EP2707187B1 - Tile cutter - Google Patents

Description

The invention relates to a tile cutter according to the preamble of claim 1.

Such a tile cutter, in which the cutting means is acted upon by the force of a force accumulator in the vertical direction, show the US 2,435,154 . US Pat. No. 6,269,994 and WO 2008/139585 A1 , The US 4,201,104 describes a tile cutter in which a cutting medium carrier is pivotally attached to a slider.

An Indian EP 0 501 053 A1 described tile cutter has a bottom plate which extends in the position of use in a horizontal direction. Above the bottom plate extending parallel to the bottom plate running guide rails on which a carriage is slidably mounted. The carriage has a lever which is extended at its downwardly facing end by a cutting medium carrier. The cutting medium carrier is designed as an angle lever and has at its downwardly facing end a cutting means in the form of a cutting wheel. A Kraftbeaufschlagungsarm of the cutting medium carrier projects into a cavity of the actuating lever and is supported there on an adjustable cam. By turning the cam, the functional position of the cutting wheel can be adjusted. This makes it possible to cut tiles of different thicknesses.

The EP 0 537 506 B1 describes a tile cutter, in which charges when charging a cutting wheel on an edge of a tile to be cut a force storage. A similar device describes the DE 29 02 497 A1 , Here a lever arm runs on the edge of the tile to be cut.

The EP 0 521 593 describes a tile cutter with a hinged to a slider lever arm, which can be pivoted by pivoting a Brecharmes. The lever arm carries at its downwardly facing end a cutting wheel and a crushing head. A similar device describes the EP 0 387142 B1 , Again, a cutting medium carrier is pivotally mounted on the carriage, which carries a cutting wheel.

The FR 2 891 762 B1 describes a tile cutter, in which sits on a cutting medium carrier an arrangement of two successively arranged cutting wheels. The cutting wheels can overflow the marginal edge of a tile to be cut.

The FR 737 243 , the US 6,269,994 B1 and the EP 2 218 564 A1 describe force accumulator whose force is adjustable and act on the cutting medium in the vertical downward direction of the tile.

The US 6,053,159 A describes a tile cutter with a bottom plate, on the longitudinal side of a base plate extension can be fastened. The bottom plate extension has a mounting tab that can be attached to the top of the bottom plate.

The EP 1388 400 B1 describes a tile cutter having bottom plate extensions which are hinged from a use position to a non-use position.

The invention has for its object to further develop a generic tile cutter nutzsvorteilhaft.

The object is achieved by the invention defined in claim 1, wherein at least two force accumulators are provided which can be brought to change the vertical force either in an operative position. The dependent claims represent advantageous developments of the invention, which are explained below. The cutting medium carrier is articulated on the carriage in such a way that, when the carriage is displaced against the cutting direction, it slides or rolls over the tile essentially without vertical application of force. The cutting medium carrier can be designed as a lever that hangs down freely in a neutral position. The cutting means may be a carbide tooth or the like. It can be a diamond point. Preferably, however, the cutting means is formed by a cutting wheel, so that the cutting medium carrier is a cutting wheel carrier. If the carriage is pushed in the cutting direction over the tile to be cut, then the cutting means, ie preferably the cutting wheel, is acted upon by an energy store in the direction of the tile to be cut, so that a notch is introduced into the upper side of the tile. The cutting process is completed when the cutting means has overflowed the entire tile, that is displaced beyond the cutting edge edge of the tile. The carriage can be pushed back into the starting position without the cutting means again acting keratinously on the top side of the tile. The cutting means without vertical force applied over the tile. The cutting means is in a neutral position before the cut and after the cut. If the cutting means abuts the edge of the tile during the displacement in the cutting direction or after the cut in the direction of reversal in the cutting direction, it must overflow the edge of the tile. Along with this, the cutting means shifts vertically away from the bottom plate. During the displacement in the cutting direction, an energy accumulator is charged in this vertical displacement of the cutting means, which is connected to a corresponding displacement of the cutting medium carrier. This energy storage delivers the vertical force when cutting, with the cutting means in the direction the top of the tile is acted upon. The cutting medium carrier may be formed as a lever which is pivotally mounted on the carriage or on a carriage associated bearing member. If the cutting means overflows the edge of the tile, the cutting medium carrier is pivoted. While the energy storage is tensioned during pivoting of the cutting medium carrier in a displacement of the carriage in the cutting direction, no energy storage is tensioned during pivoting of the cutting medium carrier in the opposite direction, ie in the direction of a second pivoting direction. Rather, the cutting medium carrier is fastened to the slide or to the bearing member in such a way that it initially abuts against an edge of the tile from a neutral position during a displacement of the slide opposite the cutting direction and is pivoted essentially free of force when the edge overflows from the neutral position. If the cutting means is designed as a cutting wheel, then it runs substantially force-free over the top of the tile, so that the slide can be moved back into the starting position after notching without significant effort. Preferably, the cutting medium carrier is designed as a multi-arm lever which is articulated on the carriage such that the cutting means arranged at the end of an arm is at a distance from the bottom plate. In the neutral position, this distance is minimal. However, it can be adjusted by shifting a height selection actuator up and down. During emergence of the cutting means, so preferably the cutting wheel on the edge of the tile increases this distance. The cutting medium carrier may be T-shaped. On one of the two T-legs of the cutting medium carrier is articulated on the carriage or on a Höheneinstellschieber. The other T-leg forms a Kraftbeaufschlagungsarm. At the end of the T-bar sits the cutting wheel. The Kraftbeaufschlagungsarm of the cutting medium carrier forms the aforementioned counter-attack. This is supported in the cutting position of a stop which is formed by a plunger of a force accumulator. Preferably, the device has a force selection actuator, which serves as a knob can be trained. By adjusting the force selection actuator, one of a plurality of force accumulators can be selectively brought into action relative to the cutting medium carrier. The various power storage units have different force / displacement laws, in particular different spring elements, such as compression springs, rubber buffers, tension springs, leaf springs or other compressible media, so that different vertical forces can be set with them. The position of the articulation point of the cutting medium carrier and the lengths or angles of the arms of the cutting medium carrier are preferably designed and adapted to the force / displacement law of the energy storage that when brought into an initial tension energy storage pivoting the Schneidarmträgers in the cutting direction, the vertical force or not only insignificantly changes. The energy accumulator may have a prestressed compression spring. If this tensioned when running the cutting means on the edge of the tile, the spring force changes in the course of the displacement of the plunger. The leverage ratios are chosen so that this spring force increase can be compensated by a changing point of attack. This has the consequence that the cutting wheel can cleanly cut even surface profiled tiles, without changing the cutting force when overflowing surface elevations. In a preferred embodiment of the energy storage the compression springs contained therein are already biased. The initial voltage is reached when the bias of the compression spring is overcome. In a further development of the invention, it is provided that the cutting medium carrier is seated on a bearing element which can be adjusted in height, in particular formed by a slide which is displaceable in the vertical direction. This bearing member preferably forms a Höheneinstellschieber, which is guided within the housing of the carriage on two guide rods. It can be acted upon by compression springs upwards. The vertical position of the bearing member arranged in the housing is preferably adjustable by means of a height-selection actuator. The height selection actuator may include a step assembly, each having a Cam of the bearing member is applied. The height selection actuator may have a slide button, which can lock in its various functional positions. For this interlocking gears are provided. The force storage carrier can be displaceable transversely to the displacement direction of the height adjustment slide. The device preferably has a breaker head, with which the notched tile can be broken. For this purpose, the crushing head is displaced vertically downwards by pivoting of a breaking lever, so that two refractive edges of the crushing head, which are at an obtuse angle, come against the upper side of the tile, which is mounted on a breaking rib extending below the cutting line. In the downward displacement of the crushing head, a pressure is exerted on the two adjacent sides of the top of the tile, so that the tile breaks along the notch.

