tile cutter

Abstract

Tile cutter with a base plate (1) extending horizontally in a use position of the tile cutter for receiving a tile (8) and with a carriage (3) which is displaceable horizontally above the base plate (1) along a guide rail (2), on which carriage a bearing member (20) carrying a cutting means (5), in particular a cutting wheel, is mounted in a height-adjustable manner, wherein the carriage (3) is guided non-pivotally on the guide rail (2) and the bearing member (20) can be fixed at different heights relative to the base plate (1) by means of a height selection actuator (27), characterized in that the bearing member (20) is formed by a vertically displaceable height adjustment slide which is supported by means of cams (25) on a step arrangement (26) of the height selection actuator (27).

Description

[0001] The invention relates to a tile cutter with a base plate extending horizontally in the use position of the tile cutter for receiving a tile and with a carriage which is displaceable horizontally above the base plate along a guide rail and on which a bearing member carrying a cutting means, in particular a cutting wheel, is mounted in a height-adjustable manner, wherein the carriage is guided non-pivotably on the guide rail and the bearing member can be fixed at different heights relative to the base plate by means of a height selection actuator.

[0002] EP 0 501 053 A1 discloses a tile cutter having a base plate that extends horizontally in the use position. Guide rails extend above the base plate, running parallel to the base plate, on which a carriage is movably mounted. The carriage has a lever that is extended at its downward-facing end by a cutting means carrier. The cutting means carrier is designed as an angle lever and has a cutting means in the form of a cutting wheel at its downward-facing end. A force-applying arm of the cutting means carrier projects into a cavity in the actuating lever and is supported there by an adjustable cam. The functional position of the cutting wheel can be adjusted by turning the cam. This allows tiles of different thicknesses to be cut.

[0003] DE 296 00 050 U1 discloses a tile cutter with a cutting means carrier hinged to a carriage, which slides or rolls over the tile when the carriage is moved opposite to the cutting direction essentially without vertical force being applied.

[0004] EP 0 537 506 B1 describes a tile cutter in which a force accumulator is charged when a cutting wheel hits the edge of a tile to be cut. DE 29 02 497 A1 describes a similar device. Here, a lever arm runs along the edge of the tile to be cut.

[0005] EP 0 521 593 A1 describes a tile cutter with a lever arm hinged to a slide, which can be pivoted by pivoting a breaker arm. The lever arm carries a cutting wheel and a breaker head at its downward-facing end. EP 0 387 142 B1 describes a similar device. Here, too, a cutting means carrier, which carries a cutting wheel, is pivotably hinged to the slide.

[0006] FR 2 891 762 B1 describes a tile cutter in which an arrangement of two cutting wheels arranged one behind the other is mounted on a cutting element carrier. The cutting wheels run over the edge of a tile to be cut.

[0007] FR 737 243 A, US 6,269,994 B1 and EP 2 218 564 A1 describe force accumulators whose force is adjustable and which act on the cutting means in a vertical downward direction onto the tile.

[0008] US Pat. No. 6,053,159 A describes a tile cutter with a base plate to whose long side a base plate extension can be attached. The base plate extension has a mounting bracket that can be attached to the top of the base plate.

[0009] EP 1 388 400 B1 describes a tile cutter having base plate extensions that can be folded up from a use position to a non-use position.

[0010] The invention is based on the object of further developing the tile cutter mentioned at the beginning in a manner that is advantageous for use.

[0011] This object is achieved by the invention specified in the claims. Firstly, it is based on the fact that the cutting means carrier is seated on a height-adjustable bearing member, in particular formed by a slide that can be displaced in the vertical direction. This bearing member preferably forms a height-adjusting slide that is guided within the housing of the carriage on two guide rods. It can be biased upwards by compression springs. 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 can have a stepped arrangement, each of which bears against a cam of the bearing member. The height selection actuator can have a sliding knob that can lock into its various functional positions. Intermeshing teeth are provided for this purpose. The energy storage carrier can be displaceable transversely to the direction of displacement of the height adjustment slide.The device preferably has a breaking head with which the notched tile can be broken. To do this, the breaking head is displaced vertically downward by pivoting a breaking lever, so that two breaking flanks of the breaking head, positioned at an obtuse angle to one another, strike the upper side of the tile, which is mounted on a breaking rib running below the cutting line. As the breaking head is moved downward, pressure is exerted on the two sides of the upper side of the tile adjacent to the notch, causing the tile to break along the notch.

