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WO2008054295A1 - Dispositif de serrage hydromécanique - Google Patents

Dispositif de serrage hydromécanique Download PDF

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Publication number
WO2008054295A1
WO2008054295A1 PCT/SE2007/000973 SE2007000973W WO2008054295A1 WO 2008054295 A1 WO2008054295 A1 WO 2008054295A1 SE 2007000973 W SE2007000973 W SE 2007000973W WO 2008054295 A1 WO2008054295 A1 WO 2008054295A1
Authority
WO
WIPO (PCT)
Prior art keywords
clamping device
piston
inner sleeve
annular piston
cooperating
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.)
Ceased
Application number
PCT/SE2007/000973
Other languages
English (en)
Inventor
Niclas Rosberg
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.)
ETP Transmission AB
Original Assignee
ETP Transmission AB
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 ETP Transmission AB filed Critical ETP Transmission AB
Publication of WO2008054295A1 publication Critical patent/WO2008054295A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • B23B31/10—Chucks characterised by the retaining or gripping devices or their immediate operating means
    • B23B31/117—Retention by friction only, e.g. using springs, resilient sleeves, tapers
    • B23B31/1171—Retention by friction only, e.g. using springs, resilient sleeves, tapers not used, see subgroups and B23B31/117
    • B23B31/1172—Retention by friction only, e.g. using springs, resilient sleeves, tapers not used, see subgroups and B23B31/117 using fluid-pressure means to actuate the gripping means
    • 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
    • B23B31/302—Hydraulic equipment, e.g. pistons, valves, rotary joints
    • 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
    • B23B31/10—Chucks characterised by the retaining or gripping devices or their immediate operating means
    • B23B31/117—Retention by friction only, e.g. using springs, resilient sleeves, tapers
    • B23B31/1177—Retention by friction only, e.g. using springs, resilient sleeves, tapers using resilient metallic rings or sleeves
    • B23B31/1178—Retention by friction only, e.g. using springs, resilient sleeves, tapers using resilient metallic rings or sleeves using fluid-pressure means to actuate the gripping means
    • 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
    • B23B31/10—Chucks characterised by the retaining or gripping devices or their immediate operating means
    • B23B31/12—Chucks with simultaneously-acting jaws, whether or not also individually adjustable
    • B23B31/20—Longitudinally-split sleeves, e.g. collet chucks
    • B23B31/201—Characterized by features relating primarily to remote control of the gripping means
    • B23B31/204—Characterized by features relating primarily to remote control of the gripping means using fluid-pressure means to actuate the gripping means
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F16D1/091—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces and comprising a chamber including a tapered piston moved axially by fluid pressure to effect clamping
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2222/00—Materials of tools or workpieces composed of metals, alloys or metal matrices
    • B23B2222/64—Nickel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2228/00—Properties of materials of tools or workpieces, materials of tools or workpieces applied in a specific manner
    • B23B2228/10—Coatings

