EP1755814A1 - Mandrins hydrauliques - Google Patents

Mandrins hydrauliques

Info

Publication number
EP1755814A1
EP1755814A1 EP05744388A EP05744388A EP1755814A1 EP 1755814 A1 EP1755814 A1 EP 1755814A1 EP 05744388 A EP05744388 A EP 05744388A EP 05744388 A EP05744388 A EP 05744388A EP 1755814 A1 EP1755814 A1 EP 1755814A1
Authority
EP
European Patent Office
Prior art keywords
enclosure
moveable member
tool
chuck
hydraulic fluid
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Withdrawn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
EP05744388A
Other languages
German (de)
English (en)
Inventor
Jeff Pratt
Dave Goodwin
John Bradley
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.)
Novanta Technologies UK Ltd
Original Assignee
Westwind Air Bearings Ltd
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 Westwind Air Bearings Ltd filed Critical Westwind Air Bearings Ltd
Publication of EP1755814A1 publication Critical patent/EP1755814A1/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Withdrawn legal-status Critical Current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
    • B23B31/02—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

Definitions

  • This invention relates to hydraulic chucks, in particular it relates to hydraulic chucks which are to be used in high speed machining operations.
  • collet chucks rely on sliding movement between the collet and the shaft taper as tools are inserted and removed from the chuck.
  • the contacting surfaces are greased.
  • grease dries out and also centrifuges away from the surfaces meaning that routine greasing maintenance is required. This is disadvantageous because it gives rise to machine down time and is a skilled operation.
  • a chuck comprising a hydraulic fluid receiving enclosure, a tool receiving portion with at least one deformable wall portion, and means for applying pressure to fluid when carried in the enclosure, the enclosure and tool receiving portion being arranged so that pressure applied to fluid in the enclosure can cause deformation of the deformable wall portion for gripping an inserted tool.
  • the means for applying pressure may comprise a moveable member which is disposed partly within the hydraulic fluid receiving enclosure and which is moveable between a first and a second position wherein the volume displaced within the enclosure by the moveable member when the member is in the first position is less than the volume displaced within the enclosure by the moveable member when the member is in the second position.
  • part within is used to refer to an element with a portion which is within the enclosure in the sense that that portion displaces volume within the enclosure rather than merely forming part of the outer boundary of the enclosure.
  • a plug or a screw which closes a port into an enclosure is not considered to be within the enclosure and nor is such a port closing plug or screw normally able to displace volume within the enclosure.
  • the moveable member may be arranged for sliding movement between the first and second positions.
  • the moveable member may be a piston.
  • the moveable member may have a first portion having a first cross-sectional area and a second portion having a second cross-sectional area.
  • the moveable member may have varying diameter along its length.
  • the first portion may have a first diameter and the second portion may have a second diameter.
  • the moveable member and hydraulic fluid enclosure may be arranged so that when the moveable member is moved in one direction between the first position and the second position, the amount of the first portion of the moveable member which is disposed within the enclosure decreases and the amount of the second portion of the moveable member which is disposed within the enclosure increases, whereas when the moveable member is moved in the other direction between the first position and the second position, the amount of the first portion of the moveable member which is disposed within the enclosure increases and the amount of the second portion of the moveable member which is disposed within the enclosure decreases.
  • the means for applying pressure may comprise pressure control means for applying selectable degrees of pressure to carried fluid to control the gripping force on an inserted tool.
  • the pressure control means may comprise said moveable member.
  • the means for applying pressure may comprise pressure intensifier means for increasing the pressure in dependence on the rotational speed of the chuck.
  • the pressure intensifier means may be centrifugally operated.
  • the pressure intensifier means may be arranged to act on the pressure control means.
  • the pressure intensifier may be arranged to act on the moveable member.
  • the moveable member may comprise a taper portion and the pressure intensifier may comprise at least one complementary taper portion.
  • the complimentary taper portion may be arranged to be driven outwards by centrifugal effects and further arranged, when so driven outwards, to interact with the moveable member taper portion to drive the moveable member in a direction which serves to increase the volume displaced within the enclosure by the moveable member. It will be seen that this action of the complimentary taper portion tends to increase the pressure in carried hydraulic fluid.
  • a part of the enclosure may be defined by the deformable wall portion.
  • the tool receiving portion may comprise three deformable wall portions.
  • the or each wall portion may comprise a respective land for contacting with an inserted tool.
  • the or each land may have a contact surface which is profiled to closely match the shape of the shank of a tool which is to be inserted.