[0012] The cutting tool carrier is hinged to the carriage in such a way that when the carriage is moved against the cutting direction it slides or rolls over the tile essentially without any vertical force being applied. The cutting tool carrier can be designed as a lever that hangs freely downwards in a neutral position. The cutting tool can be a hard metal tooth or the like. It can be a diamond tip. Preferably, however, the cutting tool is formed by a cutting wheel, so that the cutting tool carrier is a cutting wheel carrier. When the carriage is pushed over the tile to be cut in the cutting direction, the cutting tool, preferably the cutting wheel, is acted upon by a force accumulator in the direction of the tile to be cut, so that a notch is made in the top side of the tile.The cutting process is complete when the cutting tool has passed over the entire tile, i.e., has been displaced beyond the edge of the tile at the cutting end. Due to the design according to the invention, the carriage can be pushed back to its starting position without the cutting tool again creating notches on the top of the tile. According to the invention, the cutting tool is displaced over the tile without vertical force being applied. The cutting tool is in a neutral position before and after the cut. If the cutting tool hits the edge of the tile when displaced in the cutting direction or after the cut when displaced in the counter-cutting direction, it must pass over the edge of the tile. At the same time, the cutting tool is displaced vertically away from the floor slab.During the displacement in the cutting direction, this vertical displacement of the cutting tool, which is linked to a corresponding displacement of the cutting tool carrier, charges an energy accumulator. This energy accumulator supplies the vertical force during the cut, which is applied to the cutting tool in the direction of the top of the tile. The cutting tool carrier can be designed as a lever that is pivotally attached to the carriage or to a bearing member assigned to the carriage. If the cutting tool runs over the edge of the tile, the cutting tool carrier is pivoted. While the energy accumulator is tensioned when the cutting tool carrier is pivoted when the carriage is moved in the cutting direction, no energy accumulator is tensioned when the cutting tool carrier is pivoted in the opposite direction, i.e. in a second pivoting direction. Instead, the cutting tool carrier is attached to the slide orattached to the bearing member in such a way that when the carriage is moved from a neutral position against the cutting direction it first strikes an edge of the tile and is pivoted essentially force-free when it runs over the edge from the neutral position. If the cutting means is designed as a cutting wheel, it then runs essentially force-free over the upper side of the tile so that after the notch has been made the carriage can be moved back to its starting position without any significant expenditure of force. Preferably the cutting means carrier is designed as a multi-armed lever which is articulated on the carriage in such a way that the cutting means arranged at the end of one arm is at a distance from the base plate. In the neutral position this distance is minimal. However it can be adjusted up and down by moving a height selection actuator.When the cutting tool, preferably the cutting wheel, comes into contact with the edge of the tile, this distance increases. The cutting tool carrier can be T-shaped. On one of the two T-legs, the cutting tool carrier is hinged to the carriage or to a height adjustment slide. The other T-leg forms a force application arm. The cutting wheel is located at the end of the T-bar. The force application arm of the cutting tool carrier forms the counter-stop mentioned above. In the cutting position, this is supported on a stop formed by a plunger of a force storage device. The device preferably has a force selection actuator, which can be designed as a rotary knob. By adjusting the force selection actuator, one of several force storage devices can be selectively activated relative to the cutting tool carrier.The various energy storage devices 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 tool carrier and the lengths and angles of the cutting tool carrier arms are designed and adapted to the force / displacement law of the energy storage device such that, when the energy storage device is initially tensioned, pivoting the cutting arm carrier in the cutting direction does not change the vertical force or only changes it insignificantly. The energy storage device can have a pre-tensioned compression spring. If this is tensioned when the cutting tool hits the edge of the tile, the spring force changes as the ram is moved.The lever ratios are selected so that this increase in spring force is compensated by a changing point of application. This means that the cutting wheel can cleanly cut even tiles with profiled surfaces without the cutting force changing when passing over raised surfaces. In a preferred design of the energy storage devices, the compression springs contained therein are already preloaded. The initial tension is achieved when the preload of the compression spring is overcome.

[0013] Based on the above-cited US 6,269,994 B1, which describes a tile cutter with a base plate extending horizontally in the use position of the tile cutter for receiving the tile and a slider which is displaceable horizontally along a guide and to which a cutting means carrier is articulated which is acted upon by a force accumulator and which carries a cutting means at its end which is acted upon by a force accumulator in the vertical direction at least when the carriage is displaced to create a notch in the tile, the object of the invention is to increase the utility value of the tile cutter.

[0014] To achieve this task, at least two energy accumulators are provided, which can be selectively brought into an active position to change the vertical force. The two energy accumulators can have compression springs or other compressible media with different spring preloads. Each compression spring can be assigned a plunger that is guided in a guide of an energy accumulator carrier. The compression springs can be preloaded. The energy accumulator carrier can be displaced relative to the cutting medium carrier or the carriage. This displacement is preferably horizontal. A coupling rod engages the energy accumulator carrier and is seated on an eccentric pin of a rotary knob, which forms a force selection actuator.If the rotary knob is turned, the energy storage carrier can be moved horizontally so that a first energy storage device is moved in the direction of the pivot axis of the cutting means carrier and a second energy storage device, which was initially not in the operative position relative to the cutting means carrier, is brought into an operative position. The rotary knob can have an overload protection device. For example, an actuating section of the rotary knob which protrudes from the housing and is designed, for example, as a lever arm, can be connected via a spring coupling to an output shaft to which the eccentric is attached. If the output shaft is rotationally blocked, the rotary knob can rotate relative to the shaft. However, this only tensions a leg spring, for example. The overload protection device preferably consists of a leg spring wound around the shaft, the leg arms of which protrude radially and, in a neutral position, are resting on support shoulders of the shaft orThe support flanks of the rotary knob are in contact. The support flanks and support shoulders lie next to one another and can be offset by rotating the rotary knob relative to the shaft. One arm is tensioned by the support flank pointing in the direction of rotation. The other arm remains on the support shoulder. The tensioned spring develops a restoring force that moves the rotary knob back to its original position. The plungers of the energy storage devices can be optionally moved into an operative position relative to a force application arm of the cutting tool carrier. The energy storage device carrier is mounted as a slide on a bearing element of the carriage. The bearing element can be formed by a height adjustment slide. The cutting tool carrier and the energy storage device can be height-adjustable. For this purpose, the bearing element is height-adjustable.Furthermore, a breaking lever is provided which interacts with a breaking head; the latter can be height-adjustable together with the bearing member, i.e. the height adjustment slide. The height adjustment of the height adjustment slide is preferably carried out via a height selection actuator and with the aid of a stepped arrangement on which cams are supported. The stepped arrangement can be stepped flanks which have rounded bulges into which a rounded flank of the cam can lie. The height selection slide can be moved with an actuator designed as a slide, but also with an actuator designed as a rotary knob. If the actuator is designed as a rotary knob, it has a shaft which can be rotated by a rotary handle and on which a gear is seated, the teeth of which engage with a toothed arrangement, in particular a straight toothed arrangement, which is assigned to a slide which has the stepped arrangement.

[0015] The invention further relates to a tile cutter with a base plate extending horizontally in the use position of the tile cutter for receiving the tile and with a slider displaceable horizontally along a guide, a cutting means arranged thereon and a base plate extension which can be fastened to the base plate in a use position to widen the support surface for the tile.

[0016] Such a tile cutter is described in US 6,053,159 A. In order to improve the usability of this tile cutter, it is provided that the floor plate extension can be fastened underneath the floor plate when not in use. This is preferably done in a parallel position to the floor plate on two opposite edges of the floor plate. The floor plate extension can be fastened there. The floor plate extension can have a U-profile. This cross-sectional profile creates edge webs. These are formed by the U-legs of the U-profile. When in use, the edge webs point downwards so that the floor plate extension can be supported on these edge webs or the end-side bends of the edge webs. The edge webs are of a height such that a support for the floor plate extension is flush, i.e. at the same height as a support for the floor plate.The supports can be made of soft rubber. In the use position, the base plate extension is attached to the edge of the base plate. This can be achieved via a form-fitting profile engagement. The edge of the base plate, which can be formed from a hollow profile, has a profile groove, e.g. a groove with a C-shaped cross-section. A profile rib of the edge web of the base plate extension can be inserted into this profile groove, so that the base plate extension can be moved along the edge of the base plate. On their inward-facing sides, the edge webs also form retaining profiles. These retaining profiles can be formed from T-shaped profile webs that can be inserted into the profile grooves of the base plate. Both longitudinal edges of the base plate form profile grooves of this type.Thanks to this design, each edge bar of the floor slab extension rests against a respective edge of the floor slab when not in use, where it is positively connected to the floor slab. The support of the floor slab extension faces downward when not in use, allowing the tile cutter to rest on the downward-facing support of the floor slab extension.

