EP0759340B1 - Impulswerkzeug - Google Patents

Impulswerkzeug Download PDF

Info

Publication number
EP0759340B1
EP0759340B1 EP95112983A EP95112983A EP0759340B1 EP 0759340 B1 EP0759340 B1 EP 0759340B1 EP 95112983 A EP95112983 A EP 95112983A EP 95112983 A EP95112983 A EP 95112983A EP 0759340 B1 EP0759340 B1 EP 0759340B1
Authority
EP
European Patent Office
Prior art keywords
pulse
tool according
roller
pulse tool
hydraulic cylinder
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.)
Expired - Lifetime
Application number
EP95112983A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0759340A1 (de
Inventor
Konrad Kettner
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.)
Cooper Industries LLC
Original Assignee
Cooper Industries LLC
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 Cooper Industries LLC filed Critical Cooper Industries LLC
Priority to ES95112983T priority Critical patent/ES2147250T3/es
Priority to DE59508325T priority patent/DE59508325D1/de
Priority to EP95112983A priority patent/EP0759340B1/de
Priority to US08/689,129 priority patent/US5813478A/en
Priority to CA002182632A priority patent/CA2182632A1/en
Priority to BR9603450-5A priority patent/BR9603450A/pt
Publication of EP0759340A1 publication Critical patent/EP0759340A1/de
Application granted granted Critical
Publication of EP0759340B1 publication Critical patent/EP0759340B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/145—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers
    • B25B23/1453—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers for impact wrenches or screwdrivers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket

