EP2655020A1 - Système de transmission pour un outil électrique et outil électrique - Google Patents

Système de transmission pour un outil électrique et outil électrique

Info

Publication number
EP2655020A1
EP2655020A1 EP11782440.9A EP11782440A EP2655020A1 EP 2655020 A1 EP2655020 A1 EP 2655020A1 EP 11782440 A EP11782440 A EP 11782440A EP 2655020 A1 EP2655020 A1 EP 2655020A1
Authority
EP
European Patent Office
Prior art keywords
coupling
wheel
gear arrangement
unit
gear
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Withdrawn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
EP11782440.9A
Other languages
German (de)
English (en)
Inventor
Andre Ullrich
Andreas Schlegel
Holger Ruebsaamen
Juergen Dietel
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2655020A1 publication Critical patent/EP2655020A1/fr
Withdrawn legal-status Critical Current

Links

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 gear arrangement for a power tool according to the preamble of claim 1.
  • engaging clutch is understood in particular to mean a clutch in which the links for producing a torque-transmitting connection are brought into engagement by preferably relative axial displacement.
  • the coupling unit formed as an engaging clutch and the angle gear are arranged at different positions, in particular in separate units of the gear assembly.
  • the term "separate structural units" particularly describes the circumstance that both the coupling members of the coupling unit and the pair of angular gears of the angular transmission are constructed from structurally separate elements .
  • the effect of a deflection of a rotational movement is thereby brought about in the angular gear by structurally different elements of the gear arrangement, as the control or control action by the coupling unit on the rotational movement.
  • a controllable deceleration, interruption or bringing about a transmission of the rotational movement is thereby referred to as a "control or control effect”.
  • the gear arrangement according to the invention with the features of the main claim has the advantage that the formation of a wheel of the pair of Winkelrad as a coupling member designed as engagement clutch coupling unit, the transmission assembly according to the invention with the same capacity occupies a smaller space than known transmission arrangements.
  • An “pair of angle wheels” is understood to mean, in particular, an arrangement of a pair of wheels, each having an axis of rotation, in which the two axes of rotation are aligned non-parallel to one another, in particular at an angle greater than 0 ° and less than or equal to 90 ° of the pair of angled gears, an angle between 10 ° and 90 °, in particular between 50 ° and 80 °.
  • a coupling element is understood to mean, in particular, a member or element by means of which the control or control action of the coupling unit can be realized or realized.
  • the wheel of the pair of Winkelrad is arranged on a driven side of the angular gear, whereby a favorable ratio between an input gear or pinion can be set as the input side of the angular gear and the output side.
  • a gear arrangement according to the invention with particularly high efficiency can be achieved if the wheel of the pair of Winkelrad is a gear and in particular is designed as a bevel gear or a crown wheel.
  • the wheel of the pair of Winkelrad is a gear and in particular is designed as a bevel gear or a crown wheel.
  • the wheel of the pair of Winkelrad is a gear and in particular is designed as a bevel gear or a crown wheel.
  • it thereby forming the wheel as a crown wheel, since the angular gear so along an axis of rotation of a second wheel of the pair of Winkelrad, in particular the input gear or pinion, insensitive to changes in position.
  • the wheel carries on a side surface coupling means for producing an operative connection with corresponding coupling means of a second coupling member of the coupling unit.
  • a “side surface” is understood to mean, in particular, a surface of the wheel which is not oriented parallel to an axis of rotation of the wheel, preferably at an angle of at least 45 °, particularly preferably substantially perpendicular to the axis of rotation
  • Invention understood in particular means which cause a releasable, non-positive and / or positive connection between appropriately equipped coupling members, cause or can cause.
  • releasable is in this case in particular in the sense of repeatedly solvable and / or related to a rotational speed of the rotary motion in the sense of quickly detachable, preferably in the range of fractions of a revolution solvable, and / or compared to a transmitted rotational power of the rotary motion low power, Preferably, less than 15%, particularly preferably less than 2%, of the rotational power is understood to mean suitable coupling means may be formed by geometrical structures such as recesses, protuberances, claw-like, cam-like or similar structures or friction surfaces on the coupling members alternatively or additionally, the coupling means by electromagnetic Means such as magnets and / or electromagnets or suitable means known in the art for producing a releasable, non-positive and / or positive connection In each case, the releasable, non-positive and / or positive connection can be brought about, caused or brought about in pairs.
