Hub flange for tool body

Abstract

The hub flange (101) has a fixing flange (110) adapted to receive the tool body (130). The fixing flange (110) is formed with a flange socket (111) for connection to the spindle shaft. A counter flange (120) is removably connected to the fixing flange. The fixing flange (110) and the counter flange (120) are connected to each other via a conical connection (150) which is arranged coaxially with the tool axis (B) and which is formed by an inner cone (151) and an outer cone (152) which is received in the inner cone.

Description

[Technical Field]

[0001] The present invention relates to a hub flange for a tool body, in particular for a grinding body. The invention further relates to a machining tool having such a hub flange, and to a tool head equipped with this machining tool. [Background technology]

[0002] Hub flanges for grinding wheels are standardized in the standard DIN ISO 666:2013-12. According to this standard, a "hub flange" is a system consisting of a "fixed flange" and a "loose flange" for attaching the grinding wheel to a grinding spindle by friction fit. The loose flange is also called a "counter flange." The clamping force for the friction fit of the grinding wheel is applied via several screws arranged on the pitch circle that press the counter flange in the direction of the fixed flange. The fixed flange has an integrally formed socket for a frictional or positive connection with the grinding spindle. This interface of the hub flange with the grinding spindle is called the "flange socket." The part of the grinding spindle that interacts with the flange socket, i.e., the interface of the grinding spindle with the flange socket, is called the "spindle socket."

[0003] 1 shows, in a central longitudinal section, a grinding tool 100 with a prior art hub flange 101 having a grinding wheel 130 clamped therein. Such a hub flange is offered under the designation "B 160" by Reishauer AG, Wallisellen, Switzerland.

[0004] The hub flange 101 includes a fixing flange 110 and a counter flange 120. The fixing flange 110 includes a flange socket 111 for connection to the grinding spindle. During operation, the grinding spindle is positioned on the right side of FIG. 1. The fixing flange 110 has a cylindrical outer surface 112 that is defined on the spindle side by a collar 113. At the end opposite the spindle, the fixing flange 110 has a connection region 115 with a reduced diameter and a cylindrical outer contour.

[0005] The counterflange 120 has an annular shape with a cylindrical inner surface. With this inner surface, the counterflange presses against the cylindrical connection area 115 of the fixing flange 110. A cylindrical bayonet connection exists between the fixing flange 110 and the counterflange 120. The counterflange 120 has a cylindrical outer surface 122, the outer diameter of which corresponds to the outer diameter of the cylindrical outer surface 112 of the fixing flange. The outer surface 122 of the counterflange 120 is aligned with the outer surface 112 of the fixing flange 110. A collar 123 is formed at the end of the counterflange 120 opposite the spindle, which defines the outer surface 122 of the counterflange 120 at its end. The counterflange 120 is fixed to the fixing flange 110 by a ring of cap screws 125.

[0006] The grinding wheel 130 is received at its central bore on the outer surface 112 of the fixed flange 110 and the outer surface 122 of the counter-flange 120. The grinding wheel 130 is clamped axially between an annular first clamping surface 114 of the collar 113 of the fixed flange 110 and an annular second clamping surface 124 of the collar 123 of the counter-flange 120. Optionally, an intermediate washer may be inserted between the grinding wheel 130 and the clamping surface 114 or 124. A cap screw 125 connecting the counter-flange 120 to the fixed flange 110 is used to generate the clamping force. Thus, at the clamping surfaces 114, 124, there is a friction fit between the grinding wheel 130 and the respective collars 113, 123, with intermediate washers inserted as the case may be.

[0007] Gear manufacturing is increasingly using machining tools with small diameters. To achieve the desired cutting speed, such tools are typically operated at relatively high rotational speeds. These tools can be relatively long relative to their diameter. This makes them particularly susceptible to bending and torsional vibrations. However, the prior art hub flange shown in FIG. 1 is not optimal for long, relatively narrow tools. This is especially true when the tool is to be connected to a spindle shaft at both ends. Summary of the Invention

[0008] SUMMARY OF THE INVENTION It is an object of the present invention to provide a hub flange that is particularly suitable for receiving a tool body having a relatively small diameter relative to its length.

[0009] This problem is solved by a hub flange according to claim 1. Further embodiments are described in the dependent claims.

[0010] A hub flange for a tool body is proposed. The hub flange defines a tool axis. The hub flange has a fixing flange suitable for receiving the tool body. The fixing flange has a first flange socket formed therein for connection to a first spindle shaft rotatable about the tool axis. The hub flange further has a counter flange removably connected to the fixing flange. The fixing flange and the counter flange are connected to each other via a conical connection, which is arranged coaxially with the tool axis and is formed by an inner cone ("cone receptacle") and an outer cone ("cone") received in the inner cone.

[0011] Terms are used herein in accordance with the definitions in DIN ISO 666:2013-12, with the following exceptions: the term "hub flange" is also used for tool holders to which tool bodies of types other than grinding wheels are clamped; and the term "counterflange" is interpreted more broadly than in DIN ISO 666:2013-12. The term "counterflange" also includes structures that are detachably connected to a fixed flange to form a unit without the tool body being directly clamped between the fixed flange and the counterflange.

[0012] In contrast to DIN ISO 666:2013-12, the hub flange may be intended to be connected at each end to a spindle shaft. For this purpose, the counter flange may have a second flange socket for connection to a second spindle shaft. Since the counter flange can be removed from the fixed flange to replace the tool body, the diameter of the second flange socket may be selected very freely and, in particular, may be larger than the inner diameter of the bore in the tool body, if necessary. This allows the second flange socket to be designed large enough to transmit sufficient torque through it, even for tools with small bore diameters.

[0013] By having a conical connection formed between the fixing flange and the counterflange, a precisely centered connection is created that is, on the one hand, backlash-free and, on the other hand, particularly resistant to bending. Unlike the prior art hub flange shown in Figure 1, the friction fit between the fixing flange and the counterflange no longer occurs exclusively via the tool body clamped therebetween, but can instead occur directly between the fixing flange and the counterflange in the region of the conical connection. In particular, it becomes possible to design the hub flange in such a way that the clamping force that holds the tool body to the hub flange is largely independent of the force that presses the fixing flange and the counterflange axially against each other at the conical connection.

[0014] This is particularly advantageous when the tool is connected to spindle shafts on both sides, so that the hub flange is compressed and axially clamped between the two spindle shafts, resulting in an axial compressive force acting on the hub flanges on both sides. In the case of the prior art hub flange shown in Figure 1, this compressive force would be transmitted to the tool body, potentially resulting in damage to the tool body, but in the present invention, the compressive force is transmitted directly to the conical connection between the fixed flange and the counter flange, and is thereby decoupled from the tool body.