Definitions

  • the invention relates to an impulse tool, in particular a screwdriver, with the features the preamble of claim 1.
  • Such a pulse tool is known from EP 0 353 106 B1.
  • the pulse unit is radially adjustable in appropriate grooves. These grooves run for the sealing wing along a diameter of the output shaft or spindle, while the corresponding grooves for the sealing rollers are an obtuse angle smaller Include as 180 ° with the longitudinal direction of the drive spindle. Because of this inclination The grooves for the sealing rollers to each other ensure that only one Rotation position one pulse is transmitted per 360 ° rotation. The effort to manufacture of such an impulse tool and the corresponding costs are relatively high.
  • Another pulse tool is known from EP 0 254 699 B1.
  • the sealing rollers are always in contact with a rolling surface and in particular tools every half a turn of the hydraulic cylinder with the corresponding Sealing strips or compression bars in the system.
  • Offset by 90 ° to the sealing rollers projecting ribs are arranged on the output shaft or drive spindle an inclined axis of rotation of the output shaft.
  • Corresponding rib-like projections are also provided on the inner wall of the hydraulic cylinder.
  • a disadvantage of the pulse tool known from EP 0 254 699 B1 is that the Structure of the pulse unit is relatively complex. In addition to the two sealing rollers and radial grooves are additionally two ribs on the output shaft and on the inner wall of the To produce hydraulic cylinders that run inclined. This makes it more difficult and more expensive the production of the known pulse tool. Finally, the disadvantage is that the ribs must be made with high accuracy in order for the seal between the ribs of the output shaft and hydraulic cylinder is sufficiently good. On certain wear of the ribs and thus deterioration of the seal but not to be prevented after a certain period of use of the pulse tool.
  • the invention is based on the pulse tool known from EP 0 353 106 B1 based on the task of improving the known impulse tool in such a way that its construction is inexpensive while extending the operating time is simplified.
  • This task is related to an impulse tool with the features of the preamble of claim 1 solved in that the delayed radial movement a sealing roller serving as a compensating roller to the outside whose radial groove Stroke delay device.
  • the stroke delay device ensures that the Compensating roller in its radial groove a radial movement outwards in the direction Performs hydraulic cylinder. However, this movement occurs during one revolution of the cylinder so delayed that the compensating roller in a single rotational position a sealing strip is in contact. The radial movement can be decelerated to the extent that even during the remaining rotation of the hydraulic cylinder, the compensating roller only and is partially in contact with a sealing surface.
  • compensating roller and other sealing rollers which serve as an impulse roller, and associated ones Radial grooves 180 ° offset from each other.
  • One exemplary embodiment of a stroke delay device is characterized in that this is formed by the guide of the compensating roller in its radial groove, the Leveling roller compared to the impulse role with less play is guided in its radial groove.
  • This game achieves that the exchange of hydraulic fluid over the low Play between radial groove and compensating roller during one complete rotation of the hydraulic cylinder is not complete can be carried out. This leads to the delayed fluid exchange in addition to a certain vacuum between the compensating roller and radial groove, which supports the stroke deceleration.
  • a different game between radial grooves and sealing rollers can be produced by, for example, a compensating roller and pulse roller have the same dimensions and the radial grooves are different. It is also possible that the Radial grooves of the same dimensions and compensation and impulse roller have different diameters.
  • a simple application of force to the sealing roller towards the inside wall of the cylinder can be realized in that between the groove bottom and the sealing rollers, a spring element, in particular a leaf spring is arranged.
  • the stroke delay device can additionally to the guides mentioned above can be realized that to the limited radial movement of the compensating roller the spring constant of the associated spring element is less than the spring constant of the spring of the impulse roller.
  • the inner wall of the hydraulic cylinder and the Sealing strips of heavy wear when operating the pulse tool exposed it is advantageous if the inner wall of the hydraulic cylinder at least in the area of Sealing rollers is formed by a hydraulic sleeve on the Inside the sealing strips are arranged. If the Sealing strips, only the hydraulic sleeve is replaced. The rest Pulse unit can still be used.
  • High pressure and low pressure chambers in the angular momentum position are easy to form on the inside of the Hydraulic sleeve formed between the sealing strips pockets. They can be identical or with different dimensions for High pressure and low pressure chamber are manufactured.
  • the pockets are by protruding radially from the inside of the hydraulic sleeve Inner ring flanges limited, along which at least the impulse roller rolls off while the balancing roller, for example only shortly before reaching the pulse position along the inner ring flanges rolls off.
  • Hydraulic cylinder arranged between two lateral contact discs, where the engine washer adjacent to one radially inward protruding shoulder of the hydraulic cylinder and the opposite contact disc on one in the hydraulic cylinder screw-in bearing ring.
  • a central hole is concentric to the output shaft and at least over part of the output wavelength is trained in this.
