CN1929941A

CN1929941A - Vibration-damped tool holder

Info

Publication number: CN1929941A
Application number: CNA200580007054XA
Authority: CN
Inventors: F·海默; J·海默; H·科普
Original assignee: Franz Haimer Maschinenbau KG
Current assignee: Franz Haimer Maschinenbau KG
Priority date: 2004-01-16
Filing date: 2005-01-14
Publication date: 2007-03-14
Anticipated expiration: 2025-01-14
Also published as: DE102004019869A1; CN1929941B

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

The tool holder of vibration damping

Technical field

The present invention relates to a kind of tool holder, be used for an instrument that can rotate around rotation, for example boring bar tool, milling cutter, milling tool or grinding tool, wherein tool holder comprises a tensioning shaft, and this tensioning shaft has one at the one end regions and has one in order to be connected in the syndeton of lathe with one heart in order to the clamping structure of concentric setting tool in its zone, the other end.

Background technology

Such tool holder generally is known as chuck or clamping axle in drilling machine, milling machine, grinder or grinding machine that is in the general geometry lathe that determine or uncertain blade machining in the employing rotation for example.Clamping structure can have an accommodation hole that is concentric with rotation, is used to hold the fixed handle of instrument.Wherein on the circumferential surface of accommodation hole, at least one clamping surface can be set, in order to the fixed handle of setting tool.Known tool holder generally has certain axial length, and this makes it be subjected to the influence of the outer vibration that swashs basically easily, and these vibrations can be evoked in various sources.

For example numerous cutting elements, its setting is used for being clamped in such tool holder, has at least one blade or along the equally distributed many blades of its circumference at its outer surface, thereby periodically at least one blade is cut in workpiece body, so that machine away a smear metal from it when instrument rotates.Along with a reaction force is got in touch in the incision of such blade in material on blade because blade more or less impact type from a unhewn state change over to one the cutting state.Thereby the periodicity that such power is impacted depends on the number of blade of existence and the rotating speed of instrument and tool holder.But also known other vibration effect, as it for example because the unconformable cutting speed of corresponding instrument is produced, for example because the chatter of milling cutter.

Because these influences can excite tool holder around the twisting vibration of its desirable rotation and/or in an oscillation crosswise that comprises in the plane of rotation.The mixed form of these vibrations also takes place.

Summary of the invention

Therefore the objective of the invention is, a kind of tool holder that starts described pattern is provided, thereby it generally speaking is subjected to the influence of undesirable vibration not quite easily and reaches relevant higher processing precision with respect to prior art.

This purpose of the present invention reaches by a kind of tool holder that starts described pattern, it is characterized in that, one tensioning apparatus is connected in tensioning shaft, this tensioning apparatus applies a tensile force to tensioning shaft in an axial tension section of tensioning shaft, this tensile force comprises a tensioning component that in axial direction acts on, be that in tensioning shaft and the tensioning apparatus at least one constitutes sleeve at the tension section inner part wherein, it surrounds corresponding another parts with one heart.

According to the present invention, tensile force can be applied on the tool holder in any direction, as long as it has one in axial direction promptly along the tensioning component of the directive effect of rotation.But this is interpreted as that by the technical staff in axial direction the component of Zuo Yong tensioning component in total tensile force is bigger, then utilizes the accessible effect of tensioning apparatus of the present invention bigger.

Syndeton can relate to for example steep circular cone connecting axle of any pattern or the hollow shaft connection (HSK connection) that a traditional tool holder connects.Clamping structure also can relate to any pattern of tool holder, for example shrinks the chuck accommodation hole, is used for for example Weldon type of cylindrical handle or the instrument accommodation hole that comprises pinching screw of Whistle-Notch type.But split chuck or so-called general accommodation hole or cutter head accommodation hole also are suitable for.

Axially tensioning component produces the axial tensioning of machinery in axial tension section, thus its generally speaking change with respect to the state of mechanical tensioning not particularly improve the spring performance of tool holder, particularly it is at the spring hardness of axial component and tool holder.Spring rate by applying axial tensile force and can change targetedly generally, particularly improve tool holder and the relative vibration mode that on tool holder, can excite especially easily and the resonant frequency of attaching troops to a unit thereof.As known, member for example the resonant frequency of tool holder by the decision of the merchant's of spring rate and quality square root.Change targetedly by spring rate not only can influence the twisting vibration characteristic targetedly, that is the relevant vibration of tool holder around rotation, and can influence the oscillation crosswise characteristic targetedly, that is tool holder is relevant to a vibration that comprises in the plane of rotation.Tool holder is perpendicular to rotation vibration skew.Also show, under individual cases, can improve damping in the elastic range at metal material under the situation of high mechanical tensioning.

The axial tensile force that sleeve by tensioning apparatus is applied to the machinery on the tool holder can be pulling force or pressure.Tension section preferably in axial direction is arranged between clamping structure and the syndeton in this respect, outside clamping structure stretches out sleeve and the shrink-fit that is configured for instrument especially true fixedly the time.Reach by these measures, syndeton and clamping structure can be constituted enough rigidity and clamping structure where necessary for instrument compress and unclamp can be approaching for induction heating apparatus.

Set in first scheme, sleeve is moved away from each other at its each end and is bearing on the tool holder and tensioning shaft can be applied in pressure ground syndeton is connected with clamping structure with being applied in pulling force.

Perhaps, sleeve also can be bearing on the tool holder and tensioning shaft can comprise a shaft part at its each end with being applied in pressure toward each other, and it can be applied in pulling force ground syndeton is connected with clamping structure.

Supporting for the be applied in pulling force or the pressure of sleeve can be provided with suitable annular convex shoulder on tool holder.But sleeve also can at one end or on its two ends for example be fixedly connected on tool holder by melting welding or soldering etc.Certainly sleeve also can be with syndeton or/and clamping structure be combined into one.This mode fixedly connected causes tool holder durable, that can bear high load capacity.Particularly can be in the tensioning process for example wait by welding to apply afterwards fixedly connected, this simplifies the structure of tool holder significantly.

What conform with purpose is, tool holder is constituted to make tensile force be changeable, thereby tensile force that is considers that the number of the blade that exists, the rotating speed of tool holder etc. can reduce undesirable vibrational excitation according to applicable cases on a cutting instrument.In order to change tensile force, the support path of the shaft part of sleeve or tensioning shaft (Abst ü tzweg) can be via an axial manipulation that is threaded.Replacing is threaded also can be provided with the interference fit connection, and it allows axially adjustment by outside axial compressive force.The last balancing gate pit that hydraulic action also can be set in support path.Hydraulic coupling can be adjusted therein so that change tensile force.

Tensioning shaft is or/and sleeve must be connected in to antitorque commentaries on classics syndeton and clamping structure, so that can transmit the driving torque of lathe to instrument.Tool holder its rotation relatively should be bending resistance.This can reach in enough damping characteristics like this, is about on the annular convex shoulder of a reinforcement clamp locking structure that sleeve is bearing in syndeton, particularly is bearing on the radially-protruding annular lip of syndeton or with this annular convex shoulder to be connected.Annular convex shoulder is strengthened the zone of the connection side of sleeve.Because the external diameter of annular convex shoulder is usually greater than the external diameter of clamping structure, the external diameter of sleeve or/and internal diameter can increase with respect to the other end at its end in abutting connection with syndeton.The approaching conical sleeve-shaped that draws is in such a way improved the bending rigidity of tool holder.

The shaft part that is surrounded by sleeve of tensioning shaft can have sleeve-shaped equally.Particularly sleeve can also comprise a plurality of sleeve shells that are provided with one heart mutually that itself use, and they can rub mutually in a segmentation of its axial length at least and be adjacent to sealedly.Affact on its oscillating movement that causes to the frictional force damping of Chan Shenging like this.Also can one of them sleeve shell be applied in compression and another sleeve shell is applied in tension, thereby the inner sleeve shell is born the function of the shaft part of tensioning shaft simultaneously.

In addition, sleeve but its at least one sleeve shell are at least one axial end region, preferably be provided with in the middle of all by damping piece two axial end region and be adjacent to tool holder.By contact interlocking make again between sleeve and the damping piece or/and the microcosmic relative motion between damping piece and tool holder is possible, thereby suppress undesirable relative motion between tool holder and the sleeve.This also stops the generation of undesirable vibration.Damping piece guarantees to relax the impact on tool holder in addition, processes as its workpiece that for example can result from cutting.This exceed sleeve with damping piece or/and damping piece also is invalid during with being connected of being adjacent to tool holder, only.

Radially form an annular space but selectively or additionally also tool holder can be constituted make between sleeve and shaft part, it is used to be in material, particularly a flowable material under the pressure or a plastically deformable or flexible material fills up.The pressure change device preferably is set, borrows it can change the pressure of the material in annular space.The material that is under the pressure not only influences axial tensile force, and can also improve damping action when the friction of inside.The pressure change device can relate to the device that is used to change spatial volume, for example can be offset to enter the interior adjustment screw of spatial volume or/and a plunger that can be offset.

