SEPARATION DEVICE

Description

[0001] The invention relates to a separating device according to the type specified in the preamble of claim 1.

[0002] Cutting devices are known in various designs, for example as circular saws or cut-off grinders, and are used to cut wood, metal, plastic, building materials or natural stone or individual workpieces. These cutting devices have a drive motor which generates the rotational movement of a disc-shaped cutting tool, such as a circular saw blade, a cutting disc or the like. The area of ​​the cutting tool which is not engaged with the workpiece to be machined during operation can be at least partially covered or surrounded by a protective hood. In this case, a fan driven by the drive motor and a device for removing dust from the interior of the protective hood are provided, which includes an inlet opening introduced into the protective hood and connected to the pressure side of the fan, and a dust outlet opening.

[0003] Cutting devices of the type mentioned above also feature a fan that can be used to remove dust, dirt, chips, or similar materials generated during the cutting process from the immediate working area of ​​the cutting device. The fan can also simultaneously serve to cool the drive motor.

[0004] In conventional cutting devices, the workpiece is enclosed in a protective hood whose inlet opening is positioned as close as possible to the chip generation area and is oriented so that chips enter it. Within the protective hood, the chip flow is redirected if necessary or slowed down by baffle plates and directed toward the outlet opening. The chip flow is assisted by a fan or suction system and conveyed outside the protective hood.

[0005] The goal is to ensure that as many chips as possible reach the air jet and the outlet opening as a result of their tangential propulsion. The already high tangential speed of the cutting tool's cutting edge, due to the physics of cutting, is useful for this.

[0006] On the other hand, however, tears occur at the edges of the cutting edge of the cutting tool, resulting in an unclean cut on the surface of the workpiece to be cut. Using a circular saw as a cutting device, this problem can be explained as follows: In a circular saw, a saw blade cuts a panel, for example, by rotating at a speed n and moving at a relative speed Δv to it. A saw tooth of the saw blade, which engages in the material of the plate, passes through the plate at the tangential speed vt. This creates a cutting pressure p S, which on the one hand generates the shear stress τ s required for cutting due to its large gradient, but sometimes cannot be held by the material of the plate at the surface of the cutting edge exit: In a first approximation, the tensile stress permissible at the surface σ Z, Zul < ps is exceeded, resulting in the surface tearing out in the area of ​​the cutting edge exit, or chips or parts of chips remaining partially attached to the edge in the area of ​​the cutting edge exit. This tearing creates depressions on the top side of the plate in the area of ​​the cutting surface and in the cutting surface itself. This results in an unclean cut on the edges on both sides of the cutting edge exit.

[0007] To avoid such unclean cutting patterns, it is known to provide pressure media in the form of rollers on the side of the cutting tool on the cutting edge exit side of the workpiece in the area of ​​the cutting edge exit, which generate a compressive stress in the area of ​​the cutting edge exit. In this case, compressive stress is applied via the rollers σ d in the form of Hertzian compression p H = σ d applied to the workpiece in the area of ​​the cutting edge exit.

[0008] The rollers are coupled to the protective hood in such a way that they can be moved tangentially. This creates a mechanical arc. The protective hood captures the chips with maximum kinetic energy and efficiently directs them into the extraction system, allowing it to operate with reduced energy consumption. A disadvantage of this system, however, is that the roller suspension proved to be so elastic that the rollers deflected sideways and were worn away by the sawblade to such an extent that the gap between the roller and the sawblade became too large to prevent tear-out.