  • the coupling unit is designed as a friction clutch, then a controllable transmission of the rotational movement between the input side and the output side of the transmission arrangement according to the invention can be achieved in a simple manner.
  • a braked transmission can also be achieved, wherein a braked transmission means, in particular, an output rotational power reduced with respect to an input rotational power becomes.
  • the coupling unit can be closed independently of a relative rotational position of their coupling elements.
  • the coupling means are designed as corresponding friction surfaces.
  • “Corresponding friction surfaces” are understood here to mean, in particular, opposing surfaces on the coupling links which exert a non-vanishing frictional force on each other when a surface contact is brought about in the region of the friction surfaces the torque applied to the input side at least partially to the output side.
  • the friction surfaces are designed as corresponding conical surfaces.
  • corresponding conical surfaces are understood to mean, in particular, two pairs of opposite conical or conical surfaces, wherein the first is an outer surface and the second an inner surface, and wherein the outer surface can engage in such a manner in the inner surface to produce a friction connection that the surfaces are in contact, preferably in a wedging contact or connection.
  • the coupling unit is designed as a jaw coupling, wherein at least the coupling means of one of the coupling members is formed by latching recesses, in which the engagement means designed as coupling means of the other coupling member can engage.
  • one of the coupling means is designed as a rolling body, in particular as an elastically prestressed rolling element, which can engage in the claws or locking cams of the second coupling member, so that a claw or locking cam clutch can be easily formed as a fürrastkupplung.
  • An overrunning clutch has the advantage of limiting the transmitted torque to a maximum value, as a result of which advantageous additional and / or protective functions can be implemented in a power tool.
  • a power tool in particular an electric hand tool such as a depth stop screwdriver, electric screwdriver, drills or hammer drill with an electric drive unit for generating a rotational movement is obtained when a transmission arrangement according to the invention is provided for transmitting the rotational movement to a use unit.
  • a transmission arrangement according to the invention is provided for transmitting the rotational movement to a use unit.
  • a drive axis of rotation of the drive unit and an output axis of rotation of the gear assembly are not aligned parallel to each other, whereby a center of gravity of the power tool designed low, especially in an electric hand tool can be advantageously placed in front of a handle.
  • At least one control or clutch actuating means is provided for setting a clutch state.
  • a "coupling state” is understood to mean, in particular, a connection state between the coupling links and / or an adjustable parameter for a coupling strength between the coupling links
  • various means such as spring systems with adjustable spring forces or lever systems to make, for example, a pressure force in friction clutches changeable known, which can be advantageously provided depending on the requirements in a gear arrangement according to the invention
  • the spring systems or lever systems form example of corresponding "control means”.
  • Such control or clutch actuation means are sufficiently known to the person skilled in the art, for example, from DE 10 2006 057 283 A1.
  • FIG. 1 shows a depth stop screwdriver as the first application example of a transmission arrangement according to the invention
  • Fig. 2 shows a first embodiment of a wheel as a coupling member
  • FIG. 3a and 3b a second embodiment of a wheel as a coupling member
  • FIG. 5a and 5b a third embodiment of a wheel as a coupling member description of the embodiments
  • FIG. 1 shows a schematic representation of a depth stop screwdriver as a first example of a power tool 10, in particular electric hand tool with a gear arrangement 100 according to the invention.
  • the gear arrangement 100 is arranged between a drive unit 14, which comprises an electric motor 16 with a motor shaft 18, and a use unit 20.
  • a drive unit 14 which comprises an electric motor 16 with a motor shaft 18, and a use unit 20.
  • the energy supply unit 26 may also be designed as a network supply unit, not shown here but well known to a person skilled in the art.
  • the actuator unit 22 and the control and / or regulating device 24, 25 are arranged in a handle segment 28 of the housing 12, 13.
  • the energy supply unit 26, 27 is preferably arranged in an end region 29 of the handle segment 28.
  • the drive unit 14 is arranged in the example of FIG. 1 in a drive segment 30 of the housing 12, 13, while the gear assembly 100 and an internal part 32 of the use unit 20 is received in a payload segment 34 of the housing 12, 13.
  • the motor shaft 18 is rotatably mounted about a motor axis of rotation 36, wherein in one of the gear assembly 100 facing end portion 38, a pinion 102 is provided.
