EP2001625A1 - Dispositif de serrage pour outils ou pieces en rotaion - Google Patents

Dispositif de serrage pour outils ou pieces en rotaion

Info

Publication number
EP2001625A1
EP2001625A1 EP07723576A EP07723576A EP2001625A1 EP 2001625 A1 EP2001625 A1 EP 2001625A1 EP 07723576 A EP07723576 A EP 07723576A EP 07723576 A EP07723576 A EP 07723576A EP 2001625 A1 EP2001625 A1 EP 2001625A1
Authority
EP
European Patent Office
Prior art keywords
receptacle
pressure
clamping device
pressure chambers
clamping
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07723576A
Other languages
German (de)
English (en)
Inventor
Rüdiger HABERLAND
Kai Schmidt
Guido SCHÜLER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Technische Universitat Kaiserlautern
Technische Universitat Kaiserslautern
Original Assignee
Technische Universitat Kaiserlautern
Technische Universitat Kaiserslautern
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Technische Universitat Kaiserlautern, Technische Universitat Kaiserslautern filed Critical Technische Universitat Kaiserlautern
Publication of EP2001625A1 publication Critical patent/EP2001625A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control
    • B23B31/02—Chucks
    • B23B31/24—Chucks characterised by features relating primarily to remote control of the gripping means
    • B23B31/30—Chucks characterised by features relating primarily to remote control of the gripping means using fluid-pressure means in the chuck
    • B23B31/305—Chucks characterised by features relating primarily to remote control of the gripping means using fluid-pressure means in the chuck the gripping means is a deformable sleeve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control
    • B23B31/40—Expansion mandrels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2240/00—Details of connections of tools or workpieces
    • B23B2240/08—Brazed connections
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2240/00—Details of connections of tools or workpieces
    • B23B2240/16—Welded connections
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2240/00—Details of connections of tools or workpieces
    • B23B2240/21—Glued connections

Definitions

  • the invention relates to a clamping device for a rotatable about a rotation axis tool or workpiece according to the preamble of claim 1.
  • Generic clamping devices are used to attach tools or workpieces to tool spindles. They are thus part of machine tools with which, for example, a machining of the workpiece by turning, milling, drilling or grinding is achieved. In this case, either the tool can perform a rotary movement with a stationary workpiece or vice versa. Due to the development towards ever higher speeds of the tool spindles and thus of the machining tools are such machine tools in addition to the normal machining especially for micro and ultra precision cutting, as at high speeds despite small tool heads high cutting speed and machine performance is given. In combination with high-resolution displacement measuring systems, molds for micro-injection molding, hot stamping or electroplating methods, as well as masks for screen printing, but also more complex structures such as, for example, can be used. B. microturbines or Mikrofluidkanäle with a dimensional accuracy of 10 ⁇ 5 m achieve. A trend towards producing ever finer microstructures is unmistakable.
  • the clamping accuracy with which a tool or workpiece is mounted in the receptacle of the spindle is of decisive importance for its concentricity.
  • the receptacle must ensure that the machining tool or workpiece is clamped centrally and coaxially to the axis of rotation.
  • Known recordings have this collets, jaw chuck, hydraulic or thermal feed.
  • misalignments cause an imbalance, which has a negative effect on the precision of the workpiece machining and increases the tool wear, especially in connection with high speeds.
  • this process is repeated after each tool change with the appropriate amount of work.
  • clamping errors can be the cause of asymmetric stress on the cutting edges, which in turn leads to excessive wear and resulting reduced tool life and frequent tool changes.
  • the Dehnspannwerkmaschine comprises a rotatably connected to the spindle body, which has a cylindrical opening in the axis of rotation of the spindle.
  • a Dehnbüchse is used, the geometry of which with respect to the opening is such that the beginning and end of the expansion close circumferentially sealed to the inner wall of the axial opening.
  • the intermediate region has a smaller wall thickness, thereby creating an annular space surrounding the sleeve.
  • the annular space is acted upon by a pressure medium, which leads to a deformation of the expansion sleeve radially inwardly as a result and thus causes a large-scale clamping of the tool shank in the main body on all sides.