[0017] In a further development of the invention, a stop assembly is provided. This consists of a stop arm that is pivotally attached to the base plate. The stop arm can be locked in various pivoting positions. The stop arm forms a stop bar. A cross stop, which is also pivotable, is attached to this. The cross stop can be moved along the extension direction of the stop arm. For this purpose, the stop arm forms a longitudinal slot.

[0018] To achieve this objective, the tile cutter known from the prior art cited at the outset is further developed in that the carriage can be guided non-pivotably on the guide and has a height-adjustable bearing member, in particular a height adjustment slide. This can be adjusted in height using a height selection actuator. Locking means are provided with which the bearing member can be locked into various height positions. This configuration proves particularly advantageous when the cutting means is carried by a cutting means carrier, which is acted upon by an energy storage device in the direction of the base plate. The height of the cutting wheel can then be adjusted to the material thickness of the tile to be cut using the height selection actuator. The energy storage device is tensioned by the cutting means, preferably designed as a cutting wheel, running over the edge of the tile and being lifted in the process.The cutting wheel then runs over the surface of the tile with constant vertical force, creating a notch there. In a preferred embodiment of the invention, a breaking head is mounted on the carriage. This can be lowered onto the top of the tile by actuating a breaking lever in order to break the tile resting on a breaking rib along the notch. The breaking lever is pivotable about a bearing axis that is fixedly assigned to the carriage. The breaking head can be height-adjustable together with the cutting means or the cutting means carrier. When the height selection actuator is adjusted and the bearing member is displaced vertically, the breaking head and cutting means are then displaced simultaneously. The breaking head is preferably attached to a transmission lever with a push lever. The transmission lever has a short lever arm that is hinged to the bearing member and a long lever arm to which a linkage gear engages.The transmission lever is connected to the crushing lever via this linkage mechanism. The transmission mechanism can consist of a plurality of links, one of which is linked to the carriage housing and another to the end of the crushing lever. A third link can be provided which engages the transmission lever. Alternatively, the cutting medium carrier can also be height-adjusted independently of the crushing head. With this alternative, the crushing head can also be driven via a transmission lever. In this variant, however, the articulation point of the transmission lever is fixed to the housing. The rotation axis of the transmission lever can be located on the rotation axis of a guide roller. The crushing lever points diagonally upwards in the cutting direction during cutting.To bring the breaking head into an operative position, in a preferred embodiment of the invention, the breaking lever must first be raised to an upright position by projecting substantially vertically upwards. This can be achieved by a clearance in the linkage. Only during a downward movement does the breaking lever act upon the breaking head in such a way that it transfers the breaking force to the tile.

[0019] Embodiments of the invention are explained below with reference to the accompanying drawings. They show: Fig. 1 a perspective view of a first embodiment of a cutting device with the base plate extension 55 brought into the use position, Fig. 2 a representation according to Fig. 1 in one view, Fig. 3 a side view of the operating position according to Fig. 1, Fig. 4 a further perspective view in which the base plate extension 55 assumes a non-use position and is located below the base plate, Fig. 5 the section along the line VV in Fig. 4, Fig. 6 a perspective view of the carriage with its guide rollers that can be moved in the C-shaped guide rails, Fig. 7 the carriage 3 according to Fig. 6 in a different 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 along the line XX in Fig. 9, Fig. 11 the section along the line XI-XI in Fig. 8, Fig. 12 the section along the line XII-XII in Fig. 8, Fig. 13 a representation according to Fig. 11, but with crushing head 37 shifted downwards, Fig. 14 the cut according to the Fig. 9, but with relocated force storage carrier 15, Fig. 15 a representation according to Fig. 9, but with the height adjustment slider 20 moved upwards, Fig. 16 a representation according to Fig. 13, but with the height adjustment slider 20 moved upwards, Fig. 17 a representation according to Fig. 9, whereby the cutting wheel carrier 4 assumes its neutral position, Fig. 18 a follow-up to Fig. 17, wherein the carriage 3 is displaced in the cutting direction S such that the cutting wheel 5 abuts against a first tile edge 8' and has been pivoted such that the force application arm 14 of the cutting wheel carrier 4 abuts against a first tappet 11 of a first force accumulator 9, Fig. 19 a follow-up to Fig. 18, wherein the carriage 3 has been displaced further in the cutting direction S, wherein a first compression spring 10 of the first energy accumulator 9 has been tensioned, Fig. 20 a follow-up to Fig. 19 after the cut has been made, after the cutting wheel 5 has passed over a second tile edge 8" of the tile 8 and assumes its neutral position and Fig. 21 a follow-up to Fig. 20, wherein the carriage 3 has been moved back against the cutting direction S and the cutting wheel 5 has passed over the second tile edge 8" of the tile 8, Fig. 22 a perspective view of a second embodiment of a cutting device, Fig. 23 the section along the line XXIII-XXIII in Fig. 22, Fig. 24 a top view of the carriage 3, Fig. 25 a section along the line XXV-XXV in Fig. 24, Fig. 26 the section along the line XXVI-XXVI in Fig. 25, Fig. 27 the section along the line XXVII-XXVII in Fig. 26, Fig. 28 enlarged section along line XXVIII-XXVIII in Fig. 25, Fig. 28a a representation of the Fig. 28, whereby the rotary knob 31 has been turned counterclockwise relative to the shaft 69, Fig. 28b a representation according to Fig. 28a, whereby the rotary knob 31 has been turned clockwise relative to the shaft 69, Fig. 29 the section along the line XXIX-XXIX in Fig. 25, Fig. 30 the section along the line XXX-XXX in Fig. 24, Fig. 31 the section along the line XXXI-XXXI in Fig. 24, Fig. 32 a representation according to Fig. 31, but with the breaking lever 38 pivoted in an upright position and Fig. 33 a follow-up to Fig. 32, wherein the breaking lever 38 is displaced slightly downwards until the breaking head 37 has reached its operative position, Fig. 34 partially broken away an upper housing shell 52 with the essential elements for height adjustment of the cutting wheel carrier, 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 as well as the associated transmission slide 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 cut along the line XL-XL in Fig. 39.

