EP2303514A1 - Procédé pour faire fonctionner une machine-outil pourvue d'un dispositif d'embrayage - Google Patents

Procédé pour faire fonctionner une machine-outil pourvue d'un dispositif d'embrayage

Info

Publication number
EP2303514A1
EP2303514A1 EP08874778A EP08874778A EP2303514A1 EP 2303514 A1 EP2303514 A1 EP 2303514A1 EP 08874778 A EP08874778 A EP 08874778A EP 08874778 A EP08874778 A EP 08874778A EP 2303514 A1 EP2303514 A1 EP 2303514A1
Authority
EP
European Patent Office
Prior art keywords
tool
coupling device
reset
torque
tool holder
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
EP08874778A
Other languages
German (de)
English (en)
Other versions
EP2303514B1 (fr
Inventor
Willy Braun
Juergen Lennartz
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 EP2303514A1 publication Critical patent/EP2303514A1/fr
Application granted granted Critical
Publication of EP2303514B1 publication Critical patent/EP2303514B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/003—Clutches specially adapted therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit
    • B25D17/084—Rotating chucks or sockets
    • B25D17/088—Rotating chucks or sockets with radial movable locking elements co-operating with bit shafts specially adapted therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0015—Tools having a percussion-only mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/101—Emitting warning signals, e.g. visual or sound
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/165—Overload clutches, torque limiters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/195—Regulation means
    • B25D2250/205—Regulation means for torque
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/221—Sensors

Definitions

  • the invention relates to a method for operating a machine tool, in particular an electrically operable hand tool according to the preamble of the independent claims.
  • Machine tools which serve at least one rotary drive of insert tools usually have latching clutches which limit a torque acting on the insert tool to a specific, preselected limit torque.
  • a torque acting on the insert tool to a specific, preselected limit torque.
  • Drilling machines, percussion drills or drilling / combi hammers is the pre-selected limit torque and thus the Kochrastkupplung a significant importance in accident prevention.
  • the preselected limit torque represents a compromise between the lowest possible torque load of the insert tool, the machine tool and / or an operator and the highest possible working torque for using large tool diameter of the insert tool.
  • the machine tool described above has the following operating procedure in common: If an operator determines that another limit torque of the overload clutch is required for a more favorable work progress, the operator adjusts the appropriate limit torque to an actuating device of the overload clutch. This applies at the required higher limit torque as well as at the required lower limit torque. So that in both switching direction manual intervention is required. In particular, during prolonged interruption of work and / or after a change of the insert tool with a lower required limit torque than the currently set limit torque can lead to undesirable effects of the high limit torque.
  • WO 2004/024398 A1 discloses a hammer drill with a two-stage coupling device, in which an automatic reset of the coupling device to the lowest possible limit torque is triggered as soon as the hammer drill is disconnected from the mains voltage.
  • the inventive method for operating a machine tool having the features of the main claim has the advantage that the change of an insert tool and / or an exchangeable tool holder is used as an indicator of a probably different necessary limit torque of the coupling device.
  • Another advantage is to be considered that possible damage to a less stable - because eg smaller insert tool - are avoided by a too high applied limit torque by the automatic return to a lower, preferably to the lowest possible limit torque.
  • Particularly advantageous is the automatic reset to the lowest possible of the at least two limit torques of the coupling device of the machine tool.
  • the coupling device is at the lowest possible of the at least two at a change of the insert tool and / or at a change of the tool holder
  • Limiting torques MGMin reset The provision is preferably carried out automatically.
  • a return of the coupling device is effected by actuation of a first actuating element for removing the insertion tool from the tool holder.
  • an automatic reset is effected to the lowest possible of the at least two limit torques.
  • the coupling device is reset when inserting an insert tool into the tool holder, then a particularly comfortable and robust design can be realized in this way.
  • the coupling device is automatically reset to the lowest possible of the at least two limit torques when inserting the insert tool.
  • an automatic reset of the coupling device is effected upon actuation of a second actuating element for changing the replaceable tool holder.
  • an automatic reset of the coupling device is effected upon actuation of a second actuating element for changing the replaceable tool holder.
  • a torque selection device of the coupling device sets the lowest possible limit torque in an initial position, a particularly efficient implementation of the method according to the invention is achieved.
  • the torque selector device can be locked in the currently selected shift position.
  • a very flexible embodiment of the method according to the invention is characterized by the following steps: a removal and / or insertion and / or change of an insert tool in the tool holder and / or the interchangeable tool holder is detected and the torque selection device, which is provided on the coupling device is acted so o that the torque selector is returned to its original position.