  • the or each land may have a concavely profiled contact surface for contacting with the shank of an inserted tool.
  • the contact surfaces may be machined to final shape in a common boring operation carried out in the tool receiving portion.
  • a chuck comprising a main body defining a hydraulic fluid receiving enclosure and comprising a tool receiving portion with at least one deformable wall portion, the hydraulic fluid receiving enclosure and tool receiving portion being arranged so that pressure applied to fluid in the enclosure can cause deformation of the deformable wall portion for gripping an inserted tool, the chuck further comprising a moveable member which is disposed partly within the hydraulic fluid receiving enclosure and which is moveable between a first and a second position wherein the volume displaced within the enclosure by the moveable member when the member is in the first position is less than the volume displaced within the enclosure by the moveable member when the member is in the second position.
  • a chuck comprising a main body defining a hydraulic fluid receiving enclosure and comprising a tool receiving portion with at least one deformable wall portion, the hydraulic fluid receiving enclosure and tool receiving portion being arranged so that pressure applied to fluid in the enclosure can cause deformation of the deformable wall portion for gripping an inserted tool, the chuck further comprising a moveable member which is disposed partly within the hydraulic fluid receiving enclosure and which is moveable between a first and a second position wherein the volume displaced within the enclosure by the moveable member when the member is in the first position is less than the volume displaced within the enclosure by the moveable member when the member is in the second position; and a centrifugal pressure intensifier for increasing the pressure in carried hydraulic fluid in dependence on the speed of rotation of the chuck, said centrifugal pressure intensifier being arranged to act on the moveable member, the moveable member comprising a taper portion and the centrifugal pressure intensifier comprising at least one complementary taper portion, the complimentary taper portion being
  • a method of holding a tool comprising the steps of: providing hydraulic fluid into a chuck as defined above, operating the chuck to release pressure in the fluid carried in the enclosure, inserting the tool into the tool receiving portion and pressurising the fluid in the chuck to deform the deformable wall portion into contact with the inserted tool.
  • a method of manufacturing a chuck as defined above and comprising a tool receiving portion having a plurality of deformable wall portions each having a respective tool contacting land comprising the step of using a common boring operation to bore tool contact surfaces into the lands.
  • Figure 1 schematically shows a longitudinal section through a chuck
  • Figure 2 is a section on line II-II of the chuck shown in Figure 1.
  • Figure 1 schematically shows a chuck which comprises a main body or core 1
  • a tool receiving portion 4 in which a tool 5 can be
  • the tool receiving portion 4 comprises 3 deformable wall portions 41 as best seen in Figure 2.
  • the deformable wall portions 41 are connected together so as to form a triangular prism.
  • Each of the deformable wall portions 41 comprises a respective tool contacting land 42 which has a concave tool contacting surface.
  • the lands 42 can be seen in contact with the carried tool 5. It will be noted that in Figure 1 the tool 5 can be seen in contact with one of the lands 42 and in the orientation shown in Figure 1 this is above the tool. On the other hand, in Figure 1 no land is shown in contact below the tool. This is because the other two lands 42 make contact with the tool at 120 degrees separation from the upper land and thus are not visible in the section shown in
  • the tool contacting surfaces are formed by a common boring operation as one of the final stages in manufacture of the chuck.
  • this boring operation a boring operation a
  • boring tool is introduced into the tool receiving portion and the lands 42 are
  • each of the deformable wall portions 41 On the side of each of the deformable wall portions 41 opposite to that which carries the respective land 42 is a hydraulic fluid chamber 61 which forms part of a hydraulic fluid enclosure 6 which will be described in more detail below.
  • the main body or core 1 also comprises a piston receiving bore 7 at its opposite end.
  • a piston 8 is captured within the piston receiving bore 7 by a rear cover portion 71.
  • the piston receiving bore 7 and end cover 71 both define outer boundaries of further parts of the hydraulic fluid receiving enclosure 6 such that the piston 8 is disposed partly within the hydraulic fluid enclosure 6.
  • passageways or galleries 62 which serve to connect the hydraulic fluid chambers 61 adjacent to the deformable walls 41 to the piston receiving bore 7 so that there is a hydraulic fluid communication path between the piston receiving bore 7 and the hydraulic fluid chambers 61 adjacent to the deformable walls 41.
  • a hydraulic enclosure filling port 63 provided in the nose portion 2 and this port is provided with a screw plug closure 64.
  • a spring 81 is carried by the piston 8 and whilst this is schematically shown as a coil spring in Figure 1, in practice, this spring is more likely to be a wave spring. Wave springs are more tolerant to high speed rotation than conventional coil springs.
  • the spring 81 is positioned between a spring end stop sleeve 82 which is mounted in the main body of core 1 and a spring abutment portion 83 which is provided on the piston 8.
