EP2415558A2 - Machine de polissage tenue manuellement - Google Patents

Machine de polissage tenue manuellement Download PDF

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Publication number
EP2415558A2
EP2415558A2 EP11172636A EP11172636A EP2415558A2 EP 2415558 A2 EP2415558 A2 EP 2415558A2 EP 11172636 A EP11172636 A EP 11172636A EP 11172636 A EP11172636 A EP 11172636A EP 2415558 A2 EP2415558 A2 EP 2415558A2
Authority
EP
European Patent Office
Prior art keywords
planetary gear
drive motor
gear
polishing machine
hand
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11172636A
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German (de)
English (en)
Other versions
EP2415558B1 (fr
EP2415558A3 (fr
Inventor
Dirk Röck
Eckhard Rühle
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.)
Flex Elektrowerkzeuge GmbH
Original Assignee
Flex Elektrowerkzeuge GmbH
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Publication date
Application filed by Flex Elektrowerkzeuge GmbH filed Critical Flex Elektrowerkzeuge GmbH
Publication of EP2415558A2 publication Critical patent/EP2415558A2/fr
Publication of EP2415558A3 publication Critical patent/EP2415558A3/fr
Application granted granted Critical
Publication of EP2415558B1 publication Critical patent/EP2415558B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
    • B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
    • B24B23/028—Angle tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B47/00—Drives or gearings; Equipment therefor
    • B24B47/10—Drives or gearings; Equipment therefor for rotating or reciprocating working-spindles carrying grinding wheels or workpieces
    • B24B47/12—Drives or gearings; Equipment therefor for rotating or reciprocating working-spindles carrying grinding wheels or workpieces by mechanical gearing or electric power
    • 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-held polishing machine comprising a drive motor, a drive motor shaft directly driven by the drive motor, a polishing tool shaft oriented transverse to the drive motor shaft, and a reduction gear coupled to the drive motor shaft and the polishing tool shaft, which are at least two-stage is.
  • the reduction gear serves to reduce the speed of the drive motor shaft provided by the drive motor to a speed of the polishing tool shaft which is suitable for polishing operations.
  • a speed is in particular of the order of 3,500 rpm.
  • From the DE 100 47 312 A1 is a controllable planetary gear for transmitting a rotational movement with a controllable between a drive and an output via a ring gear speed change known.
  • a hand tool gearbox in particular for an angle grinder, with a rotatably mounted and driven by an electric motor drive shaft and a rotatably mounted output shaft known to drive a tool.
  • a planetary gear for transmitting torque from the drive shaft to the output shaft.
  • a hand-held power tool with a motor housing and a gear housing, wherein an electric drive motor is arranged with a motor shaft in the motor housing, a gear with an angle gear and a tool spindle are arranged in the gear housing, and wherein the tool spindle in an at least approximately right angle to the motor shaft lies and from the motor shaft is driven via the gear.
  • the gearbox has in addition to the angular gear on a planetary gear.
  • the invention has for its object to provide a hand-held polishing machine of the type mentioned, which has advantageous handling properties.
  • the reduction gear comprises a planetary gear as a reduction stage and that a rotation axis of the drive motor shaft and a main axis of the planetary gear are coaxial.
  • the planetary gear can provide a reduction stage, which has a coaxial axis of rotation to a drive motor shaft.
  • This reduction stage is designed so that a drive train is in line with the drive motor shaft.
  • the reduction gear can be realized with high smoothness and low wear.
  • An axis of rotation of the drive motor shaft and a major axis of the planetary gear are coaxial with each other.
  • the main axis of the planetary gear is, for example, a corresponding axis of a sun gear of the planetary gear, wherein the planetary gears of the planetary gear orbital to the main axis.
  • a sun gear of the planetary gear is rotatably connected to the drive motor shaft.
  • the drive torque of the drive motor can be coupled into the planetary gear.
  • a ring gear of the planetary gear rotatably disposed in a housing. This allows a planetary gear carrier (bridge) to rotate. The corresponding drive torque can be coupled into a further reduction stage.
