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EP2310171B1 - Mécanisme de frappe avec entraînement rotatif variable - Google Patents

Mécanisme de frappe avec entraînement rotatif variable Download PDF

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Publication number
EP2310171B1
EP2310171B1 EP09777496.2A EP09777496A EP2310171B1 EP 2310171 B1 EP2310171 B1 EP 2310171B1 EP 09777496 A EP09777496 A EP 09777496A EP 2310171 B1 EP2310171 B1 EP 2310171B1
Authority
EP
European Patent Office
Prior art keywords
percussion
motor
drive
movement
rotor
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.)
Not-in-force
Application number
EP09777496.2A
Other languages
German (de)
English (en)
Other versions
EP2310171A1 (fr
Inventor
Helmut Braun
Rudolf Berger
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.)
Wacker Neuson Produktion GmbH and Co KG
Original Assignee
Wacker Neuson Produktion GmbH and Co KG
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 Wacker Neuson Produktion GmbH and Co KG filed Critical Wacker Neuson Produktion GmbH and Co KG
Publication of EP2310171A1 publication Critical patent/EP2310171A1/fr
Application granted granted Critical
Publication of EP2310171B1 publication Critical patent/EP2310171B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B25D11/005—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
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/064—Means for driving the impulse member using an electromagnetic drive
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • 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
    • B25D2250/005—Adjustable tool components; Adjustable parameters
    • B25D2250/021—Stroke length
    • 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
    • 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
    • B25D2250/275—Tools having at least two similar components
    • B25D2250/281—Double motors

