US20010050466A1 - High speed drill holders - Google Patents
High speed drill holders Download PDFInfo
- Publication number
- US20010050466A1 US20010050466A1 US09/911,717 US91171701A US2001050466A1 US 20010050466 A1 US20010050466 A1 US 20010050466A1 US 91171701 A US91171701 A US 91171701A US 2001050466 A1 US2001050466 A1 US 2001050466A1
- Authority
- US
- United States
- Prior art keywords
- drill
- drill holder
- sprag
- collar
- forces
- 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.)
- Granted
Links
Images
Classifications
-
- 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
- F16D1/0852—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 between the mating surfaces of the hub and shaft
- F16D1/0858—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 between the mating surfaces of the hub and shaft due to the elasticity of the hub (including shrink fits)
-
- 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
- B23B31/14—Chucks with simultaneously-acting jaws, whether or not also individually adjustable involving the use of centrifugal force
- B23B31/142—To grip a tool or workpiece
-
- 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
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
- F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
- F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction clutching members
-
- 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
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
- F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
- F16D2043/145—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members the centrifugal masses being pivoting
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T279/00—Chucks or sockets
- Y10T279/10—Expanding
- Y10T279/1074—Rotary actuator
- Y10T279/1079—Clutch or self-actuating type
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T279/00—Chucks or sockets
- Y10T279/17—Socket type
- Y10T279/17213—Transversely oscillating jaws
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T279/00—Chucks or sockets
- Y10T279/17—Socket type
- Y10T279/17291—Resilient split socket
- Y10T279/17316—Unitary
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T279/00—Chucks or sockets
- Y10T279/24—Chucks or sockets by centrifugal force
- Y10T279/247—Chucks or sockets by centrifugal force to grip tool or workpiece
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49995—Shaping one-piece blank by removing material
- Y10T29/49996—Successive distinct removal operations
Definitions
- the present invention relates to holders, particularly collets or chucks, for holding high speed drills.
- the object of the present invention therefore is to provide a simple drill holder for high speed drilling and light routing which maintains a very high standard of accuracy, retains the drill bit tightly gripped, and is immune to the adverse affects of excessive speed, such as loosening of the drill due to centrifugal forces.
- the present invention provides a drill holder, for example a collet or chuck, for carrying a high speed drill, said drill holder comprising a collar arranged to enclose a drill shank, an outer rim support arranged for attachment to a drill, and a clamping mechanism between the collar and the outer rim support, said clamping mechanism being arranged to provide clamping forces between said outer rim support and said collar so that said collar tightly grips a drill shank, as a consequence of centrifugal forces and of off-centre sprag effect forces.
- a sprag effect force is a force due to an offset pressure in a direction opposed to that of rotation.
- Sprag effect forces were originally used on railway waggons in the nineteenth century where a sprag, or piece of timber, was placed against a wagon wheel on a railway line at an orientation directed slightly above the centre line of the wheel to act as a brake. In such a case as the wheel tries to move towards the sprag the pressure increases due to the offset force of the sprag with respect to the axle of the wheel.
- Clutches have been devised based on the sprag effect where a wedging effect increases against the direction of rotation to provide for a clutching action.
- FIGS. 1 and 2 show section and perspective views of a first embodiment
- FIG. 3 shows a section view of a second embodiment
- FIGS. 4, 5, 6 , 7 and 8 show section views of further arrangements in accordance with the invention.
- FIG. 9 shows a multi-jaw arrangement.
- the invention provides a form of collet which utilises centrifugal force coupled with use of a sprag force for keeping a collet in gripping contact with a drill shank 1 .
- the drill shank 1 is held in a series of jaws 2 spaced symmetrically about the shank.
- the jaw 2 pivots about an integral hinge 3 causing the leading edge of the jaw, at the position 4 , to exert pressure on the shank 1 .
- the hinge 3 is of the solid type where a small amount of material holds the two parts integrally together and flexes in use.
