EP2316620B1 - Outil manuel - Google Patents

Outil manuel Download PDF

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Publication number
EP2316620B1
EP2316620B1 EP20100189104 EP10189104A EP2316620B1 EP 2316620 B1 EP2316620 B1 EP 2316620B1 EP 20100189104 EP20100189104 EP 20100189104 EP 10189104 A EP10189104 A EP 10189104A EP 2316620 B1 EP2316620 B1 EP 2316620B1
Authority
EP
European Patent Office
Prior art keywords
wheel
planetary
gear
planet
housing
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.)
Not-in-force
Application number
EP20100189104
Other languages
German (de)
English (en)
Other versions
EP2316620A3 (fr
EP2316620A2 (fr
Inventor
Norbert Woecht
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.)
C&E Fein GmbH and Co
Original Assignee
C&E Fein GmbH and Co
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 C&E Fein GmbH and Co filed Critical C&E Fein GmbH and Co
Publication of EP2316620A2 publication Critical patent/EP2316620A2/fr
Publication of EP2316620A3 publication Critical patent/EP2316620A3/fr
Application granted granted Critical
Publication of EP2316620B1 publication Critical patent/EP2316620B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools

Definitions

  • the invention relates to a hand tool according to the preamble of claim 1 with a housing, with a recorded in the housing drive motor with a rotatably driven motor shaft which is coupled to a drive shaft for a tool to the drive, wherein the motor shaft and the drive shaft with a transmission Planet stages is interposed.
  • Such a hand tool is from the DE 202 20 001 U1 known.
  • Another hand tool is from the EP 1 886 769 A1 known.
  • Each of the two ring gears can take two different switching positions, so that in the known hand tool a total of four gears can be realized.
  • first ring gear with either a first or a second set planetary gears of a double planetary stage in engagement and a second ring gear between a position in which a further planetary stage is activated, and a position in which bridges this further planetary stage is to move.
  • the hand tool consequently four different speed or torque levels can be selected via the manual transmission.
  • the hand tool may be to some extent suitable for various applications.
  • a gearbox for tools which has a housing in which a first planetary gear group, a second planetary gear group and a third planetary gear group are arranged.
  • the gearbox is designed as a 3-speed gearbox.
  • the invention has for its object to provide a hand tool that in terms of its speed and torque design a variety of applications can be adapted, the input side particularly powerful electric motors should be used.
  • a hand tool with a housing, with a drive motor received in the housing with a rotatably drivable motor shaft, which can be coupled to a drive shaft for a tool to drive it, wherein the motor shaft and the drive shaft, a transmission is interposed, with a planetary gear shift stage which is designed as a double planetary stage, with a first sun gear which can be driven by the motor shaft, with at least one first planet gear, at least one second planet gear axially offset therefrom and with a first ring gear and a second ring gear, the at least one the first planetary gear and the at least one second planet gear are also engaged with the first sun gear, the at least one first planetary gear with the first ring gear and at least one second planetary gear with the second ring gear are engaged, wherein the second ring gear at the same time as the first R planet carrier is formed, on which the at least first planetary gear is received, wherein a recorded on the housing switching element is selectively coupled to the first ring gear or
  • the object of the invention is achieved in this way.
  • a switching position allows, in which the at least one second planetary gear, which is received on the second planet carrier and drives this, both by the first sun gear and by the second ring gear is driven, whereby the resulting in this switching position translation can be adapted particularly simple and in new achievable areas to prevailing conditions of use.
  • the second ring gear and the first sun gear act in the same direction on the at least one revolving second planetary gear, which now causes the respective relative movements to the second planetary gear act on this opposite, so that the second planetary gear only one drive according to the difference learn about these movements.
  • the resulting in this switching position at this planetary gear ratio can be adjusted to effect a total translation of the transmission of the hand tool, which can cover the usual applications in terms of spread and gradation.
  • both stages of the double planetary stage can each have identical diameters and modules, ie identical parts or at least identical gear tools can be used, whereby the production can be significantly simplified.
  • the transmission ratio and ratio can be better adapted to the prevailing conditions of use.
  • the transmission further comprises a planetary stage, with a third sun gear, which is driven by the motor shaft, a fourth ring gear, which is fixed to the housing, and with at least one fourth planetary gear, with the third sun gear and the fourth ring gear is engaged.
  • the entire ratio of the transmission can be more easily adapted to a predetermined by various applications target area.
  • the switching element is designed as a slide switch, which can engage positively or non-positively in a peripheral region in the first ring gear or the second ring gear.
  • the slide switch can in this case be received in the longitudinal direction in the housing and be axially displaceable substantially parallel to the motor shaft.
  • the slide switch can positively engage in the first ring gear or the second ring gear, then this can be actuated both during operation and at standstill of the hand tool.
  • a particularly high force can be transmitted in a form-locking interaction of the first or the second ring gear with the slide switch by the positive connection, slip or friction can be avoided, whereby the susceptibility to wear decreases.
  • a positive contact can also be effected with very low actuation forces.
