WO2005007351A1 - Arbeitsgerät mit handgriffabfederung - Google Patents
Arbeitsgerät mit handgriffabfederung Download PDFInfo
- Publication number
- WO2005007351A1 WO2005007351A1 PCT/EP2004/007743 EP2004007743W WO2005007351A1 WO 2005007351 A1 WO2005007351 A1 WO 2005007351A1 EP 2004007743 W EP2004007743 W EP 2004007743W WO 2005007351 A1 WO2005007351 A1 WO 2005007351A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- spring
- handle
- air
- vibration exciter
- vibration
- Prior art date
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
- B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
- B25F5/006—Vibration damping means
-
- 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
- B25D17/00—Details of, or accessories for, portable power-driven percussive tools
- B25D17/24—Damping the reaction force
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/221—Sensors
Definitions
- the invention relates to a hand-held tool according to the preamble of claim 1 and a device for vibration isolation of a handle in a tool.
- Hand-held tools in particular rotary and / or impact hammers (hereinafter referred to as hammers), rammers or the like. often have a vibration excitation device for generating a vibration required to achieve the desired work effect.
- a vibration excitation device for generating a vibration required to achieve the desired work effect.
- this is usually a percussion mechanism with which an impact effect is achieved against a tool.
- the strong vibration should affect the operator holding the implement with his hands as little as possible.
- the work tools usually have a device with which vibrations, shocks or impacts can be generated. Such devices are collectively referred to below as “vibration exciters”.
- a vibration decoupling device between the handle and the vibration exciter.
- a vibration decoupling device is usually implemented with the aid of passive spring damper elements.
- rubber elements can be inserted between the handle and the vibration exciter in order to achieve a certain vibration decoupling. Due to the limited installation space, the spring elements can have only small spring travel, which limits their suitability for vibration isolation of the handle. On the other hand, the spring elements cannot be made too soft to allow the operator to guide the implement precisely.
- DE 196 46 622 AI describes an implement that can be guided on a handle.
- the handle is actively vibration-damped by an actively controlled or regulated compensation element, the compensation element generating a compensating force or movement as a function of the vibration that can be transmitted to it in the implement.
- This compensation effect makes it possible to largely compensate for the vibration occurring in the implement, so that the handle connected downstream of the compensation element is essentially free of vibrations.
- the constructional and control engineering outlay for such a device is not insignificant.
- DE 101 00 378 AI describes a hand tool that has a vibration exciter and one between the vibration exciter and has a handle arranged vibration isolation device.
- the vibration isolation device has an actuator, via which the operating force can be at least partially compensated with an actuating force.
- the positioning force is largely independent of the actually existing vibration to be isolated.
- the vibration itself is compensated for by a spring element with a relatively soft characteristic, which is arranged parallel to the actuator.
- the actuator itself therefore does not perform any vibration damping function. Rather, it ensures that the working position of the spring element, ie its pretension, is always in a predetermined range, so that the spring element can compensate for the vibration present.
- the actuating force of the actuator is automatically set by the operator as a function of the operating force acting from outside, in particular the pressing force. In this respect, one can speak of a "semi-active" vibration isolation.
- the actuator can be designed electrically, electromagnetically or hydraulically, which requires considerable construction effort.
- EP 0 206 981 A2 describes a hand tool with a drive device which generates vibrations.
- a handle On a housing that accommodates the drive device, a handle that can be displaced to a limited extent between two stops parallel to the main vibration axis is provided.
- the stop of the handle arranged in the feed direction of the hand tool is designed as an electromagnet which, regardless of the position of the handle relative to the housing, exerts a constant, controllable force on both the handle and the housing. Vibration isolation should be achieved in this way.
- the invention is based on the object of designing a hand-held implement with semi-active vibration isolation in such a way that the construction effort is minimized. Furthermore, the invention is based on the object of specifying a device for vibration isolation of a handle in a working device, with which reliable and simple vibration decoupling of the handle is ensured, even in different operating states.
- the object is achieved by a hand-held implement according to claim 1 and by a device according to claim 16 Vibration isolation of a handle solved on a working device.
- a hand-held working device has a vibration isolation device between a first unit comprising a vibration exciter and a second unit that is movable in at least one working direction relative to the first unit.
- Part of the vibration isolation device is an actuator for generating an actuating force, with which an operating force acting in the working direction between the first and the second unit, eg. B. a pressing force is at least partially compensated.
- the actuator is operated pneumatically.
- a pneumatically operated actuator has considerable advantages over the drive principles for actuators described in DE 101 00 378 AI. Firstly, no additional medium (e.g. hydraulic oil) is required. Air as a medium is always available in sufficient quantities and can be processed without any special sealing effort. Any leakage losses are not critical. On the other hand, the regulatory effort in relation to e.g. B. electrical or electromagnetic actuators significantly lower. In addition, the energy expenditure for electrical actuators is comparatively high, since the actuators have to react quickly, which is only possible through an appropriate available power.
- no additional medium e.g. hydraulic oil
- Air as a medium is always available in sufficient quantities and can be processed without any special sealing effort. Any leakage losses are not critical.
- the regulatory effort in relation to e.g. B. electrical or electromagnetic actuators significantly lower.
- the energy expenditure for electrical actuators is comparatively high, since the actuators have to react quickly, which is only possible through an appropriate available power.
- the handle air spring is so called in order to distinguish it conceptually from an air spring that is formed in particular in an air spring hammer mechanism, but is of no further interest here.
- the handle air spring can be changed by different air filling and thus adjustable. In particular, the pressure in the air spring and / or the air volume can be changed.
- the actuator thus essentially forms a pneumatic spring with an adjusting device.
- the filling of the handle air spring can be changed with compressed air, so that the spring properties of the handle air spring can be changed accordingly.
- an air spring has a progressive spring characteristic.
- the progressiveness of the air spring can be set in a corresponding manner by means of a suitable spring control device, which is explained further below.
- the primary task of the actuator is to compensate for the operating force acting between the first and the second unit, so that the actual vibration isolation is provided by a spring element arranged parallel to the actuator can be taken over.
