EP1893388B1 - Marteau perforateur et/ou marteau pneumatique a commande de la marche a vide - Google Patents

Marteau perforateur et/ou marteau pneumatique a commande de la marche a vide Download PDF

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Publication number
EP1893388B1
EP1893388B1 EP06754484A EP06754484A EP1893388B1 EP 1893388 B1 EP1893388 B1 EP 1893388B1 EP 06754484 A EP06754484 A EP 06754484A EP 06754484 A EP06754484 A EP 06754484A EP 1893388 B1 EP1893388 B1 EP 1893388B1
Authority
EP
European Patent Office
Prior art keywords
hammer
percussion
valve
handle
sleeve
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
EP06754484A
Other languages
German (de)
English (en)
Other versions
EP1893388A1 (fr
Inventor
Rudolf Berger
Wolfgang Schmid
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 SE
Original Assignee
Wacker Construction Equipment 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 Wacker Construction Equipment AG filed Critical Wacker Construction Equipment AG
Publication of EP1893388A1 publication Critical patent/EP1893388A1/fr
Application granted granted Critical
Publication of EP1893388B1 publication Critical patent/EP1893388B1/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
    • B25D11/12—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
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • 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
    • 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
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/035—Bleeding holes, e.g. in piston guide-sleeves
    • 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
    • B25D2250/131—Idling mode of tools
    • 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
    • B25D2250/371—Use of springs

Definitions

  • the invention relates to a drilling and / or percussion hammer with idle control according to the preamble of claim 1.
  • Such a hammer and / or percussion hammer (hereinafter referred to simply as a hammer) with a contact pressure-dependent idle control is from the DE 101 45 464 A1 known.
  • the hammer has an idle passage for connecting a cavity formed between a drive piston and a percussion piston in an air spring percussion mechanism with the environment, which can be opened and closed by a valve.
  • a detection device for detecting a can be applied by the operator to the handle pressing force is arranged.
  • the valve can be activated as a function of the detected pressing force.
  • the invention has for its object to improve a generic hammer to the effect that a soft application of the hammer can be achieved by a relatively slow transition from idle mode in the impact mode.
  • An inventive hammer drill and / or percussion hammer (hereinafter referred to simply as a hammer) has a valve with which a cavity located in an air spring striking and designed to receive an air spring cavity can be brought via an idle channel with the environment in combination.
  • the valve is used to open the idle channel in idle mode and to close the idle channel in a hitting mode.
  • a detection device is provided for detecting a control variable that distinguishes the impact mode and the idling mode.
  • the valve can be opened and closed as a function of the control variable and assumes a position corresponding to the control variable.
  • a delay device is provided, by means of which the valve can be controlled such that it reaches the position corresponding to the detected control variable with a time delay.
  • the closing of the idle passage by the valve causes a transition of the air spring impact mechanism from idle operation to impact operation, because in the cavity between the drive piston and percussion piston, an air spring can form.
  • the delay device causes, even with an abrupt placement of the hammer or even with an increase in the detected pressing force due to a not foreseeable by the operator or unwanted proper motion of the hammer housing no correspondingly bypassing, in this case increased pressing force corresponding closing of the idle passage through the valve he follows. Rather, the valve changes regardless of such short-term Actions its time stretched and takes only after a certain period, the appropriate position of the recorded tax. As a result, the transition from idle mode to beat mode is relatively smooth and predictable for the operator.
  • the time delay ie the period during which the valve is closed
  • the valve is dimensioned such that it covers a period of a plurality of impact cycles, each comprising a reciprocating movement of the drive piston.
  • the valve it is expedient for the valve to change its position substantially continuously during the period defined by the time delay, ie to close the idling channel uniformly, in order to achieve the desired smooth transition from idling operation to impact operation.
  • the valve is advantageously activatable during opening in such a way that it detects one of the detected control variables, e.g. the pressing force corresponding position achieved substantially immediately.
  • the opening of the idle channel is required in the transition from impact mode to idle mode and is achieved by lifting the hammer on the handle and thus by reducing the contact pressure.
  • the hammer immediately, ie without a time delay, goes into idle mode to avoid unwanted vibrations of the hammer.
  • the valve should as soon as possible allow opening of the idle channel and venting of the air spring.
  • control variable As a control variable and thus as a criterion for distinguishing the idling operation and the impact operation, various sizes are suitable, which can be evaluated alternatively or in addition.
  • the position of a tool loaded by the hammer and / or the percussion piston and / or an anvil (intermediate piston) can be taken into account as a control variable.
  • the hammer When the hammer is lifted off the stone to be machined in idle mode, the tool with its shank slides out of the tool holder of the hammer and thus achieves a front position relative to the working direction. Accordingly, the striker and the percussion piston forward in glide a position that can never be reached in impact mode.