Thereby above-mentioned tensioning apparatus change not only suffers twisting vibration in operation but also suffer the spring performance of the tool holder of flexural vibrations also to change its vibration characteristics.Thereby the change of vibration characteristics has caused the improvement of the cutting characteristic of instrument also to cause the improvement in tool work life-span under individual cases.But when absorbing energy or catabiotic device, can reach the tangible improvement of the damping characteristic of tool holder for the tool holder configuration.Set in of the present invention one preferred form of implementation, the sleeve that produces tensile force rubs in a segmentation of its axial length at least and is adjacent to the circumference of tensioning shaft sealedly.Only its when axially each end sleeve of being connected in tool holder is in the twisting vibration of tensioning shaft or flexural vibrations with respect to the tensioning shaft motion and by its these vibrations of sealed inhibition that rub.The interference size design of the sealed circumferential surface that is close to each other that can be by tensioning shaft and sleeve of this friction realizes, for example the external diameter by tensioning shaft is with respect to the radial interference of the internal diameter of sleeve in a form of implementation, and sleeve surrounds tensioning shaft.But also can be produced as the sealed needed radial load of friction separately, for example between the circumferential surface of the diametrically contraposition by elastomeric material being pressed into tensioning shaft and sleeve.

Proved sealed needn't the extension that rub along the entire axial length of sleeve, the sealed segmentation that is limited in sleeve, just enough in the zone of one axial end especially that will rub or rather, thus remaining axial length of sleeve can be used for flexible axial tensioning.In the simple especially form of implementation, last described principle is used for the axially mounting of sleeve on tensioning shaft simultaneously on one preferred, structure.With its two ends axial bias the sleeve that is bearing on the tool holder preferably in a friction locked portions, be fixed on the tensioning shaft near the end of clamping structure vertically with it with the press-fit manner friction sealedly.The axial length of friction locked portions is specified to its axial bias power that also can bear sleeve that makes, but can brings into play the characteristic of its frictional damping to the other end of sleeve over there.

When installing on the tensioning shaft of sleeve at tool holder with sleeve for example in a pressure apparatus by overcoming interference fit with the pressure bias voltage.For needn't along the friction locked portions axial overall height propelling sleeve under the interference fit condition, sleeve and tensioning shaft at least the friction locked portions a part in have the slight conical shape that cooperatively interacts, for example slope is about 0.1.Such cone shape is self-locking.Certainly, friction locked portions itself as long as it satisfies the interference fit condition, also can be formed by periphery.

So by the pressure bias voltage install to sleeve on the tensioning shaft with its other end axially mounting on the annular convex shoulder of tool holder, particularly axially mounting is on the annular convex shoulder of syndeton.Proved in this respect conform with purpose be, will constitute tapered segment at the socket end of annular convex shoulder upper support, it is tapered vertically away from annular convex shoulder and also strengthens the footing in abutting connection with syndeton of tensioning shaft thus.

As already mentioned, axially with the sleeve of pressure bias voltage conform with the destination axially friction locked portions and axial vane surface to syndeton between the other end of tool holder upper support, have radial spacing ground to extend vertically with tensioning shaft be movably so that make sleeve in the part of its generation bias voltage.Axially in the friction locked portions and can between the circumference of tensioning shaft and sleeve interior surface but the damping ring that at least one is made by the material of elastic compression be set between the other end of tool holder upper support, thereby this sleeve zone also can be used for endergonic vibration damping simultaneously.For example such damping ring can be packed in the above-mentioned tapered segment of sleeve.

In another preferred form of implementation, set, each axial end tension of sleeve and closely be connected in tool holder, particularly friction welding, its middle sleeve have radial spacing ground to surround tensioning shaft, thereby form the doughnut to external seal between sleeve and tensioning shaft.For axial tensioning, indoorly for example inject one deformablely and absorb the material of vibrational energy during in distortion introducing under the pressure at this, it is flowable or deformable at least in the filling process and changes its denseness in this case under pressure keeps.The flowable rubber composition that for example vulcanizes in doughnut is a hardenable synthetic that be suitable for or also suitable, and its age-hardening in doughnut becomes the annular solid of a hard elastics.Sintered material also is suitable in doughnut, for example ceramic material.Above-mentioned damping material can comprise filler, and it improves the mechanical strength or the rigidity of damping material.

In another program, it is based on the principle of the hydraulic pressure generation of the axial tensioning that is used for tensioning apparatus, wherein set, sleeve with its two end axles to being bearing on the tool holder, wherein being provided with one in the support path at one of two ends of sleeve can axially movable supporting arrangement with respect to tool holder, it has at least one supporting plunger, described supporting plunger can lead in a balancing gate pit for the pressure medium that comprises flowable or plastically deformable of its configuration with moving axially, wherein disposes an adjustment element that is used for changing the pressure of pressure medium for the balancing gate pit.This balancing gate pit preferably be arranged on owing to the space requirement reason tool holder syndeton a side and can comprise a plurality of along the circumferential direction distribute can axially movable plunger, they are affacting on the socket end of adjacency on the circumference with distributing.Each plunger conforms with the destination and is arranged in each balancing gate pit independent but that be communicated with for pressure medium.Relate to the annular plunger that is concentric with rotation but preferably support plunger, it is can be axially movable in the annular space of a formation balancing gate pit.This annular plunger can separate with sleeve, but it also can be linked to be one with sleeve.

Pressure medium can relate to hydraulic oil or other incompressible liquid.But flowable plastic material also is suitable for, for example like rubber or flowable plastics or viscoelastic material.

Adjusting element also can relate to the plunger screw of pressure medium generation effect here etc.

The other end in the two ends of sleeve can be fixedly connected on tensioning shaft, for example welding or glued.But a removable safety collar that is fixed on the tensioning shaft is set on the annular lip that is used for the bearing sleeve other end preferably.Safety collar can relate to one and be tightened in the nut on the tensioning shaft or relate to the interior turn of cannelure that a radial elastic is snapped in tensioning shaft.

Certainly, the suitable selection of the wall thickness by sleeve can be optimized its spring performance.Suitable shape by sleeve also can influence spring performance.For example sleeve comprises the wavy spring part of an axial elasticity.

Not to be inconsistent the vibration that requirement takes place in order reducing, an oscillating mass piece can be set on tool holder, its resonance by differentiation reduces or even eliminates undesirable vibration on tool holder fully.Preferably this oscillating mass piece in axial direction is arranged on the tool holder movably, thereby its resonant frequency can be aligned to the resonant frequency of tool holder.The oscillating mass piece preferably is arranged on the axle of tool holder, because at first form undesirable vibration mode thereon.The oscillating mass piece can be included in the above-mentioned sleeve in addition, if for example it is at this axle of surrounded radially.Protect the oscillating mass piece to avoid externalities whereby, for example the influence of smear metal whereabouts and cooling agent.

Set in another preferred form of implementation, sleeve has radial spacing ground to surround shaft part at least in a segmentation of its axial length and forms an annular space and a damping element of annular that is adjacent to the external peripheral surface of the inner circumferential surface of sleeve and shaft part in large area radially is set in this annular space bias voltage.Such damping element guarantees that itself and the friction lock of determining merging between sleeve or the shaft part guarantee frictional damping thus.This damping element can be made of the material of rigidity basically, and preferably the material by flexible or plasticity constitutes, thereby the interior friction of this material also helps vibration damping, although damping element should the antitorque circumferential surface that be connected in sleeve and shaft part with changeing.Damping element can be pressed in the annular space by compression.But preferred annular space is limited vertically by each annular convex shoulder, axially clamps damping element so that produce radially bias voltage between them.The change of the axial spacing by each annular convex shoulder can change the bias voltage of damping element.For example but one of them annular convex shoulder can be made of the screw device of an axial dipole field of fixing on syndeton for this reason.Preferred annular space has cone shape, thereby also can reach the change that radially clamps of damping element than the material of rigidity the time.

As a whole, proved that particularly advantageous is that two parts are that tensioning shaft is made of different materials with tensioning apparatus, because if vibration must can suppress vibration so better by the zone of different materials.One of them parts particularly sleeve conform with the destination and are made of carbide alloy.This carbide alloy is a particulate, model K20 for example, but also can be coarse grain, and model K50 for example is because have higher intensity and less fragility than the carbide alloy of coarse grain.Heavy metal or metal matrix composite materials (MMC material) also are suitable for, for example ferrotianium.The plastics or the carbon fiber reinforced plastics of ceramic material and plastics, particularly glass fibre enhancing also are suitable in addition.

In above-mentioned each form of implementation, two parts that is tensioning shaft and tensioning apparatus connect to one mutually by welding where necessary.But it is particularly advantageous that following these forms of implementation have also proved, and two parts are one of tensioning shaft and tensioning apparatus via at least one transmitter shaft on the seam of tensile force is bearing in another of two parts.The surface that each seam is close to each other according to them is applied in pulling force or exerts pressure has different force-transfer characteristics, and thus because the asymmetry of this power transmission guarantees to reduce vibration.Wherein each seam can be arranged between two of the two parts circumferential surfaces that are close to each other with radially interference fit form and/or between two surfaces that axially are close to each other of two parts.Can between the surface of two formation seams, a damping material layer be set in case of necessity.

Proved importantly that in order to reduce vibration two parts are mutually relative radial alignment in the zone of seam, wherein preferably should have certain lightpressure fit between the circumferential surface of each centering.At least one of two axial ends that constitutes the parts of sleeve should constitute one of surface that is close to each other, and conforms with the destination shaping or a circumferential surface is set on another of two parts, its centring spool radially in the zone of this end.Conform with the destination, the both ends of sleeve are radial alignment by this way.

Sleeve can be its inner circumferential surface centering radially.But particularly the axial end in abutting connection with clamping structure of sleeve conforms with the destination its external peripheral surface centering radially, because the thermal expansion of clamping structure is not exerted pressure to this sleeve ends in this case.Especially in the structure of shrinking chuck, the expansion that sleeve ends causes because of the contraction chuck of thermal expansion may cause the damage of sleeve, when it is especially true when for example pottery etc. constitutes by fragile material.The end in abutting connection with syndeton of sleeve conforms with the destination also its external peripheral surface centering, because in such a way for example may be because the power of opening that the conical shape of sleeve produces centering that can be by outside and sustained.