  • the pinion 102 is preferably rotatably connected to the motor shaft 18, particularly preferably pressed onto this, welded or otherwise form, force and / or materially connected.
  • the pinion 102 may also be formed integrally with the motor shaft 18.
  • the pinion 102 is formed as a straight or helical spur gear 103 and provided to form a bevel gear 108 with a second wheel 104 as Winkelradcru 106.
  • the second wheel 104 is arranged about a rotation axis 110 on a shaft or work spindle 40, in particular freely rotatably arranged.
  • the second wheel 104 is decoupled, in particular rotationally coupled, via a bearing device 130 arranged in a central bore 105, for example a sliding bearing 131 or rolling bearing, with respect to the shaft or work spindle 40.
  • a transmission ratio IW of the angle gear 108 is between 1 and 10, preferably between 2 and 8, particularly preferably between 2.5 and 6.
  • the second wheel 104 is preferably formed as a crown wheel 112 and in this case has a straight or helical crown gear teeth 113.
  • the pinion 102 and the second wheel 104 may be embodied as a pair of bevel gears, as known to those skilled in the art.
  • the motor rotational axis 36 encloses an angle Wl of 90 ° with the axis of rotation 110 of the second wheel 104, 112.
  • the angle Wl is between 10 ° and 90 °, in particular between 50 ° and 80 °, as shown in a second embodiment of FIG. 4.
  • the application example according to FIG. 1 is a second embodiment of FIG. 4.
  • At least one coupling means 150 of a coupling unit 140 is provided on a side face 114 on the second wheel 104, in particular the crown wheel 112, preferably on the side face 114, in particular connected to the side face 114 ,
  • the coupling means 150 is formed integrally with the second wheel 104, 112, so that the second wheel 104 forms the first coupling member 152 of the coupling unit 140.
  • a second coupling member 154 of the coupling unit 140 is provided, which is preferably non-rotatably connected to the shaft or the work spindle 40.
  • an intermediate coupling member 155 is disposed, which rests in the direction of the second coupling member 154 on the first coupling member 152. In an engaged state of the second coupling member 154, this establishes a non-positive and / or positive connection with the intermediate coupling element 155 for rotational drive of the first coupling member 152.
  • a clutch actuating means 160 is further provided.
  • the clutch actuating means 160 is designed as a chain of two shaft sections 42, 44 of the shaft or work spindle 40 which are displaceable axially along the axis of rotation 110.
  • the shaft sections 42, 44 are formed and / or arranged such that an axial displacement of the first Shaft portion 42 in the direction of the coupling unit 140 to the second shaft portion is transferable.
  • the second coupling member 154 is preferably rigidly connected to the second shaft portion 44 and so via the axial displacement of the shaft portions 42, 44 engageable with the first coupling member 152 into engagement.
  • the coupling unit 140 is preferably formed as a dog clutch 141.
  • 3a and 3b show exemplary embodiments of a crown wheel 112 as a second wheel 104 of the angle gear 108. Identical or equivalent features are denoted by the same reference numerals.
  • recesses 162 are provided, which are provided for receiving correspondingly trained, not shown here engaging elements 164 of the second coupling member 154.
  • the engagement elements 164 are preferably formed claw or cam-like.
  • the latching recesses 162 and the engagement elements 164 form the coupling means 150 of the coupling members 152, 154.
  • latching recesses 162 instead of four latching recesses 162, more or fewer, in particular two, three or five latching recesses 162 are provided.
  • the number of engaging elements 164 of the second coupling member 154 is preferably limited upwardly by the number of locking recesses 162, in particular it may be advantageous to provide less, preferably only half as many engaging elements 164 as recesses 162.
  • both coupling members 152, 154 each have latching recesses 162 and engagement elements 164.
  • Fig. 2 further shows the arrangement of the bearing unit 130 in the central bore 105 of the second wheel 104, 112.
  • the bearing unit 130 is formed as a sliding bearing 131.
  • Fig. 2 shows a conical crown wheel 112, with which advantageously one of a half of a cone angle WK corresponding angle Wl is adjustable
  • Figs. 3a and 3b show an arrangement of the crown gear 113 on the zu This embodiment is particularly suitable for a nearly rectangular arrangement of the axes of rotation of the drive unit 14 and the use unit 20, as shown in the example of FIG. 1, a circumferential surface 116 vertical side surface 114 of the crown wheel.
  • Fig. 3b shows a section along the line A - A through the crown wheel 112 of Fig. 3a.
  • the latching recesses 162 of this exemplary embodiment have a latching or latching profile 168 provided essentially in the circumferential direction 166.
  • the latching or latching profile 168 is distinguished in particular by a depth of the latching recess 162 which varies over the circumferential direction.
  • This latching or latching profile 168 promotes an engaging engagement of the engagement elements 164 assigned to the second coupling element 154.