[0009] A generic cutting device with a housing is known from WO 93 / 13920 A1. A driven, disc-shaped cutting tool for cutting a workpiece is mounted in the housing. Cutting means, each with an associated cutting edge, are arranged on a circumferential side of the cutting tool. During cutting, depending on a feed rate of the cutting tool relative to the workpiece, these cutting means penetrate into the material to be cut on a cutting edge entry side of the workpiece, exit on a cutting edge exit side of the workpiece located remote therefrom, and thereby remove material from the workpiece. Furthermore, at least one pressure medium is provided, which exerts a pressure p H on the cutting edge exit side, laterally of the cutting tool in the region of the cutting edge, via the cutting edge exit surface onto the surface of the cutting edge exit side, and is pivotably mounted relative to the housing.The pressure medium is mounted at one end of at least one rocker arm. The rocker arm is connected to the housing via a first joint with a first joint axis. The rocker arm is pivotally mounted about the first joint axis. The first joint axis is arranged parallel to the rotation axis of the cutting tool. The rocker arm simply results in less elastic deformation of the pressure medium's suspension. Furthermore, the arcuate movement of the pressure medium is maintained, which is necessary to compensate for different workpiece thicknesses and thus different cutting depths of the cutting tool.

[0010] DE 23 39 373 A1 discloses a profile cutter with a counterholder. This profile cutter is used to cut grooves into a workpiece. At the end of the workpiece, the profile cutter breaks through the exit side of the workpiece. A parallelogram acts on the workpiece with the counterholder. The counterholder acts against the milling direction, i.e., the movement of the milling disk's rotational axis relative to the workpiece. Although the exit angle of the profile cutter's individual cutting edges is blunt, they extend acutely to the grain direction shown, thus eliminating the problem of chipping. Chipping when milling across the grain direction cannot be prevented with this profile cutter.

[0011] Pressure rollers are described in DE 20 2013 101 927 U1. They are used to guide workpieces under high forces, but not to provide counterpressure to the cutting pressure. The purpose of this is to prevent tearing at the cutting edges of wooden panels or corresponding deformation of plastic panels caused by the use of a scoring saw directly at the cutting edge exit.

[0012] Furthermore, pressure rollers at the cutting edge inlet and outlet are listed in EP 0 036 964 B1 in order to achieve the shortest possible force flow and thus minimal deformation of the workpiece.

[0013] A roller in the area of ​​the saw blade is also described in DE 10 2006 026 043 B4, but for saw blade production and not for saw blade use.

[0014] A kinematic guidance of elements depending on the work situation is described in DE 3 933 261 C2, however it is a belt-driven riving knife and not a tear-out prevention device during a sawing process.

[0015] Suction close to the effective point is mentioned in DE 10 2012 007 344 A1, but no kinematically inevitable connection between the main chip flight direction and the orientation of the channel is disclosed.

[0016] For dust and chip removal, DE 3 525 092 A1 proposes fixed air jets—i.e., positioned independently of the workpiece thickness. Since the kinetic energy of the chips depends quadratically on the tangential velocity vt, the additional energy expenditure must be economically weighed according to the application.

[0017] The invention is therefore based on the object of developing a cutting device according to the type specified in the preamble of claim 1 in such a way that a clean cutting pattern is ensured on the cutting edge exit side while avoiding the disadvantages mentioned.

[0018] This problem is solved by the characterizing features of claim 1 in conjunction with its preamble features.

[0019] The subclaims form advantageous developments of the invention.

[0020] The invention is based on the finding that the disadvantages mentioned can be easily avoided by a sufficiently rigid kinematic connection of the protective hood to the saw unit while maintaining the same guidance of the pressure medium at the cutting edge exit.