  • a similar Dehnspannwerkmaschine represents the chuck disclosed in DE 296 14 727 U1.
  • the chuck consists essentially of a hollow-cylindrical clamping part with an axial receiving bore for the shaft of the machining tool.
  • the clamping part has in the region of the receiving bore to a surrounding annular chamber, which is the front side each sealed.
  • the annular chamber is filled with a pressure medium and also with a pressure medium filled channel connected to a pressure-generating actuator.
  • a pressure can be initiated in the annular chamber, which leads to a radial curvature of the inner circumference of the receiving bore to the axis of rotation.
  • the outer circumference of the clamping part bulges radially outwards, so that in this way another machining tool can be fastened to the chuck body.
  • Both clamping devices are characterized by a receiving bore on all sides and a large area surrounding annular space, the receiving bore facing partition for fixing the tool shaft is deformed by pressurizing radially to the tool shank out.
  • the concomitant statically indeterminate load condition in the receiving bore requires high pressures to generate a sufficient clamping force.
  • the production of an annular space is relatively expensive, since this consists of at least two components which are connected to one another via joining processes.
  • the thin wall of the annular space for recording due to its production always has irregularities that are a hindrance to a centric tension.
  • DE 199 26 152 A1 From DE 199 26 152 A1 also a chuck for a tool spindle is known, which, however, fundamentally different from the above-described devices.
  • the chuck disclosed in DE 199 26 152 A1 is attached to the tool-side end face of a tool holder, which in turn is connected to the spindle of a machine tool via a steep taper.
  • the chuck has a central bore for receiving the tool shank.
  • the receiving bore is surrounded by a plurality of axially parallel around the receiving bore arranged around radial slots.
  • the radial slots are characterized by a radial main extension direction, whereby circumferentially acting expansion surfaces are formed.
  • the present invention seeks to provide a clamping device with respect to known devices higher clamping accuracy.
  • the essence of the invention is the clamping of the shank of a machining tool or workpiece for its attachment to a tool spindle not over its entire circumference, but only partially reach.
  • the receptacle needs to be deformed during clamping of the tool only over a partial area, the required clamping force is achieved even at relatively low pressure in the pressure chambers.
  • Another advantage results from the inventive design of the pressure chambers.
  • the arrangement according to the invention of a plurality of axially parallel pressure chambers along the receptacle or pressure chambers extending radially or tangentially to the receptacle leads to no appreciable constructive weakening of the cross section of the tensioning device.
  • a clamping device according to the invention thus has a higher rigidity over known devices and thereby enables a better concentricity.
  • the resulting from the design of the invention stability reserves can also be used for a further reduction in the dimensions of the clamping device with the advantage of obtaining extremely compact machine tools with which also previously held inaccessible places on workpieces can be edited. This is of particular importance with regard to the production of high-precision microstructures.
  • the basic body of the clamping device possessing the coaxial receptacle is monolithic.
  • the body of the part of the clamping device on the one hand has force-transmitting coupling surfaces for rotational drive and on the other coupling surfaces for clamping the tool or workpiece. This does not exclude that such a body can be supplemented to form the pressure chambers to other parts.
  • Such a base body can be produced in one clamping so that inaccuracies of the coupling surfaces due to multiple clamping of the main body or subsequent insertion of tool holding parts into the basic body, which form the tool holder, are avoided.
  • FIGS. 2 and 3 are perspective sectional views through a tensioning device according to the invention.
  • FIG. 4 shows a longitudinal view of a tensioning device according to the invention
  • FIG. 5 shows a longitudinal section through the device shown in FIG. 4 along the line V-V
  • FIG. 6 shows a cross section through the device shown in FIG. 4 along the line VI-VI, FIG.