  • the ring gear has an external thread and is fixed in the housing with the external thread.
  • the planetary gear can be mounted in a simple manner.
  • the ring gear is arranged in the housing in a conical seat.
  • a screw fixation of the ring gear can complicate an exact coaxial positioning to a rotation axis of the drive motor shaft.
  • By providing a conical seat can be realized in a simple manner coaxial alignment with high accuracy.
  • a planetary gear carrier of the planetary gear on which a plurality of planetary gears is arranged, is rotatably mounted in a housing.
  • the drive motor shaft rotatably drives the planetary gear carrier via a sun gear.
  • the drive torque of the planetary gear carrier can then in turn pass on to a further reduction stage of the reduction gear.
  • the Planetary gear carrier can fulfill a variety of tasks; it is used to attach a gear such as a bevel gear of a further reduction stage. It serves to center a sun gear. It provides a counter element for the storage of planetary gears.
  • a locking of the polishing tool shaft can be carried out via the planetary gear carrier.
  • a drive torque is provided in the planetary gear carrier by a sun gear driven by the drive motor shaft. This makes it easy to implement a reduction stage.
  • the planetary gear carrier provides the drive torque to a further reduction stage of the reduction gear.
  • the planetary gear carrier has a reduced rotational speed with respect to a rotational speed of the drive motor shaft. It has a higher speed than the polishing tool shaft.
  • polishing tool shaft is then directly coupled to the further gear stage.
  • a two-stage reduction gear can be formed in a simple manner.
  • the further reduction stage is an angle gear.
  • bevel gears are bevel gear or crown gear. This makes it possible to realize a polishing machine which has a longitudinal extension in an axis, which is in particular coaxial to a rotation axis of the drive motor shaft, wherein a rotation axis of a polishing tool is transverse and in particular perpendicular to this axis.
  • a gear of a further reduction stage of the reduction gear is rotatably connected to the planetary gear carrier.
  • the gear is, for example, a bevel gear (a bevel gear) or a crown gear (a crown gear).
  • a rotation axis of the planetary gear carrier and a rotation axis of the drive motor shaft are coaxial. This results due to a linear arrangement of the corresponding reduction stage and the drive motor shaft, a housing formation with minimized height in the direction of the axis of rotation of the polishing tool shaft.
  • a locking device for locking a rotatability of the polishing tool shaft acts on the planetary gear carrier.
  • a locking device is required to fix the polishing tool shaft in its rotation for a tool change.
  • the locking device acts directly on the planetary gear carrier.
  • an actuating element of the locking device which is actuated by a user, can be arranged outside handle regions of the polishing machine. The risk of accidental locking, for example, during operation of the polishing machine is greatly reduced.
  • no locking device must be provided, for example, in the range of an angle gear, so that the corresponding area of the polishing machine can be formed in a simple manner and this can be ergonomically optimized for handling the polishing machine (for holding by a user).
  • a planetary gear carrier can be formed in a simple manner for locking, since to hold the planet gears anyway a housing must already be present. Furthermore, in a forced locking at the outlet of the machine, the speed and the resulting rotational energy is reduced, in particular on a rotor of the motor. Due to the resulting reduced torque, the force load of a locking pin is reduced.
  • the locking device on an engagement element which is for example formed like a pin, which in a corresponding Recess of the Planetenenhoffradffys is submersed to lock its rotation. This makes it easy to achieve a rotational fixation of the polishing tool shaft via rotational fixation of the planetary gear carrier.
  • a recess device with a recess is asymmetrical with respect to a direction of rotation of the planetary gear carrier.
  • This asymmetrical design can be achieved in particular on the recess defining walls.
  • a tapered side has an elevation at the recess and, optionally, additionally has an expiring side of the recess a material reduction. This achieves a kind of intervention delay. Dipping the engagement element in a recess should be prevented during operation of the polishing machine. If the drive motor shaft is not in operation, then a user may press the engagement member toward the planetary gear carrier and cause immersion by manual rotation of the polishing tool shaft. The manual rotation is slow. During rapid rotation during operation, the increase in distance increase to the recess when the engagement member abuts the elevation prevents immersion, because during the short time of rotation of the recess via the engagement element immersion usually can not be done.
