EP1425138B1 - Hammer drill and/or percussion hammer with no-load operation control that depends on application pressure - Google Patents

Hammer drill and/or percussion hammer with no-load operation control that depends on application pressure Download PDF

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Publication number
EP1425138B1
EP1425138B1 EP20020777083 EP02777083A EP1425138B1 EP 1425138 B1 EP1425138 B1 EP 1425138B1 EP 20020777083 EP20020777083 EP 20020777083 EP 02777083 A EP02777083 A EP 02777083A EP 1425138 B1 EP1425138 B1 EP 1425138B1
Authority
EP
European Patent Office
Prior art keywords
hammer
percussion
handle
housing
drive piston
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.)
Expired - Fee Related
Application number
EP20020777083
Other languages
German (de)
French (fr)
Other versions
EP1425138A1 (en
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 Construction Equipment AG
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
Priority to DE2001145464 priority Critical patent/DE10145464C2/en
Priority to DE10145464 priority
Application filed by Wacker Construction Equipment AG filed Critical Wacker Construction Equipment AG
Priority to PCT/EP2002/010253 priority patent/WO2003024672A1/en
Publication of EP1425138A1 publication Critical patent/EP1425138A1/en
Application granted granted Critical
Publication of EP1425138B1 publication Critical patent/EP1425138B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D11/00Portable percussive tools with electromotor or other motor drive
    • B25D11/005Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D16/00Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D17/00Details of, or accessories for, portable power-driven percussive tools
    • B25D17/04Handles; Handle mountings
    • B25D17/043Handles resiliently mounted relative to the hammer housing
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2211/00Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003Crossed drill and motor spindles
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2211/00Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06Means for driving the impulse member
    • B25D2211/068Crank-actuated impulse-driving mechanisms
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2250/00General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/035Bleeding holes, e.g. in piston guide-sleeves
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2250/00General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/131Idling mode of tools
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B25HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25DPERCUSSIVE TOOLS
    • B25D2250/00General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/221Sensors

Abstract

A percussion hammer drill and/or percussion hammer that can be guided by a handgrip (2) comprises a pneumatic spring striking mechanism with a reciprocating drive piston (11) and with a percussion piston (12) that can be operated by the drive piston. A cavity (13) for accommodating a pneumatic spring is provided between the drive piston (11) and the percussion piston (12). The cavity (13) can be connected to the surrounding area via a no-load operation channel (23, 24, 25) in order to achieve a no-load operation. To this end, a valve (19) is situated inside the no-load operation channel and can be controlled according to an application force that can be applied to the handgrip (2) by the operator.

Description

The invention relates to a drill and / or percussion hammer according to the The preamble of claim 1.

Such a hammer and / or percussion hammer is e.g. from the DE-A-19847687 or DE-A-19713154.

A drill and / or hammer - hereinafter referred to as a hammer - usually has an air spring impact, in which a drive piston by an electric motor by means of a crank or wobble shaft drive is placed in an oscillating float. In front of the drive piston is a percussion piston arranged so that between the drive piston and the percussion piston is a cavity in which a Can form air spring. The air spring transmits the float of the drive piston on the percussion piston and drives this on the shaft a tool (chisel) or an intermediate striker. such Hammers are known in various embodiments.

When using the hammer to edit a specific location must the operator the tip of the tool, for. As the chisel tip, very carefully put on to prevent the chisel tip from jumping away. This is especially true in relatively smooth or elevated areas of the material to be processed. Since air spring impact of simple design tend to suddenly to start with the impact operation, however, can be the undesirable Do not always avoid jumping away. This can cause the rock is chiseled in a place that must not be damaged. At the Editing edges even risks damaging the edges Hammer or a threat to the operator himself, if the chisel of the edge jumps into space.

To solve this problem, various solutions have been proposed. So it is known, an abrupt onset of the blow by lowering To avoid the idling speed or at least mitigate. there However, there is the disadvantage that the characteristic of the speed at Running up from idle to hitting is always the same while the respective application requires an adapted run-up. The Speed reduction also prevents rapid creation of a stabilizing Centering in the material to be removed.

Another solution is z. In DE-A-197 13 154 or DE-A-197 24 531 described in the form of a so-called sleeve control. This is used the effect that the tool axially movable relative to the hammer is held and in the idle position something from the hammer housing can slip out. When placing the tool on the to be machined Rock the shank of the tool is pushed into the interior of the hammer and causes - usually relatively by displacement of the percussion piston to the drive piston - a transition from idle mode to hitting mode.