- the structure is formed by an EDM (electro-discharge machining or spark erosion) process so that the cylinder is of a suitable shape where it can be shrink fitted into a shaft at a suitable stage during the manufacturing process.
- EDM electro-discharge machining or spark erosion
- An important feature is that the bore into which the shank is fitted is finished by bore grinding in the spindle. If the shaft is supported by an air bearing, then the finished bore should run true to 0.00003 inches TIR (total indicator run out, or swing between maximum and minimum dimension). In order to facilitate bore grinding, the jaws would remain linked together in the region 5 of FIG. 1 until final assembly.
- the EDM process is used to separate the jaws, by mounting the shaft vertically, and passing a cutting wire through the hollow shaft.
- FIG. 3 An alternative form of the jaw to take account of this problem is shown in FIG. 3.
- the bob weight 7 now imposes torque to close the jaw, but the absolute magnitude of the force is limited by the flexibility of the hinge 6 .
- the flexure of the hinge 6 causes the bob weight 7 to engage the outer rim 8 at the land 9 .
- the sprag effect enhances the grip and therefore enables the collet to deal with heavy duty situations.
- FIG. 4 shows a similar arrangement to the original FIG. 1 arrangement where during rotation a bob weight 11 causes bending of a cantilever hinge 12 , resulting in contact of a jaw 13 with the tool shank (not shown but located centrally).
- the geometry of the cantilever 12 is such that when a torque is imposed on the tool shank, the cantilever is induced to bend further, thus increasing the radial pressure on the tool shank. This is operating in the same way as with the well known sprag clutch.
- FIG. 5 shows a similar arrangement to FIG. 4 but using less jaws, i.e. three, and a slightly different configuration of bob weight which therefore provides slightly different forces.
- FIG. 6 the jaw has been reduced in thickness. This is in an attempt to encourage rotation about the initial contact point 13 with a view to finally obtaining additional contact at 14 by virtue of flexure of the collet jaw.
- FIG. 9 shows a six jaw system comprising three pairs of siamesed jaws.
- alternate jaws in the direction of rotation provide a sprag force locking system while the other jaws of each pair provide pressure generated by centrifugal force but without augmentation by sprag forces.
- rotation in the reverse direction would bring in sprag forces from the other jaws.
- the spragging arrangement is not at too direct an angle otherwise pull through can arise, resulting in the collet being permanently locked. That is the radial element stands risk of snapping through the central position to a position where it is directed into the shank from the opposite direction. This can be unloaded in most cases by high speed rotation in the reverse sense, but would be impossible in the siamesed example of FIG. 9, because in that case the alternative jaws would then lock on due to spragging in the reverse direction.
- the angle of offset should always be greater than a few degrees to avoid this problem.
- the geometry of the arrangement should only introduce a relatively low spragging force since otherwise it might be impossible to remove the drill shank subsequently.
- the collet may grip the tool shank particularly tightly as a consequence of the sprag effect, and be reluctant to release the tool in the static condition afterwards.
- a tool loading/unloading mechanism therefore may be required capable of giving the tool a small sharp angular motion in the direction of drilling to effect release of the shank.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Drilling Tools (AREA)
- Gripping On Spindles (AREA)
- Peptides Or Proteins (AREA)
- Cephalosporin Compounds (AREA)
- Preparation Of Compounds By Using Micro-Organisms (AREA)
Abstract
Description
- The present invention relates to holders, particularly collets or chucks, for holding high speed drills.
- When very fine drills are used, the rotational speeds have to become very high and indeed some systems use drills rotating at speeds in the region of 180,000 rpm. Such high speeds are necessary because as the diameter of the drill becomes less, its rotational speed has to increase so as to ensure a suitably high peripheral cutting speed. However with such very high rotational speeds, centrifugal forces become very large and they then act in opposition to forces holding the drill shank in position. This then creates inaccuracies in drilling performance.