Definitions

  • the invention relates to a striking mechanism according to the preamble of claim 1 and 2.
  • Such impactors are e.g. used in electrically operated break hammers or drills and / or impact hammers.
  • the striking mechanisms usually have a motor rotating in a direction of rotation at a substantially constant rotational speed, which reciprocates a drive piston (piston) via a crank or wobble drive, which in turn is driven by a spring, e.g. an air spring drives a percussion piston (bat).
  • the stroke of the drive piston is fixed due to the specified geometry of the crank mechanism (crank radius) or the wobble mechanism (wobble stroke).
  • the rotational frequency is usually largely constant during a beating cycle due to the inertia.
  • the impact strength is fixed.
  • the frequency and impact strength can not be set independently.
  • a percussion mechanism in which a rocking lever can be reciprocated about an axis of rotation when an iron core attached to the rocker arm is attracted by two opposing magnetic coils accordingly. Characterized a reciprocating motion of a coupled to the rocker arm via a leaf spring striker is effected, which in turn acts on a chisel.
  • the invention has for its object to provide a striking mechanism with a drive in which during the period of a single stroke cycle, a control of the way and speed of the drive piston and thus the stroke is possible.
  • the beat frequency and impact strength should be variably adjustable from beat cycle to beat cycle.
  • a striking mechanism comprising a drive with a motor and a rotor provided in the motor, a drive element which can be moved back and forth by the drive in a guide device, a striking element and with a coupling device acting between the drive element and the striking element, via which the movement of the drive element is transferable to the striking element, is characterized in that the motor is controlled such that within a stroke cycle changeable, so different rotational speeds of the rotor can be generated.
  • the motor is controllable such that a change in the rotational speed is effected within a beating cycle in accordance with a predetermined algorithm for the movement of the rotor.
  • the algorithm may have a fixed path-time profile for the movement of the rotor by a controller and / or regulation. In this case, therefore, the movement of the rotor and subsequently the drive element is predetermined over time, eg only in dependence on external specifications of the operator.
  • the path-time history can change from beat cycle to beat cycle. So it is e.g. possible at a start of the percussion initially automatically soft start with relatively small stroke of the drive element, but already to achieve high operating frequency, even if the operator already operates a corresponding control element as if he wanted to operate the device at full load.
  • the fixed path-time course can thus be variable depending on a change in the environmental conditions (in particular the wishes of the operator).
  • the algorithm dictates movement of the rotor in response to events occurring on or with components of the percussion mechanism, particularly in response to actual movement of the striking element.
  • the movement of the striking element can be monitored by suitable means so that the movement of the rotor and subsequently of the driving element adapts to the striking element. If e.g. the impact element is repelled only by a small recoil, the drive element can perform a corresponding stroke to suck the striker back again.
  • the motor of the impact mechanism according to claim 2 is to be controlled such that the motor generates a reciprocating motion within a beat cycle.
  • the motor does not perform a constant rotational movement. Rather, the rotational movement of the rotor with respect to the rotational speed, the frequency but also the direction of rotation can be variably and individually controlled, even from beat cycle to beat cycle or even within a beat cycle. This is understood as a beat cycle, the period from one beat to the next.
  • the rotor does not necessarily reach a direction of the same direction but a reciprocating movement.
  • the motor is able to produce both a co-rotation and a reciprocating motion.
  • the motor can then either run in the same direction in one direction or, if necessary, a reciprocating motion, e.g. around bottom dead center. This requires high variability and controllability from the engine.
  • the motor is designed to be very low in inertia, so that the rotational movement of the motor and the derived movement of the drive element can be approximated to the course of movement of the striking element.
  • a harmonic stroke sequence can be achieved if the distance between the drive element and impact element during a stroke cycle is not too large.
  • the coupling device effective between the drive element and the striking element e.g. an air spring to be built with a smaller size, in particular shorter.
  • the theoretical potential top dead center does not necessarily have to be passed through in this mode by the drive element, because the drive element already reverses its direction of movement.
  • a transmission device can be provided between the motor and the drive element for transmitting a rotational movement generated by the motor into a longitudinal movement of the drive element.
  • the transmission device may have suitable components, such as crank mechanism, connecting rod, rack (even with uneven pitch), scenery, cam, worm, wobble, space gear, chain, timing belt, cable drive, etc.
  • the transmission device may have a translation device, such that the motor generates several revolutions of the rotor during a beat cycle. The motor then travels several turns in the same direction during one beat cycle until the engine rotational direction is reversed at top dead center or near top dead center of the drive element.
  • the motor must be suitable for an increased speed. For this he only has to provide a lower torque so that it is possible to make the engine smaller.
  • such a translation device e.g. be dispensed with a transmission intermediate stage to keep the inertial forces low.
  • the motor may e.g. as an asynchronous motor or as a synchronous motor, e.g. be designed as a magnetic motor, claw pole motor or torque motor.
  • the drive then corresponds to a linear motor, such as in the WO 03/066286 A1 or the DE 10 2005 030 340 B3 is described.
  • the motor is a rewound, that is to say functionally closed linear motor, with a rotor driven in rotation instead of an axially movable rotor in a linear motor.