  • the coupling device is reset when the power supply of the machine tool is interrupted.
  • the coupling device is automatically reset to the lowest possible of the at least two limit torques.
  • At least one optical, acoustic and / or haptic signal generator which is provided on the machine tool, is activated when a different limit value is applied to the coupling device than the lowest possible limit torque.
  • FIG. 1 shows a rotary hammer as a first embodiment in side view.
  • FIG. 2 shows an enlarged detail of the rotary hammer on FIG. 1
  • FIG. 3a shows a plan view of a coupling device along the section line A-A from FIG. 1
  • FIG. 3b shows a plan view of an alternative coupling device analogous to FIG. 3a
  • FIG. 4 shows a second exemplary embodiment in the enlarged side view
  • Fig. 5 is a flow chart of the proposed method for operating a machine tool
  • FIG. 6 is a flowchart of a variant of the method according to FIG. 5 Description of the embodiments
  • FIG. 1 shows a side sectional view of a hammer drill 10 as a first exemplary embodiment of a machine tool according to the invention, in particular of an electrically operable hand tool machine according to the invention.
  • a drive device 14 is provided for rotating and / or beating drive of a not shown here, in a frontally mounted on the housing 12 tool holder 16 insert tool.
  • the drive device 14 has an electric motor 18 as a drive unit 19, a transmission device 20 and, designed as a hammer tube 22, the tool drive shaft 23.
  • the drive unit 19 facing away from end portion 22a of the hammer tube 22 is the
  • Tool holder 16 is arranged and non-rotatably, preferably releasably, in particular changably connected to the end portion 22 a of the hammer tube 22.
  • the hammer tube 22 is rotatably received in the housing 12 stored.
  • the hammer tube 22 is received in a formed as a transmission carrier 24 inner housing 25 and rotatably supported.
  • the inner housing 25 is in turn housed in the housing 12 fixed to the housing.
  • the electric motor 18 has, according to FIG. 1, a motor shaft 26, at whose free end 27 an output pinion 28 is provided.
  • the motor shaft 26 is arranged in the present embodiment at an angle, in particular at right angles to a main axis 30 of the hammer tube 22.
  • the geometric arrangement of the motor shaft 26 is not essential to the invention. On the contrary, a machine tool according to the invention can also have arrangements of the motor shaft 26 oriented parallel to the tool drive shaft 23.
  • the output pinion 28 is operatively connected to the hammer tube 22 via the transmission device 20 such that the hammer tube 22 is rotationally driven by a rotational movement of the output pinion 28.
  • the first gear stage 32 is formed on an input side 32a by the output gear 28 and on an output side 32b by a first spur gear 34 which meshes with the output gear 28.
  • the first spur gear 34 is arranged on a parallel to the motor shaft 26 arranged transmission shaft 36 and preferably rotatably connected thereto.
  • the transmission shaft 36 is rotatably supported in the gear carrier 24.
  • a second spur gear 38 is provided, which is preferably non-rotatably connected to the transmission shaft 36.
  • the second spur gear 38 is part of a second gear stage 40, wherein the second spur gear 38 acts as an input side 40a of the second gear stage 40.
  • the second spur gear 38 meshes with a coupling spur gear 42 of a coupling device 44.
  • the clutch spur 42 thus forms an output side 40b of the second gear stage 40th
  • the coupling device 44 is designed as an overrunning clutch, in particular as an at least two-stage lockup clutch 45.
  • the coupling device 44, 45 is designed as an adjustable coupling device 44, 45.
  • the Kupplungsstirnrad 42 is disposed on a parallel to the transmission shaft 36 arranged clutch shaft 46 and freely rotatably mounted on this.
  • the Kupplungsstirnrad 42 is formed as a hollow disc rim 48 in which a clutch mechanism 50 of the coupling device 44, 45 is arranged.
  • the coupling device 44, 45 comprises a driven wheel 54 designed as a bevel gear 52, which is arranged on the coupling shaft 46.
  • the coupling spur gear 42 is operatively connected to the output gear 52, 54 such that a rotational movement of the Kupplungsstirnrads 42 is transmitted to the output gear 52, 54.
  • a shift sleeve 56 is arranged in the present embodiment.
  • the shift sleeve 56 is rotatably and axially displaceably connected to the hammer tube 22.
  • a bevel gear 60 is arranged and preferably non-rotatably connected to the shift sleeve 56.