In sleeve control, the relative movement of the tool becomes Hammer housing either directly or via an intermediate piston on a transmitted spring-loaded control sleeve. The control sleeve acts with control bores together, which open and close an idle air duct can be that of the air spring receiving cavity between Drive and percussion piston connects with the environment. The move the control sleeve thus allows the cavity with the environment of the Schlagwerks in communicating connection to bring or such Disconnect. Through this control the ventilation of the air spring cavity can be the change between idle mode and impact mode realize very reliable.

As in the sleeve control, the speed of the drive motor and thus the Beat number can remain virtually unchanged, unlike the above described speed reduction very quickly a tool stop giving Centering produced in the material to be processed. By the good controllability, the operator can set the single impact strength for each individual application case optimally determine.

However, the principle of sleeve control also has a drawback: how already explained, when moving the tool shank into the interior the hammer housing displaces the control sleeve against the action of a spring. Therefore, the pressing force to be applied by the operator becomes the spring force between the tool shank and an adjoining one Enlarged doubler and the hammer housing. Especially with heavier ones Hammering this is disadvantageous because the spring acting on the control sleeve must be designed so that they at least the weight of the tool on the one hand or the weight of the hammer on the other hand, an unwanted change from idle operation to impact operation to avoid. When working with the hammer upwards namely lies also in idle mode, the tool with its entire weight against the Control sleeve and thus against the spring, so that the spring the tool must hold. Only when the tool is pressed onto the workpiece to be machined Rock may be the change in the impact mode.

The same applies to the work down. Here must be heavy especially Breaking hammers have the option of putting the tool on the ground set down and support the entire hammer on the tool, without leaving the idling mode. Only when the hammer is pressed down by the operator to use the impact mode.

When changing the position of the hammer, z. B. when working in the horizontal direction, In addition, the otherwise existing support is missing by the weight of tool or hammer. Then the must Apply even higher forces operator.

The invention is based on the object, a drill and / or percussion hammer specify the Bauert mentioned, in which when pressing the hammer on the machined Rock a suitable circuit a reliable change between Idle and percussion ensures without the operator applied pressure increases excessively.

The solution according to the invention is specified in claim 1. advantageous Further developments of the invention are defined in the dependent claims listed.

The inventive, on a handle at a grip position feasible Drill and hammer - hereinafter referred to as hammer - has - as well known hammers - an idle channel for connecting a formed between a drive piston and a percussion piston Cavity with the environment up. In the idle passage is a valve for Open and close the idle channel provided. According to the invention the hammer characterized in that in the power flow between the grip point and the hammer housing detecting means for detecting arranged on the handle applied pressure force by the operator is and that the valve depending on the detected pressing force is controllable.

The detection device is therefore arranged at a location where possible Immediately the applied by the operator pressure force can be detected can. Thus, it is much more direct, than in the prior art is possible to capture the desire of the operator by applying the Pressing force to move the hammer from idling to impact mode.

The detection device can be realized in various forms. So it is z. B. in one embodiment of the invention possible, the handle movable relative to the hammer housing against the action of a spring system respectively. In this case, one acting on the handle corresponds Pressing force of a relative displacement between the handle and the Hammer housing. On the other hand, the detection device can also by a suitable sensor can be realized. In any case, the mechanical serves or mechatronically detected pressing force as a criterion for driving the valve, over which the cavity in the air spring impact with the environment can be associated.

Thus, for the control of the valve is not - as in the prior art - The relative displacement of the tool shaft or anvil against the Hammer housing for controlling the idling relevant. Rather, the applied by the operator contact pressure or the resulting Relativweg the handle relative to the air spring striking surrounding Hammer housing decisive. This will ensure that the for the Control of idling and impact operation necessary Andrück- or control force does not enter into the pressure applied by the operator, they So not increased, as is the case in the prior art. It will be direct the pressing force of the operator evaluated, which can not be overcome stronger spring forces must be increased.

While in the prior art one in the power flow between operator and Tool tip on the tool shank or force applied to the striker for Control of the valve (in the prior art: the control sleeve) evaluated was, according to the invention introduced the pressure applied to the handle the operator's the decisive criterion.

In an advantageous embodiment of the invention is between the handle and the hammer housing a spring system provided to the handle relative to the hammer housing with a given spring force hold. The pressing force can be determined by one of the pressing force proportional displacement of the handle relative to the hammer housing is detected.