The circumferential surface of centering outside can become one to be shaped on the parts that surround sleeve from the outside in combination.But the inside to the accurate manufacturing of the cooperation of these parts since there the indent that exists expend.For simpler manufacturing, in a form of implementation in the zone of at least one sleeve ends, especially at it in the zone of the end of clamping structure, another of two parts radially the surrounded sleeve circumferential surface by an axial covering joints, equally radially the ring of another parts of surrounded constitutes.The matching surface inside of such ring can be made more simply.

Description of drawings

Below be described in more detail various embodiments of the present invention by accompanying drawing.Wherein:

The axial profilograph of the tool holder of Fig. 1 to 7 vibration damping comprises axial sleeve with the pulling force tensioning;

The axial profilograph of the tool holder of Fig. 8 to 13 vibration damping comprises axial sleeve with strain of pressure;

Figure 14 and 15 comprises the axial profilograph of tool holder of the vibration damping of vibration damping quality;

Figure 16 comprises the axial vertical section of the tool holder of adjustable damping;

Figure 17 and 18 comprises the axial profilograph with each scheme of the tool holder of the sleeve of pressure bias voltage;

Figure 19 and 20 comprises the axial profilograph of each scheme of the tool holder of the sleeve that is applied in pulling force;

Figure 21 comprises the axial profilograph of the tool holder of damping that can be automatically controlled;

Figure 22 to 26 comprises the axial vertical section of the tool holder of the sealed damping that rubs;

Figure 27 and 28 comprises the axial vertical section of the tool holder of adjustable damping;

Figure 29 and 30 comprises the axial profilograph of the tool holder of the damping element of packing into;

Figure 31 to 33 has the axial profilograph of the tool holder of damping behavior.

The specific embodiment

First form of implementation of tool holder of the present invention is totally with 10 marks among Fig. 1.Tool holder 10 has a syndeton 12 in its zone, left part in Fig. 1, is used for tool holder 10 and is connected by known mode own with a unshowned lathe.Syndeton 12 by being connected in lathe takes place from the rotating driving device of the lathe transmission of torque to tool holder 10.

Tool holder 10 has a clamping structure 14 at its longitudinal end in contrast to syndeton 12, and it has a columniform in the example shown holes for clamping 16.The handle of instrument inserts wherein and can clamp there.In example shown in Figure 1, relate to one and be used to shrink the tool holder 10 of clamping.Clamping structure 14 is heating in the zone at holes for clamping 16 on its external peripheral surface 15 for this reason, thereby the diameter of clamping structure thermal expansion and holes for clamping 16 becomes bigger.Handle with an instrument under this heated state inserts in the holes for clamping 16, make tool holder 10 cooling or self cooling in the zone of clamping structure subsequently, thereby the contraction of the clamping structure 14 that causes by cooling between pad and clamping structure 14, pad is fixed in the holes for clamping 16 with interference fit.Such tool holder generally is known in the prior art.

Tool holder 10 can be symmetrical around rotation D rotation and about this rotation D basically.The whole direction explanations that relate to an axis in this application all relate to rotation D.This is applicable to axial direction, circumferencial direction and radial direction.

In an axial shaft part 18 between syndeton 12 and clamping structure 14, tool holder 10 is surrounded with one heart by a sleeve 20.Sleeve 20 is bearing on the tool holder 10 at two supporting-

point

22 and 24 places that in axial direction are provided with spacing each other.Supporting-point 22 is the supporting-points near syndeton 12 among Fig. 1, and supporting-point 24 is near clamping structure 14.Supporting-

point

22 and 24 extends around tool holder 10.Sleeve 20 in its Fig. 1 the right longitudinal end 26 have one around radially protuberance 28, it is protruded to inner radial by sleeve body 27.

This radially protuberance 28 along the circumference and of tool holder 10 on tool holder 10 around convex shoulder or flange 30 supporting interlockings, flange 30 protrudes to the outside from columniform basically axle outer surface 28 radius vectors of shaft part 18.The radially protuberance 28 of sleeve 20 be substantially perpendicular to bearing-surface 31 rotation D orientation, that under the assembled state of sleeve 20, point to syndeton 12 more accurately be adjacent to around the end face 33 of the sensing clamping structure 14 that is substantially perpendicular to rotation D equally of flange 30.Via forming the surface 31 of a seam and 33 contact, on supporting-point 24, can transmit a tensile force VK in axial direction effect and that point to syndeton 12 to tool holder 10.

Sleeve 20 has the radial flange 34 that a radius vector is extended to the outside at its longitudinal end 32 near syndeton 12.Radial flange 34 along the circumferential direction is provided with a plurality of through holes 36 that wait angular separation to be provided with each other.Inject screws 38 by these through holes 36, its head of screw be bearing in radial flange 34 be substantially perpendicular to rotation D's and point on the bearing-surface 39 of another longitudinal end 26.

Each screw 38 utilizes internal thread to be screwed in the tool holder 10 in the blind hole 40 for through hole 36 configurations.

By each screw 38 tighten and by its supporting on the radial flange 34 of sleeve 20, can be at supporting-point 22 places via the internal thread transmission one of blind hole 40 tensile force VK in axial direction that act on and that point to clamping structure 14.The selection of the fastening torque by screw 38 can be adjusted the numerical value of tensile force VK.For this reason by syndeton 12 radially-protruding annular lip 43 be substantially perpendicular to rotation D's and point to the bearing-surface 41 of clamping structure 14 and sleeve 20 radial flange 34 equally perpendicular to rotation D's and point between the end face 45 of syndeton 12 and reserve a gap.

But for the ease of adjusting predetermined tensile force according to a kind of form of implementation of the present invention, under the sleeve unassembled state, see, can will be arranged to make axial spacing between them at two bearing-surfaces on the tool holder greater than the axial spacing between each corresponding bearing-surface of this two bearing-surface configuration that is at sleeve.In the example of Fig. 1, the axial spacing between the bearing-surface 33 and 41 is greater than about 0.3 to 0.5 millimeter of the spacing of corresponding bearing-surface 31 and 45.Tighten screw 38 in this case simply, be close to each other up to surface 41 and 45.Because the material of the sleeve that reaches extends in and applies a predetermined tensile force on the tension section VA.

The above-mentioned tensile force VK that produces on supporting-point 24 is because of tightening the bearing reaction of the tensile force VK that screw 38 causes, so the tensile force VK that produces on each corresponding supporting-point numerically is equal sizes and opposite orientation.Therefore be under the axial compression stress of raising at the tension section VA between supporting-point 22 and 24.The axial compression stress of the raising that acts in tension section VA is higher than the axial tensioning load in the axial component of this tension section in axial direction of tool holder 10.The axial compression stress that improves by this section VA changes tool holder 10 with respect to the spring rate of the state of tensioning not, thereby also changes the vibration mode that can excite especially easily and affiliated resonant frequency thereof with the spring rate that changes on tool holder 10.This be not only applicable to tool holder 10 easy excitated around the resonant frequency of the twisting vibration of rotation D and also be applicable to the resonant frequency that comprises the oscillation crosswise in the plane of rotation D.Therefore be the spring rate that sleeve 20 and screw 38 can influence tool holder 10 by the member that constitutes a tensioning apparatus, make in the operation of tool holder 10, for example more difficultly when known one is clamped in the operation rotating speed of the cutting rotational speeds of instrument of tool holder 10 and known means anchor clamps 10 excite or undesirable vibration takes place with less probability.Therefore final the raising life-span of utilizing tool holder 10 accessible machining accuracies and instrument.

Among Fig. 2 with all following figure in identical member be provided with identical mark and subsidiary at least one letter all the time to show difference.Each member is only described in detail in conjunction with its that figure that occurs first.Consult its description in the figure that occurs first about these member lay special stress ons.The feature of the tool holder of representing in each figure can make up arbitrarily in this respect mutually.

The form of implementation of Fig. 2 is equivalent to Fig. 1's basically.Only each screw 38a injects among the tool holder 10a by through hole 36a in form of implementation shown in Figure 2 and utilizes internal thread to be screwed among the radial flange 34a in the 40a of hole.

The longitudinal axis of each screw 38a tilts with respect to rotation D.Each screw 38a is arranged to make the longitudinal axis of imagination of their prolongation to meet on one point on the rotation D ideally.By screw 38a the one power F along the directive effect of its longitudinal axis is passed to tool holder 10a whereby, this moment, this power F had in axial direction tensioning component VK and a component VR radially.Tensioning component VK, it causes a corresponding bearing reaction on supporting-point 24a, the tension section VA of tool holder 10a is under the axial compression stress with above-mentioned effect.

Fig. 3 illustrates a tool holder 10b, the difference of the tool holder of itself and Fig. 1 and 2 is that mainly sleeve body 27b constitutes conical basically and it forwards the bearing-surface 41b of the annular lip 43b of syndeton 12b to with integrally being integral on supporting-point 22b at the bigger end of diameter.Improve the bending rigidity of tool holder 10b to the tapered sleeve 20b of clamping structure 14b.Shaft portion 29b and clamping structure 14b and flange 30b constitute one and by the cylindrical hole 47 in the zone of the annular lip 43b of syndeton 12b axially among the insertion sleeve 20b.Therefore the internal diameter in hole 47 is a bit larger tham the external diameter of flange 30b.Shaft portion 29b is provided with an interference fit surface 49 at the end of adjacency syndeton 12b, and it is fixed in the hole 47 with interference fit radially.The axial bias power VK of the sleeve 20b that this cooperation is chosen to that interference fit can be born and is applied in pulling force.

