EP0818640B1 - A phase variator - Google Patents
A phase variator Download PDFInfo
- Publication number
- EP0818640B1 EP0818640B1 EP19960201944 EP96201944A EP0818640B1 EP 0818640 B1 EP0818640 B1 EP 0818640B1 EP 19960201944 EP19960201944 EP 19960201944 EP 96201944 A EP96201944 A EP 96201944A EP 0818640 B1 EP0818640 B1 EP 0818640B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- duct
- obturator
- feed duct
- discharge
- piston
- 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
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/34403—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft
- F01L1/34406—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
Definitions
- the present invention relates to a single-acting phase variator according to the preamble to claim 1.
- variators may be of the double-acting type, when two supply chambers are provided at the opposite axial ends of the piston and the piston is moved as a result of the admission of pressurized oil to one or other of the chambers.
- Single-acting variators in which a single supply chamber is provided and the piston is moved towards an actuated position, against the action of a spring, by the hydraulic thrust generated thereon by the pressure of the oil admitted to the chamber, and is moved towards the opposite, non-actuated position, by the resilient thrust of the spring when the supply of oil to the chamber stops, are also known.
- a double acting phase variator is known from EP-A-0571023 to the same applicant.
- the present invention lies in particular in the technical field of single-acting phase variators.
- a single-acting phase variator having the features outlined above is known from FR 2657648.
- the spring in order to achieve rapid movement of the piston as a result of the hydraulic thrust of the oil, the spring must offer limited resilient resistance.
- the limited resilient loading of the spring involves the disadvantage of a low resilient thrust generated on the piston during its return stroke towards the non-actuated position when the oil is discharged from the supply chamber under the effect of the resilient load, with a consequent undesired slowing of the piston.
- phase variator which is designed structurally and functionally to allow the piston to move rapidly during the return stroke towards the non-actuated position, even with limited resilient loads.
- Figures 1 and 2 are axial sections of a variator formed according to the present invention, in two different operative positions.
- a phase variator according to the invention is intended to be interposed between a camshaft A of an internal combustion engine housed in a structural portion B of the engine, and a transmission, typically of the type with a toothed belt, of which a pulley C is shown, and which controls the timing mechanism of the engine.
- the phase variator 1 comprises a hub 2 bearing a threaded shank 3 fixed to the camshaft A by a screw coupling.
- An annular piston 6 covers the hub 2, more precisely, a cylindrical portion thereof, so as to be slidable axially on the cylindrical portion of the hub.
- This portion has axial splines 7 jointly defining a set of straight teeth; in complementary manner, the piston 6 has similar internal splines 8 forming a set of straight teeth complementary to and meshing with the splines 7.
- the assembly constituted by the hub 2 and the piston 6 is surrounded by a body constituting a casing 9 of the variator.
- the casing 9 is formed by two half bodies 10 and 11 fixed together by a screw coupling 12. Moreover, the half body 10 is sealingly engaged in the half body 11 by means of a seal 12a.
- the half body 11 has external threaded holes 14 for the fixing of the pulley C by means of screws 15 and is sealingly engaged on the hub 2 by means of a seal 11a.
- the half body 10 has a generally cylindrical skirt 16 closed at one axial end by a cover 17 and open at the opposite end.
- the cover 17 is prererably laser-welded to the skirt 16.
- the cover 17 has a blind axial hole constituting a seat 18 housing and supporting the free end 2a of the hub 2.
- Two adjacent cylindrical portions 19, 20 are identified in the skirt 16 of the half body 10.
- a set of helical teeth 25 is formed in the portion 19.
- the outside of the piston 6 has a first portion 26 carrying a set of helical teeth 27 meshed with the teeth 25; the piston also has a second portion 28, the free end of which has a flange 29 extending radially outwardly and engaged sealingly with the portion 20 of the skirt 16 with the aid of a piston ring 30.