[0015] The proposed configuration also makes it possible to transmit significantly higher torques between the fixed flange and the counter flange than is possible with the prior art according to Figure 1. This has particular advantages, for example, when the hub flange is driven on both sides. For example, if two drives generate different torques, the direct connection between the fixed flange and the counter flange at the conical connection prevents the torque difference from being transmitted to the tool body.

[0016] The inner cone of the conical connection may be formed on the fixed flange and the outer cone on the counterflange. Alternatively, the inner cone may be formed on the counterflange and the outer cone on the fixed flange. Half the opening angle of the conical connection, i.e., the single taper angle of the conical surface relative to the tool axis, may be, for example, 1° to 30°, preferably 2° to 10°. The length of the conical connection may be selected to be very short in projection onto the tool axis, but is preferably at least 3 mm.

[0017] Preferably, the connection between the fixed flange and the counterflange is a conical connection with axial surface contact. A major advantage of a conical connection with axial surface contact is that the two components (the fixed flange and the counterflange, each including a flange socket formed in each flange for connection to the respective spindle shaft) are not only precisely centered but also precisely positioned axially relative to each other. This allows the two components to be reconnected precisely when they must be separated to change the grinding wheel. The connection between the flange and the corresponding counterflange has an important quality assurance function during the manufacture of the hub flange. The additional axial surface contact also allows for higher axial forces to be applied between the fixed flange and the counterflange than with a simple conical connection. This means that higher torques can be transmitted between these elements. Furthermore, torsional and bending stiffness can be further improved.

[0018] For the axial surface contact, a first axial planar contact surface is formed adjacent to the inner cone of the component (fixing flange or counterflange) on which the inner cone is formed, and a second axial planar contact surface, opposing the first planar contact surface, is formed adjacent to the outer cone of the component on which the outer cone is formed. The first and second axial planar contact surfaces press against each other to establish a friction fit. In this regard, it is advantageous if the first and second axial planar contact surfaces are arranged adjacent to the respective cones. In particular, the first planar contact surface is preferably arranged adjacent to the end face of the inner cone and in a region radially surrounding the end face of the inner cone. Correspondingly, the second planar contact surface is preferably arranged in a region radially surrounding the outer cone. A weakened portion may be provided in the material of the associated component (fixing flange or counterflange) between the front end of the inner cone and the first planar contact surface in the radial direction to increase the radial extensibility of the inner cone.

[0019] Advantageously, axially aligned screws are provided for fastening the counter flange to the fixing flange, which screws axially press the fixing flange and the counter flange together so that an axial pressing force acts between them, and which screws are advantageously evenly distributed about the tool axis to minimize imbalance.

[0020] To axially clamp the tool body to the hub flange, the hub flange preferably defines first and second clamping surfaces that face each other, such that the tool body can be axially clamped in compression between the first and second clamping surfaces. Preferably, the clamping surfaces extend perpendicular to the tool axis. This eliminates the need for the tool body to be clamped directly between the first and second clamping surfaces. For example, an intermediate washer can be inserted between each clamping surface and the tool body. The intermediate washer can be made of aluminum, for example. The intermediate washer can be extremely thin, for example, less than 1 mm thick.

[0021] In particular, the hub flange may have a positioning ring that has an axially variable position relative to the counter-flange, with a first clamping surface formed on the fixing flange and a second clamping surface formed on the positioning ring, so that tool bodies of different widths can be clamped on the hub flange, even though the relative position of the fixing flange and the counter-flange is fixed by the conical connection and the surface contact.

[0022] To change the axial position of the positioning ring, the fixing flange, or preferably the counter flange, may have an external thread, and the positioning ring may have an internal thread complementary to the external thread. The axial position of the positioning ring can be adjusted by screwing the positioning ring into place. A fixing element, such as a radial fixing pin, may be provided on or within the positioning ring to prevent unintentional rotation of the positioning ring in the fixed position. To transmit the axial clamping force from the positioning ring to the tool body, an intermediate ring may be arranged axially adjacent to the positioning ring. In this case, the intermediate ring does not rotate itself but provides a sliding surface for the clamping surface of the positioning ring. The intermediate ring prevents direct friction between the positioning ring and the tool body during the screwing of the positioning ring. The intermediate ring may have elastic properties to generate a defined clamping force on the tool body even if the length of the tool body changes, for example, during the setting process.

[0023] In an alternative embodiment, the positioning ring may be axially displaceable relative to the fixed flange and / or counterflange, and may be provided with threaded elements that are screwed into the counterflange or positioning ring to change the axial position of the positioning ring relative to the counterflange. These threaded elements may, for example, be screws that have a fixed axial position relative to the counterflange, or screws that can be threaded into or unthreaded out of the positioning ring to a variably different extent to change the axial position of the counterflange. Alternatively, the threaded element may be a set screw that can be threaded into or unthreaded out of the counterflange to a variably different extent, and this set screw applies an axial compression force to the positioning ring at its distal end. The threaded connection may be combined with an elastic element to generate a defined clamping force on the tool body, even if the tool body length changes. For example, an axial elastic element, such as a bushing with a Belleville spring, may be provided on the positioning ring, to which the aforementioned set screw applies axial pressure.

[0024] The hub flange is preferably connected to the spindle shaft via a conical connection, preferably with a surface contact. This allows for extremely precise centering of the hub flange in the grinding head. For example, the connection can be formed via one of the forms A, BF, BM, CF, or CM described in DIN ISO 666:2013-12. For this purpose, the first flange socket and / or the second flange socket can be formed as an inner or outer cone with a flat contact surface. However, alternative types of connection between the hub flange and the spindle shaft are also conceivable, for example, via a radially acting hydraulic expansion element.

[0025] It is advantageous if the two flange sockets are formed differently from one another so that the tool can only be received at a predefined position between the spindle shafts. For example, the diameters of the two flange sockets may be different.

[0026] The present invention further provides a machining tool having a hub flange of the type described above and a tool body clamped to the hub flange. While the design of the hub flange makes it particularly well suited for elongated tool bodies with relatively small diameters (e.g., a length-to-diameter ratio greater than 1), the present invention is not limited to such tool bodies. The tool body may therefore have any length-to-diameter ratio. In particular, the machining tool may be a grinding tool, particularly a tool for gear grinding. The tool body may therefore be a one-piece grinding body or a multi-component grinding body. The grinding body may, in particular, be vitrified-bonded and therefore dressable. It may, for example, contain corundum grinding grains or cubic boron nitride (cBN) grinding grains. However, the grinding body may also be polymer-bonded and, for example, specifically designed as a grinding body for abrasive grinding. Alternatively or additionally, the tool body may have a metal substrate, for example, coated with a non-dressable hard material. Any combination of similar or different tool bodies is also contemplated. In particular, the tool body may comprise a grinding wheel (grinding worm) with a worm-shaped outer contour and / or a shaping stone. In the case of a multi-component tool body, the tool body may in particular be a combination of two or more grinding worms, for example a combination of a rough grinding worm and a finish or polishing grinding worm, a combination of a grinding worm and a shaping stone, or a combination of two or more shaping stones.