Fig. 4 illustrates a tool holder 10c, the difference of the tool holder 10b of itself and Fig. 3 mainly is, replacement is fixed in interference fit 49 in the hole 47 with interference fit friction sealedly, this hole is constituted screwed hole 47c, the sealed earth's axis of shape is to tightening an external screw thread 49c therein, and this external screw thread is formed on the end that is adjacent to syndeton 12c of shaft portion 29c.Adjust the pulling force of axial action to the sleeve 20c by reversing of shaft portion 29c.

The contraction that tool holder 10d shown in Fig. 5 is not suitable for pad clamps, and is provided with a plurality of flexible clamping sectors 42 on its clamping structure 14d, and they are with tool holder axle 18d formation one.Each clamps sector 42 and can be offset to rotation D by the bending that overcomes its elastic properties of materials over there.Be applied for pad by a locking sleeve 20d and in holes for clamping 16d, clamp needed bending force.For this reason with the excircle 15d of the clamping structure of tool holder 10d coning near the longitudinal end the clamping structure of tool holder 10d constitute with being tapered.Therefore the surface normal N of the frustoconical exterior surface 15d of clamping structure 14d has component and a component radially along the direction of rotation D.

Near the longitudinal end 26d of locking sleeve 20d its clamping structure has a conical inner surface 31d.Conical inner surface 31d has the slope identical as conical external surface 15d basically.Therefore also points in axial direction direction at least of conical inner surface 31d.Each surface (under the assembled state of locking sleeve 20d) since their tapering just in time point on the one hand to rotation D over there direction radially and just in time point to axial direction over there on the other hand to syndeton 12d.Therefore surperficial 15d forms near the supporting-point 24d of clamping structure with mutual large-area contact of 31d.

On away from the axial direction of clamping structure 14d, near syndeton 12d, excircle 29d, external screw thread 44 is set at shaft part 18d.Internal thread 46 on the longitudinal end 32d of locking sleeve 20d is halved together with this external screw thread 44.The external screw thread 44 of tool holder 10d forms near the supporting-point 22d of syndeton with the screw thread interlocking of the internal thread 46 of locking sleeve 20d.Radially pass to each and clamp sector 42 by the tensile force with needs tightened on the one hand of locking sleeve 20d on tool holder 10d, and produce axial tensioning component VK, it causes that in the tension section VA of tool holder 10d an axial compressive force clamps.

For the better centering of locking sleeve 20d, in axial direction between supporting-point 22d and 24d, constitute thereon one around radial flange 48, it protrudes and is adjacent to the outer surface 29d of the shaft part 18d of tool holder 10d in large area to inner radial.

One tool holder 10e is shown again among Fig. 6, and it comprises the clamping structure 14e of the contraction clamping that is used for pad, as among Fig. 1 and 2.Therefore need radially on clamping structure 14e, not apply power by locking sleeve 20e.Therefore locking sleeve 20e is not configured to contact to a conical external surface.Locking sleeve 20e has a protuberance 28e radially on its longitudinal end 26e for clamping structure 14e configuration or rather, and it is with an end face that is substantially perpendicular to rotation D equally 50 that points to syndeton 12e and be adjacent to tool holder 10e perpendicular to the bearing-surface 31e of rotation D under the assembled state of locking sleeve 20e.Surface 31e and 50 supporting interlocking form a supporting-point 24e.Another supporting-point 22e in Fig. 5, is formed by the screw thread interlocking of the internal thread 46e of the external screw thread 44e of tool holder 10e and locking sleeve 20e.

Clamping structure 14d and 14e are arranged in tension section VA at least in part in Fig. 5 and form of implementation shown in Figure 6.

The form of implementation of tool holder 10f shown in Fig. 7 is the combination of the form of implementation of Fig. 6 and Fig. 1 and 2 basically: near the supporting-point 22f the syndeton, in Fig. 6, form by the screw thread interlocking of the internal thread 46f of an external screw thread 44f on the tool holder 10f and a sleeve 20f.

Otherwise, according near the supporting-point 24f the form of implementation formation clamping structure of Fig. 1 and 2.Consult the description of Fig. 1 and 2 or 6 for the form of implementation lay special stress on that illustrates in greater detail supporting-point 22f and 24f.

Be configured for the groove 51 of instrument interlocking in the zone of supporting-point 22f, supporting-point 22f produces the tensile force of the axial tensioning of the tension section VA that causes tool holder 10f with supporting-point 24f.Can very accurately adjust the tensile force that is applied on the tool holder 10f whereby.

Be that sleeve 20g is in its supporting interlocking of longitudinal end 32g on tool holder 10g near syndeton 12g among Fig. 8.The surperficial 45g perpendicular to rotation D of radial flange 34g is bearing on the surperficial 41g perpendicular to rotation D on the syndeton 12g of tool holder 10g.In addition near the bearing-surface 45g of syndeton 12g on tool holder 10g, constitute one surrounded radial flange 34g radially to flange 52.This guarantees the accurate concentric position of sleeve 20g about tool holder 10g to flange 52.To the centering surface 53 of the sensing inner radial of flange 52 and the sensing footpath surface 54 supporting interlockings to the outside of radial flange 34g.For fear of sleeve moving on the supporting-point 22g that forms like this, radial flange 34g with to flange 52 by one around the weld seam 55 mutual non-disconnectable formulas of tool holder be connected.

Be at supporting-point 24g on the outer surface 29g of shaft part 18g of tool holder 10g external screw thread 44g is set, tighten one thereon and adjust nut 56g.Adjust nut 56g and press to the end face that is substantially perpendicular to rotation D 57 of sleeve 20g along the direction of rotation D.The selection of the fastening torque by adjusting nut 56 can be adjusted the pressure that is applied on the sleeve 20g.Therefore the tension section VA of tool holder 10g can be under the axial tension stress targetedly.The pressure that affacts on the sleeve 20g affacts on the tool holder 10g as counter pull in tension section VA.

Among the tool holder 10g in Fig. 8, syndeton 12g, clamping structure 14g and shaft part 18g are in conjunction with constituting one.

Fig. 9 illustrates a tool holder 10h, the difference of tool holder 10g among itself and Fig. 8 mainly is, becomes the shaft part 18h of a formation axially to pass the centre bore 47h of syndeton 12h with clamping structure 14h and axially away from a side bearing one nut 56h of clamping structure 14h.It tightens on the external screw thread 44h of shaft part 18h.Can apply axial tensile force on the conical sleeve 20h here by means of nut 56h.Sleeve 20h is clamped between the annular end face that radially extends of the supporting-point 22h that constitutes seam respectively and 24h.

The tool holder 10i of one one-tenth two formation shown in Figure 10.Tool holder 10i comprises that one connects the tool holder part 60 of side, and the tool holder part 58 that syndeton 12i and clamps side is set thereon, and clamping structure 14i is set thereon.Two tool holder parts 58 and 60 are threaded mutually, the scheme one among Fig. 4 of here being similar to having among the screwed hole 47i on the tool holder part 60 that externally threaded threaded journal 49i is screwed into the syndeton side on the tool holder part 58 of clamping structure side.

Tool holder part 58 relative with 60 one is tightened to the tapered conical sleeve 20i in clamping structure there.Sleeve 20i utilizes an end face 61 perpendicular to the front side of rotation D to be adjacent to the same of clamping structure 14i and forms a seam perpendicular to the bearing-surface of rotation D.One corresponding seam is arranged between surperficial 41i and the 45i in the edge tensile force direction to syndeton 12i of sleeve 20i.Near the syndeton of sleeve 20i longitudinal end 32i is at the flange 52i of surrounded one on syndeton 12i radially and whereby about rotation D centering.Near the longitudinal end 26i of sleeve its clamping structure by tool holder part 58 with its inner periphery about rotation D centering, the front of the longitudinal end 26i clamping structure of its middle sleeve 20i near is adjacent to a damping ring 59, its in axial direction be arranged on sleeve 20i the front side longitudinal end 26i and comprise between the tool holder part 58 of clamping structure 14i.Damping ring 59 can be for example by the pottery manufacturing and than tool holder 10i or/and have different elastic properties of materials than sleeve 20i.Damping ring 59 suppresses the undesirable motion of tool holder 10i by interior friction.

Because tool holder part 58 and 60 be threaded, sleeve 20i in axial direction is under the compression in form of implementation shown in Figure 10, thereby the tension section VA of tool holder 10i is under the mechanical tension.The numerical value of this tension can suitably be selected by apply a torque of determining when two tool holder parts 58 and 60 are threaded.The possibility of the axial tensioning that one additional fine setting requires is, is adopting the very little screw thread of pitch on the axle journal 49i and on the 47i of hole.

The tool holder 10k of one two-piece type is shown again among Figure 11, and it comprises tool holder part 58k and 60k.Be different among Figure 10 is that tool holder part 58k and 60k are not threaded mutually.The more definite axle journal 49k of tool holder part 58k that says only inserts among the hole 47k of tool holder part 60k.

When fabrication tool anchor clamps 10k, it is pegged graft with an after-applied pressure at two tool holder part 58k and 60k, thereby its length is shortened according to corresponding elastic properties of materials under pressure.Wherein tool holder 10k can be shortened the corresponding surface that is adjacent to the corresponding configuration on tool holder part 60k or the 58k up to end face 45k, the 61k of the both end sides of sleeve 20k always.Then sleeve 20k is connected in corresponding tool holder part 58k and 60k at its two longitudinal ends 26k and 32k by welding non-disconnectable formula.This by apply near the longitudinal end 32k the syndeton of sleeve 20k one around weld seam 62 and near the longitudinal end 26k the clamping structure of sleeve 20k, apply one around weld seam 63 realize.Applying the axial assembling pressure loading that weld seam cancellation later on for example applies on tool holder by forcing press or clamping device, lax thereby the elastic properties of materials of the previous relative sleeve 20k of tool holder 10k that shortens takes place.Sleeve 20k is under the tension simultaneously, thereby is under the compression in the axial tension section between

weld seam

62 and 62.