  • the central bore can also be used to determine the pressure inside of the formed between the output shaft and hydraulic sleeve Fluid space can be used. It is beneficial if at least one connection hole each in the output shaft is formed between the radial grooves, which central bore and fluid space connects. The pressure determination can be done in a known manner Way done by an appropriate pressure sensor.
  • connection hole it is radial formed in the output shaft and by 90 ° to each Radial grooves offset.
  • a valve screw for stepless and adjustable closing of the throttle bore is screwed into the central bore.
  • Is for the relative displacement of the compensating piston and hydraulic cylinder a valve between the compensating piston and the fluid chamber for pressurizing the sealed against the hydraulic cylinder
  • Area of the compensating piston arranged by the relative displacement between the compensation piston and Hydraulic cylinder builds up pressure while filling the pulse unit be monitored with hydraulic fluid. Likewise can from a reduction in the relative displacement after filling the Pulse unit with hydraulic fluid or from one The shift does not occur during filling that there is a leak in the pulse unit.
  • FIG. 1 shows a longitudinal section through a pulse tool 1. The cut does not extend through in one housing 49 of the pulse tool 1 arranged components.
  • the pulse tool 1 has a pistol-like outline, wherein in a handle 50 a pusher 51 and connections 52 and 53 are arranged for compressed air and exhaust air.
  • the pusher 51 is slidably mounted in the handle 50 by means of a plunger 54.
  • the free end of the plunger 54 is adjacent to one Free end of a tilt valve 55 is arranged.
  • the ram 54 Tilting valve 55 By moving the Push button 51 to the right in FIG. 1 is the ram 54 Tilting valve 55 also tilted to the right. This will make a Valve plate 56 pivoted against the force of a compression spring 57 and gives an opening for the supply of compressed air via compressed air connection 52 to a motor 3 free.
  • the compressed air passes along a line 66 to the compressed air motor trained motor 3. Its direction of rotation is through a switch button 58 switchable.
  • motor 3 With the motor 3 is a pulse unit via a connector 47 2 connected, which rotates accordingly with motor 3.
  • a gearbox can be used between the motor 3 and the pulse unit 4 Coupling (not shown) may be arranged.
  • the pulse unit 2 is rotatably supported in the housing 49 Hydraulic cylinder 4, one on this on its engine side End fitted compensation piston 42, a bearing ring 35 and an output shaft 5 are formed.
  • the output shaft 5 protrudes from the housing 49 like a pistol, on her protruding end a connector sleeve 44 is attached.
  • the compressed air supplied to the motor 3 via line 66 becomes corresponding via the exhaust port 53 from the pulse tool 1 dissipated.
  • FIG. 2 the pulse unit 2 from FIG. 1 is enlarged and shown in longitudinal section.
  • the hydraulic cylinder 4 of the pulse unit 2 is one-sided open cylinder.
  • a hydraulic sleeve 21 is inserted in it, which bears against its inner wall 10.
  • At both ends in Axial direction 23 of the hydraulic sleeve 21 are contact discs 32 and 33.
  • the engine disk 33 closer to the engine is located on one in the radial direction 29 inwardly projecting paragraph 34 of the Hydraulic cylinder 4. This forms an annular one Stop against which in the direction of connector 47 to the engine a cylindrical cavity with compared to the cross section of the Hydraulic cylinder 4 reduced in the region of the hydraulic sleeve 21 Cross section connects.
  • the output shaft 5 is rotatably mounted inside the hydraulic cylinder 4 and the hydraulic sleeve 21 .
  • the output shaft 5 extends essentially from the connector 47 through the hydraulic cylinder 4 and protrudes from its open end.
  • the output shaft 5 essentially has a circular shape Cross-section, two in the area of the hydraulic sleeve 21 diametrically opposite, extending in the axial direction 23 Radial grooves 8 and 9 are formed in the output shaft 5. Furthermore, one extends concentrically to the output shaft 5 extending central bore 36 approximately over half the length of the Output shaft 5. This central bore 36 is in the above End section of the output shaft 5 with a hexagon socket designed to accommodate nuts or screws.
  • the output shaft 5 is in the hydraulic cylinder 4 both in the cross section of the motor-side end section of the Hydraulic sleeve as well as in one in the open end of the hydraulic sleeve 4 screwed bearing ring 35 rotatably mounted.
  • the Bearing ring 35 is with its larger diameter section screwed into the hydraulic sleeve 4 so far that it on the Contact disc 32 lies opposite the hydraulic sleeve 21.
  • radial grooves 8 and 9 are used as a compensating roller Sealing roller 6 and a sealing roller serving as an impulse role 7 slidably supported in radial directions 29.
  • the length 24 of the sealing rollers 6 and 7 corresponds to the length of the hydraulic sleeve 21 in the axial direction 23.
  • leaf springs 19 and 20 are leaf springs 19 and 20 arranged radially after the sealing rollers pressurize outside.
  • the radial grooves 8, 9 extend over a greater length as sealing rollers 6, 7 in the axial direction 23 and are on both sides about this and the system discs 32 and 33 before.
  • a compensating piston 42 is attached at the motor end of the hydraulic cylinder 4 at the motor end of the hydraulic cylinder 4 at the motor end of the hydraulic cylinder 4 is on this a compensating piston 42 is attached.
  • two O-rings 61 are provided for sealing the compensating piston 42 from the hydraulic cylinder 4. More 0 rings 61 serve to seal the output shaft 5 within the hydraulic cylinder 4, to seal the in the hydraulic cylinder 4 screwed bearing rings 35 and for sealing the output shaft 5 compared to the bearing ring 35 or Valve screw 41.
  • Valve 43 is arranged inside the wall of the hydraulic cylinder 4.
  • An associated valve ball lies on the contact disk 33 and is moved by an associated compression spring towards the system disc 33 powered. Via the valve 43 is below Pressurized hydraulic fluid between the sealed area Compensating piston 42 and hydraulic cylinder 4 can be supplied. As a result, the compensating piston 42 is relative to the hydraulic cylinder 4 in Figure 2 to the right depending on the prevailing pressure.
