EP1719581B1 - Motorized sander with swivelling head and tool holder - Google Patents

Description

The invention relates to a hand-held grinding machine, comprising a holding device for holding the grinding machine, a drive motor, which is arranged on the holding device, a tool head, which is pivotable about at least one pivot axis relative to the holding device and one on the drive motor having driven tool drive shaft, and a transmission device for transmitting torque from the drive motor to the tool drive shaft, wherein the length of the holding device relative to the tool head is adjustable and the holding means comprises a first holding member and a second holding member which are lockable relative to each other. An example of such a hangchaltene grinding machine is from the unpublished WO 2006, 039415 A2 known.

From the EP 0 727 281 B1 For example, a motorized sander is known which comprises a drive motor mounted on a distal end of a tubular rod and a flexible drive shaft operatively coupled to the drive motor and extending along the length of the tubular rod. A sanding pad is operatively coupled to the flexible drive shaft, which shaft provides for effective coupling at different positions of the head with respect to the tubular rod.

From the US 5,239,783 A a grinding machine is known in which a drive motor is coupled to a flexible shaft, which is guided in a flexible sheath.

From the US 4,782,632 A a hand-held grinding machine is known in which the motor is coupled to a shaft and a tool is coupled to a shaft, wherein the two shafts are coupled via a flexible spring drive.

From the DE 81 00 197.5 U1 For example, there is known a floor sanding machine having an abrasive motor driven sandpaper coated abrasive wheel. On the motor housing of the electric motor suitable for handling the grinding machine by a standing operator guide rod is arranged.

From the DE 100 01 091 A1 an electric hand tool is known in which a tool holder is coupled via a spindle with a drive shaft in a transmission housing, wherein the transmission housing is formed in two parts and the two parts of the transmission housing in a direction oblique to the drive shaft and the spindle Verdrehebene are rotated relative to each other and in the each desired Verdrehlage can be locked.

Other hand-held grinders are from the US 4,685,252 A , of the US 4,974,371 A and the US 1,134,116 known.

From the not pre-published WO 2006/039415 A2 An adjustable drywall sander is known which comprises a drive unit with a motor and a grinding device which is coupled to the drive unit. A telescopic arm device is coupled to the grinding device and to the drive unit.

From the EP 1 702 715 A1 For example, an extension element for a long-necked sander is known, which has fixing means in order to place it on a body of a long-necked sander.

The invention has for its object to provide a hand-held grinding machine of the type mentioned, which has an improved handling.

This object is achieved according to the invention in the hand-held grinding machine mentioned above in that the second holding element is displaceably guided in the first holding element and the drive motor is fixed to the first holding element, and that on the second holding element, a grip element is arranged whose distance from the tool head is adjustable by the positioning of the second holding element relative to the first holding element.

A user can adapt the length of the holding device to the application. This results in improved application possibilities.

The holding device has a first holding element and a second holding element which are lockable relative to each other. Due to the relative displaceability of the holding elements to each other can be adjusted in a simple manner, the length of the holding device.

It can be provided that the transmission device has a rigid shaft, which is coupled to the tool drive shaft via a transmission or a hinge device. This results in extended application possibilities.

In this solution according to the invention, the rigid shaft serves as a drive shaft for the tool head. The tool drive shaft is an output shaft of the transmission or the joint device. Through the torque transmission on the rigid shaft easily lead between the drive motor and the tool head.

It is particularly advantageous if the transmission or the hinge device is arranged on a pivot bearing or in the vicinity of a pivot bearing for the tool head. As a result, the tool head can be constructed in a simple and space-saving manner.

In particular, it is advantageous if the tool head is pivotable relative to the rigid shaft. As a result, a torque transmission is ensured even for high speeds at each pivotal position of the tool head relative to the rigid shaft.

It is particularly advantageous if a rotation axis of the rigid shaft is perpendicular to a pivot axis of the tool head. As a result, a torque transmission is ensured at each pivot position of the tool head.

It is favorable if a rotation axis of the rigid shaft and a rotation axis of the drive shaft intersect at a point in each position of the tool head. This results in an optimized torque transmission from the rigid shaft to the tool drive shaft.

In particular, the point of intersection lies on a pivot axis of the tool head. This gives a space-saving training for the transmission or the joint device and for a corresponding pivot bearing for the pivoting of the tool head.

In a structurally simple embodiment, the transmission is designed as a gear transmission. The torque transmission from the rigid shaft to the tool drive shaft via gears.

In particular, a gear is provided for transmitting torque from the rigid shaft to the tool drive shaft, which is driven by the rigid shaft and to which the tool shaft is coupled.

A space-saving and simple design of the hand-held grinding machine can be achieved if a rotation axis of the gear is coaxial with a pivot axis of the tool head. As a result, the gear can be arranged on a pivot bearing for the pivotability of the tool head relative to the holding device.

In a structurally simple embodiment, the transmission is designed as a bevel gear. As a result, torque transmission from the rigid shaft to the tool drive shaft can be achieved in a simple manner, independently of the pivoting position of the tool drive shaft.

To form the bevel gear, a bevel gear is arranged in particular on the rigid shaft and a bevel gear is arranged on the tool drive shaft. Via the bevel gear of the rigid shaft can then drive a gear. This gear in turn drives the bevel gear of the tool drive shaft and thus the tool drive shaft.

In an alternative embodiment, the rigid shaft is coupled to the tool drive shaft via a hinge device. About the hinge device, the torque of the rigid shaft is transmitted to the tool drive shaft, wherein the pivoting of the tool head is made possible. With the provision of a hinge device can be a - articulated - solid coupling between the tool drive shaft and the rigid shaft reach, which is independent of the pivotal position of the tool head.

In particular, it is advantageous if the joint device comprises a first joint element, which is pivotably coupled to the rigid shaft about a first pivot axis, and a second joint element which is pivotally coupled to the tool drive shaft about a second pivot axis. Thereby, a uniform rotational speed between the drive side (the rigid shaft) and the output side (the tool drive shaft) can be achieved, whereby the pivotability of the tool head is ensured. In particular, the joint device is designed as a combination of two universal joints (cardan joints), wherein the first joint element and the joint element form a universal joint pair.

It is favorable if the first pivot axis is oriented perpendicular to a rotation axis of the rigid shaft. As a result, with an optimized torque transmission from the rigid shaft to the drive shaft, the pivotability of the tool head can be realized in a large pivoting range.

For the same reason, it is advantageous if the second pivot axis is oriented perpendicular to a rotational axis of the tool drive shaft.

Furthermore, it is favorable for the same reason, if the first pivot axis and the second pivot axis are oriented parallel to each other. As a result, it is also possible for the deflection angle of the first joint element with respect to the rigid shaft and the bending angle of the tool drive shaft with respect to the second joint element to be at least approximately equal in magnitude. (Angular differences smaller than 50 ° and in particular smaller than 3 ° can be allowed.)

Furthermore, it is favorable if the axis of rotation of the rigid shaft intersects the first pivot axis. As a result, an optimized torque transmission can be achieved.

For the same reason, it is favorable if an axis of rotation of the tool drive shaft intersects the second pivot axis.

It is advantageous if the first joint element is pivotable about a third pivot axis, which is oriented transversely to the first pivot axis. Thereby, a synchronous torque transmission from the drive side to the output side can be achieved, so that the output side has the same rotational speed as the drive side.

For the same reason, it is favorable if the second joint element is pivotably mounted about a fourth pivot axis, which is transverse to the second pivot axis.

It is also favorable if the third pivot axis and the fourth pivot axis are oriented parallel to one another. As a result, an optimized power transmission can be achieved.

The hinge device can be formed in a simple manner when the first joint element is pivotally mounted on a connecting element to the second joint member about the third pivot axis. It can be compact and thus save space. The connecting element is then part of a propeller shaft, which comprises the rigid shaft and the tool drive shaft.

For the same reason, it is favorable if the second joint element is pivotably mounted on a connecting element to the first joint element about the fourth pivot axis.

