EP2653269A2 - Machine-outil - Google Patents

Machine-outil Download PDF

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Publication number
EP2653269A2
EP2653269A2 EP13163866.0A EP13163866A EP2653269A2 EP 2653269 A2 EP2653269 A2 EP 2653269A2 EP 13163866 A EP13163866 A EP 13163866A EP 2653269 A2 EP2653269 A2 EP 2653269A2
Authority
EP
European Patent Office
Prior art keywords
exciter
tool
dead center
pneumatic chamber
hand tool
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Withdrawn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
EP13163866.0A
Other languages
German (de)
English (en)
Other versions
EP2653269A3 (fr
Inventor
Markus Hartmann
Eduard Pfeiffer
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.)
Hilti AG
Original Assignee
Hilti AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hilti AG filed Critical Hilti AG
Publication of EP2653269A2 publication Critical patent/EP2653269A2/fr
Publication of EP2653269A3 publication Critical patent/EP2653269A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • B25D17/24—Damping the reaction force
    • B25D17/245—Damping the reaction force using a fluid
    • 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
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • 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
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/06—Means for driving the impulse member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0019—Guide-sleeves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0023—Pistons
    • 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
    • B25D2250/185—Pressure equalising means between sealed chambers
    • 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
    • B25D2250/345—Use of o-rings