  • FIG. 7 shows a cross section through the device shown in FIG. 4 along the line VII-VII on a larger scale
  • Figures 8 a to h are cross-sections of further embodiments of
  • 9 and 10 are longitudinal sections through further embodiments of the invention with different longitudinal geometry of the pressure chambers
  • FIG. 11 shows a cross section through a clamping device according to the invention with alternative pressure generation in the pressure chambers
  • FIGS. 12 a and b show a longitudinal and cross section through a tensioning device according to the invention with an alternative pressure chamber system
  • FIGS. 13 a and b show a longitudinal and cross section of a further embodiment a tensioning device according to the invention as a mandrel
  • FIGS. 14 and 15 show a cross section and a longitudinal section through a further embodiment of the invention with a two-part main body
  • FIG. 16 shows a cross section of an embodiment of the invention with a pressure chamber and a receptacle with two reference surfaces
  • FIG. 17 shows a cross-section of an embodiment of the invention with two pressure chambers and a receptacle with a reference surface
  • Figures 18 and 19 a cross section and longitudinal section through further
  • FIGS. 20 and 21 show a cross-section and a longitudinal section through a variant of the device shown in FIGS. 18 and 19 with independent pressurization of the individual pressure chambers;
  • Figure 22 is a cross-section through another embodiment of the invention with tangentially arranged for receiving pressure chambers and
  • Figure 23 is an oblique view of another embodiment of the invention with independent pressurization of the individual pressure chambers.
  • FIG. 1 shows an overview of the invention.
  • a work spindle 1 which rotates in operation about the axis of rotation 2 and on which a clamping device 3 with its perpendicular to the axis of rotation 2 extending clamping surface is rotatably mounted.
  • a machining tool 4 in the form of a milling cutter can be seen in the axis of rotation 2.
  • the tensioning device 3 has, as an essential component, a monolithic basic body 5 with a stepped cylinder Shape whose outer diameter gradually decreases from the tool-distal end to the tool-near end. This results in a first longitudinal section 6 with a large diameter, the free axial end of which forms the clamping surface to the work spindle 1 and to which a middle longitudinal section 7 of smaller diameter and a further longitudinal section 8 with a small diameter adjoins.
  • the longitudinal section 6 has circumferentially close to three circumferentially uniformly distributed axially parallel holes 9, which serve to accommodate fixing screws not shown for rotationally fixed fixing of the base body 5 on the work spindle 1.
  • a receptacle 10 in the form of a blind hole, which extends into the section 6.
  • the machining tool 4 can be used with its shaft 11 with match play.
  • the wall of the receptacle 10 thus represents the machining tool 4 aligning and at the same time force-transmitting surface to the shaft 11 of the machining tool 4.
  • Such a base body 5 can be produced in only one clamping, so that the clamping surface of the main body 5 to the work spindle 1 and the receptacle 10th are aligned exactly perpendicular to each other.
  • the receptacle 10 is surrounded at a narrow radial distance by three axially parallel, tubular pressure chambers 12, which are arranged with a uniform circumferential spacing on a common circumferential circle.
  • the pressure chambers 12 are formed by blind holes, which extend from the tool-distal end to approximately the tool-near end of the main body 5.
  • each pressure chamber 12 is formed by a threaded portion 13 whose diameter is slightly larger than the cross section of the rest of the pressure chamber 12.
  • the threaded portion 13 is intended to receive a sealing washer 14 which allows a pressure-tight closing of the pressure chamber 12 by means of a sealing screw 15 ,
  • the pressure chambers 12 and receptacle 10 overlap over approximately the entire length of the receptacle 10, wherein the overlapping region defines the clamping region 16 for the tool 4 (see FIG. 5).
  • the main body 5 forms due to the inventive arrangement of the pressure chambers 12 for receiving 10 narrow, thin-walled dividers with less Strength, which act as deformation zones 17 when pressurized (see Figure 7). Due to the circular shape of the pressure chambers 12 and 10 receiving the deformation zones 17 have a double-concave cross-section and extend strip-shaped over the entire clamping portion 16 axially parallel to the rotation axis 2. Other cross sections of the deformation zones 17 result from varying the cross sections of the pressure chambers 12 which later under Figure 8 is detailed.
  • a radially extending branch channel 18 is also formed, which extends from the outer periphery of the body 5 at a sufficient axial distance to the receptacle 10 on the axis of rotation 2 away to the pressure chamber 12 and cuts them.
  • the branch channel 18 in the form of a stepped bore has the largest diameter on the input side and is formed there by a threaded portion 19, to which a sealing portion 20 connects radially inward (see FIG. 3).
