EP2213421A1 - Mécanisme de percussion pneumatique et procédé de commande - Google Patents

Mécanisme de percussion pneumatique et procédé de commande Download PDF

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Publication number
EP2213421A1
EP2213421A1 EP20090179000 EP09179000A EP2213421A1 EP 2213421 A1 EP2213421 A1 EP 2213421A1 EP 20090179000 EP20090179000 EP 20090179000 EP 09179000 A EP09179000 A EP 09179000A EP 2213421 A1 EP2213421 A1 EP 2213421A1
Authority
EP
European Patent Office
Prior art keywords
piston
flying
pneumatic
striking
excitation
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
EP20090179000
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German (de)
English (en)
Other versions
EP2213421B1 (fr
Inventor
Alexander John
Reinhard Schulz
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
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Application filed by Hilti AG filed Critical Hilti AG
Publication of EP2213421A1 publication Critical patent/EP2213421A1/fr
Application granted granted Critical
Publication of EP2213421B1 publication Critical patent/EP2213421B1/fr
Revoked legal-status Critical Current
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • 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
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Definitions

  • the present invention relates to a pneumatic striking mechanism, in particular an electrically driven, pneumatic impact mechanism, for a machine tool, in particular a hand tool, e.g. a chisel hammer. Furthermore, the present invention relates to a control method for a pneumatic percussion.
  • An electrically driven chisel hammer with a pneumatic impact mechanism is among others from the EP 1 779 980 A2 known, the schematic representation of the percussion 501 from Fig. 6 is in Fig. 1 accepted.
  • a flying piston 569 is arranged between an excitation piston 520 and an end piece of a tool 599.
  • the flying piston 569 and the excitation piston 520 close airtight with a wall of the guide tube, so that an airtight closed space 580 between the flying piston 569 and the excitation piston 520 is formed.
  • the space 580 is hereinafter referred to as the pneumatic space 580.
  • the excitation piston 520 driven by an eccentric drive 522, 523, 531, periodically moves in the guide tube 530 back and forth. Due to its coupling to the excitation piston 520 by means of the pneumatic space 580, the flying mass 569 is likewise excited to a periodic movement between the excitation piston 520 and the end piece of the tool 599.
  • Fig. 2 shows schematically the course of the movement of exciter piston 520 and free piston 580 over the time t; the course is inter alia in Fig. 13A of EP 1 779 980 A2 shown.
  • the location axis x indicates the distance to the end piece of the tool 599.
  • the flying mass 569 reverses its direction of motion and moves at reduced speed towards the excitation piston 520.
  • the stroke H of the excitation piston 520, the angular velocity of the exciter piston 520, and the maximum length a of the pneumatic space 580 are matched to one another such that the movement of the flying piston 569, as shown, is excited resonantly by the excitation piston 520.
  • the hammering effect of the chisel hammer essentially results from the energy released in a workpiece during a blow.
  • the power consumption results from the product of the energy delivered per beat and the beat frequency of the beats. Consequently, the beat frequency of the beats must be lowered.
  • the energy released per impact depends on the kinetic energy that 569 receives up to the collision.
  • the acceleration work is done by the exciter pistons 520, which increases with increasing velocity of the exciter piston 520 in the guide tube 530.
  • the speed of the excitation piston 520 is determined by the angular velocity and the stroke H of the exciter piston 520.
  • increasing the angular velocity is not suitable due to the thus increasing impact frequency of the impacts, the stroke H of the excitation piston 520 can be increased. However, this requires a greater maximum length a of the pneumatic space 580 and thus a longer impact mechanism to ensure a resonant excitation of the flying piston 569.
  • the kinetic energy of the air piston 569 can also be achieved by increasing its mass, but then an operator experiences a higher kickback when accelerating the air piston 569 by the exciter piston 520.
  • One object is to provide a beating machine tool that allows for improved impact performance while taking ergonomic considerations into account.
  • the percussion mechanism has: a flying piston which is movable along a striking axis; a striking surface which limits movement of the flying piston along the striking axis in the direction of impact; an excitation piston limiting movement of the flying piston along the striking axis opposite to the direction of impact; a pneumatic space between the air piston and the excitation piston; a drive for periodically moving the excitation piston with a stroke along the striking axis, whereby the flying piston is excited to a periodic movement between the striking surface and exciter piston.
