EP0974428A2 - Machine à forer portable avec mécanisme à percussion mû à l' air comprimé - Google Patents

Machine à forer portable avec mécanisme à percussion mû à l' air comprimé Download PDF

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Publication number
EP0974428A2
EP0974428A2 EP99810527A EP99810527A EP0974428A2 EP 0974428 A2 EP0974428 A2 EP 0974428A2 EP 99810527 A EP99810527 A EP 99810527A EP 99810527 A EP99810527 A EP 99810527A EP 0974428 A2 EP0974428 A2 EP 0974428A2
Authority
EP
European Patent Office
Prior art keywords
pneumatic cylinder
percussion piston
compressed air
piston
hand drill
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Withdrawn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
EP99810527A
Other languages
German (de)
English (en)
Other versions
EP0974428A3 (fr
Inventor
Matthias Blessing
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.)
Hilti AG
Original Assignee
Hilti AG
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 Hilti AG filed Critical Hilti AG
Publication of EP0974428A2 publication Critical patent/EP0974428A2/fr
Publication of EP0974428A3 publication Critical patent/EP0974428A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/04—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously of the hammer piston type, i.e. in which the tool bit or anvil is hit by an impulse member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0023—Pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/341—Use of external compressors

Definitions

  • the invention relates to a hand drill with an air-powered hammer mechanism for Generation of axial impacts according to the preamble of patent claim 1.
  • At least one switching valve arranged to switch the pneumatic cylinder volumes from loading to ventilation serves to keep the percussion piston inside the To put the pneumatic cylinder in a periodic back and forth movement.
  • the switching valve is controlled with the help of limit switches, which are located in the front or can be activated in the rear end position of the percussion piston.
  • the real one The switching valve is then switched over mechanically, electrically or via Control compressed air lines.
  • a disadvantage of the known compressed air-excited striking mechanisms is that they are large Have dead volumes that occur between each pressurized and must be reloaded in a depressurized state. This not only leads to temporal Delays that have a negative impact on the attainable stroke rate. The permanent reloading from an unpressurized to a pressurized state and vice versa leads to relatively large energy losses.
  • the well-known compressed air excitation Striking mechanisms have limit switches and at least one switching valve. Result from it Switching time delays, which also have a negative impact on the impact performance can. The single impact energy and the frequency of the axial impacts generated are only controllable to a small extent via the pressure applied to the striking mechanism.
  • the object of the present invention is to overcome these disadvantages of compressed air To remedy prior art percussion devices. It is supposed to be a hand drill with a compressed air-excited percussion mechanism are created, with switching time delays can be largely switched off. The for reloading the dead volumes required energy should be reduced, and the energy balance for the impact generation should be improved overall.
  • the hand drill should also be larger Possibilities of variation in the adjustability of the single impact energy and the impact frequency of the axial blows generated.
  • the solution to these tasks is a hand drill with one within one Device housing arranged, compressed air excited percussion, which in the characteristic Section of claim 1 features listed.
  • the inventive Hand drill has an air-powered hammer mechanism for generation from axial impacts, which is connected to a compressed air source via a switching valve is.
  • the striking mechanism comprises a pneumatic cylinder which has at least one ventilation and has at least one vent hole. Is inside the pneumatic cylinder a percussion piston, which can be pressurized with compressed air and periodically against The striking element can be accelerated.
  • the striking element penetrates a front one Boundary wall of the pneumatic cylinder axially and is used for the transmission of axial Impacts on a drilling or chiseling tool clamped in a tool holder.
  • a rotary drive arranged in the housing allows rotation of the in the Tool holder clamped drilling or chisel tool around its axis.
  • the switching valve is integrated in the percussion piston and has cutouts and bores, which alternate with the ventilation hole in the pneumatic cylinder in Active connection can be brought.
  • the switching valve is located in that the switching valve is integrated in the percussion piston within the working volume of the pneumatic cylinder.
  • the vent hole is used exclusively the discharge of compressed air from the pneumatic cylinder.
  • the dead volumes that be reloaded from pressureless to pressurized state at every cycle are limited to the cutouts and holes in the switching valve. By the reduction in dead volumes becomes the energy required for reloading is reduced, and the overall energy balance for impact generation is improved.
  • the Number of lines, connections and machine elements is reduced by Instead of the separate switching valve, the percussion piston takes over the valve function. Switching delays can be avoided because the percussion piston is its own Is limit switch.
  • the percussion piston has an integrated one Switching piston on which is axially displaceable between two end positions, the The switching valve can be switched in the ventilation position.
  • the percussion piston forms a valve housing in which a cylindrical switching element is axially displaceable.
  • the switching piston By the switching piston at the forward stroke the front surface and at Reverse stroke projects beyond and beyond the rear boundary surface of the percussion piston the percussion piston in contact with the front or rear boundary wall of the pneumatic cylinder, it forms the limit switches for the two extreme positions of the Percussion piston. Switching delays between the limit switch and the switching valve are excluded because the switching piston also forms the valve body.
  • the Shift piston protrudes beyond the boundary surfaces of the percussion piston and is already in System to the front or rear boundary wall of the pneumatic cylinder before the percussion piston has reached its extreme position. This will make the Shift piston axially displaced within the percussion piston and the switching valve is switched from the loading to the venting position and vice versa.