  • the detection device is then preferably designed such that it can recognize this front position and evaluate it as a criterion for idling operation.
  • the position of a drive of the drive piston controlling, operable by the operator actuator.
  • the actuator may e.g. a throttle or throttle in a pneumatic hammer, which is movable between an open and a closed position.
  • the term "actuator”, a throttle lever for an internal combustion engine or a control button for an electric motor can be considered.
  • the pressure applied by the operator pressing force is evaluated as a control variable.
  • a detection device for detecting a by the operator applied to the handle serving as a control variable pressing force.
  • the valve can be opened and closed as a function of the detected pressing force and in each case assumes a predefined position corresponding to the pressing force.
  • the valve is moved into the closed position, so that the impact mode of the pneumatic spring impact mechanism can be absorbed.
  • the valve opens the idle channel, so that the air spring in the hammer mechanism ventilated and the impact operation is interrupted.
  • the valve can be actuated via the deceleration device such that it reaches the position corresponding to the detected pressing force with a time delay.
  • the handle on which the operator applies the pressing force is movable relative to the hammer housing.
  • the delay means does not cause the relative movement between the hammer housing and the handle directly to an immediate closing of the idle channel, but rather leads to a rather slow change in the cross section of the idle channel, so only causes a time-delayed reduction and finally closing the idle channel.
  • a control element of the valve forming, axially movable sleeve is provided, the axial position of which is variable in dependence on the pressing force.
  • This sleeve corresponds in principle to one of the DE 101 45 464 A1 known sleeve.
  • the sleeve according to the invention with the handle only in one axial direction such - for example, positively connected - that a reduction of the pressing force by the operator causes a direct and proportional change in the position of the valve.
  • the sleeve is not positively connected to the handle in the other, oppositely directed axial direction, but coupled such that increasing the pressing force and an associated displacement of the handle relative to the hammer housing via the delay means a time-delayed displacement of the sleeve causes.
  • delayed displacement is meant herein that the sleeve moves at a substantially lower velocity than the relative velocity between the handle and the hammer housing.
  • the drive piston is hollow and the percussion piston in the drive piston movable.
  • a cylindrical wall of the drive piston at least one opening is provided, which can form part of the idling channel depending on the axial position of the drive piston.
  • the drive piston is from surrounded a percussion tube, in which at least one of the opening in the wall of the drive piston associated radial opening is provided, which also forms part of the idle channel.
  • the percussion tube in turn is surrounded by the sleeve described above, which has one of the radial opening of the percussion tube associated radial opening.
  • the sleeve is axially displaceable on the percussion tube against the action of a spring device in such a way that the radial opening of the percussion tube can be moved to open the valve, while the sleeve covers the radial opening of the percussion tube for closing the valve.
  • the spring device presses the sleeve in the closed position, so that to open the valve, the sleeve must be moved against the action of the spring device.
  • the delay device has a cavity formed between the sleeve and the percussion tube, the volume of which changes as a function of the relative position of percussion tube and sleeve.
  • the cavity is substantially closed off from the environment and is continuously connected to the environment only via a defined delay opening.
  • the delay opening is dimensioned such that it ensures a predetermined air volume flow, which depends essentially on the pressure difference between the cavity and the environment.
  • the cavity may have a check valve which provides an additional opening over which an existing in the cavity air pressure is degraded if necessary. On the other hand, no air can flow into the cavity via the check valve.
  • the sleeve is moved such that the volume of the cavity is increased by the action of the spring means and the movement of the sleeve, the speed of movement of the sleeve being defined by the predetermined air flow rate through the delay opening
  • the movement speed is lower than the relative speed between the handle and the hammer housing caused by the pressing force.
  • the sleeve can thus only relatively slowly move into the predetermined by the applied pressure force target position. Since the sleeve serves as a control element for the valve, and the valve only with a time delay reaches its respective predetermined, defined by the pressing force end position, which essentially causes a complete closed position of the idle passage.
  • the vibration decoupling device moves the now relieved handle - usually by spring action - in its defined home or rest position. Then, coupled to the handle sleeve moves so that the volume of the cavity between the sleeve and striking tube is reduced, whereby in the cavity, an increased air pressure. At least a portion of the air in the cavity can flow out through the check valve. Another, but usually lesser part will also flow out of the cavity via the delay opening.
  • the movement speed of the sleeve substantially corresponds to the relative speed between the handle and the hammer housing caused by the vibration decoupling device. This is also ensured by the fact that there is a positive coupling between the sleeve and the handle in this direction of movement.
  • the detection means comprises a sensor for detecting a state in which the handle is pressed against the action of the spring system against the hammer housing, and for generating a corresponding Andschreibsignals.
