2015103697A1 (fr) 2014-01-10 2015-07-16 Litens Automotive Partnership Découpleur à capacité de roue libre et de démarrage à courroie

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1814968A1 (de) * 1968-12-16 1970-07-02 Mueller Georg Kugellager Freilaufkupplung mit kippbaren Klemmkoerpern
DE3007110C2 (de) * 1980-02-26 1984-06-20 Metabowerke GmbH & Co, 7440 Nürtingen Heckenschere
US5052533A (en) * 1987-02-09 1991-10-01 Borg-Warner Corporation One-way clutch energizing spring
DE3729632A1 (de) * 1987-09-04 1989-03-16 Schaeffler Waelzlager Kg Freilaufkupplung mit klemmkoerpern
US4878570A (en) * 1988-01-25 1989-11-07 Dana Corporation Surface hardened sprags and rollers
DE4005133A1 (de) * 1990-02-17 1991-08-22 Licentia Gmbh Handgefuehrte elektrowerkzeugmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9316585A1 *

Also Published As

Publication number Publication date
DE4206438A1 (de) 1993-09-02
JPH06507317A (ja) 1994-08-25
WO1993016585A1 (fr) 1993-09-02

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