EP0162765A1 - Kraftverstärkervorrichtung, insbesondere für Werkzeugmaschinensteuerung - Google Patents

Kraftverstärkervorrichtung, insbesondere für Werkzeugmaschinensteuerung Download PDF

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Publication number
EP0162765A1
EP0162765A1 EP85400837A EP85400837A EP0162765A1 EP 0162765 A1 EP0162765 A1 EP 0162765A1 EP 85400837 A EP85400837 A EP 85400837A EP 85400837 A EP85400837 A EP 85400837A EP 0162765 A1 EP0162765 A1 EP 0162765A1
Authority
EP
European Patent Office
Prior art keywords
piston
fluid
receiving
chamber
force
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Withdrawn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
EP85400837A
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English (en)
French (fr)
Inventor
Christian Bazot
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.)
Domange-Jarret SA
Original Assignee
Domange-Jarret SA
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 Domange-Jarret SA filed Critical Domange-Jarret SA
Publication of EP0162765A1 publication Critical patent/EP0162765A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/06—Use of special fluids, e.g. liquid metal; Special adaptations of fluid-pressure systems, or control of elements therefor, to the use of such fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors

Definitions

  • the subject of the invention is a force multiplier device, in particular for the control of machine tools.
  • Many machine tools have tool-holder mechanisms that require precise, efficient and quick attachment of tools.
  • a device conventionally used calls for fixing the tool to the tool holder by means of elastic washers, for example of the Belleville type which firmly hold the tool at the bottom of its support. The removal of the tool can only be obtained by compression of the Belleville washers, which requires the application of very high pressures, for example of the order of 1,800 daN (deca Newton).
  • Such tool-holder mechanisms equip for example lathes, cutters, etc.
  • Effort multipliers are known in the art making it possible to solve the aforementioned problems.
  • the force is applied to a "first" piston-emitter of reduced surface, displacing a hydraulic fluid in a first chamber in which it moves, and the force is received on a second "receiving" piston.
  • the ratio of the surface of the emitting piston to that of the receiving piston dictates, according to Pascal's principle, the ratio of the forces emitted and received; of course the strokes of the emitting piston and the receiving piston are in the reverse order of the forces.
  • the object of the invention is to create a new force multiplier device of the general type mentioned above, but which does not have the drawbacks thereof, taking into account a particular construction design and the use made in the field.
  • new device of the invention not of a hydraulic fluid, but of a high viscosity elastomer, such as for example a silicone gum which may have the usual temperature of use a viscosity of the order of 10 to 20.10 6 Cts (centistokes).
  • the receiving piston is formed at its front end, with a greater surface reach sliding in the working chamber and at its rear end with a reduced surface reach, at least one passage being provided in the piston, for the fluid, connecting the rear face of the piston and the internal volume of the working chamber behind said front bearing of the piston.
  • a force multiplier device 1 mounted in place inside a device 2 tool holder.
  • the tool holder device comprises a tool locking system 3 (not shown) which is tensioned by Belleville type washers 4. "Un-clamping" or disassembly of the tool is authorized if one exercises on the Belleville washers in the direction of arrow F a sufficient pressure force, for example of 1.800 daN 'over a determined stroke, for example of 3mm. It is the role of the force multiplier device 1 to allow the exertion of the force F of given value over the desired stroke from a commanded upper but lower intensity stroke force delivered for example by a pneumatic, mechanical or hydraulic cylinder 5.
  • the cylinder 5 is capable of developing a force f of the order of 545 daN over a stroke of approximately 11 mm.
  • the force is applied to the "sending" piston 6 of the device 1, which restores the force F at the other end to the "receiving" piston.
  • the device 1 is in the form of a cylinder which can be easily mounted at the rear of the tool holder 2 by introducing it into the cavity of the tool holder 2 in the direction of the arrow 8 until it stops against the shoulder 9, the fixing of the device in the tool holder being completed by fitting. the flange 10 and the fixing screw 11.
  • Figures 2 and 3 we will now refer to Figures 2 and 3 to describe in detail the force multiplier device of the invention.
  • the multiplier device 1 comprises, as already indicated, a “putting” piston 6 and a “receiving” piston 7 which are housed in a cylindrical body 12 advantageously made of bronze to facilitate the sliding of the pistons, for example of chromed steel, inside the body 12.
  • the body 12 essentially comprises two bore diameters 13 of large surface area and 14 of relatively small surface area respectively, these two surfaces corresponding respectively to the working surfaces of the "receiving" piston 7 and the "emitting” piston 6.
  • the entire assembly is advantageously circular cylindrical centered on axis 15 of the device.
  • orient the device by calling “front” (AV) one end of the device and “rear” (AR) the other end of the device.
  • the "receiving" piston 7 is formed at its front end with a bearing formed by two shoulders 16, 17 with surface corresponding to the large diameter bore 13 of the body 12, and at its AR end with a reduced surface area 18 corresponding to the small diameter 14 of the body 12.
  • the piston can be lengthened and suitably centered-in its sliding movement parallel to the axis 15.
  • an O-ring seal 19 and a split anti-extrusion ring 20 for the seal.
  • Behind the shoulder 16 is mounted a scraper seal 21 suitable for the use of the elastomeric pressure transmission fluid introduced inside the system as will be described later.
  • the receiving piston 7 has a central bore 22 opening out towards the rear increasing the volume of the working chamber.
  • the bore 22 communicates with the annular free space 23 formed between the skirt of the piston behind the shoulder 16 and the bore 13 of large diameter of the body 12 by means of passages formed by orifices 24 drilled transversely, radially through the piston skirt 7.
  • the emitting piston mounted at the rear of the device has two shoulders 25, 26 forming a sliding surface against the reduced diameter 14 of the body 12.
  • the latter is formed at its front portion with a reduced diameter section 27 on which is mounted a guide ring 28 comprising numerous orifices longitudinal 29 for the passage of the fluid.
  • Behind this ring there is successively a scraper seal 30 (similar to seal 21), the shoulder 25, an O-ring seal 31 (similar to seal 19), an anti-extrusion ring 32 (similar to the anti-extrusion ring 20) then the shoulder 26.
  • the seal 31 and the ring 32 are thus held in the groove 37 formed between the shoulders 25 and 26.
  • a borehole 33 has been made, closed at its rear part by a valve which in the example illustrated consists of a ball 34 pressed by a screw 35.
  • the volume of the chambers can be precisely calculated so that the best pressure rise and response curves of the device are obtained, by playing in particular on the size of the bore 22 formed in the "receiving" piston 7. given the quality of the elastomer used, there is no risk of any leakage from the device once the screw 34 has been replaced and the screw 35 properly tightened. Furthermore, any recharging of the device could be done simply.
  • the ratio of the forces is proportional to the ratio of the surfaces of the "emitting" piston acting in the chamber of diameter 14 and the “receiving” piston sliding by its shoulders 16, 17 in the chamber of diameter 13.
  • the stroke ratio is substantially inversely proportional to the ratio of surfaces, with a slight decrease due to the compressibility of the elastomer which ensures a g experiences pressure on the device, therefore flexible control of the tool holder.
  • the system described does not require an alignment of the "sending" piston and the "receiving” piston, although this arrangement is generally simpler and more compact.
  • the metal O-ring 40 made of spring steel retaining the receiving piston 7, front side and the peripheral slot 41 formed in the body 12 allowing it to be extracted.
  • the usual viscosity range has been indicated 1 0 to 20.10 6 Cts (centistokes). This range can be widened, for example by using viscous oils having viscosities of the order of 5 to 10 ⁇ 10 6 Cts.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Gripping On Spindles (AREA)
EP85400837A 1984-05-09 1985-04-29 Kraftverstärkervorrichtung, insbesondere für Werkzeugmaschinensteuerung Withdrawn EP0162765A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8407145A FR2564159B1 (fr) 1984-05-09 1984-05-09 Dispositif multiplicateur d'effort en particulier pour la commande de machines-outils
FR8407145 1984-05-09