  • the stepped bore serves to receive a sealing and pressure generating device 21, which is composed in detail of a sealing piece 22, a pressure piece 23 and a pressure pin 24.
  • the seal piece 22 is arranged as intended in the sealing portion 20 and seals with its annular flange relative to the threaded portion 19 from.
  • the pressure piece 23 in the threaded portion 19 can be screwed until it presses the annular flange of the seal piece 22 against a corresponding annular surface on the base body 5.
  • the pressure pin 24 can be screwed, whose radially inner end is piston-shaped and can be moved in the seal piece 22 by a screw axially in the branch channel 18.
  • the tool 4 is inserted with its shaft 11 in pressureless pressure chambers 12 axially into the receptacle 10 to the bottom. Subsequently, by screwing in the pressure pin 24, a piston movement in the sealing piece 22 in the direction of the axis of rotation 2 is performed, which leads to a uniform pressure generation in the pressure chambers 12 due to the concomitant reduction in volume in the branch channel 18. Due to the small thickness of the material in the region of the deformation zones 17, the pressure causes an elastic deformation of the deformation zones 17 in the radial direction towards the axis of rotation 2 with otherwise unchanged cross section of the main body 5.
  • the thereby adjusting statically determined clamping state allows a self-centering with high precision clamping of the tool shank 11 in the base body 5 and thus leads to an extremely high concentricity.
  • FIGS. 8 a to 8 h show different cross-sectional and arrangement variants of the pressure chambers 12, wherein different variants in number and arrangement of the pressure chambers 12 can of course be combined.
  • FIG. 8a differs from that described above only by an increase in the number of pressure chambers 12.
  • Four pressure chambers 12 are shown which surround the receptacle 10 in a symmetrical arrangement and thus form four deformation zones 17. This results in a simply statically indefinite clamping state, which allows a very high clamping accuracy at a slightly higher clamping force.
  • the embodiment according to FIG. 8b shows pressure chambers 12 with a cross-sectional shape deviating from the circular shape.
  • the pressure chambers 12 have an oval cross section, wherein the main axis of the longitudinal extension direction is tangential to the receptacle 10. This results in relatively large tangentially extending pressure surfaces 25, which lead even at low pressure to deformation of the deformation zones 17 with high, radially acting clamping force.
  • the number of pressure chambers 12 is five in the embodiment shown in Figure 8 b, with a smaller or higher number is conceivable.
  • FIG. 8 c A modification of the embodiment shown in Figure 8 b can be seen in Figure 8 c.
  • the pressure chambers 12 shown there have a curved oval cross-section, wherein the curvature of the main axis of the oval counter to the curvature of the receptacle 10 extends. In this way, an approximately line-shaped deformation zone 17 is generated at relatively low pressure.
  • the embodiment of the invention shown in FIG. 8 d shows an alternative oval cross-sectional shape in which the main axis of the oval has the same curvature sense as the receptacle 10.
  • a clamping of the tool shaft 1 1 takes place over a larger peripheral area, whereby a strip-shaped deformation zone 17 with a larger contact area and consequently higher clamping forces sets.
  • the embodiment shown in Figure 8 e of the invention has pressure chambers 12 with triangular cross-section, wherein the base of the pressure chamber 12 of the receptacle 10 faces. In this way, here too large tangential pressure surfaces 25, which cause a high clamping force at an already low pressure build-up in the pressure chambers 12.
  • the embodiment of the invention according to Figure 8 f has pressure chambers 12 with a semicircular cross section, which leads to a lower chamber volume compared to the pressure chambers 12 of the embodiment described in Figures 1 to 6.
  • the pressure chambers 12, shown in FIG. 8 g, of yet another embodiment of the invention have a rectangular cross-section, the longitudinal direction of which extends tangentially to the receptacle 10. Again, large tangential aligned pressure surfaces 25 arise with the advantages already described.
  • FIG. 8 h A further embodiment of the invention is described in FIG. 8 h, whose pressure chambers 12 are slit-shaped and follow the accommodation of the receptacle 10 at least in their middle region.
  • Each pressure chamber 12 is associated with a supply bore 26 which is offset radially outwards relative to the pressure chamber 12 and is connected via a supply web 27 to the pressure chamber 12.