  • an actuating element of the locking device is arranged in a region of the housing which surrounds the planetary gear carrier.
  • the actuating element of the locking device is an actuating device for a user.
  • the actuating element is designed in the manner of a push button. If it is arranged in the region of the housing which surrounds the planetary gear carrier, then can be easily achieved by a linear movement of the corresponding handle member, this linear movement is activated by acting on the actuator, a dipping of the engagement element in a corresponding recess.
  • the actuator is disposed outside a gripping area for holding the polishing machine by a user in the polishing process. This minimizes the risk of unintentional actuation during a polishing operation.
  • the locking device on the planetary gear carrier this can be realized in a simple manner.
  • a sun gear of the planetary gear on a front side on a centering collar.
  • the production of the polishing machine can be carried out in a simple manner.
  • the sun gear can be easily brought into operative contact with a plurality of planetary gears of the planetary gear.
  • a planetary gear carrier then has a recess for the centering collar.
  • the centering collar is positioned in this recess and advantageously does not touch it during rotation of the planetary gear carrier.
  • planetary gears of the planetary gear are each arranged on a sleeve and in particular needle sleeve, which sits on a planetary gear carrier.
  • the planetary gear can be easily manufactured.
  • the sleeve is fixed in each case via a pin element on the planetary gear carrier.
  • the planetary gear can be manufactured in a simple manner.
  • the drive motor provides a speed in the range between 20,000 rpm and 40,000 rpm.
  • the drive motor shaft is driven at this speed.
  • the reduction gear provides for a corresponding reduction.
  • the planetary gear provides an output speed in the range between 5,000 rpm and 10,000 rpm.
  • the high speed provided by the drive motor shaft is lowered to an intermediate speed.
  • the polishing tool shaft has a speed in the range between 400 U / min and 3,000 U / min and in particular in the range between 600 U / min and 2,200 U / min.
  • the speed is adjustable to adapt to a given workpiece. This results in optimized polishing results.
  • the drive motor is an electric motor.
  • a housing portion in which the drive motor is disposed provides a gripping area for a user of the polishing machine via its outer surface. A user can then embrace the polishing machine in this housing area. With the other hand he can hold the polishing machine in a head area.
  • FIG. 1 An embodiment of a polishing machine according to the invention, which in a perspective view in FIG. 1 shown and designated therein by 10, comprises a designated as a whole with 12 housing.
  • the housing 12 comprises a first housing shell 14.
  • a second housing shell 16 is fixed to the first housing shell 14.
  • the second housing shell 16 (and optionally the first housing shell 14) is formed in two parts, for example, with a first part 18 and a second part 20.
  • the housing 12 has two housing shells and a closed area.
  • the polishing machine 10 has three areas: a head 22, a central area 24, which adjoins the head 22, and an end area 26, wherein the central area 24 lies between the head 22 and the end area 26.
  • the first part 18 of the second housing shell 16 closes the housing 12 at the head 22 and the second part 20 of the second housing shell 16 closes the housing 12 at the central area 24 and the end area 26.
  • polishing tool shaft 28 which is rotatable about a rotational axis 32 in a rotational direction 30.
  • a polishing tool and in particular a polishing pad can be fixed by means of suitable fixing means.
  • the polishing tool shaft 28 protrudes beyond an underside 34 of the housing 12.
  • This underside 34 is formed by a corresponding shell part 36a of the first housing shell 14 and by corresponding shell parts 36b, 36c of the second housing shell 16.
  • the axis of rotation 32 of the polishing tool shaft 28 lies on a center plane 38 of the polishing machine. At this center plane 38, the first housing shell 14 and the second housing shell 16 abut each other at least approximately. (The first housing shell 14 and / or the second housing shell 16 may have a fold or a Falzaus brieflyung for tight completion of the housing 12).
