CN1929941B - Vibration-absorbing tool holders - Google Patents

Abstract

The invention relates to a tool holder (10) for a tool that rotates about a rotational axis (D). Said holder comprises a clamping shaft (18), one end of which is provided with a clamping section (14) containing an opening (16) that is concentric with the rotational axis (D) and that receives a retaining shaft of the tool. At least one clamping surface is provided on the peripheral casing of the opening (16) for securing the retaining shaft of the tool in a press fit. According to the invention, an axial section of the tool holder (10) that forms an axial tensioning section (VA) has a tensioning assembly (20), which exerts a tensioning force (Vk) with a tensioning force component (Vk) that acts in the axial direction on the tool holder (10) at least during the operation of the latter (10).

Description

Vibration-absorbing tool holders

technical field

The invention relates to a tool holder for a tool rotatable about an axis of rotation, such as a drilling tool, a milling cutter, a grinding tool or a grinding tool, wherein the tool holder comprises a tensioning shaft at one end thereof The upper region has a clamping structure for concentrically fixing the tool and the other end region has a connecting structure for concentric connection to the machine tool.

Background technique

Such tool holders are generally known, for example, as chucks or clamping spindles in drilling, milling, grinding or grinding machines, ie generally in machine tools with rotating geometrically defined or indefinite cutting edges. The clamping structure can have a receiving opening concentric to the axis of rotation for receiving the fastening shank of the tool. Wherein at least one clamping surface can be provided on the peripheral surface of the receiving hole for fixing the fixing handle of the tool. Known tool holders generally have a certain axial length, which makes them substantially susceptible to externally induced vibrations, which can be excited by various sources.

For example, numerous cutting tools, which are designed to be clamped in such a tool holder, have on their outer surface at least one cutting edge or a number of cutting edges uniformly distributed along its circumference so that as the tool rotates periodically at least one cutting edge cuts into the into the workpiece body to remove chips from it. As such a cutting edge penetrates into the material, a counterforce is associated at the cutting edge, since the cutting edge passes more or less impulsively from an uncut state into a cutting state. The periodicity of such force impacts depends on the number of cutting edges present and the rotational speed of the tool and thus the tool holder. However, other vibrational influences are also known, which arise, for example, from unsuitable cutting speeds for the respective tool, for example due to chatter of the milling cutter.

Due to these influences, torsional vibrations of the tool holder about its ideal axis of rotation and/or transverse vibrations in a plane containing the axis of rotation can be excited. Mixed forms of these vibrations also occur.

Contents of the invention

It is therefore the object of the present invention to provide a tool holder of the type mentioned at the outset, which is generally less susceptible to undesired vibrations than the prior art and thus achieves a correspondingly higher machining accuracy.

This object of the invention is achieved by a tool holder of the type mentioned at the outset, characterized in that a tensioning device is connected to the tensioning shaft, which exerts a tensioning force in an axial tensioning section of the tensioning shaft. On the tensioning shaft, the tensioning force comprises a tensioning force component acting in the axial direction, wherein at least one of the components in the tensioning section, namely the tensioning shaft and the tensioning device, is formed as a sleeve, It surrounds the respective other part concentrically.

According to the invention, the tensioning force can be applied to the tool holder in any direction as long as it has a tensioning force component acting in the axial direction, ie in the direction of the axis of rotation. However, it is understood by a person skilled in the art that the greater the component of the tensioning force acting in the axial direction in the total tensioning force, the greater the effect achievable with the tensioning device according to the invention.

The connection structure can involve any type of conventional tool holder connection such as a steep conical connection shaft or a hollow shaft connection (HSK connection). The clamping structure may also involve any type of tool holder, eg a shrink chuck receiving hole, a tool receiving hole for a cylindrical shank eg Weldon type or Whistle-Notch type including clamping screws. However, spring chucks or so-called universal receptacles or bit receptacles are also suitable.

The axial tension component produces a mechanical axial tension in the axial tension section, which generally changes compared to the mechanically untensioned state and in particular improves the spring properties of the tool holder, especially in the axial section And thus the spring hardness of the tool holder. By applying an axial tensioning force, the spring stiffness of the tool holder can be changed in a targeted manner, in particular increased, and the associated vibration patterns and their associated resonance frequencies can be excited particularly easily at the tool holder. As is generally known, the resonant frequency of a component such as a tool holder is determined by the square root of the quotient of spring stiffness and mass. By means of targeted changes in the spring stiffness, not only the torsional vibration behavior, i.e. the tool holder vibrating about the axis of rotation, but also the transverse vibration behavior, i.e. the tool holder vibrating about an included Vibration in the plane of the axis of rotation. The tool holder is vibratingly offset perpendicular to the axis of rotation. It has also been shown that in the elastic range of the metallic material it is possible in individual cases to increase the damping under high mechanical tension.

The mechanical axial tensioning force applied to the tool holder by the sleeve of the tensioning device can be tension or compression. In this respect, the tensioning section is preferably arranged in the axial direction between the clamping structure and the connecting structure, especially if the clamping structure protrudes beyond the sleeve and forms a shrink-fit fastening for the tool. These measures achieve that the connecting structure and the clamping structure can be designed to be sufficiently rigid and that the clamping structure is, if necessary, accessible to the induction heating device for pressing and releasing the tool.

In a first variant, it is provided that the sleeve can be supported at its ends away from each other in tension on the tool holder and that the tensioning shaft can connect the connecting structure with the clamping structure in a compressive manner.

Alternatively, the sleeve can also be supported at its ends towards one another in a compressive manner on the tool holder, and the tensioning shaft can comprise a shaft section, which connects the connection structure to the clamping structure in a tensionable manner.

Suitable annular shoulders can be provided on the tool holder for tension- or compressive-loaded support of the sleeve. However, the sleeve can also be fixedly connected to the tool holder at one or both ends, for example by welding or soldering. Of course, the sleeve can also be integrated with the connecting structure or/and the clamping structure. A fixed connection of this type results in a durable tool holder that can withstand high loads. In particular, a subsequent fastening can be applied during the tensioning process, for example by welding or the like, which considerably simplifies the construction of the tool holder.

It is expedient if the tool holder is configured such that the tensioning force is variable, so that the tensioning force can be reduced according to the application, ie taking into account the number of cutting edges present on a cutting tool, the rotational speed of the tool holder, etc. required vibration excitation. In order to vary the tensioning force, the sleeve or the bearing path of the shaft section of the tensioning shaft can be actuated via an axial screw connection. Instead of a threaded connection, a press-fit connection can also be provided, which allows axial adjustment by external axial pressure. Finally, hydraulically acting pressure chambers can also be provided in the bearing path. Therein the hydraulic pressure can be adjusted in order to change the tension.

The tensioning shaft and/or the sleeve must be connected in a rotationally fixed manner to the connecting structure and the clamping structure in order to be able to transmit the drive torque of the machine tool to the tool. The tool holder should be resistant to bending relative to its axis of rotation. This can be achieved while having sufficient damping properties in that the sleeve is supported on an annular shoulder of a reinforcing clamping structure of the connecting structure, in particular on a radially protruding annular flange of the connecting structure or in conjunction with the connected by annular shoulders. The annular shoulder reinforces the region of the connection side of the sleeve. Since the outer diameter of the annular shoulder is generally larger than the outer diameter of the clamping structure, the outer diameter and/or inner diameter of the sleeve may increase at its end adjoining the connection structure relative to the other end. The nearly conical sleeve shape obtained in this way improves the bending stiffness of the tool holder.

The shaft section of the tensioning shaft surrounded by the sleeve can likewise have the shape of a sleeve. In particular, the sleeve can also comprise a plurality of sleeve shells, which are arranged concentrically with one another and which can engage one another in a friction-fit manner at least over a section of their axial length. The frictional force thus generated acts dampingly on the resulting vibratory movement. It is also possible for one sleeve shell to be subjected to compressive stress and the other sleeve shell to be subjected to tensile stress, so that the inner sleeve shell simultaneously assumes the function of the shaft section of the tensioning shaft.

Furthermore, the sleeve, but at least one of its sleeve shells, bears against the tool holder in at least one axial end region, preferably in both axial end regions, via the central arrangement of the damping element. The contact engagement again enables microscopic relative movements between the sleeve and the damping element and/or between the damping element and the tool holder, so that undesired relative movements between the tool holder and the sleeve are prevented. This also prevents undesired vibrations from occurring. In addition, the damping element ensures that shocks on the tool holder are damped, such as may arise, for example, from chipped workpiece machining. This is also ineffective beyond the only tight connection of the sleeve to the damping element and/or the damping element to the tool holder.

Alternatively or additionally, however, the tool holder can also be configured such that an annular space is formed radially between the sleeve and the shaft section for a material under pressure, in particular a flowable material or a plastically deformable Or elastic material filled. Preferably, a pressure variation device is provided, by means of which the pressure of the material in the annular space can be varied. The material under pressure not only influences the axial tension, but also increases the damping effect in the case of inner friction. The pressure varying means may be means for varying the volume of the space, for example an adjusting screw deflectable into the volume of the space or/and a plunger deflectable.

The tensioning device described above changes the spring properties and thus the vibration properties of the tool holder which is subjected to not only torsional vibrations but also bending vibrations in operation. In individual cases, changes in the vibration behavior have led to an improvement of the cutting properties of the tool and thus to an improvement of the working life of the tool. However, a considerable improvement in the damping properties of the tool holder can be achieved if the tool holder is equipped with energy-absorbing or energy-dissipating devices. In a preferred embodiment of the invention it is provided that the tension-generating sleeve rests frictionally on the circumference of the tensioning shaft at least over a section of its axial length. The sleeve, which is connected to the tool holder only at its axial ends, moves relative to the tensioning shaft in the event of torsional or bending vibrations of the tensioning shaft and damps these vibrations by its frictional fit. This friction fit can be realized by the interference dimensioning of the circumferential surfaces of the tensioning shaft and the sleeve which abut against each other, for example in one embodiment by the radial excess of the outer diameter of the tensioning shaft relative to the inner diameter of the sleeve. surplus, the sleeve surrounds the tensioning shaft. However, it is also possible to additionally generate the radial force required for the frictional connection, for example by pressing an elastic material between the tensioning shaft and the diametrically opposite peripheral surface of the sleeve.