- The object of the present invention therefore is to provide a simple drill holder for high speed drilling and light routing which maintains a very high standard of accuracy, retains the drill bit tightly gripped, and is immune to the adverse affects of excessive speed, such as loosening of the drill due to centrifugal forces.
- Accordingly the present invention provides a drill holder, for example a collet or chuck, for carrying a high speed drill, said drill holder comprising a collar arranged to enclose a drill shank, an outer rim support arranged for attachment to a drill, and a clamping mechanism between the collar and the outer rim support, said clamping mechanism being arranged to provide clamping forces between said outer rim support and said collar so that said collar tightly grips a drill shank, as a consequence of centrifugal forces and of off-centre sprag effect forces.
- It should be explained that a sprag effect force is a force due to an offset pressure in a direction opposed to that of rotation. Sprag effect forces were originally used on railway waggons in the nineteenth century where a sprag, or piece of timber, was placed against a wagon wheel on a railway line at an orientation directed slightly above the centre line of the wheel to act as a brake. In such a case as the wheel tries to move towards the sprag the pressure increases due to the offset force of the sprag with respect to the axle of the wheel. Clutches have been devised based on the sprag effect where a wedging effect increases against the direction of rotation to provide for a clutching action.
- Several embodiments of the invention will now be described by way of example with reference to the accompanying diagrammatic drawings in which:
- FIGS. 1 and 2 show section and perspective views of a first embodiment;
- FIG. 3 shows a section view of a second embodiment,
- FIGS. 4, 5,6, 7 and 8 show section views of further arrangements in accordance with the invention, and
- FIG. 9 shows a multi-jaw arrangement.
- Referring to FIG. 1 the invention provides a form of collet which utilises centrifugal force coupled with use of a sprag force for keeping a collet in gripping contact with a drill shank1.
- The drill shank1 is held in a series of
jaws 2 spaced symmetrically about the shank. When the collet is rotated, thejaw 2 pivots about anintegral hinge 3 causing the leading edge of the jaw, at theposition 4, to exert pressure on the shank 1. It will be seen that thehinge 3 is of the solid type where a small amount of material holds the two parts integrally together and flexes in use. - It will be appreciated that the line passing through the hinge and the leading edge of the jaw does not pass through the axis of rotation. This brings in the sprag effect in such a way that when the torque is imposed on the shank in the direction of the arrow, the jaws grip more tightly. The magnitude of the effect is governed by the geometry and the size and form of the jaws. The form of the collet is shown in FIG. 2 in perspective where it may be seen that the complete device takes the form of a small cylinder of a suitable length to encompass the drill shank1.
- The structure is formed by an EDM (electro-discharge machining or spark erosion) process so that the cylinder is of a suitable shape where it can be shrink fitted into a shaft at a suitable stage during the manufacturing process. An important feature is that the bore into which the shank is fitted is finished by bore grinding in the spindle. If the shaft is supported by an air bearing, then the finished bore should run true to 0.00003 inches TIR (total indicator run out, or swing between maximum and minimum dimension). In order to facilitate bore grinding, the jaws would remain linked together in the
region 5 of FIG. 1 until final assembly. - On completion, the EDM process is used to separate the jaws, by mounting the shaft vertically, and passing a cutting wire through the hollow shaft.
- The centrifugal forces acting on the jaws of such a device at high speed can be very large, and hence it is necessary to provide means by which they can be limited to a reasonable level.