[0021] According to the invention, the rocker is constructed in several parts and forms a rocker parallelogram. The rocker parallelogram comprises a first and second partial rocker and a coupling. The first partial rocker is connected to the housing via a first housing joint and the second partial rocker is connected to the housing via a second housing joint. On the side of the first and second partial rockers remote from the associated housing joint, the coupling is articulated to the first and second partial rockers via a first and second partial rocker joint and is connected at its one free end to the pressure medium. The pressure medium is in the form of at least one roller, wherein the roller has a predetermined radius and the joint axis is offset from the axis of rotation of the cutting tool by at least the radius of the rollers in the direction of the cutting edge exit side.The rocker arm and the circular path of the pressure medium's support area, enabled by the rocker arm, are additionally formed by a four-bar linkage design with partial rockers and couplings, or by a cam-controlled gear, or by a two-axis linear drive. The parallelogram is a convex quadrilateral with opposite parallel sides, such as special trapezoids and two-dimensional parallelepipeds. Therefore, various configurations can form the parallelogram. This allows the rocker arm joints to be positioned further upwards, preventing them from colliding with the bearing and drive of the cutting tool. This allows for greater design flexibility, simplifies the design, and maintains maximum kinetic energy for chip removal.By forming the pressure medium with at least one roller, frictional forces during the feed movement are reduced and the separating movement with the separating device is facilitated. To ensure a parallelogram, the first and second partial swing arms are of the same length.

[0022] In order to enable, in particular, a uniform movement of the pressure medium with the separating tool, the joint axes of the first and second housing joints and of the first and second partial swing joints are aligned parallel to the axis of rotation of the separating tool.

[0023] According to a further development of the invention, the joint axis of the first housing joint, the second housing joint, and the rotation axis of the cutting tool are arranged on a first straight line running perpendicular to these axes. In particular, the first straight line runs perpendicular to the support plane of the cutting device.

[0024] To complete the parallelogram, the joint axes of the first partial swing arm joint, the second partial swing arm joint and the rotation axis of the roller are arranged on a second straight line running perpendicular to these axes.

[0025] In particular, the second straight line runs perpendicular to the support plane of the separating device.

[0026] Preferably, the second straight line runs parallel to the first straight line.

[0027] According to one embodiment of the invention, the rocker forms a force introduction element that transmits the force required to generate the necessary pressure on the cutting edge exit area to the cutting edge exit surface via the pressure medium. The necessary pressure is sufficient to prevent chips from tearing out.

[0028] The required pressure can be generated in different ways. On the one hand, the rocker arm regulates the pressure via the pressure medium using a defined weight.

[0029] Alternatively or in addition to this, a spring can be attached to the rocker, which acts on the cutting edge exit surface via the rocker and the pressure medium and regulates the pressure in a determinable manner.

[0030] Alternatively or in addition to this, a motorized, preferably pneumatic, drive can be connected to the rocker, which acts on the cutting edge exit surface via the rocker and the pressure medium and regulates the pressure in a determinable manner.

[0031] According to one embodiment of the invention, the pressure p H generated on the cutting edge exit surface by the pressure medium is spatially distributed in such a way that it compensates for the cutting edge pressure p S generated in the material by the cutting edges in the area of ​​the cutting edge exit surface, so that in this area the following applies: p H ≥ p S .

[0032] According to one embodiment of the kinematic chain, resistance forces in the pressure medium, such as the roller(s), resulting from the feed of the workpiece relative to the cutting tool, are transmitted into the housing by pressure forces in the rockers, which in turn press the pressure medium against the workpiece and generate pressure. This can create a predictable servo effect.

[0033] Since the cutting pressure p S generated by the cutting edge can vary due to the propulsion speed but also due to the rotational force of the cutting tool, means are provided for adjusting the pressure p H of the pressure medium on the cutting edge exit surface.

[0034] Preferably, a circular saw forms the cutting device as just described, with a saw blade as the cutting tool and saw teeth arranged on the circumference of the saw blade, each with a cutting edge as the cutting means.

[0035] The first partial swing joint and the second partial swing joint can be arranged, for example, outside the radial extension of the saw blade in the lateral view of the saw blade.

[0036] Further advantages, features and possible applications of the present invention will become apparent from the following description in conjunction with the embodiments shown in the drawings.