  • the drive can have two motors operated in opposite directions, which jointly drive the drive element. In this embodiment, it is sufficient to couple together two relatively small-sized, weak motors that move together the drive element.
  • the division of the drive into two motors increases the latitude in the design of a working implement using the striking mechanism, e.g. a departure hammer.
  • Each of the motors can in turn be individually controlled in the manner described above within a beating cycle and, for example, as a magnetic motor or Synchronous motor be formed so that on the one hand has a rotating rotor and on the other hand can be controlled as a linear motor.
  • Each of the motors can be assigned a transmission device in order to transmit the rotational movement generated by the respective motor into a longitudinal movement of the drive element. It is also possible that the motors act on a common transmission device.
  • the motors may also be coupled together in some other way to jointly drive the drive member.
  • the striking mechanism is an air spring impact mechanism, the drive element designed as a drive piston and the striking element as a percussion piston.
  • the coupling device may have a formed in a cavity between the drive piston and the percussion piston driving air spring, via which the movement of the drive piston is transferable to the percussion piston.
  • the coupling device may have a return air spring effective between the drive piston and the percussion piston in order to assist a backward movement of the percussion piston after a blow. In this way, a so-called double-acting air spring is realized.
  • the invention allows a variation of the beat frequency regardless of the variation of impact strength.
  • a high impact frequency can be achieved with a small impact strength when applying a chisel acted upon by the impact mechanism in a hammer. Idling can be achieved by quickly decelerating the engine without requiring an idle or special idler.
  • an exact impact strength control is possible even with a wide variety of recoil (the impact of the impact element on the tool) by adjusting the movement of the drive piston to the flight curve of the impact element.
  • the ratio between drive element and impact element can be adjusted depending on different ambient pressures.
  • the motor is easier to seal due to the rotationally moving parts and the rotation bearings therewith, than is required for linear motors with linear guide of a rotor.
  • the bearing point of the rotor must - since radially inwardly - record only a lower speed than is the case with the rotor of a linear motor. This reduces mass forces and friction.
  • Fig. 1 shows a schematic side view of an impact mechanism with a motor 1, which has a stator 2, a rotor 3 and an electronic control unit 4.
  • the motor is designed as a magnetic motor or synchronous motor. It thus corresponds in effect to a circumferentially closed, wound linear motor.
  • the Control electronics 4 makes it possible to generate any rotational movements, paths and rotational speeds of the rotor 3 within physical limits.
  • the rotational movement of the rotor 3 is transmitted via a pin 5 to a connecting rod 6.
  • the pin 5 and the connecting rod 6 form a transmission device in the form of a crank mechanism.
  • connecting rod 6 serving as a drive element drive piston 7 is coupled, which is within a serving as a guide device guide cylinder 8 back and forth.
  • the percussion piston 9 is reciprocable in a cavity of the drive piston 7.
  • a drive air spring 10 is formed in a known manner, which also moves the percussion piston 9 forward in particular in the event of a forward movement of the drive piston 7 in the direction of a chisel 11.
  • the percussion piston 9 strikes cyclically on the chisel 11, which is held in a tool holder 13.
  • a return air spring 12 is also formed in front of the percussion piston 9 in the interior of the drive piston 7, which supports the return movement of the percussion piston 9 after completed blow.
  • a percussion is realized with a known double-acting air spring.
  • Fig. 2 shows the movement of the drive piston (piston) over the crank angle for a conventional percussion device with a rotary drive ( Fig. 2a ) as well as the movement of the drive piston and the percussion piston (racket) over time ( Fig. 2b ).
  • the invention makes it possible in the in Fig. 1 shown Schlagwerk the drive piston individually variable to control, as in the Fig. 3 to 6 shown.
  • Fig. 3 shows the piston movement of the drive piston 7 above the crank angle.
  • the piston stroke between the maximum possible top dead center (1.0000) and bottom dead center (0.0000) is fully utilized.
  • the motor 1 is controlled such that the drive piston reaches a top dead center of only 0.3500 and then reversed again.
  • the drive piston can achieve very different courses of motion, piston strokes and frequencies, which is made possible by the respective actuation of the motor 1. For example, in the relatively small piston stroke of Fig. 5 high frequency hitting is possible over time, while at the exhaustion of the maximum possible piston stroke ( Fig. 3 ) a lower frequency is achieved.
  • the bottom dead center is not traversed during each stroke cycle.
  • the direction of rotation of the rotor 3 and thus the direction of movement of the drive piston can already be reversed before the crank drive (or a corresponding rack and pinion drive etc.) or the drive piston have reached the theoretically possible bottom dead center.
  • the drive piston is then initially moved downward by the rotation of the rotor 3, but is decelerated and moved back even before the (theoretically possible) bottom dead center is reached.
  • the bottom dead center is not traversed in this embodiment, analogous to the top dead center in connection with the embodiments of Fig. 3 to 5 applies.
  • the reciprocating motion of the rotor 3 causes a reciprocating motion of the drive piston without passing through the lower or top dead center.
  • Fig. 7 shows an example of the movement of the drive piston 7 and the percussion piston 9 over time.
  • Fig. 8 shows another embodiment of the percussion of Fig. 1 .
  • two motors 1 are provided, each driving a connecting rod 6, whereby the drive piston 7 is reciprocated in the appropriate manner.
  • the motors 1 are operated in opposite directions, as shown by the arrow.
  • the changing engine torques cancel each other, so that no lateral forces and no tilting moments act on the drive piston 7. This increases the smoothness and thus the comfort when the percussion, e.g. is used in a hand-held implement.
  • the percussion can be used in particular in a drill and / or percussion hammer or a breaker.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (15)