- the actuator since the actuator is operated pneumatically according to the invention, due to the compressibility of the air, it already has good spring properties and is therefore also used for vibration isolation.
- a hydraulically operated actuator could not perform such vibration isolation due to the incompressibility of hydraulic fluid. Electrically operated actuators would always try to counteract a deflection caused by vibrations and thus prevent a spring effect.
- the working device is a hammer drill or impact hammer (hereinafter referred to as a hammer).
- the second unit carries a handle on which the operator can guide and hold the implement.
- an air spring hammer mechanism known per se is provided, which has a drive piston driven by a motor for driving a percussion piston.
- An air spring is formed between the drive piston and the percussion piston, which transmits the movement of the drive piston to the percussion piston, which in turn strikes a tool.
- the drive piston for generating compressed air is Dining the actuator trained.
- a further advantage of a pneumatically operated actuator becomes clear.
- the drive piston of the percussion mechanism is already designed to generate compressed air, although in known percussion mechanisms only to drive the percussion piston.
- the drive piston now has a second function, namely the generation of compressed air for the actuator.
- a pressure medium such as. B. a hydraulic pump or the like.
- the z from the drive piston. B. in its return movement, forwards driving the percussion piston, displaced air can be supplied to the actuator as compressed air.
- the actuator has a compressed air reservoir that can be filled with compressed air by the drive piston.
- the compressed air reservoir not only serves as a compressed air supply for the actuator, from which compressed air can be drawn and fed to the actuator if required.
- the compressed air reservoir also homogenizes the compressed air supplied by the drive piston due to its reciprocating movement.
- the actuator has the compressed air reservoir, a valve device, the handle air spring and a handle piston.
- the compressed air reservoir can be connected to the handle air spring via the valve device, while the handle air spring acts on the handle piston which is connected to the handle.
- the core of the actuator is thus formed by the handle air spring.
- the valve device ensures that only as much compressed air from the compressed air reservoir reaches the handle air spring as is required.
- the valve device is advantageously designed such that when the handle piston has a volume circumscribing the handle air spring Reduced by a predetermined amount, compressed air can be fed from the compressed air reservoir into the handle air spring in order to achieve the specified dimension 3 for the volume of the handle air spring again. If the operator presses against the handle with increased operating force, he displaces the handle and thus the handle piston against the action of the handle air spring. Due to the compressibility of the air, the volume of the handle air spring is reduced until a predetermined minimum limit is finally reached. The valve device then opens the connection between the compressed air reservoir and the handle air spring, so that the air pressure in the handle air spring is increased. As a result, the force acting on the handle piston increases and pushes the piston again against the action of the operating force. With an appropriate setting of the system, it can thus be ensured that the handle barely changes its relative position with respect to the first unit having the air spring hammer mechanism.
- valve device also has an outlet valve in order to discharge compressed air from the handle air spring if the volume of the handle air spring exceeds a predetermined maximum value due to a displacement of the handle piston.
- This case can e.g. B. occur when the operator has first pressed the handle with high operating force and then finally withdraws the operating force because he wants to lift the device.
- the high air pressure in the handle air spring would push the handle piston and thus the handle further outwards, which would lead to the vibration isolation not working in the optimal operating range, especially when the device is relocated with less operating force.
- the outlet valve which opens a connection from the handle air spring to the outside when the handle air spring displaces the handle piston due to a reduction in the operating force and thereby increases above a predetermined maximum value.
- the valve device is preferably coupled to the handle piston.
- the handle piston can be moved between two extreme positions, depending on the pressure exerted by the handle air spring. Before these two extreme positions, piston positions can be defined, which correspond to a minimum value and a maximum value for the volume of the handle air spring. Compressed air should not be supplied to or removed from the air spring handle within these values.
- the valve device opens a respectively assigned valve, i. H. either an inlet valve that connects the compressed air reservoir and the handle air spring, or the outlet valve for discharging compressed air to the outside.
- the valve device has corresponding inlet channels for the inlet valve and outlet channels for the outlet valve, which are opened or closed depending on the position of the handle piston. The channels and their closing and opening mechanisms can be easily combined with the handle piston.
- a sensor is provided with which the relative position of the first and the second unit, that is to say in particular of the main housing receiving the striking mechanism and the drive, and of the handle which is relatively movable in relation thereto can be determined.
- the sensor should be arranged in such a way that it can at least detect the point of the optimal relative position between the two units.
- the sensor and the valve device are preferably connected to a controller, the valve device being controllable by the controller in such a way that a compressed air condition prevails in the handle air spring such that the relative positions of the first and second units detected by the sensor are in a predetermined fluctuation range being held.
- the fluctuation range is e.g. B. by the above-described maximum value and minimum value for the volume of the handle air spring Are defined.
- the control system monitors the relative position between the first and the second unit with the aid of the sensor and can trigger appropriate countermeasures if the specified fluctuation range is exceeded. On the one hand, it is thus possible to allow compressed air to flow from the compressed air reservoir into the handle air spring via the inlet valve. On the other hand, the control can also ensure that the handle air spring is relieved via the outlet valve.
- a spring device is arranged parallel to the actuator between the first and the second unit.
- the spring device can have a softer spring characteristic than the actuator.
- the spring device it is possible for the spring device to have a spring stiffness that is at least so great that the movement of an amplitude of the oscillation can be absorbed by the spring device without the spring device blocking.
- the force acting between the first unit and the second unit is essentially composed of two components: on the one hand, there is the operating force, which is essentially applied by the operator by pressing the handle from the outside. The operating force is superimposed on a force which is generated by the vibration excited in the first unit.
- the configuration according to the invention makes it possible for the operating force to be largely completely absorbed and compensated for by the actuator, the actuator ideally should have the spring stiffness “zero” or a very low spring stiffness. A slight increase in the force acting on the actuator in the low-frequency range would cause the actuator tappet to be displaced without the actuator initially countering an increased counterforce. The actuator force would only be increased if the limit positions were exceeded.
- the effect of the spring device which absorbs the changes in force or displacement caused by the vibration amplitude, is superimposed.