It is also favorable if the pivot axis of the tool head lies between the plane spanned by the first pivot axis and the third pivot axis and the plane spanned by the second pivot axis and the fourth pivot axis. As a result, the joint device can be designed to save space with optimized power transmission.

In particular, an at least three-part propeller shaft by means of the rigid shaft, the joint device and there in particular a connecting element between the first joint element and the second joint element and the tool drive shaft is formed. Such a three-part propeller shaft can realize a permanent coupling of the tool drive shaft to the drive motor, wherein the rotational speed of the drive side and the Output side is the same. It can be realized in a simple manner a pivoting of the tool head. The propeller shaft may for example also be in four parts; she then has three joints.

It is favorable if the bending angle between the rigid shaft and the first joint element and the bending angle between the tool drive shaft and the second joint element lies in one plane. This bending angle is dependent on the pivotal position of the tool head to the rigid shaft. If the bending angles lie in one plane, an optimized power transmission can be achieved at the same speed on the drive side and the driven side.

For the same reason, it is favorable if the bending angles between the rigid shaft and the first joint element and between the tool drive shaft and the second joint element are equal in magnitude. The corresponding hinge device may be a Z-arrangement or W-arrangement of two universal joints. In that the angles between the outer shafts (the rigid shaft and the tool drive shaft) and the middle shaft (the connecting element between the first joint member and the second joint member) are the same, the rotational speeds on the drive side and the driven side are the same.

It is particularly advantageous if the transmission or the joint device is coupled to the rigid shaft via a shaft element which is non-rotatably longitudinally displaceable on the rigid shaft. This allows a length compensation between the transmission or the joint device and the rigid Reach the shaft. For example, the shaft element is guided longitudinally displaceable in or on the rigid shaft.

For the same reason, it is advantageous if the transmission or the joint device is coupled to the tool drive shaft via a shaft element which is rotationally fixedly displaceable longitudinally on the tool drive shaft. The shaft element is guided, for example, longitudinally displaceable in or on the tool drive shaft.

It may also be favorable if the rigid shaft is coupled to the drive motor via a shaft element which is longitudinally displaceable in a rotationally fixed manner on the rigid shaft. This allows a length compensation can be achieved, for example, to compensate for thermal expansion can.

It is provided in particular that the rigid shaft is guided to the tool head in a hollow body. This hollow body is formed for example as a tube; For example, the tube is cylindrical. In the hollow body, the rigid shaft between pivot bearings can be free. The rigid shaft does not come into contact with the walls of the hollow body. The hollow body can also serve for the pivotable fixing of the tool head to the holding device.

It is particularly provided that the rigid shaft between the drive motor and the tool head is guided in the hollow body. It can be achieved in a simple manner, a defined "free" leadership of the rigid shaft between pivot bearings.

In particular, the tool head is pivotally supported on the hollow body via a pivot bearing. The hollow body can be formed with such a mechanical stability that the tool head can be held on it (pivotable).

It is advantageous if a cover is arranged between the tool head and the hollow body, which surrounds the gear and / or a pivot bearing at least partially. Through the cover can cover an opening through which the hollow body and the tool head are pivotally connected to each other. Through the cover can be easily prevent the ingress of dust in the transmission and in a pivot bearing.

In particular, the cover comprises a sleeve. The cuff is applied to the tool head and the hollow body. As a result, a good sealing effect can be achieved. The cuff is designed, for example, as a bellows, in order to enable relative ease of pivoting between the hollow body and the tool head in a simple manner.

It is advantageous if the tool head is pivotable about at least one pivot axis, which lies transversely to the axis of rotation of the tool drive shaft. This allows a user to guide the handheld grinder, for example, up a wall.

It can be provided. in that a tool holding device is rotatable about at least one axis of rotation which is substantially parallel to or coincides with the axis of rotation of the tool drive shaft. The rotation may be one full turn or one turn less than 360 °. By such a rotation, a tool holding device and thus a tool can be aligned; This is particularly advantageous if the tool is not rotationally symmetrical. For example, a tool holding device has a triangular outer contour in order to enable a grinding process at corners or edges. By a rotation about an axis parallel to the axis of rotation of the tool drive shaft can be achieved for a user optimized alignment.

Such a rotatability can be achieved in a simple manner if the tool head has a region with a cylindrical outer contour for forming a pivot bearing for the tool holding device. This makes it possible to provide an inner shaft on which an outer shaft can be guided.

It can be provided that the tool head has a securing device in order to lock the rotatability of a tool holding device on the tool head. This is particularly advantageous when various tool holding devices are provided as attachments that can be fixed to the tool head. For certain tool holding devices, a rotation lock must be provided in order to carry out a machining operation. In other tool holding devices, a Turnability may be required. Depending on the tool holding device attachment, the rotatability can then be blocked or released via the securing device.

It is favorable if the tool head is assigned a fixing device for fixing a tool holding device. It can basically be provided that the tool holding device is arranged integrally on the tool head. In particular, a shaft of the tool holding device is then formed by the tool drive shaft.

It is also possible that the tool holding device is detachably fixable. It can then be provided, for example, a basic unit with a drive motor, the rigid shaft and the tool head, wherein on the tool head various tool holding devices can be placed depending on the application. The tool holder attachments may differ, for example, with regard to the rotational speed or else the type of drive (rotating or oscillating). You can also differ by which tool can be fixed to them.

In particular, the tool holding device has a shaft which is coupled to the tool drive shaft or can be coupled. It may in principle be a separate element, which is connectable to the tool drive shaft. It is also possible, when the tool holding device is integrally formed on the tool head, that this shaft and the tool drive shaft are integrally formed.

In one embodiment, the tool holding device has a transmission, via which the shaft is coupled to the tool drive shaft or can be coupled. The gear can be used to set a specific movement type of a tool.

In particular, the transmission is designed as a reduction gear. In the solution according to the invention, the tool drive shaft can be driven at high speeds due to the rigid shaft. If a certain high speed is provided by the drive motor, gear reduction may be required for some applications to drive a tool at a lower speed than the maximum speed provided.

It can be provided that the shaft of the tool holding device has a rotation axis coaxial to the axis of rotation of the tool drive shaft of the tool head. A corresponding tool holding device can be formed with small transverse dimensions. A corresponding tool holding device is suitable for concrete grinding, for example.

It can also be provided that the shaft of the tool holding device has a rotation axis spaced parallel to the axis of rotation of the tool drive shaft of the tool head. This spacing can be achieved for example by the provision of a transmission.

It is also possible that the shaft is designed as an eccentric shaft. As a result, for example, a tool can be driven in an oscillatory motion.

In one embodiment, the tool holding device is rotatable about an axis of rotation parallel to the axis of rotation of the tool drive shaft rotatably fixed to the tool head. This is favorable, for example, when corner areas or edge areas are to be ground. An operator can then set up at a greater distance to such a corner area or edge area.

An embodiment of the tool holding device may have one or more locking elements for blocking the rotatability of the tool holding device about an axis of rotation parallel to the axis of rotation of the tool drive shaft. As a result, a rotationally fixed fixing of the tool holding device on the tool head can be achieved. This is advantageous for "ordinary" grinding operations.

In one embodiment, the tool holding device has a triangular outer contour, at least in a partial region. With such an outer contour, the tool holding device can be positioned in a simple manner on edge regions or corner regions. This results in an extended grinding area.

In particular, an axis of rotation for rotatability of the tool holding device relative to the tool head pierces the triangle at or in the vicinity of a center of gravity of a triangle of a triangular outer contour. (The center of gravity is the geometric center of gravity.) This makes rotation easy.

In one embodiment, it is provided that a tool can be driven in an oscillating manner on the tool holding device. The corresponding tool holding device is in particular an eccentric grinder. Due to the oscillating driving otherwise difficult to access areas such as corner areas and edge areas can be processed for grinding operations by a cylindrical grinder.

The oscillating movement of the tool is achieved for example by an eccentric drive. It can be provided, for example, an eccentric shaft or another eccentric drive.