[0027] The present invention further provides a tool head for a machine tool, in particular a gear cutting machine, having a machining tool of the type described above. The tool head further comprises a first spindle unit having a first spindle shaft rotatably mounted on the first spindle unit about a tool axis, and a second spindle unit having a second spindle shaft rotatably mounted on the second spindle unit about the tool axis. The first and second spindle units are coaxially arranged such that the machining tool can be received axially between the first and second spindle shafts. In order to receive a tool between the spindle shafts and to be able to transmit torque to the tool, spindle projections are formed on the first spindle shaft and / or the second spindle shaft, whereby a non-positive and / or positive connection to the tool can be formed at each spindle projection by an axial compressive force acting between the tool and the spindle projection, in particular via the conical connection already mentioned.

[0028] In some embodiments, the first spindle unit and the second spindle unit are housed within a common spindle housing, in which case the second spindle bearing may be held in a bearing receptacle that is axially displaceable relative to the common spindle housing to allow for machining tool changes. In other embodiments, the two spindle units are housed in separate spindle housings that are displaceable relative to one another along the workpiece axis to allow for machining tool changes.

[0029] Particular advantages are achieved when the two spindle shafts are axially clamped together with the machining tool so that an axial compressive force acts on both sides of the machining tool. For this purpose, the following design is particularly advantageous: the second spindle shaft has at least one axial bore. Correspondingly, the tool head has at least one pull rod extending through a corresponding axial bore of the second spindle shaft, the pull rod being connectable at a first end to the first spindle shaft. The pull rod is connectable at a second end to the second spindle shaft so that an axial compressive force can be exerted on the tool between the first and second spindle shafts. For this purpose, the machining tool, in particular its hub flange, also has at least one axial bore through which each pull rod can pass through a corresponding bore of the machining tool.

[0030] This type of axial pressure device forms a unit consisting of two spindle shafts and a tool that is particularly resistant to twisting and bending. The combination of the pull rod and clamping element creates high axial compression forces between the machining tool and the two spindle shafts. As a result, the unit functions as a single shaft. At the same time, this structure can be extremely compact, making it particularly suitable for machining tools with small diameters. Due to the direct connection between the fixing flange and the counter flange at the conical connection, high axial compression forces are not transmitted to the tool body, or are transmitted only to a small extent.

[0031] However, the above-described construction with a pull rod is also advantageous if the tool is designed differently from the type described above. In this regard, the invention also relates to a tool head for a machine tool, in particular a gear cutting machine, comprising: a first spindle unit having a first spindle shaft, the first spindle shaft being rotatably mounted to the first spindle unit about a tool spindle axis; a second spindle unit having a second spindle shaft, the second spindle shaft being rotatably mounted on the second spindle unit about the tool spindle axis; It has the first spindle unit and the second spindle unit are arranged such that a tool is axially receivable between the first spindle shaft and the second spindle shaft and such that the tool is rotationally driven about the tool spindle axis; the second spindle shaft has at least one axial bore; The tool head has at least one pull rod extending through an axial bore of the second spindle shaft; the pull rod being connectable at one end to the first spindle shaft in a tensioning manner; The pull rod is connectable at another end to a second spindle shaft so as to generate an axial compressive force on the tool between the first spindle shaft and the second spindle shaft. Regarding the tool head.

[0032] Preferably, there is exactly one pull rod extending through the central axial bore of the second spindle shaft, and therefore the hub flange also preferably has a central axial bore through which the pull rod can pass.

[0033] In a particularly simple embodiment, the pull rod can be connected to the first spindle shaft by screwing it axially into the first spindle shaft. For this purpose, the corresponding ends of the pull rod and the first spindle shaft can be provided with complementary threads. However, other types of connections, for example bayonet connections, are also conceivable.

[0034] The other free end of the pull rod can be provided with a clamping element forming an annular contact surface that is supported on the second spindle shaft after the pull rod is connected to the first spindle shaft and generates an axial compressive force on the second spindle shaft to press the second spindle shaft in the direction of the first spindle shaft. In the simplest case, the pull rod can be configured for this purpose as a screw with a screw head, for example. In this case, the screw can be screwed into the first spindle shaft, and the screw head can form the clamping element. The axial clamping force is then generated simply by tightening the screw.

[0035] In another, equally simple embodiment, the free end of the pull rod is provided with an external thread onto which a nut can be screwed, the nut then forming the clamping element, and the axial compression force is generated simply by tightening the nut.

[0036] Preferably, however, the tool head has a clamping element removably connectable to the pull rod, which preferably generates a compressive force acting purely axially, without clamping of the clamping element generating a torque component about the tool spindle axis. For this purpose, the clamping element has a base element that can be rigidly connected to the pull rod, for example, via a screw connection, a bayonet, or a clamping bushing. The base element may have a central receiving opening for receiving the pull rod or, if there is sufficient space, a pin that can be fixed in the axial bore of the pull rod. The clamping element further comprises an axial pressing element that is axially movable, particularly axially displaceable, relative to the base element in the direction of the second spindle shaft to axially press the second spindle shaft toward the first spindle shaft. The axial pressing element may, in particular, be annular and surround the central receiving opening or pin of the base element; in this case, the axial pressing element may also be called a "pressing ring." The axial pressing element forms the annular contact surface already described. The clamping element further comprises at least one actuating element movable relative to the base element for axially moving the axial pressure element relative to the base element. The actuating element may, for example, be a pressure screw that can be screwed into the base element along the longitudinal or transverse direction. Such clamping elements are known per se from the prior art and are commercially available in many forms.

[0037] In some embodiments, the force transmission from the actuating element to the axial pressure element is purely mechanical. For example, the actuating element may be a plurality of cap screws axially held in the base element, which can be screwed into the axial pressure element to axially displace the axial pressure element relative to the base element. In another embodiment, one or more set screws that can be adjusted in the base element in the direction of the axial pressure element via a threaded connection serve as the actuating element. In yet another embodiment, the actuating element acts, for example, on a gear that advances the axial pressure element. Such clamping elements are available, for example, under the names ESB, ESG, or ESD from Enemac GmbH, Kleinwallstadt, Germany.