Definitions

  • the present invention relates to a hydromechanical clamping device according to the preamble of claim 1.
  • WO 2004/007129A1 discloses a hydromechanical clamping device according to the preamble of claim 1 , which has the form of a chuck or a mandrel.
  • the clamping device is adapted to be with one end thereof mounted in a possibly rotary machining device, such as a drilling machine, a milling machine, a lathe machine etc. and with the other end to releasably hold a shaft tool, a work piece, a transition element or a similar object, such as a drill, a milling tool etc.
  • a drawback of the above-mentioned clamping device is that to be able to arrange connecting means for feeding of compressed fluid to the actuating pressure chamber and the deactuating pressure chamber on the same side of the clamping device, seen in the axial direction, a duct has to be provided through the inner sleeve or the outer sleeve, which makes it difficult to reduce the radial extension of the clamping device, thus making the clamping device radially unwieldy, and also increasing its weight.
  • Another drawback is that the presence of the duct causes problems of strength, which have to be compensated for by an increase of the material thickness of the clamping device or by load limits on the clamping device.
  • One object is to provide an improved or alternative clamping device.
  • a specific object is to provide a clamping device which is less unwieldy in the radial direction.
  • a further object is to provide a clamping device having a lower weight.
  • a hydromechanical clamping means comprising a fastening part adapted to be mounted in a machining device, a holder part adapted to releasably hold a tool shaft.
  • the holder part comprises an inner sleeve with an axial recess, intended to receive the tool shaft.
  • the inner sleeve and an outer sleeve define a chamber in which an annular piston is axially movable, the annular piston and one of the inner sleeve and the outer sleeve having cooperating conical surfaces, which in axial movement of the piston in a first direction are arranged to produce a radial compression of the inner sleeve and in axial movement of the piston in a second direction, opposite to the first direction, to allow a radial expansion of the inner sleeve.
  • the clamping device further comprises an actuating means arranged to produce a movement of the annular piston in said first direction, and a deactuating means arranged to produce a movement of the annular piston in said second direction.
  • the actuating means and the deactuating means are located, seen in the axial direction, on the same side of the annular piston.
  • the deactuating means can comprise a deactuating pressure chamber, which when pressurised produces said movement of the annular piston for unlocking the clamping device.
  • the actuating means can comprise an actuating pressure chamber, which when pressurised produces said movement of the annular piston for locking the clamping device.
  • pressure chamber is meant a space which when pressurised influences the activation of the clamping device.
  • the clamping device can further comprise a flange, which is joined to the annular piston and which separates said actuating pressure chamber from said deactuating pressure chamber.
  • the extension of the flange in the radial direction from a centre axis can be selected so as to obtain assembling and disassembling surfaces of suitable dimensions.
  • the flange can be integrated with the annular piston.
  • the flange can, for instance, be formed integrally with the annular piston.
  • the flange can have an assembling surface, which defines the actuating pressure chamber, and a disassembling surface, which defines the deactuating pressure chamber.
  • the assembling surface and the disassembling surface both have a radial extension from the centre axis, and can coincide with the extension of the flange in the same direction.
  • the disassembling surface is greater than the assembling surface, which results in a greater disassembling force than assembling force at the same pressure and which makes it possible to perform the disassembling operation at a lower pressure. Furthermore, a greater margin is obtained in this manner, since the pressure source does not have to be used to its maximum in connection with disassembly.
  • the assembling surface can have a greater area than a first cross- sectional area of the piston, which first cross-sectional area is located at a first end of a piston portion active against the inner sleeve and the outer sleeve, and is oriented in the same axial direction as the assembling surface.
  • the disassembling surface can have a greater area than a second cross-sectional area of the piston, which second cross-sectional area is located at a second end of a piston portion active against the inner sleeve and the outer sleeve, and is oriented in the same axial direction as the disassembling surface.
  • the actuating means can comprise an elastically compressible actuating means, which is arranged to produce said movement of the annular piston for locking the clamping device.
  • the inner sleeve can have at least one slot extending in said axial direction. By such slots, the force needed to produce the compression of the inner sleeve can be reduced.
  • a friction-modified surface can be provided on at least one of a surface of the annular piston cooperating with the inner sleeve, a surface of the annular piston cooperating with the outer sleeve, a surface of the outer sleeve cooperating with the piston and a surface of the inner sleeve cooperating with the piston.
  • a lubricating duct can be arranged on at least one of a surface of the annular piston cooperating with the inner sleeve, a surface of the annular piston cooperating with the outer sleeve, a surface of the outer sleeve cooperating with the piston and a surface of the inner sleeve cooperating with the piston.
  • the conical surface can consist of a contact surface between the inner sleeve and the annular piston.
  • the conical surface can consist of a contact surface between the outer sleeve and the annular piston.
  • Fig. 1 is a schematic sectional view of a first embodiment of a clamping device 1.
  • Fig. 2 is a schematic sectional view of a second embodiment of a clamping device 1 '.
  • Fig. 3 is a schematic sectional view of a third embodiment of a clamping device 1".
  • Fig. 4 is a schematic sectional view along the line A-A in Fig. 3 of the clamping device according to the third embodiment. Description of Embodiments
  • Fig. 1 is a schematic sectional view of an embodiment of a clamping device 1 , which is adapted to be mounted in a machine tool and to hold a shaft tool V.
  • the clamping device 1 thus has a fastening part P1 and a holder part
  • the fastening part P1 and the holder part P2 can be axially separate from one another, for example by being located at either end of the clamping device.
  • the fastening part P1 can be axially separate from one another, for example by being located at either end of the clamping device.
  • the material thicknesses shown in Fig. 1 are only schematic.
  • the thickness of the inner sleeve 2, the outer sleeve 3 and the piston 12 can be dimensioned according to the application in which the clamping means is to be used.
  • the contact surface 14 between the inner sleeve 2 and the piston 12 is a conical surface, so that a movement of the piston 12 in the direction D2 (to the left in Fig. 1) causes an expansion of the outer sleeve 3 and a compression of the inner sleeve 2.
  • the conical surface shown in Fig. 1 has a considerably greater conical angle than in a real application.
  • the conical surfaces have a conical angle such that they become self-locking.
  • the piston 12 has a flange 17, which projects radially from one end of the piston 12 and which has an assembling surface 7 and a disassembling surface 6 located on an opposite side of the flange 17.