Definitions

  • the present invention relates to a hand-held or hand-held machine tool containing a pneumatic impact mechanism, e.g. an electric hammer drill, an electric chisel hammer.
  • a pneumatic impact mechanism e.g. an electric hammer drill, an electric chisel hammer.
  • the hammer drill has a racket that is energized by an engine-driven piston via an intermediate pneumatic chamber.
  • the efficiency and the efficiency of the hammer drill should be increased by a centrifugal compressor.
  • the precompressed air from the centrifugal compressor flows through a concealable from the impactor body openings in the pneumatic chamber.
  • the centrifugal compressor increases the air pressure in the pneumatic chamber just at the time or during the period that causes optimum acceleration of the racket.
  • the bat receives an additional boost just before the impact on an anvil to increase the impact energy.
  • the user must apply a holding force when energy is transferred to the racket.
  • the transmission occurs periodically with the beat frequency of typically 10 Hz to 100 Hz of the power tool, which is why the user perceives the holding force as vibrations.
  • the vibrations should remain low for physiological reasons. Therefore, the impact energy can not be arbitrarily increased.
  • the hand tool of the invention has a tool holder for holding a chiseling tool on a working axis.
  • a pneumatic percussion mechanism has a movable racket on the working axis, a pathogen and a pneumatic chamber, which is closed by the pathogen and the racket and couples the movement of the pathogen to the racket.
  • the exciter is driven by a motor and moves back and forth between a tool-distant front dead center and a tool-near dead center.
  • a damping device includes a supercharger and a controlled one Exhaust valve. The controlled exhaust valve allows air from the supercharger to flow into the pneumatic chamber when the exciter is near the tool-remote dead center.
  • the pneumatic chamber forms a so-called air spring, which transmits forces between the pathogen and the bat.
  • the coupling strength decreases faster than linearly with the distance between the pathogen and the bat. Therefore, there is a short period of time in which the pathogen transmits the energy for the next stroke on the racket. The transmission occurs when the pathogen is half way between its dead centers.
  • the present hand tool machine increases the pressure even before the bat comes close to the pathogen, i. before the pathogen has covered half the distance between its dead centers. There, the pathogen has the highest speed and can transmit energy with the utmost efficiency. With the increased pressure, the coupling strength increases. The pathogen can thus transfer a significant amount of energy to the bat earlier. Ergo the time span for the energy transfer increases and the peak forces that occur in the process decrease.
  • a distance of the exciter to its tool-remote dead center is preferably less than 5% of the stroke of the exciter when the controlled outlet valve allows air to flow from the supercharger into the pneumatic chamber. It should be noted in particular that the pressure built up by the compressor slows down the racket. If this happens too soon or too strongly, the bat can no longer reach the pathogen when the latter is moving at its maximum speed.
  • the supercharger includes a pumping device.
  • the pumping device may be a pumping device operated independently of the hammer mechanism or a pumping device mechanically coupled to the striking mechanism.
  • the exciter can form a pump piston of the pumping device. A surface of the exciter facing away from the direction of impact closes off a compression space of the pump device and thus compresses / decompresses the compression space by its movement.
  • One embodiment may include a pot-shaped guide tube.
  • the pneumatic chamber, the exciter and the compression chamber of the pumping device are arranged on the working axis.
  • a bottom closes the compression space in the guide tube against the direction of impact.
  • An embodiment may comprise a piston rod which couples the exciter with an eccentric or a wobble drive.
  • the piston rod is guided through the floor.
  • An embodiment may comprise a guide tube, in which the exciter is guided airtight.
  • the guide tube has at least one recess in its inner surface near the tool-distant. Between the pneumatic chamber and the compressor, a channel is formed when the exciter takes the depression opposite position.
  • One embodiment has a check valve in the pathogen.
  • One embodiment has a valve that connects the pneumatic chamber to a pumping chamber when the exciter is near the tool-near dead center.
  • a pumping device lowers a pressure below the level of an ambient pressure in the pumping space until the exciter reaches the tool-near dead center.
  • the pump chamber can be completed in the direction of impact by the movable exciter.
  • a control method for the portable power tool is based on the step of increasing an air pressure in the pneumatic chamber by means of a supercharger when the exciter is in the vicinity of the tool-remote dead center.
  • the air pressure in the pneumatic chamber thus increases faster than is done solely by approaching the racket to the pathogen.
  • an air pressure in the pneumatic chamber may be lowered by means of a pumping device when the exciter is near the tool-near dead center. The air pressure thus falls faster than is done solely by removing the exciter from the racket.
  • Fig. 1 schematically shows a hammer drill 1 as an example of a chiseling hand tool.
  • the hammer drill 1 has a tool holder 2 , in which a shank end 3 of a chiseling tool, for example one of the drill bit 4 , can be used.
  • a primary drive of the hammer drill 1 is a motor 5 , which drives a striking mechanism 6 and an output shaft 7 .
  • a user can guide the hammer drill 1 by means of a handle 8 and take means of a system switch 9, the hammer drill 1 is in operation.
  • the hammer drill 1 In operation, the hammer drill 1, the drill bit 4 rotate continuously about a working axis 10 and can beat the drill bit 4 in the direction of impact 11 along the working axis 10 in a substrate.
  • the striking mechanism 6 is a pneumatic impact mechanism 6 .
  • An exciter 12 and a racket 13 are movably guided in the striking mechanism 6 along the working axis 10 .
  • the exciter 12 is coupled via an eccentric 14 or a wobble finger to the motor 5 and forced to a periodic, linear movement.
  • An air spring formed by a pneumatic chamber 15 between exciter 12 and racket 13 couples a movement of the racket 13 to the movement of the exciter 12 at.
  • the bat 13 can strike directly on a rear end of the drill bit 4 or indirectly transfer part of its pulse to the drill bit 4 via a substantially resting striker 16 .
  • the racket 13 and the exciter 12 may be formed, for example, as a piston, which are arranged in a guide tube 17 .
  • the striking mechanism 6 and preferably the further drive components are arranged within a machine housing 18 .
  • Fig. 2 shows in more detail in a longitudinal section the pneumatic percussion 6 and a supercharger 19th
  • the racket 13 is for example a cylindrical piston, which is also guided along the working axis 10 in the guide tube 17 .
  • a directed against the direction of impact 11 end face 20 of the racket 13 forms a further movable side wall of the pneumatic chamber 21st
  • a diameter of the racket 13 corresponds to the Inner diameter of the guide tube 17th
  • a bumper 13 spanning sealing ring 22 supports the airtight seal.
  • the exciter 12 is, for example, a cylindrical piston which is guided along the working axis 10 in a guide tube 17 .
  • a pointing in the direction of impact 11 end face 23 of the exciter 12 forms a movable side wall of the pneumatic chamber 15th
  • a diameter of the exciter 12 is equal to an inner diameter of the guide tube 17th
  • a lateral surface 24 of the exciter 12 closes airtight with the guide tube 17 from.
  • a sealing ring 25 supports the airtight completion of the pneumatic chamber 15th
  • the pneumatic chamber 15 is thus closed against the impact direction 11 by the exciter 12 , in the direction of impact 11 by the racket 13 and in the radial direction by the guide tube 17 .
  • the exciter 12 is mechanically driven by the motor 5 .
  • An eccentric wheel 14 driven by the motor 5 forces the exciter 12 to periodically reciprocate between a tool-remote dead center (FIG. Fig. 3 ) and a tool-near dead center.
  • a pin 26 of the eccentric 14 engages in a direction perpendicular to the axis of rotation of the eccentric wheel 14 and perpendicular to the working axis 10 extending gate 27th