  • a drive motor 40 is arranged in the housing 12, which is an electric motor ( FIGS. 2 to 4 ).
  • a switch 42 for activating / deactivating the drive motor 40 is arranged.
  • a corresponding circuit arrangement is positioned in the end region 26.
  • a cable 44 leads to the connection of the polishing machine 10 to an electrical supply device and in particular to a power supply network in the end region 26.
  • a reduction gear 46 is arranged, which is formed in two stages with a first reduction stage 48, which comprises a planetary gear 50, and with a second reduction stage 52 which is connected in series to the first reduction stage 48 and an angle gear 54 comprises ( Figures 2 . 3 ).
  • the polishing tool shaft 28 is coupled to the second reduction stage 52.
  • the polishing machine 10 includes a drive motor shaft 56 (FIG. FIG. 4 ), which is rotatable about a rotation axis 58.
  • the axis of rotation 58 is transverse and in particular perpendicular to the axis of rotation 32 of the polishing tool shaft 28.
  • the drive motor shaft 56 is part of the drive motor 40 or coupled directly to the drive motor 40.
  • the drive motor shaft 56 is connected via a bearing device 60 (FIG. FIG. 6 ) stored in the housing 12. It is rotatably connected to a rotor (armature) 62, on which a laminated core 64 ( FIG. 4 ) sits.
  • the drive motor 40 further comprises a stator 65 (FIG. FIG. 3 ) on.
  • the housing 12 is provided with louvers 66a, 66b (FIG. FIG. 1 ) are provided for air cooling of the drive motor 40, wherein louvers 66a are arranged on the head 22 and in particular on the underside 34 in the vicinity of the polishing tool shaft 28 are arranged. Louvers 66b are laterally disposed on the housing 12 in the end region 26. An air flow can be sucked through the rotor 62 through the housing 12 in the region of the drive motor 40 between the air slots 66a and 66b.
  • the drive motor shaft 56 has a speed which is on the order of 30,000 rpm.
  • the reduction gear 46 lowers the speed for the polishing tool shaft 28 and, in particular, lowers it to a speed of the order of 2,000 rpm.
  • the first reduction stage 48 of the reduction gear 46 while the rotational speed of the drive motor shaft 56 is reduced to a lying between the rotational speed of the polishing tool shaft 28 and the drive motor shaft 56 speed. For example, a reduction to a speed on the order of magnitude of 7,000 rpm.
  • the final reduction to the effective rotational speed of the polishing tool shaft 28 then takes place from this rotational speed.
  • sun gear 68 ( FIGS. 4 to 6 ) of the planetary gear 50.
  • This sun gear 68 provides for the coupling of the drive motor shaft 56 to the planetary gear 50.
  • An axis of rotation of the sun gear 68 corresponds to the axis of rotation of the drive motor shaft 56th
  • the sun gear 68 has a centering collar 70 at its front end (FIG. FIGS. 4 . 6 ).
  • the sun gear 68 has a diameter D 1 transverse to the axis of rotation 58 (FIG. FIG. 6 ) on.
  • the sun gear 68 has a diameter D 2 which is smaller than the diameter D 1 .
  • This centering collar 70 facilitates assembly of the polishing machine 10 when a planetary gear carrier 72 (FIG. Figures 2 . 3 . 7 ) is to be placed on the sun gear 68 with engagement of planetary gears 74.
  • the planetary gear carrier 72 has a cage 76 which holds a plurality of planetary gears 74. In particular, at least three planet gears 74 are provided, which are arranged at a distance.
  • the planet gears 74 each have an axis 78 which is oriented parallel to a main axis 80 of the planetary gear 50.
  • the main axis 80 is also a central axis of the planetary gear carrier 72 and the "sun center" for the planetary gears 74.
  • the cage 76 has side windows 82 corresponding to the number of planet gears 74. Through the respective window 82, a planetary gear 74 is partially submerged.
  • a planetary gear 74 has a recess 84 in which a sleeve 86 is positioned.