  • the first ring gear and the second ring gear on an outer contour, in particular an outer toothing, which is positively coupled to the slide switch.
  • the positive locking contour can be particularly easily introduced on the outer circumference of the first and second ring gear. It is conceivable to carry out the outer contour as a toothing, that is to use for the production of the transmission on already used processes and facilities in order to streamline the production can.
  • the slide switch can be coupled in a blocking position both with the first ring gear and with the second ring gear.
  • the gear can be blocked, for example, to change tools when the slide switch is fixed relative to the housing in the direction of rotation.
  • a further translation stage can be realized, namely, when the slide switch connects the first ring gear and the second ring gear against rotation, but together with these against the housing is rotatable.
  • the planetary gear shift can be blocked in itself, a rotation of the first sun can therefore be transmitted directly to the second sun gear planetary lock.
  • the third ring gear is formed as an axially displaceable locking slide on the planetary locking stage, which is selectively fixed to the housing or rotationally coupled to the second planet carrier.
  • the ring gear itself can be designed as a locking member, separate components can be saved, the manufacturing cost decreases.
  • the slide switch is coupled to a selector switch received on the housing, which is manually operable.
  • the selector switch can be coupled both with the slide switch and the locking slide to the actuation.
  • This measure makes it possible to switch all switching stages of the transmission only by pressing the selector switch.
  • the coupling of the selector switch with the slide switch or the locking slide with elastic means in particular springs.
  • a gear change can be significantly simplified, it can be taken, for example, with stationary hand tool a gear selector, even if the form-fitting geometries of the components are not in coverage, since now upon actuation of the selector switch, a spring can be biased, so that during the next operation of the hand tool, so when the form fit geometries come into coverage, the switching process can be implemented.
  • a hand tool according to the invention is shown and indicated generally at 10.
  • Such hand tools in particular electric motor operated hand tools, find use in many activities, such as drilling, screwing, grinding, polishing, impact drilling or sawing.
  • For power supply such hand tools with lines for connection to a pipeline network or with mobile energy storage, in particular accumulators, be provided.
  • the gradation represents a major obstacle to the design of conventional gear ratios. If you want to achieve the above speed values, so the gear when shifting from gear to gear change the speed by a factor of about 2. It is understood that the gradation may vary within certain limits thereof, a finite number of teeth and the avoidance of integer tooth ratios leads to values from 1.75 to 2.25 for the translation from gear to gear can be quite accepted.
  • the hand tool 10 has a housing 12 with a gear head 14 and a tool spindle 16, which serves to receive a tool 18 on.
  • the hand tool 10 is held and guided on a grip area 20.
  • a selector switch 24 is received, which can be moved by an operator to switch different gears, thus selecting different output speeds, as indicated by the arrow 26.
  • Fig. 2 shows the structure of a transmission 30 according to the invention, which is a drive motor 32 with a motor shaft 34 and a drive shaft 36 interposed.
  • the planetary locking stage 70 is provided on the output side and the planetary stage 90 on the drive side, the planetary gear shift stage 38 is interposed therebetween.
  • the arrangement of the stages can also be done differently, such as when boundary conditions in the design of the transmission line in another weighting should be taken into account. For example, at the output of the drive shaft 36 are generally low speeds, but high torque at the drive in the Motor shaft 34 act high speeds, associated with low torque. These conditions affect gear parameters, such as the number of teeth, modulus and tooth width, so the appropriate ranking of stages may affect overall design goals such as weight, space and life.
  • the planetary switching stage 38 is designed as a double planetary stage.
  • a first sun gear 40 serves to drive, by means of a first toothed portion 42 and a second toothed portion 44, the first sun gear 40 with first planetary gears 46 and second planetary gears 50 is engaged.
  • the first planetary gears 46 are coupled to a first internally toothed ring gear 48 and the second planetary gears 50 to a second internally toothed ring gear 52.
  • the planetary gears 46, 50 may each preferably be a plurality of wheels, usually about 2, 3, 4, 5 or 6 wheels.
  • benefits such as force branching, improved smoothness, reduced bearing forces and minimizing wear can be brought to bear. It is understood that the desired gear ratios can also be achieved with only one planetary gear.
  • the first planetary gears 46 are mounted on a first planetary carrier 54 on first axes 56 and the second planetary gears 50 on a second planetary carrier 58 on second axes 60.
  • the bearings can (not shown) as plain bearings, as well as rolling bearings, be formed.
  • the first planetary gears 46 cooperate with the second planetary gears 50 via the first axles 56 and the first planet carrier 54, which is also designed as a second ring gear 52.
  • a switching element 62 as in Fig. 2 shown as axially displaceable slide switch, in a position in which the second ring gear 52 is fixed to the housing 12, so causes a rotation of the first sun gear 40, a rotation of the second planet gears 50, which along roll off the fixed second ring gear 52.
  • the second planetary carrier 58 is driven via the second axes 60.
  • the second planet carrier 58 also serves as the output of the planetary gear shift stage 38, when the switching member 62 is moved in the direction of the arrow 67 in a different position in which the first ring gear 48 is fixed to the housing 12 (in Fig. 2 indicated by a dashed line, cf. this too Fig. 3 ).