  • the gate 27 is inserted along the working axis 10 guided piston rod 28 .
  • the piston rod 28 is rigidly connected to the exciter 12 .
  • the guide tube 17 is hermetically sealed to a bottom 29 at its tool-distal end.
  • the bottom 29 is arranged with respect to the racket 13 on the opposite side of the exciter 12 .
  • the bottom 29 has an exciter 12 facing bottom surface 30 , which is preferably flat.
  • a bottom 29 facing the end face 31 of the exciter 12 is preferably flat.
  • the guide tube 17 is circumferentially closed about the working axis 10 between the bottom 29 and the exciter 12 , whereby a second pneumatic chamber 21 is formed.
  • the second pneumatic chamber 21 is the compression space 21 of a supercharger 19.
  • the positively driven exciter 12 cyclically compresses the air within the compression space 21 .
  • the fully compressed volume, ie at exciter 12 at tool-remote dead center (FIG. Fig. 3 ), is between 10% and 20% of the maximum volume, ie at the exciter 12 at the tool-near dead center ( Fig. 4 ).
  • the supercharger 19 is connected via an outlet valve 32 with the pneumatic chamber 15 of the impact mechanism 6 .
  • the exemplary exhaust valve 32 opens by means of a Control edge, which is inserted as, for example, annular recess 38 in the inner wall 33 of the guide tube 17 .
  • the radial seal of the exciter 12 with the inner wall 33 of the guide tube 17 is interrupted by the recess 34 .
  • the recess 34 is so deep that the sealing ring 25 does not touch the guide tube 17 in the region of the recess 34 .
  • the sealing ring 25 closes the groove 35 along the working axis 10th
  • the valve 36 is opened when the sealing ring 25 is at the axial height with the recess 34 .
  • the air may pass between the radially outer surface of the sealing ring 25 and the surface of the recess 34 .
  • the exciter 12 preferably has in its lateral surface 37 at least one along the working axis 10 extending groove 35 which is open at both opposite end faces 23 , 31 . The air can flow in the groove 35, the sealing ring 25 .
  • the outlet valve 32 or the recess 38 is positioned such that the outlet valve 32 opens at the tool-remote dead center of the exciter 12 ( Fig. 3 ).
  • the outlet valve 32 preferably opens, at the earliest when the exciter 12 approaches the tool-distant dead center up to 5% of its stroke.
  • the exhaust valve 32 closes at the latest when the exciter 12 is further than 5% of its stroke from the tool-remote dead center. While the outlet valve 32 is opened and the supercharger 21 increases the pressure in the pneumatic chamber 21 , the racket 13 moves counter to the direction of impact 11 .
  • the exhaust valve 32 is closed clearly before the racket 13 reaches its tool-far turning point.
  • the coupling of the racket 13 to the exciter 12 for transmitting energy increases with increasing air pressure. Due to the pre-compressed air, the coupling starts earlier, which extends the energy transfer to a longer period of time. The necessary holding force of the user decreases.
  • An inlet valve 36 may connect the supercharger 21 to the pneumatic chamber 21 .
  • the exemplary intake valve 36 is based on a control edge formed by an annular recess 38 in the guide tube 17 .
  • the sealing ring 25 in the exciter 12 forms the associated closure element. As soon as the sealing ring 25 is at the axial height with the recess 38 , the inlet valve 36 opens.
  • the inlet valve 36 or the recess 38 is positioned such that it opens with the exciter 12 close to the tool-near dead center ( Fig. 4 ).
  • the inlet valve 36 opens when the distance of the exciter 12 to its tool near dead center is less than 3% of its stroke.
  • the opening of the second valve 36 preferably coincides with the impact of the racket 13 on the striker 16 or is somewhat delayed to the impact.
  • the air pressure in the pneumatic chamber 21 is greater than in the compression space 21 ; Air flows from the pneumatic chamber 21 into the compression space 21 .
  • the drop in pressure causes acceleration of the racket 13 against the direction of impact 11th This can do that Braking of the racket 13 due to the above-described increased air pressure after opening the first valve 34 are partially compensated.
  • the bottom 29 is provided on the working axis 10 with a passage 39 for the piston rod 28 .
  • a sealing ring 40 ensures an airtight completion of the implementation 39 .
  • Fig. 5 illustrates a variant of the exhaust valve 41 for the supercharger 21 .
  • the outlet valve 41 is a pressure-controlled non-return valve 42 .
  • the outlet valve 41 may be used, for example, in the exciter 12 .
  • a channel 43 connects the opposite end faces 23 , 31 of the exciter 12 .
  • the exemplary channel 43 is, for example, a groove 35 in the lateral surface 37 of the exciter 12 .
  • the check valve 42 is preferably under pretension and closes the channel 43 in the basic position.
  • the check valve 42 may be made of rubber, for example.
  • the exhaust valve 41 opens when a pressure in the compression space 21 exceeds the pressure in the pneumatic chamber 21 by at least a threshold value.
  • the threshold is, for example, 1 bar.
  • a corresponding pressure difference results when the exciter 12 approaches the tool-far dead center.
  • the exhaust valve 32 closes well before the club 13 reaches its tool-far turning point.
  • Fig. 6 illustrates a variant of the percussion mechanism 6 , which is exemplified on the illustration of Fig. 2 based.
  • the supercharger 19 is provided with a larger volume.
  • the compression space 21 is expanded by a pump reservoir 44 .
  • the pump reservoir 44 is formed, for example, by a closed shell 45 around the impact mechanism 6 .
  • the volume of the pump reservoir 44 is preferably greater than the volume of the air spring 15 , for example between twice and five times the volume.
  • the volume of the air spring 15 is defined as the volume when the bat 13 abuts the striker 16 and the exciter 12 in the dead center near the tool ( Fig. 3 ).
  • the pump reservoir 44 may be formed as a closed volume next to the impact mechanism 6 .
  • the pump storage 44 is charged by a pump 46 .
  • the pump 46 is, for example, a diaphragm pump.
  • the pump 46 may be driven electrically or with its own drive or by means of the motor 5 of the hammer drill 1 .
  • the pump 46 is continuously active and delivers air into the pump reservoir 44 .
  • a regulation 47 with an air pressure sensor 48 can advantageously limit the pumping capacity of the pump 46 in such a way that a constant desired pressure is established in the pumped storage 44 .
  • the setpoint pressure is measured on the maximum air pressure in the compressed air spring 15 , for example, the target pressure is in the range between 20% and 50% of the maximum air pressure. Typically, the air pressure in the air spring reaches a maximum value between 10 bar and 20 bar.
  • An opening 49 in the compression space 21 connects it to the pump reservoir 44 .
  • a check valve 50 at the opening 49 prevents backflow of air from the space 21 into the pump reservoir 44th In the compression chamber 21 can until the exciter 12 reaches the tool-distant dead center, build a higher pressure against the pump reservoir 44 .
  • the exhaust valve 32 formed in the exciter 12 controls the inflow of air from the pump reservoir 44 into the pneumatic chamber 15 of the air spring.
  • the opening 51 to the pump reservoir 44 may alternatively or additionally be provided in the guide tube 17 .
  • the opening 51 is preferably between the position of the exciter 12 in its dead center near the tool and its tool-distal dead center (FIG. Fig. 7 ).
  • the exciter 12 itself forms the closure body for a valve which closes or opens the opening with respect to the pneumatic chamber.
  • the distance to the tool-remote dead center is, for example, in the range between 3% and 5% of the stroke of the exciter 12 .
  • a valve 52 can also be driven electrically or magnetically.
  • the control of the valve 52 may be based on a position of the exciter 12 in the pneumatic chamber 21 .
  • the valve 52 is opened when the exciter 12 is near the tool-far dead center, ie, at a distance of 3% to 5% of the stroke.
  • the valve 52 may also open only after the exciter 12 has exceeded the tool-distant dead center.
  • the valve 52 is closed after the distance to the tool remote dead center exceeds 3% to 5% of the stroke.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Apparatus For Disinfection Or Sterilisation (AREA)
EP13163866.0A 2012-04-19 2013-04-16 Machine-outil Withdrawn EP2653269A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012206445A DE102012206445A1 (de) 2012-04-19 2012-04-19 Werkzeugmaschine