The spring system is in a particularly advantageous embodiment of the Invention Component of a device for vibration damping of Handle. Especially with larger hammers namely are embodiments known in which the handle to be held by the operator vibrationally decoupled from the rest of the hammer housing to a certain extent To achieve damping and relieve the operator. In these handle designs is the required relative mobility between handle and hammer housing already realized, so that only the pressure force proportional relative displacement must be detected.

In a particularly advantageous embodiment of the invention is a provided axially movable sleeve, which in principle from the state of Technique known control sleeve corresponds and a control of the valve forms. However, according to the invention, the axial position of the sleeve is dependent changeable by the force applied by the operator pressing force. In the prior art, however, the control sleeve could only by shift the relative displacement between tool and hammer housing, what - as described above - due to the different acting weight forces and correspondingly sized springs for supporting the Control sleeve to a significant increase to be applied by the operator Pressing force led.

In a further development of the invention, the sleeve with the handle connected positively in the axial direction, so that by the operator applied pressing force proportional relative displacement of the handle relative to the hammer housing directly as a relative displacement of Sleeve can be transmitted to the housing.

The described solution is basically for all known types of Luftfederschlagwerken suitable. These include z. B. pipe impactors, in which the drive piston and the percussion piston of the same diameter in one Pipe are arranged axially movable. Also is a hollow bat impact mechanism known, in which the percussion piston is hollow and in its interior receives the drive piston axially movable.

However, a particularly advantageous embodiment of the invention relates a hollow piston percussion, in which the drive piston is hollow and receives in its interior the percussion piston axially movable. The drive piston is radially surrounded by the sleeve, which in turn in a Schlagwerksgehäuse is guided. In drive piston, sleeve and in Schlagwerksgehäuse openings or recesses are provided, which together form the idle channel. The sleeve serves as a control of the valve and is capable of the connection between the cavity in the Inside the drive piston and the environment of the air spring impact in Depending on their axial position to open or close.

Except the above-explained mechanical realization of the invention It is also possible, the underlying technical teaching of the invention mechanical-electrical or mechatronic implement.

Thus, in another advantageous embodiment of the invention, the Detection device on a sensor with which the on the handle acting pressing force, in particular by the action of the handle can be detected against the hammer housing via the spring system. The sensor provides a pressure signal to a controller corresponding to the valve element activates to open and close the valve.

It is particularly advantageous if the sensor is a proximity sensor or a force measuring sensor is to reliably detect the acting pressing force to be able to.

In a further embodiment of the invention is also a position sensor intended to capture the location of the hammer in the room and generate a corresponding position signal. The position signal is the Supplied control, which then the Andrücksignal a correction, to z. B. exclude unwanted weight forces. Is working the operator z. B. with the hammer down, he does not have the hammer in the hand, but can support it on the ground. Vice versa When working up, the operator has the weight of the hammer complete to support the handle. This weight can be influenced by the Position sensor can be eliminated.

The core idea of the invention is to make a soft application for the hammer allow for onset of impact operation when the tool only lightly pressed on the rock to be processed. Accordingly should at this time acting on the tool power be very low and be increased only with stronger pressing. This allows the tool despite full speed of the drive motor Precise positioning without it jumping off the rock to be processed.

These and other advantages and features of the invention are explained in more detail below with reference to several examples with the aid of the accompanying figures. Show it:

Fig. 1A
a sectional view of a drilling and hammer or hammer (hammer) according to the invention according to a first embodiment in the impact mode;
Fig. 1B
a partial enlargement of Fig. 1A;
Fig. 2
an enlarged detail of the first embodiment of FIG. 1A, but in idle operation with aufsitzendem on the rock tool;
Fig. 3A
a sectional view of the hammer according to the first embodiment in the idling operation with the tool off the rock;
Fig. 3B
an enlarged detail of Fig. 3A;
Fig. 4
a sectional view of a hammer according to the invention according to a second embodiment in impact mode;
Fig. 5A
the hammer of Figure 4 in idle mode;
Fig. 5B
an enlarged detail of Fig. 5A.

Figs. 1A to 3B show the hammer according to a first embodiment in different modes and zoomed out. Of the Hammer according to the second embodiment is shown in Figs. 4 to 5B. First, the hammer according to the first embodiment with reference to Fig. 1A and 1B explained.