  • the spring element Preferably in the volume between the rear boundary surface of the Percussion piston and the rear boundary wall of the pneumatic cylinder Spring element arranged.
  • the spring element takes on the backward movement of the Percussion piston energy and thereby supports the forward acceleration in Direction of the striking element.
  • When braking the accelerated backwards Percussion piston its kinetic energy is stored in the spring and at Forward stroke returned to the percussion piston.
  • the axial arrangement of which can be changed in the pneumatic cylinder can be very simply a stroke adjustment can be realized.
  • the single impact energy and the impact frequency are very easily adjustable, without having to change the supply pressure.
  • large single impact energies are low Beat frequencies adjustable.
  • the positioning plate at a shorter distance from the striking element are axial strikes can be produced with low single impact energy and high impact frequencies.
  • the axial arrangement of the adjusting plate is preferably continuously adjustable.
  • the pneumatic cylinder in its rear section for example, with a Be equipped with an internal thread.
  • the setting plate has on its circumference corresponding external thread. This makes the stroke very easy to adjust, by screwing the positioning plate more or less far into the pneumatic cylinder becomes.
  • the axial arrangement of the The shelf is automatically adjustable. This can, for example, also in accordance with Predefinable criteria take place during the operation of the hand drill.
  • FIG. 1 shows a block diagram of the hand drill equipped according to the invention, which is generally designated 1. It has a housing 2 with a handle 3, on which a main switch 4 for activating the hand drill 1 is arranged.
  • the Supply of electrical components arranged within the housing 2 Energy is supplied via an electrical supply line, which is provided with the reference number 5 is.
  • a tool holder is located on the side of the housing 2 opposite the handle 3 6 provided, in which a drilling or chiseling tool can be clamped, which is indicated in Fig. 1 with the reference numeral 7.
  • Inside the housing 2 is a electric drive motor 8 arranged inside the housing 2 .
  • the drive shaft 9 of the drive motor is with connected to a gear arrangement 10 which has two outputs.
  • gear arrangement 10 is used for the rotary drive of the tool holder 6 clamped drilling tool 7.
  • an output shaft 11 of the Gear arrangement 10 provided with a bevel gear 12, which is in a rotationally locking Engagement with a circumferential toothing 13 of a machine spindle 14 is.
  • the torque the axially rotatable machine spindle 14 is on a transmission member 15 the tool holder 6 and the drilling tool clamped in the tool holder 7 transferable.
  • a shaft 16 which is provided at the second output of the gear arrangement 10, drives a compressor 17 for generating compressed air.
  • the output 20 of the Compressor 17 is provided with a ventilation bore 23 of a pneumatic cylinder 22 compressed air-excited percussion mechanism 21, which is preferably coaxial within the Machine spindle 14 is arranged.
  • An input 18 of the compressor 17 is connected to one Vent hole 24 of the pneumatic cylinder 22 connected.
  • To compensate for Leakage is at the entrance of the compressor 17 at least one further air inlet provided, which is indicated by the reference numeral 19.
  • From the Schlagtechnik 21 Axial impacts are generated by a striking element on the tool holder 6 clamped drilling tool 7 transferable.
  • Fig. 2 shows a schematic axial section of the air-powered hammer mechanism 21.
  • Der Pneumatic cylinder 22 has a ventilation hole 23 and a ventilation hole 24 on, which are connected to the compressed air source, for example the compressor.
  • the working space of the pneumatic cylinder 22 is through a front boundary surface 25 and a rear boundary surface 26 bounded.
  • the front boundary surface 25 is struck axially by the striking element 15, which projects into the working space.
  • the striking element 15 also fulfills the function of a Torque transmission member for the rotation of the tool holder clamped drilling tool.
  • a sealing ring 38 seals the working space of the printing cylinder in the area of the penetrating the front boundary surface 25 Döpperelements 15 to the outside.
  • the rear boundary surface 26 is with Advantage formed by an adjusting plate 27 which is provided with an external thread 28.
  • an adjusting plate 27 which is provided with an external thread 28.
  • the volume of the Working space of the pneumatic cylinder 22 can be changed by adjusting the setting plate 27.
  • the position of the positioning plate 27 can be changed manually if required.
  • the setting plate 27 depending on predefinable criteria automatically, for example with the help of a servomotor, adjustable.
  • the adjustment of the setting plate can for example also during the Operation of the hand drill done to the single impact energy and the impact frequency adjust the axial strikes generated by the striking mechanism.
  • the working space of the pneumatic cylinder 22 is in a by a percussion piston 30 front pressure chamber 35 and a rear pressure chamber 36 divided.
  • the Front pressure chamber 35 extends between the front baffle 33 of the Percussion piston 30 and the front boundary surface 25 of the pneumatic cylinder 22.
  • the rear pressure chamber 36 is in the axial direction from the rear surface 34 of the Percussion piston 30 and the rear boundary surface 26 of the adjusting plate 27 limited.
  • the percussion piston 30 has an essentially symmetrical outer contour on. Two punctures on its circumference result in connection with the cylindrical Housing of the pneumatic cylinder 22 a front annular space 31 and one rear annular space 32.
  • a coil spring 40 is located in the rear pressure chamber 36 arranged, for example in the illustrated embodiment Supporting plate 27 supports. The coil spring 40 is between the adjusting plate 27 and the Back surface 34 of the piston 30 compressible.
  • a Switching piston 41 arranged, which is axially displaceable and a greater axial length has as the percussion piston 30.
  • the switching piston 41 is constructed symmetrically and has an enlarged central section 42.
  • the axial Slidability of the switching piston 41 is by stop shoulders for the Center section 42 limited.