  • the engagement elements 164 are not represented by rolling elements (for example balls, rollers or rollers), in particular as elastically prestressed rolling elements -
  • rolling elements for example balls, rollers or rollers
  • the engagement members 164 may be formed as ramps or cams.
  • overrunning clutches whose characteristics favoring latching can be used in the gear arrangement 100 according to the invention without impairing the inventive idea.
  • FIG. 4 shows the schematic view of a hammer drill with a third exemplary embodiment of a gear arrangement 100 according to the invention as a second example of application of a power tool 10.
  • Identical or equivalent features carry the same reference numerals as the examples described above.
  • the housing 12, 13 comprises, in addition to the drive unit 14 designed as an electric motor 16, the use unit 20 and an actuation unit 22, a control and / or regulation unit 24, in particular in the form of the electronics unit 25, and the energy supply unit 26.
  • the gear assembly 100 according to the invention is provided to transfer a generated by the drive unit 14 to the motor shaft 18 drive torque on the formed as an intermediate shaft 46 shaft or work spindle 40 controllably on the use unit 20.
  • the end region 38 of the motor shaft 18 has the pinion 102, 103 already known from FIG.
  • the percussion unit 48 of the hammer drill comprises at least one percussion drive 48.
  • the percussion drive 48 has in the example of FIG. 4 a wobble drive device 52 for oscillating drive a piston unit 54 which comprises a bearing sleeve 56 which is preferably freely rotatably mounted on the intermediate shaft 46.
  • a rotary drive 50 may be provided, as indicated only schematically in FIG. 4.
  • a cone ring 62 is provided around a rotation axis 60 of the intermediate shaft 46, preferably formed.
  • the cone ring 62 has a substantially radially outwardly directed, cone-shaped outer circumferential surface 64. This is best seen in Fig. 5b.
  • the second wheel 104 which is preferably configured as a crown wheel 112, has on its side surface 114 an annular friction contour 180, which has an inner circumferential surface 182 which is directed inwards in the direction of the central bore 105 substantially radially.
  • the outer circumferential surface 64 and the inner lateral surface 182 are each designed as friction surfaces 184, in particular as friction surfaces 184 that are complementary to each other and can be brought into contact with each other in a substantially planar manner.
  • the opening angles Ol and 02 of the outer and inner lateral surface 64, 182 are formed approximately equal, so that upon engagement of the two conical surfaces 64, 182 caused by frictional force-locking connection, in particular clamping or spline connection is formed. This can be seen particularly well in FIG. 5b.
  • Friction surfaces 184 may be provided in a gear assembly 100 according to the invention.
  • the friction surfaces 184 thus form the coupling means 150 of the coupling unit 140, wherein the second wheel 104, 112 with the friction contour 180, the first coupling member 152 and the bearing sleeve 56 with cone ring 62 form the second coupling member 154 of the coupling unit 140.
  • FIG. 5 a shows an example of the second wheel 104, 112 according to FIG. 4 with the friction contour 180 of the first coupling member 152 arranged around the center bore 105.
  • the friction contour 180, 152 is analogous to the conical ring 62 of the second coupling member 154 in the form of a circumferentially closed conical sleeve.
  • at least one coupling member 152, 154 is formed as a segmented, in particular as a section interrupted Konushülsenabête.
  • DE 10 2006 057 283 AI known embodiment is provided in the power tool 10 of FIG. 4 at least one control or clutch actuator 160, which is a by a user of the power tool 10, a switching the coupling state of the coupling unit 140 allowed.
  • control or clutch actuator 160 With regard to the structure and operation of the control or clutch actuator 160, reference is made at this point to the corresponding description of DE 10 2006 057 283 AI.
  • those skilled in the art can also use other control or clutch actuating means 160 known to them in a power tool 10 having a gear arrangement 100 according to the invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un système de transmission (100) pour le transfert d'un mouvement de rotation dans un outil électrique, en particulier un outil électrique à main (10), comprenant une unité de couplage (140) conçue comme accouplement débrayable et dotée d'au moins deux organes de couplage (152, 154) et d'une transmission d'angle (108) présentant une paire de roues cylindriques à denture hélicoïdale double (106). Selon l'invention, une roue (104) de la paire de roues cylindriques à denture hélicoïdale double (106) forme un organe d'accouplement couplage (152) de l'unité de couplage (140).
EP11782440.9A 2010-12-21 2011-11-16 Système de transmission pour un outil électrique et outil électrique Withdrawn EP2655020A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010063729 DE102010063729A1 (de) 2010-12-21 2010-12-21 Getriebeanordnung für ein Elektrowerkzeug und Elektrowerkzeug
PCT/EP2011/070209 WO2012084346A1 (fr) 2010-12-21 2011-11-16 Système de transmission pour un outil électrique et outil électrique