[0020] The Fig. Figures 1 to 5 provide an overview of the structure of the tile cutter. It consists of a frame with a base plate 1, which in the exemplary embodiment is designed as a plastic or extruded aluminum profile. A breaking rib 35 extends along its longitudinal center, flanked on both sides by support surfaces 54 made of soft rubber. At each end of the base plate 1 are rail supports 34, which carry two guide rails 2 between them. The guide rails 2 are formed by C-profile rails whose openings face toward one another, so that guide rollers 33 of a carriage 3 are guided there.

[0021] At each end section of the base plate 1, next to the crushing rib 35, there is a bearing pin 67 onto which a stop arm 61 can be optionally attached. The stop arm 61 has an elongated shape and a slot 66 that extends essentially over the entire length of the stop arm 61. The base plate 1 has a slot 63 through which a clamping screw extends, which interacts with a rotary knob 64, so that the stop arm 61 can be locked in various pivoting positions relative to the crushing rib 35.

[0022] A further clamping member 65 is arranged in the slot 66 of the stop arm 61 and is connected to a transverse stop 62. The transverse stop 62 is displaceable along the stop arm 61 and is fixed in position by means of the clamping member 65.

[0023] On each of the two base plate edges 1' of the base plate 1 there is a profile groove 56 which has a C-shaped profile.

[0024] A base plate extension 55 is provided, which has the shape of a plate from which edge webs 58 protrude at opposite edges and are angled at the ends. 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 are of a height such that the support 60 is at the same height as the support surfaces 54. As a result, a tile 8 to be cut rests on the support 60. A first profile rib 57 protrudes outward from an edge web 58 and is inserted into one of the profile grooves 56.

[0025] The Fig. Figure 2 shows the base plate extension 55 in its operating position. The base plate extension 55 can be detached from the base plate 1 by pushing the first profile rib 57 out of the profile groove 56. The base plate extension 55 is then inserted into the Fig. 4 and Fig. 5. To do this, the base plate extension 55 is turned upside down so that the support 60 faces downward and the two edge webs 58 face upward. In this position, the T-shaped second profile ribs 59 projecting inward from the edge webs 58 are inserted into the profile grooves 56. In this storage position, the base plate extension 55 lies parallel below the base plate 1. The base plate 1 thus lies between the two edge webs 58.

[0026] The Fig. 3, Fig. 5, Fig. 6, Fig. 7 and Fig. 8 show the external appearance of a carriage 3, which is guided between the two guide rails 2. The carriage 3 can only be moved linearly relative to the guide rails 2. It cannot pivot relative to the guide rails 2. A handle 39 protrudes from the top of the carriage 3, forming the end of a breaking lever 38, which is pivotably connected to the housing of the carriage 3 about a bearing axis 40 that is fixed relative to the housing of the carriage 3. Via a linkage arranged inside the housing of the carriage 3, the handle 39 acts on a breaking head 37 protruding from the lower region of the carriage 3, which has two breaking jaws inclined at an acute angle on its underside. The apex of the angle lies above the breaking rib 35.

[0027] Below the carriage 3 is also a cutting wheel carrier 4, which carries a cutting wheel 5 at its lower end, which can be rolled over the tile with the aid of the carriage 3 in order to create a notch in the top surface of a tile 8. Also located on the top side of the carriage 3 are a sliding knob 32 and a rotary knob 31. The rotary knob 31 adjusts the vertical force with which the cutting wheel 5 acts on the tile 8 to be cut. The sliding knob 32 adjusts the height of the cutting wheel 5.

[0028] The cutting wheel 5 is arranged such that when the carriage 3 is moved along the guide rails 2, it is displaced vertically above the crushing rib 35.

[0029] From the Fig. 9, Fig. 10, Fig. 11 and Fig. Figure 12 shows the essential gear elements located within the housing of the carriage 3. The carriage 3 consists of two housing shells 52, 53 made of plastic, with the upper housing shell 52 forming the pivot bearing 40 for the breaking lever 38, a guide recess for the sliding knob 32, and a bearing recess for the rotary knob 31. The lower housing shell 53 forms a cutout on its downward-facing side through which a pushing lever 41, on which the breaking head 37 is mounted, and a cutout for the cutting wheel carrier 4 extend. Two guide rods 22 are mounted inside the housing between the two housing shells 52, 53. The guide rods 22 extend vertically and their ends are inserted into bearing recesses in one of the two housing shells 52, 53.

[0030] A height adjustment slide 20 is guided vertically on the two guide rods 22. The height adjustment slide 20, which forms a bearing member for the cutting wheel carrier 4, forms two guide bearing bores 21, through each of which a guide rod 22 extends. The height adjustment slide 20 is urged upwards in the vertical direction by means of compression springs 36. There, the height adjustment slide 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 arrangement 26. The step arrangement 26 has stepped recesses or steps, on which the cam 25 is supported.

[0031] The step arrangement 26 is associated with an adjustment slide 28, which can be displaced horizontally using the slide knob 32. The adjustment slide 28, together with the slide knob 32, forms a height selection actuator 27. The vertical position of the height adjustment slide 20 is adjusted by horizontally displacing the height selection actuator 27. At the various height positions of the height adjustment slide 20, the cams 25 are supported on different steps of the step arrangement 26. Two identically designed step arrangements 26 are provided, each of which interacts with one of the two cams 25.

[0032] From the Fig. 12 shows that the upper side of the adjustment slide 28 has a toothing 50. This rectangular toothing 50 engages with a conforming mating toothing 51 of the upper housing shell 52. By vertically pressing the slide button 32, the teeth of the toothing 50 and the mating toothing 51 are disengaged. When the slide button 32 is moved, the compression springs 36 press the height adjustment slide 20 upward, so that the cams 25 are always supported in one step of the step arrangement 26.