  • the valve may have a mechanically, electrically, electromechanically or electromagnetically controllable valve element.
  • the pressure signal can be fed to a controller, which correspondingly activates the valve element for opening and closing the valve, wherein the closing of the valve is stretched over a certain period of time.
  • the control thus ensures that the closing of the valve, ie the transition from idle operation to impact operation, does not occur suddenly over a very short period of time but is stretched over a longer, predefined period of time.
  • the same effects can be achieved as in the case of the purely mechanical solution described above.
  • the senor is designed as a proximity sensor or as a force measuring sensor.
  • a position sensor for detecting the position of the hammer in space relative to a horizontal plane and for generating a corresponding position signal which can be fed to the controller.
  • the controller controls the valve element while evaluating the Andrücksignals and the position signal.
  • a deviation of the position of the hammer from the horizontal plane is taken into account such that the resulting pressure signal is subjected to a correction taking into account the effective weight forces of the handle, the hammer housing and the components contained therein and a tool.
  • the position of the tool, the percussion piston and / or the anvil is evaluated as the control variable, it is advantageous if one, with respect to a working direction, the front position of the tool, the striker and / or the percussion piston applies as a criterion for idling while a relation to the front position shifted backward position as a criterion for the impact operation applies.
  • the tool chisel
  • striker and percussion piston slide out of the hammer somewhat, leaving it in an idling position that can never be reached during impact operation.
  • the position of the tool, the striker and the percussion piston is a suitable criterion for distinguishing the idling operation from the impact operation.
  • the detection device has a device for determining the position of the tool, the striker and / or the percussion piston in at least two places, wherein the one place the idling operation and the other place is assigned to the impact mode. It is therefore not necessary to detect any position of the tool, the striker or the percussion piston and provide a seamless, continuous monitoring. Rather enough it determines whether the components in question have exceeded a limit between idle position and impact position. This can be realized particularly easily if the position of the components are detected at the two points separated from the imaginary boundary.
  • an idle position of the actuator for propulsion (e.g., throttle grip) is considered a criterion for idling operation, while an operating position of the actuator is a criterion for impact operation.
  • the position of the actuator e.g. in a pneumatic hammer, evaluated to draw conclusions about idle and impact mode.
  • the detection device has a sensor for detecting the control variable and for generating a control signal and the valve comprises a mechanically, electrically, electromechanically or electromagnetically controllable valve element.
  • the control signal may then be supplied to a controller, which correspondingly activates the valve element for opening and closing the valve, wherein the closing of the valve is stretched in the intended manner over a certain period of time.
  • the electronics can also define the period of time that is required for closing.
  • the detection device can also determine whether the operator initially only slightly presses against the hammer and therefore does not want to retrieve the full impact performance. With the help of the control electronics, it is then possible to maintain intermediate states in the opening and closing of the valve as long as the operator handles the hammer in the appropriate manner, e.g. presses.
  • the Fig. 1a shows a hammer called hammer and / or percussion hammer, with a hammer housing 1 and a large parts of the hammer housing 1 surrounding the handle cover. 2
  • the term of the hammer housing 1 serves as a summary of several assemblies of the hammer, namely in particular a drive, not shown, driven by the drive wobble mechanism 3 and a Heilfedertschwerks 4.
  • a drive piston 5 of the wobble mechanism 3 in axial reciprocation offset, whereby a in a hollow recess of the drive piston 5 also axially reciprocable percussion piston 6 is reciprocated back and forth via a formed in a cavity 7 air spring.
  • the percussion piston 6 in turn strikes the insertion end of a tool 8 (in Fig. 1a a breaker chisel) held by a tool holder 9.
  • the hammer housing 1 accommodates at least part of the aforementioned components and is usually made of metal. It is surrounded in essential parts of the handle cover 2, via a non-illustrated, per se known vibration decoupling device, for example via Rubber springs, is connected to the hammer housing 1.
  • the handle cover 2 may be made of plastic and extending to the area of the tool holder 9 forward.
  • a handle 10 is provided with a handle point 11, at which the operator can hold the hammer and press against the rock to be processed.
  • a further handle 12 is provided in a front region of the handle cover 2, which the operator can grip with his other hand in a known manner for better guidance of the hammer.
  • the handle cover 2 surrounds the handle cover 2 essential parts of the hammer housing 1.
  • the handle cover 2 surrounds only a portion of the hammer housing, in particular the rear, the handle 10 to be directed portion of the hammer housing 1.
  • the handle cover 2, the hammer housing 1 does not surround, but is held only by the vibration decoupling device behind the hammer housing 1.
  • the term of a "grip hood" is therefore not to be interpreted as meaning that the hammer housing 1 must be enclosed by this.