The form of implementation of Figure 12 is equivalent to Figure 10's basically.Only near the longitudinal end 32l the syndeton of sleeve 20l no longer by flange 52l along its excircle or inner periphery centering.The end face of the longitudinal end 32l of sleeve 20l and flange 52l docks mutually in the front side or rather.In assembling process, can for example realize centering on every side here by the tie point of an outer sleeve of between flange 52l and longitudinal end 32l, rabbeting.Better centering near the longitudinal end 32l the syndeton of sleeve 20l, this longitudinal end also can constitute step-like, thereby the axial protuberance of flange 52l on the longitudinal end 32l that directly rabbets on every side to the outside at sleeve 20l also makes sleeve centering on its longitudinal end 32l like this.

Form of implementation shown in Figure 13 is equivalent to the form of implementation of above-mentioned Figure 12 under its tensioning state.The one oscillating mass piece 64 that can in axial direction move is set in addition, as by shown in the double-head arrow P on outer surface 29m.

Oscillating mass piece 64 is additional to the undesirable vibrational excitation that tool holder 10m is resisted in axial tensioning.This is not only applicable to twisting vibration and is applicable to oscillation crosswise.If tool holder 10m is evoked vibration, also make elongated shaft part 18m be in motion thus.Can reach by the suitable selection of oscillating mass piece 64 at axial installation position, oscillating mass piece and its shaft part 18m of supporting are evoked the vibration of phase place dislocation in same frequency, thus on the total system of tool holder 10m because the interference of differentiation has less or even the global vibration of the amplitude of disappearance.

The oscillating mass piece is 64 removable, ground such as can reverse, can be threaded is arranged on the shaft part 18m.Oscillating mass piece 64 is made of a simple ring, and shaft part 18m is by its endoporus 65.For fixing of the axial location of oscillating mass piece 64 on shaft part 18m, for example tighten up fixing in radial direction it in addition by pin.

Figure 14 illustrates a tool holder 10n, and it is equivalent to the tool holder 10b of Fig. 3 basically, but the tool holder 10m that is similar to Figure 13 on its shaft part 18n, support one once more can axially movable oscillating mass piece 64n.Oscillating mass piece 64n also plays the vibration damping quality, in order to reduce the amplitude in the working range of tool holder 10n.

The form of implementation of Figure 15 and the difference of Figure 13 at first are, comprise that the tool holder part 58o of clamping structure 14o only is connected in the tool holder part 60o that comprises syndeton 12o via sleeve 20o.Be integral the shaft part 18o that on tool holder part 58o, constitutes, do not extend to tool holder part 60o, and end in the space that surrounds by sleeve 20o with freely stretching out with its free longitudinal end.

Secondly the form of implementation of Figure 15 and the difference of Figure 13 are, sleeve 20o crosses a big

concentric sleeve shell

67 and 68 that is provided with of common axial component by two and constitutes.

The longitudinal end that freely stretches out of shaft part 18o allows to excite the vibration mode of the axle 18o that both sides clamp in the form of implementation that is different from Figure 13.

In the form of implementation of Figure 15, reach axial tensioning with 68 mutual relative tensionings by two sleeve shells 67.Each

sleeve shell

67 and 68 is welded in tool holder part 58o and the 60o that disposes into these longitudinal ends at its each longitudinal end separately.Centering for example reaches like this, promptly on the tool holder part 60o around the outer peripheral face of flange 52o at inner sleeve shell 68 radially on surround this sleeve shell 68, thereby reach the centering of sleeve shell 68 about tool holder part 60o.Radially inner sleeve shell 68 is again at the step part 69 of surrounded tool holder part 58o radially, thereby this step part is by inner sleeve shell 68 centerings.Sleeve shell 68 and the situation that is connected of each tool holder part 58o and 60o are equivalent to the connection situation of the form of implementation middle sleeve 20k of Figure 11 basically, and lay special stress on is consulted the description of Figure 11 in this.

After inner sleeve shell 68 is installed, tool holder 10o is in axial direction exerted pressure, described as form of implementation in conjunction with Figure 11, thus the axial length of shortening tool holder 10o.Under this state that shortens by the external force effect, outer sleeve shell 67 is connected in corresponding tool holder part 58o and 60o by welding non-disconnectable formula.Remove the axial compressive force that applies from the outside subsequently, thereby the inner sleeve shell is under the axial compression stress, and the outer sleeve shell is under the axial tension stress.

Among Figure 16,, the tool holder 10p of monomer is shown as among Fig. 1,2 and 5 to 7.One at the conical sleeve 20p of surrounded tool holder 10p radially, is welded in tool holder 10p on the radial outer end of the radial flange 34p on its longitudinal end 32p.Same sleeve 20p is welded in tool holder 10p at it on vertical end 26p of clamping structure 14p, as shown in the first half of tool holder 10p shown in Figure 16.

The axial component that is surrounded by sleeve 20p of tool holder 10p is provided with a circumferential groove along a predetermined axial component, thereby tool holder 10p determines a volume 66 with sleeve 20p, in the example of Figure 16, in this volume, inject oil 70, be full of whole volume 66 and make by oil 70.

Oil 70 when tool holder 10p rotates is because centrifugal force applies radius vector power to the outside on the inwall of sleeve 20p.Because the tapering of sleeve 20p and its fix to clamp on longitudinal end 26p and 32p, the power that this radius vector acts on to the outside causes a power that in axial direction acts on sleeve, thereby the tension section of tool holder 10p is under the mechanical compression.

Replace welding, only be adjacent to the corresponding external conical surface 29p of shaft part 18p in the zone of the longitudinal end 26p of conical sleeve its clamping structure near in large area with its circular cone inner surface 71, as shown in the Lower Half of this tool holder 10p in Figure 16.The power that radially affacts when tool holder rotates on the sleeve 20p causes one along the direction of sleeve wall component that extend and that point to syndeton 12p there, borrows its zone that makes longitudinal end 26p to syndeton 12p displacement minutely over there.This causes the circular cone inner surface 71 of sleeve 20p and the external conical surface 29p of shaft part 18p closely to be adjacent to mutually.

On this external radial flange 34p a device for exerting 72 is set, comprise one with its radially inner side face be in oil 70 wetting contact around rubber ring 74 and a plurality of adjustment screws 76 that equidistantly distribute and be provided with around the circumference of radial flange 34.Utilize adjustment screw 76 can make in the radially inside shift-in volume 66 of rubber ring 74.Improve the pressure in the oil 70 whereby, this causes the additional axial tensioning of tool holder 10p via the power effect of oil 70 on sleeve 20p.Replace one around rubber ring also can be provided with and be respectively the plunger of making by pottery, metal etc. of respectively adjusting the screw configuration, these plungers directly squeeze oily 70.

In form of implementation shown in Figure 17, in axial direction cross clamping structure 14q at the sleeve 20q of surrounded tool holder 10q radially.

Sleeve 20q is adjacent to the bearing-surface 41q that equally be substantially perpendicular to rotation near the longitudinal end 32q of syndeton 12q with its end face 45q that is substantially perpendicular to rotation D at it.

Clamping structure 14q has internal thread, and it is formed in the inwall that limits holes for clamping 16q.Be screwed into the external screw thread 78 of a milling head 80 at the internal thread of this clamping structure.The longitudinal end 26q for clamping structure 14q configuration of sleeve 20q is bearing in the back side that is substantially perpendicular to rotation D equally 79 of milling head 80 with its end face 16q that is substantially perpendicular to rotation D.Be screwed into the outer sleeve 20q of retaining among the holes for clamping 16q by milling head 80, outer sleeve 20q is under the compression, the tension section VA that is surrounded by outer sleeve of tool holder 10q is under the tension simultaneously.Replace a milling head 80 any other the instrument that clamps screw thread that has can be tightened among the holes for clamping 16q.

A form of implementation shown in Figure 18, it is equivalent to Figure 17's basically.Wherein replace milling head 80 that the relative sleeve 20r of a shrinkage sleeve 80r is tightened among the holes for clamping 16r.Shrinkage sleeve 80r has a holes for clamping 16 ' r once more, but clamping tool handle therein is described as the clamping structure 14 in conjunction with the form of implementation of Fig. 1.

In Fig. 1,2 and 5 to 8 tool holder, shaft part combines with clamping structure and syndeton and connects into one.Figure 19 illustrates a tool holder 10s, and its middle sleeve 20s combines with syndeton 12s and clamping structure 14s and constitutes one.Sleeve 20s has cone shape and forwards the end face 41s of the flange 43s that radially protrudes of syndeton 12s at the bigger end 32s of its diameter to.Clamping structure 14s has vertical bearing-surface 81 at its end towards the terminal 26s of sleeve 20s, the end face in abutting connection with clamping structure 14s that it forms supporting-point 24s and is adjacent to shaft part 18s.The terminal 49s in abutting connection with syndeton 12s of shaft part 18s radially imports and is fixed among the 47s of hole.Should be fixing can be by being similar to Fig. 3 being threaded or realizing of interference fit, the tool holder by being similar to Fig. 4 of tool holder by circular weld 83.Make shaft part 18s fixing under exerting pressure, thereby sleeve 20s is with the pulling force bias voltage.