  • the assembling surface 7 is part of a boundary surface of an actuating pressure chamber 5.
  • a radially projecting part 16 of the outer sleeve 3 forms yet another delimiting part of the actuating pressure chamber 5.
  • a portion of the piston forms a boundary surface of the actuating pressure chamber 5.
  • the disassembling surface 6 is part of a boundary surface of a deactuating pressure chamber 4.
  • a radially projecting part 15 of the inner sleeve 2 forms yet another delimiting part of the deactuating pressure chamber 4.
  • a portion of the outer sleeve located at the flange forms a boundary surface of the deactuating pressure chamber 4.
  • Connecting means 10, 11 for compressed fluid communicate via ducts
  • reference numeral P indicates the piston portion active against both the inner sleeve 2 and the outer sleeve 3, i.e. the piston portion engaged in the transmission of force between the tool and the clamping device.
  • Reference numerals E1 and E2 indicate the respective ends of the portion P.
  • the portion Pv indicates the whole portion of the piston active against the inner sleeve 2 and, thus, also against the tool V.
  • the fastening part is adapted to be mounted in a machining device in per se known manner.
  • the tool V is arranged so as to obtain some play (not shown) between the clamping device 1 and the tool V.
  • a force is applied to the assembling surface 7, which causes the annular piston 12 to move in the direction D2 (to the left in Fig. 1), whereby cooperation at the contact surface 14 of the piston 12 and the inner sleeve 2 causes the compression of the inner sleeve 22 and thus produces a contact pressure in the contact surface 22 between the inner sleeve 2 and the tool V.
  • the deactuating pressure chamber 4 can optionally be drained or unloaded in some other way when pressurising the actuating pressure chamber 5.
  • a force is applied to the disassembling surface 6, which causes the annular piston 12 to move in the direction D1 (to the right in Fig. 1), whereby the pressure in the contact surfaces 13, 14 between the piston 12 and the outer sleeve 3 and the inner sleeve 2, respectively, is unloaded, and thus also the pressure in the contact surface 22 between the inner sleeve 2 and the tool V, to allow removal of the tool V.
  • One or both contact surfaces 13, 14 between the piston 12 and, respectively, the outer sleeve 3 and the inner sleeve 2 can have a modified friction coefficient. The purpose of such a modification may be to obtain a low and even friction coefficient and/or to obtain the smallest possible difference between the static and the dynamic friction coefficients of the contact surfaces 13, 14.
  • friction-reducing coating As a non-limiting example of a friction-reducing coating, mention can be made of surface coating of so-called chemical nickel.
  • the contact surface 14 between the outer sleeve 3 and the piston 12 is instead a conical surface.
  • the actuating pressure chamber 5 and the deactuating pressure chamber 4, on the one hand, and the assembling surface 7 and the disassembling surface 6, on the other hand, are reversed, the conical surface tapering instead in the direction D1 , so that actuation or assembling is achieved by the left pressure chamber (reference numeral 5 in Fig. 2) being pressurised, and the deactuation or disassembling is achieved by the right pressure chamber (reference numeral 4 in Fig. 2) being pressurised.
  • This embodiment results in the assembling surface 7 being greater than the disassembling surface 6.
  • the contact surface 14 between the inner sleeve 2 and the piston 12, and the contact surface 13 between the outer sleeve and the piston 12 are both conical surfaces.
  • one or both of the contact surfaces 13, 14 are provided with lubricating ducts of the kind disclosed in US 4,616,948.
  • the pressurisation of the actuating and deactuating pressure chambers 5, 4, respectively, can be obtained by connecting a hydraulic pump.
  • movable pistons (not shown) arranged in flanges in the inner sleeve 2 and/or the outer sleeve 3 may be used to obtain pressurisation of the respective pressure chambers 4, 5.
  • the actuating pressure chamber (reference numeral 5 in Fig. 1 and Fig. 2) is replaced with an elastically resilient actuating means 18, which is arranged to preload the piston in the direction D2, i.e. to provide the locking of the clamping device 1 " without the use of any external means, such as a hydraulic pump.
  • the actuating means 18 can be a spring means, such as a cup spring, a helical spring, a gas spring, a compressible material or the like.
  • the deactuating pressure chamber 4 described with reference to Fig. 1 is still the same and works exactly as described in connection with Fig. 1 , i.e. when the deactuating chamber 4 is pressurised a movement of the piston is produced in the direction D1 , which unlocks the clamping device 1 ".
  • Fig. 3 also illustrates how the inner sleeve 2 may be provided with one or more longitudinal slots 25a, 25b, facilitating the contraction of the sleeve which arises when the piston 12 is moved and the clamping device 1 " is locked, thereby reducing the force required to lock/unlock the clamping device 1 ".
  • the slots are arranged in the part of the inner sleeve 2 that cooperates with the piston 12 and extend in the radial direction through the entirety of the inner sleeve 2.
  • the piston in conformity with the above-described slotted inner sleeve, is provided with one or more slots (not shown).
  • the slots (25a, 25b) described above are particularly suitable for use together with an elastically resilient actuating means 18, which is not capable of exerting a force as great as, for instance, that of the actuating pressure chamber 5 described with reference to Fig. 1.
  • the inner sleeves 2 in the clamping devices 1 , 1 ' described with reference to Fig. 1 and Fig. 2 can be provided with one or more such slots.
  • the gap between the inner sleeve 2 and the outer sleeve 3 where the piston 12 is positioned can be wholly or partly uncovered in the direction D1 , which makes it possible to limit the axial extension of the clamping device 1 , 1 ', 1", thus contributing to making the clamping device more compact in the axial direction.
  • Fig. 2 can be modified (not shown) in accordance with that shown in Figs 3 and 4, the actuating pressure chamber 5 being replaceable with an elastically resilient actuating means.
  • the deactuating pressure chamber 4 it would instead be possible to replace the deactuating pressure chamber 4 with an elastically resilient deactuating means (corresponding to the elastically resilient actuating means 18), thus obtaining a self-unlocking clamping device (not shown).
  • the flange 17 can be integrated with the piston 12.
  • the flange and the piston are formed in one piece of material, and in another embodiment they are formed of separate pieces of material which are subsequently joined together, for instance, by a threaded coupling or by a weld joint.
  • the inner sleeve and the outer sleeve can be joined together, for instance, by means of bolts or weld joints.
  • a plurality of gaskets can be arranged in a manner known per se to prevent leakage.
  • the conical surfaces can be arranged between the inner sleeve 2 and the piston 12, between the outer sleeve 3 and the piston 12 or both.
  • the chuck described above can be designed in the form of a mandrel, as illustrated in Fig. 6 of WO2004/007129A1. Furthermore, said chuck can be integrated with a fastening part P1 , i.e. a machine cone, as shown in Fig. 4 of WO2004/007129A1. For details concerning the design of the chuck or mandrel mentioned above, reference is made to WO2004/007129A1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Clamps And Clips (AREA)
  • Gripping On Spindles (AREA)