According to the invention, at least two energy accumulators are provided, which can be selectively brought into an operative position to change the vertical force. The two energy accumulators can have compression springs or other types of compressible media which have a spring preload of different degrees. Each compression spring may be associated with a plunger, which is guided in a guide of a force storage carrier. The compression springs can be biased. The force storage carrier can be displaced relative to the cutting medium carrier or the carriage. It is preferably a horizontal displacement. The power storage carrier engages a coupling rod which is seated on an eccentric pin of a rotary knob, which forms a force selection actuator. If the rotary knob is rotated, the force accumulator carrier can be displaced horizontally so that a first energy accumulator is displaced in the direction of the pivot axis of the cutting medium carrier and a second energy accumulator, which was initially not in working position to the cutting medium carrier, is brought into an operative position. The knob can have an overload protection. For example, a projecting from the housing actuating portion the knob, which is for example designed as a lever arm, be connected via a spring coupling with a driven shaft, to which the eccentric is fixed. If the output shaft is locked in rotation, then the knob may indeed rotate relative to the shaft. But only a leg spring, for example, is stretched. The overload protection preferably consists of a wound around the shaft leg spring whose leg arms protrude radially and rest in a neutral position on the support shoulders of the shaft or supporting flanks of the knob. Supporting flanks and supporting shoulders lie next to one another and can be brought into a displaced position relative to the shaft by a relative rotation of the rotary knob. Here, a leg is stretched by the pointing in the direction of rotation support flank. The other leg arm remains lying on the support shoulder. The tensioned spring develops a restoring force, which moves the knob back to its original position. Optionally, the plungers of the energy accumulators can be brought into an operative position relative to a force application arm of the cutting medium carrier. The force storage carrier is preferably mounted as a slide on a bearing member of the carriage. The bearing member may be formed by a Höheneinstellschieber. The cutting medium carrier and the energy storage device can be height adjustable. For this purpose, the bearing member is preferably height adjustable. It is also provided a crushing lever which cooperates with a crushing head, the latter can be adjusted in height together with the bearing member, so the Höheneinstellschieber. The height adjustment of the Höheneinstellschiebers preferably takes place via a height-selection actuator and with the aid of step edges, which are supported on cams. The stepped flanks can have rounded bulges into which a rounded flank of the cam can lie. The height-selection slide can be displaced with an actuator which is designed as a slide, but also with an actuator which is designed as a rotary knob. If the actuator is designed as a rotary knob, then it has a shaft rotatable by a rotary handle, on a gear sits whose teeth engage in a particular straight-line toothing, which is associated with a slide having the step assembly.

In order to further improve the utility of this tile cutter, it is provided that the bottom plate extension can be mounted in a non-use position below the bottom plate. This is preferably done in a parallel position to the bottom plate at two opposite edges of the bottom plate. There, the bottom plate extension can be attached. The bottom plate extension may have a U-profile. As a result of this cross-sectional profile, edge webs form. These are formed by the U-legs of the U-profile. In a use position, the edge webs down, so that the bottom plate extension can be supported on these edge webs or end bends of the edge webs. The edge webs have a height such that a support of the bottom plate extension flush, ie runs at the same height of a support of the bottom plate. The pads can be made of soft rubber. In the use position, the bottom plate extension is attached to the edge of the bottom plate. This can be done positively via a profile engagement. Preferably, the edge of the bottom plate, which may be formed by a hollow profile, a profile groove, for example. A groove having a C-shaped cross-section. In this profile groove, a profile rib of the edge web of the bottom plate extension can be inserted, so that the bottom plate extension along the edge of the bottom plate can be moved. On their inward facing sides, the edge bars also form retaining profiles. These retaining profiles can be formed by T-shaped profile webs, which can be inserted into the profile grooves of the bottom plate. Both longitudinal edges of the bottom plate form such shaped profiled grooves. According to this embodiment, each edge web of the bottom plate extension is in the non-use position at respectively an edge of the bottom plate and is there positively connected to the bottom plate. The support of the bottom plate extension has in the non-use position down, so that the tile cutter can be supported on the downward-facing support of the bottom plate extension.

In a development of the invention, a stop arrangement is provided. This consists of a stop arm which is pivotally attached to the bottom plate. The stop arm can be pivotally locked in different pivoting positions. The stop arm forms a stop bar. At this a transverse stop is attached, which is also pivotable. The transverse stop can be displaced along the extension direction of the stop arm. For this purpose, the stop arm forms a longitudinal slot.

The known from the input of the prior art tile cutter is further developed by the fact that the carriage can be guided pivotably on the guide and has a height-adjustable bearing member, in particular a Höheneinstellschieber. This can be adjusted in height by means of a height selection actuator. There are locking means provided, with which the bearing member can be locked in the different altitudes. This embodiment proves to be particularly advantageous if the cutting means is supported by a cutting medium carrier, which is acted upon by a force storage in the direction of the bottom plate. The height of the cutting wheel can then be adjusted by means of the height selection actuator to the material thickness of each tile to be cut. The energy storage is tense by the fact that preferably designed as a cutting wheel cutting means overflows the edge of the tile and is thereby lifted. The cutting wheel then runs with constant vertical force over the surface of the tile and creates a notch there. In a preferred embodiment of the invention sitting on the carriage a crushing head.