On a hammer housing 1, a handle 2 is axially displaceable via spring systems 3 attached. At the front end of the hammer housing 1 is a further handle 4 attached, but without meaning to the invention is and only serves to better guide the hammer.

In the spring system 3, it may be z. B. be an anti-vibration system, with the acting on the handle 2 and by the Luftfederschlagwerk or the effect of the tool generated vibrations and Collisions on the handle 2 and thus on the one handle position 2b of the handle 2 embracing hand of the operator be mitigated. As far as one known hammer such anti-vibration system already provided is, would be at this point make any structural changes. however It is also possible to install only a spring system, the one Displacement of the handle 2 relative to the handle 4 allows, due the force acting on the handle 2 via a proportional relationship pressing force can be determined.

In the interior of the handle 2, inter alia, a main switch 5 for on and Turn off the hammer provided. In addition, closes at the Handle 2 a power cord 6 on. Inside the hammer housing 1 is a Electric motor 7 is arranged, which drives a crankshaft 9 via a gear 8. The crankshaft 9 generates a reciprocating motion via a connecting rod 10 a hollow drive piston 11. Inside the reciprocating, sleeve-shaped drive piston 11 is a percussion piston 12 axially movable added. Between the drive piston 11 and the percussion piston 12, a cavity 13 is provided in which in a known manner at the relative movement between the drive piston 11 and percussion piston 12 a Air spring forms, which drives the percussion piston 12 against an anvil 14 and sucked back after a blow, so that at the next forward movement the drive piston 11 a new blow through the Impact piston 12 can be done. The striker 14 acts on one in one Tool holder 15 received shank of a tool, not shown.

Since the basic principle of such a pneumatic spring impact has long been known is, a more detailed representation is unnecessary.

Before the percussion piston 12, a front cavity 16 is provided, over a provided in a wall 17 of the drive piston 11 air duct 18 with the environment of the air spring impact, so z. B. the rest Inside the hammer housing 1, in impact mode in communicating connection stands. This avoids that in front of the percussion piston 12th in the front cavity 16 an air cushion builds up the impact effect could hinder the impact piston 12.

The drive piston 11, in particular its wall 17, is of a control sleeve 19 surrounded. The control sleeve 19 is in a part of the hammer housing 1 forming percussion housing 20 axially movable. Im shown For example, a collar 21 is provided on the control sleeve 19, which of a driver 22 is included. As can be clearly seen in FIGS. 1A and 1B, the driver 22 is directly with an extension 2a of the handle second connected, so that at least in the axial direction of the control sleeve 19th effective form-fitting coupling between the handle 2 and the control sleeve 19 is realized. As the handle 2 due to the action of the spring system 3 is movable relative to the hammer housing 1, transmits his movement over the driver 22 and the collar 21 directly to the Control sleeve 19 and moves the control sleeve 19 inside the percussion gear housing 20 axially.

The control sleeve 19 has a wall penetrating radial opening 23 on. The location of the radial opening 23 is chosen to be in any operating condition with at least one opening 24 in the wall 17 of the drive piston 11 corresponds, wherein - as Fig. 1B shows well - In the axial direction of the drive piston 11 a plurality of openings 24 in the Wall 17 are formed. Depending on the axial position of the drive piston 11th or the control sleeve 19 is at least one, sometimes two Openings 24 at the level of the radial opening 23.

On the inside of the control sleeve 19 surrounding cylindrical percussion housing 20 is a recess 25 z. B. in the form of a control sleeve 19 enclosing annular channel formed on its underside to the interior of the hammer housing 1, so the environment of the air spring impact opens.

The openings 24 in the drive piston 11, the radial opening 23 in the control sleeve 19 and the recess 25 together form an idle channel, by the idling mode of the air spring striking a communicating Connection of the cavity 13 to the surroundings of the air spring impact mechanism can be produced.

Figs. 1A and 1B show the hammer and in particular the air spring impact mechanism in impact mode. Accordingly, no communicating Connection exist between the cavity 13 and the environment. Therefore the control sleeve 19 is shifted in the percussion mechanism housing 20 such that the radial opening 23 is not above the recess 25. Thus, the Connection interrupted. The control sleeve 19, together with the of her recorded radial opening 23 a valve for opening and closing of the idle channel.