Publications (1)

Publication Number Publication Date
EP0162765A1 true EP0162765A1 (de) 1985-11-27

Family

ID=9303798

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85400837A Withdrawn EP0162765A1 (de) 1984-05-09 1985-04-29 Kraftverstärkervorrichtung, insbesondere für Werkzeugmaschinensteuerung

Country Status (2)

Country Link
EP (1) EP0162765A1 (de)
FR (1) FR2564159B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2212746A (en) * 1987-11-24 1989-08-02 Okuma Machinery Works Ltd Tool mounting apparatus
FR2742209A1 (fr) * 1995-12-08 1997-06-13 Leteurtre Patrick Verins de positionnement a un axe ou a trois axes, et procedes d'asservissement mettant en oeuvre ces verins

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB856725A (en) * 1957-12-13 1960-12-21 Harry Freeman Force transmitting device
FR1374908A (fr) * 1963-11-21 1964-10-09 Automotive Prod Co Ltd Cylindre actionné par un fluide sous pression utilisable notamment pour la commanded'un embrayage de véhicule
FR1393462A (fr) * 1964-02-11 1965-03-26 Sncf Dispositif de renvoi d'effort ou de mouvement sans articulation
GB1296312A (de) * 1971-04-07 1972-11-15
FR2157719A1 (de) * 1971-10-28 1973-06-08 Revillon Rene
FR2179572A1 (de) * 1972-04-12 1973-11-23 Jarret Jean
DE2831930A1 (de) * 1978-07-20 1980-02-07 Paul Chrubasik Linearer winkeltrieb

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB856725A (en) * 1957-12-13 1960-12-21 Harry Freeman Force transmitting device
FR1374908A (fr) * 1963-11-21 1964-10-09 Automotive Prod Co Ltd Cylindre actionné par un fluide sous pression utilisable notamment pour la commanded'un embrayage de véhicule
FR1393462A (fr) * 1964-02-11 1965-03-26 Sncf Dispositif de renvoi d'effort ou de mouvement sans articulation
GB1296312A (de) * 1971-04-07 1972-11-15
FR2157719A1 (de) * 1971-10-28 1973-06-08 Revillon Rene
FR2179572A1 (de) * 1972-04-12 1973-11-23 Jarret Jean
DE2831930A1 (de) * 1978-07-20 1980-02-07 Paul Chrubasik Linearer winkeltrieb

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2212746A (en) * 1987-11-24 1989-08-02 Okuma Machinery Works Ltd Tool mounting apparatus
GB2212746B (en) * 1987-11-24 1991-11-13 Okuma Machinery Works Ltd Tool mounting apparatus
FR2742209A1 (fr) * 1995-12-08 1997-06-13 Leteurtre Patrick Verins de positionnement a un axe ou a trois axes, et procedes d'asservissement mettant en oeuvre ces verins
WO1997021929A1 (fr) * 1995-12-08 1997-06-19 Nanotec Solution Verins de positionnement a trois axes, et procedes d'asservissement mettant en oeuvre ces verins
US6186480B1 (en) 1995-12-08 2001-02-13 Nanotec Solution Triaxial positioning actuator and control methods using same

Also Published As

Publication number Publication date
FR2564159B1 (fr) 1988-07-15
FR2564159A1 (fr) 1985-11-15

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Effective date: 19860729

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Inventor name: BAZOT, CHRISTIAN