EP1893388A1 - 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

Info

Publication number
EP1893388A1
EP1893388A1 EP06754484A EP06754484A EP1893388A1 EP 1893388 A1 EP1893388 A1 EP 1893388A1 EP 06754484 A EP06754484 A EP 06754484A EP 06754484 A EP06754484 A EP 06754484A EP 1893388 A1 EP1893388 A1 EP 1893388A1
Authority
EP
European Patent Office
Prior art keywords
drilling
valve
percussion
handle
percussion hammer
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
EP06754484A
Other languages
German (de)
English (en)
Other versions
EP1893388B1 (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

Links

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 drill and / or percussion hammer (hereinafter referred to simply as a hammer) with a pressure-dependent idle control is known from DE 101 45 464 A1.
  • 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 hammer described in DE 101 45 464 A1 has already proven itself in practice. However, it has been found that the principle described there can be further improved. In particular, the fact that the hammer performs certain proper movements during the transition from idle mode to impact mode by the activating air spring impact mechanism and the resulting oscillations, so that the hammer housing moves relative to the handle held by the operator, there is the possibility that the valve is closed prematurely, so that the impact operation ultimately but suddenly unexpectedly for the operator.
  • 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 idling channel in an idle mode and to close the idle channel in a hammering 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 an unpredictable by the operator or unwanted proper movement of the Hammergeophou- ses not correspondingly bypassing, corresponding to the increased pressure in this case closing the idle channel the valve takes place. Rather, the valve changes independently of such short-term These actions have their position extended in time and only take on the position corresponding to the recorded tax variable after a certain period of time. As a result, the transition from idle mode to beat mode is relatively smooth and predictable for the operator.
  • 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.
  • the time delay ie the period during which the valve is closed, such that it covers a period of several, each comprising a reciprocating motion of the drive piston impact cycles.
  • 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.
  • 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. be a throttle or throttle lever in a pneumatic hammer, which is between an open and a closed position movable.
  • 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 one of applied to the operator on 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 relative to the
  • Relative movement between the hammer housing and the handle is not 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 a known from DE 101 45 464 Al sleeve.
  • the sleeve is provided with the handle only in an axial direction, e.g. 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 is coupled in such a way that an increase in the pressing force and an associated displacement of the handle relative to the hammer housing via the delay device temporally delayed or time-stretched displacement of the sleeve causes.
  • time-delayed or stretched displacement is to be understood here that the sleeve moves at a substantially lower speed than the relative speed between the handle and the hammer housing is.
  • 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 or is limited.
  • 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 starting 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 smaller 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 device 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 at at least two locations, wherein the one position is the idle operation and the other place the impact mode assigned. 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
  • 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 determine the period of time that is required for closing. In this case, the detection device can also determine whether the operator initially only lightly 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.
  • Fig. Ia is a partial section through a drilling and / or percussion hammer according to the invention in idling operation;
  • FIG. 1b shows an enlarged detail of FIG. 1a
  • FIG. 2a shows a partial section of the drilling and / or percussion hammer corresponding to FIG. 1a, but in impact position;
  • FIG. 2b shows an enlarged detail of FIG. 2a
  • Fig. 2c is a further detail enlargement to Fig. 2a.
  • Fig. 3 is a section through another embodiment of a drilling and / or percussion hammer according to the invention.
  • FIG. 1 a shows a hammer called a hammer and / or percussion hammer, with a hammer housing 1 and a large part 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. Ia a breaker chisel), which is held by a tool holder 9.
  • the hammer housing 1 accommodates at least part of the above-mentioned 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 1 1, where 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 does not surround the hammer housing 1 at all, but is held behind the hammer housing 1 only by the vibration decoupling device.
  • 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 handle cover 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 grip hood 2 can move relative to the hammer housing 1.
  • 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 handle position 1 1, a detection device is provided.
  • the detection means is that the pressing force against the action of a spring means in the vibration decoupling device causes a certain displacement of the grip 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. Ia to Ic show the hammer in neutral position when the cavity 7 is in communication with its environment, that is ventilated.
  • the exact structure is better recognizable in the detail enlargements Ib and Ic.
  • 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 15 corresponding to the radial opening 15 of the percussion mechanism tube 14 is formed.
  • a sleeve 16 in the wall of which a radial opening 15 corresponding to the radial opening 15 of the percussion mechanism tube 14 is formed.
  • FIGS. 1 b and 1 c show, the opening 13 and the radial openings 15 and 17 are superimposed in such a way that they form an idling channel, via which the cavity 7 is brought into contact with the surroundings of the air spring impact mechanism 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 mode on the radial opening 15, or, as later explained with reference to FIGS. 2b and 2c, is moved in impact mode in 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 operator applies no or only a small pressure force to the handle 10. It may even pull up the hammer on the handle 10.
  • the vibration decoupling device not shown, ensures that the handle cover 2 with respect to the hammer housing 1, the idle position shown in Fig. Ia (home or rest position) occupies.
  • the pin 19 presses the sleeve 16 against the action of the spring 18 into the position that can be seen, in particular in FIG. 1 b, so that the idling channel is opened and the air spring is released in the cavity 7.
  • the effect of the spring 18 is exceeded by the stronger force effect of the vibration decoupling device.
  • 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 radial opening 17 is moved away only slowly from the radial opening 15, so that the idling channel is closed only slowly. This means that the transition from idle mode to beat mode is very smooth and easily predictable and controllable by the operator.
  • 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 reached 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 handle cover 2 and the handle 10, respectively) not immediately to a sudden change
  • the cross sections in the idle channel leads, 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 pressure 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.
  • Fig. 3 shows a section through a further embodiment of the hammer drill according to the invention, which is based on the illustration of FIG. 4 from DE 101 45 464 Al.
  • DE 101 45 464 A1 a hammer has been described with reference to this figure, 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 on mechatronic Paths done.
  • 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 Leerlaufka- 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 at the handle point 1 1, 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 detects 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 to the position shown in FIG to twist.
  • the controller 30 drives the unillustrated valve actuator to move the valve body 25 to the position shown in FIG to twist.
  • 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 striking piston 6 or the position of a stopper, not shown in the figures, which serves as an intermediate piston between the striking piston 6 and the tool 8. It is not necessary to capture the position precisely. It is essential 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.
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)

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

Family

ID=36910831

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06754484A Not-in-force EP1893388B1 (fr) 2005-06-22 2006-06-21 Marteau perforateur et/ou marteau pneumatique a commande de la marche a vide

Country Status (7)

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US (1) US8235136B2 (fr)
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DE102005028918A1 (de) 2006-12-28
JP5096327B2 (ja) 2012-12-12
US20100163260A1 (en) 2010-07-01
EP1893388B1 (fr) 2008-11-26
JP2008543588A (ja) 2008-12-04
ES2314919T3 (es) 2009-03-16
CN101203358B (zh) 2012-05-30
DE502006002207D1 (de) 2009-01-08
US8235136B2 (en) 2012-08-07
WO2006136401A1 (fr) 2006-12-28
CN101203358A (zh) 2008-06-18

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