  • the vibration decoupling device arranged between the grip hood 2 and the hammer housing 1 serves to keep away from the handle cover 2 and thus from the handle 10 the shocks and vibrations occurring during the impact generation by the air spring impact mechanism 4 and during the machining of the rock, in order to protect the operator as little as possible to expose the damaging vibrations.
  • the vibration decoupling device ensures that the handle cover 2 can move relative to the hammer housing 1. As can be seen immediately, the handle 10 can be pressed by the operator against the hammer housing 1 in such a way that the handle cover 2 slides over the hammer housing 1 towards the front, in the direction of the tool 8.
  • a detection device For detecting the pressing force which can be applied by the operator to the handle 10 or the grip point 11, a detection device is provided.
  • the detection means is that the pressing force against the action of a spring device in the vibration decoupling device causes a certain displacement of the handle cover 2 relative to the hammer housing 1. Since the spring characteristic of the vibration decoupling device is known, it can be concluded reliably that a certain pressing force also causes a certain displacement. It is also possible that the displacement is limited by a stop, for the achievement of the attack a force is required, which corresponds to a minimum required pressure force for the impact operation.
  • Fig. 1a to 1c show the hammer in neutral position when the cavity 7 is in communication with its environment, so it is ventilated.
  • the exact structure is better recognizable in the detail enlargements 1b and 1c.
  • an opening 13 is provided in the form of a longitudinal slot.
  • the drive piston 5 is radially guided by a striking mechanism tube 14 which has a radial opening 15 corresponding to the opening 13 of the drive piston 5.
  • the striking mechanism tube 14 is surrounded by a sleeve 16, in the wall of which a radial opening 17 corresponding to the radial opening 15 of the striking mechanism tube 14 is formed.
  • a sleeve 16 in the wall of which a radial opening 17 corresponding to the radial opening 15 of the striking mechanism tube 14 is formed.
  • the opening 13 and the radial openings 15 and 17 are superimposed so that they form an idle channel through which the cavity 7 is brought into contact with the environment of the air spring impact 5. Accordingly, during an axial movement of the drive piston 5, no air spring can form in the cavity 7, so that the percussion piston 6 does not have the tendency to follow the movement of the drive piston 5.
  • the air spring striker 4 also runs at idle when the drive piston 5 due to the Effect of the drive reciprocated.
  • the sleeve 16 is displaceable on the percussion tube 14 against the action of a spring 18, so that the radial opening 17 may be either in idle operation on the radial opening 15, or, as later with reference to the Fig. 2b and 2c explained, in the impact mode is shifted so that the radial opening 17 is no longer above the radial opening 15 and thus the radial opening 15 is closed by the sleeve 16. Accordingly, the sleeve 16 is a valve for the idle channel.
  • the axial position of the sleeve 16 is determined on the one hand by the action of the spring 18.
  • the sleeve 16 is supported on a front side by a pin 19, which in turn is held by the handle cover 2.
  • the pin 19 fastened to the handle cover 2 also moves forward.
  • a cavity 20 is formed between the percussion tube 14 and the sleeve 16, in particular between the end faces thereof. Since the cavity 20 is substantially sealed off from the environment, it creates a negative pressure in it due to the action of the spring 18. The negative pressure in the cavity 20 can be reduced only via a formed in the end face of the sleeve 16 delay opening 21, flows through the air into the cavity 20.
  • the pin 19 can thus move away from the sleeve 16 with a correspondingly fast and vigorous pressing the handle cover 2 by the operator. He then defines only the end position, which can be achieved by the sleeve 16, after it has moved with a time delay in the direction of the pin 19.
  • the time delay, ie the slowed axial movement of the sleeve 16, can be selected in a suitable manner by the dimensioning of the delay opening 21.
  • a deceleration device which consists essentially of the spring 18, the cavity 20 and the deceleration opening 21.
  • a check valve 22nd provided that an underlying opening 23 covers.
  • the check valve 22 may be a rubber ring which is inserted in a circumferential groove and covers a plurality of circumferentially distributed openings 23.
  • the retarding device described above causes a relative movement between the unsprung hammer mass (essentially the hammer housing 1 with the components contained therein) and the sprung hammer mass (essentially the grip hood 2 or the handle 10) not directly to a sudden change in the cross sections in the idle channel, but rather an intended time delay or time extension is achieved.
  • the hammer can be kept as long as desired in a state of reduced impact strength at full hammer rate depending on the force applied by the operator pressing force. The operator can thus keep the drive at full speed, so that the percussion works at the normal operating frequency, without already strong blows are exerted on the tool 8.
  • the hammer mechanism will not change into hammering operation just as quickly, but will require a few stroke cycles due to the deceleration device until the full impact force is reached.