  • Such complex cross sections are advantageously produced by erosion.
  • the scope of the invention also includes embodiments with pressure chambers 12 whose cross-section is variable in the longitudinal direction.
  • a preferred embodiment of the invention in this sense has pressure chambers 12 which have a larger cross-section both at the beginning and at the end of the clamping region 16 than in the region between them. This results in an initial area 28 and end portion 29 smaller thickness of the deformation zone 17, so that there elastic deformation occurs easier and faster than in the remaining area. As a result, this leads to increased clamping forces at the beginning 28 and end 29 of the clamping area 16 and thus to a statically determined clamping state, not only in cross-section, but also in the longitudinal direction of the receptacle 10. In this way, extremely high clamping accuracies are possible with a correspondingly precise concentricity.
  • FIG. 10 also shows that the pressure chambers 12 can also extend over the entire main body 5. This is the case, for example, in the case of cross-sectional shapes of the pressure chambers 12, which are produced by erosion and subsequently sealed pressure-tight on both sides.
  • FIG. 11 shows an embodiment of the invention with an alternative system for generating pressure. While in the embodiment according to FIGS. 1 to 7 the functions pressure generation and pressure supply in the branch channel 18 are realized combined, the embodiment according to FIG. 11 provides for a separation of these functions.
  • a radial branch channel 30 is introduced in section 6 of the main body 5, which intersects two pressure chambers 12 tangentially, the third pressure chamber 12 passes through and ends in the region of the base body 5 near the periphery.
  • a threaded hole in the initial region is a closing of the branch channel 30, for example analogous to the closure of the receptacle 10 by means of sealing washer 14 and sealing screw 15 is possible.
  • the puncture channel 30 is used for uniform supply of all pressure chambers 12 with a pressure medium.
  • a tangential branch channel 31 extends from the edge of the main body 5 to the end of the branch channel 30 with which it intersects. This results in a communicating system between stitch channel 30, stitch channel 31 and pressure chambers 12.
  • the beginning of the branch channel 31 is intended to receive a sealing and pressure generating device 21, as already described in Figures 1 to 6, so that what is said there.
  • This embodiment of the invention allows a larger displacement for the piston of the sealing and pressure generating device 21, which therefore finds advantageous use in clamping with greater elastic deformation.
  • Figures 12 a and b relate to an embodiment of the invention, in which the pressure chambers 12 are connected to each other via a rotationally symmetrical to the axis 2 cavity 32.
  • the cavity 32 is formed from the end face 33 of the base body 5 with an axial depth which leads to the intersection with the inner end of the pressure chambers 12. In the region facing the end face 33, the cavity 32 is turned out to receive a cover 34 with a larger diameter, which is tensioned by means of screws engaging in the threaded bores 35 against the annular surface 36 formed by the gradation and thus forms a pressure-tight closure.
  • a radial branch channel 37 leads from the outer periphery of the section 6 of the main body 5 to the cavity 32.
  • the sealing and pressure generating device already described in FIGS. 1 to 7 closes off the stitch channel 37 to the outside.
  • FIGS 13 a and b make it clear that an implementation of the invention is also possible on a mandrel on which a machining tool or workpiece with a hollow cylindrical shaft 38 is inserted.
  • a corresponding embodiment of the invention has a main body 5, the tool-near longitudinal portion 8 forms with its peripheral surface 39, the receptacle for the inner wall 40 of the tool shank 38.
  • pressure chambers 12 are formed with uniform circumferential distance and lying on a circumferential circle axially parallel to the axis of rotation 2 such that the pressure chambers 12 extend in the tool-related longitudinal section 8 with only a small distance to the peripheral surface 39.
  • the main body 5 in the area between the pressure chambers 12 and the circumferential surface 39 again forms narrow, thin-walled deformation zones 41 which elastically deform radially outward when the pressure chambers 12 are pressurized, thereby tensioning the tool shank 38.
  • FIGS. 14 and 15 show an embodiment of the invention which is advantageous with regard to the manufacturing accuracy of the pressure chambers 12.