  1. Mécanisme de frappe, comprenant :
    - un entraînement avec un moteur (1) et un rotor (3) prévu dans le moteur (1) ;
    - un élément d'entraînement (7) pouvant être déplacé d'avant en arrière par l'entraînement dans un dispositif de guidage (8) ;
    - un élément de frappe (9) ; et
    - un dispositif de couplage (10) actif entre l'élément d'entraînement (7) et l'élément de frappe (9) au moyen duquel le mouvement de l'élément d'entraînement (7) peut être transmis à l'élément de frappe (9) ;
    caractérisé en ce que :
    - le moteur (1) peut être commandé de telle sorte que des vitesses de rotation variables du rotor (3) peuvent être réalisées au cours d'un cycle de frappe ; et
    - le moteur (1) peut être commandé de telle sorte qu'une modification de la vitesse de rotation au cours d'un cycle de frappe est exécutée sur la base d'un algorithme prédéfini pour le mouvement du rotor (3) ; et
    - l'algorithme définit un mouvement du rotor (3) en fonction d'événements qui surviennent sur ou avec des composants du mécanisme de frappe, en particulier en fonction d'un mouvement effectif de l'élément de frappe (9).
  2. Mécanisme de frappe, comprenant :
    - un entraînement avec un moteur (1) et un rotor (3) prévu dans le moteur (1) ;
    - un élément d'entraînement (7) pouvant être déplacé d'avant en arrière par l'entraînement dans un dispositif de guidage (8) ;
    - un élément de frappe (9) ; et
    - un dispositif de couplage (10) actif entre l'élément d'entraînement (7) et l'élément de frappe (9) au moyen duquel le mouvement de l'élément d'entraînement (7) peut être transmis à l'élément de frappe (9) ;
    dans lequel :
    - le moteur (1) peut être commandé de telle sorte que des vitesses de rotation variables du rotor (3) peuvent être réalisées d'un cycle de frappe au cycle de frappe suivant ;
    caractérisé en ce que :
    - le moteur (1) peut être commandé de telle sorte que le moteur (1) produit un mouvement rotatif d'avant en arrière du rotor (3) au cours d'un cycle de frappe.
  3. Mécanisme de frappe selon la revendication 2, caractérisé en ce que le moteur (1) peut être commandé de telle sorte qu'une modification de la vitesse de rotation au cours d'un cycle de frappe et/ou d'un cycle de frappe au cycle de frappe suivant est exécutée sur la base d'un algorithme prédéfini pour le mouvement du rotor (3).
  4. Mécanisme de frappe selon la revendication 2 ou 3, caractérisé en ce que l'algorithme définit un mouvement du rotor (3) en fonction d'événements qui surviennent sur ou avec des composants du mécanisme de frappe, en particulier en fonction d'un mouvement effectif de l'élément de frappe (9).
  5. Mécanisme de frappe selon l'une des revendications 1 à 4, caractérisé en ce que l'algorithme présente un parcours espace-temps prédéfini de façon fixe par une commande et/ou une régulation pour le mouvement du rotor (3).
  6. Mécanisme de frappe selon l'une des revendications 1 à 5, caractérisé en ce que le moteur (1) peut être commandé de telle sorte que l'élément d'entraînement (7) entraîné par le moteur (1) atteint un parcours de déplacement qui se rapproche du parcours de déplacement de l'élément de frappe (9).
  7. Mécanisme de frappe selon l'une des revendications 1 à 6, caractérisé en ce que le moteur (1) peut être commandé de telle sorte :
    - qu'un point mort inférieur de l'élément d'entraînement (7) dirigé vers l'élément de frappe (9) est traversé au cours de chaque cycle de frappe ; et/ou
    - qu'un point mort supérieur de l'élément d'entraînement (7) situé à distance de l'élément de frappe n'est pas traversé au cours de chaque cycle de frappe.
  8. Mécanisme de frappe selon l'une des revendications 1 à 7, caractérisé en ce qu'il est prévu entre le moteur (1) et l'élément d'entraînement (7) un dispositif de transmission (5, 6) destiné à transmettre un mouvement rotatif produit par le moteur (1) dans une direction longitudinale de l'élément d'entraînement (7).
  9. Mécanisme de frappe selon l'une des revendications 1 à 8, caractérisé en ce que le dispositif de transmission présente un dispositif de démultiplication de telle sorte que le moteur (1) produit plusieurs rotations du rotor (3) pendant un cycle de frappe.
  10. Mécanisme de frappe selon l'une des revendications 1 à 9, caractérisé en ce que l'entraînement présente deux moteurs (1) fonctionnant en sens opposé qui entraînent conjointement l'élément d'entraînement (7).
  11. Mécanisme de frappe selon l'une des revendications 1 à 10, caractérisé en ce qu'un dispositif de transmission (5, 6) est adjoint à chacun des moteurs (1) afin de transmettre le mouvement rotatif produit par le moteur respectif dans une direction longitudinale de l'élément d'entraînement (7).
  12. Mécanisme de frappe selon l'une des revendications 1 à 11, caractérisé en ce que :
    - le mécanisme de frappe est un mécanisme de frappe à suspension pneumatique ;
    - l'élément d'entraînement est réalisé comme piston d'entraînement (7) ;
    - l'élément de frappe est réalisé comme piston de frappe (9) ;
    - le dispositif de couplage présente une suspension pneumatique d'entraînement (10) formée dans un espace creux entre le piston d'entraînement et le piston de frappe, au moyen de laquelle le mouvement du piston d'entraînement (7) peut être transmis au piston de frappe (9).
  13. Mécanisme de frappe selon la revendication 12, caractérisé en ce que le dispositif de couplage présente, en plus de la suspension pneumatique d'entraînement, une suspension pneumatique de rappel (12) active entre le piston d'entraînement (7) et le piston de frappe (9) afin de soutenir un mouvement vers l'arrière du piston de frappe (9) après une frappe.
  14. Mécanisme de frappe selon l'une des revendications 1 à 13, caractérisé en ce que le moteur (1) est un moteur asynchrone, un moteur magnétique ou un autre moteur synchrone.
  15. Mécanisme de frappe selon l'une des revendications 1 à 14, caractérisé en ce que le moteur (1) est réalisé comme moteur linéaire bobiné fermé en fonctionnement.
EP09777496.2A 2008-07-29 2009-07-28 Mécanisme de frappe avec entraînement rotatif variable Not-in-force EP2310171B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008035298A DE102008035298A1 (de) 2008-07-29 2008-07-29 Luftfederschlagwerk mit variablem rotatorischem Antrieb
PCT/EP2009/005468 WO2010012453A1 (fr) 2008-07-29 2009-07-28 Mécanisme percuteur pneumatique avec entraînement rotatif variable