  • the increasing of the pressing force can also be detected by an electrical or electronic detection device, which passes on a corresponding signal to a controller, by which a valve for opening and closing the idle channel is driven.
  • the respective position of the hammer can be taken into account, because the applied by the operator pressure force varies considerably depending on the position of the hammer. So the operator has a higher pressure force when working horizontally or when working on Apply head as required when working down, because in the former cases, the weight of the hammer is to be included.
  • the resulting Andschreib protector and the corresponding consequences for the change of idle mode and impact mode can be evaluated or adjusted by the controller in a suitable manner.
  • Fig. 3 shows a section through a further embodiment of the hammer drill according to the invention, on the illustration of FIG. 4 from the DE 101 45 464 A1 based.
  • a hammer in which a detection of the pressing force of the operator on the handle and a consequent influence on the position of the connection of the cavity 7 with the environment controlling valve is carried out by mechatronic means.
  • a valve body 25 is inserted into a very short idling channel.
  • the idling channel consists here only of a recess 26 in the striking mechanism tube 14 and a connecting channel 27 into which the valve body 25 is inserted.
  • the valve body 25 has in its interior a through hole and is rotatable by an actuator, not shown in the figure.
  • the valve body 25 is rotated to a position in which the through hole is not arranged in the idle passage, so that the connection between the cavity 7 and the environment of the air spring impact mechanism is interrupted.
  • the valve body 25 can be rotated by 90 ° in a position in which the through hole opens the idle channel and establishes the connection between the cavity 7 to the environment.
  • the handle 10 is movably mounted against the action of spring systems 28 relative to the hammer housing 1.
  • the relative position between the handle 10 and the hammer housing 1 is detected by means of a proximity sensor 29.
  • the proximity sensor 29 can either be designed such that it is only able to distinguish binary states, namely impact mode and idle mode. Alternatively, it is also possible to detect with the aid of a suitable proximity sensor, the exact position of the handle 10 relative to the hammer housing 1 and evaluate accordingly.
  • the proximity sensor 29 can also - for example, in the interior of the spring systems 28, but also independent of spring systems - a suitable force measuring sensor be arranged, which detects the force applied by the operator pressing force. Furthermore, it is possible to detect by a touch-sensitive force sensor in the handle 10 itself directly to the handle 11, the pressing force of the operator.
  • the proximity sensor 29 generates a pressing signal corresponding to the pressing force, be it binary or proportional to the pressing force, and forwards it to a controller 30.
  • the controller 30 senses that the operator is pressing the hammer to transition from the idle position to the impact position, the controller 30 drives the unillustrated valve actuator to move the valve body 25 into the in-valve position shown in FIG Fig. 3 to turn shown position.
  • a certain time delay should be achieved.
  • the controller 30 has the delay device and the valve actuator controls so that the desired time-stretched transition can be achieved.
  • variables other than the pressing force of the operator can be evaluated as the control variable.
  • variables other than the pressing force of the operator include in particular the position of the tool 8, the position of the percussion piston 6 or the position of a beatpiece, not shown in the figures, which serves as an intermediate piston between the percussion piston 6 and the tool 8. It is not necessary to capture the position precisely. It is essentially important to detect a change in position between the impact position and the neutral position and to determine whether the hammer is in idle mode or in impact mode. Thus, it is also not necessary that the position must be determined exactly. Rather, it is sufficient if the location of the relevant device whose position is to be determined, is detected in a certain area.

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

Abstract

L'invention concerne un marteau perforateur et/ou un marteau pneumatique comportant une poignée (10) et un boîtier (1) mobile par rapport à la poignée, contenant notamment un système de percussion à ressort pneumatique (4). Le ressort pneumatique du système de percussion (4) peut être alimenté par l'intermédiaire d'un canal de marche à vide (13, 15, 17, 26, 27) pouvant être ouvert et fermé par l'intermédiaire d'une soupape (16, 17, 25). La soupape (16, 17, 25) peut être ouverte et fermée en fonction d'une force de compression agissant sur la poignée (10), un dispositif de retardement (18, 20, 21, 29, 30) commandant la soupape (16, 17, 25) lors de la fermeture de telle manière que la soupape n'adopte la position correspondant à la force de compression détectée qu'après un certain délai. On obtient ainsi une transition douce entre la marche à vide et le fonctionnement percussif.