It is favorable in this context if the tool is fixed on the tool holding device via elastic elements. As a result, an oscillation movement, driven for example by an eccentric shaft, can be made possible in a simple manner.

In particular, elastic elements are located on or in the vicinity of corners of the tool holding device in order to be able to drive the tool in an oscillating manner.

The rigid shaft is in particular coupled directly or via a gear to the drive motor. The transmission is used for example for speed reduction. It is also possible that a transmission is provided for speed increase. But it is also possible in principle that the speed of the drive motor is adjustable and in particular is electronically adjustable.

For example, a reduction gear for coupling the drive motor is provided to the rigid shaft. As a result, for example, rotational speeds of the order of 20,000 revolutions per minute can be reduced to speeds of the order of, for example, 4,000 to 6,000 revolutions per minute or more.

It is favorable in this context, when the transmission is arranged in the same housing as the drive motor. This results in a compact construction, so that the hand-held grinding machine in turn can be used for a user in a simple manner.

It is advantageous if a fluid line is coupled to the tool head. As a result, processing residues such as dust can be extracted. In principle, it is also possible that a processing area, for example, cooling liquid such as water is supplied.

In a structurally simple embodiment, the holding device has a holding bar. This has, for example, a circular outer contour. About such a holding rod, the grinding machine can be easily hold.

It is advantageous if the holding rod is designed as a hollow body. As a result, a cavity is provided, can be transported through the fluid. For example, the cavity, a fluid line is arranged to be able to vacuum over a vacuum cleaner processing residues.

In particular, the retaining bar is designed as a fluid guiding element or a fluid guiding element is arranged on the retaining bar. The holding rod then serves in addition to holding for a user as a "holder" for a fluid guide element or forms a fluid guide element itself.

For example, a fluid line is connected to the support rod or on the support rod, a fluid line is guided, which is coupled to the tool head. This makes it easy to perform a machining residue extraction from a processing area.

It is advantageous if the tool head and / or a tool holding device have one or more fluid spaces which are in fluid-effective connection with a fluid line. As a result, it is possible to provide an extraction area or several extraction spaces in the immediate vicinity of a processing area.

In one embodiment, the second holding element is guided displaceably in the first holding element. The holding elements are formed, for example, as tubes, wherein the second holding element is guided in the first holding element. In this embodiment, the determination of the second holding element on the first holding element can be achieved in a simple manner, for example by a screw-clamp connection.

In an alternative embodiment, the second holding element is displaceably guided on the first holding element. The first holding element is, for example, a stationary element which protrudes, for example, over a housing of the drive motor. Preferably, the first holding element is formed so that in each Verschlebungsstellung the second holding element lies completely on the first holding element. As a result, a stable holding device is provided for each position of the second holding element.

In particular, an outer end of the holding device is formed by the first holding element.

For handling the grinding machine, it is favorable if a grip element is arranged on the second holding element. The grip element can be held, for example, with the right hand, and the second holding element or the first holding element can be grasped with the left hand become. The holding elements are correspondingly designed in their outer contour so that they can be gripped ergonomically.

It can be provided that the grip element has a holder for an electric cable. On the holder, the electric cable can be fixed in order to guide this defined on the grinding machine.

It is favorable if the first holding element or the second holding element or a fluid line (which is guided in the first or second holding element) has a vacuum cleaner connection. As a result, a negative pressure can be generated in a simple manner on a processing area in order to be able to vacuum out processing residues.

It can be provided a tool holding device, which can be used in a simple manner.

For this purpose, a fixing device for releasably fixing the tool holding device to the machining head and a shaft for driving a tool held by the tool holding device are provided, wherein the shaft can be coupled to the tool drive shaft of the tool head.

In this solution, a grinding machine with a tool head is a basic unit to which the tool holder can be releasably fixed as an attachment. For example, a basic unit with a uniform number of revolutions can then be provided, wherein a defined speed can be set by means of a gear in the tool-holding device.

Various types of tool holding devices for various applications can be provided which can be fixed to the tool head. For example, a concrete grinder attachment can be provided on which a high speed grinding tool is driven.

Further advantageous embodiments have already been explained in connection with the grinding machine according to the invention.

Figur 1

eine schematische Gesamtdarstellung eines Ausführungsbeispiels einer erfindungsgemäßen Schleifmaschine mit verkürzter Halteeinrichtung;

Figur 2

eine Draufsicht auf die Schleifmaschine gemäß Figur 1 mit verlängerter Halteeinrichtung;

Figur 3

eine Schnittdarstellung der Schleifmaschine gemäß Figur 1;

Figur 4

eine vergrößerte Darstellung eines Werkzeugkopf-Bereichs der Schleifmaschine gemäß Figur 1;

Figur 5

die gleiche Ansicht wie Figur 4, wobei ein erstes Ausführungsbeispiel einer Werkzeughalteeinrichtung (Betonschleifer) als Aufsatz an dem Werkzeugkopf sitzt;

Figur 6

die gleiche Ansicht wie Figur 4, wobei ein zweites Ausführungsbeispiel einer Werkzeughalteeinrichtung (Rundschleifer) als Aufsatz an dem Werkzeugkopf sitzt;

Figur 7

die gleiche Ansicht wie Figur 4, wobei ein drittes Ausführungsbeispiel einer Werkzeughalteeinrichtung (Exzenterschleifer) als Aufsatz an dem Werkzeugkopf sitzt;

Figur 8

eine Draufsicht auf den Werkzeugkopf mit Werkzeughalteeinrichtung gemäß Figur 7;

Figur 9

eine schematische Teildarstellung eines weiteren Ausführungsbeispiels einer erfindungsgemäßen Schleifmaschine; und

Figur 10

eine Teildarstellung eines weiteren Ausführungsbeispiels einer erfindungsgemäßen Schleifmaschine.

The following description of preferred embodiments is used in conjunction with the drawings for a more detailed explanation of the invention.
Show it:

FIG. 1

a schematic overall view of an embodiment of a grinding machine according to the invention with a shortened holding device;

FIG. 2

a plan view of the grinding machine according to FIG. 1 with extended holding device;

FIG. 3

a sectional view of the grinding machine according to FIG. 1 ;

FIG. 4

an enlarged view of a tool head portion of the grinding machine according to FIG. 1 ;

FIG. 5

the same view as FIG. 4 , wherein a first embodiment of a tool holding device (concrete grinder) sits as an attachment to the tool head;

FIG. 6

the same view as FIG. 4 , wherein a second embodiment of a tool holding device (circular grinder) sits as an attachment to the tool head;

FIG. 7

the same view as FIG. 4 , wherein a third embodiment of a tool holder (eccentric grinder) sits as an attachment to the tool head;

FIG. 8

a plan view of the tool head with tool holding device according to FIG. 7 ;

FIG. 9

a schematic partial view of another embodiment of a grinding machine according to the invention; and

FIG. 10

a partial view of another embodiment of a grinding machine according to the invention.

An embodiment of a hand-held grinding machine according to the invention, which in the FIGS. 1 and 2 shown and designated therein by 10, comprises a holding device 12, via which a user can hold the grinding machine 10 during processing.

On the holding device 12, a tool head 14 is arranged, on which a tool holding device 16 is releasably or permanently fixed or can be fixed.

The holding device 12 comprises a (rigid) holding rod 18 as the first holding element 19. This holding bar 18 is formed as a hollow body and in particular tubular. The holding bar 18 preferably has an edge-free outer contour and inner contour; For example, the outer contour and the inner contour are cylindrical.

In the holding bar 18, a (rigid) second holding member 20 is slidably guided. The second holding member 20 is also formed as a hollow body and, for example, tubular. It is adapted with its outer contour to the inner contour of the support rod 18, so that in the support rod 18, a displacement guide is provided.

By positioning the second holding element 20 with respect to the first holding element 19, the distance of the gripping element 22 from the tool head 14 and thus the length of the holding device 12 with respect to the tool head 14 can be adjusted.