- the vibration amplitude in turn, is not or hardly influenced by the operating force.
- the spring device must therefore have a spring have rigidity in order to be able to absorb the oscillation amplitude completely without a block setting occurring, ie without the spring device being compressed so far that corresponding stops come into contact and prevent further compression of the spring. Since the vibration amplitudes occurring during operation are essentially known beforehand, the spring device can be designed accordingly.
- the spring stiffness of the spring device should be as low as possible in order to enable a particularly soft suspension.
- the actuator it is thus possible for the actuator to compensate for the operating force acting on the implement from the outside between the first and the second unit in the manner described above, as a result of which the operating force does not cause any appreciable deformation of the soft spring device.
- the spring device is suitable for compensating for the higher-frequency vibrations caused by the vibration exciter in the first unit, as a result of which the second unit is essentially isolated from vibrations.
- the spring device therefore does not have to be deformable over the entire value range of conceivable operating forces, which would lead to a large overall length of the spring due to the soft spring characteristic. Rather, due to the compensation of the operating force by the actuator, it is possible that the spring device only has to provide a relatively small operating range for the relative movement between the first and the second unit, so that the spring device is short despite the soft spring characteristic.
- the actuating force generated by the actuator can be changed cyclically, the change taking place at the same frequency with which the drive piston moves.
- the vibration generated by the drive piston in the air spring hammer mechanism inevitably has exactly the same frequency with which the drive piston also moves. Accordingly, the frequency of the vibration to be isolated is already predetermined by the frequency of movement of the drive piston. If the actuator now operates at the same frequency, the pulsating effect of the actuator allows the actuator piston to compensated for the vibration.
- any necessary phase shifts with respect to the movement of the drive piston and the actuating work of the actuator can be solved by suitable coupling of valves of the valve device and interposition of the compressed air reservoir. So it is z.
- the drive piston it is possible for the drive piston to pump air into the compressed air reservoir when the percussion piston is acted upon and the impact piston has carried out the blow when it moves back.
- the valve between the compressed air reservoir and the handle air spring opens in order to increase the pressure in the handle air spring and thereby increase the force effect.
- the handle air spring is emptied while the compressed air reservoir is refilled.
- the maximum actuating frequency of the actuator can be lower than the frequency of the vibration generated in the first unit, that is to say in particular than the movement frequency of the drive piston. This ensures that the actuator only compensates for the external operating force, but does not actively counteract the vibration. Instead, the vibration is compensated in the manner described above by the softer spring device or - due to the compressibility of the air - passively also by the actuator.
- a compressed air generating device which is driven by the drive of the working device and which generates compressed air for the actuator independently of the actual working functions of the device.
- z. B a small screw compressor.
- the actuating force of the actuator should be adjustable such that a fluctuation range for those caused by different operating forces
- Relative positions between the first and the second unit is ensured, which is smaller than a fluctuation range that the relative positions between the first and the second unit with equally different operating forces, but without the compensating effect of the actuating force of the actuator.
- the actuator ensures that this fluctuation range is as small as possible, B. with the help of the parallel spring device to achieve the best possible vibration isolation.
- a force-generating pneumatic actuator which compensates for the pressure force averaged over a certain period of time, as in the case of level regulation.
- the actual vibration isolation is achieved either only by the spring characteristic of the air cushion in the hand-held air spring itself or additionally by the parallel connection of the passive spring device with a sufficiently low spring stiffness. This means that the flat spring characteristic curve is displaced during the oscillation process with changing contact force in such a way that the oscillation ideally oscillates around a fixed point.
- Even if essentially a semi-active vibration isolation has been described above, it is conceivable, in particular with the mechatronic variant, to achieve fully active compensation with basically the same design, in which case the demands on sensors, controls and valves are higher due to the increasing switching frequencies are. Conversely, with semi-active vibration isolation, the demands on the components are significantly lower, because the actual vibration isolation is only passive.
- the force properties of the actuator which can also consist of several smaller actuators, and the passive spring device, which in turn can also have several spring elements, are to be coordinated with one another in such a way that at least the maximum conceivable operating force can be compensated for.
- the actuator which can also consist of several smaller actuators
- the passive spring device which in turn can also have several spring elements
- the aim should be to make the handle air spring as large as possible because then the relative volume change due to the movement of the handle is small and the effective force remains almost constant.
- the piston area of the handle piston is large enough, the operating pressure in the handle air spring can be kept low.
- the change in the spring stiffness of the air spring compared to the change in the operating force can thus be kept low.
- the device for vibration isolation has a vibration exciter and a relative to the vibration exciter along a main direction, for. B. the working direction of the implement, movable handle.
- a vibration decoupling device is provided, which has a spring device via which a substantial part of the forces acting between the handle device and the vibration exciter are transmitted.
- the vibration decoupling device also has a spring control device for changing the spring stiffness and / or the pretensioning of the spring device as a function of a force acting in the main direction between the handle device and the vibration exciter, in particular the force exerted by the operator on the handle device holding force exerted in the main direction.
- a position (relative position) can also be used as the manipulated variable.
- a spring that is as soft as possible that is to say a spring device with low spring stiffness
- a soft spring has the disadvantage that even small forces can result in a considerable deformation path of the spring.
- the overall length in the main direction of the implement is significantly increased.
- a spring device with a hard characteristic i.e. a stiff spring, allows the installation space to be minimized. At the same time, however, the vibrations of the vibration exciter are only incompletely prevented from the handle.
- the invention now makes it possible, with the aid of the spring control device, to adapt the spring stiffness or, optionally, alternatively or additionally, the pretensioning of the spring device to the respective external conditions, in particular the effective force, and to adjust the spring properties so that the permissible spring travel and the permissible rela- tive shift between handle device and vibration exciter can be used.
- the force applied by the operator changes, if at all, only relatively slowly in a low-frequency range. Even an impact load by the operator occurs at a low frequency.
- the vibrations generated by the vibration exciter in the implement are of higher frequency.
- the spring control device does not record the changes in force caused by the vibrations between the handle device and the vibration exciter. The spring control device thus only reacts to the forces applied by the operator by holding or pressing the implement.