[0033] A force storage carrier 15 is arranged inside the height adjustment slide 20. The force storage carrier 15 has two vertically extending cavities of different lengths, each containing a compression spring 10, 10'. The compression spring 10, 10' rests upwards on a base of the cavity. The downward-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' is restrained with vertical freedom of movement in the cavity accommodating the compression spring 10, 10'. The two ends of the pin 48 each engage in vertical pin guide slots 49. The compression springs 10, 10' have different spring stiffnesses. They are thus capable of exerting forces of varying magnitude on the plungers 11, 11'. The compression springs 10, 10' are preloaded and inserted into the cavities of the force storage carrier 15.The preload is maintained by the pins 48, which are supported on the ends of the pin guide slots 49.

[0034] The force storage carrier 15 is horizontally displaceably attached to the height adjustment slide 20 by means of two guide pins 16, each of which engages a horizontal slide guide slot 17 of the height adjustment slide 20. The force storage carrier 15 forms a force storage eye 30, into 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 engages through a coupling rod eye 24 of the coupling rod 18. The eccentric pin 23 projects from the rotary knob 31 and, together with the rotary knob 31 and the coupling rod 18, forms a force selection actuator 19. By turning the rotary knob 31 and the associated displacement of the eccentric pin 23, the force storage carrier 15 is displaced in the horizontal direction, whereby the guide pins 16 move in the slide guide slots 17 assigned to them.

[0035] On a downwardly projecting extension of the height adjustment slide 20 is a first pivot axis 13, about which a cutting wheel carrier, essentially in the shape of a T, is pivotally connected to the height adjustment slide 20. The cutting wheel carrier 4 has a downwardly projecting cutting wheel carrier arm 12, which forms the T-leg. The first pivot axis 13 is located at the end of one T-web. The end of the other T-web, which forms a force application arm 14, is a counter-stop 7 formed by a recess. The counter-stop 7 interacts with the rounded end faces of the rams 11, 11'. The ram ends thus form stops 6, 6'.

[0036] In the in the Fig. In the operating position shown in Figure 9, the second energy accumulator 9' is in an inactivated state. The second stop 6' assigned to it lies outside the range of the counter-stop 7. In this operating position, the counter-stop 7 interacts exclusively with the first stop 6, which is assigned to the first energy accumulator 9. The first compression spring 10 of the first energy accumulator 9 has a lower spring constant than the second compression spring 10' of the second energy accumulator 9'. However, the opposite situation can also exist. It is important that the spring constants of the compression springs 10, 10' differ.

[0037] By turning the rotary knob 31 in the Fig. In the operating position shown in Figure 14, the first stop 6 and thus the first energy accumulator 9 are moved closer to the first pivot axis 13, so that the force of the first compression spring 10 exerts a reduced torque on the force application arm 14. In this operating position, however, the second stop 6' of the second energy accumulator 9' is located in the effective range of the counter-stop 7, so that both energy accumulators 9, 9' interact with the cutting wheel carrier 4, i.e., are tensioned, when the cutting wheel carrier 4 is pivoted counterclockwise about its first pivot axis 13. Pivoting the cutting wheel carrier 4 in the opposite direction, however, occurs without overcoming a spring force.

[0038] The angular positions and lengths of the cutting wheel support arm 12 and the force application arm 14, as well as the position of the first pivot axis 13, are selected with respect to the force / displacement law of the two compression springs 10, 10' such that the increasing spring force of the compression springs 10, 10' with increasing compression is compensated by a changing arrangement of the cutting wheel support arm 12 and the force application arm 14. This results in the cutting wheel 5 always being loaded with the same vertical force, essentially regardless of the pivot position of the cutting wheel support 4. Preferably, the two compression springs 10, 10' are spring-loaded, so that a limit force must be overcome to compress the compression spring 10, 10'.

[0039] The Fig. Figure 15 shows an operating position in which the height adjustment slide 20 has been moved all the way up by moving the slide knob 32. Even in this operating position, the cutting force of the cutting wheel 5 can be adjusted by turning the rotary knob 31. The coupling rod eye 24 of the coupling rod 18 slides up or down on the eccentric pin 23 as the height adjustment slide 20 is moved up or down.

[0040] From the Fig. 11, Fig. 13 and Fig. 16 also shows that, along with the vertical displacement of the cutting wheel 5 or the cutting wheel carrier 4, the crushing head 37 also shifts upwards. This is a consequence of the arrangement of a linkage mechanism within the housing of the carriage 3.

[0041] From the Fig. 10 shows that the linkage mechanism is designed in two parts. The height adjustment slide 20 and the force storage carrier 15 supported by it are located between each part of the linkage mechanism.

[0042] The linkage mechanism initially includes the three links 44, 45, and 47. These are coupled to a transmission lever 42, which carries a thrust lever 41. The transmission lever 42 is firmly connected to the height adjustment slide 20 by its second pivot axis 43. The second pivot axis 43 thus moves vertically together with the height adjustment slide 20. The transmission lever 42 has an elongated shape with a shorter lever arm relative to a thrust lever articulation point 41' of the thrust lever 41. The longer lever arm of the transmission lever 42 is connected to a first link 44 at the articulation point 42'. The first link 44 is connected to the two other links 45 and 47 at a triple first link articulation point 44'. A second link 45 is connected to a third pivot axis 46 on the housing of the slide 3.A second linkage point 47' of a third linkage 47 is located on the shorter lever arm of the breaking lever 38, which carries the handle 39 at its long end.

[0043] Based on the Fig. 11, in which the breaking head 37 has a raised position, the breaking lever 38 in the position shown in Fig. 13, the breaking head 37 moves vertically downwards beyond the height level of the cutting wheel 5 in order to break the tile 8, in which a slot has previously been made, along the slot.

[0044] Based on the Fig. 11, the cutting wheel carrier 4, the energy storage carrier 15 and the crushing head 37 are also pulled upwards. If from this position the crushing lever 38 is moved into the position shown in Fig. 16, the crushing head 37 lowers below the height level of the cutting wheel 5.

[0045] The functioning of the cutting wheel 5 or the cutting wheel carrier 4 is explained by the Fig. 17 to 21. The Fig. Figure 17 shows the cutting wheel carrier 4 hanging downward without force from the first pivot axis 13. In this neutral position, the center of gravity of the cutting wheel carrier 4 is located below the first pivot axis 13. A line drawn through the axis of the cutting wheel 5 and the first pivot axis 13 runs on a slope. This slope points in the direction of cutting direction S. The height adjustment slide 20 is adjusted so that the cutting wheel 5 is above the floor slab 1, but below the first tile edge 8' of a tile 8 to be cut.