[0038] In another embodiment, the force is transmitted from the actuating element to the axial pressure element hydraulically. For this purpose, the actuating element may be configured, for example, as a pressure screw, which generates pressure in a hydraulic system when screwed in, and this pressure acts on the axial pressure element. Such clamping elements are available, for example, from Albert Schrem Werkzeugfabrik GmbH, Herbrechtingen, Germany.

[0039] Instead of generating an axial compressive force between the pull rod and the second spindle shaft using a clamping element that remains on the pull rod during operation, it is also conceivable to first generate the compressive force using a clamping tool, secure the connection in a clamped state with a quick nut, and then remove the clamping tool again.

[0040] However, the tool may be clamped between the first and second spindle shafts in ways other than using a continuous pull rod, as long as the resulting unit is a tightly clamped unit including two spindle shafts and a tool. Accordingly, a first pull rod may be connectable to the tool at a first end, for example, by threading or via a hollow-shank taper connection. In this case, the first pull rod may extend through an axial bore of the first spindle shaft and be connectable to the first spindle shaft at a second end so as to generate an axial compressive force between the first spindle shaft and the tool. A second pull rod may be disposed on the opposite side of the tool. In this case, the second pull rod may be connectable to the tool at a first end, for example, by threading or via a hollow-shank taper connection. In this case, the second pull rod may extend through an axial bore of the second spindle shaft and may be connectable at its second end to the second spindle shaft so as to generate an axial compressive force between the second spindle shaft and the tool.

[0041] As an alternative to axial pressure by a pull rod, the hub flange may be connectable to the at least one spindle shaft in another way, in particular the hub flange may be provided with at least one thread, preferably a threaded bore, for connecting the at least one spindle shaft to the hub flange.

[0042] To facilitate tool changes, it is advantageous if the second spindle unit is axially displaceable relative to the first spindle unit. If both spindle units are accommodated in a common spindle housing, this can be achieved by having a spindle bearing for the second spindle shaft that is axially displaceable relative to the spindle housing.

[0043] The first and / or second spindle units may include a drive motor configured to drive the corresponding spindle shaft in rotation about the tool spindle axis, thereby driving the tool. In some embodiments, only the first spindle unit includes a drive motor, and the second spindle unit forms a passive counter-spindle for the first spindle unit without its own drive motor. In another form, the second spindle unit also includes its own drive motor. Each drive motor may, in particular, be a direct drive.

[0044] The invention further provides a machine tool comprising a tool head of the above-mentioned type and at least one workpiece spindle for driving a workpiece in rotation about the workpiece axis. The machine tool may be configured as a gear cutting machine, in particular as a gear grinding machine. For this purpose, the machine tool may include a (in particular suitably programmed) machine control system configured to cause the machine to machine, by means of a tool, gear teeth of a workpiece received in the at least one workpiece spindle. In particular, the machine control system may be configured to cause the machine to machine gear teeth of the workpiece by form grinding or generating gear grinding. For this purpose, the machine control system may be configured to establish a suitable rotational connection between the workpiece spindle and the tool spindle.

[0045] Preferred embodiments of the present invention are described below with reference to the drawings, which are for illustrative purposes only and should not be construed as limiting. [Brief explanation of the drawings]

[0046] [Figure 1] 1 is a central longitudinal cross-sectional view showing a grinding tool having a hub flange according to the prior art; [Figure 2] 1 is a perspective view showing a grinding tool having a hub flange according to a first embodiment of the present invention. [Figure 3]FIG. 3 is a central vertical cross-sectional view showing the grinding tool of FIG. 2. [Figure 4] FIG. 3 is a perspective view showing a hub flange of the grinding tool of FIG. 2. [Figure 5] 7 is a central longitudinal cross-sectional view taken along plane VV in FIG. 6, showing an enlarged detail of the hub flange in FIG. 4. [Figure 6] FIG. 5 is a front view showing a counter flange of the hub flange of FIG. 4. [Figure 7] FIG. 10 is a diagram showing a portion of a central longitudinal cross-sectional view of a grinding tool having a hub flange according to a second embodiment. [Figure 8] FIG. 10 is a diagram showing a portion of a central longitudinal cross-sectional view of a grinding tool having a hub flange according to a third embodiment. [Figure 9] FIG. 10 is a diagram showing a portion of a central vertical cross-sectional view of a grinding tool having a hub flange according to a fourth embodiment. [Figure 10] FIG. 2 is a schematic perspective view of a tool head. [Figure 11] FIG. 11 is a perspective cross-sectional view of the tool head of FIG. 10. [Figure 12] FIG. 2 is a central vertical cross-sectional view showing a clamp nut. [Figure 13] FIG. 14 is a perspective view showing the clamp nut of FIG. 13. [Figure 14] FIG. 1 is a schematic perspective view of a machine tool for hardening and finishing gears by generating gear grinding. DETAILED DESCRIPTION OF THE INVENTION

[0047] [Definition] Gear cutting machine: a machine configured to produce or machine gear teeth, especially internal or external gear teeth, on a workpiece. For example, a gear cutting machine may be a fine machining machine for machining pre-toothed workpieces, and in particular a hardening and finishing machine for machining pre-toothed workpieces after hardening. The gear cutting machine is equipped with a machine control system programmed to control the automatic machining of gear teeth.

[0048] Gear generating: Gear machining in which a tool rolls on the workpiece and performs a cutting action. Various gear generating processes are known, where a distinction is made between processes with a geometrically non-defined cutting edge, such as gear grinding or gear honing, and processes with a geometrically defined cutting edge, such as gear hobbing, gear skiving, gear shaving or gear shaping.

[0049] Generating Gear Grinding: The generating gear grinding process is a continuous chip removal process in which axisymmetric periodic structures are produced using a geometrically variable cutting edge, using a grinding wheel with a worm-shaped outer contour ("grinding worm") as the tool. The tool and workpiece are mounted on a rotating spindle. The rotational motion typical of the process is achieved by combining the rotational motion of the tool and workpiece about the rotation axis. This rotational motion, together with the axial feed motion of the tool or workpiece along the workpiece axis, produces the cutting action.

[0050] Tool Head: As used herein, the term "tool head" refers to an assembly configured to receive and rotationally drive a machining tool. In particular, the tool head may be mounted on a rotating bed and / or one or more slides for aligning and positioning the tool relative to a workpiece.

[0051] Spindle Unit: In machine tool construction, a rotatable shaft onto which a tool or workpiece can be clamped is typically referred to as a "spindle." However, an assembly including a rotatable shaft, as well as an associated spindle bearing for rotatably supporting the shaft and an associated housing, is also often referred to as a "spindle." The term "spindle" is used in this context herein. A shaft alone is referred to as a "spindle shaft." An assembly having a spindle shaft and at least an associated spindle bearing is referred to as a "spindle unit." A "spindle unit" may have its own housing, or may be housed in a common housing with another spindle unit.