This can be lowered by pressing a breaking lever on the top of the tile to break the lying on a crushing rib tile along the notch. The breaking lever is pivotable about a bearing axis, which is assigned to the carriage stationary. The crushing head can be adjusted in height together with the cutting means or the cutting medium carrier. In an adjustment of the height selection actuator and an associated vertical displacement of the bearing member then crushing and cutting means are simultaneously shifted in height. The crushing head is preferably fastened with a push lever to a transmission lever. The transmission lever has a short lever arm, which is articulated on the bearing member, and a long lever arm, which engages a link mechanism. With this link mechanism, the transmission lever is connected to the breaking lever. The linkage may consist of a plurality of links, one of which is hinged to the housing of the carriage and another link at the end of the break lever. It may be provided a third link, which acts on the transmission lever. Alternatively, the cutting medium carrier can also be adjusted in height independently of the crushing head. Also in this alternative, the crushing head can be driven by a transmission lever. However, the articulation point of the transmission lever is fixed to the housing in this variant. The axis of rotation of the transmission lever may lie in the axis of rotation of a guide roller. The break lever points obliquely in the cutting direction during the cut. In order to bring the crushing head into an operative position, the breaking lever in a preferred embodiment of the invention must first be brought into an upright position by projecting substantially vertically upwards. This can be done by a clearance in the linkage. Only in the course of a downward movement of the breaking lever of the crushing head is applied so that it transmits the refractive power to the tile.

Fig. 1

eine perspektivische Darstellung eines ersten Ausführungsbeispieles einer Schneidevorrichtung mit in die Gebrauchsstellung gebrachter Bodenplattenerweiterung 55,

Fig. 2

eine Darstellung gemäß Fig. 1 in einer Ansicht,

Fig. 3

eine Seitenansicht der Betriebsstellung gemäß Fig. 1,

Fig. 4

eine weitere perspektivische Darstellung, bei der die Bodenplattenerweiterung 55 eine Nichtgebrauchsstellung einnimmt und sich unterhalb der Bodenplatte befindet,

Fig. 5

den Schnitt gemäß der Linie V-V in Fig. 4,

Fig. 6

eine perspektivische Darstellung des Schlittens mit seinen in den C-förmig gestalteten Führungsschienen verlagerbaren Führungsrollen,

Fig. 7

den Schlitten 3 gemäß Fig. 6 in einer anderen perspektivischen Darstellung,

Fig. 8

eine Draufsicht auf den Schlitten 3 gemäß Pfeil VIII in Fig. 7,

Fig. 9

einen Schnitt gemäß der Linie IX-IX in Fig. 8,

Fig. 10

den Schnitt gemäß der Linie X-X in Fig. 9,

Fig. 11

den Schnitt gemäß der Linie XI-XI in Fig. 8,

Fig. 12

den Schnitt gemäß der Linie XII-XII in Fig. 8,

Fig. 13

eine Darstellung gemäß Fig. 11, jedoch mit nach unten verlagertem Brechkopf 37,

Fig. 14

den Schnitt gemäß der Fig. 9, jedoch mit verlagertem Kraftspeicherträger 15,

Fig. 15

eine Darstellung gemäß Fig. 9, jedoch mit nach oben verlagertem Höheneinstellschieber 20,

Fig. 16

eine Darstellung gemäß Fig. 13, jedoch mit nach oben verlagertem Höheneinstellschieber 20,

Fig. 17

eine Darstellung gemäß Fig. 9, wobei der Schneidradträger 4 seine Neutralstellung einnimmt,

Fig. 18

eine Folgedarstellung zu Fig. 17, wobei der Schlitten 3 in Schnittrichtung S derart verlagert ist, dass das Schneidrad 5 gegen eine Fliesenkante 8' anstößt und dabei derart verschwenkt worden ist, dass der Kraftbeaufschlagungsarm 14 des Schneidradträgers 4 an einem Stößel 11 eines Kraftspeichers 9 anstößt,

Fig.19

eine Folgedarstellung zu Fig. 18, wobei der Schlitten 3 weiter in Schnittrichtung S verlagert worden ist, wobei sich eine Druckfeder 10 des Kraftspeichers 9 gespannt hat,

Fig. 20

eine Folgedarstellung zu Fig. 19 nach erfolgtem Schnitt, nachdem das Schneidrad 5 die Randkante 8" der Fliese 8 überlaufen hat und seine Neutralstellung einnimmt und

Fig. 21

eine Folgedarstellung zu Fig. 20, wobei der Schlitten 3 entgegen der Schnittrichtung S zurückverlagert worden ist und das Schneidrad 5 die Kante 8" der Fliese 8 überlaufen hat,

Fig. 22

eine perspektivische Darstellung eines zweiten Ausführungsbeispiels einer Schneidevorrichtung,

Fig. 23

den Schnitt gemäß der Linie XXIII-XXIII in Fig. 22,

Fig. 24

eine Draufsicht auf den Schlitten 3,

Fig. 25

einen Schnitt gemäß der Linie XXV-XXV in Fig. 24,

Fig. 26

den Schnitt gemäß der Linie XXVI-XXVI in Fig. 25,

Fig. 27

den Schnitt gemäß der Linie XXVII-XXVII in Fig. 26,

Fig. 28

vergrößert den Schnitt gemäß der Linie XXVIII-XXVIII in Fig. 25,

Fig. 28a

eine Darstellung der Fig. 28, wobei der Drehknopf 31 entgegen Uhrzeigersinn gegenüber dem Schaft 69 verdreht worden ist,

Fig. 28b

eine Darstellung gemäß Fig. 28a, wobei der Drehknopf 31 im Uhrzeigersinn gegenüber dem Schaft 69 verdreht worden ist,

Fig. 29

den Schnitt gemäß der Linie XXIX-XXIX in Fig. 25,

Fig. 30

den Schnitt gemäß der Linie XXX-XXX in Fig. 24,

Fig. 31

den Schnitt gemäß der Linie XXXI-XXXI in Fig. 24,

Fig. 32

eine Darstellung gemäß Fig. 31, jedoch mit in einer Aufrechtstellung verschwenktem Brechhebel 38 und

Fig. 33

eine Folgedarstellung zu Fig. 32, wobei der Brechhebel 38 geringfügig abwärts verlagert ist, bis der Brechkopf 37 seine Wirkstellung erreicht hat,

Fig. 34

teilweise aufgebrochen eine Gehäuseschale 52 mit den wesentlichen Elementen zur Höhenverstellung des Schneidradträgers

Fig. 35

ein drittes Ausführungsbeispiel in einer Darstellung gemäß Fig. 34, bei dem das Höhenauswahl-Stellglied 27 als Drehknopf 81 ausgebildet ist,

Fig. 36

den Drehknopf 81 mit Schaft 28 und Zahnrad 80 sowie den zugehörigen Übertragungsschieber 75 mit Zahnstange 79,

Fig. 37

ein viertes Ausführungsbeispiel in einer perspektivischen Darstellung,

Fig. 38

die Seitenansicht auf das vierte Ausführungsbeispiel,

Fig. 39

einen Schnitt gemäß der Linie XXXIX-XXXIX in Fig. 38 und

Fig. 40

einen Schnitt gemäß der Linie XL-XL in Fig. 39.