  • a front stop shoulder 43 is through the Jump in diameter of the stepped bore 39 formed in the percussion piston 30.
  • the rear stop shoulder 45 is from the boundary surface of a locating bushing 44 formed, which surrounds the rear portion of the switching piston 41 and in the stepped bore 39 is screwed in or held in a press fit.
  • the axial Distance of the stop schools 43 and 45 is greater than the axial extent of the Diameter expanded central portion 42 and limits the axial displacement of the switching piston 41 mounted within the percussion piston 30.
  • the switching piston 41 is provided with bores and annular spaces, which together with the annular spaces 31, 32 and control bores of the percussion piston 30 have an integrated valve function Endpoint switchover result.
  • FIG. 3 and 4 show the percussion piston 30 in its forward stroke in the direction of the striking element 15.
  • the switching piston 41 has axial blind bores 46 and 48 provided, the mouths in the front and in the rear pressure chamber 35th or 36 points.
  • the axial blind holes 46 and 48 are with valve chambers 47 or 51 in connection, which are punctures on the circumference of the enlarged Center section 42 are formed.
  • a connecting hole 50 connects the front annular space 31 of the percussion piston 30 with the stepped bore 39 Ventilation bore 23 to the pneumatic cylinder 22 supplied compressed air is permanent on the annular space 31, while the rear annular space 32 permanently with the Vent hole 24 is connected.
  • the one lying against the front annular space 31 arrives Compressed air via the connection hole 50 into the valve chamber 51 and via the blind hole 48 into the rear pressure chamber 36.
  • the percussion piston 30 accelerated in the direction of the striking element 15.
  • the front pressure chamber 31 is via the blind hole 46, the valve chamber 47 and one in the percussion piston 30 provided control bore 52 through the vent hole 24 in the pneumatic cylinder 22 vented.
  • Fig. 3 shows the percussion piston 30 in a position just before its Baffle 33 bumps against the striking element 15.
  • the longer switching piston 41 protrudes the baffle 33 of the percussion piston 30 and is already in contact with front boundary surface 25 of the pneumatic cylinder 22.
  • Fig. 4 shows the state in which the percussion piston 30 its extreme front position has reached and the switching piston 41 is completely axially displaced.
  • the back one Section of the switching piston 41 projects beyond the rear surface 34 of the percussion piston 30.
  • the compressed air passes through the mouth the front blind hole 46 in the of the baffle 33 and the front Boundary surface 25 limited, front pressure chamber.
  • 4 is the front one Pressure chamber shown completely closed.
  • the kinetic energy of the Percussion piston 30 is delivered to the striker 15. This bounces off Percussion piston 30 immediately afterwards, the front pressure chamber again is opened and can be filled with compressed air.
  • Fig. 5 shows the percussion piston 30 during the reverse stroke, just before its rearward stroke Extreme position.
  • the rear pressure chamber 36 is almost completely closed.
  • the coil spring 40 is between the rear surface 34 of the percussion piston 30 and the setting plate 27 pressed together. It is used for energy storage at Backward movement of the percussion piston 30.
  • the front pressure chamber 35 is almost fully open.
  • the ventilation of the front and rear Pressure chambers 35 and 36 take place according to the diagram explained with reference to FIG. 4. In in the position shown is the switching piston projecting beyond the rear surface 34 41 already in contact with the rear boundary surface 26. By moving on of the percussion piston 30 to its rear dead center, the switching process of Valve performed automatically.
  • the percussion piston 30 has reached its rear dead center.
  • the Switching process by axially shifting the switching piston 41 is complete and the valve is switched.
  • the coil spring 40 has its greatest possible compression reached. When relaxing, it supports the acceleration of the percussion piston 30 in Direction of the striking element 15 by applying the energy stored in it to it delivers.
  • the axial displacement of the switching piston 41 reaches the Ventilation bore 23 and the front annular space 31 adjacent compressed air via the Connection bore 50, the valve chamber 51 and the blind bore 48 in the opening rear pressure chamber and accelerates the percussion piston 30 in the direction of the striking element 15.
  • the front pressure chamber 35 is in turn over the Blind hole 46, the valve chamber 47, the control hole 52, the rear Annulus 32 and the vent hole 24 vented.
  • the inventive integration of the switching valve in the percussion piston has the The advantage is that the valve function and the end switching function are fulfilled by one part become. The end position detection and the switchover take place simultaneously. Switching delays can be avoided in this way.
  • the energy is stored during the backward movement the percussion piston with the aid of a spring element, in particular one Coil spring. As a result, a forward and return stroke continuous energy supply by the compressor. Additional pressure accumulators are not required.
  • the energy storage can also be done via an air cushion take place between the rear surface of the percussion piston and the rear Boundary surface of the pneumatic cylinder is built up.
  • the rear boundary surface in the area of the mouth of the blind hole in Shift piston is provided with recesses, which during the switching process of the Switch piston already allow ventilation of the rear pressure chamber and prevent complete closure at the rear dead center.
  • Percussion mechanism according to the invention can also be arranged in a hand-held device, the Compressed air reservoir for the operation of the striking mechanism.
  • the hand drill can also be operated as a whole via a compressed air source be operable. In this case, both the rotary drive of the drilling tool and also the operation of the striking mechanism with the aid of a compressed air source, for example one Compressed air line.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Drilling And Boring (AREA)
EP99810527A 1998-07-22 1999-06-14 Machine à forer portable avec mécanisme à percussion mû à l' air comprimé Withdrawn EP0974428A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19832946A DE19832946A1 (de) 1998-07-22 1998-07-22 Handbohrgerät mit drucklufterregtem Schlagwerk
DE19832946 1998-07-22