Publications (2)

Publication Number Publication Date
EP2310171A1 EP2310171A1 (fr) 2011-04-20
EP2310171B1 true EP2310171B1 (fr) 2014-03-12

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Application Number Title Priority Date Filing Date
EP09777496.2A Not-in-force EP2310171B1 (fr) 2008-07-29 2009-07-28 Mécanisme de frappe avec entraînement rotatif variable

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Country Link
US (1) US8534376B2 (fr)
EP (1) EP2310171B1 (fr)
CN (1) CN102105271B (fr)
DE (1) DE102008035298A1 (fr)
WO (1) WO2010012453A1 (fr)

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DE10346534A1 (de) * 2003-10-07 2005-05-12 Bosch Gmbh Robert Handwerkzeugmaschine mit einem Schlagwerk sowie Verfahren zum Betreiben der Handwerkzeugmaschine
EP1607186A1 (fr) * 2004-06-18 2005-12-21 HILTI Aktiengesellschaft Perceuse à percussion / marteau piqueur électro-pneumatique à énergie d'impact modifiable
DE102005010737A1 (de) 2005-03-09 2006-09-14 Rückle GmbH Werkzeugfabrik Antriebsvorrichtung, insbesondere für Schwenktische
DE102005030340B3 (de) 2005-06-29 2007-01-04 Wacker Construction Equipment Ag Schlagwerk mit elektrodynamischem Linearantrieb
DE102006059076A1 (de) 2006-12-14 2008-06-19 Robert Bosch Gmbh Schlagwerk einer Elektrohandwerkzeugmaschine

Also Published As

Publication number Publication date
CN102105271A (zh) 2011-06-22
US8534376B2 (en) 2013-09-17
EP2310171A1 (fr) 2011-04-20
WO2010012453A1 (fr) 2010-02-04
DE102008035298A1 (de) 2010-02-04
CN102105271B (zh) 2013-11-20
US20110127055A1 (en) 2011-06-02

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