  • the stroke is selected as a function of a maximum length of the pneumatic space such that the periodic movement of the flying piston on the way between a strike on the striking surface and a minimum approach to the excitation piston has in the meantime a speed of zero.
  • the maximum length of the pneumatic space is the distance of the excitation piston to the flying mass when the exciter piston is in its position remote from the tool holder and the flying mass is arranged adjacent to the striking surface.
  • the maximum length serves as a size for laying out and characterizing the impact mechanism.
  • the pneumatic space usually takes at no time the maximum length.
  • Circulation of the flying bucket in the striking mechanism is composed of a first phase with a movement from the minimum approach to the exciting piston to the beat and a second phase with a movement from the striking position to the next minimum approach to the exciting piston.
  • the first phase and the second phase are completed together within a period of time dictated by the period of movement of the exciter piston. Due to the deceleration of the flying piston until the momentary standstill, the duration of the second phase increases at the expense of the duration of the first phase.
  • the flying piston manages the distance between minimum approach and the stroke in a shorter time, ergo, as desired, with a higher speed.
  • the deceleration of the air piston during the second phase takes place when the dimensions of stroke and maximum length of the pneumatic space are suitably selected.
  • the pneumatic space is compressed, since the excitation piston still moves in the direction of impact after the impact or the flying mass initially moves at a greater speed counter to the direction of impact than the exciter piston. This results in a pressure increase in the pneumatic space, which slows down the flying mass.
  • the pressure increase is greater, the smaller the volume of the pneumatic space or the greater the remaining stroke movement of the excitation piston in the direction of clubface.
  • intermittent stoppage can be designed by reducing the maximum length or increasing the stroke and maintaining other known parameters of a known percussion mechanism.
  • the stoppage of the flying piston is only temporary. Typically, a force due to positive or negative pressure in the pneumatic space acts on the flying mass. If the pressure in the pneumatic space corresponds to the ambient pressure, the movement of the excitation piston leads to an increase or a decrease in the pressure, which is accelerated as a result of the flying pistons.
  • the striking mechanism has: a flying piston which is movable along a striking axis; a striking surface which limits movement of the flying piston along the striking axis in the direction of impact; an excitation piston limiting movement of the flying piston along the striking axis opposite to the direction of impact; a pneumatic space between the air piston and the excitation piston; a drive for periodically moving the excitation piston with a stroke along the striking axis, whereby the flying piston is excited to a periodic movement between the striking surface and exciter piston.
  • the control method sets a repetition rate of the periodic motion in response to a maximum length of the pneumatic space such that the periodic movement of the flying piston on the way between a strike on the striking surface and a minimum approach to the exciting piston has a zero speed in the meantime.
  • One embodiment provides that the stroke is selected in dependence on the maximum length of the pneumatic space such that the flying piston changes the direction of movement at least once during the movement between the striking surface and a following minimum approach to the exciter piston.
  • a change in the direction of movement during the second phase results in a longer path traveled by the flying piston during one revolution.
  • the velocity of the flying piston during the first phase is higher, also taking into account the boundary condition of the given period of time for one revolution.
  • An embodiment provides that the stroke is selected in dependence on the maximum length of the pneumatic space such that the flying piston touches the striking surface at least twice between two successive minimum approaches to the excitation piston.
  • the reversal of the direction of movement by the second impact leads to a high velocity of the flying mass at the end of the second phase.
  • the flying piston can therefore approach the exciter piston strongly and experiences a higher acceleration in the direction of the striking surface due to the pneumatic space thereafter.
  • Fig. 3 shows schematically as an example of a striking hand tool an electro-pneumatic chisel hammer 1, other examples not shown are, inter alia, rotary hammers, combi hammers.
  • a drive train with a primary drive 3, a drive shaft 4 and a striking mechanism 5 is arranged. Between the primary drive 3 and the drive shaft 4, a transmission 7 may be connected.
  • the primary drive 3 is preferably an electric motor, for example a universal motor or a brushless motor.
  • the drive shaft 4 is rotated at speeds in the range between 1 Hz and 100 Hz, for example at 10 Hz to 60 Hz.