- An alternative form of the jaw to take account of this problem is shown in FIG. 3. Here it may be seen that not only has the jaw been reduced in size, but also has an additional solid hinge which is provided at6. The
bob weight 7 now imposes torque to close the jaw, but the absolute magnitude of the force is limited by the flexibility of thehinge 6. When rotation has generated sufficient grip of the shank, the flexure of thehinge 6, causes thebob weight 7 to engage theouter rim 8 at the land 9. It will be appreciated that there are a wide variety of configurations all within the compass of this concept. As indicated earlier, the sprag effect enhances the grip and therefore enables the collet to deal with heavy duty situations. - Further variations are then shown in FIGS.4 to 8. FIG. 4 shows a similar arrangement to the original FIG. 1 arrangement where during rotation a
bob weight 11 causes bending of acantilever hinge 12, resulting in contact of ajaw 13 with the tool shank (not shown but located centrally). The geometry of thecantilever 12 is such that when a torque is imposed on the tool shank, the cantilever is induced to bend further, thus increasing the radial pressure on the tool shank. This is operating in the same way as with the well known sprag clutch. - The number of jaws is dependent on the particular application, and indeed on design choice as is the particular shaping of the
bob weight 11. Thus, FIG. 5 shows a similar arrangement to FIG. 4 but using less jaws, i.e. three, and a slightly different configuration of bob weight which therefore provides slightly different forces. - In FIG. 6 the jaw has been reduced in thickness. This is in an attempt to encourage rotation about the
initial contact point 13 with a view to finally obtaining additional contact at 14 by virtue of flexure of the collet jaw. - In FIG. 7 the mass of the bob weight at17 has been increased to improve torque transmission.
- And then in FIG. 8 a
second hinge 16 has been incorporated to allow greater movement of thebob weight 17, this results in theweight 17 finally coming into contact with apositive stop 18. For high speed operation it is imperative that provision is made to avoid excessive movement of the bob weights which would result in unacceptable stress levels. - Finally FIG. 9 shows a six jaw system comprising three pairs of siamesed jaws. In this case alternate jaws in the direction of rotation provide a sprag force locking system while the other jaws of each pair provide pressure generated by centrifugal force but without augmentation by sprag forces. In this case rotation in the reverse direction would bring in sprag forces from the other jaws.
- In all the described cases, it is important that the spragging arrangement is not at too direct an angle otherwise pull through can arise, resulting in the collet being permanently locked. That is the radial element stands risk of snapping through the central position to a position where it is directed into the shank from the opposite direction. This can be unloaded in most cases by high speed rotation in the reverse sense, but would be impossible in the siamesed example of FIG. 9, because in that case the alternative jaws would then lock on due to spragging in the reverse direction. Thus, the angle of offset should always be greater than a few degrees to avoid this problem. Also in the FIG. 9 example the geometry of the arrangement should only introduce a relatively low spragging force since otherwise it might be impossible to remove the drill shank subsequently.
- In all of these described examples adequate provision is necessary to ensure that the drill shank is correctly located within the bore of the collet. When a tool shank is loaded automatically into the collet it is important that it is inserted to a specific depth, governed by a stop to the rear of the collet bore. In the static condition, that is when the collet is open, it will be appreciated that there is no gripping force to secure the tool shank centrally in the defined axial position. The presence of an 0-ring located in an annular groove in the collet bore overcomes this problem, although it has to be said that this particular measure has been used previously in other forms of collet. Generally the 0-ring section would have a nominal bore of 0.125 inches with a sectional diameter of 1 mm.
- It should also be noted that in use the collet may grip the tool shank particularly tightly as a consequence of the sprag effect, and be reluctant to release the tool in the static condition afterwards. A tool loading/unloading mechanism therefore may be required capable of giving the tool a small sharp angular motion in the direction of drilling to effect release of the shank.