[0052] [Hub flange according to the first embodiment] 2 and 3 show a machining tool 100. The machining tool 100 has a hub flange 101, and a tool body 130 is clamped to the hub flange. The hub flange 101 is shown alone in FIGS. 4 to 6. Functionally similar parts are given the same reference numerals as in FIG. 1.

[0053] In this example, the tool body 130 is a grinding tool. Therefore, in this example, the machining tool 100 is a grinding tool. However, other types of tool bodies 130 may be provided.

[0054] The hub flange 101 defines a tool axis B about which the hub flange can rotate. The hub flange includes a fixing flange 110 and a counter flange 120. The fixing flange 110 has a first flange socket 111 at its right end in FIG. 3 for connection to a first spindle shaft. In this example, the first flange socket 111 is formed as an internal cone (a "tapered socket") with a flat contact surface disposed inside the internal cone, specifically a short tapered receptacle 1:4 according to DIN ISO 702-1:2010-04. The fixing flange 110 has a cylindrical outer side surface 112. The side surface 112 is defined by a collar 113 at the end of the fixing flange 110 where the first flange socket 111 is formed. The collar 113 has an enlarged outer diameter. The collar forms an annular first clamping surface 114 for the tool body 130. The first clamping surface 114 extends in a plane perpendicular to the tool axis B. A central hole 116 extends through the fixing flange 110 along the tool axis B. Locating holes 117 are used to position and fix the fixing flange 110 circumferentially during clamping of the tool body 130. A machine-readable data carrier, such as an RFID tag or an optical code, may be arranged in a receiving notch 118 on the periphery. Balancing holes 119 are provided for balancing purposes and / or allow the attachment of additional balancing weights. At the left end of FIG. 3 , i.e., the end opposite the first flange socket 111, the fixing flange 110 is formed with another internal cone ("tapered socket") 151. This internal cone 151 is particularly clearly shown in FIG. 5 . An area of ​​the end face of the fixing flange 110 adjacent to and surrounding the inner cone 151 forms a first planar contact surface 153. The first planar contact surface 153 extends in a direction perpendicular to the tool axis B.

[0055] At its end located on the left side in FIG. 3, i.e., at the end opposite to the first flange socket 111, the counterflange 120 has a second flange socket 121. In this case, the second flange socket 121 is also formed as an inner cone ("tapered socket") with a flat contact surface arranged inside this inner cone, specifically as a 1:4 short taper receptacle in accordance with DIN ISO 702-1:2010-04. At its end located on the right side in FIG. 3, i.e., at the end facing the fixing flange 110, the counterflange 120 is formed with an outer cone ("taper") 152 complementary to the inner cone ("tapered socket") 151 of the fixing flange 110. The outer cone 152 is radially surrounded by an annular second flat contact surface 154 facing the first flat contact surface 153 of the fixing flange (see FIG. 6). A central bore 126 extends through the counter flange 120 along the tool axis B. The bore 126 is aligned with the bore 116 in the fixing flange 110. Together, the bores 116 and 126 form a continuous axial bore through the hub flange 101.

[0056] The counter-flange 120 is connected to the fixed flange 110 via a conical connection with a surface contact. The tapered connection 150 is formed by an inner taper 151 on the fixed flange 110 and a complementary outer taper 152 on the counter-flange 120. The surface contact is formed by two complementary planar contact surfaces 153, 154.

[0057] One important advantage of this design is that, especially for small grinding wheels, this division of the hub flange allows the flange sockets 111, 121 for torque transmission to be selected with significantly larger diameters on both sides than if both flange sockets were located on the fixed flange. However, any separation would be detrimental, so a strong connection is required. This is ensured by the conical connection with surface contact. Furthermore, this type of connection ensures that the fixed flange 110 and counter flange 120 are fully engaged again after each grinding wheel change and can be easily separated again.

[0058] The counter flange 120 is secured to the fixed flange 110 by a number of cap screws 125 evenly distributed around the circumference. The cap screws 125 create a defined axial contact pressure between the fixed flange 110 and the counter flange 120. The axial contact pressure is transferred directly through a conical connection that includes a face contact between the fixed flange 110 and the counter flange 120.

[0059] The counter flange 120 has an outer surface provided with an external thread 127, onto which a positioning ring 140 is screwed. The positioning ring 140 has a number of longitudinal grooves 141 formed on its outer periphery, allowing it to be rotated with an appropriate wrench. To prevent unintentional rotation of the positioning ring 140, the positioning ring 140 can be fixed to the counter flange 120 by radial fixing pins 142. The positioning ring 140 forms a second clamping surface 144 on its end face facing the fixing flange 110. The second clamping surface 144 extends in a plane perpendicular to the tool axis B. The second clamping surface faces the first clamping surface 114 provided on the fixing flange 110.

[0060] The tool body 130 has a central bore along the tool axis B. The tool body 130 is pressed onto the fixing flange 110 at this bore. In the region of the bore, the tool body has an inner surface on the outer surface 112 of the fixing flange 110. The tool body 130 is supported in the axial direction by a first clamping surface 114 provided on the fixing flange 110. A thin intermediate washer 131, which may be made of aluminum, may be provided between the tool body 130 and the first clamping surface 114. The tool body 130 is fixed to the hub flange 101 by a positioning ring 140 and an intermediate ring 145. A thin intermediate washer 132, which may also be made of aluminum, may be provided between the tool body and the intermediate ring 145. In this case, the positioning ring 140 applies an axial clamping force to the tool body 130 at the second clamping surface 144 via the intermediate ring 145 and, if provided, the intermediate washer 132. By proper positioning of the positioning ring 140 , this axial clamping force can be adjusted independently of the axial contact pressure between the fixed flange 110 and the counter flange 120 .

[0061] To clamp the tool body 130, the following procedure is followed: First, the counter flange 120 is loosened from the fixed flange 110. The positioning ring 140 is screwed back as far as possible in the direction of the second flange socket 121, and the intermediate ring 145 is pushed back as far as possible. The tool body 130, together with the intermediate washers 131 and 132, if necessary, are slid along the fixed flange 110, and the counter flange 120 is fixed to the fixed flange 110 by the screws 125. The screws 125 are then tightened until a sufficient axial contact force is created between the fixed flange 110 and the counter flange 120. During this process, the tool body 130 is not yet axially clamped. Only after the connection between the fixed flange 110 and the counter flange 120 is established, is the positioning ring 140 then screwed forward until the desired axial clamping force is applied to the tool body 130 via the intermediate ring 145. This allows the axial clamping force on the tool body 130 to be set independently of the axial contact force between the fixed flange 110 and the counter flange 120 .