  • the rotational movement of the drive shaft 4 is transmitted by the striking mechanism 5 in a periodic impact movement along a striking axis 8.
  • a held in a tool holder 9 tool is driven out of the chisel hammer 1 by the periodic beats along the striking axis 8 in the direction of impact 99 out.
  • a return of the tool in the chisel hammer 1 against the direction of impact 99 is effected by pressing the chisel hammer 1 to a workpiece.
  • Fig. 4 shows an exemplary construction of the striking mechanism. 5
  • the striking mechanism 5 has an excitation piston 12 and a flying piston 13 which are movable along the striking axis 8.
  • the excitation piston 12 and the flying piston are guided through a wall 11 of a guide tube 10.
  • a striker 20 is mounted in an anvil guide 21.
  • a tool-facing end 22 is in contact with a tool 8 which is held in the tool holder 9.
  • a tool-facing end 23 of the striker 20 protrudes from the anvil guide 21 in the interior of the guide tube 10. In the beating operation of the striker 20 abuts a tool facing away from the end 24 of the striker guide 21. In this position, the tool facing away from end 23 of the striker 20 defines the position of the striking surface 27 of the impact mechanism. 5
  • the striker 20 may be provided as an intermediary between the flying mass 13 and a tool 8 in the impact mechanism 5. This allows in particular a design of the impact mechanism 5, which is independent of a mass of the tool 8 used.
  • the striker 20 can be chosen much heavier than the typical mass of the tool 8 for this purpose.
  • no striker 20 is provided.
  • the flying mass 13 strikes directly on an end face of the tool 8.
  • the end face forms the striking surface 27 in this case.
  • the tool 8 is engaged in the tool holder 9 as far as possible in the direction of the impact mechanism 5. In this position, the tool 8 defines the clubface.
  • the exciter piston 12 is forced by the drive shaft 4 to a periodic movement along the striking axis 14.
  • the drive shaft 4 is rotated about its axis of rotation 30 and thereby moves an axis of rotation 30 eccentrically arranged wobble finger 31.
  • the wobble finger 31 is connected via a linkage 32 with the exciter piston 12.
  • a stroke H of the exciter piston 12 is defined as the distance between the two positions in which the excitation piston 12 of the striking surface 27 is closest to or farthest away.
  • the stroke H of the excitation piston 12 is predetermined by the distance 33 of the wobble finger 31 from the rotation axis 30 and corresponds approximately to twice the crank radius 33 of the wobble finger 31.
  • the movement of the exciter piston 12 is periodic and depending on the design of the eccentric drive 4, the movement is sinusoidal or, to a good approximation, sinusoidal.
  • the excitation piston 12 and the flying mass 13 define an air-tightly sealed space between them, the pneumatic space 19.
  • a cross-sectional area A of the pneumatic space 19 corresponds approximately to a cross-sectional area of the flying piston 13 and the excitation piston 12.
  • An airtight termination may e.g. be achieved by sealing rings 15, 16.
  • the pneumatic space 19 has a maximum length L when the excitation piston 12 is at the maximum distance to the impact surface 27 and the flying mass 13 is adjacent to the impact surface 27.
  • a simple model of the trajectory of the flying piston 13 is explained below with reference to a conventional impact mechanism and a striking mechanism 5 according to one embodiment.
  • the model is used to find parameters of the percussion mechanism 5, in which the flying mass 13 between a blow to the striking surface 27 and a next minimum distance to the excitation piston 12 is braked to at least standstill or even changes its direction of movement.
  • Fig. 5 shows a trajectory 100 of the flying piston 13 for a conventional, long impact mechanism, plotted over the time t.
  • the trajectory 100 is determined by means of an ad-initio simulation.
  • the trajectory 101 of the excitation piston 12 is also shown.
  • the trajectory 100 of the long impact mechanism can be subdivided into two phases 102, 103 limited by reversal points 104, 105 of the trajectory 100.
  • the first reversal point 104 results at the minimum distance of the flying piston 13 to the exciting piston 12.
  • the second turning point 105 results from the impact of the flying piston 13 on the striking surface 27.
  • the trajectory in the region of the first reversing point 104 can be described by a collision of the flying piston 13 on the moving exciter piston 12.
  • the effective mass of the excitation piston 12 is assumed to be infinite, because the exciter piston 12 is rigidly coupled to the drive.
  • the first reversal point 104 coincides with the maximum velocity of the exciter piston 12.
  • the amount of speed v 2 of the flying piston 13 after the impact is less than the speed v 1 before the shock, since a part of the kinetic energy of the flying piston 12 in the striker 20th is transmitted.
  • the form factor e has values from 0 to 1; for short stocky partners in the vicinity of 1 and more elongated Stospartner in the vicinity of 0.
  • Exemplary values for the impact number k are in the range of 0.05 to 0.35.