[0037] In the description, claims, and drawings, the terms and associated reference symbols used in the list of reference symbols below are used. In the drawings, the following definitions apply: Fig. 1a a schematic side view of a saw blade engaging a workpiece to illustrate the problem underlying the invention; Fig. 1b an enlarged detailed view of Figure 1a, Fig. 2 a schematic side view of the area of ​​a roller next to the saw blade, Fig. 3 a detailed view of a saw tooth of a saw blade in a workpiece with rollers, Fig. 4 a schematic view of a first embodiment not according to the invention; Fig. 5 a schematic view of a second embodiment not according to the invention; Fig. 6 a schematic view of a third embodiment not according to the invention; Fig. 7 a schematic view of a fourth embodiment according to the invention; Fig. 8 a side view of a fifth embodiment not according to the invention; Fig. 9 a sectional view AA of Fig. 8 ; Fig. 10a shows a side view of a sixth embodiment not according to the invention with a first cutting depth; Fig. 10b shows a side view of a sixth embodiment not according to the invention with a second cutting depth, and Fig. 10c shows a side view of a sixth embodiment not according to the invention with a third cutting depth.

[0038] In the Fig. 1a, Fig. 1b , Fig. 2 and Fig. 3 The problem of an unclean cut pattern that occurs during cutting, especially during sawing, is schematically illustrated in detail.

[0039] During circular sawing, a saw blade 10 of a circular saw 8 (not shown in detail here) cuts, for example, a plate 12 as a workpiece to be cut by rotating at the speed n and moving at the relative speed Δv to this. A saw tooth 14 of the saw blade 10 with a cutting edge 14a, which engages in the material of the plate 12, passes through the plate 12 with the tangential speed vt. This creates a cutting pressure p S , which on the one hand, due to its large gradient, reduces the shear stress τ required for machining s generated, but sometimes cannot be held by the material of the plate 12 at the top side 16 of the cutting edge exit: In a first approximation, the permissible tensile stress σ on the surface of the top side 16 is Z , Permit < p S is exceeded and the surface in the area 18 of the cutting edge exit consequently tears out, or chips or parts of chips are still partially connected to the edge 22 in the area 18 of the cutting edge exit. The tearing results in depressions on the upper side 16 of the plate 12 in the area of ​​the cutting surface 20 and in the cutting surface 20 itself. This results in an unclean cutting pattern on the edges 22 on both sides of the cutting edge exit.

[0040] To avoid such unclean cutting patterns, rollers 24 must be provided on the side of the saw blade 10 on the cutting edge exit side of the plate 12 in the area 18 of the cutting edge exit. These rollers generate a compressive stress in the area 18 of the cutting edge exit. In this case, compressive stress σ d in the form of Hertzian compression p H = σ d applied to the workpiece in the area 18 of the cutting edge exit. The rollers 24 are arranged spatially identically on both sides of the saw blade 10, only on mutually spaced sides of the saw blade 10. In principle, it is possible to provide only one roller in the area 18 of the cutting edge exit. However, two rollers 24 are preferably provided.

[0041] If two rollers 24 enclose the saw blade 10 on both sides in such a way that the pressures applied by the rollers 24 to the upper side 16 of the plate 12 in the area 18 of the cutting edge exit coincide, p S through p H overcompensated and tear-out prevented. An exact alignment of the base line FL of a roller 24 and the cutting edge exit line SL of the saw tooth 14a of the saw blade 14 is not required. It is sufficient if the spatially distributed pressures p H and ps coincide so that σ z, zul is never exceeded. A small gap SP between rollers 24 and saw blade 10 is also permissible, as long as the strength requirement is met. This gap SP causes additional bending stresses, which must also be compensated.

[0042] According to the Fig. 4According to a first embodiment not according to the invention, the roller 24 is detachably connected via a rocker 26 to a housing 28 (not shown in detail here). The stop point 30 on the housing 28 of the rocker 24 lies with the radius R of the rollers 24 above a rotation axis 32 of the saw blade 10. The base line FL of both rollers 24 at any cutting height always follows exactly the cutting edge exit line SL and the pressures p S and p H coincide perfectly.