Abstract

L'invention concerne un dispositif de serrage hydromécanique comprenant une partie fixation (P1) conçue pour être montée dans un dispositif d'usinage et une partie support (P2) conçue pour supporter de manière libérable un arbre d'outil (V). La partie support (P2) comprend un manchon intérieur (2) pourvu d'un évidement axial et prévu pour recevoir l'arbre d'outil (V). Le manchon intérieur (2) et un manchon extérieur (3) définissent une chambre dans laquelle un piston annulaire (12) est mobile axialement. Le piston annulaire et le manchon intérieur ou le manchon extérieur comportent des surfaces coniques coopérantes (13, 14) qui, lors d'un déplacement axial du piston dans une première direction, sont agencées pour produire une compression radiale du manchon intérieur, et qui, lors d'un déplacement axial du piston dans une seconde direction opposée à la première direction, sont agencées pour permettre une dilatation radiale du manchon intérieur. Le dispositif de serrage (1) comprend en outre des moyens d'actionnement (5) agencés pour produire un déplacement du piston annulaire (12) dans ladite première direction, et des moyens de désactionnement (4) agencés pour produire un déplacement du piston annulaire (12) dans la seconde direction. Les moyens d'actionnement (5) et les moyens de désactionnement (4) sont localisés, vus dans la direction axiale, sur le même côté du piston annulaire (12).
PCT/SE2007/000973 2006-11-02 2007-11-01 Dispositif de serrage hydromécanique Ceased WO2008054295A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0602320-4 2006-11-02
SE0602320A SE530537C2 (sv) 2006-11-02 2006-11-02 Hydromekanisk fastspänningsanordning

Publications (1)

Publication Number Publication Date
WO2008054295A1 true WO2008054295A1 (fr) 2008-05-08

Family

ID=39156130

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2007/000973 Ceased WO2008054295A1 (fr) 2006-11-02 2007-11-01 Dispositif de serrage hydromécanique

Country Status (2)