It has been proved that the frictional fit does not have to extend along the axial full length of the sleeve, rather it is sufficient to limit the frictional fit to a section of the sleeve, especially in the region of an axial end thereof, so that the sleeve's The remaining axial length can be used for elastic axial tensioning. In a preferred, structurally particularly simple embodiment, the last-mentioned principle is also used for the axial support of the sleeve on the tensioning shaft. The sleeve, which is axially biased at its two ends on the tool holder, is fastened to the tensioning shaft in a friction-fit manner, preferably in a friction-fit section, with its end in the axial direction approaching the clamping structure. superior. The axial length of the frictional engagement portion is determined such that it can also withstand the axial biasing force of the sleeve, but its frictional damping properties can be exerted towards the other end of the sleeve.

During installation of the sleeve on the tensioning shaft of the tool holder, the sleeve is biased with pressure, for example in a pressure device, by counteracting a press fit. In order not to have to push the sleeve along the full axial height of the friction fit in press-fit conditions, the sleeve and the tensioning shaft have a cooperating slightly conical shape at least in a part of the friction fit, for example with a slope of about 0.1 . Such a conical shape is self-locking. Of course, the friction fit portion itself may also be formed by the cylindrical surface as long as it satisfies the press-fit condition.

The sleeve thus mounted on the tensioning shaft by pressure bias bears with its other end axially on the annular shoulder of the tool holder, in particular axially on the annular shoulder of the connecting structure. It has proven expedient in this respect to form the sleeve end bearing on the annular shoulder as a conical section which tapers axially away from the annular shoulder and thereby also reinforces the abutment connection of the tensioning shaft. footing.

As already mentioned, the axially pressure-biased sleeve expediently has a radial distance from the tensioning shaft axially between the friction fit part and the other end axially facing the connecting structure, which is supported on the tool holder Extend axially so that the sleeve is movable at its biased portion. At least one damping ring made of elastically compressible material can be arranged between the circumference of the tensioning shaft and the inner surface of the sleeve in the axial direction between the friction fit part and the other end supported on the tool holder, so that the sleeve The barrel area can also be used simultaneously for energy-absorbing vibration damping. For example, such a damping ring can be inserted into the above-mentioned conical part of the sleeve.

In a further preferred embodiment it is provided that the respective axial ends of the sleeve are tension-resistant and tightly connected to the tool holder, in particular friction welded, wherein the sleeve surrounds the tensioning shaft at a radial distance, so that the sleeve An outwardly sealed annular chamber is formed between the barrel and the tensioning shaft. For axial tensioning, a deformable and vibration-energy-absorbing material is introduced into the chamber under pressure, for example, when deformed, which is flowable or deformable at least during the filling process and in this case in the Change its consistency under pressure. For example, flowable rubber compounds vulcanized in the annular chamber are suitable or also hardenable synthetic substances, which age harden in the annular chamber to form a hard elastic annular body. Materials which can be sintered in the annular chamber are also suitable, for example ceramic materials. The aforementioned damping material may contain fillers, which increase the mechanical strength or stiffness of the damping material.

In another variant, which is based on the principle of hydraulic pressure generation for the axial tensioning of the tensioning device, it is provided that the sleeve is axially supported on the tool holder with its two ends, wherein at both ends of the sleeve One of the bearing paths is provided with an axially displaceable bearing device relative to the tool holder, which has at least one bearing plunger in a pressure medium containing a flowable or plastically deformable pressure medium assigned thereto. The pressure chamber is axially displaceably guided, wherein an adjusting element for varying the pressure in the pressure medium is assigned to the pressure chamber. For reasons of space, the pressure chamber is preferably arranged on one side of the connecting structure of the tool holder and can comprise a plurality of axially displaceable plungers distributed in the circumferential direction, which act distributed over the circumference on the adjacent sleeve end . The plungers are expediently arranged in separate pressure chambers which communicate with the pressure medium. Preferably, however, the supporting plunger is an annular plunger concentric to the axis of rotation, which is axially displaceable in an annular space forming the pressure chamber. The annular plunger may be separate from the sleeve, but it may also be integral with the sleeve.

The pressure medium can be hydraulic oil or other incompressible liquids. However, flowable plastic materials are also suitable, for example rubbery or flowable plastics or viscoelastic substances.

The adjusting element can here also be a plunger screw or the like which acts on the pressure medium.

The other of the two ends of the sleeve can be fixedly connected, for example welded or glued, to the tensioning shaft. Preferably, however, a safety ring which is detachably fastened on the tensioning shaft is arranged on the annular flange for supporting the other end of the sleeve. The safety ring may be a nut screwed on the tensioning shaft or a spring ring snapped elastically in the annular groove of the tensioning shaft in the radial direction.

Of course, by suitable selection of the wall thickness of the sleeve, its spring properties can be optimized. The spring properties can also be influenced by a suitable shape of the sleeve. For example, the sleeve comprises an axially elastic wave spring portion.

In order to reduce undesired vibrations, a vibration mass can be arranged on the tool holder, which reduces or even completely eliminates undesired vibrations on the tool holder by means of differentiated resonances. The seismic mass is preferably arranged displaceably in the axial direction on the tool holder, so that its resonance frequency can be adjusted to the resonance frequency of the tool holder. The seismic mass is preferably arranged on the axis of the tool holder, since undesired modes of vibration first develop there. Furthermore, the seismic mass can be contained in the aforementioned sleeve, for example if it surrounds the shaft radially on the outside. This protects the vibrating mass from external influences, such as falling chips and coolant.

In a further preferred embodiment it is provided that the sleeve surrounds the shaft section at a radial distance at least in a section of its axial length to form an annular space and a large The ring-shaped damping element bears in contact with the inner peripheral surface of the sleeve and the outer peripheral surface of the shaft section. Such a damping element ensures a defined frictional lock between itself and the sleeve or shaft section and thus frictional damping. The damping element can consist of a substantially rigid material, but preferably of an elastic or plastic material, so that the internal friction of this material also contributes to vibration damping, although the damping element should be connected to the sleeve and the shaft section in a torsionally fixed manner of the circumferential surface. The damping element can be pressed into the annular space by compression. Preferably, however, the annular space is axially delimited by annular shoulders, between which the damping element is axially clamped in order to produce a radial bias. The biasing of the damping element can be varied by varying the axial spacing of the annular shoulders. For this purpose, for example, one of the annular shoulders can be formed by an axially deflectable screw arrangement fixed on the connecting structure. Preferably, the annular space has a conical shape, so that a change in the radial clamping of the damping element can also be achieved with stiffer materials.

Overall, it has proven to be particularly advantageous if the two parts, tensioning shaft and tensioning device, are made of different materials, since vibrations can be damped better if they have to pass through regions of different materials. One of the parts, in particular the sleeve, expediently consists of hard metal. The cemented carbide is fine-grained, such as type K20, but can also be coarse-grained, such as type K50, since coarser-grained cemented carbide has higher strength and is less brittle. Heavy metals or metal matrix composites (MMC materials) are also suitable, such as ferro-titanium. Furthermore, ceramic materials and plastics, in particular glass-fiber-reinforced plastics or carbon-fibre-reinforced plastics, are also suitable.

In the embodiments described above, the two parts, ie the tensioning shaft and the tensioning device, are joined together in one piece by welding, if necessary. However, embodiments have also proven to be particularly advantageous in that one of the two parts, the tensioning shaft and the tensioning device, is supported on the other of the two parts via at least one axial tension-transmitting seam. The individual seams have different force-transmitting properties according to whether the surfaces which abut them against each other are subjected to tension or pressure, and thus ensure a reduction in vibrations due to this asymmetry of the force transmission. The seams can be arranged here between two radially press-fitting circumferential surfaces of the two parts which abut one another and/or between two axially abutting surfaces of the two parts. A layer of damping material can optionally be arranged between the two surfaces forming the joint.

In order to reduce vibrations it has proven to be important that the two parts are aligned radially relative to one another in the region of the joint, wherein preferably there should be a certain light press fit between the circumferential surfaces of the respective pair. At least one of the two axial ends of the parts constituting the sleeve should form one of the surfaces that abut against each other, and on the other of the two parts, a peripheral surface is suitably formed or provided with an inner diameter in the region of the end. to the centering sleeve. Expediently, the ends of the sleeve are radially centered in this way.

The sleeve may be centered on its radially inner circumferential surface. In particular, however, the axial end face of the sleeve adjoining the clamping structure is expediently centered on its radially outer circumferential surface, since in this case the thermal expansion of the clamping structure does not exert pressure on the sleeve end. Particularly in the construction of shrink chucks, expansion of the sleeve end due to the thermally expanding shrink chuck can lead to damage to the sleeve, especially when it consists of a brittle material such as ceramic or the like. The end of the sleeve adjoining the connecting structure is expediently also centered on its outer circumferential surface, since in this way, for example, opening forces which may arise due to the conical shape of the sleeve can be absorbed by the centering on the outside.

The outer centering peripheral surface can be integrally formed on the part surrounding the sleeve from the outside. However, the precise production of the inner fit of the component is complex due to the undercut present there. For simpler production, in one embodiment in the region of at least one end of the sleeve, in particular in the region of its end adjoining the clamping structure, the other radial outer surface of the two parts surrounds the circumferential surface of the sleeve. It consists of a ring which covers the seam axially and which also surrounds the other part radially on the outside. The inner mating surface of such a ring can be produced relatively simply.

Description of drawings

Exemplary embodiments of the invention are described in more detail below with reference to the drawings. in:

Figures 1 to 7 are axial longitudinal sections of a vibration-damping tool holder, including a sleeve tensioned in tension in the axial direction;

Figures 8 to 13 are axial longitudinal sections of a vibration-damping tool holder, including a sleeve tensioned axially under pressure;

Figures 14 and 15 are axial longitudinal sections of a damped tool holder including a damping mass;

Figure 16 includes an axial longitudinal section of a tool holder with adjustable damping;

Figures 17 and 18 are axial longitudinal sections of various versions of the tool holder including a pressure biased sleeve;

Figures 19 and 20 are axial longitudinal sections of various versions of the tool holder including the sleeve under tension;

FIG. 21 is an axial longitudinal sectional view of a tool holder including electrically controllable damping;

Figures 22 to 26 include axial longitudinal sections of a friction-lock damped tool holder;

Figures 27 and 28 include axial longitudinal sections of a tool holder with adjustable damping;

Figures 29 and 30 include axial longitudinal sections of the tool holder with the damping element installed;

Figures 31 to 33 are axial longitudinal sections of a tool holder with damping properties.