[0062] The hub flange 101 can be configured to accommodate only specific types of tool bodies 130. For example, different outer diameters of the outer surface 112 can be provided depending on the type of tool body 130. In particular, a grinding body having corundum grinding grains can have a larger outer diameter than a grinding body having cBN grinding grains. This ensures that a cBN grinding body cannot be accidentally attached to a hub flange provided for a corundum grinding body, or vice versa. Instead of having different diameters for different tool types, this can also be achieved by providing different shapes, such as grooves, polygonal regions, or serrations in the hub flange.

[0063] To ensure that the two flange sockets 111, 121 are precisely aligned with one another, the fixed flange 110 and the counter flange 120 are manufactured in pairs and proportioned to each other.

[0064] [Second to Fourth Embodiments] 7 shows a second embodiment. This embodiment differs from the first embodiment mainly in the way in which the tool body 130 is clamped to the hub flange 101. As in the first embodiment, a positioning ring 140 is provided for this purpose. This positioning ring is axially displaceable relative to the counter-flange 120. A plurality of adjusting screws 146 in the form of cap screws are threaded into the positioning ring 140. The adjusting screws 146 are evenly distributed around the circumference. The adjusting screws are axially supported by the counter-flange 120 so that they are prevented from axial movement in the direction of the second flange socket 122. When the cap screws 146 are threaded out of the positioning ring 140, they press the positioning ring 140 axially against the tool body 130, which generates an axial clamping force.

[0065] A third embodiment is shown in Figure 8. This embodiment also differs from the first embodiment mainly in the way in which the tool body 130 is clamped to the hub flange 101. Again, the locating ring 140 is axially displaceable relative to the counter-flange 120. For this purpose, locating pins 147 in the form of set screws guided by threads in the counter-flange 120 are used. When the locating pins 147 are screwed into the counter-flange, they press the locating ring 140 axially against the tool body 130, thereby generating an axial clamping force.

[0066] 9 shows a fourth embodiment. This embodiment is largely the same as the third embodiment. However, unlike the third embodiment, axial spring elements 148 in the form of spring bushings are arranged in the locating ring 140. Locating pins 147 act on these spring elements. Due to their elastic properties, these spring elements ensure that a sufficient axial clamping force is still applied to the tool body 130, even if the length of the tool body 130 changes, for example, due to a setting process on the tool body 130.

[0067] [Tool head with machining tool] Figures 10 and 11 show a tool head equipped with a machining tool 100 according to one of the embodiments described above. For clarity, the machining tool 100 is shown only diagrammatically.

[0068] The tool head includes a base 310. A linear guide 311 is formed in the base 310. A first spindle unit 320 and a second spindle unit 330 are guided in the linear guide 311 so as to be displaceable along the shift direction Y. For this purpose, the spindle units have corresponding guide shoes 326, 336, respectively. The machining tool 100 is held between the spindle units 320, 330. A tool axis B extends parallel to the shift direction Y.

[0069] The second spindle unit 320 and the first spindle unit 330 can be coupled together after the machining tool 100 is received therebetween. Once coupled, the units can be moved together in a shift direction Y by a shift drive and ball screw 312 (not shown) to vary the area of ​​the tool that engages the workpiece along the tool axis.

[0070] In this example, the spindle unit 320 is a motor-driven spindle and includes a drive motor 324 that drives a first spindle shaft 322 to rotate about the tool axis B. The first spindle shaft 322 is supported by a spindle bearing 323 in a spindle housing 321 of the first spindle unit 320. In this example, the second spindle unit 330 is a counter-spindle and includes a non-driven second spindle shaft 332 that is supported by a spindle bearing 333 in a spindle housing 331 of the second spindle unit 330. However, instead of this configuration, both spindle units 320, 330 may be driven.

[0071] The tool-side ends of the spindle shafts 322, 332 are formed with opposing spindle sockets in the form of spindle lugs 325, 335. The shape of the spindle lugs is complementary to the shape of the flange sockets 111, 121 of the hub flange 101 of the machining tool 100, and each has a conically tapered shape towards the machining tool 100 and a flat contact surface on each end face. For example, each spindle lug may be formed as a tapered shank 1:4 in accordance with DIN ISO 702-1:2010-04.

[0072] Thus, there is a conical connection with face contact between each of the flange sockets 111, 121 and the spindle lugs 325, 335. The conical connection may have different diameters at the two ends of the machining tool 100 to ensure that the machining tool 100 can only be received between the spindle lugs 325, 335 in the correct orientation.

[0073] The machining tool 100 is axially clamped between the spindle lugs 325, 335 by a pull rod 370 and a clamping nut 372. To this end, the machining tool 100 and the second spindle shaft 332 each have a central axial bore extending therethrough. The first spindle shaft 322 also has a central axial bore at its tool-side end. An internal thread is formed in this bore. The pull rod 370 is inserted through the spindle shaft 332 and the central bore of the machining tool 100. At its end facing the first spindle unit 320, the pull rod 370 has an external thread that screws into the internal thread of the first spindle shaft 322. The pull rod also has an external thread at its other end. A clamping nut 372 is screwed onto this external thread. When the clamping nut 372 is tightened, the clamping nut 372 applies axial pressure to the second spindle shaft 332 in the direction of the machining tool 100. This causes the machining tool 100 to be clamped axially between the spindle projections 325, 335. This provides a single continuous shaft with high bending and torsional stiffness.

[0074] A first balancing unit 350 is arranged on the first spindle shaft 322 in the axial region between the housing 321 of the first spindle unit 320 and the machining tool 100. A second balancing unit 360 is arranged on the second spindle shaft 332 in the axial region between the housing 331 of the second spindle unit 330 and the machining tool 100. The balancing units 350, 360 surround each spindle shaft 322, 332 outside the housing of each spindle unit 320, 330. Each balancing unit has a housing that tapers from the assigned spindle unit toward the machining tool 100. The tapered outer contour of the balancing units 350, 360 reduces the risk of collision between the balancing unit and the workpiece. Each balancing unit 350, 360 is formed as a ring-shaped balancing system. The two balancing units 350, 360 are used to balance the system comprising the machining tool 100 and the spindle shafts 322, 332 clamped thereto on two balancing planes. Alternatively, it is conceivable that at least one balancing element is arranged on the hub flange.

[0075] [Clamp nut] 12 and 13 show an exemplary clamp nut 372 that may be used with a tool head such as those described above.