[0046] Based on the Fig. 17, the cutting wheel 5 runs against the first tile edge 8' of the tile 8. As the cutting wheel 3 is further displaced in the cutting direction S, the cutting wheel carrier 4 pivots, with the axis of the cutting wheel 5 passing through an imaginary vertical line through the first pivot axis 13. A type of over-center position is reached. In the position shown in Fig. In the over-center position shown in Figure 18, in which the line drawn through the first pivot axis 13 and the rotational axis of the cutting wheel 5 also lies on an incline, the counter-stop 7 has moved against the first stop 6 of a first plunger 11 of the first energy accumulator 9. Up to this point, the pivoting of the cutting wheel carrier 4 was essentially force-free.

[0047] In the course of a further displacement of the carriage 3 in the cutting direction S, the Fig. 19 is reached. The cutting wheel 5 runs over the first tile edge 8' of the tile 8 and thereby changes its distance from the base plate 1. This distance increases until the cutting wheel 5 can run along the upper side of the tile 8. Along with this pivoting of the cutting wheel carrier 4 from the position shown in Fig. 18 shown position into the Fig. In the position shown in Figure 19, the first force accumulator 9 is tensioned, compressing the first compression spring 10. A force is exerted on the force application arm 14 via the first plunger 11. This force is the cause of the vertical force with which the cutting wheel 5 acts on the surface of the tile 8. If the carriage 3 is now moved in the cutting direction S over the tile 8, the cutting wheel 5 cuts a notch into the top of the tile 8.

[0048] As soon as the cutting wheel 5 has passed the opposite second tile edge 8" of the tile 8, the cutting wheel carrier 4 falls back into its Fig. Neutral position shown in Figure 20.

[0049] If the carriage 3 is moved in the opposite direction from this neutral position, the cutting wheel 5 runs over the second tile edge 8" of the tile 8, whereby the cutting wheel carrier 4 pivots in a second pivoting direction until the Fig. 21 is reached. In this operating position, the cutting wheel 5 rolls essentially force-free over the upper side of the tile 8. In this position, the carriage 3 can also be displaced in the cutting direction S without the cutting wheel 5 having a notch-generating effect.

[0050] By means of a substantially force-reduced displacement movement of the carriage 3, the optimal horizontal position is selected, in which the breaking head 37 takes effect by pivoting the breaking lever 38. The two breaking jaws act on the tile 8 on both sides of the breaking rib 35, so that the tile 8 breaks along the created notch.

[0051] If a higher vertical force is required, the rotary knob 31 is adjusted so that the second stop 6' of a second tappet 11' rests against the counter stop 7 and is in a Fig. 19 analog operating position the second compression spring 10' is compressed.

[0052] The Fig. The second embodiment shown in Figures 22 to 33 essentially corresponds to the first embodiment. The same reference numerals denote technically equivalent elements, which is why reference is made to the preceding explanations in this regard.

[0053] The guide rails 2 are also C-shaped in cross-section. A total of three guide rollers 33, mounted around pivot axes, roll in the facing openings of the guide rails 2 on each side. Located on the underside of the carriage 3 is the cutting wheel carrier 4, which is also height-adjustable here or optionally acted upon by two different energy stores 9, 9'. The height adjustment slide 20, with which the cutting wheel carrier 4 is adjusted in height, is designed differently than in the first embodiment. However, here too, the height can be adjusted using a sliding knob 32, which acts on an adjustment slide 28, to which step arrangements 26 are assigned, which interact with cams 25 of the height adjustment slide 20. Guide pins 16 also protrude into slide guide slots 17. Fig. 26 and Fig. 27 shows that the sliding knob 32 locks into various locking positions by means of two offset locking cams 50'. One or more locking cams 50' selectively engage in associated tooth-like locking recesses 51' of the housing. The locking cams 50' are each acted upon by a compression spring.

[0054] The force selection actuator 19 also has a rotary knob 31. A handle lever protrudes from the rotary knob 31. The eccentric pin 23, which engages the coupling rod eye 24 of the coupling rod 18, is rotatably mounted in the housing and connected to the rotary knob 31 via an elastic leg spring 68.

[0055] The torque is transmitted from the rotary knob 31 to the shaft 69 via the legs of the leg spring 68. When the cutting wheel is in the cutting position, movement of the energy storage carrier 15 is blocked. The shaft 69 cannot be rotated in this position. If a torque is nevertheless applied to the rotary knob 31, only the leg spring 68 is tensioned, but the shaft 69 is not rotated.

[0056] In the Fig. In the unloaded neutral position shown in Figure 28, a first arm 68' of the leg spring 68 rests against a first support shoulder 77 of the shaft 69. A second arm 68" of the leg spring 68 wound around the shaft 69 rests against a second support shoulder 77' of the shaft. Support flanks 78, 78' run flush with the support shoulders 77, 77' and are connected in a rotationally fixed manner 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'.

[0057] If the rotary knob 31 is actuated by applying a torque to the lever arm in an anti-clockwise direction, whereby the shaft 69 is rotationally blocked, the Fig. 28a, in which the rotary knob 31 has moved relative to the shaft 69 under tension of the leg spring 68. A first support flank 78 has thereby detached itself from the first arm 68' of the leg springs 68. A second support flank 78' has rotated the opposite second arm 68" and thereby removed it from the second support shoulder 77'. When the torque is removed, the tension of the tensioned leg spring 68 ensures that the rotary knob 31 is moved back into the Fig. Neutral position shown in Figure 28.

[0058] The Fig. Figure 28b shows the clockwise rotation of the rotary knob 31 relative to the rotationally blocked shaft 69. Here, the second support flank 78' detaches from the second arm 68" of the leg spring. However, the second arm 68" still rests on the second support shoulder 77'. The first arm 68' was tensioned by the first support flank 78 and has thereby detached from the first support shoulder 77. Here, too, the tensioned leg spring 68 rotates the rotary knob 31 back to the position shown in Fig. Neutral position shown in Figure 28.