Claims (29)

  1. Marteau perforateur et/ou marteau à percussion, comportant
    - un mécanisme de percussion à amortissement pneumatique avec un piston d'actionnement (5) mobile en va-et-vient, une cavité (7) étant formée entre le piston d'actionnement (5) et le piston de percussion (6) en vue de recevoir un amortisseur pneumatique ;
    - un conduit de marche à vide (13, 15, 17) destiné à relier la cavité (7) avec l'environnement du mécanisme de percussion à amortissement pneumatique et à ventiler la cavité (7) pendant une marche à vide ;
    - un clapet (16, 17) monté dans le conduit de marche à vide (13, 15, 17) pour ouvrir le conduit de marche à vide pendant la marche à vide et fermer le conduit de marche à vide pendant la marche en mode de percussion ; et comportant
    - un dispositif de détection destiné à détecter les grandeurs de commande faisant la distinction entre la marche en mode de percussion et la marche à vide ;
    sachant que
    - le clapet (16, 17) peut être ouvert ou fermé en fonction de la grandeur de commande et, pour ce faire, est amené dans une position correspondant à la grandeur de commande ;
    caractérisé en ce que
    - il est prévu un dispositif de temporisation (18, 20, 21), par lequel le clapet (16, 17), au moment de la fermeture, est activé de telle sorte qu'il atteint avec un retard de temps la position correspondant à la grandeur de commande ; et en ce que
    - le retard de temps est choisi de telle sorte qu'il couvre un intervalle de temps de plusieurs cycles de percussion comportant chacun un mouvement de va-et-vient du piston d'actionnement (5).
  2. Marteau perforateur et/ou marteau à percussion selon la revendication 1, caractérisé en ce que le clapet (16, 17), au moment de l'ouverture, est actionné de telle sorte qu'il atteint sensiblement immédiatement la position correspondant à la grandeur de commande.
  3. Marteau perforateur et/ou marteau à percussion selon la revendication 1 ou 2, caractérisé en ce que le clapet (16, 17) change sa position, sensiblement en continu, pendant l'intervalle de temps défini par le retard de temps.
  4. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la grandeur de commande est une grandeur sélectionnée dans le groupe :
    - force de pression applicable par un utilisateur,
    - position d'un outil (8),
    - position du piston de percussion (6),
    - position d'une bouterolle,
    - position d'un organe de manoeuvre, commandant un actionnement du piston d'actionnement (5) et pouvant être manipulé par l'utilisateur.
  5. Marteau perforateur et/ ou marteau à percussion selon l'une quelconque des revendications 1 à 4, caractérisé en ce que
    - il est prévu au moins une poignée (10) avec une zone de préhension (11) pour que l'utilisateur puisse tenir et pousser le marteau perforateur et/ ou marteau à percussion ;
    - la grandeur de commande est une force de pression que l'utilisateur peut appliquer sur la poignée (10) ;
    - au moins le mécanisme de percussion à amortissement pneumatique est entouré par un carter (1) du marteau ;
    - le dispositif de détection, destiné à détecter la force de pression, est disposé dans le flux des forces entre la zone de préhension (11) et le carter (1) du marteau ;
    - le clapet (16, 17) peut être ouvert et fermé en fonction de la force de pression détectée et, pour ce faire, est amené dans une position correspondant à la force de pression ; et en ce que
    - le clapet (16, 17), au moment de la fermeture, est actionné par le dispositif de temporisation (18, 20, 21) de telle sorte qu'il atteint avec le retard de temps la position correspondant à la force de pression détectée.
  6. Marteau perforateur et/ ou marteau à percussion selon l'une quelconque des revendications 1 à 5, caractérisé en ce que sous l'effet d'une augmentation de la force de pression le marteau passe de la marche à vide à la marche en mode de percussion et sous l'effet d'une diminution de la force de pression le marteau passe de la marche en mode de percussion à la marche à vide.
  7. Marteau perforateur et/ou marteau à percussion selon la revendication 5 ou 6, caractérisé en ce que la poignée (10) est mobile par rapport au carter (1) du marteau.
  8. Marteau perforateur et/ou marteau à percussion selon la revendication 7, caractérisé en ce qu'entre la poignée (10) et le carter (1) du marteau, il est prévu un système de ressort, faisant partie du dispositif de détection, afin que la poignée (10) soit maintenue par rapport au carter (1) du marteau par une force de ressort prédéfinissable.
  9. Marteau perforateur et/ou marteau à percussion selon la revendication 8, caractérisé en ce que le dispositif de détection comporte une butée, qui est couplée à la poignée (10) et qui peut être déplacée par rapport au carter (1) du marteau au moyen de la poignée (10) à l'encontre de l'action du système de ressort, de telle sorte que son déplacement est sensiblement proportionnel à la force de pression exercée par l'utilisateur.
  10. Marteau perforateur et/ou marteau à percussion selon la revendication 8 ou 9, caractérisé en ce que le système de ressort fait aussi partie d'un dispositif destiné à neutraliser les vibrations dans la poignée (10).