The position of the second holding element 20 relative to the first holding element 19 is infinitely adjustable. For this purpose, a screw-clamping device 26 is provided with a nut 28 (FIG. FIGS. 1 to 3 ). This nut 28 is guided on the first holding element 19 via a thread 30 ( FIG. 3 ) And with the second holding member 20 can be clamped. Due to the jamming of the nut 28 and the second holding member 20, the position of the second holding member 20 is fixed to the first holding member 19.

The nut 28 also serves as a blocking element for the submersibility of the second retaining element 20 in the first retaining element 19: When the grip element 22 abuts the nut 28 ( FIG. 3 ), then the second element 20 can not move further into the first holding element 19.

In the FIGS. 1 and 3 a position of the second holding member 20 with respect to the first holding member 19 is shown, in which the holding device 12 has a minimum length relative to the tool head 14; the second retaining element 20 is so far immersed in the first retaining element 18 that the grip element 22 rests against the nut 28.

In FIG. 2 an extended position of the holding device 12 is shown, in which the gripping element 22 is spaced from the nut 28.

The grip element 22 has a holder 32 on which an electric cable 34 for cable management can be fixed.

The second element 22 may have a vacuum cleaner port 36 at one end to connect a vacuum cleaner (not shown in the drawing).

On the holding bar 18, a housing 38 is fixed in a central region, in which a drive motor 40 (FIG. FIG. 3 ) is arranged. The housing 38 is designed so that a motor shaft 42 spaced from the support rod 18 is positioned substantially parallel to a longitudinal direction 44 of the support rod 18. In the longitudinal direction 44, the second holding element 20 is guided relative to the retaining rod 18 as the first holding element 19 releasably displaceable.

The drive motor 40 is arranged below the holding rod 18.

The drive motor 40 is supplied via the electric cable 34 with electrical energy. On the housing 38, for example, a sealed switch 46 is arranged.

In the housing 38, a gear 48 may be arranged, which is in particular a reduction gear. About such a gear 48, the speed can be reduced. (It is basically also possible to provide a transmission gear or a non-speed-changing transmission.

The motor shaft 42 is coupled directly or via the gear 48 to a rigid shaft 50, which is guided to the tool head 14. The rigid shaft 50 is oriented parallel to the longitudinal direction 44 of the holding rod 18. It is parallel or coaxial with the motor shaft 42.

The rigid shaft 50 is guided in a (rigid) hollow body 52, which is arranged parallel to the holding rod 18. The hollow body 52 is in particular tubular. It is fixed to the housing 38 at one end 54. In a central region 56 of the hollow body 52 is connected via a web 58 with the holding bar 18. The web 58 is at or in the region of one end 60 of the support rod 18, said end 60 is located at a portion of the support rod 18 which extends beyond a side 62 of the housing 38 addition. The side 62 of the housing 38 is opposite to a side 64, over which that part of the support rod 18 extends, on which the screw-clamping device 26 is arranged.

The motor shaft 42 rotates about a rotation axis 66 which is substantially parallel to the longitudinal direction 44. The rigid shaft 50 rotates (driven by the drive motor 40) about an axis of rotation 68 which is substantially parallel to the axis of rotation 66 of the drive motor 40. By the gear 48, the rotation axis 68 is offset parallel to the rotation axis 66, that is, this has a greater distance to the support rod 18 as the axis of rotation 66 of the drive motor 40. It is basically also possible that a transmission is provided which does not have a reduction gear is to increase the distance of the rotation axis 68 of the support rod 18 as compared to the motor shaft 42.

It is also possible in principle that the axis of rotation 68 and the axis of rotation 66 are coaxial.

The rigid shaft 50 rotates about the axis of rotation 68 and is freely supported in the (rigid) hollow body 52, that is, the rigid shaft 50 is spaced from the walls of the hollow body 52 out.

The tool head 14 is pivotable about a pivot axis 70 relative to the holding device 12. The pivot axis 70 is transverse and in particular perpendicular to the axis of rotation 68 of the rigid shaft 50, namely for each pivot angle 72. The pivot angle 72 is defined in a plane which is spanned by the axis of rotation 68 of the rigid shaft 50 and a direction 74 perpendicular to a tool effective area. At a pivoting angle of 0 °, the direction 74 and the axis of rotation 68 of the rigid shaft 50 are coaxially oriented. The pivot axis 70 is perpendicular to this plane.

The pivotability of the tool head 14 on the holding device 12 is provided by a pivoting of the tool head 14 on the hollow body 52. For this purpose, a pivot bearing 76 is provided ( FIG. 4 ), which is arranged in a housing 78 of the tool head 14. The pivot bearing 76 includes, for example, a cylindrical pin 80 which is rotatably disposed in the housing 78. This cylindrical pin 80 forms an inner shaft. On the pin 80, a ring member 82 is guided, which forms an outer shaft. This ring member 82 is firmly seated on the hollow body 52; it is (movably) positioned in the housing 78.

The housing 78 has an opening 84 through which a part 86 of the hollow body 52 is guided, on which the ring element 82 is fixed. The breakthrough opening 84 is in this case designed such that the swivel angle range is fixed over it, and furthermore the "zero position" (swivel angle 0 °) is defined. The pivoting angle 0 ° is determined by the fact that the part 86 bears against a first wall 88 of the aperture 84. The maximum pivoting angle (which is, for example, in the range between 30 ° and 80 °) is defined by the fact that the part 86 rests against a wall 90 of the opening 84 opposite the first wall 88. (In FIG. 4 this concern is shown at maximum swing angle.)

In the housing 78, a tool drive shaft 92 is rotatably mounted about a rotation axis 94. The axis of rotation 94 is coaxial with the direction 74, that is, the axis of rotation 94 and the axis of rotation 68 of the rigid shaft 50 span a plane to which the pivot axis 70 is perpendicular.

The tool drive shaft 92 is mounted in the housing 78 of the tool head 14 via a first pivot bearing 96 and a spaced second pivot bearing 98. These rotary bearings 96, 98 are in particular ball bearings.

The rigid shaft 50 is rotatably mounted in the region of one end of the hollow body 52 via a rotary bearing 100, such as a ball bearing, in order to obtain a defined guidance and attack on the tool head 14.

The transmission of the torque from the motor shaft 42 to the tool head 14 via a transmission device 102, which includes the rigid shaft 50. This transmission device 102 comprises a gear 104 for coupling the rigid shaft 50 to the tool drive shaft 92. The rigid shaft 50 is a drive shaft relative to this gear 104 and the tool drive shaft 92 is an output shaft relative to this gear 104.

The gear 104 is formed so that the tool drive shaft 92 is driven at the same speed as the rigid shaft 50 and thereby the pivoting of the tool head 14 is ensured on the holding device 12.

The transmission 104 is disposed in the housing 78 on the pivot bearing 76. It is designed as a gear transmission and in particular as a bevel gear.

The gear 104 is configured such that the axis of rotation 68 of the rigid shaft 50 and the axis of rotation 94 of the tool drive shaft 92 intersect at each relative position of the tool head 14 to the rigid shaft 50 at a point. This intersection lies on the pivot axis 70.

The transmission 104 comprises an annular gear 106, which is arranged rotatably about an axis of rotation in the housing 78, wherein this axis of rotation coincides with the pivot axis 70.

At one end of the rigid shaft 50, a bevel gear 108 is arranged, which engages with teeth in corresponding teeth of the gear 106; by rotation of the rigid shaft 50, the gear 106 is rotated.

At one end of the tool drive shaft 92 also sits a bevel gear 110, which is coupled to the gear 106. By rotation of the gear 106, the tool drive shaft 92 is rotated, that is, the gear 106 transmits the torque of the rigid shaft 50 to the tool drive shaft 92. This torque transmission is independent of the pivot angle 72 of the tool head 14 with respect to the holding device 12th

Between the housing 78 and a front region of the hollow body 52, a cover 112 is arranged, which is in particular designed as a sleeve. This cover 112 serves to cover the aperture 84 to prevent the ingress of dust, liquid and the like into the housing 78.

For example, the cover 102 is formed as a bellows 114 which sealingly abuts at one end 116 on an outer side of the hollow body 52 and sealingly abuts the housing 78 at the other end 118.