  • the shift sleeve 56 has a first shift position with respect to an axial displacement V and at least one further, second shift position.
  • the shift sleeve 56 In the first shift position, the shift sleeve 56 is positioned axially such that the bevel gear 60 is engaged with the bevel gear 52 of the clutch device 44, 45, so that rotational movement of the bevel gear 52 is transmitted to the bevel gear 60. As a result, a rotary drive of the hammer tube 22 is effected.
  • This switching position is shown in Fig. 1.
  • the shift sleeve 56 is positioned axially such that the bevel gear 60 with the bevel gear 52 of the coupling device 44, 45 is disengaged, whereby the rotary drive of the hammer tube 22 is deactivated.
  • the arrangement described above can transmit a rotational movement of the motor shaft 26 to the hammer tube 22 and thus to the tool holder 16 and the insert tool received therein, not shown here.
  • the gear device 20 of the hammer drill 10 of the embodiment includes a percussion drive 62 for driving a striking mechanism 64.
  • the impact mechanism 64 is designed as a Luftpolstertschwerk.
  • the striking mechanism drive 62 is designed as an eccentric drive 66.
  • the first spur gear 34 has an eccentric pin 68 arranged at a radial distance from the transmission shaft 36. The first spur gear 34 acts like this As an eccentric 70. Via a connecting rod 72 or a connecting rod 73 a percussion piston 74 of the impact mechanism 64 is operatively connected to the eccentric pin 68 and driven by this.
  • eccentric drive 66 is also possible, in which a separate eccentric wheel 70 is provided, which is optionally also arranged on the transmission shaft 36 or driven by at least one further gear stage. It is also possible to use an eccentric shaft or crankshaft instead of the eccentric wheel 70.
  • type of impact mechanism drive 62 is not essential to the invention, so that other percussion drives known to the person skilled in the art, such as e.g. Taumelfingerantriebe, coaxial drives, rocker arm or push rod drives can be used in a machine tool according to the invention.
  • the percussion piston 74 is arranged axially displaceable in a rear end region 76 of the hammer tube 22.
  • an air cushion 78 and a racket 80 which is likewise axially displaceable in the hammer tube 22, are provided in front of the percussion piston 74.
  • the hammer drill 10 further comprises an axially displaceable in the hammer tube 22 in front of the racket 80 arranged intermediate header 82.
  • the racket 80 which is driven in the known manner by the air cushion 78 as an air spring, transmits impact impulses to the intermediate header 82, which in turn transmit the impact pulses to an insertion end 83 of an insert tool can. Since neither the exact structure nor the associated precise mode of action of the impact mechanism 64 are essential to the invention, the person skilled in the art will be referred to the relevant literature at this point.
  • Clutch mechanism 50 of the clutch device 44, 45 has a first and a second clutch disc 84, 85, which are accommodated along the clutch shaft 46 lying one above the other in the disc rim 48.
  • the disc rim 48 has on an inner circumferential surface 86 latching depressions 88, as they are best seen in Fig. 3a or Fig. 3b.
  • the locking recesses 88 have a directed in the circumferential direction locking profile 89 and extend parallel to the coupling shaft 46 in the axial direction.
  • FIGS. 3 a and 3 b show two different embodiments, which differ in the design of the latching profile 89 and the number of latching depressions 88.
  • Corresponding to the number of locking recesses 88 are provided in the clutch plates 84, 85 to the outer diameter open radial grooves 90.
  • the radial grooves 90 are provided by an inner retaining ring 91 completed.
  • each radial groove 90 designed as a coil springs spring element 92 and, in the direction of the outer diameter in front of the spring element 92 arranged locking element 94 is added.
  • the locking element 94 is designed as a cylindrical pin or ball.
  • the spring element 92 is biased such that the detent element 94 is pressed with a defined detent force FR against the inner circumferential surface 86 of the disk rim 48, in particular into the detent recess 88.
  • the number of locking recesses 88 and of corresponding radial grooves 90 can be chosen freely. In particular, it is also possible that the number of locking recesses 88 and the number of radial grooves 90 differ from each other. Preferably, however, a radially symmetrical arrangement of locking recesses 88 and radial grooves 90 is selected over the circumference. Due to the radial symmetry as uniform as possible loading of the clutch mechanism 50 is achieved.
  • the embodiments shown in FIGS. 3a and 3b have eight or four locking depressions 88 and radial grooves 90 distributed uniformly over the circumference.