[0076] The clamping nut 372 includes a base element 373 defining a central bore with an internal thread for screwing the base element 373 onto a pull rod with a corresponding external thread. At one end, the base element 373 has an external hexagonal nut. A support ring 374 is attached to the base element 373. The support ring abuts against a collar of the base element 373 so that axial movement in one direction (toward the left in FIG. 9 ) is prevented. Furthermore, an annular axial pressure element 375 is guided axially displaceably in the base element 373. A plurality of actuating elements 376 in the form of pressure screws are screwed into the axial pressure element 375 and are axially supported by the support ring 374 so that axial movement in one direction (toward the left in FIG. 9 ) is prevented. By loosening the pressure screw from the axial pressing element 375, the axial pressing element 375 is advanced relative to the base element 373 in the direction opposite to the support direction (to the right in FIG. 9).

[0077] To clamp the tool 100 between the two spindle shafts 322, 332, the axial pressure element 375 is first moved completely backward relative to the base element 373 by screwing the pressure screw into the axial pressure element 375 as far as possible. The clamping nut 372 is then screwed onto the pull rod 370 and adjusted relative to the second spindle shaft 332 by the hexagonal external shape of the base element 373. This is done with a relatively low torque. The pressure screw then advances the annular axial pressure element 375 in a controlled manner toward the second spindle shaft 332 until the desired clamping force acts on the tool 340. The axial pressure element 375 is thereby supported by the annular contact surface on the second spindle shaft 332.

[0078] Of course, other constructions of clamping nuts may also be used, as are known per se from the prior art, for example the force transmission may take place in a manner different from that shown, in particular hydraulic clamping nuts may be used.

[0079] Instead of a clamping nut with an internal thread, a clamping element may also be used which can be connected to the pull rod in a manner other than a threaded connection, for example via a bayonet or clamping bush.

[0080] [Example machine tool structure] 14 shows an example of a machine tool for hard-finishing gears by generating gear grinding. The machine has a machine bed 600 on which a tool support 200 is arranged so as to be displaceable along a horizontal feed direction X. A Z-slide 210 is arranged on the tool support 200 so as to be displaceable along a vertical direction Z. The Z-slide 210 supports a swiveling bed 220 which is swivellable relative to the Z-slide 210 about a horizontal swiveling axis A. The swiveling axis A is parallel to the feed direction X. A tool head 300, shown only diagrammatically, is arranged on the swiveling bed 220. The shift direction Y is perpendicular to the X-axis and forms an adjustable angle with the Z-axis about the A-axis.

[0081] Additionally, a pivotable workpiece support in the form of a rotary turret 400 is disposed on the machine bed 600. The rotary turret 400 is pivotable about a vertical pivot axis C3 between a plurality of rotational positions. The rotary turret supports two workpiece spindles 500, each of which can clamp a workpiece 510. Each of the workpiece spindles 500 is drivable to rotate about a workpiece axis. In FIG. 12, the workpiece axis of the visible workpiece spindle 500 is designated C2. The workpiece axis of the workpiece spindle not visible in FIG. 12 is referred to as the C1 axis. The two workpiece spindles are disposed on the rotary turret 400 at diametrically opposite positions (i.e., offset 180° with respect to the pivot axis C3). In this way, one of the two workpiece spindles can be loaded and unloaded while a workpiece is being machined on the other workpiece spindle. This significantly avoids undesirable non-productive time. The concept of such a machine is known, for example, from WO 00 / 035621.

[0082] The machine has a machine control system 700, shown only diagrammatically, which includes a number of control modules 710 and a control panel 720. Each control module 710 controls a machine axis and / or receives signals from sensors.

[0083] [Other changes] The interface between the spindle shaft 322, 332 and the machining tool 100 may be configured differently from the embodiment described above. In particular, different types of conical connections may be used. Any known conical connection may be used, for example, types A, BF, BM, CF or CM as described in DIN ISO 666:2013-12. For further details, reference is made to DIN ISO 666:2013-12 and other standards as described in DIN EN ISO 1119:2012-04, DIN ISO 702-1:2010-04, ISO 12164-1:2001-12 and ISO 12164-2:2001-12.

[0084] As explained above, instead of or in addition to using a machine-readable data carrier, the identification of the hub flange or the tool formed therewith may be performed by other means, for example by mechanical coding, which may be implemented, for example, by one or more notches that allow unique identification of at least the type of hub flange.

[0085] The pull rod 370 may extend through the first spindle shaft 322 rather than through the second spindle shaft 332 and may be connected at its end to the second spindle shaft 332. In this case, the clamping element therefore exerts an axial force on the first spindle shaft in the direction of the second spindle shaft.

[0086] For axial clamping of the machining tool 100 between the first spindle shaft 322 and the second spindle shaft 332, two or more pull rods extending parallel to each other and spaced radially from the tool spindle axis B and positioned at different angular positions relative to the tool spindle axis B may be used instead of or in addition to one central pull rod.

[0087] The fixing and axial clamping of the machining tool 100 between the first and second spindle shafts under pressure may also be achieved in a manner other than by means of a continuous pull rod, for example by means of a clamping system arranged inside the respective spindle shafts. For this purpose, the connection between the machining tool and the spindle shafts may be achieved, for example, by means of a hollow shank taper (HSK) in accordance with ISO 12164-1:2001-12 and ISO 12164-2:2001-12.

[0088] The tool body may be configured differently from the embodiments described above, in particular the tool body may consist of several parts.

[0089] The tool body may be dressable or non-dressable. A non-dressable tool body may, for example, have a metal base with a hard material coating. Such a tool body can, in principle, be attached to the hub flange in the same way as a dressable tool body. However, it is also conceivable to instead manufacture a one-piece tool whose outer contour in the region of the connection point with the tool spindle is formed according to the flange socket 111, 121, and the hard material coating is an integral component of this one-piece tool. In this case, the tool may be identified in the same way as described above for the hub flange, using a machine-readable data carrier and / or by mechanical coding. Such a one-piece tool may be part of a tool family that includes the tools with hub flanges and one-piece tools described above. [Explanation of symbols]

[0090] 100 Grinding Tools 101 Hub flange 110 Fixed flange 111 First flange socket 112 External surface 113 Color 114 Clamping surface 115 Connection Area 116 Center hole 117 Positioning hole 118 accommodation notch 119 Balancing hole 120 Counter flange 121 Second flange socket 122 External surface 123 Color 124 Clamping surface 125 Cap Screw 126 Center hole 127 male thread 130 Whetstone 131,132 Intermediate washer 140 Positioning ring 141 longitudinal groove 142 fixing pin 144 Clamping surface 145 Intermediate Ring 146 Adjusting screw 147 Locating Pin 148 Spring element 150 conical connection 151 Inner cone (tapered socket) 152 Outer cone (tapered) 153 First Planar Contact Surface 154 Second Planar Contact Surface 200 Tool support 210 Z-slide 220 Rotating body 300 Tool Head 310 Base 311 Linear Guide 312 Ball screw drive unit 320 First Spindle Unit 321 First spindle housing 322 First spindle shaft 323 First Spindle Bearing 324 Drive motor 325 First spindle protrusion 326 Guide shoe 330 Second Spindle Unit 321 Second spindle housing 332 Second spindle shaft 333 Second Spindle Bearing 335 Second spindle protrusion 336 Guide shoe 350 First Balancing Unit 360 Second Balancing Unit 370 pull rod 372 Clamp nut 400 rotation turret 500 Workpiece Spindle 510 workpieces 600 Machine Bed 700 Machine Control System 710 Control Module 720 Control Panel X,Y,Z linear axis A Swivel Axis B Tool axis C1,C2 workpiece axis C3 Tower rotation axis