- the vibration path available for vibration isolation would be increasingly restricted. This is compensated for by the spring control device in that when the operator has a static holding force and thus a zero position of the vibration, the handle device is displaced relative to the vibration exciter such that the handle device is in a predetermined desired position.
- the spring control device increases the spring stiffness in order to compensate the operator force with sufficient spring force. From a static point of view, the grip device thus remains in the predetermined target position. When the vibration is applied, the grip device can move relative to the vibration exciter within a predetermined working range because the higher-frequency force changes caused by the vibration are not corrected.
- the relative position of the grip device to the vibration exciter is kept in the predetermined working range by the spring control device in conjunction with the force acting.
- the spring control device thus ensures that the relative position always remains within the predetermined working range. In this way, extreme positions and thus z. B. a solid contact between the handle device and vibration exciter can be avoided by touching, in which the vibrations would be completely transmitted to the handle device.
- the spring control device strives for the handle device to be held essentially in a desired position in the work area, even with a changing holding force, which corresponds to a predetermined relative position between the handle device and the vibration exciter. It is particularly advantageous if the desired position corresponds at the same time to a central position of the work area, so that the grip device can be moved forwards and backwards from the central position over essentially the same length of movement to respective limit or end positions along the main direction. In this way, the handle device can swing symmetrically about the central position and thereby compensate for the vibration generated by the vibration exciter.
- the spring device can be controlled by the spring control device in such a way that the spring device has an increased rigidity in an idling mode in which the force acting between the handle device and the vibration exciter is below a predetermined limit value. It has been found that hammers in particular have a tendency to jump away from the attachment point when they are attached to a new drilling site. If the spring device has a soft characteristic curve, it is in principle difficult to guide the implement, which further promotes jumping away. If, however, the spring device has an increased rigidity, the implement can be guided particularly securely when the attachment is applied, if the operator does not yet press the device with full force, that is to say which is below the predetermined limit value.
- the stiffness of the spring device can be reduced by the spring control device in such a way that the handle device can be in the desired target position of the working area ,
- the spring device When starting the work process, in which the implement is still in idle mode, the spring device is therefore stiff in order to enable good maneuverability. The moment the operator presses against the implement and desires a transition from idle to work, the spring stiffness is reduced to achieve the improved vibration isolation. The spring stiffness will then inevitably not be too low, since the pressing force must be compensated by the operator. Accordingly, good operability of the implement is guaranteed in the work operation.
- the spring device has an air spring which acts between the handle device and the vibration exciter and which preferably receives air from an air pump.
- the air pump can be operated by a drive motor of the implement.
- the air pump can be coupled to a fan wheel for the drive motor or can be arranged as an additional pump element.
- the air pump is representative of many other possibilities for forming an air pressure generating device with which pressurized air can be supplied to the air spring. Accordingly, when an air pump is referred to below, this is also generally understood to mean an air delivery device or an air pressure generating device.
- the air pump is operated by the oscillating relative movement between the handle device and the vibration exciter. Because of the relative mobility of the handle device required for the vibration isolation, a drive movement is present which can be used advantageously for the air pump.
- the air pump has a pump chamber provided between the handle device and the vibration exciter, the volume of which constantly changes as a result of the oscillating relative movement.
- the air pump can also be arranged between the vibration exciter and a third mass. Air can flow into the pump chamber from the surroundings via a first check valve when the volume of the pump chamber increases.
- the air can be conveyed from the pump chamber into an air spring chamber via a second check valve, in which the air spring forms when the volume of the pump chamber decreases with a corresponding counter-movement of the handle device.
- the interplay between the first and the second check valve ensures an essentially constant supply air flow from the air pump to the air spring, averaged over time.
- the spring control device has a valve device by means of which the exhaust air flow from the air spring can be controlled as a function of the relative position of the handle device.
- the rigidity of the spring device can thus be adjusted by regulating the exhaust air flow. If more air flows out of the air spring than is supplied by the air pump, the spring stiffness is reduced. Conversely, the spring stiffness can be increased in that the exhaust air flow is set lower than the supply air flow, so that in total more air flows into the air spring.
- the valve device has a valve opening which is evident when the handle device is further away from the vibration exciter. This allows air to flow out of the air spring, reducing the spring stiffness. If the operator's pressing force remains unchanged, this leads to the handle device moving closer to the vibration exciter. If the handle device has approached the vibration exciter beyond the target or middle position of the work area, the valve opening can be at least partially closed again. This increases the air pressure in the air spring and the air spring becomes stiffer. Accordingly, the handle device can no longer approach the vibration exciter. If necessary, the handle device is even pushed back by the ever increasing air pressure in the air spring, so that it assumes the desired position.
- the spring control device has a valve device by means of which the supply air flow to the air spring can be controlled as a function of the relative position of the handle device.
- the exhaust air flow from the air spring is essentially constant.
- the air pressure in the air spring can thus be regulated in a manner similar to that already described above.
- the pressure increase is not achieved by adding to the amount of gas in the spring volume of the air spring achieved, but by reducing the volume with a constant amount of gas.
- This z. B. can be done by an actuator actuator task z. This can be done, for example, by introducing or discharging a liquid into a cavity coupled to the air spring - separated from the actual air volume of the air spring by a membrane or a piston. Alternatively, a piston or a bellows wall can be moved by a mechanical drive and thus change the volume of the amount of air in the air spring.
- the gas space for the air spring is hermetically sealed. It could therefore also be filled with a gas other than air. For example, if a single-atom gas (noble gas) were used, the adiabatic losses would be lower, so that the "air spring” (better here: gas spring) would heat up less. It is recommended to fill the spring with helium, neon, argon (inexpensive) or krypton.
- air spring is expressly intended to include gas springs with fillings other than air.
- the designation as an air spring is therefore only used for easier understanding, but should not be understood in this context to mean that only spring fillings with air are recorded. In this sense, an air spring is synonymous with a gas spring.
- the handle device can have at least one, but also two or more handles.