- Braking means are provided between the hub 2 and the casing 9. These means comprise a ring 34 having a conical outer surface and a cylindrical inner surface and restrained axially on the hub 2.
- the half body 11 in turn has a conical inner surface in contact with the conical outer surface of the ring 34; the conical coupling between the two conical surfaces of the ring 34 and of the half body 11 is indicated 35.
- the ring 34 has peripheral recesses, indicated 36.
- the hub 2 has an axial cavity 41 closed at one end by the cover 17 and extended at its opposite end by a feed duct 51 for pressurized oil or other servo means for the operative control of the phase variator, with a branch directed through the structure B of the engine to a control valve 5.
- the cavity 41 houses a torsionally and axially preloaded, cylindrical, helical spring 45 made from a square-sectioned wire.
- One end 45a of the spring is restrained in a first seat 47 in the cover 17 and the opposite end 45b is housed with clearance in a second seat 48 in the hub 2.
- the spring 45 pushes against the half body 10 at one end and against the hub 2 at the other end to preload the surfaces 35 for mutual coupling.
- it produces a resilient force biasing the piston 6 towards the non-actuated position of Figure 1.
- the seat 48 is extended by a discharge hole 52 opening outside the hub 2 in a rebate 53 defined between the variator 1 and the structure B.
- one or more discharge holes 52 open in the hub 2 in positions other than in the seat 48 and, in this case, the dimensions of the seat need not allow for the clearance indicated above.
- a plurality of radial holes 54 is formed in the skirt of the hub 2 at its end disposed against the cover 17, for discharging oil by blowby downstream of the sets of teeth 25, 27.
- a valve 60 is provided between the feed duct 51 and a distribution and discharge duct 55 opening in the supply chamber 33.
- the valve 60 comprises a tubular body 61 bearing a base 64 at one end and screwed at the opposite end into a threaded seat 65 at the end of the feed duct 51 facing the cavity 41.
- An obturator 63 housed in the tubular body 61 is urged resiliently into abutment with a shoulder 67 of the feed duct 51 by a spring 66.
- the obturator 63 comprises a head 68 with a cylindrical skirt having a surface 69 which faces into the feed duct 51 and is therefore sensitive to the oil pressure supplied therein, as well as a rod 70 extending from the end opposite the surface 69 and bearing an enlarged, cylindrical guide portion 71.
- the rod 70 also serves to limit the travel of the obturator 63 by abutting the base 64, as will be explained further below.
- a plurality of discharge openings 72 is formed in the tubular body 61.
- the discharge holes 72 are arranged so as to put the distribution and discharge duct 55 into fluid communication with the cavity 41 when the head 68 is in abutment with the shoulder 67, closing the valve 60.
- control valve 5 is shut off and there is consequently an absence of appreciable oil pressure in the feed duct 51 and the head of the obturator 63 is disposed against the shoulder 67, closing the valve 60.
- the distribution and discharge duct 55 is in fluid communication with the cavity 41 through the discharge openings 72, that is, the chamber 33 is connected to the discharge by the hole 52.
- the pressurized oil is thus supplied through the duct 55 into the chamber 33 bringing about a movement of the piston 6 towards the actuated position with the opposition of the spring 45 ( Figure 2).
- the invention thus solves the problem set, achieving numerous advantages in comparison with known solutions.
- One advantage lies in the fact that the variator structure according to the invention achieves a faster return of the piston to the non-actuated position as a result of the direct discharge from the first chamber, avoiding the need to make the oil flow back along the feed duct and through the control valve of the variator.
- Another advantage is constituted by the fact that the valve for the alternative connection between the distribution and discharge duct and the feed duct or the discharge opening is piloted directly by the pressure detected in the feed duct without the need for other valve systems and/or branches of the hydraulic circuit.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Description
- The present invention relates to a single-acting phase variator according to the preamble to claim 1.
- These variators are used in internal combustion engines for changing the phase relationship between the camshaft and the engine shaft.