Detailed ways

A first embodiment of the tool holder according to the invention is generally designated 10 in FIG. 1 . The tool holder 10 has, in the region of its left end in FIG. 1 , a connecting structure 12 for connecting the tool holder 10 to a machine tool, not shown, in a manner known per se. The torque transmission from the rotary drive of the machine tool to the tool holder 10 takes place via a connection 12 connected to the machine tool.

At its longitudinal end opposite the connecting structure 12 , the tool holder 10 has a clamping structure 14 which has a cylindrical clamping hole 16 in the example shown. The shank of the tool is inserted therein and can be clamped there. The example shown in FIG. 1 is a tool holder 10 for shrink clamping. For this purpose, the clamping structure 14 is heated on its outer circumferential surface 15 in the region of the clamping hole 16 , so that the clamping structure expands thermally and the diameter of the clamping hole 16 becomes larger. In this heated state, the shank of a tool is inserted into the clamping hole 16, and the tool holder 10 is subsequently cooled or self-cooled in the region of the clamping structure, so that the cooling-induced tension between the tool shank and the clamping structure 14 With the contraction of the clamping structure 14 , the tool shank is fixed in the clamping hole 16 with a press fit. Such tool holders are generally known in the prior art.

The tool holder 10 is rotatable about an axis of rotation D and is also substantially symmetrical about the axis of rotation D. As shown in FIG. All directional statements referring to an axis in this application refer to the axis D of rotation. This applies to the axial direction, the circumferential direction and the radial direction.

In an axial shaft section 18 between connecting structure 12 and clamping structure 14 , tool holder 10 is surrounded concentrically by a sleeve 20 . The sleeve 20 is supported on the tool holder 10 at two bearing points 22 and 24 which are spaced apart from each other in the axial direction. The support point 22 in FIG. 1 is the support point close to the connection structure 12 , while the support point 24 is close to the clamping structure 14 . Bearing points 22 and 24 extend around tool holder 10 . At its longitudinal end 26 on the right in FIG. 1 , the sleeve 20 has a circumferential radial projection 28 which protrudes radially inwards from the sleeve body 27 .

The radial protrusion 28 engages along the circumference of the tool holder 10 with a shoulder or flange 30 extending around the tool holder 10 from the substantially cylindrical shaft outer surface 28 of the shaft section 18 toward the radially outward. The bearing surface 31 of the radial projection 28 of the sleeve 20 , which is oriented substantially perpendicularly to the axis of rotation D and which in the assembled state of the sleeve 20 points towards the connecting structure 12 , bears relatively precisely against the surrounding flange 30 is also substantially Perpendicular to the axis of rotation D, the end face 33 of the clamping structure 14 is directed. Via the contact of the surfaces 31 and 33 forming a joint, a tensioning force VK acting in the axial direction and directed towards the connecting structure 12 can be transmitted to the tool holder 10 at the bearing point 24 .

At its longitudinal end 32 close to the connecting structure 12 , the sleeve 20 has a radial flange 34 extending radially outward. The radial flange 34 is provided with a plurality of through holes 36 arranged at equiangular intervals along the circumferential direction. Screws 38 are inserted through these through-holes 36 , the heads of which rest on a bearing surface 39 of the radial flange 34 that is substantially perpendicular to the axis of rotation D and points toward the other longitudinal end 26 .

The screws 38 are screwed into the tool holder 10 with internal threads in blind holes 40 assigned to the through-holes 36 .

Through the tightening of the screws 38 and their support on the radial flange 34 of the sleeve 20 , a force acting in the axial direction and directed towards the clamping structure 14 can be transmitted at the support point 22 via the internal thread of the blind hole 40 . The tension VK. The value of the tensioning force VK can be adjusted by selecting the tightening torque of the screw 38 . To this end, the bearing surface 41 of the annular flange 43 protruding radially from the connection structure 12 is substantially perpendicular to the axis of rotation D and directed to the clamping structure 14 , and the radial flange 34 of the sleeve 20 is also perpendicular to the rotation axis. A gap is left between the end faces 45 of the axis D and pointing toward the connecting structure 12 .

But according to a kind of embodiment of the present invention in order to adjust predetermined tensioning force conveniently, see under the unassembled state of sleeve, can be arranged to make the axial spacing between them greater than in The axial distance between the corresponding bearing surfaces of the sleeve assigned to the two bearing surfaces. In the example of FIG. 1 , the axial spacing between the bearing surfaces 33 and 41 is greater than the spacing of the corresponding bearing surfaces 31 and 45 by approximately 0.3 to 0.5 mm. In this case the screw 38 is simply tightened until the surfaces 41 and 45 abut each other. Due to the material extension of the reaching sleeve, a predetermined tensioning force is exerted on the tensioning section VA.

The above-mentioned tension force VK generated on the support point 24 is the supporting reaction force of the tension force VK caused by tightening the screw 38, so the tension force VK generated on each corresponding support point is equal in magnitude and opposite in value. Directed. The stretched section VA between the bearing points 22 and 24 is therefore under increased axial compressive stress. The increased axial compressive stress acting in the tension section VA is higher than the axial tension load in the axial section of the tool holder 10 which adjoins this tension section in the axial direction. The axial compressive stresses increased by this section VA change the spring stiffness of the tool holder 10 relative to an untensioned state, so that with the changed spring stiffness also changes the forms of vibrations that can be excited particularly easily on the tool holder 10 and their associated Resonance frequency. This applies both to the resonant frequencies of torsional vibrations about the axis of rotation D which are likely to be excited in the tool holder 10 , and also to the resonant frequencies of transverse vibrations in a plane containing the axis of rotation D. FIG. Therefore, the spring stiffness of the tool holder 10 can be influenced by the components forming the tensioning device, namely the sleeve 20 and the screw 38, so that during operation of the tool holder 10, for example, in the known cutting process of a tool clamped to the tool holder 10 Undesirable vibrations are more difficult to excite or occur with less probability at higher rotational speeds and given operating rotational speeds of the tool holder 10 . Ultimately, the machining accuracy achievable with the tool holder 10 and the tool life are thus increased.

Components that are the same in FIG. 2 and in all subsequent figures are always provided with the same designation and are identified by at least one letter. Each component is only described in detail in connection with the figure in which it first appears. With regard to these components, reference is especially made to their description in the figures in which they first appear. The features of the tool holders shown in the individual figures can be combined with one another as desired in this respect.

The embodiment of FIG. 2 corresponds substantially to that of FIG. 1 . Only the screws 38a in the embodiment shown in FIG. 2 are inserted into the tool holder 10a through the through-holes 36a and are screwed into the radial flange 34a in the holes 40a with an internal thread.

The longitudinal axis of each screw 38 a is inclined relative to the axis D of rotation. The screws 38 a are arranged such that their elongated imaginary longitudinal axes intersect the axis of rotation D ideally at one point. As a result, a force F acting in the direction of its longitudinal axis is transmitted by the screw 38a to the tool holder 10a, this force F now having a tension component VK in the axial direction and a force component VR in the radial direction . The tensioning component VK, which causes a corresponding bearing counterforce at the bearing point 24a, again subjects the tensioning section VA of the tool holder 10a to an axial compressive stress with the above-described effect.

FIG. 3 shows a tool holder 10b which differs from the tool holder of FIGS. 1 and 2 mainly in that the sleeve body 27b is substantially conical and is integrally integrated at the bearing point 22b at the end with a larger diameter. Ground to the bearing surface 41b of the annular flange 43b of the connecting structure 12b. The sleeve 20b that tapers towards the clamping structure 14b improves the bending stiffness of the tool holder 10b. The shaft part 29b is formed in one piece with the clamping structure 14b and the flange 30b and is inserted axially into the sleeve 20b through a cylindrical bore 47 in the region of the annular flange 43b of the connecting structure 12b. The inner diameter of the hole 47 is therefore slightly larger than the outer diameter of the flange 30b. The shaft portion 29b is provided at one end adjacent to the connecting structure 12b with a press fit surface 49 which is secured in the bore 47 with a radial press fit. The fit is chosen such that the press fit can withstand the axial biasing force VK of the sleeve 20b being pulled.

FIG. 4 shows a tool holder 10c which differs from the tool holder 10b of FIG. 3 mainly in that instead of a press fit 49 fixed in a bore 47 with a press fit and a frictional fit, the bore is formed as a threaded bore 47c, in which In this case, an external thread 49c is axially screwed in a positive fit, which is formed on the end of the shaft part 29c adjoining the connecting structure 12c. The tension acting axially on the sleeve 20c is adjusted by twisting the shaft portion 29c.

The tool holder 10d shown in FIG. 5 is not suitable for the retraction clamping of tool holders, but a plurality of elastic clamping segments 42 are provided on its clamping structure 14d, which are formed in one piece with the tool holder shaft 18d. The clamping segments 42 can be deflected toward the axis of rotation D by bending against the elasticity of their material. The bending force required for clamping the tool shank in the clamping hole 16d is applied via a clamping sleeve 20d. For this purpose, the outer circumference 15d of the clamping structure of the tool holder 10d is formed conically taperingly towards the longitudinal end near the clamping structure of the tool holder 10d. A surface normal N of the frustoconical outer surface 15d of the clamping structure 14d thus has a component in the direction of the axis of rotation D and a component in the radial direction.

A longitudinal end 26d of the locking sleeve 20d in the vicinity of its clamping structure has a conical inner surface 31d. The conical inner surface 31d has substantially the same slope as the conical outer surface 15d. The conical inner surface 31d therefore also points at least in the axial direction. Due to their conicity the surfaces (in the assembled state of the locking sleeve 20d) point on the one hand in exactly the radial direction towards the axis of rotation D and on the other hand in the exactly axial direction towards the connecting structure 12d . The mutual large-area contact of the surfaces 15d and 31d thus forms the bearing point 24d in the vicinity of the clamping structure.

In the axial direction away from the clamping structure 14d, close to the connecting structure 12d, an external thread 44 is provided on the outer circumference 29d of the shaft section 18d. An internal thread 46 on the longitudinal end 32d of the locking sleeve 20d engages with this external thread 44 . The threaded engagement of the external thread 44 of the tool holder 10d with the internal thread 46 of the locking sleeve 20d forms the bearing point 22d in the vicinity of the connecting structure. On the one hand, the tightening of the locking sleeve 20d on the tool holder 10d transmits the required tensioning force in the radial direction to the respective clamping sectors 42 and generates an axial tensioning component VK, which in the tool holder 10d An axial pressure clamping is caused in tensioning section VA.