  • the inner ring flanges 27 and 28 according to FIG. 2 make two concentric to each other, eccentric to the hydraulic cylinder 4 arranged circles 30, 31 determined. With these circles are 3 pulse roller 7 and compensating roller 6 in the system.
  • the Fluid space 39 between the output shaft 5 and the inside 22 of the hydraulic sleeve 21 is formed by two pockets 25 and 26 which between two radially projecting sealing strips 11 and 12 extend. In the axial direction 23, see FIG. 2, the pockets extend between the inner ring flanges 27 and 28. Since the bags communicate with each other, is even when the hydraulic cylinder 4 and the hydraulic sleeve 21 rotate in the direction of rotation 62 an exchange of the hydraulic fluid 63 between the bags possible. Only in the pulse position according to the figure 8 are the pockets created by the balance roller 6 and impulse roller 7 on sealing strips 11 and 12 from each other Cut. In this position, the cylinder 4 generates a pulse the output shaft 5 transmitted.
  • FIG 3 shows the connecting bores 37 and 38, which are offset by 90 ° relative to the sealing rollers 6, 7 and are arranged diametrically to each other.
  • the connecting hole 38 is with a central bore 36 by means of a throttle bore 40 connected.
  • the cross section of the throttle bore is less than the cross section of the connecting bore 38.
  • Figure 3 shows a 60 ° compared to a pulse position in Direction of rotation 62 represents twisted movement phase
  • the way in the movement phases according to FIGS. 4 to 8 is the hydraulic cylinder 4 with sealing sleeve 21 by a further 60 ° each the output shaft 5 rotated.
  • hydraulic cylinder 4 and hydraulic sleeve 21 are around rotated another 60 ° in the direction of rotation 62 with respect to the output shaft 5.
  • the compensating roller 6 is in System with circles 30, 31, that is, it lies on the inner ring flanges 27 and 28 according to FIG. 2.
  • the pulse position are both balancing role 6 and pulse role 7 with the corresponding sealing strips 11 or 12 in the system, so that the pockets 25, 26 are separated and an exchange of hydraulic fluid between these pockets no longer can take place.
  • the pocket 26 becomes a high-pressure chamber 64 and the bag 25, see Figure 3, to a low pressure chamber 65.
  • the different pressure conditions in the chambers are distinguished by a different number and one different sizes of circles to represent the hydraulic fluid 63 shown.
  • connection of high pressure chamber 64 and low pressure chamber 65 via the connecting bores 37 and 38 and via the throttle bore 40 can be done by screwing in the valve screw 41 are limited according to Figure 2, whereby the hardness of the on the output shaft 5 in Figure 8 transmitted pulses adjustable is.
  • the sealing strips 11 and 12 are designed with different heights, so that due to the stroke delay device 13 Compensating roller 6 during one revolution of the hydraulic cylinder 4 so far from its radial groove over the circumference 16 of the output shaft 5 moved out that they only continue with the radial inwardly projecting sealing strip 11 comes into contact.
  • the sealing strips 11 and 12 between extend the inner ring flanges 27 and 28 and connect them. They are of the same height as this, so that in the pulse position according to FIG. 8 compensating roller 6 and pulse roller 7 over their entire length 24 with the inner ring flanges 27 and 28 and the sealing strips 11 and 12 are in the system.
  • sealing strips 11 and 12 are shown for emphasis with exaggerated height. For the same reason, the representation itself became better known Components, such as a shutdown device for the motor when a set torque is reached or the like, dispensed with in FIGS. 1 and 2.
  • the pulse unit 2 is with an incompressible medium to Example a hydraulic fluid filled.
  • the sealing rollers are only in a single rotational position of the hydraulic cylinder 4 along their entire length with the inside 22 of the hydraulic sleeve 21. In this position, the fluid space 39 separated into a high pressure chamber and a low pressure chamber. This position corresponds to the transmission of impulses to the output shaft 5. The transfer only takes so long until the Sealing strips 11, 12 have run over the sealing rollers and Output shaft by a certain angle of rotation due to the different Pressure conditions in the chambers. This is followed by the next rotation of the hydraulic cylinder 4 an acceleration of the pulse unit again.
  • the pulse unit can be accelerated over a full revolution, what is the energy transfer to the bolt / nut compared to the transfer increased by two pulses per revolution.
  • the pulse tool according to the invention as a multiple and in particular To use as a two-pulse unit is to use two in the latter case the compensating rollers and impulse rollers in radial grooves of the output shaft described above to be provided with appropriate stroke delay devices for the compensating rollers. In this way, each revolution of hydraulic cylinder 4 with hydraulic sleeve 21 each transmit two pulses to the output shaft.
  • sealing strips and connecting holes can be arranged analogously for two compensating rollers and two impulse rollers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Earth Drilling (AREA)
  • Hydraulic Motors (AREA)
  • Actuator (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
EP95112983A 1995-08-17 1995-08-17 Impulswerkzeug Expired - Lifetime EP0759340B1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
ES95112983T ES2147250T3 (es) 1995-08-17 1995-08-17 Herramienta de impulsos.
DE59508325T DE59508325D1 (de) 1995-08-17 1995-08-17 Impulswerkzeug
EP95112983A EP0759340B1 (de) 1995-08-17 1995-08-17 Impulswerkzeug
US08/689,129 US5813478A (en) 1995-08-17 1996-07-30 Pulse tool
CA002182632A CA2182632A1 (en) 1995-08-17 1996-08-02 Pulse tool
BR9603450-5A BR9603450A (pt) 1995-08-17 1996-08-16 Ferramenta de impulso