- an elastic stop is provided between the handle device and the vibration exciter. At least part of the force acting between the handle device and the vibration exciter can be transmitted via the stop if the spring stiffness of the spring device is not sufficient to transmit the entire force.
- the stop corresponds to a classic spring element (e.g. a rubber spring or a foam element). However, it only transfers forces in one direction. This can ensure that, for. B. the pressing or holding force of the operator if necessary from the handle device can be transferred directly to the vibration exciter via the stop.
- the elastic stop ensures that vibration decoupling is also possible in this case, albeit to a lesser extent.
- a second stop can also be provided to absorb forces in the opposite direction, in particular if the implement is quickly relieved of load by the operator or if the supporting surface suddenly yields under the action of the pressing force.
- the implements affected by the invention are often used in a dusty environment (e.g. for demolition work).
- the air sucked in for filling the air spring should therefore be cleaned at least by a filter.
- these filters will quickly become occupied, which can lead to clogging or throttling of the intake air flow for the air spring if insufficient maintenance is required, but also to the passage of larger amounts of dust.
- increased wear particularly due to pushing relative movements, is to be expected. Therefore, it is advantageous if the air released from the air spring in a largely enclosed space, for. B. a bellows or a filter bag, at least partially collected and from there can be reused for refilling the air spring.
- the drain opening from the air spring and the suction opening of the air pump can then open into this room.
- the air for the air spring can accordingly be supplied from an air reservoir. It is particularly advantageous if the air discharged from the air spring can be returned to the air reservoir. This means that the air can be buffered in the air reservoir serving as an intermediate reservoir before it is blown back into the air spring under pressure via the air pump. In this way, it is possible to keep the exchange of the air provided for the air spring with the ambient air low, so as to prevent contamination, e.g. B. by dust to minimize. An essentially closed air circuit is thus achieved, in which only the mostly unavoidable leakage losses due to fresh air from the outside need to be compensated.
- the volume of the required Air volume can adjust.
- Fig. 1 shows schematically a sectional side view of an implement according to the invention
- FIG. 2 shows the implement from FIG. 1, with the hammer mechanism partially cut open and the actuator according to the invention
- FIG. 3 shows an enlarged detail from FIG. 2;
- Fig. 5 shows a schematic section through a working device with the device according to the invention for vibration isolation of a handle.
- Fig. 1 shows the basic structure of the implement according to the invention using the example of a hammer drill and / or percussion hammer.
- a first unit 1 and a second unit 2 are connected to one another via a vibration isolation device 3.
- the vibration isolation device 3 has an actuator 4 and a spring device 5. Furthermore, 2 guide elements 6 are arranged between the first unit 1 and the second unit, which are intended to prevent the two units 1, 2 from tilting.
- the guide elements 6 can be made of rubber or plastic and in this respect also contribute to vibration isolation.
- a drive motor is arranged in a known manner - therefore not shown in detail - which moves a drive piston 7, which can be seen in FIG. 2, back and forth via a crankshaft.
- a drive piston 7 Before the drive piston 7, d. H. in a working direction A, an impact piston, not shown, is arranged.
- the movement of the drive piston 7 forms an air spring 8 between the drive piston 7 and the percussion piston, which in turn drives the percussion piston so that it strikes against a tool end (not shown) or an intermediate striker.
- the mode of operation of such air spring percussion mechanisms is known, so that no further explanation is necessary at this point.
- a handle 9 is formed on the second unit 2 at the rear end.
- FIGS. 2 and 3 essentially relate to the same representation, they are described together below.
- the actuator 4 has a compressed air reservoir 10, a handle air spring 11 and a handle piston 12.
- a component of the actuator is also a valve device, which comprises an inlet valve 13 and an outlet valve 14.
- the inlet valve 13 and the outlet valve 14 essentially consist of a groove milled into a cylinder, which faces a closed cylinder surface. The function will be explained in more detail later.
- the compressed air reservoir 10 is also equipped with an inlet check valve 15 and an outlet check valve 16.
- the handle piston 12 is positively connected to the handle 9 in the axial direction.
- an annular rubber or foam element 17 is provided. In any case, it is ensured that the axial movement of the handle piston 12 is transmitted exactly to the handle 9, and vice versa.
- the drive piston 7 sucks air from the environment into a rear space 19 via a check valve 18 when it moves forward in the working direction A.
- the air from the rear space 19 is pressed into the compressed air reservoir 10 via the inlet check valve 15.
- air is then sucked in again via the check valve 18. If an overpressure arises in the compressed air reservoir 10, this can be reduced via the outlet check valve 16.
- the handle 9 moves forward in the working direction A relative to the first unit 1.
- the handle piston 12 also penetrates deeper into the compressed air reservoir 10 with a plunger 20 , until a communicating connection between the compressed air reservoir 10 and the handle air spring 11 is established via a groove 13a of the inlet valve 13.
- compressed air can flow from the compressed air reservoir 10 into the handle air spring 11, which acts, among other things, against a piston surface 21 and finally moves the handle piston 12 together with the handle 9 and the second unit 2 back against the working direction A.
- the disruptive relative movement between first unit 1 and second unit 2 can be compensated for in a very short time.
- the handle 9 with the second unit 2 moves backwards relative to the first unit 1, counter to the working direction A. Consequently, the handle piston 12 also slides back and forth finally releases the groove 14a on the outlet valve 14, so that compressed air can flow out of the handle air spring 11 into the environment until the compressed air in the handle air spring 11 is completely reduced.
- the second unit 2 is also on the first unit by stops, not shown, for. B. also secured via the guide elements 6 to avoid a complete loosening of the second unit 2. The stops ensure that the outlet valve 14 is opened without the handle piston 12 completely sliding out of its guide.
- the actuator 4 is already able to isolate vibrations to a considerable extent.
- the spring device 5 is arranged in the form of a helical spring with a soft spring characteristic. Without the actuator 4, the spring device 5 would be completely compressed on the handle 9 even with low operating force, so that it would no longer have a vibration-isolating effect. With the aid of the actuator 4, however, it is possible to maintain the relative position shown in the figures between the first unit 1 and the second unit 2, so that the spring device 5 can still provide sufficient spring travel. This spring travel is suitable for effectively isolating the vibration generated in the first unit 1 from the handle 9.