Publications (2)

Publication Number Publication Date
EP2653269A2 true EP2653269A2 (fr) 2013-10-23
EP2653269A3 EP2653269A3 (fr) 2017-01-04

Family

ID=48184025

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13163866.0A Withdrawn EP2653269A3 (fr) 2012-04-19 2013-04-16 Machine-outil

Country Status (5)

Country Link
US (1) US20130277077A1 (fr)
EP (1) EP2653269A3 (fr)
JP (1) JP2013223916A (fr)
CN (1) CN103372851B (fr)
DE (1) DE102012206445A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2871028A1 (fr) * 2013-11-11 2015-05-13 HILTI Aktiengesellschaft Machine-outil manuelle

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DE102012206452A1 (de) * 2012-04-19 2013-10-24 Hilti Aktiengesellschaft Handwerkzeugmaschine und Steuerungsverfahren
JP5487266B2 (ja) * 2012-09-26 2014-05-07 株式会社エーコー 騒音低減型地下穿孔用のハンマードリル
EP3000560A1 (fr) * 2014-09-25 2016-03-30 HILTI Aktiengesellschaft Appareil d'enfoncement à ressort à gaz
EP3181298A1 (fr) * 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil a percussion
EP3260239A1 (fr) * 2016-06-24 2017-12-27 HILTI Aktiengesellschaft Machine-outil portative

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2871028A1 (fr) * 2013-11-11 2015-05-13 HILTI Aktiengesellschaft Machine-outil manuelle
WO2015067590A1 (fr) * 2013-11-11 2015-05-14 Hilti Aktiengesellschaft Machine-outil à main

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CN103372851B (zh) 2016-07-27
DE102012206445A1 (de) 2013-10-24
JP2013223916A (ja) 2013-10-31
US20130277077A1 (en) 2013-10-24
EP2653269A3 (fr) 2017-01-04
CN103372851A (zh) 2013-10-30

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