  • the impact number (q) may be chosen to be 0.22 if a ratio m 1 / m 2 of the mass (m 1 ) of the striker to the mass (m 2 ) of the flying mass (13) is greater than 1.2, and otherwise the number of impacts (q) should be 0.12.
  • the volume V of the pneumatic space 19 changes.
  • the pressure p within the pneumatic space 19 also changes.
  • a force on the flying mass 13 results due to the pressure difference of the surroundings (approx bar) and the pressure p within the pneumatic space 19.
  • the flying piston 13 thus also experiences an acceleration between the two reversal points 104, 105, which increases or decreases its velocity v 1 v 2 .
  • the volume of the pneumatic space 2 in the first and second phases 102, 103 changes only slightly compared to the neutral volume V 0 . This is partly due to the, compared to the maximum length L, low stroke H. Correspondingly, there are only minimal deviations from the ambient pressure p 0 and low forces on the flying mass 13. The influence of the pneumatic space 19 on the movement of the flying mass 13 in the long impact mechanism is negligible.
  • the velocity v 1 remains approximately constant during the first phase 102 and the velocity v 2 during the second phase 103.
  • the trajectory 200 likewise has the two reversal points 204, 205, which result from a minimal approach to the exciter piston 13 and a subsequent impact on the striking surface 27.
  • the flying mass 13 moves from the first turning point 204 to the second turning point 205, similarly to a long striking mechanism.
  • v 3 is the velocity shortly before the first reversal point 204.
  • the second phase 203 of the short impact mechanism 5 differs from the second phase 103 of the long impact mechanism.
  • the velocity of the flying mass 13 is reduced to zero, in the illustrated example the movement of the flying mass 13 even reverses.
  • the driving force for the braking results from the strong coupling of the flying piston 13 to the exciting piston 12 by means of the pneumatic space 19.
  • parameters of the percussion mechanism 5 are estimated, in which the speed v 2 of the flying piston 13 is braked to at least zero after the second reversal point 205.
  • the decelerating force results from the overpressure ( p - p 0 ) of the pneumatic space 19 with respect to the environment, which acts on the cross-sectional area A of the pneumatic space 19. Due to the movement of the flying piston 13 in the direction of the excitation piston 12, the volume V of the pneumatic chamber 19 also decreases and, correspondingly, the overpressure ( p - p 0 ) increases.
  • T 1 ⁇ 4 f -1
  • the excitation piston 12 moves slowly.
  • a change in the pressure p in the pneumatic Room 19 is dominated during the period T by the movement of the flying piston 13.
  • the excitation piston 12 reaches a speed which is significantly greater than the speed v 2 of the flying piston 13.
  • the relative distance increases rapidly and is soon greater than 1 ⁇ 2 L , which is why the flying mass 13 is accelerated again in the direction of the exciter piston 12.
  • the flying mass 13 stops when the integral of the decelerating force over the time period T corresponds to the momentum of the flying mass 13, ie v 2 ⁇ m 2 , after the second turning point 204: v 2 ⁇ m 2 ⁇ ⁇ ! ⁇ 0 T A ⁇ p 0 ⁇ V 0 / V ⁇ - 1 d t ,
  • T ( N f ) -1 : L ⁇ 2 ⁇ L - H ⁇ ⁇ ⁇ L - H + L ⁇ 2 ⁇ L - H ⁇ - 1 ⁇ 1 - q q ⁇ N 2 ⁇ ⁇ H ⁇ ⁇ ! ⁇ m 2 A ⁇ p 0 ⁇ N 2 ⁇ f 2 , It can be seen from the inequality that increasing the cross-sectional area A, stroke H and / or decreasing the mass m 2 of the flying mass 13, the maximum length L of the pneumatic space 19, the beat frequency f tends to result in a striking mechanism 5, in which the movement of the flying piston 13 is braked to a standstill.
  • the flying mass 12 takes about a period of time from 1 ⁇ 8 f -1 to 1 ⁇ 4 f -1 for its movement to the striking surface 27.
  • the braking can take place within a period of time from 1 ⁇ 8 f -1 to 1 ⁇ 4 f -1 , for which reason N is at least 4, preferably 6 or 8.
  • N is at least 4, preferably 6 or 8.
  • the parameters of the impact mechanism 5 can be determined according to the above inequality with the selected N.
  • the parameters of the percussion mechanism 5 are selected such that the flying mass 13 in the percussion mechanism 5 after the second reversal point 205 again touches the striking surface 27 (point 206) before the flying mass 13 flies up to the first reversal point 204.
  • the extension of the trajectory of the flying piston 13 allows a higher speed while maintaining the beat frequency f.
  • the impact mechanism 5 can be designed according to the above inequality, wherein N is greater than 5, preferably greater than 8 or 10 is selected.
  • the parameter N may be chosen to be greater than 8 for the two times hitting during one revolution of the flying piston.
  • FIGS. 7 to 9 show further embodiments.
  • the for the interpretation of the percussion of Fig. 4 The above rules can also be applied to these percussion types.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP09179000.6A 2009-01-30 2009-12-14 Mécanisme de percussion pneumatique et procédé de commande Revoked EP2213421B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910008189 DE102009008189A1 (de) 2009-01-30 2009-01-30 Pneumatisches Schlagwerk und Steuerungsverfahren