- FIG. 4 shows a second embodiment of the invention. While a purely mechanical solution was shown in FIGS. 2 and 3, FIG. 4 relates to a mechatronic implementation of the invention. If essentially the same components are used as in FIGS. 2 and 3, the same reference symbols are also used. There is no need to describe these components again.
- valve device An essential difference can be found in the valve device: the air flow to and from the handle air spring 11 is ensured with the aid of valves which can be controlled by a control (not shown), namely an inlet valve 22 and an outlet valve 23.
- the controller receives essential information from a sensor 24 with which the relative position between the first unit 1 and the second unit 2 is detected.
- the sensor 24 can be any proximity sensor, e.g. B. a Hall sensor act.
- the sensor 24 should be designed such that it detects the relative position of the two units 1, 2. at least recorded in the desired optimal range.
- control uses the sensor 24 to detect a displacement of the second unit 2 due to an operating force acting on the handle 9, it causes a change in the rigidity of the handle air spring 11 by correspondingly actuating the inlet valve 22 or the outlet valve 23. Accordingly, the handle piston is displaced 12 and the handle 9 in the desired manner.
- the control system is able to allow a certain fluctuation range, which essentially depends on the available spring travel of the spring device 5.
- the actuating frequency of the actuator determined by the controller can be lower than the frequency of the vibration generated in the first unit. As a result, the demands on the control and the components of the actuator are comparatively low. However, it is also possible to select the actuating frequency of the actuator higher than the oscillation frequency. Then the actuator would be able to actively counteract the vibration. However, this requires a correspondingly fast control and fast valves 23, 24.
- Figure 5 shows a schematic section through a working device with the inventive device for vibration isolation of a handle.
- FIG. 5 shows a section through an upper or rear part, facing away from a tool, of a percussion hammer serving as an implement.
- the device according to the invention is particularly suitable for hand-held tools in which vibrations or shocks are generated in order to achieve the desired working effect. It is important here that the operator guiding or holding the implement is protected against vibrations and shocks.
- a vibration exciter 31 is shown only schematically in FIG. 5 as a housing box. He has z. B. a drive, such as an electric or internal combustion engine, and ayesshaveeinrich- tion on.
- the movement converting device converts the movement usually generated as a rotary movement by the drive into a slower rotary movement suitable for the respective application or also oscillating back and forth movement. So it is z.
- the motion changing device is customary to design the motion changing device as a transmission with a crank mechanism that drives an impact mechanism. From the striking mechanism, impacts are generated with the aid of a percussion piston, which impact on a tool, e.g. B. a chisel.
- the invention is typically also suitable for rotary hammers or rammers or other working devices in which a vibration decoupling of the handle is useful.
- vibration exciter 31 The part of the implement in which vibrations or shocks are generated is thus referred to as vibration exciter 31.
- the term stands for various constellations that can be selected by the specialist depending on the type of implement.
- the vibration exciter 31 is coupled to a handle device 32 designed as a handle hood in FIG.
- the grip device 32 can partially surround the vibration exciter 31, as shown in FIG. 5. However, it can also be provided spatially separated from the vibration exciter 31.
- the grip device 32 is movable relative to the vibration exciter 31 at least along a main direction A.
- a guide (not shown in FIG. 5), known per se (for example by means of parallel swinging) is provided between the handle device 32 on the vibration exciter 31.
- the grip device 32 can also be movable relative to the vibration exciter 31 in other directions deviating from the main direction A, if this is technically unavoidable or even desirable.
- Two handles 33 are provided on the handle device 32, by which the operator can hold and guide the implement. Numerous variants are also known for the design of the handles 33. In a hammer drill z. B. instead of the two handles 33, a single handle in the form of a pistol or spade handle.
- An air spring piston 34 is fastened to the vibration exciter 31.
- the air spring piston is enclosed by a spring cylinder 35 formed by part of the wall of the handle device 32, so that an air spring chamber 36 is formed in a cavity between the air spring piston 34 and the spring cylinder 35, which holds the actual air spring 37. It can be seen that the air pressure in the air spring 37 increases when the handle device 32 is pressed closer to the vibration exciter 31 in direction A.
- the air spring piston 34, the spring cylinder 35, the air spring chamber 36 and the air spring 37 together form a spring device 38.
- an elastic stop 39 is provided, against which the handle device 32 can strike if the force exerted in direction A is so great that the air spring 37 is fully compressed or if the air spring 37 contains too little air, to ensure sufficient spring action.
- the elastic stop 39 ensures that a certain vibration isolation of the handle device 32 is ensured even if the handle device 32 is in direct contact with the air spring piston 34 and thus the vibration exciter 31 via the stop 39.
- a pump piston 40 is also provided on the vibration exciter 31 and is enclosed by a part of the wall of the handle device 32 serving as a pump cylinder 41.
- the pump cylinder 41 surrounds the pump piston 40 in such a way that a pump chamber 42 is formed.
- An air pump 43 is thereby formed.
- Air can flow into the pump chamber 42 from the surroundings of the working device via a one-way valve or first check valve 44 when the handle device 32 moves away from the vibration exciter 31 and the volume of the pump chamber 42 thereby increases.
- the resulting negative pressure sucks the air into the pump chamber 42 via the first check valve 44.
- the handle device 32 is moved in the direction A against the vibration exciter 31, the volume of the pump chamber is reduced. mer 42, so that the pressurized air can flow into the air spring chamber 36 via a second check valve 45 and an inlet opening 46. A backflow of air into the environment is prevented by the first check valve 44. This increases the air pressure in the air spring chamber 36 and increases the rigidity of the air spring 37.
- the vibration exciter 31 Since the vibration exciter 31 generates substantially continuous vibrations or continuously recurring impacts and vibrations resulting therefrom, the vibration exciter 31 tends to move back and forth continuously.
- the supply air flow into the air spring chamber 36 comes to a standstill when the air pressure generated by the air pump 43 is not higher than the pressure prevailing in the air spring chamber 36. Then, however, the air spring 37 has reached its maximum possible stiffness.