Claims

1. A hub flange (101) for a tool body (130), comprising: a fixing flange (110) defining a tool axis (B) and configured to receive the tool body (130), the fixing flange (110) having a first flange socket (111) formed therein for connection to a first spindle shaft (322) rotatable about the tool axis (B); a counter flange (120) removably connected to the fixed flange; It has The fixing flange (110) and the counter flange (120) are connected to each other via a conical connection (150), the conical connection (150) being arranged coaxially with respect to the tool axis (B) and being formed by an inner cone (151) and an outer cone (152) received in the inner cone (151); A first planar contact surface (153) is formed adjacent to the inner cone (151), and a second planar contact surface (154) facing the first planar contact surface (153) is formed adjacent to the outer cone (152), the first planar contact surface (153) and the second planar contact surface (154) extending perpendicular to the tool axis, and the fixing flange (110) and the counter flange (120) press against each other so that a friction fit is formed between the first planar contact surface (153) and the second planar contact surface (154). A hub flange (101).

2. A hub flange (101) for a tool body (130), a fixing flange (110) defining a tool axis (B) and configured to receive the tool body (130), the fixing flange (110) having a first flange socket (111) formed therein for connection to a first spindle shaft (322) rotatable about the tool axis (B); a counter flange (120) removably connected to the fixed flange; It has The fixing flange (110) and the counter flange (120) are connected to each other via a conical connection (150), the conical connection (150) being arranged coaxially with respect to the tool axis (B) and being formed by an inner cone (151) and an outer cone (152) received in the inner cone (151); The counter flange (120) is formed with a second flange socket (121) for connection to a second spindle shaft (332) rotatable about the tool axis (B). A hub flange characterized by:

3. The hub flange (101) of claim 1 or 2, wherein the inner cone (151) is formed on the fixing flange (110) and the outer cone (152) is formed on the counter flange (120).

4. A hub flange (101) as described in claim 1 or 2, wherein the inner cone (151) is formed on the counter flange (120) and the outer cone (152) is formed on the fixed flange (110).

5. 2. The hub flange (101) according to claim 1, wherein the first planar contact surface (153) is disposed in an area adjacent to the inner cone (151) on a front side opposite to the second planar contact surface (154), and the second planar contact surface (154) is disposed in an area surrounding the outer cone (152).

6. The hub flange (101) according to any one of claims 1 to 5, wherein the conical connection portion (150) has a plurality of axial threads (125) that press the fixing flange (110) and the counter flange (120) together in the axial direction.

7. The hub flange (101) according to any one of claims 1 to 6, wherein the hub flange (101) defines a first clamping surface (114) and a second clamping surface (144) such that the tool body (130) can be axially clamped between the first clamping surface (114) and the second clamping surface (144).

8. A hub flange (101) for a tool body (130), comprising: a fixing flange (110) defining a tool axis (B) and configured to receive the tool body (130), the fixing flange (110) having a first flange socket (111) formed therein for connection to a first spindle shaft (322) rotatable about the tool axis (B); a counter flange (120) removably connected to the fixed flange; It has The fixing flange (110) and the counter flange (120) are connected to each other via a conical connection (150), the conical connection (150) being arranged coaxially with respect to the tool axis (B) and being formed by an inner cone (151) and an outer cone (152) received in the inner cone (151); The fixed flange (110) has a positioning ring (140) having an axially variable position relative to the counter flange (120), a first clamping surface (114) formed on the fixed flange (110) and a second clamping surface (144) formed on the positioning ring (140), and the tool body (130) can be axially clamped between the first clamping surface (114) and the second clamping surface (144). A hub flange (101).

9. 9. The hub flange (101) of claim 8, wherein the counter flange (120) or the fixing flange (110) has external threads (127), the positioning ring (140) has internal threads that are complementary to the external threads, and the screwing action of the positioning ring (140) changes the axial position of the positioning ring (140) relative to the counter flange (120).

10. 10. The hub flange (101) of claim 9, further comprising an intermediate ring (142) disposed axially adjacent to the positioning ring (140) for transmitting an axial clamping force from the positioning ring (140) to the tool body (130).

11. 9. The hub flange (101) of claim 8, wherein the positioning ring (140) is axially displaceable relative to the fixing flange (110) and / or the counter flange (120), and the hub flange (101) has a plurality of threaded elements that are threaded into the counter flange (120) or the positioning ring (140) to change the axial position of the positioning ring (140) relative to the counter flange (120).

12. Hub flange according to any one of claims 1 to 11, wherein the first flange socket (111) is formed as an inner or outer cone with a flat contact surface.

13. Hub flange according to any one of claims 1 to 12, having an axial through-hole (116, 126).

14. A processing tool (100), comprising: A hub flange (101) according to any one of claims 1 to 13; a tool body (130) clamped to the hub flange (101); The machining tool (100) has

15. A tool head (300) for a machine tool, comprising: A machining tool (100) according to claim 14; a first spindle unit (320) having a first spindle shaft (322); a second spindle unit (330) having a second spindle shaft (332); It has The first spindle shaft is attached to the first spindle unit (320) so as to be rotatable about the tool axis (B); The second spindle shaft is attached to the second spindle unit (330) so as to be rotatable about the tool axis (B); the first spindle unit (320) and the second spindle unit (330) are coaxially arranged with respect to each other such that the machining tool (100) is receivable axially between the first spindle shaft (322) and the second spindle shaft (332); Tool head (300).

16. 16. The tool head (300) of claim 15, wherein the machining tool (100) is axially clamped between the first spindle shaft (322) and the second spindle shaft (332) such that an axial compressive force acts on both sides of the machining tool (100).

17. The second spindle shaft (332) and the machining tool (100) each have an axial through-hole; the tool head (300) has a pull rod (370) extending through the axial through-holes of the second spindle shaft (332) and the machining tool (100), the pull rod (370) being connectable at one end to the first spindle shaft (322); the pull rod (370) is connectable at a second end to the second spindle shaft (332) such that an axial compressive force can be exerted on the machining tool (100) between the first spindle shaft (322) and the second spindle shaft (332); The tool head (300) of claim 16.

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