Embodiments of the invention are explained below with reference to accompanying drawings. Show it:

Fig. 1

a perspective view of a first embodiment of a cutting device with brought into the position of use Bodenplattenerweiterung 55,

Fig. 2

a representation according to Fig. 1 in a view

Fig. 3

a side view of the operating position according to Fig. 1 .

Fig. 4

another perspective view in which the bottom plate extension 55 occupies a non-use position and is located below the bottom plate,

Fig. 5

the section along the line VV in Fig. 4 .

Fig. 6

a perspective view of the carriage with its displaceable in the C-shaped guide rails guide rollers,

Fig. 7

the carriage 3 according to Fig. 6 in another perspective view,

Fig. 8

a plan view of the carriage 3 according to arrow VIII in Fig. 7 .

Fig. 9

a section along the line IX-IX in Fig. 8 .

Fig. 10

the section according to the line XX in Fig. 9 .

Fig. 11

the section according to the line XI-XI in Fig. 8 .

Fig. 12

the section according to the line XII-XII in Fig. 8 .

Fig. 13

a representation according to Fig. 11 but with the crushing head 37 displaced downwards,

Fig. 14

the cut according to the Fig. 9 but with displaced force storage carrier 15,

Fig. 15

a representation according to Fig. 9 but with upwardly displaced height adjustment slide 20,

Fig. 16

a representation according to Fig. 13 but with upwardly displaced height adjustment slide 20,

Fig. 17

a representation according to Fig. 9 , wherein the cutter carrier 4 assumes its neutral position,

Fig. 18

a follow-up presentation to Fig. 17 in which the carriage 3 is displaced in the cutting direction S in such a way that the cutting wheel 5 abuts against a tile edge 8 'and has been pivoted in such a way that the force application arm 14 of the cutter wheel carrier 4 abuts a tappet 11 of an energy store 9;

Figure 19

a follow-up presentation to Fig. 18 wherein the carriage 3 has been further displaced in the cutting direction S, wherein a compression spring 10 of the energy accumulator 9 has stretched,

Fig. 20

a follow-up presentation to Fig. 19 after the cut after the cutting wheel 5 has overflowed the peripheral edge 8 "of the tile 8 and assumes its neutral position and

Fig. 21

a follow-up presentation to Fig. 20 wherein the carriage 3 has been shifted back against the cutting direction S and the cutting wheel 5 has overrun the edge 8 "of the tile 8,

Fig. 22

a perspective view of a second embodiment of a cutting device,

Fig. 23

the section according to the line XXIII-XXIII in Fig. 22 .

Fig. 24

a top view of the carriage 3,

Fig. 25

a section according to the line XXV-XXV in Fig. 24 .

Fig. 26

the section according to the line XXVI-XXVI in Fig. 25 .

Fig. 27

the section according to the line XXVII-XXVII in Fig. 26 .

Fig. 28

increases the section according to the line XXVIII-XXVIII in Fig. 25 .

Fig. 28a

a representation of Fig. 28 wherein the rotary knob 31 has been rotated counterclockwise relative to the shaft 69,

Fig. 28b

a representation according to Fig. 28a wherein the rotary knob 31 has been rotated in a clockwise direction relative to the shaft 69,

Fig. 29

the section according to the line XXIX-XXIX in Fig. 25 .

Fig. 30

the section according to the line XXX-XXX in Fig. 24 .

Fig. 31

the section according to the line XXXI-XXXI in Fig. 24 .

Fig. 32

a representation according to Fig. 31 , but with crushing lever 38 and pivoted in an upright position

Fig. 33

a follow-up presentation to Fig. 32 wherein the breaking lever 38 is displaced slightly downward until the breaking head 37 has reached its operative position,

Fig. 34

partially broken a housing shell 52 with the essential elements for height adjustment of the Schneidradträgers

Fig. 35

a third embodiment in a representation according to Fig. 34 in which the height-selection actuator 27 is designed as a rotary knob 81,

Fig. 36

the rotary knob 81 with shaft 28 and gear 80 and the associated transfer slider 75 with rack 79,

Fig. 37

A fourth embodiment in a perspective view,

Fig. 38

the side view of the fourth embodiment,

Fig. 39

a section along the line XXXIX-XXXIX in Fig. 38 and

Fig. 40

a section along the line XL-XL in Fig. 39 ,

The Fig. 1 to 5 show in an overview the structure of the tile cutter. It consists of a frame which has a bottom plate 1, which is formed in the embodiment as a plastic or aluminum extruded profile. In the longitudinal center extends a crushing rib 35, which is flanked on both sides by made of soft rubber pads 54. At the respective ends of the bottom plate 1 are rail supports 34 which carry two rails 2 between them. The rails 2 are formed by C-profile rails, their openings facing each other, so that guide rollers 33 of a carriage 3 can be performed there.

At an end portion of the bottom plate 1 are located next to the crushing rib 35 each have a bearing pin 67, on which either a stop arm 61 can be plugged. The stop arm 61 has an elongate shape and has a slot 66 which extends substantially over the entire length of the stop arm 61. The bottom plate 1 has a slot 63, which passes through a clamping screw, which cooperates with a rotary knob 64, so that the stop arm 61 in different pivotal positions relative to the crushing rib 35 can be determined.

In the slot 66 of the stop arm 61, a further clamping member 65 is arranged, which is connected to a transverse stop 62. The transverse stop 62 can be displaced along the stop arm 61 and fixed in position by means of the clamping member 65.

At the two longitudinal edges 1 'of the bottom plate 1 is in each case a profile groove 56 which has a C-shaped profile.

There is a bottom plate extension 55 is provided, which has the shape of a plate, protrude from the opposite edges edge webs 58, which are angled end. On the broad side surface of the base plate extension 55 is a support 60, which is also made of soft plastic. The edge webs 58 have a height such that the support 60 is at the same height as the supports 54. As a result, a tile 8 to be cut can be supported on the support 60. From an edge web 58 a profile rib 57 projects outwards, which can be inserted into one of the profile grooves 56.

The Fig. 2 shows the bottom plate extension 55 in its operating position. The bottom plate extension 55 can be achieved by the bottom plate 1 in that the profile rib 57 is pushed out of the profile groove 56. The bottom plate extension 55 can then in the in the Fig. 4 and 5 shown storage position be brought. For this purpose, the bottom plate extension 55 is turned upside down, so that the support 60 facing down and the two edge webs 58 upwards. In this position, the projecting from the edge webs 58 inwardly T-shaped profile ribs 59 can be inserted into the profile grooves 56. In this Verwahrstellung the bottom plate extension 55 is parallel to the bottom plate 1. The bottom plate 1 thus lies between the two edge webs 58th

The Fig. 3 . 5 . 6 . 7 and 8th show the external appearance of a carriage 3, which is guided between the two rails 2. The carriage 3 is compared to the guide rails 2 only linearly displaceable. It can not be pivoted relative to the guide rails 2. From the top of the carriage 3 protrudes a handle 39 which forms the end of a breaking lever 38 which is hinged about a -related to the housing of the carriage 3- fixed bearing axis 40 pivotally mounted on the housing of the carriage 3. About one inside the Housing of the carriage 3 arranged linkage acts the handle 39 on a protruding from the lower region of the carriage 3 crushing head 37, which has two inclined at an acute angle crushing jaws on its underside. The angle vertex is above the crushing rib 35.