The corresponding position of the control sleeve 19 is effected by that the operator the handle 2 against the hammer housing 1 and the effect the spring systems 3 pushes forward. Accordingly, he also pushes that Tool against the rock to be processed. The pressure force proportional Relative displacement of the handle 2 relative to the hammer housing 1 is transmitted directly to the control sleeve 19, so that the desired, in Figs. 1A and 1B shown axial position of the control sleeve 19 occurs.

Advantageously, in the region of the driver 22 in the figures Not shown seal provided, the ingress of dirt in prevents the interior of the hammer housing.

Fig. 2 shows an enlarged detail of the hammer of Fig. 1A, however in idle mode, with the tool on the rock to be machined seated, without any pressure by the operator.

By placing the tool on the rock is the striker 14 in its rear, moved into the interior of the hammer housing 1 Position.

The fact that the operator does not apply a pressing force, the spring system presses 3 the handle 2 relative to the hammer housing 1 to the rear, so that the handle 2 together with the control sleeve 19 to the rear relocated. As a result, the radial opening 23 moves over the recess 25, see FIG that on the always located at the height of the radial opening 23 openings 24 of the drive piston 11 a communicating connection from the cavity 13 is made to the environment of the air spring percussion. Accordingly can in the cavity 13 no Luftüber- or -unterdruck and do not build up any resulting air spring. Rather, despite further reciprocation of the drive piston 11 permanently effective Ventilation of the cavity 13, so that the percussion piston 12 in his Position remains.

Due to the displacement of the control sleeve 19 has also trained in her second radial opening 26 axially displaced so that the front Cavity 16 of the environment connecting air duct 18 is interrupted. Accordingly, the front cavity 16 is decoupled from the environment, so that a remaining air supply in its interior an air cushion forms that counteracts another blow by the percussion piston 12.

When the operator wants to record the beat operation, it becomes slow press against the handle 2 and thus the control sleeve 19 against the effect Move the spring system 3 until the idle channel by shifting the radial opening 23 is interrupted. This builds up inside of the cavity 13 gently on an air spring, the first only light blows of the percussion piston 12 generated against the striker 14. Only with complete separation the radial opening 23 of the recess 25 can the full effect of the air spring impactor. Through clever shaping of the radial opening 23, z. B. in the form of a slot, can be constructive on the Change between idle mode and impact mode influence.

Finally, FIGS. 3A and 3B show the hammer according to the invention in FIG Idle operation when the tool is completely lifted from the rock. The striker 14 is accordingly in its forward position, because the tool slides out of the hammer housing 1.

The position of the handle 2 and the control sleeve 19 in relation to Hammer housing 1 is unchanged from the position shown in Fig. 2. The idle channel is accordingly opened via the radial opening 23, so that the cavity 13 can be ventilated. In Fig. 3B is above In addition, a pocket 27 or recess in the wall 17 of the drive piston 11 recognizable. About the pocket 27, the air spring in the cavity 13 are constantly refilled with air during impact operation, to compensate for any air loss between the blows. The underlying principle is known, so that's another discussion unnecessary.

Figures 4, 5A and 5B show the hammer of the invention in a second Embodiment. While the first embodiment described above purely mechanical way of detecting the pressing force of the operator on the handle and a consequent influence of the Position of the connection of the cavity 13 with the environment controlling Valve enabled, the second embodiment is based on a mechatronic Solution. As far as the same components as in the first embodiment are also used, the same reference numerals listed. On a new description of the corresponding elements is waived.

Instead of the control sleeve 19 is a valve body 30 in the second Embodiment used very short idle channel. The idle channel consists here only of a recess 31 in the percussion mechanism housing 20th and a connecting passage 32 into which the valve body 30 is inserted. The valve body 30 has a through hole 33 in its interior on. As can be seen in FIGS. 4 and 5A and 5B, the valve body 30 is rotatable. For this purpose, an actuator, not shown in the figures, is provided.

While in Fig. 4, the valve body 30 is rotated to a position in which the Through hole 33 is not arranged in the idle channel, so that the Connection between the cavity 13 and the surroundings of the air spring impact mechanism is interrupted, in Figs. 5A and 5B is a position of Valve body 30 can be seen, in which the through hole 33, the idle channel opens and the connection between the cavity 13 to the environment manufactures.