  • the sleeve 86 is in particular pressed into the recess 84, so that the corresponding planetary gear 74 pressed against the sleeve 86 is fixed.
  • On the sleeve 86 in turn sits a pin member 88 which is fixed to the cage 76.
  • the cage 76 has a disc element 90 for this purpose.
  • a ring member 92 is positioned.
  • the pin member 88 of the corresponding planetary gear 74 is fixed to the disc member 90 and to the opposing ring member 92.
  • the planet gears 74 are seated between the disc member 90 and the ring member 92, wherein lands 94 connect the disc member 90 and the ring member 92. Between adjacent webs 94, the respective windows 82 are formed.
  • a spindle extension 96 is formed on the disc element 90. This spindle extension 76 serves to connect to the second stage 52 of the reduction gear 46th
  • the ring member 92 has a penetration region 98 through which the sun gear 68 has penetrated.
  • the sun gear 68 is engaged with the planetary gears 74.
  • the planetary gear carrier 72 is rotatably disposed around a rotation axis 100 in the housing 12.
  • the axis of rotation 100 is coaxial with the axis of rotation 58 of the drive motor shaft 56 and thus also coaxial with the main axis 80 of the planetary gear 50th
  • the planetary gear carrier 72 has on the disk element 90 a recess 97 (FIG. FIG. 7 ) for the centering collar 70 of the sun gear 68.
  • the centering collar 70 can dip when the Planetenenzahnradisme 72 is correctly positioned with respect to the sun gear 68 with engagement of the planetary gears 74 to the sun gear 68.
  • the recess 97 is preferably designed so that the sun gear 68 in the region of the centering collar 70 does not touch the planetary gear carrier 72.
  • a pivot bearing 102 is disposed between the sun gear 68 and the bearing means 60 ( FIG. 6 ), over which the planetary gear carrier 72 can be supported in this area without hindering the rotation.
  • a further pivot bearing 104 is arranged, which in particular the second reduction stage 52 of the reduction gear 46 is adjacent, via which the planetary gear carrier 72 is rotatably supported in the housing 12 in the region of the spindle extension 96.
  • a ring gear 106 is rotatably on the head 22 is positioned.
  • the ring gear 106 has a gear teeth 108 facing the planetary gear wheels 74 of the planetary gear carrier 72 and adapted to them.
  • the toothing of the planet gears 74 engages in this toothing 108 of the ring gear 106.
  • the rotation of the sun gear 68 by the drive motor shaft 56 causes a rotation of the planetary gear carrier 72 with the spindle extension 96 as a whole about the axis of rotation 100.
  • the rotatably arranged in housing 12, the ring gear 106 to which the planet gears 74 engage, constitutes a counter element of the planetary gear 50.
  • the ratio of the planetary gear 50 is determined by the ratio of the number of teeth of the teeth 108 of the ring gear 106 to the number of teeth of the sun gear 68. The larger this ratio, the larger the reduction, that is, the smaller the rotational speed of the planetary gear carrier 72 and thus the spindle extension 96 in comparison to the rotational speed of the drive motor shaft 56th
  • the ratio of the speed of the sun gear 68 (and thus the drive motor shaft 56) to the speed of the spindle extension 96 is in the range of 3 to 5.
  • a typical ratio for the number of teeth the toothing 108 to the number of teeth of the sun gear 68 is of the order of 3.
  • the ring gear 106 has an external thread 110, with which it is screwed in the housing 12 for rotationally fixed fixing to a corresponding mating thread.
  • a conical seat 112 is provided in order to obtain an exact alignment of a central axis of the ring gear 106 coaxially with the axis of rotation 100.
  • Gears of the planetary gear 50 and in particular the planet gears 74 are preferably made of a plastic material. This makes it possible to achieve a noise reduction in comparison with metallic gears.
  • the sun gear 68 and ring gear 106 may be made of a plastic material or metal.
  • an angle gear 54 is realized as a bevel gear.