Publications (2)

Publication Number Publication Date
EP2213421A1 true EP2213421A1 (fr) 2010-08-04
EP2213421B1 EP2213421B1 (fr) 2017-06-21

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ID=42091569

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EP09179000.6A Revoked EP2213421B1 (fr) 2009-01-30 2009-12-14 Mécanisme de percussion pneumatique et procédé de commande

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US (1) US9132541B2 (fr)
EP (1) EP2213421B1 (fr)
DE (1) DE102009008189A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104608098A (zh) * 2013-11-05 2015-05-13 蒋世芬 手持式破坏拆解器

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10131042B2 (en) 2013-10-21 2018-11-20 Milwaukee Electric Tool Corporation Adapter for power tool devices
EP3697574A1 (fr) 2017-10-20 2020-08-26 Milwaukee Electric Tool Corporation Outil à percussion
US11059155B2 (en) 2018-01-26 2021-07-13 Milwaukee Electric Tool Corporation Percussion tool
EP3626399A1 (fr) * 2018-09-20 2020-03-25 Hilti Aktiengesellschaft Machine-outil portative et procédé de fonctionnement d'une machine-outil portative

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB467673A (en) * 1934-12-27 1937-06-22 Siemens Ag Improvements in and relating to power driven percussive tools in which springs are arranged between the striking hammer and the driving mechanism
DE1938738A1 (de) 1969-07-30 1971-02-04 Daiichi Kikai Seisakusho Co Lt Freikolben-Druckluftschlaggeraet
CH649604A5 (en) 1980-07-11 1985-05-31 Vni I Pk I Percussive machine
SU1579766A1 (ru) * 1988-09-23 1990-07-23 Московское Научно-Производственное Объединение По Механизированному Строительному Инструменту И Отделочным Машинам Компрессионно-вакуумна машина ударного действи
EP1779980A2 (fr) 2003-03-21 2007-05-02 Black & Decker, Inc. Système limitant les vibrations pour outil électrique, et outil électrique incorporant ce système

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4014392A (en) * 1973-03-01 1977-03-29 Ross Frederick W Stabilized piston-cylinder impact device
US4201269A (en) * 1977-01-24 1980-05-06 Ross Frederick W Impact device with linear single acting air spring
GB2069399B (en) * 1980-02-12 1983-10-19 V Ni I P Konstrukt I Mek I Ruc Percussive tool
DE3304916A1 (de) * 1983-02-12 1984-08-16 Robert Bosch Gmbh, 7000 Stuttgart Bohrhammer
SU1256950A1 (ru) * 1983-09-06 1986-09-15 Всесоюзный Научно-Исследовательский И Проектно-Конструкторский Институт Механизированного И Ручного Строительно-Монтажного Инструмента,Вибраторов И Строительно-Отделочных Машин Компрессионно-вакуумна машина ударного действи
SU1617139A1 (ru) * 1988-08-09 1990-12-30 Московское Научно-Производственное Объединение По Механизированному Строительному Инструменту И Отделочным Машинам Компрессионно-вакуумна машина ударного действи
EP1607186A1 (fr) * 2004-06-18 2005-12-21 HILTI Aktiengesellschaft Perceuse à percussion / marteau piqueur électro-pneumatique à énergie d'impact modifiable

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB467673A (en) * 1934-12-27 1937-06-22 Siemens Ag Improvements in and relating to power driven percussive tools in which springs are arranged between the striking hammer and the driving mechanism
DE1938738A1 (de) 1969-07-30 1971-02-04 Daiichi Kikai Seisakusho Co Lt Freikolben-Druckluftschlaggeraet
CH649604A5 (en) 1980-07-11 1985-05-31 Vni I Pk I Percussive machine
SU1579766A1 (ru) * 1988-09-23 1990-07-23 Московское Научно-Производственное Объединение По Механизированному Строительному Инструменту И Отделочным Машинам Компрессионно-вакуумна машина ударного действи
EP1779980A2 (fr) 2003-03-21 2007-05-02 Black & Decker, Inc. Système limitant les vibrations pour outil électrique, et outil électrique incorporant ce système

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104608098A (zh) * 2013-11-05 2015-05-13 蒋世芬 手持式破坏拆解器

Also Published As

Publication number Publication date
DE102009008189A1 (de) 2010-08-05
EP2213421B1 (fr) 2017-06-21
US20100224380A1 (en) 2010-09-09
US9132541B2 (en) 2015-09-15

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