For better centering of the locking sleeve 20d, a circumferential radial flange 48 is formed on it in the axial direction between the bearing points 22d and 24d, which protrudes radially inwards and lies in contact over a large area. The outer surface 29d of the shaft section 18d of the tightening tool holder 10d.

FIG. 6 again shows a tool holder 10 e , which includes a clamping structure 14 e for the shrink clamping of a tool shank, as already in FIGS. 1 and 2 . It is therefore not necessary to exert a force in the radial direction on the clamping structure 14e by the locking sleeve 20e. The locking sleeve 20e is therefore not configured to come into contact with a conical outer surface. Rather, the locking sleeve 20e has a radial projection 28e on its longitudinal end 26e assigned to the clamping structure 14e, which, in the assembled state of the locking sleeve 20e, points toward the connection structure 12e and is perpendicular to the The bearing surface 31 e on the axis of rotation D bears against an end surface 50 of the tool holder 10 e which is likewise substantially perpendicular to the axis D of rotation. The supporting engagement of surfaces 31e and 50 forms a supporting point 24e. The other bearing point 22e, as in FIG. 5, is formed by the threaded engagement of the external thread 44e of the tool holder 10e with the internal thread 46e of the locking sleeve 20e.

In the embodiment shown in FIGS. 5 and 6 , the clamping structures 14 d and 14 e are located at least partially in the tensioning section VA.

The embodiment of the tool holder 10f shown in FIG. 7 is basically a combination of the embodiments of FIG. 6 and FIGS. 1 and 2: the support point 22f near the connection structure, as in FIG. It is formed by thread engagement with the internal thread 46f of a sleeve 20f.

Conversely, according to the embodiment of FIGS. 1 and 2 , a bearing point 24f near the clamping structure is formed. For a more detailed description of the embodiment of bearing points 22 f and 24 f , reference is especially made to the description of FIGS. 1 and 2 or 6 .

A recess 51 for engaging a tool is formed in the region of the bearing point 22f which, together with the bearing point 24f, generates a tensioning force which causes an axial tensioning of the tensioning section VA of the tool holder 10f. As a result, the tension applied to the tool holder 10f can be adjusted very precisely.

FIG. 8 shows the bearing engagement of the sleeve 20g at its longitudinal end 32g close to the connecting structure 12g on the tool holder 10g. A surface 45g of the radial flange 34g which is perpendicular to the axis of rotation D bears on a surface 41g which is perpendicular to the axis of rotation D of the connecting structure 12g of the tool holder 10g. Furthermore, the bearing surface 45g adjacent to the connecting structure 12g forms a centering collar 52 on the tool holder 10g which surrounds the radial collar 34g radially outwardly. This centering flange 52 ensures a precise concentric position of the sleeve 20g with respect to the tool holder 10g. A radially inwardly directed centering surface 53 of the centering flange 52 engages in bearing engagement with a radially outwardly directed surface 54 of the radial flange 34 g. In order to prevent the sleeve from shifting at the bearing point 22g formed in this way, the radial flange 34g and the centering flange 52 are non-detachably connected to each other by a weld seam 55 around the tool holder.

At the support point 24g, an external thread 44g is provided on the outer surface 29g of the shaft section 18g of the tool holder 10g, on which an adjusting nut 56g is screwed. The adjusting nut 56g presses in the direction of the axis of rotation D against an end face 57 of the sleeve 20g that is substantially perpendicular to the axis of rotation D. As shown in FIG. The pressure applied to the sleeve 20g can be adjusted by adjusting the selection of the tightening torque of the nut 56 . The clamping section VA of the tool holder 10g can thus be subjected to axial tensile stress in a targeted manner. The compressive force acting on the sleeve 20g acts as a counter-tensioning force on the tool holder 10g in the tensioning section VA.

In the tool holder 10g in FIG. 8, the connecting structure 12g, the clamping structure 14g and the shaft section 18g are combined to form one piece.

FIG. 9 shows a tool holder 10h, which differs from the tool holder 10g in FIG. 8 mainly in that the shaft section 18h, which is formed in one piece with the clamping structure 14h, passes axially through the central hole 47h of the connection structure 12h and in the axial direction The side remote from the clamping structure 14h supports a nut 56h. It is screwed onto the external thread 44h of the shaft section 18h. An axial tension can be exerted on the conical sleeve 20h here by means of the nut 56h. The sleeve 20h is clamped between radially extending annular end faces of bearing points 22h and 24h, each configured as a seam.

FIG. 10 shows a two-piece tool holder 10i. The tool holder 10i comprises a connection-side tool holder part 60, on which the connection structure 12i is arranged, and a clamping-side tool holder part 58, on which the clamping structure 14i is arranged. The two tool holder parts 58 and 60 are screwed together, here analogously to the solution in FIG. Threaded hole 47i on part 60.

Tool holder portions 58 and 60 are screwed against a conical sleeve 20i that tapers toward the clamping structure. The sleeve 20i rests with a front end face 61 perpendicular to the axis of rotation D against the bearing surface of the clamping structure 14i, which is likewise perpendicular to the axis of rotation D, forming a seam. A corresponding seam is provided between the surfaces 41i and 45i on the side of the sleeve 20i facing the connection structure 12i in the direction of tension. The longitudinal end 32i of the sleeve 20i in the vicinity of the connecting structure surrounds a flange 52i on the connecting structure 12i radially on the outside and is thereby centered with respect to the axis of rotation D. As shown in FIG. The longitudinal end 26i of the sleeve in the vicinity of its clamping structure is centered with its inner circumference with respect to the axis of rotation D by the tool holder part 58, wherein the front of the longitudinal end 26i of the sleeve 20i in the vicinity of the clamping structure bears against a damping ring 59 arranged in the axial direction between the front longitudinal end 26i of the sleeve 20i and the tool holder portion 58 comprising the clamping structure 14i. The damping ring 59 can be produced, for example, from ceramic and have a different material elasticity than the tool holder 10i and/and than the sleeve 20i. The damping ring 59 dampens undesired movements of the tool holder 10i by means of internal friction.

In the embodiment shown in FIG. 10 , due to the screwed connection of the tool holder parts 58 and 60 , the sleeve 20 i is under compressive stress in the axial direction, so that the clamping section VA of the tool holder 10 i is under mechanical tensile stress. The value of this tensile stress can be suitably selected by applying a certain torque when the two tool holder parts 58 and 60 are screwed together. An additional fine-tuning required axial tensioning possibility consists in the use of very small pitch threads on the journal 49i and on the bore 47i.

Also shown in FIG. 11 is a two-piece tool holder 10k comprising tool holder portions 58k and 60k. Unlike in FIG. 10, tool holder portions 58k and 60k are not threaded to each other. Rather, the journal 49k of the tool holder part 58k is only inserted into the bore 47k of the tool holder part 60k.

During the production of the tool holder 10k, a pressure is applied to it after the two tool holder parts 58k and 60k have been plugged together, so that its length is shortened under the action of the pressure according to the corresponding material elasticity. In this case, the tool holder 10k can be shortened until the end faces 45k, 61k of the sleeve 20k rest against correspondingly configured corresponding surfaces on the tool holder part 60k or 58k. The sleeve 20k is then non-detachably connected at its two longitudinal ends 26k and 32k to the corresponding tool holder portions 58k and 60k by welding. This is achieved by applying a circumferential weld seam 62 on the longitudinal end 32k near the connecting structure of the sleeve 20k and a circumferential weld seam 63 on the longitudinal end 26k near the clamping structure of the sleeve 20k. After application of the weld seam, the axial assembly pressure load on the tool holder is removed, for example by means of a press or clamping device, so that the material elasticity of the previously shortened tool holder 10 k relative to the sleeve 20 k relaxes. At the same time the sleeve 20k is under tensile stress, so that the axially tensioned section between the weld seams 62 and 62 is under compressive stress.

The embodiment of FIG. 12 corresponds substantially to that of FIG. 10 . Only the longitudinal end 321 of the sleeve 201 near the connecting structure is no longer centered by the flange 521 along its outer or inner circumference. Rather, the longitudinal end 32l of the sleeve 20l and the end face of the flange 52l abut one another at the front. During assembly, centering can be achieved, for example, by a connection point of the outer sleeve engaging all around between the flange 52l and the longitudinal end 32l. For better centering of the longitudinal end 32l of the sleeve 20l in the vicinity of the connecting structure, this longitudinal end can also be formed stepped, so that the flange 52l engages around the radially outer circumference of the longitudinal end of the sleeve 20l An axial protrusion on 32l and so that the sleeve is centered on its longitudinal end 32l.

The embodiment shown in FIG. 13 corresponds in its tensioned state to the embodiment of FIG. 12 described above. In addition, a seismic mass 64 is arranged on the outer surface 29 m, as indicated by the double arrow P, which is movable in the axial direction.

The vibrating mass 64 is additionally axially tensioned against undesired vibrational excitation of the tool holder 10m. This applies not only to torsional vibrations but also to transverse vibrations. If the tool holder 10m is excited to vibrate, this also sets the elongated shaft section 18m into motion. By suitable selection of the axial placement position of the seismic mass 64 it can be achieved that the seismic mass and the shaft section 18m supporting it are excited with vibrations which are phase-shifted at the same frequency, so that the overall system of the tool holder 10m due to the differentiation The interference occurs with a total vibration of smaller or even vanishing amplitude.

The seismic mass 64 is arranged on the shaft section 18m in such a way that it can be moved, twisted, screwed, etc. The seismic mass 64 is formed as a simple ring, through which the shaft section 18m passes through its bore 65 . For the fixation of the axial position of the seismic mass 64 on the shaft section 18 m, it is additionally secured in the radial direction, for example by means of pins.

FIG. 14 shows a tool holder 10n which essentially corresponds to the tool holder 10b of FIG. 3 , but which, like the tool holder 10m of FIG. 13 , again supports an axially displaceable seismic mass 64n on its shaft section 18n. The vibration mass 64n also acts as a damping mass to reduce vibration amplitudes within the working range of the tool holder 10n.