[0059] To prevent unwanted rotation of the shaft 69 when the cutting wheel carrier 4 is unloaded, the shaft 69 is secured in both of its rotational end positions by a locking pin 70. This is spring-loaded and engages in one of two locking openings 71 offset by 90° to each other.

[0060] The Fig. 30 shows that the cams 25, which are rounded at the ends, engage in curved recesses of the step arrangement 26.

[0061] Here, too, the crushing head 37 is located at the end of a thrust lever 41, which is vertically movable. At the thrust lever articulation point 41', a pin, which is firmly connected to the transmission lever 42, engages in a longitudinal slot 74 of the thrust lever 41. The transmission lever 42 is pivotally mounted in the region of an axis of a guide roller 33 about a second pivot axis 43 fixed to the housing. The free end of the transmission lever 42 has a pin 42' acting as a bearing journal, which engages in a guide slot 73 that extends in the shape of the base. The first link 44 is pivotally mounted to the pin 42'. The second link 45 is pivotally mounted at a first link articulation point 44', which is also pivotable about a third pivot axis 46 fixed to the housing. This third pivot axis 46 is also at the level of a guide roller axis.

[0062] The third link 47, which is coupled to the break lever 38 and acts as a pull tab, engages at the first link pivot point 44', where the first link 44 is pivoted to the second link 45. The second link pivot point 47', where the third link 47 is pivoted to the break lever 38, lies between the bearing axis 40 of the break lever 38 and the handle 39. The second link pivot point 47' is formed by a pin that is curvedly guided in a link guide slot 72.

[0063] In this embodiment, the cutting wheel 5 is vertically displaceable independently of the crushing head 37. In this embodiment, the vertical displacement of the crushing head 37 occurs exclusively by pivoting the crushing lever 38 about its bearing axis 40. In this embodiment, the bearing axis 40 is located within the housing, which consists of several housing shells 52, 53.

[0064] The functioning of the breaking lever 38 is shown in the Fig. 31 to 33. The Fig. Figure 31 shows the situation immediately after the cut. The breaker lever 38 points diagonally in the cutting direction. The breaker head 37 is away from the surface of the scored tile 8. In order to activate the breaker head 37, the breaker lever 38 must be moved from its diagonally forward position into an upright position, which is shown in the Fig. 32. During this pivoting movement, the breaking head 37 lowers until it touches the surface of the tile 8. Subsequently, the pin forming the push lever pivot point 41' moves within the vertically extending longitudinal slot 74 of the push lever 41.

[0065] Only when the breaking lever 38 has overcome its upright position and the movement of the handle has its downward component upon further pivoting does the pin forming the push lever pivot point 41' reach the end of the longitudinal slot 74 and actuates the push lever 41 in a vertical direction, so that the breaking head 37 exerts a breaking force on the tile 8. This occurs during a downward movement of the handle 39.

[0066] The Fig. Figure 34 shows the essential elements for adjusting the height of the cutting wheel carrier 4 and for moving the energy storage carrier 15. The height adjustment slide 20 forms a frame. The cams 25 point upwards from the two longer frame legs, which run parallel to one another. The energy storage carrier 15 is arranged within the frame and interacts via the coupling rod 18 with the eccentric pin 23 projecting eccentrically from the shaft 69. The energy storage carrier 15 is displaced within the frame opening. It is vertically fixed to the height adjustment slide 20 by the guide pins 16 engaging in the slide guide slots 17, but can move vertically within the length of the slide guide slots 17. A transmission slide 75 is coupled in motion to the adjustment slide 28 and forms the rib-like step arrangement 26.

[0067] Guide ribs 76 protrude from each of the two housing shells 52, 53, which protrude into guide channels of the height adjustment slide 20 to guide the height adjustment slide 20 in the vertical direction. Extensions protrude from the two mutually facing ends of the height adjustment slide 20 and are supported by the compression springs 36.

[0068] The Fig. 35, Fig. 36 show a further embodiment in which the height selection actuator 27 is designed as a rotary knob 81. The rotary knob 81 is non-rotatably coupled to a gear 80 by a transmission shaft 82. The shaft 82 is rotatably mounted in the housing.

[0069] The gear 80 engages with a toothing 79 of a transmission slide 75, which forms the step arrangement 26. This step arrangement 26 cooperates with the cam 25, as shown in the Fig. 34. The toothing 79 forms the wall of an elongated recess into which the gear 80 is inserted. During rotational adjustment, the teeth of the gear 80 are supported on the smooth wall of the recess opposite the toothing 79.

[0070] By turning the rotary knob 81, the transmission slide 75 is displaced. A locking pawl 83 engages in one of several locking recesses 84 arranged circumferentially offset around the transmission shaft 82 in order to prevent rotation of the rotary knob 81.

[0071] The Fig. The fourth embodiment shown in Figures 37 to 40 relates to a tile cutter with guide rails 2 and a base plate 1 held by two rail supports 34, wherein a carriage 3 is guided on the two guide rails 2 having a circular cross-section. The guide rails 2, formed from tubes or solid rods, extend through guide cavities of a guide element 85, which is manufactured as a plastic molded part. Two essentially mirror-symmetrical guide elements 85 are provided, each forming mutually facing bearing axes 86, which are inserted into housing shells 52, 53 that are fixedly (non-rotatably) connected to the guide elements 85.

[0072] The housing shells 52, 53 contain a gear arrangement as shown in the previously described figures of the second embodiment, for which reason reference is made to the relevant explanations.

[0073] As with the embodiments described above, the breaking lever arrangement has a fork shape. Two parallel breaking levers 38 protrude from a handle 39 like forks. The gear arrangement, with which the breaking force can be preset or the height of the cutting wheel carrier 4 can be adjusted, extends between the two breaking levers. Nested between the two breaking levers 38 are a height adjustment slide 20 and a force storage carrier 15, with the force storage carrier 15 being displaceable horizontally and the height adjustment slide 20 vertically. Above the height adjustment slide 20 is the transmission slide 75, also arranged between the two breaking levers 38, which is displaced horizontally by actuating the slide button 32 in order to adjust the height of the height adjustment slide 20.

[0074] The crushing head 37 is here directly connected to the crushing lever 38 by means of a thrust lever 41. The thrust lever linkage point 41', at which the thrust lever 41 is connected to the crushing lever 38, is formed by a laterally projecting extension of the crushing lever 38.