- the air pump 43 and the spring device 38 are accordingly to be designed in such a way that a separation between the handle device 32 and the vibration exciter 31 is ensured even under theoretical maximum stress (maximum force exerted by the operator in direction A), so that those arising in the vibration exciter 31 Vibrations can only be transmitted to the handle device 32 via the air spring 37, but not via further solid-state contacts, not even via the stop 39.
- An outlet opening 47 is formed in the wall of the handle device 32.
- the outlet opening 47 is positioned such that it is covered or not covered by the air spring piston 34 serving as a slide, depending on the relative position between the grip device 32 and the vibration exciter 31.
- the air spring piston 34 covers the outlet opening 47 serving as a valve opening when the gripping device 32 has been approached to the vibration exciter 31 via a certain point. This will be the case in particular if the operator with a correspondingly large holding or pressing force in direction A suppressed.
- the air pressure in the air spring 37 is increased by the continuous supply air from the air pump 43 until the air spring 37 is strong enough to push the handle device 32 back against the pressing force of the operator and thus against the direction A.
- the handle device 32 is moved back until the air spring piston 34 at least partially clears the outlet opening 47. Then air can then flow out of the air spring 37 into the environment via the outlet opening 47, so that the air pressure in the air spring 37 is reduced again.
- the handle device 32 can move closer to the vibration exciter 31 again.
- a control serving as a spring control device is ensured, on the basis of which the relative position between the handle device 32 and the vibration exciter 31 even with changing external, essentially static forces, such as, for example, B. the holding force of the operator, is always kept in a defined work area, preferably even in a target position.
- the desired position will usually correspond to a position in which the air spring piston 34 partially covers the outlet opening 47 in the manner shown in the figure. Then there will be a balance between the supply air flow from the air pump 43 and the exhaust air flow via the outlet opening 47, so that the spring force generated by the air spring 37 corresponds to the force acting from the outside.
- a middle position is particularly suitable as the target position for the control of the air spring 37, in which approximately the same movement paths of the grip device 32 to the vibration exciter 31 and away from the vibration exciter 31 are ensured.
- the vibration exciter 31 can vibrate well relative to the handle device 32.
- the regulation of the air spring 37 has a certain deliberate inertia.
- the vibration frequencies of the vibration exciter are significantly higher than the frequencies of the control speed, so that the vibrations cause no or only a negligible change in the spring stiffness of the air spring 37.
- the spring properties are therefore predominantly or exclusively due to the outside of the handle device 32 and thus the vibration exciter 31 acting force, especially by the holding force of the operator, changed.
- the air spring 37 compensates for the higher-frequency vibrations of the vibration exciter 31, so that effective vibration isolation of the handle device 32 takes place.
- the exhaust air flow from the air spring 37 is constant, while the supply air flow is controlled or regulated accordingly by the air pump in order to achieve the desired change in the spring properties of the air spring 37.
- a movable mass oscillator is arranged between the vibration exciter 31 and the handle device 32 and is moved back and forth by the vibrations of the vibration exciter.
- the air spring 37 has an increased rigidity when the implement is idling.
- the air spring 37 is correspondingly stiff when idling, the operator can better guide the hammer and make the drilling.
- the air The piston 34 are designed so that it covers the outlet opening 47 in a relative position in which the handle device 32 is far away, that is to say pushed back to the vibration exciter 31. Only when the handle device 32 is pressed against the vibration exciter 31 does the air spring piston 4 open the outlet opening 47, so that the rigidity of the air spring 37 is initially significantly reduced.
- the grip device 32 can reach the desired setpoint position (eg middle position) before the air spring piston 34 closes the outlet opening 47 again in the manner described above.
- corresponding control grooves can be provided in the side walls of the air spring piston 34, which, depending on the relative position, connect the air spring 37 to the outlet opening 47.
- the operating point of the spring characteristic of the air spring 37 can always be kept in a range which relatively large vibrations of the vibration exciter 31 to the handle device 32. As a result, the vibrations and shocks are effectively isolated from the handle device 32.
- An implement according to the invention thus has an air spring between the vibrating first unit and the second unit to be immobilized (eg handle).
- the spring properties of the air spring can advantageously be changed in that the degree of filling of the air spring the air pressure or the air spring can be changed.
- proposals for air pressure generating devices and for spring control devices have been described above.
- the drive of the implement, for. B. via a drive piston of the air spring hammer mechanism which enable the required generation of air pressure.
- the oscillating relative movement between the first and the second unit can be used to derive a pumping movement for the conveyance of the air and the generation of compressed air.