Publications (2)

Publication Number Publication Date
EP0974428A2 true EP0974428A2 (fr) 2000-01-26
EP0974428A3 EP0974428A3 (fr) 2003-02-12

Family

ID=7874904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99810527A Withdrawn EP0974428A3 (fr) 1998-07-22 1999-06-14 Machine à forer portable avec mécanisme à percussion mû à l' air comprimé

Country Status (5)

Country Link
US (1) US6209659B1 (fr)
EP (1) EP0974428A3 (fr)
JP (1) JP2000071117A (fr)
CN (1) CN1251794A (fr)
DE (1) DE19832946A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7868750B2 (en) 2008-02-06 2011-01-11 Ford Global Technologies, Llc System and method for controlling a safety restraint status based on driver status
US8106759B2 (en) 2008-02-06 2012-01-31 Ford Global Technologies, Llc System and method for controlling early low fuel warning based on driver status
US8258939B2 (en) 2008-02-06 2012-09-04 Ford Global Technologies, Llc System and method for controlling one or more vehicle features based on driver status
US8280580B2 (en) 2008-02-06 2012-10-02 Ford Global Technologies, Llc System and method for controlling electronic stability control based on driver status
US8306728B2 (en) 2008-02-06 2012-11-06 Ford Global Technologies, Llc System and method for controlling object detection based on driver status