The embodiment of FIG. 15 differs from FIG. 13 primarily in that the tool holder part 58o including the clamping structure 14o is only connected via the sleeve 20o to the tool holder part 60o including the connecting structure 12o. The shaft section 18o formed integrally on the tool holder part 58o does not extend with its free longitudinal end to the tool holder part 60o, but ends freely projecting in the space enclosed by the sleeve 20o.

The embodiment of FIG. 15 then differs from FIG. 13 in that the sleeve 20 o is formed by two sleeve shells 67 and 68 arranged concentrically across a large common axial section.

The freely protruding longitudinal ends of the shaft section 18o allow vibrations to be excited differently from the shaft 18o clamped on both sides in the embodiment of FIG. 13 .

In the embodiment of FIG. 15 the axial tensioning is achieved by tensioning the two sleeve shells 67 and 68 relative to each other. Each sleeve shell 67 and 68 is individually welded at each of its longitudinal ends to the tool holder portions 58o and 60o provided for these longitudinal ends. The centering is achieved, for example, in that the circumferential flange 52o on the tool holder part 60o surrounds the sleeve housing 68 on the outer peripheral surface of the radially inner sleeve housing 68, so that the sleeve housing 68 is aligned with respect to the tool holder part 60o. Alignment. The radially inner sleeve shell 68 in turn surrounds a step 69 of the tool holder part 58 o radially on the outside, so that this step is centered by the inner sleeve shell 68 . The connection of the socket housing 68 to the respective tool holder parts 58o and 60o substantially corresponds to the connection of the socket 20k in the embodiment of FIG.

After mounting the inner sleeve shell 68 , the tool holder 10 o is pressed in the axial direction, as described in connection with the embodiment of FIG. 11 , so that the axial length of the tool holder 10 o is shortened. In this shortened state by the external force, the outer sleeve shell 67 is non-detachably connected to the corresponding tool holder parts 58o and 60o by welding. The axial pressure applied from the outside is subsequently relieved, so that the inner sleeve shell is under axial compressive stress and the outer sleeve shell is under axial tensile stress.

In FIG. 16 , as already in FIGS. 1 , 2 and 5 to 7 , a one-piece tool holder 10 p is shown. A conical sleeve 20p which surrounds the tool holder 10p radially on the outside is welded to the tool holder 10p at the radially outer end of the radial flange 34p on its longitudinal end 32p. Likewise the sleeve 20p is welded to the tool holder 10p at its longitudinal end 26p facing the clamping structure 14p, as shown in the upper half of the tool holder 10p shown in FIG. 16 .

The axial portion of the tool holder 10p surrounded by the sleeve 20p is provided with a circumferential groove along a predetermined axial portion, so that the tool holder 10p together with the sleeve 20p defines a volume 66, in the example of FIG. Oil 70 is injected such that the entire volume 66 is filled with oil 70 .

As the tool holder 10p rotates, the oil 70 exerts a radially outward force on the inner wall of the sleeve 20p due to centrifugal force. Due to the taper of the sleeve 20p and its fixed clamping on the longitudinal ends 26p and 32p, this radially outwardly acting force causes a force acting in the axial direction on the sleeve so that the tensioning section of the tool holder 10p under mechanical compressive stress.

Instead of being welded, the conical sleeve in the region of its longitudinal end 26p in the vicinity of its clamping structure rests only largely with its conical inner surface 71 on the corresponding conical outer surface 29p of the shaft section 18p, as shown in FIG. 16 The lower half of the tool holder 10p is shown. The force acting on the sleeve 20p in the radial direction during the rotation of the tool holder causes a force component extending in the direction of the sleeve wall and directed towards the connection structure 12p, whereby the region of the longitudinal end 26p is directed towards the connection structure. The 12p side shifts slightly. This causes the conical inner surface 71 of the sleeve 20p and the conical outer surface 29p of the shaft section 18p to come into close contact with each other.

In addition, a pressure device 72 is provided on the radial flange 34p, comprising a surrounding rubber ring 74 whose radial inner surface is in wetting contact with the oil 70, and a circumferential rubber ring 74 which is equidistantly distributed around the circumference of the radial flange 34. A plurality of adjustment screws 76. The rubber ring 74 can be moved radially inwards into the volume 66 by means of an adjusting screw 76 . This increases the pressure in the oil 70 , which, via the force action of the oil 70 on the sleeve 20 p , leads to an additional axial tensioning of the tool holder 10 p. Instead of a surrounding rubber ring, plungers made of ceramic, metal or the like may also be provided respectively assigned to the adjusting screws, which directly displace the oil 70 .

In the embodiment shown in FIG. 17 , the sleeve 20 q which surrounds the tool holder 10 q on the radially outer side extends beyond the clamping structure 14 q in the axial direction.

At its longitudinal end 32q close to the connecting structure 12q , the sleeve 20q rests with its end face 45q substantially perpendicular to the axis of rotation D against a bearing surface 41q also substantially perpendicular to the axis of rotation.

The clamping structure 14q has an internal thread formed in the inner wall defining the clamping hole 16q. The external thread 78 of a milling head 80 is screwed into the internal thread of the clamping structure. The longitudinal end 26q of the sleeve 20q assigned to the clamping structure 14q bears with its end face 16q substantially perpendicular to the axis of rotation D on the rear face 79 of the milling head 80 which is also substantially perpendicular to the axis D of rotation. By screwing the milling head 80 into the clamping hole 16q and abutting against the outer sleeve 20q, the outer sleeve 20q is under compressive stress, while the tension section VA of the tool holder 10q surrounded by the outer sleeve is under tensile stress. Instead of a milling head 80 any other tool with a clamping thread can be screwed into the clamping hole 16q.

FIG. 18 shows an embodiment which essentially corresponds to that of FIG. 17 . In this case, instead of the milling head 80 , a shrink sleeve 80r is screwed against the sleeve 20r into the clamping hole 16r. The shrink sleeve 80r again has a clamping hole 16'r, into which a tool shank can be clamped, as described in conjunction with the clamping arrangement 14 of the embodiment of FIG. 1 .

In the tool holders of Figures 1, 2 and 5 to 8, the shaft section is combined with the clamping structure and the connecting structure in one piece. Figure 19 shows a tool holder 10s in which the sleeve 20s is formed in one piece in combination with the connecting structure 12s and the clamping structure 14s. The sleeve 20s has a conical shape and turns at its larger diameter end 32s into the end face 41s of the radially protruding flange 43s of the connection structure 12s. At its end facing the end 26s of the sleeve 20s, the clamping structure 14s has a vertical bearing surface 81 which forms the bearing point 24s and rests against the end face of the shaft section 18s which adjoins the clamping structure 14s. The end 49s of the shaft section 18s adjoining the connecting structure 12s is radially introduced and fixed in the bore 47s. This fixing can be achieved by a press fit similar to the tool clamp of FIG. 3 , by a threaded connection similar to the tool clamp of FIG. 4 or by a circular weld 83 . The shaft section 18s is secured under applied pressure so that the sleeve 20s is biased in tension.

FIG. 20 shows a variant of the tool holder of FIG. 19 . Here too, the sleeve 20t is connected in one piece with the connecting structure 12t and the clamping structure 14t and encloses a separate shaft section 18t via which the sleeve 20t can be tensioned. In this case, the sleeve-shaped shaft section 18 t is arranged at its longitudinal end 26 t close to the clamping structure 14 t via a compensating element 82 , which bears against a projection 84 of the clamping structure 14 t .

A clamping element 85 is screwed into the tool holder 10t from the side of the connecting structure 12t. The external thread on the clamping element 85 engages with the internal thread in the connecting structure 12t of the tool holder 10t. A damping element 59t described above with reference to FIG. 10 is arranged axially centrally between the clamping element 85 and the longitudinal end 32t of the shaft section 18t facing the connection structure 12t . A compensating element 82 is also used to prevent the passage of heat from the shrink clamping structure 14t, but this compensating element can be omitted.

The shaft section 18t is hollow for the passage of cooling fluid and has an axially adjustable stop device 86 at its longitudinal end 26t, which forms a stop for a tool shank to be inserted into the clamping hole 16t. Axial end stop. Such a stop arrangement can also be provided in the other described embodiments.

FIG. 21 shows a tool holder 10u on which a material different from the material of the tool holder 10u is sleeve-shaped, preferably shrink-fitted, on its longitudinal end region from the connection structure 12u to the vicinity of its clamping structure. 87. Axial tensioning of the axial section 18u of the tool holder 10u is thereby also achieved. The material may be metal, ceramic or an electrostrictive material which changes its longitudinal dimension in at least one spatial direction by applying an electrical voltage. It is thus possible to vary the force exerted by it on the tool holder 10u by applying a voltage to the mounted material.

FIG. 22 shows a tool holder 10v of the retraction clamp type comprising a tensioning shaft 18v, which protrudes axially at one end from an axially perpendicular shoulder 88v formed by a connecting structure 12v and along the edge of its clamping structure 14v. The side axially remote from the connecting structure 12v includes a central clamping hole 16v for the shrink clamping of a tool shank (not shown in greater detail), as explained in greater detail with reference to FIG. 1 . Between the connection structure 12v and the clamping structure 14v, the tensioning shaft 18v is surrounded by a sleeve 20v forming a tensioning device, which is axially supported at a bearing point 22v with its end adjoining the connection structure 12v on a support point 22v. On the annular end face 88 . The sleeve 20v is mounted by its other bearing end 24v axially adjoining the clamping structure 14v in a friction fit region 89 on the circumference of the shaft section 18v in a force-fit manner. The sleeve 20v extends axially between the friction-locking region 89 and the support point 22v, while being spaced radially from the shaft section 18v to form an annular gap 90 . The inner surface of the inner surface of the sleeve 20v and the inner surface of the shaft section 18v on the inner surface of the sleeve 20v and the inner surface of the shaft section 18v in the friction fit portion 89 have a steep conical shape 91, which is divided by about 0.1 along the predetermined axial length. The slope of the shaft tapers axially toward the clamping structure 14v and gives the cone of the shaft section 18v an interference relative to the end position of the mounted sleeve 20v in order to produce an interference fit. Of course, the surfaces that abut one another in the frictional fit 89 can also be designed as cylindrical surfaces. To generate the prestressing force, the front face 92 of the sleeve facing the clamping structure 14v is pressed against the annular surface 41v with a force of several tons, for example 10 tons, which results in an elastic tension of the sleeve 20v. The press fit generally produces a securing force in the region 89 which holds the thus prestressed sleeve 20v in its prestressed position. At the same time, however, a relative movement between the sleeve 20v and the tensioning shaft 18v is permitted against the frictional locking force in the region of the frictional engagement portion 89 facing the connection structure 12v in the axial direction, whereby torsional vibrations and bending of the shaft section 18v are suppressed vibration.