Also in the second embodiment, the handle 2 is relative to the Hammer housing 1 movably mounted against the action of spring systems 3. The relative position between the handle 2 and hammer housing 1 is detected by means of a proximity sensor 34. The proximity sensor 34 may either be construed as having only binary states, viz Impact operation idling operation, capable of distinguishing. Alternatively it is It is also possible with the help of a suitable proximity sensor, the exact Position of the handle 2 relative to the hammer housing 1 to detect and evaluate accordingly. Instead of the proximity sensor 34 can also - z. B. inside the spring systems 3, but also independent of spring systems - Be arranged a suitable force measuring sensor, that of the operator applied pressing force detected. Furthermore, it is possible by a touch-sensitive Force measuring sensor in the handle 2 itself directly at the Handle 2b to detect the pressing force of the operator.

The proximity sensor 34 generates a pressing signal corresponding to the pressing force - be it binary or proportional to the pressure force - and conduct it to a controller 35 on. When the controller 35 recognizes that the operator presses the hammer so that a transition from the idle position is desired in the impact position, the controller 35 controls the valve actuator, not shown, to the valve body 30 in the in To rotate Fig. 4 shown position. When lifting the hammer and the corresponding Slackening of the pressing force is the reverse process initiated.

In another, not shown in the figures embodiment is about In addition, a position sensor is provided which determines the position of the hammer in Space, in particular the inclination of the tool axis, detected and a corresponding Position signal to the controller 35 outputs. The controller 35 evaluates the position signal to the effect that by the position and thus by the working direction caused weight forces of the tool and hammer working upwards by the operator at the handle 2 in addition, or when working down to the tool act and support the blow, in the evaluation of the Andrücksignals can be considered. This can otherwise due to the gravitational effect very different pressure forces ever be uniformed according to the direction of use.

Both the mechanical solution according to the first embodiment as also the mechatronic solution of the further described embodiments allow a particularly gentle start of the hammer. The operator The tip of the tool can be careful at the desired location put on and by increasing the pressing force a shift of the Handle 2 and thus cause a gentle onset of impact operation.

Claims (13)