  • the spring 81 serves to bias the piston 8 towards the right (in the orientation as shown in Figure 1). As will be explained in more detail below, this corresponds to a position in which pressure is exerted on the hydraulic fluid in the hydraulic fluid enclosure 6 such as to tend to deform the deformable wall portions 41 thereby gripping the inserted tool 5.
  • centrifugal pressure intensifier arrangement 9 At the inner end of the piston 8 there is provided a centrifugal pressure intensifier arrangement 9.
  • Sealing means 84 are carried by the piston 8 in the region where the piston passes through the end cover 71 and through the spring stop sleeve 82.
  • the sealing means 84 which may for example comprise O-ring seals, serve to prevent hydraulic fluid in the hydraulic fluid enclosure 6 from leaking out of the rear part of the chuck or leaking forwards into the centrifugal pressure intensifier arrangement 9.
  • the piston 8 has two main portions 8 a, 8b which are disposed within the hydraulic fluid enclosure 6. These portions are provided on either side of the spring abutment portion 83. A first of these portions 8a is that part which carries the spring 81 and has a diameter A.
  • the second main portion 8b is on the other side of the spring abutment portion 83 and has a diameter B which is smaller than the diameter A of the first main portion 8a.
  • first main portion 8a is partly housed within the spring stop sleeve 82 and also that part of the second portion 8b is housed within the end cover 71.
  • These portions housed within the spring stop portion 81 and end cover 71 are not considered to be within the hydraulic fluid enclosure 6 since they do not contribute to any displacement of volume in the hydraulic fluid enclosure 6.
  • movement of the piston 8 can be used to alter the pressure in the hydraulic fluid and consequently movement of the piston 8 may be used to alter the pressure felt in the pressure chambers 61 adjacent to the deformable walls 41.
  • These pressure changes will allow the deformable walls 41 to relax as the pressure is lowered and cause the walls to be further deformed into gripping contact with an inserted tool as the pressure increases.
  • the piston 8 is pushed, using a pushrod (not shown), towards the position shown in Figure 1 against the force of the spring 81 and hydraulic fluid is introduced into the hydraulic fluid enclosure 6.
  • the screw plug 64 is then inserted into the fluid port 63 and sealed.
  • the piston will tend to move to the right (in the orientation shown in Figure 1) under the action of the spring 81 so reducing the available volume in the hydraulic fluid enclosure 6.
  • a pushrod again is used to push the piston 8 towards the position shown in Figure 1 so reducing the pressure in the hydraulic fluid enclosure 6 and so allowing the deformable walls 42 to relax such that a tool may be inserted.
  • the action of the pushrod may be removed so that the piston 8 again moves to the right (in the orientation shown in Figure 1) under the action of the spring so that the hydraulic fluid pressures serves to deform the deformable walls 41 into gripping contact with the inserted tool via the respective lands 42.
  • the pushrod may again be used to push the piston 8 towards the position shown in Figure 1 to reduce the pressure in the hydraulic fluid and allow the deformable walls to relax.
  • the pushrod actuation mechanism for moving the piston to allow the insertion and removal of tools can be part of the overall chuck design and disposed in the rear part 3 of the shaft. More normally, however, the pushrod mechanism will be mounted in a machine on which the chuck is also mounted. The pushrod does not rotate with the body of the chuck and need only contact the end of the piston 8 when the chuck is stationary.
  • the centrifugal pressure intensifier mechanism 9 comprises an inner tapered body 91 and a plurality of taper wedge jaws 92.
  • the jaw portions 92 are carried by the inner tapered body 91 in a way which allows the jaws 92 to move radially outwards under the influence of centrifugal force.
  • the jaw portions 92 have taper surfaces which are complementary to the tapered bore 85 in the end of the piston 8 such that as the jaw portions 92 move outwards under the effect of centrifugal force, the interaction between the jaw portions 92 and the internal taper 85 of the piston 8 drives the piston 8 to the right (in the orientation shown in Figure 1).
  • the spring stop sleeve 82 is provided as a separate component which is mounted into the core or main body 1. This gives an advantage that deferring lengths of spring sleeve 82 may be used to determine the rest position of the piston 8 within the assembly. This can determine the degree of pressure which is exerted on the hydraulic fluid when the piston is in this rest position.
  • the lands 42 are finish bored to final size after the chuck has been assembled. Furthermore, this operation may take place with the complete assembly supported in its own bearings to minimise runout.
  • the tool receiving portion 4 is machined by wire Electro Discharge Machining (EDM) from a solid blank and this blank is then turned and bored to give the outer shape and so as it may receive the piston 8 assembly.
  • EDM Electro Discharge Machining
  • the tool receiving portion in contrast to a conventional tapered collet is of constant cross section along its length. This means that the outer surfaces of the deformable walls form a generally uniform triangular prism and the profiled surfaces of the bored lands 42 bound a cylindrical cavity for receiving the tool 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gripping On Spindles (AREA)
  • Drilling And Boring (AREA)