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DE10033362A1 (de) * 2000-07-08 2002-01-17 Hilti Ag Elektrohandwerkzeug mit Leerschlagabschaltung
DE10117123A1 (de) * 2001-04-06 2002-10-17 Bosch Gmbh Robert Handwerkzeugmaschine
DE10145464C2 (de) * 2001-09-14 2003-08-28 Wacker Construction Equipment Bohr- und/oder Schlaghammer mit anpressdruckabhängiger Leerlaufsteuerung
DE10259566A1 (de) * 2002-12-19 2004-07-01 Hilti Ag Schlagende Elektrohandwerkzeugmaschine
US6715562B1 (en) * 2003-05-08 2004-04-06 Power Network Industry, Co., Ltd. Output shaft locking device
EP1514518A1 (fr) * 2003-09-11 2005-03-16 SDGI Holdings, Inc. Instruments à percussion pour la préparation des plateaux vertébraux
JP4200918B2 (ja) 2004-02-09 2008-12-24 日立工機株式会社 穿孔機
DE102005028918A1 (de) * 2005-06-22 2006-12-28 Wacker Construction Equipment Ag Bohr- und/oder Schlaghammer mit Leerlaufsteuerung
SE529615C2 (sv) * 2006-02-20 2007-10-09 Atlas Copco Rock Drills Ab Slagverk och bergborrmaskin samt förfarande för att styra slagkolvens slaglängd
DE102006000253A1 (de) * 2006-05-30 2007-12-06 Hilti Ag Schlagende Handwerkzeugmaschine mit axial beweglich gelagertem Schlagwerk
DE102006054288A1 (de) * 2006-11-17 2008-05-21 A & M Electric Tools Gmbh Bohrhammer
US7926690B1 (en) * 2007-06-13 2011-04-19 Tippmann Sr Dennis J Combustion powered driver
DE102007050307A1 (de) * 2007-10-22 2009-04-23 Robert Bosch Gmbh Handwerkzeugmaschine
US8240394B2 (en) * 2008-12-09 2012-08-14 Sp Air Kabushiki Kaisha Hammer with vibration reduction mechanism
US10052747B2 (en) * 2012-09-03 2018-08-21 Makita Corporation Hammer tool
AT513849B1 (de) * 2013-03-04 2014-08-15 Tmt Bbg Res And Dev Gmbh Steuerung der Arbeitsfrequenz eines Schlagwerkes
US10189173B1 (en) * 2017-11-16 2019-01-29 Storm Pneumatic Tool Co., Ltd. Pneumatic tool
CN114986466B (zh) * 2022-06-21 2025-04-22 北京润泽金松科技发展有限责任公司 一种破拆工具设备
WO2025088211A1 (fr) * 2023-10-28 2025-05-01 Rhefor (Deutschland) Gmbh Outil de travail à mécanisme de percussion électropneumatique

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7868750B2 (en) 2008-02-06 2011-01-11 Ford Global Technologies, Llc System and method for controlling a safety restraint status based on driver status
US8106759B2 (en) 2008-02-06 2012-01-31 Ford Global Technologies, Llc System and method for controlling early low fuel warning based on driver status
US8258939B2 (en) 2008-02-06 2012-09-04 Ford Global Technologies, Llc System and method for controlling one or more vehicle features based on driver status
US8280580B2 (en) 2008-02-06 2012-10-02 Ford Global Technologies, Llc System and method for controlling electronic stability control based on driver status
US8306728B2 (en) 2008-02-06 2012-11-06 Ford Global Technologies, Llc System and method for controlling object detection based on driver status
US8384535B2 (en) 2008-02-06 2013-02-26 Ford Global Technologies, Llc System and method for controlling early low fuel warning based on driver status
US8548730B2 (en) 2008-02-06 2013-10-01 Ford Global Technologies, Llc System and method for controlling object detection based on driver status
US8576061B2 (en) 2008-02-06 2013-11-05 Ford Global Technologies, Llc System and method for controlling one or more vehicle features based on driver status

Also Published As

Publication number Publication date
JP2000071117A (ja) 2000-03-07
DE19832946A1 (de) 2000-01-27
CN1251794A (zh) 2000-05-03
EP0974428A3 (fr) 2003-02-12
US6209659B1 (en) 2001-04-03

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