  • the drive of the second planet gears 50 takes place via the first sun gear 40 both directly, via the second gear section 44, and indirectly, via the first gear section 42, the first planet gears 46, the first axes 56, the first planet carrier 54 and the second ring gear 52nd
  • contours are formed on these and on the switching element 62, namely a form-fitting contour 64a, 64b on the switching element 62, an outer contour 65a on the first ring gear 48 and an outer contour 65b on the second ring gear
  • these contours are indicated as teeth, but it can also be, for example, to splines and splines or other shaft-hub connections that allow axial displacement of the elements against each other.
  • the spring 68 may be formed as a leaf spring or wire bending spring.
  • the switching element 62 namely only indirectly via the spring 68, is acted upon.
  • the transmission 30 in a state in which the switching member 62 can not be brought directly into contact with the outer contour 65a of the first ring gear 48 and the housing contour 66a, so caused by the switching movement bias of the spring 68 can not be reduced immediately.
  • This bias acts on the switching member 62 and can now cause an automatic displacement of the switching element 62 in the new position, such as when the next activation of the drive motor 32, the components of the transmission 30 are in motion, so that there is an orientation in the the switching member 62 can be moved to the new position.
  • the planetary locking stage 70 On the output side of the transmission 30, the planetary locking stage 70 is arranged. It is a planetary stage with a second sun gear 72, which in the present case coincides with the second planet carrier 58, that is, by the planetary gear 38 is operable.
  • the second sun gear 72 is in permanent engagement with third planetary gears 74, which is a third internally toothed ring gear 76 associated.
  • the third planet gears 74 are mounted on a third planet carrier 78 via third axes 80.
  • the planetary locking stage 70 can be selectively used in a translation operation by the third ring gear 76 engages a form-fitting contour 82 in a housing contour 83 of the housing 12 and thus fixed to this. Now, the third planet gears 74 roll relative to the third ring gear 76 when driven by the second sun gear 72. The result is an output movement of the third planet carrier 78, which is in the same direction as the initiated rotational movement through the second sun gear 72.
  • the planetary locking stage 70 can also be bridged or blocked when the third ring gear 76 is displaced in the direction of the second planet carrier 58, (in Fig. 2 indicated by a dashed line, cf. this too Fig. 4 ). This may be effected by suitable means, preferably by the selector switch 24, but such coupled operation is in Fig. 2 not considered.
  • the second planet carrier 58 has in its peripheral region a toothing 84 which corresponds to the internal toothing of the third ring gear 76.
  • the third ring gear 72 itself is axially displaced to effect the blockage. It is also conceivable to use this purpose a separate locking slide, approximately analogous to the switching slide formed as a switching member 62 in the planetary gear 38th
  • the transmission 30 is preceded by a further planetary stage 90.
  • a third sun gear 92 which is coupled to the motor shaft 34 drives fourth planet gears 94, which roll against a fourth internally toothed ring gear 96 and drive in the course of this rolling movement a fourth planetary carrier 98, where they fourth Axles 100 are included.
  • the fourth planet carrier 98 coincides with the first sun gear 40 of the planetary gear shift stage 38.
  • FIGS. 3 and 4 represent so-called transmission plans of a transmission 30 according to the invention, wherein a much simplified, symbolic representation is used.
  • the transmission 30 essentially has the aforementioned configuration, namely the planetary gear shift stage 38, the planetary gear lock stage 70 and the planetary stage 90.
  • the transmission 30 is arranged between the drive motor 32 and the drive shaft 36, with an example between the drive motor 32 and the input-side planetary stage 90 a clutch 102 is provided, while between the output-side planetary locking stage 70 and the drive shaft 36, a brake 104 is indicated.
  • the second ring gear 52 of the planetary gear shift stage 38 is fixed by the switching member 62 on the housing 12, the third ring gear 76 is also on the housing 12 is received against rotation and only engaged with the third planetary gears 74, this position corresponds to the representation in Fig. 2 ,
  • the transmission 30 acts strongly reducing, so that there are 36 high output torques at low speeds on the drive shaft.
  • the planetary gear shift stage 38 acts as a simple planetary stage and the planetary blocking stage 70 is activated.
  • either the planetary gear shift stage 38 can be brought from a state in which it acts as a simple planetary stage, in a state where it is operated as a closed differential gear, or the planetary blocking stage 70 can be disabled, so that they are not translating , but only acts directly transmitting.
  • a possible fourth gear of the transmission 30 results from the constellation in Fig. 4 , If, in addition, the switching element 62 is now displaced into a position which corresponds to the numbering 62 'in FIG Fig. 3 corresponds to the transmission 30 only relatively small ratios of an input speed and thus at the drive shaft 36 high output speeds, associated with low output torques.
  • means may be provided to realize a spindle stop in the transmission 30.
  • Blocking the drive train facilitates the exchange of tools, in particular the release of a clamping drill.
  • a position can be provided for the slidable third ring gear 76, in which it is both in engagement with the teeth 84 of the second planet carrier 58 and with the housing contour 83, whereupon the second planet carrier 58 no longer rotate relative to the housing 12 could.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Claims (9)