Publications (1)

Publication Number Publication Date
EP2655020A1 true EP2655020A1 (fr) 2013-10-30

Family

ID=44971034

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11782440.9A Withdrawn EP2655020A1 (fr) 2010-12-21 2011-11-16 Système de transmission pour un outil électrique et outil électrique

Country Status (5)

Country Link
EP (1) EP2655020A1 (fr)
CN (1) CN103269833A (fr)
DE (1) DE102010063729A1 (fr)
RU (1) RU2013133707A (fr)
WO (1) WO2012084346A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013202027B4 (de) 2013-02-07 2024-09-26 Robert Bosch Gmbh Tragbare Werkzeugmaschine mit einem Haupt- und einem Bügelgriff
DE102018216573A1 (de) 2018-09-27 2020-04-02 Robert Bosch Gmbh Sicherheitsbremsvorrichtung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1095068A (en) * 1965-10-14 1967-12-13 Mets Owerke Kg Closs Rauch & S Improvements in motor-driven grinders comprising bevel gearings
DE2158598B2 (de) * 1971-11-26 1974-05-09 Metabowerke Kg, Closs, Rauch & Schnizler, 7440 Nuertingen Schmiervorrichtung für Getriebe mit Betrieb in allen Lagen
DE3328955A1 (de) * 1983-08-11 1985-02-21 Robert Bosch Gmbh, 7000 Stuttgart Winkelschleifer mit einer sicherheitskupplung
DE102006057283A1 (de) 2006-12-05 2008-06-12 Robert Bosch Gmbh Handwerkzeug

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012084346A1 *

Also Published As

Publication number Publication date
CN103269833A (zh) 2013-08-28
RU2013133707A (ru) 2015-01-27
WO2012084346A1 (fr) 2012-06-28
DE102010063729A1 (de) 2012-09-27

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