[0043] Tear-out is avoided even in the event of limited elastic deformation of the system and / or manufacturing inaccuracies, i.e., an offset between the root line FL and the cutting edge exit line SL. Preferably, the root line FL of the roller 24 and the cutting edge exit line SL of the cutting edge 14a of the sawtooth 14 are congruent. To ensure this, among other things, the pivot point 30 is offset upwards relative to the rotational axis 32 of the saw blade 10 by the radius R of the roller 24.

[0044] For each roller 24, a rocker 26 is provided, which can rotate around a common axis of rotation at the stop point. The rocker 26 is always oriented perpendicular to the tangential velocity vt of the saw blade 10 or the saw tooth 14. If a protective hood (not shown here) is mounted, it captures the chips with maximum kinetic energy and efficiently directs them into the extraction system. This allows the extraction system to operate with reduced energy consumption.

[0045] According to a further embodiment not according to the invention, the rocker 26 is designed as a parallelogram guide, see Fig. 5The parallelogram is a convex quadrilateral with opposite parallel sides, like special trapezoids and two-dimensional parallelepipeds. Therefore, different configurations can form the parallelogram. In the present case, the rocker arm 26 is constructed in several parts and forms a rocker parallelogram. The rocker arm 26 comprises a first partial rocker arm 34, a second partial rocker arm 36, and a coupling 38. The first partial rocker arm 34 is connected to the housing 28 via a first housing joint 30a, and the second partial rocker arm 36 is connected via a second housing joint 30b. The coupling 38 is connected on the side of the first partial rocker 34 and second partial rocker 36 remote from the associated housing joint 30a, 30b in an articulated manner via a first and second partial rocker joint 40a, 40b to the first partial rocker 34 and second partial rocker 36 and at one of its free ends to the roller 24.

[0046] The joint axes of the first and second housing joints 30a, 30b and the first and second partial swing joints 40a, 40b are aligned parallel to the rotational axis of the saw blade 10. The joint axis 30c of the first housing joint 30a, the second housing joint 30b, and the rotational axis of the saw blade 10 are arranged on a first straight line 42 running perpendicular to these axes. The first straight line 42 runs perpendicular to a support plane 44 of the circular saw 8.

[0047] The joint axes of the first partial swing joint 40a, the second partial swing joint 40b, and the rotation axis of the roller 24 are arranged on a second straight line 46 running perpendicular to these axes. The second straight line 46 runs perpendicular to the support plane 44 of the circular saw 8.

[0048] The circular saw 8 is to be designed structurally and mechanically with regard to its overall rigidity with regard to permissible gaps SP as well as offsets of the base line FL and cutting edge exit line SL so that, depending on the material to be machined, the permissible tensile stress σ on its surface z, zul is not exceeded.

[0049] The pressure p H generated by the rollers 24 on the upper side 16 of the workpiece is introduced by a force which acts on the rollers 24 via the rocker 26. The rocker 26 forms a force introduction element which transfers the required force to generate the necessary pressure, i.e. the pressure p H, on the area 18 of the cutting edge exit via the roller 24 onto the cutting edge exit surface, which is large enough to prevent the chips from tearing out. The force can be generated by the dead weight of the rocker 26, which is large enough to generate the necessary pressure. In addition, the force can also be generated by a spring on the rocker 26 (not shown in detail here), which acts on the cutting edge exit surface via the rocker 26 and the roller 24 and generates the necessary pressure.A motor drive is also conceivable, which acts on the rocker 26 and generates a corresponding force, which acts via the rocker and the roller on the cutting edge exit surface and generates the necessary pressure.

[0050] In any case, the pressure p H of the roller 24 generated on the cutting edge exit surface is spatially distributed in such a way that it compensates for the cutting pressure p S generated in the material by the cutting edges 14a in the area of ​​the cutting edge exit surface, so that in this area the following applies: p H ≥ p S .

[0051] In addition, means for adjusting the pressure of the rollers may also be provided.