- These variators may be of the double-acting type, when two supply chambers are provided at the opposite axial ends of the piston and the piston is moved as a result of the admission of pressurized oil to one or other of the chambers.
- Single-acting variators, in which a single supply chamber is provided and the piston is moved towards an actuated position, against the action of a spring, by the hydraulic thrust generated thereon by the pressure of the oil admitted to the chamber, and is moved towards the opposite, non-actuated position, by the resilient thrust of the spring when the supply of oil to the chamber stops, are also known.
- A double acting phase variator is known from EP-A-0571023 to the same applicant.
- The present invention lies in particular in the technical field of single-acting phase variators.
- A single-acting phase variator having the features outlined above is known from FR 2657648.
- In these variators, in order to achieve rapid movement of the piston as a result of the hydraulic thrust of the oil, the spring must offer limited resilient resistance. On the other hand, the limited resilient loading of the spring involves the disadvantage of a low resilient thrust generated on the piston during its return stroke towards the non-actuated position when the oil is discharged from the supply chamber under the effect of the resilient load, with a consequent undesired slowing of the piston.
- Moreover, it should be borne in mind that the oil is normally discharged from the chamber through the supply duct or through a branch thereof. As a result, the discharged oil, which has to flow back along these ducts and through the control valve, offers considerable resistance to the return of the piston. This tends to slow the piston, particularly when the oil temperature is low.
- Compromise solutions are therefore sought but these penalize the performance of the variator both during the actuation stroke and during the return stroke towards the non-actuated position.
- The problem upon which the present invention is based is that of providing a phase variator which is designed structurally and functionally to allow the piston to move rapidly during the return stroke towards the non-actuated position, even with limited resilient loads.
- This problem is solved by the invention by means of a phase variator according to the appended claims.
- Further characteristics and advantages of the invention will become clearer from the following detailed description of a preferred embodiment thereof, described, by way of non-limiting example, with reference to the appended drawings, in which:
- Figures 1 and 2 are axial sections of a variator formed according to the present invention, in two different operative positions.
- A phase variator according to the invention, generally indicated 1 in the drawings, is intended to be interposed between a camshaft A of an internal combustion engine housed in a structural portion B of the engine, and a transmission, typically of the type with a toothed belt, of which a pulley C is shown, and which controls the timing mechanism of the engine.
- The phase variator 1 comprises a
hub 2 bearing a threadedshank 3 fixed to the camshaft A by a screw coupling. - An
annular piston 6 covers thehub 2, more precisely, a cylindrical portion thereof, so as to be slidable axially on the cylindrical portion of the hub. This portion hasaxial splines 7 jointly defining a set of straight teeth; in complementary manner, thepiston 6 has similarinternal splines 8 forming a set of straight teeth complementary to and meshing with thesplines 7. - The assembly constituted by the
hub 2 and thepiston 6 is surrounded by a body constituting a casing 9 of the variator. - The casing 9 is formed by two
half bodies half body 10 is sealingly engaged in thehalf body 11 by means of aseal 12a. - The
half body 11 has external threadedholes 14 for the fixing of the pulley C by means ofscrews 15 and is sealingly engaged on thehub 2 by means of aseal 11a. - The