[0075] The two guide elements 85 form bearing axes 86, which are inserted into cup-shaped recesses of the housing shells 52, 53. The housing shells 52, 53, or the gear housing consisting of them, are located between the two firmly connected breaker levers 38, which form bearing eyes 87 at their ends, with which the breaker levers 38 are rotatably mounted about the bearing axes 86.

[0076] A base plate extension 55 has a first profile rib 57, which interacts with a profile groove 56 of the base plate in such a way that the first profile rib 57 and the profile groove 56 engage in a hook-like manner, so that the base plate extension 55 can be temporarily fastened to the base plate edge 1'. Hooks 88 are located on the underside of the base plate extension 55, with which the base plate extension 55 can be fastened to the underside of the base plate 1 (see Fig. 22). The hooks 88 engage in locking recesses in the base plate edge 1' of the base plate 1. The Fig. 39 upward-facing support surface of the base plate extension 55 then points downwards. List of reference symbols: 1 base plate 1' floor slab edge 2 guide rails 3 sleds 4 cutting wheel carriers 5 Cutting media, cutting wheel 6 first attack 6' second stop 7 Counter stop 8 tiles 8' first tile edge 8" second tile edge 9 first energy storage 9' second energy storage 10 first compression spring 10' second compression spring 11 first plunger 11' second plunger 12 Cutting wheel carrier arm 13 first swivel axis 14 Force application arm 15 energy storage carriers 16 guide pins 17 Slider guide slot 18 Coupling rod 19 Force selection actuator 20 Height adjustment slide, bearing link 21 leadership camps 22 Guide rod 23 Eccentric pin 24 coupling rod eye 25 cams 26 step arrangement 27 Height selection actuator 28 adjustment slides 29 cones 30 energy storage eye 31 Rotary knob 32 sliding knob 33 Leadership role 34 rail supports 35 Crushing rib 36 compression spring 37 crushing head 38 breaking levers 39 Handle 40 Bearing axle, pivot bearing 41 Thrust lever 41' thrust lever pivot point 42 transmission lever 42' transmission lever articulation point 43 second swivel axis 44 first driver 44' first handlebar connection point 45 second handlebar 46 third swivel axis 47 third driver 47' second handlebar attachment point 48 Guide pin, cross pin 49 Tenon guide slot 50 gearing 50' locking cams 51 Counter-toothing 51' rest trough 52 upper housing shell 53 lower housing shell 54 contact surface 55 Floor slab extension 56 profile groove 57 first profile rib 58 edge bridge 59 second profile rib 60th edition 61 Stop arm 62 Cross stop 63 slot 64 clamping link, rotary knob 65 clamping link 66 slot 67 bearing journals 68 torsion spring 68' first arm 68" second arm 69 shaft 70 locking pins 71 locking opening 72 Handlebar guide slot 73 Guide slot 74 Longitudinal slot 75 transmission slide 76 Guide rib 77 first supporting shoulder 77' second support shoulder 78 first supporting flank 78' second supporting flank 79 Rack, toothing 80 gear 81 Rotary knob 82 transmission shaft 83 locking latch 84 locking recess 85 guide element 86 bearing axle 87 bearing eye 88 hooks S Cutting direction

Claims

[1] Tile cutter with a base plate (1) extending horizontally in a use position of the tile cutter for receiving a tile (8) and a carriage (3) which is displaceable horizontally above the base plate (1) along a guide rail (2), on which carriage a bearing member (20) carrying a cutting means (5), in particular a cutting wheel, is mounted in a height-adjustable manner, wherein the carriage (3) is guided non-pivotably on the guide rail (2) and the bearing member (20) can be fixed at different heights relative to the base plate (1) by means of a height selection actuator (27), characterized by that the bearing member (20) is formed by a vertically displaceable height adjustment slide which is supported by means of cams (25) on a step arrangement (26) of the height selection actuator (27). [2] Tile cutter according to claim 1, characterized bythat the step arrangement (26) has troughs or steps arranged in a step-like manner, on each of which the cam (25) can be supported, wherein an end face of the cam (25) is rounded. [3] Tile cutter according to one of the preceding claims, characterized by that the height selection actuator (27) is formed by an adjustment slide (28) and a sliding knob (32), wherein the adjustment slide (28) is displaceable in the horizontal direction by means of the sliding knob (32). [4] Tile cutter according to claim 3, characterized by that the step arrangement (26) is assigned to the adjusting slide (28). [5] Tile cutter according to one of claims 3 or 4, characterized bythat the upper side of the adjusting slide (28) has a toothing (50) which engages in a form-adapted counter-toothing (51) of an upper housing shell (52) of the slide (3), wherein the teeth of the toothing (50, 51) can be disengaged by vertical pressure on the sliding button (32). [6] Tile cutter according to one or more of the preceding claims, characterized by that the height adjustment slide (20) carries a breaking head (37) which can be displaced by pivoting a breaking lever (38) in the direction of the base plate (1). [7] Tile cutter according to claim 6, characterized by that the breaking head (37) is coupled to the height adjustment slide (20) in such a way that the breaking head (37) is displaced in height together with the cutting wheel (5) when the height adjustment slide (20) is adjusted. [8] Tile cutter with a base plate (1) extending horizontally in a use position of the tile cutter for receiving a tile (8) and a carriage (3) displaceable horizontally above the base plate (1) along a guide rail (2), on which a bearing member (20) carrying a cutting means, in particular a cutting wheel (5), is mounted in a height-adjustable manner, wherein the carriage (3) is guided non-pivotably on the guide rail (2) and the bearing member (20) can be fixed at different heights relative to the base plate (1) by means of a height selection actuator (27), characterized by that the height selection actuator (27) forms a rotary knob (81) which engages with a gear wheel (80) on a rack (79) of a transmission slide (75) having a step arrangement (26). [9] Tile cutter according to claim 8, characterized bythat the rotary knob (81) is coupled to the gear (80) in a rotationally fixed manner by means of a transmission shaft (82), the transmission shaft (82) being rotatably mounted in a housing shell (52, 53) formed by the carriage (3). [10] Tile cutter according to claim 9, characterized by that a plurality of locking recesses (84) are arranged circumferentially offset around the transmission shaft (82), into which a locking pawl (83) engages in order to prevent the rotational position of the rotary knob (81) from rotating.

Images