Abstract

La présente invention concerne un mandrin comprenant un corps principal (1) définissant une enceinte (6) recevant un fluide hydraulique et comprenant une partie réceptrice d'outil (4) avec au moins une partie paroi déformable (41), l'enceinte recevant le fluide hydraulique et la partie réceptrice d'outil étant agencée de sorte que la pression appliquée au fluide dans l'enceinte puissent entraîner la déformation de la partie paroi de façon à assurer la préhension d'un outil introduit, ce mandrin comprenant aussi un piston mobile (8) qui est placé en partie à l'intérieur de l'enceinte recevant le fluide hydraulique et qui est mobile entre une première et une seconde position dans lesquelles le volume déplacé à l'intérieur de l'enceinte par l'élément mobile lorsque le piston (8) est la première position est inférieur au volume déplacé à l'intérieur de l'enceinte par le piston mobile lorsque ce piston est dans la seconde position et, un intensificateur de pression centrifuge (9) destiné à augmenter la pression dans le fluide hydraulique porté en fonction de la vitesse de rotation du mandrin, cet intensificateur de pression centrifuge étant agencé de façon à agir sur le piston mobile, ce piston mobile comprenant une partie en cône (85) et cet intensificateur de pression centrifuge comprenant des mâchoires (92) possédant un cône complémentaire. Des mâchoires (92) sont agencées de façon à être entraînées vers l'extérieur par des effets centrifuges et également agencés, quand elles sont ainsi entraînées vers l'extérieur, de façon à interagir avec la partie en cône (85) du piston mobile (8) de façon à entraîner ce piston mobile dans une direction qui sert à augmenter le volume déplacé à l'intérieur de l'enceinte (6) par ce piston mobile (8).
EP05744388A 2004-05-25 2005-05-23 Mandrins hydrauliques Withdrawn EP1755814A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB0411686.9A GB0411686D0 (en) 2004-05-25 2004-05-25 Hydraulic chucks
PCT/GB2005/001992 WO2005115665A1 (fr) 2004-05-25 2005-05-23 Mandrins hydrauliques