The cover 112 is formed so that the covering action for the relative pivotal position between the hollow body 52 and the tool head 14 is present.

The tool head 14 has a connection 120 for a fluid line 122. This fluid line 122 is guided at least between the connection 120 and the holding rod 18 and in particular connected to the end 60 of the holding rod 18. The connection 120 is formed, for example, on a tubular element 124, which sits firmly on the tool head 14.

It can be provided that the fluid line 122 is coupled to the retaining bar 18. It may also be provided that the fluid line 122 is performed by the holding rod 18 and by the second holding member 20 and is in fluidly effective connection with the vacuum cleaner port 36. In this case, when the second holding element 20 is displaced relative to the holding bar 18, the second holding element 20 is also displaced relative to the fluid line 122.

Via the fluid line 122, processing waste and in particular dust can be extracted from a processing area.

In principle, it can also be provided that, for example, water can be conveyed to a processing area via the fluid line 122.

In principle, it can also be provided that a cavity 126 of the first holding element 18 (which continues in the second holding element 20) comprises a plurality of chambers and comprises, for example, a first chamber and a second chamber. For example, processing residues can be sucked off via the first chamber and fluid can be supplied to the processing area via the second chamber.

The fluid line 122 is flexible, so that the pivoting of the tool head 14 is ensured on the holding device 12.

The tubular element 124 is arranged at a distance from the tool drive shaft 92.

The housing 78 in one embodiment has a region 128 with a cylindrical outer contour, this region extending parallel to the direction 74 rotationally symmetrical to an axis of symmetry 130 ( FIG. 4 ). The axis of symmetry 130 is spaced parallel to the axis of rotation 94 of the tool drive shaft 92.

The region 128 with a cylindrical outer contour makes it possible to provide a pivot bearing for a correspondingly designed tool holding device 16 in order to enable its rotation on the tool head 14. The housing 78 forms an inner shaft about which the tool holding device is rotatable to its orientation.

A securing device 132 may also be provided in order to lock the rotatability of the tool holding device 16 on the tool head 14, that is to enable the tool holding device 16 to be secured against rotation on the tool head 14. For example, the securing device 132 comprises one or more recesses 134 (FIG. FIG. 4 ), in each of which a locking pin of a tool holding device can engage as a blocking element.

In one embodiment of a grinding machine according to the invention, it is provided that the tool holding device 16 is an integral part of the tool head 14.

In another embodiment, tool holding devices can be detachably connected as attachments with the tool head 14, wherein, for example, different tool holding devices can be provided depending on the application.

A first embodiment of a tool holding device according to the invention, which in FIG. 5 shown there and designated as a whole by 136, has a housing 138 in which a shaft 140 is arranged. The shaft 140 is spaced in a first pivot 142 and in a second Rotary bearing 144 rotatably guided. The pivot bearings 142, 144 are, for example, ball bearings. An axis of rotation of the shaft 140 is coaxial with the axis of rotation 94 of the tool drive shaft 92.

The shaft 140 is rotatably coupled directly to the tool drive shaft 92. The shaft 140 then rotates at the same speed as the tool drive shaft 92.

With the shaft 140, a tool plate 146 is rotatably connected to which a tool such as a grinding wheel can be fixed.

The housing 138 has an extension 148 in which the tool plate 146 is positioned.

In the housing 138, a channel 150 is arranged, which is connectable to the tubular element 124 of the tool head 14. This channel 150 points into a fluid space 152 above the tool plate 146. The fluid space 152 surrounds the tool plate 146 in an annular manner.

The extension 148 has an annular wall 154, wherein between the tool plate 146 and the wall 154, an annular space 156 is formed, which communicates with the fluid chamber 152 in fluidly effective connection. As a result, machining residues can be sucked through the channel 150.

The housing 138 has a hollow cylinder space 158 with which it can be placed on the area 128 of the tool head 14. It can be a axial fixation of the tool holder 136 to the tool head 14 done.

The tool holding device 136 has one or more locking pins 159 as locking elements, which or which dive into the corresponding recess or recesses 134 when the tool holding device 136 is fixed to the tool head 14. As a result, the relative rotatability of the tool holding device 136 on the tool head 14 is blocked.

The grinding machine 10 with the tool holder 136 functions as follows:

A user grasps the hand-held grinding machine 10 on the holding device 12. For example, he holds the handle 24 with his right hand and includes the holding bar 18 or the second holding member 20 with the left hand. The length of the holding device 12 (that is, the relative position of the second holding member 20 to the first holding member 19) set according to the application.

By actuating the switch 46, the drive motor 40 is activated. As a result, the motor shaft 42 is set in rotation. For example, a typical speed is on the order of 20,000 revolutions per minute.

If a reduction gear is provided as the transmission 48, then this speed is reduced to, for example, 4 500 revolutions per minute or 6,000 revolutions per minute. With this speed, the rigid shaft 50 is driven.

At this speed, the tool drive shaft 92 and thereby the shaft 140 and thus the tool is driven in a rotational movement.

The tool holding device 136 is formed in this embodiment as a detachable attachment and thus in particular as a replaceable attachment for the grinding machine 10.

Tool speeds of the order of magnitude of up to approximately 6,000 revolutions per minute or more can be achieved (depending on the reduction by the gear 48). This allows, for example, grinding concrete. The tool holder 136 may be configured as a concrete grinder.

By way of the fluid line 122, it is possible to extract machining residues and, in particular, machining chips and machining dust.

By the torque transmission from the drive motor 40 to the tool head 14 via the rigid shaft 50 high rotational speeds for a tool are possible; the number of revolutions can be on the order of 6,000 revolutions per minute. By the solution according to the invention, a higher power can be transmitted. Compared to the transmission via a flexible shaft and the wear on the transmission shaft from the drive motor 40 to the tool head 14 (in this case, the rigid shaft 50) is reduced.

It is also possible in principle that the speed of the drive motor 40 is adjustable; For example, the speed is electronically adjustable. For the reduction then no mechanical transmission as the transmission 48 is necessary. In principle, it is also possible to provide a transmission gearbox for engines with a low rotational speed.

In a second embodiment of a tool holding device, which in FIG. 6 shown and designated there as a whole by 160, a housing 162 is provided, in which a tool plate 164 is rotatably mounted. The housing 162 has an extension region 166 for this purpose.

The tool plate 164 is non-rotatably coupled to a shaft 168, which rotates about an axis of rotation 170. The shaft 168 is mounted in a pivot bearing 172; This pivot bearing is in particular a ball bearing.

The axis of rotation 170 is spaced parallel to the axis of rotation 94 of the tool drive shaft 92.

The tool holder 160 has a stub shaft 174, which is rotatably mounted in a pivot bearing 176 with a rotation axis coaxial with the axis of rotation 94 of the tool drive shaft 92. The stub shaft 174 is rotatably coupled to the tool drive shaft 92.

For coupling the stub shaft 174 to the shaft 168, a gear 178 is provided. The gear 178 includes a gear 180 which is rotatably connected to the shaft 168. The gear 180 is over the stub shaft 174 is driven in a rotational movement to rotate the shaft 168. The stub shaft 174 has gear teeth as a gear, in which the gear 180 engages. Relative to the transmission 178, the stub shaft 174 is a drive shaft and the shaft 168 is an output shaft.

By the transmission 178, a speed reduction is achieved; the speed of the tool drive shaft 92 can be reduced to achieve a reduced speed for certain applications. For example, a reduction by a factor of three. If the tool drive shaft 92 is driven, for example, with a number of revolutions of 4 500 revolutions per minute, then can be achieved by such a reduction, a speed of 1 500 revolutions per minute on the shaft 168 and thus for a tool.

The tool holding device 160 includes one or more locking pins 182, which can dive into the corresponding recess or recesses 134 of the tool head 14 in order to fix the tool holding device 136 in a rotationally fixed manner to the tool head 14.

The tool holder 160 includes, as described in connection with the tool holder 136, a hollow cylinder space 184, via which it can be placed on the tool head 14.