half body 10 has a generallycylindrical skirt 16 closed at one axial end by acover 17 and open at the opposite end. Thecover 17 is prererably laser-welded to theskirt 16. Thecover 17 has a blind axial hole constituting aseat 18 housing and supporting thefree end 2a of thehub 2. - Two adjacent
cylindrical portions skirt 16 of thehalf body 10. - A set of
helical teeth 25 is formed in theportion 19. In complementary manner, the outside of thepiston 6 has afirst portion 26 carrying a set ofhelical teeth 27 meshed with theteeth 25; the piston also has asecond portion 28, the free end of which has aflange 29 extending radially outwardly and engaged sealingly with theportion 20 of theskirt 16 with the aid of apiston ring 30. - The
piston 6, together with thehub 2 and thehalf bodies - Braking means are provided between the
hub 2 and the casing 9. These means comprise aring 34 having a conical outer surface and a cylindrical inner surface and restrained axially on thehub 2. - The
half body 11 in turn has a conical inner surface in contact with the conical outer surface of thering 34; the conical coupling between the two conical surfaces of thering 34 and of thehalf body 11 is indicated 35. - The
ring 34 has peripheral recesses, indicated 36. - The
hub 2 has anaxial cavity 41 closed at one end by thecover 17 and extended at its opposite end by afeed duct 51 for pressurized oil or other servo means for the operative control of the phase variator, with a branch directed through the structure B of the engine to acontrol valve 5. - The
cavity 41 houses a torsionally and axially preloaded, cylindrical,helical spring 45 made from a square-sectioned wire. Oneend 45a of the spring is restrained in afirst seat 47 in thecover 17 and the opposite end 45b is housed with clearance in a second seat 48 in thehub 2. Thespring 45 pushes against thehalf body 10 at one end and against thehub 2 at the other end to preload thesurfaces 35 for mutual coupling. At the same time, owing to the torsional load on the sets of teeth, it produces a resilient force biasing thepiston 6 towards the non-actuated position of Figure 1. - The seat 48 is extended by a
discharge hole 52 opening outside thehub 2 in arebate 53 defined between the variator 1 and the structure B. - Alternatively, one or
more discharge holes 52 open in thehub 2 in positions other than in the seat 48 and, in this case, the dimensions of the seat need not allow for the clearance indicated above. - A plurality of
radial holes 54 is formed in the skirt of thehub 2 at its end disposed against thecover 17, for discharging oil by blowby downstream of the sets ofteeth - A
valve 60 is provided between thefeed duct 51 and a distribution anddischarge duct 55 opening in thesupply chamber 33. - The
valve 60 comprises a tubular body 61 bearing abase 64 at one end and screwed at the opposite end into a threadedseat 65 at the end of thefeed duct 51 facing thecavity 41. Anobturator 63 housed in the tubular body 61 is urged resiliently into abutment with a shoulder 67 of thefeed duct 51 by a spring 66. - The
obturator 63 comprises ahead 68 with a cylindrical skirt having asurface 69 which faces into thefeed duct 51 and is therefore sensitive to the oil pressure supplied therein, as well as arod 70 extending from the end opposite thesurface 69 and bearing an enlarged, cylindrical guide portion 71. Therod 70 also serves to limit the travel of theobturator 63 by abutting thebase 64, as will be explained further below. - A plurality of
discharge openings 72 is formed in the tubular body 61. - The
discharge holes 72 are arranged so as to put the distribution anddischarge duct 55 into fluid communication with thecavity 41 when thehead 68 is in abutment with the shoulder 67, closing thevalve 60. - The operation of the variator 1 will be described below, starting from a first, non-actuated operative condition, shown in Figure 1.