  • In the clutch shaft 46 is an axially displaceable spool 96 a
  • the coupling shaft 46 is designed as a hollow tube 98 which is open at one end and at whose preferably closed end 100 the bevel gear 52 of the coupling device 44, 45 is arranged, preferably formed.
  • the hollow tube 98 is rotatably supported by bearings in the gear carrier 24.
  • the spool 96 has at least one, preferably two or more, radially outwardly facing control vanes 102. These control vanes 102 project with a free end 104 through corresponding control grooves 106, which are provided in the hollow tube 98.
  • the inner retaining rings 91, 91 a of the clutch discs 84, 85 have on their outer surface of their inner diameter a number of receiving grooves 108, 109 for receiving the free ends 104 of the control vanes 102.
  • the number of receiving grooves 108, 109 is at least equal to the number of control vanes 102 of the spool 96.
  • the free ends 104 of the control vanes 102 can by axial displacement of the spool 96 selectively with the receiving grooves 108, 109 of the two clutch plates 84, 85 in engagement to be brought.
  • the spool 96 is in a first axial control position SP1 when the control vanes 102 with the receiving grooves 108 of the first
  • Clutch plate 84 are engaged.
  • the control vanes 102 engage with the receiving grooves 109 of the second clutch disc 85.
  • the free ends 104 of the control vanes 102 in an axial intermediate position of the spool 96 can also be brought into engagement simultaneously with the receiving grooves 108, 109 of the two clutch discs 84, 85.
  • the effective limit torque MG depends essentially on the value of the latching force FR, the number of pairs of radial grooves 90 and locking recesses 88 of the clutch disc 84, 85 and the geometric shape of the locking recesses 88 and / or the locking elements 94.
  • a first effective limit torque MG1 can be provided for the first clutch disc 84, which deviates from an effective second limit torque MG2 of the second clutch disc 85.
  • the first limit torque MG1 is preferably smaller than the second limit torque MG2. If the first limit torque MG1 is the lowest limit torque MG that can be set with the clutch device 44, 45, it is also possible to speak of the lowest possible limit torque MGmin.
  • the spool 96 is shown in the second control position, so that the second limit torque MG2 in the illustrated state of the hammer drill 10 is effective.
  • an elastic return element 1 12 is arranged, wherein the elastic return element 1 12 on an inner bearing surface 1 14 toward the preferably closed end 100 of the hollow tube 98 is supported.
  • an actuator 1 18 is provided at an opposite, free end 1 16 of the spool 96.
  • the actuating device 1 18 has a first switching state and at least one further switching state.
  • the actuating device 118 comprises a latching device 120 with a latching position which makes the at least one further switching state releasably lockable.
  • the latching device 120 has a triggering device 122 which makes a locked state of the latching device 120 releasable in an unlocking position.
  • the triggering device 122 can be understood as an example of a means 122 'for resetting the coupling device 44, 45 to a lower, preferably the lowest possible limit torque.
  • the operating device 118, a preferably accessible to the housing 12, switching unit 124 for actuating the actuator 118 by an operator.
  • the actuating device 1 18 is designed as a mechanical actuator 1 18a.
  • the actuator 118a is an example of a mechanical means according to the gist of the present invention.
  • the switching unit 124 in this case has a switching element 126 which is arranged accessible to the operator 12 on the housing.
  • the switching element 126 is designed as a shift lever 128 which is movably received in the housing 12 and projects with one end 128 a partially out of the housing 12.
  • the shift lever 128 is designed pivotable about a pivot axis 130.
  • the pivot axis 130 is preferably carried out substantially perpendicular to the coupling shaft 46 of the coupling device 44, 45.
  • a rocker arm 132 is provided at another, lying in the housing 12 end 128b of the shift lever 128, a rocker arm 132 is provided. One end 132 a of the rocker arm 132 protrudes into a receptacle 134 at the end 128 a of the shift lever 128.
  • a second end 132 b of the rocker arm 132 has a fastening element 136.
  • the fastener 136 of the rocker arm 132 is connected to the free end 1 16 of the spool 96, preferably releasably connected.
  • the free end 16 of the control slide 96 has a receiving groove 138.
  • the fastening element 136 is designed as a fastening fork 140, which engages in the receiving groove 138.
  • the rocker arm 132 is pivotable about a rocker shaft 141, which is aligned substantially perpendicular to the coupling shaft 46 of the coupling device 44, 45.
  • the locking device 120 of the actuating device 118a is designed as a locking device 120a.