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP95112983A EP0759340B1 (de) 1995-08-17 1995-08-17 Impulswerkzeug

Publications (2)

Publication Number Publication Date
EP0759340A1 EP0759340A1 (de) 1997-02-26
EP0759340B1 true EP0759340B1 (de) 2000-05-10

Family

ID=8219534

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95112983A Expired - Lifetime EP0759340B1 (de) 1995-08-17 1995-08-17 Impulswerkzeug

Country Status (6)

Country Link
US (1) US5813478A (es)
EP (1) EP0759340B1 (es)
BR (1) BR9603450A (es)
CA (1) CA2182632A1 (es)
DE (1) DE59508325D1 (es)
ES (1) ES2147250T3 (es)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202009009427U1 (de) 2009-07-09 2010-11-11 Cooper Power Tools Gmbh & Co. Ohg Impulswerkzeug

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE509915C2 (sv) * 1997-06-09 1999-03-22 Atlas Copco Tools Ab Hydraulisk momentimpulsgeneratoror
JP3615125B2 (ja) * 2000-03-30 2005-01-26 株式会社マキタ オイルユニット及び電動工具
US6708778B2 (en) * 2001-01-12 2004-03-23 Makita Corporation Hydraulic unit with increased torque
US6487940B2 (en) 2001-01-23 2002-12-03 Associated Toolmakers Incorporated Nut driver
JP4200918B2 (ja) * 2004-02-09 2008-12-24 日立工機株式会社 穿孔機
ES2338690T3 (es) * 2006-11-13 2010-05-11 COOPER POWER TOOLS GMBH & CO. Herramienta con mecanismo hidraulico de percusion.
US20120137875A1 (en) * 2010-10-05 2012-06-07 Lin Tien Cylinder assembly for pneumatic motor and pneumatic motor comprising the same
TW201406501A (zh) * 2013-10-31 2014-02-16 Quan-Zheng He 氣動工具的衝擊組