In order to improve the rigidity of the shaft section 18v, the end region of the sleeve 20v adjacent to the connection structure 12v is formed as a conical portion 93 tapering towards the clamping structure 14v, covered with a hard elastic material surrounding the tensioning shaft 18v. Made damping ring 94.

FIG. 23 shows a variant of a retractable tool holder 10w, which differs from the solution of FIG. 22 only in that the frictional fit part 89w is first dimensioned for the frictional damping of the tool holder 10w, in which the shaft The section 18w has a radial interference with respect to the inner diameter of the sleeve 20w, while the bearing point 24w is formed by a nut 95 at which the sleeve 20w is supported with a pretension force FK, which is screwed to the external thread of the tensioning shaft 18w superior. Here again the biasing force clamping the sleeve between its bearing points 22w and 24w is several tons, eg 10 tons. Furthermore, the shape of the sleeve 20w corresponds to the shape of the sleeve 20v in FIG. 22 , but in addition a further damping ring 96 is provided between the sleeve 20w and the tensioning shaft 18w in the region of the end facing the clamping structure 14w.

The difference between the embodiment according to FIG. 24 and the solution of FIG. 23 is basically only that a part of the axial length of the sleeve 20x is formed as a sleeve-shaped wave spring 97, which not only generates a shaft during axial or radial clamping. spring force and radial spring force.

FIG. 25 shows a variant in which the principle of the variant from FIG. 22 is realized in an embodiment similar to the variant from FIG. 1 . For axial tensioning of the sleeve 20y, an inwardly protruding radial projection 28y is formed on its end adjoining the clamping structure 14y in order to form the bearing point 24y, which bears against a shoulder 30y of the shaft section 18y. At the other end adjoining the connecting structure 12y, the sleeve 20y is provided with a radially outwardly projecting radial flange 34y, which is clamped against the annular shoulder 41y of the connecting structure 12y by means of screws 38y for generating a biasing force VK. In this embodiment, too, a friction fit section 89y is provided, in which the optionally conical (section 91y) outer circumference of the shaft section 18y is radially opposed to the likewise conical inner circumferential surface of the sleeve 20y in this region. Clamp to create a friction fit. In the region of bearing point 22y, the inner peripheral surface of sleeve 20y is conically shaped and again covers a damping ring 94y. The sleeve 20y extends axially between the flange 34y and the frictional fit 89y, forming an annular gap 90y at a radial distance from the shaft section 18y.

FIG. 26 shows a collapsible tool holder 10z, which, in the embodiment according to FIG. 5, realizes the principle of the variant of FIG. 23 . But the support point 24z adjacent to the clamping structure 14z is formed by a radially inwardly protruding radial protrusion 28z, which abuts against the annular shoulder 30z of the tensioning shaft 18z, while the sleeve 20z is formed on one side of the connecting structure 12z. The side is internally threaded onto the external thread 44z of the tensioning shaft 18z to form the bearing point 22z. The sleeve 20z surrounds the circumference of the shaft section 18z adjoining the bearing point 24z in a friction fit portion 89z. The shaft section 18z has a radial interference in this region and can be slightly conical like the inner peripheral surface of the sleeve 20z. Furthermore, the sleeve 20z extends at a radial distance (annular gap 90z) from the shaft section 18z. The various damper rings are seen in the 94z and 96z.

FIG. 27 shows a collapsible tool holder 10aa similar to that of FIG. 16 . A similar conical sleeve 20aa is mounted on the conical tensioning shaft 18aa to form an annular chamber 66aa and is sealingly and fixedly connected to the tool holder 10aa along the full circumference at two support points 22aa and 24aa, here by welding. In this exemplary embodiment, the sleeve is mounted with its one end on the annular end face 41aa of the connection structure 12aa which surrounds the foot of the shaft section 18aa. The sleeve 20aa is provided at its other end forming the bearing point 24aa with a radially inwardly protruding annular flange 28aa which abuts against the axially directed annular shoulder 30aa of the shaft section 18aa in the same direction as the shoulder 41aa. The sleeve 20aa is therefore connected to the shaft section 18aa at the two bearing points 22aa and 24aa during a production process, in particular by friction welding.

The annular space 66aa between the shaft section 18aa and the sleeve 20aa is accessible from the outside via an inlet channel 99 , here via a further channel 98 in the center of the tool holder 10aa. In order to generate a preload, a flowable material is pressed into annular space 66aa via channels 98 and 99 during production of tool holder 10aa, where it subsequently increases in consistency. The material may be a rubber compound which is vulcanized in chamber 66aa. However, it can also be a hardenable plastic, such as resin or the like, which hardens over time in the annular space 66aa. Sinterable materials are likewise suitable. The material charged into the annular chamber 66aa expands the sleeve 20aa and thereby generates an axial biasing force VK. The inserted material must be able to harden under the increased filling pressure so that it can also maintain the increased pressure in the hardened state. The material may have elastic properties and/or fit against the sleeve 20aa or the shaft section 18aa with a friction fit. Of course, material can optionally also be introduced from the outside through the bore of sleeve 22aa, as this is illustrated in FIG. 16 .

FIG. 28 shows another variant of the retractable tool holder 10bb, in which, similarly to the variant in FIG. 22, one end of the sleeve 20bb constituting the tensioning device axially adjoining the clamping structure 14bb is in a frictional fit portion 89bb Stick tight shaft 18bb. The friction fit portion 89bb does not have to exert an axial securing force for the press fit securing of the sleeve 20bb. The sleeve is supported with its end adjoining the clamping structure 14bb on a radially elastic safety ring 95bb, which snaps releasably into an annular groove on the circumference of the tensioning shaft 18bb. Instead of safety ring 95bb, a nut screwed onto tensioning shaft 18bb can optionally also be provided analogously to the variant in FIG. 23 . The circumferential shape of the tensioning shaft 18bb and the sleeve 22bb adjoining it can again have the shape of a self-locking, steeply conical 91bb in the friction fit portion 89bb. As it was explained with reference to FIG. 22 . Of course, here, as in all the above-mentioned variants, instead of a conical shape, a cylindrical friction-locking region can also be provided. This friction fit is again achieved by a certain interference of the diameter of the shaft section 18bb with respect to the inner diameter of the sleeve 20bb.

The end of the sleeve 20bb that adjoins the connecting structure 12bb in the axial direction is supported axially by means of a hydraulic support device 100 . The bearing device 100 has an annular chamber 102 filled with a hydraulic pressure medium 101 and concentric to the axis of rotation D, in which an annular plunger 103 is guided axially displaceable in a sealing manner. The sleeve 20bb bears on the annular plunger 103 in the region of the annular surface 41bb formed on the foot of the shaft section 18bb. The plunger screw 104 , which communicates with the pressure medium 101 in the annular chamber 102 , allows a variable pressure loading of the pressure medium 101 and thus allows axial tensioning of the sleeve 20 bb via the annular plunger 103 .

The pressure medium may involve hydraulic oil or the like. Flowable and/or rubber-elastic materials or also viscoelastic substances are also suitable. Of course, the annular plunger 103 can also be integrally formed on the sleeve 20bb.

Some embodiments, not shown in more detail, allow a tensile load of the sleeve 20 bb even in the case of an installation in which the movement of the bearing device 100 is reversible. Furthermore, of course, the bearing device 100 can also be used in all other above-mentioned tool holders for the axial clamping of tensioning devices.

FIG. 29 shows a solution of a tool holder 10cc whose basic structure is similar to that of the tool holder 10h in FIG. 9 . The tool holder 10cc has a substantially conical sleeve 20cc clamped by pressure between the support point 22cc of the connection structure 12cc and the support point 24cc of the clamping structure 14cc, which is supported by the end face 45cc of the larger diameter end 32cc A seam is formed on an end surface 41cc extending perpendicularly to the axis of the annular flange 43cc of the connecting structure 12cc. The smaller diameter end 26cc of the sleeve 20cc bears with its end face 61cc on an annular shoulder 110 of the clamping structure 14cc to form a seam. The seams formed at support points 22cc and 24cc have vibration dampening properties.

Furthermore, the sleeve 20cc is radially centered in the region of its front end with a light press fit. Formed on the connecting structure 12cc is an annular flange 52cc having an outer peripheral surface 53cc adapted to the taper of the sleeve 20cc to center the sleeve 20cc on its inner peripheral surface 54cc. In the region of the support point 24cc, the clamping structure 14cc is provided with an annular shoulder 119, the outer peripheral surface 120 of which rests with a light radial press fit against the inner peripheral surface 121 of the sleeve 20cc and radially centers the sleeve 20cc.

The sleeve 20cc is made of cemented carbide, such as fine-grained cemented carbide such as model K20, or coarse-grained cemented carbide such as model K50. However, the sleeve can also consist of a heavy metal or a metal matrix composite (MMC), such as ferro-titanium. Ceramic or glass-fibre-reinforced plastic or carbon-fiber-reinforced plastic is also suitable as material for the sleeve 20 cc. Of course, the sleeve 20cc may also be constructed of tool steel, although the above materials are preferred. Furthermore, of course, the above-mentioned sleeves can likewise be formed from the preferred materials.

The clamping structure 14cc is integrally connected in one piece with a cylindrical shaft section 18cc, the free end of which is centered in an annular groove 47cc of the connecting structure 12cc, but guided axially displaceably. A clamping screw 56 cc clamps the shaft section 18 cc against the connecting structure 12 cc and thus ensures the pressure bias of the sleeve 20 cc. Of course, other force-transmitting fastening means can also be provided instead of the clamping screw 56cc, as explained with reference to FIGS. 3 , 4 , 10 , 14 and 19 for fastening the tensioning shaft in the connection.

The conical sleeve 20cc extends between bearing points 22cc and 24cc at a radial distance from the shaft section 18cc to form a conical annular chamber 111 . At least one (here a plurality of) annular damping elements 112 are arranged in the annular chamber 111, and each damping element abuts against the outer circumference 29cc of the shaft section 18cc on one side and on the other side against the sleeve with a radial bias and frictionally locked 20cc inner circumference 113 . The damping elements 112 consist of a rubber-elastic or hard-elastic material and are fixed axially between two retaining rings 115 , 117 . Each damping element 112 dampens these vibrations when the shaft section 18cc vibrates torsionally relative to the sleeve 20cc and when vibrates flexurally.