Figure 20 illustrates a flexible program of the tool holder of Figure 19.Here sleeve 20t also combines with syndeton 12t and clamping structure 14t and connects into one and surround an independent shaft part 18t, and sleeve 20t can be subjected to the pulling force tensioning via it.Here the shaft part 18t of sleeve shaped is provided with a protuberance 84 that is adjacent to clamping structure 14t at it near the longitudinal end 26t of the clamping structure 14t centre by a compensating element, 82.

From the side of syndeton 12t one clamping element 85 is tightened the tool holder 10t.Internal thread among the syndeton 12t of external screw thread on the clamping element 85 and tool holder 10t is halved together.Clamping element 85 and shaft part 18t towards a damping element 59t who had before described by Figure 10 is set in the middle of vertically between the longitudinal end 32t of syndeton 12t.One compensating element, 82 also is used to stop the heat passage from contraction clip locking structure 14t, but can cancel this compensating element.

Shaft part 18t constitutes hollow and has an in axial direction adjustable stop device 86 at its longitudinal end 26t in order to lead the supercooling fluid, its constitutes one and is used for an axial terminal block that is inserted into the pad of holes for clamping 16t.Such stop device also can be arranged in the form of implementation of other descriptions.

A tool holder 10u shown in Figure 21 becomes the material 87 that sleeve shaped is installed, preferred shrink fit one is different from tool holder 10u material at it thereon from syndeton 12u near the longitudinal end regions its clamping structure.Also reach the axial tensioning of the axial direction part 18u of tool holder 10u whereby.This material can be the material that metal, pottery or an electricity cause contraction, and it changes its longitudinal size by applying a voltage along at least one direction in space.Therefore can change the power that is applied to by it on tool holder 10u by on the material of installing, applying a voltage.

Figure 22 illustrates a tool holder 10v who comprises the contraction clamp type of a tensioning shaft 18v, it is at one end axially protruded by the convex shoulder 88v of an axis normal that constitutes by syndeton 12v and at the holes for clamping 16v that comprises a center vertically away from the side of syndeton 12v of its clamping structure 14v, clamp the pad that is not shown in further detail in order to shrink, be described in more detail by Fig. 1 as it.Tensioning shaft 18v is surrounded by a sleeve 20v who constitutes tensioning apparatus between syndeton 12v and clamping structure 14v, and this sleeve is bearing on the end face 88 of an annular at a supporting-point 22v place vertically with its end in abutting connection with syndeton 12v.Sleeve 20v axially is installed on the circumference of shaft part 18v with press-fit manner in a friction sealed regional 89 in abutting connection with the supported end 24v of clamping structure 14v by its another.Sleeve 20v axially extends between friction sealed regional 89 and supporting-point 22v, radially separates with shaft part 18v simultaneously to form an annular gap 90.Overlapped circumferential surface is that the circumferential surface with shaft part 18v on the inner surface of sleeve 20v has a steep coniform shape 91 with interference fit in friction locked portions 89, and it axially is tapered and the circular cone that makes shaft part 18v has an interference so that the generation interference fit with respect to the terminal location of the sleeve 20v that installs to clamping structure 14v with about 0.1 slope along predetermined axial length over there.But certainly, the surface that is close to each other in friction locked portions 89 also can constitute periphery.For produce pretightning force with sleeve towards the power of the front 92 usefulness numbers of clamping structure 14v ton 10 tons defeat for example to annular surface 41v, this causes the elastic tension power of sleeve 20v.Be force-fitted in the zone 89 and generally speaking produce bed knife, it remains on the sleeve 20v of such pretension the position of its pretension.But the while allows to overcome the friction lock relative motion between sleeve 20v and tensioning shaft 18v with joint efforts vertically friction locked portions 89 in the zone of syndeton 12v, suppress twisting vibration and the flexural vibrations of shaft part 18v whereby.

In order to improve the rigidity of shaft part 18v, the end regions that is adjacent to syndeton 12v of sleeve 20v constitutes the tapered tapered segment 93 over there to clamping structure 14v, covers a damping ring 94 of being made by the hard elastics material around tensioning shaft 18v.

Figure 23 illustrates the scheme of the tool holder 10w of a shrinkage type, the difference of the scheme of itself and Figure 22 only is, friction locked portions 89w at first determines size for the frictional damping of tool holder 10w, shaft part 18w has the radial interference with respect to the internal diameter of sleeve 20w in this friction locked portions, supporting-point 24w is made of a nut 95 simultaneously, sentence pretightning force FK bearing sleeve 20w at this supporting-point, it tightens on the external screw thread of tensioning shaft 18w.The biasing force that here sleeve is clamped between its supporting-point 22w and the 24w also is several tons, for example 10 tons.The shape of this outer sleeve 20w is equivalent to the shape of Figure 22 middle sleeve 20v, but in addition in the zone of the end of clamping structure 14w another damping ring 96 is being set between sleeve 20w and tensioning shaft 18w.

Difference by the scheme of the form of implementation of Figure 24 and Figure 23 only is that basically the part of the axial length of sleeve 20x constitutes the wavy spring 97 of sleeve shaped, and it not only produces axle spring power but also produces radial spring power when axially or radially clamping.

Figure 25 illustrates a scheme, wherein is similar to the principle that realizes the scheme of Figure 22 in the form of implementation of scheme of Fig. 1 one.For axial tensioning sleeve 20y, on the end of clamping structure 14y, be shaped one at it in order to form supporting-point 24y to projecting inward radially protuberance 28y, it is bearing on the convex shoulder 30y of shaft part 18y.Sleeve 20y is provided with a radial flange 34y who radially outward stretches out at the other end of adjacency syndeton 12y, and it is in order to produce the annular convex shoulder 41y clamping of biasing force VK with the relative syndeton 12y of each screw 38y.Also be provided with a friction locked portions 89y in this form of implementation, conical where necessary (part 91y) excircle of shaft part 18y radially clamps with respect to the same conical inner circumferential surface in this zone of sleeve 20y and to form friction sealed therein.In the zone of supporting-point 22y, the inner circumferential surface of sleeve 20y constitutes conical and covers a damping ring 94y once more.Sleeve 20y extends between flange 34y and friction locked portions 89y vertically, has radial spacing ground to form an annular gap 90y with shaft part 18y.

Figure 26 illustrates the tool holder 10z of a shrinkage type, and it realizes the principle of the scheme of Figure 23 in pressing the form of implementation of Fig. 5.But the supporting-point 24z in abutting connection with clamping structure 14z radially forms to projecting inward radially protuberance 28z by one, this protuberance is adjacent to the annular convex shoulder 30z of tensioning shaft 18z, and sleeve 20z tightens to internal thread in the side of syndeton 12z on the external screw thread 44z of tensioning shaft 18z to form supporting-point 22z.Sleeve 20z is adjacent to supporting-point 24z surrounds shaft part 18z in a friction locked portions 89z circumference.Shaft part 18z has radial interference and can equally constitute slightly conical with the inner circumferential surface of sleeve 20z in this zone.This outer sleeve 20z and shaft part 18z have radial spacing to extend (annular gap 90z).In 94z and 96z, can see each damping ring.

Figure 27 illustrates the tool holder 10aa of a shrinkage type, and it is similar to the scheme of Figure 16.One same conical sleeve 20aa installs on conical tensioning shaft 18aa and forms a doughnut 66aa and in the sealing of two supporting-point 22aa and 24aa upper edge wholecircle week be fixedly connected to tool holder 10aa, here by welding.In this embodiment, sleeve is installed in the one end on the annular end face 41aa of syndeton 12aa, and this syndeton is surrounded the footing of shaft part 18aa.Sleeve 20aa is provided with the annular lip 28aa that radially inwardly stretches out on the other end of its formation supporting-point 24aa, it is adjacent to axial sensing such as the unidirectional annular convex shoulder 30aa of convex shoulder 41aa of shaft part 18aa.Therefore sleeve 20aa is connected with shaft part 18aa by friction welding in a process on two supporting-point 22aa and 24aa especially.

Doughnut 66aa between shaft part 18aa and sleeve 20aa is enterable via an input channel 99 from the outside, here via another passage 98 at the center of tool holder 10aa.Via passage 98 and 99 flowable material is pressed in the doughnut 66aa when the fabrication tool anchor clamps 10aa in order to produce a pretightning force, this material increases its denseness subsequently in doughnut 66aa.This material can relate to a rubber composition, and it vulcanizes in the 66aa of chamber.But also can relate to hardenable plastics, resin etc. for example, its age-hardening in doughnut 66aa.Sintered material is suitable for equally.The material among the doughnut 66aa of packing into expands sleeve 20aa and produces axial bias power VK thus.The material of packing into must harden under the pressure of packing into that improves, thereby it also can keep the pressure of raising under the state of sclerosis.This material can have elastic characteristic and/or with sealed sleeve 20aa or the shaft part 18aa of being adjacent to that rub.Certainly, where necessary also can be from the outside by the hole of the sleeve 22aa material of packing into, as this illustrated in fig. 16.

Figure 28 illustrates another program of the tool holder 10bb of shrinkage type, wherein is similar to the scheme of Figure 22, constitute tensioning apparatus sleeve 20bb in a friction locked portions 89bb, be adjacent to tensioning shaft 18bb in abutting connection with the end of clamping structure 14bb vertically.Friction locked portions 89bb needn't apply axial restraint power for the interference fit of sleeve 20bb fixes.Sleeve with its in abutting connection with the end bearing of clamping structure 14bb on the safety collar 95bb of a radial elastic, it is removable to be snapped in the cannelure on the circumference of tensioning shaft 18bb.The scheme that replaces safety collar 95bb can be similar to Figure 23 also is provided with a nut that tightens on the tensioning shaft 18bb where necessary.The circumferential shapes of tensioning shaft 18bb and the sleeve 22bb that is adjacent to it can have the shape of the steep conical 91bb of a self-locking once more in friction locked portions 89bb.Illustrated as it by Figure 22.Certainly, here as in all above-mentioned scheme, also replacing taper shape that the sealed zone of one cylindrical friction is set.To reach this friction with respect to certain interference of sleeve 20bb internal diameter sealed for diameter by shaft part 18bb once more.