[0052] According to the Fig. 6According to a third embodiment not according to the invention, the roller 24 is detachably connected to the housing 28 via the rocker arm 26. In principle, this embodiment corresponds to the first embodiment. However, the roller 24 is not mounted directly on the rocker arm 26, but rather via a saw shoe 48, so that the pivot axis 50 of the saw shoe 48 and the associated joint 52 between the free end of the rocker arm 26 and the saw shoe 48 is aligned with the base line FL of the roller 24 resting on the workpiece 12 and the cutting edge exit line SL.

[0053] The roller 24 is rotatably mounted in the saw shoe 48. The saw shoe 48 is connected to the rocker 26 in the area of ​​the base of the roller 24 via the joint 52. The roller 24 is mounted in the saw shoe 48, guided perpendicularly to a support surface of the saw shoe 48, and is tensioned against a stop 54 by a spring 56. The roller 24 protrudes slightly from the bottom of the saw shoe 48 and is lifted by the workpiece 12, allowing it to roll freely and compensate for the cutting pressure.

[0054] In actual designs, the pivot point of the saw shoe 48 is usually located further forward than the circular saw 8. Here, too, a coupling can be achieved through a much more complex kinematics such that the base line FL of the roller 24 and the cutting edge exit line SL are aligned. The pressure of the roller 24 against the workpiece 12 can be applied and controlled, for example, by forces from its own weight and / or pneumatic cylinders.

[0055] An alternative parallelogram guide to the second embodiment is shown in Fig. 7 shown. A saw shoe 58 is also provided, which is guided over the workpiece during the sawing operation. The saw shoe 58 is coupled to the saw 8 with a geometrically identical, but mechanically independent four-bar chain kinematics 60. The advantage of this coupling is that the roller 24 rests on cams 62 arranged in front and behind the roller 24 on the saw shoe 58 and thus lies in a defined position when the circular saw 8 is lifted off.

[0056] A more concrete version shows Fig. 8 and 9, in which a conical roller 64 on one side of the saw blade 10 also enables miter cuts. On the other side of the saw blade 10 is a cylindrical roller 66 with a recess 68, which ensures concentrated pressure at the cutting edge exit. Both rollers 64 and 66 are guided on adjustment axes 70 by means of bearings 72. Adjustment to compensate for material removal by the saw blade 10 is achieved via a thread in a roller holder 74. The adjustment axis 70 is secured against rotation by means of a clamping screw 76 in the roller holder 74.

[0057] For the concrete implementation, the Figures 10a, 10b and 10c the immersion of the saw blade 10 at three different depths into the workpiece 12. A total of three hoods 78 are movable relative to each other in such a way that all chips are caught and removed, and the saw blade 10 is always encapsulated. Figures 10a and 10bthe first partial swing joint 40a and the second partial swing joint 40b are arranged outside the radial extension of the saw blade 10 in the lateral view of the saw blade 10. List of reference symbols

[0058] 8Circular saw 10Saw blade 12Panel as workpiece to be cut 14Sawtooth 14aCutting edge of the sawtooth 14 16Top of the workpiece 18Area of ​​the cutting edge exit 20Cutting surface 22Edges in the area of ​​the cutting surface 20 24Roller 26Rocker 28Housing 30Stop point 30aFirst housing joint, bottom 30bSecond housing joint, top 30cJoint axis 32Axis of rotation of the saw blade 10 34First partial rocker, bottom 36Second partial rocker, top 38Coupling, vertically aligned 40aFirst partial rocker joint, bottom 40bSecond partial rocker joint, top 42First straight line 44Support plane of the circular saw 8 46Second straight line 48Saw shoe 50Pivoting axis of the saw shoe 52Joint 54Stop 56Spring 58Saw shoe 60Four-bar linkage kinematics 62Cam 64Tapered roller 66Cylindrical roller 68Recess 70Adjustment axes 72Bearing 74Roller holder 76Clamping screw 78Cover FLFoot line SLCutting edge exit line SPGap RRadius of the roller 24