  11. Marteau perforateur et/ ou marteau à percussion selon l'une quelconque des revendications 1 à 10, caractérisé en ce qu'il est prévu une gaine (16) mobile axialement, laquelle forme un élément de commande du clapet (16, 17) et dont la position axiale peut varier en fonction de la grandeur de commande, en particulier en fonction de la force de pression.
  12. Marteau perforateur et/ou marteau à percussion selon la revendication 11, caractérisé en ce que la gaine (16) est reliée à la poignée (10) dans une direction axiale, de telle sorte qu'une diminution de la force de pression exercée par l'utilisateur induit une variation immédiate et proportionnelle de la position du clapet (16, 17).
  13. Marteau perforateur et/ou marteau à percussion selon la revendication 11 ou 12, caractérisé en ce que la gaine (16) est couplée à la poignée (10) dans l'autre direction axiale de telle sorte qu'une augmentation de la force de pression et un déplacement de la poignée (10), lié à celle-ci, par rapport au carter (1) du marteau induisent, par l'intermédiaire du dispositif de temporisation, un déplacement retardé dans le temps de la gaine (16).
  14. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 1 à 13, caractérisé en ce que
    - le piston d'actionnement (5) est creux ;
    - le piston de percussion (6) est mobile axialement dans le piston d'actionnement (5) ; et en ce que
    - il est prévu dans une paroi cylindrique du piston d'actionnement (5) au moins une ouverture (13) qui, en fonction de la position axiale du piston d'actionnement (5), forme une partie du conduit de marche à vide.
  15. Marteau perforateur et/ou marteau à percussion selon la revendication 14, caractérisé en ce que le piston d'actionnement (5) est entouré par un tube (14) du mécanisme de percussion, dans lequel est prévue au moins une ouverture radiale (15), qui est associée à l'ouverture (13) dans le piston d'actionnement (5) et qui forme une partie du conduit de marche à vide.
  16. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 11 à 15, caractérisé en ce que
    - le tube (14) du mécanisme de percussion est entouré par la gaine (16) ;
    - la gaine (16) comporte une ouverture radiale (17), associée à l'ouverture radiale (15) du tube (14) du mécanisme de percussion ;
    - la gaine (16) est apte à se déplacer axialement sur le tube (14) du mécanisme de percussion à l'encontre de l'action d'un dispositif à ressort (18), de sorte que pour ouvrir le clapet, l'ouverture radiale (17) de la gaine (16) puisse être déplacée au-dessus de l'ouverture radiale (15) du tube (14) du mécanisme de percussion et, pour fermer le clapet, la gaine (16) masque l'ouverture radiale (15) du tube (14) du mécanisme de percussion.
  17. Marteau perforateur et/ou marteau à percussion selon la revendication 16, caractérisé en ce que le dispositif à ressort (18) pousse la gaine (16) dans la position de fermeture.
  18. Marteau perforateur et/ou marteau à percussion selon la revendication 16 ou 17, caractérisé en ce que
    - le dispositif de temporisation comporte une cavité (20), qui est réalisée entre la gaine (16) et le tube (14) du mécanisme de percussion et dont le volume varie en fonction de la position relative du tube (14) du mécanisme de percussion et de la gaine (16) ;
    - la cavité (20) communique avec l'environnement par l'intermédiaire d'une ouverture de temporisation (21) ;
    - en ce que l'ouverture de temporisation (21) est dimensionnée de telle sorte qu'elle garantit un flux volumique prédéterminé de l'air.
  19. Marteau perforateur et/ou marteau à percussion selon la revendication 18, caractérisé en ce que la cavité (20) comporte un clapet de retenue (22, 23), par l'intermédiaire duquel il est possible de supprimer une surpression de l'air régnant dans la cavité (20).
  20. Marteau perforateur et/ou marteau à percussion selon la revendication 18 ou 19, caractérisé en ce que, pendant une augmentation de la force de pression, la gaine (16) se déplace de telle sorte que le volume de la cavité (20) s'agrandit, la vitesse de déplacement de la gaine (16) étant limitée par le flux volumique prédéterminé de l'air par l'intermédiaire de l'ouverture de temporisation (21), en particulier plus faible qu'une vitesse relative, produite par la force de pression, entre la poignée (10) et le carter (1) du marteau.
  21. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 18 à 20, caractérisé en ce que, pendant une diminution de la force de pression, la gaine (16) se déplace de telle sorte que le volume de la cavité (20) est diminué, sachant qu'au moins une partie de l'air contenu dans la cavité (20) afflue vers l'extérieur par l'intermédiaire du clapet de retenue (22, 23), de telle sorte que la vitesse de déplacement de la gaine (16) correspond sensiblement à la vitesse relative entre la poignée (10) et le carter (1) du marteau.