  • This has a main body 5 'with a longitudinal section 6' with a large diameter to form a clamping surface for coupling to the tool spindle 1.
  • the longitudinal section 6 ' integrally joins a coaxial thin-walled receiving cylinder 45 with integrated receptacle 10 for the tool shank 11.
  • the cylindrical outer circumferential surface of the receiving cylinder 45 is up to the start and end of three with uniform angular distance of 120 ° arranged peripheral sections ground flat. This results in the outer jacket of the receiving cylinder 45 extending in the longitudinal direction, strip-shaped planar surfaces 47. In the region of the flat surfaces 47 thus resulting Materialausschreibn 11, for receiving 10, which are deformed when pressurized radially to the axis of rotation 2.
  • a cylindrical fitting sleeve 46 is pushed onto the receiving cylinder 45 and glued to this pressure-tight, welded or soldered.
  • the flat surfaces 47 of the receiving cylinder 45 and the inner circumference of the fitting sleeve 46 thus form the pressure chambers 12 in the interface between these components.
  • one or more axial channels 48 are provided, each of which is provided with a pressure generating device 49.
  • a pressure generating device 49 it is also possible to provide only one pressure generating device 49 and to connect all the pressure chambers 12 to one another with a common pressure chamber system.
  • the axial channels 48 can thereby completely penetrate the longitudinal section 6 ', the resulting openings being closed on the front side of the longitudinal section 6' in the region of the receiving cylinder 45 in the course of pushing on the fitting sleeve 46 as a result of its wall thickness.
  • this embodiment of the invention is in addition to the already mentioned high manufacturing accuracy in the extremely compact by this manufacturing size.
  • spindle systems are possible thanks to the invention, which are also suitable for processing difficult to access areas of a workpiece.
  • this embodiment of the invention is characterized by a geometry of the pressure chambers 12, which reduces voltage spikes in the material as a result of the continuous transitions in the flat surfaces 47 and thus increases the overall durability of the clamping device.
  • FIG. 1 Another embodiment of the invention is shown in FIG.
  • the basic body 5 shown there largely corresponds to that already described above, differences being mainly due to the receptacle 10 'arranged in the section 7, whose cross section deviates from the circular shape.
  • the cross section of the receptacle 10 ' is composed essentially of a semicircular peripheral portion 50 and the two reference surfaces 51 and 52, which preferably intersect at an angle of 45 °. This results in a symmetrical plane 53 mirror image of the receptacle 10 '.
  • a pressure chamber 12 which forms the deformation zone 17 with the semicircular peripheral portion 50 of the receptacle 10'.
  • the pressurization of the pressure chamber 12 can be carried out according to the possibilities already described in other embodiments.
  • FIG. 17 A modified embodiment of the invention is disclosed in FIG. 17.
  • the receptacle 10 "shown there again has a cross section deviating from the circular shape with a U-shaped peripheral portion 54 whose leg ends are connected by the reference surface 55. This in turn results in a tangential arrangement of the reference surface 55 and a symmetrical plane 56 mirror image embodiment of the recording 10 ".
  • pressure chambers 60 which, starting from the peripheral surface of the portion 7 of the main body 5 in radial Extend direction towards the receptacle 10 and end at a short distance in front of the receptacle 10. This results in between the bottom of each pressure chamber 60 and the circumference of the receptacle 10 each have a deformation zone 17 with approximately punctiform or oval extent.
  • the pressure chambers 60 shown in FIGS. 18 and 19 each have a pressure-resistant closure 61 in the peripheral region of the main body 5, as already described in connection with previous embodiments.
  • the arrangement of the pressure chambers 60 preferably takes place in two with respect to the axis of rotation 2 at an axial distance from each other and perpendicular to the axis of rotation 2 extending clamping planes 62 and 63, of which the clamping plane 63 coincides with the sectional plane XIIX and thus corresponds to the representation in FIG. It can be seen that the three pressure chambers 60 are arranged at a uniform angular distance of 120 ° to each other.
  • the course of the clamping planes 62 and 63 within the main body 5 is selected such that the deformation zones 17 result in the beginning and end regions of the receptacle 10. Additional clamping planes, for example in the middle region of the receptacle 10, are within the scope of the invention and can serve to increase the clamping force.