  1. Outil manuel comprenant un boîtier (12), un moteur d'entraînement (32) reçu dans le boîtier (12) avec un arbre de moteur (34) pouvant être entraîné en rotation, lequel peut être accouplé à un arbre d'entraînement (36) pour un outil, en vue de son entraînement, une transmission (30) étant interposée entre l'arbre de moteur (34) et l'arbre d'entraînement (3b),
    avec un étage de commutation planétaire (38) qui est réalisé sous forme d'étage planétaire double, avec une première roue solaire (40) qui peut être entraînée par l'arbre de moteur (34), avec au moins un premier pignon planétaire (46), au moins un deuxième pignon planétaire (50) décalé axialement par rapport à celui-ci et une première couronne (48) ainsi qu'une deuxième couronne (52), l'au moins un premier pignon planétaire (46) et l'au moins un deuxième pignon planétaire (50) étant en prise simultanément avec la première roue solaire (40), l'au moins un premier pignon planétaire (46) étant en prise avec la première couronne (48) et l'au moins un deuxième pignon planétaire (50) étant simultanément en prise avec la deuxième couronne (52), la deuxième couronne (52) étant réalisée simultanément en tant que premier support planétaire (54), sur lequel est reçu l'au moins un premier pignon planétaire (46), un organe de commutation (62) reçu sur le boîtier (12) pouvant être accouplé de manière sélective à la première couronne (48) ou à la deuxième couronne (52) de l'étage de commutation planétaire (38), afin de fixer ou de libérer celui-ci, caractérisé par
    un étage de verrouillage planétaire (70) qui est réalisé sous forme d'étage planétaire avec une deuxième roue solaire (72), une troisième couronne (76) et au moins un troisième pignon planétaire (74) en prise les uns avec les autres, la deuxième roue solaire (72) étant connectée de manière solidaire en rotation à un deuxième support planétaire (58) sur lequel est reçu l'au moins un deuxième pignon planétaire (50) de l'étage de commutation planétaire (38), et la troisième couronne (76) pouvant être fixée de manière sélective au boîtier (12) ou au contraire pouvant être maintenue de manière rotative par rapport au boîtier (12) et pouvant être accouplée de manière fixée en rotation au deuxième support planétaire (58), et la première roue solaire (40) présentant une première portion de denture (42) avec un premier diamètre de cercle primitif et une deuxième portion de denture (44) avec un deuxième diamètre de cercle primitif qui est inférieur au premier diamètre de cercle primitif, l'au moins un premier pignon planétaire (46) étant en prise avec la première portion de denture (42) et l'au moins un deuxième pignon planétaire (50) étant en prise avec la deuxième portion de denture (44).
  2. Outil manuel (10) selon la revendication 1, caractérisé en ce que la transmission (30) présente en outre un étage planétaire (90) avec une troisième roue solaire (92) qui peut être entraînée par l'arbre de moteur (34), une quatrième couronne (96) qui est fixée au boîtier (12) ainsi qu'au moins un quatrième pignon planétaire (94) qui est en prise avec la troisième roue solaire (92) et la quatrième couronne (96).
  3. Outil manuel (10) selon la revendication 1 ou 2, caractérisé en ce que l'organe de commutation (62) est réalisé sous forme de coulisseau de commutation qui peut venir en prise au niveau d'une région périphérique par engagement par correspondance de forme ou par force dans la première couronne (48) ou la deuxième couronne (52).
  4. Outil manuel (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que la première couronne (48) et la deuxième couronne (52) présentent un contour extérieur (65), en particulier une denture extérieure, qui peut être accouplé(e) par engagement par correspondance de forme avec le coulisseau de commutation.
  5. Outil manuel (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que le coulisseau de commutation peut être accouplé dans une position de verrouillage à la fois avec la première couronne (48) et avec la deuxième couronne (52).
  6. Outil manuel (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que la troisième couronne (76) est réalisée au niveau de l'étage de verrouillage planétaire (70) en tant que coulisseau de blocage déplaçable axialement, qui peut être fixé de manière sélective au boîtier (12) ou qui peut être accouplé de manière fixée en rotation au deuxième support planétaire (58).
  7. Outil manuel (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que le coulisseau de commutation est accouplé à un commutateur de sélection (24) reçu sur le boîtier (12), lequel peut être actionné manuellement.
  8. Outil manuel (10) selon la revendication 7, caractérisé en ce que le commutateur de sélection (24) peut être accouplé à la fois au coulisseau de commutation et au coulisseau de blocage en vue de leur actionnement.
  9. Outil manuel (10) selon la revendication 7 ou 8, caractérisé en ce que l'accouplement du commutateur de sélection (24) au coulisseau de commutation ou au coulisseau de blocage s'effectue avec des moyens élastiques, en particulier des ressorts (68).
EP20100189104 2009-10-29 2010-10-27 Outil manuel Not-in-force EP2316620B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910051844 DE102009051844A1 (de) 2009-10-29 2009-10-29 Handwerkzeug