  • the locking device 120a has for this purpose a locking lever 142, a
  • the locking lever 142 is designed as an angle lever 146.
  • a first end 146 a of the angle lever 146 is angled at a distance from rocker shaft 141 at an angle, preferably at right angles to a first, preferably to the coupling shaft 46 parallel lever arm 147 a in the direction of the spool 96.
  • At the first end 146a of the bell crank 146 is a
  • Detent element 148 is provided, preferably formed.
  • the latching element 148 is a latching profile 150 parallel to the coupling shaft 46.
  • the latching profile 150 is wedge-shaped to the first end 146a down sloping.
  • the coupling device 44, 45 facing side 150 b latching profile 150 is designed substantially flat.
  • the closing element 145 is arranged between the coupling shaft 46 preferably parallel extending part of the first lever arm 147a and a relative to the locking lever 142 fixed contact surface.
  • the closing element 145 is arranged between the coupling shaft 46 preferably parallel extending part of the first lever arm 147a and a relative to the locking lever 142 fixed contact surface.
  • the closing element 145 is arranged between the coupling shaft 46 preferably parallel extending part of the first lever arm 147a and a relative to the locking lever 142 fixed contact surface.
  • the closing element 145 is designed as a helical spring.
  • the closing element 145 is designed and arranged such that the locking lever 142 is returned to
  • the latching element 148 covers at the first end 146a of the locking lever 146 a pivoting area 152 of the second end 132b of the rocker arm 132 so that a pivotal movement of the rocker arm 132 substantially only in a first, coming from the direction of the side 150a of Einrastprofils 150 pivoting direction R1 is possible.
  • a pivoting movement of the rocker arm 142 in a second, coming from the direction of the side 150b of the latching profile 150 pivot direction R2 is largely blocked by the substantially planar design of the Einrastprofils 150 on the side 150b of the locking element 148. This avoids spontaneous return of the spool 96 from the second control position SP2 selected by the operator to the control position SP1.
  • a blocking action of the latching device 120 is designed so that a triggering of the latching device 120 is possible by manually operating the switching element 126, so that the operator can switch back to the control position SP1 and thus to the first limit torque MG1.
  • a first lever arm 147a substantially opposite side of the Arretierhebelschwenkachse 144 is further provided a second, preferably rectilinearly executed lever arm 147b. This is largely freely movable during a movement in the first pivoting direction R1. Facing away from the coupling shaft 46
  • a control rod 154 is arranged as a mechanical element 155 of the triggering device 122.
  • the triggering device 122 comprises, in addition to the control rod 154, a restoring element 156 which, in the present exemplary embodiment according to FIGS. 1 and 2, is supported on the gear carrier 24.
  • the control rod 154 is designed as an angled push rod. At one end of the tool holder 16 facing 154a, it protrudes with a pickup element 158 from the end, the tool holder 16 facing the end of the housing 12th
  • a second end 154b of the control rod 154 is arranged on the side of the second lever arm 147b facing away from the coupling shaft 46, preferably directly adjacent, in a particularly preferred manner in contact with the second lever arm 147b.
  • a contact surface 162 is provided in an angular transition region 160 of the control rod 154.
  • the return element 156 is provided.
  • the restoring element 156 thereby generates a restoring force directed in the direction of the tool holder 16, which restrains the control rod 154 in an axial starting position.
  • the tool holder 16 comprises a first actuating element 164.
  • the first actuating element 164 serves to unlock a factory locking of a tool holder of the tool holder 16 by the operator. After unlocking an insert tool can be removed or replaced.
  • Such tool holder 16 are well known to those skilled in the art, so that a detailed description is omitted here.
  • the first actuating element 164 is designed as an actuating sleeve 164a. To unlock the actuating sleeve 164a is moved by the operator in the direction of the machine tool so as to trigger the release.
  • the pickup element 158 is arranged so that a front-side contact surface 166 of the actuating sleeve 164 a upon actuation by the operator a pressure on the
  • Transducer element 158 exerts.
  • the control rod 154 is displaced axially in the housing 12 in the direction of the coupling device 44, 45 against the restoring force of the return element 156.
  • This axial displacement is transmitted via the second end 154b of the control rod 154 to the second lever arm 147b of the locking lever 146.
  • the locking lever 146 against the closing force of the
  • a mechanical actuating device 118a In addition to the embodiment of a mechanical actuating device 118a described in the first exemplary embodiment, alternative mechanical devices for switching one-sided locking of at least two control positions SP1, SP2 of a control slide 96 are known to the person skilled in the art.