  • an axial branch channel 64 is used, which intersects or penetrates the pressure chambers 60 succeeding one another in both clamping planes 62 and 63.
  • the branch channel 64 is provided with a pressure generating device 65, which has already been described in FIGS. 2 and 3 in the first exemplary embodiment.
  • all pressure chambers 60 form a corresponding pressure chamber system analogous to that shown in FIGS. 12a and b Embodiment.
  • the puncture channels 61 can open into a coaxial cavity, to which a radial pressure branch for generating specific radial pressure is connected.
  • FIGS. 20 and 21 A further modification of the invention is shown in FIGS. 20 and 21. This differs from that described in FIGS. 18 and 19 only in that the individual radial pressure chambers 60 are not interconnected, that is to say they do not form a communicating chamber system. Instead, each radial pressure chamber 60 has its own pressure generating device 65 in the region near the periphery for independent pressure generation in the individual pressure chambers 60, both in the clamping plane 62 and 63 analogous to the embodiment described in Figure 23.
  • FIG. 22 Another variant of the invention is shown in FIG. 22.
  • the difference to the above-described embodiment is that the pressure chambers 60 'are not radially aligned with the receptacle 10, but lead to formation of deformation zones 17 at a small distance to the receptacle 10 over.
  • this embodiment corresponds to those mentioned in FIGS. 18, 19 and 20, 21, in particular with regard to the number of pressure chambers, their arrangement in clamping planes and the different possibilities for generating pressure in the pressure chambers 60 '.
  • the advantage of this embodiment of the invention is inter alia that the deformation zones 17 are reduced in their extent substantially to a point, which can achieve very high Einspanngenaumaschineen.
  • the invention comprises variations of the pressure chambers 60 in number, it being possible analogous to the embodiments of Figs. 16 and 17, a radial or tangential pressure chamber 60, 60 'in conjunction with two reference surfaces or two Pressure chambers 60, 60 'in conjunction with a reference surface or more than three pressure chambers 60, 60' provide.
  • FIG. 23 shows this system in conjunction with axially directed pressure chambers 12.
  • the implementation of this idea in conjunction with radial pressure chambers 60 has already been described in FIGS. 20 and 21. Transfer to embodiments with tangential pressure chambers 60 'is also possible.
  • each stitch channel 65 has the pressure generating device described in FIGS. 2 and 3, consisting of sealing piece 22, pressure piece 23 and pressure pin 24.
  • the invention is not limited to the combinations of features disclosed within individual embodiments, but that in the context of the invention, combinations of individual features or feature groups of different embodiments lie among each other.
  • the mandrel shown in Figures 13a and b can of course also be combined with a pressure distribution system as described in Figures 12a and b, or the pressure chambers 12, 60, 60 'may have cross-sections as disclosed in Figures 8a-h vary in number. It is also possible to transfer the manner of pressure generation and pressure distribution in the pressure chambers 12, 60, 60 'from one embodiment to another without the scope of To leave invention.

Abstract

L'invention concerne un dispositif de serrage pour un outil (4, 38) ou une pièce qui peuvent tourner autour d'un axe de rotation (2), présentant un corps de base (5, 5') disposé coaxialement par rapport à l'axe de rotation (2) et doté à son extrémité située du côté de l'outil ou de la pièce d'un logement (10, 10', 10', 39) coaxial par rapport à l'axe de rotation (2) et qui présente pour le serrage de l'outil (4, 38) ou de la pièce un système à chambre sous pression qui a pour effet une déformation du logement (10, 10', 10', 39) sous l'action d'un fluide sous pression. Pour obtenir une plus haute précision de centrage, l'invention propose que le système de chambre sous pression comprenne au moins une chambre sous pression (12; 60; 60') disposée uniquement dans certaines parties à une petite distance du logement (10; 10'; 10'; 39) de telle sorte que la pression exercée par la ou les chambres sous pression (12; 60; 60') entraîne que la zone située entre la ou les chambres sous pression (12; 60; 60') et le logement (10; 39) forme une zone de déformation (17; 41) qui se déforme radialement en direction du logement (10; 39).