Claims

1. Cutting device having a housing (28), a driven disk-shaped cutting tool mounted in the housing (28) for cutting a workpiece (12), with cutting means (14) each having an associated cutting edge (14a) being arranged on a circumferential side of the cutting tool (10), which cutting means (14), during cutting, will penetrate into the material of the workpiece (12) to be cut on a cutting edge entry side of the workpiece (12) as a function of a feed speed of the cutting tool (10) relative to the workpiece (12), and will emerge on a cutting edge exit side of the workpiece (12) remote therefrom, thereby removing material from the workpiece (12) by cutting, with at least one means of exerting pressure being provided that exerts a pressure (pH), via a cutting edge outlet surface, on the surface of the cutting edge outlet side laterally of the cutting tool (10) in the region (18) of the cutting edge (14a) and that is pivotally mounted relative to the housing (28), which pressure exerting means (24) is supported in at least one rocker (26) at one end thereof, which rocker (26) is connected to the housing (28) via a first joint (30), wherein the rocker (26) is pivotally mounted about a first joint axis of the joint (30), wherein the first joint axis is arranged parallel to the axis of rotation (32) of the cutting tool (10), and wherein the pressure exerting means is in the form of at least one roller (24), which roller (24) has predetermined radius (R), and the axis of the joint is offset relative to the axis of rotation (32) of the cutting tool (10) by the radius (R) of the roller (24) in the direction of the cutting edge exit side, characterized in that the rocker (26) is composed of several parts and forms a rocker parallelogram which comprises first and second partial rockers (34, 36) and a coupler (38), with the first partial rocker (34) being connected to the housing (28) via a first housing joint (30a) and the second partial rocker (36) being connected to the housing (28) via a second housing joint (30b), which coupler (38), at the side of the first and second partial rockers (34,36) that is remote from the associated housing joint (30a, 30b), is connected in each case in an articulated manner via first and second partial rocker joints (40a, 40b) to the first and second partial rockers (34, 36) and has its one free end connected to the pressure exerting means (24), and wherein the rocker, and the circular path of the support region of the pressure exerting means made possible by the rocker, is additionally formed by a four-bar linkage with partial rockers and couplers, or by a cam-controlled transmission, or by a two-axis linear drive.

2. Cutting device according to claim 1, characterized in that the first partial rocker (34) and the second partial rocker (36) are of the same length.

3. Cutting device according to any one of the preceding claims, characterized in that the joint axes of the first and second housing joints (30a, 30b) and of the first and second partial rocker joints (40a, 40b) are aligned parallel to the axis of rotation (32) of the cutting tool (10).

4. Cutting device according to any one of the preceding claims, characterized in that the joint axis of the first housing joint (30a), of the second housing joint (30b) and the axis of rotation (32) of the cutting tool (10) are arranged on a first straight line (42) which is perpendicular to these axes.

5. Cutting device according to claim 4, characterized in that the first straight line (42) is perpendicular to the support plane (44) of the cutting device.

6. Cutting device according to any one of the preceding claims, characterized in that the joint axes of the first partial rocker joint (40a), of the second partial rocker joint (40b) and the axis of rotation of the roller (24) are arranged on a second straight line (46) which is perpendicular to these axes.

7. Cutting device according to claim 6, characterized in that the second straight line (46) is perpendicular to the support plane (44) of the cutting device.

8. Cutting device according to any one of the preceding claims, characterized in that a circular saw (8) forms the cutting device, with a saw blade (10) as the cutting tool and saw teeth (14) arranged on and around the circumference of the saw blade (10), each with a cutting edge (14a) as cutting means.

9. Cutting device according to any one of the preceding claims, characterized in that, when the saw blade (10) is viewed from the side, the first partial rocker joint (40a) and the second partial rocker joint (40b) are arranged outside the radial extent of the saw blade (10).