The axial end in abutting connection with syndeton 12bb of sleeve 20bb is by supporting arrangement 100 axially mountings of a hydraulic pressure.Supporting arrangement 100 has a doughnut that is concentric with rotation D 102 that is full of the pressure medium 101 of hydraulic pressure, can guide an annular plunger 103 hermetically therein with moving axially.Sleeve 20bb at the regional internal support of the annular surface 41bb on the footing that is formed in shaft part 18bb on annular plunger 103.Thereby the variable pressure load of the plunger screw 104 authorized pressure media 101 that are communicated with pressure medium 101 in doughnut 102 also allows the axial tensioning of sleeve 20bb via annular plunger 103.

Pressure medium can relate to the hydraulic pressure wet goods.Flowable or/and the material of caoutchouc elasticity or also viscoelastic material also are suitable for.Certainly, annular plunger 103 also can be formed on the sleeve 20bb with being combined into one.

Be not shown in further detail some forms of implementation, promptly under the reversible installation situation of the motion of supporting arrangement 100, allow the tensile load of sleeve 20bb yet.Certain in addition, supporting arrangement 100 also can be used for the axial clamping of tensioning apparatus in whole other above-mentioned tool holders.

Figure 29 illustrates the scheme of a tool holder 10cc, and its basic structure is similar to the tool holder 10h among Fig. 9.Tool holder 10cc has a conical basically sleeve 20cc who clamps with pressure between the supporting-point 24cc of the supporting-point 22cc of syndeton 12cc and clamping structure 14cc, its end face 45cc with the bigger end 32cc of diameter is bearing in the end face 41cc that extends on the axis normal ground of the annular lip 43cc of syndeton 12cc and goes up and form a seam.The less end 26cc of the diameter of sleeve 20cc is bearing in its end face 61cc on the annular convex shoulder 110 of clamping structure 14cc and forms a seam.The seam that forms on supporting-point 22cc and 24cc has the characteristic of vibration damping.

This outer sleeve 20cc its front end the zone in the lightpressure fit radial alignment.Shaping one annular lip 52cc on syndeton 12cc, its external peripheral surface 53cc with the tapering that is adapted to sleeve 20cc make the sleeve 20cc last centering of circumferential surface 54cc within it.In the zone of supporting-point 24cc, clamping structure 14cc is provided with an annular convex shoulder 119, and its external peripheral surface 120 is adjacent to the inner circumferential surface 121 of sleeve 20cc and makes sleeve 20cc radial alignment with lightpressure fit radially.

Sleeve 20cc is made of carbide alloy, for example carbide alloy of particulate such as model K20, or the carbide alloy of coarse grain such as model K50.But sleeve also can by heavy metal or metal matrix composite materials (MMC) for example ferrotianium constitute.The plastics or the carbon fiber reinforced plastics that strengthen as the material of sleeve 20cc also suitable ceramic or glass fibre.Certainly, though above-mentioned each material is preferred, sleeve 20cc also can be made of tool steel.Certain in addition, above-mentioned each sleeve can be made of preferable material equally.

Clamping structure 14cc combines with a cylindrical shaft part 18cc and to connect into one, and the free end of shaft part is centering in the annular groove 47cc of syndeton 12cc, but can lead with moving axially.One pinching screw 56cc makes the relative syndeton 12cc of shaft part 18cc clamp and guarantee thus the pressure bias voltage of sleeve 20cc.Certainly, replace pinching screw 56cc that the fixture of other power transmission also can be set, as it for tensioning shaft fixing in syndeton by Fig. 3,4,10,14 and 19 illustrated.

Conical sleeve 20cc between supporting-point 22cc and 24cc to have radial spacing ground to extend with shaft part 18cc and to form a conical annular chamber 111.Damping element 112 of at least one (here for a plurality of) annular is set in doughnut 111, and another side is adjacent to the inner periphery 113 of sleeve 20cc Yi Bian each damping element sealedly is adjacent to the excircle 29cc of shaft part 18cc with bias voltage friction radially.Each damping element 112 is made of material caoutchouc elasticity or hard elastics and is axially fixed between two baffle rings 115,117.When shaft part 18cc during with respect to sleeve 20cc twisting vibration and during flexural vibrations each damping element 112 suppress these vibrations.

Each damping element 112 can have radial interference with respect to inner periphery 113 or excircle 29cc, thereby each damping element is installed in the doughnut 111 with interference fit radially.Additional or selectively also can be by the radially bias voltage of the existing damping element 112 of the axial clamp consolidation between two baffle rings 115,117, promptly make another baffle ring 115 that is supported on doughnut 111 relatively in abutting connection with its baffle ring 117 be in a predetermined size by the terminal 32cc annular convex shoulder 52cc of centering on syndeton 12cc that makes sleeve 20cc.Dwindling of axial spacing by baffle ring 115,117 reaches radially clamping in this case.Additional or selectively damping element 112 can be squeezed in the diminishing gap of doughnut 111 to improve radially bias voltage.

Sleeve 20cc can be as being made of tool steel in whole above-mentioned forms of implementation, but for improving damping characteristic preferably by the carbide alloy manufacturing, also can be like this in above-mentioned each form of implementation as it.

Figure 30 illustrates a tool holder 10dd, the difference of the tool holder of itself and Figure 29 at first is, baffle ring 117dd is not bearing on the annular convex shoulder 52dd of the terminal 32dd centering that makes bearing sleeve 20dd, and be bearing on the screw shell 119, it is tightened among the concentric screwed hole 47dd of syndeton 12dd.Thereby screw shell 119 allows to adjust the axial spacing between baffle ring 115dd and the 117dd and adjusts the radially bias voltage of damping element 112dd.The end regions 49dd of shaft part 18dd by means of screw 56dd with the relative syndeton 12dd tensioning of pulling force, so that make sleeve 20dd with the pressure bias voltage.Certainly, the terminal 49dd of shaft part 18dd where necessary also can by screw shell 119 and can be in screw shell 119 or syndeton 12dd centering.So terminal 49dd is centered among the syndeton 12dd, and terminal 49dd also can be connected in syndeton 12dd with being subjected to tensile load separately, as more than this for force closure with shape sealed be connected described.

Figure 31 illustrates a flexible program of the tool holder of Figure 29, but is different from the tool holder of Figure 29, does not comprise damping element 112 between its shaft part 18ee and its sleeve 20ee.Shaft part 18ee is similar to Figure 10 and tightens among the screwed hole 47ee of syndeton 12ee with its free end in addition.But clamping point 22ee to be forming a seam by the mode radial alignment of Figure 29 explanation, and annular lip 119ee is adjacent to the external peripheral surface 121ee of sleeve 20ee and forms a seam from the axial end 26ee of surrounded sleeve 20ee radially and with its inner circumferential surface 120ee.Its advantage is that the thermal expansion that constitutes the clamping structure 14ee that shrinks chuck does not influence the terminal 26ee of sleeve 20ee and therefore can not take place the thermal expansion of sleeve 20ee is damaged.This is particularly advantageous by fragile material when for example pottery etc. constitutes at sleeve 20ee as mentioned above.

The zone of the tool holder of the tool holder 10ff shown in Figure 32 and Figure 31 only is, make sleeve 20ff towards the end 26ff of clamping structure 14ff radially the convex shoulder of centering do not become a ground to be connected in clamping structure 14ff, and constitute by support ring 119ff one independent, that for example constitute by steel etc., this support ring with its inner circumferential surface 120ff and radially lightpressure fit surround the external peripheral surface 121ff of sleeve 20ff and the external peripheral surface 122 of clamping structure 14ff.Ring 119ff makes the end 26ff of sleeve 20ff with respect to clamping structure 14ff centering.Though the inner circumferential surface 120ee of the tool holder 10ee among Figure 31 needs higher manufacturing expense, the inner surface 120ff of ring 119ff makes as matching surface marked downly.Sleeve 20ff is made of above material by Figure 29 explanation.

Figure 33 illustrates a tool holder 10gg who is similar to the tool holder 10ee among Figure 31.But what be different from tool holder 10ee is, sleeve 20gg in abutting connection with the end 32gg of syndeton 12gg by an annular lip 52gg in the footpath centering to the outside, illustrate by Fig. 8 as this.But supporting-point 22gg constitutes seam in this case.Syndeton 12gg can bear with the annular lip 55gg of lightpressure fit centring spool 20gg in the footpath to the outside because the power of opening that produces of the axial tensile force of the sleeve 20gg that is provided with coning, and the error of centralization do not occur.

Each feature of tool holder shown in Fig. 1 to 33 can make up arbitrarily mutually.

Claims

1. tool holder, being used for can be around the instrument of rotation (D) rotation particularly boring bar tool, milling cutter, milling tool or grinding tool, this tool holder comprises a tensioning shaft, and 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; It is characterized in that, one tensioning apparatus is connected in this tensioning shaft, this tensioning apparatus applies tensile force to this tensioning shaft in an axial tension section of tensioning shaft, this tensile force comprises a tensioning component that in axial direction acts on, wherein each parts is that in tensioning shaft and the tensioning apparatus at least one constitutes sleeve (20) in tension section, and this sleeve surrounds corresponding another parts (18) with one heart.