EP07723576A 2006-03-24 2007-03-26 Dispositif de serrage pour outils ou pieces en rotaion Withdrawn EP2001625A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610013662 DE102006013662A1 (de) 2006-03-24 2006-03-24 Spannvorrichtung für rotierende Werkzeuge oder Werkstücke
PCT/EP2007/002629 WO2007110213A1 (fr) 2006-03-24 2007-03-26 Dispositif de serrage pour outils ou pièces en rotation

Publications (1)

Publication Number Publication Date
EP2001625A1 true EP2001625A1 (fr) 2008-12-17

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EP07723576A Withdrawn EP2001625A1 (fr) 2006-03-24 2007-03-26 Dispositif de serrage pour outils ou pieces en rotaion

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Country Link
EP (1) EP2001625A1 (fr)
DE (1) DE102006013662A1 (fr)
WO (1) WO2007110213A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012111456C5 (de) * 2012-11-27 2017-07-13 Kennametal Inc. Hydraulisches Dehnspannfutter und Verfahren zur Herstellung eines solchen Dehnspannfutters
DE102015117590B3 (de) * 2015-10-15 2017-03-09 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Spanneinrichtung zum Fixieren eines Werkzeugs in einer Werkzeugmaschine
GB2551996B (en) * 2016-07-05 2021-09-15 Fives Landis Ltd Tool mounting assemblies and methods of operation thereof
DE102016119752A1 (de) * 2016-10-17 2018-04-19 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Hydraulische Dehnspanneinrichtung
DE102017209076A1 (de) * 2017-05-30 2018-12-06 MAPAL Fabrik für Präzisionswerkzeuge Dr. Kress KG Hydrodehnspannfutter
DE102018108306A1 (de) * 2018-04-09 2019-10-10 Schaeffler Technologies AG & Co. KG Hydrodehnspannwerkzeug
DE102019111281A1 (de) * 2019-05-02 2020-11-05 Haimer Gmbh Hydraulisch spannbarer Werkzeug-/Werkstückhalter
CN114749968B (zh) * 2022-03-01 2023-06-06 深圳大学 刀具夹具

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE745845C (de) * 1939-12-02 1944-05-15 Hans Johann Hofer Einspannvorrichtung fuer Werkzeugmaschinen
DE1777257B2 (de) * 1965-03-03 1971-03-25 Hydraulischer spanndorn
US3592482A (en) * 1968-05-27 1971-07-13 Scully Jones Co Hydraulic chuck
DE3148677C2 (de) * 1981-12-09 1986-04-10 Carl Hurth Maschinen- und Zahnradfabrik GmbH & Co, 8000 München Vorrichtung zum lösbaren radialen und axialen Spannen eines mit einer mittigen Bohrung versehenen Werkzeugs oder Werkstücks auf einem Dorn od. dgl.
DE3909630A1 (de) * 1989-03-23 1990-09-27 Daimler Benz Ag Spannwerkzeug zum kraftschluessigen und hochpraezisen spannen von werkstuecken
JPH05285714A (ja) * 1992-04-14 1993-11-02 Fuji Seiko Kk ハイドロリックホルダ
DE19643311C1 (de) * 1996-10-21 1997-11-13 Conrad Apparatebau Gmbh Vorrichtung und Verfahren zum Halten und Bearbeiten von stab- oder rohrförmigen Werkstücken
SE516951C2 (sv) * 1999-03-30 2002-03-26 Sandvik Ab Hydraulisk chuck med deformerbar griphylsa samt fastspänningsmetod
DE20023140U1 (de) * 2000-02-16 2003-01-30 Schunk Gmbh & Co Kg Dehnspannwerkzeug
DE10125154B4 (de) * 2000-05-26 2012-01-19 Sterman Technische Systeme Gmbh Vorrichtung zum lösbaren Halten eines Werkzeuges sowie Spannhülse hierfür
DE10131480A1 (de) * 2000-07-07 2002-01-17 Svenska Prec Sverktyg Ab Eskil Hydraulverriegelung
US20020045521A1 (en) * 2000-10-16 2002-04-18 Hideki Mochida Spindle unit for a machine tool

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007110213A1 *

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