Each damping element 112 may have a radial interference with respect to the inner circumference 113 or the outer circumference 29 cc, so that each damping element is installed in the annular chamber 111 with a radial force fit. Additionally or alternatively, the radial biasing of the damping element 112 can also be achieved by axial clamping between the two retaining rings 115, 117, i.e. by means of an annular ring centering the end 32cc of the sleeve 20cc on the connecting structure 12cc. The shoulder 52cc places the stop ring 117 adjoining it at a predetermined size relative to the other stop ring 115 supported on the annular chamber 111. In this case, the radial clamping is achieved by reducing the axial spacing of the retaining rings 115 , 117 . Additionally or alternatively, the damping element 112 can be driven into the tapered gap of the annular chamber 111 to increase the radial bias.

The sleeve 20 cc can consist of tool steel, as in all the above-mentioned embodiments, but is preferably produced from cemented carbide for improved damping properties, as it can also be in the above-mentioned embodiments.

Fig. 30 shows a tool holder 10dd, which differs from the tool holder of Fig. 29 firstly in that the retaining ring 117dd is not supported on the annular shoulder 52dd which centers the end 32dd of the support sleeve 20dd, but on a threaded On the sleeve 119, it is screwed into the concentric threaded hole 47dd of the connecting structure 12dd. Threaded sleeve 119 allows adjustment of the axial spacing between stop rings 115dd and 117dd and thus the radial bias of damping element 112dd. End region 49dd of shaft section 18dd is tensioned against connecting structure 12dd by means of screw 56dd in order to press-bias sleeve 20dd. Of course, the end 49dd of the shaft section 18dd can optionally also pass through the threaded sleeve 119 and can be centered in the threaded sleeve 119 or in the connecting structure 12dd. In this way, the end 49dd is centered in the connection structure 12dd, and the end 49dd can also be connected to the connection structure 12dd in a tension-loaded manner, as described above for non-positive and form-fit connections.

FIG. 31 shows a variant of the tool holder of FIG. 29 , but unlike the tool holder of FIG. 29 , no damping element 112 is included between its shaft section 18ee and its sleeve 20ee. The outer shaft section 18ee is screwed with its free end into the threaded hole 47ee of the connecting structure 12ee similarly to FIG. 10 . However, the clamping point 22ee is radially centered to form a seam in the manner explained by means of FIG. The outer peripheral surface 121ee of 20ee forms a seam. This has the advantage that thermal expansion of the clamping structure 14ee formed as a shrink chuck does not affect the end 26ee of the sleeve 20ee and thus thermal expansion damage to the sleeve 20ee is not possible. This is particularly advantageous when the sleeve 20ee is constructed of a brittle material such as ceramic or the like as described above.

The tool holder 10ff shown in FIG. 32 differs from the tool holder in FIG. 31 only in that the radially centered shoulder of the end 26ff of the sleeve 20ff facing the clamping structure 14ff is integrally connected to the clamping structure. 14ff, but consists of a separate support ring 119ff made of steel, for example, which surrounds the outer circumferential surface 121ff of the sleeve 20ff and the outer surface of the clamping structure 14ff with its inner circumferential surface 120ff and radial light press fit. Circumferential surface 122 . Ring 119ff centers one end 26ff of sleeve 20ff relative to clamping structure 14ff. While the inner circumferential surface 120ee of the tool holder 10ee in FIG. 31 requires higher manufacturing costs, the inner surface 120ff of the ring 119ff can be manufactured cheaply as a mating surface. The sleeve 20ff consists of the material explained above with reference to FIG. 29 .

FIG. 33 shows a tool holder 10gg similar to the tool holder 10ee in FIG. 31 . Unlike the tool holder 10ee, however, the end 32gg of the sleeve 20gg adjoining the connecting structure 12gg is centered radially on the outside by an annular collar 52gg, as already explained with reference to FIG. 8 . In this case, however, bearing point 22gg is formed as a seam. The radially outer ring flange 55gg of the connecting structure 12gg centering the sleeve 20gg with a light press fit can withstand the opening force due to the axial tension of the conically arranged sleeve 20gg without centering errors.

The individual features of the tool holders shown in FIGS. 1 to 33 are freely combinable with one another.

Claims (66)

1. tool holder, being used for can be around the instrument of rotation (D) rotation, and this tool holder comprises:

One tensioning shaft, this tensioning shaft has a clamping structure in order to concentric setting tool (14) at the one end regions, and has a syndeton (12) in order to be connected in lathe with one heart in its zone, the other end;

One tensioning apparatus, this tensioning apparatus is connected in this tensioning shaft, this tensioning apparatus applies tensile force to this tensioning shaft in an axial tension section that in axial direction is arranged between clamping structure (14) and the syndeton (12), this tensile force comprises a tensioning component that in axial direction acts on, wherein two parts are that in tensioning shaft and the tensioning apparatus one constitutes sleeve (20b in tension section, 20c, 20f-20s, 20u-20x, 20z, 20aa-20gg), this sleeve surrounds corresponding another parts (18) in described two parts with one heart

Wherein clamping structure (14) stretch out sleeve (20b, 20c, 20f-20s, 20u-20x, 20z, 20aa-20gg) outside;

It is characterized in that sleeve (20b, 20c, 20f-20s, 20u-20x, 20z, 20aa-20gg) have one over there, and the shrink-fit that clamping structure (14) is configured for instrument is fixed to its external diameter and/or internal diameter that increases gradually in abutting connection with the end of syndeton (12).

2. according to the described tool holder of claim 1, it is characterized in that, sleeve (20b, 20c, 20f, 20k-20p, 20s, 20u, 20z, 20aa) be bearing in that tool holder (10) is gone up and tensioning shaft comprises a shaft part (18), this shaft part can be applied in pressure ground syndeton (12) is connected with clamping structure (14) with can being applied in away from each other pulling force.

3. according to the described tool holder of claim 2, it is characterized in that, sleeve (20b, 20c, 20f, 20k-20p, 20s, 20u, 20z, 20aa) near the end (26) of clamping structure (14) the annular convex shoulder away from syndeton (12) (30), and be tightened on the tool holder or be fixedly connected on tool holder at its other end (32) from back side interlocking tensioning shaft.

4. according to the described tool holder of claim 3, it is characterized in that, sleeve (20) has an annular lip of radially outward stretching out (34) at the described other end (32), and the annular convex shoulder that extends radially outwardly (43) of the relative syndeton of this annular lip (12) is tightened.

5. according to the described tool holder of claim 3, it is characterized in that sleeve (20f) has internal thread (44f) at the described other end (32f), this internal thread is tightened on the external screw thread (46f) of tensioning shaft.

6. according to the described tool holder of claim 2, it is characterized in that, sleeve (20b, 20c, 20n, 20s) rabbet the annular convex shoulder (33b away from syndeton (12) of tool holder near the end (26) of clamping structure (14) zone from the back side at it at clamping structure (14), 33c, 33n) or with tool holder link into an integrated entity, and at its other end (32b, 32c 32n) links into an integrated entity with the annular lip of radially outward stretching out (43) of syndeton (12), and tensioning shaft force closure and shape in tension regions be bearing in sealedly tool holder on the fixing surface of syndeton (12).

7. according to the described tool holder of claim 2, it is characterized in that sleeve (20s) is with clamping structure (14s) and syndeton (12s) links into an integrated entity and the zone of clamping structure is bearing on the zone of syndeton (12s) via shaft part (18s).

8. according to the described tool holder of claim 7, it is characterized in that shaft part (18s) constitutes the member that separates with clamping structure (14s) and syndeton (12s).

9. according to the described tool holder of claim 1, it is characterized in that sleeve (20g, 20h-20k, 20q, 20r, 20u-20x, 20bb, 20cc, 20dd, 20ee, 20ff is 20gg) at its each end (26,32) be bearing on the tool holder and tensioning shaft comprises a shaft part (18), this shaft part can be applied in pulling force ground syndeton (12) is connected with clamping structure (14) with can being applied in pressure mutually.

10. according to the described tool holder of claim 9, it is characterized in that sleeve (20g, 20h, 20i, 20q, 20r, 20w, 20x, 20cc, 20dd, 20ee, 20ff, 20gg) be bearing on the syndeton (12) with the one axial end, and be bearing in one with its other end can be with respect to member (18h, 18i, the 18cc that syndeton is axially tightened or interference fit connects, 18dd, 18ee, 18gg, 56,56n, 58,80,95) on the annular convex shoulder.

11., it is characterized in that described member constitutes the threaded collar (56) that tightens on the tensioning shaft according to the described tool holder of claim 10.

12. according to the described tool holder of claim 11, it is characterized in that, described annular convex shoulder be formed in tensioning shaft (18h, 18i, 18cc, 18dd, 18ee 18gg) goes up and this tensioning shaft is threadedly connected to the zone of syndeton.

13. according to the described tool holder of claim 10, it is characterized in that, describedly can constitute the instrument (80) that is fixed in the clamping structure with respect to the member that syndeton is axially tightened or interference fit connects.

14., it is characterized in that annular convex shoulder (79r) is formed on the clamping structure (14r) and this clamping structure can be fixed on the tensioning shaft (18r) with moving axially according to the described tool holder of claim 10.

15., it is characterized in that sleeve (20v) is bearing on the syndeton (12) with the one axial end according to the described tool holder of claim 9, and hold on tensioning shaft (18v) with its other end sealed twelve Earthly Branches that rub.

16., it is characterized in that sleeve (20o) comprises a plurality of sleeve shells (67,68) that are provided with one heart mutually according to the described tool holder of claim 1.

17., it is characterized in that sleeve shell (67,68) is adjacent at least mutually according to the described tool holder of claim 16 in a segmentation of its axial length.

18., it is characterized in that one of sleeve shell (67,68) is stressed and another sleeve shell (67,68) is subjected to pulling force according to the described tool holder of claim 16.

19., it is characterized in that radially (20p forms an annular space (66) 20aa) and between the shaft part of tensioning shaft (18), wherein fills up a material that is under the pressure at sleeve according to the described tool holder of claim 1.