Publications (1)

Publication Number Publication Date
EP1755814A1 true EP1755814A1 (fr) 2007-02-28

Family

ID=32671047

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05744388A Withdrawn EP1755814A1 (fr) 2004-05-25 2005-05-23 Mandrins hydrauliques

Country Status (6)

Country Link
EP (1) EP1755814A1 (fr)
JP (1) JP2008500191A (fr)
CN (1) CN1980763A (fr)
GB (1) GB0411686D0 (fr)
TW (1) TW200603924A (fr)
WO (1) WO2005115665A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009021345A1 (fr) * 2007-08-15 2009-02-19 Swisscetec Gmbh Dispositif de serrage et module de base associé
CN104249258B (zh) * 2013-06-28 2016-12-28 上海宏功机械科技有限公司 一种刀具液压机械夹紧头及自动液压换刀装置
DE102015115180A1 (de) * 2015-09-09 2017-03-09 GDS Präzisionszerspanungs GmbH Spannvorrichtung, insbesondere hydraulische Spannvorrichtung
DE102015118757B3 (de) * 2015-11-02 2017-01-05 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Hydraulische Dehnspanneinrichtung
DE102016220343A1 (de) 2016-10-18 2018-04-19 Robert Bosch Gmbh Schnellspannvorrichtung für eine zumindest eine rotierend antreibbare Abtriebswelle aufweisende tragbare Werkzeugmaschine, insbesondere Winkelschleifmaschine
DE102019111281A1 (de) * 2019-05-02 2020-11-05 Haimer Gmbh Hydraulisch spannbarer Werkzeug-/Werkstückhalter
EP4032644A4 (fr) * 2019-09-20 2023-06-07 Big Daishowa Co., Ltd. Mandrin hydraulique
TWI724759B (zh) 2020-01-17 2021-04-11 寅翊智造股份有限公司 夾持裝置

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Publication number Priority date Publication date Assignee Title
FR1115393A (fr) * 1954-12-13 1956-04-23 Renault Mandrin extensible
US3592482A (en) * 1968-05-27 1971-07-13 Scully Jones Co Hydraulic chuck
DE3108249A1 (de) * 1981-03-05 1982-09-16 Fritz Schunk GmbH Fabrik für Spannwerkzeuge, 7128 Lauffen Dehnspannwerkzeug
DE3248148C2 (de) * 1982-12-27 1985-01-31 Daimler-Benz Ag, 7000 Stuttgart Klemmhülse
DE3805527A1 (de) * 1988-02-23 1989-08-31 Schunk Fritz Gmbh Werkzeugwechselsystem
SE469214B (sv) * 1991-11-29 1993-06-07 Etp Transmission Ab Maskinspindel med integrerad chuck samt foerfarande foer framstaellning daerav
JP3317419B2 (ja) * 1994-02-07 2002-08-26 黒田精工株式会社 液圧チャック
JPH11254214A (ja) * 1998-03-13 1999-09-21 Ohashi Kogyo Kk 高速対応フローティングチャック
GB9809603D0 (en) * 1998-05-07 1998-07-01 Renishaw Plc Tool change apparatus
US20020045521A1 (en) * 2000-10-16 2002-04-18 Hideki Mochida Spindle unit for a machine tool
JP2003165006A (ja) * 2001-11-28 2003-06-10 Miki Sugino 棒状ワークのチャック装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005115665A1 *

Also Published As

Publication number Publication date
CN1980763A (zh) 2007-06-13
GB0411686D0 (en) 2004-06-30
TW200603924A (en) 2006-02-01
WO2005115665A1 (fr) 2005-12-08
JP2008500191A (ja) 2008-01-10

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