The tool holder 160 is designed, for example, as a cylindrical grinder attachment, wherein a rotational speed is provided (in dependence on the gear 178), which is smaller than the rotational speed of the rigid shaft 50 and the tool drive shaft 92.

Otherwise, the tool holder 160 functions as described above in connection with the tool holder 136.

In a third embodiment of a tool holding device, which in the FIGS. 7 and 8th shown there and designated as a whole by 186, a housing 188 is provided, which has a triangular outer contour 190. The housing 188 has an extension portion 192 in which a tool plate 194 is disposed. The extension portion 192 has a triangular shape having a first corner 196a, a second corner 196b, and a third corner 196c (not shown in the drawing).

In particular, the triangle is an equilateral triangle.

The housing 188 may have a bevel 198 or chamfer on an outside.

The housing 188 has a hollow cylinder space 200, via which it can be placed rotatably on the tool head 14. The axis of symmetry 130 as the axis of rotation of the tool holder 186 pierces the center of gravity of the triangular structure 190.

The tool plate 194 is arranged and formed such that a tool 202 held by it is arranged outside of the housing 188.

In the housing 188, a shaft 204 is rotatably guided, which is rotatably coupled to the tool drive shaft 92. For rotation guidance of the shaft 204, a first pivot bearing 206 and a spaced second pivot bearing 208 are provided.

The shaft 204 is formed as an eccentric shaft with an eccentric portion 210, that is with a portion having an axis 212 which is parallel spaced from the axis of rotation 94 of the tool drive shaft 92. About this eccentric portion 210, the shaft 204 is coupled to the tool plate 194. The eccentric region 210 is guided in a rotary bearing 214.

About the eccentric portion 210, the rotational movement of the tool drive shaft 92 can be converted into an oscillating movement of the tool plate 194 and thus of the tool 202.

The tool plate 194 is held by elastic elements 216a, 216b, 216c on the housing 188. The elastic elements 216a, 216b, 216c are, in particular, rubber blocks or rubber strips. In each case, an elastic element is assigned to a corner area of the triangular structure 190. The tool plate 194 is "free" held on the housing 188 to allow an oscillatory movement.

The formation of the elastic members 216a, 216b, 216c determines the moving shape of the tool 202.

The triangular structure 190 of the housing 188 allows grinding at corner regions and edge regions. The tool 202 also has a triangular structure to allow for grinding at corners.

The tool holder 186 is designed as an eccentric grinding attachment. It can be placed on the tool head 14 and rotated there. For example, a stop for blocking the free rotation is provided by 360 °. This allows alignment for corner areas or edge areas of an application.

Disposed in the housing 188 are one or more fluid spaces 218 which are in fluid communication with the tube member 124. This allows extraction of processing residues.

To drive the oscillation movement of the tool plate 194, another eccentric device may be provided as an eccentric shaft 204.

In a further embodiment ( FIG. 9 ) of a grinding machine according to the invention, a rigid shaft 226 is provided which, like the rigid shaft 50 described above, is coupled to the drive motor. This rigid shaft 226 is guided in a hollow body 228. On the rigid shaft 226 is rotatably connected to this a shaft member 230. The shaft member 230 is rotatably supported via a bearing means 232 to the hollow body 228. The bearing device 232 is formed for example via plain bearings or ball bearings.

The shaft member 230 is coupled to the rigid shaft 226 and may be considered part of the rigid shaft 226. It is for length compensation in a certain range relative to the rigid shaft 226 slidably. For this purpose, the rigid shaft 226 has a recess 234 and the shaft element 230 has an immersion region 236, with which it is immersed in the recess 234. The immersion region 236 and the recess 234 are designed such that, in the case of a non-rotatable coupling between the shaft element 230 and the rigid shaft 226, a longitudinal displacement in a direction parallel to a rotation axis 238 is possible. This flexibility is in FIG. 9 indicated by the double arrow 240.

On the hollow body 228, a tool head 242 is pivotably mounted on a pivot bearing 244 about a pivot axis 246. The pivot axis 246 is perpendicular to the axis of rotation 238 and is cut by this.

The tool head 242 has a tool drive shaft 248. This is rotatable about a rotation axis 250. The rotation axis 250 also intersects the pivot axis 246. As a result, the axis of rotation 238 of the rigid shaft and the axis of rotation 250 of the tool drive shaft 250 intersect in the pivot axis 246 of the tool head 242.

The rigid shaft 226 is coupled via the shaft member 230 to the tool drive shaft 248 via a hinge device 252.

The tool head 242 is otherwise configured as described above. The hinge device 252 is a universal joint pair or a universal joint pair educated. It comprises a first joint element 254, which is pivotably coupled about a first pivot axis 256 to the shaft element 230 and thus to the rigid shaft 226. The first pivot axis 256 is parallel to the pivot axis 246 of the tool head 242 and is perpendicular to the axis of rotation 238 of the rigid shaft 226.

Furthermore, the first joint element 254 is mounted pivotably on a connecting element 260 about a third pivot axis 258. The third pivot axis 258 is transverse to the first pivot axis 256 and to the axis of rotation 238. In particular, the third pivot axis 258 is perpendicular to the first pivot axis 256.

The tool drive shaft 248 is coupled to the hinge assembly 252 via a second hinge member 262. The second hinge element is pivotally mounted about a second pivot axis 264 on the tool drive shaft 248. The second pivot axis 264 lies transversely to the axis of rotation 50 of the tool drive shaft 248. The second pivot axis 264 is also mounted on the connecting element 260 about a fourth pivot axis 266. The fourth pivot axis 266 is transverse to the axis of rotation 50. It is also transverse and in particular perpendicular to the second pivot axis 264th

The connecting member 260 connects the first joint member 254 and the second joint member 262 with each other and thus also connects the rigid shaft 226 and the tool drive shaft 248. Thus, a three-piece propeller shaft is formed, which includes the rigid shaft 226, the connecting member 260 and the tool drive shaft 248. (In this context, the shaft member 230 is considered part of the rigid shaft 226.)

The first pivot axis 256 and the second pivot axis 264 are parallel to each other. Further, the third pivot axis 258 and the fourth pivot axis 266 are parallel to each other, in each pivotal position of the tool head 242.

The first pivot axis 256 and the third pivot axis 258 span a plane. Further, the second pivot axis 264 and the fourth pivot axis 266 span a plane. The pivot axis 246 of the pivot bearing 244 is located between these two levels, in each pivotal position of the tool head 242nd

The flexion angle α ₁ between the hinge device 252 and the rigid shaft 226 and the flexure angle α ₂ between the hinge device 252 and the tool drive shaft 248 is dependent on the pivotal position of the tool head 242. The hinge device 252 is formed and the coupling to the rigid shaft 226 and To the tool drive shaft 248 takes place such that the bending angles α ₁ and α _{2 are} in the same plane. In particular, the points of intersection between the first pivot axis 256 and the third pivot axis 258 and the second pivot axis 264 and the fourth pivot axis 266 lie in the same plane.

Furthermore, the deflection angles α ₁ and α ₂ are at least approximately equal in magnitude. Angular differences smaller than 3 ° may be possible.

As a result of this design of the joint device, it is possible for the same speed to be present on the drive side (on the rigid shaft 226 side) and on the output side (the side of the tool drive shaft 248) at each pivoting position of the tool head 242.

The hinge device 256 is made compact with the pair of hinge elements 254 and 262 and the connector 260 between them. The connecting element 260 forms a middle shaft between the outer shafts 262 (rigid shaft) and 258 (tool drive shaft). At the in FIG. 9 As shown, a W-arrangement is present, since the bending angle is in the same direction.

In a further embodiment, which is in FIG. 10 is shown, a holding device 270 comprises a first holding element 272, which is for example tubular. On the first holding element, a drive motor 274 is arranged, which sits in particular in a housing 276. Connected to the housing is a hollow body 278, in which a rigid shaft 280 is guided, which corresponds to the rigid shaft 50 or 226.

The hollow body 278 and the first holding element 272 are connected via a web 282, which in the vicinity of a tool head (in FIG. 10 not shown) sits.