Publications (3)

Publication Number Publication Date
EP2316620A2 EP2316620A2 (fr) 2011-05-04
EP2316620A3 EP2316620A3 (fr) 2013-11-13
EP2316620B1 true EP2316620B1 (fr) 2014-12-03

Family

ID=43416818

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100189104 Not-in-force EP2316620B1 (fr) 2009-10-29 2010-10-27 Outil manuel

Country Status (2)

Country Link
EP (1) EP2316620B1 (fr)
DE (1) DE102009051844A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009060929A1 (de) 2009-12-23 2011-06-30 C. & E. Fein GmbH, 73529 Handwerkzeug
DE102012211914B4 (de) 2012-04-05 2023-06-15 Robert Bosch Gmbh Handwerkzeugmaschine mit einem Planetengetriebe
DE102017119807A1 (de) * 2017-08-29 2019-02-28 Festool Gmbh Hand-Werkzeugmaschine

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3525208A1 (de) * 1984-07-16 1986-01-23 Japan Strage Battery Co. Ltd., Kyoto Untersetzungsgetriebe
DE19754165A1 (de) * 1997-12-06 1999-06-10 Festo Tooltechnic Gmbh & Co Elektrisches Drehwerkzeug, insbesondere Akkuschrauber
DE10156392B4 (de) * 2001-11-16 2008-04-10 Robert Bosch Gmbh Gangschaltvorrichtung für ein mehrstufiges Getriebe eines Elektrowerkzeugs
DE10222824A1 (de) * 2002-05-21 2003-12-04 Hilti Ag Elektrowerkzeug mit mehrstufigem Getriebe
DE20209356U1 (de) * 2002-06-15 2002-10-02 Schelb, Bernhard, Dr.-Ing., 44809 Bochum Getriebe für Elektrowerkzeuge
US6655470B1 (en) * 2002-12-23 2003-12-02 Power Network Industry Co., Ltd. Speed changing mechanism for tools
DE102006025538A1 (de) * 2006-06-01 2007-12-06 Metabowerke Gmbh Elektrohandwerkzeuggerät
DE102006037191A1 (de) 2006-08-09 2008-02-14 Tts Tooltechnic Systems Ag & Co. Kg Werkzeugmaschine mit mehrstufigem Planetengetriebe
JP5030601B2 (ja) * 2007-01-22 2012-09-19 株式会社マキタ 電動工具

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Publication number Publication date
EP2316620A3 (fr) 2013-11-13
DE102009051844A1 (de) 2011-05-05
EP2316620A2 (fr) 2011-05-04

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