- In this condition, the
control valve 5 is shut off and there is consequently an absence of appreciable oil pressure in thefeed duct 51 and the head of theobturator 63 is disposed against the shoulder 67, closing thevalve 60. The distribution anddischarge duct 55 is in fluid communication with thecavity 41 through thedischarge openings 72, that is, thechamber 33 is connected to the discharge by thehole 52. - As a result of the operation of the
control valve 5, an oil pressure is established in thefeed duct 51 and produces a hydraulic thrust on thesurface 69 of thehead 68. When a predetermined threshold value is exceeded, and thus the hydraulic thrust exerted on thesurface 69 is greater than the resilient loading of the spring 66, theobturator 63 is moved towards thebase 64, bringing about a connection between thefeed duct 51 and the distribution anddischarge duct 55 and shutting off the previous connection between the distribution anddischarge duct 55 and thedischarge openings 72. - The pressurized oil is thus supplied through the
duct 55 into thechamber 33 bringing about a movement of thepiston 6 towards the actuated position with the opposition of the spring 45 (Figure 2). - When the supply of oil to the
feed duct 51 is shut off by the operative control of thevalve 5, the pressure in theduct 51 falls below the threshold value necessary to overcome the thrust of the spring 66 and theobturator 63 is consequently moved towards the shoulder 67 until it is disposed against thesurface 69 of thehead 68. - As a result of this movement, the distribution and
discharge duct 55 is reconnected to thedischarge openings 72 and, through these, to thecavity 41 and thedischarge hole 52, causing rapid and immediate discharge of the oil from thechamber 33. It will be noted that the oil is thus not forced to flow back along thefeed duct 51 and through thevalve 5, achieving the advantageous effect of a rapid return of thepiston 6 to the non-actuated position without the need for a large resilient loading of thespring 45. - The invention thus solves the problem set, achieving numerous advantages in comparison with known solutions.
- One advantage lies in the fact that the variator structure according to the invention achieves a faster return of the piston to the non-actuated position as a result of the direct discharge from the first chamber, avoiding the need to make the oil flow back along the feed duct and through the control valve of the variator.
- Another advantage is constituted by the fact that the valve for the alternative connection between the distribution and discharge duct and the feed duct or the discharge opening is piloted directly by the pressure detected in the feed duct without the need for other valve systems and/or branches of the hydraulic circuit.
Claims (4)
- A single-acting phase variator (1) comprising a casing (9), a hub (2) and a piston (6) jointly defining a supply chamber (33) for a pressurized servo means, resilient means (45) urging the piston (6) towards a non-actuated position, and a distribution and discharge duct (55) for the pressurized servo means, opening in the chamber (33), the piston (6) being moved towards an actuated position, under the effect of the servo means supplied to the chamber and with the opposition of the resilient means (45), valve means (60) being provided in the distribution and discharge duct (55) and being arranged to connect the duct alternatively to a feed duct (51) for the servo means or to a discharge opening (72) for the rapid discharge of the servo means from the chamber (33), characterized in that said valve means (60) comprise detector means (68) for detecting the pressure established in the feed duct (51) and obturator means (63) controlled by the detector means for connecting the distribution and discharge duct (55) to the discharge opening (72) when the pressure of the servo means detected in the feed duct (51) is below a predetermined threshold value and for connecting the distribution duct (55) to the feed duct (51) when the pressure of the servo means detected in the feed duct is above the threshold value.
- A phase variator according to Claim 1, in which the detector means comprise an obturator (63) guided for sliding in a valve (60), with the opposition of a spring (66) and subject to the pressure established in the feed duct (51).
- A phase variator according to Claim 2, in which the obturator means and the detector means are integrated in the obturator (63).
- A phase variator according to Claim 3, in which the valve means (60) comprise a tubular body (61) housing the obturator (63), the tubular body (61) being fixed in an axial seat of the hub (2) as an extension of the feed duct (51), the obturator comprising a head (68) bearing a surface (69) facing into the feed duct (51).