  • the polishing machine 10 has a locking device 118 for the rotationally fixed fixing of the polishing tool shaft 28 for a tool change or for the insertion of a tool.
  • the locking device 118 is designed so that it acts on the planetary gear carrier 72 and this fixed in rotation. This rotationally fixed fixation causes mediated via the second reduction stage 52 of the reduction gear 46, a rotationally fixed fixation of the polishing tool shaft 28th
  • the locking device 118 has an engagement element 120 arranged on the head 22 above the planetary gear carrier 74, for example in the form of a pin element 120.
  • This pin element 120 is supported by a spring 122.
  • the spring 122 tends to urge a lower end of the pin member 120 away from the planetary gear carrier 72 in a direction transverse to the axis of rotation 100.
  • an operator To move the lower end of the pin member 120 in the corresponding opposite direction, an operator must exert a corresponding force on an actuator 124.
  • the actuating element 124 is designed in particular as a head, which sits on the pin element 120 and can be actuated from an outer side of the housing 12 in the manner of a push button.
  • the planetary gear carrier 74 has at the ring member 92 spaced a recess means with recesses 126, in which the pin member 120 can dip. If a pin member 120 is immersed in a corresponding recess 126, then the rotatability of the planetary gear carrier 72 and thus the rotatability of the polishing tool shaft 28 is locked.
  • the housing 12 has a rounded transition stage 130 on an upper side 128 opposite the underside 34 on the head 22.
  • the height of the housing 12 increases in a height direction which is parallel to the direction of the axis of rotation 32.
  • the angle gear 54 is arranged in that area with the larger height.
  • the planetary gear 50 is arranged in that area with the larger height.
  • the lower-height area 132 a grip area for a user is formed, through which it can hold the polishing machine 10 in polishing, that is, the area 132 is a holding area.
  • the housing 12 is rounded at one end 134.
  • the housing 12 further includes a handle portion 136 for a user in the central region 24.
  • a Handabloisêt 138 On the handle portion 136 may be arranged a Handabloisêt 138, which is formed for example by an increase on an outer side of the housing 12.
  • Another gripping area 139 is formed at the end area 26.
  • a user can grasp the grip area 139 with one hand and grasp the area 132 with the other hand.
  • the actuator 124 is disposed outside of the area 132 and outside of the grip area 139. This reduces the risk of unintentional operation.
  • the locking device 118 is arranged in particular on the housing 12 at a region which surrounds the planetary gear carrier 72 and in particular its ring element 92.
  • the recess means for dipping the pin member 120 is asymmetrically configured with respect to a rotational direction of the planetary gear carrier 72.
  • the locking means 118 acts on a "mid-speed range", namely the planetary gear carrier 72.
  • the recesses 126 is associated with a respective increase 140 on corresponding boundary walls on a sloping side and assigned a decrease 142 on the opposite running side.
  • the pin member 120 may be inadvertently in the direction of the ring member 92 is pressed, then an increase 140 prevents penetration into the corresponding recess 126 and thereby an abrupt stop of the Planetenenzahnradambas 72 due to an intervention delay.
  • the lock is such that when the drive motor shaft 56 is stationary, the pin member 120 is moved by applying force to the actuator 124 in the direction of the planetary gear carrier 72 and the polishing tool shaft 28 is rotated manually by the user until the pin member 120 can dip into a corresponding recess 126. If the rotation of the planetary gear carrier 72 is correspondingly slow, as achieved, for example, by manual rotation of the polishing tool shaft 28, then a dipping and thus a blocking of the rotation can take place.
  • the rising side elevation 140 will cause some sort of time delay for the dip of the pin member 120.
  • the planetary gear carrier 72 has so further rotated that no immersion can take place, since the recess 126 has moved past the pin member 120.