Country Link
SE (1) SE530537C2 (fr)
WO (1) WO2008054295A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105517740A (zh) * 2013-09-13 2016-04-20 三菱综合材料株式会社 切削工具
WO2019026060A1 (fr) * 2017-07-31 2019-02-07 Iscar Ltd. Système porte-outil ayant des éléments captifs et non libérables, procédé de fabrication et d'assemblage de celui-ci et outil de coupe
US20240024962A1 (en) * 2022-07-22 2024-01-25 Kennametal Inc. Expansion Clamping Sleeve and Hydraulic Expansion Clamping Chuck

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3502362A1 (de) * 1984-01-26 1985-08-01 P.& E. Pneumatic- und Electronic-Gerätebau GmbH, 7210 Rottweil Spannstock
US4557166A (en) * 1982-02-12 1985-12-10 Kurt Jauch Automatic multiple workpiece turning machine
US4580796A (en) * 1982-04-10 1986-04-08 Albert Schrem Werkzeugfabrik Gmbh Hydraulic clamping nut
DE3510643A1 (de) * 1985-03-23 1986-09-25 Sitema Gesellschaft für Sicherheitstechnik und Maschinenbau mbH, 7500 Karlsruhe Klemmkopf
SU1364405A1 (ru) * 1985-12-18 1988-01-07 Павлодарский Индустриальный Институт Устройство дл механизированного креплени инструмента
WO2004007129A1 (fr) * 2002-07-17 2004-01-22 Etp Transmission Ab Dispositif de pince hydromecanique
WO2005110649A1 (fr) * 2004-05-18 2005-11-24 Etp Transmission Ab Embrayage a friction, ensemble piston et table de presse comprenant un embrayage a friction et procede associe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4557166A (en) * 1982-02-12 1985-12-10 Kurt Jauch Automatic multiple workpiece turning machine
US4580796A (en) * 1982-04-10 1986-04-08 Albert Schrem Werkzeugfabrik Gmbh Hydraulic clamping nut
DE3502362A1 (de) * 1984-01-26 1985-08-01 P.& E. Pneumatic- und Electronic-Gerätebau GmbH, 7210 Rottweil Spannstock
DE3510643A1 (de) * 1985-03-23 1986-09-25 Sitema Gesellschaft für Sicherheitstechnik und Maschinenbau mbH, 7500 Karlsruhe Klemmkopf
SU1364405A1 (ru) * 1985-12-18 1988-01-07 Павлодарский Индустриальный Институт Устройство дл механизированного креплени инструмента
WO2004007129A1 (fr) * 2002-07-17 2004-01-22 Etp Transmission Ab Dispositif de pince hydromecanique
WO2005110649A1 (fr) * 2004-05-18 2005-11-24 Etp Transmission Ab Embrayage a friction, ensemble piston et table de presse comprenant un embrayage a friction et procede associe

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105517740A (zh) * 2013-09-13 2016-04-20 三菱综合材料株式会社 切削工具
WO2019026060A1 (fr) * 2017-07-31 2019-02-07 Iscar Ltd. Système porte-outil ayant des éléments captifs et non libérables, procédé de fabrication et d'assemblage de celui-ci et outil de coupe
US10668541B2 (en) 2017-07-31 2020-06-02 Iscar, Ltd. Tool holding system having captive and non-releasable members, method of manufacture and assembly of same and cutting tool
JP2020529325A (ja) * 2017-07-31 2020-10-08 イスカル リミテッド 拘束的かつ解放不能な部材を有する工具保持具、その製造及び組立て方法、並びに切削工具
TWI748120B (zh) * 2017-07-31 2021-12-01 以色列商艾斯卡公司 具有受控制及不可釋放構件的刀具固持系統、其製造及組裝方法及切削刀具
RU2767135C2 (ru) * 2017-07-31 2022-03-16 Искар Лтд. Система удержания инструмента, имеющая захватные и неразъемные элементы, способ ее изготовления и сборки и режущий инструмент
JP7142038B2 (ja) 2017-07-31 2022-09-26 イスカル リミテッド 拘束的かつ解放不能な部材を有する工具保持具、その製造及び組立て方法、並びに切削工具
IL271252B2 (en) * 2017-07-31 2023-06-01 Iscar Ltd A tool holder with locked parts, a method for its manufacture, and a cutting tool including the same
US20240024962A1 (en) * 2022-07-22 2024-01-25 Kennametal Inc. Expansion Clamping Sleeve and Hydraulic Expansion Clamping Chuck

Also Published As

Publication number Publication date
SE530537C2 (sv) 2008-07-01
SE0602320L (sv) 2008-05-03

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