  • deviating switching elements 126 such as rotary switches, rocker switches, slide switches and similar switches for manual operation of the coupling device 44, 45 can be used according to the invention.
  • the transmission from the actuating device 118a to the control slide 96 can also be achieved in a different manner in a known manner, without any changes essential to the invention being necessary.
  • traction devices such as cable or Bowden cables, or similar arrangements are used.
  • deviating locking devices 120 and / or reset devices 122 may be provided.
  • the transmission of the actuation of the first actuating element 164, for example as a lever, push or pull device can be solved differently, without interfering with the character of the invention.
  • FIG. 4 A second embodiment of a machine tool according to the invention is shown in FIG. 4 and will be described below.
  • the hammer drill 310 corresponds in this embodiment in its basic structure of the first embodiment, so that reference is made to the description in the preceding paragraphs.
  • the reference numbers of identical or equivalent features are increased by 300 in this case.
  • the actuating device 418 is designed as an electromechanical actuating device 418b.
  • the actuator 418a is an example of an electromechanical means according to the gist of the present invention.
  • the actuating device 418b has an actuator unit 466.
  • the actuator 466 is designed as a solenoid 466a.
  • the actuating device 418b preferably comprises a control unit 468 and at least one first sensor unit 470.
  • the switching magnet 466 a has an electromagnet 472, which is preferably designed as an annular coil.
  • the electromagnet 472 has a guide bore 476 provided in a transverse plane 474. In the guide bore 476 along the guide bore 476 axially displaceably arranged magnet armature 478 is provided.
  • the transverse plane 474 is oriented perpendicular to the coupling shaft 346 of the coupling device 344, 345.
  • the guide bore 476 of the electromagnet 472 is aligned parallel, in particular coaxially with the coupling shaft 346.
  • the magnet armature 478 is formed in the present embodiment predominantly pin-shaped.
  • a fastening device 480 is provided at one, the electromagnet 472 opposite end 478a of the electromagnet 478.
  • the free end 416 of the spool 396 of the coupling device 344, 345 is attached.
  • the spool 396 has a receiving groove 438 for positive connection between the
  • different attachment geometries for a positive connection between spool 396 and armature 478 or other fastening concepts can be used without being essential to the invention.
  • the armature 478 and the spool 396 may also be designed as a one-piece component.
  • a permanent magnet 482 is arranged such that the armature 478 is brought in a transition from a de-energized state to a energized state of the electromagnet 472 from a first switching position in at least one second switching position.
  • the permanent magnet 482 is designed as a bar magnet 482a.
  • the bar magnet 482a forms a shaft 478c of the magnet armature 478.
  • the solenoid 472 of the solenoid 466a is electrically connected to the control unit 468.
  • the control unit 468 can switch back and forth between the de-energized and the energized state of the electromagnet 472.
  • the spool 396 following the first embodiment already described, is reset by the return element 412 from the second control position SP2 in the first control position SP1.
  • the electromagnet 472 When the electromagnet 472 is placed in the energized state, a restoring force of the return element 412 is overcome, and the spool 396 is shifted from the first control position SP1 to the second control position SP2.
  • the control unit 468 is accessible via a dial 369 accessible to the operator on the housing 312, e.g. a switch, a button, a sensor field, etc., operable. Via second electrical connection, the control unit 468 is connected to the first
  • the first sensor unit 470 serves to monitor an operating state of the first actuating element 464 on the tool holder 316 of the machine tool according to the invention.
  • the first sensor unit 470 may comprise a mechanical touch sensor 470a - e.g. identify a button - or a non-contact motion sensor 470b.
  • the first sensor unit 470 is designed as a contactless motion sensor 470b, in particular as a Hall sensor 471.
  • a triggering ring 484 is provided in the first actuating element 464 designed as an actuating sleeve 464a.
  • the actuating sleeve 464a engages around a cylindrical end region 486 of the housing 312.
  • a sensor element 488 of the non-contact motion sensor 470b arranged such that the release ring 484 surrounds the sensor element 488 in a circumferential radial distance.
  • the sensor element 488 is designed as a Hall sensor 488a.
  • the release ring 484 is preferably made of a permanent magnetic material, so that an axial movement of the operation sleeve 464a and thus of the trigger ring 484 to the Hall sensor 488a generates a detectable Hall voltage as a sensor signal in the Hall sensor 488a.
  • the sensor signal is transmitted to the control unit 470, whereby the operating state of the first operating member 464 can be monitored.