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19960201944 EP0818640B1 (en) | 1996-07-11 | 1996-07-11 | A phase variator |
DE1996611440 DE69611440T2 (en) | 1996-07-11 | 1996-07-11 | A phase adjustment device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19960201944 EP0818640B1 (en) | 1996-07-11 | 1996-07-11 | A phase variator |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0818640A1 EP0818640A1 (en) | 1998-01-14 |
EP0818640B1 true EP0818640B1 (en) | 2001-01-03 |
Family
ID=8224170
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19960201944 Expired - Lifetime EP0818640B1 (en) | 1996-07-11 | 1996-07-11 | A phase variator |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0818640B1 (en) |
DE (1) | DE69611440T2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4224944B2 (en) * | 2000-03-01 | 2009-02-18 | トヨタ自動車株式会社 | Valve timing control device for internal combustion engine |
DE10141213B4 (en) * | 2001-08-23 | 2008-11-20 | Bayerische Motoren Werke Aktiengesellschaft | Arrangement of a camshaft in the cylinder head of an internal combustion engine |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2760619B2 (en) * | 1990-01-30 | 1998-06-04 | 株式会社ユニシアジェックス | Valve timing control device for internal combustion engine |
IT1244112B (en) * | 1990-12-18 | 1994-07-05 | Goriziane Spa Off Mec | PERFECTED PHASE VARIATOR. |
IT1259099B (en) * | 1992-05-19 | 1996-03-11 | Carraro Spa | PHASE VARIATOR |
IT1271511B (en) * | 1993-10-06 | 1997-05-30 | Carraro Spa | PHASE VARIATOR BETWEEN THE CRANKSHAFT AND THE CAMSHAFT OF AN INTERNAL COMBUSTION ENGINE |
-
1996
- 1996-07-11 EP EP19960201944 patent/EP0818640B1/en not_active Expired - Lifetime
- 1996-07-11 DE DE1996611440 patent/DE69611440T2/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE69611440T2 (en) | 2001-08-23 |
EP0818640A1 (en) | 1998-01-14 |
DE69611440D1 (en) | 2001-02-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US5713319A (en) | Phase variator | |
US5645225A (en) | Variable injection hole type fuel injection nozzle | |
US4895113A (en) | Device for relative angular adjustment between two drivingly connected shafts | |
US4811698A (en) | Valve timing adjusting mechanism for internal combustion engine for adjusting timing of intake valve and/or exhaust valve corresponding to engine operating conditions | |
US5720684A (en) | Hydraulic tensioner with internal pressure relief | |
US5474038A (en) | Device for continuous automatic angular adjustment between two shafts in driving relationship | |
US5203290A (en) | Intake and/or exhaust-valve timing control sytem for internal combustion engine | |
US5170755A (en) | Valve opening and closing timing control apparatus | |
US8607823B2 (en) | Pressure control valve | |
US5271360A (en) | Valve opening and closing timing control apparatus | |
US4862843A (en) | Valve timing control device for use in internal combustion engine | |
JP2009534598A (en) | Chain or belt tensioner | |
KR0152373B1 (en) | Camshaft phase changing device | |
US5309873A (en) | Valve timing control system for internal combustion engine | |
US5263442A (en) | Valve timing control apparatus | |
US5209193A (en) | Intake- and/or exhaust-valve timing control system for internal combustion engines | |
US5197421A (en) | Valve timing control apparatus | |
US5201289A (en) | Valve timing control system for internal combustion engine | |
US5033327A (en) | Camshaft phasing drive with wedge actuators | |
GB2327737A (en) | Variable phase coupling | |
EP0818640B1 (en) | A phase variator | |
US5167206A (en) | Continuously variable valve timing control system | |
US5592910A (en) | Camshaft phase changing device | |
EP0492557B1 (en) | Valve timing control system of internal combustion engine | |
EP0818641B1 (en) | A phase variator |
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 |
|
17P | Request for examination filed |
Effective date: 19970524 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE ES FR GB |
|
AKX | Designation fees paid |
Free format text: DE ES FR GB |
|
RBV | Designated contracting states (corrected) |
Designated state(s): DE ES FR GB |
|
17Q | First examination report despatched |
Effective date: 19980929 |
|
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 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE ES FR GB |
|
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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20010103 Ref country code: ES Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY Effective date: 20010103 |
|
REF | Corresponds to: |
Ref document number: 69611440 Country of ref document: DE Date of ref document: 20010208 |
|
EN | Fr: translation not filed | ||
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: 20010711 |
|
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 | ||
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20010711 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20120730 Year of fee payment: 17 |
|
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: 20140201 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 69611440 Country of ref document: DE Effective date: 20140201 |