Below the carriage 3 is also a cutting wheel carrier 4, which carries at its lower end a cutting wheel 5, which can be rolled for the purpose of making a notch in the top of a tile 8 by means of the carriage 3 on the tile. On the top of the carriage 3 is also a slide button 32 and a knob 31. With the knob 31, the vertical force can be adjusted with which the cutting roller 5 acts on the tile 8 to be cut. With the slide button 32, the height of the cutting wheel 5 can be adjusted. The cutting roller 5 is arranged so that it is displaced vertically above the crushing rib 35 when the carriage 3 is displaced along the guide rails 2.

From the Fig. 9 . 10 . 11 and 12 are the essential transmission elements, which are located within the housing of the carriage 3, can be seen. The carriage 3 consists of two housing shells 52, 53, which are made of plastic, wherein the upper housing shell 52, the pivot bearing 40 for the breaking lever 39, a guide recess for the slide button 32 and a bearing recess for the knob 31 is formed. The lower housing shell 53 forms on its downwardly facing side a break, through which a thrust lever 41, on which the crushing head 37 is mounted, and a break for the cutting wheel 4 from. Between the two housing shells 52,53 two guide rods 22 are mounted inside the housing. The guide rods 22 extend in the vertical direction and put with their ends in bearing recesses in each case one of the two housing shells 52, 53rd

On the two guide rods 22, a Höheneinstellschieber 20 is guided in the vertical direction. The height adjustment slide, which forms a bearing member for the cutting wheel carrier 4, forms for this purpose two guide bearing bores 21, through which a guide rod 22 protrudes. By means of compression springs 36 of the Höheneinstellschieber is applied in the vertical direction upwards. There, the Höheneinstellschieber 20 has two cams 25 with a rounded cam end face. The cam end faces of the cams 25 are each supported on a step assembly 26. The step arrangement has stepped troughs or steps, on which each of the cam 25 can be supported.

The step assembly 26 is associated with a shifter 28 which can be moved in the vertical direction by means of the slide button 32. The adjusting slide 28 forms, together with the slide button 32, a height-selection actuator 27. By horizontal displacement of the height selection actuator 27, the vertical position of the Höheneinstellschiebers 20 can be adjusted. In the different heights of the Höheneinstellschiebers 20, the cams 25 are based on different stages of the step assembly 26 from. There are two equal design stage assemblies 26 are provided, each cooperating with one of the two cams 25.

From the Fig. 12 It can be seen that the top of the adjusting slide 28 has a toothing 50. This rectangular toothing 50 engages in a shape-matched counter-toothing 51 of the housing shell 52. By vertical pressure on the slide button 32, the teeth of the teeth 50, 51 can be disengaged. If the slide button 32 is moved, the compression springs 36 press the height adjustment slide 20 upwards, so that the cams 25 can always be supported in one step of the step arrangement 26.

Inside the Höheneinstellschiebers 20, a force storage carrier 15 is arranged. The force storage carrier 15 has two vertically extending, different lengths cavities, in each of which a compression spring 10, 10 'is located. The compression spring 10,10 'is supported at the top of a bottom of the cavity. The downwardly facing end of the compression spring 10,10 'acts on an end face of a plunger 11,11'. By means of a transverse pin 48, the plunger 11,11 'with vertical movement release in the compression spring 10, 10' receiving cavity tied up. The two ends of the pin 48 each engage in vertical guide slots 49. The compression springs 10,10 'have different spring stiffnesses. They are thus able to exert different forces on the plunger 11,11 '. The compression springs 10,10 'are biased in the cavities of the force storage carrier 15 a. The bias is maintained with the pins 48, which are supported at the ends of the guide slots 49.

By means of two guide pins 16 which each engage in a horizontal guide slot 17 of the Höheneinstellschiebers 20, the force accumulator support 15 is mounted horizontally displaceable on Höheneinstellschieber 20. The force storage carrier 15 forms an eye 30, in which a pin 29 of a coupling rod 18 engages. The coupling rod 18 is coupled to an eccentric pin 23. The eccentric pin 23 extending in the vertical direction thereby passes through an eye 24 of the coupling rod 18. The eccentric pin 23 protrudes from the rotary knob 31 and forms together with the knob 31 and the coupling rod 18 a force selection actuator 19. By turning the knob 31 and the associated Displacement of the eccentric pin 23, the force accumulator carrier 15 can be displaced in the horizontal direction, wherein the guide pin 16 move in their associated guide slots 17.

On a downwardly projecting extension of the Höheneinstellschiebers 20 is a pivot axis 13 about which a substantially the shape of a T-pointing Schneidradträger is pivotally hinged to the Höheneinstellschieber 20. The cutting wheel carrier 4 has a downwardly projecting Schneidradträgerarm 12, which forms the T-leg. At the end of a T-bar sits the pivot axis 13. The end of the other T-bar, which forms a Kraftbeaufschlagungsarm 14, there is a counter-stop 7, which is formed by a trough. The counter-stop 7 interacts with the rounded end faces of the plungers 11, 11 '. The plunger ends thus form stops 6, 6 '.

In the in the Fig. 9 shown operating position, the energy storage 9 'is in an inactivated state. The associated with him stop 6 'is outside the range of the counter-attack 7. The counter-stop 7 cooperates in this operating position exclusively with the stop 6, which is associated with the energy storage 9. The spring 10 of the energy accumulator 9 has a lower spring constant than the spring 10 'of the energy accumulator 9'. But it can also be reversed conditions. It is essential that the spring constants of the compression springs 10,10 'differ.

By turning the knob 31 in the in the Fig. 14 shown operating position of the stop 6 and thus the energy storage 9 is moved closer to the pivot axis 13 zoom, so that the force of the compression spring 10 can exert a reduced torque on the Kraftbeaufschlagungsarm 14. In this operating position, the stop 6 'of the energy accumulator 9' but in the area of action of the counter-stop 7, so that both power storage 9, 9 'cooperate with the Schneidradträger 4, so be curious when the Schneidradträger 4 is pivoted about its pivot axis 13 in the counterclockwise direction , A pivoting of the cutter carrier 4 in the opposite direction, however, takes place without overcoming a spring force.