  • the second embodiment corresponds to the first embodiment already described.
  • the operator can set the limit torque MG of the coupling device 344, 345 via the selector element 369.
  • the first sensor unit 470 accepts this actuation and reports it as a sensor signal to the control unit 468.
  • the sensor signal in the control unit 468 reverses from the energized state of the electromagnet 472 in the de-energized state, whereby the spool 396 of the coupling device 344, 345 is returned to the first control position SP1.
  • Sensor unit 470 act as means 322 'for resetting the coupling device 344, 345 in a lower, preferably the lowest possible limit torque.
  • the actuator unit 466 may be designed so that the return element 412 can be dispensed with.
  • the actuator 466 has in this case at least two stable switching states, between which can be switched over the control unit 468.
  • a second sensor unit 490 is provided.
  • the second sensor unit 490 monitors the switching position of the actuator unit 466 and / or the
  • the second sensor unit 490 is also with the control unit 470 electrically connected, so that the control unit 470 can evaluate the current switching state of the coupling device 344, 345 via a second sensor signal of the second sensor unit 490.
  • control unit 468 of the machine tool comprises a control logic for monitoring an availability of a supply voltage. If there is an interruption of the supply voltage, the control unit 468 causes a provision of the coupling device 344, 345 to the lowest possible limit torque.
  • the described functionality can be transmitted analogously to known machine tools with detachable, in particular exchangeable tool holders 316 '.
  • a further sensor unit 470 ' is provided in the exchangeable tool holder 316', which monitors an actuation of a second actuating element 164 'and communicates it in an analogous manner to the control unit 468.
  • a blocking device with reset device can be provided which makes at least one of the two coupling devices 44a, 44b blockable such that the coupling device 44a blocks with the lowest possible limit torque MGmin and the coupling device 44b is activated with the higher limit torque.
  • the reset device is operatively connected to the first actuating sleeve of the tool holder such that the blockage of the coupling device 44a is canceled with the lowest possible limit torque MGmin and this is effective again.
  • the idea of the invention can be transferred without restriction to a transmission device 20 with a single-stage, adjustable coupling device 44c with variable limit torque MGV, as are known inter alia from DE 101 30 520 A1.
  • a control mechanism is provided which makes the biasing force of the spring members 92c of the clutch mechanism 50c variable. The operation otherwise corresponds to the coupling device 44, 45 described above. If this control mechanism is so connected to one of the above-described actuators 1 18, 318 that
  • Operation of the first actuating element 164, 464 causes a reset to the lowest biasing force of the spring elements 92c, so this interaction corresponds to the claimed inventive idea.
  • the machine tool according to the invention has at least one optical, acoustic and / or haptic signal transmitter, which is activated when a torque value other than the lowest possible limit torque is applied to the coupling device 44, 45.
  • a display element may be provided on the machine tool according to the invention, which displays the currently selected limit torque visible to the operator.
  • Fig. 5 the invention-relevant steps of a method for operating a machine tool, in particular an electrically operable hand tool having at least one tool drive shaft for direct or indirect rotary drive an insert tool, in particular according to one of the embodiments described above, shown schematically in the process.
  • the reference numerals of the above-described examples with the same or equivalent features are increased by 300.
  • a demand for a modified limit torque MGW with respect to the coupling device 644, 645 provided between the drive unit 619 and the tool drive shaft 623 and coupling with one another occurs during a work process
  • the operator selects the desired limit torque MGW in a first step 791.
  • a corresponding actuating device 718 is provided on the machine tool according to the invention, which acts on the torque selector 697.
  • the torque selection device 697 sets the currently applied limit torque MGlst to the desired limit torque in a second process step 792 MGW. Examples of the actuator 718 and the torque selector 697 are described in the previous embodiments, to which reference is made at this point.
  • This sub-process can be used by the operator both to increase and to reduce the currently applied limit torque MGlst.
  • an additional subprocess 793 is triggered as soon as at least one corresponding process prerequisite is fulfilled.
  • a substep 794 the triggering of a removal, insertion and / or change of the insertion tool in the tool holder 616 of the machine tool is monitored as the first possible process requirement 794a.
  • such a sub-step 794 may be implemented as a monitoring of an actuation state of the first actuation element 764.
  • a tool holder of the tool holder 616 can be monitored directly for the presence of the insertion shaft 683 of the insert tool. If the aforementioned event occurs, then in a next sub-step 795 a reset of the
  • the coupling device 644, 645 may for this purpose be provided with a torque selector 697 which, in an initial position, sets the lowest possible limit torque MGM in the adjustable coupling device 644, 645.