2. according to the described tool holder of claim 1, it is characterized in that tension section in axial direction is arranged between clamping structure (14) and the syndeton (12).

3. according to the described tool holder of claim 2, it is characterized in that clamping structure (14) stretches out outside the sleeve (20) and the shrink-fit that is configured for instrument is fixed.

4. according to one of claim 1 to 3 described tool holder, it is characterized in that sleeve (20,20a-f, n, l, m, o, p, s-u, z, aa) be moved away from each other and be bearing in that tool holder (10) is gone up and tensioning shaft comprises a shaft part (18) with being applied in pulling force, this shaft part can be applied in pressure ground syndeton (12) is connected with clamping structure (14).

5. according to the described tool holder of claim 4, it is characterized in that, sleeve (20) is near the end (26) of clamping structure (14) annular convex shoulder away from syndeton (12) (30) from back side interlocking tensioning shaft, and is tightened on the tool holder or fixes by non-disconnectable seam, particularly welding especially at its other end (32) and be connected in tool holder.

6. according to the described tool holder of claim 5, 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.

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

8. according to the described tool holder of claim 4, it is characterized in that, sleeve (20b, c, n, s) rabbet the annular convex shoulder away from syndeton (12) (33) of tool holder from the back side or become one to be connected in tool holder at it near the end (26) of clamping structure (14) zone at clamping structure (14), and become one at its other end (32) and be connected in tool holder, particularly be connected in 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).

9. according to the described tool holder of claim 4, it is characterized in that one of sleeve (20s) one-tenth especially integrally is connected with syndeton (12s) with clamping structure (14s) regularly and the zone of clamping structure is bearing on the zone of syndeton (12s) via shaft part (18s).

10. according to the described tool holder of claim 9, it is characterized in that shaft part (18s) constitutes the member that separates with clamping structure (14s) and syndeton (12s).

11. according to one of claim 1 to 3 described tool holder, it is characterized in that sleeve (20g, h-k, q, r, u-x, bb, cc, dd) be bearing on the tool holder and tensioning shaft comprises a shaft part (18) at its each end (26,32), 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.

12., it is characterized in that sleeve (20g according to the described tool holder of claim 11, h, i, q, r, w x) is bearing on the radially-protruding annular lip (43) that particularly is bearing in syndeton (12) on the syndeton (12) with the one axial end, and is bearing in the member (56 that can axially tighten with respect to syndeton with its other end, 56n, 58,80,95) on the annular convex shoulder.

13., 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 12.

14., it is characterized in that described annular convex shoulder is formed in tensioning shaft, and (18h, i) last and this tensioning shaft is threadedly connected to the zone of syndeton according to the described tool holder of claim 12.

15., it is characterized in that the described other end of sleeve (20g) is bearing on the annular convex shoulder of the instrument (80) that is fixed in the clamping structure according to the described tool holder of claim 12.

16., it is characterized in that annular convex shoulder (79r) is formed on the clamping structure (14) and this clamping structure can be fixed on the tensioning shaft (18r) with moving axially according to the described tool holder of claim 12.

17. according to the described tool holder of claim 11, it is characterized in that, sleeve (20v) is bearing on the syndeton (12) with the one axial end, be bearing in especially on the radially-protruding annular lip (43) of syndeton (12), and hold on tensioning shaft (18v) with its other end sealed twelve Earthly Branches that rub.

18. according to one of claim 1 to 17 described tool holder, it is characterized in that, sleeve (20b, f-s, u-z, aa-cc) have one to its external diameter that increases gradually in abutting connection with the end of syndeton (12) over there or/and internal diameter.

19., it is characterized in that sleeve (20o) comprises a plurality of sleeve shells (67,68) that are provided with one heart mutually according to one of claim 1 to 18 described tool holder.

20., it is characterized in that sleeve shell (67,68) is adjacent at least mutually according to the described tool holder of claim 19 in a segmentation of its axial length.

21., 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 claim 19 or 20 described tool holders.

22. according to one of claim 1 to 21 described tool holder, it is characterized in that, radially at sleeve (20p, aa) form an annular space (66) and between the shaft part (18), wherein fill up material, particularly flowable material or plastically deformable or a flexible material that is under the pressure.

23. according to the described tool holder of claim 22, it is characterized in that, sleeve (20p, aa) each axial end tension and closely be connected in tool holder (10), particularly by friction welding, 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, particularly flexible material under the pressure.

24., it is characterized in that according to claim 22 or 23 described tool holders, pressure change device (76) is set, can change the pressure of material in annular space (66) whereby.

25. according to one of claim 1 to 24 described tool holder, it is characterized in that shaft part (18) or sleeve (20) are stressed with regard to these parts, be subjected to the parts of pulling force to carry out axially mounting with respect to another via a damping piece (59).

26., it is characterized in that (20v-z bb) is adjacent to the circumference of tensioning shaft (18) to sleeve at least in a segmentation of its axial length according to one of claim 1 to 25 described tool holder.

27. according to the described tool holder of claim 26, it is characterized in that, sleeve (20v-z, bb) 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).

28. according to claim 26 or 27 described tool holders, it is characterized in that, sleeve (20v-z, bb) and tensioning shaft (18v) at least the friction locked portions (89) a part in have the slight conical shape that cooperatively interacts.

29. according to one of claim 26 to 28 described tool holder, it is characterized in that, sleeve (20v-x, bb) 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.

30. according to the described tool holder of claim 29, it is characterized in that, vertically friction locked portions (89) and between the other end of tool holder (10v) upper support at the circumference of tensioning shaft (18) and sleeve (20v) but inner circumferential surface between at least one damping ring of being made by the material of elastic compression (94) is set.

31. according to one of claim 1 to 30 described tool holder, 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, c, f-s, v-z, aa-dd) the end (32) at annular convex shoulder (41) upper support constitutes conical portion, and this conical portion is tapered away from annular convex shoulder (41) vertically.

32., it is characterized in that conical portion covers at least one damping ring (94) according to the described tool holder of claim 31.

33., it is characterized in that sleeve is vertically with the pressure bias voltage according to claim 31 or 32 described tool holders.

34., it is characterized in that sleeve (20x) comprises the wavy spring part (97) of an axial elasticity according to one of claim 1 to 33 described tool holder.

35. according to one of claim 1 to 34 described tool holder, 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).

36. according to the described tool holder of claim 35, 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.

37., it is characterized in that adjusting element (104) is the plunger screw that affacts on the pressure medium (101) according to claim 35 or 36 described tool holders.

38. according to one of claim 35 to 37 described tool holder, 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), particularly is bearing on the removable safety collar (95bb) that is fixed on the tensioning shaft (18).

39. according to one of claim 1 to 38 described tool holder, it is characterized in that, sleeve (20cc) has radial spacing ground to surround shaft part (18) 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).

40. according to the described tool holder of claim 39, 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.

41., it is characterized in that one of them baffle ring (117dd) can be offset vertically according to the described tool holder of claim 40, in order to change the bias voltage of damping element (112).

42. according to the described tool holder of claim 41, 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.

43., it is characterized in that annular space (111) has cone shape according to the described tool holder of claim 39 to 42.

44., 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 43.

45. according to one of claim 1 to 44 described tool holder, it is characterized in that, sleeve (20m, n, o) in a segmentation of its axial length, there is radial spacing ground to surround shaft part (18) at least and forms an annular space and go up vibration damping mass (65m is set in this annular space at shaft part (18), n, o).

46., it is characterized in that (65m, n are movably along shaft part (18) o) to the vibration damping mass according to the described tool holder of claim 45.

47., it is characterized in that two parts are that tensioning shaft is made of different materials with tensioning apparatus according to one of claim 1 to 46 described tool holder.

48. tool holder according to claim 47, it is characterized in that one of them parts particularly sleeve (20) are made of the plastics or the carbon fiber reinforced plastics of carbide alloy or heavy metal or metal matrix composite materials or pottery or plastics, particularly glass fibre enhancing in the zone of tensile force at its transmitter shaft at least.

49., 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 one of claim 1 to 48 described tool holder, 22a, h, i, q, r, s, v-z, aa-gg, 24,24a-i, n, q, r, v-z aa-gg) is bearing on another of two parts.

50., it is characterized in that (24v-z bb) 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 49.

51. according to claim 49 or 50 described tool holders, it is characterized in that, and seam (22,22a, h, i, q, r, s, v-z, aa-dd, 24,24a-i, n, q, r, w-z aa-gg) is arranged between two surfaces that axially are close to each other of two parts.

52. according to one of claim 49 to 51 described tool holder, it is characterized in that, between the surface of two formation seams, damping material layer (59 be set; 59t).

53. according to one of claim 49 to 52 described tool holder, 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.

54. according to the described tool holder of claim 53, it is characterized in that, be provided with respectively on the two ends of sleeve in the surface that forms seam and the zone of sleeve by the circumferential surface of another parts centering radially at two ends.

55., it is characterized in that the circumferential surface of described another parts is adjacent to the circumferential surface of sleeve with press-fit manner radially according to claim 53 or 54 described tool holders.

56., it is characterized in that the circumferential surface of described another parts is at the regional inner radial surrounded sleeve of at least one axial end portion of sleeve according to one of claim 53 to 55 described tool holder.

57., it is characterized in that the circumferential surface of described another 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 56.

58. according to claim 56 or 57 described tool holders, it is characterized in that, in the zone of at least one end of sleeve (20ff), especially in the zone of its end (26ff) in abutting connection with clamping structure (14ff), two parts described another at the circumferential surface of surrounded sleeve (20ff) radially by an axial covering joints, same in the ring of described another parts of surrounded (119ff) formation radially.