The angular positions and lengths of the lever arms 12,14 and the position of the pivot axis 13 is selected with respect to the force / displacement law of the two compression springs 10, 10 ', that increasing with increasing compression spring force of the compression springs 10, 10' through a changing lever arrangement is compensated. This has the consequence that the cutting wheel 5 is always loaded independently of the pivot position of the cutter wheel 4 always with the same vertical force. Preferably, the two compression springs 10,10 'spring-biased, so that for compression of the compression spring 10,10', a limiting force must be overcome.

The Fig. 15 shows an operating position in which has been moved by moving the slide button 32 of the Höheneinstellschieber 20 to the very top. Also in this operating position, the cutting force of the cutting wheel 5 can be adjusted by turning the rotary knob 31. The eye 24 of the coupling rod 18 slides in the vertical displacement of the Höheneinstellschiebers 20 on the eccentric pin 23 upwards or downwards.

From the Fig. 11 . 13 and 16 In addition, it can be seen that, along with the vertical displacement of the cutting wheel 5 or the cutter wheel carrier 4, the crushing head 37 also moves upwards. This is a consequence of the arrangement of a steering gear within the housing of the carriage. 3

From the Fig. 10 It can be seen that the linkage is doubly formed. Between each configuration of the steering gear sits the Höheneinstellschieber 20 and carried by him force storage device 15th

To the linkage initially include the three links 44, 45 and 47. These are coupled to a transmission lever 42 which carries a push lever 41. Of the Transmission lever 42 is connected with its pivot axis 43 fixed to the Höheneinstellschieber 20. The pivot axis 43 thus shifts together with the Höheneinstellschieber 20 in the vertical direction. The transmission lever 42 has an elongate shape with a shorter lever arm, based on a pivot point 41 'of the push lever 41. The longer lever arm of the transmission lever 42 is connected to the joint 44' with the handlebar 44. At a triple articulation point 44 'of the handlebar 44 is connected to the two other links 45 and 47. The handlebar 45 is connected to a pivot axis 46 on the housing of the carriage 3. The pivot point 47 'of the handlebar 47 sits on the shorter lever arm of the breaking lever 38, which carries the handle 39 at its long end.

Is based on the in Fig. 11 illustrated position in which the crushing head 37 has a raised position, the breaking lever 38 in the in Fig. 13 shifted swivel position, so the crushing head 37 moves vertically downwards beyond the height level of the cutting wheel 5 to break the tile 8, in which a slot has been previously introduced, along the slot.

Is based on the in the Fig. 11 shown operating position of Höheneinstellschieber 20 shifted upward, so Schneidradträger 4, power storage carrier 15 and break head 37 are dragged upwards. From this position, the breaking lever 38 in the in Fig. 16 pivoted operating position shown, so the crushing head 37 lowers below the height level of the cutting wheel. 5

The operation of the cutting wheel 5 and the Schneidradträgers 4 is based on the Fig. 17 to 21 explained. The Fig. 17 shows the cutter carrier 4, as it hangs down on the pivot axis 13 without force. The focus of Schneidradträgers 4 is located in this neutral position below the Pivot axis 13. A drawn through the axis of the cutting wheel 5 and the pivot axis 13 line runs on a slope. This slope points in the direction of the cutting direction S. The Höheneinstellschieber 20 is adjusted so that the cutting wheel 5 is above the bottom plate 1, but below the peripheral edge 8 'of a tile 8 to be cut.

Is based on the in Fig. 17 In the course of further displacement of the carriage 3 in the cutting direction S, therefore, the cutter wheel carrier 4 pivots, the axis of the cutting wheel 5 being pivoted by an imaginary position Vertical line through the pivot axis 13 passes. It is achieved a kind of over-center position. In the in Fig. 18 shown Übertotpunktlage in which the drawn by the pivot axis 13 and the axis of rotation of the cutting wheel 5 line is also on a slope, the counter-stop 7 has entered against the stop 6 of the plunger 11 of the energy accumulator 9. Until then, the pivoting of the Schneidradträgers 4 was substantially free of forces.

In the course of a further displacement of the carriage 3 in the cutting direction S, the in Fig. 19 achieved operating position achieved. The cutting wheel 5 overflows the marginal edge 8 'of the tile 8, thereby changing its distance from the base plate 1. This distance increases until the cutting wheel 5 can run along on the upper side of the tile 8. Along with this pivoting of the Schneidradträgers 4 of the in Fig. 18 position shown in the in Fig. 19 shown position of the energy storage 9 is tensioned, wherein the compression spring 10 is compressed. About the plunger 11, a force is exerted on the Kraftbeaufschlagungsarm 14. This force is the cause of the vertical force with which the cutting wheel 5 acts on the surface of the tile 8. If now the carriage 3 is displaced in the cutting direction S over the tile 8, then the cutting wheel 5 cuts a notch in the upper side of the tile 8.

As soon as the cutting wheel 5 has overflowed the opposite edge edge 8 "of the tile 8, the cutting wheel carrier 4 falls back into its own position due to gravity Fig. 20 illustrated neutral position.

If the carriage 3 is displaced out of this neutral position in the opposite direction, then the cutting wheel 5 overflows the marginal edge 8 "of the tile 8, wherein the cutting wheel carrier 4 pivots in a second pivoting direction until the in Fig. 21 shown operating position is reached. In this operating position, the cutting wheel 5 rolls substantially force-free over the top of the tile 8. In this position, the carriage 3 can be displaced in the cutting direction S without the cutting wheel 5 kerberzeugend comes into effect.

By an essentially power-reduced sliding movement of the carriage 3 thus the optimal horizontal position can be selected, in which the crushing head 37 comes into effect by pivoting the breaking lever 38. The two crushing jaws act on the tile 8 on the two sides of the crushing rib 35, so that the tile 8 breaks along the notch created.

If a higher vertical force required, the knob 31 can be switched so that the stop 6 'of the plunger 11' abuts the counter-stop 7 and in a to Fig. 19 analog operating position, the compression spring 10 'is compressed.

That in the FIGS. 22 to 33 illustrated second embodiment substantially corresponds to the first embodiment. Denote the same reference numerals here technically equivalent elements, so reference is made in this regard to the preceding statements.

The guide rails 2 are also designed here in cross-section C-shaped. In the mutually facing openings of the guide rails 2 roll on each side from a total of three guide rollers 33, which are mounted about axes of rotation. At the bottom of the carriage 3 is the cutter carrier 4, which is also adjustable in height here and can optionally be acted upon by two different force accumulators 9, 9 '. The Höheneinstellschieber 20 with which the Schneidradträger 4 can be adjusted in height, is designed differently designed, as in the first embodiment. However, here too, the height can be shifted with the aid of a slide button 32, which acts on an adjusting slide 28, to which step arrangements 26 are associated, which cooperate with cams 25 of the height adjustment slide 20. Guide pins 16 protrude here in guide slots 17th Den FIGS. 26 and 27 It can be seen that the slide button 32 in different locking positions by means of two offset locking cams 50 'can lock. One or more locking cams 50 'engage optionally in associated tooth-like arranged locking recesses 51' of the housing. The locking cams 50 'are acted upon by a respective compression spring.