A fluid line 284 which leads to the tool head is coupled to or guided by the first retaining element 272. The first holding element 272 has correspondingly an inner cavity.

At an outer end 286, the first retaining element 272 has a connection 286 for a vacuum cleaner.

An outer end of the first holding member 272 also defines an outer end of the corresponding grinding machine.

On the first holding element 272 a particular tubular second holding element 282 is guided displaceably. At or near one end of this second support member 282, a handle member 290 is fixedly arranged. Due to the displacement position of the second holding element 288 on the first holding element 272, the distance of the gripping element 290 to the housing 276 or to the connection 286 is predetermined. This distance is adjustable. For this purpose, a fixing device 292 is provided, via which the longitudinal position of the second holding element 282 can be fixed to the first holding element 272.

In FIG. 10 For example, a position of the second retaining element 288 on the first retaining element 272 is shown, in which the grip element 290 bears against the housing 276. For this purpose, the housing 276 has, for example, a recess 294 into which a holding base 296 for the grip element 290 can be inserted.

From the in FIG. 10 shown position, the second holding element 288 can be moved with the handle member 290 away from the housing 276 (in FIG. 10 indicated by the arrow 298).

On the housing 276, a handle member 300 is fixedly arranged or formed. This grip element is designed in particular as a bow-shaped handle.

The first holding element 272 is designed such that in every position of the second holding element 288 it is guided completely, that is to say over its entire length, on the first holding element 272. In the furthest withdrawn position (in FIG. 10 indicated by non-solid lines and provided with the reference numeral 302), the second holding element 288 has its greatest distance from the web 282.

It can be provided that on the rigid shaft 280, a shaft member 304 rotatably mounted longitudinally displaceable. This shaft element is immersed, for example, over a dip area in a recess of the rigid shaft 280, wherein the immersion area and the recess are formed so that a longitudinal displacement parallel to a rotation axis of the rigid shaft 280 is made possible. This solution allows a length compensation to be achieved.

Claims (69)