Claims (7)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GBGB9901718.8A GB9901718D0 (en) | 1999-01-26 | 1999-01-26 | High speed drill holders |
GB9901718.8 | 1999-01-26 | ||
GB9901718 | 1999-01-26 | ||
PCT/GB2000/000038 WO2000044519A1 (en) | 1999-01-26 | 2000-01-10 | High speed drill holders |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/GB2000/000038 Continuation WO2000044519A1 (en) | 1999-01-26 | 2000-01-10 | High speed drill holders |
Publications (2)
Publication Number | Publication Date |
---|---|
US20010050466A1 true US20010050466A1 (en) | 2001-12-13 |
US6443462B2 US6443462B2 (en) | 2002-09-03 |
Family
ID=10846542
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/911,717 Expired - Fee Related US6443462B2 (en) | 1999-01-26 | 2001-07-25 | High speed drill holders |
Country Status (9)
Country | Link |
---|---|
US (1) | US6443462B2 (en) |
EP (1) | EP1144148B1 (en) |
JP (1) | JP4567202B2 (en) |
CN (1) | CN1153642C (en) |
AT (1) | ATE235340T1 (en) |
AU (1) | AU1990600A (en) |
DE (1) | DE60001805T2 (en) |
GB (1) | GB9901718D0 (en) |
WO (1) | WO2000044519A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1332817A1 (en) * | 2002-02-04 | 2003-08-06 | Schunk GmbH & Co. KG Fabrik für Spann- und Greifwerkzeuge | Chuck |
NL2002128C (en) * | 2008-10-23 | 2010-04-26 | Univ Delft Tech | Rotary connector for a rotating shank or axle. |
US9447823B2 (en) | 2008-10-23 | 2016-09-20 | Micro Turbine Technology Bv | Rotary connector for a rotating shank or axle |
WO2017076921A1 (en) * | 2015-11-02 | 2017-05-11 | Schunk Gmbh & Co. Kg Spann- Und Greiftechnik | Expansion chuck |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4762448B2 (en) * | 2001-07-24 | 2011-08-31 | パスカルエンジニアリング株式会社 | Work pallet positioning and fixing device |
AT500140A1 (en) * | 2003-06-12 | 2005-11-15 | W & H Dentalwerk Buermoos Gmbh | JIG |
DE50304879D1 (en) * | 2003-11-06 | 2006-10-12 | Schunk Gmbh & Co Kg | Intermediate bushing for a chuck and method for its production |
EP1669621B1 (en) * | 2004-12-13 | 2007-01-03 | Schunk GmbH & Co. KG Spann- und Greiftechnik | Clamping device |
DE102005056440A1 (en) * | 2005-11-26 | 2007-05-31 | Kennametal Inc. | Clamping device for drill bit has clamping shell in more than one part, preferably in two parts |
TWI273951B (en) * | 2005-12-07 | 2007-02-21 | Hou-Fei Hu | Retaining device |
US7547168B1 (en) | 2008-04-17 | 2009-06-16 | Kosmowski Wojciech B | High speed spindle system and centrifugal chuck |
JP5386256B2 (en) * | 2008-09-29 | 2014-01-15 | 日立ビアメカニクス株式会社 | Chuck |
DE102013103427A1 (en) * | 2013-04-05 | 2014-10-23 | Franz Haimer Maschinenbau Kg | tool holder |
CN103203643B (en) * | 2013-05-02 | 2015-03-11 | 哈尔滨工业大学 | Magnetic self-pretightening device for high-speed electric main shaft chuck |
DE102014105652A1 (en) * | 2014-04-22 | 2015-10-22 | Föhrenbach GmbH | Centrifugal clamping system |
US9050661B1 (en) * | 2014-06-13 | 2015-06-09 | Interdyne Systems Inc | Centrifugal collet for high speed operation |
GB2534907A (en) * | 2015-02-05 | 2016-08-10 | Gsi Group Ltd | Rotary tool holder assemblies |
GB2588160B (en) * | 2019-10-10 | 2022-09-21 | Univ Brunel | Adaptive precision chuck |
DE102020113330B3 (en) * | 2020-05-16 | 2021-05-27 | Schenck Rotec Gmbh | Component for connecting a clamping fixture to a shaft |