The force selection actuator 19 has here also a knob 31. From the knob 31 protrudes a handle lever. The eccentric pin 23, which engages in the eye 24 of the coupling rod 18 is rotatably mounted in the housing and connected via an elastic leg spring 68 with the knob 31. The torque transmission from the rotary knob 31 to the shaft 69 via the legs of the leg spring 68. If the cutting wheel in cutting position, so a displacement of the force storage carrier 15 is blocked. The shaft 69 can not be rotated in this position. If nevertheless a torque is applied to the rotary knob 31, so only the leg spring 68 is stretched, but not the shaft 69 is rotated.

In the in Fig. 28 shown unencumbered neutral position is an arm 68 'of the leg spring 68 to a support shoulder 77 of the shaft 69 at. The other arm 68 "of the leg spring 68 wound around the shaft 69 bears against a support shoulder 77 'of the shaft. Support flanks 78, 78' are flush with the support shoulders 77, 77 'and are non-rotatably connected to the rotary knob 31. The arms 68 ', 68 "of the leg spring 68 act on both the two support shoulders 77, 77' and the two support flanks 78, 78 '.

If the rotary knob 31 is acted upon by applying a torque on the lever arm counterclockwise, wherein the shaft 69 is locked in rotation, so in the Fig. 28a achieved position shown in which the knob 31 has moved under tension of the leg spring 68 relative to the shaft 69. The support flank 78 has thereby released from the arm 68 'of the torsion springs 68. The other support flank 78 'has rotated the opposite arm 68 "while removing it from the support shoulder 77. When the torque is removed, the tension of the tensioned leg spring 68 causes the rotary knob 31 to shift back into the inward position Fig. 28 illustrated neutral position.

The Fig. 28b shows the rotation of the knob 31 relative to the rotationally blocked shaft 69 in a clockwise direction. Here the supporting flank 78 'separates from the leg spring arm 68 "but the arm 68" still rests on the supporting shoulder 77'. The other arm 68 'has been stretched by the support flank 78 and has thereby released from the support shoulder 77. Again, the tensioned leg spring 68 rotates the knob 31 after canceling the torque back into the in Fig. 28 illustrated neutral position.

To avoid accidental rotation of the shaft 69 with unloaded cutting wheel carrier 4, the shaft 69 is secured in its two rotational end positions of a locking pin 70. This is spring-loaded and engages in one of two mutually 90 ° offset latching openings 71 a.

Of the Fig. 30 It can be seen that the end rounded cam 25 engage in arcuate troughs of the step assembly 26.

The crushing head 37 is also located here at the end of a push lever 41 which is displaceable in the vertical direction. At the Schubhebelanlenkstelle 41 'engages a pin which is fixedly connected to the transmission lever 42, in a longitudinal slot 74 of the push lever 41. The transmission lever 42 is rotatably articulated in the region of an axis of a guide roller 33 about a housing-fixed pivot axis 43. The free end of the transmission lever 42 has a pin 42 acting as a bearing pin, which engages in a guide slot 37, which extends in the form of a floor. On the pin 42 ', a link 44 is articulated, which is articulated at a pivot point 44' on a handlebar 45, which is also pivotable about a housing-fixed pivot axis 46. This pivot axis is at the height of a guide roller axis.

At the articulation point 44 ', on which the handlebar 44 is articulated on the handlebar 45, a handlebar 47 engages, which is coupled to the breaking lever 38 and which acts as a pull tab. The articulation point 47 ', on which the link 47 is articulated on the breaking lever 38, is located between the bearing axis 40 of the breaking lever 38 and handle 39. The articulation point 47' is formed by a pin which is guided in a guide slot 72 bow.

In this embodiment, the cutting wheel 5 is vertically displaceable independently of the crushing head 37. The vertical displacement of the crushing head 37 takes place in this embodiment exclusively by pivoting the breaking lever 38 about its pivot axis 40. The pivot axis 40 is in the embodiment within the housing, which consists of a plurality of housing shells 52, 53.

The operation of the breaking lever 38 show the FIGS. 31 to 33 , The Fig. 31 shows the situation immediately after the cut. The breaking lever 38 has an angle in the cutting direction. The crushing head 37 is removed from the surface of the scribed tile 8. In order to bring the crushing head 37 into effect, the breaking lever 38 must be brought from its obliquely forward position in an upright position, which in the Fig. 32 is shown. In the course of this pivotal displacement, the crushing head 37 lowers until it touches the surface of the tile 8. Subsequently, the pin, which forms the Schubhebelanlenkstelle 41 'moves within the vertical slot 74 of the push lever 41st

Only when the breaking lever 38 has overcome its upright position and the further movement of the handle has its downward component of the Schubhebelanlenkstelle 41 'forming pin reaches the end of the longitudinal slot 74 and acts on the thrust lever 41 in the vertical direction, so that the crushing head 37 is a refractive power can exert on the tile 8. This takes place during a downward movement of the handle 39.

The Fig. 34 shows the essential elements for height adjustment of the Schneidradträgers 4 and for displacing the force accumulator support 15. The Höheneinstellschieber 20 forms a frame. Of the two mutually parallel longer frame legs, the cam 25 upwards. Within the frame of the force storage carrier 15 is arranged, over the Coupling rod 18 cooperates with the eccentrically abragenden on the shaft 69 eccentric pin 23. The force storage carrier 15 can be displaced within the frame opening. He is doing with the engaging in the guide slots 17 guide pin 16 höhengefesselt to the Höheneinstellschieber 20, but can move in the vertical direction in the context of the length of the guide slots 17. A transfer slider 75 is coupled in motion with the adjustment slide 28 and forms the rib-like arranged steps 26 from.

From each of the two housing shells 52, 53 protrude guide ribs 76 which protrude into guide channels of the Höheneinstellschiebers 20 to guide the Höheneinstellschieber 20 in the vertical direction. From the two ends facing away from each other of Höheneinstellschiebers 20 protrude from extensions, which are supported on the compression springs 36.

The Fig. 35 . 36 show a further embodiment in which the height selection actuator 27 is designed as a knob 81. The rotary knob 81 is rotatably coupled to a transmission shaft 82 to a gear 80. The shaft 82 is rotatably mounted in the housing.

The gear 80 engages in a toothing 79 of a slider 75, which forms the step assembly 26. This step assembly 26 cooperates with the cam 25, as shown in the Fig. 34 is shown. The toothing 79 forms the wall of an elongated recess into which the gear 80 is immersed. The teeth of the gear 80 can be supported during Drehverstellen on the toothing 79 opposite smooth wall of the recess.