20. according to the described tool holder of claim 19, it is characterized in that, sleeve (20p, each axial end tension 20aa) and closely be connected in tool holder (10), sleeve (20) have radial spacing ground to surround tensioning shaft (18) and for the axial tension that produces sleeve (20) between tensioning shaft (18) and sleeve (20) insertion be in material under the pressure.

21., it is characterized in that according to the described tool holder of claim 19, pressure change device (76) is set, can change the pressure of material in annular space (66) whereby.

22. according to the described tool holder of claim 1, it is characterized in that, in shaft part of tensioning shaft (18) and the sleeve (20) be stressed one via a damping piece (59) with respect in the shaft part (18) of tensioning shaft and the sleeve (20) be subjected to pulling force another carry out axially mounting.

23. according to the described tool holder of claim 1, it is characterized in that, sleeve (20v-20z, 20bb) at least in a segmentation of its axial length friction be adjacent to the circumference of tensioning shaft (18) sealedly.

24. according to the described tool holder of claim 23, it is characterized in that, sleeve (20v-20z, 20bb) with its two ends axial bias be bearing on the tool holder (10) axially in a friction locked portions (89), sealedly being bearing in regularly vertically on the tensioning shaft (18) of its middle sleeve (20) with the press-fit manner friction near the end of clamping structure (14).

25. according to the described tool holder of claim 23, it is characterized in that, sleeve (20v-20z, 20bb) and tensioning shaft (18v) at least the friction locked portions (89) a part in have the slight conical shape that cooperatively interacts.

26. according to the described tool holder of claim 23, it is characterized in that, sleeve (20v-20x, 20bb) vertically with the pressure bias voltage be bearing in that tool holder (10) is gone up and at friction locked portions (89) and axial vane surface encirclement tensioning shaft (18) in radial spacing ground is arranged between the end that is bearing in tool holder (10) of syndeton (12) vertically.

27. according to the described tool holder of claim 26, it is characterized in that, but at least one damping ring of being made by the material of elastic compression (94) is arranged to vertically in friction locked portions (89) and between the other end of tool holder (10v) upper support, and between the inner circumferential surface of the circumference of tensioning shaft (18) and sleeve (20v).

28. according to the described tool holder of claim 1, it is characterized in that, tensioning shaft (18) changes the annular convex shoulder (41) of syndeton (12) and sleeve (20) axially mounting on annular convex shoulder (41), and sleeve (20b, 20c, 20f-20s at least, 20u-20x, 20z, the end (32) at annular convex shoulder (41) upper support 20aa-20gg) constitutes conical portion, and this conical portion is tapered away from annular convex shoulder (41) vertically.

29., it is characterized in that conical portion covers at least one damping ring (94,112) according to the described tool holder of claim 28.

30., it is characterized in that sleeve is vertically with the pressure bias voltage according to the described tool holder of claim 28.

31., it is characterized in that sleeve (20x) comprises the wavy spring part (97) of an axial elasticity according to the described tool holder of claim 1.

32. according to the described tool holder of claim 1, it is characterized in that, sleeve (20bb) is bearing on the tool holder (10) vertically with its two ends, wherein being provided with one in the support path at one of two ends of sleeve (20bb) can be with respect to the axially movable supporting arrangement of tool holder (10) (100), this supporting arrangement has at least one supporting plunger (103), described supporting plunger can lead in the balancing gate pit (102) of the pressure medium that comprises flowable or plastically deformable (101) that is its configuration with moving axially, wherein is that balancing gate pit (102) configuration is adjusted element (104) in order to change the pressure in the pressure medium (101).

33. according to the described tool holder of claim 32, it is characterized in that, supporting plunger (103) constitutes that form in the annular space of balancing gate pit (102) one can axially movable annular plunger, and one of two ends of sleeve (20bb) are bearing in this circular column or coupled beyond the Great Wall.

34., it is characterized in that adjusting element (104) is the plunger screw that affacts on the pressure medium (101) according to the described tool holder of claim 32.

35., it is characterized in that the other end in the two ends of sleeve (20bb) is fixedly connected on tensioning shaft (18) or axially mounting on an annular lip of tensioning shaft (18) according to the described tool holder of claim 32.

36. according to the described tool holder of claim 1, it is characterized in that, sleeve (20cc) has radial spacing ground to surround the shaft part (18cc) of tensioning shaft at least in a segmentation of its axial length and forms an annular space (111), and the large tracts of land that an annular radially is set in this annular space bias voltage is adjacent to the damping element (112) of the external peripheral surface (29cc) of the inner circumferential surface (113) of sleeve and shaft part (18cc).

37. according to the described tool holder of claim 36, it is characterized in that, damping element (112) but constitute and annular space (11) limits vertically by baffle ring (115,117) by the material of elastic compression, between them, clamp damping element (112) vertically so that produce radially bias voltage.

38., it is characterized in that one of them baffle ring (117dd) can be offset vertically according to the described tool holder of claim 37, in order to change the bias voltage of damping element (112).

39. according to the described tool holder of claim 38, it is characterized in that, but the baffle ring of axial dipole field (117dd) by one in syndeton (12dd) but the screw device (119) of going up fixing axial dipole field constitute.

40., it is characterized in that annular space (111) has cone shape according to the described tool holder of claim 36.

41., it is characterized in that damping element (112) is along the direction bias voltage that dwindles in conical annular space (111) according to the described tool holder of claim 40.

42. according to the described tool holder of claim 1, it is characterized in that, sleeve (20m, 20n, 20o) in a segmentation of its axial length, there is radial spacing ground to surround the shaft part (18) of tensioning shaft at least and forms an annular space and go up vibration damping mass (65m is set in this annular space at shaft part (18), 65n, 65o).

43., it is characterized in that (65m, 65n are movably along shaft part (18) 65o) to the vibration damping mass according to the described tool holder of claim 42.

44., it is characterized in that two parts are that tensioning shaft is made of different materials with tensioning apparatus according to the described tool holder of claim 1.

45. the tool holder according to claim 44 is characterized in that, parts in described two parts are made of carbide alloy or heavy metal or metal matrix composite materials or pottery or plastics in the zone of tensile force at its transmitter shaft at least.

46., it is characterized in that two parts are that one of tensioning shaft and tensioning apparatus transmit the seam (22 of tensile force via at least one according to the described tool holder of claim 1,22a, 22h, 22i, 22q, 22r, 22s, 22v-22z, 22aa-22gg, 24,24a-i, 24n, 24q, 24r, 24v-24z 24aa-24gg) is bearing on another of two parts.

47., it is characterized in that (24v-24z 24bb) is arranged on two of two parts with between the circumferential surface that radially press-fit manner is close to each other to seam according to the described tool holder of claim 46.

48. according to the described tool holder of claim 46, it is characterized in that, and seam (22,22a, 22h, 22i, 22q, 22r, 22s, 22v-22z, 22aa-22dd, 24,24a-24i, 24n, 24q, 24r, 24w-24z 24aa-24gg) is arranged between two surfaces that axially are close to each other of two parts.

49. according to the described tool holder of claim 46, it is characterized in that, between the surface of two formation seams, damping material layer (59 be set; 59t).

50. according to the described tool holder of claim 46, it is characterized in that, at least one of two axial ends that constitutes the parts of sleeve forms in the surface that is close to each other of seam one and a shaping or circumferential surface (120) is set on another of two parts, this circumferential surface centring spool radially in the zone of this end.

51. according to the described tool holder of claim 50, it is characterized in that, on the two ends of sleeve, be provided with respectively the surface that forms seam and sleeve in the zone at two ends by the circumferential surface of described another parts in described two parts centering radially.

52., it is characterized in that the circumferential surface of described another parts of described two parts is adjacent to the circumferential surface of sleeve with press-fit manner radially according to the described tool holder of claim 50.

53., it is characterized in that the circumferential surface of described another parts in described two parts is at the regional inner radial surrounded sleeve of at least one axial end portion of sleeve according to the described tool holder of claim 50.

54., it is characterized in that the circumferential surface of described another parts in described two parts surrounds the end near clamping structure of sleeve to the outside at least in the footpath according to the described tool holder of claim 53.

55. according to the described tool holder of claim 53, it is characterized in that, in the zone of at least one end of sleeve (20ff), described another parts in described two parts the circumferential surface of surrounded sleeve (20ff) radially by an axial covering joints, constitute at the ring of described another parts of surrounded (119ff) radially equally.

56. according to the described tool holder of claim 3, it is characterized in that, and sleeve (20b, 20c, 20f, 20k-20p, 20s, 20u, 20z 20aa) fixes by non-disconnectable seam at its other end (32) and is connected in tool holder.

57. according to the described tool holder of claim 56, it is characterized in that, and sleeve (20b, 20c, 20f, 20k-20p, 20s, 20u, 20z 20aa) fixes by welding at its other end (32) and is connected in tool holder.

58., it is characterized in that sleeve (20g, 20h, 20i according to the described tool holder of claim 10,20q, 20r, 20w, 20x, 20cc, 20dd, 20ee, 20ff 20gg) is bearing on the radially-protruding annular lip (43) of syndeton (12) with the one axial end.

59., it is characterized in that sleeve (20v) is bearing on the radially-protruding annular lip (43) of syndeton (12) with the one axial end according to the described tool holder of claim 15.

60. according to the described tool holder of claim 19, it is characterized in that, in annular space (66), fill up a flowable material or plastically deformable or flexible material.

61., it is characterized in that (20p, each axial end aa) is connected in tool holder (10) by the mode of friction welding to sleeve according to the described tool holder of claim 20.

62. according to the described tool holder of claim 20, it is characterized in that, between tensioning shaft (18) and sleeve (20), insert flexible material for the axial tension that produces sleeve (20).

63., it is characterized in that the other end axially mounting in the two ends of sleeve (20bb) is on a removable safety collar (95bb) that is fixed on the tensioning shaft (18) according to the described tool holder of claim 35.

64. the tool holder according to claim 45 is characterized in that, the described parts in described two parts are sleeve (20).

65. the tool holder according to claim 45 is characterized in that, described plastics are plastics or carbon fiber reinforced plastics that glass fibre strengthens.

66. according to the described tool holder of claim 55, it is characterized in that, in the zone of the end in abutting connection with clamping structure (14ff) of sleeve (20ff) (26ff), described another parts in described two parts the circumferential surface of surrounded sleeve (20ff) radially by an axial covering joints, constitute at the ring of described another parts of surrounded (119ff) radially equally.

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