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3192739A (en) * 1963-04-18 1965-07-06 Ingersoll Rand Co Sealing device
US3304746A (en) * 1965-02-01 1967-02-21 Ingersoll Rand Co Torque control device
US4175408A (en) * 1976-12-10 1979-11-27 Honda Giken Kogyo Kabushiki Kaisha Apparatus for absorbing oil pressure in an impact type tool
SE450222B (sv) * 1986-07-24 1987-06-15 Atlas Copco Ab Hydraulisk momentimpulsgenerator
JPH0223964U (es) 1988-07-29 1990-02-16
US5172772A (en) * 1991-03-11 1992-12-22 Cooper Industries, Inc. Hydro-impulse screw tool
SE9201405L (sv) * 1992-05-05 1993-06-21 Atlas Copco Tools Ab Hydraulisk momentimpulsgenerator
SE9400270D0 (sv) * 1994-01-28 1994-01-28 Atlas Copco Tools Ab Hydraulic torque impulse generator

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202009009427U1 (de) 2009-07-09 2010-11-11 Cooper Power Tools Gmbh & Co. Ohg Impulswerkzeug

Also Published As

Publication number Publication date
US5813478A (en) 1998-09-29
ES2147250T3 (es) 2000-09-01
DE59508325D1 (de) 2000-06-15
EP0759340A1 (de) 1997-02-26
BR9603450A (pt) 2004-08-17
CA2182632A1 (en) 1997-02-18

Similar Documents

Publication Publication Date Title
DE4028595C2 (es)
DE3817873A1 (de) Werkzeugrevolver
DE69601884T2 (de) Hydraulischer Drehschlagmechanismus
WO1996023670A1 (de) Antriebsvorrichtung, insbesondere radantrieb für kettenfahrzeuge
EP0759340B1 (de) Impulswerkzeug
WO1999057423A1 (de) Vorrichtung zur hydraulischen drehwinkelverstellung einer welle zu einem antriebsrad
DE2236257B2 (de) Reibungsgetriebe mit veränderlicher Übersetzung
DE2009324A1 (de) Schlagkupplung zur Erzeugung von Drehschlägen insbes. auf Werkzeuge
EP0735935B1 (de) Impulsschlagwerk, insbesondere für impulsschrauber
DE3347016C2 (es)
DE3904944C2 (de) Hydrostatisches Getriebe
EP0772746B1 (de) Positionierantrieb, insbesondere für eine werkzeugmaschine
DE2839408A1 (de) Hilfsgesteuerter fluidmotor mit veraenderlicher verdraengung
DE4113617C2 (es)
EP0650419A1 (de) Hydraulisches antriebs- und bremssystem.
DE1576142C3 (de) Hydraulisch oder pneumatisch betätig ter Drehantrieb
DE2516154A1 (de) Impulsgeber
DE4018084C1 (es)
DE102008022009A1 (de) Nockenwellenverstelleinrichtung
EP1090229A1 (de) Regelvorrichtung für hydraulische arbeitsgeräte
EP1287232B1 (de) Axialkolbenmaschine
DE19506663C2 (de) Impulsschrauber
EP1835111B1 (de) Türbetätigungsvorrichtung, insbesondere für eine Drehtür
DE2821339A1 (de) Hydraulische kolbenzylindervorrichtung zur hervorrufung einer axialen kolbenvibration
DE2508268B2 (de) Steuerkolben für hydraulische Druckmittelfolgesteuerungen, insbesondere für ein Lenkventil einer Servolenkeinrichtung von Fahrzeugen

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE ES FR GB IT LI SE

17P Request for examination filed

Effective date: 19970818

17Q First examination report despatched

Effective date: 19980217

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE ES FR GB IT LI SE

ITF It: translation for a ep patent filed
REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20000510

REF Corresponds to:

Ref document number: 59508325

Country of ref document: DE

Date of ref document: 20000615

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: JACOBACCI & PERANI S.A.

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000818

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2147250

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20030702

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20030804

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20031006

Year of fee payment: 9

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20010911

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040817

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040831

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040831

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20040817

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050429

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050817

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20080829

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20080808

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100302

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090818