By turning the knob 27, the transfer slider 75 can be moved. A latch 83 engages in one of several circumferentially offset order the transmission shaft 82 arranged latching recesses 84 in order to drehrehemmen the rotational position of the knob 81.

That in the FIGS. 37 to 40 illustrated fourth embodiment relates to a tile cutter with two rail supports 34 held rails 2 and bottom plate 1, wherein at the two a circular cross-section having rails 2, a carriage 3 is guided. The rails 2 formed by tubes or solid rods pass through guide cavities of a guide element 85, which can be manufactured as a plastic molded part. There are two substantially mirror-symmetrically designed guide elements 85 are provided which each form mutually facing bearing shafts 68, stuck in fixed (non-rotatable) with the guide elements 85 housing shells 52, 53 stuck.

The housing shells 52, 53 include a gear arrangement, as shown in the previously described figures of the second embodiment, which is why reference is made to the relevant embodiments.

As in the embodiments described above, the break lever assembly has a fork shape. From a handle 39 project fork-like two parallel crushing lever 38 from. Between the two break levers, the gear arrangement extends, with which the refractive power can be preset or the height of the Schneidradträgers 4 is adjustable. Between the two arms is thus nested a Höheneinstellschieber 20 and an energy storage carrier 15, wherein the force storage carrier 15 in the horizontal direction and the Höheneinstellschieber 20 is displaced in the vertical direction. Above the Höheneinstellschiebers 20 is also disposed between the two arms 38 slide 75, the can be displaced in the horizontal direction by operation of the slide button 32 to adjust the height of the Höheneinstellschiebers 20.

The crushing head 37 is articulated directly here by means of a push lever 41 to the breaking lever 38. The articulation point 41 ', on which the thrust lever 41 is articulated on the breaking lever 38, is formed by a laterally projecting extension of the breaking lever 38.

The two guide elements 85 form bearing axles 86, which are stuck in cup-shaped recesses of the housing shells 52, 53. The housing shells 52, 53 and the transmission housing consisting of these is located between the two firmly interconnected crushing levers 38, which form at their ends bearing eyes 87, with which the breaking lever 38 are rotatably mounted about the bearing axles 86.

An extension plate 55 has a profile element 57, which cooperates with a profile element 56 of the base plate such that the profile elements 56, 57 hook-like mesh, so that the bottom plate extension 55 temporarily on the bottom plate edge 1 'can be fastened. At the bottom of the bottom plate extension 55 are hooks 88, with which the bottom plate extension 55 on the underside of the bottom plate 1 can be fastened (see Fig. 22 ). The hooks 88 each engage in recesses of the edge 1 'of the bottom plate 1. The in the Fig. 39 upwardly facing support surface of the bottom plate extension 55 then points downwards.

Claims (14)

1. Tile cutter comprising a base plate (1) which extends in the horizontal direction when the tile cutter is in the use position and is intended for receiving the tile (8), and a slide (3) that can be moved in the horizontal direction along a guide (2), a cutting means carrier (4), to which an energy accumulator (9, 9') applies force, being articulated to the slide and carrying cutting means (5) at its end, to which cutting means an energy accumulator (9, 9') applies force in the vertical direction in order to produce a notch on the tile (8) at least when the slide (3) is moved, characterised in that at least two energy accumulators (9, 9') are provided which can optionally be moved into a use position in order to vary the vertical force.
2. Tile cutter according to claim 1, characterised in that the energy accumulators (9, 9') are assigned an energy accumulator carrier (15) which can be moved relative to the cutting means carrier (4).
3. Tile cutter according to either claim 1 or claim 2, characterised in that each energy accumulator (9, 9') forms a ram (11, 11') that acts on a force-application arm (14) of the cutting means carrier (4).
4. Tile cutter according to either claim 2 or claim 3, characterised in that the energy accumulator carrier (15) is mounted on a bearing element (20) of the slide (3) as a slider and can be moved by means of a force-selection control element (19), such that one of the rams (11, 11') optionally acts on the end of the force-application arm (14).
5. Tile cutter according to claim 4, characterised in that the force-selection control element (19) comprises a rotary knob (31), in particular having a lever that is securely coupled to an output shaft (69) to prevent overloading, on which output shaft an eccentric pin (23) sits which is coupled to the energy accumulator carrier (15) in terms of movement.
6. Tile cutter according to claim 5, characterised in that the overload protection device is in the form of a leg spring (68), the leg arms of which abut support collars (77, 77') of the shaft (69) or support sides (78, 78') of the rotary knob (31).
7. Tile cutter according to any of the preceding claims 1 to 6, characterised in that the cutting means carrier (4) and the energy accumulators (9, 9') sit on a bearing element (20), which is assigned to the slide (3) so as to be adjustable in height.
8. Tile cutter according to claim 7, characterised in that, together with the bearing element (20), the height of a breaker head (37), which can be moved vertically downwards by operating a breaker lever (38), can be adjusted.
9. Tile cutter according to either claim 7 or claim 8, characterised in that the bearing element (20) is or comprises a height-adjustment slider, the height of which can be adjusted by means of a height-selection control element (27) having stepped sides (26).
10. Tile cutter according to any of the preceding claims, characterised in that the cutting means carrier (4) is articulated to the slide (3) in such a way that it slides or rolls over the tile, counter to the cutting direction (S) and substantially without vertical application of force, when the slide (3) is moved.
11. Tile cutter according to claim 10, characterised in that the cutting means carrier (4) is a lever which has a plurality of arms and is articulated to the slide (3) in such a way that the cutting means (5) arranged at the end of a cutting means carrier arm (12) is spaced apart from the base plate (1) by a distance that is as small as possible when in the neutral position and increases when the cutting means (5) approaches the edge (8', 8") of the tile (8).
12. Tile cutter according to either claim 10 or claim 11, characterised in that a force-application arm (14) of the cutting means carrier (4) forms the counter stop (7) that is acted upon by a ram (11, 11') of the energy accumulator (9, 9') during the cutting process.
13. Tile cutter according to any of the preceding claims, characterised by a base plate extension (55) which can be attached to the base plate (1) in a use position in order to increase the contact surface (54) for the tile (8), it being possible to attach the base plate extension (55) to the underside of the base plate (1) in a non-use position.
14. Tile cutter according to any of the preceding claims, characterised in that the bearing element (20) carries a breaker head (37) which can be moved towards the base plate (1) by pivoting a breaker lever (38), the breaker head (37) being coupled to the bearing element (20) in such a way that the breaker head (37), together with the cutting means (5), is moved in height when the height of the bearing element (20) is adjusted, and in particular can be pivoted about a bearing axis (40) that is assigned to the slide (3) such that it cannot move, and acts on a transmission lever (42), which is articulated to the bearing element (20), by means of a link gear (44, 45, 47), by means of which transmission lever the breaker head (27) is coupled to the bearing element (20).

Images