  • a reset of the torque selector 697 is effected in its starting position in the partial step 795.
  • sub-step 795 is preceded by an additional checking step 796, which compares the currently selected limit torque MGlst with the lowest possible limit torque MGMin. Only in the event that MGlst is actually greater than MGMin will a reset be triggered after substep 795.
  • substep 794 comprises a second, alternative process requirement 794b.
  • a triggering of a change of an exchangeable tool holder 616 ' is monitored on the machine tool and initiated on the occurrence of an event 794b of the sub-step 795.
  • a second, alternative process requirement 794b is monitored on the machine tool and initiated on the occurrence of an event 794b of the sub-step 795.
  • Actuator 764b provided, the actuation state is monitored accordingly.
  • a further preferred development of the method according to the invention comprises an additional sub-process for monitoring the power supply of the machine tool. If a connection to a voltage source is achieved in sub-step 797, a monitoring unit 798 sends a corresponding signal. This signal will as process requirement 794c, analogous to the process prerequisites 794a, 794b described above, as the trigger for process step 793.
  • FIG. 6 shows a variant of the flowchart of FIG. 5.
  • the process requirements 794, 794a, 794b, 794c bring about a provision of the torque selector 97, 397, 697 in their starting position.
  • the torque selector 97, 397, 697 By the provision of the torque selector 97, 397, 697, a provision of the coupling device 44 is effected to the lowest possible limit torque.
  • a signal generator provided on the machine tool is activated when a limit torque MG.sub.Lst deviating from the lowest possible limit torque MGMin is applied.
  • the signal generator can be designed as optical, acoustic and / or haptic signal generator.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

L'invention concerne un procédé pour faire fonctionner une machine-outil, en particulier une machine-outil portative électrique, comprenant au moins un arbre d'entraînement d'outil (23, 323, 623) pour entraîner un outil en rotation directement ou indirectement. Ledit outil est logé dans un porte-outil relié à l'arbre d'entraînement d'outil (23, 323, 623), en particulier relié de manière amovible à la machine-outil. L'arbre d'entraînement d'outil (23, 323, 623) peut être accouplé à un dispositif d'entraînement (14, 314, 614) au moyen d'un dispositif d'embrayage (44, 44a, 44b, 44c, 45, 344, 345, 644, 645). Ce dispositif d'embrayage (44, 44a, 44b, 44c, 45, 344, 345, 644, 645) présente au moins deux couples limites différents, pouvant être sélectionnés de préférence par un opérateur. En cas de changement d'outil et/ou de changement de porte-outil, le couple limite du dispositif d'embrayage (44, 44a, 44b, 44c, 45, 344, 345, 644, 645) est ramené à une valeur réduite, de préférence à la valeur minimale.
EP08874778.7A 2008-06-24 2008-11-27 Procédé pour faire fonctionner une machine-outil pourvue d'un dispositif d'embrayage Not-in-force EP2303514B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810002594 DE102008002594A1 (de) 2008-06-24 2008-06-24 Verfahren zum Betrieb einer Werkzeugmaschine mit Kupplungsvorrichtung
PCT/EP2008/066318 WO2009156005A1 (fr) 2008-06-24 2008-11-27 Procédé pour faire fonctionner une machine-outil pourvue d'un dispositif d'embrayage

Publications (2)

Publication Number Publication Date
EP2303514A1 true EP2303514A1 (fr) 2011-04-06
EP2303514B1 EP2303514B1 (fr) 2016-06-01

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EP08874778.7A Not-in-force EP2303514B1 (fr) 2008-06-24 2008-11-27 Procédé pour faire fonctionner une machine-outil pourvue d'un dispositif d'embrayage

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Country Link
US (1) US8905153B2 (fr)
EP (1) EP2303514B1 (fr)
CN (1) CN102076465A (fr)
DE (1) DE102008002594A1 (fr)
RU (1) RU2011101775A (fr)
WO (1) WO2009156005A1 (fr)

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Also Published As

Publication number Publication date
WO2009156005A1 (fr) 2009-12-30
EP2303514B1 (fr) 2016-06-01
DE102008002594A1 (de) 2009-12-31
CN102076465A (zh) 2011-05-25
RU2011101775A (ru) 2012-07-27
US8905153B2 (en) 2014-12-09
US20110139471A1 (en) 2011-06-16

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