- using simple mechanical control devices it is possible to always adapt the air pressure in the air spring or its air filling to the circumstances, that is to say, above all, the pressing force applied by the operator.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006519864A JP2009513366A (ja) | 2003-07-15 | 2004-07-13 | ばね弾性減衰式ハンドグリップを備えた作業機械 |
US10/595,046 US7527107B2 (en) | 2003-07-15 | 2004-07-13 | Working tool with damped handle |
EP04740970A EP1646480B8 (de) | 2003-07-15 | 2004-07-13 | Arbeitsgerät mit handgriffabfederung |
DE502004009319T DE502004009319D1 (de) | 2003-07-15 | 2004-07-13 | Arbeitsgerät mit handgriffabfederung |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10332109.8 | 2003-07-15 | ||
DE2003132109 DE10332109B4 (de) | 2003-07-15 | 2003-07-15 | Arbeitsgerät mit Handgriffabfederung |
DE102004025674.8 | 2004-05-26 | ||
DE200410025674 DE102004025674A1 (de) | 2004-05-26 | 2004-05-26 | Vorrichtung zur Schwingungsisolation eines Handgriffs bei einem Arbeitsgerät |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005007351A1 true WO2005007351A1 (de) | 2005-01-27 |
Family
ID=34081649
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2004/007743 WO2005007351A1 (de) | 2003-07-15 | 2004-07-13 | Arbeitsgerät mit handgriffabfederung |
Country Status (6)
Country | Link |
---|---|
US (1) | US7527107B2 (de) |
EP (1) | EP1646480B8 (de) |
JP (1) | JP2009513366A (de) |
DE (1) | DE502004009319D1 (de) |
ES (1) | ES2321942T3 (de) |
WO (1) | WO2005007351A1 (de) |
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GB2421466A (en) * | 2004-12-24 | 2006-06-28 | Bamford Excavators Ltd | Percussion power tool apparatus with shock absorbing piston arrangement |
EP1726408A1 (de) * | 2005-05-25 | 2006-11-29 | BBG Baugeräte GmbH & Co KG | Handgeführter, vibrationsgedämpfter Drucklufthammer |
EP2251152A1 (de) * | 2009-05-11 | 2010-11-17 | Robert Bosch GmbH | Handwerkzeugmaschine, insbesondere Elektrohandwerkzeugmaschine |
WO2010130512A1 (de) * | 2009-05-11 | 2010-11-18 | Robert Bosch Gmbh | Handwerkzeugmaschine, insbesondere elektrohandwerkzeugmaschine |
EP2468455A1 (de) * | 2009-12-25 | 2012-06-27 | Makita Corporation | Schlagwerkzeug |
EP2653267A1 (de) * | 2012-04-19 | 2013-10-23 | HILTI Aktiengesellschaft | Handwerkzeugmaschine |
CN109884985A (zh) * | 2019-03-11 | 2019-06-14 | 上海理工大学 | 数控机床整机加工状态动态特性的测量方法 |
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US8047302B2 (en) * | 2001-12-21 | 2011-11-01 | Wacker Neuson Produktion GmbH & Co. KG | Drilling and/or striking hammer with a lubricating device |
SE528471C2 (sv) * | 2004-07-05 | 2006-11-21 | Atlas Copco Constr Tools Ab | Vibrationsdämpat slående verktyg med tryckluftmatningsorgan |
FR2896544B1 (fr) * | 2006-01-26 | 2008-05-02 | Vianney Rabhi | Ensemble culasse et bloc moteur pour moteur a rapport volumetrique variable |
DE102006000253A1 (de) * | 2006-05-30 | 2007-12-06 | Hilti Ag | Schlagende Handwerkzeugmaschine mit axial beweglich gelagertem Schlagwerk |
DE102006027774A1 (de) * | 2006-06-16 | 2007-12-20 | Robert Bosch Gmbh | Handwerkzeugmaschine |
DE102007000093A1 (de) * | 2007-02-15 | 2008-08-21 | Hilti Ag | Handwerkzeuggerät |
US8100745B2 (en) * | 2007-03-16 | 2012-01-24 | Black & Decker Inc. | Low vibration sander with a flexible top handle |
DE102007048887B4 (de) * | 2007-10-11 | 2017-10-26 | Andreas Stihl Ag & Co. Kg | Handgeführtes Arbeitsgerät |
US20090114412A1 (en) * | 2007-11-05 | 2009-05-07 | Black And Decker Inc. | Power tool having housing with enhanced impact resistance |
WO2009094617A1 (en) * | 2008-01-24 | 2009-07-30 | Lord Corporation | Powered construction ground compactor and method of making |
CN101676052B (zh) * | 2008-09-19 | 2013-10-30 | 德昌电机(深圳)有限公司 | 带力度感应装置的电钻 |
DE102009000363A1 (de) * | 2009-01-21 | 2010-07-22 | Hilti Aktiengesellschaft | Schlagwerk und Handwerkzeugmaschine |
JP5361504B2 (ja) * | 2009-04-10 | 2013-12-04 | 株式会社マキタ | 打撃工具 |
US8097067B2 (en) * | 2009-05-06 | 2012-01-17 | 3M Innovative Properties Company | Runtime sensor for small forced air handling units |
US8196675B2 (en) * | 2010-03-24 | 2012-06-12 | Sing Hua Industrial Co., Ltd. | Impact hammer with pre-pressing damping and buffering effect |
DE102012206452A1 (de) * | 2012-04-19 | 2013-10-24 | Hilti Aktiengesellschaft | Handwerkzeugmaschine und Steuerungsverfahren |
RU2702181C2 (ru) | 2014-11-12 | 2019-10-04 | Макита Корпорейшн | Бойковое устройство |
US20160271778A1 (en) * | 2015-03-21 | 2016-09-22 | Chih Kuan Hsieh | Fixing Structure for Cylinder |
CN107097184B (zh) * | 2016-02-19 | 2021-08-31 | 株式会社牧田 | 作业工具 |
TWI751176B (zh) * | 2016-08-31 | 2022-01-01 | 日商工機控股股份有限公司 | 打釘機、壓力調節器和打釘單元 |
EP3501750A1 (de) * | 2017-12-19 | 2019-06-26 | Hilti Aktiengesellschaft | Vibrationsgedämpfte handwerkzeugmaschine |
JP7139128B2 (ja) * | 2018-03-21 | 2022-09-20 | 株式会社マキタ | 作業工具 |
EP4331773A1 (de) * | 2022-08-29 | 2024-03-06 | Hilti Aktiengesellschaft | Bohr- oder meisselhammer mit einem schwingungsentkoppelten gerätegehäuse |
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- 2004-07-13 JP JP2006519864A patent/JP2009513366A/ja active Pending
- 2004-07-13 WO PCT/EP2004/007743 patent/WO2005007351A1/de active Application Filing
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GB2421466A (en) * | 2004-12-24 | 2006-06-28 | Bamford Excavators Ltd | Percussion power tool apparatus with shock absorbing piston arrangement |
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Also Published As
Publication number | Publication date |
---|---|
EP1646480B8 (de) | 2009-08-05 |
EP1646480B1 (de) | 2009-04-08 |
JP2009513366A (ja) | 2009-04-02 |
EP1646480A1 (de) | 2006-04-19 |
DE502004009319D1 (de) | 2009-05-20 |
US20070034396A1 (en) | 2007-02-15 |
US7527107B2 (en) | 2009-05-05 |
ES2321942T3 (es) | 2009-06-15 |
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