  22. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 5 à 21, caractérisé en ce que
    - le dispositif de détection comporte un capteur, qui est destiné à détecter une situation, dans laquelle la poignée (10) est poussée contre le carter (1) du marteau à l'encontre de l'action du système de ressort, et qui est destiné à générer un signal de pression ;
    - le clapet comporte un élément de clapet actionnable par voie mécanique, électrique, électromécanique ou électromagnétique ; et en ce que
    - le signal de pression est destiné à être acheminé vers une commande, qui actionne l'élément de clapet en conséquence pour l'ouverture et la fermeture du clapet, la fermeture du clapet s'étendant sur un intervalle de temps déterminé.
  23. Marteau perforateur et/ou marteau à percussion selon la revendication 22, caractérisé en ce que le capteur est un capteur de proximité ou capteur de force.
  24. Marteau perforateur et/ou marteau à percussion selon la revendication 22 ou 23, caractérisé en ce que
    - il est prévu un capteur de position destiné à détecter la position dans l'espace du marteau perforateur et/ou marteau à percussion par rapport à un plan horizontal et destiné à générer un signal de position correspondant ;
    - le signal de position est destiné à être acheminé vers la commande ; et en ce que
    - la commande actionne l'élément de clapet sur la base de l'analyse du signal de pression et du signal de position.
  25. Marteau perforateur et/ou marteau à percussion selon la revendication 24, caractérisé en ce que lors de l'analyse du signal de pression et du signal de position, une divergence de la position du marteau perforateur et/ou marteau à percussion par rapport au plan horizontal est prise en compte de telle sorte que le signal de pression qui en résulte est corrigé en tenant compte des poids effectifs de la poignée (10), du carter (1) du marteau et des composants, montés dans ce dernier, ainsi que d'un outil.
  26. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 1 à 25, caractérisé en ce qu'une position avant, par référence à une direction de travail, de l'outil (8), de la bouterolle et/ou du piston de percussion (6) est un critère pour la marche à vide, alors qu'une position, décalée vers l'arrière par rapport à la position avant, de l'outil (8), de la bouterolle et/ou du piston de percussion (6) est un critère pour la marche en mode de percussion.
  27. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 1 à 26, caractérisé en ce que le dispositif de détection comporte un dispositif destiné à déterminer la position de l'outil (8), de la bouterolle et/ou du piston de percussion (6) en deux emplacements au moins, un emplacement pouvant être associé à la marche à vide et l'autre à la marche en mode de percussion.
  28. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 1 à 27, caractérisé en ce qu'une position de marche à vide de l'accélérateur est un critère pour la marche à vide, alors qu'une position de service de l'accélérateur est un critère pour la marche en mode de percussion.
  29. Marteau perforateur et/ou marteau à percussion selon l'une quelconque des revendications 1 à 28, caractérisé en ce que
    - le dispositif de détection comporte un capteur destiné à détecter la grandeur de commande et à générer un signal de commande ;
    - le clapet comporte un élément de clapet actionnable par voie mécanique, électrique, électromécanique ou électromagnétique ; et en ce que
    - le signal de commande est destiné à être acheminé vers une commande, qui actionne l'élément de clapet en conséquence pour l'ouverture et la fermeture du clapet, la fermeture du clapet s'étendant sur un intervalle de temps déterminé.
EP06754484A 2005-06-22 2006-06-21 Marteau perforateur et/ou marteau pneumatique a commande de la marche a vide Not-in-force EP1893388B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005028918A DE102005028918A1 (de) 2005-06-22 2005-06-22 Bohr- und/oder Schlaghammer mit Leerlaufsteuerung
PCT/EP2006/005978 WO2006136401A1 (fr) 2005-06-22 2006-06-21 Marteau perforateur et/ou marteau pneumatique a commande de la marche a vide

Publications (2)

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EP1893388A1 EP1893388A1 (fr) 2008-03-05
EP1893388B1 true EP1893388B1 (fr) 2008-11-26

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US (1) US8235136B2 (fr)
EP (1) EP1893388B1 (fr)
JP (1) JP5096327B2 (fr)
CN (1) CN101203358B (fr)
DE (2) DE102005028918A1 (fr)
ES (1) ES2314919T3 (fr)
WO (1) WO2006136401A1 (fr)

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JP5096327B2 (ja) 2012-12-12
ES2314919T3 (es) 2009-03-16
DE102005028918A1 (de) 2006-12-28
WO2006136401A1 (fr) 2006-12-28
DE502006002207D1 (de) 2009-01-08
CN101203358A (zh) 2008-06-18
US8235136B2 (en) 2012-08-07
US20100163260A1 (en) 2010-07-01
EP1893388A1 (fr) 2008-03-05
CN101203358B (zh) 2012-05-30
JP2008543588A (ja) 2008-12-04

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