  1. Hammer drill and/or percussion hammer having
    at least one handle (2) having a gripping point (2b) for an operator to hold the hammer drill and/or percussion hammer and apply pressure thereto;
    a pneumatic spring percussion mechanism having a drive piston (11), which can be moved in a reciprocating manner, and a percussion piston (12) which can be driven by the drive piston (11), wherein a hollow space (13) for accommodating a pneumatic spring is formed between the drive piston (11) and the percussion piston (12);
    a no-load channel (23, 24, 25) for connecting the hollow space (13) to the surroundings of the pneumatic spring percussion mechanism and for ventilating the hollow space (13) during no-load operation;
    a valve (19, 23) disposed in the no-load channel (23, 24, 25) for opening and closing the no-load channel; and having
    a hammer housing (1) surrounding at least the pneumatic spring percussion mechanism;
    characterised in that
    a detecting device (2a, 3; 3, 34) for detecting a pressure force which can be applied to the handle (2) by the operator is disposed in the flow of force between the gripping point (2b) and the hammer housing (1); and in that
    the valve (19, 23) can be actuated in dependence upon the detected pressure force.
  2. Hammer drill and/or percussion hammer as claimed in Claim 1, characterised in that the handle (2) can be moved relative to the hammer housing (1).
  3. Hammer drill and/or percussion hammer as claimed in Claim 2, characterised in that a spring system (3) appertaining to the detecting device is provided between the handle (2) and the hammer housing (1) in order to maintain the handle (2) relative to the hammer housing (1) with a predetermined spring force.
  4. Hammer drill and/or percussion hammer as claimed in Claim 3, characterised in that the detecting device comprises an extension (2a) which is coupled with the handle (2) and can be displaced by means of the handle (2) with respect to the hammer housing (1) against the action of the spring system (3) in such a manner that its displacement is essentially proportional to the pressure force of the operator.
  5. Hammer drill and/or percussion hammer as claimed in Claim 3 or 4, characterised in that the spring system (3) is also a component of a device for damping the vibrations of the handle (2).
  6. Hammer drill and/or percussion hammer as claimed in any one of Claims 1 to 5, characterised in that a sleeve (19) is provided which can be moved axially and forms a control element of the valve, wherein the axial position of the sleeve can be changed in dependence upon the pressure force.
  7. Hammer drill and/or percussion hammer as claimed in Claim 6, characterised in that the sleeve (19) is connected to the handle (2) in the axial direction in a positive-locking manner.
  8. Hammer drill and/or percussion hammer as claimed in any one of Claims 1 to 7,
    characterised in that
    the drive piston (11) is formed so as to be hollow;
    the percussion piston (12) can be moved axially in the drive piston (11); and in that
    several apertures (24) are provided in a cylindrical wall (17) of the drive piston (11), are disposed next to each other in relation to an axial direction of the drive piston (11) and each form part of the no-load channel depending upon the axial position of the drive piston (11).
  9. Hammer drill and/or percussion hammer as claimed in Claim 8, characterised in that
    the drive piston (11) is radially surrounded by the sleeve (19);
    a radial aperture (23) forming part of the no-load channel is provided in the sleeve (19) and is located over at least one of the apertures (24) in the wall (17) of the drive piston (11) in each operating condition of the pneumatic spring percussion mechanism;
    the sleeve (19) is guided in a percussion mechanism housing (20);
    a recess (25) which likewise forms part of the no-load channel and communicates with the surroundings is provided in the percussion mechanism housing (20); and in that
    the radial aperture (23) can be moved, in dependence upon the pressure force, over the recess (25) in the percussion mechanism housing (20) for no-load operation of the pneumatic spring percussion mechanism in such a manner that the hollow space (13) in the drive piston (11) communicates with the surroundings via the apertures (24) in the lateral wall (17) of the drive piston (11), the radial aperture (23) in the sleeve (19) and the recess (25) in the percussion mechanism housing (20).
  10. Hammer drill and/or percussion hammer as claimed in any one of Claims 1 to 5,
    characterised in that
    the detecting device comprises a sensor (34) for detecting a condition in which the handle (2) is pressed against the hammer housing (1) against the action of the spring system (3), and for producing a pressure signal;
    the valve comprises a valve element (30) which can be actuated in a mechanical, electrical, electromechanical or electromagnetic manner; and in that
    the pressure signal can be supplied to a controller (35) which correspondingly actuates the valve element (30) in order to open and close the valve.
  11. Hammer drill and/or percussion hammer as claimed in Claim 10, characterised in that the sensor is a proximity sensor (34) or a force measurement sensor.
  12. Hammer drill and/or percussion hammer as claimed in Claim 10 or 11,
    characterised in that
    a position sensor is provided for detecting the spatial position of the hammer drill and/or percussion hammer relative to a horizontal plane and for producing a corresponding position signal;
    the position signal can be supplied to the controller (35); and in that
    the controller (35) actuates the valve element (30) by evaluating the pressure signal and the position signal.
  13. Hammer drill and/or percussion hammer as claimed in Claim 11, characterised in that upon evaluation of the pressure signal and of the position signal, deviation of the position of the hammer drill and/or percussion hammer from the horizontal plane can be taken into account such that the resulting pressure signal can be corrected, taking into account the effective weight forces of the handle (2), of the hamming housing (1) and of the components contained therein as well as of a tool.
EP20020777083 2001-09-14 2002-09-12 Hammer drill and/or percussion hammer with no-load operation control that depends on application pressure Expired - Fee Related EP1425138B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE2001145464 DE10145464C2 (en) 2001-09-14 2001-09-14 Drill and / or impact hammer with idle control depending on the contact pressure
DE10145464 2001-09-14
PCT/EP2002/010253 WO2003024672A1 (en) 2001-09-14 2002-09-12 Hammer drill and/or percussion hammer with no-load operation control that depends on application pressure

Publications (2)

Publication Number Publication Date
EP1425138A1 EP1425138A1 (en) 2004-06-09
EP1425138B1 true EP1425138B1 (en) 2005-07-20

Family

ID=7699118

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020777083 Expired - Fee Related EP1425138B1 (en) 2001-09-14 2002-09-12 Hammer drill and/or percussion hammer with no-load operation control that depends on application pressure

Country Status (6)

Country Link
US (1) US6913088B2 (en)
EP (1) EP1425138B1 (en)
JP (1) JP4243539B2 (en)
DE (1) DE10145464C2 (en)
ES (1) ES2243767T3 (en)
WO (1) WO2003024672A1 (en)

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Also Published As

Publication number Publication date
DE10145464C2 (en) 2003-08-28
DE10145464A1 (en) 2003-04-10
JP2005502488A (en) 2005-01-27
US20040177981A1 (en) 2004-09-16
ES2243767T3 (en) 2005-12-01
US6913088B2 (en) 2005-07-05
EP1425138A1 (en) 2004-06-09
WO2003024672A1 (en) 2003-03-27
JP4243539B2 (en) 2009-03-25

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