1. A handheld abrasion machine, comprising a holding device (12; 270) for holding the abrasion machine, a drive motor (40; 274) which is arranged on the holding device (12; 270), a tool head (14; 242) which is arranged to pivot relative to the holding device (12; 270) about at least one pivotal axis (70; 246) and comprises a tool drive shaft (92; 248) that is driven by the drive motor (40; 274) and a transfer device (102) for transmitting torque from the drive motor (14; 274) to the tool drive shaft (92; 248), wherein the length of the holding device (12; 270) with respect to the tool head (14) is adjustable and the holding device (12; 270) comprises a first holding element (19; 272) and a second holding element (20; 288) which are displaceable relative to one another in lockable manner,
   characterized in that the second holding element (20; 288) is guided in displaceable manner in or on the first holding element (19; 272) and the drive motor (40; 274) is fixed to the first holding element (19; 272), and in that a handle element (22; 290) is arranged on the second holding element (20; 288), the spacing of said handle element relative to the tool head (14; 242) being adjustable by the positioning of the second holding element (20; 288) with respect to the first holding element (19; 272).
2. An abrasion machine in accordance with Claim 1, characterized in that the transfer device (102) comprises a rigid shaft (50; 226) which is coupled to the tool drive shaft (92; 248) by gearing (104) or a linkage device (252).
3. An abrasion machine in accordance with Claim 2, characterized in that the gearing (104) or the linkage device (252) is arranged on a pivotal bearing (76; 244) or in the proximity of a pivotal bearing (76; 244) for the tool head (14; 242).
4. An abrasion machine in accordance with Claim 2 or 3, characterized in that the tool head (14; 242) is arranged to pivot relative to the rigid shaft (50; 226).
5. An abrasion machine in accordance with any of the Claims 2 to 4, characterized in that a rotational axis (68; 238) of the rigid shaft (50; 226) is located perpendicularly relative to a pivot axis (70; 246) of the tool head (14; 242).
6. An abrasion machine in accordance with any of the Claims 2 to 5, characterized in that a rotational axis (68; 238) of the rigid shaft (50; 226) and a rotational axis (94; 250) of the tool drive shaft (92; 248) intersect at a point in each position of the tool head (14; 242).
7. An abrasion machine in accordance with Claim 6, characterized in that the point of intersection is located on a pivot axis (70; 246) of the tool head (14; 242).
8. An abrasion machine in accordance with any of the Claims 2 to 7, characterized in that the gearing (104) is in the form of a toothed gear unit.
9. An abrasion machine in accordance with Claim 8, characterized in that, for the purposes of transferring torque from the rigid shaft (50) to the tool drive shaft (92), there is provided a gear wheel (106) which is driven by the rigid shaft (50) and which is coupled to the tool drive shaft (92).
10. An abrasion machine in accordance with Claim 9, characterized in that a rotational axis of the gear wheel (106) is coaxial with a pivot axis (70) of the tool head (14).
11. An abrasion machine in accordance with any of the Claims 2 to 10, characterized in that the gearing (104) is in the form of a bevel gear unit.
12. An abrasion machine in accordance with Claim 11, characterized in that a bevel gear (108) is arranged on the rigid shaft (50).
13. An abrasion machine in accordance with Claim 11 or 12, characterized in that a bevel gear (110) is arranged on the tool drive shaft (92).
14. An abrasion machine in accordance with any of the Claims 2 to 8, characterized in that the linkage device (252) comprises a first joint element (254) which is coupled to the rigid shaft (226) in pivotal manner so that it is pivotal about a first pivot axis (256), and comprises a second joint element (262) which is coupled to the tool drive shaft (248) such that it is pivotal about a second pivot axis (264).
15. An abrasion machine in accordance with Claim 14, characterized in that the first pivot axis (256) is oriented perpendicularly relative to a rotational axis (238) of the rigid shaft (226).
16. An abrasion machine in accordance with Claim 14 or 15, characterized in that the second pivot axis (264) is oriented perpendicularly relative to a rotational axis (250) of the tool drive shaft (248).
17. An abrasion machine in accordance with any of the Claims 14 to 16, characterized in that the first pivot axis (256) and the second pivot axis (264) are oriented parallel to each other.
18. An abrasion machine in accordance with any of the Claims 14 to 17, characterized in that a rotational axis (238) of the rigid shaft (226) intersects the first pivot axis (256).
19. An abrasion machine in accordance with any of the Claims 14 to 18, characterized in that a rotational axis (250) of the tool drive shaft (248) intersects the second pivot axis (264).
20. An abrasion machine in accordance with any of the Claims 14 to 19, characterized in that the first joint element (254) is pivotal about a third pivot axis (258) which is oriented transversely relative to the first pivot axis (256).
21. An abrasion machine in accordance with Claim 20, characterized in that the second joint element (262) is mounted pivotally about a fourth pivot axis (266) which is transverse to the second pivot axis (262).
22. An abrasion machine in accordance with Claim 21, characterized in that the third pivot axis (258) and the fourth pivot axis (266) are oriented parallel to each other.
23. An abrasion machine in accordance with any of the Claims 20 to 22, characterized in that the first joint element (254) is mounted on a connecting element (260) to the second joint element (262) pivotally about the third pivot axis (258).
24. An abrasion machine in accordance with any of the Claims 21 to 23, characterized in that the second joint element (262) is mounted on a connecting element (260) to the first joint element (254) pivotally about the fourth pivot axis (266).
25. An abrasion machine in accordance with any of the Claims 20 to 24, characterized in that the pivot axis (246) of the tool head (242) is located between the plane defined by the first pivot axis (256) and the third pivot axis (258) and the plane defined by the second pivot axis (264) and the fourth pivot axis (266).
26. An abrasion machine in accordance with any of the Claims 14 to 25, characterized in that an at least three-part drive shaft is formed by means of the rigid shaft (226), the linkage device (252) and the tool drive shaft (248).
27. An abrasion machine in accordance with any of the Claims 14 to 26, characterized in that the inclination angle (α₁) between the rigid shaft (226) and the first joint element (254) and the inclination angle (α₂) between the tool drive shaft (248) and the second joint element (262) are located in one plane.
28. An abrasion machine in accordance with Claim 27, characterized in that the magnitudes of the inclination angle (α₁) between the rigid shaft (226) and the first joint element (254) and the inclination angle (α₂) between the tool drive shaft (248) and the second joint element (262) are at least approximately equal.
29. An abrasion machine in accordance with any of the Claims 2 to 28, characterized in that the linkage device (250) is coupled to the rigid shaft (226) by a shaft element (230) which is longitudinally displaceable on the rigid shaft (226) in mutually non-rotatable manner.
30. An abrasion machine in accordance with any of the Claims 2 to 29, characterized in that the linkage device (252) is coupled to the tool drive shaft by a shaft element which is longitudinally displaceable on the tool drive shaft (248) in mutually non-rotatable manner.
31. An abrasion machine in accordance with any of the Claims 2 to 30, characterized in that the rigid shaft (280) is coupled to the drive motor (274) by a shaft element (304) which is longitudinally displaceable on the rigid shaft (280) in mutually non-rotatable manner.
32. An abrasion machine in accordance with any of the Claims 2 to 31, characterized in that the rigid shaft (50; 280) is guided to the tool head (14) in a hollow body (52; 278).
33. An abrasion machine in accordance with Claim 32, characterized in that the rigid shaft (50; 280) is guided through the hollow body (52; 278) between the drive motor (40; 274) and the tool head (14).
34. An abrasion machine in accordance with Claim 32 or 33, characterized in that the tool head (14; 242) is held pivotally on the hollow body (52) by means of a pivotal bearing (76; 244).
35. An abrasion machine in accordance with any of the Claims 32 to 34, characterized in that a cover (112), which at least partly surrounds the gearing (104) or the linkage device (250) and/or a pivotal bearing (76), is arranged between the tool head (14) and the hollow body (52).
36. An abrasion machine in accordance with Claim 35, characterized in that the cover (112) comprises a sleeve (114).
37. An abrasion machine in accordance with any of the preceding Claims, characterized in that the tool head (14; 242) is pivotal about at least one pivot axis (70; 246) which is located transversely relative to the rotational axis (94; 250) of the tool drive shaft (92; 248).
38. An abrasion machine in accordance with any of the preceding Claims, characterized in that a tool holding device (186) is rotatable about at least one axis of rotation (130) which is substantially parallel to the rotational axis (94) of the tool drive shaft (92) or coincides therewith.
39. An abrasion machine in accordance with Claim 38, characterized in that the tool head (14) comprises a region (128) having a cylindrical outer contour for forming a rotary bearing for a tool holding device (16; 186).
40. An abrasion machine in accordance with any of the preceding Claims, characterized in that the tool head (14) comprises a security device (132) for preventing a tool holding device (16; 136; 160) from rotating on the tool head (14).
41. An abrasion machine in accordance with any of the preceding Claims, characterized in that the tool head (14) has associated therewith a fixing device for fixing a tool holding device (16; 136; 160; 186).
42. An abrasion machine in accordance with Claim 41, characterized in that the tool holding device (16; 136; 160; 186) is arranged to be fixed in releasable manner.
43. An abrasion machine in accordance with Claim 41 or 42, characterized in that the tool holding device (136; 160; 186) comprises a shaft (140; 168; 204) which is coupled or is arranged to be coupled to the tool drive shaft (92).
44. An abrasion machine in accordance with any of the Claims 41 to 43, characterized in that the tool holding device (160) comprises gearing (178) via which the shaft (168) is coupled or is arranged to be coupled to the tool drive shaft (92).
45. An abrasion machine in accordance with Claim 44, characterized in that the gearing (178) is in the form of a reduction gear unit.
46. An abrasion machine in accordance with any of the Claims 41 to 45, characterized in that a shaft (140) of the tool holding device (136) comprises a rotational axis which is coaxial with the rotational axis (94) of the tool drive shaft (92) of the tool head (14).
47. An abrasion machine in accordance with any of the Claims 41 to 46, characterized in that a shaft (168) of the tool holding device (160) comprises a rotational axis (170) which is parallel to and spaced from the rotational axis (94) of the tool drive shaft (92) of the tool head (14).
48. An abrasion machine in accordance with any of the Claims 41 to 47, characterized in that a shaft of the tool holding device (186) is in the form of an eccentric shaft (204).
49. An abrasion machine in accordance with any of the Claims 41 to 48, characterized in that the tool holding device (186) is arranged to be fixed on the tool head (14) such as to be rotatable about an axis of rotation (130) which is parallel to the rotational axis (94) of the tool drive shaft (92).
50. An abrasion machine in accordance with any of the Claims 41 to 49, characterized in that the tool holding device (136; 160) comprises one or more blocking elements (159; 182) for preventing the tool holding device (136; 160) from rotating about an axis of rotation (130) which is parallel to the rotational axis (94) of the tool drive shaft (92).
51. An abrasion machine in accordance with any of the Claims 41 to 50, characterized in that at least a partial region of the outer contour of the tool holding device (186) is triangular.
52. An abrasion machine in accordance with Claim 51, characterized in that, with regard to a triangle of the triangular outer contour, an axis of rotation (130) for the rotatability of the tool holding device (186) relative to the tool head (14) passes through the triangle at or in the proximity of a centroid of the triangle.
53. An abrasion machine in accordance with any of the Claims 41 to 52, characterized in that a tool (202) is arranged to be driven in oscillatory manner by the tool holding device (186).
54. An abrasion machine in accordance with Claim 53, characterized in that the tool (202) is driven eccentrically.
55. An abrasion machine in accordance with Claim 53 or 54, characterized in that the tool (202) is fixed to the tool holding device (186) by means of resilient elements (216a, 216b, 216c).
56. An abrasion machine in accordance with Claim 55, characterized in that resilient elements (216a, 216b, 216c) are arranged at or in the proximity of corners (196a, 196b, 196c) of the tool holding device (186).
57. An abrasion machine in accordance with any of the Claims 2 to 56, characterized in that the rigid shaft (50) is coupled directly or through gearing (48) to the drive motor (40).
58. An abrasion machine in accordance with Claim 57, characterized in that a reduction gear is provided for coupling the drive motor (40) to the rigid shaft (50).
59. An abrasion machine in accordance with Claim 57 or 58, characterized in that the gearing (48) is arranged in the same housing (38) as the drive motor (40).
60. An abrasion machine in accordance with any of the preceding Claims, characterized in that the tool head (14) is coupled to a fluid line (122).
61. An abrasion machine in accordance with any of the preceding Claims, characterized in that the holding device (12; 270) comprises a holding bar (18; 272; 288).
62. An abrasion machine in accordance with Claim 61, characterized in that the holding bar (18; 272) is in the form of a hollow body.
63. An abrasion machine in accordance with Claim 61, characterized in that the holding bar (18; 272) is in the form of a fluid conveying element or a fluid conveying element is arranged on the holding bar (18; 272).
64. An abrasion machine in accordance with Claim 62 or 63, characterized in that there is connected to the holding bar (18; 272) a fluid line (122), or there is guided on the holding bar (18) a fluid line (122), which is coupled to the tool head (14).
65. An abrasion machine in accordance with any of the preceding Claims, characterized in that the tool head (14) and/or a tool holding device (136; 160; 186) comprises one or more fluid chambers (152; 156; 218) which is or are connected in fluidic manner to a fluid line (122).
66. An abrasion machine in accordance with any of the preceding Claims, characterized in that the length is adjustable in continuous manner.
67. An abrasion machine in accordance with any of the preceding Claims, characterized in that an outer end of the holding device (270) is formed by the first holding element (272).
68. An abrasion machine in accordance with any of the preceding Claims, characterized in that the handle element (22; 290) comprises a holder (32) for an electrical cable (34).
69. An abrasion machine in accordance with any of the preceding Claims, characterized in that the first holding element (272) or the second holding element (20) or a fluid line (122) comprises a vacuum cleaner connector.

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