  • the hand-held polishing machine 10 of the invention operates as follows:
  • a multi-stage and in particular two-stage reduction gear 46 is provided between the drive motor 40 and the polishing tool shaft 28. This is coupled on the input side to the drive motor shaft 56 and coupled on the output side to the polishing tool shaft 28. On the input side, the reduction gear 46 is acted upon by the drive torque and the rotational speed of the drive motor shaft 56. On the output side (output side), the reduction gear 46 of the polishing tool shaft 28 and thus a corresponding polishing tool provides the drive torque with a through the Reduction gear 46 set speed, which is smaller than the rotational speed of the drive motor shaft 56th
  • the first reduction stage 48 of the reduction gear 46 which is coupled to the drive motor shaft 56, a planetary gear 50.
  • a flat housing 12 This in turn makes it possible to hold the polishing machine 10 by hand close to the central region 24 of the housing 12. This results in easy handling for a user.
  • the planetary gear carrier 74 of the planetary gear 50 conveys the drive torque of the drive motor shaft 56 to the bevel gear 114 of the angular gear 54.
  • the planetary gear carrier 72 thus serves to attach and drive the bevel gear 114.
  • He is a counter element for the storage of the planet gears 74. He serves to center the Sun gear 68.
  • the locking device 118 acts on the planetary gear carrier 72, so that a corresponding actuating element 124 is far away from a grip region 132 on the head 22 and then according to the housing 12 can be formed there with minimized dimensions.
  • the bevel gear 54 then need not be designed so that a locking device can act on it.
  • the existing anyway for the planetary gear carrier 72 cage 76 can be used with corresponding recesses 126 for the locking device 118.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
EP11172636.0A 2010-08-05 2011-07-05 Machine de polissage tenue manuellement Active EP2415558B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010038976A DE102010038976A1 (de) 2010-08-05 2010-08-05 Handgehaltene Poliermaschine

Publications (3)

Publication Number Publication Date
EP2415558A2 true EP2415558A2 (fr) 2012-02-08
EP2415558A3 EP2415558A3 (fr) 2016-07-13
EP2415558B1 EP2415558B1 (fr) 2022-10-26

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EP11172636.0A Active EP2415558B1 (fr) 2010-08-05 2011-07-05 Machine de polissage tenue manuellement

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3450099A1 (fr) * 2017-08-28 2019-03-06 Siprotool AG Machine de meulage de surface destinée au meulage et au polissage du sol

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Publication number Priority date Publication date Assignee Title
DE10047312A1 (de) 2000-09-25 2002-05-08 Hilti Ag Steuerbares Planetengetriebe
DE10258863A1 (de) 2002-12-17 2004-07-08 Robert Bosch Gmbh Handwerkzeugmaschinengetriebe und Handwerkzeugmaschine
WO2008014806A1 (fr) 2006-08-02 2008-02-07 A & M Electric Tools Gmbh Outil électronique guidé à la main avec un engrenage planétaire

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GB1130679A (en) * 1966-10-11 1968-10-16 Atlas Copco Ab Improvements in rotary pneumatic nut runners and like tools
US6102632A (en) * 1998-04-23 2000-08-15 Black & Decker Inc. Two speed right angle drill
US20050279519A1 (en) * 2004-06-17 2005-12-22 One World Technologies Limited Right angle impact driver
JP2009220202A (ja) * 2008-03-14 2009-10-01 Techway Industrial Co Ltd 電気式研磨ガン

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Publication number Priority date Publication date Assignee Title
DE10047312A1 (de) 2000-09-25 2002-05-08 Hilti Ag Steuerbares Planetengetriebe
DE10258863A1 (de) 2002-12-17 2004-07-08 Robert Bosch Gmbh Handwerkzeugmaschinengetriebe und Handwerkzeugmaschine
WO2008014806A1 (fr) 2006-08-02 2008-02-07 A & M Electric Tools Gmbh Outil électronique guidé à la main avec un engrenage planétaire

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3450099A1 (fr) * 2017-08-28 2019-03-06 Siprotool AG Machine de meulage de surface destinée au meulage et au polissage du sol

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EP2415558B1 (fr) 2022-10-26
DE102010038976A1 (de) 2012-02-09
EP2415558A3 (fr) 2016-07-13

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