JP7055855B1 (en) | 2020-10-30 | 2022-04-18 | ヤマハ発動機株式会社 | Resin parts with mounting holes, assembly parts with them and saddle-mounted vehicles |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
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US2481094A (en) * | 1945-02-05 | 1949-09-06 | Timken Roller Bearing Co | Centrifugal chuck |
FR976808A (en) * | 1948-10-20 | 1951-03-22 | Self-tightening rotating device | |
US2729038A (en) * | 1953-10-30 | 1956-01-03 | Alma A Hutchins | Rotary abrading machine heads |
US3975029A (en) * | 1974-08-13 | 1976-08-17 | George Washington Benjamin | Drill bit centrifugal vise |
DE2749115C2 (en) * | 1977-11-03 | 1986-07-03 | GMN Georg Müller Nürnberg GmbH, 8500 Nürnberg | Chuck-like quick release device for internal and external clamping |
US4802680A (en) * | 1986-03-21 | 1989-02-07 | Siemens Aktiengesellschaft | Coaxial collet chuck |
US4821859A (en) * | 1987-05-11 | 1989-04-18 | Textron Inc. | Self adjusting rotor for a centrifugal clutch |
GB9320639D0 (en) * | 1993-10-07 | 1993-11-24 | Westwind Air Bearings Ltd | Centrifugal locking drill |
JP3317419B2 (en) * | 1994-02-07 | 2002-08-26 | 黒田精工株式会社 | Hydraulic chuck |
JP3809624B2 (en) * | 1997-01-17 | 2006-08-16 | 太平洋セメント株式会社 | Lever displacement expansion mechanism |
-
1999
- 1999-01-26 GB GBGB9901718.8A patent/GB9901718D0/en not_active Ceased
-
2000
- 2000-01-10 WO PCT/GB2000/000038 patent/WO2000044519A1/en active IP Right Grant
- 2000-01-10 CN CNB008030278A patent/CN1153642C/en not_active Expired - Fee Related
- 2000-01-10 EP EP00900241A patent/EP1144148B1/en not_active Expired - Lifetime
- 2000-01-10 AT AT00900241T patent/ATE235340T1/en not_active IP Right Cessation
- 2000-01-10 JP JP2000595808A patent/JP4567202B2/en not_active Expired - Fee Related
- 2000-01-10 AU AU19906/00A patent/AU1990600A/en not_active Abandoned
- 2000-01-10 DE DE60001805T patent/DE60001805T2/en not_active Expired - Fee Related
-
2001
- 2001-07-25 US US09/911,717 patent/US6443462B2/en not_active Expired - Fee Related
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1332817A1 (en) * | 2002-02-04 | 2003-08-06 | Schunk GmbH & Co. KG Fabrik für Spann- und Greifwerkzeuge | Chuck |
NL2002128C (en) * | 2008-10-23 | 2010-04-26 | Univ Delft Tech | Rotary connector for a rotating shank or axle. |
WO2010047594A1 (en) * | 2008-10-23 | 2010-04-29 | Mtt Bv (Micro Turbine Technology B.V.) | Rotary connector for a rotating shank or axle |
US9447823B2 (en) | 2008-10-23 | 2016-09-20 | Micro Turbine Technology Bv | Rotary connector for a rotating shank or axle |
WO2017076921A1 (en) * | 2015-11-02 | 2017-05-11 | Schunk Gmbh & Co. Kg Spann- Und Greiftechnik | Expansion chuck |
Also Published As
Publication number | Publication date |
---|---|
CN1153642C (en) | 2004-06-16 |
DE60001805T2 (en) | 2003-12-18 |
JP2002535156A (en) | 2002-10-22 |
GB9901718D0 (en) | 1999-03-17 |
EP1144148A1 (en) | 2001-10-17 |
US6443462B2 (en) | 2002-09-03 |
WO2000044519A1 (en) | 2000-08-03 |
EP1144148B1 (en) | 2003-03-26 |
JP4567202B2 (en) | 2010-10-20 |
ATE235340T1 (en) | 2003-04-15 |
CN1337894A (en) | 2002-02-27 |
DE60001805D1 (en) | 2003-04-30 |
AU1990600A (en) | 2000-08-18 |
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